JPH0439587B2 - - Google Patents
Info
- Publication number
- JPH0439587B2 JPH0439587B2 JP25129085A JP25129085A JPH0439587B2 JP H0439587 B2 JPH0439587 B2 JP H0439587B2 JP 25129085 A JP25129085 A JP 25129085A JP 25129085 A JP25129085 A JP 25129085A JP H0439587 B2 JPH0439587 B2 JP H0439587B2
- Authority
- JP
- Japan
- Prior art keywords
- refrigerant
- heat exchanger
- heater
- heating
- compressor
- 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
Links
- 239000003507 refrigerant Substances 0.000 claims description 118
- 238000010438 heat treatment Methods 0.000 claims description 44
- 239000007788 liquid Substances 0.000 claims description 15
- 238000001816 cooling Methods 0.000 claims description 9
- 238000005057 refrigeration Methods 0.000 claims description 3
- 230000000694 effects Effects 0.000 description 6
- 238000010586 diagram Methods 0.000 description 4
- 238000004378 air conditioning Methods 0.000 description 3
- 230000007423 decrease Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
Landscapes
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Description
【発明の詳細な説明】
産業上の利用分野
本発明は冷媒加熱器を有するヒートポンプ式冷
暖房装置に関するものである。DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a heat pump air-conditioning system having a refrigerant heater.
従来の技術
従来のこの種の冷暖房装置は第３図に示すよう
に、暖房運転時に凝縮器として作用する室内熱交
換器３の中間に電気ヒーター６を設けて、暖房運
転時に室内熱交換器３で凝縮した一部または全部
の冷媒を蒸発気化させ、再度前記室内熱交換器３
で再凝縮させて暖房能力を確保するようになつて
いた。（例えば、特公昭45−38038号公報）又、第
４図に示すように、室内熱交換器３と並列に液冷
媒を送るポンプ７と冷媒加熱器８を供えた冷媒加
熱装置９を設け、暖房運転時の暖房能力を確保す
るようになつていた。（例えば、実公昭50−37255
号公報）
発明が解決しようとする問題点
しかしながら第３図のような構成では室内熱交
換器３の中間位置に冷媒加熱器６を設けているの
で室内熱交換器３が大型となるとともに電気ヒー
タ６の容量に制約があるという問題点を有してい
た。又、第４図の構成では液冷媒を送るポンプ７
と冷媒加熱器８を有する冷媒加熱装置９を室内熱
交換器と並列に設けているので、ポンプ７から冷
媒加熱器８への冷媒液送量と冷媒加熱器８の加熱
量とのバランス、制御性及びポンプ７の信頼性、
イニシヤルコスト、ランニングコストという問題
点を有していた。BACKGROUND TECHNOLOGY As shown in FIG. 3, this type of conventional air-conditioning system has an electric heater 6 disposed between an indoor heat exchanger 3 that functions as a condenser during heating operation, and the indoor heat exchanger 3 acts as a condenser during heating operation. Part or all of the refrigerant condensed in
The heating capacity was ensured by re-condensing the gas. (For example, Japanese Patent Publication No. 45-38038) Furthermore, as shown in FIG. 4, a refrigerant heating device 9 equipped with a pump 7 for feeding liquid refrigerant and a refrigerant heater 8 is provided in parallel with the indoor heat exchanger 3, It was designed to ensure heating capacity during heating operation. (For example, Jikko Sho 50-37255
Problems to be Solved by the Invention However, in the configuration as shown in FIG. However, there was a problem in that the capacity of 6 was limited. In addition, in the configuration shown in FIG. 4, the pump 7 for sending liquid refrigerant
Since a refrigerant heating device 9 having a refrigerant heater 8 and a refrigerant heater 8 is installed in parallel with the indoor heat exchanger, the amount of refrigerant liquid sent from the pump 7 to the refrigerant heater 8 and the amount of heating by the refrigerant heater 8 can be balanced and controlled. performance and reliability of the pump 7;
This had the problem of initial cost and running cost.
