JPH07301467A - Plural-stage heat pump apparatus - Google Patents
Plural-stage heat pump apparatusInfo
- Publication number
- JPH07301467A JPH07301467A JP6094092A JP9409294A JPH07301467A JP H07301467 A JPH07301467 A JP H07301467A JP 6094092 A JP6094092 A JP 6094092A JP 9409294 A JP9409294 A JP 9409294A JP H07301467 A JPH07301467 A JP H07301467A
- Authority
- JP
- Japan
- Prior art keywords
- pressure side
- refrigerant
- state
- wet vapor
- vapor state
- 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.)
- Pending
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/05—Compression system with heat exchange between particular parts of the system
- F25B2400/053—Compression system with heat exchange between particular parts of the system between the storage receiver and another part of the system
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/13—Economisers
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、中間冷却器の上部から
気相状態で取り出した冷媒を高圧側圧縮機・凝縮器・高
圧側膨張手段の順に通過させて、湿り蒸気状態で前記中
間冷却器に戻す高圧側循環系と、前記中間冷却器の下部
から液相状態で取り出した冷媒を低圧側膨張手段・蒸発
器・低圧側圧縮機の順に通過させて、過熱気相状態で前
記中間冷却器に戻す低圧側循環系とが備えられている複
段ヒートポンプ装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention allows a refrigerant taken out from an upper portion of an intercooler in a vapor phase state to pass through a high pressure side compressor, a condenser, and a high pressure side expansion means in this order to obtain the intermediate cooling in a wet vapor state. High pressure side circulation system to be returned to the reactor, and the refrigerant taken out from the lower part of the intercooler in the liquid phase state is passed through the low pressure side expansion means, the evaporator and the low pressure side compressor in this order, and the intermediate cooling is performed in the superheated gas phase state. And a low pressure side circulation system for returning to the reactor.
【０００２】[0002]
【従来の技術】この種の複段ヒートポンプ装置は、高圧
側膨張手段からの湿り蒸気状態の冷媒と、低圧側圧縮機
からの過熱気相状態の冷媒とを中間冷却器に戻して熱交
換させて、高圧側圧縮機に供給する冷媒の温度を下げる
ので、単一の冷媒循環系を備えている単段ヒートポンプ
装置に比べて、高圧側圧縮機から吐出される冷媒の温度
が下がり、高圧側圧縮機に使用されている潤滑油の劣化
を抑制できるとともに、圧縮機による圧縮効率の低下を
防止できるが、2. Description of the Related Art A multi-stage heat pump device of this type returns a refrigerant in a wet vapor state from a high pressure side expansion means and a refrigerant in a superheated gas phase state from a low pressure side compressor to an intermediate cooler for heat exchange. Since the temperature of the refrigerant supplied to the high-pressure side compressor is lowered, the temperature of the refrigerant discharged from the high-pressure side compressor is lower than that of the single-stage heat pump device equipped with a single refrigerant circulation system. While it is possible to suppress deterioration of the lubricating oil used in the compressor, it is possible to prevent the compression efficiency from decreasing due to the compressor.
【０００３】従来、図８に示すように、湿り蒸気状態の
冷媒と過熱気相状態の冷媒とを中間冷却器０１内で直接
熱交換させるにあたって、湿り蒸気状態の冷媒を中間冷
却器０１の内部気相域ＧＡに供給する高圧側供給路０２
と、過熱気相状態の冷媒を中間冷却器３の内部気相域Ｇ
Ａに供給する低圧側供給路０３との各々を中間冷却器０
１の器壁内面０４に対して略直交する方向に接続して、
それら供給路０２，０３の開口０５，０６を当該器壁内
面０４に形成し、湿り蒸気状態の冷媒と過熱気相状態の
冷媒との各々を、これらの開口０５，０６から中間冷却
器０１内に各別に流入させて、流入したこれらの冷媒ど
うしが自発的に当該中間冷却器０１内で混ざり合いなが
ら互いに接触することで直接熱交換させている。Conventionally, as shown in FIG. 8, when the refrigerant in the wet vapor state and the refrigerant in the superheated vapor phase state are directly heat-exchanged in the intercooler 01, the refrigerant in the wet vapor state is placed inside the intercooler 01. High-pressure side supply path 02 for supplying to the gas phase area GA
And the refrigerant in the superheated gas phase state, the internal gas phase region G of the intercooler 3
Each of the low-pressure side supply path 03 for supplying A to the intercooler 0
1 is connected in a direction substantially orthogonal to the inner wall surface 04 of the vessel wall,
The openings 05, 06 of the supply paths 02, 03 are formed on the inner surface 04 of the vessel wall, and the refrigerant in the wet vapor state and the refrigerant in the superheated vapor phase state are introduced into the intercooler 01 through the openings 05, 06. The respective refrigerants that have flowed into each other spontaneously spontaneously mix with each other in the intercooler 01 and come into direct contact with each other to directly perform heat exchange.
【０００４】尚、図中、０７は、熱交換した後の気相状
態の冷媒を高圧側圧縮機に導出する気相冷媒導出路、０
８は、熱交換した後の液相状態の冷媒を低圧側膨張手段
に導出する液相冷媒導出路である。In the figure, reference numeral 07 denotes a gas-phase refrigerant discharge path for discharging the gas-phase refrigerant after heat exchange to the high-pressure side compressor, and 0.
Reference numeral 8 denotes a liquid-phase refrigerant outlet passage for leading the refrigerant in a liquid state after heat exchange to the low pressure side expansion means.
【０００５】[0005]
【発明が解決しようとする課題】この為、湿り蒸気状態
の冷媒と過熱気相状態の冷媒との熱交換が不充分で、湿
り蒸気状態の冷媒のうちの液分が充分加熱されないで高
圧側圧縮機に吸い込まれ易く、高圧側圧縮機の運転エネ
ルギーがそのような液分を蒸発させる為に無駄に消費さ
れて、供給された冷媒を所定圧力まで圧縮するに要する
高圧側圧縮機の運転エネルギーが増大する欠点があり、
更には、高圧側圧縮機が液圧縮状態で運転された場合に
は、当該高圧側圧縮機を破損し易い欠点もある。Therefore, the heat exchange between the refrigerant in the wet vapor state and the refrigerant in the superheated vapor phase state is insufficient, and the liquid content of the refrigerant in the wet vapor state is not sufficiently heated, so that the high pressure side It is easy to be sucked into the compressor, and the operating energy of the high-pressure side compressor is wasted to evaporate such liquid, and the operating energy of the high-pressure side compressor required to compress the supplied refrigerant to a prescribed pressure. Has the drawback that
Further, when the high-pressure side compressor is operated in a liquid compression state, the high-pressure side compressor is likely to be damaged.
【０００６】又、湿り蒸気状態の冷媒と過熱気相状態の
冷媒との熱交換が不充分であることに起因して、過熱気
相状態の冷媒が充分冷却されないまま高圧側圧縮機に供
給され易いので、高圧側圧縮機に供給される冷媒の温度
が充分に下がりにくく、圧縮機による圧縮効率の低下を
効果的に防止できない欠点がある。Further, due to insufficient heat exchange between the refrigerant in the wet vapor state and the refrigerant in the superheated vapor phase state, the refrigerant in the superheated vapor phase state is supplied to the high pressure side compressor without being sufficiently cooled. Since it is easy, the temperature of the refrigerant supplied to the high-pressure side compressor is not easily lowered sufficiently, and there is a drawback that the reduction in compression efficiency due to the compressor cannot be effectively prevented.
