JPH07293473A - High pressure dome-type compressor - Google Patents
High pressure dome-type compressorInfo
- Publication number
- JPH07293473A JPH07293473A JP6088141A JP8814194A JPH07293473A JP H07293473 A JPH07293473 A JP H07293473A JP 6088141 A JP6088141 A JP 6088141A JP 8814194 A JP8814194 A JP 8814194A JP H07293473 A JPH07293473 A JP H07293473A
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- pump
- pressure side
- high pressure
- bearing housing
- 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.)
- Withdrawn
Links
- 230000006835 compression Effects 0.000 claims abstract description 20
- 238000007906 compression Methods 0.000 claims abstract description 20
- 230000002093 peripheral effect Effects 0.000 claims description 15
- 230000001603 reducing effect Effects 0.000 claims description 7
- 238000000638 solvent extraction Methods 0.000 claims 1
- 238000005461 lubrication Methods 0.000 abstract description 14
- 230000003247 decreasing effect Effects 0.000 abstract 1
- 238000005086 pumping Methods 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 239000000945 filler Substances 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000003466 welding 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
- 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
- F04C18/023—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 both members are moving
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Rotary Pumps (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は高圧ドーム形圧縮機、特
に、高圧ドーム形のスクロール圧縮機に関するものであ
る。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a high pressure dome type compressor, and more particularly to a high pressure dome type scroll compressor.
【０００２】[0002]
【従来の技術】従来、高圧ドーム形圧縮機、特に高圧ド
ーム形のスクロール圧縮機は、モータに連結する駆動軸
で駆動される圧縮要素を備え、密閉ケーシング内に高圧
ガスを吐出する一方、前記圧縮要素の低圧側を軸受ハウ
ジングにより前記密閉ケーシングの高圧内部と区画する
ようにしている。さらに、前記軸受ハウジングに、前記
圧縮要素の低圧側と、前記密閉ケーシングの高圧内部と
に臨む軸受を介して前記駆動軸を支持させると共に、前
記軸受の低圧側と高圧側との途中に給油口を開口させ
て、前記密閉ケーシング底部の油溜から前記軸受及び圧
縮要素の摺動部に差圧給油するようにしている。2. Description of the Related Art Conventionally, a high-pressure dome type compressor, in particular, a high-pressure dome type scroll compressor has a compression element driven by a drive shaft connected to a motor, and discharges high pressure gas into a hermetically sealed casing. The low pressure side of the compression element is partitioned by the bearing housing from the high pressure interior of the closed casing. Further, the bearing housing is made to support the drive shaft through a bearing facing the low pressure side of the compression element and the high pressure inside of the hermetic casing, and a fuel filler port is provided midway between the low pressure side and the high pressure side of the bearing. Is opened to allow differential pressure oil supply from the oil reservoir at the bottom of the closed casing to the sliding portions of the bearing and the compression element.
【０００３】しかしながら、前記軸受への給油を差圧給
油により行っていたため、該軸受の前記給油口の開口部
から低圧側への給油は充分に行えたが、高圧側への給油
は、差圧が生じないことや、前記ケーシング内の高圧ガ
ス流体の前記軸受への流入などが原因で給油が充分行え
ず潤滑不良が生じ、特に、該軸受の高圧側端部において
は、前記駆動軸による片当たりが生じ易く、焼き付けが
生じていた。However, since the bearing is lubricated by differential pressure lubrication, the low pressure side can be sufficiently lubricated from the opening of the lubrication port of the bearing, but the high pressure side is lubricated by differential pressure lubrication. Does not occur, or due to the inflow of high-pressure gas fluid in the casing into the bearing, insufficient lubrication occurs, resulting in poor lubrication. The hit was easy to occur, and the baking occurred.
【０００４】そこで、従来では、例えば、特開昭６４−
８７８９４号公報に記載されているように、前記軸受の
前記給油口の開口部から高圧側にかけて、前記軸受の内
周面か、又は、前記駆動軸に螺旋状の給油溝を形成する
ことにより粘性ポンプ作用を生じさせるようにしてい
た。Therefore, in the past, for example, Japanese Patent Laid-Open No. 64-64-
As described in Japanese Patent No. 87894, a viscosity is increased by forming a spiral oil supply groove on the inner peripheral surface of the bearing or on the drive shaft from the opening of the oil supply port of the bearing to the high pressure side. It was designed to create a pumping action.
【０００５】即ち、前記公報に記載のスクロール圧縮機
は、図７に示すように、横形密閉ケーシングＡ内の長手
方向一側に、圧縮要素Ｂと軸受ハウジングＣとを内装し
て、前記圧縮要素Ｂの固定スクロールＤと前記軸受ハウ
ジングＣとにより、前記固定スクロールＤの吐出口Ｊが
開口し、高圧ドームとなる前記ケーシングＡの内部空間
から区画する低圧空間Ｅを形成して、この低圧空間Ｅに
吸入管Ｈを開口させると共に、前記低圧空間Ｅに可動ス
クロールＦを内装して、この可動スクロールＦを前記ケ
ーシングＡの他側に設けるモータＭの駆動軸Ｇに連結
し、この駆動軸Ｇを、一端が前記低圧空間Ｅに連通し、
他端がケーシングＡの内部空間に連通する筒状の軸受Ｋ
を介して前記軸受ハウジングＣに軸受支持している。That is, in the scroll compressor described in the above publication, as shown in FIG. 7, a compression element B and a bearing housing C are internally provided on one side in the longitudinal direction inside a horizontal hermetic casing A, and the compression element is By the fixed scroll D of B and the bearing housing C, the discharge port J of the fixed scroll D is opened to form a low pressure space E which is partitioned from the internal space of the casing A which is a high pressure dome. The suction pipe H is opened at the same time, a movable scroll F is installed in the low pressure space E, and the movable scroll F is connected to a drive shaft G of a motor M provided on the other side of the casing A. , One end communicates with the low pressure space E,
Cylindrical bearing K whose other end communicates with the internal space of casing A
The bearing is supported by the bearing housing C via.
【０００６】そして、以上の構成において、前記軸受Ｋ
の軸方向中間部に給油口Ｌを形成し、該給油口Ｌに、一
端が前記軸受Ｋの内周側に開口し、他端が前記ケーシン
グＡ底部の油溜Ｏに開口する給油管Ｎを接続すると共
に、前記軸受Ｋの内周面で、前記給油口Ｌから高圧側に
かけて螺旋溝Ｑを形成し、この螺旋溝Ｑによる粘性ポン
プ作用により、前記給油口Ｌに差圧給油される油を前記
軸受Ｋの高圧側端部にも強制給油できるようにして、前
記軸受Ｋの高圧側軸受端部における潤滑不良を防止する
ようにしたものである。尚、図７においてＰは、前記給
油口Ｌから可動スクロールＦの背面側とを連通する給油
通路である。In the above structure, the bearing K
Is formed at an axially intermediate portion of the oil supply port L, and an oil supply pipe N having one end opened to the inner peripheral side of the bearing K and the other end opened to an oil sump O at the bottom of the casing A is formed at the oil supply port L. The spiral groove Q is formed on the inner peripheral surface of the bearing K from the oil supply port L to the high pressure side while being connected, and the oil supplied to the oil supply port L under differential pressure is supplied by the viscous pumping action of the spiral groove Q. The high pressure side end portion of the bearing K can be forcibly supplied with oil to prevent poor lubrication at the high pressure side bearing end portion of the bearing K. In FIG. 7, P is an oil supply passage that connects the oil supply port L to the back side of the movable scroll F.
