WO2011062118A1 - Echangeur de chaleur du type à plaques et dispositif de pompe à chaleur - Google Patents

Echangeur de chaleur du type à plaques et dispositif de pompe à chaleur Download PDF

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Publication number
WO2011062118A1
WO2011062118A1 PCT/JP2010/070192 JP2010070192W WO2011062118A1 WO 2011062118 A1 WO2011062118 A1 WO 2011062118A1 JP 2010070192 W JP2010070192 W JP 2010070192W WO 2011062118 A1 WO2011062118 A1 WO 2011062118A1
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WO
WIPO (PCT)
Prior art keywords
plate
long side
wave
outer peripheral
peripheral edge
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PCT/JP2010/070192
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English (en)
Japanese (ja)
Inventor
伊東　大輔
毅浩 林
Original Assignee
三菱電機株式会社
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Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to US13/510,633 priority Critical patent/US20120227438A1/en
Priority to EP10831513.6A priority patent/EP2503277B1/fr
Priority to CN201080052178.0A priority patent/CN102667391B/zh
Publication of WO2011062118A1 publication Critical patent/WO2011062118A1/fr
Priority to HK12112886.8A priority patent/HK1172080A1/zh

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    • 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
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/046—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being linear, e.g. corrugations
    • 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
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/04—Fastening; Joining by brazing

