JPS6028935Y2 - Heat pump air conditioning system - Google Patents
Heat pump air conditioning systemInfo
- Publication number
- JPS6028935Y2 JPS6028935Y2 JP9346780U JP9346780U JPS6028935Y2 JP S6028935 Y2 JPS6028935 Y2 JP S6028935Y2 JP 9346780 U JP9346780 U JP 9346780U JP 9346780 U JP9346780 U JP 9346780U JP S6028935 Y2 JPS6028935 Y2 JP S6028935Y2
- Authority
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- Prior art keywords
- pipe
- expansion valve
- heating
- pressure
- liquid
- 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
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Description
【考案の詳細な説明】
本考案はヒートポンプ式冷暖房装置、詳しくは圧縮機、
四路切換弁、冷房時蒸発器となり暖房時凝縮器となる室
内熱交換器、冷房時凝縮器となり暖房時蒸発器となる室
外熱交換器、受液器、冷房用膨張弁、暖房用膨張弁、を
備えたヒートポンプ式冷暖房装置に関する。[Detailed description of the invention] This invention is a heat pump air conditioning system, specifically a compressor,
Four-way switching valve, indoor heat exchanger that becomes an evaporator during cooling and a condenser during heating, an outdoor heat exchanger that becomes a condenser during cooling and an evaporator during heating, liquid receiver, expansion valve for cooling, expansion valve for heating. The present invention relates to a heat pump type air-conditioning device equipped with.
一般に化種装置は、暖房運転時、暖房負荷が小さくなる
と、室外熱交換器の蒸発能力が、室内熱交換器の凝縮能
力にくらべて過大になるため、凝縮温度及び圧力が異常
に高くなって運転できなくなり、その結果運転範囲が狭
くなる問題があった。In general, when a heating load becomes small during heating operation, the evaporation capacity of the outdoor heat exchanger becomes excessive compared to the condensation capacity of the indoor heat exchanger, resulting in an abnormally high condensation temperature and pressure. There was a problem that the vehicle could no longer be operated, resulting in a narrower operating range.
このため従来では吐出ガス管と吸入ガス管との間に制御
弁を介装したバイパス通路を設けて、前記制御弁の開度
制御により吐出ガスを吸入側にバイパスさせるようにし
ていた。For this reason, in the past, a bypass passage with a control valve interposed between the discharge gas pipe and the suction gas pipe was provided, and the discharge gas was bypassed to the suction side by controlling the opening degree of the control valve.
従って暖房負荷が大幅に小さくなって、室内外熱交換器
のバランスの違いが大きくなると、バイパス量も大きく
しなければならないため、前記、制御弁は大きな容量の
ものを用いる必要があり、制御弁の外形寸法が大きくな
ると共に高価となる問題があった。Therefore, when the heating load becomes significantly smaller and the difference in the balance between the indoor and outdoor heat exchangers becomes large, the amount of bypass must also be increased. There was a problem in that the outer dimensions of the device became larger and the cost increased.
特に、1台の室外ユニットに複数台の室内ユニットを接
続する冷暖房装置において、暖房時室内ユニットを単に
1台のみ運転する低負荷運転時には、蒸発能力が凝縮能
力にくらべて特に大きくなることが避けられず、そのた
め、制御弁は、容量の一層大きなものを用いる必要があ
った。In particular, in air-conditioning equipment that connects multiple indoor units to one outdoor unit, during low-load operation where only one indoor unit is operated during heating, the evaporation capacity should not be particularly large compared to the condensation capacity. Therefore, it was necessary to use a control valve with a larger capacity.
しかして、以上の如き問題に対し、先に、圧縮機の吐出
ガス管と、暖房用膨張弁の入口側と受液器とを結ぶ高圧
液管との間に、ホットガスバイパス管を設け、このバイ
パス管に高圧制御弁を介装したものを提案した(実開昭
55−28437号公報)。Therefore, in order to solve the above problems, first, a hot gas bypass pipe was installed between the discharge gas pipe of the compressor and the high-pressure liquid pipe connecting the inlet side of the heating expansion valve and the liquid receiver. A proposal was made to install a high pressure control valve in this bypass pipe (Japanese Utility Model Publication No. 55-28437).
