JPH1089270A - Screw rotor - Google Patents

Screw rotor

Info

Publication number
JPH1089270A
JPH1089270A JP27678196A JP27678196A JPH1089270A JP H1089270 A JPH1089270 A JP H1089270A JP 27678196 A JP27678196 A JP 27678196A JP 27678196 A JP27678196 A JP 27678196A JP H1089270 A JPH1089270 A JP H1089270A
Authority
JP
Japan
Prior art keywords
shaft
rotor
screw
hole
central
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.)
Granted
Application number
JP27678196A
Other languages
Japanese (ja)
Other versions
JP3803812B2 (en
Inventor
Tetsuya Sasage
徹哉 捧
Yukihiro Kojima
幸裕 小島
Noboru Toda
登 戸田
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hokuetsu Industries Co Ltd
Original Assignee
Hokuetsu Industries Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Hokuetsu Industries Co Ltd filed Critical Hokuetsu Industries Co Ltd
Priority to JP27678196A priority Critical patent/JP3803812B2/en
Priority to CN97102933A priority patent/CN1112515C/en
Publication of JPH1089270A publication Critical patent/JPH1089270A/en
Application granted granted Critical
Publication of JP3803812B2 publication Critical patent/JP3803812B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

PROBLEM TO BE SOLVED: To employ simple shaft coupling, to employ a rotor part being the same to various kinds of machines having different shaft lengths, to dissolve a problem on a high cost by removing the useless use of a material and reducing the high number of manufacturing processes, to facilitate handling through division of a shaft, to reduce the size of a machine for moulding, to facilitate machining in a way that machining of only a shaft for an exclusive use suffices for machining of a rotor, to prevent the occurrence of an error in assembly, and to perform smooth coupling of a shaft. SOLUTION: A central shaft 3 is extended through a rotor part 1, formed in the tooth shape of a screw, to an outer end 2 on the axis of the rotor part 1. A small shaft 5 and a fit-in hole are formed in the outer end 4 of the central shaft 3. A fit-in hole 7 or a small shaft is formed on a separately manufactured rotor shaft 6 fitted in externally or internally of the small shaft 5 or a fitin hole. Lengths from the small shaft 5 or the fit-in hole to the rotor end faces 2 and 2a of of each of most starting ends 26 and 26a and innermost and outermost ends 27 and 27a are the same each other with the rotor part 1 nipped therebetween. Further, a ventilation hole 25 extending from a fit-in hole 7 recessed in the rotor shaft 6 or the central shaft to a shaft end on the opposite side is formed in the rotor shaft 6 or the central shaft.

Description

【発明の詳細な説明】DETAILED DESCRIPTION OF THE INVENTION

【０００１】[0001]

【発明の属する技術分野】スクリュ流体機械に使用する
スクリュロータに関するものであり、特に圧縮機、膨張
機、真空ポンプ等に使用するスクリュロータに関するも
のである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a screw rotor used for a screw fluid machine, and more particularly to a screw rotor used for a compressor, an expander, a vacuum pump and the like.

【０００２】[0002]

【従来の技術】従来、この種のスクリュロータは、ロー
タ部とロータ軸とが一体的に形成されている。例えば、
ロータ部とロータ軸とは同一金属材料から削りだし加工
されている。または、金属製のロータ軸の周囲に合成樹
脂製のロータを一体成形したものもある。そして、機種
間でロータ部の寸法が共通であっても、スクリュ流体機
械の吐出圧力や駆動原動機が変わったり、スクリュ流体
機械の使用用途に応じて軸長や軸径又は軸部の表面処理
が変わるため、ロータの製作工程が複雑となりかつ種類
が多い。このことにより種々の問題があった、スクリュ
ロータ各部の直径を例にとると、一般にロータ歯部の直
径は軸部の約３〜４倍となっているのが普通である。そ
のため製作上次のような問題がある。 （１）ロータ部と軸部とは同一金属材料から削りだし加
工されている場合は、ロータ歯部の直径に見合ったサイ
ズの素材を用い、これを所望とする軸部の直径まで切削
加工で削りだす必要がある。そのため、材料や加工工数
に多大な無駄が生じる。 （２）金属製の軸の周囲に熱硬化性の合成樹脂製のロー
タを一体成形したものである場合は、軸の直径に見合っ
た金属材料を準備すればよいが、軸径の割に軸長が長い
ため、加工に際し芯振れ対策等の配慮が必要となり、生
産性が悪くなる。 （３）併せて、ロータ軸長が長いため、ロータ部の成形
型も大型で高額となる他成形時の作業性も悪い。また、
表面処理に際しても同様に作業性が悪い。 （４）例えば、圧縮作用空間に水を噴射して該空間内の
冷却と密閉とを行う水噴射式圧縮機等に使用し、軸部が
大気もしくは水分を含む流体に触れる場合は、長期使用
の間に錆が発生し当該軸封部の漏洩や摺動部の異常摩耗
の原因となる。 （５）ロータ部の歯形寸法は共通であるも軸部の直径や
軸長が異なるため、部品の共通化ができず製作と管理上
も複雑である。2. Description of the Related Art Conventionally, in this type of screw rotor, a rotor portion and a rotor shaft are integrally formed. For example,
The rotor part and the rotor shaft are machined from the same metal material. Alternatively, there is a rotor in which a synthetic resin rotor is integrally formed around a metal rotor shaft. And, even if the dimensions of the rotor part are common between the models, the discharge pressure and drive motor of the screw fluid machine change, and the shaft length, shaft diameter, or surface treatment of the shaft part vary depending on the intended use of the screw fluid machine. As a result, the manufacturing process of the rotor becomes complicated and there are many types. For this reason, taking the diameter of each part of the screw rotor as an example, which has various problems, the diameter of the rotor tooth part is generally about 3 to 4 times the diameter of the shaft part. Therefore, there are the following problems in production. (1) When the rotor portion and the shaft portion are cut out from the same metal material, a material having a size corresponding to the diameter of the rotor tooth portion is used, and the material is cut to a desired diameter of the shaft portion. It needs to be sharpened. As a result, a large amount of waste occurs in the materials and processing steps. (2) When a rotor made of thermosetting synthetic resin is integrally formed around a metal shaft, a metal material suitable for the diameter of the shaft may be prepared. Since the length is long, it is necessary to take measures such as a run-out countermeasure at the time of processing, and the productivity is reduced. (3) In addition, since the rotor shaft length is long, the mold for the rotor portion is large and expensive, and the workability during molding is poor. Also,
Workability is similarly poor during surface treatment. (4) Used for a water injection compressor or the like that cools and seals the space by injecting water into the compression action space, and when the shaft portion comes into contact with the atmosphere or a fluid containing moisture, it is used for a long time. Rust is generated during this, causing leakage of the shaft sealing portion and abnormal wear of the sliding portion. (5) Although the rotor section has the same tooth profile dimensions, the diameter and the shaft length of the shaft section are different, so that the parts cannot be shared and the production and management are complicated.

