JPH067028B2 - Heat pump type air conditioner - Google Patents
Heat pump type air conditionerInfo
- Publication number
- JPH067028B2 JPH067028B2 JP15912385A JP15912385A JPH067028B2 JP H067028 B2 JPH067028 B2 JP H067028B2 JP 15912385 A JP15912385 A JP 15912385A JP 15912385 A JP15912385 A JP 15912385A JP H067028 B2 JPH067028 B2 JP H067028B2
- Authority
- JP
- Japan
- Prior art keywords
- refrigerant
- heat exchanger
- heating
- cooling
- expansion valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Landscapes
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Description
【発明の詳細な説明】 (イ)産業上の利用分野 本発明は空気調和機として利用されるヒートポンプ式冷
暖房装置に関する。The present invention relates to a heat pump type cooling and heating apparatus used as an air conditioner.
(ロ)従来の技術 ヒートポンプ式冷暖房装置において、暖房運転時に室外
側熱交換器が凍結しないように凍結防止用の熱交換器を
用いると共に、外気温の低下に伴ない室外側熱交換器で
冷媒が充分に蒸発しきれなくなって圧縮機に液冷媒が戻
ってしまうのでこれを防止する為に冷媒容器の液面変位
箇所と冷媒容器の下部とに暖房用毛細管を接続したもの
が特公昭58−21188号公報で開示されている。(B) Conventional technology In a heat pump type cooling and heating device, a heat exchanger for freezing is used to prevent the outdoor heat exchanger from freezing during heating operation, and the refrigerant is used in the outdoor heat exchanger as the outside air temperature decreases. However, the liquid refrigerant returns to the compressor because it cannot fully evaporate, and in order to prevent this, the one in which a heating capillary tube is connected to the liquid level displacement portion of the refrigerant container and the lower portion of the refrigerant container is Japanese Patent Publication No. 58- No. 21188 is disclosed.
(ハ)発明が解決しようとする問題点 暖房時に凍結防止用の熱交換器に導く冷媒量はこの熱交
換器での損失熱量を最小限に抑える為に室外側熱交換器
が凍結しない程度に、且つ圧縮機に液冷媒が戻らない程
度に設定されるのが好ましいが、暖房用毛細管の抵抗設
定でこれに対応するのは極めて困難であった。(C) Problems to be solved by the invention The amount of refrigerant introduced to the heat exchanger for freeze prevention during heating should be such that the outdoor heat exchanger does not freeze in order to minimize the amount of heat loss in this heat exchanger. It is preferable that the liquid refrigerant is not returned to the compressor, but it is extremely difficult to cope with this by setting the resistance of the heating capillary tube.
又、凍結防止用の熱交換器は冷房時に凝縮器として作用
するにとどまり、暖房時のように過冷却コイルとして作
用しない為、安定した冷媒減圧制御が行なえない問題点
を有していた。Further, the heat exchanger for freeze prevention functions only as a condenser during cooling, and does not function as a supercooling coil like during heating, so that there is a problem that stable refrigerant pressure reduction control cannot be performed.
本発明はかかる問題点を解決したヒートポンプ式冷暖房
装置を提供するものである。The present invention provides a heat pump type cooling and heating device that solves the above problems.