本発明はかかる従来の問題を解消するもので、
機器の小型化、経済性、信頼性をはかる目的のも
のである。 The present invention solves such conventional problems,
The purpose is to make the equipment smaller, more economical, and more reliable.
問題点を解決するための手段
上記問題点を解決するために本発明の冷暖房装
置は、圧縮機、四方弁、室内熱交換器、膨張装
置、室外熱交換器とから冷凍サイクルを構成する
とともに、前記室内熱交換器と並列に第１の逆止
弁、液溜めタンク、第２の逆止弁、冷媒加熱器を
順次連結し、かつ前記液溜めタンクと前記第２の
逆止弁と前記冷媒加熱器と並列に開閉弁を有する
バイパス管を設けてなり、前記圧縮機吐出ライン
にエゼクターを設けてエゼクター効果により前記
冷媒加熱器内の媒体を吸引するように冷媒密閉回
路を構成したものである。Means for Solving the Problems In order to solve the above problems, the air conditioning system of the present invention includes a refrigeration cycle including a compressor, a four-way valve, an indoor heat exchanger, an expansion device, and an outdoor heat exchanger. A first check valve, a liquid reservoir tank, a second check valve, and a refrigerant heater are sequentially connected in parallel with the indoor heat exchanger, and the liquid reservoir tank, the second check valve, and the refrigerant A closed refrigerant circuit is constructed in which a bypass pipe having an on-off valve is provided in parallel with the heater, and an ejector is provided in the compressor discharge line to suck the medium in the refrigerant heater by the ejector effect. .
作 用
本発明は上記構成によつて、開閉弁を開にして
冷媒液溜めタンクの内圧を冷媒加熱器の内圧とバ
ランスさせ、冷媒液溜めタンクと冷媒加熱器のヘ
ツド差で冷媒液溜めタンク内の液冷媒を冷媒加熱
器へ送り加熱して蒸発ガス化した冷媒を圧縮機と
四方弁間に設けたエゼクターで吸引し、圧縮機の
吐出ガスに合流させて室内熱交換器へ送り被加熱
側へ放熱して凝縮能力を高めるシステムである
為、室内熱交換器に電気ヒータを付加することも
なく、又、冷媒ポンプも不用となり、機器の小型
化、冷媒ポンプのイニシヤルコスト、ランニング
コストの低減化もはかれる。Effects According to the above configuration, the present invention balances the internal pressure of the refrigerant reservoir tank with the internal pressure of the refrigerant heater by opening the on-off valve, and uses the head difference between the refrigerant reservoir tank and the refrigerant heater to balance the internal pressure of the refrigerant reservoir tank with the internal pressure of the refrigerant heater. The liquid refrigerant is sent to the refrigerant heater, and the evaporated and gasified refrigerant is sucked in by the ejector installed between the compressor and the four-way valve, merged with the discharge gas of the compressor, and sent to the indoor heat exchanger on the heated side. Since this system increases condensing capacity by dissipating heat to the indoor heat exchanger, there is no need to add an electric heater to the indoor heat exchanger, and no refrigerant pump is required, reducing the size of the equipment and reducing the initial cost and running cost of the refrigerant pump. It can also be reduced.
実施例
以下、本発明の一実施例を添付図面にもとづい
て説明する。Embodiment Hereinafter, an embodiment of the present invention will be described based on the accompanying drawings.
