JPH1019476A - Condenser - Google Patents

Abstract

PROBLEM TO BE SOLVED: To equalize the quantity of inflow of steam to each part of a group of pipes so as to lessen the pressure loss by constituting the steam passage outside a group of pipes so that the sectional area of the passage may decrease as it goes downward of the steam flow. SOLUTION: The residual steam and the uncondensed gas which have not condensed in a lane's section 3a and a close back section 3b join each other at the lower part of a group of pipes, and the flow becomes largest at the lower part of the space part 7. As against this, the sectional area of the passage of the space part 7 grows larger downward, so the flow velocity and the static pressure of each part of top and bottom of the space part 7 become roughly equal. That is, the pressure difference between the steam inflow side and the gas outflow side of the group of pipes 3 are roughly the same, so steam flows equally in each part of the group of pipes 3. Accordingly, there is no such place that much steam concentrates partially and the pressure loss increases, and the pressure of the steam can be kept low as a whole.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a condenser, and more particularly to a condenser in which pressure loss is reduced by improving the arrangement of heat transfer tubes constituting a tube group.

[0002]

2. Description of the Related Art A condenser is widely used as a device for condensing exhaust steam of a steam turbine and recovering the same as condensate. In general, a condenser has a vessel that communicates with a steam outlet of a steam turbine, and has a pipe group including a number of heat transfer tubes through which cooling water flows in the vessel. The steam discharged from the steam turbine comes into contact with a tube group in the condenser and exchanges heat, so that latent heat is deprived and condensed, and collected as condensate.

FIGS. 9 and 10 show a specific configuration of a conventional condenser. The condenser indicated by reference numeral 101 as a whole is
It has a very large container body 102 having a substantially rectangular shape in a plane, has a tube group 103 composed of tens of thousands of heat transfer tubes inside the container body 102, and has a lower portion of the tube group 103 (container body 1).
02 is provided with a condensate sump 104.

On both sides of the tube group 103, tube sheets 110a, 11
0b is vertically provided, and water chambers 111a and 111b are continuously provided on both left and right sides of the tube sheets 110a and 110b.
The water chamber 111a is connected to the water chamber 11 via the heat transfer tubes of the tube group 103.
1b, the cooling water flows from the water chamber 111a through the tube group 103 as shown by the arrow in FIG.
Flows to

[0005] Above the condenser 101, a steam turbine 112 is provided. The steam outlet of the steam turbine 112 communicates with the container body 102 of the condenser 101,
The steam discharged therefrom, as shown by the arrow in FIG.
It flows down in the container body 102 and contacts the pipe group 103 to exchange heat and is stored as condensate in the condensate sump 104 and extracted by a pump (not shown).

FIG. 10 is a view of the condenser 101 of FIG. 9 cut in a direction perpendicular to the longitudinal direction of the heat transfer tube. FIG.
As shown in FIG. 0, the tube group 103 of the condenser 101 has heat transfer tubes arranged so as to form a bell shape as a whole, and a pair of bell-shaped tube groups 103 is arranged symmetrically. . The above bell shape has a substantially vertical side, and the tube group 1
The distance L between the side wall 03 and the side wall of the container body 102 is set substantially constant at the upper and lower portions of the tube group 103.

The tube group 103 includes a lanes section 103.
a, a closed pack section 103b. The lanes section 103a is outside the tube bank 103 and introduces the exhaust flow of the steam turbine 112,
Part of the heat exchange between cooling water and steam. In order to guide the steam flow, the lanes section 103a is provided with a cut portion 103c in which no heat transfer tube is arranged.

[0008] The close pack section 103b is inside the tube group 103, and the heat transfer tubes are regularly arranged. The close pack section 103b exchanges heat between the steam flowing through the lanes section 103a and the cooling water.

A gas cooling section 106 surrounded by an enclosure frame 105 is formed below the tube group 103. Further, inside the tube group 103, a space portion 107 is formed which forms a flow path for residual vapor or non-condensable gas flowing through the lanes section 103a and the close pack section 103b.
Inside the space 107, a partition plate 108 for guiding the residual steam and the like is provided.

At the periphery of the tube group 103, the steam flows obliquely downward at the upper part of the tube group 103 and horizontally at the side parts. In order to prevent interference between the obliquely downward steam flow at the upper part of the tube bank 103 and the horizontal steam flow at the side parts, a deflector 109 is inserted between them.

In the condenser 101 having the above configuration, the steam flowing out of the steam turbine 112 flows down the inside of the container body 102 toward the tube group 103 as shown by the arrow in FIG. The steam that has reached the tube group 103 flows into the tube group 103, and exchanges heat with cooling water (in this case, seawater is often used) flowing through the heat transfer tube through the water chamber 111a. And the latent heat is deprived and condensed, and collected in the condensate sump 104. On the other hand, the cooling water that has absorbed the heat
It is returned to the ocean or the like via b.

In addition, the residual steam that has not been completely condensed in the tube group 103 and the non-condensable gas that is not condensed, such as air, is generated by the tube group 1
After flowing out into the space 107 inside the gas passage 03 and guided to the gas cooling unit 106 along the partition plate 108 disposed in the space 107, the gas is extracted outside by a gas extraction device (not shown). .

FIG. 11 shows an example of another type of tube arrangement different from the condenser tube group shown in FIGS. The condenser generally denoted by reference numeral 113 has a very large container body 102 having a substantially rectangular flat surface, and a large group of large tube groups 103 including a large number of heat transfer tubes therein.
have. A steam turbine (not shown) is provided above the container body 102.

The tube group 103 is provided with a heat transfer tube having a rectangular cross section, and has a space portion 107 formed at the center thereof through which residual steam or non-condensable gas flows. The space 107 is provided with a gas cooling unit 106 surrounded by an enclosure frame 105.

The tube group 103 includes a lanes section 103.
a, a closed pack section 103b.

The lanes section 103a includes the tube group 10
3 to guide the steam into the tube group 103,
Part of the heat exchange between cooling water and steam. Notches 103 for guiding steam are provided in the lanes section 103a.
c is provided.

The closed pack section 103b is located inside the tube group 103, in which heat transfer tubes are regularly arranged, and performs heat exchange between steam passing through the lanes section 103a and cooling water.

Around the tube group 103, the steam flows downward in the upper part of the tube group 103, diagonally downward in the side part of the tube group 103, and upward in the lower part of the tube group 103. . Considering this steam flow, the tube group 103
A deflector 109 is inserted in the lower part of the lower part of FIG. 3 for interference of the steam flow and discharge of the condensed water. In addition, condenser 11
3 is provided with a condensate reservoir 104 at the bottom.

