JPH0267494A - Twin compressor - Google Patents
Twin compressorInfo
- Publication number
- JPH0267494A JPH0267494A JP21683188A JP21683188A JPH0267494A JP H0267494 A JPH0267494 A JP H0267494A JP 21683188 A JP21683188 A JP 21683188A JP 21683188 A JP21683188 A JP 21683188A JP H0267494 A JPH0267494 A JP H0267494A
- Authority
- JP
- Japan
- Prior art keywords
- compressor
- capacity
- electric compressor
- compression capacity
- compressive capacity
- 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
- 230000006835 compression Effects 0.000 claims abstract description 33
- 238000007906 compression Methods 0.000 claims abstract description 33
- 239000007789 gas Substances 0.000 abstract description 4
- 239000003507 refrigerant Substances 0.000 abstract description 3
- 230000007423 decrease Effects 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 230000002411 adverse Effects 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/02—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for several pumps connected in series or in parallel
-
- 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
- F25B2400/07—Details of compressors or related parts
- F25B2400/075—Details of compressors or related parts with parallel compressors
- F25B2400/0751—Details of compressors or related parts with parallel compressors the compressors having different capacities
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
【発明の詳細な説明】
〔発明の目的〕
（産業上の利用分野）
本発明は、密閉ケース内に２組の電動圧縮機本体を組込
んだ、いわゆるツイン形圧縮機に係り、特に能力可変幅
の設定構造の改良に関する。[Detailed Description of the Invention] [Object of the Invention] (Industrial Application Field) The present invention relates to a so-called twin-type compressor in which two sets of electric compressor bodies are incorporated in a sealed case, and particularly relates to a twin compressor with variable capacity. Concerning improvements to the width setting structure.
（従来の技術）
近時、能力可変幅を容易かつ確実に拡大可能なインバー
タ方式を採用し、上記圧縮機の運転周波数を最適条件に
適応するよう変化させるものが一般的である。(Prior Art) Recently, it has become common to adopt an inverter system that can easily and reliably expand the range of variable capacity, and to change the operating frequency of the compressor to suit optimum conditions.
（発明が解決しようとする課題）
ところで、複数（２〜１０台）の室内機を接続する、い
わゆるマルチ型エアコン装置に用いられる圧縮機として
は、たとえスクロール形でかつインバータ方式を採用し
た圧縮機であっても、通常の能力可変幅では運転条件を
満足することができなくなる。(Problem to be Solved by the Invention) By the way, as a compressor used in a so-called multi-type air conditioner device that connects a plurality of (2 to 10) indoor units, even if it is a scroll type compressor that uses an inverter method. Even so, the operating conditions cannot be satisfied with the normal capacity variable range.
すなわち第２図に示すように、たとえばインバータ方式
を採用した圧縮機においては運転周波数が３０〜１２０
Ｈ２の範囲が多用され、したがって可変比４である。こ
のときは圧縮機のＣ０Ｐ（成績係数）が高くなり、最適
な運転状況が得られる。しかしながら、室内機が複数台
接続されるいわゆるマルチ型エアコン装置に上記圧縮機
を用いると、低周波数側および高周波数側ともに可変幅
を拡大しなければならない。たとえば、１５〜２００Ｈ
２の範囲に運転周波数の可変幅を拡大すると、同図で明
らかなように、上記通常可変幅から突出した部分でのＣ
ＯＰの低下が極端に大となって、信頼性に悪影響を与え
ることになる。In other words, as shown in Figure 2, for example, in a compressor that uses an inverter system, the operating frequency is 30 to 120.
The H2 range is often used, hence the variable ratio of 4. At this time, the C0P (coefficient of performance) of the compressor becomes high, and optimal operating conditions can be obtained. However, if the above compressor is used in a so-called multi-type air conditioner device in which a plurality of indoor units are connected, the variable range must be expanded on both the low frequency side and the high frequency side. For example, 15-200H
When the variable range of the operating frequency is expanded to the range of 2, as is clear from the figure, C
The decrease in OP becomes extremely large, which adversely affects reliability.
