JP3334538B2 - Air conditioner - Google Patents

Air conditioner

Info

Publication number
JP3334538B2
JP3334538B2 JP02641997A JP2641997A JP3334538B2 JP 3334538 B2 JP3334538 B2 JP 3334538B2 JP 02641997 A JP02641997 A JP 02641997A JP 2641997 A JP2641997 A JP 2641997A JP 3334538 B2 JP3334538 B2 JP 3334538B2
Authority
JP
Japan
Prior art keywords
heat exchanger
refrigerant
tube
supercooling
expansion mechanism
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
JP02641997A
Other languages
Japanese (ja)
Other versions
JPH10220898A (en
Inventor
武夫 植野
英樹 辻井
政樹 山本
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Daikin Industries Ltd
Original Assignee
Daikin Industries Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Daikin Industries Ltd filed Critical Daikin Industries Ltd
Priority to JP02641997A priority Critical patent/JP3334538B2/en
Publication of JPH10220898A publication Critical patent/JPH10220898A/en
Application granted granted Critical
Publication of JP3334538B2 publication Critical patent/JP3334538B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers

Landscapes

  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Description

【発明の詳細な説明】DETAILED DESCRIPTION OF THE INVENTION

【０００１】[0001]

【発明の属する技術分野】この発明は、過冷却方式を採
用した空気調和機に関する。The present invention relates to an air conditioner employing a supercooling system.

【０００２】[0002]

【従来の技術】従来、この種の空気調和機としては、図
６に示すものがある(特開平６−３３１２２３号公報)。
この空気調和機は、主回路と過冷却回路からなる。上記
主回路は、圧縮機１０１と凝縮器１０２と熱交換器内蔵
高圧レシーバ１０３とメイン膨張弁１０５と蒸発器１０
６とアキュムレータ１０７とが順に接続された回路で構
成されている。また、上記過冷却回路は、上記高圧レシ
ーバ１０３の出口から過冷却用膨張弁１０８を経由して
レシーバ１０３が内蔵する過冷却用コイル１１０に接続
され、このコイル１１０から上記アキュムレータ１０７
の入口に接続された回路で構成されている。2. Description of the Related Art A conventional air conditioner of this type is shown in FIG. 6 (JP-A-6-331223).
This air conditioner includes a main circuit and a subcooling circuit. The main circuit includes a compressor 101, a condenser 102, a high-pressure receiver 103 with a built-in heat exchanger, a main expansion valve 105, and an evaporator 10
6 and an accumulator 107 are sequentially connected. The supercooling circuit is connected from the outlet of the high-pressure receiver 103 to a supercooling coil 110 built in the receiver 103 via a subcooling expansion valve 108, and from the coil 110 to the accumulator 107.
It is composed of a circuit connected to the entrance of.

【０００３】この空気調和機は、上記凝縮器１０２から
の高温冷媒を、高圧レシーバ１０３を経て過冷却用膨張
弁１０８を通過させて低温にし、この低温にした冷媒を
過冷却用コイル１１０に通して、凝縮器１０２から高圧
レシーバ１０３に入った高温冷媒を冷やす。これによ
り、蒸発器１０６における冷凍効果を増大させることが
できる。In this air conditioner, the high-temperature refrigerant from the condenser 102 passes through a high-pressure receiver 103, passes through a supercooling expansion valve 108, and is cooled, and the low-temperature refrigerant is passed through a supercooling coil 110. Then, the high-temperature refrigerant that has entered the high-pressure receiver 103 from the condenser 102 is cooled. Thereby, the refrigeration effect in the evaporator 106 can be increased.

【０００４】[0004]

【発明が解決しようとする課題】しかし、上記従来の空
気調和機では、冷媒流の方向は、圧縮機１０１から凝縮
器１０２、凝縮器１０２から蒸発器１０６の方向に限ら
れる。もし、仮に、四路切換弁を設けて、冷媒流の方向
を逆にして、この蒸発器１０６を凝縮器、この凝縮器１
０２を蒸発器として用いようとしても、過冷却回路を正
常に働かせることができない。However, in the above-described conventional air conditioner, the direction of the refrigerant flow is limited to the direction from the compressor 101 to the condenser 102 and from the condenser 102 to the evaporator 106. If a four-way switching valve is provided to reverse the direction of the refrigerant flow, the evaporator 106 is used as a condenser,
Even if an attempt is made to use 02 as an evaporator, the subcooling circuit cannot operate normally.

【０００５】そこで、この発明の目的は、冷媒流れ方向
を切り換えても、変わりなく過冷却の効果を得ることが
できる空気調和機を提供することにある。An object of the present invention is to provide an air conditioner that can obtain a supercooling effect without changing the refrigerant flow direction.

【０００６】[0006]

【課題を解決するための手段】上記目的を達成するた
め、請求項１の発明の空気調和機は、圧縮機と、四路切
換弁と、一端が上記四路切換弁に接続された室外熱交換
器と、メイン膨張機構と、一端が上記四路切換弁に接続
された室内熱交換器とを備えた空気調和機において、第
１端から第２端に向かって順方向の第１逆止弁と第２端
から第３端に向かって逆方向の第２逆止弁と第３端から
第４端に向かって逆方向の第３逆止弁と第４端から第１
端に向かって順方向の第４逆止弁とで構成され、上記第
１端が上記室外熱交換器の他端に接続され、上記第３端
が上記室内熱交換器の他端に接続され、上記第２端と第
４端との間に上記メイン膨張機構が接続されたブリッジ
整流回路と、上記ブリッジ整流回路の第２端と上記圧縮
機の吸込口との間に接続され、上記第２端から上記メイ
ン膨張機構への冷媒を冷やすように配置された過冷却用
熱交換器と、上記第２端と上記過冷却用熱交換器との間
に接続された過冷却用膨張機構とを備え、 一端が上記メ
イン膨張機構に接続され、他端が開放された内管と、上
記内管の一端と他端との間の部分を包み、一端側が上記
圧縮機の吸入口に接続され、他端側端部にオリフィスが
形成された中管と、上記内管および中管を包み、一端側
が上記ブリッジ整流回路の第２端に接続された外管とで
構成された三重管式熱交換器が、上記過冷却用熱交換器
と過冷却用膨張機構とを構成したことを特徴としてい
る。According to a first aspect of the present invention, there is provided an air conditioner comprising: a compressor, a four-way switching valve, and an outdoor heat exchanger having one end connected to the four-way switching valve. A first check in a forward direction from a first end to a second end in an air conditioner including an exchanger, a main expansion mechanism, and an indoor heat exchanger having one end connected to the four-way switching valve. A second check valve in the opposite direction from the valve to the third end from the second end; a third check valve in the opposite direction from the third end to the fourth end;
A fourth check valve in a forward direction toward the end, wherein the first end is connected to the other end of the outdoor heat exchanger, and the third end is connected to the other end of the indoor heat exchanger. A bridge rectifier circuit having the main expansion mechanism connected between the second end and the fourth end, and a bridge rectifier circuit connected between a second end of the bridge rectifier circuit and a suction port of the compressor; A supercooling heat exchanger arranged to cool the refrigerant from two ends to the main expansion mechanism, and a supercooling expansion mechanism connected between the second end and the supercooling heat exchanger. equipped with a, one end of the main
An inner tube connected to the in-expansion mechanism and open at the other end;
Wrap the part between one end and the other end of the inner tube, one end
The orifice is connected to the suction port of the compressor and the other end
The formed inner tube and the inner tube and the inner tube are wrapped around one end.
Is the outer tube connected to the second end of the bridge rectifier circuit.
The configured triple tube heat exchanger is
And a supercooling expansion mechanism .

【０００７】この請求項１の発明によれば、上記四路切
換弁を冷房位置にすれば、冷媒は、順に、室内熱交換
器、圧縮機、室外熱交換器、ブリッジ整流回路と流れ、
室外熱交換器は凝縮器として働き、室内熱交換器は蒸発
器として働く。According to the first aspect of the present invention, when the four-way switching valve is set to the cooling position, the refrigerant flows sequentially through the indoor heat exchanger, the compressor, the outdoor heat exchanger, and the bridge rectifier circuit.
The outdoor heat exchanger acts as a condenser and the indoor heat exchanger acts as an evaporator.

【０００８】上記凝縮器としての室外熱交換器からの冷
媒は、上記ブリッジ整流回路の第１端に入り、第１逆止
弁を通過し第２端から出た冷媒のメイン流はメイン膨張
弁を通過して、上記ブリッジ整流回路の第４端に入り、
第３逆止弁を通って蒸発器として働く室内熱交換器に達
する。Refrigerant from the outdoor heat exchanger as the condenser enters the first end of the bridge rectifier circuit, passes through the first check valve, and exits from the second end. Through the fourth end of the bridge rectifier circuit,
A third non-return valve leads to an indoor heat exchanger acting as an evaporator.

【０００９】一方、上記第１逆止弁を通過し第２端から
出た冷媒の残りの部分は、過冷却用膨張機構を通過する
ことで冷やされてから、過冷却用熱交換器に達し、この
過冷却用熱交換器に達した冷えた冷媒は、上記ブリッジ
回路の第２端からメイン膨張弁に向かう冷媒を冷やして
から、圧縮機の吸込口に達する。On the other hand, the remaining portion of the refrigerant that has passed through the first check valve and exited from the second end is cooled by passing through the subcooling expansion mechanism, and then reaches the supercooling heat exchanger. The cooled refrigerant that has reached the supercooling heat exchanger cools the refrigerant flowing from the second end of the bridge circuit to the main expansion valve, and then reaches the suction port of the compressor.

