KR20160099624A - Heat exchanger - Google Patents

Abstract

In the heat exchanger, a cooling air line 28 through which cooling air (AC) flows, a compressed air branch line 27 through which compressed air (A2) flows, and heat exchange between cooling air (AC) and compressed air A plurality of heat exchanging units 41 and 42 provided in parallel with the flow direction of the cooling air AC and a plurality of heat exchanging units 41 and 42 disposed on the downstream side in the flow direction of the cooling air A flow rate regulating valve 43 for regulating the flow rate of the compressed air A2 flowing through the second heat exchanging section 42, temperature sensors 71 and 72 for detecting the temperature of the compressed air A2, (72) for adjusting the opening degree of the flow rate adjusting valve (43) in accordance with the temperature of the compressed air (A2)

Description

Heat Exchanger {HEAT EXCHANGER}

The present invention relates to a heat exchanger that performs heat exchange between a primary fluid and a secondary fluid.

When the secondary fluid is cooled or heated by performing heat exchange between the primary fluid and the secondary fluid, there is a heat exchanger in which the inlet header and the outlet header are connected by a plurality of heat transfer tubes. In such a heat exchanger, when the secondary fluid supplied to the inlet header flows through the plurality of heat transfer tubes and flows through the outlet header, the primary fluid is cooled or heated by the primary fluid contacting the heat transfer tube.

For example, there is a heat exchanger having the structure described in Patent Document 1 below. The heat exchanger disclosed in Patent Document 1 is a heating / vaporizing device for heating or vaporizing a low-temperature fluid. The heat exchanger is configured to heat or cool a low-temperature fluid flowing through a heat transfer tube constituting the panel, Vaporize. In addition, an adjustment valve is provided immediately before the inlet of the two headers or the manifold, and the supply of the low temperature fluid to the heat exchanger panel is stopped in accordance with the variation of the supply amount of the low temperature fluid, The control valve is operated so that the flow rate at the time of the load is maintained.

In the case of adjusting the temperature of the primary fluid by performing heat exchange between the primary fluid and the secondary fluid, it is conceivable that a part of the primary fluid is mixed with the primary fluid after heat exchange without heat exchange. For example, a heat exchanger is provided in the primary fluid channel, and a bypass channel is provided in the primary fluid channel to bypass the heat exchanger. The temperature of the primary fluid is adjusted by increasing or decreasing the flow rate of the primary fluid flowing through the bypass flow path.

Such a heat exchanger is described in, for example, Patent Documents 2 and 3 below.

JP-A-2009-052724 Japanese Patent Application Laid-Open No. 2005-221180 Japanese Patent Application Laid-Open No. 2005-226957

The heat exchanger in which the inlet header and the outlet header are connected to each other through a plurality of heat transfer tubes is a heat exchanger in which a secondary fluid flows in each heat transfer tube and a primary fluid flows outside the heat transfer tubes perpendicularly to the heat transfer tube, Heat exchange is carried out. At this time, when the flow rate of the secondary fluid is lowered, the flow rate of the secondary fluid flowing through each of the heat transfer tubes is decreased. Therefore, in the heat transfer pipe disposed on the upstream side of the primary fluid, the secondary fluid is in a supercooled state or an overheated state Throw away. Therefore, even in the heat exchanger in which the inlet header and the outlet header are connected by a plurality of heat transfer tubes, the supply of the low temperature fluid to the heat exchange panel can be stopped in accordance with the variation of the supply amount of the low temperature fluid, It is preferable that the supercooling degree or superheat of the secondary fluid can be suppressed.

When the flow rate of the primary fluid flowing from the primary fluid channel to the bypass channel is increased, the flow rate of the primary fluid flowing through the heat exchanger is decreased. As a result, the heat exchanger increases the amount of heat exchange and becomes a superheated state or supercooled state of the primary fluid at the outlet portion. In the heat exchanger, when the secondary fluid is in an overheated state or a supercooled state, a large heat load acts on a structural member (for example, a heat transfer tube) of the heat exchanger. Therefore, measures must be taken in advance, . When the primary fluid is in an overheated state or a supercooled state, by-products may be generated, and this by-product may adversely affect the heat exchanger.

An object of the present invention is to provide a heat exchanger capable of suppressing supercooling or overheating of a secondary fluid by appropriately performing heat exchange even if the flow rate of the primary fluid fluctuates.

Another object of the present invention is to provide a heat exchanger capable of adjusting the temperature of the primary fluid with high accuracy and suppressing the overheating or supercooling of the primary fluid.

In order to achieve the above object, the heat exchanger of the present invention performs heat exchange in a primary flow passage through which a primary fluid flows, a secondary flow passage through which a secondary fluid flows in the primary flow passage, and a primary fluid and a secondary fluid And a flow regulating valve for regulating the flow rate of the primary fluid flowing through the plurality of heat exchanging units.

Thus, the primary fluid flowing through the plurality of heat exchanging portions is cooled or heated by heat exchange with the secondary fluid. When the state of the primary fluid flowing through the plurality of heat exchanging portions fluctuates, the opening degree of the flow regulating valve is adjusted in accordance with the state of the primary fluid. Therefore, in the plurality of heat exchanging portions, The flow rate of the primary fluid flowing through the heat exchange unit located on the side of the heat exchanger is adjusted. As a result, the influence of the secondary fluid on each of the heat exchanging portions is reduced, and the high temperature and low temperature are suppressed. As a result, even if the state of the primary fluid fluctuates, the supercooling or heating of the primary fluid can be suppressed by appropriately performing heat exchange.

The heat exchanger of the present invention is a heat exchanger for exchanging heat between a primary flow channel through which a primary fluid flows, a secondary flow channel through which a secondary fluid flows in the primary flow channel, a primary fluid and a secondary fluid, A flow rate adjusting valve for adjusting a flow rate of the primary fluid flowing through the plurality of heat exchanging units, a state detecting sensor for detecting a state of the primary fluid, And a control section for adjusting the opening degree of the flow rate adjusting valve in accordance with the detected state of the primary fluid.

Thus, the primary fluid flowing through the plurality of heat exchanging portions is cooled or heated by heat exchange with the secondary fluid. When the state of the primary fluid flowing through the plurality of heat exchanging portions fluctuates, the opening degree of the flow regulating valve is adjusted in accordance with the state of the primary fluid, so that the plurality of heat exchanging portions are located on the downstream side in the flow direction of the secondary fluid The flow rate of the primary fluid flowing through the heat exchanging portion is adjusted. As a result, the influence of the secondary fluid on each of the heat exchanging portions is reduced, and the high temperature and low temperature are suppressed. As a result, even if the state of the primary fluid fluctuates, the supercooling of the secondary fluid or the overheating can be suppressed by appropriately performing the heat exchange.

In the heat exchanger of the present invention, it is preferable that the plurality of heat exchanging units are provided with a separate inlet header at one end and a common outlet header at the other end, and the primary flow path is connected to the inlet header and the outlet header And the flow rate regulating valve is provided in the primary fluid channel connected to the inlet header.

Therefore, since the flow rate regulating valve is provided in the primary fluid flow passage branched to the upstream side in the plurality of heat exchanging portions and connected to the heat exchange portion located on the downstream side in the flow direction of the secondary fluid, , The flow rate of the primary fluid flowing through the plurality of heat exchanging units can be adjusted with high accuracy.

In the heat exchanger of the present invention, it is preferable that the plurality of heat exchanging units are provided with an inlet header common to one end portion and a separate outlet header at the other end portion, and the primary flow path is connected to the inlet header and the outlet header And the flow rate regulating valve is provided in the primary fluid channel connected to the outlet header.

Therefore, by providing the flow rate regulating valve in the primary fluid channel connected to the heat exchanging unit located on the downstream side in the flow direction of the secondary fluid by connecting the primary fluid branched on the downstream side in the plurality of heat exchanging units, The flow rate of the primary fluid flowing through the plurality of heat exchanging units can be adjusted with high accuracy.

In the heat exchanger of the present invention, the state detecting sensor is a temperature sensor for detecting the temperature of the primary fluid at the outlet side of the plurality of heat exchanging units, And the opening degree of the flow rate adjusting valve is made smaller when the temperature difference of the differential fluid becomes larger than a preset predetermined temperature difference.

Therefore, when the temperature difference of the primary fluid flowing through the plurality of heat exchanging units becomes larger than the predetermined temperature difference, the opening degree of the flow regulating valve is made small, so that the flow rate of the primary fluid flowing through the heat exchanging unit located on the downstream side in the flow direction of the secondary fluid . As a result, the influence of the secondary fluid on the heat exchange portion located on the upstream side in the flow direction is reduced, and the supercooling or overheating of the primary fluid can be suppressed.

In the heat exchanger of the present invention, the state detection sensor is a flow rate sensor for detecting the flow rate of the primary fluid at the inlet side of the plurality of heat exchange units, and the control unit controls the flow rate of the primary fluid at the inlet side of the plurality of heat exchange units And the opening degree of the flow rate adjusting valve is made smaller when the flow rate of the differential fluid is smaller than a predetermined flow rate set in advance.

Therefore, when the flow rate of the primary fluid flowing through the plurality of heat exchanging sections is smaller than the predetermined flow rate, the opening degree of the flow rate adjusting valve is made small. Therefore, the flow rate of the primary fluid flowing through the heat exchange section located on the downstream side in the flow direction of the secondary fluid . As a result, the influence of the secondary fluid on the heat exchange portion located on the upstream side in the flow direction is reduced, and the supercooling or overheating of the primary fluid can be suppressed.

