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EP2977704B1 - Plattenwärmetauscher und kältekreislaufvorrichtung damit - Google Patents

Plattenwärmetauscher und kältekreislaufvorrichtung damit Download PDF

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Publication number
EP2977704B1
EP2977704B1 EP13878608.2A EP13878608A EP2977704B1 EP 2977704 B1 EP2977704 B1 EP 2977704B1 EP 13878608 A EP13878608 A EP 13878608A EP 2977704 B1 EP2977704 B1 EP 2977704B1
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EP
European Patent Office
Prior art keywords
upstream
plate
straightening plate
flow straightening
flow
Prior art date
Legal status (The legal status 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 status listed.)
Active
Application number
EP13878608.2A
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English (en)
French (fr)
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EP2977704A1 (de
EP2977704A4 (de
Inventor
Daisuke Ito
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication date
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Publication of EP2977704A1 publication Critical patent/EP2977704A1/de
Publication of EP2977704A4 publication Critical patent/EP2977704A4/de
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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-type heat exchanger and a refrigeration cycle apparatus including the same.
  • This kind of plate-type heat exchanger has a passage hole serving as a fluid inlet, and a fluid flowing in from the passage hole passes through the inner fin.
  • the fluid flows at a lower velocity on the side farther away from the passage hole and flows at a higher velocity on the side closer to the passage hole.
  • a flow velocity distribution is likely to occur inside the flow passage, and a region of a low velocity becomes a fluid stagnation part and fails to function as a heat transfer surface.
  • the uneven flow causes an increase in pressure loss. Therefore, in Patent Literatures 1 to 3, a flow straightening part for uniformizing the flow velocity distribution is provided.
  • Patent literature 1 discloses a plate type heat exchanger with the features in the preamble of claim 1.
  • Both of the flow straightening parts of Patent Literatures 1 and 2 are configured by intricately combining a plurality of sheet-like members, which makes them costly and difficult to produce.
  • the flow straightening member of Patent Literature 3 is formed by partially cutting and raising, and molding one sheet-like member, or folding a sheet-like member several times, and therefore further simplification of the structure is desired.
  • the present invention has been devised in view of these problems, and an object of the invention is to provide a low-cost plate-type heat exchanger which can uniformize flow velocity distribution with a simple structure and a refrigeration cycle apparatus including this plate-type heat exchanger.
  • a plate-type heat exchanger as defined in claim 1.
  • a low-cost plate-type heat exchanger can be obtained which can uniformize flow velocity distribution with a simple structure by virtue of the disposition of the flow straightening plate.
  • Fig. 1 is a view showing a typical inner-finned plate-type heat exchanger in an embodiment of the present invention.
  • Fig. 2 is a view showing one example of inner fins 2 of Fig. 1 .
  • Fig. 3 is an enlarged perspective view of the major part of Fig. 1 .
  • components given the same reference signs are the same or equivalent components, and this applies throughout the entire text of the specification.
  • the forms of the components represented in the entire text of the specification are mere examples, and the forms of the components are not limited to those described herein.
  • the inner-finned plate-type heat exchanger (hereinafter simply referred to as a "plate heat exchanger") has a plurality of heat transfer plates 1 which are flat heat transfer surfaces.
  • the plurality of heat transfer plates 1 are provided at predetermined intervals, and first flow passages A through which a first fluid flows and second flow passages B through which a second fluid flows are alternately formed between the plurality of heat transfer plates 1.
  • first flow passages A through which a first fluid flows and second flow passages B through which a second fluid flows are alternately formed between the plurality of heat transfer plates 1.
  • the flow direction of the first fluid and the flow direction of the second fluid are indicated by the reference signs x and y, respectively.
  • Each of the first flow passages A and the second flow passages B is provided with an inner fin 2 which promotes heat transfer.
  • side plates 3 functioning as a reinforcement are provided, and these side plates 3, the plurality of heat transfer plates 1, and the inner fins 2 are joined integrally as a whole.
  • an offset fin is used as the inner fin 2.
  • the offset fin has a configuration in which ridges and valleys in a plate width direction of a corrugated fin are formed in a staggered manner by being shifted by a half ridge in the plate width direction at a predetermined pitch in the longitudinal direction of the plate.
