JP2005054738A - Lubricating oil feeding device and double structure rotary shaft for high-speed rotary machine - Google Patents

Lubricating oil feeding device and double structure rotary shaft for high-speed rotary machine Download PDF

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JP2005054738A
JP2005054738A JP2003288522A JP2003288522A JP2005054738A JP 2005054738 A JP2005054738 A JP 2005054738A JP 2003288522 A JP2003288522 A JP 2003288522A JP 2003288522 A JP2003288522 A JP 2003288522A JP 2005054738 A JP2005054738 A JP 2005054738A
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lubricating oil
hollow cylindrical
cylindrical tube
speed
shaft
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Toshio Ono
敏雄 小野
Hiroyuki Yagi
広幸 八木
Hidenori Takamatsu
英紀 高松
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IHI Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0467—Elements of gearings to be lubricated, cooled or heated
    • F16H57/0469—Bearings or seals

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
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Abstract

<P>PROBLEM TO BE SOLVED: To provide a lubricating oil feeding device and a double structure rotary shaft capable of surely feeding lubricating oil to both ends of a high-speed rotary shaft, greatly reducing weight by halving the length of external piping, easily assuring dynamic balance at high-speed rotation, and suppressing shaft vibration in an engine operation rotation zone in a high-speed rotary machine such as a gas turbine. <P>SOLUTION: This device is provided with a thin hollow cylindrical tube 12 that surrounds the high-speed rotary shaft and is coaxially attached between bearings at both ends of the high-speed rotary shaft 2, and a center support mechanism 14 supporting a center in the axial direction of the hollow cylindrical tube from the outside and rotating in synchronization with the thin hollow cylindrical tube. Lubricating oil is fed from one bearing to the other bearing through a gap between the hollow cylindrical tube 12 and the high speed rotary shaft 2. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

本発明は、高速回転軸の両端部に潤滑油を供給すると共に、軽量化と軸振動の抑制を行う高速回転機械の潤滑油供給装置と２重構造の回転軸に関する。   The present invention relates to a lubricating oil supply device for a high-speed rotating machine and a double-structured rotating shaft that supplies lubricating oil to both ends of a high-speed rotating shaft and reduces weight and suppresses shaft vibration.

ガスタービンは、圧縮機、燃焼器及びタービン、等を備え、圧縮機で圧縮された空気により燃焼器で燃料を燃焼させ、燃焼器で発生した燃焼ガスによりタービンを駆動し、このタービンにより圧縮機を駆動するようになっている。また、２軸ガスタービンエンジンの場合には、更に、タービンの排気ガスにより駆動される低圧タービンと、この低圧タービンにより駆動されるファンを備えている。   The gas turbine includes a compressor, a combustor, a turbine, and the like. The fuel is burned by the combustor using the air compressed by the compressor, and the turbine is driven by the combustion gas generated by the combustor. Is supposed to drive. In the case of a two-shaft gas turbine engine, a low-pressure turbine driven by turbine exhaust gas and a fan driven by the low-pressure turbine are further provided.

上述したガスタービンにおいて、圧縮機とタービンは通常細長いシャフト（以下、連結シャフトと呼ぶ）で直接連結される。この連結シャフトは両端部が軸受で支持され、その危険速度（固有振動数）がエンジンの運用回転域内に入らないように、シャフトの断面二次モーメントや断面積が設定される。   In the gas turbine described above, the compressor and the turbine are usually directly connected by an elongated shaft (hereinafter referred to as a connecting shaft). Both ends of this connecting shaft are supported by bearings, and the cross-sectional secondary moment and cross-sectional area of the shaft are set so that the critical speed (natural frequency) does not enter the operating rotation range of the engine.

なお、ガスタービンにおける軸振動を抑える手段として、例えば特許文献１が開示されている。   For example, Patent Document 1 is disclosed as means for suppressing shaft vibration in a gas turbine.

