JP2002372323A - Refrigerating cycle - Google Patents
Refrigerating cycleInfo
- Publication number
- JP2002372323A JP2002372323A JP2001184362A JP2001184362A JP2002372323A JP 2002372323 A JP2002372323 A JP 2002372323A JP 2001184362 A JP2001184362 A JP 2001184362A JP 2001184362 A JP2001184362 A JP 2001184362A JP 2002372323 A JP2002372323 A JP 2002372323A
- Authority
- JP
- Japan
- Prior art keywords
- gas
- heat exchanger
- evaporator
- liquid separator
- refrigerant
- 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.)
- Granted
Links
Landscapes
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、蒸発器として機能
する熱交換器の熱交換路での圧力損失の増加や熱交換性
能の低下を防止する冷凍サイクルに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigeration cycle for preventing an increase in pressure loss and a decrease in heat exchange performance in a heat exchange path of a heat exchanger functioning as an evaporator.
【０００２】[0002]
【従来の技術】この種の従来の冷凍サイクルとして、例
えば、特開平９−１５２２１６号公報には、蒸発器とし
て機能する熱交換器の熱交換路の途中の冷媒を気液分離
する気閾分離器を設けたものが開示されている。以下、
この公報に記載の冷凍サイクルについて、図４を参照し
て説明する。2. Description of the Related Art As a conventional refrigeration cycle of this kind, for example, Japanese Patent Application Laid-Open No. Hei 9-152216 discloses a gas threshold separation for separating a refrigerant in the middle of a heat exchange path of a heat exchanger functioning as an evaporator. An arrangement with a vessel is disclosed. Less than,
The refrigeration cycle described in this publication will be described with reference to FIG.
【０００３】図４は空調室内に据え付けられる室内ユニ
ットと、屋外に設置される室外ユニットによって構成さ
れる空気調和機の冷凍サイクルである。この冷凍サイク
ル１０は、圧縮機１１と、この圧縮機１１の吐出口１１
ａ及び吸入口１１ｂに接続された四方切換弁１２と、こ
の四方切換弁１２に接続された室内熱交換器１３及び室
外熱交換器１４と、室内熱交換器１３と室外熱交換器１
４との間に設けられた膨張弁１５とを備えて構成されて
いる。FIG. 4 shows a refrigeration cycle of an air conditioner comprising an indoor unit installed in an air-conditioned room and an outdoor unit installed outdoors. The refrigeration cycle 10 includes a compressor 11 and a discharge port 11 of the compressor 11.
a, a four-way switching valve 12 connected to the suction port 11b, an indoor heat exchanger 13 and an outdoor heat exchanger 14 connected to the four-way switching valve 12, an indoor heat exchanger 13, and an outdoor heat exchanger 1.
4 and an expansion valve 15 provided between them.
【０００４】この構成により、暖房運転時には冷媒が、
圧縮機１１の吐出口１１ａから吐出され、四方切換弁１
２から室内熱交換器１３、膨張弁１５及び室外熱交換器
１４へと流れ、四方切換弁１２から再び圧縮機１１の吸
入口１１ｂに流れるように循環する。また、冷房運転時
には四方切換弁１２が切り換えられ、冷媒は圧縮機１１
の吐出口１１ａから吐出され、四方切換弁１２から逆に
室外熱交換器１４、膨張弁１５及び室内熱交換器１３へ
と流れ、四方切換弁１２から再び圧縮機１１の吸入口１
１ｂに吸入されるように循環する。[0004] With this configuration, during the heating operation, the refrigerant is
The four-way switching valve 1 is discharged from a discharge port 11 a of the compressor 11.
2, the refrigerant flows to the indoor heat exchanger 13, the expansion valve 15, and the outdoor heat exchanger 14, and circulates from the four-way switching valve 12 to the suction port 11 b of the compressor 11 again. During the cooling operation, the four-way switching valve 12 is switched, and the refrigerant is supplied to the compressor 11.
And flows from the four-way switching valve 12 to the outdoor heat exchanger 14, the expansion valve 15 and the indoor heat exchanger 13, and from the four-way switching valve 12 to the suction port 1 of the compressor 11 again.
Circulates so as to be sucked into 1b.
【０００５】ここで、室内熱交換器１３は、図示を省略
した多数枚の放熱フィンに複数本の熱交換パイプを貫通
させて形成した２つの冷媒が並流する熱交換路１３ａ，
１３ｂを備え、２つの熱交換路１３ａ，１３ｂの両端は
互いに接続され、その一端側の接続部が四方切換弁１２
に、他端側の接続部が膨張弁１５に接続されている。ま
た、室外熱交換器１４は、長方形の多数枚の放熱フィン
を貫通する複数本の熱交換パイプを蛇行するように接続
することによって、２つの熱交換路１４ａ，１４ｂが放
熱フィンの長手方向両側に分離して形成されている。[0005] The indoor heat exchanger 13 has a plurality of heat-radiating fins (not shown) through which a plurality of heat-exchange pipes are passed.
13b, the two ends of the two heat exchange paths 13a and 13b are connected to each other, and the connection at one end thereof is connected to the four-way switching valve 12
In addition, a connection portion on the other end side is connected to the expansion valve 15. Further, the outdoor heat exchanger 14 is connected in a meandering manner to a plurality of heat exchange pipes penetrating a large number of rectangular heat radiation fins, so that the two heat exchange paths 14a and 14b are formed on both longitudinal sides of the heat radiation fins. Are formed separately.
