JP5139019B2 - Cooling system - Google Patents

Cooling system Download PDF

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JP5139019B2
JP5139019B2 JP2007252732A JP2007252732A JP5139019B2 JP 5139019 B2 JP5139019 B2 JP 5139019B2 JP 2007252732 A JP2007252732 A JP 2007252732A JP 2007252732 A JP2007252732 A JP 2007252732A JP 5139019 B2 JP5139019 B2 JP 5139019B2
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refrigerant
heat exchanger
primary
plate
pipe
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JP2009085453A (en
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和芳 関
明彦 平野
進一 加賀
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Hoshizaki Electric Co Ltd
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Description

本発明は、冷却装置に関し、更に詳細には、一次冷媒を機械的に強制循環する一次回路と二次冷媒を自然循環する二次回路と、一次冷媒および二次冷媒の熱交換を行なう熱交換器とを備える冷却装置に関するものである。   The present invention relates to a cooling device, and more specifically, a primary circuit that mechanically circulates a primary refrigerant, a secondary circuit that naturally circulates a secondary refrigerant, and heat exchange that performs heat exchange between the primary refrigerant and the secondary refrigerant. And a cooling device.

一次冷媒を機械的に強制循環させる一次回路と、二次冷媒が自然循環する二次回路とを備え、一次冷媒と二次冷媒との間で熱交換するよう構成した冷却装置がある(例えば特許文献１参照)。このような冷却装置９０の一次回路９４は、図１７に示すように、気相一次冷媒を圧縮する圧縮機ＣＭと、圧縮した一次冷媒を液化する凝縮器ＣＤと、液相一次冷媒の圧力を低下させる膨張弁ＥＶと、プレート式熱交換器１１０に設けられて液相一次冷媒を気化する一次熱交換部９６とを配管９８で接続して構成されると共に、二次回路１０４は、プレート式熱交換器１１０に設けられて気相二次冷媒を液化する二次熱交換部１０６と、液相二次冷媒を気化する蒸発器ＥＰとを別の配管１０８で接続して構成されて、プレート式熱交換器１１０において一次冷媒と二次冷媒とが熱交換することで、最終的に二次回路１０４の蒸発器ＥＰを冷却するようになっている。そして、このような冷却装置９０を備えた冷凍機器では、一次回路９４の構成部材ＣＭ,ＣＤ,ＥＶおよびプレート式熱交換器１１０を、外気に晒された開放空間に配設すると共に、台板１１２を介して開放空間の下方に画成した閉鎖空間に二次回路１０４を構成する蒸発器ＥＰを配設して、閉鎖空間内を冷却するよう構成される。
特開２００２−４８４８４号公報 There is a cooling device that includes a primary circuit that mechanically circulates the primary refrigerant and a secondary circuit that naturally circulates the secondary refrigerant, and is configured to exchange heat between the primary refrigerant and the secondary refrigerant (for example, patents). Reference 1). As shown in FIG. 17, the primary circuit 94 of such a cooling device 90 includes a compressor CM that compresses the gas phase primary refrigerant, a condenser CD that liquefies the compressed primary refrigerant, and the pressure of the liquid phase primary refrigerant. The expansion valve EV to be lowered and the primary heat exchanging part 96 that is provided in the plate heat exchanger 110 and vaporizes the liquid phase primary refrigerant are connected by a pipe 98, and the secondary circuit 104 has a plate type. A plate formed by connecting a secondary heat exchange unit 106 provided in the heat exchanger 110 for liquefying the gas phase secondary refrigerant and an evaporator EP for vaporizing the liquid phase secondary refrigerant through another pipe 108. In the heat exchanger 110, the primary refrigerant and the secondary refrigerant exchange heat to finally cool the evaporator EP of the secondary circuit 104. In the refrigeration equipment provided with such a cooling device 90, the constituent members CM, CD, EV of the primary circuit 94 and the plate heat exchanger 110 are disposed in an open space exposed to the outside air, and a base plate. An evaporator EP that constitutes the secondary circuit 104 is disposed in a closed space defined below the open space via 112 to cool the inside of the closed space.
JP 2002-48484 A

ところで、前記プレート式熱交換器１１０では、前記一次冷媒と二次冷媒との間の熱交換効率を向上するため、該プレート式熱交換器１１０の外周囲を断熱材ＨＩで覆うよう構成される。すなわち、プレート式熱交換器１１０を断熱材ＨＩで覆うことにより、一次冷媒の蒸発により冷却されるプレート式熱交換器１１０の熱損失を防止すると共に、結露や凍結といった不具合を防ぐようになっている。また、プレート式熱交換器１１０で熱交換する二次冷媒も冷温となるため、前述と同様に、二次回路を構成する配管１０８の外周囲を断熱材ＨＩで覆って、熱損失や、結露、凍結を防止している。このように、従来の冷却装置では、低温となるプレート式熱交換器１１０や二次回路の配管１０８を断熱材で覆う必要があり、製造工程が増加して製造コストが嵩む原因となっていた。   By the way, the plate heat exchanger 110 is configured to cover the outer periphery of the plate heat exchanger 110 with a heat insulating material HI in order to improve the heat exchange efficiency between the primary refrigerant and the secondary refrigerant. . That is, by covering the plate heat exchanger 110 with the heat insulating material HI, heat loss of the plate heat exchanger 110 cooled by evaporation of the primary refrigerant is prevented, and problems such as condensation and freezing are prevented. Yes. In addition, since the secondary refrigerant that exchanges heat with the plate heat exchanger 110 is also cold, the outer periphery of the pipe 108 constituting the secondary circuit is covered with a heat insulating material HI in the same manner as described above, so that heat loss and dew condensation are achieved. Prevents freezing. Thus, in the conventional cooling device, it is necessary to cover the plate-type heat exchanger 110 and the secondary circuit pipe 108 that are at a low temperature with the heat insulating material, which increases the manufacturing process and increases the manufacturing cost. .

そこで、本発明は、熱交換器における熱損失等の不具合を防止し得ると共に、製造コストを低減し得る冷却装置を提供することを目的とする。   Then, an object of this invention is to provide the cooling device which can prevent troubles, such as a heat loss in a heat exchanger, and can reduce manufacturing cost.

前記課題を克服し、所期の目的を達成するため、本発明に係る冷却装置は、
一次冷媒を機械的に強制循環する一次回路と、二次冷媒を自然循環する二次回路と、一次冷媒および二次冷媒の間で熱交換する熱交換器とを備え、前記一次回路を配設する開放空間と、前記二次回路を配設する閉鎖空間とを断熱壁部により区切るよう構成された冷却装置において、
前記熱交換器を前記断熱壁部内に埋め込むよう配設し、
前記断熱壁部は、前記開放空間に開口する開口部から前記熱交換器を収納可能な収納部と、前記収納部の開口部を閉成する断熱蓋体とを有し、
前記収納部の内壁面と断熱蓋体との間に、冷媒の消炎距離以下の間隔に設定された隙間を介在させたことを要旨とする。 In order to overcome the above-mentioned problems and achieve the intended purpose, a cooling device according to the present invention includes:
A primary circuit that mechanically circulates the primary refrigerant, a secondary circuit that naturally circulates the secondary refrigerant, and a heat exchanger that exchanges heat between the primary refrigerant and the secondary refrigerant. In a cooling device configured to partition an open space to be closed and a closed space in which the secondary circuit is disposed by a heat insulating wall,
Arranging the heat exchanger to be embedded in the heat insulating wall ,
The heat insulating wall portion includes a storage portion that can store the heat exchanger from an opening portion that opens into the open space, and a heat insulating lid that closes the opening portion of the storage portion,
The gist is that a gap set at an interval equal to or less than the extinguishing distance of the refrigerant is interposed between the inner wall surface of the storage portion and the heat insulating lid .

すなわち、開放空間と閉鎖空間とを区切る断熱壁部に熱交換器を埋め込むことで、熱交換器の熱損失を防止して一次冷媒と二次冷媒との熱交換効率の向上を図ることができ、また部品点数削減によるコスト低減や、製造工程の簡略化が図られる。また、熱交換器において二次熱交換部に接続する配管も、低温域となる閉鎖空間に配設し得るから、これら配管を断熱する断熱材を設ける必要がなく、コスト低減を図り得る。
また、前記収納部内の熱交換器から冷媒が漏出した場合であっても、漏出した冷媒が閉鎖空間内に侵入するのを阻止して、隙間を介して開放空間側に放散し得る。更に、前記隙間は、冷媒の消炎距離以下に設定されているから、冷媒として可燃性冷媒を用いた場合に、該収納部内で冷媒が発火することはない。 In other words, by embedding a heat exchanger in the heat insulating wall that divides the open space and the closed space, it is possible to prevent heat loss of the heat exchanger and improve the heat exchange efficiency between the primary refrigerant and the secondary refrigerant. In addition, the cost can be reduced by reducing the number of parts and the manufacturing process can be simplified. In addition, since the pipe connected to the secondary heat exchange section in the heat exchanger can also be arranged in a closed space that is a low temperature region, it is not necessary to provide a heat insulating material that insulates these pipes, and the cost can be reduced.
Further, even when the refrigerant leaks from the heat exchanger in the storage unit, the leaked refrigerant can be prevented from entering the closed space and diffused to the open space side through the gap. Furthermore, since the gap is set to be equal to or less than the flame extinguishing distance of the refrigerant, when a combustible refrigerant is used as the refrigerant, the refrigerant does not ignite in the storage portion.

請求項２に係る冷却装置は、前記断熱蓋体と熱交換器との間に、冷媒の消炎距離以下の間隔に設定された隙間を介在させたことを要旨とする。
このように、断熱蓋体と熱交換器との間にも、一次冷媒の消炎距離以下の間隔に設定された隙間を介在させることで、熱交換器から冷媒が漏出した場合には、冷媒を速やかに開放空間へ放散し得る。また、この断熱蓋体と熱交換器との間の隙間を、冷媒の消炎距離以下に設定することで、前述と同様に、冷媒として可燃性冷媒を用いた場合に、該収納部内で冷媒が発火することはない。 The gist of the cooling device according to claim 2 is that a gap set at an interval equal to or shorter than the extinguishing distance of the refrigerant is interposed between the heat insulating lid and the heat exchanger .
Thus, by interposing a gap set at an interval equal to or shorter than the extinguishing distance of the primary refrigerant between the heat insulating lid and the heat exchanger, if the refrigerant leaks from the heat exchanger, the refrigerant is removed. It can quickly dissipate into open space. In addition, by setting the gap between the heat insulating lid and the heat exchanger to be equal to or less than the flame extinguishing distance of the refrigerant, as described above, when a flammable refrigerant is used as the refrigerant, the refrigerant is contained in the storage unit. There is no ignition.

請求項３に係る冷却装置は、前記熱交換器は、複数のプレートを所要間隔離間するように並列に対向配置し、対向するプレートの間に形成される流路に、前記一次冷媒および二次冷媒が交互に流通させるよう構成されることを要旨とする。
前記熱交換器として、所謂プレート式熱交換器を用いることで、プレートの数を変えることにより熱交換器の容量を簡単に変更できる。 According to a third aspect of the present invention, in the cooling device, the heat exchanger includes a plurality of plates arranged in parallel so as to be spaced apart from each other by a predetermined distance, and the primary refrigerant and the secondary are disposed in a flow path formed between the opposed plates. The gist is that the refrigerant is configured to flow alternately .
By using a so-called plate heat exchanger as the heat exchanger, the capacity of the heat exchanger can be easily changed by changing the number of plates.

請求項４に係る冷却装置は、前記熱交換器は、外管と、前記外管の内部に挿通された内管とから構成され、前記外管および内管に、前記一次冷媒および二次冷媒を対向流となるよう流通させるよう構成されることを要旨とする。
前記熱交換器として、外管内に内管を挿通した所謂二重管式熱交換器を用いることで、熱交換器自体の構成を簡単にでき、コスト低減が図られる。 The cooling device according to claim 4, wherein the heat exchanger includes an outer pipe and an inner pipe inserted into the outer pipe, and the primary refrigerant and the secondary refrigerant are provided in the outer pipe and the inner pipe, respectively. The gist of the invention is that it is configured to circulate in a counterflow.
By using a so-called double-pipe heat exchanger in which the inner tube is inserted into the outer tube as the heat exchanger, the configuration of the heat exchanger itself can be simplified and the cost can be reduced.

すなわち、本発明によれば、熱交換器での熱損失等の不具合を防止し得ると共に製造コストを低減し得る。   That is, according to the present invention, problems such as heat loss in the heat exchanger can be prevented and the manufacturing cost can be reduced.

次に、本発明に係る冷却装置につき、好適な実施例を挙げて、添付図面を参照して以下に説明する。実施例では、店舗等の業務用途に用いられ、野菜や肉等の物品を多量に収納し得る大型の縦型冷蔵庫に設けられる冷却装置を例に挙げて説明する。なお、従来技術において説明した部材・構成と同一の部材・構成に関しては、同一の符号を付してある。   Next, the cooling device according to the present invention will be described below with reference to the accompanying drawings by way of preferred embodiments. In the embodiment, a cooling device provided in a large-sized vertical refrigerator that is used for business purposes such as a store and can store a large amount of articles such as vegetables and meat will be described as an example. In addition, the same code | symbol is attached | subjected about the same member and structure as the member and structure demonstrated in the prior art.

図１に示すように、実施例１に係る縦型冷蔵庫１０は、収納室(閉鎖空間)１４を内部画成した断熱構造の箱体１２と、この箱体１２の上方に設けられ、金属パネル１８により外壁を構成したキャビネット１６とを備えている。箱体１２には、前側に開放して物品の出し入れ口となる開口部１２ａが収納室１４に連通して開設される。また箱体１２の前部には、断熱扉２２が図示しないヒンジにより回動可能に配設され、断熱扉２２を開放することで開口部１２ａを介して収納室１４に対する物品の出し入れが許容されると共に、断熱扉２２を閉成することで収納室１４を密閉し得るようになっている。   As shown in FIG. 1, a vertical refrigerator 10 according to the first embodiment includes a box 12 having a heat insulating structure that internally defines a storage room (closed space) 14, and a metal panel provided above the box 12. The cabinet 16 which comprises the outer wall by 18 is provided. In the box 12, an opening portion 12 a that opens to the front side and serves as an entry / exit port for goods is opened in communication with the storage chamber 14. Further, a heat insulating door 22 is rotatably disposed at a front portion of the box body 12 by a hinge (not shown), and by opening the heat insulating door 22, an article can be taken into and out of the storage chamber 14 through the opening 12a. In addition, the storage chamber 14 can be sealed by closing the heat insulating door 22.

前記キャビネット１６の内部には、収納室１４を冷却するための冷却装置３２の一部および該冷却装置３２を制御する制御用電装箱(図示せず)が配設される機械室(開放空間)２０が画成される(図２参照)。機械室２０の底部には、箱体１２の天板１２ｂに載置されて、該機械室２０に配設する機器の共通基板となる台板(断熱壁部)２４が設置されている。そして、キャビネット１６の外壁をなす金属パネル１８には、機械室２０に連通する空気流通孔(図示せず)が適宜部位に開設され、この空気流通孔を介して機械室２０内の雰囲気と外気とが入替わるようになっている。   Inside the cabinet 16, a machine room (open space) in which a part of a cooling device 32 for cooling the storage chamber 14 and a control electrical box (not shown) for controlling the cooling device 32 are arranged. ) 20 is defined (see FIG. 2). At the bottom of the machine room 20, a base plate (heat insulating wall part) 24 that is placed on the top plate 12 b of the box 12 and serves as a common substrate for the devices disposed in the machine room 20 is installed. The metal panel 18 forming the outer wall of the cabinet 16 is provided with air circulation holes (not shown) communicating with the machine room 20 at appropriate locations, and the atmosphere in the machine room 20 and the outside air are communicated through the air circulation holes. And are to be replaced.

前記収納室１４の上部には、箱体１２における天板１２ｂの下面から所定間隔離間して冷却ダクト２６が配設され、この冷却ダクト２６と、箱体１２の天板１２ｂに開設した切欠口１２ｃを介して収納室１４側に臨む台板２４との間に冷却室２８が画成される。この冷却室２８は、冷却ダクト２６の底部前側に形成した吸込口２６ａおよび後側に形成した冷気吹出口２６ｂを介して収納室１４に連通して、閉鎖空間としての収納室１４の一部を構成している。吸込口２６ａには送風ファン３０が配設され、該送風ファン３０を駆動することで、吸込口２６ａから収納室１４の空気を冷却室２８に取込み、冷気吹出口２６ｂから冷却室２８の冷気が収納室１４に送出される。天板１２ｂの切欠口１２ｃは、台板２４で気密的に塞がれて、収納室１４(冷却室２８)と機械室２０とは、台板２４で区切られて互いに独立した空間となっている(図１参照)。   In the upper part of the storage chamber 14, a cooling duct 26 is disposed at a predetermined distance from the lower surface of the top plate 12b in the box 12, and the cooling duct 26 and a notch formed in the top plate 12b of the box 12 are provided. A cooling chamber 28 is defined between the base plate 24 facing the storage chamber 14 via 12c. The cooling chamber 28 communicates with the storage chamber 14 through a suction port 26a formed on the front side of the bottom of the cooling duct 26 and a cold air outlet 26b formed on the rear side, and a part of the storage chamber 14 as a closed space is formed. It is composed. A blower fan 30 is disposed at the suction port 26a. By driving the blower fan 30, the air in the storage chamber 14 is taken into the cooling chamber 28 from the suction port 26a, and the cool air in the cooling chamber 28 is drawn from the cool air outlet 26b. It is sent to the storage chamber 14. The notch 12c of the top plate 12b is hermetically closed by the base plate 24, and the storage chamber 14 (cooling chamber 28) and the machine room 20 are separated from each other by the base plate 24 and become independent spaces. (See FIG. 1).

