JP7002420B2 - Direct contact condenser and power plant - Google Patents

Description

Embodiments of the present invention relate to a direct contact condenser and a power plant.

Geothermal energy is attracting attention as one of the renewable energies that has little impact on the environment, and recently, geothermal power generation plants using geothermal energy are becoming widespread.

In a geothermal power plant, in order to keep the exhaust pressure of the turbine at a negative pressure (vacuum), the high-temperature steam in the turbine exhaust and the low-temperature cooling water may be heat-exchanged by a condenser to condense the steam. In geothermal power plants, there is no need to reuse condensed condensate of water vapor as in thermal power generation, so direct contact condensers with a simple structure and efficient heat exchange are often used. ..

The direct contact type condenser is a device that directly contacts the turbine exhaust and the cooling water, and is mainly classified into a tray (perforated plate) type and a droplet spray type (spray type). The tray type is a method in which the cooling water that falls from the tray due to the dynamic pressure of the turbine exhaust that has flowed into the condenser is miniaturized and introduced into the turbine exhaust. The spray type is a method in which cooling water is atomized using a spray nozzle and injected into the turbine exhaust. Further, in this type of condenser, the lower exhaust type (upper inflow type) or the horizontal exhaust type (horizontal inflow type) is often adopted as the introduction type of the turbine exhaust.

The steam from the geothermal production wells used in geothermal power generation generally contains non-condensable gas such as carbon dioxide, and the concentration of the non-condensable gas varies depending on the production well, but is generally 0.3 to 10. It is about 0 wt%. The value of the concentration of this non-condensable gas corresponds to a value of 1000 times or more that of steam used in a general thermal power plant or a nuclear power plant. Since such non-condensable gas can inhibit heat transfer between steam and cooling water in the condenser and inhibit condensation of steam, the condenser discharges the non-condensed gas without retaining it. It is important to keep the exhaust pressure of the turbine at a negative pressure (vacuum).

Japanese Unexamined Patent Publication No. 11-6857 Japanese Patent No. 5404175

By the way, the spray-type condenser for geothermal power generation includes a turbine exhaust duct, a steam condensing section for accommodating a spray nozzle as a cooling water supply means, and a non-condensing gas cooling section as main parts. After passing through the turbine exhaust duct, the turbine exhaust discharged from the turbine is guided to the steam condensing section, where the steam contained therein is condensed. Then, the non-condensable gas such as carbon dioxide that does not condense in the steam condensing section and the water vapor accompanying the non-condensable gas are guided to the non-condensing gas cooling section, and after being further cooled, are discharged from the condenser. In the non-condensable gas cooling unit, the condensated water condensed by the cooling is discharged from the condensate discharge port, and the non-condensed gas is discharged from another discharge port.

In such a condenser, the turbine exhaust flowing into the steam condensing section comes into contact with the cooling water, and the steam contained in the turbine exhaust condenses, so that the flow velocity of the turbine exhaust flowing in the steam condensing section gradually decreases. go. Therefore, in the flow inside the condenser, the flow velocity is high on the turbine exhaust duct side of the steam condensing section, but on the non-condensing gas cooling section side, the flow velocity becomes slow due to the almost condensation of water vapor, and the flow stays. Is likely to occur. When the flow is stagnant inside the condenser in this way, the non-condensable gas collects in the stagnant region, and the heat transfer efficiency between the water vapor and the cooling water inside the condenser deteriorates, and the condenser There is a risk that the internal vacuum will deteriorate. If the degree of vacuum inside the condenser deteriorates, the power generation efficiency of the plant will decrease.

The present invention has been made to solve such a problem, and it is possible to stably maintain the degree of vacuum inside the condenser in a desired state by suppressing the retention of the flow inside the condenser. The purpose is to provide a direct contact condenser and a power plant that can be used.

The direct contact type water condenser according to an embodiment is connected to a turbine exhaust duct into which turbine exhaust from a turbine flows in and the turbine exhaust duct, and receives turbine exhaust from the turbine exhaust duct from the side or above. The main body container, the cooling water supply pipe that supplies cooling water to the inside of the main body container, and the turbine exhaust duct side in the main body container when the main body container receives turbine exhaust from the side. Is provided on the opposite side and opens in the horizontal direction, and when the main body body container receives turbine exhaust from above, is provided in the main body body container at a position horizontally separated from the turbine exhaust duct and is horizontal. A gas inlet portion that opens in the direction, a gas cooling chamber connected to the main body body container via the gas inlet portion, and a baffle plate arranged inside the main body body container so as to face the gas inlet portion. And, it has. A flow opening through which turbine exhaust passes is formed between the upper portion of the baffle plate and the inner wall surface of the main body container that faces the upper portion of the baffle plate in the vertical direction.
Further, the power plant according to the embodiment includes the above-mentioned direct contact condenser.