In the condenser 113 having the above-described structure, the steam discharged from the steam turbine flows down in the vessel body 102 toward the pipe group 103 as shown by the arrow in FIG.
It flows into the tube group 103 from all sides.

The steam contacts the lanes section 103a and the close pack section 103b to transfer heat, loses latent heat, condenses, and is collected in the condensate sump 13. The residual steam and the non-condensable gas that have passed through the tube group 103 are guided to a gas cooling unit 106 provided substantially at the center of the tube group 103, and then extracted outside by a gas extraction device (not shown). On the other hand, the cooling water that has absorbed the heat of the steam is returned to the ocean or the like via the water chamber.

[0021]

However, the above-mentioned conventional condenser has room for improvement in terms of pressure loss.
First, the importance of reducing pressure loss in a steam turbine will be described.

Generally, the back pressure of a steam turbine is related to the pressure loss of the condenser. The back pressure of the steam turbine is a pressure obtained by adding a pressure loss in the condenser to a pressure in the condenser tube group where the steam condenses. Therefore, when the pressure loss of steam in the condenser is large, the back pressure of the steam turbine increases,
Turbine output decreases and power generation efficiency deteriorates.

As described above, suppressing the pressure loss of steam in the condenser is one of the important technical problems for improving the power generation efficiency.

The pressure loss of the tube group depends on the skill of the heat transfer tube arrangement. By arranging the heat transfer tubes so that steam flows evenly and without interruption to the tube group, the pressure loss of the tube group can be reduced. If steam cannot flow evenly into the heat transfer tube arrangement in the tube bank, a large amount of steam will be concentrated locally, the steam flow speed there will increase, the flow resistance will increase, and the pressure loss of steam as a whole tube bank Increase.

In the case of the conventional bell-shaped tube group 101 shown in FIG. 10, the steam discharged from the steam turbine gradually flows into the tube group from the upper part of the tube group, and flows in the steam flow path outside the tube group. The steam flow rate in the lower steam flow path is reduced by the amount of steam flowing into the tube group from the upper portion of the tube group. On the other hand, in the conventional bell-shaped condenser 101, the container body 102 and the tube group 1
03 is almost constant at the upper and lower portions of the tube bank, so that the flow velocity of the steam in the steam flow path outside the upper part of the tube group is lower than the flow velocity outside the lower part of the tube group, and the static pressure is accordingly reduced. Is getting higher.

Further, the space which is a steam flow path from the closed pack section of the tube group to the gas cooling section is condensed by the tube group from the upper part of the tube group to the lower part of the tube group. Unretained residual steam and uncondensed gas (collectively referred to as gas) are gradually collected by merging, and the flow rate is highest at the lower part of the tube group and the flow velocity is high. For this reason, the static pressure of the fluid is lower in the lower part of the space.

From the viewpoint of the pressure difference between the steam inflow side and the gas outflow side of the tube bank, the pressure difference between the steam inflow side and the steam outflow side is small at the upper part of the tube group, and the pressure difference is small at the lower part of the tube group. Is big. For this reason, there is a problem that the steam flow rate is larger at the lower part of the tube group than at the upper part of the tube group, and it is difficult for steam to flow evenly through the tube group.

In addition to the cause of the non-uniformity of the steam flow rate due to the cross-sectional area of the steam flow path around the pipe group, in the conventional condenser, the non-uniformity of the steam flow rate due to the non-uniformity of the flow rate of the steam flowing down the vessel body. There were also problems. This will be described below with reference to FIG.

Generally, due to the structure connecting the steam turbine and the condenser, the exhaust steam discharged from the steam turbine has a high steam velocity near the side wall of the condenser body, and has a high steam velocity at the center of the condenser. Tended to be slow.

FIG. 12 shows an example of the flow velocity distribution of steam to the tube group in a cross-sectional direction perpendicular to the longitudinal direction of the heat transfer tubes. As shown in this figure, the steam velocity is high near the side wall of the condenser body. On the other hand, if the height of the condenser is made extremely high, the velocity distribution will gradually become even, and the steam flow velocity distribution will be almost uniform near the inlet of the tube bank. Generally, the height of the condenser cannot be sufficiently increased from the viewpoint of space, cost, and the like.

For this reason, as for the amount of steam flowing into the tube group, more steam flows to the vessel body side, and the amount of steam flowing to the central part of the condenser decreases. In such a condenser, the amount of steam originally flowing into the tube group was originally biased, and as a result, the pressure loss of the condenser was increased.

Therefore, an object of the present invention is to provide a condenser having a small pressure loss by equalizing the amount of steam flowing into each section of the tube bank.

[0033]

According to a first aspect of the present invention, there is provided a condenser according to the first aspect of the present invention, wherein a plurality of steams are discharged from a steam turbine into a vessel body in a direction crossing the steam flow. In the condenser provided with a tube group in which the heat transfer tubes are arranged in parallel, the steam flow path outside the tube group is configured such that the flow path cross-sectional area decreases as going downstream of the steam flow. It is characterized by having.

[0034] In the condenser according to a second aspect of the present invention, in the condenser according to the first aspect, the steam flow path outside the tube group has a distance between the tube group and a side wall of the container body. It is characterized in that it decreases as it goes downstream of the steam flow.

According to a third aspect of the present invention, in the condenser according to the first aspect, the steam flow path outside the tube group has a reduced steam flow path cross-sectional area toward the downstream of the steam flow. And a flow guide for causing the flow guide to be provided.

A condenser according to a fourth aspect of the present invention is provided with a tube group in which a number of heat transfer tubes are arranged in parallel in a direction crossing the steam flow in a vessel body in which the steam discharged from the steam turbine flows. In the condenser, the tube group has a flow path on a gas outflow side, and the flow path is configured such that a flow path cross-sectional area increases toward a downstream of the gas flow. It is a feature.

A condenser according to a fifth aspect of the present invention is provided with a tube group in which a number of heat transfer tubes are arranged in parallel in a direction crossing the steam flow in a vessel body through which steam discharged from the steam turbine flows. In the condenser, the tube group has more heat transfer tubes in a region near the side wall of the container body than other portions of the tube group.

The condenser according to claim 6 of the present application is provided with a tube group in which a number of heat transfer tubes are arranged in parallel in a direction crossing the steam flow in a vessel body in which the steam discharged from the steam turbine flows down. In the condenser, the tube group has a gas cooling unit that cools gas flowing out to a gas outflow side, and a distance between each gas outflow side unit of the tube group and each gas cooling unit unit is substantially uniform. It is characterized by being constituted.