【０００７】本発明は上記実情に鑑みてなされたもので
あって、湿り蒸気状態の冷媒を中間冷却器に供給する手
段を工夫することにより、湿り蒸気状態の冷媒のうちの
液分の高圧側圧縮機への供給を抑制して、高圧側圧縮機
の運転エネルギーの増大やその破損を招きにくい複段ヒ
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 the above circumstances, and by devising a means for supplying a refrigerant in a wet vapor state to an intercooler, a high-pressure side of a liquid component of the refrigerant in a wet vapor state is devised. An object of the present invention is to provide a multi-stage heat pump device that suppresses supply to the compressor and is unlikely to cause increase in operating energy of the high-pressure side compressor and damage thereof.
【０００８】又、本発明は、湿り蒸気状態の冷媒のうち
の液分の高圧側圧縮機への供給を効率よく抑制できるよ
うにすることを目的とする。Another object of the present invention is to efficiently suppress the supply of the liquid component of the refrigerant in the wet vapor state to the high pressure side compressor.
【０００９】又、本発明は、湿り蒸気状態の冷媒のうち
の液分の遠心分離を効率良く促進できるようにすること
を目的とする。Another object of the present invention is to make it possible to efficiently promote the centrifugal separation of the liquid component of the refrigerant in the wet vapor state.
【００１０】又、本発明は、湿り蒸気状態の冷媒のうち
の液分の遠心分離を、エネルギーの無駄が少ない状態で
効率良く促進できるようにすることを目的とする。Another object of the present invention is to make it possible to efficiently promote centrifugal separation of a liquid component of a wet vapor state refrigerant in a state where energy waste is small.
【００１１】又、本発明は、湿り蒸気状態の冷媒のうち
の液分の高圧側圧縮機への供給を効果的に抑制しなが
ら、湿り蒸気状態の冷媒と過熱気相状態の冷媒との熱交
換を促進して、圧縮機による圧縮効率の低下を効果的に
防止できるようにすることを目的とする。Further, according to the present invention, the heat of the wet vapor state refrigerant and the superheated vapor phase state refrigerant is effectively suppressed while effectively suppressing the supply of the liquid of the wet vapor state refrigerant to the high pressure side compressor. It is an object of the present invention to facilitate exchange and effectively prevent a reduction in compression efficiency due to a compressor.
【００１２】[0012]
【課題を解決するための手段】上記目的を達成する為の
本発明の特徴構成は、中間冷却器の上部から気相状態で
取り出した冷媒を高圧側圧縮機・凝縮器・高圧側膨張手
段の順に通過させて、湿り蒸気状態で前記中間冷却器に
戻す高圧側循環系と、前記中間冷却器の下部から液相状
態で取り出した冷媒を低圧側膨張手段・蒸発器・低圧側
圧縮機の順に通過させて、過熱気相状態で前記中間冷却
器に戻す低圧側循環系とが備えられている複段ヒートポ
ンプ装置であって、前記高圧側膨張手段を通過した湿り
蒸気状態の冷媒を、前記中間冷却器の内部気相域に、そ
の器壁内面に沿って流動させる状態で供給する高圧側供
給手段が設けられている点にある。The characteristic constitution of the present invention for attaining the above object is that the refrigerant taken out from the upper portion of the intercooler in a gas phase state is used in the high pressure side compressor / condenser / high pressure side expansion means. The high-pressure side circulation system which is passed through in order and returned to the intercooler in the wet vapor state, and the refrigerant taken out in the liquid phase state from the lower part of the intercooler in the order of the low-pressure side expansion means, the evaporator and the low-pressure side compressor. A multi-stage heat pump device comprising: a low-pressure side circulation system that is passed through and returned to the intermediate cooler in a superheated gas phase state, wherein the refrigerant in a wet vapor state that has passed through the high-pressure side expansion means is the intermediate A high-pressure side supply means for supplying in a state of flowing along the inner surface of the cooler is provided in the internal gas phase region of the cooler.
【００１３】前記高圧側供給手段が、湿り蒸気状態の冷
媒を前記器壁内面に沿って旋回流動させる状態で前記内
部気相域に供給する高圧側供給路を設けて構成されてい
る場合は、湿り蒸気状態の冷媒から液分を遠心分離して
器壁内面に凝集させ易く、湿り蒸気状態の冷媒のうちの
液分の高圧側圧縮機への供給を効率よく抑制できる。In the case where the high pressure side supply means is provided with a high pressure side supply passage for supplying the refrigerant in a wet vapor state to the internal gas phase region in a state of swirling and flowing along the inner surface of the vessel wall, It is easy to centrifuge the liquid component from the wet vapor state refrigerant to agglomerate it on the inner surface of the vessel wall, and efficiently supply the liquid component of the wet vapor state refrigerant to the high-pressure side compressor.
【００１４】前記高圧側供給手段が、湿り蒸気状態の冷
媒を水平方向又は略水平方向に向けて供給する状態で設
けられている場合、或いは、前記内部気相域の器壁内面
に、湿り蒸気状態の冷媒の旋回流動方向に長い凹溝が設
けられている場合は、いずれも、湿り蒸気状態の冷媒か
らの液分の遠心分離を効率良く促進できる。When the high pressure side supply means is provided in a state of supplying the refrigerant in a wet vapor state in a horizontal direction or a substantially horizontal direction, or on the inner surface of the inner wall of the internal vapor phase region, the wet vapor is provided. When the long groove is provided in the swirling flow direction of the refrigerant in the state, the centrifugal separation of the liquid component from the refrigerant in the wet vapor state can be efficiently promoted in any case.
【００１５】前記高圧側供給手段が、前記湿り蒸気状態
の冷媒を前記内部気相域に供給する高圧側供給管を前記
中間冷却器の器壁に対してその接線方向又は略接線方向
に接続するとともに、その管端開口を前記器壁内面に形
成して構成されている場合は、湿り蒸気状態の冷媒から
の液分の遠心分離を、エネルギーの無駄が少ない状態で
効率良く促進できる。The high-pressure side supply means connects a high-pressure side supply pipe for supplying the refrigerant in the wet vapor state to the internal vapor phase region in a tangential direction or a substantially tangential direction to a wall of the intercooler. In addition, when the tube end opening is formed on the inner surface of the vessel wall, the centrifugal separation of the liquid component from the refrigerant in the wet vapor state can be efficiently promoted with little waste of energy.
【００１６】前記高圧側供給手段が、前記湿り蒸気状態
の冷媒を前記内部気相域に供給する高圧側供給管を前記
中間冷却器の器壁に対して貫通接続するとともに、その
管端開口を前記内部気相域に臨む器壁内面に対向させる
状態で近接配置して構成されている場合は、湿り蒸気状
態の冷媒のうちの液分を器壁内面に衝突させて当該器壁
内面に凝集させ易く、湿り蒸気状態の冷媒のうちの液分
の高圧側圧縮機への供給を効率よく抑制できる。The high pressure side supply means connects the high pressure side supply pipe for supplying the refrigerant in the wet vapor state to the internal vapor phase region to the wall of the intercooler through the pipe end opening. In the case where they are arranged close to each other so as to face the inner surface of the vessel wall facing the internal vapor phase region, the liquid component of the refrigerant in the wet vapor state collides with the inner surface of the vessel wall and is condensed on the inner surface of the vessel wall. Therefore, the supply of the liquid in the wet vapor state refrigerant to the high-pressure side compressor can be efficiently suppressed.
【００１７】前記低圧側圧縮機を通過した過熱気相状態
の冷媒を前記器壁内面に沿って流動する湿り蒸気状態の
冷媒に供給する低圧側供給手段が設けられている場合
は、湿り蒸気状態の冷媒のうちの液分の高圧側圧縮機へ
の供給を効果的に抑制しながら、湿り蒸気状態の冷媒と
過熱気相状態の冷媒との熱交換を促進して、圧縮機によ
る圧縮効率の低下を効果的に防止できる。In the case where a low pressure side supply means for supplying the superheated vapor phase refrigerant passing through the low pressure side compressor to the wet vapor state refrigerant flowing along the inner surface of the vessel wall is provided, the wet vapor state is provided. While effectively suppressing the supply of the liquid component of the refrigerant to the high-pressure side compressor, the heat exchange between the refrigerant in the wet vapor state and the refrigerant in the superheated gas phase state is promoted to improve the compression efficiency of the compressor. The decrease can be effectively prevented.