【０００３】しかして、スクリュ圧縮機ではあるが、重
量軽減のために中空小径部と中空大径部とに分割して加
工し、各対向端面を摩擦圧接によって接合しよううとす
るものとして、実開昭５７−１０５４１８号公報がある
が、中空軸にしかつその接合も摩擦圧接による接合で上
述の種々の課題を解決せんとするものではない。また、
単に各クランク軸部をスプラインにより結合し、そのス
プライン結合部に弾性体を注入して摩耗を減らし騒音を
も低減しようとするものとして、実開昭５６−４９３１
１号公報がある。さらに、プロペラシヤフトにおいて、
プロペラシヤフトとヨークのいずれか一方に溝を形成
し、この溝に係合する突起を他方に形成したものとし
て、実開平２−７１１０８号公報があり、さらにまた、
特公昭５２−２５５６２号公報のように圧縮機の羽根車
に一体になったスリーブを設け、このスリーブの穴に螺
子が切られ、軸の螺子部が受容されて組立てられるもの
である、しかし、これらのものは、一般的な取付けをい
かに確実にせんとするか等であって、上述の種々の課題
を解決せんとするものではない。In order to reduce the weight of the screw compressor, however, the screw compressor is divided into a small hollow portion and a large hollow portion, and each of the opposed end faces is to be joined by friction welding. Japanese Patent Application Laid-Open No. 57-105418 discloses a method in which the above-mentioned various problems are not solved by using a hollow shaft and joining by friction welding. Also,
Each crankshaft is simply connected by a spline, and an elastic body is injected into the spline connection to reduce wear and reduce noise.
No. 1 publication. Furthermore, in propeller shafts,
Japanese Unexamined Utility Model Publication No. 2-71108 discloses that a groove is formed in one of the propeller shaft and the yoke, and a protrusion that engages with the groove is formed on the other.
As disclosed in Japanese Patent Publication No. 52-25562, an integral sleeve is provided on the impeller of the compressor, a screw is cut in a hole of the sleeve, and a screw portion of the shaft is received and assembled. These are methods for surely securing a general attachment, and do not solve the above-described various problems.

【０００４】[0004]

【発明が解決しようとする課題】そこで、第１又は第２
に、簡単な軸結合を採用することで、軸長の異なる多機
種に同一のロータ部を採用することができ、スクリュロ
ータ材料に無駄があったり、製作加工に多大な工数を要
しているためコスト高となっていたのを解消し、さら
に、軸を分割でき取扱いが容易で、成形用の機械を小型
化し、多機種の内の専用軸の加工のみでよく軸部の加工
を容易にして製作コストを引き下げること。第３に、第
１又は第２のいずれかの課題にくわえて、ロータ部とロ
ータ軸との組み立て間違えの防止を図り、より製作コス
トを低減すること。第４と第５に、第１乃至第３のいず
れかの課題にくわえて、中心軸は合成樹脂により被覆さ
れているため、軸部の防錆対策として、必要な部分だけ
を容易に防錆処理又は表面処理をできるようにしたり、
耐食材料の採用を容易にすること。第６に、第１乃至第
５のいずれかの課題にくわえて、ロータ軸又は中心軸に
凹設した嵌入穴からその反対側の軸端に貫通する通気孔
を穿設したことにより、軸結合がスムーズに嵌入される
のでその挿入作業が楽に、確実にできると共に、凹設部
の運転中と停止中の温度差による空気の流通（呼吸作
用）ができること。第７と第８に、第１乃至第６のいず
れかの課題にくわえて、中心軸に外嵌する側の材料の線
膨張率が内嵌する軸に比べ小さいため、圧縮作用に伴う
伝導熱によって嵌合が締まる方向に作用させ、長期にわ
たり嵌合状態を確実に保持させること。SUMMARY OF THE INVENTION Therefore, the first or second
In addition, by adopting a simple shaft connection, the same rotor part can be used for many models with different shaft lengths, and the screw rotor material is wasted and a lot of man-hours are required for manufacturing and processing. As a result, the cost has been eliminated, the shaft can be divided and handling is easy, the molding machine is downsized, and the machining of the shaft is easy with only the machining of dedicated shafts among many models. To reduce production costs. Thirdly, in addition to the first or second problem, it is intended to prevent a mistake in assembling the rotor portion and the rotor shaft, and to further reduce the manufacturing cost. Fourth and fifthly, in addition to any of the first to third problems, since the central shaft is covered with a synthetic resin, only a necessary portion can be easily rust-proofed as a measure against rust of the shaft. Treatment or surface treatment,
To facilitate the use of corrosion resistant materials. Sixth, in addition to any of the first to fifth problems, by forming a ventilation hole penetrating from a fitting hole recessed in the rotor shaft or the central shaft to a shaft end on the opposite side, shaft coupling is achieved. Is smoothly and securely inserted so that the insertion operation can be performed easily and reliably, and air can flow (respiratory action) due to a temperature difference between the operation of the recessed portion and the stoppage of the recessed portion. Seventh and eighth, in addition to any of the first to sixth problems, since the coefficient of linear expansion of the material externally fitted to the center shaft is smaller than that of the shaft fitted internally, the heat transfer caused by the compression action In the direction in which the fitting is tightened to ensure that the fitting is maintained for a long time.

