JP7253948B2 - Squeeze film damper and rotary machine - Google Patents

Squeeze film damper and rotary machine Download PDF

Info

Publication number
JP7253948B2
JP7253948B2 JP2019055581A JP2019055581A JP7253948B2 JP 7253948 B2 JP7253948 B2 JP 7253948B2 JP 2019055581 A JP2019055581 A JP 2019055581A JP 2019055581 A JP2019055581 A JP 2019055581A JP 7253948 B2 JP7253948 B2 JP 7253948B2
Authority
JP
Japan
Prior art keywords
gap
region
radially
oil
inner member
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.)
Active
Application number
JP2019055581A
Other languages
Japanese (ja)
Other versions
JP2020060290A (en
Inventor
映明 山脇
泰憲 時政
種宏 篠原
倫平 川下
真人 岩▲崎▼
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.)
Mitsubishi Heavy Industries Ltd
Original Assignee
Mitsubishi Heavy Industries 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 Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Priority to CN201910951731.7A priority Critical patent/CN111005937B/en
Priority to US16/589,741 priority patent/US11053977B2/en
Publication of JP2020060290A publication Critical patent/JP2020060290A/en
Application granted granted Critical
Publication of JP7253948B2 publication Critical patent/JP7253948B2/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Landscapes

  • Vibration Prevention Devices (AREA)
  • Support Of The Bearing (AREA)

Description

本開示は、スクイズフィルムダンパ及び回転機械に関する。 The present disclosure relates to squeeze film dampers and rotary machines.

従来、蒸気タービン、ガスタービン又は圧縮機を含む回転機械は、ロータ軸を支持するための軸受装置を備えている。例えば、ロータ軸の少なくとも下側部分を軸受メタルによって径方向から支持するジャーナル軸受は、ロータ軸と軸受メタルとの間に油を供給して油膜を形成し、ロータ軸と軸受メタルとの直接的な金属接触を防止するようになっている。 Traditionally, rotary machines, including steam turbines, gas turbines or compressors, have bearing arrangements for supporting a rotor shaft. For example, in a journal bearing that radially supports at least the lower portion of the rotor shaft with a bearing metal, oil is supplied between the rotor shaft and the bearing metal to form an oil film, and direct contact between the rotor shaft and the bearing metal is achieved. are designed to prevent unwanted metal-to-metal contact.

さらに、上記軸受メタル、或いは、軸受パッドを介してロータ軸を支持する円環（内環）は、より大径の円環（外環）を介して支持され得る。そして、軸受メタルや内環と外環との隙間に油を供給し、該軸受メタル又は内環の外周面と外環の内周面との間に油膜を形成することで、所謂スクイズ作用による制振機能を備えたスクイズフィルムダンパ軸受が知られている（例えば特許文献１参照）。 Furthermore, the annular ring (inner ring) that supports the rotor shaft via the bearing metal or bearing pad can be supported via a larger diameter annular ring (outer ring). Oil is supplied to the gap between the bearing metal or the inner ring and the outer ring to form an oil film between the outer peripheral surface of the bearing metal or the inner ring and the inner peripheral surface of the outer ring. A squeeze film damper bearing having a damping function is known (see Patent Document 1, for example).

特開２００３－８３３２５号公報JP-A-2003-83325

上記特許文献１に開示されたスクイズフィルムダンパ軸受は、油膜切れを防止するため、外環の内周に沿って形成される隙間に油を供給するようになっている。しかし、このような油膜のスクイズ作用のみに基づくダンパは、油の粘度を選択ないし調整する以外にそのダンピング性能の調整が困難であり、仮に油の粘度を選択又は調整しても、上記ダンピング性能を大きく向上させることが難しい場合がある。 The squeeze film damper bearing disclosed in Patent Document 1 supplies oil to a gap formed along the inner circumference of the outer ring in order to prevent the oil film from running out. However, it is difficult to adjust the damping performance of such a damper based solely on the squeezing action of the oil film other than by selecting or adjusting the viscosity of the oil. can be difficult to improve significantly.

上述の事情に鑑みて、本開示の少なくとも一実施形態は、簡易な構成でスクイズフィルムダンパ及び回転機械の減衰性能の向上を図ることを目的とする。 In view of the circumstances described above, an object of at least one embodiment of the present disclosure is to improve damping performance of a squeeze film damper and a rotating machine with a simple configuration.

（１）本開示の少なくとも一実施形態に係るスクイズフィルムダンパは、軸受部を支持する内側部材と、周方向に延在する隙間を挟んで前記内側部材に対向するように、前記内側部材の外周側に設けられる外側部材と、前記隙間に設けられ、前記隙間のうち径方向内側の第１領域と、前記隙間のうち径方向外側の第２領域とを連通する複数の連通孔を有する有孔部材と、前記第１領域に油を供給するための給油路と、を備えている。 (1) A squeeze film damper according to at least one embodiment of the present disclosure includes an inner member that supports a bearing portion, and an outer periphery of the inner member facing the inner member across a gap extending in the circumferential direction. an outer member provided on the outer side of the gap, and a plurality of communication holes provided in the gap for communicating a radially inner first area of the gap and a radially outer second area of the gap. A member and an oil supply passage for supplying oil to the first region are provided.

上記（１）に記載の構成によれば、内側部材と外側部材との隙間に、径方向内側の第１領域と径方向外側の第２領域とを連通する複数の連通孔を含む有孔部材を配置したことにより、軸受部及び内側部材が振動した際には、内側部材の外周面に追従して油の一部が有孔部材の連通孔を通過し、当該通過の際に抵抗力を受ける。つまり、従来のスクイズ効果に加えて、有孔部材の連通孔を通過する油が上記内側部材の振動に対するダンパとして機能するから、簡易な構成でスクイズフィルムダンパの減衰性能を大幅に向上させることができる。
なお、有孔部材の減衰効果は、個々の有孔部材が搭載される回転機械の振動特性に応じて、例えば連通孔の数、大きさ、配置、配向、形状等を任意に設定することで調整し得る。 According to the configuration described in (1) above, the perforated member includes a plurality of communication holes in the gap between the inner member and the outer member that communicate the radially inner first region and the radially outer second region. When the bearing portion and the inner member vibrate, part of the oil follows the outer peripheral surface of the inner member and passes through the communication holes of the perforated member, and the resistance force is generated during the passage. receive. In other words, in addition to the conventional squeeze effect, the oil passing through the communication holes of the perforated member functions as a damper against the vibration of the inner member, so that the damping performance of the squeeze film damper can be greatly improved with a simple structure. can.
The damping effect of the perforated member can be obtained by arbitrarily setting the number, size, arrangement, orientation, shape, etc. of the communication holes according to the vibration characteristics of the rotating machine on which each perforated member is mounted. can be adjusted.

（２）幾つかの実施形態では、上記（１）の構成において、前記給油路は、前記内側部材の軸方向端部から前記第１領域に前記油を導く内部流路を含んでいてもよい。 (2) In some embodiments, in the configuration of (1) above, the oil supply path may include an internal flow path that guides the oil from the axial end of the inner member to the first region. .

上記（２）の構成によれば、内側部材の軸方向端部から該内側部材内の内部流路に油を供給することで、第１領域に油を供給することができる。このため、例えば外側部材及び有孔部材を径方向に貫通するような油の給油経路を設ける必要がない。つまり、内側部材の軸方向端部から内部流路に油を供給する簡易な構成により、上記（１）で述べた効果を享受することができる。 According to the configuration (2) above, oil can be supplied to the first region by supplying oil from the axial end of the inner member to the internal flow path in the inner member. Therefore, for example, it is not necessary to provide an oil supply path that radially penetrates the outer member and the perforated member. That is, the effect described in (1) above can be obtained with a simple configuration that supplies oil to the internal flow path from the axial end of the inner member.

（３）幾つかの実施形態では、上記（２）の構成において、前記内部流路は、前記軸方向端部から軸方向に延在する軸方向延在部と、前記軸方向延在部に連続して前記径方向に延在する径方向延在部とを含んでいてもよい。 (3) In some embodiments, in the configuration of (2) above, the internal flow path includes an axially extending portion extending axially from the axial end portion, and and a radially extending portion continuously extending in the radial direction.

上記（３）の構成によれば、内側部材の軸方向端部から内部流路に供給された油が、軸方向延在部と径方向延在部とを経由して第１領域に供給される。よって、内部流路の設計の自由度を向上させることができる。 According to the configuration (3) above, the oil supplied from the axial end portion of the inner member to the internal flow path is supplied to the first region via the axially extending portion and the radially extending portion. be. Therefore, it is possible to improve the degree of freedom in designing the internal flow path.

（４）幾つかの実施形態では、上記（３）の構成において、一の前記軸方向延在部につき一又は複数の前記径方向延在部が形成されていてもよい。 (4) In some embodiments, in the configuration of (3) above, one or a plurality of radially extending portions may be formed for each axially extending portion.

上記（４）の構成によれば、軸方向延在部に導かれた油は、当該軸方向延在部に連続して径方向に延在する一又は複数の径方向延在部を介して第１領域に供給される。よって、一の軸方向延在部に連続して所望の数の径方向延在部を形成することにより、内側部材のうち内部流路が設けられた周方向位置において、軸方向における一又は複数の適切な位置から第１領域に油を供給して油膜を形成することができる。 According to the configuration (4) above, the oil guided to the axially extending portion flows through one or more radially extending portions that are continuous with the axially extending portion and extend in the radial direction. It is supplied to the first area. Therefore, by forming a desired number of radially extending portions continuously from one axially extending portion, one or a plurality of radially extending portions in the axial direction can be provided at circumferential positions of the inner member where the internal flow passages are provided. oil can be supplied to the first region from an appropriate position to form an oil film.

（５）幾つかの実施形態では、上記（１）の構成において、前記給油路は、前記外側部材及び前記有孔部材を前記径方向に貫通して前記油を前記第１領域に供給するように構成されていてもよい。 (5) In some embodiments, in the configuration of (1) above, the oil supply passage penetrates the outer member and the perforated member in the radial direction to supply the oil to the first region. may be configured to

上記（５）の構成によれば、第１領域に供給するための油が、外側部材及び有孔部材を径方向に貫通するように構成された給油路を介して供給される。この構成では、内側部材の軸方向における給油経路の接地面積を抑制した簡易な構成により、上記（１）で述べた効果を享受することができる。 According to the configuration (5) above, the oil to be supplied to the first region is supplied through the oil supply passage configured to radially penetrate the outer member and the perforated member. With this configuration, the effect described in (1) above can be obtained with a simple configuration in which the contact area of the oil supply path in the axial direction of the inner member is suppressed.

（６）幾つかの実施形態では、上記（１）～（５）の何れか一つに記載の構成において、前記有孔部材は、周方向に間隔を隔てた複数箇所で前記外側部材に支持されていてもよい。 (6) In some embodiments, in the configuration according to any one of (1) to (5) above, the perforated member is supported by the outer member at a plurality of locations spaced apart in the circumferential direction. may have been

上記（６）の構成によれば、有孔部材を外側部材で支持することにより、有孔部材と外側部材との相対的な移動を規制することができる。また、周方向に間隔を隔てた複数箇所において有孔部材を支持することにより、例えば有孔部材を周方向の一か所で支持する場合に比べて両者をより強固に固定することができる。このような構成により、例えば軸受部及び内側部材が振動した際には、外側部材に支持された有孔部材に対して内側部材が相対的に接近及び離反する。よって、内側部材が振動する度、有孔部材の連通孔に油を効果的に通過させることができるから、有孔部材による減衰効果をより効率的に発揮させることができる。 With configuration (6) above, by supporting the perforated member with the outer member, relative movement between the perforated member and the outer member can be restricted. Moreover, by supporting the perforated member at a plurality of locations spaced apart in the circumferential direction, both can be fixed more firmly than, for example, when the perforated member is supported at one location in the circumferential direction. With such a configuration, for example, when the bearing portion and the inner member vibrate, the inner member relatively approaches and separates from the perforated member supported by the outer member. Therefore, every time the inner member vibrates, the oil can effectively pass through the communication holes of the perforated member, so that the damping effect of the perforated member can be exhibited more efficiently.

（７）幾つかの実施形態では、上記（１）～（６）の何れか一つに記載の構成において、前記内側部材及び前記有孔部材間の寸法Ｄと前記連通孔の直径ｄとが０．１ｄ＜Ｄ＜１０ｄを満たしてもよい。 (7) In some embodiments, in the configuration according to any one of (1) to (6) above, the dimension D between the inner member and the perforated member and the diameter d of the communication hole are 0.1d<D<10d may be satisfied.

連通孔を通過する油による減衰効果は、連通孔の径が大きすぎても小さすぎても適切に得られない虞がある。
この点、上記（７）の構成によれば、内側部材と有孔部材との隙間の寸法Ｄに対して連通孔の直径ｄが同一オーダーの範囲を満たすから、個々の有孔部材が搭載される回転機械の振動特性に応じて上記連通孔の数、大きさ、配置、配向、形状等を任意に設定することにより、適切な減衰特性に調整することができる。 If the diameter of the communication hole is too large or too small, the damping effect of the oil passing through the communication hole may not be obtained appropriately.
In this regard, according to the configuration (7), the diameter d of the communicating hole satisfies the range of the same order as the dimension D of the gap between the inner member and the perforated member, so that each perforated member can be mounted. By arbitrarily setting the number, size, arrangement, orientation, shape, etc. of the communication holes according to the vibration characteristics of the rotating machine, it is possible to adjust the damping characteristics appropriately.

（８）幾つかの実施形態では、上記（１）～（７）の何れか一つに記載の構成において、前記連通孔は、前記径方向に沿って延在する円筒状に形成されていてもよい。 (8) In some embodiments, in the configuration according to any one of (1) to (7) above, the communication hole is formed in a cylindrical shape extending along the radial direction. good too.

上記（８）の構成によれば、連通孔の形状を、径方向に沿って延在する円筒状とすることにより、簡易な構成で上記（１）～（７）の何れか一つで述べた効果を享受することができる。 According to the above configuration (8), the shape of the communication hole is a cylindrical shape extending along the radial direction, thereby simplifying the configuration described in any one of the above (1) to (7). You can enjoy the effect.

（９）幾つかの実施形態では、上記（１）～（８）の何れか一つに記載の構成において、少なくとも前記有孔部材において最も軸方向端部側に配置された前記連通孔は、その中
心軸が、前記径方向において内側より外側が前記軸方向端部に近接するように前記径方向から傾斜していてもよい。 (9) In some embodiments, in the configuration according to any one of (1) to (8) above, at least the communication hole disposed closest to the axial end in the perforated member includes: The center axis may be inclined from the radial direction such that the outer side is closer to the axial end than the inner side in the radial direction.

振動により、筒状の外側部材に内接するようにして内側部材が接近する際、両者の隙間に介在する油は周方向のほか軸方向にも移動する。
この点、上記（９）の構成によれば、連通孔の中心軸が、径方向の外側ほど軸方向端部側に近接するように径方向から傾斜しているから、軸方向端部側に押し出されることで軸方向の速度成分を有する油を、連通孔に容易に流入させることができる。よって、連通孔による減衰効果をより効率的に発揮させることができる。 Due to vibration, when the inner member approaches the cylindrical outer member so as to come in contact with it, the oil intervening in the gap between the two moves not only in the circumferential direction but also in the axial direction.
In this regard, according to the above configuration (9), the central axis of the communicating hole is inclined from the radial direction so that the outer side in the radial direction is closer to the axial end side. By being pushed out, the oil having a velocity component in the axial direction can easily flow into the communication hole. Therefore, the damping effect of the communication hole can be exhibited more efficiently.