The condenser according to claim 7 of the present application is provided with a tube group in which a number of heat transfer tubes are arranged in parallel in a direction crossing the steam flow in a vessel body in which the steam discharged from the steam turbine flows down. In the condenser, the tube group is provided with a heat transfer tube having a smaller tube diameter and a smaller pitch than other portions of the tube group in a region near a side wall of the container body. Things.

The condenser according to claim 8 of the present application is provided with a pipe group in which a number of heat transfer tubes are arranged in parallel in a direction crossing the steam flow in a vessel body in which the steam discharged from the steam turbine flows down. In the condenser, the tube group is provided with a heat transfer member that increases the heat transfer performance of the heat transfer tube on an inner surface of the heat transfer tube in a region near a side wall of the container body.

A condenser according to a ninth aspect of the present invention is the condenser according to the eighth aspect, wherein the heat transfer body comprises a fin formed spirally on the inner surface of the heat transfer tube. .

In the condenser according to the first aspect of the present invention, the flow path cross-sectional area of the steam flowing toward the tube group is reduced toward the downstream side of the steam. For this reason, the flow velocity and static pressure of the steam entering the tube group can be equalized at each part of the steam inlet side of the tube group, and the steam can be uniformly guided to the tube group, and the pressure loss of the entire tube group can be kept low. Become.

In the condenser according to the second aspect of the present invention, since the distance between the tube group and the side wall of the container body decreases toward the downstream side of the steam, the flow velocity of the steam entering the tube group is reduced. The static pressure can be equalized at each part of the steam inlet side of the tube group, and the steam can be uniformly guided to the tube group, and the pressure loss of the entire tube group can be kept low.

In the condenser according to the third aspect of the present invention, a flow guide is provided such that the flow passage cross-sectional area of the steam flowing toward the tube group becomes smaller toward the downstream side of the steam. For this reason, the flow velocity and static pressure of the steam entering the tube group can be equalized at each part of the steam inlet side of the tube group, and the steam can be uniformly guided to the tube group, and the pressure loss of the entire tube group can be kept low. Become.

In the condenser according to a fourth aspect of the present invention, the cross-sectional area of the flow path on the gas outflow side is increased toward the gas cooling section. For this reason, the flow velocity and the static pressure of the gas exiting from the tube group can be made uniform in each part of the tube group, so that the steam can be uniformly guided to the tube group, and the pressure loss of the entire tube group can be kept low.

In the condenser according to the fifth aspect of the present invention, a number of heat transfer tubes are arranged closer to the container body than the center of the tube group. This makes it possible to condense more steam flowing toward the vessel body side of the tube group.Therefore, by equalizing the condensation of the steam, the amount of steam flowing around the tube group is small, and the entire tube group is condensed. Pressure loss can be kept low.

In the condenser according to the sixth aspect of the present invention, since the distance between each part on the gas outflow side and each part of the gas cooling part is made substantially constant, the flow velocity and the static pressure of steam exiting from the tube group are reduced. The steam can be evenly distributed in each section of the tube group, and the steam can be evenly guided to the tube group.
It is possible to keep the pressure loss of the entire tube group low.

In the condenser according to the present invention, the pitch and diameter of some of the heat transfer tubes are changed so that the heat transfer performance is better on the container body side than on the center side of the tube group. For this reason, more steam flowing toward the vessel body side of the tube group can be condensed more, so that the amount of steam flowing around the tube group is small, and the pressure loss of the entire tube group can be kept low. .

In the condenser according to the present invention, a heat transfer body is provided on the inner surface of some of the heat transfer tubes so that the heat transfer performance is better on the container body side than on the center side of the tube group. For this reason, more steam flowing toward the vessel body side of the tube group can be condensed more, so that the amount of steam flowing around the tube group is small, and the pressure loss of the entire tube group can be kept low. .

In the condenser according to a ninth aspect of the present invention, the heat transfer body is a spiral fin formed on the inner surface of the heat transfer tube.
Therefore, more steam flowing toward the vessel body side of the tube group can be condensed more, pressure loss of the entire tube group can be kept low, and the heat transfer performance of the entire inside and outside of the tube can be effectively improved. The living organisms and dust in the cooling water hardly adhere to the pipe, and the heat transfer pipe can be easily processed.

[0051]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Next, an embodiment of a condenser according to the present invention will be described below with reference to the accompanying drawings.

FIG. 1 shows an embodiment (hereinafter referred to as a first embodiment) of a condenser according to claims 1, 2, and 4 of the present application.

The condenser 1 has a very large container body 2 having a substantially rectangular shape in a plane. A steam turbine (not shown) is provided on the upper part of the container body 2. A large tube group 3 including heat transfer tubes is provided. A condensate reservoir 4 is provided below the tube group 3, that is, at the bottom of the container body 2.

The tube group 3 of this embodiment is composed of a pair of trapezoidal and semicircular shapes, and is arranged in parallel with the longitudinal direction of the container body 2 (perpendicular to the plane of FIG. 1). Have been.

Each of the pair of tube groups 3 has a shape which symmetrically expands downward as a whole. The distance L between the tube group 3 and the side wall of the container body 2 is configured to decrease from the upper portion to the lower portion of the tube group 3.
The distance L is preferably set so as to gradually decrease downward so that the flow velocity of the steam flowing into the tube group 3 becomes constant at each part of the tube group 3 as described later.

A gas cooling section 6 surrounded by an enclosure frame 5 is provided below the tube group 3. In the center of the tube group 3, a space portion 7 that serves as a flow path of the residual steam and the non-condensable gas toward the gas cooling portion 6 is provided. A substantially vertical partition plate 8 is provided at the center of the space 7.

The cross-sectional area of the flow passage in the space 7 is configured to increase downward. Preferably, the flow path cross-sectional area of the space 7 is such that residual steam and non-condensable gas flowing out of the space 7 through the tube group 3
It is set so as to increase in accordance with the increase in the flow rate at the lower part where the merging occurs.

The tube group 3 includes a lanes section 3a and a closed pack section 3b. The lanes section 3a is located outside the tube group 3 and introduces the exhaust flow of the steam turbine and performs a part of the heat exchange between the cooling water and the steam. Lanes section 3 to guide the steam flow
A is provided with a cut portion 3c in which no heat transfer tube is arranged.

The closed pack section 3b includes the tube group 3
Inside, the heat transfer tubes are regularly arranged.
The close pack section 3b performs heat exchange between cooling water and steam.

The arrangement of the tubes in the tube group 3 is such that steam is guided obliquely downward in the upper part of the tube group 3 and horizontally in the side parts. A baffle plate 9 is inserted between the obliquely downward steam flow at the upper part of the tube bank 3 and the horizontal steam flow at the side to prevent interference and condensate discharge.

