JP4504091B2

JP4504091B2 - Control valve

Info

Publication number: JP4504091B2
Application number: JP2004143934A
Authority: JP
Inventors: 克也大村
Original assignee: Toshiba Corp
Current assignee: Toshiba Corp
Priority date: 2004-05-13
Filing date: 2004-05-13
Publication date: 2010-07-14
Anticipated expiration: 2024-05-13
Also published as: JP2005325750A

Description

本発明は、蒸気等の流体の流量を調節する加減弁に係り、特に騒音を低減させた加減弁に関する。 The present invention relates to an adjusting valve that adjusts the flow rate of a fluid such as steam, and more particularly to an adjusting valve that reduces noise.

従来、蒸気タービン等の設備には蒸気の流量を調整するために図２１に示すような加減弁が設けられる。 Conventionally, equipment such as a steam turbine is provided with an adjusting valve as shown in FIG. 21 in order to adjust the flow rate of steam.

加減弁１は、弁ケーシング２内に棒状の弁棒３を覆う状態で固定された筒状の主弁４と弁座５とを備え、弁棒３を介して主弁４を弁座５に向けて進退駆動させることにより主弁４を弁座５の座面６に着脱可能に接触させることができるように構成される。 The control valve 1 includes a cylindrical main valve 4 and a valve seat 5 fixed in a state of covering a rod-shaped valve stem 3 in a valve casing 2, and the main valve 4 is connected to the valve seat 5 via the valve stem 3. The main valve 4 can be detachably brought into contact with the seat surface 6 of the valve seat 5 by being driven forward and backward.

そして、弁ケーシング２内において、主弁４の側面側から主弁４と弁座５との隙間を経由し、さらに弁座５の孔内部に向かう蒸気Ｙの流路７が形成され、加減弁１は主弁４と弁座５との弁開度を調節することにより、主弁４と弁座５との隙間を通過する蒸気Ｙの流量を調節することができる。 In the valve casing 2, a steam Y flow path 7 is formed from the side surface side of the main valve 4 through the gap between the main valve 4 and the valve seat 5 and further toward the inside of the hole of the valve seat 5. 1 can adjust the flow rate of the steam Y passing through the gap between the main valve 4 and the valve seat 5 by adjusting the valve opening degree of the main valve 4 and the valve seat 5.

また、弁棒３の外周は筒状のスリーブ８で覆われ、さらに、スリーブ８と主弁４は、筒状のガイドスリーブ９で覆われる。スリーブ８はガイドスリーブ９に固定され、さらにガイドスリーブ９は弁ケーシング２に固定される。これにより、スリーブ８で弁棒３は長手方向と主直な方向に移動して傾かないように保護される一方、ガイドスリーブ９で主弁４は長手方向と垂直な方向に移動して傾かないように保護される。 The outer periphery of the valve stem 3 is covered with a cylindrical sleeve 8, and the sleeve 8 and the main valve 4 are covered with a cylindrical guide sleeve 9. The sleeve 8 is fixed to the guide sleeve 9, and the guide sleeve 9 is further fixed to the valve casing 2. As a result, the valve stem 3 is protected by the sleeve 8 so as not to move and tilt in the direction perpendicular to the longitudinal direction, while the main valve 4 does not move and tilt in the direction perpendicular to the longitudinal direction by the guide sleeve 9. As protected.

一方、主弁４とガイドスリーブ９との間、主弁４ないし弁棒３とスリーブ８の間の間隙部１０に、主弁４の側面から流れてくる蒸気Ｙのうち一部の蒸気Ｙ１が流れ込み、主弁４とガイドスリーブ９との間、主弁４とスリーブ８との間、弁棒３とスリーブ８との間により蒸気Ｙ１の流路が形成される。 On the other hand, some steam Y 1 out of steam Y flowing from the side surface of the main valve 4 is in the gap 10 between the main valve 4 and the guide sleeve 9 and between the main valve 4 or the valve stem 3 and the sleeve 8. A flow path of steam Y1 is formed between the main valve 4 and the guide sleeve 9, between the main valve 4 and the sleeve 8, and between the valve stem 3 and the sleeve 8.

そこで、加減弁１では、主弁４の外表面に主弁４の横断面の外周方向に複数の溝１１が一定のピッチＰ_０で設けられて、蒸気Ｙ１の流れを乱すことにより主弁２とガイドスリーブ９とに流れ込む蒸気Ｙ１の流量が低減されるように構成される。 Therefore, in the control valve 1, a plurality of grooves 11 are provided on the outer surface of the main valve 4 in the outer peripheral direction of the cross section of the main valve 4 at a constant pitch P ₀ , thereby disturbing the flow of the steam Y 1 to disturb the main valve 2. And the flow rate of the steam Y1 flowing into the guide sleeve 9 is reduced.

一般に、流体の流路の壁面に溝や空洞部が存在し、溝や空洞部近傍をせん断流体が流れるとキャビティートーンと呼ばれる純音に近い流体自励音が発生する。これは、溝や空洞部近傍において渦流れ等の乱れた流れが生じることにより発生する圧力変動と音波によるフィードバックループが形成されるためである。 In general, there are grooves or cavities on the wall surface of the fluid flow path, and when a shear fluid flows in the vicinity of the grooves or cavities, fluid self-excited sound called a cavity tone is generated. This is because a feedback loop is formed by pressure fluctuations and sound waves generated by a turbulent flow such as a vortex flow in the vicinity of the groove or cavity.

このため、従来の加減弁１においては、主弁４とガイドスリーブ９との間の間隙部１０において、蒸気Ｙ１は主弁４の各溝１１に対してせん断流となるため流体自励音が生じる。さらに、主弁４の各溝１１は等ピッチで設けられているため、各溝１１において同様な周波数の流体自励音がそれぞれ生じ、生じた各流体自励音は蒸気Ｙ１が上流側から下流側に流れるにつれて互いに増幅されてより大きな騒音ないし振動となる。 For this reason, in the conventional control valve 1, since the steam Y <b> 1 becomes a shear flow with respect to each groove 11 of the main valve 4 in the gap portion 10 between the main valve 4 and the guide sleeve 9, the fluid self-excited sound is generated. Arise. Furthermore, since each groove 11 of the main valve 4 is provided at an equal pitch, fluid self-excited sound having the same frequency is generated in each groove 11, and the generated fluid self-excited sound is generated by the steam Y1 downstream from the upstream side. As they flow to the side, they are amplified together, resulting in greater noise or vibration.

また、加減弁１の主弁４等の各構成部から騒音や振動が発生すると、発生した騒音や振動の振動数と一致した固有振動数を持つ構成部や加減弁１に接続された部品は共鳴して騒音，振動がさらに増幅される。 In addition, when noise or vibration is generated from each component such as the main valve 4 of the adjusting valve 1, components having a natural frequency that matches the frequency of the generated noise or vibration and components connected to the adjusting valve 1 are The noise and vibration are further amplified by resonance.

このように増幅した振動は、弁棒３、主弁４およびスリーブ８などの薄肉部に対して大きな機械的な応力を発生させ、それにより弁棒３などに微小亀裂などが発生する場合もある。さらに、振動により弁棒３とスリーブ８が摩耗し、場合によってはその寿命を低減させることもある。そのため、肉厚やリブを設けることによって、構造的に耐振動性を持たせた加減弁が提案されている（例えば特許文献１参照）。
特開２００１−１６１０１１号公報 The vibrations thus amplified may cause a large mechanical stress on thin portions such as the valve stem 3, the main valve 4 and the sleeve 8, thereby causing a micro crack or the like in the valve stem 3 or the like. . Furthermore, the valve stem 3 and the sleeve 8 are worn by vibration, and in some cases, the service life may be reduced. For this reason, an adjusting valve that is structurally resistant to vibration by providing a wall thickness or a rib has been proposed (for example, see Patent Document 1).
JP 2001-161011 A

ところで、加減弁１に接続される配管の固有振動数に一致する振動数の騒音ないし振動が加減弁１に発生すると共鳴現象により騒音、振動がさらに増幅される。配管の固有振動数には、配管長さに依存する気柱振動の固有振動数の他に配管の内径に依存する高次音響モードの固有振動数があるが、特に配管の高次音響モードによる固有振動数と加減弁１で発生する騒音および振動の振動数が一致した場合には、より大きな騒音、振動が発生する。 By the way, when noise or vibration having a frequency corresponding to the natural frequency of the pipe connected to the control valve 1 is generated in the control valve 1, noise and vibration are further amplified by a resonance phenomenon. In addition to the natural frequency of air column vibration that depends on the pipe length, the natural frequency of the pipe includes the natural frequency of the higher order acoustic mode that depends on the inner diameter of the pipe. When the natural frequency matches the noise generated by the adjusting valve 1 and the vibration frequency, larger noise and vibration are generated.

そして、加減弁１から生じた騒音および振動が増幅されると、増幅された騒音および振動は加減弁１のみならず加減弁１に接続された配管や蒸気タービンその他の機器に伝播し、各機器の破損等の事故を引き起こす原因となる恐れがある。 When the noise and vibration generated from the control valve 1 are amplified, the amplified noise and vibration are propagated not only to the control valve 1 but also to pipes connected to the control valve 1, steam turbines, and other devices. There is a risk of causing an accident such as damage.

本発明はかかる従来の事情に対処するためになされたものであり、より小さい騒音ないし振動で流体の流量を調節することが可能な加減弁を提供することを目的とする。 The present invention has been made in order to cope with such a conventional situation, and an object thereof is to provide an adjusting valve capable of adjusting the flow rate of fluid with less noise or vibration.

本発明に係る加減弁は、上述の目的を達成するために、請求項１に記載したように、流体の流路上に設けられた弁座と、この弁座との隙間により前記流体の流路を形成するとともに前記隙間の量である弁開度を調節可能に設けられた主弁と、この主弁を固定する弁棒と、この弁棒を保護するスリーブと、前記主弁を保護するガイドスリーブとを備え、前記主弁、ガイドスリーブ、弁棒、スリーブの隙間により形成される間隙部のうち前記ガイドスリーブの前記間隙部に面した部位に、不等ピッチで複数の溝を設けたことを特徴とするものである。 In order to achieve the above-mentioned object, the adjusting valve according to the present invention is, as described in claim 1, a valve seat provided on the fluid passage and a fluid passage by the gap between the valve seat. And a main valve provided to be able to adjust the valve opening that is the amount of the gap, a valve stem that fixes the main valve, a sleeve that protects the valve stem, and a guide that protects the main valve And provided with a plurality of grooves at unequal pitches in a portion of the gap formed by the gap between the main valve, guide sleeve, valve stem, and sleeve and facing the gap of the guide sleeve. It is characterized by.

また、本発明に係る加減弁は、上述の目的を達成するために、請求項２に記載したように、流体の流路上に設けられた弁座と、この弁座との隙間により前記流体の流路を形成するとともに前記隙間の量である弁開度を調節可能に設けられた主弁と、この主弁を固定する弁棒と、この弁棒を保護するスリーブと、前記主弁を保護するガイドスリーブとを備え、前記主弁、ガイドスリーブ、弁棒、スリーブの隙間により形成される間隙部の所要の部位に、前記間隙部に流れ込んだ前記流体に圧力変動が誘起されにくい横断面形状の溝を設けたことを特徴とするものである。 Further, in order to achieve the above-mentioned object, the adjusting valve according to the present invention has a valve seat provided on the fluid flow path and a gap between the valve seat and the fluid seat. A main valve that forms a flow path and can adjust the valve opening that is the amount of the gap, a valve rod that fixes the main valve, a sleeve that protects the valve rod, and the main valve are protected A cross-sectional shape that is less likely to induce pressure fluctuations in the fluid that has flowed into the gap at a required portion of the gap formed by the gap between the main valve, guide sleeve, valve stem, and sleeve. The groove is provided.

また、本発明に係る加減弁は、上述の目的を達成するために、請求項７に記載したように、配管により形成された流体の流路上に設けられた複数の加減弁構成部品により構成され、この加減弁構成部品のうち所要の加減弁構成部品の固有振動数を前記配管の内径に依存する高次音響モードの固有振動数から離調したことを特徴とするものである。 Further, in order to achieve the above-mentioned object, the regulator valve according to the present invention is constituted by a plurality of regulator valve components provided on a fluid flow path formed by piping as described in claim 7. Of the regulating valve components, the natural frequency of a required regulating valve component is detuned from the natural frequency of a higher-order acoustic mode that depends on the inner diameter of the pipe.

