JPH01177482A - Scroll compressor - Google Patents
Scroll compressorInfo
- Publication number
- JPH01177482A JPH01177482A JP62332005A JP33200587A JPH01177482A JP H01177482 A JPH01177482 A JP H01177482A JP 62332005 A JP62332005 A JP 62332005A JP 33200587 A JP33200587 A JP 33200587A JP H01177482 A JPH01177482 A JP H01177482A
- Authority
- JP
- Japan
- Prior art keywords
- chamber
- scroll
- compression
- pressure
- thrust bearing
- 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
- 238000007906 compression Methods 0.000 claims abstract description 138
- 230000006835 compression Effects 0.000 claims abstract description 136
- 239000012530 fluid Substances 0.000 claims description 10
- 230000007246 mechanism Effects 0.000 claims description 2
- 238000000638 solvent extraction Methods 0.000 claims 1
- 230000009191 jumping Effects 0.000 abstract description 6
- 238000000034 method Methods 0.000 abstract description 2
- 238000004519 manufacturing process Methods 0.000 abstract 1
- 239000003921 oil Substances 0.000 description 85
- 239000010687 lubricating oil Substances 0.000 description 43
- 239000007789 gas Substances 0.000 description 36
- 239000003507 refrigerant Substances 0.000 description 32
- 238000002347 injection Methods 0.000 description 17
- 239000007924 injection Substances 0.000 description 17
- 239000007788 liquid Substances 0.000 description 16
- 230000002093 peripheral effect Effects 0.000 description 14
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 10
- 230000008859 change Effects 0.000 description 10
- 230000002829 reductive effect Effects 0.000 description 10
- 235000014676 Phragmites communis Nutrition 0.000 description 7
- 230000009471 action Effects 0.000 description 7
- 229910052751 metal Inorganic materials 0.000 description 7
- 239000002184 metal Substances 0.000 description 7
- 238000004080 punching Methods 0.000 description 6
- 238000005057 refrigeration Methods 0.000 description 6
- 230000000694 effects Effects 0.000 description 5
- 229910052742 iron Inorganic materials 0.000 description 5
- 238000005192 partition Methods 0.000 description 5
- 229910000838 Al alloy Inorganic materials 0.000 description 4
- 229910000831 Steel Inorganic materials 0.000 description 4
- 230000002159 abnormal effect Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 239000011347 resin Substances 0.000 description 4
- 229920005989 resin Polymers 0.000 description 4
- 230000002441 reversible effect Effects 0.000 description 4
- 238000007789 sealing Methods 0.000 description 4
- 239000010959 steel Substances 0.000 description 4
- 238000001816 cooling Methods 0.000 description 3
- 230000001050 lubricating effect Effects 0.000 description 3
- 238000005461 lubrication Methods 0.000 description 3
- 125000006850 spacer group Chemical group 0.000 description 3
- 238000004804 winding Methods 0.000 description 3
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 230000036316 preload Effects 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 229910001209 Low-carbon steel Inorganic materials 0.000 description 1
- 239000004809 Teflon Substances 0.000 description 1
- 229920006362 Teflon® Polymers 0.000 description 1
- 230000001133 acceleration Effects 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- QVGXLLKOCUKJST-UHFFFAOYSA-N atomic oxygen Chemical compound [O] QVGXLLKOCUKJST-UHFFFAOYSA-N 0.000 description 1
- 230000002238 attenuated effect Effects 0.000 description 1
- 239000011324 bead Substances 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000005520 cutting process Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 238000011038 discontinuous diafiltration by volume reduction Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 239000001307 helium Substances 0.000 description 1
- 229910052734 helium Inorganic materials 0.000 description 1
- SWQJXJOGLNCZEY-UHFFFAOYSA-N helium atom Chemical compound [He] SWQJXJOGLNCZEY-UHFFFAOYSA-N 0.000 description 1
- 238000001746 injection moulding Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 229910001234 light alloy Inorganic materials 0.000 description 1
- 230000007257 malfunction Effects 0.000 description 1
- 230000000116 mitigating effect Effects 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 238000000465 moulding Methods 0.000 description 1
- 229910052757 nitrogen Inorganic materials 0.000 description 1
- 239000001301 oxygen Substances 0.000 description 1
- 229910052760 oxygen Inorganic materials 0.000 description 1
- 230000036961 partial effect Effects 0.000 description 1
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- 230000005855 radiation Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Landscapes
- Rotary Pumps (AREA)
Abstract
Description
【発明の詳細な説明】
産業上の利用分野
本発明はスクロール圧縮機の過負荷軽減に関するもので
ある。DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to overload mitigation of scroll compressors.
従来の技術
低振動、低騒音特性を備えたスクロール圧縮機は、吸入
室が外周部に有り、吐出ポートが渦巻きの中心部に設け
られ、圧縮流体の流れが一方向で往復動圧縮機や回転式
圧縮機のような流体を圧縮するための吐出弁を必要とせ
ず圧縮比が一定で、吐出脈動も比較的小さくて大きな吐
出空間を必要としないことが一般に知られている。Conventional technology Scroll compressors with low vibration and low noise characteristics have a suction chamber on the outer periphery and a discharge port in the center of the spiral. It is generally known that this type of compressor does not require a discharge valve for compressing fluid, has a constant compression ratio, has relatively small discharge pulsation, and does not require a large discharge space.
また、振動や騒音特性をより一層改善するために、圧縮
機高速運転時などにおける旋回スクロールのジャンピン
グ現象を少なくする方策として第１６図、第１７図の構
成が考えられている。Furthermore, in order to further improve vibration and noise characteristics, the configurations shown in FIGS. 16 and 17 have been considered as a measure to reduce the jumping phenomenon of the orbiting scroll during high-speed operation of the compressor.
同図は駆動シャフト１００７の先端部の駆動ピン１００
７ａに連結する旋回スクロール１００１の鏡板ｔ００１
ａが固定スクロール１００２（７）ｉ板１００２ａとフ
レーム１００８との間に微少隙間で支持され、圧縮機の
始動、停止時、高速運転時など圧縮負荷や回転部材の慣
性力などが変化する際に旋回スクロール１００１ｍがジ
ャンピングするのを阻止し、旋回スクロール１０ｏ１と
固定スクロール１００２との軸方向微少隙間を確保して
圧縮室の密封を図り、圧縮効率を高めると共に、部材間
の衝突により生じる異常音、振動、摺動部耐久性低下を
防止する工夫がなされている（特開昭５５−１４２９０
２号公報、米国特許３９９４６３３号公報など）。The figure shows the drive pin 100 at the tip of the drive shaft 1007.
End plate t001 of the orbiting scroll 1001 connected to 7a
The fixed scroll 1002 (7) is supported with a small gap between the i-plate 1002a and the frame 1008, and is used when the compression load or the inertia of rotating members changes, such as when starting, stopping, or high-speed operation of the compressor. This prevents the orbiting scroll 1001m from jumping, ensures a small gap in the axial direction between the orbiting scroll 10o1 and the fixed scroll 1002, and seals the compression chamber to improve compression efficiency, and also prevents abnormal noises caused by collisions between members. Efforts have been made to prevent vibration and deterioration of the durability of sliding parts (Japanese Patent Application Laid-open No. 55-14290).
2, U.S. Pat. No. 3,994,633, etc.).
発明が解決しようとする問題点
しかし、スクロール圧縮機は圧縮比が一定なために、液
圧縮などにより圧縮室内が異常圧力上昇した場合に圧縮
室間隙間を広げて圧縮流体を漏洩させ、圧縮室圧力を降
下させることが出来ないので、圧縮負荷の増大、部品の
破損、摺動部耐久性の低下を生じるというスクロール圧
縮機特有の問題がある。Problems to be Solved by the Invention However, since scroll compressors have a constant compression ratio, if the pressure inside the compression chamber increases abnormally due to liquid compression, etc., the gap between the compression chambers is widened and the compressed fluid leaks, causing the compression chamber to leak. Since the pressure cannot be lowered, there are problems unique to scroll compressors, such as increased compression load, damage to parts, and decreased durability of sliding parts.
また、この液圧縮問題解決のための方策として、第１８
図の構成が考えられている。In addition, as a measure to solve this liquid compression problem, the 18th
The composition of the figure has been considered.
同図は固定スクロール２００１ｅを軸方向に移動可能な
構成にし、板バネ２０２３ｅの付勢力と背圧室２０１５
に吐出圧力を導入してその背圧力とで固定スクロール２
００１ｅを旋回スクロール２００１ｂに押圧し、旋回ス
クロールと固定スクロールとの間の軸方向隙間を無くし
て圧縮室の密封を図り、圧縮効率を高めると共に圧縮室
内で液圧縮が生じた時、固定スクロール２００１・が旋
回スクロール２００１ｄから軸方向に離反して圧縮室圧
力を降下せしめて負荷を軽減する構成である（米国特許
３６００１１４号公報）。The figure shows a structure in which the fixed scroll 2001e is movable in the axial direction, and the urging force of the leaf spring 2023e and the back pressure chamber 2015
Introducing discharge pressure to the fixed scroll 2 and its back pressure
001e is pressed against the orbiting scroll 2001b, the axial gap between the orbiting scroll and the fixed scroll is eliminated, the compression chamber is sealed, and the compression efficiency is increased. When liquid compression occurs in the compression chamber, the fixed scroll 2001. is separated from the orbiting scroll 2001d in the axial direction to lower the compression chamber pressure and reduce the load (US Pat. No. 3,600,114).
しかし、固定スクロール２００１・を旋回スクロール２
００１ｄに常に押圧する構成では、その付勢力を大きく
する必要があり両スクロールの接触面の摩擦や摩耗によ
り耐久性が低下し、入力損失も大きいという問題があっ
た。However, the fixed scroll 2001 and the orbiting scroll 2
In the configuration in which the pressure is constantly pressed to 001d, it is necessary to increase the urging force, and there are problems in that durability is reduced due to friction and wear of the contact surfaces of both scrolls, and input loss is also large.
また、過負荷防止策として米国特許３８１７６６４号公
報などのように旋回スクロールを駆動軸の主軸と直角方
向に移動させる構成も考えられているが、部品構成が複
雑で振動や騒音特性の改善に難点があり、コスト高で圧
縮機の外形寸法が大きくなるなど、振動、騒音特性の改
善と過負荷軽減を同時に実現できるスクロール圧縮機が
望まれていた。Additionally, as a measure to prevent overload, a structure in which the orbiting scroll is moved in a direction perpendicular to the main axis of the drive shaft, such as in U.S. Pat. Due to the high cost and large external dimensions of the compressor, there was a desire for a scroll compressor that could simultaneously improve vibration and noise characteristics and reduce overload.
問題点を解決するための手段
上記問題を解決するために本発明のスクロール圧縮機は
、旋回スクロールが駆動軸を支承する本体フレームと固
定スクロールとの間に配置され、本体フレームの側に設
けられて軸方向にのみ移動が可能なスラスト軸受と固定
スクロールとの間に微少隙間を設けて挾まれており、ス
ラスト軸受は本体フレームとの間に適当な軸方向隙間を
維持しながら吐出流体圧力または吐出圧力と吸入圧力と
の間の中間流体圧力を利用して常に旋回スクロールの方
向に付勢されたものである。Means for Solving the Problems In order to solve the above problems, the scroll compressor of the present invention has an orbiting scroll disposed between a main body frame supporting a drive shaft and a fixed scroll, and provided on the side of the main body frame. The thrust bearing, which can move only in the axial direction, and the fixed scroll are sandwiched with a small gap between them. It is always biased in the direction of the orbiting scroll by using the intermediate fluid pressure between the discharge pressure and the suction pressure.
作 用
本発明は上記構成によって、圧縮室圧力が正常で順次移
行する圧縮室の圧縮圧力により旋回スクロールに作用し
てスラスト軸受の側に向かうスラスト力がスラスト軸受
に作用する付勢力よりも小さい場合は、旋回スクロール
と固定スクロールとの間で軸方向に微少隙間が保たれて
圧縮室の密封を維持し、効率の良い圧縮作用をすると共
に成る程度の負荷変動時や加減速運転時、高速運転時で
も旋回スクロールのジャンピングや傾きを防止して振動
の少ない静粛な圧縮運転を続ける。According to the above-mentioned structure, when the compression chamber pressure is normal and the thrust force acting on the orbiting scroll and directed toward the thrust bearing is smaller than the urging force acting on the thrust bearing due to the compression pressure in the compression chamber changing sequentially. A small gap is maintained in the axial direction between the orbiting scroll and the fixed scroll to maintain the sealing of the compression chamber and provide efficient compression, as well as during moderate load fluctuations, acceleration/deceleration operation, and high-speed operation. This prevents the orbiting scroll from jumping or tilting, allowing quiet compression operation with little vibration.