【０００７】[0007]
【発明が解決しようとする課題】ところが、以上の圧縮
機では、前記螺旋溝Ｑによる粘性ポンプ作用で前記軸受
Ｋにおける前記給油口Ｌに対し高圧側にも給油すること
はできるが、前記ケーシングＡ内の高圧に打ち勝って、
この粘性ポンプによる油の汲上げ量を充分確保する必要
があるから、前記螺旋溝Ｑのリード角を大きくし、か
つ、巻き数を多くする必要があり、このため、前記軸受
Ｋの軸受長さが長くなり、前記ケーシングＡ全体が大き
くなる問題があるし、また、前記軸受Ｋの内周面に前記
螺旋溝Ｑを形成するから、その形成が困難となる問題が
ある。However, in the above compressor, although it is possible to supply oil to the high pressure side with respect to the oil supply port L in the bearing K by viscous pump action by the spiral groove Q, the casing A Overcoming the high pressure inside,
Since it is necessary to secure a sufficient amount of oil to be pumped by the viscous pump, it is necessary to increase the lead angle of the spiral groove Q and increase the number of turns. Therefore, the bearing length of the bearing K is increased. Is long and the entire casing A is large, and since the spiral groove Q is formed on the inner peripheral surface of the bearing K, it is difficult to form the spiral groove Q.
【０００８】本発明の目的は、簡単な構成で作業も簡単
に行え、また、前記軸受における高圧側端部の潤滑を良
好に行える高圧ドーム形圧縮機を提供することにある。An object of the present invention is to provide a high-pressure dome type compressor which has a simple structure and can be easily operated, and which can favorably lubricate the high pressure side end portion of the bearing.
【０００９】[0009]
【課題を解決するための手段】上記目的を達成するた
め、請求項１記載の発明は、駆動軸６で駆動され、密閉
ケーシング１内に高圧ガスを吐出する圧縮要素３を備
え、この圧縮要素３の低圧側と、前記密閉ケーシング１
の高圧内部とを区画する軸受ハウジング７に、前記圧縮
要素３の低圧側と、密閉ケーシング１の高圧内部とに臨
む軸受７０を介して前記駆動軸６を支持すると共に、前
記軸受７０の低圧側と高圧側との途中に給油口７２を開
口させた高圧ドーム形圧縮機において、前記軸受７０に
おける高圧側端部の外側近くに、前記駆動軸６の回転に
伴い駆動回転し、前記高圧側端部の圧力を減圧させるポ
ンプ板９を設けたのである。To achieve the above object, the invention according to claim 1 is provided with a compression element 3 which is driven by a drive shaft 6 and discharges high-pressure gas into a closed casing 1. 3, the low pressure side and the closed casing 1
The bearing housing 7 that divides the high pressure inside of the bearing 70 supports the drive shaft 6 through a bearing 70 facing the low pressure side of the compression element 3 and the high pressure inside of the closed casing 1, and the low pressure side of the bearing 70. In the high-pressure dome compressor in which the oil supply port 72 is opened in the middle of the high-pressure side and the high-pressure side, the bearing 70 is driven to rotate near the outside of the high-pressure side end with the rotation of the drive shaft 6, and the high-pressure side end. The pump plate 9 for reducing the pressure of the part is provided.
【００１０】請求項２記載の発明は、前記ポンプ板９を
前記軸受ハウジング７の高圧側側面に近接させて前記駆
動軸６に取付けたのである。According to the second aspect of the present invention, the pump plate 9 is attached to the drive shaft 6 in close proximity to the high pressure side surface of the bearing housing 7.
【００１１】請求項３の発明は、前記密閉ケーシング１
に、前記軸受ハウジング７の高圧側側面に近接して、前
記駆動軸６を連結するモータ２を内装し、このモータ２
のロータ２１における軸受ハウジング側端部に、前記ポ
ンプ板９を取付けたのである。The invention of claim 3 relates to the closed casing 1
A motor 2 which connects the drive shaft 6 to the side of the bearing housing 7 on the high pressure side.
The pump plate 9 is attached to the end of the rotor 21 on the bearing housing side.
【００１２】請求項４記載の発明は、前記ポンプ板９の
前記軸受ハウジング７に対向するポンプ面９２に、径方
向中心側から外周方向に放射状に延びる複数のポンプ羽
根９１を設けたのである。According to a fourth aspect of the present invention, the pump surface 92 of the pump plate 9 facing the bearing housing 7 is provided with a plurality of pump blades 91 extending radially from the center side in the radial direction to the outer peripheral direction.
【００１３】請求項５記載の発明は、前記ポンプ板９の
前記軸受ハウジング７に対向するポンプ面９２に、径方
向中心側から外周方向に放射状に延びる複数のポンプ溝
９４を設けたのである。According to the fifth aspect of the present invention, the pump surface 92 of the pump plate 9 facing the bearing housing 7 is provided with a plurality of pump grooves 94 extending radially from the center side in the radial direction to the outer peripheral direction.
【００１４】[0014]
【作用】請求項１記載の発明では、前記軸受７０におけ
る高圧側端部の外側近くに、前記駆動軸６の回転に伴い
駆動回転し、前記高圧側端部の圧力を減圧させるポンプ
板９を設けたから、このポンプ板９の回転による前記高
圧側端部の減圧により、差圧給油で前記高圧側端部にま
で有効に給油できるのである。即ち、前記ポンプ板９を
前記高圧側端部近くに設けたから、このポンプ板９の回
転で、前記ポンプ面９２と前記軸受ハウジング７の高圧
側側面との間に形成される微小隙間のガス又は油を含む
ガスが、前記ポンプ面９２の回転による遠心力作用によ
り、ガスまたは油の粘性抵抗で該ポンプ面９２に沿って
径方向外方に向けて吐き出されることになり、この結
果、前記微小隙間が負圧状態となって、前記軸受７０の
高圧側軸受端部の圧力が減圧されるのであって、この減
圧で前記給油口７２に溜る油を差圧により前記軸受７０
の高圧側軸受端部にまで給油することができる。According to the first aspect of the invention, a pump plate 9 is provided near the outside of the high pressure side end portion of the bearing 70, which is driven and rotated by the rotation of the drive shaft 6 to reduce the pressure of the high pressure side end portion. Since the pump plate 9 is provided, the high pressure side end portion is depressurized by the rotation of the pump plate 9, so that the high pressure side end portion can be effectively lubricated by differential pressure lubrication. That is, since the pump plate 9 is provided near the high pressure side end portion, the rotation of the pump plate 9 causes gas in a minute gap formed between the pump surface 92 and the high pressure side surface of the bearing housing 7 or The gas containing oil is expelled radially outward along the pump surface 92 due to the viscous resistance of the gas or oil due to the centrifugal force action due to the rotation of the pump surface 92. The pressure in the high pressure side bearing end portion of the bearing 70 is reduced due to the negative pressure in the gap, and the oil accumulated in the oil supply port 72 is reduced in pressure by the pressure reduction.
It is possible to supply oil to the high pressure side end of the bearing.