(ニ)問題点を解決するための手段 圧縮機、冷暖流路切換用の四方弁、室内側熱交換器、冷
媒容器、冷媒減圧素子、室外側熱交換器を順次環状に連
結してヒートポンプ式冷凍サイクルを構成する冷暖房装
置において、冷媒減圧素子として圧縮機の吸込冷媒の状
態を検出して動作する冷暖房用の膨張弁と、冷房用毛細
管と、暖房用毛細管とを使用すると共に室外側熱交換器
と熱交換関係に補助熱交換器を配設して、前記冷媒容器
の下部から導出される液冷媒がこの補助熱交換器を介し
て膨張弁と冷房用毛細管とに並流される冷房サイクル
と、この冷媒容器の下部から導出される液冷媒が前記補
助熱交換器を介して膨張弁に導かれると共に冷媒容器の
液面変位箇所から導出される冷媒が暖房用毛細管に導か
れる暖房サイクルとを形成したものである。(D) Means for solving the problems A heat pump type in which a compressor, a four-way valve for switching the cooling / heating flow path, an indoor heat exchanger, a refrigerant container, a refrigerant pressure reducing element, and an outdoor heat exchanger are sequentially connected in an annular shape. In a cooling and heating device that constitutes a refrigeration cycle, an expansion and cooling valve for cooling and heating that operates by detecting the state of the suction refrigerant of the compressor as a refrigerant pressure reducing element, a cooling capillary tube, and a heating capillary tube are used, and outdoor heat exchange is also used. And a cooling cycle in which an auxiliary heat exchanger is arranged in a heat exchange relationship with the heat exchanger, and the liquid refrigerant drawn out from the lower portion of the refrigerant container flows in parallel to the expansion valve and the cooling capillary tube via the auxiliary heat exchanger. , A heating cycle in which the liquid refrigerant derived from the lower portion of the refrigerant container is guided to the expansion valve via the auxiliary heat exchanger and the refrigerant derived from the liquid level displacement portion of the refrigerant container is guided to the heating capillary tube. Is formed
(ホ)作用 暖房運転時は室内側熱交換器が凝縮器として、室外側熱
交換器が蒸発器として作用し、通常運転時における冷媒
流量は暖房用毛細管で主に制御されると共に膨張弁でそ
の不足分を補う程度に制御される。外気温度が高く暖房
能力が充分に出る時は室外側熱交換器で充分冷媒過熱度
がとれる為、膨張弁が最大に開かれて補助熱交換器に冷
媒が多く流れ、高圧圧力の上昇が抑えられる。外気温度
が低くなるとこれに伴ない膨張弁の開度が小さくなって
補助熱交換器を流れる高圧液冷媒が減少し、損失熱量が
最小限に抑えられる。更に、外気温度が低下して冷媒容
器内の液面が下がり暖房用毛細管に液冷媒が流れなくな
ると膨張弁による冷媒制御のみとなり、室外側熱交換器
の冷媒過熱度が一定に維持される。(E) Action During heating operation, the indoor heat exchanger acts as a condenser and the outdoor heat exchanger acts as an evaporator, and the refrigerant flow rate during normal operation is mainly controlled by the heating capillary tube and the expansion valve. It is controlled to compensate for the shortage. When the outside air temperature is high and the heating capacity is sufficient, the outdoor heat exchanger can provide sufficient refrigerant superheat, so the expansion valve is opened to the maximum and a large amount of refrigerant flows to the auxiliary heat exchanger, suppressing an increase in high pressure. To be When the outside air temperature becomes lower, the opening degree of the expansion valve becomes smaller accordingly, the high-pressure liquid refrigerant flowing through the auxiliary heat exchanger decreases, and the amount of heat loss is minimized. Further, when the outside air temperature is lowered and the liquid level in the refrigerant container is lowered to stop the liquid refrigerant from flowing into the heating capillaries, only the refrigerant control by the expansion valve is performed and the refrigerant superheat degree of the outdoor heat exchanger is maintained constant.
又、冷房運転時は室外側熱交換器が凝縮器として、室内
側熱交換器が蒸発器として作用すると共に補助熱交換器
は冷媒容器から導出される液冷媒のみが流れて過冷却コ
イルとして作用し、過冷却された冷媒は膨張弁と冷房用
毛細管とを並流する際、安定した液状態で減圧制御され
る。Also, during cooling operation, the outdoor heat exchanger acts as a condenser, the indoor heat exchanger acts as an evaporator, and the auxiliary heat exchanger acts as a supercooling coil because only the liquid refrigerant drawn from the refrigerant container flows. When the supercooled refrigerant flows in parallel with the expansion valve and the cooling capillary tube, the decompression control is performed in a stable liquid state.
(ヘ)実施例 本発明の実施例を図面に基づいて説明すると、(1)は圧
縮機、(2)は冷暖流路切換用の四方弁、(3)は室内側熱交
換器、(4)は冷媒容器、(5)は室外側熱交換器、(6)はこ
の室外側熱交換器の下部に熱交換関係に配設された補助
熱交換器である。(F) Example An example of the present invention will be described with reference to the drawings. (1) is a compressor, (2) is a four-way valve for switching the heating / cooling flow path, (3) is an indoor heat exchanger, and (4) ) Is a refrigerant container, (5) is an outdoor heat exchanger, and (6) is an auxiliary heat exchanger disposed in a heat exchange relationship below the outdoor heat exchanger.