  • the plurality of heat transfer plates 1 and the two side plates 3 are formed of a substantially rectangular metal flat plate, and a first fluid inflow pipe 4, a first fluid outflow pipe 5, a second fluid inflow pipe 6, and a second fluid outflow pipe 7 are provided at four corners of one of the two side plates 3.
  • Each heat transfer plate 1 has a first opening 11, a second opening 12, a third opening 13, and a fourth opening 14 formed at positions corresponding to the first fluid inflow pipe 4, the first fluid outflow pipe 5, the second fluid inflow pipe 6, and the second fluid outflow pipe 7.
  • These first opening 11, second opening 12, third opening 13, and fourth opening 14 form an inflow port of the first flow passage A, an outflow port of the first flow passage A, an inflow port of the second flow passage B, and an outflow port of the second flow passage B, respectively.
  • a cover part 21 (see Fig. 3 ) is provided around the first opening 11 and the second opening 12 or around the third opening 13 and the fourth opening 14. This cover part 21 seals the third opening 13 and the fourth opening 14 in the first flow passage A where the first fluid flows, and seals the first opening 11 and the second opening 12 in the second flow passage B where the second fluid flows. Thus, inflow of the second fluid into the first flow passage A is blocked, as well as inflow of the first fluid into the second flow passage B is blocked.
  • openings communicating with the inner fin 2 will be referred to as passage holes.
  • the first opening 11 and the second opening 12 are the passage holes in the first flow passage A
  • the third opening 13 and the fourth opening 14 are passage holes in the second flow passage B.
  • the passage hole serving as a fluid inlet will be referred to as an upstream-side passage hole 20a
  • the passage hole serving as a fluid outlet will be referred to as a downstream-side passage hole 20b.
  • flow passages where no distinction is made between the first flow passage A and the second flow passage B, these will be simply referred to as flow passages.
  • the first fluid and the second fluid these will be simply referred to as fluids.
  • the fluid flowing into the flow passage from the upstream-side passage hole 20a flows generally at a higher velocity in the vicinity of the upstream-side passage hole 20a and at a lower velocity at a distance from the upstream-side passage hole 20a.
  • the fluid does not flow easily to a region M which is at a large distance from the upstream-side passage hole 20a, so that the fluid stagnates in the region M.
  • the effective heat transfer area decreases.
  • the present invention has adopted the following configuration. That is, a sheet-like flow straightening plate 30 for uniformizing flow velocity is disposed in each of the first flow passages A and the second flow passages B between the upstream-side passage hole 20a and the inner fin 2. The flow straightening plate 30 is disposed in the heat transfer plate 1 so as to separate between the upstream-side passage hole 20a and the inner fin 2.
  • Fig. 4 is a view illustrating the flow straightening plate 30 of Fig. 3 , in which Fig. 4(a) is a front view, Fig. 4(b) is a cross-sectional view along the line A-A of Fig. 4(a), and Fig. 4(c) is a side view.
  • Fig. 4 is a view illustrating the features of the flow straightening plate 30 of Fig. 3 , and the number, scale, etc. of opening parts 31 do not exactly correspond to those of Fig. 3 . The same applies to the drawings illustrating the flow straightening plate 30 to be described later.
  • the plurality of opening parts 31 are formed at intervals in the separation direction of the flow straightening plate 30 (longitudinal direction of the flow straightening plate 30).
  • the opening areas of the plurality of opening parts 31 are designed so that the flow passage resistance of the flow straightening plate 30 decreases from the side on which the distance to the upstream-side passage hole 20a is smaller toward the side on which the distance is larger. More specifically, the opening areas of the plurality of opening parts 31 increase in the order of their positions from the side on which the distance to the upstream-side passage hole 20a is smaller toward the side on which the distance is larger in the flow straightening plate 30.
  • the plurality of opening parts 31 are circular in this example, and the diameter of the opening parts 31a on the side of a region A1 which is farther away from the upstream-side passage hole 20a is larger than the diameter of the opening parts 31b on the side of a region A2 which is closer to the upstream-side passage hole 20a.
  • the opening areas are designed in two stages in this example, the number of stages is not limited to two and may be made in a larger number of stages.