本発明に係る加減弁においては、より小さい騒音ないし振動で流体の流量を調節することができる。 In the adjusting valve according to the present invention, the flow rate of the fluid can be adjusted with less noise or vibration.

本発明に係る加減弁の実施の形態について添付図面を参照して説明する。 An embodiment of an adjusting valve according to the present invention will be described with reference to the accompanying drawings.

（実施例１）
図１は本発明に係る加減弁の第１の実施形態を示す断面構成図である。 Example 1
FIG. 1 is a cross-sectional configuration diagram showing a first embodiment of an adjusting valve according to the present invention.

蒸気タービン等の設備に導かれる流体の一例としての蒸気Ｘの流路には、上流側から図示しない蒸気止め弁と蒸気Ｘの流量を調整するための加減弁２０とが設けられる。 In the flow path of the steam X as an example of the fluid guided to equipment such as a steam turbine, a steam stop valve (not shown) and an adjusting valve 20 for adjusting the flow rate of the steam X are provided from the upstream side.

加減弁２０は、棒状の弁棒２１に固定された筒状の主弁２２と弁座２３とを弁ケーシング２４内に設けた構成である。そして、筒状の主弁２２の内部に弁棒２１の一端が挿入され、挿入された弁棒２１の端部に主弁２２が固定される一方、弁棒２１の他端は弁ケーシング２４の外部に導かれる。弁棒２１は長手方向に移動可能であり、弁棒２１の移動に伴って主弁２２は弁棒２１の長手方向に移動可能に構成される。 The control valve 20 has a configuration in which a cylindrical main valve 22 and a valve seat 23 fixed to a rod-shaped valve rod 21 are provided in a valve casing 24. One end of the valve stem 21 is inserted into the cylindrical main valve 22 and the main valve 22 is fixed to the end of the inserted valve stem 21, while the other end of the valve stem 21 is connected to the valve casing 24. Guided outside. The valve stem 21 is movable in the longitudinal direction, and the main valve 22 is configured to be movable in the longitudinal direction of the valve stem 21 as the valve stem 21 moves.

また、弁棒２１の外周は筒状のスリーブ２５で覆われ、さらに、弁棒２１を覆う主弁２２およびスリーブ２５は、筒状のガイドスリーブ２６で覆われる。ガイドスリーブ２６は弁ケーシング２４に固定され、さらにスリーブ２５はガイドスリーブ２６に固定される。 The outer periphery of the valve stem 21 is covered with a cylindrical sleeve 25, and the main valve 22 and the sleeve 25 covering the valve stem 21 are covered with a cylindrical guide sleeve 26. The guide sleeve 26 is fixed to the valve casing 24, and the sleeve 25 is fixed to the guide sleeve 26.

そして、弁棒２１はスリーブ２５により長手方向と主直な方向に移動して傾かないように保護される一方、弁棒２１の長手方向には移動可能に構成される。このためスリーブ２５は、弁棒２１および主弁２２のいずれに対しても隙間を有する状態で設けられる。 The valve stem 21 is protected by the sleeve 25 from moving in the direction perpendicular to the longitudinal direction so as not to tilt, while being movable in the longitudinal direction of the valve stem 21. For this reason, the sleeve 25 is provided in a state having a gap with respect to both the valve stem 21 and the main valve 22.

同様に、主弁２２はガイドスリーブ２６により長手方向と垂直な方向に移動し傾かないように保護される一方、主弁２２の長手方向には移動可能に構成される。このためガイドスリーブ２６はスリーブ２５とは密着して固定される一方、主弁２２との間に隙間を有する状態で設けられる。 Similarly, the main valve 22 is configured to move in the longitudinal direction of the main valve 22 while being protected by the guide sleeve 26 so as not to move and tilt in the direction perpendicular to the longitudinal direction. For this reason, the guide sleeve 26 is provided in close contact with the sleeve 25 while having a gap between the guide sleeve 26 and the main valve 22.

一方、主弁２２の弁棒２１が突出しない側の端部側にはテーパ状孔２７を有する筒状の弁座２３が設けられ、弁座２３のテーパ状孔２７の径が大きい側の端部側内面は座面２８を形成する。そして、弁棒２１を介して主弁２２を駆動させることにより主弁２２を弁座２３の座面２８に着脱可能に接触させることができるように構成される。 On the other hand, a cylindrical valve seat 23 having a tapered hole 27 is provided on the end of the main valve 22 on the side where the valve rod 21 does not protrude, and the end of the valve seat 23 on the side where the diameter of the tapered hole 27 is large. The part-side inner surface forms a seating surface 28. And it is comprised so that the main valve 22 can be made to contact the seat surface 28 of the valve seat 23 so that attachment or detachment is possible by driving the main valve 22 via the valve rod 21. FIG.

そして、主弁２２の側面側から主弁２２と弁座２３との隙間を経由し、さらに弁座２３のテーパ状孔２７内部に向かう蒸気Ｘの流路２９が形成される。さらに弁座２３のテーパ状孔２７の主弁２２が設けられない側、すなわち加減弁２０の下流側の蒸気Ｘの流路２９は配管３０に接続される。そして、加減弁２０の蒸気Ｘの流路２９の下流側に接続された配管３０は図示しない蒸気タービンに接続され、加減弁２０を経由した蒸気Ｘは蒸気タービンに導かれるように構成される。 Then, a flow path 29 of steam X is formed from the side surface side of the main valve 22 through the gap between the main valve 22 and the valve seat 23 and further toward the inside of the tapered hole 27 of the valve seat 23. Further, the flow path 29 of the steam X on the side where the main valve 22 of the tapered hole 27 of the valve seat 23 is not provided, that is, the downstream side of the control valve 20 is connected to the pipe 30. The piping 30 connected to the downstream side of the steam X flow path 29 of the control valve 20 is connected to a steam turbine (not shown), and the steam X passing through the control valve 20 is guided to the steam turbine.

この結果、加減弁２０は、弁棒２１を介して主弁２２を長手方向に駆動させることにより主弁２２と弁座２３との隙間の量すなわち弁開度を調節し、主弁２２と弁座２３との隙間における蒸気Ｘの流量を調節することができるように構成される。 As a result, the adjusting valve 20 drives the main valve 22 in the longitudinal direction via the valve rod 21 to adjust the amount of clearance between the main valve 22 and the valve seat 23, that is, the valve opening degree. It is comprised so that the flow volume of the vapor | steam X in the clearance gap with the seat 23 can be adjusted.

すなわち、加減弁２０は、主弁２２を長手方向に駆動させて弁開度を調節することにより、図示しない蒸気止め弁側から流れてくる蒸気Ｘのうち所要の流量の蒸気Ｘを調節して蒸気タービンに導くことができる。 That is, the adjusting valve 20 adjusts the steam X having a required flow rate among the steam X flowing from the steam stop valve (not shown) by driving the main valve 22 in the longitudinal direction and adjusting the valve opening degree. It can be led to a steam turbine.

一方、主弁２２とガイドスリーブ２６との間、主弁２２ないし弁棒２１とスリーブ２５の間には間隙部３１が形成されるため、主弁２２の側面から流れてくる蒸気Ｘのうち一部の蒸気Ｘ１は主弁２２とガイドスリーブ２６との間に流れ込む。このため、主弁２２とガイドスリーブ２６との間、主弁２２スリーブ２５との間、弁棒２１とスリーブ２５との間の間隙部３１により蒸気Ｘ１の流路が形成される。このうち主弁２２とガイドスリーブ２６との間の蒸気Ｘ１の流路は環状に形成されるため、主弁２２とガイドスリーブ２６との間の間隙部３１を流れる蒸気Ｘ１の流れの向きは主弁２２の長手方向となる。 On the other hand, since a gap 31 is formed between the main valve 22 and the guide sleeve 26 and between the main valve 22 or the valve stem 21 and the sleeve 25, one of the steam X flowing from the side surface of the main valve 22. Part of the steam X1 flows between the main valve 22 and the guide sleeve 26. For this reason, the flow path of the steam X1 is formed by the gap portion 31 between the main valve 22 and the guide sleeve 26, between the main valve 22 sleeve 25, and between the valve stem 21 and the sleeve 25. Among these, since the flow path of the steam X1 between the main valve 22 and the guide sleeve 26 is formed in an annular shape, the flow direction of the steam X1 flowing through the gap 31 between the main valve 22 and the guide sleeve 26 is the main direction. It becomes the longitudinal direction of the valve 22.

そこで、主弁２２の外表面には主弁２２の横断面の外周方向に少なくとも３つ以上の任意数の溝３２が設けられる。すなわち、主弁２２とガイドスリーブ２６との間の間隙部３１を流れる蒸気Ｘ１の流量を低減させるため、蒸気Ｘ１が流れる方向に対して所要の角度で、例えば垂直な向きで主弁２２の外表面に任意数の溝３２を設け、蒸気Ｘ１の流れに乱れを生じさせるように構成される。 Therefore, at least three or more arbitrary number of grooves 32 are provided on the outer surface of the main valve 22 in the outer peripheral direction of the cross section of the main valve 22. That is, in order to reduce the flow rate of the steam X1 flowing through the gap portion 31 between the main valve 22 and the guide sleeve 26, the outside of the main valve 22 is at a required angle with respect to the direction in which the steam X1 flows, for example, in a vertical direction. An arbitrary number of grooves 32 are provided on the surface, and the flow of the steam X1 is disturbed.

一般に、流体の流路の壁面に溝や空洞部が存在し、溝や空洞部近傍をせん断流体が流れるとキャビティートーンと呼ばれる純音に近い流体自励音が発生する。これは、溝や空洞部近傍をせん断流体が流れると、溝や空洞部近傍において渦流れ等の乱れた流れが生じ、乱流の発生に伴う圧力変動と音波によるフィードバックループが形成されるためである。 In general, there are grooves or cavities on the wall surface of the fluid flow path, and when a shear fluid flows in the vicinity of the grooves or cavities, fluid self-excited sound called a cavity tone is generated. This is because when a shear fluid flows in the vicinity of a groove or cavity, a turbulent flow such as a vortex flow occurs in the vicinity of the groove or cavity, and a pressure loop and a feedback loop due to sound waves are formed due to the generation of turbulent flow. is there.

このため、主弁２２とガイドスリーブ２６との間の蒸気Ｘ１の流路において、主弁２２の外表面の各溝３２近傍を蒸気Ｘ１が通過する際には、蒸気Ｘ１は各溝３２に対してせん断流となり流体自励音が生じる。 For this reason, in the flow path of the steam X1 between the main valve 22 and the guide sleeve 26, when the steam X1 passes in the vicinity of each groove 32 on the outer surface of the main valve 22, the steam X1 flows to each groove 32. As a result, shear flow is generated and self-excited fluid is generated.

そこで、主弁２２の外表面の各溝３２間の各ピッチＰ_１は一定とされず不等ピッチとされる。すなわち、主弁２２の外表面のある１つ溝３２近傍を蒸気Ｘ１が通過する際に生じた流体自励音の周波数と、別の溝３２近傍を蒸気Ｘ１が通過する際に生じた流体自励音の周波数とが互いに異なる値となるように各溝３２が主弁２２の外表面に形成される。 Therefore, each pitch P ₁ between each of the grooves 32 of the outer surface of the main valve 22 is unequal pitch not constant. That is, the frequency of the fluid self-excited sound generated when the steam X1 passes in the vicinity of one groove 32 on the outer surface of the main valve 22 and the fluid self-generated when the steam X1 passes in the vicinity of another groove 32. Each groove 32 is formed on the outer surface of the main valve 22 so that the frequency of the excitation sound is different from each other.

そして、主弁２２の外表面の各溝３２近傍で生じた各流体自励音が互いに強め合って増幅されないように構成される。 And it is comprised so that each fluid self-excited sound produced in the vicinity of each groove | channel 32 of the outer surface of the main valve 22 may mutually strengthen, and may not be amplified.

次に加減弁２０の作用について説明する。 Next, the operation of the control valve 20 will be described.

まず、図示しない蒸気止め弁から加減弁２０に蒸気Ｘが導かれる。加減弁２０に導かれた蒸気Ｘは、主弁２２の側面側から主弁２２と弁座２３との隙間を経由し、弁座２３のテーパ状孔２７に向かって流れる。 First, the steam X is guided to the control valve 20 from a steam stop valve (not shown). The steam X guided to the control valve 20 flows from the side surface side of the main valve 22 through the gap between the main valve 22 and the valve seat 23 toward the tapered hole 27 of the valve seat 23.