【００１５】従って、前記軸受ハウジング７における前
記軸受７０の高圧側端部の外側近くに前記ポンプ板９を
設けるだけの簡単な構成で、該ポンプ板９の回転による
減圧作用で、前記高圧側軸受端部の潤滑を充分行えるの
で、従来のように、前記軸受７０の軸受長さが長くなる
ことはないし、前記ケーシング１が大型化するようなこ
ともなく、前記高圧側軸受端部への給油を可能として、
その焼付けを防止できるし、この軸受端部からの高圧ガ
スの流入による軸受全体の潤滑不良も防止できるのであ
る。Therefore, with the simple construction in which the pump plate 9 is provided near the outside of the high pressure side end of the bearing 70 in the bearing housing 7, the high pressure side bearing can be operated by the pressure reducing action by the rotation of the pump plate 9. Since the end portion can be sufficiently lubricated, the bearing length of the bearing 70 does not become long and the casing 1 does not increase in size as in the conventional case, and oil is supplied to the end portion of the high pressure side bearing. As possible
The seizure can be prevented, and the poor lubrication of the entire bearing due to the inflow of high-pressure gas from the end of the bearing can be prevented.
【００１６】また、請求項２記載の発明では、前記ポン
プ板９を前記軸受ハウジング７の高圧側側面に近接させ
て前記駆動軸６に取付けたから、前記ポンプ板９の構成
を簡単にできるし、また、その取付けも簡単に行えるの
である。According to the second aspect of the invention, since the pump plate 9 is attached to the drive shaft 6 so as to be close to the high pressure side surface of the bearing housing 7, the structure of the pump plate 9 can be simplified. In addition, it can be easily attached.
【００１７】請求項３の発明は、前記密閉ケーシング１
に、前記軸受ハウジング７の高圧側側面に近接して、前
記駆動軸６を連結するモータ２を内装し、このモータ２
のロータ２１における軸受ハウジング側端部に、前記ポ
ンプ板９を取付けたから、回転部材である前記ロータ２
１を利用して前記ポンプ板９を回転させられ、しかも、
前記モータ２を前記軸受ハウジング７の高圧側側面に近
接させていることも相俟って、前記ケーシング１の小型
化が可能になりながら、前記軸受７０の潤滑を充分行え
るのである。According to a third aspect of the present invention, the closed casing 1 is provided.
A motor 2 which connects the drive shaft 6 to the side of the bearing housing 7 on the high pressure side.
Since the pump plate 9 is attached to the end portion of the rotor 21 on the bearing housing side of the rotor 21,
1 can be used to rotate the pump plate 9, and
Since the motor 2 is located close to the high pressure side surface of the bearing housing 7, the casing 1 can be downsized and the bearing 70 can be sufficiently lubricated.
【００１８】請求項４記載の発明は、前記ポンプ板９の
前記軸受ハウジング７に対向するポンプ面９２に、径方
向中心側から外周方向に放射状に延びる複数のポンプ羽
根９１を設けたから、ガスまたは油の前記ポンプ板９へ
の接触面積を大きくすることができるので、それだけガ
ス又は油の粘性抵抗による吐き出し量を多くでき、前記
ポンプ板９による減圧をより良好に行えるのである。ま
た、前記ポンプ羽根９１を形成することにより、前記ポ
ンプ板９の外径を大きくすることなく前記軸受７０の高
圧側端部の減圧効果が期待できるのである。According to the fourth aspect of the invention, the pump surface 92 of the pump plate 9 facing the bearing housing 7 is provided with a plurality of pump blades 91 radially extending from the radial center side to the outer peripheral direction. Since the contact area of oil with the pump plate 9 can be increased, the amount of discharge due to the viscous resistance of gas or oil can be increased accordingly, and the pressure reduction by the pump plate 9 can be performed better. Further, by forming the pump blades 91, it is possible to expect a pressure reducing effect at the high pressure side end of the bearing 70 without increasing the outer diameter of the pump plate 9.
【００１９】請求項５記載の発明は、前記ポンプ板９の
前記軸受ハウジング７に対向するポンプ面９２に、径方
向中心側から外周方向に放射状に延びる複数のポンプ溝
９４を設けたから、ガスまたは油の前記ポンプ板９への
接触面積を大きくすることができるので、それだけガス
又は油の粘性抵抗による吐き出し量を多くでき、前記ポ
ンプ板９による減圧をより良好に行えるのである。According to the fifth aspect of the present invention, the pump surface 92 of the pump plate 9 facing the bearing housing 7 is provided with a plurality of pump grooves 94 radially extending from the center side in the radial direction to the outer peripheral direction. Since the contact area of oil with the pump plate 9 can be increased, the amount of discharge due to the viscous resistance of gas or oil can be increased accordingly, and the pressure reduction by the pump plate 9 can be performed better.
【００２０】[0020]
【実施例】本発明の第１実施例を図１に基づいて説明す
る。図１に示す第１実施例は、横形の共回りスクロール
圧縮機であって、この圧縮機は、高圧ドームを形成する
横長密閉ケーシング１の内部で長手方向一側に、ロータ
２１とステータ２２とから成るモータ２を配設すると共
に、前記ケーシング１の内方他側に共回り型のスクロー
ル圧縮要素３を配設している。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of the present invention will be described with reference to FIG. The first embodiment shown in FIG. 1 is a horizontal co-rotating scroll compressor. This compressor has a rotor 21 and a stator 22 on one side in the longitudinal direction inside a horizontally long hermetic casing 1 forming a high pressure dome. And a co-rotating scroll compression element 3 on the inner and other sides of the casing 1.
【００２１】この圧縮要素３は、前記モータ２のロータ
２１に結合される駆動軸６の端部に一体に突設した駆動
スクロール４と、従動筒部５１が突設され、前記駆動ス
クロール４の駆動に伴い従動回転しながら旋回運動する
従動スクロール５とから構成され、また、前記駆動スク
ロール４を軸受支持する駆動側軸受ハウジング７と、前
記従動スクロール５を軸受支持する従動側軸受ハウジン
グ８とを対設させて、これら各ハウジング７，８を取付
ボルト１４などで結合することにより、前記ケーシング
１の高圧内部空間と区画された低圧空間１１を形成する
のであって、この低圧空間１１に、前記圧縮要素３の前
記駆動及び従動スクロール４，５を対向状に内装してい
る。前記圧縮要素３は、前記従動スクロール５に、前記
駆動スクロール４の鏡板４２を挟み込むようにスラスト
プレート３１をボルト結合して、前記従動スクロール５
と前記スラストプレート３１により前記駆動スクロール
４を抱き込み状態に保持するようにしている。The compression element 3 is provided with a drive scroll 4 integrally projecting from an end of a drive shaft 6 connected to the rotor 21 of the motor 2 and a driven cylinder 51. The driven scroll 5 includes a driven scroll 5 which is driven to rotate while being driven and rotates, and a driven bearing housing 7 which supports the driven scroll 4 and a driven bearing housing 8 which supports the driven scroll 5. By installing the housings 7 and 8 facing each other and connecting the housings 7 and 8 with a mounting bolt 14 or the like, a low-pressure space 11 that is partitioned from the high-pressure internal space of the casing 1 is formed. The drive and driven scrolls 4 and 5 of the compression element 3 are internally mounted in a facing manner. The compression element 3 is configured such that the thrust plate 31 is bolted to the driven scroll 5 so that the end plate 42 of the drive scroll 4 is sandwiched between the driven scroll 5 and the driven scroll 5.
With the thrust plate 31, the drive scroll 4 is held in the embraced state.
