JP2003028146A - Guide bearing device - Google Patents
Guide bearing deviceInfo
- Publication number
- JP2003028146A JP2003028146A JP2001214766A JP2001214766A JP2003028146A JP 2003028146 A JP2003028146 A JP 2003028146A JP 2001214766 A JP2001214766 A JP 2001214766A JP 2001214766 A JP2001214766 A JP 2001214766A JP 2003028146 A JP2003028146 A JP 2003028146A
- Authority
- JP
- Japan
- Prior art keywords
- guide
- bearing device
- rotating body
- guide sector
- sector
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 239000012530 fluid Substances 0.000 claims abstract description 28
- 230000001050 lubricating effect Effects 0.000 claims abstract description 28
- 239000000463 material Substances 0.000 claims abstract description 24
- 239000010723 turbine oil Substances 0.000 claims abstract description 23
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 15
- 239000004696 Poly ether ether ketone Substances 0.000 claims abstract description 12
- 239000002657 fibrous material Substances 0.000 claims abstract description 12
- 229920002530 polyetherether ketone Polymers 0.000 claims abstract description 12
- 229920000049 Carbon (fiber) Polymers 0.000 claims abstract description 11
- 239000004917 carbon fiber Substances 0.000 claims abstract description 11
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 claims abstract description 11
- LFQSCWFLJHTTHZ-UHFFFAOYSA-N Ethanol Chemical compound CCO LFQSCWFLJHTTHZ-UHFFFAOYSA-N 0.000 claims abstract description 6
- 239000002861 polymer material Substances 0.000 claims description 3
- 238000012856 packing Methods 0.000 abstract 1
- 229910001361 White metal Inorganic materials 0.000 description 8
- 239000010969 white metal Substances 0.000 description 8
- JUPQTSLXMOCDHR-UHFFFAOYSA-N benzene-1,4-diol;bis(4-fluorophenyl)methanone Chemical compound OC1=CC=C(O)C=C1.C1=CC(F)=CC=C1C(=O)C1=CC=C(F)C=C1 JUPQTSLXMOCDHR-UHFFFAOYSA-N 0.000 description 7
- 238000013016 damping Methods 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
- OKKJLVBELUTLKV-UHFFFAOYSA-N Methanol Chemical compound OC OKKJLVBELUTLKV-UHFFFAOYSA-N 0.000 description 3
- 230000008602 contraction Effects 0.000 description 3
- 238000005461 lubrication Methods 0.000 description 3
- 239000002184 metal Substances 0.000 description 3
- 230000007423 decrease Effects 0.000 description 2
- 230000000704 physical effect Effects 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
- 238000005299 abrasion Methods 0.000 description 1
- 230000002238 attenuated effect Effects 0.000 description 1
- 238000009933 burial Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000002844 melting Methods 0.000 description 1
- 230000008018 melting Effects 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 229920000642 polymer Polymers 0.000 description 1
- 238000003756 stirring Methods 0.000 description 1
Landscapes
- Sliding-Contact Bearings (AREA)
- Support Of The Bearing (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】この発明は、例えば水車発電
機などの回転電機の回転体を支えるガイド軸受装置に関
するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a guide bearing device for supporting a rotating body of a rotating electric machine such as a water turbine generator.
【０００２】[0002]
【従来の技術】図７は、例えば特許２８０３９７２号公
報に開示された従来のガイド軸受装置を示す図であり、
図７（ａ）はガイド軸受装置の断面図、図７（ｂ）は平
面図であり、図において、符号１１は回転軸を中心とし
て回転する回転体、１２は回転体１１の半径方向荷重を
支持するガイドセクタ、１３はガイドセクタ１２の表面
に鋳込まれたホワイトメタル、１４はガイドセクタ１２
と回転体１１の間に設けられたギャップ、１５はギャッ
プ１４を調整するためのガイドセクタ１２の背面に設け
られた調整ボルト、１６は回転体１１とガイドセクタ１
２の間に満たされた潤滑流体であるタービン油、１７は
タービン油１６を収容する槽である。2. Description of the Related Art FIG. 7 is a diagram showing a conventional guide bearing device disclosed in, for example, Japanese Patent No. 2803972.
7A is a cross-sectional view of the guide bearing device, and FIG. 7B is a plan view. In the drawing, reference numeral 11 is a rotating body that rotates about a rotation axis, and 12 is a radial load of the rotating body 11. A guide sector to support, 13 is a white metal cast on the surface of the guide sector 12, and 14 is a guide sector 12
Between the rotor 11 and the rotating body 11, 15 is an adjusting bolt provided on the back surface of the guide sector 12 for adjusting the gap 14, 16 is the rotating body 11 and the guide sector 1.
Turbine oil that is a lubricating fluid filled between 2 and 17 is a tank that stores the turbine oil 16.
