WO2014147804A1 - Échangeur de chaleur du type à plaques et dispositif de cycle de réfrigération le comportant - Google Patents

Échangeur de chaleur du type à plaques et dispositif de cycle de réfrigération le comportant Download PDF

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Publication number
WO2014147804A1
WO2014147804A1 PCT/JP2013/058210 JP2013058210W WO2014147804A1 WO 2014147804 A1 WO2014147804 A1 WO 2014147804A1 JP 2013058210 W JP2013058210 W JP 2013058210W WO 2014147804 A1 WO2014147804 A1 WO 2014147804A1
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WIPO (PCT)
Prior art keywords
plate
flow path
fluid
passage hole
rectifying plate
Prior art date
Application number
PCT/JP2013/058210
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English (en)
Japanese (ja)
Inventor
伊東　大輔
Original Assignee
三菱電機株式会社
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.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to EP13878608.2A priority Critical patent/EP2977704B1/fr
Priority to JP2015506497A priority patent/JP6091601B2/ja
Priority to PCT/JP2013/058210 priority patent/WO2014147804A1/fr
Priority to CN201420068680.6U priority patent/CN203785330U/zh
Publication of WO2014147804A1 publication Critical patent/WO2014147804A1/fr
Priority to HK16104130.5A priority patent/HK1216114A1/zh

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Classifications

    • 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
    • F28D9/0031—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 paired plates touching each other
    • F28D9/0043—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 paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005—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 paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/022—Evaporators with plate-like or laminated elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements
    • F28F3/027—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements with openings, e.g. louvered corrugated fins; Assemblies of corrugated strips
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/06—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being attachable to the element
    • 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
    • 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
    • F28F9/0278—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of stacked distribution plates or perforated plates arranged over end plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/043—Condensers made by assembling plate-like or laminated elements
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles

Definitions

  • the present invention relates to a plate heat exchanger and a refrigeration cycle apparatus including the plate heat exchanger.
  • Patent Documents 1 to 3 include a rectifying unit that makes the flow velocity distribution uniform.
  • Both of the rectifying sections of Patent Documents 1 and 2 are configured by combining a plurality of plate-like members in a complicated manner, and thus there is a problem that production is difficult and cost is high.
  • the rectifying member of Patent Document 3 is formed by cutting and forming a single plate-like member, or bending a plurality of plate-like members, and further simplification of the structure is required.
  • the present invention has been made in view of these points, and an object thereof is to provide a low-cost plate heat exchanger capable of making the flow velocity distribution uniform with a simple structure and a refrigeration cycle apparatus including the same.
  • the first flow path and the second flow path are alternately formed between a plurality of heat transfer plates provided at predetermined intervals, and the first flow path and the second flow path are formed.
  • a plate-type heat exchanger in which inner fins are respectively provided in a path, wherein each of the plurality of heat transfer plates includes a first fluid inlet to the first flow path or a second fluid inlet to the second flow path.
  • Each plate is provided with a plate-like rectifying plate so as to partition the upstream passage hole and the inner fin, and the rectifying plate has a plurality of openings serving as flow paths for the first fluid or the second fluid.
  • the flow resistance becomes smaller as it goes from the side closer to the upstream passage hole to the side farther from the side. In which the opening area of the number of openings is adjusted.
  • the plate-type heat exchanger of the present invention can provide a low-cost plate-type heat exchanger that can make the flow velocity distribution uniform with a simple structure by arranging the rectifying plates.
  • FIG. 1 It is explanatory drawing of the baffle plate 30 of FIG.
  • FIG. 3 It is explanatory drawing of the modification 4 of the baffle plate 30 of FIG.
  • explanatory drawing of the modification 5 of the baffle plate 30 of FIG. It is a principal part expansion perspective view of the plate type heat exchanger which concerns on Embodiment 2 of this invention.
  • FIG. 1 is a view showing a general inner fin type plate heat exchanger according to an embodiment of the present invention.
  • FIG. 2 is a diagram illustrating an example of the inner fin 2 of FIG. 3 is an enlarged perspective view of a main part of FIG.
  • the same reference numerals are the same or equivalent, and this is common throughout the entire specification.
  • the forms of the constituent elements appearing in the entire specification are merely examples and are not limited to these descriptions.
  • the inner fin type plate heat exchanger (hereinafter simply referred to as “plate heat exchanger”) has a plurality of heat transfer plates 1 having flat heat transfer surfaces.
  • the plurality of heat transfer plates 1 are provided at predetermined intervals, and a first flow path A through which the first fluid flows and a second flow path B through which the second fluid flows between the plurality of heat transfer plates 1.
  • the flow direction of the first fluid is x
  • the flow direction of the second fluid is y.
  • each of the 1st flow path A and the 2nd flow path B is provided with the inner fin 2 which accelerates
  • the side plate 3 which plays the role of reinforcement is provided in the both ends of the lamination direction of the several heat exchanger plate 1, and the whole is integrally joined with the several heat exchanger plate 1 and the inner fin 2. As shown in FIG. Yes.
  • offset fins are used for the inner fins 2.
  • the offset fin has a configuration in which the peaks and valleys in the plate width direction of the corrugated fins are shifted by half a mountain in the plate width direction every predetermined pitch in the longitudinal direction of the plate and are formed in a staggered pattern.
  • the plurality of heat transfer plates 1 and the two side plates 3 are made of a substantially rectangular flat plate made of metal, and have a first fluid inflow pipe 4 and a first fluid at one of the four side plates 3.
  • An outflow pipe 5 for one fluid, an inflow pipe 6 for the second fluid, and an outflow pipe 7 for the second fluid are provided.
  • the heat transfer plate 1 has a first fluid inlet pipe 4, a first fluid outlet pipe 5, a second fluid inlet pipe 6, and a second fluid outlet pipe 7 at positions corresponding to the first fluid inlet pipe 4.
  • An opening 11, a second opening 12, a third opening 13, and a fourth opening 14 are formed.
  • the first opening 11, the second opening 12, the third opening 13, and the fourth opening 14 are an inlet of the first channel A, an outlet of the first channel A, and an inlet of the second channel B, respectively.
  • the outlet of the second flow path B is formed.
  • a blocking portion 21 (see FIG. 3) is provided around the first opening 11 and the second opening 12 or the third opening 13 and the fourth opening 14.
  • the blocking portion 21 has the third opening 13 and the fourth opening 14 sealed in the first flow path A through which the first fluid flows, and the first opening in the second flow path B through which the second fluid flows. 11 and the second opening 12 are sealed. In this way, the second fluid is prevented from flowing into the first flow path A, and the first fluid is prevented from flowing into the second flow path B.
  • the opening communicating with the inner fin 2 is referred to as a passage hole. Therefore, in the first flow path A, the third opening 13 and the fourth opening 14 become passage holes, and in the second flow path B, the first opening 11 and the second opening 12 become passage holes.
  • a passage hole serving as a fluid inlet is referred to as an upstream passage hole 20 a and a passage hole serving as a fluid outlet is referred to as a downstream passage hole 20 b.
  • flow paths when the first flow path A and the second flow path B are not distinguished, they are simply referred to as flow paths.
  • the first fluid and the second fluid are not distinguished, they are simply referred to as fluids.
  • the flow velocity of the fluid flowing into the flow path from the upstream side passage hole 20a is generally fast in the vicinity of the upstream side passage hole 20a and slow in the distance. For this reason, the fluid hardly flows in the region M far from the upstream passage hole 20a, and the fluid stays. Therefore, since the flow rate of the fluid flowing downstream from the region M is reduced, the effective heat transfer area is reduced.
  • a plate-like rectifying plate 30 for equalizing the flow velocity is disposed between the upstream passage hole 20a and the inner fin 2.
  • the rectifying plate 30 is disposed on the heat transfer plate 1 so as to partition the upstream side passage hole 20a and the inner fin 2 from each other.
  • FIG. 4A and 4B are explanatory views of the current plate 30 in FIG. 3, in which FIG. 4A is a front view, FIG. 4B is a cross-sectional view taken along the line AA in FIG. 4 is an explanatory diagram for explaining the characteristics of the current plate 30 in FIG. 3, and the number, scale, and the like of the openings 31 do not correspond exactly to those in FIG. 3. This is the same in the explanatory view of the current plate 30 described later.
  • a plurality of openings 31 are formed at intervals in the partition direction of the rectifying plate 30 (longitudinal direction of the rectifying plate 30).
  • the opening areas of the plurality of openings 31 are adjusted so that the flow path resistance of the rectifying plate 30 decreases as the distance from the side closer to the upstream passage hole 20a in the rectifying plate 30 increases. ing. Specifically, the opening areas of the plurality of openings 31 are formed larger in the order in which the rectifying plate 30 is located on the side farther from the side closer to the upstream passage hole 20a.