【００２２】また、前記駆動側軸受ハウジング７は、前
記低圧空間１１と、前記密閉ケーシング１の高圧内部と
に臨み、前記駆動軸６を支持する第１軸受７０を備え、
前記ケーシング１内に望む高圧側側面を平坦な面に形成
している。そして、前記従動側軸受ハウジング８は、前
記第１軸受７０で軸受支持される前記駆動軸６の軸心に
対し偏心した位置に突設される軸部８１を設けており、
該軸部８１を第２軸受８０を介して前記従動筒部５１内
に嵌合して、該従動筒部５１を回転自由に軸受支持する
ようにしている。Further, the drive side bearing housing 7 is provided with a first bearing 70 which faces the low pressure space 11 and the high pressure inside of the hermetic casing 1 and supports the drive shaft 6.
The side surface on the high pressure side desired in the casing 1 is formed into a flat surface. The driven-side bearing housing 8 is provided with a shaft portion 81 projecting at a position eccentric to the shaft center of the drive shaft 6 supported by the first bearing 70,
The shaft portion 81 is fitted into the driven cylinder portion 51 via the second bearing 80, and the driven cylinder portion 51 is rotatably supported by the bearing.
【００２３】さらに、前記駆動軸６には、一端側を前記
駆動スクロール４に開設する吐出口４１に連通させ、か
つ、他端側を前記モータ２と前記駆動側軸受ハウジング
７との間に形成される空間に開口させる吐出通路６１を
形成しており、前記従動側軸受ハウジング８には、前記
低圧空間１１に低圧ガスを導入する吸入管１２を接続し
ている。Further, one end of the drive shaft 6 is communicated with a discharge port 41 formed in the drive scroll 4, and the other end is formed between the motor 2 and the drive bearing housing 7. A discharge passage 61 that opens into the space is formed, and a suction pipe 12 that introduces low-pressure gas into the low-pressure space 11 is connected to the driven-side bearing housing 8.
【００２４】従って、以上の構成において、前記モータ
２の駆動に伴い前記駆動軸６を介して駆動スクロール４
が回転駆動されるとき、前記従動スクロール５を駆動ス
クロール４に従動させながら前記従動筒部５１を中心に
旋回運動させ、この旋回運動によって、前記ケーシング
１を貫通して、前記従動側軸受ハウジング８に接続した
前記吸入管１２から低圧ガスが前記低圧空間１１内に導
入され、このガスが前記各スクロール４，５間の圧縮室
内に吸入されて圧縮され、圧縮された高圧のガスを、前
記駆動スクロール４に設けた前記吐出口４１から前記駆
動軸６内の吐出通路６１を経て前記ケーシング１の内部
空間へと吐出するようにしている。Therefore, in the above structure, the drive scroll 4 is driven through the drive shaft 6 as the motor 2 is driven.
When the driven scroll 5 is driven to rotate, the driven scroll 5 is swung about the driven cylinder portion 51 while being driven by the driving scroll 4, and this swiveling motion penetrates the casing 1 to move the driven side bearing housing 8 Low-pressure gas is introduced into the low-pressure space 11 from the suction pipe 12 connected to, and this gas is sucked into the compression chamber between the scrolls 4 and 5 and compressed, and the compressed high-pressure gas is driven by the drive. It discharges from the discharge port 41 provided in the scroll 4 to the internal space of the casing 1 through the discharge passage 61 in the drive shaft 6.
【００２５】また、前記駆動側軸受ハウジング７には、
一端がケーシング１底部に形成される油溜１３に連通
し、他端が前記第１軸受７０の内周面で、該第１軸受７
０の低圧側と高圧側との途中に開口する給油口７２に連
通する給油通路７１を形成して、前記ケーシング１内の
高圧空間と前記低圧空間１１との差圧で前記油溜１３の
油を前記第１軸受７０に給油するようにしている。Further, the drive side bearing housing 7 includes
One end communicates with the oil reservoir 13 formed at the bottom of the casing 1, and the other end is the inner peripheral surface of the first bearing 70.
The oil supply passage 71 communicating with the oil supply port 72 opened in the middle of the low pressure side and the high pressure side of 0 is formed, and the oil in the oil sump 13 is divided by the differential pressure between the high pressure space in the casing 1 and the low pressure space 11. Is supplied to the first bearing 70.
【００２６】しかして、第１実施例では、前記第１軸受
７０における高圧側端部の外側近くに、前記駆動軸６の
回転に伴い駆動回転し、前記高圧側端部の圧力を減圧さ
せるポンプ板９を設けるのであり、該ポンプ板９を前記
駆動側軸受ハウジング７の高圧側側面に近接させて前記
駆動軸６に取付けるのである。In the first embodiment, however, a pump for rotating the drive shaft 6 near the outside of the high pressure side end of the first bearing 70 to rotate the drive shaft 6 to reduce the pressure of the high pressure side end. The plate 9 is provided, and the pump plate 9 is attached to the drive shaft 6 close to the high pressure side surface of the drive side bearing housing 7.
【００２７】具体的には、図１乃至図３に示すように、
前記ポンプ板９は、内径が前記駆動軸６の外径と同径
で、外径が前記ロータ２１の外径より小径のドーナツ状
の円板から成り、一方の面に、径方向中心側から外周方
向に放射状に延びる複数のポンプ羽根９１を形成し、該
ポンプ羽根９１形成側をポンプ面９２として、このポン
プ面９２を前記駆動側軸受ハウジング７の高圧側側面に
微小隙間を介して対向させるように前記ポンプ板９を前
記駆動軸６に挿通し、取付けるのである。Specifically, as shown in FIGS. 1 to 3,
The pump plate 9 is formed of a donut-shaped disc having an inner diameter that is the same as the outer diameter of the drive shaft 6 and an outer diameter that is smaller than the outer diameter of the rotor 21. A plurality of pump blades 91 that radially extend in the outer peripheral direction are formed, and the side on which the pump blades 91 are formed is a pump surface 92, and the pump surface 92 is opposed to the high-pressure side surface of the drive-side bearing housing 7 with a minute gap. Thus, the pump plate 9 is inserted into the drive shaft 6 and attached.
【００２８】前記ポンプ板９の前記駆動軸６への取付け
は、圧入または溶接でもよいが、図に示した実施例で
は、前記ポンプ板９の前記駆動軸６への取付位置の軸方
向前後に溝６２，６２を形成して、該各溝６２，６２に
図３に示すＣ型の止め具９３を嵌め込んで、固定するよ
うにしている。この止め具９３は、内径が前記駆動軸６
の外径より小さく前記溝６２，６２に嵌め込み可能な大
きさで、一部が切断されたＣ型のリング状のばねワッシ
ャで、これら止め具９３，９３を前記溝６２，６２に嵌
め込む場合、前記止め具９３，９３を拡径して前記駆動
軸６に挿通させ、前記各溝６２，６２に嵌め込むことに
より、前記ポンプ板９を両側からばね力で押圧して固定
するごとく成すのである。The pump plate 9 may be attached to the drive shaft 6 by press fitting or welding, but in the embodiment shown in the drawings, the pump plate 9 is attached to the drive shaft 6 axially forward and backward. Grooves 62, 62 are formed, and a C-shaped stopper 93 shown in FIG. 3 is fitted into each of the grooves 62, 62 so as to be fixed. The stopper 93 has an inner diameter of the drive shaft 6
When the stoppers 93, 93 are fitted in the grooves 62, 62 with a C-shaped ring-shaped spring washer which is smaller in outer diameter than the outer diameter and can be fitted in the grooves 62, 62 and is partially cut. By expanding the diameters of the stoppers 93, 93 and inserting them into the drive shaft 6 and fitting them in the grooves 62, 62, the pump plate 9 is pressed by spring force from both sides to be fixed. is there.
