JP2607707B2 - Scroll fluid machine - Google Patents
Scroll fluid machineInfo
- Publication number
- JP2607707B2 JP2607707B2 JP1315252A JP31525289A JP2607707B2 JP 2607707 B2 JP2607707 B2 JP 2607707B2 JP 1315252 A JP1315252 A JP 1315252A JP 31525289 A JP31525289 A JP 31525289A JP 2607707 B2 JP2607707 B2 JP 2607707B2
- Authority
- JP
- Japan
- Prior art keywords
- oil
- bearing
- drive shaft
- scroll
- pressure
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
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
- F04C29/023—Lubricant distribution through a hollow driving shaft
-
- 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
- F04C2240/00—Components
- F04C2240/50—Bearings
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Description
【発明の詳細な説明】 〔産業上の利用分野〕 本発明は圧縮機、膨張機あるいは液体ポンプなどに利
用されるスクロール流体機械に関する。The present invention relates to a scroll fluid machine used for a compressor, an expander, a liquid pump, or the like.
スクロール流体機械の圧縮作用の原理、およびこの種
のスクロール流体機械における駆動軸に作用する力，給
油方法，軸受構造等は特公昭61−19803号公報，特公昭6
3−16561号公報に記載されている。従来、この種のスク
ロール流体機械のフレーム下端に設けられている軸受へ
の給油方法は駆動軸の回転によって生じる遠心力によっ
て給油していた。また、フレームに設けたすべり軸受で
一端を吐出圧力、他端を中間圧力とした軸受の給油方法
は駆動軸の外周面に軸線と平行な給油溝を設け、一端を
軸内に設けた油穴と給油穴によって連通すると共に、油
溝の他端は中間圧力となるようにし、吐出圧力と中間圧
力の差圧力によって給油を行っていた。なお、給油溝は
荷重の作用線から外れた位置に設けられており、また給
油溝の抵抗によって給油量の調整を行う構造となってい
た。The principle of the compression action of a scroll fluid machine, and the force acting on the drive shaft, the lubrication method, the bearing structure, etc. of this kind of scroll fluid machine are described in JP-B-61-19803 and JP-B-6-197803.
No. 3-16561. Conventionally, a lubricating method for a bearing provided at a lower end of a frame of this kind of scroll fluid machine has been to lubricate by centrifugal force generated by rotation of a drive shaft. In addition, a lubrication method for a bearing in which one end is a discharge pressure and the other end is an intermediate pressure by a slide bearing provided on a frame is provided with an oil supply groove parallel to an axis on an outer peripheral surface of a drive shaft, and an oil hole provided at one end in the shaft. And an oil supply hole, and the other end of the oil groove is set at an intermediate pressure, and the oil is supplied by a differential pressure between the discharge pressure and the intermediate pressure. The lubrication groove was provided at a position deviated from the line of action of the load, and the lubrication amount was adjusted by the resistance of the lubrication groove.
上記従来技術は、フレーム下端に設けたすべり軸受へ
の給油は、駆動軸の回転による給油穴内の油の遠心力に
よる圧力で給油を行っているため、圧力が小さく給油量
を確保するのが困難であった。特に駆動軸の回転数が小
さい場合はさらに困難であり、軸受のかじりを生じ、摩
耗および焼付けを起こすことがあった。In the above prior art, oil is supplied to the slide bearing provided at the lower end of the frame by the pressure of the centrifugal force of the oil in the oil supply hole due to the rotation of the drive shaft, so that the pressure is small and it is difficult to secure the oil supply amount. Met. In particular, when the rotation speed of the drive shaft is small, it is more difficult, and galling of the bearing may occur, causing wear and seizure.
また、駆動軸の外周面に軸線と平行な給油溝を設け、
この給油溝の抵抗によって、吐出圧力と中間圧力の差圧
力で給油を行う方法では、圧力差が大きいため溝の深さ
によって抵抗が変化し、給油量を安定化させるのが困難
であった。Also, an oil supply groove parallel to the axis is provided on the outer peripheral surface of the drive shaft,
In the method of supplying oil at the pressure difference between the discharge pressure and the intermediate pressure by the resistance of the oil supply groove, the resistance changes depending on the depth of the groove due to the large pressure difference, and it has been difficult to stabilize the oil supply amount.