【００１８】[0018]
【作用】湿り蒸気状態の冷媒を中間冷却器の器壁内面に
沿って積極的に流動させるから、温度境界層が器壁内面
に沿って形成されにくい状態で、湿り蒸気状態の冷媒と
中間冷却器の器壁との熱交換が促進され、その結果、湿
り蒸気状態の冷媒の温度が低下して、その冷媒に含まれ
る液分の凝集が促進されるから、湿り蒸気状態の冷媒の
うちの液分の粒が大きく成長して中間冷却器の下部に落
下し易くなる。[Function] Since the refrigerant in the wet vapor state is positively caused to flow along the inner surface of the intercooler, the temperature boundary layer is hard to be formed along the inner surface of the inner wall and the refrigerant in the wet vapor state and the intermediate cooling are formed. Heat exchange with the vessel wall of the container is promoted, as a result, the temperature of the refrigerant in the wet vapor state is lowered, and the aggregation of the liquid component contained in the refrigerant is promoted. The liquid particles grow large and easily fall to the lower part of the intercooler.
【００１９】高圧側供給手段が、湿り蒸気状態の冷媒を
器壁内面に沿って旋回流動させる状態で内部気相域に供
給する高圧側供給路を設けて構成されている場合は、湿
り蒸気状態の冷媒のうちの質量の比較的大きい液分が遠
心分離されて器壁内面に凝集し易い。In the case where the high-pressure side supply means is provided with a high-pressure side supply passage for supplying the refrigerant in the wet vapor state to the internal gas phase region in a state of swirling and flowing along the inner surface of the vessel wall, the wet vapor state A liquid component having a relatively large mass of the refrigerant is likely to be centrifuged and aggregated on the inner surface of the vessel wall.
【００２０】高圧側供給手段が、湿り蒸気状態の冷媒を
水平方向又は略水平方向に向けて供給する状態で設けら
れている場合は、湿り蒸気状態の冷媒の流動経路が長い
螺旋状に形成され、湿り蒸気状態の冷媒が比較的長時間
に亘って旋回流動し易い。When the high-pressure side supply means is provided in a state of supplying the refrigerant in the wet vapor state in the horizontal direction or the substantially horizontal direction, the flow path of the refrigerant in the wet vapor state is formed in a long spiral shape. The refrigerant in the wet vapor state easily swirls and flows for a relatively long time.
【００２１】内部気相域の器壁内面に、湿り蒸気状態の
冷媒の旋回流動方向に長い凹溝が設けられている場合
は、湿り蒸気状態の冷媒の旋回流動方向が安定する。When a long groove is formed in the inner wall surface of the internal vapor phase region in the swirling flow direction of the refrigerant in the wet vapor state, the swirling flow direction of the refrigerant in the wet vapor state is stable.
【００２２】高圧側供給手段が、湿り蒸気状態の冷媒を
内部気相域に供給する高圧側供給管を中間冷却器の器壁
に対してその接線方向又は略接線方向に接続するととも
に、その管端開口を器壁内面に形成して構成されている
場合は、内部気相域に供給された直後の湿り蒸気状態の
冷媒が器壁内面に沿って直ちに旋回流動し易く、湿り蒸
気状態の冷媒が中間冷却器内に滞留しにくい。The high-pressure side supply means connects the high-pressure side supply pipe for supplying the refrigerant in a wet vapor state to the internal vapor phase region in a tangential direction or a substantially tangential direction with respect to the wall of the intercooler, and the pipe. When the end opening is formed on the inner surface of the vessel wall, the refrigerant in the wet vapor state immediately after being supplied to the internal gas phase region easily swirls along the inner surface of the vessel wall, and the refrigerant in the wet vapor state. Is hard to stay in the intercooler.
【００２３】高圧側供給手段が、湿り蒸気状態の冷媒を
内部気相域に供給する高圧側供給管を中間冷却器の器壁
に対して貫通接続するとともに、その管端開口を内部気
相域に臨む器壁内面に対向させる状態で近接配置して構
成されている場合は、管端開口から吹き出される湿り蒸
気状態の冷媒のうちの、質量の比較的大きい液分がその
慣性力で器壁内面に衝突し易くなり、そのような液分が
当該器壁内面に凝集して分離され易い。The high-pressure side supply means penetrates the high-pressure side supply pipe for supplying the refrigerant in the wet vapor state to the internal vapor phase region to the wall of the intercooler, and has its pipe end opening in the internal vapor phase region. In the case where they are arranged close to each other so as to face the inner surface of the vessel wall facing the, the liquid component having a relatively large mass of the wet vapor state refrigerant blown out from the pipe end opening is It becomes easy to collide with the inner surface of the wall, and such a liquid component is easily aggregated and separated on the inner surface of the vessel wall.
【００２４】低圧側圧縮機を通過した過熱気相状態の冷
媒を器壁内面に沿って流動する湿り蒸気状態の冷媒に供
給する低圧側供給手段が設けられている場合は、過熱気
相状態の冷媒が速い速度で流動している湿り蒸気状態の
冷媒中に攪拌混合され易いので、湿り蒸気状態の冷媒と
過熱気相状態の冷媒との熱交換が促進されるとともに、
湿り蒸気状態の冷媒の液分のうちでも比較的軽くて高圧
側圧縮機に吸い込まれ易い細かな液分がその熱交換によ
って蒸発し易い。In the case where the low-pressure side supply means for supplying the refrigerant in the superheated vapor phase state that has passed through the low pressure side compressor to the refrigerant in the wet vapor state flowing along the inner surface of the vessel wall is provided, Since the refrigerant is easily agitated and mixed in the wet vapor state refrigerant flowing at a high speed, heat exchange between the wet vapor state refrigerant and the superheated vapor phase state refrigerant is promoted,
Among the liquid components of the refrigerant in the wet vapor state, the relatively small liquid components that are easily sucked into the high-pressure side compressor are easily evaporated by heat exchange.
【００２５】[0025]
【発明の効果】請求項１記載の複段ヒートポンプ装置
は、湿り蒸気状態の冷媒のうちの液分を中間冷却器の下
部に落下させ易いので、湿り蒸気状態の冷媒のうちの液
分の分離を促進して、その液分の高圧側圧縮機への供給
を抑制でき、高圧側圧縮機の運転エネルギーの増大やそ
の破損を招きにくい。In the multi-stage heat pump device according to the first aspect, since the liquid component of the wet vapor state refrigerant is easily dropped to the lower part of the intercooler, the liquid component of the wet vapor state refrigerant is separated. It is possible to suppress the supply of the liquid to the high-pressure side compressor, and it is unlikely that the operating energy of the high-pressure side compressor is increased and the liquid is damaged.
【００２６】請求項２記載の複段ヒートポンプ装置は、
湿り蒸気状態の冷媒のうちの液分が遠心分離されて器壁
内面に凝集し易いので、湿り蒸気状態の冷媒からの液分
の分離が一層促進され、湿り蒸気状態の冷媒のうちの液
分の高圧側圧縮機への供給を効率よく抑制できる。The multi-stage heat pump device according to claim 2 is
Since the liquid content of the refrigerant in the wet vapor state is centrifugally separated and easily aggregates on the inner surface of the vessel wall, the separation of the liquid content from the refrigerant in the wet vapor state is further promoted, and the liquid content of the refrigerant in the wet vapor state is increased. The power supply to the high-pressure side compressor can be efficiently suppressed.
