JP2015068612A - Direct contact type condenser - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a direct contact type condenser such that a noncondensable gas can be smoothly discharged from the condenser.SOLUTION: A direct contact type condenser includes: a condensation chamber (2) into which a mixed gas of steam discharged from a steam turbine and a noncondensable gas is introduced; and a gas cooling chamber (3) which is coupled to a lower part of the condensation chamber and extends in a horizontal first direction (X). The condensation chamber and gas cooling chamber are provided with first and second spray nozzles (12) respectively. The condensation chamber and gas cooling chamber communicate with each other through a communication port (6) provided in a wall body partitioning off the condensation chamber and gas cooling chamber. An exhaust port (7) is provided in a side part of the gas cooling chamber at a first-directional end of the gas cooling chamber. The exhaust port is sucked and the mixed gas having flowed in the gas cooling chamber from the condensation chamber through the communication port (6) flows to the exhaust port.

Description

  Embodiments of the invention relate to a direct contact condenser.

  In a geothermal power plant, steam turbine exhaust steam is introduced into a condenser. There are two types of condensers for geothermal power plants: a surface contact condenser using a cooling pipe and a direct contact condenser using a cooling water spray. Often used. The direct contact type condenser condenses the steam by bringing the coolant sprayed from the coolant spray nozzle into direct contact with the steam.

  Unlike the steam used in thermal power plants, nuclear power plants and the like, geothermal steam contains a large amount of non-condensable gas such as carbon dioxide. Since high-concentration non-condensable gas is one of the factors that hinder the condensation of steam, it is possible to efficiently cool the non-condensable gas inside the condenser and discharge it smoothly outside the condenser. Regardless of the type, it is important to improve condenser performance. Therefore, it is desired to prevent the non-condensable gas from staying in the condenser and to realize a smooth flow.

JP-A-8-121979

  An object of an embodiment of the present invention is to provide a direct contact condenser that can smoothly discharge non-condensable gas from the condenser.

  According to one embodiment, a condensation chamber having an inlet into which a mixed gas of steam and non-condensable gas discharged from a steam turbine is introduced downward, a first spray nozzle that sprays cooling water into the condensation chamber, and condensation A direct contact condenser is provided that includes a gas cooling chamber connected to the lower portion of the chamber and extending in a horizontal first direction, and a second spray nozzle that sprays cooling water into the gas cooling chamber. The condensing chamber and the gas cooling chamber communicate with each other through a communication port provided in a wall body that partitions the condensing chamber and the gas cooling chamber. In addition, at the end of the gas cooling chamber in the first direction, an exhaust port is provided on the side of the gas cooling chamber. The exhaust port is sucked, and the mixed gas that has flowed from the condensing chamber through the communication port into the gas cooling chamber flows to the exhaust port.

It is a figure which shows 1st Embodiment of a condenser, Comprising: The perspective view which shows only the wall body which comprises a condensing chamber and a gas cooling chamber. The figure which shows the II-II cross section in FIG. The figure which shows the III-III cross section in FIG. It is a figure which shows 2nd Embodiment of a condenser, Comprising: The figure which shows the cross section similar to FIG. It is a figure which shows 2nd Embodiment of a condenser, Comprising: The perspective view which shows only the wall body which comprises a condensing chamber and a gas cooling chamber. The figure which shows the VI-VI cross section in FIG. The figure which shows the VII-VII cross section in FIG.

  With reference to the accompanying drawings, an embodiment of a lower exhaust type direct contact condenser (spray condenser) will be described below. In each embodiment, the same code | symbol is attached | subjected to the member which has the same thru | or similar function, and duplication description shall be abbreviate | omitted.

[First Embodiment]
First, a first embodiment will be described with reference to FIGS. In order to facilitate explanation of the directions, XYZ rectangular coordinate forms are set in the drawings. The Z direction is a vertical direction, and the XY plane is a horizontal plane.