【０００３】次に従来のガイド軸受装置の動作について
説明する。回転軸１１の回転に伴い、タービン油１６は
回転体１１に引きずられてガイドセクタ１２の摺動面
（ホワイトメタル１３形成面）に流れ込む。タービン油
１６が摺動面に流れ込むことによって、ガイドセクタ１
２は、その表面にくさび膜を形成し、このくさび膜を介
して、回転体１１はガイドセクタ１２と接触することな
く回転することができる。また、回転体１１は回転電機
の機械的および磁気的なアンバランスによりギャップ１
４の中で振れ回りを生じようとするが、ガイドセクタ１
２の表面のくさび膜による剛性（バネ剛さ）および減衰
により振れ回りは抑えられる。このくさび膜の剛性およ
び減衰は使用する潤滑流体の粘度が高いほど、また回転
体１１とガイドセクタ１２間のギャップ１４が狭いほど
大きくなる。Next, the operation of the conventional guide bearing device will be described. As the rotating shaft 11 rotates, the turbine oil 16 is dragged by the rotating body 11 and flows into the sliding surface of the guide sector 12 (white metal 13 forming surface). When the turbine oil 16 flows into the sliding surface, the guide sector 1
2 forms a wedge film on its surface, and the rotating body 11 can rotate without contacting the guide sector 12 via this wedge film. In addition, the rotor 11 has a gap 1 due to the mechanical and magnetic imbalance of the rotating electric machine.
Attempt to generate whirling in 4 but guide sector 1
The whirling is suppressed by the rigidity (spring stiffness) and damping due to the wedge film on the surface of 2. The rigidity and damping of the wedge film increase as the viscosity of the lubricating fluid used increases and the gap 14 between the rotor 11 and the guide sector 12 decreases.
【０００４】回転電機のガイドセクタ１２の摺動面材料
として、一般的に用いられているホワイトメタルは、な
じみ性および異物の埋修性に優れているものの、融点が
２５０℃と低く、金属と接触したときの耐磨耗特性にも
乏しい。このため、回転電機のガイド軸受装置は、運転
時に回転体１１とガイドセクタ１２が金属接触しない十
分なギャップ１４を保ち、かつ、回転電機のアンバラン
スによる回転体１１の過大な振れ回りの発生を抑制する
のに十分なくさび膜の剛性と減衰を持つことができるよ
うに、潤滑流体として粘度の高いタービン油１６を使用
するとともに、ギャップ１４が０．１ｍｍ〜０．５ｍｍ
程度の適正な状態となるように据え付けられていた。White metal, which is generally used as a material for the sliding surface of the guide sector 12 of a rotating electric machine, has excellent conformability and burial of foreign matter, but has a low melting point of 250 ° C. It also has poor wear resistance when contacted. Therefore, the guide bearing device of the rotating electric machine maintains a sufficient gap 14 in which the rotating body 11 and the guide sector 12 do not come into metal contact with each other during operation, and an excessive whirling of the rotating body 11 due to an imbalance of the rotating electric machine occurs. Highly viscous turbine oil 16 is used as the lubricating fluid and the gap 14 is between 0.1 mm and 0.5 mm so that it can have sufficient wedge film stiffness and damping to suppress.
It was installed so that it was in a proper condition.
【０００５】例えば、５００ＭＶＡ級の水車発電機の場
合、ガイド軸受における回転体１１の摺動速度は７０ｍ
／ｓｅｃを超える。この周速で、ガイド軸受が境界潤滑
状態となり、軸受摺動面が回転体１１と金属接触する
と、軸受摺動面が溶融するため、発電機の運転が継続不
可能となる。このため、発電機の運転中は常に軸受温度
を監視し、軸受温度が設定温度を越えた時点で発電機を
直ちに緊急停止させるシーケンスとしている。For example, in the case of a 500 MVA class turbine generator, the sliding speed of the rotor 11 in the guide bearing is 70 m.
/ Sec is exceeded. At this peripheral speed, the guide bearing enters the boundary lubrication state, and when the bearing sliding surface makes metal contact with the rotating body 11, the bearing sliding surface is melted, so that the generator cannot continue to operate. For this reason, the bearing temperature is constantly monitored during operation of the generator, and the generator is immediately stopped immediately when the bearing temperature exceeds the set temperature.
【０００６】また、回転体１１が回転することで、ガイ
ドセクタ１２の摺動部分および回転体１１とタービン油
１６が接する部分では、タービン油１６にせん断流が生
じることで損失が発生する。このガイド軸受装置の損失
量は、タービン油１６の粘度および回転体１１とガイド
セクタ１２間のギャップ１４に大きく依存し、潤滑流体
の粘度が高いほど、あるいは、ギャップ１４が狭いほ
ど、発生する損失は大きくなり、例えば、５００ＭＶＡ
級の水車発電機の場合、１０００ｋＷにも達する。Further, as the rotating body 11 rotates, a shear flow is generated in the turbine oil 16 at a sliding portion of the guide sector 12 and a portion where the rotating body 11 and the turbine oil 16 are in contact with each other, resulting in loss. The loss amount of this guide bearing device largely depends on the viscosity of the turbine oil 16 and the gap 14 between the rotating body 11 and the guide sector 12, and the higher the viscosity of the lubricating fluid or the narrower the gap 14, the more loss that occurs. Becomes larger, for example, 500 MVA
In the case of a water turbine generator of the class, it reaches 1000kW.