図２に示す如く、冷却装置３２は、一次冷媒を強制循環する機械圧縮式の一次回路３４と、二次冷媒が自然対流するサーモサイフォンからなる二次回路４４との２系統の回路を、傾斜配置されたプレート式熱交換器(熱交換器)ＨＥを介して接続(カスケード接続)した二次ループ冷凍回路が採用される。プレート式熱交換器ＨＥは、一次回路３４を構成する一次熱交換部３６と、この一次熱交換部３６とは別系統に形成されて、二次回路４４を構成する二次熱交換部４６とを備え、収納室１４と機械室２０とを区画する台板２４内に配設されている(図１参照)。すなわち、一次回路３４および二次回路４４には、独立した冷媒循環経路が夫々形成されている。また、一次回路３４を循環する一次冷媒としては、蒸発熱や飽和圧等の冷媒としての特性に優れているブタンやプロパン等のＨＣ系の冷媒またはアンモニアなどが採用され、二次回路４４を循環する二次冷媒としては、毒性、可燃性および腐食性を有していない安全性の高い二酸化炭素が採用される。   As shown in FIG. 2, the cooling device 32 tilts two systems of circuits, a mechanical compression primary circuit 34 forcibly circulating the primary refrigerant and a secondary circuit 44 composed of a thermosiphon in which the secondary refrigerant naturally convects. A secondary loop refrigeration circuit connected (cascade connection) via a plate type heat exchanger (heat exchanger) HE arranged is employed. The plate heat exchanger HE includes a primary heat exchange unit 36 that constitutes the primary circuit 34, and a secondary heat exchange unit 46 that is formed in a separate system from the primary heat exchange unit 36 and constitutes the secondary circuit 44. And disposed in a base plate 24 that divides the storage chamber 14 and the machine chamber 20 (see FIG. 1). That is, independent refrigerant circulation paths are formed in the primary circuit 34 and the secondary circuit 44, respectively. Further, as the primary refrigerant circulating in the primary circuit 34, HC refrigerant such as butane or propane having excellent characteristics as a refrigerant such as heat of evaporation and saturation pressure, ammonia, or the like is adopted and circulated in the secondary circuit 44. As the secondary refrigerant, carbon dioxide having high safety that does not have toxicity, flammability, and corrosivity is employed.

(一次回路)
前記一次回路３４は、気相一次冷媒を圧縮する圧縮機ＣＭと、圧縮した一次冷媒を液化する凝縮器ＣＤと、液相一次冷媒の圧力を低下させる膨張弁ＥＶと、前記プレート式熱交換器ＨＥに設けられて液相一次冷媒を蒸発させる一次熱交換部３６とを備える。そして、一次回路３４においては、凝縮器ＣＤ,膨張弁ＥＶおよび一次熱交換部３６を、液相一次冷媒が流通する一次液配管３８で接続し、一次熱交換部３６,圧縮機ＣＭおよび凝縮器ＣＤを、気相一次冷媒が流通する一次ガス配管４０で接続している(図２参照)。すなわち、一次回路３４では、圧縮機ＣＭによる一次冷媒の圧縮により、圧縮機ＣＭ、凝縮器ＣＤ、膨張弁ＥＶ、一次熱交換部３６(プレート式熱交換器ＨＥ)および圧縮機ＣＭの順に一次冷媒が強制循環し、一次熱交換部３６において液相一次冷媒が気化することでプレート式熱交換器ＨＥを冷却する(図３参照)。 (Primary circuit)
The primary circuit 34 includes a compressor CM for compressing the gas phase primary refrigerant, a condenser CD for liquefying the compressed primary refrigerant, an expansion valve EV for reducing the pressure of the liquid primary refrigerant, and the plate heat exchanger. And a primary heat exchange unit 36 provided in the HE to evaporate the liquid phase primary refrigerant. In the primary circuit 34, the condenser CD, the expansion valve EV, and the primary heat exchange unit 36 are connected by a primary liquid pipe 38 through which the liquid phase primary refrigerant flows, and the primary heat exchange unit 36, the compressor CM, and the condenser are connected. CDs are connected by a primary gas pipe 40 through which a gas phase primary refrigerant flows (see FIG. 2). That is, in the primary circuit 34, the primary refrigerant is compressed in the order of the compressor CM, the condenser CD, the expansion valve EV, the primary heat exchanger 36 (plate heat exchanger HE), and the compressor CM by the compression of the primary refrigerant by the compressor CM. Is forcedly circulated, and the liquid phase primary refrigerant is vaporized in the primary heat exchanging section 36 to cool the plate heat exchanger HE (see FIG. 3).

また、前記圧縮機ＣＭおよび凝縮器ＣＤは、機械室２０において台板２４上に共通的に配設され、凝縮器ＣＤを強制冷却する凝縮器ファンＦＭも、該凝縮器ＣＤに対向して台板２４上に配設される。すなわち、凝縮器ファンＦＭの駆動によりパネル１８に開設した空気流通孔から外気が機械室２０に取込まれて、凝縮器ＣＤおよび圧縮機ＣＭと熱交換するようになっている。なお、前述した制御用電装箱は、機械室２０において凝縮器ファンＦＭによる空気の流れを阻害しない位置(実施例１では機械室２０の側部)で台板２４上に配設されている。   The compressor CM and the condenser CD are commonly disposed on the base plate 24 in the machine room 20, and a condenser fan FM for forcibly cooling the condenser CD is also placed on the stage facing the condenser CD. Arranged on the plate 24. That is, outside air is taken into the machine room 20 from the air circulation hole opened in the panel 18 by driving the condenser fan FM, and heat is exchanged with the condenser CD and the compressor CM. The control electrical box described above is disposed on the base plate 24 at a position that does not obstruct the air flow by the condenser fan FM in the machine room 20 (side of the machine room 20 in the first embodiment). .

(二次回路)
前記二次回路４４は、前記プレート式熱交換器ＨＥに設けられて気相二次冷媒を液化する二次熱交換部４６と、液相二次冷媒を気化する蒸発器ＥＰとを備えている(図２参照)。そして、二次回路４４は、二次熱交換部４６と蒸発器ＥＰとを接続する配管として、二次熱交換部４６から蒸発器ＥＰへ重力の作用下に液相二次冷媒を導く二次液配管４８と、蒸発器ＥＰから二次熱交換部４６へ気相二次冷媒を導く二次ガス配管５０とを有している。ここで、蒸発器ＥＰは台板２４の下方に画成される冷却室２８に配設されて、台板２４内に配設される二次熱交換部４６(プレート式熱交換器ＨＥ)より下方に蒸発器ＥＰが位置するよう構成されている。すなわち、蒸発器ＥＰが二次熱交換部４６(プレート式熱交換器ＨＥ)より下方に配置された二次回路４４では、前記一次回路３４における圧縮機ＣＭの動作により強制冷却されるプレート式熱交換器ＨＥ(二次熱交換部４６)において凝縮された液相二次冷媒が重力作用下に蒸発器ＥＰへ流下し、流下した液相二次冷媒が蒸発器ＥＰにおいて冷却室２８(機械室２０)内の空気と熱交換して蒸発することで二次熱交換部４６に再び戻る冷媒循環サイクルを構成している。なお、前記二次回路４４には、二次ガス配管５０の途中に膨張タンク５４が接続されており、冷却装置３２の停止時に常温では液化しない二次冷媒の圧力上昇を抑制するようになっている(図２参照)。 (Secondary circuit)
The secondary circuit 44 includes a secondary heat exchange unit 46 that is provided in the plate heat exchanger HE and liquefies the gas phase secondary refrigerant, and an evaporator EP that vaporizes the liquid phase secondary refrigerant. (See Figure 2). The secondary circuit 44 is a pipe that connects the secondary heat exchange unit 46 and the evaporator EP, and leads the secondary secondary refrigerant from the secondary heat exchange unit 46 to the evaporator EP under the action of gravity. It has a liquid pipe 48 and a secondary gas pipe 50 that guides the gas phase secondary refrigerant from the evaporator EP to the secondary heat exchange unit 46. Here, the evaporator EP is disposed in the cooling chamber 28 defined below the base plate 24, and from a secondary heat exchange section 46 (plate type heat exchanger HE) disposed in the base plate 24. The evaporator EP is configured to be positioned below. That is, in the secondary circuit 44 in which the evaporator EP is disposed below the secondary heat exchanger 46 (plate heat exchanger HE), the plate heat that is forcibly cooled by the operation of the compressor CM in the primary circuit 34. The liquid phase secondary refrigerant condensed in the exchanger HE (secondary heat exchange section 46) flows down to the evaporator EP under the action of gravity, and the liquid phase secondary refrigerant that has flowed down flows into the cooling chamber 28 (machine room) in the evaporator EP. 20) It constitutes a refrigerant circulation cycle that returns to the secondary heat exchange section 46 by exchanging heat with the air inside and evaporating. An expansion tank 54 is connected to the secondary circuit 44 in the middle of the secondary gas pipe 50 so as to suppress an increase in the pressure of the secondary refrigerant that does not liquefy at room temperature when the cooling device 32 is stopped. (See FIG. 2).

ここで、前記蒸発器ＥＰは、管路を蛇行させた蒸発管(冷媒経路)５２を有し、前記二次液配管４８に接続する蒸発管５２の流入端５２ａが、蒸発器ＥＰの上部に設けられると共に、前記二次ガス配管５０に接続する蒸発管５２の流出端５２ｂが、蒸発器ＥＰの下部に設けられている(図２参照)。すなわち、前記蒸発器ＥＰは、蒸発管５２の流入端５２ａが流出端５２ｂより上方に位置するようになっている。また蒸発管５２は、流入端５２ａと流出端５２ｂとの上下幅の間に延在するよう形成され、蒸発管５２に流入した液相二次冷媒を、重力の作用下に流出端５２ｂ側まで拡散させるように導くようになっている。より具体的には、蒸発管５２は、傾斜する直線部分が上下の関係で葛折り状態で折り重なると共に、屈曲部分が横方向に離間した蛇行形状に管路が形成され、この管路が流入端５２ａ側から流出端５２ｂ側に向かうにつれて下り勾配となるよう構成されている。   Here, the evaporator EP has an evaporation pipe (refrigerant path) 52 having a meandering pipe line, and an inflow end 52a of the evaporation pipe 52 connected to the secondary liquid pipe 48 is formed above the evaporator EP. In addition, an outflow end 52b of the evaporation pipe 52 connected to the secondary gas pipe 50 is provided at the lower part of the evaporator EP (see FIG. 2). That is, the evaporator EP is configured such that the inflow end 52a of the evaporation pipe 52 is located above the outflow end 52b. The evaporation pipe 52 is formed so as to extend between the upper and lower widths of the inflow end 52a and the outflow end 52b, and the liquid-phase secondary refrigerant that has flowed into the evaporation pipe 52 is moved to the outflow end 52b side under the action of gravity. Guided to diffuse. More specifically, the evaporating pipe 52 is formed in a meandering shape in which the inclined straight part is folded in a distorted state in an up-and-down relationship, and the bent part is laterally spaced, and this pipe line is formed at the inflow end. It is comprised so that it may become a downward slope as it goes to the outflow end 52b side from 52a side.

(プレート式熱交換器ＨＥ)
前記プレート式熱交換器ＨＥは、図３に示すように、複数のプレート６０を所要間隔離間するように並列に対向配置して構成され、対向するプレート６０,６０の間に、前記一次回路３４の一次熱交換部３６を構成する第１の流路６０ａと、前記二次回路４４の二次熱交換部４６を構成する第２の流路６０ｂとが並列に複数形成される。ここで、前記第１の流路６０ａと、第２の流路６０ｂとは、前記プレート６０の重ね合わせ方向に交互に位置するよう独立して形成されて、前記一次液配管３８および一次ガス配管４０の夫々が各第１の流路６０ａに連通するよう構成されると共に、前記二次液配管４８および二次ガス配管５０の夫々が各第２の流路６０ｂに連通するよう構成される。すなわち、プレート式熱交換器ＨＥでは、隣接する第１および第２の流路６０ａ,６０ｂに一次冷媒および二次冷媒を独立して流通させることで、各プレート６０を介して一次冷媒および二次冷媒間で熱交換を図るようになっている。 (Plate type heat exchanger HE)
As shown in FIG. 3, the plate heat exchanger HE is configured by arranging a plurality of plates 60 facing each other in parallel so as to be spaced apart from each other, and the primary circuit 34 is disposed between the opposed plates 60, 60. A plurality of first flow paths 60a constituting the primary heat exchange section 36 and a plurality of second flow paths 60b constituting the secondary heat exchange section 46 of the secondary circuit 44 are formed in parallel. Here, the first flow path 60a and the second flow path 60b are independently formed so as to be alternately positioned in the overlapping direction of the plates 60, and the primary liquid pipe 38 and the primary gas pipe. Each of 40 is configured to communicate with each first flow path 60a, and each of the secondary liquid piping 48 and the secondary gas piping 50 is configured to communicate with each second flow path 60b. That is, in the plate heat exchanger HE, the primary refrigerant and the secondary refrigerant are allowed to flow independently through the respective plates 60 by allowing the primary refrigerant and the secondary refrigerant to flow independently through the adjacent first and second flow paths 60a and 60b. Heat is exchanged between the refrigerants.

ここで、図３に示すように、前記プレート式熱交換器ＨＥは、前記第１および第２の流路６０ａ,６０ｂが水平面に対して所要の傾斜角θで交叉するよう前記台板２４内に配設される(図４参照)。そして、プレート式熱交換器ＨＥにおける機械室２０に対向する面側(傾斜上面側)に前記一次液配管３８および一次ガス配管４０を接続し、プレート式熱交換器ＨＥにおける収納室１４に対向する面側(傾斜下面側)に前記二次液配管４８および二次ガス配管５０を接続するよう構成されている。また、前記一次液配管３８および二次液配管４８は、前記プレート式熱交換器ＨＥの同一端部側(図３または図４では傾斜下端部側)で各対応の熱交換部３６,４６に接続されると共に、前記一次ガス配管４０および二次ガス配管５０は、プレート式熱交換器ＨＥにおける一次液配管３８および二次液配管４８から離間する端部側(図３または図４では傾斜上端部側)で各対応の熱交換部３６,４６に接続されている。   Here, as shown in FIG. 3, the plate-type heat exchanger HE is arranged in the base plate 24 so that the first and second flow paths 60a and 60b intersect at a required inclination angle θ with respect to a horizontal plane. (See FIG. 4). The primary liquid pipe 38 and the primary gas pipe 40 are connected to the surface side (inclined upper surface side) facing the machine chamber 20 in the plate heat exchanger HE, and face the storage chamber 14 in the plate heat exchanger HE. The secondary liquid pipe 48 and the secondary gas pipe 50 are connected to the surface side (inclined lower surface side). Further, the primary liquid pipe 38 and the secondary liquid pipe 48 are connected to the corresponding heat exchanging portions 36 and 46 on the same end side (inclined lower end side in FIG. 3 or FIG. 4) of the plate heat exchanger HE. In addition, the primary gas pipe 40 and the secondary gas pipe 50 are connected to the end side away from the primary liquid pipe 38 and the secondary liquid pipe 48 in the plate heat exchanger HE (in FIG. 3 or FIG. Are connected to the corresponding heat exchanging parts 36, 46 on the part side).

なお、以下の説明では、前記プレート式熱交換器ＨＥにおける液配管３８,４８を接続した端部側を基準として、プレート式熱交換器ＨＥと水平面とがなす角を傾斜角θとして表わすものとする。また、一次液配管３８および二次液配管４８から一次ガス配管４０および二次ガス配管５０へ向けてプレート式熱交換器ＨＥが上方傾斜する場合における傾斜角θを正の値とし、該プレート式熱交換器ＨＥが下方傾斜する場合における傾斜角θを負の値とする。   In the following description, the angle between the plate heat exchanger HE and the horizontal plane is expressed as an inclination angle θ with reference to the end portion side where the liquid pipes 38 and 48 are connected in the plate heat exchanger HE. To do. Further, when the plate type heat exchanger HE is inclined upward from the primary liquid pipe 38 and the secondary liquid pipe 48 to the primary gas pipe 40 and the secondary gas pipe 50, the inclination angle θ is set to a positive value. The inclination angle θ when the heat exchanger HE is inclined downward is a negative value.