【０００５】[0005]

【課題を解決するための手段】本発明は上記課題を解決
するために、第１に、スクリュ流体機械のスクリュロー
タにおいて、スクリュ歯形を形成するロータ部と該ロー
タ部の軸心上の少なくとも一方の外端に中心軸を延設
し、該中心軸の外端には段差を設けて小径軸を突設する
と共に、該小径軸に嵌入穴を凹設した別製のロータ軸を
外嵌して軸接合したことを特徴とする。第２に、この軸
接合をスクリュ歯形を形成するロータ部と該ロータ部の
軸心上の少なくとも一方の外端に中心軸を延設し、該中
心軸の外端には嵌入穴を凹設すると共に、該嵌入穴に小
径軸を突設した別製のロータ軸を内嵌して軸接合した軸
接合としてもよい。そして、上述の軸接合手段として
は、穴径を軸径より小さくし、軸を嵌入穴に圧入或いは
焼きバメで接合する。また、穴と軸とにスプライン加工
を施し軸接合したり、穴と軸とに螺子を切り、螺子係合
としてもよい。第３に、第１又は第２のいずれかの技術
手段に加えて、前記ロータ部の中心軸に突設した小径軸
又は凹設した嵌入穴の最始端と最内外端のそれぞれから
ロータ端面までの長さは該ロータ部を挟んで両軸端共に
略同寸法に設定したことを特徴とする。第４に、第１乃
至第３のいずれかの技術手段に加えて、前記ロータ部は
金属製の中心軸の周囲に熱硬化性の合成樹脂製のロータ
を一体成形したものであることを特徴とする。第５に、
第４の技術手段に加えて、前記ロータ部はその中心軸外
周の表面をロータ部と同質の合成樹脂で被覆成形したこ
とを特徴とする。第６に、第１乃至第５のいずれかの技
術手段に加えて、前記ロータ軸の略軸心には、該ロータ
軸又は中心軸に凹設した嵌入穴からその反対側の軸端に
貫通する通気孔を穿設したことを特徴とする。第７に、
第１又は第３乃至第６のいずれかの技術手段に加えて、
ロータ部の中心軸に外嵌接合するロータ軸の材料は、該
中心軸に用いる材料よりも線膨脹係数の小なる性質を有
する金属材料であることを特徴とする。第８に、第２乃
至第６のいずれかの技術手段に加えて、ロータ部の中心
軸に用いる材料は、該中心軸に内嵌接合するロータ軸よ
りも線膨脹係数の小なる性質を有する金属材料であるこ
とを特徴とする。SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, the present invention firstly provides a screw rotor of a screw fluid machine in which at least one of a rotor portion forming a screw tooth profile and at least one on an axis of the rotor portion is provided. A central shaft is extended at the outer end of the shaft, a step is provided at the outer end of the central shaft, a small-diameter shaft is protruded, and a separate rotor shaft having a fitting hole formed in the small-diameter shaft is externally fitted. It is characterized in that it is shaft-joined. Secondly, a central shaft is extended at a rotor portion forming a screw tooth profile and at least one outer end on the axis of the rotor portion, and a fitting hole is formed at the outer end of the central shaft. In addition, a shaft joint may be formed by internally fitting a separately manufactured rotor shaft having a small-diameter shaft protruding from the fitting hole. As the above-mentioned shaft joining means, the hole diameter is made smaller than the shaft diameter, and the shaft is pressed into the fitting hole or joined by shrink fitting. Further, the hole and the shaft may be splined to join the shaft, or the hole and the shaft may be screwed to engage with the screw. Third, in addition to any one of the first and second technical means, from the start end and the innermost and outermost ends of the small-diameter shaft or the recessed insertion hole protruding from the central axis of the rotor portion to the rotor end surface. The length is set to be substantially the same at both shaft ends with the rotor portion interposed therebetween. Fourthly, in addition to any one of the first to third technical means, the rotor portion is obtained by integrally molding a rotor made of a thermosetting synthetic resin around a metal center shaft. And Fifth,
In addition to the fourth technical means, the rotor portion is characterized in that the outer peripheral surface of the center axis is covered with a synthetic resin of the same quality as the rotor portion. Sixth, in addition to any one of the first to fifth technical means, a substantially axial center of the rotor shaft passes through a fitting hole recessed in the rotor shaft or the central shaft to a shaft end on the opposite side. A vent hole is formed. Seventh,
In addition to the first or third to sixth technical means,
The material of the rotor shaft, which is externally fitted to the center shaft of the rotor portion, is a metal material having a smaller linear expansion coefficient than the material used for the center shaft. Eighth, in addition to any one of the second to sixth technical means, the material used for the central shaft of the rotor portion has a property of a smaller linear expansion coefficient than that of the rotor shaft internally fitted to the central shaft. It is a metal material.

