JPH0125913B2 - - Google Patents
Info
- Publication number
- JPH0125913B2 JPH0125913B2 JP56206918A JP20691881A JPH0125913B2 JP H0125913 B2 JPH0125913 B2 JP H0125913B2 JP 56206918 A JP56206918 A JP 56206918A JP 20691881 A JP20691881 A JP 20691881A JP H0125913 B2 JPH0125913 B2 JP H0125913B2
- Authority
- JP
- Japan
- Prior art keywords
- casing
- rotor
- male
- gap
- cross
- 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
Links
- 230000006866 deterioration Effects 0.000 description 6
- 230000000694 effects Effects 0.000 description 5
- 230000032683 aging Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000012790 confirmation Methods 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
- 239000003507 refrigerant Substances 0.000 description 1
- 238000005057 refrigeration 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
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary-Type Compressors (AREA)
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は、冷媒を圧縮して冷凍作用をなさしめ
る、あるいは空気を圧縮し空気源を提供するスク
リユー圧縮機に関するものである。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a screw compressor that compresses refrigerant to provide a refrigeration effect or compresses air to provide an air source.
従来の技術について、第１図、第２図により説
明する。
The conventional technology will be explained with reference to FIGS. 1 and 2.
第１図に、従来のロータ外周摩耗防止策を示
す。すなわち、ロータ軸心を真円のケーシング孔
に対し反負荷方向にずらし、稼動時、圧力差によ
り荷重が作用した場合に生じるロータ変形、軸受
隙間内での軸受の動きならびに軸受変形を吸収す
る様にしている。 FIG. 1 shows a conventional rotor outer circumferential wear prevention measure. In other words, the rotor axis is shifted in the direction opposite to the load with respect to the perfectly circular casing hole, so as to absorb the rotor deformation that occurs when a load is applied due to pressure difference during operation, the movement of the bearing within the bearing clearance, and the deformation of the bearing. I have to.
しかしならがら、第１図における起動時のロー
タ１，２とケーシング３との接触を防止するた
め、吐出側ロータ、ケーシング間ギヤツプ４をあ
る程度とる必要があり、この状態で上記目的であ
る稼動時のロータ１，２とケーシング３の接触を
防止するため吸入側ロータ・ケーシング間ギヤツ
プ５を大きくとるにはケーシング孔の径DM，DF
を大きくする必要がある。この結果として、中間
圧部分のロータ・ケーシング間ギヤツプ６も大き
くなり性能低下の原因となつていた。
However, in order to prevent contact between the rotors 1 and 2 and the casing 3 during startup in FIG. 1, it is necessary to provide a certain gap 4 between the rotor on the discharge side and the casing. In order to increase the gap 5 between the rotor and casing on the suction side in order to prevent contact between the rotors 1 and 2 and the casing 3, the diameters of the casing holes D M and D F are required.
needs to be made larger. As a result, the gap 6 between the rotor and the casing in the intermediate pressure section also becomes large, causing performance deterioration.
第２図に、ロータとケーシングの接触防止を行
なわない場合のロータとケーシングの摩耗状態を
示す。 FIG. 2 shows the state of wear between the rotor and the casing when no contact between the rotor and the casing is prevented.
スクリユー圧縮機のロータ上での圧力分布は、
圧縮室が、螺線状を呈しているため、ロータ円周
方向と軸方向で説明され得るものであり、第２図
に示すロータ１，２では右手上方が吐出、左手下
方が吸入となる。また、ロータ下部が吸入〜中間
圧、上部が中間〜吐出圧、側面すなわち円周横部
分が中間圧となる。勿論吸入が上で吐出が下にな
ることも圧縮機の構造に依り、ありうる。一方、
ケーシングについても、圧力分布状態はロータと
同一である。 The pressure distribution on the screw compressor rotor is
Since the compression chamber has a spiral shape, it can be explained in terms of the circumferential direction and the axial direction of the rotor, and in the rotors 1 and 2 shown in FIG. 2, the upper right hand is the discharge, and the lower left hand is the suction. Further, the lower part of the rotor has a suction to intermediate pressure, the upper part has an intermediate to discharge pressure, and the side surface, that is, the lateral part of the circumference, has an intermediate pressure. Of course, depending on the structure of the compressor, it is also possible for the suction to be at the top and the discharge to be at the bottom. on the other hand,
The pressure distribution state of the casing is also the same as that of the rotor.
