JPS62101808A - Device for regulating bearing lubrication pressure - Google Patents
Device for regulating bearing lubrication pressureInfo
- Publication number
- JPS62101808A JPS62101808A JP24153985A JP24153985A JPS62101808A JP S62101808 A JPS62101808 A JP S62101808A JP 24153985 A JP24153985 A JP 24153985A JP 24153985 A JP24153985 A JP 24153985A JP S62101808 A JPS62101808 A JP S62101808A
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- valve
- oil
- pressure regulating
- regulating valve
- 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
Abstract
Description
【発明の詳細な説明】
〔発明の利用分野〕
本発明は、タービン潤滑油設備の中で、軸受の潤滑油系
統の油圧を、制御し、ポンプ起動時においても、正常な
油圧の、潤滑油を供給するための装置である。Detailed Description of the Invention [Field of Application of the Invention] The present invention controls the oil pressure of a lubricating oil system of a bearing in a turbine lubricating oil equipment, and maintains the lubricating oil at normal oil pressure even when the pump is started. This is a device for supplying
従来のタービン潤滑油の軸受供給圧力の調整は圧力調整
弁の出口側(二次圧)の油圧でのみ制御していたため調
整弁の特性から、油圧ポンプ起動時に、圧力の上昇に追
従して、弁を閉じることが出来ずに、必要以上に、軸受
給油圧力が上昇し。Conventionally, the bearing supply pressure of turbine lubricating oil was controlled only by the hydraulic pressure on the outlet side (secondary pressure) of the pressure regulating valve. Due to the characteristics of the regulating valve, when the hydraulic pump is started, it follows the rise in pressure. The valve could not be closed, and the bearing oil supply pressure increased more than necessary.
給油系統に悪影響を及ぼす結果となった。なお、この種
の装置として、関連するものに、例えば、実開昭59−
84202号がある。This resulted in a negative impact on the refueling system. In addition, related devices of this type include, for example, Utility Model Application No. 59-
There is No. 84202.
本発明の目的は、主油ポンプ起動時に、潤滑油圧力調整
弁により、発生する圧力調整弁出口の油圧上昇を防止し
、タービンの各軸受への供給油圧の正常化と、本系統に
、設置されている計器の誤動作による事故を防止するこ
とにある。The purpose of the present invention is to prevent the oil pressure from rising at the outlet of the pressure adjustment valve that occurs when the main oil pump starts up, and to normalize the oil pressure supplied to each bearing of the turbine. The aim is to prevent accidents caused by malfunction of the instruments used.
従来、タービン発電プラントにおいて、軸受への潤滑油
の供給油圧変動により、軸受油圧の異常という、計器関
係の誤動作を生じ、軸受への悪影響を与えた事柄につい
て着目した。In the past, in turbine power generation plants, we focused on a problem in which fluctuations in the oil pressure supplied to lubricating oil to the bearings caused abnormalities in the bearing oil pressure, which caused instrument-related malfunctions and had a negative impact on the bearings.
軸受供給油圧の異常は、軸受給油圧力調整弁の構造から
生じており、機構を改善することにより、最適化するこ
ととした。The abnormality in the bearing oil supply pressure was caused by the structure of the bearing oil supply pressure regulating valve, and we decided to optimize it by improving the mechanism.
上記で、述べた、圧力調整弁は、弁出口側圧力を、感知
し、弁を閉じる機構となっていたが、本発明は、圧力変
動を生じる、起動時には、弁入口側の圧力に一時的に制
御させ、通常運転に入った時には、弁出口側圧力により
、制御を行う形にする調整装置である。The pressure regulating valve described above has a mechanism that senses the pressure on the valve outlet side and closes the valve, but the present invention temporarily changes the pressure on the valve inlet side at the time of startup, which causes pressure fluctuations. This is an adjustment device that controls the valve by the pressure on the valve outlet side when normal operation begins.