【００１０】また、上記四路切換弁を暖房位置にすれ
ば、冷媒は、順に、圧縮機、室内熱交換器、ブリッジ整
流回路、室外熱交換器と流れ、室内熱交換器は凝縮器と
して働き、室外熱交換器は蒸発器として働く。When the four-way switching valve is set to the heating position, the refrigerant flows sequentially through the compressor, the indoor heat exchanger, the bridge rectifier circuit, and the outdoor heat exchanger, and the indoor heat exchanger functions as a condenser. , The outdoor heat exchanger acts as an evaporator.

【００１１】上記凝縮器としての室内熱交換器からの冷
媒は、上記ブリッジ整流回路の第３端に入り、第２逆止
弁を通過し第２端から出た冷媒のメイン流はメイン膨張
弁を通過して、上記ブリッジ整流回路の第４端に入り、
第４逆止弁を通って蒸発器として働く室外熱交換器に達
する。Refrigerant from the indoor heat exchanger as the condenser enters the third end of the bridge rectifier circuit, passes through the second check valve, and exits from the second end. Through the fourth end of the bridge rectifier circuit,
Through a fourth check valve, an outdoor heat exchanger serving as an evaporator is reached.

【００１２】一方、上記第２逆止弁を通過し第２端から
出た冷媒の残りの部分は、過冷却用膨張機構を通過する
ことで冷やされてから、過冷却用熱交換器に達し、この
過冷却用熱交換器に達した冷えた冷媒は、上記ブリッジ
回路の第２端からメイン膨張弁に向かう冷媒を冷やして
から、圧縮機の吸込口に達する。On the other hand, the remaining portion of the refrigerant that has passed through the second check valve and exited from the second end is cooled by passing through the subcooling expansion mechanism, and then reaches the supercooling heat exchanger. The cooled refrigerant that has reached the supercooling heat exchanger cools the refrigerant flowing from the second end of the bridge circuit to the main expansion valve, and then reaches the suction port of the compressor.

【００１３】このように、この発明によれば、四路切換
弁を冷房位置にしたときには、凝縮器として働く室外熱
交換器からの冷媒のサブ流を過冷却用膨張機構と過冷却
用熱交換器とで冷やし、この冷えた冷媒でメイン流の冷
媒を冷やした上で、蒸発器として働く室内熱交換器に導
入する。したがって、蒸発器としての室内熱交換器の能
力と効率の向上を図れる。したがって、冷房能力の向上
を図れ、かつ、冷房効率の向上を図れる。As described above, according to the present invention, when the four-way switching valve is in the cooling position, the sub-flow of the refrigerant from the outdoor heat exchanger serving as a condenser is exchanged with the subcooling expansion mechanism and the subcooling heat exchange. After cooling the main stream refrigerant with the cooled refrigerant, the refrigerant is introduced into an indoor heat exchanger serving as an evaporator. Therefore, the performance and efficiency of the indoor heat exchanger as an evaporator can be improved. Therefore, the cooling capacity can be improved and the cooling efficiency can be improved.

【００１４】また、四路切換弁を暖房位置にしたときに
は、凝縮器として働く室内熱交換器からの冷媒のサブ流
を過冷却用膨張機構と過冷却用熱交換器とで冷やし、こ
の冷えた冷媒でメイン流の冷媒を冷やした上で、蒸発器
として働く室外熱交換器に導入する。したがって、蒸発
器としての室外熱交換器の能力と効率の向上を図れる。
したがって、暖房能力の向上を図れ、かつ、暖房効率の
向上を図れる。When the four-way switching valve is set to the heating position, the sub-flow of the refrigerant from the indoor heat exchanger serving as a condenser is cooled by the subcooling expansion mechanism and the subcooling heat exchanger, and the cooled sub-flow is cooled. After cooling the main stream refrigerant with the refrigerant, the refrigerant is introduced into an outdoor heat exchanger that functions as an evaporator. Therefore, the performance and efficiency of the outdoor heat exchanger as an evaporator can be improved.
Therefore, the heating capacity can be improved, and the heating efficiency can be improved.

【００１５】したがって、この発明によれば、冷媒流れ
方向を切り換えても、変わりなく過冷却の効果を得るこ
とができる。Therefore, according to the present invention, even if the flow direction of the refrigerant is switched, the effect of supercooling can be obtained without any change.

【００１６】また、この請求項１の発明によれば、ブリ
ッジ整流回路の第２端から外管の一端側に流入した冷媒
は、外管の他端側に至り、サブ流が中管の他端側端部の
オリフィスから中管内に膨張しながら流入する。この膨
張によりサブ流入冷媒が冷え、この冷えたサブ流入冷媒
は、上記外管の他端側から内管の開放他端に流入してメ
イン膨張機構に向かうメイン流入冷媒を冷やし、同時
に、外管の一端側から他端側に向かう冷媒(メイン流＋
サブ流)を冷やす。このように、この三重管式熱交換器
は、冷えたサブ流入冷媒が流れる中管の内側と外側と
に、冷媒のメイン流が流れる外管と内管とを配している
から、冷えたサブ流入冷媒とメイン流との熱交換効率が
良い。したがって、過冷却の増大を図れ、能力,効率を
一層増大させることができる。また、この三重管式熱交
換器によって、過冷却用熱交換器と過冷却用膨張機構と
が一体化されるから、配管が簡単になり、全体がコンパ
クトになる。 [0016] According to the invention of claim 1, refrigerant from the second end of the bridge rectifier circuit has flown into one end of the outer tube, it reaches the other end of the outer tube, the other middle tube sub stream It flows into the middle pipe while expanding from the orifice at the end side. This expansion cools the sub-inflow refrigerant, and the cooled sub-inflow refrigerant flows from the other end of the outer tube into the open other end of the inner tube, cools the main inflow refrigerant toward the main expansion mechanism, and at the same time, cools the outer tube. Refrigerant flowing from one end to the other end (main flow +
Sub flow). As described above, the triple tube heat exchanger is cooled because the outer tube and the inner tube through which the main flow of the refrigerant flows are arranged inside and outside the middle tube through which the cooled sub-inflow refrigerant flows. Good heat exchange efficiency between the sub-inflow refrigerant and the main flow. Therefore, the supercooling can be increased, and the capacity and efficiency can be further increased. Further, since the triple-tube heat exchanger integrates the supercooling heat exchanger and the supercooling expansion mechanism, the piping is simplified and the whole becomes compact.

【００１７】また、請求項２の発明の空気調和機は、圧
縮機と、四路切換弁と、一端が上記四路切換弁に接続さ
れた室外熱交換器と、メイン膨張機構と、一端が上記四
路切換弁に接続された室内熱交換器とを備えた空気調和
機において、第１端から第２端に向かって順方向の第１
逆止弁と第２端から第３端に向かって逆方向の第２逆止
弁と第３端から第４端に向かって逆方向の第３逆止弁と
第４端から第１端に向かって順方向の第４逆止弁とで構
成され、上記第１端が上記室外熱交換器の他端に接続さ
れ、上記第３端が上記室内熱交換器の他端に接続され、
上記第２端と第４端との間に上記メイン膨張機構が接続
されたブリッジ整流回路と、上記ブリッジ整流回路の第
２端と上記圧縮機の吸込口との間に接続され、上記第２
端から上記メイン膨張機構への冷媒を冷やすように配置
された過冷却用熱交換器と、上記第２端と上記過冷却用
熱交換器との間に接続された過冷却用膨張機構とを備
え、 一端が上記ブリッジ整流回路の第２端に接続され、
他端が開放された内管と、上記内管の一端と他端との間
の部分を包み、一端側が上記圧縮機の吸入口に接続さ
れ、他端側端部にオリフィスが形成された中管と、上記
内管および中管を包み、一端側が上記メイン膨張機構に
接続された外管とで構成された三重管式熱交換器が、上
記過冷却用熱交換器と過冷却用膨張機構とを構成したこ
とを特徴としている。Further, the air conditioner of the invention according to claim 2 is a compressor, a four-way switching valve, an outdoor heat exchanger having one end connected to the four-way switching valve, a main expansion mechanism, and one end. In the air conditioner provided with the indoor heat exchanger connected to the four-way switching valve, the first air conditioner is arranged in a forward direction from the first end to the second end.
A check valve, a second check valve in a reverse direction from the second end to the third end, a third check valve in a reverse direction from the third end to the fourth end, and a fourth check valve from the fourth end to the first end. A fourth check valve in the forward direction, the first end is connected to the other end of the outdoor heat exchanger, the third end is connected to the other end of the indoor heat exchanger,
A bridge rectifier circuit in which the main expansion mechanism is connected between the second end and the fourth end; and a second rectifier circuit connected between the second end of the bridge rectifier circuit and a suction port of the compressor;
A supercooling heat exchanger arranged to cool the refrigerant from the end to the main expansion mechanism, and a supercooling expansion mechanism connected between the second end and the supercooling heat exchanger. with one end connected to the second end of the bridge rectifier circuit,
Between the inner tube with the other end open and one end and the other end of the inner tube
And one end is connected to the suction port of the compressor.
A middle tube having an orifice formed at the other end,
Wraps the inner and middle tubes, one end of which is the main expansion mechanism
The triple tube heat exchanger consisting of the connected outer tube
It is characterized by comprising a subcooling heat exchanger and a subcooling expansion mechanism .

