JPH0328677B2 - - Google Patents
Info
- Publication number
- JPH0328677B2 JPH0328677B2 JP13933085A JP13933085A JPH0328677B2 JP H0328677 B2 JPH0328677 B2 JP H0328677B2 JP 13933085 A JP13933085 A JP 13933085A JP 13933085 A JP13933085 A JP 13933085A JP H0328677 B2 JPH0328677 B2 JP H0328677B2
- Authority
- JP
- Japan
- Prior art keywords
- refrigerant
- heating
- heat exchanger
- evaporator
- 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 113
- 238000010438 heat treatment Methods 0.000 claims description 95
- 238000001816 cooling Methods 0.000 claims description 13
- 238000005057 refrigeration Methods 0.000 claims description 4
- 238000001704 evaporation Methods 0.000 claims description 2
- 230000008020 evaporation Effects 0.000 claims 1
- 239000007788 liquid Substances 0.000 description 13
- 238000010586 diagram Methods 0.000 description 4
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 238000004378 air conditioning Methods 0.000 description 2
- 238000005086 pumping Methods 0.000 description 2
- 230000007423 decrease Effects 0.000 description 1
- 238000005516 engineering process Methods 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
本発明は冷媒加熱蒸発器を有するヒートポンプ
式冷暖房装置、給湯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 and a hot water supply system having a refrigerant heating evaporator.
従来の技術
従来のこの種の冷房付加熱装置は第３図に示す
ように、加熱熱交換器３の中間に電気ヒータ６を
設けて、暖房運転時に加熱熱交換器３で凝縮した
一部または全部の冷媒を蒸発気化した後、さらに
前記加熱熱交換器３で再凝縮させて暖房能力確保
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、加熱熱
交換器３と並列に液冷媒を圧送するポンプ７と加
熱器８を持つ冷媒加熱装置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加熱熱交
換器３の中間位置に冷媒加熱器６を設けているの
で加熱熱交換器３が大型となるとともに電気ヒー
タ６の容量に制約を受けるという問題点を有して
いた。又、第４図のような構成では液冷媒を圧送
するポンプ７と加熱器８を持つ冷媒加熱装置９を
加熱熱交換器３と並列に設けているので、ポンプ
７から加熱器８への冷媒液送量と加熱器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, a conventional cooling additional heat device of this type is provided with an electric heater 6 in the middle of a heating heat exchanger 3 to absorb a portion of the heat that is condensed in the heating heat exchanger 3 during heating operation. After all the refrigerant has been evaporated, it is further condensed in the heating heat exchanger 3 to ensure heating capacity. (For example, Tokuko Sho 45-
Publication No. 38038). In addition, as shown in Fig. 4, a refrigerant heating device 9 having a pump 7 for pumping liquid refrigerant and a heater 8 is provided in parallel with the heating heat exchanger 3 to ensure heating capacity during heating operation. was. (For example, Japanese Utility Model Publication No. 50-37255) Problems to be Solved by the Invention However, in the configuration as shown in FIG. 3 is large in size, and the capacity of the electric heater 6 is limited. In addition, in the configuration shown in FIG. 4, a refrigerant heating device 9 having a pump 7 for pumping liquid refrigerant and a heater 8 is provided in parallel with the heating heat exchanger 3, so that the refrigerant from the pump 7 to the heater 8 is The balance between the amount of liquid fed and the amount of heating by the heater 8, controllability, 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房付加
熱装置は、圧縮機、四方弁、加熱熱交換器、減圧
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、前記加熱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の逆止弁と前記冷
媒液溜めタンクより低位置の冷媒加熱蒸発器を備
え、かつ前記冷媒液溜めタンクと前記第２の逆止
弁と前記冷媒加熱蒸発器と並列に開閉弁を具備す
るバイパス管を設けて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 cooling additional heat device of the present invention configures a refrigeration cycle from a compressor, a four-way valve, a heating heat exchanger, a pressure reduction device, and an outdoor heat exchanger. In addition, a first check valve, a refrigerant liquid reservoir tank, a second check valve, and a refrigerant heating evaporator located lower than the refrigerant liquid reservoir tank are provided in parallel with the heating heat exchanger, and the refrigerant liquid reservoir A refrigerant closed circuit is constructed by providing a bypass pipe equipped with an on-off valve in parallel with the tank, the second check valve, and the refrigerant heating evaporator.
