JP2013079633A - Steam turbine lubricating oil supply device and steam turbine system - Google Patents

Steam turbine lubricating oil supply device and steam turbine system Download PDF

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JP2013079633A
JP2013079633A JP2011221090A JP2011221090A JP2013079633A JP 2013079633 A JP2013079633 A JP 2013079633A JP 2011221090 A JP2011221090 A JP 2011221090A JP 2011221090 A JP2011221090 A JP 2011221090A JP 2013079633 A JP2013079633 A JP 2013079633A
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oil
lubricating oil
bearing
steam turbine
oil supply
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JP5868648B2 (en
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Kura Shindo
蔵 進藤
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Toshiba Corp
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Abstract

PROBLEM TO BE SOLVED: To facilitate adjustment of a supply oil amount of lubricating oil to a bearing, and enable fine adjustment of lubricating oil conditions to each bearing even during operation of a steam turbine.SOLUTION: According to one embodiment, a steam turbine lubricating oil supply device supplies lubricating oil to bearings 14a, 14b, ..., 14j supporting a rotary shaft 11 of the steam turbine 12. A circulation device includes: a bearing stand 15 covering the bearings; an oil tank 16 for storing lubricating oil; a main oil pump 17 driven by an AC electric motor 22 to raise pressure of lubricating oil in the oil tank 16; an oil supply pipe 28 for leading the lubricating oil whose pressure is raised by the main oil pump 17 to the bearings; an oil return pipe 32 for returning lubricating oil discharged from the bearing stand 15 to the oil tank 16; an oil cooler 20 for cooling lubricating oil; a throttle valve 31 disposed in the middle of the oil supply pipe 28; and a fixed orifice 30 connected in parallel with the throttle valve 31.

Description

本発明の実施形態は、蒸気タービン潤滑油供給装置および蒸気タービンシステムに関する。   Embodiments described herein relate generally to a steam turbine lubricating oil supply apparatus and a steam turbine system.

大型蒸気タービンの各軸受に潤滑油を供給する潤滑油供給装置では、軸受を覆う軸受台と、電動機によって駆動される主油ポンプと、主油ポンプで昇圧された潤滑油を油タンクから軸受に導く油供給管と、軸受台から排出された潤滑油を油タンクに戻す油戻り管と、を備えたものが知られている。   In a lubricating oil supply device that supplies lubricating oil to each bearing of a large steam turbine, a bearing base that covers the bearing, a main oil pump that is driven by an electric motor, and lubricating oil boosted by the main oil pump is transferred from the oil tank to the bearing. An oil supply pipe that guides the oil and a oil return pipe that returns the lubricating oil discharged from the bearing stand to the oil tank is known.

特開２０１０−１４２７０９号公報JP 2010-142709 A

大型蒸気タービンでは、回転軸が長くなり、軸受の数も多くなる。このため、油供給管が長くなって配管の圧力損失が増加し、油タンクから遠い軸受になればなるほど供給油圧が低下し本来の設計油圧を維持できない可能性がある。   In a large steam turbine, a rotating shaft becomes long and the number of bearings also increases. For this reason, the oil supply pipe becomes longer, the pressure loss of the pipe increases, and the further away the bearing is from the oil tank, the lower the supply hydraulic pressure, and the original design hydraulic pressure may not be maintained.

また、軸受の数が多くなることにより、軸受の不安定事象（軸振動等）の発生する確率が高まる。これに対処すべく軸受への潤滑油量を増加させて不安定事象の対策を施す場合には、各軸受の直前に設置された軸受オリフィスを取り外してオリフィス孔サイズの微調整を試行錯誤で行う必要があった。このため、その都度蒸気タービンを停止する必要がありこれら起動・停止操作も含めた一連の作業が非常に煩雑であった。   In addition, an increase in the number of bearings increases the probability of occurrence of unstable events (shaft vibration or the like) of the bearings. In order to cope with this, when taking measures against unstable events by increasing the amount of lubricating oil to the bearing, the bearing orifice installed immediately before each bearing is removed and fine adjustment of the orifice hole size is performed by trial and error. There was a need. For this reason, it is necessary to stop the steam turbine each time, and a series of operations including starting and stopping operations are very complicated.

本発明の実施形態は上述の点を鑑みてなされたものであり、軸受への潤滑油の供給油量の調整が容易にでき、さらには蒸気タービンの運転中であっても蒸気タービンを停止することなく、各軸受の潤滑油条件を微調整できるようにすることを目的とする。   The embodiment of the present invention has been made in view of the above points, and can easily adjust the amount of lubricating oil supplied to the bearing, and can also stop the steam turbine even during operation of the steam turbine. An object of the present invention is to make it possible to finely adjust the lubricating oil conditions of each bearing.

本発明の実施形態に係る蒸気タービン潤滑油供給装置は、蒸気タービンの回転軸を回転保持する複数の軸受に潤滑油を供給する蒸気タービン潤滑油供給装置において、前記軸受を覆う軸受台と、前記軸受よりも低い位置に配置されて前記潤滑油を溜める油タンクと、第１の電動機によって駆動されて前記油タンク内の潤滑油を昇圧する主油ポンプと、前記主油ポンプで昇圧された潤滑油を前記軸受に導く油供給管と、前記軸受台から排出された潤滑油を落下させて前記油タンクに戻す油戻り管と、前記油供給管の途中に配置された絞り弁と、前記絞り弁に並列に接続された固定オリフィスと、を有することを特徴とする。   A steam turbine lubricating oil supply device according to an embodiment of the present invention is a steam turbine lubricating oil supply device that supplies lubricating oil to a plurality of bearings that rotate and hold a rotating shaft of a steam turbine. An oil tank that is disposed at a position lower than the bearing and stores the lubricating oil, a main oil pump that is driven by a first electric motor to increase the pressure of the lubricating oil in the oil tank, and a lubricating pressure that is increased by the main oil pump An oil supply pipe for guiding oil to the bearing, an oil return pipe for dropping the lubricating oil discharged from the bearing base and returning it to the oil tank, a throttle valve disposed in the middle of the oil supply pipe, and the throttle And a fixed orifice connected in parallel to the valve.