そして、冷媒減圧素子として、感温素子(7)と均圧管(8)
を気液分離器(9)の冷媒入口側に設けることにより圧縮
機(1)の吸込冷媒の状態を検出して動作する冷暖房用の
温度式自動膨張弁(10)と、冷房サイクル時に膨張弁(10)
と並流される冷媒を減圧する冷房用毛細管(11)と、冷媒
容器(4)の液面変位箇所(12)と室外側熱交換器(5)との間
に介在される暖房用毛細管(13)とが使用されており、冷
房サイクル時に膨張弁(10)と冷房用毛細管(11)とに冷媒
が並流され、且つ暖房サイクル時に膨張弁(10)と暖房用
毛細管(13)とに冷媒が並流されるように4個の逆止弁(1
4)(15)(16)(17)が設けられている。Then, as a refrigerant pressure reducing element, a temperature sensing element (7) and a pressure equalizing tube (8)
By installing on the refrigerant inlet side of the gas-liquid separator (9), the temperature type automatic expansion valve for cooling and heating that operates by detecting the state of the suction refrigerant of the compressor (1) and the expansion valve during the cooling cycle (Ten)
A cooling capillary tube (11) for decompressing the refrigerant flowing in parallel with the heating capillary tube (13) interposed between the liquid level displacement portion (12) of the refrigerant container (4) and the outdoor heat exchanger (5). ) Is used, the refrigerant is co-flowed to the expansion valve (10) and the cooling capillary tube (11) during the cooling cycle, and the refrigerant is added to the expansion valve (10) and the heating capillary tube (13) during the heating cycle. 4 check valves (1
4) (15) (16) (17) are provided.
併せて、補助熱交換器(6)は冷暖房の何れの運転におい
ても、冷媒容器(4)の下部から導出される高圧液冷媒を
外気と熱交換させて過冷却させる過冷却コイルとして作
用し、特に暖房運転時においては室外側熱交換器(5)の
下部が凍結するのを防止する凍結防止コイルとしても作
用するようになっている。Together, the auxiliary heat exchanger (6) acts as a supercooling coil for supercooling by exchanging heat between the high pressure liquid refrigerant drawn from the lower part of the refrigerant container (4) and the outside air in any operation of cooling and heating, In particular, during heating operation, it also acts as a freeze prevention coil that prevents the lower part of the outdoor heat exchanger (5) from freezing.
以上の如く構成されており、先づ暖房運転について説明
する。通常運転時では冷媒容器(4)内に液冷媒が多量に
溜まり込むように冷媒充填量が設定されていると共に冷
媒流量を暖房用毛細管(13)で主に制御し膨張弁(10)でそ
の不足分を補う程度に制御するように設定してあるの
で、圧縮機(1)からの吐出冷媒は実線状態にある四方弁
(2)−室内側熱交換器(3)−逆止弁(14)−冷媒容器(4)を
経た後、冷媒容器(4)の液面変位箇所(12)から多量の高
圧液冷媒が導出されて暖房用毛細管(13)で減圧されると
共に冷媒容器(4)の下部から導出される少量の高圧液冷
媒は補助熱交換器(6)で外気と熱交換して過冷却された
後、膨張弁(10)で減圧される。そしてこの減圧された液
冷媒は暖房用毛細管(13)で減圧された液冷媒と逆止弁(1
5)を出た後、合流し、その後、室外側熱交換器(5)に流
入して蒸発気化し、四方弁(2)−気液分離器(9)を経て圧
縮機(1)に帰還される。かかる暖房サイクルにより、凝
縮器として作用する室内側熱交換器(3)で室内が暖房さ
れ、且つ、この暖房運転中、室外側熱交換器(5)の下部
は補助熱交換器(6)から放出される顕熱によって加熱さ
れる。The heating operation is configured as described above, and the heating operation will be described first. During normal operation, the refrigerant filling amount is set so that a large amount of liquid refrigerant accumulates in the refrigerant container (4), and the refrigerant flow rate is mainly controlled by the heating capillary tube (13) and the expansion valve (10) Since the control is set to compensate for the shortage, the refrigerant discharged from the compressor (1) is a four-way valve in a solid line.