【０００６】また、室外熱交換器１４の熱交換路１４
ａ，１４ｂを形成するそれぞれの熱交換パイプの接続端
部間に、２つの入側接続口１６ａ及び出側接続口１６ｂ
が接続され、熱交換路１４ａ及び熱交換路１４ｂ間を液
相の冷媒が流通するように気液分離器１６が直列に挿入
されている。さらに、気液分離器１６の気相分排出口１
６ｃには、中間部に開閉弁である電磁弁１９が設けられ
たバイパス管１７の一端が接続され、このバイパス管１
７の他端が、四方切換弁１２と圧縮機１１の吸入口１１
ｂとの間を接続する冷媒吸入流路１８に接続されてい
る。The heat exchange path 14 of the outdoor heat exchanger 14
a, 14b between the connection ends of the heat exchange pipes forming the two inlet connection ports 16a and the outlet connection port 16b.
Are connected, and a gas-liquid separator 16 is inserted in series so that a liquid-phase refrigerant flows between the heat exchange path 14a and the heat exchange path 14b. Further, the gas-phase discharge port 1 of the gas-liquid separator 16
6c is connected to one end of a bypass pipe 17 provided with an electromagnetic valve 19 which is an opening / closing valve at an intermediate portion.
7 is connected to the four-way switching valve 12 and the suction port 11 of the compressor 11.
b is connected to a refrigerant suction flow path 18 that connects between the refrigerant suction passages b and b.
【０００７】これにより、暖房運転時に、室外熱交換器
１４の熱交換路１４ａで熱交換によって気液混合状態と
なった冷媒は、気液分離器１６で気相分が除かれて液相
分が多い状態で熱交換路１４ｂでの熱交換が行われるこ
とになり、管内の冷媒の流速が高速度とならず圧力損失
の増加が抑制され、また、熱交換路１４ａと熱交換路１
４ｂとが冷媒の流通方向に直列に１パスとなるように接
続され、冷媒を分流することによって生じる熱交換性能
の低下を防止することができる。As a result, during the heating operation, the refrigerant in the gas-liquid mixed state due to heat exchange in the heat exchange path 14a of the outdoor heat exchanger 14 has its gas phase removed by the gas-liquid separator 16 and has its liquid phase separated. The heat exchange in the heat exchange path 14b is performed in a state where there is a large amount of heat, the flow velocity of the refrigerant in the pipe does not become high, the increase in pressure loss is suppressed, and the heat exchange path 14a and the heat exchange path 1
4b is connected in series with the flow direction of the refrigerant so as to form one pass, and it is possible to prevent a decrease in heat exchange performance caused by dividing the refrigerant.
【０００８】[0008]
【発明が解決しようとする課題】上述した従来の冷凍サ
イクルにおいては、バイパス管１７が四方切換弁１２と
圧縮機１１の吸入口１１ｂとを接続する冷媒吸入流路１
８に接続されているため、圧縮機１１の振動分を吸収す
る必要性から、配管構造が複雑になるという問題があっ
た。In the above-described conventional refrigeration cycle, the bypass pipe 17 connects the four-way switching valve 12 and the suction port 11b of the compressor 11 with the refrigerant suction flow path 1.
8, there is a problem that the piping structure becomes complicated due to the necessity of absorbing the vibration of the compressor 11.
【０００９】また、室内外の温度や圧縮機１１の回転数
などの使用条件によっては、気液分離器１６から液相の
冷媒がバイパス管１７を介して、圧縮機１１の吸入口１
１ｂに導かれるいわゆる、液バックの可能性があるた
め、使用条件に応じて電磁弁１９を閉成する必要があ
り、常時気液分離の効果が得られないという問題もあっ
た。In addition, depending on operating conditions such as indoor and outdoor temperatures and the number of revolutions of the compressor 11, a liquid-phase refrigerant flows from the gas-liquid separator 16 through the bypass pipe 17 and is supplied to the suction port 1 of the compressor 11.
Since there is a possibility of so-called liquid back being led to 1b, it is necessary to close the solenoid valve 19 according to use conditions, and there is also a problem that the effect of gas-liquid separation cannot always be obtained.
【００１０】さらに、室外熱交換器１４の熱交換路に対
する接続位置に応じて使用電力が変化するという問題も
あった。Further, there is another problem that the electric power used varies depending on the connection position of the outdoor heat exchanger 14 to the heat exchange path.
【００１１】本発明は上記の問題点を解決するためにな
されたもので、その目的は気液分離器からのバイパス管
の配管構造を簡易化することのできる冷凍サイクルを提
供するにある。SUMMARY OF THE INVENTION The present invention has been made to solve the above problems, and an object of the present invention is to provide a refrigeration cycle which can simplify a piping structure of a bypass pipe from a gas-liquid separator.
【００１２】本発明の他の目的は気液分離器からの液バ
ックを抑制して、気液分離システムの信頼性の向上を図
り得る冷凍サイクルを提供するにある。Another object of the present invention is to provide a refrigeration cycle capable of suppressing the liquid back from the gas-liquid separator and improving the reliability of the gas-liquid separation system.