  • a plurality of openings 31 are formed in a circular shape here, and the diameter of the opening 31a on the region A1 side far from the upstream passage hole 20a is close to the upstream passage hole 20a. It is formed larger than the diameter of the opening 31b on the A2 side.
  • the opening area is adjusted in two stages, but the opening area is not limited to two stages, and a plurality of stages may be used.
  • each opening 31a located on the region A1 side far from the upstream passage hole 20a is larger than each opening 31b located on the region A2 side close to the upstream passage hole 20a. Therefore, the flow resistance on the region A1 side where the flow velocity is slow in the rectifying plate 30 is smaller than that on the region A2 side where the flow velocity is fast, and the fluid easily flows into the region M. Thereby, the flow velocity in the XY direction can be made uniform, and the retention of fluid in the region M can be improved. As a result, the downstream portion of the region M in the heat transfer plate 1 can function as a heat transfer surface, and the effective heat transfer area can be expanded.
  • the length L1 in the XY direction of the region A1 in which the opening 31 is formed large may be shorter than the length L2 in the same direction of the closing portion 21.
  • the flow path formed by the blocking portion 21 and the rectifying plate 30 is narrower than the flow path between the upstream passage hole 20a and the rectifying plate 30 and hardly flows into the region M. For this reason, a region of L1 having a low resistance is provided in the rectifying plate 30, but if L1 is made larger than L2, the fluid flows out from the opening 31 in L1 on the near side before flowing into the region M, and the speed is increased. It is difficult to make uniform. By making L1 smaller than L2, the speed can be made more uniform than when L1> L2.
  • the closing portion 21 becomes a resistance of the fluid flowing into the region M, but the present invention can be adjusted to reduce the increase in pressure loss due to this resistance by adjusting the opening area of the rectifying plate 30. For this reason, it is effective in improving the deviation of the flow velocity distribution.
  • the shape of each opening 31 is not limited to a circle, and may be a square, a rectangle, or the like.
  • the diameters of the openings 31a in the region A1 are all the same, and the diameters of the openings 31b are also the same in the region A2, but the diameter gradually increases as the distance from the upstream passage hole 20a increases. You may comprise so that it may become large.
  • the plate-shaped rectifying plate 30 is disposed between the upstream passage hole 20a provided in the heat transfer plate 1 and the inner fin 2 so as to partition the both.
  • the current plate 30 was provided with a plurality of openings 31 at intervals in the partition direction. Furthermore, the opening area of the plurality of openings 31 was adjusted so that the flow resistance when the fluid passed through the rectifying plate 30 was smaller on the side farther than the side closer to the upstream passage hole 20a. Thereby, the flow velocity distribution can be made uniform, the uneven flow rate on the inlet side of the inner fin 2 can be improved, the effective heat transfer area can be increased, and the pressure loss can be reduced.
  • the current plate 30 has a simple structure in which a hole is formed in the plate-like member, it is easy to manufacture, and the effect of expanding the effective heat transfer area and reducing pressure loss can be realized at a low cost. It is possible to reduce the weight.
  • the current plate 30 has a simple structure in which holes are made in the plate-like member, the size of each opening 31 for making the flow velocity distribution uniform can be easily adjusted. Further, although it is inexpensive even if the rectifying plate 30 is made of a single component, if it is molded integrally with the inner fin 2, the number of components is reduced, and therefore the cost is further reduced. Further, the rectifying plate 30 can be joined to the heat transfer plate 1 by brazing, and the plate heat exchanger can be manufactured at low cost by integral brazing.
  • the partition that is a portion between the openings 31 has an action of mixing the fluid that has passed through the openings 31, and preferably acts to equalize the flow velocity.
  • the rectifying plate 30 is arranged upright so as to partition between the upstream side passage hole 20a and the inner fin 2, the installation of the rectifying plate 30 functioning as a distribution improving mechanism does not require a wide space, It can be installed in a small space.
  • the region M in which the stagnation is likely to occur is a portion where the flow rate of the fluid is slow when the rectifying plate 30 is not provided. For this reason, when the fluid is water and the plate heat exchanger is used as an evaporator, the temperature is locally lowered and becomes a starting point of freezing.
  • the flow velocity of the fluid in the region M can be increased, freezing can be suppressed and quality can be improved.
  • the plate heat exchanger of the first embodiment has effects such as high heat transfer, low pressure loss, and high reliability, a CO 2 refrigerant having a small evaporation capacity, a hydrocarbon having a large pressure loss, A combustible refrigerant such as a low GWP refrigerant can also be used.
  • the offset fin is a heat transfer promoting body having a low pressure loss and has a small resistance, so that the fluid easily flows linearly. For this reason, if the current plate 30 is not provided and the fluid does not flow into the region M, the fluid hardly flows into the region downstream from the region M. In this case, the effective heat transfer area is reduced as described above. However, it is possible to reduce pressure loss and expand the effective heat transfer area by using offset fins with low pressure loss as the heat transfer surface and further combining with the rectifying plate 30.
  • the leading edge effect refers to an effect that can be realized by actively using the leading edge portion of the flat plate as a heat transfer portion by utilizing the property that the heat transfer coefficient is good at the leading edge portion of the flat plate. That is, when a flat plate is placed in the flow, the boundary layer is thin at the leading edge of the flat plate and becomes thicker toward the downstream. For this reason, heat transfer becomes favorable in the front edge part of a flat plate where the thickness of a boundary layer is thin.
  • the current plate 30, the offset fins, and the heat transfer plate 1 having a flat heat transfer surface can be manufactured by pressing, and a plate heat exchanger having high heat transfer performance with low pressure loss can be manufactured at low cost. If the plate heat exchanger has a low pressure loss, less power is required to operate the fluid. For this reason, the capacity
  • the inner fin of the present invention is not limited to the offset fin.
  • the inner fin 2 of the present invention includes not only fins formed separately from the heat transfer plate 1 but also fins formed by corrugating the surface of the heat transfer plate 1.
  • the uniform distribution of the flow rate is necessary on the inlet side of the flow path and not on the outlet side. Therefore, it is possible to reduce the cost by providing the rectifying plate 30 only on the inlet side, not on both the inlet side and the outlet side.
  • the number, shape, and arrangement of the openings 31 of the rectifying plate 30 are not limited to the structure shown in FIG. 1, and various modifications can be made, for example, as in Modifications 1 to 4 below.