【００２７】請求項３記載の複段ヒートポンプ装置は、
湿り蒸気状態の冷媒が器壁内面に沿って比較的長時間に
亘って旋回流動させ易いので、湿り蒸気状態の冷媒のう
ちの液分の遠心分離を効率良く促進できる。The multi-stage heat pump device according to claim 3 is
Since the refrigerant in the wet vapor state easily swirls along the inner surface of the vessel wall for a relatively long time, centrifugal separation of the liquid in the refrigerant in the wet vapor state can be efficiently promoted.
【００２８】請求項４記載の複段ヒートポンプ装置は、
湿り蒸気状態の冷媒の旋回流動方向が安定するので、湿
り蒸気状態の冷媒のうちの液分の遠心分離を効率良く促
進できる。The multi-stage heat pump device according to claim 4 is
Since the swirling flow direction of the refrigerant in the wet vapor state is stable, the centrifugal separation of the liquid of the refrigerant in the wet vapor state can be efficiently promoted.
【００２９】請求項５記載の複段ヒートポンプ装置は、
中間冷却器に供給された直後の湿り蒸気状態の冷媒が中
間冷却器内に滞留しにくいので、湿り蒸気状態の冷媒の
うちの液分の遠心分離を、エネルギーの無駄が少ない状
態で効率良く促進できる。The multi-stage heat pump device according to claim 5 is
The refrigerant in the wet vapor state immediately after being supplied to the intercooler is less likely to stay in the intercooler, so the centrifugal separation of the liquid of the refrigerant in the wet vapor state is efficiently promoted with less waste of energy. it can.
【００３０】請求項６記載の複段ヒートポンプ装置は、
湿り蒸気状態の冷媒のうちの液分が器壁内面に衝突して
当該器壁内面に凝集し易いので、湿り蒸気状態の冷媒か
らの液分の分離が一層促進され、湿り蒸気状態の冷媒の
うちの液分の高圧側圧縮機への供給を効率よく抑制でき
る。A multi-stage heat pump device according to claim 6 is
Since the liquid content of the refrigerant in the wet vapor state collides with the inner surface of the vessel wall and easily aggregates on the inner surface of the vessel wall, the separation of the liquid content from the refrigerant in the wet vapor state is further promoted, and the refrigerant in the wet vapor state is It is possible to efficiently suppress the supply of the liquid of the liquid to the high-pressure side compressor.
【００３１】請求項７記載の複段ヒートポンプ装置は、
湿り蒸気状態の冷媒と過熱気相状態の冷媒との熱交換が
促進されるとともに、湿り蒸気状態の冷媒の液分のうち
でも比較的軽くて高圧側圧縮機に吸い込まれ易い細かな
液分が蒸発し易いので、湿り蒸気状態の冷媒のうちの液
分の高圧側圧縮機への供給を効果的に抑制しながら、圧
縮機による圧縮効率の低下を効果的に防止できる。A multi-stage heat pump device according to claim 7 is
The heat exchange between the refrigerant in the wet vapor state and the refrigerant in the superheated vapor phase state is promoted, and among the liquid components of the refrigerant in the wet vapor state, fine liquid components that are relatively light and easily sucked into the high pressure side compressor are generated. Since it easily evaporates, it is possible to effectively suppress the decrease in the compression efficiency of the compressor while effectively suppressing the supply of the liquid of the refrigerant in the wet vapor state to the high-pressure side compressor.
【００３２】[0032]
〔第１実施例〕図４，図５は複段ヒートポンプ装置の一
例としての空調装置を示し、室外空気Ａ１を吸放熱対象
とする室外熱交換器１と、室外熱交換器１に室外空気Ａ
１を通風する外気ファンＦ１と、室内空気の冷却・加熱
を行う室内熱交換器２と、室内熱交換器２で調整した空
気Ａ２を空調対象域へ送給する給気ファンＦ２とが設け
られ、室外熱交換器１と室内熱交換器２とに亘って冷媒
を循環させることで、室外空気Ａ１を吸放熱源として、
室内空気を冷却又は加熱する二段圧縮ヒートポンプ回路
が構成されている。[First Embodiment] FIGS. 4 and 5 show an air conditioner as an example of a multi-stage heat pump device, which includes an outdoor heat exchanger 1 for absorbing and radiating outdoor air A1, and an outdoor air exchanger 1 having outdoor air A.
1, an outdoor air fan F1 that ventilates 1, an indoor heat exchanger 2 that cools and heats indoor air, and an air supply fan F2 that sends the air A2 adjusted by the indoor heat exchanger 2 to an air conditioning target area. By circulating the refrigerant between the outdoor heat exchanger 1 and the indoor heat exchanger 2, the outdoor air A1 is used as a heat absorption / radiation source,
A two-stage compression heat pump circuit that cools or heats indoor air is configured.
【００３３】尚、前記二段圧縮ヒートポンプ回路におい
て、黒塗りの太線はその部分の冷媒状態が高圧気相であ
ることを示し、ハッチングを施した太線はその部分の冷
媒状態が液相であることを示し、点ハッチングを施した
太線はその部分の冷媒状態が気液二相（湿り蒸気）であ
ることを示し、白抜きの太線はその部分の冷媒状態が低
圧気相であることを示している。In the two-stage compression heat pump circuit, the thick black line indicates that the refrigerant state of that portion is the high-pressure gas phase, and the thick hatched line indicates that the refrigerant state of that portion is the liquid phase. , The thick line with dot hatching indicates that the refrigerant state of that part is gas-liquid two-phase (wet vapor), and the white thick line indicates that the refrigerant state of that part is low-pressure gas phase. There is.
【００３４】前記二段圧縮ヒートポンプ回路には、室外
熱交換器１に対する第１膨張弁ｅｘ１と、室内熱交換器
２に対する第２膨張弁ｅｘ２と、高圧側圧縮機ＣｍＨと
低圧側圧縮機ＣｍＬとの二つの圧縮機と、これら二つの
圧縮機ＣｍＨ，ＣｍＬと第１膨張弁ｅｘ１と第２膨張弁
ｅｘ２が接続される中間冷却器３と、高圧側圧縮機Ｃｍ
Ｈから導出される高圧気相状態の冷媒を空調モードに応
じて室外熱交換器１又は室内熱交換器２に択一的に導入
可能な第１、第２電磁弁Ｖ１，Ｖ２と、空調モードに応
じて室外熱交換器１又は室内熱交換器２から導出される
低圧気相状態の冷媒を低圧側圧縮機ＣｍＬに導入可能な
第３、第４電磁弁Ｖ３，Ｖ４とが設けられている。In the two-stage compression heat pump circuit, a first expansion valve ex1 for the outdoor heat exchanger 1, a second expansion valve ex2 for the indoor heat exchanger 2, a high pressure side compressor CmH and a low pressure side compressor CmL. Two compressors, the two compressors CmH and CmL, the intercooler 3 to which the first expansion valve ex1 and the second expansion valve ex2 are connected, and the high-pressure side compressor Cm.
First and second solenoid valves V1 and V2 that can selectively introduce the high-pressure gas-phase refrigerant that is derived from H into the outdoor heat exchanger 1 or the indoor heat exchanger 2 according to the air conditioning mode, and the air conditioning mode The third and fourth solenoid valves V3 and V4 that can introduce the low-pressure gas-phase refrigerant that is discharged from the outdoor heat exchanger 1 or the indoor heat exchanger 2 into the low-pressure side compressor CmL are provided. .