万−１液圧縮などが生じて瞬時的に圧縮室圧力が異常上
昇した場合は、旋回スクロールに作用するスラスト力が
スラスト軸受に作用する付勢力よりも大きくなり、スラ
スト軸受は本体フレームとの間の隙間を小さくする方向
に移動し、旋回スクロールと固定スクロールとの間の軸
方向隙間が大きくなる。その結果、圧縮室の密封を解除
して圧縮室圧力を降下せしめ、圧縮負荷を軽減し、再び
正常な圧縮運転に復帰させて動力損失の低減を図ると共
に、圧縮機の破損や摺動部の摩耗を防止して振動、騒音
、耐久性に優れた効率の良いスクロール圧縮機が提供で
きる。If compression chamber pressure suddenly rises abnormally due to liquid compression, the thrust force acting on the orbiting scroll becomes greater than the urging force acting on the thrust bearing, and the thrust bearing The axial clearance between the orbiting scroll and the fixed scroll increases. As a result, the compression chamber is unsealed, the pressure in the compression chamber is lowered, the compression load is reduced, and normal compression operation is restored to reduce power loss. It is possible to provide an efficient scroll compressor that prevents wear, reduces vibration, noise, and has excellent durability.
実施例
以下、本発明の実施例のスクロール圧縮機について、図
面を参照しながら説明する。Embodiments Hereinafter, scroll compressors according to embodiments of the present invention will be described with reference to the drawings.
第１図において、１は鉄製の密閉ケースで、その内部全
体は吐出室２に連通する高圧雰囲気となり、上部にモー
タ３、下部に圧縮部を配置し、モータ３の回転子３ａに
固定された駆動軸４を支承する圧縮部の本体フレーム５
により、密閉ケース？
°１の内部がモータ室６と吐出重重に仕切られている。In Fig. 1, reference numeral 1 denotes a sealed iron case, the entire interior of which is in a high-pressure atmosphere communicating with a discharge chamber 2, with a motor 3 in the upper part and a compression part in the lower part, which is fixed to the rotor 3a of the motor 3. Main body frame 5 of the compression part that supports the drive shaft 4
Is it a closed case? The inside of 1 is partitioned into a motor chamber 6 and a discharge weight.
本体フレーム５は軽量化と軸受部の熱発散を主目的とし
た熱伝導特性に優れたアルミニウム合金製で、その外周
部に溶接性に優れた鉄製ライナー８が焼ばめ固定され、
ライナー８の外周面が密閉ケース１に全周内接し部分的
に溶接固定されている。The main body frame 5 is made of an aluminum alloy with excellent heat conduction properties, with the main purpose of reducing weight and dissipating heat from the bearing part, and an iron liner 8 with excellent weldability is fixed to the outer periphery by shrink fitting.
The outer peripheral surface of the liner 8 is inscribed in the sealed case 1 all around and is partially fixed by welding.
モータ３の固定子３ｂの両端外周部は、密閉ケース１に
内接固定された軸受フレーム９と本体フレーム５によっ
て支持固定されている。駆動軸４は軸受フレーム９に設
けられた上部軸受１０、本体フレーム５の上端部に設け
られた下部軸受１１、本体フレーム５の中央部に設けら
れた主軸受１２、本体フレーム５の上端面とモータ３の
回転子３ａの下部端面との間に設けられたスラスト玉軸
受１３とで支持され、その下端部には駆動軸４の主軸か
ら偏心した偏心軸受１４が設けられている。The outer peripheral portions of both ends of the stator 3b of the motor 3 are supported and fixed by a bearing frame 9 and a main body frame 5 which are internally fixed to the sealed case 1. The drive shaft 4 includes an upper bearing 10 provided on a bearing frame 9, a lower bearing 11 provided on the upper end of the main body frame 5, a main bearing 12 provided in the center of the main body frame 5, and an upper end surface of the main body frame 5. It is supported by a thrust ball bearing 13 provided between the lower end surface of the rotor 3a of the motor 3, and an eccentric bearing 14 eccentric from the main axis of the drive shaft 4 is provided at its lower end.
本体フレーム５の下端面にはアルミニウム合金製の固定
スクロール１５が固定され、固定スクロール１５は渦巻
き状の固定スクロールラップ１５ａと鏡板１５ｂから成
り、鏡板１５ｂの中央部には固定スクロールラップ１５
ａの巻き始め部に開口する吐出ポート１６が吐出室２に
も開口して設けられ、固定スクロールラップ１５暑の外
周部には吸入室１７が設けられている。A fixed scroll 15 made of aluminum alloy is fixed to the lower end surface of the main body frame 5, and the fixed scroll 15 consists of a spiral fixed scroll wrap 15a and an end plate 15b.
A discharge port 16 that opens at the beginning of the winding is also opened to the discharge chamber 2, and a suction chamber 17 is provided at the outer periphery of the fixed scroll wrap 15.
固定スクロールラップ１５ｍに噛み合って圧縮室を形成
する渦巻き状の旋回スクロールランプ１１３ａと駆動軸
４の偏心軸受１４に支持された旋回軸１８ｂとを直立さ
せたラップ支持円板１８ｃとから成るアルミニウム合金
製の旋回スクロール１８は固定スクロール１５と本体フ
レーム５と駆動軸４とに囲まれて配置されており、旋回
軸１８ｂの外周部に高張力鋼材料から成るスリーブ１９
が焼ばめ固定され、ラップ支持円板１８ａの表面は硬化
処理されている。It is made of aluminum alloy and consists of a spiral orbiting scroll lamp 113a that engages with a fixed scroll wrap 15m to form a compression chamber, and a wrap support disk 18c that stands upright with a rotation shaft 18b supported by an eccentric bearing 14 of a drive shaft 4. The orbiting scroll 18 is arranged surrounded by the fixed scroll 15, the main body frame 5, and the drive shaft 4, and a sleeve 19 made of high-strength steel material is attached to the outer periphery of the orbiting shaft 18b.
are fixed by shrink fit, and the surface of the lap support disk 18a is hardened.
本体フレーム５に固定された平行ピン１９に拘束されて
軸方向にのみ移動が可能なスラスト軸受２０と固定スク
ロール１５の鏡板１５ｂとの間にはスペーサ２１が設け
られ、スペーサ２１の軸方向寸法は油膜による摺動面の
シール性向上のためにラップ支持円板１８ａの厚さより
も約０．０１５〜０．０２０ ｍｍ大きく設定されてい
る。A spacer 21 is provided between the thrust bearing 20, which is restrained by a parallel pin 19 fixed to the main body frame 5 and can only move in the axial direction, and the end plate 15b of the fixed scroll 15, and the axial dimension of the spacer 21 is The thickness is set approximately 0.015 to 0.020 mm larger than the thickness of the lap support disk 18a in order to improve the sealing performance of the sliding surface by an oil film.
駆動軸４の偏心軸受１４の底部と旋回スクロール１日の
旋回軸１８ｂの端部との間の偏心軸受空間３６とラップ
支持円板１８ｃの外周部空間３７とは旋回軸ｔａｂとラ
ップ支持円板１８ｃに設けられた油水Ａ３８ｍにより連
通されている。The eccentric bearing space 36 between the bottom of the eccentric bearing 14 of the drive shaft 4 and the end of the orbiting shaft 18b of the orbiting scroll 1 and the outer peripheral space 37 of the lap support disk 18c are defined by the orbiting axis tab and the lap support disk. It is communicated by oil water A38m provided at 18c.
スラスト軸受２０は第２図、第６図のように、その中央
部が２つの平行な直線部分２２とそれに連なる２つの円
弧状曲線部分２３から成る形状に貫通成形されている。As shown in FIGS. 2 and 6, the thrust bearing 20 is formed through a central portion into a shape consisting of two parallel straight portions 22 and two arcuate curved portions 23 connected thereto.
旋回スクロール自転阻止用のオルダムリング２４は、焼
結成形やインジェクション成形工法などに適した軽合金
や樹脂材料から成り、第４図のように両面が平行な薄い
環状板２４ｍとその一面に設けられた一対の平行キ一部
分２４ｂとから成り、環状板２４ｍの外輪郭は２つの平
行な直線部分２５とそれに連なる２つの円弧状曲線部分
２６から成り、直線部分２５は第６図のようにスラスト
軸受２０の直線部分２２に微少隙間で係合し、摺動可能
であり、平行キ一部分２４ｂの側面２４ｃは、直線部分
２５の中央部で直交し、第１図、第２図のように旋回ス
クロール１８のラップ支持円板１８ｏに設けられた一対
のキー溝７１に微少隙間で係合し、摺動可能な形状に設
定されている。The Oldham ring 24 for preventing rotation of the orbiting scroll is made of a light alloy or resin material suitable for sinter molding, injection molding, etc., and is provided on one side of a thin annular plate 24m with parallel surfaces as shown in Fig. 4. The outer contour of the annular plate 24m consists of two parallel straight parts 25 and two arcuate curved parts 26 connected thereto, and the straight parts 25 are thrust bearings as shown in FIG. The side surface 24c of the parallel key part 24b is orthogonal to the straight part 25 at the center of the straight part 25, and as shown in FIGS. 1 and 2, it is slidable. It is set in a shape that allows it to engage with a pair of key grooves 71 provided in the 18 lap support disks 18o with a small gap and to be able to slide.
なお、環状板２４ａの内輪郭は外輪郭に類似した形状で
ある。また、平行キ一部分２４ｂの付は根に設けられた
ヘコミ部２４ｄは潤滑油の通路にもなる。Note that the inner contour of the annular plate 24a has a shape similar to the outer contour. Further, a recessed portion 24d provided at the root of the parallel key portion 24b also serves as a passage for lubricating oil.
第１図、第３図のように、本体フレーム５とスラスト軸
受２ｏとの間には約０．１ｍｍ前後のレリース隙間２７
が設けられ、そのレリース隙間２７に対向して本体フレ
ーム５にも環状溝２８が設けられ、環状溝２８を囲んだ
ゴム製のシールリング７０が本体フレーム５とスラスト
軸受２０との間に装着されている。As shown in Figures 1 and 3, there is a release gap 27 of approximately 0.1 mm between the main body frame 5 and the thrust bearing 2o.
An annular groove 28 is also provided in the main body frame 5 opposite to the release gap 27, and a rubber seal ring 70 surrounding the annular groove 28 is installed between the main body frame 5 and the thrust bearing 20. ing.
モータ室６の上部と吐出室２とは密閉ケース１の側壁を
貫通して接続されたバイパス吐出管２９を介して連通し
、バイパス吐出管２９のモータ室６への開口位置は固定
子３ｂの上部コイルエンド３０の側面に対向し、バイパ
ス吐出管２９の上部開口端と密閉ケース１の上面に接続
された吐出管３１とは軸受フレーム５に設けられた抜き
穴３２、密閉ケース１の上面と軸受フレーム９との間に
配置され多数の***を有したパンチングメタル３３を介
して連通している。The upper part of the motor chamber 6 and the discharge chamber 2 communicate with each other via a bypass discharge pipe 29 that passes through the side wall of the sealed case 1 and is connected to the upper part of the motor chamber 6. The discharge pipe 31, which faces the side surface of the upper coil end 30 and is connected to the upper open end of the bypass discharge pipe 29 and the upper surface of the sealed case 1, has a hole 32 provided in the bearing frame 5, and the upper surface of the sealed case 1. It communicates with the bearing frame 9 via a punching metal 33 having a large number of small holes.
モータ室６の下部に設けられた吐出室油溜３４はモータ
室６の上部とモータ３の固定子３ｂの外周の一部をカッ
トして設けた冷却通路３５により連通されている。また
、吐出室油溜３４は本体フレーム５に設けられた油室Ｂ
５８ｂを経由して環状Ｗ１ｊ２８に通じると共に、オル
ダムリング２４が配置された旋回スクロール１８の背圧
室３９にも主軸受１２の摺動部微・少隙間を介して通じ
、更に偏心軸受１４に設けられた油溝Ａ４０ｍを介して
偏心軸受空間３６へも連通している。A discharge chamber oil reservoir 34 provided in the lower part of the motor chamber 6 is communicated with the upper part of the motor chamber 6 by a cooling passage 35 provided by cutting a part of the outer periphery of the stator 3b of the motor 3. Further, the discharge chamber oil reservoir 34 is an oil chamber B provided in the main body frame 5.
58b to the annular W1j28, and also to the back pressure chamber 39 of the orbiting scroll 18 in which the Oldham ring 24 is disposed, through a small gap in the sliding part of the main bearing 12, and further provided in the eccentric bearing 14. It also communicates with the eccentric bearing space 36 via the oil groove A40m.
また。本体フレーム５に設けられた油室Ｂ５８ｂは駆動
軸４の下部軸受１１に対応する下部軸受４ａの表面に設
けられた螺線状油溝４１にも通じており、螺線状油溝４
１の巻方向は駆動軸４が正回転する時に潤滑油の粘性を
利用したネジポンプ作用の生じるように設けられ、その
終端は下部軸受４ａの途中まで形成されている。Also. The oil chamber B58b provided in the main body frame 5 also communicates with the spiral oil groove 41 provided on the surface of the lower bearing 4a corresponding to the lower bearing 11 of the drive shaft 4.
