KR101734288B1

KR101734288B1 - Heat exchanger

Info

Publication number: KR101734288B1
Application number: KR1020150061873A
Authority: KR
Inventors: 김영인; 김긍구; 최순; 배영민; 한훈식; 신수재; 지성균
Original assignee: 한국원자력연구원
Priority date: 2015-04-30
Filing date: 2015-04-30
Publication date: 2017-05-12
Also published as: KR20160129557A

Abstract

A heat exchanger assembled by laminating a plurality of plates, wherein the heat exchanger includes a tapered portion which is disposed in a circumferential direction inside the reactor vessel and which is formed on a side surface facing each other so that the width of the inner side surface becomes narrower toward the center portion of the reactor vessel To a heat exchanger. Thereby, the utilization efficiency of the arrangement space can be improved.

Description

Heat Exchanger {HEAT EXCHANGER}

The present invention relates to a heat exchanger arranged inside a reactor vessel to reduce the loss of the arrangement space.

The plate-type heat exchanger was developed by Heatric Co. (US 4665975A, published on May 19, 1987) in the United Kingdom and is widely used in general industrial fields.

The plate-type heat exchanger is a heat exchanger of which the welding between the plates of the heat exchanger is eliminated by using a dense flow path arrangement and diffusion bonding technique by photo-chemical etching technique.

As a result, the plate-type heat exchanger of the printing plate type has high durability against high-temperature and high-pressure environment, and has advantages of high integration and excellent heat exchange performance. Therefore, it can be applied to various fields such as heating and cooling system, fuel cell, automobile, chemical process, medical device, And is being applied to a wide variety of fields such as an evaporator, a condenser, a cooler, a radiator, a heat exchanger, and a reactor. In addition, since the manufacturing technique of the printed substrate type uses a photo-chemical etching technique, it is advantageous to process the flow path more freely than the general processing method.

The plate heat exchanger to be utilized as one example of the present invention has been widely used in industry for over 100 years. A plate type heat exchanger generally forms a flow path by pushing a plate. Accordingly, the application field is similar to that of the printing plate heat exchanger, but it is used more and more in low pressure and low pressure environments. The heat exchange performance of a plate heat exchanger is smaller than that of a plate-type heat exchanger, and is superior to a shell and tube heat exchanger. Also, the plate heat exchanger has a characteristic of being easier to manufacture than the plate heat exchanger of the printing plate type.

The plate-type heat exchanger or steam generator in the present invention refers to a plate-type heat exchanger or a steam generator, as long as there is a difference in the processing method or the joining method of the plate (plate) Or steam generators are all referred to collectively.

FIGS. 1A to 1D are plan views showing a rectangular-shaped steam generator module 11 arranged in various numbers in an integral nuclear reactor.

1, eight steam generator modules 11 are shown in FIG. 1B, twelve steam generator modules 11 in FIG. 1b, eighteen steam generator modules 11 in FIG. 1c, sixteen steam generator modules 11 in FIG. Are arranged inside the reactor vessel (10) along the circumferential direction.

However, when the steam generator is disposed in the reactor vessel 10, the space inside the reactor vessel 10 is large due to the dead space formed between the adjacent steam generator modules 11, It is difficult to minimize the space of the steam generator, which is one of the great advantages of the steam generator. In addition, since the heat exchange efficiency is lower than the number of steam generators disposed in the reactor vessel 10, that is, the steam generator occupies a large space due to the dead space, there is a limit in reducing the size of the reactor vessel 10.

In addition, referring to the patent document of US 8272429 B2, a structure in which a quadrangular heat exchanger is disposed inside a circular container and a horizontal flow path is disposed in the heat exchanger is proposed, There is a disadvantage in that the flow resistance during operation is increased and the natural circulation flow at the time of the accident is lowered and it occupies a lot of dead space in a rectangular shape and thus is not suitable for constructing a compact integral reactor.

It is therefore an object of the present invention to provide a heat exchanger capable of optimizing the size of a reactor vessel in order to minimize the loss of layout space when a plate or plate heat exchanger is disposed inside a reactor vessel.

In order to achieve the object of the present invention, a heat exchanger according to the present invention is a heat exchanger which is assembled by stacking a plurality of plates. The heat exchanger is arranged in a circumferential direction inside a reactor vessel, And tapered portions formed on the side surfaces facing each other so as to become narrower toward the center.

According to an embodiment of the present invention, the outer shape of the heat exchanger may have a polygonal structure.

According to an embodiment of the present invention, each of the plurality of plates may have a different channel fraction.

According to one embodiment of the present invention, the plate may be assembled by diffusion bonding.

According to one embodiment of the present invention, the plate may be assembled by a gasket or welding.

According to an embodiment of the present invention, at least one of the plurality of plates may include a portion having a width different from that of the other plate.

According to one embodiment of the present invention, both sides of the heat exchanger may be cut.

According to another aspect of the present invention, there is provided a heat exchanger, which is assembled by stacking a plurality of plates, the heat exchanger being disposed in a reactor vessel along a circumferential direction, And a plurality of plate assemblies which are assembled by laminating the plurality of plate assemblies, wherein the plurality of plate assemblies comprises: a first plate assembly; And a second plate assembly coupled to both sides of the first plate assembly and having a lateral side length shorter than the first plate assembly.

According to another embodiment of the present invention, a header may be provided on each of the plate assemblies.

According to another embodiment of the present invention, the plurality of plate assemblies may be connected by a single header.

According to another aspect of the present invention, there is further provided a monitoring flow path between the plates for monitoring damage to the flow path.

According to another embodiment of the present invention, the plate forming the secondary flow path of the plurality of plates may include a flow path resistance portion in the secondary flow path.

