JPS63205492A - Scroll compressor - Google Patents
Scroll compressorInfo
- Publication number
- JPS63205492A JPS63205492A JP3855887A JP3855887A JPS63205492A JP S63205492 A JPS63205492 A JP S63205492A JP 3855887 A JP3855887 A JP 3855887A JP 3855887 A JP3855887 A JP 3855887A JP S63205492 A JPS63205492 A JP S63205492A
- Authority
- JP
- Japan
- Prior art keywords
- oil
- main shaft
- rotor
- hole
- oil supply
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 238000003780 insertion Methods 0.000 claims description 14
- 230000037431 insertion Effects 0.000 claims description 14
- 239000003921 oil Substances 0.000 abstract description 58
- 239000010687 lubricating oil Substances 0.000 abstract description 13
- 239000000945 filler Substances 0.000 abstract 3
- 238000005086 pumping Methods 0.000 abstract 1
- 230000006835 compression Effects 0.000 description 6
- 238000007906 compression Methods 0.000 description 6
- 238000004891 communication Methods 0.000 description 3
- 239000012530 fluid Substances 0.000 description 3
- 239000000463 material Substances 0.000 description 3
- 239000007769 metal material Substances 0.000 description 3
- 230000002159 abnormal effect Effects 0.000 description 2
- 239000003795 chemical substances by application Substances 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000005461 lubrication Methods 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 230000002411 adverse Effects 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000010363 phase shift Effects 0.000 description 1
- 239000003507 refrigerant Substances 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 238000004804 winding Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/028—Means for improving or restricting lubricant flow
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は、例えば冷凍装置や空気調和装置等の機器に使
用するスクロール圧縮機に関する。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a scroll compressor used in equipment such as refrigeration equipment and air conditioners.
先ず、スクロール流体機械の原理について簡単に述べる
。First, the principle of the scroll fluid machine will be briefly described.
第６図はスクロール流体機械を圧縮機として用いた場合
の基本的な構成要素と圧縮原理を示しており、同図にお
いて、符号７１は固定スクロール、７２は揺動スクロー
ル、７３は吸入室、７４は吐出ボート、７５は圧縮室で
ある。また、符号０は前記固定スクロール７１の中心で
ある。なお、前記固定スクロール７１および前記揺動ス
クロール７２は、同一の形状で巻方向が互いに反対の渦
巻７１ａ、７２ａを有しており、これら渦巻７１ａ。FIG. 6 shows the basic components and compression principle when a scroll fluid machine is used as a compressor. In the figure, 71 is a fixed scroll, 72 is an oscillating scroll, 73 is a suction chamber, and 74 is a fixed scroll. is a discharge boat, and 75 is a compression chamber. Further, the code 0 is the center of the fixed scroll 71. The fixed scroll 71 and the swinging scroll 72 have spirals 71a and 72a having the same shape and opposite winding directions, and these spirals 71a.
７２ａの形状は従来から知られているようにインボリュ
ート曲線１田弧等から構成されている。The shape of 72a is constituted by an involute curve, etc., as is conventionally known.
次に、スクロール圧縮機の動作について説明する。Next, the operation of the scroll compressor will be explained.
今、固定スクロール７１は空間に対し静止しており、揺
動スクロール７２は固定スクロール７１に対して１８０
６位相のずれた状態で組み合わされ、固定スクロール７
１の中心Ｏの回りを自転しない公転運動を行い、第６図
ｆａｌ、 （ｂｌ、 （Ｃ）および（ｄｌに示すように
０°、９０’、１８０°、２７０゜として運動する。同
図（ａｌに示すＯｏの状態で吸入室７３のガスの閉じ込
みが完了し、渦巻７１ａ。Now, the fixed scroll 71 is stationary with respect to space, and the swinging scroll 72 is 180 degrees relative to the fixed scroll 71.
6 Fixed scroll 7 combined with phase shift
It performs orbital motion without rotating around the center O of 1, and moves at 0°, 90', 180°, and 270° as shown in Figure 6 fal, (bl, (C), and (dl). The confinement of gas in the suction chamber 73 is completed in the state Oo shown in al, and the swirl 71a is formed.
