NZ606822B2 - Direct contact condenser for steam turbine - Google Patents

Abstract

Improvements to a direct contact condenser which can prevent cooling water sprayed from spray nozzles from reaching the turbine blades of an axial-flow turbine which can damage the turbine blade. Direct contact condenser consists of three major sections which are attached directly to the turbine; an exhaust gas inlet part (11); a steam cooling chamber (12); and a water storage part (13). The steam cooling chamber includes a first cooling water spraying mechanism (21) which sprays the cooling water from a perpendicular to a downstream direction which prevents water on the blades of the turbine; a second cooling water spraying mechanism (30) which sprays in all directions; and a non-condensable gas chamber. n exhaust gas inlet part (11); a steam cooling chamber (12); and a water storage part (13). The steam cooling chamber includes a first cooling water spraying mechanism (21) which sprays the cooling water from a perpendicular to a downstream direction which prevents water on the blades of the turbine; a second cooling water spraying mechanism (30) which sprays in all directions; and a non-condensable gas chamber.

Description

DESCRIPTION DIRECT CONTACT CONDENSER FOR STEAM TURBINE Technical Field The present invention relates to a direct contact condenser for a steam turbine which.directly sprays g water to a turbine exhaust gas containing steam and non—condensable gases both exhausted from the steam e to cool and condense the steam turbine.

Background Art [0002} A direct contact condenser for an flow exhaust turbine, which is one type of the direct contact ser for a steam turbine, causes turbine exhaust gases exhausted fronlthe axial—flow exhaust turbine to directly contact.with cooling water, thereby condensing steam. Hence, it is important in performance how to increase the contact area.of the cooling water in contact he steam, and the cooling water is discharged and atomized to a space through a spray nozzle.

Moreover, it is important to optimize the layout of structural objects that disturb the flow path of the steam, and to minimize the pressure loss of the steam flow.

An example conventional condenser for an axial-flow exhaust turbine includes an exhaust duct that connects an open end of the steam turbine with the condenser, causes the exhaust exhausted from the steam turbine in a substantially ntal direction to change a flow direction in the downward direction through the exhaust duct, and causes the exhaust to flow in the condenser from the upper space thereof . er, a structure is known which has a buter ed in the condenser in the flow direction of the exhaust and a spray water preventer in the exhaust duct (see, for example, Patent Document 1).

As another known structure, there is a condenser that includes:aninletpartthatintroducesturbineexhaustgases containing steam and non—condensable gases in a steam cooling chamber in a substantially horizontal direction; a plurality of first spray nozzles disposed in the steam cooling chamber and connected to a plurality of spray pipings in the introduced direction of the turbine exhaust gases, respectively, to spray cooling water to the turbine exhaust the bottom of the steam gases; and a water storage ed at cooling chamber for g condensed water condensed from the steam through.the ng of the cooling water (see, for example, Patent Document 2).

Prior Art Documents Patent Documents Patent Document 1: JP 3962 A Patent Document 2: JP 2010—270925 A Summary of the ion Problem to be Solved According to the conventional example disclosed in Patent Document 1, the turbine exhaust gases rged by the axial-flow exhaust turbine in the horizontal direction are guided in the vertical direction through the exhaust duct, and are supplied to the condenser from the upper space thereof.

Cooling water supply pipings are disposed in the downward flow direction.of the turbine exhaust gases in the condenser, and the cooling water supply pipings are ed with respective nozzle bodies to spray the cooling water in the ion orthogonaltx>theflowdirectidnoftheturbineexhaustgases.

At the uppermost nozzle body, a nozzle close to the axial—flow exhaustturbinehasaaflatfan—shapedsplashzone,andnozzles having a circular cone—shaped splash zone are disposed in the 2O other directions . Furthermore, the exhaust duct is ed witkla spray water preventer. Accordingly, the nozzle close totheaxial—flowexhaustturbinehasaiflatfan—shapedsplash zone which prevents the spray water from ing toward the axial—flow exhaust turbine, and the exhaust duct is provided with the spray water preventer, so that it is possible to prevent the turbine blade of the axial-flow exhaust turbine from colliding with the spray water and being damaged. There which avoids are, however, unsolved problems that a structure the spray water from colliding with the turbine blade of the axial—fltmzexhaust turbine becomes complex, and.the flows of the turbine exhaust gases are disturbed since the spray water preventer is provided in the exhaust duct.