【０００６】[0006]

【実施の形態】以下、本発明のスクリュ流体機械につい
て説明するが、便宜上スクリュ流体機械を例にして記載
する。以下、図１乃至図５の実施例に基づいて説明す
る。図１と図２に示すように、スクリュ歯形を形成する
ロータ部１と該ロータ部１の軸心上の少なくとも一方の
外端２に中心軸３を延設し、該中心軸３の外端４には段
差を設けて小径軸５を突設すると共に、該小径軸５に嵌
入穴７を凹設した別製のロータ軸６を外嵌して軸接合し
た。この場合、好ましくはロータ部１の他端２ａにも上
述と同一の中心軸３ａ、小径軸５ａ、別製のロータ軸６
ａ、嵌入穴７ａを同様に設けてある。そして、前記ロー
タ部１の中心軸３、３ａに設けた小径軸５、５ａの最始
端２６、２６ａと最外端２７、２７ａのそれぞれからロ
ータ端面であるロータ部の外端２、２ａまでの長さは該
ロータ部１を挟んで両軸端共に略同寸法に設定してあ
る。図２はスクリュロータの軸接合前の状態を示す断面
図で、図１と同一部位は同一符号を付すことで説明を省
略する。以下本発明ではロータ部とはスクリュ歯形を形
成したロータ歯部をも含む。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, a screw fluid machine according to the present invention will be described. For convenience, a screw fluid machine will be described as an example. Hereinafter, a description will be given based on the embodiment of FIGS. As shown in FIGS. 1 and 2, a center shaft 3 is extended from a rotor portion 1 forming a screw tooth profile and at least one outer end 2 on the axis of the rotor portion 1. A small-diameter shaft 5 protrudes from the step 4 with a step, and another rotor shaft 6 having a fitting hole 7 formed in the small-diameter shaft 5 is externally fitted and shaft-joined. In this case, preferably, the other end 2a of the rotor portion 1 is also provided with the same central shaft 3a, small-diameter shaft 5a, and separate rotor shaft 6 as described above.
a, the fitting hole 7a is similarly provided. Then, from the start ends 26, 26a and the outermost ends 27, 27a of the small diameter shafts 5, 5a provided on the central shafts 3, 3a of the rotor portion 1 to the outer ends 2, 2a of the rotor portion which are the rotor end surfaces. The length is set to be substantially the same on both shaft ends with the rotor portion 1 interposed therebetween. FIG. 2 is a cross-sectional view showing a state before the screw rotor is joined to the shaft, and the same parts as those in FIG. Hereinafter, in the present invention, the rotor portion also includes a rotor tooth portion having a screw tooth shape.

【０００７】また、図３に示すように、上述の軸接合
を、スクリュ歯形を形成するロータ部１ｃと該ロータ部
１ｃの軸心上の少なくとも一方の外端８に中心軸９を延
設し、該中心軸９の外端には嵌入穴１０を凹設すると共
に、該嵌入穴１０に小径軸１２を突設した別製のロータ
軸１１を内嵌した軸接合としてもよい。この場合、好ま
しくはロータ部１ｃの他端８ａにも上述と同一の中心軸
９ａの外端には嵌入穴１０ａを凹設すると共に、別製の
ロータ軸１１ａに小径軸１２ａを突設し、該小径軸１２
ａを前記嵌入穴１０ａに内嵌した軸接合手段が同様にと
られている。この場合、好ましくは、前記ロータ部１ｃ
の中心軸に凹設した嵌入穴１０、１０ａの最始端２８、
２８ａと最内端２９、２９ａのそれぞれからロータ端面
であるロータ部の外端８、８ａまでの長さは該ロータ部
１ｃを挟んで両軸端共に略同寸法に設定してある。そし
て、上述の各実施例の軸接合手段としては、穴径を軸径
より小さくし、軸を嵌入穴に圧入或いは焼きバメで接合
する。また、穴と軸とにスプライン加工を施し軸接合し
たり、穴と軸とに螺子を切り、螺子係合としてもよい。As shown in FIG. 3, the above-mentioned shaft joining is performed by extending a center shaft 9 to a rotor portion 1c forming a screw tooth profile and at least one outer end 8 on the axis of the rotor portion 1c. A shaft joint may be formed in which an insertion hole 10 is recessed at the outer end of the center shaft 9 and another rotor shaft 11 having a small-diameter shaft 12 protruding from the insertion hole 10 is internally fitted. In this case, preferably, the other end 8a of the rotor portion 1c is also provided with a recessed hole 10a at the outer end of the same central shaft 9a as described above, and a small-diameter shaft 12a is protruded from another rotor shaft 11a. The small diameter shaft 12
The shaft joining means in which a is internally fitted into the fitting hole 10a is similarly employed. In this case, preferably, the rotor portion 1c is used.
Of the fitting holes 10, 10a recessed in the central axis of
The length from the innermost end 28a and the innermost ends 29, 29a to the outer ends 8, 8a of the rotor portion, which is the rotor end surface, is set to substantially the same size at both shaft ends with the rotor portion 1c interposed therebetween. As the shaft joining means in each of the above-described embodiments, the hole diameter is made smaller than the shaft diameter, and the shaft is press-fitted into the fitting hole or joined by shrink fitting. Further, the hole and the shaft may be splined to join the shaft, or the hole and the shaft may be screwed to engage with the screw.

