JP2012112270A - Combined steam valve and steam turbine - Google Patents

Combined steam valve and steam turbine Download PDF

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JP2012112270A
JP2012112270A JP2010260628A JP2010260628A JP2012112270A JP 2012112270 A JP2012112270 A JP 2012112270A JP 2010260628 A JP2010260628 A JP 2010260628A JP 2010260628 A JP2010260628 A JP 2010260628A JP 2012112270 A JP2012112270 A JP 2012112270A
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valve
steam
seat
stop
valve body
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JP5701019B2 (en
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Toshiya Nishimura
利也 西村
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Mitsubishi Heavy Industries Ltd
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Mitsubishi Heavy Industries Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • F01D17/12—Final actuators arranged in stator parts
    • F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
    • F01D17/141—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path
    • F01D17/145—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path by means of valves, e.g. for steam turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F16K1/34—Cutting-off parts, e.g. valve members, seats
    • F16K1/44—Details of seats or valve members of double-seat valves
    • F16K1/443—Details of seats or valve members of double-seat valves the seats being in series
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K39/00—Devices for relieving the pressure on the sealing faces
    • F16K39/02—Devices for relieving the pressure on the sealing faces for lift valves
    • F16K39/024—Devices for relieving the pressure on the sealing faces for lift valves using an auxiliary valve on the main valve

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Turbines (AREA)
  • Lift Valve (AREA)
  • Details Of Valves (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide a combined steam valve, along with a steam turbine with the same, having small turbulence of a steam flow after passing through the steam valve and facilitating space-saving when performing layout.SOLUTION: A stop valve 10 and a control valve 20 are provided in a common valve casing 40 in a combined steam valve 1. The stop valve 10 includes a first valve element 12, a first valve seat 14 with which the first valve element 12 is in abutment when the valve is closed, and a first valve rod 16 attached to the first valve element 12. The control valve 20 includes a second valve element 22, a second valve seat 24 with which the second valve element 22 is in abutment when the valve is closed, and a second valve rod 26 attached to the second valve element 22. The valve casing 40 includes a stop valve chamber 42 for housing the stop valve 10, a control valve chamber 44 for housing the control valve 20, a steam inlet 46 for supplying steam to the stop valve chamber 42, a straight intermediate flow path 48 provided between the stop valve chamber 42 and the control valve chamber 44, and a steam outlet 50 for discharging the steam from the control valve chamber 44. The first valve rod 16 of the stop valve 10 and the second valve rod 26 of the control valve 20 extend in opposite directions with the intermediate flow path 48 therebetween.

Description

本発明は、例えば火力発電所や原子力発電所等で用いられる組合せ蒸気弁およびこれを備えた蒸気タービンに関する。   The present invention relates to a combination steam valve used in, for example, a thermal power plant or a nuclear power plant, and a steam turbine including the same.

火力発電所や原子力発電所等の蒸気タービンは、異常時に蒸気の供給を遮断したり、負荷変化に応じて蒸気量を調節したりするために、多数の蒸気弁が設けられている。このうち、異常時に蒸気の供給を遮断するものは止め弁と称され、負荷変化に応じて蒸気量を調節するものは加減弁と称される。   Steam turbines such as thermal power plants and nuclear power plants are provided with a large number of steam valves in order to shut off the supply of steam in the event of an abnormality or to adjust the amount of steam in accordance with load changes. Among these, a valve that shuts off the supply of steam in the event of an abnormality is called a stop valve, and a valve that adjusts the amount of steam according to a load change is called an adjusting valve.

これら止め弁及び加減弁は、高圧かつ大流量の蒸気量を扱うため大型である。このため、止め弁及び加減弁のレイアウトを効率的に行って、省スペース化を図ることが望まれる。そこで、止め弁及び加減弁を共通の弁ケーシングに設けた組合せ蒸気弁が知られている。   These stop valves and control valves are large in order to handle high-pressure and high-flow rate steam. For this reason, it is desired to save the space by efficiently laying out the stop valves and adjusting valves. Therefore, a combination steam valve in which a stop valve and an adjustment valve are provided in a common valve casing is known.

例えば、特許文献１には、加減弁として機能する第１弁体と、この第１弁体の下流側に配置され、止め弁として機能する第２弁体とが共通の弁ケーシングに組み込まれた組合せ蒸気弁が記載されている。この組合せ蒸気弁では、１個の弁室に第１弁体（加減弁）及び第２弁体（止め弁）の両方が設けられており、上流側の第１弁体により蒸気の流量を制御するとともに、下流側の第２弁体により蒸気を緊急時に遮断するようになっている。   For example, in Patent Document 1, a first valve body that functions as an adjusting valve and a second valve body that is disposed downstream of the first valve body and functions as a stop valve are incorporated in a common valve casing. A combination steam valve is described. In this combined steam valve, both the first valve body (adjustment valve) and the second valve body (stop valve) are provided in one valve chamber, and the flow rate of steam is controlled by the upstream first valve body. At the same time, the steam is shut off in an emergency by the second valve body on the downstream side.

また、特許文献２及び３には、止め弁と、この止め弁の下流側に配置される加減弁とが共通の弁ケーシングに組み込まれた組合せ蒸気弁が記載されている。この組合せ蒸気弁では、２個の弁室に止め弁と加減弁とがそれぞれ配置され、該２つの弁室の間に連通路が設けられている。そして、上流側の止め弁により蒸気を緊急時に遮断するとともに、下流側の加減弁によりタービン負荷に応じて蒸気量を調節するようになっている。   Patent Documents 2 and 3 describe a combination steam valve in which a stop valve and an adjusting valve arranged on the downstream side of the stop valve are incorporated in a common valve casing. In this combination steam valve, stop valves and control valves are respectively arranged in two valve chambers, and a communication path is provided between the two valve chambers. The upstream stop valve shuts off the steam in an emergency, and the downstream control valve adjusts the steam amount according to the turbine load.

特開２００６−１０５１３０号公報JP 2006-105130 A 特開２０１０−４３５９１号公報JP 2010-43591 A 特開昭６１−９２３７１号公報JP 61-92371 A

ところで、組合せ蒸気弁では、蒸気量の調節機能を有するという性質上、加減弁は常に途中開度（微開状態）で運転されるから、加減弁の通過後に蒸気流が乱れやすい傾向がある。そして、この蒸気流の乱れは、組合せ蒸気弁各部の振動の原因となるから、加減弁を通過した後の蒸気流の乱れが少ない組合せ蒸気弁の開発が望まれる。   By the way, in the combination steam valve, because of the property of having a function of adjusting the amount of steam, the adjusting valve is always operated at a halfway opening (slightly open state), so that the steam flow tends to be disturbed after passing through the adjusting valve. And since this turbulent steam flow causes vibrations in each part of the combined steam valve, it is desired to develop a combined steam valve with less turbulent steam flow after passing through the adjusting valve.

この点、特許文献１に記載の組合せ蒸気弁では、第１弁体（加減弁）及び第２弁体（止め弁）が同一の弁室に設けられ、第１弁体の直後に第２弁体が配置されているため、第２弁体が障害物となって、第１弁体を通過後の蒸気流を乱す場合がある。もちろん、第２弁体を常に大きくリフトしておくことで、第２弁体による蒸気流の干渉を抑制できるが、止め弁としての第２弁体のリフト量を大きくすると、緊急時における迅速な蒸気の遮断が困難になってしまう。   In this regard, in the combination steam valve described in Patent Document 1, the first valve body (regulating valve) and the second valve body (stop valve) are provided in the same valve chamber, and the second valve body is located immediately after the first valve body. Since the body is arranged, the second valve body may become an obstacle and disturb the steam flow after passing through the first valve body. Of course, it is possible to suppress the steam flow interference caused by the second valve body by always lifting the second valve body large, but if the lift amount of the second valve body as the stop valve is increased, the emergency speed can be increased quickly. It becomes difficult to shut off the steam.