  • the opening area of the opening parts 31a located on the side of the region A1 farther away from the upstream-side passage hole 20a is larger than the opening area of the opening parts 31b located on the side of the region A2 closer to the upstream-side passage hole 20a. Accordingly, in the flow straightening plate 30, the flow passage resistance on the side of the region A1 where the flow velocity is lower is smaller than the flow passage resistance on the side of the region A2 where the flow velocity is higher, so that the fluid flows more easily to the region M. Thus, it is possible to uniformize the flow velocity in the X-Y direction and remedy the fluid stagnation in the region M. As a result, since the portion downstream from the region M in the heat transfer plate 1 is allowed to function as a heat transfer surface, the effective heat transfer area can be increased.
  • a length L1 in the X-Y direction of the region A1 where the opening parts 31 are larger should be shorter than a length L2 in the same direction of the cover part 21. Since the flow passage formed by the cover part 21 and the flow straightening plate 30 is narrower than the flow passage between the upstream-side passage hole 20a and the flow straightening plate 30, the fluid does not flow easily to the region M. For this reason, the flow straightening plate 30 is provided with the region of the length L1 having a smaller resistance; however, if the length L1 is larger than the length L2, the fluid flows out of the opening parts 31 inside the region of the length L1 on the near side before flowing into the region M, which makes it difficult to uniformize the velocity. If the length L1 is smaller than the length L2, the velocity can be further uniformized compared with the case of L1 > L2.
  • the opening areas in the flow straightening plate 30 can be designed so as to reduce the increase in pressure loss due to this resistance. This is effective for the remedy of unevenness in flow velocity distribution.
  • the shapes of the opening parts 31 are not limited to circular but may be square, rectangular, etc.
  • the diameters of the opening parts 31a in the region A1 are all the same, and the diameters of the opening parts 31b in the region A2 are all the same as well, but the diameters may be gradually increased as the distance from the upstream-side passage hole 20a increases.
  • the sheet-like flow straightening plate 30 is disposed between the upstream-side passage hole 20a and the inner fin 2 provided in the heat transfer plate 1 so as to separate between them.
  • the plurality of opening parts 31 are provided at intervals in the separation direction in the flow straightening plate 30.
  • the opening areas of the plurality of opening parts 31 are designed so that the flow passage resistance to the fluid while passing through the flow straightening plate 30 is smaller on the side farther away from the upstream-side passage hole 20a than on the side closer to the upstream-side passage hole 20a.
  • the flow straightening plate 30 is simply structured with a sheet-like member having holes bored therein, the production is easy and the effect of the increased effective heat transfer area and the reduced pressure loss can be obtained at low cost, as well as a weight reduction can be achieved.
  • the flow straightening plate 30 is simply structured with a sheet-like member having holes bored therein, the size of each opening part 31 can also be easily adjusted to uniformize the flow velocity distribution. While producing the flow straightening plate 30 as a single part is also inexpensive, molding the flow straightening plate 30 integrally with the inner fin 2 is more inexpensive, as the number of parts is reduced in that way.
  • the flow straightening plate 30 can be joined on the heat transfer plate 1 by brazing, and the plate-type heat exchanger can be manufactured inexpensively by integral brazing.
  • partition walls which are portions between each two opening parts 31, have an effect of mixing the fluid passing through the opening parts 31, which in turn has a favorable effect on uniformization of the flow velocity.
  • the flow straightening plate 30 Since the flow straightening plate 30 is disposed upright so as to separate between the upstream-side passage hole 20a and the inner fin 2, the flow straightening plate 30, which functions as a distribution improving mechanism, requires no large space for installation but can be installed in a small space.
  • the region M where stagnation is likely to occur is a portion where the flow velocity of a fluid is low if the flow straightening plate 30 is not provided. Therefore, when the fluid is water and the plate-type heat exchanger is used as an evaporator, the temperature decreases locally and the region M becomes a freezing starting point. In Embodiment 1, by contrast, freezing can be suppressed since the flow velocity of the fluid in the region M can be increased, so that quality improvement can be achieved.
  • the plate-type heat exchanger of Embodiment 1 has advantages such as high heat transfer efficiency, low pressure loss, and high reliability, CO 2 refrigerant having a low evaporation capacity, hydrocarbon refrigerant having a large pressure loss, and flammable refrigerant such as a low GWP refrigerant become also available.