【０００８】さらに、図４に示すように、ロータ部１ｄ
は金属製の中心軸１３の周囲に熱硬化性の合成樹脂製の
ロータを一体成形したものである。そして、該ロータ部
１ｄの金属製の中心軸１３上の少なくとも一方の外端３
２に中心軸１５を延設し、該中心軸１５の外端には嵌入
穴１６を凹設すると共に、該嵌入穴１６に小径軸１８を
突設した別製のロータ軸１７を内嵌した第３実施例の軸
接合とした。この形状を、図５に示すように、ロータ部
１ｅの金属製の中心軸１９上の少なくとも一方の外端３
５に周囲に合成樹脂を被覆した中心軸２０を延設し、該
中心軸２０の外端２１には段差を設けて小径軸２２を突
設すると共に、該小径軸２２にはロータ部１ｅとは別製
のロータ軸２３の端部に凹設した嵌入穴２４を外嵌して
第４実施例の軸接合としてもよい。そして、これらの第
３と第４実施例においても、好ましくは各々の他端３２
ａ、３５ａにも各図４、図５と全く同じ構造の軸接合手
段が施されている、その同一符号にａを付すことで説明
を省略する。さらに、この場合も好ましくは、前記ロー
タ部１ｄの各中心軸に凹設した嵌入穴１６、１６ａの最
始端３０、３０ａと最内端３１、３１ａのそれぞれから
ロータ部の外端３２、３２ａまでの長さ並びに前記ロー
タ部１ｅの中心軸に設けた小径軸２２、２２ａの最始端
３３、３３ａと最外端３４、３４ａのそれぞれからロー
タ部の外端３５、３５ａまでの長さは各該ロータ部１
ｄ、１ｅを挟んで両軸端共にそれぞれ略同寸法に設定し
てある。さらに、これらの軸接合手段としては、穴径を
軸径より小さくし、好ましくは嵌入穴を温め（軸を冷却
してもよい）て軸を嵌入穴に圧入するか、上述のように
穴と軸とにスプライン加工を施し軸接合したり、穴と軸
とに螺子を切り、螺子係合としてもよい。さらにまた、
前記ロータ部はその中心軸外周の表面をロータ部と同質
の合成樹脂で被覆成形した技術手段をも採用できる。[0008] Further, as shown in FIG.
Is formed by integrally molding a rotor made of a thermosetting synthetic resin around a central shaft 13 made of metal. Then, at least one outer end 3 on the metal center shaft 13 of the rotor portion 1d.
2, a central shaft 15 is extended, a fitting hole 16 is recessed at the outer end of the central shaft 15, and a separate rotor shaft 17 having a small-diameter shaft 18 protruding from the fitting hole 16 is internally fitted. The shaft was joined in the third embodiment. As shown in FIG. 5, this shape is changed to at least one outer end 3 on the metal center shaft 19 of the rotor portion 1e.
A central shaft 20, which is covered with a synthetic resin, extends around 5, and a small-diameter shaft 22 projects from the outer end 21 of the central shaft 20 with a step. The shaft fitting of the fourth embodiment may be formed by externally fitting a recessed fitting hole 24 at the end of a separate rotor shaft 23. In the third and fourth embodiments, preferably, the other ends 32 are preferably used.
A and 35a are also provided with shaft connecting means having exactly the same structure as in FIGS. 4 and 5, respectively. The description is omitted by attaching a to the same reference numeral. Further, in this case, it is also preferable that the outermost ends 32 and 32a of the rotor part be respectively connected to the start ends 30, 30a and the innermost ends 31 and 31a of the fitting holes 16 and 16a recessed in the respective central axes of the rotor part 1d. And the length from the start end 33, 33a and the outermost end 34, 34a of the small diameter shaft 22, 22a provided on the central axis of the rotor portion 1e to the outer end 35, 35a of the rotor portion, respectively. Rotor part 1
Both ends of the shaft are set to have substantially the same dimensions with respect to d and 1e. Further, as these shaft joining means, the hole diameter is made smaller than the shaft diameter, and preferably, the shaft is press-fitted into the hole by warming the hole (the shaft may be cooled), or as described above. The shaft and the shaft may be splined and joined to each other, or a screw may be cut into the hole and the shaft to engage with the screw. Furthermore,
The rotor section may employ a technical means in which the outer surface of the center shaft is coated with a synthetic resin of the same quality as the rotor section.

【０００９】なお、上述の各第１乃至第４実施例におい
て、軸接合手段としての嵌入穴と小径軸の形状は、円
形、三角形、四角形、多角形等でよく、さらに、中心軸
の一端に嵌入穴を凹設し、他端に小径軸を突設するよう
に異なる形状としてもよい。また、図４に示すように、
ロータ部１ｄの金属製の中心軸１３の延設した周囲は合
成樹脂で被覆されていなく、さらに、図５に示すよう
に、ロータ部１ｅの金属製の中心軸１９の延設した周囲
には合成樹脂を被覆した中心軸２０としているが、使用
条件等によってはロータ部１ｅの金属製の中心軸１９の
延設した周囲を合成樹脂を被覆せずに金属製にしたり、
或いは、ロータ部１ｄの金属製の中心軸１３の延設した
周囲を合成樹脂で被覆してもよい。In each of the first to fourth embodiments described above, the shape of the fitting hole and the small diameter shaft as the shaft joining means may be circular, triangular, quadrangular, polygonal, or the like. The fitting hole may be formed in a concave shape and the other end may be formed in a different shape such that a small diameter shaft protrudes. Also, as shown in FIG.
The extended periphery of the metal center shaft 13 of the rotor portion 1d is not covered with a synthetic resin, and further, as shown in FIG. 5, the extended periphery of the metal center shaft 19 of the rotor portion 1e is Although the central shaft 20 is coated with a synthetic resin, the extended periphery of the metal central shaft 19 of the rotor portion 1e may be made of metal without coating with the synthetic resin, depending on the use conditions and the like.
Alternatively, the extended periphery of the metal center shaft 13 of the rotor portion 1d may be covered with a synthetic resin.

【００１０】さらには、図１乃至図５の各実施例のいず
れのものに加えて、前記ロータ軸６、６ａ、１１、１１
ａ、１７、１７ａ、２３、２３ａの略軸心には、該ロー
タ軸又は中心軸に凹設した各嵌入穴７、７ａ、１０、１
０ａ、１６、１６ａ、２４、２４ａからその反対側の軸
端に貫通する通気孔２５、２５ａ…を穿設した。この場
合略軸心とは、各通気孔２５、２５ａ…は各嵌入穴７、
７ａ、１０、１０ａ、１６、１６ａ、２４、２４ａのい
ずれの部位が外気と連通すればよいので本発明では幾何
学上の軸心でないので略軸心という（製作上センターの
軸心に孔を穿設してもよい）。Further, in addition to any of the embodiments shown in FIGS. 1 to 5, the rotor shafts 6, 6a, 11, 11
a, 17, 17a, 23, and 23a, the respective fitting holes 7, 7a, 10, 1 that are recessed in the rotor shaft or the central shaft are provided in the substantially axial centers thereof.
Vent holes 25, 25a ... penetrating from 0a, 16, 16a, 24, 24a to the shaft ends on the opposite side. In this case, the substantially axial center means that each of the ventilation holes 25, 25a.
7a, 10, 10a, 16, 16a, 24, and 24a, it is only necessary to communicate with the outside air. Therefore, the present invention is not a geometrical axis in the present invention. May be drilled).