  • Each of the modifications has a configuration in which a plurality or one opening 31 is formed so that the flow resistance when passing through the rectifying plate 30 is smaller on the side farther than the side near the upstream passage hole 20a. .
  • FIGS. 5A and 5B are explanatory views of a first modification of the current plate 30 in FIG. 3, where FIG. 5A is a front view, FIG. 5B is a cross-sectional view taken along the line AA in FIG.
  • the plurality of openings 31 are provided in each of the region A1 and the region A2, but one opening 31 (31a, 31b) may be provided in each of the region A1 and the region A2.
  • FIG. 5 shows an example in which the shape of the opening 31 is rectangular. Also in this configuration, as in FIG. 4, the opening area 31a on the region A1 side far from the upstream passage hole 20a is made larger than the opening portion 31b on the region A2 side near the upstream passage hole 20a. ing.
  • FIG. 6A and 6B are explanatory views of a second modification of the current plate 30 in FIG. 3, in which FIG. 6A is a front view, FIG. 6B is a cross-sectional view taken along the line AA in FIG.
  • the diameter of the opening 31 is different in each of the region A1 and the region A2, but in FIG. 6, all the openings have the same diameter, and the number of the openings 31 is increased as the distance from the upstream passage hole 20a increases. I try to increase it.
  • the opening area of the opening 31 is increased in two steps from the side closer to the upstream passage hole 20a to the side farther from the side closer to the upstream side passage hole 20a.
  • the number of steps is not limited to two. Shows an example of three stages.
  • FIG. 7A and 7B are explanatory views of a third modification of the rectifying plate 30 in FIG. 3, in which FIG. 7A is a front view, FIG. 7B is a cross-sectional view taken along the line AA in FIG. In FIG. 7, the number of openings 31 is one, and the opening area of the rectifying plate 30 increases as the distance from the upstream passage hole 20a increases from the shorter side.
  • FIG. 8A and 8B are explanatory views of a fourth modification of the current plate 30 in FIG. 3, in which FIG. 8A is a front view, FIG. 8B is a plan view, and FIG. 8C is a side view.
  • the rectifying plate 30 in FIG. 8 is such that the height of the rectifying plate 30 in the stacking direction (the left-right direction in FIG. 1) decreases as the distance from the upstream side passage hole 20a in the rectifying plate 30 increases. Is formed.
  • the rectifying plate 30 shown in FIG. 3 to FIG. 8 has a simple rectifying plate shape, but may be configured as in the following modified example 5 shown in FIG.
  • FIG. 9A and 9B are explanatory views of Modification 5 of the current plate 30 shown in FIG. 3, wherein FIG. 9A is a front view, FIG. 9B is an end view taken along the line AA of FIG. .
  • the rectifying plate 30 has a configuration in which a pair of leg portions 32 extending in parallel to each other in a direction orthogonal to the rectifying plate 30 is provided from both ends of the rectifying plate 30 in a short direction (a direction orthogonal to the partition direction). . By making each of the pair of leg portions 32 a joint surface with the heat transfer plate 1, the rectifying plate 30 becomes a support column.
  • the current plate 30 when it is formed into the shape shown in FIG. 9, if it is manufactured by a press, it can be manufactured by one press, so that it can be manufactured at a low cost.
  • Embodiment 2 FIG. The second embodiment is different from the first embodiment with respect to the arrangement of the current plate 30. Other points are the same as in the first embodiment. Note that the modification applied to the same components as those in the first embodiment is similarly applied to the second embodiment.
  • FIG. 10 is an enlarged perspective view of a main part of the plate heat exchanger according to Embodiment 2 of the present invention.
  • the rectifying plate 30 is inclined and provided on the heat transfer plate 1 so that the distance between the rectifying plate 30 and the inner fin 2 decreases from the side closer to the upstream passage hole 20a toward the far side. .
  • the same effect as in the first embodiment can be obtained, and the fluid that has flowed into the flow path from the upstream-side passage hole 20a can be guided to the region M.
  • This makes it easier for the fluid to flow to the region M than when the rectifying plate 30 is disposed orthogonal to the flow direction as in the first embodiment.
  • the flow velocity distribution can be adjusted more finely by adjusting the inclination angle of the rectifying plate 30 in the second embodiment.
  • Embodiment 3 FIG.
  • the rectifying plate 30 is disposed between the upstream passage hole 20 a and the inner fin 2 in each of the first flow path A and the second flow path B.
  • the rectifying plate 30 is also disposed between the downstream passage hole 20b and the inner fin 2.
  • Other points are the same as in the first and second embodiments. Note that the modification applied to the same components as those in the first embodiment is similarly applied to the second embodiment.
  • FIG. 11 is a perspective view of a plate heat exchanger according to Embodiment 3 of the present invention. As shown in FIG. 11, the rectifying plate 30 is also arranged between the downstream passage hole 20 b and the inner fin 2.
  • the same effects as those of the first and second embodiments can be obtained, and the rectifying plates 30 are arranged on both the upstream side and the downstream side. Side distribution is improved. Thereby, compared with the case where the baffle plate 30 is arrange
  • the rectifying plate 30 is located at the entrance / exit of the flow path, the flow of the heat exchanger for fluid such as an air conditioner capable of switching between cooling and heating or an air conditioner capable of simultaneous cooling and heating is changed. It is effective when applied to a device whose direction is switched in the opposite direction.
  • the inlet side rectifying plate 30 and the outlet side rectifying plate 30 are matched to the density change.
  • the total opening area of the openings 31 may be made different. For example, when the inlet side is liquid and the outlet side is steam (that is, the density is lower than that of the liquid and the pressure loss when passing through the opening 31 tends to increase), as shown in FIG.
  • the total opening area of the current plate 30 on the left side of 12 may be larger than the total opening area of the current plate 30 on the inlet side (right side in FIG. 12). Thereby, the pressure loss can be reduced.
  • Embodiment 4 relates to a refrigeration cycle apparatus to which the plate heat exchanger according to any one of the first to third embodiments is applied.
  • FIG. 13 is a diagram showing a refrigerant circuit of the refrigeration cycle apparatus 40 according to Embodiment 4 of the present invention.
  • the refrigeration cycle apparatus 40 is a general refrigeration cycle apparatus including a compressor 41, a condenser (including a gas cooler) 42, a throttle device 43, and an evaporator 44.
  • the plate heat exchanger according to any one of the first to third embodiments is applied as one or both of the condenser 42 and the evaporator 44 of the refrigeration cycle apparatus 40.
  • the refrigeration cycle apparatus 40 having high energy saving and high reliability and low cost can be obtained.
  • the refrigerant circuit shown in FIG. 13 is an example, and the refrigerant circuit to which the plate heat exchanger of the present invention is applied is not limited to the configuration shown in FIG.
  • a refrigerant circuit that can be switched between cooling and heating by providing a four-way valve may be used, or a refrigerant circuit that can be operated simultaneously with cooling and heating.
  • the present invention can be used for many industrial and household equipment equipped with a plate heat exchanger, such as air conditioning, power generation, and food sterilization equipment.