【００１８】この請求項２の発明では、ブリッジ整流回
路の第２端から内管の一端側に流入した冷媒は、外管の
他端側に至り、サブ流が中管の他端側端部のオリフィス
から中管内に膨張しながら流入する。この膨張によりサ
ブ流入冷媒が冷え、この冷えたサブ流入冷媒は、上記内
管の開放他端から外管の他端側に流入してメイン膨張機
構に向かうメイン流入冷媒を冷やし、同時に、内管の一
端側から他端側に向かう冷媒（メイン流＋サブ流)を冷
やす。このように、この三重管式熱交換器は、冷えたサ
ブ流入冷媒が流れる中管の内側と外側とに、冷媒のメイ
ン流が流れる外管と内管とを配しているから、冷えたサ
ブ流入冷媒とメイン流との熱交換効率が良い。したがっ
て、過冷却の増大を図れ、能力,効率を一層増大させる
ことができる。また、この三重管式熱交換器によって、
過冷却用熱交換器と過冷却用膨張機構とが一体化される
から、配管が簡単になり、全体がコンパクトになる。ま
た、請求項３の発明の空気調和機は、請求項１または２
に記載の空気調和機において、上記三重管式熱交換器の
中管は外周面もしくは内周面にフィンを有していること
を特徴としている。According to the second aspect of the present invention, the refrigerant flowing from the second end of the bridge rectifier circuit to one end of the inner pipe reaches the other end of the outer pipe, and the sub-flow flows to the other end of the middle pipe. Flows into the middle pipe while expanding from the orifice. This expansion cools the sub-inflow refrigerant, and the cooled sub-inflow refrigerant flows into the other end of the outer pipe from the open other end of the inner pipe and cools the main inflow refrigerant toward the main expansion mechanism. Cools the refrigerant (main flow + sub flow) flowing from one end side to the other end side. As described above, the triple tube heat exchanger is cooled because the outer tube and the inner tube through which the main flow of the refrigerant flows are arranged inside and outside the middle tube through which the cooled sub-inflow refrigerant flows. Good heat exchange efficiency between the sub-inflow refrigerant and the main flow. Therefore, the supercooling can be increased, and the capacity and efficiency can be further increased. Also, with this triple tube heat exchanger,
Since the supercooling heat exchanger and the supercooling expansion mechanism are integrated, the piping is simplified and the whole becomes compact. The air conditioner according to the third aspect of the present invention provides the air conditioner according to the first or second aspect.
In the air conditioner described in (1), the middle tube of the triple tube heat exchanger has a fin on an outer peripheral surface or an inner peripheral surface.

【００１９】この請求項３の発明では、上記フィンによ
り、中管内のサブ流入冷媒と上記外管内の冷媒との熱交
換効率を向上させることができるから、過冷却の増大を
図れ、能力,効率の一層の増大を図れる。According to the third aspect of the present invention, since the heat exchange efficiency between the sub-inflow refrigerant in the middle tube and the refrigerant in the outer tube can be improved by the fins, the supercooling can be increased, and the capacity and efficiency can be improved. Can be further increased.

【００２０】[0020]

【発明の実施の形態】以下、この発明を図示の実施の形
態により詳細に説明する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, the present invention will be described in detail with reference to the illustrated embodiments.

【００２１】〔実施の形態〕 図１(Ａ)に、この発明の空気調和機の実施の形態を示
す。この実施形態は、室外熱交換器１と、室内熱交換器
２と、圧縮機３と、四路切換弁５と、ブリッジ整流回路
６と、メイン膨張弁７と、三重管式熱交換器８と、受液
器１０とを備えている。[0021] [implementation of Embodiment FIG. 1 (A), the illustrated form of implementation of the air conditioner of the present invention. Implementation form of this is an outdoor heat exchanger 1, the indoor heat exchanger 2, a compressor 3, a four-way switching valve 5, a bridge rectifier circuit 6, a main expansion valve 7, the triple pipe heat exchanger A vessel 8 and a liquid receiver 10 are provided.

【００２２】上記圧縮機３の吐出口３ａは四路切換弁５
の吸入口５ａに接続され、圧縮機３の吸込口３ｂは四路
切換弁５の吐出口５ｂに接続されている。そして、上記
四路切換弁５の第１中継口５ｃは上記室外熱交換器１の
一端１ａに接続されており、四路切換弁５の第２中継口
５ｄは室内熱交換器２の一端２ａに接続されている。そ
して、上記室外熱交換器１の他端１ｂは、ブリッジ整流
回路６の第１端６ａに接続されている。このブリッジ整
流回路６は、第１端６ａと第２端６ｂとの間に接続され
た第１逆止弁１１と、第２端６ｂと第３端６ｃとの間に
接続された第２逆止弁１２と、第３端６ｃと第４端６ｄ
との間に接続された第３逆止弁１３と、第４端６ｄと第
１端６ａとの間に接続された第４逆止弁１４とからな
る。The discharge port 3a of the compressor 3 has a four-way switching valve 5
, And a suction port 3b of the compressor 3 is connected to a discharge port 5b of the four-way switching valve 5. The first relay port 5c of the four-way switching valve 5 is connected to one end 1a of the outdoor heat exchanger 1, and the second relay port 5d of the four-way switching valve 5 is connected to one end 2a of the indoor heat exchanger 2. It is connected to the. The other end 1b of the outdoor heat exchanger 1 is connected to a first end 6a of the bridge rectifier circuit 6. The bridge rectifier circuit 6 includes a first check valve 11 connected between the first end 6a and the second end 6b, and a second check valve 11 connected between the second end 6b and the third end 6c. Stop valve 12, third end 6c and fourth end 6d
And a fourth check valve 14 connected between the fourth end 6d and the first end 6a.

【００２３】上記ブリッジ整流回路６の第２端６ｂは受
液器１０の入口に接続されており、この受液器１０の出
口は上記三重管式熱交換器８の外管１６の一端１６ａに
接続されている。図４にも示すように、この三重管式熱
交換器８は、上記外管１６と中管１７と内管１８とで構
成されている。この内管１８の一端１８ａがメイン膨張
弁７に接続され、他端１８ｂが開放されている。また、
上記中管１７は、上記内管１８の一端１８ａと他端１８
ｂとの間の部分を包むように上記内管１８に固定されて
いる。この中管１７の一端側１７ａが電磁弁２０を介し
て上記圧縮機３の吸入口３ｂに接続され、他端側端部１
７ｂにオリフィス２１が形成されている。このオリフィ
ス２１が過冷却用膨張機構を構成している。また、上記
外管１６は、上記内管１８および中管１７を包むように
中管１７に固定されている。A second end 6b of the bridge rectifier circuit 6 is connected to an inlet of a receiver 10, and an outlet of the receiver 10 is connected to one end 16a of an outer tube 16 of the triple tube heat exchanger 8. It is connected. As shown in FIG. 4, the triple tube heat exchanger 8 includes the outer tube 16, the middle tube 17, and the inner tube 18. One end 18a of the inner pipe 18 is connected to the main expansion valve 7, and the other end 18b is open. Also,
The middle tube 17 is connected to one end 18 a and the other end 18 of the inner tube 18.
b, and is fixed to the inner tube 18 so as to wrap the portion between them. One end 17a of the middle pipe 17 is connected to the suction port 3b of the compressor 3 via the electromagnetic valve 20, and the other end 1
An orifice 21 is formed in 7b. The orifice 21 constitutes a subcooling expansion mechanism. The outer tube 16 is fixed to the middle tube 17 so as to surround the inner tube 18 and the middle tube 17.

【００２４】上記中管１７の外周面にはこの外周面を周
方向に取り巻いている複数のフィン２２が形成されてい
る。また、上記内管１８の開放他端１８ｂは、上記外管
１６の一端１６ａから他端に向かって流れて来た冷媒に
対する開口面積が大きくなるように、斜めに開口してい
る。そして、上記オリフィス２１は、上記開放他端１８
ｂの背後下流側に配されている。したがって、冷媒のメ
イン流は上記内管１８の開放他端１８ｂから流入し、冷
媒の過冷却用サブ流は上記中管１７のオリフィス２１か
ら流入することになる。A plurality of fins 22 are formed on the outer peripheral surface of the middle pipe 17 in a circumferential direction around the outer peripheral surface. The open other end 18b of the inner pipe 18 is opened obliquely so that the opening area for the refrigerant flowing from one end 16a of the outer pipe 16 toward the other end is increased. The orifice 21 is connected to the open other end 18.
It is arranged downstream behind b. Therefore, the main flow of the refrigerant flows from the open other end 18b of the inner pipe 18, and the sub-cooling sub-flow of the refrigerant flows from the orifice 21 of the middle pipe 17.

【００２５】そして、上記メイン膨張弁７は上記ブリッ
ジ整流回路６の第４端６ｄに接続されており、第３端６
ｃは室内熱交換器２の他端２ｂに接続されている。ま
た、この室内熱交換器２の一端２ａは上記四路切換弁５
の第２中継口５ｄに接続されている。The main expansion valve 7 is connected to the fourth end 6d of the bridge rectifier circuit 6, and is connected to the third end 6d.
c is connected to the other end 2b of the indoor heat exchanger 2. One end 2a of the indoor heat exchanger 2 is connected to the four-way switching valve 5 described above.
Is connected to the second relay port 5d.

【００２６】そして、この実施の形態では、非共沸混合
冷媒を採用した。[0026] In the implementation form of this, employing a non-azeotropic refrigerant.