（１０）幾つかの実施形態では、上記（１）～（８）の何れか一つに記載の構成において、前記連通孔は、前記径方向において内側より外側が小径に形成されていてもよい。 (10) In some embodiments, in the configuration according to any one of (1) to (8) above, the communication hole may be formed such that the outer side thereof has a smaller diameter than the inner side thereof in the radial direction. .

上記（１０）の構成によれば、内側部材と外側部材とが接近する際、連通孔に油を容易に流入させることができる。またその際、連通孔の出口側である径方向外側が内側より小径に形成されていることで、より高い減衰効果を発揮させることができる。 With configuration (10) above, when the inner member and the outer member approach each other, oil can easily flow into the communication hole. Further, in this case, a higher damping effect can be achieved by forming the radially outer side, which is the outlet side of the communicating hole, to have a smaller diameter than the inner side.

（１１）幾つかの実施形態では、上記（１）～（８）の何れか一つに記載の構成において、前記連通孔は、前記径方向において内側より外側が大径に形成されていてもよい。 (11) In some embodiments, in the configuration according to any one of (1) to (8) above, the communication hole may be formed such that the outer side is formed to have a larger diameter than the inner side in the radial direction. good.

上記（１１）の構成によれば、内側部材と外側部材とが離反する際、連通孔に油を容易に流入させることができる。またその際、連通孔の出口側である径方向内側が外側より小径に形成されていることで、より高い減衰効果を発揮させることができる。 With configuration (11) above, when the inner member and the outer member are separated from each other, oil can easily flow into the communication hole. Further, in this case, a higher damping effect can be achieved by forming the radial inner side, which is the outlet side of the communication hole, to have a smaller diameter than the outer side.

（１２）幾つかの実施形態では、上記（１）～（８）の何れか一つに記載の構成において、前記連通孔は、前記径方向外側の円筒部と該円筒部における前記径方向の内側端に連続し前記径方向内側に向けて拡開されたテーパ部とを含んでいてもよい。 (12) In some embodiments, in the configuration according to any one of (1) to (8) above, the communication hole is formed between the radially outer cylindrical portion and the radially outer portion of the cylindrical portion. A tapered portion that continues to the inner end and expands radially inward may be included.

上記（１２）の構成によれば、径方向に沿って円筒部とテーパ部とを含む複数の貫通孔を含んだ有孔部材により、上記（１）～（８）の何れか一つで述べた効果を享受することができる。 According to the configuration (12) above, the perforated member having a plurality of through-holes including a cylindrical portion and a tapered portion along the radial direction can be used as described in any one of (1) to (8) above. You can enjoy the effect.

（１３）幾つかの実施形態では、上記（１）～（６）の何れか一つに記載の構成において、前記連通孔は、スリット状に形成されていてもよい。 (13) In some embodiments, in the configuration according to any one of (1) to (6) above, the communication hole may be formed in a slit shape.

上記（１３）の構成によれば、連通孔の形状を、スリット状とすることにより、簡易な構成で上記（１）～（６）の何れか一つで述べた効果を享受することができる。 According to the configuration (13) above, by making the shape of the communicating hole slit-shaped, it is possible to enjoy the effect described in any one of the above (1) to (6) with a simple configuration. .

（１４）幾つかの実施形態では、上記（１）～（１３）の何れか一つに記載の構成において、前記有孔部材は、前記連通孔が設けられた領域が前記径方向内側に突出した凸部と、前記凸部と前記内側部材との間の前記第１領域を密封するとともに、前記内側部材を前記径方向外側から支持する密封支持部と、を有していてもよい。 (14) In some embodiments, in the configuration according to any one of (1) to (13) above, the perforated member has a region in which the communication hole is provided protrudes radially inward. and a sealing support portion that seals the first region between the protrusion and the inner member and supports the inner member from the radially outer side.

上記（１４）の構成によれば、密封支持部により内側部材が支持されるとともに第１領域が密封されることで、内側部材が振動した際に、第１領域に供給された油が連通孔に流れるようにすることができる。したがって、油が連通孔を通過する際に付与される抵抗力によって、スクイズフィルムダンパによる減衰性能を大幅に向上させることができる。 According to the configuration (14) above, the inner member is supported by the sealing support portion and the first region is sealed. can be made to flow to Therefore, the damping performance of the squeeze film damper can be greatly improved by the resistance applied when the oil passes through the communication hole.

（１５）幾つかの実施形態では、上記（１４）に記載の構成において、
前記密封支持部は、前記第１領域を密封するシール部材と、前記内側部材を支持する支持機構と、を有していても良い。 (15) In some embodiments, in the configuration described in (14) above,
The sealing support may have a sealing member that seals the first region and a support mechanism that supports the inner member.

上記（１５）の構成によれば、シール部材によって第１領域を密封することができ、また、支持機構によって内側部材を支持するようにスクイズフィルムダンパを構成することができる。 With configuration (15) above, the first region can be sealed by the seal member, and the squeeze film damper can be configured to support the inner member by the support mechanism.

（１６）幾つかの実施形態では、上記（１５）に記載の構成において、
前記支持機構は、前記凸部と一体として形成されるとともに前記径方向に伸縮可能に構成された切欠部材であり、前記切欠部材は、前記シール部材を収容する収容凹部を備えていても良い。 (16) In some embodiments, in the configuration described in (15) above,
The support mechanism may be a notch member that is integrally formed with the convex portion and configured to be expandable and contractable in the radial direction, and the notch member may include an accommodation recess that accommodates the seal member.

上記（１６）の構成によれば、切欠部材によって内側部材を支持することができ、また、切欠部材の収容凹部にシールが収容されることで、第１領域を密封することができる。また、切欠部材の切欠を調整することで、切欠部材の剛性を調整することができる。 With configuration (16) above, the inner member can be supported by the notch member, and the first region can be sealed by accommodating the seal in the accommodation recess of the notch member. Moreover, the rigidity of the notch member can be adjusted by adjusting the notch of the notch member.

（１７）幾つかの実施形態では、上記（１４）に記載の構成において、前記密封支持部は、前記径方向に伸縮可能なベローズであっても良い。 (17) In some embodiments, in the configuration described in (14) above, the sealing support may be a radially expandable bellows.

上記（１７）の構成によれば、ベローズによって、内側部材を支持するとともに第１領域を密封することができるので、内側部材の支持と第１領域の密封を一つの部材で実現することができ、簡易な構成で、上記（１４）で述べた効果を享受することができる。 According to the above configuration (17), the bellows can support the inner member and seal the first region, so that the support of the inner member and the sealing of the first region can be achieved with a single member. , the effect described in (14) above can be enjoyed with a simple configuration.

（１８）幾つかの実施形態では、上記（１）～（１７）の何れか一つに記載の構成において、前記隙間は、軸方向端の少なくとも一部が開放されていてもよい。 (18) In some embodiments, in the configuration according to any one of (1) to (17) above, at least a part of the axial end of the gap may be open.

上記（１８）の構成によれば、第１領域に供給され、連通孔を介して第２領域に移動した油を、該第２領域の開放された軸方向端から排出することができる。 With configuration (18) above, the oil that has been supplied to the first area and moved to the second area via the communication hole can be discharged from the open axial end of the second area.

（１９）幾つかの実施形態では、上記（１４）～（１７）の何れか一つに記載の構成において、前記有孔部材は、前記第２領域の前記径方向外側に取り付けられ、前記第２領域を密封する密封部材を有し、前記密封部材は、前記第２領域との境界に薄膜のダイヤフラムを備え、前記密封部材により形成された空間に、ガスが封入され、前記ダイヤフラムは、前記ガスと前記第２領域を流通する前記油の圧力差によって前記径方向に変形可能であっても良い。 (19) In some embodiments, in the configuration according to any one of (14) to (17) above, the perforated member is attached to the radially outer side of the second region, A sealing member that seals two regions is provided, the sealing member includes a thin-film diaphragm at a boundary with the second region, a gas is enclosed in a space formed by the sealing member, and the diaphragm It may be possible to deform in the radial direction by a pressure difference between the gas and the oil flowing through the second region.

上記（１９）の構成によれば、第２領域が密封部材により密封されていることで、スクイズフィルムダンパに供給される油を循環させる構造をとる必要がなくなる。即ち、油が循環する際に油に空気が混入することが抑制されるので、スクイズフィルムダンパの減衰性能が低下することを抑制することができる。 With configuration (19) above, since the second region is sealed by the sealing member, there is no need to adopt a structure for circulating the oil supplied to the squeeze film damper. That is, it is possible to prevent the damping performance of the squeeze film damper from deteriorating because air is prevented from being mixed with the oil when the oil is circulated.

ダイヤフラムが、密封部材により形成された空間に封入されたガスと第２領域を流通する油の圧力差によって、変形可能であることにより、密封部材が第２領域を密封した状態でも、油が連通孔を介して第１領域と第２領域を行き来することができる。したがって、第２領域が密封された状態でも、油が連通孔を流入する際に抵抗力を受けることによって、スクイズフィルムダンパの減衰性能を大幅に向上させることができる。 The diaphragm is deformable due to the pressure difference between the gas enclosed in the space formed by the sealing member and the oil flowing through the second region, so that the oil communicates even when the sealing member seals the second region. It is possible to go back and forth between the first area and the second area through the hole. Therefore, even when the second region is sealed, the damping performance of the squeeze film damper can be greatly improved by receiving resistance when the oil flows into the communication hole.

（２０）幾つかの実施形態では、（１９）に記載の構成において、前記密封部材は、前記凸部に取り外し可能に取り付けられていても良い。 (20) In some embodiments, in the configuration described in (19), the sealing member may be removably attached to the projection.

上記（２０）の構成によれば、密封部材を凸部に取り外し可能に取り付けることによって、スクイズフィルムダンパの減衰性能を柔軟に調整することができる。詳細には、密封部材のガス領域の圧力を調整することができるため、スクイズフィルムダンパの減衰性能を調整することができる。 With configuration (20) above, the damping performance of the squeeze film damper can be flexibly adjusted by detachably attaching the sealing member to the projection. Specifically, since the pressure in the gas region of the sealing member can be adjusted, the damping performance of the squeeze film damper can be adjusted.

（２１）幾つかの実施形態では、スクイズフィルムダンパは、軸受部を支持する内側部材と、前記内側部材と所定の間隔を空けて、前記内側部材の外周側に設けられる有孔部材と、を有し、前記有孔部材は、少なくとも一つの取り外し可能なユニットと、前記ユニットを挿入可能な空間が形成された円弧部と、を備え、前記ユニットは、径方向内側の端部であるとともに、前記内側部材と接する第一部材と、径方向外側の端部であるとともに、前記第一部材と隙間を空けて設けられ、前記円弧部に取り付けられる第二部材と、前記隙間に設けられ、前記隙間のうち前記径方向内側の第１領域と、前記隙間のうち前記径方向外側の第２領域とを連通する複数の連通孔を有する第三部材と、前記第１領域を密封するとともに前記第一支持部を前記径方向外側から支持する密封支持部と、前記第二部材の前記径方向内側に取り付けられ、前記第２領域を密封する密封部材と、を備え、前記密封部材は、前記第２領域との境界に薄膜のダイヤフラムを備え、前記密封部材により形成された空間にガスが封入され、前記ダイヤフラムは、前記ガスと前記第２領域を流通する前記油の圧力差によって前記径方向に変形可能である。 (21) In some embodiments, the squeeze film damper includes an inner member that supports the bearing portion, and a perforated member provided on the outer peripheral side of the inner member with a predetermined gap from the inner member. wherein said perforated member comprises at least one detachable unit and an arc portion having a space into which said unit can be inserted, said unit being a radially inner end, and a first member that is in contact with the inner member; a second member that is a radially outer end portion and is provided with a gap from the first member and is attached to the arc portion; a third member having a plurality of communication holes communicating between a radially inner first region of the gap and a radially outer second region of the gap; A sealing support portion that supports one support portion from the radially outer side; and a sealing member that is attached to the radially inner side of the second member and seals the second region; A thin film diaphragm is provided at the boundary between the two regions, gas is sealed in the space formed by the sealing member, and the diaphragm moves in the radial direction due to the pressure difference between the gas and the oil flowing through the second region. It is transformable.

上記（２１）の構成によれば、交換可能なユニットを設けることにより、ユニットに適用するガス圧を調整すること、油種を変更すること、油の脱気の程度を調整することにより、スクイズフィルムダンパの減衰性能を調整することができる。 According to the configuration (21) above, by providing a replaceable unit, the squeeze gas pressure applied to the unit can be adjusted, the type of oil can be changed, and the degree of oil degassing can be adjusted. The damping performance of the film damper can be adjusted.

（２２）本開示の少なくとも一実施形態に係る回転機械は、上記（１）～（２１）の何れか一つに記載のスクイズフィルムダンパと、ロータ軸と、前記ロータ軸を回転可能に支持する軸受部とを備えている。 (22) A rotary machine according to at least one embodiment of the present disclosure includes the squeeze film damper according to any one of (1) to (21) above, a rotor shaft, and rotatably supporting the rotor shaft. and a bearing.

上記（２２）の構成によれば、上記（１）～（２１）の何れか一つで述べたスクイズフィルムダンパによる減衰効果を備えた回転機械を得ることができる。 According to the configuration (22) above, it is possible to obtain a rotary machine having the damping effect of the squeeze film damper described in any one of (1) to (21) above.

本開示の少なくとも一実施形態によれば、簡易な構成でスクイズフィルムダンパの減衰性能の向上を図ることができる。 According to at least one embodiment of the present disclosure, it is possible to improve damping performance of a squeeze film damper with a simple configuration.

