JP2006112734A

JP2006112734A - Storage-type heat exchanger

Info

Publication number: JP2006112734A
Application number: JP2004301705A
Authority: JP
Inventors: Isao Fujinami; 功藤波; Nariyuki Takaoka; 成幸高岡; Yasunari Okamoto; 康令岡本
Original assignee: Daikin Industries Ltd
Current assignee: Daikin Industries Ltd
Priority date: 2004-10-15
Filing date: 2004-10-15
Publication date: 2006-04-27

Abstract

<P>PROBLEM TO BE SOLVED: To provide a storage-type heat exchanger capable of equalizing a distribution of ice water and a distribution of a temperature caused by the melting of a sensible-heat storage material in air cooling, and obtaining a stable heat exchanging quantity for a specific time or longer. <P>SOLUTION: In this storage-type heat exchanger wherein a heat transfer tube where a refrigerant passes is composed of synthetic resin small-diameter tubes 2a, 2b, a number of the small-diameter tubes 2a, 2b are arranged at prescribed intervals to constitute a heat exchanger 2, and the heat exchanger 2 is stored in a heat storage container 1 having the sensible-heat storage material, a refrigerant flow rate variable means for adjusting a refrigerant inflow rate by changing a cross-sectional area of the small-diameter tube 2a or 2b is mounted at the refrigerant inlet side of the small-diameter tube 2a or 2b forming a air cooling circuit. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本願発明は、放冷時における冷媒流量調節機能を備えた蓄熱熱交換器に関するものである。 The present invention relates to a heat storage heat exchanger having a refrigerant flow rate adjustment function during cooling.

従来から、例えば蓄熱槽内に固相と液相に相変化する潜熱蓄熱材を収容し、固相状態の潜熱蓄熱材を融解することによって蓄熱する一方、利用時には外部からの冷媒で同潜熱蓄熱材を凝固させることによって熱を取り出すフィンチューブ式の蓄熱熱交換器は良く知られている（例えば特許文献１参照）。 Conventionally, for example, a latent heat storage material that changes phase between a solid phase and a liquid phase is accommodated in a heat storage tank, and heat is stored by melting the solid phase latent heat storage material. Fin tube type heat storage heat exchangers that extract heat by solidifying a material are well known (see, for example, Patent Document 1).

この蓄熱熱交換器は、潜熱蓄熱材を用いているために、水などの顕熱蓄熱材に比べて蓄熱密度は高いが、他方熱伝達率が低く、特に水の対流熱伝達のように大きな熱伝達率を得ることが困難である。 Since this heat storage heat exchanger uses a latent heat storage material, the heat storage density is higher than that of sensible heat storage materials such as water, but on the other hand, the heat transfer coefficient is low, especially as large as convective heat transfer of water. It is difficult to obtain a heat transfer coefficient.

また、フィンチューブ式の熱交換器では、フィンカラーがあるために、例えばフィンピッチを１．２ｍｍ以下に縮小することが困難で、単位体積当たりの伝熱面積も１６７０ｍ²／ｍ³以下と小さく、フィン効率やフィンと伝熱管との間の接触抵抗などから、形状的、構造的にも放熱時における熱の取出スピードを向上させるには一定の限界がある。 Further, since the fin tube type heat exchanger has a fin collar, it is difficult to reduce the fin pitch to 1.2 mm or less, for example, and the heat transfer area per unit volume is as small as 1670 m ² / m ³ or less. From the viewpoint of fin efficiency and contact resistance between the fin and the heat transfer tube, there is a certain limit to improving the heat extraction speed during heat radiation in terms of shape and structure.

さらに、フィンチューブ式の熱交換器には、その管板外部に曲がり管部がある。そして、この曲がり管部分にはフィンがないため、蓄熱も放熱もできない。そのため同領域における５〜１０％程度の蓄熱材が無駄になっている（有効に使えない）。 Furthermore, the fin tube type heat exchanger has a bent tube portion outside the tube plate. And since this bending pipe part does not have a fin, neither heat storage nor heat dissipation is possible. Therefore, about 5 to 10% of the heat storage material in the same area is wasted (cannot be used effectively).

また、蓄熱時の冷媒配管と放熱（利用）時の冷媒配管とが異なる構成の場合にフィンチューブ式熱交換器を用いると、伝熱管とフィンとの距離が長くなって、フィン効率が大幅に低下する。 Also, if the finned tube heat exchanger is used when the refrigerant piping at the time of heat storage and the refrigerant piping at the time of heat dissipation (use) are different, the distance between the heat transfer tube and the fin becomes long, and the fin efficiency is greatly increased. descend.

そこで、本願発明者等は、このような事情に鑑み、上記フィンチューブに変えて合成樹脂製の細径管を用い、それら細径管を蓄熱容器内に平行又はクロス構造にして配設することにより、伝熱管密度の高い細径多管構造の蓄熱熱交換器を形成することによって、水などの顕熱蓄熱材を用いた場合にも、蓄熱材中における蓄熱密度および熱伝達率が高く、放冷時の熱の取出速度を有効に向上させた蓄熱熱交換器を提案している（特許文献２参照）。 Therefore, in view of such circumstances, the inventors of the present application use thin tubes made of synthetic resin instead of the fin tubes, and arrange these thin tubes in a heat storage container in a parallel or cross structure. By forming a heat storage heat exchanger with a small-diameter multi-tube structure with a high heat transfer tube density, even when using a sensible heat storage material such as water, the heat storage density and heat transfer coefficient in the heat storage material are high, A heat storage heat exchanger in which the heat extraction speed during cooling is effectively improved has been proposed (see Patent Document 2).