このように、給油溝を駆動軸に設けた場合は、抵抗を
大きくする必要があるため、溝は非常に小さく設けるこ
とが必要であり、溝内に油を溜めるのは困難であると同
時に、溝内の片側は吐出圧力、端面は中間圧力であり、
溝内で吐出圧力から中間圧力まで減圧されるため、油に
含まれた冷媒が溝内で沸騰し油切れを生じ軸のかじりを
生じ摩耗および焼付けをおこすことがあった。As described above, when the oil supply groove is provided on the drive shaft, it is necessary to increase the resistance, so the groove needs to be provided very small, and it is difficult to store oil in the groove, and at the same time, One side in the groove is the discharge pressure, the end face is the intermediate pressure,
Since the pressure is reduced from the discharge pressure to the intermediate pressure in the groove, the refrigerant contained in the oil may boil in the groove, cause the oil to run out, seize the shaft, and cause wear and seizure.
本発明の目的は、フレームに設けたすべり軸受の摩耗
および焼付きを防止したスクロール流体機械を得ること
にある。An object of the present invention is to provide a scroll fluid machine in which a sliding bearing provided on a frame is prevented from being worn and seized.
上記目的を達成するために、本発明は台板上にうず巻
状のラップを有する固定スクロールと旋回スクロールと
を有し、該旋回スクロールを駆動する駆動軸を軸受支持
するフレームと前記前回スクロールの背面側との間に形
成した背面空間を吐出圧力と吸入圧力との中間的な圧力
となるように構成するとともに、前記フレームが前記駆
動軸を旋回スクロール側の第１の軸受とフレーム端側の
第２の軸受で支承したスクロール流体機械において、駆
動軸の軸芯部分に設けられ、油溜りからの潤滑油を導く
給油通路と、給油通路から第２の軸受の内周面と駆動軸
との摺動部へ連通された給油穴と、第２の軸受の内周面
に、給油穴と干渉しない位置から駆動軸の回転によって
潤滑油を第２の軸受の吐出圧力となる一端面側から中間
的な圧力となる背面空間に排出する方向に連通された螺
旋状の油溝とを備えたものである。In order to achieve the above object, the present invention has a fixed scroll having a spiral wrap on a base plate and an orbiting scroll, and a frame bearing-supporting a drive shaft for driving the orbiting scroll, and a frame of the previous scroll. The rear space formed between the rear side and the rear side is configured to have an intermediate pressure between the discharge pressure and the suction pressure, and the frame connects the drive shaft with the first bearing on the orbiting scroll side and the end on the frame end side. In a scroll fluid machine supported by a second bearing, an oil supply passage provided in a shaft core portion of a drive shaft for guiding lubricating oil from an oil reservoir, and an inner peripheral surface of the second bearing and the drive shaft from the oil supply passage. The lubricating oil is supplied to the inner peripheral surface of the second bearing from the position that does not interfere with the lubricating hole by the rotation of the drive shaft. Back pressure It is obtained by a communicated with helical oil grooves in the direction of discharge between.
上記構成したことにより、本発明は以下の作用があ
る。With the above configuration, the present invention has the following operations.
（ａ）油溝は給油穴と干渉しない位置から第２の軸受の
吐出圧力となる一端面側から中間的な圧力となる背面空
間に排出する方向に連通されているので、給油穴によっ
て第２の軸受の内周面に導かれた潤滑油は、吐出圧力と
中間圧の差圧で駆動軸との摺動部を介して油溝へ流れ
る。(A) Since the oil groove is communicated from a position where it does not interfere with the oil supply hole to a direction from the one end face side where the discharge pressure of the second bearing becomes the discharge pressure to the back space where the intermediate pressure is generated, the second oil supply hole allows the oil groove to communicate. The lubricating oil guided to the inner peripheral surface of the bearing flows into the oil groove through a sliding portion with the drive shaft at a differential pressure between the discharge pressure and the intermediate pressure.
これにより、摺動部を通って潤滑油が循環することに
なるので、駆動軸と内周面との摺動部へ確実に給油する
ことができる。As a result, the lubricating oil circulates through the sliding portion, so that the oil can be reliably supplied to the sliding portion between the drive shaft and the inner peripheral surface.
また、油溝は螺旋状となっているので、潤滑油を摺動
部の全体にむらなく、かつ保持して溜めることができる
ので、始動時などにおいても一時的な給油不足となるこ
とがない。Further, since the oil groove is helical, the lubricating oil can be retained and stored evenly in the entire sliding portion, so that there is no temporary oil shortage even at the time of starting or the like. .
