JPH086207Y2 - Direct air conditioning heat pump device - Google Patents
Direct air conditioning heat pump deviceInfo
- Publication number
- JPH086207Y2 JPH086207Y2 JP9099090U JP9099090U JPH086207Y2 JP H086207 Y2 JPH086207 Y2 JP H086207Y2 JP 9099090 U JP9099090 U JP 9099090U JP 9099090 U JP9099090 U JP 9099090U JP H086207 Y2 JPH086207 Y2 JP H086207Y2
- Authority
- JP
- Japan
- Prior art keywords
- gas
- refrigerant
- air
- liquid
- pressure
- 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 - Lifetime
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- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Other Air-Conditioning Systems (AREA)
Description
【考案の詳細な説明】 （産業上の利用分野） 本考案は、大型ビルディングなどの空調システムに適
用可能な直接空調式ヒートポンプ装置に係り、冷房運転
時における冷房効率を向上させる構造に関する。DETAILED DESCRIPTION OF THE INVENTION (Industrial field of application) The present invention relates to a direct air conditioning heat pump device applicable to an air conditioning system of a large building or the like, and to a structure for improving cooling efficiency during a cooling operation.
（従来の技術） 従来の直接空調式ヒートポンプ装置としては、例えば
特開昭62−225833号公報に記載されている直接空調式ヒ
ートポンプ装置が知られている。(Prior Art) As a conventional direct air-conditioning heat pump device, for example, a direct air-conditioning heat pump device described in JP-A-62-225833 is known.
この直接空調式ヒートポンプ装置は、第３図に示すよ
うに、建物の最底所に圧縮機31とアキュムレータ32と受
液器33と膨張弁34とを含む管系を設け、建物の最高所に
空気熱交換器35と気液分離器36を含む管系を設け、地上
各階にそれぞれ空調機37a,37b,37cを設けてあり、前記
圧縮機31と空気熱交換器35とをガス切換え弁38aを介し
て高温ガス供給管39で接続し、さらに前記高温ガス供給
管39より分岐し、開閉弁40a,40b,40cを介して各空調機3
7a,37b,37cに接続してある。As shown in FIG. 3, this direct air-conditioning heat pump device is provided with a pipe system including a compressor 31, an accumulator 32, a liquid receiver 33, and an expansion valve 34 at the bottom of the building, and is installed at the top of the building. A pipe system including an air heat exchanger 35 and a gas-liquid separator 36 is provided, and air conditioners 37a, 37b, 37c are provided on each floor above the ground, and the compressor 31 and the air heat exchanger 35 are connected to a gas switching valve 38a. Via the high temperature gas supply pipe 39, further branched from the high temperature gas supply pipe 39, each air conditioner 3 via the on-off valves 40a, 40b, 40c.
It is connected to 7a, 37b, 37c.
また、前記受液器33と気液分離器36とを前記膨張弁34
を介装した気液二相流管41で接続し、前記受液器33と空
気熱交換器35とを液切換え弁42を介装した高温液戻し管
43で接続し、さらに高温液戻し管43から分岐し開閉弁44
a,44b,44cを介して各空調機37a,37b,37cに接続し、前記
気液分離器36の液取出口36aと各空調機37a,37b,37cとを
低温液供給管45を通じて開閉弁46a,46b,46cおよび流量
調整弁47a,47b,47cを介して接続し、前記気液分離器36
のガス取出口36bと前記圧縮機31の吸入側をアキュムレ
ータ32を介して低温ガス戻し管48で接続し、さらに低温
ガス戻し管48が分岐し、開閉弁49a,49b,49cを介して各
空調機37a,37b,37cに接続してある。Further, the liquid receiver 33 and the gas-liquid separator 36 are connected to the expansion valve 34
High-temperature liquid return pipe in which the liquid receiver 33 and the air heat exchanger 35 are connected by a gas-liquid two-phase flow pipe 41
Connected with 43, and further branched from the high temperature liquid return pipe 43 and opened / closed valve 44
Connected to each air conditioner 37a, 37b, 37c via a, 44b, 44c, the liquid outlet 36a of the gas-liquid separator 36 and each air conditioner 37a, 37b, 37c open / close valve through the low temperature liquid supply pipe 45 46a, 46b, 46c and flow rate adjusting valves 47a, 47b, 47c, and the gas-liquid separator 36.
The gas outlet 36b of the compressor 31 and the suction side of the compressor 31 are connected by the low temperature gas return pipe 48 via the accumulator 32, and the low temperature gas return pipe 48 is branched, and each air conditioner is operated via the on-off valves 49a, 49b, 49c. Connected to machines 37a, 37b, 37c.
また、前記気液分離器36のガス戻し口36cと前記空気
熱交換器35はガス切換え弁38bを介してガス戻し管50で
接続し、前記気液分離器36の液取出口36dと前記空調熱
交換器35は液切換え弁42bを介して液供給管51で接続し
て構成されている。The gas return port 36c of the gas-liquid separator 36 and the air heat exchanger 35 are connected by a gas return pipe 50 via a gas switching valve 38b, and the liquid outlet 36d of the gas-liquid separator 36 and the air conditioner are connected. The heat exchanger 35 is configured to be connected by a liquid supply pipe 51 via a liquid switching valve 42b.
