JP2020038015A - Condenser - Google Patents

Abstract

To enable efficient heat exchange even in a case where a temperature gradient occurs from an inflow part to an outflow part in a condenser.SOLUTION: A condenser 100 includes: a body shell container 110 which receives turbine exhaust exhausted from a steam turbine in a substantially horizontal direction as condenser internal gas and serves as a condenser internal gas passage; an inflow part 111 which couples the stream turbine to the body shell container 110; a coolant spray structure which sprays a coolant to an interior of the body shell container 110 and condenses the condenser internal gas; a discharge part of the condenser internal gas which is not condensed in the body shell container 110 to the outside of the body shell container 110; and a coolant recirculation structure 130 which is attached to the inner side of the body shell container 110 and has one or multiple circulation units 130a which receive the coolant reached and recirculate the coolant to the upstream side of flow of the condenser internal gas by gravity.SELECTED DRAWING: Figure 4

Description

  Embodiments of the present invention relate to a condenser for a steam turbine.

  In a power generation system using a Rankine cycle, a condenser is provided to reduce the pressure at the outlet of the steam turbine to achieve an increase in output. In the condenser, the condensable gas discharged from the steam turbine is brought into contact with a cooling unit or a cooling fluid, and the temperature is reduced to a saturation temperature of the gas, so that the condensable gas is liquefied.

  The liquefaction method used in the condenser includes a surface contact type in which a coolant flows through the inside of the hollow tube and condenses the gas on the outer surface of the hollow tube, and the coolant is directed to the gas using a spray nozzle or the like. There is a direct contact type that ejects.

  The former surface contact type is widely used in thermal power and nuclear power generation systems and the like, and the working fluid and the coolant are not mixed due to restrictions on the properties of the evaporator supply water. The latter is mainly used in a geothermal power generation system, and is excellent in heat transfer performance because mixing and heat exchange of steam and a coolant are performed without passing through a heat transfer tube.

  In the case of the direct contact type, the flow of gas and liquid inside the condenser varies depending on the positional relationship between the rotating shaft of the turbine and the condenser. When the turbine is located above the condenser, a generally downward gas flow field is formed inside the condenser, so that the coolant is accelerated downward by the force received from the gas flow and gravity. On the other hand, in the case of an axial exhaust system in which a condenser is provided on an extension of the turbine rotation shaft, the gas flow direction and the direction in which gravity acts are greatly different. In both configurations, the cooling liquid injected from the spray nozzle or the like directly falls into the hot well, or collides with the inner wall surface of the condenser and then flows down the wall surface to reach the hot well. Further, also in the side exhaust system in which a condenser is provided on the side of the turbine rotating shaft, the gas flow direction and the direction in which gravity acts are greatly different, and the relationship between the two is the same as in the axial exhaust system.

  The condenser is required to reduce the turbine outlet pressure. There is a close relationship between the turbine outlet pressure and the gas liquefaction capacity of the condenser.As a measure to enhance the capacity, the ribs on the inner wall inside the main body shell are formed along the flow direction of the exhaust steam from the gas inlet to the outlet. There is known a method of increasing a contact area between a member in a main body container and a turbine exhaust by providing the same.

JP 2013-155611 A

  As described above, a part of the injected coolant collides with the inner wall of the condenser and flows down on the wall. Generally, the coolant is injected at a temperature lower than the temperature of the gas in the condenser, and the temperature gradually increases while exchanging heat with the atmospheric gas. If the contact time between the ambient gas and the coolant is long enough, the coolant temperature rises close to the gas temperature. On the other hand, if the contact time is insufficient, the difference between the coolant temperature and the gas temperature becomes relatively large, and reaches the inner wall surface in the state of the supercooled liquid. At this time, heat exchange with the atmosphere gas continues even while flowing down on the inner wall surface, but when the distance between the wall arrival position and the hot well is small, there is a concern that a sufficient temperature rise will not be achieved.

  In geothermal power generation systems, it is necessary to consider the effects of non-condensable gases. Geothermal steam may include non-condensable gases such as carbon dioxide and hydrogen sulfide in addition to water vapor. When such a gas flows into the condenser, the concentration of the non-condensable gas gradually increases with the progress of condensation along the flow in the vessel. If the proportion of the non-condensable gas in the total gas increases, the partial pressure of water vapor decreases, and the gas temperature decreases. Since there is a correlation between the gas temperature drop amount and the condensation rate of water vapor, a temperature gradient is generated in the condenser from the inflow portion to the outflow portion.

