JPH0739836B2 - Scroll gas compressor - Google Patents
Scroll gas compressorInfo
- Publication number
- JPH0739836B2 JPH0739836B2 JP63159996A JP15999688A JPH0739836B2 JP H0739836 B2 JPH0739836 B2 JP H0739836B2 JP 63159996 A JP63159996 A JP 63159996A JP 15999688 A JP15999688 A JP 15999688A JP H0739836 B2 JPH0739836 B2 JP H0739836B2
- Authority
- JP
- Japan
- Prior art keywords
- scroll
- chamber
- compression
- pressure
- orbiting scroll
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
- 238000007906 compression Methods 0.000 claims description 130
- 230000006835 compression Effects 0.000 claims description 128
- 239000003921 oil Substances 0.000 claims description 58
- 239000010687 lubricating oil Substances 0.000 claims description 44
- 230000002093 peripheral effect Effects 0.000 claims description 33
- 239000012530 fluid Substances 0.000 claims description 10
- 230000007246 mechanism Effects 0.000 claims description 7
- 239000007789 gas Substances 0.000 description 34
- 239000003507 refrigerant Substances 0.000 description 28
- 238000002347 injection Methods 0.000 description 20
- 239000007924 injection Substances 0.000 description 20
- 230000008859 change Effects 0.000 description 14
- 239000007788 liquid Substances 0.000 description 11
- 230000002159 abnormal effect Effects 0.000 description 7
- 230000009471 action Effects 0.000 description 7
- 230000001603 reducing effect Effects 0.000 description 6
- 230000000694 effects Effects 0.000 description 5
- 229910000838 Al alloy Inorganic materials 0.000 description 4
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 4
- 238000007789 sealing Methods 0.000 description 4
- 229910000831 Steel Inorganic materials 0.000 description 3
- 229910045601 alloy Inorganic materials 0.000 description 3
- 239000000956 alloy Substances 0.000 description 3
- 238000001816 cooling Methods 0.000 description 3
- 229910052751 metal Inorganic materials 0.000 description 3
- 239000002184 metal Substances 0.000 description 3
- 238000005192 partition Methods 0.000 description 3
- 230000002265 prevention Effects 0.000 description 3
- 125000006850 spacer group Chemical group 0.000 description 3
- 239000010959 steel Substances 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
- 239000004809 Teflon Substances 0.000 description 2
- 229920006362 Teflon® Polymers 0.000 description 2
- 238000004891 communication Methods 0.000 description 2
- 230000006866 deterioration Effects 0.000 description 2
- 229910052742 iron Inorganic materials 0.000 description 2
- 230000009191 jumping Effects 0.000 description 2
- 239000000314 lubricant Substances 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000003825 pressing Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 238000004080 punching Methods 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 238000005299 abrasion Methods 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
- 230000015572 biosynthetic process Effects 0.000 description 1
- 239000011248 coating agent Substances 0.000 description 1
- 238000000576 coating method Methods 0.000 description 1
- 239000000805 composite resin Substances 0.000 description 1
- 238000005520 cutting process Methods 0.000 description 1
- 230000006837 decompression Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000011038 discontinuous diafiltration by volume reduction Methods 0.000 description 1
- 230000001747 exhibiting effect Effects 0.000 description 1
- 239000000835 fiber Substances 0.000 description 1
- 230000017525 heat dissipation Effects 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
- 238000005470 impregnation Methods 0.000 description 1
- 238000001746 injection moulding Methods 0.000 description 1
- 229910001234 light alloy Inorganic materials 0.000 description 1
- 230000001050 lubricating effect Effects 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
- 230000000149 penetrating effect Effects 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 239000011347 resin Substances 0.000 description 1
- 229920005989 resin Polymers 0.000 description 1
- 230000002393 scratching effect Effects 0.000 description 1
- 238000005245 sintering Methods 0.000 description 1
- 239000013585 weight reducing agent Substances 0.000 description 1
- 238000009736 wetting Methods 0.000 description 1
Landscapes
- Rotary Pumps (AREA)
Description
【発明の詳細な説明】 産業上の利用分野 本発明は、スクロール気体圧縮機の過負荷軽減に関する
ものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to reducing the overload of a scroll gas compressor.
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
室が外周部にあり、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式圧縮機や回転
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。2. Description of the Related Art A scroll compressor with low vibration and low noise characteristics has a suction chamber at the outer periphery and a discharge port at the center of the spiral. It is generally known that a discharge valve for compressing fluid such as a rotary compressor is not required, the compression ratio is constant, the discharge pulsation is relatively small, and a large discharge space is not required.
また、固定スクロールと旋回スクロールの両部材によっ
て形成された圧縮室内で、流体が圧縮される際の圧縮圧
力により、両部材を軸方向に引き離そうとする力が生
じ、圧縮室内の密封が不完全となり、圧縮流体漏れが増
大し、効率低下を招くので、旋回スクロールの背面に圧
縮流体圧力を付勢したり、バネ装置などで押圧したりし
て軸方向押し付け力を与え、両部材が離反するのを防ぐ
構成も知られている。Also, in the compression chamber formed by both the fixed scroll and orbiting scroll members, the compression pressure when the fluid is compressed causes a force to separate the two members in the axial direction, resulting in incomplete sealing of the compression chamber. Since the leakage of the compressed fluid increases and the efficiency is reduced, the compressed fluid pressure is applied to the back surface of the orbiting scroll, or the spring device is pressed to apply the axial pressing force to separate the two members from each other. It is also known to prevent this.
しかし、前者の場合の圧縮流体圧力だけの付勢では、特
に冷時起動の際には背圧付勢に必要な圧縮流体圧力が起
動初期から上昇しておらず、旋回スクロールが固定スク
ロールに密着していないので、旋回スクロールの背面の
側の流体が圧縮室外周部の吸入側に流入して圧力降下
し、旋回スクロールへの背圧付勢が出来なく、圧縮空間
の漏れが大きいので、圧縮室圧力が上昇しないという欠
点を有している。However, in the former case, the compression fluid pressure required for back pressure bias does not rise from the initial startup, especially when the engine is cold, and the orbiting scroll is in close contact with the fixed scroll. Since the fluid on the back side of the orbiting scroll flows into the suction side of the outer periphery of the compression chamber and the pressure drops, back pressure cannot be applied to the orbiting scroll, and there is a large leak in the compression space. It has the disadvantage that the chamber pressure does not rise.
また、後者の場合は、旋回スクロールとバネ装置との間
の摺動面に、摩擦抵抗が生じて、動力損失や摺動部耐久
性の低下を招くという欠点を有していることも知られて
いる。Further, in the latter case, it is also known that there is a drawback that frictional resistance occurs on the sliding surface between the orbiting scroll and the spring device, resulting in power loss and deterioration of sliding portion durability. ing.
また、スクロール圧縮機の特徴である低振動や低騒音特
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15図、第16図の構成が考えられてい
る。Further, in order to further improve the low vibration and low noise characteristics which are the characteristics of the scroll compressor, as a measure to reduce the jumping phenomenon of the orbiting scroll at the time of high speed operation of the compressor, FIG. 15 and FIG. The configuration of is considered.
同図は、駆動シャフト1007の先端部の駆動ピン1007aに
連結する旋回スクロール1001の鏡板1001aが、固定スク
ロール1002の鏡板1002aと、フレーム1008との間に微少
隙間で支持され、旋回スクロールの背面に、圧縮途中の
中間圧力流体を導入し、背圧付勢して上記の起動時の問
題を解決すると共に、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1001がジャンピングするのを阻止
し、旋回スクロール1001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、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
−142902号公報）。This figure shows that the end plate 1001a of the orbiting scroll 1001 connected to the drive pin 1007a at the tip of the drive shaft 1007 is supported by a small gap between the end plate 1002a of the fixed scroll 1002 and the frame 1008, and is attached to the back of the orbiting scroll. , Introducing an intermediate pressure fluid during compression to urge the back pressure to solve the above problems at startup, as well as the compression load, inertial force of rotating members, etc. when the compressor is started, stopped, or operated at high speed. When the change occurs, the orbiting scroll 1001 is prevented from jumping, a small axial gap between the orbiting scroll 1001 and the fixed scroll 1002 is secured to seal the compression chamber, and the compression efficiency is improved, and the space between the members is increased. Measures have been taken to prevent abnormal noise caused by collisions and deterioration of durability of sliding parts (Japanese Patent Laid-Open No. 55
-142902 publication).
また、第17図の構成も考えられている。The configuration shown in FIG. 17 is also 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、背圧室2015に吐出圧力を導入して、その背圧力
と板バネ2023eの付勢力とで固定スクロール2001eを旋回
スクロール2001dに押圧し、旋回スクロール2001dと、固
定スクロール2001e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2001e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号明
細書）。In the figure, the fixed scroll 2001e is configured to be movable in the axial direction, the discharge pressure is introduced into the back pressure chamber 2015, and the back pressure and the biasing force of the leaf spring 2023e press the fixed scroll 2001e against the orbiting scroll 2001d. However, by eliminating the axial gap between the orbiting scroll 2001d and the fixed scroll 2001e to seal the compression chamber and improve the compression efficiency, and when liquid compression occurs in the compression chamber, the fixed scroll 2001e turns the orbiting scroll 2001d. The pressure is reduced by axially moving away from the compression chamber to reduce the load (US Pat. No. 3,600,114).
