JP2008298287A - Fixing system for rotor of rotating fluid machine - Google Patents

Fixing system for rotor of rotating fluid machine Download PDF

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JP2008298287A
JP2008298287A JP2008138811A JP2008138811A JP2008298287A JP 2008298287 A JP2008298287 A JP 2008298287A JP 2008138811 A JP2008138811 A JP 2008138811A JP 2008138811 A JP2008138811 A JP 2008138811A JP 2008298287 A JP2008298287 A JP 2008298287A
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rotor
shaft
shank
diameter
fluid machine
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JP5620633B2 (en
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Massimo Pinzauti
マッシモ・ピンザウティ
Massimo Camatti
マッシモ・カマッティ
Giampaolo Bertoni
ジァンパオロ・バートーニ
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Nuovo Pignone SpA
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/266—Rotors specially for elastic fluids mounting compressor rotors on shafts

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  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a fixing system between a rotor and a rotating shaft of a centrifugal compressor. <P>SOLUTION: In the fixing system, The rotor 18 has a profile which comprises a nearly concave first front surface 24 and a nearly convex second rear surface 26 opposite to the first front surface 24. The rotor 18 also has a central portion 28 restrained by interference fitting on a rotating shaft 14 of a rotating fluid machine (a centrifugal compressor), and equipped with a shank 30 connected with the second rear surface 26. In that case, the system comprises at least one check ring 32 assembled by interference fitting on the shank 30 of the rotor 18. The check ring 32 has a first internal circumferential surface 34 coupled by interference fitting with the shank 30, and a second internal circumferential surface 36 coupled by interference fitting with the shaft 14 to increase torque which can be transmitted from the shaft 14 to the rotor 18. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

本発明は、回転流体機械のロータ用の固定システムに関し、より具体的には、遠心型圧縮機のロータと回転シャフトとの間の固定システムに関する。   The present invention relates to a fixing system for a rotor of a rotating fluid machine, and more particularly to a fixing system between a rotor and a rotating shaft of a centrifugal compressor.

圧縮機が機械的エネルギーを用いて圧縮性流体（ガス）の圧力を上昇させることができる機械であることは、知られている。産業用プロセスプラントで用いられる様々なタイプの圧縮機の中で、一般的にドライバ（電気モータ又は蒸気タービン）によって駆動されるロータ又はタービンホイールと呼ばれる機関の回転による遠心加速の形態でエネルギーがガスに供給されるいわゆる遠心圧縮機について言及することができる。   It is known that a compressor is a machine that can use mechanical energy to increase the pressure of a compressible fluid (gas). Among the various types of compressors used in industrial process plants, energy is typically gas in the form of centrifugal acceleration by the rotation of an engine called a rotor or turbine wheel driven by a driver (electric motor or steam turbine). Mention may be made of so-called centrifugal compressors supplied to the plant.

遠心圧縮機には、いわゆる単相構成としての単一のロータ、又は多相圧縮機と呼ばれる直列配置の幾つかのロータを設けることができる。より具体的には、遠心圧縮機の各相は通常、加圧対象ガスのための吸入ダクトと、ガスに運動エネルギーを与えることができるロータと、その機能はロータから出るガスの運動エネルギーを圧力エネルギーに変換することであるディフューザとから構成される。   Centrifugal compressors can be provided with a single rotor in a so-called single-phase configuration or several rotors in series, called a multi-phase compressor. More specifically, each phase of a centrifugal compressor typically has a suction duct for the gas to be pressurized, a rotor capable of imparting kinetic energy to the gas, and its function pressures the kinetic energy of the gas exiting the rotor. It consists of a diffuser that is to convert energy.

遠心圧縮機のロータは一般的に、ディスクの形態であり、その中心部分には様々な数のベーンを支持することができるハブが配置される。ハブには、通常楔留めすることによって遠心圧縮機の回転シャフトに対してロータを拘束することを可能にする中心貫通孔が設けられる。   Centrifugal compressor rotors are generally in the form of discs, at the center of which are arranged hubs capable of supporting various numbers of vanes. The hub is provided with a central through hole that allows the rotor to be constrained relative to the rotary shaft of the centrifugal compressor, usually by wedge fastening.