  As described above, since the temperature of the coolant rises with the upper limit of the ambient gas temperature, the upper limit of the temperature of the coolant injected near the outlet is lower than that at the inlet. This feature is prominent in a direct contact type condenser combined with an axial exhaust turbine or a side exhaust turbine, and causes a reduction in heat exchange efficiency of the condenser.

  Therefore, an embodiment of the present invention aims to enable effective heat exchange even when a temperature gradient is generated from an inflow portion to an outflow portion in a condenser.

  In order to achieve the above object, the condenser according to the present embodiment receives a turbine exhaust discharged from a steam turbine in a substantially horizontal direction as a gas in the device, and a main body vessel serving as a flow path of the gas in the device, An inflow portion connecting the steam turbine and the main body container, a cooling liquid spraying structure for injecting a cooling liquid into the main body container and condensing the inside gas, and not condensing in the main body container The remaining portion of the gas inside the container is discharged to the outside of the main body container, and is attached to the inside of the main body container, receives the cooling liquid that has reached, and upstream of the flow of the gas inside the container by gravity. And a coolant reflux structure having one or more reflux units for reflux.

  According to the embodiment of the present invention, effective heat exchange can be performed even when a temperature gradient occurs from the inflow portion to the outflow portion in the condenser.

It is an elevation sectional view showing the composition of the condenser concerning a 1st embodiment. FIG. 2 is a cross-sectional view taken along line II-II of FIG. 1 illustrating a configuration of the condenser according to the first embodiment. FIG. 3 is a cross-sectional view taken along line III-III of FIG. 1 illustrating a configuration of the condenser according to the first embodiment. FIG. 4 is a cross-sectional view taken along line IV-IV of FIG. 2, illustrating a configuration of a cooling liquid reflux structure of the condenser according to the first embodiment. FIG. 5 is a cross-sectional view taken along line VV of FIG. 4 illustrating a cooling liquid reflux structure of the condenser according to the first embodiment. FIG. 6 is a cross-sectional view taken along line VI-VI of FIG. 5, illustrating a cooling liquid reflux structure of the condenser according to the first embodiment. It is a partial elevation sectional view for explaining the inclination angle of the inclined plate of the cooling liquid recirculation structure of the condenser concerning a 1st embodiment. It is a graph which shows the state distribution of the flow direction of the fluid inside the condenser concerning a 1st embodiment. FIG. 4 is a thermal expansion diagram for explaining an effect of the condenser according to the first embodiment. FIG. 4 is a physical property data diagram of steam for describing an effect of the condenser according to the first embodiment. It is an elevation sectional view showing the composition of the condenser concerning a 1st embodiment in the case of a turbine of a side exhaust system. It is a development view of the cooling liquid recirculation structure seen along the side plate of the condenser concerning a 2nd embodiment. FIG. 13 is a cross-sectional view taken along line XIII-XIII of FIG. 12 illustrating a cooling liquid reflux structure of a condenser according to a second embodiment. FIG. 14 is a cross-sectional view taken along line XIV-XIV of FIG. 13 illustrating a cooling liquid reflux structure of the condenser according to the second embodiment. It is a development view of a cooling liquid recirculation structure seen along with a side plate of a condenser concerning a 3rd embodiment. FIG. 16 is a cross-sectional view taken along line XVI-XVI of FIG. 15 illustrating a cooling liquid reflux structure of the condenser according to the third embodiment. FIG. 17 is a cross-sectional view taken along line XVII-IVII of FIG. 16 and illustrating a cooling liquid reflux structure of a condenser according to a third embodiment. It is a development view of the cooling liquid recirculation structure seen along the side plate of the condenser concerning a 4th embodiment. FIG. 19 is a cross-sectional view taken along line IXX-IXX of FIG. 18, showing a cooling liquid reflux structure of a condenser according to a fourth embodiment. FIG. 20 is a cross-sectional view taken along line XX-XX of FIG. 19 illustrating a cooling liquid reflux structure of a condenser according to a fourth embodiment.

