JPH02173366A - Twine type compressing device - Google Patents
Twine type compressing deviceInfo
- Publication number
- JPH02173366A JPH02173366A JP32727388A JP32727388A JPH02173366A JP H02173366 A JPH02173366 A JP H02173366A JP 32727388 A JP32727388 A JP 32727388A JP 32727388 A JP32727388 A JP 32727388A JP H02173366 A JPH02173366 A JP H02173366A
- Authority
- JP
- Japan
- Prior art keywords
- compressor
- oil
- compressors
- pipe
- suction pipe
- 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.)
- Granted
Links
- 230000006835 compression Effects 0.000 claims abstract description 21
- 238000007906 compression Methods 0.000 claims abstract description 21
- 238000000034 method Methods 0.000 abstract 1
- 238000005461 lubrication Methods 0.000 description 3
- 239000003507 refrigerant Substances 0.000 description 3
- 239000000470 constituent Substances 0.000 description 2
- 230000006866 deterioration Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Landscapes
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
Description
【発明の詳細な説明】
（産業上の利用分野）
本発明は、主としてビルなどの空調に使用されるツイン
形圧縮装置に関する。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a twin-type compression device mainly used for air conditioning of buildings and the like.
（従来の技術）
従来、この種ツイン形圧縮装置は、例えば実開昭５９−
８１７９１号公報に記載され、かつ、第４図に示したご
とく、底部に油溜（０）をもつ密閉ケーシング（Ｃ）内
に、モータ（Ｍ）と圧縮要素（ＣＦ）とを組込んだ２つ
の第１及び第２圧縮機（ＣＰＩ）（ＣＦ２）を備え、こ
れら各圧縮機（ＣＰＩ）（ＣＦ２）の各ケーシング（Ｃ
）に、それぞれ吸入管（Ｔ）から分岐された第１及び第
２分岐管（Ｔｌ）（Ｔ２）を接続すると共に、前記各ケ
ーシング（Ｃ）の下部間を均油管（ＯＴ）で相互に連通
させ、該均油管（ＯＴ）で前記各ケンング（Ｃ）内の圧
力差によって発生する油量のアンバランスを是正するよ
うにしている。(Prior art) Conventionally, this type of twin-type compression device has been developed, for example, by
As described in Japanese Patent No. 81791 and shown in Fig. 4, a motor (M) and a compression element (CF) are assembled in a sealed casing (C) having an oil reservoir (0) at the bottom. the first and second compressors (CPI) (CF2), each casing (C
) are connected to the first and second branch pipes (Tl) (T2) branched from the suction pipe (T), respectively, and the lower portions of each of the casings (C) are communicated with each other by an oil equalizing pipe (OT). The oil equalizing pipe (OT) corrects the imbalance in the amount of oil caused by the pressure difference in each of the Kengs (C).
（発明が解決しようとする課題）
所で、以上のツイン形圧縮装置では、前記各圧縮機（Ｃ
ＰＩ）（ＣＦ２）の分担能力に差異を設け、負荷変動に
対応して最適な運転を行うのが通常であるが、斯かる場
合に、高能力運転が行われる例えば第１圧縮機（ＣＰＩ
）側では、その圧縮要素（ＣＦ）への吸入量の増大に伴
いケーシング（Ｃ）の内部圧力が相対的に低下され、逆
に低能力運転が行われる第２圧縮機（ＣＦ２）側では、
その圧縮要素（ＣＦ）への吸入量の減少に伴いケーシン
グ（Ｃ）の内部圧力が相対的に高められることになり、
この結果、前記各ケーシング（Ｃ）間には、若干の高低
差圧が付与される。このため、前記均油管（ＯＴ）は、
本来の油量バランスの是正手段として適正に機能せす、
この均油管（ＯＴ）を介して、内部圧力が高い低能力側
の第２圧縮機（ＣＦ２）から、内部圧力が低い高能力側
の第１圧縮機（ＣＰＩ）へと油の移動が行われ、前記各
圧縮機（ＣＰＩ）（ＣＦ２）に油量のアンバランスが発
生することになる。従って、前記第２圧縮機（ＣＦ２）
側では、油切れを起こして潤滑性能を損なう虞れがあり
、また、前記第１圧縮機（ＣＰＩ）側では、過剰給油と
なって油圧縮を行ったりするなとの問題を招いたのであ
る。(Problem to be Solved by the Invention) However, in the above twin compressor, each of the compressors (C
It is normal to differentiate the shared capacities of the PI) (CF2) and perform optimal operation in response to load fluctuations, but in such a case, for example, the first compressor (CPI)
) side, the internal pressure of the casing (C) is relatively reduced as the suction amount to the compression element (CF) increases, and conversely, on the second compressor (CF2) side where low capacity operation is performed,
As the amount of suction into the compression element (CF) decreases, the internal pressure of the casing (C) becomes relatively high.
