JP2010164244A - Primary heat transfer surface heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a cross flow type primary heat transfer surface heat exchanger having a simple structure and reducing the number of components and improving heat exchange efficiency. <P>SOLUTION: In the primary heat transfer surface heat exchanger, high-temperature fluid passages 6 and low-temperature fluid passages 7 are alternately formed between layers formed by laminating corrugated fins 3. The primary surface heat exchanger includes a heat transfer core 2 in which main flowing directions of fluid H, L in the respective fluid passages 6, 7 intersect with each other, and the main flowing directions of the fluid H, L in the respective fluid passages 6, 7 intersect with ridges 3 of all of the corrugated fins 3 forming the fluid passages 6, 7. In the heat exchanger, it is preferable that the ridges 3b of the corrugated fins 3 laminated on each other intersect with each other within a range of 60-120° of an angle and that the main flowing directions of the fluid H, L intersect with the ridges 3b of all of the corrugated fins 3 at the same angle. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a primary heat transfer type heat exchanger having a heat transfer core in which corrugated fins are stacked and a high-temperature fluid passage and a low-temperature fluid passage are alternately formed between the layers, and in particular, in each fluid passage in the heat transfer core. The present invention relates to a cross-flow type primary surface heat exchanger in which the main flow directions of the fluids cross each other.

  In recent years, a distributed energy system has been promising from the viewpoint of effective use of energy, and heat engines such as small gas turbines and high-temperature fuel cells that generate electricity directly from fuel through chemical processes have been actively developed. Yes. In these distributed energy systems, the exhaust heat recovery performance greatly affects the performance of the gas turbine and the high-temperature fuel cell. Therefore, it is required to use a high-performance heat exchanger capable of effective heat exchange.

  In addition, various high-performance heat exchangers are installed in aircraft. For example, a heat exchanger for recovering exhaust heat from the turbine engine and an intercooler that reduces the temperature of compressed air flowing into the compressor of the turbine engine with outside air are typical. In addition, there are heat exchangers that cool engine oil with outside air and heat exchangers that cool air for cooling components such as bearings with outside air.

  As heat exchangers used in gas turbines, high-temperature fuel cells, aircraft, and the like, shell and tube heat exchangers, finned tube heat exchangers, and plate fin heat exchangers are generally known.

  However, the shell and tube heat exchanger and the fin tube heat exchanger are simple and inexpensive, but they are inferior in compactness. On the other hand, the plate fin type heat exchanger can achieve high heat exchange efficiency and can be downsized by selecting the laminated arrangement of the high-temperature fluid passage and the low-temperature fluid passage. It is. For this reason, use of any heat exchanger has been limited.

  In addition, these heat exchangers have a heat transfer core that exchanges heat between a high-temperature fluid and a low-temperature fluid. When a header and a nozzle serving as an inflow / outflow portion of each fluid are attached to the heat transfer core, Welding is essential. For this reason, conventionally, it is necessary to consider welding heat input that affects the performance of the heat transfer core and to consider the introduction of an automatic welder in order to reduce the cost of the heat exchanger. In terms of condition setting and capital investment, a great amount of man-hours and costs were considered problems.

  On the other hand, in recent years, instead of a shell-and-tube heat exchanger, a fin-tube heat exchanger, and a plate fin-type heat exchanger, for example, a primary transmission type heat exchanger disclosed in Patent Document 1 has been adopted. It is being considered.

  In the primary heat transfer type heat exchanger, corrugated fins are stacked as a heat transfer core to form a high-temperature fluid passage and a low-temperature fluid passage between each layer, and a high-temperature fluid passage and a low-temperature fluid passage are formed of corrugated fins as a heat transfer surface. It is the structure which partitions off, and heat exchange is performed only between a corrugated fin between the high temperature fluid and low temperature fluid which distribute | circulate each fluid passage.