  Hereinafter, a condenser and a method for improving the heat exchange performance of the condenser according to the embodiment of the present invention will be described with reference to the drawings. Here, the same or similar parts are denoted by the same reference numerals, and overlapping description is omitted.

[First Embodiment]
FIG. 1 is an elevational sectional view showing the configuration of the condenser according to the first embodiment. FIG. 2 is a sectional view taken along line II-II of FIG. FIG. 3 is a sectional view taken along line III-III in FIG.

  The condenser 100 has a main body case 110, an inflow part 111 for connecting the steam turbine 10 to the main body case 110, an exhaust part 115 for guiding gas to the outside of the main body case 110, and a coolant spray structure 120.

  The condenser 100 is a device generally called a condenser. The condenser 100 receives turbine exhaust gas from the steam turbine 10, sprays a coolant, and directly contacts the turbine exhaust gas to condense the turbine exhaust steam and condense water. And the pressure in the chamber is maintained at a negative pressure.

  FIG. 1 shows a case where the steam turbine 10 is an axial exhaust turbine 11. The axial exhaust turbine 11 is a steam turbine 10 of a type in which turbine exhaust flowing from a final stage blade (not shown) after performing work is discharged in an axial direction opposite to the generator 20. The turbine exhaust contains uncondensed gas in addition to the turbine exhaust steam.

  The main body vessel 110 includes members that form a closed space 110a, an inflow portion 111 that connects the closed space 110a with the axial exhaust turbine 11, and a non-condensable gas and a steam that has not been condensed from the closed space 110a. And a discharge unit 115 for discharging. The closed space 110a includes a hot well 116 for temporarily storing condensed condensed water, two opposed side shells 112 provided between the inflow portion 111 and the discharge portion 115, an upper plate 113, and an inflow portion. An end plate 114 is provided so as to be opposed to 111 and has a discharge portion 115 formed therein.

  Most of the turbine exhaust steam in the turbine exhaust flowing into the closed space 110a from the inflow part 111 is condensed and condensed, and moves to the hot well 116 side. Therefore, the weight flow rate of the non-condensable gas and the non-condensed steam flowing out of the discharge section 115 is smaller than the weight flow rate of the turbine exhaust flowing in from the inlet section 111. For this reason, the flow path cross section of the discharge section 115 is smaller than the flow path cross section of the inflow section 111. In order to reduce the pressure loss in the closed space 110a, the side shell 112 and the upper plate 113 are formed in a curved shape in the vicinity of the end plate 114 so as to smooth the flow in the closed space 110a.

  Here, for convenience of explanation, directions are indicated by symbols. The direction from the inflow part 111 to the discharge part 115 is defined as an X direction. A direction from one of the two side trunks 112 (right side as viewed from the inflow section 111) to the other (left side as viewed from the inflow section) is defined as a Y direction. The vertical direction is defined as the Z direction.

  A cooling liquid reflux structure 130 is attached to the surface of each of the two side shells 112 on the closed space 110a side. Details of the cooling liquid reflux structure 130 will be described later with reference to FIGS.

  The cooling liquid distribution structure 120 includes a mother pipe 121, a plurality of branch pipes 122, a plurality of ejection section headers 123, and a plurality of ejection sections 124.

  The mother pipe 121 is disposed above the hot well 116 along the Z direction and extends vertically upward, penetrates the main body vessel 110, and includes, for example, a cooling tower (not shown) for cooling condensate. Connected to a cooling source.

  The plurality of branch pipes 122 (FIGS. 2 and 3) are arranged substantially horizontally along the Y direction with an interval in the Z direction. Each of the plurality of branch pipes 122 has an end connected to the mother pipe 121. From each of the branch pipes 122, a plurality of tubular injection section headers 123 are branched and extend in the horizontal direction (X direction). A plurality of spray units 124 such as spray nozzles are attached to each of the spray unit headers 123 at intervals in the X direction. In addition, at each X-direction position of the tubular injection section header 123, an injection section 124 that injects cooling water downward is provided.

