JPS59176489A - Screw fluid machine - Google Patents
Screw fluid machineInfo
- Publication number
- JPS59176489A JPS59176489A JP4881483A JP4881483A JPS59176489A JP S59176489 A JPS59176489 A JP S59176489A JP 4881483 A JP4881483 A JP 4881483A JP 4881483 A JP4881483 A JP 4881483A JP S59176489 A JPS59176489 A JP S59176489A
- Authority
- JP
- Japan
- Prior art keywords
- rotor
- clearance
- timing gear
- bearing
- rotors
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
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)
Abstract
Description
【発明の詳細な説明】
〔発明の利用分野〕
本発明はスクリュ流体機械全般に係り、特に運転乗件が
厳しく高速運転を必要とする単段オイルフリースクリュ
圧縮機に関する。DETAILED DESCRIPTION OF THE INVENTION [Field of Application of the Invention] The present invention relates to screw fluid machines in general, and particularly to a single-stage oil-free screw compressor which has severe operating conditions and requires high-speed operation.
〔発明の背１〕
１ずオイルフリースクリュ圧縮機の全体構造を第１図を
参照して説明する。オスロータ１とメスロータ２は噛合
状態にてケーシングに収納されている。ケーシングは吸
入ケーシング４、吐出ケーシング３、エンドカベ５より
なり、吐出ケーシング３に上記両ロータを収納し、吸入
側端部に吸入ケーシング４を配置し、ロータ軸Ｉｓ、２
Ｓおよびｌｃｌ、２ｄｉケーシングの軸貫通部に配置し
た軸シール材８に挿入し、この軸シール８は圧縮空気の
シール及び軸受へ送給された油をシールする。[Background of the Invention 1] 1. The overall structure of an oil-free screw compressor will be explained with reference to FIG. 1. A male rotor 1 and a female rotor 2 are housed in a casing in a meshed state. The casing consists of a suction casing 4, a discharge casing 3, and an end wall 5. Both rotors are housed in the discharge casing 3, the suction casing 4 is arranged at the suction side end, and the rotor shafts Is, 2
It is inserted into the shaft seal material 8 placed in the shaft penetration part of the S, lcl, and 2di casings, and this shaft seal 8 seals the compressed air and seals the oil sent to the bearing.
さらに両ロータはラジアル荷重を軸受６により、スラス
ト荷重を軸受７によりそれぞれ支承されている。オスロ
ータとメスロータの吐出ｌ１ｌｌ＠端には１対のタイミ
ングギヤ９，１０が噛合状態で装置され、両ロータ同士
が非接触状態で回転するように配置されている。またオ
スロータの吸入側軸ＩＳＯ軸端にはピニオン１１が装着
され、図示されていないプルギヤにて駆動される。駆動
源よりピニオン１１に回転力が伝達されると、１対のオ
スロータとメスロータはタイミングギヤ９，１０によっ
て微小間隙を保持しながら、同期して回転する。その結
果、吸入空気は図示しない吸入通路を経て、両ロータの
歯形にて形成された吸入空間に吸入され、両ロータの回
転に伴い歯形空間は順次減少し、封入空気は吐出され、
圧縮空気となり、図示しない吐出ボートから吐出され種
々の用途に供される。Furthermore, the radial load of both rotors is supported by a bearing 6, and the thrust load is supported by a bearing 7, respectively. A pair of timing gears 9 and 10 are disposed in mesh with each other at the discharge l1ll@ ends of the male rotor and the female rotor, and the two rotors are arranged to rotate without contacting each other. A pinion 11 is attached to the ISO shaft end of the male rotor on the suction side, and is driven by a pull gear (not shown). When rotational force is transmitted to the pinion 11 from the drive source, the pair of male and female rotors rotate synchronously while maintaining a small gap by the timing gears 9 and 10. As a result, the intake air passes through a suction passage (not shown) and is drawn into the intake space formed by the tooth profiles of both rotors, and as both rotors rotate, the tooth profile space gradually decreases and the sealed air is discharged.
The compressed air is discharged from a discharge boat (not shown) and used for various purposes.