ここで、前記プレート式熱交換器ＨＥは、傾斜角θが−４°＜θ≦４５°の範囲となるよう前記台板２４に配設される。前記傾斜角４５°＜θに設定した場合には、傾斜配設したプレート式熱交換器ＨＥの高さ寸法が大きくなり過ぎ、該プレート式熱交換器ＨＥの台板２４内への配設が困難となる。また、前記プレート式熱交換器ＨＥの傾斜角θを−４°＜θに設定することで、前記二次回路４４の二次熱交換部４６において二次冷媒を二次ガス配管５０から二次液配管４８へ自然循環させて所要の冷凍能力を発揮し得る一方で、該傾斜角θをθ≦−４°に設定した場合には、二次熱交換部４６において二次冷媒が二次液配管４８から二次ガス配管５０へ循環して冷凍能力の低下を招来する。なお、二次熱交換部４６にける二次ガス配管５０から二次液配管４８への二次冷媒の循環を正循環と指称し、二次液配管４８から二次ガス配管５０への二次冷媒の循環を逆循環と指称する。また、前記二次熱交換部４６で二次冷媒を正循環させつつ、プレート式熱交換器ＨＥを台板２４内に配設するには、傾斜角θを−４°＜θ≦８°に設定するのが好適である。傾斜角θを８°＜θに設定すると、収納室１４と機械室２０との断熱を図るのに必要な厚み寸法以上に台板２４が厚くなる。   Here, the plate heat exchanger HE is disposed on the base plate 24 so that the inclination angle θ is in the range of −4 ° <θ ≦ 45 °. When the inclination angle is set to 45 ° <θ, the height of the inclined plate heat exchanger HE becomes too large, and the plate heat exchanger HE is disposed in the base plate 24. It becomes difficult. Further, by setting the inclination angle θ of the plate heat exchanger HE to −4 ° <θ, the secondary refrigerant is supplied from the secondary gas pipe 50 to the secondary in the secondary heat exchange section 46 of the secondary circuit 44. While the required refrigeration capacity can be exhibited by natural circulation to the liquid pipe 48, the secondary refrigerant is converted into the secondary liquid in the secondary heat exchange unit 46 when the inclination angle θ is set to θ ≦ −4 °. The refrigerant is circulated from the pipe 48 to the secondary gas pipe 50 to cause a reduction in refrigeration capacity. Note that the circulation of the secondary refrigerant from the secondary gas pipe 50 to the secondary liquid pipe 48 in the secondary heat exchange section 46 is referred to as normal circulation, and the secondary refrigerant from the secondary liquid pipe 48 to the secondary gas pipe 50 is referred to. The circulation of the refrigerant is referred to as reverse circulation. In order to arrange the plate heat exchanger HE in the base plate 24 while the secondary refrigerant is normally circulated in the secondary heat exchange section 46, the inclination angle θ is set to −4 ° <θ ≦ 8 °. It is preferable to set. When the inclination angle θ is set to 8 ° <θ, the base plate 24 becomes thicker than the thickness dimension necessary for heat insulation between the storage chamber 14 and the machine chamber 20.

また、前記プレート式熱交換器ＨＥは、前記第２の流路６０ｂにおいて対向するプレート６０,６０の間が例えば１ｍｍ程度の狭小な関係に設定されて、液相二次冷媒の粘性力や表面張力等が作用して、二次回路４４側の第２の流路６０ｂ(二次熱交換部４６)の下部が液相二次冷媒で塞がれる所謂液封が生じるように構成されている(図３参照)。実施例１では、液相二次冷媒の流通により二次熱交換部４６の第２の流路６０ｂに生じる液封部６２(図３参照)が、気相二次冷媒に対する抵抗部として機能し、蒸発器ＥＰで蒸発した気相二次冷媒が逆流するのを防止している。   Further, the plate heat exchanger HE has a narrow relationship of about 1 mm between the opposing plates 60, 60 in the second flow path 60b, for example, so that the viscous force or surface of the liquid phase secondary refrigerant is reduced. The lower part of the second flow path 60b (secondary heat exchanging portion 46) on the secondary circuit 44 side is configured so as to cause a so-called liquid sealing in which the lower portion of the second flow path 60b (secondary heat exchanging portion 46) is closed with the liquid phase secondary refrigerant. (See Figure 3). In the first embodiment, the liquid sealing portion 62 (see FIG. 3) generated in the second flow path 60b of the secondary heat exchange portion 46 due to the circulation of the liquid phase secondary refrigerant functions as a resistance portion with respect to the gas phase secondary refrigerant. The vapor phase secondary refrigerant evaporated in the evaporator EP is prevented from flowing backward.

次に、前述したプレート式熱交換器ＨＥを水平面に対して傾斜角θとなるよう配設する配設方法につき説明する。実施例１では、図８に示すように、前記台板２４の外面を構成する外郭部材２４ａ,２４ａと、前記プレート式熱交換器ＨＥの傾斜上端側との間に突起部２５を設けて、該外郭部材２４ａに対してプレート式熱交換器ＨＥが所定の傾斜角θで位置決めされるよう構成されている。ここで、前記突起部２５は、前記台板２４の外郭部材２４ａ,２４ａまたはプレート式熱交換器ＨＥの何れかに設けられる。また、前記突起部２５は、発泡スチロール等の断熱性能を有する部材により形成される。なお、前記外郭部材２４ａ,２４ａには、プレート式熱交換器ＨＥに接続する各配管３８,４８,４０,５０を挿通する通孔(図示せず)が対応的に開設されており、目地材(図示せず)により各配管３８,４８,４０,５０と通孔との隙間を封止される。   Next, an arrangement method for arranging the plate heat exchanger HE described above at an inclination angle θ with respect to a horizontal plane will be described. In Example 1, as shown in FIG. 8, a protrusion 25 is provided between outer members 24a and 24a constituting the outer surface of the base plate 24 and the inclined upper end side of the plate heat exchanger HE, A plate heat exchanger HE is positioned with respect to the outer member 24a at a predetermined inclination angle θ. Here, the protrusion 25 is provided on either the outer members 24a, 24a of the base plate 24 or the plate heat exchanger HE. Moreover, the said protrusion part 25 is formed with the member which has heat insulation performances, such as a polystyrene foam. The outer members 24a and 24a have correspondingly formed through holes (not shown) through which the pipes 38, 48, 40 and 50 connected to the plate heat exchanger HE are inserted. The gaps between the pipes 38, 48, 40, 50 and the through holes are sealed by (not shown).

そして、プレート式熱交換器ＨＥを台板２４の外郭部材２４ａに対して傾斜させた状態で、各外郭部材２４ａの外側を所定の発泡治具７２,７２で固定すると共に、プレート式熱交換器ＨＥに接続する一次液配管３８および一次ガス配管４０を第１拘束治具７４で固定し、また二次液配管４８および二次ガス配管５０の夫々を第２拘束治具７６で固定する。この状態で、前記外郭部材２４ａ,２４ａ間に発泡材を充填して硬化させ、発泡材が硬化した後に各治具７２,７４,７６の夫々を取り外すことにより、台板２４内にプレート式熱交換器ＨＥが傾斜状態で配設される。その後、前記縦型冷蔵庫１０における箱体１２の天板１２ｂに、前記台板２４を水平に設置することにより、台板２４内に配設された前記プレート式熱交換器ＨＥが水平面に対して傾斜角θで傾斜するようになっている。   The plate-type heat exchanger HE is inclined with respect to the outer member 24a of the base plate 24, and the outer sides of the outer members 24a are fixed by predetermined foaming jigs 72 and 72, and the plate-type heat exchanger The primary liquid pipe 38 and the primary gas pipe 40 connected to the HE are fixed by a first restraining jig 74, and the secondary liquid pipe 48 and the secondary gas pipe 50 are each fixed by a second restraining jig 76. In this state, the outer shell members 24a and 24a are filled with a foaming material and cured, and after the foaming material is cured, the jigs 72, 74, and 76 are removed, so that the plate-type heat is placed in the base plate 24. The exchanger HE is arranged in an inclined state. Thereafter, the plate-type heat exchanger HE disposed in the base plate 24 is placed on the horizontal surface by horizontally installing the base plate 24 on the top plate 12b of the box 12 in the vertical refrigerator 10. It is inclined at an inclination angle θ.

〔実施例１の作用〕
次に、実施例１に係る冷却装置の作用について説明する。 [Operation of Example 1]
Next, the operation of the cooling device according to the first embodiment will be described.

先ず、プレート式熱交換器ＨＥが４°≦θ≦４５°の傾斜角θで配設された場合について説明する。冷却装置３２では、冷却運転を開始すると、一次回路３４および二次回路４４の夫々で冷媒の循環が開始される。このとき、一次回路３４では、圧縮機ＣＤおよび凝縮器ファンＦＭが駆動され、圧縮機ＣＭで圧縮された気相一次冷媒が一次ガス配管４０を介して凝縮器ＣＤに供給され、凝縮器ファンＦＭによる強制冷却により凝縮液化することで液相一次冷媒が得られる。この液相一次冷媒は、一次液配管３８を介して膨張手段ＥＶで減圧され、プレート式熱交換器ＨＥの一次熱交換部３６において二次熱交換部４６を流通する二次冷媒から熱を奪って(吸熱)一挙に膨張気化する。すなわち、一次回路３４は、プレート式熱交換器ＨＥ(二次熱交換部４６)を強制冷却するように機能する。そして、一次熱交換部３６で蒸発した気相一次冷媒は、一次ガス配管４０を経て圧縮機ＣＭに帰還する強制循環サイクルを繰返す。   First, the case where the plate heat exchanger HE is disposed at an inclination angle θ of 4 ° ≦ θ ≦ 45 ° will be described. In the cooling device 32, when the cooling operation is started, circulation of the refrigerant is started in each of the primary circuit 34 and the secondary circuit 44. At this time, in the primary circuit 34, the compressor CD and the condenser fan FM are driven, and the gas phase primary refrigerant compressed by the compressor CM is supplied to the condenser CD through the primary gas pipe 40, and the condenser fan FM. A liquid phase primary refrigerant is obtained by condensing and liquefying by forced cooling. This liquid primary refrigerant is decompressed by the expansion means EV through the primary liquid pipe 38, and takes heat from the secondary refrigerant flowing through the secondary heat exchange section 46 in the primary heat exchange section 36 of the plate heat exchanger HE. (Endothermic) expands and vaporizes all at once. That is, the primary circuit 34 functions to forcibly cool the plate heat exchanger HE (secondary heat exchange unit 46). Then, the gas phase primary refrigerant evaporated in the primary heat exchange unit 36 repeats the forced circulation cycle that returns to the compressor CM through the primary gas pipe 40.

一方、前記二次回路４４では、一次回路３４を循環する一次冷媒により二次熱交換部４６(プレート式熱交換器ＨＥ)が冷却されているから、該二次熱交換部４６においては気相二次冷媒が凝縮して液相二次冷媒に相変化する。ここで、プレート式熱交換器ＨＥを４°≦θ≦４５°の傾斜角θで傾斜させた状態では、二次熱交換部４６(プレート式熱交換器ＨＥ)における二次液配管４８の接続部位が二次ガス配管５０の接続部位より下方に位置している。すなわち、二次液配管４８の接続部位と二次ガス配管５０の接続部位との間に生ずる高低差(ヘッド差)により、気相から液相に変化することで比重が増加した液相二次冷媒が二次熱交換部４６の第２の流路６０ｂに沿って重力の作用下に自然流下する。更に、二次回路４４では、二次熱交換部４６を台板２４内に配置する一方、蒸発器ＥＰを台板２４の下方に位置する冷却室２８に配設することで、二次熱交換部４６と蒸発器ＥＰとの間に落差を設けてある。このため、二次熱交換部４６に接続した二次液配管４８を介して、液相二次冷媒が蒸発器ＥＰへ向けて重力の作用下に自然流下する。液相二次冷媒は、蒸発器ＥＰの蒸発管５２を流通する過程で冷却室２８内の空気と熱交換して蒸発し、気相二次冷媒に状態変化する。そして、気相二次冷媒は、二次ガス配管５０を介して蒸発器ＥＰから二次熱交換部４６へ還流し、二次回路４４ではポンプやモータ等の動力を用いることなく、簡単な構成で二次冷媒が自然循環するサイクルが繰返される。   On the other hand, in the secondary circuit 44, the secondary heat exchange unit 46 (plate heat exchanger HE) is cooled by the primary refrigerant circulating in the primary circuit 34. The secondary refrigerant condenses and changes into a liquid phase secondary refrigerant. Here, in a state where the plate heat exchanger HE is inclined at an inclination angle θ of 4 ° ≦ θ ≦ 45 °, the connection of the secondary liquid piping 48 in the secondary heat exchange section 46 (plate heat exchanger HE) is performed. The part is located below the connection part of the secondary gas pipe 50. That is, the liquid phase secondary whose specific gravity is increased by changing from the gas phase to the liquid phase due to the height difference (head difference) generated between the connection portion of the secondary liquid pipe 48 and the connection portion of the secondary gas pipe 50. The refrigerant naturally flows under the action of gravity along the second flow path 60b of the secondary heat exchange unit 46. Further, in the secondary circuit 44, the secondary heat exchange unit 46 is disposed in the base plate 24, while the evaporator EP is disposed in the cooling chamber 28 located below the base plate 24, thereby performing secondary heat exchange. A head is provided between the portion 46 and the evaporator EP. For this reason, the liquid phase secondary refrigerant naturally flows under the action of gravity toward the evaporator EP via the secondary liquid pipe 48 connected to the secondary heat exchange unit 46. The liquid phase secondary refrigerant evaporates by exchanging heat with the air in the cooling chamber 28 in the process of flowing through the evaporation pipe 52 of the evaporator EP, and changes its state to a gas phase secondary refrigerant. Then, the gas phase secondary refrigerant is refluxed from the evaporator EP to the secondary heat exchange unit 46 via the secondary gas pipe 50, and the secondary circuit 44 has a simple configuration without using power from a pump, a motor, or the like. The cycle in which the secondary refrigerant naturally circulates is repeated.

そして、前記送風ファン３０により吸込口２６ａから冷却室２８に吸引された収納室１４の空気を、冷却された蒸発器ＥＰに吹付けて蒸発器ＥＰと熱交換し、蒸発器ＥＰと熱交換した冷気を冷却室２８から冷気吹出口２６ｂを介して収納室１４に送出することで、収納室１４が冷却される。更に、収納室１４を冷却して温度上昇した空気が吸込口２６ａを介して再び冷却室２８内に戻るサイクルを反復することで、収納室１４内が所定温度まで冷却される。   Then, the air in the storage chamber 14 sucked into the cooling chamber 28 from the suction port 26a by the blower fan 30 is blown onto the cooled evaporator EP to exchange heat with the evaporator EP, and to exchange heat with the evaporator EP. The storage chamber 14 is cooled by sending the cold air from the cooling chamber 28 to the storage chamber 14 via the cold air outlet 26b. Furthermore, the inside of the storage chamber 14 is cooled to a predetermined temperature by repeating a cycle in which the air whose temperature has increased by cooling the storage chamber 14 returns to the cooling chamber 28 again through the suction port 26a.

このように、前記冷却装置３２では、一次回路３４と二次回路４４とをプレート式熱交換器ＨＥで接続したことで、このプレート式熱交換器ＨＥの一次熱交換部３６および二次熱交換部４６において、一次回路３４の一次冷媒と二次回路４４の二次冷媒とが蒸発および凝縮作用下に熱交換を行なう。すなわち、実施例１のプレート式熱交換器ＨＥでは、一次熱交換部３６の一次冷媒と二次熱交換部４６の二次冷媒との間で、相互の潜熱を利用して熱交換するよう構成され、顕熱による熱交換と比べて効率的な熱交換を行なうことができる。   Thus, in the cooling device 32, the primary circuit 34 and the secondary circuit 44 are connected by the plate heat exchanger HE, so that the primary heat exchange unit 36 and the secondary heat exchange of the plate heat exchanger HE are performed. In the part 46, the primary refrigerant of the primary circuit 34 and the secondary refrigerant of the secondary circuit 44 exchange heat under the action of evaporation and condensation. That is, the plate heat exchanger HE according to the first embodiment is configured to perform heat exchange between the primary refrigerant of the primary heat exchange unit 36 and the secondary refrigerant of the secondary heat exchange unit 46 using mutual latent heat. As a result, heat exchange can be performed more efficiently than heat exchange by sensible heat.

ここで、前記プレート式熱交換器ＨＥを傾斜配置したことで、プレート式熱交換器ＨＥを直立状態で設置する場合に較べて、一次液配管３８と一次ガス配管４０との高低差を小さくでき、重力に逆らって流通しつつ蒸発する一次冷媒の密度の上昇割合が抑えられる。このため、プレート式熱交換器ＨＥを直立状態で設置する形態に較べて、一次回路３４での一次冷媒の使用量を減少することができる。前記一次回路３４に必要とされる一次冷媒量を減少することで、法令等で規定された冷媒の使用上限量を上回るのを回避することができ、また一次冷媒として使用する冷媒の種類についての選択肢の幅が広がる。   Here, by arranging the plate heat exchanger HE in an inclined manner, the difference in height between the primary liquid pipe 38 and the primary gas pipe 40 can be reduced as compared with the case where the plate heat exchanger HE is installed in an upright state. The rate of increase in the density of the primary refrigerant that evaporates while circulating against gravity is suppressed. For this reason, compared with the form which installs plate type heat exchanger HE in an upright state, the usage-amount of the primary refrigerant | coolant in the primary circuit 34 can be reduced. By reducing the amount of primary refrigerant required for the primary circuit 34, it is possible to avoid exceeding the use upper limit amount of the refrigerant stipulated by laws and regulations, etc., and the type of refrigerant used as the primary refrigerant A wider range of options.

