WO2012117597A1 - 多段圧復水器およびこれを備えた蒸気タービンプラント - Google Patents
多段圧復水器およびこれを備えた蒸気タービンプラント Download PDFInfo
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- WO2012117597A1 WO2012117597A1 PCT/JP2011/071277 JP2011071277W WO2012117597A1 WO 2012117597 A1 WO2012117597 A1 WO 2012117597A1 JP 2011071277 W JP2011071277 W JP 2011071277W WO 2012117597 A1 WO2012117597 A1 WO 2012117597A1
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- Prior art keywords
- pressure
- low
- pressure side
- condensate
- condenser
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28B—STEAM OR VAPOUR CONDENSERS
- F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
- F28B1/02—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using water or other liquid as the cooling medium
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K9/00—Plants characterised by condensers arranged or modified to co-operate with the engines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K9/00—Plants characterised by condensers arranged or modified to co-operate with the engines
- F01K9/003—Plants characterised by condensers arranged or modified to co-operate with the engines condenser cooling circuits
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28B—STEAM OR VAPOUR CONDENSERS
- F28B7/00—Combinations of two or more condensers, e.g. provision of reserve condenser
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28B—STEAM OR VAPOUR CONDENSERS
- F28B9/00—Auxiliary systems, arrangements, or devices
- F28B9/02—Auxiliary systems, arrangements, or devices for feeding steam or vapour to condensers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28B—STEAM OR VAPOUR CONDENSERS
- F28B9/00—Auxiliary systems, arrangements, or devices
- F28B9/08—Auxiliary systems, arrangements, or devices for collecting and removing condensate
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F25/00—Component parts of trickle coolers
- F28F25/02—Component parts of trickle coolers for distributing, circulating, and accumulating liquid
- F28F25/08—Splashing boards or grids, e.g. for converting liquid sprays into liquid films; Elements or beds for increasing the area of the contact surface
- F28F25/087—Vertical or inclined sheets; Supports or spacers
Definitions
- the present invention relates to a multi-stage pressure condenser used in a steam turbine plant.
- the steam that drives the steam turbine is exhausted from the turbine and guided to a condenser.
- the steam led to the condenser is condensed by exchanging heat with the cooling water led to the condenser and condensed.
- the condensed water condensed in the condenser is heated via the heater and supplied to the boiler.
- the heated condensate supplied to the boiler is converted into steam and used as a drive source for the steam turbine.
- FIG. 5 shows a schematic configuration diagram of a two-stage multi-stage pressure condenser including, for example, a high-pressure and a low-pressure condenser.
- the low-pressure condenser 2 has a porous partition 8 that divides the longitudinal direction of the low-pressure cylinder 3 into an upper part and a lower part. 4, a low-pressure side cooling pipe group 5 provided on the upper side of the low-pressure side cylinder 3 to which the cooling water is guided, and a reheating chamber 6 positioned below the low-pressure side cylinder 3.
- Exhaust gas (low-pressure side steam) from a steam turbine (not shown) guided to the upper side of the low-pressure side cylinder 3 is condensed by heat exchange with cooling water guided to the low-pressure side cooling pipe group 5, and is recovered. It becomes water and is stored above the pressure bulkhead 4 to form a condensate pool 7. Since the pressure partition wall 4 is provided with a plurality of holes 8, the low-pressure side condensate flows down from the condensate pool 7 to the reheat chamber 6.
- the reheat chamber 6 is connected to a steam duct 13 that guides the exhaust of the steam turbine above the high pressure side condenser 22 to the reheat chamber 6 of the low pressure side condenser 2. Therefore, the low-pressure side condensate flowing down to the reheating chamber 6 comes into gas-liquid contact with the high-pressure side steam guided from the steam duct 13 and is reheated.
- the reheat efficiency improves as the time during which the low-pressure condensate to be reheated is in gas-liquid contact with the exhaust of the high-pressure side steam increases.
- Patent Document 1 discloses providing a tray 9 for storing and overflowing the low-pressure side condensate flowing down from the porous 8 in the reheating chamber 6 as shown in FIG. ing.
- Patent Document 2 discloses that an angle steel with its apex facing upward or a spiral element is suspended from a pressure bulkhead.
- Patent Document 3 discloses that a cylindrical liquid film extending in the longitudinal direction of the low-pressure side cylinder is suspended from the pressure partition into the reheat chamber.
- the pressure partition 4a part 4a of the low pressure side condenser 2 is lowered by, for example, about 50 cm to the reheating chamber 6 side to increase the volume of the condensate reservoir 7, thereby reducing the low pressure side cooling. Measures are taken to prevent the tube group (not shown) from being submerged in the condensate reservoir 7.
- the part 4a of the pressure partition 4 is lowered to the reheating chamber 6 in this way, the distance from the part 4a of the pressure partition 4 having the perforations 8 to the tray 9 is shortened, and the low pressure side flowing down.