特開２００１−２０７１６３号公報（明細書第１−９頁、図３−７）Japanese Patent Laid-Open No. 2001-207163 (Specification, page 1-9, FIG. 3-7) 特開２００４−１０５８４号公報（明細書第１−９頁、図５−７）Japanese Patent Laying-Open No. 2004-1058 (Specification, page 1-9, FIG. 5-7)

ところで、このような水などの顕熱蓄熱材に適した細径多管構造の蓄熱熱交換器において、蓄熱材を氷結化することにより蓄熱した熱を放冷する際に、放冷開始時は放冷回路を形成している細径管周りの氷が解けて有効な（あるいは過剰な）熱交換量を出すものの、放冷時間の経過とともに氷の量が減少することから、次第に熱交換量は低下し、長時間に亘って安定した熱交換量を得ることが難しい。 By the way, in the heat storage heat exchanger with a small-diameter multi-tubular structure suitable for such sensible heat storage materials such as water, when cooling the heat stored by freezing the heat storage material, Although the ice around the small-diameter tube forming the cooling circuit is melted and an effective (or excessive) heat exchange amount is produced, the amount of ice gradually decreases as the cooling time elapses. It is difficult to obtain a stable heat exchange amount for a long time.

また構造上、放冷回路入口側で細径管に近いものは解けやすいが、放冷回路出口側で細径管から遠いものは解けにくい、という氷融解状態のアンバランスが生じる。 Also, due to the structure, there is an imbalance in the ice-melted state that the one close to the small diameter tube on the inlet side of the cooling circuit is easy to unravel, but the one far from the small diameter tube on the outlet side of the cooling circuit is difficult to unravel.

このような問題に対する対策として、例えば図５に示すように、冷媒供給管３０から冷媒入口ヘッダ３１を介して各放冷用細径管（パス部）２ａ，２ａ・・・に分配供給される放冷用の冷媒（流体）の流入量を同多数本の細径管２ａ，２ａ・・・各々の入口部で調節し得るように、多数の開閉制御弁Ｖ₁〜Ｖｎを設けるとともに、さらに冷媒の入口側ヘッダ３１と出口側ヘッダ３２とをストレートに結ぶバイパス通路ＢＰを設け、各開閉制御弁Ｖ₁〜Ｖｎによって放冷用の各細径管２ａ，２ａ・・・へ供給される冷媒の一部をバイパス通路ＢＰを介して出口側ヘッダ３２から冷媒排出管３５にバイパスさせることにより、冷媒流入量を所望の量に制限して、一定時間以上安定した放冷能力を維持させる方法が考えられる。 As a countermeasure against such a problem, for example, as shown in FIG. 5, it is distributed and supplied from the refrigerant supply pipe 30 to each of the cooling-use small diameter pipes (pass portions) 2a, 2a,. A number of open / close control valves V _{1 to} Vn are provided so that the inflow amount of the refrigerant (fluid) for cooling can be adjusted at the inlets of the plurality of small-diameter pipes 2a, 2a. A bypass passage BP that straightly connects the inlet header 31 and the outlet header 32 of the refrigerant is provided, and the refrigerant supplied to the small-diameter tubes 2a, 2a,... For cooling by the open / close control valves V _{1 to} Vn. Is a method in which a part of the refrigerant is bypassed from the outlet side header 32 to the refrigerant discharge pipe 35 via the bypass passage BP, thereby limiting the refrigerant inflow amount to a desired amount and maintaining a stable cooling capacity for a predetermined time or more. Conceivable.

このような構成によれば、放冷能力のセーブを図ることができるとともに、熱交部全体に亘って氷水分布および温度分布を可能な限り均一化し、一定時間以上安定した熱交換量が得られるようになる。 According to such a configuration, it is possible to save the cooling capacity, make the ice water distribution and the temperature distribution as uniform as possible over the entire heat exchanger, and obtain a stable heat exchange amount over a predetermined time. It becomes like this.

しかし、現実問題として、合成樹脂製で、しかも管径の極めて小さい多数本の細径管２ａ，２ａ・・・の各々に、図５のように微細かつ精密な開閉制御弁Ｖ₁〜Ｖｎを設けることは不可能に近いし、その通路径の狭さを考えると、弁体内でゴミ等が詰まりやすく、信頼性の点でも問題が多い。また、多数の開閉制御弁Ｖ₁〜Ｖｎを開閉制御するのは、開閉制御自体も大変である。 However, as a real problem, fine and precise open / close control valves V _{1 to} Vn as shown in FIG. 5 are provided on each of a large number of small diameter pipes 2 a, 2 a. It is almost impossible to provide it, and considering the narrow passage diameter, dust and the like are easily clogged in the valve body, and there are many problems in terms of reliability. In addition, opening / closing control of the large number of opening / closing control valves V _{1 to} Vn is also difficult.

そこで、本願発明では、このような事情に鑑み、放冷回路を形成している細径管そのものの通路断面積を変えることにより、簡単かつ確実に放冷時における放冷回路側細径管への冷媒流入量を調節できるようにすることによって、放冷能力のセーブを図るとともに、熱交部全体に亘って氷水分布および温度分布を可能な限り均一化し、一定時間以上安定した熱交換量が得られるようにした蓄熱熱交換器を提供することを目的とするものである。 Therefore, in the present invention, in view of such circumstances, by changing the passage cross-sectional area of the small-diameter tube itself forming the cooling circuit, the cooling circuit side small-diameter tube can be easily and reliably cooled. By adjusting the refrigerant inflow rate, the cooling capacity can be saved, and the ice water distribution and temperature distribution can be made as uniform as possible over the entire heat exchanger, ensuring a stable amount of heat exchange over a certain period of time. An object of the present invention is to provide a heat storage heat exchanger that can be obtained.

本願発明は、上記の目的を達成するために、次のような課題解決手段を備えて構成されている。 In order to achieve the above object, the present invention is configured with the following problem solving means.