そこで考えられるのは、たとえば２台のインバータ方式
の圧縮機を並列に接続して、同時もしくは単独運転をな
すようにした装置である。この場合、全ての室内機で同
時にもしくは任意の室内機のみでの熱交換作用が可能と
なるが、運転周波数が通常の可変幅の圧縮機であれば能
力可変比を充分にとることができず、信頼性が低いもの
である。What can be considered is, for example, a device in which two inverter-type compressors are connected in parallel and operated simultaneously or independently. In this case, it is possible to exchange heat with all indoor units at the same time or only with any indoor unit, but if the operating frequency is a compressor with a normal variable range, it will not be possible to achieve a sufficient variable capacity ratio. , has low reliability.
本発明は上記事情に着目してなされたものであり、たと
えマルチ型エアコン装置に用いられる圧縮機であっても
、単体の圧縮機であり、しかも運転周波数が通常の使用
範囲で高いＣＯＰを保持するとともに能力可変幅を拡大
して運転状況に無理なく適応でき、高い信頼性が得られ
るツイン形圧縮機を提供しようとするものである。The present invention has been made in view of the above circumstances, and even if the compressor is used in a multi-type air conditioner, it is a single compressor and maintains a high COP within the normal operating frequency range. At the same time, the present invention aims to provide a twin-type compressor that can be easily adapted to operating conditions by widening the range of variable capacity and that can provide high reliability.
（課題を解決する手段）
すなわち本発明においては、密閉ケース内に２組の電動
圧縮機本体を組込んでなり、上記電動圧縮機本体は、大
きい圧縮能力の第１の電動圧縮機本体と、小さい圧縮能
力でかつレリース機構を設けた第２の電動圧縮機本体と
からなることを特徴とするツイン形圧縮機である。(Means for Solving the Problems) That is, in the present invention, two sets of electric compressor bodies are assembled in a sealed case, and the electric compressor bodies include a first electric compressor body having a large compression capacity; This is a twin-type compressor characterized by having a small compression capacity and consisting of a second electric compressor main body provided with a release mechanism.
（作用）
このようにして構成することにより、高いＣＯＰを保持
する範囲の運転周波数でありながら、圧縮能力の小さい
第２の電動圧縮機本体に対してレリース作用をなせば最
少圧縮能力がさらに小さくなり、この圧縮能力と第１．
第２の電動圧縮機本体の最大圧縮能力の合計との割合で
ある能力可変比が極めて大になる。(Function) With this configuration, even if the operating frequency is within a range that maintains a high COP, if a release action is performed on the second electric compressor main body, which has a small compression capacity, the minimum compression capacity becomes even smaller. Therefore, this compression ability and the first.
The variable capacity ratio, which is the ratio to the total maximum compression capacity of the second electric compressor main body, becomes extremely large.
