JP2689659B2 - Scroll compressor - Google Patents
Scroll compressorInfo
- Publication number
- JP2689659B2 JP2689659B2 JP1316028A JP31602889A JP2689659B2 JP 2689659 B2 JP2689659 B2 JP 2689659B2 JP 1316028 A JP1316028 A JP 1316028A JP 31602889 A JP31602889 A JP 31602889A JP 2689659 B2 JP2689659 B2 JP 2689659B2
- Authority
- JP
- Japan
- Prior art keywords
- scroll
- slider
- main shaft
- oil
- oil flow
- 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
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
-
- 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
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
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〕 この発明は、空調用・冷蔵庫用に用いられるスクロー
ル圧縮機にかかわり、特に油流路の改良に関するもので
ある。Description: TECHNICAL FIELD The present invention relates to a scroll compressor used for an air conditioner / refrigerator, and particularly relates to improvement of an oil flow path.
第５図は例えば特開昭59−120794号公報に示された従
来のスクロール圧縮機の要部軸方向断面図、第６図はそ
の要部横断面図である。図において、（１）は固定スク
ロール、（２）は固定スクロール（１）とともに圧縮室
（1a）を形成する揺動スクロール、（３）は揺動スクロ
ール（２）の反圧縮室側にあるスラスト面、（４）はス
ラスト面（３）の中心部に設けられた揺動軸、（５）は
揺動スクロール（２）のスラスト面（３）をスラスト軸
受（5a）を介して支承するフレーム、（６）はフレーム
（５）に主軸受（5b）を介して支承されかつ揺動スクロ
ール（２）に駆動力を伝達する主軸、（７）は主軸
（６）を駆動するモータ、（８）は揺動軸（４）に回転
自在に収められかつ主軸（６）の軸線と直角な面内にお
いてスライド可能であるスライダー、（９）は主軸
（６）にその軸方向に貫通するように設けられた第１の
油流路、（10）は揺動軸（４）とスライダー（８）とで
囲まれた第２の油流路、（11）は主軸（６）とスライダ
ー（８）とで囲まれた第３の油流路、（12）は主軸
（６）と揺動スクロール（２）とで囲まれた第４の油流
路、（13）は固定スクロール（１）と揺動スクロール
（２）とが接触する接点である。FIG. 5 is an axial sectional view of a main part of a conventional scroll compressor disclosed in, for example, JP-A-59-120794, and FIG. 6 is a horizontal cross-sectional view of the main part. In the figure, (1) is a fixed scroll, (2) is an orbiting scroll that forms a compression chamber (1a) with the fixed scroll (1), and (3) is thrust on the side opposite to the compression chamber of the orbiting scroll (2). Surface, (4) a swing shaft provided at the center of the thrust surface (3), and (5) a frame for supporting the thrust surface (3) of the swing scroll (2) through a thrust bearing (5a). , (6) are main shafts that are supported by the frame (5) via main bearings (5b) and transmit the driving force to the orbiting scroll (2), (7) are motors that drive the main shaft (6), and (8) ) Is a slider that is rotatably housed in the swing shaft (4) and is slidable in a plane perpendicular to the axis of the main shaft (6), and (9) so that it penetrates the main shaft (6) in its axial direction. The first oil flow path provided (10) includes a swing shaft (4) and a slider (8). The enclosed second oil passage, (11) is the third oil passage enclosed by the spindle (6) and the slider (8), and (12) is the spindle (6) and the orbiting scroll (2). A fourth oil flow path surrounded by and is a contact point (13) where the fixed scroll (1) and the orbiting scroll (2) come into contact with each other.
次に動作について説明する。モータ（７）の駆動力は
主軸（６）に伝達され、主軸（６）の回転によりスライ
ダー（８）は一定偏心量ｒを保ちつつ回転し、またスラ
イダー（８）と主軸（６）との接触面に沿って移動可能
であり、スライダー（８）の回転により揺動スクロール
（２）は一定偏心量を保ちつつ揺動運動を繰り返すこと
により、固定スクロール（１）と揺動スクロール（２）
とで囲まれた圧縮室（1a）の体積が減少し圧縮が行われ
るが、第６図において揺動スクロール（２）とスライダ
ー（８）との遠心力Fcと圧縮を行うことにより生ずるガ
ス負荷力Fgが働き、その合力Ｆなる力が揺動スクロール
（２）と固定スクロール（１）に押しつけ、揺動スクロ
ール（２）を固定スクロール（１）との接点（13）は隙
間がなく漏れの少ない圧縮を行うことができる。Next, the operation will be described. The driving force of the motor (7) is transmitted to the main shaft (6), the rotation of the main shaft (6) causes the slider (8) to rotate while maintaining a constant eccentricity r, and the slider (8) and the main shaft (6). The movable scroll is movable along the contact surface, and the orbiting scroll (2) repeats the orbiting motion while maintaining a constant eccentric amount by the rotation of the slider (8), thereby the fixed scroll (1) and the orbiting scroll (2).
