JP5494017B2 - Heat exchanger and heat pump water heater using the same - Google Patents
Heat exchanger and heat pump water heater using the same Download PDFInfo
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- JP5494017B2 JP5494017B2 JP2010045155A JP2010045155A JP5494017B2 JP 5494017 B2 JP5494017 B2 JP 5494017B2 JP 2010045155 A JP2010045155 A JP 2010045155A JP 2010045155 A JP2010045155 A JP 2010045155A JP 5494017 B2 JP5494017 B2 JP 5494017B2
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Description
本発明は、ヒートポンプ給湯機における熱交換器の構成に関するものである。 The present invention relates to a configuration of a heat exchanger in a heat pump water heater.
図７は、従来の水−冷媒熱交換器の局部断面図、図８は断面の詳細図である。 FIG. 7 is a local sectional view of a conventional water-refrigerant heat exchanger, and FIG. 8 is a detailed sectional view.
従来の水−冷媒熱交換器は、２本の中径管１１、１２を互いに密着させながら絡み合うように螺旋状にねじり合わせて構成する。 The conventional water-refrigerant heat exchanger is configured by twisting together two medium-diameter pipes 11 and 12 in a spiral shape so that they are intertwined with each other.
これにより、大径管１０内を流れる流体と中径管内を流れる流体は螺旋状に乱流化され、伝熱促進が図れ、熱交換効率の高い熱交換器がえられるというものである（例えば、特許文献１参照）。 As a result, the fluid flowing in the large-diameter pipe 10 and the fluid flowing in the medium-diameter pipe are turbulently spiraled, heat transfer is promoted, and a heat exchanger with high heat exchange efficiency is obtained (for example, , See Patent Document 1).
しかしながら、従来の構成では、大径管１０内に中径管１１、１２を挿入し、製造するため、図８において、大径管１０の内面と中径管１１、１２の外面の最接近する隙間部分１９は、隙間を確保する必要がある。 However, in the conventional configuration, the medium diameter pipes 11 and 12 are inserted into the large diameter pipe 10 and manufactured. Therefore, in FIG. 8, the inner surface of the large diameter pipe 10 and the outer surface of the medium diameter pipes 11 and 12 are closest to each other. The gap portion 19 needs to secure a gap.
特に、従来の構成は、中径管１１、１２の断面が略円形であるため、中径管１１、１２の断面積を大きくしすぎると、最接近する隙間部分１９が確保できず、大径管１０に中径管１１、１２を挿入することができず、製作不可になってしまうという課題を有していた。 Particularly, in the conventional configuration, since the cross sections of the medium diameter pipes 11 and 12 are substantially circular, if the cross sectional area of the medium diameter pipes 11 and 12 is excessively large, the closest gap portion 19 cannot be secured, and the large diameter pipes 11 and 12 are large. The medium-diameter pipes 11 and 12 cannot be inserted into the pipe 10, and there is a problem that the production becomes impossible.
また、最接近する隙間部分１９を確保すると、中径管１１、１２の断面積は大きくすることができず、大径管内の流体が流れる部分１７の断面積を減らすことができない。 Further, if the closest gap portion 19 is secured, the cross-sectional area of the medium-diameter pipes 11 and 12 cannot be increased, and the cross-sectional area of the part 17 through which the fluid flows in the large-diameter pipe cannot be reduced.
したがって、大径管内を流れる流体の流速を向上させることができず、熱伝達率に限界があり、能力を向上させることができないという課題を有していた。 Therefore, the flow velocity of the fluid flowing in the large-diameter pipe cannot be improved, and there is a problem that the heat transfer rate is limited and the capacity cannot be improved.
本発明は、前記従来の課題を解決するもので、熱交換性能に優れた熱交換器を提供することを目的とする。 This invention solves the said conventional subject, and it aims at providing the heat exchanger excellent in heat exchange performance.