また、本発明の実施形態に係る蒸気タービンシステムは、回転軸およびその回転軸を回転保持する複数の軸受を含む蒸気タービンと、前記複数の軸受に潤滑油を供給する潤滑油供給装置と、を有する蒸気タービンシステムにおいて、前記潤滑油供給装置は、前記軸受を覆う軸受台と、前記軸受よりも低い位置に配置されて前記潤滑油を溜める油タンクと、第１の電動機によって駆動されて前記油タンク内の潤滑油を昇圧する主油ポンプと、前記主油ポンプで昇圧された潤滑油を前記軸受に導く油供給管と、前記軸受台から排出された潤滑油を落下させて前記油タンクに戻す油戻り管と、前記油供給管の途中に配置された絞り弁と、前記絞り弁に並列に接続された固定オリフィスと、を有すること、を特徴とする。   In addition, a steam turbine system according to an embodiment of the present invention includes a steam turbine that includes a rotating shaft and a plurality of bearings that rotate and hold the rotating shaft, and a lubricating oil supply device that supplies lubricating oil to the plurality of bearings. In the steam turbine system, the lubricating oil supply device includes a bearing base that covers the bearing, an oil tank that is disposed at a lower position than the bearing and stores the lubricating oil, and is driven by a first electric motor so that the oil A main oil pump that boosts the lubricating oil in the tank, an oil supply pipe that guides the lubricating oil boosted by the main oil pump to the bearing, and drops the lubricating oil discharged from the bearing base into the oil tank. It has an oil return pipe for returning, a throttle valve arranged in the middle of the oil supply pipe, and a fixed orifice connected in parallel to the throttle valve.

本発明の実施形態によれば、蒸気タービンの複数の軸受への潤滑油の供給油量の調整が容易にでき、さらには蒸気タービンの運転中であっても蒸気タービンを停止することなく、各軸受の潤滑油条件を微調整できる。これにより、蒸気タービンの稼働率向上を図ることができる。   According to the embodiment of the present invention, it is possible to easily adjust the amount of lubricating oil supplied to a plurality of bearings of a steam turbine, and further, without stopping the steam turbine even during operation of the steam turbine, Fine adjustment of the lubricating oil conditions of the bearing. Thereby, the operation rate improvement of a steam turbine can be aimed at.

本発明に係る蒸気タービン潤滑油供給装置の第１の実施形態を示す系統構成図である。1 is a system configuration diagram showing a first embodiment of a steam turbine lubricating oil supply device according to the present invention. 本発明に係る蒸気タービン潤滑油供給装置の第２の実施形態を示す系統構成図である。It is a system configuration | structure figure which shows 2nd Embodiment of the steam turbine lubricating oil supply apparatus which concerns on this invention. 本発明に係る蒸気タービン潤滑油供給装置の第３の実施形態を示す系統構成図である。It is a system configuration | structure figure which shows 3rd Embodiment of the steam turbine lubricating oil supply apparatus which concerns on this invention. 図３の個別容積型昇圧ポンプユニットの具体的構成を示す構成図である。It is a block diagram which shows the specific structure of the separate volume type | mold pressure | voltage rise pump unit of FIG.

以下、本発明の実施形態について、図面を参照して説明する。ここで、互いに同一または類似の部分には共通の符号を付して、重複説明は省略する。   Hereinafter, embodiments of the present invention will be described with reference to the drawings. Here, the same or similar parts are denoted by common reference numerals, and redundant description is omitted.

［第１の実施形態］
図１は、本発明に係る蒸気タービン潤滑油供給装置の第１の実施形態を示す系統構成図である。 [First Embodiment]
FIG. 1 is a system configuration diagram showing a first embodiment of a steam turbine lubricating oil supply device according to the present invention.

共通の回転軸１１に複数の蒸気タービン１２および発電機１３が結合されていて、これらが、複数（図示の例では１０個）の軸受１４ａ、１４ｂ、・・・、１４ｊによって回転支持されている。回転軸１１は水平方向に延びている。軸受台１５は、軸受１４ａ、１４ｂ、・・・、１４ｊを収納するとともに軸受１４ａ、１４ｂ、・・・、１４ｊの周囲を密閉するように覆っており、回転軸１１との接触部分にはラビリンスパッキンを使用した図示しない油切りシールが設けられている。   A plurality of steam turbines 12 and a generator 13 are coupled to a common rotating shaft 11, and these are rotatably supported by a plurality of bearings 14a, 14b, ..., 14j (10 in the illustrated example). . The rotating shaft 11 extends in the horizontal direction. The bearing stand 15 accommodates the bearings 14a, 14b,..., 14j and covers the bearings 14a, 14b,. An oil drain seal (not shown) using a packing is provided.

軸受１４ａ、１４ｂ、・・・、１４ｊよりも下方に、潤滑油を溜める油タンク１６が配置されている。油タンク１６には、２台の主油ポンプ１７、１８と、非常用油ポンプ１９と油冷却器２０と、ガス抽出機２１が取り付けられている。２台の主油ポンプ１７、１８は、交流電動機（第１の電動機）２２、２３によって駆動される。交流電動機２２、２３の電源は電力系統から得る。２台の主油ポンプ１７、１８のうちの１台は常用の主油ポンプ１７であり、他の１台はバックアップ用の主油ポンプ１８である。非常用油ポンプ１９は非常用の直流電源（図示せず）により、直流電動機（第３の電動機）２４によって駆動される。   An oil tank 16 for storing lubricating oil is disposed below the bearings 14a, 14b, ..., 14j. Two main oil pumps 17 and 18, an emergency oil pump 19, an oil cooler 20, and a gas extractor 21 are attached to the oil tank 16. The two main oil pumps 17 and 18 are driven by AC motors (first motors) 22 and 23. The power sources of the AC motors 22 and 23 are obtained from the power system. One of the two main oil pumps 17, 18 is a regular main oil pump 17, and the other is a backup main oil pump 18. The emergency oil pump 19 is driven by a DC motor (third motor) 24 by an emergency DC power source (not shown).