  • the offset fin is used as the inner fin 2, the following effects can be obtained.
  • the offset fin is a heat transfer promotion body having low pressure loss, and due to its small resistance, the fluid flows easily in a linear manner. Therefore, if the flow straightening plate 30 is not provided and the fluid does not flow into the region M, almost no fluid would flow to 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 achieve a reduction of the pressure loss and an increase of the effective heat transfer area by using the offset fin having low pressure loss as a heat transfer surface, and further combining it with the flow straightening plate 30.
  • a leading edge effect of the offset fin allows enhanced heat transfer as well as suppression of increase in pressure loss.
  • the leading edge effect refers to an effect that is realized by preferentially using a leading edge portion of a flat plate as a heat transfer part based on the property that the heat transfer rate is favorable at the leading edge portion of the flat plate. That is, when a flat plate is placed in a flow, the boundary layer is thin at the leading edge of the flat plate, and the thickness increases toward the downstream side. Accordingly, the heat transfer is favorable at the leading edge portion of the flat plate where the boundary layer is thin.
  • each of the flow straightening plate 30, the offset fin, the heat transfer plate 1 being a flat heat transfer surface can be produced by pressing, a plate-type heat exchanger having low pressure loss and high heat transfer performance can be manufactured inexpensively. If the plate-type heat exchanger has low pressure loss, the power required for activating a fluid is reduced. Accordingly, the capacity of a pump and a compressor serving as a power source for circulating the fluid into the plate-type heat exchanger can be reduced.
  • the inner fin 2 of the present invention is not limited to the offset fin.
  • the inner fin 2 of the present invention is not limited to the fin which is formed separately from the heat transfer plate 1, but also includes a fin which is formed, for example, by corrugating the surface of the heat transfer plate 1.
  • An equal distribution of the flow rate is required on the inlet side of the flow passage, and is not required on the outlet side. Therefore, instead of providing the flow straightening plate 30 on both inlet side and outlet side, providing the flow straightening plate 30 only on the inlet side can reduce the cost.
  • the number, shape, and disposition of the opening parts 31 of the flow straightening plate 30 are not limited to those in the structure shown in Fig. 1 , and various modifications can be made, for example, as shown in the following Modified Examples 1 to 4.
  • Each of these modified examples has a configuration in which the plurality of or one opening part 31 is formed so that the flow passage resistance to a fluid while passing through the flow straightening plate 30 is smaller on the side farther away from the upstream-side passage hole 20a than on the side closer to the upstream-side passage hole 20a.
  • Each of the modified examples has an effect of uniformizing the flow velocity.
  • Fig. 5 is a view illustrating Modified Example 1 of the flow straightening plate 30 of Fig. 3 , in which Fig. 5(a) is a front view, Fig. 5(b) is a cross-sectional view along the line A-A of Fig. 5(a), and Fig. 5(c) is a side view.
  • FIG. 4 shows an example in which the shape of the opening part 31 is rectangular.
  • the opening area of the opening part 31a on the side of the region A1 farther away from the upstream-side passage hole 20a is larger than the opening area of the opening part 31b on the side of the region A2 closer to the upstream-side passage hole 20a.
  • Fig. 6 is a view illustrating Modified Example 2 of the flow straightening plate 30 of Fig. 3 , in which Fig. 6(a) is a front view, Fig. 6(b) is a cross-sectional view along the line A-A of Fig. 6(a), and Fig. 6(c) is a side view.
  • the diameters of the opening parts 31 are different between the region A1 and the region A2
  • the diameters are all the same and the number of the opening parts 31 disposed increases as the distance to the upstream-side passage hole 20a increases.
  • the opening areas of the opening parts 31 are increased in two stages, from the side on which the distance to the upstream-side passage hole 20a is smaller toward the side on which the distance is larger.
  • the number of stages is not limited to two, and Fig. 6 shows an example of three stages.
  • Fig. 7 is a view illustrating Modified Example 3 of the flow straightening plate 30 of Fig. 3 , in which Fig. 7(a) is a front view, Fig. 7(b) is a cross-sectional view along the line A-A of Fig. 7(a), and Fig. 7(c) is a side view.