ロータ１，２の摩耗状態は、吐出側端面７近傍
の外周部分が顕著であり、摩耗量ｄだけロータ・
ケーシング間ギヤツプが広がることになる。ケー
シング２側については、図中斜線部分８すなわち
ロータ１，２が圧力により押される部分の、ロー
タ１，２同様、吐出端面近傍が著しい。 The state of wear of the rotors 1 and 2 is remarkable in the outer circumferential portion near the discharge side end face 7, and the rotor
The gap between the casings will widen. As for the casing 2 side, the shaded area 8 in the figure, that is, the area where the rotors 1 and 2 are pushed by pressure, is remarkable in the vicinity of the discharge end surface, similar to the rotors 1 and 2.
スクリユー圧縮機の経時性能低下は、稼動中の
ロータ外周摩耗によるロータ・ケーシング間ギヤ
ツプ増大に起因する場合が多く、ロータ外周が摩
耗すると、吐出側ロータ・ケーシング間ギヤツプ
はもとより、ロータ全周に渡りギヤツプが広が
る。また、第１図に示す如く、ロータ軸心をずら
してロータとケーシングの接触の防止をするにし
ても、ロータの変形、軸受の隙間を考慮すると、
ケーシング孔をある程度大きくとる必要があり、
そのため、中間圧部分のロータ・ケーシング間ギ
ヤツプについても大となり初期性能の低下が生じ
るという問題があつた。 Performance deterioration over time in screw compressors is often due to an increase in the gap between the rotor and casing due to rotor outer circumference wear during operation. The gap widens. Furthermore, as shown in Fig. 1, even if the rotor axis is shifted to prevent contact between the rotor and the casing, considering the deformation of the rotor and the gap between the bearings,
It is necessary to make the casing hole somewhat large,
As a result, the gap between the rotor and the casing in the intermediate pressure section becomes large, resulting in a problem that the initial performance deteriorates.
本発明の目的は、圧縮機のロータ・ケーシング
間ギヤツプを小さくすることにより性能向上を図
り、さらに駆動時のスクリユー圧縮機のロータ外
周摩耗を防止し、信頼性の向上と同時にロータ・
ケーシング間ギヤツプの増大に伴う性能低下を防
ぐスクリユー圧縮機を提供することにある。 The purpose of the present invention is to improve performance by reducing the gap between the rotor and casing of a compressor, and furthermore, to prevent wear on the outer circumference of the rotor of a screw compressor during drive, and at the same time improve reliability.
It is an object of the present invention to provide a screw compressor that prevents performance deterioration due to an increase in the gap between casings.