- the gas-liquid contact time between the condensate and the high-pressure side steam was shortened and the reheating efficiency was lowered.
- the present invention has been made in view of the above circumstances, and provides a multistage pressure condenser capable of further improving the reheat efficiency without increasing the size, and a steam turbine plant including the same. is there.
- the multi-stage pressure condenser includes a plurality of chambers having different pressures, a pressure partition having a plurality of holes dividing the low-pressure chamber, which is the low-pressure side chamber, in the vertical direction, and the pressure Cooling provided at the upper part of the low-pressure chamber partitioned by a partition wall, where cooling water is introduced and heat-exchanged with the low-pressure side steam led to the low-pressure chamber to condense the low-pressure side steam into the low-pressure side condensate
- a high-pressure-side steam introducing means for introducing the high-pressure-side steam into the reheating chamber, and parallel to each other along the flow-down direction of the low-pressure side condensate flowing down from the hole of the pressure partition below the pressure partition.
- a plurality of plate-like members disposed, each plate-like member having a front The flow-down direction of the low pressure side condensate cross-section and forms at least one concavo-convex shape.
- the low-pressure side condensate flowing down from the hole in the pressure partition comes into gas-liquid contact with the high-pressure side steam introduced into the reheating chamber when flowing down.
- a plurality of plate-like members arranged in parallel to each other along the flow-down direction of the low-pressure side condensate flowing down from the holes of the pressure partition walls are provided below the pressure partition walls.
- the cross section in the flow-down direction of the low-pressure side condensate is designed to form at least one uneven shape.
- the manufacturing cost is low and installation is easy. Therefore, the increase in the manufacturing cost and manufacturing time of the multistage pressure condenser can be suppressed.
- the distance between the plate-like members arranged in parallel to each other is variable.
- the distance between the plate-like members variable, the low-pressure side condensate flowing between the plate-like members is adjusted to flow down and the low-pressure side condensate flowing down is brought into contact with both plate-like members,
- the flow rate can be controlled. Therefore, the gas-liquid contact time and contact area between the high-pressure side steam and the low-pressure side condensate can be increased. Therefore, the reheat efficiency can be increased without changing the size of the multistage pressure condenser.
- the plate-like member is porous.
- a plate-like member having porosity is used.
- the low-pressure side condensate flowing down along the plate-like member can be dispersed and refined, and the high-pressure side steam can also pass between the plate-like members. Therefore, the gas-liquid contact area between the high-pressure side steam and the low-pressure side condensate can be increased.
- the manufacturing cost can also be suppressed by utilizing (processing) the existing punching metal material for the plate-like member having the perforations.
- the plate-like member has a pocket portion that opens toward the low-pressure side condensate flowing down along the plate-like member.
- the plate-shaped member provided with a pocket part exists as a ready-made product. Therefore, an increase in the manufacturing cost of the multistage pressure condenser can be suppressed.
- a receiving member for storing and overflowing the low-pressure side condensate flowing down from the plate member is provided below the plate member.
- a receiving member for storing and overflowing the low-pressure condensate flowing down from the plate-like member is provided below the plate-like member. For this reason, the low-pressure side condensate that has overflowed and flowed down from the receiving member creates a circulating flow in the low-pressure side condensate stored in the reheating chamber, and contacts the high-pressure side steam introduced into the reheating chamber over a wide area. Will be. Therefore, the reheat efficiency can be increased.
- a part of the pressure partition is provided with a depression in the lower part.
- a steam turbine plant according to the second aspect of the present invention includes the multi-stage pressure condenser as described above.
- a plurality of plate-like shapes arranged in parallel to each other along the flow direction of the low-pressure side condensate flowing down from the hole of the pressure partition wall.
- the member is provided below the pressure partition, and the cross section in the flow direction of the low-pressure side condensate of each of the plate-like members forms at least one uneven shape.
- the manufacturing cost is low and installation is easy. Therefore, the increase in the manufacturing cost and manufacturing time of the multistage pressure condenser can be suppressed.
- the steam turbine plant (not shown) having the illustrated multistage pressure condenser 1 mainly includes a steam turbine (not shown), the multistage pressure condenser 1, and a boiler (not shown). It is configured.
- the steam that has finished the expansion work in the steam turbine is introduced from the steam turbine to the multistage condenser 1 and cooled by the multistage condenser 1 to be condensed and condensate.
- the condensed water condensed in the multistage condenser 1 is heated by a feed water heater (not shown) and then supplied to the boiler.
- the condensate supplied to the boiler is converted into steam and used as a drive source for the steam turbine.
- the multi-stage pressure condenser 1 has a plurality of chambers having different pressures, a high pressure side condenser (high pressure chamber) 22 which is a high pressure side chamber, and a low pressure which is a low pressure side chamber.
- a side condenser (low pressure chamber) 2 is provided.
- the high-pressure side condenser 22 has a high-pressure side cylinder 23 which is a high-pressure side chamber, and a high-pressure side cooling pipe group 25 provided in the high-pressure side cylinder 23.