７２２間に圧縮室７５が形成される。そして、揺動スク
ロール７２の運動に伴い、圧縮室７５は順次その容積を
減じ、その中のガスは圧縮されて固定スクロール７１の
中心部に設けられた吐出ポート７４から排出される。A compression chamber 75 is formed between 722. As the orbiting scroll 72 moves, the compression chamber 75 gradually reduces its volume, and the gas therein is compressed and discharged from the discharge port 74 provided at the center of the fixed scroll 71.
スクロール圧縮機の名前で知られている装置の概略は以
上の通りである。The outline of the device known as a scroll compressor is as follows.
従来、この種のスクロール圧縮機は特願昭５９−４２５
０３号に開示され、第７図に示すように構成されている
。これを同図に基づいて説明すると、同図において、符
号１で示すものは渦巻１ａを台板１ｂの一側に有する固
定スクロール、２は渦巻２ａを台板２ｂの一側に有する
揺動スクロール、３は吸入口（吸入室）、４は吐出ポー
ト、５は両渦巻１ａ、２ａを互いに組み合わせた時雨渦
巻１ａ、２ａ間に形成される圧縮室、６は上下方向に設
けられた大小２つの孔７ａ、７ｂからなる段状の挿通孔
７をその軸線上に有するスクロール圧縮機用のロータで
ある。このロータ６の両孔のうち大孔７ａはカウンタボ
アと呼ばれており、後述する主軸の両輪光間を大きくと
るために形成されている。８はこのロータ６と同一の軸
線上に設けられ運転時にロータ６と共に回転するオイル
ポンプ用の筒体（オイルキャンプ）、９はこの筒体８の
上方に設けられかつ前記ロータ６の小孔７ｂ内に固定さ
れた段状の主軸、１０および１１は軸受フレーム、１２
はモータステータ、１３はシェル、１４はこのシェル１
３の底部に設けられた油溜、１５はオルダム継手、１６
は邪魔板、１７は吸入管、１８は吐出管、１９は前記主
軸９の大径部９ａに形成した偏心孔６０ａ内に固着され
かつ前記揺動スクロール２の揺動スクロール軸２ｃを軸
支する揺動スクロール軸受、２０は前記主軸９の大径部
９ａの外周面６１ａを軸支する第１の主軸受、２１は前
記主軸９の小径部９ｂを軸支する第２の主軸受、２２は
前記揺動スクロール２の台板２ｂを軸方向から支承する
第１のスラスト軸受、２３は前記主軸９の大径部９ａと
小径部９ｂ間の段部９Ｃを軸方向から支承する第２のス
ラスト軸受、２４は前記主軸９に偏心するように設けら
れ開口部２４ａを有する給油孔、２５はガス抜き孔、２
６および２７は返油孔、２８および２９は吸入ガス経路
用の連通路である。なお、前記固定スクロール１は軸受
フレーム１０．１１と共にボルト（図示せず）等によっ
て共線めされている。Conventionally, this type of scroll compressor was manufactured by patent application No. 59-425.
It is disclosed in No. 03 and is configured as shown in FIG. To explain this based on the same figure, in the same figure, the reference numeral 1 indicates a fixed scroll having a spiral 1a on one side of the base plate 1b, and 2 indicates an oscillating scroll having a spiral 2a on one side of the base plate 2b. , 3 is an inlet (suction chamber), 4 is a discharge port, 5 is a compression chamber formed between the sigure volutes 1a and 2a by combining both volutes 1a and 2a, and 6 is a large and small space provided in the vertical direction. This is a rotor for a scroll compressor, which has a stepped insertion hole 7 consisting of holes 7a and 7b on its axis. Among the two holes of the rotor 6, the large hole 7a is called a counterbore, and is formed to increase the distance between the two wheel lights of the main shaft, which will be described later. 8 is a cylinder (oil camp) for an oil pump that is provided on the same axis as this rotor 6 and rotates together with the rotor 6 during operation; 9 is a cylinder that is provided above this cylinder 8 and is located in the small hole 7b of the rotor 6; a stepped main shaft fixed therein; 10 and 11 are bearing frames; 12;
is the motor stator, 13 is the shell, and 14 is this shell 1
Oil reservoir provided at the bottom of 3, 15 Oldham joint, 16
17 is a baffle plate, 17 is a suction pipe, 18 is a discharge pipe, and 19 is fixed in an eccentric hole 60a formed in the large diameter portion 9a of the main shaft 9, and pivotally supports the oscillating scroll shaft 2c of the oscillating scroll 2. An oscillating scroll bearing, 20 is a first main bearing that pivotally supports the outer peripheral surface 61a of the large diameter portion 9a of the main shaft 9, 21 is a second main bearing that pivotally supports the small diameter portion 9b of the main shaft 9, 22 is a A first thrust bearing axially supports the base plate 2b of the oscillating scroll 2, and a second thrust bearing 23 supports the stepped portion 9C between the large diameter portion 9a and the small diameter portion 9b of the main shaft 9 from the axial direction. a bearing; 24 is an oil supply hole provided eccentrically to the main shaft 9 and has an opening 24a; 25 is a gas vent hole;
6 and 27 are oil return holes, and 28 and 29 are communication passages for the suction gas path. Note that the fixed scroll 1 and the bearing frame 10.11 are collinear with each other by bolts (not shown) or the like.