According to the present invention, the degree of vacuum inside the condenser can be stably maintained in a desired state by suppressing the retention of the flow inside the condenser.

It is the schematic sectional drawing in the vertical direction of the direct contact type condenser which concerns on 1st Embodiment. It is sectional drawing which follows the II-II line of FIG. FIG. 3 is a cross-sectional view taken along the line III-III of FIG. It is sectional drawing which follows the IV-IV line of FIG. It is a figure which shows the flow velocity vector of the turbine exhaust in the inside of the direct contact type condenser which concerns on 1st Embodiment. It is a figure which shows the flow velocity vector of the turbine exhaust inside the condenser when the baffle plate is removed from the direct contact type condenser which concerns on 1st Embodiment. (A) is a diagram showing a baffle plate included in the direct contact condenser according to the second embodiment, and (B) and (C) are modifications of the second embodiment. It is a figure which shows. It is the schematic sectional drawing in the vertical direction of the direct contact type condenser which concerns on 3rd Embodiment. It is sectional drawing which follows the IX-IX line of FIG.

Hereinafter, each embodiment will be described in detail with reference to the accompanying drawings.

<First Embodiment>
FIG. 1 is a schematic cross-sectional view in the vertical direction of the direct contact type condenser 1 (hereinafter, abbreviated as the condenser 1) according to the first embodiment. 2 is a cross-sectional view taken along line II-II of FIG. 1, FIG. 3 is a cross-sectional view taken along line III-III of FIG. 1, and FIG. 4 is a cross-sectional view taken along line IV-IV of FIG. Is.

The condenser 1 shown in FIG. 1 is connected to a turbine exhaust duct 10 into which turbine exhaust from a turbine (not shown) flows in, and a main body body connected to the turbine exhaust duct 10 and receiving turbine exhaust from the turbine exhaust duct 10 from the side. The container 11, the cooling water supply pipe 12 that supplies cooling water to the inside of the main body container 11, and the gas inlet portion that is provided on the side of the main body container 11 opposite to the turbine exhaust duct 10 side and opens in the horizontal direction. 13, a gas cooling chamber 14 connected to the main body container 11 via the gas inlet portion 13, a baffle plate 15 arranged inside the main body body container 11 so as to face the gas inlet portion 13, and cooling water. It is provided with a mixed water outlet nozzle 16 for discharging the mixed water of the cooling water supplied by the supply pipe 12 and the condensed water condensed from the turbine exhaust from the main body container 11.

The turbine exhaust duct 10 extends so as to allow turbine exhaust from the turbine to flow in the horizontal direction, and is connected to the first side wall portion 11A of the main body container 11. As shown by the arrow A, the main body body container 11 allows the exhaust gas from the turbine exhaust duct 10 to flow in from the side in the horizontal direction, and directly connects the turbine exhaust gas and the cooling water supplied from the cooling water supply pipe 12. It is configured to condense the water vapor contained in the turbine exhaust by contacting with. That is, the condenser 1 according to the present embodiment is a so-called horizontal inflow side direct contact condenser. Further, the condenser 1 according to the present embodiment is incorporated in a power generation plant, and is specifically configured as a condenser for a geothermal power generation plant.

In the main body container 11 of the present embodiment, the upper portion of the second side wall portion 11B horizontally facing the first side wall portion 11A to which the turbine exhaust duct 10 is connected is formed in a curved shape, but the turbine exhaust duct 10 is formed. The cross-sectional shape on the vertical surface orthogonal to the horizontal direction in which the turbine exhaust flows is rectangular, and the cross-sectional shape on the horizontal plane is also rectangular (see FIGS. 2 and 4). .. The shape of the main body container 11 is not particularly limited to the shape in the present embodiment, and the cross-sectional shape on the vertical surface may be circular, for example.

The cooling water supply pipe 12 is a spray-type cooling water supply means, and the piping portion 12A through which the cooling water for condensing the turbine exhaust is passed and the cooling water in the piping portion 12A are introduced into the main body container 11. It has a spray nozzle 12B for the purpose of using the spray nozzle 12B. The piping portion 12A is attached to the third and fourth side wall portions 11C and 11D of the main body container 11 which face each other in a direction orthogonal to the direction in which the first and second side wall portions 11A and 11B of the main body container 11 face each other. It is provided in a straddling state (see FIG. 4). Further, a plurality of spray nozzles 12B are provided on the upper surface and the lower surface of the piping portion 12A at intervals in the longitudinal direction. In the present embodiment, a plurality of such cooling water supply pipes 12 are provided and arranged in a matrix inside the main body container 11.