On.the other hand, according to the prior art disclosed in Patent Document 2, the turbine t gases exhausted.by the axial—flow t turbine in the horizontal direction are introduced in the condenser ed in the horizontal direction, and the plurality of spray pipings in the introduced direction of the turbine exhaust gas flow are ted.with.the plurality of first spray nozzles, thereby spraying the cooling water in the direction orthogonal to the introduced direction of the turbine t gas flow.

However, since no rmeasure for the reverse flow<3f the spray water is employed, there is an unsolved problem that part of the cooling water sprayed from the spray nozzles in the circular conical shape may reach the axial—flow exhaust turbine, and may damage the turbine blade.

[0008] Hence, the present invention has been made in view of the above—explained unsolved problems, and it is an object ofthepresentinventiontogmovideamulectcontactcondenser for a steam turbine which can surely prevent g water sprayed from spray nozzles from reaching the turbine blade of an axial-flow turbine, while introducing turbine exhaust gases ted by the steam turbine in the horizontal direction to cool such gases.

Alternatively, it is an object of the invention to at least provide the public with a useful .

Solution to the Problem

[0009] To lish at least one of the above objects, there is provided a direct contact condenser for a steam turbine, the direct contact condenser comprising: an exhaust gas inlet part configured to introduce a turbine exhaust gas containing steam and a non-condensable gas of the steam turbine in a horizontal direction; a steam cooling chamber configured to spray cooling water to the turbine exhaust gas introduced through the exhaust gas inlet part to cool the turbine exhaust gas; and a water storage which is disposed at a bottom of the steam cooling chamber and which stores sed water cooled from the steam and the cooling water, the steam cooling chamber comprising: a first cooling water spraying mechanism which is disposed at the exhaust gas inlet part side and which sprays the cooling water within a range restricted to a downstream direction of the turbine exhaust gas; and a second cooling water ng mechanism which is disposed at a downstream side of the first cooling water ng ism and which sprays the cooling water to the turbine t gas in all directions.

[0010] ing to the steam turbine direct contact condenser of a second aspect of the present invention, the first cooling water spraying mechanism may comprise a plurality of cooling (followed by page 5a) water spray pipings extend in a direction orthogonal to a guiding direction of the turbine t gas, in [followed by page 6] - 5a - communicationvdthiicoolingwatersupplypiping,andareeach formed with a ity of spray nozzles in a lengthwise direction.

According to the steam turbine direct contact condenser of a third¢aspect.of the present invention, the first cooling water spraying mechanism may comprise: a coupling piping configured to couple the ing cooling water spray pipings in parallel with the turbine exhaust gas, in a flow path of the turbine exhaust gas; and a ity of spray nozzles formed on a bottom side of the coupling piping.

According to the steam e direct contact condenser of a fourth aspect of the present ion, the plurality of spray nozzles formed on the coupling piping may spray the cooling water in at least either one of the downward direction and an obliquely downstream side.

According to the steam turbinetiirect contact condenser of a fifth aspect of the present invention, the second cooling water spraying mechanism may comprise a plurality of cooling 2O water spray pipings extend in a direction orthogonal to a guideddirectrnloftheturbineexhaustgas,incommunication with a cooling water supply piping, and each formed with a plurality of spray s in a lengthwise direction.

According to a sixth aspect of the present invention, the steam turbine direct contact condenser may further comprise: a gas cooling chamber which is formed at least either one of a downstream side and a side of the second cooling watersprayingnechanism, amdwhichcausesarxnhcondensable gas remaining in the e exhaust gas to which the cooling water is sprayed to flow, and the gas cooling chamber ses a plurality of third cooling water spraying mechanisms which are formed in communication at either one of the downstream side and the side of the second cooling water sprayinglnechanism, and.which.spray the cooling water to the non—condensable gas remaining in the turbine exhaust gas.

According to a seventh.aspect of the present invention, the steam turbine direct contact condenser may further comprise a ion plate having an opened bottom and disposed between the second cooling water spraying mechanism and the third g water spraying mechanisms.