  Since the heat transfer area between the high temperature fluid and the low temperature fluid can be largely secured by the corrugated fin, the primary surface heat transfer type heat exchanger is extremely excellent in heat exchange efficiency. Further, since the primary transmission type heat exchanger can reduce the tube plate which is essential in the case of the plate fin type heat exchanger, the number of parts can be reduced and the manufacturing cost required for assembly can be suppressed.

  FIG. 1 is a view showing an example of a corrugated fin used in a heat transfer core of a conventional primary surface heat exchanger. FIG. 1 (a) is a perspective view of corrugated fins stacked on each other, and FIG. ) Shows plan views of the corrugated fins, respectively. As shown in the figure, the conventional corrugated fin 3 is made of a thin alloy sheet such as stainless steel, which is formed into a corrugated shape, and has a rectangular shape as a whole.

  The corrugated fin 3 shown in FIG. 1 has an outer peripheral portion 3a that is crushed by press working, and the crushed outer peripheral portion 3a has a fluid passage between the corrugated fins 3 stacked on each other. The spacer bar 4 shown in 2 is joined. In such a conventional corrugated fin 3, each ridge 3b which becomes a wave-like top is arranged in parallel to both ends (at right angles to the other ends).

  2A and 2B are diagrams showing a configuration example of a heat transfer core in a conventional primary transfer heat exchanger, in which FIG. 2A is a perspective view and FIG. 2B is a plan view with a side plate removed. FIG. 3C is a front view of the outlet of the hot fluid passage, and FIG. 4D is a front view of the outlet of the cold fluid passage. The heat transfer core 2 of the conventional primary surface heat exchanger shown in the figure is configured using the corrugated fins 3 shown in FIG.

  Specifically, in the corrugated fin 3, a pair of spacer bars 4 are joined to both end portions of the crushed outer peripheral portion 3a and the other end portions on the back surface thereof. The heat transfer core 2 is configured by stacking the corrugated fins 3 to which the spacer bars 4 are joined and welding the spacer bars 4 that overlap each other. Side plates 5 are brazed to the corrugated fins 3 arranged at the uppermost and lowermost stages of the heat transfer core 2.

  In this heat transfer core 2, the corrugated fins 3 b of the laminated corrugated fins 3 are arranged so as to be orthogonal to each other, and the high temperature fluid passage 6 and the low temperature fluid passage 7 are alternately formed between the corrugated fins 3. 2B, the high temperature fluid H flowing through the high temperature fluid passage 6 and the low temperature fluid L flowing through the low temperature fluid passage 7 are respectively the fluid passage 6 in the heat transfer core 2, 7 flows from the inlet to the outlet as the main flow direction, and the main flow directions are orthogonal to each other.

  The primary surface heat exchanger having such a heat transfer core 2 is formed as a cross flow type heat exchanger in which the main flow directions of the fluids H and L are orthogonal to each other. In the primary transmission type heat exchanger, the fluids H and L in the fluid passages 6 and 7 flow along one flange 3b of the corrugated fins 3 forming the fluid passages 6 and 7, In the process, heat exchange can be efficiently performed through the corrugated fins 3 that partition the two.

International Publication WO2008 / 143318 Pamphlet

  As described above, primary heat transfer type heat exchangers can achieve higher heat exchange efficiency and lower assembly costs than shell and tube type heat exchangers, finned tube type heat exchangers, and plate fin type heat exchangers. Suppression can also be expected.

  However, the practical use of primary transmission type heat exchangers requires higher performance and lower cost, and therefore, the structure is simpler and easier to assemble, and components such as countercurrent heat It is required that the distributor, which is essential for the exchanger, can be reduced, and that further excellent heat exchange efficiency can be realized. In particular, a primary transmission type heat exchanger used in an aircraft is required to be further compact and lightweight.

  The present invention has been made in view of the above-described requirements, and an object thereof is to provide a primary transmission type heat exchanger capable of reducing the number of parts with a simple structure and improving heat exchange efficiency. To do.