The gas inlet portion 13 is provided in the second side wall portion 11B, specifically, is provided in the lower portion of the second side wall portion 11B which is parallel to the vertical direction, and is located diagonally downward with respect to the turbine exhaust duct 10. do. As shown in FIG. 3, the gas inlet portion 13 in the present embodiment has a rectangular cross-sectional shape in the vertical plane, and as shown in FIG. 1, the lower side portion thereof is the main body container 11. It is flush with the bottom wall. Further, the gas inlet portion 13 in the present embodiment has a duct shape in which rectangular cross-sectional portions are continuous by a certain length, but the gas inlet portion 13 is formed on the second side wall portion 11B of the main body container 11. It may be just an opening. Further, the cross-sectional shape of the gas inlet portion 13 may be circular or the like.

The gas cooling chamber 14 forms a space for receiving and cooling the turbine exhaust, specifically, the turbine exhaust that has not been condensed in the main body container 11 via the gas inlet portion 13, and in the present embodiment. It has a rectangular parallelepiped shape. The gas cooling chamber 14 is connected to the gas inlet portion 13 at its side wall portion, and extends in the vertical direction so as to allow the turbine exhaust gas flowing in from the gas inlet portion 13 to flow upward.

A cooling water supply pipe (not shown) is provided inside the gas cooling chamber 14, and the turbine exhaust flowing into the gas cooling chamber 14 is cooled by the cooling water supplied from the cooling water supply pipe inside the gas cooling chamber 14. It is condensed or cooled in a gaseous state. The cooling water supply pipe inside the gas cooling chamber 14 may be the same as the cooling water supply pipe 12 inside the main body container 11. Further, a gas outlet portion 14A is provided in the upper part of the gas cooling chamber 14, so that the turbine exhaust gas in a gaseous state is discharged from the gas outlet portion 14A.

On the other hand, the bottom wall portion of the gas cooling chamber 14 in the present embodiment is flush with the lower side portion (bottom wall portion) of the gas inlet portion 13 and the bottom wall portion of the main body container 11. Here, in the present embodiment, the hot well 17 is formed by the lower portions of the main body container 11, the gas inlet portion 13, and the gas cooling chamber 14. The hot well 17 is a portion for storing the mixed water MW of the cooling water supplied to the main body container 11 and the gas cooling chamber 14 and the condensed water condensed from the turbine exhaust gas. In the present embodiment, the mixed water MW is accumulated in the hot well 17 in a constant amount. The water level of the mixed water MW is adjusted by a pump (not shown).

The baffle plate 15 is arranged so that a pair of main surfaces facing each other in the thickness direction are parallel to each other in the vertical direction, and one of the main surfaces faces the gas inlet portion 13 in the horizontal direction. Further, the baffle plate 15 is arranged at a position horizontally separated from the downstream opening of the turbine exhaust duct 10, and more specifically, in the vicinity of the cooling water supply pipe 12 located closest to the gas inlet portion 13, this example. Is arranged on the turbine exhaust duct 10 side of the cooling water supply pipe 12 which is closest to the gas inlet portion 13. The baffle plate 15 does not necessarily have to be parallel to the vertical direction, and may be arranged so as to be inclined with respect to the vertical direction.

As shown in FIG. 2, the baffle plate 15 in the present embodiment is a plate body that is elongated in the horizontal direction, and is fixed in a state of straddling the third side wall portion 11C and the fourth side wall portion 11D of the main body container 11. The turbine exhaust gas flow portion is not formed between the third side wall portion 11C and the fourth side wall portion 11D on which the turbine exhaust is located. On the other hand, a flow opening 18 through which turbine exhaust passes is formed between the upper portion 15A of the baffle plate 15 and the inner wall surface of the main body container 11 facing the upper portion 15A in the vertical direction. Further, the baffle plate 15 is in a state of floating with respect to the bottom wall portion of the main body body container 11, and a gap is also formed between the lower portion of the baffle plate 15 and the bottom wall portion of the main body body container 11. By forming this gap, the condensed water and the like generated in the main body container 11 and the condensed water and the like generated in the gas cooling chamber 14 are mixed and accumulated in the hot well 17, and these are collectively collected in the mixed water outlet nozzle 16. It becomes possible to discharge from.