さらに、油溝の螺旋の方向は、駆動軸の回転によって
潤滑油を第２の軸受の一端面側から背面空間に排出する
方向となっているので、給油のための差圧が駆動軸の回
転により低下するという影響を避けることができる。Furthermore, since the direction of the spiral of the oil groove is such that the lubricating oil is discharged from one end surface side of the second bearing to the back space by the rotation of the drive shaft, the differential pressure for lubrication causes the rotation of the drive shaft to rotate. Can be avoided.
（ｂ）さらに、駆動軸の軸芯部分に設けられた給油通路
は、第２の軸受の内周面において、駆動軸と内周面との
摺動部に油溜りの潤滑油を導くように給油穴を介して連
通される。(B) Further, the oil supply passage provided in the shaft core portion of the drive shaft is configured to guide the lubricating oil in the oil reservoir to the sliding portion between the drive shaft and the inner peripheral surface on the inner peripheral surface of the second bearing. It is communicated via a refueling hole.
これにより、油溜り内の潤滑油は、直接に第２の軸受
と駆動軸との摺動部へ給油されるのでその給油量を充分
確保することができる。Thus, the lubricating oil in the oil sump is directly supplied to the sliding portion between the second bearing and the drive shaft, so that a sufficient amount of lubricating oil can be secured.
以下、本発明の一実施例を第１図，第２図および第３
図により説明する。第１図は本発明を実施した密閉形ス
クロール圧縦機の全体構造断面図を示す。Hereinafter, an embodiment of the present invention will be described with reference to FIGS.
This will be described with reference to the drawings. FIG. 1 is a sectional view showing the overall structure of a hermetic scroll pressurizing machine embodying the present invention.
第１図において、密閉容器１内の上方には圧縮機部２
が、下方には電動機３がそれぞれ配設され、また密閉容
器１の底部には潤滑油の油溜り４が形成されている。圧
縮機部２は、台板上にうず巻状のラップ5aをもつ固定ス
クロール５と、同じく台板上にうず巻状のラップ6aをも
つ旋回スクロール６と、固定スクロール５と一体化され
旋回スクロール６を支持するフレーム７とを備え、固定
スクロール５および旋回スクロール６のラップどうしを
噛合せた構成となっている。In FIG. 1, a compressor unit 2
However, electric motors 3 are provided below, and a lubricating oil sump 4 is formed at the bottom of the sealed container 1. The compressor unit 2 includes a fixed scroll 5 having a spiral wrap 5a on a base plate, a orbiting scroll 6 also having a spiral wrap 6a on a base plate, and an orbiting scroll integrated with the fixed scroll 5. And a frame 7 for supporting the fixed scroll 5 and the wrap of the orbiting scroll 6.
また、旋回スクロール６とフレーム７との間には、旋
回スクロール６の自転を防止するオルダム機構８が設け
られている。電動機３は密閉容器１に圧入締結され、ク
ランク軸（駆動軸）９を介して旋回スクロール６を旋回
運動させるようになっている。クランク軸９はフレーム
７に設けた主軸受10と下部軸受11とで支持され、そのク
ランクピンは旋回スクロール６の背面に設けた旋回軸受
12と嵌合されている。An Oldham mechanism 8 for preventing rotation of the orbiting scroll 6 is provided between the orbiting scroll 6 and the frame 7. The electric motor 3 is press-fitted and fastened to the closed casing 1 so as to make the orbiting scroll 6 orbit via a crankshaft (drive shaft) 9. The crankshaft 9 is supported by a main bearing 10 and a lower bearing 11 provided on a frame 7, and its crankpin is provided on a turning bearing provided on the back of the orbiting scroll 6.
Mated with 12.
クランク軸９内には主軸受10,下部軸受11および旋回
軸受12へ潤滑油を導く給油通路13が設けられ、かつ電動
機３の軸端には油溜り４の潤滑油を吸い上げて給油通路
13へ送り込む給油装置14が設けられている。An oil supply passage 13 for guiding lubricating oil to the main bearing 10, the lower bearing 11, and the slewing bearing 12 is provided in the crankshaft 9, and the lubricating oil in the oil sump 4 is sucked at the shaft end of the electric motor 3 to supply the lubricating oil.
