JP2014016083A - Heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress drift current of a fluid passing through a core, in a heat exchanger 1 including a core 2 having at least a first passage 21 where a first fluid flows and a second passage 22 where a second fluid flows.SOLUTION: A first passage includes a plurality of channels connecting an inflow port opening at an inflow surface 31 of a core and an outflow port opening at an outflow surface 32, and between the channels, a flow passage resistance is different from each other. A heat exchanger is disposed on the inflow surface side relative to the core, and includes: a first type rectification member 51 for equalizing dynamic pressure distribution to the inflow surface of a first fluid flowing into the core; and a second type rectification member 52 for reducing passage flow rate difference resulting from the flow passage resistance difference between the channels.

Description

  The technology disclosed herein relates to a heat exchanger, and more particularly to a structure of a heat exchanger that can suppress a drift of a fluid passing through a core that is a heat transfer section.

  Conventionally, due to the shape and arrangement of header tanks and nozzles in the heat exchanger, there is a known drift phenomenon that the flow distribution of the fluid passing through the core of the heat exchanger is not uniform and is biased. . For example, in Patent Document 1, the shape of the header tank is elongated from the opening position of the inflow nozzle toward the back side in the fluid inflow direction, so that the core is far from the nozzle opening. In a plate fin type heat exchanger where the flow rate of the back side part is greater than the flow rate of the near side part near the nozzle opening, a baffle plate (rectifier) may be placed in the header tank. Have been described. The fluid flowing into the header tank through the nozzle is prevented from flowing to the back side of the header tank by interfering with the baffle plate, and the drift of the fluid passing through the core is suppressed.

  Similarly, in Patent Document 2, in a plate fin type heat exchanger having a header tank that extends vertically downward from the upper end position where the inflow nozzle opens, a cylindrical rectifier that protrudes upward from the bottom of the header tank is provided. Thus, by reducing the cross section of the flow path near the bottom in the header tank, the fluid flowing downward into the header tank via the inlet is prevented from flowing to the bottom side of the header tank, and the core A technique for suppressing the drift of the fluid passing therethrough is described.

  On the other hand, in Patent Document 3 and Patent Document 4, in a multi-tube heat exchanger having a header tank having a shape in which an inflow nozzle opens in the center and gradually expands from there to the core, the vicinity of the nozzle opening A technique is described in which the flow of fluid flowing through the nozzle is made to collide with the flow rectifying body and diffuse outward by disposing the flow rectifying body on the nozzle, thereby suppressing the drift of the fluid passing through the core.

JP 2002-310593 A JP 2007-71434 A JP-A-50-139454 JP 2001-248980 A

  Suppressing the drift of the fluid passing through the core as described above increases the heat exchange efficiency in the core, which is advantageous, for example, in reducing the size of the heat exchanger. Here, the drift that can occur in the heat exchangers described in Patent Documents 1 to 4 described above is such that the dynamic pressure of the fluid that is about to flow into the core is not relative to the inflow surface of the core where many inflow ports open. This is due to the even distribution. All the rectifiers described in each patent document have a function of making the dynamic pressure distribution on the inflow surface of the core as uniform as possible by lowering the high dynamic pressure.

  On the other hand, according to the study by the present inventors, even when the flow resistances of a large number of flow paths constituting the core are different from each other, the drift of the fluid passing through the core occurs. For example, in the core of a plate fin heat exchanger, each channel defined by corrugated fins disposed in the passage corresponds to a flow path, and a distributor fin that changes the flow direction of the fluid is disposed in the passage. Therefore, when the flow path length from the inlet to the outlet is different between the channels and the flow resistances are different from each other, or in the core of the multi-tubular heat exchanger, it corresponds to the flow path. When each pipe is bent in a U-shape, the flow path length is different for each pipe and the flow resistance is different. As a specific example, the flow resistance is different. Because the channel resistance is different for each channel, the flow rate through which the channel with relatively low flow resistance passes is relatively high, while the flow rate through which the channel with relatively high flow resistance passes is high. By becoming a pairwise less is the drift of the fluid passing through the core occurs. The deviation due to the flow resistance difference between the flow paths constituting the core may be different from the deviation due to the dynamic pressure distribution of the fluid with respect to the inflow surface described above. Even if such a rectifier is provided, it cannot be eliminated.

  The technology disclosed herein has been made in view of such a point, and an object thereof is to suppress the drift of the fluid passing through the core of the heat exchanger.

  The inventors of the present application provide two types of rectifying members having different configurations for each of two types of drift generation causes, ie, a fluid dynamic pressure distribution with respect to the inflow surface of the core and a flow resistance difference between a plurality of channels in the core. By providing, it decided to suppress the drift of the fluid which passes a core.