  • the number of the opening parts 31 is one, and the opening area increases from the side on which the distance to the upstream-side passage hole 20a is smaller toward the side on which the distance is larger in the flow straightening plate 30.
  • Fig. 8 is a view illustrating Modified Example 4 of the flow straightening plate 30 of Fig. 3 , in which Fig. 8(a) is a front view, Fig. 8(b) is a plan view, and Fig. 8(c) is a side view.
  • the flow straightening plate 30 of Fig. 8 is formed so that the height of the flow straightening plate 30 in the stacking direction (left-right direction in Fig. 1 ) decreases from the side on which the distance to the upstream-side passage hole 20a is smaller toward the side on which the distance is larger in the flow straightening plate 30.
  • flow straightening plates 30 shown in Fig. 3 to Fig. 8 have a simple sheet-like shape
  • the flow straightening plate 30 may be configured as in Modified Example 5 shown in Fig. 9 .
  • Fig. 9 is a view illustrating Modified Example 5 of the flow straightening plate 30 of Fig. 3 , in which Fig. 9(a) is a front view, Fig. 9(b) is a cross-sectional end view along the line A-A of Fig. 9(a), and Fig. 9(c) is a side view.
  • This flow straightening plate 30 has a pair of leg portions 32 which extend parallel to each other in a direction orthogonal to the flow straightening plate 30 from both ends in the short direction (direction orthogonal to the separation direction) of the flow straightening plate 30.
  • each of the pair of leg portions 32 serves a joint surface between the flow straightening plate 30 and the heat transfer plate 1
  • the flow straightening plate 30 serves as a support column. Then, it is possible to adjust the area of the joint surface between the pair of leg portions 32 and the heat transfer plate 1 according to the required strength by adjusting the lengths of the pair of leg portions 32.
  • Embodiment 2 is different from Embodiment 1 in terms of the disposition of the flow straightening plate 30.
  • Embodiment 2 is otherwise the same as Embodiment 1.
  • the modified examples applicable to the same component parts as those of Embodiment 1 shall be similarly applicable to Embodiment 2.
  • Fig. 10 is an enlarged perspective view of the major part of the plate-type heat exchanger according to Embodiment 2 of the present invention.
  • the flow straightening plate 30 is provided at an angle on the heat transfer plate 1 so that the clearance between the flow straightening plate 30 and the inner fin 2 decreases from the side closer to the upstream-side passage hole 20a toward the side farther away from the upstream-side passage hole 20a.
  • Embodiment 1 With this configuration, the same effects as in Embodiment 1 can be obtained, as well as the fluid flowing into the flow passage from the upstream-side passage hole 20a can be guided to the region M.
  • the fluid flows more easily to the region M than in the case where the flow straightening plate 30 is disposed orthogonally to the flow direction as in Embodiment 1. Therefore, a finer adjustment of the flow velocity distribution is made possible by the adjustment of the inclination angle of the flow straightening plate 30 of Embodiment 2 in addition to the designing of the opening areas of the opening parts 31 of Embodiment 1.
  • the flow straightening plate 30 is disposed in each of the first flow passages A and the second flow passages B between the upstream-side passage hole 20a and the inner fin 2.
  • the flow straightening plate 30 is disposed between the downstream-side passage hole 20b and the inner fin 2 as well.
  • Embodiment 3 is otherwise the same as Embodiments 1 and 2.
  • the modified examples applicable to the same component parts as those of Embodiment 1 shall be similarly applicable to Embodiment 3.
  • Fig. 11 is a perspective view of the plate-type heat exchanger according to Embodiment 3 of the present invention.
  • the flow straightening plate 30 is disposed between the downstream-side passage hole 20b and the inner fin 2 as well.
  • Embodiment 3 the same effects as Embodiments 1 and 2 can be obtained, and since the flow straightening plate 30 is disposed on both of the upstream side and the downstream side, the distribution is improved not only on the inlet side but also on the outlet side. Therefore, compared with the case where the flow straightening plate 30 is disposed only at the inlet, higher effects can be obtained in terms of an increase of the effective heat transfer area, a reduction of the pressure loss, and suppression of freezing.