In the heat exchanger of the present invention, the state detection sensor may be a pressure sensor for detecting the pressure of the primary fluid at the inlet side of the plurality of heat exchanging units, and the control unit may include: And the opening degree of the flow rate adjusting valve is made smaller when the pressure of the differential fluid is larger than a predetermined pressure.

Therefore, when the pressure of the primary fluid flowing through the plurality of heat exchanging units is lower than the predetermined pressure, the opening degree of the flow regulating valve is made small. Therefore, the flow rate of the primary fluid flowing through the heat exchanging unit located on the downstream side in the secondary fluid flowing direction . As a result, the influence of the secondary fluid on the heat exchange portion located on the upstream side in the flow direction is reduced, and the supercooling or overheating of the primary fluid can be suppressed.

In the heat exchanger of the present invention, a plurality of the flow rate adjusting valves are provided corresponding to the plurality of heat exchanging units, and the control unit controls the flow rate adjusting valves in the plurality of heat exchanging units in accordance with the state of the primary fluid detected by the state detecting sensor And the opening degree of the plurality of flow rate adjusting valves is adjusted so that the flow rate of the primary fluid flowing through the heat exchanging unit located on the downstream side in the flow direction of the secondary fluid of the plurality of flow regulating valves is reduced.

Therefore, by adjusting the flow rate of the primary fluid flowing through the plurality of heat exchanging sections, the effect of the secondary fluid on each heat exchanging section is reduced, and the supercooling degree or overheating of the primary fluid can be suppressed with high accuracy.

In order to achieve the above object, the heat exchanger of the present invention is a heat exchanger comprising: a primary flow passage through which a primary fluid flows; a secondary flow passage through which a secondary fluid flows in the primary flow passage; A bypass flow passage for bypassing at least one heat exchange section of the plurality of heat exchange sections, a flow rate adjustment valve for adjusting a flow rate of the primary fluid flowing through the bypass flow passage, and a plurality of heat exchange sections A temperature sensor for measuring the temperature of the primary fluid at the outlet side of the secondary fluid and a control section for adjusting the opening of the flow control valve in accordance with the temperature of the primary fluid detected by the temperature sensor.

Therefore, the flow rate of the primary fluid for bypassing at least one of the plurality of heat exchangers is adjusted to adjust the opening degree of the flow rate adjusting valve in accordance with the temperature of the primary fluid at the outlet side of the heat exchanger. At this time, since the primary fluid bypasses at least one heat exchange section, the primary fluid that has passed through the heat exchange section is prevented from being heated to a higher temperature or lowered in temperature even if the flow rate temporarily decreases. As a result, the temperature of the primary fluid can be adjusted with high accuracy, and the overheating or supercooling of the primary fluid can be suppressed.

In the heat exchanger of the present invention, it is preferable that the plurality of heat exchanging units have a first heat exchanging unit and a second heat exchanging unit connected in series, wherein one end of the bypass channel is connected to the inlet of the first heat exchanging unit, And is connected to the connection portion of the first heat exchanging portion and the second heat exchanging portion.

Accordingly, the primary fluid passing through the bypass flow path is supplied to the connection portion between the first heat exchange portion and the second heat exchange portion, whereby the primary fluid heat-exchanged in the first heat exchange portion is mixed with the primary fluid passing through the bypass flow path And the high temperature or low temperature of the primary fluid in the second heat exchanging part is suppressed, whereby the overheating or the supercooling of the primary fluid can be suppressed.

In the heat exchanger of the present invention, the first heat exchanging portion and the second heat exchanging portion are arranged in parallel, and the inlet portion of the first heat exchanging portion and the outlet portion of the second heat exchanging portion are disposed at one end, And a connecting portion is disposed.

Therefore, by arranging the first heat exchanging portion and the second heat exchanging portion in parallel and efficiently circulating the primary fluid, the device can be downsized.

In the heat exchanger of the present invention, the connecting portion is a header to which the downstream end of the first heat exchanging portion and the upstream end of the second heat exchanging portion are connected.

Therefore, by making the connecting portion a header, the first heat exchanging portion and the second heat exchanging portion can be easily connected, and the primary fluid that has passed through the heat exchanging portion and the primary fluid that has passed through the bypass passage can be properly mixed.

In the heat exchanger of the present invention, the connecting portion is a connecting pipe for connecting the downstream side end portion of the first heat exchanging portion and the upstream side end portion of the second heat exchanging portion.

Therefore, by making the connecting portion a connecting pipe, the first heat exchanging portion and the second heat exchanging portion can be compactly connected, and the structure can be simplified.

In the heat exchanger of the present invention, the flow rate adjusting valve is provided in the bypass flow passage.

Therefore, the structure can be simplified and the manufacturing cost can be reduced.

In the heat exchanger of the present invention, the flow rate adjusting valve is a three-way valve provided at the branching portion of the primary flow path and the bypass flow path.

Therefore, the flow rate of the primary fluid flowing through the bypass flow path can be adjusted with high accuracy.

According to the heat exchanger of the present invention, since the flow rate of the primary fluid flowing through the heat exchange unit located on the downstream side in the flow direction of the secondary fluid is adjusted according to the state of the primary fluid, heat exchange is properly performed The supercooling degree or the overheating of the primary fluid can be suppressed.

According to the heat exchanger of the present invention, it is possible to provide a plurality of heat exchanging units for performing heat exchange between the primary fluid and the secondary fluid, and a bypass flow path for bypassing at least one of the plurality of heat exchanging units, Since the flow rate of the primary fluid flowing through the bypass flow path is adjusted in accordance with the temperature of the primary fluid at the outlet side of the heat exchanging section, the temperature of the primary fluid can be adjusted with high accuracy and the overheat or supercooling .

1 is a schematic structural view showing a gas turbine.
2 is a schematic view showing a heat exchanger.
3 is a schematic configuration diagram of the heat exchanger of the first embodiment.
4 is a schematic configuration diagram of a heat exchanger showing a modification of the first embodiment.
5 is a schematic view showing the heat exchanger operation of the first embodiment.
Fig. 6 is a schematic configuration diagram of the heat exchanger of the second embodiment. Fig.
7 is a schematic configuration diagram of a heat exchanger showing a modification of the second embodiment.
8 is a schematic configuration diagram of the heat exchanger of the third embodiment.
9 is a schematic configuration diagram of a heat exchanger showing a modification of the third embodiment.
10 is a schematic configuration diagram of the heat exchanger of the fourth embodiment.
11 is a schematic configuration diagram showing a gas turbine.
12 is a schematic view showing a heat exchanger.
13 is a schematic configuration diagram of the heat exchanger of the fifth embodiment.
14 is a schematic configuration diagram of a heat exchanger showing a modification of the fifth embodiment.
15 is a schematic diagram showing a conventional heat exchanger operation.
16 is a schematic view showing the heat exchanger operation of the fifth embodiment.
17 is a schematic configuration diagram of a heat exchanger according to the sixth embodiment.
18 is a schematic configuration diagram of a heat exchanger showing a modification of the sixth embodiment.
19 is a schematic configuration diagram of a heat exchanger of a seventh embodiment.

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, a preferred embodiment of a heat exchanger according to the present invention will be described in detail with reference to the accompanying drawings. It should be noted that the present invention is not limited by these embodiments, and when there are a plurality of embodiments, the embodiments may be combined.

[First Embodiment]

1 is a schematic structural view showing a gas turbine.

1, the gas turbine 10 is constituted by a compressor 11, a combustor 12, and a turbine 13. As shown in Fig. The gas turbine 10 is connected to a generator 14 and is capable of generating electricity.

The compressor (11) and the turbine (13) are integrally rotatably connected by a rotary shaft (21). The compressor (11) compresses the air (A) introduced from the air introduction line (22). The combustor 12 mixes the compressed air A1 supplied from the compressor 11 through the compressed air supply line 23 and the fuel gas L supplied from the fuel gas supply line 24 and burns them. The turbine 13 is rotated by the combustion gas G supplied from the combustor 12 through the combustion gas supply line 25.

The gas turbine 10 is configured to perform the heat exchange between the compressed air A2 as a part of the compressed air A1 compressed by the compressor 11 and the cooling air AC introduced from the outside and the fuel gas L, The heat exchanger 26 is provided. The heat exchanger 26 is provided at a position where the fuel gas supply line 24, the compressed air branch line 27 for supplying the compressed air A2 and the cooling air line 28 are gathered. The heat exchanger 26 heats the compressed air A2 by the cooling air AC and also heats the fuel gas L by the heated air AH whose temperature has risen. The cooled compressed air (A2) is supplied through a vehicle compartment of the turbine (13) and cools the blade and the like as cooling air.

The generator 14 is integrally rotatably connected to the compressor 11 by a coaxial rotary shaft 29 and is capable of generating electricity by rotating the turbine 13. [

2 is a schematic view showing a heat exchanger.

As shown in Fig. 2, the heat exchanger 26 is provided with two heat exchangers 32, 33 in the housing 31. As shown in Fig. The housing 31 is provided with an air inlet 34 at a lower portion thereof and an introduction fan 35 at an air inlet 34 and an air outlet 36 at an upper portion thereof.

The first heat exchanger 32 performs heat exchange between the compressed air A2 compressed by the compressor 11 and the cooling air AC introduced from the outside. That is, the first heat exchanger 32 cools the compressed air (A2) by the cooling air (AC) at room temperature. The second heat exchanger 33 cools the compressed air (A2) and performs heat exchange between the heated air (AH) and the fuel gas (L), which have become hot. That is, the cooling air (AC) becomes hot air (AH) by cooling the compressed air (A2), and the second heat exchanger (33) Heat it.