従来技術では第１図に示すように、圧縮機の高圧側にス
ラス＋［受が配置されていた。従って、運転時にロータ
の温度が上昇し、熱膨張によってロータの高圧側端面ど
ケーシング壁とのクリアランス（以下端面クリアランス
）が増大して、性能低下の要因となっていた。またタイ
ミングギヤがラジアル軸受より遠く離れた位置に配置さ
れで藝たため、ガス荷重によるタイミングギヤ部の軸変
位が大きく、軸振動発生の原因となっていた。タイミン
グギヤ部の＠変位が大きくなると、ギヤの年俸精度が高
くても１留合が不規則となる。これはタイミングギヤの
回転伝達誤差（オスロータを一足回転速度で回転し、メ
スロータを駆動した時のメスロータの回転方向の進み遅
れ〕が大きくなることを意味しておシ、ロータの曲げお
よびねじり振動の発生要因となる。その結果、性能向上
のためにロータ間クリアランスを小さくするとロータ同
士が接触して焼損がおき、ロータ間クリアランスの縮小
すなわち、性能向上の妨げとなっていた。In the prior art, as shown in FIG. 1, a sluth bridge was placed on the high pressure side of the compressor. Therefore, the temperature of the rotor increases during operation, and the clearance between the high-pressure side end face of the rotor and the casing wall (hereinafter referred to as end face clearance) increases due to thermal expansion, resulting in a decrease in performance. Furthermore, since the timing gear was located far away from the radial bearing, the shaft displacement of the timing gear portion due to the gas load was large, causing shaft vibration. When the displacement of the timing gear section becomes large, even if the annual salary accuracy of the gear is high, the 1st station becomes irregular. This means that the timing gear's rotational transmission error (advance/delay in the female rotor's rotational direction when the male rotor is rotated at one rotational speed and the female rotor is driven) becomes large. As a result, when the inter-rotor clearance is reduced in order to improve performance, the rotors come into contact with each other and burnout occurs, which reduces the inter-rotor clearance and thus impedes performance improvement.
本発明の目的はロータ温度の上昇による端面クリアラン
スの増大および軸振動を低減することによってロータ間
クリアランスを縮小し、高性能、高信頼性の単段オイル
フリースクリュ圧縮機を提供することにある。An object of the present invention is to provide a high-performance, highly reliable single-stage oil-free screw compressor that reduces inter-rotor clearance by increasing end face clearance and reducing shaft vibration due to rise in rotor temperature.
本発明は、タイミングギヤの回転伝達誤差を小さく押え
るため可能な限シラシアル軸受の近傍にタイミングギヤ
を配置して軸変位を小さくしたことを特徴とする。The present invention is characterized in that the timing gear is disposed as close to the radial bearing as possible to reduce shaft displacement in order to suppress the rotation transmission error of the timing gear.
以下本発明の一実施例を第２図にょシ説明する。 An embodiment of the present invention will be described below with reference to FIG.
オスロータ１のスラスト軸受７ｏを駆動側すなわちピニ
オンギヤＩＩＫ隣接させて軸端に配置する。The thrust bearing 7o of the male rotor 1 is disposed on the drive side, that is, at the shaft end adjacent to the pinion gear IIK.
またメスロータ２のスラスト力は吸入側のアンギュラ玉
軸受６０で支承する。以上のようにするとタイミングギ
ヤ９，１（ｌ吐出側ラジアル軸受６に隣接させて配置で
きる。Further, the thrust force of the female rotor 2 is supported by an angular ball bearing 60 on the suction side. By doing so, the timing gears 9, 1 (l) can be placed adjacent to the discharge side radial bearing 6.
ｇ３図はピニオンギヤ１１とプルギヤ３００との噛合状
態を示したものである。ケーシング４０の一部分は切欠
かれており、ピニオンギヤ１１の一部を露出させている
。すなわち、ピニオンギヤ１１は第３図の状態でプルギ
ヤ３００と噛合い、図示しない駆動源によって駆動され
る。Figure g3 shows the meshing state between the pinion gear 11 and the pull gear 300. A portion of the casing 40 is cut out, exposing a portion of the pinion gear 11. That is, the pinion gear 11 meshes with the pull gear 300 in the state shown in FIG. 3, and is driven by a drive source (not shown).
従来技術ではスラスト軸受７が吐出側に配置（第１図参
照ンされていたため、第２図における端面クリアランス
Ｂは圧縮機が運転され、ロータ温度が上昇すると熱膨張
によって増大し、圧縮機性能が低下する。一方、本発明
の場合はスラスト軸受６０．７０を吸入側に配置（第２
図参照）しであるため、圧縮機の運転時に端面クリアラ
ンスＢが従来技術の場合とは逆に縮小することに々シ、
高効率圧縮機の提供が可能となる。なお、本発明の場合
は第２図の如くオスロータのスラスト軸受７０、メスロ
ータの吸入側軸受６０はスタフイングボックス２００，
１００で支承されておシ、端面クリアランスＢはスペー
サ２２０，１２０の厚さすなわちＡ、Ｃの値を調整する
ことによｐ任意に変えることができる。In the conventional technology, the thrust bearing 7 was placed on the discharge side (see Fig. 1), so the end face clearance B in Fig. 2 increases due to thermal expansion when the compressor is operated and the rotor temperature rises, and the compressor performance deteriorates. On the other hand, in the case of the present invention, the thrust bearings 60 and 70 are arranged on the suction side (second
(see figure), the end face clearance B often decreases during compressor operation, contrary to the case of the prior art.
It becomes possible to provide a high-efficiency compressor. In addition, in the case of the present invention, as shown in FIG.
The end face clearance B can be arbitrarily changed by adjusting the thickness of the spacers 220, 120, that is, the values of A and C.