  With the configuration as described above, the injection units 124 are three-dimensionally arranged in the closed space 110a at appropriate intervals. The cooling liquid spraying structure 120 has the above-described configuration of the mother pipe 121, the plurality of branch pipes 122, the plurality of ejection section headers 123, and the plurality of ejection sections 124, which are arranged as described above. Although the case has been described as an example, the present invention is not limited to this. Other configurations and arrangements may be used as long as the injection unit 124 is arranged three-dimensionally in the closed space 110a.

  FIG. 4 is a cross-sectional view taken along the line IV-IV of FIG. 2 showing a configuration of the cooling liquid reflux structure of the condenser according to the first embodiment. The cooling liquid reflux structure 130 has a plurality of reflux units 130a. That is, three recirculation units 130a are attached to the side trunks 112 facing each other. The three reflux units 130a are inclined so that their positions in the vertical direction (Z direction) increase along the flow direction (X direction). That is, it is inclined in the minus X direction.

  As shown in FIG. 3, the height position of the uppermost part of each reflux unit 130a, that is, the most downstream part in the flow direction, is such that the cooling liquid injected from the injection part 124 arranged at the uppermost part The height position is set so as to be lower than the height position directly reaching.

  Further, the three reflux units 130a are arranged substantially parallel to each other with an interval in the Z direction. The number of reflux units 130a included in the coolant reflux structure 130 is not limited to three on each side. For example, one or two or four or more may be provided for one side. Alternatively, a different number of reflux units 130a may be arranged on the side shells 112 facing each other.

  Note that, for example, a part of the lowermost reflux unit 130a may be buried in the condensate in the hot well 116.

  5 is a sectional view taken along line VV of FIG. 4, and FIG. 6 is a sectional view taken along line VI-VI of FIG.

  Each reflux unit 130a is a single continuous plate that is attached to the side body 112 at an angle. Each of the reflux units 130a has a width continuously expanding in a direction opposite to the X direction. One side 131a of the reflux unit 130a is connected to the side body 112. The joining method may be welding or mechanical joining with bolts or the like.

  Note that the reflux unit 130a is not limited to a single plate. A plurality of plates may be connected mechanically or by welding.

  As shown in FIG. 5, the Z direction position of the opposite side 131b is higher than the side 131a connected to the side shell 112 of the reflux unit 130a. That is, the inclination angle Φ of the inclination in the minus Y direction from the vertically upward direction of the reflux unit 130a is smaller than 90 degrees.

  FIG. 7 is a partial vertical sectional view for explaining the inclination angle of the inclined plate of the coolant reflux structure. FIG. 7 shows a case where the side trunk 112 is inclined in the Y direction by an angle か ら from a vertically upward direction in the XY cross section. In other words, this corresponds to a case where the horizontal cross section of the hot well 116 is larger in the condenser 100 than in the upper portion that receives the turbine exhaust.

  In this case, in order to hold the coolant, the side body 112 is inclined in the Y direction by an angle Ψ from the vertically upward direction, and the recirculation unit 130a is inclined in the Y direction by an angle か ら from the vertically upward direction. It is necessary to set the difference between the angles, that is, the angle Φ between the side shell 112 and the recirculation unit 130a, to an angle smaller than (90 degrees-Ψ). In other words, the angle (Φ + Ψ) at which the recirculation unit 130a is inclined in the Y direction by an angle か ら from a vertically upward direction must be smaller than 90 degrees.

  Next, the operation of the condenser 100 in the present embodiment will be described.

  With the above configuration, during operation of the steam turbine 10, the cooling liquid supplied from the cooling source is supplied by the cooling liquid distribution structure 120 configured as shown in FIGS. The air is sprayed from the plurality of injection units 124 into the closed space 110a via the plurality of branch pipes 122 and the plurality of injection unit headers 123. Here, the spraying of the cooling liquid is performed by the injection units 124 that are arranged almost uniformly three-dimensionally in the closed space 110a. From each of the spraying parts 124, the coolant is sprayed from positions horizontally and circumferentially spaced from each other. Note that the spray direction of the coolant is not limited to the horizontal direction, and may have an elevation angle or a depression angle from the horizontal direction.

  On the other hand, turbine exhaust from the axial exhaust turbine 11 flows into the closed space 110a from the inflow portion 111. The subsequent flow of the turbine exhaust that has flowed into the closed space 110a is hereinafter referred to as in-vessel gas. The in-vessel gas is the same as the turbine exhaust gas at the inflow section 111, and is obtained by mixing non-condensable gas into turbine exhaust steam.