第１図において、１０は圧縮機、１１は四方弁
であり、暖房運転と冷房運転の冷媒流れ方向を変
える。１２は室内熱交換器であり、暖房運転時は
冷媒の凝縮作用、冷房運転時は冷媒の蒸発作用を
行なう。１３は膨張装置、１４は室外熱交換器で
あり、暖房運転時において大気熱エンタルピーが
大きい時に冷媒の蒸発作用を行ない、冷房運転時
には冷媒の凝縮作用を行なう。又、前記圧縮機１
０、前記四方弁１１、前記室内熱交換器１２、前
記膨張装置１３、前記室外熱交換器１４は順次連
結されている。１５は第１の逆止弁、１６は冷媒
液溜めタンク、１７は第２の逆止弁、１８は冷媒
加熱器であり、前記冷媒液溜めタンク１６より低
位置に設けられており、暖房運転時において大気
熱エンタルピーが小さく、前記室外熱交換器１４
での大気熱吸熱量が少ない為に暖房能力が不足す
る場合に加熱源１９によつて、冷媒を蒸発ガス化
させる。又、前記第１の逆止弁１５と前記冷媒液
溜めタンク１６と前記第２の逆止弁１７と前記冷
媒加熱器１８は順次連結されて前記室内熱交換器
１２と並列に設けられており、冷媒の流れは前記
室内熱交換器１２、前記第１の逆止弁１５、前記
冷媒液溜めタンク１６、前記第２の逆止弁、前記
冷媒加熱器１８への一方向に流れる様に構成され
ている。２０は開閉弁であり、前記冷媒液溜めタ
ンク１６と前記第２の逆止弁１７と前記冷媒加熱
器１８と並列からなるバイパス管２１の管途中に
具備されている。２２はエゼクターであり、前記
圧縮機１０の吐出ラインの中に設けられており、
前記圧縮機１０からの吐出冷媒ガス流によるエゼ
クター効果で前記冷媒加熱器１８で蒸発ガス化し
た冷媒を吸引して前記圧縮機１０からの吐出冷媒
ガスと合流する。 In FIG. 1, 10 is a compressor, and 11 is a four-way valve, which changes the direction of refrigerant flow between heating operation and cooling operation. Reference numeral 12 denotes an indoor heat exchanger, which performs a refrigerant condensing action during heating operation, and a refrigerant evaporation action during cooling operation. 13 is an expansion device, and 14 is an outdoor heat exchanger, which evaporates the refrigerant when the atmospheric thermal enthalpy is large during heating operation, and condenses the refrigerant during cooling operation. Moreover, the compressor 1
0, the four-way valve 11, the indoor heat exchanger 12, the expansion device 13, and the outdoor heat exchanger 14 are connected in sequence. 15 is a first check valve, 16 is a refrigerant reservoir tank, 17 is a second check valve, and 18 is a refrigerant heater, which is provided at a lower position than the refrigerant reservoir tank 16, and which is used for heating operation. When the atmospheric heat enthalpy is small, the outdoor heat exchanger 14
When heating capacity is insufficient due to a small amount of atmospheric heat absorbed, the refrigerant is evaporated and gasified by the heating source 19. Further, the first check valve 15, the refrigerant reservoir tank 16, the second check valve 17, and the refrigerant heater 18 are sequentially connected and provided in parallel with the indoor heat exchanger 12. , the refrigerant is configured to flow in one direction to the indoor heat exchanger 12, the first check valve 15, the refrigerant reservoir tank 16, the second check valve, and the refrigerant heater 18. has been done. Reference numeral 20 denotes an on-off valve, which is provided in the middle of a bypass pipe 21 that is arranged in parallel with the refrigerant reservoir tank 16, the second check valve 17, and the refrigerant heater 18. 22 is an ejector, which is provided in the discharge line of the compressor 10,
Due to the ejector effect of the refrigerant gas flow discharged from the compressor 10, the refrigerant evaporated and gasified by the refrigerant heater 18 is sucked and merges with the refrigerant gas discharged from the compressor 10.