所が、その冷暖房装置によると、前記した従来の問題を
解決できたのであるが、前記高圧制御弁が動作して、ホ
ットガスが前記高圧液管に流れる時、前記膨張弁におい
て、断続的な異音が発生し、聴覚に不快感を与える問題
があった。However, according to the air conditioning system, the above-mentioned conventional problems could be solved, but when the high pressure control valve operates and hot gas flows into the high pressure liquid pipe, the expansion valve may experience intermittent There was a problem in that the noise generated caused discomfort to the hearing.
そこで、本考案は、前記した従来の問題を解決しながら
、しかも、先に提案した冷暖房装置の問題点も解決すべ
く考案したもので、前記バイパス管の前記高圧液管への
接続位置と、前記暖房用膨張弁の入口側との間の高圧液
管に、ミキシングタンクを介装したところを特徴とする
ものである。Therefore, the present invention was devised to solve the above-mentioned conventional problems and also solve the problems of the air conditioning system proposed earlier. It is characterized in that a mixing tank is interposed in the high-pressure liquid pipe between the heating expansion valve and the inlet side.
以下、本考案ヒートポンプ式冷暖房装置の実施例を図面
に基づいて説明する。DESCRIPTION OF THE PREFERRED EMBODIMENTS Examples of the heat pump air-conditioning apparatus of the present invention will be described below with reference to the drawings.
第1図に示したものは、1台の室外ユニットAに、連絡
配管Cを介して5台の室内ユニットBを接続可能と威し
たヒートポンプ式冷暖房装置である。What is shown in FIG. 1 is a heat pump air-conditioning system in which five indoor units B can be connected to one outdoor unit A via connecting pipes C.
なお、第1図では、1台の室内ユニットBのみを接続し
た状態を示したが、以下の説明では、5台の室内ユニッ
トBを接続したものとして説明する。Although FIG. 1 shows a state in which only one indoor unit B is connected, the following description will be made assuming that five indoor units B are connected.
前記室外ユニットAは、圧縮機1、四路切換弁2、冷房
時凝縮器となり暖房時蒸発器となる室外熱交換器3、暖
房用感温膨張弁4.該膨張弁4と並列に接続する逆止弁
5、受液器6、アキュムレータ7を具備し、これら機器
を冷媒配管8により連結している。The outdoor unit A includes a compressor 1, a four-way switching valve 2, an outdoor heat exchanger 3 that serves as a condenser during cooling and an evaporator during heating, a temperature-sensitive expansion valve 4 for heating. A check valve 5, a liquid receiver 6, and an accumulator 7 are connected in parallel with the expansion valve 4, and these devices are connected by a refrigerant pipe 8.
そして、冷媒配管8における高圧液管9とガス管10と
に、ヘッダを介してそれぞれ5本の液側支管9a・・・
とガス側支管10a・・・とを接続している。Five liquid-side branch pipes 9a are connected to the high-pressure liquid pipe 9 and the gas pipe 10 in the refrigerant pipe 8 via headers, respectively.
and the gas side branch pipe 10a... are connected.
液側支管9a・・・には冷房時開く電磁弁S■1・・・
を介装すると共に、液側支管9a・・・の冷房時開く電
磁弁SV1・・・の出口側位置からは、それぞれ連絡支
管9b・・・を分岐させて、これら各連絡支管9b・・
・に逆止%V□を介装し、該連絡支管9bを分配器9d
を介して連絡管9Cに接続し、該連絡管9cの端部を、
高圧液管9における受液器6と前記ヘッダとの中間位置
に接続している。The liquid side branch pipe 9a... has a solenoid valve S■1... that opens during cooling.
At the same time, connecting branch pipes 9b... are branched from the outlet side positions of the solenoid valves SV1... which open during cooling of the liquid side branch pipes 9a...
・A check %V□ is interposed in the connecting branch pipe 9b to the distributor 9d.
is connected to the communication pipe 9C via the
It is connected to the high pressure liquid pipe 9 at an intermediate position between the liquid receiver 6 and the header.
また、前記ガス側支管10a・・・には、逆止弁CV2
を並列状に接続した暖房時開く電磁弁S■2・・・を介
装している。In addition, the gas side branch pipe 10a... has a check valve CV2.