一方、特許文献２に記載の組合せ蒸気弁では、止め弁の下流側に加減弁が配置されており、加減弁を通過した後の蒸気流を乱す障害物はないから、蒸気流の乱れは比較的少ない。
ところが、止め弁の弁棒及びこれを進退させるアクチュエータが弁室間の連通路に沿って延在する一方で、加減弁の弁棒及びアクチュエータは連通路に直交する方向に沿って延在している。ここで、止め弁と加減弁の弁棒及びアクチュエータは、組合せ蒸気弁のサイズ全体に占める割合が比較的大きい。このため、特許文献２に記載の組合せ蒸気弁のように、止め弁の弁棒及びアクチュエータと加減弁の弁棒及びアクチュエータとが互いに直交するように配置すると、組合せ蒸気弁の全体形状が略Ｔ字状になってしまい、複数の組合せ蒸気弁をレイアウトする際に、省スペース化することが難しい。 On the other hand, in the combination steam valve described in Patent Document 2, the control valve is arranged downstream of the stop valve, and there is no obstacle that disturbs the steam flow after passing through the control valve. Less.
However, while the valve stem of the stop valve and the actuator for advancing and retracting the valve rod extend along the communication path between the valve chambers, the valve rod and the actuator of the adjustable valve extend along the direction orthogonal to the communication path. Yes. Here, the valve rods and actuators of the stop valve and the adjusting valve account for a relatively large proportion of the total size of the combination steam valve. For this reason, if the valve stem and actuator of the stop valve and the valve stem and actuator of the adjusting valve are arranged so as to be orthogonal to each other as in the combination steam valve described in Patent Document 2, the overall shape of the combination steam valve is approximately T. It becomes a letter shape, and it is difficult to save space when laying out a plurality of combination steam valves.

本発明は、上述の事情に鑑みてなされたものであり、蒸気弁を通過した後の蒸気流の乱れが少なく、レイアウト時の省スペース化を容易に行いうる組合せ蒸気弁およびこれを備える蒸気タービンを提供することを目的とする。   The present invention has been made in view of the above-described circumstances, and there is little steam flow disturbance after passing through the steam valve, and a combined steam valve that can easily save space during layout, and a steam turbine including the same The purpose is to provide.

本発明に係る組合せ蒸気弁は、止め弁および加減弁が共通の弁ケーシングに設けられた組合せ蒸気弁であって、第１弁体、前記第１弁体が閉弁時に当接する第１弁座および前記第１弁体に取り付けられた第１弁棒を有する止め弁と、前記止め弁の下流側に配置され、第２弁体、前記第２弁体が閉弁時に当接する第２弁座および前記第２弁体に取り付けられた第２弁棒を有する加減弁と、前記止め弁を収納する止め弁室、前記加減弁を収納する加減弁室、前記止め弁室に蒸気を供給する蒸気入口部、前記止め弁室と前記加減弁室との間に設けられるストレート形状の中間流路、および、前記加減弁室からの蒸気を排出する蒸気出口部を有する弁ケーシングとを備え、前記止め弁の前記第１弁棒と、前記加減弁の前記第２弁棒とは、前記中間流路を挟んで反対方向に延在していることを特徴とする。   The combination steam valve according to the present invention is a combination steam valve in which a stop valve and an adjustment valve are provided in a common valve casing, and the first valve seat and the first valve seat with which the first valve body abuts when the valve is closed. And a stop valve having a first valve rod attached to the first valve body, and a second valve seat disposed on the downstream side of the stop valve, the second valve body and the second valve body abutting when the valve is closed And a control valve having a second valve rod attached to the second valve body, a stop valve chamber for storing the stop valve, a control valve chamber for storing the control valve, and steam for supplying steam to the stop valve chamber An inlet portion, a straight intermediate flow path provided between the stop valve chamber and the control valve chamber, and a valve casing having a steam outlet for discharging steam from the control valve chamber, the stop The first valve rod of the valve and the second valve rod of the regulating valve are the intermediate flow path Characterized in that it extends in the opposite direction across.

この組合せ蒸気弁によれば、止め弁と加減弁を別々の弁室に収納するとともに、止め弁を加減弁の上流側に配置したので、加減弁を通過した後の蒸気流の乱れを抑制できる。
また、止め弁の第１弁棒と加減弁の第２弁棒とを、中間流路を挟んで反対方向に延在するように配置したので、組合せ蒸気弁の全体形状は中間流路に沿って延びる略直線状となる。よって、複数の組合せ蒸気弁をレイアウトする際に、省スペース化を図ることが可能となる。 According to this combined steam valve, the stop valve and the regulating valve are housed in separate valve chambers, and the stop valve is arranged upstream of the regulating valve, so that it is possible to suppress the turbulence of the steam flow after passing through the regulating valve. .
Further, since the first valve rod of the stop valve and the second valve rod of the adjusting valve are arranged so as to extend in opposite directions across the intermediate flow path, the overall shape of the combination steam valve is along the intermediate flow path It becomes a substantially straight line extending. Therefore, it is possible to save space when laying out a plurality of combination steam valves.

上記組合せ蒸気弁において、前記弁ケーシングの内壁には、前記中間流路の全長にわたって、前記第１弁座および前記第２弁座が一体化された共通弁座が設けられていることが好ましい。   In the combination steam valve, it is preferable that a common valve seat in which the first valve seat and the second valve seat are integrated is provided on the inner wall of the valve casing over the entire length of the intermediate flow path.

このように、止め弁の第１弁座と加減弁の第２弁座を共通化することで、部品数が減少し、組合せ蒸気弁の組立て作業の効率が向上する。また、第１弁座と第２弁座との間に継ぎ目がなく平滑面であるから、継ぎ目部分で蒸気流が乱れてしまうことがない。   Thus, by sharing the first valve seat of the stop valve and the second valve seat of the adjusting valve, the number of parts is reduced, and the efficiency of assembly work of the combination steam valve is improved. Further, since there is no seam between the first valve seat and the second valve seat, the steam flow is not disturbed at the joint.

この場合、前記共通弁座は、前記第１弁座のシート部よりも蒸気流れ方向における上流側においてのみ、前記弁ケーシングの内壁に固定されていることが好ましい。   In this case, it is preferable that the common valve seat is fixed to the inner wall of the valve casing only on the upstream side in the steam flow direction from the seat portion of the first valve seat.

このように、共通弁座の弁ケーシングの内壁への固定は、止め弁（第１弁座）のシート部よりも上流側においてのみ行い、止め弁のシート部よりも下流側では行わないようにすることで、固定用の締結部材等によって蒸気流が乱れることがない。   In this way, the common valve seat is fixed to the inner wall of the valve casing only on the upstream side of the seat portion of the stop valve (first valve seat), and not on the downstream side of the seat portion of the stop valve. By doing so, the steam flow is not disturbed by the fastening member for fixing.

上記組合せ蒸気弁において、前記第２弁座は、蒸気流れ方向における上流側から下流側に向かって拡径していることが好ましい。   In the combined steam valve, the second valve seat preferably has a diameter that increases from the upstream side toward the downstream side in the steam flow direction.

このように、加減弁の第２弁座を、蒸気流の上流側から下流側に向かって拡径する形状とすれば、第２弁座のシート部の上流側よりも該シート部の下流側のほうが蒸気の流路面積が大きい。このため、中間流路から供給される蒸気は、第２弁座のシート部を通過する際に流速が遅くなり、第２弁座のシート部の下流側における蒸気流の乱れが抑制される。よって、第２弁座のシート部を通過した蒸気流が第２弁座に付着したままのアニュラーフローの状態が維持され、組合せ蒸気弁の各部の振動を抑制できる。
なお、アニュラーフローとは、蒸気流が弁座に沿って環状に流れることをいう。一般的に、アニュラーフローの形成によって、蒸気流が安定化し、組合せ蒸気弁各部の振動を抑制可能であると言われている。 In this way, if the second valve seat of the adjusting valve has a shape that expands from the upstream side of the steam flow toward the downstream side, the downstream side of the seat portion is more upstream than the upstream side of the seat portion of the second valve seat. The steam passage area is larger. For this reason, when the vapor | steam supplied from an intermediate flow path passes the seat part of a 2nd valve seat, a flow velocity becomes slow, and disturbance of the steam flow in the downstream of the seat part of a 2nd valve seat is suppressed. Therefore, the state of the annular flow in which the steam flow that has passed through the seat portion of the second valve seat remains attached to the second valve seat is maintained, and vibration of each portion of the combination steam valve can be suppressed.
The annular flow means that the vapor flow flows in an annular shape along the valve seat. In general, it is said that the formation of the annular flow stabilizes the steam flow and can suppress the vibration of each part of the combined steam valve.