上記構成において、冷房運転時は圧縮機１０で
圧縮された高温高圧の冷媒ガスは四方弁１１を第
１図の破線方向に流れ室外熱交換器１４に流入す
る。そして、大気へ放熱して凝縮液化し膨張装置
１３で減圧されて室内熱交換器１２に流入し、室
内空気から熱を奪い蒸発ガス化して前記四方弁１
１を通り圧縮機１０にもどる。次に暖房運転時を
述べる。最初に室外温度が比較的に高く大気熱エ
ンタルピーが大きい場合のヒートポンプ単独運転
を述べる。圧縮機１０で圧縮された高温高圧の冷
媒ガスは四方弁１１を第１図の実線方向に示す如
く流れ室内熱交換器１２に流入し、室内空気へ放
熱して凝縮液化し、（この際に室内を暖房する。）
膨張装置１３に流入して膨張減圧されて室外熱交
換器１４に流入する。そして、大気熱を吸熱して
蒸発ガス化し前記四方弁１１を通り前記圧縮機１
０にもどる。又、大気熱エンタルピーが少なく暖
房能力が不足する場合には、前記ヒートポンプ運
転と冷媒加熱器１８の冷媒加熱の併用運転するこ
とができる。この場合には加熱源１９をONし、
冷媒加熱器１８で高圧冷媒を加熱し蒸発ガス化さ
せ、前記圧縮機１０で圧縮された高温高圧の冷媒
ガスがエゼクター２２を通る際に吸引されて前記
圧縮機で吐出された高温高圧の冷媒ガスと合流し
室内熱交換器１２に流入し、ここで放熱して凝縮
液化させて膨張装置１３と冷媒液溜めタンク１６
に分流する。そして膨張装置１３に流入した冷媒
は前記ヒートポンプ運転時と同様に室外熱交換器
１４で大気熱を吸熱して蒸発ガス化し圧縮機１０
にもどる。一方、前記冷媒液溜めタンク１６に流
入した液冷媒は、圧力が前記冷媒加熱器１８の圧
力よりも低くなつているので開閉弁２０を開とし
た時に前記冷媒液溜めタンク１６と前記冷媒加熱
器１８の圧力を等しくさせ、前記冷媒液溜めタン
ク１６と前記冷媒加熱器１８の位置ヘツド差で前
記冷媒液溜めタンク１６内の液冷媒を前記冷媒加
熱器１８へ流し、加熱源１９で冷媒を加熱し蒸発
ガス化させる。その時の圧力−エンタルピのモリ
エル線図を第２図に示す。第２図において図中番
号は第１図の番号と同一である。ヒートポンプ単
独運転時の暖房能力Q1は圧縮機吐出冷媒量GR1と
すると、大気からの吸熱量QE＝GR1×Δi1（Δi1は
室外熱交換器１４の入口、出口の冷媒エンタルピ
ー差）、暖房能力Q1＝GR1×Δi2（Δi2は室内熱交換
器１２の入口、出口の冷媒エンタルピー差）と表
わせる。一方、ヒートポンプ運転と冷媒加熱器１
８との併用運転時には暖房能力ＱがＱ＝Q1＋Q2
（Q2＝GR2×Δi2，GR2は冷媒液溜めタンク１６、
冷媒加熱器１８を循環する冷媒循環量）となり、
Q2だけ暖房能力が向上する。次に、さらに室外
温度が低下し大気熱エンタルピーが小さくなつ
て、室外熱交換器１４でほとんど大気熱を吸熱で
きず暖房能力が不足する場合には、前記冷媒加熱
器１８、前記室内熱交換器１２、冷媒液溜めタン
ク１６の冷媒回路で冷媒加熱運転することができ
る。この場合には、室外熱交換器１４で大気熱は
吸熱しないけれども、室外温度及び大気エンタル
ピーに関係なく暖房能力が必要だけ取り出すこと
ができる。いわゆる暖房能力に必要な熱量だけ加
熱源１９を入力すればよい。従つて、負荷（暖房
能力）が小さくてよい場合には運転効率の良いヒ
ートポンプ単独運転を行ない、負荷が大きくなる
につれて、ヒートポンプ運転と冷媒加熱運転の併
用、さらには冷媒加熱単独運転へと絶えず暖房能
力を確保しつつランニングコストも低減すること
ができる。そして、室内熱交換器１２に電気ヒー
タを付加する必要もなく、又、冷媒ポンプも不必
要となる為に機器の小型化、イニシヤルコスト、
ランニングコストも低減できる。 In the above configuration, during cooling operation, high-temperature, high-pressure refrigerant gas compressed by the compressor 10 flows through the four-way valve 11 in the direction of the broken line in FIG. 1 and flows into the outdoor heat exchanger 14. Then, it radiates heat to the atmosphere, condenses and liquefies, is depressurized by the expansion device 13, and flows into the indoor heat exchanger 12, where it absorbs heat from the indoor air and becomes evaporated and gasified.