A solenoid valve S2 connected in parallel and opened during heating is installed.
そして、これら各液側支管9aとガス側支管10aとの
間に前記連絡配管C・・・を介して前記室内ユニットB
を接続している。The indoor unit B is connected between the liquid side branch pipe 9a and the gas side branch pipe 10a via the communication pipe C...
are connected.
前記室内ユニットBは、冷房時蒸発器となり暖房時凝縮
器となる室内熱交換器11と、暖房用膨張弁12に逆止
弁13を並列接続した回路とを冷媒配管14により接続
している。The indoor unit B has an indoor heat exchanger 11 that serves as an evaporator during cooling and a condenser during heating, and a circuit in which a heating expansion valve 12 and a check valve 13 are connected in parallel through a refrigerant pipe 14.
そして、前記圧縮機1は、負荷の大きさに応じて例えば
高圧あるいは低圧を検知して4極と2極とに極数変換可
能なモータにより駆動されるもので、この実施例では、
全負荷容量と172負荷容量とに容量制御可能と威して
いる。The compressor 1 is driven by a motor that can detect, for example, high pressure or low pressure depending on the size of the load and change the number of poles between 4 poles and 2 poles. In this embodiment,
The capacity can be controlled between full load capacity and 172 load capacity.
しかして、第1図に示したものは、以上のごとく構成す
るヒートポンプ式冷暖房装置において、前記圧縮機1の
吐出口と四路切換弁2とを結ぶ前記冷媒配管8の吐出ガ
ス管8aと、前記暖房用膨張弁4の入口側と受液器6と
を結ぶ高圧液管9にホットガスバイパス管15を設け、
このバイパス管15に暖房運転時、高圧圧力が設定値以
上になることにより開動作する高圧制御弁16を介装す
ると共に、前記バイパス管15の高圧液管9への接続位
置と、前記暖房用膨張弁4の入口側との間の前記高圧液
管9にミキシングタンク20を介装したのである。Therefore, in the heat pump type air-conditioning system configured as described above, what is shown in FIG. A hot gas bypass pipe 15 is provided in the high pressure liquid pipe 9 connecting the inlet side of the heating expansion valve 4 and the liquid receiver 6,
This bypass pipe 15 is equipped with a high pressure control valve 16 that opens when the high pressure becomes higher than a set value during heating operation, and the connection position of the bypass pipe 15 to the high pressure liquid pipe 9 and the heating A mixing tank 20 is interposed between the high pressure liquid pipe 9 and the inlet side of the expansion valve 4.
前記バイパス管15の高圧液管9への接続位置は、前記
膨張弁4の入口側に近い箇所が好ましい。The connection position of the bypass pipe 15 to the high-pressure liquid pipe 9 is preferably close to the inlet side of the expansion valve 4.
これは、前記バイパス管15からバイパスしたホットガ
スが前記受液器6に逆流するのを少なくするためで、前
記ホットガスが前記受液器6に逆流すると、その内圧が
高くなり、前記室内熱交換器11から凝縮液冷媒が出に
くくなることがあるためである。This is to reduce the backflow of the hot gas bypassed from the bypass pipe 15 to the liquid receiver 6. When the hot gas flows back to the liquid receiver 6, its internal pressure increases, causing the indoor heat to rise. This is because it may become difficult for condensed refrigerant to come out from the exchanger 11.
又、前記接続位置と、前記膨張弁4の入口側との間の高
圧液管9に介装する前記ミキシングタンク20は、第2
図のごとく胴体21の頂部に、底部22に向かって突入
し、前記底部22に対向して開口する入口管23を密閉
状に取付けると共に、前記胴体21の側部で、前記頂部
側には、前記入口管23と直交する方向に出口管24を
密閉状に取付けるのである。Further, the mixing tank 20 interposed in the high pressure liquid pipe 9 between the connection position and the inlet side of the expansion valve 4 is a second
As shown in the figure, an inlet pipe 23 that protrudes toward the bottom 22 and opens opposite the bottom 22 is attached to the top of the body 21 in a sealed manner, and at the side of the body 21 and on the top side, The outlet pipe 24 is installed in a sealed manner in a direction perpendicular to the inlet pipe 23.
