JP2015152264A - heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat exchanger capable of suppressing overcooling or overheating of a secondary fluid by appropriately implementing heat exchange even if a flow volume of a primary fluid varies.SOLUTION: A heat exchanger comprises: a cooling air line 28 in which cooling air AC flows; a compressed-air branch line 27 in which compressed air A2 flows; heat exchange units 41 and 42 implementing heat exchange between the cooling air AC and the compressed air A2 and provided to be aligned in a flow direction of the cooling air AC; a flow regulating valve 43 regulating a flow volume of the compressed air A2 flowing in the second heat exchange units 42 located downstream in the flow direction of the cooling air AC out of the heat exchange units 41 and 42; temperature sensors 71 and 72 detecting a temperature of the compressed air A2; and a control unit 73 adjusting the opening of the flow regulating valve 43 in response to the temperature of the compressed air A2 detected by the temperature sensors 71 and 72.

Description

  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 exchanging heat between the primary fluid and the secondary fluid, there is a heat exchanger configured by connecting an inlet header and an outlet header with a large number of heat transfer tubes. In such a heat exchanger, when the secondary fluid supplied to the inlet header flows to the outlet header through a number of heat transfer tubes, it is cooled or heated by the primary fluid that contacts the heat transfer tubes.

  For example, there is a heat exchanger having a configuration described in Patent Document 1 below. The heat exchanger described in Patent Document 1 is a heating / vaporization device that heats or vaporizes a low-temperature fluid, and heat transfer that constitutes the panel by causing a heat medium to flow down along both sides of the heat exchange panel. Heat or vaporize the cryogenic fluid flowing in the tube. A control valve is provided in front of the inlets of the two headers or manifolds to stop the supply of the cryogenic fluid to some of the heat exchanger panels according to fluctuations in the supply amount of the cryogenic fluid and to perform the remaining heat exchange. The control panel operates the control valve so that the flow rate at the steady load is maintained.

JP 2009-052724 A

  A heat exchanger in which an inlet header and an outlet header are connected by a large number of heat transfer tubes allows the secondary fluid to flow into each heat transfer tube, while allowing the primary fluid to flow orthogonally to the heat transfer tube outside each heat transfer tube. Thus, heat exchange is performed between the primary fluid and the secondary fluid. At this time, if the flow rate of the secondary fluid decreases, the flow rate of the secondary fluid flowing through each heat transfer tube decreases, so in the heat transfer tube arranged upstream of the primary fluid, the secondary fluid is in a supercooled state or overheated. It becomes a state. For this reason, even in a heat exchanger in which an inlet header and an outlet header are connected by a large number of heat transfer tubes, as in the heating / vaporization apparatus described in Patent Document 1, the heat exchange panel is moved to a heat exchange panel. It is desirable that the supply of the low-temperature fluid can be stopped so that the secondary fluid can be prevented from being overcooled or overheated.

  The present invention solves the above-described problems, and provides a heat exchanger that can suppress overcooling or overheating of a secondary fluid by appropriately performing heat exchange even when the flow rate of the primary fluid fluctuates. The purpose is to do.

  In order to achieve the above object, a heat exchanger according to the present invention includes a primary flow path through which a primary fluid flows, a secondary flow path through which a secondary fluid flows in the primary flow path, and a primary fluid and a secondary fluid. A plurality of heat exchanging portions arranged in parallel in the flow direction of the primary fluid while performing heat exchange, and a flow rate adjusting valve for adjusting the flow rate of the primary fluid flowing through the plurality of heat exchanging portions. It is.

  Therefore, the primary fluid flowing through the plurality of heat exchange units is cooled or heated by exchanging heat with the secondary fluid. When the state of the primary fluid flowing through the plurality of heat exchange units varies, the position of the flow rate adjustment valve is adjusted according to the state of the primary fluid, so that the position of the secondary fluid in the plurality of heat exchange units is downstream of the flow direction. The flow rate of the primary fluid flowing through the heat exchanging section is adjusted. Therefore, the influence which a secondary fluid has on each heat exchange part decreases, and high temperature and low temperature are suppressed. As a result, even if the state of the primary fluid fluctuates, it is possible to suppress overcooling or heating of the primary fluid by appropriately exchanging heat.

  The heat exchanger according to the present invention performs heat exchange between the primary flow path through which the primary fluid flows, the secondary flow path through which the secondary fluid flows in the primary flow path, and the primary fluid and the secondary fluid. A plurality of heat exchange units arranged in parallel in the fluid flow direction, a flow rate adjusting valve for adjusting a flow rate of the primary fluid flowing through the plurality of heat exchange units, a state detection sensor for detecting a state of the primary fluid, and the state And a control unit that adjusts the opening of the flow rate adjusting valve in accordance with the state of the primary fluid detected by the detection sensor.

  Therefore, the primary fluid flowing through the plurality of heat exchange units is cooled or heated by exchanging heat with the secondary fluid. When the state of the primary fluid flowing through the plurality of heat exchange units varies, the position of the flow rate adjustment valve is adjusted according to the state of the primary fluid, so that the position of the secondary fluid in the plurality of heat exchange units is downstream of the flow direction. The flow rate of the primary fluid flowing through the heat exchanging section is adjusted. Therefore, the influence which a secondary fluid has on each heat exchange part decreases, and high temperature and low temperature are suppressed. As a result, even if the state of the primary fluid fluctuates, it is possible to suppress overcooling or overheating of the secondary fluid by appropriately performing heat exchange.