この場合、前記第２弁体の弁頭部は凹形状であることが好ましい。   In this case, it is preferable that the valve head of the second valve body has a concave shape.

これにより、シート部の上流側において弁頭部の凹部に蒸気流が一旦滞留し、蒸気流が弁座に沿うように整流されるので、アニュラーフローをより一層安定化することができる。   As a result, the steam flow once stays in the concave portion of the valve head on the upstream side of the seat portion, and the steam flow is rectified so as to follow the valve seat, so that the annular flow can be further stabilized.

また、上記組合せ蒸気弁は、前記第２弁体の外周に設けられ、前記第２弁体を案内する円筒状の弁体ガイドをさらに備え、前記第２弁体の弁頭部には、前記第２弁体及び前記弁体ガイドで囲まれた内部空間を前記中間流路に連通するバランス穴が形成されており、前記第２弁座のシート部の直径よりも、前記弁体ガイドの内径が大きいことが好ましい。   The combination steam valve further includes a cylindrical valve body guide that is provided on an outer periphery of the second valve body and guides the second valve body, and the valve head of the second valve body includes the A balance hole is formed to communicate the inner space surrounded by the second valve body and the valve body guide to the intermediate flow path, and the inner diameter of the valve body guide is larger than the diameter of the seat portion of the second valve seat. Is preferably large.

このように、バランス穴を設けることで、第２弁体及び弁体ガイドで囲まれた内部空間と、第２弁体の上流側の中間流路とにおける蒸気圧力が同等になる。ここで、第２弁座のシート部の直径よりも、弁体ガイドの内径のほうが大きいから、全体として第２弁体に作用する正味の蒸気力は、蒸気流の下流側から上流側に向かう方向（すなわち、加減弁の閉弁方向）である。こうして、加減弁の第２弁体に作用する正味の蒸気力によって、加減弁が閉まる方向に第２弁体が常に引っ張られるから、第２弁体の調心性が向上し、蒸気流の乱れをより一層抑制できる。   Thus, by providing the balance hole, the vapor pressure in the internal space surrounded by the second valve body and the valve body guide and the intermediate flow path upstream of the second valve body become equal. Here, since the inner diameter of the valve body guide is larger than the diameter of the seat portion of the second valve seat, the net steam force acting on the second valve body as a whole is directed from the downstream side to the upstream side of the steam flow. Direction (that is, the valve closing direction of the adjusting valve). Thus, since the second valve body is always pulled in the direction in which the control valve is closed by the net steam force acting on the second valve body of the control valve, the alignment of the second valve body is improved and the steam flow is disturbed. It can be further suppressed.

本発明に係る蒸気タービンは、複数の上記組合せ蒸気弁と、前記複数の組合せ蒸気弁が接続されるとともに、ロータを収納するタービン車室とを備え、前記複数の組合せ蒸気弁は、前記タービン車室の両側にロータ軸方向に沿って配置されることを特徴とする。   The steam turbine according to the present invention includes a plurality of the combination steam valves, and a turbine casing in which the plurality of combination steam valves are connected and accommodates a rotor, and the plurality of combination steam valves includes the turbine wheel. It is arranged along the rotor axial direction on both sides of the chamber.

上述のように、上記組合せ蒸気弁は、止め弁の第１弁棒と加減弁の第２弁棒とを、中間流路を挟んで反対側に、略同一の軸線上に延在するように配置したので、組合せ蒸気弁の全体形状は中間流路に沿って延びる略直線状である。
本発明に係る蒸気タービンは、略直線状の複数の組合せ蒸気弁をタービン車室の両側にロータ軸方向に沿って配置したので、設置スペースを削減できる。 As described above, the combination steam valve is configured so that the first valve rod of the stop valve and the second valve rod of the adjustment valve extend on substantially the same axis on the opposite side across the intermediate flow path. Since it has been arranged, the overall shape of the combination steam valve is substantially linear extending along the intermediate flow path.
In the steam turbine according to the present invention, a plurality of substantially straight combination steam valves are arranged on both sides of the turbine casing along the rotor axial direction, so that the installation space can be reduced.

上記蒸気タービンにおいて、前記複数の組合せ蒸気弁は、前記タービン車室の両側に少なくとも一対ずつ設けられており、前記少なくとも一対の組合せ蒸気弁は、鉛直方向および前記ロータ軸方向に直交する方向にずらして配置されていることが好ましい。   In the steam turbine, the plurality of combination steam valves are provided at least one pair on both sides of the turbine casing, and the at least one pair of combination steam valves are shifted in a direction perpendicular to the vertical direction and the rotor axial direction. Are preferably arranged.

一対の組合せ蒸気弁をレイアウトするにあたって、組合せ蒸気弁の設置スペース（水平面上の設置面積）の削減が望まれる一方、それぞれの組合せ蒸気弁のメンテナンス性を確保する必要がある。
この点、上記組合せ蒸気弁は略直線状であるから、略直線状の少なくとも一対の組合せ蒸気弁をタービン車室の両側のそれぞれに設けるにあたって、組合せ蒸気弁を鉛直方向および前記ロータ軸方向に直交する方向にずらして配置することができる。そして、このように組合せ蒸気弁をずらして配置することで、設置スペースの削減とメンテナンス性の向上とを両立できる。 In laying out a pair of combination steam valves, it is desired to reduce the installation space (installation area on a horizontal plane) of the combination steam valve, but it is necessary to ensure the maintainability of each combination steam valve.
In this respect, since the combination steam valve is substantially linear, when providing at least one pair of substantially straight combination steam valves on both sides of the turbine casing, the combination steam valve is perpendicular to the vertical direction and the rotor axial direction. It can be shifted in the direction to do. Further, by shifting the combination steam valves in this way, it is possible to achieve both reduction in installation space and improvement in maintainability.

本発明によれば、止め弁と加減弁を別々の弁室に収納するとともに、止め弁を加減弁の上流側に配置したので、加減弁を通過した後の蒸気流の乱れを抑制できる。
また、止め弁の第１弁棒と加減弁の第２弁棒とを、中間流路を挟んで反対方向に延在するように配置したので、組合せ蒸気弁の全体形状は中間流路に沿って延びる略直線状である。よって、複数の組合せ蒸気弁をレイアウトする際に、省スペース化を図ることが可能となる。 According to the present invention, the stop valve and the adjusting valve are housed in separate valve chambers, and the stop valve is arranged on the upstream side of the adjusting valve, so that it is possible to suppress turbulence in the steam flow after passing through the adjusting valve.
Further, since the first valve rod of the stop valve and the second valve rod of the adjusting valve are arranged so as to extend in opposite directions across the intermediate flow path, the overall shape of the combination steam valve is along the intermediate flow path It is a substantially straight line extending. Therefore, it is possible to save space when laying out a plurality of combination steam valves.

組合せ蒸気弁の構成例を示す断面図である。It is sectional drawing which shows the structural example of a combination steam valve. 図１に示す組合せ蒸気弁の加減弁周辺の拡大図である。FIG. 2 is an enlarged view of the vicinity of an adjusting valve of the combination steam valve shown in FIG. 1. 図１に示す組合せ蒸気弁を備える蒸気タービンの構成例を示す上面図である。It is a top view which shows the structural example of a steam turbine provided with the combination steam valve shown in FIG. 図３に示す蒸気タービンをＡ方向から視た正面図である。It is the front view which looked at the steam turbine shown in FIG. 3 from the A direction.