【００２９】以上の構成とすることにより、前記駆動軸
６の回転駆動による運転時、前記低圧空間１１と前記ケ
ーシング１内の高圧空間との差圧により、前記給油通路
７１から前記油溜１３の油が前記給油口７２まで汲み上
げられて、前記第１軸受７０の前記給油口７２から低圧
側が潤滑される。With the above-mentioned structure, when the drive shaft 6 is driven to rotate, the differential pressure between the low pressure space 11 and the high pressure space in the casing 1 causes the oil sump 13 to flow from the oil supply passage 71 to the oil reservoir 13. The oil is pumped up to the oil supply port 72, and the low pressure side of the first bearing 70 is lubricated from the oil supply port 72.
【００３０】また、前記駆動軸６の回転に伴い、前記ポ
ンプ板９も回転するので、前記ポンプ面９２と前記駆動
側軸受ハウジング７の高圧側側面との間に形成される微
小隙間のガス又は油を含むガスが、前記ポンプ面９２の
回転による遠心力作用により、ガスや、ガスに含まれる
油の粘性抵抗で該ポンプ面９２に沿って径方向外方に向
けて吐き出されることになり、この結果、前記微小隙間
が負圧状態となって、前記第１軸受７０の高圧側軸受端
部の圧力を減圧することができ、この減圧で前記給油口
７２に溜る油を前記した差圧により前記第１軸受７０の
高圧側軸受端部にまで給油することができる。Further, since the pump plate 9 also rotates with the rotation of the drive shaft 6, the gas in the minute gap formed between the pump surface 92 and the high pressure side surface of the drive side bearing housing 7 or The gas containing oil will be discharged radially outward along the pump surface 92 due to the viscous resistance of the gas and the oil contained in the gas due to the centrifugal force action by the rotation of the pump surface 92. As a result, the minute gap becomes a negative pressure state, so that the pressure at the high pressure side bearing end portion of the first bearing 70 can be reduced, and the oil accumulated in the oil supply port 72 is reduced by the pressure difference due to the pressure reduction. It is possible to supply oil to the high pressure side bearing end of the first bearing 70.
【００３１】従って、前記駆動側軸受ハウジング７にお
ける前記第１軸受７０の高圧側端部の外側近くに前記ポ
ンプ板９を設けるだけの簡単な構成で、該ポンプ板９に
よる減圧作用で、前記高圧側軸受端部の潤滑を充分行え
るので、従来のように、前記第１軸受７０の軸受長さが
長くなることにより、前記ケーシング１が大型化するよ
うなことなく、前記高圧側軸受端部の焼付けを防止でき
るし、この軸受端部からの高圧ガスの流入による軸受全
体の潤滑不良も防止できるのである。Therefore, the pump plate 9 has a simple structure in which only the pump plate 9 is provided near the outside of the high pressure side end portion of the first bearing 70 in the drive side bearing housing 7. Since the side bearing end portion can be sufficiently lubricated, the bearing length of the first bearing 70 is increased as in the conventional case, so that the casing 1 is not increased in size and the high pressure side bearing end portion It is possible to prevent seizure, and it is also possible to prevent poor lubrication of the entire bearing due to the inflow of high-pressure gas from the end of the bearing.
【００３２】そして、前記ポンプ板９は、前記駆動軸６
に前記駆動側軸受ハウジング７の高圧側側面に近接させ
て取付けるようにしているので、簡単な構成で、その取
付けも簡単に行えるのである。The pump plate 9 is attached to the drive shaft 6
Since it is mounted close to the high-pressure side surface of the drive-side bearing housing 7, it can be mounted easily with a simple structure.
【００３３】さらに、第１実施例においては、前記ポン
プ面９２にポンプ羽根９１を複数形成しているので、ガ
スまたは油のポンプ板９への接触面積を大きくすること
ができ、それだけガス又は油の粘性抵抗による吐き出し
量を多くでき、前記ポンプ板９による減圧をより良好に
行えるのである。また、前記ポンプ羽根９１を形成する
ことにより、前記ポンプ板９の外径を大きくすることな
く前記第１軸受７０の高圧側端部の減圧効果が期待でき
るのである。Further, in the first embodiment, since a plurality of pump blades 91 are formed on the pump surface 92, the contact area of the gas or oil with the pump plate 9 can be increased, and the gas or oil can be increased accordingly. The discharge amount due to the viscous resistance can be increased, and the pressure reduction by the pump plate 9 can be performed more favorably. Further, by forming the pump blades 91, it is possible to expect a pressure reducing effect at the high pressure side end portion of the first bearing 70 without increasing the outer diameter of the pump plate 9.
【００３４】また、前記第１実施例では、前記ポンプ板
９のポンプ面９２に複数のポンプ羽根９１を形成した
が、図４に示す第２実施例のように、ポンプ羽根９１は
形成しなくともよい。このときは、前記ポンプ板９の面
積を大きくして、微小隙間を径方向に長く形成すること
が好ましく、第２実施例では、前記ポンプ板９の外径を
前記ロータ２１の外径とほぼ同径に形成している。斯く
する場合でも、前記ポンプ板９のポンプ面９２を前記駆
動側軸受ハウジング７の高圧側側面に近接させて微小隙
間を形成することにより、充分給油を行えるだけの負圧
を生じさせることができ、高圧側軸受端部への給油は、
充分行えるのである。In the first embodiment, a plurality of pump blades 91 are formed on the pump surface 92 of the pump plate 9, but the pump blades 91 are not formed as in the second embodiment shown in FIG. Good. At this time, it is preferable to increase the area of the pump plate 9 to form a minute gap in the radial direction. In the second embodiment, the outer diameter of the pump plate 9 is substantially equal to the outer diameter of the rotor 21. They are formed with the same diameter. Even in this case, by forming the minute gap by bringing the pump surface 92 of the pump plate 9 close to the high pressure side surface of the drive side bearing housing 7, it is possible to generate a negative pressure sufficient for refueling. , Lubrication to the high pressure side bearing end is
You can do it enough.
【００３５】尚、第１及び第２実施例では、前記ポンプ
板９は、前記駆動軸６に取付けるようにしたが、該駆動
軸６に一体に成形するようにしてもよい。斯くするとき
には、前記ポンプ板９の前記駆動軸６への組付作業が省
けるので、組付け工数の増加を防止できるのである。Although the pump plate 9 is attached to the drive shaft 6 in the first and second embodiments, it may be formed integrally with the drive shaft 6. In this case, the work of assembling the pump plate 9 to the drive shaft 6 can be omitted, so that the number of assembling steps can be prevented from increasing.