このとき、加減弁２０は、弁棒２１を介して主弁２２を長手方向に駆動させることにより主弁２２と弁座２３との隙間の量すなわち弁開度を調節し、主弁２２と弁座２３との隙間における蒸気Ｘの流量が所要の流量となるように調整される。 At this time, the adjusting valve 20 adjusts the amount of clearance between the main valve 22 and the valve seat 23, that is, the valve opening degree, by driving the main valve 22 in the longitudinal direction via the valve rod 21. The flow rate of the steam X in the gap with the seat 23 is adjusted to a required flow rate.

そして、主弁２２と弁座２３との隙間を通過した所要の流量の蒸気Ｘは弁座２３のテーパ状孔２７内を経由した後、配管３０内に流出される。さらにこの配管３０内を経由した所要の流量の蒸気Ｘは蒸気タービンに導かれ、蒸気タービンの入力エネルギとして仕事をする。 Then, the steam X having a required flow rate that has passed through the gap between the main valve 22 and the valve seat 23 passes through the tapered hole 27 of the valve seat 23 and then flows out into the pipe 30. Further, the steam X having a required flow rate through the pipe 30 is guided to the steam turbine and works as input energy of the steam turbine.

一方、主弁２２の側面から流れてくる蒸気Ｘのうち一部の蒸気Ｘ１は主弁２２とガイドスリーブ２６との間の間隙部３１に流れ込み、主弁２２の長手方向に向かって流れる。 On the other hand, a part of the steam X 1 flowing from the side surface of the main valve 22 flows into the gap 31 between the main valve 22 and the guide sleeve 26 and flows in the longitudinal direction of the main valve 22.

ここで、主弁２２の外表面には複数の溝３２が、主弁２２の横断面の外周方向すなわち蒸気Ｘ１が流れる方向に対して垂直な向きで設けられているため、蒸気Ｘ１の流れは乱れて主弁２２とガイドスリーブ２６との間の間隙部３１に流れ込む蒸気Ｘ１の流量は低減される。 Here, since the plurality of grooves 32 are provided on the outer surface of the main valve 22 in a direction perpendicular to the outer peripheral direction of the cross section of the main valve 22, that is, the direction in which the steam X1 flows, the flow of the steam X1 is The flow rate of the steam X1 that is disturbed and flows into the gap 31 between the main valve 22 and the guide sleeve 26 is reduced.

さらに、このとき主弁２２の各溝３２近傍には、蒸気Ｘ１の流れに伴って流体自励音が生じる。ここで、主弁２２の各溝３２間の各ピッチＰ_１は一定とされず不等ピッチであり、各溝３２近傍において生じた流体自励音の周波数は互いに異なるため、各流体自励音同士は互いに強め合うことなく増幅が抑制されてより小さい騒音ないし振動を伴って伝播する。 Further, at this time, fluid self-excited sound is generated in the vicinity of each groove 32 of the main valve 22 along with the flow of the steam X1. Here, each pitch P ₁ between each of the grooves 32 of the main valve 22 is nonuniform pitch not constant, the frequency of the fluid itself励音generated in each groove 32 near differ from each other, each of the fluid itself励音Amplification is suppressed and the waves propagate with less noise or vibration without strengthening each other.

この結果、加減弁２０により蒸気Ｘは、より小さい騒音ないし振動で流量が調整されて蒸気タービンに導かれる。 As a result, the flow rate of the steam X is adjusted by the control valve 20 with less noise or vibration and guided to the steam turbine.

すなわち加減弁２０は、主弁２２とガイドスリーブ２６との間の間隙部３１に流れ込む蒸気Ｘ１の流量を低減させるために主弁２２の外表面に設けられた各溝３２間の各ピッチＰ_１を不等ピッチとすることにより、主弁２２の各溝３２近傍を蒸気Ｘ１が通過することにより流体自励音が生じても、生じた各流体自励音の周波数が互いに異なるものとして流体自励音の増幅を抑制させる構成である。 In other words, the adjusting valve 20 has a pitch P ₁ between the grooves 32 provided on the outer surface of the main valve 22 in order to reduce the flow rate of the steam X 1 flowing into the gap 31 between the main valve 22 and the guide sleeve 26. By making the pitches unequal, even if the fluid self-excited sound is generated by the passage of the steam X1 in the vicinity of the grooves 32 of the main valve 22, the frequencies of the generated self-excited sounds are different from each other. In this configuration, amplification of excitation sound is suppressed.

従来の加減弁１においては、主弁の外表面に設けられた各溝は等ピッチＰ_０であるため、主弁５１とガイドスリーブ５８との間に流れ込んだ蒸気Ｘ１により、主弁の各溝近傍において同程度の周波数の流体自励音がそれぞれ生じ、上流側から下流側に蒸気Ｘ１が流れるにつれて次第に各流体自励音が互いに増幅され、大きな騒音，振動となるという問題があった。 In the conventional control valve 1, each groove provided on the outer surface of the main valve has an equal pitch P ₀ , and therefore each groove of the main valve is caused by the steam X 1 flowing between the main valve 51 and the guide sleeve 58. In the vicinity, fluid self-excited sounds having the same frequency are generated, and as the steam X1 flows from the upstream side to the downstream side, the fluid self-excited sounds gradually amplify each other, resulting in large noise and vibration.

加減弁２０においては、主弁２２の外表面に設けられた各溝３２間の各ピッチＰ_１が不等ピッチであるため、主弁２２とガイドスリーブ２６との間の隙間に流れ込む蒸気Ｘ１の流量を低減させることができるのみならず、主弁２２の各溝３２近傍で流体自励音が生じても各流体自励音の周波数は互いに異なるものとして増幅を抑制し、加減弁２０の振動ないし騒音を低減させることができる。 In control valve 20, since the pitch P ₁ between the grooves 32 provided on the outer surface of the main valve 22 is unequal pitch, steam X1 flowing into the gap between the main valve 22 and the guide sleeve 26 Not only can the flow rate be reduced, but even if fluid self-excited sounds are generated in the vicinity of the grooves 32 of the main valve 22, the frequency of each fluid self-excited sound is different from each other to suppress amplification, and vibration of the adjusting valve 20. In addition, noise can be reduced.

さらに、例えば蒸気タービンに使用される蒸気Ｘの流量調整を行うための加減弁においては、蒸気タービンに流入する前の蒸気Ｘは高温かつ高圧であるため、蒸気タービン設備に用いられる機器の中では特に過酷な条件で使用される。 Further, for example, in the control valve for adjusting the flow rate of the steam X used in the steam turbine, the steam X before flowing into the steam turbine is high temperature and high pressure. Used in particularly severe conditions.

このため、蒸気タービンに使用される加減弁にはより高い機械強度の信頼性が要求されるが、加減弁２０では蒸気タービンの運転時のように過酷な条件で使用されても、振動を低減させて信頼性を向上させることができる。 For this reason, the control valve used in the steam turbine is required to have higher mechanical strength reliability. However, the control valve 20 reduces vibration even when used in harsh conditions such as during operation of the steam turbine. Reliability can be improved.

尚、加減弁２０において、主弁２２の外表面に設けられた各溝３２の間隔は、必要な程度で各流体自励音の増幅を抑制することができればよい。従って、少なくとも溝３２間のピッチＰ_１が異なる部位が２箇所存在すればよく、互いに等ピッチとなるような溝３２を主弁２２の外表面に設けても良い。すなわち、全ての溝３２間のピッチＰ_１が不等ピッチとなる構成、全ての溝３２間のピッチＰ_１のうち一部のみが不等ピッチとなるように溝３２が形成される構成のいずれであってもよい。 In addition, in the control valve 20, the space | interval of each groove | channel 32 provided in the outer surface of the main valve 22 should just be able to suppress amplification of each fluid self-excited sound to a required extent. Accordingly, it is sufficient that at least two parts having different pitches P ₁ between the grooves 32 exist, and the grooves 32 having the same pitch may be provided on the outer surface of the main valve 22. That is, any configuration structure in which the pitch P ₁ between all the grooves 32 becomes irregular pitch, the groove 32 so that only a portion of the pitch P ₁ between all the grooves 32 becomes irregular pitch is formed It may be.

また、加減弁２０において、主弁２２とガイドスリーブ２６との間の隙間に流れ込む蒸気Ｘ１の流量を低減させることができれば、主弁２２の外表面に設けられた各溝３２の間隔自体および溝３２の数は任意である。 In addition, if the flow rate of the steam X1 flowing into the gap between the main valve 22 and the guide sleeve 26 can be reduced in the control valve 20, the distance between the grooves 32 provided on the outer surface of the main valve 22 and the groove itself. The number 32 is arbitrary.

（実施例２）
図２は本発明に係る加減弁の第２の実施形態を示す断面構成図である。 (Example 2)
FIG. 2 is a cross-sectional configuration diagram showing a second embodiment of the adjusting valve according to the present invention.

図２に示された、加減弁２０Ａでは、主弁２２とガイドスリーブ２６との間の隙間に流れ込む蒸気Ｘ１の流量を低減させるための溝３２を設ける部位が図１に示す加減弁２０と相違する。他の構成および作用については図１に示す加減弁２０と実質的に異ならないため同一の構成については同符号を付して説明を省略する。 The control valve 20A shown in FIG. 2 is different from the control valve 20 shown in FIG. 1 in that the groove 32 for reducing the flow rate of the steam X1 flowing into the gap between the main valve 22 and the guide sleeve 26 is provided. To do. Since other configurations and operations are not substantially different from those of the adjusting valve 20 shown in FIG. 1, the same components are denoted by the same reference numerals and description thereof is omitted.

加減弁２０Ａでは、加減弁２０において主弁２２の外表面に設けられた溝３２と同様な不等ピッチの複数の溝３２が、主弁２２の外表面に設けられる代わりに筒状のガイドスリーブ２６の内表面に設けられる。このとき、ガイドスリーブ２６の内表面の溝３２は、蒸気Ｘ１の流れに対して垂直な方向となるように設けられる。 In the control valve 20 </ b> A, a plurality of grooves 32 of unequal pitch similar to the grooves 32 provided on the outer surface of the main valve 22 in the control valve 20 are provided on the outer surface of the main valve 22 instead of a cylindrical guide sleeve. 26 on the inner surface. At this time, the groove 32 on the inner surface of the guide sleeve 26 is provided in a direction perpendicular to the flow of the steam X1.

このため、加減弁２０Ａでは、図１に示す加減弁２０と同様の効果を得ることができる。 For this reason, in the control valve 20A, the effect similar to the control valve 20 shown in FIG. 1 can be acquired.

（実施例３）
図３は本発明に係る加減弁の第３の実施形態を示す断面構成図である。 Example 3
FIG. 3 is a cross-sectional configuration diagram showing a third embodiment of the adjustable valve according to the present invention.

図３に示された、加減弁２０Ｂでは、主弁２２の溝３２ａ近傍の形状が図１に示す加減弁２０と相違する。他の構成および作用については図１に示す加減弁２０と実質的に異ならないため同一の構成については同符号を付して説明を省略する。 In the control valve 20B shown in FIG. 3, the shape of the main valve 22 near the groove 32a is different from that of the control valve 20 shown in FIG. Since other configurations and operations are not substantially different from those of the adjusting valve 20 shown in FIG. 1, the same components are denoted by the same reference numerals and description thereof is omitted.

加減弁２０Ｂでは、主弁２２の外表面に複数の溝３２ａが規則的なピッチＰ_２で設けられる。ただし、主弁２２の溝３２ａ近傍の形状は、主弁２２とガイドスリーブ２６との間の間隙部３１に蒸気Ｘ１の渦流れや流れの剥離等の乱れた流れが形成されにくい、すなわち蒸気Ｘ１に圧力変動が誘起されにくい形状とされる。 In control valve 20B, a plurality of grooves 32a on the outer surface of the main valve 22 are provided at a regular pitch _{P 2.} However, the shape of the main valve 22 in the vicinity of the groove 32a is less likely to form a turbulent flow such as a vortex flow of the steam X1 or flow separation in the gap 31 between the main valve 22 and the guide sleeve 26, that is, the steam X1. The shape is such that pressure fluctuations are not easily induced.

図４は図３に示す主弁２２の溝３２ａ近傍の一例を示す拡大断面図である。 4 is an enlarged cross-sectional view showing an example of the vicinity of the groove 32a of the main valve 22 shown in FIG.