以下、添付図面に従って本発明の実施形態について説明する。ただし、この実施形態に記載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、特定的な記載がない限り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。   Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings. However, the dimensions, materials, shapes, relative arrangements, and the like of the components described in this embodiment are not intended to limit the scope of the present invention unless otherwise specified, and are merely illustrative examples. Only.

図１は、組合せ蒸気弁の構成例を示す断面図である。図２は、図１に示す組合せ蒸気弁の加減弁周辺の拡大図である。   FIG. 1 is a cross-sectional view showing a configuration example of a combination steam valve. FIG. 2 is an enlarged view of the vicinity of the adjusting valve of the combination steam valve shown in FIG.

図１に示すように、組合せ蒸気弁１は、止め弁１０及び加減弁２０が共通の弁ケーシング４０に設けられた構成を有する。止め弁１０が緊急時に蒸気流を遮断する役割を担う一方で、加減弁２０は負荷変化に応じて蒸気量を調節するようになっている。   As shown in FIG. 1, the combination steam valve 1 has a configuration in which a stop valve 10 and an adjustment valve 20 are provided in a common valve casing 40. While the stop valve 10 plays a role of blocking the steam flow in an emergency, the control valve 20 adjusts the amount of steam according to the load change.

弁ケーシング４０は、蒸気流れの上流側から順に、蒸気入口部４６、止め弁室４２、中間流路４８、加減弁室４４及び蒸気出口部５０を有する。止め弁室４２には止め弁１０が収納され、加減弁室４４には加減弁２０が収納される。止め弁室４２及び加減弁室４４は、それぞれ、弁ケーシング４０に取り付けられたボンネット５２によって閉じられている。
蒸気入口部４６から供給される蒸気は、止め弁室４２を流れた後、中間流路４８を経て加減弁室４４に流入し、最終的に蒸気出口部５０から排出される。 The valve casing 40 includes a steam inlet 46, a stop valve chamber 42, an intermediate flow path 48, an adjusting valve chamber 44, and a steam outlet 50 in order from the upstream side of the steam flow. A stop valve 10 is accommodated in the stop valve chamber 42, and an adjustment valve 20 is accommodated in the adjustment valve chamber 44. The stop valve chamber 42 and the adjustable valve chamber 44 are each closed by a bonnet 52 attached to the valve casing 40.
The steam supplied from the steam inlet 46 flows through the stop valve chamber 42, then flows into the control valve chamber 44 through the intermediate flow path 48, and is finally discharged from the steam outlet 50.

止め弁室４２に収納された止め弁１０は、第１弁体１２と、第１弁体１２が閉弁時に当接する第１弁座１４と、第１弁体１２に取り付けられた第１弁棒１６と、第１弁棒１６を案内するガイドブシュ１８とを有する。   The stop valve 10 housed in the stop valve chamber 42 includes a first valve body 12, a first valve seat 14 with which the first valve body 12 comes into contact when the valve is closed, and a first valve attached to the first valve body 12. It has a rod 16 and a guide bush 18 for guiding the first valve rod 16.

第１弁体１２は、止め弁１０の閉弁時に第１弁座１４のシート部１４Ａに当接する主弁１２Ａと、この主弁１２Ａに内包された副弁１２Ｂとにより構成される。なお、主弁１２Ａの内壁面１３は、副弁１２Ｂにとっての弁座として機能する。   The first valve body 12 includes a main valve 12A that contacts the seat portion 14A of the first valve seat 14 when the stop valve 10 is closed, and a sub valve 12B included in the main valve 12A. The inner wall surface 13 of the main valve 12A functions as a valve seat for the sub valve 12B.

第１弁棒１６は、一端が第１弁体１２の副弁１２Ｂに取り付けられ、他端がアクチュエータ（図３のアクチュエータ８）に連結されている。この第１弁棒１６を介して、アクチュエータの駆動力が第１弁体１２の副弁１２Ｂに伝わるようになっている。   One end of the first valve rod 16 is attached to the sub-valve 12B of the first valve body 12, and the other end is connected to an actuator (actuator 8 in FIG. 3). The driving force of the actuator is transmitted to the auxiliary valve 12B of the first valve body 12 through the first valve rod 16.

第１弁棒１６を案内するガイドブシュ１８は、ボンネット５２に埋設されている。これにより、アクチュエータによって駆動される第１弁棒１６は、ガイドブシュ１８内を摺動し、第１弁棒１６の中心軸Ｃ１に沿って移動する。 A guide bush 18 that guides the first valve stem 16 is embedded in the bonnet 52. As a result, the first valve stem 16 driven by the actuator slides in the guide bush 18 and moves along the central axis C 1 of the first valve stem 16.

止め弁１０では、第１弁棒１６が取り付けられた副弁１２Ｂは、所定のリフト量までは単独で進退するが、所定のリフト量に達すると主弁１２Ａとともに進退するようになっている。このため、アクチュエータによって第１弁棒１６を介して副弁１２Ｂを開弁方向（図１の上方向）に移動させると、所定のリフト量までは副弁１２Ｂのみが移動し、副弁１２Ｂが先に開く。この後、さらにアクチュエータによって第１弁棒１６を介して副弁１２Ｂを開弁方向に移動させると、所定のリフト量において副弁１２Ｂが主弁１２Ａとともに移動するようになり、主弁１２Ａも開かれる。このように、最初に副弁１２Ｂを開くことで、主弁１２Ａの前後の圧力差を低減することができ、副弁１２Ｂよりもシート径の大きい主弁１２Ａを小さな駆動力で開くことができる。   In the stop valve 10, the sub-valve 12B to which the first valve rod 16 is attached moves forward and backward independently up to a predetermined lift amount, but moves forward and backward together with the main valve 12A when the predetermined lift amount is reached. For this reason, when the sub valve 12B is moved in the valve opening direction (upward in FIG. 1) via the first valve rod 16 by the actuator, only the sub valve 12B moves until the predetermined lift amount, and the sub valve 12B Open first. Thereafter, when the auxiliary valve 12B is further moved in the valve opening direction via the first valve rod 16 by the actuator, the auxiliary valve 12B moves together with the main valve 12A at a predetermined lift amount, and the main valve 12A is also opened. It is. Thus, by opening the auxiliary valve 12B first, the pressure difference before and after the main valve 12A can be reduced, and the main valve 12A having a larger seat diameter than the auxiliary valve 12B can be opened with a small driving force. .

止め弁１０の外周には、蒸気に含まれる異物を除去する円筒状のストレーナ１７が設けられている。ストレーナ１７によって、所定のサイズ以上の異物が除去されるので、ストレーナ１７よりも下流側の組合せ蒸気弁１の各部（止め弁１０及び加減弁２０）および組合せ蒸気弁１が接続される蒸気タービンを異物による故障から保護することができる。
また、止め弁室４２の蒸気入口部４６から遠い側にはバッフルプレート１９が設けられている。バッフルプレート１９は、ストレーナ１７の外周面と止め弁室４２の内壁面との間に配置され、ストレーナ１７の外周を迂回してきた蒸気流を整流するようになっている。 A cylindrical strainer 17 for removing foreign substances contained in the steam is provided on the outer periphery of the stop valve 10. Since the foreign material having a predetermined size or larger is removed by the strainer 17, the steam turbine to which each part (stop valve 10 and adjusting valve 20) and the combined steam valve 1 of the combined steam valve 1 downstream of the strainer 17 are connected is connected. It can be protected from failure due to foreign matter.
A baffle plate 19 is provided on the side of the stop valve chamber 42 far from the steam inlet 46. The baffle plate 19 is disposed between the outer peripheral surface of the strainer 17 and the inner wall surface of the stop valve chamber 42, and rectifies the steam flow that bypasses the outer periphery of the strainer 17.

