JPH0584396B2 - - Google Patents
Info
- Publication number
- JPH0584396B2 JPH0584396B2 JP3214485A JP3214485A JPH0584396B2 JP H0584396 B2 JPH0584396 B2 JP H0584396B2 JP 3214485 A JP3214485 A JP 3214485A JP 3214485 A JP3214485 A JP 3214485A JP H0584396 B2 JPH0584396 B2 JP H0584396B2
- Authority
- JP
- Japan
- Prior art keywords
- scroll
- pin
- boss
- drive pin
- orbiting
- 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 - Fee Related
Links
- 238000007906 compression Methods 0.000 description 13
- 230000006835 compression Effects 0.000 description 12
- 230000002159 abnormal effect Effects 0.000 description 3
- 230000007423 decrease Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 230000005856 abnormality Effects 0.000 description 1
- 238000009825 accumulation Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
- 239000003507 refrigerant Substances 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
- F01C17/06—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements
- F01C17/063—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements with only rolling movement
-
- 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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
- F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
- F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
Description
【発明の詳細な説明】
産業上の利用分野
本発明は、冷凍サイクル等に使用するスクロー
ル型圧縮機に関するものである。DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a scroll compressor used in refrigeration cycles and the like.
従来の技術
以下図面を参照しながら、従来のスクロール型
圧縮機の一例について説明する。BACKGROUND OF THE INVENTION An example of a conventional scroll compressor will be described below with reference to the drawings.
まず第４図によりスクロール型圧縮機の圧縮原
理を説明する。第４図において１ａは固定スクロ
ールラツプ、２ａは旋回スクロールラツプ、３は
吐出孔である。 First, the compression principle of a scroll type compressor will be explained with reference to FIG. In FIG. 4, 1a is a fixed scroll wrap, 2a is an orbiting scroll wrap, and 3 is a discharge hole.
第４図ａにおいて、固定および旋回スクロール
ラツプ１ａ，２ａの組合せにより、ある密閉され
た圧縮空間４が形成される。この圧縮空間４は、
旋回スクロール２が固定スクロール１中心のまわ
りを半径r0で旋回することにより、ｂ図およびｃ
図に示すように中心部に移動しながらその容積を
縮小し、ｄ図において最高圧力となり吐出孔３か
ら吐出されて流体圧縮作用を行う。 In FIG. 4a, a closed compression space 4 is formed by the combination of fixed and orbiting scroll wraps 1a, 2a. This compressed space 4 is
As the orbiting scroll 2 rotates around the center of the fixed scroll 1 with a radius of r 0 , figures b and c
As shown in the figure, the volume decreases as it moves toward the center, and in figure d it reaches the highest pressure and is discharged from the discharge hole 3 to perform a fluid compression action.
次に従来の構造について、第５図、第６図を用
いて説明する。５は密閉ケーシング、６は電動機
部であり、その上部にはブロツク７、固定スクロ
ール１、旋回スクロール２、自転防止機構８にて
構成される機械部本体９が固定されている。固定
スクロール１は、鏡板１ｂ及び鏡板１ｂに直立す
るインボリユート又はインボリユートに類似した
曲線にて形成され、一様な厚さと高さを有するラ
ツプ１ａより構成され、鏡板１ｂにてブロツク７
に固定されている。又、旋回スクロール２は鏡板
２ｂ及び鏡板２ｂに直立し、固定スクロール１の
ラツプ１ａと同じ曲線を有するラツプ２ａより構
成され、鏡板２ｂは、固定スクロール１の鏡板１
ｂとブロツク７に僅かなクリアランスを設けては
さみ込み支持され、かつ自転防止機構８により拘
束されている。 Next, the conventional structure will be explained using FIGS. 5 and 6. 5 is a sealed casing, 6 is an electric motor section, and a mechanical section main body 9 consisting of a block 7, a fixed scroll 1, an orbiting scroll 2, and an anti-rotation mechanism 8 is fixed to the upper part thereof. The fixed scroll 1 is composed of an end plate 1b and a lap 1a formed of an involute or a curve similar to an involute that stands upright on the end plate 1b, and has a uniform thickness and height.
is fixed. The orbiting scroll 2 is composed of an end plate 2b and a lap 2a standing upright on the end plate 2b and having the same curve as the wrap 1a of the fixed scroll 1.
b and the block 7 with a slight clearance between them and are supported, and restrained by an anti-rotation mechanism 8.