The volume of the compression chamber (1a) surrounded by and is reduced and compression is performed, but in FIG. 6, the centrifugal force Fc between the orbiting scroll (2) and the slider (8) and the gas load generated by the compression The force Fg acts and the resultant force F presses against the orbiting scroll (2) and the fixed scroll (1), and the contact (13) between the orbiting scroll (2) and the fixed scroll (1) has no gap and no leakage. Less compression can be done.
次いで、スライダー（８）及びスラスト面（３）の潤
滑油の油流路について説明する。スライダー（８）は主
軸（６）と揺動スクロール（２）とで囲まれた容積内に
収められ、この容積内での軸方向への移動が容易である
為にスライダー（８）近傍の油流路は非常に不安定な状
態になっており、またスライダー（８）は径方向に移動
可能であるので第３の油流路（11）は一般に十分に通路
抵抗が小さくなっており、通常主軸（６）の軸方向に貫
通する第１の油流路（９）に入った油の大部分は第３の
油流路（11）に進入し、次いで第４の油流路（12）を通
りスラスト面（３）を潤滑し、第３の油流路（11）に対
して通路抵抗の高い第２の油流路（10）に一部の油が入
り、第４の油流路（12）を通りスラスト面（３）を潤滑
する。Next, the oil passage of the lubricating oil of the slider (8) and the thrust surface (3) will be described. The slider (8) is housed in a volume surrounded by the main shaft (6) and the orbiting scroll (2), and the oil in the vicinity of the slider (8) can be easily moved in this volume in the axial direction. Since the flow passage is in an extremely unstable state and the slider (8) is movable in the radial direction, the third oil flow passage (11) generally has a sufficiently small passage resistance, Most of the oil that has entered the first oil passage (9) penetrating in the axial direction of the main shaft (6) enters the third oil passage (11), and then the fourth oil passage (12). To lubricate the thrust surface (3), part of the oil enters the second oil passage (10) having a high passage resistance with respect to the third oil passage (11), and the fourth oil passage Lubricate the thrust surface (3) through (12).
従来のスクロール圧縮機は以上のように構成されてい
るので、スライダー（８）と揺動軸（４）との軸受摺動
隙間である第２の油流路（10）への油流量が著しく少な
く、揺動軸（４）の焼付，摩耗等による軸受の作動不良
を起しやすく、圧縮機の信頼性を低下させるとともに、
揺動軸（４）の油流量不足により軸受のメカロスによる
入力が増加し、圧縮機の性能を低下させるなどの問題点
があった。Since the conventional scroll compressor is configured as described above, the oil flow rate to the second oil flow path (10), which is the bearing sliding gap between the slider (8) and the swing shaft (4), is extremely large. It is less likely to cause malfunction of the bearing due to seizure or wear of the rocking shaft (4), reducing the reliability of the compressor, and
Due to insufficient oil flow rate of the oscillating shaft (4), the mechanical loss of the bearing increases the input, and the performance of the compressor deteriorates.
この発明は上記のような問題点を解消するためになさ
れたもので、スライダーが揺動軸受内において主軸の軸
線方向に移動可能であってもスライダーと揺動軸との隙
間への油流量を確実かつ十分に得ることのできるスクロ
ール圧縮機を得ることを目的とする。The present invention has been made to solve the above problems, and even if the slider is movable in the swing bearing in the axial direction of the main shaft, the oil flow rate to the gap between the slider and the swing shaft is reduced. An object is to obtain a scroll compressor that can be obtained reliably and sufficiently.