公知のタイプのロータにおいて、特に特定の流体で作動することができるように鋼鉄ではなく軽金属合金（例えば、アルミニウム）で該ロータを製造した場合に発生する問題の１つは、圧縮機の作動時にシャフトとの間の十分な締まり嵌めを維持することである。事実、機械の作動時に１つ又は複数のロータとシャフトとの間に適切な締まり嵌めを維持することは、ロータの平衡状態を維持しかつロータ自体の仕事エネルギーに必要なトルクをシャフトからロータに伝達するための必要条件である。この第２の態様は、シャフトの上に嵌合取付けしたロータにとって中でも特に重大である。事実、特にアルミニウム合金で製造した場合における熱膨張及びまた遠心力の影響によるロータハブの半径方向膨張は、鋼鉄で製造された同様の最終製品に対して極めて大きくなり、その結果、締まり嵌めの全体的又は部分的喪失を促進し、いずれにしてもトルクの伝達を不十分なものにする。   In known types of rotors, one of the problems that arises when the rotor is made of a light metal alloy (eg, aluminum) rather than steel so that it can operate with a particular fluid is that during compressor operation. Maintaining a good interference fit with the shaft. In fact, maintaining a proper interference fit between one or more rotors and the shaft during machine operation maintains the balance of the rotor and the torque required for the work energy of the rotor itself from the shaft to the rotor. It is a necessary condition for transmission. This second aspect is particularly critical for a rotor fitted on a shaft. In fact, the radial expansion of the rotor hub due to the effects of thermal expansion and / or centrifugal forces, especially when manufactured from aluminum alloys, is very large for similar end products manufactured from steel, resulting in an overall interference fit. Or it promotes partial loss and in any case makes the transmission of torque insufficient.

具体的には、軽量アルミニウム合金で製造したロータは、それらアルミニウム合金がロータハブ−シャフト間の低い特異的接触圧力を引き起こす低い弾性率とロータの作動時に大部分の締まり嵌めの喪失を引き起こす高い熱膨張率とを有するので、単純にはシャフト上に嵌合取付けすることができない。現時点では、アルミニウムで製造したロータの唯一の公知の用途は、シャフトのヘッド上への、すなわちセンタリングシステム及びトルク伝達が極めて容易である圧縮機シャフトの端部でのそれらの嵌合取付けを想定している。   Specifically, rotors made of lightweight aluminum alloys have low elastic modulus that causes low specific contact pressure between the rotor hub and shaft, and high thermal expansion that causes loss of most interference fits during rotor operation. Simply cannot fit onto the shaft. At present, the only known applications of rotors made of aluminum envisage their fitting mounting on the shaft head, ie at the end of the compressor shaft where the torque transmission is very easy. ing.

従って、本発明の目的は、回転流体機械のロータ用の固定システム、より具体的には特にアルミニウム合金で製造したロータを用いる場合にシャフトとロータとの間の締まり嵌めによる力の伝達を保証するのに適した遠心型圧縮機のロータと回転シャフトとの間の固定システムを提供することによって、公知の技術によるロータに関する問題を解決することである。   Accordingly, it is an object of the present invention to ensure the transmission of force by an interference fit between a shaft and a rotor when using a fixing system for a rotor of a rotating fluid machine, more particularly when using a rotor made of aluminum alloy. To solve the problems associated with known art rotors by providing a fixing system between the rotor and rotating shaft of the centrifugal compressor suitable for the above.

本発明の別の目的は、アルミニウム合金で製造したロータの組立体が多相型圧縮機のシャフトの端部の１つに対応するだけでなくそのシャフトに沿っても適切なセンタリング及びトルク伝達を保証するのを可能にする、回転流体機械のロータ用の固定システムを提供することである。   Another object of the present invention is that a rotor assembly made of an aluminum alloy not only corresponds to one of the ends of the shaft of a multiphase compressor, but also provides proper centering and torque transmission along that shaft. It is to provide a fixing system for the rotor of a rotating fluid machine that makes it possible to guarantee.