Hereinafter, the first heat exchanger as the heat exchanger of the first embodiment will be described. 3 is a schematic configuration diagram of the heat exchanger of the first embodiment.

As shown in Fig. 3, the first heat exchanger 32 of the first embodiment includes a compressed air branch line 27 as a primary flow path, a cooling air line 28 as a secondary flow path, The first heat exchanging unit 41 and the second heat exchanging unit 42 and the flow rate adjusting valve 43 are provided. Here, the primary fluid is compressed air (A2), and the secondary fluid is cooling air (AC).

The compressed air branch line 27 and the cooling air line 28 are arranged to be substantially orthogonal. The first heat exchanging part 41 and the second heat exchanging part 42 are arranged in the flow direction of the compressed air A2 and the second heat exchanging part 42 is provided to the first heat exchanging part 41 And is disposed on the downstream side in the flow direction of the compressed air (A2).

The first heat exchanging unit 41 and the second heat exchanging unit 42 are provided in the compressed air branch line 27 and perform heat exchange between the compressed air A2 and the cooling air AC, And are arranged in parallel with each other. The first heat exchanging part 41 is provided with an inlet header 51 at one end and the second inlet port header 52 is provided at one end of the second heat exchanging part 42. The first heat exchanging portion 41 and the second heat exchanging portion 42 are provided at the other end with a common outlet header 53. The first branch passage 54a and the second branch passage 54b are branched as the primary fluid supply passage and the first branch passage 54a is connected to the first heat exchange section 41 And the second branch passage 54b is connected to the nozzle 56 of the inlet header 52 of the second heat exchanger 42. The second branch passage 54b is connected to the nozzle 55 of the inlet header 51 in the second heat exchanger 42, A collecting flow path 54c as a primary fluid discharge path is provided in the compressed air branch line 27 and is connected to the nozzle 57 of the outlet header 53. [

The flow rate adjusting valve 43 is provided in the second branch passage 54b to adjust the flow rate of the compressed air A2 flowing through the second branch passage 54b.

The first heat exchanger 32 normally operates by setting the opening of the flow rate regulating valve 43 at 100% (full opening). The compressed air A2 supplied from the compressed air branch line 27 to the first heat exchanging unit 41 and the second heat exchanging unit 42 through the first branch passage 54a and the second branch passage 54b, Are equal to each other. The compressed air (A2) is cooled and discharged by heat exchange with the cooling air (AC) when flowing through the first heat exchanger (41) and the second heat exchanger (42).

When the flow rate of the compressed air (A2) flowing through the compressed air branch line (27) decreases, the opening degree of the flow regulating valve (43) is reduced. As a result, the flow rate of the compressed air (A2) supplied to the second heat exchanger (42) through the second branch passage (54b) is reduced while the flow rate of the compressed air (A2) supplied to the first heat exchanger The flow rate of the compressed air A2 to be supplied is relatively increased. When the flow rate of the compressed air (A2) in the first heat exchanging part (41) increases, when the cooling air (AC) and the compressed air (A2) exchange heat, the first heat exchanger The heat load of the heat exchanging part 41 becomes high, and the supercooling degree is suppressed.

Further, the configuration of the first heat exchanger 32 is not limited to that described above. 4 is a schematic configuration diagram of a heat exchanger showing a modification of the first embodiment.

4, the first heat exchanger 32A showing a modified example of the first embodiment includes a compressed air branch line 27, a cooling air line 28, a first heat exchanger 41, A second heat exchanger 42, and a flow rate adjusting valve 43. [

The first heat exchanging part (41) and the second heat exchanging part (42) are provided with a common inlet header (61) at one end. The first heat exchanging unit 41 is provided with an outlet header 62 at the other end and the second heat exchanging unit 42 is provided with an outlet header 63 at the other end thereof. The compressed air branch line 27 is provided with a supply flow path 64a as a primary fluid supply path and connected to the nozzle 65 of the inlet header 61. [ The compressed air branch line 27 is branched into the first branch passage 64b and the second branch passage 64c as the primary fluid discharge passage and the first branch passage 64a is connected to the first heat exchange section 41 And the second branch passage 64c is connected to the nozzle 67 of the outlet header 63 of the second heat exchanger 42. The second branch passage 64c is connected to the nozzle 67 of the outlet header 63 of the second heat exchanger 42,

The flow rate adjusting valve 43 is provided in the second branch passage 64c and adjusts the flow rate of the compressed air A2 flowing through the second branch passage 64c.

The first heat exchanger 32A normally operates by setting the opening of the flow rate regulating valve 43 to 100% (full opening). That is, the flow rates of the compressed air (A2) supplied from the compressed air branch line (27) to the first heat exchanger (41) and the second heat exchanger (42) through the supply passage (64a) are equal. The compressed air (A2) is cooled and discharged by heat exchange with the cooling air (AC) when flowing through the first heat exchanger (41) and the second heat exchanger (42).

When the flow rate of the compressed air (A2) flowing through the compressed air branch line (27) decreases, the opening degree of the flow regulating valve (43) is reduced. Thereby, the flow rate of the compressed air A2 discharged from the second heat exchanger 42 through the second branch passage 64c is reduced, while the flow rate of the compressed air A2 discharged from the first heat exchanger 41 via the first branch passage 64b The flow rate of the compressed air A2 to be discharged is relatively increased. When the flow rate of the compressed air (A2) in the first heat exchanging part (41) increases, when the cooling air (AC) and the compressed air (A2) exchange heat, the first heat exchanger The heat load of the heat exchanging part 41 becomes high, and the supercooling degree is suppressed.

Here, the operation of the first heat exchanger 32, 32A will be described. 5 is a schematic view showing the heat exchanger operation of the first embodiment.

The flow rates of the compressed air A2 supplied to the respective heat exchanging sections 41 and 42 from the inlet header 51 and 52 are equal to each other when the opening degree of the flow rate adjusting valve 43 is fully opened as shown in Fig. . As a result, when the cooling air (AC) acts on each of the heat exchanging portions 41 and 42 at this time, the cooling air (AC) at the inlet portion (C1) , The temperature rises by cooling the compressed air (A2), and the temperature Tb is discharged at the outlet (C3). As a result, the compressed air (A2) is cooled to a predetermined temperature.

On the other hand, when the flow rate of the compressed air A2 flowing through the compressed air branch line 27 decreases, the opening degree of the flow regulating valve 43 is reduced (for example, The flow rate of the compressed air (A2) supplied from the inlet header (52) to the second heat exchanger (42) increases with respect to the flow rate of the compressed air (A2) supplied to the heat exchanger (41). As a result, when the cooling air (AC) acts on the heat exchanging portions 41 and 42 at this time, the cooling air (AC) at the inlet portion (C1) The temperature rises by cooling the compressed air A2 and the temperature Tb is discharged between the first heat exchanging unit 41 and the second heat exchanging unit 42 at a temperature C2. As a result, the compressed air (A2) is cooled to a predetermined temperature.

The total amount of the compressed air A2 flowing through the compressed air branch line 27 is supplied to the first heat exchanging unit 41 and the first heat exchanging unit 41 is supplied with the flow amount adjusting valve 43. Therefore, The flow rate of the compressed air A2 flowing per unit time increases, and the flow rate of the compressed air A2 increases. As a result, the compressed air A2 absorbs more heat in the cooling air (AC) while passing through the first heat exchanging portion 41, and the first heat exchanging portion 41 and the second heat exchanging portion 42 The temperature Tb is obtained. As a result, the supercooling degree in the first heat exchanging portion (41) is suppressed. On the other hand, the compressed air (A2) does not flow through the second heat exchanging portion (42), but the supercooling degree here is also suppressed because the compressed air (A2) whose temperature rises acts.

As described above, in the heat exchanger of the first embodiment, the cooling air line 28 as the primary flow path through which the cooling air (AC) as the primary fluid flows and the compression as the secondary flow path through which the compressed air (A2) A first heat exchanging part 41 as a plurality of heat exchanging parts that perform heat exchange in the cooling air (AC) and compressed air (A2) and are juxtaposed in the flow direction of the cooling air (AC) And a flow rate of the compressed air (A2) flowing through the second heat exchanging part (42) located on the downstream side in the flow direction of the cooling air (AC) in the plurality of heat exchanging parts (41, 42) The flow rate control valve 43 is provided.

Therefore, the compressed air (A2) flowing through the plurality of heat exchanging units (41, 42) is cooled by heat exchange with the cooling air (AC). When the flow rate of the compressed air A2 flowing through the plurality of heat exchanging units 41 and 42 fluctuates, the opening degree of the flow rate adjusting valve 43 is adjusted in accordance with the flow rate of the compressed air A2, The flow rate of the compressed air (A2) flowing through the second heat exchanger (42) located on the downstream side in the flow direction of the cooling air (AC) As a result, the influence of the cooling air (AC) on the heat exchanging portions (41, 42) is small, and the increase in temperature and the decrease in temperature are suppressed. As a result, even if the flow rate of the compressed air (A2) fluctuates, the supercooling of the compressed air (A2) can be suppressed by properly performing heat exchange.

[Second Embodiment]

Fig. 6 is a schematic structural view of the heat exchanger of the second embodiment, and Fig. 7 is a schematic structural view of a heat exchanger showing a modification of the second embodiment. Members having the same functions as those of the above-described embodiment are denoted by the same reference numerals, and a detailed description thereof will be omitted.