この直接空調式ヒートポンプ装置により冷房を行う場
合、圧縮機31により圧縮された高温高圧の冷媒ガスが、
高温ガス供給管39を通って空気熱交換器35に流入する。
この空気熱交換器35において冷媒ガスが凝縮され、高温
液戻し管43を通って受液器33に流入する。さらに受液器
33の冷媒液は膨張弁34により減圧され、低温低圧の気液
二相流体となり気液二相流管41を通って気液分離器36に
流入する。この時の気液分離器36の液面の高さは膨張弁
34の開度により調節される。そして、この気液分離器36
内の冷媒液は低温液供給管45を通って各空調機37a,37b,
37cに供給される。この各空調機37a,37b,37cにおいて冷
媒液は蒸発し、室内空気を冷却する。そして、各空調機
37a,37b,37cで気化された冷媒ガスは、前記気液分離器3
6で分離された冷媒ガスとともに低圧ガス戻し管48を通
って圧縮機31の吸入側に戻る。When performing cooling with this direct air conditioning heat pump device, the high-temperature high-pressure refrigerant gas compressed by the compressor 31 is
It flows into the air heat exchanger 35 through the hot gas supply pipe 39.
The refrigerant gas is condensed in the air heat exchanger 35 and flows into the liquid receiver 33 through the high temperature liquid return pipe 43. Further receiver
The refrigerant liquid 33 is decompressed by the expansion valve 34, becomes a low temperature low pressure gas-liquid two-phase fluid, and flows into the gas-liquid separator 36 through the gas-liquid two-phase flow pipe 41. At this time, the height of the liquid surface of the gas-liquid separator 36 is the expansion valve.
It is adjusted by the opening of 34. And this gas-liquid separator 36
The refrigerant liquid inside passes through the low temperature liquid supply pipe 45 and is supplied to each air conditioner 37a, 37b,
Supplied to 37c. In each of the air conditioners 37a, 37b, 37c, the refrigerant liquid evaporates and cools the indoor air. And each air conditioner
Refrigerant gas vaporized in 37a, 37b, 37c, the gas-liquid separator 3
It returns to the suction side of the compressor 31 through the low pressure gas return pipe 48 together with the refrigerant gas separated in 6.
このようにして冷房運転は行われる。 In this way, the cooling operation is performed.
（考案が解決しようとする課題） 一般に、大型ビル内部に立体的に分散して空調機が設
置されている場合、各空調機の設置状態が異るととも
に、各空調機の使用条件も異っている。(Problems to be solved by the invention) Generally, when air conditioners are three-dimensionally distributed inside a large building, the installation condition of each air conditioner differs and the usage conditions of each air conditioner also differ. ing.
そこで、従来の上記の第３図に示す直接空調式ヒート
ポンプ装置を大型ビルの空調システムとして適用する場
合、最上部に設置されている気液分離器36には冷暖房切
換のための開閉弁38a,38b,42a,42bが設けられているだ
けなので、低温の冷媒液は、前記気液分離器36より低温
液供給管45を介して各空調機37a,37b,37cに重力ヘッド
により供給されるので、各空調機37a,37b,37cの冷却能
力の増減、運転または停止による液流量および圧力の変
動の影響が低温液供給管45を通じて他の空調機37a,37b,
37cの運転に影響するという問題がある。Therefore, when the conventional direct air-conditioning heat pump device shown in FIG. 3 is applied as an air conditioning system for a large building, the gas-liquid separator 36 installed at the top has an opening / closing valve 38a for switching between heating and cooling, Since only 38b, 42a, 42b are provided, the low-temperature refrigerant liquid is supplied from the gas-liquid separator 36 to the respective air conditioners 37a, 37b, 37c via the low-temperature liquid supply pipe 45 by the gravity head. The increase / decrease in the cooling capacity of each air conditioner 37a, 37b, 37c, the influence of the fluctuation of the liquid flow rate and the pressure due to the operation or stoppage of the other air conditioners 37a, 37b,
There is a problem that affects the operation of 37c.
また、気液分離器36内部の液面と空調機37a,37b,37c
との間に十分な落差がないと、冷媒液が低温液供給管45
内を流れにくいという問題もある。In addition, the liquid level inside the gas-liquid separator 36 and the air conditioners 37a, 37b, 37c
If there is not enough head between the refrigerant liquid and the low temperature liquid supply pipe 45
There is also the problem that it is difficult to flow inside.
また、空調機37a,37b,37cの作動中に生じる圧力変動
が低温液供給管45内にフラッシュガスを発生させること
があり、このフラッシュガスのベーパーロックにより冷
媒液が流れにくくなり、このため空調機37a,37b,37cに
よっては冷房効率が非常に悪いという問題もある。Further, pressure fluctuations that occur during the operation of the air conditioners 37a, 37b, 37c may generate flash gas in the low temperature liquid supply pipe 45, and the vapor lock of this flash gas makes it difficult for the refrigerant liquid to flow, so that air conditioning is performed. There is also a problem that the cooling efficiency is very poor depending on the machines 37a, 37b, 37c.