  Specifically, the technology disclosed herein has at least a first passage through which a first fluid flows and a second passage through which a second fluid flows, and heat exchange between the first fluid and the second fluid It concerns on the heat exchanger provided with the core which performs at least.

  The core has an inflow surface into which the first fluid flows in and an outflow surface from which the first fluid flows out, and at least the first passage includes an inlet opening in the inflow surface and the It includes a plurality of channels that connect the outlet opening that opens to the outflow surface, and is configured to have different flow path resistance between the plurality of channels.

  And the said heat exchanger is arrange | positioned at the said inflow surface side with respect to the said core, and the 1st type rectification | straightening member which aims at equalization of dynamic pressure distribution with respect to the said inflow surface of the said 1st fluid which flows in into the said core And a second type of rectifying member provided so as to reduce a flow rate difference caused by a flow resistance difference between the plurality of channels constituting the first passage of the core.

  Here, the “plurality of channels” includes not only a configuration in which the channels are partitioned from each other but also a configuration in which the fluid flows substantially along the channels although the channels are not completely partitioned from each other.

  According to this configuration, for example, due to the configuration of the inflow header tank connected to the core, the configuration of the inflow nozzle attached to the header tank, and the like, the dynamic pressure distribution of the first fluid is uneven with respect to the inflow surface of the core. In the heat exchanger, the first type rectifying member is arranged on the inflow surface side with respect to the core so as to equalize the dynamic pressure distribution. This first type of rectifying member can be constituted by a baffle or the like that reduces the dynamic pressure by interfering with the flow of the first fluid flowing in from the inflow nozzle, for example.

  On the other hand, in a heat exchanger in which a channel resistance difference occurs due to, for example, a channel length difference or a channel diameter difference between a plurality of channels constituting the first passage in the core, the first type rectification A second type of rectifying member is provided separately from the member. The second type of rectifying member is provided so as to reduce the flow rate difference caused by the flow path resistance difference. Specifically, the second type of rectifying member flows between a plurality of channels by restricting the inflow flow rate of the first fluid or restricting the outflow flow rate at least for a channel having a relatively low flow resistance. Even if a path resistance difference occurs, the flow rate difference passing through each channel is reduced.

  In this way, by providing two types of rectifying members, the first type of rectifying member and the second type of rectifying member, the drift caused by the fluid dynamic pressure distribution with respect to the inflow surface of the core, and between the plurality of channels in the core It is possible to effectively suppress both the drift due to the difference in flow path resistance, and the heat exchange efficiency of the heat exchanger can be improved. This is advantageous, for example, for downsizing the heat exchanger.

  The core is not limited to performing heat exchange between the two types of fluids of the first fluid and the second fluid, and may be configured to perform heat exchange between three or more types of fluids.

  The second type rectifying member may be disposed on the outflow surface side with respect to the core.

  As described above, the second type of rectifying member adjusts the inflow flow rate of the first fluid between the plurality of channels on the inflow side of the first passage, or between the plurality of channels on the outflow side of the first passage. By adjusting the outflow rate of the first fluid, the flow rate difference is reduced. The second type of rectifying member can be arranged on either the inflow surface side or the outflow surface side with respect to the core.

  However, since the first type rectifying member is arranged on the inflow surface side with respect to the core, when the second type rectifying member is arranged on the inflow surface side with respect to the core, for example, the arrangement space It may be difficult to arrange two types of rectifying members due to restrictions or the like.

  Here, as will be described later, the second type of rectifying member can be constituted by a plate-like member having a large number of holes penetratingly formed in a predetermined arrangement. The distribution of the aperture ratio (the area of the holes per unit area) becomes uneven by appropriately changing the diameter, number, and / or interval of the holes formed through the second type of rectifying member. What is necessary is just to comprise. On the other hand, the inflow surface of the core in which the inlets of each channel are arranged at equal intervals and the outflow surface of the core in which the outlets are arranged at equal intervals reflect the channel resistance of each channel. Since the flow path resistance distribution is set, the second type rectifying member is set so that the distribution characteristic of the aperture ratio in the second type rectifying member corresponds to the characteristic of the flow path resistance distribution on the inflow surface or the outflow surface. What is necessary is just to arrange | position relative to an inflow surface or an outflow surface. In other words, if the portion with a low aperture ratio is arranged so as to face a portion with a low flow resistance on the inflow surface or the outflow surface, the flow rate of the first fluid is limited at least for a channel with a relatively low flow resistance. Or limiting the outflow rate.

  When the second type of rectifying member having such a configuration is arranged on the inflow surface side with respect to the core, if the second type of rectifying member is arranged away from the inflow surface, the second type of rectifying member is opened along with passing through the second type of rectifying member. The effect of providing the flow rate difference of the first fluid according to the distribution of the rate is reduced before reaching the inflow surface, and the function as the second type of rectifying member cannot be exhibited. Therefore, it is desirable to arrange the second type of rectifying member close to the inflow surface.

