WO2014010180A1 - Échangeur thermique - Google Patents

Échangeur thermique Download PDF

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Publication number
WO2014010180A1
WO2014010180A1 PCT/JP2013/003907 JP2013003907W WO2014010180A1 WO 2014010180 A1 WO2014010180 A1 WO 2014010180A1 JP 2013003907 W JP2013003907 W JP 2013003907W WO 2014010180 A1 WO2014010180 A1 WO 2014010180A1
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WO
WIPO (PCT)
Prior art keywords
type
core
rectifying member
fluid
inflow
Prior art date
Application number
PCT/JP2013/003907
Other languages
English (en)
Japanese (ja)
Inventor
謙一郎 福井
高橋　弘行
章裕 田辺
藤田　泰広
Original Assignee
住友精密工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=49915665&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=WO2014010180(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by 住友精密工業株式会社 filed Critical 住友精密工業株式会社
Priority to US14/413,689 priority Critical patent/US20150136366A1/en
Priority to CN201380036190.6A priority patent/CN104428622A/zh
Priority to EP13817311.7A priority patent/EP2889570B1/fr
Priority to EA201590160A priority patent/EA030192B1/ru
Priority to BR112015000249A priority patent/BR112015000249A2/pt
Publication of WO2014010180A1 publication Critical patent/WO2014010180A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/005—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for only one medium being tubes having bent portions or being assembled from bent tubes or being tubes having a toroidal configuration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0006—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the plate-like or laminated conduits being enclosed within a pressure vessel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0062—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by spaced plates with inserted elements
    • F28D9/0068—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by spaced plates with inserted elements with means for changing flow direction of one heat exchange medium, e.g. using deflecting zones
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/028—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using inserts for modifying the pattern of flow inside the header box, e.g. by using flow restrictors or permeable bodies or blocks with channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • F28F2009/222—Particular guide plates, baffles or deflectors, e.g. having particular orientation relative to an elongated casing or conduit

Definitions

  • 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.
  • Patent Document 2 describes a plate fin type heat exchanger having a header tank extending vertically downward from an upper end position where an inflow nozzle opens.
  • this plate fin type heat exchanger by providing a cylindrical rectifier projecting upward from the bottom in the header tank, the cross section of the flow path near the bottom in the header tank is reduced.
  • a technique is described in which the fluid flowing downward into the header tank through the inlet is prevented from flowing to the bottom side of the header tank, thereby suppressing the drift of the fluid passing through the core.
  • Patent Document 3 and Patent Document 4 describe a multi-tube heat exchanger having a header tank having a shape in which an inflow nozzle is opened at the center and gradually expands from there to a core.
  • a multi-tube heat exchanger by arranging a rectifier near the opening of the nozzle, the fluid flow flowing through the nozzle collides with the rectifier and diffuses outward, A technique for suppressing the drift of the fluid passing through the core is described.
  • 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.
  • the channel length from the inlet to the outlet becomes different between the channels, and the channel resistances are different from each other.
  • each pipe corresponding to the flow path is bent in a U shape, so that the flow path length is different for each pipe and the flow path resistance is different. .
  • the flow rate resistance is different for each channel.
  • a channel having a relatively high flow resistance has a relatively low flow rate, and as a result, a 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 differ from the deviation due to the dynamic pressure distribution of the fluid with respect to the inflow surface described above, and are described in Patent Documents 1 to 4. 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.
  • 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.
  • the said heat exchanger is arrange
  • the “plurality of channels” includes not only a configuration in which the channels are partitioned from each other but also a configuration in which fluid flows substantially along the channels although the channels are not completely partitioned from each other.
  • the dynamic pressure distribution of the first fluid is uneven with respect to the inflow surface of the core.
  • 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.
  • 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.
  • 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.
  • 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.
  • the arrangement space It may be difficult to arrange two types of rectifying members due to restrictions or the like.
  • the second type 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) of the second type of rectifying member can be changed by appropriately changing the diameter of the holes formed therethrough, the number of holes, and / or the interval between the holes. What is necessary is just to comprise so that it may become uneven.
  • 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.
  • 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
  • the second type of rectifying member having such a configuration 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 opens 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the second type of rectifying member is disposed on the outflow surface side of the core because it can be relatively freely disposed while ensuring its function.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • FIG. 1A is a partially broken front view schematically showing the structure of a heat exchanger
  • FIG. 1B is a partially broken side view schematically showing the structure of a heat exchanger
  • FIG. 2 is a front view illustrating the first type of rectifying member.
  • FIG. 3 is a front view illustrating a second type of rectifying member.
  • FIG. 4 is a front view showing a second type of rectifying member having a shape different from that in FIG. 3.
  • FIG. 5 is a view corresponding to FIG. 1 and showing a heat exchanger in which a second type of rectifying member having a configuration different from that of FIG. 1 is arranged.
  • FIG. 6 is a view corresponding to FIG. 1 showing a heat exchanger in which the second type of rectifying member is arranged on the inflow side of the first passage.
  • FIG. 7 is a view corresponding to FIG. 1 and showing a heat exchanger in which the first type rectifying member is omitted.
  • FIG. 1 schematically shows a configuration of a heat exchanger 1 according to the embodiment.
  • 1A corresponds to a front view of the heat exchanger 1
  • FIG. 1B corresponds to a side view of the heat exchanger 1.
  • FIG. 1A the vertical direction in FIG. 1A is called the X direction
  • the horizontal direction is called the Y direction
  • 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.
  • 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.
  • 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.
  • 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.
  • 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. leak.
  • 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.
  • 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
  • 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.
  • the corrugated fins 211 various types of corrugated fins 211 such as a plain type and a perforated type can be adopted.
  • 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.
  • 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.
  • 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).
  • 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).
  • the upper end surface thereof becomes the first fluid inflow surface 31, and the side surface at the lower portion of the core 2 becomes the first fluid outflow surface 32.
  • 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.
  • 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 attached in the inflow header tanks 41 and 43.
  • the first type of rectifying member 51 is configured to equalize the fluid dynamic pressure distribution with respect to the first and second fluid inflow surfaces 31 and 33. 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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
  • 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. This first type of rectifying member 51 is arranged so as to cross the flow of the fluid flowing in through the inflow nozzles 411 and 431, and as shown in FIG. 1B, on the inner wall of the inflow header tanks 41 and 43, for example, It is fixed by welding or the like.
  • the first type 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.
  • the current flows so as to spread in the Y direction.
  • 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.
  • 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.
  • 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. You may abbreviate
  • a plurality of baffles may be arranged in the header tanks 41 and 43.
  • 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.
  • 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.
  • 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.
  • 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).
  • 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.
  • 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.
  • 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.
  • 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.
  • straightening member 52 is attached corresponding to distribution of flow-path resistance reflected on the outflow surfaces 32 and 34 mentioned above.
  • 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.
  • 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.
  • 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.
  • 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.
  • the second type of rectifying member 52 suppresses the drift due to the flow resistance difference between the plurality of channels. This is advantageous for improving the heat exchange efficiency of the heat exchanger 1.
  • the arrangement of the second type 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 flow rate difference caused by a 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.
  • the drift caused by the fluid dynamic pressure distribution with respect to the inflow surfaces 31 and 33 of the core 2 (illustration example)
  • 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)
  • two types of drifts having different generation mechanisms are suppressed by the two types of rectification members, ie, the first type rectification member 51 and the second type rectification member 52, so that each of the two types of drifts can be accurately detected. It becomes possible to suppress, and the heat exchange efficiency of the heat exchanger 1 improves.
  • 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.
  • 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.
  • 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.
  • 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.
  • the second type rectifying member 52 may be attached in the inflow header tank 41 instead of being attached 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.
  • the second type rectifying member 52 when the second type rectifying member 52 is disposed relative to the inflow surface 31, it is preferable that the second type rectifying member 52 is disposed close to the inflow surface 31 in order to sufficiently exhibit the drift current suppressing 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.
  • the portion of the second type rectifying member 52 that is, the opening
  • 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.
  • the second type rectifying member 52 is attached to the inflow header tank 41, it may be difficult to adjust the arrangement position thereof.
  • the first type of rectifying member 51 is mounted in the inflow header tank 41
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the second type rectifying member 52 may be attached to the inflow side with respect to the core 2.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)