図４に示すように、加減弁２０Ｂにおける主弁２２の溝３２ａ近傍の形状は、主弁２２に設けられる隣接する各溝３２ａ間のピッチＰ_２が規則的に変化する形状とされる。すなわち各溝３２ａ間のピッチＰ_２が徐々に規則的に広くなるように、あるいは徐々に狭くなるように主弁２２に溝３２ａが設けられる。 As shown in FIG. 4, the groove 32a near the shape of the main valve 22 in the control valve 20B, the pitch P ₂ between the grooves 32a adjacent provided in the main valve 22 is a regularly varying shapes. Or groove 32a is provided in the main valve 22 so that the pitch P ₂ is such gradually widened regularly, or gradually narrows between the grooves 32a.

例えば、主弁２２には４つの溝３２ａが設けられ、各溝３２ａ間の３箇所のピッチＰ_２を一方側から他方側に向かってａ_１，ａ_２，ａ_３とすると式（１）のような関係となる。 For example, four grooves 32a are provided in the main valve 22, when the pitch _{P 2} of three between the grooves 32a from one side toward the other side and _a _1, a 2, _{a 3} formula (1) It becomes such a relationship.

［数１］
ａ_１＜ａ_２＜ａ_３ ……（１）
すなわち、主弁２２に設けられる各溝３２ａ間のピッチＰ_２は、主弁２２とガイドスリーブ２６との間の間隙部３１を流れる蒸気Ｘ１に圧力変動が誘起されにくいピッチＰ_２とされる。 [Equation 1]
a ₁ <a ₂ <a ₃ (1)
That is, the pitch P ₂ between the grooves 32a provided in the main valve 22 is the pitch P ₂ less likely to be induced pressure fluctuation in the steam X1 flowing gap 31 between the main valve 22 and the guide sleeve 26.

図５は図３に示す主弁２２の溝３２ａ近傍の別の例を示す拡大断面図である。 FIG. 5 is an enlarged sectional view showing another example of the vicinity of the groove 32a of the main valve 22 shown in FIG.

図５に示すように、加減弁２０Ｂにおける主弁２２の溝３２ａの長さ方向の横断面形状は、主弁２２とガイドスリーブ２６との間の間隙部３１に流れ込んだ蒸気Ｘ１に圧力変動が誘起されにくい形状とされ、各溝３２ａは例えば等ピッチＰ_２で設けられる。 As shown in FIG. 5, the longitudinal cross-sectional shape of the groove 32 a of the main valve 22 in the control valve 20 </ b> B is such that pressure variation occurs in the steam X <b> 1 flowing into the gap portion 31 between the main valve 22 and the guide sleeve 26. is the induced difficult shape, each groove 32a is provided at an equal pitch P _2, for example.

すなわち例えば図５に示すように主弁２２の溝３２ａのうちある溝３２ａの長さ方向の横断面形状は傾斜角度が非線対称なＶ字状とされ、別の溝３２ａの断面形状は線対称のＶ字状とされる。 That is, for example, as shown in FIG. 5, the cross-sectional shape in the length direction of a groove 32a among the grooves 32a of the main valve 22 is a V-shape whose inclination angle is axisymmetric, and the cross-sectional shape of another groove 32a is a line. It is a symmetrical V-shape.

加減弁２０Ｂでは、主弁２２に設けられる各溝３２ａ間のピッチＰ_２ないし各溝３２ａの断面形状が、主弁２２とガイドスリーブ２６との間の間隙部３１に流れ込んだ蒸気Ｘ１に圧力変動が誘起されにくいピッチＰ_２ないし断面形状であるため、流体自励音の発生量を低減させることができる。 In control valve 20B, the cross-sectional shape of the pitch _{P 2} or Kakumizo 32a between the grooves 32a provided in the main valve 22, pressure fluctuations in the steam X1 flowing into the gap portion 31 between the main valve 22 and the guide sleeve 26 Since the pitch P ₂ or the cross-sectional shape is less likely to be induced, the amount of fluid self-excited sound can be reduced.

このため、加減弁２０Ｂでは、主弁２２とガイドスリーブ２６との間の間隙部３１に流れ込む蒸気Ｘ１の流量を低減させることができるとともに、流体自励音の発生を抑制して振動および騒音を低減させることができる。 For this reason, in the control valve 20B, the flow rate of the steam X1 flowing into the gap 31 between the main valve 22 and the guide sleeve 26 can be reduced, and vibration and noise are suppressed by suppressing generation of fluid self-excited sound. Can be reduced.

（実施例４）
図６は本発明に係る加減弁の第４の実施形態を示す断面構成図である。 (Example 4)
FIG. 6 is a cross-sectional configuration diagram showing a fourth embodiment of the adjusting valve according to the present invention.

図６に示された、加減弁２０Ｃでは、主弁２２とガイドスリーブ２６との間の隙間に流れ込む蒸気Ｘ１の流量を低減させるための溝３２ａを設ける部位が図３に示す加減弁２０Ｂと相違する。他の構成および作用については図３に示す加減弁２０Ｂと実質的に異ならないため同一の構成については同符号を付して説明を省略する。 The control valve 20C shown in FIG. 6 is different from the control valve 20B shown in FIG. 3 in that a groove 32a for reducing the flow rate of the steam X1 flowing into the gap between the main valve 22 and the guide sleeve 26 is provided. To do. Since other configurations and operations are not substantially different from the control valve 20B shown in FIG. 3, the same components are denoted by the same reference numerals and description thereof is omitted.

加減弁２０Ｃでは、加減弁２０Ｂにおいて主弁２２の外表面に設けられた溝３２ａと同様な蒸気Ｘ１の圧力変動が誘起されにくいピッチＰ_２ないし断面形状の複数の溝３２ａが、主弁２２の外表面に設けられる代わりに筒状のガイドスリーブ２６の内表面に設けられる。 In control valve 20C, a plurality of grooves 32a of the pitch P ₂ to the cross-sectional shape pressure fluctuation is difficult to induce the groove 32a similar vapor X1 provided on the outer surface of the main valve 22 in the control valve 20B is, the main valve 22 Instead of being provided on the outer surface, it is provided on the inner surface of the cylindrical guide sleeve 26.

このため、加減弁２０Ｃでは、図３に示す加減弁２０Ｂと同様の効果を得ることができる。 For this reason, in the control valve 20C, the effect similar to the control valve 20B shown in FIG. 3 can be acquired.

（実施例５）
図７は本発明に係る加減弁の第５の実施形態を示す断面構成図である。 (Example 5)
FIG. 7 is a cross-sectional configuration diagram showing a fifth embodiment of the adjusting valve according to the present invention.

図７に示された、加減弁２０Ｄでは、主弁２２の溝３２ａ近傍の形状が図３に示す加減弁２０Ｂと相違する。他の構成および作用については図３に示す加減弁２０Ｂと実質的に異ならないため同一の構成については同符号を付して説明を省略する。 In the control valve 20D shown in FIG. 7, the shape of the main valve 22 near the groove 32a is different from the control valve 20B shown in FIG. Since other configurations and operations are not substantially different from the control valve 20B shown in FIG. 3, the same components are denoted by the same reference numerals and description thereof is omitted.

加減弁２０Ｄでは、蒸気Ｘ１の圧力変動が誘起されにくい断面形状の複数の溝３２ａが不等ピッチＰ_１で主弁２２の外表面に設けられる。 In control valve 20D, a plurality of grooves 32a of hard cross section pressure fluctuations are induced vapor X1 is provided on the outer surface of the main valve 22 at irregular pitches P _1.

このため、加減弁２０Ｄでは、図１に示す加減弁２０と図３に示す加減弁２０Ｂの双方の効果を得ることができる。すなわち、加減弁２０Ｄでは、主弁２２とガイドスリーブ２６との間の隙間に流れ込む蒸気Ｘ１の流量を低減させることができるとともに、流体自励音の発生を抑制し、かつ流体自励音が生じても増幅されることを回避させて加減弁２０Ｄの振動および騒音を低減させることができる。 For this reason, in the control valve 20D, the effect of both the control valve 20 shown in FIG. 1 and the control valve 20B shown in FIG. 3 can be acquired. That is, in the control valve 20D, the flow rate of the steam X1 flowing into the gap between the main valve 22 and the guide sleeve 26 can be reduced, the generation of the fluid self-excited sound is suppressed, and the fluid self-excited sound is generated. However, the vibration and noise of the adjusting valve 20D can be reduced by avoiding amplification.

（実施例６）
図８は本発明に係る加減弁の第６の実施形態を示す断面構成図である。 (Example 6)
FIG. 8 is a cross-sectional configuration diagram showing a sixth embodiment of the adjustable valve according to the present invention.

図８に示された、加減弁２０Ｅでは、主弁２２とガイドスリーブ２６との間の隙間に流れ込む蒸気Ｘ１の流量を低減させるための溝３２ａを設ける部位が図７に示す加減弁２０Ｄと相違する。他の構成および作用については図７に示す加減弁２０Ｄと実質的に異ならないため同一の構成については同符号を付して説明を省略する。 The control valve 20E shown in FIG. 8 is different from the control valve 20D shown in FIG. 7 in that a groove 32a for reducing the flow rate of the steam X1 flowing into the gap between the main valve 22 and the guide sleeve 26 is provided. To do. Since other configurations and operations are not substantially different from the control valve 20D shown in FIG. 7, the same components are denoted by the same reference numerals and description thereof is omitted.

加減弁２０Ｅでは、加減弁２０Ｄにおいて主弁２２の外表面に設けられた溝３２ａと同様に、蒸気Ｘ１の圧力変動が誘起されにくい断面形状の複数の溝３２ａが、主弁２２の外表面に設けられる代わりに筒状のガイドスリーブ２６の内表面に不等ピッチＰ_１で設けられる。 In the control valve 20E, like the groove 32a provided on the outer surface of the main valve 22 in the control valve 20D, a plurality of grooves 32a having a cross-sectional shape in which the pressure fluctuation of the steam X1 is difficult to be induced are formed on the outer surface of the main valve 22. provided at irregular pitches P ₁ to the inner surface of the cylindrical guide sleeve 26 instead of being provided.

このため、加減弁２０Ｅでは、図７に示す加減弁２０Ｄと同様の効果を得ることができる。 For this reason, in the control valve 20E, the effect similar to the control valve 20D shown in FIG. 7 can be acquired.

尚、加減弁２０Ｂ、２０Ｃ、２０Ｄ、２０Ｅにおいて主弁２２あるいはガイドスリーブ２６の溝３２ａ近傍の形状は、主弁２２とガイドスリーブ２６との間の間隙部３１に流れ込んだ蒸気Ｘ１に圧力変動が誘起されにくい形状であれば、溝３２ａの幅、深さ、広がり角度、端部の面取りの有無および形状並びに溝３２ａの数およびピッチＰ_１、Ｐ_２は任意であり、かつ同一の主弁２２あるいはガイドスリーブ２６における各溝３２ａの形状が互いに異なるものであってもよい。 In addition, in the control valves 20B, 20C, 20D, and 20E, the shape of the main valve 22 or the guide sleeve 26 in the vicinity of the groove 32a is such that the pressure variation occurs in the steam X1 that flows into the gap 31 between the main valve 22 and the guide sleeve 26. If the shape is difficult to induce, the width, depth, spread angle, presence / absence of chamfering and shape of the groove 32, the number of grooves 32a and the pitches P ₁ and P ₂ are arbitrary, and the same main valve 22 is used. Or the shape of each groove | channel 32a in the guide sleeve 26 may mutually differ.

また、全ての溝３２ａあるいは各溝３２ａ間のピッチＰ_１、Ｐ_２を蒸気Ｘ１の流れに乱れが生じにくい横断面形状あるいはピッチＰ_２とする必要はなく、一部の溝３２ａあるいは各溝３２ａ間のピッチＰ_１、Ｐ_２を蒸気Ｘ１の流れに乱れが生じにくい形状あるいはピッチＰ_２としてもよい。 Further, it is not necessary that the pitches P ₁ and P ₂ between all the grooves 32a or the grooves 32a have a cross-sectional shape or a pitch P _{2 in} which the flow of the steam X1 is less likely to be disturbed. The pitches P ₁ and P ₂ between them may have a shape or pitch P _{2 in} which the flow of the steam X ₁ is not easily disturbed.

（実施例７）
図９は本発明に係る加減弁の第７の実施形態を示す断面構成図である。 (Example 7)
FIG. 9 is a cross-sectional configuration diagram showing a seventh embodiment of the adjusting valve according to the present invention.