An oil supply device 14 for feeding the oil to the fuel supply 13 is provided.
圧縮機部２は、旋回スクロール６が電動機３で駆動さ
れるクランク軸９を介して旋回運動されると、旋回スク
ロール6,固定スクロール５により形成される空間（圧縮
室）がスクロール中心方向に移動するにつれて容積を減
少して、吸入した冷媒ガスを圧縮する。圧縮された冷媒
ガスは固定スクロールの台板の中央に設けられた吐出口
16から密閉容器内の上部空間17へ吐出される。When the orbiting scroll 6 is orbited through the crankshaft 9 driven by the electric motor 3, the space (compression chamber) formed by the orbiting scroll 6 and the fixed scroll 5 moves toward the center of the scroll. As the pressure decreases, the volume of the refrigerant gas decreases and the sucked refrigerant gas is compressed. The compressed refrigerant gas is discharged at the center of the base plate of the fixed scroll.
It is discharged from 16 to the upper space 17 in the closed container.
また、旋回スクロールの背面には、圧縮行程のガスが
導かれる中間圧室15が形成されている。中間圧室15の圧
力は冷媒ガスの吸入圧力と吐出圧力の中間の圧力であ
り、スクロールの摺動部への給油は、吐出圧力と中間室
圧力の差圧を利用して行われる。第２図は下部軸受11を
説明するための拡大図である。主軸受10は外輪10a,内輪
10b,コロ10c等からなるコロ軸受であり、内輪10bの下端
にはクランク軸９を支えるためスラスト軸受18を設けて
ある。スラスト軸受18の表面には溝が設けられている。
このようにして下部軸受11の上端面部は中間圧室15の圧
力状態になっており、下端部の圧力は吐出圧力状態にな
っている。Further, an intermediate pressure chamber 15 into which gas in the compression stroke is guided is formed on the back surface of the orbiting scroll. The pressure in the intermediate pressure chamber 15 is an intermediate pressure between the suction pressure and the discharge pressure of the refrigerant gas, and the supply of oil to the sliding portion of the scroll is performed using the differential pressure between the discharge pressure and the intermediate chamber pressure. FIG. 2 is an enlarged view for explaining the lower bearing 11. Main bearing 10 is outer ring 10a, inner ring
A roller bearing including a roller 10b, a roller 10c, and the like. A thrust bearing 18 for supporting the crankshaft 9 is provided at a lower end of the inner ring 10b. The surface of the thrust bearing 18 is provided with a groove.
Thus, the upper end surface of the lower bearing 11 is in the pressure state of the intermediate pressure chamber 15, and the pressure of the lower end is in the discharge pressure state.
また、下部軸受11と摺動するクランク軸９には摺動部
と給油通路13とを連通するように給油穴20が設けられて
いる。同時に、下部軸受11にはこの給油通路20と干渉し
ない位置からクランク軸９の回転によって溝内の油を上
端へ排出する方向に下部軸受11の上端までを連通する螺
旋状の油溝19が設けられている。潤滑油は給油装置14よ
り一方は給油通路13を通り下部軸受11の摺動部を介して
油溝19を通って中間圧室15へ、他方は旋回軸受12を潤滑
した後、中間圧室15へ流入する。中間圧室15へ流入した
潤滑油は中間穴6bを介して圧縮室に流入し、冷媒ガスと
混合した状態で固定スクロール５の中央に設けた吐出口
16より密閉容器１内の上部空間17へ吐出する。このよう
に、中間圧室15へは旋回軸受12と下部軸受11を給油した
油が流入する。The crankshaft 9 that slides with the lower bearing 11 is provided with a lubrication hole 20 so that the sliding portion communicates with the lubrication passage 13. At the same time, the lower bearing 11 is provided with a helical oil groove 19 communicating from the position not interfering with the oil supply passage 20 to the upper end of the lower bearing 11 in a direction in which oil in the groove is discharged to the upper end by rotation of the crankshaft 9. Have been. After lubricating the lubricating oil from the lubricating device 14 through the lubrication passage 13 to the intermediate pressure chamber 15 through the oil groove 19 through the sliding portion of the lower bearing 11, and the other lubricating the slewing bearing 12, Flows into The lubricating oil flowing into the intermediate pressure chamber 15 flows into the compression chamber via the intermediate hole 6b, and is provided at the center of the fixed scroll 5 in a state of being mixed with the refrigerant gas.