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蒸発器の内圧
とバランスさせ、冷媒液溜めタンクと冷媒加熱蒸
発器のヘツド差で冷媒液溜めタンク内の液冷媒を
冷媒加熱蒸発器へ送り加熱して蒸発ガス化した冷
媒を加熱熱交換器へ送り被加熱側へ放熱して凝縮
液化させて冷媒液溜めタンクへ戻すシステムであ
る為、加熱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
ングコストも低減できる。According to the above-mentioned structure, the present invention balances the internal pressure of the refrigerant storage tank with the internal pressure of the refrigerant heating evaporator by opening the on-off valve, and the refrigerant storage is adjusted by the head difference between the refrigerant storage tank and the refrigerant heating evaporator. The system sends the liquid refrigerant in the tank to the refrigerant heating evaporator, heats it, and evaporates and gasifies the refrigerant, which sends the heat to the heating heat exchanger, radiates heat to the heated side, condenses and liquefies it, and returns it to the refrigerant storage tank. There is no need to add an electric heater to the heat exchanger, and no refrigerant pump is required, making it possible to downsize the equipment and reduce the initial cost and running cost of the refrigerant pump.
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、加熱運転と冷房運転の冷媒流れ方向を変
える。１２は加熱熱交換器であり、加熱運転時は
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は減圧装置、１４は室外熱交換器で
あり、加熱運転時に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１０、前
記四方弁１１、前記加熱熱交換器１２、前記減圧
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は冷媒加熱蒸
発器であり、前記冷媒液溜タンク１６より低位置
に設けられており、加熱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１
６と前記第２の逆止弁と前記冷媒加熱蒸発器１８
は順次連結されて前記加熱熱交換器１２と並列に
設けられており、冷媒の流れは前記加熱熱交換器
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１７、前記冷媒加熱
蒸発器１８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と前記冷媒加熱蒸発
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。 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 a heating heat exchanger, which condenses the refrigerant during heating operation and evaporates refrigerant during cooling operation. 13 is a pressure reducing 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. Further, the compressor 10, the four-way valve 11, the heating heat exchanger 12, the pressure reducing 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 heating evaporator, which is provided at a lower position than the refrigerant reservoir tank 16, When the capacity is insufficient, the heat source 19 evaporates and gasifies the refrigerant. or,
The first check valve 15 and the refrigerant reservoir tank 1
6, the second check valve, and the refrigerant heating evaporator 18
are sequentially connected and provided in parallel with the heating heat exchanger 12, and the refrigerant flows through the heating heat exchanger 12, the first check valve 15, the refrigerant reservoir tank 16, and the second The check valve 17 is configured to allow the refrigerant to flow in one direction in the refrigerant heating evaporator 18 . 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 heating evaporator 18.
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減圧装置
１３で減圧されて加熱熱交換器１２に流入し、被
冷却体（空気、水等）から熱を奪い蒸発ガス化し
て前記四方弁１１を通り前記圧縮機１０にもど
る。次に加熱運転時を述べる。最初に大気熱エン
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図の実線方向に流れ加熱
熱交換器１２に流入し被加熱媒体（空気、水等）
へ放熱して凝縮液化し、（この際に被加熱媒体が
空気であれば室内暖房、水であれば給湯装置に利
用する。）減圧装置１３に流入して減圧されて室
外熱交換器１４に流入し、大気熱を吸熱して蒸発
ガス化して前記四方弁１１を通り前記圧縮機１０
にもどる。又、大気熱エンタルピーが少なく加熱
能力が不足する場合には前記ヒートポンプ運転と
冷媒加熱蒸発器１８の冷媒加熱の併用運転するこ
とができ、この場合には加熱源１９をONし、冷
媒加熱蒸発器１８で高圧冷媒を加熱し蒸発ガス化
させて前記圧縮機１０で圧縮された高温高圧の冷
媒ガスと合流し加熱熱交換器１２に流入し、ここ
で放熱して凝縮液化させて減圧装置１３と冷媒液
溜めタンク１６に分流する。そして減圧装置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、前記冷媒溜めタ
ンク１６に流入した液冷媒は、圧力が前記冷媒加
熱蒸発機１８の圧力より低くなつているので開閉
弁２０を開とした時に前記液溜めタンク１６と前
記冷媒加熱蒸発器１８の圧力を等しくさせ、前記
冷媒液溜めタンク１６と前記冷媒加熱蒸発器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蒸発器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
Ｐ−ｉモリエル線図（Ｐ：圧力、ｉ：エンタルピ
ー）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
転時の加熱能力Q1は圧縮冷媒循環量GR1とすると
大気からの吸熱量QE＝GR1×△i1（△i1は室外熱交
換器１４入口、出口の冷媒エンタルピー差）、加
熱能力Q1＝GR1×△i2（△i2は加熱熱交換器１２入
口、出口の冷媒エンタルピー差）と表わせるのに
対しヒートポンプ運転と冷媒加熱蒸発器１８との
併用運転時には加熱能力ＱがＱ＝Q1＋Q2（Q2＝
GR2×△i2、GR2は冷媒液溜めタンク１６と冷媒加
熱蒸発器１８を循環する冷媒量）となりQ2だけ
向上する。次にさらに大気熱エンタルピーが小さ
くなり加熱能力が不足する場合には前記冷媒加熱
蒸発器１８、前記加熱熱交換器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、この場合には室外熱交換器１４で大気熱を
吸熱しないけれども、大気エンタルピーに関係な