According to an embodiment or another example of the present invention, the plate forming the primary flow path of the plurality of plates or the play forming the secondary flow path may include an open or stream-like flow path at least partially opened .

According to another embodiment of the present invention, any one of the primary flow path, the secondary flow path, and the monitoring flow path formed on the plurality of plates may be formed between two plates overlapping each other.

According to an example or another example related to the present invention, the second through n-th plate assemblies may be gradually shortened in length from the second plate assembly to the n-th plate assembly.

According to the present invention, the plate heat exchanger and the steam generator can be manufactured in various shapes, so that the heat exchanger or the steam generator can be efficiently disposed inside the reactor vessel, and the utilization efficiency of the internal space of the reactor vessel can be efficiently increased .

In addition, when the steam generators constructed in the polygonal structure are installed inside the integrated reactor, the space utilization efficiency is increased by about 20% or more.

In addition, the maintenance space required for reducing the size of main equipment and internal structures inside the reactor vessel is reduced, and the size of the reactor building is reduced, thereby improving the economic efficiency of the nuclear power plant.

In addition, since the size of the reactor vessel is reduced by arranging the plate heat exchanger or the steam generator compactly inside the reactor vessel, the reactor vessel manufacturing cost can be reduced and the load requirement can be alleviated.

FIGS. 1A to 1D are plan views showing a square-shaped steam generator module in which a plurality of square-shaped steam generator modules are arranged in various numbers in an integrated reactor.
2A to 2F are plan views showing various arrangement structures of a heat exchanger according to the present invention.
3 is a schematic view showing a vertical section of a steam generator disposed inside a nuclear reactor vessel of an integral nuclear reactor.
4 is a schematic diagram for comparing the size of a heat exchanger of the present invention with a conventional heat exchanger (rectangular heat exchanger).
FIG. 5A is a plan view and a side view showing the detailed shape of the plate heat exchanger of the present invention. FIG. Figs. 5B and 5C are cross-sectional views taken along line AA in Fig. 5A.
FIG. 6A is a plan view and a side view showing the detailed shape of the plate heat exchanger of the present invention. FIG. 6B and 6C are cross-sectional views taken along line BB in Fig. 6A.
FIG. 7 is a plan view and a cross-sectional side view of the plate assembly of FIG. 5C. FIG.
8A is a schematic view showing a method of manufacturing a heat exchanger according to an embodiment of the present invention.
8B is a schematic view showing a method of manufacturing a heat exchanger according to another embodiment of the present invention.
9A is a schematic view showing a method of manufacturing a heat exchanger according to another embodiment of the present invention.
9B is a schematic view showing a method of manufacturing a heat exchanger according to another embodiment of the present invention.
10A is a cross-sectional view illustrating a channel shape of a plate according to an embodiment of the present invention.
FIG. 10B is a cross-sectional view illustrating a channel shape of a plate according to another embodiment of the present invention. FIG.
10C is a cross-sectional view showing a plate on which a streamlined flow path is formed.
11A is a cross-sectional view illustrating a channel shape of a plate according to an embodiment of the present invention.
FIG. 11B is a cross-sectional view showing a channel shape of a plate according to another embodiment of the present invention. FIG.
FIG. 11C is a cross-sectional view illustrating a channel shape of a plate according to another embodiment of the present invention. FIG.
12 is a schematic view showing a monitoring flow path plate according to the present invention.

Hereinafter, a heat exchanger according to the present invention will be described in detail with reference to the drawings. In the present specification, the same or similar reference numerals are given to different embodiments in the same or similar configurations. As used herein, the singular forms "a", "an" and "the" include plural referents unless the context clearly dictates otherwise. In this specification, a plate type refers to a plate type and a printing plate type, unless otherwise specified.

The present invention relates to the arrangement of a plate heat exchanger and a steam generator (110).

The heat exchanger described in this specification includes a steam generator 110 that generates steam to convert heat energy generated from a nuclear power plant or the like into power.

The present invention is derived to provide an optimized sized reactor vessel 100 with minimal space loss when a plurality of heat exchangers or steam generators 110 are disposed within the reactor vessel 100.

In order to minimize the loss of the installation space of the heat exchanger, the plate type heat exchanger and the steam generator 110 are provided with a channel structure of the plate so as to have a polygonal structure, and heat exchangers and steam A method of constructing the generator 110 is presented.

In the case of applying the arrangement structure of the heat exchanger or the steam generator 110, it is possible to apply the plate heat exchanger or the steam generator 110 in various forms to a space where the space constraint is large, It is possible to eliminate a space loss of 20% or more, which can greatly contribute to the improvement of the economical efficiency of the integrated reactor.

Here, since the present invention can be applied to a plate-type or plate-type heat exchanger, the object of the present invention is not limited to the steam generator 110 of a nuclear power plant.

The plate heat exchanger or steam generator 110 according to the present invention can be manufactured in two embodiments.

For example, first, at least two plates having the same size are stacked to assemble the steam generator 110, and a plate in which the flow path is entirely disposed and a plate in which the flow path is partially disposed are stacked and coupled, The steam generator 110 having a polygonal structure can be manufactured.

Secondly, at least two plates having the channels as a whole are stacked to assemble the steam generator 110, and plates having different sizes, i.e., the same vertical length (vertical length) and different horizontal lengths (horizontal length) Accordingly, the steam generator 110 having a polygonal structure can be manufactured.

When the heat exchanger manufactured according to the above-described embodiment is disposed along the circumferential direction inside the reactor vessel 100, utilization efficiency of the arrangement space can be improved.

On the other hand, the heat exchanger or steam generator 110 using the plate type can generate a very large heat transfer area, which can greatly reduce the size of the heat exchanger or the steam generator 110 as compared with the conventional shell and tube heat exchanger or the steam generator 110.