It is discharged from 16 into the upper space 17 in the closed container 1. Thus, the oil that has supplied the slewing bearing 12 and the lower bearing 11 flows into the intermediate pressure chamber 15.
以上は下部軸受11内に単一の螺旋状の油溝19を設けた
一実施例を示したが、第５図に示すように、複数の螺旋
状の油溝19を設け、摺動部へ給油量を増加することも可
能である。第６図は、第５図に示した軸受の展開図を示
す。ここで、油溝21a,21bを第３図，第４図に示した油
溝19に追加したもので、距離l1,l2はほぼ等しく、また2
1a,21bは円筒状にした時、一個の油溝となるように距離
l3,l4は等しくなっている。The above shows one embodiment in which a single helical oil groove 19 is provided in the lower bearing 11, but as shown in FIG. 5, a plurality of helical oil grooves 19 are provided, and It is also possible to increase the amount of refueling. FIG. 6 shows a developed view of the bearing shown in FIG. Here, the oil grooves 21a and 21b are added to the oil groove 19 shown in FIGS. 3 and 4, and the distances l 1 and l 2 are substantially equal.
1a and 21b are distances so that they become one oil groove when made cylindrical.
l 3 and l 4 are equal.
第７図，第８図は油溝形状の異なる実施例を示す。第
７図では、給油通路20から下部軸受11へ給油される油量
を減少させるために油溝の幅の一部を狭くした例であ
る。7 and 8 show different embodiments having different oil groove shapes. FIG. 7 shows an example in which a part of the width of the oil groove is reduced in order to reduce the amount of oil supplied from the oil supply passage 20 to the lower bearing 11.
第８図は給油通路20から下部軸受11へ給油される油量
を増加させるために円周油溝と螺旋状油溝を連通して設
けた一例を示す。FIG. 8 shows an example in which a circumferential oil groove and a spiral oil groove are provided so as to communicate with each other to increase the amount of oil supplied from the oil supply passage 20 to the lower bearing 11.
本発明によれば以下の効果が得られる。 According to the present invention, the following effects can be obtained.
（ｉ）溝深さを大きくすることが可能となり、溝に油を
溜める容量が増大し、充分な給油量を確保でき軸受の焼
付けを防ぐことができる。(I) The groove depth can be increased, the capacity for storing oil in the groove increases, a sufficient amount of oil can be secured, and seizure of the bearing can be prevented.
（ii）このため装置が停止した場合でも螺旋状溝の中の
油は流下することがなく、したがって始動時でも充分な
油が保持されているので、始動時の抵抗が少なく焼付く
こともない。また油は摺動部に介在し下部軸受の両端で
吐出圧力と中間圧力間のシールを確実に行なえる。さら
に中間室に吐出圧力がかかることがなく旋回スクロール
に過大な力がかかるということがない。(Ii) For this reason, even if the device is stopped, the oil in the spiral groove does not flow down, so that sufficient oil is retained even at the time of starting, so that the resistance at the time of starting is small and there is no seizure. . Further, the oil is interposed in the sliding portion and can reliably seal between the discharge pressure and the intermediate pressure at both ends of the lower bearing. Further, no discharge pressure is applied to the intermediate chamber, and no excessive force is applied to the orbiting scroll.
（iii）下部軸受への給油を吐出圧力と中間圧力の差圧
で行うことが可能となるため、遠心力給油に比べ給油量
が増加できる。(Iii) Oil supply to the lower bearing can be performed at a pressure difference between the discharge pressure and the intermediate pressure, so that the amount of oil supply can be increased as compared with centrifugal force oil supply.
（iv）螺旋状溝を有しているので、摺動部全体に確実に
給油できるので焼付けを防止できる。(Iv) Since the helical groove is provided, the entire sliding portion can be reliably lubricated, so that seizure can be prevented.