  As the vapor of the inside gas flows in the X direction, it sequentially comes into contact with the droplets ejected from the ejection unit 124 and condenses into condensate, that is, condensate.

  The condensed water falls into the hot well 116, and a part of the condensed water falls on the respective reflux units 130a of the coolant reflux structure 130.

  The cooling liquid that has dropped onto the reflux unit 130a is held in a space between the reflux unit 130a and the side shell 112 that is inclined in the minus Y direction. A component force acts on the held cooling liquid in the minus X direction along the gravity return unit 130a. As a result, the coolant held in the space between the reflux unit 130a and the side shell 112 moves in the minus X direction. As described above, it is possible to guide the coolant in the direction of the inflow portion 111 (minus X direction) without using an additional means such as a pump.

  The coolant flows through the space between the reflux unit 130a and the side body 112, and the coolant falls into the space between the reflux unit 130a and the side body 112. For this reason, the flow rate of the coolant flowing on the surface of the reflux unit 130a gradually increases in the minus X direction.

  On the other hand, since the width of the reflux unit 130a gradually increases in the minus X direction, the cross-sectional area of the flow path formed by the reflux unit 130a and the side shell 112 also increases. As a result, both the condensed water falling directly or along the side shell 112 and the condensed water flowing through the flow path can be appropriately held.

  The cooling liquid flowing through the flow path formed by the reflux unit 130a and the side shell 112 exchanges heat with the gas in the atmosphere via the upper surface or partially via the reflux unit 130a.

  FIG. 8 is a graph showing a state distribution in the flow direction of the fluid inside the condenser according to the first embodiment. The horizontal axis represents the distance along the flow direction of the internal gas from the reception of the internal gas in the closed space 110a to the exhaust thereof.

  The two-dot chain line described as (Pv + Pg) indicates the pressure of the gas in the chamber. The pressure drops at the discharge position by the pressure loss ΔP from the inflow position to the discharge position. Here, Pv is the partial pressure of the steam, and Pg is the partial pressure of the non-condensable gas.

  The dashed line indicated as (Pv) indicates the distribution of the partial pressure of steam in the gas in the chamber. As the gas in the vessel advances in the flow direction, the vapor condenses sequentially, so that the partial pressure of the vapor decreases. In general, in the vicinity of the discharge unit 115, the degree of reduction in the partial pressure of the steam increases.

  Solid lines denoted as (Ts) indicate temperatures at respective X-direction positions. This temperature is the saturation temperature of the vapor partial pressure at each X-direction position. That is, the saturation temperature continuously decreases along the X direction.

  Inside the condenser 100, the coolant injected from the injection unit 124 exchanges heat with the internal gas, reaches the inner wall of the main body container 110 such as the side body 112, and flows down on the wall surface. . When the liquid temperature of the cooling liquid at the time of reaching the inner wall is lower than the temperature of the inside gas of the atmosphere, heat exchange between the cooling liquid and the inside gas is performed also on the surface of the inner wall.

  However, the distance from the arrival point of the inner wall to the hot well 116 immediately below the inner wall is not a sufficient distance for recovering the temperature of the coolant by heat exchange between the coolant and the gas in the chamber. On the other hand, in the present embodiment, most of the coolant that has reached the side shell 112 is held by the recirculation unit 130 a while moving downward along the wall surface of the side shell 112. The cooling liquid held in the reflux unit 130a further exchanges heat with surrounding gas in the process of flowing in the reflux unit 130a in the minus X direction. In this way, by increasing the flow-down distance, the temperature of the coolant can be effectively recovered.

  As described above, the temperature of the inside gas increases in the minus X direction. Therefore, by circulating the coolant in the minus X direction, the temperature of the gas inside the chamber around the coolant increases. This raises the upper limit of the temperature at which the temperature of the coolant increases due to heat exchange with the gas in the chamber. As a result, an effect similar to that of the countercurrent heat exchanger is added, and the heat exchange performance is improved as compared with the case where the coolant reflux structure 130 is not provided.