6, the first heat exchanger 32B includes a compressed air branch line 27, a cooling air line 28, a first heat exchanging unit 41, A first temperature sensor 71 and a second temperature sensor 72 as status detection sensors, and a control unit 73. The first temperature sensor 71, the second temperature sensor 72,

The first temperature sensor 71 and the second temperature sensor 72 are provided in the outlet header 53. The first temperature sensor 71 detects the temperature (state) of the compressed air A2 discharged from the first heat exchanger 41 to the outlet header 53 and outputs the detected temperature to the controller 73. The second temperature sensor 72 detects the temperature (state) of the compressed air A2 discharged from the second heat exchanger 42 to the outlet header 53 and outputs the detected temperature to the controller 73. The control unit 73 adjusts the opening degree of the flow rate adjusting valve 43 in accordance with the temperature of the compressed air A2 detected by the first temperature sensor 71 and the second temperature sensor 72. [ That is, when the temperature difference of the compressed air (A2) detected by each of the temperature sensors (71, 72) becomes larger than a preset predetermined temperature difference, the control unit (73) decreases the opening degree of the flow rate adjusting valve (43). The opening degree of the flow rate adjusting valve 43 is adjusted so that the temperature of the compressed air A2 detected by the first temperature sensor 71 and the second temperature sensor becomes a predetermined temperature difference.

The first heat exchanger 32B normally operates by setting the opening of the flow rate regulating valve 43 at 100% (full opening). The compressed air A2 supplied from the compressed air branch line 27 to the first heat exchanging unit 41 and the second heat exchanging unit 42 through the first branch passage 54a and the second branch passage 54b, Are equal to each other. The compressed air (A2) is cooled and discharged by heat exchange with the cooling air (AC) when flowing through the first heat exchanger (41) and the second heat exchanger (42).

When the deviation between the temperature of the compressed air A2 discharged from the first heat exchanging unit 41 and the temperature of the compressed air A2 discharged from the second heat exchanging unit 42 is greater than the predetermined temperature difference, It is judged that the flow rate of the compressed air (A2) flowing through the compressed air branch line (27) is reduced. At this time, the controller 73 reduces the opening degree of the flow rate adjusting valve 43 and adjusts the flow rate so that the temperature of the compressed air A2 detected by the first temperature sensor 71 and the second temperature sensor becomes a predetermined temperature difference The opening degree of the valve 43 is adjusted. As a result, the flow rate of the compressed air (A2) supplied to the second heat exchanger (42) through the second branch passage (54b) is reduced while the flow rate of the compressed air (A2) supplied to the first heat exchanger The flow rate of the compressed air A2 to be supplied is relatively increased. When the flow rate of the compressed air (A2) in the first heat exchanging part (41) increases, when the cooling air (AC) and the compressed air (A2) exchange heat, the first heat exchanger The heat load of the heat exchanging part 41 becomes high, and the supercooling degree is suppressed.

Further, the configuration of the first heat exchanger 32 is not limited to that described above. 7, the first temperature sensor 71 of the first heat exchanger 32C is connected to the first branch passage 64b connected to the outlet header 62 of the first heat exchanger 41 And detects the temperature of the compressed air A2 discharged from the first heat exchanging unit 41 and outputs the detected temperature to the control unit 73. [ The second temperature sensor 72 is provided in the second branch passage 64c connected to the outlet header 63 of the second heat exchanger 42 and is connected to the compressed air discharged from the second heat exchanger 42 A2, and outputs the detected temperature to the control unit 73. [ The control unit 73 adjusts the opening degree of the flow rate adjusting valve 43 in accordance with the temperature of the compressed air A2 detected by the first temperature sensor 71 and the second temperature sensor 72. [ That is, when the temperature difference of the compressed air (A2) detected by each of the temperature sensors (71, 72) becomes larger than a preset predetermined temperature difference, the control unit (73) decreases the opening degree of the flow rate adjusting valve (43). The opening degree of the flow rate adjusting valve 43 is adjusted so that the temperature of the compressed air A2 detected by the first temperature sensor 71 and the second temperature sensor becomes a predetermined temperature difference.

Thus, in the heat exchanger of the second embodiment, the cooling air line 28 through which the cooling air (AC) flows, the compressed air branch line 27 through which the compressed air A2 flows, the cooling air (AC) A plurality of heat exchanging portions 41 and 42 for performing heat exchange in the cooling air flow A2 and lined up in the flow direction of the cooling air AC and a plurality of heat exchanging portions 41 and 42 for flowing the cooling air AC in the plurality of heat exchanging portions 41 and 42, A flow rate regulating valve 43 for regulating the flow rate of the compressed air A2 flowing through the second heat exchanging portion 42 located on the downstream side of the direction of the flow of the compressed air A2, And a control section 73 for adjusting the opening degree of the flow rate adjusting valve 43 in accordance with the temperature of the compressed air A2 detected by the temperature sensors 71 and 72.

Therefore, the compressed air (A2) flowing through the plurality of heat exchanging units (41, 42) is cooled by heat exchange with the cooling air (AC). When the temperature of the compressed air A2 flowing through the plurality of heat exchanging units 41 and 42 fluctuates, the opening degree of the flow regulating valve 43 is adjusted in accordance with the temperature of the compressed air A2, The flow rate of the compressed air (A2) flowing through the second heat exchanger (42) located on the downstream side in the flow direction of the cooling air (AC) As a result, the influence of the cooling air (AC) on the heat exchanging portions (41, 42) is small, and the increase in temperature and the decrease in temperature are suppressed. As a result, even if the flow rate of the compressed air (A2) fluctuates, the supercooling of the compressed air (A2) can be suppressed by properly performing heat exchange.

In the heat exchanger of the second embodiment, when the temperature difference of the compressed air (A2) on the outlet side of the plurality of heat exchanging sections (41, 42) becomes larger than a preset predetermined temperature difference, the control section (73) The opening degree of the flow rate regulating valve 43 is adjusted so that the temperature difference of the compressed air A2 becomes equal to the predetermined temperature difference. When the opening degree of the flow regulating valve 43 is reduced, the flow rate of the compressed air (A2) flowing through the second heat exchanging part (42) located on the downstream side in the flow direction of the cooling air (AC) decreases. Therefore, the influence of the compressed air (A2) on the first heat exchanging part (41) located on the upstream side in the flow direction of the cooling air (AC) is reduced, and the supercooling degree of the compressed air (A2) can be suppressed.

By suppressing the supercooling degree of the compressed air A2, a large heat load does not act on the constituent members of the heat exchangers 41 and 42 (for example, heat transfer tubes and the like), and the increase of the plate thickness is not required An increase in manufacturing cost can be suppressed. In addition, since the supercooling degree of the compressed air (A2) is suppressed, generation of drain in the second heat exchanger (42) is suppressed, and generation of rust by the drain can be prevented.

In the first heat exchanger 32B, a flow rate regulating valve 43 is provided in the second branch passage 54b connected to the inlet header 52 of the second heat exchanger 42. In the first heat exchanger 32C, a flow rate regulating valve 43 is provided in the second branch passage 64c connected to the outlet header 63 of the second heat exchanger 42. Therefore, the flow rate of the compressed air (A2) flowing through the plurality of heat exchanging sections (41, 42) can be adjusted with high accuracy.

[Third embodiment]

FIG. 8 is a schematic structural view of a heat exchanger of a third embodiment, and FIG. 9 is a schematic structural view of a heat exchanger showing a modification of the third embodiment. Members having the same functions as those of the above-described embodiment are denoted by the same reference numerals, and a detailed description thereof will be omitted.

8, the first heat exchanger 32D includes a compressed air branch line 27, a cooling air line 28, a first heat exchanging unit 41, A two-heat exchanging unit 42, a flow rate adjusting valve 43, a flow rate sensor 81 as a state detecting sensor, and a control unit 73.

The flow sensor 81 is provided in the compressed air branch line 27. The flow rate sensor 81 detects the flow rate (state) of the compressed air A2 flowing through the compressed air branch line 27 and outputs it to the control section 73. [ The control unit 73 adjusts the opening degree of the flow rate adjusting valve 43 in accordance with the flow rate of the compressed air A2 detected by the flow rate sensor 81. [ That is, when the flow rate of the compressed air (A2) detected by the flow rate sensor (81) is smaller than a predetermined flow rate set in advance, the controller (73) reduces the opening degree of the flow rate adjusting valve (43).

The first heat exchanger 32 normally operates by setting the opening of the flow rate regulating valve 43 at 100% (full opening). The compressed air A2 supplied from the compressed air branch line 27 to the first heat exchanging unit 41 and the second heat exchanging unit 42 through the first branch passage 54a and the second branch passage 54b, Are equal to each other. The compressed air (A2) is cooled and discharged by heat exchange with the cooling air (AC) when flowing through the first heat exchanger (41) and the second heat exchanger (42).

When the flow rate of the compressed air (A2) supplied to the first heat exchanging section (41) becomes smaller than the predetermined flow rate, the control section (73) reduces the opening degree of the flow rate adjusting valve (43). As a result, the flow rate of the compressed air (A2) supplied to the second heat exchanger (42) through the second branch passage (54b) is reduced while the flow rate of the compressed air (A2) supplied to the first heat exchanger The flow rate of the compressed air A2 to be supplied is relatively increased. When the flow rate of the compressed air (A2) in the first heat exchanging part (41) increases, when the cooling air (AC) and the compressed air (A2) exchange heat, the first heat exchanger The heat load of the heat exchanging part 41 becomes high, and the supercooling degree is suppressed.