本発明によるこれら目的は、請求項１に特定したような回転流体機械のロータ用の固定システムを提供することによって達成される。   These objects according to the invention are achieved by providing a fixing system for the rotor of a rotating fluid machine as specified in claim 1.

本発明の更なる詳細は、後続の請求項に示いている。   Further details of the invention are given in the subsequent claims.

本発明による回転流体機械のロータ用の固定システムの特徴及び利点は、添付の概略的な図面を参照しての以下の例示的なかつ非限定的な説明から一層明らかになるであろう。   The features and advantages of a locking system for a rotor of a rotating fluid machine according to the present invention will become more apparent from the following exemplary and non-limiting description with reference to the accompanying schematic drawings.

特に図１を参照すると、この図は、その全体を参照符号１０で表した一般的多相型遠心圧縮機を示している。圧縮機１０は、その中にシャフト１４が回転可能に組立てられたケーシング又はステータ１２を含み、シャフト１４は、一連の支持軸受１６上に載置される。一連のロータ１８は、シャフト１４上に嵌合取付けされ、次にロータの各々には、ほぼ半径方向の展開部を有する一連の円周方向ベーン２０が設けられる。チャネル又はダイヤフラム２２がケーシング１２上に配置され、これらチャネル又はダイヤフラム２２は、圧縮性流体（ガス）を第１の相に向かってまたこの第１の相から後続の層に送って、次に圧縮機１０から圧力下で吐出するのを可能にする。   With particular reference to FIG. 1, this figure shows a typical multiphase centrifugal compressor, generally designated 10. The compressor 10 includes a casing or stator 12 in which a shaft 14 is rotatably assembled, and the shaft 14 rests on a series of support bearings 16. A series of rotors 18 are fitted over the shaft 14 and each of the rotors is then provided with a series of circumferential vanes 20 having a generally radial deployment. Channels or diaphragms 22 are disposed on the casing 12, and these channels or diaphragms 22 send compressive fluid (gas) towards the first phase and from this first phase to subsequent layers and then compressed. Allows discharge from the machine 10 under pressure.

図２を参照すると、この図は、好ましくはアルミニウム合金で製造され、かつより一般には鋼鉄ロータで発生するものと同じようにシャフト１４上に締まり嵌めで組立てられた単一のロータ１８の断面図である。   Referring to FIG. 2, this is a cross-sectional view of a single rotor 18 that is preferably made of an aluminum alloy and more commonly assembled with an interference fit on the shaft 14 as occurs with a steel rotor. It is.

ロータ１８は、ほぼ凹面形の第１の前面２４及び第１の前面２４に対向するほぼ凸面形の第２の後面２６を含む輪郭を有する。   The rotor 18 has a contour that includes a first surface 24 that is generally concave and a second rear surface 26 that is generally convex opposite the first front surface 24.

一般に「ハブ」と呼ばれ、圧縮機１０のシャフト１４に対して締まり嵌めで拘束されるように構成されたロータ１８の中心部分２８には、適当な長さを有しかつロータ１８自体の後面２６に連結されたシャンク３０が設けられる。   A central portion 28 of the rotor 18, generally referred to as a “hub” and configured to be constrained with an interference fit with respect to the shaft 14 of the compressor 10, has a suitable length and the rear surface of the rotor 18 itself. A shank 30 connected to 26 is provided.

本発明によると、異なる直径を備えた２つの別個の内周面３４及び３６を有するチェックリング３２が、ロータ１８のシャンク３０上に締まり嵌めによって組立てられる。より大きい直径を有する第１の周面３４は、シャンク３０の外径Ｄｅ（図３）と締まり嵌めで結合され、一方、小さい直径を有する第２の周面３６は、シャフト１４上に締まり嵌めで直接結合される。このようにして、圧縮機１０の作動時にシャンク３０の外径とチェックリング３２との間に発生する締まり嵌めの増強を得ることができる。 In accordance with the present invention, a check ring 32 having two separate inner peripheral surfaces 34 and 36 with different diameters is assembled on the shank 30 of the rotor 18 by an interference fit. A first peripheral surface 34 having a larger diameter is coupled with an outer diameter De (FIG. 3) of the shank 30 with an interference fit, while a second peripheral surface 36 having a smaller diameter is tightened on the shaft 14. Directly coupled with a fit. In this way, it is possible to obtain an increase in the interference fit generated between the outer diameter of the shank 30 and the check ring 32 when the compressor 10 is operated.