発明が解決しようとする課題 しかし、第15図、第16図の場合は、スクロール圧縮機の
圧縮比が一定なために、液圧縮などにより圧縮室内が異
常上昇した場合には、旋回スクロールの鏡板が軸方向に
微少隙間しか移動できず、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
下を生じるという課題がある。DISCLOSURE OF THE INVENTION Problems to be Solved by the Invention However, in the case of FIGS. 15 and 16, since the compression ratio of the scroll compressor is constant, when the compression chamber abnormally rises due to liquid compression or the like, the orbiting scroll end plate is used. Can move only a small gap in the axial direction, it cannot expand the gap between the compression chambers to leak the compressed fluid and reduce the pressure of the compression chambers, so the compression load increases, the parts are damaged, and the sliding parts durability There is a problem in that
また、第17図のように固定スクロール2001eを旋回スク
ロール2001d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、上述の如く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、動力損失も大きいとい
う課題があった。Further, in the configuration in which the fixed scroll 2001e is pressed against the orbiting scroll 2001d as shown in FIG. 17, it is necessary to increase the urging force, and as described above, the durability is reduced due to the friction and wear of the contact surfaces of both scrolls. There was a problem that power loss was also large.
また、過負荷防止策として米国特許第3817664号などの
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。Further, as a measure for preventing overload, a configuration in which the orbiting scroll is moved in the direction perpendicular to the main shaft of the drive shaft as in U.S. Pat. There has been a demand for a scroll compressor which is difficult to improve, and which is capable of simultaneously improving vibration and noise characteristics and reducing overload, such as an increase in cost and an increase in external dimensions of the compressor.
課題を解決するための手段 上記課題を解決するために本発明のスクロール圧縮機
は、旋回スクロールが自転阻止部材を介して旋回スクロ
ールに旋回運動させる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、旋回スクロール
のラップ支持円板は、ラップ支持円板を支持する本体フ
レームのスラスト軸受と固定スクロールの鏡板との間に
微少遊合状態で支持された構成において、ラップ支持円
板の反圧縮室側背面を内側の背圧室と外側の外周部空間
とに区画すべく、ラップ支持円板とスラスト軸受との摺
動面のいずれか一方には、自転阻止部材に係合して自転
阻止機構を形成する摺動溝に干渉しない環状溝を設け、
環状溝に環状リングを遊合状態で装着してラップ支持円
板の本体フレームの側を内側の背圧室と外側の外周部空
間とに区画し、本体フレームの外側の油溜の潤滑油が背
圧室と外周部空間及び吸入室または圧縮室に順次通じる
油通路を設け、環状リングがラップ支持円板とスラスト
軸受との摺動面に接した時、環状溝の底面と環状リング
との間に隙間が存在すべく環状溝を設けたものである。Means for Solving the Problems In order to solve the above problems, the scroll compressor of the present invention includes a main body frame that supports a drive shaft that orbits a orbiting scroll to orbit through a rotation preventing member, and a fixed scroll. The wrap support disc of the orbiting scroll is disposed between the thrust bearing of the main body frame that supports the wrap support disc and the end plate of the fixed scroll in a slightly loosely fitted state. In order to partition the rear surface of the anti-compression chamber side into the back pressure chamber on the inside and the outer peripheral space on the outside, one of the sliding surfaces of the lap support disk and the thrust bearing is engaged with the rotation preventing member. By providing an annular groove that does not interfere with the sliding groove that forms the rotation prevention mechanism,
An annular ring is loosely attached to the annular groove to partition the body frame side of the lap support disc into an inner back pressure chamber and an outer peripheral space, and the lubricating oil in the oil reservoir outside the body frame is When an oil passage that leads to the back pressure chamber and the outer peripheral space and the suction chamber or the compression chamber is provided in order, and when the annular ring contacts the sliding surface of the lap support disk and the thrust bearing, the bottom of the annular groove and the annular ring An annular groove is provided so that there is a gap between them.
作用 本発明は上記構成によって、圧縮機起動初期のような背
圧室と吸入室の圧力差が余り無い場合や、定常運転時の
ような背圧室と吸入室の圧力差が有る場合には、環状リ
ングがラップ支持円板とスラスト軸受の摺動面の潤滑油
を油掻き作用する。環状溝の周辺に収集された潤滑油
は、環状溝と環状リングとの間の隙間およびラップ支持
円板とスラスト軸受との摺動面と環状リングの隙間を油
密封し、背圧室から吸入室の側に旋回スクロール背圧用
の流体が流入するのを防ぎ、背圧室圧力を保持して旋回
スクロールのラップ支持円板を固定スクロールの鏡板に
付勢接触させ、圧縮室を密封して吸入気体を圧縮する。Action The present invention has the above-described configuration, in the case where there is not much pressure difference between the back pressure chamber and the suction chamber, such as in the initial stage of compressor startup, or when there is a pressure difference between the back pressure chamber and the suction chamber, such as in steady operation. The annular ring scrapes the lubricating oil on the sliding surfaces of the lap support disk and the thrust bearing. Lubricating oil collected around the annular groove seals the gap between the annular groove and the annular ring, the sliding surface between the lap support disc and the thrust bearing, and the annular ring, and sucks it from the back pressure chamber. The fluid for orbiting scroll back pressure is prevented from flowing into the chamber side, the back pressure chamber pressure is maintained and the orbiting scroll wrap support disc is urged into contact with the fixed scroll end plate, and the compression chamber is sealed and sucked. Compress the gas.
万一、圧縮室内で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、あるいは、旋回スクロールと
固定スクロールとの間の軸方向隙間部に、異物噛み込み
が生じた場合などは、旋回スクロールに作用するスラス
ト力が旋回スクロールの背面に作用する付勢力よりも大
きくなり、旋回スクロールが軸方向に移動し、旋回スク
ロールのラップ支持円板が固定スクロールの鏡板から離
れて本体フレームに支持されると共に、圧縮室の密封を
解除して、圧縮室圧力を降下させたり、噛み込み異物を
除去したりして、圧縮負荷の軽減させ、圧縮圧縮機の破
損や摺動部の摩耗を防止して振動、騒音、耐久性に優れ
たスクロール気体圧縮機が提供できる。In the unlikely event that liquid compression etc. occurs in the compression chamber and the pressure in the compression chamber suddenly rises abnormally, or foreign matter is caught in the axial gap between the orbiting scroll and fixed scroll. The thrust force acting on the orbiting scroll becomes larger than the urging force acting on the back surface of the orbiting scroll, the orbiting scroll moves in the axial direction, the wrap supporting disk of the orbiting scroll moves away from the end plate of the fixed scroll, and the main frame The compression load is reduced by releasing the seal of the compression chamber to lower the pressure in the compression chamber and removing foreign matter that is trapped in the compressor. It is possible to provide a scroll gas compressor excellent in vibration, noise and durability by preventing the above.
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。Embodiment Hereinafter, a scroll compressor according to an embodiment 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と吐出室２とに仕
切られている。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のライナー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。In FIG. 1, reference numeral 1 denotes an iron-made hermetic case, the inside of which is a high-pressure atmosphere communicating with the discharge chamber 2, a motor 3 is arranged in the upper part, a compression part is arranged in the lower part, and the drive is fixed to the rotor 3a of the motor 3. The interior of the hermetically sealed case 1 is partitioned into a motor chamber 6 and a discharge chamber 2 by a body frame 5 of a compression unit that supports the shaft 4. The main body frame 5 is made of an aluminum alloy having excellent heat conduction characteristics mainly for weight reduction and heat dissipation of the bearing portion, and an iron liner 8 having excellent weldability is provided on the outer peripheral portion thereof.
Is shrink-fitted and fixed, and the outer peripheral surface of the liner 8 is sealed case 1
It is inscribed all around and is welded and partially fixed.
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 hermetically sealed case 1. The drive shaft 4 includes an upper bearing 10 provided on the bearing frame 9, a lower bearing 11 provided on an upper end portion of the main body frame 5, a main bearing 12 provided on a central portion of the main body frame 5, an upper end surface of the main body frame 5. Rotor 3a of motor 3
An eccentric bearing 14 which is eccentric from the main shaft of the drive shaft 4 is provided at a lower end portion thereof, which is supported by a thrust ball bearing 13 provided between the drive shaft 4 and a lower end surface thereof.
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15
bの中央部には、固定スクロールラップ15a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15a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 body frame 5, and the fixed scroll 15 is composed of a spiral fixed scroll wrap 15a and an end plate 15b.
A discharge port 16 that opens to the winding start portion of the fixed scroll wrap 15a is provided in the center of b so as to also open to the discharge chamber 2, and a suction chamber 17 is provided on the outer peripheral portion of the fixed scroll wrap 15a. .
固定スクロールラップ15a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ップ18a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94が焼ばめ固定さ
れ、ラップ支持円板18cの表面は硬化処理されている。Aluminum alloy composed of a spiral orbiting scroll wrap 18a that meshes with a fixed scroll wrap 15a to form a compression chamber, and a lap support disk 18c in which the orbiting shaft 18b supported by the eccentric bearing 14 of the drive shaft 4 is upright. The orbiting scroll 18 made of metal is arranged so as to be surrounded by the fixed scroll 15, the main body frame 5 and the drive shaft 4, and a sleeve 94 made of a high tensile steel material is shrink-fitted and fixed to the outer peripheral portion of the orbiting shaft 18b. The surface of the lap supporting disk 18c is hardened.
本体フレーム５に固定された割りピン形の平行ピン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2
1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18cの
厚さよりも約0.015〜0.020mm大きく設定されている。Thrust bearing 20 that can be moved only in the axial direction by being constrained by split pin-shaped parallel pins 19 fixed to the body frame 5.
And the end plate 15b of the fixed scroll 15 between the spacer 2
1 is provided, and the axial dimension of the spacer 21 is set to be about 0.015 to 0.020 mm larger than the thickness of the lap supporting disk 18c in order to improve the sealing property of the sliding surface by the oil film.