The configuration of the first heat exchanger 32D is not limited to that described above. 9, in the first heat exchanger 32E, the flow rate sensor 81 is provided in the compressed air branch line 27, and the compressed air A2 supplied to the respective heat exchanging units 41, And outputs the detected flow rate to the control unit 73. The control unit 73 adjusts the opening degree of the flow rate adjusting valve 43 in accordance with the temperature of the compressed air A2 detected by the flow rate sensor 81. [ That is, when the flow rate of the compressed air (A2) detected by the flow rate sensor (81) is smaller than a predetermined flow rate set in advance, the controller (73) reduces the opening degree of the flow rate adjusting valve (43).

As described above, in the heat exchanger according to the third embodiment, the flow rate sensor 81 for detecting the flow rate of the compressed air A2 and the flow rate detecting unit 81 for detecting the flow rate of the compressed air A2 detected by the flow rate sensor 81 are smaller A control section 73 for reducing the opening degree of the flow control valve 43 is provided.

Therefore, when the flow rate of the compressed air A2 flowing through the plurality of heat exchanging units 41 and 42 is smaller than the predetermined flow rate, the opening degree of the flow rate adjusting valve 43 is reduced, The flow rate of the secondary fluid decreases. As a result, the influence of the cooling air (AC) on the first heat exchanging part (41) is reduced, and the supercooling degree of the compressed air (A2) can be suppressed.

In the third embodiment, the flow rate sensor 81 is provided in the compressed air branch line 27 to detect the flow rate (state) of the compressed air A2 flowing through the compressed air branch line 27. However, The present invention is not limited to this configuration. For example, a pressure sensor may be provided in the compressed air branch line 27 to detect the pressure (state) of the compressed air A2 flowing through the compressed air branch line 27. The control unit 73 reduces the opening degree of the flow rate adjusting valve 43 when the pressure of the compressed air A2 flowing through the compressed air branch line 27 detected by the pressure sensor becomes larger than a preset pressure. Even in this case, the supercooling degree of the compressed air (A2) can be suppressed.

[Fourth Embodiment]

10 is a schematic configuration diagram of the heat exchanger of the fourth embodiment. Members having the same functions as those of the above-described embodiment are denoted by the same reference numerals, and a detailed description thereof will be omitted.

10, the first heat exchanger 90 includes a compressed air branch line 27, a cooling air line 28, and four heat exchanging units 91, 92, and 93 A flow rate sensor (state detection sensor) 99, and a control unit 100. The flow rate control valves 95, 96, 97,

The first heat exchanging part 91 is provided with an inlet header 101 at one end thereof and the second heat exchanging part 92 is provided with an inlet header 102 at one end thereof and a third heat exchanging part 93 The inlet header 103 is provided at one end and the inlet header 104 is provided at one end of the fourth heat exchanging unit 94. The heat exchangers 91, 92, 93, An outlet header 105 is provided. The compressed air branch line 27 is branched into the first branch passage 105a and the second branch passage 105b and the third branch passage 105c and the fourth branch passage 105d as the primary fluid supply passage, 102, 103, and 104, respectively. The compressed air branch line 27 is provided with a collecting flow path 105e as a primary fluid discharge path and connected to the outlet header 105. [

The flow rate adjusting valves 95, 96, 97, and 98 are provided in the branching flow paths 105a, 105b, 105c, and 105d, and compressed air A2 flowing through the second branching flow paths 105a, 105b, 105c, Of the flow rate. The flow rate sensor 99 is provided in the compressed air branch line 27 and detects the flow rate (state) of the compressed air A2 flowing through the compressed air branch line 27 and outputs the detected flow rate to the control unit 100. The control unit 100 adjusts the opening degree of the flow rate adjusting valves 95, 96, 97, and 98 in accordance with the flow rate of the compressed air A2 detected by the flow rate sensor 99. [ That is, when the flow rate of the compressed air (A2) detected by the flow rate sensor 99 is smaller than a predetermined flow rate set in advance, the control section 100 reduces the opening degree of the flow rate adjustment valves 95, 96, 97, and 98 .

When the flow rate of the compressed air A2 supplied to the first heat exchanger 91 becomes smaller than the predetermined flow rate, the control unit 100 adjusts the opening degree of the flow rate adjusting valves 95, 96, 97, 98, (91, 92, 93, 94) on the downstream side in the flow direction of the refrigerant (AC) is adjusted so that the flow rate becomes smaller. Therefore, when the cooling air (AC) and the compressed air (A2) exchange heat, the heat load becomes higher toward the first heat exchanging part (91), and the supercooling degree is suppressed.

Although the flow sensor 99 is used as the state detector in the fourth embodiment, it may be a temperature sensor or a pressure sensor.

As described above, in the heat exchanger of the fourth embodiment, a plurality of flow control valves 95, 96, 97 and 98 are provided corresponding to the plurality of heat exchanging units 91, 92, 93 and 94, The flow rate of the compressed air A2 flowing through the respective heat exchanging units 91, 92, 93, and 94 is adjusted according to the flow rate of the compressed air A2 detected by the flow rate sensor 99. [

Therefore, by adjusting the flow rate of the compressed air A2 flowing through the plurality of heat exchanging units 91, 92, 93, and 94, the influence of the cooling air AC on the respective heat exchanging units 91, 92, 93, So that the supercooling degree of the compressed air A2 can be suppressed with high accuracy.

In the above-described embodiment, the heat exchanging portions 41, 42, 91, 92, 93, and 94 are formed by straight heat transfer tubes, but they may be formed by U-shaped heat transfer tubes.

In the above-described embodiment, the heat exchanger of the present invention is applied to the gas turbine 10 and the compressed air (secondary fluid) A2 is heated by the cooling air (primary fluid) The present invention is not limited to this configuration. That is, the heat exchanger of the present invention can be applied to a separate part of the gas turbine 10 or to a field other than the gas turbine 10 (for example, a boiler).

In the above-described embodiment, the heat exchanger is used to cool the secondary fluid by the primary fluid. Alternatively, the heat exchanger may be a heat exchanger that heats the secondary fluid by the primary fluid. In this case, have.

[Fifth Embodiment]

11 is a schematic configuration diagram showing a gas turbine.

In the fifth embodiment, as shown in Fig. 11, the gas turbine 10 is constituted by a compressor 11, a combustor 12, and a turbine 13. As shown in Fig. The gas turbine 10 is connected to a generator 14 and is capable of generating electricity.

The compressor (11) and the turbine (13) are integrally rotatably connected by a rotating shaft (121). The compressor (11) compresses the air (A) introduced from the air introduction line (122). The combustor 12 mixes the compressed air A1 supplied from the compressor 11 through the compressed air supply line 123 and the fuel gas L supplied from the fuel gas supply line 124 and burns them. The turbine 13 is rotated by the combustion gas G supplied from the combustor 12 through the combustion gas supply line 125.

The gas turbine 10 is configured to perform the heat exchange between the compressed air A2 as a part of the compressed air A1 compressed by the compressor 11 and the cooling air AC introduced from the outside and the fuel gas L, The heat exchanger 126 is provided. The heat exchanger 126 is provided at a position where the fuel gas supply line 124, the compressed air branch line 127 for supplying the compressed air A2 and the cooling air line 128 are gathered. The heat exchanger 126 cools the compressed air A2 by the cooling air AC and heats the fuel gas L by the heated air AH whose temperature has risen. The compressed compressed air (A2) is supplied through the passenger compartment of the turbine (13) and cools the vanes and the like as cooling air.

The generator 14 is integrally rotatably connected to the compressor 11 by a coaxial rotary shaft 129 and is capable of generating electricity by rotating the turbine 13. [

12 is a schematic view showing a heat exchanger.

As shown in FIG. 12, in the heat exchanger 126, two heat exchangers 1312 and 133 are disposed in the housing 131. The housing 131 is provided with an air inlet 134 at a lower portion thereof and an introduction fan 135 at an air inlet 134 and an air outlet 136 at an upper portion thereof.

The first heat exchanger 132 performs heat exchange between the compressed air A2 compressed by the compressor 11 and the cooling air AC introduced from the outside. That is, the first heat exchanger 132 cools the compressed air (A2) by the cooling air (AC) at normal temperature. The second heat exchanger 133 cools the compressed air A2 and performs heat exchange between the heated air AH and the fuel gas L that has become hot. That is, the cooling air (AC) becomes hot air (AH) at high temperature by cooling the compressed air (A2), and the second heat exchanger (133) Heat it.

Hereinafter, the second heat exchanger as the heat exchanger of the fifth embodiment will be described. 13 is a schematic configuration diagram of the heat exchanger of the fifth embodiment.

13, the second heat exchanger 133 of the fifth embodiment includes a fuel gas supply line 124 as a primary flow path, a cooling air line 128 as a secondary flow path, A bypass flow path 143, a flow rate adjusting valve 144, a temperature sensor 145 (first heat exchanging part), a first heat exchanging part 141 as a heat exchanging part, a second heat exchanging part 142 as a heat exchanging part, And a control unit 146, Here, the primary fluid is fuel gas (L) and the secondary fluid is heated air (AH).

The first heat exchanging unit 141 and the second heat exchanging unit 142 are provided in the fuel gas supply line 124 and perform heat exchange with the fuel gas L and the heated air AH, And are arranged in parallel with each other. An inlet header 151 is provided at one end of the first heat exchanging unit 141 and an upstream end of the fuel gas supply line 124 is connected to the nozzle 152 of the inlet header 151. An outlet header 153 is provided at one end of the second heat exchanger 142 and a downstream end of the fuel gas supply line 124 is connected to the nozzle 154 of the outlet header 153. The other end of the first heat exchanging part 141 and the other end of the second heat exchanging part 142 are connected by a connection header 155. The first heat exchanging unit 141 and the second heat exchanging unit 142 are constituted by a group of heat transfer tubes composed of a plurality of heat transfer tubes and the ends of the heat transfer tubes are connected to the tube plates of the headers 151 and 1513155, .