Abstract

La présente invention concerne un échangeur thermique dont le premier passage est configuré pour contenir une pluralité de canaux reliant une ouverture d'admission à une face d'orifice d'entrée de faisceau et une ouverture de sortie à une face d'orifice de sortie et de sorte que la résistance du chemin d'écoulement soit différente entre la pluralité de canaux. L'échangeur thermique comporte un premier type d'organe de rectification, disposé dans le côté de la face d'entrée du faisceau, capable d'égaliser la distribution des pressions dynamiques pour la face d'orifice d'entrée d'un premier fluide circulant dans le faisceau, et un second type d'organe de rectification agencé pour réduire la différence dans le débit d'écoulement entraînée par la différence dans la résistance de chemin d'écoulement entre la pluralité de canaux.
PCT/JP2013/003907 2012-07-09 2013-06-21 Échangeur thermique WO2014010180A1 (fr)

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US14/413,689 US20150136366A1 (en) 2012-07-09 2013-06-21 Heat exchanger
CN201380036190.6A CN104428622A (zh) 2012-07-09 2013-06-21 热交换器
EP13817311.7A EP2889570B1 (fr) 2012-07-09 2013-06-21 Échangeur thermique
EA201590160A EA030192B1 (ru) 2012-07-09 2013-06-21 Теплообменник
BR112015000249A BR112015000249A2 (pt) 2012-07-09 2013-06-21 trocador de calor

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JP2012153240A JP5795994B2 (ja) 2012-07-09 2012-07-09 熱交換器
JP2012-153240 2012-07-09

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WO2014010180A1 true WO2014010180A1 (fr) 2014-01-16

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EP (1) EP2889570B1 (fr)
JP (1) JP5795994B2 (fr)
CN (1) CN104428622A (fr)
BR (1) BR112015000249A2 (fr)
EA (1) EA030192B1 (fr)
WO (1) WO2014010180A1 (fr)

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WO2021106719A1 (fr) * 2019-11-25 2021-06-03 ダイキン工業株式会社 Échangeur de chaleur
CN113928574A (zh) * 2021-11-19 2022-01-14 中国直升机设计研究所 一种直升机冷却系统的热交换器

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EP2889570A4 (fr) 2016-06-08
CN104428622A (zh) 2015-03-18
EP2889570A1 (fr) 2015-07-01
JP5795994B2 (ja) 2015-10-14
BR112015000249A2 (pt) 2017-06-27
JP2014016083A (ja) 2014-01-30
EA201590160A1 (ru) 2015-05-29
US20150136366A1 (en) 2015-05-21
EA030192B1 (ru) 2018-07-31
EP2889570B1 (fr) 2017-08-09

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