（実施例）
以下、本発明の一実施例を第１図にもとづいて説明する
。図中Ｓは密閉ケースであり、この密閉ケースＳ内にた
とえばインバータ方式の電動圧縮機本体Ａが組込まれる
。すなわち上記電動圧縮機本体Ａは、第１の電動圧縮機
本体１と、第２の電動圧縮機本体２とからなる。いずれ
の電動圧縮機本体１．２も、電動機部３，４と、スクロ
ール式の圧縮機部５，６とからなり、互いに極く一般的
な形状構造でよい。ただし後述するように、第１の電動
圧縮機本体１は圧縮能力が大、第２の電動圧縮機本体２
は圧縮能力が小になるよう構成する。上記密閉ケースＳ
の側壁には吸込管７が接続され、たとえば蒸発器などの
冷凍サイクル構成機器に連通ずる。この吸込管７から密
閉ケースＳ内に吸込まれる被圧縮ガスである冷媒ガスは
、第１゜第２の電動圧縮機本体１．２に設けられる吸込
通路を介してそれぞれの圧縮機部５．６に導入され、こ
こで圧縮されるようになっている。また互いの圧縮機部
５．６は吐出マフラ８．９を備えていて、これら吐出マ
フラ８．９は吐出連通管１０を介して連通ずる。さらに
第２の電動圧縮機本体２側の吐出マフラ９には吐出管１
１が接続され、これは密閉ケースＳを貫通して凝縮器に
連通ずる。したがって、第１．第２の電動圧縮機本体１
，２の圧縮機部５．６で圧縮され、かつ互いの吐出マフ
ラ８．９に吐出される冷媒ガスは吐出連通管１０を介し
て合流し、かつ吐出管１１を介して凝縮器に吐出される
ようになっている。なお、上記第２の電動圧縮機本体２
のみ、その圧縮機部６にレリース機構を構成するレリー
ス管１２が接続される。(Example) Hereinafter, an example of the present invention will be described based on FIG. In the figure, S denotes a closed case, and an inverter-type electric compressor main body A, for example, is incorporated into this closed case S. That is, the electric compressor main body A includes a first electric compressor main body 1 and a second electric compressor main body 2. Each electric compressor main body 1.2 consists of electric motor sections 3, 4 and scroll type compressor sections 5, 6, and each may have a very general shape and structure. However, as will be described later, the first electric compressor body 1 has a large compression capacity, and the second electric compressor body 2 has a large compression capacity.
is configured so that the compression capacity is small. The above sealed case S
A suction pipe 7 is connected to the side wall of the refrigeration cycle and communicates with a refrigeration cycle component such as an evaporator. The refrigerant gas, which is the gas to be compressed, is sucked into the sealed case S from the suction pipe 7 through suction passages provided in the first and second electric compressor bodies 1.2 to the respective compressor sections 5. 6, and is now compressed. Further, each compressor section 5.6 is provided with a discharge muffler 8.9, and these discharge mufflers 8.9 communicate with each other via a discharge communication pipe 10. Further, a discharge pipe 1 is provided in the discharge muffler 9 on the side of the second electric compressor main body 2.
1 is connected, which passes through the closed case S and communicates with the condenser. Therefore, the first. Second electric compressor main body 1
The refrigerant gases compressed by the compressor sections 5.6 of the two compressors 5.6 and discharged to the discharge mufflers 8.9 of the two converge via the discharge communication pipe 10, and are discharged to the condenser via the discharge pipe 11. It has become so. Note that the second electric compressor main body 2
Only, a release pipe 12 constituting a release mechanism is connected to the compressor section 6.
このレリース管１２は中途部に図示しない開閉機構を備
え、かつその端部は上記吸込管７の中途部に接続される
。The release pipe 12 is provided with an opening/closing mechanism (not shown) in the middle, and its end is connected to the middle of the suction pipe 7.
このようにして構成される圧縮機の基本運転条件として
、たとえば運転周波数を３０〜１２０Ｈ２，第１．第２
の電動圧縮機本体１．２の合計圧縮能力を６）ｆ’、
レリース率を２０％と設定する。The basic operating conditions for the compressor configured in this way include, for example, an operating frequency of 30 to 120H2, a 1st. Second
The total compression capacity of the electric compressor body 1.2 is 6) f',
Set the release rate to 20%.
そして、第１．第２の電動圧縮機本体１，２の基本圧縮
能力が６）−Ｐであるところから、第１の電動圧４縮機
本体ｌの圧縮能力を４）Ｐ、第２の電動圧縮機本体２の
圧縮能力を２１−Ｐとしたときが、最も優れた運転を得
られる。And the first. Since the basic compression capacity of the second electric compressor main bodies 1 and 2 is 6)-P, the compression capacity of the first electric compressor main body l is 4)P, and the second electric compressor main body 2 is The best operation can be obtained when the compression capacity is set to 21-P.