【００２７】なお、上記図１(Ａ)に符号〜で示した
各部分での冷媒の状態を、図３のモリエル線図に符号
〜で示した。The state of the refrigerant in each part indicated by reference numerals in FIG. 1A is indicated by reference numerals in the Mollier diagram of FIG.

【００２８】上記構成の空気調和機では、まず、上記四
路切換弁５を図１(Ａ)に実線で示したような冷房位置に
すれば、冷媒は、順に、室内熱交換器２、圧縮機３(図
３の→)、室外熱交換器１、ブリッジ整流回路６と
流れ、室外熱交換器１は凝縮器として働き、室内熱交換
器２は蒸発器として働く。In the air conditioner having the above configuration, first, if the four-way switching valve 5 is set to the cooling position as shown by the solid line in FIG. 1 (A), the refrigerant flows into the indoor heat exchanger 2 and the compression The heat flows through the heat exchanger 3 (→ in FIG. 3), the outdoor heat exchanger 1, and the bridge rectifier circuit 6, and the outdoor heat exchanger 1 functions as a condenser and the indoor heat exchanger 2 functions as an evaporator.

【００２９】上記凝縮器としての室外熱交換器１からの
冷媒は、上記ブリッジ整流回路６の第１端６ａに入り、
第１逆止弁１１を通過し第２端６ｂから出た冷媒は、受
液器１０を経て(図３の)、三重管式熱交換器８の外管
１６の一端１６ａから流入する(図３の)。ここで、上
記流入冷媒の内、内管１８の開放他端１８ｂに流入し、
この内管１８を経て(図３の)、メイン膨張弁７に至る
流れがメイン流である。そして、上記メイン流は、さら
に、メイン膨張弁７を通過して、上記ブリッジ整流回路
６の第４端６ｄに入り、第３逆止弁１３を通って(図３
の)、蒸発器として働く室内熱交換器２に達する。The refrigerant from the outdoor heat exchanger 1 as the condenser enters the first end 6a of the bridge rectifier circuit 6,
The refrigerant that has passed through the first check valve 11 and has exited from the second end 6b flows through the liquid receiver 10 (FIG. 3) and flows in from one end 16a of the outer tube 16 of the triple tube heat exchanger 8 (see FIG. 3). Here, of the inflow refrigerant, it flows into the open other end 18b of the inner pipe 18,
The flow that reaches the main expansion valve 7 via the inner pipe 18 (of FIG. 3) is the main flow. Then, the main flow further passes through the main expansion valve 7, enters the fourth end 6d of the bridge rectification circuit 6, and passes through the third check valve 13 (FIG. 3).
) Arrives at the indoor heat exchanger 2 which acts as an evaporator.

【００３０】一方、上記第１逆止弁１１を通過し第２端
６ｂから出て、外管１６の一端１６ａに流入した冷媒の
内、上記中管１７のオリフィス２１に流入する流れ(図
３の→)が過冷却のためのサブ流である。このサブ
流は全体の約１０％である。このサブ流は、過冷却用膨
張機構としての上記オリフィス２１を通過することで冷
やされてから、中管１７の一端側１７ａに向かって流れ
る。この中管１７中を流れる冷えた冷媒は、外管１６お
よび内管１８を流れるメイン流を図３の→のように
冷やしてから、飽和ガス状態(図３の)になって、電磁
弁２０を通って圧縮機３の吸入口３ｂに達する。On the other hand, the flow of the refrigerant that has passed through the first check valve 11 and exited from the second end 6b and has flowed into the one end 16a of the outer tube 16 flows into the orifice 21 of the middle tube 17 (FIG. 3). →) is the sub flow for supercooling. This substream is about 10% of the total. This sub-flow is cooled by passing through the orifice 21 as a subcooling expansion mechanism, and then flows toward one end 17a of the middle pipe 17. The cooled refrigerant flowing through the middle pipe 17 cools the main stream flowing through the outer pipe 16 and the inner pipe 18 as shown by → in FIG. Through the compressor 3 to the suction port 3b of the compressor 3.

【００３１】また、上記四路切換弁５を図１(Ａ)に破線
で示したような暖房位置にすれば、冷媒は、順に、圧縮
機３(図３の→)、室内熱交換器２、ブリッジ整流回
路６、室外熱交換器１と流れ、室内熱交換器２は凝縮器
として働き、室外熱交換器１は蒸発器として働く。When the four-way switching valve 5 is set to the heating position as shown by the broken line in FIG. 1A, the refrigerant flows into the compressor 3 (→ in FIG. 3) and the indoor heat exchanger 2 in this order. , The bridge rectifier circuit 6, the outdoor heat exchanger 1, the indoor heat exchanger 2 functions as a condenser, and the outdoor heat exchanger 1 functions as an evaporator.

【００３２】上記凝縮器としての室内熱交換器２からの
冷媒は、上記ブリッジ整流回路６の第３端６ｃに入り、
第２逆止弁１２を通過し第２端６ｂから出た冷媒は、受
液器１０を経て(図３の)、メイン流が、外管１６(図
３の)、内管１８を通過して(図３の)、メイン膨張
弁７を通過して(図３の)、上記ブリッジ整流回路６の
第４端６ｄに入り、第４逆止弁１４を通って蒸発器とし
て働く室外熱交換器１に達する。The refrigerant from the indoor heat exchanger 2 as the condenser enters the third end 6c of the bridge rectification circuit 6,
The refrigerant flowing through the second check valve 12 and leaving the second end 6b passes through the liquid receiver 10 (FIG. 3), and the main flow passes through the outer pipe 16 (FIG. 3) and the inner pipe 18. (FIG. 3), passes through the main expansion valve 7 (FIG. 3), enters the fourth end 6d of the bridge rectifier circuit 6, passes through the fourth check valve 14, and serves as an outdoor heat exchanger. It reaches the container 1.

【００３３】一方、上記第２逆止弁１２を通過し第２端
６ｂから出て、受液器１０を通過した冷媒は、サブ流が
外管１６から中管１７のオリフィス２１を通過すること
(図３の→)で冷やされてから、中管１７中を流れる
ことによって、外管１６および内管１８を流れるメイン
流を、図３の→のように、冷やしてから、圧縮機３
の吸入口３ｂに達する(図３の)。On the other hand, the refrigerant that has passed through the second check valve 12, exited from the second end 6 b, and passed through the liquid receiver 10 has a sub-flow passing through the orifice 21 of the outer pipe 16 and the middle pipe 17.
After being cooled at (→ in FIG. 3), the main flow flowing through the outer pipe 16 and the inner pipe 18 is cooled as shown by → in FIG.
(FIG. 3).

【００３４】このように、この実施形態によれば、四路
切換弁５を冷房位置(実線)にしたときには、凝縮器とし
て働く室外熱交換器１からの冷媒のサブ流を三重管式熱
交換器８内で冷やし、この冷えたサブ流の冷媒でメイン
流の冷媒を冷やした上で、メイン流を蒸発器として働く
室内熱交換器２に導入する。したがって、蒸発器として
の室内熱交換器２の能力と効率の向上を図れる。したが
って、冷房能力の向上を図れ、かつ、冷房効率の向上を
図れる。[0034] Thus, according to the implementation form of this, the four-way switching valve 5 and cooling position when the (solid line), sub-stream triple tube type of refrigerant from the outdoor heat exchanger 1 acting as a condenser After cooling in the heat exchanger 8, the main stream refrigerant is cooled by the cooled sub stream refrigerant, and the main stream is introduced into the indoor heat exchanger 2 serving as an evaporator. Therefore, the capacity and efficiency of the indoor heat exchanger 2 as an evaporator can be improved. Therefore, the cooling capacity can be improved and the cooling efficiency can be improved.

【００３５】また、四路切換弁５を暖房位置にしたとき
には、凝縮器として働く室内熱交換器２からの冷媒のサ
ブ流を三重管式熱交換器８で冷やし、この冷えた冷媒で
メイン流の冷媒を冷やした上で、メイン流を蒸発器とし
て働く室外熱交換器１に導入する。したがって、蒸発器
としての室外熱交換器１の能力と効率の向上を図れる。
したがって、暖房能力の向上を図れ、かつ、暖房効率の
向上を図れる。When the four-way switching valve 5 is set to the heating position, the sub-flow of the refrigerant from the indoor heat exchanger 2 serving as a condenser is cooled by the triple tube heat exchanger 8, and the cooled refrigerant is used as the main flow. After cooling the refrigerant, the main stream is introduced into the outdoor heat exchanger 1 serving as an evaporator. Therefore, the performance and efficiency of the outdoor heat exchanger 1 as an evaporator can be improved.
Therefore, the heating capacity can be improved, and the heating efficiency can be improved.

【００３６】したがって、この実施形態によれば、冷媒
流れ方向を切り換えても、変わりなく過冷却の効果を得
ることができる。[0036] Thus, according to the implementation form of this, it is also possible to switch the refrigerant flow direction, to obtain the effect of supercooling no different.

【００３７】ここで、上記過冷却によって能力が向上す
る理由を説明する。蒸発器(冷房時の室内熱交換器２,暖
房時の室外熱交換器１)の能力Ｑは、 Ｑ＝Ｋ・Ａ・Δtm ……………(１) で表される。この式(１)において、Ｋは熱通過率であ
り、Ａは熱交換面積であり、Δtmは周囲の空気温度と内
部の冷媒温度との温度差である。上記空気温度を一定と
すると、冷媒温度が低い程、能力Ｑが増大する。Here, the reason why the performance is improved by the supercooling will be described. The capacity Q of the evaporator (the indoor heat exchanger 2 at the time of cooling and the outdoor heat exchanger 1 at the time of heating) is represented by Q = KAA.DELTA.tm (1). In this equation (1), K is the heat transfer rate, A is the heat exchange area, and Δtm is the temperature difference between the ambient air temperature and the internal refrigerant temperature. Assuming that the air temperature is constant, the capacity Q increases as the refrigerant temperature decreases.