- the low pressure side condenser 2 has a low pressure side cylinder 3 which is a low pressure side chamber, and a low pressure side cooling pipe group (cooling pipe group) 5 provided in the low pressure side cylinder 3.
- the low-pressure condenser 2 is divided by a pressure partition 4 that divides the low-pressure condenser 2 in the vertical direction and has a plurality of holes 8.
- the pressure partition 4 is provided so that the distance between the lower surface of the pressure partition 4 and the bottom surface of the low-pressure side body 3 is, for example, 1000 mm.
- a low pressure side cooling pipe group 5 is provided on the upper portion of the low pressure side condenser 2 partitioned by the pressure partition 4.
- a reheating chamber 6 is provided at the lower part of the low pressure side condenser 2 partitioned by the pressure partition 4.
- Cooling water is introduced into the low-pressure side cooling pipe group 5 provided on the upper side of the low-pressure side condenser 2.
- the cooling water introduced into the low-pressure side cooling pipe group 5 condenses the low-pressure side steam led to the low-pressure side condenser 2 into condensate (hereinafter referred to as “low-pressure side condensate”).
- the pressure partition 4 is a perforated plate.
- the plurality of holes 8 provided in the pressure partition 4 are flow-down holes, and flow down the low-pressure side condensate condensed on the upper side of the low-pressure side condenser 2 to the reheat chamber 6.
- a corrugated plate (plate-shaped member) is disposed along the flow direction of the low-pressure side condensate flowing down from the hole 8 provided in the pressure partition 4. 10 is provided.
- a plurality of corrugated plates 10 are provided and arranged in parallel to each other.
- the corrugated plate 10 has an uneven shape (zigzag shape) in which a cross section in the flow direction of the low-pressure side condensate alternately forms a plurality (at least one) of valleys. That is, it is a shape in which peaks and valleys formed on the left and right are repeated along the vertical direction.
- the corrugated plate 10 is manufactured to have a thickness of 3 mm by SUS304, for example.
- the corrugated plates 10 arranged in parallel to each other below the pressure bulkhead 4 to form a corrugated plate group are arranged with an interval of about 5 mm, for example, 100 pieces are provided.
- a tray (receiving member) 9 is provided below the lower end of the plurality of corrugated plates 10 and in the lower part of the reheating chamber 6.
- the tray 9 is provided such that its lower surface is at a distance of, for example, about 200 mm from the bottom surface of the low-pressure side barrel 3.
- the low-pressure side condensate flows down from the corrugated plate 10.
- the low-pressure side condensate flowing down to the tray 9 is collected (stored) in the tray 9 and overflows from the tray 9 and falls.
- seawater is supplied as cooling water to the low-pressure side cooling pipe group 5 provided in the low-pressure condenser 2.
- Seawater supplied to the low-pressure side cooling pipe group 5 is sent from a connecting pipe (not shown) to the high-pressure side cooling pipe group 25 of the high-pressure side condenser 22.
- Seawater sent to the high-pressure side cooling pipe group 25 is discharged from a discharge pipe (not shown).
- the low pressure side steam exhausted after finishing the work in the steam turbine is guided to the upper part of the low pressure side condenser 2.
- the low-pressure side steam led to the upper part of the low-pressure side condenser 2 is condensed by being cooled by the low-pressure side cooling pipe group 5 in which seawater is led into each pipe. It is said.
- the low-pressure side condensate thus condensed is stored in the upper part of the low-pressure side condenser 2 (above the pressure bulkhead 4 in FIG. 1) to form a condensate pool 7.
- the distance between the water surface of the condensate pool 7 and the lowest stage of the low pressure side cooling pipe group 5 is a predetermined value. The distance is about 30 cm.
- the pressure partition 4 Since the pressure partition 4 is provided with a plurality of holes 8, the low-pressure side condensate accumulated in the condensate reservoir 7 flows down from the holes 8.
- the low-pressure condensate flowing down (passing through) the holes 8 flows along the surfaces of the plurality of corrugated plates 10 provided below the pressure partition 4.
- the high pressure side steam exhausted after finishing the work in the steam turbine is guided into the high pressure side condenser 22.
- the high-pressure side steam introduced into the high-pressure side condenser 22 is condensed by being cooled by the high-pressure side cooling pipe group 25 in which seawater is introduced into each pipe (hereinafter referred to as “high-pressure side condensate”). And stored in the high pressure side condenser 22.
- the high pressure side condenser 22 and the reheating chamber 6 of the low pressure side condenser 2 are connected by a steam duct (high pressure side steam introducing means) 11, the high pressure side steam in the high pressure side condenser 22 is It will be introduced into the reheating chamber 6 from the steam duct 11.
- the high-pressure side steam introduced into the reheating chamber 6 makes gas-liquid contact with the low-pressure side condensate flowing down from the pressure partition 4 along the surface of the corrugated plate 10.