この発明に係わるスクロール圧縮機は、揺動軸受に主
軸の軸線方向に移動自在および周方向に回転自在に収め
られ、かつ前記主軸の軸線と直角な面内においてスライ
ド可能であって固定スクロール中心に対して揺動スクロ
ール中心が偏心量可変となるように主軸端のガイドピン
に係合したスライダーを備えたスクロール圧縮機におい
て、 前記主軸にその軸線方向に貫通するように設けられた
第１の油流路と、前記揺動軸受とスライダーとの間に主
軸の軸線方向に設けられた第２の油流路とを備え、前記
スライダーの揺動スクロール側端面が段付形状部となり
その中央部に中凹部が形成され、該中凹部の深さは前記
スライダーの軸線方向移動可能量より大きく、該中凹部
と前記第２の油流路が連通すべく、前記段付形状部に切
り欠き部が形成されたものである。A scroll compressor according to the present invention is housed in a rocking bearing so as to be movable in the axial direction of the main shaft and rotatable in the circumferential direction, and is slidable in a plane perpendicular to the axis of the main shaft. On the other hand, in a scroll compressor including a slider engaged with a guide pin at the end of a main shaft so that the oscillating scroll center has a variable eccentric amount, a first oil provided so as to penetrate the main shaft in its axial direction. A flow path and a second oil flow path provided in the axial direction of the main shaft between the rocking bearing and the slider are provided, and the end surface of the slider on the rocking scroll side becomes a stepped shape portion at the center thereof. An inner concave portion is formed, and the depth of the inner concave portion is larger than the axially movable amount of the slider, and a cutout portion is formed in the stepped shape portion so that the inner concave portion and the second oil flow path communicate with each other. Formed It was a thing.
この発明においては、第１の油流路に入った油の大部
分が第２の油流路を通ることにより、スライダーが揺動
スクロールと接する位置にある場合でもスライダーの回
転に伴い揺動軸受とスライダーとの間に十分な潤滑油が
入り込み、揺動軸受の作動不良を防ぎ、圧縮機の性能を
確保することができる。In the present invention, most of the oil that has entered the first oil flow path passes through the second oil flow path, so that the rocking bearing is associated with the rotation of the slider even when the slider is in a position in contact with the rocking scroll. Sufficient lubricating oil enters between the slider and the slider to prevent malfunction of the rocking bearing and ensure the performance of the compressor.
以下、この発明の一実施例を第１図〜第４図について
説明する。An embodiment of the present invention will be described below with reference to FIGS.
第１図は軸方向断面図で、第２図は第１図の要部断面
図であり、前記従来のものと同一または相当部分には同
一符号を付して説明を省略する。第１図および第２図に
おいて、（14）はスラスト面（３）の中心部に設けられ
た揺動軸受、（8A）は揺動軸受（14）に軸方向移動自在
および回転自在に収められかつ主軸（６）の軸線と直角
な面内においてスライド可能であるスライダー、（10
A）は揺動軸受（14）とスライダー（8A）との間に軸方
向に設けた第２の油流路、（11A）はスライダー（8A）
が径方向に移動可能である為の空間であるところの第３
の油流路、（12A）はスライダー（8A）の揺動スクロー
ル側端面と揺動スクロール（２）との隙間であるところ
の第４の油流路、（15）はスライダー（8A）とフレーム
（５）との隙間であるところの第５の油流路である。FIG. 1 is a sectional view in the axial direction, and FIG. 2 is a sectional view of an essential part of FIG. In FIGS. 1 and 2, (14) is a rocking bearing provided at the center of the thrust surface (3), and (8A) is housed in the rocking bearing (14) so as to be axially movable and rotatable. And a slider that can slide in a plane perpendicular to the axis of the main shaft (6), (10
(A) is a second oil passage axially provided between the rocking bearing (14) and the slider (8A), and (11A) is a slider (8A).
Is a space for being movable in the radial direction.
Oil passage, (12A) is a fourth oil passage that is a gap between the orbiting scroll side end surface of the slider (8A) and the orbiting scroll (2), and (15) is the slider (8A) and the frame. It is a fifth oil flow path which is a gap with (5).