The bypass passage 143 bypasses the first heat exchanger 141 among the first heat exchanger 141 and the second heat exchanger 142. The bypass passage 143 has its base end connected to the fuel gas supply line 124 on the upstream side of the first heat exchanging section 141 and its tip end connected to the nozzle 156 of the connection header 155. The flow rate adjusting valve 144 is provided in the bypass flow path 143 and adjusts the flow rate of the fuel gas L flowing through the bypass flow path 143.

The temperature sensor 145 is provided in the fuel gas supply line 124 at the outlet side of the second heat exchanger 142 and measures the temperature of the fuel gas L and outputs it to the control unit 146. The control unit 146 adjusts the opening degree of the flow rate adjusting valve 144 in accordance with the temperature of the fuel gas L measured by the temperature sensor 145. The control unit 146 adjusts the opening degree of the flow rate adjusting valve 144 such that the temperature of the fuel gas L falls within a predetermined temperature range set in advance. That is, when the temperature of the fuel gas L becomes higher than the predetermined temperature range, the control unit 146 increases the opening degree of the flow rate adjusting valve 144. When the temperature of the fuel gas L becomes lower than the predetermined temperature region, The opening degree of the flow rate adjusting valve 144 is reduced.

The second heat exchanger 133 normally operates with the flow rate regulating valve 144 opened to 0 (fully closed). The fuel gas L flows through the fuel gas supply line 124 and flows to the first heat exchanger 141 and flows to the second heat exchanger 142 through the connection header 155. The fuel gas L is heated and discharged by heat exchange with the heated air AH.

The control unit 146 adjusts the opening degree of the flow rate adjusting valve 144 so that the temperature of the fuel gas L falls within the predetermined temperature range. For example, when the temperature of the cooling air (AC) increases due to the rise in temperature, the temperature of the heated air (AH) also increases and the amount of heat exchange in the first heat exchanging unit 141 and the second heat exchanging unit 142 The amount of heat absorbed by the fuel gas L) increases and the temperature of the fuel gas L exceeds the predetermined temperature range. At this time, when the temperature of the fuel gas L becomes higher than the predetermined temperature range, the control unit 146 increases the opening degree of the flow rate adjusting valve 144. [ A portion of the fuel gas L flows from the fuel gas supply line 124 to the bypass flow path 143 and flows from the connection header 155 to the second heat exchange portion 142 . That is, a part of the fuel gas L bypasses the first heat exchanging unit 141 and is directly supplied to the second heat exchanging unit 142. Because of this, the low-temperature fuel gas L bypassing the first heat exchanger 141 is mixed with the high-temperature fuel gas L heated by the first heat exchanger 141 in the connection header 155 , The temperature of the fuel gas (L) flowing through the second heat exchanger (142) is lowered. As a result, the temperature of the fuel gas L discharged from the second heat exchanging portion 142 is lowered and falls within the predetermined temperature range.

The configuration of the second heat exchanger 133 is not limited to that described above. 14 is a schematic configuration diagram of a heat exchanger showing a modification of the fifth embodiment.

14, the second heat exchanger 133A includes a fuel gas supply line 124, a cooling air line 128, a first heat exchanger 141 and a second heat exchanger 142, A bypass flow passage 143, a flow rate adjusting valve 147, a temperature sensor 145, and a control section 146. [

The bypass passage 143 bypasses the first heat exchanger 141 and has a proximal end connected to the fuel gas supply line 124 on the upstream side of the first heat exchanger 141, 155, respectively. The flow regulating valve 147 is a three-way valve provided at the branching portion of the fuel gas supply line 124 and the bypass flow path 143. The three-way valve 147 controls the opening degree of the first heat exchanging unit 141 and the opening degree of the bypass flow passage with respect to the fuel gas supply line 124. The bypass flow passage 143, And adjusts the flow rate of the fuel gas L flowing in the fuel gas flow direction.

Here, the operation of the second heat exchangers 133 and 133A will be described in comparison with a conventional heat exchanger. FIG. 15 is a schematic view showing a conventional heat exchanger operation, and FIG. 16 is a schematic view showing a heat exchanger operation of the fifth embodiment.

As shown in Fig. 15, the conventional heat exchanger 001 is provided in the fuel gas supply passage 002, and has a bypass flow passage 003 bypassing the heat exchanger 001 with respect to the fuel gas supply passage 002, And a flow control valve 004 is provided in the bypass flow passage 003. [ When the flow control valve (004) is opened by a predetermined degree, the fuel gas flows from the fuel gas supply passage (002) to the heat exchanger (001) at the position t1 and heated. On the other hand, a part of the fuel gas flowing in the bypass flow path 003 is not heated and the temperature does not rise. At the position t2, the fuel gas is discharged from the heat exchanger 001, and at the position t3, the high-temperature fuel gas and the low-temperature fuel gas through the bypass passage 003 are mixed, . Conventionally, since the flow rate of the fuel gas flowing through the heat exchanger 001 decreases, the heat load of the fuel gas increases and exceeds the upper limit temperature ta at the outlet of the heat exchanger 001.

16, the second heat exchanger 133 of this embodiment has the first heat exchanger 141 and the second heat exchanger 142, and the bypass flow path 143 is connected to the first heat exchanger 141 (141) and the second heat exchanger (142). As a result, when the flow regulating valve 144 is opened by a predetermined degree, the fuel gas flows from the fuel gas supply passage 143 to the first heat exchanger 141 at the position t1, and is heated to raise the temperature. On the other hand, a part of the fuel gas flowing in the bypass flow path 143 is not heated and the temperature does not rise. At the position t2, the heated fuel gas flows from the first heat exchanging unit 141 to the second heat exchanging unit 142, and the low-temperature fuel gas passing through the bypass flow path 143 flows into the second heat exchanging unit 142, (142). Here, by mixing the high-temperature fuel gas and the low-temperature fuel gas, the temperature is lowered. Thereafter, all of the fuel gas is heated by the second heat exchanger 142, so that the temperature rises to a predetermined temperature at the position t3. In the present embodiment, by returning the low-temperature fuel gas to the connection portions of the heat exchange units 141 and 142, the upper limit temperature ta is prevented from exceeding the outlet of the second heat exchanger 133.

As described above, in the heat exchanger of the fifth embodiment, the fuel gas supply line 124 through which the fuel gas L as the primary fluid flows, the cooling air line 128 through which the heated air AH as the secondary fluid flows, A first heat exchanging unit 141 and a second heat exchanging unit 142 for performing heat exchange in the fuel gas L and the heated air AH, a bypass flow path 143 bypassing the first heat exchanging unit 141, A flow rate regulating valve 144 for regulating the flow rate of the fuel gas L flowing through the bypass flow path 143 and a temperature sensor 144 for measuring the temperature of the fuel gas L at the outlet side of the heat exchanging part 142, And a control unit 146 that adjusts the opening degree of the flow rate adjusting valve 144 in accordance with the temperature of the fuel gas L detected by the temperature sensor 145 is provided.

Therefore, the opening degree of the flow rate adjusting valve 144 is adjusted in accordance with the temperature of the fuel gas L at the outlet side of the second heat exchanging portion 142, so that the amount of the fuel gas L that bypasses the first heat exchanging portion 141 (L) is adjusted. At this time, since the fuel gas L bypasses only a part of the first heat exchanging unit 141, the fuel gas L passing through the first heat exchanging unit 141, even if the flow rate temporarily decreases, Is suppressed. As a result, in the heat exchanger of the first embodiment, the temperature of the fuel gas L can be adjusted with high accuracy, and the overheat of the fuel gas L can be suppressed.

By suppressing the overheating of the fuel gas L, a large heat load does not act on the structural members of the heat exchanger 142 (for example, a heat transfer tube or the like), and the increase of the plate thickness is not required, Can be suppressed. Further, since the overheat of the fuel gas L is suppressed, no by-product (for example, iron sulfide: FeS) is generated and the adverse effect of the by-product on the heat exchangers 133 and 133A can do.

The first heat exchanger 141 and the second heat exchanger 142 are connected in series and one end of the bypass passage 143 is connected to the inlet side of the first heat exchanger 141 in the heat exchanger of the fifth embodiment And the other end is connected to the connection header 155 of the first heat exchanging unit 141 and the second heat exchanging unit 142. The fuel gas L flowing through the bypass flow path 143 is supplied to the connection header 155 and flows through the fuel gas L heated by the first heat exchange section 141 and the bypass flow path 143 The low temperature fuel gas L is mixed and the high temperature of the fuel gas L in the second heat exchanger 142 is suppressed and the overheating of the fuel gas L can be suppressed.

In the heat exchanger of the fifth embodiment, the first heat exchanging unit 141 and the second heat exchanging unit 142 are arranged in parallel, and the inlet header 151 of the first heat exchanging unit 141 and the second heat exchanging unit And the connection header 155 is disposed at the other end. Therefore, by arranging the first heat exchanging unit 141 and the second heat exchanging unit 142 in parallel to efficiently circulate the fuel gas L, the apparatus can be downsized.

In the heat exchanger of the fifth embodiment, the downstream end of the first heat exchanging unit 141 and the upstream end of the second heat exchanging unit 142 are connected by the connection header 155. Therefore, by making the connection portion the connection header 155, the first heat exchange portion 141 and the second heat exchange portion 142 can be easily connected, and the fuel gas L that has passed through the heat exchange portion 141 The fuel gas L that has passed through the bypass passage 143 can be appropriately mixed.