  In the heat exchanger according to the present invention, each of the plurality of heat exchange units is provided with an individual inlet header at one end and a common outlet header at the other end, and the primary flow path includes the inlet header and the The flow rate adjusting valve is provided in the primary fluid flow path connected to the outlet header and connected to the inlet header.

  Therefore, the primary fluid flow path branched to the upstream side in the plurality of heat exchange sections is connected, and the flow rate adjusting valve is provided in the primary fluid flow path connected to the heat exchange section located downstream in the flow direction of the secondary fluid. Therefore, the flow rate of the primary fluid flowing through the plurality of heat exchange units can be adjusted with high accuracy.

  In the heat exchanger according to the present invention, the plurality of heat exchanging portions are provided with a common inlet header at one end portion and an individual outlet header at the other end portion, and the primary flow path includes the inlet header and the It is connected to the outlet header, and the flow rate adjusting valve is provided in the primary fluid flow path connected to the outlet header.

  Therefore, the primary fluid branched to the downstream side in the plurality of heat exchange units is connected, and the flow rate adjustment valve is provided in the primary fluid flow path connected to the heat exchange unit 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 exchange units can be adjusted with high accuracy.

  In the heat exchanger according to the present invention, the state detection sensor is a temperature sensor that detects a temperature of a primary fluid on an outlet side of the plurality of heat exchange units, and the control unit is an outlet side of the plurality of heat exchange units. When the temperature difference of the primary fluid in is larger than a predetermined temperature difference set in advance, the opening degree of the flow rate adjusting valve is reduced.

  Therefore, when the temperature difference between the primary fluids flowing through the plurality of heat exchange units becomes larger than the predetermined temperature difference, the heat exchange located downstream in the flow direction of the secondary fluid is performed in order to reduce the opening of the flow rate adjustment valve. The flow rate of the primary fluid flowing through the section decreases. For this reason, the influence of the secondary fluid on the heat exchanging portion located on the upstream side in the flow direction is reduced, and it is possible to suppress overcooling or overheating of the primary fluid.

  In the heat exchanger according to the present invention, the state detection sensor is a flow rate sensor that detects a flow rate of a primary fluid on an inlet side of the plurality of heat exchange units, and the control unit is an inlet side of the plurality of heat exchange units. When the flow rate of the primary fluid in is less than a predetermined flow rate set in advance, the opening of the flow rate adjustment valve is reduced.

  Therefore, when the flow rate of the primary fluid flowing through the plurality of heat exchange units is less than a predetermined flow rate, in order to reduce the opening of the flow rate adjustment valve, the heat exchange unit located on the downstream side in the secondary fluid flow direction is provided. The flow rate of the flowing primary fluid is reduced. For this reason, the influence of the secondary fluid on the heat exchanging portion located on the upstream side in the flow direction is reduced, and it is possible to suppress overcooling or overheating of the primary fluid.

  In the heat exchanger according to the present invention, the state detection sensor is a pressure sensor that detects a pressure of a primary fluid on an inlet side of the plurality of heat exchange units, and the control unit is an inlet side of the plurality of heat exchange units. When the pressure of the primary fluid in is larger than a predetermined pressure set in advance, the opening degree of the flow rate adjusting valve is reduced.

  Therefore, when the pressure of the primary fluid flowing through the plurality of heat exchange units becomes less than a predetermined pressure, the heat exchange unit located downstream in the flow direction of the secondary fluid is used to reduce the opening of the flow rate adjustment valve. The flow rate of the flowing primary fluid is reduced. For this reason, the influence of the secondary fluid on the heat exchanging portion located on the upstream side in the flow direction is reduced, and it is possible to suppress overcooling or overheating of the primary fluid.

  In the heat exchanger of the present invention, a plurality of the flow rate adjustment valves are provided corresponding to the plurality of heat exchange units, and the control unit is configured to change the plurality of flow rate control valves according to the state of the primary fluid detected by the state detection sensor. The opening degree of the plurality of flow rate adjustment valves is adjusted so that 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 in the heat exchange unit is reduced.

  Therefore, by adjusting the flow rate of the primary fluid flowing through the plurality of heat exchange units, the influence of the secondary fluid on each heat exchange unit can be reduced, and the supercooling or overheating of the primary fluid can be suppressed 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 downstream in the flow direction of the secondary fluid is adjusted according to the state of the primary fluid, the state of the primary fluid varies. However, it is possible to suppress overcooling or overheating of the primary fluid by appropriately performing heat exchange.