- the low-pressure condensate flowing down along the surface of the corrugated sheet 10 is collected on the tray 9 from the lower end of the corrugated sheet 10.
- the low-pressure side condensate collected in the tray 9 overflows from the tray 9 and falls.
- the low-pressure side condensate dropped from the tray 9 is accumulated in the reheat chamber 6.
- a confluence section (not shown) is provided in the lower part of the reheating chamber 6, a confluence section (not shown) is provided.
- a bypass connecting pipe 12 as a bypass means connects to the lower part of the high pressure side condenser 22 at the junction.
- the high-pressure side condensate stored in the high-pressure side condenser 22 is led to the merging portion via the bypass connecting pipe 12 and merged with the low-pressure side condensate to be condensed.
- the condensate merged at the merge section is sent to a feed water heater by a condensate pump (not shown).
- the high-pressure side condensate led from the bypass connecting pipe 12 to the junction is bypassed the low-pressure side condensate stored in the reheat chamber 6 and led to the junction,
- the high pressure side condensate can be merged into the condensate while keeping the temperature high. Therefore, high-temperature condensate can be sent out from the condensate pump.
- the corrugated plate 10 has a plurality of concave and convex shapes.
- the time for movement (fluidization) increases. Therefore, the time during which the low-pressure side condensate flowing down the surface of the corrugated plate 10 and the high-pressure side steam come into gas-liquid contact increases. Since the time during which the low-pressure condensate flowing down and the high-pressure steam come into gas-liquid contact increases, the temperature of the low-pressure condensate heated by the high-pressure steam is higher than when the corrugated plate 10 is not used. Become.
- the low-pressure side condensate flowing down from the corrugated plate 10 to the tray 9 is heated to a higher temperature while being in gas-liquid contact with the high-pressure side steam while being collected in the tray 9. Further, the low-pressure side condensate falling from the tray 9 causes a circulation flow in the low-pressure side condensate stored in the reheat chamber 6. Therefore, the surface of the low-pressure side condensate and the high-pressure side steam come into contact with each other over a wide area to cause surface turbulent heat transfer and heat the condensate.
- the increase in the gas-liquid contact time between the low-pressure side condensate flowing down along the surface of the corrugated plate 10 and the high-pressure side steam, and the gas between the low-pressure side condensate and the high-pressure side steam collected in the tray 9 are as follows.
- the condensate can be heated sufficiently without changing the distance at which the low-pressure side condensate falls, that is, the distance between the pressure partition 4 and the bottom surface of the low-pressure side barrel 3. Therefore, the reheat efficiency can be further improved without increasing the size of the multistage pressure condenser 1.
- each corrugated plate 10 disposed in parallel with each other along the flow direction of the low-pressure condensate flowing down from the hole 8 of the pressure partition 4 are provided below the pressure partition 4.
- the cross section of each corrugated plate 10 in the flow-down direction of the low-pressure condensate forms a plurality (at least one) of uneven shapes.
- the area where the low pressure side condensate flowing down from the hole 8 of the pressure partition 4 contacts the corrugated plate 10 can be increased. Therefore, the gas-liquid contact time between the high-pressure side steam introduced into the reheating chamber 6 and the low-pressure side condensate can be increased. Therefore, the reheat efficiency can be easily increased without changing the overall size of the multistage pressure condenser 1.
- the manufacturing cost is low and the installation is easy. Therefore, an increase in manufacturing cost and manufacturing time of the multistage pressure condenser 1 can be suppressed.
- a tray (receiving member) 9 that stores and overflows the low-pressure condensate flowing down from the corrugated plate 10 is provided below the lower end of the corrugated plate 10. Therefore, the low-pressure side condensate that has overflowed and flowed down from the tray 9 causes a circulation flow in the low-pressure side condensate stored in the reheat chamber 6, and the high-pressure side steam introduced into the reheat chamber 6 and a large area. Will come in contact. Therefore, the reheat efficiency can be increased.
- the multi-stage pressure condenser 1 has been described using a two-stage condenser having the high-pressure condenser 22 and the low-pressure condenser 2, but the present invention is not limited to this.
- it may be a condenser having three stages of a high pressure side condenser, an intermediate pressure side condenser, and a low pressure side condenser.
- the corrugated plate is installed below the pressure partition provided in the intermediate pressure side condenser and the low pressure side condenser.
- the distance between corrugated plates (plate-like members) provided in parallel to each other is provided so as to be adjustable. For example, by changing the distance between the corrugated plates from about 5 mm described in the first embodiment to about 2 mm, the falling film thickness of the low-pressure condensate flowing down between the corrugated plates can be adjusted. The flow rate of the side condensate can be reduced.
- the multistage pressure condenser Since the flow speed of the low-pressure side condensate flowing down the surface of the corrugated sheet can be reduced without changing the length of the extension direction between the corrugated sheets (the flow direction of the low-pressure side condensate), the multistage pressure condenser The gas-liquid contact time between the low-pressure side condensate and the high-pressure side steam can be increased without changing the size of.