1 and returns to the compressor 10. Next, we will discuss heating operation. First, we will discuss the independent operation of the heat pump when the outdoor temperature is relatively high and the atmospheric thermal enthalpy is large. The high-temperature, high-pressure refrigerant gas compressed by the compressor 10 flows through the four-way valve 11 as shown by the solid line in FIG. (Heat the room.)
It flows into the expansion device 13, is expanded and decompressed, and flows into the outdoor heat exchanger 14. Then, it absorbs atmospheric heat and converts it into evaporative gas, passing through the four-way valve 11 to the compressor 1.
Return to 0. Further, when the heating capacity is insufficient due to a small atmospheric thermal enthalpy, the heat pump operation and the refrigerant heating of the refrigerant heater 18 can be operated in combination. In this case, turn on the heating source 19,
The high-pressure refrigerant is heated in the refrigerant heater 18 to evaporate and gasify, and the high-temperature, high-pressure refrigerant gas compressed by the compressor 10 is sucked when passing through the ejector 22 and discharged by the compressor. It flows into the indoor heat exchanger 12, where it radiates heat, condenses and liquefies it, and is sent to the expansion device 13 and the refrigerant reservoir tank 16.
Divided into. Then, the refrigerant that has flowed into the expansion device 13 absorbs atmospheric heat in the outdoor heat exchanger 14 and evaporates and gasifies it into a compressor 10, as in the case of the heat pump operation.
Return to On the other hand, since the pressure of the liquid refrigerant that has flowed into the refrigerant reservoir tank 16 is lower than the pressure of the refrigerant heater 18, when the on-off valve 20 is opened, the refrigerant reservoir tank 16 and the refrigerant heater 18, the liquid refrigerant in the refrigerant reservoir tank 16 flows to the refrigerant heater 18 due to the difference in position between the refrigerant reservoir tank 16 and the refrigerant heater 18, and the refrigerant is heated by the heat source 19. and evaporate into gas. The pressure-enthalpy Mollier diagram at that time is shown in Figure 2. In FIG. 2, the numbers in the figure are the same as those in FIG. If the heating capacity Q 1 when the heat pump is operated alone is the amount of refrigerant discharged from the compressor G R1 , then the amount of heat absorbed from the atmosphere Q E = G R1 × Δi 1 (Δi 1 is the refrigerant enthalpy difference between the inlet and outlet of the outdoor heat exchanger 14 ), heating capacity Q 1 =G R1 ×Δi 2 (Δi 2 is the refrigerant enthalpy difference between the inlet and outlet of the indoor heat exchanger 12). On the other hand, heat pump operation and refrigerant heater 1
When operating in combination with 8, the heating capacity Q is Q = Q 1 + Q 2
(Q 2 = G R2 ×Δi 2 , G R2 is the refrigerant reservoir tank 16,
The amount of refrigerant circulated through the refrigerant heater 18),
Heating capacity increases by Q2 . Next, when the outdoor temperature further decreases and the atmospheric heat enthalpy becomes smaller, and the outdoor heat exchanger 14 is unable to absorb much of the atmospheric heat and the heating capacity is insufficient, the refrigerant heater 18, the indoor heat exchanger 14 12. The refrigerant circuit of the refrigerant reservoir tank 16 can perform refrigerant heating operation. In this case, although the outdoor heat exchanger 14 does not absorb atmospheric heat, it is possible to extract as much heating capacity as necessary regardless of the outdoor temperature and atmospheric enthalpy. It is only necessary to input the heat source 19 by the amount of heat required for the so-called heating capacity. Therefore, when the load (heating capacity) is small, the heat pump is operated independently, which has high operational efficiency, and as the load increases, the heat pump and refrigerant heating are combined, and then the refrigerant heating is switched to independent operation, which provides constant heating. It is possible to reduce running costs while ensuring capacity. Furthermore, there is no need to add an electric heater to the indoor heat exchanger 12, and no refrigerant pump is required, resulting in equipment downsizing, initial costs, and
Running costs can also be reduced.