（１）第１の課題解決手段
この発明の第１の課題解決手段は、冷媒の通る伝熱管部分が合成樹脂製の細径管２ａ，２ａ、２ｂ，２ｂ・・・よりなり、該細径管２ａ，２ａ，２ｂ，２ｂ・・・が所定の間隔を保って多数本配設されて熱交換器２を形成しているとともに、該熱交換器２が顕熱蓄熱材を蓄えた蓄熱容器１内に収納されてなる蓄熱熱交換器において、放冷回路を形成する細径管２ａ，２ａ・・・又は２ｂ，２ｂ・・・の冷媒の入口側部分に、当該細径管２ａ，２ａ・・・又は２ｂ，２ｂ・・・そのものの通路断面積を変えることにより、冷媒流入量の調節を行う冷媒流量可変手段を設けたことを特徴としている。 (1) First Problem Solving Means The first problem solving means of the present invention is that the heat transfer tube portion through which the refrigerant passes is made of synthetic resin small diameter tubes 2a, 2a, 2b, 2b. A plurality of tubes 2a, 2a, 2b, 2b... Are arranged at predetermined intervals to form a heat exchanger 2, and the heat exchanger 2 stores a sensible heat storage material. In the heat storage heat exchanger housed in 1, the small-diameter pipes 2a, 2a are provided at the refrigerant inlet side portions of the small-diameter pipes 2a, 2a,. ... or 2b, 2b ... itself is provided with a refrigerant flow rate varying means for adjusting the refrigerant inflow amount by changing the passage cross-sectional area.

このような構成によると、放冷時における同冷媒流量可変手段による放冷回路側細径管２ａ，２ａ・・・又は２ｂ，２ｂ・・・への冷媒流入量の調節により、放冷時における放冷能力のセーブが可能となるとともに、熱交部全体の氷水分布及び温度分布が可及的に均一化され、一定時間以上安定した熱交換量が得られるようになる。 According to such a configuration, at the time of cooling, by adjusting the refrigerant inflow amount to the cooling circuit side narrow pipes 2a, 2a... Or 2b, 2b. The cooling capacity can be saved, and the ice water distribution and temperature distribution in the entire heat exchanger are made as uniform as possible, and a stable heat exchange amount can be obtained for a certain time or more.

しかも、同冷媒流量可変手段の冷媒流入量の調節は、放冷回路を形成する細径管２ａ，２ａ・・・又は２ｂ，２ｂ・・・そのものの冷媒の入口側部分の通路断面積を変えることにより、冷媒流入量の調節が行われるようになっている。 Moreover, the adjustment of the refrigerant inflow amount of the refrigerant flow rate varying means changes the passage sectional area of the refrigerant inlet side portion of the small-diameter pipes 2a, 2a,..., 2b, 2b,. As a result, the refrigerant inflow amount is adjusted.

したがって、放冷時の各パスの冷媒流量を単一の作動手段で共通に、しかも外部から簡単に調節制御するように構成することができ、多数本の細径のパスの各々に多数の開閉制御弁を設ける場合の困難や、弁体内部のゴミ詰まりによる信頼性の問題を生じさせることなく、安定した放冷能力の制御を行うことが可能となる。 Therefore, the refrigerant flow rate of each path during cooling can be configured to be controlled and controlled in common by a single operating means and easily from the outside, and a large number of small-diameter paths can be opened and closed. It becomes possible to control the cooling capacity stably without causing difficulty in providing a control valve and causing problems of reliability due to dust clogging inside the valve body.

（２）第２の課題解決手段
この発明の第２の課題解決手段は、上記第１の課題解決手段の構成において、放冷回路の冷媒入口ヘッダ３１と出口ヘッダ３２間には、放冷回路を形成する細径管２ａ，２ａ・・・又は２ｂ，２ｂ・・・と並列に同細径管２ａ，２ａ・・・又は２ｂ，２ｂ・・・をバイパスするバイパス通路ＢＰが設けられている。 (2) Second Problem Solving Means According to a second problem solving means of the present invention, in the configuration of the first problem solving means, a cooling circuit is provided between the refrigerant inlet header 31 and the outlet header 32 of the cooling circuit. Is provided in parallel with the small diameter pipes 2a, 2a,..., 2b, 2b,. .

このような構成によると、放冷回路を形成している細径管２ａ，２ａ・・・又は２ｂ，２ｂ・・・への冷媒流入量を制限した時の冷媒入口ヘッダ３１部分に留まる冷媒をスムーズに冷媒出口ヘッダ３２側にバイパスさせることができる。 According to such a configuration, the refrigerant remaining in the refrigerant inlet header 31 when the refrigerant inflow amount to the narrow tubes 2a, 2a... 2b, 2b. It can be smoothly bypassed to the refrigerant outlet header 32 side.

したがって、運転効率を悪化させなくて済む。 Therefore, it is not necessary to deteriorate the driving efficiency.

（３）第３の課題解決手段
この発明の第３の課題解決手段は、上記第１又は第２の課題解決手段の構成において、冷媒流量可変手段が、細径管２ａ，２ａ・・・又は２ｂ，２ｂ・・・そのものを押圧変形させる押圧変形装置により構成されている。 (3) Third Problem Solving Means According to a third problem solving means of the present invention, in the configuration of the first or second problem solving means, the refrigerant flow rate varying means is a small-diameter pipe 2a, 2a. 2b, 2b... Itself is configured by a press deformation device that presses and deforms.

このような構成によると、同押圧変形装置により、細径管２ａ，２ａ・・・又は２ｂ，２ｂ・・・自体が、外部から偏平な断面楕円形状に押圧変形され、その通路断面積が小さくなって、効果的に冷媒の流入量が制限される。 According to such a configuration, the thin tube 2a, 2a,..., 2b, 2b,... Itself is pressed and deformed from the outside into a flat cross-sectional elliptical shape, and the passage cross-sectional area is small. Thus, the amount of refrigerant flowing in is effectively limited.