The winding direction of No. 1 is provided so that a screw pump action using the viscosity of the lubricating oil occurs when the drive shaft 4 rotates forward, and the end thereof is formed halfway to the lower bearing 4a.
第６図、第７図のように、固定スクロール１５は吸入室
１７の両端を連通ずる円弧状の吸入通路４２が設けられ
、それに直交する円形の吸入穴４３が固定スクロールラ
ップ１５ｍの側面に対しても直角方向に設けられ、吸入
穴４３の底部は平面で吸入通路４２の側面にまで到達し
ている。第８図のように、吸入穴４３の中心は吸入通路
４２の底面４４とずれており、吸入通路４２への開口部
寸法Ｗ４５は吸入穴４３の直径寸法より小さく設けられ
ている。また、吸入穴４３にはアキュームレータ４６の
吸入管４７が接続されており、吸入穴４３の底面４４と
吸入管端面４８との間には吸入管４７の内径寸法および
吸入管端面４８と底面４４との間の吸入穴深さ寸法Ｌ４
９よりも大きく且つ開口寸法Ｗ４５よりも大きい円形薄
鋼板の逆止弁５０が配置されている。逆止弁５０の表面
は油濡れ特性が悪く弾力性に富んだテフロンまたはゴム
などがコーティングされている。As shown in FIGS. 6 and 7, the fixed scroll 15 is provided with an arc-shaped suction passage 42 that communicates both ends of the suction chamber 17, and a circular suction hole 43 perpendicular to the arc-shaped suction passage 42 is formed on the side surface of the fixed scroll wrap 15m. The bottom of the suction hole 43 is flat and reaches the side surface of the suction passage 42 . As shown in FIG. 8, the center of the suction hole 43 is offset from the bottom surface 44 of the suction passage 42, and the opening dimension W45 to the suction passage 42 is set smaller than the diameter dimension of the suction hole 43. Further, a suction pipe 47 of an accumulator 46 is connected to the suction hole 43, and between the bottom surface 44 of the suction hole 43 and the suction pipe end surface 48, the inner diameter dimension of the suction pipe 47 and the suction pipe end surface 48 and the bottom surface 44 are connected. Suction hole depth dimension L4 between
A check valve 50 made of a circular thin steel plate having a diameter larger than 9 and an opening size W45 is disposed. The surface of the check valve 50 is coated with Teflon or rubber, which has poor oil wettability and is highly elastic.
吸入室１７にも吐出室２にも連通しない第２圧縮室５１
と外周部空間３７とは、第２圧縮室５１に開口して鏡板
１５ｂに設けられた細径のインジェクション穴５２、鏡
板１５ｂと樹脂製の断熱カバー５３とで形成されたイン
ジェクション溝５４、外周部空間３７に開口した段付き
形状の油室Ｃ３８ｃとから成るインジェクション通路５
５で連通され、油室Ｃ３８ａの大径部５６には第９図に
示すような外周の一部に切欠き５７を有する薄鋼板製の
逆止弁５８とコイルスプリング５９とが配置されている
。コイルスプリング５９は断熱カバー５３に押えられて
逆止弁５８を常時付勢する。外周部空間３７への油室Ｃ
３８ｃの開口位置は、第１０図、第１１図に示す如く、
吐出ポート１６に連通ずる第３圧縮室６０の容積減少行
程が終了する近傍にまで旋回スクロール１８が移動した
（第１０図参照）時に外周部空間３７と油室Ｃ３８ｃと
が連通し、それ以外の時（第１１図参照）にはラップ支
持円板１１３ｃ＋によって遮断される位置に設けられて
いる。A second compression chamber 51 that does not communicate with either the suction chamber 17 or the discharge chamber 2
The outer peripheral space 37 includes a small diameter injection hole 52 opened to the second compression chamber 51 and provided in the end plate 15b, an injection groove 54 formed by the end plate 15b and a resin heat insulating cover 53, and an outer peripheral part. An injection passage 5 consisting of a stepped oil chamber C38c opening into the space 37
A check valve 58 made of a thin steel plate having a notch 57 in a part of its outer periphery and a coil spring 59 are disposed in the large diameter portion 56 of the oil chamber C38a as shown in FIG. . The coil spring 59 is pressed by the heat insulating cover 53 and always biases the check valve 58. Oil chamber C to outer peripheral space 37
The opening position of 38c is as shown in FIGS. 10 and 11.
When the orbiting scroll 18 moves close to the end of the volume reduction stroke of the third compression chamber 60 that communicates with the discharge port 16 (see FIG. 10), the outer peripheral space 37 and the oil chamber C38c communicate with each other, and the other At the time (see FIG. 11), it is provided at a position where it is blocked by the lap support disk 113c+.
第１２図において、横軸は駆動軸４の回転角度を示し、
縦軸は冷媒圧力を示し、吸入・圧縮・吐出過程における
冷媒ガスの圧力変化状態を示し、実線６２は正常圧力で
運転時の圧力変化を示し、点線６３は異常圧力上昇運転
時の圧力変化を表わす。In FIG. 12, the horizontal axis indicates the rotation angle of the drive shaft 4,
The vertical axis shows the refrigerant pressure, and shows the pressure change state of the refrigerant gas during the suction, compression, and discharge processes.The solid line 62 shows the pressure change during normal pressure operation, and the dotted line 63 shows the pressure change during abnormal pressure rise operation. represent.
第１３図において、横軸は駆動軸４の回転角度を示し、
縦軸は冷媒圧力を示し、実線６４は吐出室２にも吸入室
１７にも連通しない第２圧縮室５１ａ、５１ｂのインジ
ェクション穴５２ｍ。In FIG. 13, the horizontal axis indicates the rotation angle of the drive shaft 4,
The vertical axis indicates the refrigerant pressure, and the solid line 64 indicates the injection holes 52m of the second compression chambers 51a and 51b that do not communicate with either the discharge chamber 2 or the suction chamber 17.
５２ｂの開口位置における圧力変化を示し、点線６５は
吸入室１７に連通する第１圧縮室６１ａ。The dotted line 65 indicates the first compression chamber 61a that communicates with the suction chamber 17.
６１ｂ（第６図参照）の定点における圧力変化を示し、
−点鎖線６６は吐出室２に連通ずる第３圧縮室６０ａ、
６０ｂの定点における圧力変化を示し、二点鎖線６７は
第１圧縮室ｅｔｍ、６１ｂと第２圧縮室５１ｍ、５１ｂ
との間の定点における圧力変化を示し、２重点線６８は
背圧室３９の圧力変化を示す。61b (see Figure 6) shows the pressure change at a fixed point,
- the dotted chain line 66 indicates a third compression chamber 60a communicating with the discharge chamber 2;
60b shows the pressure change at a fixed point, and the two-dot chain line 67 indicates the first compression chamber etm, 61b and the second compression chamber 51m, 51b.
The double dotted line 68 shows the pressure change in the back pressure chamber 39.
第１４図は別の実施例のスクロール冷媒圧縮機の縦断面
図で、１０１ｍ、１０１ｂは鉄製の密閉ケース、１８０
は鉄製の本体フレーム１０５をボルト固定した軟鋼製の
仕切り板で、その外周面部で密閉ケースｌ０１ｍ、１０
１ｂと共に単一の溶接ビード１８１によって溶接密封さ
れ、密閉ケース１０１ｍ、１０Ｉｂ内を上側の吐出室１
０２と下側の駆動室１０６（低圧側）とに仕切っている
。FIG. 14 is a vertical cross-sectional view of a scroll refrigerant compressor of another embodiment, where 101 m and 101b are iron closed cases, 180
is a mild steel partition plate to which an iron main body frame 105 is fixed with bolts.
The upper discharge chamber 1 is welded and sealed together with 1b by a single weld bead 181, and the inside of the sealed case 101m and 10Ib is connected to the upper discharge chamber 1.
02 and a lower drive chamber 106 (low pressure side).
フレーム１０５に支承され、インバータ電源（図示せず
）によって運転制御されるモータ１０３により、回転駆
動される駆動軸１０４の上端部の偏心穴１３６には、旋
回スクロール１１８の旋回軸１１８ｂがはめ込まれ、旋
回スクロール１１８の自転阻止用のオルダムリング１２
４が、本体フレーム１０５に固定された平行ピン（ｒｆ
！１示せず）に拘束されて軸方向にのみ移動が可能なス
ラスト軸受１２０と旋回スクロール１１８の各溝に係合
し、旋回スクロール１１８にかみ合う固定スクロール１
１５が、仕切り板１８０にボルト固定され、固定スクロ
ール１１５の鏡板１１５ｂには吐出ポート１１６が設け
られ、鏡板１１５ｂの上面には、リードバルブ型の給油
通路制御弁装置１８２が取り付けられている。An orbiting shaft 118b of an orbiting scroll 118 is fitted into an eccentric hole 136 at the upper end of a drive shaft 104 which is supported by a frame 105 and is rotationally driven by a motor 103 whose operation is controlled by an inverter power supply (not shown). Oldham ring 12 for preventing the rotation of the orbiting scroll 118
4 is a parallel pin (rf
! A fixed scroll 1 that engages with each groove of the orbiting scroll 118 and a thrust bearing 120 that is restrained by the orbiting scroll 118 (not shown) and can move only in the axial direction.
15 is bolted to a partition plate 180, a discharge port 116 is provided on the end plate 115b of the fixed scroll 115, and a reed valve type oil supply passage control valve device 182 is attached to the upper surface of the end plate 115b.
スラスト軸受１２０は、シールリング１７０の弾性力で
常に旋回スクロール１１８の方へ付勢され、仕切り板１
８０に当接してその移動を規制されている。しかし、旋
回スクロール１１８を固定スクロール１１５に押し付け
て旋回スクロール１１８の円滑な旋回運動を阻害せぬよ
うに微少隙間（約０．０２０ ｍｍ ）を確保できる軸
方向の寸法設定がなされている。The thrust bearing 120 is always urged toward the orbiting scroll 118 by the elastic force of the seal ring 170, and the partition plate 1
80 and its movement is restricted. However, the dimensions in the axial direction are set such that a minute gap (approximately 0.020 mm) can be secured so that the orbiting scroll 118 is not pressed against the fixed scroll 115 and the smooth orbiting movement of the orbiting scroll 118 is not obstructed.
吐出室１０２の底部は吐出室油溜１３４となり、その上
部には多数の***を有した傘状のパンチングメタル１３
３が密閉ケース１０１ａに取り付けられ、密閉ケース１
０１−とパンチングメタル１３３との間には細樹脂線材
から成るフィルタ１８３が詰められている。吐出室１０
２は密閉ケース１０１−の上面に設けられた吐出管１３
１、外部の冷凍サイクル配管系をそれぞれ経て密閉ケー
ス１０１ｂの側面に設けられた吸入管１４７を通じ、低
圧側の駆動室１０６に連通している。また駆動室１０６
の底部にはモータ室油溜１８４が設けられている。The bottom of the discharge chamber 102 becomes a discharge chamber oil reservoir 134, and the upper part is an umbrella-shaped punching metal 13 with many small holes.
3 is attached to the sealed case 101a, and the sealed case 1
A filter 183 made of a thin resin wire is packed between the punching metal 133 and the punching metal 133. Discharge chamber 10
2 is a discharge pipe 13 provided on the upper surface of the sealed case 101-
1. It communicates with the drive chamber 106 on the low pressure side through an external refrigeration cycle piping system and a suction pipe 147 provided on the side surface of the sealed case 101b. In addition, the drive chamber 106
A motor chamber oil reservoir 184 is provided at the bottom of the motor chamber.
吐出室１０２にも吸入室１１７にも連通しない第２圧縮
室１５１と吐出室油溜１３４との間は、鏡板１１５ｂに
設けられた油吸い込み穴１８５、鏡板１１５ｂに薄鋼板
製のリード弁１８６と共に取り付けられた給油通路制御
弁装置１８２の弁押え１８７と鏡板１１５ｂとの間に形
成された弁室間１８８、リード弁１８６の打ち抜き穴１
８９、鏡板１１５ｂに設けられた極細通路のインジェク
ション穴１５２とから成る絞り通路を有した第１給油通
路によって連通している。Between the second compression chamber 151, which does not communicate with either the discharge chamber 102 or the suction chamber 117, and the discharge chamber oil reservoir 134, an oil suction hole 185 provided in the end plate 115b and a reed valve 186 made of a thin steel plate are provided in the end plate 115b. Between the valve chambers 188 formed between the valve holder 187 and the end plate 115b of the attached oil supply passage control valve device 182, and the punched hole 1 of the reed valve 186
89, and the injection hole 152, which is an extremely narrow passage provided in the end plate 115b, communicates with the first oil supply passage having a throttle passage.