上記目的は、ケーシング内に互いにかみ合う一
対の雄、雌ロータとを備えたスクリユー圧縮機に
おいて、前記ケーシングは吸入側から吐出側にか
けて２段階に異なる前記雄、雌ロータの軸線に直
交する断面形状を有するケーシング孔を備え、吸
入側の前記断面形状は２つの交錯する前記雄ロー
タの軸心を中心とする円弧と前記雌ロータの軸心
を中心とする円弧とによつて形成されており、吐
出側の前記断面形状は吸入側の前記断面形状を形
成した円弧に加え、前記雄、雌ロータの軸心より
駆動時に前記雄、雌ロータに加わる負荷方向に偏
心しした位置を中心とした円弧とによつて形成さ
れることによつて達成される。
The above object is a screw compressor equipped with a pair of male and female rotors that mesh with each other in a casing, in which the casing has a cross-sectional shape perpendicular to the axes of the male and female rotors that differs in two stages from the suction side to the discharge side. the cross-sectional shape on the suction side is formed by two intersecting circular arcs centered on the axial center of the male rotor and circular arcs centered on the axial center of the female rotor; In addition to the circular arc forming the cross-sectional shape on the suction side, the cross-sectional shape on the side is an arc centered at a position eccentric from the axis of the male and female rotors in the direction of the load applied to the male and female rotors during driving. This is achieved by forming the
雄、雌各ロータの軸心を中心としたケーシング
孔のほかに吐出側にのみ軸心から偏心した位置を
中心とした円弧の断面を有する孔を設けることに
よつて、駆動時のロータの変形によるロータとケ
ーシングの接触を防ぐことができる。その際、ケ
ーシング全体でみれば４つの円で形成されたケー
シング孔となつており、かつこれは吐出側のみに
設けられているものであるから、接触による経時
性能の低下のみならず漏れによる初期性能の低下
も防ぐことができる。
In addition to the casing holes centered on the axes of the male and female rotors, a hole with an arcuate cross section centered on a position eccentric from the axis is provided only on the discharge side to prevent rotor deformation during driving. This prevents contact between the rotor and casing. At this time, since the casing hole is formed by four circles when looking at the casing as a whole, and this hole is provided only on the discharge side, not only does the performance deteriorate over time due to contact, but also the initial damage due to leakage. Deterioration in performance can also be prevented.
以下、本発明の実施例を第３図により説明す
る。吐出側ロータ・ケーシング間ギヤツプを形成
するケーシング孔９，１０の中心を起動時にロー
タ１，２とケーシング３とが接触しない程度のギ
ヤツプ４分だけとれる位置１１，１２におく。さ
らに稼動時にロータ１，２の変形ならびに軸受の
動きを考慮し、吸入側ロータ・ケーシング間ギヤ
ツプ５が確保されるだけ、ギヤツプ５を形成する
ケーシング孔１３，１４の中心をずらし位置１
５，１６に置く。すなわち雄ロータ１、雌ロータ
２に対するケーシング孔は、孔９，１３および孔
１０，１４にて形成される瓢状断面を有する孔と
なる。初期性能を向上させさらに稼動中のロータ
とケーシングの接触による性能の経時低下を生じ
させず、接触に伴うロータとケーシングの焼付を
防止するため、性能にほとんど影響を及ぼさない
吸入側ロータ・ケーシング間ギヤツプ、すなわち
第２図に示したケーシング接触部分８の部分のギ
ヤツプを広げる様、従来より固執して来た真円断
面のケーシング孔を改め、ケーシング孔を負荷方
向に逃げた瓢状断面にした。この瓢状断面は、交
錯する２円で形成され、加工も容易にできる。
An embodiment of the present invention will be described below with reference to FIG. The centers of the casing holes 9 and 10 that form the gap between the discharge side rotor and the casing are placed at positions 11 and 12 that provide a gap of 4 minutes so that the rotors 1 and 2 and the casing 3 do not come into contact during startup. Furthermore, taking into consideration the deformation of the rotors 1 and 2 and the movement of the bearings during operation, the centers of the casing holes 13 and 14 forming the gap 5 are shifted to the position 1 to ensure the gap 5 between the rotor and the casing on the suction side.
Place it on 5,16. That is, the casing holes for the male rotor 1 and the female rotor 2 are holes having a gourd-shaped cross section formed by the holes 9 and 13 and the holes 10 and 14. In order to improve initial performance, prevent performance deterioration over time due to contact between the rotor and casing during operation, and prevent seizure of the rotor and casing due to contact, the suction side rotor and casing have been designed to have little effect on performance. In order to widen the gap at the casing contact portion 8 shown in Figure 2, the casing hole, which had traditionally had a perfect circular cross section, was changed to a gourd-shaped cross section that ran away in the load direction. . This gourd-shaped cross section is formed by two intersecting circles and can be easily processed.