FIG. 1 is a schematic configuration diagram illustrating a gas turbine. FIG. 2 is a schematic diagram showing a heat exchange device. FIG. 3 is a schematic configuration diagram of the heat exchanger according to the first embodiment. FIG. 4 is a schematic configuration diagram of a heat exchanger that represents a modification of the first embodiment. FIG. 5 is a schematic diagram illustrating the operation of the heat exchanger according to the first embodiment. FIG. 6 is a schematic configuration diagram of a heat exchanger according to the second embodiment. FIG. 7 is a schematic configuration diagram of a heat exchanger that represents a modification of the second embodiment. FIG. 8 is a schematic configuration diagram of a heat exchanger according to the third embodiment. FIG. 9 is a schematic configuration diagram of a heat exchanger that represents a modification of the third embodiment. FIG. 10 is a schematic configuration diagram of a heat exchanger according to the fourth embodiment.

  Exemplary embodiments of a heat exchanger according to the present invention will be described below in detail with reference to the accompanying drawings. In addition, this invention is not limited by this embodiment, and when there are two or more embodiments, what comprises combining each embodiment is also included.

[First Embodiment]
FIG. 1 is a schematic configuration diagram illustrating a gas turbine.

  In the first embodiment, as illustrated in FIG. 1, the gas turbine 10 includes a compressor 11, a combustor 12, and a turbine 13. The gas turbine 10 is connected to a generator 14 and can generate power.

  The compressor 11 and the turbine 13 are connected by a rotating shaft 21 so as to be integrally rotatable. The compressor 11 compresses the air A taken in from the air intake line 22. The combustor 12 mixes and combusts 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. The turbine 13 is rotated by the combustion gas G supplied from the combustor 12 through the combustion gas supply line 25.

  Further, the gas turbine 10 includes a heat exchange device 26 that exchanges heat between the compressed air A2 of the compressed air A1 compressed by the compressor 11, the cooling air AC taken from the outside, and the fuel gas L. Is provided. The heat exchange device 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 exchange device 26 cools the compressed air A2 with the cooling air AC and heats the fuel gas L with the heated air AH whose temperature has increased. The cooled compressed air A2 is supplied through the casing of the turbine 13 and cools the blades as cooling air.

  The generator 14 is connected to the compressor 11 through a coaxial rotary shaft 29 so as to be integrally rotatable, and can generate electric power when the turbine 13 rotates.

  FIG. 2 is a schematic diagram showing a heat exchange device.

  As shown in FIG. 2, the heat exchange device 26 has two heat exchangers 32 and 33 disposed in a housing 31. The housing 31 is provided with an air intake port 34 at the lower portion, an intake fan 35 is provided at the air intake port 34, and an air exhaust port 36 is provided at the upper portion.

  The first heat exchanger 32 exchanges heat between the compressed air A2 compressed by the compressor 11 and the cooling air AC taken from the outside. That is, the first heat exchanger 32 cools the compressed air A2 with the normal temperature cooling air AC. In addition, the second heat exchanger 33 performs heat exchange between the heated air AH and the fuel gas L, which have become a high temperature by cooling the compressed air A2. That is, the cooling air AC becomes the high-temperature heating air AH by cooling the compressed air A2, and the second heat exchanger 33 heats the fuel gas L with the heating air AH.

  Hereinafter, the 1st heat exchanger as a heat exchanger of a 1st embodiment is explained. FIG. 3 is a schematic configuration diagram of the heat exchanger according to 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, and a plurality of (in this embodiment). 2) first heat exchange unit 41 and second heat exchange unit 42, and a flow rate adjusting valve 43. 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 so as to be substantially orthogonal to each other. And the 1st heat exchange part 41 and the 2nd heat exchange part 42 are arranged in parallel in the flow direction of compressed air A2, and the 2nd heat exchange part 42 is compressed air A2 to the 1st heat exchange part 41. It is arrange | positioned in the downstream of the flow direction.

  The 1st heat exchange part 41 and the 2nd heat exchange part 42 are provided in the compressed air branch line 27, and heat-exchange with compressed air A2 and cooling air AC, and are provided adjacent in parallel. In addition, they are arranged in parallel to each other. The first heat exchanging part 41 is provided with an individual inlet header 51 at one end, and the second heat exchanging part 42 is provided with an individual inlet header 52 at one end. Moreover, the 1st heat exchange part 41 and the 2nd heat exchange part 42 are provided with the common exit header 53 in the other end part. The compressed air branch line 27 is divided into a first branch channel 54 a and a second branch channel 54 b as primary fluid supply channels, and the first branch channel 54 a is connected to the nozzle 55 of the inlet header 51 in the first heat exchange unit 41. The second branch flow path 54b is connected to the nozzle 56 of the inlet header 52 in the second heat exchange section 42. Further, the compressed air branch line 27 is provided with a collective flow path 54 c as a primary fluid discharge path, and is connected to the nozzle 57 of the outlet header 53.

  The flow rate adjusting valve 43 is provided in the second branch flow path 54b, and adjusts the flow rate of the compressed air A2 flowing through the second branch flow path 54b.

  The first heat exchanger 32 is normally operated with the flow rate adjustment valve 43 opened at 100% (fully open). That is, the flow rate of the compressed air A2 supplied from the compressed air branch line 27 to the first heat exchange part 41 and the second heat exchange part 42 via the first branch flow path 54a and the second branch flow path 54b is the same. It has become. When the compressed air A2 flows through the first heat exchange unit 41 and the second heat exchange unit 42, the compressed air A2 is cooled and discharged by exchanging heat with the cooling air AC.