ラップ支持円板18cのスラスト軸受20との摺動面の最外
部には、環状溝81が設けられ、その内部に、焼結合金製
の弾性を有する環状リング82が微少隙間で装着され、そ
の最大軸方向微少隙間は0.025mm以上で、油膜形成が可
能な程度である。また、環状リング82は、第４図のよう
に自由状態で、その円周方向に対して傾斜して切断され
た切り口を有して開いており、その切り口は、環状リン
グ82が環状溝81に装着された時、環状リング82の外側面
が、その弾性力で環状溝81の外側面に密接して微少隙間
を有する程度に設定されている。また、環状溝81の幅と
環状リング82の幅とは、全周囲に渡って同一寸法でな
く、環状リング82が環状溝81内で一回転出来ない状態に
構成されている。An annular groove 81 is provided at the outermost part of the sliding surface of the lap support disk 18c with respect to the thrust bearing 20, and an annular ring 82 having elasticity made of a sintered alloy is mounted inside the annular groove 81 with a minute gap. The maximum axial gap is 0.025 mm or more, which is enough to form an oil film. Further, the annular ring 82 is open in a free state as shown in FIG. 4 with a cut portion that is cut obliquely with respect to the circumferential direction, and the cut portion is formed by the annular ring 82 and the annular groove 81. The outer surface of the annular ring 82 is set so as to be in close contact with the outer surface of the annular groove 81 and have a minute gap when it is mounted on. Further, the width of the annular groove 81 and the width of the annular ring 82 are not the same size over the entire circumference, and the annular ring 82 is configured in a state in which it cannot make one rotation in the annular groove 81.
駆動軸４の偏心軸受14の底部と旋回スクロール18の旋回
軸18bの軸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18bとラップ支持円板
18cに設けられた油穴A38aにより連通されている。The eccentric bearing space 36 between the bottom portion of the eccentric bearing 14 of the drive shaft 4 and the shaft portion of the orbiting shaft 18b of the orbiting scroll 18, and the outer peripheral space 37 of the lap supporting disk 18c are the orbiting shaft 18b and the wrap supporting circle. Board
It is communicated with by an oil hole A38a provided in 18c.
スラスト軸受20は焼結合金製で、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。The thrust bearing 20 is made of a sintered alloy and, as shown in FIGS. 2 and 6, is formed by penetrating the central portion thereof into two parallel straight line portions 22 and two arcuate curved line portions 23 connected to the straight line portions 22. ing.
旋回スクロール18の自転阻止部材（以下、オルダムリン
グという）24は、焼結成形や射出成形工法などに適した
軽合金や強化繊維複合樹脂材料から成り、含油特性も有
し、第５図のように両面が平行な薄い環状板24aと、そ
の一面に設けられた一対の平行キー部分24bとから成
り、環状板24a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が第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、平行キー部分
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
18c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。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
ー部分24bの付け根に設けられたヘコミ部24dは、潤滑油
の通路にもなる。また、円弧状曲線部分に設けられたヘ
コミ部24eも同様な潤滑油の通路である。The rotation preventing member (hereinafter referred to as Oldham ring) 24 of the orbiting scroll 18 is made of a light alloy or a reinforced fiber composite resin material suitable for sintering molding, injection molding, etc., and also has oil impregnation characteristics, as shown in FIG. Is composed of a thin annular plate 24a whose both sides are parallel to each other, and a pair of parallel key portions 24b provided on one surface of the annular plate 24a.
And two arcuate curved portions 26 connected to it, and the straight line portion 25 is, as shown in FIG. 6, the straight line portion of the thrust bearing 20.
It is slidable by engaging with 22 with a small clearance, and the parallel key part
The side surface 24c of 24b is orthogonal to the central portion of the straight line portion 25, and
The lap support disk of the orbiting scroll 18 as shown in FIGS.
Engage with a pair of key grooves 71 provided in 18c with a minute gap,
It has a slidable shape. The inner contour of the annular plate 24a has a shape similar to the outer contour. Further, the dent portion 24d provided at the base of the parallel key portion 24b also serves as a passage for the lubricating oil. Further, the dent portion 24e provided in the arc-shaped curved portion is a similar lubricating oil passage.
第１図、第３図のように、本体フレーム５とスラスト軸
受20との間には、約0.1mm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 FIG. 1 and FIG. 3, a release gap 27 of about 0.1 mm is provided between the body frame 5 and the thrust bearing 20. The release gap 27 faces the release gap 27, and the body frame 5 also has an annular groove. A rubber seal ring 70, which is provided with 28 and surrounds the annular groove 28, is mounted between the body frame 5 and the thrust bearing 20.
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９に設けられた抜き穴3
2、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、多数の小穴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 portion of the motor chamber 6 and the discharge chamber 2 are communicated with each other through a bypass discharge pipe 29 connected to penetrate the side wall of the sealed case 1, and the opening position of the bypass discharge pipe 29 to the motor chamber 6 is the stator. The discharge pipe 31 facing the side surface of the upper coil end 30 of 3b and connected to the upper open end of the bypass discharge pipe 29 and the upper surface of the hermetically sealed case 1 is a through hole 3 provided in the bearing frame 9.
2. It is arranged between the upper surface of the closed case 1 and the bearing frame 9 and communicates with each other through 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に設けられた油穴B38bを
経由して環状溝28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A40aを介して偏心軸受け空間36へも連通してい
る。The discharge chamber oil sump 34 provided in the lower portion of the motor chamber 6 communicates with the upper portion of the motor chamber 6 and a cooling passage 35 provided by cutting a part of the outer periphery of the stator 3b of the motor 3. In addition, the discharge chamber oil sump 34 communicates with the annular groove 28 via an oil hole B38b provided in the main body frame 5, and also the main bearing 12 in the back pressure chamber 39 of the orbiting scroll 18 in which the Oldham ring 24 is arranged. Through the minute gap of the sliding portion, and further communicates with the eccentric bearing space 36 through an oil groove A40a provided in the eccentric bearing 14.
また、本体フレーム５に設けられた油穴B38bは、駆動軸
４の下部軸受け11に対応する下部軸部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41の巻き
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。The oil hole B38b provided in the main body frame 5 also communicates with the spiral oil groove 41 provided on the surface of the lower shaft portion 4a corresponding to the lower bearing 11 of the drive shaft 4, and the spiral oil groove B38b is provided. The winding direction of the groove 41 is provided so that a screw pump action utilizing the viscosity of the lubricating oil is generated when the drive shaft 4 rotates in the forward direction, and the end of the groove 41 is formed up to the middle of the lower bearing 4a.
第７図、第８図のように、固定スクロール15は、吸入室
17の両端を連通す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
15a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。
また、第９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L49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、弾性力に富
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. 7 and 8, the fixed scroll 15 has a suction chamber.
An arc-shaped suction passage 42 that communicates both ends of the 17 is provided, and a circular suction hole 43 orthogonal to the suction passage 42 is formed in the fixed scroll wrap.
It is also provided in a direction perpendicular to the side surface of 15a, and the bottom of the suction hole 43 is flat and reaches the side surface of the suction passage 42.
Further, as shown in FIG. 9, the center of the suction hole 43 is displaced from the bottom surface 44 of the suction passage 42, and the dimension W45 of the opening to the suction passage 42 is increased.
Are smaller than the diameter of the suction hole 43. The suction pipe 43 of the 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
A check valve 50 made of a circular thin steel plate that is larger than the suction hole depth dimension L49 between and and larger than the opening dimension W45 is arranged. The surface of the check valve 50 has a poor oil wetting property and is coated with Teflon or rubber having a high elasticity.
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5
4、外周部空間37に開口した段付き形状の油穴C38cとか
ら成るインジェクション通路55で連通され、油穴C38cの
大径部56には、第10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支弁58と、コイルスプリング59
とが配置されている。The second compression chamber 51 and the outer peripheral space 37, which are not in communication with the suction chamber 17 or the discharge chamber 2, have a small-diameter injection hole 52 provided in the end plate 15b and opened in the second compression chamber 51, and an end plate 15b. Injection groove 5 formed with resin heat insulating cover 53
4, communicated by an injection passage 55 consisting of a stepped oil hole C38c opening to the outer peripheral space 37, and the large diameter portion 56 of the oil hole C38c is cut into a part of the outer circumference as shown in FIG. Lack
Check valve 58 made of sheet steel with 57 and coil spring 59
And are arranged.
コイルスプリング59は、断熱カバー53に押さえられて逆
止弁58を常時付勢する。外周部空間37への油穴C38cの開
口位置は、第11図、第12図に示す如く、吐出ポート16に
連通する第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11図参照）時
に、外周部空間37と油穴C38cとが連通し、それ以外の時
（第12図参照）にはラップ支持円板18cによって遮断さ
れる位置に設けられている。The coil spring 59 is pressed by the heat insulating cover 53 and constantly urges the check valve 58. As shown in FIG. 11 and FIG. 12, the opening position of the oil hole C38c to the outer peripheral space 37 is such that the orbiting scroll 18 reaches the vicinity of the end of the volume reduction stroke of the third compression chamber 60 communicating with the discharge port 16. Is located at a position where the outer peripheral space 37 and the oil hole C38c communicate with each other when (see FIG. 11) moves, and is blocked by the lap support disc 18c at other times (see FIG. 12). There is.
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、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は異常圧力上昇時の圧力変
化を示す。In FIG. 13, the horizontal axis represents the rotation angle of the drive shaft 4, the vertical axis represents the refrigerant pressure, the pressure change state of the refrigerant gas in the suction / compression / discharge processes, and the solid line 62 represents the normal pressure during operation. The pressure change is shown, and the dotted line 63 shows the pressure change when the abnormal pressure rises.