このミキシングタンク20は、第1図及び第3図のごと
く、前記胴体21を、その底部22が下側に、頂部が上
側に位置させて用いてもよいし、また、第4図のごとく
、前記底部22と頂部とを水平方向に配置して用でもよ
い。This mixing tank 20 may be used with the body 21 positioned with the bottom 22 on the lower side and the top on the upper side as shown in FIGS. 1 and 3, or as shown in FIG. The bottom portion 22 and the top portion may be arranged horizontally.
何れの場合でも、前記入口管23から液冷媒とガス冷媒
とが分離した状態で流れ込んでも、これら液冷媒及びガ
ス冷媒は、前記胴体21の内部で混合撹乱し、ガス冷媒
の気泡が分断されて、液冷媒に混ざり合うのである。In any case, even if the liquid refrigerant and the gas refrigerant flow into the inlet pipe 23 in a separated state, the liquid refrigerant and the gas refrigerant are mixed and disturbed inside the body 21, and the bubbles of the gas refrigerant are separated. , it mixes with the liquid refrigerant.
従って前記出口管24からは、液冷媒とガス冷媒とが平
均的に混ざり合った状態で流出し、前記膨張弁4に至る
のであつて、該膨張弁4の通過時、断続的な異音は生じ
ないのである。Therefore, the liquid refrigerant and the gas refrigerant flow out from the outlet pipe 24 in an evenly mixed state and reach the expansion valve 4, and when passing through the expansion valve 4, there is no intermittent noise. It does not occur.
尚、第1図において、31は、キャピラリチューブ31
aをもったリキッドインジェクション回路で、受液器6
と暖房用膨張弁4との間の高圧液管9からアキュムレー
タ7に連通し、冷暖房時高圧液冷媒の一部を減圧してア
キュムレータ7から圧縮機1に供給賦圧縮機1を冷却す
べく威している。In addition, in FIG. 1, 31 is a capillary tube 31.
In the liquid injection circuit with a, the liquid receiver 6
A high-pressure liquid pipe 9 between the heating expansion valve 4 and the heating expansion valve 4 is connected to the accumulator 7, and a part of the high-pressure liquid refrigerant is depressurized during heating and cooling and is supplied from the accumulator 7 to the compressor 1. are doing.
又、32は、暖房時停止中の室内ユニットB・・・に冷
媒が液状で貯溜するのを防止する液溜り防止回路で、キ
ャピラリチューブ32aと逆止弁32bとを直列にして
介装した回路32cを、各電磁弁SV□・・・の暖房時
出口側の液側支管9・・・から、室外熱交換器3と暖房
用膨張弁4との間の低圧液管17に連通させたものであ
る。32 is a liquid accumulation prevention circuit that prevents refrigerant from accumulating in liquid form in the indoor unit B when it is stopped during heating, and is a circuit in which a capillary tube 32a and a check valve 32b are connected in series. 32c is connected to the low pressure liquid pipe 17 between the outdoor heat exchanger 3 and the heating expansion valve 4 from the liquid side branch pipe 9 on the heating outlet side of each solenoid valve SV□... It is.
又、4a、4bは暖房用膨張弁4の感温筒及び外部均圧
管、33は吸入圧力調整弁、34はドライヤフィルタ、
35はフィルタ、36は閉鎖弁、37は室外ファン、3
8は消音器、HPSは高圧圧力開閉器、LPSは低圧圧
力開閉器である。Further, 4a and 4b are the temperature sensing cylinder and external pressure equalizing pipe of the heating expansion valve 4, 33 is the suction pressure regulating valve, 34 is the dryer filter,
35 is a filter, 36 is a closing valve, 37 is an outdoor fan, 3
8 is a silencer, HPS is a high pressure switch, and LPS is a low pressure switch.
しかして、以上の構成において、暖房運転を行なう場合
、四路切換弁2を実線のごとく切換えて圧縮機1の運転
により行なうのであり、例えば室内ユニットBが5台と
も作動する全負荷時においては、圧縮機1は全負荷容量
で運転され、又室内ユニットBが3台作動する略1/2
荷時においては、圧縮機1は1n負荷容量で運転される
のである。Therefore, in the above configuration, when performing heating operation, the four-way selector valve 2 is switched as shown by the solid line to operate the compressor 1. For example, at full load when all five indoor units B are operating, , compressor 1 is operated at full load capacity, and three indoor units B are operated at approximately 1/2
During loading, the compressor 1 is operated with a load capacity of 1n.