In the case of the plate type, it is possible to apply the conventional plate heat exchanger technology having excellent heat exchange efficiency, and even when applying some improvements (increase in flow area) for reducing the flow path resistance, The size of the steam generator can be significantly reduced.

In addition, when the present invention is applied to an integrated reactor, the size of the steam generator 110 is further reduced by about 20% or more, which is more effective. Accordingly, it is possible to reduce the size of the reactor vessel 100 and the reactor building, thereby further improving the economical efficiency of the nuclear power plant.

2A to 2F are plan views showing various arrangement structures of a heat exchanger according to the present invention.

The heat exchanger according to the present invention is arranged adjacent to each other along the circumferential direction inside the reactor vessel 100. The number of heat exchangers may vary depending on the reactor.

The steam generator 110, which will be described hereinafter, is an example of a heat exchanger, and the configuration and configuration of the steam generator 110 may be equally applied to a heat exchanger. Also, the shape and configuration of the heat exchanger can be equally applied to the steam generator 110.

The heat exchanger shown in FIG. 2A is a steam generator 110, and eight steam generators 110 are disposed in the reactor vessel 100 along the circumferential direction. In this case, the interval between two adjacent steam generators 110 may be approximately 45 degrees.

The steam generator 110 may be formed in a polygonal shape by further arranging a plurality of plates on both sides. At this time, the lamination direction of the plates arranged further is the both side directions of the respective steam generators 110 in the plan view of FIG. 2A.

For example, the outer shape of the horizontal cross-section of the steam generator 110 may be hexagonal and the hexagonal horizontal cross-sectional shape will be described in more detail. The inner side surface (inner edge surface) and the outer side surface Are parallel to each other and can be at right angles to the radial direction of the reactor vessel (100). A portion of both sides of the steam generator 110 (a portion close to the outer edge surface) may be parallel to the radial direction of the reactor vessel, and the remaining portion of both sides of the steam generator 110 A tapered portion may be formed.

The tapered portion forms a remaining part of both sides of the steam generator 110 so that the width of the inner side becomes narrower from the outer side to the inner side of the steam generator 110.

Further, an inlet / outlet header may be provided on the rear surface of the steam generator 110 to distribute the fluid to the flow path of each plate in the steam generator 110 or to collect the fluid from each flow path.

In the reactor vessel 100 shown in FIG. 2B, twelve steam generators 110 are disposed.

In the reactor vessel 100 shown in FIG. 2C, 18 steam generators 110 are disposed.

In the reactor vessel 100 shown in FIG. 2D, eight steam generators 210 are disposed.

However, it is possible to increase the size of the steam generator 210 by changing the shape of the header 211. For example, when the thickness of the header 211 (the radial width of the reactor vessel 100) is increased and both side portions of the header 211 connected to the plate disposed on both sides of the steam generator 210 are inclined The length of the plate in which the steam generator 210 is additionally disposed can be extended.

In the reactor vessel 100 shown in FIG. 2E, eight steam generators 110 are disposed.

The eight steam generators 110 may be composed of four rectangular steam generators 11 and four hexagonal steam generators 110. The rectangular steam generators 11 and the hexagonal steam generators 110 may be alternately As shown in FIG.

In the reactor vessel 100 shown in FIG. 2F, sixteen steam generators 110 are disposed.

However, eight of the steam generators 11 and 110 shown in FIG. 2F are steam generators 11 having a rectangular horizontal cross-sectional shape when viewed from the top, and the remaining eight are steam generators 110 having a horizontal cross- have. The rectangular steam generator 11 and the polygonal steam generator 110 may be alternately disposed along the circumferential direction.

According to the steam generator 110 having the polygonal structure shown in FIGS. 2A to 2F, the space for arranging the steam generator 110 can be reduced by about 20% or more. However, in the structure having a large inner diameter of the reactor vessel 100, the effect of reducing the space efficiency is reduced, and it can be increased in a structure having a small inner diameter.

According to the steam generator 110 shown in FIGS. 2E and 2F, the steam generator 110 of a polygonal structure and the steam generator 11 of a conventional rectangular structure are mixed, The steam generator 11 is taken out of the nuclear reactor having the structure in which the steam generator 110 is taken out to the inside of the vessel.

3 is a schematic diagram showing a vertical section of a steam generator 110 disposed within a reactor vessel 100 of an integral nuclear reactor.

A core 12 is provided below the inner center of the reactor vessel 100 and a plurality of steam generators 110 are disposed symmetrically with respect to the inside of the reactor vessel 100 on the basis of the vertical center line of the reactor vessel 100. The plurality of steam generators 110 may be elongated in the longitudinal direction (vertical direction) relative to the lateral direction (horizontal direction) with respect to the vertical cross section of the reactor vessel 100. The steam generator 110 may be configured identically to the plate heat exchanger.

A plurality of control rod driving devices 13 may be disposed between the steam generators 110 so that the control rods can be inserted into the core 12 or the control rods can be drawn out from the core 12. [

A pressurizer 15 is provided above the reactor vessel 100 to suppress boiling of the coolant and to control the operating pressure.

A reactor coolant pump 14 is installed inside the reactor vessel 100 to circulate the primary system fluid.

An inlet header 121 is installed on the lower side of the steam generator 110 and a water supply system is connected to the inlet header 121 by a main water supply pipe 16 to supply secondary system fluid from the water supply system to the steam generator 110 Can be supplied.

An outlet header 122 is provided on the upper side of the steam generator 110 and the turbine system is connected to the outlet header 122 by a main engine 17 to generate heat from the primary system fluid in the steam generator 110 As the steam is delivered to the secondary system fluid, the steam produced in the steam generator 110 may be supplied to the turbine system.