【００１１】さらにまた、ロータ部の中心軸に外嵌接合
するロータ軸６、６ａ、２３、２３ａの材料は、該中心
軸に用いる材料よりも線膨脹係数の小なる性質を有する
金属材料である。又は、ロータ部の中心軸に用いる材料
は、該中心軸に内嵌接合するロータ軸１１、１１ａ、１
７、１７ａよりも線膨脹係数の小なる性質を有する金属
材料であるFurther, the material of the rotor shafts 6, 6a, 23, and 23a that are externally fitted to the center shaft of the rotor portion is a metal material having a property of a smaller linear expansion coefficient than the material used for the center shaft. . Alternatively, the material used for the central axis of the rotor portion may be the rotor axes 11, 11a, 1
It is a metal material that has a lower linear expansion coefficient than 7, 17a.

【００１２】次ぎに、動作と主な作用について図６の圧
縮機に基づいて説明すると、ロータ部と別製のロータ軸
とを各実施例の形状及び種々の軸接合手段によって構成
されたものは、図６のように外観上は何等変わらず、そ
のスクリュ流体機械のスクリュロータの機能上も変わら
ない。そこで、本発明による種々の技術手段の作用につ
いて説明する。ロータ部と軸部とを分割構造としたの
で、ロータ部（ロータ歯部も含む）の寸法の共通化が図
れるため、専用の加工機で量産できる一方、軸部は当該
軸部同士で単独加工され、それぞれの完成後両者を焼き
バメ等により嵌合接合し所望のロータにまとめられる。
これにより完成したスクリュロータは加工品質及び性能
共に安定したものとなり、大幅な加工工数の低減と製作
コストの低減とが可能となる。併せて、部品の共通化に
より部品管理も容易となる。また、中心軸は合成樹脂に
より被覆されているため、軸の防錆効果の他、流体機械
の運転中作用室と軸受室との軸封部の僅かな隙間に万一
接触があっても焼き付くことがない。Next, the operation and main function will be described with reference to the compressor shown in FIG. 6. The rotor portion and the separately manufactured rotor shaft are formed by the shape of each embodiment and various shaft connecting means. As shown in FIG. 6, there is no change in appearance, and there is no change in the function of the screw rotor of the screw fluid machine. Therefore, the operation of various technical means according to the present invention will be described. Since the rotor part and the shaft part have a split structure, the dimensions of the rotor part (including the rotor tooth part) can be shared, so mass production can be performed with a dedicated processing machine. After completion of each, the two are fitted and joined by shrink fitting or the like and assembled into a desired rotor.
As a result, the completed screw rotor becomes stable in both processing quality and performance, and it is possible to greatly reduce the number of processing steps and the manufacturing cost. At the same time, component management is facilitated by sharing components. In addition, since the central shaft is covered with a synthetic resin, in addition to the rust-preventing effect of the shaft, even if there is any contact in the slight gap between the working chamber and the bearing chamber during the operation of the fluid machine, even if there is any contact, it is seized. Nothing.

【００１３】さらに、スクリュロータの中心軸とロータ
軸との嵌合時、凹設部に残留する空気はロータ軸に穿設
した通気孔から外部に逃げる。よって、凹設部の運転中
と停止中の温度差による空気の流通（呼吸作用）ができ
接合も確実にできる。さらにまた、中心軸に外嵌する側
の材料の線膨張率が内嵌する軸に比べ小さいため、圧縮
作用に伴う伝導熱によって嵌合が締まる方向に作用す
る。よって長期にわたり嵌合状態を確実に保持できる。
そして、長期の運転期間中にロータ歯部又はロータ軸が
磨耗したときには、オーバホール時等にそれぞれの該当
する部品だけを交換すればよい。Further, when the central shaft of the screw rotor is fitted to the rotor shaft, the air remaining in the recessed portion escapes to the outside through a ventilation hole formed in the rotor shaft. Therefore, the air can flow (respiratory action) due to the temperature difference between the operation of the recessed portion and the stoppage of the recessed portion, and the joining can be reliably performed. Furthermore, since the coefficient of linear expansion of the material that is externally fitted to the center shaft is smaller than that of the shaft that is internally fitted, it acts in the direction in which the fitting is tightened by conduction heat accompanying the compression action. Therefore, the fitted state can be reliably maintained for a long time.
Then, when the rotor tooth portion or the rotor shaft is worn during a long operation period, only the corresponding parts need to be replaced at the time of overhaul or the like.

【００１４】[0014]