【００３８】ここで、仮に、上記三重管式熱交換器８が
無い場合には、蒸発器内の冷媒温度は、図３のモリエル
線図では、に示す受液器１０での冷媒温度Ｔ０と、
で示す圧縮機３の入口での冷媒温度Ｔ１との平均温度に
なる。上記実施形態では、上記Ｔ０＝約３.５℃であ
り、Ｔ１＝約７.５℃であるので、平均温度は、約５.５
℃になる。Here, if the triple-tube heat exchanger 8 is not provided, the refrigerant temperature in the evaporator becomes the refrigerant temperature T 0 in the liquid receiver 10 shown in the Mollier diagram of FIG. When,
And the average temperature with the refrigerant temperature T1 at the inlet of the compressor 3 as shown in FIG. In the above embodiment, since the above T 0 = about 3.5 ° C. and T 1 = about 7.5 ° C., the average temperature is about 5.5 ° C.
° C.

【００３９】これに対し、上記三重管式熱交換器８が有
る場合には、蒸発器内の冷媒温度は、図３のモリエル線
図で、に示す箇所での冷媒温度Ｔ６＝約２.５℃と、
Ｔ１＝約７.５℃との平均温度＝約５.０℃になる。On the other hand, in the case where the triple tube heat exchanger 8 is provided, the refrigerant temperature in the evaporator is the refrigerant temperature T 6 at the point shown by the Mollier diagram in FIG. 5 ° C,
The average temperature with T 1 = about 7.5 ° C. = about 5.0 ° C.

【００４０】したがって、今、上記周囲空気の温度の平
均が１３℃(ＷＢ(湿球温度))であるとすると、三重管式
熱交換器８が無い場合の能力Ｑ０に対して、三重管式熱
交換器８が有る場合の能力Ｑ１の割合は、 （Ｑ１／Ｑ０）×１００％＝｛(１３−５)／(１３−５.５)｝×１００％ ≒１０７％ となる。したがって、上記三重管式熱交換器８を設ける
ことによって、同じ動力で約７％の能力およびＣＯＰの
向上が図れる。[0040] Thus, now, on the ability Q 0 if When the average temperature of the ambient air is 13 ° C. (WB (wet-bulb temperature)), a triple tube heat exchanger 8 is not, triple pipe ratio of capacity to Q 1 if the expression heat exchanger 8 there is a (Q 1 / Q 0) × 100% = {(13-5) / (13-5.5)} × 100% ≒ 107% . Therefore, by providing the triple-tube heat exchanger 8, the capacity and COP can be improved by about 7% with the same power.

【００４１】また、一般に、過負荷運転では、メイン膨
張弁７の前で(の箇所で)、冷媒が液とガスの混在状態
になって、蒸発器への冷媒供給不足をきたすことがある
が、上記実施形態によれば、メイン膨張弁７の前(の
箇所)での過冷却温度が約１０℃あるので、広い範囲の
負荷に対して、上記のような蒸発器への冷媒供給不足を
発生させることなく正常に運転できる。In general, in the overload operation, the refrigerant may be in a mixed state of liquid and gas in front of (at) the main expansion valve 7, which may cause a shortage of the refrigerant supply to the evaporator. According to the above-described embodiment, the supercooling temperature before (at) the main expansion valve 7 is about 10 ° C., so that the refrigerant supply to the evaporator as described above is insufficient for a wide range of load. It can operate normally without generating.

【００４２】また、この空気調和機は、冷媒として非共
沸混合冷媒を用いたから、液体から気体への遷移時に温
度差が生じることになって、蒸発開始時の温度が一層低
くなって、蒸発器の内外の温度差が大きくなって、能
力,効率を一層増大させることができる。In this air conditioner, since a non-azeotropic mixed refrigerant is used as a refrigerant, a temperature difference occurs at the time of transition from a liquid to a gas. The temperature difference between the inside and outside of the vessel becomes large, and the capacity and efficiency can be further increased.

【００４３】また、この空気調和機は、三重管式熱交換
器８が過冷却用熱交換器と過冷却用膨張機構とを構成し
ている。この三重管式熱交換器８によれば、ブリッジ整
流回路６の第２端６ｂから外管１６の一端側に流入した
冷媒は、外管１６の他端側に至り、サブ流が中管１７の
他端側端部１７ｂのオリフィス２１から中管１７内に膨
張しながら流入する。この膨張によりサブ流入冷媒が冷
え、この冷えたサブ流入冷媒は、外管１６の他端側から
内管１８の開放他端１８ｂに流入してメイン膨張弁７に
向かうメイン流入冷媒を冷やし、同時に、外管１６の他
端側から一端側に向かう冷媒(メイン流＋サブ流)を冷や
す。このように、この三重管式熱交換器８は、冷えたサ
ブ流入冷媒が流れる中管１７の内側と外側とに、冷媒の
メイン流が流れる外管１６と内管１８とを配しているか
ら、冷えたサブ流入冷媒とメイン流との熱交換効率が良
い。したがって、過冷却の増大を図れ、能力,効率を一
層増大させることができる。In this air conditioner, the triple tube heat exchanger 8 constitutes a supercooling heat exchanger and a supercooling expansion mechanism. According to the triple tube heat exchanger 8, the refrigerant flowing from the second end 6b of the bridge rectifier circuit 6 to one end of the outer tube 16 reaches the other end of the outer tube 16, and the sub-flow flows to the middle tube 17 Flows from the orifice 21 at the other end 17b of the inner pipe 17 into the middle pipe 17 while expanding. This expansion cools the sub-inflow refrigerant, and the cooled sub-inflow refrigerant flows from the other end of the outer pipe 16 into the open other end 18b of the inner pipe 18 to cool the main inflow refrigerant toward the main expansion valve 7, and at the same time, Then, the refrigerant (main flow + sub flow) flowing from the other end of the outer tube 16 to the one end is cooled. As described above, the triple tube heat exchanger 8 has the outer tube 16 and the inner tube 18 through which the main flow of the refrigerant flows, inside and outside the middle tube 17 through which the cooled sub-inflow refrigerant flows. Therefore, the heat exchange efficiency between the cooled sub-inflow refrigerant and the main stream is good. Therefore, the supercooling can be increased, and the capacity and efficiency can be further increased.

【００４４】また、この三重管式熱交換器８によって、
過冷却用熱交換器と過冷却用膨張機構とが一体化される
から、配管が簡単になり、全体がコンパクトになる。The triple tube heat exchanger 8 also
Since the supercooling heat exchanger and the supercooling expansion mechanism are integrated, the piping is simplified and the whole becomes compact.

【００４５】また、図１に示すように、上記三重管式熱
交換器８は、外管１６,中管１７,内管１８の上部の一端
１６ａ,１７ａ,１８ａを受液器１０への配管,圧縮機３
への配管,メイン膨張弁７への配管に接続している。し
たがって、配管接続はすべて上部で行う構造であるから
製作作業が容易である。As shown in FIG. 1, the triple-tube heat exchanger 8 includes one end 16a, 17a, 18a at the upper part of the outer tube 16, the middle tube 17, and the inner tube 18 connected to a pipe to the receiver 10. , Compressor 3
To the main expansion valve 7. Therefore, since the pipe connection is all performed at the upper portion, the manufacturing operation is easy.

【００４６】また、この実施形態では、上記三重管式熱
交換器８の中管１７の外周面に複数のフィン２２を有し
ているから、上記中管１７内のサブ流入冷媒と上記外管
１６内の冷媒との熱交換効率を向上させることができ
る。したがって、過冷却の増大を図れ、能力,効率の一
層の増大を図れる。外管１６内では冷媒液の流速が遅い
(約０.９ｍ／秒)から、上記中管１７外周のフィン２２
で熱交換面積を大きくして熱伝達を良くしているのであ
る。図５に示すように、流速が高いほど熱通過率も大き
くなる。そして、中管１７内では冷媒は２相流であり流
速も速く(約１２ｍ／秒)、また、内管１８内でも冷媒の
流速が速い(約５ｍ／秒)から、中管１７の外周に比べて
フィンの必要性は小さい。[0046] In the implementation form of this, because they have a plurality of fins 22 on the outer circumferential surface of the middle tube 17 of the triple pipe heat exchanger 8, the sub-inlet refrigerant and above within the hollow tube 17 The heat exchange efficiency with the refrigerant in the outer tube 16 can be improved. Therefore, the supercooling can be increased, and the capacity and efficiency can be further increased. The flow rate of the refrigerant liquid is slow in the outer tube 16
(About 0.9 m / sec), the fins 22 on
This increases the heat exchange area to improve heat transfer. As shown in FIG. 5, the higher the flow velocity, the higher the heat transmission rate. In the middle pipe 17, the refrigerant is a two-phase flow and has a high flow rate (about 12 m / sec). Also, in the inner pipe 18, the coolant has a high flow rate (about 5 m / sec). In comparison, the need for fins is small.