  On the other hand, on the downstream side of the second type rectifying member having a large number of through holes, a large speed gradient is generated between an opening portion corresponding to the through hole and a non-opening portion corresponding to a portion other than the through hole. Therefore, if the second type of rectifying member is too close to the inflow surface, the velocity gradient affects the inflow of the first fluid through the inlet of each channel that opens to the inflow surface of the core. That is, the flow rate of the first fluid increases in the channel where the inlet is opposed to the through hole, while the first fluid hardly flows in the channel where the inlet is not opposed to the through hole. End up. This not only fulfills the function of the second type of rectifying member, but also may increase the flow rate difference between the plurality of channels. Therefore, when the second type rectifying member is arranged on the inflow surface side of the core, it is often difficult to adjust the arrangement position.

  On the other hand, in the configuration in which the second type of rectifying member is arranged on the outflow surface side of the core, the first type of rectifying member and the second type of rectifying member are connected to the inflow surface side and the outflow surface side with respect to the core. Therefore, it is easy to secure an arrangement space for each of the first type rectifying member and the second type rectifying member. In addition, when the second type of rectifying member having a large number of through holes is disposed relative to the outflow surface, it is easier to perform the function when it is disposed close to the outflow surface, while it is disposed on the inflow surface side. In contrast, since there is no need to consider the speed gradient on the downstream side of the second type of rectifying member, there is an advantage that the degree of freedom of arrangement of the second type of rectifying member is relatively high.

  Therefore, it is advantageous that the second type of rectifying member is disposed on the outflow surface side of the core in that it can be relatively freely disposed while ensuring its function.

  On the outflow surface of the core, the outlets of the plurality of channels are arranged at equal intervals, while a predetermined flow resistance distribution corresponding to the flow resistance of each channel is reflected. The second-type rectifying member is a plate-like member disposed so as to face at least a part of the outflow surface, and has a plurality of holes penetrating in the plate thickness direction. In the second type of rectifying member, the aperture ratio defined by the plurality of holes is set to have a characteristic distribution corresponding to the flow path resistance distribution reflected on the outflow surface. It is good also as.

  Here, the distribution characteristic of the opening ratio in the second type of rectifying member corresponds to the flow resistance distribution reflected on the outflow surface, and the portion where the flow resistance is high has a high opening ratio and the fluid easily passes therethrough. However, in the portion where the flow resistance is low, the aperture ratio may be lowered to make it difficult for the fluid to pass. In this way, even if there is a flow resistance difference between the plurality of channels, the flow rate of the first fluid passing through each channel is adjusted by the second type of rectifying member, and the flow rate difference between the plurality of channels is adjusted. Is suppressed. That is, the drift due to the flow resistance difference between the plurality of channels is suppressed.

  The core is a plate fin type configured by alternately laminating a plurality of the first passages and a plurality of the second passages, and at least in each of the first passages, a flow in the first passage is provided. Distributor fins for changing the direction may be provided.

  In other words, by disposing the distributor fin in the first passage of the core configured in the plate fin type, the flow path length between the plurality of channels becomes different, resulting in a flow resistance difference. However, since the second type of rectifying member described above reduces the flow rate difference due to the flow path resistance difference, the drift of the fluid passing through the core is suppressed.

  As described above, according to the above heat exchanger, the first type rectifying member for suppressing the drift caused by the dynamic pressure distribution of the fluid with respect to the inflow surface of the core, and the flow paths between the plurality of channels in the core By separately providing the second type rectifying member for suppressing the drift due to the resistance difference, it becomes possible to effectively suppress the drift in the heat exchanger, improving the heat exchange efficiency, This is advantageous for downsizing of the exchanger.

(A) The partially broken front view which shows the structure of a heat exchanger roughly, (b) The partially broken side view which shows the structure of a heat exchanger roughly. It is a front view which illustrates the 1st type straightening member. It is a front view which illustrates the 2nd type straightening member. It is a front view which shows the 2nd type rectification | straightening member of a shape different from FIG. FIG. 2 is a view corresponding to FIG. 1 showing a heat exchanger in which a second type of rectifying member having a configuration different from that of FIG. FIG. 2 is a view corresponding to FIG. 1 and showing a heat exchanger in which a second type of rectifying member is arranged on the inflow side of the first passage. It is a FIG. 1 corresponding view which shows the heat exchanger which abbreviate | omitted the 1st type rectifying member.