このように構成されたスクロール圧縮機においては、ロ
ータ６が回転すると主軸９およびオルダム継手１５を介
して揺動スクロール２が公転運動を始める。このとき、
冷媒ガスは吸入管１７からシェル１３内に吸入され実線
矢印で示すように軸受フレーム１１とモータステータ１
２との間の連通孔２８．ロータ６とモータステータ１２
との間のエアギャップ等を通過してモータを冷却した後
、シェル１３と軸受フレーム１０．１１との間の連通孔
２９を経て吸入口３から圧縮室６への取り込まれ圧縮さ
れる。そして、圧縮ガスは吐出ポート４を経て吐出管１
８から圧縮機外に排出される。In the scroll compressor configured in this manner, when the rotor 6 rotates, the oscillating scroll 2 begins to revolve via the main shaft 9 and the Oldham joint 15. At this time,
The refrigerant gas is sucked into the shell 13 through the suction pipe 17, and is then sucked into the bearing frame 11 and the motor stator 1 as shown by the solid arrow.
2 and the communication hole 28. Rotor 6 and motor stator 12
After passing through an air gap between the shell 13 and the bearing frame 10.11 to cool the motor, the air is drawn into the compression chamber 6 from the suction port 3 through the communication hole 29 between the shell 13 and the bearing frame 10.11, and is compressed. Then, the compressed gas passes through the discharge port 4 into the discharge pipe 1
8 is discharged from the compressor.
一方、油溜１４の潤滑油は、破線矢印で示すように移動
し、筒体８および給油孔２４による遠心ポンプ作用によ
って各軸受１９，２１を給油し、さらに軸受１９からは
軸受２２．２０．２３の順に給油する。ここで、使用潤
滑油は返油孔２６゜２７を通過して油溜１４に戻される
。On the other hand, the lubricating oil in the oil reservoir 14 moves as shown by the broken line arrow, and is supplied to each of the bearings 19, 21 by the centrifugal pump action of the cylinder 8 and the oil supply hole 24, and is further supplied from the bearing 19 to the bearings 22, 20, . Refuel in the order of 23. Here, the lubricating oil used passes through the oil return holes 26 and 27 and is returned to the oil reservoir 14.
ところで、この種のスクロール圧縮機においては、主軸
９の回転による遠心ポンプ作用によって揺動スクロール
軸受１９に潤滑油を供給する給油方式が採用されている
ため、給油能力が主軸９の回転数ならびに主軸９の中心
軸線と給油孔２４の軸線間の距離に大きく左右される。Incidentally, in this type of scroll compressor, a lubrication method is adopted in which lubricating oil is supplied to the oscillating scroll bearing 19 by the centrifugal pump action caused by the rotation of the main shaft 9. 9 and the axis of the oil supply hole 24.