- the multistage pressure condenser according to the present embodiment and the steam turbine plant including the multistage pressure condenser have the following operational effects.
- the distance between the corrugated plates (plate-like members) variable, the low-pressure side condensate flowing between the corrugated plates is adjusted by adjusting the flow thickness of the low-pressure condensate to contact both corrugated plates.
- the flow rate can be controlled. Therefore, the gas-liquid contact time and contact area between the high-pressure side steam and the low-pressure side condensate can be increased. Therefore, the reheat efficiency can be increased without changing the size of the multistage pressure condenser.
- the multi-stage pressure condenser of this embodiment and the steam turbine including the same are different from those of the first embodiment in that they have a pocket portion that opens toward the low-pressure side condensate where the corrugated plate flows down, and the others are the same. It is. Therefore, about the same structure, the same code
- FIG. 2 shows a partially enlarged schematic configuration diagram of the low pressure side condenser of the multistage pressure condenser according to the present embodiment.
- the corrugated plate 20 has a concavo-convex shape (zigzag shape) in which the cross-section in the flow-down direction of the low-pressure condensate alternately forms a plurality (at least one) of valleys and is as shown in FIG.
- the concavo-convex convex portion has a pocket portion 21 that opens toward the low-pressure side condensate flowing down along the surface of the corrugated plate 20.
- the low-pressure side condensate that flows down along the surface of the corrugated plate 20 from the hole 8 provided in the pressure partition 4 reaches the convex portion of the concavo-convex shape. Since the convex portion is provided with the pocket portion 21 that opens toward the flow-down direction of the low-pressure side condensate, the low-pressure side condensate flows into the pocket portion 21.
- the low-pressure side condensate accumulated in the pocket portion 21 overblows from the pocket portion 21 and flows down along the surface of the concave portion of the corrugated plate 20 below the pocket portion 21.
- the low-pressure side condensate flowing down from the hole 8 provided in the pressure partition 4 is guided from the surface of the convex portion of the corrugated plate 20 to the pocket portion 21 and overflows from the pocket portion 21 to form a concave portion. It is repeated that it flows down along the surface of the sheet and falls onto the tray (receiving member) 9.
- the low-pressure side condensate guided to the pocket portion 21 from the surface of the convex portion of the corrugated plate 20 agitates the low-pressure side condensate stored in the pocket portion 21. Therefore, the contact area between the low pressure side condensate and the high pressure side steam increases. As a result, it is possible to efficiently raise the temperature of the low-pressure side condensate flowing down the corrugated plate 20 through good heat transfer.
- the multistage pressure condenser according to the present embodiment and the steam turbine plant including the multistage pressure condenser have the following operational effects.
- the corrugated plate (plate-shaped member) 20 provided with the pocket portion 21 opened toward the low-pressure side condensate flowing down is used.
- the low-pressure side condensate flowing down along the corrugated plate 20 can be temporarily stored in the pocket portion 21. Therefore, the low pressure side condensate can be stirred and flowed down in the pocket portion 21. Therefore, the gas-liquid contact area between the high-pressure side steam and the low-pressure side condensate can be increased.
- the corrugated sheet 20 provided with the pocket part 21 exists as a ready-made product. Therefore, an increase in the manufacturing cost of a multistage pressure condenser (not shown) can be suppressed.
- FIG. 34 The partial schematic block diagram of the low voltage
- a part 34 a where the corrugated plate (plate-like member) 10 is provided is depressed downward to form a condensate reservoir 37.
- the distance between the pressure partition wall 34 and the bottom surface of the low-pressure side body (not shown) is, for example, 1000 mm
- a part 34a of the pressure partition wall 34 is formed to be recessed downward, for example, by about 500 mm.
- the pressure difference between the high pressure side condenser (high pressure chamber) and the low pressure side condenser (low pressure chamber) 2 constituting the multistage pressure condenser (not shown) becomes large (for example, 50 mmHg)
- the amount of low-pressure condensate collected above the pressure partition 34 increases.
- the increased low-pressure side condensate accumulates in a part 34 a of the pressure partition wall 34 to form a condensate pool 37. Therefore, the distance between the lowermost stage of the low-pressure side cooling pipe group (cooling pipe group) and the water surface of the condensate pool 37 can be maintained at a predetermined distance (about 30 cm).
- a plurality of corrugated plates 10 are provided below a part 34 a of the pressure partition 34 forming the condensate pool 37. Therefore, when the corrugated plate 10 is not provided even if the flow length in the extending direction of the corrugated plate 10 (the flow direction of the low-pressure side condensate) is shortened due to the depression 34a of the pressure partition wall 34 being depressed downward. As compared with the above, the gas-liquid contact time between the low-pressure side condensate and the high-pressure side steam can be lengthened to raise the temperature of the low-pressure side condensate.