  In order to achieve the above object, the present inventors pay attention to the arrangement relationship between the main flow direction of the fluid in each fluid passage and the corrugated fin ridge in the primary transmission type heat exchanger, and CFD (Computational Fluid Dynamics) Analysis and various tests were conducted, and extensive studies were made. As a result, in order to reduce the number of parts with a simple structure and further improve the heat exchange efficiency, a cross flow method in which the main flow directions of the fluid in each fluid passage intersect each other is adopted, and the main flow direction of each fluid is changed. It has been found that it is effective to dispose not only the corrugated fin of one corrugated fin forming the fluid passage but also the corrugated fin of any corrugated fin.

  This invention is completed based on said knowledge, The summary exists in the following primary transmission type heat exchanger. That is, in a primary surface heat transfer type heat exchanger having a heat transfer core in which corrugated fins are stacked to alternately form high-temperature fluid passages and low-temperature fluid passages between the layers, and the main flow directions of the fluid in each fluid passage intersect each other. The primary flow surface type heat exchanger is characterized in that the main flow direction of the fluid in each fluid passage intersects with the corrugated fins of any corrugated fin forming the fluid passage.

  In this heat exchanger, the corrugated fins stacked on each other intersect each other within an angle range of 60 ° to 120 °, and the main flow direction of the fluid in each fluid passage is that of any corrugated fin forming the fluid passage. It is preferable to intersect with the ridge at an equal angle.

  In the above heat exchanger, one of the fluids is a gas and the other is a liquid, and the angle at which the main flow direction of the gas intersects the corrugated fins is such that the main flow direction of the liquid is the corrugated fin. It is preferable that the angle is smaller than the angle crossing the ridge. This is because the pressure loss of the gas that is easily affected by the flow path resistance can be suppressed.

  The heat exchanger includes a casing in which the heat transfer core is provided, an inlet header and an inlet nozzle that form an inflow portion of each fluid to the heat transfer core, and each fluid from the heat transfer core. An outlet header and an outlet nozzle that respectively form an outflow portion of the heat transfer core, and a spacer bar that secures the fluid passage is joined to an outer peripheral portion of the corrugated fin that is crushed by pressing. The corrugated fins to which spacer bars are joined are stacked in the casing, the heat transfer core, the casing, the inlet header and inlet nozzle, the outlet header and outlet nozzle, It is preferable to join by brazing. This is because joining by brazing can reduce deformation at the time of joining and suppress the generation of thermal stress compared to joining by welding. This is because the working time required for welding can be shortened and the manufacturing cost can be reduced.

  Further, in the above heat exchanger, the heat transfer core is joined to the outer peripheral portion of the corrugated fin that is crushed by pressing, and a spacer bar that secures the fluid passage is joined, and the spacer bar is joined. Corrugated fins are stacked in the casing, and both end portions of the spacer bar protrude from the outer peripheral portion of the corrugated fin, and both end portions can be fitted into the casing. By doing so, when assembling the heat exchanger, spacer bar and corrugated fin positioning jigs are unnecessary, and the assembly is facilitated.

  Such a primary transmission type heat exchanger can be reduced in size and weight as the heat exchange efficiency is improved, and thus can be suitably employed as an aircraft heat exchanger.

  According to the primary transmission type heat exchanger of the present invention, since the main flow direction of the fluid in each fluid passage intersects with any corrugated fin, both fluids form the fluid passage. The turbulent flow effect is promoted by flowing while passing over the fins in order, and in this process, the corrugated fins that partition the two can be effectively contacted to perform heat exchange efficiently, thereby improving the heat exchange efficiency. It becomes possible. For this reason, it can be set as a more compact and lightweight heat exchanger compared with the conventional primary transmission type heat exchanger which has the same heat exchange performance. In addition, since the cross-flow method is adopted, a distributor is not required, the number of parts can be reduced, and the structure is simplified.