Definitions

  • This invention relates to a plate heat exchanger.
  • Some conventional plate heat exchangers support a top and bottom plate by providing a plurality of ridges in the longitudinal direction of the plate (see, for example, Patent Document 1). Moreover, there exists what combined the vertex of the V-shaped wave part of the upper and lower plates (for example, refer patent document 2).
  • plate type heat exchangers have firstly had problems such as an increase in pressure loss due to an increase in flow velocity for improving heat transfer of fluid, and secondly, stagnation due to an increase in pressure loss and clogging of dust.
  • Patent Document 1 the solution of Patent Document 1 is taken, but since the fluid flows only into the flow path formed by the long-axis ridges, the spread of the fluid in the short-axis direction becomes worse.
  • Patent Document 2 when the tops of the V-shaped waves are matched with the upper and lower plates as in Patent Document 2, the ends of the waves on the outer peripheral side are not matched. There was a problem that the area was increased, the flow path was narrowed, and the pressure loss was increased.
  • This invention is intended to provide a plate type heat exchanger having a simple structure and low fluid pressure loss and good heat conversion efficiency.
  • the plate heat exchanger of this invention is A plurality of rectangular plates having a long side, a short side, and an outer peripheral edge forming a space for sealing a fluid are laminated so that the long sides overlap each other, the short sides, the outer peripheral edges, Each plate is processed into a wave shape that is displaced in the stacking direction, Adjacent plates, when viewed from the stacking direction, indicate the wave bottom of one plate, indicate a plurality of virtual bottom edges extending in a direction different from the direction of the long side, and indicate the wave top of the other plate.
  • the adjacent plates are Of the intersections existing on one bottom ridge line, the contact portion corresponding to the intersection point closest to the outer peripheral edge portion along the long side is substantially the same as the outer peripheral edge portion along the long side. It was formed in the position which corresponds.
  • the pressure loss of the fluid can be reduced and the heat exchange rate can be improved.
  • the plate heat exchanger can be downsized (volume saving) by reducing pressure loss and improving thermal efficiency.
  • power consumption is reduced with improvement in thermal efficiency, and CO2 emission can be reduced.
  • FIG. 3 shows a plate heat exchanger 100 according to the first embodiment.
  • FIG. 3 shows adjacent plates in the first embodiment.
  • FIG. 6 shows a dimension b in the second embodiment.
  • FIG. 10 illustrates a region c in Embodiment 3.
  • FIG. 10 illustrates a region d in Embodiment 4. The figure explaining the state which shortened the ridgeline of the wave in Embodiment 5 for every wave.
  • FIG. 10 is a diagram for explaining a gap dimension e in a sixth embodiment. The figure which shows each cross section of the plate in the plate-type heat exchanger.
  • FIG. 1 is a diagram illustrating a plate heat exchanger 100 according to the first embodiment.
  • FIG. 1A is a side view of the plate heat exchanger 100.
  • FIG. (2) FIG.1 (b) is a front view (X arrow view).
  • the arrow X direction in FIG. 1A is the stacking direction of the plates.
  • the reinforcing side plate 1 shown in FIG. 1B is located on the outermost side and includes a fluid inlet / outlet pipe.
  • the reinforcing side plate 1 includes an inflow pipe 5 for the first fluid, an inflow pipe 6 for the second fluid, an outflow pipe 7 for the first fluid, and an outflow pipe 8 for the second fluid.
  • FIG.1 (c) shows the upper side heat-transfer plate 2 which comprises the flow path of the 1st fluid and the 2nd fluid.
  • FIG.1 (d) shows the lower heat-transfer plate 3 which a wave shape is set facing the upper heat-transfer plate 2, and comprises the flow path of the 1st fluid and the 2nd fluid.
  • FIG.1 (e) shows the side plate 4 for a reinforcement located in the outermost side.
  • FIG. 1 (f) is a diagram showing a state in which the upper heat transfer plate 2 and the lower heat transfer plate 3 are overlapped.
  • FIG. 1 (f) shows the shape of the upper heat transfer plate 2 that is actually visible when viewed in the direction of the arrow X in FIG.
  • the wave shape of the heat plate 3 is indicated by a dotted line.
  • FIG. 2 is an enlarged view of a range Y indicated by a broken line.
  • FIG. 8 shows a section AA ′ (FIG. 1C) and a section BB ′ to a section DD ′ (FIG. 2).
  • the short side (the short side 2-1 of the upper heat transfer plate 2, the short side 3-1 of the lower heat transfer plate 3) and the long side (upper side transfer).
  • a plurality of rectangular plates having the outer peripheral edge portion 3-3) of the lower heat transfer plate 3 are stacked so as to overlap each other between the long sides, the short sides, and the outer peripheral portions.
  • Each plate is processed in a wave shape that is displaced in the stacking direction (X direction).
  • FIG. 2 is a front view of the heat transfer plate.
  • FIG. 2 is an enlarged view of a range Y in FIG.
  • the end 9 of the wave trough (bottom) of the upper heat transfer plate 2 and the end 10 of the crest of the lower plate are in the minor axis direction (Z direction) from the outer peripheral edge 2-3.
  • the junction 11 (contact portion) of the upper and lower plates (upper heat transfer plate 2 and lower heat transfer plate 3) having the shortest dimension is formed.
  • This is characterized in that the dimension a (the dimension from the outer peripheral edge portion 12 toward the minor axis direction (Z direction)) in the drawing can be shortened.
  • the dimension a is a dimension from the outer peripheral edge 2-3 toward the minor axis direction (Z direction).
  • the junction point having the shortest dimension in the minor axis direction (Z direction) means a junction point that appears first when proceeding from the outer peripheral edge 2-3 in the minor axis direction.
  • the solid line on the surface of the upper heat transfer plate 2 indicates the wave shape
  • the dotted line indicates the wave shape of the lower heat transfer plate 3 below the upper heat transfer plate 2.
  • a range 32 surrounded by a broken line frame indicates a wave cross-sectional shape of the upper heat transfer plate 2.
  • Dotted lines x1, y1, and z1 indicate a mountain, a valley, and a mountain in this order.
  • a range 33 surrounded by a broken line frame indicates a cross-sectional shape of the wave of the lower heat transfer plate 3.
  • Dotted lines x2, y2, and z2 indicate a valley, a mountain, and a valley in order.
  • the upper heat transfer plate 2 and the lower heat transfer plate 3 which are adjacent plates show the bottom of the wave of the upper heat transfer plate 2 and have a long side 2-2.