第14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5
2a,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,61b（第７図参照）の
定点における圧力変化を示し、一点鎖線66は吐出室２に
連通する第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61a,61bと第２圧縮室51
a,51bとの間の定点における圧力変化を示し、二重点線6
8は背圧室39の圧力変化を示す。In FIG. 14, 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 of the second compression chambers 51a, 51b that do not communicate with the discharge chamber 2 or the suction chamber 17. Five
2a and 52b show the pressure change at the opening position, the dotted line 65 shows the pressure change at the fixed point of the first compression chambers 61a and 61b (see FIG. 7) communicating with the suction chamber 17, and the alternate long and short dash line 66 shows the discharge chamber 2. A pressure change at a fixed point of the communicating third compression chambers 60a, 60b is shown, and a two-dot chain line 67 indicates the first compression chambers 61a, 61b and the second compression chambers 51.
Shows the pressure change at a fixed point between a and 51b.
Reference numeral 8 indicates a pressure change in the back pressure chamber 39.
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 described.
第１図〜第14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47、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61a,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51a,51b、第３圧縮室60a,60b
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。In FIG. 1 to FIG. 14, when the drive shaft 4 is rotationally driven by the motor 3, the orbiting scroll 18 orbits, and the suction refrigerant gas containing lubricating oil from the refrigeration cycle connected to the compressor is transferred to the accumulator 46. It flows into the suction chamber 17 through the connected suction pipe 47, suction hole 43, and suction passage 42, and is confined in the compression chamber via the first compression chambers 61a and 61b formed between the orbiting scroll 18 and the fixed scroll 15. The second compression chambers 51a, 51b and the third compression chambers 60a, 60b that are always enclosed spaces
To the discharge chamber 2 through the discharge port 16 in the central portion.
圧縮機内圧力が均衡した状態からの圧縮機起動初期に
は、圧縮室内の圧縮冷媒圧力によって旋回スクロール18
に吐出ポート16と反対の方向のスラスト力が作用する。
しかし、旋回スクロール18の背面には付勢に必要な背圧
力が生じていないので、旋回スクロール18が固定スクロ
ール15から離れスラスト軸受20に支持される。この時、
圧縮室の軸方向には、約0.015〜0.020mmの隙間が生じ
る。その結果、圧縮室内圧力が一時的に降下して、起動
初期の圧縮負荷が軽減する。At the beginning of the compressor starting from the state where the pressure inside the compressor is balanced, the orbiting scroll 18 is caused by the pressure of the compressed refrigerant in the compression chamber.
Thrust force acts in the direction opposite to the discharge port 16.
However, since the back pressure necessary for biasing is not generated on the back surface of the orbiting scroll 18, the orbiting scroll 18 is separated from the fixed scroll 15 and is supported by the thrust bearing 20. At this time,
A gap of about 0.015 to 0.020 mm is formed in the axial direction of the compression chamber. As a result, the pressure in the compression chamber temporarily drops, and the compression load in the initial stage of startup is reduced.
なお、スラスト軸受20が旋回スクロール18を支持する初
期の支持力は後述する如く、シールリング70の弾性力と
補助的なバネ装置（例えば、第17図の2023のような板バ
ネ）に依存する。The initial supporting force for the thrust bearing 20 to support the orbiting scroll 18 depends on the elastic force of the seal ring 70 and an auxiliary spring device (for example, a leaf spring like 2023 in FIG. 17) as described later. .
一方、旋回スクロール18に追従して旋回運動をする弾性
体の環状リング82が、ラップ支持円板18cと接するスラ
スト軸受20の摺動面の潤滑油を油掻きして環状溝81の周
辺に収集し、環状溝81と環状リング82との間の隙間およ
び環状リング82とスラスト軸受20との間の隙間を油密封
する。その結果、背圧室39から吸入室17側に、潤滑油と
その中に溶解した冷媒ガスが流入せず、後述する経過を
経て次第に背圧室圧力が高まる。その背圧力により、旋
回スクロール18のラップ支持円板18cが固定スクロール1
5の鏡板15bに付勢接触し、圧縮室の軸方向隙間が無くな
り、圧縮室が密封され、吸入冷媒ガスが効率良く圧縮さ
れ、安定運転が継続する。On the other hand, an annular ring 82 made of an elastic body that follows the orbiting scroll 18 to orbit and scrapes the lubricating oil on the sliding surface of the thrust bearing 20 in contact with the lap support disk 18c and collects it around the annular groove 81. Then, the gap between the annular groove 81 and the annular ring 82 and the gap between the annular ring 82 and the thrust bearing 20 are oil-sealed. As a result, the lubricating oil and the refrigerant gas dissolved therein do not flow from the back pressure chamber 39 to the suction chamber 17 side, and the back pressure chamber pressure gradually increases after a later-described process. Due to the back pressure, the wrap support disk 18c of the orbiting scroll 18 is fixed to the scroll 1
The urging contact with the end plate 15b of No. 5 eliminates the axial gap of the compression chamber, the compression chamber is sealed, the suction refrigerant gas is efficiently compressed, and stable operation is continued.
万一、圧縮室内で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18に作用する
スラスト力が、旋回スクロール18の背面に作用する付勢
力よりも大きくなり、旋回スクロール18が軸方向に移動
し、旋回スクロール18のラップ支持円板18cが、固定ス
クロール15の鏡板15bから離れてスラスト軸受20に支持
されると共に、圧縮室の密封が解除して、圧縮室圧力が
降下し、圧縮負荷が軽減する。In the unlikely event that liquid compression occurs in the compression chamber and the pressure in the compression chamber suddenly rises abnormally, the thrust force acting on the orbiting scroll 18 becomes larger than the biasing force acting on the back surface of the orbiting scroll 18, The orbiting scroll 18 moves in the axial direction, the lap support disk 18c of the orbiting scroll 18 is supported by the thrust bearing 20 away from the end plate 15b of the fixed scroll 15, and the compression chamber is unsealed, so that the compression chamber The pressure drops and the compression load is reduced.
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。これにより、潤滑油の一部が分離され、その
後、軸受フレーム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の小穴を
通る際に、潤滑油の慣性力や表面付着により潤滑油が効
果的に分離される。The discharge refrigerant gas containing the lubricating oil returns to the motor chamber 6 in the compressor again via the bypass discharge pipe 29 piped to the outside of the compressor, and is then discharged from the discharge pipe 31 to the external refrigeration cycle. When flowing into the chamber 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. As a result, a part of the lubricating oil is separated, and after that, when passing through the hole 32 provided in the bearing frame 9, when changing the flow direction or when passing through the small hole of the punching metal 33, the inertia of the lubricating oil Lubricating oil is effectively separated by force or 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を冷却しながら吐出室油溜34に収集され
る。After lubricating the sliding surface of the upper bearing, a part of the lubricating oil separated from the discharge gas passes through the cooling passage 35 together with the remaining lubricating oil and is collected in the discharge chamber oil sump 34 while cooling the motor 3. .
吐出室油溜34の潤滑油は、駆動軸４の下部軸部4aの表面
に設けられた螺旋状油溝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 4a of the drive shaft 4, and the lubricating oil in the end portion of the lower shaft portion 4a is supplied. When the lubricating oil passes through the minute bearing gap, the atmosphere of the discharged refrigerant gas in the motor chamber 6 and the upstream space of the main bearing 12 are shut off by the sealing action of the oil film.
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。その
後、偏心軸受14の油溝A40a、偏心軸受空間36、旋回スク
ロール18を通る油穴A38を経て漸次減圧されながら外周
部空間37に流入し、更に間欠的に開口する油穴C38c、イ
ンジェクション溝54、インジェクション穴52a,52bを経
て第２圧縮室51a,51bに流入し、その通路途中の各摺動
面を潤滑する。The lubricating oil containing the dissolved discharge refrigerant gas of the discharge chamber oil sump 34 is reduced to an intermediate pressure between the discharge pressure and the suction pressure when passing through the minute gap of the main bearing 12, and flows into the back pressure chamber 39. After that, the oil groove A40a of the eccentric bearing 14, the eccentric bearing space 36, and the oil hole A38 passing through the orbiting scroll 18 flow into the outer peripheral portion space 37 while being gradually decompressed, and the oil hole C38c and the injection groove 54 which are intermittently opened. , Through the injection holes 52a, 52b, into the second compression chambers 51a, 51b, and lubricate 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27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の端面に当接する。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15
aの端面とラップ支持円板18cとの間、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、隣接する圧縮空間の気体漏れを少なくする。Further, since the discharge chamber oil sump 34 also communicates with the annular groove 28 and the release gap 27, the thrust bearing 20 is
It is urged to come into contact with the end surface of the spacer 21. Then, the lap support disk 18c of the orbiting scroll 18 is
And the end plate 15b of the fixed scroll 15 are held in a small gap and slide smoothly, and the fixed scroll wrap 15
The gap between the end surface of a and the wrap support disk 18c and the end surface of the orbiting scroll wrap 18a and the end plate 15b are also kept small, thereby reducing gas leakage in the adjacent compression space.
第２圧縮室51a,51bのインジェクション穴52a,52b開口部
は、第14図の如くの圧力変化をし、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
圧力は低い。そのため、背圧室39からの潤滑油は、間欠
的に第２圧縮室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51a,51b内
の圧縮冷媒ガスは、細径のインジェクション穴52a,52b
で減圧されて、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。The openings of the injection holes 52a, 52b of the second compression chambers 51a, 51b change in pressure as shown in FIG. 14 and are instantaneously higher than the back pressure chamber pressure 68 which changes following the pressure of the discharge chamber 2. However, the average pressure is low. Therefore, the lubricating oil from the back pressure chamber 39 intermittently flows into the second compression chambers 51a and 51b, and the second compression chambers 51a and 51b are instantaneously higher than the back pressure chamber pressure 68 during normal operation. The compressed refrigerant gas inside is a small diameter injection hole 52a, 52b.
The pressure inside the injection groove 54 is reduced by the pressure in the injection groove 54, and there is little instantaneous backflow to the injection groove 54.
Not higher than 68.