部品間の締まり嵌めを増大させかつシャフト１４から各ロータ１８へのトルクの伝達率を高めるために、図２に示すように、シャフト１４の外面とチェックリング３２の第２の内面３６との間に、１つ又はそれ以上のキー３８を挿入するのが好ましい。   In order to increase the interference fit between the parts and increase the transmission rate of torque from the shaft 14 to each rotor 18, as shown in FIG. 2, between the outer surface of the shaft 14 and the second inner surface 36 of the check ring 32. Preferably, one or more keys 38 are inserted.

シャフト１４からロータ１８に伝達することができるトルクをさらに増大させるために、ロータ１８の前面側上にもすなわちロータ１８自体のアイ４０に対応させても、チェックリング３２を適用することができる。   In order to further increase the torque that can be transmitted from the shaft 14 to the rotor 18, the check ring 32 can also be applied on the front side of the rotor 18, ie corresponding to the eye 40 of the rotor 18 itself.

圧縮機１０の効率に関するテスト及び制御に基づいて、シャンク３０の外径Ｄｅとの間のシャフト１４の直径Ｄの比率は基本となるものであり、またチェックリング３２の外径Ｄａとの間のシャフト１４の直径Ｄの比率並びにそれぞれシャンク３０の有効長さと第２の表面３６の長さすなわちチェックリング３２の有効長さとを表すシャフト１４の軸方向に沿って測定した長さＬｃとＬａ（図３参照）との間のシャフト１４の直径Ｄの比率もまた基本となるものであることが判った。 Based on the test and control for the efficiency of the compressor 10, the ratio of the diameter D of the shaft 14 between the outer diameter D e of the shank 30 are those underlying, also the outer diameter D a of the check ring 32 The ratio of the diameter D of the shaft 14 between them and the length L c measured along the axial direction of the shaft 14 representing the effective length of the shank 30 and the length of the second surface 36, ie the effective length of the check ring 32, respectively. It has been found that the ratio of the diameter D of the shaft 14 to L a (see FIG. 3) is also fundamental.

寸法、張力及び効率間の良好な妥協点は、シャフト１４の直径Ｄに関する以下の比率で得られた。
Ｄｅ／Ｄ＝１．１０〜１．２５
Ｄａ／Ｄ＝１．４０〜１．６０
Ｌｃ／Ｄ＝０．２５〜０．３５
Ｌａ／D＝０．４０〜０．７０
図２及び図３に示すように、チェックリング３２は、軸方向の障害すなわち言い換えると多相圧縮機１０のロータ１８のピッチに関係するように、その長さがロータ１８のシャンク３０に加えてシャフト１４の軸方向に延びているので、チェックリング３２自体には、ダイヤフラム２２に対応するような適当な形状になったその外面の一部分４２を設けて、相間ラビリンスシールの直径を増大させることができる。 A good compromise between size, tension and efficiency was obtained with the following ratio for the diameter D of the shaft 14.
D e /D=1.10 to 1.25
D a /D=1.40 to 1.60
L c /D=0.25~0.35
L a /D=0.40-0.70
As shown in FIGS. 2 and 3, the check ring 32 has a length in addition to the shank 30 of the rotor 18 so as to relate to the axial obstruction, in other words, the pitch of the rotor 18 of the multiphase compressor 10. Because it extends in the axial direction of the shaft 14, the check ring 32 itself may be provided with a portion 42 of its outer surface that is appropriately shaped to accommodate the diaphragm 22 to increase the diameter of the interphase labyrinth seal. it can.