As a result, a slight differential pressure between the casings (C) is applied between the casings (C). Therefore, the oil equalizing pipe (OT) is
It functions properly as a means of correcting the original oil quantity balance.
Via this oil equalizing pipe (OT), oil is transferred from the second compressor (CF2) on the low capacity side, where the internal pressure is high, to the first compressor (CPI) on the high capacity side, where the internal pressure is low. , an imbalance in the amount of oil will occur in each of the compressors (CPI) (CF2). Therefore, the second compressor (CF2)
On the side, there is a risk of running out of oil and impairing lubrication performance, and on the side of the first compressor (CPI), excessive oil supply may occur, causing problems such as not performing oil compression. .
本発明は以上のような問題に鑑みてなしたもので、その
目的は、各圧縮機間の油量バランスを適正に保持できて
、潤滑性能の低下や過剰給油による油圧縮なとの問題を
なくすことができるツイン形圧縮装置を提供することに
ある。The present invention was made in view of the above-mentioned problems, and its purpose is to maintain an appropriate oil balance between each compressor, thereby eliminating problems such as deterioration of lubrication performance and oil compression due to excessive oil supply. An object of the present invention is to provide a twin-type compression device that can be eliminated.
（課題を解決するための手段）
上記目的を達成するために、本発明では、密閉ケーシン
グ（Ｃ）にモータ（Ｍ）と圧縮要素（ＣＦ）とを内装し
た第１圧縮機（１）と第２圧縮機（２）とを備え、該冬
用縮機（１）（２）間に均油管（６）を接続したツイン
形圧縮装置において、前記第１及び第２圧縮機（１）（
２）をインバータ制御により能力調節可能に構成すると
共に、負荷変化に追従させて常時前記第１圧縮機（１）
を第２圧縮機（２）よりも低い周波数で運転する運転制
御手段（７）と、吐出管（５）に流出された油を、高周
波数側の第２圧縮機（２）よりも低周波数側の第１圧縮
機（１）に多く戻す油戻し機構（８）とを設けたもので
ある。(Means for Solving the Problem) In order to achieve the above object, the present invention provides a first compressor (1) in which a motor (M) and a compression element (CF) are housed in a sealed casing (C); In a twin type compression device comprising two compressors (2) and an oil equalizing pipe (6) connected between the winter compressors (1) and (2), the first and second compressors (1) (
2) is configured such that its capacity can be adjusted by inverter control, and the first compressor (1) is always configured to follow load changes.
an operation control means (7) for operating the oil at a lower frequency than that of the second compressor (2); A return mechanism (8) is provided to return a large amount of oil to the first compressor (1) on the side.
前記油戻し機構（８）は、第２圧縮機（２）に接続する
第２吸入管（４）の端部（４ａ）を、第１圧縮機（１）
に接続する第１吸入管（３）の途中であって該吸入管（
３）の管内壁（３ａ）よりも内方側に突出状に接続して
構成される。The oil return mechanism (8) connects the end (4a) of the second suction pipe (4) connected to the second compressor (2) to the first compressor (1).
In the middle of the first suction pipe (3) connected to the suction pipe (
3) is connected in a protruding manner inwardly from the tube inner wall (3a).