油タンク１６内に溜まった潤滑油は、２台の主油ポンプ１７、１８および非常用油ポンプ１９から、それぞれ、逆止弁２５、２６、２７を介して油冷却器２０に送れられるように構成されている。油冷却器２０は潤滑油を冷却することができる。   The lubricating oil accumulated in the oil tank 16 is sent from the two main oil pumps 17 and 18 and the emergency oil pump 19 to the oil cooler 20 through check valves 25, 26, and 27, respectively. It is configured. The oil cooler 20 can cool the lubricating oil.

油冷却器２０を出た潤滑油は、油供給管２８を通して、油タンク１６の外に送り出される。油供給管２８は分岐していて潤滑油を各軸受１４ａ、１４ｂ、・・・、１４ｊに供給することができる。油供給管２８の分岐の下流側で各軸受１４ａ、１４ｂ、・・・、１４ｊの上流側に軸受オリフィス２９ａ、２９ｂ、・・・、２９ｊが取り付けられている。   The lubricating oil exiting the oil cooler 20 is sent out of the oil tank 16 through the oil supply pipe 28. The oil supply pipe 28 is branched and can supply lubricating oil to the bearings 14a, 14b,. Bearing orifices 29a, 29b,..., 29j are attached downstream of the branch of the oil supply pipe 28 and upstream of the bearings 14a, 14b,.

油冷却器２０を出た潤滑油が分岐する上流側の油供給管２８には固定オリフィス３０が配置され、この固定オリフィス３０と並列に絞り弁３１が配置されている。   A fixed orifice 30 is arranged in the upstream oil supply pipe 28 where the lubricating oil exiting the oil cooler 20 branches, and a throttle valve 31 is arranged in parallel with the fixed orifice 30.

軸受台１５と油タンク１６の間で油供給管２８を覆うように油戻り管３２が配置されており、軸受１４ａ、１４ｂ、・・・、１４ｊに供給された潤滑油は油戻り管３２を通って重力により油タンク１６に落下するように構成されている。   An oil return pipe 32 is disposed between the bearing base 15 and the oil tank 16 so as to cover the oil supply pipe 28, and the lubricating oil supplied to the bearings 14 a, 14 b,. It is configured to pass through the oil tank 16 due to gravity.

油タンク１６内には潤滑油の液面３３が形成され、ガス抽出機２１は、液面３３より上の空間に溜まったガスを排出する。これにより、油タンク１６内の液面３３より上の空間および軸受台１５内および油戻り管３２内部の空間を、大気圧に対して負圧に保つことができる。   A liquid level 33 of the lubricating oil is formed in the oil tank 16, and the gas extractor 21 discharges the gas accumulated in the space above the liquid level 33. Thereby, the space above the liquid level 33 in the oil tank 16 and the space in the bearing stand 15 and the oil return pipe 32 can be maintained at a negative pressure with respect to the atmospheric pressure.

固定オリフィス３０および絞り弁３１よりも下流側で一つの軸受オリフィス２９ａよりも上流側の油供給管２８に圧力計３４が取り付けられている。   A pressure gauge 34 is attached to the oil supply pipe 28 downstream of the fixed orifice 30 and the throttle valve 31 and upstream of the one bearing orifice 29a.

潤滑油は主油ポンプ１７、１８から排出され、油冷却器２０によって冷却された後に、互いに並列に設置された固定オリフィス３０と絞り弁３１を通過する。その後、軸受オリフィス２９ａ、２９ｂ、・・・、２９ｊを通して各軸受１４ａ、１４ｂ、・・・、１４ｊに供給される。   The lubricating oil is discharged from the main oil pumps 17 and 18, cooled by the oil cooler 20, and then passes through the fixed orifice 30 and the throttle valve 31 installed in parallel to each other. Thereafter, the bearings are supplied to the bearings 14a, 14b,..., 14j through the bearing orifices 29a, 29b,.

各軸受１４ａ、１４ｂ、・・・、１４ｊに供給される潤滑油は、固定オリフィス３０と絞り弁３１に分かれて全量通過するが、固定オリフィス３０で潤滑油量の支配的な分量を流し、絞り弁３１は油圧の微調整のための少量を流すように設計されている。したがって、蒸気タービン１２の起動前の油圧調整に当たって、複数の軸受オリフィス２９ａ、２９ｂ、・・・、２９ｊのうちの一つの軸受オリフィス２９ａの上流に設置された圧力計３４により、その軸受１４ａに供給される潤滑油（軸受給油）の圧力値を確認し、適正な設計圧力値でなければ絞り弁３１の弁開度を任意に調整すればよい。   The lubricating oil supplied to each of the bearings 14a, 14b,..., 14j is divided into the fixed orifice 30 and the throttle valve 31, and passes through the entire amount. The valve 31 is designed to flow a small amount for fine adjustment of the hydraulic pressure. Therefore, when adjusting the hydraulic pressure before starting the steam turbine 12, the pressure gauge 34 installed upstream of one of the plurality of bearing orifices 29a, 29b,..., 29j is supplied to the bearing 14a. The pressure value of the lubricating oil (bearing oil supply) to be used is confirmed, and if the design pressure value is not appropriate, the valve opening of the throttle valve 31 may be arbitrarily adjusted.