特許文献１の「ガスタービンロータ」は、一方のホイールディスク５６ａのリム部５７ａと隣りのホイールディスク５６ｂのリム部５７ｂとの外径側に離調手段５３を設け、この離調手段５３により、ホイールディスクの質量重量を調整し、使用回転速度から危険速度を離調させ、運転中に発生する軸振動を低く抑えるものである。   The "gas turbine rotor" of Patent Document 1 is provided with a detuning means 53 on the outer diameter side of the rim portion 57a of one wheel disc 56a and the rim portion 57b of the adjacent wheel disc 56b. By adjusting the mass and weight of the wheel disc, the critical speed is detuned from the operating rotational speed, and the shaft vibration generated during operation is kept low.

特開２０００−４５７０２号公報JP 2000-45702 A

圧縮機とタービンを連結シャフトで直接連結する場合、連結シャフトの両端部を支持する軸受やその他の機器の潤滑のために、連結シャフトの両端部に潤滑油を供給する必要がある。
しかし、連結シャフトは一般に長く（１〜２ｍ）、両端部の潤滑油供給箇所は、前後に離れているため、それぞれに潤滑油の供給ラインと戻りラインを設けると、外部配管長さが長くなり、重量が過大となるばかりでなく、配管系統が複雑化する問題点があった。 When a compressor and a turbine are directly connected by a connecting shaft, it is necessary to supply lubricating oil to both ends of the connecting shaft in order to lubricate bearings and other devices that support both ends of the connecting shaft.
However, the connecting shaft is generally long (1 to 2 m), and the lubricating oil supply points at both ends are separated from each other in the front and rear. Therefore, if a lubricating oil supply line and a return line are provided for each, the length of the external pipe becomes long. In addition to the excessive weight, the piping system is complicated.

また、この問題を解決するために、連結シャフトの両端部の一方から潤滑油を供給し、エンジン内部で一方から他方に潤滑油を移送させ、他方から潤滑油を戻すようにできれば、供給ラインと戻りラインがそれぞれ１本で足り、外部配管長さが半減し、大幅な軽量化が可能である。
しかし、この場合、一方から他方に内部で潤滑油を移送させる構造が複雑となりやすく、かつ高速回転する連結シャフトを介在するため、高速回転時の動バランスがとりにくく、かつエンジンの運用回転域内に入る軸振動が発生しやすい問題点があった。 In order to solve this problem, if the lubricating oil is supplied from one end of the connecting shaft, the lubricating oil is transferred from one to the other inside the engine, and the lubricating oil is returned from the other, the supply line and Only one return line is required, the external piping length is halved, and a significant weight reduction is possible.
However, in this case, the structure for transferring the lubricating oil from one side to the other tends to be complicated, and a connecting shaft that rotates at high speed is interposed, so that it is difficult to balance the dynamics at high speed rotation, and within the operating rotation range of the engine. There was a problem that entering shaft vibration was likely to occur.

本発明は、上述した問題点を解決するために創案されたものである。すなわち、本発明の目的は、ガスタービン等の高速回転機械において、高速回転軸の両端部に潤滑油を確実に供給でき、外部配管長さを半減させて大幅な軽量化が可能であり、高速回転時の動バランスが容易にとれ、かつエンジンの運用回転域内に入る軸振動を抑制することができる高速回転機械の潤滑油供給装置と２重構造の回転軸を提供することにある。   The present invention has been developed to solve the above-described problems. That is, the object of the present invention is to reliably supply the lubricating oil to both ends of the high-speed rotating shaft in a high-speed rotating machine such as a gas turbine, and to reduce the length of the external pipe by half and to reduce the weight significantly. An object of the present invention is to provide a lubricating oil supply device for a high-speed rotating machine and a double-structured rotating shaft that can easily achieve dynamic balance during rotation and suppress shaft vibrations that enter the operating rotation range of the engine.