（４）第４の課題解決手段
この発明の第４の課題解決手段は、上記第３の課題解決手段の構成において、押圧変形装置が、細径管２ａ，２ａ・・・又は２ｂ，２ｂ・・・を固定支持する支持部材５ｂと、細径管２ａ，２ａ・・・又は２ｂ，２ｂ・・・を押圧する押圧部材５ａと、該押圧部材５ａを押圧作動させる押圧駆動手段６とから構成されている。 (4) Fourth Problem Solving Means According to a fourth problem solving means of the present invention, in the configuration of the third problem solving means, the pressing deformation device is a small diameter tube 2a, 2a,. .. Composed of a supporting member 5b for fixing and supporting, a small diameter tube 2a, 2a... Or 2b, 2b..., And a pressing drive means 6 for pressing the pressing member 5a. Has been.

このような構成によると、押圧部材５ａが、押圧駆動手段６により押圧駆動されることにより、細径管２ａ，２ａ・・・又は２ｂ，２ｂ・・・が、上記支持部材５ｂと該押圧部材５ａとの間に挟まれて偏平な断面楕円形状に押圧変形されて、通路断面積が効果的に縮小される。 According to such a configuration, when the pressing member 5a is pressed and driven by the pressing drive means 6, the small diameter tubes 2a, 2a,..., 2b, 2b. 5a is pressed and deformed into a flat cross-sectional ellipse shape, and the passage cross-sectional area is effectively reduced.

（５）第５の課題解決手段
この発明の第５の課題解決手段は、上記第４の課題解決手段の構成において、押圧駆動手段６が、圧力駆動手段により構成されている。 (5) Fifth Problem Solving Means According to a fifth problem solving means of the present invention, in the configuration of the fourth problem solving means, the pressure driving means 6 is constituted by a pressure driving means.

このような構成によると、押圧部材５ａが、例えばエアシリンダ、油圧シリンダ等の圧力駆動手段６により確実に押圧駆動されることにより、細径管２ａ，２ａ・・・又は２ｂ，２ｂ・・・が、支持部材５ｂと押圧部材５ａとの間に挟まれて、偏平な断面楕円形状に押圧変形し、その通路断面積をスムーズに縮小して、効果的に冷媒の流入量を制限する。 According to such a configuration, when the pressing member 5a is reliably pressed and driven by the pressure driving means 6 such as an air cylinder or a hydraulic cylinder, the small diameter tubes 2a, 2a,..., 2b, 2b. However, it is sandwiched between the support member 5b and the pressing member 5a, and is pressed and deformed into a flat cross-sectional elliptical shape, and the passage cross-sectional area is smoothly reduced to effectively limit the inflow amount of the refrigerant.

（６）第６の課題解決手段
この発明の第６の課題解決手段は、上記第４の課題解決手段の構成において、押圧駆動手段６が、電気的な駆動手段により構成されている。 (6) Sixth Problem Solving Means According to a sixth problem solving means of the present invention, in the configuration of the fourth problem solving means, the pressing drive means 6 is constituted by an electric drive means.

このような構成によると、押圧部材５ａが、例えば電磁アクチュエータやモータなどの電気的な駆動手段により、確実に押圧駆動されることにより、細径管２ａ，２ａ・・・又は２ｂ，２ｂ・・・が、支持部材５ｂと押圧部材５ａとの間に挟まれて、偏平な断面楕円形状に押圧変形し、その通路断面積をスムーズに縮小して、効果的に冷媒の流入量を制限する。 According to such a configuration, when the pressing member 5a is reliably pressed and driven by an electric driving means such as an electromagnetic actuator or a motor, the small diameter tubes 2a, 2a,..., 2b, 2b,. However, it is sandwiched between the support member 5b and the pressing member 5a and is pressed and deformed into a flat cross-sectional elliptical shape, and the passage cross-sectional area is smoothly reduced to effectively limit the inflow amount of the refrigerant.

以上の結果、本願発明によると、放冷時の細径伝熱管各パスの冷媒流量を、単一の変形作動手段で共通に、しかも外部から自由に調節制御することができる。 As a result of the above, according to the present invention, the refrigerant flow rate in each path of the small-diameter heat transfer tube at the time of cooling can be adjusted and controlled in common by a single deformation operating means and freely from the outside.

したがって、多数本の細径の伝熱管各パスの各々に多数の開閉制御弁を設ける場合の困難や、弁体内部のゴミ詰まりによる信頼性の問題等を全く生じさせることなく、長時間に亘って安定した放冷能力の制御を行うことができる。 Therefore, there is no difficulty in providing a large number of open / close control valves in each of a large number of small-diameter heat transfer tubes, and there is no problem of reliability due to dust clogging inside the valve body. And stable cooling ability can be controlled.

（最良の実施の形態１）
図１〜図４は、本願発明の最良の実施の形態１に係る放冷能力調節手段を備えた蓄熱熱交換器の構成を示している。 (Best Embodiment 1)
1 to 4 show the configuration of a heat storage heat exchanger provided with a cooling capacity adjusting means according to the best embodiment 1 of the present invention.

先ず図１は、同蓄熱熱交換器全体の構成を示している。符号１は、水等所望の種類の顕熱蓄熱材が所定量貯留された方形箱型の蓄熱容器、符号２は、蓄熱熱交換器であり、この蓄熱熱交換器２は、蓄熱容器１内に浸漬状態で収納されている。 First, FIG. 1 shows the configuration of the entire heat storage heat exchanger. Reference numeral 1 denotes a rectangular box-type heat storage container in which a predetermined amount of sensible heat storage material such as water is stored, and reference numeral 2 denotes a heat storage heat exchanger. The heat storage heat exchanger 2 is provided in the heat storage container 1. Is stored in a dipped state.