く加熱能力が必要だけ取り出せる。いわゆる加熱
能力に必要分、加熱源１９をインプツトすればよ
い。従つて、必要な加熱能力（負荷）に応じて加
熱能力を取り出すことができる上に、加熱熱交換
器１２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と
いう効果がある。 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 pressure reducing device 13, flows into the heating heat exchanger 12, absorbs heat from the object to be cooled (air, water, etc.), evaporates and becomes gas, passes through the four-way valve 11, and Return to compressor 10. Next, the heating operation will be described. First, we will discuss the independent operation of the heat pump when 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 in the direction of the solid line in FIG.
(At this time, if the medium to be heated is air, it is used for indoor heating; if it is water, it is used for a hot water supply system.) It flows into the pressure reducing device 13, is depressurized, and is sent to the outdoor heat exchanger 14. The air flows into the compressor 10 after absorbing atmospheric heat, evaporating into gas, and passing through the four-way valve 11 to the compressor 10.
Return to In addition, when the atmospheric thermal enthalpy is low and the heating capacity is insufficient, the heat pump operation and the refrigerant heating of the refrigerant heating evaporator 18 can be operated in combination. In this case, the heating source 19 is turned on and the refrigerant heating evaporator At step 18, the high-pressure refrigerant is heated to evaporate and gasify, join with the high-temperature, high-pressure refrigerant gas compressed by the compressor 10, and flow into the heating heat exchanger 12, where it radiates heat, condenses and liquefies, and connects to the pressure reducing device 13. The refrigerant is diverted to the refrigerant reservoir tank 16. And pressure reducing device 13
The refrigerant flowing into the refrigerant absorbs atmospheric heat in the outdoor heat exchanger 14, evaporates into gas, and returns to the compressor 10, as in the case of the heat pump operation. On the other hand, since the pressure of the liquid refrigerant that has flowed into the refrigerant storage tank 16 is lower than the pressure of the refrigerant heating evaporator 18, when the on-off valve 20 is opened, the liquid refrigerant flows between the liquid refrigerant tank 16 and the refrigerant heating evaporator 18. The pressures of the refrigerant reservoir tank 16 and the refrigerant heating evaporator 18 are made equal.
The liquid refrigerant in the refrigerant storage tank 16 flows into the refrigerant heating evaporator 18 at a position difference of , and the refrigerant is heated by the heat source 19 and evaporated into gas. A P-i Mollier diagram (P: pressure, i: enthalpy) at that time is shown in FIG. In FIG. 2, the numbers in the figure are the same as those in FIG. The heating capacity Q1 when the heat pump is operated alone is the compressed refrigerant circulation amount G R1 , the amount of heat absorbed from the atmosphere Q E = G R1 × △i1 (△i1 is the refrigerant enthalpy difference between the inlet and outlet of the outdoor heat exchanger 14), heating capacity Q1=G R1 ×△i2 (△i2 is the refrigerant enthalpy difference between the inlet and outlet of the heating heat exchanger 12), whereas when the heat pump is operated in combination with the refrigerant heating evaporator 18, the heating capacity Q is Q=Q1+Q2 (Q2＝
G R2 ×△i2, G R2 is the amount of refrigerant circulating through the refrigerant storage tank 16 and the refrigerant heating evaporator 18), and is improved by Q2. Next, when the atmospheric heat enthalpy further decreases and the heating capacity is insufficient, the refrigerant heating operation can be performed in the refrigerant circuit of the refrigerant heating evaporator 18, the heating heat exchanger 12, and the refrigerant reservoir tank 16. In this case, Although the outdoor heat exchanger 14 does not absorb atmospheric heat, it can extract as much heating capacity as necessary regardless of the atmospheric enthalpy. The heating source 19 may be input in an amount necessary for the so-called heating capacity. Therefore, the heating capacity can be extracted according to the required heating capacity (load), and there is no need to add an electric heater to the heating heat exchanger 12.