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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

L'invention porte sur un échangeur de chaleur du type à plaques, lequel échangeur est configuré de telle manière que des premiers passages d'écoulement (A) et des seconds passages d'écoulement (B) sont formés en alternance entre des plaques de transfert de chaleur (1) disposées à des intervalles prédéterminés, et de telle manière que des ailettes internes (2) sont disposées sur les premiers passages d'écoulement (A) et les seconds passages d'écoulement (B). Chacune des plaques de transfert de chaleur (1) comporte : un trou de passage amont (20a) qui joue le rôle soit d'entrée pour admettre un premier fluide dans le premier passage d'écoulement (A) soit d'entrée pour admettre un second fluide dans le second passage d'écoulement (B); et un trou de passage aval (20b) qui joue le rôle soit de sortie pour laisser sortir le premier fluide hors du premier passage d'écoulement (A) soit de sortie pour laisser sortir le second fluide hors du second passage d'écoulement (B). Chacun des premiers passages d'écoulement (A) et des seconds passages d'écoulement (B) a, installé à l'intérieur de celui-ci, une plaque de régulation d'écoulement (30) montée de façon à séparer le trou de passage amont (20a) et l'ailette interne (2). Chacune des plaques de régulation d'écoulement (30) a des ouvertures (31) jouant le rôle de passages d'écoulement pour le premier fluide ou le second fluide, et est configurée de telle sorte que les zones des ouvertures (31) sont réglées de telle sorte que la résistance du passage d'écoulement diminue à partir du côté proche du trou de passage amont (20a) vers le côté éloigné de celui-ci.
PCT/JP2013/058210 2013-03-22 2013-03-22 Échangeur de chaleur du type à plaques et dispositif de cycle de réfrigération le comportant WO2014147804A1 (fr)