１０は吸入孔であり、吐出孔３は固定スクロー
ル１のインボリユートの中心部に、又吸入孔１０
は固定スクロール１のインボリユートの鏡板１ｂ
の外縁部に設けられている。１１は旋回スクロー
ル２に、そのラツプ２ａと反対側の面に設けられ
たボス部であり、ラツプ２ａのインボリユートの
中心と同心である。１２はブロツク７に支承され
たシヤフトであり、機械部本体９の端部に設けら
れシヤフト中心よりr1だけ偏心した偏心部１２ａ
を旋回スクロール２のボス部１１に収納すること
により電動機部６と旋回スクロール２を連結して
いる。１３は旋回スクロール２の背面に形成され
た背圧室であり、旋回スクロール２のラツプ２ａ
側とは鏡板１ｂ，２ｂによりシールされ、固定ス
クロール１と旋回スクロール２により形成される
圧縮空間４と旋回スクロール２に設けた連結孔１
４ａ，１４ｂを介して連通している。１５は吸入
孔１０と連通する吸入管、１６は吐出管である。 10 is a suction hole, the discharge hole 3 is located in the center of the involute of the fixed scroll 1, and the suction hole 10 is
is the end plate 1b of the involute of the fixed scroll 1
It is provided on the outer edge of the Reference numeral 11 denotes a boss portion provided on the surface of the orbiting scroll 2 opposite to the wrap 2a, and is concentric with the center of the involute of the wrap 2a. Reference numeral 12 denotes a shaft supported by the block 7, and an eccentric portion 12a provided at the end of the machine body 9 and eccentric by r 1 from the shaft center.
is housed in the boss portion 11 of the orbiting scroll 2, thereby connecting the electric motor section 6 and the orbiting scroll 2. 13 is a back pressure chamber formed on the back surface of the orbiting scroll 2, and the lap 2a of the orbiting scroll 2
The compression space 4 formed by the fixed scroll 1 and the orbiting scroll 2 and the connecting hole 1 provided in the orbiting scroll 2 are sealed from the side by the end plates 1b and 2b.
4a and 14b. 15 is a suction pipe communicating with the suction hole 10, and 16 is a discharge pipe.
以上のように構成されたスクロール型圧縮機に
ついて以下その動作について説明する。 The operation of the scroll compressor configured as above will be explained below.
シヤフト１２が回転運動を開始すると、吸入孔
１０から流入した冷媒は機械部本体９で圧縮さ
れ、吐出孔３から一旦密閉ケーシング５に吐出さ
れた後、吐出管１６を介して冷却システム（図示
せず）に吐出される。 When the shaft 12 starts rotating, the refrigerant flowing through the suction hole 10 is compressed in the mechanical body 9, and is once discharged from the discharge hole 3 into the sealed casing 5, and then passes through the discharge pipe 16 to the cooling system (not shown). z) is discharged.
また第６図は機械部本体９におけるある回転角
度の圧縮状態を示している。シヤフト１２の偏心
部１２ａはシヤフト１２中心よりr1だけ偏心して
おり、理論上の旋回半径r0との差Ｃ＝r0−r1だけ
両ラツプ間に隙間が存在しながら第４図に示した
圧縮原理に従つて圧縮作用が行われる。 Further, FIG. 6 shows the compressed state of the mechanical part main body 9 at a certain rotation angle. The eccentric portion 12a of the shaft 12 is eccentric by r 1 from the center of the shaft 12, and the difference from the theoretical turning radius r 0 is C = r 0 − r 1 , with a gap existing between both laps as shown in FIG. The compression action is carried out according to the compression principle.