また、瓢状断面を形成する２円の径は、同径で
も異径でも良いが、加工性を考慮すると、同径の
方が良いと考える。本中心の偏心量dM，dFは実験
的確認によれば雄雌ロータの径DM，DFの比とし
てdM／DM，dF／DF＝２〜５×10-4が、良好であ
つた。 Further, the diameters of the two circles forming the gourd-shaped cross section may be the same diameter or different diameters, but considering workability, it is thought that it is better to have the same diameter. According to experimental confirmation , the eccentricities d M and d F of the main center are d M /D M and d F /D F = 2 to 5 × 10 -4 as the ratio of the diameters D M and D F of the male and female rotors. , it was good.
本実施例によれば、稼動時、ロータ１，２およ
びケーシング３の接触摩耗が生じることなく、初
期の従来より小さくすることができるロータ・ケ
ーシング間ギヤツプが保たれ、性能の向上と同時
に経時低下をなくすことができ、また接触焼付の
防止ともなり、信頼性の向上にも寄与する。 According to this embodiment, during operation, contact wear between the rotors 1, 2 and the casing 3 does not occur, and the gap between the rotor and the casing, which can be made smaller than the earlier conventional method, is maintained, and performance is improved while reducing aging. It also prevents contact seizure and contributes to improved reliability.
第４図において、ケーシング孔の断面形状は、
第３図同様、２円で形成される瓢状断面である
が、第２図に示す様に、ロータ１，２とケーシン
グ３の接触摩耗状態が吐出側端面１７の近傍、負
荷方向側であることを考え、吸入側ロータ・ケー
シング間ギヤツプを形成する方の孔を深さＬと
し、Ｌより深い部分については、吐出側ロータ・
ケーシング間ギヤツプを形成する孔と同一とす
る。すなわち吐出端面１７よりＬまでは瓢状断
面、Ｌより深い部分は真円断面となる。Ｌの長さ
はロータ１，２およびケーシング３の摩耗状態な
らびに、圧縮機のラジアル方向吸入口１８が負荷
方向のケーシング孔内面の存在することを考慮す
れば、ロータ全長の最大２分の１あれば充分と考
える。 In Fig. 4, the cross-sectional shape of the casing hole is
As in Fig. 3, it has a gourd-shaped cross section formed by two circles, but as shown in Fig. 2, the contact wear between the rotors 1, 2 and the casing 3 is near the discharge side end face 17, on the load direction side. Considering this, the hole that forms the gap between the suction side rotor and the casing is set to a depth L, and the part deeper than L is set to the discharge side rotor.
It is the same as the hole that forms the gap between the casings. That is, the section from the discharge end surface 17 to L has a gourd-shaped cross section, and the portion deeper than L has a perfect circular cross section. The length of L should be at most 1/2 of the total length of the rotor, taking into consideration the wear conditions of the rotors 1, 2 and casing 3, and the fact that the compressor's radial suction port 18 is located on the inner surface of the casing hole in the load direction. I think that is sufficient.
本実施例によれば、性能に特に顕著な影響を及
ぼす吐出側ロータ・ケーシング間ギヤツプを小さ
く、さらに一定に保つことができ、性能の向上な
らびに経時低下をなくすことができる。 According to this embodiment, the gap between the discharge side rotor and the casing, which has a particularly significant effect on performance, can be kept small and constant, thereby improving performance and eliminating deterioration over time.
本発明によれば、ロータ・ケーシング間ギヤツ
プの設定値を小さくすることができると同時に従
来生じていたロータ・ケーシングの接触摩耗によ
るロータ・ケーシング間ギヤツプの増加を防止す
ることができ、初期性能を向上させ、さらにその
性能を維持することができる。
According to the present invention, it is possible to reduce the set value of the gap between the rotor and the casing, and at the same time, it is possible to prevent the increase in the gap between the rotor and the casing due to the contact wear of the rotor and the casing, which conventionally occurs, thereby improving the initial performance. It is possible to improve and maintain its performance.