すなわち、運転周波数が３０〜１２０Ｈ２である場合の
可変比は、上記第２図からも明らかなように４であり、
したがって第１の圧縮機１の能力可変幅は２）Ｐ〜８）
ｆ’、第２の電動圧縮機本体２では１〜４）Ｐになる。That is, the variable ratio when the operating frequency is 30 to 120H2 is 4, as is clear from FIG. 2 above,
Therefore, the capacity variable range of the first compressor 1 is 2)P~8)
f', and 1 to 4) P in the second electric compressor main body 2.
しかしながら、上記第２の電動圧縮機本体２においてレ
リース作用をなすと、レリース率の２０％分だけ圧縮能
力か低下して最少圧縮能力は０．８１−Ｐになる。この
ような運転条件にある圧縮機としては、最少圧縮能力が
第２の電動圧縮機本体２のみ運転し、かつレリース作用
をなしたときである０、８１−Ｐであり、かつ第１゜第
２の電動圧縮機本体１，２を同時に最大圧縮能力で運転
すれば、最大圧縮能力は合計値である１２）Ｐとなる。However, when a release action is performed in the second electric compressor main body 2, the compression capacity decreases by 20% of the release rate, and the minimum compression capacity becomes 0.81-P. For a compressor under such operating conditions, the minimum compression capacity is 0.81-P when only the second electric compressor main body 2 is operated and a release action is performed, and the minimum compression capacity is 0. If the two electric compressor bodies 1 and 2 are operated at the maximum compression capacity at the same time, the maximum compression capacity will be the total value 12)P.
したがって、この圧縮機の能力可変比は１５（１２十０
．８）である。Therefore, the variable capacity ratio of this compressor is 15 (12
．． 8).
なお、以下に、基本運転条件は同一に設定するが、第１
．第２の圧縮機本体１，２の圧縮能力を異ならせた圧縮
機の例を上げて上記圧縮機■と比較してみる。In addition, the basic operating conditions are set the same below, but the first
．． An example of a compressor in which the second compressor main bodies 1 and 2 have different compression capacities will be given and compared with the above compressor (2).
たとえば、第１．第２の電動圧縮機本体１，２を同じ３
）ｆ’とした圧縮機■の場合には、互いの最少圧縮能力
が１．５ＨＰであるとともに、レリース率２０％だから
１．２）Ｐになる。最大圧縮能力は、可変比が４だから
６１−Ｐになる。その結果、このような圧縮機■として
の最少圧縮能力は一方の電動圧縮機本体のみ作動させた
ときの１．２）ｆ’、最大圧縮能力は双方の電動圧縮機
本体１．２の最大圧縮能力の合計である１２１−Ｐとな
って、能力可変比は１０である。また参考例として、第
１．第２の電動圧縮機本体１．２の基本圧縮能力は上記
一実施例と同一であるが、第２の電動圧縮機本体２にレ
リース機構を備えていない圧縮機■についての能力可変
幅等を、上記各圧縮機とともに下記表にまとめて示す。For example, 1st. The second electric compressor main bodies 1 and 2 are the same 3
) In the case of the compressor (2) with f', the mutual minimum compression capacity is 1.5 HP and the release rate is 20%, so it becomes 1.2) P. Since the variable ratio is 4, the maximum compression capacity is 61-P. As a result, the minimum compression capacity of such a compressor ■ is 1.2) f' when only one electric compressor body is operated, and the maximum compression capacity is the maximum compression capacity of both electric compressor bodies 1.2 The total capacity is 121-P, and the capacity variable ratio is 10. Also, as a reference example, 1. The basic compression capacity of the second electric compressor main body 1.2 is the same as that of the above-mentioned embodiment, but the variable capacity width etc. of the compressor , are summarized in the table below along with each of the above compressors.
このように同じ運転条件でありながら、第１の電動圧縮
機本体１の圧縮能力を大とし、第２の電動圧縮機本体２
の圧縮能力を小にして、かつレリース機構１２を備えた
圧縮機■の能力可変比が、他の圧縮機■および■のどれ
よりも大であることがわかる。すなわち、たとえマルチ
型エアコン装置に用いたとしても、使用運転範囲で高い
ＣＯＰを保持できるとともに能力可変幅が極めて大であ
るから、信頼性の高い運転をなすことができる。In this way, under the same operating conditions, the compression capacity of the first electric compressor main body 1 is increased, and the compression capacity of the second electric compressor main body 2 is increased.