この第１の実施形態では、電動機駆動の主油ポンプ１７、１８を有することから、蒸気タービン１２の起動前に潤滑油（軸受給油）の圧力値を確定することができる利点がある。これにより、蒸気タービンの複数の軸受への潤滑油の供給油量の調整が容易にでき、さらには蒸気タービンの運転中であっても蒸気タービンを停止することなく、各軸受の潤滑油条件を微調整できる。これにより、蒸気タービンの稼働率向上を図ることができる。   In the first embodiment, since the motor driven main oil pumps 17 and 18 are provided, there is an advantage that the pressure value of the lubricating oil (bearing oil supply) can be determined before the steam turbine 12 is started. This makes it easy to adjust the amount of lubricating oil supplied to a plurality of bearings of the steam turbine, and even during operation of the steam turbine, the lubricating oil conditions of each bearing can be adjusted without stopping the steam turbine. Fine adjustment. Thereby, the operation rate improvement of a steam turbine can be aimed at.

以上説明した実施形態では、固定オリフィス３０と絞り弁３１は、油冷却器２０の下流側に配置するものとしたが、変形例として、固定オリフィス３０と絞り弁３１を油冷却器２０の上流側に配置することもできる。この場合でも作用・効果は上記の例と同様である。また、変形例として、図示しないが、油圧監視用として圧力計をその他の軸受オリフィスの前に設置することもできる。   In the embodiment described above, the fixed orifice 30 and the throttle valve 31 are arranged on the downstream side of the oil cooler 20, but as a modification, the fixed orifice 30 and the throttle valve 31 are arranged on the upstream side of the oil cooler 20. It can also be arranged. Even in this case, the action and effect are the same as in the above example. As a modification, although not shown, a pressure gauge can be installed in front of other bearing orifices for monitoring the hydraulic pressure.

［第２の実施形態］
図２は、本発明に係る蒸気タービン潤滑油供給装置の第２の実施形態を示す系統構成図である。 [Second Embodiment]
FIG. 2 is a system configuration diagram showing a second embodiment of the steam turbine lubricating oil supply device according to the present invention.

この実施形態では、油冷却器２０と、固定オリフィス３０および絞り弁３１の間の分岐点３５で油供給管２８が分岐していて、分岐した一方の油供給管（第１の油供給管）２８ａに固定オリフィス３０ａおよび絞り弁３１ａが互いに並列に接続されているとともに、分岐した他方の油供給管（第２の油供給管）２８ｂにも同様に固定オリフィス３０ｂおよび絞り弁３１ｂが互いに並列に接続されている。第１の油供給管２８ａおよび第２の油供給管２８ｂは、それぞれが、さらに下流側で分岐して、第１の油供給管２８ａは、分岐部に近い位置から順に１番目から６番目の軸受１４ａ、１４ｂ、・・・、１４ｆ（第１の軸受グループ）に接続され、第２の油供給管２８ｂは、分岐部に近い位置から順に７番目受から１０番目の軸受１４ｇ、１４ｈ、１４ｉ、１４ｊ（第２の軸受グループ）に、それぞれの軸受オリフィス２９ａ、２９ｂ、・・・、２９ｊを介して接続されている。   In this embodiment, the oil supply pipe 28 is branched at a branch point 35 between the oil cooler 20 and the fixed orifice 30 and the throttle valve 31, and one branched oil supply pipe (first oil supply pipe). The fixed orifice 30a and the throttle valve 31a are connected in parallel with each other 28a, and the fixed orifice 30b and the throttle valve 31b are similarly connected in parallel with the other branched oil supply pipe (second oil supply pipe) 28b. It is connected. Each of the first oil supply pipe 28a and the second oil supply pipe 28b is further branched on the downstream side, and the first oil supply pipe 28a is first to sixth in order from the position close to the branch portion. The second oil supply pipe 28b is connected to the bearings 14a, 14b,..., 14f (first bearing group) and the seventh to tenth bearings 14g, 14h, 14i in order from the position close to the branch portion. , 14j (second bearing group) through respective bearing orifices 29a, 29b,..., 29j.

固定オリフィス３０ａおよび絞り弁３１ａよりも下流側で第１の軸受グループの一つの軸受オリフィス２９ａよりも上流側の第１の油供給管２８ａに第１の圧力計３４ａが取り付けられており、同様に、固定オリフィス３０ｂおよび絞り弁３１ｂよりも下流側で第２の軸受グループの一つの軸受オリフィス２９ｇよりも上流側の第２の油供給管２８ｂに第２の圧力計３４ｇが取り付けられている。他の構成は第１の実施形態と同様である。   A first pressure gauge 34a is attached to a first oil supply pipe 28a downstream of the fixed orifice 30a and the throttle valve 31a and upstream of one bearing orifice 29a of the first bearing group. The second pressure gauge 34g is attached to the second oil supply pipe 28b downstream of the fixed orifice 30b and the throttle valve 31b and upstream of one bearing orifice 29g of the second bearing group. Other configurations are the same as those of the first embodiment.

この実施形態で、蒸気タービン１２の起動前の油圧調整時に、第１の圧力計３４ａにより、第１の軸受グループに供給される潤滑油（軸受給油）の圧力値を確認し、適正な設計圧力値でなければ第１グループの絞り弁３１ａの弁開度を調整する。   In this embodiment, when adjusting the hydraulic pressure before starting the steam turbine 12, the pressure value of the lubricating oil (bearing oil) supplied to the first bearing group is confirmed by the first pressure gauge 34a, and an appropriate design pressure is confirmed. If not, the valve opening of the first group of throttle valves 31a is adjusted.

また同様に、蒸気タービン１２の起動前の油圧調整時に、第２の圧力計３４ｇにより、第２の軸受グループに供給される潤滑油の圧力値を確認し、適正な設計圧力値でなければ第２グループの絞り弁３１ｂの弁開度を調整する。   Similarly, when the hydraulic pressure is adjusted before the steam turbine 12 is started, the pressure value of the lubricating oil supplied to the second bearing group is confirmed by the second pressure gauge 34g. The valve opening degree of the two groups of throttle valves 31b is adjusted.