A monitoring header 123 is provided on the side of the steam generator 110 and a sensor 130 is installed on the monitoring header 123 to determine whether the steam generator 110 is damaged.

The operation of the steam generator 110 disposed in the reactor vessel 100 shown in FIG. 3 will be described.

1) Flow path of the primary fluid: The primary fluid of the reactor coolant system whose temperature is increased by receiving heat from the core 12 flows into the upper portion of the steam generator 110 by the circulating power of the reactor coolant pump 14 And flows along one of the flow paths (primary flow path) of the plate, exchanges heat with the secondary fluid, and is cooled and discharged to the reactor coolant system through the primary fluid outlet header 122 under the steam generator 110 and the discharge pipe, (12).

2) Secondary fluid movement path: The secondary fluid (water supply) supplied to the water inlet header 121 under the steam generator 110 by the water pump circulation power of the water supply system is supplied to the other flow path The secondary fluid is gradually transformed into steam and the secondary fluid (steam) flows through the secondary fluid outlet header 122 on the upper portion of the steam generator 110 and the steam pipe 17 To the turbine system.

3) Surveillance flow path: When the flow path of the primary fluid or the secondary fluid is damaged and the primary fluid or the secondary fluid flows out to the monitoring flow path, the state of the monitoring flow path is changed, and the flow path of the monitoring flow path And is collected by the monitoring header 123 and measured by the sensor 130. If an abnormality above the predetermined value is detected, the heat exchanger or steam generator 110 related equipment is stopped.

4 is a schematic diagram for comparing the size of a heat exchanger of the present invention with a conventional heat exchanger (rectangular heat exchanger).

4 shows a state where a plurality of plates are coupled to each other in a heat exchanger, and a flow path may be formed in each plate.

The shape of the heat exchanger shown in Fig. 4 is a horizontal cross-sectional shape as seen from the top of the reactor vessel.

The rectangular plate module 11 located at the upper side in Fig. 4 is a plate of the same size, and the polygon plate module 110 located at the lower side of Fig. 4 is formed by joining both sides of the rectangular plate assembly Bottom side) are further combined so as to be symmetrical with respect to the horizontal line.

In Fig. 4, the upper rectangular plate module 11 is used in a conventional heat exchanger, and the lower polygonal plate module 110 can be used in a heat exchanger according to the present invention.

4, the heat exchanger 110 of the present invention has a larger size than the conventional heat exchanger 11 in addition to the heat exchanger plate, so that the size of the heat exchanger increases in the lateral direction .

The enlarged heat exchanger 110 is arranged in the same number in the reactor vessel of the same size as the conventional one so that the amount of heat exchange can be increased. If an expanded steam generator is deployed in the reactor vessel, steam generation can be increased by transferring more heat from the primary system fluid to the secondary system fluid.

FIG. 5A is a plan view and a side view showing the detailed shape of the plate heat exchanger of the present invention. FIG. 5B and 5C are cross-sectional views taken along line A-A in Fig. 5A.

The plate-type heat exchanger of FIG. 5A includes a heat exchanger casing 111 vertically disposed inside a reactor vessel and forming an outer shape of the heat exchanger, inlet and outlet headers 112a and 121 formed in the heat exchanger casing 111, , 122).

A primary system inlet inlet guide or inlet header 112a is formed above the heat exchanger casing 111 to distribute the flow rate of the primary system (reactor coolant system) fluid to the primary inlet of the steam generator 110, The flow can be smoothly formed. This is optional and does not have to be installed.

The primary system receiving outlet header 112b is formed below the heat exchanger casing 111 so that the primary system water discharged from the steam generator 110 can be collected and supplied to the circulating flow path of the reactor coolant system. This is not a required configuration and may be deployed differently depending on the characteristics of the reactor coolant pump and the reactor coolant system.

A water supply inlet header 121 is formed on the lower side of the heat exchanger casing 111 and a water supply system can be connected to the water supply inlet header 121 through a connection nozzle 114 installed on the side of the reactor vessel . A steam outlet header 122 is formed above the heat exchanger casing 111 and a turbine system (steam pipe) can be connected to the steam outlet header 122 through a connecting nozzle 114 installed on the side of the reactor vessel. Accordingly, the water can be supplied into the heat exchanger casing 111 or the steam can be discharged to the outside of the heat exchanger casing 111.

FIG. 5B is a horizontal sectional view showing a heat exchanger in which plate aggregates of fine group units are bonded to different sides of the heat exchanger in different sizes according to fine groups.

Plate aggregates (110a, 110b) are provided inside the heat exchanger casing (111). The plate assemblies 110a and 110b are formed by laminating a plurality of plates. Each plate has a plurality of flow paths through which a high temperature fluid flows or a plurality of flow paths through which a low temperature fluid flows. The high temperature and low temperature fluids are relative, the fluid supplying the heat source is referred to as a high temperature fluid, and the fluid supplied with the heat source is referred to as a low temperature fluid. For example, the hot fluid may be fluid in the primary system in the nuclear reactor, and the cold fluid may be fluid in the secondary system.

The plate 110b1 of the high temperature fluid and the plate 110b2 of the low temperature fluid are alternately stacked one on top of the other or the plurality of high temperature fluid plates 110b1 are arranged one after the other, One fluid plate 110b2 may be disposed. On the contrary, after one hot fluid plate 110b1 is disposed, a plurality of low temperature fluid plates 110b2 may be disposed.

A first plate assembly 110a in which plates of the same size are laminated is disposed in the middle of the heat exchanger shown in FIG. 5B, and the first plate assembly 110a has different lateral lengths on the upper and lower sides of the first plate assembly 110a And the second through n-th plate assemblies 110b in the fine group unit are laminated.