According to the turbine<flirect contact condenser of an eighth aspect of the present invention, the water storage m.provided.with.a connection port at a bottom of the water storage connected to a condensate pump, controls a water level n a normal operation water level where the connection port is completely below the water level and a maximum operation water level higher than the normal operation water level during a successive operation of the sate pump, and has a water storage capacity set in such a way that the water level does not exceed an abnormal maximum water level lower tharla.bottom‘of the exhaust gas inlet part even if the water level exceeds the maximum operation water level due to a raise in the water level by remaining cooling water when the condensate pump abnormally stops. ageous Effects of the Invention According to the present invention, the turbine exhaust gases ning steam and ndensable gases ted by the steam turbine in the horizontal direction are introduced into the steam cooling chamber in the horizontal direction through the exhaust gas inlet part. In the steam cooling chamber, there are provided: the first cooling water sprayinglnechanisnlhaving the spray direction.of the cooling water restricted within the spray range from a side to the downstream side of the turbine t gases; and the second cooling water spraying mechanism disposed at the downstream side of the first cooling water spraying mechanism and spraying the cooling water to the turbine exhaust gases in all directions. Accordingly, there is anhadvantage that can prevent the sprayed cooling water from reaching the steam turbine, while cooling the turbine exhaust gases in the original exhausted direction.

Brief Description of the Drawings is a sectional view illustrating a direct contact condenser for a steam turbine according to a first embodiment of the present ion; is a plan View with a top panel removed from the condenser in is an enlarged plan view of a first cooling water spraying mechanism; is a cross-sectional view illustrating a direct contact condenser for a steam turbine according to a second embodiment of the present invention; is a plan view with a top panel removed from the condenser in is a plan view illustrating a case in which the steam e direct contact condenser of the present ion is d to a side exhaust steam turbine; and is a plan view illustrating a case in which the steam turbine direct contact condenser according to the present invention is applied to a both-side exhaust steam turbine.

Description of Embodiments Unless the context clearly requires otherwise, throughout the ption and the claims, the words “comprise”, “comprising”, and the like are to be construed in an inclusive sense as opposed to an exclusive or exhaustive sense; that is to say, in the sense of ding, but not limited to". [0016a] An explanation will be given of embodiments of the t invention with reference to the accompanying drawings. (followed by page 9a) is a cross-sectional view illustrating a case in which a direct contact condenser for a steam turbine of the present invention is applied to an axial-flow exhaust steam turbine according to a first embodiment. is a plan view with a top plate d from the condenser.

In those figures, reference l 1 indicates an axial-flow exhaust steam turbine, and this axial-flow exhaust steam turbine 1 includes a plurality of rotor blades 3 fixed [followed by page 10] - 9a - (followed by page 10) to a turbine shaft 2 held in a rotatable manner substantially horizontally; and.a plurality of stator blades 5 provided in a casing 4 so as to face the respective rotor blades 3. A rotational shaft 7 of a power generator 6 is d with.an end of the turbine shaft 2 protruding to the exterior of the casing 4.

Turbine exhaust gases containing steam and non—condensable gases exhausted by the axial—flow exhaust steam turbine 1 from the large—diameter end of the casing 4 in the horizontal ion are guided to a steam turbine direct contact condenser 10.

This steam turbine direct contact condenser 10 includes an exhaust gas inlet part 11 that introduces, in the horizontal direction, the turbine exhaust gases exhausted by the axial—flow exhaust steam e 1 from the casing 4 in the ntal direction, a steam cooling chamber 12 which is disposed at the downstream side of the exhaust gas inlet part 11.and.which.sprays cooling water to the turbine exhaust introduced in the horizontal direction to cool such gases gases, a water storage 13 which.is disposed.at the bottom of the steam g chamber 12 and which stores condensed moistures cooled from the steam, and a gas cooling chamber 14 provided at the downstream side of the steam g chamber 12.

The exhaust gas inlet part 11 is coupled.with the casing 4 of the axial—flow exhaust steam turbine 1 through a bellows 11a, and is formed in a relatively short duct shape in the axial direction which introduces the turbine exhaust gases in the horizontal direction by a horizontal top plate 11b, a right downward—sloping bottom plate 11c, and front plates lld and lie spreading in a tapered shape.

As illustrated in and the steam cooling chamber 12 es a first cooling water sprayinglnechanism 21 disposed at the exhaust gas inlet part 11 side, and a second cooling water spraying mechanisn130 linked.to the downstream side of the first cooling water spraying mechanism 21.