この結果、圧縮機が定格回転数より低い回転数で運転さ
れると、給油能力が急激に低下して潤滑に必要な油量が
不足し、揺動スクロール軸受１９等が焼損したり異常摩
耗したりする虞があった。特に、スクロール圧縮機は、
固定スクロール１．揺動スクロール等の圧縮機用構成部
品をシェル１３内の下方に設置することが技術面、コス
ト面で困難であることから、これらの構成部品は潤滑油
の貯溜面から相当高い位置に位置付けられており、この
ため給油孔２４の軸線方向寸法を大きく設定しなければ
ならず、低回転数運転時に給油不足が生じ易いという問
題があった。As a result, when the compressor is operated at a rotation speed lower than the rated rotation speed, the oil supply capacity decreases rapidly and the amount of oil necessary for lubrication becomes insufficient, causing burnout or abnormal wear of the oscillating scroll bearing 19, etc. There was a risk that the In particular, scroll compressors
Fixed scroll 1. Since it is difficult from a technical and cost standpoint to install compressor components such as the oscillating scroll below the shell 13, these components are located at a considerably high position from the lubricating oil reservoir surface. Therefore, the axial dimension of the oil supply hole 24 must be set large, which poses a problem in that oil supply is likely to be insufficient during low rotational speed operation.
そこで、主軸９の外径を大きい寸法に設定することが考
えられるが、この場合挿通孔７の口径や主軸受２１の直
径が大きくなってモータ効率が低下したり、軸受部分の
回転損失が生じたりするという不都合があった。Therefore, it may be possible to set the outer diameter of the main shaft 9 to a larger size, but in this case, the diameter of the insertion hole 7 and the diameter of the main bearing 21 will become larger, reducing motor efficiency and causing rotational loss in the bearing part. There was the inconvenience of
本発明はこのような事情に鑑みなされたもので、低速運
転時にも軸受部分への必要な油量の潤滑油を供給するこ
とができ、もって圧縮機運転上の信頼性を向上させるこ
とができるスクロール圧縮機を提供するものである。The present invention was developed in view of these circumstances, and it is possible to supply the required amount of lubricating oil to the bearing portion even during low-speed operation, thereby improving the reliability of compressor operation. The present invention provides a scroll compressor.
本発明に係るスクロール圧縮機は、ロータの挿通孔内の
段部に対向する段部およびこの段部に開口する給油孔を
有する主軸を備え、この主軸の大径部とロータの内周面
との間に環状体を装着することにより、挿通孔の段部上
方に給油孔に連通ずるオイルポケットを形成し、このオ
イルポケットに連通ずる給油路を主軸に設けたものであ
る。The scroll compressor according to the present invention includes a main shaft having a stepped portion opposite to the stepped portion in the insertion hole of the rotor and an oil supply hole opening in the stepped portion, and a large diameter portion of the main shaft and an inner circumferential surface of the rotor. By attaching an annular body between them, an oil pocket communicating with the oil supply hole is formed above the stepped portion of the insertion hole, and an oil supply passage communicating with the oil pocket is provided on the main shaft.
本発明においては、主軸の外径を大きく設定することな
く、給油経路の偏心量を大きくすることができる。In the present invention, the amount of eccentricity of the oil supply path can be increased without increasing the outer diameter of the main shaft.
第１図は本発明に係るスクロール圧縮機の要部を示す断
面図、第２図は同じくスクロール圧縮機の環状体を示す
斜視図で、同図以下において第６図と同一の部材につい
ては同一の符号を付し、詳細な説明は省略する。同図に
おいて、符号３１で示すものは前記揺動スクロール２に
回転力を伝達する段状の主軸で、焼き嵌めあるいは圧入
によって前記ロータ６の小孔７ｂ内に大孔７ａ内を挿通
し嵌合固定されており、外周面には前記挿通孔７内の段
部７ｃに対向する段部３１ａが設けられている。また、
この主軸３１には前記段部３１ａに開口する給油孔３２
が設けられている。３３はオイルポンプ用の筒体で、前
記主軸９の下方に位置し前記挿通孔７の小孔７ｂ内に嵌
合固定され、かつ前記ロータ６と同一の軸線上に設けら
れており、運転時にロータ６と共に回転するように構成
されている。３４は前記給油孔３２に連通ずるオイルポ
ケットで、前記主軸３１の大径部３１ａと前記ロータ６
の内周面との間にＦｅ系の金属材料から＝８−
なる環状体３５を焼き嵌めあるいは圧入によって装着す
ることにより、前記挿通孔７の段部７Ｃ上方に形成され
ている。３６はこのオイルポケット３４に連通ずる給油
溝で、前記主軸３１の外周面に形成されている。この給
油溝３６は偏心量が前記給油孔３２の偏心量より小さく
なる位置に位置付けられている。Fig. 1 is a cross-sectional view showing the main parts of a scroll compressor according to the present invention, and Fig. 2 is a perspective view showing the annular body of the scroll compressor. The detailed explanation will be omitted. In the figure, the reference numeral 31 denotes a stepped main shaft that transmits rotational force to the oscillating scroll 2, and is fitted by inserting the large hole 7a into the small hole 7b of the rotor 6 by shrink fitting or press fitting. It is fixed, and a stepped portion 31a facing the stepped portion 7c in the insertion hole 7 is provided on the outer circumferential surface. Also,
This main shaft 31 has an oil supply hole 32 that opens in the step portion 31a.