第２圧縮室51a,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
圧縮冷媒ガス漏れを防ぎ、圧縮室間の摺動面を潤滑しな
がら圧縮冷媒ガスと共に吐出室２に再び吐出される。The lubricating oil injected into the second compression chambers 51a and 51b merges with the lubricating oil that has flowed into the compression chambers together with the suction refrigerant gas, and seals a minute gap between adjacent compression chambers with an oil film to prevent leakage of the compressed refrigerant gas. While being lubricated on the sliding surface between the compression chambers, the compressed refrigerant gas is discharged again to the discharge chamber 2.
また、前述のように圧縮機起動初期には、シールリング
70の弾性力やバネ装置によりスラスト軸受20を介して旋
回スクロール18を支持するが、圧縮機起動安定後の背圧
室39に差圧給油された潤滑油は、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18cを鏡
板15b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。また、背圧室39の潤
滑油は、スラスト軸受20とラップ支持円板18cとの摺動
面の隙間に介在し、ラップ支持円板18cの環状溝81に装
着された環状リング82の旋回運動に伴う油掻き作用で、
潤滑油が環状リング82の内外周に収集され、環状溝81と
環状リング82との微少隙間、ラップ支持円板18cとスラ
スト軸受20との隙間（約0.015〜0.020mm）の密封する。In addition, as mentioned above, the seal ring
The orbiting scroll 18 is supported via the thrust bearing 20 by the elastic force of 70 and the spring device, but the lubricating oil differentially supplied to the back pressure chamber 39 after the compressor has been stabilized stabilizes the urging force of the intermediate pressure. By acting on 18, the lap support disk 18c seals the sliding surface with the end plate 15b with a pressing oil film, and cuts off the communication between the outer peripheral space 37 and the suction chamber 17. Further, the lubricating oil in the back pressure chamber 39 is present in the gap between the sliding surfaces of the thrust bearing 20 and the lap support disk 18c, and the rotational movement of the annular ring 82 mounted in the annular groove 81 of the lap support disk 18c. With the oil scratching effect of
Lubricating oil is collected on the inner and outer circumferences of the annular ring 82, and seals a minute gap between the annular groove 81 and the annular ring 82 and a gap (about 0.015 to 0.020 mm) between the lap support disk 18c and the thrust bearing 20.
なお、旋回運動に基づく環状リング82の慣性力によって
環状リング82が環状溝81内を回転しようとする。しか
し、環状溝81の溝幅が環状リング81よりも狭い部分が有
り、また、その外方向への弾性力によって環状リング81
が環状溝82の外側面に密接しているので、環状リング82
は、環状溝81内を円周方向と半径方向に移動できない。
また、環状溝81内での環状リング82の切り口部が密着し
ているので、この部分からの漏れも生じない。The annular ring 82 tries to rotate in the annular groove 81 by the inertial force of the annular ring 82 based on the turning motion. However, there is a portion where the groove width of the annular groove 81 is narrower than that of the annular ring 81, and due to the outward elastic force of the annular ring 81.
Close to the outer surface of the annular groove 82, the annular ring 82
Cannot move in the annular groove 81 in the circumferential direction and the radial direction.
In addition, since the cut portion of the annular ring 82 in the annular groove 81 is in close contact with the annular groove 81, leakage does not occur from this portion.
また、圧縮機の冷時起動後しばらくの間は、第13図、第
14図から理解できるように、吐出室２の圧力が、第２圧
縮室51a,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,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
よって外周部空間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。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59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。In addition, for a while after the cold start of the compressor,
As can be understood from FIG. 14, the pressure in the discharge chamber 2 is lower than the pressure in the second compression chambers 51a, 51b, and the refrigerant gas in the middle of compression passes from the second compression chambers 51a, 51b through the injection passage 55 to the back pressure chamber. However, due to the non-return action of the check valve 58, the back flow to the outer peripheral space 37 is blocked, and the discharge chamber oil sump 34
This lubricating oil is differentially supplied to the back pressure chamber 39 and the outer peripheral space 37 as the pressure in the discharge chamber 2 rises. Then, as the pressure in the discharge chamber 2 rises, the lubricating oil in the outer peripheral space 21 is injected into the second compression chambers 51a, 51b from the injection holes 52a, 52b against the biasing force of the coil spring 59.
したがって、冷時起動直後のように、吸入冷媒ガスの圧
力が非常に高く、スクロール圧縮機の圧縮比が一定であ
ることから圧縮室圧力も非常に高くなった場合、あるい
は、異常な液圧縮が生じた場合などは、上述のように旋
回スクロール18が固定スクロール15から離反し、スラス
ト軸受20に支持される。しかしながら、背圧付勢された
スラスト軸受20は、異常に上昇した圧縮室圧力により生
じて旋回スクロール18に作用するスラスト荷重を支持で
きず、レリース隙間27を減少させる方向に後退して、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
が拡大する。これにより、圧縮室間に多くの漏れが生じ
て圧縮室圧力が急低下し、圧縮負荷が瞬時に軽減した
後、スラスト軸受20が瞬時に元の位置に復帰して、背圧
室39の圧力は著しい低下もせず、安定運転が再継続す
る。Therefore, when the pressure of the suction refrigerant gas is very high and the compression ratio of the scroll compressor is constant, and the pressure in the compression chamber is also very high, such as immediately after cold start, or abnormal liquid compression occurs. When it occurs, the orbiting scroll 18 separates from the fixed scroll 15 and is supported by the thrust bearing 20 as described above. However, the thrust bearing 20 biased by the back pressure cannot support the thrust load acting on the orbiting scroll 18 caused by the abnormally increased pressure in the compression chamber, and is retracted in the direction of decreasing the release gap 27 to cause the orbiting scroll. The axial gap between 18 and the fixed scroll 15 increases. As a result, a large amount of leakage occurs between the compression chambers, the compression chamber pressure drops sharply, the compression load is instantly reduced, and then the thrust bearing 20 instantly returns to its original position, and the pressure in the back pressure chamber 39 is reduced. Does not decrease significantly, and stable operation resumes.
また、旋回スクロール18と固定スクロール15との間の軸
方向隙間部に異物噛み込みが生じた場合も上述と同様
に、スラスト軸受20が後退して異物を除去する。Also, when foreign matter is caught in the axial gap between the orbiting scroll 18 and the fixed scroll 15, the thrust bearing 20 retreats and removes the foreign matter in the same manner as described above.
また、冷時起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13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
通す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。Further, the pressure in the compression chamber when instantaneous liquid compression occurs at the initial stage of cold start-up or during steady operation causes abnormal pressure rise and overcompression as indicated by the dotted line 63 in FIG. Since the volume of the high-pressure space communicating with it is large, the rise in discharge chamber pressure is extremely small.
また、液圧縮により第２圧縮室51a,51bに連通するイン
ジェクション溝54なども異常圧力上昇するが、細径の油
穴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、スラスト軸受け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け20が
後退し、圧縮室圧力が降下して正常運転を継続する。Further, due to the liquid compression, the injection groove 54 and the like communicating with the second compression chambers 51a and 51b also have an abnormal pressure rise, but due to the throttling effect of the small-diameter oil hole C38c and the check function of the check valve 58, the outer peripheral space 37 The injection groove 54 is cut off from the injection groove 54. As a result, the pressure in the back pressure chamber 39 does not change, and the thrust bearing 20
There is no change in the back pressure urging force that acts on the back of the. As a result, at the time of liquid compression, the thrust bearing 20 moves backward as described above due to the excessive thrust force acting on the orbiting scroll 18, and the compression chamber pressure drops to continue normal operation.
なお、減圧縮途中でスラスト軸受け20が後退することに
より、圧縮室圧力は第13図の一点鎖線63aの如く途中で
降圧する。Incidentally, the thrust bearing 20 retracts during the decompression, so that the pressure in the compression chamber is reduced in the middle as indicated by the alternate long and short dash line 63a 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18
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７図の位置から第８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との間の空気は吐出圧力を保持する。After the compressor stops, the orbiting scroll 18
Reverse swirling torque is generated in the swirl scroll 18, and the swirling scroll 18 swirls in the reverse direction, and the discharged refrigerant gas flows back to the suction side. Following the reverse flow of the discharged refrigerant gas, the check valve 50 moves from the position shown in FIG. 7 to the position shown in FIG. 8 and the Teflon coating applied to the surface of the check valve 50 causes the end face 48 of the suction pipe to move. It seals and stops the reverse flow of the discharged refrigerant gas, and the reverse orbit of the orbiting scroll 18 stops and the suction passage
The air between 42 and the discharge port 16 holds 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39との間の空間は暫くのあいだ、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
が逆旋回し、第３圧縮室60a,60bが拡大した位置に停止
し、油穴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。In addition, the passage communicating with the compression chamber with the check valve 58 of the injection passage as a boundary has the discharge pressure, but the outer peripheral space 37
The space between the back pressure chamber 39 and the back pressure chamber 39 keeps the intermediate pressure for a while, and gradually approaches the discharge pressure due to a slight inflow of lubricating oil from the discharge chamber oil sump 34. Orbiting scroll when the compressor is stopped 18
Reversely swivels, the third compression chambers 60a, 60b stop at the enlarged position, and the opening of the oil hole C38c to the outer peripheral space 37 is blocked by the lap support disk 18c.
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がインジェクション通路55を遮断するので、
外周部空間37から圧縮室への潤滑油の流入がない。After the compressor is stopped, the check valve 58 shuts off the injection passage 55 by the urging force of the coil spring 59.
There is no inflow of lubricating oil from the outer peripheral space 37 into the compression chamber.