そして、これらの運転状態においては、凝縮圧力は、正
常に維持れるのであって、吐出ガス圧力は、前記高圧制
御弁16が開動作し始める前記設定圧力Pより低い正常
圧力に保持され、高圧制御弁16は閉鎖している。In these operating conditions, the condensing pressure is maintained normally, and the discharge gas pressure is maintained at a normal pressure lower than the set pressure P at which the high pressure control valve 16 starts to open, and the high pressure control Valve 16 is closed.
斯かる運転状態から室内ユニットBが1台のみ作動する
状態になると、凝縮圧力が上昇し、その結果吐出ガス圧
力は前記高圧制御弁16の設定圧力Pより増加するので
あり、そのため、高圧制御弁16が開いて、吐出ガス圧
力の増加分に見合う量のホットガスが暖房用膨張弁4の
入口側の高圧液管9に流入する。When the state changes from such an operating state to a state in which only one indoor unit B operates, the condensing pressure increases, and as a result, the discharge gas pressure increases from the set pressure P of the high pressure control valve 16. 16 opens, and an amount of hot gas corresponding to the increase in discharge gas pressure flows into the high-pressure liquid pipe 9 on the inlet side of the heating expansion valve 4.
しかしして、斯く流入したホットガスが暖房用膨張弁4
に流入されるため、前記ガス冷媒により前記膨張弁4の
機能が阻害されて、該膨張弁4を通る液冷媒が減少し、
その結果冷媒循環量が減少することとなるのであり、膨
張弁4から流出する冷媒は、液量にくらべてガス量が多
大となった乾き度の高い状態となって、室外熱交換器3
に流入るのである。However, the hot gas that has flowed into the heating expansion valve 4
, the gas refrigerant inhibits the function of the expansion valve 4, and the liquid refrigerant passing through the expansion valve 4 decreases;
As a result, the amount of refrigerant circulating will decrease, and the refrigerant flowing out from the expansion valve 4 will be in a highly dry state with a large amount of gas compared to the amount of liquid, and the refrigerant will flow out from the outdoor heat exchanger 3.
It flows into.
斯くのごとく室外熱交換器3を循環する冷媒量が少なく
なると共に循環冷媒の乾き度が高目のため、該室外熱交
換器3の蒸発能力が減少して、1台の室内熱交換器11
の凝縮能力とのバランスがとれた状態となり、吐出ガス
圧力は前記設定圧力P避退の安全な圧力状態に抑制され
るのである。As the amount of refrigerant circulating through the outdoor heat exchanger 3 decreases and the dryness of the circulating refrigerant is high, the evaporation capacity of the outdoor heat exchanger 3 decreases and one indoor heat exchanger 11
The condensing capacity of the discharge gas is in a balanced state, and the discharge gas pressure is suppressed to a safe pressure state where the set pressure P is evacuated.
しかも、前記ホットガスのバイパス時、該ホットガスは
、高圧液管9の中の液冷媒と一緒に入口管23から前記
ミキシングタンク20中に所定速度で流入し、この速度
エネルギーによって前記ミキシングタンク20にほぼ満
杯に充満している液冷媒と均一に混合し、気液混合状態
で出口管24を流通し、前記膨張弁4を通るので、該膨
張弁4において、聴覚に不快感を与える断続的な異音が
発生することはないのである。Moreover, when the hot gas is bypassed, the hot gas flows into the mixing tank 20 from the inlet pipe 23 at a predetermined speed together with the liquid refrigerant in the high-pressure liquid pipe 9, and this velocity energy causes the mixing tank 20 to flow into the mixing tank 20. The liquid refrigerant is uniformly mixed with the liquid refrigerant that is almost completely filled, and flows through the outlet pipe 24 in a gas-liquid mixed state and passes through the expansion valve 4. No abnormal noise is generated.