本考案はこのような点に鑑み成されたもので、冷房の
ヒートポンプサイクルにおいて、冷媒液を気液分離器か
ら各空調機に常時十分に供給し、これにより各空調機の
冷媒液入口部に設けられている流量調整弁に達する冷媒
の供給圧力を一定に保ち、多数の空調機が設置された大
型ビルの空調システムに適用可能な直接空調式ヒートポ
ンプ装置を提供することを目的とする。The present invention has been made in view of such a point, and in the heat pump cycle of cooling, the refrigerant liquid is always sufficiently supplied from the gas-liquid separator to each air conditioner, so that the refrigerant liquid inlet portion of each air conditioner is supplied. An object of the present invention is to provide a direct air-conditioning heat pump device that can be applied to an air conditioning system of a large building in which a large number of air conditioners are installed while keeping the supply pressure of the refrigerant reaching a flow rate adjusting valve provided constant.
（課題を解決するための手段） 本考案の直接空調式ヒートポンプ装置は、冷媒液入口
部に流量調整弁を設けている複数の空調機を立体的に分
散させて設置し、最高所位置にある空調機より高所に気
液分離器および空気熱交換器を設け、最底所位置にある
空調機より底所に受液器、圧縮機および膨張弁を設け、
順に前記圧縮機、前記空気熱交換器、前記受液器、前記
膨張弁、前記気液分離器および前記空調機からなる冷房
のヒートポンプサイクルを形成し、前記各空調機にフロ
ン系冷媒を直接通じて冷暖房を行う直接空調式ヒートポ
ンプ装置において、前記気液分離器に、前記各空調機の
冷媒ガス出口部とともに圧縮機の吸入口に接続される冷
媒ガス出口部は、この気液分離器内部の圧力を一定に制
御し、かつ、この気液分離器内部の圧力を前記各空調機
の冷媒ガス出口部の冷媒圧力よりも高く調節する圧力調
整手段を設けたものである。(Means for Solving the Problem) The direct air-conditioning type heat pump device of the present invention has a plurality of air conditioners having a flow rate adjusting valve provided at the refrigerant liquid inlet, which are three-dimensionally distributed and installed at the highest position. A gas-liquid separator and an air heat exchanger are installed above the air conditioner, and a receiver, a compressor and an expansion valve are installed below the air conditioner at the bottom position.
A cooling heat pump cycle comprising the compressor, the air heat exchanger, the liquid receiver, the expansion valve, the gas-liquid separator, and the air conditioner is formed in order, and a CFC-based refrigerant is directly passed to each air conditioner. In a direct air-conditioning heat pump device that performs cooling and heating by means of the gas-liquid separator, the refrigerant gas outlet part connected to the suction port of the compressor together with the refrigerant gas outlet part of each air conditioner is A pressure adjusting means is provided for controlling the pressure to be constant and for adjusting the pressure inside the gas-liquid separator higher than the refrigerant pressure at the refrigerant gas outlet of each of the air conditioners.
（作用） 本考案の直接空調式ヒートポンプ装置は、気液分離器
を最高所位置に設置されている空調機よりも高所に設置
し、この気液分離器の圧縮機の吸入口に接続する冷媒ガ
ス出口部に圧力調整手段を設けているので、冷房運転時
には、この冷媒ガス出口部に連通する低温ガス戻し管内
の冷媒圧力より前記気液分離器内の冷媒圧力が高くなる
ように調整され、この気液分離器内の冷媒圧力を一定に
制御する。従って、この気液分離器より低温液供給管を
介して各空調機に供給される冷媒液は、重力ヘッドと前
記圧力調整手段により生じた調整圧力差分とによってこ
の低温液供給管内を各空調機に向けて流れるので、各空
調機には気液分離器との落差が不十分でも室内の冷却に
必要な冷媒液が常時十分に供給される。また、圧力調整
手段の作用により、各必要な冷媒液が常時十分に供給さ
れるので、各空調機の冷媒液入口部に設けられている流
量調整弁に達する冷媒の供給圧力は、空調機の運転条件
の変化により、圧縮機の吸入圧力が変動しても、一定に
調整され、低温液供給管内で冷媒液よりフラッシュガス
が発生しにくくなり、ベーパーロックにより冷媒液の流
入が阻止されることも減少する。従って、各空調機にお
ける冷房効率は改善されて向上する。(Operation) In the direct air-conditioning type heat pump device of the present invention, the gas-liquid separator is installed at a higher place than the air conditioner installed at the highest position, and is connected to the suction port of the compressor of this gas-liquid separator. Since the pressure adjusting means is provided at the refrigerant gas outlet, during cooling operation, the refrigerant pressure in the gas-liquid separator is adjusted to be higher than the refrigerant pressure in the low temperature gas return pipe communicating with the refrigerant gas outlet. , The pressure of the refrigerant in the gas-liquid separator is controlled to be constant. Therefore, the refrigerant liquid supplied from the gas-liquid separator to each air conditioner through the low temperature liquid supply pipe moves through the low temperature liquid supply pipe into each air conditioner due to the adjustment pressure difference generated by the gravity head and the pressure adjusting means. Since the air flows toward each of the air conditioners, the refrigerant liquid necessary for cooling the room is always sufficiently supplied to each air conditioner even if the head of the air-liquid separator is insufficient. Further, since each necessary refrigerant liquid is always sufficiently supplied by the action of the pressure adjusting means, the supply pressure of the refrigerant reaching the flow rate adjusting valve provided at the refrigerant liquid inlet of each air conditioner is Even if the suction pressure of the compressor fluctuates due to changes in operating conditions, it is adjusted to a constant level, and flash gas is less likely to be generated than the refrigerant liquid in the low-temperature liquid supply pipe, and the vapor lock prevents the refrigerant liquid from flowing in. Also decreases. Therefore, the cooling efficiency in each air conditioner is improved and improved.