図９に示された、加減弁２０Ｆでは、蒸気Ｘ１の流路に形成される溝３２ａの構成が図３に示す加減弁２０Ｂと相違する。他の構成および作用については図３に示す加減弁２０Ｂと実質的に異ならないため同一の構成については同符号を付して説明を省略する。 In the control valve 20F shown in FIG. 9, the configuration of the groove 32a formed in the flow path of the steam X1 is different from the control valve 20B shown in FIG. Since other configurations and operations are not substantially different from the control valve 20B shown in FIG. 3, the same components are denoted by the same reference numerals and description thereof is omitted.

加減弁２０Ｆでは、主弁２２とガイドスリーブ２６との間の間隙部３１に流れ込む蒸気Ｘ１の流量を低減させるために、蒸気Ｘ１の圧力変動が誘起されにくい断面形状の複数の溝３２ａが、主弁２２の外表面および筒状のガイドスリーブ２６の内表面の双方に不等ピッチＰ_１で設けられる。 In the control valve 20F, in order to reduce the flow rate of the steam X1 flowing into the gap portion 31 between the main valve 22 and the guide sleeve 26, a plurality of grooves 32a having a cross-sectional shape in which the pressure fluctuation of the steam X1 is difficult to be induced are formed. provided at irregular pitches P ₁ to both the outer surface and the inner surface of the cylindrical guide sleeve 26 of the valve 22.

ここで、主弁２２の外表面の溝３２ａとガイドスリーブ２６の内表面の溝２０とが互いに対向する数が、より少なくなる位置に溝３２ａおよび溝３２ａが設けられる。 Here, the grooves 32a and 32a are provided at positions where the number of the grooves 32a on the outer surface of the main valve 22 and the grooves 20 on the inner surface of the guide sleeve 26 face each other is smaller.

加減弁２０Ｆにおいて、主弁２２は弁座２３と接触して弁開度が全閉となる位置から最大の流量の蒸気Ｘが主弁２２と弁座２３との間を流れることができる弁開度が全開となる位置まで移動することができる。 In the control valve 20F, the main valve 22 is in contact with the valve seat 23 and is opened so that the steam X having the maximum flow rate can flow between the main valve 22 and the valve seat 23 from the position where the valve opening degree is fully closed. It can move to a position where the degree is fully open.

このため、主弁２２の外表面の溝３２ａとガイドスリーブ２６の内表面の溝３２ａとの相対的な位置関係は主弁２２の位置によって変化するが、主弁２２の移動範囲において、主弁２２を移動させた場合に主弁２２の外表面の溝３２ａとガイドスリーブ２６の内表面の溝３２ａとが互いに対向する箇所の数がより少なくなるように構成される。 For this reason, the relative positional relationship between the groove 32a on the outer surface of the main valve 22 and the groove 32a on the inner surface of the guide sleeve 26 varies depending on the position of the main valve 22. When moving 22, the number of the locations where the groove 32 a on the outer surface of the main valve 22 and the groove 32 a on the inner surface of the guide sleeve 26 face each other is reduced.

例えば、主弁２２を移動させた場合に、主弁２２の溝３２ａとガイドスリーブ２６の溝３２ａとが最大でも１箇所のみ対向し、他の各溝３２ａは互いに対向しないような位置とされる。 For example, when the main valve 22 is moved, the groove 32a of the main valve 22 and the groove 32a of the guide sleeve 26 are opposed to each other at only one place, and the other grooves 32a are not opposed to each other. .

ただし、主弁２２を移動させた場合に、主弁２２の溝３２ａとガイドスリーブ２６の溝３２ａとが対向する数は低減されるように構成されていれば複数箇所であってもよい。 However, when the main valve 22 is moved, a plurality of locations may be used as long as the number of the grooves 32a of the main valve 22 and the grooves 32a of the guide sleeve 26 facing each other is reduced.

このため、加減弁２０Ｆでは、主弁２２とガイドスリーブ２６との間の間隙部３１を流れる蒸気Ｘ１に、主弁２２の溝３２ａとガイドスリーブ２６の溝３２ａとが対向することによる圧力変動が誘起されるのを抑制することができる。 For this reason, in the control valve 20F, pressure fluctuation due to the groove 32a of the main valve 22 and the groove 32a of the guide sleeve 26 facing the steam X1 flowing through the gap 31 between the main valve 22 and the guide sleeve 26 is caused. Induction can be suppressed.

そして、主弁２２とガイドスリーブ２６との間の隙間に流れ込む蒸気Ｘ１の流量を低減させることができるとともに、流体自励音の発生をさらに抑制し、かつ流体自励音が生じても増幅されることを回避させて加減弁２０Ｆの振動および騒音を低減させることができる。 The flow rate of the steam X1 flowing into the gap between the main valve 22 and the guide sleeve 26 can be reduced, the generation of the fluid self-excited sound is further suppressed, and the fluid self-excited sound is amplified. Thus, vibration and noise of the adjusting valve 20F can be reduced.

尚、加減弁２０Ｆにおいて主弁２２およびガイドスリーブ２６の溝３２ａ近傍の形状は、溝３２ａの対向箇所数が低減される構成であれば、溝３２ａの幅、深さ、広がり角度、端部の面取りの有無および形状並びに溝３２ａの数およびピッチＰ_１は任意であり、かつ同一の主弁２２あるいはガイドスリーブ２６における各溝３２ａの形状が互いに異なるものであってもよい。 If the shape of the main valve 22 and the guide sleeve 26 in the vicinity of the groove 32a in the adjusting valve 20F is such that the number of opposed portions of the groove 32a is reduced, the width, depth, spread angle, and end of the groove 32a are reduced. the number and the pitch P ₁ of the presence or absence of chamfering and shape and the groove 32a is arbitrary, and may be one in which the shape of each groove 32a in the same main valve 22 or the guide sleeves 26 are different from each other.

（実施例８）
図１０は本発明に係る加減弁の第８の実施形態を示す断面構成図である。 (Example 8)
FIG. 10 is a cross-sectional configuration diagram showing an eighth embodiment of the adjustable valve according to the present invention.

図１０に示された、加減弁２０Ｇでは、ガイドスリーブ２６ａの形状および主弁２２の溝３２の構成が図１に示す加減弁２０と相違する。他の構成および作用については図１に示す加減弁２０と実質的に異ならないため同一の構成については同符号を付して説明を省略する。 In the control valve 20G shown in FIG. 10, the shape of the guide sleeve 26a and the configuration of the groove 32 of the main valve 22 are different from those of the control valve 20 shown in FIG. Since other configurations and operations are not substantially different from those of the adjusting valve 20 shown in FIG. 1, the same components are denoted by the same reference numerals and description thereof is omitted.

加減弁２０Ｇにおいて生じた騒音の周波数と加減弁２０Ｇに接続された配管３０の内径Ｄに依存する高次音響モードによる周波数とが一致すると共鳴現象によって、より大きな騒音ないし振動が発生する。 When the frequency of noise generated in the control valve 20G matches the frequency of the higher-order acoustic mode depending on the inner diameter D of the pipe 30 connected to the control valve 20G, more noise or vibration is generated due to the resonance phenomenon.

ここで、配管３０の高次音響モードの周波数ωは一般に式（２）で求められる。 Here, the frequency ω of the higher-order acoustic mode of the pipe 30 is generally obtained by Expression (2).

［数２］
ω＝Ｃａ{Ｕｍｎ^２／（Ｄ／２）^２＋ｋｚ^２}^{（１／２）} ……（２）
ただし、Ｃａは流体すなわち蒸気Ｘ、Ｘ１の音速、Ｄは配管３０の内径、Ｕｍｎはｎ次の第１種ベッセル関数のｍ番目の根、ｋｚは配管３０内の軸方向波数を示す。 [Equation 2]
ω = Ca {Umn ² / (D / 2) ² + kz ² } ^(1/2) (2)
Where Ca is the speed of sound of the fluid, that is, steam X and X1, D is the inner diameter of the pipe 30, Umn is the mth root of the first-order Bessel function of the nth order, and kz is the axial wave number in the pipe 30.

加減弁２０Ｇに騒音ないし振動が生じると、騒音および振動は加減弁２０Ｇのみならず加減弁２０Ｇに接続された配管３０および蒸気タービンに伝播して各機器の破損等の事故に繋がる恐れがある。 When noise or vibration is generated in the control valve 20G, the noise and vibration may propagate not only to the control valve 20G but also to the piping 30 and the steam turbine connected to the control valve 20G, leading to an accident such as damage to each device.

そこで加減弁２０Ｇでは、加減弁２０Ｇから生じる騒音の周波数が加減弁２０Ｇに接続された配管３０の内径Ｄによる高次音響モードの周波数と異なる周波数となって離調するように、ガイドスリーブ２６ａの固有振動数が調整されてガイドスリーブ２６ａの形状が形成される。すなわち、ガイドスリーブ２６ａの外周形状を調整して例えば壁厚の一部を増加させて剛性を増加させることにより、ガイドスリーブ２６ａの固有振動数が調整され、加減弁２０Ｇから生じる騒音の振動数が配管３０の高次音響モードの固有振動数から離調される。 Therefore, in the control valve 20G, the frequency of the noise generated from the control valve 20G is detuned so that the frequency of the guide sleeve 26a is different from the frequency of the higher acoustic mode due to the inner diameter D of the pipe 30 connected to the control valve 20G. The natural frequency is adjusted to form the shape of the guide sleeve 26a. That is, by adjusting the outer peripheral shape of the guide sleeve 26a to increase the rigidity by increasing a part of the wall thickness, for example, the natural frequency of the guide sleeve 26a is adjusted, and the frequency of noise generated from the adjusting valve 20G is adjusted. It is detuned from the natural frequency of the higher-order acoustic mode of the pipe 30.

一方、加減弁２０Ｇにおいて主弁２２の溝３２の幅、深さ、広がり角度、端部の面取りの有無および形状並びに溝３２の数およびピッチは任意であり、かつ同一の主弁２２における各溝３２の形状が互いに異なるものであってもよい。さらに、ガイドスリーブ２６ａに溝３２を設けてもよい。 On the other hand, in the adjusting valve 20G, the width, depth, spread angle, presence / absence of chamfering and shape of the end portion, and the number and pitch of the grooves 32 are arbitrary, and each groove in the same main valve 22 is provided. The shapes of 32 may be different from each other. Further, the groove 32 may be provided in the guide sleeve 26a.

加減弁２０Ｇにおいては、ガイドスリーブ２６ａの固有振動数が調整され、加減弁２０Ｇから生じる騒音の周波数が配管３０の高次音響モードの周波数から離調されるため、加減弁２０Ｇから騒音が生じても、騒音の周波数が配管３０の高次音響モードの周波数と異なる。このため、配管３０と騒音との共鳴現象に伴う騒音の増幅を回避させることが可能となり加減弁２０Ｇの振動および騒音を低減させることができる。 In the control valve 20G, the natural frequency of the guide sleeve 26a is adjusted, and the frequency of noise generated from the control valve 20G is detuned from the frequency of the higher-order acoustic mode of the pipe 30, so that noise is generated from the control valve 20G. However, the frequency of the noise is different from the frequency of the higher-order acoustic mode of the pipe 30. For this reason, it is possible to avoid amplification of noise due to the resonance phenomenon between the pipe 30 and noise, and vibration and noise of the adjusting valve 20G can be reduced.

そして、蒸気タービンに接続されて高温かつ高圧の蒸気Ｘの流量調整を行うような特に過酷な条件で加減弁２０Ｇが使用されても、機械強度上より高い信頼性を得ることができる。 And even if the regulating valve 20G is used under particularly severe conditions such that the flow rate of the high-temperature and high-pressure steam X is connected to the steam turbine, higher reliability in terms of mechanical strength can be obtained.

（実施例９）
図１１は本発明に係る加減弁の第９の実施形態を示す断面構成図である。 Example 9
FIG. 11 is a cross-sectional configuration diagram showing a ninth embodiment of an adjusting valve according to the present invention.

図１１に示された、加減弁２０Ｈでは、ガイドスリーブ２６ｂの形状が図１０に示す加減弁２０Ｇと相違する。他の構成および作用については図１０に示す加減弁２０Ｇと実質的に異ならないため同一の構成については同符号を付して説明を省略する。 In the control valve 20H shown in FIG. 11, the shape of the guide sleeve 26b is different from that of the control valve 20G shown in FIG. Since other configurations and operations are not substantially different from the control valve 20G shown in FIG. 10, the same components are denoted by the same reference numerals and description thereof is omitted.