本発明の詳細な説明する。 The present invention will be described in detail.
第2図に、潤滑油供給系統の基本概略図を示す。FIG. 2 shows a basic schematic diagram of the lubricating oil supply system.
主油ポンプ1又は2を運転(起動)し、油を軸受給油配
管4を通し、−次圧力調整弁5により、油圧を約5Kに
減圧し、次に、油冷却器6を経て、配管7より二次圧力
調整弁8に入り、圧力を約1.2Kに減圧し、配管1o
を経て、タービン16のロータ13と軸受15との間に
潤滑油を供給し、軸受排油は、軸受箱14より排油管1
7を通り、油タンク9に戻る。また、配管4には一次圧
力調整弁5の出口側に、非常用油ポンプ3が接続してお
り、主油ポンプ1,2とも、故障の際は、軸受給油を行
うため、起動する形となっている。The main oil pump 1 or 2 is operated (started), the oil is passed through the bearing oil supply pipe 4, the oil pressure is reduced to approximately 5K by the second pressure regulating valve 5, and then the oil is passed through the oil cooler 6 to the pipe 7. enters the secondary pressure regulating valve 8, reduces the pressure to approximately 1.2K, and connects the pipe 1o.
lubricating oil is supplied between the rotor 13 of the turbine 16 and the bearing 15, and the bearing waste oil is passed from the bearing box 14 to the oil drain pipe 1.
7 and return to oil tank 9. In addition, an emergency oil pump 3 is connected to the piping 4 at the outlet side of the primary pressure regulating valve 5, and both the main oil pumps 1 and 2 are configured to start in order to supply bearing oil in the event of a failure. It has become.
主油ポンプは、1台がバックアンプ用として設置されて
いる。One main oil pump is installed for the backup amplifier.
潤滑油供給系統において、潤滑油の圧力は、主油ポンプ
出口よりの圧油を、圧力調整弁5,8にて2段階に減圧
している。しかし、圧力調整の際、圧力調整弁の構造的
問題から、起動待圧力が、異常上昇する。これにより、
軸受及び計器類に悪影響をおよぼす。悪影響を排除する
ことを目的としている。In the lubricating oil supply system, the pressure of the lubricating oil is reduced in two stages by pressure regulating valves 5 and 8 from the main oil pump outlet. However, when adjusting the pressure, the starting pressure increases abnormally due to a structural problem with the pressure regulating valve. This results in
Adversely affects bearings and instruments. The purpose is to eliminate negative effects.
圧力調整弁の構造を第3図に示す。The structure of the pressure regulating valve is shown in Figure 3.
圧力調整弁8について、油の流れと、出口圧力の調整、
メカニズムを説明する。Regarding the pressure regulating valve 8, adjusting the oil flow and outlet pressure,
Explain the mechanism.
入口ボート16′より流入する油の圧力が低い場合、出
口側ボート17′に入った油の圧力が低いため、油流入
ボート12′より、油室18′に入る油の圧力も低く、
弁体9′を上方向(閉方向)に動作させるダイヤフラム
13′に加わる圧力が小さく、バネ14′の力が打勝て
ず、開のままの状態となる。しかし、供給油の圧力が上
昇するのに伴い、油室18に加わる力が上昇し、弁体9
′を引き上げ、閉方向に動作する。(本邦上部に。When the pressure of the oil flowing into the inlet boat 16' is low, the pressure of the oil entering the outlet boat 17' is low, so the pressure of the oil entering the oil chamber 18' is also lower than that of the oil inlet boat 12'.
The pressure applied to the diaphragm 13' that moves the valve body 9' upward (in the closing direction) is small, and the force of the spring 14' cannot be overcome, resulting in the valve body remaining open. However, as the pressure of the supplied oil increases, the force applied to the oil chamber 18 increases, and the valve body 9
′ and moves in the closing direction. (In the upper part of Japan.