この最良の実施の形態１における蓄熱熱交換器２は、例えば多数本（例えば数百本程度・・・但し、図では一部の本数で代表）の弾力性（復元力）のある合成樹脂製の細径管（中空細径管）をクロス構造（メッシュ構造）に編成した複数枚の偏平な単位熱交換器ユニットＨ₁〜Ｈｎを、図２に示すように上下方向に多数段積層（例えば２００段程度・・・但し、図では一部の段数で代表）したものとなっている。そして、それら各単位熱交換器ユニットＨ₁〜Ｈｎの各々は、例えば外径０．２ｍｍ〜０．６ｍｍ程度の弾性変形可能な合成樹脂製の細径管２ａ，２ａ・・・、２ｂ，２ｂ・・・を、多数本Ｘ−Ｙ方向に交互にクロスさせて配設し、それらを接着剤などで相互に連結固定することにより、相互の間に均一な所定の蓄熱材介在空間を保った状態で略水平面方向に保持されている。 The heat storage heat exchanger 2 according to the best embodiment 1 is made of, for example, a synthetic resin having a large number (for example, about several hundreds, however, representative of some of them in the figure) having elasticity (restoring force). A plurality of flat unit heat exchanger units H _{1 to} Hn obtained by knitting a thin pipe (hollow thin pipe) in a cross structure (mesh structure) as shown in FIG. About 200 stages (however, in the figure, representative of some stages). Each of the unit heat exchanger units H _{1 to} Hn is, for example, an elastically deformable synthetic resin thin tube 2a, 2a,..., 2b, 2b having an outer diameter of about 0.2 mm to 0.6 mm. Are arranged in an alternating manner in the X-Y direction, and are connected and fixed to each other with an adhesive or the like, thereby maintaining a uniform predetermined heat storage material intervening space between them. It is held in a substantially horizontal plane state.

これら多数本の細径管２ａ，２ａ・・・、２ｂ，２ｂ・・・は、その縦方向（図１の図面前後方向）の寸法と横方向（図１の図面左右方向）の寸法を所定の比率に設定した平面方形の形状となるようにし、それら各端部を対辺方向に位置して設けられた冷媒分配ヘッダ３１，３２、３１，３２に等間隔で接続連通せしめられている。 These multiple small diameter tubes 2a, 2a,..., 2b, 2b... Have predetermined dimensions in the vertical direction (front-rear direction in FIG. 1) and in the horizontal direction (left-right direction in FIG. 1). A flat rectangular shape set to the above ratio is connected to and communicated with refrigerant distribution headers 31, 32, 31, 32 provided with their respective ends positioned in the opposite direction at equal intervals.

これら各対辺方向に連通する冷媒分配ヘッダ３１，３２、３１，３２は、それぞれ蓄冷時又は放冷時（熱取出時）の各動作に応じて冷媒の入口ヘッダ３１、冷媒の出口ヘッダ３２として機能する。 The refrigerant distribution headers 31, 32, 31, 32 communicating in the opposite directions function as a refrigerant inlet header 31 and a refrigerant outlet header 32 in accordance with respective operations during cold storage or cooling (heat extraction), respectively. To do.

このような構成によると、冷媒の通る伝熱管部分が弾力性があって弾性変形および弾性変形後の元の形状への復元が可能な合成樹脂製の細径管２ａ，２ａ・・・、２ｂ，２ｂ・・・よりなり、しかも該合成樹脂製の細径管２ａ，２ａ・・・、２ｂ，２ｂ・・・が所定の間隔を保って多数本メッシュ構造に編成されて、複数の単位熱交換器ユニットＨ₁〜Ｈｎを形成し、これら複数の単位熱交換器ユニットＨ₁〜Ｈｎの各々が、例えば図２のように上下方向に所定の間隔（ピッチ）を置いて多段構造に積層された状態で、上述の蓄熱容器１内に収納されて、図１のような蓄熱熱交換器２を構成する。 According to such a configuration, the thin tube 2a, 2a,..., 2b made of synthetic resin, which is elastic and can be restored to its original shape after elastic deformation by the heat transfer tube portion through which the refrigerant passes. 2b, and the synthetic resin small diameter tubes 2a, 2a,..., 2b, 2b. The exchanger units H _{1 to} Hn are formed, and each of the plurality of unit heat exchanger units H _{1 to} Hn is stacked in a multistage structure with a predetermined interval (pitch) in the vertical direction as shown in FIG. In this state, the heat storage heat exchanger 2 as shown in FIG.

したがって、蓄熱容器１内の顕熱蓄熱材中に、伝熱管である多数本の合成樹脂製の細径管２ａ，２ａ・・・、２ｂ，２ｂ・・・が、均一かつ均等に密集した状態で、フィンなどを介することなくダイレクトに接触して分布するようになり、顕熱蓄熱材と細径管２ａ，２ａ・・・、２ｂ，２ｂ・・・との間の熱抵抗が大きく低減され、細径管２ａ，２ａ・・・、２ｂ，２ｂ・・・内を流れる冷媒と顕熱蓄熱材との熱伝達率（熱伝達性能）が、蓄冷時および放冷時共に大きく向上する。その結果、それら何れの場合の熱交換性能も大きく向上する。 Therefore, in the sensible heat storage material in the heat storage container 1, a large number of synthetic resin small-diameter tubes 2a, 2a,..., 2b, 2b. Therefore, the heat resistance between the sensible heat storage material and the small diameter tubes 2a, 2a,..., 2b, 2b. The heat transfer coefficient (heat transfer performance) between the refrigerant flowing through the small diameter tubes 2a, 2a,..., 2b, 2b... And the sensible heat storage material is greatly improved both during cold storage and during cooling. As a result, the heat exchange performance in either case is greatly improved.