Note that both ends of the tube group 3 are inserted through the tube sheet 10. Further, the gas cooling unit 6 is connected to a gas extraction device (not shown).

Next, the operation and effects of the condenser 1 having the above configuration will be described below. In the condenser 1, the steam flowing from the steam turbine (not shown) to the container body 2 flows toward the pipe group 3 as shown by the arrow shown in FIG. 1, and the lanes section 3a and the closed pack section 3b in this order. Be guided. Here, the steam transfers heat to and from the cooling water passing through the heat transfer tube through a water chamber (not shown), loses its latent heat, condenses, and is collected in the condensate sump 4. On the other hand, the cooling water that has absorbed heat is supplied to a water chamber (not shown) on the opposite side.
And returned to the ocean.

As mentioned above, most of the steam is
While passing through the cooling water, the latent water is deprived of latent heat and condensed. The residual steam and the non-condensable gas flow into the space 7 at the center of the tube group 3, and the partition plate 8 disposed in the space 7 The gas is guided to the gas cooling unit 6 along the path, and is extracted outside the condenser 1 by a gas extracting device (not shown).

According to the condenser 1, the pressure loss in the condenser 1 can be minimized.

The steam discharged from the steam turbine flows downward inside the container body 2, reaches the tube group 3, and gradually flows into the tube group 3 from above the tube group 3. In the flow path outside the tube group 3, that is, the flow path between the tube group 3 and the side wall of the container body 2 and the flow path between the tube group 3, only the amount of the steam flowing into the tube group 3 at the upper portion is used. , The steam flow decreases toward the bottom.

On the other hand, in the condenser 1 of the present embodiment, the tube group 3 is expanded downward as a whole, and the steam outside the tube group 3 corresponds to the decrease in the steam flow rate. The cross-sectional area of the flow path is gradually reduced. Thereby, the flow velocity of the steam flowing in each of the upper and lower portions of the tube group 3 becomes substantially uniform, and the static pressure of the inflow steam in each portion of the tube group 3 becomes substantially uniform.

Further, in the space portion 7 which flows out of the close pack section 3b and becomes the flow path toward the gas cooling section 6, the flow path cross-sectional area increases from the upper part of the tube group to the lower part of the tube group.

The residual steam and non-condensable gas not condensed in the lanes section 3a and the closed pack section 3b join at the lower part of the tube group and have the highest flow rate at the lower part of the space 7. On the other hand, since the flow path cross-sectional area of the space 7 increases downward, the flow velocity and the static pressure of each of the upper and lower portions of the space 7 become substantially uniform.

That is, according to the condenser 1 of the present embodiment, the pressure difference between the steam inflow side and the gas outflow side of the tube group 3 is substantially the same in each of the upper and lower portions of the tube group 3. In each part of 3, the steam flows evenly. In this way, the uniform flow of steam in each section of the tube bank means that there is no place where a large amount of steam is concentrated and the pressure loss increases,
The performance of the tube bank can be maximized. That is, the pressure loss of steam can be kept low as a whole.

As is clear from the above description, in order to minimize the pressure loss of the entire tube group, the pressure difference between the steam inflow side and the gas outflow side of each section of the tube group should be equalized. In the first embodiment, the static pressure at each portion of the tube group on the steam inflow side and the static pressure at each portion of the tube group on the gas outflow side are made uniform. The present invention also includes a condenser in which the pressure difference between the steam inflow side and the gas outflow side is made uniform in each section of the tube group even if there is some uneven distribution of the static pressure of the fluid on the gas outflow side.

FIG. 2 shows an embodiment (hereinafter referred to as a second embodiment) of the condenser according to claims 1 and 3 of the present application. This will be described below. For easy understanding, the same components of the condenser will be described with the same reference numerals.

The condenser 11 of the second embodiment is shown in FIGS.
10, a steam turbine is provided at the upper part of the container body 2, and a pair of bell-shaped cross-section pipes 3 as shown in FIG. I have.

Outside these tube groups 3, there are provided flow guides 12 for dividing the flow path of the steam flowing into the tube groups 3. The flow guide 12 includes the flow guide 12 and the tube group 3.
Is set such that the distance L from the top to the bottom of the tube group 3 decreases from the upper portion of the tube group 3.

A gas cooling section 6 surrounded by an enclosure frame 5 is provided below the tube group 5. In the center of the tube group 3, a space 7 serving as a flow path for the residual steam flowing to the gas cooling unit 6 and the non-condensable gas is arranged. Inside each space 7,
Two partition plates 13 are provided.

The partition plate 13 is installed so that the distance L ′ between the pipe group 3 and the gas outflow side becomes larger toward the lower part of the space 7.

A condensate reservoir 4 is provided at the bottom of the container body 2. The tube group 3 includes a lanes section 3a and a closed pack section 3b, similarly to the condenser 1 of FIG. 1, and the lanes section 3a is provided with a cut portion 3c. Further, similarly to the condenser 1 of FIG. 1, a deflector 9 is inserted above the tube group 3.

Next, the operation and effects of the condenser 11 having the above configuration will be described below. In the condenser 11, the steam flowing out of the steam turbine flows downward in the vessel body 2 and reaches the pipe group 3. The steam around the tube group 3 is guided by the flow guide 12, and flows in the lanes section 3a and the close pack section 3b of the tube group 3 in this order. By the heat transfer tubes of the lanes section 3a and the closed pack section 3b, the steam exchanges heat with the cooling water passing through the heat transfer tube, loses latent heat, condenses, and is collected in the condensate sump 4. . On the other hand, the cooling water that has absorbed the heat flows from one water chamber to the other water chamber, and is returned to the ocean or the like.

The residual steam and the non-condensable gas flowing out of the close pack section 3b flow into the gas cooling unit 6 through the space 7 in which the partition plate 13 is provided, and are extracted by a gas extracting device (not shown).

As described below, the condenser 11 can also reduce the pressure loss of the entire condenser similarly to the condenser 1 of FIG. 1 as described below.

In the condenser 11 of the second embodiment, the water is guided by the flow guide 12 and gradually flows into the inside of the tube group 3 from above the tube group 3. In the lower part of the steam flow path outside the tube group 3,
The steam flow rate is reduced by the amount of steam flowing into the inside of the tube group 3 at the upper part of the tube group 3.

On the other hand, the flow guide 1 of the condenser 11
In No. 2, since the width L of the steam flow path outside the tube group 3 is reduced in response to the decrease in the steam flow rate, the flow velocity of the steam flowing into each part of the tube group 3 becomes substantially uniform. For this reason, the static pressure of the steam flowing into each section of the tube group is kept substantially uniform.