【効果】第１又は第２に、スクリュロータのロータ部と
軸部とを分割構造としたので、ロータ部の寸法が同じで
あればロータ部については同一の加工段取りで加工でき
るので、生産性が向上し安定した加工品質を維持でき、
かつ部品管理も容易である。また、簡単な軸結合を採用
することで、軸長の異なる多機種に同一のロータ部を採
用することができ、スクリュロータ材料に無駄をなく
し、製作加工に多大な工数を不要としコスト高となって
いたのを解消し、さらに、軸を分割でき取扱いが容易
で、軸が短くできるため成形用の機械を小型化し、多機
種の内の専用軸の加工のみでよく軸部の加工を容易にし
て製作コストを大幅に引き下げることができた。さら
に、軸部については表面処理その他の複雑な製作工程を
経る過程でも、部品自体がロータ部に比べて小さいため
取扱いも楽で作業性もよい。第３に、第１又は第２のい
ずれかの効果にくわえて、ロータ部とロータ軸との組み
立て間違いの防止ができ、加工部品の共通化を図り、よ
り製作コストを低減することができた。第４と第５に、
第１乃至第３のいずれかの効果にくわえて、中心軸は合
成樹脂により被覆されているため、軸部の防錆対策とし
て、必要な部分だけを容易に防錆処理又は表面処理をで
きるようにしたり、耐食材料の採用が容易である。第６
に、第１乃至第５のいずれかの効果にくわえて、ロータ
軸又は中心軸に凹設した嵌入穴からその反対側の軸端に
貫通する通気孔を穿設したことにより、軸結合がスムー
ズに嵌入されるのでその挿入作業が楽に、確実にできる
と共に、凹設部の運転中と停止中の温度差による空気の
流通（呼吸作用）ができる。第７と第８に、第１乃至第
６のいずれかの効果にくわえて、中心軸に外嵌する側の
材料の線膨張率が内嵌する軸に比べ小さいため、圧縮作
用に伴う伝導熱によって嵌合が締まる方向に作用させ、
長期にわたり嵌合状態を確実に保持させれる。First and secondly, since the rotor part and the shaft part of the screw rotor are divided, if the dimensions of the rotor part are the same, the rotor part can be processed by the same processing setup, so that the productivity is improved. And maintain stable machining quality.
Also, parts management is easy. In addition, by adopting simple shaft coupling, the same rotor part can be adopted for many models with different shaft lengths, eliminating waste of screw rotor material, eliminating the need for a large number of man-hours in manufacturing and processing, and increasing cost. In addition, the shaft can be divided and the handling is easy, and the shaft can be shortened, so the molding machine can be downsized. As a result, the production cost was significantly reduced. Further, even in the process of going through the surface treatment and other complicated manufacturing steps, the shaft itself is easy to handle and easy to work because the parts themselves are smaller than the rotor. Third, in addition to the effects of either the first or the second, it is possible to prevent an erroneous assembly of the rotor part and the rotor shaft, to achieve a common working part, and to further reduce the manufacturing cost. . Fourth and fifth,
In addition to any of the first to third effects, since the central shaft is covered with a synthetic resin, only a necessary portion can be easily subjected to rust-proofing or surface treatment as a measure for preventing rust of the shaft. And it is easy to adopt a corrosion-resistant material. Sixth
In addition to the effect of any one of the first to fifth aspects, a ventilation hole penetrating from a fitting hole formed in the rotor shaft or the central shaft to a shaft end on the opposite side is formed, so that shaft coupling is smooth. As a result, the insertion work can be performed easily and reliably, and air can flow (respiratory action) due to the temperature difference between the operation of the concave portion and the stop of the concave portion. Seventh and eighth, in addition to the effect of any one of the first to sixth aspects, since the coefficient of linear expansion of the material externally fitted to the central shaft is smaller than that of the shaft fitted internally, the heat transfer caused by the compression action Act in the direction in which the fitting is tightened,
The fitting state can be reliably maintained for a long time.

【図面の簡単な説明】[Brief description of the drawings]

【図１】本発明によるスクリュロータの第１実施例を示
す断面図である。FIG. 1 is a sectional view showing a first embodiment of a screw rotor according to the present invention.

【図２】本発明による第１実施例のスクリュロータの軸
接合前の状態を示す断面図である。FIG. 2 is a cross-sectional view showing a state before screw joining of the screw rotor of the first embodiment according to the present invention.

【図３】本発明によるスクリュロータの第２実施例を示
す断面図である。FIG. 3 is a sectional view showing a second embodiment of the screw rotor according to the present invention.

【図４】本発明によるスクリュロータの第３実施例を示
す断面図である。FIG. 4 is a sectional view showing a third embodiment of the screw rotor according to the present invention.

【図５】本発明によるスクリュロータの第４実施例を示
す断面図である。FIG. 5 is a sectional view showing a fourth embodiment of the screw rotor according to the present invention.

【図６】スクリュロータの圧縮機を示す要部概略断面図
である。FIG. 6 is a schematic sectional view of a main part showing a compressor of the screw rotor.

【符号の説明】[Explanation of symbols]

１、１ｂ乃至１ｅ
ロータ部 ２、２ａ、８、８ａ、３２、３２ａ、３５、３５ａ
ロータ部の外端 ３、３ａ、９、９ａ、１５、１５ａ、２０、２０ａ
中心軸 ４、４ａ、２１、２１ａ
中心軸の外端 ５、５ａ、１２、１２ａ、１８、１８ａ、２２、２２ａ
小径部 ６、６ａ、１１、１１ａ、１７、１７ａ、２３、２３ａ
ロータ軸 ７、７ａ、１０、１０ａ、１６、１６ａ、２４、２４ａ
嵌入部 １３、１９
金属製の中心軸 ２５、２５ａ
通気孔1, 1b to 1e
Rotor part 2, 2a, 8, 8a, 32, 32a, 35, 35a
Outer end of rotor part 3, 3a, 9, 9a, 15, 15a, 20, 20a
Central axis 4, 4a, 21, 21a
Outer end of central axis 5, 5a, 12, 12a, 18, 18a, 22, 22a
Small diameter part 6, 6a, 11, 11a, 17, 17a, 23, 23a
Rotor shaft 7, 7a, 10, 10a, 16, 16a, 24, 24a
Fitting parts 13, 19
Metal center shaft 25, 25a
Vent

Claims (8)