The first cooling water spraying ism 21 includes a.water supplylnain piping 22 which.is disposed.at the center in the back—and-forth direction at the bottom side of the steam cooling chamber 12 and which supplies the cooling water, and a total of six spray pipings 24, which are three lines multipliedlnrtworows(whenviewedi11aplanarview),coupled directly or via branched.pipings 23 to the water supply main piping 22. The spray pipings 24 extend ally in a ion.orthogonal to the turbine exhaust gases guided in the horizontal direction.

Each spray piping 24 is formed with five spray nozzles at tive upper locations in contact with the turbine exhaust gases with a predetermined interval .

As illustrated in those spray nozzles 25 are ed on an outer circumferential surface that is a backward side relative to a back—and—forth ntal line Ll passing through the center point of the spray piping 24 in such a way that the coolingwatersprayingdirectionbecomesthedownstreamside.

That is, the spray nozzles 25 are, for example, formed so as to extend on the lines at i 45 degrees in the radial direction across a horizontal line L2 orthogonal to the back—and—forth ion horizontal line Ll at the center points of the spray pipings 24. Those spray nozzles 25 spray the cooling water in a spray zone of a circular conical shape at a wide angle of, for example, 100 degrees. Hence, the ion of the sprayed cooling water is cted within a range from the side of the spray piping 24 to the flow direction of the turbine exhaust gases, and no cooling water is sprayed in the direction toward the rotor blades 3 of the steam turbine l.

The attachment angle of the spray nozzles 25 and the angle of the sprayed cooling water are not limited to the above ned examples, and the attachment angle and the angle of the sprayed g water can.be set arbitrary as long as no cooling water is sprayed toward the turbine 1.

Moreover,asjllustratediilFIG.J” therespectivespray pipings 24 adjoining to each other in the flow direction of the turbine exhaust gases are coupled er through a coupling piping 26 at an area where no spray nozzle 25 is formed.

Likewise,thespraypipin924an:theoutermostdownstreamside is coupled.witk1a spray piping 31 of the second.cooling water sprayinguechanimnzlfacingwiththatspraypiping24through a coupling piping 27. Furthermore, spray nozzles 28 that spray the cooling water downward or to the obliquely downstream side are formed at the lower faces of the respective coupling pipings 26 and 27. [00221 As illustrated in the second cooling water spraying mechanism 30 includes a total of 12 spray pipings 31 which are provided at respective intersections of a matrix of four rows ining a predetermined interval in the flow direction of the turbine exhaust gases when viewed in a planar view, and three lines in the back—and—forth direction, and which intersect with the flow direction of the turbine exhaust gases so as to extend in the vertical direction. The spray piping 31 of each row is directly coupled with the water supply main piping 22 or through a ed piping 32 and the cooling water is supplied to the spray piping. The spray nozzles 33 are formed on five levels in each of those spray pipings 31 at the upper n side in contact with the e exhaust gases with a predetermined interval. As illustrated in four spray nozzles 33 are formed in the circumferential direction of each spray piping 31 at an interval of 90 degrees.

Moreover, a spray zone of a circular conical shape is formed from each spray nozzle 33 at a wide angle of, for example, 100 degrees, and sprays the cooling water within this spray zone. Hence, the cooling water can be sprayed in the all directions around the spray piping 31. In this case, also, the ment angle of the spray nozzle 33 and the spray angle can be set arbitrary.

The gas cooling chamber 14 is partitioned by a partition plate 40 having a bottom opened and in communication with the steam cooling chamber 12, and a third cooling water spraying mechanimnthatspraysthecoolingwatertotheturbineexhaust gases ning non—condensable gases and accompanying steam) introduced through the partition plate 40 from the upper space is provided.

As illustrated in the third cooling water spraying mechanism 41 has a ng piping 42 which is placed at the center so as to be coupled.with the water supply main piping 22 and which extends in the vertical direction. A cooling water reservoir 43 is in communication with the upper end of the coupling piping 42. The cooling water reservoir 43 is provided with spray nozzles 44 which are formed on the bottom face of the cooling water reservoir 43 at a ermined interval and which spray the cooling water to the lower space. Moreover, the cooling water reservoir 43 is formed with openings 46 which are disposed at respective ons where no spray nozzle 44 is present and which allow the turbine exhaust gases to pass through to a gas exhaust part 45 above the cooling water reservoir 43 .