  Hereinafter, an embodiment of a heat exchanger will be described based on the drawings. In addition, the following description of preferable embodiment is an illustration. FIG. 1 schematically illustrates a configuration of a heat exchanger 1 according to the embodiment, where (a) corresponds to a front view of the heat exchanger 1 and (b) corresponds to a side view of the heat exchanger 1. To do. For convenience of explanation, the vertical direction in FIG. 1A is called the X direction, the horizontal direction is called the Y direction, and the horizontal direction in FIG. 1B is called the Z direction.

  The heat exchanger 1 has a plate fin type core 2 that performs heat exchange between the first fluid and the second fluid. As shown in FIG. 1A, the core 2 includes a first passage 21 through which the first fluid flows and a second passage 22 through which the second fluid flows alternately stacked in the Y direction with the tube plate 23 interposed therebetween. Is made up of. In the illustrated example, the core 2 has a rectangular parallelepiped shape in which the Z-direction length shown in FIG. 1B is set shorter than the X-direction length and the Y-direction length shown in FIG. Yes. The shape of the core 2 is not limited to such a shape, and various shapes can be adopted.

  As indicated by a solid line arrow, the first fluid flows into the first passage 21 from the upper end surface of the core 2 and flows downward in the core 2, and then flows out from the side surface at the lower end portion of the core 2 in the Z direction. Is configured to do. As indicated by the white arrow, the second fluid flows into the second passage 22 from the lower end surface of the core 2 and flows upward in the core 2, and then from the side surface at the upper end portion of the core 2 in the Z direction. It is configured to flow out. Thus, the core 2 is configured in a so-called counterflow type in which the first fluid and the second fluid flow so as to face each other. However, the configuration of the core 2 is not limited to this, and it may be a parallel flow type in which the flow directions of the first fluid and the second fluid are set to be the same, or the flow directions of the first fluid and the second fluid may be different. It is good also as a crossflow type | mold which mutually orthogonally crosses.

  In each first passage 21 in the core 2, corrugated fins 211 are arranged as schematically shown in FIG. 1B, and each first passage 21 is moved in the Z direction by the corrugated fins 211. Is divided into a plurality of channels. As the corrugated fins 211, various types of corrugated fins 211 such as a plain type and a perforated type can be adopted. Although not shown, corrugated fins are also disposed in the second passages 22, and the second passages are also partitioned into a plurality of channels arranged in the Z direction by the corrugated fins. Furthermore, although illustration is omitted, for example, serrated fins may be arranged in the first and / or second passages 21 and 22. In this case, although the plurality of channels are not completely partitioned, the fluid flows mainly in the X direction along the fins, and thus is substantially the same as being partitioned into the plurality of channels.

  In each first passage 21, a distributor fin 212 is disposed on the outflow side corresponding to the lower end portion of the core 2, so that the flow direction in the first passage 21 is downward from the X direction. It is changed to the horizontal direction in the Z direction (leftward in FIG. 1B). In each second passage 22, a distributor fin 222 is disposed on the outflow side corresponding to the upper end portion of the core 2, so that the flow direction in the second passage 22 is upward in the X direction. To the horizontal direction in the Z direction (rightward in FIG. 1B).

  Thus, in the rectangular parallelepiped core 2, the upper end surface thereof becomes the first fluid inflow surface 31, and the side surface of the lower portion of the core 2 becomes the first fluid outflow surface 32. On the other hand, the lower end surface of the core 2 becomes the inflow surface 33 of the second fluid, and the side surface in the upper part of the core 2 becomes the outflow surface 34 of the second fluid.

  An inflow header tank 41 for attaching the first fluid to each channel of each first passage 21 is attached to the inflow surface 31 of the first fluid with respect to the core 2 configured as described above. Yes. The inflow header tank 41 has an elongated shape in the Y direction corresponding to the shape of the inflow surface 31 of the first fluid, and the first fluid flows into the center of the inflow header tank 41 in the Y direction. An inflow nozzle 411 is attached. On the other hand, an outflow header tank 42 is attached to the outflow surface 32 of the first fluid in the core 2 for collecting and outflowing the first fluid that has passed through the channels of the first passages. The outflow header tank 42 also has an elongated shape in the Y direction, and an outflow nozzle 421 through which the first fluid flows out is attached to the center of the outflow header tank 42 in the Y direction. An inflow header tank 43 is attached to the inflow surface 33 of the second fluid, and an outflow header tank 44 is attached to the outflow surface 34 of the second fluid. The inflow header tank 43 and the outflow header tank 44 for the second fluid have the same configuration as the inflow header tank 41 and the outflow header tank 42 for the first fluid, and the inflow nozzle 431 and the outflow nozzle 441 are provided at the center in the Y direction, respectively. It is attached.