The space 7 on the gas outflow side of the tube group 3
Also, the partition plate 13 is formed so that the flow path cross-sectional area of the lower part of the tube group 3 is larger than that of the upper part of the tube group 3. For this reason, the flow velocity of the fluid flowing in the space 7 is also substantially uniform,
The static pressure on the gas outflow side of the tube group 3 is also kept substantially uniform.

As described above, the pressure difference between the steam inflow side and the gas outflow side of the tube group is substantially the same in both the upper part and the lower part of the tube group 3 so that the steam flows evenly through the tube group 3. It has become. Accordingly, there is no portion where a large amount of steam enters to increase the pressure loss, and the pressure loss of the steam in the entire tube group can be kept low.

Even if there is a slight variation in the flow velocity of the steam outside or inside the tube group 3, the present invention is included as long as the pressure difference between the steam inflow side and the gas outflow side is uniform.

FIG. 3 shows an embodiment (hereinafter referred to as a third embodiment) of the condenser according to claims 1 and 2 of the present application. This will be described below.

The condenser 15 of this embodiment is an improvement of the conventional condenser shown in FIG. 11, and has one tube group 3 having a trapezoidal cross section inside the container body 2. doing.

The upper part of the tube group 3 has a trapezoidal short side, and has a shape in which the width of the tube group becomes wider toward the lower part of the tube group. A gas cooling unit 6 surrounded by an enclosure frame 5 is provided at the center of the tube group 3. A condensate reservoir 4 is provided at the bottom of the container body 2.

The tube group 3 includes a lanes section 3a and a closed pack section 3b, and a baffle plate 9 for interfering with steam flow and draining condensed water is inserted below the tube group 3.

Next, the operation and effect of the condenser 15 having the above configuration will be described below. In the condenser 15 of the present embodiment, the steam flowing out of the steam turbine flows toward the tube group 3 as shown by an arrow in FIG. The steam that has reached the tube group 3 flows into the tube group 3 in the order of the lanes section 3a and the close pack section 3b. In the lanes section 3a and the closed pack section 3b,
The steam exchanges heat with the cooling water passing through the heat transfer tube through the water chamber, loses latent heat, condenses, and is collected in the condensate sump 4. On the other hand, the cooling water that has absorbed the heat is returned to the ocean or the like through the water chamber on the opposite side.

The residual steam and non-condensable gas exiting from the closed pack section 3b flow into a gas cooling section 6 surrounded by an enclosure 5, and are extracted by a gas extraction device (not shown).

According to the condenser 15, similar to the condensers of the first and second embodiments, as described below,
Overall, the pressure loss of the condenser can be minimized.

In the condenser 15, the steam gradually flows from the upper part of the tube group 3 to the inside of the tube group 3, and in the steam flow path outside the tube group 3, the steam flow rate at the lower part is lower than that at the upper part. On the other hand, since the tube group 3 of the present embodiment has a trapezoidal shape whose cross section expands downward, the distance L between the container body 2 and the tube group 3 is reduced by the tube group. It becomes smaller as it goes from the upper part 3 to the lower part of the tube group 3, and the flow velocity of the steam flowing into the tube group 3 from the upper and lower parts of the tube group 3 becomes almost uniform. As a result, the static pressure of the steam flowing into each section of the tube bank is kept substantially uniform.

As described above, since the steam is substantially uniform in each portion of the tube group 3 on the steam inflow side, the steam flows evenly into the tube group 3, and a large amount of steam enters and the pressure increases. There is no place to increase the loss, and the pressure loss of steam in the entire tube group 3 can be kept low.

FIG. 4 shows claims 1, 2, 4, and 5 of the present invention.
1 shows an embodiment of a condenser according to the present invention (hereinafter, referred to as a fourth embodiment). This will be described below.

The condenser 16 of this embodiment has a steam turbine on the upper part of the container body 2, and inside the container body 2, two bell-shaped tube groups 3 each having an asymmetrical cross section are symmetrically arranged. It is arranged.

In the tube group 3, the number of heat transfer tubes arranged on the container body 2 side (the side closer to the side wall of the container body 2) is larger than that on the center side of the tube group (the center portion of the container body 2). Are arranged so as to increase. The container body 2 side of the tube group 3 is
The distance L between the container body 2 and the tube group 5 is configured to decrease from the upper part to the lower part. The tube group 3 is composed of a lanes section 3a and a closed pack section 3b, like the tube group 3 of the condenser 1 shown in FIG. 1, and a baffle plate 9 is inserted into the upper part of the tube group 3. I have.

A space 7 is formed at the center of the tube group 3, and a partition plate 8 is provided inside the space 7. The flow path area of the space 7 increases from the upper part to the lower part.

Below the tube group 3, a gas cooling unit 6 surrounded by an enclosure frame 5 is provided. A condensate reservoir 4 is formed at the bottom of the container body 2.

Next, the operation and effect of the condenser 16 having the above configuration will be described below. Condenser 1 of the present embodiment
At 6, the steam flowing out of the steam turbine flows down toward the tube group 3 as shown by the arrow in FIG. The steam that has reached the tube group 3 flows into the tube group 3 through the lanes section 3a and the closed pack section 3b of the tube group 3. In the lanes section 3a and the closed pack section 3b, the steam exchanges heat with the cooling water passing through the heat transfer tube through the water chamber, deprives of latent heat, condenses, and is collected in the condensate sump 4. . On the other hand, the cooling water that has absorbed the heat is returned to the ocean or the like through the water chamber on the opposite side. The residual steam and the non-condensable gas flowing out of the close pack section 3b flow into the gas cooling unit 6 and are extracted by a gas extracting device (not shown).

The condenser 16 is the condenser 1 described above.
(First embodiment), 11 (second embodiment), 15 (third embodiment)
Similarly to the embodiment, the pressure difference between the steam inflow side and the gas outflow side becomes substantially uniform in each part of the tube group 3.

That is, in the steam flow path outside the tube group 3, the steam flow rate decreases at the lower part of the steam flow path by the amount of steam flowing into the tube group 3 at the upper part of the tube group 3. The distance L from the tube group 3 becomes smaller toward the lower part of the tube group 3 corresponding to the steam flow rate, and the cross-sectional area of the steam flow path becomes smaller. For this reason, the flow velocity of the steam entering each part of the tube group 3 is substantially uniform, and the static pressure of the steam at each part of the tube group 3 on the steam inflow side is maintained substantially uniform.

The space 7 on the gas outflow side of the tube group 3 is
The lower the lower the residual steam and the non-condensable gas merge, the higher the flow rate. In response to this, the flow path cross-sectional area of the space 7 also increases as it goes down. For this reason, the flow velocity and the static pressure of the steam and the like are kept substantially uniform in each part on the gas outflow side of the tube group 3.