  The condenser has a condenser body 1. The condenser body 1 has a condensing chamber 2 and a gas cooling chamber 3 connected to the lower portion of the condensing chamber 2. The gas cooling chamber 3 extends with the width direction (X direction) of the condenser as the first direction in the center of the condenser depth method (Y direction). As shown in FIG. 1, the condensing chamber 2 and the gas cooling chamber 3 are not only the same width, but the gas cooling chamber 3 can be narrower than the condensing chamber 2, for example.

  The condensing chamber 2 and the gas cooling chamber 3 are vertically divided by a partition wall 4 that forms a part of the bottom wall 2a of the condensing chamber 2 and at the same time the ceiling wall of the gas cooling chamber 3, that is, a wall body. The bottom wall 2a and the partition wall 4 can be comprised with the same board | plate material.

  Communication that connects the condensing chamber 2 and the gas cooling chamber 3 to the central portion of the bottom wall 2a of the condensing chamber 2 (the central portion in the X direction and the central portion in the Y direction), that is, the central portion in the X direction of the partition wall 4. A mouth 6 is provided.

  At the upper end of the condensing chamber 2, a turbine exhaust inlet 2 b into which exhaust from the steam turbine 5 schematically shown in FIG. 2 flows is provided. The axial direction of the steam turbine 2 coincides with the X direction.

  One exhaust port 7 is provided in each of the wall bodies 3a at both ends in the longitudinal direction (X direction) of the gas cooling chamber 3. An exhaust pipe (not shown) is connected to each exhaust port 7, and a vacuum pump or an ejector (not shown) is interposed in the exhaust pipe (not shown) to suck the gas cooling chamber 3.

  In the condenser body 2, a large number of cooling water supply pipes 10 extend in the vertical direction (Z direction) at intervals in the horizontal direction. A plurality of spray nozzles 12 (only some of which are shown in FIG. 2) are attached to each cooling water supply pipe 10.

  The spray nozzle 12 can be installed in various horizontal directions (various directions in the XY plane), but FIG. 2 shows only those facing the X positive direction and the X negative direction. Yes. The direction of the spray nozzle 12 may be other than the horizontal direction.

  Cooling water is supplied to the cooling water supply pipe 10 via the header 14, and this cooling water is sprayed from each spray nozzle 12.

  It is also possible to form a spray nozzle by the hole perforated in the cooling water supply pipe 10 itself.

  A part of the plurality of cooling water supply pipes 10 (enclosed by a one-dot chain line in FIG. 3) passes through the bottom wall 2a and continuously extends in the condensation chamber 2 and the gas cooling chamber 3 as shown in FIG. Some of the plurality of spray nozzles 12 provided in the cooling water supply pipe 10 spray the cooling water into the condensing chamber 2, and the other spray nozzles 12 cool into the gas cooling chamber 3. Spray water. With this configuration, the installation cost of the cooling water supply pipe 10 can be reduced.

  The remaining portions of the plurality of cooling water supply pipes 10 (not surrounded by the one-dot chain line in FIG. 3) are in the condensation chamber 2 but not in the gas cooling chamber 3. That is, the cooling water supply pipe 10 is provided in a region of the bottom wall 2a of the condensation chamber 2 where the gas cooling chamber 3 is not provided. The spray nozzle 12 provided in the cooling water supply pipe 10 sprays the cooling water only in the condensation chamber 2.

  Of the plurality of spray nozzles 12, the one in the condensing chamber 2 may be referred to as the first spray nozzle and the second spray nozzle in the gas cooling chamber 3.

  The operation of the condenser according to the first embodiment will be described below.

  The exhaust from the steam turbine 5 flows into the condensing chamber 2 from the turbine exhaust inlet 2b as indicated by the white arrow in FIG. This exhaust is a mixed gas of steam and a non-condensable gas such as carbon dioxide.