従って、本発明による回転流体機械のロータ用の、特に遠心型圧縮機のロータと回転シャフトとの間の固定システムは、前に記載した目的を達成することを理解することができる。事実、本システムによると、たとえロータが軽金属合金（アルミニウム合金）で製造されている場合であっても、シャフトからロータに必要なトルクを伝達することが可能になり、また機械のシャフト上におけるロータのセンタリングを維持して、圧縮機の作動時にロータの不均衡を誘発する危険性を除去する。   It can therefore be seen that the fixing system for the rotor of a rotary fluid machine according to the invention, in particular between the rotor of a centrifugal compressor and the rotary shaft, achieves the previously described object. In fact, according to the present system, even if the rotor is made of a light metal alloy (aluminum alloy), it is possible to transmit the necessary torque from the shaft to the rotor, and the rotor on the shaft of the machine. Is maintained to eliminate the risk of inducing rotor imbalance during compressor operation.

このように着想した本発明の回転流体機械のロータ用の固定システムは、とにかく全て同じ発明概念に含まれる多数の修正及び変更を行うことができ、さらに細部全ては、技術的に均等な要素によって置き換えることができる。実際には、使用する材料、また同様に形状及び寸法は、技術的要求により変更することができる。   The inventive locking system for a rotor of a rotating fluid machine of the present invention can make any number of modifications and changes all included in the same inventive concept anyway, and all the details are determined by technically equivalent elements. Can be replaced. In practice, the materials used, as well as the shape and dimensions, can be changed according to technical requirements.

従って、本発明の保護範囲は、提出した特許請求の範囲によって定まる。   Accordingly, the scope of protection of the present invention is determined by the appended claims.

２つの支持軸受間でシャフトの上に嵌合取付けした一連のロータを備えた一般的な多相遠心圧縮機の部分断面図。1 is a partial cross-sectional view of a typical multiphase centrifugal compressor having a series of rotors fitted and mounted on a shaft between two support bearings. 本発明による回転流体機械のロータ用の固定システムの概略断面図。1 is a schematic cross-sectional view of a fixing system for a rotor of a rotary fluid machine according to the present invention. 幾つかの基本的大きさを示す、本発明による回転流体機械のロータ用の固定システムの別の概略断面図。FIG. 4 is another schematic cross-sectional view of a fixing system for a rotor of a rotating fluid machine according to the present invention showing several basic dimensions.

符号の説明Explanation of symbols

１０ 圧縮機
１２ ケーシング又はステータ
１４ シャフト
１６ 支持軸受
１８ ロータ
２０ 円周方向ベーン
２２ チャネル又はダイヤフラム
２４ 第１の前面
２６ 第２の後面
２８ 中心部分
３０ シャンク
３２ チェックリング
３４ 第１の内周面
３６ 第２の内周面
３８ キー
４０ アイ
４２ 外面の一部分
Ｄ シャフトの直径
Ｄａ チェックリングの外径
Ｄｅ 外径
Ｌａ チェックリングの有効長さ
Ｌｃ シャンクの有効長さ DESCRIPTION OF SYMBOLS 10 Compressor 12 Casing or stator 14 Shaft 16 Support bearing 18 Rotor 20 Circumferential vane 22 Channel or diaphragm 24 1st front surface 26 2nd rear surface 28 Center part 30 Shank 32 Check ring 34 1st inner peripheral surface 36 1st 2 Inner peripheral surface 38 Key 40 Eye 42 Part of outer surface D Shaft diameter D a Outer diameter of check ring De Outer diameter L a Effective length of check ring L c Effective length of shank

Claims (8)