It is a figure which shows an example of the corrugated fin used for the heat transfer core of the conventional primary surface-type heat exchanger, The figure (a) is a perspective view of the corrugated fin laminated | stacked mutually, The figure (b) is those figures. The top view of a corrugated fin is shown, respectively. It is a figure which shows the structural example of the heat transfer core in the conventional primary surface-type heat exchanger, The figure (a) is a perspective view, The figure (b) is a top view in the state except the side plate, The figure (C) is a front view of the outlet of the high-temperature fluid passage, and (d) is a front view of the outlet of the low-temperature fluid passage. It is a figure which shows an example of the corrugated fin used for the heat-transfer core of the primary surface type heat exchanger of this invention, The figure (a) is a perspective view of the corrugated fin laminated | stacked mutually, The figure (b) is them Plan views of corrugated fins are respectively shown. It is a figure which shows the structural example of the heat-transfer core in the primary surface-type heat exchanger of this invention, The figure (a) is a perspective view, The figure (b) is a top view in the state except the side plate, FIG. 3C is a front view of the outlet of the high temperature fluid passage, and FIG. 4D is a front view of the outlet of the low temperature fluid passage. It is a figure which shows the other structural example of the heat transfer core in the primary surface type heat exchanger of this invention, The figure (a) is a top view which shows the corrugated fin laminated | stacked mutually, The figure (b) is the figure. The top view in the state which removed the side plate of the heat-transfer core is each shown. It is a figure which shows the result of having evaluated the performance of the heat-transfer core by the CFD analysis which distribute | circulated the fluid to the fluid channel | path formed between corrugated fins, The figure (a) is the crossing angle | corner ( The relationship between the sandwiching angle) and the pressure loss is shown, and FIG. 5B shows the relationship between the sandwiching angle and the heat transfer performance. It is a top view which shows the example of whole structure of the primary transmission type heat exchanger of this invention.

  Embodiments of a cross-flow type primary surface heat exchanger of the present invention will be described in detail below with reference to the drawings.

  FIG. 3 is a view showing an example of the corrugated fin used in the heat transfer core of the primary surface heat exchanger of the present invention. FIG. 3 (a) is a perspective view of the corrugated fins stacked on each other. b) shows plan views of the corrugated fins. As shown in the figure, the corrugated fin 3 used in the primary transmission type heat exchanger of the present invention is made of a thin alloy sheet and formed into a corrugated shape so as to have a pleating property. It is a shape.

  As for the corrugated fin 3 shown in FIG. 3, the outer peripheral part 3a is crushed by press work. A spacer bar 4 shown in FIG. 4 to be described later is joined to the crushed outer peripheral portion 3a to secure a fluid passage between the corrugated fins 3 stacked on each other.

  In the corrugated fin 3 according to the present invention, the corrugated fins 3b serving as the wave-like top portions are not parallel to both end portions (not perpendicular to the other end portions) on the front and back surfaces of the region excluding the outer peripheral portion 3a. In contrast, they are inclined at a predetermined angle. FIG. 3 illustrates a state in which the flange 3b of the corrugated fin 3 is inclined at 30 ° with respect to both end portions.

  For the alloy sheet as the material of the corrugated fin 3, it is preferable to use a stainless steel material, a Ni-based super heat-resistant alloy, an aluminum alloy, or the like having high strength and excellent heat resistance. As the stainless steel material, for example, SUS347, SUS321, SUS310, SUS310S, SUS304 or the like can be used, and as the Ni-based superalloy, for example, Inconel 625 or the like can be used. Moreover, 3003, 4004, 6951 etc. are applicable as an aluminum alloy.

  The thickness of the alloy sheet is preferably in the range of 0.06 to 0.15 mm, particularly about 0.10 mm, so that the alloy sheet can be formed into a fine corrugated shape and the outer peripheral portion 3a can be pressed.

  Further, the corrugated fins 3 are preferably set to have a number of fins 3b per unit length, that is, the number of fins of 20 to 30 fin / inch so that the heat transfer area and strength can be maintained while maintaining compactness. More preferably, it is 25 fin / inch or more. From the same viewpoint, the height of the flange 3b, that is, the fin height is preferably 1.5 to 3.0 mm, and more preferably 2.5 mm or less.