Since a refrigerant pump is also not required, it has the effect of downsizing the equipment and reducing initial costs and running costs.
発明の効果
以上のように本発明の冷房付加熱装置によれば
次の効果が得られる。Effects of the Invention As described above, the cooling additional heat device of the present invention provides the following effects.
(1) 圧縮機、四方弁、加熱熱交換器、減圧装置、
室外熱交換器とから冷凍サイクルを構成すると
ともに、前記加熱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
熱蒸発器を備え、かつ、前記冷媒溜めタンクと
前記第２の逆止弁と前記冷媒加熱蒸発器と並列
に開閉弁を有するバイパス管を設け、前記冷媒
液溜めタンクの高さ位置を前記冷媒加熱蒸発器
より高くして冷媒密閉回路を構成しているの
で、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蒸発器
内の圧力を等しくさせ、前記冷媒液溜めタンク
と前記冷媒加熱蒸発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蒸発
器に流し、蒸発ガス化させて冷媒エンタルピー
を増加し、その熱量をヒートポンプサイクル側
の熱量に付加し加熱能力を増加させることがで
きる為に、加熱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, heating heat exchanger, pressure reducing device,
A refrigeration cycle is configured from an outdoor heat exchanger, and a first check valve, a refrigerant reservoir tank, a second check valve, and a refrigerant heating evaporator are provided in parallel with the heating heat exchanger, and the A bypass pipe having an on-off valve is provided in parallel with the refrigerant storage tank, the second check valve, and the refrigerant heating evaporator, and the height of the refrigerant storage tank is higher than the refrigerant heating evaporator to seal the refrigerant. Since the circuit is configured, by opening the on-off valve, the pressure in the refrigerant storage tank and the pressure in the refrigerant heating evaporator are equalized, and the pressure in the refrigerant storage tank and the refrigerant heating evaporator are equalized. The liquid refrigerant in the refrigerant storage tank flows into the refrigerant heating evaporator due to the difference in the position of the refrigerant, evaporates and gasifies it to increase the refrigerant enthalpy, and adds that amount of heat to the amount of heat on the heat pump cycle side to increase the heating capacity. Therefore, there is no need to add an electric heater to the heating heat exchanger, and there is no need to use a refrigerant pump, so it is possible to downsize the equipment and reduce initial costs and running costs.
(2) 大気熱エンタルピーが大きく、加熱負荷が小
さい場合には運転効率の良いヒートポンプサイ
クルで加熱運転を行ない、能力が加熱負荷より
少し不足する場合には、ヒートポンプ運転と冷
媒加熱蒸発器の併用運転で加熱能力不足を解消
し、さらに能力が加熱負荷よりも小さい場合に
は冷媒加熱蒸発器の運転で負荷を満足すること
ができ、運転効率の良い状態で絶えず負荷を満
足することができる。(2) When the atmospheric heat enthalpy is large and the heating load is small, a heat pump cycle with high operating efficiency is used for heating operation, and when the capacity is slightly less than the heating load, a combination of heat pump operation and refrigerant heating evaporator is operated. In addition, if the capacity is smaller than the heating load, the load can be satisfied by operating the refrigerant heating evaporator, and the load can be constantly satisfied with good operating efficiency.
第１図は本発明の一実施例における冷房付加熱
装置の冷媒回路図、第２図は圧力−エンタルピー
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……加
熱熱交換器、１３……減圧装置、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
媒加熱蒸発器、２０……開閉弁、２１……バイパ
ス管。
FIG. 1 is a refrigerant circuit diagram of a cooling additional heat device according to an embodiment of the present invention, FIG. 2 is a pressure-enthalpy diagram, and FIGS. 3 and 4 are refrigerant circuit diagrams of a conventional air-conditioning and heating device. 10... Compressor, 11... Four-way valve, 12... Heating heat exchanger, 13... Pressure reduction device, 14... Outdoor heat exchanger, 15... First check valve, 16... Refrigerant liquid reservoir Tank, 17...Second check valve, 18...Refrigerant heating evaporator, 20...Opening/closing valve, 21...Bypass pipe.