  As described above, the heat exchange performance is improved by extending the time in which the heat exchange of the cooling liquid with the gas inside the vessel is possible, and the flow of the gas inside the vessel is recirculated to the upstream side such as in a countercurrent heat exchanger. Improvement of heat exchange performance is achieved in two aspects of improvement of heat exchange performance. By improving the heat exchange performance, the amount of steam condensed in the gas in the vessel increases. As a result, the saturation pressure in the condenser 100 can be reduced.

  Here, with reference to FIG. 9 and FIG. 10, an effect caused by a decrease in the pressure in the condenser 100 will be described.

  FIG. 9 is a thermal expansion diagram for explaining the effect of the condenser according to the first embodiment. The horizontal axis is the entropy of steam s, and the vertical axis is the enthalpy of steam h (kJ / kg). FIG. 9 shows a macro state change from the steam inlet to the steam outlet of the steam turbine 10. Therefore, the state change for each paragraph is omitted.

  It is assumed that the state is indicated by a point P1 at the inlet of the steam turbine 10, the pressure is pin1, and the temperature is Tin. The enthalpy of the steam at this time is hin. The pressure of the steam discharged from the last stage blade after performing the work in each stage of the steam turbine 10 is defined as pout1. If the state changes without increasing the entropy, the outlet of the steam turbine 10 will be in a state shown by a point P30, and the enthalpy of the steam in this case is he10. The heat drop Δh1 obtained by multiplying the adiabatic heat drop Δh10, which is the difference between the enthalpy hin of the steam at the inlet of the steam turbine 10 and the enthalpy he10 of the steam turbine 10, by the internal efficiency η of the steam turbine 10 is converted into mechanical energy in the steam turbine 10. Corresponding to the heat energy to be applied. As the pressure of the condenser 100 is lower, the heat drop Δh1 becomes larger, and the output of the steam turbine 10 increases.

  FIG. 10 is a physical property data diagram of steam for explaining the effect of the condenser. The horizontal axis is the steam pressure (MPa). On the vertical axis, the first axis on the left is the enthalpy of steam (kJ / kg), and the second axis on the right is the temperature (° C.) of the steam. The solid line is the enthalpy hs of the saturated steam, the dashed line is the enthalpy hk of the superheated steam 10 degrees higher than the saturation temperature, and the two-dot chain line is the saturation temperature Ts.

  As shown in FIG. 10, the change of the enthalpy with respect to the change of the saturated steam and the pressure is particularly large in a low pressure region. This tendency is the same for superheated steam.

  When the pressure level is about the same as the exhaust pressure of the steam turbine 10, for example, when the pressure is 0.005 MPa, the pressure level on the high pressure side such as the inlet pressure of the steam turbine 10 is 1 MPa, for example. The change of the enthalpy with respect to the change, that is, the slope of the curve in FIG.

  Thus, it can be seen that the enthalpy of the exhaust steam can be greatly reduced by reducing the exhaust pressure. As a result, an effect of increasing the heat drop Δh converted into the output of the steam turbine 10 is obtained.

  FIG. 11 is an elevational sectional view showing a configuration of the condenser according to the first embodiment in the case of a side exhaust type turbine. In the side exhaust type turbine 12, the turbine exhaust is discharged from the turbine main body 12a in a substantially horizontal direction. As in the case of the axial exhaust turbine 11, the condenser 100 receives the turbine exhaust discharged in a substantially horizontal direction through the inlet 111. The condenser 100 has the same arrangement and configuration as the case of the axial exhaust turbine 11 such that the end plate 114 is disposed at a position facing the inflow portion 111, and the effect on the heat exchange efficiency is also small. This is the same as the case of No. 11.

  In addition, even if the height positions of the inflow part 111 and the discharge part 115 in the vertical direction are different, the positions in the horizontal direction may be different. That is, even in this case, since the gas in the chamber moves in the horizontal direction, the coolant can be returned to the inflow portion 111 side in the horizontal direction by using the effect of gravity. The injection units are also distributed in the horizontal direction, and a temperature distribution is formed in the condenser 100 in the horizontal direction. Therefore, the reflux of the cooling liquid also improves the heat exchange performance in the condenser 100 described above. For the same reason, the direction of the turbine exhaust is not limited to the horizontal direction as long as there is a speed component in the horizontal direction.