発明の効果
以上のように本発明の冷暖房装置によれば次の
効果が得られる。Effects of the Invention As described above, the heating and cooling device of the present invention provides the following effects.
(1) 圧縮機、四方弁、室内熱交換器、膨張装置、
室外熱交換器とから冷凍サイクルを構成すると
ともに、前記室内熱交換器と並列に第１の逆止
弁と冷媒液溜めタンクと第２の逆止弁と冷媒加
熱器を備え、かつ、前記冷媒液溜めタンクと第
２の逆止弁と前記冷媒加熱器と並列に開閉弁を
有するバイパス管を設け、前記圧縮機吐出ライ
ンにエゼクターを設けて前記冷媒加熱器で蒸発
ガス化した冷媒を吐出ラインに吸引する構成か
らなり、又、前記冷媒液溜めタンクの高さ位置
を前記冷媒加熱器より高くして冷媒密閉回路を
構成している為、暖房運転時に暖房能力が不足
する場合には室内熱交換器から流出した液冷媒
を冷媒液溜めタンクに納め、前記開閉弁を開に
することによつて前記冷媒液溜めタンク内の圧
力と前記冷媒加熱器内の圧力を等しくさせ、前
記冷媒液溜めタンクと前記冷媒加熱器の位置ヘ
ツド差で前記冷媒液溜めタンク内の液冷媒を前
記冷媒加熱器に流し、蒸発ガス化させる。そし
て前記圧縮機の吐出ラインへ前記エゼクターの
エゼクター効果により吸引され、前記圧縮機の
吐出冷媒と合流させて室内熱交換器に流れ暖房
能力を増加させることができる。よつて、室内
熱交換器に電気ヒーターを付加することもな
く、又、冷媒ポンプを用いる必要もない為に機
器の小型化及びイニシヤルコスト、ランニング
コストも低減することができる。(1) Compressor, four-way valve, indoor heat exchanger, expansion device,
A refrigeration cycle is constituted by an outdoor heat exchanger, and a first check valve, a refrigerant reservoir tank, a second check valve, and a refrigerant heater are provided in parallel with the indoor heat exchanger, and the refrigerant A bypass pipe having an on-off valve is provided in parallel with a liquid storage tank, a second check valve, and the refrigerant heater, and an ejector is provided in the compressor discharge line to discharge the refrigerant evaporated and gasified by the refrigerant heater into the discharge line. In addition, since the height of the refrigerant liquid storage tank is higher than the refrigerant heater to form a refrigerant sealed circuit, indoor heat can be absorbed when heating capacity is insufficient during heating operation. The liquid refrigerant flowing out of the exchanger is stored in a refrigerant reservoir tank, and the pressure in the refrigerant reservoir tank and the pressure in the refrigerant heater are equalized by opening the on-off valve, and the refrigerant reservoir Due to the difference in position between the tank and the refrigerant heater, the liquid refrigerant in the refrigerant reservoir tank is caused to flow into the refrigerant heater and is evaporated and gasified. The refrigerant is then sucked into the discharge line of the compressor by the ejector effect of the ejector, merges with the refrigerant discharged from the compressor, and flows to the indoor heat exchanger, increasing the heating capacity. Therefore, there is no need to add an electric heater to the indoor heat exchanger, and there is no need to use a refrigerant pump, so it is possible to downsize the device and reduce initial costs and running costs.