【００１３】本発明のもう一つの目的は消費電力を低減
することのできる冷凍サイクルを提供するにある。Another object of the present invention is to provide a refrigeration cycle capable of reducing power consumption.
【００１４】[0014]
【課題を解決するための手段】請求項１に係る発明は、
気相の冷媒を圧送する圧縮機の吐出側と吸入側の間に、
第１の熱交換器と第２の熱交換器とを直列に管接続し、
第１及び第２の熱交換器のいずれか一方を蒸発器とし、
いずれか他方を凝縮器としてそれぞれ機能させると共
に、蒸発器と凝縮器の役割を逆転させる四方切換弁が圧
縮機の吐出経路及び吸入経路に設けられた冷凍サイクル
において、蒸発器として機能する熱交換器の熱交換路の
途中の冷媒を気液分離する気液分離器と、気液分離器で
分離された気相の冷媒を、蒸発器として機能する熱交換
器の出口と四方切換弁とを接続する管路に流入させるバ
イパス管と、を備えたことを特徴とする。The invention according to claim 1 is
Between the discharge side and the suction side of the compressor that pumps the gas phase refrigerant,
Connecting a first heat exchanger and a second heat exchanger in series with a pipe;
One of the first and second heat exchangers is an evaporator,
A heat exchanger that functions as an evaporator in a refrigeration cycle in which one of the other functions as a condenser and a four-way switching valve that reverses the role of the evaporator and the condenser is provided in the discharge path and the suction path of the compressor. A gas-liquid separator for gas-liquid separation of the refrigerant in the middle of the heat exchange path, and a gas-phase refrigerant separated by the gas-liquid separator is connected to the outlet of the heat exchanger functioning as an evaporator and a four-way switching valve. And a bypass pipe that flows into a pipeline that performs the bypass operation.
【００１５】請求項２に係る発明は、請求項１に記載の
冷凍サイクルにおいて、バイパス管の少なくとも一部
を、蒸発器として機能する熱交換器の鉛直方向の全長の
略３／４以上の高さ位置に設けたことを特徴とする。According to a second aspect of the present invention, in the refrigeration cycle according to the first aspect, at least a part of the bypass pipe has a height of about の or more of a total length in the vertical direction of the heat exchanger functioning as an evaporator. It is characterized in that it is provided at the position.
【００１６】請求項３に係る発明は、請求項１又は２に
記載の冷凍サイクルにおいて、蒸発器として機能する熱
交換器の熱交換路のうち、冷媒の乾き度が０．５±０．
２である位置、又は、熱交換路の全長に対して入口から
５０±２０％の長さ位置に気液分離器を設けたことを特
徴とする。According to a third aspect of the present invention, in the refrigeration cycle according to the first or second aspect, the dryness of the refrigerant in the heat exchange path of the heat exchanger functioning as an evaporator is 0.5 ± 0.5.
2. The gas-liquid separator is provided at a position 2 or at a position 50 ± 20% from the inlet with respect to the entire length of the heat exchange path.
【００１７】請求項４に係る発明は、請求項１乃至３の
いずれか１項に記載の冷凍サイクルにおいて、気液分離
器を境として、上流側の熱交換路の本数よりも下流側の
直後の熱交換路の本数を少なくしたことを特徴とする。According to a fourth aspect of the present invention, in the refrigeration cycle according to any one of the first to third aspects, the refrigeration cycle is located immediately downstream of the number of upstream heat exchange paths with respect to the gas-liquid separator. Characterized in that the number of heat exchange paths is reduced.
【００１８】請求項５に係る発明は、請求項１乃至４の
いずれか１項に記載の冷凍サイクルにおいて、バイパス
管に逆止弁を設けたことを特徴とする。According to a fifth aspect of the present invention, in the refrigeration cycle according to any one of the first to fourth aspects, a check valve is provided in the bypass pipe.
【００１９】請求項６に係る発明は、請求項１乃至４の
いずれか１項に記載の冷凍サイクルにおいて、気液分離
器が設けられる熱交換器が蒸発器として機能するとき開
放され、凝縮器として機能するとき閉成される二方弁を
バイパス管に設けたことを特徴とする。According to a sixth aspect of the present invention, in the refrigeration cycle according to any one of the first to fourth aspects, the heat exchanger provided with the gas-liquid separator is opened when the heat exchanger functions as an evaporator, and the condenser is opened. A two-way valve, which is closed when functioning as, is provided in the bypass pipe.
【００２０】請求項７に係る発明は、請求項６に記載の
冷凍サイクルにおいて、気液分離器が設けられる熱交換
器の除霜運転時に二方弁を開放することを特徴とする。According to a seventh aspect of the present invention, in the refrigeration cycle according to the sixth aspect, the two-way valve is opened during a defrosting operation of the heat exchanger provided with the gas-liquid separator.
【００２１】[0021]
【発明の実施の形態】以下、本発明を図面に示す好適な
実施形態に基づいて詳細に説明する。図１は本発明に係
る冷凍サイクルの一実施形態の構成を示す系統図であ
り、図中、従来装置を示した図４と同一の要素には同一
の符号を付してその説明を省略する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, the present invention will be described in detail based on preferred embodiments shown in the drawings. FIG. 1 is a system diagram showing a configuration of an embodiment of a refrigeration cycle according to the present invention. In the figure, the same elements as those in FIG. .