加減弁２０Ｈでは、ガイドスリーブ２６の外周形状を調整して例えば壁厚の一部を薄くして剛性を減少させることにより、ガイドスリーブ２６ｂの固有振動数が調整され、加減弁２０Ｈから生じる騒音の周波数が配管３０の高次音響モードの周波数から離調される。 In the adjusting valve 20H, the natural frequency of the guide sleeve 26b is adjusted by adjusting the outer peripheral shape of the guide sleeve 26 to reduce the rigidity by, for example, reducing a part of the wall thickness, and the noise generated from the adjusting valve 20H is reduced. The frequency is detuned from the frequency of the higher order acoustic mode of the pipe 30.

このため、加減弁２０Ｈでは、加減弁２０Ｇと同様の効果を得ることができる。 For this reason, in the control valve 20H, the same effect as the control valve 20G can be acquired.

（実施例１０）
図１２は本発明に係る加減弁の第１０の実施形態を示す断面構成図である。 (Example 10)
FIG. 12 is a sectional view showing a tenth embodiment of the adjusting valve according to the present invention.

図１２に示された、加減弁２０Ｉでは、主弁２２ａの形状および主弁２２ａの溝３２の構成が図１に示す加減弁２０と相違する。他の構成および作用については図１に示す加減弁２０と実質的に異ならないため同一の構成については同符号を付して説明を省略する。 In the control valve 20I shown in FIG. 12, the shape of the main valve 22a and the configuration of the groove 32 of the main valve 22a are different from those of the control valve 20 shown in FIG. Since other configurations and operations are not substantially different from those of the adjusting valve 20 shown in FIG. 1, the same components are denoted by the same reference numerals and description thereof is omitted.

加減弁２０Ｉでは、主弁２２ａの外周形状を調整して例えば壁厚の一部を厚くして剛性を増加させることにより、主弁２２ａの固有振動数が調整され、加減弁２０Ｉから生じる騒音の周波数が配管３０の高次音響モードの周波数から離調される。 In the adjusting valve 20I, the natural frequency of the main valve 22a is adjusted by adjusting the outer peripheral shape of the main valve 22a to increase the rigidity by increasing a part of the wall thickness, for example. The frequency is detuned from the frequency of the higher order acoustic mode of the pipe 30.

一方、加減弁２０Ｉにおいて主弁２２ａの溝３２の幅、深さ、広がり角度、端部の面取りの有無および形状並びに溝３２の数およびピッチは任意であり、かつ同一の主弁２２ａにおける各溝３２の形状が互いに異なるものであってもよい。さらに、ガイドスリーブ２６ｂに溝３２を設けてもよい。 On the other hand, in the control valve 20I, the width, depth, spread angle, presence / absence and shape of the end portion of the groove 32, and the number and pitch of the grooves 32 are arbitrary, and each groove in the same main valve 22a. The shapes of 32 may be different from each other. Further, the groove 32 may be provided in the guide sleeve 26b.

このため、加減弁２０Ｉでは、加減弁２０Ｇと同様の効果を得ることができる。 For this reason, in the control valve 20I, the same effect as the control valve 20G can be acquired.

（実施例１１）
図１３は本発明に係る加減弁の第１１の実施形態を示す断面構成図である。 (Example 11)
FIG. 13 is a cross-sectional configuration diagram showing an eleventh embodiment of an adjustable valve according to the present invention.

図１３に示された、加減弁２０Ｊでは、主弁２２ｂの形状が図１２に示す加減弁２０Ｉと相違する。他の構成および作用については図１２に示す加減弁２０Ｉと実質的に異ならないため同一の構成については同符号を付して説明を省略する。 In the control valve 20J shown in FIG. 13, the shape of the main valve 22b is different from the control valve 20I shown in FIG. Since other configurations and operations are not substantially different from the control valve 20I shown in FIG. 12, the same components are denoted by the same reference numerals and description thereof is omitted.

加減弁２０Ｊでは、主弁２２ｂの外周形状を調整して例えば壁厚の一部を薄くして剛性を減少させることにより、主弁２２ｂの固有振動数が調整され、加減弁２０Ｊから生じる騒音の周波数が配管３０の高次音響モードの周波数から離調される。 In the adjusting valve 20J, the natural frequency of the main valve 22b is adjusted by adjusting the outer peripheral shape of the main valve 22b to reduce the rigidity by, for example, reducing a part of the wall thickness, thereby reducing the noise generated from the adjusting valve 20J. The frequency is detuned from the frequency of the higher order acoustic mode of the pipe 30.

このため、加減弁２０Ｊでは、加減弁２０Ｉと同様の効果を得ることができる。 For this reason, in the control valve 20J, the same effect as the control valve 20I can be acquired.

尚、加減弁２０Ｇ、２０Ｈ、２０Ｉ、２０Ｊにおいて、ガイドスリーブ２６ａ，２６ｂあるいは主弁２２ａ，２２ｂの固有振動数を調整するために、ガイドスリーブ２６ａ，２６ｂあるいは主弁２２ａ，２２ｂの形状を変更することにより調整したが、加減弁２０Ｇ、２０Ｈから生じる騒音の周波数を配管３０の高次音響モードの周波数から離調できれば、ガイドスリーブ２６ａ，２６ｂあるいは主弁２２ａ，２２ｂ単独のみならず加減弁２０Ｇ、２０Ｈを構成する加減弁構成部品のうち所要の加減弁構成部品の任意の部位の形状を変更することにより固有振動数を調整してもよい。 In the control valves 20G, 20H, 20I, and 20J, the shape of the guide sleeves 26a and 26b or the main valves 22a and 22b is changed in order to adjust the natural frequency of the guide sleeves 26a and 26b or the main valves 22a and 22b. However, if the frequency of noise generated from the control valves 20G and 20H can be detuned from the frequency of the higher acoustic mode of the pipe 30, not only the guide sleeves 26a and 26b or the main valves 22a and 22b but also the control valves 20G and 20G, The natural frequency may be adjusted by changing the shape of any part of the required regulating valve component among the regulating valve components constituting 20H.

また、ガイドスリーブ２６ａ，２６ｂあるいは主弁２２ａ，２２ｂやその他の加減弁２０Ｇ、２０Ｈを構成する部品の固有振動数を調整する場合において、形状を変更するのみならず剛性の異なる材質に変更するという方法により固有振動数を調整してもよい。 In addition, when adjusting the natural frequency of the parts constituting the guide sleeves 26a and 26b or the main valves 22a and 22b and the other regulating valves 20G and 20H, the shape is not only changed, but is changed to a material having a different rigidity. The natural frequency may be adjusted by a method.

（実施例１２）
図１４は本発明に係る加減弁の第１２の実施形態を示す断面構成図である。 Example 12
FIG. 14 is a sectional configuration diagram showing a twelfth embodiment of the adjusting valve according to the present invention.

図１４に示された、加減弁２０Ｋでは、主弁２２ｃの形状および主弁２２ｃの溝３２の構成が図１に示す加減弁２０と相違する。他の構成および作用については図１に示す加減弁２０と実質的に異ならないため同一の構成については同符号を付して説明を省略する。 In the control valve 20K shown in FIG. 14, the shape of the main valve 22c and the configuration of the groove 32 of the main valve 22c are different from those of the control valve 20 shown in FIG. Since other configurations and operations are not substantially different from those of the adjusting valve 20 shown in FIG. 1, the same components are denoted by the same reference numerals and description thereof is omitted.

加減弁２０Ｋにおいて筒状の主弁２２ｃは筒状のガイドスリーブ２６で覆われるため、主弁２２ｃとガイドスリーブ２６の二重管状部分から環状の間隙部３１ａが形成される。このため、加減弁２０Ｋには、主弁２２とガイドスリーブ２６とで形成される環状の間隙部３１ａの長さｂ_１に応じた周波数の気柱共鳴が生じる。 In the control valve 20K, the cylindrical main valve 22c is covered with the cylindrical guide sleeve 26, so that an annular gap 31a is formed from the double tubular portion of the main valve 22c and the guide sleeve 26. Therefore, the control valve 20K, columnar resonance frequency occurs in accordance with the length b ₁ of the annular gap 31a formed between the main valve 22 and the guide sleeve 26.

そこで、加減弁２０Ｋでは主弁２２ｃの長さが調整される。そして、主弁２２ｃとガイドスリーブ２６とで形成される環状の間隙部３１ａの長さｂ_１を調整することにより、主弁２２ｃとガイドスリーブ２６とで形成される環状の間隙部３１ａで生じる気柱共鳴の振動数が、加減弁２０Ｋに接続される配管３０の高次音響モードの固有振動数と異なる振動数となるように離調される。 Therefore, the length of the main valve 22c is adjusted in the adjusting valve 20K. Then, by adjusting the length b ₁ of the annular gap 31a formed between the main valve 22c and the guide sleeve 26, feel caused by annular gap 31a formed between the main valve 22c and the guide sleeve 26 The frequency of the column resonance is detuned so as to be different from the natural frequency of the higher-order acoustic mode of the pipe 30 connected to the adjusting valve 20K.

一方、加減弁２０Ｋにおいて主弁２２ｃの溝３２の幅、深さ、広がり角度、端部の面取りの有無および形状並びに溝３２の数およびピッチは任意であり、かつ同一の主弁２２ｃにおける各溝３２の形状が互いに異なるものであってもよい。さらに、ガイドスリーブ２６に溝３２を設けてもよい。 On the other hand, in the control valve 20K, the width, depth, spread angle, presence / absence of chamfering and shape of the end portion, and the number and pitch of the grooves 32 are arbitrary, and each groove in the same main valve 22c. The shapes of 32 may be different from each other. Further, the guide sleeve 26 may be provided with a groove 32.

加減弁２０Ｋでは、主弁２２ｃとガイドスリーブ２６とで形成される環状の間隙部３１ａにおいて気柱共鳴が生じても、生じた気柱共鳴の周波数が配管３０の高次音響モードの周波数から離調されるため、加減弁２０Ｋの振動および騒音が配管３０との共鳴現象により増幅されるのを抑制することができる。このため、加減弁２０Ｋの振動および騒音を低減させることができる。 In the control valve 20K, even if air column resonance occurs in the annular gap portion 31a formed by the main valve 22c and the guide sleeve 26, the frequency of the generated air column resonance is separated from the frequency of the higher-order acoustic mode of the pipe 30. Therefore, the vibration and noise of the adjusting valve 20K can be suppressed from being amplified by the resonance phenomenon with the pipe 30. For this reason, the vibration and noise of the adjusting valve 20K can be reduced.

（実施例１３）
図１５は本発明に係る加減弁の第１３の実施形態を示す断面構成図である。 (Example 13)
FIG. 15 is a cross-sectional view showing a thirteenth embodiment of the adjusting valve according to the present invention.

図１５に示された、加減弁２０Ｌでは、主弁２２ｄの形状が図１４に示す加減弁２０Ｋと相違する。他の構成および作用については図１４に示す加減弁２０Ｋと実質的に異ならないため同一の構成については同符号を付して説明を省略する。 In the control valve 20L shown in FIG. 15, the shape of the main valve 22d is different from the control valve 20K shown in FIG. Since other configurations and operations are not substantially different from the control valve 20K shown in FIG. 14, the same components are denoted by the same reference numerals and description thereof is omitted.

加減弁２０Ｌでは、筒状の主弁２２ｄの外表面の任意の部位、例えば端部に溝あるいは段差を設けることにより、主弁２２ｄとガイドスリーブ２６とで形成される環状の間隙部３１ａの長さｂ_１が調整される。そして、主弁２２ｄとガイドスリーブ２６とで形成される環状の間隙部３１ａで生じる気柱共鳴の周波数が、加減弁２０Ｌに接続される配管３０の高次音響モードの周波数と異なる周波数となるように離調される。 In the adjusting valve 20L, a groove or a step is provided at an arbitrary portion on the outer surface of the cylindrical main valve 22d, for example, at the end, thereby increasing the length of the annular gap portion 31a formed by the main valve 22d and the guide sleeve 26. and _{b 1} is adjusted. The frequency of air column resonance generated in the annular gap portion 31a formed by the main valve 22d and the guide sleeve 26 is different from the frequency of the higher-order acoustic mode of the pipe 30 connected to the control valve 20L. Is detuned.

このため、加減弁２０Ｌでは、加減弁２０Ｋと同様な効果を得ることができる。 For this reason, in the control valve 20L, the same effect as the control valve 20K can be acquired.

（実施例１４）
図１６は本発明に係る加減弁の第１４の実施形態を示す断面構成図である。 (Example 14)
FIG. 16 is a cross-sectional configuration diagram showing a fourteenth embodiment of an adjusting valve according to the present invention.

図１６に示された、加減弁２０Ｍでは、ガイドスリーブ２６ｃの形状および主弁２２の溝３２の構成が図１に示す加減弁２０と相違する。他の構成および作用については図１に示す加減弁２０と実質的に異ならないため同一の構成については同符号を付して説明を省略する。 In the control valve 20M shown in FIG. 16, the shape of the guide sleeve 26c and the configuration of the groove 32 of the main valve 22 are different from those of the control valve 20 shown in FIG. Since other configurations and operations are not substantially different from those of the adjusting valve 20 shown in FIG. 1, the same components are denoted by the same reference numerals and description thereof is omitted.

加減弁２０Ｍでは、筒状のガイドスリーブ２６ｃの内表面のうち、主弁２２のガイドスリーブ２６ｃ側の端部側の所要の部位に溝あるいは段差を設けることにより、主弁２２とガイドスリーブ２６ｃとで形成される環状の間隙部３１ａの長さｂ_１が調整される。そして、主弁２２とガイドスリーブ２６ｃとで形成される環状の間隙部３１ａで生じる気柱共鳴の周波数が、加減弁２０Ｍに接続される配管３０の高次音響モードの周波数と異なる周波数となるように離調される。 In the control valve 20M, a groove or a step is provided in a required portion of the inner surface of the cylindrical guide sleeve 26c on the end side of the main valve 22 on the guide sleeve 26c side, whereby the main valve 22 and the guide sleeve 26c length b ₁ of the annular gap portion 31a is adjusted tHAT formed. The frequency of air column resonance generated in the annular gap portion 31a formed by the main valve 22 and the guide sleeve 26c is different from the frequency of the higher-order acoustic mode of the pipe 30 connected to the adjusting valve 20M. Is detuned.

一方、加減弁２０Ｍにおいて主弁２２の溝３２の幅、深さ、広がり角度、端部の面取りの有無および形状並びに溝３２の数およびピッチは任意であり、かつ同一の主弁２２における各溝３２の形状が互いに異なるものであってもよい。さらに、ガイドスリーブ２６ｃに溝３２を設けてもよい。 On the other hand, in the adjusting valve 20M, the width, depth, spread angle, presence / absence of chamfering and shape of the end portion, and the number and pitch of the grooves 32 are arbitrary, and each groove in the same main valve 22 is provided. The shapes of 32 may be different from each other. Further, the groove 32 may be provided in the guide sleeve 26c.

このため、加減弁２０Ｍでは、加減弁２０Ｋと同様な効果を得ることができる。 For this reason, in the control valve 20M, the same effect as the control valve 20K can be acquired.

（実施例１５）
図１７は本発明に係る加減弁の第１５の実施形態を示す断面構成図である。 (Example 15)
FIG. 17 is a sectional view showing the fifteenth embodiment of the adjusting valve according to the present invention.

図１７に示された、加減弁２０Ｎでは、ガイドスリーブ２６ｄの形状が図１６に示す加減弁２０Ｍと相違する。他の構成および作用については図１６に示す加減弁２０Ｍと実質的に異ならないため同一の構成については同符号を付して説明を省略する。 In the control valve 20N shown in FIG. 17, the shape of the guide sleeve 26d is different from that of the control valve 20M shown in FIG. Since other configurations and operations are not substantially different from the control valve 20M shown in FIG. 16, the same components are denoted by the same reference numerals and description thereof is omitted.

加減弁２０Ｎでは、筒状のガイドスリーブ２６ｄの内表面のうち、主弁２２側の端部における所要の部位に溝あるいは段差を設けることにより、主弁２２とガイドスリーブ２６ｄとで形成される環状の間隙部３１ａの長さｂ_１が調整される。そして、主弁２２とガイドスリーブ２６ｄとで形成される環状の間隙部３１ａで生じる気柱共鳴の周波数が、加減弁２０Ｎに接続される配管３０の高次音響モードの周波数と異なる周波数となるように離調される。 In the adjusting valve 20N, a groove or a step is provided in a required portion at the end on the main valve 22 side of the inner surface of the cylindrical guide sleeve 26d, thereby forming an annular shape formed by the main valve 22 and the guide sleeve 26d. length _{b 1} of the gap 31a is adjusted. The frequency of the air column resonance generated in the annular gap 31a formed by the main valve 22 and the guide sleeve 26d is different from the frequency of the higher acoustic mode of the pipe 30 connected to the adjusting valve 20N. Is detuned.

このため、加減弁２０Ｎでは、加減弁２０Ｋと同様な効果を得ることができる。 For this reason, in the control valve 20N, the effect similar to the control valve 20K can be acquired.

（実施例１６）
図１８は本発明に係る加減弁の第１６の実施形態を示す断面構成図である。 (Example 16)
FIG. 18 is a sectional view showing the sixteenth embodiment of the adjustable valve according to the present invention.

図１８に示された、加減弁２０Ｏでは、スリーブ２５ａの形状および主弁２２の溝３２の構成が図１に示す加減弁２０と相違する。他の構成および作用については図１に示す加減弁２０と実質的に異ならないため同一の構成については同符号を付して説明を省略する。 In the control valve 20O shown in FIG. 18, the shape of the sleeve 25a and the configuration of the groove 32 of the main valve 22 are different from those of the control valve 20 shown in FIG. Since other configurations and operations are not substantially different from those of the adjusting valve 20 shown in FIG. 1, the same components are denoted by the same reference numerals and description thereof is omitted.

加減弁２０Ｏにおいて、棒状の弁棒２１は筒状のスリーブ２５ａで覆われるため、弁棒２１とスリーブ２５ａとの間に環状の間隙部３１ｂが形成される。このため、加減弁２０Ｏには、弁棒２１とスリーブ２５ａとで形成される環状の間隙部３１の長さｂ_２に応じた周波数の気柱共鳴が生じる。 In the control valve 20O, the rod-shaped valve rod 21 is covered with a cylindrical sleeve 25a, and thus an annular gap portion 31b is formed between the valve rod 21 and the sleeve 25a. Therefore, the control valve 20O, columnar resonance frequency occurs in accordance with the length b ₂ of the annular gap 31 formed between valve stem 21 and the sleeve 25a.

そこで、加減弁２０Ｏでは、スリーブ２５ａの主弁２２側端部の内表面における所要の部位に溝あるいは段差を設けることにより、弁棒２１とスリーブ２５ａとで形成される環状の間隙部３１ｂの長さｂ_２が調整される。そして、弁棒２１とスリーブ２５ａとで形成される環状の間隙部３１ｂで生じる気柱共鳴の周波数が、加減弁２０Ｏに接続される配管３０の高次音響モードの周波数と異なる周波数となるように離調される。 Therefore, in the control valve 20O, by providing a groove or a step at a required portion on the inner surface of the end portion on the main valve 22 side of the sleeve 25a, the length of the annular gap portion 31b formed by the valve stem 21 and the sleeve 25a is increased. The length _b2 is adjusted. The frequency of air column resonance generated in the annular gap 31b formed by the valve stem 21 and the sleeve 25a is different from the frequency of the higher-order acoustic mode of the pipe 30 connected to the control valve 20O. Detuned.

一方、加減弁２０Ｏにおいて主弁２２の溝３２の幅、深さ、広がり角度、端部の面取りの有無および形状並びに溝３２の数およびピッチは任意であり、かつ同一の主弁２２における各溝３２の形状が互いに異なるものであってもよい。さらに、ガイドスリーブ２６に溝３２を設けてもよい。 On the other hand, in the control valve 20O, the width, depth, spread angle, presence / absence and shape of the end portion of the groove 32, and the number and pitch of the grooves 32 are arbitrary, and each groove in the same main valve 22 is provided. The shapes of 32 may be different from each other. Further, the guide sleeve 26 may be provided with a groove 32.

加減弁２０Ｏでは、弁棒２１とスリーブ２５ａとで形成される環状の間隙部３１ｂにおいて気柱共鳴が生じても、生じた気柱共鳴の周波数が配管３０の高次音響モードの周波数から離調されるため、加減弁２０Ｏの振動および騒音が配管３０との共鳴現象により増幅されるのを抑制することができる。このため、加減弁２０Ｏの振動および騒音を低減させることができる。 In the control valve 20O, even if air column resonance occurs in the annular gap 31b formed by the valve stem 21 and the sleeve 25a, the frequency of the generated air column resonance is detuned from the frequency of the higher-order acoustic mode of the pipe 30. Therefore, the vibration and noise of the adjusting valve 20O can be suppressed from being amplified by the resonance phenomenon with the pipe 30. For this reason, the vibration and noise of the adjusting valve 20O can be reduced.

（実施例１７）
図１９は本発明に係る加減弁の第１７の実施形態を示す断面構成図である。 (Example 17)
FIG. 19 is a cross-sectional view showing a seventeenth embodiment of the adjusting valve according to the present invention.

図１９に示された、加減弁２０Ｐでは、スリーブ２５ｂの形状が図１８に示す加減弁２０Ｏと相違する。他の構成および作用については図１８に示す加減弁２０Ｏと実質的に異ならないため同一の構成については同符号を付して説明を省略する。 In the control valve 20P shown in FIG. 19, the shape of the sleeve 25b is different from that of the control valve 20O shown in FIG. Since other configurations and operations are not substantially different from the control valve 20O shown in FIG. 18, the same components are denoted by the same reference numerals and description thereof is omitted.

加減弁２０Ｐでは、スリーブ２５ｂの内表面における所要の部位に単一ないし複数の溝あるいは段差を設けることにより、弁棒２１とスリーブ２５ｂとで形成される環状の間隙部３１ｂが分割されてその長さｂ_３、ｂ_４が調整される。そして、弁棒２１とスリーブ２５ｂとで形成される環状の間隙部３１ｂで生じる気柱共鳴の周波数が、加減弁２０Ｐに接続される配管３０の高次音響モードの周波数と異なる周波数となるように離調される。 In the control valve 20P, by providing a single or a plurality of grooves or steps at a required portion on the inner surface of the sleeve 25b, the annular gap 31b formed by the valve stem 21 and the sleeve 25b is divided and its length is increased. is _b 3, _{b 4} is adjusted. The frequency of the air column resonance generated in the annular gap 31b formed by the valve stem 21 and the sleeve 25b is different from the frequency of the higher-order acoustic mode of the pipe 30 connected to the control valve 20P. Detuned.

このため、加減弁２０Ｐでは、加減弁２０Ｏと同様な効果を得ることができる。 For this reason, in the control valve 20P, the effect similar to the control valve 20O can be acquired.

（実施例１８）
図２０は本発明に係る加減弁の第１８の実施形態を示す断面構成図である。 (Example 18)
FIG. 20 is a sectional configuration diagram showing an eighteenth embodiment of the adjusting valve according to the present invention.

図２０に示された、加減弁２０Ｑでは、スリーブ２５ｃの形状が図１８に示す加減弁２０Ｏと相違する。他の構成および作用については図１８に示す加減弁２０Ｏと実質的に異ならないため同一の構成については同符号を付して説明を省略する。 In the control valve 20Q shown in FIG. 20, the shape of the sleeve 25c is different from that of the control valve 20O shown in FIG. Since other configurations and operations are not substantially different from the control valve 20O shown in FIG. 18, the same components are denoted by the same reference numerals and description thereof is omitted.

加減弁２０Ｑでは、スリーブ２５ｃの主弁２２と逆側端部の内表面における所要の部位に溝あるいは段差を設けることにより、弁棒２１とスリーブ２５ｃとで形成される環状の間隙部３１ｂの長さｂ_２が調整される。そして、弁棒２１とスリーブ２５ｃとで形成される環状の間隙部３１ｂで生じる気柱共鳴の周波数が、加減弁２０Ｑに接続される配管３０の高次音響モードの周波数と異なる周波数となるように離調される。 In the adjusting valve 20Q, a groove or a step is provided in a required portion on the inner surface of the sleeve 25c on the opposite side end portion from the main valve 22, so that the length of the annular gap portion 31b formed by the valve stem 21 and the sleeve 25c is increased. The length _b2 is adjusted. The frequency of the air column resonance generated in the annular gap 31b formed by the valve stem 21 and the sleeve 25c is different from the frequency of the higher order acoustic mode of the pipe 30 connected to the control valve 20Q. Detuned.

このため、加減弁２０Ｑでは、加減弁２０Ｏと同様な効果を得ることができる。 For this reason, in the control valve 20Q, the same effect as the control valve 20O can be acquired.

加減弁２０Ｋ，２０Ｌ，２０Ｍ，２０Ｎ，２０Ｏ，２０Ｐ，２０Ｑにおいては、主弁２２，２２ａ，２２ｂ，２２ｃ，２２ｄとガイドスリーブ２６，２６ａ，２６ｂ，２６ｃ，２６ｄあるいは弁棒２１とスリーブ２５ａ，２５ｂ，２５ｃにより形成される二重管状部位の環状の間隙部３１ａ，３１ｂの長さｂ_１、ｂ_２、ｂ_３、ｂ_４を調節したが、その他の加減弁構成部品で二重管状に形成される部分の環状の間隙部の長さを調節し、環状の間隙部で生じる気柱共鳴の周波数が、加減弁２０Ｋ，２０Ｌ，２０Ｍ，２０Ｎ，２０Ｏ，２０Ｐ，２０Ｑに接続される配管３０の高次音響モードの周波数と異なる周波数となるように離調してもよい。 In the control valves 20K, 20L, 20M, 20N, 20O, 20P, 20Q, the main valves 22, 22a, 22b, 22c, 22d and the guide sleeves 26, 26a, 26b, 26c, 26d or the valve rods 21 and the sleeves 25a, 25b 25c, the lengths b ₁ , b ₂ , b ₃ , b ₄ of the annular gaps 31a, 31b of the double tubular portion formed by the two tubular portions are adjusted. The length of the annular gap portion of the pipe 30 connected to the control valves 20K, 20L, 20M, 20N, 20O, 20P, and 20Q is adjusted so that the frequency of the air column resonance generated in the annular gap portion is high. You may detune so that it may become a frequency different from the frequency of the next acoustic mode.

尚、各実施形態における加減弁２０，２０Ａ，２０Ｂ，２０Ｃ，２０Ｄ，２０Ｅ，２０Ｆ，２０Ｇ，２０Ｈ，２０Ｉ，２０Ｊ，２０Ｋ，２０Ｌ，２０Ｍ，２０Ｎ，２０Ｏ，２０Ｐ，２０Ｑを複合的に組み合わせて構成してもよい。 The control valves 20, 20A, 20B, 20C, 20D, 20E, 20F, 20G, 20H, 20I, 20J, 20K, 20L, 20M, 20N, 20O, 20P, and 20Q are combined and combined in each embodiment. May be.

また、主弁２２ないしガイドスリーブ２６の溝３２は蒸気Ｘ１が流れる方向に対して正確に垂直に設けられる必要はなく、適切に蒸気Ｘ１の流れに乱れを生じさせて流量を低減させることができれば向きは任意であり、かつ各溝３２は必ずしも平行である必要はない。 Further, the groove 32 of the main valve 22 or the guide sleeve 26 does not need to be provided exactly perpendicularly to the direction in which the steam X1 flows, and if the flow rate can be reduced by appropriately disturbing the flow of the steam X1. The orientation is arbitrary, and the grooves 32 do not necessarily have to be parallel.

さらに、溝３２は、主弁４とガイドスリーブ２６との間、主弁４ないし弁棒２１とスリーブ２５の間の間隙部３１に面していれば、主弁２２やガイドスリーブ２６に限らず弁棒２１あるいはスリーブ２５に設けても良い。 Further, the groove 32 is not limited to the main valve 22 and the guide sleeve 26 as long as it faces the gap 31 between the main valve 4 and the guide sleeve 26 and between the main valve 4 or the valve stem 21 and the sleeve 25. It may be provided on the valve stem 21 or the sleeve 25.

また、ガイドスリーブ２６は弁ケーシング２４に直接固定せずに、他の加減弁構成部品に固定してもよい。 Further, the guide sleeve 26 may be fixed not to the valve casing 24 directly but to other adjustable valve components.

本発明に係る加減弁の第１の実施形態を示す断面構成図。The cross-sectional block diagram which shows 1st Embodiment of the adjustment valve which concerns on this invention. 本発明に係る加減弁の第２の実施形態を示す断面構成図。The cross-sectional block diagram which shows 2nd Embodiment of the adjustment valve which concerns on this invention. 本発明に係る加減弁の第３の実施形態を示す断面構成図。Sectional block diagram which shows 3rd Embodiment of the adjustment valve which concerns on this invention. 図３に示す主弁の溝傍の一例を示す拡大断面図。The expanded sectional view which shows an example of the groove side of the main valve shown in FIG. 図３に示す主弁の溝近傍の別の例を示す拡大断面図。The expanded sectional view which shows another example of the groove vicinity of the main valve shown in FIG. 本発明に係る加減弁の第４の実施形態を示す断面構成図。Sectional block diagram which shows 4th Embodiment of the adjustment valve which concerns on this invention. 本発明に係る加減弁の第５の実施形態を示す断面構成図。Sectional block diagram which shows 5th Embodiment of the adjustment valve which concerns on this invention. 本発明に係る加減弁の第６の実施形態を示す断面構成図。Sectional block diagram which shows 6th Embodiment of the adjustment valve which concerns on this invention. 本発明に係る加減弁の第７の実施形態を示す断面構成図。Sectional block diagram which shows 7th Embodiment of the adjustment valve which concerns on this invention. 本発明に係る加減弁の第８の実施形態を示す断面構成図。Sectional block diagram which shows 8th Embodiment of the adjustment valve which concerns on this invention. 本発明に係る加減弁の第９の実施形態を示す断面構成図。Sectional block diagram which shows 9th Embodiment of the adjustment valve which concerns on this invention. 本発明に係る加減弁の第１０の実施形態を示す断面構成図。Sectional block diagram which shows 10th Embodiment of the adjustment valve which concerns on this invention. 本発明に係る加減弁の第１１の実施形態を示す断面構成図。Sectional block diagram which shows 11th Embodiment of the adjustment valve which concerns on this invention. 本発明に係る加減弁の第１２の実施形態を示す断面構成図。The cross-sectional block diagram which shows 12th Embodiment of the adjustment valve which concerns on this invention. 本発明に係る加減弁の第１３の実施形態を示す断面構成図。Sectional block diagram which shows 13th Embodiment of the adjustment valve which concerns on this invention. 本発明に係る加減弁の第１４の実施形態を示す断面構成図。Sectional block diagram which shows 14th Embodiment of the adjustment valve which concerns on this invention. 本発明に係る加減弁の第１５の実施形態を示す断面構成図。Sectional block diagram which shows 15th Embodiment of the adjustment valve which concerns on this invention. 本発明に係る加減弁の第１６の実施形態を示す断面構成図。The cross-sectional block diagram which shows 16th Embodiment of the adjustment valve which concerns on this invention. 本発明に係る加減弁の第１７の実施形態を示す断面構成図。The cross-sectional block diagram which shows 17th Embodiment of the adjustment valve which concerns on this invention. 本発明に係る加減弁の第１８の実施形態を示す断面構成図。Sectional block diagram which shows 18th Embodiment of the adjustment valve which concerns on this invention. 従来の加減弁の構成を示す断面図。Sectional drawing which shows the structure of the conventional regulating valve.

Explanation of symbols

２０，２０Ａ，２０Ｂ，２０Ｃ，２０Ｄ，２０Ｅ，２０Ｆ，２０Ｇ，２０Ｈ，２０Ｉ，２０Ｊ，２０Ｋ，２０Ｌ，２０Ｍ，２０Ｎ，２０Ｏ，２０Ｐ，２０Ｑ加減弁
２１弁棒
２２，２２ａ，２２ｂ，２２ｃ，２２ｄ主弁
２３弁座
２４弁ケーシング
２５，２５ａ，２５ｂ，２５ｃスリーブ
２６，２６ａ，２６ｂ，２６ｃ，２６ｄガイドスリーブ
２７テーパ状孔
２８座面
２９流路
３０配管
３１，３１ａ，３１ｂ間隙部
３２，３２ａ溝
Ｘ、Ｘ１蒸気 20, 20A, 20B, 20C, 20D, 20E, 20F, 20G, 20H, 20I, 20J, 20K, 20L, 20M, 20N, 20O, 20P, 20Q Adjustable Valve 21 Valve Rod 22, 22a, 22b, 22c, 22d Main Valve 23 Valve seat 24 Valve casing 25, 25a, 25b, 25c Sleeve 26, 26a, 26b, 26c, 26d Guide sleeve 27 Tapered hole 28 Seat surface 29 Channel 30 Piping 31, 31a, 31b Gap 32, 32a Groove X , X1 steam

Claims

A valve seat provided on the fluid flow path, a main valve provided with a gap between the valve seat and the fluid flow path, and a valve opening, which is the amount of the gap, adjustable. A valve rod that fixes the valve, a sleeve that protects the valve rod, and a guide sleeve that protects the main valve, of the gap formed by the gap between the main valve, the guide sleeve, the valve rod, and the sleeve A regulating valve characterized in that a plurality of grooves are provided at unequal pitches at a portion facing the gap portion of the guide sleeve.

A valve seat provided on the fluid flow path, a main valve provided with a gap between the valve seat and the fluid flow path, the valve opening being the amount of the gap being adjustable, and the main valve A valve rod that fixes the valve, a sleeve that protects the valve rod, and a guide sleeve that protects the main valve, and a required gap portion formed by a gap between the main valve, the guide sleeve, the valve rod, and the sleeve And a groove having a cross-sectional shape in which pressure fluctuation is not easily induced in the fluid flowing into the gap.

3. The adjustable valve according to claim 2 , wherein the groove is provided in a portion of the main valve facing the gap.

The adjusting valve according to claim 2 , wherein the groove is provided in a portion of the guide sleeve facing the gap.

3. The adjustable valve according to claim 1, wherein the groove is provided in a portion of the main valve and the guide sleeve facing the gap portion. 4.

The groove is provided in a portion facing the gap portion of both the main valve and the guide sleeve, and the pitch of the groove is such that the groove of the main valve and the groove of the guide sleeve face each other. 3. The adjusting valve according to claim 1, wherein the pitch is reduced.

A higher order that is constituted by a plurality of regulating valve components provided on a fluid flow path formed by piping, and that the natural frequency of a required regulating valve component among the regulating valve components depends on the inner diameter of the piping. An adjustable valve characterized by being detuned from the natural frequency of the acoustic mode.

The regulating valve component is provided such that a valve seat provided on a fluid flow path and a gap between the valve seat and the valve seat form the fluid flow path, and the valve opening that is the amount of the gap can be adjusted. A main valve, a valve stem that fixes the main valve, a sleeve that protects the valve stem, and a guide sleeve that protects the main valve, and the natural frequency of the guide sleeve is increased by the inner diameter of the pipe. The adjusting valve according to claim 7, wherein the adjusting valve is detuned from the natural frequency of the next acoustic mode.

The regulating valve component is provided such that a valve seat provided on a fluid flow path and a gap between the valve seat and the valve seat form the fluid flow path, and the valve opening that is the amount of the gap can be adjusted. A main valve, a valve stem that fixes the main valve, a sleeve that protects the valve stem, and a guide sleeve that protects the main valve, and the natural frequency of the main valve is increased by the inner diameter of the pipe. The adjusting valve according to claim 7, wherein the adjusting valve is detuned from the natural frequency of the next acoustic mode.

The regulating valve component includes a regulating valve component configured in a double tubular shape to form an annular gap, and an air column generated in the annular gap by adjusting the length of the annular gap. 8. The adjusting valve according to claim 7, wherein the natural frequency of vibration is detuned from the natural frequency of a higher-order acoustic mode due to the inner diameter of the pipe.

The regulating valve component is provided such that a valve seat provided on a fluid flow path and a gap between the valve seat and the valve seat form the fluid flow path, and the valve opening that is the amount of the gap can be adjusted. A main valve, a valve stem that fixes the main valve, a sleeve that protects the valve stem, and a guide sleeve that protects the main valve, and are formed by the main valve and the guide sleeve. 8. The adjusting valve according to claim 7, wherein the natural frequency of the air column vibration generated in the annular gap portion of the tubular portion is detuned from the natural frequency of the higher order acoustic mode due to the inner diameter of the pipe.

The regulating valve component is provided such that a valve seat provided on a fluid flow path and a gap between the valve seat and the valve seat form the fluid flow path, and the valve opening that is the amount of the gap can be adjusted. A main tube, a valve stem for fixing the main valve, a sleeve for protecting the valve stem, and a guide sleeve for protecting the main valve, and formed by the valve stem and the sleeve. 8. The adjusting valve according to claim 7, wherein the natural frequency of the air column vibration generated in the annular gap of the portion is detuned from the natural frequency of the higher order acoustic mode due to the inner diameter of the pipe.