【００３５】前記第１膨張弁ｅｘ１と第２膨張弁ｅｘ２
と中間冷却器３との間には、室外熱交換器１又は室内熱
交換器２のいずれか一方を蒸発器Ｅとして機能させると
きには、その蒸発器Ｅとして機能させる熱交換器に対応
する第１膨張弁ｅｘ１又は第２膨張弁ｅｘ２が低圧側膨
張手段として機能するよう流路切換可能な第５、第６電
磁弁Ｖ５，Ｖ６と、室外熱交換器１又は室内熱交換器２
のいずれか他方を凝縮器Ｃとして機能させるときには、
その凝縮器Ｃとして機能させる熱交換器に対応する第１
膨張弁ｅｘ１又は第２膨張弁ｅｘ２が高圧側膨張手段と
して機能するよう流路切換可能な第７、第８電磁弁Ｖ
７，Ｖ８とが設けられている。The first expansion valve ex1 and the second expansion valve ex2
When either the outdoor heat exchanger 1 or the indoor heat exchanger 2 functions as the evaporator E, the first heat exchanger corresponding to the heat exchanger that functions as the evaporator E is provided between the intermediate cooler 3 and the intercooler 3. The fifth and sixth electromagnetic valves V5 and V6 capable of switching the flow paths so that the expansion valve ex1 or the second expansion valve ex2 functions as the low-pressure side expansion means, and the outdoor heat exchanger 1 or the indoor heat exchanger 2
When causing the other of the above to function as the condenser C,
The first corresponding to the heat exchanger to function as the condenser C
The seventh and eighth electromagnetic valves V whose flow paths can be switched so that the expansion valve ex1 or the second expansion valve ex2 functions as the high-pressure side expansion means.
7 and V8 are provided.
【００３６】前記中間冷却器３は縦長の円筒形タンクを
設けて構成され、高圧側膨張手段として機能する第１膨
張弁ｅｘ１又は第２膨張弁ｅｘ２を通過した湿り蒸気状
態の冷媒を中間冷却器３の内部気相域ＧＡに、器壁内面
３ａに沿って流動させる状態で供給する高圧側供給手段
としての高圧側供給路４と、低圧側圧縮機ＣｍＬを通過
した過熱気相状態の冷媒を、器壁内面３ａに沿って流動
する湿り蒸気状態の冷媒に供給する低圧側供給手段とし
ての低圧側供給路５とが連通接続され、高圧側供給路４
から導入した湿り蒸気状態の冷媒と、低圧側供給路５か
ら導入した過熱気相状態の冷媒とを中間冷却器３内で直
接熱交換させて、熱交換した後の気相状態の冷媒を、タ
ンク頂部に開口する状態で連通接続した第１導出路６か
ら高圧側圧縮機ＣｍＨに導出し、熱交換した後の液相状
態の冷媒を、タンク底部に開口する状態で連通接続した
第２導出路７から低圧側膨張手段として機能する第１膨
張弁ｅｘ１又は第２膨張弁ｅｘ２に導出するよう構成さ
れている。The intercooler 3 is constructed by providing a vertically long cylindrical tank, and the refrigerant in a wet vapor state that has passed through the first expansion valve ex1 or the second expansion valve ex2 functioning as high-pressure side expansion means is intercooled. 3, a high pressure side supply passage 4 as a high pressure side supply means for supplying in a state of flowing along the inner wall surface 3a to the inner gas phase region GA of 3, and a refrigerant in a superheated gas phase state that has passed through the low pressure side compressor CmL. , A low-pressure side supply passage 5 as a low-pressure side supply means for supplying the refrigerant in a wet vapor state flowing along the inner wall surface 3a, and is connected to the high-pressure side supply passage 4.
The refrigerant in the wet vapor state introduced from the above and the refrigerant in the superheated gas phase introduced from the low-pressure side supply passage 5 are directly heat-exchanged in the intercooler 3, and the refrigerant in the gas phase after heat exchange is performed. The second derivation in which the refrigerant in the liquid phase state after being discharged to the high-pressure side compressor CmH from the first derivation path 6 connected and connected in the state of opening at the top of the tank and being heat-exchanged is connected in the state of opening in the bottom of the tank. It is configured to lead from the passage 7 to the first expansion valve ex1 or the second expansion valve ex2 that functions as the low pressure side expansion means.
【００３７】尚、図中、白抜きの電磁弁は開いている状
態を示し、黒塗りの電磁弁は閉じている状態を示してい
る。In the figure, the white solenoid valve shows the open state, and the black solenoid valve shows the closed state.
【００３８】図４は、空調モードを冷房モードに切り換
えた状態の二段圧縮ヒートポンプ回路を示し、この冷房
モードでは、第２電磁弁Ｖ２と第３電磁弁Ｖ３と第５電
磁弁Ｖ５と第８電磁弁Ｖ８を閉じるとともに、第１電磁
弁Ｖ１と第４電磁弁Ｖ４と第６電磁弁Ｖ６と第７電磁弁
Ｖ７を開いて、中間冷却器３から気相状態で取り出した
冷媒を高圧側圧縮機ＣｍＨ・凝縮器Ｃとして機能させる
室外熱交換器１・高圧側膨張手段としての第１膨張弁ｅ
ｘ１の順に通過させて、湿り蒸気状態で中間冷却器３に
戻す高圧側循環系と、中間冷却器３から液相状態で取り
出した冷媒を低圧側膨張手段としての第２膨張弁ｅｘ２
・蒸発器Ｅとして機能させる室内熱交換器２・低圧側圧
縮機ＣｍＬの順に通過させて、過熱気相状態で中間冷却
器３に戻す低圧側循環系とが構成されている。FIG. 4 shows the two-stage compression heat pump circuit in a state where the air conditioning mode is switched to the cooling mode. In this cooling mode, the second solenoid valve V2, the third solenoid valve V3, the fifth solenoid valve V5, and the eighth solenoid valve V5. The solenoid valve V8 is closed, and the first solenoid valve V1, the fourth solenoid valve V4, the sixth solenoid valve V6, and the seventh solenoid valve V7 are opened to compress the refrigerant taken out from the intercooler 3 in the vapor phase on the high pressure side. Machine CmH / outdoor heat exchanger 1 functioning as condenser C / first expansion valve e as high pressure side expansion means
x1 and the second high-pressure side circulation system for returning to the intercooler 3 in the wet vapor state, and the second expansion valve ex2 as the low-pressure side expansion means for the refrigerant taken out from the intercooler 3 in the liquid phase state.
The indoor heat exchanger 2 that functions as the evaporator E and the low-pressure side compressor CmL are passed in this order, and the low-pressure side circulation system that returns to the intercooler 3 in the superheated gas phase state is configured.
【００３９】又、図５は、空調モードを暖房モードに切
り換えた状態の二段圧縮ヒートポンプ回路を示し、第２
電磁弁Ｖ２と第３電磁弁Ｖ３と第５電磁弁Ｖ５と第８電
磁弁Ｖ８を開くとともに、第１電磁弁Ｖ１と第４電磁弁
Ｖ４と第６電磁弁Ｖ６と第７電磁弁Ｖ７を閉じて、中間
冷却器３から気相状態で取り出した冷媒を高圧側圧縮機
ＣｍＨ・凝縮器Ｃとして機能させる室内熱交換器２・高
圧側膨張手段としての第２膨張弁ｅｘ２の順に通過させ
て、湿り蒸気状態で中間冷却器３に戻す高圧側循環系
と、中間冷却器３から液相状態で取り出した冷媒を低圧
側膨張手段としての第１膨張弁ｅｘ１・蒸発器Ｅとして
機能させる室外熱交換器１・低圧側圧縮機ＣｍＬの順に
通過させて、過熱気相状態で中間冷却器３に戻す低圧側
循環系とが構成されている。FIG. 5 shows the two-stage compression heat pump circuit in the state where the air conditioning mode is switched to the heating mode.