【００２２】図１に示した冷凍サイクル２０は、本発明
に直接関係する室外熱交換器２１と、これに付帯的に設
けられる気液分離器１６とを中心にして記載し、室内熱
交換器の系統を省略して示してある。そして、上述した
と同様に、室外熱交換器が蒸発器として機能する暖房モ
ードでの運転時を主にして説明する。The refrigeration cycle 20 shown in FIG. 1 mainly describes an outdoor heat exchanger 21 directly related to the present invention and a gas-liquid separator 16 attached to the outdoor heat exchanger 21. Are omitted from the illustration. Then, as described above, the description will be given mainly of the operation in the heating mode in which the outdoor heat exchanger functions as an evaporator.
【００２３】ここで、暖房モードでの運転時に蒸発器と
して機能する室外熱交換器２１は、膨張弁１５を通して
送り込まれる液相冷媒の入口２７と、四方切換弁１２に
送り出す気相冷媒の出口２８とを備える。液相冷媒の入
口２７には熱交換路２１ａ及び熱交換路２１ｂの各一端
が共通に接続され、これらの熱交換路２１ａ，２１ｂの
他端は相互に接続されると共に、１本の配管によって気
液分離器１６の入側接続口１６ａに接続されている。気
液分離器１６の出側接続口１６ｂは１本の配管によって
熱交換路２１ｃの一端に接続されている。この熱交換路
２１ｃの他端は、互いに分岐された熱交換路２１ｄ及び
熱交換路２１ｅの一端に共通に接続され、さらに、これ
らの熱交換路２１ｄ，２１ｅの他端は気相冷媒の出口２
８に接続されている。しかして、室外熱交換器２１の流
路は２−１−２パスを形成し、気液分離器１６の上流側
は２パスで、下流側は１パスとなっている。Here, the outdoor heat exchanger 21 functioning as an evaporator during the operation in the heating mode has an inlet 27 for a liquid-phase refrigerant fed through the expansion valve 15 and an outlet 28 for a gas-phase refrigerant sent to the four-way switching valve 12. And One end of the heat exchange path 21a and one end of the heat exchange path 21b are commonly connected to the inlet 27 of the liquid-phase refrigerant, and the other ends of the heat exchange paths 21a and 21b are connected to each other and are connected by one pipe. It is connected to the inlet connection port 16a of the gas-liquid separator 16. The outlet connection port 16b of the gas-liquid separator 16 is connected to one end of the heat exchange path 21c by one pipe. The other end of the heat exchange path 21c is commonly connected to one end of a heat exchange path 21d and one end of a heat exchange path 21e which are branched from each other. Further, the other ends of the heat exchange paths 21d and 21e are connected to an outlet of a gas-phase refrigerant. 2
8 is connected. Thus, the flow path of the outdoor heat exchanger 21 forms a 2-1-2 path, the upstream side of the gas-liquid separator 16 has two paths, and the downstream side has one path.
【００２４】また、室外熱交換器２１の気相冷媒の出口
２８は、その途中に連結部２４が設けられた冷媒吸入流
路２２によって四方切換弁１２に接続されている。そし
て、気液分離器１６の気相分排出口１６ｃがバイパス管
２５によって冷媒吸入流路２２の連結部２４に接続され
ている。このバイパス管２５の途中には、気液分離器１
６で分離された気相の冷媒を冷媒吸入流路２２に流入さ
せ、冷房運転時に冷媒吸入流路２２から気液分離器１６
に対して冷媒が戻ることを阻止する逆止弁２６が設けら
れている。An outlet 28 of the gas-phase refrigerant of the outdoor heat exchanger 21 is connected to the four-way switching valve 12 by a refrigerant suction passage 22 provided with a connecting portion 24 in the middle thereof. The gas-phase-port outlet 16 c of the gas-liquid separator 16 is connected to the connection portion 24 of the refrigerant suction passage 22 by a bypass pipe 25. In the middle of the bypass pipe 25, the gas-liquid separator 1
The refrigerant in the gaseous phase separated in step 6 is allowed to flow into the refrigerant suction flow path 22, and the gas-liquid separator 16 is removed from the refrigerant suction flow path 22 during the cooling operation.
A check valve 26 is provided for preventing the refrigerant from returning to the valve.
【００２５】なお、液相冷媒の入口２７は室外熱交換器
２１の設置状態でみて、鉛直方向下方に配置され、気相
冷媒の出口２８は鉛直方向上方に配置され、連結部２４
は室外熱交換器２１の鉛直方向の全長の略３／４以上の
高さ位置に設けられている。When the outdoor heat exchanger 21 is installed, the inlet 27 of the liquid-phase refrigerant is disposed vertically downward, and the outlet 28 of the gas-phase refrigerant is disposed vertically upward,
Is provided at a height of about 3/4 or more of the total length of the outdoor heat exchanger 21 in the vertical direction.
【００２６】さらに、気液分離器１６は２−１−２パス
を形成する熱交換路のうち、冷媒の乾き度が０．５±
０．２である位置、又は、熱交換路の全長に対して入口
から５０±２０％の長さ位置に設けられている。Further, the gas-liquid separator 16 has a dryness of the refrigerant of 0.5 ± 0.5 in the heat exchange path forming the 2-1-2 path.
It is provided at a position of 0.2 or 50 ± 20% of the total length of the heat exchange path from the inlet.