第一実施形態に係る回転機械を示す側断面図である。BRIEF DESCRIPTION OF THE DRAWINGS It is a sectional side view which shows the rotating machine which concerns on 1st embodiment. 第一実施形態に係る回転機械を示す軸方向断面図であり、図１のＡ－Ａ線断面図である。FIG. 2 is an axial cross-sectional view showing the rotating machine according to the first embodiment, and is a cross-sectional view taken along the line AA of FIG. 1; 第一実施形態に係るスクイズフィルムダンパの部分拡大図である。3 is a partially enlarged view of the squeeze film damper according to the first embodiment; FIG. 第一実施形態の他の例に係るスクイズフィルムダンパの部分拡大図であり、内部流路における一の軸方向延在部に一の径方向延在部を配置した場合を示す図である。FIG. 10 is a partially enlarged view of the squeeze film damper according to another example of the first embodiment, showing a case where one radially extending portion is arranged in one axially extending portion of the internal flow path. 第一実施形態の他の例に係るスクイズフィルムダンパの部分拡大図であり、同複数の径方向延在部を配置した場合を示す図である。FIG. 6 is a partially enlarged view of the squeeze film damper according to another example of the first embodiment, showing a case where the plurality of radially extending portions are arranged; 第一実施形態の他の例に係るスクイズフィルムダンパの部分拡大図である。FIG. 5 is a partially enlarged view of a squeeze film damper according to another example of the first embodiment; 第一実施形態の他の例に係るスクイズフィルムダンパを示す概略図である。FIG. 5 is a schematic diagram showing a squeeze film damper according to another example of the first embodiment; 第一実施形態の他の例における連通孔を示す概略図である。It is a schematic diagram showing a communicating hole in another example of the first embodiment. 第一実施形態の他の例における連通孔を示す概略図である。It is a schematic diagram showing a communicating hole in another example of the first embodiment. 第一実施形態の他の例における連通孔を示す概略図である。It is a schematic diagram showing a communicating hole in another example of the first embodiment. 第一実施形態の他の例における連通孔を示す概略図である。It is a schematic diagram showing a communicating hole in another example of the first embodiment. 第一実施形態の他の例における連通孔を示す概略図である。It is a schematic diagram showing a communicating hole in another example of the first embodiment. 第一実施形態の他の例における連通孔を示す概略図である。It is a schematic diagram showing a communicating hole in another example of the first embodiment. 第一実施形態の一例に係る回転機械（蒸気タービン）を示す概略図である。BRIEF DESCRIPTION OF THE DRAWINGS It is the schematic which shows the rotating machine (steam turbine) which concerns on an example of 1st embodiment. 第一実施形態の一例に係る回転機械（圧縮機）を示す図である。It is a figure which shows the rotary machine (compressor) which concerns on an example of 1st embodiment. 第二実施形態に係る回転機械を示す軸方向断面図である。It is an axial sectional view showing a rotary machine according to a second embodiment. （ａ）は、第二実施形態に係るシール部材及び支持機構を示す図である。（ｂ），（ｃ）はそれぞれ第に実施形態の他の例に係るシール部材及び芯保持機構を示す図である。(a) is a figure which shows the sealing member and support mechanism which concern on 2nd embodiment. (b) and (c) are diagrams showing a seal member and a lead holding mechanism according to other examples of the first embodiment, respectively. 第三実施形態に係るスクイズフィルムダンパの要部拡大図である。FIG. 11 is an enlarged view of a main part of a squeeze film damper according to a third embodiment; 第三実施形態の他の例に係る回転機械を示す軸方向断面図である。FIG. 11 is an axial cross-sectional view showing a rotating machine according to another example of the third embodiment;

［第一実施形態］
以下、添付図面を参照して本発明の第一実施形態について説明する。ただし、実施形態として記載されている又は図面に示されている構成部品の寸法、材質、形状、その相対的配置等は、本発明の範囲をこれに限定する趣旨ではなく、単なる説明例にすぎない。
例えば、「ある方向に」、「ある方向に沿って」、「平行」、「直交」、「中心」、「同心」或いは「同軸」等の相対的或いは絶対的な配置を表す表現は、厳密にそのような配置を表すのみならず、公差、若しくは、同じ機能が得られる程度の角度や距離をもって相対的に変位している状態も表すものとする。
例えば、「同一」、「等しい」及び「均質」等の物事が等しい状態であることを表す表現は、厳密に等しい状態を表すのみならず、公差、若しくは、同じ機能が得られる程度の差が存在している状態も表すものとする。
例えば、四角形状や円筒形状等の形状を表す表現は、幾何学的に厳密な意味での四角形状や円筒形状等の形状を表すのみならず、同じ効果が得られる範囲で、凹凸部や面取り部等を含む形状も表すものとする。
一方、一の構成要素を「備える」、「含む」、又は、「有する」という表現は、他の構成要素の存在を除外する排他的な表現ではない。 [First embodiment]
A first embodiment of the present invention will be described below with reference to the accompanying drawings. However, the dimensions, materials, shapes, relative arrangements, etc. of the components described as embodiments or shown in the drawings are not intended to limit the scope of the present invention, and are merely illustrative examples. do not have.
For example, expressions denoting relative or absolute arrangements such as "in a direction", "along a direction", "parallel", "perpendicular", "center", "concentric" or "coaxial" are strictly not only represents such an arrangement, but also represents a state of relative displacement with a tolerance or an angle or distance to the extent that the same function can be obtained.
For example, expressions such as "identical", "equal", and "homogeneous", which express that things are in the same state, not only express the state of being strictly equal, but also have tolerances or differences to the extent that the same function can be obtained. It shall also represent the existing state.
For example, expressions that express shapes such as squares and cylinders do not only represent shapes such as squares and cylinders in a geometrically strict sense, but also include irregularities and chamfers to the extent that the same effect can be obtained. The shape including the part etc. shall also be represented.
On the other hand, the expressions "comprising", "including", or "having" one component are not exclusive expressions excluding the presence of other components.

図１は、第一実施形態に係る回転機械を示す側断面図である。図２は、第一実施形態に係る回転機械を示す軸方向断面図であり、図１のＡ―Ａ線断面図である。図３は、第一実施形態に係るスクイズフィルムダンパの部分拡大図である。
図１～図３に非限定的に例示するように、第一実施形態に係る回転機械１は、回転するロータ軸２と、ロータ軸２を回転可能に支持する軸受部８と、軸受部８の振動を抑制するためのスクイズフィルムダンパ１０と、を備えている。 FIG. 1 is a side sectional view showing a rotating machine according to the first embodiment. FIG. 2 is an axial cross-sectional view showing the rotating machine according to the first embodiment, and is a cross-sectional view along line AA in FIG. FIG. 3 is a partially enlarged view of the squeeze film damper according to the first embodiment.
As non-limitingly illustrated in FIGS. 1 to 3, the rotary machine 1 according to the first embodiment includes a rotating rotor shaft 2, a bearing portion 8 that rotatably supports the rotor shaft 2, and a bearing portion 8 and a squeeze film damper 10 for suppressing the vibration of.

回転機械１は、例えば、作動流体からの流体力を動翼３に受けてロータ軸２が回転するガスタービン、蒸気タービン（例えば図１２Ａ参照）、ターボチャージャー、又はインペラ５を回転させて流体を圧送する圧縮機（例えば図１２Ｂ参照）、或いはエンジン等、回転軸（例えばロータ軸２）を有する種々の機械を含んでもよい。なお、図１２Ｂは、ギア４を介して連結されたロータ軸２を軸受部８で支持するように構成されたギアド圧縮機を模式的に示している。 The rotary machine 1 is, for example, a gas turbine, a steam turbine (for example, see FIG. 12A), a turbocharger, or a turbocharger in which a rotor shaft 2 rotates by receiving fluid force from a working fluid on moving blades 3, or rotates an impeller 5 to generate fluid. It may include various machines having a rotating shaft (eg, rotor shaft 2), such as a pumping compressor (see, eg, FIG. 12B), or an engine. Note that FIG. 12B schematically shows a geared compressor configured so that the rotor shaft 2 connected via the gear 4 is supported by the bearing portion 8 .

ロータ軸２は、軸受部８に支持されて、その中心軸Ｏが実質的に水平方向に沿って延在するように配置され得る。このロータ軸２は、種々の芯保持機構により、その中心軸Ｏを実質的に保持し得るように構成されていてもよい。なお、ロータ軸２の中心軸Ｏを維持するための芯保持機構について、ここでは説明を省略する。
上記ロータ軸２の外周には、周方向に沿って複数の動翼３を有する一以上の動翼段（図示略）が取り付けられていてもよい。 The rotor shaft 2 is supported by the bearings 8 and can be arranged such that its central axis O extends substantially along the horizontal direction. The rotor shaft 2 may be configured such that its central axis O can be substantially held by various core holding mechanisms. Description of the core holding mechanism for maintaining the central axis O of the rotor shaft 2 is omitted here.
One or more rotor blade stages (not shown) having a plurality of rotor blades 3 may be attached to the outer periphery of the rotor shaft 2 along the circumferential direction.

軸受部８は、例えば、ロータ軸２を径方向から支持するジャーナル軸受であってもよい。このような軸受部８は、例えば、ロータ軸２の軸方向視における断面形状が環状の軸受メタルとして構成され得る。また、軸受部８は、円筒状又は環状の軸受部材を周方向において複数（例えば２～４つ）に分割することで、上記ロータ軸２の軸方向視における断面形状が円弧状又は扇形を呈する軸受パッドとして構成されてもよい。軸受部８としての軸受パッドは、傾動しない固定型の他、例えばピボット９（図６参照）により傾動可能に支持された所謂ティルティングパッド軸受を含んでもよい。
各軸受部８は、略水平方向に延在するロータ軸２の少なくとも下側部分を支持するように配置される。例えば一つの軸受部８でロータ軸２の下部を支持するように構成してもよいし、複数の軸受部８により、ロータ軸２の外周を複数の方向から支持する構成としてもよい。
なお、図２では、軸方向視にて左右及び上下に分割された４つの軸受部８でロータ軸２の外周を摺動可能に支持する構成例を示しているが、周方向における軸受部８の分割数、及び、分割された各軸受部８（又はそれらの隙間）の周方向における配置は、各々の軸受部８が適用される回転機械１の仕様に応じて任意に設定され得る。
そして、ロータ軸２と軸受部８との間に図示しない給油ラインから油６４を供給することにより、ロータ軸２が回転した際に該ロータ軸２と軸受部８との間に油膜が形成され、ロータ軸２と軸受部８との直接的な金属接触が防止されてロータ軸２が円滑に回転できるようになっている。 The bearing portion 8 may be, for example, a journal bearing that radially supports the rotor shaft 2 . Such a bearing portion 8 can be configured, for example, as a bearing metal having an annular cross-sectional shape when viewed in the axial direction of the rotor shaft 2 . The bearing portion 8 is formed by dividing a cylindrical or annular bearing member into a plurality (for example, 2 to 4 pieces) in the circumferential direction, so that the cross-sectional shape of the rotor shaft 2 when viewed in the axial direction is arcuate or fan-shaped. It may be configured as a bearing pad. The bearing pad as the bearing portion 8 may include a so-called tilting pad bearing that is tiltably supported by a pivot 9 (see FIG. 6), in addition to a fixed type that does not tilt.
Each bearing portion 8 is arranged to support at least a lower portion of the rotor shaft 2 extending substantially horizontally. For example, one bearing portion 8 may support the lower portion of the rotor shaft 2 , or a plurality of bearing portions 8 may support the outer circumference of the rotor shaft 2 from a plurality of directions.
Note that FIG. 2 shows a configuration example in which the outer circumference of the rotor shaft 2 is slidably supported by four bearing portions 8 divided into left, right, and top and bottom when viewed in the axial direction. can be arbitrarily set according to the specifications of the rotating machine 1 to which each bearing 8 is applied.
By supplying oil 64 from an oil supply line (not shown) between the rotor shaft 2 and the bearing portion 8, an oil film is formed between the rotor shaft 2 and the bearing portion 8 when the rotor shaft 2 rotates. , direct metallic contact between the rotor shaft 2 and the bearing portion 8 is prevented so that the rotor shaft 2 can rotate smoothly.

続いて、本開示の少なくとも一実施形態に係るスクイズフィルムダンパ１０について図１～図３を参照し詳しく説明する。
図１～図３に非限定的に例示するように、本開示の少なくとも一実施形態に係るスクイズフィルムダンパ１０は、上記軸受部８の外周側に設けられた所謂背面ダンパであり、軸受部８を支持する内側部材２０と、周方向に延在する隙間４０を挟んで内側部材２０に対向するように、該内側部材２０の外周側に設けられる外側部材３０と、隙間４０に設けられ、上記隙間４０のうち径方向内側の第１領域４１と、上記隙間４０のうち径方向外側の第２領域４２とを連通する複数の連通孔５１を有する有孔部材５０と、第１領域４１に油６４を供給するための給油路６０と、を備えている。 Next, a squeeze film damper 10 according to at least one embodiment of the present disclosure will be described in detail with reference to FIGS. 1-3.
As non-limitingly illustrated in FIGS. 1 to 3, the squeeze film damper 10 according to at least one embodiment of the present disclosure is a so-called rear damper provided on the outer peripheral side of the bearing portion 8. and an outer member 30 provided on the outer peripheral side of the inner member 20 so as to face the inner member 20 across a gap 40 extending in the circumferential direction. A perforated member 50 having a plurality of communication holes 51 communicating between a radially inner first area 41 of the gap 40 and a radially outer second area 42 of the gap 40 , and oil in the first area 41 . and an oil supply passage 60 for supplying 64.

内側部材２０は、例えば軸受部８の周りに設けられた環状又は円筒状のダンパジャーナル（キャリアリング又は軸受ハウジングとも称する）であってもよい。内側部材２０としての軸受ハウジングは、半円筒状の上側ハウジング２０Ａと半円筒状の下側ハウジング２０Ｂとで構成されていてもよい。この内側部材２０は、ロータ軸２及び軸受部８と同心に配置されていてもよく、軸受部８を当該軸受部８の径方向外側から支持するように構成され得る。 The inner member 20 may be, for example, an annular or cylindrical damper journal (also called a carrier ring or bearing housing) provided around the bearing portion 8 . The bearing housing as the inner member 20 may be composed of a semi-cylindrical upper housing 20A and a semi-cylindrical lower housing 20B. The inner member 20 may be arranged concentrically with the rotor shaft 2 and the bearing portion 8 and may be configured to support the bearing portion 8 from the radially outer side of the bearing portion 8 .

外側部材３０は、内側部材２０の外周面２２を周方向の全域に亘って覆うようにして、該内側部材２０と同心に配置された筒状体（又は環状体）であってもよい。この外側部材３０は、上記内側部材２０との間に所定の隙間４０を隔てて配置され得る。 The outer member 30 may be a cylindrical body (or an annular body) arranged concentrically with the inner member 20 so as to cover the entire circumferential surface 22 of the inner member 20 . The outer member 30 can be arranged with a predetermined gap 40 between the inner member 20 and the outer member 30 .

隙間４０は、周方向の全域に亘って形成されていてもよい（例えば図２参照）。つまり、隙間４０は、内側部材２０と外側部材３０との間に周方向の全域に亘って油膜が形成されるようにして、軸方向視にて環状に構成され得る。このような隙間４０は、回転機械１の停止時において上記周方向の全域に亘って一定の間隔となるように構成されてもよい。
また、隙間４０は、例えば周方向における少なくとも一部の範囲に形成されていてもよい。この場合の隙間４０は、周方向の少なくとも一か所に形成されていてもよいし、周方向の複数箇所に分散して設けられていてもよいし、周方向の少なくとも一部において径方向に重複するように設けられていてもよい。つまり、このような隙間４０を有するスクイズフィルムダンパ１０は、例えば、ＩＳＦＤ（ｉｎｔｅｇｒａｔｅｄ ｓｑｕｅｅｚｅ ｆｉｌｍ ｄａｍｐｅｒ）（Ｒ）を含み得る。 The gap 40 may be formed over the entire circumferential area (see FIG. 2, for example). That is, the gap 40 can be formed in an annular shape when viewed in the axial direction so that an oil film is formed over the entire circumferential area between the inner member 20 and the outer member 30 . Such a gap 40 may be configured to have a constant interval over the entire circumferential direction when the rotary machine 1 is stopped.
Also, the gap 40 may be formed, for example, in at least a partial range in the circumferential direction. The gap 40 in this case may be formed in at least one place in the circumferential direction, may be dispersed in a plurality of places in the circumferential direction, or may be formed radially in at least a part of the circumferential direction. You may provide so that it may overlap. That is, the squeeze film damper 10 having such a gap 40 can include, for example, an integrated squeeze film damper (ISFD) (R).