(2) -Indoor heat exchanger (3) -Check valve (14) -After passing through the refrigerant container (4), a large amount of high-pressure liquid refrigerant is discharged from the liquid level displacement point (12) of the refrigerant container (4). After being decompressed by the heating capillary tube (13) and a small amount of high-pressure liquid refrigerant discharged from the lower part of the refrigerant container (4) is supercooled by exchanging heat with the outside air in the auxiliary heat exchanger (6), The pressure is reduced by the expansion valve (10). The depressurized liquid refrigerant and the check valve (1) are decompressed by the heating capillary tube (13).
After exiting 5), they merge and then flow into the outdoor heat exchanger (5) to evaporate and vaporize, and then return to the compressor (1) via the four-way valve (2) -gas-liquid separator (9). To be done. By such a heating cycle, the room is heated by the indoor heat exchanger (3) acting as a condenser, and during this heating operation, the lower part of the outdoor heat exchanger (5) is separated from the auxiliary heat exchanger (6). It is heated by the sensible heat released.
特に、外気温度が高く室外側熱交換器(5)で冷媒が充分
に蒸発気化して冷媒過熱度を充分とれる状態では膨張弁
(10)が最大に開いて補助熱交換器(6)には冷媒が多く流
れるようになるので、室外へ排出される顕熱量が多くな
って室内側熱交換器(3)での加熱量が減少する為、サー
モサイクルによる圧縮機(1)の発停回数が減少すると共
に高圧圧力が低下して動力消費量が少なく抑えられる。Especially when the outside air temperature is high and the refrigerant is sufficiently vaporized in the outdoor heat exchanger (5) and the degree of refrigerant superheat is sufficient, the expansion valve
Since (10) opens to the maximum and a large amount of refrigerant flows to the auxiliary heat exchanger (6), the amount of sensible heat discharged to the outside increases and the heating amount in the indoor heat exchanger (3) increases. Because of the decrease, the number of times the compressor (1) is started and stopped by the thermocycle is reduced, and the high pressure is reduced, so that the power consumption can be suppressed to be small.
一方、外気温度が低く室外側熱交換器(5)での蒸発能力
が減少して冷媒過熱度が小さくなると膨張弁(10)は徐々
に閉じて補助熱交換器(6)に流入する高圧液冷媒が減少
し、損失熱量が最小限に抑えられる。On the other hand, when the outside air temperature is low and the evaporation capacity in the outdoor heat exchanger (5) decreases and the refrigerant superheat degree decreases, the expansion valve (10) gradually closes and the high-pressure liquid flowing into the auxiliary heat exchanger (6). Refrigerant is reduced and the amount of heat loss is minimized.
更に外気温度が低下して液冷媒が気液分離器(9)に溜ま
り込むことにより冷媒容器(4)内の冷媒の液面(18)が液
面変位箇所(12)より下がって暖房用毛細管(13)に液冷媒
が供給されなくなると膨張弁(10)のみによる冷媒減圧制
御に切り換って冷媒過熱度を一定に保つ安定した運転状
態が維持される。When the outside air temperature further decreases and the liquid refrigerant accumulates in the gas-liquid separator (9), the liquid level (18) of the refrigerant in the refrigerant container (4) drops below the liquid level displacement point (12) and the heating capillary tube When the liquid refrigerant is no longer supplied to (13), it is switched to refrigerant pressure reduction control by only the expansion valve (10), and a stable operating state in which the refrigerant superheat degree is kept constant is maintained.
このように暖房運転時、外気温度の低下に伴なって暖房
用毛細管(13)と膨張弁(10)とによる冷媒制御から膨張弁
(10)のみによる冷媒制御に切り換わるが、この暖房運転
中は膨張弁(10)により常時、液冷媒が補助熱交換器(6)
を流れているので、この熱交換器から放出される顕熱で
室外側熱交換器(5)の下部は加熱されて凍結が防止さ
れ、且つ膨張弁(10)は補助熱交換器(6)で過冷却された
液冷媒を導入することにより安定した減圧制御が行なわ
れる。In this way, during heating operation, the expansion valve is changed from the refrigerant control by the heating capillary tube (13) and the expansion valve (10) as the outside air temperature decreases.
Switching to refrigerant control by (10) only, during this heating operation, the expansion valve (10) always keeps the liquid refrigerant in the auxiliary heat exchanger (6).
Flow through the heat exchanger, the lower part of the outdoor heat exchanger (5) is heated by the sensible heat released from this heat exchanger to prevent freezing, and the expansion valve (10) is connected to the auxiliary heat exchanger (6). Stable depressurization control is performed by introducing the supercooled liquid refrigerant.