It can be seen that the capacity variable ratio of the compressor (2), which has a small compression capacity and is equipped with the release mechanism 12, is greater than any of the other compressors (2) and (2). That is, even when used in a multi-type air conditioner, a high COP can be maintained within the operating range of use, and the variable range of capacity is extremely wide, so that highly reliable operation can be achieved.
以上説明したように本発明によれば、比較的簡単な設定
条件の圧縮機であり、通常の使用運転範囲で高いＣＯＰ
を保持でき、能力可変幅が極めて大となって、信頼性の
高い運転をなすという効果を奏する。As explained above, according to the present invention, the compressor has relatively simple setting conditions and has a high COP in the normal operating range.
can be maintained, the variable range of capacity is extremely wide, and highly reliable operation is achieved.
第１図は本発明の一実施例を示すツイン形圧縮機の概略
縦断面図、第２図は圧縮機の運転特性図である。
Ｓ・・・密閉ケース、Ａ・・・電動圧縮機本体、１・・
・第１の電動圧縮機本体、２・・・第２の電動圧縮機本
体、１１・・・レリース機構（レリース管）。
ＣＯＰ
第１図
出願人代理人 弁理士 鈴江武彦
第２図FIG. 1 is a schematic vertical cross-sectional view of a twin compressor showing an embodiment of the present invention, and FIG. 2 is a diagram showing operating characteristics of the compressor. S... Sealed case, A... Electric compressor body, 1...
- First electric compressor main body, 2... second electric compressor main body, 11... release mechanism (release tube). COP Figure 1 Applicant's agent Patent attorney Takehiko Suzue Figure 2
Claims (1)
動圧縮機本体は、大きい圧縮能力の第１の電動圧縮機本
体と、小さい圧縮能力の第２の電動圧縮機本体とからな
り、上記小さい圧縮能力の第２の電動圧縮機本体にのみ
レリース機構を設けたことを特徴とするツイン形圧縮機
。Two sets of electric compressor bodies are assembled in a sealed case, and the electric compressor body consists of a first electric compressor body having a large compression capacity and a second electric compressor body having a small compression capacity. A twin compressor characterized in that a release mechanism is provided only in the second electric compressor main body having a small compression capacity.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP21683188A JPH0267494A (en) | 1988-08-31 | 1988-08-31 | Twin compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP21683188A JPH0267494A (en) | 1988-08-31 | 1988-08-31 | Twin compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0267494A true JPH0267494A (en) | 1990-03-07 |
Family
ID=16694579
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP21683188A Pending JPH0267494A (en) | 1988-08-31 | 1988-08-31 | Twin compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0267494A (en) |
Cited By (4)
| 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 |
| US5358387A (en) * | 1991-05-29 | 1994-10-25 | Hitachi Ltd. | Oil-free scroll compressor |
| US5385453A (en) * | 1993-01-22 | 1995-01-31 | Copeland Corporation | Multiple compressor in a single shell |
| JP2012515880A (en) * | 2009-01-23 | 2012-07-12 | ビッツァー クールマシーネンバウ ゲーエムベーハー | Multiple scroll compressors having different volume indexes and systems and methods for the same |
-
1988
- 1988-08-31 JP JP21683188A patent/JPH0267494A/en active Pending
Cited By (4)
| 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 |
| US5358387A (en) * | 1991-05-29 | 1994-10-25 | Hitachi Ltd. | Oil-free scroll compressor |
| US5385453A (en) * | 1993-01-22 | 1995-01-31 | Copeland Corporation | Multiple compressor in a single shell |
| JP2012515880A (en) * | 2009-01-23 | 2012-07-12 | ビッツァー クールマシーネンバウ ゲーエムベーハー | Multiple scroll compressors having different volume indexes and systems and methods for the same |
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