ロータ（１８）が、ほぼ凹面形の第１の前面（２４）及び前記第１の前面（２４）に対向するほぼ凸面形の第２の後面（２６）を含む輪郭と、回転流体機械（１０）の回転シャフト（１４）上に締まり嵌めで拘束されかつ該ロータ（１８）の第２の後面（２６）と連結されたシャンク（３０）を備えるように構成された該ロータ（１８）の中心部分（２８）とを有する、該回転流体機械（１０）のロータ（１８）用の固定システムであって
前記ロータ（１８）のシャンク（３０）上に締まり嵌めによって組立てられた少なくとも１つのチェックリング（３２）を含み、
前記チェックリング（３２）が、前記シャンク（３０）に締まり嵌めで結合された第１の内周面（３４）と前記シャフト（１４）に締まり嵌めで結合された第２の内周面（３６）とを有し、前記シャフト（１４）から前記ロータ（１８）に伝達することができるトルクを増大させる、
ことを特徴とするシステム。 A rotor (18) having a generally concave first front surface (24) and a generally convex second rear surface (26) opposite the first front surface (24); and a rotating fluid machine (10 The center of the rotor (18) configured to include a shank (30) constrained with an interference fit on the rotating shaft (14) and coupled to the second rear surface (26) of the rotor (18). A locking system for a rotor (18) of the rotating fluid machine (10) having a portion (28) and assembled by an interference fit on a shank (30) of the rotor (18) (32)
The check ring (32) has a first inner peripheral surface (34) coupled to the shank (30) with an interference fit and a second inner peripheral surface (36) coupled to the shaft (14) with an interference fit. And increase the torque that can be transmitted from the shaft (14) to the rotor (18).
A system characterized by that. 前記第１の内周面（３４）が、前記第２の内周面（３６）に対して、より大きい直径を有することを特徴とする、請求項１記載のシステム。   The system according to claim 1, characterized in that the first inner peripheral surface (34) has a larger diameter than the second inner peripheral surface (36). 前記シャフト（１４）の外面と前記チェックリング（３２）の第２の内周面（３６）との間に、１つ又は複数のキー（３８）が挿入されて、部品間の締まり嵌めを増大させかつ前記シャフト（１４）から前記ロータ（１８）へのトルクの伝達率を高めることを特徴とする、請求項２記載のシステム。   One or more keys (38) are inserted between the outer surface of the shaft (14) and the second inner peripheral surface (36) of the check ring (32) to increase the interference fit between the parts. The system according to claim 2, characterized in that the transmission rate of torque from the shaft (14) to the rotor (18) is increased. 前記シャンク（３０）の外径（Ｄｅ）と前記シャフト（１４）の直径（Ｄ）との間の比率が、１．１０〜１．２５の範囲内にあることを特徴とする、請求項１又は請求項２記載のシステム。 The ratio between the outer diameter (D e ) of the shank (30) and the diameter (D) of the shaft (14) is in the range of 1.10 to 1.25. The system according to claim 1 or 2. 前記チェックリング（３２）の外径（Ｄａ）と前記シャフト（１４）の直径（Ｄ）との間の比率が、１．４０〜１．６０の範囲内にあることを特徴とする、請求項１又は請求項２記載のシステム。 The ratio between the outer diameter (D a ) of the check ring (32) and the diameter (D) of the shaft (14) is in the range of 1.40 to 1.60. The system according to claim 1 or claim 2. 前記シャフト（１４）の軸方向に沿って測定した前記シャンク（３０）の長さ（Ｌｃ）と該シャフト（１４）の直径（Ｄ）との間の比率が、０．２５〜０．３５の範囲内にあることを特徴とする、請求項１又は請求項２記載のシステム。 The ratio between the length (L c ) of the shank (30) measured along the axial direction of the shaft (14) and the diameter (D) of the shaft (14) is 0.25 to 0.35. The system according to claim 1 or 2, characterized in that it is within the range. 前記シャフト（１４）の軸方向に沿って測定した前記第２の内周面（３６）の長さ（Ｌａ）と該シャフト（１４）の直径（Ｄ）との間の比率が、０．４０〜０．７０の範囲内にあることを特徴とする、請求項１又は請求項２記載のシステム。 The ratio between the length (L a ) of the second inner peripheral surface (36) measured along the axial direction of the shaft (14) and the diameter (D) of the shaft (14) is 0. The system according to claim 1 or 2, characterized in that it is in the range of 40 to 0.70. 前記請求項のいずれかによるロータ（１８）用の固定システムを含むことを特徴とする、回転流体機械（１０）。   Rotary fluid machine (10), characterized in that it comprises a fixing system for a rotor (18) according to any of the preceding claims.
JP2008138811A 2007-05-30 2008-05-28 Fixing system for rotor and rotating fluid machine including the system Expired - Fee Related JP5620633B2 (en)

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