In the heat exchanger of the fifth embodiment, the flow rate regulating valve 144 is provided in the bypass flow path 143. Therefore, the structure can be simplified and the manufacturing cost can be reduced.

In the heat exchanger of the fifth embodiment, the flow rate regulating valve 147 is a three-way valve provided in the branching portion of the fuel gas supply line 124 and the bypass flow path 143. Therefore, the flow rate of the fuel gas L flowing into the bypass flow path 143 can be adjusted with high accuracy.

[Sixth Embodiment]

FIG. 17 is a schematic structural view of a heat exchanger of a sixth embodiment, and FIG. 18 is a schematic structural view of a heat exchanger showing a modification of the sixth embodiment. Members having the same functions as those of the above-described embodiment are denoted by the same reference numerals, and a detailed description thereof will be omitted.

17, the second heat exchanger 133B includes a fuel gas supply line 124, a cooling air line 128, a first heat exchanging unit 141, and a second heat exchanging unit 141. In the sixth embodiment, A heat exchanging portion 142, a bypass flow passage 143, a flow rate adjusting valve 144, a temperature sensor 145, and a control portion 146.

The first heat exchanging unit 141 and the second heat exchanging unit 142 are provided in the fuel gas supply line 124 and perform heat exchange with the fuel gas L and the heated air AH, And are arranged in parallel with each other. An inlet header 151 is provided at one end of the first heat exchanging unit 141 and an upstream end of the fuel gas supply line 124 is connected to the nozzle 152 of the inlet header 151. An outlet header 153 is provided at one end of the second heat exchanger 142 and a downstream end of the fuel gas supply line 124 is connected to the nozzle 154 of the outlet header 153. The first heat exchanging unit 141 is provided with an outlet header 157 at the other end and the inlet header 158 is connected to the other end of the second heat exchanging unit 142. The outlet header 157 of the first heat exchanging unit 141 and the inlet header 158 of the second heat exchanging unit 142 are connected by a connecting pipe 159 as a connecting portion.

The bypass flow path 143 bypasses one heat exchanging unit 141 among the plurality of heat exchanging units 141 and 142. The bypass passage 143 has its base end connected to the fuel gas supply line 124 on the upstream side of the first heat exchanging unit 141 and its tip end connected to the connection pipe 159. The flow rate adjusting valve 144 is provided in the bypass flow path 143 and adjusts the flow rate of the fuel gas L flowing through the bypass flow path 143.

The temperature sensor 145 is provided in the fuel gas supply line 124 at the outlet side of the second heat exchanger 142 and measures the temperature of the fuel gas L and outputs it to the control unit 146. The control unit 146 adjusts the opening degree of the flow rate adjusting valve 144 in accordance with the temperature of the fuel gas L measured by the temperature sensor 145. The control unit 146 adjusts the opening degree of the flow rate adjusting valve 144 such that the temperature of the fuel gas L falls within a predetermined temperature range set in advance.

The configuration of the second heat exchanger 133B is not limited to that described above. 18, the second heat exchanger 133C includes a fuel gas supply line 124, a cooling air line 128, a first heat exchanger 141 and a second heat exchanger 142, A bypass flow passage 143, a flow rate adjusting valve 147, a temperature sensor 145, and a control section 146. [

The bypass passage 143 bypasses the first heat exchanger 141 and has a proximal end connected to the fuel gas supply line 124 on the upstream side of the first heat exchanger 141, 159). The flow regulating valve 147 is a three-way valve provided at the branching portion of the fuel gas supply line 124 and the bypass flow path 143. The flow adjustment valve (three-way valve) 147 adjusts the opening degree of the first heat exchange section 141 and the opening degree of the bypass flow passage 143 with respect to the fuel gas supply line 124, And adjusts the flow rate of the fuel gas (L) flowing to the fuel cell (143).

The functions of the second heat exchangers 133B and 133C are substantially the same as those of the fifth embodiment described above, and the description thereof is omitted here.

As described above, in the heat exchanger of the sixth embodiment, the outlet header 157 of the first heat exchanging unit 141 and the inlet header 158 of the second heat exchanging unit 142 are connected by the connecting pipe 159 as the connecting unit have. Therefore, by forming the connection portion as the connection pipe 159, the first heat exchanging portion 141 and the second heat exchanging portion 142 can be compactly connected, and the structure can be simplified.

[Seventh Embodiment]

19 is a schematic configuration diagram of a heat exchanger of a seventh embodiment. Members having the same functions as those of the above-described embodiment are denoted by the same reference numerals, and a detailed description thereof will be omitted.

19, the second heat exchanger 160 includes a fuel gas supply line 124, a cooling air line 128, a first heat exchanging unit 161, and a second heat exchanging unit 161. In the seventh embodiment, A second heat exchanging unit 162, a third heat exchanging unit 163, a bypass flow path 1614165, flow rate regulating valves 166 and 167, a temperature sensor 168, and a control unit 169.

Heat exchange units 161 and 1612163 are provided in the fuel gas supply line 124 and perform heat exchange with the fuel gas L and the heated air AH and are connected in series and arranged in parallel with each other . An inlet header 171 is provided at one end of the first heat exchanging unit 161 and an upstream end of the fuel gas supply line 124 is connected to the nozzle 172 of the inlet header 171. The first heat exchanger 161 is provided with an outlet header 173 at the other end thereof. The second heat exchanger 162 has an inlet header 174 at the other end and an outlet header 175 at one end. The third heat exchanger 163 is provided with an inlet header 176 at one end and an outlet header 177 at the other end and a fuel gas supply line 124 Is connected to the downstream-side end of the gasket.

The outlet header 173 of the first heat exchanger 161 and the inlet header 174 of the second heat exchanger 162 are connected by a connection pipe 179. The outlet header 175 of the second heat exchanger 162 and the inlet header 176 of the third heat exchanger 163 are connected by a connection pipe 180.

The first bypass passage 164 bypasses the first heat exchanger 161 and the second bypass passage 165 connects the first heat exchanger 161 and the second heat exchanger 162 to each other. Pass. The first bypass passage 164 has its base end connected to the fuel gas supply line 124 on the upstream side of the first heat exchanger 161 and its tip end connected to the connection pipe 179. The base end of the second bypass flow path 165 is connected to the fuel gas supply line 124 on the upstream side of the first heat exchange section 161 and the tip end of the second bypass flow path 165 is connected to the connection pipe 180. The first flow control valve 166 is provided in the first bypass passage 164 and adjusts the flow rate of the fuel gas L flowing through the first bypass passage 164. The second flow rate regulating valve 167 is provided in the second bypass flow path 165 and regulates the flow rate of the fuel gas L flowing through the second bypass flow path 165.

The temperature sensor 168 is provided in the fuel gas supply line 124 at the outlet side of the third heat exchanging unit 163 and measures the temperature of the fuel gas L and outputs it to the control unit 169. The control unit 169 adjusts the opening degree of the flow rate adjusting valves 166 and 167 in accordance with the temperature of the fuel gas L measured by the temperature sensor 168. [ The control unit 169 adjusts the opening of the flow rate adjusting valves 166 and 167 so that the temperature of the fuel gas L falls within a predetermined temperature range set in advance. That is, when the temperature of the fuel gas L becomes higher than the predetermined temperature range, the control unit 169 increases the opening degree of the flow regulating valves 166 and 167, and when the temperature of the fuel gas L is lower than the predetermined temperature region The opening of the flow regulating valves 166 and 167 is reduced.

The second heat exchanger 160 normally operates by setting the flow rate regulating valves 166 and 167 to 0 (fully closed). When the fuel gas L flows through the fuel gas supply line 124 and flows through the respective heat exchanging units 161 and 1612163, the fuel gas L is heated by heat exchange with the heated air AH.

The control unit 169 adjusts the opening of the flow rate adjusting valves 166 and 167 so that the temperature of the fuel gas L falls within the predetermined temperature range. For example, when the temperature of the cooling air (AC) increases due to the rise in the temperature, the temperature of the heated air (AH) also increases and the heat exchange amount (heat of the fuel gas Absorption amount) increases and the temperature of the fuel gas L exceeds the predetermined temperature range. At this time, when the temperature of the fuel gas L becomes higher than the predetermined temperature range, first, the control section 169 increases the opening degree of the second flow regulating valve 167. A portion of the fuel gas L is supplied from the fuel gas supply line 124 to the third heat exchanging unit 163 through the bypass flow path 165 in accordance with the opening degree of the second flow regulating valve 167. [ That is, a part of the fuel gas L is directly supplied to the third heat exchanging unit 163 bypassing the first heat exchanging unit 161 and the second heat exchanging unit 162. The high temperature fuel gas L heated by the first heat exchanging unit 161 and the second heat exchanging unit 162 is supplied to the first heat exchanging unit 161 and the second heat exchanging unit 162, The temperature of the fuel gas L flowing through the third heat exchanging portion 163 is lowered because the fuel gas L in the third heat exchanging portion 163 is mixed in the connecting pipe 180. As a result, the temperature of the fuel gas L discharged from the third heat exchanging part 163 is lowered and becomes lower than the predetermined temperature range.