また、前記プレート式熱交換器ＨＥを傾斜配置する場合には、二次液配管４８と二次ガス配管５０との高低差も小さくなるため、重力作用による二次冷媒の流通量が低下する。このため、熱伝達率の低い顕熱による熱交換を行なう形態では、一次冷媒と二次冷媒との間の熱交換効率の低下を招来して冷却能力が低下する要因となるため、通常は採用し得ない。これに対して、実施例１に係る冷却装置３２は、一次回路３４と二次回路４４とをプレート式熱交換器ＨＥで接続し、この熱交換器ＨＥにおいて一次回路３４の一次冷媒と二次回路４４の二次冷媒とを蒸発および凝縮作用下に熱交換を行なうよう構成されている。すなわち、顕熱に比べて非常に高い熱伝達率を持つ潜熱同士による熱交換がプレート式熱交換器ＨＥで行なわれるから、プレート式熱交換器ＨＥを傾斜配置することにより二次冷媒の重力による自然流下量が減少したとしても、熱交換器ＨＥにおける熱交換量が低下するのを防止でき、冷却装置３２の冷却能力を損なうことはない。   Further, when the plate heat exchanger HE is inclined, the difference in height between the secondary liquid pipe 48 and the secondary gas pipe 50 is also reduced, so that the flow rate of the secondary refrigerant due to the gravity action is reduced. For this reason, in the form of heat exchange by sensible heat with a low heat transfer coefficient, it is usually adopted because it causes a decrease in the heat exchange efficiency between the primary refrigerant and the secondary refrigerant and the cooling capacity decreases. I can't. On the other hand, in the cooling device 32 according to the first embodiment, the primary circuit 34 and the secondary circuit 44 are connected by the plate heat exchanger HE, and the primary refrigerant and the secondary refrigerant of the primary circuit 34 are connected to the heat exchanger HE. The secondary refrigerant of the circuit 44 is configured to exchange heat under the action of evaporation and condensation. That is, since the heat exchange between the latent heats having a very high heat transfer rate compared to the sensible heat is performed in the plate heat exchanger HE, the plate heat exchanger HE is inclined and arranged due to the gravity of the secondary refrigerant. Even if the natural flow rate decreases, it is possible to prevent the heat exchange amount in the heat exchanger HE from decreasing, and the cooling capacity of the cooling device 32 is not impaired.

次に、プレート式熱交換器ＨＥが−４°＜θ＜４°の傾斜角θで配設された場合について説明する。この場合であっても一次回路３４側における一次冷媒の流通過程は、プレート式熱交換器ＨＥを４°≦θ≦４５°の傾斜角θで配設する場合と同様である。すなわち、プレート式熱交換器ＨＥを直立状態で設置する場合に較べて、一次液配管３８と一次ガス配管４０との高低差を小さくできるから、一次冷媒の使用量低減が図られる。   Next, the case where the plate heat exchanger HE is disposed at an inclination angle θ of −4 ° <θ <4 ° will be described. Even in this case, the flow of the primary refrigerant on the primary circuit 34 side is the same as the case where the plate heat exchanger HE is disposed at an inclination angle θ of 4 ° ≦ θ ≦ 45 °. That is, as compared with the case where the plate heat exchanger HE is installed in an upright state, the difference in height between the primary liquid pipe 38 and the primary gas pipe 40 can be reduced, so that the amount of primary refrigerant used can be reduced.

一方で、プレート式熱交換器ＨＥを、傾斜角θが−４°＜θ＜４°の範囲となるまで傾斜させると、二次熱交換部４６における二次液配管４８の接続部位と二次ガス配管５０の接続部位との間に生ずる高低差(ヘッド差)が小さくなり、重力作用による二次冷媒の循環方向が決定し得なくなることから、冷却装置３２の冷凍能力が低下することも考えられる。ここで、プレート式熱交換器ＨＥを傾斜角θが−４°＜θ＜４°の範囲となるまで傾斜させた状態では、前記一次冷媒は蒸発を伴って状態変化することから、一次熱交換部３６は、気相一次冷媒の流出側の温度に較べて液相一次冷媒の流入側の温度が低くなる(図５(a)参照)。すなわち、二次熱交換部４６では、二次ガス配管５０側の温度に較べて二次液配管４８側の温度の方が低くなる。一方、二次熱交換部４６においては、気相二次冷媒が凝縮して液相二次冷媒に相変化することから、凝縮作用の高い低温側(すなわち二次液配管４８側)に液相二次冷媒が集約され(冷媒集約作用)、二次液配管４８を介して液相二次冷媒を蒸発器ＥＰへ流下させ得る。このように、プレート式熱交換器ＨＥを傾斜角θが−４°＜θ＜４°の範囲となるまで傾斜させて設置したとしても、二次熱交換部４６における冷媒集約作用により、二次冷媒が正循環するよう循環方向を決定づけ得るから、冷却装置３２の冷凍能力を維持し得る(図５(a)参照)。なお、プレート式熱交換器ＨＥの傾斜角θをθ≦−４°となるまでプレート式熱交換器ＨＥを傾斜させると、二次熱交換部４６の温度差による二次液配管４８側への液相二次冷媒の集約作用より、ヘッド差に起因して液相二次冷媒が二次液配管４８側から二次ガス配管５０側へ流下する重力作用が上回るようになり、循環方向の逆転を招来する可能性が高くなる。   On the other hand, when the plate-type heat exchanger HE is inclined until the inclination angle θ is in the range of −4 ° <θ <4 °, the secondary liquid piping 48 in the secondary heat exchange section 46 is connected to the secondary portion. The difference in height (head difference) generated between the gas pipe 50 and the connected portion is reduced, and the circulation direction of the secondary refrigerant due to the gravitational action cannot be determined, so that the cooling capacity of the cooling device 32 may be reduced. It is done. Here, in the state in which the plate heat exchanger HE is inclined until the inclination angle θ is in the range of −4 ° <θ <4 °, the primary refrigerant changes its state with evaporation. The temperature of the inflow side of the liquid phase primary refrigerant is lower in the portion 36 than the temperature of the outflow side of the gas phase primary refrigerant (see FIG. 5A). That is, in the secondary heat exchange section 46, the temperature on the secondary liquid pipe 48 side is lower than the temperature on the secondary gas pipe 50 side. On the other hand, in the secondary heat exchange section 46, the gas phase secondary refrigerant condenses and changes into a liquid phase secondary refrigerant, so that the liquid phase is placed on the low temperature side (that is, the secondary liquid piping 48 side) with high condensing action. The secondary refrigerant is collected (refrigerant collecting action), and the liquid phase secondary refrigerant can flow down to the evaporator EP via the secondary liquid pipe 48. Thus, even if the plate-type heat exchanger HE is installed so as to be inclined until the inclination angle θ is in the range of −4 ° <θ <4 °, the secondary heat exchange unit 46 causes the secondary heat exchanging effect to cause the secondary heat exchange. Since the circulation direction can be determined so that the refrigerant circulates normally, the refrigeration capacity of the cooling device 32 can be maintained (see FIG. 5A). If the plate heat exchanger HE is tilted until the tilt angle θ of the plate heat exchanger HE becomes θ ≦ −4 °, the temperature of the secondary heat exchange section 46 is increased to the secondary liquid pipe 48 side. The concentration effect of the liquid phase secondary refrigerant is greater than the gravity effect of the liquid phase secondary refrigerant flowing down from the secondary liquid pipe 48 side to the secondary gas pipe 50 side due to the head difference, and the circulation direction is reversed. Is more likely to be invited.

ところで、収納室１４(冷却室２８)の冷却が充分に進行して、収納室１４(冷却室２８)内の空気と二次冷媒との間の熱交換量が減少すると、一次冷媒と二次冷媒との間の熱交換量も減少する(すなわち冷凍負荷が減少する)。冷凍負荷が減少すると、液相一次冷媒が一次熱交換部３６の流出側(一次ガス配管４０側)まで飽和状態となる。この場合一次熱交換部３６での圧力損失の影響により温度グライドが生ずるため、一次熱交換部３６の流出側(一次ガス配管４０側)の温度が流入側(一次液配管３８側)の温度より低くなり温度勾配の逆転減少が現れる(図５(b)参照)。この場合には、二次回路４４における二次冷媒は、凝縮作用の高い低温側(すなわち二次ガス配管５０側)に集約されることになるため、二次冷媒の循環方向が逆転する。   By the way, when the cooling of the storage chamber 14 (cooling chamber 28) sufficiently proceeds and the amount of heat exchange between the air in the storage chamber 14 (cooling chamber 28) and the secondary refrigerant decreases, the primary refrigerant and the secondary refrigerant The amount of heat exchange with the refrigerant also decreases (that is, the refrigeration load decreases). When the refrigeration load is reduced, the liquid phase primary refrigerant is saturated up to the outflow side (primary gas pipe 40 side) of the primary heat exchange unit 36. In this case, temperature glide is generated due to the pressure loss in the primary heat exchange section 36, so the temperature on the outflow side (primary gas pipe 40 side) of the primary heat exchange section 36 is higher than the temperature on the inflow side (primary liquid pipe 38 side). It becomes lower and the reverse decrease of the temperature gradient appears (see FIG. 5 (b)). In this case, the secondary refrigerant in the secondary circuit 44 is concentrated on the low temperature side (that is, the secondary gas pipe 50 side) having a high condensing action, so that the circulation direction of the secondary refrigerant is reversed.

ここで、実施例１に係るプレート式熱交換器ＨＥでは、一次回路３４における一次液配管３８と二次回路４４における二次液配管４８とを同一端部側に設けると共に、一次回路３４における一次ガス配管４０と二次回路４４における二次ガス配管５０とを同一端部側に設けるよう構成してあるから、通常の運転時には、プレート式熱交換器ＨＥにおける一次冷媒と二次冷媒とは対向流をなし、一次冷媒と二次冷媒との間で効率的な熱交換が行なわれる。一方で、冷却装置３２の冷凍負荷が減少して二次冷媒の流通方向が逆転した場合には、プレート式熱交換器ＨＥにおける一次冷媒と二次冷媒とは平行流をなすため、対向流よりも流体間の温度差が増大して一次冷媒と二次冷媒との間の熱交換効率が低下する。すなわち、実施例１に係る冷却装置３２では、収納室１４内が冷却されて冷却装置３２の冷却能力が過剰になる状況では、二次冷媒の循環方向が逆転することで自動的に冷却能力を抑制し得る。従って、収納室１４の温度に応じて冷却装置３２の冷凍能力を制御する電磁弁等の特別な部品を設ける必要がなく、部品点数の削減によるコスト低減を図り得ると共に、故障等の不具合が発生し難くなることから、冷却装置３２の動作に対する信頼性が向上する。   Here, in the plate heat exchanger HE according to the first embodiment, the primary liquid pipe 38 in the primary circuit 34 and the secondary liquid pipe 48 in the secondary circuit 44 are provided on the same end side, and the primary in the primary circuit 34. Since the gas pipe 40 and the secondary gas pipe 50 in the secondary circuit 44 are provided on the same end side, the primary refrigerant and the secondary refrigerant in the plate heat exchanger HE are opposed to each other during normal operation. A flow is made and efficient heat exchange is performed between the primary refrigerant and the secondary refrigerant. On the other hand, when the refrigeration load of the cooling device 32 decreases and the flow direction of the secondary refrigerant is reversed, the primary refrigerant and the secondary refrigerant in the plate heat exchanger HE form a parallel flow, so that the counter flow However, the temperature difference between the fluids increases and the heat exchange efficiency between the primary refrigerant and the secondary refrigerant decreases. That is, in the cooling device 32 according to the first embodiment, in the situation where the inside of the storage chamber 14 is cooled and the cooling capacity of the cooling device 32 becomes excessive, the cooling capacity is automatically increased by reversing the circulation direction of the secondary refrigerant. Can be suppressed. Accordingly, it is not necessary to provide a special part such as a solenoid valve for controlling the refrigeration capacity of the cooling device 32 according to the temperature of the storage chamber 14, and the cost can be reduced by reducing the number of parts, and troubles such as failure occur Therefore, the reliability of the operation of the cooling device 32 is improved.

ところで、実施例１に係る冷却装置３２の二次回路４４では、蒸発器ＥＰにおける蒸発管５２の流入端５２ａ(二次液配管４８との接続部)を蒸発器ＥＰの上部に設けると共に、流出端５２ｂ(二次ガス配管５０との接続部)を蒸発器ＥＰの下部に設けることで、流入端５２ａを流出端５２ｂより上方に位置させて、流入端５２ａと流出端５２ｂとの間に落差が生ずるよう構成されている。しかも、蒸発管５２は、流出端５２ｂと流入端５２ａとの間において、直線部分が上下の関係で折り重なった蛇行形状とすると共に、流入端５２ａ側から流出端５２ｂ側に向かうにつれて下方傾斜するように管路を形成している。すなわち、蒸発管５２は、二次冷媒が正循環する状況においては、全体として二次冷媒の循環方向前側に向けて下り勾配となるから、流入端５２ａ(二次液配管４８)から蒸発管５２に流入した液相二次冷媒を、重力の作用下に管路に沿って流出端５２ｂ(二次ガス配管５０)側に誘導しつつ蒸発させることができる。従って、冷却装置３２の通常運転時には、蒸発器ＥＰにおいて、蒸発管５２の流入端５２ａ近傍で液相二次冷媒が留まって当該流入端５２ａ近傍で優先的に蒸発するのではなく、二次冷媒が管路に沿って流出端５２ｂ側に自然に拡散することにより、伝熱面積を広く確保して蒸発器ＥＰの熱交換効率を向上し得る(図６参照)。   By the way, in the secondary circuit 44 of the cooling device 32 according to the first embodiment, the inflow end 52a of the evaporator pipe 52 in the evaporator EP (connecting portion with the secondary liquid pipe 48) is provided at the upper part of the evaporator EP and the outflow is performed. By providing the end 52b (connection portion with the secondary gas pipe 50) at the lower part of the evaporator EP, the inflow end 52a is positioned above the outflow end 52b, and there is a drop between the inflow end 52a and the outflow end 52b. Is configured to occur. In addition, the evaporation pipe 52 has a meandering shape in which the linear portion is folded up and down between the outflow end 52b and the inflow end 52a, and is inclined downward from the inflow end 52a toward the outflow end 52b. A pipe line is formed. That is, the evaporation pipe 52 is inclined downward toward the front side in the circulation direction of the secondary refrigerant as a whole in a situation where the secondary refrigerant is normally circulated, and therefore, the evaporation pipe 52 from the inflow end 52a (secondary liquid pipe 48). The liquid phase secondary refrigerant that has flowed into the pipe can be evaporated while being guided to the outflow end 52b (secondary gas pipe 50) side along the pipe line under the action of gravity. Therefore, during normal operation of the cooling device 32, in the evaporator EP, the liquid phase secondary refrigerant stays in the vicinity of the inflow end 52a of the evaporation pipe 52 and does not preferentially evaporate in the vicinity of the inflow end 52a. Is naturally diffused along the conduit toward the outflow end 52b, so that a wide heat transfer area can be secured and the heat exchange efficiency of the evaporator EP can be improved (see FIG. 6).

一方で、冷却装置３２の冷凍負荷が減少して二次冷媒の流通方向が逆転した場合には、液相二次冷媒は二次ガス配管５０側(すなわち流出端５２ｂ側)から前記蒸発器ＥＰに流入し、蒸発器ＥＰで蒸発した気相二次冷媒は二次液配管４８(すなわち流入端５２ａ側)から流出する。すなわち、二次冷媒の流通方向が逆転すると、蒸発器ＥＰでは、二次回路における二次冷媒の循環方向前側に向けて上り勾配となるから、蒸発管５２に流入した液相二次冷媒は、重力作用により蒸発管５２の流出端５２ｂ近傍に留まって優先的に蒸発し、通常運転時とは反対に伝熱面積が小さくなるため、蒸発器ＥＰの熱交換効率が低下する(図７参照)。すなわち、実施例１に係る冷却装置３２では、収納室１４内が冷却されて冷却装置３２の冷却能力が過剰になる状況では、一次冷媒および二次冷媒間での熱交換効率を低下するだけでなく、蒸発器ＥＰでの熱交換効率をも低下させて自動的に冷却能力を抑制し得る。   On the other hand, when the refrigeration load of the cooling device 32 is reduced and the flow direction of the secondary refrigerant is reversed, the liquid phase secondary refrigerant flows from the secondary gas pipe 50 side (that is, the outflow end 52b side) to the evaporator EP. The gas phase secondary refrigerant that has flowed into the evaporator and evaporated in the evaporator EP flows out from the secondary liquid pipe 48 (that is, the inflow end 52a side). That is, when the flow direction of the secondary refrigerant is reversed, the evaporator EP has an upward gradient toward the front side in the circulation direction of the secondary refrigerant in the secondary circuit. Therefore, the liquid phase secondary refrigerant flowing into the evaporation pipe 52 is Gravity action preferentially evaporates by staying in the vicinity of the outflow end 52b of the evaporation pipe 52, and the heat transfer area becomes smaller as opposed to normal operation, so that the heat exchange efficiency of the evaporator EP decreases (see FIG. 7). . That is, in the cooling device 32 according to the first embodiment, in a situation where the inside of the storage chamber 14 is cooled and the cooling capacity of the cooling device 32 becomes excessive, only the heat exchange efficiency between the primary refrigerant and the secondary refrigerant is reduced. In addition, the cooling capacity can be automatically suppressed by reducing the heat exchange efficiency in the evaporator EP.