As a result, the pressure difference between the steam inflow side and the gas outflow side in each portion of the tube group 3 becomes substantially uniform, and the pressure loss of the entire condenser can be minimized.

As described below, according to the condenser 16 of this embodiment, the steam is uniformly condensed in accordance with the uneven flow velocity distribution of the steam in the container body 2, and the pressure loss is reduced. Can be reduced.

As already described with reference to FIG. 12, generally, the steam flowing out of the steam turbine has a high steam velocity near the side wall of the vessel body of the condenser and a low velocity at the center of the condenser. There are many. In these condensers, a large amount of steam flows on the vessel body side of the tube group, and a small amount of steam flows on the center side of the condenser in the tube group.

The condenser 16 of this embodiment has a large number of heat transfer tubes on the side of the tube group 3 close to the container body 2, and relatively close to the center part of the container body 2. It has a small number of heat transfer tubes. The large number of heat transfer tubes arranged on the container body 2 side can condense more steam flowing more in the tube group 3 on the container body 2 side. Thus, the condenser 16 of the present embodiment makes the amount of steam flowing through the tube group 3 uniform, reduces irregular flow (wraparound) around the tube group 3 due to non-condensed steam, and reduces the tube group. The overall pressure loss can be kept low.

Next, referring to FIG.
One embodiment of the condenser according to the fifth and sixth embodiments (hereinafter, referred to as a fifth embodiment) will be described.

FIG. 5 shows a fifth embodiment of the condenser according to the present invention. The condenser 17 of FIG.
A steam turbine (not shown) is provided on the upper part of the container body 2, and two are disposed symmetrically inside the container body 2,
A tube group 3 having a heat transfer tube is provided only on the container body 2 side.

In the tube group 3, the side surface on the container body 2 side is inclined as a whole, and the distance L between the container body 2 and the tube group 3 is L.
Becomes smaller from the upper part to the lower part. The steam inflow side to the tube group 3 is provided only on the container body 2 side, and the center side of the tube group 3 is covered by an enclosing frame 5 surrounding the entire tube group 3.

The tube group 3 is constituted by a lanes section 3a and a closed pack section 3b. The lanes section 3a has a notch 3 for introducing steam.
c is provided. A gas cooling unit 6 is provided inside the tube group 3, that is, at the center of the tube group 3. The distance between the gas cooling unit 6 and the gas outflow side surface of the close pack section 3b is configured to be substantially equal at any position of the gas cooling unit 6.

A gas suction section 18 is provided between the inside of the gas cooling section 6 and the frame 5. The gas suction portion 18 is a portion into which the fluid flowing out of the gas cooling portion 6 flows. After flowing in the longitudinal direction of the heat transfer tube of the condenser 17 from the gas suction portion 18, the gas suction portion 18 is externally provided by a gas extraction device (not shown). Is extracted. A condensate reservoir 4 is provided at the bottom of the container body 2.

Next, the operation and effect of the condenser 17 having the above configuration will be described below. In the condenser 17, the steam flowing out of the steam turbine flows down in the container body 2 as shown by the arrow in FIG. The steam arriving around the tube group 3 is divided into the lanes section 3a and the closed pack section 3
b and flows into the inside of the tube group 3. The steam exchanges heat with the cooling water passing through the heat transfer tube through the water chamber in the lanes section 3a and the closed pack section 3b, loses latent heat, condenses, and is collected in the condensate sump 4. On the other hand, the cooling water that has absorbed the heat is returned to the ocean or the like through the water chamber on the opposite side.

The residual steam and the non-condensable gas flowing out of the close pack section 3b are directed toward the gas cooling section 6 and are extracted outside the vessel via a gas suction section 18 by a gas extracting device (not shown).

According to the condenser 17, the condensers 1 (first embodiment), 11 (second embodiment), 15
As in (Third Embodiment) and 16 (Fourth Embodiment), the pressure difference between the steam inflow side and the gas outflow side in each part of the tube group 3 becomes substantially uniform.

That is, the steam gradually flows from the upper part of the tube group 3 into the tube group, and the steam flow rate in the steam flow path outside the lower part of the tube group 3 is smaller than that in the upper part of the tube group 3. Become.
On the other hand, in the tube group 3 of the condenser 17, the distance L between the container body 2 and the tube group 3 decreases as the distance from the upper part of the tube group 3 to the lower part of the tube group 3 decreases. Thereby, the flow velocity of the steam flowing into the tube group 3 at each part of the tube group 3 becomes substantially uniform,
The static pressure of the inflow steam is kept substantially uniform in each part of the tube group 3.

Further, since the distance between the closed pack section 3b (gas outlet side of the tube group 3) and the gas cooling section 6 is almost equal at any position of the closed pack section 3b, the gas outlet side of the tube group 3 is provided. In each part, the flow velocity and static pressure of residual steam and the like become uniform.

Thus, in each of the upper and lower portions of the tube group 3,
The pressure difference between the steam inflow side and the gas outflow side becomes equal,
Vapor flows evenly. Since the steam flows evenly in each section of the tube group 3, there is no place where a large amount of steam flows in and the pressure loss is increased, and the pressure loss of the steam in the entire tube group can be kept low.

The condenser 17 of the present embodiment also responds to uneven flow velocity distribution of the steam in the container body 2 and performs more heat exchange with the steam near the side wall of the container body 2. In addition, the pressure loss due to the flow of uncondensed vapor can be reduced.

That is, when the flow velocity of the steam is high near the side wall of the container body 2, more steam flows toward the container body 2 side of the tube group 3. On the other hand, the tube group 3 of this embodiment is Since the tube group 3 provided with more heat transfer tubes on the two sides is installed symmetrically, more steam flowing to the container body 2 side of the tube group 3 can be condensed more, and the tube of uncondensed steam can be condensed. The wrap around around the group is small, and the pressure loss of the entire tube group can be kept low.

Next, an embodiment of a condenser according to claim 7 of the present invention (hereinafter referred to as a sixth embodiment) will be described with reference to FIG.

FIG. 6 shows a sixth embodiment of the condenser according to the present invention. The condenser 19 in FIG. 6 has a container body 2, a steam turbine is provided on the upper part of the container body 2, and a pair of cross-section bell-shaped pipe groups 3 is provided inside the container body 2.

The tube group 3 includes a lanes section 3a and a closed park section 3b, and the lanes section 3a is provided with a cutout 3c.

A heat transfer pipe having a reduced pipe diameter and pitch is arranged at a part (shown by oblique lines in FIG. 6) of the pipe group 3 of the condenser 19 on the container body 2 side. FIG. 7 shows in detail the periphery of the heat transfer tube portion in which the tube diameter and the pitch are reduced. As shown in FIG. 7, more heat transfer tubes having a smaller diameter are arranged on the container body 2 side of the lanes section 3 a in a staggered tube arrangement of regular triangles.