【０００７】[0007]
【発明が解決しようとする課題】従来のガイド軸受装置
は、上記のように構成されているので、軸受内部に発生
する損失低下を目的として潤滑流体の粘度を低下させた
場合、くさび膜の剛性および減衰が低下し、回転体１１
の振れ回りが過大となるだけでなく、最悪の場合には回
転体１１とガイドセクタ１２が金属接触状態となり、ガ
イドセクタ１２が焼損する可能性があるなどの問題点が
あった。Since the conventional guide bearing device is constructed as described above, when the viscosity of the lubricating fluid is reduced in order to reduce the loss generated inside the bearing, the rigidity of the wedge film is reduced. And the damping is reduced, and the rotor 11
Not only becomes excessive, but in the worst case, the rotating body 11 and the guide sector 12 are brought into metal contact with each other, and there is a possibility that the guide sector 12 is burned.
【０００８】この発明は上記のような問題を解決するた
めになされたものであり、摺動面材料として、特に高温
時の機械強度および耐磨耗特性に優れた高分子材料ポリ
エーテルエーテルケトン（以下、ＰＥＥＫとする。）に
炭素繊維などの繊維材料を充填した材料を用いたガイド
セクタを回転体に押し付けた状態で据え付けるととも
に、軸受の潤滑流体としてタービン油よりも粘度の低
い、例えば水のような低粘度潤滑流体を使用すること
で、発生損失が少ないガイド軸受装置を得るとともに、
潤滑流体の粘度低下による回転軸の過大振動発生を防止
し、信頼性の高いガイド軸受装置を得ることを目的とし
ている。The present invention was made in order to solve the above problems, and as a sliding surface material, a polymer material polyetheretherketone (excellent in mechanical strength and abrasion resistance particularly at high temperature) (Hereinafter referred to as PEEK), a guide sector made of a material filled with a fiber material such as carbon fiber is installed in a state of being pressed against the rotating body, and the bearing lubricating fluid has a lower viscosity than turbine oil, such as water. By using such a low-viscosity lubricating fluid, a guide bearing device with less generated loss can be obtained, and
The purpose of the present invention is to prevent the occurrence of excessive vibration of the rotating shaft due to the decrease in the viscosity of the lubricating fluid and to obtain a highly reliable guide bearing device.
【０００９】[0009]
【課題を解決するための手段】この発明に係わるガイド
軸受装置は、回転体の荷重を支持するガイドセクタを備
えた回転電機のガイド軸受装置において、上記ガイドセ
クタの摺動面材料として、高分子材料ポリエーテルエー
テルケトンに繊維材料を充填した材料を用い、上記回転
体と上記ガイドセクタ間にタービン油より低粘度の潤滑
流体を満たし、上記ガイドセクタを上記回転体に押し付
けた状態で据え付けるものである。A guide bearing device according to the present invention is a guide bearing device for a rotary electric machine having a guide sector for supporting a load of a rotating body, wherein a polymer is used as a sliding surface material of the guide sector. Material Polyetheretherketone using a material filled with a fiber material, filled with a lubricating fluid having a viscosity lower than that of turbine oil between the rotor and the guide sector, and the guide sector is installed in a state of being pressed against the rotor. is there.
【００１０】また、この発明に係わるガイド軸受装置
は、上記のような構成において、上記繊維材料として炭
素繊維を用い、上記潤滑流体として水またはアルコール
を用いるものである。In the guide bearing device according to the present invention, carbon fiber is used as the fibrous material and water or alcohol is used as the lubricating fluid in the above structure.
【００１１】さらに、この発明に係わるガイド軸受装置
は、上記のような構成に加え、上記ガイドセクタの背面
側にバネを備えたものである。Further, the guide bearing device according to the present invention is provided with a spring on the back side of the guide sector in addition to the above structure.
【００１２】また、この発明に係わるガイド軸受装置
は、上記のような構成に加え、上記ガイドセクタの背面
側にダンパを備えたものである。Further, the guide bearing device according to the present invention has a damper on the back side of the guide sector in addition to the above structure.
【００１３】[0013]
【発明の実施の形態】実施の形態１．次に、この発明の
実施の形態１のガイド軸受装置について図１〜図４を用
いて説明する。図１はこの発明の実施の形態１の回転電
機のガイド軸受装置を示す図であり、図１（ａ）はガイ
ド軸受装置の断面図、図１（ｂ）は平面図である。図２
はガイド軸受装置を構成するガイドセクタの斜視図、図
３は水とタービン油との物性値を比較した図、図４は摺
動面材料として用いるＰＥＥＫに炭素繊維を含浸した材
料とホワイトメタルとの物性値を比較した図である。BEST MODE FOR CARRYING OUT THE INVENTION Embodiment 1. Next, the guide bearing device according to the first embodiment of the present invention will be described with reference to FIGS. 1 is a diagram showing a guide bearing device for a rotary electric machine according to Embodiment 1 of the present invention. FIG. 1 (a) is a sectional view of the guide bearing device, and FIG. 1 (b) is a plan view. Figure 2
Is a perspective view of a guide sector constituting a guide bearing device, FIG. 3 is a view comparing physical properties of water and turbine oil, and FIG. 4 is a PEEK material used as a sliding surface material, which is a material impregnated with carbon fiber, and white metal. It is the figure which compared the physical property value of.