【００２７】上記のように構成された本実施形態の動作
について、特に、従来装置と構成を異にする部分を中心
にして以下に説明する。先ず、圧縮機１１から圧送され
た気相の冷媒は四方切換弁１２を通して図１では図示を
省略した室内熱交換器に送り込まれ、ここで熱交換され
て液相の冷媒となり、冷媒流量の制御を行う膨張弁１５
を介して、液相冷媒の入口２７から室外熱交換器２１に
流入する。室外熱交換器２１の内部においては、熱交換
路２１ａ及び熱交換路２１ｂによってそれぞれ熱交換が
行われ、気相分と液相分とが混合した気液２相状態の冷
媒が気液分離器１６に流入する。気液分離器１６はこの
冷媒を気相分と液相分とに分離し、このうち、気相分は
バイパス管２５を通して冷媒吸入流路２２に送り込ま
れ、液相分は熱交換路２１ｃに送りこまれてここで熱交
換が行われ、さらに、熱交換路２１ｄ，２１ｅに分流し
てそれぞれにて熱交換が行われ、略全部の冷媒が気相分
として気相冷媒の出口２８から冷媒吸入流路２２に送り
出される。この気相冷媒はバイパス管２５からのものと
合流して、四方切換弁１２を介して、サクションカップ
２３に流入し、圧縮機１１はその吸入口１１ｂから吸入
して吐出口１１ａから吐出させる。The operation of the present embodiment configured as described above will be described below, particularly focusing on parts that differ in configuration from the conventional apparatus. First, the gas-phase refrigerant pumped from the compressor 11 is sent to an indoor heat exchanger (not shown in FIG. 1) through the four-way switching valve 12, where the heat is exchanged to become a liquid-phase refrigerant, and the refrigerant flow rate is controlled. Expansion valve 15
, Flows into the outdoor heat exchanger 21 from the inlet 27 of the liquid-phase refrigerant. Inside the outdoor heat exchanger 21, heat is exchanged by the heat exchange path 21a and the heat exchange path 21b, and a gas-liquid two-phase refrigerant in which a gas phase component and a liquid phase component are mixed is separated into a gas-liquid separator. Flow into 16. The gas-liquid separator 16 separates the refrigerant into a gaseous phase component and a liquid phase component, of which the gaseous phase component is sent to the refrigerant suction passage 22 through the bypass pipe 25, and the liquid phase component is transferred to the heat exchange path 21c. The heat is exchanged here and heat exchange is performed. Further, the heat is exchanged by dividing the heat into the heat exchange paths 21d and 21e. It is sent out to the channel 22. This gas-phase refrigerant merges with the refrigerant from the bypass pipe 25, flows into the suction cup 23 via the four-way switching valve 12, and the compressor 11 sucks in from the suction port 11b and discharges it from the discharge port 11a.
【００２８】ここで、四方切換弁１２とサクションカッ
プ２３との接続部分は、圧縮機１１の振動を吸収する部
分であり、図４に示した従来の冷凍サイクルはこの部位
にバイパス管を接続したため、その配管構造の複雑化を
余儀なくされた。この実施形態においては室外熱交換器
２１の気相冷媒の出口２８と四方切換弁１２とを接続す
る冷媒吸入流路２２の連結部２４にバイパス管２５を接
続したため、圧縮機１１の振動を吸収する構造を採用す
る必要性がなくなることから、配管構造を簡易化するこ
とができる。Here, the connecting portion between the four-way switching valve 12 and the suction cup 23 is a portion for absorbing the vibration of the compressor 11, and the conventional refrigeration cycle shown in FIG. 4 has a bypass pipe connected to this portion. , Complicating its piping structure. In this embodiment, since the bypass pipe 25 is connected to the connection portion 24 of the refrigerant suction flow path 22 that connects the gas-phase refrigerant outlet 28 of the outdoor heat exchanger 21 and the four-way switching valve 12, vibration of the compressor 11 is absorbed. Since there is no need to adopt a structure that performs the above, the piping structure can be simplified.
【００２９】また、この実施形態では、室外熱交換器２
１の下方に液相冷媒入口２７を、上方に気相冷媒出口２
８を配置し、連結部２４を室外熱交換器２１の鉛直方向
の全長の略３／４以上の高さ位置に、最適には気相冷媒
出口２８と同等又はより高い位置に設けている。これに
よって、気液分離器１６から液相の冷媒がバイパス管２
５に流出しても液相分は重力により上方に到達し難いよ
うな抵抗を受けることとなり、液バック現象を抑制する
ことができる。これによって、気液分離システムの信頼
性を向上させることができる。なお、連結部２４に限ら
ず、バイパス管２５の一部が上記高さに位置するように
すれば同一の効果を得ることができる。In this embodiment, the outdoor heat exchanger 2
1, a liquid-phase refrigerant inlet 27 and a gas-phase refrigerant outlet 2 above.
8 and the connecting portion 24 is provided at a height of about 略 or more of the total length of the outdoor heat exchanger 21 in the vertical direction, and optimally at a position equivalent to or higher than the gas-phase refrigerant outlet 28. As a result, the refrigerant in the liquid phase is supplied from the gas-liquid separator 16 to the bypass pipe 2.