本発明によれば、高速回転軸の両端部の軸受の間に高速回転軸を囲み同軸に取り付けられた薄肉の中空円筒管と、該中空円筒管の軸方向中央部を外側から支持し薄肉の中空円筒管と同期して回転する中央支持機構とを備え、前記中空円筒管と高速回転軸の隙間を通して、軸受の一方から他方に潤滑油を供給する、ことを特徴とする高速回転機械の潤滑油供給装置が提供される。   According to the present invention, a thin-walled hollow cylindrical tube that is coaxially mounted between the bearings at both ends of the high-speed rotation shaft and is coaxially mounted, and supports the axially central portion of the hollow cylindrical tube from the outside. Lubricating a high-speed rotating machine comprising a central support mechanism that rotates in synchronization with the hollow cylindrical tube, and supplying lubricating oil from one of the bearings to the other through a gap between the hollow cylindrical tube and the high-speed rotating shaft An oil supply apparatus is provided.

上記本発明の構成によれば、中央支持機構を備え、中空円筒管の軸方向中央部を外側から支持し薄肉の中空円筒管と同期して回転するので、中空円筒管の共振点をエンジンの運用回転域から回避させることができる。
また、中空円筒管と高速回転軸の隙間を通して、軸受の一方から他方に潤滑油を供給するので、供給ラインと戻りラインがそれぞれ１本で足り、外部配管長さを半減し、大幅なエンジンの軽量化が可能となる。
更に、薄肉の中空円筒管は、高速回転軸に同軸に取り付けられるので、高速回転時の動バランスが容易にとれる。 According to the configuration of the present invention, the center support mechanism is provided, and the axial central portion of the hollow cylindrical tube is supported from the outside and rotates in synchronization with the thin hollow cylindrical tube. It can be avoided from the operational rotation area.
Also, since lubricating oil is supplied from one of the bearings to the other through the gap between the hollow cylindrical tube and the high-speed rotating shaft, one supply line and one return line are sufficient, reducing the length of the external piping by half. Weight reduction is possible.
Furthermore, since the thin hollow cylindrical tube is coaxially attached to the high-speed rotation shaft, the dynamic balance during high-speed rotation can be easily achieved.

本発明の好ましい実施形態によれば、前記中央支持機構は、高速回転軸と同期して回転するディスクの内方端部に取り付けられ、中空円筒管の中央部外面に接触して支持するリング部材である。   According to a preferred embodiment of the present invention, the central support mechanism is attached to the inner end of a disk that rotates in synchronization with a high-speed rotation shaft, and is a ring member that contacts and supports the outer surface of the center of the hollow cylindrical tube. It is.

この構成により、ディスク（圧縮機ディスク又はタービンディスク）が、高速回転軸と同期して回転するので、その内方端部にリング部材を取り付けるだけで、軽量の中央支持機構を構成することができる。
また、リング部材を軸対称に形成するだけで、高速回転時の動バランスが容易にとれる。 With this configuration, the disk (compressor disk or turbine disk) rotates in synchronization with the high-speed rotation shaft, so that a light-weight central support mechanism can be configured simply by attaching a ring member to the inner end of the disk. .
Moreover, the dynamic balance at the time of high-speed rotation can be easily taken only by forming the ring member symmetrically.

前記リング部材は、前記ディスクの内方端部から軸方向に張り出した部材であることが好ましい。
この構成により、リング部材を例えばディスクと一体に製作、組立、分解ができ、高速回転時の動バランスが容易にとれ、組立・分解が容易となる。 The ring member is preferably a member protruding in the axial direction from the inner end of the disk.
With this configuration, the ring member can be manufactured, assembled, and disassembled integrally with the disk, for example, and the dynamic balance during high-speed rotation can be easily obtained, and assembly and disassembly are facilitated.