ところで、このような細径多管構造の蓄熱熱交換器２において、今例えば図1の左右方向右側の冷媒分配ヘッダ３１が熱交部放冷回路の冷媒入口ヘッダ、同左側の冷媒分配ヘッダ３２が同熱交部放冷回路の冷媒出口ヘッダであり、それらの間の多数本の細径管２ｂ，２ｂ・・・が同熱交部放冷回路のパス部を形成しているとすると、図１の上下方向の蓄冷回路（下方から上方に細径管２ａ，２ａ・・・を介して冷媒が流れる）により蓄熱した熱を放冷する際に、放冷開始時は同多数本の細径管２ｂ，２ｂ・・・周りの氷が解けて有効な（あるいは過剰な）熱交換量を出すものの、放冷時間の経過とともに氷の量が減少することから、次第に熱交換量は低下し、長時間に亘って安定した熱交換量を得ることが難しい。 By the way, in such a heat storage heat exchanger 2 having a small-diameter multi-tubular structure, for example, the right refrigerant distribution header 31 in FIG. 1 is the refrigerant inlet header of the heat exchanger cooling circuit and the left refrigerant distribution header 32. Is a refrigerant outlet header of the heat exchanger cooling circuit, and a plurality of thin tubes 2b, 2b ... between them form a path portion of the heat exchanger cooling circuit, When the heat stored in the up-and-down cold storage circuit (the refrigerant flows from the lower side to the upper side through the small diameter tubes 2a, 2a,...) In FIG. 1 is allowed to cool, Although the ice around the diameter tubes 2b, 2b... Melts and produces an effective (or excessive) heat exchange amount, the amount of ice decreases as the cooling time elapses, so the heat exchange amount gradually decreases. It is difficult to obtain a stable heat exchange amount over a long period of time.

また構造上、同放冷回路入口側で、細径管２ｂ，２ｂ・・・に近いものは解けやすいが、放冷回路出口側で細径管２ｂ，２ｂ・・・から遠いものは解けにくい、という氷融解状態のアンバランスが生じる。 In addition, the structure close to the small diameter pipes 2b, 2b... Is easy to unwind on the inlet side of the cooling circuit, but the distance from the small diameter pipes 2b, 2b. An unbalanced ice melting state occurs.

このような問題に対する対策として、例えば図１の冷媒供給管３３および接続管３３ａから冷媒入口ヘッダ３１を介して放冷回路の各細径管（パス）２ｂ，２ｂ・・・に分配供給される放冷用の冷媒の流入量を同細径管２ｂ，２ｂ・・・各々の入口部で所定量以下に調節し得るように、前述の図５のような多数の開閉制御弁Ｖ₁〜Ｖｎを設け、それら各開閉制御弁Ｖ₁〜Ｖｎによって放冷用の各細径管２ｂ，２ｂ・・・へ供給される冷媒の一部をバイパス通路ＢＰを介して冷媒出口ヘッダ３２から、接続管３４ａを介して冷媒排出管３４側にバイパスさせることにより、冷媒流入量を所望の量に制限して、一定時間以上安定した放冷能力を維持させる方法が考えられる。 As a countermeasure against such a problem, for example, the refrigerant supply pipe 33 and the connection pipe 33a in FIG. 1 are distributed and supplied to the small diameter pipes (paths) 2b, 2b,. A large number of open / close control valves V _{1 to} Vn as shown in FIG. 5 so that the inflow amount of the refrigerant for cooling can be adjusted to a predetermined amount or less at the respective inlet portions of the small-diameter tubes 2b, 2b. the provided, each of those thin tube 2b for cooling by the opening and closing control valves V ₁ to Vn, a part of the refrigerant from the refrigerant outlet header 32 via the bypass passage BP supplied to 2b · · ·, connecting pipes By bypassing to the refrigerant | coolant discharge pipe 34 side via 34a, the refrigerant | coolant inflow amount is restrict | limited to a desired quantity, and the method of maintaining the stable cooling ability more than fixed time can be considered.

しかし、すでに述べたように合成樹脂製の多数本の細径管２ｂ，２ｂ・・・の各々に、図５のような微細かつ精密な開閉制御弁Ｖ₁〜Ｖｎを設けることは不可能に近いし、その通路径の狭さを考えると、弁体内部にゴミ等が詰まりやすく、信頼性の点でも問題が多い。また、多数の開閉制御弁Ｖ₁〜Ｖｎを開閉制御するのは、それ自体大変である。 However, as described above, it is impossible to provide fine and precise opening / closing control valves V _{1 to} Vn as shown in FIG. 5 in each of a large number of the thin tubes 2b, 2b. Considering the narrowness of the passage diameter, dust and the like are easily clogged inside the valve body, and there are many problems in terms of reliability. In addition, it is difficult to control opening and closing a large number of opening / closing control valves V _{1 to} Vn.

そこで、この実施の形態では、そのような事情に鑑み、上記細径多管構造の蓄熱熱交換器２において、上記放冷回路のパス部を形成している細径管２ｂ，２ｂ・・・の冷媒の入口側端部に、当該細径管２ｂ，２ｂ・・・そのものを、例えば図４のように押圧変形させることにより、その通路断面積を小さくすることによって冷媒流量の調節を行う冷媒流量可変手段を設けている。 Therefore, in this embodiment, in view of such circumstances, in the heat storage heat exchanger 2 having the small diameter multi-tube structure, the small diameter tubes 2b, 2b,. The small diameter pipes 2b, 2b,... Themselves are pressed and deformed, for example, as shown in FIG. A flow rate variable means is provided.

この押圧変形による冷媒流量可変手段は、例えば図１〜図４に示すように、同細径管２ｂ，２ｂ・・・を下方側で受け止める固定側支持部材５ｂと、同細径管２ｂ，２ｂ・・・を上方側から押圧して圧縮変形させる可動側押圧部材５ａと、該押圧部材５ａを上下方向に昇降作動させる押圧駆動手段（圧力駆動手段）としてのエアシリンダ６とからなり、エアシリンダ６の伸縮ロッド６ａの下端（先端）に押圧部材５ａが固着支持されている。 As shown in FIGS. 1 to 4, for example, the refrigerant flow rate varying means by the pressure deformation includes a fixed-side support member 5b for receiving the same small diameter pipes 2b, 2b... On the lower side, and the same small diameter pipes 2b, 2b. .. Are pressed from above and compressed and deformed, and an air cylinder 6 as pressure driving means (pressure driving means) for moving the pressing member 5a up and down in the vertical direction. A pressing member 5a is fixedly supported on the lower end (tip) of the telescopic rod 6a.