前記従来の課題を解決するために、本発明の熱交換器は、１次流体が流れる配管と、２次流体が流れる配管と、を備え、前記２次流体が流れる配管は複数本で、かつ、前記１次流体が流れる前記配管内に配設されるとともに、前記２次流体が流れる前記配管の長手方向の軸に対する直角断面が、楕円形状であり、前記２次流体が流れる前記配管の外表面に多数の凹みを設け、多数の前記凹みの深さは、短径方向の凹みより長径方向の凹みの方が深いことを特徴とするもので、１次流体が流れる配管と前記２次流体が流れる配管との隙間を確保しながら、前記２次流体が流れる配管の断面積を大きくすることができるため、前記２次流体が流れる配管の内表面積及び外表面積を大きくすることができ、前記２次流体が流れる配管の伝熱性能を向上させることができる。 In order to solve the conventional problem, the heat exchanger according to the present invention includes a pipe through which a primary fluid flows and a pipe through which a secondary fluid flows, and a plurality of pipes through which the secondary fluid flows, and the with the primary fluid is arranged in said pipe flows, cross section perpendicular with respect to the longitudinal axis of the pipe where the secondary fluid flows, elliptical der is, of the pipe in which the secondary fluid flows A plurality of recesses are provided on the outer surface, and the depth of the plurality of recesses is characterized in that the recesses in the major axis direction are deeper than the recesses in the minor axis direction. Since the cross-sectional area of the pipe through which the secondary fluid flows can be increased while ensuring a gap with the pipe through which the fluid flows, the inner surface area and the outer surface area of the pipe through which the secondary fluid flows can be increased, Improve heat transfer performance of piping through which the secondary fluid flows It can be.
本発明によれば、熱交換性能に優れた熱交換器を提供できる。 According to the present invention, a heat exchanger excellent in heat exchange performance can be provided.
第１の発明は、１次流体が流れる配管と、２次流体が流れる配管と、を備え、前記２次流体が流れる配管は複数本で、かつ、前記１次流体が流れる前記配管内に配設されるとともに、前記２次流体が流れる前記配管の長手方向の軸に対する直角断面が、楕円形状であり、前記２次流体が流れる前記配管の外表面に多数の凹みを設け、多数の前記凹みの深さは、短径方向の凹みより長径方向の凹みの方が深いことを特徴とする熱交換器で、１次流体が流れる配管と前記２次流体が流れる配管との隙間を確保しながら、前記２次流体が流れる配管の断面積を大きくすることができるため、前記２次流体が流れる配管の内表面積及び外表面積を大きくすることができ、前記２次流体が流れる配管の伝熱性能を向上させることができる。 A first aspect of the present invention is a piping primary fluid flows, and a piping secondary fluid flows, in pipe plurality of the secondary fluid flows, and distribution within said pipe the primary fluid flows while being set, provided cross section perpendicular with respect to the longitudinal axis of the pipe where the secondary fluid flows, Ri elliptical der, a large number of depressions on the outer surface of the pipe in which the secondary fluid flows, said number of said The depth of the recess is a heat exchanger characterized in that the recess in the major axis direction is deeper than the recess in the minor axis direction, and a clearance between the pipe through which the primary fluid flows and the pipe through which the secondary fluid flows is secured. However, since the cross-sectional area of the pipe through which the secondary fluid flows can be increased, the inner surface area and the outer surface area of the pipe through which the secondary fluid flows can be increased, and the heat transfer of the pipe through which the secondary fluid flows. Performance can be improved.