なお、第２グループにおける固定オリフィス３０ｂと絞り弁３１ｂの下流側圧力（出口圧力）は、第１グループに比べ油供給配管が長くなっており、配管の圧力損失が生じるので、両グループの固定オリフィスのサイズが同一であれば、第２グループの絞り弁３１ｂの方が弁開度が大きいように（絞りが少ないように）設定される。   Note that the downstream pressure (outlet pressure) of the fixed orifice 30b and the throttle valve 31b in the second group is longer in the oil supply pipe than in the first group, and pressure loss of the pipe occurs. Are the same, the second group of throttle valves 31b is set so that the valve opening is larger (the throttle is less).

以上説明したように、第２の実施形態によれば、油タンク１６から離れた第２グループであっても、軸受１４ｇ、１４ｈ、１４ｉ、１４ｊに供給される油圧は第１グループと変わらずに調整することができる。なお、グループ数を増加させればさらに小まめな設定が可能となる。   As described above, according to the second embodiment, the hydraulic pressure supplied to the bearings 14g, 14h, 14i, and 14j is the same as that in the first group even in the second group separated from the oil tank 16. Can be adjusted. If the number of groups is increased, a smaller setting can be made.

［第３の実施形態］
図３は、本発明に係る蒸気タービン潤滑油供給装置の第３の実施形態を示す系統構成図である。また、図４は、図３の個別容積型昇圧ポンプユニットの具体的構成を示す構成図である。 [Third Embodiment]
FIG. 3 is a system configuration diagram showing a third embodiment of the steam turbine lubricating oil supply device according to the present invention. FIG. 4 is a block diagram showing a specific configuration of the individual volume type booster pump unit of FIG.

この第３の実施形態は第１の実施形態の変形である。この第３の実施形態では、軸受オリフィス２９ａ、２９ｂ、・・・、２９ｊの各上流側の油供給管２８に個別ポンプユニット３６ａ、３６ｂ、・・・、３６ｊが配置されている。個別ポンプユニット３６ａ、３６ｂ、・・・、３６ｊはそれぞれ、図４に示すように、互いに並列に接続された個別容積型昇圧ポンプ３７と個別逆止弁３８とを有する。個別容積型昇圧ポンプ３７は交流電動機（第２の電動機）３９によって駆動される。図では個別ポンプユニット３６ａを例にとってその構成を示しているが、他の個別ポンプユニットも同様の構成である。   This third embodiment is a modification of the first embodiment. In the third embodiment, individual pump units 36a, 36b,..., 36j are arranged in the oil supply pipes 28 on the upstream side of the bearing orifices 29a, 29b,. Each of the individual pump units 36a, 36b,..., 36j includes an individual positive pressure pump 37 and an individual check valve 38 connected in parallel to each other, as shown in FIG. The individual positive pressure pump 37 is driven by an AC motor (second motor) 39. In the drawing, the configuration is shown by taking the individual pump unit 36a as an example, but the other individual pump units have the same configuration.

個別容積型昇圧ポンプ３７は、油冷却器２０を出て固定オリフィス３０または絞り弁３１を通った潤滑油を昇圧して軸受オリフィス２９ａ、２９ｂ、・・・、２９ｊへ送るものである。個別容積型昇圧ポンプ３７は、たとえば、ギアポンプやベーンポンプ、ネジポンプなどに代表される容積型ポンプである。個別容積型昇圧ポンプ３７を駆動する電動機は、誘導電動機を使用し、回転数を可変速にすることが可能な図示しないインバータを設置して回転数の設定を行うように構成されているのが好ましい。個別容積型昇圧ポンプ３７の流量は回転数に比例することから、流量を制御することができる。   The individual volume type booster pump 37 boosts the lubricating oil that has exited the oil cooler 20 and passed through the fixed orifice 30 or the throttle valve 31 and sends it to the bearing orifices 29a, 29b,..., 29j. The individual positive displacement pump 37 is a positive displacement pump represented by a gear pump, a vane pump, a screw pump, or the like. The electric motor that drives the individual positive pressure pump 37 uses an induction motor, and is configured to set the rotational speed by installing an inverter (not shown) capable of making the rotational speed variable. preferable. Since the flow rate of the individual positive pressure pump 37 is proportional to the rotational speed, the flow rate can be controlled.

個別逆止弁３８は、個別容積型昇圧ポンプ３７の吐出側から吸い込み側への逆流を阻止し、個別容積型昇圧ポンプ３７の吸い込み側から吐出側へ個別容積型昇圧ポンプ３７を通らずに流れる流れを許容するものである。   The individual check valve 38 prevents a reverse flow from the discharge side to the suction side of the individual positive pressure booster pump 37 and flows from the suction side to the discharge side of the individual positive pressure booster pump 37 without passing through the individual positive pressure pump 37. It allows flow.

また、図３に示すように、個別ポンプユニット３６ａ、３６ｂ、・・・、３６ｊの下流側で各軸受オリフィス２９ａ、２９ｂ、・・・、２９ｊの上流側の給油管それぞれに、圧力計３４ａ、３４ｂ、・・・、３４ｊが取り付けられている。   In addition, as shown in FIG. 3, pressure gauges 34a, 36a, 36b,..., 36j are respectively provided on the oil supply pipes upstream of the bearing orifices 29a, 29b,. 34b, ..., 34j are attached.

他の構成は第１の実施形態と同様である。   Other configurations are the same as those of the first embodiment.