また、圧縮機運転中、主軸受12の給油上流側は、吐出室
油溜34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が旋回スクロール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10と主軸受12と
の間の隙間の範囲内で、駆動軸４の不釣り合いや圧縮負
荷に起因して、倒れが生じるのを阻止し、上部軸受10と
主軸受12の片当たりを防止する。Further, during operation of the compressor, the oil supply upstream side of the main bearing 12 communicates with the discharge chamber oil sump 34, and the oil supply downstream side has a back pressure chamber 39 at an intermediate pressure state.
And a differential pressure is generated therebetween, and the drive shaft 4 to which the rotor 3a of the motor 3 is fixed is urged toward the orbiting scroll 18. This urging force is supported by the main body frame 5 via the thrust ball bearing 13, and within the range of the gap between the upper bearing 10 and the main bearing 12, the drive shaft 4 is subject to imbalance and compression load of the drive shaft 4. As a result, the occurrence of tilting is prevented and partial contact between the upper bearing 10 and the main bearing 12 is prevented.
また、圧縮機運転時の温度上昇により、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。Further, due to the temperature rise during operation of the compressor, the main body frame 5 made of aluminum alloy thermally expands to expand the iron liner 8, and the outer peripheral surface of the liner 8 and the inner wall of the hermetically sealed case 1 are intimately adhered to each other. This improves the airtightness between the oil sump 34 and the discharge chamber 2 and strengthens the fixing between the main body frame 5 and the hermetically sealed case 1 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51a,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61a,61bに
油インジェクションしてもよい。Further, in the above embodiment, the lubricating oil in the discharge chamber oil sump 34 is oil-injected into the second compression chambers 51a and 51b, but the first compression chambers 61a and 61b leading to the suction chamber 17 are oil-injected into the second compression chambers 51a and 51b. You may.
まだ、上記実施例ではスラスト軸受20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51a,51
bなどから中間圧力冷媒ガスを導入してもよい。また、
上記実施例では環状溝81と環状リング82を旋回スクロー
ル18のラップ支持円板18cに配置したが、スラスト軸受2
0の摺動面に配置しても同様の作用と効果を発揮する。In the above embodiment, the lubricating oil in the discharge chamber oil sump 34 is introduced into the release gap 27 and the annular groove 28 provided on the back surface of the thrust bearing 20. However, the discharge refrigerant gas from the motor chamber 6 and the second compression chambers 51a and 51a.
Intermediate pressure refrigerant gas may be introduced from b or the like. Also,
In the above embodiment, the annular groove 81 and the annular ring 82 are arranged on the lap support disk 18c of the orbiting scroll 18, but the thrust bearing 2
Even if it is arranged on the sliding surface of 0, the same action and effect are exhibited.
以上のように上記実施例によれば、旋回スクロール18
が、自転阻止機構を形成するオルダムリング24を介し
て、旋回スクロール18に旋回運動させる駆動軸４を支承
する本体フレーム５と、固定スクロール15との間に配置
され、旋回スクロール18のラップ支持円板18cは、ラッ
プ支持円板18cを支持する本体フレーム５のスラスト軸
受20と固定スクロール15の鏡板15bとの間に微少遊合状
態で支持された構成において、ラップ支持円板18cの反
圧縮室側背面を内側の背圧室39と外側の外周部空間37と
に区画すべく、ラップ支持円板18cのスラスト軸受20と
の摺動面には、オルダムリング15に係合して自転阻止機
構を形成するキー溝71に干渉しない環状溝81を設け、環
状溝81に環状リング82を遊合状態で装着してラップ支持
円板18cの本体フレーム５の側を内側の背圧室39と外側
の外周部空間37とに区画し、本体フレーム５の外側の吐
出室油溜34の潤滑油が背圧室39と外周部空間37及び第２
圧縮室51a,51bに順次通じるべく、本体フレーム５に設
けられた油穴38b,駆動軸４と主軸受12との間の軸受隙
間，旋回スクロール18を通る油穴A38a,鏡板15bに設けら
れた油穴C38c,インジェクション溝54,インジェクション
穴52a,51bを経由する油通路を設け、環状リング82がス
ラスト軸受20に接した時、環状溝81の底面と環状リング
82との間に隙間が存在すべく環状溝81を設けたことによ
り、圧縮機起動初期のような背圧室39と吸入室17の圧力
差が余り無い場合や、定常運転時のような背圧室39と吸
入室17の圧力差が有る場合には、旋回スクロール18に追
従して旋回運動をする焼結合金製の弾性を有する環状リ
ング82がラップ支持円板18cと接する本体フレーム５の
摺動面の潤滑油を油掻き作用をして潤滑油を環状溝81の
周辺に収集し、その潤滑油を環状溝81と環状リング82と
の間の隙間や、環状リング82とスラスト軸受20との間の
隙間に充満させて油密封し、背圧室39から吸入室17の側
に、潤滑油や潤滑油中に含まれる冷媒ガスが無制限に流
入するのを防ぎ、背圧室圧力を保持して旋回スクロール
18のラップ支持円板18cを固定スクロール15の鏡板15bに
付勢接触させ、圧縮室を密封して吸入冷媒ガスを圧縮
し、圧縮効率を向上することが出来る。As described above, according to the above embodiment, the orbiting scroll 18
Is disposed between the fixed scroll 15 and the main body frame 5 that supports the drive shaft 4 that causes the orbiting scroll 18 to orbit through the Oldham ring 24 that forms the rotation preventing mechanism, and the wrap support circle of the orbiting scroll 18 is provided. The plate 18c is supported in a slightly loose state between the thrust bearing 20 of the main body frame 5 that supports the lap support disk 18c and the end plate 15b of the fixed scroll 15, and the anti-compression chamber of the lap support disk 18c. In order to divide the side back surface into an inner back pressure chamber 39 and an outer peripheral space 37, the sliding surface of the lap support disk 18c with the thrust bearing 20 is engaged with the Oldham ring 15 to prevent rotation. The annular groove 81 that does not interfere with the key groove 71 that forms the key groove 71 is provided, and the annular ring 82 is mounted in the annular groove 81 in a loose state so that the body frame 5 side of the lap support disk 18c is located inside the back pressure chamber 39 and outside It is divided into the outer peripheral space 37 and the main body frame 5 Lubricating oil back pressure chamber 39 of the outer discharge chamber oil reservoir 34 and the outer peripheral portion space 37 and the second
An oil hole 38b provided in the main body frame 5, a bearing gap between the drive shaft 4 and the main bearing 12, an oil hole A38a passing through the orbiting scroll 18, and an end plate 15b so as to sequentially communicate with the compression chambers 51a, 51b. An oil passage is provided through the oil hole C38c, the injection groove 54, and the injection holes 52a and 51b, and when the annular ring 82 contacts the thrust bearing 20, the bottom surface of the annular groove 81 and the annular ring
By providing the annular groove 81 so that there is a clearance between the back pressure chamber 39 and the suction chamber 17, there is not much pressure difference between the back pressure chamber 39 and the suction chamber 17 in the initial stage of compressor start-up, or in the normal operation. When there is a pressure difference between the pressure chamber 39 and the suction chamber 17, the elastic annular ring 82 made of a sintered alloy that follows the orbiting scroll 18 and makes an orbiting motion makes contact with the lap support disk 18c. The lubricating oil on the sliding surface acts as an oil scraper to collect the lubricating oil around the annular groove 81, and the lubricating oil is collected in the gap between the annular groove 81 and the annular ring 82, the annular ring 82 and the thrust bearing 20. The space between the back pressure chamber 39 and the suction chamber 17 is filled with oil to prevent the lubricant gas or the refrigerant gas contained in the lubricant oil from flowing into the suction chamber 17 side indefinitely. Hold and orbit scroll
The lap support disk 18c of 18 is urged into contact with the end plate 15b of the fixed scroll 15 to seal the compression chamber and compress the suction refrigerant gas, thereby improving the compression efficiency.
万一、圧縮室内で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18に作用する
スラスト力が、旋回スクロール18の背面に作用する付勢
力よりも大きくなり、旋回スクロール18が軸方向に移動
し、背圧室39と吸入室17との間の気密を保持しながら旋
回スクロール18のラップ支持円板18cが、固定スクロー
ル15の鏡板15bから離れてスラスト軸受20に支持される
と共に、圧縮室の軸方向密封を解除して、圧縮室圧力を
降下させ、圧縮負荷を軽減して圧縮機の破損や摺動部の
摩耗を防止し、耐久性を向上することも出来る。In the unlikely event that liquid compression occurs in the compression chamber and the pressure in the compression chamber suddenly rises abnormally, the thrust force acting on the orbiting scroll 18 becomes larger than the biasing force acting on the back surface of the orbiting scroll 18, The orbiting scroll 18 moves in the axial direction, and the lap support disc 18c of the orbiting scroll 18 is separated from the end plate 15b of the fixed scroll 15 and the thrust bearing 20 while maintaining the airtightness between the back pressure chamber 39 and the suction chamber 17. The axial sealing of the compression chamber is released, the pressure in the compression chamber is reduced, the compression load is reduced, damage to the compressor and abrasion of sliding parts are prevented, and durability is improved. You can also
また、上記実施例によれば、ラップ支持円板18cに設け
られた環状溝81の溝寸法の一部が環状リング82の幅寸法
よりも狭く、全周にわたって同一にしないことにより、
環状リング82が環状溝81内で相対的な回転移動をしない
ので、環状リング82と環状溝81との間の摺動面摩耗がな
く、環状リング82と環状溝81との間の微少隙間を維持で
き、上述の効果をいつまでも発揮させることが出来る。Further, according to the above embodiment, a part of the groove size of the annular groove 81 provided in the lap support disk 18c is narrower than the width dimension of the annular ring 82, and is not the same over the entire circumference.
Since the annular ring 82 does not make a relative rotational movement in the annular groove 81, there is no wear on the sliding surface between the annular ring 82 and the annular groove 81, and there is a small gap between the annular ring 82 and the annular groove 81. It can be maintained and the above effects can be exhibited forever.