  FIG. 4 is a view showing a configuration example of a heat transfer core in a primary surface heat transfer heat exchanger according to the present invention, where FIG. 4 (a) is a perspective view, and FIG. FIG. 4C is a plan view, FIG. 3C is a front view of the outlet of the hot fluid passage, and FIG. The heat transfer core 2 of the primary surface heat exchanger of the present invention shown in the figure is configured using the corrugated fins 3 shown in FIG.

  Specifically, in the corrugated fin 3, a pair of spacer bars 4 are joined to both ends of the crushed outer peripheral portion 3a, and a pair of spacer bars 4 are joined to the other end portions on the back surface. . The heat transfer core 2 is configured by stacking the corrugated fins 3 to which the spacer bars 4 are joined and joining the spacer bars 4 that overlap each other. Side plates 5 are brazed to the corrugated fins 3 arranged at the uppermost and lowermost stages of the heat transfer core 2.

  In this heat transfer core 2, the corrugated fins 3 b of the corrugated fins 3 are arranged so that the corrugated fins 3 b of the laminated corrugated fins 3 cross each other at a predetermined angle. The hot fluid passage 6 and the cold fluid passage 7 are alternately formed. And as shown by the solid line arrow in FIG.4 (b), the high temperature fluid H which distribute | circulates the high temperature fluid channel | path 6, and the low temperature fluid L which distribute | circulates the low temperature fluid channel | path 7 are the fluid channel | path 6 in the heat-transfer core 2, respectively. 7 flows from the inlet to the outlet as the main flow direction, and the main flow directions are orthogonal to each other.

  In the heat transfer core 2 shown in FIG. 4, the corrugated fins 3 b forming the high temperature fluid passage 6 intersect at an angle θ 1 of 60 °, and the corrugated fin 3 forming the low temperature fluid passage 7 has a flange 3 b of 120 °. The state which cross | intersected by angle (theta) 2 of this is illustrated. In the following description, the crossing angles θ1 and θ2 of the flanges 3b of the laminated corrugated fins 3 are also referred to as “sandwich angles”.

  The main flow direction of the high-temperature fluid H intersects the ridges 3b of both corrugated fins 3 forming the high-temperature fluid passage 6, and intersects with any ridge 3b at an equal angle (30 °). Similarly, the main flow direction of the cryogenic fluid L intersects with the ridges 3b of both corrugated fins 3 forming the cryogenic fluid passage 7, and intersects with any ridge 3b at an equal angle (60 °). That is, in the present embodiment, the corrugated fins 3 of the corrugated fins 3 are arranged symmetrically with respect to the main flow directions of the fluids H and L in the fluid passages 6 and 7.

  The primary surface heat exchanger having such a heat transfer core 2 is formed as a cross flow type heat exchanger in which the main flow directions of the fluids H and L are orthogonal to each other. In this primary transmission type heat exchanger, the fluids H and L in the fluid passages 6 and 7 are disturbed by flowing while passing over the flanges 3b of both corrugated fins 3 forming the fluid passages 6 and 7 in sequence. The flow effect is promoted, and in the process, heat exchange can be performed efficiently through the corrugated fins 3 that partition the two. At that time, since the fluids H and L are effectively in contact with both corrugated fins 3 forming the fluid passages 6 and 7, the primary transmission type heat exchanger according to the present invention is a primary cross-flow type primary. The heat exchange efficiency can be improved as compared with the transmission type heat exchanger. As a result, it is possible to make the heat exchanger more compact and lighter than the conventional primary transmission type heat exchanger having the same heat exchange performance.

  FIG. 5 is a view showing another configuration example of the heat transfer core in the primary surface transfer heat exchanger according to the present invention. FIG. 5 (a) is a plan view showing the corrugated fins stacked on each other, and FIG. (B) has each shown the top view in the state except the side plate of the heat-transfer core. As shown in FIG. 5 (a), the corrugated fins 3 of the present embodiment are formed into a parallelogram as a whole, and in the same manner as the corrugated fins 3 shown in FIG. Provided with the heel 3b.