The gas exhaust part 45 is formed with t ports 47 that exhaust the turbine exhaust gases in the back—and—forth direction and in the right direction.

Furthermore, the water storage 13 is formed so as to sag downward below the steam g chamber 12 and the gas g chamber 14, and a connection port 51 connected.with a condensate pump 50 at the exterior is formed at the center part of the bottom of the water storage. The water storage 13 controls the water level so as to be located n a normal operation water level where the connection port is completely below the water level and a maximum operation water level higher than the normal operation water level, while the condensate pump 50 is successively operating.

A water storing volume is set in such a way that the water level does not exceed an abnormal maximum water level lower than the bottom of the exhaust gas inlet part even if the water level s the m operation water level due to the raisedwaterlevelbythecoolingwaterpassingthroughduring a closing time of, for example, changing the state of the cooling water supply valve (unillustrated) provided in the watersupplymainpiping221x>aclosedstateandtheremaining cooling water in the water supply main piping 22 the branched pipings 23, the spray pipings 24, the coupling pipings 26 and 27, the spray pipings 31, the coupling piping 42 all subsequent to the cooling water supply valve, and the cooling water reservoir 43 when.the condensate pump 50 is abnormally stopped due to a blackout or a breakdown, etc.

Next, an explanation will be given of an operation according to the first ment.

When.both axial-flow exhaust steam turbine l and steam edirectcontactcondenserlOare:UItheoperatingstate, the turbine exhaust gases containing the steam exhausted.by the axial—flow exhaust steam turbine 1 from the casing 4 in the horizontal direction and the non—condensable gases are introducede1the steam.turbine1direct contact condenser 10.

In.the turbine<iirect contact.condenser 10, the turbine exhaust gases are introduced through the exhaust gas inlet part 11, while maintaining the flow ion in the horizontal direction, and the e exhaust gases are ed to the steam cooling chamber 12 at the downstream side.

[0027] Thefirstcoolingwatersprayingmechanimn21iséfisposed at the exhaust gas inlet part 11 side in the steam cooling chamber 12. The first g water spraying mechanism 21 has spray nozzles 25 formed at respective back sides of the spray pipings 24 which traverse the turbine exhaust gases and extend in the al direction. Hence, the spray zone of thecoolingvmtersprayedfromeachspraynozzleisrestricted to a spray area, which is arranged behind the horizontal line Ll interconnecting the center points of the front and back spray pipings 24 and is arranged at the downstream side of the turbine exhaust gases from.respective sides of the spray Accordingly, no cooling water sprayed from the spray nozzle 25 is directed.to the rotor blades 3‘of the axial—flow exhaust steam turbine 1, and it is unnecessary to provide an additional mechanism that suppresses a reverse flow of the sprayed cooling water. Hence, the turbine exhaust gases exhausted by the axial—flow exhaust steam turbine 1 can be smoothly introduced into the first cooling water spraying mechanism 21 with little piping resistance.

At this time, it is unnecessary that the spray'direction of the cooling water sprayed from the spray nozzles 25 is strictly limited to a direction from the direction orthogonal to the flow direction of the turbine exhaust gases to the downstream side. Since the cooling water is pushed back by the force of the flowing turbine exhaust gases, the cooling water may be sprayed slightly toward the am side.

The cooling water sprayed from the first g water spraying mechanism 21 causes part of steam in the turbine exhaust gases to be cooled and to become condensed water, and the condensed water is stored in the water storage 13. In the first cooling water spraying ism 21, since the coupling s 26 and 27 are also provided with spray nozzles 28 in addition to the spray pipings 24 disposed in theverticaldirection,thecoolingefficiencycflftheturbine exhaust gases can be improved by what ponds to the spray nozzles 28. Moreover, since the spray direction of the cooling water d from the spray s 28 is set to an obliquely downward direction, it becomes possible to surely the axial—flow suppress a reverse flow of the cooling water to exhaust steam turbine l.

The turbine exhaust gases that have passed through the first cooling water spraying mechanism 21 enter the second cooling water spraying mechanism 21, and the cooling water is d from the five levels of spray nozzles 33 ed on the 12 spray s 31 in all directions around each spray piping31. Accordingly,thesteamleftj11theturbineexhaust gases is cooled and most of the cooled steam becomes condensed water and stored in the water storage 13.