【００４７】また、この空気調和機は、上記ブリッジ整
流回路６の第２端６ｂと三重管式熱交換器８の外管１６
との間に接続された受液器１０を有しているから、ブリ
ッジ整流回路６の第２端６ｂから出た冷媒が液体と気体
との混合状態であっても、この冷媒を上記受液器１０で
液体と気体とに分離してから、下方の液体のみを三重管
式熱交換器８に導くことができる。したがって、冷媒を
三重管式熱交換器８で効率よく冷却できる。したがっ
て、過冷却の増大を図れ、能力,効率の一層の増大を図
れる。Further, the air conditioner has a structure in which the second end 6b of the bridge rectifier circuit 6 and the outer tube 16 of the triple tube heat exchanger 8 are connected.
And the liquid receiver 10 connected between the second end 6b of the bridge rectifier circuit 6 and the refrigerant received from the second end 6b. After the separation into liquid and gas in the vessel 10, only the liquid below can be led to the triple tube heat exchanger 8. Therefore, the refrigerant can be efficiently cooled by the triple tube heat exchanger 8. Therefore, the supercooling can be increased, and the capacity and efficiency can be further increased.

【００４８】なお、上記電磁弁２０を閉じれば、上記三
重管式熱交換器８の中管１７に冷媒が流入しなくなり、
中管１７内のサブ流によるメイン流の過冷却はなくな
る。したがって、運転を停止するとき、能力制御を止め
るとき、入力オーバーのとき、圧縮機３の吐出圧力が上
昇し冷媒供給量を減らしたいときには、電磁弁２０を閉
じればよい。一方、通常運転中は、電磁弁２０を開い
て、能力,ＣＯＰを向上させる。また、デフロスト中に
は、電磁弁２０を開いて、デフロスト時間を短縮させ
る。また、冷凍機をオフにする前の一定時間には、電磁
弁２０を開いて、中管１７内の液を抜いて、液封を防止
する。また、起動前に、電磁弁２０を開いて、高圧,低
圧をバランスさせ、起動を容易にする。また、吐出管温
度が上昇したときに、電磁弁２０を開いて、圧縮機３に
幾分湿りのガスを吸入させて、吐出ガス温度上昇による
油の劣化を防ぐ。When the solenoid valve 20 is closed, the refrigerant does not flow into the middle pipe 17 of the triple tube heat exchanger 8,
Subcooling of the main flow by the subflow in the middle pipe 17 is eliminated. Therefore, the solenoid valve 20 may be closed when the operation is stopped, when the capacity control is stopped, when the input is over, when the discharge pressure of the compressor 3 is increased and the refrigerant supply amount is to be reduced. On the other hand, during normal operation, the solenoid valve 20 is opened to improve the capacity and COP. During defrost, the solenoid valve 20 is opened to reduce the defrost time. Also, during a certain period of time before the refrigerator is turned off, the solenoid valve 20 is opened to drain the liquid in the middle pipe 17 to prevent liquid sealing. Before starting, the solenoid valve 20 is opened to balance the high pressure and the low pressure, thereby facilitating the starting. Also, when the discharge pipe temperature rises, the solenoid valve 20 is opened to allow the compressor 3 to inhale a somewhat humid gas to prevent oil deterioration due to the discharge gas temperature rise.

【００４９】尚、上記実施形態では、中管１７の外周面
にフィン２２を形成したが、中管１７の内周面にフィン
２２を形成してもよい。[0049] In the above you facilities embodiment has formed the fin 22 on the outer circumferential surface of the middle tube 17, the inner peripheral surface of the middle tube 17 may be formed fins 22.

【００５０】また、上記実施形態では、三重管式熱交換
器８の外管１６の一端１６ａを上流の受液器１０に接続
する一方、内管１８の一端１８ａを下流のメイン膨張弁
７に接続したが、外管１６の一端１６ａをメイン膨張弁
７に接続し、内管１８の一端１８ａを受液器１０に接続
してもよい。[0050] Further, in the above you facilities embodiment, a triple tube type while connecting one end 16a of the outer tube 16 upstream of the receiver 10 of the heat exchanger 8, the one end 18a of the inner pipe 18 downstream of the main expansion valve 7, one end 16 a of the outer pipe 16 may be connected to the main expansion valve 7, and one end 18 a of the inner pipe 18 may be connected to the receiver 10.

【００５１】また、上記実施形態では、整流手段とし
て、ブリッジ整流回路６を用いたが、図１(Ｂ)に示すよ
うに、４つの電磁弁Ａ,Ｂ,Ｃ,Ｄで構成されたブリッジ
整流回路６０を用いてもよい。この場合、冷房時には電
磁弁Ｂ,Ｃを開いて、電磁弁Ａ,Ｄを閉じる一方、暖房時
には電磁弁Ａ,Ｄを開き、電磁弁Ｂ,Ｃを閉じるようにす
れば、上記ブリッジ整流回路６と同様の整流動作を行え
る。また、ブリッジ整流回路６に替えて、図１(Ｃ)に示
す四路切換弁６００を用いてもよい。この場合、冷房時
には経路Ｘ１,Ｘ２(実線)を導通させて経路Ｙ１,Ｙ
２(破線)を閉塞させる一方、暖房時には経路Ｘ１,Ｘ２
を閉塞させて経路Ｙ１,Ｙ２を導通させれば、上記ブリ
ッジ整流回路６と同様の整流動作を行える。[0051] In the above you facilities embodiment, as the rectifying means, is used to bridge rectifier circuit 6, as shown in FIG. 1 (B), 4 single solenoid valves A, B, C, composed of D A bridge rectifier circuit 60 may be used. In this case, the solenoid valves B and C are opened during cooling and the solenoid valves A and D are closed, while the solenoid valves A and D are opened and the solenoid valves B and C are closed during heating. The same rectifying operation can be performed. Further, a four-way switching valve 600 shown in FIG. 1C may be used instead of the bridge rectifier circuit 6. In this case, at the time of cooling, the paths X 1 and X 2 (solid lines) are made conductive so that the paths Y 1 and Y
2 (broken line) is closed, while the paths X 1 and X 2
Is closed and the paths Y 1 and Y 2 are conducted, so that the same rectifying operation as the bridge rectifying circuit 6 can be performed.

【００５２】〔参考例〕 次に、この発明の参考例を図２に示す。この参考例は、
上記三重管式熱交換器８に替えて、過冷却用膨張機構と
してのキャピラリ５１と、過冷却用熱交換器としての２
重管５２とを備えた点と受液器１０を備えていない点と
だけが、上述の実施形態と異なる。したがって、この過
冷却機構に関して重点的に説明する。 Reference Example Next, FIG. 2 shows a reference example of the present invention. This reference example
Instead of the triple tube heat exchanger 8, a capillary 51 as a supercooling expansion mechanism and a capillary 51 as a supercooling heat exchanger are used.
Point only which is not provided with a point and a heavy pipe 52 and the receiver 10 is different from the implementation described above. Therefore, this supercooling mechanism will be mainly described.

【００５３】この参考例は、ブリッジ整流回路６の第２
端６ｂと第４端６ｄの間の回路だけが、上記実施形態と
異なる。すなわち、ブリッジ整流回路６の第２端６ｂに
キャピラリ５１が接続され、このキャピラリ５１に２重
管５２の過冷却用コイル５７が接続されている。この２
重管５２の過冷却用コイル５７は電磁弁２０を介して圧
縮機３の吸入口３ｂに接続されている。そして、上記第
２端６ｂからの配管５５は上記２重管５２を経由してメ
イン膨張弁７に接続されている。このメイン膨張弁７は
ブリッジ整流回路６の第４端６ｄに接続されている。This reference example is a second embodiment of the bridge rectifier circuit 6.
Only circuit between the end 6b and a fourth end 6d is different from the implementation form. That is, the capillary 51 is connected to the second end 6 b of the bridge rectifier circuit 6, and the supercooling coil 57 of the double pipe 52 is connected to the capillary 51. This 2
The supercooling coil 57 of the heavy pipe 52 is connected to the suction port 3 b of the compressor 3 via the solenoid valve 20. The pipe 55 from the second end 6b is connected to the main expansion valve 7 via the double pipe 52. The main expansion valve 7 is connected to the fourth end 6d of the bridge rectification circuit 6.

【００５４】この空気調和機は、ブリッジ整流回路６の
第２端６ｂから２重管５２を経由してメイン膨張弁７に
至る冷媒がメイン流であり、上記ブリッジ整流回路６の
第２端６ｂからキャピラリ５１に流入した冷媒が過冷却
用コイル５７に流入するサブ流となる。このサブ流が２
重管５２でメイン流を冷やすことで過冷却がなされる。In this air conditioner, the refrigerant flowing from the second end 6b of the bridge rectifier circuit 6 to the main expansion valve 7 via the double pipe 52 is the main flow, and the second end 6b of the bridge rectifier circuit 6 is The refrigerant that has flowed into the capillary 51 from above becomes a subflow that flows into the supercooling coil 57. This sub flow is 2
Supercooling is performed by cooling the main stream with the heavy pipe 52.

【００５５】尚、上記実施の形態では、冷媒として非共
沸混合冷媒を用いたが、冷媒として共沸混合冷媒を用い
てもよい。さらには、冷媒として単一成分の冷媒を用い
てもよい。[0055] Incidentally, in the embodiment above you facilities, but using a non-azeotropic refrigerant as the refrigerant, may be used-azeotropic refrigerant as the refrigerant. Further, a single component refrigerant may be used as the refrigerant.