設置されているバネ14′とボルト15′は、出口側の
圧力の調整用として用いられている)ポンプ1が起動す
る際、調整弁の減圧機構の応答性から、圧力上昇に追従
出来ず、弁開度と二次油圧特性が第4図の如くあられれ
てしまう。これは、ポンプ起動の時、圧力調整弁8の出
口側(二次側)が圧力OKであり、弁は全開の状態とな
っており、起動直後には、全開状態を維持してしまうた
めである。この特性を、第6図に示している。The installed spring 14' and bolt 15' are used to adjust the pressure on the outlet side.) When the pump 1 starts up, it is unable to follow the pressure increase due to the responsiveness of the pressure reducing mechanism of the regulating valve. The valve opening degree and secondary hydraulic characteristics will be distorted as shown in Fig. 4. This is because when the pump is started, the pressure on the outlet side (secondary side) of the pressure regulating valve 8 is OK and the valve is fully open, and it remains fully open immediately after starting. be. This characteristic is shown in FIG.
ポンプ起動時の圧力、−次油圧(調整弁入口側)特性を
、A1に示している。調整弁出口(二次側)油圧特性を
A4に示している。通常運転時の圧力をP4とし、配管
設計圧力をP3’ とすると、二次油圧のピークは、
P3にあられれ、設計圧力を越えてしまう。これにより
、各軸受及び計器類に悪影響を及ぼすのである。The pressure and secondary oil pressure (adjustment valve inlet side) characteristics at pump startup are shown in A1. The hydraulic characteristics of the regulating valve outlet (secondary side) are shown in A4. Assuming that the pressure during normal operation is P4 and the piping design pressure is P3', the peak of the secondary hydraulic pressure is:
P3 will fall and the design pressure will be exceeded. This adversely affects bearings and instruments.
本発明は、この圧力変動の調整を行うことでタービン潤
滑油設備の保護を目的としている。The present invention aims to protect turbine lubricating oil equipment by adjusting this pressure fluctuation.
軸受給油圧力調整装置の構造(機構)を第1図に示す。The structure (mechanism) of the bearing oil supply pressure adjustment device is shown in Fig. 1.
本装置において、二次圧力調整弁の構造は、出口側の油
流入ボート12′を削除し、圧力調整装置Eよりのボー
ト32を設ける。In this device, the structure of the secondary pressure regulating valve is such that the oil inflow boat 12' on the outlet side is removed and a boat 32 from the pressure regulating device E is provided.
圧力調整装置Eは、起動特配管7より減圧していない油
圧を配管26に導き、オリフィス29により流量を制限
し、次に安全弁30にて、油圧力を軸受給油圧力より少
し下げ、配管27を通し、パイロットハウジング20の
下部ボートDとアキュームレータ31及びパイロット弁
ボートAに油を供給する。油はボートAよりボートBに
流れ、圧力調整弁8の弁体駆動部に流入し、調整弁を閉
方向に動かす。しかし、弁体9の動作は、アキュームレ
ータ31に油が流入するため、配管19よりの油の分圧
が低下するために、除々に閉じ、圧力の上昇カーブは第
7図、F3に示すように勾配がゆるやかとなる。又、ポ
ンプ起動時、油圧が上昇して行くと、ボートDより供給
されている油圧により、パイロット弁の弁体は、パイロ
ット上部に設置されているバネ23の力に打ち勝って、
上側へ動作し、ポートGとポートBに油が流れ、圧力調
整弁8の二次側(出口側)油圧を制御し、滑らかに移行
する。出口側圧力制御に移行した状態を第5図に示す。The pressure regulator E guides the unreduced hydraulic pressure from the startup special pipe 7 to the pipe 26, restricts the flow rate with the orifice 29, and then lowers the hydraulic pressure slightly below the bearing oil supply pressure with the safety valve 30, and then controls the pipe 27. Through this, oil is supplied to the lower boat D of the pilot housing 20, the accumulator 31, and the pilot valve boat A. Oil flows from boat A to boat B, flows into the valve body driving section of pressure regulating valve 8, and moves the regulating valve in the closing direction. However, as oil flows into the accumulator 31, the partial pressure of oil from the pipe 19 decreases, so the valve body 9 gradually closes, and the pressure rise curve becomes as shown in F3 in FIG. The slope becomes gentle. Furthermore, when the pump is started, as the oil pressure increases, the oil pressure supplied from the boat D causes the valve body of the pilot valve to overcome the force of the spring 23 installed above the pilot.