If the temperature of the fuel gas L is not sufficiently lowered even if the opening degree of the second flow rate adjusting valve 167 is increased, then the control section 169 sets the opening degree of the first flow rate adjusting valve 166 to a large value do. At this time, the second flow regulating valve 167 may be closed. The fuel gas L is partially supplied from the fuel gas supply line 124 to the second heat exchanger 162 through the bypass flow path 164 in accordance with the opening degree of the first flow rate regulating valve 166. [ That is, a part of the fuel gas L bypasses the first heat exchanging part 161 and is directly supplied to the second heat exchanging part 162. Because of this, the low-temperature fuel gas L bypassing the first heat exchanger 161 is mixed with the high-temperature fuel gas L heated by the first heat exchanger 161 in the connection pipe 179 , The temperature of the fuel gas (L) flowing through the second heat exchanger (162) decreases. As a result, the temperature of the fuel gas L discharged from the second heat exchanging portion 162 is lowered and falls within the predetermined temperature range.

As described above, in the heat exchanger of the seventh embodiment, the fuel gas supply line 124, the cooling air line 128, the heat exchanging units 161 and 1612163 for performing the heat exchange between the fuel gas L and the heated air AH A first bypass passage 164 for bypassing the first heat exchanging portion 161 and a second bypass passage 165 for bypassing the first heat exchanging portion 161 and the second heat exchanging portion 162 167 for regulating the flow rate of the fuel gas L flowing through the bypass passage 1614165 and the flow rate control valves 166, 167 for regulating the flow rate of the fuel gas L at the outlet side of the third heat exchanger 163 A temperature sensor 168 for measuring the temperature and a control unit 169 for adjusting the opening degree of the flow rate adjusting valves 166 and 167 according to the temperature of the fuel gas L detected by the temperature sensor 168.

The opening degree of the flow rate adjusting valves 166 and 167 is adjusted in accordance with the temperature of the fuel gas L at the outlet side of the third heat exchanging portion 163 disposed on the most downstream side, , 162) of the fuel gas (L) is adjusted. At this time, since the fuel gas L partially bypasses only the first heat exchanging unit 161 or the respective heat exchanging units 161 and 162, the fuel gas L is supplied to the respective heat exchanging units 162 and 163, The extremely high temperature of the fuel gas L passing through the heat exchanging part 163 is suppressed even if the flow rate thereof temporarily decreases. As a result, in the heat exchanger of the seventh embodiment, the temperature of the fuel gas L can be adjusted with high accuracy, and the overheating of the fuel gas L can be suppressed.

Although the two heat exchanging units 141 and 142 or the three heat exchanging units 161 and 1612163 are provided in the above-described embodiment, a plurality of heat exchanging units may be provided, or three or more heat exchanging units may be provided. At this time, the bypass flow passage 1413164 bypasses the first heat exchange portions 141 and 161, and the bypass flow passage 165 bypasses the first and second heat exchange portions 161 and 162 However, the present invention is not limited to this configuration. For example, the bypass flow path may bypass only the second heat exchange section 162, or the bypass flow path may bypass only the third heat exchange section 163.

In the above-described embodiment, the heat exchangers 141, 142, 161, 162, and 163 are formed by straight tubes, but they may be formed by U-shaped heat transfer tubes.

Although the heat exchanger of the present invention is applied to the gas turbine 10 and the fuel gas (primary fluid) L is heated by the heated air (secondary fluid) AH in the above-described embodiment, The present invention is not limited to this configuration. That is, the heat exchanger of the present invention can be applied to a separate part of the gas turbine 10 or to a field other than the gas turbine 10 (for example, a boiler).

In the above-described embodiment, the heat exchanger is used to heat the secondary fluid by the primary fluid. However, the heat exchanger may be a heat exchanger that cools the primary fluid by the secondary fluid. In this case, have.

10 Gas Turbine
11 compressor
12 combustor
13 Turbines
14 generator
24 fuel gas supply line
26 Heat exchanger
27 Compressed air branch line (primary flow path)
28 Cooling air line (2nd flow path)
32, 32A, 32B, 32C, 32D, 32E, 90 The first heat exchanger
33 Second Heat Exchanger (Heat Exchanger)
41, 91 First heat exchanger
42, 92,
43, 95, 96, 97, 98 Flow regulating valve
71, 72 Temperature sensor (status detection sensor)
73,
81, 99 Flow sensor (status sensor)
AC cooling air (secondary fluid)
A2 Compressed air (primary fluid)
124 Fuel gas supply line (primary flow path)
126 Heat exchanger
127 compressed air branch line
128 Cooling air line (2nd flow path)
132 first heat exchanger
133, 133A, 133B, 133C, 160 A second heat exchanger (heat exchanger)
141, 161 The first heat exchanger
142 and 162,
143, 164, 165 Bypass channel
144, 166, 167 Flow regulating valve
145, 168 Temperature sensor
146,
151, 158, 171, 174, 176 Inlet header
153, 157, 173, 175, 177 exit header
155 Connection header (connection part)
159 Connection piping (connection part)
163 Third heat exchanger
AC cooling air
AH Heating air (secondary fluid)
L fuel gas (primary fluid)

Claims (15)

A primary flow path through which the primary fluid flows,
A second flow path through which the secondary fluid flows in the primary flow path,
A plurality of heat exchanging units that perform heat exchange between the primary fluid and the secondary fluid and are juxtaposed in the flow direction of the primary fluid,
A flow rate adjusting valve for adjusting a flow rate of the primary fluid flowing through the plurality of heat exchanging units;
And a heat exchanger. A primary flow path through which the primary fluid flows,
A second flow path through which the secondary fluid flows in the primary flow path,
A plurality of heat exchanging units that perform heat exchange between the primary fluid and the secondary fluid and are juxtaposed in the flow direction of the primary fluid,
A flow rate adjusting valve for adjusting a flow rate of the primary fluid flowing through the plurality of heat exchanging units,
A state detection sensor for detecting a state of the primary fluid,
And a controller for adjusting the opening degree of the flow rate adjusting valve in accordance with the state of the primary fluid detected by the state detecting sensor
And a heat exchanger. The method of claim 2,
Wherein the plurality of heat exchanging units are provided with a separate inlet header at one end and a common outlet header at the other end and the primary flow path is connected to the inlet header and the outlet header, Wherein the flow control valve is provided in the primary fluid passage. The method of claim 2,
Wherein the plurality of heat exchanging units are provided with an inlet header common to one end and a separate outlet header at the other end and the primary flow path is connected to the inlet header and the outlet header, Wherein the flow control valve is provided in the primary fluid passage. The method according to any one of claims 2 to 4,
Wherein the state detection sensor is a temperature sensor for detecting a temperature of a primary fluid at an outlet side of the plurality of heat exchanging units and wherein the control unit is configured to set the temperature difference of the primary fluid at the outlet side of the plurality of heat exchanging units And the opening degree of the flow rate adjusting valve is made smaller when the temperature difference is larger than a predetermined temperature difference. The method according to any one of claims 2 to 4,
Wherein the state detection sensor is a flow rate sensor for detecting a flow rate of the primary fluid at the inlet side of the plurality of heat exchanging units and the control unit controls the flow rate of the primary fluid at the inlet side of the plurality of heat exchanging units And the opening degree of the flow rate regulating valve is made smaller when the flow rate regulating valve is smaller than the predetermined flow rate. The method according to any one of claims 2 to 4,
Wherein the state detecting sensor is a pressure sensor for detecting a pressure of a primary fluid at an inlet side of the plurality of heat exchanging units and the control unit is configured to control the pressure of the primary fluid at the inlet side of the plurality of heat exchanging units And the opening degree of the flow rate adjusting valve is made smaller when the pressure is larger than a predetermined pressure. The method according to any one of claims 2 to 7,
Wherein a plurality of the flow rate adjusting valves are provided corresponding to the plurality of heat exchanging units and the control unit is configured to decrease the flow rate of the primary fluid flowing through the plurality of heat exchanging units according to the state of the primary fluid detected by the state detecting sensor And the opening degree of the plurality of flow rate adjusting valves is adjusted so that the flow rate adjusting valve is opened. A primary flow path through which the primary fluid flows,
A second flow path through which the secondary fluid flows in the primary flow path,
A plurality of heat exchanging units for performing heat exchange between the primary fluid and the secondary fluid,
A bypass flow path for bypassing at least one of the plurality of heat exchange sections,
A flow rate regulating valve for regulating the flow rate of the primary fluid flowing through the bypass flow path,
A temperature sensor for measuring the temperature of the primary fluid at the outlet side of the plurality of heat exchanging units,
And a controller for adjusting the opening degree of the flow rate adjusting valve in accordance with the temperature of the primary fluid detected by the temperature sensor
And a heat exchanger. The method of claim 9,
Wherein the plurality of heat exchanging portions includes a first heat exchanging portion and a second heat exchanging portion connected in series, wherein the bypass flow path has one end connected to the inlet of the first heat exchanging portion, and the other end connected to the first heat exchanging portion, 2 heat exchanging unit. The method of claim 10,
Wherein the first heat exchanging part and the second heat exchanging part are arranged in parallel and the inlet part of the first heat exchanging part and the outlet part of the second heat exchanging part are disposed at one end and the connecting part is disposed at the other end Heat exchanger. The method according to claim 10 or 11,
Wherein the connecting portion is a header to which a downstream end portion of the first heat exchanging portion and an upstream end portion of the second heat exchanging portion are connected. The method according to claim 10 or 11,
Wherein the connecting portion is a connecting pipe connecting the downstream end of the first heat exchanging portion and the upstream end of the second heat exchanging portion. The method according to any one of claims 9 to 13,
Wherein the flow control valve is provided in the bypass flow passage. The method according to any one of claims 9 to 13,
Wherein the flow rate adjusting valve is a three-way valve provided at a branching portion of the primary flow path and the bypass flow path.

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