また、ロータとケーシングの接触を防止したこ
とで、接触によるロータとケーシングの焼付を防
止することができ信頼性の向上が図れる。 Furthermore, by preventing contact between the rotor and the casing, seizure of the rotor and the casing due to contact can be prevented, and reliability can be improved.
第１図は、従来技術を示す圧縮機のロータ部分
を吐出側より表したものの説明図、第２図は、ロ
ータの摩耗状態を示す外観図である。第３図、第
４図は、各々本発明の実施例を示す圧縮機ロータ
部分の断面図である。
１…雄ロータ、２…雌ロータ、３…ケーシン
グ、４…吐出側ギヤツプ、５…吸入側ギヤツプ、
８…ケーシング接触部分、９，１０，１３，１４
…ケーシング穴、１１，１２，１５，１６…ケー
シング穴中心。
FIG. 1 is an explanatory view of a rotor portion of a compressor according to the prior art, viewed from the discharge side, and FIG. 2 is an external view showing the wear state of the rotor. 3 and 4 are cross-sectional views of a compressor rotor portion, each showing an embodiment of the present invention. 1...Male rotor, 2...Female rotor, 3...Casing, 4...Discharge side gap, 5...Suction side gap,
8...Casing contact part, 9, 10, 13, 14
...Casing hole, 11, 12, 15, 16...Casing hole center.
Claims (1)
ロータを備えたスクリユー圧縮機において、前記
ケーシングは吸入側から吐出側にかけて２段階に
異なる前記雄、雌ロータの軸線に直交する断面形
状を有するケーシング孔を備え、吸入側の前記断
面形状は２つの交錯する前記雄ロータの軸心を中
心とする円弧と前記雌ロータの軸心を中心とする
円弧とによつて形成されており、吐出側の前記断
面形状は吸入側の前記断面形状を形成した円弧に
加え、前記雄、雌ロータの軸心より駆動時に前記
雄、雌ロータに加わる負荷方向に偏心した位置を
中心とした円弧とによつて形成されていることを
特徴とするスクリユー圧縮機。1. In a screw compressor equipped with a pair of male and female rotors that engage with each other in a casing, the casing has a casing hole having a cross-sectional shape perpendicular to the axis of the male and female rotors that differs in two stages from the suction side to the discharge side. The cross-sectional shape on the suction side is formed by two intersecting circular arcs centered on the axial center of the male rotor and circular arcs centered on the axial center of the female rotor, and the cross-sectional shape on the discharge side The shape is formed by, in addition to the circular arc forming the cross-sectional shape on the suction side, an arc centered at a position eccentric from the axis of the male and female rotors in the direction of the load applied to the male and female rotors during driving. A screw compressor characterized by:
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP20691881A JPS58110889A (en) | 1981-12-23 | 1981-12-23 | Screw compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP20691881A JPS58110889A (en) | 1981-12-23 | 1981-12-23 | Screw compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS58110889A JPS58110889A (en) | 1983-07-01 |
| JPH0125913B2 true JPH0125913B2 (en) | 1989-05-19 |
Family
ID=16531230
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP20691881A Granted JPS58110889A (en) | 1981-12-23 | 1981-12-23 | Screw compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS58110889A (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61152990A (en) * | 1984-12-26 | 1986-07-11 | Hitachi Ltd | Screw vacuum pump |
| JPH06100082B2 (en) * | 1986-10-24 | 1994-12-12 | 株式会社日立製作所 | Skrillyu fluid machine |
| JPH07111184B2 (en) * | 1988-12-05 | 1995-11-29 | 株式会社荏原製作所 | Screw compressor |
| JP2016065475A (en) * | 2014-09-24 | 2016-04-28 | 株式会社デンソー | Screw pump |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5735649Y2 (en) * | 1979-12-25 | 1982-08-06 | ||
| JPS56103691U (en) * | 1980-01-12 | 1981-08-13 |
-
1981
- 1981-12-23 JP JP20691881A patent/JPS58110889A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS58110889A (en) | 1983-07-01 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EXPY | Cancellation because of completion of term |