The solenoid valve V2, the third solenoid valve V3, the fifth solenoid valve V5, and the eighth solenoid valve V8 are opened, and the first solenoid valve V1, the fourth solenoid valve V4, the sixth solenoid valve V6, and the seventh solenoid valve V7 are closed. Then, the refrigerant taken out in the vapor phase from the intercooler 3 is passed through the high pressure side compressor CmH, the indoor heat exchanger 2 functioning as the condenser C, and the second expansion valve ex2 as the high pressure side expansion means in this order, High-pressure side circulation system that returns to the intercooler 3 in the wet vapor state, and outdoor heat exchange that causes the refrigerant taken out from the intercooler 3 in the liquid phase state to function as the first expansion valve ex1 and the evaporator E as low-pressure side expansion means. A low-pressure side circulation system is configured to pass through the device 1 and the low-pressure side compressor CmL in this order, and to return to the intercooler 3 in the superheated gas phase state.
【００４０】前記高圧側供給路４は、図１乃至図３に示
すように、湿り蒸気状態の冷媒を中間冷却器３の内部気
相域ＧＡに水平方向又は略水平方向に向けて供給する高
圧側供給管４ａを、当該中間冷却器３の器壁に対してそ
の接線方向又は略接線方向に接続するとともに、その管
端開口４ｂを器壁内面３ａに形成して構成され、湿り蒸
気状態の冷媒が器壁内面３ａに沿って、図中の点ハッチ
ングの矢印で示す方向に旋回流動させる状態で内部気相
域ＧＡに供給されるように構成してある。As shown in FIGS. 1 to 3, the high-pressure side supply passage 4 supplies the refrigerant in a wet vapor state to the internal vapor phase region GA of the intercooler 3 in a horizontal direction or a substantially horizontal direction. The side supply pipe 4a is connected to the wall of the intercooler 3 in a tangential direction or a substantially tangential direction, and the pipe end opening 4b is formed on the inner wall 3a of the wall to form a wet steam state. The refrigerant is supplied to the internal gas phase region GA in a state of swirling and flowing along the inner wall surface 3a in the direction indicated by the dotted arrow in the figure.
【００４１】又、内部気相域ＧＡの器壁内面３ａには、
器壁を環状に膨出させて形成した湿り蒸気状態の冷媒の
旋回流動方向に長い凹溝３ｂが設けられ、管端開口４ｂ
がこの凹溝３ｂ底部に臨む状態で形成されている。Further, on the inner surface 3a of the vessel wall in the internal gas phase region GA,
A long concave groove 3b is provided in the swirling flow direction of the refrigerant in a wet vapor state formed by bulging the vessel wall in an annular shape, and the pipe end opening 4b is formed.
Are formed so as to face the bottom of the concave groove 3b.
【００４２】前記低圧側供給路５は、過熱気相状態の冷
媒を中間冷却器３の内部気相域ＧＡに水平方向又は略水
平方向に向けて供給する低圧側供給路管５ａを、当該中
間冷却器３の器壁に対してその接線方向又は略接線方向
に接続するとともに、その管端開口５ｂを前述の凹溝３
ｂよりも上方位置の器壁内面３ａに形成して構成され、
過熱気相状態の冷媒が器壁内面３ａに沿って湿り蒸気状
態の冷媒の旋回流動方向とは逆向きの、図中の黒塗りの
矢印で示す方向に旋回流動させる状態で内部気相域ＧＡ
に供給されるように構成してある。The low-pressure side supply passage 5 includes a low-pressure side supply passage pipe 5a for supplying the refrigerant in a superheated vapor phase state to the internal vapor phase region GA of the intercooler 3 in a horizontal direction or a substantially horizontal direction. It is connected to the wall of the cooler 3 in a tangential direction or a substantially tangential direction, and the pipe end opening 5b is connected to the concave groove 3 described above.
It is formed by being formed on the inner surface 3a of the vessel wall located above b.
When the refrigerant in the superheated gas phase is swirling along the inner wall surface 3a in the direction opposite to the swirling flow direction of the refrigerant in the wet vapor state, the internal gas phase region GA is shown.
It is configured to be supplied to.
【００４３】このように、湿り蒸気状態の冷媒の旋回流
動方向と過熱気相状態の冷媒の旋回流動方向とを逆向き
に設定することで、これらの冷媒どうしの攪拌混合が促
進されるとともに、これらの冷媒どうしが衝突し易いの
で、湿り蒸気状態の冷媒と過熱気相状態の冷媒との熱交
換が一層促進され、圧縮器による圧縮効率の低下を効果
的に防止できる。As described above, the swirling flow direction of the refrigerant in the wet vapor state and the swirling flow direction of the refrigerant in the superheated gas phase state are set to be opposite to each other, whereby stirring and mixing of these refrigerants are promoted, and Since these refrigerants are likely to collide with each other, heat exchange between the refrigerant in the wet vapor state and the refrigerant in the superheated vapor phase state is further promoted, and reduction in compression efficiency by the compressor can be effectively prevented.
【００４４】又、液分の凝集が促進された後の湿り蒸気
状態の冷媒に、過熱気相状態の冷媒が攪拌混合されるの
で、高圧側圧縮機に吸い込まれ易い細かい液分が過熱気
相状態の冷媒との熱交換で蒸発し易く、その液分の高圧
側圧縮機への供給を抑制できる。Further, since the refrigerant in the superheated vapor phase state is agitated and mixed with the refrigerant in the wet vapor state after the condensation of the liquid fractions is promoted, the fine liquid fraction which is easily sucked into the high pressure side compressor is superheated in the superheated vapor phase It is easy to evaporate by heat exchange with the refrigerant in the state, and the supply of the liquid to the high-pressure side compressor can be suppressed.
【００４５】尚、蒸発器として機能する室外熱交換器１
又は室内熱交換器２を通過して導出された温度の低い気
相状態の冷媒を低圧側圧縮機ＣｍＬに導出する冷媒流路
９の途中に、その温度の低い気相状態の冷媒と、中間冷
却器３底部に溜まっている液相状態の冷媒とを熱交換さ
せる熱交換器１０を設けて、第２導出路７から導出され
る液相状態の冷媒を温度の低い気相状態の冷媒で冷却す
るので、液相状態が安定している過冷却状態の冷媒を低
圧側膨張手段として機能する第１膨張弁ｅｘ１又は第２
膨張弁ｅｘ２に供給でき、低圧側膨張手段による減圧膨
張を安定化できる効果がある。The outdoor heat exchanger 1 functioning as an evaporator
Alternatively, in the middle of the refrigerant flow path 9 for leading the low-temperature refrigerant in the gas phase, which has been led out through the indoor heat exchanger 2, to the low-pressure side compressor CmL, the low-temperature gas-phase refrigerant and the intermediate The heat exchanger 10 for exchanging heat with the liquid-phase refrigerant accumulated at the bottom of the cooler 3 is provided, and the liquid-phase refrigerant discharged from the second outlet path 7 is converted into a low-temperature gas-phase refrigerant. Since it is cooled, the first expansion valve ex1 or the second expansion valve ex1 that functions as the low-pressure side expansion means uses the refrigerant in the supercooled state in which the liquid phase state is stable.
It can be supplied to the expansion valve ex2, and there is an effect that the decompression expansion by the low pressure side expansion means can be stabilized.
【００４６】〔第２実施例〕図６は、湿り蒸気状態の冷
媒を器壁内面３ａに沿って旋回流動させる状態で内部気
相域ＧＡに供給する高圧側供給路４の別実施例を示し、
この高圧側供給路４は、湿り蒸気状態の冷媒を中間冷却
器３の内部気相域ＧＡに斜め下方に向けて供給する高圧
側供給管４ａを、当該中間冷却器３の器壁に対してその
接線方向又は略接線方向に接続するとともに、その管端
開口４ｂを器壁内面３ａに形成して構成され、湿り蒸気
状態の冷媒が、図中の点ハッチングの矢印で示すよう
に、器壁内面３ａに沿って斜め下方に向けて螺旋状に旋
回流動させる状態で内部気相域ＧＡに供給されるように
構成してある。[Second Embodiment] FIG. 6 shows another embodiment of the high pressure side supply passage 4 for supplying the refrigerant in the wet vapor state to the internal gas phase region GA in a state of swirling and flowing along the inner wall surface 3a. ,
The high-pressure side supply passage 4 has a high-pressure side supply pipe 4a for supplying the refrigerant in a wet vapor state to the internal gas phase region GA of the intercooler 3 obliquely downward with respect to the wall of the intercooler 3. The pipe end opening 4b is connected to the tangential direction or the substantially tangential direction, and the pipe end opening 4b is formed on the inner surface 3a of the vessel wall. It is configured so as to be supplied to the internal gas phase region GA in a state of being spirally swirling downwardly along the inner surface 3a.