  Cooling water is sprayed in the horizontal direction from the spray nozzle 12 in the condensing chamber 2, and the sprayed cooling water mist falls downward due to gravity. The vapor in the mixed gas flowing down in the condensation chamber 2 is cooled and condensed by coming into contact with the cooling water mist. Condensed water (condensate) passes through the communication port 6 and falls into the gas cooling chamber 3, and is discharged from the gas cooling chamber 3 through the drain line 8 provided on the bottom wall 3 b of the gas cooling chamber 3.

  The flow rate of the mixed gas in the condensation chamber 2 is not uniform. In the illustrated embodiment, due to the connection relationship with the steam turbine 5, the inflow speed of the mixed gas is relatively large at both ends in the X direction in FIG. , It tends to be relatively small at the center in the X direction.

  As the condensation progresses in the condensing chamber 2 and the amount of vapor contained in the mixed gas decreases, the flow velocity of the mixed gas decreases. For this reason, the flow rate of the mixed gas is particularly low at the center in the X direction where the flow rate is originally low, and the retention of the mixed gas (especially the condensed gas contained therein) is likely to occur (the communication port 6 is not at the position shown in the figure). If).

  However, in the first embodiment, since the communication port 6 is provided in the central portion of the bottom wall 2a of the condensation chamber 2, the mixed gas existing in the region where the stagnation is likely to occur is not cooled and gas cooling is performed. It is sucked into the room 3. In addition, the mixed gas at a site away from the communication port 6 is also sucked into the gas cooling chamber 3 through the communication port 6. As described above, the non-condensable gas smoothly flows out to the gas cooling chamber 3 without staying in the condensation chamber 2, so that it is possible to prevent the vapor condensation efficiency from being lowered due to retention of the non-condensable gas in the condensation chamber 2.

  The mixed gas in which a large amount of vapor is removed by condensation in the condensation chamber 2 and the ratio of the non-condensable gas is increased is discharged through the communication port 6 into the gas cooling chamber 3 substantially downward.

  Since the inside of the gas cooling chamber 3 is sucked through the exhaust port 7, the mixed gas flowing into the gas cooling chamber 3 is substantially horizontal (X positive direction and X negative direction) as shown by solid line arrows in FIG. ), Flows in the gas cooling chamber 3 in the horizontal direction toward the exhaust port 7, and is discharged from the exhaust port 7 in the substantially horizontal direction.

  Cooling water is sprayed in the horizontal direction also from the spray nozzle 12 in the gas cooling chamber 3, and the condensed gas cannot be fully condensed in the condensation chamber 2 due to contact between the mixed gas and the cooling water or the spray nozzle spray droplets. The vapor is condensed, and the non-condensable gas in the mixed gas is further cooled.

  In the first embodiment, since the mixed gas contacts the cooling water mist while flowing in the gas cooling chamber 3 in the horizontal direction, the pressure loss in the gas cooling chamber 3 can be reduced, and the mixed gas, particularly the non-condensable gas. Can be smoothly discharged out of the gas cooling chamber 3. The reason is as follows.

  The cooling water mist sprayed from the spray nozzle 12 in the gas cooling chamber 3 is sprayed in various horizontal directions, but the mist travels in the horizontal direction in a very short time immediately after spraying. After that, it falls downward due to gravity. The degree to which the cooling water mist falling downward becomes the resistance of the flow of the mixed gas flowing in the horizontal direction is small, and therefore the pressure loss in the gas cooling chamber 3 can be reduced.

  On the other hand, when the mixed gas is caused to flow upward in the gas cooling chamber 3, the flow of the cooling water mist that falls downward due to gravity becomes an opposite flow that opposes the flow of the mixed gas. The pressure loss becomes larger than in the case of the embodiment.

  If only the flow of the cooling water mist in the gas cooling chamber 3 is prevented from becoming a counter flow opposite to the flow of the mixed gas, both the flow of the cooling water mist and the flow of the mixed gas are directed downward. In this case, however, the height of the gas cooling chamber 3 is increased, the overall height of the condenser body 1 is increased, and the degree of freedom of installation of the condenser (for example, conditions such as digging down the building) is increased. Since it falls, it is not preferable.