【００１４】図において、１は回転軸を中心として回転
する回転体、２は回転体１の半径方向荷重を支持するガ
イドセクタ、３はガイドセクタ２の摺動面に設けられた
ＰＥＥＫに炭素繊維などを充填した摺動面材料、４はガ
イドセクタ２の回転体１への押し付け力を調整するため
にガイドセクタ２の背面に設けられた調整ボルト、５は
回転体１とガイドセクタ２の間に満たされる、タービン
油よりも粘度の低い低粘度潤滑流体、６は低粘度潤滑流
体５を収容するための槽である。なお、図１（ｂ）のＦ
で示す矢印は、ガイドセクタ２を回転体１の回転軸方向
に押し付ける押し付け力を示している。In the figure, 1 is a rotating body that rotates about a rotation axis, 2 is a guide sector that supports the radial load of the rotating body 1, and 3 is carbon fiber in PEEK provided on the sliding surface of the guide sector 2. And the like, 4 is an adjusting bolt provided on the back surface of the guide sector 2 for adjusting the pressing force of the guide sector 2 against the rotating body 1, and 5 is between the rotating body 1 and the guide sector 2. Is a low-viscosity lubricating fluid having a viscosity lower than that of the turbine oil, and 6 is a tank for containing the low-viscosity lubricating fluid 5. In addition, F of FIG.
The arrow indicated by indicates the pressing force for pressing the guide sector 2 in the rotation axis direction of the rotating body 1.
【００１５】従来のガイド軸受装置では、ガイドセクタ
の摺動面材料としてホワイトメタルを用いていたが、こ
の発明では、ホワイトメタルに代えて、ＰＥＥＫに繊維
材料として例えば炭素繊維を充填させた材料を用いる。
炭素繊維以外にも、ＰＥＥＫに充填させることで強度を
増すことができる繊維材料であれば、同様に用いること
ができる。さらに、従来では槽内に満たしていたのはタ
ービン油であったが、この発明ではタービン油（ＶＧ３
２：３０×１０-3Ｐａ・ｓｅｃ ａｔ １００℃）より
も低粘度の低粘度潤滑流体として、水またはそれと同等
の粘度のメタノール、メタノールなどのアルコールを満
たしている。さらに、ガイドセクタ２を回転体１に押し
付けた状態で据え付けている。In the conventional guide bearing device, white metal is used as the sliding surface material of the guide sector, but in the present invention, a material obtained by filling PEEK with a fiber material such as carbon fiber is used instead of the white metal. To use.
Other than carbon fiber, any fiber material can be similarly used as long as it is a fiber material whose strength can be increased by filling PEEK. Further, in the past, turbine oil was filled in the tank, but in the present invention, turbine oil (VG3
As a low-viscosity lubricating fluid having a viscosity lower than 2: 30 × 10 −3 Pa · sec at 100 ° C.), water or an alcohol such as methanol having a viscosity equivalent to that of water is filled. Further, the guide sector 2 is installed while being pressed against the rotating body 1.
【００１６】次に、この実施の形態１によるガイド軸受
装置の動作について説明する。回転電機の運転に伴い、
回転体１が回転すると、低粘度潤滑流体５は回転体１に
引きずられてガイドセクタ２の摺動面（摺動面材料３の
表面）に流れ込む。低粘度潤滑流体５がガイドセクタ２
の摺動面に強制的に供給されることにより、ガイドセク
タ２の表面には、くさび膜が形成され、そのくさび膜内
に圧力が発生することで、ガイドセクタ２は回転電機の
半径方向荷重および回転体１の振動を支持する。Next, the operation of the guide bearing device according to the first embodiment will be described. With the operation of the rotating electric machine,
When the rotating body 1 rotates, the low-viscosity lubricating fluid 5 is dragged by the rotating body 1 and flows into the sliding surface (the surface of the sliding surface material 3) of the guide sector 2. The low-viscosity lubricating fluid 5 is the guide sector 2
By being forcibly supplied to the sliding surface of the guide sector 2, a wedge film is formed on the surface of the guide sector 2, and pressure is generated in the wedge film, so that the guide sector 2 receives the radial load of the rotating electric machine. And supports the vibration of the rotating body 1.
【００１７】例えば、図３に示すように、水は、その粘
度が、１００℃の条件下で０．７×１０-3Ｐａ・ｓｅ
ｃ、タービン油（ＩＳＯ ＶＧ３２，４６，６８）は、
その粘度が、１００℃の条件下で３０〜５０×１０-3Ｐ
ａ・ｓｅｃであり、水の粘度はタービンの粘度の約１/
５０〜１/１００と低く、タービン油を使用する場合に
比べて同じギャップであれば水を潤滑流体として用いた
場合には、くさび膜の剛性および減衰定数は１/数１０
に低下する。しかしながら、ガイドセクタ２はその背面
に設けられた調整ボルト４により回転体１に一定の面圧
で押し当てられているため、回転体１は回転軸に向って
押し付けられるとともに、回転体１とガイドセクタ２間
の隙間は微小であり、回転体１は過大な振動が発生する
ことなく、回転電機を正常に運転することが可能とな
る。For example, as shown in FIG. 3, water has a viscosity of 0.7 × 10 −3 Pa · se under the condition of 100 ° C.
c, turbine oil (ISO VG32, 46, 68)
Its viscosity is 30 to 50 × 10 −3 P under the condition of 100 ° C.
a · sec, and the viscosity of water is about 1 / the viscosity of the turbine.