（実施例） 本考案の直接空調式ヒートポンプ装置の一実施例を第
１図および第２図に基づいて説明する。(Embodiment) An embodiment of a direct air-conditioning type heat pump device of the present invention will be described with reference to FIGS. 1 and 2.
第１図にこの直接空調式ヒートポンプ装置を構成する
冷房回路の構成図を示す。FIG. 1 shows a block diagram of a cooling circuit which constitutes this direct air conditioning heat pump device.
冷房を必要とする建物の各所に空調機1a,1b,1cが設置
され、最高所に設置されている空調機1cよりも高所に、
気液分離器２、圧力調整手段３、空気熱交換器４が設け
られ、最底所に設置されている空調機1aよりも底所に、
圧縮機５、膨張弁６、受液器７が設けられている。Air conditioners 1a, 1b, 1c are installed at various places in the building that require cooling, and at a higher place than the air conditioner 1c installed at the highest place,
The gas-liquid separator 2, the pressure adjusting means 3, and the air heat exchanger 4 are provided, and at the bottom of the air conditioner 1a installed at the bottom,
A compressor 5, an expansion valve 6 and a liquid receiver 7 are provided.
前記圧縮機５は駆動装置８により駆動され、この圧縮
機５の吐出口には高温ガス供給管９が接続され、この高
温ガス供給管９はガス切換え弁10を介して空気熱交換器
４に接続している。さらに、この空気熱交換器４は液切
換え弁11を介装した高温液戻し管12を介して前記受液器
７に接続している。The compressor 5 is driven by a driving device 8, and a hot gas supply pipe 9 is connected to a discharge port of the compressor 5, and the hot gas supply pipe 9 is connected to an air heat exchanger 4 via a gas switching valve 10. Connected. Further, the air heat exchanger 4 is connected to the liquid receiver 7 via a high temperature liquid return pipe 12 having a liquid switching valve 11 interposed therein.
この受液器７は膨張弁６を介装した気液二相流管13を
介して前記気液分離器２に接続している。The liquid receiver 7 is connected to the gas-liquid separator 2 via a gas-liquid two-phase flow pipe 13 having an expansion valve 6 interposed therein.
この気液分離器２の液流出口は低温液供給管14が接続
し、この低温液供給管14より分岐し、順に開閉弁15a,15
b,15c、流量調整弁16a,16b,16cを介して各空調機1a,1b,
1cの冷媒液入口部に接続している。A low-temperature liquid supply pipe 14 is connected to the liquid outlet of the gas-liquid separator 2 and branched from the low-temperature liquid supply pipe 14 to open / close valves 15a, 15 in order.
b, 15c, the flow control valves 16a, 16b, 16c through the air conditioners 1a, 1b,
It is connected to the refrigerant liquid inlet of 1c.
また、前記気液分離器２の冷媒ガス出口部は、圧力調
整手段３を介して低圧ガス戻し管17が接続し、この低圧
ガス戻し管17より分岐し、開閉弁18a,18b,18cを介して
各空調機1a,1b,1cの冷媒ガス出口部に接続している。さ
らに、この低圧ガス戻し管17は前記圧縮機５の吸入口に
接続している。The low pressure gas return pipe 17 is connected to the refrigerant gas outlet of the gas-liquid separator 2 via the pressure adjusting means 3, and is branched from the low pressure gas return pipe 17 via the on-off valves 18a, 18b, 18c. And is connected to the refrigerant gas outlet of each air conditioner 1a, 1b, 1c. Further, the low pressure gas return pipe 17 is connected to the suction port of the compressor 5.
前記圧力調整手段３は、前記気液分離器２内部の冷媒
圧力を一定に制御するようになっており、さらに、この
気液分離器２内部の冷媒圧力を低圧ガス戻し管17内の圧
力よりも高く調整するようになっている。The pressure adjusting means 3 is adapted to control the refrigerant pressure inside the gas-liquid separator 2 to be constant, and further, the refrigerant pressure inside the gas-liquid separator 2 is set to be lower than the pressure inside the low-pressure gas return pipe 17. Is also adjusted to a higher value.
このように上記構成によって直接空調式ヒートポンプ
装置の冷房のヒートポンプサイクルが構成される。As described above, the above-described configuration constitutes a cooling heat pump cycle of the direct air conditioning type heat pump device.
次に、上記実施例の作用について説明する。 Next, the operation of the above embodiment will be described.
この直接空調式ヒートポンプ装置の冷房運転を行う
際、圧縮機５にて圧縮された高温高圧の冷媒ガスは高温
ガス供給管９を通って空気熱交換器４に流入される。こ
の空気熱交換器４において冷媒ガスは凝縮され、液切換
え弁11、高温液戻し管12を通って受液器７に流入する。When performing the cooling operation of the direct air-conditioning heat pump device, the high-temperature and high-pressure refrigerant gas compressed by the compressor 5 flows into the air heat exchanger 4 through the high-temperature gas supply pipe 9. The refrigerant gas is condensed in the air heat exchanger 4 and flows into the liquid receiver 7 through the liquid switching valve 11 and the high temperature liquid return pipe 12.