有孔部材５０は、上記内側部材２０の外周を囲むようにして、該内側部材２０と外側部材３０との隙間４０に遊挿される。この有孔部材５０は、ロータ軸２、軸受部８、内側部材２０及び外側部材３０と同心に配置されていてもよく、内側部材２０の外周よりも大径、且つ、外側部材３０の内周よりも小径の、実質的に円筒状又は環状の部材に形成され得る。有孔部材５０の材料は特に限定しないが、例えば、上記外側部材３０と同等の材料で形成されていてもよい。 The perforated member 50 is loosely inserted into the gap 40 between the inner member 20 and the outer member 30 so as to surround the outer periphery of the inner member 20 . The perforated member 50 may be arranged concentrically with the rotor shaft 2 , the bearing portion 8 , the inner member 20 and the outer member 30 , and has a diameter larger than the outer circumference of the inner member 20 and an inner circumference of the outer member 30 . It can be formed into a substantially cylindrical or annular member of smaller diameter. Although the material of the perforated member 50 is not particularly limited, it may be made of the same material as the outer member 30, for example.

連通孔５１は、所謂オリフィス穴であり、上記第１領域４１と第２領域４２とを連通するようにして、有孔部材５０の軸方向及び周方向に亘って複数設けられる。各連通孔５１は、例えば、軸方向又は周方向に等間隔に並んで配置されていてもよい。 The communication holes 51 are so-called orifice holes, and are provided in plurality in the axial direction and the circumferential direction of the perforated member 50 so as to communicate the first region 41 and the second region 42 . The communication holes 51 may be arranged at equal intervals in the axial direction or the circumferential direction, for example.

上記有孔部材５０を隔てて配置される隙間４０の第１領域４１と第２領域４２とは、ロータ軸２の径方向において実質的に同じ間隔を有していてもよい。 The first region 41 and the second region 42 of the gap 40 arranged across the perforated member 50 may have substantially the same distance in the radial direction of the rotor shaft 2 .

給油路６０は、ロータ軸２の軸方向又は径方向から隙間４０の第１領域４１に油６４を案内し得るように構成される。つまり、本開示のスクイズフィルムダンパ１０は、有孔部材５０の連通孔５１を介して、径方向内側の第１領域４１から径方向外側の第２領域４２に油６４が移動するようになっている。上記給油路６０は、ロータ軸２の軸方向において動翼３に流体力を作用させる作動流体（不図示）の流れ方向における上流側又は下流側に配置され得る。周方向における給油路６０の配置及びその数は特に限定されない。例えば図１には、軸方向において作動流体の流れの上流側に給油路６０を設けた例を非限定的に示している。 The oil supply passage 60 is configured to guide the oil 64 from the axial direction or radial direction of the rotor shaft 2 to the first region 41 of the gap 40 . That is, in the squeeze film damper 10 of the present disclosure, the oil 64 moves from the radially inner first region 41 to the radially outer second region 42 via the communication hole 51 of the perforated member 50 . there is The oil supply passage 60 may be arranged upstream or downstream in the axial direction of the rotor shaft 2 in the direction of flow of working fluid (not shown) that applies fluid force to the rotor blades 3 . The arrangement and number of oil supply passages 60 in the circumferential direction are not particularly limited. For example, FIG. 1 shows a non-limiting example in which an oil supply passage 60 is provided on the upstream side of the flow of working fluid in the axial direction.

以上の構成において、給油路６０を介して隙間４０の第１領域４１に油６４が供給されると、油６４の自重により（例えば周方向の比較的下側の領域）、又は、第１領域４１内に供給された油６４の圧力により、第１領域４１から連通孔５１を介して第２領域４２に油６４が流入し、第１領域４１及び第２領域４２を含む隙間４０に油膜が形成される。
この状態で、例えばロータ軸２の回転に伴い軸受部８及びこれを支持する内側部材２０が振動すると、内側部材２０の外周面２２と有孔部材５０の内周面との間隔、すなわち第１領域４１の間隔が振動に応じて変化する。この間隔の変化により、第１領域４１内の油６４で形成される油膜が軸方向又は周方向に移動し、当該移動に伴う油６４の粘性抵抗に起因した所謂スクイズ作用により圧力が発生し、上記振動に対する減衰効果が得られる。 In the above configuration, when the oil 64 is supplied to the first region 41 of the gap 40 via the oil supply passage 60, the weight of the oil 64 (for example, the relatively lower region in the circumferential direction) or the first region Due to the pressure of the oil 64 supplied into the interior 41, the oil 64 flows from the first region 41 into the second region 42 via the communication hole 51, and an oil film is formed in the gap 40 including the first region 41 and the second region 42. It is formed.
In this state, for example, when the bearing 8 and the inner member 20 supporting it vibrate due to the rotation of the rotor shaft 2, the distance between the outer peripheral surface 22 of the inner member 20 and the inner peripheral surface of the perforated member 50, that is, the first The spacing of the regions 41 changes in response to vibration. Due to the change in this interval, the oil film formed by the oil 64 in the first region 41 moves in the axial direction or the circumferential direction, and pressure is generated by the so-called squeeze action caused by the viscous resistance of the oil 64 accompanying the movement, A damping effect against the above vibration is obtained.

さらに、本開示のスクイズフィルムダンパ１０によれば、内側部材２０と外側部材３０との隙間４０に、径方向内側の第１領域４１と径方向外側の第２領域４２とを連通する複数の連通孔５１を含む有孔部材５０を配置した構成により、例えばロータ軸２の回転に伴い軸受部８及びこれを支持する内側部材２０が振動した際には、内側部材２０の外周面２２に追従して油６４の一部が有孔部材５０の連通孔５１を通過し、当該通過の際に油６４が抵抗力を受ける。すなわち、従来のスクイズ効果に加えて、有孔部材５０の連通孔５１を通過する油６４が上記軸受部８及び内側部材２０の振動に対するダンパとして機能するから、簡易な構成でスクイズフィルムダンパ１０の減衰性能を大幅に向上させることができるのである。
なお、有孔部材５０の減衰効果は、個々の有孔部材５０が搭載される回転機械１の振動特性に応じて、例えば連通孔５１の数、大きさ、配置、配向、形状等を任意に設定することで調整し得る。 Further, according to the squeeze film damper 10 of the present disclosure, the gap 40 between the inner member 20 and the outer member 30 has a plurality of communicating portions that connect the radially inner first region 41 and the radially outer second region 42 . Due to the configuration in which the perforated member 50 including the hole 51 is arranged, for example, when the bearing portion 8 and the inner member 20 supporting the bearing portion 8 vibrate due to the rotation of the rotor shaft 2, the outer peripheral surface 22 of the inner member 20 is followed. As a result, part of the oil 64 passes through the communication holes 51 of the perforated member 50, and the oil 64 receives a resistance force during the passage. That is, in addition to the conventional squeeze effect, the oil 64 passing through the communication hole 51 of the perforated member 50 functions as a damper against the vibration of the bearing portion 8 and the inner member 20, so that the squeeze film damper 10 can be realized with a simple structure. Damping performance can be greatly improved.
The damping effect of the perforated member 50 depends on the vibration characteristics of the rotating machine 1 on which each perforated member 50 is mounted. You can adjust it by setting

また、本実施形態の幾つかの例において、隙間４２は、軸方向端の少なくとも一部が開放されていてもよい（図１参照）。この場合、少なくとも第２領域４２の軸方向端の少なくとも一部が開放されていればよい。つまり、第１領域４１の軸方向端は開放されていてもよいし閉塞されていてもよい。このような構成は、例えば軸受部８に対して軸方向の一方（例えば作動流体の流れ方向の上流側）及び他方（同下流側）に設けられる図示しないエンドプレートの配置や形状により任意に設定し得る。なお、第２領域４２の軸方向端は、作動流体の流れ方向の上流側又は下流側のうち何れか一方が開放され他方が閉塞されていてもよいし、周方向の一部が開放された構成としてもよい。
このように隙間４２の軸方向端の少なくとも一部を開放した構成によれば、第１領域４１に供給され、連通孔５１を介して第２領域４２に移動した油６４を、該第２領域４２の開放された軸方向端から排出することができる。 Also, in some examples of the present embodiment, the gap 42 may be open at least partially at its axial end (see FIG. 1). In this case, at least part of the axial end of the second region 42 should be open. That is, the axial end of the first region 41 may be open or closed. Such a configuration can be arbitrarily set, for example, by the arrangement and shape of end plates (not shown) provided on one side (for example, the upstream side in the flow direction of the working fluid) and the other side (for example, the downstream side) in the axial direction with respect to the bearing portion 8. can. The axial end of the second region 42 may be open on either one of the upstream side and the downstream side in the flow direction of the working fluid and the other may be closed, or may be partially open in the circumferential direction. may be configured.
According to the configuration in which at least a part of the axial end of the gap 42 is opened in this way, the oil 64 supplied to the first region 41 and moved to the second region 42 via the communication hole 51 is transferred to the second region. The open axial ends of 42 can be discharged.

本実施形態の幾つかの例では、内側部材２０及び有孔部材５０間の寸法Ｄと連通孔５１の直径ｄとが０．１ｄ＜Ｄ＜１０ｄを満たしてもよい（図３参照）。
連通孔５１を通過する油６４による減衰効果は、連通孔５１の径が大きすぎても小さすぎても適切に得られない虞がある。
この点、上記の構成によれば、内側部材２０と有孔部材５０との隙間（第１領域４１）の寸法Ｄに対して連通孔５１の直径ｄが同一オーダーの範囲を満たすから、個々の有孔部材５０が搭載される回転機械１の振動特性に応じて上記連通孔５１の数、大きさ、配置、配向、形状等を任意に設定することにより、適切な減衰特性に調整することができる。 In some examples of this embodiment, the dimension D between the inner member 20 and the perforated member 50 and the diameter d of the communication hole 51 may satisfy 0.1d<D<10d (see FIG. 3).
The damping effect of the oil 64 passing through the communication hole 51 may not be properly obtained if the diameter of the communication hole 51 is too large or too small.
In this regard, according to the above configuration, the diameter d of the communicating hole 51 satisfies the range of the same order as the dimension D of the gap (the first region 41) between the inner member 20 and the perforated member 50. By arbitrarily setting the number, size, arrangement, orientation, shape, etc. of the communication holes 51 according to the vibration characteristics of the rotary machine 1 on which the perforated member 50 is mounted, it is possible to adjust the damping characteristics appropriately. can.

図４Ａ及び図４Ｂは、第一実施形態の他の例に係るスクイズフィルムダンパの部分拡大図である。図４Ａ及び図４Ｂに非限定的に例示するように、幾つかの実施形態における給油路６０は、内側部材２０の軸方向端部２４から第１領域４１に油６４を導く内部流路６２を含んでいてもよい。
内部流路６２は、内側部材２０の周方向において少なくとも一部に形成されていればよく、該周方向における複数箇所に（例えば等間隔に）形成されていてもよい。
このように内部流路６２を設けた構成によれば、内側部材２０の軸方向端部２４から内部流路６２に油６４を供給することで、第１領域４１に油６４を供給することができるから、例えば外側部材３０及び有孔部材５０を径方向に貫通するような油６４の経路を設ける必要がない。つまり、内側部材２０の軸方向端部２４から内部流路６２に油６４を供給する簡易な構成により、本開示の何れかの実施形態で述べる効果を享受することができる。 4A and 4B are partial enlarged views of squeeze film dampers according to other examples of the first embodiment. As non-limitingly illustrated in FIGS. 4A and 4B , oil feed passage 60 in some embodiments includes an internal flow passage 62 that directs oil 64 from axial end 24 of inner member 20 to first region 41 . may contain.
The internal flow path 62 may be formed at least partially in the circumferential direction of the inner member 20, and may be formed at a plurality of locations (for example, at equal intervals) in the circumferential direction.
According to the configuration in which the internal flow path 62 is provided in this manner, the oil 64 can be supplied to the first region 41 by supplying the oil 64 from the axial end portion 24 of the inner member 20 to the internal flow path 62 . Thus, there is no need to route oil 64 through, for example, the outer member 30 and the perforated member 50 radially. That is, with a simple configuration for supplying oil 64 from the axial end portion 24 of the inner member 20 to the internal flow path 62, the effects described in any of the embodiments of the present disclosure can be enjoyed.

さらに、第一実施形態の幾つかの例における内部流路６２は、軸方向端部２４から軸方向に延在する軸方向延在部６２Ａと、該軸方向延在部６２Ａに連続して径方向に延在する径方向延在部６２Ｂとを含んでいてもよい（図４Ａ及び図４Ｂ参照）。
このように構成すれば、内側部材２０の軸方向端部２４から内部流路６２に供給された油６４が、軸方向延在部６２Ａと径方向延在部６２Ｂとを経由して第１領域４１に供給される。よって、内部流路６２の設計の自由度を向上させることができる。
なお、このように軸方向延在部６２Ａと径方向延在部６２Ｂとを含む内部流路６２の場合、一の軸方向延在部６２Ａにつき一（図４Ａ参照）又は複数（図４Ｂ参照）の径方向延在部６２Ｂが形成されてもよい。このようにすれば、軸方向延在部６２Ａに導かれた油６４は、当該軸方向延在部６２Ａに連続して径方向に延在する一又は複数の径方向延在部６２Ｂを介して第１領域４１に供給される。よって、一の軸方向延在部６２Ａに連続して所望の数の径方向延在部６２Ｂを形成することにより、内側部材２０のうち内部流路６２が設けられた周方向位置において、軸方向における一又は複数の適切な位置から第１領域４１に油６４を供給して油膜を形成することができる。
さらに、内部流路６２は、内側部材２０の内部において該内側部材２０の周方向に油６４を導く周方向延在部（図示省略）を含んでいてもよい。 Further, the internal flow passage 62 in some examples of the first embodiment includes an axially extending portion 62A extending axially from the axial end portion 24 and a diametrical portion continuous with the axially extending portion 62A. and a radially extending portion 62B (see FIGS. 4A and 4B).
With this configuration, the oil 64 supplied from the axial end portion 24 of the inner member 20 to the internal flow path 62 flows through the axially extending portion 62A and the radially extending portion 62B into the first region. 41. Therefore, the degree of freedom in designing the internal flow path 62 can be improved.
In the case of the internal flow path 62 including the axially extending portion 62A and the radially extending portion 62B, one (see FIG. 4A) or a plurality (see FIG. 4B) per axially extending portion 62A. radially extending portion 62B may be formed. In this way, the oil 64 guided to the axially extending portion 62A is passed through one or more radially extending portions 62B that are continuous with the axially extending portion 62A and extend in the radial direction. It is supplied to the first area 41 . Therefore, by forming a desired number of radially extending portions 62B continuously from one axially extending portion 62A, the axial Oil 64 can be supplied to the first region 41 from one or more suitable locations in to form an oil film.
Further, the internal flow path 62 may include a circumferentially extending portion (not shown) that guides the oil 64 in the circumferential direction of the inner member 20 inside the inner member 20 .