止め弁１０の下流側には加減弁２０が設けられている。加減弁２０は、図１及び２に示すように、第２弁体２２と、第２弁体２２が閉弁時に当接する第２弁座２４と、第２弁体２２に取り付けられた第２弁棒２６と、第２弁棒２６を案内するガイドブシュ２８とを有する。   An adjusting valve 20 is provided on the downstream side of the stop valve 10. As shown in FIGS. 1 and 2, the control valve 20 includes a second valve body 22, a second valve seat 24 with which the second valve body 22 contacts when the valve is closed, and a second valve body 22 attached to the second valve body 22. A valve stem 26 and a guide bush 28 for guiding the second valve stem 26 are provided.

従来から、上流側から下流側に向かって徐々に縮径する弁座を用い、弁体の基部から弁頭部に向かって蒸気を流すようにした蒸気弁が当業者間で定着していた。これに対し、本実施形態では、アニュラーフローの安定化の観点から、加減弁２０の第２弁座２４を上流側から下流側に向かって拡径する形状にするとともに、第２弁体２２の弁頭部２３から基部に向かって蒸気を流すようにしている。
このように、加減弁２０の第２弁座２４は、蒸気流れ方向における上流側から下流側に向かって徐々に拡径する形状を有するから、第２弁座２４のシート部２４Ａの上流側よりも該シート部２４Ａの下流側のほうが蒸気の流路面積が大きい。このため、中間流路４８から供給される蒸気は、第２弁座２４のシート部２４Ａを通過する際に流速が遅くなり、第２弁座２４のシート部の下流側における蒸気流の乱れが抑制される。よって、第２弁座２４のシート部２４Ａを通過した蒸気流が第２弁座２４に付着したままのアニュラーフローの状態が維持され、組合せ蒸気弁１の各部の振動を抑制できる。
なお、本願発明者が行った数値流体力学（Computational Fluid Dynamics：ＣＦＤ）を用いた計算結果によれば、本実施形態の加減弁２０は、従来の構成の加減弁に比べて約１０ｄＢの騒音（振動）低下効果が得られた。 Conventionally, a steam valve that uses a valve seat that gradually decreases in diameter from the upstream side toward the downstream side and that allows steam to flow from the base of the valve body toward the valve head has been established by those skilled in the art. On the other hand, in the present embodiment, from the viewpoint of the stabilization of the annular flow, the second valve seat 24 of the adjusting valve 20 is shaped to expand from the upstream side to the downstream side, and the second valve body 22 Steam is allowed to flow from the valve head 23 toward the base.
Thus, since the second valve seat 24 of the control valve 20 has a shape that gradually increases in diameter from the upstream side to the downstream side in the steam flow direction, from the upstream side of the seat portion 24A of the second valve seat 24. Also, the flow path area of the steam is larger on the downstream side of the seat portion 24A. For this reason, when the steam supplied from the intermediate flow path 48 passes through the seat portion 24A of the second valve seat 24, the flow velocity becomes slow, and the steam flow is disturbed on the downstream side of the seat portion of the second valve seat 24. It is suppressed. Therefore, the state of the annular flow in which the steam flow that has passed through the seat portion 24 </ b> A of the second valve seat 24 remains attached to the second valve seat 24 is maintained, and the vibration of each portion of the combination steam valve 1 can be suppressed.
In addition, according to the calculation result using the Computational Fluid Dynamics (CFD) performed by the inventor of the present application, the control valve 20 of the present embodiment has a noise (about 10 dB) compared to the control valve of the conventional configuration ( Vibration) reduction effect was obtained.

第２弁座２４のシート部２４Ａから上流側に延ばしたシート部２４Ａにおける接線Ｔが、第２弁体２２の中心軸（すなわち、第２弁棒２６の中心軸Ｃ２）に対してなす角度θ（図２参照）は、２５〜５０度であることが好ましい。このように、シート部２４Ａの接線Ｔが第２弁体２２の中心軸に対してなす角度θを２５度以上にすることで、シート部２４Ａを境に流路面積を急拡大させて、シート部２４Ａの上流側に比べて下流側の蒸気流の流速を十分遅くして、蒸気流の干渉をより確実に抑制できる。一方、同角度θを５０度以下にすることで、噴流衝突が回避でき、流体騒音が低下し騒音を小さくすることができる。 The angle formed by the tangent line T in the seat portion 24A extending upstream from the seat portion 24A of the second valve seat 24 with respect to the central axis of the second valve body 22 (that is, the central axis C 2 of the second valve rod 26). θ (see FIG. 2) is preferably 25 to 50 degrees. Thus, by setting the angle θ formed by the tangent line T of the seat portion 24A to the central axis of the second valve body 22 to be 25 degrees or more, the flow passage area is rapidly expanded with the seat portion 24A as a boundary. Compared to the upstream side of the portion 24A, the flow velocity of the downstream steam flow can be sufficiently slowed down, and the interference of the steam flow can be more reliably suppressed. On the other hand, by setting the angle θ to 50 degrees or less, jet collision can be avoided, fluid noise can be reduced, and noise can be reduced.

また、加減弁２０の第２弁座２４は、図１に示すように、止め弁１０の第１弁座１４と一体化された共通弁座４として設けられている。共通弁座４は、中間流路４８の全長にわたって設けられ、弁ケーシング４０の内壁に固定される。
このように、止め弁１０の第１弁座１４と加減弁２０の第２弁座２４を共通化することで、部品数が減少し、組合せ蒸気弁１の組立て作業の効率が向上する。また、第１弁座１４と第２弁座２４との間に継ぎ目がなく平滑面であるから、継ぎ目部分で蒸気流が乱れてしまうことがない。 Moreover, the 2nd valve seat 24 of the adjustment valve 20 is provided as the common valve seat 4 integrated with the 1st valve seat 14 of the stop valve 10, as shown in FIG. The common valve seat 4 is provided over the entire length of the intermediate flow path 48 and is fixed to the inner wall of the valve casing 40.
Thus, by sharing the first valve seat 14 of the stop valve 10 and the second valve seat 24 of the control valve 20, the number of parts is reduced and the efficiency of the assembly work of the combination steam valve 1 is improved. In addition, since there is no seam between the first valve seat 14 and the second valve seat 24, the steam flow is not disturbed at the seam portion.

共通弁座４は、第１弁座１４のシート部１４Ａよりも蒸気流れ方向における上流側においてのみ、弁ケーシング４０の内壁に固定されていることが好ましい。例えば、シート部１４Ａよりも上流側の位置で、締結部材６によって共通弁座４を弁ケーシング４０の内壁に固定してもよい。
このように、共通弁座４の弁ケーシング４０の内壁への固定は、止め弁１０のシート部１４Ａよりも上流側においてのみ行い、止め弁１０のシート部１４Ａよりも下流側では行わないようにすることで、固定用の締結部材６によって蒸気流が乱れることがない。また、共通弁座４の片側（止め弁１０側）のみが締結部材６により固定され、共通弁座４の反対側は締結部材６による固定点を始点として自由に熱膨張可能であるから、加減弁２０の起動停止時に、急激な温度変化によって発生する熱応力に起因した共通弁座４の損傷を防止できる。さらに、組合せ蒸気弁１を縦置き（鉛直方向に沿って配置）する場合、共通弁座４を止め弁１０側から抜き取ることで、下方の加減弁２０の第２弁体２２等を止め弁１０側に抜くことができ、組合せ蒸気弁１の分解作業が容易になる。 The common valve seat 4 is preferably fixed to the inner wall of the valve casing 40 only on the upstream side in the steam flow direction from the seat portion 14A of the first valve seat 14. For example, the common valve seat 4 may be fixed to the inner wall of the valve casing 40 by the fastening member 6 at a position upstream of the seat portion 14A.
In this manner, the common valve seat 4 is fixed to the inner wall of the valve casing 40 only on the upstream side of the seat portion 14A of the stop valve 10 and not on the downstream side of the seat portion 14A of the stop valve 10. By doing so, the steam flow is not disturbed by the fastening member 6 for fixing. Further, only one side (stop valve 10 side) of the common valve seat 4 is fixed by the fastening member 6, and the opposite side of the common valve seat 4 can be freely thermally expanded starting from the fixing point by the fastening member 6. When the valve 20 is started and stopped, the common valve seat 4 can be prevented from being damaged due to thermal stress generated by a sudden temperature change. Furthermore, when the combination steam valve 1 is installed vertically (arranged along the vertical direction), the common valve seat 4 is removed from the stop valve 10 side, whereby the second valve body 22 and the like of the lower adjusting valve 20 are stopped. The combination steam valve 1 can be easily disassembled.