第３図および第４図は第１図のスライダー（8A）部の
詳細図である。第３図に示すようにスライダー（8A）は
円筒形状をしており、その円筒側面に軸方向に沿って一
部平坦面が形成され、揺動軸受（14）の内面とともに第
２の油流路（10A）が画成される。また、中央部に主軸
（６）のガイドピン（17）に嵌合してスライダー（8A）
を軸線と直角な面内にあってスライド可能なようにガイ
ドスリット（18）が貫通している。このガイドスリット
（18）は前述のようにガイドピン（17）に対してスライ
ダー（8A）がスライド可能なように第３の油流路（11
A）が軸方向にわたって設けられている。更に、スライ
ダー（8A）の反揺動スクロール側端面（19）は平坦であ
り、揺動スクロール側端面（20）は深さδ２の中凹部
（21）が形成されるよう段付形状部（22）となってい
る。そして、中凹部（21）と第２の油流路（10A）とは
互いに連通するべく切り欠き部（23）が設けられてい
る。3 and 4 are detailed views of the slider (8A) portion of FIG. As shown in FIG. 3, the slider (8A) has a cylindrical shape, and a flat surface is partially formed along the axial direction on the side surface of the cylinder. The slider (8A) and the inner surface of the rocking bearing (14) form a second oil flow. Road (10A) is defined. Further, the slider (8A) is fitted to the guide pin (17) of the main shaft (6) at the center part.
A guide slit (18) is provided so as to be slidable in a plane perpendicular to the axis. The guide slit (18) is provided with the third oil passage (11) so that the slider (8A) can slide with respect to the guide pin (17) as described above.
A) is provided in the axial direction. Further, the end face (19) of the slider (8A) on the side opposite to the orbiting scroll is flat, and the end face (20) on the side of the orbiting scroll is stepped so that a middle recess (21) of depth δ 2 is formed. 22). A notch (23) is provided so that the middle recess (21) and the second oil passage (10A) communicate with each other.
このようにしてスライダー（8A）が揺動軸受（14）内
にあって軸方向に移動したとしても段付形状部（22）に
よって規則され、その結果反揺動スクロール側端面（1
9）に発生する隙間δ１に比べδ２≫δ１と形成するこ
とにより、第４と第２の油流路（12A），（10A）の通路
抵抗の和は第３と第５の油流路（11A），（15）の通路
抵抗の和に比べて十分に小さくでき、第１の油流路
（９）を流出した油は第4,第２の油流路（12A），（10
A）を大半が通過して流すことができる。In this way, even if the slider (8A) moves axially in the orbiting bearing (14), it is regulated by the stepped shape portion (22), and as a result, the end face (1
By forming the δ 2 »δ 1 compared with the gap [delta] 1 occurring 9), the fourth and the second oil passage (12A), (10A) is the sum of the passage resistance third and fifth oil The oil can be made sufficiently smaller than the sum of the passage resistances of the flow paths (11A) and (15), and the oil flowing out of the first oil flow path (9) can be supplied to the fourth, second oil flow paths (12A), ( Ten
Most of A) can be flowed through.
このようにして主軸（６）の軸方向に貫通する第１の
油流路（９）の入った油が、スラスト面（３）に導かれ
る流路には２通りあり、一方は第２図の実線の矢印で示
すように第４の油流路（12A）を通り第２の油流路（10
A）に至りスラスト面（３）に導かれる流路であり、他
方は第３の油流路（11A）から第５の油流路（15）を通
りスラスト面（３）に導かれるものであるが、スライダ
ー（8A）が揺動軸受（14）内にあって軸方向に移動した
場合でも、第３図における段付形状部（22）によってス
ライダー（8A）の軸方向への移動は規制されるので、中
凹部（21）の深さδ２は反揺動スクロール側端面（19）
に発生する隙間δ１に比べδ２≫δ１と形成されている
ので、第４と第２の油流路（12A），（10A）の通路抵抗
の和は第３と第５の油流路（11A），（15）の通路抵抗
の和に比べて十分に小さくなり、第１の油流路（９）を
流出した油の大部分が第4,第２の油流路（12A），（10
A）を流れ、揺動軸受（14）とスライダー（8A）を十分
に潤滑し、スラスト面（３）に導かれてスラスト面
（３）の潤滑を行なう。In this way, there are two kinds of oil in the first oil flow path (9) that penetrates the main shaft (6) in the axial direction, and the oil is introduced into the thrust surface (3). As indicated by the solid line arrow, the second oil flow path (10A) passes through the fourth oil flow path (12A).