この第３の実施形態によれば、蒸気タービン１２の起動前の油圧調整時に主油ポンプ１７を起動し、固定オリフィス３０と絞り弁３１を通過した潤滑油（軸受給油）は、各軸受１４ａ、１４ｂ、・・・、１４ｊに設置された個別ポンプユニット３６ａ、３６ｂ、・・・、３６ｊ内の個別逆止弁３８を通り各軸受オリフィス２９ａ、２９ｂ、・・・、２９ｊを通って各軸受１４ａ、１４ｂ、・・・、１４ｊに給油される。   According to the third embodiment, the main oil pump 17 is activated at the time of hydraulic pressure adjustment before the activation of the steam turbine 12, and the lubricating oil (bearing oil) that has passed through the fixed orifice 30 and the throttle valve 31 is supplied to each bearing 14a, .., 14j, the individual pump units 36a, 36b,..., 36j through the individual check valves 38 and the bearing orifices 29a, 29b,. , 14b,..., 14j.

この時、個別容積型昇圧ポンプ３７は停止しており、容積型の油ポンプであることから、個別容積型昇圧ポンプ３７の内部を通過する流れは生じない。また、固定オリフィス３０と絞り弁３１の開度は第１の実施形態と同じように調整されているため、各軸受１４ａ、１４ｂ、・・・、１４ｊに給油される状況は第１の実施形態と同様である。   At this time, the individual positive displacement pump 37 is stopped and is a positive displacement oil pump, so that no flow passes through the individual positive displacement pump 37. Further, since the opening degrees of the fixed orifice 30 and the throttle valve 31 are adjusted in the same manner as in the first embodiment, the situation where the oil is supplied to the bearings 14a, 14b,. It is the same.

やがて蒸気タービン１２を起動した後、たとえば第７の軸受１４ｇに不安定事象（軸振動等）が発生した場合、第７の軸受１４ｇに設置された個別ポンプユニット３６ｇの個別容積型昇圧ポンプ３７を起動し、第７の軸受１４ｇに対応する軸受オリフィス２９ｇの上流に設置された圧力計３４ｇを見ながら、この個別ポンプユニット３６ｇの個別容積型昇圧ポンプ３７の回転数を変化させて軸受オリフィス２９ｇの入口圧力を上昇させ、軸受１４ｇへの給油量を増加させるように作動させる。この時、個別ポンプユニット３６ｇの個別逆止弁３８の吐出側圧力は個別ポンプユニット３６ｇの個別容積型昇圧ポンプ３７の吐出圧となるので個別ポンプユニット３６ｇの個別逆止弁３８は閉止する。   Eventually, after starting the steam turbine 12, for example, when an unstable event (shaft vibration or the like) occurs in the seventh bearing 14g, the individual displacement type booster pump 37 of the individual pump unit 36g installed in the seventh bearing 14g is changed. Starting up, while looking at the pressure gauge 34g installed upstream of the bearing orifice 29g corresponding to the seventh bearing 14g, the rotational speed of the individual positive pressure pump 37 of this individual pump unit 36g is changed to change the bearing orifice 29g. The inlet pressure is increased, and the oil supply amount to the bearing 14g is increased. At this time, since the discharge side pressure of the individual check valve 38 of the individual pump unit 36g becomes the discharge pressure of the individual positive pressure pump 37 of the individual pump unit 36g, the individual check valve 38 of the individual pump unit 36g is closed.

なお、たとえば個別ポンプユニット３６ｇの個別容積型昇圧ポンプ３７を停止させると、油供給管２８からの潤滑油（軸受給油）は、その個別ポンプユニット３６ｇの個別逆止弁３８を開弁し軸受オリフィス２９ｇを介して軸受１４ｇに給油される。そのため、たとえ個別容積型昇圧ポンプ３７の運転中に不適合が発生して停止しても、潤滑油（軸受給油）は確実に給油される。   For example, when the individual displacement type booster pump 37 of the individual pump unit 36g is stopped, the lubricating oil (bearing oil) from the oil supply pipe 28 opens the individual check valve 38 of the individual pump unit 36g and opens the bearing orifice. Oil is supplied to the bearing 14g through 29g. Therefore, even if a nonconformity occurs during operation of the individual positive pressure pump 37 and stops, the lubricating oil (bearing oil) is reliably supplied.

以上のように、第３の実施形態によれば各軸受１４ａ、１４ｂ、・・・、１４ｊに供給される潤滑油流量を単独で個別に調整することができ、またその不安定事象（軸振動等）の変化状況（対策状況）を同時進行で確認しながら調整できる利点があるため、蒸気タービンを停止する必要がない。   As described above, according to the third embodiment, the flow rate of the lubricating oil supplied to each of the bearings 14a, 14b,..., 14j can be individually adjusted, and the unstable event (shaft vibration) Etc.), it is not necessary to stop the steam turbine.

なお、図３では全ての軸受１４ａ、１４ｂ、・・・、１４ｊに対応させて個別ポンプユニット３６ａ、３６ｂ、・・・、３６ｊを設置したが、対象となる蒸気タービン１２の種類によってはその必要はなく、経験的に不安定事象（軸振動等）の発生しやすい軸受にのみ設置することでもよい。   In FIG. 3, individual pump units 36a, 36b,..., 36j are installed corresponding to all the bearings 14a, 14b,..., 14j, but this is necessary depending on the type of the target steam turbine 12. However, it may be installed only on bearings that are empirically unstable (shaft vibration, etc.).

また、油タンク１６から遠い軸受における油圧低下問題を解決するためには、油タンク１６から遠い軸受にのみ個別ポンプユニットを設置してもよい。   Further, in order to solve the problem of the hydraulic pressure drop in the bearing far from the oil tank 16, the individual pump unit may be installed only in the bearing far from the oil tank 16.

［他の実施形態］
以上、本発明のいくつかの実施形態を説明したが、これらの実施形態は、例として提示したものであり、発明の範囲を限定することは意図していない。これら実施形態は、その他の様々な形態で実施されることが可能であり、発明の要旨を逸脱しない範囲で、種々の省略、置き換え、変更を行うことができる。これら実施形態やその変形は、発明の範囲や要旨に含まれると同様に、特許請求の範囲に記載された発明とその均等の範囲に含まれるものである。 [Other Embodiments]
As mentioned above, although some embodiment of this invention was described, these embodiment is shown as an example and is not intending limiting the range of invention. These embodiments can be implemented in various other forms, and various omissions, replacements, and changes can be made without departing from the spirit of the invention. These embodiments and their modifications are included in the scope and gist of the invention, and are also included in the invention described in the claims and the equivalents thereof.