  When the flow rate of the compressed air A2 flowing through the compressed air branch line 27 decreases, the opening degree of the flow rate adjustment valve 43 is reduced. Then, the flow rate of the compressed air A2 supplied to the second heat exchange part 42 via the second branch flow path 54b decreases, while being supplied to the first heat exchange part 41 via the first branch flow path 54a. The flow rate of the compressed air A2 increases relatively. When the flow rate of the compressed air A2 in the first heat exchange unit 41 increases, when the cooling air AC and the compressed air A2 exchange heat, the heat of the first heat exchange unit 41 is larger than the heat load of the second heat exchange unit 42. The load becomes high and supercooling is suppressed.

  In addition, the structure of the 1st heat exchanger 32 is not limited to what was mentioned above. FIG. 4 is a schematic configuration diagram of a heat exchanger that represents a modification of the first embodiment.

  As shown in FIG. 4, the first heat exchanger 32A representing a modification of the first embodiment includes a compressed air branch line 27, a cooling air line 28, a first heat exchange unit 41, and a second heat exchange unit. 42 and a flow rate adjusting valve 43.

  The first heat exchange part 41 and the second heat exchange part 42 are provided with a common inlet header 61 at one end. The first heat exchanging part 41 is provided with an individual outlet header 62 at the other end, and the second heat exchanging part 42 is provided with an individual outlet header 63 at the other end. The compressed air branch line 27 is provided with a supply flow path 64 a as a primary fluid supply path, and is connected to the nozzle 65 of the inlet header 61. The compressed air branch line 27 is divided into a first branch flow path 64 b and a second branch flow path 64 c as a primary fluid discharge path, and the first branch flow path 64 a is a nozzle of the outlet header 62 of the first heat exchange unit 41. 66, and the second branch flow path 64c is connected to the nozzle 67 of the outlet header 63 of the second heat exchange section.

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

  The first heat exchanger 32A normally operates with the opening of the flow rate adjustment valve 43 set to 100% (fully open). That is, the flow rates of the compressed air A2 supplied from the compressed air branch line 27 to the first heat exchange unit 41 and the second heat exchange unit 42 via the supply flow path 64a are equal. When the compressed air A2 flows through the first heat exchange unit 41 and the second heat exchange unit 42, the compressed air A2 is cooled and discharged by exchanging heat with the cooling air AC.

  When the flow rate of the compressed air A2 flowing through the compressed air branch line 27 decreases, the opening degree of the flow rate adjustment valve 43 is reduced. As a result, the flow rate of the compressed air A2 discharged from the second heat exchange section 42 via the second branch flow path 64c decreases, while being discharged from the first heat exchange section 41 via the first branch flow path 64b. The flow rate of the compressed air A2 increases relatively. When the flow rate of the compressed air A2 in the first heat exchange unit 41 increases, when the cooling air AC and the compressed air A2 exchange heat, the heat of the first heat exchange unit 41 is larger than the heat load of the second heat exchange unit 42. The load becomes high and supercooling is suppressed.

  Here, the operation of the first heat exchangers 32 and 32A will be described. It is the schematic showing the effect | action of the heat exchanger of 1st Embodiment.

  As shown in FIG. 5, when the opening degree of the flow rate adjusting valve 43 is fully open, the flow rate of the compressed air A2 supplied from the inlet headers 51 and 52 to the heat exchange units 41 and 42 is equal. Therefore, at this time, when the cooling air AC acts on each of the heat exchanging portions 41 and 42, the cooling air AC that is the atmospheric temperature Ta at the inlet portion C1 cools the compressed air A2, as represented by a one-dot chain line. The temperature rises and the temperature reaches Tb at the outlet C3 and is discharged. Therefore, 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 amount of the flow rate adjustment valve 43 is reduced (for example, fully closed), so that it is supplied from the inlet header 51 to the first heat exchange unit 41. The flow rate of the compressed air A2 supplied from the inlet header 52 to the second heat exchange unit 42 increases with respect to the flow rate of the compressed air A2. Therefore, at this time, when the cooling air AC acts on the heat exchange units 41 and 42, the cooling air AC having the atmospheric temperature Ta at the inlet portion C1 cools the compressed air A2 as shown by the solid line. The temperature rises and is discharged at a temperature Tb at C2 between the first heat exchange unit 41 and the second heat exchange unit 42. Therefore, the compressed air A2 is cooled to a predetermined temperature.

  That is, by fully closing the flow rate adjusting valve 43, the entire amount of the compressed air A2 flowing through the compressed air branch line 27 is supplied to the first heat exchanging unit 41, so that the first heat exchanging unit 41 is changed per unit time. The flow rate of the flowing compressed air A2 increases, and the flow rate of the compressed air A2 increases. Therefore, the compressed air A2 absorbs more heat by the cooling air AC while passing through the first heat exchange unit 41, and the temperature of the compressed air A2 is C2 between the first heat exchange unit 41 and the second heat exchange unit 42. Tb. Therefore, overcooling in the first heat exchange unit 41 is suppressed. On the other hand, although the compressed air A2 does not flow in the second heat exchanging section 42, the compressed air A2 whose temperature has increased acts, so that the supercooling here is also suppressed.