尚、以上ごとく1台の室内ユニットBのみ作動させる低
負荷運転時、室外熱交換器3には乾き度の大きな少量の
冷媒が循環するため、吸入ガスの圧力が低下して過熱度
が上昇することが生じても、前記リキッドインジェクシ
ョン回路31より液冷媒がアキュムレータ7側に供給さ
れるため、吸入ガス圧力ひいては過熱度は正常値に保持
できるのである。As described above, during low-load operation in which only one indoor unit B is operated, a small amount of refrigerant with a high degree of dryness circulates in the outdoor heat exchanger 3, so the pressure of the suction gas decreases and the degree of superheating increases. Even if this happens, the liquid refrigerant is supplied from the liquid injection circuit 31 to the accumulator 7 side, so that the suction gas pressure and thus the degree of superheat can be maintained at normal values.
又、以上の説明では、1台の室外ユニットAに5台の室
内ユニットBを接続し、かつ室内ユニットBの作動台数
に応じて圧縮機1の容量を2段階に制御すべく威したも
のについて説明したが、暖房運転の低負荷時に、凝縮圧
力、温度が異常に上昇することが生ずる、各種のヒート
ポンプ式冷暖房装置に適用できるのである。Furthermore, in the above explanation, five indoor units B are connected to one outdoor unit A, and the capacity of the compressor 1 is controlled in two stages according to the number of operating indoor units B. As described above, the present invention can be applied to various heat pump air-conditioning devices in which the condensing pressure and temperature abnormally increase during low-load heating operation.
以上の如く本考案は、圧縮機の吐出口と四路切換弁とを
結ぶ吐出ガス管と、暖房用膨張弁の入口側と受液器とを
結ぶ高圧液管との間にホットガスバイパス管を設け、こ
のバイパス管に暖房運転時、高圧圧力が設定値以上にな
ることにより開動作する高圧制御弁を介装すべく威した
のであるから、暖房運転の低負荷時、前記バイパス管を
介してバイパスするホットガスにより前記膨張弁は正常
な冷媒量調節機能を発揮することができないので、たと
え最大開度に開いたとしても、前記膨張弁を通る液冷媒
は少なくなり、このため、僅かの吐出ガスが暖房用膨張
弁に流入するだけで、暖房用膨張弁を流通する冷媒量を
減少させられ、この減少により、室外熱交換器の蒸発圧
力が低下して、前記室内熱交換器の凝縮圧力を低下させ
られるのである。As described above, the present invention provides a hot gas bypass pipe between the discharge gas pipe that connects the discharge port of the compressor and the four-way switching valve, and the high-pressure liquid pipe that connects the inlet side of the heating expansion valve and the liquid receiver. This bypass pipe was equipped with a high-pressure control valve that opened when the high pressure exceeded a set value during heating operation. The expansion valve cannot perform its normal refrigerant amount adjustment function due to the hot gas bypassing the expansion valve. Just by the discharge gas flowing into the heating expansion valve, the amount of refrigerant flowing through the heating expansion valve is reduced, and due to this reduction, the evaporation pressure in the outdoor heat exchanger decreases, causing condensation in the indoor heat exchanger. The pressure can be lowered.
従って、蒸発能力と凝縮能力とをバランスさせられるの
であり、また前記高圧制御弁は容量が小さくて外形寸法
が小さく安価なものを使用することが可能となったので
ある。Therefore, it is possible to balance the evaporation capacity and the condensation capacity, and it has become possible to use a high-pressure control valve with a small capacity, small external size, and low cost.
しかも、前記バイパス管を介してバイパスするホットガ
スは、前記バイパス管の高圧液管への接続位置と、前記
暖房用膨張弁の入口側との間の高圧液管に介装したミキ
シングタンクで、高圧液冷媒と混合し、気液混合状態で
前記膨張弁に入るので、該膨張弁において断続的な異音
が生ずることはないし、また、冷媒の流れに脈動があっ
ても吸収できるのである。Moreover, the hot gas bypassed through the bypass pipe is fed to a mixing tank interposed in the high-pressure liquid pipe between the connection position of the bypass pipe to the high-pressure liquid pipe and the inlet side of the heating expansion valve. Since it is mixed with the high-pressure liquid refrigerant and enters the expansion valve in a gas-liquid mixed state, intermittent abnormal noise does not occur in the expansion valve, and even if there is pulsation in the flow of the refrigerant, it can be absorbed.