It moves upward, causing oil to flow into ports G and B, controlling the secondary side (outlet side) hydraulic pressure of the pressure regulating valve 8, and making a smooth transition. FIG. 5 shows a state in which the pressure control on the outlet side has been started.
本機構を用いた場合の二次圧力変化を、第8図に示す。Figure 8 shows the secondary pressure change when this mechanism is used.
二次圧力は、第6図に示すような圧力ピークがなく、か
つ滑らかに通常運転圧力P4に移行している。The secondary pressure has no pressure peaks as shown in FIG. 6, and smoothly transitions to the normal operating pressure P4.
第9図に、電磁パイロットを用いた実施例について示す
。FIG. 9 shows an embodiment using an electromagnetic pilot.
油圧パイロットとの差について示す。The difference with the hydraulic pilot is shown below.
ポンプ1が起動すると、起動スイッチより信号が入力線
36よりタイマー35に入る。When the pump 1 is started, a signal from the start switch is input to the timer 35 via the input line 36.
このタイマーは、起動よりある時間、電磁弁パイロット
33のコイルに行く電気を止める。その時間長さは、第
8図のTaで示すことが出来る。This timer stops the electricity going to the coil of the solenoid valve pilot 33 for a certain period of time after activation. The time length can be indicated by Ta in FIG.
13時間が過ぎると、電気が電磁パイロット33のコイ
ルを励時、パイロット弁のボートを切換える。After 13 hours, electricity energizes the coil of the electromagnetic pilot 33 and switches the pilot valve boat.
本発明によれば、タービン潤滑油系統の軸受給油系統に
おいて、軸受給油圧力の過大圧力の変動による。計装関
連の誤動作、具体的には、計器の機器自体の耐圧損傷及
び誤動作を生じる。これらは、圧力計、圧力スイッチ等
全ての系統内計器で含まれます。また、高圧力により、
調整弁出口側の設計圧力を越え、配管自体の危険性をも
生じる。According to the present invention, in the bearing oil supply system of the turbine lubricating oil system, the problem is due to excessive pressure fluctuations in the bearing oil supply pressure. Instrumentation-related malfunctions, specifically, pressure damage and malfunctions of the instrumentation itself. These include all system instruments such as pressure gauges and pressure switches. Also, due to high pressure,
The design pressure on the outlet side of the regulating valve may be exceeded, creating a danger to the piping itself.
これらの全てが防止され、高信頼性を確保することが可
能となる。また、本発明は、事業用タービンばかりでな
く、産業用タービンにおいても適用範囲が広い。All of these can be prevented and high reliability can be ensured. Further, the present invention has a wide range of application not only to commercial turbines but also to industrial turbines.