In the present embodiment, the mixed water MW is controlled to be accumulated in a constant amount in the hot well 17, but specifically, in the mixed water outlet nozzle 16, the water surface height of the mixed water MW is higher than that of the lower part of the baffle plate 15. The opening and closing is controlled so that it becomes higher. Therefore, the gap between the lower part of the baffle plate 15 and the bottom wall portion of the main body container 11 is not intended to be used for the passage of turbine exhaust. The lower portion of the baffle plate 15 may be in contact with the bottom wall portion of the main body container 11, and in this case, a through hole for allowing condensed water to pass may be formed in the baffle plate 15.

Further, referring to FIGS. 1, 2 and 4, in the present embodiment, the cross-sectional area of the flow opening 18 in the vertical plane is S1, the baffle plate 15 and the side wall portion of the main body container 11 (specifically, the second). The relationship of S1 ≧ S2 is established when the cross-sectional area of the space formed on the gas inlet portion 13 side in the horizontal plane of the fourth side wall portions 11B to 11D) is S2. In addition, in FIG. 2, the range of the flow opening 18 is shown by a region with thin dots, and in FIG. 4, the above-mentioned space formed by the baffle plate 15 and the side wall portion of the main body container 11 is shown. The range of is indicated by the area with dark dots. Further, when the wall portion facing the baffle plate 15 does not exist when the cross-sectional area S2 is obtained, the extension surface of the wall portion on which the gas inlet portion 13 is formed is virtually extended into the gas inlet portion 13. Above, the cross-sectional area S2 is obtained from the space surrounded by the extension surface, the baffle plate 15, and the pair of wall portions located on both sides of the extension surface and the baffle plate 15.

Further, referring to FIGS. 3 and 4, when the cross-sectional area of the gas inlet portion 13 where the turbine exhaust passes in the vertical plane is S3 and the cross-sectional area of the gas cooling chamber 14 in the horizontal plane is S4, S2 ≧ S3. And / or, the relationship of S2 ≧ S4 is established, and more specifically, the relationship of S2 ≧ S3 and S2 ≧ S4 is established, and in addition, the relationship of S3 ≧ S4 is also established. That is, the relationship of S1 ≧ S2 ≧ S3 ≧ S4 is established. The "portion through which the turbine exhaust passes in the gas inlet portion 13" in the present embodiment corresponds to a portion above the water surface of the mixed water MW in the gas inlet portion 13. When the portion where the mixed water MW is collected is not formed in the gas inlet portion 13, the entire gas inlet portion 13 becomes a portion through which the turbine exhaust gas passes. Further, in FIG. 3, the range of the “portion through which the turbine exhaust passes in the gas inlet portion 13” is shown by the hatched region, and in FIG. 4, the range of the gas cooling chamber 14 is hatched. Shown by.

In the present embodiment, the turbine exhaust gas that has flowed into the main body container 11 by forming the flow opening 18 above the baffle plate 15 is between the flow opening 18, the baffle plate 15 and the second side wall portion 11B. , The gas inlet portion 13, and the gas cooling chamber 14 flow in this order. Here, by establishing the above-mentioned relationship of S1 to S4, the decrease in the flow velocity of the turbine exhaust gas from the main body container 11 to the gas cooling chamber 14 is suppressed. From the viewpoint of suppressing the decrease in the flow velocity of the turbine exhaust gas, it is preferable that the relationship of S1 ≧ S2 ≧ S3 ≧ S4 is established as in the present embodiment, but the relationship of S1 to S4 is the embodiment of the present embodiment. Not limited.

Next, the operation of this embodiment will be described.

In the condenser 1 according to the present embodiment, when a turbine (not shown) is driven, the turbine exhaust from the turbine flows into the main body container 11 from the turbine exhaust duct 10 as shown by the arrow A in FIG. .. The turbine exhaust that has flowed into the main body container 11 is in direct contact with the cooling water sprinkled from the spray nozzle 12B of the cooling water supply pipe 12, so that the water vapor contained therein is condensed. Here, when the turbine exhaust contains non-condensable gas such as water vapor and carbon dioxide, the non-condensed turbine exhaust gas containing the non-condensed gas that is not condensed in the main body container 11 and the water vapor that accompanies it is the gas inlet. It is guided to the gas cooling chamber 14 via the unit 13, where it is further cooled and discharged to the outside.