is provided. Reference numeral 33 denotes a cylinder for the oil pump, which is located below the main shaft 9, is fitted and fixed in the small hole 7b of the insertion hole 7, and is provided on the same axis as the rotor 6, during operation. It is configured to rotate together with the rotor 6. 34 is an oil pocket that communicates with the oil supply hole 32, and is connected to the large diameter portion 31a of the main shaft 31 and the rotor 6.
An annular body 35 made of Fe-based metal material is fitted between the inner circumferential surface of the through hole 7 by shrink fitting or press fitting, thereby forming the annular body 35 above the stepped portion 7C of the insertion hole 7. An oil supply groove 36 communicates with the oil pocket 34 and is formed on the outer peripheral surface of the main shaft 31. The oil supply groove 36 is positioned at a position where the amount of eccentricity is smaller than the amount of eccentricity of the oil supply hole 32.
このように構成されたスクロール圧縮機においては、挿
通孔７の段部７ｃの上方にオイルポケット３４を形成し
たから、主軸３１の外径を太き（設定することなく、主
軸３１の中心軸線からの給油孔３２および給油溝３６の
偏心量を大きくすることができる。In the scroll compressor configured in this way, since the oil pocket 34 is formed above the stepped portion 7c of the insertion hole 7, the outer diameter of the main shaft 31 can be made thicker (without setting it, from the central axis of the main shaft 31). The amount of eccentricity of the oil supply hole 32 and the oil supply groove 36 can be increased.
したがって、運転時に筒体３３内の潤滑油に作用する遠
心力が大きくなるから、定格回転数より低い回転数で主
軸３１を回転しても、主軸受２０゜２１等の軸受部分に
必要な油量の潤滑油を供給することができる。この場合
、第１図に破線で示すように遠心ポンプ作用によって筒
体３３内を上昇した潤滑油が、小孔７ｂ、給油溝３６を
通過した後、オイルポケット３４を経て給油孔３２に圧
送される。Therefore, since the centrifugal force acting on the lubricating oil in the cylinder 33 increases during operation, even if the main shaft 31 is rotated at a rotation speed lower than the rated rotation speed, the oil required for the bearing parts such as the main bearings 20 and 21 will be reduced. can supply a large amount of lubricating oil. In this case, as shown by the broken line in FIG. 1, the lubricating oil that has risen inside the cylinder 33 due to the action of the centrifugal pump passes through the small hole 7b and the oil supply groove 36, and is then forced into the oil supply hole 32 through the oil pocket 34. Ru.
なお、本実施例においては、給油路としての給油溝３６
を主軸３１の外周面とロータ６の内周面との間に形成す
る例を示したが、本発明はこれに限定されるものではな
く、第３図に示すように主軸３７内に給油孔３８を設け
ても実施例と同様の効果を奏する。同図において、符号
３９で示す筒体は主軸３７の下端部に取り付けられてい
る。この場合、主軸３７はロータ６に挿通されており、
これによりロータ６の取付強度を高くすることができる
。In addition, in this embodiment, the oil supply groove 36 as the oil supply path
Although an example is shown in which an oil supply hole is formed between the outer circumferential surface of the main shaft 31 and the inner circumferential surface of the rotor 6, the present invention is not limited to this, and as shown in FIG. Even if 38 is provided, the same effects as in the embodiment can be obtained. In the figure, a cylindrical body designated by reference numeral 39 is attached to the lower end of the main shaft 37. In this case, the main shaft 37 is inserted through the rotor 6,
Thereby, the mounting strength of the rotor 6 can be increased.