  • this plate-type heat exchanger is effective when applied to a device in which the flow direction of a fluid inside a heat exchanger switches to the opposite direction, such as an air-conditioning device capable of switching between cooling and heating or an air-conditioning device capable of cooling and heating simultaneous operation.
  • the total opening area of the opening parts 31 may be varied according to the change in density between the flow straightening plate 30 on the inlet side and the flow straightening plate 30 on the outlet side.
  • the total opening area of the flow straightening plate 30 on the outlet side may be larger than the total opening area of the flow straightening plate 30 on the inlet side (on the right side in Fig. 12 ).
  • the pressure loss can be reduced.
  • Embodiment 4 relates to a refrigeration cycle apparatus to which the plate-type heat exchanger of any one of Embodiment 1 to Embodiment 3 is applied.
  • Fig. 13 is a view showing a refrigerant circuit of a refrigeration cycle apparatus 40 according to Embodiment 4 of the present invention.
  • the refrigeration cycle apparatus 40 is a typical refrigeration cycle apparatus which includes a compressor 41, a condenser (including a gas cooler) 42, an expansion device 43, and an evaporator 44. As one or both of the condenser 42 and the evaporator 44 of the refrigeration cycle apparatus 40, the plate-type heat exchanger of any one of Embodiment 1 to Embodiment 3 is applied.
  • Embodiment 4 it is possible to obtain the low-cost refrigeration cycle apparatus 40, which has high reliability and energy saving performance, by including the plate-type heat exchanger of Embodiment 1 to Embodiment 3.
  • the refrigerant circuit shown in Fig. 13 is an example, and the refrigerant circuit to which the plate-type heat exchanger of the present invention is applied is not limited to the configuration of Fig. 13 .
  • the refrigerant circuit may be a circuit which is provided with a four-way valve and can switch between cooling and heating, or a circuit which is capable of cooling and heating simultaneous operation.
  • Examples of applications of the present invention include many industrial and household appliances equipped with a plate-type heat exchanger, such as an air-conditioner, a power generator, and a heat-sterilization treatment apparatus for food.
  • a plate-type heat exchanger such as an air-conditioner, a power generator, and a heat-sterilization treatment apparatus for food.

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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)

Claims (7)

  1. Plattenwärmetauscher, in dem erste Strömungsdurchlässe (A) und zweite Strömungsdurchlässe (B) zwischen einer Vielzahl von Wärmeübertragungsplatten (1), die in vorherbestimmten Abständen vorgesehen sind, abwechselnd angeordnet sind und die ersten Strömungsdurchlässe (A) und die zweiten Strömungsdurchlässe (B) jeweils mit einer inneren Rippe (2) versehen sind, dadurch gekennzeichnet, dass
    jede der Vielzahl von Wärmeübertragungsplatten (1) ein stromaufwärtsseitiges Durchlassloch (20a), dienend als ein Einlass eines Fluids in den ersten Strömungsdurchlass (A) oder als ein Einlass eines zweiten Fluids in den zweiten Strömungsdurchlass (B), und ein stromabwärtsseitiges Durchlassloch (20b), dienend als ein Auslass des ersten Fluids aus dem ersten Strömungsdurchlass (A) oder als ein Auslass des zweiten Fluids aus dem zweiten Strömungsdurchlass (B), aufweist,
    eine stromaufwärtsseitige Strömungsausrichtungsplatte (30) in jedem von dem ersten Strömungsdurchlass (A) und dem zweiten Strömungsdurchlass (B) angeordnet ist, um jeden Strömungsdurchlass in eine Seite des stromaufwärtsseitigen Durchlasslochs (20a) und Seite der inneren Rippe (2) zu trennen,
    die stromaufwärtige Strömungsausrichtungsplatte (30) eine Vielzahl von Öffnungsteilen (31) aufweist, die als ein Strömungsdurchlass für das erste Fluid oder das zweite Fluid dienen, und Öffnungsbereiche der Vielzahl von Öffnungsteilen (31) so ausgestaltet sind, dass ein Strömungsdurchlasswiderstand aufgrund der stromaufwärtsseitigen Strömungsausrichtungsplatte (30) auf einer Seite, auf der ein Abstand zum stromaufwärtsseitigen Durchlassloch (20a) größer ist als auf einer Seite, auf der der Abstand kleiner ist,
    eine stromabwärtsseitige Strömungsausrichtungsplatte (30) zwischen dem stromabwärtsseitigen Durchlassloch (20b) und der inneren Rippe (2) angeordnet ist, und
    die stromabwärtsseitige Strömungsausrichtungsplatte (30) eine Vielzahl von Öffnungsteilen (31) aufweist, die die gleichen Formen wie Formen der Vielzahl von Öffnungsteilen (31) der stromaufwärtsseitigen Strömungsausrichtungsplatte (30) haben, und eine Gesamtöffnungsfläche der Vielzahl von Öffnungsteilen (31) der stromabwärtsseitigen Strömungsausrichtungsplatte (30) sich von der der stromaufwärtsseitigen Strömungsausrichtungsplatte (30) unterscheidet.