図５は、第一実施形態の他の例に係るスクイズフィルムダンパの部分拡大図である。図５に非限定的に例示するように、幾つかの実施形態における給油路６０は、外側部材３０及び有孔部材５０を径方向に貫通して油６４を第１領域４１に供給するように構成されていてもよい。このような給油路６０は、上記周方向又は軸方向において一つ又は複数設けられていてもよい。
このように、外側部材３０及び有孔部材５０を径方向に貫通する給油路６０を介して第１領域４１に油６４が供給される構成によれば、内側部材２０の軸方向における給油路６０の接地面積を抑制した簡易な構成により、本開示の効果を享受することができる。 FIG. 5 is a partially enlarged view of a squeeze film damper according to another example of the first embodiment. As non-limitingly illustrated in FIG. 5 , oil feed passage 60 in some embodiments extends radially through outer member 30 and perforated member 50 to supply oil 64 to first region 41 . may be configured. One or a plurality of such oil supply passages 60 may be provided in the circumferential direction or the axial direction.
Thus, according to the configuration in which the oil 64 is supplied to the first region 41 via the oil supply passage 60 radially penetrating the outer member 30 and the perforated member 50, the oil supply passage 60 in the axial direction of the inner member 20 It is possible to enjoy the effects of the present disclosure with a simple configuration that suppresses the ground contact area.

図６は、第一実施形態の他の例に係るスクイズフィルムダンパを示す概略図である。図６に非限定的に例示するように、幾つかの実施形態における有孔部材５０は、周方向に間隔を隔てた複数箇所で外側部材３０に支持されていてもよい。
このような構成は、例えば、有孔部材５０と外側部材３０とを固定的に接続する支持部３２を設けることで達成され得る。支持部３２は、例えば有孔部材５０の外周面と外側部材３０の内周面とを接続するように構成してもよいし（図６参照）、有孔部材５０及び外側部材３０の軸方向端部同士を接続するように構成してもよい。有孔部材５０と外側部材３０との間（第２領域４２）に支持部３２を設ける場合、各支持部３２が、軸方向の少なくとも一部に延在するように形成すればよい。
このように有孔部材５０を外側部材３０で支持することにより、有孔部材５０と外側部材３０との相対的な移動を規制することができる。また、周方向に間隔を隔てた複数箇所において有孔部材５０を支持することにより、例えば有孔部材５０を周方向の一か所で支持する場合に比べて両者をより強固に固定することができる。このような構成により、例えば軸受部８及び内側部材２０が振動した際には、外側部材３０に支持された有孔部材５０に対して内側部材２０が相対的に接近及び離反する。よって、内側部材２０が振動する度、有孔部材５０の連通孔５１に油６４を効果的に通過させることができるから、有孔部材５０による減衰効果をより効率的に発揮させることができる。 FIG. 6 is a schematic diagram showing a squeeze film damper according to another example of the first embodiment. As non-limitingly illustrated in FIG. 6, the perforated member 50 in some embodiments may be supported by the outer member 30 at multiple circumferentially-spaced locations.
Such a configuration may be achieved, for example, by providing a support 32 that fixedly connects the perforated member 50 and the outer member 30 . The support portion 32 may be configured, for example, to connect the outer peripheral surface of the perforated member 50 and the inner peripheral surface of the outer member 30 (see FIG. 6), or connect the perforated member 50 and the outer member 30 in the axial direction. It may be configured to connect the ends together. When the support portions 32 are provided between the perforated member 50 and the outer member 30 (the second region 42), each support portion 32 may be formed to extend at least partly in the axial direction.
By supporting the perforated member 50 with the outer member 30 in this manner, relative movement between the perforated member 50 and the outer member 30 can be restricted. In addition, by supporting the perforated member 50 at a plurality of locations spaced apart in the circumferential direction, both members can be fixed more firmly than, for example, when the perforated member 50 is supported at one location in the circumferential direction. can. With such a configuration, for example, when the bearing portion 8 and the inner member 20 vibrate, the inner member 20 relatively approaches and separates from the perforated member 50 supported by the outer member 30 . Therefore, since the oil 64 can be effectively passed through the communication holes 51 of the perforated member 50 every time the inner member 20 vibrates, the damping effect of the perforated member 50 can be exhibited more efficiently.

続いて、連通孔５１の構成例について説明する。
幾つかの例における連通孔５１は、例えば図１～図６に例示するように、円筒状に形成されていてもよい。この場合、連通孔５１は、円筒の中心軸が径方向に沿って延在するように形成されていてもよい（例えば図３参照）。
このように、連通孔５１の形状を、径方向に沿って延在する円筒状とすることにより、簡易な構成で本開示の何れか一つで述べる効果を享受することができる。 Next, a configuration example of the communication hole 51 will be described.
The communication hole 51 in some examples may be formed in a cylindrical shape, as illustrated in FIGS. 1 to 6, for example. In this case, the communication hole 51 may be formed so that the central axis of the cylinder extends along the radial direction (see FIG. 3, for example).
In this way, by making the shape of the communication hole 51 cylindrical extending along the radial direction, it is possible to enjoy the effects described in any one of the present disclosure with a simple configuration.

図７～図１０は、各々、第一実施形態の他の例における連通孔を示す概略図である。
幾つかの例における連通孔５１は、例えば図７に例示するように、径方向において内側より外側が小径に形成されていてもよい。例えば、連通孔５１は、径方向において内側より外側が小径の円錐台状に形成され得る。
このような構成によれば、内側部材２０と外側部材３０とが接近する際、連通孔５１に油６４を容易に流入させることができる。またその際、連通孔５１の出口側である径方向外側が内側より小径に形成されていることで、より高い減衰効果を発揮させることができる。 7 to 10 are schematic diagrams showing communication holes in other examples of the first embodiment.
The communication hole 51 in some examples may be formed to have a smaller diameter on the outside than on the inside in the radial direction, as illustrated in FIG. 7, for example. For example, the communication hole 51 may be formed in a truncated cone shape with a smaller diameter on the outside than on the inside in the radial direction.
With such a configuration, the oil 64 can easily flow into the communication hole 51 when the inner member 20 and the outer member 30 approach each other. Further, in this case, a higher damping effect can be achieved by forming the radially outer side, which is the outlet side, of the communication hole 51 to have a smaller diameter than the inner side.

また、幾つかの例における連通孔５１は、例えば図８に例示するように、径方向において内側より外側が大径に形成されていてもよい。例えば、連通孔５１は、径方向において内側より外側が大径の円錐台状に形成され得る。
この構成によれば、内側部材２０と外側部材３０とが離反する際、連通孔５１に油６４を容易に流入させることができる。またその際、連通孔５１の出口側である径方向内側が外側より小径に形成されていることで、より高い減衰効果を発揮させることができる。 Also, in some examples, the communication hole 51 may be formed so that the outer diameter is larger than the inner diameter in the radial direction, as illustrated in FIG. 8, for example. For example, the communication hole 51 may be formed in a truncated cone shape having a larger diameter on the outside than on the inside in the radial direction.
According to this configuration, the oil 64 can easily flow into the communication hole 51 when the inner member 20 and the outer member 30 are separated from each other. Further, in this case, a higher damping effect can be achieved by forming the radially inner side, which is the outlet side, of the communication hole 51 to have a smaller diameter than the outer side.

また、幾つかの例における連通孔５１は、例えば図９に例示するように、径方向外側の円筒部５２と該円筒部５２における径方向の内側端に連続し径方向内側に向けて拡開されたテーパ部５３とを含んでいてもよい。
このような構成によれば、径方向に沿って円筒部５２とテーパ部５３とを含む複数の連通孔５１を含んだ有孔部材５０により、本開示の何れか一つで述べた効果を享受することができる。 9, the communication hole 51 in some examples is connected to the radially outer cylindrical portion 52 and the radially inner end of the cylindrical portion 52 and expands radially inward. and a tapered portion 53 .
According to such a configuration, the perforated member 50 including the plurality of communication holes 51 including the cylindrical portion 52 and the tapered portion 53 along the radial direction provides the effects described in any one of the present disclosure. can do.

さらに、幾つかの例では、例えば図１０に例示するように、少なくとも有孔部材５０において最も軸方向端部２４側に配置された連通孔５１の中心軸５１Ａが、径方向において内側より外側が軸方向端部２４に近接するように径方向から傾斜していてもよい。
振動により、筒状の外側部材３０に内接するようにして内側部材２０が接近する際、両者の隙間４０に介在する油６４は周方向のほか軸方向にも移動する。
この点、連通孔５１の中心軸５１Ａが、径方向において内側より外側が軸方向端部２４側に近接するように径方向から傾斜した構成によれば、軸方向端部２４側に押し出されることで軸方向の端部側に向かう速度成分を有する油６４を、連通孔５１に容易に流入させることができる。よって、連通孔５１による減衰効果をより効果的に発揮させることができる。 Furthermore, in some examples, for example, as illustrated in FIG. 10, at least the central axis 51A of the communication hole 51 arranged closest to the axial end 24 side in the perforated member 50 is positioned radially outward from the inner side. It may be radially tapered to be proximate the axial end 24 .
When the inner member 20 approaches the cylindrical outer member 30 so as to be inscribed with the vibration due to vibration, the oil 64 intervening in the gap 40 between the two moves not only in the circumferential direction but also in the axial direction.
In this regard, if the central axis 51A of the communication hole 51 is inclined from the radial direction so that the outer side is closer to the axial end portion 24 side than the inner side in the radial direction, it will be pushed out to the axial end portion 24 side. , the oil 64 having a velocity component directed toward the ends in the axial direction can be easily caused to flow into the communication hole 51 . Therefore, the damping effect of the communication hole 51 can be exhibited more effectively.

さらに、幾つかの例における連通孔５１は、例えば、図１１（ａ），（ｂ）に例示するように、スリット８８であっても良い。このように、連通孔５１を、スリット８８とすることにより、簡易な構成で本開示の何れか一つで述べる効果を享受することができる。なお、スリット８８の配置の仕方に特に制限はなく、図１１（ａ）に示すように、複数のスリット８８の長手方向が同じ方向を向くように配置しても良いし、図１１（ｂ）に示すように、スリット８８の長手方向が異なる方向を向くように配置しても良い。 Furthermore, the communication holes 51 in some examples may be slits 88, for example, as illustrated in FIGS. 11(a) and 11(b). In this way, by using the communication hole 51 as the slit 88, it is possible to enjoy the effect described in any one of the present disclosure with a simple configuration. There is no particular limitation on how the slits 88 are arranged, and as shown in FIG. , the longitudinal direction of the slits 88 may be arranged in different directions.

以上、本開示の第一実施形態について、図面を参照しながら説明した。なお、本開示は上述した実施形態に限定されることはなく、上述した実施形態に変形を加えた形態や、これらの形態を適宜組み合わせた形態も含む。例えば、連通孔５１の形状、個数、配置、配置間隔等は特に制限されない。 The first embodiment of the present disclosure has been described above with reference to the drawings. Note that the present disclosure is not limited to the above-described embodiments, and includes modifications of the above-described embodiments and modes in which these modes are combined as appropriate. For example, the shape, number, arrangement, arrangement interval, etc. of the communication holes 51 are not particularly limited.

［第二実施形態］
以下、本開示の第二実施形態について、図１３及び図１４を参照して説明する。第二実施形態では、第一実施形態と同様の構成要素には同一の符号を付して詳細な説明を省略する。図１３は、本開示の第二実施形態に係る回転機械を示す軸方向断面図である。図１４（ａ）は、本発明の第二実施形態に係るシール部材及び支持機構を示す図である。（ｂ），（ｃ）はそれぞれ第二実施形態の他の例に係るシール部材及び支持機構を示す図である。 [Second embodiment]
A second embodiment of the present disclosure will be described below with reference to FIGS. 13 and 14. FIG. In the second embodiment, components similar to those in the first embodiment are denoted by the same reference numerals, and detailed descriptions thereof are omitted. FIG. 13 is an axial cross-sectional view showing a rotary machine according to a second embodiment of the present disclosure; FIG. 14(a) is a diagram showing a sealing member and a support mechanism according to a second embodiment of the present invention. (b) and (c) are diagrams showing a sealing member and a support mechanism according to other examples of the second embodiment, respectively.

図１３に示すように、第二実施形態では、有孔部材５４のうち、連通孔５１が設けられた領域が、径方向内側に突出することによって、凸部６５が形成されている。凸部６５は、周方向に間隔を空けて複数が設けられる。この時、凸部６５と内側部材２０との間の隙間に第１領域４１が形成され、凸部６５の径方向外側に第２領域４２が形成される。このとき、周方向に隣り合う凸部６５の間の領域が図示しない外側部材に取り付けられることにより固定される。また、内側部材２０の内周面のうち、凸部６５と径方向に対向する部分は、平坦になっている。 As shown in FIG. 13, in the second embodiment, the area of the perforated member 54 in which the communication hole 51 is provided protrudes radially inward, thereby forming the convex portion 65 . A plurality of protrusions 65 are provided at intervals in the circumferential direction. At this time, the first region 41 is formed in the gap between the convex portion 65 and the inner member 20 , and the second region 42 is formed radially outside the convex portion 65 . At this time, the regions between the convex portions 65 adjacent in the circumferential direction are fixed by being attached to an outer member (not shown). A portion of the inner peripheral surface of the inner member 20 that faces the convex portion 65 in the radial direction is flat.

凸部６５は、連通孔５１のほかに、第１領域４１を密封するとともに、内側部材２０を径方向外側から支持する密封支持部６９を有する。本実施形態の場合、図１４（ａ）に示すように、密封支持部６９は、伸縮性を有する材料から形成され、径方向に伸縮可能なベローズ７２である。ベローズ７２は、第１領域４１の軸方向端部及び周方向端部に配置されることにより、第１領域４１を周方向及び軸方向に密封している。また、ベローズ７２の径方向における一端は、凸部６５と接触し、他端は、内側部材２０の外周面２２と接触している。これによりベローズ７２は、第１領域４１の間隔の変化によって径方向に伸縮可能であり、内側部材２０を径方向外側から支持している。この時、第１領域４１は、ベローズ７２によって密封されているが、第２領域４２の軸方向端部は解放されている。 In addition to the communication hole 51 , the convex portion 65 has a sealing support portion 69 that seals the first region 41 and supports the inner member 20 from the radially outer side. In this embodiment, as shown in FIG. 14(a), the sealing support 69 is a bellows 72 that is made of an elastic material and that is radially elastic. The bellows 72 are arranged at the axial end and the circumferential end of the first region 41 to seal the first region 41 in the circumferential and axial directions. One end of the bellows 72 in the radial direction is in contact with the convex portion 65 and the other end is in contact with the outer peripheral surface 22 of the inner member 20 . Accordingly, the bellows 72 can expand and contract in the radial direction by changing the interval of the first regions 41, and supports the inner member 20 from the radial outside. At this time, the first region 41 is sealed by the bellows 72, but the axial ends of the second region 42 are open.