固定スクロール１１５とスラスト軸受１２０との間に配
置された旋回スクロール１１８の旋回スクロールラップ
１１８ａを支持するラップ支持円盤１１８ｂと、スラス
ト軸受１２０と駆動軸１０４とで形成された背圧室１３
９との間は、第１給油通路の途中から分岐して弁室間１
８８、リード弁１８６の打ち抜き穴１８９暑、鏡板１１
５ｂに設けられた油室Ａ１３８ｍ、仕切り板１８０に設
けられた極細通路の油室Ｂ１３１３ｂ１本体フレーム１
０５に設けられた油室Ｃ１３８ｃ、スラスト軸受１２０
と本体フレーム１０５との間に設けられ、その外周部を
ゴム製のシールリング１７０で支持・密封されたレリー
ス隙間１２７、スラスト軸受１２０に設けられた油室Ｒ
１３８ｄとで構成される給油通路により連通している。A back pressure chamber 13 formed by a wrap support disk 118b that supports the orbiting scroll wrap 118a of the orbiting scroll 118 disposed between the fixed scroll 115 and the thrust bearing 120, the thrust bearing 120, and the drive shaft 104.
9 is branched from the middle of the first oil supply passage and is connected to the valve chamber 1.
88, punched hole 189 of reed valve 186, mirror plate 11
Oil chamber A138m provided in 5b, oil chamber B1313b1 with extremely narrow passage provided in partition plate 180, main body frame 1
Oil chamber C138c provided in 05, thrust bearing 120
A release gap 127 is provided between the main body frame 105 and the outer periphery thereof is supported and sealed by a rubber seal ring 170, and an oil chamber R is provided in the thrust bearing 120.
138d through a fuel supply passage.
背圧室１３９と低圧側の駆動室との間は主軸受１１２の
軸受隙間、偏心軸受１１４の隙間、駆動軸１０４に設け
られた偏心油室１９０と、横部穴１９１、駆動軸１０４
を支承し、本体フレーム１０５の下端に設けられた下部
軸受１９２と主軸受１１２との間の軸受油溜１９３、下
部軸受１９２の軸受隙間とで構成される絞り通路を有し
た第１潤滑通路により連通している。Between the back pressure chamber 139 and the drive chamber on the low pressure side are the bearing gap of the main bearing 112, the gap of the eccentric bearing 114, the eccentric oil chamber 190 provided in the drive shaft 104, the side hole 191, and the drive shaft 104.
The first lubrication passage supports the main body frame 105 and has a throttle passage composed of a bearing oil reservoir 193 between the lower bearing 192 and the main bearing 112 provided at the lower end of the main body frame 105, and a bearing clearance of the lower bearing 192. It's communicating.
また、背圧室１３９と吸入室１１７との間は、スラスト
軸受１２０とランプ支持円板１１８ｂとの摺動面や、オ
ルダムリング１２４の摺動面を介して構成される第２潤
滑通路によって連通している。Further, the back pressure chamber 139 and the suction chamber 117 are communicated through a second lubrication passage formed through the sliding surface of the thrust bearing 120 and the lamp support disk 118b and the sliding surface of the Oldham ring 124. are doing.
以上のように構成されたスクロール気体圧縮機について
、その動作を説明する。The operation of the scroll gas compressor configured as above will be explained.
第１図〜第１３図において、モータ３によって駆動軸４
が回転駆動すると旋回スクロール１８が旋回運動をし、
圧縮機に接続した冷凍サイクルから潤滑油を含んだ吸入
冷媒ガスが、アキュームレータ４６に接続した吸入管４
７、吸入穴４３、吸入通路４２を順次経て吸入室１７に
流入し、旋回スクロール１８と固定スクロール１５との
間に形成された第１圧縮室６１ｍ、６１ｂを経て圧縮室
内に閉じ込められ、常時密閉空間となる第２圧縮室５１
ａ、５１ｂ、第３圧縮室６０ａ、Ｓｏｂへと順次移送圧
縮され、中央部の吐出ポート１６を経て吐出室２へと吐
出される。1 to 13, the drive shaft 4 is driven by the motor 3.
When is driven to rotate, the orbiting scroll 18 makes an orbiting motion,
Suction refrigerant gas containing lubricating oil from the refrigeration cycle connected to the compressor flows into the suction pipe 4 connected to the accumulator 46.
7. It flows into the suction chamber 17 through the suction hole 43 and the suction passage 42 sequentially, passes through the first compression chambers 61m and 61b formed between the orbiting scroll 18 and the fixed scroll 15, and is confined in the compression chamber, so that it is always sealed. Second compression chamber 51 serving as space
a, 51b, the third compression chamber 60a, and Sob, where it is sequentially transferred and compressed, and is discharged into the discharge chamber 2 through the discharge port 16 in the center.
潤滑油を含んだ吐出冷媒ガスは圧縮機外部へ配管された
バイパス吐出管２９を経て再び圧縮機内のモータ室６に
帰還した後、外部の冷凍サイクルへ吐出管３１から排出
されるが、モータ室６に流入する際に、モータ３の上部
コイルエンド３０の側面に衝突してモータ巻き線の表面
に付着する。The discharged refrigerant gas containing lubricating oil returns to the motor chamber 6 inside the compressor via the bypass discharge pipe 29 piped to the outside of the compressor, and then is discharged from the discharge pipe 31 to the external refrigeration cycle. 6, it collides with the side surface of the upper coil end 30 of the motor 3 and adheres to the surface of the motor winding.
これにより、潤滑油の一部が分離され、その後−受フレ
ーム９に設けられた抜き穴３２を通過する際に、流れ方
向を変えたり、パンチングメタル３３の***を通過する
際に、潤滑油の慣性力や表面付着などにより潤滑油が効
果的に分離される。As a result, a part of the lubricating oil is separated, and then the lubricating oil is changed in flow direction when passing through the punch hole 32 provided in the receiving frame 9, or when passing through the small hole in the punching metal 33. Lubricating oil is effectively separated due to inertia and surface adhesion.
吐出ガスから分離された潤滑油の一部は、上部軸受の摺
動面を潤滑した後、残りの潤滑油と共に冷却通路３５を
通り、モータ３を冷却しながら下部の吐出室油溜３４に
収集される。A part of the lubricating oil separated from the discharge gas lubricates the sliding surface of the upper bearing, and then passes through the cooling passage 35 along with the remaining lubricating oil, and is collected in the lower discharge chamber oil sump 34 while cooling the motor 3. be done.
吐出室油溜３４の潤滑油は、駆動軸４の下部軸部４ｍの
表面に設けられた螺線状油溝４１のネジポンプ作用によ
り、スラスト玉軸受１３へ給油され、下部軸部４ａの端
部の微少軸受隙間を潤滑油が通過する際に、その油膜の
シール作用により、モータ室６の吐出冷媒ガス雰囲気と
主軸受１２の上流側空間とが遮断される。The lubricating oil in the discharge chamber oil sump 34 is supplied to the thrust ball bearing 13 by the screw pump action of the spiral oil groove 41 provided on the surface of the lower shaft portion 4m of the drive shaft 4, and is supplied to the thrust ball bearing 13 at the end of the lower shaft portion 4a. When the lubricating oil passes through the minute bearing gap, the sealing action of the oil film blocks the discharged refrigerant gas atmosphere of the motor chamber 6 from the upstream space of the main bearing 12.
吐出室油溜３４の溶解吐出冷媒ガスを含んだ潤滑油は、
主軸受１２の微少隙間を通過する際に、吐出圧力と吸入
圧力との中間圧力に減圧され、背圧室３９に流入する。The lubricating oil containing the dissolved discharged refrigerant gas in the discharge chamber oil sump 34 is
When passing through the small gap in the main bearing 12, the pressure is reduced to an intermediate pressure between the discharge pressure and the suction pressure, and the fluid flows into the back pressure chamber 39.
その後、偏心軸受１４の油溝Ａ ４０ ａ １偏心軸受
室間３６、旋回スクロール１８を通る油室Ａ３８を経て
外周部空間３７に流入し、更に間欠的に開口する油室Ｃ
３８ｃ、インジェクション溝５４、インジェクション穴
５２ａ。Thereafter, the oil groove A 40 a of the eccentric bearing 14 flows into the outer circumferential space 37 via the oil chamber A 38 that passes through the eccentric bearing chamber 36 and the orbiting scroll 18, and then the oil chamber C that opens intermittently.
38c, injection groove 54, injection hole 52a.
５２ｂを経て第２圧縮室５ｔａ、５１ｂに流入し、その
通路途中の各摺動面を潤滑する。It flows into the second compression chambers 5ta and 51b via 52b, and lubricates each sliding surface in the middle of the passage.
また、吐出室油溜３４は、環状溝２８やレリース隙間２
７とも通じているので、スラスト軸受２０はその背圧力
により付勢されてスペーサ２１の端部に当接する。そし
て、旋回スクロール１８のラップ支持円板１８ｃは、ス
ラスト軸受２０と固定スクロール１５の鏡板１５ｂとの
間で微少隙間を保持されて円滑に摺動すると共に、固定
スクロールラップ１５ａの端面とラップ支持円板１８ｃ
との間、ならびに、旋回スクロールラップ１８ａの端面
と鏡板１５ｂとの間の隙間も微少に保持されて隣接する
圧縮室間の気体漏れを少なくする。In addition, the discharge chamber oil reservoir 34 is connected to the annular groove 28 and the release gap 2.
7, the thrust bearing 20 is urged by the back pressure and comes into contact with the end of the spacer 21. The lap support disk 18c of the orbiting scroll 18 slides smoothly with a slight gap maintained between the thrust bearing 20 and the end plate 15b of the fixed scroll 15, and the end surface of the fixed scroll wrap 15a and the lap support disk 18c. Board 18c
Also, the gaps between the end face of the orbiting scroll wrap 18a and the end plate 15b are kept small to reduce gas leakage between adjacent compression chambers.
第２圧縮室５１ｇ、５１ｂのインジェクション穴５２ａ
、５２ｂ開口部は、第１３図の如くの圧力変化６４をし
、吐出室２の圧力に追従して変化する背圧室圧力６８よ
りも瞬時的に高いが平均圧力が低い。そのため背圧室３
９からの潤滑油は、間欠的に第２圧 室５１ａ、５１ｂ
に流入し、また正常運転時の背圧室圧力６８よりも瞬時
的に高い第２圧縮室５１ｍ、５１ｂ内の圧縮冷媒ガスは
、細径のインジェクション穴５２ｍ、５２ｂど減衰され
て瞬時的なインジェクション溝５４への逆流が少なく、
インジェクション溝５４内の圧力が背圧室圧力６８より
も高くならない。Injection holes 52a of second compression chambers 51g and 51b
, 52b, the pressure changes 64 as shown in FIG. 13, and the average pressure is lower than the back pressure chamber pressure 68, which changes in accordance with the pressure in the discharge chamber 2, although it is instantaneously higher. Therefore, back pressure chamber 3
The lubricating oil from 9 is intermittently supplied to the second pressure chambers 51a and 51b.
The compressed refrigerant gas in the second compression chambers 51m, 51b, which flows into the back pressure chamber 68 during normal operation and which is instantaneously higher than the back pressure chamber pressure 68 during normal operation, is attenuated by the small diameter injection holes 52m, 52b and instantaneously injected. There is less backflow to the groove 54,
The pressure within the injection groove 54 does not become higher than the back pressure chamber pressure 68.
第２圧縮室５１ｍ、５１ｂにインジェクションされた潤
滑油は、吸入冷媒ガスと共に圧縮室に流入した潤滑油と
合流し、隣接する圧縮室間の微少隙間を油膜により密封
して圧縮気体漏れを防ぎ、圧縮室間の摺動面を潤滑しな
がら圧縮気体と共に吐出室２に再び吐出される。The lubricating oil injected into the second compression chambers 51m and 51b joins with the lubricating oil that has flowed into the compression chambers together with the suction refrigerant gas, and the minute gaps between adjacent compression chambers are sealed with an oil film to prevent compressed gas leakage. The compressed gas is again discharged into the discharge chamber 2 while lubricating the sliding surfaces between the compression chambers.
また、背圧室３９に差圧給油された潤滑油は、シールリ
ング７０の弾性力と共に中間圧力の付勢力を旋回スクロ
ール１８に作用させて、ラップ支持円板１８ａを鏡板１
５ｂとの摺動面に押圧油膜シールし、外周部空間３７と
吸入室１７との間の連通を遮断すると共に、スラスト軸
受２０とラップ支持円板１８ａとの摺動面の隙間も潤滑
シールする。In addition, the lubricating oil supplied to the back pressure chamber 39 exerts an intermediate pressure urging force on the orbiting scroll 18 together with the elastic force of the seal ring 70 to move the lap support disk 18a onto the end plate 1.