  The heat exchanger 1 includes a first rectifying member 51 and a second rectifying member 52 for each of the first passage 21 through which the first fluid flows and the second passage 22 through which the second fluid flows. A type of rectifying member is attached. The first type rectifying member 51 is mounted in the inflow header tanks 41 and 43, and is configured to equalize the fluid dynamic pressure distribution with respect to the inflow surfaces 31 and 33 of the first and second fluids. Has been. That is, both the core 2 and the inflow header tanks 41 and 43 have an elongated shape in the Y direction, while the inflow nozzles 411 and 431 are attached to the center of the inflow header tanks 41 and 43 in the Y direction. Furthermore, the length of the inflow header tanks 41 and 43 in the X direction is relatively short. As a result, the fluid flowing into the inflow header tanks 41 and 43 hardly spreads in the Y and Z directions. This tendency is particularly remarkable when the flow velocity of the fluid flowing in through the inflow nozzles 411 and 431 is high. This is because the fluid dynamic pressure is extremely high in the vicinity of the region where the openings of the inflow nozzles 411 and 431 are projected onto the inflow surfaces 31 and 33, while the fluid dynamic pressure is in the region outside the region. The outer peripheral edges of the inflow surfaces 31 and 33 are relatively low, and the fluid dynamic pressure distribution with respect to the inflow surfaces 31 and 33 is further uneven, so that the fluid dynamic pressure is further reduced. Such an uneven dynamic pressure distribution causes a drift in which the flow rate of the fluid passing through the passage on the center side in the Y direction is large while the flow rate of the fluid passing through the passages on both sides in the Y direction is reduced. In the core 2 of the illustrated example, the drift generated due to the nonuniformity of the dynamic pressure distribution corresponds to the drift in the stacking direction of the first passage 21 and the second passage 22 in the core 2.

  The first type rectifying member 51 has a function of equalizing the fluid dynamic pressure distribution with respect to the inflow surfaces 31 and 33. Specifically, the first type of rectifying member 51 in the figure is configured by a plate-like baffle disposed in the vicinity of the opening of the inflow nozzles 411 and 431 attached to the center of the inflow header tanks 41 and 43. Yes. As shown in an enlarged view in FIG. 2, the first type of rectifying member 51 has a plurality of through holes 511 penetrating in the plate thickness direction. The through holes 511 have the same diameter and are substantially the same. It arrange | positions so that it may become equal intervals.

  The first type of rectifying member 51 has a length in the Y direction that is slightly larger than the size of the openings of the inflow nozzles 411 and 431, and the first type of rectifying member 51 passes through the inflow nozzles 411 and 431. It arrange | positions so that the flow of the inflowing fluid may be crossed, and as shown in FIG.1 (b), it fixes to the inner wall of the inflow header tanks 41 and 43 by welding etc., for example.

  The first type of rectifying member 51 interferes with the fluid flow that has flowed into the inflow header tanks 41 and 43 through the inflow nozzles 411 and 431. A part of the fluid flows in the X direction as it is through the through hole 511 of the first type rectifying member 51, while the remaining fluid is the first type as shown by a solid line arrow in FIG. By changing the flow direction so as to bypass the rectifying member 51, the current flows so as to spread in the Y direction. As a result, the fluid dynamic pressure distribution is equalized with respect to the inflow surfaces 31 and 33, and the drift of the fluid flowing into the core 2 is suppressed in the stacking direction of the first and second passages 21 and 22. . That is, the amount of inflow into the plurality of first passages 21 and the plurality of second passages 22 is equalized. This is advantageous for improving the heat exchange efficiency of the heat exchanger 1.

  Here, the first type of rectifying member 51 may be disposed closer to the opening of the inflow nozzles 411 and 431 than the inflow surfaces 31 and 33 of the core 2, and the inflow header tank 41, through the inflow nozzles 411 and 431. This is advantageous in improving the dispersibility of the fluid flowing into 43 and preventing the drift in the stacking direction of the first and second passages 21 and 22. The dynamic pressure distribution on the inflow surfaces 31 and 33 is related to the size of the inflow surfaces 31 and 33, the shape of the inflow header tanks 41 and 43, the shape and arrangement of the inflow nozzles 411 and 431, the inflow speed of the fluid, and the like. However, if the size of the first type rectifying member 51, the size, number and arrangement of the through holes 511, and the arrangement position thereof are appropriately set according to the state of the dynamic pressure distribution. Good. The through hole may be omitted as necessary, and a plurality of baffles may be arranged.