連通孔５１は、第一実施形態で述べた構成が適用される。一例には、第１実施形態で述べたオリフィス穴のような径方向に沿って円筒形に形成された構成であっても良いし、スリット８８であっても良い。連通孔５１は、凸部６５の内周面に規則的に複数個が配置されている。 The configuration described in the first embodiment is applied to the communication hole 51 . For example, it may be a configuration formed cylindrical along the radial direction like the orifice hole described in the first embodiment, or it may be a slit 88 . A plurality of communication holes 51 are regularly arranged on the inner peripheral surface of the projection 65 .

以上の構成において、図示しない給油路により、第１領域４１に油６４を供給すると、油６４の自重により、又は、第１領域４１内に供給された油６４の圧力により、第１領域４１から連通孔５１を介して第２領域４２に油６４が流入し、第１領域４１及び第２領域４２を含む隙間４０に油膜が形成される。なお、給油路は、一例には、第一実施形態で述べた給油路６０が適用される。 In the above configuration, when the oil 64 is supplied to the first region 41 through an oil supply passage (not shown), the weight of the oil 64 or the pressure of the oil 64 supplied into the first region 41 causes the oil 64 to flow out of the first region 41. The oil 64 flows into the second area 42 through the communication hole 51 and forms an oil film in the gap 40 including the first area 41 and the second area 42 . As an example of the oil supply path, the oil supply path 60 described in the first embodiment is applied.

この状態で、例えばロータ軸２の回転に伴い軸受部８及びこれを支持する内側部材２０が振動すると、内側部材２０の外周面２２と凸部６５の内周面との間隔、すなわち第１領域４１の間隔が振動に応じて変化する。この間隔の変化により、第１領域４１内の油６４の粘性抵抗に起因した所謂スクイズ作用により圧力が発生し、上記振動に対する減衰効果が得られる。 In this state, for example, when the bearing portion 8 and the inner member 20 supporting it vibrate due to the rotation of the rotor shaft 2, the distance between the outer peripheral surface 22 of the inner member 20 and the inner peripheral surface of the projection 65, that is, the first region The spacing of 41 changes in response to vibration. Due to the change in this interval, pressure is generated by a so-called squeezing action caused by the viscous resistance of the oil 64 in the first region 41, and a damping effect on the vibration is obtained.

さらに、上記の構成によれば、凸部６５の径方向内側の第１領域４１と径方向外側の第２領域４２とを連通する複数の連通孔５１を含む有孔部材５４を配置した構成により、例えばロータ軸２の回転に伴い軸受部８及びこれを支持する内側部材２０が振動した際には、内側部材２０の外周面２２に追従して油６４の一部が有孔部材５４の連通孔５１を通過し、当該通過の際に油６４が抵抗力を受ける。すなわち、従来のスクイズ効果に加えて、有孔部材５４の連通孔５１を通過する油６４が上記軸受部８及び内側部材２０の振動に対するダンパとして機能するため、簡易な構成で減衰性能を大幅に向上させることができる。 Furthermore, according to the above configuration, the perforated member 54 including the plurality of communication holes 51 communicating between the radially inner first region 41 and the radially outer second region 42 of the convex portion 65 is arranged. For example, when the bearing 8 and the inner member 20 supporting it vibrate due to the rotation of the rotor shaft 2 , part of the oil 64 follows the outer peripheral surface 22 of the inner member 20 and communicates with the perforated member 54 . It passes through the hole 51 and the oil 64 experiences resistance during its passage. That is, in addition to the conventional squeeze effect, the oil 64 passing through the communication hole 51 of the perforated member 54 functions as a damper against the vibrations of the bearing portion 8 and the inner member 20, so that the damping performance is greatly improved with a simple configuration. can be improved.

また、有孔部材５４のうち、連通孔５１が設けられた領域を径方向内側に突出させて凸部６５を形成し、周方向端部及び軸方向端部に密封支持部７２を配置することで、第１領域４１が密封される。これより、油６４が周方向及び軸方向へ流れることが抑制され、油６４の径方向への流れを促進することができる。即ち、油６４が連通孔５１を介して流れるようにすることができるので、上記抵抗力による減衰効果を効率良く付与することができ、減衰性能を更に向上させることができる。なお、有孔部材５４の減衰効果は、個々の有孔部材５４が搭載される回転機械１の振動特性に応じて、凸部６５の数や配置等を任意に設定することで調整し得る。 In addition, the region of the perforated member 54 where the communication hole 51 is provided protrudes radially inward to form the convex portion 65, and the sealing support portions 72 are arranged at the circumferential end portion and the axial end portion. , the first region 41 is sealed. As a result, the oil 64 is prevented from flowing in the circumferential and axial directions, and the radial flow of the oil 64 can be promoted. That is, since the oil 64 can be made to flow through the communication hole 51, the damping effect due to the resistance can be efficiently imparted, and the damping performance can be further improved. The damping effect of the perforated member 54 can be adjusted by arbitrarily setting the number and arrangement of the projections 65 according to the vibration characteristics of the rotary machine 1 on which each perforated member 54 is mounted.

さらに、隙間４２の軸方向端の少なくとも一部を開放した構成にすることにより、第１領域４１に供給され、連通孔５１を介して第２領域４２に移動した油６４を、該第２領域４２の開放された軸方向端から排出することができる。 Furthermore, by opening at least a part of the axial end of the clearance 42, the oil 64 supplied to the first region 41 and moved to the second region 42 via the communication hole 51 is transferred to the second region. The open axial ends of 42 can be discharged.

以上、本開示の第二実施形態について説明したが、本開示の要旨を逸脱しない限りにおいて、上記の構成に種々の変更や改修を施すことが可能である。例えば、密封支持部６９は、上述した構成に限られない。一例には、図１４（ｂ）に示すように、密封支持部６９は、支持機構６６と、シール部材６８と、を有する。 Although the second embodiment of the present disclosure has been described above, various changes and modifications can be made to the above configuration without departing from the gist of the present disclosure. For example, the sealing support portion 69 is not limited to the configuration described above. For example, as shown in FIG. 14(b), the sealing support 69 has a support mechanism 66 and a sealing member 68. As shown in FIG.

支持機構６６は、凸部６５の周方向端部及び軸方向端部に設けられ、内側部材２０を径方向外側から支持する。また、支持機構６６は、内側部材２０の振動に伴って、径方向に変形可能であり、一例には、図１４（ｂ）に示すように、凸部６５と一体に形成された切欠部材である。切欠部材は、所定の剛性を有する部材を周方向の両側から切欠くことにより、剛性が調整され、径方向に変形可能なように構成されている。また、切欠部材の径方向内側の端部は、内側部材２０と接触するとともにシール部材６８を収容する収容凹部７０が形成されている。収容凹部７０は、支持機構６６の径方向内側の端部に設けられて、径方向内側に窪む凹部であり、支持機構６６と内側部材２０の間にシール部材６８を収容するための空間を画定している。この時、凸部６５と対向する内側部材２０の部分は、径方向外側に突出している。なお、支持機構６６の剛性は、切欠きの数や形状等を任意に設定することで任意に調整し得る。 The support mechanism 66 is provided at the circumferential end and the axial end of the projection 65 and supports the inner member 20 from the radial outside. In addition, the support mechanism 66 can be deformed in the radial direction along with the vibration of the inner member 20. For example, as shown in FIG. be. The notch member is configured so that the rigidity is adjusted by notching a member having a predetermined rigidity from both sides in the circumferential direction, and the notch member can be deformed in the radial direction. A housing recess 70 that contacts the inner member 20 and houses the seal member 68 is formed at the radially inner end of the notch member. The accommodation recess 70 is a recess that is provided at the radially inner end of the support mechanism 66 and is recessed radially inward, and provides a space for accommodating the seal member 68 between the support mechanism 66 and the inner member 20 . demarcated. At this time, the portion of the inner member 20 facing the convex portion 65 protrudes radially outward. The rigidity of the support mechanism 66 can be arbitrarily adjusted by arbitrarily setting the number and shape of the notches.

シール部材６８は、支持機構６６の収容凹部７０に収容される。シール部材６８には、Ｏリング等のシール部品が用いられる。各支持機構６６の収容凹部７０に設けられたシール部材６８は内側部材２０と接触して、第１領域４１を周方向及び軸方向に密封している。なお、切欠部材の径方向内側の端部と内側部材２０の外周面２２とを溶接等により接合することで、第１領域４１を密封した場合には、必ずしもシール部材６８を設けることを要しない。 The seal member 68 is housed in the housing recess 70 of the support mechanism 66 . A sealing component such as an O-ring is used for the sealing member 68 . A seal member 68 provided in the housing recess 70 of each support mechanism 66 is in contact with the inner member 20 to seal the first region 41 circumferentially and axially. In addition, when the first region 41 is sealed by joining the radially inner end portion of the notch member and the outer peripheral surface 22 of the inner member 20 by welding or the like, the sealing member 68 is not necessarily required. .

また、別の例では、図１４（ｃ）のように、支持機構６６を弾性部材で構成し、シール部材６８には、Ｏリング等のシール部品が用いられるように構成しても良い。この時、弾性部材の端部は、内側部材２０の外周面２２と凸部６５にそれぞれ取り付けられ、弾性部材は、内側部材２０の振動に伴って径方向に伸縮可能なように構成されている。 In another example, as shown in FIG. 14(c), the support mechanism 66 may be made of an elastic member, and the sealing member 68 may be made of a seal component such as an O-ring. At this time, the ends of the elastic member are attached to the outer peripheral surface 22 and the convex portion 65 of the inner member 20, respectively, and the elastic member is configured to expand and contract in the radial direction as the inner member 20 vibrates. .

［第三実施形態］
以下、本開示の第三実施形態について、図１５及び図１６を参照して説明する。第三実施形態では、上記の実施形態と同様の構成要素には同一の符号を付して詳細な説明を省略する。図１５は、第三実施形態に係るスクイズフィルムダンパの要部拡大図である。図１６は、第三実施形態の他の例に係る回転機械を示す軸方向断面図である。 [Third embodiment]
A third embodiment of the present disclosure will be described below with reference to FIGS. 15 and 16. FIG. In the third embodiment, the same reference numerals are assigned to the same components as in the above-described embodiment, and detailed description thereof will be omitted. FIG. 15 is an enlarged view of the essential part of the squeeze film damper according to the third embodiment. FIG. 16 is an axial cross-sectional view showing a rotating machine according to another example of the third embodiment.

図１５に示すように、第三実施形態では、第二実施形態の第２領域４２を密封するように、有孔部材５４に密封部材８０が取り付けられている点で第二実施形態と相違する。詳細には、図１５に示すように、密封部材８０は、第２領域４２を径方向外側から密封するように、有孔部材５４の外周面に取り付けられている。一例には、密封部材８０は、凸部６５にボルト等の図示しない締結具を用いて、取り外し可能に取り付けられている。この時、第１領域４１と第２領域４２は、密封されている。なお、図１５では、密封支持部６９として切欠部材及びシール部材を示しているが、実施形態２で述べた他の密封支持部６９が適用されても良い。 As shown in FIG. 15, the third embodiment differs from the second embodiment in that a sealing member 80 is attached to the perforated member 54 so as to seal the second region 42 of the second embodiment. . Specifically, as shown in FIG. 15, the sealing member 80 is attached to the outer peripheral surface of the perforated member 54 so as to radially seal the second region 42 from the outside. In one example, the sealing member 80 is detachably attached to the protrusion 65 using fasteners (not shown) such as bolts. At this time, the first area 41 and the second area 42 are sealed. Note that FIG. 15 shows a notch member and a seal member as the sealing support portion 69, but other sealing support portions 69 described in the second embodiment may be applied.

また、密封部材８０が取り付けられることにより、第２領域４２の径方向外側に空間が形成されている。そして、該空間にガスが封入されることにより、密封部材８０の内部にガス領域８４が形成される。さらに、ガス領域８４と第２領域４２の境界には、薄膜のダイヤフラム８２が設けられている。ダイヤフラム８２は、外力の作用に伴い変形可能な柔軟性を持った材料で構成されている。一例には、ダイヤフラム８２は、ゴムや金属等の材料から構成される。これより、ダイヤフラム８２は、ガス領域８４と第２領域４２の圧力差により、径方向に変形可能なように構成されている。 A space is formed radially outside the second region 42 by attaching the sealing member 80 . A gas region 84 is formed inside the sealing member 80 by filling the space with gas. Furthermore, a thin film diaphragm 82 is provided at the boundary between the gas region 84 and the second region 42 . The diaphragm 82 is made of a flexible material that can be deformed under the action of an external force. In one example, diaphragm 82 is constructed from a material such as rubber or metal. Thus, the diaphragm 82 is configured to be radially deformable due to the pressure difference between the gas region 84 and the second region 42 .

以上の構成において、図示しない給油路により、凸部６５と内側部材２０との間の隙間での第１領域４１に油６４を供給すると、油６４の自重により、又は、第１領域４１内に供給された油６４の圧力により、第１領域４１から連通孔５１を介して第２領域４２に油６４が流入し、第１領域４１及び第２領域４２を含む隙間４０に油膜が形成される。なお、給油路は、一例には、第一実施形態で述べた給油路６０が適用される。 In the above configuration, when the oil 64 is supplied to the first region 41 in the gap between the convex portion 65 and the inner member 20 through an oil supply passage (not shown), the weight of the oil 64 causes the oil to flow into the first region 41. Due to the pressure of the supplied oil 64, the oil 64 flows from the first region 41 to the second region 42 via the communication hole 51, and an oil film is formed in the gap 40 including the first region 41 and the second region 42. . As an example of the oil supply path, the oil supply path 60 described in the first embodiment is applied.

この状態で、例えばロータ軸２の回転に伴い、軸受部８及びこれを支持する内側部材２０が振動すると、内側部材２０の外周面２２と凸部６５の内周面との間隔、すなわち第１領域４１の間隔が振動に応じて変化する。この間隔の変化により、第１領域４１内の油６４の粘性抵抗に起因した所謂スクイズ作用により圧力が発生し、上記振動に対する減衰効果が得られる。 In this state, when the bearing portion 8 and the inner member 20 supporting the bearing portion 8 vibrate as the rotor shaft 2 rotates, the distance between the outer peripheral surface 22 of the inner member 20 and the inner peripheral surface of the projection 65, that is, the first The spacing of the regions 41 changes in response to vibration. Due to the change in this interval, pressure is generated by a so-called squeezing action caused by the viscous resistance of the oil 64 in the first region 41, and a damping effect on the vibration is obtained.