The second through n-th plate assemblies 110b in the fine group unit are heat exchange plates further disposed in the heat exchanger in order to reduce the space loss of the heat exchanger.

In order to form the tapered portion 110c at the side edge portions of the polygonal heat exchanger, the second to nth plate aggregates 110b are separated from the first plate aggregate 110a, that is, The lateral width (transverse length) of each plate assembly may gradually become shorter toward the n-plate assembly.

Thus, except for the length of the n-plate assembly having the shortest length in the top or bottom of the heat exchanger, the length from the right edge to the left edge of the heat exchanger increases along the upper side of the heat exchanger The width between the lower side surfaces becomes narrower. This is to minimize the distance between the heat exchangers and to enlarge the size of the heat exchanger when the heat exchangers are disposed along the circumferential direction inside the reactor vessel.

The second through n-th plate assemblies 110b in the fine group unit refers to a plate having a predetermined thickness, which is a group of two or three groups, for example, joined together. The number of plates in the fine group unit may vary depending on the design conditions, not the predetermined values. Instead of the plate assembly 110b of the fine group unit, a single plate having a different length may be laminated to the upper and lower sides of the first plate assembly 110a.

5C is a horizontal sectional view showing a heat exchanger in which groups of plate assemblies 310a and 310b are grouped into groups of different sizes on the side of a heat exchanger.

A first plate assembly 310a in which plates of the same size are laminated is disposed in the middle of the heat exchanger shown in FIG. 5C, and the first plate assembly 310a has different lateral lengths on the upper and lower sides of the first plate assembly 310a And the second plate assembly 310b of the group unit may be laminated.

Here, the group of plate assemblies means a plate having a certain thickness, for example, four to six groups. The number of plates in the group unit may vary depending on the design conditions, not the predetermined values.

The group of plate assemblies 310a and 310b has the same function and purpose as the plate assemblies 110a and 110b of the fine group unit. However, the plate assemblies 310a and 310b differ in that the number of plates in the group unit is large and small.

FIG. 6A is a plan view and a side view showing the detailed shape of the plate heat exchanger of the present invention. FIG. 6B and 6C are cross-sectional views taken along line B-B in Fig. 6A.

A monitoring header 123 is formed on the middle side of the heat exchanger casing 111 shown in FIG. 6A and a sensor connection portion is connected to the monitoring header 123 to detect whether the fluid flowing into the monitoring header 123 is detected It is possible to judge whether or not the heat exchanger is damaged.

FIG. 6B is a horizontal sectional view showing a heat exchanger in which plate assemblies 110b of fine group units are bonded to different sides of a heat exchanger by fine groups.

6C is a horizontal sectional view showing a heat exchanger in which plate assemblies 310 of group units are joined to each other in different sizes on the side of a heat exchanger.

6A to 6C are similar to Figs. 5A to 5C, and therefore, the same constitution will be omitted for the sake of clarity.

However, a monitoring plate 110b3 is additionally provided between the high-temperature fluid plate 110b1 and the low-temperature fluid plate 110b2 of FIGS. 6b and 6c to monitor whether the high-temperature or low-temperature flow path is damaged. The monitoring plate 110b3 is not necessarily provided additionally, but may be formed by utilizing the fluid plates 110b1 and 110b2 according to the characteristics of the flow path configuration. As the monitoring sensor is connected to the monitoring plate 110b3, it is possible to monitor a physical or chemical state change transmitted from each flow channel to the header in case of damage.

FIG. 7 is a plan view and a cross-sectional side view of the plate assembly of FIG. 5C. FIG.

7 is a plan view showing a first plate assembly 310a having the same length (width and channel width) as the first plate assembly 310a, N plate assembly 310b are stacked.

7 is a side view showing a plate of one of the first plate assemblies 310a from the left, and the right figure is a side view of the first plate assemblies 310a of the second to nth plate assemblies 310b. The plate assembly 310b1 arranged next to the first plate assembly 310a of the second through n-th plate assemblies 310b is shown on the right side. And a right side view is a side view showing a plate assembly 310b3 disposed thirdly adjacent to the first plate assembly 310a among the second to nth plate assemblies 310b.

In the plan view of FIG. 7, the second plate assembly 310b shows a state in which a portion where the flow path is not formed is cut. In the side view of FIG. 7, the second plate assembly 310b shows the plate shape before cutting.

That is, from the left side view in the side view of FIG. 7, a flow path 311 is formed on the entire surface of the first plate assembly 310a. And the proportion of the portion where the flow path 311 is not formed increases gradually toward the right side. For example, the number of channels of the second plate 310b1 from the left to the right is 6, the number of channels of the right plate 310b2 is then 3, and the number of channels of the right plate 310b3 is one. The number of flow paths shown in FIG. 7 is only one example, and is not limited thereto. The shape and length of the illustrated flow path 311 are merely exemplary.

After the plate assemblies 310a and 310b constructed as shown in the side view of FIG. 7 are joined by diffusion bonding or welding, a plate or a plate assembly 310b in which a flow path is not formed, as shown in the plan view of FIG. 7, The polygonal heat exchanger 110 can be constructed.

Although the flow path plate of the plate shown in Fig. 7 is described as an example of the flow path plate of the secondary fluid, the flow path plate of the primary fluid can also constitute the heat exchanger according to the same concept and principle as those of Fig.

8A is a schematic view showing a method of manufacturing a heat exchanger according to an embodiment of the present invention.

The heat exchanger plate assemblies 310a and 310b shown in the uppermost portion of FIG. 8A include a first plate assembly 310a in which a flow path is formed on the entire surface and a first plate assembly 310b in which a flow path is not formed in the upper and lower portions of the first plate assembly 310a And a second through n-th plate assemblies 310b including the second through n-th plate assemblies 310b. The first plate assembly 310a and the second to nth plate assemblies 310b may be joined by diffusion bonding or welding. In addition, the first plate assembly 310a and the second to nth plate assemblies 310b may be hermetically sealed after the edges are fastened to each other by a bolt, and then a gasket is installed between the plates or plate assemblies.