  As described above, according to the present embodiment, even when a temperature gradient occurs from the inflow part 111 to the discharge part 115 in the condenser 100, effective heat exchange becomes possible, and the output of the steam turbine 10 increases. Can be achieved.

[Second embodiment]
FIG. 12 is a developed view of the cooling liquid reflux structure viewed along a side plate of the condenser according to the second embodiment. 13 is a cross-sectional view taken along line XIII-XIII of FIG. 12, and FIG. 14 is a cross-sectional view taken along line XIV-XIV of FIG.

  This embodiment is a modification of the first embodiment. In the second embodiment, the reflux unit 130b is formed so as to protrude vertically upward. That is, the inclination angle with respect to the flow direction is formed so as to monotonously decrease along the flow direction.

  Specifically, the inclination angle θ1 of the recirculation unit 130b at the position G1 is larger than the inclination angle θ2 downstream of the position G1, that is, at a position G2 where X is large. That is, it is formed so that the inclination angle becomes larger toward the upstream. The other points are the same as in the first embodiment.

  The gas inside the vessel is sequentially condensed by heat exchange with the cooling liquid as it flows. For this reason, the weight flow rate of the inside gas decreases in the flow direction. Although pressure loss occurs in the flow direction, the pressure in the vessel is almost the same, so that the volume flow rate also decreases in the flow direction. Except near the end plate 114, the cross-sectional area in the condenser 100 in the flow direction is substantially constant. Alternatively, the change in cross-sectional area along the flow direction is small.

  For this reason, the flow velocity of the gas inside the vessel is higher on the upstream side in the flow direction of the gas inside the vessel than on the downstream side. When the coolant flows over the reflux unit 130b, if the flow rate of the gas in the chamber is excessive, the coolant may blow up, and the fluid may be blocked at an intermediate position of the reflux unit 130b. . In the second embodiment, the angle of inclination with respect to the horizontal line gradually increases as approaching the inflow portion 111. The greater the inclination angle, the greater the gravity component in the flow direction of the coolant. As a result, in a region where the gas flow velocity is high, the acceleration of gravity in the moving direction of the coolant becomes large, and it is possible to prevent blow-up.

[Third Embodiment]
FIG. 15 is a developed view of the cooling liquid reflux structure viewed along the side plate of the condenser according to the third embodiment. 16 is a cross-sectional view taken along the line XVI-XVI of FIG. 15, and FIG. 17 is a cross-sectional view taken along the line XVII-XVII of FIG.

  The third embodiment is a modification of the first embodiment. Each reflux unit 130c in the present embodiment has a bottom plate 132b and a side plate 132a.

  The bottom plate 132b is formed so as to extend in the flow direction of the internal gas and to be wider toward the upstream side of the flow of the internal gas. Further, one side of the bottom plate 132b is connected to the side trunk 112. In the cross section perpendicular to the flow direction, the bottom plate 132b is arranged in the horizontal direction as shown in FIG.

  The side plate 132a has a plate shape extending along the bottom plate 132b, and is connected to the other side of the bottom plate 132b. The side plate 132a is arranged so that its width direction is vertical. The side plate 132a is not limited to the vertical direction. In other words, it is only necessary that the mounting member be mounted so that the height in the vertical direction is higher than the bottom plate 132b with respect to the horizontal direction, and the side shell 112, the side plate 132a, and the side plate 132b can hold the cooling liquid.

  The cooling liquid reflux structure 130 according to the present embodiment having the reflux unit 130c configured as described above has a larger size than the case where the reflux unit 130a according to the first embodiment is used. The size protruding inward can be reduced. As a result, an increase in pressure loss in the condenser 100 due to the provision of the coolant reflux structure 130 in the condenser 100 can be suppressed.

[Fourth embodiment]
FIG. 18 is a developed view of the cooling liquid reflux structure viewed along the side plate of the condenser according to the fourth embodiment. FIG. 19 is a sectional view taken along the line IXX-IXX in FIG. 18. FIG. 20 is a sectional view taken along line XX-XX in FIG.

  The fourth embodiment is a modification of the third embodiment. In the present embodiment, it is the side plate 133a that is formed wider toward the upstream side of the flow of the gas in the chamber, and the bottom plate 133b is formed to have a constant width. The other points are the same as the third embodiment.