発明が解決しようとする問題点
しかしながら上記のような構成では、固定スク
ロール１と旋回スクロール２の渦巻間には常に半
径方向隙間Ｃが形成されている。従つてこのよう
な半径方向隙間Ｃが存在することは、圧縮空気４
の半径方向の隙間のシールが行い難く、かつ半径
方向の隙間Ｃを通じて圧縮空間４内部のガスが低
圧側へ漏れてしまうことになる。このことは最終
的に、吐出孔３から吐出されるガス量が減じ体積
効率が低下するとともに、漏れたガスを再度圧縮
することになり、モータ入力が増加し、成績係数
が低下するという問題点を有していた。Problems to be Solved by the Invention However, in the above configuration, a radial gap C is always formed between the spirals of the fixed scroll 1 and the orbiting scroll 2. Therefore, the existence of such a radial gap C means that the compressed air 4
It is difficult to seal the radial gap C, and the gas inside the compression space 4 leaks to the low pressure side through the radial gap C. This ultimately leads to a problem in that the amount of gas discharged from the discharge hole 3 decreases and the volumetric efficiency decreases, and the leaked gas has to be compressed again, increasing the motor input and lowering the coefficient of performance. It had
本発明は上記点に鑑みなされたもので、運転中
に旋回スクロールを半径方向に移動可能にしてラ
ツプ間の半径方向隙間を０とし、高性能で信頼性
のあるスクロール型圧縮機を提供するものであ
る。 The present invention has been made in view of the above points, and provides a high-performance and reliable scroll type compressor in which the orbiting scroll is movable in the radial direction during operation to eliminate the radial gap between laps. It is.
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スクロー
ル型圧縮機は、旋回スクロールを、ラツプを有す
るスクロール部材とシヤフトを嵌合するボス部を
有するボス部材とから構成し、いずれか一方の部
材に円運動を与えるための駆動ピンをスクロール
部材の中心より偏心させて設けるとともに、他方
の部材に駆動ピンと略同径で駆動ピンが嵌合され
る偏心穴を設け、かつ、いずれか一方の部材に駆
動ピンとは異なる位置にピンを設けると共に他方
の部材にピンより大径の案内穴を設けスクロール
部材をボス部材に対して所定の範囲で駆動ピンを
中心に移動可能とした構造としたものである。Means for Solving the Problems In order to solve the above problems, the scroll compressor of the present invention includes an orbiting scroll composed of a scroll member having a lap and a boss member having a boss portion into which a shaft is fitted. , a drive pin for imparting circular motion to one of the members is provided eccentrically from the center of the scroll member, and an eccentric hole having approximately the same diameter as the drive pin and into which the drive pin is fitted is provided in the other member, and , a pin is provided in one of the members at a position different from the drive pin, and a guide hole with a larger diameter than the pin is provided in the other member so that the scroll member can be moved within a predetermined range relative to the boss member around the drive pin. The structure is as follows.
作 用
本発明は上記した構成によつて、旋回スクロー
ルと固定スクロールの両ラツプ間の半径方向隙間
を０にするものである。Effects The present invention has the above-described configuration to reduce the radial clearance between the laps of the orbiting scroll and the fixed scroll to zero.
実施例
以下本発明の一実施例のスクロール型圧縮機に
ついて図面を参照しながら説明する。尚、従来例
と同一部分は同一符号を付し詳細な説明を省略す
る。Embodiment A scroll compressor according to an embodiment of the present invention will be described below with reference to the drawings. Note that the same parts as in the conventional example are given the same reference numerals and detailed explanations are omitted.