The joining methods such as gaskets, diffusion bonding, welding, etc. are applicable between plates or between plate assemblies or plate and plate assemblies.

Then, a portion of the bonded plate assemblies 310a and 310b where the flow path of the second through n-th plate assemblies 310b is not formed is cut.

Next, one header 122 and an outlet nozzle connection portion 114 are connected to the right side surfaces of the first plate assembly 310a and the second through nth plate assemblies 310b.

By the above-described process, a polygonal heat exchanger can be manufactured.

Here, the flow path of each plate or plate assembly 310b is blocked (plugged) with a cut portion portion where the flow path is not formed, and is communicated with a portion connected to the header 122 to allow fluid to flow in and out.

8B is a schematic view showing a method of manufacturing a heat exchanger according to another embodiment of the present invention.

According to the heat exchanger manufacturing method shown in Fig. 8B, the shape of the header 322 is different. The shape of the header can be changed to extend the length (width, channel width) of the plate aggregate (310a, 310b) of the heat exchanger.

The length (width and channel width) of the second through n-th plate assemblies 310b shown in FIG. 8B is shifted to the right (toward the header connecting portion) as compared with the second through n-th plate assemblies 310b shown in FIG. . The lateral width of the header 322 is increased toward the outermost n-plate assembly 310b for connecting the elongated second plate assembly 310b.

Although the second through the n-th plate assembly 310b in Fig. 8 (b) are different in that their lengths (width and channel installation width) are further extended, the other configurations are similar to the plate assembly 310a in Fig. 8 .

9A is a schematic view showing a method of manufacturing a heat exchanger according to another embodiment of the present invention.

According to the heat exchanger manufacturing method shown in Fig. 9A, the first plate assembly 410a and the second plate assembly 410b are initially fabricated separately. In other words, both the first plate assembly 410a and the second plate assembly 410b are constituted by a plurality of plates in which a flow passage is formed on the entire surface. Each plate assembly is joined by diffusion bonding, welding, or the like. 7, the first plate assembly 310a and the second plate assembly 310b are cut to have the same size, and the first plate assembly 310a formed on the entire surface of the flow passage, The plate aggregates 310a and 310b shown in FIG. 7 and the plate aggregates 310a and 310b shown in FIG. 9A are separated from each other in that a portion of the second plate aggregate 310b having no flow path is cut off after the second plate aggregate 310b, And the plate assemblies 410a and 410b of FIG. 9B are different from each other.

Then, the first plate assembly 410a and the second plate assembly 410b separately manufactured are joined to each other by welding or the like.

Then, the first plate assembly 410a and the second plate assembly 410b are connected and assembled by one header 222. [ The header 222 and plate assemblies 410a and 410b may be joined by welding. An outlet nozzle connection 214 is further provided in the header 222.

Thereby, the heat exchanger product can be completed.

9B is a schematic view showing a method of manufacturing a heat exchanger according to another embodiment of the present invention.

9B, similar to FIG. 9A in that a first plate assembly 410a and a second plate assembly 410b having different sizes are separately manufactured, but the plate assemblies 410a and 410b 222b, and 222c are provided for each of the plate assemblies 410a and 410b, and the headers 222a, 222b, and 222c are connected to the plate assemblies 410a and 410b.

That is, the first plate assembly 410a and the second plate assembly 410b are welded and connected to a separate first header 222a (respective inlet or outlet header) and a second header 222b, The header 222a and the second header 222b may be welded to the third header 222c again via a connection. An outlet nozzle connection portion 214 is further provided in the third header 222c.

Thus, the manufacture of the heat exchanger is completed.

Although the second plate assembly 410b is shown on both sides of the first plate assembly 410a in FIGS. 9A and 9B, it is not limited thereto and may further include third to nth plate assemblies, To the n-th plate assembly, the lateral length of each plate assembly can be shortened.

FIG. 10A is a cross-sectional view showing a channel shape of a plate 510a according to an embodiment of the present invention.

A plurality of primary flow paths are formed in the heat exchanger plate 510a shown in Fig. 10A in the vertical direction, and the primary fluid can flow in the vertical direction. In particular, in the case of the flow path shown in Fig. 10A, the fluid flows from the upper part to the lower part. The primary flow path plate 510a may be divided into an inlet region 511, a main heat generating portion 512, and an outlet region 513 from the top in each section. The upper portion of the inlet area 511 is connected to the inlet header 512a so that the primary fluid is distributed to the respective flow paths in the inlet header 512a. In the main heating portion 512, the primary fluid undergoes heat exchange with the fluid flowing in the main heating portion of the adjacent plate. The lower portion of the outlet region 513 is connected to the outlet header 512b so that the heat exchanged fluid is collected in the outlet header 512b. However, the headers 512a and 512b are not necessarily installed and may not be installed according to the nuclear power plant.

10B is a cross-sectional view illustrating a flow path shape of the plate 610a according to another embodiment of the present invention.

The channel shape of the heat exchanger plate 610a shown in Fig. 10B is open. The open-type flow path means a flow path capable of fluid movement between adjacent ones of the flow paths. In the open type, a transverse flow path 620 is further formed between the closed type flow paths, so that the fluid can flow between the adjacent flow paths.

A plate having a streamlined channel shape can be formed instead of the open channel shown in FIG. 10B.

10C is a sectional view showing a plate 710a on which a streamlined flow path is formed.