In the direct contact condenser on the horizontal inflow side where the turbine exhaust duct 10 and the gas inlet portion 13 face each other in the horizontal direction, the turbine exhaust flow velocity is high on the turbine exhaust duct 10 side. Most of the water vapor is condensed on the gas inlet portion 13 side, so that the flow velocity of the turbine exhaust is slowed down, and the flow tends to be stagnant. In particular, in the upper region on the second side wall portion 11B side where the gas inlet portion 13 is formed, the flow tends to stay in a wide range.

On the other hand, in the present embodiment, by providing the baffle plate 15 facing the gas inlet portion 13, a part of the turbine exhaust from the turbine exhaust duct 10 is a baffle plate 15 as shown by the arrow B in FIG. It is turned around and an upward flow is generated. As a result, the flow converted by the baffle plate 15 interferes (collides) with the flow that tends to stay in the upper region on the second side wall portion 11B side where the gas inlet portion 13 is formed, so that the flow stays. The range can be reduced and suppressed. As a result, in the present embodiment, the turbine exhaust (specifically, the uncondensed turbine exhaust) flowing into the main body container 11 from the turbine exhaust duct 10 is smoothly directed toward the gas inlet portion 13 as shown by the arrow C. Will flow to.

Here, FIG. 6 is a diagram showing a flow velocity vector of turbine exhaust inside the condenser when the baffle plate 15 is removed from the condenser 1, and the flow velocity vector is indicated by an arrow. The flow velocity vector in the figure indicates the direction of the flow depending on the direction of the arrow, and the longer the length of the arrow, the larger the flow velocity. The flow velocity vector shown in FIG. 6 is specified based on the simulation by the inventor of the present invention.

As described above, in the direct contact condenser on the horizontal inflow side where the turbine exhaust duct 10 and the gas inlet portion 13 face each other in the horizontal direction, the turbine exhaust flow velocity is high on the turbine exhaust duct 10 side. However, since most of the water vapor is condensed on the gas inlet 13 side, the flow velocity of the turbine exhaust is slowed down, and the flow tends to stay. In particular, in the upper region on the second side wall portion 11B side where the gas inlet portion 13 is formed, the flow tends to stay in a wide range. Based on this tendency, in the simulation results shown in FIG. 6, slow flows in various directions are widely distributed in the upper region on the second side wall portion 11B side where the gas inlet portion 13 is formed, and the flow stays over a wide range. Has occurred.

On the other hand, FIG. 5 is a diagram showing a flow velocity vector of the turbine exhaust inside the condenser 1 provided with the baffle plate 15, and the velocity vector is specified based on the same simulation as in the case of FIG. .. When the baffle plate 15 is provided, the retention of the flow inside the main body container 11 is suppressed, as is clear by comparing the result of FIG. 5 with the result of the case without the baffle plate 15 of FIG. There is. Specifically, the distribution of slow flows in various directions is smaller than that in FIG. From such a simulation result, it can be seen that when the baffle plate 15 is provided, the turbine exhaust gas flowing into the main body container 11 flows smoothly toward the gas inlet portion 13.

Then, the turbine exhaust flowing toward the gas inlet portion 13 is taken from the through opening 18 above the baffle plate 15 between the baffle plate 15 and the second side wall portion 11B, the gas inlet portion 13 and the gas cooling chamber 14. The turbine exhaust gas, which flows in order and remains in a gaseous state, is discharged to the outside as shown by arrow D. Here, in the present embodiment, the cross-sectional area of the flow opening 18 in the vertical plane is S1, the baffle plate 15 and the side wall portions of the main body container 11 (specifically, the second to fourth side wall portions 11B to 11D). When the cross-sectional area of the space formed on the gas inlet portion 13 side in the horizontal plane is S2, the relationship of S1 ≧ S2 is established. As a result, a decrease in the flow velocity of the turbine exhaust flowing from the flow opening 18 to the baffle plate 15 and the second side wall portion 11B is suppressed, and the pressure loss of the turbine exhaust is suppressed. As a result, the retention of the flow is suppressed even between the baffle plate 15 and the second side wall portion 11B from the flow opening 18.