押圧部材５ａは、例えば図１に示すように、多数本並設された放冷回路側細径管２ｂ，２ｂ・・・の冷媒入口ヘッダ３１側各端部に位置して、その配列幅部分の全体を下方側で均一に受け止め、また同様の状態で上方側から均一に押圧できるように、同配列幅に対応した長さを有して構成されており、エアシリンダ６は、同押圧部材５ａの長手方向中間部分に対応して設けられている。もちろん、このエアシリンダ６は押圧部材５ａの両端側に設けるようにしてもよい。その方が全体に亘って均一な押圧力を作用させることができる。 For example, as shown in FIG. 1, the pressing member 5 a is positioned at each end portion on the refrigerant inlet header 31 side of a plurality of the cooling circuit side narrow tubes 2 b, 2 b. The air cylinder 6 is configured to have a length corresponding to the arrangement width so that the whole can be uniformly received on the lower side and can be uniformly pressed from the upper side in the same state. 5a is provided corresponding to the middle part in the longitudinal direction. Of course, the air cylinder 6 may be provided at both ends of the pressing member 5a. That way, a uniform pressing force can be applied throughout.

そして、この実施の形態の構成においても、上記放冷回路の冷媒入口ヘッダ３１と出口ヘッダ３２間には、同放冷回路を形成している細径管２ｂ，２ｂ・・・と並列に同細径管２ｂ，２ｂ・・・をバイパスするバイパス通路ＢＰが設けられている。 Also in the configuration of this embodiment, the refrigerant inlet header 31 and the outlet header 32 of the cooling circuit are connected in parallel with the small diameter tubes 2b, 2b,... Forming the cooling circuit. A bypass passage BP that bypasses the small diameter tubes 2b, 2b... Is provided.

したがって、今例えば図３に示すように、エアシリンダ６のシリンダ部６ｂ内が負圧の伸縮ロッド６ａ収縮状態（上昇状態）では、押圧部材５ａが細径管２ｂ，２ｂ・・・の上方に上昇しており、細径管２ｂ，２ｂ・・・の各々は、全く圧縮変形されることなく、最も通路断面積が大きい断面正円形の筒状体で、放冷用の冷媒供給管３３から冷媒入口ヘッダ３１を介して分配される放冷用の冷媒を効率良く流通させて、冷媒出口ヘッダ３２側にスムーズに供給し得る状態にある。 Therefore, for example, as shown in FIG. 3, when the inside of the cylinder portion 6b of the air cylinder 6 is in a contracted state (upward state) where the telescopic rod 6a is in a negative pressure, the pressing member 5a is located above the small diameter tubes 2b, 2b. Each of the small-diameter pipes 2b, 2b... Is a cylindrical body having a perfectly circular cross section with the largest passage cross-sectional area without any compression deformation, and from the refrigerant supply pipe 33 for cooling. It is in a state where the cooling-use refrigerant distributed through the refrigerant inlet header 31 can be efficiently distributed and smoothly supplied to the refrigerant outlet header 32 side.

一方、同状態において、放冷を開始しようとする時は、図３中の矢印に示すように、上記冷媒入口ヘッダ３１側冷媒流量可変手段のエアシリンダ６のシリンダ６ｂ内にエアパイプ７を介して図示しないエアポンプからのエアを供給することによって、押圧部材５ａを所定ストローク量下降させることによって、図４のように、放冷回路のパス部を形成している細径管２ｂ，２ｂの冷媒入口側端部を偏平な断面楕円形状に圧縮変形させて、その通路断面積を小さくし、放冷用冷媒の流入量を所定量以下に制限する。 On the other hand, in the same state, when starting to cool, as shown by the arrow in FIG. 3, the air inlet 7 is inserted into the cylinder 6b of the air cylinder 6 of the refrigerant inlet header 31 side refrigerant flow rate varying means. By supplying air from an air pump (not shown) and lowering the pressing member 5a by a predetermined stroke amount, the refrigerant inlets of the small-diameter tubes 2b and 2b forming the path portion of the cooling circuit as shown in FIG. The side end portion is compressed and deformed into a flat cross-sectional elliptical shape, the passage cross-sectional area is reduced, and the inflow amount of the cooling refrigerant is limited to a predetermined amount or less.

そして、それにより同細径管２ｂ，２ｂ・・・の冷媒入口側〜出口側周辺の氷を全体に亘って略均等な状態で徐々に融解させながら冷熱を取り出すことによって、できるだけ放冷能力が一定した長い放冷運転時間を確保する。 Then, by taking out the cold heat while gradually melting the ice around the refrigerant inlet side to the outlet side of the same thin diameter pipes 2b, 2b... Ensure constant and long cooling operation time.

このような構成によると、冷媒流量可変手段による放冷回路側細径管２ｂ，２ｂ・・・への冷媒流入量の調節により、熱交部全体の氷水分布及び温度分布が可及的に均一化され、一定時間以上安定した熱交換量が得られるようになる。 According to such a configuration, the ice water distribution and the temperature distribution in the entire heat exchanger are made as uniform as possible by adjusting the amount of refrigerant flowing into the cooling circuit side small diameter tubes 2b, 2b. Thus, a stable heat exchange amount for a certain time or more can be obtained.

そして、このように細径管２ｂ，２ｂ・・・への冷媒流入量を制限した時の冷媒入口ヘッダ３１部分に留まる冷媒は、上記バイパス通路ＢＰによりスムーズに冷媒出口ヘッダ３２側にバイパスさせる。 And the refrigerant | coolant which stays in the refrigerant | coolant inlet header 31 part when restrict | limiting the refrigerant | coolant inflow amount to the small diameter pipes 2b, 2b ... in this way is smoothly bypassed to the refrigerant | coolant outlet header 32 side by the said bypass passage BP.