また、実施例１に係るプレート式熱交換器ＨＥでは、前記台板２４の外郭部材２４ａ,２４ａまたはプレート式熱交換器ＨＥに突起部２５を設けて、当該プレート式熱交換器ＨＥを外郭部材２４ａ上に配設することにより、所定の傾斜角θでプレート式熱交換器ＨＥを傾斜させ、この状態で外郭部材２４ａ,２４ａの間に発泡材を充填・硬化するよう構成されている。すなわち、前記突起部２５を設けるだけでプレート式熱交換器ＨＥを傾斜角θで傾斜させ得るから、プレート式熱交換器ＨＥの位置決めを簡潔に行ない得る。また、外郭部材２４ａ,２４ａの間に発泡材を充填するに先立って、プレート式熱交換器ＨＥに接続する一次液配管３８および一次ガス配管４０を第１拘束治具７４で固定すると共に、二次液配管４８および二次ガス配管５０の夫々を第２拘束治具７６で固定するよう構成してあるから、発泡材の充填・硬化時にプレート式熱交換器ＨＥが位置ズレするのを防止でき、プレート式熱交換器ＨＥを所定の傾斜角θで確実に保持することが可能となる。   Further, in the plate heat exchanger HE according to the first embodiment, the protrusions 25 are provided on the outer members 24a and 24a of the base plate 24 or the plate heat exchanger HE, and the plate heat exchanger HE is used as the outer member. By being disposed on 24a, the plate heat exchanger HE is inclined at a predetermined inclination angle θ, and in this state, the foam material is filled and cured between the outer members 24a, 24a. That is, since the plate heat exchanger HE can be inclined at the inclination angle θ simply by providing the projection 25, the plate heat exchanger HE can be simply positioned. Prior to filling the foam material between the outer members 24a, 24a, the primary liquid pipe 38 and the primary gas pipe 40 connected to the plate heat exchanger HE are fixed by the first restraining jig 74, Since each of the secondary liquid pipe 48 and the secondary gas pipe 50 is configured to be fixed by the second restraining jig 76, it is possible to prevent the plate heat exchanger HE from being displaced during filling and curing of the foam material. The plate heat exchanger HE can be reliably held at a predetermined inclination angle θ.

また、収納室１４と機械室２０とを断熱する台板２４内にプレート式熱交換器ＨＥを埋め込むよう構成することで、該プレート式熱交換器ＨＥの熱損失を防止して一次冷媒と二次冷媒との熱交換効率の向上を図ることができるから、プレート式熱交換器ＨＥの外周を別途設けた断熱材で覆う必要がなく、部品点数削減によるコスト低減と共に、製造工程の簡略化が図られる。特に、収納室１４と機械室２０との断熱を図る台板２４には、断熱性能の高い発泡材が利用されることから、プレート式熱交換器ＨＥに別途断熱材を取り付ける場合に比して断熱性能の向上が図られ、熱損失の低減を効果的に図り得る利点もある。   Further, by configuring the plate heat exchanger HE to be embedded in the base plate 24 that insulates the storage chamber 14 and the machine chamber 20, heat loss of the plate heat exchanger HE is prevented, and the primary refrigerant and Since it is possible to improve the efficiency of heat exchange with the secondary refrigerant, there is no need to cover the outer periphery of the plate heat exchanger HE with a separate heat insulating material, which reduces costs by reducing the number of parts and simplifies the manufacturing process. Figured. In particular, the base plate 24 for heat insulation between the storage chamber 14 and the machine room 20 uses a foam material having high heat insulation performance, so that compared to a case where a separate heat insulation material is attached to the plate heat exchanger HE. There is an advantage that the heat insulation performance can be improved and the heat loss can be effectively reduced.

また、プレート式熱交換器ＨＥを台板２４に埋め込むことにより、前記収納室１４(冷却室２８)とプレート式熱交換器ＨＥとを接続する二次液配管４８および二次ガス配管５０の夫々を低温域にのみ配管することができ、プレート式熱交換器ＨＥを機械室２０に配設して二次液配管４８および二次ガス配管５０を機械室２０内に配管する従来の構成に較べて熱損失の大幅な低減を図り得る。また、二次液配管４８および二次ガス配管５０は低温域(冷却室２８)にのみ配管されるから、これら配管４８,５０を断熱する断熱材を設ける必要がなく、コスト低減を図り得る利点もある。更に、前記プレート式熱交換器ＨＥが台板２４の発泡材で支持されることで、該プレート式熱交換器ＨＥを支持する支持部材を別途設ける必要がなく、構造の簡略化や部品点数削減によるコスト低減を図り得る。   Further, by embedding the plate heat exchanger HE in the base plate 24, each of the secondary liquid pipe 48 and the secondary gas pipe 50 that connect the storage chamber 14 (cooling chamber 28) and the plate heat exchanger HE. Compared to the conventional configuration in which the plate type heat exchanger HE is disposed in the machine room 20 and the secondary liquid pipe 48 and the secondary gas pipe 50 are piped in the machine room 20. Heat loss can be greatly reduced. Further, since the secondary liquid pipe 48 and the secondary gas pipe 50 are piped only in the low temperature region (cooling chamber 28), there is no need to provide a heat insulating material for insulating the pipes 48, 50, and the cost can be reduced. There is also. Further, since the plate heat exchanger HE is supported by the foam material of the base plate 24, it is not necessary to separately provide a support member for supporting the plate heat exchanger HE, and the structure is simplified and the number of parts is reduced. The cost can be reduced.

更に、プレート式熱交換器ＨＥを台板２４内に埋め込むことで、機械室２０に空きスペースを確保でき、機械室２０に配設される凝縮器ＣＤ、凝縮器ファンＦＭ、圧縮機ＣＤ、膨張タンク５４、その他部材の配置の自由度が向上する。また、実施例１に係る冷却装置３２では、凝縮器ファンＦＭの駆動によりキャビネット１６の前側から機械室２０に取込まれて凝縮器ＣＤおよび圧縮機ＣＭと熱交換した空気が膨張タンク５４に吹付けられて、膨張タンク５４が昇温する。ここで、膨張タンク５４に滞留する二次冷媒の量は、圧力および温度に応じて変化する値であり、この圧力は、一次回路３４において運転条件等で決定される蒸発温度に依存するので変化させることができない。そこで、膨張タンク５４を一次回路３４の排熱により昇温することで、膨張タンク５４内の二次冷媒密度が低下するので、膨張タンク５４に滞留する二次冷媒の量を減少させることができる。膨張タンク５４に滞留する二次冷媒の量を減少させると、二次回路４４における二次冷媒量を低減できるメリットがある。   Further, by embedding the plate heat exchanger HE in the base plate 24, an empty space can be secured in the machine room 20, and the condenser CD, the condenser fan FM, the compressor CD, and the expansion provided in the machine room 20 are expanded. The degree of freedom in arranging the tank 54 and other members is improved. Further, in the cooling device 32 according to the first embodiment, the air taken into the machine room 20 from the front side of the cabinet 16 and exchanging heat with the condenser CD and the compressor CM is blown to the expansion tank 54 by driving the condenser fan FM. In addition, the expansion tank 54 is heated. Here, the amount of the secondary refrigerant staying in the expansion tank 54 is a value that changes according to the pressure and temperature, and this pressure changes because it depends on the evaporation temperature determined by operating conditions and the like in the primary circuit 34. I can't let you. Therefore, by raising the temperature of the expansion tank 54 by the exhaust heat of the primary circuit 34, the secondary refrigerant density in the expansion tank 54 is reduced, so that the amount of the secondary refrigerant staying in the expansion tank 54 can be reduced. . If the amount of the secondary refrigerant staying in the expansion tank 54 is reduced, there is an advantage that the amount of secondary refrigerant in the secondary circuit 44 can be reduced.

次に、実施例２に係る冷却装置につき説明する。但し、実施例２に係る冷却装置は、実施例１で説明した冷却装置３２と基本的に同一構成であり、同一の機能を有する部材・構成には同一の符号を付して詳細な説明を省略する。   Next, a cooling device according to the second embodiment will be described. However, the cooling device according to the second embodiment is basically the same in configuration as the cooling device 32 described in the first embodiment, and members / configurations having the same functions are denoted by the same reference numerals and detailed explanations are given. Omitted.

実施例２に係る冷却装置３２では、一次回路３４の一次液配管３８における凝縮器ＣＤと一次熱交換部３６との間に設けられる膨張弁ＥＶとして、流通する液相一次冷媒の温度を検知して絞り度を変更可能な温度検知型の膨張弁が設けられている。具体的には、前記膨張弁ＥＶは、一次液配管３８を流通する液相一次冷媒の温度が所定温度以上に上昇した場合に、絞り度を小さくして一次熱交換部３６へ流通する液相一次冷媒量を減少するよう調整する。   In the cooling device 32 according to the second embodiment, the temperature of the circulating liquid phase primary refrigerant is detected as an expansion valve EV provided between the condenser CD and the primary heat exchange unit 36 in the primary liquid pipe 38 of the primary circuit 34. In addition, a temperature detection type expansion valve that can change the throttle degree is provided. Specifically, the expansion valve EV is configured such that when the temperature of the liquid phase primary refrigerant flowing through the primary liquid pipe 38 rises to a predetermined temperature or more, the expansion degree EV is reduced and the liquid phase flowing to the primary heat exchange unit 36 is reduced. Adjust to reduce the amount of primary refrigerant.

すなわち、前述したようにプレート式熱交換器ＨＥを−４°＜θ＜４°の傾斜角θで配設した状態においては、収納室１４(冷却室２８)内の空気と二次冷媒との間の熱交換量が減少して冷凍負荷が減少すると、液相一次冷媒が一次熱交換部３６の流出側(一次ガス配管４０側)まで飽和状態となり、一次熱交換部３６での圧力損失の影響により温度グライドが生ずる。実施例２に係る冷却装置３２では、一次熱交換部３６において温度グライドが生じ、液相一次冷媒が所定温度に昇温すると、前記一次熱交換部３６へ流通する液相一次冷媒量を減少するよう前記膨張弁ＥＶが絞り度を調整する。すなわち、前記膨張弁ＥＶにより一次熱交換部３６へ流通する液相一次冷媒量が減少することで、一次熱交換部３６における温度グライドの発生が防止でき、一次熱交換部３６における流入側(一次液配管３８側)の温度が、流出側(一次ガス配管４０側)の温度より低温に維持される。このため、二次回路４４では、凝縮作用の高い低温側(すなわち二次液配管４８側)に液相二次冷媒を集約し得るから、二次冷媒の循環方向の逆転現象を防止し得る。また、前記プレート式熱交換器ＨＥにおける一次熱交換部３６を流通する一次冷媒量が減少することにより、一次冷媒と二次冷媒との間の熱交換量が減少するから、収納室１４内が冷却されて冷却装置３２の冷却能力が過剰になる状況では、二次冷媒の循環方向を逆転することなく自動的に冷却能力を抑制し得る。   That is, as described above, in the state in which the plate heat exchanger HE is disposed at the inclination angle θ of −4 ° <θ <4 °, the air in the storage chamber 14 (cooling chamber 28) and the secondary refrigerant When the amount of heat exchange between them decreases and the refrigeration load decreases, the liquid phase primary refrigerant becomes saturated up to the outflow side (primary gas pipe 40 side) of the primary heat exchange unit 36, and the pressure loss in the primary heat exchange unit 36 is reduced. Temperature glide occurs due to the influence. In the cooling device 32 according to the second embodiment, when temperature glide occurs in the primary heat exchange unit 36 and the liquid phase primary refrigerant is heated to a predetermined temperature, the amount of liquid phase primary refrigerant flowing to the primary heat exchange unit 36 is reduced. The expansion valve EV adjusts the degree of throttling. That is, by reducing the amount of the liquid phase primary refrigerant flowing to the primary heat exchange unit 36 by the expansion valve EV, generation of temperature glide in the primary heat exchange unit 36 can be prevented, and the inflow side (primary The temperature of the liquid pipe 38 side) is maintained at a lower temperature than the temperature of the outflow side (primary gas pipe 40 side). For this reason, in the secondary circuit 44, since the liquid phase secondary refrigerant can be concentrated on the low temperature side (that is, the secondary liquid pipe 48 side) having a high condensing action, the reverse phenomenon of the circulation direction of the secondary refrigerant can be prevented. In addition, since the amount of primary refrigerant flowing through the primary heat exchange unit 36 in the plate heat exchanger HE is reduced, the amount of heat exchange between the primary refrigerant and the secondary refrigerant is reduced. In a situation where the cooling capacity of the cooling device 32 becomes excessive due to cooling, the cooling capacity can be automatically suppressed without reversing the circulation direction of the secondary refrigerant.

このように、実施例２に係る冷却装置３２では、温度検知型の膨張弁ＥＶを設けることにより、プレート式熱交換器ＨＥを−４°＜θ＜４°の傾斜角θで配設した状態においても二次冷媒の自然循環方向を一定に維持し得ると共に、冷却装置３２の冷却能力の制御が可能となる。また、実施例２では、一次回路３４に温度検知型の膨張弁ＥＶを設けるようにしたが、プレート式熱交換器ＨＥにおける一次熱交換部３６の容量を大きくしたり、一次回路３４を流通する一次冷媒量を減少することによっても、冷凍負荷が減少する局面において一次熱交換部３６の温度勾配を一定に維持することができ、二次回路４４における二次冷媒の循環方向を一定に保ち得る。   Thus, in the cooling device 32 according to the second embodiment, by providing the temperature detection type expansion valve EV, the plate-type heat exchanger HE is disposed at an inclination angle θ of −4 ° <θ <4 °. In this case, the natural circulation direction of the secondary refrigerant can be kept constant, and the cooling capacity of the cooling device 32 can be controlled. In the second embodiment, the temperature detection type expansion valve EV is provided in the primary circuit 34. However, the capacity of the primary heat exchange unit 36 in the plate heat exchanger HE is increased, or the primary circuit 34 is distributed. By reducing the amount of primary refrigerant, the temperature gradient of the primary heat exchange unit 36 can be kept constant in a phase where the refrigeration load is reduced, and the circulation direction of the secondary refrigerant in the secondary circuit 44 can be kept constant. .

次に、実施例３に係る冷却装置につき説明する。但し、実施例３に係る冷却装置は、実施例１で説明した冷却装置３２と基本的に同一構成であり、同一の機能を有する部材・構成には同一の符号を付して詳細な説明を省略する。   Next, a cooling device according to Embodiment 3 will be described. However, the cooling device according to the third embodiment is basically the same in configuration as the cooling device 32 described in the first embodiment, and members / configurations having the same functions are denoted by the same reference numerals and detailed description is given. Omitted.

実施例３では、プレート式熱交換器ＨＥを水平面に対して傾斜角θとなるよう配設する別の製造方法につき説明する。実施例３に係る冷却装置３２では、図９に示すように、台板２４を構成する外郭部材２４ａに、水平面に対する傾斜角度がθとなる傾斜面８０が形成されており、この傾斜面８０に前記プレート式熱交換器ＨＥを設置することで、プレート式熱交換器ＨＥが水平面に対して傾斜角θで位置決めされるようになっている。そして、プレート式熱交換器ＨＥを台板２４の外郭部材２４ａに対して傾斜させた状態で、各外郭部材２４ａの外側を所定の発泡治具７２,７２で固定すると共に、プレート式熱交換器ＨＥに接続する一次液配管３８および一次ガス配管４０を第１拘束治具７４で固定し、また二次液配管４８および二次ガス配管５０の夫々を第２拘束治具７６で固定する。この状態で、前記外郭部材２４ａ,２４ａ間に発泡材を充填して硬化させ、発泡材が硬化した後に各治具７２,７４,７６の夫々を取り外すことにより、台板２４内にプレート式熱交換器ＨＥが傾斜状態で配設される。その後、前記縦型冷蔵庫１０における箱体１２の天板１２ｂに、前記台板２４を水平に設置することにより、台板２４内に配設された前記プレート式熱交換器ＨＥが水平面に対して傾斜角θで傾斜するよう構成される。   In the third embodiment, another manufacturing method in which the plate heat exchanger HE is disposed at an inclination angle θ with respect to the horizontal plane will be described. In the cooling device 32 according to the third embodiment, as illustrated in FIG. 9, an inclined surface 80 having an inclination angle θ with respect to a horizontal plane is formed on the outer member 24 a configuring the base plate 24. By installing the plate heat exchanger HE, the plate heat exchanger HE is positioned at an inclination angle θ with respect to the horizontal plane. The plate-type heat exchanger HE is inclined with respect to the outer member 24a of the base plate 24, and the outer sides of the outer members 24a are fixed by predetermined foaming jigs 72 and 72, and the plate-type heat exchanger The primary liquid pipe 38 and the primary gas pipe 40 connected to the HE are fixed by a first restraining jig 74, and the secondary liquid pipe 48 and the secondary gas pipe 50 are each fixed by a second restraining jig 76. In this state, the outer shell members 24a and 24a are filled with a foaming material and cured, and after the foaming material is cured, the jigs 72, 74, and 76 are removed, so that the plate-type heat is placed in the base plate 24. The exchanger HE is arranged in an inclined state. Thereafter, the plate-type heat exchanger HE disposed in the base plate 24 is placed on the horizontal surface by horizontally installing the base plate 24 on the top plate 12b of the box 12 in the vertical refrigerator 10. It is configured to incline at an inclination angle θ.