It is as low as 50 to 1/100, and when water is used as the lubricating fluid, the rigidity and damping constant of the wedge film are 1 / several tens when compared with the case where turbine oil is used, if the gap is the same.
Fall to. However, since the guide sector 2 is pressed against the rotating body 1 with a constant surface pressure by the adjusting bolt 4 provided on the back surface thereof, the rotating body 1 is pressed toward the rotating shaft and the rotating body 1 and the guide sector 2 are guided. The gap between the sectors 2 is very small, and the rotating body 1 can operate the rotating electric machine normally without generating excessive vibration.
【００１８】また、このとき、ガイドセクタ２の摺動面
は部分的に境界潤滑状態となるが、ガイドセクタ２の表
面に設けたＰＥＥＫに炭素繊維を含浸させた摺動面材料
３は、図４にその引張強さ、比磨耗量を示すように、従
来のホワイトメタルに比べて、高温時の機械強度および
耐磨耗性に優れている。具体的には、摺動面材料３の引
張強さ（１００℃の条件下で）、比磨耗量（７０℃の条
件下で）がそれぞれ、１５０Ｎ/ｍｍ2、３．５×１０-9
ｍｍ3/（Ｎｍ）であるのに対し、ホワイトメタルは、３
０Ｎ/ｍｍ2、８．３×１０-7ｍｍ3/（Ｎｍ）という値と
なっている。このため、ガイドセクタ２の摺動面の一部
が境界潤滑状態となっても、摺動面の損傷は軽微に抑え
られ、回転電機の運転を安定して継続することが可能で
ある。At this time, the sliding surface of the guide sector 2 is partially in the boundary lubrication state, but the sliding surface material 3 in which PEEK provided on the surface of the guide sector 2 is impregnated with carbon fiber is The tensile strength and the specific wear amount are shown in No. 4, which is superior to the conventional white metal in mechanical strength and wear resistance at high temperature. Specifically, the tensile strength of the sliding surface material 3 (under the condition of 100 ° C.) and the specific wear amount (under the condition of 70 ° C.) are 150 N / mm 2 , 3.5 × 10 −9 , respectively.
mm 3 / (Nm), while white metal has 3
The values are 0 N / mm 2 and 8.3 × 10 −7 mm 3 / (Nm). Therefore, even if a part of the sliding surface of the guide sector 2 is in the boundary lubrication state, damage to the sliding surface is suppressed to a slight extent, and the operation of the rotary electric machine can be stably continued.
【００１９】また、水はタービン油に比べて粘度が約１
/５０〜１/１００であり、従来のタービン油を潤滑流体
として使用したガイド軸受装置に比べて、回転体１の回
転に伴う攪拌損失は約１/３、ガイド軸受内部の摺動損
失は約１/１０に低減される。Further, water has a viscosity of about 1 as compared with turbine oil.
/ 50 to 1/100, which is about 1/3 of the stirring loss due to the rotation of the rotating body 1 and about the sliding loss inside the guide bearing, compared with the conventional guide bearing device using turbine oil as a lubricating fluid. It is reduced to 1/10.
【００２０】以上のように、この実施の形態１のガイド
軸受装置によれば、潤滑流体に水またはそれと同等の粘
度のアルコールなどの低粘度潤滑流体５を用い、ガイド
セクタ２の摺動面材料３としてＰＥＥＫに炭素繊維など
の繊維材料を充填した材料を使用するため、回転体１は
常に回転軸に向って押し付けられているとともに、回転
体１とガイドセクタ２との間の隙間は微小となるため、
回転体１に過大な振動が発生することなく回転電機を安
定して運転することが可能である。As described above, according to the guide bearing device of the first embodiment, the low-viscosity lubricating fluid 5 such as water or alcohol having the same viscosity as that is used as the lubricating fluid, and the sliding surface material of the guide sector 2 is used. Since PEEK is filled with a fiber material such as carbon fiber as the material 3, the rotor 1 is always pressed toward the rotation axis, and the gap between the rotor 1 and the guide sector 2 is very small. Because,
It is possible to stably operate the rotating electric machine without generating excessive vibration in the rotating body 1.