A pressure oil film is sealed on the sliding surface between the thrust bearing 20 and the lap support disk 18a, thereby blocking communication between the outer peripheral space 37 and the suction chamber 17, and sealing the gap between the sliding surface between the thrust bearing 20 and the lap support disk 18a with lubrication. .
また、圧縮機の冷時始動後しばらくの間は、第１２図、
第１３図から理解できるように、吐出室２の圧力が第２
圧縮室５１ｍ、５１ｂの圧力よりも低く、圧縮途中の冷
媒ガスが第２圧縮室５１ａ。In addition, for a while after the compressor starts cold, as shown in Fig. 12,
As can be understood from Fig. 13, the pressure in the discharge chamber 2 is
The refrigerant gas is in the second compression chamber 51a, which is lower than the pressure in the compression chambers 51m and 51b and is in the middle of being compressed.
５１ｂからインジェクション通路５５を経て背圧室３９
に逆流しようとするが、逆止弁５８の逆止作用にて外周
部空間３７への逆流が阻止され、吐出室油溜３４の潤滑
油は吐出室２の圧力上昇と共に背圧室３９、外周部空間
３７にまで差圧給油される。51b to the back pressure chamber 39 via the injection passage 55.
However, the backflow to the outer circumferential space 37 is prevented by the non-return action of the check valve 58, and as the pressure in the discharge chamber 2 increases, the lubricating oil in the discharge chamber 2 flows into the back pressure chamber 39 and the outer circumference. Differential pressure oil is supplied to the inner space 37.
したがって、冷時始動初期のスラスト軸受２０への背圧
付勢力が圧縮室圧力により生じ、旋回スクロール１８を
固定スクロール１５から離反させようとするスラスト荷
重に抗しながらスラスト軸受２０が微少に後退して、旋
回スクロール１８と固定スクロール１５との間の軸方向
隙間を拡大する。これにより圧縮空間に漏れを生じて圧
縮室圧力を下げ、始動初期の圧縮負荷を軽減する。Therefore, a back pressure urging force is generated on the thrust bearing 20 by the compression chamber pressure at the initial stage of cold start, and the thrust bearing 20 moves slightly backward while resisting the thrust load that tends to separate the orbiting scroll 18 from the fixed scroll 15. As a result, the axial clearance between the orbiting scroll 18 and the fixed scroll 15 is expanded. This causes leakage in the compression space, lowering the compression chamber pressure and reducing the compression load at the initial stage of startup.
その後、吐出室２の圧力上昇に伴い、外周部空間２１の
潤滑油は、コイルスプリング５′９の付勢力に抗してイ
ンジェクション穴５２ａ、５２ｂから第２圧縮室５１ａ
、５１ｂへインジェクションされる。Thereafter, as the pressure in the discharge chamber 2 increases, the lubricating oil in the outer peripheral space 21 flows from the injection holes 52a and 52b into the second compression chamber 51a against the urging force of the coil spring 5'9.
, 51b.
また、冷時始動初期や定常運転時に、瞬時的な液圧縮が
生じた場合の圧縮室圧力は、第１２図の点線６３のよう
に異常な圧力上昇と過圧縮が生じるが、吐出室２とそれ
に連通ずる高圧空間容積が大きいため、吐出室圧力の上
昇は極めて小さい。In addition, when instantaneous liquid compression occurs at the initial stage of a cold start or during steady operation, the pressure in the compression chamber will be abnormally increased and overcompressed as shown by the dotted line 63 in Fig. 12. Since the volume of the high-pressure space communicating therewith is large, the rise in the discharge chamber pressure is extremely small.
また、液圧縮により第２圧縮室５１ｍ、５１ｂに連通ず
るインジェクション溝５４なども異常圧力上昇するが、
細径の油室Ｃ３８ｃの絞り効果と逆止弁５８の逆止作用
により、゛外周部空間３７とインジェクション溝５４と
の間は遮断される。その結果、背圧室３９の圧力は変わ
らず、スラスト軸受２０の背面に作用する背圧付勢力に
も変動がない。その結果、液圧縮時には、旋回スクロー
ル１８に作用する過大なスラスト力によって上述のよう
にスラスト軸受２０が後退し、圧縮室圧力が降下してそ
の後は正常運転を継続する。Furthermore, due to liquid compression, the pressure in the injection groove 54 communicating with the second compression chambers 51m and 51b also increases abnormally.
Due to the throttling effect of the small diameter oil chamber C38c and the check action of the check valve 58, the space between the outer peripheral space 37 and the injection groove 54 is cut off. As a result, the pressure in the back pressure chamber 39 does not change, and the back pressure urging force acting on the back surface of the thrust bearing 20 does not change. As a result, during liquid compression, the thrust bearing 20 retreats as described above due to the excessive thrust force acting on the orbiting scroll 18, the pressure in the compression chamber decreases, and normal operation continues thereafter.
なお、液圧縮途中でスラスト軸受２０が後退することに
より、圧縮室圧力は第１２図の一点鎖線６３ｍの如く途
中で降圧する。In addition, as the thrust bearing 20 retreats during liquid compression, the pressure in the compression chamber drops midway as shown by the dashed line 63m in FIG.
圧縮機停止後は、圧縮室内圧力により旋回スクロール１
８に逆旋回トルクが生じ、旋回スクロール１８が逆旋回
して吐出冷媒ガスが吸入側に逆流する。この吐出冷媒ガ
スの逆流に追従して、逆止弁５０が第６図の位置から第
７図の位置に移動し、逆止弁５０の表面に施されたテフ
ロン被膜により、吸入管端面４８を密封して吐出冷媒ガ
スの逆流を制止し、旋回スクロール１８の逆旋回が停止
し、吸入通路４２と吐出ポート１６との間の空間は吐出
圧力を保持する。After the compressor stops, the orbiting scroll 1
A reverse rotation torque is generated at 8, the orbiting scroll 18 rotates in the reverse direction, and the discharged refrigerant gas flows back to the suction side. Following this backflow of the discharged refrigerant gas, the check valve 50 moves from the position shown in FIG. 6 to the position shown in FIG. The airtight seal prevents the reverse flow of the discharged refrigerant gas, the reverse rotation of the orbiting scroll 18 is stopped, and the space between the suction passage 42 and the discharge port 16 maintains the discharge pressure.
また、インジェクション通路の逆止弁５８を境にして圧
縮室に連通する通路は、吐出圧力になるが、外周部空間
３７と背圧室ａ９との間の空間はしばらくの間、中間圧
力を保持し、吐出室油溜３４からの潤滑油微少流入によ
り、次第に吐出圧力に近づく。圧縮機停止時、旋回スク
ロール１８は逆転し、第３圧縮室６０ａ、ｓｏｂが拡大
した位置に停止し、油水Ｃ３８ｃの外周部空間３７への
開口部は、ラップ支持円板１８ｃにより遮断される。圧
縮機停止後は、コイルスプリング５９の付勢力によって
も逆止弁５８がインジェク通路５５を遮断するので、外
周部空間３７から圧縮室への潤滑油流入がない。In addition, the passage communicating with the compression chamber with the check valve 58 of the injection passage as a border has a discharge pressure, but the space between the outer peripheral space 37 and the back pressure chamber a9 maintains an intermediate pressure for a while. However, due to the slight inflow of lubricating oil from the discharge chamber oil reservoir 34, the pressure gradually approaches the discharge pressure. When the compressor is stopped, the orbiting scroll 18 reverses and stops at a position where the third compression chamber 60a and sob are enlarged, and the opening of the oil/water C38c to the outer peripheral space 37 is blocked by the lap support disk 18c. After the compressor is stopped, the check valve 58 blocks the injection passage 55 due to the biasing force of the coil spring 59, so no lubricating oil flows into the compression chamber from the outer peripheral space 37.
また、圧縮機運転中、主軸受１２の給油上流側は、吐出
室油溜ａ４に連通し、給油下流側は中間圧力状態の背圧
室３９に連通してその間に差圧が生じ、モータ３の回転
子３ａを固定した駆動軸４力旋回スクロール１８の方向
へ付勢される。この付勢力は、スラスト玉軸受１３を介
して本体フレーム５に支持され、駆動軸４が上部軸受１
ｏ、主軸受１２との間の隙間の範囲内で倒れるのを規制
し、軸受の片当りを防止する。Also, during compressor operation, the oil supply upstream side of the main bearing 12 communicates with the discharge chamber oil sump a4, and the oil supply downstream side communicates with the back pressure chamber 39 in an intermediate pressure state, and a pressure difference is generated between them, and the motor 3 The drive shaft to which the rotor 3a of the rotor 3a is fixed is urged in the direction of the four-power orbiting scroll 18. This biasing force is supported by the main body frame 5 via the thrust ball bearing 13, and the drive shaft 4 is supported by the upper bearing 1.
o. To prevent the bearing from falling down within the gap between it and the main bearing 12, and to prevent uneven bearing contact.
また、圧縮機運転時の温変上昇により、アルミニウム合
金製の本体フレーム５は熱膨張して鉄製のライナー８を
拡管し、ライナー８の外周面と密閉ケース１の内壁との
密着を強めて吐出室油溜３４と吐出室２との間の気密を
向上させると共に、本体フレーム５と密閉ケース１との
固定を強めて互いの剛性向上に役立つ。Furthermore, due to temperature fluctuations during compressor operation, the aluminum alloy body frame 5 thermally expands and expands the iron liner 8, which strengthens the close contact between the outer peripheral surface of the liner 8 and the inner wall of the sealed case 1, and discharges. This improves the airtightness between the chamber oil reservoir 34 and the discharge chamber 2, and strengthens the fixation between the main body frame 5 and the sealed case 1, which helps to improve the rigidity of each other.
また、上記実施例では吐出室油溜３４の潤滑油を第２圧
縮室５１ｍ、５１ｂに油インジェクションしたが、圧縮
機使用条件などにより吸入室１７に通じる第１圧縮室６
１ｍ、６１ｂに油インジェクションしてもよい。In the above embodiment, the lubricating oil in the discharge chamber oil sump 34 was injected into the second compression chambers 51m and 51b.
Oil injection may be performed at 1 m and 61b.
また、上記実施例ではスラスト軸受２２の背面に設けた
レリース隙間２７や環状溝２８に吐出室油溜３４の潤滑
油を導入したが、モータ室６の吐出冷媒ガスや第２圧縮
室５１ｍ、５１ｂなどから中間圧力冷媒ガスを導入して
もよい。Furthermore, in the above embodiment, the lubricating oil from the discharge chamber oil reservoir 34 is introduced into the release gap 27 and the annular groove 28 provided on the back surface of the thrust bearing 22, but the lubricating oil from the discharge chamber oil sump 34 and the discharged refrigerant gas from the motor chamber 6 and the second compression chambers 51m and 51b are An intermediate-pressure refrigerant gas may be introduced from, for example.
また、上記実施例ではスラスト軸受２２への予圧付勢力
をシールリング７０の弾性力を利用したが、スラスト軸
受２２の背圧面積が不足する場合などは、バネ装置など
で付勢力を付加してもよい。Furthermore, in the above embodiment, the elastic force of the seal ring 70 is used to preload the thrust bearing 22, but if the back pressure area of the thrust bearing 22 is insufficient, a spring device or the like may be used to apply the biasing force. Good too.
次に、第１４図、第１５図により、本発明の他の実施例
の動作について説明する。Next, the operation of another embodiment of the present invention will be explained with reference to FIGS. 14 and 15.
第１４図、第１５図において、モータ１０３によって駆
動軸１０４が回転駆動を始めると、旋回スクロール１１
８が旋回運動をし、圧縮機に接続した冷凍サイクルから
吸入冷媒ガスが吸入管１４７を通して駆動室に流入し、
その中に含まれる潤滑油の一部が分離された後、吸入通
路を経て吸入室１１−７に吸入される。この吸入冷媒ガ
スは、旋回スクロール１１８と固定スクロール１１５と
の間に形成され、吸入室１１７に通じる第１圧縮室を経
て圧縮室内に閉じ込められ、旋回スクロール１１８の旋
回運動に伴って第２圧縮室１５１ｍ。14 and 15, when the drive shaft 104 starts rotating by the motor 103, the orbiting scroll 11
8 makes a rotating motion, and suction refrigerant gas flows into the drive chamber through the suction pipe 147 from the refrigeration cycle connected to the compressor.
After a part of the lubricating oil contained therein is separated, it is sucked into the suction chamber 11-7 through the suction passage. This suction refrigerant gas is formed between the orbiting scroll 118 and the fixed scroll 115, passes through a first compression chamber communicating with the suction chamber 117, and is confined in the compression chamber. 151m.
１５１ｂ、第３圧縮室へと順次移送圧縮され、中央部の
吐出ポート１１６を経て吐出室１０２へと吐出される。151b, and is sequentially transferred and compressed to the third compression chamber, and is discharged to the discharge chamber 102 through the discharge port 116 in the center.