  As described above, in the heat exchanger according to 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 secondary flow path through which the compressed air A2 as the secondary fluid flows. The first heat exchanging section 41 and the second heat exchanging section 27 as a plurality of heat exchanging sections arranged in parallel in the flow direction of the cooling air AC while performing heat exchange between the compressed air branch line 27 and the cooling air AC and the compressed air A2. A heat exchange unit 42 and a flow rate adjustment valve 43 that adjusts the flow rate of the compressed air A2 that flows through the second heat exchange unit 42 that is located downstream in the flow direction of the cooling air AC in the plurality of heat exchange units 41 and 42 are provided. ing.

  Therefore, the compressed air A2 flowing through the plurality of heat exchange units 41 and 42 is cooled by exchanging heat with the cooling air AC. When the flow rate of the compressed air A2 flowing through the plurality of heat exchange units 41 and 42 varies, the opening of the flow rate adjustment valve 43 is adjusted in accordance with the flow rate of the compressed air A2, so that the cooling air in the plurality of heat exchange units 41 and 42 The flow rate of the compressed air A2 that flows through the second heat exchange unit 42 that is located on the downstream side in the AC flow direction is adjusted. Therefore, the cooling air AC has little influence on the heat exchanging parts 41 and 42, and high temperature and low temperature are suppressed. As a result, even if the flow rate of the compressed air A2 fluctuates, it is possible to suppress overcooling of the compressed air A2 by appropriately exchanging heat.

[Second Embodiment]
FIG. 6 is a schematic configuration diagram of a heat exchanger according to the second embodiment, and FIG. 7 is a schematic configuration diagram of a heat exchanger representing a modification of the second embodiment. In addition, the same code | symbol is attached | subjected to the member which has the same function as embodiment mentioned above, and detailed description is abbreviate | omitted.

  In the second embodiment, as shown in FIG. 6, the first heat exchanger 32B includes a compressed air branch line 27, a cooling air line 28, a first heat exchange unit 41, a second heat exchange unit 42, The flow control valve 43 includes a first temperature sensor 71 and a second temperature sensor 72 as state detection sensors, and a control unit 73.

  The first temperature sensor 71 and the second temperature sensor 72 are provided on the outlet header 53. The first temperature sensor 71 detects the temperature (state) of the compressed air A <b> 2 discharged from the first heat exchange unit 41 to the outlet header 53 and outputs it to the control unit 73. The second temperature sensor 72 detects the temperature (state) of the compressed air A <b> 2 discharged from the second heat exchange unit 42 to the outlet header 53, and outputs it to the control unit 73. The controller 73 adjusts the opening degree of the flow rate adjustment valve 43 according to the temperature of the compressed air A2 detected by the first temperature sensor 71 and the second temperature sensor 72. That is, the control unit 73 reduces the opening degree of the flow rate adjusting valve 43 when the temperature difference between the compressed air A2 detected by the temperature sensors 71 and 72 becomes larger than a predetermined temperature difference set in advance. Then, 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 is within a predetermined temperature difference.

  The first heat exchanger 32B normally operates with the opening of the flow rate adjustment valve 43 set to 100% (fully open). That is, the flow rate of the compressed air A2 supplied from the compressed air branch line 27 to the first heat exchange part 41 and the second heat exchange part 42 via the first branch flow path 54a and the second branch flow path 54b is the same. It has become. When the compressed air A2 flows through the first heat exchange unit 41 and the second heat exchange unit 42, the compressed air A2 is cooled and discharged by exchanging heat with the cooling air AC.

  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 becomes larger than a predetermined temperature difference, the control unit 73 compresses the compressed air. It is determined that the flow rate of the compressed air A2 flowing through the branch line 27 has decreased. At this time, the control unit 73 reduces the opening degree of the flow rate adjustment valve 43 so that the temperature of the compressed air A2 detected by the first temperature sensor 71 and the second temperature sensor is within a predetermined temperature difference. Adjust the opening. Then, the flow rate of the compressed air A2 supplied to the second heat exchange part 42 via the second branch flow path 54b decreases, while being supplied to the first heat exchange part 41 via the first branch flow path 54a. The flow rate of the compressed air A2 increases relatively. When the flow rate of the compressed air A2 in the first heat exchange unit 41 increases, when the cooling air AC and the compressed air A2 exchange heat, the heat of the first heat exchange unit 41 is larger than the heat load of the second heat exchange unit 42. The load becomes high and supercooling is suppressed.

  In addition, the structure of the 1st heat exchanger 32 is not limited to what was mentioned above. As shown in FIG. 7, in the first heat exchanger 32C, the first temperature sensor 71 is provided in the first branch flow path 64b connected to the outlet header 62 in the first heat exchange section 41, and the first heat exchange is performed. The temperature of the compressed air A <b> 2 discharged from the unit 41 is detected and output to the control unit 73. The second temperature sensor 72 is provided in the second branch flow path 64c connected to the outlet header 63 in the second heat exchange unit 42, detects the temperature of the compressed air A2 discharged from the second heat exchange unit 42, Output to the control unit 73. The control unit 73 adjusts the opening degree of the flow rate adjustment valve 43 according to the temperature of the compressed air A2 detected by the first temperature sensor 71 and the second temperature sensor 72. That is, the control unit 73 reduces the opening degree of the flow rate adjusting valve 43 when the temperature difference between the compressed air A2 detected by the temperature sensors 71 and 72 becomes larger than a predetermined temperature difference set in advance. Then, 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 is within a predetermined temperature difference.