In the condenser 19 having the above configuration,
The steam flowing out of the steam turbine is transferred to the vessel body 2 of the tube group 3.
First, the lanes section 3a of the heat transfer tube arrangement portion having a small pipe diameter and a small pitch, then the normal lanes section 3a, and then the closed pack section 3b
And heat exchange with the heat transfer tube.

The steam exchanges heat with the heat transfer tubes of the tube group 3, condenses, and is collected in the condensate sump 4.

According to the condenser 19 of the present embodiment, the steam is uniformly condensed with respect to the steam flow having a non-uniform flow rate in the container body 2 to reduce the pressure loss due to the non-condensed steam flowing around. Can be.

That is, as described with reference to FIG. 12, the flow velocity of the steam discharged from the steam turbine tends to be higher near the side wall of the vessel body than at the center of the condenser. In order to condense these vapors, a larger heat transfer performance is required for the tube group 3 on the container body 2 side, but the tube group 3 of the condenser 19 of the present embodiment is located on the container body 2 side. Pipe diameter,
A heat transfer tube with a small pitch is provided, and the heat transfer performance on the container body 2 side is high. Thereby, more steam flowing toward the vessel body 2 side of the tube group 3 can be condensed more, less wraparound around the tube group due to uncondensed steam can be achieved, and the pressure loss of the entire tube group can be reduced.

Finally, one embodiment of the condenser according to claims 8 and 9 of the present application (hereinafter referred to as a seventh embodiment)
This will be described below with reference to FIGS.

A condenser 20 according to the seventh embodiment has a container body 2 and a tube group 3 as shown in FIG. The difference of the condenser 20 of this embodiment from the condenser 19 of the sixth embodiment is that a heat transfer tube having high heat transfer performance shown in FIG. 8 is provided in the hatched portion of the tube group 3 in FIG. That is.

FIG. 8 is a partially cutaway sectional view of the heat transfer tube having high heat transfer performance. As shown in FIG. 8, this heat transfer tube having high heat transfer performance has a spiral fin 21 on the inner surface.

In the condenser 20 having the above configuration,
The steam flowing out of the steam turbine is transferred to the vessel body 2 of the tube group 3.
It flows more to the side, where it comes into contact with a heat transfer tube with helical fins 21 on its inner surface, followed by heat exchange with a normal heat transfer tube without fins. The steam condensed by the heat exchange is collected in the condenser 4.

According to the condenser 20 of this embodiment, the steam can be uniformly condensed. That is, generally, as shown in FIG. 12, the flow velocity of the steam discharged from the steam turbine is higher near the side wall of the vessel body than in the center of the condenser, and the same tendency is observed in the upper part of the tube group. . In order to uniformly condense these vapors, higher heat transfer performance is required for the tube group 3 on the container body 2 side. On the other hand, the tube group 3 of the condenser 20 of the present embodiment is provided with the heat transfer tube having the high heat transfer performance having the spiral fin 21 on the container body 2 side. The side has higher heat transfer performance than the central part. Thereby, the steam having an uneven flow rate distribution around the pipe group 3 can be uniformly condensed, and the uncondensed steam flowing around the pipe group can be reduced, and the pressure loss of the entire pipe group can be kept low.

In this embodiment, since the fins 21 are provided on the inner surface side of the heat transfer tube, the heat transfer performance inside the tube with a low heat transfer coefficient can be improved, and the heat transfer performance of the entire heat transfer tube can be improved. Can be raised effectively. In addition, since the fins 21 are provided in a spiral shape, the velocity of the cooling water is also provided in the circumferential direction of the heat transfer tube, so that it is difficult to attach organisms and dust in the cooling water to the heat transfer tube. be able to.

In the above example, the heat transfer tube having high heat transfer performance is a heat transfer tube having the spiral fins 21 provided on the inner surface. However, the heat transfer tube is not limited to the spiral fin, and may have any shape for improving the heat transfer performance. , For example, a heat transfer tube provided with an inward projection of any shape. Among these heat transfer bodies, the spiral fins 21 can be easily processed by cutting or the like, and can be said to be an example of a preferable heat transfer body.

[0135]

As is apparent from the above description, according to the condenser of the first aspect of the present invention, as the steam flow path outside the tube group moves toward the downstream side of the steam flow, the steam flow is reduced. Since the cross-sectional area of the flow passage is reduced, the flow velocity and the static pressure of the steam flowing into the tube group are equalized in each portion of the tube group on the steam inflow side. Thus, the steam can be uniformly guided to the tube group, and the pressure loss of the entire tube group can be kept low.

Further, according to the condenser of the second aspect of the present invention,
Since the distance between the tube group and the side wall of the container body decreases as the position goes downstream of the steam flow, the flow velocity and the static pressure of the steam flowing into the tube group become uniform at each portion of the tube group on the steam inflow side. Thus, the steam can be uniformly guided to the tube group, and the pressure loss of the entire tube group can be kept low.

According to the condenser of the third aspect of the present invention,
Since the flow guide that reduces the cross-sectional area of the steam flow path as it goes downstream of the steam flow is disposed, the flow velocity and the static pressure of the steam flowing into the tube group are equalized at each portion of the tube group on the steam inflow side. This allows the steam to be evenly distributed to the tube bank,
The pressure loss of the entire tube group can be kept low.

Further, according to the condenser of the fourth aspect of the present invention,
Since the cross-sectional area of the flow path of the residual vapor or non-condensable gas provided on the gas outflow side increases toward the downstream of the gas flow, the flow velocity and static pressure of the gas flowing out of the tube group It becomes uniform in each part on the gas outflow side. Thus, the steam can be uniformly guided to the tube group, and the pressure loss of the entire tube group can be kept low.

According to the condenser of claim 5 of the present invention,
Since more heat transfer tubes are arranged on the side closer to the side wall of the container body than the center side of the tube group, more steam flowing to the container body side of the tube group can be condensed more, so steam Wrap around the tube group is small, and the pressure loss of the entire tube group can be kept low.

According to the condenser of claim 6 of the present invention,
Since the distance between the gas cooling unit and each part on the gas outflow side of the tube group is made substantially uniform, the flow velocity and the static pressure of the gas flowing out of the tube group can be made uniform in each part of the tube group. Thus, the steam can be uniformly guided to the tube group, and the pressure loss of the entire tube group can be kept low.