Even if the liquid flows out, the liquid phase receives a resistance that does not easily reach the upper side due to gravity, and the liquid back phenomenon can be suppressed. Thereby, the reliability of the gas-liquid separation system can be improved. The same effect can be obtained if not only the connecting portion 24 but also a part of the bypass pipe 25 is located at the above-mentioned height.
【００３０】ところで、室外熱交換器２１の熱交換路の
途中の冷媒を気液分離する気液分離器の接続位置は、熱
交換路の全長のどの途中位置が適当であるかを決定する
ための実験結果を図２に示す。図２は電力容量が１ＨＰ
（馬力）の一般家庭用の空気調和機に本実施形態に示す
気液分離器１６を新たに設けるとき、蒸発器の入口から
の流路長の比率と入力電力の軽減量（及び入力電力の軽
減率）の関係をプロットして得られた線図である。この
図から明らかなように、流路長の比率が０（％）（蒸発
器の入口）であってもある程度の入力電力の軽減効果が
得られ、この位置から流路長の比率が大きくなるに従っ
て入力電力の軽減効果は次第に大きくなり、流路長の比
率が５０（％）で最大となり、この位置から流路長の比
率が大きくなるに従って入力電力の軽減効果は次第に小
さくなり、１００（％）の位置で入力電力の軽減効果は
ゼロになっている。By the way, the connection position of the gas-liquid separator for gas-liquid separation of the refrigerant in the middle of the heat exchange path of the outdoor heat exchanger 21 is to determine which halfway position of the entire length of the heat exchange path is appropriate. FIG. 2 shows the results of the experiment. Figure 2 shows that the power capacity is 1HP
When the gas-liquid separator 16 according to the present embodiment is newly provided in an air conditioner for general household (horsepower), the ratio of the flow path length from the inlet of the evaporator to the reduction amount of the input power (and the input power FIG. 3 is a diagram obtained by plotting the relationship of (reduction rate). As is clear from this figure, even if the ratio of the flow path length is 0 (%) (the inlet of the evaporator), a certain effect of reducing the input power can be obtained, and the flow path length ratio increases from this position. , The effect of reducing the input power gradually increases, and becomes maximum when the ratio of the flow path length is 50 (%). As the ratio of the flow path length increases from this position, the reduction effect of the input power gradually decreases to 100 (%). The effect of reducing the input power is zero at the position ().
【００３１】しかして、実用的には熱交換路の全長に対
して入口から５０±２０％の長さ位置に気液分離器を設
けることが妥当と考えられ。この場合、蒸発器の入口の
気相の冷媒がその出口にて全て気相の冷媒に移行する理
想的な状態とすれば、上記入口からの流路長比率を冷媒
の乾き度に置き換えることができるため、冷媒の乾き度
が０．５±０．２である位置に気液分離器を設けるよう
にしても、同様な結果が得られ、これによって、消費電
力を低減することができる。However, in practice, it is considered appropriate to provide the gas-liquid separator at a position 50 ± 20% from the inlet with respect to the entire length of the heat exchange path. In this case, assuming an ideal state in which the gas-phase refrigerant at the inlet of the evaporator is all transferred to the gas-phase refrigerant at the outlet, the flow path length ratio from the inlet can be replaced with the dryness of the refrigerant. Therefore, even if the gas-liquid separator is provided at a position where the dryness of the refrigerant is 0.5 ± 0.2, similar results can be obtained, and power consumption can be reduced.
【００３２】ところで、特開平９−１５２２１６号公報
に記載のものは、バイパス管１７の途中に二方弁として
の電磁弁１９を設け、暖房運転時にこれに通電して開放
状態とし、運転状態に応じて液バックの可能性がある場
合にこれを閉成したため、暖房運転時間に応じて、例え
ば、５（Ｗ）程度の電力を消費し続ける構成になってい
た。本実施形態では、バイパス管２５に逆止弁２６を設
けているので、消費電力低減の効果が高められる。In the device described in Japanese Patent Application Laid-Open No. Hei 9-152216, a solenoid valve 19 is provided as a two-way valve in the middle of the bypass pipe 17, and when the heating operation is performed, the solenoid valve 19 is energized to be opened, and the operation state is changed. Accordingly, when there is a possibility of liquid back, the liquid back is closed, so that, for example, power of about 5 (W) is continuously consumed according to the heating operation time. In the present embodiment, since the check valve 26 is provided in the bypass pipe 25, the effect of reducing power consumption is enhanced.
【００３３】なお、除霜運転時には、暖房運転モードの
途中に四方切換弁１２を切り換えて室外熱交換器２１に
気相の冷媒を送り込む必要性がある。この時、逆止弁２
６の代わりに二方弁である電磁弁を用いることによっ
て、暖房モードでの運転時にこの二方弁を開放し、冷房
モードでの運転時にこの二方弁を閉成し、除霜運転時に
この二方弁を開放する構成とすることもできる。これに
よって、除霜運転時に暖かい気相冷媒をバイパス管２
５，気液分離器１６を介して熱交換路２１ａ，２１ｂに
直接導くことができ、霜の溶けにくい部分の除霜を効果
的に行うことができる。気液分離システムを除霜運転に
効果的に利用することができる。この場合、逆止弁を用
いた場合の開閉音を防止するという効果も得られる。At the time of the defrosting operation, it is necessary to switch the four-way switching valve 12 during the heating operation mode to send the gaseous refrigerant to the outdoor heat exchanger 21. At this time, check valve 2
By using an electromagnetic valve that is a two-way valve instead of 6, the two-way valve is opened during operation in the heating mode, the two-way valve is closed during operation in the cooling mode, and the two-way valve is closed during the defrosting operation. The two-way valve may be opened. As a result, during the defrosting operation, the warm gas-phase refrigerant is
5, it can be directly guided to the heat exchange paths 21a and 21b via the gas-liquid separator 16, and the defrosting of the portion where the frost hardly melts can be effectively performed. The gas-liquid separation system can be effectively used for the defrosting operation. In this case, the effect of preventing the opening and closing noise when the check valve is used is also obtained.