Most of the steam is eliminated as condensed water in the second.cooling water spraying mechanism 30, and.thus the remainingnon—condensablegasesandaccompanyingstewninthe turbine t gases are introduced in the gas cooling chamber 14 through the opening at the bottom of the partition plate 40. Since the cooling water is sprayed from.the spray s 44 formed on the bottom face of the cooling water reservoir 43 formed above the gas cooling chamber 14, the non—condensable gases are cooled, guided to the gas exhaust part 45 through the openings 46 formed in the cooling water reservoir 43, and exhausted to the exterior through the respective exhaust ports 47.

[0032] On the other hand, the water level of the condensed water and the cooling water stored in the water storage 13 is controlladbetweentherwrmaloperationwaterlevelwherethe tion port 51 of the condensate pump 50 becomes completely below the water level and the maximum operation water level higher than the normal operation water level through successive operation of the condensate pump 50.

In this state, when the condensate pump 50 abnormally stops due to a blackout or a breakdown, etc . the cooling water supply valve (not rated) provided in the water supply ping22:Hsautomaticallyclosed. r,thecooling water supplied during the closing time until the cooling water supply valve is fully Closed, and the remaining cooling water in the water supply main piping 22, the branched pipings 23, the spray pipings 24 the coupling pipings 26 and 27 the spray , , pipings 31, the coupling piping 42, and the g water reservoir 43 all subsequent to the cooling water supply valve are stored in the water storage 13.

At this time, the water storage capacity of the water storage 13 is set in such a way that the abnormal maximum water level does not reach the bottom of the exhaust gas inlet part 11 even if the water storage capacity of the water storage 13 absorbs the increased amount of the cooling water when the sate pump 50 is stopped. Accordingly, it becomes possible to surely suppress a reverse flow of the cooing water to the axial—flow exhaust steam turbine 1.

Next, an explanation will be given of a second embodiment of the present invention with reference to and According to the second embodiment, the gas g chamber 14 is provided at the side faces of the steam cooling chamber 12 instead of a case in which the gas cooling chamber is provided at the downstream side in the flow direction of the turbine exhaust gases of the steam cooling chamber 12.

That is, according to the second embodiment, as illustrated in and an end of the second cooling water spraying mechanism 30 in the steam cooling chamber 12 in.the flow<directicu1of the turbine exhaust gases is blocked off. Instead.of this structure, the gas g chambers 14 are in communication with both back and forth side faces facing the spray pipings 31 of the two rows at the right end of the second g water spraying mechanism 30 through the above-explained ion plate 40. The other structures are the same as those of the above-explained first embodiment.

The cooling water is supplied to the front and rear gas cooling chambers 14 from the water supply main piping 22 through branched pipings 60.

Also in the second ment, most of the steam contained in the turbine t gases is cooled by the cooling water sprayed from the spray nozzles 33 of the second cooling water spraying mechanism 30 in the steam cooling r 12 in all directions, becomes condensed water, and is stored in the water storage 13. The steam is eliminated through the second cooling water spraying mechanism 30, and the remaining non-condensable gases and associated steam are cooled in the front and rear gas cooling chambers 14 at both sides, and are exhausted to the exterior through the gas t part 45. Also in the second embodiment, the same advantages and effects as those of the above—explained.first embodiment are achievable.

In the first and second embodiments, the explanations have been given of the case in which the turbine exhaust gases having the steam ted from the steam cooling chamber 12 and eliminated are introduced into the gas cooling chamber 14 to cool the turbine exhaust gases. The present invention is, however, not limited to this case, and when the turbine t gases cooled by the second cooling water spraying mechanism 30 has a low temperature, the gas cooling chamber 14 can be eliminated.

Moreover, in the first and.second.embodiments, although. the explanations have been given of the case in which the steam turbine direct contact condenser 10 of the present invention is d to the axial—flow exhaust steam turbine 1, the present invention is not limited to this case. That is, as illustrated in the steam turbine direct contact condenser 10 of the t invention can be applied to a side t steam turbine 70 .

As illustrated in the steam e direct contact condenser 10 of the present invention steam can be applied to each of both sides of both—side exhaust turbine 71.

Industrial Applicability According to the present invention, there is provided a direct contact condenser for a steam turbine which can surely'prevent cooling water sprayed from spray'nozzles from reaching the turbine blade of an flow turbine, while introducing the turbine exhaust gases exhausted by the steam turbine into the horizontal direction to cool such gases.