Further, when the cross-sectional area of the gas inlet portion 13 in the vertical plane through which the turbine exhaust passes is S3 and the cross-sectional area of the gas cooling chamber 14 in the horizontal plane is S4, the relationship of S2 ≧ S3 and / or S2 ≧ S4. Is true. As a result, a decrease in the flow velocity of the turbine exhaust flowing from between the baffle plate 15 and the second side wall portion 11B to the gas inlet portion 13 and the gas cooling chamber 14 is also suppressed, and the pressure loss of the turbine exhaust is suppressed. As a result, the retention of the flow from between the baffle plate 15 and the second side wall portion 11B is suppressed even in the gas inlet portion 13 and the gas cooling chamber 14. More specifically, in the present embodiment, the relationship of S1 ≧ S2 ≧ S3 ≧ S4 is established, so that the decrease in the flow velocity of the turbine exhaust gas is effectively suppressed, and the retention of the flow after the flow opening 18 is effectively suppressed. It will be suppressed.

Therefore, according to the present embodiment, the degree of vacuum inside the condenser can be stably maintained in a desired state by suppressing the retention of the flow inside the condenser.

That is, the turbine exhaust discharged from the turbine in the geothermal power plant is a mixed fluid of water vapor and non-condensable gas. In this case, only water vapor is condensed in the main body container 11, so that the turbine exhaust flows downstream. The flow velocity gradually decreases and the concentration of non-condensable gas increases. Therefore, on the gas cooling chamber 14 side of the main body container 11, the concentration of non-condensable gas becomes high and the flow velocity of the turbine exhaust becomes slow, so that the flow tends to stay. If such a flow stays, the non-condensable gas is less likely to be discharged from the condenser 1, the heat transfer performance is deteriorated, and the degree of vacuum inside the condenser may be deteriorated. On the other hand, in the present embodiment, by providing the baffle plate 15 facing the gas inlet portion 13, the retention of the flow inside the condenser can be suppressed, and the retention of the non-condensed gas inside the condenser is suppressed. To. As a result, the non-condensable gas can be discharged smoothly, so that the degree of vacuum inside the condenser can be stably maintained in a desired state.

In particular, the relationship of S2 ≧ S3 and / or S2 ≧ S4 and the relationship of S1 ≧ S2 are established. As a result, the retention of the flow after the flow opening 18 is suppressed and the non-condensed gas is effectively discharged, so that the degree of vacuum inside the condenser can be effectively improved.

<Second embodiment>
Next, the direct contact condenser according to the second embodiment will be described with reference to FIG. 7. Of the components of the condenser according to the present embodiment, the same components as those of the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.

As shown in FIG. 7A, the present embodiment is different from the first embodiment in that the baffle plate 15 is provided with the gap portion 15S penetrating in the horizontal direction. A plurality of gap portions 15S are provided, and are formed in a slit shape that is long in the horizontal direction.

Further, with reference to FIGS. 2 to 4, in the present embodiment, the cross-sectional area of the flow opening 18 in the vertical plane is S1, and the side wall portion of the baffle plate 15 and the main body container 11 (specifically, the second to fourth side wall portions). 11B to 11D) have S2 the cross-sectional area of the space formed on the gas inlet 13 side in the horizontal plane, S3 the cross-sectional area of the gas inlet 13 in the vertical plane through which the turbine exhaust passes, and the horizontal plane of the gas cooling chamber 14. When the cross-sectional area in is S4 and the cross-sectional area of the gap portion 15S in the vertical plane (total cross-sectional area of the plurality of gap portions 15S) is S5, the relationship of S1 + S5 ≧ S2 is established. Further, the relationship of S2 ≧ S3 and / or S2 ≧ S4 is established.

In the condenser according to the second embodiment as described above, the turbine exhaust gas flows to the gas inlet portion 13 side through the gap portion 15S of the baffle plate 15, and is in front of the baffle plate 15, that is, the baffle. Flow retention is less likely to occur on the turbine exhaust duct 10 side of the plate 15.

In the first embodiment described above, the baffle plate 15 is installed to suppress the retention of the flow inside the main body container 11, but the baffle plate 15 completely passes through the horizontal direction of the flow colliding with itself. When shutting off, there is a possibility that the flow tends to stay in front of the baffle plate 15 (on the turbine exhaust duct 10 side). On the other hand, in the present embodiment, since the turbine exhaust gas can pass through the gap portion 15S by providing the gap portion 15S in the baffle plate 15, it is possible to prevent the flow from staying in front of the baffle plate 15. As a result, the non-condensable gas can be discharged smoothly, so that the degree of vacuum inside the condenser can be reliably maintained in a desired state.

Further, by establishing the relationship of S1 + S5 ≧ S2 as described above, it is possible to suppress a decrease in the flow velocity of the turbine exhaust gas flowing from the flow opening 18 and the gap portion 15S between the baffle plate 15 and the second side wall portion 11B. , Turbine exhaust pressure loss can be suppressed. As a result, the retention of the flow after the flow opening 18 and the gap portion 15S can be suppressed, so that a desired degree of vacuum can be obtained more reliably.