又、冷房運転時は四方弁(2)を破線状態に切り換えるこ
とにより、圧縮機(1)からの吐出冷媒は四方弁(2)−室外
側熱交換器(5)−逆止弁(16)−冷媒容器(4)−補助熱交換
器(6)を流れた後、分配されて多量の液冷媒が冷房用毛
細管(11)を、小量の液冷媒が膨張弁(10)と逆止弁(17)と
を流れ、その後合流して室内側熱交換器(3)−四方弁(2)
−気液分離器(9)を経て圧縮機(1)に帰還される。かかる
冷房サイクルにより、蒸発器として作用する室内側熱交
換器(3)で室内が冷房され、且つこの運転中は補助熱交
換器(6)で冷媒容器(4)からの高圧液冷媒が過冷却される
ことにより冷房用毛細管(11)と膨張弁(10)を並流する液
冷媒はフラッシュガス分を含まない安定した液状態で減
圧制御されている。Also, during cooling operation, by switching the four-way valve (2) to the broken line state, the refrigerant discharged from the compressor (1) is four-way valve (2) -outdoor heat exchanger (5) -check valve (16). -Refrigerant container (4) -After flowing through the auxiliary heat exchanger (6), a large amount of the distributed liquid refrigerant flows through the cooling capillaries (11), and a small amount of the liquid refrigerant flows through the expansion valve (10) and the check valve. (17) and then merge into the indoor heat exchanger (3) -four-way valve (2)
-Returned to the compressor (1) via the gas-liquid separator (9). By such a cooling cycle, the room is cooled by the indoor heat exchanger (3) acting as an evaporator, and during this operation, the auxiliary heat exchanger (6) supercools the high-pressure liquid refrigerant from the refrigerant container (4). As a result, the pressure of the liquid refrigerant flowing in the cooling capillary tube (11) and the expansion valve (10) in parallel is controlled under reduced pressure in a stable liquid state containing no flash gas.
尚、上記実施例において、感温素子(7)と均圧管(8)を有
する温度式自動膨張弁(10)を用いたが、この代わりに圧
縮機(1)の吸込冷媒の温度を検出してモータが駆動する
電動式膨張弁やヒータが発熱する熱電式膨張弁を用いて
も良い。In the above embodiment, the temperature type automatic expansion valve (10) having the temperature sensing element (7) and the pressure equalizing pipe (8) was used, but instead of this, the temperature of the suction refrigerant of the compressor (1) was detected. An electric expansion valve driven by a motor or a thermoelectric expansion valve generated by a heater may be used.
(ト)発明の効果 本発明によれば、暖房運転時には暖房用毛細管が、冷房
運転時には冷房用毛細管が夫々主となって冷媒流量を制
御しているので、膨張弁はその不足分を補う程度の小容
量のもので良く、製造コストを割安にすることができ
る。(G) Effect of the Invention According to the present invention, the heating capillaries during the heating operation and the cooling capillaries mainly during the cooling operation mainly control the refrigerant flow rate, so that the expansion valve compensates for the shortage. With a small capacity, the manufacturing cost can be reduced.
併せて、冷暖房運転時の何れにおいても補助熱交換器が
過冷却コイルとして作用する為、膨張弁にはフラッシュ
ガスを含まない液冷媒が常に流れて安定した減圧制御が
行なわれ、効率の良い冷暖房運転を行なうことができ
る。In addition, since the auxiliary heat exchanger acts as a supercooling coil during any heating / cooling operation, liquid refrigerant that does not contain flash gas always flows through the expansion valve to perform stable pressure reduction control, resulting in efficient cooling / heating. You can drive.