  On the other hand, unlike the first type rectifying member 51, the second type rectifying member 52 is different from the flow rate difference due to the flow resistance between the plurality of channels in each first passage 21 and each second passage 22. Has the function of reducing the size. That is, as described above, the distributor fins 212 and 222 are provided in the first passages 21 and the second passages 22 of the core 2, so that the corrugated fins 211 and 222 in the passages 21 and 22 are provided. The channels defined by the distributor fins 212 and 222 have different flow path lengths from the inlet to the outlet. In the example shown in FIG. 1B, a channel having an outlet opening relatively upward on the outflow surface 32 of the first passage 21 has a relatively short flow path length and is relatively downwardly opened. The channel having the outflow port is relatively long in flow path length. Such a difference in flow path length causes a flow path resistance difference between channels, and a flow path resistance difference causes a flow rate difference of fluid passing between the channels. In other words, in the illustrated example, the first passage 21 has a relatively large flow rate through the channel having the outlet opening relatively upward on the outflow surface 32, and has the outlet opening relatively downward. The flow through the channel is relatively low. Although not shown, the channel having the outlet opening relatively upward on the outflow surface 34 of the second passage 22 has a relatively long flow path length. Since the channel length of the channel having the outlet opening relatively open to the lower side is relatively short, the flow rate passing therethrough is relatively large. The outflow surfaces 32 and 34 reflect the flow resistance distribution corresponding to the flow resistance of the channel. In the core 2 of the illustrated example, the drift generated due to the flow resistance difference between the plurality of channels corresponds to the drift in the Z direction (width direction).

  Unlike the first type of rectifying member 51, the second type of rectifying member 52 having a function of suppressing drift due to the difference in flow path resistance between the plurality of channels is disposed in the outflow header tanks 42 and 44. Yes. Specifically, the second type of rectifying member 52 is a plate-like member disposed in the outflow header tanks 42 and 44 in the vicinity of the outflow surfaces 32 and 34 so as to face the outflow surfaces 32 and 34. It is configured. The second type rectifying member 52 is also fixed to the inner walls of the outflow header tanks 42 and 44 by, for example, welding.

  As shown in FIG. 3, the second type of rectifying member 52 is also formed with a plurality of through holes 521 having the same diameter as the first type of rectifying member 51 so as to penetrate in the plate thickness direction. Yes. On the other hand, the through-holes 521 of the second type of rectifying member 52 are not arranged at equal intervals, and the interval is relatively wide in the upper portion of the sheet of FIG. It is arranged so that it becomes narrower. Thereby, the opening ratio (the area of the hole per unit area) of the second type rectifying member 52 is relatively low in the upper part and relatively high in the lower part. Such a 2nd type rectification | straightening member 52 is attached corresponding to distribution of flow-path resistance reflected on the outflow surfaces 32 and 34 mentioned above. That is, the portion with a low opening ratio in the second type of rectifying member 52 is opposed to the outlet of the channel having a relatively low flow resistance at the outflow surfaces 32 and 34, and the opening ratio of the second type of rectifying member 52 is The high part is mounted so that it is opposite the outlet of the channel with a relatively high flow resistance at the outflow surfaces 32,34. Specifically, with respect to the outflow surface 32 of the first fluid, as shown in FIG. 3, the second type of rectifying member 52 has a lower opening ratio on the upper side and a higher opening ratio on the lower side. It is attached in the state to become. On the other hand, with respect to the outflow surface 34 of the second fluid, the second type rectifying member 52 is in a state where the top and bottom are reversed from the state shown in FIG. It is attached in a state where the high part is on the upper side. By doing so, a portion having a low opening ratio in the second type of rectifying member 52 is opposed to the outlet of the channel having a relatively low flow resistance. Since the portion with a high opening ratio in the second type rectifying member 52 is opposed to the outlet of the relatively high channel, the fluid easily flows out. As a result, even if there is a flow resistance difference between the plurality of channels, the flow rate difference of the fluid passing through the plurality of channels is reduced. That is, the second type of rectifying member 52 suppresses the drift due to the flow resistance difference between the plurality of channels. This is also advantageous for improving the heat exchange efficiency of the heat exchanger 1.

  Arranging the second type of rectifying member 52 at a position relatively close to the outflow surfaces 32 and 34 has a high effect of suppressing the occurrence of a passage flow rate difference due to the flow path resistance difference. If the second type rectifying member 52 is arranged away from the outflow surfaces 32, 34, the effect of limiting the outflow flow rate from the channel by reducing the opening ratio of the second type rectifying member 52 is reduced. is there.

  Thus, by providing two types of rectifying members, the first type of rectifying member 51 and the second type of rectifying member 52, the drift caused by the fluid dynamic pressure distribution with respect to the inflow surfaces 31 and 33 of the core 2 (illustration example) Then, the drift in the stacking direction of the first passage 21 and the second passage 22) and the drift due to the flow resistance difference between the plurality of channels in the core 2 (the drift in the width direction of the core 2 in the illustrated example) Can be suppressed together. That is, two types of drifts with different generation mechanisms are suppressed by the two types of rectification members, the first type rectification member 51 and the second type rectification member 52, respectively, thereby optimizing each of the two types of drift. It becomes possible to suppress, and the heat exchange efficiency of the heat exchanger 1 improves.