  Thus, in the heat exchanger of the second embodiment, heat is exchanged between 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, and the cooling air AC and the compressed air A2. And a plurality of heat exchanging portions 41 and 42 arranged in parallel in the flow direction of the cooling air AC, and a second heat exchanging portion located downstream of the cooling air AC in the flow direction of the plurality of heat exchanging portions 41 and 42 42, a flow rate adjusting valve 43 that adjusts the flow rate of the compressed air A2 flowing through the temperature sensor 42, temperature sensors 71 and 72 that detect the temperature of the compressed air A2, and flow rate adjustment according to the temperature of the compressed air A2 detected by the temperature sensors 71 and 72. A control unit 73 for adjusting the opening degree of the valve 43 is provided.

  Therefore, the compressed air A2 flowing through the plurality of heat exchange units 41 and 42 is cooled by exchanging heat with the cooling air AC. When the temperature of the compressed air A2 flowing through the plurality of heat exchanging parts 41 and 42 fluctuates, the cooling air in the plurality of heat exchanging parts 41 and 42 is adjusted to adjust the opening degree of the flow rate adjusting valve 43 according to the temperature of the compressed air A2. The flow rate of the compressed air A2 that flows through the second heat exchange unit 42 that is located on the downstream side in the AC flow direction is adjusted. Therefore, the cooling air AC has little influence on the heat exchanging parts 41 and 42, and high temperature and low temperature are suppressed. As a result, even if the flow rate of the compressed air A2 fluctuates, it is possible to suppress overcooling of the compressed air A2 by appropriately exchanging heat.

  In the heat exchanger according to the second embodiment, the control unit 73 controls the flow rate adjustment valve when the temperature difference of the compressed air A2 on the outlet side of the plurality of heat exchange units 41 and 42 becomes larger than a predetermined temperature difference set in advance. The opening degree of the flow rate adjusting valve 43 is adjusted so that the opening degree of the 43 is reduced and the temperature difference of the compressed air A2 is within a predetermined temperature difference. When the opening degree of the flow rate adjusting valve 43 is reduced, the flow rate of the compressed air A2 flowing through the second heat exchange unit 42 located on the downstream side in the flow direction of the cooling air AC decreases. Therefore, the influence which compressed air A2 has on the 1st heat exchange part 41 located in the upstream of the flow direction of cooling air AC decreases, and it can control overcooling of compressed air A2.

  And by suppressing supercooling of compressed air A2, a big heat load does not act on the structural members (for example, heat exchanger tubes, etc.) of the heat exchangers 41, 42, and an increase in plate thickness is unnecessary. An increase in manufacturing cost can be suppressed. Moreover, since overcooling of compressed air A2 is suppressed, generation | occurrence | production of the drain in the 2nd heat exchanger 42 is suppressed, and generation | occurrence | production of the rust by this drain can be prevented.

  In the first heat exchanger 32B, the flow rate adjustment valve 43 is provided in the second branch flow path 54b connected to the inlet header 52 of the second heat exchange unit 42. Further, in the first heat exchanger 32C, the flow rate adjustment valve 43 is provided in the second branch flow path 64c connected to the outlet header 63 of the second heat exchange unit 42. Therefore, the flow rate of the compressed air A2 flowing through the plurality of heat exchange units 41 and 42 can be adjusted with high accuracy.

[Third Embodiment]
FIG. 8 is a schematic configuration diagram of a heat exchanger according to the third embodiment, and FIG. 9 is a schematic configuration diagram of a heat exchanger representing a modification of the third embodiment. In addition, the same code | symbol is attached | subjected to the member which has the same function as embodiment mentioned above, and detailed description is abbreviate | omitted.

  In the third embodiment, as shown in FIG. 8, the first heat exchanger 32D includes a compressed air branch line 27, a cooling air line 28, a first heat exchange unit 41, a second heat exchange unit 42, It has a flow rate adjusting valve 43, a flow rate sensor 81 as a state detection sensor, and a control unit 73.

  The flow sensor 81 is provided in the compressed air branch line 27. The flow sensor 81 detects the flow rate (state) of the compressed air A <b> 2 flowing through the compressed air branch line 27 and outputs it to the control unit 73. The control unit 73 adjusts the opening degree of the flow rate adjustment valve 43 according to the flow rate of the compressed air A2 detected by the flow rate sensor 81. That is, the control unit 73 reduces the opening degree of the flow rate adjusting valve 43 when the flow rate of the compressed air A2 detected by the flow rate sensor 81 becomes smaller than a predetermined flow rate set in advance.