また、本実施例においては、環状体３５の材料としてＦ
ｅ系の金属材料からなる場合を示したが、本発明はＣｕ
系あるいはＡＩ系の金属材料からなるものでも何等差し
支えない。すなわち、環状体３５の材料は、ロータ６の
主軸３１に対する固着力に悪影響を及ぼさない程度の剛
性をもつ材料であればよい。In addition, in this embodiment, F is used as the material of the annular body 35.
Although the case is shown in which it is made of e-based metal material, the present invention
There is no problem even if it is made of metal material such as aluminum or AI. That is, the material of the annular body 35 may be any material as long as it has a rigidity that does not adversely affect the fixing force of the rotor 6 to the main shaft 31.
さらに、本発明における環状体３５の形状は前述した実
施例に限定されず、その取付作業性を良好にするために
例えば第４図および第５図に示す環状体４０．４１でも
よく、その形状は適宜変更することが自由である。Further, the shape of the annular body 35 in the present invention is not limited to the above-mentioned embodiments, and may be an annular body 40, 41 shown in FIGS. 4 and 5, for example, in order to improve the installation workability. are free to change as appropriate.
以上説明したように本発明によれば、ロータの挿通孔内
の段部に対向する段部およびこの段部に開口する給油孔
を有する主軸を備え、この主軸の大径部とロータの内周
面との間に環状体を装着することにより、挿通孔の段部
上方に給油孔に連通ずるオイルポケットを形成し、この
オイルポケットに連通ずる給油路を主軸に設けたので、
給油経路の偏心量を大きくすることができる。したがっ
て、従来のように給油不足による軸受の焼損や異常摩耗
が生じることがないから、低速運転時にも軸受部分への
必要な油量の潤滑油を供給することかでき、圧縮機運転
上の信頼性を向上させることができる。また、従来のよ
うに主軸の外径を大きく設定する必要がないから、それ
だけモータ効率の低下および回転損失の発生を防止する
こともできる。As explained above, according to the present invention, the main shaft is provided with a stepped portion opposite to the stepped portion in the insertion hole of the rotor, and an oil supply hole opened in the stepped portion, and the large diameter portion of the main shaft and the inner periphery of the rotor are provided. By installing an annular body between the surface and the surface, an oil pocket that communicates with the oil supply hole is formed above the step of the insertion hole, and an oil supply path that communicates with this oil pocket is provided on the main shaft.
The amount of eccentricity of the oil supply path can be increased. Therefore, there is no risk of burnout or abnormal wear of the bearings due to lack of oil supply, unlike in the past, and the necessary amount of lubricating oil can be supplied to the bearings even during low-speed operation, ensuring reliable compressor operation. can improve sex. Further, since it is not necessary to set the outer diameter of the main shaft large as in the conventional case, it is possible to prevent a decrease in motor efficiency and occurrence of rotational loss.
第１図は本発明に係るスクロール圧縮機の要部を示す断
面図、第２図は同じくスクロール圧縮機の環状体を示す
斜視図、第３図は他の実施例を示す断面図、第４図およ
び第５図は他の実施例における環状体を示す斜視図、第
６図（ａｌ〜（ｄ）はスクロール流体機械の原理を説明
するための図、第７図は従来のスクロール圧縮機を示す
断面図である。
６・・・ロータ、７・・・挿通孔、７ａ・・・大孔、７
ｂ・・・小孔、７ｃ・・・段部、３１・・・・主軸、３
１ａ・・・段部、３２・・・給油孔、３３・・・筒体、
３４・・・オイルポケット、３５・・・環状体、３６・
・・給油溝。
代 理 人 大 岩 増 雄
第７図
１・事件の表示 特願昭２ニー’１３’；’；）Ｊ
’５２、発明の名称
スフリール５．六壱（
３、補正をする者
代表者志岐守哉
４、代理人
５、補正の対象
（１１明細書の発明の詳細な説明の欄
（２）図面
６、補正の内容
（１１明細書６頁１７行〜１８行の「軸受２２゜２０．
２．３の順に給油する」を「軸受２０，２２゜２３の順
に給油する」と補正する。
（２）同書７頁１１行の「揺動スクロール等」を「揺動
スクロール２等」と補正する。
（３）第７図を添付図面の通り補正する。
以 上
第７図FIG. 1 is a sectional view showing essential parts of a scroll compressor according to the present invention, FIG. 2 is a perspective view showing an annular body of the scroll compressor, FIG. 3 is a sectional view showing another embodiment, and FIG. 5 and 5 are perspective views showing annular bodies in other embodiments, FIGS. 6 (al to d) are diagrams for explaining the principle of a scroll fluid machine, and FIG. 7 is a diagram showing a conventional scroll compressor. It is a sectional view showing 6... Rotor, 7... Insertion hole, 7a... Large hole, 7
b...Small hole, 7c...Step, 31...Main shaft, 3
1a...Step part, 32...Oil supply hole, 33...Cylinder body,
34... Oil pocket, 35... Annular body, 36.