  Here, the second type of rectifying member 52 illustrated in FIG. 3 changes the aperture ratio by changing the arrangement interval of the through holes 521 having the same diameter, but is differently arranged at the same interval. The aperture ratio may be changed by changing the diameter of the through hole. Moreover, you may change the aperture ratio of the 2nd type rectification | straightening member 52 by changing both the diameter and arrangement | positioning space | interval of a through-hole.

  Further, the shape of the through hole in the second type of rectifying member 52 is not limited to a round hole as illustrated in FIG. 3, and may be, for example, a long hole shaped through hole 531 as shown in FIG. 4. In the example shown in FIG. 4, both the size and the arrangement interval of the long hole-shaped through-holes 531 are changed, but only the size is changed or only the arrangement interval is changed to open the opening. The rate may be changed.

  Further, the aperture ratio of the second type rectifying member 52 may be continuously changed in the X direction as shown in FIG. 3, or may be changed stepwise in the X direction as shown in FIG. You may make it make it.

  The second type rectifying member 52 is also arranged so as to face only at least a part of the outflow surface 32 as shown in FIG. May be. FIG. 5 shows an example in which the second type of rectifying member 52 for the first passage 21 is arranged so as to face approximately half of the outflow surface 32. The portion where the second type rectifying member 52 is not disposed is equivalent to increasing the aperture ratio.

  Further, the second type rectifying member 52 may be mounted in the inflow header tank 41 instead of being mounted in the outflow header tank 42. FIG. 6 shows an example in which the second type rectifying member 52 for the first passage 21 is attached in the inflow header tank 41. This second type of rectifying member 52 may also be configured by a plate-like member having a changed aperture ratio as shown in FIGS. 3 and 4, and the second type of rectifying member 52 has an aperture ratio distribution. By attaching it relative to the inflow surface 31 so as to correspond to the distribution of the channel resistance at the inflow surface 31, the flow rate flowing into each channel is adjusted according to the channel resistance, and between the plurality of channels. It becomes possible to reduce the difference between the passage flow rates.

  Here, also when arrange | positioning 2nd type rectification | straightening member 52 relative to the inflow surface 31, it is preferable when it arrange | positions close to the inflow surface 31 in order to fully exhibit a drift control function. That is, the second type of rectifying member 52 mounted in the inflow header tank 41 is provided with a difference in flow rate of fluid passing therethrough, and thus inflow rate difference with respect to the inflow surface 31 by making the opening ratios different. Reduce the flow rate difference between multiple channels. Therefore, when the second type of rectifying member 52 is arranged away from the inflow surface 31, the effect of providing a fluid flow rate difference by passing through the second type of rectifying member 52 fades before reaching the inflow surface 31. It ends up. On the other hand, if the second type rectifying member 52 is too close to the inflow surface 31, the portion of the second type rectifying member 52 (that is, the opening) and the other portion (that is, the non-opening portion). The velocity gradient of the fluid generated between the two channels affects the inflow into each channel through the inflow surface 31. Specifically, the inflow rate increases at the inlet facing the opening, while the fluid hardly flows into the inlet facing the non-opening. This not only does not exhibit the function of the second type of rectifying member 52 for reducing the flow rate difference between the plurality of channels, but may also increase the flow rate difference. As described above, when the second type rectifying member 52 is attached to the inflow header tank 41, it may be difficult to adjust the arrangement position thereof. On the other hand, as shown in FIG. 1 and the like, when the second type rectifying member 52 is attached to the outflow header tank 42, it is not necessary to consider the speed gradient after passing through the second type rectifying member 52. Therefore, the degree of freedom in arrangement is high, and it is possible to effectively suppress the drift caused by the flow resistance difference between the plurality of channels.

  Further, since the first type of rectifying member 51 is mounted in the inflow header tank 41, when the second type of rectifying member 52 is mounted in the inflow header tank 41, the two types of rectifying members 51, 52 are both It is attached in the inflow header tank 41. For this reason, depending on the configuration of the inflow header tank 41 and the configuration of the inflow nozzle 411, it may be difficult to dispose the two types of rectifying members 51 and 52 so that their functions are fully exhibited. . The attachment of the second type of rectifying member 52 in the outflow header tank 42 means that the first type and the second type of rectifying members 51 and 52 are arranged separately on the inflow side and the outflow side with respect to the core 2. Therefore, each of the first-type and second-type rectifying members 51 and 52 is advantageous in optimal arrangement.

