JPS6018916B2 - condensate equipment - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a device for reheating condensate condensed in a condenser in a power plant equipped with a feedwater pump-driven turbine.

In thermal and nuclear power plants equipped with conventional feed water pump driving turbines, as shown in FIG. Pump drive turbine exhaust inlet account 5
The inflowing water pump drive turbine exhaust steam Y, which flows into the main condenser 4, mixes with the exhaust steam Y2 of the main turbine 6, condenses on the cooling pipe 8, and becomes condensed water into the hot well 9. Fall.

The condensate remaining in the hot well 9 is sucked out of the condenser 4 by a condensate pump 1 and sent to a feed water heater (not shown). On the other hand, the gas that does not condense on the cooling pipe 8 is subcooled in the air cooling section 2 on the east side of the cooling pipe, which in this case contains the gas of the main turbine and the feed water pump drive turbine, and is then subcooled in the air extractor 7 to the condenser. 4 It is sucked out. In this way, the exhaust steam of the feedwater pump-driven turbine is cooled and condensed with cooling water through the condenser cooling pipe together with the main turbine exhaust steam.
It has the following drawbacks.

[1' In a turbine plant, it is not possible for the cooling water to recover the heat taken from the exhaust steam to condense the exhaust steam and return it to the turbine cycle, so the heat of the turbine exhaust steam driven by the feed water pump is also discarded into the cooling water. It turns out.

When the '21 feedwater pump drive turbine exhaust steam flows into the main condenser, it collides with the main turbine exhaust steam, disturbing the main turbine exhaust flow and causing pressure loss.

This pressure loss is larger than expected, leading to a decrease in turbine output. Generally, it is known that the thermal efficiency of the turbine cycle increases if the condensed water condensed in the condenser is reheated and supplied to the turbine cycle.For example, in a double pressure condenser, condensate from the low pressure chamber is transferred to the high pressure chamber. The condensate is then reheated using steam in a high-pressure chamber (Utility Model Publication No. 49-29124).

Therefore, instead of condensing the exhaust steam of the feed water pump drive turbine with cooling water together with the main turbine exhaust steam, if the exhaust steam of the feed water pump drive turbine is condensed in condensed water, which is the condensation of the main turbine exhaust steam, it is possible to The heat content of the exhaust steam of the pump-driven turbine helps to raise the temperature of the condensate.

In other words, by raising the temperature of condensate and returning it to a boiler or the like, it is possible to increase the thermal efficiency of the entire turbine plant. For example, in a 1100MW class nuclear power plant,
When the main condenser is operated at a vacuum level of 72 Hg,
According to the conventional method, the condenser outlet temperature of condensate is 33. However, if the condensate is reheated by the feedwater pump-driven turbine exhaust steam, the temperature of the condensate will be 1. 9qo, which is about 6.7°C higher than the conventional method. The present invention has been made in view of the above-mentioned points, and the present invention aims to improve the thermal efficiency of a turbine plant and prevent disturbance of main turbine exhaust steam caused by feedwater pump-driven turbine exhaust flowing into the condenser. Our goal is to provide the following.

An embodiment of the present invention will be described below with reference to the drawings.

As shown in FIGS. 2 and 3, the present invention comprises a high pressure chamber 11 installed at the bottom of the main condenser 4 and a non-condensable gas discharge device 12 disposed above the high pressure chamber 11. The high pressure chamber 11 is
It is divided by a ceiling plate 13 (which can also serve as the bottom plate of the main condenser 4), a bottom plate 14, and side plates 25a and 15b,
It consists of an upper condensate distribution section 16, a lower condensate reheat section 17, and a reheat hotwell 18.

The condensate distribution section 16 is connected to a downpipe 19 communicating with the hot well 9 of the main condenser 4 by penetrating through the ceiling plate 13.

Directly below this downcomer pipe 19, as shown in FIGS. 2 and 3, a condensate receiver 20 is provided, and on both sides of the condensate receiver 20, perforated plates 21 for distributing and dispersing condensate are provided. ing.
A water supply pump drive turbine exhaust inlet port 22 is installed on one side plate 15a forming a side surface of the condensate reheating section 17, and a non-condensable gas outlet port 23 is installed on the opposite side plate 15b. A condensate outlet box 24 is installed on the bottom plate 14 at the bottom of the reheat hot well 18 and is connected to a condensate pipe 25. In addition, a balance pipe 2 is provided between the condensate distribution section 16 and the condensate reheat section 17.
6 is provided to communicate between both. The non-condensable gas discharge device 12 has one end connected to the non-condensable gas outlet 23 provided on the side plate 15b of the high pressure chamber 11, and the other end connected to the air cooling section in the east of the cooling pipe 8 in the main condenser 4. 2, and is composed of a non-condensable gas exhaust pipe 28 with a throttle 27 provided in the middle.