たとえば、上記第２の実施形態の特徴と第３の実施形態の特徴を組み合わせて適用することもできる。   For example, the features of the second embodiment and the features of the third embodiment can be applied in combination.

１１ 回転軸
１２ 蒸気タービン
１３ 発電機
１４ａ，１４ｂ，・・・，１４ｊ 軸受
１５ 軸受台
１６ 油タンク
１７、１８ 主油ポンプ
１９ 非常用油ポンプ
２０ 油冷却器
２１ ガス抽出機
２２、２３ 交流電動機（第１の電動機）
２４ 直流電動機（第３の電動機）
２５、２６、２７ 逆止弁
２８，２８ａ，２８ｂ 油供給管
２９ａ，２９ｂ，・・・，２９ｊ 軸受オリフィス
３０，３０ａ，３０ｂ 固定オリフィス
３１，３１ａ，３１ｂ 絞り弁
３２ 油戻り管
３３ 液面
３４，３４ａ，３４ｂ，・・・，３４ｊ 圧力計
３５ 分岐点
３６ａ，３６ｂ，・・・，３６ｊ 個別ポンプユニット
３７ 個別容積型昇圧ポンプ
３８ 個別逆止弁
３９ 交流電動機（第２の電動機） DESCRIPTION OF SYMBOLS 11 Rotating shaft 12 Steam turbine 13 Generator 14a, 14b, ..., 14j Bearing 15 Bearing stand 16 Oil tank 17, 18 Main oil pump 19 Emergency oil pump 20 Oil cooler 21 Gas extractor 22, 23 AC motor ( First electric motor)
24 DC motor (third motor)
25, 26, 27 Check valves 28, 28a, 28b Oil supply pipes 29a, 29b, ..., 29j Bearing orifices 30, 30a, 30b Fixed orifices 31, 31a, 31b Throttle valves 32 Oil return pipes 33 Liquid level 34, 34j Pressure gauge 35 Branch points 36a, 36b,..., 36j Individual pump unit 37 Individual volumetric booster pump 38 Individual check valve 39 AC motor (second motor)

Claims (12)