また、２次流体が流れる配管の外表面に多数の凹みを設けたことを特徴とするもので、２次流体が流れる配管表面を流れる流体の流れを乱流にすることができ、伝熱性能を向上させることができ、熱交換器の効率を向上させることができる。また、２次流体が流れる配管の外表面に設けた凹みの深さは、短径方向の凹みより長径方向の凹みの方が深いことを特徴とするもので、２次流体が流れる配管内を通る流体の圧力損失の増加を抑制しながら、２次流体が流れる配管の外表面の熱伝達率の向上を図ることができる。 Further, characterized in that provided with a plurality of depressions in piping external surface of the secondary fluid flows, can be fluid flow through the piping surface the secondary fluid flows turbulent, Den Thermal performance can be improved and the efficiency of the heat exchanger can be improved. The depth of the recess is provided on the outer surface of the piping which secondary fluid flows, it better than in the minor axis direction indentations major axis depressions deeper characterized in, the pipe of the secondary fluid flows The heat transfer coefficient of the outer surface of the pipe through which the secondary fluid flows can be improved while suppressing an increase in pressure loss of the fluid passing through the pipe.
第２の発明は、前記１次流体が流れる前記配管を大径菅とし、前記２次流体が流れる前記配管は、小径菅と前記小径管の外周に密着させた中径管とを有し、複数本の前記２次流体が流れる前記配管は、互いに螺旋状にねじり合わせて構成され、複数本の前記２次流体が流れる前記配管が挿入される前記大径管の内径が、複数本の前記２次流体が流れる前記配管の長径の合計よりも小さいことを特徴とするもので、中径管を軸直角の断面が楕円形状に変形させ、複数本の中径管をねじり合わせることで、中径管の表面積を最大限に大きくした状態で、大径管に挿入することできる。 The second invention, the pipes in which the primary fluid flows to a large径菅, the pipe in which the secondary fluid flows, possess a diameter pipes in which in close contact with the outer periphery of the smaller diameter but smaller diameter tube, the pipe in which a plurality of the secondary fluid flows, is configured for twisting spirally together, the inner diameter of the large diameter tube to the pipe a plurality of the secondary fluid flows is inserted, a plurality of It is characterized by being smaller than the sum of the major diameters of the pipes through which the secondary fluid flows , by deforming the medium diameter pipe into an elliptical cross section perpendicular to the axis, and twisting a plurality of medium diameter pipes together, The medium diameter tube can be inserted into a large diameter tube with the surface area maximized.
また、複数の中径管を絡み合うようにねじり合わせる際に、楕円管の短径方向に潰れる力が加わっても、短径方向の凹みを深くすることで、強度を確保することができ、中径管が潰れて小径管の流路を閉塞することなく加工できる。 In addition, when twisting a plurality of medium-diameter pipes so as to be entangled, even if a force that crushes in the short-diameter direction of the elliptical pipe is applied, the strength can be ensured by deepening the dent in the short-diameter direction. Processing can be performed without crushing the diameter pipe and closing the flow path of the small diameter pipe.
また、凹みを深くすることで、さらに乱流促進を図ることができ、ねじりによる乱流促進を活かすことができ、熱伝達率を向上させることができる。 Further, by deepening the dent, turbulent flow can be further promoted, turbulent flow promotion by twisting can be utilized, and the heat transfer rate can be improved.
第３の発明は、水出口付近の大径管の内径が、水入口付近の大径管の内径より大きくすることで、高温で析出しやすいスケールが付着しても詰まりにくく、長時間の使用に耐えることができる。 The third aspect of the invention is that the inner diameter of the large-diameter pipe near the water outlet is larger than the inner diameter of the large-diameter pipe near the water inlet, so that even if a scale that is likely to precipitate at high temperature adheres, it will not clog and can be used for a long time. Can withstand.
第４の発明は、第１〜３のいずれかの発明の熱交換器を備えたヒートポンプ給湯機で、高効率のヒートポンプ給湯機を提供できる。 4th invention is a heat pump water heater provided with the heat exchanger of any one of 1st-3rd invention, and can provide a highly efficient heat pump water heater.
以下、本発明の実施の形態について、図面を参照しながら説明する。なお、この実施の形態によって本発明が限定されるものではない。 Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the present invention is not limited to the embodiments.