- the multistage pressure condenser according to the present embodiment and the steam turbine plant including the multistage pressure condenser have the following operational effects.
- a part 34a of the pressure partition wall 34 in which the corrugated plate (plate-like member) 10 is provided below the pressure partition wall 34 is recessed downward. Therefore, the volume of the condensate sump 37 in which the low-pressure side condensate stored above the pressure partition 34 is stored can be increased.
- the portion 34a of the pressure partition 34 is recessed downward, the distance between the portion 34a of the pressure partition 34 and the bottom surface of the reheating chamber 6 is shortened, but provided below the portion 34a of the pressure partition 34.
- the corrugated sheet 10 has a plurality of (at least one) irregular shapes, the gas-liquid contact time can be maintained. Therefore, when the pressure difference between the high pressure side condenser (high pressure chamber) and the low pressure side condenser (low pressure chamber) 2 is large, the low pressure side cooling pipe group (cooling pipe group) is prevented from being submerged, and the multistage pressure recovery is performed. Reheating efficiency can be maintained without changing the overall size of the water vessel (not shown).
- FIG. 4 is a perspective view of the corrugated plate of the low pressure side condenser of the multistage pressure condenser according to the present embodiment.
- the corrugated plate 40 has a concavo-convex shape (zigzag shape) in which the cross section in the flow direction of the low-pressure condensate (shown by the white arrow in FIG. 4) alternately forms a plurality (at least one) of valleys.
- zigzag shape the cross section in the flow direction of the low-pressure condensate
- the low-pressure side condensate flowing along the surface of the corrugated plate 40 from a hole (not shown) provided in a part 34a (see FIG. 3) of the pressure partition wall 34 reaches the corrugated plate 40 surface. Since the corrugated plate 40 has a perforation 41 and is open, the low-pressure side condensate flows down the corrugated plate 40 and the perforated 41 and flows into the adjacent corrugated plate 40 surface. It will be a thing.
- the low-pressure side condensate falls to the tray (receiving member) 9 (see FIG. 3).
- the low-pressure side condensate flowing down into the perforations 41 of the corrugated plate 40 is dispersed and refined on the adjacent corrugated plate 40 surface.
- the high-pressure side steam also passes through the perforations 41 as indicated by dotted arrows in FIG. Therefore, the contact area between the low pressure side condensate and the high pressure side steam increases. Thereby, good heat transfer is performed and the low-pressure side condensate flowing down the corrugated plate 40 can be efficiently heated.
- the multistage pressure condenser according to the present embodiment and the steam turbine plant including the multistage pressure condenser have the following operational effects.