また、本発明によれば、外側回転軸の内側で内側回転軸が回転する２重構造の回転軸であって、外側回転軸の固有振動数を調整するため、ディスクボア部から張出した部材で外側回転軸を支持する、ことを特徴とする２重構造の回転軸が提供される。
この構成により、例えば高圧系（高圧圧縮機、高圧タービン）の回転軸の内側に、低圧系（ファン、低圧圧縮機、低圧タービン）の回転軸が設けられているようなガスタービンエンジンの外側回転軸の固有振動数を調整することができる。 In addition, according to the present invention, the rotary shaft having a double structure in which the inner rotary shaft rotates inside the outer rotary shaft, the member protruding from the disk bore portion to adjust the natural frequency of the outer rotary shaft. A dual-structured rotating shaft is provided that supports an outer rotating shaft.
With this configuration, for example, the outer rotation of the gas turbine engine in which the rotation shaft of the low pressure system (fan, low pressure compressor, low pressure turbine) is provided inside the rotation shaft of the high pressure system (high pressure compressor, high pressure turbine). The natural frequency of the shaft can be adjusted.

上述したように、本発明は、回転部であるディスクに支持機構を付加し、中空円筒管の軸方向中央部を支持することにより、共振点を運用回転域から回避させるものであり、中空円筒管と高速回転軸の隙間を通して軸受の一方から他方に潤滑油を供給する共通サンプ化が可能になることで、エンジンの軽量化に寄与できると共に、軸振動共振点を十分に回避した中空円筒管の設計が可能になった。   As described above, the present invention adds a support mechanism to the disk, which is a rotating part, and supports the central part in the axial direction of the hollow cylindrical tube, thereby avoiding the resonance point from the operating rotational range. Hollow cylinder tube that can contribute to weight reduction of engine and sufficiently avoid shaft vibration resonance point by enabling common sump to supply lubricant from one side of bearing to the other through gap between tube and high-speed rotating shaft The design of became possible.

すなわち、本発明の高速回転機械の潤滑油供給装置と２重構造の回転軸は、ガスタービン等の高速回転機械において、高速回転軸の両端部に潤滑油を確実に供給でき、外部配管長さを半減させて大幅な軽量化が可能であり、高速回転時の動バランスが容易にとれ、かつエンジンの運用回転域内に入る軸振動を抑制することができる、等の優れた効果を有する。   That is, the lubricating oil supply device of the high-speed rotating machine of the present invention and the double-structured rotating shaft can reliably supply the lubricating oil to both ends of the high-speed rotating shaft in a high-speed rotating machine such as a gas turbine. Can be significantly reduced in weight, and it has excellent effects such as being able to easily achieve a dynamic balance during high-speed rotation and suppressing shaft vibrations that enter the operating rotation range of the engine.

以下、本発明の好ましい実施形態を図面を参照して説明する。なお各図において共通する部分には同一の符号を付し、重複した説明を省略する。   Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings. In addition, the same code | symbol is attached | subjected to the common part in each figure, and the overlapping description is abbreviate | omitted.

図１は、本発明の潤滑油供給装置を備えた高速回転機械の部分構成図である。この図は、ガスタービンの圧縮機部分の半断面図であり、１は回転中心、２は圧縮機とタービンを連結する連結シャフト、３は圧縮機ディスク、４は圧縮機動翼、５は圧縮機静翼、６はケーシングである。以下、連結シャフトを「高速回転軸」、圧縮機ディスクを単に「ディスク」と呼ぶ。   FIG. 1 is a partial configuration diagram of a high-speed rotating machine provided with the lubricating oil supply device of the present invention. This figure is a half sectional view of a compressor portion of a gas turbine, wherein 1 is a rotation center, 2 is a connecting shaft for connecting the compressor and the turbine, 3 is a compressor disk, 4 is a compressor blade, and 5 is a compressor. A stationary blade 6 is a casing. Hereinafter, the connecting shaft is referred to as “high-speed rotating shaft”, and the compressor disk is simply referred to as “disk”.

図１において、本発明の潤滑油供給装置は、薄肉の中空円筒管１２と中央支持機構１４を備える。   In FIG. 1, the lubricating oil supply apparatus of the present invention includes a thin hollow cylindrical tube 12 and a central support mechanism 14.