【００３４】また、上述した二方弁の電力消費を抑制す
るという観点では、一般にメカトロ弁と称されるパルス
モータを利用した弁を採用することができる。図３はバ
イパス管２５にメカトロ弁を用いるものとして、蒸発器
の入口からの流路長の比率と、使用するメカトロ弁の口
径及びその絞り量の関係を示した図表で、例えば、蒸発
器の入口からの流路長の比率が５０（％）の位置では弁
口径が５．０（ｍｍ）のものを全開状態で使用すること
によって、特別な絞り機構を用いることなしに良好な気
液分離機能が得られる。Further, from the viewpoint of suppressing the power consumption of the two-way valve, a valve using a pulse motor generally called a mechatronic valve can be employed. FIG. 3 is a table showing the relationship between the ratio of the flow path length from the inlet of the evaporator, the diameter of the mechatronic valve to be used, and the amount of restriction thereof, assuming that the mechatronic valve is used for the bypass pipe 25. At the position where the ratio of the flow path length from the inlet is 50 (%), by using the valve with the valve diameter of 5.0 (mm) in the fully open state, good gas-liquid separation can be performed without using a special throttle mechanism. The function is obtained.
【００３５】一方、気液分離を行うに当たり、上流側の
熱交換路と比較して下流の直後の熱交換路の本数が少な
い状況で気相の冷媒をバイパスさせれば、下流に圧送さ
れる気相の冷媒を効果的に分離することができ、液相の
冷媒を下流に圧送する抵抗を減らすことができる。本実
施形態では、熱交換路２１ａ及び２１ｂの出口側を共通
に接続し、１本の管路で気液分離器１６に導き、さら
に、気液分離器１６の１本の管路によって熱交換路２１
ｃに移送する構成になっているため、気液分離特性を向
上させることができる。なお、気液分離器１６の下流側
でも最終的には複数の熱交換路に分流させる必要がある
が、本実施形態では熱交換路２１ｃの出口側を熱交換路
２１ｄ，２１ｅに分流させる構成であるため、三方ベン
ドと称される分流器で済むため安価に構成できる利点も
得られる。On the other hand, in performing gas-liquid separation, if the gaseous phase refrigerant is bypassed in a situation where the number of heat exchange paths immediately downstream is smaller than that of the upstream heat exchange path, the refrigerant is pumped downstream. The gas phase refrigerant can be effectively separated, and the resistance of pumping the liquid phase refrigerant downstream can be reduced. In the present embodiment, the outlet sides of the heat exchange paths 21a and 21b are commonly connected, guided to the gas-liquid separator 16 by one pipe, and further heat-exchanged by one pipe of the gas-liquid separator 16. Road 21
c, the gas-liquid separation characteristics can be improved. In addition, although it is necessary to finally divide the flow into a plurality of heat exchange paths even on the downstream side of the gas-liquid separator 16, in the present embodiment, the configuration is such that the outlet side of the heat exchange path 21c is diverted to the heat exchange paths 21d and 21e. Therefore, there is also obtained an advantage that it can be configured at a low cost because a current divider called a three-way bend is sufficient.
【００３６】[0036]
【発明の効果】以上の説明によって明らかなように、本
発明によれば、気液分離器からのバイパス管の配管構造
を簡易化することのできる冷凍サイクルを提供すること
ができる。As is apparent from the above description, according to the present invention, it is possible to provide a refrigeration cycle that can simplify the piping structure of the bypass pipe from the gas-liquid separator.
【図１】本発明に係る冷凍サイクルの一実施形態の構成
を示す系統図。FIG. 1 is a system diagram showing a configuration of an embodiment of a refrigeration cycle according to the present invention.
【図２】図１に示した実施形態の動作を説明するため
に、熱交換路の途中の冷媒を気液分離する気液分離器の
接続位置と入力電力の低減量との関係を示す図表。FIG. 2 is a chart showing a relationship between a connection position of a gas-liquid separator for gas-liquid separation of a refrigerant in the middle of a heat exchange path and a reduction amount of input power in order to explain an operation of the embodiment shown in FIG. .
【図３】図１に示した実施形態のバイパス管にメカトロ
弁と称されるパルスモータを利用した弁を採用した場合
における蒸発器の入口からの流路長の比率と、使用する
メカトロ弁の口径及びその絞り量の関係を示した図表。FIG. 3 shows the ratio of the flow path length from the inlet of the evaporator when a valve using a pulse motor called a mechatronic valve is employed in the bypass pipe of the embodiment shown in FIG. 4 is a table showing the relationship between the aperture and the amount of aperture.
【図４】従来の冷凍サイクルの構成を示す系統図。FIG. 4 is a system diagram showing a configuration of a conventional refrigeration cycle.