...Oil supply groove. Agent Masuo Oiwa Figure 7 1/Indication of the case Patent application 2013 '13';';)J
'52, Name of the invention Soufrill 5. Rokuichi (3. Person making the amendment Representative Moriya Shiki 4, Agent 5, Subject of amendment (11 Detailed description of the invention column (2) of the specification) Drawing 6, Contents of the amendment (11 Specification page 6) Lines 17-18 "Bearing 22°20.
2.3, "lubricate in this order" is corrected to "lubricate bearings 20, 22, and 23 in this order." (2) Correct "oscillating scroll, etc." on page 7, line 11 of the same book to "oscillating scroll 2, etc." (3) Figure 7 will be corrected as shown in the attached drawings. Above Figure 7
Claims (5)
の挿通孔をその軸線上に有するスクロール圧縮機用のロ
ータと、このロータと同一の軸線上に設けられロータと
共に回転するオイルポンプ用の筒体と、この筒体の上方
に設けられかつ前記ロータの小孔内に固定され前記挿通
孔内の段部に対向する段部およびこの段部に開口する給
油孔を有する主軸とを備え、この主軸の大径部と前記ロ
ータの内周面との間に環状体を装着することにより、前
記挿通孔の段部上方に前記給油孔に連通するオイルポケ
ットを形成し、このオイルポケットに連通する給油路を
前記主軸に設けたことを特徴とするスクロール圧縮機。(1) A rotor for a scroll compressor that has a stepped insertion hole on its axis consisting of two large and small holes provided in the vertical direction, and an oil pump that is provided on the same axis as this rotor and rotates together with the rotor. a main shaft having a step provided above the cylinder, fixed in the small hole of the rotor and facing the step in the insertion hole, and an oil supply hole opening in the step. By installing an annular body between the large diameter portion of the main shaft and the inner circumferential surface of the rotor, an oil pocket communicating with the oil supply hole is formed above the stepped portion of the insertion hole, and this oil pocket A scroll compressor characterized in that the main shaft is provided with an oil supply passage communicating with the main shaft.
１項記載のスクロール圧縮機。(2) The scroll compressor according to claim 1, wherein the cylindrical body is fixed to the rotor.
項記載のスクロール圧縮機。(3) Claim 1 in which the cylinder is fixed to the main shaft
Scroll compressor as described in section.
位置に位置付けられている特許請求の範囲第１項、また
は第２項または第３項記載のスクロール圧縮機。(4) The scroll compressor according to claim 1, 2, or 3, wherein the oil supply hole is located at a position having an eccentricity larger than the eccentricity of the oil supply path.
る特許請求の範囲第１項、または第２項または第４項記
載のスクロール圧縮機。(5) The scroll compressor according to claim 1, 2, or 4, wherein the oil supply passage is located between the main shaft and the rotor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3855887A JPS63205492A (en) | 1987-02-20 | 1987-02-20 | Scroll compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3855887A JPS63205492A (en) | 1987-02-20 | 1987-02-20 | Scroll compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS63205492A true JPS63205492A (en) | 1988-08-24 |
Family
ID=12528622
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3855887A Pending JPS63205492A (en) | 1987-02-20 | 1987-02-20 | Scroll compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS63205492A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008190329A (en) * | 2007-01-31 | 2008-08-21 | Daikin Ind Ltd | Hermetic compressor |
-
1987
- 1987-02-20 JP JP3855887A patent/JPS63205492A/en active Pending
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008190329A (en) * | 2007-01-31 | 2008-08-21 | Daikin Ind Ltd | Hermetic compressor |
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