中空円筒管１２は、高速回転軸２の両端部の軸受（図示せず）の間に高速回転軸２を囲み同軸に取り付けられている。中空円筒管１２の両端部は、図示しないシール材を介して水密に高速回転軸２又は軸受部材に取り付けられ、図に破線の矢印で示すように、中空円筒管１２と高速回転軸２の隙間を通して、軸受の一方から他方に潤滑油を供給できるようになっている。なお、この流れは、圧縮機側（図で左）からタービン側（図で右）に向かうのが好ましいが、逆であってもよい。   The hollow cylindrical tube 12 surrounds the high-speed rotation shaft 2 and is coaxially mounted between bearings (not shown) at both ends of the high-speed rotation shaft 2. Both ends of the hollow cylindrical tube 12 are attached to the high-speed rotating shaft 2 or the bearing member in a water-tight manner via a sealing material (not shown), and a gap between the hollow cylindrical tube 12 and the high-speed rotating shaft 2 is indicated by a dashed arrow in the figure. Through this, lubricating oil can be supplied from one of the bearings to the other. This flow is preferably directed from the compressor side (left in the figure) to the turbine side (right in the figure), but may be reversed.

中空円筒管１２は、高速回転軸２との間に隙間を形成する機能を有するのみであり、潤滑油の圧力に耐える範囲で可能な限り薄肉であるのが好ましく、例えば１〜３ｍｍ程度であるのがよい。   The hollow cylindrical tube 12 only has a function of forming a gap with the high-speed rotating shaft 2, and is preferably as thin as possible within a range that can withstand the pressure of the lubricating oil, for example, about 1 to 3 mm. It is good.

また、中空円筒管１２は、その軸方向中央部に外側から支持するための支持部１２ａを有する。この支持部１２ａは、中空円筒管１２の外方に膨らんだ中空円筒形であり、外周面が回転中心１と同軸に形成されている。この支持部１２ａは、中空円筒管１２と一体に形成されているのが好ましいが、別部品であってもよい。   Further, the hollow cylindrical tube 12 has a support portion 12a for supporting from the outside at the axial center portion thereof. The support portion 12 a has a hollow cylindrical shape that swells outward from the hollow cylindrical tube 12, and an outer peripheral surface is formed coaxially with the rotation center 1. The support portion 12a is preferably formed integrally with the hollow cylindrical tube 12, but may be a separate part.

中央支持機構１４は、中空円筒管１２の軸方向中央部を外側から支持し、高速回転軸２と同期して回転する機能を有する。
中央支持機構１４は、この例では、高速回転軸と同期して回転するディスク３の内方端部に取り付けられた中空リング部材であり、その内周面が支持部１２ａと同軸の円筒面であり、中空円筒管１２の中央部外面に接触して支持するようになっている。
また、この例では、中空リング部材は、ディスク３の内方端部から軸方向に張り出して一体に成形されている。 The central support mechanism 14 has a function of supporting the central portion in the axial direction of the hollow cylindrical tube 12 from the outside and rotating in synchronization with the high-speed rotation shaft 2.
In this example, the central support mechanism 14 is a hollow ring member attached to the inner end portion of the disk 3 that rotates in synchronization with the high-speed rotation shaft, and the inner peripheral surface thereof is a cylindrical surface that is coaxial with the support portion 12a. Yes, it contacts and supports the outer surface of the central part of the hollow cylindrical tube 12.
Further, in this example, the hollow ring member is integrally formed by protruding in the axial direction from the inner end portion of the disk 3.

上述した構成により、連結シャフト（高速回転軸２）の両端部の一方から潤滑油を供給し、エンジン内部で一方から他方に潤滑油を移送させ、他方から潤滑油を戻すようにできる。従って、供給ラインと戻りラインがそれぞれ１本で足り、外部配管長さが半減し、大幅な軽量化が可能となる。   With the above-described configuration, the lubricating oil can be supplied from one end of the connecting shaft (high-speed rotating shaft 2), the lubricating oil can be transferred from one to the other inside the engine, and the lubricating oil can be returned from the other. Therefore, one supply line and one return line are sufficient, the external pipe length is reduced by half, and a significant weight reduction is possible.