【００３６】次に第３実施例について、図５に基づいて
説明する。図５に示す共回り型のスクロール圧縮機は、
前記従動スクロール５に従動軸５２を突設して、該従動
軸５２を従動側軸受ハウジング８に設ける筒状軸受部８
２において第２軸受８０を介して軸受支持するようにし
たものであり、前記従動スクロール５を前記駆動スクロ
ール４とスラストプレート３１により抱き込み状態で保
持している。さらに、前記駆動軸６は、モータ２のロー
タ２１から外方に突出させ、前記駆動軸６に形成する吐
出通路６１を反スクロール側端部において開口するよう
に貫通形成している。また、前記ロータ２１から外方に
突出される先端側は、前記ケーシング１における前記モ
ータ２の反圧縮要素側空間に設けた支持体１５に第３軸
受１６を介して第１軸受７０と共に両持ち状に軸受支持
している。また、第１及び第２実施例と同部材について
は同じ符号で示す。Next, a third embodiment will be described with reference to FIG. The co-rotating scroll compressor shown in FIG.
A cylindrical bearing portion 8 in which a driven shaft 52 is provided so as to project from the driven scroll 5 and the driven shaft 52 is provided in a driven side bearing housing 8.
2, the bearing is supported via the second bearing 80, and the driven scroll 5 is held by the drive scroll 4 and the thrust plate 31 in an embraced state. Further, the drive shaft 6 is formed so as to project outward from the rotor 21 of the motor 2 and the discharge passage 61 formed in the drive shaft 6 is penetrated so as to open at the end portion on the side opposite to the scroll side. Further, the tip end side projecting outward from the rotor 21 is both-sided together with the first bearing 70 via the third bearing 16 on the support body 15 provided in the space of the casing 1 on the side opposite to the compression element of the motor 2. The bearings are supported in a shape. The same members as those in the first and second embodiments are designated by the same reference numerals.
【００３７】そして、第３実施例では、前記モータ２
を、前記駆動側軸受ハウジング７の高圧側側面に近接し
て配設し、このモータ２のロータ２１における軸受ハウ
ジング側端部に、ポンプ板９を取付けたのである。In the third embodiment, the motor 2
Is disposed close to the high pressure side surface of the drive side bearing housing 7, and the pump plate 9 is attached to the end of the rotor 21 of the motor 2 on the bearing housing side.
【００３８】具体的には、図５及び図６に示すように、
前記ポンプ板９は、内径が前記駆動軸６に接触しない程
度に、該駆動軸６の外径より大きく、外径が前記モータ
２のステータ２２の内径より大きいドーナツ状の円板か
ら成り、一方の面に、径方向中心側から外周方向に放射
状に延びる複数のポンプ溝９４を形成して、該ポンプ溝
９４形成側をポンプ面９２と成す一方、他方の面に、前
記ロータ２１のエンドリング２３と同じ外径と内径を有
する筒状の環状突起部９５を形成し、該環状突起部９５
を前記ロータ２１の駆動側軸受ハウジング側に位置する
前記エンドリング２３の端面に固定するのであって、前
記環状突起部９５は、その突起高さを、前記エンドリン
グ２３に固定した際に、前記ポンプ板９が前記ステータ
２２に形成されるコイルエンド２４に接触しないで、か
つ、前記ポンプ面９２が前記駆動側軸受ハウジング７の
高圧側側面に微小隙間を介して近接して対向する高さと
なし、前記ロータ２１の回転時に、前記ポンプ板９が前
記コイルエンド２４に接触しないようにしている。Specifically, as shown in FIG. 5 and FIG.
The pump plate 9 is formed of a donut-shaped disc having an inner diameter larger than the outer diameter of the drive shaft 6 and an outer diameter larger than the inner diameter of the stator 22 of the motor 2 so that the inner diameter does not come into contact with the drive shaft 6. Is formed with a plurality of pump grooves 94 radially extending from the center side in the radial direction to the outer peripheral direction, and the side on which the pump grooves 94 are formed is a pump surface 92, while the other surface is provided with an end ring of the rotor 21. 23, a tubular annular protrusion 95 having the same outer diameter and inner diameter as that of 23 is formed.
Is fixed to the end face of the end ring 23 located on the drive side bearing housing side of the rotor 21, and the annular projection 95 has the projection height when fixed to the end ring 23. The pump plate 9 does not come into contact with the coil end 24 formed on the stator 22, and the pump surface 92 is close to the high-pressure side surface of the drive-side bearing housing 7 with a minute gap therebetween so as to have a height. The pump plate 9 is prevented from coming into contact with the coil end 24 when the rotor 21 rotates.
【００３９】以上の構成とした第３実施例においても、
前記モータ２が駆動すると、前記ロータ２１の回転に伴
い前記ポンプ板９も回転するので、この回転駆動によ
り、前記ポンプ面９２と前記駆動側軸受ハウジング７の
高圧側側面との間に形成される微小隙間のガス又は油
が、前記ポンプ面９２の回転による遠心力作用により、
ガスまたは油の粘性抵抗で該ポンプ面９２に沿って径方
向外方に向けて吐き出されるされることになり、前記微
小隙間が負圧状態となって、前記給油口７２に溜る油が
差圧により前記第１軸受７０の高圧側軸受端部にまで給
油されることになり、前記高圧側軸受端部の潤滑を充分
行えるのである。Also in the third embodiment having the above structure,
When the motor 2 is driven, the pump plate 9 is also rotated with the rotation of the rotor 21, so that by this rotational driving, the pump plate 92 is formed between the pump surface 92 and the high pressure side surface of the drive side bearing housing 7. The gas or oil in the minute gap is subjected to centrifugal force due to the rotation of the pump surface 92,
The viscous resistance of gas or oil causes the gas to be discharged radially outward along the pump surface 92, causing the minute gap to be in a negative pressure state, so that the oil accumulated in the oil supply port 72 has a differential pressure. As a result, oil is supplied to the high pressure side bearing end of the first bearing 70, and the high pressure side bearing end can be sufficiently lubricated.
【００４０】また、前記ポンプ板９は、回転部材である
前記ロータ２１を利用して取付けられるから、つまり、
前記ロータ２１のエンドリング２３を、前記駆動側軸受
ハウジング７の高圧側側面に近接させた上で、前記エン
ドリング２３に取付けるだけで、前記ロータ２１の回転
に伴って回転する前記ポンプ板９の減圧作用で、従来の
ように前記第１軸受７０を長くすることなく前記第１軸
受７０の高圧側端部に充分給油することができるのであ
る。従って、第３実施例では、特に、前記モータ２を前
記駆動側軸受ハウジング７の高圧側側面に近接させてい
ることも相俟って、前記ケーシング１の小型化も可能に
なりながら、前記第１軸受７０の潤滑を充分行えるので
ある。Further, since the pump plate 9 is attached using the rotor 21 which is a rotating member, that is,
The end ring 23 of the rotor 21 is brought close to the high-pressure side surface of the drive-side bearing housing 7 and then attached to the end ring 23, whereby the pump plate 9 that rotates as the rotor 21 rotates. Due to the pressure reducing action, it is possible to sufficiently supply oil to the high pressure side end portion of the first bearing 70 without lengthening the first bearing 70 as in the conventional case. Therefore, in the third embodiment, the size of the casing 1 can be reduced and the size of the casing 1 can be reduced while the motor 2 is brought close to the high pressure side surface of the drive side bearing housing 7. 1 The bearing 70 can be sufficiently lubricated.
【００４１】また、第３実施例においては、前記ポンプ
面９２に前記ポンプ溝９４を複数形成しているので、ガ
スまたは油の接触面積を大きくすることができるので、
それだけガス又は油の粘性抵抗を受ける量が多くなり、
前記ポンプ板９による減圧をより良好に行えるのであ
る。Further, in the third embodiment, since the plurality of pump grooves 94 are formed in the pump surface 92, it is possible to increase the contact area of gas or oil.