  In order to allow a certain amount of cooling water mist to take more heat from the mixed gas (cooling water mist does more work), the heat exchange time between the cooling water mist and the mixed gas must be reduced. It is necessary to make it sufficiently long. To this end, it is necessary to ensure a long drop distance of the cooling water mist. Actually, the condensation chamber 2 in which the condensation of steam is mainly performed is designed in such a viewpoint, and both the cooling water mist and the mixed gas move a relatively long vertical distance. Furthermore, the temperature of the mixed gas is lowered by the cooling water, and the temperature difference becomes small, and the temperature exchange efficiency is reduced. Therefore, the condensing chamber 2 is designed to be long in the vertical direction.

  However, the mixed gas flowing into the gas cooling chamber 3 has already had much steam removed in the condensing chamber 2, and both the steam partial pressure and the steam temperature are low. And since the phase change does not accompany the cooling of the non-condensable gas, it is not necessary for the cooling water mist to take much heat from the non-condensable gas. Therefore, the necessity for moving the cooling water mist and the mixed gas over a relatively long vertical distance is low. Therefore, there is almost no demerit caused by flowing the mixed gas in the gas cooling chamber 3 in the horizontal direction. Further, since the cooling water in the gas cooling chamber 3 condenses the steam for a very short time after the injection, the cooling chamber 3 is not designed to be long in the height direction, and the mixed gas flows in the horizontal direction after the injection. The contact time between the cooling water and the mixed gas is ensured.

  As described above, according to the first embodiment, non-condensable gas can be smoothly discharged out of the gas cooling chamber 3. For this reason, it is possible to prevent a decrease in gas cooling performance due to gas retention in the gas cooling chamber 3. Moreover, since the gas flow from the condensation chamber 2 to the gas cooling chamber 3 becomes smoother by preventing the gas stagnation in the gas cooling chamber 3, the condensation performance of the vapor in the condensation chamber 2 is also improved. be able to.

  In the first embodiment, the longitudinal direction (first direction) of the gas cooling chamber 3 is the X direction. However, the present invention is not limited to this, and the Y direction is the longitudinal direction (first direction). The gas cooling chamber 3 may be installed so that The installation direction (X, Y direction) of the gas cooling chamber 3 is the same in the following embodiments.

[Second Embodiment]
FIG. 4 shows a second embodiment of the condenser. In the second embodiment, the cooling water supply pipe 10 is installed horizontally (for example, in the X direction) in the condensing chamber 2 and the gas cooling chamber 3. Both ends of each cooling water supply pipe 10 installed in the condensing chamber 2 are firmly fixed to opposing side walls constituting the condensing chamber 2. In the second embodiment, a vertical header 14 is used.

  According to the above configuration, the cooling water supply pipe 10 also functions as a reinforcing member for the condenser body 1. For this reason, at least a part of the reinforcing member that is required to be provided in the condenser body 1 can be reduced, and the structure of the condenser body 1 can be simplified.

  The spraying direction of the spray nozzle 12 provided in the cooling water supply pipe 10 is not limited to directly below, and can be in various directions (horizontal direction, diagonally upward (downward) direction, etc.).

  The shapes of the condensing chamber 2 and the gas cooling chamber 3 in this second embodiment and the flow of the mixed gas in these chambers are the same as in the first embodiment, and the second embodiment is also a non-condensable gas as in the first embodiment. Can be discharged smoothly from the condenser body 2, so that the efficiency of the condenser can be improved.

[Third Embodiment]
Next, a third embodiment will be described with reference to FIGS.

  In the third embodiment, the condensing chamber 2 is divided into two chambers 2A and 2B by the partition member 20. Hereinafter, the chamber 2A is also referred to as a first condensing chamber 2A, and the chamber 2B is also referred to as a second condensing chamber 2B.