したがって、放冷時の各パスの冷媒流量を単一の作動手段で共通に、しかも外部から簡単に簡単に調節制御するように構成することができ、多数本の細径のパスの各々に多数の開閉制御弁を設ける
場合の困難や、弁体内部のゴミ詰まりによる信頼性の問題を生じさせることなく、安定した放冷能力の制御を行うことが可能となる。 Therefore, the refrigerant flow rate of each path during cooling can be configured to be controlled and controlled easily and easily from the outside by a single operating means. Therefore, it is possible to control the cooling capacity stably without causing the difficulty in providing the open / close control valve and the problem of reliability due to dust clogging inside the valve body.

（最良の実施の形態２）
上記最良の実施の形態１の構成では、押圧部材５ａが、例えばエアシリンダ、油圧シリンダ等の圧力駆動手段により押圧駆動されるようにしたが、これは例えば電磁プランジャ等の電磁アクチュエータやモータなどの電気的な駆動手段により、押圧駆動されるようにしてもよい。 (Best Mode 2)
In the configuration of the first embodiment, the pressing member 5a is driven to be pressed by pressure driving means such as an air cylinder or a hydraulic cylinder. This may be an electromagnetic actuator such as an electromagnetic plunger or a motor. You may make it press-drive by an electrical drive means.

（最良の実施の形態３）
なお、上記各実施の形態の構成において、さらに上述の蓄熱容器１に機械的な振動（微細振動）を加える加振手段を付加するようにすることもできる。 (Best Mode 3)
In addition, in the structure of each said embodiment, the vibration means which adds mechanical vibration (fine vibration) to the above-mentioned thermal storage container 1 can also be added.

このようにして蓄熱容器１内の氷水状態の顕熱蓄熱材に微細な振動を与えるようにすると、熱交部全体の氷水分布及び温度分布が、より可及的に均一化され、より安定した熱交換量が得られるようになる。 In this way, if fine vibration is given to the sensible heat storage material in the ice water state in the heat storage container 1, the ice water distribution and the temperature distribution of the entire heat exchanger are made more uniform and more stable. The amount of heat exchange can be obtained.

本願発明の最良の実施の形態１に係る蓄熱熱交換器全体の構成を示す上面図である。It is a top view which shows the structure of the whole heat storage heat exchanger which concerns on the best Embodiment 1 of this invention. 同蓄熱熱交換器の要部である熱交換器ユニット積層部分の構成を示す断面図である。It is sectional drawing which shows the structure of the heat exchanger unit lamination | stacking part which is the principal part of the heat storage heat exchanger. 同蓄熱熱交換器の要部である細径管端部の圧縮変形作用を利用した流量可変手段の構成を示す断面図である。It is sectional drawing which shows the structure of the flow volume variable means using the compression deformation effect | action of the small diameter pipe end part which is the principal part of the same heat storage heat exchanger. 同蓄熱熱交換器の要部である流量可変手段の作用を示す拡大断面図であるIt is an expanded sectional view which shows the effect | action of the flow volume variable means which is the principal part of the same heat storage heat exchanger. 本願発明の参考例（検討例）に係る蓄熱熱交換器の流量可変手段部分の構成を示す平面図である。It is a top view which shows the structure of the flow volume variable means part of the thermal storage heat exchanger which concerns on the reference example (examination example) of this invention.

Explanation of symbols

１は蓄熱容器、２は蓄熱熱交換器、２ａ，２ｂは合成樹脂製の細径管、３１は冷媒入口ヘッダ、３２は冷媒出口ヘッダ、３３ａは冷媒入口ヘッダ３１と冷媒供給管３３との間の接続管、Ｈ₁〜Ｈｎは単位熱交換器ユニットである。 1 is a heat storage container, 2 is a heat storage heat exchanger, 2a and 2b are thin tubes made of synthetic resin, 31 is a refrigerant inlet header, 32 is a refrigerant outlet header, and 33a is between the refrigerant inlet header 31 and the refrigerant supply pipe 33. The connecting pipes H _{1 to} Hn are unit heat exchanger units.

Claims

The heat transfer tube portion through which the refrigerant passes is composed of synthetic resin small diameter tubes (2a), (2a), (2b), (2b)..., And the small diameter tubes (2a), (2a), (2b) , (2b)... Are arranged at a predetermined interval to form a heat exchanger (2), and the heat exchanger (2) stores a sensible heat storage material. In the heat storage heat exchanger housed in 1, in the refrigerant inlet side portion of the small-diameter pipes (2a), (2a)... Or (2b), (2b). The refrigerant flow rate variable means for adjusting the refrigerant inflow amount is provided by changing the cross-sectional area of the small-diameter pipe (2a), (2a)... Or (2b), (2b). A heat storage heat exchanger characterized by that.

Between the refrigerant inlet header (31) and the outlet header (32) of the cooling circuit, the small diameter pipes (2a), (2a)... Or (2b), (2b). The heat storage heat exchange according to claim 1, characterized in that a bypass passage BP is provided in parallel with the same small-diameter pipe (2a), (2a) ... or (2b), (2b) ... vessel.

The refrigerant flow rate varying means is constituted by a press deformation device that presses and deforms the small-diameter pipes (2a), (2a)... Or (2b), (2b). The heat storage heat exchanger according to 1 or 2.

The pressing deformation device includes a support member (5b) for fixing and supporting the small-diameter pipes (2a), (2a), or (2b), (2b), and the small-diameter pipes (2a), (2a). , Or (2b), (2b), and a pressing drive means (6) for pressing the pressing member 5a. Item 4. The heat storage heat exchanger according to item 3.

The heat storage heat exchanger according to claim 4, wherein the pressing drive means (6) comprises pressure driving means.

The heat storage heat exchanger according to claim 4, wherein the pressing drive means (6) comprises an electric drive means.