この受液器７内の冷媒液は膨張弁６により減圧されて
低温低圧の気液二相流体となり、気液二相流管13を通っ
て気液分離器２に流入する。The refrigerant liquid in the liquid receiver 7 is decompressed by the expansion valve 6 to become a low-temperature low-pressure gas-liquid two-phase fluid, and flows into the gas-liquid separator 2 through the gas-liquid two-phase flow pipe 13.
この気液分離器２内の冷媒圧力は前記圧力調整手段３
により常に一定に保たれており、また、この圧力調整手
段３により、気液分離器２内の冷媒圧力は各空調機1a,1
b,1cの冷媒ガス出口部の冷媒圧力よりも高く調節されて
いるので、この気液分離器２内で分離された冷媒液は、
重力ヘッドと前記圧力調整手段３の前後に生じた圧力差
とにより、低温液供給管14を通って各空調機1a,1b,1cに
送られる。この時、各空調機1a,1b,1cへの冷媒供給量は
それぞれの空調機1a,1b,1cに取付けられている流量調整
弁16a,16b,16cにより制御される。The refrigerant pressure in the gas-liquid separator 2 is the pressure adjusting means 3 described above.
Is always kept constant by the pressure adjusting means 3, and the pressure of the refrigerant in the gas-liquid separator 2 is adjusted by the pressure adjusting means 3.
Since it is adjusted to be higher than the refrigerant pressure at the refrigerant gas outlets of b and 1c, the refrigerant liquid separated in the gas-liquid separator 2 is
By the gravity head and the pressure difference generated before and after the pressure adjusting means 3, the air is sent to each air conditioner 1a, 1b, 1c through the low temperature liquid supply pipe 14. At this time, the amount of refrigerant supplied to each air conditioner 1a, 1b, 1c is controlled by the flow rate adjusting valves 16a, 16b, 16c attached to each air conditioner 1a, 1b, 1c.
次に、各空調機1a,1b,1cにおいて、冷媒液は各空調機
1a,1b,1c内部を循環している空気と熱交換を行いなが
ら、冷媒ガス出口部近傍までに気化されて、室内空気を
冷却する。この各空調機1a,1b,1cから流出された冷媒ガ
スは、前記気液分離器２で分離された冷媒ガスとともに
低圧ガス戻し管17を圧縮機５の吸入口に戻り、ヒートポ
ンプサイクルが構成されて室内の冷房が行われる。Next, in each air conditioner 1a, 1b, 1c, the refrigerant liquid is
While exchanging heat with the air circulating inside 1a, 1b, 1c, it is vaporized to the vicinity of the refrigerant gas outlet to cool the indoor air. The refrigerant gas flowing out from each of the air conditioners 1a, 1b, 1c returns to the suction port of the compressor 5 through the low pressure gas return pipe 17 together with the refrigerant gas separated by the gas-liquid separator 2 to form a heat pump cycle. The room is cooled.
次に、冷媒にフレオンR22を使用した場合の冷房運転
の一例を第２図に示すモリエル線図に基づいて説明す
る。Next, an example of the cooling operation when Freon R22 is used as the refrigerant will be described based on the Mollier diagram shown in FIG.
まず、Ａ点で圧縮機５に吸入された低温低圧の冷媒ガ
スは圧力16.63kg/cm2ｇ、温度75℃の高温高圧のガスと
なりＢ点で吐出され、空気熱交換器４で凝縮して凝縮液
化点であるＣ点を通り、過冷却されてＤ点で40℃の液体
となり受液器７に溜まる。First, the low-temperature low-pressure refrigerant gas sucked into the compressor 5 at the point A becomes a high-temperature high-pressure gas having a pressure of 16.63 kg / cm 2 g and a temperature of 75 ° C., and is discharged at the point B and condensed in the air heat exchanger 4. After passing through the condensing and liquefying point C, it is supercooled to become a liquid of 40 ° C. at the point D and accumulates in the liquid receiver 7.
この受液器７内の冷媒液は、膨張弁６で断熱膨張して
気液二相流体となりＥ点で気液分離器２に入る。この気
液分離器２においてガスは液体と分離され、このガスは
Ｆ点となり圧力調整手段３により圧力を約1kg/cm2下げ
られてＡ点で圧縮機５に吸入される。The refrigerant liquid in the liquid receiver 7 is adiabatically expanded by the expansion valve 6 to become a gas-liquid two-phase fluid and enters the gas-liquid separator 2 at point E. In the gas-liquid separator 2, the gas is separated from the liquid, and the gas becomes the point F, the pressure is lowered by about 1 kg / cm 2 by the pressure adjusting means 3, and is sucked into the compressor 5 at the point A.