吐出冷媒ガス中に含まれる潤滑油の一部は、その自重お
よびパンチングメタル１３３の***や細樹脂線から成る
フィルタ１８３を通過する際にその表面などに付着など
して吐出冷媒ガスから分離し、吐出室油溜１３４に収集
される。残りの潤滑油は、吐出冷媒ガスと共に吐出管１
３１を経て外部の冷凍サイクルへ搬出され、吸入冷媒ガ
スと共に吸入管１４７を通って圧縮機内に帰還する。A part of the lubricating oil contained in the discharged refrigerant gas is separated from the discharged refrigerant gas due to its own weight and adheres to the surface of the punched metal 133 when passing through the small holes of the punching metal 133 and the filter 183 made of thin resin wire. The oil is collected in the discharge chamber oil sump 134. The remaining lubricating oil flows into the discharge pipe 1 along with the discharged refrigerant gas.
31 to the external refrigeration cycle, and returns to the compressor through the suction pipe 147 together with the suction refrigerant gas.
圧縮機の冷時始動後しばらくの間は、上述のように吐出
室１０２の圧力が第２圧縮室１５１ｍ。For a while after the cold start of the compressor, the pressure in the discharge chamber 102 remains at the second compression chamber 151m as described above.
１５１ｂの圧力よりも低いので、吐出室油溜１３４の潤
滑油は第１給油通路を通じて差圧給油されず、また、逆
止弁効果によって第２圧縮室１５１ｍ。151b, the lubricating oil in the discharge chamber oil reservoir 134 is not supplied under differential pressure through the first oil supply passage, and due to the check valve effect, the lubricating oil in the discharge chamber oil sump 134 is supplied to the second compression chamber 151m.
１５１ｂから圧縮途中気体が吐出室油溜１３４に逆流も
せず、スラスト軸受１２０のレリース隙間１２７や旋回
スクロール１１８の背圧室１３９に流入することもなく
、各摺動部の残留潤滑油によって各摺動面が潤滑される
。The gas during compression does not flow back into the discharge chamber oil reservoir 134 from 151b, nor does it flow into the release gap 127 of the thrust bearing 120 or the back pressure chamber 139 of the orbiting scroll 118, and the residual lubricating oil in each sliding part Moving surfaces are lubricated.
また、背圧室１３９やレリース隙間１２７の圧力が低い
ので上述のように始動初期にはスラスト軸受１２０が微
少に後退して始動初期負荷を軽減する。In addition, since the pressure in the back pressure chamber 139 and the release gap 127 is low, the thrust bearing 120 moves back slightly at the initial stage of startup to reduce the initial startup load as described above.
圧縮機の冷時始動後しばらくの後、吐出室１０２の圧力
が第２圧縮室１５１ａ、１５１ｂの圧力以上に上昇した
後、吐出室油溜１３４の潤滑油は、給油通路制御弁装置
１８２のリード弁１８６の付勢力に抗して第１給油通路
を経由する。そして漸次減圧され、第２圧縮室１５１ｍ
、１５１ｂに差圧給油されると共に、第１給油通路の途
中から分岐して構成される第２給油通路の油室１３８ｍ
。After a while after the cold start of the compressor, the pressure in the discharge chamber 102 rises above the pressure in the second compression chambers 151a and 151b, and then the lubricating oil in the discharge chamber oil sump 134 is transferred to the lead of the oil supply passage control valve device 182. The oil passes through the first oil supply passage against the biasing force of the valve 186. Then, the pressure is gradually reduced, and the second compression chamber 151m
, 151b, and an oil chamber 138m of a second oil supply passage which is branched from the middle of the first oil supply passage.
.
１３８ｂ、１３８ａを経て漸次減圧され、吐出側圧力と
吸入側圧力との中間圧力に調整されてレリース隙間１２
７と背圧室１３９に差圧給油される。The pressure is gradually reduced through 138b and 138a, and the pressure is adjusted to an intermediate pressure between the discharge side pressure and the suction side pressure, and the release gap 12
7 and the back pressure chamber 139 are supplied with differential pressure oil.
第２圧縮室１５１ｍ（１５１ｂ）に差圧給油された潤滑
油は、吸入ガスと共に圧縮室に流入した潤滑油と合流し
、隣接する圧縮室間の微小隙間を油膜により密封して圧
縮気体漏れを防ぎ、圧縮室間の摺動面を潤滑しながら圧
縮気体と共に吐出室１０２に再び吐出される。The lubricating oil supplied to the second compression chamber 151m (151b) at a differential pressure merges with the lubricating oil that has flowed into the compression chamber together with the suction gas, and the minute gap between adjacent compression chambers is sealed with an oil film to prevent compressed gas leakage. The compressed gas is then discharged into the discharge chamber 102 again together with the compressed gas while lubricating the sliding surfaces between the compression chambers.
レリース隙間１２７と背圧室１３９に給油された中間圧
力の潤滑油は、旋回スクロール１１８へ背圧力による付
勢力を与えて圧縮室内圧力により、固定スクロール１１
５から離反しようとする旋回スクロフル１１８に作用す
る下向きのスラスト力を軽減し、旋回スクロール１１８
とスラスト軸受１２０との間の摺動面に作用するスラス
ト荷重を小さくすると共に、スラスト軸受１２０を付勢
して仕切り板に当接させ、固定スクロール１１５とスラ
スト軸受１２０との間に旋回スクロール１１８を微少隙
間で挾み、旋回スクロール１１８の円滑な旋回運動を可
能にする。また、背圧室１３９の背圧力は旋回スクロー
ル１１８がスラスト軸受１２０から離反しないように調
整されているので、背圧室１３９と吸入室１１７とは常
時密接し、潤滑油はこの摺動面を通過する際に減圧され
た後、オルダムリング１２４の摺動面を潤滑して吸入冷
媒ガスに混入し、再び圧縮室に流入する。The intermediate pressure lubricating oil supplied to the release gap 127 and the back pressure chamber 139 applies an urging force to the orbiting scroll 118 due to the back pressure, and the pressure in the compression chamber causes the fixed scroll 11 to
The downward thrust force acting on the orbiting scroll 118 that is trying to move away from the orbiting scroll 118 is reduced, and the orbiting scroll 118
In addition to reducing the thrust load acting on the sliding surface between the fixed scroll 115 and the thrust bearing 120, the thrust bearing 120 is urged to contact the partition plate, and the orbiting scroll 118 is placed between the fixed scroll 115 and the thrust bearing 120. are sandwiched by a minute gap to enable smooth orbiting movement of the orbiting scroll 118. In addition, the back pressure in the back pressure chamber 139 is adjusted so that the orbiting scroll 118 does not separate from the thrust bearing 120, so the back pressure chamber 139 and the suction chamber 117 are always in close contact with each other, and the lubricating oil covers this sliding surface. After being depressurized as it passes through, it lubricates the sliding surface of the Oldham ring 124, mixes it into the suction refrigerant gas, and flows into the compression chamber again.
また、残りの潤滑油は、第１潤滑通路を通じて旋回軸１
１８ｂと偏心°穴１３６との隙間、偏心穴１３６、偏心
油穴１９０１横油穴１９１を通る給油通路と主軸受１１
２の隙間とを経て軸受油溜１９３に流入し、下部軸受１
９２の微少隙間を通して最終減圧される。そして駆動室
１０６に流入し、その一部は吸入冷媒ガスに混入して再
び圧縮室へ流入するが、残りの潤滑油はモータ室油溜１
８４に収集される。モータ室油溜１８４の潤滑油は、密
閉ケース１０１ｂを介して自然放熱により冷却され、′
その油面がある程度高くなると、モータ１０３の回転子
の下端部に拡散されて駆動室１０６内の吸入冷媒ガスに
混入し、再び圧縮室へ流入して最終的には吐出室油溜１
３４に収集される。In addition, the remaining lubricating oil is passed through the first lubricating passage to the pivot shaft 1.
18b and the eccentric hole 136, the oil supply passage passing through the eccentric hole 136, the eccentric oil hole 1901, the horizontal oil hole 191, and the main bearing 11
The oil flows into the bearing oil reservoir 193 through the gap in the lower bearing 1.
The final pressure is reduced through 92 minute gaps. The lubricating oil then flows into the drive chamber 106, and part of it mixes with the suction refrigerant gas and flows into the compression chamber again, but the remaining lubricating oil flows into the motor chamber oil sump 106.
Collected at 84. The lubricating oil in the motor chamber oil sump 184 is cooled by natural heat radiation through the sealed case 101b.
When the oil level rises to a certain level, it is diffused to the lower end of the rotor of the motor 103, mixed with the suction refrigerant gas in the drive chamber 106, flows into the compression chamber again, and finally ends up in the discharge chamber oil sump 1.
Collected on 34th.
また、冷時始動初期や定常運転時に瞬時的な液圧縮が生
じて第２圧縮室１５１＠、１５１ｂ内が異常圧力上昇し
た場合は、上述と同様にリード弁１８６の逆止弁作用に
より、圧縮冷媒ガスが吐出室油溜１３４へ逆流せず、ま
た、レリース隙間１２７や背圧室１３９への流入もなく
、背圧力の上昇もないことから、スラスト軸受１２０が
孝退して継続的な異常圧力上昇を防ぐ。In addition, if instantaneous liquid compression occurs during the initial stage of cold start or steady operation and abnormal pressure rises inside the second compression chambers 151@, 151b, the check valve action of the reed valve 186 prevents compression. Since the refrigerant gas does not flow back into the discharge chamber oil sump 134, nor does it flow into the release gap 127 or the back pressure chamber 139, nor does the back pressure increase, the thrust bearing 120 retires and continues to malfunction. Prevent pressure rise.
圧縮機停止後は吸入室１１７と駆動室１０６との間の吸
入通路に設けられた逆止弁（図示なし）により、吸入通
路を塞ぎ、吐出室１０２から吸入室１１７までの圧力は
圧縮空間の隙間を通じて吐出室１０２ρ圧力に等しくな
り、油吸い込み穴１８５の開口端をリード弁１８６が塞
ぐ。その結果、圧縮機停止直後の吐出室油溜１３４の潤
滑油は、第２圧縮室１５１ｍ、１５１ｂと背圧室１３９
へ差圧給油されず、背圧室１３９の潤滑油は、第１給油
通路を通じて駆動室１０６にその差圧が一定値以下にな
るまで僅かづつ戻される。After the compressor is stopped, a check valve (not shown) provided in the suction passage between the suction chamber 117 and the drive chamber 106 closes the suction passage, and the pressure from the discharge chamber 102 to the suction chamber 117 is reduced to the pressure in the compression space. The pressure becomes equal to the pressure in the discharge chamber 102 through the gap, and the reed valve 186 closes the open end of the oil suction hole 185. As a result, the lubricating oil in the discharge chamber oil sump 134 immediately after the compressor stops is transferred to the second compression chambers 151m, 151b and the back pressure chamber 139.
The lubricating oil in the back pressure chamber 139 is not supplied with differential pressure to the drive chamber 106 through the first oil supply passage until the differential pressure becomes below a certain value.
なお、上記実施例では、レリース隙間１２７や背圧室１
３９へ吐出室油溜１３４の潤滑油を中間圧力にまで減圧
したが、スラスト軸受１２０や背圧室１３９の寸法構成
などにより゛減圧しなくともよい。In addition, in the above embodiment, the release gap 127 and the back pressure chamber 1
Although the lubricating oil in the discharge chamber oil reservoir 134 is reduced to an intermediate pressure, it may not be necessary to reduce the pressure depending on the dimensions of the thrust bearing 120 and the back pressure chamber 139.
以上のように上記実施例によれば旋回スクロール１８は
駆動軸４を支承する本体フレーム５と固定スクロール１
５との間に配置され、本体フレーム５の側に設けられて
軸方向にのみ移動が可能なスラスト軸受２０と固定スク
ロール１５との間に微少隙間（約０．０２０ｍｍ）を設
けて挾まれており、スラスト軸受２０は本体フレーム５
との間に適当なレリース隙間２７を維持しながら吐出室
油溜３４の潤滑油圧力を利用して、常に旋回スクロ−ル
１５の方向に背圧付勢されることにより、圧縮室圧力が
正常な運転時には、固定スクロール１５とスラスト軸受
２０との間に微少隙間で挾まれた旋回スクロール１Ｂは
倒れやジャンピングに起因する摺動面との衝突や片当り
のない円滑な旋回運動をする。As described above, according to the above embodiment, the orbiting scroll 18 includes the main body frame 5 supporting the drive shaft 4 and the fixed scroll 1.
5, and is sandwiched with a small gap (approximately 0.020 mm) between the thrust bearing 20, which is provided on the main body frame 5 side and is movable only in the axial direction, and the fixed scroll 15. The thrust bearing 20 is attached to the main body frame 5.