  In the heat transfer core 2 configured by laminating the corrugated fins 3 shown in FIG. 5A, as shown by the solid line arrow in FIG. 5B, the high-temperature fluid H flowing through the high-temperature fluid passage 6 and the low-temperature fluid The low-temperature fluid L flowing through the passage 7 flows in the direction from the inlet to the outlet of the heat transfer core 2 as the main flow direction, and the main flow directions are inclined and intersect with each other. That is, the primary surface heat exchanger having such a heat transfer core 2 is formed as an oblique AC heat exchanger.

  In this oblique AC type primary transmission type heat exchanger, as in the cross flow type primary transmission type heat exchanger described above, the fluids H and L in the fluid passages 6 and 7 are transferred to the fluid passages 6 and 7. 7, the corrugated fins 3 of the two corrugated fins 3 that flow through the corrugated fins 3 sequentially flow, so that both the corrugated fins 3 can be effectively brought into contact with each other by the turbulent flow effect, thereby improving the heat exchange efficiency.

  Therefore, a cross flow method in which the main flow directions of the fluids flowing through each fluid passage intersect each other, such as a cross flow method and a diagonal alternating current method, is adopted, and any corrugation that forms the fluid passages by the main flow direction of each fluid. By adopting a primary transmission type heat exchanger that is arranged so as to intersect with the fin ridges, it is possible to realize a more compact and lighter weight than a conventional primary transmission type heat exchanger having the same heat exchange performance. It becomes possible.

  Since the heat exchanger of the present invention is a cross-flow system, it is not necessary to install a distributor section, which is essential in the counter-current system, and since it is a primary transmission type heat exchanger, a plate fin type heat exchanger As a result, the tube plate that is essential is also unnecessary, and as a result, the number of parts can be reduced and the structure can be simplified.

  A suitable range of the sandwiching angles θ1 and θ2 shown in FIG.

  FIG. 6 is a diagram showing the results of evaluating the performance of the heat transfer core by CFD analysis in which fluid is circulated through the fluid passage formed between the corrugated fins. FIG. 6A shows the relationship between the sandwiching angle and the pressure loss. FIG. 4B shows the relationship between the included angle and the heat transfer performance. In the figure, under the condition that the corrugated fin ridges are arranged symmetrically with respect to the main flow direction of the fluid, the analysis is performed by changing the sandwiching angle by 20 ° from 40 to 140 ° in increments of 60 °. The pressure loss and heat transfer performance at each sandwich angle are displayed using the ratio 1).

  As shown in FIGS. 6A and 6B, both the pressure loss and the heat transfer performance of the fluid passage increase as the sandwiching angle increases. That is, if the sandwiching angle is set to be large, the flow resistance increases when the fluid flows through the fluid passage while sequentially passing over the corrugated fins, and the heat transfer performance increases accordingly. For this reason, in order to obtain excellent heat exchange efficiency, it is preferable to set the sandwiching angle large.

  However, as shown in FIG. 6A, when the sandwich angle exceeds 120 °, the pressure loss increases rapidly. This means that the flow path resistance becomes significant, which hinders the use of the heat exchanger. For this reason, in order to ensure excellent heat exchange efficiency without any problem in use, it is desirable to set the sandwich angle within a range of 60 ° to 120 °.

  In the heat transfer core 2 shown in FIGS. 4 and 5, a gas such as air or gas and a liquid such as cooling water or hot water can be adopted as the fluids H and L to be heat exchanged. Moreover, both can employ | adopt gas and both can also employ | adopt a liquid.