（実施の形態１）
本発明の第１の実施の形態について、図１〜図３を用いて説明する。図１は平面図、図２は側面図、図３は、Ａ−Ａ断面での断面図である。
(Embodiment 1)
A first embodiment of the present invention will be described with reference to FIGS. 1 is a plan view, FIG. 2 is a side view, and FIG. 3 is a cross-sectional view taken along the line AA.
図１、図２において、１００は水冷媒熱交換器、１０１、１０２は大径管、１９３は冷媒側入口、１９４は冷媒側の出口、１９１は水側の入口、１９２は水側の出口である。また、Ａは大径管１０１と大径管１０２の接続部である。 1 and 2, 100 is a water refrigerant heat exchanger, 101 and 102 are large diameter pipes, 193 is a refrigerant side inlet, 194 is a refrigerant side outlet, 191 is a water side inlet, and 192 is a water side outlet. is there. A is a connecting portion between the large diameter tube 101 and the large diameter tube 102.
図３において、１１１は中径管、１１２は小径管、Ｄ１は中径管１１１の長径、Ｄ２は中径管１１１の短径、１５１は水流路、１５２は冷媒流路、１３０は２本の中径管１１１に外接する円を示す。 In FIG. 3, 111 is a medium diameter pipe, 112 is a small diameter pipe, D1 is a long diameter of the medium diameter pipe 111, D2 is a short diameter of the medium diameter pipe 111, 151 is a water flow path, 152 is a refrigerant flow path, and 130 is two pipes. A circle circumscribing the medium diameter pipe 111 is shown.
以上のように構成された水冷媒熱交換器について、以下の動作、作用を説明する。 The following operation | movement and effect | action are demonstrated about the water refrigerant | coolant heat exchanger comprised as mentioned above.
図１、図２において、１次流体である低温の水は、水入口１９１から流入し、大径管１０１、１０２内を通り、水出口１９２より流出する。 In FIG. 1 and FIG. 2, low-temperature water, which is the primary fluid, flows from the water inlet 191, passes through the large-diameter pipes 101 and 102, and flows out from the water outlet 192.
一方、２次流体である冷媒（例えば、二酸化炭素）は、ヒートポンプサイクル（図示せず）にて加熱された高温の冷媒が、冷媒入口１９３から流入し、大径管１０１、１０２に挿入された小径管１１２内を通り、冷媒出口１９４より流出する。大径管１０１と１０２とは、接続部Ａで接続されており、大径管１０２の内径は、大径管１０１の内径より大きい管で構成されている。なお、この水冷媒熱交換器にて生成されたお湯が、例えば、床暖房や給湯等に利用される。 On the other hand, as a secondary fluid refrigerant (for example, carbon dioxide), a high-temperature refrigerant heated by a heat pump cycle (not shown) flows from the refrigerant inlet 193 and is inserted into the large-diameter pipes 101 and 102. It passes through the small diameter pipe 112 and flows out from the refrigerant outlet 194. The large-diameter pipes 101 and 102 are connected by a connection portion A, and the large-diameter pipe 102 has an inner diameter larger than that of the large-diameter pipe 101. In addition, the hot water produced | generated with this water refrigerant | coolant heat exchanger is utilized for floor heating, hot water supply, etc., for example.
図３において、中径管１１１と小径管１１２とは、その断面が長径Ｄ１と短径Ｄ２からなる楕円形で形成されている。大径管１０１、１０２内を流れる低温の流体は流路１５１を通り、また、小径管１１２内を流れる高温の流体は流路１５２を通る。 In FIG. 3, the medium diameter pipe 111 and the small diameter pipe 112 are formed in an elliptical shape with a cross section consisting of a long diameter D1 and a short diameter D2. The low temperature fluid flowing in the large diameter pipes 101 and 102 passes through the flow path 151, and the high temperature fluid flowing in the small diameter pipe 112 passes through the flow path 152.