【００２１】また、定常運転時にガイド軸受摺動面が回
転体１と接触しても、摺動面の損傷は軽微に抑えること
ができ、回転電機の運転を安定して継続することができ
る。さらに、タービン油に比べて低粘度の潤滑流体をガ
イド軸受の潤滑流体として使用したので、ガイド軸受装
置内で発生する損失を低減することができ、ガイド軸受
装置の冷却器容量を低減できるとともに、回転電機の効
率を向上させることができる。Further, even if the sliding surface of the guide bearing comes into contact with the rotating body 1 during steady operation, damage to the sliding surface can be suppressed to a slight extent, and the operation of the rotary electric machine can be stably continued. Furthermore, since a lubricating fluid having a viscosity lower than that of turbine oil is used as the lubricating fluid for the guide bearing device, it is possible to reduce the loss generated in the guide bearing device and reduce the cooler capacity of the guide bearing device. The efficiency of the rotating electric machine can be improved.
【００２２】実施の形態２．図５はこの発明の実施の形
態２のガイド軸受装置を示す図であり、図５（ａ）はそ
の断面図、図５（ｂ）はその平面図をそれぞれ示してい
る。図において、符号７はガイドセクタ２の背面側に、
調整ボルト４との間に設けられたバネであり、その他、
既に説明に用いた符号と同一符号は同一または相当部分
を示すものである。Embodiment 2. 5A and 5B are views showing a guide bearing device according to a second embodiment of the present invention. FIG. 5A is a sectional view thereof and FIG. 5B is a plan view thereof. In the figure, reference numeral 7 is on the back side of the guide sector 2,
A spring provided between the adjusting bolt 4 and the other,
The same reference numerals as those already used in the description indicate the same or corresponding portions.
【００２３】上述の実施の形態１では、ガイドセクタ２
は回転体１に押し付けられて据え付けられることを示し
た。従って、槽６の熱変形や遠心力による回転体１の変
形などによりガイドセクタ２の押し付け力Ｆは大きく変
化し、ガイドセクタ２の回転体１への過大な押し付け力
が生じると摺動面の異常磨耗につながってしまう。そこ
で、図５に示すように、ガイドセクタ２と調整ボルト４
との間にバネ７を設けることで、槽６の熱変形や回転体
１の変形をバネ７の弾力性で吸収し、ガイドセクタ２の
押し付け力Ｆの変化量を低減することができる。さら
に、ガイドセクタ２の据え付け時の初期押し付け力がバ
ネ７の伸縮量により任意に設定できるため、押し付け力
の調整が容易となる。In the first embodiment described above, the guide sector 2
Indicates that the rotating body 1 is pressed and installed. Therefore, the pressing force F of the guide sector 2 changes greatly due to the thermal deformation of the tank 6 or the deformation of the rotating body 1 due to the centrifugal force, and when an excessive pressing force of the guide sector 2 against the rotating body 1 is generated, the sliding surface moves. It will lead to abnormal wear. Therefore, as shown in FIG. 5, the guide sector 2 and the adjusting bolt 4 are
By providing the spring 7 between and, the thermal deformation of the tank 6 and the deformation of the rotating body 1 can be absorbed by the elasticity of the spring 7, and the amount of change in the pressing force F of the guide sector 2 can be reduced. Further, the initial pressing force at the time of installing the guide sector 2 can be arbitrarily set by the expansion and contraction amount of the spring 7, so that the pressing force can be easily adjusted.
【００２４】実施の形態３．図６はこの発明の実施の形
態３のガイド軸受装置を示す図であり、図６（ａ）はそ
の断面図、図６（ｂ）はその平面図をそれぞれ示してい
る。図において、符号８はガイドセクタ２の背面側に、
調整ボルト４との間に設けられたダンパであり、このダ
ンパ８は、一般的には、上述の実施の形態２において示
したバネ７とともに用いる。その他、既に説明に用いた
符号と同一符号は同一または相当部分を示すものであ
る。Embodiment 3. 6A and 6B are views showing a guide bearing device according to a third embodiment of the present invention. FIG. 6A is a sectional view thereof, and FIG. 6B is a plan view thereof. In the figure, reference numeral 8 is on the back side of the guide sector 2,
The damper 8 is provided between the adjusting bolt 4 and the adjusting bolt 4, and the damper 8 is generally used together with the spring 7 shown in the second embodiment. In addition, the same reference numerals as those already used in the description indicate the same or corresponding portions.
【００２５】上述の実施の形態１および実施の形態２に
おいて示したように、ガイドセクタ２は回転体１に押し
付けられて据え付けられているため、回転体１の振動は
ガイドセクタ２を介して全て槽６に伝わることから、槽
６の疲労破壊や槽６に過大な振動が発生することが懸念
される。そこで、図６に示すように、ガイドセクタ２と
調整ボルト４との間にダンパ８を設けることで、回転体
１の振動をダンパ８で減衰し、槽６に伝わる振動を低減
することができ、ガイド軸受装置の信頼性を向上させる
ことができる。As shown in the above-described first and second embodiments, the guide sector 2 is installed by being pressed against the rotating body 1, so that the vibration of the rotating body 1 is entirely transmitted through the guide sector 2. Since it is transmitted to the tank 6, there is a concern that the tank 6 may be damaged by fatigue or excessive vibration may be generated in the tank 6. Therefore, as shown in FIG. 6, by providing a damper 8 between the guide sector 2 and the adjusting bolt 4, the vibration of the rotating body 1 can be attenuated by the damper 8 and the vibration transmitted to the tank 6 can be reduced. The reliability of the guide bearing device can be improved.