しかも、暖房運転時において、外気温が高い時は膨張弁
が最大に開かれて高圧圧力の上昇を抑え、外気温度が低
くなると膨張弁の開度が小さくなって補助熱交換器での
損失熱量を最小限に抑え、更に外気温度が低下して冷媒
容器内の液面が下がると暖房用毛細管で冷媒が減圧され
なくなって膨張弁による冷媒制御のみに自動的に切り換
わる、といった具合に外気温度の変化に対応しながら室
外側熱交換器の凍結と圧縮機への液戻りを防止した幅広
い運転制御を行なうことができる。Moreover, during heating operation, when the outside air temperature is high, the expansion valve is opened to the maximum to suppress the rise in high pressure, and when the outside air temperature is decreased, the opening of the expansion valve becomes smaller and the amount of heat loss in the auxiliary heat exchanger is reduced. When the outside air temperature further decreases and the liquid level in the refrigerant container drops, the refrigerant is not decompressed in the heating capillary tube and only the refrigerant control by the expansion valve is automatically switched to the outside air temperature. It is possible to perform a wide range of operation control that prevents freezing of the outdoor heat exchanger and liquid return to the compressor while responding to changes in
図面は本発明の実施例を示すヒートポンプ式冷暖房装置
の冷媒回路図である。 (1)…圧縮機、(2)…四方弁、(3)…室内側熱交換器、(4)
…冷媒容器、(5)…室外側熱交換器、(6)…補助熱交換
器、(10)…膨張弁、(11)…冷房用毛細管、(12)…液面変
位箇所、(13)…暖房用毛細管。Drawing is a refrigerant circuit diagram of a heat pump type air conditioner which shows an example of the present invention. (1) ... Compressor, (2) ... Four-way valve, (3) ... Indoor heat exchanger, (4)
... Refrigerant container, (5) ... Outdoor heat exchanger, (6) ... Auxiliary heat exchanger, (10) ... Expansion valve, (11) ... Cooling capillary tube, (12) ... Liquid level displacement location, (13) … Heating capillaries.
───────────────────────────────────────────────────── フロントページの続き (56)参考文献 特開 昭59−71961(JP,A) 特開 昭61−101762(JP,A) 特開 昭61−15051(JP,A) ─────────────────────────────────────────────────── ─── Continuation of front page (56) Reference JP-A-59-71961 (JP, A) JP-A-61-101762 (JP, A) JP-A-61-15051 (JP, A)
Claims (1)
熱交換器、冷媒容器、冷媒減圧素子、室外側熱交換器を
順次環状に連結してヒートポンプ式冷凍サイクルを構成
したものにおいて、冷媒減圧素子として圧縮機の吸込冷
媒の状態を検出して動作する冷暖房用の膨張弁と、冷房
用毛細管と、暖房用毛細管とを使用すると共に室外側熱
交換器と熱交換関係に補助熱交換器を配設して、前記冷
媒容器の下部から導出される液冷媒がこの補助熱交換器
を介して膨張弁と冷房用毛細管とに並流される冷房サイ
クルと、この冷媒容器の下部から導出される液冷媒が前
記補助熱交換器を介して膨張弁に導かれると共にこの冷
媒容器の液面変位箇所から導出される冷媒が暖房用毛細
管に導かれる暖房サイクルとを形成したことを特徴とす
るヒートポンプ式冷暖房装置。1. A heat pump type refrigeration cycle in which a compressor, a four-way valve for switching cooling / heating channels, an indoor heat exchanger, a refrigerant container, a refrigerant pressure reducing element, and an outdoor heat exchanger are sequentially connected in an annular shape. In, using the expansion valve for cooling and heating that operates by detecting the state of the suction refrigerant of the compressor as the refrigerant decompression element, the cooling capillary tube, and the heating capillary tube, and assist in the heat exchange relationship with the outdoor heat exchanger. A cooling cycle in which a heat exchanger is provided and the liquid refrigerant led out from the lower portion of the refrigerant container flows in parallel to the expansion valve and the cooling capillary tube via the auxiliary heat exchanger, and from the lower portion of the refrigerant container The liquid refrigerant to be led out is guided to the expansion valve through the auxiliary heat exchanger, and the refrigerant to be led out from the liquid level displacement portion of the refrigerant container forms a heating cycle in which it is led to the heating capillary tube. Heat pump type Heating.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15912385A JPH067028B2 (en) | 1985-07-18 | 1985-07-18 | Heat pump type air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15912385A JPH067028B2 (en) | 1985-07-18 | 1985-07-18 | Heat pump type air conditioner |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6219659A JPS6219659A (en) | 1987-01-28 |
| JPH067028B2 true JPH067028B2 (en) | 1994-01-26 |
Family
ID=15686735
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP15912385A Expired - Lifetime JPH067028B2 (en) | 1985-07-18 | 1985-07-18 | Heat pump type air conditioner |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH067028B2 (en) |
-
1985
- 1985-07-18 JP JP15912385A patent/JPH067028B2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6219659A (en) | 1987-01-28 |
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