  The first heat exchanger 32 is normally operated with the flow rate adjustment valve 43 opened at 100% (fully open). That is, the flow rate of the compressed air A2 supplied from the compressed air branch line 27 to the first heat exchange part 41 and the second heat exchange part 42 via the first branch flow path 54a and the second branch flow path 54b is the same. It has become. When the compressed air A2 flows through the first heat exchange unit 41 and the second heat exchange unit 42, the compressed air A2 is cooled and discharged by exchanging heat with the cooling air AC.

  When the flow rate of the compressed air A2 supplied to the first heat exchange unit 41 is less than the predetermined flow rate, the control unit 73 decreases the opening degree of the flow rate adjustment valve 43. Then, the flow rate of the compressed air A2 supplied to the second heat exchange part 42 via the second branch flow path 54b decreases, while being supplied to the first heat exchange part 41 via the first branch flow path 54a. The flow rate of the compressed air A2 increases relatively. When the flow rate of the compressed air A2 in the first heat exchange unit 41 increases, when the cooling air AC and the compressed air A2 exchange heat, the heat of the first heat exchange unit 41 is larger than the heat load of the second heat exchange unit 42. The load becomes high and supercooling is suppressed.

  In addition, the structure of 1st heat exchanger 32D is not limited to what was mentioned above. As shown in FIG. 9, in the first heat exchanger 32E, the flow rate sensor 81 is provided in the compressed air branch line 27 to detect and control the flow rate of the compressed air A2 supplied to the heat exchange units 41 and 42. To the unit 73. The control unit 73 adjusts the opening degree of the flow rate adjustment valve 43 according to the temperature of the compressed air A2 detected by the flow rate sensor 81. That is, the control unit 73 reduces the opening degree of the flow rate adjusting valve 43 when the flow rate of the compressed air A2 detected by the flow rate sensor 81 becomes smaller than a predetermined flow rate set in advance.

  As described above, in the heat exchanger according to the third embodiment, the flow rate sensor 81 that detects the flow rate of the compressed air A2 and the flow rate of the compressed air A2 detected by the flow rate sensor 81 are less than a predetermined flow rate that is set in advance. A control unit 73 for reducing the opening degree of the flow rate adjusting valve 43 is provided.

  Therefore, when the flow rate of the compressed air A2 flowing through the plurality of heat exchange units 41 and 42 is less than a predetermined flow rate, the secondary fluid flowing through the second heat exchange unit 42 is used to reduce the opening degree of the flow rate adjustment valve 43. The flow rate decreases. Therefore, the influence which cooling air AC has on the 1st heat exchange part 41 decreases, and it can control overcooling of compressed air A2.

  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 limited to this configuration. is not. 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. And the control part 73 makes the opening degree of the flow regulating valve 43 small, when the pressure of the compressed air A2 which flows through the compressed air branch line 27 which the pressure sensor detected becomes larger than the predetermined pressure set beforehand. Even in this case, overcooling of the compressed air A2 can be suppressed.

[Fourth Embodiment]
FIG. 10 is a schematic configuration diagram of a heat exchanger according to the fourth embodiment. In addition, the same code | symbol is attached | subjected to the member which has the same function as embodiment mentioned above, and detailed description is abbreviate | omitted.

  In the fourth embodiment, as shown in FIG. 10, the first heat exchanger 90 includes a compressed air branch line 27, a cooling air line 28, four heat exchange units 91, 92, 93, 94, and a flow rate. It has adjustment valves 95, 96, 97, 98, a flow rate sensor (state detection sensor) 99, and a control unit 100.

  The first heat exchange part 91 is provided with an inlet header 101 at one end, the second heat exchange part 92 is provided with an inlet header 102 at one end, and the third heat exchange part 93 is provided with an inlet header 103 at one end. The fourth heat exchanging portion 94 is provided with an inlet header 104 at one end, and each of the heat exchangers 91, 92, 93, 94 is provided with an outlet header 105 at the other end. The compressed air branch line 27 is divided into a first branch flow path 105a, a second branch flow path 105b, a third branch flow path 105c, and a fourth branch flow path 105d as primary fluid supply paths. 103 and 104. Further, the compressed air branch line 27 is provided with a collective flow path 105 e as a primary fluid discharge path, and is connected to the outlet header 105.

  The flow rate adjusting valves 95, 96, 97, 98 are provided in the respective branch flow paths 105a, 105b, 105c, 105d, and the flow rate of the compressed air A2 flowing through the second branch flow paths 105a, 105b, 105c, 105d is controlled. To be adjusted. The flow rate sensor 99 is provided in the compressed air branch line 27, detects the flow rate (state) of the compressed air A <b> 2 flowing through the compressed air branch line 27, and outputs it to the control unit 100. The control unit 100 adjusts the opening degree of the flow rate adjusting valves 95, 96, 97, and 98 according to 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 less than a predetermined flow rate set in advance, the control unit 100 decreases 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 exchange unit 91 is less than the predetermined flow rate, the control unit 100 adjusts the opening degree of the flow rate adjusting valves 95, 96, 97, 98, and the flow direction of the cooling air AC The flow rate is adjusted so that the heat exchange portions 91, 92, 93, and 94 on the downstream side of the air flow are reduced. Therefore, when the cooling air AC and the compressed air A2 exchange heat, the heat load increases toward the first heat exchanging portion 91 side, and overcooling is suppressed.