【００２６】[0026]
【発明の効果】以上説明したように、この発明のガイド
軸受装置によれば、回転体の荷重を支持するガイドセク
タを備えた回転電機のガイド軸受装置において、上記ガ
イドセクタの摺動面材料として、高分子材料ポリエーテ
ルエーテルケトンに繊維材料を充填した材料を用い、上
記回転体と上記ガイドセクタ間にタービン油より低粘度
の潤滑流体を満たし、上記ガイドセクタを上記回転体に
押し付けた状態で据え付けるため、このガイド軸受装置
の運転時に、回転体に過大な振動が発生することなく、
安定した運転をすることができ、ガイドセクタの摺動面
材料が回転体と接触したとしても、損傷は軽微に抑える
ことができ、回転電機の運転を継続することができる。
また、タービン油より低粘度の潤滑流体を使用すること
により、ガイド軸受装置内で発生する損失を低減するこ
とができる。As described above, according to the guide bearing device of the present invention, in the guide bearing device of the rotary electric machine provided with the guide sector for supporting the load of the rotating body, as the sliding surface material of the guide sector. In the state where the polymer material polyetheretherketone is filled with a fiber material, a lubricating fluid having a viscosity lower than that of turbine oil is filled between the rotor and the guide sector, and the guide sector is pressed against the rotor. Since it is installed, during the operation of this guide bearing device, excessive vibration does not occur in the rotating body,
Stable operation can be performed, and even if the sliding surface material of the guide sector comes into contact with the rotating body, damage can be suppressed to a slight extent, and operation of the rotating electric machine can be continued.
Further, by using a lubricating fluid having a viscosity lower than that of turbine oil, it is possible to reduce the loss generated in the guide bearing device.
【００２７】また、この発明のガイド軸受装置によれ
ば、上記繊維材料として炭素繊維を用い、上記潤滑流体
として水またはアルコールを用いることで、上記と同様
の効果を奏することができる。According to the guide bearing device of the present invention, carbon fiber is used as the fibrous material, and water or alcohol is used as the lubricating fluid, so that the same effect as described above can be obtained.
【００２８】さらに、この発明のガイド軸受装置によれ
ば、上記ガイドセクタの背面側にバネを備えたため、ガ
イド軸受装置の構成部品に変形が生じたとしても、その
変形に依存する変化量をバネの伸縮により吸収し、ガイ
ドセクタに過大な面圧が作用することを抑制し、ガイド
軸受装置の信頼性を向上させることができる。また、ガ
イドセクタの据え付け時の初期押し付け力をバネの伸縮
量により任意に設定できるため、押し付け力の調整が容
易となる。Further, according to the guide bearing device of the present invention, since the spring is provided on the back side of the guide sector, even if the components of the guide bearing device are deformed, the amount of change depending on the deformation is changed by the spring. It is possible to suppress the excessive surface pressure acting on the guide sector due to the expansion and contraction of the guide sector, and to improve the reliability of the guide bearing device. Moreover, since the initial pressing force at the time of installing the guide sector can be arbitrarily set by the expansion and contraction amount of the spring, the pressing force can be easily adjusted.
【００２９】また、この発明のガイド軸受装置によれ
ば、上記ガイドセクタの背面側にダンパを備えたため、
回転体の振動をダンパにより減衰することができ、ガイ
ド軸受装置の信頼性を向上させることができる。Further, according to the guide bearing device of the present invention, since the damper is provided on the back side of the guide sector,
The vibration of the rotating body can be damped by the damper, and the reliability of the guide bearing device can be improved.
【図１】 この発明の実施の形態１におけるガイド軸受
装置の断面図および平面図である。FIG. 1 is a sectional view and a plan view of a guide bearing device according to a first embodiment of the present invention.
【図２】 この発明の実施0の形態１におけるガイドセ
クタを示す斜視図である。FIG. 2 is a perspective view showing a guide sector according to the first embodiment of the present invention.
【図３】 この発明の実施の形態１の説明に必要な図で
ある。FIG. 3 is a diagram necessary for explaining Embodiment 1 of the present invention.
【図４】 この発明の実施の形態１の説明に必要な図で
ある。FIG. 4 is a diagram necessary for explaining Embodiment 1 of the present invention.
【図５】 この発明の実施の形態２におけるガイド軸受
装置の断面図および平面図である。5A and 5B are a sectional view and a plan view of a guide bearing device according to a second embodiment of the present invention.
【図６】 この発明の実施の形態３におけるガイド軸受
装置の断面図および平面図である。FIG. 6 is a sectional view and a plan view of a guide bearing device according to a third embodiment of the present invention.
【図７】 従来のガイド軸受装置を示す断面図および平
面図である。FIG. 7 is a sectional view and a plan view showing a conventional guide bearing device.
１ 回転体 ２ ガイドセクタ ３ 摺動面材料 ４ 調整ボルト ５ 低粘度潤滑流体 ６ 槽 ７ バネ ８ ダンパ。 1 rotating body 2 Guide sector 3 Sliding surface material 4 adjustment bolts 5 Low viscosity lubricating fluid 6 tanks 7 spring 8 Damper.