また上記実施例によれば、環状リング82は外方向に広が
ろうとする弾性力を有し、環状溝81の外側面に密接する
ことにより、旋回スクロール18に追従して環状リング82
が旋回運動する際に、環状リング82と環状溝81との間で
半径方向の移動がなく、両部品間の隙間を密封する油膜
形成が安定すると共に衝突も生じないので、静粛で安定
した圧縮運転ができる。Further, according to the above-described embodiment, the annular ring 82 has an elastic force that tends to spread outward, and by closely contacting the outer surface of the annular groove 81, the annular ring 82 follows the orbiting scroll 18.
There is no radial movement between the annular ring 82 and the annular groove 81 during the swiveling movement of the ring, and the formation of the oil film that seals the gap between both parts is stable and no collision occurs, so quiet and stable compression is achieved. Can drive.
また上記実施例によれば、ラップ支持円板18cに設けら
れた環状溝81内で、一対の切り口面が密着すべく環状リ
ング82に切り口を設けたことにより、環状リング82に弾
性力を備えさせながら環状リング82の切り口部を通じて
背圧室39の潤滑油が吸入室17に無制限に流入するのを阻
止し、圧縮効率の低下を防ぐことが出来る。Further, according to the above-described embodiment, the annular ring 82 is provided with the elastic force in the annular groove 81 provided in the lap support disk 18c by providing the annular ring 82 with the cut surfaces so that the pair of cut surfaces come into close contact with each other. While preventing this, the lubricating oil in the back pressure chamber 39 is prevented from flowing into the suction chamber 17 without restriction through the cut portion of the annular ring 82, and the reduction in compression efficiency can be prevented.
また上記実施例によれば、旋回スクロール18が、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との間に一定隙間を
設けて挾まれており、スラスト軸受20は、本体フレーム
５との間に一定の軸方向隙間を維持しながら吐出室２に
通じる吐出室油溜34の潤滑油圧力を利用して、常に旋回
スクロール18の方向に付勢させたことにより、万一、圧
縮室内で異常な液圧縮が生じて瞬時的に圧縮室圧力が著
しく上昇し、旋回スクロール18に作用するスラスト力が
旋回スクロール18の背面に作用する付勢力よりも大きく
なり、旋回スクロール18が軸方向に移動し、背圧室39と
吸入室17との間の気密を保持しながら旋回スクロール18
のラップ支持円板18cが、固定スクロール15の鏡板15bか
ら離れて圧縮室の軸方向隙間を生じさせても、正常な圧
力にまで圧縮室圧力の降下させることが出来ない場合に
は、ラップ支持円板18cがスラスト軸受20に支持された
状態で、スラスト軸受20が潤滑油圧力の付勢力に抗して
レリース隙間27を減少させる方向に後退させ、旋回スク
ロール18を固定スクロール15の鏡板15bから更に離反さ
せて、圧縮室の軸方向隙間を拡大し、圧縮室圧力を瞬時
的に降下させることが出来るので、圧縮負荷を軽減して
圧縮機の破損や摺動部の摩耗を防止し、耐久性を向上す
ることも出来る。また、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に大きな異物が噛み込み、旋
回スクロール18が後退し、ラップ支持円板18cがスラス
ト軸受20を押接して過負荷の生じた場合も、上述と同様
な作用によって過負荷軽減効果を発揮すると共に、噛み
込み異物を圧縮冷媒ガスの流れによって除去し、旋回ス
クロール18と固定スクロール15の異常摩耗を阻止して圧
縮冷媒ガス漏れを防ぎ、圧縮効率の低下を防ぐことも出
来る。Further, according to the above-described embodiment, the orbiting scroll 18 is provided on the side of the main body frame 5, and is sandwiched between the fixed bearing 15 and the thrust bearing 20 movable only in the axial direction. The thrust bearing 20 is always attached in the direction of the orbiting scroll 18 by utilizing the lubricating oil pressure of the discharge chamber oil sump 34 that communicates with the discharge chamber 2 while maintaining a constant axial gap with the main body frame 5. By energizing, by any chance, abnormal liquid compression will occur in the compression chamber and the pressure in the compression chamber will momentarily rise significantly, and the thrust force acting on the orbiting scroll 18 will be greater than the biasing force acting on the back surface of the orbiting scroll 18. Becomes larger, the orbiting scroll 18 moves in the axial direction, and the orbiting scroll 18 is maintained while maintaining the airtightness between the back pressure chamber 39 and the suction chamber 17.
If the wrap support disk 18c of the above does not allow the compression chamber pressure to drop to the normal pressure even if the wrap support disk 18c of the fixed scroll 15 is separated from the end plate 15b of the fixed scroll 15 to create an axial gap of the compression chamber, With the circular plate 18c supported by the thrust bearing 20, the thrust bearing 20 is retracted in the direction in which the release gap 27 is reduced against the biasing force of the lubricating oil pressure, and the orbiting scroll 18 is moved from the end plate 15b of the fixed scroll 15. By further separating them, the axial clearance of the compression chamber can be expanded and the pressure in the compression chamber can be momentarily dropped, so the compression load is reduced, damage to the compressor and wear of the sliding parts are prevented, and durability is improved. It can also improve the sex. Also, when a large foreign matter is caught in the gap between the orbiting scroll 18 and the fixed scroll 15 in the axial direction, the orbiting scroll 18 retracts, and the lap support disk 18c presses the thrust bearing 20 to cause an overload. In addition to exhibiting an overload reducing effect by the same action as described above, the trapped foreign matter is removed by the flow of the compressed refrigerant gas, the abnormal wear of the orbiting scroll 18 and the fixed scroll 15 is prevented, and the compressed refrigerant gas leakage is prevented, It is also possible to prevent a decrease in compression efficiency.
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気体
圧縮機の場合も同様の作用効果を期待できる。Although the refrigerant compressor has been described in the above embodiment,
Similar effects can be expected in the case of other gas compressors such as oxygen, nitrogen, and helium 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、自転阻止機
構を介して旋回スクロールを旋回運動させる駆動軸を支
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、旋回スクロールのラップ支持円板は、ラップ支持円
板を支持する本体フレームのスラスト軸受と固定スクロ
ールの鏡板との間に微少遊合状態で支持された構成にお
いて、ラップ支持円板の反圧縮室側背面を内側の背圧室
と外側の外周部空間とに区画すべく、ラップ支持円板と
スラスト軸受との摺動面のいずれか一方には、自転阻止
部材に係合して自転阻止機構を形成する摺動溝に干渉し
ない環状溝を設け、環状溝に環状リングを遊合状態で装
着してラップ支持円板の本体フレームの側を内側の背圧
室と外側の外周部空間とに区画し、本体フレームの外側
の油溜の潤滑油が背圧室と外周部空間及び吸入室または
圧縮室に順次通じる油通路を設け、環状リングがラップ
支持円板とスラスト軸受との摺動面に接した時、環状溝
の底面と環状リングとの間に隙間が存在すべく環状溝を
設けたことにより、圧縮機起動初期のような背圧室と吸
入室の圧力差が余り無い場合や、定常運転時のような背
圧室と吸入室の圧力差が有る場合には、環状リングがラ
ップ支持円板とスラスト軸受の摺動面の潤滑油を油掻き
作用する。環状溝の周辺に収集された潤滑油は、環状溝
と環状リングとの間の隙間およびラップ支持円板とスラ
スト軸受との摺動面と環状リングの隙間を油密封し、背
圧室から吸入室の側に潤滑油や気体が無制限に流入する
のを防ぎ、背圧室圧力を保持して旋回スクロールのラッ
プ支持円板を固定スクロールの鏡板に付勢接触させ、圧
縮室を密封して吸入気体を圧縮する。As described above, according to the present invention, the orbiting scroll is arranged between the fixed scroll and the main frame that supports the drive shaft that causes the orbiting scroll to orbit through the rotation preventing mechanism, and the orbiting scroll wrap support is provided. The disc is supported in a slightly loose state between the thrust bearing of the main body frame that supports the wrap support disc and the end plate of the fixed scroll. A sliding groove that engages with a rotation prevention member to form a rotation prevention mechanism on one of the sliding surfaces of the lap support disk and the thrust bearing so as to be divided into a pressure chamber and an outer peripheral space. An annular groove that does not interfere with the annular groove, and the annular ring is fitted in the annular groove in a loose state to partition the main frame side of the lap support disc into an inner back pressure chamber and an outer peripheral space, and Outside oil sump Is provided with an oil passage through which the lubricating oil in the order of the back pressure chamber, the outer peripheral space and the suction chamber or the compression chamber is provided, and when the annular ring makes contact with the sliding surface of the lap support disk and the thrust bearing, By providing an annular groove so that there is a gap between the annular ring and the annular ring, when there is not much pressure difference between the back pressure chamber and the suction chamber at the beginning of compressor start-up, or during normal operation, the back pressure chamber When there is a pressure difference between the suction chamber and the suction chamber, the annular ring scrapes the lubricating oil on the sliding surfaces of the lap support disk and the thrust bearing. Lubricating oil collected around the annular groove seals the gap between the annular groove and the annular ring, the sliding surface between the lap support disc and the thrust bearing, and the annular ring, and sucks it from the back pressure chamber. Prevents unlimited inflow of lubricating oil and gas to the chamber side, keeps the back pressure chamber pressure and urges the orbiting scroll wrap support disc to the fixed scroll end plate to seal and inhale the compression chamber. Compress the gas.