さらに、内側部材２０と外側部材３０との隙間４０に、径方向内側の第１領域４１と径方向外側の第２領域４２とを連通する複数の連通孔５１を含む有孔部材５４を配置した構成により、例えばロータ軸２の回転に伴い、軸受部８及びこれを支持する内側部材２０が振動した際には、内側部材２０の外周面２２に追従して油６４の一部が有孔部材５４の連通孔５１を通過し、当該通過の際に油６４が抵抗力を受ける。すなわち、従来のスクイズ効果に加えて、有孔部材５４の連通孔５１を通過する油６４が上記軸受部８及び内側部材２０の振動に対するダンパとして機能するため、簡易な構成で減衰性能を大幅に向上させることができる。 Further, in the gap 40 between the inner member 20 and the outer member 30, a perforated member 54 including a plurality of communication holes 51 communicating between the radially inner first region 41 and the radially outer second region 42 is arranged. Due to the configuration, when the bearing portion 8 and the inner member 20 supporting the bearing portion 8 vibrate due to the rotation of the rotor shaft 2, part of the oil 64 follows the outer peripheral surface 22 of the inner member 20 and moves to the perforated member. The oil 64 passes through the communication hole 51 of 54, and the oil 64 receives a resistance force during the passage. That is, in addition to the conventional squeeze effect, the oil 64 passing through the communication hole 51 of the perforated member 54 functions as a damper against the vibrations of the bearing portion 8 and the inner member 20, so that the damping performance is greatly improved with a simple configuration. can be improved.

また、有孔部材５４の連通孔５１が設けられた領域を径方向内側に突出させて凸部６５を形成し、周方向端部及び軸方向端部にシール部材６８を配置することで、第１領域４１が密封される。これより、油６４の周方向及び軸方向への流れが抑制され、油６４の径方向への流れを促進することができる。即ち、油６４が連通孔５１を介して流れるように流れを促進することができるので、上記抵抗力によるダンパの機能を効率良く付与することができ、減衰性能を更に向上させることができる。なお、有孔部材５４の減衰効果は、個々の有孔部材５４が搭載される回転機械１の振動特性に応じて、凸部６５を設ける数や配置等を任意に設定することで調整し得る。 In addition, the area of the perforated member 54 in which the communication hole 51 is provided protrudes radially inward to form the convex portion 65, and the sealing member 68 is arranged at the circumferential end portion and the axial end portion, whereby the second 1 area 41 is sealed. As a result, the circumferential and axial flows of the oil 64 are suppressed, and the radial flow of the oil 64 can be promoted. That is, the oil 64 can be promoted to flow through the communication hole 51, so that the damper function by the resistance can be efficiently provided, and the damping performance can be further improved. The damping effect of the perforated member 54 can be adjusted by arbitrarily setting the number and arrangement of the projections 65 according to the vibration characteristics of the rotary machine 1 on which each perforated member 54 is mounted. .

さらに、本実施形態の場合、第２領域４２が密封部材８０により密封されていることで、油６４が循環する際に空気が混入することが抑制される。これより、油６４に空気が混入することにより、減衰性能が低下することを抑制することができる。 Furthermore, in the case of the present embodiment, since the second region 42 is sealed by the sealing member 80, it is possible to prevent air from entering when the oil 64 circulates. As a result, it is possible to suppress deterioration in damping performance due to air being mixed in the oil 64 .

さらに、本実施形態では、密封部材８０にガス領域８４を設けて、ガス領域８４と第２領域４２の境界に、径方向に変形可能なダイヤフラム８２を設けている。これにより、密封部材８０が第２領域４２を密封した状態でも、ガス領域８４と油６４の差圧により、ダイヤフラム８２が径方向に変形することで、油６４が連通孔５１を介して第１領域４１と第２領域４２を行き来することができる。したがって、第２領域４２が密封された状態でも、油６４が連通孔５１を流入する際に抵抗力を受けることによって、減衰性能を大幅に向上させることができる。 Furthermore, in this embodiment, the sealing member 80 is provided with a gas region 84 and a radially deformable diaphragm 82 is provided at the boundary between the gas region 84 and the second region 42 . As a result, even when the sealing member 80 seals the second region 42 , the pressure difference between the gas region 84 and the oil 64 causes the diaphragm 82 to deform in the radial direction, allowing the oil 64 to flow through the communication hole 51 to the first region 42 . It is possible to go back and forth between the area 41 and the second area 42 . Therefore, even when the second region 42 is sealed, the damping performance can be greatly improved by receiving resistance when the oil 64 flows into the communication hole 51 .

また、密封部材８０を凸部６５に取り外し可能に取り付けることによって、密封部材８０のガス領域８４の圧力を調整することができるため、減衰性能を調整することができる。 Further, by detachably attaching the sealing member 80 to the convex portion 65, the pressure of the gas region 84 of the sealing member 80 can be adjusted, so that the damping performance can be adjusted.

以上、本発明の第三実施形態について説明したが、本発明の要旨を逸脱しない限りにおいて、上記の構成に種々の変更や改修を施すことが可能である。例えば、本実施形態の他の例として、図１６に示すように、有孔部材５４を取り外し可能なユニット９０と、ユニット９０を挿入可能な空間が形成された円弧部９８と、から構成することができる。円弧部９８には、周方向に少なくとも一つ以上の空間が形成され、ユニット９０が挿入可能なように構成されている。 Although the third embodiment of the present invention has been described above, various changes and modifications can be made to the above configuration without departing from the gist of the present invention. For example, as another example of the present embodiment, as shown in FIG. 16, a unit 90 from which the perforated member 54 can be removed, and an arc portion 98 formed with a space into which the unit 90 can be inserted. can be done. At least one or more spaces are formed in the arc portion 98 in the circumferential direction so that the unit 90 can be inserted therein.

ユニット９０は、径方向内側の端部であるとともに、内側部材２０に接する第一部材９２と、径方向外側の端部であるとともに、第一部材９２と径方向に隙間を空けて設けられて、円弧部９８に取り付けられる第二部材９４と、該隙間に設けられて、径方向内側の第１領域４１と、径方向外側の第２領域４２とを連通する複数の連通孔５１を有する第三部材９６と、第１領域４１を密封するとともに第一部材９２を径方向外側から支持する密封支持部６９と、第二部材９４の径方向内側に取り付けられ、第２領域４２を密封する密封部材８０と、を備えている。 The unit 90 is provided with a radially inner end and a first member 92 in contact with the inner member 20 and a radially outer end with a gap in the radial direction from the first member 92 . , a second member 94 attached to the arc portion 98, and a plurality of communication holes 51 provided in the gap for communicating the radially inner first region 41 and the radially outer second region 42. A third member 96, a sealing support portion 69 that seals the first region 41 and supports the first member 92 from the radially outer side, and a seal that is attached radially inwardly of the second member 94 and seals the second region 42. a member 80;

第一部材９２は、板状の部材であり、ユニット９０が挿入された時に、内側部材２０に接している。第一部材９２は、例えば、ボルト等の締結具を用いて内側部材２０に固定されていても良い。 The first member 92 is a plate-like member and is in contact with the inner member 20 when the unit 90 is inserted. The first member 92 may be secured to the inner member 20 using, for example, fasteners such as bolts.

第二部材９４は、第一部材９２と同様に板状の部材であるが、幅が第一部材９２よりも大きく形成され、円弧部９８に取り付けられている。なお、第二部材９４の幅は、必ずしも第一部材９２の幅よりも大きく形成されている必要はなく、ユニット９０が外側部材３０に取り付けられていれば、形状、寸法等は限定されない。そのため、必ずしも、第二部材９４が外側部材３０の外周面に取り付けられる必要はない。一例には、第二部材９４の側面が円弧部９８の側面に取り付けられることにより固定されていても良い。 The second member 94 is a plate-shaped member like the first member 92 , but has a width greater than that of the first member 92 and is attached to the arc portion 98 . The width of the second member 94 does not necessarily have to be larger than the width of the first member 92, and the shape, dimensions, etc. are not limited as long as the unit 90 is attached to the outer member 30. Therefore, the second member 94 does not necessarily have to be attached to the outer peripheral surface of the outer member 30 . For example, the side surface of the second member 94 may be fixed by attaching it to the side surface of the arc portion 98 .

第三部材９６は、第一部材９２と第二部材９４との間に形成された隙間に配置され、径方向内側の第一領域４１と径方向外側の第二領域４２を画定する板状の部材である。また、第三部材９６には、複数の連通孔５１が設けられている。複数の連通孔５１の形状は、上記の各実施形態で述べた形状と同様の構成が適用される。なお、第１領域には、油６４が予め充填されている。 The third member 96 is disposed in a gap formed between the first member 92 and the second member 94, and is a plate-like member that defines a radially inner first region 41 and a radially outer second region 42. It is a member. Also, the third member 96 is provided with a plurality of communication holes 51 . The shape of the plurality of communication holes 51 has the same configuration as the shape described in each of the above embodiments. Note that the first region is filled with oil 64 in advance.

密封支持部６９は、第一領域４１の軸方向及び周方向の端部に設けられ、第一領域４１を密封する。また、密封支持部６９は、第一部材９２を径方向外側から支持している。密封支持部６９には、上記の実施形態で述べた構成が適用され、一例には、ベローズ７２である。 The sealing supports 69 are provided at the axial and circumferential ends of the first region 41 to seal the first region 41 . Further, the sealing support portion 69 supports the first member 92 from the radial outside. The structure described in the above embodiment is applied to the sealing support portion 69, and the bellows 72 is an example.

また、ユニット９０は、第二部材９４の径方向内側に設けられ、第２領域４２を密封する密封部材８０を有する。密封部材８０の構成は、本実施形態の密封部材８０の構成と同様である。即ち、密封部材８０は、ダイヤフラム８２と、ガス領域８４と、を有する。これらの構成は本実施形態の密封部材８０と同様であるので、詳細な説明を省略する。 The unit 90 also has a sealing member 80 that is provided radially inside the second member 94 and seals the second region 42 . The configuration of the sealing member 80 is the same as the configuration of the sealing member 80 of this embodiment. That is, the sealing member 80 has a diaphragm 82 and a gas region 84 . Since these configurations are the same as those of the sealing member 80 of the present embodiment, detailed description thereof will be omitted.

上記の構成によれば、ユニット９０が円弧部９８に形成された空間に挿入された状態で、内側部材２０が振動すると、ユニット９０の内部に存在する第１領域４１の間隔が変化し、ユニット９０が上記振動に対するダンパとして機能し、本実施形態で述べた効果と同様の効果を享受することができる。 According to the above configuration, when the inner member 20 vibrates while the unit 90 is inserted into the space formed in the arc portion 98, the interval between the first regions 41 existing inside the unit 90 changes, and the unit 90 functions as a damper against the vibration, and the same effects as those described in this embodiment can be obtained.

加えて、ユニット９０は有孔部材５４に取り外し可能に取り付けられているため、ユニット９０に使用する油種を変更することや、油６４の脱気の程度を調整すること、ガス領域８２に封入するガスの種類を変更することにより、減衰性能を調整することができる。したがって、回転機械１の振動特性に合わせてユニット９０を構成することができる。 In addition, since the unit 90 is removably attached to the perforated member 54, it is possible to change the type of oil used in the unit 90, adjust the degree of degassing of the oil 64, and seal the gas region 82. Damping performance can be adjusted by changing the type of gas used. Therefore, the unit 90 can be configured according to the vibration characteristics of the rotating machine 1 .

以上、本発明の実施の形態について図面を参照して詳述したが、具体的な構成はこれらの実施の形態に限られるものではなく、本発明の要旨を逸脱しない範囲の設計変更等も含まれる。 As described above, the embodiments of the present invention have been described in detail with reference to the drawings, but the specific configuration is not limited to these embodiments, and design changes etc. within the scope of the present invention are included. be

１ 回転機械
２ ロータ軸
３ 動翼
４ ギア
５ インペラ
８ 軸受部（軸受メタル、軸受パッド）
９ ピボット
１０ スクイズフィルムダンパ
２０ 内側部材
２０Ａ 上側ハウジング
２０Ｂ 下側ハウジング
２２ 外周面
２４ 軸方向端部
３０ 外側部材
３２ 支持部
４０ 隙間
４１ 第１領域
４２ 第２領域
５０，５４ 有孔部材
５１ 連通孔
５１Ａ 中心軸
５２ 円筒部
５３ テーパ部
６０ 給油路
６２ 内部流路
６２Ａ 軸方向延在部
６２Ｂ 径方向延在部
６４ 油
６５ 凸部
６６ 支持機構
６８ シール部材
６９ 密封支持部
７０ 収容凹部
７２ ベローズ
８０ 密封部材
８２ ダイヤフラム
８４ ガス領域
８８ スリット
９０ ユニット
９２ 第一部材
９４ 第二部材
９６ 第三部材
９８ 円弧部 1 rotating machine 2 rotor shaft 3 rotor blade 4 gear 5 impeller 8 bearing (bearing metal, bearing pad)
9 pivot 10 squeeze film damper 20 inner member 20A upper housing 20B lower housing 22 outer peripheral surface 24 axial end 30 outer member 32 support 40 gap 41 first region 42 second regions 50, 54 perforated member 51 communicating hole 51A Central shaft 52 Cylindrical portion 53 Tapered portion 60 Oil supply passage 62 Internal flow passage 62A Axial extending portion 62B Radial extending portion 64 Oil 65 Convex portion 66 Support mechanism 68 Seal member 69 Seal support portion 70 Accommodating recess 72 Bellows 80 Seal member 82 diaphragm 84 gas region 88 slit 90 unit 92 first member 94 second member 96 third member 98 arc portion

Claims (21)