A) is a flow path leading to the thrust surface (3), and the other is a flow path from the third oil flow path (11A) to the thrust surface (3) through the fifth oil flow path (15). However, even if the slider (8A) moves in the rocking bearing (14) and moves in the axial direction, the stepped shape portion (22) in FIG. 3 restricts the movement of the slider (8A) in the axial direction. Therefore, the depth δ 2 of the inner concave portion (21) is equal to that of the end face (19) on the side of the non-oscillating scroll.
Because it is formed and δ 2 »δ 1 compared with the gap [delta] 1 generated in the fourth and second oil passages (12A), the passage sum of the resistances and the third and fifth oil flow in (10A) It is sufficiently smaller than the sum of the passage resistances of the passages (11A) and (15), and most of the oil flowing out of the first oil passage (9) is the fourth and second oil passages (12A). ,(Ten
A) to sufficiently lubricate the rocking bearing (14) and the slider (8A), and guide the thrust surface (3) to lubricate the thrust surface (3).
以上のようにこの発明によれば、スライダーが主軸の
軸線方向に移動可能で、スライダーの揺動スクロール側
端面が揺動スクロール底部に接触した場合でも、第１の
油流路から中凹部と切り欠き部で形成される油流路を通
って確実にかつ十分にスライダーの揺動軸受との隙間へ
の油流量を得ることができ、揺動軸受の焼付、摩耗等の
作動不良が起こりにくく、圧縮機の信頼性を向上させる
ことができるとともに、揺動軸受の温度上昇を低く押さ
えて軸受のメカロスによる入力の増加を低く押さえる
等、圧縮機の性能を向上させるという効果が得られる。As described above, according to the present invention, the slider is movable in the axial direction of the main shaft, and even when the end surface of the slider on the oscillating scroll side comes into contact with the oscillating scroll bottom portion, the first oil flow path cuts into the middle concave portion. It is possible to reliably and sufficiently obtain the oil flow rate to the gap between the slider and the swing bearing through the oil flow path formed by the cutout portion, and it is difficult for malfunctions such as seizure and wear of the swing bearing to occur. The reliability of the compressor can be improved, and the effect of improving the performance of the compressor can be obtained, such as suppressing the temperature rise of the rocking bearing to be small and suppressing the increase in input due to mechanical loss of the bearing.
第１図はこの発明の一実施例によるスクロール圧縮機の
軸方向断面図、第２図は第１図の要部断面図、第３図は
スライダー（8A）の立体図、第４図はスライダー（8A）
の正面図、第５図は従来のスクロール圧縮機の要部軸方
向断面図、第６図は第５図の要部横断面図である。 図において、（１）は固定スクロール、（２）は揺動ス
クロール、（３）はスラスト面、（５）はフレーム、
（６）は主軸、（７）はモータ、（8A）はスライダー、
（９）は第１の油流路、（10A）は第２の油流路、（11
A）は第３の油流路、（12A）は第４の油流路、（14）は
揺動軸受、（15）は第５の油流路、（16）は揺動軸受底
部、（17）はガイドピン、（18）はガイドスリット、
（19）は反揺動軸受端面、（20）は揺動軸受端面、（2
1）は中凹部、（22）は段付形状部、（23）は切欠部を
示す。 なお、図中同一符号は同一または相当部分を示す。FIG. 1 is an axial sectional view of a scroll compressor according to an embodiment of the present invention, FIG. 2 is a sectional view of an essential part of FIG. 1, FIG. 3 is a three-dimensional view of a slider (8A), and FIG. 4 is a slider. (8A)
FIG. 5 is an axial sectional view of a main part of a conventional scroll compressor, and FIG. 6 is a horizontal sectional view of the main part of FIG. In the figure, (1) is a fixed scroll, (2) is an orbiting scroll, (3) is a thrust surface, (5) is a frame,
(6) is the spindle, (7) is the motor, (8A) is the slider,
(9) is the first oil flow path, (10A) is the second oil flow path, (11
(A) is the third oil flow path, (12A) is the fourth oil flow path, (14) is the rocking bearing, (15) is the fifth oil flow path, (16) is the rocking bearing bottom, 17) is a guide pin, (18) is a guide slit,
(19) is the end face of anti-oscillating bearing, (20) is the end face of the oscillating bearing, (2)
1) shows a middle concave portion, (22) shows a stepped shape portion, and (23) shows a cutout portion. In the drawings, the same reference numerals indicate the same or corresponding parts.