【００４７】尚、本実施例では、低圧側圧縮機ＣｍＬを
通過した過熱気相状態の冷媒を、器壁内面３ａに沿って
流動する湿り蒸気状態の冷媒に供給する低圧側供給手段
としての低圧側供給路５が、過熱気相状態の冷媒を中間
冷却器３の内部気相域ＧＡに斜め上方に向けて供給する
低圧側供給管５ａを、当該中間冷却器３の器壁に対して
その接線方向又は略接線方向に接続するとともに、その
管端開口５ｂを高圧側供給管４ａの管端開口４ｂよりも
下方位置の器壁内面３ａに形成して構成され、過熱気相
状態の冷媒が、図中の黒塗りの矢印で示すように、器壁
内面３ａに沿って、湿り蒸気状態の冷媒の旋回流動方向
とは逆向きの螺旋状に旋回流動させる状態で内部気相域
ＧＡに供給されるように構成してある。In this embodiment, the low-pressure side supply means for supplying the superheated vapor-phase refrigerant passing through the low-pressure side compressor CmL to the wet-vapor-state refrigerant flowing along the inner wall surface 3a of the vessel wall. The low-pressure side supply pipe 5a, which supplies the refrigerant in the superheated gas phase state to the internal gas phase region GA of the intercooler 3 in an obliquely upward direction, is provided on the side wall 5 of the intercooler 3 with respect to the wall of the intercooler 3. It is connected in a tangential direction or a substantially tangential direction, and its pipe end opening 5b is formed on the inner wall surface 3a of the high pressure side supply pipe 4a below the pipe end opening 4b. As shown by the black arrow in the figure, the refrigerant is supplied to the internal gas phase region GA along the inner wall surface 3a in a state in which the refrigerant in the wet vapor state swirls in a spiral direction opposite to the swirling flow direction. It is configured to be performed.
【００４８】又、本実施例では、内部気相域ＧＡの器壁
内面３ａに、高圧側供給管４ａの管端開口位置と低圧側
供給管５ａの管端開口位置とに亘って、冷媒の旋回流動
方向に沿う螺旋状の凹溝３ｂを一連に形成して、湿り蒸
気状態の冷媒と過熱気相状態の冷媒とを強制的に衝突さ
せながら互いに逆向きの螺旋状に旋回流動させるように
構成したので、湿り蒸気状態の冷媒と過熱気相状態の冷
媒との熱交換がなお一層促進される。その他の構成は第
１実施例と同様である。Further, in the present embodiment, on the inner wall surface 3a of the internal gas phase region GA, the refrigerant is spread over the pipe end opening position of the high pressure side supply pipe 4a and the pipe end opening position of the low pressure side supply pipe 5a. A spiral groove 3b is formed in series along the swirling flow direction so that the refrigerant in the wet vapor state and the refrigerant in the superheated vapor phase state are forced to collide with each other to swirl and flow in opposite spiral directions. Since it is configured, the heat exchange between the refrigerant in the wet vapor state and the refrigerant in the superheated vapor phase state is further promoted. Other configurations are similar to those of the first embodiment.
【００４９】〔第３実施例〕図７は、高圧側供給手段の
別実施例を示し、この高圧側供給手段は、湿り蒸気状態
の冷媒を内部気相域ＧＡに供給する高圧側供給管４ａを
中間冷却器３の器壁に対して貫通させる状態で接続する
とともに、ラッパ状に拡径したその管端開口４ｂを内部
気相域ＧＡに臨む器壁内面３ａに対向させる状態で近接
配置して、管端開口４ｂから図中の矢印で示すように吹
き出される湿り蒸気状態の冷媒のうちの、質量の比較的
大きい液分がその慣性力で器壁内面３ａに衝突して、当
該器壁内面３ａに凝集分離され易くしてある。[Third Embodiment] FIG. 7 shows another embodiment of the high pressure side supply means. This high pressure side supply means is a high pressure side supply pipe 4a for supplying a refrigerant in a wet vapor state to the internal gas phase region GA. Is connected to the wall of the intercooler 3 in a state of penetrating through the wall, and the pipe end opening 4b of which the diameter is expanded in a trumpet shape is closely arranged so as to face the inner wall 3a of the wall facing the internal gas phase region GA. Of the refrigerant in the wet vapor state blown out from the pipe end opening 4b as indicated by the arrow in the figure, a liquid component having a relatively large mass collides with the inner wall 3a of the vessel wall due to its inertial force. The inner wall surface 3a is easily aggregated and separated.
【００５０】又、過熱気相状態の冷媒を中間冷却器３の
内部気相域ＧＡに供給する低圧側供給管５ａの管端開口
５ｂを、高圧側供給管４ａの管端開口４ｂの略直上位置
に配置してある。その他の構成は第１実施例と同様であ
る。Further, the pipe end opening 5b of the low pressure side supply pipe 5a for supplying the superheated vapor phase refrigerant to the internal vapor phase region GA of the intercooler 3 is substantially directly above the pipe end opening 4b of the high pressure side supply pipe 4a. It is located in the position. Other configurations are similar to those of the first embodiment.
【００５１】〔その他の実施例〕 １．本発明による複段ヒートポンプ装置は、冷房や暖房
の空調用途に限定されるものでなく、冷熱や恩熱を扱う
各種分野の種々の用途に適用でき、三段以上の複段ヒー
トポンプ装置であっても良い。 ２．高圧側供給路を構成する高圧側供給管の管端開口
を、中間冷却器の器壁内面よりも中間冷却器の径方向内
側に突出させて、湿り蒸気状態の冷媒を器壁内面に沿っ
て旋回流動させる状態で内部気相域に供給するよう構成
しても良い。[Other Embodiments] 1. The multi-stage heat pump device according to the present invention is not limited to air-conditioning applications such as cooling and heating, and can be applied to various applications in various fields dealing with cold heat and heat, and is a multi-stage heat pump device with three or more stages. Is also good. 2. The pipe end opening of the high-pressure side supply pipe that constitutes the high-pressure side supply passage is made to project inward in the radial direction of the intercooler rather than the inner surface of the intercooler wall, so that the refrigerant in the wet vapor state is along the inner wall surface of the intercooler. It may be configured to supply to the internal gas phase region in a state of swirling and flowing.
【００５２】尚、特許請求の範囲の項に図面との対照を
便利にするために符号を記すが、該記入により本発明は
添付図面の構成に限定されるものではない。It should be noted that reference numerals are added to the claims for convenience of comparison with the drawings, but the present invention is not limited to the structures of the accompanying drawings by the entry.
【図１】要部の一部破断側面図FIG. 1 is a partially cutaway side view of a main part.
【図２】要部の水平断面図FIG. 2 is a horizontal sectional view of a main part
【図３】要部の水平断面図FIG. 3 is a horizontal sectional view of a main part
【図４】冷房モードの冷媒循環系を示す冷媒回路図FIG. 4 is a refrigerant circuit diagram showing a refrigerant circulation system in a cooling mode.
【図５】暖房モードの冷媒循環系を示す冷媒回路図FIG. 5 is a refrigerant circuit diagram showing a refrigerant circulation system in a heating mode.
【図６】第２実施例を示す要部の一部破断側面図FIG. 6 is a partially cutaway side view of an essential part showing a second embodiment.