- the corrugated plate (plate member) 40 provided with the perforations 41 toward the low-pressure side condensate flowing down was used. Thereby, the low-pressure side condensate flowing down along the corrugated plate 40 can be dispersed and refined, and the high-pressure side steam can also pass between the corrugated plates 40. Therefore, the gas-liquid contact area between the high-pressure side steam and the low-pressure side condensate can be increased.
- the manufacturing cost can be reduced by using (processing) the existing punching metal material.
- Multi-stage pressure condenser Low pressure condenser (low pressure chamber) 4 Pressure bulkhead 5 Low pressure side cooling pipe group (cooling pipe group) 6 Reheating chamber 8 Hole 9 Tray (receiving member) 10 Corrugated plate (plate-like member) 11 Steam duct (high-pressure side steam introduction means) 22 High pressure condenser (high pressure chamber) 41 porous
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Abstract
Description
高圧および低圧の復水器からなる多段圧復水器1のうち低圧側復水器2は、低圧側胴3の長手方向を上方と下方とに仕切っている多孔8を有している圧力隔壁4と、低圧側胴3の上方側に設けられて冷却水が導かれる低圧側冷却管群5と、低圧側胴3の下方に位置する再熱室6とを主に備えている。
また、特許文献2には、頂点を上に向けた山形鋼や、螺旋状のエレメントを圧力隔壁から吊下げることが開示されている。
さらに、特許文献3には、低圧側胴の長手方向に延在する円筒形状液膜を圧力隔壁から再熱室内に吊下げることが開示されている。
本発明の第一の態様に係る多段圧復水器は、圧力が異なる複数の室と、低圧側の該室である低圧室を上下方向に分割する複数の孔を有する圧力隔壁と、該圧力隔壁によって仕切られた前記低圧室の上部に設けられて、冷却水が導入されて前記低圧室に導かれた低圧側蒸気と熱交換することにより該低圧側蒸気を低圧側復水に凝縮する冷却管群と、前記圧力隔壁によって仕切られた前記低圧室の下部であって、前記圧力隔壁の前記孔から流下する前記低圧側復水が溜まる再熱室と、高圧側の前記室である高圧室内の高圧側蒸気を前記再熱室に導入する高圧側蒸気導入手段と、前記圧力隔壁の下方には、該圧力隔壁の前記孔から流下する前記低圧側復水の流下方向に沿って互いに平行に配設される複数の板状部材と、を備え、各該板状部材は、前記低圧側復水の流下方向の断面が少なくとも1つの凹凸形状を形成するものである。
また、多孔を備えている板状部材には、既存パンチングメタル材を利用(加工)することで、製造コストも抑えられる。
以下、本発明に係る多段圧復水器について図1に基づいて説明する。
図1には、本実施形態に係る多段圧復水器の概略構成図が示されている。
図示の多段圧復水器1を有している蒸気タービンプラント(図示せず)は、蒸気タービン(図示せず)と、多段圧復水器1と、ボイラ(図示せず)とから主に構成されている。
低圧側復水器2内に設けられている低圧側冷却管群5に冷却水として、例えば、海水が供給される。低圧側冷却管群5に供給された海水は、図示しない連結管から高圧側復水器22の高圧側冷却管群25に送出される。高圧側冷却管群25に送出された海水は、図示しない排出管から排出される。
圧力隔壁4の孔8から流下する低圧側復水の流下方向に沿って互いに平行に配設されている100枚(複数)の波板(板状部材)10を圧力隔壁4の下方に設けて、これら各波板10の低圧側復水の流下方向の断面が複数(少なくとも1つ)の凹凸形状を形成するようにすることとした。これにより、圧力隔壁4の孔8から流下する低圧側復水が波板10と接触する面積を増加させることができる。そのため、再熱室6に導入される高圧側蒸気と低圧側復水との気液接触時間を増加させることができる。したがって、多段圧復水器1の全体的な大きさを変えることなく、再熱効率を容易に増加させることができる。
本実施形態の多段圧復水器およびこれを備えている蒸気タービンは、波板間の距離が可変である点で、第1実施形態と相違しその他は同様である。したがって、同一の構成については、同一の符号を付してその説明を省略する。
波板(板状部材)間の距離を可変にすることによって、波板間に形成される低圧側復水の流下液膜厚さを調整して流下する低圧側復水を両波板に接触させると共に、流下速度を制御することができる。そのため、高圧側蒸気と低圧側復水との気液接触時間および接触面積を増加させることができる。したがって、多段圧復水器の大きさを変えることなく、再熱効率を増加させることができる。
本実施形態の多段圧復水器およびこれを備えている蒸気タービンは、波板が流下する低圧側復水に向かって開口するポケット部を有する点で、第1実施形態と相違しその他は同様である。したがって、同一の構成については、同一の符号を付してその説明を省略する。
波板20は、低圧側復水の流下方向の断面が交互に複数(少なくとも1つ)の山谷を形成している凹凸形状(ジグザグ形状)を成しており、かつ、図2に示すように、凹凸形状の凸部には、波板20の表面に沿って流下する低圧側復水に向かって開口しているポケット部21を有している。
流下する低圧側復水に向かって開口しているポケット部21を備えている波板(板状部材)20を用いることとした。これにより、波板20に沿って流下した低圧側復水を一旦ポケット部21に溜めることができる。そのため、ポケット部21において低圧側復水を攪拌させて流下することができる。したがって、高圧側蒸気と低圧側復水との気液接触面積を増加させることができる。
本実施形態の多段圧復水器およびこれを備えている蒸気タービンは、波板が設けられている圧力隔壁の一部が下方に窪んでいる点で、第1実施形態と相違しその他は同様である。したがって、同一の構成については、同一の符号を付してその説明を省略する。
圧力隔壁34は、波板(板状部材)10が設けられている一部34aが下方に窪んで復水だまり37を形成している。圧力隔壁34と低圧側胴(図示せず)の底面との距離が例えば1000mmとされているうち、圧力隔壁34の一部34aは、例えば、約500mm下方に窪むように形成されている。