一方、気液分離器２において分離された液体はＧ点と
なり、低温液供給管14を通って各空調機1a,1b,1cにそれ
ぞれ供給される。この気液分離器２に最近接する空調機
1cと気液分離器２との落差が例えば3mとするとＧ点より
圧力が0.36kg/cm2高くなったＨ点で空調機1cの流量調整
弁16cに入る。冷媒ガスの比重は無視できるので、Ｈ点
とＩ点との圧力差1.36kg/cm2だけ冷媒ガスの圧力は降下
してＩ点で空調機1c内の冷媒液は気化を開始する。この
冷媒液がＩ点よりＡ天まで圧力5.5kg/cm2ｇ、蒸発温度
８℃で気化して22℃の室内循環空気を16℃まで冷却す
る。そして、気化した冷媒ガスはＡ点より圧縮機５に吸
入されてヒートポンプサイクルを構成する。On the other hand, the liquid separated in the gas-liquid separator 2 becomes the point G and is supplied to each of the air conditioners 1a, 1b, 1c through the low temperature liquid supply pipe 14. The air conditioner closest to this gas-liquid separator 2
If the drop between the 1c and the gas-liquid separator 2 is, for example, 3 m, the pressure enters the flow rate adjusting valve 16c of the air conditioner 1c at the H point where the pressure is higher than the G point by 0.36 kg / cm 2 . Since the specific gravity of the refrigerant gas can be ignored, the pressure of the refrigerant gas drops by 1.36 kg / cm 2 of the pressure difference between the H point and the I point, and the refrigerant liquid in the air conditioner 1c starts vaporizing at the I point. This refrigerant liquid is vaporized at a pressure of 5.5 kg / cm 2 g from point I to A heaven at an evaporation temperature of 8 ° C to cool indoor circulating air at 22 ° C to 16 ° C. Then, the vaporized refrigerant gas is sucked into the compressor 5 from the point A to form a heat pump cycle.
上記の冷房のヒートポンプサイクルにおいては、各空
調機1a,1b,1cにおいて冷風が発生するときの冷媒蒸発温
度が一定になるように、すなわち、圧縮機５の冷媒吸入
圧力が一定になるように圧縮機５が制御されて運転して
いる。In the above heat pump cycle for cooling, compression is performed so that the refrigerant evaporation temperature when cold air is generated in each air conditioner 1a, 1b, 1c becomes constant, that is, the refrigerant suction pressure of the compressor 5 becomes constant. Machine 5 is operating under control.
しかし、空調機1a,1b,1cの運転台数や負荷状態が変化
すると、圧縮機５の制御にもかかわらず圧縮機５の吸入
圧力は変動し、前記気液分離器２内の冷媒圧力を変化さ
せることがある。However, when the number of operating air conditioners 1a, 1b, 1c and the load state change, the suction pressure of the compressor 5 fluctuates despite the control of the compressor 5 and the refrigerant pressure in the gas-liquid separator 2 changes. There is something to do.
従って、前記圧力調整手段３により気液分離器２内の
冷媒圧力を一定に制御することで、各空調機1a,1b,1cの
運転台数や負荷状態の変動による圧縮機５の吸入圧力の
変動の影響を受けずに、各空調機1a,1b,1cを運転するこ
とができる。Therefore, by controlling the refrigerant pressure in the gas-liquid separator 2 to be constant by the pressure adjusting means 3, the suction pressure of the compressor 5 varies depending on the number of operating air conditioners 1a, 1b, 1c and the load condition. The respective air conditioners 1a, 1b, 1c can be operated without being affected by.
また、前記気液分離器２内の冷媒圧力は常時一定であ
るから、この気液分離器２より低温液供給管14を通って
各空調機1a,1b,1cの冷媒液入口部に設けられている流量
調整弁16a,16b,16cへ供給される冷媒液の圧力は一定と
なるので、冷房効率は安定する。さらに、低温液供給管
14でのフラッシュガスの発生も防ぐことができる。Since the pressure of the refrigerant in the gas-liquid separator 2 is always constant, it is provided at the refrigerant liquid inlet of each air conditioner 1a, 1b, 1c through the low-temperature liquid supply pipe 14 from the gas-liquid separator 2. Since the pressure of the refrigerant liquid supplied to the flow rate adjusting valves 16a, 16b, 16c is constant, the cooling efficiency is stable. In addition, low temperature liquid supply pipe
The generation of flash gas at 14 can also be prevented.
また、各空調機1a,1b,1cへは、冷媒液は重力ヘッド
と、気液分離器２の冷媒圧力と各空調機1a,1b,1cの冷媒
ガス出口部の圧力との圧力差によって供給されるので、
各空調機1a,1b,1cに冷媒液は常に十分流入する。Further, the refrigerant liquid is supplied to each air conditioner 1a, 1b, 1c by the gravity head and the pressure difference between the refrigerant pressure of the gas-liquid separator 2 and the pressure of the refrigerant gas outlet of each air conditioner 1a, 1b, 1c. Because it is done
The refrigerant liquid always flows sufficiently into each air conditioner 1a, 1b, 1c.
また、冷媒液が重力ヘッドと前記圧力調整手段３によ
って生じた圧力差とによって各空調機1a,1b,1cに十分供
給され、冷媒液にフラッシュガスが発生することを防止
できるので、多数の空調機に冷媒液を供給可能となり、
多数の空調機を立体的に分散して設置できる。Further, since the refrigerant liquid is sufficiently supplied to each of the air conditioners 1a, 1b, 1c by the gravity head and the pressure difference generated by the pressure adjusting means 3, it is possible to prevent flash gas from being generated in the refrigerant liquid. It becomes possible to supply the refrigerant liquid to the machine,
Many air conditioners can be installed in three dimensions.
さらに、圧力調整手段３を、各空調機1a,1b,1cの冷媒
ガス出口部とともに低温ガス戻し管17を介して圧縮機５
の吸入口に接続される冷媒ガス出口部に設けることによ
り、各空調機1a,1b,1cに冷媒液を十分に供給できる構成
を簡略に実現できる。Further, the pressure adjusting means 3 is connected to the compressor 5 via the low temperature gas return pipe 17 together with the refrigerant gas outlets of the air conditioners 1a, 1b and 1c.