According to the condenser of the seventh aspect of the present invention,
Since the pitch and pipe diameter of some of the heat transfer tubes on the container body side of the tube group are smaller than those on the center side of the tube group, the heat transfer performance on the container body side of the tube group is higher than that on the center side. It is possible to condense more steam flowing toward the vessel body side of the tube group. This makes it possible to reduce the amount of steam flowing around the tube group, and to keep the pressure loss of the entire tube group low.

According to the condenser of claim 8 of the present invention,
Since a heat transfer body that improves heat transfer performance is provided on the inner surface of a part of the heat transfer tube on the vessel body side of the tube group, more steam flowing to the vessel body side of the tube group can be more condensed, and the tube group And the flow rate of steam to the air can be made uniform. This makes it possible to reduce the amount of steam flowing around the tube group, and to keep the pressure loss of the entire tube group low.

According to the condenser of the ninth aspect of the present invention,
Since the heat transfer body is a spiral fin formed on the inner surface of the heat transfer tube, more steam flowing toward the vessel body side of the tube group can be condensed more, thereby keeping the pressure loss of the entire tube group low. As a result, the heat transfer performance of the entire inside and outside of the tube can be effectively improved, and the adhesion of organisms and dust in the cooling water to the heat transfer tube can be reduced. Further, the heat transfer tube having the spiral fin also has an advantage that it can be easily processed.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view of a condenser according to a first embodiment of the present invention having a tube group in which heat transfer tubes are arranged in a combination of a trapezoid and a semicircle, in a direction perpendicular to the longitudinal direction of the heat transfer tubes. FIG.

FIG. 2 is a cross-sectional view of a condenser according to a second embodiment of the present invention provided with a flow guide for gradually reducing a cross-sectional area of a steam flow path, which is cut in a direction perpendicular to a longitudinal direction of a heat transfer tube. FIG.

FIG. 3 shows a condenser according to a third embodiment of the present invention having a tube group in which heat transfer tubes are arranged in a trapezoidal shape expanding downward, cut in a direction perpendicular to the longitudinal direction of the heat transfer tubes. FIG.

FIG. 4 shows a condenser according to a fourth embodiment of the present invention in which bell-shaped tube groups having asymmetrical cross sections are disposed symmetrically, and is cut in a direction perpendicular to the longitudinal direction of the heat transfer tubes. Sectional view.

FIG. 5 is a cross-sectional view of a condenser according to a fifth embodiment of the present invention including a tube group having heat transfer tubes only on the container body side, cut in a direction perpendicular to the longitudinal direction of the heat transfer tubes.

FIG. 6 shows a sixth embodiment or a seventh embodiment of the present invention in which a heat transfer tube having a reduced pipe diameter and a pitch or a heat transfer tube having a spiral fin provided on an inner surface is disposed on a part of a container body side. Sectional drawing which cut | disconnected and showed such a condenser in the direction perpendicular | vertical to the longitudinal direction of a heat exchanger tube.

FIG. 7 is an enlarged view showing an arrangement of heat transfer tubes in which the tube diameter and the pitch are reduced.

FIG. 8 is a diagram showing a partially cut-away heat transfer tube having a spiral fin on an inner surface.

FIG. 9 is a sectional view showing a conventional condenser cut along a longitudinal direction of a heat transfer tube.

FIG. 10 is a cross-sectional view showing a conventional condenser cut along a direction perpendicular to a longitudinal direction of a heat transfer tube.

FIG. 11 is a cross-sectional view showing another conventional condenser having a different heat transfer tube arrangement cut along a direction perpendicular to the longitudinal direction of the heat transfer tubes.

FIG. 12 is a graph showing an example of a flow velocity distribution of steam flowing to a tube group in a cross-sectional direction perpendicular to a longitudinal direction of a heat transfer tube.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Condenser 2 Container body 3 Tube group 3a Lanes section 3b Close pack section 4 Condenser 5 Frame 6 Gas cooling unit 7 Space 8 Partition plate 9 Deflector plate 10 Tube plate 11 Condenser 12 Flow guide 13 Partition plate 15 Condenser 16 Condenser 17 Condenser 18 Gas suction unit 19 Condenser 20 Condenser 21 Spiral fin

Claims (9)

[Claims] 1. A condenser comprising: a tube group in which a number of heat transfer tubes are arranged in parallel in a direction crossing a steam flow in a vessel body in which steam discharged from a steam turbine flows down; The condenser according to claim 1, wherein the outer steam flow path is configured such that a cross-sectional area of the flow path decreases toward the downstream of the steam flow. 2. The steam flow path outside the tube bundle, wherein the distance between the tube bundle and the side wall of the vessel body decreases as the distance downstream of the steam flow decreases. Condenser described. 3. The method according to claim 1, wherein the steam flow path outside the tube group is provided with a flow guide for reducing a cross-sectional area of the steam flow path as it goes downstream of the steam flow. Water bowl. 4. A condenser comprising a tube group in which a number of heat transfer tubes are arranged in parallel in a direction crossing a steam flow in a vessel body in which steam discharged from a steam turbine flows down, wherein the tube group is A condenser having a flow path on a gas outflow side, wherein the flow path is configured such that a flow path cross-sectional area increases toward a downstream side of the gas flow. 5. A condenser provided with a tube group in which a number of heat transfer tubes are arranged in parallel in a direction crossing a steam flow in a vessel body in which steam discharged from a steam turbine flows down, wherein the tube group is In an area near the side wall of the container body,
A condenser having more heat transfer tubes than other portions of the tube group. 6. A condenser provided with a tube group in which a number of heat transfer tubes are arranged in parallel in a direction crossing a steam flow in a vessel body in which steam discharged from a steam turbine flows down, wherein the tube group is A gas cooling unit that cools the gas flowing out to the gas outflow side, wherein the distance between each part of the tube bank on the gas outflow side and each part of the gas cooling unit is configured to be substantially uniform. Condenser. 7. A condenser comprising a tube group in which a number of heat transfer tubes are arranged in parallel in a direction crossing the steam flow in a vessel body in which steam discharged from the steam turbine flows down, wherein the tube group is In an area near the side wall of the container body,
A condenser according to claim 1, wherein a heat transfer tube having a smaller diameter and a smaller pitch than other portions of the tube group is provided. 8. A condenser comprising a tube group in which a number of heat transfer tubes are arranged in parallel in a direction crossing the steam flow in a vessel body in which steam discharged from the steam turbine flows down, wherein the tube group is In an area near the side wall of the container body,
A condenser, wherein a heat transfer member for increasing the heat transfer performance of the heat transfer tube is provided on the inner surface of the heat transfer tube. 9. The condenser according to claim 8, wherein the heat transfer body comprises a fin formed in a spiral shape on the inner surface of the heat transfer tube.