In FIG. 7A, the gap portion 15S is formed in a slit shape that is elongated in the horizontal direction, but the shape of the gap portion 15S is not particularly limited. For example, examples of modifications to the shape of the gap portion 15S include a vertically elongated shape as shown in FIG. 7 (B) and a circular shape as shown in FIG. 7 (C). Further, the gap portion 15S may have an elliptical shape or the like.

<Third embodiment>
Next, the direct contact condenser according to the third embodiment will be described with reference to FIGS. 8 and 9. Of the components of the condenser according to the present embodiment, the same components as those of the first and second embodiments are designated by the same reference numerals, and the description thereof will be omitted.

The condenser according to the present embodiment is different from the first embodiment in that it is an upward inflow type direct contact condenser. Specifically, the water condensing device according to the present embodiment shown in FIG. 8 is connected to the turbine exhaust duct 10 into which the turbine exhaust from the turbine flows in and the turbine exhaust duct 10, and upwards the turbine exhaust from the turbine exhaust duct 10. The main body body container 11 that receives from the main body body container 11, the cooling water supply pipe 12 that supplies cooling water to the inside of the main body body container 11, and the main body body container 11 that is provided in the main body body container 11 at a position horizontally separated from the turbine exhaust duct 10 in the horizontal direction. A gas inlet portion 13 that opens, a gas cooling chamber 14 connected to the main body body container 11 via the gas inlet portion 13, and a baffle plate arranged inside the main body body container 11 so as to face the gas inlet portion 13. It is equipped with 15. A passage opening 18 through which turbine exhaust passes is formed between the upper portion 15A of the baffle plate 15 and the inner wall surface of the main body container 11 facing the upper portion 15A in the vertical direction.

The main body container 11 is formed to be elongated in the horizontal direction, and the turbine exhaust duct 10 is connected to the central position in the longitudinal direction of the upper portion thereof. As shown by the arrow A', the main body body container 11 allows the exhaust gas from the turbine exhaust duct 10 to flow in from above along the vertical direction, and inside the main body body container 11, the cooling water from the cooling water supply pipe 12 is directly sent to the turbine exhaust gas. By contacting, the water vapor contained in the turbine exhaust is condensed. In the present embodiment, the gas inlet portion 13, the gas cooling chamber 14, and the baffle plate 15 are provided on one side and the other side of the main body container 11 at the center position in the longitudinal direction. That is, the main body container 11 is provided with a pair of gas inlet portions 13, a pair of gas cooling chambers 14, and a pair of baffle plates 15. Further, FIG. 9 is a cross-sectional view taken along the line IX-IX of FIG. 8, and as shown in the figure, the cross-sectional shape of the main body container 11 on the vertical plane orthogonal to the longitudinal direction is circular.

Also in this embodiment, the baffle plate 15 is arranged so that the pair of main surfaces facing each other in the thickness direction are parallel to each other in the vertical direction, and one of the main surfaces faces the gas inlet portion 13 in the horizontal direction. However, also in this embodiment, the baffle plate 15 may be arranged so as to be inclined with respect to the vertical direction. Further, as shown in FIG. 9, since the cross-sectional shape of the main body container 11 on the vertical surface is circular, the side portion of the baffle plate 15 is curved along the arc of the main body container 11. Further, the baffle plate 15 in the present embodiment is arranged at a position horizontally separated from the downstream opening of the turbine exhaust duct 10, and more specifically, the gas inlet portion 13 side of the end portion of the cooling water supply pipe 12. Is located in. In this embodiment, the cooling water supply pipe 12 is arranged along the longitudinal direction of the main body container 11.

Further, also in the present embodiment, as shown in FIG. 8, the cross-sectional area of the flow opening 18 formed above the baffle plate 15 in the vertical plane is S1, and the baffle plate 15 and the side wall portion of the main body container 11 have a cross-sectional area. When the cross-sectional area of the space formed on the gas inlet portion 13 side in the horizontal plane is S2, the relationship of S1 ≧ S2 is established.