Claims (1)
用を行ない、冷房運転時に蒸発作用を行なう加熱
熱交換器、減圧装置、室外熱交換器とから冷凍サ
イクルを構成するとともに、前記加熱熱交換器と
並列に第１の逆止弁と冷媒液溜めタンクと第２の
逆止弁と冷媒加熱蒸発器を備え、かつ、前記冷媒
液溜めタンクと前記第２の逆止弁と前記冷媒加熱
蒸発器と並列に開閉弁を具備するバイパス管を設
けて冷媒密閉回路を構成した冷房付加熱装置。 ２ 冷媒液溜めタンクの高さ位置は前記冷媒加熱
蒸発器よりも高位置に設けて構成された特許請求
の範囲第１項記載の冷房付加熱装置。 ３ 冷房運転時は前記圧縮機、前記四方弁、前記
室外熱交換器、前記減圧装置、前記加熱熱交換器
とから構成される冷凍サイクル運転を行ない、加
熱運転時は前記圧縮機、前記四方弁、前記加熱熱
交換器、前記減圧装置、前記室外熱交換器とから
構成されるヒートポンプサイクル運転と、前記圧
縮機、前記四方弁、前記加熱熱交換器、前記減圧
装置、前記室外熱交換器と前記冷媒液溜めタン
ク、前記冷媒加熱蒸発器とから構成されるヒート
ポンプと冷媒加熱の併用運転と、前記加熱熱交換
器、前記冷媒液溜めタンク、前記冷媒加熱蒸発器
とから構成される冷媒加熱運転との運転制御を行
なう制御装置を備えた特許請求の範囲第１項記載
の冷房付加熱装置。[Scope of Claims] 1. A refrigeration cycle is constituted by a compressor, a four-way valve, a heating heat exchanger that performs a refrigerant condensing action during heating operation and an evaporation action during cooling operation, a pressure reduction device, and an outdoor heat exchanger. , comprising a first check valve, a refrigerant reservoir tank, a second check valve, and a refrigerant heating evaporator in parallel with the heating heat exchanger, and the refrigerant reservoir tank and the second check valve. and a cooling additional heat device in which a bypass pipe equipped with an on-off valve is provided in parallel with the refrigerant heating evaporator to form a refrigerant closed circuit. 2. The cooling additional heat device according to claim 1, wherein the refrigerant storage tank is provided at a height higher than the refrigerant heating evaporator. 3 During cooling operation, a refrigeration cycle operation consisting of the compressor, the four-way valve, the outdoor heat exchanger, the pressure reducing device, and the heating heat exchanger is performed, and during the heating operation, the compressor and the four-way valve are operated. , a heat pump cycle operation consisting of the heating heat exchanger, the pressure reducing device, and the outdoor heat exchanger; and the compressor, the four-way valve, the heating heat exchanger, the pressure reducing device, and the outdoor heat exchanger. A combined operation of a heat pump and refrigerant heating comprising the refrigerant storage tank and the refrigerant heating evaporator; and a refrigerant heating operation comprising the heating heat exchanger, the refrigerant storage tank and the refrigerant heating evaporator. The cooling additional heat device according to claim 1, further comprising a control device for controlling the operation of the air conditioner.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60139330A JPS62774A (en) | 1985-06-25 | 1985-06-25 | Cooling additional heat device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60139330A JPS62774A (en) | 1985-06-25 | 1985-06-25 | Cooling additional heat device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS62774A JPS62774A (en) | 1987-01-06 |
| JPH0328677B2 true JPH0328677B2 (en) | 1991-04-19 |
Family
ID=15242801
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP60139330A Granted JPS62774A (en) | 1985-06-25 | 1985-06-25 | Cooling additional heat device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS62774A (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2691347B2 (en) * | 1988-04-03 | 1997-12-17 | 日本合成化学工業株式会社 | Method for producing photosensitive resin and photosensitive resin composition |
-
1985
- 1985-06-25 JP JP60139330A patent/JPS62774A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS62774A (en) | 1987-01-06 |
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| EXPY | Cancellation because of completion of term |