  A gas cooling chamber 3 is provided between the lower portion of the first condensing chamber 2A and the lower portion of the second condensing chamber 2B. The gas cooling chamber 3 extends in the width direction (Y direction) of the condenser at the central portion of the condenser width method (X direction). As shown in FIG. 5, the condensing chamber 2 and the gas cooling chamber 3 are not only the same width, but the gas cooling chamber 3 can be narrower than the condensing chamber 2, for example.

  A first portion of the partition member 20 between the first condensing chamber 2A and the gas cooling chamber 3 (that is, the wall body 3c that partitions the first condensing chamber 2A and the gas cooling chamber 3) has a first portion in the Y direction. A communication port 6 </ b> A (6) that connects the condensing chamber 2 </ b> A and the gas cooling chamber 3 is provided. Similarly, in the central portion of the partition member 20 between the second condensing chamber 2B and the gas cooling chamber 3 (that is, the wall body 3c that partitions the second condensing chamber 2B and the gas cooling chamber 3) in the center in the Y direction. In addition, a communication port 6B (6) for communicating the second condensing chamber 2B and the gas cooling chamber 3 is provided.

  As shown in FIG. 6, in the first condensing chamber 2A, the second condensing chamber 2B, and the gas cooling chamber 3, a large number of cooling water supply pipes 10 are spaced apart from each other in the horizontal direction, and the vertical direction (Z Direction). As in the first embodiment, each cooling water supply pipe 10 is provided with a plurality of spray nozzles 12 (only part of which are shown in FIG. 6).

  The operation of the condenser according to the third embodiment will be described below.

  Exhaust gas (mixed gas) from the steam turbine 5 flows into the first and second condensing chambers 2A and 2B from the turbine exhaust inlet 2b.

  In this 3rd Embodiment, the partition member 20 is provided in the X direction center part in which the flow velocity of mixed gas is the slowest, Thereby, the X direction center part of a condensation chamber is lose | eliminated. The total flow path width in the X direction of the first and second condensation chambers 2A, 2B is narrower than the total flow path width in the X direction of the condensation chamber 2 of the first embodiment.

  For this reason, the portion where the flow rate of the mixed gas is as slow as the central portion in the X direction of the condensing chamber 2 of the first embodiment is in the condensing chamber 2 (first and second condensing chambers 2A and 2B) of the third embodiment. not exist. For this reason, compared with 1st Embodiment, the residence in a condensation chamber does not arise easily.

  However, the flow velocity distribution is also present in the first and second condensing chambers 2 </ b> A and 2 </ b> B, and the flow velocity of the mixed gas in the region near the partition member 20 is smaller than the flow velocity of the mixed gas in the region far from the partition member 20. Accordingly, in this region, gas retention tends to occur relatively easily.

  However, in the third embodiment, the wall that partitions the first and second condensing chambers 2A, 2B and the gas cooling chamber 3 at the lower end of the region near the partition member 20 where the flow rate of the mixed gas tends to be small. Since the communication ports 6A and 6B are provided at the center in the Y direction of the body (the lower end of the partition member 20), the mixed gas existing in the region where the stagnation is likely to occur is not retained in the gas cooling chamber 3 Sucked into.

  The mixed gas, in which a large amount of vapor is removed by condensation in the first and second condensing chambers 2A and 2B and the ratio of non-condensable gas is increased, passes into the gas cooling chamber 3 through the communication ports 6A and 6B. It flows in the horizontal direction (X direction).

  Since the inside of the gas cooling chamber 3 is sucked through the exhaust port 7, the mixed gas flowing into the gas cooling chamber 3 changes its direction approximately 90 degrees as shown by the solid line arrow in FIG. In the gas cooling chamber 3, the gas flows in a substantially horizontal direction (Y direction) and is discharged from the exhaust port 7 in a substantially horizontal direction.