  In the present embodiment configured as described above, the size of the protrusion from the side shell 112 to the inside of the main body shell container 110 can be further reduced than in the third embodiment. As a result, a margin in the horizontal direction is generated, and restrictions on the arrangement are relaxed.

[Other Embodiments]
Although some embodiments of the present invention have been described above, these embodiments are presented as examples and are not intended to limit the scope of the invention. Further, the features of each embodiment may be combined. Furthermore, these embodiments can be implemented in other various forms, and various omissions, replacements, and changes can be made without departing from the spirit of the invention. These embodiments and their modifications are included in the scope and gist of the invention, and are also included in the invention described in the claims and equivalents thereof.

  DESCRIPTION OF SYMBOLS 10 ... Steam turbine, 11 ... Axial exhaust turbine, 12 ... Side exhaust type turbine, 12a ... Turbine main body, 20 ... Generator, 100 ... Condenser, 110 ... Main body case, 110a ... Closed space, 111 ... Inflow part , 112 ... side body, 113 ... top plate, 114 ... end plate, 115 ... discharge unit, 116 ... hot well, 120 ... coolant spray structure, 121 ... base tube, 122 ... branch tube, 123 ... injection unit header, 124 ... injection unit, 130 ... coolant reflux structure, 130a, 130b, 130c, 130d ... reflux unit, 131a, 131b ... side, 132a ... side plate, 132b ... bottom plate, 133a ... side plate, 133b ... bottom plate

Claims (7)

A main body vessel that receives turbine exhaust discharged in a substantially horizontal direction from the steam turbine as gas in the vessel, and serves as a flow path of the gas in the vessel,
An inflow section connecting the steam turbine and the main body vessel,
A coolant spraying structure for injecting a coolant into the main body container and condensing the chamber gas;
A discharge unit for discharging the remaining in-vessel gas not condensed in the main body container to the outside of the main body container,
A coolant reflux structure having one or more reflux units that are attached to the inside of the main body container and receive the coolant and reach the upstream side of the flow of the internal gas by gravity by gravity;
A condenser comprising: The main body container,
An end plate provided with an opening formed to be opposed to the inflow portion and connected to the discharge portion,
A hot well that constitutes the bottom of the main body container and temporarily stores the condensate generated by the condensation;
Two opposite side trunks connecting the inflow portion and the end plate and extending along the vertical direction and along the flow direction of the internal gas,
An upper plate connected to the two side trunks and extending along a flow direction of the internal gas, and forming a closed space in combination with the side trunks, the end plate and the hot well;
Has,
The condenser according to claim 1, wherein each of the one or more reflux units is attached to the side shell.   The one reflux unit or each of the plurality of reflux units is formed in a weir shape capable of holding the cooling liquid, and the height position thereof decreases toward the upstream side of the flow of the gas in the vessel. 3. The condenser according to claim 2, wherein the condenser is arranged.   Each of the one reflux unit or the plurality of reflux units has a plate shape extending in the flow direction of the internal gas and having a width increasing toward the upstream side of the flow of the internal gas, and in a horizontal direction. The condenser according to claim 2, wherein the condenser is attached to the side body with an inclination.   Each of the one reflux unit or the plurality of reflux units extends in the flow direction of the internal gas and becomes wider toward the upstream side of the flow of the internal gas, and one of the side units has the side body. A bottom plate connected to the side plate connected to the other side of the bottom plate so that the height in the vertical direction is higher than the bottom plate with respect to the horizontal direction in a plate shape extending along the bottom plate. The condenser according to claim 2 or 3, wherein:   The one reflux unit or each of the plurality of reflux units has a substantially constant width and extends in the flow direction of the internal gas, and a bottom plate having one side connected to the side body; It is connected to the other side of the bottom plate so that the width becomes wider toward the upstream side of the flow and extends in a plate shape extending along the bottom plate so that the height in the vertical direction is higher than the bottom plate with respect to the horizontal direction. The condenser according to claim 2, further comprising: a side plate that is provided.   7. The one reflux unit or each of the plurality of reflux units is formed such that an inclination angle with respect to a flow direction monotonically decreases along the flow direction. The condenser according to any one of the preceding claims.

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