（作用）
以」二のツイン形圧縮装置では、前記運転制御手段（７
）により前記第１圧縮機（１）が第２圧縮機（２）より
も常に低い周波数で運転され、換言すれば、第１圧縮機
（１）が第２圧縮機（２）に対し常に内部圧力大に保持
され、また、前記油戻し機構（８）により前記第２圧縮
機（２）に対し内部圧力が大の第１圧縮機（１）側に多
量の油が戻されるのであり、従って、前記均油管（６）
を介して第１圧縮機（１）から第２圧縮機（２）側に常
時部が移動され、各圧縮機（１）（２）間の油面高さが
均一化されるのである。(Function) In the second twin type compressor, the operation control means (7)
), the first compressor (1) is always operated at a lower frequency than the second compressor (2), in other words, the first compressor (1) is always operated at a lower frequency than the second compressor (2). The pressure is kept high, and a large amount of oil is returned by the oil return mechanism (8) to the first compressor (1), which has a high internal pressure, with respect to the second compressor (2). , the oil equalizing pipe (6)
The oil level is constantly moved from the first compressor (1) to the second compressor (2) via the compressor, thereby equalizing the oil level between the compressors (1) and (2).
また、前記油戻し機構（８）の構成手段として、前記第
２圧縮機（２）に接続される第２吸入管（４）の端部（
４ａ）を、前記第１圧縮機（１）に接続される第１吸入
管（３）の途中で、該吸入管（３）の管内壁（３ａ）よ
りも内方側に突出状に接続させるききには、吸入ガスに
混入された油が、その濡れ性により前記第１吸入管（３
）の管内壁（３ａ）を伝わって第１圧縮機（１）側に多
量に供給され、一方、端部（４ａ）が前記管内壁（３ａ
）に突入された第２吸入管（４）から第２圧縮機（２）
への油供給量は小となり、従って、以上の配管構成を利
用することにより、構造簡単としながら、所期の目的が
達成できる。Further, as a constituent means of the oil return mechanism (8), an end (
4a) is connected in the middle of the first suction pipe (3) connected to the first compressor (1) so as to protrude inward from the inner wall (3a) of the suction pipe (3). At this time, the oil mixed in the suction gas flows through the first suction pipe (3) due to its wettability.
) is supplied in large quantities to the first compressor (1) through the pipe inner wall (3a), while the end (4a) is supplied to the pipe inner wall (3a).
) from the second suction pipe (4) into the second compressor (2)
The amount of oil supplied to the piping is small, so by using the piping configuration described above, the intended purpose can be achieved while keeping the structure simple.
（実施例）
第１図に示したツイン形圧縮装置は、密閉ケーシング（
Ｃ）の内部に、モータ（Ｍ）と圧縮要素（ＣＦ）とを組
込んだ第１圧縮機（１）と第２圧縮機（２）とを備え、
これら圧縮機（１）（２）の各ケーシング（Ｃ）に、そ
れぞれ第１及び第２吸入管（３）（４）を接続すると共
に、前記各圧縮要素（ＣＦ）の冷媒吐出域に外部吐出管
（５）を接続する一方、前記各ケーシング（Ｃ）の下部
間で、その各油溜（ａ）の規定油量に見合う油面高さ位
置に、油量バランスを是正するための均油管（６）を接
続している。(Example) The twin compressor shown in Fig. 1 has a hermetic casing (
C) includes a first compressor (1) and a second compressor (2) incorporating a motor (M) and a compression element (CF),
The first and second suction pipes (3) and (4) are connected to each casing (C) of these compressors (1) and (2), respectively, and the refrigerant is discharged externally to the refrigerant discharge area of each compression element (CF). While connecting the pipe (5), an oil equalizing pipe for correcting the oil quantity balance is installed between the lower parts of each of the casings (C) at an oil level height corresponding to the prescribed oil quantity of each oil sump (a). (6) is connected.