次にタイミン（ギヤ部の軸変位について第４図を参照し
て本発明と従来技術との相違について説明スル。ロータ
の圧縮機構部分にはガスの圧縮力による荷重が作用し、
その結果ロータには軸変位δが生じる。本発明ではタイ
ミングギヤを吐出側のラジアル軸受に隣接させて配置し
であるため、タイミングギヤ部の軸変位は３里となシ、
従来技術の場合のδ２よシは明らかに小さくなる。その
数値を試算した結果ではδ１／δ２ ＜ ０．５となシ
、本発明の場合はその軸変位を半減できる。Next, we will explain the difference between the present invention and the prior art with reference to FIG.
As a result, an axial displacement δ occurs in the rotor. In the present invention, since the timing gear is arranged adjacent to the radial bearing on the discharge side, the axial displacement of the timing gear part is 3 ri.
δ2 in the case of the prior art is obviously smaller. As a result of trial calculation of the numerical value, δ1/δ2 < 0.5, and in the case of the present invention, the axial displacement can be halved.
タイミングギヤ部の軸変位が大きくなると軸振動の原因
となシ、ロータ間クリアランスの縮小の妨げとなって圧
縮機効率低下の大きな要因となる。If the shaft displacement of the timing gear section becomes large, it will cause shaft vibration, and it will also prevent the reduction of the clearance between the rotors, which will be a major factor in reducing the efficiency of the compressor.
また、タイミングギヤの加工精度をいくら高くしても無
意味となる。Moreover, no matter how high the processing precision of the timing gear is, it is meaningless.
以上のように本発明によれば運転時の端面クリヂランス
の増大を防止でき、またタイミングギヤ部の軸変位を小
さく抑制することによって軸振動全低減し、その結果ロ
ータ間クリアランスの縮小が可能となる。従って、高効
率、高信頼性の圧縮機を提供できる。As described above, according to the present invention, it is possible to prevent an increase in the end face clearance during operation, and by suppressing the shaft displacement of the timing gear part, the shaft vibration is completely reduced, and as a result, it is possible to reduce the clearance between the rotors. . Therefore, a compressor with high efficiency and high reliability can be provided.
第１図は従来技術を示した横断面図、第２図は本発明を
示した横断面図、第３図はピニオンギヤの駆動方法の説
明図、第４図はロータの軸変位の説明図である。Fig. 1 is a cross-sectional view showing the prior art, Fig. 2 is a cross-sectional view showing the present invention, Fig. 3 is an explanatory view of the pinion gear driving method, and Fig. 4 is an explanatory view of the axial displacement of the rotor. be.
Claims (1)
それぞれのロータがタイミングギヤによって微小間隙を
保持しながら回転するスクリュ流体機械において、ラジ
アル軸受とタイミングギヤとを隣接させて配置したこと
を特徴とするスクリュ流体機械。 ２、 メスロータの低圧側軸受にラジアルおよびスラス
ト力を支承する軸受を用いたこと全特徴とする前記第１
項のスクリュ流体機械。[Claims] 1. A male rotor and a female rotor are included in the casing,
A screw fluid machine in which each rotor rotates with a minute gap maintained by a timing gear, characterized in that a radial bearing and a timing gear are arranged adjacent to each other. 2. The first aspect is characterized in that a bearing that supports radial and thrust forces is used as the low-pressure side bearing of the female rotor.
Section Screw Fluid Machinery.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4881483A JPS59176489A (en) | 1983-03-25 | 1983-03-25 | Screw fluid machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4881483A JPS59176489A (en) | 1983-03-25 | 1983-03-25 | Screw fluid machine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS59176489A true JPS59176489A (en) | 1984-10-05 |
Family
ID=12813673
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP4881483A Pending JPS59176489A (en) | 1983-03-25 | 1983-03-25 | Screw fluid machine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS59176489A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61223295A (en) * | 1985-03-27 | 1986-10-03 | Hitachi Ltd | Vacuum pump with oil-free screw |
| US7682084B2 (en) * | 2003-07-18 | 2010-03-23 | Kobe Steel, Ltd. | Bearing and screw compressor |
| CN102705230A (en) * | 2012-05-09 | 2012-10-03 | 苏州百胜动力机器有限公司 | Gear pump |
-
1983
- 1983-03-25 JP JP4881483A patent/JPS59176489A/en active Pending
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61223295A (en) * | 1985-03-27 | 1986-10-03 | Hitachi Ltd | Vacuum pump with oil-free screw |
| JPH0588392B2 (en) * | 1985-03-27 | 1993-12-22 | Hitachi Ltd | |
| US7682084B2 (en) * | 2003-07-18 | 2010-03-23 | Kobe Steel, Ltd. | Bearing and screw compressor |
| CN102705230A (en) * | 2012-05-09 | 2012-10-03 | 苏州百胜动力机器有限公司 | Gear pump |
| CN102705230B (en) * | 2012-05-09 | 2015-09-02 | 苏州百胜动力机器股份有限公司 | A kind of gear pump |
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