【００５６】[0056]

【発明の効果】以上より明らかなように、請求項１の発
明の空気調和機によれば、四路切換弁を冷房位置にした
ときには、凝縮器として働く室外熱交換器からの冷媒の
サブ流を吸入管(過冷却膨張機構)に導くことで膨張さ
せ、その時の蒸発潜熱により、メイン流の冷媒を冷やし
た上で、蒸発器として働く室内熱交換器に導入する。し
たがって、蒸発器としての室内熱交換器の能力と効率の
向上を図れる。したがって、冷房能力の向上を図れ、か
つ、冷房効率の向上を図れる。また、四路切換弁を暖房
位置にしたときには、凝縮器として働く室内熱交換器か
らの冷媒のサブ流を吸入管に導くことで膨張させ、その
時の蒸発潜熱により、メイン流の冷媒を冷やした上で、
蒸発器として働く室外熱交換器に導入する。したがっ
て、蒸発器としての室外熱交換器の能力と効率の向上を
図れる。したがって、暖房能力の向上を図れ、かつ、暖
房効率の向上を図れる。As is clear from the above, according to the air conditioner of the first aspect of the present invention, when the four-way switching valve is set to the cooling position, the sub-flow of the refrigerant from the outdoor heat exchanger serving as a condenser. Is introduced into a suction pipe (supercooling expansion mechanism) to expand the refrigerant. The main flow refrigerant is cooled by the latent heat of evaporation at that time, and then introduced into an indoor heat exchanger that functions as an evaporator. Therefore, the performance and efficiency of the indoor heat exchanger as an evaporator can be improved. Therefore, the cooling capacity can be improved and the cooling efficiency can be improved. When the four-way switching valve was set to the heating position, the sub-flow of the refrigerant from the indoor heat exchanger serving as a condenser was expanded by introducing the sub-flow to the suction pipe, and the main flow refrigerant was cooled by the latent heat of evaporation at that time. Above,
It is introduced into an outdoor heat exchanger that works as an evaporator. Therefore, the performance and efficiency of the outdoor heat exchanger as an evaporator can be improved. Therefore, the heating capacity can be improved, and the heating efficiency can be improved.

【００５７】したがって、この発明によれば、冷媒流れ
方向を切り換えても、変わりなく過冷却の効果を得るこ
とができる。Therefore, according to the present invention, even if the flow direction of the refrigerant is switched, the effect of supercooling can be obtained without any change.

【００５８】また、請求項１の発明によれば、冷えたサ
ブ流入冷媒が流れる中管の内側と外側とに、冷媒のメイ
ン流が流れる外管と内管とを配しているから、冷えたサ
ブ流入冷媒とメイン流との熱交換効率が良い。したがっ
て、過冷却の増大を図れ、能力,効率を一層増大させる
ことができる。また、この三重管式熱交換器によって、
過冷却用熱交換器と過冷却用膨張機構とが一体化される
から、配管が簡単になり、全体がコンパクトになる。According to the first aspect of the present invention, since the outer pipe and the inner pipe through which the main flow of the refrigerant flows are disposed inside and outside the middle pipe through which the cooled sub-inflow refrigerant flows, the cooling pipe is cooled. Good heat exchange efficiency between the sub-inflow refrigerant and the main flow. Therefore, the supercooling can be increased, and the capacity and efficiency can be further increased. Also, with this triple tube heat exchanger,
Since the supercooling heat exchanger and the supercooling expansion mechanism are integrated, the piping is simplified and the whole becomes compact.

【００５９】また、請求項２の発明によれば、ブリッジ
整流回路の第２端から内管の一端側に流入した冷媒は、
外管の他端側に至り、サブ流が中管の他端側端部のオリ
フィスから中管内に膨張しながら流入する。この三重管
式熱交換器は、冷えたサブ流入冷媒が流れる中管の内側
と外側とに、冷媒のメイン流が流れる外管と内管とを配
しているから、冷えたサブ流入冷媒とメイン流との熱交
換効率が良い。したがって、過冷却の増大を図れ、能
力,効率を一層増大させることができる。また、この三
重管式熱交換器によって、過冷却用熱交換器と過冷却用
膨張機構とが一体化されるから、配管が簡単になり、全
体がコンパクトになる。According to the second aspect of the present invention, the refrigerant flowing from the second end of the bridge rectifier circuit to one end of the inner tube is:
The sub-flow reaches the other end of the outer tube, and the sub-flow expands into the middle tube from the orifice at the other end of the middle tube. This triple tube heat exchanger has an outer tube and an inner tube through which the main flow of the refrigerant flows, inside and outside the middle tube through which the cooled sub-inflow refrigerant flows. Good heat exchange efficiency with main flow. Therefore, the supercooling can be increased, and the capacity and efficiency can be further increased. Further, since the triple-tube heat exchanger integrates the supercooling heat exchanger and the supercooling expansion mechanism, the piping is simplified and the whole becomes compact.

【００６０】また、請求項３の発明は、請求項１または
２に記載の空気調和機において、上記三重管式熱交換器
の中管は外周面もしくは内周面にフィンを有している。
この請求項３の発明によれば、上記フィンにより、中管
内のサブ流入冷媒と上記外管内の冷媒との熱交換効率を
向上させることができるから、過冷却の増大を図れ、能
力,効率の一層の増大を図れる。Further, the invention of claim 3 is based on claim 1 or
3. In the air conditioner described in 2 , the middle tube of the triple tube heat exchanger has a fin on an outer peripheral surface or an inner peripheral surface.
According to the third aspect of the present invention, the heat exchange efficiency between the sub-inflow refrigerant in the middle tube and the refrigerant in the outer tube can be improved by the fins, so that supercooling can be increased, and the capacity and efficiency can be improved. Further increase can be achieved.

【図面の簡単な説明】[Brief description of the drawings]

【図１】 図１(Ａ)はこの発明の空気調和機の実施の形
態を示す回路図であり、図１(Ｂ)と図１(Ｃ)は整流手段
の変形例を示す図である。[1] Figure 1 (A) is a circuit diagram showing an implementation form of the air conditioner of the present invention, FIG. 1 (C) and FIG. 1 (B) is a view showing a modification of the rectification means .

【図２】 この発明の空気調和機の参考例を示す回路図
である。FIG. 2 is a circuit diagram showing a reference example of the air conditioner of the present invention.

【図３】 上記実施形態の動作を説明するモリエル線図
である。3 is a Mollier chart for explaining the operation of the upper you facilities embodiment.

【図４】 上記実施形態が有する三重管式熱交換器の構
造を示す断面図である。4 is a sectional view showing the structure of a triple-tube heat exchanger having the above you facilities embodiment.

【図５】 冷媒の流速ｖと熱通過率Ｋとの関係を示す特
性図である。FIG. 5 is a characteristic diagram illustrating a relationship between a flow velocity v of a refrigerant and a heat transmittance K.

【図６】 従来の空気調和機を示す回路図である。FIG. 6 is a circuit diagram showing a conventional air conditioner.

【符号の説明】[Explanation of symbols]

１…室外熱交換器、２…室内熱交換器、３…圧縮機、３
ａ…吐出口、３ｂ…吸込口、５…四路切換弁、６…ブリ
ッジ整流回路、７…メイン膨張弁、８…三重管熱交換
器、１０…受液器、１１…第１逆止弁、１２…第２逆止
弁、１３…第３逆止弁、１４…第４逆止弁、１６…外
管、１７…中管、１８…内管、２１…オリフィス、２２
…フィン、５１…キャピラリ、５２…２重管。1: outdoor heat exchanger, 2: indoor heat exchanger, 3: compressor, 3
a: discharge port, 3b: suction port, 5: four-way switching valve, 6: bridge rectifier circuit, 7: main expansion valve, 8: triple pipe heat exchanger, 10: liquid receiver, 11: first check valve , 12 ... second check valve, 13 ... third check valve, 14 ... fourth check valve, 16 ... outer pipe, 17 ... middle pipe, 18 ... inner pipe, 21 ... orifice, 22
... fins, 51 ... capillaries, 52 ... double tubes.

フロントページの続き (56)参考文献 特開 平５−60411（ＪＰ，Ａ) 特開 平６−331223（ＪＰ，Ａ) 特公 平２−53704（ＪＰ，Ｂ２) (58)調査した分野(Int.Cl.7，ＤＢ名) F25B 13/00 F25B 40/00 - 40/06 Continuation of front page (56) References JP-A-5-60411 (JP, A) JP-A-6-331223 (JP, A) JP-B-2-53704 (JP, B2) (58) Fields investigated (Int .Cl. 7 , DB name) F25B 13/00 F25B 40/00-40/06

Claims (3)