しかして、以上のツイン形圧縮装置において、前記第１
及び第２圧縮機（１）（２）を、それぞれインバータ制
御運転可能に構成し、これら圧縮機（１）（２）の各モ
ータ（Ｍ）をイン／＜−夕運転制御手段（７）に接続し
て、この運転制御手段（７）からの指令で、負荷変動に
対応して常に前記第１圧縮機（１）側が第２圧縮機（２
）よりも低い周波数で運転されるようになすと共に、前
記各圧縮機（１）（２）への冷媒吸入経路に油戻し機構
（８）を設けて、該油戻し機構（８）で高周波数側の前
記第２圧縮機（２）よりも低周波数側の第１圧縮機（１
）に多量の油を戻すようにしたのである。Therefore, in the above twin compression device, the first
and the second compressors (1) and (2) are each configured to be able to be operated under inverter control, and each motor (M) of these compressors (1) and (2) is connected to an in/<-inverter operation control means (7). In response to a command from the operation control means (7), the first compressor (1) side always switches to the second compressor (2
), and an oil return mechanism (8) is provided in the refrigerant suction path to each of the compressors (1) and (2). The first compressor (1) on the lower frequency side than the second compressor (2) on the side
) to return a large amount of oil.
前記油戻し機構（８）は、例えば、第２図に示したよう
に構成するのであり、即ち、前記第１圧縮機（１）に至
る第１吸入管（３）の上下方向中間部位に、該吸入管（
３）内を流れる吸入ガス流に対し直交するように、前記
第２圧縮機（２）に至る第２吸入管（４）の端部（４ａ
）を水平方向に向けて接続すると共に、この第２吸入管
（４）の端部（４ａ）を前記第１吸入管（３）の管内壁
（３ａ）よりも内方側に突出させるのである。The oil return mechanism (8) is configured, for example, as shown in FIG. The suction tube (
3) An end (4a) of the second suction pipe (4) leading to the second compressor (2) so as to be perpendicular to the suction gas flow flowing therethrough.
) are connected horizontally, and the end (4a) of the second suction pipe (4) is made to protrude inward beyond the inner wall (3a) of the first suction pipe (3). .
以上の構成とすることにより、ビル空調などの運転時に
は、前記運転制御手段（７）からの指令で、前記第１圧
縮機（１）が第２圧縮機（２）よりも常に低い周波数で
運転され、換言すれば、前記各圧縮機（１）（２）の各
ケーシング（Ｃ）間に、第１圧縮機（１）側が第２圧縮
機（２）側に対し常に内部圧力大となる強制差圧が発生
することとなる。With the above configuration, when operating a building air conditioner, etc., the first compressor (1) always operates at a lower frequency than the second compressor (2) based on the command from the operation control means (7). In other words, between the casings (C) of the compressors (1) and (2), the internal pressure is always higher on the first compressor (1) side than on the second compressor (2) side. A differential pressure will occur.
また、前記第２吸入管（４）の端部（４ａ）が、第１吸
入管（３）の途中でその管内壁（３ａ）よりも内方側に
突出状に接続されていることから、吸入ガスへの混入油
は、その濡れ性により前記第１吸入管（３）の管内壁（
３ａ）を伝わって第１圧縮機（１）側に多量に供給され
、一方、端部（４ａ）が前記管内壁（３ａ）に突入され
た第２吸入管（４）から第２圧縮機（２）への油供給量
は小となり、従って、多量の油が供給された高圧側の第
１圧縮機（１）から、低圧側の第２圧縮機（２）へと前
記均油管（６）を介して油の移動が行われ、各圧縮機（
１）（２）間の油面高さが均一となるのである。Furthermore, since the end (4a) of the second suction pipe (4) is connected to the first suction pipe (3) in a protruding manner inward from the inner wall (3a) of the pipe, Due to its wettability, the oil mixed into the suction gas will coat the inner wall of the first suction pipe (3) (
3a) to the first compressor (1), while a large amount of water is supplied to the second compressor (1) from the second suction pipe (4) whose end (4a) is inserted into the pipe inner wall (3a). 2) is small, and therefore the oil equalizing pipe (6) is passed from the first compressor (1) on the high pressure side, which is supplied with a large amount of oil, to the second compressor (2) on the low pressure side. The oil movement is carried out through each compressor (
The oil level height between 1) and (2) becomes uniform.
第３図は、横軸に、第１及び第２圧縮機の負荷率（％）
をとり、縦軸に、運転周波数（Ｈｚ）と能力（Ｋｃａｌ
）及び再圧縮機間の差圧（ｋｇ ／Ｃ♂・Ｇ）をとった
各グラフを示している。In Figure 3, the horizontal axis shows the load factor (%) of the first and second compressors.