第1図は本発明の一実施例の蒸気タービン潤滑油軸受給
油圧力調整装置の系統図、第2図は潤滑油供給系統概略
図、第3図は従来の圧力調整弁の構成図、第4図は圧力
調整弁開度と調整弁出口側圧力の特性曲線図、第5図は
圧力調整装置の通常運転時の状態図、第6図は圧力調整
弁の従来の一次圧、二次圧の特性曲線図、第7図は圧力
調整装置設置時の一次圧と二次圧の特性曲線図、第8図
は実際運転に入った時の二次正特性曲線図、第9図は電
磁パイロットを用いた実施例の構成図である。1・・・
主油ポンプ、2・・・主油ポンプ、3・・・非常用油ポ
ンプ、5・・・−水圧力調整弁、6・・・油冷却器、7
・・・軸受給油配管、8・・・二次圧力調整弁、29・
・・オリフィス、30・・・安全弁、31・・・アキュ
ムレータ、33・・・電磁弁、34・・・電気配線。Fig. 1 is a system diagram of a steam turbine lubricating oil bearing oil supply pressure regulating device according to an embodiment of the present invention, Fig. 2 is a schematic diagram of a lubricating oil supply system, Fig. 3 is a configuration diagram of a conventional pressure regulating valve, and Fig. 4 is a schematic diagram of a lubricating oil supply system. The figure shows the characteristic curve of the pressure regulating valve opening and the pressure on the outlet side of the regulating valve, Figure 5 shows the state of the pressure regulator during normal operation, and Figure 6 shows the conventional primary pressure and secondary pressure of the pressure regulating valve. Characteristic curve diagram, Figure 7 is a characteristic curve diagram of primary pressure and secondary pressure when the pressure regulator is installed, Figure 8 is a secondary positive characteristic curve diagram when actual operation begins, and Figure 9 is a diagram of the electromagnetic pilot. It is a block diagram of the Example used. 1...
Main oil pump, 2...Main oil pump, 3...Emergency oil pump, 5...-Water pressure adjustment valve, 6...Oil cooler, 7
...Bearing oil supply piping, 8...Secondary pressure regulating valve, 29.
... Orifice, 30 ... Safety valve, 31 ... Accumulator, 33 ... Solenoid valve, 34 ... Electrical wiring.
Claims (1)
口側より、配管を取り出し、また、圧力調整弁動作に用
いる油を供給する配管を設け、装置内部としては、調整
弁入口側からの配管にオリフィス、安全弁を設け、アキ
ュムレータ、圧力調整弁制御パイロット弁を設け、圧力
調整弁制御用パイロット弁は、ポンプ起動から、ポンプ
正常運転油圧に、移行した際、圧力調整弁入口側油圧か
ら、圧力調整弁出口側油圧力による制御に移行する機構
を有していることを特徴とする軸受給油圧力調整装置。1. As a pressure regulating device, pipes are taken out from the inlet and outlet sides of the pressure regulating valve, and piping is installed to supply oil used for pressure regulating valve operation. An orifice and a safety valve are installed in the piping, and an accumulator and a pressure regulating valve control pilot valve are installed. A bearing oil supply pressure regulating device characterized by having a mechanism for shifting control to control using hydraulic pressure on the outlet side of a pressure regulating valve.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP24153985A JPS62101808A (en) | 1985-10-30 | 1985-10-30 | Device for regulating bearing lubrication pressure |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP24153985A JPS62101808A (en) | 1985-10-30 | 1985-10-30 | Device for regulating bearing lubrication pressure |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS62101808A true JPS62101808A (en) | 1987-05-12 |
Family
ID=17075855
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP24153985A Pending JPS62101808A (en) | 1985-10-30 | 1985-10-30 | Device for regulating bearing lubrication pressure |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS62101808A (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2072782A1 (en) * | 2007-12-21 | 2009-06-24 | Techspace Aero S.A. | Recirculation valve in an aeronautical engine |
JP5377626B2 (en) * | 2009-02-18 | 2013-12-25 | 株式会社東芝 | Lubricating oil system |
-
1985
- 1985-10-30 JP JP24153985A patent/JPS62101808A/en active Pending
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2072782A1 (en) * | 2007-12-21 | 2009-06-24 | Techspace Aero S.A. | Recirculation valve in an aeronautical engine |
US8881870B2 (en) | 2007-12-21 | 2014-11-11 | Techspace Aero S.A. | Recirculation valve in an aircraft engine |
JP5377626B2 (en) * | 2009-02-18 | 2013-12-25 | 株式会社東芝 | Lubricating oil system |
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