  2. Plattenwärmetauscher nach Anspruch 1, wobei eine Gesamtöffnungsfläche von einer von der stromaufwärtsseitigen Strömungsausrichtungsplatte (30) und der stromabwärtsseitigen Strömungsausrichtungsplatte (30), die ein Fluid mit einer geringeren Dichte passiert, größer ist als eine Gesamtöffnungsfläche einer anderen von der stromaufwärtsseitigen Strömungsausrichtungsplatte (30) und der stromabwärtsseitigen Strömungsausrichtungsplatte (30), die ein Fluid mit einer höheren Dichte passiert.
  3. Plattenwärmetauscher nach Anspruch 1 oder 2, wobei die Öffnungsbereiche der Vielzahl von Öffnungsteilen (31) der stromaufwärtsseitigen Strömungsausrichtungsplatte (30) größer sind auf einer Seite, auf der ein Abstand zwischen der Vielzahl von Öffnungsteilen (31) der stromaufwärtsseitigen Strömungsausrichtungsplatte (30) und dem stromaufwärtsseitigen Durchlassloch (20a) größer ist als auf einer Seite, auf der der Abstand kleiner ist.
  4. Plattenwärmetauscher nach einem der Ansprüche 1 bis 3, wobei die Vielzahl von Öffnungsteilen (31) der stromaufwärtsseitigen Strömungsausrichtungsplatte (30) die gleiche Größe haben, und
    die Anzahl der Vielzahl von Öffnungsteilen (31) der stromaufwärtsseitigen Strömungsausrichtungsplatte (30) auf der Seite größer ist, auf der der Abstand zwischen der stromaufwärtsseitigen Strömungsausrichtungsplatte (30) und dem stromaufwärtsseitigen Durchlassloch (20a) größer ist als auf der Seite, auf der der Abstand in der stromaufwärtsseitigen Strömungsausrichtungsplatte (30) kleiner ist.
  5. Plattenwärmetauscher nach einem der Ansprüche 1 bis 4, wobei die innere Rippe (2) eine versetzte Rippe ist.
  6. Plattenwärmetauscher nach einem der Ansprüche 1 bis 5, wobei die stromaufwärtsseitige Strömungsausrichtungsplatte (30) ferner ein Paar Schenkelabschnitte (32) aufweist, die sich parallel zueinander in einer Richtung orthogonal zur stromaufwärtsseitigen Strömungsausrichtungsplatte (30) von beiden Enden in einer Richtung orthogonal zu einer Trennungsrichtung der stromaufwärtsseitigen Strömungsausrichtungsplatte (30) erstrecken, und das Paar Schenkelabschnitte (32) als eine Verbindungsoberfläche zwischen der stromaufwärtsseitigen Strömungsausrichtungsplatte (30) und jeder der Wärmeübertragungsplatten (1) dient.
  7. Kältekreislaufeinrichtung (40), umfassend den Plattenwärmetauscher nach einem der Ansprüche 1 bis 6.
EP13878608.2A 2013-03-22 2013-03-22 Plattenwärmetauscher und kältekreislaufvorrichtung damit Active EP2977704B1 (de)

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HK1216114A1 (zh) 2016-10-14
WO2014147804A1 (ja) 2014-09-25
EP2977704A4 (de) 2017-02-01
JP6091601B2 (ja) 2017-03-08
CN203785330U (zh) 2014-08-20
JPWO2014147804A1 (ja) 2017-02-16

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