圧力隔壁34のうち下方に波板(板状部材)10が設けられている圧力隔壁34の一部34aを下方に窪ませることとした。そのため、圧力隔壁34の上方に貯まる低圧側復水が貯水する復水だまり37の容積を増加させることができる。また、下方に圧力隔壁34の一部34aが窪むことによって、圧力隔壁34の一部34aと再熱室6の底面との距離が短くなるが、圧力隔壁34の一部34aの下方に設けられている波板10が複数(少なくとも1つ)の凹凸形状を有するため、気液接触時間を維持することが可能となる。したがって、高圧側復水器(高圧室)と低圧側復水器(低圧室)2との圧力差が大きい場合における低圧側冷却管郡(冷却管群)の水没を防止すると共に、多段圧復水器(図示せず)の全体的な大きさを変えることなく再熱効率を維持することができる。
本実施形態の多段圧復水器およびこれを備えている蒸気タービンは、波板に多孔を有する点で、第4実施形態と相違しその他は同様である。したがって、同一の構成については、同一の符号を付してその説明を省略する。
波板40は、低圧側復水の流下方向(図4の白抜きした矢印で示す)の断面が交互に複数(少なくとも1つ)の山谷を形成している凹凸形状(ジグザグ形状)を成しており、かつ、図4に示すように、凹凸形状面に多孔41を有している。
波板40の多孔41に流下した低圧側復水は、隣接している波板40面で、分散されて微細化される。また高圧側蒸気も図4の点線の矢印で示すように、多孔41を通過する。そのため、低圧側復水と高圧側蒸気との接触面積が増加する。これにより、良好な熱伝達が行われて波板40を流下する低圧側復水を効率的に昇温することができる。
流下する低圧側復水に向かって多孔41を備えている波板(板状部材)40を用いることとした。これにより、波板40に沿って流下した低圧側復水を分散、微細化することができ、高圧側蒸気も波板40間を通過することができる。そのため、高圧側蒸気と低圧側復水との気液接触面積を増加させることができる。
多孔41を備えている波板40には、既存パンチングメタル材を利用(加工)することで、製造コストも抑えられる。
2 低圧側復水器(低圧室)
4 圧力隔壁
5 低圧側冷却管群(冷却管群)
6 再熱室
8 孔
9 トレイ(受け部材)
10 波板(板状部材)
11 蒸気ダクト(高圧側蒸気導入手段)
22 高圧側復水器(高圧室)
41 多孔
Claims (7)
- 圧力が異なる複数の室と、
低圧側の該室である低圧室を上下方向に分割する複数の孔を有する圧力隔壁と、
該圧力隔壁によって仕切られた前記低圧室の上部に設けられて、冷却水が導入されて前記低圧室に導かれた低圧側蒸気と熱交換することにより該低圧側蒸気を低圧側復水に凝縮する冷却管群と、
前記圧力隔壁によって仕切られた前記低圧室の下部であって、前記圧力隔壁の前記孔から流下する前記低圧側復水が溜まる再熱室と、
高圧側の前記室である高圧室内の高圧側蒸気を前記再熱室に導入する高圧側蒸気導入手段と、
前記圧力隔壁の下方には、該圧力隔壁の前記孔から流下する前記低圧側復水の流下方向に沿って互いに平行に配設される複数の板状部材と、を備え、
各該板状部材は、前記低圧側復水の流下方向の断面が少なくとも1つの凹凸形状を形成する多段圧復水器。 - 互いに平行に配設される前記板状部材間の距離が可変である請求項1に記載の多段圧復水器。
- 前記板状部材は、多孔を備える請求項1または請求項2に記載の多段圧復水器。
- 前記板状部材は、該板状部材に沿って流下する前記低圧側復水に向かって開口するポケット部を備える請求項1から請求項3のいずれかに記載の多段圧復水器。
- 前記板状部材の下方には、該板状部材から流下した前記低圧側復水を貯めてオーバーフローさせる受け部材を設ける請求項1から請求項4のいずれかに記載の多段圧復水器。
- 前記圧力隔壁は、前記板状部材が設けられる一部が下方に窪んでいる請求項1から請求項5のいずれかに記載の多段圧復水器。
- 請求項1から請求項6のいずれかに記載の多段圧復水器を備えた蒸気タービンプラント。
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EP11859853.1A EP2682701B1 (en) | 2011-02-28 | 2011-09-16 | Multistage pressure condenser and steam turbine plant equipped with same |
CN201180037157.6A CN103038594B (zh) | 2011-02-28 | 2011-09-16 | 多级压力冷凝器及具备该多级压力冷凝器的蒸汽涡轮设备 |
KR1020137001159A KR20130054316A (ko) | 2011-02-28 | 2011-09-16 | 다단압 복수기 및 이것을 구비한 증기 터빈 플랜트 |
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WO2014126154A1 (ja) * | 2013-02-13 | 2014-08-21 | 三菱日立パワーシステムズ株式会社 | 復水器、これを備えている多段圧復水器、復水器に用いる再熱モジュール |
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JP5885990B2 (ja) * | 2011-10-13 | 2016-03-16 | 三菱重工業株式会社 | 多段圧復水器及びこれを備えるタービンプラント |
US9488416B2 (en) | 2011-11-28 | 2016-11-08 | Mitsubishi Hitachi Power Systems, Ltd. | Multistage pressure condenser and steam turbine plant having the same |
US11369966B2 (en) * | 2015-09-18 | 2022-06-28 | Arizona Board Of Regents On Behalf Of Arizona State University | Layered structure for improved sealing of microwell arrays |
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JP5721471B2 (ja) | 2015-05-20 |
KR20130054316A (ko) | 2013-05-24 |
US9188393B2 (en) | 2015-11-17 |
CN103038594A (zh) | 2013-04-10 |
EP2682701B1 (en) | 2016-06-15 |
EP2682701A1 (en) | 2014-01-08 |
EP2682701A4 (en) | 2015-03-25 |
JP2012180956A (ja) | 2012-09-20 |
US20120216541A1 (en) | 2012-08-30 |
CN103038594B (zh) | 2015-09-30 |
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