第２弁座２４に対して閉弁時に当接する第２弁体２２は、先端側（第２弁座２４に近い側）に凹形状の弁頭部２３を有する。このように、第２弁体２２の弁頭部２３を凹形状とすることで、図２の流線１００で示すように、第２弁座２４のシート部２４Ａの上流側において弁頭部２３の凹部に蒸気流が一旦滞留し、蒸気流が第２弁座２４に沿うように整流される。よって、アニュラーフローをより一層安定化することができる。   The second valve body 22 that comes into contact with the second valve seat 24 when the valve is closed has a concave valve head 23 on the distal end side (side closer to the second valve seat 24). Thus, by making the valve head 23 of the second valve body 22 into a concave shape, as shown by the streamline 100 in FIG. 2, the valve head 23 on the upstream side of the seat portion 24 </ b> A of the second valve seat 24. The steam flow once stays in the concave portion of the gas and is rectified so that the steam flow follows the second valve seat 24. Therefore, the annular flow can be further stabilized.

図２に示すように、第２弁体２２の外周には、第２弁体２２を案内する円筒状の弁体ガイド３０が設けられている。この弁体ガイド３０の内径ＤＧは、第２弁座２４のシート部２４Ａの直径（シート径）Ｄ０よりも大きい。また、第２弁体２２の弁頭部２３には、第２弁体２２及び弁体ガイド３０で囲まれた内部空間３２を中間流路４８に連通するバランス穴３４が形成されている。 As shown in FIG. 2, a cylindrical valve body guide 30 that guides the second valve body 22 is provided on the outer periphery of the second valve body 22. The inner diameter D G of the valve body guide 30 is greater than the diameter (seat diameter) D 0 of the seat portion 24A of the second valve seat 24. The valve head 23 of the second valve body 22 is formed with a balance hole 34 that communicates the internal space 32 surrounded by the second valve body 22 and the valve body guide 30 to the intermediate flow path 48.

このように、バランス穴３４を設けることで、第２弁体２２及び弁体ガイド３０で囲まれた内部空間３２と、第２弁体２２の上流側の中間流路４８とにおける蒸気圧力が同等になる。ここで、第２弁座２４のシート部２４Ａの直径Ｄ０よりも、弁体ガイド３０の内径ＤＧのほうが大きいから、全体として第２弁体２２に作用する正味の蒸気力は、蒸気流の下流側から上流側に向かう方向（すなわち、加減弁の閉弁方向）である。こうして、加減弁２０の第２弁体２２に作用する正味の蒸気力によって、加減弁２０が閉まる方向に第２弁体２２が常に引っ張られるから、第２弁体２２の調心性が向上し、蒸気流の乱れをより一層抑制できる。 Thus, by providing the balance hole 34, the vapor pressure in the internal space 32 surrounded by the second valve body 22 and the valve body guide 30 and the intermediate flow path 48 on the upstream side of the second valve body 22 are equal. become. Here, than the diameter D 0 of the seat portion 24A of the second valve seat 24, because there is the larger inner diameter D G of the valve body guide 30, the steam forces the net acting on the second valve body 22 as a whole, a vapor stream Direction from the downstream side to the upstream side (that is, the valve closing direction of the adjusting valve). Thus, since the second valve body 22 is always pulled in the direction in which the control valve 20 is closed by the net steam force acting on the second valve body 22 of the control valve 20, the alignment of the second valve body 22 is improved. The turbulence of the steam flow can be further suppressed.

第２弁体２２には第２弁棒２６が取り付けられる。加減弁２０の第２弁棒２６と、止め弁１０の第１弁棒１６とは、図１に示すように、中間流路４８を挟んで反対方向に延在している。なお、図１に示す例では、加減弁２０の第２弁棒２６は、その中心軸Ｃ２が、止め弁１０の第１弁棒１６の中心軸Ｃ１と略一致するように配置されている。 A second valve rod 26 is attached to the second valve body 22. As shown in FIG. 1, the second valve rod 26 of the control valve 20 and the first valve rod 16 of the stop valve 10 extend in opposite directions with the intermediate flow path 48 interposed therebetween. In the example shown in FIG. 1, the second valve rod 26 of the adjusting valve 20 is arranged so that the central axis C 2 thereof substantially coincides with the central axis C 1 of the first valve rod 16 of the stop valve 10. Yes.

また第２弁棒２６は、第２弁体２２が取り付けられた端部とは反対側の端部で、アクチュエータ（図３のアクチュエータ９）に連結されている。この第２弁棒２６を介して、アクチュエータの駆動力が第２弁体２２に伝わるようになっている。   The second valve rod 26 is connected to an actuator (actuator 9 in FIG. 3) at the end opposite to the end to which the second valve body 22 is attached. The driving force of the actuator is transmitted to the second valve body 22 via the second valve rod 26.

第２弁棒２６を案内するガイドブシュ２８は、ボンネット５２に埋設されている。これにより、アクチュエータによって駆動される第２弁棒２６は、ガイドブシュ２８内を摺動し、第２弁棒２６の中心軸Ｃ２に沿って移動する。 A guide bush 28 for guiding the second valve stem 26 is embedded in the bonnet 52. As a result, the second valve stem 26 driven by the actuator slides in the guide bush 28 and moves along the central axis C 2 of the second valve stem 26.

上記構成の組合せ蒸気弁１によれば、止め弁１０と加減弁２０を別々の弁室（４２，４４）に収納するとともに、止め弁１０を加減弁２０の上流側に配置したので、加減弁２０を通過した後の蒸気流の乱れを抑制できる。
また、止め弁１０の第１弁棒１６と加減弁２０の第２弁棒２６とを、中間流路４８を挟んで反対方向に延在するように配置したので、組合せ蒸気弁１の全体形状は中間流路４８に沿って延びる略直線状である。よって、複数の組合せ蒸気弁１をレイアウトする際に、省スペース化を図ることが可能となる。
また、組合せ蒸気弁の場合、蒸気タービンの起動時や、止め弁による蒸気遮断時には、中間流路が低温となり結露が発生して、下流側の加減弁の開度不良を招くことがある。この点、上記構成の組合せ蒸気弁１によれば、止め弁１０と加減弁２０の間にある中間流路４８を短くしたので、結露発生による加減弁２０の開度不良が極めて少なくなる。更に、共通弁座４が、中間流路４８の全長に亘って（第１弁座１４から第２弁座２４まで）延在しているため、熱伝導による加熱効果のため、中間流路４８内における結露の発生が少なくなる。 According to the combined steam valve 1 having the above configuration, the stop valve 10 and the control valve 20 are housed in separate valve chambers (42, 44), and the stop valve 10 is disposed on the upstream side of the control valve 20, so the control valve Disturbance of the steam flow after passing through 20 can be suppressed.
Further, since the first valve rod 16 of the stop valve 10 and the second valve rod 26 of the control valve 20 are arranged so as to extend in opposite directions across the intermediate flow path 48, the overall shape of the combination steam valve 1 Is a substantially straight line extending along the intermediate flow path 48. Therefore, it is possible to save space when laying out the plurality of combination steam valves 1.
In the case of a combined steam valve, when the steam turbine is started or when steam is shut off by a stop valve, the intermediate flow path becomes low in temperature and condensation may occur, resulting in a poor opening degree of the downstream regulating valve. In this regard, according to the combined steam valve 1 configured as described above, the intermediate flow path 48 between the stop valve 10 and the control valve 20 is shortened, so that the degree of opening of the control valve 20 due to the occurrence of condensation is extremely reduced. Furthermore, since the common valve seat 4 extends over the entire length of the intermediate flow path 48 (from the first valve seat 14 to the second valve seat 24), the intermediate flow path 48 is due to a heating effect due to heat conduction. The occurrence of condensation in the interior is reduced.