１１ 圧縮機 １２ 四方切換弁 １５ 膨張弁 １６ 気液分離器 ２０ 冷凍サイクル ２１ 蒸発器として機能する室外熱交換器 ２１ａ〜２１ｅ 熱交換路 ２２ 冷媒吸入流路 ２３ サクションカップ ２４ 連結部 ２５ バイパス管 ２６ 逆止弁 DESCRIPTION OF SYMBOLS 11 Compressor 12 Four-way switching valve 15 Expansion valve 16 Gas-liquid separator 20 Refrigeration cycle 21 Outdoor heat exchanger functioning as an evaporator 21a-21e Heat exchange path 22 Refrigerant suction flow path 23 Suction cup 24 Connecting part 25 Bypass pipe 26 Reverse Stop valve
Claims (7)
入側の間に、第１の熱交換器と第２の熱交換器とを直列
に管接続し、前記第１及び第２の熱交換器のいずれか一
方を蒸発器とし、いずれか他方を凝縮器としてそれぞれ
機能させると共に、蒸発器と凝縮器の役割を逆転させる
四方切換弁が前記圧縮機の吐出経路及び吸入経路に設け
られた冷凍サイクルにおいて、 蒸発器として機能する前記熱交換器の熱交換路の途中の
冷媒を気液分離する気液分離器と、 前記気液分離器で分離された気相の冷媒を、蒸発器とし
て機能する前記熱交換器の出口と前記四方切換弁とを接
続する管路に流入させるバイパス管と、 を備えたことを特徴とする冷凍サイクル。1. A first heat exchanger and a second heat exchanger are connected in series between a discharge side and a suction side of a compressor for pumping a gaseous refrigerant, and the first and second heat exchangers are connected in series. One of the two heat exchangers functions as an evaporator, and the other functions as a condenser. A four-way switching valve for reversing the role of the evaporator and the condenser is provided in the discharge path and the suction path of the compressor. In the provided refrigeration cycle, a gas-liquid separator for gas-liquid separation of the refrigerant in the middle of the heat exchange path of the heat exchanger functioning as an evaporator, and a gas-phase refrigerant separated by the gas-liquid separator, A refrigeration cycle comprising: a bypass pipe that flows into a pipe connecting the outlet of the heat exchanger functioning as an evaporator and the four-way switching valve.
器として機能する前記熱交換器の鉛直方向の全長の略３
／４以上の高さ位置に設けたことを特徴とする請求項１
に記載の冷凍サイクル。2. The heat exchanger, which functions as an evaporator, has at least a portion of at least a part of the bypass pipe having a length of approximately 3
2. The apparatus according to claim 1, wherein the height is set to / 4 or more.
The refrigeration cycle according to 1.
換路のうち、冷媒の乾き度が０．５±０．２である位
置、又は、熱交換路の全長に対して入口から５０±２０
％の長さ位置に前記気液分離器を設けたことを特徴とす
る請求項１又は２に記載の冷凍サイクル。3. The heat exchange path of the heat exchanger functioning as an evaporator, wherein the dryness of the refrigerant is 0.5 ± 0.2 or 50% from the inlet with respect to the entire length of the heat exchange path. ± 20
3. The refrigeration cycle according to claim 1, wherein the gas-liquid separator is provided at a position corresponding to a% length.
換路の本数よりも下流側の直後の熱交換路の本数を少な
くしたことを特徴とする請求項１乃至３のいずれか１項
に記載の冷凍サイクル。4. The apparatus according to claim 1, wherein the number of heat exchange paths immediately downstream of the gas-liquid separator is smaller than the number of heat exchange paths of the upstream side. Item 2. The refrigeration cycle according to item 1.
徴とする請求項１乃至４のいずれか１項に記載の冷凍サ
イクル。5. The refrigeration cycle according to claim 1, wherein a check valve is provided in the bypass pipe.
が蒸発器として機能するとき開放され、凝縮器として機
能するとき閉成される二方弁を前記バイパス管に設けた
ことを特徴とする請求項１乃至４のいずれか１項に記載
の冷凍サイクル。6. The bypass pipe is provided with a two-way valve which is opened when the heat exchanger in which the gas-liquid separator is provided functions as an evaporator and closed when it functions as a condenser. The refrigeration cycle according to any one of claims 1 to 4, wherein
の除霜運転時に前記二方弁を開放することを特徴とする
請求項６に記載の冷凍サイクル。7. The refrigeration cycle according to claim 6, wherein the two-way valve is opened during a defrosting operation of the heat exchanger provided with the gas-liquid separator.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001184362A JP4408591B2 (en) | 2001-06-19 | 2001-06-19 | Refrigeration cycle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001184362A JP4408591B2 (en) | 2001-06-19 | 2001-06-19 | Refrigeration cycle |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2002372323A true JP2002372323A (en) | 2002-12-26 |
| JP4408591B2 JP4408591B2 (en) | 2010-02-03 |
Family
ID=19024134
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2001184362A Expired - Fee Related JP4408591B2 (en) | 2001-06-19 | 2001-06-19 | Refrigeration cycle |
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| Country | Link |
|---|---|
| JP (1) | JP4408591B2 (en) |
-
2001
- 2001-06-19 JP JP2001184362A patent/JP4408591B2/en not_active Expired - Fee Related
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