次に、上述した構造における中空円筒管１２の危険速度について検討する。
高速回転軸２や中空円筒管１２は、まっすぐな一様断面のはりであり、断面が左右対称であるとみなすことができる。この場合、はりの横振動が対称面内で生ずるとすると、自由振動の運動方程式は、数１の（１）式で表される。ここで、ｔは時間、ｘははりの長手方向にとった座標、ｕははりの横変位、Ｅははりの材料の縦弾性係数、Ｉははりの断面二次モーメント、Ａははりの断面積、ρははりの材料の密度である。
この運動方程式からはりの横振動の固有振動数ｆ（Ｈｚ）は、数１の（２）式で表される。ここで、ｌははりの長さ、λは境界条件及び振動モードによって定まる無次元の係数である。 Next, the critical speed of the hollow cylindrical tube 12 in the structure described above will be examined.
The high-speed rotation shaft 2 and the hollow cylindrical tube 12 are beams having a straight uniform cross section, and the cross section can be regarded as being symmetric. In this case, assuming that the lateral vibration of the beam occurs in the plane of symmetry, the equation of motion of free vibration is expressed by Equation (1) in Equation 1. Here, t is the time, x is the coordinate taken in the longitudinal direction of the beam, u is the lateral displacement of the beam, E is the longitudinal elastic modulus of the material of the beam, I is the moment of inertia of the beam, and A is the beam cross section. , Ρ is the density of the beam material.
From this equation of motion, the natural frequency f (Hz) of the lateral vibration of the beam is expressed by equation (2). Here, l is the length of the beam, and λ is a dimensionless coefficient determined by the boundary condition and the vibration mode.

Figure 2005054738
Figure 2005054738

表１は、両端が回転可能に支持された場合の無次元係数λの例であり、１、２、３次振動の場合に、無次元係数λはそれぞれ、π、２π、３πであることが、理論的に求められている。   Table 1 is an example of the dimensionless coefficient λ when both ends are rotatably supported. In the case of 1, 2, and 3rd order vibrations, the dimensionless coefficient λ is π, 2π, and 3π, respectively. Sought theoretically.

Figure 2005054738
Figure 2005054738

上述した数１の（２）式から、高速回転軸２、中空円筒管１２、及び中間部で支持した中空円筒管１２の危険速度（固有振動数）を求めることができる。このうち、高速回転軸２の危険速度は、エンジンの運用回転域内に入らないように、断面二次モーメントや断面積が設定されているので、ここでは省略する。   The critical speed (natural frequency) of the high-speed rotating shaft 2, the hollow cylindrical tube 12, and the hollow cylindrical tube 12 supported by the intermediate portion can be obtained from the above-described equation (2). Of these, the critical speed of the high-speed rotating shaft 2 is omitted here because the secondary moment of inertia and the cross-sectional area are set so as not to fall within the operating rotational range of the engine.

表２は、中空円筒管のみ（Ｃａｓｅ１）と、これを中間部で支持した場合（Ｃａｓｅ２）の近似計算例である。また、図２は、この計算例に基づき作製したキャンベル線図である。なお、この例では、危険速度が問題となる１次振動数のみを対象としている。

Figure 2005054738
Table 2 shows an approximate calculation example of only a hollow cylindrical tube (Case 1) and a case where this is supported by an intermediate part (Case 2). FIG. 2 is a Campbell diagram produced based on this calculation example. In this example, only the primary frequency in which the critical speed is a problem is targeted.
Figure 2005054738

図２において、横軸はロータ回転数であり、縦軸は固有振動数である。また、図中の斜めの直線Ａは高速回転軸２を示し、２本の縦線Ｂ，Ｃは、エンジン負荷が「アイドリング」と「最大」の場合を示している。また、２本の横線Ｄ，Ｅは、Ｃａｓｅ１とＣａｓｅ２（本発明）の場合を示している。   In FIG. 2, the horizontal axis is the rotor rotation speed, and the vertical axis is the natural frequency. In addition, an oblique straight line A in the figure indicates the high-speed rotation shaft 2, and two vertical lines B and C indicate a case where the engine load is “idling” and “maximum”. In addition, two horizontal lines D and E indicate cases of Case 1 and Case 2 (the present invention).