  When gas and liquid are employed as the fluids H and L, for example, gas is supplied to the heat transfer core 2 by a fan or blower, and liquid is supplied to the heat transfer core 2 by a pump. In this case, since the gas feeding force by the fan or blower is lower than the liquid feeding force by the pump, if the gas flow path resistance is excessive in the heat transfer core 2, the gas cannot be sufficiently supplied. For this reason, it is preferable to reduce the flow resistance in the heat transfer core 2 in the fluid passage through which the gas flows rather than in the fluid passage through which the liquid flows. Is preferably set to be smaller than the angle at which the main flow direction of the liquid intersects the corrugated fins 3b. This configuration is also effective for suppressing gas pressure loss because gas is more susceptible to flow path resistance than liquid.

  A configuration in which the primary transmission type heat exchanger of the present invention can be applied practically will be described.

  FIG. 7 is a plan view showing an example of the entire configuration of the primary transmission type heat exchanger of the present invention. In the same figure, the side plate 5 on the upper surface side is partially broken.

  As shown in the drawing, the primary heat transfer type heat exchanger 1 includes a casing 8 in which a heat transfer core 2 is installed, an inlet header 9a for high-temperature fluid, an inlet nozzle 10a, an outlet header 11a, and an outlet side. The nozzle 12a is composed of a low temperature fluid inlet header 9b, an inlet nozzle 10b, an outlet header 11b, and an outlet nozzle 12b. The inlet headers 9a and 9b and the inlet nozzles 10a and 10b form inflow portions of the fluids H and L to the heat transfer core 2, respectively. The outlet headers 11a and 11b and the outlet nozzles 12a and 11b form outlet portions of the fluids H and L from the heat transfer core 2, respectively.

  When assembling the heat exchanger 1 having such a configuration, the corrugated fins 3 to which the spacer bars 4 are joined are stacked in the casing 8 before the side plates 5 on the upper surface side are attached. At this time, both end portions 4 a of the spacer bar 4 are formed in advance so as to protrude from the outer peripheral portion of the corrugated fin 3, and the end portions 4 a of the spacer bar 4 protruding from each corner of the corrugated fin 3 are fitted into the casing 8. Thus, the corrugated fins 3 and the spacer bars 4 can be positioned with respect to the casing 8. This eliminates the need for a separate positioning jig and facilitates assembly.

  The side plates 5 are arranged so as to cover the uppermost corrugated fins 3 in the casing 8, and the inlet headers 9 a, 9 b and the side headers 9 a, 9 b and so as to cover each side surface of the casing 8 including the side plate 5 as an upper surface. The inlet nozzles 10a and 10b, the outlet headers 11a and 11b, and the outlet nozzles 12a and 12b are arranged, and these are integrally heated and brazed. Thereby, the laminated corrugated fins 3 are brazed and joined, and at the same time, the casing 8, the inlet headers 9a and 9b and the inlet nozzles 10a and 10b, and the outlet headers 11a and 11b and the outlet nozzle. 12a, 12b can be brazed and joined, and the primary transmission type heat exchanger 1 can be comprised.

  With such a configuration, when assembling the primary transmission type heat exchanger, the welding work can be reduced, and the entire heat exchanger can be joined by a single heat treatment. It is not necessary to consider heat and to consider the introduction of an automatic welder, and it is possible to further reduce the cost required for assembling the heat exchanger. And compared with the joining by welding, the deformation | transformation of the heat-transfer core at the time of joining can be made small, and generation | occurrence | production of a thermal stress can be suppressed.

  However, the heat transfer core 2 composed of the laminated corrugated fins 3, the casing 8, the headers 9a, 9b, 11a, 11b and the nozzles 10a, 10b, 12a, 12b are not joined by a single heat treatment. It is also possible to join them individually by welding or the like.

  As described above, the primary transmission type heat exchanger of the present invention adopting the cross flow method can be reduced in size and weight as the heat exchange efficiency is improved, and is therefore suitably used as an aircraft heat exchanger. can do.

  In addition, the present invention is not limited to the above-described embodiment, and various modifications can be made without departing from the spirit of the present invention. For example, in the above-described embodiment, the corrugated fin is a plain type in which wrinkles that are wavy apexes are arranged in a straight line, but a herringbone type in which fin fins are arranged in a meandering manner can also be adopted. This is because the corrugated fin can function as a primary heat transfer type heat exchanger as long as the corrugated fin has no holes or cuts.