【図７】第３実施例を示す要部の一部破断側面図FIG. 7 is a partially cutaway side view of a main part showing a third embodiment.
【図８】従来例を示す要部の拡大断面図FIG. 8 is an enlarged cross-sectional view of a main part showing a conventional example.
３ 中間冷却器 ３ａ 器壁内面 ３ｂ 凹溝 ４ 高圧側供給手段（高圧側供給路） ４ａ 高圧側供給管 ４ｂ 管端開口 ５ 低圧側供給手段 Ｃ 凝縮器 ＣｍＨ 高圧側圧縮機 ＣｍＬ 低圧側圧縮機 ｅｘ１ 高圧側膨張手段（低圧側膨張手段） ｅｘ２ 高圧側膨張手段（低圧側膨張手段） Ｅ 蒸発器 ＧＡ 内部気相域 3 Intercooler 3a Inner wall surface 3b Recessed groove 4 High pressure side supply means (high pressure side supply path) 4a High pressure side supply pipe 4b Pipe end opening 5 Low pressure side supply means C Condenser CmH High pressure side compressor CmL Low pressure side compressor ex1 High pressure side expansion means (low pressure side expansion means) ex2 High pressure side expansion means (low pressure side expansion means) E Evaporator GA Internal gas phase region
Claims (7)
取り出した冷媒を高圧側圧縮機（ＣｍＨ）・凝縮器
（Ｃ）・高圧側膨張手段（ｅｘ１又はｅｘ２）の順に通
過させて、湿り蒸気状態で前記中間冷却器（３）に戻す
高圧側循環系と、前記中間冷却器（３）の下部から液相
状態で取り出した冷媒を低圧側膨張手段（ｅｘ２又はｅ
ｘ１）・蒸発器（Ｅ）・低圧側圧縮機（ＣｍＬ）の順に
通過させて、過熱気相状態で前記中間冷却器（３）に戻
す低圧側循環系とが備えられている複段ヒートポンプ装
置であって、 前記高圧側膨張手段（ｅｘ１又はｅｘ２）を通過した湿
り蒸気状態の冷媒を、前記中間冷却器（３）の内部気相
域（ＧＡ）に、その器壁内面（３ａ）に沿って流動させ
る状態で供給する高圧側供給手段（４）が設けられてい
る複段ヒートポンプ装置。1. The refrigerant taken out in the vapor phase from the upper part of the intercooler (3) is passed through a high pressure side compressor (CmH), a condenser (C), and a high pressure side expansion means (ex1 or ex2) in this order. , A high pressure side circulation system which returns to the intermediate cooler (3) in a wet vapor state, and a refrigerant taken out in a liquid phase state from a lower portion of the intermediate cooler (3) to a low pressure side expansion means (ex2 or e).
x1) -evaporator (E) -low-pressure side compressor (CmL), and a multi-stage heat pump device provided with a low-pressure side circulation system that returns to the intercooler (3) in a superheated gas phase state. The refrigerant in the wet vapor state that has passed through the high pressure side expansion means (ex1 or ex2) is introduced into the internal gas phase region (GA) of the intercooler (3) along the inner surface (3a) of the vessel wall. A multi-stage heat pump device provided with high-pressure side supply means (4) for supplying in a fluidized state.
状態の冷媒を前記器壁内面（３ａ）に沿って旋回流動さ
せる状態で前記内部気相域（ＧＡ）に供給する高圧側供
給路を設けて構成されている請求項１記載の複段ヒート
ポンプ装置。2. The high-pressure side supply means for supplying the high-pressure side supply means (4) to the internal gas phase region (GA) in a state in which the refrigerant in a wet vapor state is swirled along the inner surface (3a) of the vessel wall. The multi-stage heat pump device according to claim 1, which is configured by providing a passage.
状態の冷媒を水平方向又は略水平方向に向けて供給する
状態で設けられている請求項２記載の複段ヒートポンプ
装置。3. The multi-stage heat pump device according to claim 2, wherein the high-pressure side supply means (4) is provided in a state of supplying the refrigerant in a wet vapor state in a horizontal direction or a substantially horizontal direction.
ａ）に、湿り蒸気状態の冷媒の旋回流動方向に長い凹溝
（３ｂ）が設けられている請求項３記載の複段ヒートポ
ンプ装置。4. The inner wall surface (3) of the inner gas phase region (GA)
The multi-stage heat pump device according to claim 3, wherein a groove (3b) that is long in the swirling flow direction of the refrigerant in the wet vapor state is provided in a).
蒸気状態の冷媒を前記内部気相域（ＧＡ）に供給する高
圧側供給管（４ａ）を前記中間冷却器（３）の器壁に対
してその接線方向又は略接線方向に接続するとともに、
その管端開口（４ｂ）を前記器壁内面（３ａ）に形成し
て構成されている請求項２，３又は４記載の複段ヒート
ポンプ装置。5. The high pressure side supply means (4) is a container of the intercooler (3), wherein the high pressure side supply pipe (4a) supplies the refrigerant in the wet vapor state to the internal gas phase region (GA). While connecting to the wall in its tangential direction or approximately tangential direction,
The multi-stage heat pump device according to claim 2, 3 or 4, wherein the tube end opening (4b) is formed on the inner surface (3a) of the vessel wall.
蒸気状態の冷媒を前記内部気相域（ＧＡ）に供給する高
圧側供給管（４ａ）を前記中間冷却器（３）の器壁に対
して貫通接続するとともに、その管端開口（４ｂ）を前
記内部気相域（ＧＡ）に臨む器壁内面（３ａ）に対向さ
せる状態で近接配置して構成されている請求項１記載の
複段ヒートポンプ装置。6. The high-pressure side supply pipe (4a) for supplying the refrigerant in the wet vapor state to the internal gas phase region (GA) is a container of the intercooler (3). 2. The structure is arranged so as to be penetratingly connected to a wall, and to be arranged in proximity so that the tube end opening (4b) faces the inner surface (3a) of the vessel wall facing the internal gas phase region (GA). Multi-stage heat pump device.
過熱気相状態の冷媒を前記器壁内面（３ａ）に沿って流
動する湿り蒸気状態の冷媒に供給する低圧側供給手段
（５）が設けられている請求項１，２，３，４，５又は
６記載の複段ヒートポンプ装置。7. A low pressure side supply means (5) for supplying the superheated vapor phase refrigerant passing through the low pressure side compressor (CmL) to the wet vapor state refrigerant flowing along the inner wall surface (3a). The multi-stage heat pump device according to claim 1, 2, 3, 4, 5 or 6, further comprising:
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6094092A JPH07301467A (en) | 1994-05-06 | 1994-05-06 | Plural-stage heat pump apparatus |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6094092A JPH07301467A (en) | 1994-05-06 | 1994-05-06 | Plural-stage heat pump apparatus |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH07301467A true JPH07301467A (en) | 1995-11-14 |
Family
ID=14100816
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP6094092A Pending JPH07301467A (en) | 1994-05-06 | 1994-05-06 | Plural-stage heat pump apparatus |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH07301467A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7802441B2 (en) | 2004-05-12 | 2010-09-28 | Electro Industries, Inc. | Heat pump with accumulator at boost compressor output |
| US7849700B2 (en) | 2004-05-12 | 2010-12-14 | Electro Industries, Inc. | Heat pump with forced air heating regulated by withdrawal of heat to a radiant heating system |
-
1994
- 1994-05-06 JP JP6094092A patent/JPH07301467A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7802441B2 (en) | 2004-05-12 | 2010-09-28 | Electro Industries, Inc. | Heat pump with accumulator at boost compressor output |
| US7849700B2 (en) | 2004-05-12 | 2010-12-14 | Electro Industries, Inc. | Heat pump with forced air heating regulated by withdrawal of heat to a radiant heating system |
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