By providing it at the refrigerant gas outlet connected to the suction port, it is possible to simply realize a configuration capable of sufficiently supplying the refrigerant liquid to each of the air conditioners 1a, 1b, 1c.
従って、大型ビルの空調の冷房システムとして直接空
調式ヒートポンプ装置を適用することができるので、冷
媒と空気との直接熱交換による高効率化によるエネルギ
ーの節約、配管腐食のメインテナンスフリー化などの元
来直接空調式ヒートポンプ装置の有する効果が大型ビル
の空調システムにも期待できる。Therefore, a direct air-conditioning heat pump device can be applied as a cooling system for air conditioning of large buildings, so energy saving due to high efficiency by direct heat exchange between refrigerant and air, maintenance-free pipe corrosion, etc. The effect of the direct air-conditioning type heat pump device can be expected in the air conditioning system of a large building.
（考案の効果） 本考案の直接空調式ヒートポンプ装置によれば、気液
分離器は圧縮機の吸入口に接続する冷媒ガス出口部に圧
力調整手段を設け、冷房運転時には、気液分離器内の冷
媒圧力を一定に制御し、この気液分離器内の冷媒圧力
を、この冷媒ガス出口部に連通する各空調機の冷媒ガス
出口部の冷媒圧力よりも高く調整している。そこで、重
力ヘッドのみならず、圧力調整手段の前後に生じた圧力
差を用いて、各空調機の冷媒液入口部と冷媒ガス出口部
との間に十分な圧力差を生じさせ、冷却に要する冷媒液
を気液分離器から各空調機に常時十分に供給できる。そ
して、各空調機の運転台数や負荷状態の変動による圧縮
機の吸入圧力の変動があっても、影響を受けずに各空調
機に冷媒液を十分に供給できるため、各空調機の冷媒液
入口部に設けられている流量調整弁に流入する冷媒液の
供給圧力を一定にして、各空調機を効率良く運転するこ
とができる。また、各空調機に冷媒液を十分に供給でき
るため、気液分離器と各空調機とを接続する低温液供給
管内にフラッシュガスが発生しにくくなり、ベーパーロ
ックにより冷媒液の通過が阻止されることが減少するた
め、、多数の空調機に冷媒液を供給することができ、多
数の空調機を立体的に分散して設置できる。さらに、圧
力調整手段を、各空調機の冷媒ガス出口部とともに圧縮
機の吸入口に接続される冷媒ガス出口部に設けることに
より、簡略な構成で各空調機に冷媒液を十分に供給でき
る。このようにして、元来直接空調式ヒートポンプ装置
の有する効果、すなわち冷媒と空気との直接熱交換によ
る高効率化によるエネルギーの節約、配管腐食のメイン
テナンスフリー化などが、大型ビルの空調システムにも
期待できる。(Effect of the Invention) According to the direct air-conditioning heat pump device of the present invention, the gas-liquid separator is provided with the pressure adjusting means at the refrigerant gas outlet connected to the suction port of the compressor, and the inside of the gas-liquid separator is provided during the cooling operation. The refrigerant pressure is controlled to be constant, and the refrigerant pressure inside the gas-liquid separator is adjusted to be higher than the refrigerant pressure at the refrigerant gas outlet of each air conditioner communicating with the refrigerant gas outlet. Therefore, not only the gravity head but also the pressure difference generated before and after the pressure adjusting means is used to generate a sufficient pressure difference between the refrigerant liquid inlet portion and the refrigerant gas outlet portion of each air conditioner, which is required for cooling. The refrigerant liquid can always be sufficiently supplied from the gas-liquid separator to each air conditioner. Even if the suction pressure of the compressor fluctuates due to fluctuations in the number of operating air conditioners and load conditions, the refrigerant liquid can be sufficiently supplied to each air conditioner without being affected. It is possible to operate each air conditioner efficiently by keeping the supply pressure of the refrigerant liquid flowing into the flow rate adjusting valve provided at the inlet portion constant. In addition, since the refrigerant liquid can be sufficiently supplied to each air conditioner, flash gas is less likely to be generated in the low temperature liquid supply pipe connecting the gas-liquid separator and each air conditioner, and the vapor lock prevents passage of the refrigerant liquid. Therefore, the refrigerant liquid can be supplied to a large number of air conditioners, and a large number of air conditioners can be three-dimensionally dispersed and installed. Further, by providing the pressure adjusting means at the refrigerant gas outlet of each air conditioner together with the refrigerant gas outlet of the compressor, the refrigerant liquid can be sufficiently supplied to each air conditioner with a simple configuration. In this way, the effects of the direct air-conditioning heat pump device, that is, the energy savings due to the high efficiency of direct heat exchange between the refrigerant and the air, and the maintenance-free pipe corrosion, can be applied to the air conditioning system of large buildings. Can be expected.