The streamlined flow path shown in FIG. 10C is formed between the plurality of flow path guide protrusions 721 provided inside the plate 710a. The flow path guide protrusions 721 are formed in a streamlined shape, and the streamlined flow paths are recessed in the form of a groove. The flow path guide protrusions 721 may be formed at regular intervals in the lateral direction and the longitudinal direction, and the flow path guide protrusions 721 spaced in the longitudinal direction may be staggered from each other.

11A is a cross-sectional view illustrating a channel shape of a plate according to an embodiment of the present invention.

The plate 810b shown in Fig. 11A shows the secondary flow path shape of the heat exchanger.

The flow path shape of the plate 810b shown in Fig. 11A is a closed type. The closed type flow path means a flow path without fluid movement between adjacent flow paths. The secondary flow path plate may be divided into an inlet region 811, a main heat-generating portion 812, and an outlet region 813 from the bottom in each section. The flow path between the inlet region 811 and the outlet region 813 is formed by a horizontal flow path extending in the horizontal direction while being spaced apart from the lower side portion of the side surface of the secondary flow path plate by a predetermined distance and a horizontal flow path extending in the vertical direction at the end of the horizontal flow path, And a vertical flow path connected to the flow path.

The secondary fluid flows from the lower side of the plate 810b and is discharged to the upper right side of the plate 810b. However, it is not limited to such a channel shape.

The flow path of the inlet region 811 is connected to the inlet header 812a so that the secondary fluid can be distributed to the flow path of the inlet region 811 through the inlet header 812a. The flow path of the outlet region 813 is connected to the outlet header 812b so that fluid can be collected from the main transmission portion 813 through the outlet header 812b.

11B is a cross-sectional view illustrating a flow path shape of the plate 910b according to another embodiment of the present invention.

The channel shape of the plate 910b shown in Fig. 11B is partially open. The partially open flow path means that only a part of the open flow path capable of fluid movement between adjacent flow paths is formed. For example, only the main flow passage 912 and a part of the inlet region 911d form an open flow passage (a transverse flow passage connecting the longitudinal flow passage).

A common header portion 911a, a flow path resistance portion 911b (or an economizer), a flow path enlarging portion 911c, and the like may be further provided on the upstream side of the inlet region 911d.

The common header portion 911a may be composed of a plurality of horizontal flow paths extending in the horizontal direction from a lower side of one side of the plate 910b and a plurality of vertical flow paths extending in the vertical direction in the horizontal flow paths. The vertical flow path is connected to an orifice (corresponding to the orifice of the helical steam generator) of the flow path resistance portion 911b to be described later, and distributes the flow amount to the flow path resistance portion 911b.

Generally, in the heat exchanger used as a steam generator, the flow path resistance portion 911b may cause unstable flow during vapor formation. For example, the amount of heat of the high temperature transferred from the primary system is not transmitted equally to the flow paths of the main heat conduction part 912 and the inlet area 911d, and the amount of heat transferred to each flow path is different, The steam generation time may be different from each other, so that the pressure distribution in the flow path may be uneven and the pressure may fluctuate due to the pressure wave generated in the steam formation.

In order to solve such a problem, when the flow path is formed in the form of a bend-like flow path formed to be curved in the left-right direction rather than a straight line by appropriately narrowing the width of the flow path in the inlet region 911d, the flow path resistance of the inlet region 911d becomes large , And even when pressure fluctuation occurs in the main heating portion 912, the flow path resistance of the inlet region 911d can be suppressed.

The economizer can stabilize the flow in the inlet region 911d and increase the heat transfer efficiency when the shell side outside the tube in the shell & tube type steam generator is used as the flow path of the secondary fluid (water / steam) have.

The flow expanding portion 911c is a flow path for connecting the flow path of the flow path resistance portion 911b to the flow path of the main heating portion 912. The flow path width of the flow path portion 911b from the flow path of the flow path resistance portion 911b to the flow path of the main heat transfer portion 912 It gets bigger. As a result, the flow resistance after the main heating portion 912 decreases due to an increase in the flow cross-sectional area.

In the case of the partially open channel shown in Fig. 11B, the resistance can be configured to be a smaller streamline type.

11C is a cross-sectional view showing a channel shape of the plate 1010b according to another embodiment of the present invention.

The channel shape of the plate 1010b shown in Fig. 11C is open. Open transverse flow paths are formed in both the inlet region 1011d, the main heat generating portion 1012, and the outlet region 1013, and fluid movement is formed between the adjacent flow paths.

In the case of the fully opened flow path shown in Fig. 11C, the resistance can be configured to be a smaller streamlined type.

The flow path shape in each embodiment is not limited to this, and may be applied in other forms.

12 is a schematic view showing the monitoring channel plate 1110 according to the present invention.

A monitoring channel 1111 is formed in the monitoring channel plate 1110 shown in Fig. However, the monitoring channel 1111 is not necessarily formed in the monitoring channel plate 1110, but may be formed on one side of the primary channel plate or the secondary fluid plate. The monitoring channel plate 1110 is disposed between the primary fluid plate and the secondary fluid plate, and the monitoring channel 1111 is formed of a micro channel having a size much smaller than that of the primary channel or the secondary channel . The monitoring channel may be in the form of a lattice. The monitoring flow path 1111 is an open flow path, and is connected to each other so as to allow fluids to move between adjacent flow paths, that is, a horizontal flow path and a vertical flow path. And, all the monitoring channels are connected to the header. Thereby, when a damage occurs in either the primary fluid plate or the secondary fluid plate, it is conveyed along the monitoring channel communicated, so that the physical or chemical state can be collected into the header and sensed by the sensor.

Since the flow path of the monitoring channel 1111 is very small, the heat transfer resistance between the primary fluid plate and the secondary fluid plate can be minimized. Further, according to the application of the fine flow path, the structural effect caused by the narrowing of the gap between the first flow path-monitoring flow path-second flow path can be minimized.