Further, when the cross-sectional area of the gas inlet portion 13 in the vertical plane through which the turbine exhaust passes is S3 and the cross-sectional area of the gas cooling chamber 14 in the horizontal plane is S4, the relationship of S2 ≧ S3 and / or S2 ≧ S4. More specifically, also in this embodiment, the relationship of S2 ≧ S3 and S2 ≧ S4 is established, and further, the relationship of S3 ≧ S4 is also established. That is, the relationship of S1 ≧ S2 ≧ S3 ≧ S4 is established. Also in the present embodiment, the "portion through which the turbine exhaust passes in the gas inlet portion 13" corresponds to the portion above the water surface of the mixed water MW in the gas inlet portion 13. Further, also in the present embodiment, the baffle plate 15 may be provided with the gap portion 15S as described in the second embodiment, and in this case, the relationship of S1 + S5 ≧ S2 may be established.

The same effect as that of the first embodiment can be obtained in the condenser according to the third embodiment as described above. The upward inflow type direct contact condenser such as the condenser according to the present embodiment is often used in a relatively small plant having an output of 10 MW or less. In such an upward inflow type direct contact condenser, the turbine exhaust gas flows in from above and then branches to the left and right. Therefore, in order to improve the efficiency of condensation, the gas cooling chamber is used as in the present embodiment. It is common that 14 is installed on the left and right. In the present embodiment, by providing the baffle plate 15 corresponding to each of the gas cooling chambers 14, it is possible to effectively suppress the retention of the flow that may occur on the left and right.

Although each embodiment has been described above, each of the above embodiments is presented as an example and is not intended to limit the scope of the invention. This novel embodiment can be implemented in various other embodiments, and various omissions, replacements, and changes can be made without departing from the gist of the invention. This embodiment and its modifications are included in the scope and gist of the invention, and are also included in the scope of the invention described in the claims and the equivalent scope thereof.

1 ... Direct contact condenser, 10 ... Turbine exhaust duct, 11 ... Main body container, 11A ... First side wall, 11B ... Second side wall, 11C ... Third side wall, 11D ... Fourth side wall, 12 ... Cooling water supply pipe, 12A ... Piping part, 12B ... Spray nozzle, 13 ... Gas inlet part, 14 ... Gas cooling chamber, 14A ... Gas outlet part, 15 ... Baffle plate, 15A ... Upper part, 15S ... Void part, 16 ... Mixing water outlet nozzle, 17 ... hot well, 18 ... flow opening

Claims (5)

The turbine exhaust duct into which the turbine exhaust from the turbine flows in, and
A main body container connected to the turbine exhaust duct and receiving turbine exhaust from the turbine exhaust duct from the side or above.
A cooling water supply pipe that supplies cooling water to the inside of the main body container,
When the main body container receives turbine exhaust from the side, the main body container is provided on the side opposite to the turbine exhaust duct side of the main body container and opens horizontally, and the main body container exhausts the turbine from above. In the case of accepting, a gas inlet portion provided in the main body container at a position horizontally separated from the turbine exhaust duct and opening horizontally, and
A gas cooling chamber connected to the main body container via the gas inlet portion,
A baffle plate arranged inside the main body container so as to face the gas inlet portion is provided.
A direct contact condenser in which a flow opening through which turbine exhaust passes is formed between the upper part of the baffle plate and the inner wall surface of the main body body container facing the upper part of the baffle plate in the vertical direction. The cross-sectional area of the space formed by the baffle plate and the side wall portion of the main body container on the gas inlet side in the horizontal plane is S2, and the cross-sectional area of the gas inlet portion where the turbine exhaust passes in the vertical plane is S3. The direct contact condenser according to claim 1, wherein the relationship of S2 ≧ S3 and / or S2 ≧ S4 holds when the cross-sectional area of the gas cooling chamber in the horizontal plane is S4. The cross-sectional area of the flow opening between the upper part of the baffle plate and the upper part of the baffle plate and the inner wall surface of the main body container facing up and down in the vertical direction is S1, the baffle plate and the main body container. The direct contact type water condenser according to claim 1 or 2, wherein the relationship of S1 ≧ S2 is established when the cross-sectional area of the space formed on the side wall of the gas inlet portion on the horizontal plane is S2. The baffle plate is provided with a gap portion that penetrates in the horizontal direction.
The cross-sectional area of the flow opening between the upper part of the baffle plate and the upper part of the baffle plate and the inner wall surface of the main body body container facing up and down in the vertical direction is S1, the baffle plate and the main body body container. The relationship of S1 + S5 ≧ S2 is established when the cross-sectional area of the side wall portion of the space formed on the gas inlet portion side in the horizontal plane is S2 and the cross-sectional area of the void portion in the vertical plane is S5. The direct contact type water recovery device according to 2. A power plant comprising the direct contact condenser according to any one of claims 1 to 4.

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