(2) 室外温度が高く大気熱エンタルピーが大きく
て暖房負荷が小さい場合には運転効率の良いヒ
ートポンプサイクルで暖房運転を行ない、大気
熱エンタルピーの低下により暖房能力が負荷よ
りも少し不足する場合には、ヒートポンプ運転
と冷媒加熱器による冷媒加熱の併用運転で暖房
能力不足を解消し、さらに能力が負荷よりも小
さい場合には冷媒加熱器による冷媒加熱単独運
転で負荷を満足することができる。従つて、運
転効率の良い状態で常に負荷を満足することが
できる。(2) When the outdoor temperature is high, the atmospheric heat enthalpy is large, and the heating load is small, heating operation is performed using the heat pump cycle, which has high operational efficiency.If the heating capacity is slightly insufficient than the load due to a decrease in atmospheric heat enthalpy, Insufficient heating capacity can be solved by a combined operation of heat pump operation and refrigerant heating by a refrigerant heater, and if the capacity is smaller than the load, the load can be satisfied by the refrigerant heating only operation by the refrigerant heater. Therefore, the load can always be satisfied with good operating efficiency.
第１図は本発明の一実施例における冷暖房装置
の冷媒回路図、第２図は冷媒の圧力−モリエル線
図、第３図、第４図は従来の冷暖房装置の冷媒回
路図である。
１０……圧縮機、１１……四方弁、１２……冷
媒加熱器、１３……膨張装置、１４……室外熱交
換器、１５……第１の逆止弁、１６……冷媒液溜
めタンク、１７……第２の逆止弁、１８……冷媒
加熱器、２０……開閉弁、２２……エゼクター。
FIG. 1 is a refrigerant circuit diagram of a heating and cooling system according to an embodiment of the present invention, FIG. 2 is a refrigerant pressure-Mollier diagram, and FIGS. 3 and 4 are refrigerant circuit diagrams of a conventional heating and cooling system. 10... Compressor, 11... Four-way valve, 12... Refrigerant heater, 13... Expansion device, 14... Outdoor heat exchanger, 15... First check valve, 16... Refrigerant liquid reservoir tank , 17...Second check valve, 18...Refrigerant heater, 20...Opening/closing valve, 22...Ejector.
Claims (1)
室外熱交換器とから冷凍サイクルを構成し、前記
室内熱交換器と並列に第１の逆止弁、冷媒液溜め
タンク、第２の逆止弁、冷媒加熱器を順次連結
し、かつ前記液溜めタンクと前記第２の逆止弁と
前記冷媒加熱器と並列に開閉弁を有するバイパス
管を設け、前記圧縮機吐出ラインにエゼクターを
設けて前記冷媒加熱器内の媒体を吸引する冷暖房
装置。 ２ 冷媒液溜めタンクは前記冷媒加熱器よりも高
い位置に設けた特許請求の範囲第１項記載の冷暖
房装置。[Claims] 1. Compressor, four-way valve, indoor heat exchanger, expansion device,
A refrigeration cycle is constructed from an outdoor heat exchanger, and a first check valve, a refrigerant liquid storage tank, a second check valve, and a refrigerant heater are sequentially connected in parallel with the indoor heat exchanger, and the liquid A heating and cooling system in which a bypass pipe having an on-off valve is provided in parallel with a reservoir tank, the second check valve, and the refrigerant heater, and an ejector is provided in the compressor discharge line to suck the medium in the refrigerant heater. 2. The heating and cooling apparatus according to claim 1, wherein the refrigerant reservoir tank is provided at a higher position than the refrigerant heater.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60251290A JPS62108967A (en) | 1985-11-08 | 1985-11-08 | Air conditioning equipment |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60251290A JPS62108967A (en) | 1985-11-08 | 1985-11-08 | Air conditioning equipment |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS62108967A JPS62108967A (en) | 1987-05-20 |
| JPH0439587B2 true JPH0439587B2 (en) | 1992-06-30 |
Family
ID=17220604
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP60251290A Granted JPS62108967A (en) | 1985-11-08 | 1985-11-08 | Air conditioning equipment |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS62108967A (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2538164Y2 (en) * | 1990-09-25 | 1997-06-11 | 横浜ゴム株式会社 | Golf club head |
-
1985
- 1985-11-08 JP JP60251290A patent/JPS62108967A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS62108967A (en) | 1987-05-20 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EXPY | Cancellation because of completion of term |