すなわち、実施例３に係る冷却装置３２では、前記台板２４の外郭部材２４ａに傾斜面８０を設けて、当該プレート式熱交換器ＨＥを傾斜面８０上に配設することにより、所定の傾斜角θでプレート式熱交換器ＨＥを傾斜させ得るから、プレート式熱交換器ＨＥの位置決めを簡潔に行ない得る。また、前述と同様に、外郭部材２４ａ,２４ａの間に発泡材を充填するに先立って、プレート式熱交換器ＨＥに接続する一次液配管３８および一次ガス配管４０を第１拘束治具７４で固定すると共に、二次液配管４８および二次ガス配管５０の夫々を第２拘束治具７６で固定するよう構成してあるから、発泡材の充填・硬化時にプレート式熱交換器ＨＥが位置ズレするのを防止でき、プレート式熱交換器ＨＥを所定の傾斜角θで確実に保持することが可能となる。   That is, in the cooling device 32 according to the third embodiment, the outer surface member 24a of the base plate 24 is provided with the inclined surface 80, and the plate heat exchanger HE is disposed on the inclined surface 80, thereby providing a predetermined inclination. Since the plate heat exchanger HE can be inclined at the angle θ, the positioning of the plate heat exchanger HE can be performed simply. Similarly to the above, the primary liquid pipe 38 and the primary gas pipe 40 connected to the plate heat exchanger HE are connected by the first restraining jig 74 prior to filling the foam material between the outer members 24a and 24a. Since the secondary liquid pipe 48 and the secondary gas pipe 50 are each fixed by the second restraining jig 76, the plate heat exchanger HE is displaced when the foam material is filled and cured. Therefore, the plate heat exchanger HE can be reliably held at a predetermined inclination angle θ.

次に、実施例４に係る冷却装置につき説明する。但し、実施例４に係る冷却装置は、実施例１で説明した冷却装置３２と基本的に同一構成であり、同一の機能を有する部材・構成には同一の符号を付して詳細な説明を省略する。   Next, a cooling device according to Embodiment 4 will be described. However, the cooling device according to the fourth embodiment has basically the same configuration as the cooling device 32 described in the first embodiment, and members and configurations having the same functions are denoted by the same reference numerals and detailed description thereof is omitted. Omitted.

実施例４では、プレート式熱交換器ＨＥを水平面に対して傾斜角θとなるよう配設する更に別の製造方法につき説明する。実施例４に係る冷却装置３２では、図１０に示すように、台板２４を構成する外郭部材２４ａに対して前記プレート式熱交換器ＨＥ(一次熱交換部３６および二次熱交換部４６)が平行になるよう設置される。そして、各外郭部材２４ａの外側を所定の発泡治具７２,７２で固定すると共に、プレート式熱交換器ＨＥに接続する一次液配管３８および一次ガス配管４０を第１拘束治具７４で固定し、また二次液配管４８および二次ガス配管５０の夫々を第２拘束治具７６で固定する。この状態で、前記外郭部材２４ａ,２４ａ間に発泡材を充填して硬化させ、発泡材が硬化した後に各治具７２,７４,７６の夫々を取り外すことにより、台板２４と平行になる姿勢でプレート式熱交換器ＨＥが配設される。その後、前記縦型冷蔵庫１０における箱体１２の天板１２ｂに、前記台板２４を傾斜角θで傾斜するよう設置することにより、台板２４内に配設された前記プレート式熱交換器ＨＥが水平面に対して傾斜角θで傾斜するよう構成される。   In the fourth embodiment, another manufacturing method in which the plate heat exchanger HE is disposed at an inclination angle θ with respect to the horizontal plane will be described. In the cooling device 32 according to the fourth embodiment, as shown in FIG. 10, the plate heat exchanger HE (the primary heat exchanging unit 36 and the secondary heat exchanging unit 46) with respect to the outer member 24 a constituting the base plate 24. Are installed in parallel. Then, the outside of each outer member 24a is fixed by predetermined foaming jigs 72, 72, and the primary liquid pipe 38 and the primary gas pipe 40 connected to the plate heat exchanger HE are fixed by the first restraining jig 74. Further, each of the secondary liquid pipe 48 and the secondary gas pipe 50 is fixed by the second restraining jig 76. In this state, the foam member is filled and cured between the outer members 24a and 24a, and after the foam material is cured, the jigs 72, 74, and 76 are removed to be parallel to the base plate 24. A plate type heat exchanger HE is arranged. Thereafter, the plate-type heat exchanger HE disposed in the base plate 24 is installed on the top plate 12b of the box 12 in the vertical refrigerator 10 by inclining the base plate 24 at an inclination angle θ. Is inclined with respect to a horizontal plane at an inclination angle θ.

ここで、外郭部材２４ａを水平面に対して傾斜角θで傾斜するよう台板２４を箱体１２に設置するには、図１１(a)に示すように、箱体１２における前記台板２４を設置する部位に高低差を設けることで、該箱体１２に台板２４を設置した際に、箱体１２の高低差により台板２４を傾斜角θで傾斜させることができる。また、図１１(b)に示すように、台板２４の一端部に下方に垂下する支持部８２を形成すれば、台板２４を箱体１２に設置した際に、支持部８２により台板２４を傾斜角θで傾斜させることが可能となる。   Here, in order to install the base plate 24 in the box 12 so that the outer member 24a is inclined at an inclination angle θ with respect to the horizontal plane, as shown in FIG. By providing a height difference in the installation site, when the base plate 24 is installed in the box 12, the base plate 24 can be inclined at an inclination angle θ due to the height difference of the box 12. Further, as shown in FIG. 11 (b), if a support portion 82 that hangs downward is formed at one end of the base plate 24, the base plate 24 is supported by the support portion 82 when the base plate 24 is installed on the box 12. 24 can be tilted at the tilt angle θ.

このように、実施例４に係る冷却装置３２では、プレート式熱交換器ＨＥを平行に埋め込んだ台板２４を、水平面に対して傾斜角θで傾斜するよう箱体１２に配設することにより、プレート式熱交換器ＨＥも水平面に対して傾斜角θで傾斜させ得る。すなわち、プレート式熱交換器ＨＥを台板２４に配設する際に、該プレート式熱交換器ＨＥ自体の傾斜角θを調整する必要がないから、製造工程の簡略化を図り得る。また台板２４の傾斜により水平面に対するプレート式熱交換器ＨＥの傾斜角θを調整し得るから、台板２４内にプレート式熱交換器ＨＥを傾斜配設する構成に較べて、プレート式熱交換器ＨＥの傾斜角θの調整を容易に行ない得る利点がある。また、前述と同様に、外郭部材２４ａ,２４ａの間に発泡材を充填するに先立って、プレート式熱交換器ＨＥに接続する一次液配管３８および一次ガス配管４０を第１拘束治具７４で固定すると共に、二次液配管４８および二次ガス配管５０の夫々を第２拘束治具７６で固定するよう構成してあるから、発泡材の充填・硬化時にプレート式熱交換器ＨＥが位置ズレするのを防止できる。   As described above, in the cooling device 32 according to the fourth embodiment, the base plate 24 in which the plate heat exchanger HE is embedded in parallel is disposed in the box body 12 so as to be inclined at the inclination angle θ with respect to the horizontal plane. The plate heat exchanger HE can also be inclined at an inclination angle θ with respect to the horizontal plane. That is, when the plate heat exchanger HE is disposed on the base plate 24, it is not necessary to adjust the inclination angle θ of the plate heat exchanger HE itself, so that the manufacturing process can be simplified. In addition, since the inclination angle θ of the plate heat exchanger HE with respect to the horizontal plane can be adjusted by the inclination of the base plate 24, the plate type heat exchange is compared with the configuration in which the plate type heat exchanger HE is inclined in the base plate 24. There is an advantage that the inclination angle θ of the vessel HE can be easily adjusted. Similarly to the above, the primary liquid pipe 38 and the primary gas pipe 40 connected to the plate heat exchanger HE are connected by the first restraining jig 74 prior to filling the foam material between the outer members 24a and 24a. Since the secondary liquid pipe 48 and the secondary gas pipe 50 are each fixed by the second restraining jig 76, the plate heat exchanger HE is displaced when the foam material is filled and cured. Can be prevented.

次に、実施例５に係る冷却装置につき説明する。但し、実施例５に係る冷却装置は、実施例１で説明した冷却装置３２と基本的に同一構成であり、同一の機能を有する部材・構成には同一の符号を付して詳細な説明を省略する。また、実施例５では冷却装置を横型冷蔵庫に設置する場合を例にして説明する。   Next, a cooling device according to Embodiment 5 will be described. However, the cooling device according to the fifth embodiment is basically the same in configuration as the cooling device 32 described in the first embodiment, and members / configurations having the same functions are denoted by the same reference numerals and detailed description is given. Omitted. Moreover, Example 5 demonstrates as an example the case where a cooling device is installed in a horizontal refrigerator.

図１２(a)に示すように、実施例５に係る横型冷蔵庫１２０は、収納室(閉鎖空間)１４を内部画成した断熱構造の箱体１２を横長に形成すると共に、この箱体１２の側方に、機械室(開放空間)２０を画成するキャビネット１６が設けられている。すなわち、実施例５に係る横型冷蔵庫１２０では、一次回路３４と二次回路４４とが左右に並ぶよう配置される。そして、前記一次回路３４の一次熱交換部３６および二次回路４４の二次熱交換部４６を設けたプレート式熱交換器ＨＥが、前記収納室１４と機械室１６とを区画する箱体１２の横壁部１２４内に埋め込むよう配設されている(図１２(b)参照)。このとき、前記一次回路３４における一次液配管３８および二次回路４４における二次液配管４８がプレート式熱交換器ＨＥの下端部に接続されると共に、一次ガス配管４０および二次ガス配管５０が上端部に接続される。なお、図１２(b)では、プレート式熱交換器ＨＥを直立状態で配設した例を示してあるが、該プレート式熱交換器ＨＥを水平面に対して傾斜させるよう横壁部１２４内に配設することも可能である。   As shown in FIG. 12 (a), the horizontal refrigerator 120 according to the fifth embodiment forms a horizontally long box 12 having a heat insulating structure in which a storage room (closed space) 14 is internally defined. A cabinet 16 that defines a machine room (open space) 20 is provided on the side. That is, in the horizontal refrigerator 120 according to the fifth embodiment, the primary circuit 34 and the secondary circuit 44 are arranged side by side. The plate-type heat exchanger HE provided with the primary heat exchanging portion 36 of the primary circuit 34 and the secondary heat exchanging portion 46 of the secondary circuit 44 is a box 12 that partitions the storage chamber 14 and the machine chamber 16. It is arrange | positioned so that it may embed in the horizontal wall part 124 of this (refer FIG.12 (b)). At this time, the primary liquid pipe 38 in the primary circuit 34 and the secondary liquid pipe 48 in the secondary circuit 44 are connected to the lower end of the plate heat exchanger HE, and the primary gas pipe 40 and the secondary gas pipe 50 are connected. Connected to the upper end. FIG. 12 (b) shows an example in which the plate heat exchanger HE is disposed upright. However, the plate heat exchanger HE is disposed in the horizontal wall portion 124 so as to be inclined with respect to the horizontal plane. It is also possible to set up.

このように、横型冷蔵庫１２０における横壁部１２４にプレート式熱交換器ＨＥを埋め込むよう配設した場合であっても、実施例１と同様にプレート式熱交換器ＨＥの熱損失を防止して一次冷媒と二次冷媒との熱交換効率の向上を図ることができ、また部品点数削減によるコスト低減や、製造工程の簡略化が図られる。また、二次液配管４８や二次ガス配管５０に関しても、実施例１と同様に、低温域(収納室１４)にのみ配管されるから、これら配管４８,５０を断熱する断熱材を設ける必要がなく、コスト低減を図り得る利点もある。   Thus, even if it is a case where it arrange | positions so that the plate-type heat exchanger HE may be embedded in the horizontal wall part 124 in the horizontal refrigerator 120, the heat loss of the plate-type heat exchanger HE is prevented similarly to Example 1, and it is primary. The heat exchange efficiency between the refrigerant and the secondary refrigerant can be improved, the cost can be reduced by reducing the number of parts, and the manufacturing process can be simplified. In addition, since the secondary liquid pipe 48 and the secondary gas pipe 50 are also piped only in the low temperature region (the storage chamber 14) as in the first embodiment, it is necessary to provide a heat insulating material that insulates the pipes 48 and 50. There is also an advantage that the cost can be reduced.

次に、実施例６に係る冷却装置につき説明する。但し、実施例６に係る冷却装置は、実施例１で説明した冷却装置３２と基本的に同一構成であり、同一の機能を有する部材・構成には同一の符号を付して詳細な説明を省略する。   Next, a cooling device according to Embodiment 6 will be described. However, the cooling device according to the sixth embodiment is basically the same in configuration as the cooling device 32 described in the first embodiment, and members / configurations having the same functions are denoted by the same reference numerals and detailed explanations are given. Omitted.

実施例６に係る冷却装置３２では、一次冷媒と二次冷媒との間で熱交換を行なう熱交換器として、外管１３０と、該外管１３０内に挿通された内管１３２とから構成された二重管式熱交換器ＨＥ’が用いられている。前記二重管式熱交換器ＨＥ’は、図１３に示すように、渦巻き状に巻回した外管１３０の内側に３本の内管１３２を挿通するよう構成され、該外管１３０内を前記一次冷媒が流通すると共に、各内管１３２内を前記二次冷媒が流通するよう構成される。すなわち、凝縮器ＣＤで凝縮した一次冷媒が蒸発する一次熱交換部として前記外管１３０が機能し、該外管１３０で蒸発した一次冷媒との熱交換により二次冷媒を凝縮する二次熱交換部として前記各内管１３２が機能する。なお、外管１３０内に挿通する内管１３２の数は、３本に限られるものではなく、１本または２本以上の複数の内管１３２を外管１３０内に挿通してもよい。   The cooling device 32 according to the sixth embodiment includes an outer tube 130 and an inner tube 132 inserted into the outer tube 130 as a heat exchanger that exchanges heat between the primary refrigerant and the secondary refrigerant. A double tube heat exchanger HE ′ is used. As shown in FIG. 13, the double pipe heat exchanger HE ′ is configured to insert three inner pipes 132 inside the outer pipe 130 wound in a spiral shape. The primary refrigerant flows, and the secondary refrigerant flows in each inner pipe 132. In other words, the outer pipe 130 functions as a primary heat exchange part in which the primary refrigerant condensed in the condenser CD evaporates, and secondary heat exchange in which the secondary refrigerant is condensed by heat exchange with the primary refrigerant evaporated in the outer pipe 130. Each inner tube 132 functions as a part. Note that the number of inner tubes 132 inserted into the outer tube 130 is not limited to three, and one or more inner tubes 132 may be inserted into the outer tube 130.

そして、前記各内管１３２と蒸発器ＥＰとを接続する二次液配管４８が、前記外管１３０に対して一次液配管３８の接続端側に接続されると共に、該各内管１３２と蒸発器ＥＰとを接続する二次ガス配管５０が、該外管１３０における前記一次ガス配管４０の接続端側に接続され、外管１３０内を流通する一次冷媒と内管１３２内を流通する二次冷媒とが対向流となるよう構成されている。また、実施例６に係る二重管式熱交換器ＨＥ’は、前述した実施例１と同様に、収納室１４と機械室２０とを断熱する台板２４内に埋め込むよう構成され、該二重管式熱交換器ＨＥ’の熱損失を防止して一次冷媒と二次冷媒との熱交換効率の向上を図るようになっている。従って、二重管式熱交換器ＨＥ’の外周を別途設けた断熱材で覆う必要がなく、部品点数削減によるコスト低減と共に、製造工程の簡略化が図られる。特に、収納室１４と機械室２０との断熱を図る台板２４には、断熱性能の高い発泡材が利用されることから、二重管式熱交換器ＨＥ’に別途断熱材を取り付ける場合に比して断熱性能の向上が図られ、熱損失の低減を効果的に図り得る利点もある。また、前述したプレート式熱交換器ＨＥに比べて構成の簡単な二重管式熱交換器ＨＥ’を用いることで、コスト低減が図られる。   A secondary liquid pipe 48 connecting the inner pipes 132 and the evaporator EP is connected to the connection end side of the primary liquid pipe 38 with respect to the outer pipe 130, and the inner pipes 132 are evaporated. A secondary gas pipe 50 that connects the vessel EP is connected to the connection end side of the primary gas pipe 40 in the outer pipe 130, and a primary refrigerant that circulates in the outer pipe 130 and a secondary that circulates in the inner pipe 132. It is comprised so that a refrigerant | coolant may become a counterflow. Further, the double-pipe heat exchanger HE ′ according to the sixth embodiment is configured to be embedded in a base plate 24 that insulates the storage chamber 14 and the machine chamber 20 in the same manner as in the first embodiment. The heat loss of the heavy pipe heat exchanger HE ′ is prevented and the heat exchange efficiency between the primary refrigerant and the secondary refrigerant is improved. Therefore, it is not necessary to cover the outer periphery of the double-pipe heat exchanger HE 'with a separately provided heat insulating material, thereby reducing the cost by reducing the number of parts and simplifying the manufacturing process. In particular, the base plate 24 that insulates the storage room 14 and the machine room 20 uses a foam material having high heat insulation performance. Therefore, when a separate heat insulation material is attached to the double-pipe heat exchanger HE ′. In comparison, the heat insulation performance is improved, and there is an advantage that heat loss can be effectively reduced. In addition, the use of the double-pipe heat exchanger HE 'having a simpler structure than the plate heat exchanger HE described above can reduce the cost.