中径管１１１を楕円にすることは、２本の中径管１１１に外接する円の直径１３０を維持しながら、言い換えると、大径管１０１との隙間を確保しながら、短径Ｄ２より長径Ｄ１を長くすることができ、その分、中径管１１１の断面積を大きくすることができる。 Making the middle-diameter pipe 111 into an ellipse means that the diameter of the circle circumscribing the two middle-diameter pipes 111 is maintained, in other words, a larger diameter than the short diameter D2 while ensuring a gap with the large-diameter pipe 101. D1 can be lengthened, and the cross-sectional area of the medium diameter tube 111 can be increased accordingly.
これにより、小径管１１２の内表面積及び中径管１１１の外表面積を大きくすることができ、小径管内面の伝熱性能及び中径管外面の伝熱性能を向上させることができる。 Thereby, the inner surface area of the small diameter tube 112 and the outer surface area of the medium diameter tube 111 can be increased, and the heat transfer performance of the inner surface of the small diameter tube and the heat transfer performance of the outer surface of the medium diameter tube can be improved.
また、小径管１１２の断面積を大きくできることで、小径管１１２内を流れる高温の流体の流速を遅くでき、圧力損失を低減でき、伝熱性能を向上させることができる。 In addition, since the cross-sectional area of the small-diameter pipe 112 can be increased, the flow rate of the high-temperature fluid flowing through the small-diameter pipe 112 can be slowed, pressure loss can be reduced, and heat transfer performance can be improved.
また、大径管１０１内を流れる低温の流体の流路１５１を小さくすることができ、流速を増大させることが可能となり、中径管１１１の外表面の熱伝達率を向上させることができる。 Further, the flow path 151 of the low-temperature fluid flowing in the large-diameter pipe 101 can be reduced, the flow velocity can be increased, and the heat transfer coefficient of the outer surface of the medium-diameter pipe 111 can be improved.
また、大径管１０１の内径より大径管１０２の内径を大きくすることは次のような効果を可能とする。低温の水は、水入口１９１から入り、小径管内を通る高温の流体と熱交換
しながら徐々に温度が上昇し、水出口１９２付近ではかなりの高温になる。水が高温になると、低温では溶け込むことができたスケール成分（例えば、カルシウムやマグネシウムなど）は、高温では固体となって析出してしまう。
Further, making the inner diameter of the large diameter tube 102 larger than the inner diameter of the large diameter tube 101 enables the following effects. Low-temperature water enters from the water inlet 191 and gradually increases in temperature while exchanging heat with the high-temperature fluid passing through the small-diameter pipe, and reaches a considerably high temperature in the vicinity of the water outlet 192. When water becomes high temperature, the scale components (for example, calcium and magnesium) that can be dissolved at low temperature become solid and precipitate at high temperature.
析出したスケールは、中径管１１１の外表面や大径管１０２の内表面に付着し、水が通過する際の圧力損失を増大させてしまう。ここで、大径管１０１の内径よりも高温部に使用する水管の内径を大きくした大径管１０２を用いることで、スケールが多少付着しても圧力損失の急激な上昇を抑制でき、長期間の使用に耐える水冷媒熱交換器を有することができる。 The deposited scale adheres to the outer surface of the medium-diameter tube 111 and the inner surface of the large-diameter tube 102, and increases the pressure loss when water passes. Here, by using the large-diameter pipe 102 in which the inner diameter of the water pipe used in the high-temperature part is larger than the inner diameter of the large-diameter pipe 101, a rapid increase in pressure loss can be suppressed even if some scale is attached. Can have a water-refrigerant heat exchanger that can withstand the use of
（実施の形態２）
本発明の第２の実施の形態について、図４〜図６を用いて説明する。第２の実施の形態は、実施の形態１で説明した中径管の表面に凹みを設けたことを特徴とし、その凹みが短径側の凹みより、長径側の凹みを深くしたことを特徴とするものである。
(Embodiment 2)
A second embodiment of the present invention will be described with reference to FIGS. The second embodiment is characterized in that a recess is provided on the surface of the medium-diameter tube described in the first embodiment, and the recess has a deeper recess on the longer diameter side than the recess on the shorter diameter side. It is what.