  For example, as shown in FIG. 7, in the heat exchanger 10 in which the dynamic pressure distribution of the fluid with respect to the inflow surface 31 is substantially equalized, the first type rectifying member may be omitted. That is, in FIG. 7, the passage of the first fluid is configured as ducts 44 and 45, so that the dynamic pressure distribution is substantially equalized with respect to the inflow surface 31 for the first fluid of the core 2. Therefore, the first type rectifying member is unnecessary. On the other hand, in each of the first passages 21 in the core 2, at least the distributor fins 212 are disposed in the same manner as described above, so that there is a difference in flow resistance between a plurality of channels. Therefore, in the heat exchanger 10 shown in FIG. 7, the second type of rectifying member 52 is disposed relative to the outflow surface 32, and thereby, the core 2 that may be generated due to the difference in flow path resistance. It is possible to avoid the drift of the first fluid in the width direction. In the example shown in FIG. 7, the second type rectifying member 52 may be attached in the inflow header tank 41.

  In addition, depending on the configuration of the heat exchanger, the first type and / or the second type of rectifying member may be arranged only for one of the flow path for the first fluid and the flow path for the second fluid. obtain.

  In addition, the first type of rectifying member that suppresses the drift caused by the dynamic pressure distribution is not limited to the baffle, and various known configurations may be used depending on the configuration of the inflow header tank and the configuration and arrangement of the inflow nozzle. It is possible to employ a straightening member.

  Further, here, the first and second rectifying members are described by taking the heat exchangers 1 and 10 having the plate fin type core 2 as an example. It is also possible to apply the first and second rectifying members. In a multi-tube heat exchanger, for example, in a configuration in which a tube is bent in a U shape, a flow path resistance difference is generated, and drift can occur. The second type of rectifying member is effective in suppressing drift even in such a multitubular heat exchanger.

  In both the plate fin type heat exchanger and the multi-tube heat exchanger, the flow resistance difference is not only due to the difference in the flow path length, It can be caused by differences in both length and cross-sectional area. In any of the second type rectifying members, it is possible to reduce the flow rate difference caused by the flow path resistance difference.

  As described above, the heat exchanger disclosed herein includes the first type of rectifying member that equalizes the dynamic pressure distribution of the fluid with respect to the inflow surface, and the passage flow rate due to the flow resistance difference between the plurality of channels. Since the drift of the fluid can be suppressed by the second type of rectifying member that reduces the difference, it is advantageous for improving the heat exchange efficiency in various heat exchangers. In addition, since the flow rate of the fluid passing through each channel is equalized, for example, a catalyst carrier is built in each channel, and a heat exchanger (that is, used for reacting the fluid passing therethrough) In the case of a catalytic reactor), it is advantageous for improving the reaction efficiency and consequently the performance.

DESCRIPTION OF SYMBOLS 1 Heat exchanger 10 Heat exchanger 2 Core 21 1st channel | path 22 2nd channel | path 211 Corrugated fins 212 and 222 Distributor fins 31 and 33 Inflow surface 32 and 34 Outflow surface 51 1st type rectification member 52 2nd type rectification member 521, 531 Through hole

Claims (4)

A heat exchanger having at least a first passage through which a first fluid flows and a second passage through which a second fluid flows, and a core for performing at least heat exchange between the first fluid and the second fluid Because
The core has an inflow surface into which the first fluid flows and an outflow surface from which the first fluid flows out, respectively.
At least the first passage includes a plurality of channels that connect the inflow port that opens to the inflow surface and the outflow port that opens to the outflow surface, and is configured to have different flow resistance between the plurality of channels. And
A first type of rectifying member that is disposed on the inflow surface side with respect to the core and that equalizes a dynamic pressure distribution of the first fluid flowing into the core with respect to the inflow surface;
A heat exchanger further comprising a second type of rectifying member provided so as to reduce a flow rate difference caused by a flow resistance difference between the plurality of channels constituting the first passage of the core. . The heat exchanger according to claim 1,
The second type rectifying member is a heat exchanger disposed on the outflow surface side with respect to the core. The heat exchanger according to claim 2,
On the outflow surface of the core, the outlets of the plurality of channels are arranged at equal intervals, while a predetermined flow resistance distribution corresponding to the flow resistance of each channel is reflected. ,
The second type of rectifying member is a plate-like member disposed so as to face at least a part of the outflow surface, and has a plurality of holes formed so as to penetrate therethrough. And
In the second type of rectifying member, the opening ratio defined by the plurality of holes is set to have a characteristic distribution corresponding to a flow path resistance distribution reflected on the outflow surface. . The heat exchanger according to any one of claims 1 to 3,
The core is a plate fin type configured by alternately laminating a plurality of the first passages and a plurality of the second passages,
A heat exchanger in which a distributor fin for changing a flow direction in the first passage is disposed at least in each first passage.

Images