【特許請求の範囲】[Claims] 【請求項１】スクリュ流体機械のスクリュロータにおい
て、スクリュ歯形を形成するロータ部と該ロータ部の軸
心上の少なくとも一方の外端に中心軸を延設し、該中心
軸の外端には段差を設けて小径軸を突設すると共に、該
小径軸に嵌入穴を凹設した別製のロータ軸を外嵌して軸
接合したことを特徴とするスクリュロータ。1. A screw rotor for a screw fluid machine, wherein a central axis is extended to a rotor part forming a screw tooth profile and at least one outer end on an axis of the rotor part, and an outer end of the central shaft is A screw rotor characterized in that a small-diameter shaft is protruded by providing a step, and a separately manufactured rotor shaft having a fitting hole formed in the small-diameter shaft is externally fitted and shaft-joined. 【請求項２】スクリュ流体機械のスクリュロータにおい
て、スクリュ歯形を形成するロータ部と該ロータ部の軸
心上の少なくとも一方の外端に中心軸を延設し、該中心
軸の外端には嵌入穴を凹設すると共に、該嵌入穴に小径
軸を突設した別製のロータ軸を内嵌して軸接合したこと
を特徴とするスクリュロータ。2. A screw rotor of a screw fluid machine, wherein a central axis is extended to a rotor portion forming a screw tooth profile and at least one outer end on an axis of the rotor portion, and an outer end of the central shaft is A screw rotor in which a fitting hole is formed in a recess, and another rotor shaft having a small-diameter shaft protruding from the fitting hole is internally fitted and axially joined. 【請求項３】前記ロータ部の中心軸から突設した小径軸
又は凹設した嵌入穴の最始端と最内外端のそれぞれから
ロータ端面までの長さは該ロータ部を挟んで両軸端共に
略同寸法に設定したことを特徴とする請求項１又は請求
項２に記載のスクリュロータ。3. The length from the start end and the innermost and outermost ends of the small-diameter shaft or the recessed fitting hole protruding from the center axis of the rotor portion to the rotor end face is the same for both shaft ends with the rotor portion interposed therebetween. The screw rotor according to claim 1, wherein the screw rotor has substantially the same dimensions. 【請求項４】前記ロータ部は金属製の中心軸の周囲に熱
硬化性の合成樹脂製のロータを一体成形したものである
ことを特徴とする請求項１乃至請求項３のいずれか１項
に記載のスクリュロータ。4. The rotor according to claim 1, wherein a rotor made of a thermosetting synthetic resin is integrally formed around a metal central shaft. The screw rotor according to 1. 【請求項５】前記ロータ部はその中心軸外周の表面をロ
ータ部と同質の合成樹脂で被覆成形したことを特徴とす
る請求項４に記載のスクリュロータ。5. The screw rotor according to claim 4, wherein said rotor portion is formed by coating the outer surface of the center shaft with a synthetic resin of the same quality as the rotor portion. 【請求項６】前記ロータ軸の略軸心には、該ロータ軸又
は中心軸に凹設した嵌入穴からその反対側の軸端に貫通
する通気孔を穿設したことを特徴とする請求項１乃至請
求項５のいずれか１項に記載のスクリュロータ。6. A vent hole penetrating from a fitting hole recessed in the rotor shaft or the central shaft to a shaft end on the opposite side from the substantially central axis of the rotor shaft. The screw rotor according to any one of claims 1 to 5. 【請求項７】ロータ部の中心軸に外嵌接合するロータ軸
の材料は、該中心軸に用いる材料よりも線膨脹係数の小
なる性質を有する金属材料であることを特徴とする請求
項１又は請求項３乃至請求項６のいずれか１項に記載の
スクリュロータ。7. The material of the rotor shaft, which is externally fitted to the center shaft of the rotor portion, is a metal material having a smaller linear expansion coefficient than the material used for the center shaft. Or the screw rotor according to any one of claims 3 to 6. 【請求項８】ロータ部の中心軸に用いる材料は、該中心
軸に内嵌接合するロータ軸よりも線膨脹係数の小なる性
質を有する金属材料であることを特徴とする請求項２乃
至請求項６のいずれか１項に記載のスクリュロータ。8. The material used for the central axis of the rotor portion is a metal material having a smaller linear expansion coefficient than that of the rotor axis which is internally fitted to the central axis. Item 7. The screw rotor according to any one of Items 6.
JP27678196A 1996-03-27 1996-09-12 Screw rotor Expired - Fee Related JP3803812B2 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP27678196A JP3803812B2 (en) 1996-09-12 1996-09-12 Screw rotor
CN97102933A CN1112515C (en) 1996-03-27 1997-03-04 Shaft structure of screw rotor for screw fluid machinery

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP27678196A JP3803812B2 (en) 1996-09-12 1996-09-12 Screw rotor

Publications (2)

Publication Number Publication Date
JPH1089270A true JPH1089270A (en) 1998-04-07
JP3803812B2 JP3803812B2 (en) 2006-08-02

Family

ID=17574284

Family Applications (1)

Application Number Title Priority Date Filing Date
JP27678196A Expired - Fee Related JP3803812B2 (en) 1996-03-27 1996-09-12 Screw rotor

Country Status (1)

Country Link
JP (1) JP3803812B2 (en)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011157921A (en) * 2010-02-03 2011-08-18 Mitsubishi Electric Corp Two-cylinder rotary compressor
CN102195415A (en) * 2010-03-19 2011-09-21 上海电气集团上海电机厂有限公司 Sleeving method of coupler
US8512019B2 (en) 2008-06-13 2013-08-20 Kobe Steel, Ltd. Screw compression apparatus
CN111749897A (en) * 2019-03-29 2020-10-09 株式会社丰田自动织机 Coupling structure of shaft member and fluid machine

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8512019B2 (en) 2008-06-13 2013-08-20 Kobe Steel, Ltd. Screw compression apparatus
JP2011157921A (en) * 2010-02-03 2011-08-18 Mitsubishi Electric Corp Two-cylinder rotary compressor
CN102195415A (en) * 2010-03-19 2011-09-21 上海电气集团上海电机厂有限公司 Sleeving method of coupler
CN111749897A (en) * 2019-03-29 2020-10-09 株式会社丰田自动织机 Coupling structure of shaft member and fluid machine
CN111749897B (en) * 2019-03-29 2022-05-24 株式会社丰田自动织机 Coupling structure of shaft member and fluid machine

Also Published As

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