───────────────────────────────────────────────────── フロントページの続き (72)発明者 中村 利之 静岡県静岡市小鹿３丁目18番１号 三菱 電機株式会社静岡製作所内 (56)参考文献 特開 昭59−120794（ＪＰ，Ａ) 特開 昭62−182484（ＪＰ，Ａ) ─────────────────────────────────────────────────── ─── Continuation of front page (72) Inventor Toshiyuki Nakamura 3-18-1, Oga, Shizuoka-shi, Shizuoka Mitsubishi Electric Corporation Shizuoka Works (56) Reference JP-A-59-120794 (JP, A) JP Sho 62-182484 (JP, A)
Claims (1)
の組合わせにより圧縮室を形成する揺動スクロールと、
この揺動スクロールの圧縮室と反対側のスラスト面中心
部に設けられた揺動軸受と、前記揺動スクロールのスラ
スト面を支承するフレームと、このフレームに支承され
かつ前記揺動スクロールに駆動力を伝達する主軸と、こ
の主軸を駆動するモータと、前記揺動軸受に前記主軸の
軸線方向に移動自在および周方向に回転自在に収めら
れ、かつ前記主軸の軸線と直角な面内においてスラスト
可能であって固定スクロール中心に対して揺動スクロー
ル中心が偏心量可変となるように主軸端のガイドピンに
係合したスライダーとを備えたスクロール圧縮機におい
て、 前記主軸にその軸線方向に貫通するように設けられた第
１の油流路と、前記揺動軸受とスライダーとの間に主軸
の軸線方向に設けられた第２の油流路とを備え、前記ス
ライダーの揺動スクロール側端面が段付形状部となりそ
の中央部に中凹部が形成され、該中凹部の深さは前記ス
ライダーの軸線方向移動可能量より大きく、該中凹部と
前記第２の油流路が連通すべく、前記段付形状部に切り
欠き部が形成されたことを特徴とするスクロール圧縮
機。1. A fixed scroll, and an orbiting scroll which forms a compression chamber by a combination of the fixed scroll and the fixed scroll.
A rocking bearing provided in the center of the thrust surface of the orbiting scroll opposite to the compression chamber, a frame for supporting the thrust surface of the orbiting scroll, and a driving force for the orbiting scroll which is supported by the frame. And a motor for driving the main shaft, and the oscillating bearing is housed in the oscillating bearing so as to be movable in the axial direction of the main shaft and rotatable in the circumferential direction, and thrustable in a plane perpendicular to the axial line of the main shaft. And a scroll compressor provided with a slider engaged with a guide pin at the end of the main spindle so that the oscillating scroll center can change the eccentricity amount with respect to the fixed scroll center, so as to penetrate the main shaft in the axial direction thereof. And a second oil flow passage provided in the axial direction of the main shaft between the rocking bearing and the slider, The scroll-side end surface serves as a stepped portion, and a central concave portion is formed in the central portion thereof. The depth of the central concave portion is larger than the axially movable amount of the slider, and the central concave portion and the second oil flow passage are connected. A scroll compressor, wherein a cutout portion is formed in the stepped portion so as to pass therethrough.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1316028A JP2689659B2 (en) | 1989-12-04 | 1989-12-04 | Scroll compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1316028A JP2689659B2 (en) | 1989-12-04 | 1989-12-04 | Scroll compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH03175188A JPH03175188A (en) | 1991-07-30 |
| JP2689659B2 true JP2689659B2 (en) | 1997-12-10 |
Family
ID=18072448
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1316028A Expired - Lifetime JP2689659B2 (en) | 1989-12-04 | 1989-12-04 | Scroll compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2689659B2 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2915852B2 (en) | 1996-09-06 | 1999-07-05 | 三菱重工業株式会社 | Scroll compressor |
| US6471499B1 (en) * | 2001-09-06 | 2002-10-29 | Scroll Technologies | Scroll compressor with lubrication directed to drive flat surfaces |
| EP1978257A1 (en) * | 2007-04-04 | 2008-10-08 | Scroll Technologies | Scroll compressor with slider block having upper surface over enlarged area |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0678756B2 (en) * | 1986-02-03 | 1994-10-05 | 松下冷機株式会社 | Scroll compressor |
-
1989
- 1989-12-04 JP JP1316028A patent/JP2689659B2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPH03175188A (en) | 1991-07-30 |
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