(57)【特許請求の範囲】(57) [Claims] 【請求項１】 圧縮機(３)と、四路切換弁(５)と、一端
が上記四路切換弁(５)に接続された室外熱交換器(１)
と、メイン膨張機構(７)と、一端が上記四路切換弁(５)
に接続された室内熱交換器(２)とを備えた空気調和機に
おいて、 第１端(６ａ)から第２端(６ｂ)に向かって順方向の第１
逆止弁(１１)と第２端(６ｂ)から第３端(６ｃ)に向かっ
て逆方向の第２逆止弁(１２)と第３端(６ｃ)から第４端
(６ｄ)に向かって逆方向の第３逆止弁(１３)と第４端
(６ｄ)から第１端(６ａ)に向かって順方向の第４逆止弁
(１４)とで構成され、上記第１端(６ａ)が上記室外熱交
換器(１)の他端(１ｂ)に接続され、上記第３端(６ｃ)が
上記室内熱交換器(２)の他端(２ｂ)に接続され、上記第
２端(６ｂ)と第４端(６ｄ)との間に上記メイン膨張機構
(７)が接続されたブリッジ整流回路(６)と、 上記ブリッジ整流回路(６)の第２端(６ｂ)と上記圧縮機
(３)の吸込口(３ｂ)との間に接続され、上記第２端(６
ｂ)から上記メイン膨張機構(７)への冷媒を冷やすよう
に配置された過冷却用熱交換器(８)と、 上記第２端(６ｂ)と上記過冷却用熱交換器(８)との間に
接続された過冷却用膨張機構(８)とを備え、 一端(１８ａ)が上記メイン膨張機構(７)に接続され、他
端(１８ｂ)が開放された内管(１８)と、上記内管(１８)
の一端(１８ａ)と他端(１８ｂ)との間の部分を包み、一
端側(１７ａ)が上記圧縮機(３)の吸入口(３ｂ)に接続さ
れ、他端側端部(１７ｂ)にオリフィス(２１)が形成され
た中管(１７)と、上記内管(１８)および中管(１７)を包
み、一端側(１６ａ)が上記ブリッジ整流回路(６)の第２
端(６ｂ)に接続された外管(１６)とで構成された三重管
式熱交換器(８)が、上記過冷却用熱交換器と過冷却用膨
張機構とを構成し たことを特徴とする空気調和機。An outdoor heat exchanger (1) having a compressor (3), a four-way switching valve (5), and one end connected to the four-way switching valve (5).
And a main expansion mechanism (7), and one end of the four-way switching valve (5)
An air conditioner comprising an indoor heat exchanger (2) connected to a first end (6a) and a first end (6b) in a forward direction from the second end (6b).
The second check valve (12) and the third end (6c) to the fourth end in the opposite direction from the check valve (11) to the third end (6c) from the second end (6b).
Third check valve (13) and fourth end in the opposite direction toward (6d)
(6d) Fourth check valve in the forward direction from the first end (6a)
(14), the first end (6a) is connected to the other end (1b) of the outdoor heat exchanger (1), and the third end (6c) is connected to the indoor heat exchanger (2). And the main expansion mechanism is connected between the second end (6b) and the fourth end (6d).
A bridge rectifier circuit (6) to which (7) is connected; a second end (6b) of the bridge rectifier circuit (6);
(3) is connected between the suction port (3b) and the second end (6).
b) a supercooling heat exchanger ( 8) arranged to cool the refrigerant from the main expansion mechanism (7) to the main expansion mechanism (7); a second end (6b) and the supercooling heat exchanger ( 8) . with connected supercooling expansion mechanism and (8) between the one end (18a) is connected to the main expansion mechanism (7), the other
An inner tube (18) having an open end (18b);
Wrap the portion between one end (18a) and the other end (18b) of the
The end side (17a) is connected to the suction port (3b) of the compressor (3).
And an orifice (21) is formed at the other end (17b).
The inner tube (17) and the inner tube (18) and the middle tube (17).
One end (16a) is the second end of the bridge rectifier circuit (6).
A triple tube comprising an outer tube (16) connected to the end (6b)
Type heat exchanger (8) is provided with the supercooling heat exchanger and the supercooling expansion.
An air conditioner characterized by comprising a tension mechanism . 【請求項２】 圧縮機(３)と、四路切換弁(５)と、一端
が上記四路切換弁(５)に接続された室外熱交換器(１)
と、メイン膨張機構(７)と、一端が上記四路切換弁(５)
に接続された室内熱交換器(２)とを備えた空気調和機に
おいて、 第１端(６ａ)から第２端(６ｂ)に向かって順方向の第１
逆止弁(１１)と第２端(６ｂ)から第３端(６ｃ)に向かっ
て逆方向の第２逆止弁(１２)と第３端(６ｃ)から第４端
(６ｄ)に向かって逆方向の第３逆止弁(１３)と第４端
(６ｄ)から第１端(６ａ)に向かって順方向の第４逆止弁
(１４)とで構成され、上記第１端(６ａ)が上記室外熱交
換器(１)の他端(１ｂ)に接続され、上記第３端(６ｃ)が
上記室内熱交換器(２)の他端(２ｂ)に接続され、上記第
２端(６ｂ)と第４端(６ｄ)との間に上記メイン膨張機構
(７)が接続されたブリッジ整流回路(６)と、 上記ブリッジ整流回路(６)の第２端(６ｂ)と上記圧縮機
(３)の吸込口(３ｂ)との間に接続され、上記第２端(６
ｂ)から上記メイン膨張機構(７)への冷媒を冷やすよう
に配置された過冷却用熱交換器(８)と、 上記第２端(６ｂ)と上記過冷却用熱交換器(８)との間に
接続された過冷却用膨張機構(８)とを備え、 一端(１８ａ)が上記ブリッジ整流回路(６)の第２端(６
ｂ)に接続され、他端(１８ｂ)が開放された内管(１８)
と、上記内管(１８)の一端(１８ａ)と他端(１８ｂ)との
間の部分を包み、一端側(１７ａ)が上記圧縮機(３)の吸
入口(３ｂ)に接続され、他端側端部(１７ｂ)にオリフィ
ス(２１)が形成された中管(１７)と、上記内管(１８)お
よび中管(１７)を包み、一端側(１６ａ)が上記メイン膨
張機構(７)に接続された外管(１６)とで構成された三重
管式熱交換器(８)が、上記過冷却用熱交換器と過冷却用
膨張機構とを構成した ことを特徴とする空気調和機。2. An outdoor heat exchanger (1) having a compressor (3), a four-way switching valve (5), and one end connected to the four-way switching valve (5).
And a main expansion mechanism (7), and one end of the four-way switching valve (5)
An air conditioner comprising an indoor heat exchanger (2) connected to a first end (6a) and a first end (6b) in a forward direction from the second end (6b).
The second check valve (12) and the third end (6c) to the fourth end in the opposite direction from the check valve (11) to the third end (6c) from the second end (6b).
Third check valve (13) and fourth end in the opposite direction toward (6d)
(6d) Fourth check valve in the forward direction from the first end (6a)
(14), the first end (6a) is connected to the other end (1b) of the outdoor heat exchanger (1), and the third end (6c) is connected to the indoor heat exchanger (2). And the main expansion mechanism is connected between the second end (6b) and the fourth end (6d).
A bridge rectifier circuit (6) to which (7) is connected; a second end (6b) of the bridge rectifier circuit (6);
(3) is connected between the suction port (3b) and the second end (6).
b) a supercooling heat exchanger ( 8) arranged to cool the refrigerant from the main expansion mechanism (7) to the main expansion mechanism (7); a second end (6b) and the supercooling heat exchanger ( 8) . comprising connected a supercooling expansion mechanism (8) between the second end of the one end (18a) is the bridge rectifier circuit (6) (6
b) and an inner tube (18) open at the other end (18b).
And one end (18a) and the other end (18b) of the inner tube (18).
One end side (17a) wraps the space between the compressors (3).
The orifice is connected to the inlet (3b) and the other end (17b)
And the inner tube (18) and the inner tube (18),
And the middle tube (17), and one end side (16a) is
And an outer tube (16) connected to the tensioning mechanism (7).
The tube type heat exchanger (8) is used for the supercooling heat exchanger and the supercooling
An air conditioner comprising an expansion mechanism . 【請求項３】 請求項１または２に記載の空気調和機に
おいて、 上記三重管式熱交換器(８)の中管(１７)は外周面もしく
は内周面にフィン(２２)を有していることを特徴とする
空気調和機。3. A air conditioner according to claim 1 or 2, middle tube of the triple-tube heat exchanger (8) (17) has a fin (22) on the outer circumferential surface or inner circumferential surface An air conditioner characterized in that:
JP02641997A 1997-02-10 1997-02-10 Air conditioner Expired - Fee Related JP3334538B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP02641997A JP3334538B2 (en) 1997-02-10 1997-02-10 Air conditioner

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP02641997A JP3334538B2 (en) 1997-02-10 1997-02-10 Air conditioner

Publications (2)

Publication Number Publication Date
JPH10220898A JPH10220898A (en) 1998-08-21
JP3334538B2 true JP3334538B2 (en) 2002-10-15

Family

ID=12193024

Family Applications (1)

Application Number Title Priority Date Filing Date
JP02641997A Expired - Fee Related JP3334538B2 (en) 1997-02-10 1997-02-10 Air conditioner

Country Status (1)

Country Link
JP (1) JP3334538B2 (en)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1762794B1 (en) * 1999-10-18 2017-03-22 Daikin Industries, Ltd. Refrigerating device
JP4715561B2 (en) * 2006-03-06 2011-07-06 ダイキン工業株式会社 Refrigeration equipment
KR100938697B1 (en) * 2009-02-11 2010-01-25 (주)라템이엔씨 Liquid gas heat exchanger and the circulating cooling method
CN106642792B (en) * 2017-01-20 2022-04-19 珠海格力电器股份有限公司 Enhanced vapor injection air conditioning unit
CN110207427B (en) * 2019-06-14 2021-04-27 广东美的暖通设备有限公司 Heat exchanger, refrigerating system and air conditioner
CN113063237A (en) * 2019-12-31 2021-07-02 青岛奥利凯中央空调有限公司 Ultra-wide-loop temperature air source heat pump system and control method
CN116294454B (en) * 2023-02-24 2024-08-09 青岛海尔空调电子有限公司 Drying system and control method for drying system

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