The monitoring channel 1111 may be provided between the plurality of plates and may additionally include a monitoring channel for detecting a gap between the plurality of plates coupled to each other by diffusion bonding or welding .

The monitoring flow path 1111 can be provided in a double manner.

Accordingly, the present invention has the following advantages by providing various types of play-type heat exchangers for increasing the utilization efficiency of the arrangement space and a method of manufacturing the same.

First, since the plate heat exchanger and the steam generator can be manufactured in various shapes, efficient space arrangement is possible.

Second, when a steam generator with a polygonal structure is built and the space utilization efficiency is increased by about 20% or more when installed in the reactor vessel of the integral reactor, the size of the reactor vessel is reduced and the economical efficiency of the nuclear power plant is improved.

Third, since the size of main equipment and internal structures inside the reactor vessel is reduced, the maintenance space required is reduced, and the size of the reactor building is reduced, thereby improving the economical efficiency of the nuclear power plant.

Fourth, the adoption of a compact plate-type heat exchanger or steam generator can alleviate load requirements.

Fifth, it is possible to mitigate the maintenance difficulty of the plate heat exchanger and the steam generator by installing the monitoring fine flow paths together.

Sixth, by stopping plate-type heat exchanger (or steam generator) and reactor operation when a plate type heat exchanger (or steam generator) abnormality is detected by installing a monitoring micro-flow path, The safety can be greatly improved.

Seventh, a plate-type heat exchanger or a steam generator of a plate type heat exchanger can remove a weld portion at a core portion where heat transfer occurs except for the inlet and outlet nozzles.

The heat exchanger described above is not limited to the configuration and the method of the embodiments described above, but the embodiments may be configured by selectively combining all or a part of each embodiment so that various modifications can be made.

12: Core
13: Control rod driving device
14: reactor coolant pump
15: Presser
16: Water supply pipe
17:
100: Reactor vessel
110: Steam generator
110a, 310a, 410a: a first plate assembly
110b, 310b, 410b: a second plate assembly
110b1: high temperature fluid plate
110b2: Low temperature fluid plate
510a, 610a, 710a, 810b, 910b, 1010b:
110c, and 310c:
111: Heat exchanger casing
112a, 512a, 612a, 712a, 812a, 912a, 1010a:
112b, 512b, 612b, 712b, 812b, 912b, 1010b:
121: entrance header
122: exit header
123: Header for monitoring
130: sensor
222,322: Header
222a: first header
222b: second header
222c: third header
214, 314: outlet nozzle connection
721: Flow guide projection
511, 611, 711, 811, 911d, 1011d:
911a, 1011a: Common header
911b and 1011b:
911c, and 1011c:
512, 1212, 1212, 1212, 1212:
513, 613, 713, 813, 913,
1110: Surveillance plate
1111: Surveillance Euro

Claims

In a heat exchanger assembled by laminating a plurality of plates,
And a tapered portion formed on a side surface facing each other so that the width of the inner surface becomes narrower toward the center of the reactor vessel,
Wherein at least one of the plurality of plates includes a portion in which the flow path is formed and a portion in which the flow path is not formed,
Wherein the tapered portion is formed by a cut portion of the at least one plate in which a portion where the flow path is not formed is cut to reduce the width,
Wherein the flow path is recessed in the plurality of plates by photochemical etching,
Wherein at least one of the plurality of plates disposed in the tapered portion has a reduced ratio of a portion where the flow path is formed toward the outward plate of the plurality of plates.

The method according to claim 1,
And the outer shape is a polygonal structure.

The method according to claim 1,
Wherein at least one of the at least one plate has a different ratio between a portion where the flow path is formed and a portion where the flow path is not formed.

The method according to claim 1,
Wherein said plate is assembled by diffusion bonding.

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The method according to claim 1,
Wherein the tapered portion is formed by performing diffusion bonding of the plurality of plates, and cutting the portion of the at least one plate where the flow path of the at least one plate is not formed at a predetermined inclination angle.

In a heat exchanger assembled by laminating a plurality of plates,
A plurality of plate assemblies arranged in a reactor vessel in a circumferential direction and assembled by laminating plates having flow paths formed on the entire surface thereof,
Wherein the plurality of plate assemblies include:
A tapered portion formed on a side surface facing each other such that a width of an inner side of the tapered portion becomes narrower toward a center portion of the reactor vessel;
A first plate assembly; And
Wherein a side plate of the first plate assembly is laterally laminated on both side surfaces of the first plate assembly and the lateral length of each plate assembly is further away from the first plate assembly than the first plate assembly And a second to an n-th plate assembly formed so as to be gradually shortened,
And the second to n-th plate assemblies gradually decrease in the number of the flow paths from the second plate assembly to the n-th plate assembly.

8. The method of claim 7,
And a header is provided on each of the plate assemblies.

8. The method of claim 7,
Wherein the plurality of plate assemblies are connected by a single header.

8. The method of claim 1 or 7,
And a monitoring flow path for monitoring whether the flow path is damaged between the plates.

8. The method of claim 1 or 7,
Wherein the plate forming the secondary flow path of the plurality of plates receives the heat source includes the flow path resistance portion in the secondary flow path.

8. The method of claim 1 or 7,
Wherein the plate forming the primary flow path for supplying the heat source among the plurality of plates or the plate for forming the secondary flow path receiving the heat source includes the flow path of the open or stream structure at least partially opened.

8. The method of claim 1 or 7,
One of a primary flow path for supplying a heat source formed on the plurality of plates, a secondary flow path for supplying a heat source, and a monitoring flow path for monitoring damage of the flow path is formed between two plates Features a heat exchanger.

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