In the condensing device configured in this way, the condensed water condensed in the main condenser 4 falls into the hot well 9.
From the downcomer pipe 19 connected to the lower part, the condensate passes through the condensate receiver 20 in the high pressure chamber 11 and flows onto the condensate distribution perforated plate 21 due to the difference in gravity. This condensate receiver 20 includes a main condenser 4 and a high pressure chamber 11.
The porous plate 21 is provided in order to maintain a pressure difference between the perforated plate 21 and the perforated plate 21, and to allow condensate to flow uniformly onto the perforated plate 21. The condensate flowing onto the perforated plate 21 is almost uniformly distributed to the lower condensate reheating section 17 while maintaining the jetting velocity head h necessary for dispersing a predetermined amount of condensate from the dispersion holes. On the other hand, exhaust steam from the feedwater pump drive turbine l passes through the exhaust pipe 3 and flows into the condensate reheating section 17 of the high pressure chamber 11 from the feedwater pump drive turbine exhaust inlet account 22, and the exhaust steam that has fallen from the perforated plate 21 flows into the condensate reheating section 17 of the high pressure chamber 11. Direct contact with water. This high pressure chamber 11 has a pressure higher than the internal pressure of the main condenser 4 and is made to be able to withstand the pressure of exhaust steam from the feedwater pump driving turbine 1 .
There, the condensate is heated to near the saturated steam temperature in the high pressure chamber 11 by heat exchange through direct contact with the feed water pump drive turbine exhaust steam. In other words, the temperature of the condensate increases by the difference in saturated steam temperature with respect to the internal pressure of the main condenser 4 and the internal pressure of the high pressure chamber 11. When the condensate is heated, the solubility of the gas in the condensate decreases, so that gas is released from the condensate.

In other words, the condensate is degassed. In addition, non-condensable gas in the exhaust steam of the feed water pump driving turbine also remains in the high pressure chamber 11. Since it is unfavorable for such gas to remain in the condensate reheating section 17 in terms of heat exchange, the internal pressure of the main condenser 4 and the high pressure chamber 1
1, the non-condensable gas is discharged from the non-condensable gas outlet 23 to the air cooling section 2 of the main condenser 4 through the non-condensable gas discharge pipe 28. At this time, the amount of non-condensable gas is controlled by a throttle 27 provided in the middle of the exhaust pipe 28. The non-condensable gas in the high pressure chamber 11 discharged to the air cooling section 2 is supercooled together with the non-condensable gas in the main condenser 4 and is sucked out of the main condenser 4 by the air extractor 7.

In short, the non-condensable gas is discharged at the point where it is cooled the most, but steam corresponding to the partial pressure relative to the temperature of the discharge section is discharged together with the non-condensable gas, so the air cooling section 2 of the main condenser 4 When the steam is supercooled, the vapor is condensed, so that the non-condensable gas is compressed, which reduces the negative impact of the air extractor 7. As shown in FIG. 4, this non-condensable gas discharge device 12 connects a cooler 29 in the middle of the non-condensable gas discharge pipe 28 to supply this non-condensable gas instead of the air cooling section 2 of the main condenser 4. A similar effect can be obtained by subcooling the air using the cooler 29 and sucking it out using the air extractor 7 connected to the main condenser 4.

In addition, in FIG. 4, the non-condensable gas supercooled by the cooler 29 is sucked out separately by an air extractor (not shown) that is separate from the air extractor 7 connected to the main condenser 4. Also good.

Furthermore, in the above explanation, the non-condensable gas is discharged to the air cooling section 2 of the main condenser 4 through the throttle 27 through the discharge pipe 28, but this discharge pipe 28 is connected to the inside of the condenser 4. There is nothing wrong with just that.

The condensing device that drops condensate from the main condenser 4 into the high pressure chamber 11 due to the difference in gravity has been described above, but as shown in FIG. The condensate is sent to the high pressure chamber 11, and the condensate reheated in the high pressure chamber 11 is sent to the booster pump 30' to the trowel feed water heater (not shown).
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As explained above, according to the present invention, the exhaust steam of the turbine driven by the water supply pump is introduced into the high pressure chamber installed separately instead of the main condenser, thereby recovering the heat amount of the exhaust steam into condensate, and then An unprecedented advantage is achieved in that the condensate is degassed and does not disturb the main turbine exhaust steam flow.

[Brief explanation of the drawing]

Fig. 1 is a cross-sectional view perpendicular to the cooling pipe of a conventional condenser and a simple system diagram of its surroundings, Fig. 2 is a cross-sectional view of the condensing device according to the present invention, and Fig. 3 is the same as that of Fig. 2. 4 and 5 are schematic diagrams showing other embodiments of the condensing device according to the present invention. 1... Water pump drive turbine, 4...
・Main condenser, 6...Main turbine, 7...
・Air extractor, 9...・Hotwell, 11...
...High pressure chamber, 12...Noncondensable gas discharge device, 1
6... Condensate distribution section, 17... Condensate reheating section,
18...Reheat hot well, 19...
Downpipe, 20... Condensate receiver, 21... Perforated plate, 26... Balance pipe, 28... Non-condensable gas discharge pipe, 29... ··Cooler. Figure 3 Figure 4 Figure 1 Figure 2 Figure 5

Claims (1)

[Claims] 1. A main condenser and a high-pressure chamber connected to the main condenser, the main condenser having an upper part inside the container for guiding exhaust steam from the main turbine into the main condenser. A cooling pipe group for condensing water, an air cooling section for extracting and cooling non-condensable gas generated when the exhaust steam is condensed, and a hot well below these for collecting the condensate of the exhaust steam, The high-pressure chamber takes in the condensate through the downcomer pipe connected to the hot well in the upper part of the vessel, and has a condensate distribution section that distributes this condensate, and a lower part of the chamber that introduces the exhaust steam from the boiler feed water pump driving turbine into the interior. , a boiler comprising a condensate reheating section that directly contacts the condensate and heats it to an appropriate temperature, and further comprising a noncondensable gas discharge device that connects the condensate reheating section and the air cooling section. A condensing device characterized in that it is configured such that non-condensable gas generated during condensation of feedwater pump-driven turbine exhaust steam is extracted to the outside through an air cooling section. 2. A condensate receiver is formed in the condensate distribution section, and the other end of the downcomer tube connected to the hot well faces the bottom of the condensate receiver. Condensing equipment.