, and the vertical axis shows the operating frequency (Hz) and capacity (Kcal
) and the differential pressure between the recompressor (kg/C♂・G) are shown.
第３図の下部側に示したように、第１圧縮機と第２圧縮
機との周波数を変動することにより、同図の中間に示し
た合算能力グラフが得られ、また、同図の上部側に示し
たように、再圧縮機間の強制差圧グラフが得られ、この
再圧縮機間で発生する強制差圧により、第１圧縮機側か
ら第２圧縮機側に油の移動が行われるのである。As shown in the lower part of Figure 3, by varying the frequencies of the first compressor and the second compressor, the total capacity graph shown in the middle of the figure can be obtained. As shown on the side, a forced differential pressure graph between the recompressors is obtained, and the forced differential pressure generated between the recompressors causes oil to move from the first compressor side to the second compressor side. It will be destroyed.
尚、同図において、負荷率３０％〜４５％の低負荷時に
は、第２圧縮機（２）のみ運転を継続し、第１圧縮機（
１）は停止させており、すなわち、該第１圧縮機（１）
を第２圧縮機（２）に対し低周波数とするのは停止（周
波数二〇）を含む概念である。In the figure, when the load is low (30% to 45%), only the second compressor (2) continues to operate, and the first compressor (2) continues to operate.
1) is stopped, that is, the first compressor (1)
The concept of having a low frequency with respect to the second compressor (2) includes stopping (frequency 20).
（発明の効果）
以上説明したように、本発明のツイン形圧縮装置では、
第１及び第２圧縮機（１）（２）をインバータ制御によ
り能力調節可能に構成すると共に、負荷変化に追従させ
て常時第１圧縮機（１）を第２圧縮機（２）よりも低い
周波数で運転する運転制御手段（７）と、吐出管（５）
に流出された油を、高周波数側の第２圧縮機（２）より
も低周波数側の第１圧縮機（１）に多く戻ず油戻し機構
（８）とを設けたから、各圧縮機（１）（２）間の油量
バランスを均一化できて、潤滑性能の低下や過剰給油に
よる油圧縮などの問題を解決できるに至ったのである。(Effects of the Invention) As explained above, in the twin compression device of the present invention,
The first and second compressors (1) and (2) are configured so that their capacities can be adjusted by inverter control, and the first compressor (1) is always lower than the second compressor (2) by following load changes. Operation control means (7) operated by frequency and discharge pipe (5)
Since the oil return mechanism (8) is provided, the oil spilled in the first compressor (1) on the low frequency side does not return more oil than the second compressor (2) on the high frequency side to the first compressor (1) on the low frequency side. By equalizing the oil amount balance between 1) and (2), it has become possible to solve problems such as deterioration of lubrication performance and oil compression due to excessive oil supply.
また、前記油戻し機構（８）の構成手段として、前記第
２圧縮機（２）に接続される第２吸入管（４）の端部（
４ａ）を、前記第１圧縮機（１）に接続される第１吸入
管（３）の途中で、該吸入管（３）の管内壁（３ａ）よ
りも内方側に突出状に接続させるときには、簡単な構成
でもって、所期の目的が達成できるのである。Further, as a constituent means of the oil return mechanism (8), an end (
4a) is connected in the middle of the first suction pipe (3) connected to the first compressor (1) so as to protrude inward from the inner wall (3a) of the suction pipe (3). Sometimes, a simple configuration can achieve the intended purpose.