第1図は本考案の実施例を示す冷媒配管系統図、第2図
は、ミキシングタンクの断面図、第3図及び第4図は、
ミキシングタンクの使用例を示す説明図である。
1・・・・・・圧縮機、2・・・・・・四路切換弁、3
・・・・・・室外熱交換器、4・・・・・・暖房用膨張
弁、6・・・・・・受液器、8a・・・・・・吐出ガス
管、9・・・・・・高圧液管、11・・・・・・室内熱
交換器、12・・・・・・冷房用膨張弁、15・・・・
・・ホットガスバイパス管、16・・・・・・高圧制御
弁、20・・・・・・ミキシングタンク。Fig. 1 is a refrigerant piping system diagram showing an embodiment of the present invention, Fig. 2 is a sectional view of a mixing tank, and Figs. 3 and 4 are:
It is an explanatory view showing an example of use of a mixing tank. 1... Compressor, 2... Four-way switching valve, 3
...Outdoor heat exchanger, 4...Heating expansion valve, 6...Liquid receiver, 8a...Discharge gas pipe, 9... ... High pressure liquid pipe, 11 ... Indoor heat exchanger, 12 ... Air conditioning expansion valve, 15 ...
...Hot gas bypass pipe, 16...High pressure control valve, 20...Mixing tank.
Claims (1)
縮器となる室内熱交換器、冷房時凝縮器となり暖房時蒸
発器となる室外熱交換器3、受液器6、冷房用膨張弁1
2、暖房用膨張弁4を備えたヒートポンプ式冷暖房装置
において、前記圧縮機1の吐出と四路切換弁2とを結ぶ
吐出ガス管8aと、前記暖房用膨張弁4の入口側と受液
器6とを結ぶ高圧液管の間にホットガスバイパス管15
を設け、このバイパス管15に暖房運転時高圧圧力が設
定値以上になることにより開動作する高圧制御弁16を
介装すると共に、前記バイパス管15の前記高圧液管9
゛への接続位置と、前記暖房用膨張弁4の入口側との間
の高圧液管9に、ミキシングタンク20を゛介装したこ
とを特徴とするヒートポンプ式冷暖房装置。Compressor 1, four-way switching valve 2, indoor heat exchanger that becomes an evaporator during cooling and a condenser during heating, outdoor heat exchanger 3 that becomes a condenser during cooling and an evaporator during heating, liquid receiver 6, for cooling. expansion valve 1
2. In a heat pump type air-conditioning device equipped with a heating expansion valve 4, a discharge gas pipe 8a connecting the discharge of the compressor 1 and the four-way switching valve 2, and a liquid receiver and the inlet side of the heating expansion valve 4. A hot gas bypass pipe 15 is connected between the high pressure liquid pipe connecting the
A high-pressure control valve 16 is provided in the bypass pipe 15, which opens when the high pressure exceeds a set value during heating operation, and the high-pressure liquid pipe 9 of the bypass pipe 15
A heat pump type air-conditioning and heating system characterized in that a mixing tank 20 is interposed in a high-pressure liquid pipe 9 between a connection position to a heating expansion valve 4 and an inlet side of the heating expansion valve 4.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP9346780U JPS6028935Y2 (en) | 1980-07-01 | 1980-07-01 | Heat pump air conditioning system |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP9346780U JPS6028935Y2 (en) | 1980-07-01 | 1980-07-01 | Heat pump air conditioning system |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS5716768U JPS5716768U (en) | 1982-01-28 |
JPS6028935Y2 true JPS6028935Y2 (en) | 1985-09-02 |
Family
ID=29455413
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP9346780U Expired JPS6028935Y2 (en) | 1980-07-01 | 1980-07-01 | Heat pump air conditioning system |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS6028935Y2 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4989511B2 (en) * | 2008-02-22 | 2012-08-01 | 三菱電機株式会社 | Air conditioner |
-
1980
- 1980-07-01 JP JP9346780U patent/JPS6028935Y2/en not_active Expired
Also Published As
Publication number | Publication date |
---|---|
JPS5716768U (en) | 1982-01-28 |
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