万一、圧縮室内で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、旋回スクロールの背面に作用する付勢力よ
りも大きくなり、旋回スクロールが軸方向に移動し、旋
回スクロールのラップ支持円板が固定スクロールの鏡板
から離れて本体フレームに支持されると共に、圧縮室の
密封を解除して、圧縮室圧力を降下させ、圧縮負荷の軽
減によって圧縮機の破損や摺動部の摩耗を防止し、振
動、騒音、耐久性に優れた効果を有するスクロール気体
圧縮機を提供することができる。If liquid compression occurs in the compression chamber and the pressure in the compression chamber rises abnormally momentarily, the thrust force that acts on the orbiting scroll becomes greater than the biasing force that acts on the back surface of the orbiting scroll, causing the orbiting scroll to scroll. Move in the axial direction, the wrap support disc of the orbiting scroll is separated from the end plate of the fixed scroll and supported by the main body frame, and the compression chamber pressure is released by reducing the compression chamber pressure and reducing the compression load. Thus, it is possible to provide a scroll gas compressor that prevents damage to the compressor and wear of the sliding portion, and that has excellent effects of vibration, noise, and durability.
第１図は本発明の一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シールリング部とスラ
スト軸受部の部分詳細図、第４図は同圧縮機におけるシ
ールリングの外観図、第５図は同圧縮機におけるオルダ
ムリングの外観図、第６図は同圧縮機におけるオルダム
機構部の組立外観図、第７図は第１図におけるＡ−Ａ線
に沿った横断面図、第８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９図は第８図におけるＢ
−Ｂ線に沿った部分断面図、第10図は同圧縮機の給油通
路に用いる逆止弁の外観図、第11図、第12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13図は同圧縮機の収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14図は各圧縮機にお
ける定点の圧力変化を示す特性図、第15図、第17図はそ
れぞれ異なる従来のスクロール圧縮機の縦断面図、第16
図は第15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、15a……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、18c……ラップ支持円板、20……スラスト
軸受、27……リリース隙間、28……環状溝、34……吐出
室油溜、39……背圧室、70……シールリング、81……環
状溝、82……環状リング、83……半径方向隙間。FIG. 1 is a longitudinal sectional view of a scroll refrigerant compressor according to an embodiment of the present invention, FIG. 2 is an exploded view of main parts of the compressor, and FIG. 3 is a seal ring portion and a thrust bearing portion of the compressor. Partial detailed view, FIG. 4 is an external view of a seal ring in the same compressor, FIG. 5 is an external view of an Oldham ring in the same compressor, FIG. 6 is an assembled external view of an Oldham mechanism portion in the same compressor, and FIG. 1 is a cross-sectional view taken along the line AA in FIG. 1, FIG. 8 is a position explanatory view of a check valve in a suction pipe connecting portion of the compressor, and FIG. 9 is B in FIG.
-Partial cross-sectional view taken along line B, Fig. 10 is an external view of a check valve used in the oil supply passage of the compressor, and Figs. 11 and 12 are movements of the compression chamber near the discharge port of the compressor. Explanatory drawing, FIG. 13 is a characteristic diagram showing the pressure change of the refrigerant gas from the income stroke to the discharge stroke of the compressor, FIG. 14 is a characteristic chart showing the pressure change at a fixed point in each compressor, FIG. 15, FIG. Fig. 17 is a vertical sectional view of a conventional scroll compressor,
The drawing is a partially enlarged view of FIG. 2 ... Discharge chamber, 3 ... Motor, 4 ... Drive shaft, 5 ... Body frame, 15 ... Fixed scroll, 15a ... Fixed scroll wrap, 15b ... End plate, 16 ... Discharge port, 17 ...
… Suction chamber, 18 …… Swirl scroll, 18a …… Swirl scroll wrap, 18c …… Wrap support disk, 20 …… Thrust bearing, 27 …… Release gap, 28 …… Annular groove, 34 …… Discharge chamber oil sump , 39 …… back pressure chamber, 70 …… seal ring, 81 …… annular groove, 82 …… annular ring, 83 …… radial gap.
Claims (5)
形成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、前記ラップ支持円板の
自転阻止部材を介して、前記旋回スクロールに旋回運動
させる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、前記ラップ支持円板は、前記
ラップ支持円板を支持する前記本体フレームのスラスト
軸受と前記鏡板との間に微少遊合状態で支持された構成
において、前記ラップ支持円板の反圧縮室側背面を内側
の背圧室と外側の外周部空間とに区画すべく、前記ラッ
プ支持円板と前記スラスト軸受との摺動面のいずれか一
方には、前記自転阻止部材に係合して自転阻止機構を形
成する摺動溝に干渉しない環状溝を設け、前記環状溝に
環状リングを遊合状態で装着して前記ラップ支持円板の
前記本体フレームの側を内側の背圧室と外側の外周部空
間とに区画し、前記本体フレームの外側の油溜の潤滑油
が前記背圧室と前記外周部空間及び吸入室または圧縮室
に順次通じる油通路を設け、前記環状リングが前記ラッ
プ支持円板と前記スラスト軸受との摺動面に接した時、
前記環状溝の底面と前記環状リングとの間に隙間が存在
すべく前記環状溝を設けたスクロール気体圧縮機。1. A spiral fixed scroll wrap formed on one surface of an end plate forming a part of the fixed scroll,
The orbiting scroll wrap on the wrap support disc that forms a part of the orbiting scroll is rotatably and rotatably meshed to form a spiral compression space between both scrolls, and a discharge port is provided at the center of the fixed scroll wrap. A suction chamber is provided outside the fixed scroll wrap, and the compression space is divided into a plurality of compression chambers that continuously move from the suction side toward the discharge side to form a scroll compression mechanism that compresses fluid. The orbiting scroll is disposed between the fixed scroll and the main frame that supports a drive shaft that causes the orbiting scroll to orbit through the rotation preventing member of the wrap supporting disc. Is a structure in which the thrust bearing of the main body frame that supports the lap support disk and the end plate are supported in a slightly loose state, One of the sliding surfaces of the lap support disk and the thrust bearing, the back surface of the support disk on the side opposite to the compression chamber is divided into an inner back pressure chamber and an outer peripheral space. An annular groove that does not interfere with a sliding groove that engages with a rotation preventing member to form a rotation preventing mechanism is provided, and an annular ring is fitted in the annular groove in a loosely fitted state, and the side of the main frame of the lap support disk Is divided into an inner back pressure chamber and an outer peripheral space, and an oil passage through which lubricating oil in an oil reservoir on the outer side of the main body frame sequentially communicates with the back pressure chamber and the outer peripheral space and the suction chamber or the compression chamber. Provided, when the annular ring is in contact with the sliding surface of the lap support disk and the thrust bearing,
A scroll gas compressor provided with the annular groove so that a gap exists between the bottom surface of the annular groove and the annular ring.
って同一でない請求項１に記載のスクロール気体圧縮
機。2. The scroll gas compressor according to claim 1, wherein the width dimensions of the annular groove and the annular ring are not the same over the entire circumference.
環状溝の外周側壁に密接した請求項１または２に記載の
スクロール気体圧縮機。3. The annular ring has elasticity in its radial direction,
The scroll gas compressor according to claim 1 or 2, which is in close contact with the outer peripheral side wall of the annular groove.
環状リングに切り口を設けた請求項１または２に記載の
スクロール気体圧縮機。4. The scroll gas compressor according to claim 1, wherein a cut is provided in the annular ring so that the pair of cut surfaces come into close contact with each other in the annular groove.
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一定隙間を設けて挟まれており、前
記スラスト軸受は、前記本体フレームとの間に一定の軸
方向隙間を維持しながら吐出気体圧力または吐出圧力と
吸入圧力との間の中間気体圧力を利用して、常に前記旋
回スクロールの方向に付勢された請求項１・２・３・４
のいずれかに記載のスクロール気体圧縮機。5. An orbiting scroll is provided on the side of the main body frame and is sandwiched with a fixed gap provided between a thrust bearing movable only in the axial direction and a fixed scroll. 2. The pressure is always urged in the direction of the orbiting scroll by utilizing a discharge gas pressure or an intermediate gas pressure between the discharge pressure and a suction pressure while maintaining a constant axial gap with the main body frame.・ 2 ・ 3.4
The scroll gas compressor according to any one of 1.
Priority Applications (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63159996A JPH0739836B2 (en) | 1988-06-28 | 1988-06-28 | Scroll gas compressor |
| KR1019880017493A KR950008694B1 (en) | 1987-12-28 | 1988-12-26 | 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 |
| EP88121792A EP0322894B1 (en) | 1987-12-28 | 1988-12-28 | Scroll compressor |
| DE3888147T DE3888147T2 (en) | 1987-12-28 | 1988-12-28 | Scroll compressor. |
| US07/291,233 US4958993A (en) | 1987-12-28 | 1988-12-28 | Scroll compressor with thrust support means |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63159996A JPH0739836B2 (en) | 1988-06-28 | 1988-06-28 | Scroll gas compressor |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP6256506A Division JP2615527B2 (en) | 1994-10-21 | 1994-10-21 | Scroll gas compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH029978A JPH029978A (en) | 1990-01-12 |
| JPH0739836B2 true JPH0739836B2 (en) | 1995-05-01 |
Family
ID=15705722
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP63159996A Expired - Lifetime JPH0739836B2 (en) | 1987-12-28 | 1988-06-28 | Scroll gas compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0739836B2 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2782858B2 (en) * | 1989-10-31 | 1998-08-06 | 松下電器産業株式会社 | Scroll gas compressor |
| JP2752763B2 (en) * | 1990-02-09 | 1998-05-18 | 株式会社日立製作所 | Scroll compressor and manufacturing method thereof |
| JP2615527B2 (en) * | 1994-10-21 | 1997-05-28 | 松下電器産業株式会社 | Scroll gas compressor |
| TWI251641B (en) * | 2004-12-31 | 2006-03-21 | Ind Tech Res Inst | A volute apparatus with an axial gap control function |
-
1988
- 1988-06-28 JP JP63159996A patent/JPH0739836B2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPH029978A (en) | 1990-01-12 |
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