  3 and 4 show a state in which the main flow direction of the fluid in each fluid passage intersects with the corrugated fins of any corrugated fin forming the fluid passage at the same angle. And the angle intersecting the other eyelid may be different. That is, in each fluid passage, fin fins can be arranged asymmetrically with respect to the main flow direction of each fluid. This is because, as long as the main flow direction of each fluid intersects with the corrugated fin ridges, the fins are effectively in contact with any fin, so that the heat exchange efficiency can be improved.

  According to the primary transmission type heat exchanger of the present invention, since the main flow direction of the fluid in each fluid passage intersects with any corrugated fin, both fluids form the fluid passage. The corrugated fins flow while passing over the corrugated fins one after another, and in the process, the corrugated fins partitioning the two can be effectively contacted so that heat can be exchanged efficiently and the heat exchange efficiency can be improved. Further, with the adoption of the cross flow method, the number of parts can be reduced and the structure is simplified.

  Therefore, the primary transmission type heat exchanger of the present invention can be configured at low cost while sufficiently ensuring heat exchange performance, and can be widely applied as a heat exchanger used in a distributed energy system, an aircraft, or the like.

1: primary heat transfer type heat exchanger, 2: heat transfer core,
3: Corrugated fin, 3a: outer peripheral part, 3b: collar,
4: spacer bar, 4a: end, 5: side plate,
6: high temperature fluid passage, 7: low temperature fluid passage, 8: casing
9a, 9b: incoming header, 10a, 10b: incoming nozzle,
11a, 11b: outlet header, 12a, 12b: outlet nozzle,
H: High temperature fluid, L: Low temperature fluid

Claims (6)

In the primary surface heat transfer type heat exchanger having a heat transfer core in which high-temperature fluid passages and low-temperature fluid passages are alternately formed between each layer by laminating corrugated fins, and the main flow directions of the fluid in each fluid passage intersect each other,
A primary heat transfer type heat exchanger characterized in that a main flow direction of a fluid in each fluid passage intersects with a corrugated fin ridge forming the fluid passage. Corrugated fin ridges stacked on each other intersect within an angle of 60 ° to 120 °,
2. The primary surface heat exchanger according to claim 1, wherein a main flow direction of the fluid in each fluid passage intersects with a corrugated fin of each corrugated fin forming the fluid passage at an equal angle. One of the fluids is a gas and the other is a liquid;
3. The primary transmission type according to claim 1, wherein an angle at which a main flow direction of the gas intersects with the corrugated fin ridge is smaller than an angle at which the liquid main flow direction intersects with the corrugated fin ridge. Heat exchanger. A casing in which the heat transfer core is provided, an inlet header and an inlet nozzle that form an inflow portion of each fluid to the heat transfer core, and an outflow portion of each fluid from the heat transfer core, respectively. An outlet header and an outlet nozzle;
In the heat transfer core, a spacer bar that secures the fluid passage is joined to an outer peripheral portion of the corrugated fin that is crushed by pressing, and the corrugated fin to which the spacer bar is joined is stacked in the casing. Become
The heat transfer core, the casing, the inlet header and inlet nozzle, and the outlet header and outlet nozzle are joined by brazing. Primary heat transfer type heat exchanger as described. The heat transfer core is formed by joining a spacer bar that secures the fluid passage to an outer peripheral portion of the corrugated fin that has been crushed by press working, and the corrugated fin to which the spacer bar is joined is stacked in a casing. ,
The primary transfer type heat exchanger according to any one of claims 1 to 4, wherein both end portions of the spacer bar protrude from an outer peripheral portion of the corrugated fin, and both end portions are fitted into the casing.   The primary-surface-transfer heat exchanger according to any one of claims 1 to 5, wherein the primary-surface-transfer heat exchanger is an aircraft heat exchanger.

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