また、前記二重管式熱交換器ＨＥ’を台板２４内に固定する構成として、前述の実施例１〜５と同様に、台板２４の外郭部材２４ａ,２４ａの間に発泡材を充填するに先立って、二重管式熱交換器ＨＥ’に接続する一次液配管３８および一次ガス配管４０を第１拘束治具７４で固定すると共に、二次液配管４８および二次ガス配管５０の夫々を第２拘束治具７６で固定することで、発泡材の充填・硬化時に二重管式熱交換器ＨＥ’が位置ズレするのを防止でき、二重管式熱交換器ＨＥ’を所定位置で確実に保持することが可能となる。   Further, as a configuration for fixing the double-pipe heat exchanger HE ′ in the base plate 24, a foaming material is filled between the outer members 24a and 24a of the base plate 24 as in the first to fifth embodiments. Prior to this, the primary liquid pipe 38 and the primary gas pipe 40 connected to the double pipe heat exchanger HE ′ are fixed by the first restraining jig 74, and the secondary liquid pipe 48 and the secondary gas pipe 50 are connected. By fixing each with the second restraining jig 76, it is possible to prevent the displacement of the double tube heat exchanger HE 'during filling and curing of the foam material, and the double tube heat exchanger HE' is predetermined. It becomes possible to hold it securely in position.

次に、実施例７に係る冷却装置につき説明する。但し、実施例７に係る冷却装置は、実施例１で説明した冷却装置３２と基本的に同一構成であり、同一の機能を有する部材・構成には同一の符号を付して詳細な説明を省略する。   Next, a cooling device according to Embodiment 7 will be described. However, the cooling device according to the seventh embodiment has basically the same configuration as the cooling device 32 described in the first embodiment, and members and configurations having the same functions are denoted by the same reference numerals and detailed description thereof will be made. Omitted.

図１４に示すように、前記収納室１４と機械室１６とを区画する台板２２４の台板本体２２４ａには、該機械室１６に開口して前記プレート式熱交換器ＨＥを収納可能な収納部２２６が形成されており、該収納部２２６の開口部２２６ａを、断熱蓋体２２８により閉成することで、該プレート式熱交換器ＨＥが台板２２４内に埋め込まれるよう構成されている。なお、前記断熱蓋体２２８は、前記台板本体２２４ａと同一の発泡材を断熱蓋体２２８の外郭体(図示せず)に充填・硬化することで形成される。   As shown in FIG. 14, a base plate body 224 a of a base plate 224 that partitions the storage chamber 14 and the machine chamber 16 is a storage that opens into the machine chamber 16 and can store the plate heat exchanger HE. A portion 226 is formed, and the plate heat exchanger HE is embedded in the base plate 224 by closing the opening 226 a of the storage portion 226 with a heat insulating lid 228. The heat insulating lid 228 is formed by filling and curing the same foam material as that of the base plate main body 224a in an outer body (not shown) of the heat insulating lid 228.

図１４に示すように、前記断熱蓋体２２８は、前記台板本体２２４ａにおける収納部２２６を画成する内壁面２２４ｂと断熱蓋体２２８との間、および前記プレート式熱交換器ＨＥと断熱蓋体２２８との間に、プレート式熱交換器ＨＥ内を循環する冷媒の消炎距離以下の間隔に設定された隙間Ｓが介在する状態で固定される。また、同様に、前記収納部２２６に収納したプレート式熱交換器ＨＥの外周と、前記収納部２２６を画成する内壁面２２４ｂとの間にも隙間Ｓが介在するように、該プレート式熱交換器ＨＥが収納部２２６に設置されている。なお、前記隙間Ｓの間隔は、例えば一次冷媒としてブタンを採用する場合には、１．８ｍｍ以下に設定され、一次冷媒としてプロパンを採用する場合には１．７ｍｍ以下に設定される。   As shown in FIG. 14, the heat insulating lid 228 is formed between the inner wall surface 224 b defining the storage portion 226 in the base plate body 224 a and the heat insulating lid 228, and between the plate heat exchanger HE and the heat insulating lid. Between the body 228, it fixes in the state which the clearance gap S set to the space | interval below the flame extinction distance of the refrigerant | coolant which circulates in the plate type heat exchanger HE is interposed. Similarly, the plate-type heat exchanger 226 is arranged such that a gap S is interposed between the outer periphery of the plate heat exchanger HE stored in the storage portion 226 and the inner wall surface 224b that defines the storage portion 226. The exchanger HE is installed in the storage unit 226. The gap S is set to, for example, 1.8 mm or less when butane is used as the primary refrigerant, and is set to 1.7 mm or less when propane is used as the primary refrigerant.

一方で、前記台板２２４を貫通した二次液配管４８および二次ガス配管５０の周囲に生ずる隙間はパッキン２３０により気密的に閉成される。このパッキン２３０の取り付け構造としては、例えば、図１４に示すように、前記プレート式熱交換器ＨＥと前記二次液配管４８および二次ガス配管５０との接続端部に取り付けたパッキン２３０を、前記台板２２４(台板本体２２４ａ)に密着させるよう構成される。また、パッキン２３０の取り付け構造の別例として、図１５(a)に示すように、二次液配管４８および二次ガス配管５０に取り付けたパッキン２３０を、台板本体２２４ａ内に埋め込むよう構成してもよく、また図１５(b)に示すように、プレート式熱交換器ＨＥおよび台板本体２２４ａの対向面の全面に、シート状に形成したパッキン２３０が密着するよう構成してもよい。すなわち、台板２２４を貫通した二次液配管４８および二次ガス配管５０の周囲に生ずる隙間をパッキン２３０で密閉することで、台板２２４により収納室１４と収納部２２６とが気密的に隔絶される。   On the other hand, a gap generated around the secondary liquid pipe 48 and the secondary gas pipe 50 penetrating the base plate 224 is hermetically closed by the packing 230. As an attachment structure of the packing 230, for example, as shown in FIG. 14, a packing 230 attached to a connecting end portion between the plate heat exchanger HE and the secondary liquid pipe 48 and the secondary gas pipe 50, The base plate 224 (the base plate body 224a) is configured to be in close contact with the base plate 224. As another example of the mounting structure of the packing 230, as shown in FIG. 15A, the packing 230 attached to the secondary liquid pipe 48 and the secondary gas pipe 50 is embedded in the base plate body 224a. Alternatively, as shown in FIG. 15 (b), the packing 230 formed in a sheet shape may be in close contact with the entire opposing surfaces of the plate heat exchanger HE and the base plate body 224a. That is, the gap formed around the secondary liquid pipe 48 and the secondary gas pipe 50 penetrating the base plate 224 is sealed with the packing 230, so that the storage chamber 14 and the storage portion 226 are hermetically separated by the base plate 224. Is done.

このように、前記プレート式熱交換器ＨＥが設置された収納部２２６は、台板本体２２４ａの内壁面２２４ｂと断熱蓋体２２８との間、およびプレート式熱交換器ＨＥと断熱蓋体２２８との間に形成した隙間Ｓを介して機械室１６に連通する一方、収納室１４とは気密的に隔離される。従って、前記収納部２２６内のプレート式熱交換器ＨＥから冷媒が漏出した場合であっても、漏出した冷媒が収納室１４に侵入するのを阻止して、前記隙間Ｓを介して機械室１６側に放散し得る。また、前記隙間Ｓは、冷媒の消炎距離以下に設定されているから、冷媒(実施例７では一次冷媒)として可燃性の冷媒を用いた場合に、該収納部２２６内で冷媒が発火することはない。更に、前記隙間Ｓは、前記プレート式熱交換器ＨＥの略全周囲に形成されているから、冷媒が漏出した場合には、該冷媒を速やかに機械室１６へ放出することができる。   As described above, the storage unit 226 in which the plate heat exchanger HE is installed has a space between the inner wall surface 224b of the base plate body 224a and the heat insulating lid body 228, and between the plate heat exchanger HE and the heat insulating lid body 228. While communicating with the machine room 16 through a gap S formed between them, the storage room 14 is hermetically isolated. Therefore, even if the refrigerant leaks from the plate heat exchanger HE in the storage portion 226, the leaked refrigerant is prevented from entering the storage chamber 14, and the machine chamber 16 is interposed via the gap S. Can dissipate to the side. Further, since the gap S is set to be equal to or less than the flame extinguishing distance of the refrigerant, when a combustible refrigerant is used as the refrigerant (the primary refrigerant in the seventh embodiment), the refrigerant ignites in the storage portion 226. There is no. Further, since the gap S is formed in substantially the entire periphery of the plate heat exchanger HE, when the refrigerant leaks, the refrigerant can be quickly discharged to the machine chamber 16.

更に、実施例７では、台板２２４(台板本体２２４ａ)に形成した収納部２２６にプレート式熱交換器ＨＥを設置した後に、該収納部２２６の開口部２２６ａを断熱蓋体２２８で閉成することにより、台板２２４内にプレート式熱交換器ＨＥが埋め込まれるよう構成したから、実施例１等のように台板２４の外郭部材２４ａの間にプレート式熱交換器ＨＥを配置した状態で発泡材を充填して硬化させる構成に比べて、プレート式熱交換器ＨＥを容易に台板２２４内に埋め込むことが可能となる。また、プレート式熱交換器ＨＥを傾斜配置する場合には、台板２２４(台板本体２２４ａ)に形成した収納部２２６にプレート式熱交換器ＨＥを設置することで、プレート式熱交換器ＨＥの角度調節を容易になし得る利点がある。   Furthermore, in Example 7, after installing plate type heat exchanger HE in the accommodating part 226 formed in the base plate 224 (base plate main body 224a), the opening part 226a of this accommodating part 226 is closed with the heat insulation cover body 228. Since the plate heat exchanger HE is embedded in the base plate 224, the plate heat exchanger HE is disposed between the outer members 24a of the base plate 24 as in the first embodiment. Therefore, the plate heat exchanger HE can be easily embedded in the base plate 224 as compared with the configuration in which the foam material is filled and cured. Further, when the plate heat exchanger HE is inclined, the plate heat exchanger HE is installed in the storage portion 226 formed on the base plate 224 (the base plate body 224a), so that the plate heat exchanger HE is installed. There is an advantage that the angle can be easily adjusted.

次に、実施例８に係る冷却装置につき説明する。但し、実施例８に係る冷却装置は、実施例１で説明した冷却装置３２と基本的に同一構成であり、同一の機能を有する部材・構成には同一の符号を付して詳細な説明を省略する。   Next, a cooling device according to Embodiment 8 will be described. However, the cooling device according to the eighth embodiment has basically the same configuration as the cooling device 32 described in the first embodiment, and members and configurations having the same functions are denoted by the same reference numerals and detailed description thereof will be made. Omitted.

図１６に示すように、前記収納室１４と機械室１６とを区画する台板３２４の台板本体３２４ａには、機械室１６側に突出する台座部３２５が形成されており、該台座部３２５に、該機械室１６に開口して前記プレート式熱交換器ＨＥを収納可能な収納部３２６を形成するよう構成される。そして、前記収納部３２６の開口部３２６ａを、断熱蓋体３２８により閉成することで、該プレート式熱交換器ＨＥが台板３２４内に埋め込まれるよう構成されている。ここで、前述した実施例７と同様に、前記断熱蓋体３２８は、前記台座部３２５における収納部３２６を画成する内壁面３２５ａと断熱蓋体３２８との間、および前記プレート式熱交換器ＨＥと断熱蓋体３２８との間に、プレート式熱交換器ＨＥ内を循環する冷媒の消炎距離以下の間隔に設定された隙間Ｓが介在する状態で固定される。   As shown in FIG. 16, a base plate body 324 a of a base plate 324 that partitions the storage chamber 14 and the machine chamber 16 is formed with a base portion 325 that protrudes toward the machine chamber 16, and the base portion 325. In addition, a storage portion 326 that is open to the machine chamber 16 and can store the plate heat exchanger HE is formed. The plate heat exchanger HE is embedded in the base plate 324 by closing the opening 326a of the storage portion 326 with a heat insulating lid 328. Here, similarly to the above-described seventh embodiment, the heat insulating lid 328 is provided between the inner wall surface 325a defining the storage portion 326 in the pedestal portion 325 and the heat insulating lid 328, and the plate heat exchanger. Between HE and the heat insulation cover body 328, it fixes in the state in which the clearance gap S set to the space | interval below the extinction distance of the refrigerant | coolant which circulates in the plate type heat exchanger HE is interposed.

また、前記プレート式熱交換器ＨＥに接続する二次液配管４８および二次ガス配管５０の夫々は、前記収納部３２６を画成する内底面３２５ｂから台座部３２５の側部に貫通するよう設けられている。すなわち、前記二次液配管４８および二次ガス配管５０は、前記収納部３２６から機械室１６内に一旦導出された後に、前記台板本体３２４ａを貫通して収納室１４側の蒸発器ＥＰに接続される。   In addition, each of the secondary liquid pipe 48 and the secondary gas pipe 50 connected to the plate heat exchanger HE is provided so as to penetrate from the inner bottom surface 325b defining the storage portion 326 to the side portion of the pedestal portion 325. It has been. That is, the secondary liquid pipe 48 and the secondary gas pipe 50 are once led out from the storage portion 326 into the machine chamber 16, and then penetrate the base plate body 324a to the evaporator EP on the storage chamber 14 side. Connected.

そして、台板本体３２４ａを貫通した二次液配管４８および二次ガス配管５０の周囲に生ずる隙間をパッキン３３０により気密的に閉成するようになっている。このパッキン３３０の取り付け構造としては、前記二次液配管４８および二次ガス配管５０との接続端部に取り付けたパッキン３３０を、前記台板３２４(台板本体３２４ａ)に密着させるよう構成される。なお、前述と同様に、二次液配管４８および二次ガス配管５０に取り付けたパッキン３３０を、台板本体３２４ａ内に埋め込むよう構成してもよい。   A gap generated around the secondary liquid pipe 48 and the secondary gas pipe 50 penetrating the base plate main body 324 a is hermetically closed by the packing 330. The packing 330 is attached to the base plate 324 (the base plate body 324a) in close contact with the packing 330 attached to the connection end of the secondary liquid pipe 48 and the secondary gas pipe 50. . As described above, the packing 330 attached to the secondary liquid pipe 48 and the secondary gas pipe 50 may be embedded in the base plate body 324a.

このように、前記プレート式熱交換器ＨＥが設置された収納部３２６は、台座部３２５の内壁面３２５ａと断熱蓋体３２８との間、およびプレート式熱交換器ＨＥと断熱蓋体２２８との間に形成した隙間Ｓを介して機械室１６に連通する。従って、前記収納部３２６内のプレート式熱交換器ＨＥから冷媒が漏出した場合であっても、漏出した冷媒が収納室１４に侵入するのは阻止され、前記隙間Ｓを介して機械室１６側に放散し得る。また、前記隙間Ｓは、冷媒の消炎距離以下に設定されているから、冷媒として可燃性冷媒を用いた場合に、該収納部３２６内で冷媒が発火することはない。更に、実施例８では、台板３２４(台座部３２５)に形成した収納部３２６にプレート式熱交換器ＨＥを設置した後に、該収納部３２６の開口部３２６ａを断熱蓋体３２８で閉成することにより、台板３２４内にプレート式熱交換器ＨＥが埋め込まれるよう構成したから、実施例１等のように台板２４の外郭部材２４ａの間にプレート式熱交換器ＨＥを配置した状態で発泡材を充填して硬化させる構成に比べて、プレート式熱交換器ＨＥを容易に台板３２４内に埋め込むことが可能となる。また、プレート式熱交換器ＨＥを傾斜配置する場合には、台板３２４(台座部３２５)に形成した収納部３２６にプレート式熱交換器ＨＥを設置することで、プレート式熱交換器ＨＥの角度調節を容易になし得る。   As described above, the storage portion 326 in which the plate heat exchanger HE is installed has a space between the inner wall surface 325a of the pedestal portion 325 and the heat insulating lid 328, and between the plate heat exchanger HE and the heat insulating lid 228. It communicates with the machine room 16 through a gap S formed therebetween. Therefore, even if the refrigerant leaks from the plate heat exchanger HE in the storage portion 326, the leaked refrigerant is prevented from entering the storage chamber 14, and the machine chamber 16 side is interposed through the gap S. Can be dissipated. In addition, since the gap S is set to be equal to or shorter than the extinguishing distance of the refrigerant, the refrigerant does not ignite in the storage portion 326 when a combustible refrigerant is used as the refrigerant. Furthermore, in Example 8, after installing the plate-type heat exchanger HE in the storage portion 326 formed on the base plate 324 (base portion 325), the opening 326a of the storage portion 326 is closed by the heat insulating lid 328. Thus, since the plate heat exchanger HE is embedded in the base plate 324, the plate heat exchanger HE is disposed between the outer members 24a of the base plate 24 as in the first embodiment. Compared to the configuration in which the foam material is filled and cured, the plate heat exchanger HE can be easily embedded in the base plate 324. When the plate heat exchanger HE is inclined, the plate heat exchanger HE is installed in the storage portion 326 formed on the base plate 324 (base portion 325), so that the plate heat exchanger HE is installed. The angle can be adjusted easily.