第１図、第２図において、旋回スクロール２
は、ラツプ２ａを有するスクロール部材２ｃとボ
ス部１１を有するボス部材２ｄとで構成されてい
る。そしてボス部材２ｄの反ボス部側には、スク
ロール部材２ｃの中心O1と偏心した位置に駆動
ピン１７（中心O2）が設けてあり、スクロール
部材２ｃの反ラツプ側には駆動ピン１７が嵌合さ
れる駆動ピン１７と略同径の偏心穴１８が設けて
ある。 In FIGS. 1 and 2, the orbiting scroll 2
is composed of a scroll member 2c having a lap 2a and a boss member 2d having a boss portion 11. A drive pin 17 (center O 2 ) is provided on the opposite side of the boss member 2 d at a position eccentric to the center O 1 of the scroll member 2 c, and a drive pin 17 is provided on the opposite side of the scroll member 2 c. An eccentric hole 18 having approximately the same diameter as the drive pin 17 to be fitted is provided.
またボス部材２ｄの反ボス部側には、駆動ピン
１７と異つた位置にピン１９が突出しており、ス
クロール部材２ｃの反ラツプ側でピン１９とほぼ
相対する位置に、ピン１９より大径の案内穴２０
が設けてある。尚２１は背圧室１７を中圧に保つ
ための連通管である。 Further, a pin 19 protrudes from the side opposite to the boss portion of the boss member 2d at a position different from that of the drive pin 17, and a pin 19 with a larger diameter than the pin 19 is provided at a position substantially opposite to the pin 19 on the side opposite to the wrap of the scroll member 2c. Guide hole 20
is provided. Note that 21 is a communication pipe for maintaining the back pressure chamber 17 at an intermediate pressure.
以上のように構成されたスクロール型圧縮機に
ついて第２図、第３図を用いて動作を説明する。 The operation of the scroll compressor configured as above will be explained using FIGS. 2 and 3.
第４図の圧縮原理に従つて圧縮作用が行われる
と、旋回スクロール２には、第３図に示すように
偏心方向に遠心力Fc、反偏心方向にラツプを引き
離そうとする力（ラジアル力）Fr、旋回軌道の接
線方向に作用する力（接線力）F〓が働く。そして
これら作用力の合力Fsは図に示すとおりの方向に
働くことになる。 When the compression action is performed according to the compression principle shown in Fig. 4, the orbiting scroll 2 receives a centrifugal force F c in the eccentric direction as shown in Fig. 3, and a force (radial force) that tries to separate the wraps in the anti-eccentric direction. ) F r , a force (tangential force) F〓 acts in the tangential direction of the orbit. The resultant force F s of these acting forces acts in the direction shown in the figure.
ところが駆動ピン１７はスクロール部材２ｃの
中心よりも偏心して設けてあるため、スクロール
部材２ｃは、合力Fsの直線O1，O2と直角方向の
分力Fs′によつて、駆動ピン１７の中心O2まわり
に回転させられようとし、ピン１９の径と案内穴
２０の径の余裕内で旋回半径は増大する。そして
この結果、ラツプ２ａ，１ａ間の半径方向隙間Ｃ
は詰まることになり、ラツプ２ａ，１ａどうしが
接触した時点でバランスし、半径方向隙間Ｃは０
となる。 However, since the drive pin 17 is provided eccentrically from the center of the scroll member 2c, the scroll member 2c is moved by the drive pin 17 due to the component force F s ' in the direction perpendicular to the straight lines O 1 and O 2 of the resultant force F s . The turning radius increases within the margin between the diameter of the pin 19 and the diameter of the guide hole 20. As a result, the radial gap C between the laps 2a and 1a
will become clogged, and when the laps 2a and 1a come into contact, they will be balanced and the radial clearance C will be 0.
becomes.
また運転中に液圧縮や異物のかみ込み等の異常
現象が生じた場合、スクロール部材２ｃはピン１
９径と案内穴２０径の余裕内だけ旋回半径が減少
する方向に移動し、異常現象から定常運転状態に
復帰する。 In addition, if an abnormal phenomenon occurs during operation, such as liquid compression or foreign matter getting caught, the scroll member 2c
The turning radius is moved within the margin of diameter 9 and diameter 20 of the guide hole, and the normal operating state is restored from the abnormal phenomenon.