Therefore, the amount of viscous resistance of gas or oil increases,
The pressure reduction by the pump plate 9 can be performed more favorably.
【００４２】前記第３実施例では、前記ポンプ板９のポ
ンプ面９２に複数の前記ポンプ溝９４を形成したが、前
記第１実施例のようにポンプ羽根を形成してもよいし、
また、前記ポンプ溝９４やポンプ羽根は設けなくともよ
い。このときは、前記した第２実施例と同様に、前記ポ
ンプ板９のポンプ面９２を前記駆動側軸受ハウジング７
の高圧側側面に近接させて微小隙間を形成することによ
り、充分負圧を生じさせることができるので、高圧側軸
受端部への給油は、充分行えるのである。In the third embodiment, the plurality of pump grooves 94 are formed in the pump surface 92 of the pump plate 9, but the pump blades may be formed as in the first embodiment.
Further, the pump groove 94 and the pump blade may not be provided. At this time, similarly to the second embodiment described above, the pump surface 92 of the pump plate 9 is attached to the drive side bearing housing 7
By forming a minute gap in the vicinity of the side surface on the high pressure side, a sufficient negative pressure can be generated, so that the high pressure side bearing end can be sufficiently lubricated.
【００４３】尚、前記各実施例は、共回り型のスクロー
ル圧縮機について説明したが、本発明は、固定スクロー
ルと可動スクロールとから成る公転式のスクロール圧縮
機にも適用できるし、給油方法も、前記した実施例のよ
うに差圧給油に限らず、油ポンプによる強制給油をする
場合にも適用できる。また、駆動軸を軸受支持する軸受
を有する圧縮機であれば、何れの圧縮機にも対応でき
る。さらに、前記ポンプ板９は、そのポンプ面９２に凸
凹を形成して、表面積を大きくするようにして、ガス又
は油の接触面積を大きくするようにしてもよい。Although each of the above embodiments has been described with respect to a co-rotating scroll compressor, the present invention can be applied to a revolving scroll compressor including a fixed scroll and a movable scroll, and a refueling method is also applicable. The present invention can be applied not only to differential pressure lubrication as in the above-described embodiment but also to forced lubrication by an oil pump. Further, any compressor can be used as long as it has a bearing that supports the drive shaft as a bearing. Further, the pump plate 9 may be formed with an uneven surface on its pump surface 92 so as to increase the surface area so as to increase the contact area of gas or oil.
【００４４】[0044]
【発明の効果】請求項１記載の発明によれば、前記軸受
７０における高圧側端部の外側近くに、前記駆動軸６の
回転に伴い駆動回転し、前記高圧側端部の圧力を減圧さ
せるポンプ板９を設けたから、このポンプ板９を設ける
だけの簡単な構成で、該ポンプ板９の回転による減圧作
用で、前記高圧側軸受端部の潤滑を充分行えるので、従
来のように、前記軸受７０の軸受長さが長くなることは
ないし、前記ケーシング１が大型化するようなこともな
く、前記高圧側軸受端部への給油を可能として、その焼
付けを防止できるし、この軸受端部からの高圧ガスの流
入による軸受全体の潤滑不良も防止できるのである。According to the first aspect of the present invention, the bearing 70 is driven and rotated near the outside of the high pressure side end portion along with the rotation of the drive shaft 6 to reduce the pressure of the high pressure side end portion. Since the pump plate 9 is provided, it is possible to sufficiently lubricate the high pressure side bearing end portion by the depressurizing action by the rotation of the pump plate 9 with a simple configuration only by providing the pump plate 9. The bearing length of the bearing 70 does not increase, the casing 1 does not increase in size, oil can be supplied to the high-pressure side bearing end portion, and seizure can be prevented. It is also possible to prevent poor lubrication of the entire bearing due to inflow of high-pressure gas from the.
【００４５】また、請求項２記載の発明によれば、前記
ポンプ板９を前記軸受ハウジング７の高圧側側面に近接
させて前記駆動軸６に取付けたから、前記ポンプ板９の
構成を簡単にできるし、その取付けも簡単に行えるので
ある。According to the second aspect of the present invention, since the pump plate 9 is attached to the drive shaft 6 in the vicinity of the high pressure side surface of the bearing housing 7, the structure of the pump plate 9 can be simplified. However, it can be easily installed.
【００４６】請求項３の発明によれば、前記密閉ケーシ
ング１に、前記軸受ハウジング７の高圧側側面に近接し
て、前記駆動軸６を連結するモータ２を内装し、このモ
ータ２のロータ２１における軸受ハウジング側端部に、
前記ポンプ板９を取付けたから、回転部材である前記ロ
ータ２１を利用して前記ポンプ板９を回転させられ、さ
らに、前記モータ２を前記軸受ハウジング７の高圧側側
面に近接させていることも相俟って、前記ケーシング１
の小型化が可能になりながら、前記軸受７０の潤滑を充
分行えるのである。According to the invention of claim 3, a motor 2 for connecting the drive shaft 6 is provided in the closed casing 1 in proximity to the high pressure side surface of the bearing housing 7, and the rotor 21 of the motor 2 is installed. At the bearing housing side end of
Since the pump plate 9 is attached, the pump plate 9 can be rotated using the rotor 21 that is a rotating member, and the motor 2 can be brought close to the high-pressure side surface of the bearing housing 7. In addition, the casing 1
The bearing 70 can be sufficiently lubricated while the size can be reduced.
【００４７】請求項４記載の発明によれば、前記ポンプ
板９の前記軸受ハウジング７に対向するポンプ面９２
に、径方向中心側から外周方向に放射状に延びる複数の
ポンプ羽根９１を設けたから、ガスまたは油の前記ポン
プ板９への接触面積を大きくすることができるので、そ
れだけガス又は油の粘性抵抗による吐き出し量を多くで
き、前記ポンプ板９による減圧をより良好に行えるので
ある。また、前記ポンプ羽根９１を形成することによ
り、前記ポンプ板９の外径を大きくすることなく前記軸
受７０の高圧側端部の減圧効果が期待できるのである。According to the fourth aspect of the invention, the pump surface 92 of the pump plate 9 facing the bearing housing 7 is provided.
In addition, since a plurality of pump blades 91 radially extending from the radial center side to the outer peripheral direction are provided, the contact area of the gas or oil with the pump plate 9 can be increased, and thus the viscous resistance of the gas or oil is increased. The discharge amount can be increased, and the pressure reduction by the pump plate 9 can be performed more favorably. Further, by forming the pump blades 91, it is possible to expect a pressure reducing effect at the high pressure side end of the bearing 70 without increasing the outer diameter of the pump plate 9.
【００４８】請求項５記載の発明によれば、前記ポンプ
板９の前記軸受ハウジング７に対向するポンプ面９２
に、径方向中心側から外周方向に放射状に延びる複数の
ポンプ溝９４を設けたから、ガスまたは油の前記ポンプ
板９への接触面積を大きくすることができるので、それ
だけガス又は油の粘性抵抗による吐き出し量を多くで
き、前記ポンプ板９による減圧をより良好に行えるので
ある。According to the fifth aspect of the present invention, the pump surface 92 of the pump plate 9 facing the bearing housing 7 is provided.