Claims (4)
備えた回転電機のガイド軸受装置において、上記ガイド
セクタの摺動面材料として、高分子材料ポリエーテルエ
ーテルケトンに繊維材料を充填した材料を用い、上記回
転体と上記ガイドセクタ間にタービン油より低粘度の潤
滑流体を満たし、上記ガイドセクタを上記回転体に押し
付けた状態で据え付けることを特徴とするガイド軸受装
置。1. A guide bearing device for a rotary electric machine comprising a guide sector for supporting a load of a rotating body, wherein a material obtained by filling a polymer material polyetheretherketone with a fiber material is used as a sliding surface material of the guide sector. A guide bearing device, characterized in that a lubricating fluid having a viscosity lower than that of turbine oil is filled between the rotating body and the guide sector, and the guide sector is installed while being pressed against the rotating body.
記潤滑流体として水またはアルコールを用いることを特
徴とする請求項１記載のガイド軸受装置。2. The guide bearing device according to claim 1, wherein carbon fiber is used as the fiber material, and water or alcohol is used as the lubricating fluid.
たことを特徴とする請求項１記載のガイド軸受装置。3. The guide bearing device according to claim 1, wherein a spring is provided on the back side of the guide sector.
えたことを特徴とする請求項１または請求項３記載のガ
イド軸受装置。4. The guide bearing device according to claim 1, wherein a damper is provided on the back side of the guide sector.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001214766A JP2003028146A (en) | 2001-07-16 | 2001-07-16 | Guide bearing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001214766A JP2003028146A (en) | 2001-07-16 | 2001-07-16 | Guide bearing device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2003028146A true JP2003028146A (en) | 2003-01-29 |
Family
ID=19049528
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2001214766A Pending JP2003028146A (en) | 2001-07-16 | 2001-07-16 | Guide bearing device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2003028146A (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007127026A (en) * | 2005-11-02 | 2007-05-24 | Hitachi Engineering & Services Co Ltd | Lubricating system for underwater bearing equipment |
| JP2007255614A (en) * | 2006-03-24 | 2007-10-04 | Hitachi Engineering & Services Co Ltd | Water lubricating guide bearing device and water turbine mounted with the same |
| WO2010079767A1 (en) * | 2009-01-09 | 2010-07-15 | 三菱重工業株式会社 | Damper structure and rotating machine |
| KR101294213B1 (en) | 2011-10-13 | 2013-08-08 | (주)동서기연 | A tilting pad of the bearing |
| US9512873B2 (en) | 2011-04-05 | 2016-12-06 | Kabushiki Kaisha Toshiba | Bearing device and hydraulic machine |
| WO2017042322A1 (en) | 2015-09-11 | 2017-03-16 | John Crane Bearing Technology Gmbh | Tilting segment and tilting segment sliding bearing |
-
2001
- 2001-07-16 JP JP2001214766A patent/JP2003028146A/en active Pending
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007127026A (en) * | 2005-11-02 | 2007-05-24 | Hitachi Engineering & Services Co Ltd | Lubricating system for underwater bearing equipment |
| JP2007255614A (en) * | 2006-03-24 | 2007-10-04 | Hitachi Engineering & Services Co Ltd | Water lubricating guide bearing device and water turbine mounted with the same |
| WO2010079767A1 (en) * | 2009-01-09 | 2010-07-15 | 三菱重工業株式会社 | Damper structure and rotating machine |
| JP2010159858A (en) * | 2009-01-09 | 2010-07-22 | Mitsubishi Heavy Ind Ltd | Damper structure and rotating machine |
| US8425118B2 (en) | 2009-01-09 | 2013-04-23 | Mitsubishi Heavy Industries, Ltd. | Damper structure and rotary machine |
| US9512873B2 (en) | 2011-04-05 | 2016-12-06 | Kabushiki Kaisha Toshiba | Bearing device and hydraulic machine |
| KR101294213B1 (en) | 2011-10-13 | 2013-08-08 | (주)동서기연 | A tilting pad of the bearing |
| WO2017042322A1 (en) | 2015-09-11 | 2017-03-16 | John Crane Bearing Technology Gmbh | Tilting segment and tilting segment sliding bearing |
| DE102015115385A1 (en) * | 2015-09-11 | 2017-03-16 | John Crane Bearing Technology Gmbh | Tilting segment and tilting pad plain bearing |
| JP2018526598A (en) * | 2015-09-11 | 2018-09-13 | ジョン・クレーン・ベアリング・テクノロジー・ゲゼルシャフト・ミト・ベシュレンクテル・ハフツング | Tilt segment and tilt segment sliding bearing |
| DE102015115385B4 (en) | 2015-09-11 | 2019-08-01 | Miba Industrial Bearings Germany Gmbh | Tilting segment and tilting pad plain bearing |
| US10393178B2 (en) | 2015-09-11 | 2019-08-27 | Miba Industrial Bearings Germany Gmbh | Tilting segment and tilting segment sliding bearing |
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