表２及び図２から、薄肉（ｔ＝１ｍｍ）の中空円筒管１２をＬ（ｌ）＝１ｍの支持スパンで支持した場合には、１次モードの固有振動数が高速回転軸２の運用回転域に完全に入ってしまい、そのままでは共振は避けられないことがわかる。
これに対して、本発明の場合（Ｃａｓｅ２）、中空円筒管１２をＬ（ｌ）＝０．７ｍの中間位置で支持するだけで、１次モードの固有振動数が上昇し、高速回転軸２の運用回転域を確実に回避することができることがわかる。 From Table 2 and FIG. 2, when the thin-walled (t = 1 mm) hollow cylindrical tube 12 is supported with a support span of L (l) = 1 m, the natural frequency of the primary mode is the operational rotation of the high-speed rotating shaft 2. It turns out that it completely enters the region, and resonance is unavoidable as it is.
On the other hand, in the case of the present invention (Case 2), the natural frequency of the primary mode increases only by supporting the hollow cylindrical tube 12 at an intermediate position of L (l) = 0.7 m, and the high-speed rotating shaft 2 It can be seen that the operational rotation range can be reliably avoided.

上述したように本発明の構成によれば、中央支持機構１４を備え、中空円筒管１２の軸方向中央部を外側から支持し高速回転軸２と同期して回転するので、中空円筒管１２の共振点をエンジンの運用回転域から容易に回避させることができる。
また、中空円筒管１２と高速回転軸２の隙間を通して、軸受の一方から他方に潤滑油を供給するので、供給ラインと戻りラインがそれぞれ１本で足り、外部配管長さを半減し、大幅なエンジンの軽量化が可能となる。
更に、薄肉の中空円筒管１２は、高速回転軸２に同軸に取り付けられるので、高速回転時の動バランスが容易にとれる。 As described above, according to the configuration of the present invention, the central support mechanism 14 is provided, and the axial central portion of the hollow cylindrical tube 12 is supported from the outside and rotates in synchronization with the high-speed rotation shaft 2. The resonance point can be easily avoided from the operating rotation range of the engine.
Further, since lubricating oil is supplied from one of the bearings to the other through the gap between the hollow cylindrical tube 12 and the high-speed rotating shaft 2, one supply line and one return line are sufficient, and the length of the external pipe is reduced by half. Engine weight can be reduced.
Furthermore, since the thin hollow cylindrical tube 12 is coaxially attached to the high-speed rotation shaft 2, a dynamic balance during high-speed rotation can be easily obtained.

また、ディスク３（圧縮機ディスク又はタービンディスク）が、高速回転軸２と同期して回転するので、その内方端部に中空リング部材１４を取り付けるだけで、軽量の中央支持機構を構成することができる。また、中空リング部材１４を軸対称に形成するだけで、高速回転時の動バランスが容易にとれる。   Further, since the disk 3 (compressor disk or turbine disk) rotates in synchronization with the high-speed rotating shaft 2, a lightweight central support mechanism can be configured by simply attaching the hollow ring member 14 to the inner end thereof. Can do. Moreover, the dynamic balance at the time of high speed rotation can be easily taken only by forming the hollow ring member 14 symmetrically.

更に中空リング部材１４を、ディスク３の内方端部から軸方向に張り出して一体成形した構成により、中空リング部材１４をディスク３と一体に製作、組立、分解ができるので、高速回転時の動バランスが容易にとれ、組立・分解が容易となる。   Furthermore, since the hollow ring member 14 is integrally formed by projecting from the inner end of the disk 3 in the axial direction, the hollow ring member 14 can be manufactured, assembled, and disassembled integrally with the disk 3, Balance is easy, and assembly and disassembly are easy.