  In the third embodiment, similarly to the first embodiment, in the first and second condensing chambers 2A and 2B and the gas cooling chamber 3, the mixed gas is generated by the cooling water mist sprayed from the spray nozzle 12. To be cooled.

  Also in the third embodiment, as in the first embodiment, the retention prevention effect in the condensing chamber 2 (first and second condensing chambers 2A and 2B) by providing the communication ports 6A and 6B is obtained, and the horizontal By providing the gas cooling chamber 3 extending in the direction, the pressure loss reducing effect and the overall height suppressing effect of the condenser body can be obtained.

  Although the embodiments of the present invention have been described above, the embodiments are illustrative, and the scope of the present invention is not limited to the above-described embodiments, and does not depart from the spirit of the present invention. Various changes are possible.

2, 2A, 2B Condensing chamber 3 Gas cooling chamber 6, 6A, 6B Communication port 7 Exhaust port 10 Tubular body (cooling water supply pipe)
12 Spray nozzle

Claims (7)

A condensation chamber having an inlet through which a mixed gas of steam and non-condensable gas discharged from the steam turbine is introduced downward;
A first spray nozzle for spraying cooling water into the condensing chamber;
A gas cooling chamber connected to a lower portion of the condensing chamber and extending in a horizontal first direction;
Provided in a wall that partitions the condensation chamber and the gas cooling chamber, and a communication port for communicating the condensation chamber and the gas cooling chamber;
A second spray nozzle for spraying cooling water into the gas cooling chamber;
An exhaust port provided at a side of the gas cooling chamber at an end of the gas cooling chamber in the first direction;
With
The direct contact condenser, wherein the exhaust port is sucked, and the mixed gas flowing into the gas cooling chamber from the condensation chamber through the communication port flows to the exhaust port.   The communication port is provided in a central portion with respect to the first direction of the wall body that partitions the condensation chamber and the gas cooling chamber, and the exhaust ports are provided at both ends of the gas cooling chamber in the first direction. The direct contact condenser of Claim 1 provided in the side part of the said gas cooling chamber.   The communication port is provided in a wall body that vertically separates the condensing chamber and the gas cooling chamber so that the condensing chamber and the gas cooling chamber communicate with each other in the vertical direction. The direct contact condenser according to claim 2, wherein the non-condensable gas flowing downward into the cooling chamber changes its direction in the horizontal direction and flows toward the exhaust port.   When the horizontal direction orthogonal to the first direction is the second direction, the width of the gas cooling chamber in the second direction is smaller than the width of the condensation chamber in the second direction, and the gas cooling chamber is The direct contact condenser according to claim 3, wherein the direct contact condenser is provided at a central portion of the condensing chamber with respect to the second direction.   At least a part of the first spray nozzle and the second spray nozzle are provided in the same tubular body, the tubular body extends vertically through the bottom wall body, and the bottom of the tubular body is the bottom. 5. The direct according to claim 3, wherein the first spray nozzle is provided in a portion above the wall body, and the second spray nozzle is provided in a portion of the tubular body below the bottom wall body. Contact condenser.   5. The direct contact according to claim 3, wherein the first spray nozzle is provided in a tubular body that extends in a horizontal direction, and the tubular body also functions as a reinforcing member that connects side wall bodies facing each other in the condensation chamber. Formula condenser.   When the horizontal direction orthogonal to the first direction is the second direction, the condensing chamber is divided into two chambers in the second direction by a partition member, and these chambers are divided into a first condensing chamber and a second condensing chamber. In this case, the gas cooling chamber is provided between the first condensing chamber and the second condensing chamber, and the communication port is a first port between the gas cooling chamber and the first condensing chamber. The mixed gas that is provided in the wall and the second wall between the gas cooling chamber and the second condensing chamber, respectively, and flows into the gas cooling chamber from the communication port in the second direction is the first direction. The direct contact condenser according to claim 1 or 2, wherein the flow is directed toward the exhaust port while changing its direction.

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