次に、上述の組合せ蒸気弁１を備える蒸気タービンについて説明する。図３は、組合せ蒸気弁１を備える蒸気タービンの構成例を示す上面図である。図４は、図３に示す蒸気タービンをＡ方向から視た正面図である。
なお、以下で説明する蒸気タービンは左右対称の形状であるから、図３及び４では蒸気タービンの左半分のみを示している。 Next, a steam turbine provided with the above-described combination steam valve 1 will be described. FIG. 3 is a top view illustrating a configuration example of a steam turbine including the combination steam valve 1. FIG. 4 is a front view of the steam turbine shown in FIG. 3 as viewed from the A direction.
Since the steam turbine described below has a symmetrical shape, only the left half of the steam turbine is shown in FIGS.

蒸気タービン６０は、複数の組合せ蒸気弁１（１Ａ，１Ｂ）と、ロータが収納されたタービン車室６２とを備える。組合せ蒸気弁１は、タービン車室６２の上流側に設けられている。これにより、タービン車室６２に流入する蒸気流は、組合せ蒸気弁１の止め弁１０によって緊急時に遮断されるとともに、組合せ蒸気弁１の加減弁２０によって負荷変化に応じて蒸気量が調節される。   The steam turbine 60 includes a plurality of combination steam valves 1 (1A, 1B) and a turbine casing 62 in which a rotor is accommodated. The combination steam valve 1 is provided on the upstream side of the turbine casing 62. Thereby, the steam flow flowing into the turbine casing 62 is interrupted by the stop valve 10 of the combination steam valve 1 in an emergency, and the amount of steam is adjusted by the adjusting valve 20 of the combination steam valve 1 according to the load change. .

組合せ蒸気弁１は、上述のとおり、第１弁棒１６及び第２弁棒２６が中間流路４８を挟んで反対方向に延在する構成を有するため、組合せ蒸気弁１の全体形状は中間流路４８に沿って延びる略直線状である。このことは、第１弁棒１６に連結されるアクチュエータ８および第２弁棒２６に連結されるアクチュエータ９を含めた組合せ蒸気弁１の全体形状を示した図３から明らかである。
したがって、略直線状の複数の組合せ蒸気弁１をタービン車室６２の両側にロータ軸方向に沿って配置することができる。これにより、蒸気タービン６０の設置スペースを削減できる。
また、組合せ蒸気弁１が略直線状であることから、タービン車室６２のすぐ近くに組合せ蒸気弁１を配置することができる。これにより、タービン車室６２への配管を短くして、配管における圧力損失を低減できる。 As described above, the combination steam valve 1 has a configuration in which the first valve rod 16 and the second valve rod 26 extend in opposite directions with the intermediate flow path 48 interposed therebetween. A substantially straight line extending along the path 48. This is apparent from FIG. 3 showing the overall shape of the combination steam valve 1 including the actuator 8 connected to the first valve stem 16 and the actuator 9 connected to the second valve stem 26.
Accordingly, a plurality of substantially straight combination steam valves 1 can be arranged on both sides of the turbine casing 62 along the rotor axial direction. Thereby, the installation space of the steam turbine 60 can be reduced.
Further, since the combination steam valve 1 is substantially linear, the combination steam valve 1 can be disposed in the immediate vicinity of the turbine casing 62. Thereby, the piping to the turbine casing 62 can be shortened, and the pressure loss in the piping can be reduced.

複数の組合せ蒸気弁１（１Ａ，１Ｂ）は、図３及び４に示すように、タービン車室６２の左右両側に一対ずつ設けられている。そして、これら一対の組合せ蒸気弁１Ａ及び１Ｂは、鉛直方向および前記ロータ軸方向に直交する方向にずらして配置されている。   As shown in FIGS. 3 and 4, a plurality of combination steam valves 1 (1 </ b> A, 1 </ b> B) are provided in pairs on the left and right sides of the turbine casing 62. The pair of combination steam valves 1A and 1B are arranged so as to be shifted in the vertical direction and the direction orthogonal to the rotor axial direction.

一対の組合せ蒸気弁をレイアウトするにあたって、組合せ蒸気弁の設置スペース（水平面上の設置面積）の削減が望まれる一方、それぞれの組合せ蒸気弁のメンテナンス性を確保する必要がある。
この点、本実施形態に係る組合せ蒸気弁１（１Ａ，１Ｂ）は略直線状であるから、一対の組合せ蒸気弁１Ａ及び１Ｂを鉛直方向および前記ロータ軸方向に直交する方向にずらして配置することができる。そして、このように組合せ蒸気弁１Ａ及び１Ｂをずらして配置することで、設置スペースの削減とメンテナンス性の向上とを両立できる。 In laying out a pair of combination steam valves, it is desired to reduce the installation space (installation area on a horizontal plane) of the combination steam valve, but it is necessary to ensure the maintainability of each combination steam valve.
In this respect, since the combination steam valve 1 (1A, 1B) according to the present embodiment is substantially linear, the pair of combination steam valves 1A and 1B are shifted in the vertical direction and the direction orthogonal to the rotor axial direction. be able to. Then, by arranging the combination steam valves 1A and 1B in such a manner, the installation space can be reduced and the maintainability can be improved.

以上、本発明の実施形態について詳細に説明したが、本発明はこれに限定されず、本発明の要旨を逸脱しない範囲において、各種の改良や変形を行ってもよいのはいうまでもない。   As mentioned above, although embodiment of this invention was described in detail, it cannot be overemphasized that this invention is not limited to this, In the range which does not deviate from the summary of this invention, various improvement and deformation | transformation may be performed.

例えば、上述の実施形態では、図１に示す全体構成を有する組合せ蒸気弁１について説明したが、組合せ蒸気弁１は、止め弁１０と加減弁２０が別々の弁室に設けられ、止め弁１０の第１弁棒１６と加減弁２０の第２弁棒２６とが中間流路４８を挟んで反対方向に延在する構成であれば特に限定されない。特に、止め弁１０の第１弁体１２および加減弁２０の第２弁体２２の構成は、上述の例に限定されない。   For example, in the above-described embodiment, the combination steam valve 1 having the overall configuration illustrated in FIG. 1 has been described. However, the combination steam valve 1 includes the stop valve 10 and the control valve 20 provided in separate valve chambers, and the stop valve 10. The first valve rod 16 and the second valve rod 26 of the control valve 20 are not particularly limited as long as the first valve rod 16 and the second valve rod 26 extend in opposite directions across the intermediate flow path 48. In particular, the configuration of the first valve body 12 of the stop valve 10 and the second valve body 22 of the control valve 20 is not limited to the above example.

また、図３及び４には、タービン車室６２の左右両側にそれぞれ一対ずつ組合せ蒸気弁１（１Ａ，１Ｂ）を設けた蒸気タービン６０について説明したが、組合せ蒸気弁１（１Ａ，１Ｂ）の数はこの例に限定されない。例えば、タービン車室６２の左右両側にｎ個（ただしｎ≧３）ずつ組合せ蒸気弁１を配置してもよい。   3 and 4, the steam turbine 60 provided with a pair of combined steam valves 1 (1A, 1B) on each of the left and right sides of the turbine casing 62 has been described, but the combination steam valve 1 (1A, 1B) The number is not limited to this example. For example, n (where n ≧ 3) combination steam valves 1 may be arranged on both the left and right sides of the turbine casing 62.