Since the plurality of pump grooves 94 radially extending from the center side in the radial direction to the outer peripheral direction are provided, the contact area of the gas or oil with the pump plate 9 can be increased, and thus the viscous resistance of the gas or oil is increased. The discharge amount can be increased, and the pressure reduction by the pump plate 9 can be performed more favorably.
【図１】本発明の高圧ドーム形圧縮機の第１実施例を示
す圧縮機の一部切欠縦断面図。FIG. 1 is a partially cutaway vertical sectional view of a high pressure dome type compressor according to a first embodiment of the present invention.
【図２】第１実施例のポンプ板を示す正面図。FIG. 2 is a front view showing a pump plate of the first embodiment.
【図３】第１実施例のポンプ板を駆動軸に固定するため
の止め具。FIG. 3 is a stopper for fixing the pump plate of the first embodiment to a drive shaft.
【図４】第２実施例の圧縮機の一部切欠縦断面図。FIG. 4 is a partially cutaway vertical sectional view of a compressor according to a second embodiment.
【図５】第３実施例の圧縮機の縦断面図。FIG. 5 is a vertical sectional view of a compressor according to a third embodiment.
【図６】第３実施例のポンプ板を示す断面図。FIG. 6 is a sectional view showing a pump plate of a third embodiment.
【図７】従来の圧縮機を示す縦断面図。FIG. 7 is a vertical cross-sectional view showing a conventional compressor.
１ 密閉ケーシング ２ モータ ２１ ロータ ３ 圧縮要素 ６ 駆動軸 ７ 軸受ハウジング（駆動側） ７０ 軸受（第１） ７２ 給油口 ９ ポンプ板 ９１ ポンプ羽根 ８２ ポンプ面 ９４ ポンプ溝 1 Sealed Casing 2 Motor 21 Rotor 3 Compression Element 6 Drive Shaft 7 Bearing Housing (Drive Side) 70 Bearing (First) 72 Oil Filling Port 9 Pump Plate 91 Pump Blade 82 Pump Surface 94 Pump Groove
───────────────────────────────────────────────────── フロントページの続き (72)発明者 谷和 弘通 大阪府堺市築港新町３丁12番地 ダイキン 工業株式会社堺製作所臨海工場内 (72)発明者 澤潟 昌稔 大阪府堺市築港新町３丁12番地 ダイキン 工業株式会社堺製作所臨海工場内 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Hiromichi Taniwa, 3-12 Tsukiko Shinmachi, Sakai City, Osaka Prefecture Daikin Industries, Ltd. Sakai Factory Co., Ltd. Inside the seaside factory (72) Inventor Masatoshi Sawagata 3 Tsukiko Shinmachi, Sakai City, Osaka Prefecture Ding 12 Daikin Industrial Co., Ltd. Sakai Works, inside the seaside factory
Claims (5)
（１）内に高圧ガスを吐出する圧縮要素（３）を備え、
この圧縮要素（３）の低圧側と、前記密閉ケーシング
（１）の高圧内部とを区画する軸受ハウジング（７）
に、前記圧縮要素（３）の低圧側と、密閉ケーシング
（１）の高圧内部とに臨む軸受（７０）を介して前記駆
動軸（６）を支持すると共に、前記軸受（７０）の低圧
側と高圧側との途中に給油口（７２）を開口させた高圧
ドーム形圧縮機において、前記軸受（７０）における高
圧側端部の外側近くに、前記駆動軸（６）の回転に伴い
駆動回転し、前記高圧側端部の圧力を減圧させるポンプ
板（９）を設けていることを特徴とする高圧ドーム形圧
縮機。1. A compression element (3), which is driven by a drive shaft (6) and discharges high-pressure gas into a closed casing (1),
Bearing housing (7) partitioning the low pressure side of the compression element (3) and the high pressure interior of the closed casing (1)
Support the drive shaft (6) via a bearing (70) facing the low pressure side of the compression element (3) and the high pressure inside of the hermetic casing (1), and the low pressure side of the bearing (70). In a high-pressure dome type compressor having an oil supply port (72) opened in the middle between the high pressure side and the high pressure side, the drive rotation is performed near the outside of the high pressure side end of the bearing (70) with the rotation of the drive shaft (6). A high-pressure dome compressor is provided with a pump plate (9) for reducing the pressure on the high-pressure side end.
高圧側側面に近接させて駆動軸（６）に取付けている請
求項１記載の高圧ドーム形圧縮機。2. The high-pressure dome type compressor according to claim 1, wherein the pump plate (9) is mounted on the drive shaft (6) close to the high-pressure side surface of the bearing housing (7).
（７）の高圧側側面に近接して、駆動軸（６）を連結す
るモータ（２）を内装し、このモータ（２）のロータ
（２１）における軸受ハウジング側端部に、ポンプ板
（９）を取付けている請求項１記載の高圧ドーム形圧縮
機。3. A hermetic casing (1) is internally provided with a motor (2) for connecting a drive shaft (6) in the vicinity of a high pressure side surface of a bearing housing (7), and a rotor (2) of the motor (2). 21. The high-pressure dome type compressor according to claim 1, wherein a pump plate (9) is attached to an end of the bearing housing side in 21).
対向するポンプ面（９２）に、径方向中心側から外周方
向に放射状に延びる複数のポンプ羽根（９１）を設けて
いる請求項１乃至３の何れか１項に記載の高圧ドーム形
圧縮機。4. The pump surface (92) of the pump plate (9) facing the bearing housing (7) is provided with a plurality of pump blades (91) radially extending from the radial center side to the outer peripheral direction. The high-pressure dome type compressor according to any one of 1 to 3.
対向するポンプ面（９２）に、径方向中心側から外周方
向に放射状に延びる複数のポンプ溝（９４）を設けてい
る請求項１乃至３の何れか１項に記載の高圧ドーム形圧
縮機。5. A pump surface (92) of the pump plate (9) facing the bearing housing (7) is provided with a plurality of pump grooves (94) radially extending from the radial center side to the outer peripheral direction. The high-pressure dome type compressor according to any one of 1 to 3.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6088141A JPH07293473A (en) | 1994-04-26 | 1994-04-26 | High pressure dome-type compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6088141A JPH07293473A (en) | 1994-04-26 | 1994-04-26 | High pressure dome-type compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH07293473A true JPH07293473A (en) | 1995-11-07 |
Family
ID=13934664
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP6088141A Withdrawn JPH07293473A (en) | 1994-04-26 | 1994-04-26 | High pressure dome-type compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH07293473A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP3372837A1 (en) * | 2017-03-06 | 2018-09-12 | LG Electronics Inc. | Scroll compressor |
| CN108591062A (en) * | 2018-01-19 | 2018-09-28 | 上海威乐汽车空调器有限公司 | The structure of the cooling of electric scroll compressor bearing and lubrication |
-
1994
- 1994-04-26 JP JP6088141A patent/JPH07293473A/en not_active Withdrawn
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP3372837A1 (en) * | 2017-03-06 | 2018-09-12 | LG Electronics Inc. | Scroll compressor |
| US10815994B2 (en) | 2017-03-06 | 2020-10-27 | Lg Electronics Inc. | Mutual rotating scroll compressor |
| CN108591062A (en) * | 2018-01-19 | 2018-09-28 | 上海威乐汽车空调器有限公司 | The structure of the cooling of electric scroll compressor bearing and lubrication |
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