第１図は本発明にかかるツイン形圧縮装置の配管図、第
２図は油戻し機構の実施例を示す断面図、第３図は負荷
率の変動による各特性を示すグラフ、第４図は従来例を
示す配管図である。
（１）・・・・Φ第１圧縮機
（２）・・・拳・第２圧縮機
（３）−・・・・第１吸入管
（３ａ）・・・ｅ管内壁
（４）・・・・・第２吸入管
（４ａ）・・・拳端部
（５）・・・・・吐出管
（６）１・・・均油管
（７）−・Φ・・運転制御手段
（８）・・・拳・油戻し機構
（Ｃ）・・・・ｅ密閉ケーソング
（ＣＦ）・・・・圧縮要素
（Ｍ）・・・・・モータFig. 1 is a piping diagram of the twin compressor according to the present invention, Fig. 2 is a sectional view showing an embodiment of the oil return mechanism, Fig. 3 is a graph showing various characteristics due to variations in load factor, and Fig. 4 is It is a piping diagram showing a conventional example. (1)...Φ1st compressor (2)...Fist/2nd compressor (3)...1st suction pipe (3a)...e pipe inner wall (4)... ...Second suction pipe (4a)...Fist end (5)...Discharge pipe (6) 1...Oil equalizing pipe (7)--Φ...Operation control means (8)-・・Fist/oil return mechanism (C)・・e Sealed case song (CF)・・Compression element (M)・・・Motor
Claims (1)
（ＣＦ）を内装した第１圧縮機（１）と第２圧縮機（２
）とを備え、該各圧縮機（１）（２）間に均油管（６）
を接続したツイン形圧縮装置において、前記第１及び第
２圧縮機（１）（２）をインバータ制御により能力調節
可能に構成すると共に、負荷変化に追従させて常時前記
第１圧縮機（１）を第２圧縮機（２）よりも低い周波数
で運転する運転制御手段（７）と、吐出管（５）に流出
された油を、高周波数側の第２圧縮機（２）よりも低周
波数側の第１圧縮機（１）に多く戻す油戻し機構（８）
とを設けたことを特徴とするツイン形圧縮装置。 ２）油戻し機構（８）が、第２圧縮機（２）に接続する
第２吸入管（４）の端部（４ａ）を、第１圧縮機（１）
に接続する第１吸入管（３）の途中であって該吸入管（
３）の管内壁（３ａ）よりも内方側に突出状に接続して
構成されている請求項１記載のツイン形圧縮装置。[Claims] 1) A first compressor (1) and a second compressor (2) in which a motor (M) and a compression element (CF) are housed in a sealed casing (C).
), and an oil equalizing pipe (6) between each compressor (1) and (2).
In the twin compressor device in which the first and second compressors (1) and (2) are configured to be able to adjust their capacities by inverter control, the first compressor (1) is always configured to follow load changes. an operation control means (7) for operating the oil at a lower frequency than that of the second compressor (2); Oil return mechanism (8) that returns more oil to the first compressor (1) on the side
A twin-type compression device characterized by being provided with. 2) The oil return mechanism (8) connects the end (4a) of the second suction pipe (4) to the second compressor (2) to the first compressor (1).
In the middle of the first suction pipe (3) connected to the suction pipe (
2. The twin compression device according to claim 1, wherein the twin compression device is connected in a protruding manner inwardly from the inner wall (3a) of the tube.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63327273A JPH0639950B2 (en) | 1988-12-24 | 1988-12-24 | Twin type compression device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63327273A JPH0639950B2 (en) | 1988-12-24 | 1988-12-24 | Twin type compression device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH02173366A true JPH02173366A (en) | 1990-07-04 |
| JPH0639950B2 JPH0639950B2 (en) | 1994-05-25 |
Family
ID=18197280
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP63327273A Expired - Lifetime JPH0639950B2 (en) | 1988-12-24 | 1988-12-24 | Twin type compression device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0639950B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5211031A (en) * | 1990-05-24 | 1993-05-18 | Hitachi, Ltd. | Scroll type compressor and refrigeration cycle using the same |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6055787U (en) * | 1983-09-26 | 1985-04-18 | 三菱電機株式会社 | Parallel compression refrigeration equipment |
-
1988
- 1988-12-24 JP JP63327273A patent/JPH0639950B2/en not_active Expired - Lifetime
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6055787U (en) * | 1983-09-26 | 1985-04-18 | 三菱電機株式会社 | Parallel compression refrigeration equipment |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5211031A (en) * | 1990-05-24 | 1993-05-18 | Hitachi, Ltd. | Scroll type compressor and refrigeration cycle using the same |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0639950B2 (en) | 1994-05-25 |
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