１ 組合せ蒸気弁
４ 共通弁座
６ 締結部材
１０ 止め弁
１２ 第１弁体
１２Ａ 主弁
１２Ｂ 副弁
１４ 第１弁座
１４Ａ シート部
１６ 第１弁棒
１７ ストレーナ
１８ ガイドブシュ
１９ バッフルプレート
２０ 加減弁
２２ 第２弁体
２３ 弁頭部
２４ 第２弁座
２４Ａ シート部
２６ 第２弁棒
２８ ガイドブシュ
３０ 弁体ガイド
３２ 内部空間
３４ バランス穴
４０ 弁ケーシング
４２ 止め弁室
４４ 加減弁室
４６ 蒸気入口部
４８ 中間流路
５０ 蒸気出口部
５２ ボンネット
６０ 蒸気タービン
６２ タービン車室
１００ 流線 DESCRIPTION OF SYMBOLS 1 Combination steam valve 4 Common valve seat 6 Fastening member 10 Stop valve 12 1st valve body 12A Main valve 12B Sub valve 14 1st valve seat 14A Seat part 16 1st valve rod 17 Strainer 18 Guide bush 19 Baffle plate 20 Adjusting valve 22 Second valve element 23 Valve head 24 Second valve seat 24A Seat part 26 Second valve rod 28 Guide bush 30 Valve element guide 32 Internal space 34 Balance hole 40 Valve casing 42 Stop valve chamber 44 Adjustable valve chamber 46 Steam inlet 48 Intermediate flow path 50 Steam outlet 52 Bonnet 60 Steam turbine 62 Turbine casing 100 Streamline

Claims (8)

止め弁および加減弁が共通の弁ケーシングに設けられた組合せ蒸気弁であって、
第１弁体、前記第１弁体が閉弁時に当接する第１弁座および前記第１弁体に取り付けられた第１弁棒を有する止め弁と、
前記止め弁の下流側に配置され、第２弁体、前記第２弁体が閉弁時に当接する第２弁座および前記第２弁体に取り付けられた第２弁棒を有する加減弁と、
前記止め弁を収納する止め弁室、前記加減弁を収納する加減弁室、前記止め弁室に蒸気を供給する蒸気入口部、前記止め弁室と前記加減弁室との間に設けられるストレート形状の中間流路、および、前記加減弁室からの蒸気を排出する蒸気出口部を有する弁ケーシングとを備え、
前記止め弁の前記第１弁棒と、前記加減弁の前記第２弁棒とは、前記中間流路を挟んで反対方向に延在していることを特徴とする組合せ蒸気弁。 A combination steam valve in which a stop valve and an adjusting valve are provided in a common valve casing,
A stop valve having a first valve body, a first valve seat with which the first valve body abuts when the valve is closed, and a first valve rod attached to the first valve body;
An adjusting valve having a second valve body disposed downstream of the stop valve, a second valve seat with which the second valve body abuts when the valve is closed, and a second valve rod attached to the second valve body;
A stop valve chamber for storing the stop valve, a control valve chamber for storing the control valve, a steam inlet for supplying steam to the stop valve chamber, and a straight shape provided between the stop valve chamber and the control valve chamber An intermediate flow path, and a valve casing having a steam outlet for discharging steam from the control valve chamber,
The combination steam valve, wherein the first valve rod of the stop valve and the second valve rod of the control valve extend in opposite directions across the intermediate flow path. 前記弁ケーシングの内壁には、前記中間流路の全長にわたって、前記第１弁座および前記第２弁座が一体化された共通弁座が設けられていることを特徴とする請求項１に記載の組合せ蒸気弁。   The common valve seat in which the first valve seat and the second valve seat are integrated is provided on the inner wall of the valve casing over the entire length of the intermediate flow path. Combination steam valve. 前記共通弁座は、前記第１弁座のシート部よりも蒸気流れ方向における上流側においてのみ、前記弁ケーシングの内壁に固定されていることを特徴とする請求項２に記載の組合せ蒸気弁。   3. The combined steam valve according to claim 2, wherein the common valve seat is fixed to the inner wall of the valve casing only on the upstream side in the steam flow direction from the seat portion of the first valve seat. 前記第２弁座は、蒸気流れ方向における上流側から下流側に向かって拡径していることを特徴とする請求項１乃至３のいずれか一項に記載の組合せ蒸気弁。   The combined steam valve according to any one of claims 1 to 3, wherein the diameter of the second valve seat is increased from the upstream side toward the downstream side in the steam flow direction. 前記第２弁体の弁頭部は凹形状であることを特徴とする請求項４に記載の組合せ蒸気弁。   The combined steam valve according to claim 4, wherein the valve head of the second valve body has a concave shape. 前記第２弁体の外周に設けられ、前記第２弁体を案内する円筒状の弁体ガイドをさらに備え、
前記第２弁体の弁頭部には、前記第２弁体及び前記弁体ガイドで囲まれた内部空間を前記中間流路に連通するバランス穴が形成されており、
前記第２弁座のシート部の直径よりも、前記弁体ガイドの内径が大きいことを特徴とする請求項４又は５に記載の組合せ蒸気弁。 A cylindrical valve body guide that is provided on an outer periphery of the second valve body and guides the second valve body;
The valve head of the second valve body is formed with a balance hole that communicates the internal space surrounded by the second valve body and the valve body guide with the intermediate flow path,
The combined steam valve according to claim 4 or 5, wherein an inner diameter of the valve body guide is larger than a diameter of a seat portion of the second valve seat. 請求項１乃至６のいずれか一項に記載された複数の組合せ蒸気弁と、
前記複数の組合せ蒸気弁が接続されるとともに、ロータを収納するタービン車室とを備え、
前記複数の組合せ蒸気弁は、前記タービン車室の両側にロータ軸方向に沿って配置されることを特徴とする蒸気タービン。 A plurality of combination steam valves according to any one of claims 1 to 6;
The plurality of combination steam valves are connected, and a turbine casing that houses a rotor is provided,
The plurality of combination steam valves are disposed along both sides of the turbine casing along a rotor axial direction. 前記複数の組合せ蒸気弁は、前記タービン車室の両側に少なくとも一対ずつ設けられており、
前記少なくとも一対の組合せ蒸気弁は、鉛直方向および前記ロータ軸方向に直交する方向にずらして配置されていることを特徴とする請求項７に記載の蒸気タービン。 The plurality of combination steam valves are provided at least one pair on both sides of the turbine casing,
The steam turbine according to claim 7, wherein the at least one pair of combination steam valves are arranged so as to be shifted in a vertical direction and a direction orthogonal to the rotor axial direction.
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CN102797519A (en) * 2012-08-30 2012-11-28 山东青能动力股份有限公司 Highly-stable complex molded line inlet valve
JP2015068309A (en) * 2013-09-30 2015-04-13 三菱重工業株式会社 On-off valve and vapor turbine
JP2016084788A (en) * 2014-10-28 2016-05-19 三菱日立パワーシステムズ株式会社 Main steam valve and steam turbine
US10119416B2 (en) 2014-10-28 2018-11-06 Mitsubishi Hitachi Power Systems, Ltd. Main steam valve and steam turbine
WO2017073466A1 (en) * 2015-10-30 2017-05-04 三菱日立パワーシステムズ株式会社 Vapor valve and vapor turbine system
JP2017082722A (en) * 2015-10-30 2017-05-18 三菱日立パワーシステムズ株式会社 Steam valve and steam turbine system
CN108138580A (en) * 2015-10-30 2018-06-08 三菱日立电力***株式会社 Steam valve and steam turbine system
CN107061862A (en) * 2017-06-01 2017-08-18 东方电气集团东方汽轮机有限公司 A kind of valve crosshead connecting structure

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