以上のように本実施例によれば、運転中にラツ
プ間の半径方向隙間Ｃを０にし、又異常現象時に
はラツプ間の半径方向隙間Ｃを増大させて定常運
転状態に復帰させることが出来る。 As described above, according to this embodiment, the radial gap C between the laps can be set to 0 during operation, and when an abnormality occurs, the radial gap C between the laps can be increased to restore the normal operating state.
発明の効果
以上のように本発明は、旋回スクロールをラツ
プを有するスクロール部材とボス部を有するボス
部材とから構成し、一方には旋回スクロール中心
と偏心して駆動ピンを設け、他方には駆動ピンと
略同径で駆動ピンが嵌合される偏心穴を設け、か
つ一方に駆動ピンとは異なる位置にピンを設け、
他方にピンより大径の案内穴を設け、スクロール
部材に対し所定の範囲で駆動ピンを中心に移動可
能にして運転中に旋回半径を可変する、換言する
とラツプ間の半径方向隙間を可変することができ
るようになり、体積効率が高くモータ入力が少な
い所謂成績係数が良好な、また液圧縮、ゴミかみ
等の異常現象が回避でき信頼性の高いコンプレツ
サを得ることが出来る。Effects of the Invention As described above, the present invention comprises an orbiting scroll consisting of a scroll member having a lap and a boss member having a boss portion, a drive pin is provided eccentrically from the center of the orbiting scroll on one side, and a drive pin is provided on the other side. An eccentric hole with approximately the same diameter into which the drive pin is fitted is provided, and a pin is provided on one side at a different position from the drive pin,
On the other hand, a guide hole with a larger diameter than the pin is provided, and the scroll member is movable within a predetermined range around the drive pin, so that the turning radius can be varied during operation, in other words, the radial gap between the laps can be varied. This makes it possible to obtain a highly reliable compressor that has high volumetric efficiency, low motor input, and a good so-called coefficient of performance, and can avoid abnormal phenomena such as liquid compression and dirt accumulation.
第１図は本発明の一実施例におけるスクロール
型圧縮機の縦断面図、第２図は本発明の一実施例
の旋回スクロール部分の詳細を示す拡大断面図、
第３図は第２図のＡ−Ａ数の断面図、第４図はス
クロール型圧縮機の圧縮原理の説明図、ａ〜ｄは
その圧縮過程の推移図、第５図は従来のスクロー
ル型圧縮機の縦断面図で、第６図は従来の旋回ス
クロール部分の詳細を示す拡大断面図である。
１……固定スクロール、１ａ……固定スクロー
ルのラツプ、１ｂ……固定スクロールの鏡板、２
……旋回スクロール、２ａ……旋回スクロールの
ラツプ、２ｂ……旋回スクロールの鏡板、２ｃ…
…スクロール部材、２ｄ……ボス部材、８……自
転防止機構、１２……シヤフト、１７……駆動ピ
ン、１８……偏心穴、１９……ピン、２０……案
内穴。
FIG. 1 is a longitudinal cross-sectional view of a scroll compressor according to an embodiment of the present invention, and FIG. 2 is an enlarged cross-sectional view showing details of an orbiting scroll portion according to an embodiment of the present invention.
Fig. 3 is a cross-sectional view taken along line A-A in Fig. 2, Fig. 4 is an explanatory diagram of the compression principle of a scroll type compressor, a to d is a transition diagram of the compression process, and Fig. 5 is a conventional scroll type compressor. FIG. 6 is a longitudinal cross-sectional view of the compressor, and FIG. 6 is an enlarged cross-sectional view showing details of a conventional orbiting scroll portion. 1... fixed scroll, 1a... fixed scroll wrap, 1b... fixed scroll end plate, 2
... Orbiting scroll, 2a... Orbiting scroll wrap, 2b... Orbiting scroll end plate, 2c...
...scroll member, 2d...boss member, 8...rotation prevention mechanism, 12...shaft, 17...drive pin, 18...eccentric hole, 19...pin, 20...guide hole.