Reference Signs List 1 Axial—flow exhaust steam turbine 2 Turbine shaft 3 Rotor blade 4 Casing Stator blade 6 Power generator Steam turbine direct contact condenser 11 Exhaust gas inlet part 12 Steam cooling chamber 13 Water e 14 Gas cooling chamber 21 First cooling water spraying mechanism 22 Water supply main piping 23 Branched piping 24 Spray piping 25 Spray nozzle 26, 27 Coupling piping 28 Spray nozzle Second cooling water ng mechanism 31 Spray piping 32 Branched piping 33 Spray nozzle 41 Third cooling water spraying mechanism 42 Coupling piping 43 g water reservoir 44 Spray nozzle 45 Gas exhaust part 50 Condensate pump 51 Connection port

Claims (9)

1. A direct contact ser for a steam turbine, the direct contact condenser comprising: 5 an exhaust gas inlet part configured to introduce a turbine exhaust gas containing steam and a non-condensable gas of the steam turbine in a horizontal direction; a steam cooling chamber configured to spray cooling water to the turbine exhaust gas introduced through the exhaust gas 10 inlet part to cool the turbine exhaust gas; and a water storage which is disposed at a bottom of the steam cooling chamber and which stores condensed water generated by cooling the steam, and the cooling water, the steam cooling chamber sing: 15 a first cooling water ng mechanism which is disposed at the t gas inlet part side and which sprays the cooling water within a range restricted to a downstream direction of the turbine exhaust gas; and a second cooling water spraying mechanism which sprays 20 the cooling water to the turbine t gas cooled by the first cooling water spraying mechanism in all directions.

2. The steam turbine direct contact ser according to claim 1, wherein the first cooling water ng 25 mechanism comprises a plurality of cooling water spray pipings extend in a direction orthogonal to a guiding direction of the turbine exhaust gas, in communication with a cooling water supply piping, and are each formed with a plurality of spray nozzles in a lengthwise direction.

3. The steam turbine direct contact condenser accordingtxaclahn2,whereinthefirstcoolingwaterspraying ism comprises: a coupling piping configured to couple the adjoining cooling water spray pipings in parallel with the turbine t gas, in a flow path of the turbine exhaust gas; and 10 a plurality of spray nozzles formed.on.a bottom side of the coupling piping.

4. The steam turbine direct contact condenser according to claim 3, wherein the plurality of spray nozzles 15 formed on the coupling piping spray the cooling water in at least either one of the rd direction and an obliquely downstream side.

5. The steam e direct contact condenser 20 according to any one of claims 1 to 4, wherein the second g water spraying mechanism comprises a plurality of cooling water spray pipings extend in a direction orthogonal to a guided direction of the turbine exhaust gas, in communication with a cooling water supply piping, and each 25 formed with a plurality of spray nozzles in a lengthwise direction.

6. The steam e direct contact condenser according to any one of claims 1 to 5, further comprising: a gas cooling chamber which is formed at least either 5 one of a downstream side and a side of the second cooling water spraying mechanism , and which causes a non-condensable gas remaining in the turbine exhaust gas to which the cooling water is d to flow, and wherein the gas cooling chamber comprises a plurality 10 of third cooling water spraying mechanisms which are formed in communication at either one of the ream side and the side of the second cooling water spraying mechanism, and which spray the cooling water to the ndensable gas remaining in the turbine exhaust gas.

7. The steam turbine direct contact condenser according to claim 6, further sing a partition plate having an opened bottom and disposed between the second cooling water spraying mechanism and the third cooling water 20 spraying mechanisms.

8. The steam e direct contact condenser according to any one of claims 1 to 7, wherein the water storage is provided with a connection port at a bottom of the water 25 storage, the connection port being connected to a condensate pump which controls a water level between a normal operation water level where the connection port is completely below the water level and a maximum operation water level higher than the normal operation water level during a successive operation of the sate pump, such that the water level does not exceed an abnormal maximum water level lower than a bottom of the exhaust gas inlet part even if the water level 5 s the maximum operation water level due to a raise in the water level caused by remaining cooling water when the condensate pump abnormally stops.

9. A direct contact condenser for a steam turbine 10 substantially as herein described with reference to any one of the embodiments shown in the accompanying