また、前記プレート式熱交換器ＨＥに接続する二次液配管４８および二次ガス配管５０を、前記台座部３２５の収納部３２６から機械室１６へ一旦導出した後に、前記台板本体３２４ａを貫通して収納室１４側の蒸発器ＥＰに接続しているから、該二次液配管４８および二次ガス配管５０と、台座部３２５内に充填された発泡材との間に生ずる微少な隙間(図示せず)を介しても、前記収納部３２６が機械室１６に連通する。従って、プレート式熱交換器ＨＥから冷媒の漏出が発生したとしても、該冷媒が収納室１４に侵入することはない。また、二次液配管４８および二次ガス配管５０を、台座部３２５から機械室１６内に一旦導出した後に、前記台板本体３２４ａを貫通して収納室１４側の蒸発器ＥＰに接続するよう構成したことで、該二次液配管４８および二次ガス配管５０と台板本体３２４ａとを密閉するパッキン３３０が機械室１６に露出する。従って、パッキン３３０が経年的に劣化したとしても、該パッキン３３０を容易に交換し得る利点がある。   Further, the secondary liquid pipe 48 and the secondary gas pipe 50 connected to the plate heat exchanger HE are once led out from the storage portion 326 of the pedestal portion 325 to the machine chamber 16 and then penetrated through the base plate main body 324a. Since it is connected to the evaporator EP on the storage chamber 14 side, a minute gap (between the secondary liquid pipe 48 and the secondary gas pipe 50 and the foamed material filled in the pedestal portion 325 ( The storage portion 326 communicates with the machine room 16 even through a not-shown). Therefore, even if the refrigerant leaks from the plate heat exchanger HE, the refrigerant does not enter the storage chamber 14. Further, the secondary liquid pipe 48 and the secondary gas pipe 50 are once led out from the pedestal portion 325 into the machine chamber 16 and then penetrated through the base plate body 324a to be connected to the evaporator EP on the storage chamber 14 side. With the configuration, the packing 330 that seals the secondary liquid pipe 48 and the secondary gas pipe 50 and the base plate body 324 a is exposed to the machine chamber 16. Therefore, even if the packing 330 deteriorates with time, there is an advantage that the packing 330 can be easily replaced.

(変更例)
本発明に係る冷却装置としては、前述した各実施例のものに限られるものではなく、種々の変更が可能である。 (Example of change)
The cooling device according to the present invention is not limited to the above-described embodiments, and various modifications can be made.

各実施例では、断熱壁部を構成する外郭部材に傾斜面を設けたり、該外郭部材またはプレート式熱交換器に設けた突起部により、プレート式熱交換器を傾斜状態で配置するよう構成したが、プレート式熱交換器の各配管を位置決め固定する治具のみにより、プレート式熱交換器を傾斜状態で位置決めすることもできる。   In each embodiment, the outer member constituting the heat insulating wall is provided with an inclined surface, or the plate heat exchanger is arranged in an inclined state by the protrusion provided on the outer member or the plate heat exchanger. However, it is also possible to position the plate heat exchanger in an inclined state using only a jig for positioning and fixing each pipe of the plate heat exchanger.

また、蒸発器の蒸発管としては、外周に半径方向へ延出するフィンを設けた所謂フィンチューブや、外周に半径方向へ延出するフィンを螺旋状に設けた所謂スパイラルフィンチューブを採用してもよい。また、蒸発管の管路としては、流入端で複数(２系統)の系統に分岐されて、これら複数系統の分岐蒸発管が、循環方向前側に向けて下り勾配となるように蛇行状に延在し、流出端で再びまとめられる構成も採用し得る。   Moreover, as an evaporator tube of the evaporator, a so-called fin tube having a radially extending fin on the outer periphery, or a so-called spiral fin tube having a spiral extending radially on the outer periphery is adopted. Also good. Further, the pipes of the evaporation pipes are branched into a plurality of (two systems) systems at the inflow end, and these plurality of system branch evaporation pipes extend in a meandering manner so as to have a downward slope toward the front side in the circulation direction. It is also possible to adopt a configuration that exists and is brought together again at the outflow end.

各実施例では、蒸発管を流入端側から流出端側に向かうにつれて下方傾斜するように形成したが、全体として流出端側への重力作用下に液化冷媒を拡散し得るのであれば、管路の一部に流出端側に向けて上方傾斜する部位あるいは水平に延在する部位を設けてもよい。   In each embodiment, the evaporation pipe is formed so as to incline downward from the inflow end side to the outflow end side. However, if the liquefied refrigerant can be diffused under the action of gravity toward the outflow end side as a whole, the pipe line A part that is inclined upward toward the outflow end side or a part that extends horizontally may be provided in a part of the part.

各実施例では、二次回路における蒸発器において、二次液配管に接続する流入端を二次ガス配管に接続する流出端より上部に位置するよう構成したが、これに限られるものではなく、二次液配管に接続する流入端を二次ガス配管に接続する流出端より下部に位置するよう構成することも可能である。   In each example, in the evaporator in the secondary circuit, the inflow end connected to the secondary liquid pipe is configured to be located above the outflow end connected to the secondary gas pipe, but is not limited thereto, It is also possible to configure so that the inflow end connected to the secondary liquid pipe is positioned below the outflow end connected to the secondary gas pipe.

各実施例では、気相二次冷媒の逆流を防ぐ手段として、プレート式熱交換器における二次熱交換部の流路に形成される液封部を利用したが、これに限定されず、熱交換器の内部における二次液配管との接続部近傍から二次液配管の間に、気相二次冷媒に対し流通抵抗となる抗力を設ければよい。例えば、熱交換器の内底部または二次液配管の途中に液相二次冷媒を貯留する構成として、この貯留部に溜る二次冷媒のヘッド(水頭)を抵抗部としてもよい。更には、二次液配管に流れ抵抗が大きくなる手段や、絞り部あるいはトラップ等を設ける配管形状としたり、あるいは二次液配管に介挿した逆止弁等も抵抗部として用いることができる。これら種々の態様の抵抗部を単体で用いるだけでなく、実施例１および変更例の構成を組合わせて抵抗部として機能させてもよい。   In each embodiment, as a means for preventing the back flow of the gas phase secondary refrigerant, a liquid seal formed in the flow path of the secondary heat exchange section in the plate heat exchanger is used. What is necessary is just to provide the drag which becomes distribution resistance with respect to a gaseous-phase secondary refrigerant between the secondary liquid piping from the connection part vicinity with the secondary liquid piping in the inside of an exchanger. For example, as a configuration in which the liquid phase secondary refrigerant is stored in the inner bottom portion of the heat exchanger or in the middle of the secondary liquid pipe, a head (water head) of the secondary refrigerant stored in the storage portion may be used as the resistance portion. Furthermore, a means for increasing the flow resistance in the secondary liquid pipe, a pipe shape provided with a throttle part or a trap, or a check valve inserted in the secondary liquid pipe can be used as the resistance part. In addition to using the resistance portions of these various modes alone, the configurations of the first embodiment and the modified example may be combined to function as a resistance portion.

各実施例では、機械室に配設する機器の共通基板となる台板により、機械室と収納室との間で空気の流通がないように収納室と機械室とを区切る構成であるが、機械室と収納室とを箱体の天板で区切る構成であってもよい。   In each embodiment, the storage chamber and the machine room are separated so that there is no air flow between the machine room and the storage room by a base plate that is a common substrate of the equipment disposed in the machine room. The machine room and the storage room may be separated from each other by a box top plate.

各実施例では、冷却装置を冷蔵庫に採用する場合を例にして説明したが、冷凍庫、冷凍・冷蔵庫、ショーケースおよびプレハブ庫等の所謂貯蔵庫、その他空調機器等にも適用可能である。   In each of the embodiments, the case where the cooling device is employed in the refrigerator has been described as an example.

本発明の好適な実施例１に係る冷却装置により冷却される冷蔵庫を示す側断面図である。It is a sectional side view which shows the refrigerator cooled with the cooling device which concerns on suitable Example 1 of this invention. 実施例１に係る冷却装置を示す概略回路図である。1 is a schematic circuit diagram illustrating a cooling device according to Embodiment 1. FIG. 実施例１に係るプレート式熱交換器の断面図である。1 is a cross-sectional view of a plate heat exchanger according to Example 1. FIG. 実施例１に係るプレート式熱交換器の設置状態を示す概略説明図である。It is a schematic explanatory drawing which shows the installation state of the plate type heat exchanger which concerns on Example 1. FIG. 実施例１に係るプレート式熱交換器における温度勾配と二次冷媒の流通方向との関係を示す概略説明図であって、(a)は二次冷媒が正循環する状態を示し、(b)は二次冷媒が逆循環する状態を示す。It is a schematic explanatory drawing which shows the relationship between the temperature gradient in the plate type heat exchanger which concerns on Example 1, and the distribution direction of a secondary refrigerant | coolant, (a) shows the state in which a secondary refrigerant is circulating normally, (b) Indicates a state in which the secondary refrigerant is reversely circulated. 図２に示す蒸発器のＡ−Ａ線断面図であって、二次冷媒が正循環する状態を示す。It is AA sectional view taken on the line of the evaporator shown in FIG. 2, Comprising: The state which a secondary refrigerant | coolant circulates normally is shown. 図２に示す蒸発器のＢ−Ｂ線断面図であって、二次冷媒が逆循環する状態を示す。It is a BB sectional view of the evaporator shown in Drawing 2, and shows the state where a secondary refrigerant carries out reverse circulation. 実施例１に係るプレート式熱交換器の配設方法を示す概略説明図である。It is a schematic explanatory drawing which shows the arrangement | positioning method of the plate type heat exchanger which concerns on Example 1. FIG. 実施例３に係るプレート式熱交換器の配設方法を示す概略説明図である。It is a schematic explanatory drawing which shows the arrangement | positioning method of the plate type heat exchanger which concerns on Example 3. FIG. 実施例４に係るプレート式熱交換器の配設方法を示す概略説明図である。It is a schematic explanatory drawing which shows the arrangement | positioning method of the plate type heat exchanger which concerns on Example 4. FIG. 実施例４に係るプレート式熱交換器を配設した台板を傾斜して配設する配設方法を示す概略説明図であって、(a)は箱体構造により傾斜させる構造を示し、(b)は台板構造により台板を傾斜させる構造を示す。It is a schematic explanatory drawing which shows the arrangement | positioning method which inclines and arrange | positions the base plate which arrange | positioned the plate-type heat exchanger which concerns on Example 4, Comprising: (a) shows the structure made to incline with a box structure, b) shows a structure in which the base plate is inclined by the base plate structure. (a)は、実施例５に係る冷却装置により冷却される横型冷蔵庫を示す側断面図であり、(b)は実施例５に係る冷却装置を示す概略回路図である。(a) is a sectional side view showing a horizontal refrigerator cooled by the cooling device according to the fifth embodiment, and (b) is a schematic circuit diagram showing the cooling device according to the fifth embodiment. 実施例６に係る二重管式熱交換器を模式的に示した説明図である。It is explanatory drawing which showed typically the double tube | pipe type heat exchanger which concerns on Example 6. FIG. 実施例７に係る冷却装置におけるプレート式熱交換器を、台板の収納部に設置した状態で示す概略説明図である。It is a schematic explanatory drawing shown in the state which installed the plate type heat exchanger in the cooling device which concerns on Example 7 in the accommodating part of a baseplate. 実施例７に係るパッキンの取付構造を示す概略説明図であって、(a)はパッキンを台板内に埋め込んだ状態を示し、(b)はプレート式熱交換器および台板本体の対向面の全面にパッキンを密着させた状態を示す。It is a schematic explanatory drawing which shows the attachment structure of the packing which concerns on Example 7, Comprising: (a) shows the state which embedded the packing in the base plate, (b) is the opposing surface of a plate type heat exchanger and a base plate main body. The state where the packing is in close contact with the entire surface is shown. 実施例８に係るプレート式熱交換器を、台板の台座部に形成した収納部に設置した状態で示す概略説明図である。It is a schematic explanatory drawing shown in the state installed in the storage part formed in the base part of the base plate of the plate type heat exchanger which concerns on Example 8. FIG. 従来技術に係る冷却装置を模式的に示した説明図である。It is explanatory drawing which showed typically the cooling device which concerns on a prior art.

符号の説明Explanation of symbols

１４ 収納室(閉鎖空間)，２０ 機械室(開放空間)，２４ 台板(断熱壁部)
３４ 一次回路，３６ 一次熱交換部，４４ 二次回路，４６ 二次熱交換部
１２４ 横壁部(断熱壁部)，２２４ 台板(断熱壁部)，２２４ｂ 内壁面
２２６ 収納部，２２６ａ 開口部，２２８ 断熱蓋体，３２４ 台板(断熱壁部)
３２５ａ 内壁面，３２６ 収納部，３２６ａ 開口部，３２８ 断熱蓋体
ＨＥ プレート式熱交換器(熱交換器)，ＨＥ’ 二重管式熱交換器(熱交換器)
Ｓ 隙間 14 storage room (closed space), 20 machine room (open space), 24 base plate (heat insulation wall)
34 primary circuit, 36 primary heat exchanging part, 44 secondary circuit, 46 secondary heat exchanging part 124 lateral wall part (heat insulation wall part), 224 base plate (heat insulation wall part), 224b inner wall surface 226 storage part, 226a opening part, 228 Thermal insulation cover, 324 Base plate (thermal insulation wall)
325a Inner wall surface, 326 storage, 326a opening, 328 Insulation cover HE plate type heat exchanger (heat exchanger), HE 'double tube heat exchanger (heat exchanger)
S clearance

Claims (4)

一次冷媒を機械的に強制循環する一次回路(34)と、二次冷媒を自然循環する二次回路(44)と、一次冷媒および二次冷媒の間で熱交換する熱交換器(HE,HE’)とを備え、前記一次回路(34)を配設する開放空間(20)と、前記二次回路(44)を配設する閉鎖空間(14)とを断熱壁部(24,124,224,324)により区切るよう構成された冷却装置において、
前記熱交換器(HE,HE’)を前記断熱壁部(24,124,224,324)内に埋め込むよう配設し、
前記断熱壁部(24,124,224,324)は、前記開放空間(20)に開口する開口部(226a,326a)から前記熱交換器(HE,HE’)を収納可能な収納部(226,326)と、前記収納部(226,326)の開口部(226a,326a)を閉成する断熱蓋体(228,328)とを有し、
前記収納部(226,326)の内壁面(224b,325a)と断熱蓋体(228,328)との間に、冷媒の消炎距離以下の間隔に設定された隙間(S)を介在させた
ことを特徴とする冷却装置。 A primary circuit (34) that mechanically circulates the primary refrigerant, a secondary circuit (44) that naturally circulates the secondary refrigerant, and a heat exchanger (HE, HE that exchanges heat between the primary refrigerant and the secondary refrigerant) '), And an open space (20) in which the primary circuit (34) is disposed and a closed space (14) in which the secondary circuit (44) is disposed are separated by a heat insulating wall (24, 124, 224, 324). In the configured cooling device,
The heat exchanger (HE, HE ′) is disposed so as to be embedded in the heat insulating wall (24, 124, 224, 324) ,
The heat insulating wall portions (24, 124, 224, 324) include storage portions (226, 326) that can store the heat exchangers (HE, HE ') from openings (226a, 326a) that open to the open space (20), and the storage portions. A heat insulating lid (228,328) for closing the opening (226a, 326a) of (226,326),
A gap (S) set at an interval equal to or less than the extinguishing distance of the refrigerant is interposed between the inner wall surface (224b, 325a) of the storage portion (226, 326) and the heat insulating lid (228, 328). A cooling device characterized by. 前記断熱蓋体(228,328)と熱交換器(HE,HE’)との間に、冷媒の消炎距離以下の間隔に設定された隙間(S)を介在させた請求項１記載の冷却装置。 The heat insulating lid (228,328) and the heat exchanger (HE, HE ') and between the cooling apparatus of claim 1, wherein the set gap quenching distance following intervals refrigerant (S) is interposed. 前記熱交換器(HE)は、複数のプレート(60)を所要間隔離間するように並列に対向配置し、対向するプレート(60,60)の間に形成される流路(60a,60b)に、前記一次冷媒および二次冷媒が交互に流通させるよう構成される請求項１または２記載の冷却装置。 In the heat exchanger (HE), a plurality of plates (60) are arranged opposite to each other in parallel so as to be spaced apart from each other, and flow paths (60a, 60b) formed between the opposed plates (60, 60). The cooling device according to claim 1 or 2 , wherein the primary refrigerant and the secondary refrigerant are configured to flow alternately. 前記熱交換器(HE’)は、外管(130)と、前記外管(130)の内部に挿通された内管(132)とから構成され、前記外管(130)および内管(132)に、前記一次冷媒および二次冷媒を対向流となるよう流通させるよう構成される請求項１または２記載の冷却装置。 The heat exchanger (HE ′) includes an outer tube (130) and an inner tube (132) inserted into the outer tube (130). The outer tube (130) and the inner tube (132) 3) The cooling device according to claim 1 or 2 , wherein the primary refrigerant and the secondary refrigerant are circulated in a counter flow.
JP2007252732A 2007-09-27 2007-09-27 Cooling system Expired - Fee Related JP5139019B2 (en)

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