  In the fourth embodiment, the flow sensor 99 is applied as the state detector, but a temperature sensor or a pressure sensor may be used.

  Thus, in the heat exchanger of the fourth embodiment, a plurality of flow rate adjusting valves 95, 96, 97, 98 are provided corresponding to the plurality of heat exchange units 91, 92, 93, 94, and the control unit 100 is The flow rate of the compressed air A2 flowing through the heat exchanging portions 91, 92, 93, 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 portions 91, 92, 93, 94, the influence of the cooling air AC on the heat exchanging portions 91, 92, 93, 94 is reduced, and the compression is performed. Supercooling of the air A2 can be suppressed with high accuracy.

  In the above-described embodiment, each heat exchanging portion 41, 42, 91, 92, 93, 94 is configured by a straight heat transfer tube, but may be configured by a U-shaped heat transfer tube.

  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) AC. However, the present invention is limited to this configuration. Is not to be done. That is, the heat exchanger of the present invention can be applied to other parts of the gas turbine 10 and other fields (for example, a boiler) than the gas turbine 10.

  In the above-described embodiment, the heat exchanger that cools the secondary fluid with the primary fluid is used. However, a heat exchanger that heats the secondary fluid with the primary fluid may be used. In this case, overheating by the heat exchanger is suppressed. can do.

DESCRIPTION OF SYMBOLS 10 Gas turbine 11 Compressor 12 Combustor 13 Turbine 14 Generator 24 Fuel gas supply line 26 Heat exchange apparatus 27 Compressed air branch line (primary flow path)
28 Cooling air line (secondary flow path)
32, 32A, 32B, 32C, 32D, 32E, 90 First heat exchanger 33 Second heat exchanger (heat exchanger)
41,91 1st heat exchange part 42,92 2nd heat exchange part 43,95,96,97,98 Flow control valve 71,72 Temperature sensor (state quantity detection sensor)
73,100 Control unit 81,99 Flow sensor (state quantity detection sensor)
AC cooling air (secondary fluid)
A2 Compressed air (primary fluid)

Claims (8)

A primary flow path through which the primary fluid flows;
A secondary channel through which a secondary fluid flows in the primary channel;
A plurality of heat exchanging units that perform heat exchange between the primary fluid and the secondary fluid and are arranged in parallel in the flow direction of the primary fluid;
A flow rate adjusting valve that adjusts the flow rate of the primary fluid flowing through the plurality of heat exchange units;
The heat exchanger characterized by having. A primary flow path through which the primary fluid flows;
A secondary channel through which a secondary fluid flows in the primary channel;
A plurality of heat exchanging units that perform heat exchange between the primary fluid and the secondary fluid and are arranged in parallel in the flow direction of the primary fluid;
A flow rate adjusting valve that adjusts the flow rate of the primary fluid flowing through the plurality of heat exchange units;
A state detection sensor for detecting the state of the primary fluid;
A controller that adjusts the opening of the flow rate adjustment valve according to the state of the primary fluid detected by the state detection sensor;
The heat exchanger characterized by having.   The plurality of heat exchanging units are provided with individual inlet headers 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. The heat exchanger according to claim 2, wherein the flow rate adjusting valve is provided in the primary fluid flow path connected to a header.   The plurality of heat exchanging portions are provided with a common inlet header at one end, and provided with an individual outlet header at the other end, and the primary flow path is connected to the inlet header and the outlet header, and the outlet The heat exchanger according to claim 2, wherein the flow rate adjusting valve is provided in the primary fluid flow path connected to a header.   The state detection sensor is a temperature sensor that detects the temperature of the primary fluid on the outlet side of the plurality of heat exchange units, and the control unit is configured so that the temperature difference of the primary fluid on the outlet side of the plurality of heat exchange units is in advance. The heat exchanger according to any one of claims 2 to 4, wherein when the temperature difference becomes larger than a set predetermined temperature difference, the opening degree of the flow rate adjusting valve is reduced.   The state detection sensor is a flow rate sensor that detects the flow rate of the primary fluid on the inlet side of the plurality of heat exchange units, and the control unit presets the flow rate of the primary fluid on the inlet side of the plurality of heat exchange units. The heat exchanger according to any one of claims 2 to 4, wherein when the flow rate becomes smaller than the predetermined flow rate, the opening degree of the flow rate adjustment valve is reduced.   The state detection sensor is a pressure sensor that detects the pressure of the primary fluid on the inlet side of the plurality of heat exchange units, and the control unit presets the pressure of the primary fluid on the inlet side of the plurality of heat exchange units. The heat exchanger according to any one of claims 2 to 4, wherein when the pressure exceeds a predetermined pressure, the opening of the flow rate adjustment valve is reduced.   A plurality of the flow rate adjusting valves are provided corresponding to the plurality of heat exchange units, and the control unit is configured to control the primary fluid flowing through the plurality of heat exchange units according to the state of the primary fluid detected by the state detection sensor. The heat exchanger according to any one of claims 2 to 7, wherein the openings of the plurality of flow rate adjustment valves are adjusted so that the flow rate decreases.

Images