蒸気タービンの回転軸を回転保持する複数の軸受に潤滑油を供給する蒸気タービン潤滑油供給装置において、
前記軸受を覆う軸受台と、
前記軸受よりも低い位置に配置されて前記潤滑油を溜める油タンクと、
第１の電動機によって駆動されて前記油タンク内の潤滑油を昇圧する主油ポンプと、
前記主油ポンプで昇圧された潤滑油を前記軸受に導く油供給管と、
前記軸受台から排出された潤滑油を落下させて前記油タンクに戻す油戻り管と、
前記油供給管の途中に配置された絞り弁と、
前記絞り弁に並列に接続された固定オリフィスと、
を有することを特徴とする蒸気タービン潤滑油供給装置。 In a steam turbine lubricating oil supply device that supplies lubricating oil to a plurality of bearings that rotate and hold a rotating shaft of a steam turbine,
A bearing stand covering the bearing;
An oil tank disposed at a position lower than the bearing and storing the lubricating oil;
A main oil pump driven by a first electric motor to boost the lubricating oil in the oil tank;
An oil supply pipe for guiding the lubricating oil boosted by the main oil pump to the bearing;
An oil return pipe for dropping the lubricating oil discharged from the bearing stand and returning it to the oil tank;
A throttle valve disposed in the middle of the oil supply pipe;
A fixed orifice connected in parallel to the throttle valve;
A steam turbine lubricating oil supply device comprising: 前記複数の軸受は複数の軸受グループに分けられ、
前記油供給管は、前記複数の軸受グループそれぞれに対応して分岐しており、
前記絞り弁および固定オリフィスが前記油供給管の分岐のそれぞれに配置されていること、
を特徴とする請求項１に記載の蒸気タービン潤滑油供給装置。 The plurality of bearings are divided into a plurality of bearing groups,
The oil supply pipe is branched corresponding to each of the plurality of bearing groups,
The throttle valve and the fixed orifice are disposed in each branch of the oil supply pipe,
The steam turbine lubricating oil supply device according to claim 1. 前記複数の軸受それぞれの上流側の前記油供給管に各軸受ごとの軸受オリフィスが配置されていることを特徴とする請求項１または請求項２に記載の蒸気タービン潤滑油供給装置。   The steam turbine lubricating oil supply device according to claim 1 or 2, wherein a bearing orifice for each bearing is arranged in the oil supply pipe on the upstream side of each of the plurality of bearings. 前記軸受オリフィスそれぞれの上流側の前記油供給管に前記第１の電動機とは別の個別の第２の電動機によって駆動される個別容積型昇圧ポンプが配置され、
前記個別容積型昇圧ポンプに並列に、当該個別容積型昇圧ポンプの駆動方向に逆向きの流れを阻止する個別逆止弁が配置されていること、
を特徴とする請求項３に記載の蒸気タービン潤滑油供給装置。 An individual positive pressure pump driven by an individual second electric motor different from the first electric motor is disposed in the oil supply pipe on the upstream side of each of the bearing orifices,
In parallel with the individual positive pressure booster pump, an individual check valve for preventing a reverse flow in the driving direction of the individual positive pressure booster pump is disposed,
The steam turbine lubricating oil supply device according to claim 3. 前記油供給配管の前記絞り弁および固定オリフィスより下流側で前記軸受の上流側に圧力計が取り付けられていることを特徴とする請求項１に記載の蒸気タービン潤滑油供給装置。   The steam turbine lubricating oil supply device according to claim 1, wherein a pressure gauge is attached to the upstream side of the bearing on the downstream side of the throttle valve and fixed orifice of the oil supply pipe. 前記油供給配管の分岐のそれぞれに、前記絞り弁および固定オリフィスより下流側で前記軸受の上流側に圧力計が取り付けられていることを特徴とする請求項２に記載の蒸気タービン潤滑油供給装置。   The steam turbine lubricating oil supply device according to claim 2, wherein a pressure gauge is attached to each branch of the oil supply pipe and downstream of the throttle valve and fixed orifice and upstream of the bearing. . 前記油供給配管の前記個別容積型昇圧ポンプの下流側で前記軸受オリフィスの上流側それぞれに圧力計が取り付けられていることを特徴とする請求項４に記載の蒸気タービン潤滑油供給装置。   The steam turbine lubricating oil supply device according to claim 4, wherein a pressure gauge is attached to each upstream side of the bearing orifice on the downstream side of the individual positive pressure pump in the oil supply pipe. 前記主油ポンプの下流側で前記軸受の上流側の前記油供給管に潤滑油を冷却する油冷却機が設けられていること、を特徴とする請求項１ないし請求項７のいずれか一項に記載の蒸気タービン潤滑油供給装置。   8. The oil cooler for cooling the lubricating oil is provided in the oil supply pipe on the downstream side of the main oil pump and on the upstream side of the bearing. 8. The steam turbine lubricating oil supply apparatus described in 1. 前記主油ポンプは複数台が並列に接続されていること、を特徴とする請求項１ないし請求項８のいずれか一項に記載の蒸気タービン潤滑油供給装置。   The steam turbine lubricating oil supply device according to any one of claims 1 to 8, wherein a plurality of the main oil pumps are connected in parallel. 第３の電動機によって駆動されて前記油タンク内の潤滑油を昇圧する非常用油ポンプをさらに有し、
前記非常用油ポンプで昇圧された潤滑油は前記主油ポンプと並列に接続されて前記油供給管に接続されており、
前記第３の電動機は非常用直流電源で駆動される電動機であること、
を特徴とする請求項１ないし請求項９のいずれか一項に記載の蒸気タービン潤滑油供給装置。 An emergency oil pump that is driven by a third electric motor and pressurizes the lubricating oil in the oil tank;
The lubricating oil boosted by the emergency oil pump is connected in parallel to the main oil pump and connected to the oil supply pipe,
The third electric motor is an electric motor driven by an emergency DC power supply;
The steam turbine lubricating oil supply device according to any one of claims 1 to 9, wherein: 前記油タンクに溜められた前記潤滑油の上方の前記油タンク内のガスを抽出するガス抽出機をさらに有すること、を特徴とする請求項１ないし請求項１０のいずれか一項に記載の蒸気タービン潤滑油供給装置。   The steam according to any one of claims 1 to 10, further comprising a gas extractor that extracts gas in the oil tank above the lubricating oil stored in the oil tank. Turbine lubricant supply device. 回転軸および前記回転軸を回転保持する複数の軸受を含む蒸気タービンと、前記複数の軸受に潤滑油を供給する潤滑油供給装置と、を有する蒸気タービンシステムにおいて、
前記潤滑油供給装置は、
前記軸受を覆う軸受台と、
前記軸受よりも低い位置に配置されて前記潤滑油を溜める油タンクと、
第１の電動機によって駆動されて前記油タンク内の潤滑油を昇圧する主油ポンプと、
前記主油ポンプで昇圧された潤滑油を前記軸受に導く油供給管と、
前記軸受台から排出された潤滑油を落下させて前記油タンクに戻す油戻り管と、
前記油供給管の途中に配置された絞り弁と、
前記絞り弁に並列に接続された固定オリフィスと、
を有すること、を特徴とする蒸気タービンシステム。 In a steam turbine system comprising: a rotating turbine and a steam turbine including a plurality of bearings that rotate and hold the rotating shaft; and a lubricating oil supply device that supplies lubricating oil to the plurality of bearings,
The lubricating oil supply device includes:
A bearing stand covering the bearing;
An oil tank disposed at a position lower than the bearing and storing the lubricating oil;
A main oil pump driven by a first electric motor to boost the lubricating oil in the oil tank;
An oil supply pipe for guiding the lubricating oil boosted by the main oil pump to the bearing;
An oil return pipe for dropping the lubricating oil discharged from the bearing stand and returning it to the oil tank;
A throttle valve disposed in the middle of the oil supply pipe;
A fixed orifice connected in parallel to the throttle valve;
A steam turbine system.
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CN103470935A (en) * 2013-08-30 2013-12-25 江苏江海润液设备有限公司 Lubricating oil device of gas turbine
CN104235194A (en) * 2014-09-11 2014-12-24 兖州煤业股份有限公司 Steam turbine generator unit
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CN105402582A (en) * 2015-12-29 2016-03-16 中国长江三峡集团公司 Entire shafting synchronous shaft automatic forced lubrication pressure device and method
CN106246247A (en) * 2016-09-29 2016-12-21 华北电力科学研究院有限责任公司 A kind of thermal power plant's Turbo-generator Set lubricating oil system and on off control method thereof
CN107355663A (en) * 2017-06-26 2017-11-17 江苏江海润液设备有限公司 A kind of control method of phase modulation lubricating oil system
CN110821581A (en) * 2019-11-06 2020-02-21 四川航天中天动力装备有限责任公司 Hot-end fuel lubricating oil pipeline structure of turbine engine
KR20210115639A (en) * 2020-03-16 2021-09-27 홍재준 Lubricating oil supply system and a control method of the same
KR20210115637A (en) * 2020-03-16 2021-09-27 홍재준 Lubricating oil supply system and a control method of the same
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KR102373357B1 (en) * 2020-03-16 2022-03-11 홍재준 Lubricating oil supply system and a control method of the same

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