By using the lubricating oil pressure in the discharge chamber oil sump 34 and always applying back pressure in the direction of the orbiting scroll 15 while maintaining an appropriate release gap 27 between the During normal operation, the orbiting scroll 1B, which is sandwiched between the fixed scroll 15 and the thrust bearing 20 with a small gap, performs a smooth orbiting motion without collisions with sliding surfaces or uneven contact caused by falling or jumping.
その結果、圧縮室間の軸方向微少隙間を確保して圧縮冷
媒ガス漏れを防いで高圧縮効率の維持と騒音や振動の少
ない耐久性に優れた圧縮機を提供することは当然ながら
、冷時始動初期などに冷凍サイクルから多量の液冷媒が
圧縮機内に帰還し、圧縮過程で液圧縮が生じて圧縮室圧
力が異常上昇を始め、固定スクロール１５から離反する
方向ｆζ旋回スクロール１８に作用するスラスト力が一
時的に過大になる場合でも、スラスト軸受２０がモータ
室６の方へ後退するので、旋回スクロール１８が固定ス
クロール１５との軸方向隙間を広げて圧縮室間の密封を
解除し、圧縮室圧力が瞬時に降圧して圧縮機負荷が軽減
され、耐久性を高めることができる。As a result, it is natural to secure a small axial gap between compression chambers to prevent compressed refrigerant gas leakage, maintain high compression efficiency, and provide a highly durable compressor with less noise and vibration. A large amount of liquid refrigerant returns to the compressor from the refrigeration cycle at the beginning of startup, etc., and liquid compression occurs during the compression process, and the pressure in the compression chamber begins to rise abnormally, causing a thrust that acts on the orbiting scroll 18 in the direction fζ away from the fixed scroll 15. Even if the force becomes temporarily excessive, the thrust bearing 20 retreats toward the motor chamber 6, so the orbiting scroll 18 widens the axial gap with the fixed scroll 15, releases the seal between the compression chambers, and reduces the compression. The chamber pressure drops instantly, reducing the load on the compressor and increasing durability.
また、液圧縮が生じない場合でも、圧縮比が一定なため
、始動時は吸入圧力が比較的高く、圧縮室圧力は安定運
転時よりも極めて高くなるが、スラスト軸受２ｏの常時
付勢力の適正設定により、起動負荷を軽減することがで
きる。In addition, even when liquid compression does not occur, the compression ratio is constant, so the suction pressure is relatively high at startup, and the compression chamber pressure is much higher than during stable operation, but the constant biasing force of the thrust bearing 2o is appropriate. Depending on the settings, the startup load can be reduced.
また、ｈ記実施例によればラップ支持円板１８ｃのスラ
スト軸受２０の側に旋回スクロール１８の背圧室３９を
形成し、背圧室３９と吐出室油溜３４とを主軸受１２の
微少隙間を介して連通ずることにより、背圧室３９を中
間圧力にしその背圧力により旋回スクロール１８を圧縮
空間の側へ常時付勢してスラスト軸受２０に作用させる
背圧による付勢力を小さくできる。その結果、液圧縮な
どで、圧縮空間が異常圧力上昇して旋回スクロール１８
が固定スクロール１５から離反する場合のスラスト軸受
２０の後退応答性が良く、異常圧縮時の圧縮空間圧力を
迅速に降下させることができる。また、スラスト軸受２
０の小形化によって圧縮機の小型化を図ることもできる
。Further, according to the embodiment h, the back pressure chamber 39 of the orbiting scroll 18 is formed on the side of the thrust bearing 20 of the lap support disk 18c, and the back pressure chamber 39 and the discharge chamber oil sump 34 are By communicating through the gap, the back pressure chamber 39 is set to an intermediate pressure, and the back pressure constantly urges the orbiting scroll 18 toward the compression space, thereby reducing the urging force due to the back pressure acting on the thrust bearing 20. As a result, due to liquid compression, etc., the pressure in the compression space increases abnormally and the orbiting scroll 18
When the thrust bearing 20 separates from the fixed scroll 15, the backward response of the thrust bearing 20 is good, and the compression space pressure at the time of abnormal compression can be quickly lowered. In addition, thrust bearing 2
By reducing the size of the compressor, the compressor can also be made smaller.
また、上記実施例によればスラスト軸受２０にシールリ
ング７０やバネ装置（図示なし）の弾性力を利用して予
圧付勢すること（こより、圧縮室圧力が一時的に上昇し
、背圧室３９の圧力が低い圧縮機始動初期でも、旋回ス
クロール１８に作用するスラスト力によってスラスト軸
受２０が大きく後退せず、固定スクロール１５と旋回ス
クロール１８との間の隙間を適正に保つ。したがって、
圧縮室隙間過大による圧縮不能を防止すると共にスラス
ト軸受２０のレリース隙間２７を大きく設定でき、液圧
縮時の負荷軽減連応性を良くすることもできる。In addition, according to the above embodiment, the thrust bearing 20 is preloaded using the elastic force of the seal ring 70 and the spring device (not shown) (thereby, the pressure in the compression chamber temporarily increases, and the pressure in the back pressure chamber increases). Even in the early stages of compressor startup when the pressure at 39 is low, the thrust bearing 20 does not move back significantly due to the thrust force acting on the orbiting scroll 18, and the gap between the fixed scroll 15 and the orbiting scroll 18 is maintained appropriately.
In addition to preventing the inability to compress due to an excessive compression chamber gap, the release gap 27 of the thrust bearing 20 can be set large, and load reduction coordination during liquid compression can be improved.
また、上記実施例によれば、スラスト軸受２０と本体フ
レーム５との間に設けたスラスト軸受背圧室形成のため
のゴム製のシールリング７０の弾性力を利用して予圧付
勢することにより、安価な圧縮負荷＠減装置を実現でき
る。Further, according to the above embodiment, preload is applied by utilizing the elastic force of the rubber seal ring 70 for forming the thrust bearing back pressure chamber provided between the thrust bearing 20 and the main body frame 5. , it is possible to realize an inexpensive compression load @ reduction device.
また、上記実施例では冷媒圧縮機について説明したが、
潤滑油を使用する酸素、窒素、ヘリウムなどの他の斌体
圧縮機の場合も同様の作用効果を期待できる。Furthermore, in the above embodiment, the refrigerant compressor was explained, but
Similar effects can be expected in the case of other gas compressors such as oxygen, nitrogen, and helium compressors that use lubricating oil.
発明の効果
以上のように本発明は、旋回スクロールが駆動軸を支承
する本体フレームと固定スクロールとの間に配置され、
本体フレームの側に設けられて軸方向にのみ移動が可能
なスラスト軸受と固定スクロールとの間に微少隙間を設
けて挾まれており、スラスト軸受は本体フレームとの間
に適当な軸方向隙間を維持しながら吐出流体圧力または
吐出圧力と吸入圧力との間の中間流体圧力を利用して常
に旋回スクロールの方向に付勢されることにより、圧縮
室圧力が正常安定状態の運転時には、固定スクロールと
スラスト軸受との間に微少隙間で挾まれた旋回スクロー
ルは、圧縮作用や慣性力、摺動抵抗などに基づく旋回ス
クロールを転覆させようとするモーメントやジャンピン
グ現象を受けずに、摺動面との衝突や片当りのない静粛
で振動の少ない旋回運動をする。これにより、圧縮室間
の軸方向の微少隙間を確保して圧縮流体漏れを防ぎ、圧
縮効率を高め、騒音や振動特性をより一層改善すること
ができる。また圧縮過程での液圧縮などにより、圧縮室
圧力が異常上昇を始め、固定スクロールから離反する方
向に旋回スクロールに作用するスラスト荷重が一時的に
過大になる場合は、スラスト軸受が本体フレームとの隙
間を狭める方向に後退するので、旋回スクロールが固定
スクロールとの軸方向隙間を広げて圧縮室間の密封を解
除し、圧縮室圧力を降圧し、圧縮負荷を軽減して耐久性
を高めることができる。Effects of the Invention As described above, the present invention has an orbiting scroll disposed between a main body frame supporting a drive shaft and a fixed scroll,
The thrust bearing, which is installed on the side of the main body frame and can move only in the axial direction, is sandwiched between the fixed scroll with a small gap, and the thrust bearing has an appropriate axial gap between it and the main body frame. By constantly biasing the orbiting scroll in the direction of the orbiting scroll using the discharge fluid pressure or the intermediate fluid pressure between the discharge pressure and the suction pressure while maintaining the compression chamber pressure, when the compression chamber pressure is in a normal and stable state, the fixed scroll and The orbiting scroll, which is sandwiched between the thrust bearing and the sliding surface with a small gap, is free from the moment or jumping phenomenon that tends to overturn the orbiting scroll due to compression action, inertia force, sliding resistance, etc. It performs quiet turning motion with less vibration and no collisions or uneven hits. Thereby, it is possible to secure a minute gap in the axial direction between the compression chambers, prevent leakage of compressed fluid, increase compression efficiency, and further improve noise and vibration characteristics. In addition, if the pressure in the compression chamber begins to rise abnormally due to liquid compression during the compression process, and the thrust load acting on the orbiting scroll in the direction away from the fixed scroll becomes temporarily excessive, the thrust bearing may Since the orbiting scroll moves backward in the direction of narrowing the gap, the orbiting scroll widens the axial gap with the fixed scroll, releases the seal between the compression chambers, lowers the compression chamber pressure, reduces the compression load, and increases durability. can.
また、液圧縮が生じない場合でも、圧縮比が一定なため
に、閉配管系で使用される圧縮機の始動初期は、吸入圧
力が比較的高く、圧縮負荷も安定運転時よりも極めて高
くなるが、スラスト軸受への常時付勢力を適切設定する
ことにより、起動負荷も軽減できるなど、圧縮効率、振
動・騒音特性、耐久性に優れた効果を有するスクロール
圧縮機を提供することができる。In addition, even when liquid compression does not occur, the compression ratio is constant, so the suction pressure is relatively high at the beginning of the startup of a compressor used in a closed piping system, and the compression load is also much higher than during stable operation. However, by appropriately setting the constant biasing force on the thrust bearing, it is possible to provide a scroll compressor that has excellent effects in compression efficiency, vibration and noise characteristics, and durability, such as reducing the startup load.
第１図は本発明の第１の実施例におけるスクロール冷媒
圧縮機の縦断面図、第２図は同圧縮機における主要部品
の分解図、第３図は同圧縮機におけるスラスト軸受のシ
ール部詳細部分断面図、第４図は同圧縮機におけるオル
ダムリングの外観図、第５図は同圧縮機におけるオルダ
ム機構部の組み立て外観図、第６図は第１図におけるＡ
−Ａ線に沿った横断面図、第７図は同圧縮機の吸入管接
続部における逆止弁の位置説明図、第８図は第７図にお
けるＢ−８線に沿った部分断面図、第９図は同圧縮機の
給油通路に用いる逆止弁の外観図、第１０図、第１１図
はそれぞれ同圧縮機の吐出ポート付近における圧縮室の
移動説明図、第１２図は同圧縮機の吸入行程から吐出行
程までの冷媒ガスの圧力変化を示す特性図、第１３図は
各圧縮室における定点の圧力変化を示す特性図、第１４
図は本発明の第２の実施例におけるスクロール冷媒圧縮
機の縦断面図、第１５図は同圧縮機における給油通路制
御弁装置のリード弁取り付は外観図、第１６図、第１８
図はそれぞれ異なる従来例を示すスクロール圧縮機の縦
断面図、第１７図は第１６図の部分拡大図である。
２・・・・・・吐出室、３・・・・・・モータ、４・・
・・・・駆動軸、５・・・・・・本体フレーム、１５・
・・・・・固定スクロール、１５ｍ・・・・・・固定ス
クロールラップ、１５ｂ・・・・・・鏡板、１６・・・
・・・吐出ポート、１７・・・・・・吸入室、１８・・
・・・・旋回スクロール、１８ａ・・・・・・旋回スク
ロールラップ、１８Ｇ・・・・・・ラップ支持円板、２
０・・・・・・スラスト軸受、３４・・・・・・吐出室
油溜、３９・・・・・・背圧室、７０・・・・・シール
リング、１０５・・・・・・本体フレーム、１１５・・
・・・・固定スクロール、１１８・・・・・・旋回スク
ロール、１２０・・・・・・スラスト軸受、１３９・・
・・・・背圧室。
代理人の氏名 弁理士 中 尾 敏 男 ほか１名ノ５
−リ固定スクロール
第６図
６／１）
９−ｍ−逆止弁
第８図
四儒
ノＸＺ−−−油穴Ａ
第１６図Fig. 1 is a vertical cross-sectional view of a scroll refrigerant compressor according to the first embodiment of the present invention, Fig. 2 is an exploded view of the main parts of the compressor, and Fig. 3 is details of the seal portion of the thrust bearing in the compressor. FIG. 4 is an external view of the Oldham ring in the same compressor, FIG. 5 is an assembled external view of the Oldham mechanism in the same compressor, and FIG. 6 is A in FIG. 1.