第１図は本考案の直接空調式ヒートポンプ装置の一例を
示す冷房のヒートポンプサイクルの構成図、第２図は同
上冷媒としてフレオンR22を使用した場合の冷房のヒー
トポンプサイクルのモリエル線図、第３図は従来の直接
空調式ヒートポンプ装置の一例を示す構成図である。 1a,1b,1c……空調機、２……気液分離器、３……圧力調
整手段、４……空気熱交換器、５……圧縮機、６……膨
張弁、７……受液器、16a,16b,16c……流量調整弁。FIG. 1 is a configuration diagram of a cooling heat pump cycle showing an example of the direct air conditioning type heat pump device of the present invention, FIG. 2 is a Mollier diagram of a cooling heat pump cycle when Freon R22 is used as a refrigerant, FIG. FIG. 4 is a configuration diagram showing an example of a conventional direct air conditioning heat pump device. 1a, 1b, 1c ... Air conditioner, 2 ... Gas-liquid separator, 3 ... Pressure adjusting means, 4 ... Air heat exchanger, 5 ... Compressor, 6 ... Expansion valve, 7 ... Liquid receiving 16a, 16b, 16c ... Flow rate control valve.
───────────────────────────────────────────────────── フロントページの続き (71)出願人 999999999 レム熱エンジニアリング株式会社 千葉県匝瑳郡光町宮川5654番地 (72)考案者 甲斐崎 充典 神奈川県川崎市麻生区王禅寺450番地の80 (72)考案者 岩崎 保孝 兵庫県西宮市甲陽園日の出町２丁目62番地 (72)考案者 小川 正人 愛知県名古屋市緑区池上台２丁目144番地 (72)考案者 真田 勝 茨城県稲敷郡茎崎町高見原３丁目３番18号 (72)考案者 岡田 末吉 埼玉県川口市川口２丁目16番５号 (72)考案者 重清 秀雄 東京都立川市曙町３丁目41番14号 (72)考案者 原 健 千葉県匝瑳郡光町宮川5655番地 ─────────────────────────────────────────────────── ─── Continuation of the front page (71) Applicant 999999999 Rem Heat Engineering Co., Ltd. 5654 Miyagawa, Hikari-cho, Sora-gun, Chiba (72) Inventor Mitsunori Kaizaki 80 (72) devised at 450 Ozenji, Aso-ku, Kawasaki-shi, Kanagawa Author Yasutaka Iwasaki 2-62, Koyoen Hinode-cho, Nishinomiya-shi, Hyogo (72) Inventor Masato Ogawa 2-144, Ikegamidai, Midori-ku, Nagoya-shi, Aichi (72) Masaru Sanada 3 Takamihara, Kashizaki-cho, Inashiki-gun, Ibaraki Prefecture 3-18 (72) Inventor Sueyoshi Okada 2-16-5 Kawaguchi, Kawaguchi City, Saitama Prefecture (72) Hideo Shigekiyo 3-41-1414 Akebonocho, Tachikawa-shi, Tokyo (72) Ken Ken Hara, Chiba 5655 Miyagawa, Hikari-cho, Sosa-gun, Japan
Claims (1)
数の空調機を立体的に分散させて設置し、最高所位置に
ある空調機より高所に気液分離器および空気熱交換器を
設け、最底所位置にある空調機より底所に受液器、圧縮
機および膨張弁を設け、順に前記圧縮機、前記空気熱交
換器、前記受液器、前記膨張弁、前記気液分離器および
前記空調機からなる冷房のヒートポンプサイクルを形成
し、前記各空調機にフロン系冷媒を直接通じて冷暖房を
行う直接空調式ヒートポンプ装置において、 前記気液分離器は、前記各空調機の冷媒ガス出口部とと
もに圧縮機の吸入口に接続される冷媒ガス出口部は、こ
の気液分離器内部の圧力を一定に制御し、かつ、この気
液分離器内部の圧力を前記各空調機の冷媒ガス出口部の
冷媒圧力よりも高く調節する圧力調整手段を設けたこと
を特徴とする直接空調式ヒートポンプ装置。1. A plurality of air conditioners, each having a flow rate adjusting valve provided at a refrigerant liquid inlet, are three-dimensionally dispersed and installed, and a gas-liquid separator and an air heat exchanger are installed at a higher place than an air conditioner at a highest position. A receiver, a receiver, a compressor and an expansion valve are installed at the bottom of the air conditioner at the lowest position, and the compressor, the air heat exchanger, the receiver, the expansion valve and the air In a direct air-conditioning heat pump device that forms a cooling heat pump cycle consisting of a liquid separator and the air conditioner, and directly cools and heats a freon-based refrigerant to each of the air conditioners, wherein the gas-liquid separator is each of the air conditioners. The refrigerant gas outlet connected to the compressor suction port together with the refrigerant gas outlet controls the internal pressure of the gas-liquid separator to be constant, and controls the internal pressure of the gas-liquid separator to the air conditioner. Adjust to higher than the refrigerant pressure at the refrigerant gas outlet of A direct air-conditioning type heat pump device characterized in that a pressure adjusting means is provided.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9099090U JPH086207Y2 (en) | 1990-08-30 | 1990-08-30 | Direct air conditioning heat pump device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9099090U JPH086207Y2 (en) | 1990-08-30 | 1990-08-30 | Direct air conditioning heat pump device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0450365U JPH0450365U (en) | 1992-04-28 |
| JPH086207Y2 true JPH086207Y2 (en) | 1996-02-21 |
Family
ID=31826215
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP9099090U Expired - Lifetime JPH086207Y2 (en) | 1990-08-30 | 1990-08-30 | Direct air conditioning heat pump device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH086207Y2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008196843A (en) * | 2008-03-31 | 2008-08-28 | Daikin Ind Ltd | Refrigeration equipment |
-
1990
- 1990-08-30 JP JP9099090U patent/JPH086207Y2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0450365U (en) | 1992-04-28 |
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