第１図は本発明の一実施例を密閉形スクロール圧縮機の
縦断面図、第２図は第１図の軸受部分の拡大断面図、第
３図は下部軸受部の断面図、第４図は第３図の展開図、
第５図は他の一実施例の部分断面図、第６図は第５図の
展開図、第７図，第８図は他の実施例の下部軸受の展開
図である。 １……密閉容器,2……圧縮機器,5……固定スクロール,6
……旋回スクロール,7……フレーム,9……クランク軸
（駆動軸）,10……主軸受,11……下部軸受,12……旋回
軸受,13……給油通路,15……中間圧室,19……油溝,20…
…給油穴。1 is a longitudinal sectional view of a hermetic scroll compressor according to an embodiment of the present invention, FIG. 2 is an enlarged sectional view of a bearing portion of FIG. 1, FIG. 3 is a sectional view of a lower bearing portion, and FIG. Is a development view of FIG. 3,
FIG. 5 is a partial sectional view of another embodiment, FIG. 6 is a developed view of FIG. 5, and FIGS. 7 and 8 are developed views of a lower bearing of another embodiment. 1 ... closed container, 2 ... compressor, 5 ... fixed scroll, 6
... orbiting scroll, 7 ... frame, 9 ... crankshaft (drive shaft), 10 ... main bearing, 11 ... lower bearing, 12 ... orbiting bearing, 13 ... oil supply passage, 15 ... intermediate pressure chamber , 19 …… oil groove, 20…
… A lubrication hole.
Claims (1)
クロールと旋回スクロールとを有し、該旋回スクロール
を駆動する駆動軸を軸受支持するフレームと前記旋回ス
クロールの背面側との間に形成した背面空間を吐出圧力
と吸入圧力との中間的な圧力となるように構成するとと
もに、前記フレームが前記駆動軸を旋回スクロール側の
第１の軸受とフレーム端側の第２の軸受で支承し、前記
駆動軸の下端に油溜りが形成されたスクロール流体機械
において、 前記駆動軸の軸芯部分に設けられ、前記油溜りからの潤
滑油を導く給油通路と、 前記給油通路から前記第２の軸受の内周面と前記駆動軸
との摺動部へ連通された給油穴と、 前記第２の軸受の内周面に、前記給油穴と干渉しない位
置から前記駆動軸の回転によって潤滑油を前記第２の軸
受の前記吐出圧力となる一端面側から前記中間的な圧力
となる前記背面空間に排出する方向に連通された螺旋状
の油溝と を備えたことを特徴とするスクロール流体機械。An orbiting scroll having a fixed scroll having a spiral wrap on a base plate, and a frame supporting a drive shaft for driving the orbiting scroll and a back side of the orbiting scroll. The rear space thus formed is configured to have an intermediate pressure between the discharge pressure and the suction pressure, and the frame supports the drive shaft with a first bearing on the orbiting scroll side and a second bearing on the frame end side. In a scroll fluid machine in which an oil reservoir is formed at a lower end of the drive shaft, an oil supply passage provided at a shaft core portion of the drive shaft and guiding lubricating oil from the oil reservoir; A lubrication hole communicating with a sliding portion between the inner peripheral surface of the bearing and the drive shaft; and a lubricating oil formed by rotating the drive shaft from a position not interfering with the lubricating hole on the inner peripheral surface of the second bearing. The second axis Scroll fluid machine that from the a discharge pressure end face of comprising the said intermediate pressure communicating in a direction to discharge the back space to be a helical oil grooves.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1315252A JP2607707B2 (en) | 1989-12-06 | 1989-12-06 | Scroll fluid machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1315252A JP2607707B2 (en) | 1989-12-06 | 1989-12-06 | Scroll fluid machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH03179189A JPH03179189A (en) | 1991-08-05 |
| JP2607707B2 true JP2607707B2 (en) | 1997-05-07 |
Family
ID=18063198
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1315252A Expired - Fee Related JP2607707B2 (en) | 1989-12-06 | 1989-12-06 | Scroll fluid machine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2607707B2 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3448466B2 (en) * | 1997-09-17 | 2003-09-22 | 三洋電機株式会社 | Scroll compressor |
| KR100504931B1 (en) * | 1997-09-17 | 2005-11-22 | 산요덴키가부시키가이샤 | Scroll compressor |
| JP3448469B2 (en) * | 1997-09-26 | 2003-09-22 | 三洋電機株式会社 | Scroll compressor |
| JP5380482B2 (en) * | 2011-03-08 | 2014-01-08 | 日立アプライアンス株式会社 | Scroll compressor |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62110593U (en) * | 1985-12-27 | 1987-07-14 | ||
| JP2675313B2 (en) * | 1987-11-21 | 1997-11-12 | サンデン株式会社 | Scroll compressor |
-
1989
- 1989-12-06 JP JP1315252A patent/JP2607707B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH03179189A (en) | 1991-08-05 |
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