図４〜図６において、図４は中径管の中心軸に直角方向の断面図、図５は図４を９０度回転した中径管の断面図、図６は中径管の中心軸上で分割した断面の詳細図を示す。 4 to 6, FIG. 4 is a cross-sectional view perpendicular to the central axis of the medium-diameter tube, FIG. 5 is a cross-sectional view of the medium-diameter tube rotated 90 degrees from FIG. 4, and FIG. The detailed drawing of the cross section divided | segmented by is shown.
図４、図５において、１１１は中径管、１１２は小径管、１５２は小径管内を流れる低温の流体の流路、１３１は長径方向に設けた凹み、１３２は短径方向に設けた凹み、Ｈ１は長径方向の凹みの深さ、Ｈ２は短径方向の凹みの深さ、１４１は短径方向に加わる力を示す。図６において、２本の中径管１１１をねじり合わせ、大径管１０１内に挿入した状態を示す。 4 and 5, 111 is a medium-diameter pipe, 112 is a small-diameter pipe, 152 is a flow path of a low-temperature fluid flowing in the small-diameter pipe, 131 is a depression provided in the major axis direction, 132 is a depression provided in the minor axis direction, H1 is the depth of the recess in the major axis direction, H2 is the depth of the recess in the minor axis direction, and 141 is the force applied in the minor axis direction. FIG. 6 shows a state in which two medium-diameter pipes 111 are twisted and inserted into the large-diameter pipe 101.
以上のように構成された水冷媒熱交換器について、以下の動作、作用を説明する。 The following operation | movement and effect | action are demonstrated about the water refrigerant | coolant heat exchanger comprised as mentioned above.
図４、５において、中径管１１１の表面には、凹み１３１と１３２があり、凹み１３１は長径方向に設けた凹みで、深さＨ１を有しており、凹み１３２は短径方向に設けた凹みで、深さＨ２を有している。この深さは、短径方向の凹みの深さＨ２より、長径方向の凹みの深さＨ１を大きくしている。 4 and 5, the surface of the medium-diameter pipe 111 has dents 131 and 132. The dent 131 is a dent provided in the major axis direction and has a depth H1, and the dent 132 is provided in the minor axis direction. It is a dent and has a depth H2. This depth is greater than the depth H2 of the recess in the minor axis direction, and the depth H1 of the recess in the major axis direction.
ここで、図６に示すような中径管をねじり合わせる加工を施した際に、短径方向の力１４１が生じ、中径管１１１はつぶれようとするが、Ｈ１の深さが深いことで短径方向の力１４１が加わっても耐えることができ、つぶれることなく所定の小径管内の流路１５２を確保しながら、製造が可能となる。 Here, when the process of twisting the medium diameter pipes as shown in FIG. 6 is performed, a force 141 in the short diameter direction is generated, and the medium diameter pipe 111 tends to collapse, but the depth of H1 is deep. Even if the force 141 in the short diameter direction is applied, it can endure and can be manufactured while securing the flow path 152 in a predetermined small diameter pipe without being crushed.
また、長径方向の凹みの深さＨ１を深くすることで、小径管１１２内を通る流体の圧力損失の増加を抑制しながら、中径管の外表面の熱伝達率の向上を図ることができる。 Further, by increasing the depth H1 of the recess in the long diameter direction, it is possible to improve the heat transfer coefficient of the outer surface of the medium diameter pipe while suppressing an increase in pressure loss of the fluid passing through the small diameter pipe 112. .