Priority Applications (5)

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EP13878608.2A EP2977704B1 (fr) 2013-03-22 2013-03-22 Échangeur de chaleur du type à plaques et dispositif de cycle de réfrigération le comportant
JP2015506497A JP6091601B2 (ja) 2013-03-22 2013-03-22 プレート式熱交換器及びそれを備えた冷凍サイクル装置
PCT/JP2013/058210 WO2014147804A1 (fr) 2013-03-22 2013-03-22 Échangeur de chaleur du type à plaques et dispositif de cycle de réfrigération le comportant
CN201420068680.6U CN203785330U (zh) 2013-03-22 2014-02-18 板式换热器及具有该板式换热器的制冷循环装置
HK16104130.5A HK1216114A1 (zh) 2013-03-22 2016-04-12 板式換熱器及具有該板式換熱器的製冷循環裝置

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PCT/JP2013/058210 WO2014147804A1 (fr) 2013-03-22 2013-03-22 Échangeur de chaleur du type à plaques et dispositif de cycle de réfrigération le comportant

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JP2018189352A (ja) * 2017-04-28 2018-11-29 株式会社前川製作所 熱交換器
WO2020110685A1 (fr) * 2018-11-26 2020-06-04 三菱電機株式会社 Échangeur de chaleur de type à plaques et système de distribution d'eau chaude de type à pompe à chaleur
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CN115210522A (zh) * 2020-03-05 2022-10-18 翰昂汽车零部件有限公司 板式热交换器
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JP7505400B2 (ja) 2020-12-25 2024-06-25 株式会社富士通ゼネラル 熱交換器

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JP6091601B2 (ja) 2017-03-08
EP2977704A1 (fr) 2016-01-27
JPWO2014147804A1 (ja) 2017-02-16

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