なお本発明は、上述した実施形態に限定されるものではなく、本発明の要旨を逸脱しない範囲で種々の変更が可能である。例えば、本発明は、ガスタービンに限定されず、高速回転軸を有する圧縮機、タービン、その他の高速回転機械に適用することができる。   The present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the gist of the present invention. For example, the present invention is not limited to a gas turbine, but can be applied to a compressor, a turbine, and other high-speed rotating machines having a high-speed rotating shaft.

本発明の潤滑油供給装置を備えた高速回転機械の部分構成図である。It is a partial block diagram of the high-speed rotary machine provided with the lubricating oil supply apparatus of this invention. 本発明の実施例を示すキャンベル線図である。It is a Campbell diagram which shows the Example of this invention. 特許文献１の「ガスタービンロータ」の模式図である。2 is a schematic diagram of a “gas turbine rotor” of Patent Document 1. FIG.

符号の説明Explanation of symbols

１ 回転中心、２ 高速回転軸（連結シャフト）、
３ ディスク（圧縮機ディスク）、４ 圧縮機動翼、
５ 圧縮機静翼、６ ケーシング、
１２ 中空円筒管、１２ａ 支持部、
１４ 中央支持機構（中空リング部材）

1 rotation center, 2 high-speed rotation shaft (connection shaft),
3 disks (compressor disks), 4 compressor blades,
5 Compressor vanes, 6 casing,
12 hollow cylindrical tube, 12a support part,
14 Center support mechanism (hollow ring member)

Claims (3)

高速回転軸の両端部の軸受の間に高速回転軸を囲み同軸に取り付けられた薄肉の中空円筒管と、該中空円筒管の軸方向中央部を外側から支持し高速回転軸と同期して回転する中央支持機構とを備え、
前記中空円筒管と高速回転軸の隙間を通して、軸受の一方から他方に潤滑油を供給する、ことを特徴とする高速回転機械の潤滑油供給装置。 A thin-walled hollow cylindrical tube that is coaxially mounted around the high-speed rotation shaft between the bearings at both ends of the high-speed rotation shaft, and supports the central portion in the axial direction of the hollow cylindrical tube from the outside and rotates in synchronization with the high-speed rotation shaft And a central support mechanism that
A lubricating oil supply device for a high-speed rotating machine, wherein the lubricating oil is supplied from one of the bearings to the other through a gap between the hollow cylindrical tube and the high-speed rotating shaft. 前記中央支持機構は、高速回転軸と同期して回転するディスクの内方端部に取り付けられ、中空円筒管の中央部外面に接触して支持する中空リング部材である、ことを特徴とする請求項１に記載の高速回転機械の潤滑油供給装置。 The central support mechanism is a hollow ring member that is attached to an inner end portion of a disk that rotates in synchronization with a high-speed rotation shaft and supports the outer surface of a central portion of a hollow cylindrical tube. Item 2. A lubricating oil supply device for a high-speed rotating machine according to Item 1. 前記中空リング部材は、前記ディスクの内方端部から軸方向に張り出した一体成形部材である、ことを特徴とする請求項２に記載の高速回転機械の潤滑油供給装置。

The lubricating oil supply device for a high-speed rotating machine according to claim 2, wherein the hollow ring member is an integrally formed member that projects in an axial direction from an inner end of the disk.

JP2003288522A 2003-08-07 2003-08-07 Lubricating oil feeding device and double structure rotary shaft for high-speed rotary machine Pending JP2005054738A (en)

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* Cited by examiner, † Cited by third party
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JP2016538483A (en) * 2013-11-25 2016-12-08 スネクマ Turbomachine with shaft sleeve and associated sleeve tube
JP2017502189A (en) * 2013-11-26 2017-01-19 ゼネラル・エレクトリック・カンパニイ Radial tie bolt support spring

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JP2016538483A (en) * 2013-11-25 2016-12-08 スネクマ Turbomachine with shaft sleeve and associated sleeve tube
JP2017502189A (en) * 2013-11-26 2017-01-19 ゼネラル・エレクトリック・カンパニイ Radial tie bolt support spring

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