以上のように、本発明に係る熱交換器は、ヒートポンプサイクルと給湯サイクルが一体に構成された一体型ヒートポンプ給湯機、別体に構成された分離型ヒートポンプ給湯機、給湯用熱交換器で加熱したお湯をそのまま出湯できる直接出湯型ヒートポンプ給湯機などの各種ヒートポンプ給湯機の水―冷媒熱交換器に適用でき、給湯機能のほかに、浴槽給湯、暖房機能、乾燥機能を有するヒートポンプ装置にも適用できる。 As described above, the heat exchanger according to the present invention is heated by an integrated heat pump water heater in which a heat pump cycle and a hot water supply cycle are integrated, a separate heat pump water heater configured separately, and a heat exchanger for hot water supply. It can be applied to water-refrigerant heat exchangers of various heat pump water heaters such as direct hot water heat pump water heaters that can discharge hot water as it is. it can.
１００ 水冷媒熱交換器
１０１、１０２ 大径管
１１１ 中径管
１１２ 小径管
１２１ 水入口管
１２２ 水出口管
１３１ 冷媒入口管
１３２ 冷媒出口管
１４１ 中径管が短径方向に受ける力
１５１ 大径管内を流れる流体の流路
１５２ 小径管内を流れる流体の流路
１９１、１９２ 水の流れ方向
１９３、１９４ 冷媒の流れ方向
Ｄ１ 長径
Ｄ２ 短径
Ｈ１、Ｈ２ 凹みの深さ
DESCRIPTION OF SYMBOLS 100 Water refrigerant | coolant heat exchanger 101,102 Large diameter pipe 111 Medium diameter pipe 112 Small diameter pipe 121 Water inlet pipe 122 Water outlet pipe 131 Refrigerant inlet pipe 132 Refrigerant outlet pipe 141 The force which a medium diameter pipe receives to a short diameter direction 151 In large diameter pipe Fluid flow path 152 Fluid flow path in small diameter pipes 191, 192 Water flow direction 193, 194 Refrigerant flow direction D1 Long diameter D2 Short diameter H1, H2 Depth of recess
Claims (4)
２次流体が流れる配管と、を備え、
前記２次流体が流れる配管は複数本で、かつ、前記１次流体が流れる前記配管内に配設されるとともに、
前記２次流体が流れる前記配管の長手方向の軸に対する直角断面が、楕円形状であり、
前記２次流体が流れる前記配管の外表面に多数の凹みを設け、
多数の前記凹みの深さは、短径方向の凹みより長径方向の凹みの方が深いことを特徴とする熱交換器。 Piping through which the primary fluid flows;
A pipe through which a secondary fluid flows,
In piping plurality of the secondary fluid flows, and, while being disposed in said pipe the primary fluid flows,
Section perpendicular relative to the longitudinal axis of the pipe where the secondary fluid flows, Ri elliptical der,
A number of depressions are provided on the outer surface of the pipe through which the secondary fluid flows,
The depth of a large number of the recesses is such that the recesses in the major axis direction are deeper than the recesses in the minor axis direction .
前記２次流体が流れる前記配管は、小径菅と前記小径管の外周に密着させた中径管とを有し、
複数本の前記２次流体が流れる前記配管は、互いに螺旋状にねじり合わせて構成され、
複数本の前記２次流体が流れる前記配管が挿入される前記大径管の内径が、複数本の前記２次流体が流れる前記配管の長径の合計よりも小さいことを特徴とする請求項１に記載の熱交換器。 The pipe the primary fluid flows to a large径菅,
Wherein the secondary fluid flows piping possess a diameter pipes in which in close contact with the outer periphery of the small diameter but with the small diameter tube,
The pipe plurality of the secondary fluid flows are configured for twisting spirally with each other,
Claim the pipe which a plurality of the secondary fluid flows the inner diameter of the large diameter tube to be inserted may be smaller than the sum of the major diameter of the pipe a plurality of the secondary fluid flows 1 The heat exchanger as described in.
The heat pump water heater provided with the heat exchanger of any one of the said Claims 1-3 .
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| JP4063237B2 (en) * | 2004-04-06 | 2008-03-19 | 松下電器産業株式会社 | Heat exchange device and heat pump water heater using the same |
| JP2009264644A (en) * | 2008-04-24 | 2009-11-12 | Panasonic Corp | Heat exchanger |
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