軸受部を支持する内側部材と、
周方向に延在する隙間を挟んで前記内側部材に対向するように、前記内側部材の外周側に設けられる外側部材と、
前記隙間に設けられ、前記隙間のうち径方向内側の第１領域と、前記隙間のうち径方向外側の第２領域とを連通する複数の連通孔を有する有孔部材と、
前記第１領域に油を供給するための給油路と、
を備え、
前記給油路は、前記外側部材及び前記有孔部材を径方向に貫通して前記油を前記第１領域に供給するように構成されているスクイズフィルムダンパ。 an inner member supporting the bearing;
an outer member provided on the outer peripheral side of the inner member so as to face the inner member across a gap extending in the circumferential direction;
a perforated member provided in the gap and having a plurality of communication holes communicating between a radially inner first area of the gap and a radially outer second area of the gap;
an oil supply passage for supplying oil to the first region;
with
The squeeze film damper, wherein the oil supply passage radially penetrates the outer member and the perforated member to supply the oil to the first region. 軸受部を支持する内側部材と、
周方向に延在する隙間を挟んで前記内側部材に対向するように、前記内側部材の外周側に設けられる外側部材と、
前記隙間に設けられ、前記隙間のうち径方向内側の第１領域と、前記隙間のうち径方向外側の第２領域とを連通する複数の連通孔を有する有孔部材と、
前記第１領域に油を供給するための給油路と、
を備え、少なくとも前記有孔部材において最も軸方向端部側に配置された前記連通孔は、その中心軸が、径方向において内側より外側が前記軸方向端部に近接するように径方向から傾斜しているスクイズフィルムダンパ。 an inner member supporting the bearing;
an outer member provided on the outer peripheral side of the inner member so as to face the inner member across a gap extending in the circumferential direction;
a perforated member provided in the gap and having a plurality of communication holes communicating between a radially inner first area of the gap and a radially outer second area of the gap;
an oil supply passage for supplying oil to the first region;
wherein the central axis of at least the communicating hole arranged closest to the end in the axial direction in the perforated member is inclined from the radial direction so that the outer side is closer to the axial end than the inner side in the radial direction. squeeze film damper. 軸受部を支持する内側部材と、
周方向に延在する隙間を挟んで前記内側部材に対向するように、前記内側部材の外周側に設けられる外側部材と、
前記隙間に設けられ、前記隙間のうち径方向内側の第１領域と、前記隙間のうち径方向外側の第２領域とを連通する複数の連通孔を有する有孔部材と、
前記第１領域に油を供給するための給油路と、
を備え、前記連通孔は、径方向において内側より外側が小径に形成されているスクイズフィルムダンパ。 an inner member supporting the bearing;
an outer member provided on the outer peripheral side of the inner member so as to face the inner member across a gap extending in the circumferential direction;
a perforated member provided in the gap and having a plurality of communication holes communicating between a radially inner first area of the gap and a radially outer second area of the gap;
an oil supply passage for supplying oil to the first region;
A squeeze film damper , wherein the communication hole is formed to have a smaller diameter on the outside than on the inside in the radial direction . 軸受部を支持する内側部材と、
周方向に延在する隙間を挟んで前記内側部材に対向するように、前記内側部材の外周側に設けられる外側部材と、
前記隙間に設けられ、前記隙間のうち径方向内側の第１領域と、前記隙間のうち径方向外側の第２領域とを連通する複数の連通孔を有する有孔部材と、
前記第１領域に油を供給するための給油路と、
を備え、前記連通孔は、径方向において内側より外側が大径に形成されているスクイズフィルムダンパ。 an inner member supporting the bearing;
an outer member provided on the outer peripheral side of the inner member so as to face the inner member across a gap extending in the circumferential direction;
a perforated member provided in the gap and having a plurality of communication holes communicating between a radially inner first area of the gap and a radially outer second area of the gap;
an oil supply passage for supplying oil to the first region;
A squeeze film damper , wherein the communication hole is formed to have a larger diameter on the outside than on the inside in the radial direction . 軸受部を支持する内側部材と、
周方向に延在する隙間を挟んで前記内側部材に対向するように、前記内側部材の外周側に設けられる外側部材と、
前記隙間に設けられ、前記隙間のうち径方向内側の第１領域と、前記隙間のうち径方向外側の第２領域とを連通する複数の連通孔を有する有孔部材と、
前記第１領域に油を供給するための給油路と、
を備え、前記連通孔は、径方向外側の円筒部と該円筒部における径方向の内側端に連続し径方向内側に向けて拡開されたテーパ部とを含むスクイズフィルムダンパ。 an inner member supporting the bearing;
an outer member provided on the outer peripheral side of the inner member so as to face the inner member across a gap extending in the circumferential direction;
a perforated member provided in the gap and having a plurality of communication holes communicating between a radially inner first area of the gap and a radially outer second area of the gap;
an oil supply passage for supplying oil to the first region;
wherein the communication hole includes a radially outer cylindrical portion and a tapered portion that continues from a radially inner end of the cylindrical portion and expands radially inward. 軸受部を支持する内側部材と、
周方向に延在する隙間を挟んで前記内側部材に対向するように、前記内側部材の外周側に設けられる外側部材と、
前記隙間に設けられ、前記隙間のうち径方向内側の第１領域と、前記隙間のうち径方向外側の第２領域とを連通する複数の連通孔を有する有孔部材と、
前記第１領域に油を供給するための給油路と、
を備え、前記連通孔は、スリット状に形成されているスクイズフィルムダンパ。 an inner member supporting the bearing;
an outer member provided on the outer peripheral side of the inner member so as to face the inner member across a gap extending in the circumferential direction;
a perforated member provided in the gap and having a plurality of communication holes communicating between a radially inner first area of the gap and a radially outer second area of the gap;
an oil supply passage for supplying oil to the first region;
A squeeze film damper , wherein the communication hole is formed in a slit shape . 軸受部を支持する内側部材と、
周方向に延在する隙間を挟んで前記内側部材に対向するように、前記内側部材の外周側に設けられる外側部材と、
前記隙間に設けられ、前記隙間のうち径方向内側の第１領域と、前記隙間のうち径方向外側の第２領域とを連通する複数の連通孔を有する有孔部材と、
前記第１領域に油を供給するための給油路と、
を備え、
前記有孔部材は、
前記連通孔が設けられた領域が径方向内側に突出した凸部と、
前記凸部と前記内側部材との間の前記第１領域を密封するとともに、前記内側部材を径方向外側から支持する密封支持部と、スクイズフィルムダンパ。 an inner member supporting the bearing;
an outer member provided on the outer peripheral side of the inner member so as to face the inner member across a gap extending in the circumferential direction;
a perforated member provided in the gap and having a plurality of communication holes communicating between a radially inner first area of the gap and a radially outer second area of the gap;
an oil supply passage for supplying oil to the first region;
with
The perforated member is
a convex portion in which the area provided with the communication hole protrudes radially inward;
a sealing support portion that seals the first region between the convex portion and the inner member and supports the inner member from the radially outer side; and a squeeze film damper. 前記密封支持部は、
前記第１領域を密封するシール部材と、
前記内側部材を支持する支持機構と、
を有する請求項７に記載のスクイズフィルムダンパ。 The sealing support includes:
a sealing member that seals the first region;
a support mechanism that supports the inner member;
8. The squeeze film damper of claim 7 , comprising: 前記支持機構は、前記凸部と一体として形成されるとともに径方向に伸縮可能に構成された切欠部材であり、
前記切欠部材は、前記シール部材を収容する収容凹部を備える、請求項８に記載のスクイズフィルムダンパ。 The support mechanism is a notch member formed integrally with the convex portion and configured to be expandable and contractable in a radial direction,
9. The squeeze film damper according to claim 8 , wherein said notch member has a housing recess for housing said seal member. 前記密封支持部は、径方向に伸縮可能なベローズである、請求項７に記載のスクイズフィルムダンパ。 8. The squeeze film damper of claim 7 , wherein the sealing support is a radially expandable bellows. 前記隙間は、軸方向端の少なくとも一部が開放されている請求項１～１０の何れか一項に記載のスクイズフィルムダンパ。 The squeeze film damper according to any one of claims 1 to 10 , wherein at least a part of the axial end of the gap is open. 前記有孔部材は、前記第２領域の径方向外側に取り付けられ、前記第２領域を密封する密封部材を有し、
前記密封部材は、前記第２領域との境界に薄膜のダイヤフラムを備え、
前記密封部材により形成された空間に、ガスが封入され、
前記ダイヤフラムは、前記ガスと前記第２領域を流通する前記油の圧力差によって径方向に変形可能である、
請求項７から請求項１０の何れか一項に記載のスクイズフィルムダンパ。 the perforated member has a sealing member mounted radially outwardly of the second region to seal the second region;
the sealing member comprises a thin film diaphragm at the boundary with the second region;
A gas is enclosed in the space formed by the sealing member,
The diaphragm is radially deformable due to a pressure difference between the gas and the oil flowing through the second region.
A squeeze film damper according to any one of claims 7 to 10 . 前記密封部材は、前記凸部に取り外し可能に取り付けられる、請求項１２に記載のスクイズフィルムダンパ。 13. The squeeze film damper of claim 12 , wherein said sealing member is removably attached to said protrusion. 前記給油路は、前記内側部材の軸方向端部から前記第１領域に前記油を導く内部流路を含む、請求項２から１３のいずれか一項に記載のスクイズフィルムダンパ。 14. The squeeze film damper according to any one of claims 2 to 13 , wherein the oil supply passage includes an internal channel that guides the oil from an axial end of the inner member to the first region. 前記内部流路は、前記軸方向端部から軸方向に延在する軸方向延在部と、前記軸方向延在部に連続して径方向に延在する径方向延在部とを含む、請求項１４に記載のスクイズフィルムダンパ。 The internal flow path includes an axially extending portion that extends axially from the axial end portion, and a radially extending portion that is continuous with the axially extending portion and extends in the radial direction. 15. The squeeze film damper of claim 14 . 一の前記軸方向延在部につき一又は複数の前記径方向延在部が形成されている請求項１５に記載のスクイズフィルムダンパ。 16. The squeeze film damper according to claim 15 , wherein one or more radially extending portions are formed for each axially extending portion. 前記有孔部材は、周方向に間隔を隔てた複数箇所で前記外側部材に支持されている請求項１～１３の何れか一項に記載のスクイズフィルムダンパ。 The squeeze film damper according to any one of claims 1 to 13 , wherein the perforated member is supported by the outer member at a plurality of locations spaced apart in the circumferential direction. 前記内側部材及び前記有孔部材間の寸法Ｄと前記連通孔の直径ｄとが０．１ｄ＜Ｄ＜１０ｄを満たす、
請求項１～５、７～１３、１７の何れか一項に記載のスクイズフィルムダンパ。 A dimension D between the inner member and the perforated member and a diameter d of the communicating hole satisfy 0.1d<D<10d,
The squeeze film damper according to any one of claims 1-5, 7-13 and 17 . 前記連通孔は、径方向に沿って延在する円筒状に形成されている、請求項１～５、７～１３、１７、１８の何れか一項に記載のスクイズフィルムダンパ。 The squeeze film damper according to any one of claims 1 to 5, 7 to 13, 17 and 18 , wherein the communication hole is formed in a cylindrical shape extending along the radial direction. 軸受部を支持する内側部材と、
前記内側部材と所定の間隔を空けて、前記内側部材の外周側に設けられる有孔部材と、を有し、
前記有孔部材は、
少なくとも一つの取り外し可能なユニットと、
前記ユニットを挿入可能な空間が形成された円弧部と、を備え、
前記ユニットは、
径方向内側の端部であるとともに、前記内側部材と接する第一部材と、
径方向外側の端部であるとともに、前記第一部材と隙間を空けて設けられ、前記円弧部に取り付けられる第二部材と、
前記隙間に設けられ、前記隙間のうち径方向内側の第１領域と、前記隙間のうち径方向外側の第２領域とを連通する複数の連通孔を有する第三部材と、
前記第１領域を密封するとともに前記第一部材を径方向外側から支持する密封支持部と、
前記第二部材の径方向内側に取り付けられ、前記第２領域を密封する密封部材と、を備え、
前記密封部材は、前記第２領域との境界に薄膜のダイヤフラムを備え、
前記密封部材により形成された空間にガスが封入され、
前記ダイヤフラムは、前記ガスと前記第２領域を流通する油の圧力差によって径方向に変形可能である、スクイズフィルムダンパ。 an inner member supporting the bearing;
a perforated member provided on the outer peripheral side of the inner member at a predetermined distance from the inner member,
The perforated member is
at least one removable unit;
and an arc portion formed with a space into which the unit can be inserted,
Said unit is
a first member that is a radially inner end and is in contact with the inner member;
a second member, which is a radially outer end portion, is provided with a gap from the first member, and is attached to the arc portion;
a third member provided in the gap and having a plurality of communication holes communicating between a radially inner first region of the gap and a radially outer second region of the gap;
a sealing support portion that seals the first region and supports the first member from the radially outer side;
a sealing member attached radially inward of the second member and sealing the second region;
the sealing member comprises a thin film diaphragm at the boundary with the second region;
A gas is enclosed in the space formed by the sealing member,
The squeeze film damper, wherein the diaphragm is radially deformable by a pressure difference between the gas and the oil flowing through the second region. 請求項１から請求項１３の何れか一項に記載のスクイズフィルムダンパと、
ロータ軸と、
前記ロータ軸を回転可能に支持する軸受部と、
を備えた回転機械。 a squeeze film damper according to any one of claims 1 to 13 ;
a rotor shaft;
a bearing that rotatably supports the rotor shaft;
A rotary machine with
JP2019055581A 2018-10-04 2019-03-22 Squeeze film damper and rotary machine Active JP7253948B2 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201910951731.7A CN111005937B (en) 2018-10-04 2019-09-30 Squeeze film damper and rotary machine
US16/589,741 US11053977B2 (en) 2018-10-04 2019-10-01 Squeeze film damper and rotary machine

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2018188775 2018-10-04
JP2018188775 2018-10-04

Publications (2)

Publication Number Publication Date
JP2020060290A JP2020060290A (en) 2020-04-16
JP7253948B2 true JP7253948B2 (en) 2023-04-07

Family

ID=70218997

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2019055581A Active JP7253948B2 (en) 2018-10-04 2019-03-22 Squeeze film damper and rotary machine

Country Status (1)

Country Link
JP (1) JP7253948B2 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7493476B2 (en) 2021-03-17 2024-05-31 三菱重工業株式会社 Bearing device and rotating machine

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2018145969A (en) 2017-03-06 2018-09-20 パナソニックＩｐマネジメント株式会社 Turbo compressor

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6246830U (en) * 1985-09-12 1987-03-23
JPH0532653Y2 (en) * 1986-12-02 1993-08-20

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2018145969A (en) 2017-03-06 2018-09-20 パナソニックＩｐマネジメント株式会社 Turbo compressor

Also Published As

Publication number Publication date
JP2020060290A (en) 2020-04-16

Similar Documents

Publication Publication Date Title
JP5974582B2 (en) Bearing support structure
JP5936725B1 (en) Journal bearing device and rotating machine
RU2005132219A (en) DEVICE FOR SUPPORT AND DIRECTION OF A ROTATING SHAFT, TURBO MACHINE ROTARY SHAFT AND TURBO MACHINE
KR20150074036A (en) Fluid film hydrodynamic flexure pivot tilting pad semi-floating ring journal bearing with compliant dampers
CN109114106B (en) Bearing damper element, bearing and compressor element equipped therewith and method of manufacture
JP7253948B2 (en) Squeeze film damper and rotary machine
JPH0676806B2 (en) Support assembly for rotating shaft
JP6990122B2 (en) Blades and rotary machines
CN108799399B (en) Squeeze film damper assembly
JP4296292B2 (en) Fluid bearing
US11053977B2 (en) Squeeze film damper and rotary machine
JPH08505462A (en) Pressure damper seal
GB2317205A (en) Vibration damping bearing mount
JP2014043919A (en) Rolling bearing device for turbocharger
WO2018029836A1 (en) Journal bearing and rotary machine
WO2016043090A1 (en) Rotary machine
JPH11141545A (en) Squeeze film damper bearing
WO2019187023A1 (en) Rotating machine and turbocharger
JP2018017136A (en) Motor pump
JP7396489B2 (en) supercharger
WO2020183933A1 (en) Rotating machine, and seal ring
JP6437838B2 (en) Journal bearing and rotating machine
JP6403594B2 (en) Journal bearing and rotating machine
JP6403593B2 (en) Journal bearing and rotating machine
JP6651599B2 (en) Variable nozzle mechanism and rotating machine equipped with the same

Legal Events

Date Code Title Description
A521 Request for written amendment filed

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20200212

A521 Request for written amendment filed

Free format text: JAPANESE INTERMEDIATE CODE: A821

Effective date: 20200212

A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20211220

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20220915

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20220927

A521 Request for written amendment filed

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20221128

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20230228

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20230328

R150 Certificate of patent or registration of utility model

Ref document number: 7253948

Country of ref document: JP

Free format text: JAPANESE INTERMEDIATE CODE: R150

S111 Request for change of ownership or part of ownership

Free format text: JAPANESE INTERMEDIATE CODE: R313113

R350 Written notification of registration of transfer

Free format text: JAPANESE INTERMEDIATE CODE: R350