Claims (1)
を直立させた固定及び旋回スクロール１，２と、
両スクロール１，２を互いにラツプ１ａ，２ａを
内側にしてかみ合せ、前記旋回スクロール２が自
転運動しないように前記固定スクロール１に対し
旋回運動させる自転防止機構８を備え、前記旋回
スクロール２はラツプ２ａを有したスクロール部
材２ｃとシヤフト１２と嵌合されるボス部１１を
有したボス部材２ｄとで構成され、前記スクロー
ル部材２ｃまたはボス部材２ｄのいずれか一方に
前記スクロール部材２ｃに円運動を与えるための
駆動ピン１７を前記スクロール部材２ｃの中心よ
り偏心させて設けるとともに、前記駆動ピン１７
の配設されていないスクロール部材２ｃまたはボ
ス部材２ｄに前記駆動ピン１７と略同径で前記駆
動ピン１７が嵌合される偏心穴１８を設け、か
つ、前記スクロール部材２ｃまたはボス部材２ｄ
のいずれか一方の前記駆動ピン１７とは異なる位
置にピン１９を設けると共に、前記ピン１９が配
設されていないスクロール部材２ｃまたはボス部
材２ｄにピン１９より大径の案内穴２０を設け、
前記スクロール部材２ｃを前記ボス部材２ｄに対
して所定の範囲で前記駆動ピン１７を中心に移動
可能に取付けてなるスクロール型圧縮機。1 Spiral wraps 1a, 2a on end plates 1b, 2b
fixed and orbiting scrolls 1 and 2 that stand upright;
Both scrolls 1 and 2 are engaged with each other with their laps 1a and 2a inside, and an anti-rotation mechanism 8 is provided to rotate the orbiting scroll 2 relative to the fixed scroll 1 so that the orbiting scroll 2 does not rotate on its axis. 2a and a boss member 2d having a boss portion 11 that is fitted with the shaft 12, the scroll member 2c or the boss member 2d is configured to provide circular motion to the scroll member 2c. A driving pin 17 is provided eccentrically from the center of the scroll member 2c, and the driving pin 17 is provided eccentrically from the center of the scroll member 2c.
An eccentric hole 18 having approximately the same diameter as the drive pin 17 and into which the drive pin 17 is fitted is provided in the scroll member 2c or the boss member 2d that is not provided with the scroll member 2c or the boss member 2d.
A pin 19 is provided at a position different from the drive pin 17 of either one, and a guide hole 20 having a larger diameter than the pin 19 is provided in the scroll member 2c or the boss member 2d where the pin 19 is not provided,
A scroll type compressor in which the scroll member 2c is movably attached to the boss member 2d within a predetermined range around the drive pin 17.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3214485A JPS61192882A (en) | 1985-02-20 | 1985-02-20 | Scroll type compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3214485A JPS61192882A (en) | 1985-02-20 | 1985-02-20 | Scroll type compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS61192882A JPS61192882A (en) | 1986-08-27 |
| JPH0584396B2 true JPH0584396B2 (en) | 1993-12-01 |
Family
ID=12350699
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3214485A Granted JPS61192882A (en) | 1985-02-20 | 1985-02-20 | Scroll type compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS61192882A (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US9523361B2 (en) | 2011-01-11 | 2016-12-20 | Lg Electronics Inc. | Scroll compressor having back pressure chamber that operatively contains a discharge pressure and an intermediate pressure during different periods of time within a single compression cycle |
| KR101300261B1 (en) * | 2011-11-09 | 2013-08-23 | 엘지전자 주식회사 | Scroll compressor |
| KR101368396B1 (en) * | 2011-11-09 | 2014-03-03 | 엘지전자 주식회사 | Scroll compressor |
| KR101300258B1 (en) * | 2011-11-09 | 2013-08-23 | 엘지전자 주식회사 | Scroll compressor |
-
1985
- 1985-02-20 JP JP3214485A patent/JPS61192882A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS61192882A (en) | 1986-08-27 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |