WO2016067995A1 - 主蒸気弁、及び蒸気タービン - Google Patents
主蒸気弁、及び蒸気タービン Download PDFInfo
- Publication number
- WO2016067995A1 WO2016067995A1 PCT/JP2015/079697 JP2015079697W WO2016067995A1 WO 2016067995 A1 WO2016067995 A1 WO 2016067995A1 JP 2015079697 W JP2015079697 W JP 2015079697W WO 2016067995 A1 WO2016067995 A1 WO 2016067995A1
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- WO
- WIPO (PCT)
- Prior art keywords
- plate portion
- axis
- main steam
- fluid
- valve
- Prior art date
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Classifications
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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
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/08—Cooling; Heating; Heat-insulation
- F01D25/10—Heating, e.g. warming-up before starting
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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
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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
- F01D17/02—Arrangement of sensing elements
- F01D17/08—Arrangement of sensing elements responsive to condition of working-fluid, e.g. pressure
- F01D17/085—Arrangement of sensing elements responsive to condition of working-fluid, e.g. pressure to temperature
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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
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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
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
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- 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
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- 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
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- 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
- F16K1/54—Arrangements for modifying the way in which the rate of flow varies during the actuation of the valve
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- 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
- F16K47/00—Means in valves for absorbing fluid energy
- F16K47/08—Means in valves for absorbing fluid energy for decreasing pressure or noise level and having a throttling member separate from the closure member, e.g. screens, slots, labyrinths
Definitions
- the present invention relates to a main steam valve provided in a steam line such as a steam turbine, and a steam turbine.
- a steam line such as a steam turbine
- a steam turbine a steam turbine
- a steam line such as a steam turbine provided in a power generation facility or the like is provided with a main steam valve that adjusts the flow rate of the fluid (steam) to be supplied and stops the supply of the fluid.
- the main steam valve includes a casing in which a fluid flow path is formed, and a valve body that is movably provided along an axis in the flow path.
- a valve seat that can be closed by a valve body is formed in the flow path inside the casing. The valve body moves toward the first side in the axial direction to approach the valve seat, and the valve body moves away from the valve seat by moving to the second side in the axial direction. Thereby, the flow area of the gap between the valve body and the valve seat is changed to adjust the fluid flow rate.
- Patent Document 1 discloses a main steam valve further provided with a strainer housed in a casing and a shielding plate provided on a side surface of the strainer. On the outer peripheral surface of the strainer, a plurality of fine through holes for allowing fluid to pass are provided.
- the fluid flowing in from the main steam inlet flows along the outer peripheral surface of the strainer, and also flows from the outside to the inside of the strainer through the through hole.
- the fluid which flowed into the inside of a strainer flows toward the main steam outlet opened in the direction which cross
- a secondary flow is generated by flowing the fluid so as to bend at an acute angle, and a swirling vortex is generated by another fluid flowing into the velocity deficient portion of the secondary flow.
- the flow of the fluid in a strainer is controlled and the generation
- a swirl vortex may be generated near the outer peripheral surface of the valve body that is not provided with a shielding plate.
- the swirl vortex is generated in the flow path as described above, the kinetic energy of the fluid is lost, and the pressure loss in the main steam valve may increase. As a result, the efficiency of the steam turbine or the like to which the fluid is supplied is reduced.
- the present invention has been made in view of such a problem, and provides a main steam valve and a steam turbine that suppress an increase in pressure loss by weakening a swirl vortex generated in a flow path. .
- the main steam valve includes a cylindrical guide extending about the axis, a valve body slidably disposed in the axial direction inside the guide, and the valve body.
- a valve shaft that moves in the axial direction between the open position and the closed position, and a flow path that leads out the fluid introduced from the inflow direction along the axial direction in the outflow direction that intersects the inflow direction, are formed.
- a casing in which a valve seat with which the valve body in the closed position abuts is formed on the inner surface, and a valve chamber formed inside the casing.
- a baffle plate is provided in a region between the outer peripheral surface of the guide and the inner surface of the casing to divide a swirling vortex swirling around a swiveling axis extending in the circumferential direction of the axis of the guide.
- the swirling vortex generated in the flow path is divided by the baffle plate.
- the baffle plate can suppress that a swirl
- the loss of the kinetic energy of the fluid by a swirling vortex can be reduced, and the increase in pressure loss can be suppressed.
- the baffle plate is provided between the outer peripheral surface of the guide and the inner surface of the casing located on the opposite side to the fluid outflow direction in the valve chamber. In this region, a first plate portion extending in the fluid outflow direction may be provided.
- the first plate portion may form a gap between the radially inner end portion and the outer peripheral surface of the guide.
- the radially inner end of the first plate portion approaches the outer peripheral surface of the guide as it goes to the back side in the inflow direction. It may be inclined.
- the radially inner end of the first plate portion is separated from the outer peripheral surface of the guide toward the back side in the inflow direction. It may be inclined.
- the baffle plate has a width direction intersecting a fluid inflow direction and a fluid outflow direction in the valve chamber. And a second plate portion extending in a direction perpendicular to the axial direction may be provided in a region between the outer peripheral surface of the guide and the inner surface of the casing.
- the second plate portion includes a front side plate portion that is formed only on the front side in the fluid inflow direction, and a rear side in the fluid inflow direction. You may be comprised from at least any one with the back side board part currently formed only in.
- the swirling vortex generated in the fluid flow path is deformed so as to extend in the fluid outflow direction by the second plate portion.
- the loss of the kinetic energy of the fluid by a swirling vortex can be reduced, and the increase in pressure loss can be suppressed.
- the main flow of the fluid can pass through the back side of the front side plate part and the front side of the back side plate part. For this reason, it can suppress that the main flow of a fluid is disturbed and pressure loss increases.
- the front side plate portion is provided on one side in the circumferential direction of the axis with respect to the arrangement position of the first plate portion, and
- the side plate portion may be provided on the other side in the circumferential direction of the axis with respect to the arrangement position of the first plate portion.
- the swirl vortex is extended in the circumferential direction, and the density of the vortex is reduced. That is, the swirl vortex can be weakened.
- the front side plate portion and the back side plate portion may be configured such that the positions in the axial direction partially overlap each other.
- the front side plate portion and the back side plate portion may be configured such that positions in the axial direction do not overlap each other.
- the second plate portion has an axis around a range of 45 ° to 135 ° with respect to an arrangement position of the first plate portion. It may be provided at the circumferential position.
- the swirl vortex is extended in the circumferential direction, and the density of the vortex is reduced. That is, the swirl vortex can be weakened.
- the second plate portion is 80 ° to 100 ° on the basis of the arrangement position of the first plate portion. It may be provided at a circumferential position around the axis in the range.
- the swirl vortex is further extended in the circumferential direction to reduce the density of the vortex. That is, the swirl vortex can be further weakened.
- the second plate portion has an axis around 90 ° with respect to the arrangement position of the first plate portion. It may be provided at a circumferential position.
- the swirling vortex flow is most elongated in the circumferential direction, thereby reducing the vortex density. That is, the swirl vortex can be weakened most.
- the steam turbine includes the main steam valve according to any one of the first to thirteenth aspects.
- FIG. 1 is a schematic view of a steam turbine plant according to an embodiment of the present invention. It is sectional drawing of the main steam valve which concerns on embodiment of this invention. It is the schematic diagram showing the valve chamber of the main steam valve which concerns on 1st embodiment of this invention. It is a figure which shows the modification of the main steam valve which concerns on 1st embodiment of this invention. It is a figure which shows the other modification of the main steam valve which concerns on 1st embodiment of this invention. It is a figure which shows the main steam valve which concerns on 2nd embodiment of this invention. It is a figure which shows the modification of the main steam valve which concerns on 2nd embodiment of this invention. It is a figure which shows the other modification of the main steam valve which concerns on 2nd embodiment of this invention.
- a steam turbine plant 100 includes a rotor 102 that rotates about an axis, a steam turbine 101 connected to the rotor 102, and a fluid (steam) F from a steam supply source (not shown) to the steam turbine 101.
- a steam supply pipe 103 to be supplied and a steam discharge pipe 104 connected to the downstream side of the steam turbine 101 to discharge steam are provided.
- the steam supply pipe 103 has a main steam valve 1 that adjusts the flow rate of the fluid F flowing through the steam supply pipe 103.
- the main steam valve 1 is a device for adjusting the flow rate of the fluid F supplied to the steam turbine 101 and stopping the supply of the fluid F.
- FIG. 2 is a cross-sectional view of the main steam valve 1 according to the present embodiment.
- the axis O extends along the inflow direction (the left-right direction in FIG. 2) of the fluid F
- the inflow side of the fluid F is the first end O1 (left side in FIG. 2) of the axis O
- the inflow side of the fluid F is the first end O1 (left side in FIG. 2) of the axis O
- the opposite side is referred to as a second end O2 of the axis O (the right side in FIG. 2).
- the intersection line C is a direction that intersects the axis O and extends along the outflow direction of the fluid F (vertical direction in FIG. 2), and the first end C1 ( The upper side in FIG.
- intersection line C (lower side in FIG. 2).
- a direction (vertical direction in FIG. 3) intersecting the axis O and the intersection line C is referred to as a width direction.
- the intersecting line C is perpendicular to the axis O, but is not necessarily perpendicular to the axis O, as long as it intersects the axis O at an angle.
- the main steam valve 1 includes a casing 2, a valve body 3, and a valve shaft 4.
- the casing 2 includes a valve chamber 7 that accommodates the valve body 3 therein, an inlet 10 and an outlet 11 that communicate with the valve chamber 7, and an opening 8 that faces the inlet 10 across the valve chamber 7. .
- the inner circumferential surface 7a of the valve chamber 7 is formed in a substantially concave spherical shape.
- the valve chamber 7 opens toward the first end O1 side in the axis O direction and communicates with the inflow port 10. Further, the valve chamber 7 opens toward the second end C2 side in the intersection line C and communicates with the outflow port 11.
- the inflow port 10 has a cross-sectional shape perpendicular to the axis O that is circular with the axis O as the center, and has an inner diameter that is smaller than the inner diameter of the valve chamber 7.
- a steam pipe or the like (not shown) is connected to the inflow port 10.
- a valve seat 5 On the inner surface of the casing 2 from the inlet 10 to the inner peripheral surface 7a of the valve chamber 7, a valve seat 5 in which the inner diameter (cross-sectional area) of the inlet 10 gradually increases toward the second end O2 side in the axis O direction. Is formed.
- the outflow port 11 has a cross-sectional shape orthogonal to the intersecting line C having a circular shape centering on the intersecting line C, and has an inner diameter smaller than the inner diameter of the valve chamber 7.
- a steam pipe (not shown) or the like is connected to the outlet 11. In this way, a fluid flow path 12 that is continuous from the inlet 10 to the outlet 11 through the valve chamber 7 is formed in the casing 2.
- the opening 8 is formed on the second end O2 side in the axis O direction of the casing 2.
- a holding member 9 that closes the opening 8 and holds the valve body 3 is attached to the opening 8.
- the holding member 9 is formed with a cylindrical guide 6 centering on the axis O and extending toward the first end O1 in the axis O direction.
- the valve body 3 is formed in a cylindrical shape extending in the direction of the axis O, and the outer peripheral surface thereof is inserted into the guide 6 so as to be slidable in the direction of the axis O with respect to the inner peripheral surface of the guide 6.
- the valve body 3 has a valve head 3 a that can close the valve seat 5 of the valve chamber 7 on the first end O1 side in the axis O direction.
- the valve shaft 4 has a cylindrical shape extending in the direction of the axis O, and a tip portion on the first end O1 side in the direction of the axis O is fixed to the central portion of the valve head 3a.
- the tip of the valve shaft 4 on the second end O2 side in the axis O direction protrudes outside the valve chamber 7 and is connected to an actuator (not shown).
- the valve shaft 4 is provided so as to be able to advance and retract along the axis O.
- the inner peripheral surface 7a of the valve chamber 7 in the region on the first end C1 side in the intersecting line C direction (the region on the opposite side to the outflow direction of the fluid F in the valve chamber 7) A plate-like first plate portion 21 (baffle plate) is provided.
- the first plate portion 21 has a plate shape extending along a plane including the axis O and the intersecting line C.
- the first plate portion 21 is formed such that the radially outer end of the axis O follows the curved surface of the inner peripheral surface 7 a of the valve chamber 7. As a result, the radially outer end of the first plate portion 21 is in close contact with the inner peripheral surface 7a of the valve chamber 7 in the entire region of the axis O direction.
- the end portion of the first plate portion 21 facing inward in the radial direction forms a straight line parallel to the axis O, and has a gap in the intersecting line C direction with the guide 6.
- the first plate portion 21 protrudes from the inner peripheral surface 7 a of the valve chamber 7 toward the inner side in the radial direction of the axis O, and the protruding tip forms a gap with the guide 6.
- valve body 3 By moving the valve shaft 4 to the second end O2 side in the axis O direction by an actuator (not shown), the valve body 3 together with the valve head 3a connected to the valve shaft 4 is moved to the second end in the axis O direction. Move to the O2 side. As a result, the fluid F flows between the valve head 3 a and the valve seat 5, so that the inflow port 10 and the valve chamber 7 communicate with each other. By moving the valve body 3 together with the valve shaft 4 to the second end O2 side in the direction of the axis O, the valve body 4 is opened (open position).
- the fluid F is introduced into the valve chamber 7 from the inlet 10 through the valve head 3a and the valve seat 5, and the inner peripheral surface 7a of the valve chamber and the outer peripheral surface of the guide 6 are introduced.
- a fluid flow path 12 that leads from the outlet 11 through the space 6a is formed.
- the fluid F flowing out from the outlet 11 is supplied to a steam turbine (not shown) connected downstream of the main steam valve 1.
- the main steam valve 1 increases or decreases the flow rate of the fluid F flowing between the valve head 3a and the valve seat 5 in accordance with the amount of movement of the valve body 3 in the axis O direction.
- the flow rate can be adjusted as appropriate.
- the fluid F that has flowed in through between the valve head 3a and the valve seat 5 moves toward the second end O2 side in the axis O direction along the inner peripheral surface 7a of the valve chamber 7. It flows toward.
- the fluid F that flows along the inner peripheral surface 7 a of the valve chamber 7 then flows along the opening 8, and further flows toward the first end O ⁇ b> 1 side in the axis O direction along the guide 6.
- the fluid F that has flowed toward the first end O1 in the axis O direction is pushed by the fluid F newly flowing in from the inflow port 10, and flows again toward the second end O2 in the axis O direction.
- Such a flow is continuous, and a swirling vortex swirling around a swirling axis extending in the circumferential direction of the axis O is generated.
- the direction in which the turning axis extends is not limited to the direction orthogonal to the axis O, and may be a direction that intersects the axis O with an angle.
- the swirling vortex generated as described above is generated in the valve chamber 7 in the region on the first end C1 side in the direction of the intersecting line C of the valve chamber 7. It flows between the inner peripheral surface 7a of the guide and the outer peripheral surface 6a of the guide 6 and flows toward the outlet 11. Thereby, in the valve chamber 7, the loss of the kinetic energy of the fluid F arises, and pressure loss may increase.
- the swirl vortex can be divided in the region on the first end C1 side in the direction of the intersecting line C of the valve chamber 7.
- the swirl vortex generated in the fluid flow path 12 can be weakened.
- the loss of kinetic energy of the fluid F in the main steam valve can be reduced, and an effect of suppressing an increase in pressure loss can be obtained.
- the first plate portion 21 protrudes from the inner peripheral surface 7 a of the valve chamber 7 toward the inside in the radial direction of the axis O, and the protruding tip is between the guide 6. It is provided so as to form a gap.
- the configuration in which the end portion of the first plate portion 21 facing inward in the radial direction forms a straight line parallel to the axis O has been described.
- the first plate portion 21 is not limited to this configuration.
- the end of the first plate portion 21 facing inward in the radial direction may be provided so as to be inclined in the width direction with respect to the axis O direction.
- the end portion of the first plate portion 21 facing inward in the radial direction is inclined so as to approach the outer peripheral surface of the guide 6 toward the back side in the fluid inflow direction. Accordingly, it is possible to suppress the development of the swirling vortex on the back side in the inflow direction of the fluid and allow the main flow of the fluid to pass on the near side in the inflow direction. Furthermore, since the swirling vortex is stretched in the circumferential direction, the density of the vortex is reduced. More specifically, the swirl vortex can be divided in the region on the first end C1 side in the intersecting line C direction of the valve chamber 7 to weaken the swirl vortex. Thereby, the loss of the kinetic energy of the fluid F due to the swirling vortex can be reduced, and the increase in pressure loss can be suppressed.
- the end of the first plate portion 21 facing inward in the radial direction may be inclined so as to move away from the outer peripheral surface of the guide 6 toward the inner side in the fluid inflow direction.
- a plate-like second plate portion 22 is provided on 7a.
- the 2nd board part 22 is comprised from the near side board part 22a and the back side board part 22b.
- the front side plate portion 22a and the back side plate portion 22b have a plate shape including the axis O and extending along a plane orthogonal to the intersecting line C.
- the front side plate portion 22a is provided on one side in the width direction of the valve chamber 7 and is formed so as to continue from the first end O1 side in the axis O direction to the vicinity of the center of the valve chamber 7 along the axis O. It extends so that there may be a gap between the guide 6 and the other side in the width direction.
- the rear side plate portion 22b is provided on the other side in the width direction of the valve chamber 7 and is formed so as to continue from the second end O2 side in the direction of the axis O to the vicinity of the center of the valve chamber along the axis O. It extends so as to have a gap with the guide 6 toward one side in the width direction.
- the swirling vortex generated in the fluid flow path 12 is divided by the front side plate portion 22a and the back side plate portion 22b in the width direction of the valve chamber 7. Thereby, it can suppress that a swirl
- the front side plate portion 22a is formed from the first end O1 side in the axis O direction to the vicinity of the center of the valve chamber 7 along the axis O, and from the vicinity of the center of the valve chamber 7 in the axis O direction to the second end O2. It is not formed on the side. For this reason, since the main flow of the fluid F can pass the 2nd end O2 side in the axis line O direction of the valve chamber 7, it can suppress that the main flow of the fluid F is disturbed and pressure loss increases.
- the back side plate portion 22b is formed from the second end O2 side in the axis O direction to the vicinity of the center of the valve chamber along the axis O, and from the vicinity of the center in the axis O direction of the valve chamber 7 to the first end O1 side. Is not formed. For this reason, the fluid F tends to pass through a region in which the front side plate portion 22 a and the back side plate portion 22 b are not provided in the width direction of the valve chamber 7. Thereby, the swirling vortex generated in the fluid flow path 12 is deformed so as to extend in the direction of the axis C in the region on one side and the other side in the width direction of the valve chamber 7. Thereby, the swirl vortex generated in the fluid flow path 12 can be weakened.
- the main flow of the fluid F can pass the 1st end O1 side in the axis line O direction of the valve chamber 7, it can suppress that the main flow of the fluid F is prevented and pressure loss increases.
- the swirl vortex flows in the inflow direction of the fluid F by changing the position where the second plate portion 22 is provided on the near side and the far side in the inflow direction of the fluid F on one side and the other side in the width direction. It can be suppressed that the flow is biased to only the front side or the back side. Thereby, it can suppress that a swirl
- the second plate portion 22 includes the front side plate portion 22a provided on the one side in the width direction and the back side plate portion 22b provided on the other side in the width direction.
- the 2nd board part 22 may be comprised from the back side board part 22b provided in the width direction one side, and the near side board part 22a provided in the width direction other side.
- the second plate portion 22 may have a configuration in which either the front-side plate portion 22a or the back-side plate portion 22b is provided on either one side or the other side in the width direction.
- the second plate portion 22 may have a configuration in which a plurality of front side plate portions 22a and back side plate portions 22b are provided.
- the position in the crossing line C direction of the near side board part 22a and the back side board part 22b may differ by the one side and the other side of the width direction. Even with such a configuration, the same effects as those of the above-described embodiment can be obtained.
- the front side plate portion 22a and the back side plate portion 22b may partially overlap each other in the crossing line C direction. According to such a configuration, the swirl vortex can be extended in the circumferential direction of the intersection line C, and therefore the swirl vortex can be further weakened.
- the front side plate portion 22a and the back side plate portion 22b are arranged in the circumferential direction in the range of 45 ° to 135 ° with respect to the first plate portion 21 when viewed from the direction of the crossing line C. It is preferable to be provided. More preferably, the front side plate portion 22a and the back side plate portion 22b are provided at circumferential positions in the range of 80 ° to 100 °. Most preferably, the front side plate portion 22 a and the back side plate portion 22 b are provided at a circumferential position of 90 ° with respect to the first plate portion 21.
- the swirl vortex is extended in the circumferential direction of the intersecting line C, thereby reducing the density of the vortex.
- vortex vortex can be weakened most.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
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- Control Of Turbines (AREA)
- Valve Housings (AREA)
Abstract
Description
本願は、2014年10月28日に出願された特願2014-219725号に基づき優先権を主張し、その内容をここに援用する。
主蒸気弁は、内部に流体の流路が形成されるケーシングと、流路内で軸線に沿って移動可能に設けられた弁体と、を備えている。ケーシング内部の流路には、弁体によって閉塞可能な弁座が形成されている。弁体が軸線方向における第一側に移動することにより弁座に接近し、弁体が軸線方向における第二側に移動することにより弁座から離間する。これにより、弁体と弁座との隙間の流路面積を変化させ流体流量が調整される。
本発明の第一の態様によれば、主蒸気弁は、軸線を中心として延びる筒状のガイドと、該ガイドの内側に軸線方向に摺動可能に配置された弁体と、該弁体を開位置と閉位置との間で前記軸線方向に移動させる弁軸と、前記軸線方向に沿う流入方向から導入される流体を、前記流入方向に交差する流出方向に導出する流路を形成するとともに、内面に前記閉位置の弁体が当接する弁座が形成されたケーシングと、前記ケーシングの内側に形成される弁室と、を備える。前記弁室には、前記ガイドの外周面と前記ケーシングの内面との間の領域に、前記ガイドの前記軸線の周方向に延びる旋回軸回りに旋回する旋回渦流を分断させる邪魔板が設けられている。
以下、本発明の第一実施形態に係る主蒸気弁1について図を参照して説明する。
図1に示すように、蒸気タービンプラント100は、軸線を中心に回転するロータ102と、ロータ102に接続される蒸気タービン101と、図示しない蒸気供給源から流体(蒸気)Fを蒸気タービン101に供給する蒸気供給管103と、蒸気タービン101の下流側に接続されて蒸気を排出する蒸気排出管104とを備えている。
蒸気供給管103は、蒸気供給管103内を流通する流体Fの流通量を調整する主蒸気弁1を有している。
主蒸気弁1は、蒸気タービン101に供給する流体Fの流量を調整したり、流体Fの供給を停止するための装置である。
以降の説明において、軸線Oは流体Fの流入方向(図2における左右方向)沿って延び、流体Fの流入側を軸線Oの第一端O1(図2における左側)、流体Fの流入側と反対側を軸線Oの第二端O2(図2における右側)と称する。また、交差線Cは軸線Oに交差する方向であって流体Fの流出方向(図2における上下方向)に沿って延び、流体Fの流出方向と反対側を交差線Cの第一端C1(図2における上側)、流体Fの流出側を交差線Cの第二端C2(図2における下側)と称する。さらに、軸線Oと交差線Cとに交差する方向(図3における上下方向)を幅方向と称する。なお、本実施形態では交差線Cが軸線Oに直交しているが、必ずしも直交している必要はなく、軸線Oと角をなして交差していればよい。
流入口10から弁室7の内周面7aにかけて、ケーシング2の内面には、軸線O方向における第二端O2側に向かって流入口10の内径(断面積)が漸次拡大する弁座5が形成されている。
このようにして、ケーシング2には、流入口10から弁室7を経て、流出口11へと連続する流体流路12が形成されている。
換言すれば、第一板部21は、弁室7の内周面7aから軸線Oの径方向内側に向かって張り出すように、かつ、張り出した先端がガイド6との間で隙間を形成するように設けられている。
ここで、第一板部21が設けられていない主蒸気弁においては、弁室7の交差線C方向における第一端C1側の領域において、上記のように生成された旋回渦流が弁室7の内周面7aとガイド6の外周面6aの間を通り、流出口11に向って流れていく。これにより、弁室7において流体Fの運動エネルギのロスが生じ、圧力損失が増加する可能性がある。
次に、本発明の第二実施形態に係る主蒸気弁1について図6を参照して説明する。
第一実施形態と共通の構成には同一の符号を付して詳細説明を省略する。
本実施形態では、主蒸気弁1が板状の第二板部22(邪魔板)を有する点において第一実施形態とは異なっている。
2 ケーシング
3 弁体
3a 弁頭部
4 弁軸
5 弁座
6 ガイド
6a 外周面
7 弁室
7a 内周面
8 開口部
9 保持部材
10 流入口
11 流出口
12 流体流路(流路)
21 第一板部(邪魔板)
22 第二板部(邪魔板)
22a 手前側板部(第二板部)
22b 奥側板部(第二板部)
100 蒸気タービンプラント
101 蒸気タービン
102 ロータ
103 蒸気供給管
104 蒸気排出管
F 流体(蒸気)
O 軸線
C 交差線
Claims (14)
- 軸線を中心として延びる筒状のガイドと、
該ガイドの内側に軸線方向に摺動可能に配置された弁体と、
該弁体を開位置と閉位置との間で前記軸線方向に移動させる弁軸と、
前記軸線方向に沿う流入方向から導入される流体を、前記流入方向に交差する流出方向に導出する流路を形成するとともに、内面に前記閉位置の弁体が当接する弁座が形成されたケーシングと、
前記ケーシングの内側に形成される弁室と、
を備え、
前記弁室には、前記ガイドの外周面と前記ケーシングの内面との間の領域に、前記ガイドの前記軸線の周方向に延びる旋回軸回りに旋回する旋回渦流を分断させる邪魔板が設けられている主蒸気弁。 - 前記邪魔板は、前記弁室の前記ガイドの外周面と前記ケーシングの内面との間の領域であって、流体の流出方向と反対側の領域に、流体の流出方向に延在する第一板部を有する請求項1に記載の主蒸気弁。
- 前記第一板部は、径方向内側の端部が前記ガイドの外周面との間で隙間を形成している請求項2に記載の主蒸気弁。
- 前記第一板部の径方向内側の端部が、前記流入方向の奥側に向かうに従って前記ガイドの外周面に近づくように傾斜している請求項3に記載の主蒸気弁。
- 前記第一板部の径方向内側の端部が、前記流入方向の奥側に向かうに従って前記ガイドの外周面から離れるように傾斜している請求項3に記載の主蒸気弁。
- 前記邪魔板は、前記弁室の前記ガイドの外周面と前記ケーシングの内面との間の領域にであって、流体の流入方向と流体の流出方向とに交差する幅方向において、前記軸線方向に直交する方向に向かって延在する第二板部を有する請求項2から5のいずれか一項に記載の主蒸気弁。
- 前記第二板部は、流体の流入方向の手前側にのみ形成されている手前側板部と、流体の流入方向の奥側のみに形成されている奥側板部との、少なくともいずれか一方から構成されている請求項6に記載の主蒸気弁。
- 前記手前側板部は、前記第一板部の配置位置を基準として前記軸線の周方向一方側に設けられており、
前記奥側板部は、前記第一板部の配置位置を基準として前記軸線の周方向他方側に設けられている請求項7に記載の主蒸気弁。 - 前記手前側板部と前記奥側板部とは、前記軸線方向の位置が互いに一部のみ重なる請求項8に記載の主蒸気弁。
- 前記手前側板部と前記奥側板部とは、前記軸線方向の位置が互いに重ならない請求項8に記載の主蒸気弁。
- 前記第二板部は、前記第一板部の配置位置を基準として45°~135°の範囲の軸線回りの周方向位置に設けられている請求項6又は7に記載の主蒸気弁。
- 前記第二板部は、前記第一板部の配置位置を基準としてとして80°~100°の範囲の軸線回りの周方向位置に設けられている請求項6から8のいずれか一項に記載の主蒸気弁。
- 前記第二板部は、前記第一板部の配置位置を基準として90°の軸線回りの周方向位置に設けられている請求項6から9のいずれか一項に記載の主蒸気弁。
- 請求項1から13の何れか1項に記載の主蒸気弁を備える蒸気タービン。
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DE112015004881.2T DE112015004881B4 (de) | 2014-10-28 | 2015-10-21 | Hauptdampfventil und Dampfturbine |
CN201580054660.0A CN106795776B (zh) | 2014-10-28 | 2015-10-21 | 主蒸汽阀以及蒸汽轮机 |
US15/517,784 US10119416B2 (en) | 2014-10-28 | 2015-10-21 | Main steam valve and steam turbine |
JP2016556519A JP6269855B2 (ja) | 2014-10-28 | 2015-10-21 | 主蒸気弁、及び蒸気タービン |
KR1020177009668A KR101921848B1 (ko) | 2014-10-28 | 2015-10-21 | 주 증기 밸브 및 증기 터빈 |
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KR101921848B1 (ko) | 2018-11-23 |
JP6269855B2 (ja) | 2018-01-31 |
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