- A cross-sectional view taken along line A, FIG. 7 is an explanatory diagram of the position of the check valve at the suction pipe connection part of the same compressor, and FIG. 8 is a partial cross-sectional view taken along line B-8 in FIG. 7. Figure 9 is an external view of a check valve used in the oil supply passage of the compressor, Figures 10 and 11 are explanatory diagrams of movement of the compression chamber near the discharge port of the compressor, and Figure 12 is of the same compressor. 13 is a characteristic diagram showing the pressure change of refrigerant gas from the suction stroke to the discharge stroke, FIG. 13 is a characteristic diagram showing the pressure change at a fixed point in each compression chamber, and FIG.
The figure is a vertical sectional view of a scroll refrigerant compressor according to a second embodiment of the present invention, FIG. 15 is an external view of the reed valve installation of the oil supply passage control valve device in the same compressor, and FIGS. 16 and 18 are
The figures are longitudinal sectional views of scroll compressors showing different conventional examples, and FIG. 17 is a partially enlarged view of FIG. 16. 2...Discharge chamber, 3...Motor, 4...
... Drive shaft, 5 ... Body frame, 15.
...Fixed scroll, 15m...Fixed scroll wrap, 15b... End plate, 16...
...Discharge port, 17...Suction chamber, 18...
...Orbiting scroll, 18a...Orbiting scroll wrap, 18G...Wrap support disk, 2
0...Thrust bearing, 34...Discharge chamber oil sump, 39...Back pressure chamber, 70...Seal ring, 105...Main body Frame, 115...
... Fixed scroll, 118 ... Orbiting scroll, 120 ... Thrust bearing, 139 ...
...Back pressure chamber. Name of agent: Patent attorney Toshio Nakao and 1 other person No.5
- Fixed scroll Fig. 6 6/1) 9-m - Check valve Fig. 8 Four Confucian XZ --- Oil hole A Fig. 16
Claims (3)
された渦巻き状の固定スクロールラップに対して旋回ス
クロールの一部をなすラップ支持円板上の旋回スクロー
ルラップを揺動回転自在に噛み合わせ、両スクロール間
に渦巻き形の圧縮空間を形成し、前記固定スクロールラ
ップの中心部には吐出ポートを設け、前記固定スクロー
ルラップの外側には吸入室を設け、前記圧縮空間は吸入
側より吐出側に向けて連続移行する複数個の圧縮室に区
画されて流体を圧縮するスクロール圧縮機構を形成し、
前記旋回スクロールは駆動軸を支承する本体フレームと
前記固定スクロールとの間に配置され、前記本体フレー
ムの側に設けられて軸方向にのみ移動が可能なスラスト
軸受と前記固定スクロールとの間に微小隙間を設けて挾
まれており、前記スラスト軸受は前記本体フレームとの
間に適当な軸方向隙間を維持しながら吐出流体圧力また
は吐出圧力と吸入圧力との間の中間流体圧力を利用して
常に前記旋回スクロールの方向に付勢されたスクロール
圧縮機。(1) The orbiting scroll wrap on the wrap support disk, which is part of the orbiting scroll, is engaged with the spiral fixed scroll wrap formed on one surface of the end plate, which is part of the fixed scroll, so that it can swing and rotate freely. , a spiral compression space is formed between both scrolls, a discharge port is provided in the center of the fixed scroll wrap, a suction chamber is provided on the outside of the fixed scroll wrap, and the compression space is arranged from the suction side to the discharge side. Forms a scroll compression mechanism that compresses fluid by partitioning into a plurality of compression chambers that continuously move toward
The orbiting scroll is disposed between a main body frame that supports a drive shaft and the fixed scroll, and a minute roller is disposed between the fixed scroll and a thrust bearing provided on the side of the main body frame and capable of moving only in the axial direction. The thrust bearing always maintains an appropriate axial clearance with the main body frame by utilizing the discharge fluid pressure or the intermediate fluid pressure between the discharge pressure and the suction pressure. A scroll compressor biased in the direction of the orbiting scroll.
ールの背圧室を形成し、前記背圧室と圧縮空間または吐
出室に通じる空間とを連通した特許請求の範囲第１項記
載のスクロール圧縮機。(2) Scroll compression according to claim 1, wherein a back pressure chamber of the orbiting scroll is formed on the thrust bearing side of the wrap support disk, and the back pressure chamber is communicated with a compression space or a space communicating with a discharge chamber. Machine.
１項または第２項記載のスクロール圧縮機。（４） ス
ラスト軸受と本体フレームとの間に設けたスラスト軸受
背圧室形成シール部材の弾性力を利用して予圧付勢した
特許請求の範囲第３項記載のスクロール圧縮機。(3) A scroll compressor according to claim 1 or 2, wherein the thrust bearing is preloaded. (4) The scroll compressor according to claim 3, wherein the scroll compressor is preloaded using the elastic force of the thrust bearing back pressure chamber forming seal member provided between the thrust bearing and the main body frame.
Priority Applications (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP62332005A JPH07117049B2 (en) | 1987-12-28 | 1987-12-28 | Scroll compressor |
| KR1019880017493A KR950008694B1 (en) | 1987-12-28 | 1988-12-26 | Scroll type compressor |
| US07/291,233 US4958993A (en) | 1987-12-28 | 1988-12-28 | Scroll compressor with thrust support means |
| EP88121792A EP0322894B1 (en) | 1987-12-28 | 1988-12-28 | Scroll compressor |
| CA000587150A CA1329183C (en) | 1987-12-28 | 1988-12-28 | Delivery pressure operated thrust control system for working contact surfaces in a scroll compressor |
| DE3888147T DE3888147T2 (en) | 1987-12-28 | 1988-12-28 | Scroll compressor. |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP62332005A JPH07117049B2 (en) | 1987-12-28 | 1987-12-28 | Scroll compressor |
Related Child Applications (3)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP7105470A Division JP2674562B2 (en) | 1995-04-28 | 1995-04-28 | Scroll refrigerant compressor with refueling control means |
| JP8304375A Division JP2870509B2 (en) | 1996-11-15 | 1996-11-15 | Scroll gas compressor |
| JP30437696A Division JP2785819B2 (en) | 1996-11-15 | 1996-11-15 | Scroll compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH01177482A true JPH01177482A (en) | 1989-07-13 |
| JPH07117049B2 JPH07117049B2 (en) | 1995-12-18 |
Family
ID=18250073
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP62332005A Expired - Fee Related JPH07117049B2 (en) | 1987-12-28 | 1987-12-28 | Scroll compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH07117049B2 (en) |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1991006768A1 (en) * | 1989-11-02 | 1991-05-16 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor |
| WO1991006763A1 (en) * | 1989-10-31 | 1991-05-16 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor |
| WO1991006773A1 (en) * | 1989-11-02 | 1991-05-16 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor |
| WO1991006770A1 (en) * | 1989-11-02 | 1991-05-16 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor |
| WO1991006767A1 (en) * | 1989-11-02 | 1991-05-16 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor |
| WO1991006772A1 (en) * | 1989-11-02 | 1991-05-16 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor |
| WO1991006766A1 (en) * | 1989-11-02 | 1991-05-16 | Matsushita Electric Industrial Co., Ltd. | Scroll compression |
| US5213489A (en) * | 1989-11-02 | 1993-05-25 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor with axial vibration prevention for a shaft bearing |
| US5340287A (en) * | 1989-11-02 | 1994-08-23 | Matsushita Electric Industrial Co., Ltd. | Scroll-type compressor having a plate preventing excess lift of the crankshaft |
| US5395222A (en) * | 1989-11-02 | 1995-03-07 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor having recesses on the scroll wraps |
| US5829959A (en) * | 1994-09-16 | 1998-11-03 | Hitachi, Ltd. | Scroll compressor |
| US7163386B2 (en) | 2004-04-12 | 2007-01-16 | Hitachi Appliances, Inc. | Scroll compressor having a movable auxiliary portion with contact plane of a stopper portion to contact a pane of the fixed scroll through elastic pressure of high pressure fluid |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS55142902A (en) * | 1979-04-25 | 1980-11-07 | Hitachi Ltd | Scroll fluid machine |
| JPS55177089U (en) * | 1979-06-05 | 1980-12-19 | ||
| JPS5929790A (en) * | 1982-08-11 | 1984-02-17 | Hitachi Ltd | Scroll type hydraulic machine |
| JPS60166781A (en) * | 1984-02-09 | 1985-08-30 | Matsushita Refrig Co | Scroll type compressor |
| JPS61223288A (en) * | 1985-03-28 | 1986-10-03 | Matsushita Electric Ind Co Ltd | Scroll compressor |
| JPS62218678A (en) * | 1986-03-18 | 1987-09-26 | Hitachi Ltd | Scroll compressor |
| JPH01138387A (en) * | 1987-11-26 | 1989-05-31 | Hitachi Ltd | Scroll compressor |
-
1987
- 1987-12-28 JP JP62332005A patent/JPH07117049B2/en not_active Expired - Fee Related
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS55142902A (en) * | 1979-04-25 | 1980-11-07 | Hitachi Ltd | Scroll fluid machine |
| JPS55177089U (en) * | 1979-06-05 | 1980-12-19 | ||
| JPS5929790A (en) * | 1982-08-11 | 1984-02-17 | Hitachi Ltd | Scroll type hydraulic machine |
| JPS60166781A (en) * | 1984-02-09 | 1985-08-30 | Matsushita Refrig Co | Scroll type compressor |
| JPS61223288A (en) * | 1985-03-28 | 1986-10-03 | Matsushita Electric Ind Co Ltd | Scroll compressor |
| JPS62218678A (en) * | 1986-03-18 | 1987-09-26 | Hitachi Ltd | Scroll compressor |
| JPH01138387A (en) * | 1987-11-26 | 1989-05-31 | Hitachi Ltd | Scroll compressor |
Cited By (23)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5263822A (en) * | 1989-10-31 | 1993-11-23 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor with lubrication passages to the main bearing, revolving bearing, back-pressure chamber and compression chambers |
| WO1991006763A1 (en) * | 1989-10-31 | 1991-05-16 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor |
| US5520526A (en) * | 1989-10-31 | 1996-05-28 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor with axially biased scroll |
| WO1991006765A1 (en) * | 1989-10-31 | 1991-05-16 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor |
| WO1991006764A1 (en) * | 1989-10-31 | 1991-05-16 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor |
| JPH03149387A (en) * | 1989-11-02 | 1991-06-25 | Matsushita Electric Ind Co Ltd | Scroll compressor |
| US5217359A (en) * | 1989-11-02 | 1993-06-08 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor with regulated oil flow to the back pressure chamber |
| WO1991006772A1 (en) * | 1989-11-02 | 1991-05-16 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor |
| WO1991006766A1 (en) * | 1989-11-02 | 1991-05-16 | Matsushita Electric Industrial Co., Ltd. | Scroll compression |
| JPH03149380A (en) * | 1989-11-02 | 1991-06-25 | Matsushita Electric Ind Co Ltd | Scroll compressor |
| WO1991006768A1 (en) * | 1989-11-02 | 1991-05-16 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor |
| US5213489A (en) * | 1989-11-02 | 1993-05-25 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor with axial vibration prevention for a shaft bearing |
| US5213490A (en) * | 1989-11-02 | 1993-05-25 | Matsushita Electric Industrial Co., Ltd. | Scroll-type compressor with discharge opening above the lubricant reservoir |
| US5215452A (en) * | 1989-11-02 | 1993-06-01 | Matsushita Electric Industrial Co., Ltd. | Compressor having an oil pump ring associated with the orbiting shaft |
| WO1991006767A1 (en) * | 1989-11-02 | 1991-05-16 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor |
| US5217360A (en) * | 1989-11-02 | 1993-06-08 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor with swirling impeller biased by cooled lubricant |
| WO1991006770A1 (en) * | 1989-11-02 | 1991-05-16 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor |
| US5340287A (en) * | 1989-11-02 | 1994-08-23 | Matsushita Electric Industrial Co., Ltd. | Scroll-type compressor having a plate preventing excess lift of the crankshaft |
| US5395222A (en) * | 1989-11-02 | 1995-03-07 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor having recesses on the scroll wraps |
| WO1991006773A1 (en) * | 1989-11-02 | 1991-05-16 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor |
| US5829959A (en) * | 1994-09-16 | 1998-11-03 | Hitachi, Ltd. | Scroll compressor |
| US6174150B1 (en) | 1994-09-16 | 2001-01-16 | Hitachi, Ltd. | Scroll compressor |
| US7163386B2 (en) | 2004-04-12 | 2007-01-16 | Hitachi Appliances, Inc. | Scroll compressor having a movable auxiliary portion with contact plane of a stopper portion to contact a pane of the fixed scroll through elastic pressure of high pressure fluid |
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| Publication number | Publication date |
|---|---|
| JPH07117049B2 (en) | 1995-12-18 |
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