  • the bottom of the wave shown by each bottom ridgeline and the top of the wave shown by each top ridgeline join (contact) at intersection 23, and form a junction (contact part).
  • the upper heat transfer plate 2 and the lower heat transfer plate 3 are configured so that the outer peripheral edge portion 2 along the long side 2-2 at the intersection existing on a certain bottom ridge line, for example, the bottom ridge line 21. 3 is formed at a position substantially coincident with the outer peripheral edge 2-3 along the long side 2-2.
  • FIG. 3 shows a case where a dimension b corresponding to the dimension a is longer than that of the dimension a with respect to FIG. That is, in the case of FIG. 3, the junction point 11 corresponding to the intersection 23 at the end closest to the outer peripheral edge 2-3 along the long side 2-2 among the intersections existing on the bottom ridge line 21 is the long side 2. -2 is formed at a position separated from the outer peripheral edge 2-3 along the line -2 inward (Z direction) by a dimension b. In contrast to the dimension b, the flow path is widened when the dimension is as short as the dimension a in FIG. Moreover, since the retention amount of brazing material can be reduced when the dimension a is short, an effective heat transfer area increases and heat exchange performance improves.
  • the required number of plates of the plate heat exchanger for the required capacity of the air conditioner can be configured to a minimum, and the retention of foreign matter such as refrigeration machine oil and dust in the plate heat exchanger can be suppressed.
  • a highly reliable plate heat exchanger can be provided. With the plate heat exchanger 100, it is possible to use a fluid having a large pressure loss, such as a hydrocarbon or a low GWP refrigerant.
  • the plate heat exchanger 100 of the first embodiment is effective in reducing the pressure loss of the fluid.
  • the joining point of the upper and lower plates having the shortest dimension in the short axis direction with respect to the outer peripheral edge portion in the major axis direction of the plate was arranged as a wave substantially matching the outer peripheral edge portion in the major axis direction.
  • the distance (dimension a) between the joint points of the upper and lower plates, which are the shortest dimension in the minor axis direction with respect to the outer peripheral edge is shortened, so that the retention amount of the wax formed at the outer peripheral edge can be reduced and the flow path is expanded Therefore, pressure loss can be reduced.
  • the plate heat exchanger formed by laminating a plurality of plates having passage holes serving as fluid inlets and outlets at the four corners, in the minor axis direction with respect to the outer peripheral edge portion of the major axis direction of the plate
  • the plate heat exchanger has been described in which waves are arranged so that the joining point of the upper and lower plates in the shortest dimension substantially coincides with the outer peripheral edge in the major axis direction.
  • Embodiment 2 FIG.
  • the end point 9 (end of the bottom ridge line) of the wave valley of the upper heat transfer plate 2 and the end point 10 (end of the top ridge line) of the peak of the lower heat transfer plate 3 are matched.
  • the distance between the outer peripheral edge 2-3 of the plate and the joining point 11 of the upper and lower plates having the shortest dimension in the minor axis direction (z direction) was minimized. That is, the junction 11 is made to substantially coincide with the outer peripheral edge 2-3. Thereby, the pressure loss was reduced.
  • the outer peripheral edge portion (the outer peripheral edge portion along the long side) in the major axis direction of the plate and the junction point of the upper and lower plates having the shortest dimension in the minor axis direction (z direction)
  • a specific distance specific dimension b described later
  • the description will be given with reference to FIG. 3 again used in the first embodiment.
  • the dimension b shorter than the dimension a is effective in reducing the pressure loss.
  • the second embodiment a case will be described in which a flow path is secured and suitable if the dimension b is not as small as the dimension a and is within a predetermined range.
  • the dimension b between the outer peripheral edge of the plate and the joining point 11 of the upper and lower plates having the shortest dimension in the minor axis direction (z direction) is too small, that is, the dimension b is not as small as the dimension a.
  • the brazing material at the outer peripheral edge and the brazing material at the joining point are gathered, the brazing material stays between the dimensions b, and the flow path becomes narrow.
  • the dimension b is set to a predetermined size in which the brazing material does not stay. Thereby, the area
  • the dimension b when the dimension in the minor axis direction of the plate is 70 mm, the dimension b is preferably 3 to 4.5 mm.
  • the dimension b can be adjusted according to the dimension in the minor axis direction of the plate, the wave angle ⁇ , the wave pitch, the physical properties of the fluid, and the use conditions.
  • the wave angle ⁇ when the dimension b is 3 to 4.5 mm, the wave angle ⁇ (the wave angle ⁇ 1 of the upper heat transfer plate 2 and the wave angle ⁇ 2 of the lower heat transfer plate 3) is 60 degrees to 70 degrees. Degree. A range of 62.5 ° to 67.5 ° is more preferable.
  • the upper heat transfer plate 2 and the lower heat transfer plate 3 are joined to the intersection at the end closest to the outer peripheral edge along the long side among the intersections existing on one bottom ridge line.
  • the direction in which the bottom ridge line extends (the direction of the bottom ridge line determined by the wave angle ⁇ 1)
  • the direction in which the top ridge line extends the direction of the top ridge line determined by the wave angle ⁇ 2)
  • the upper heat transfer plate 2 and the lower heat transfer plate 3 are such that the closer the direction of the bottom ridge line and the direction of the top ridge line are to the direction perpendicular to the direction of the long side, It is formed at a position away from the part. That is, the dimension b is preferably increased from about “3 to 4.5 mm” as the wave angle ⁇ 1 and the wave angle ⁇ 2 approach 90 degrees.
  • Embodiment 3 will be described with reference to FIG.
  • the dimension (distance) between the joint point of the upper and lower plates and the outer peripheral edge portion is concerned.
  • Embodiment 3 the case where the ridgeline of the wave of one of the upper and lower plates is shortened will be described.
  • FIG. 4 is a front view of the plate according to the third embodiment.
  • the upper heat transfer plate 2 and the lower heat transfer plate 3 are expressed.
  • the wave ridgeline of the upper heat transfer plate 2 is shortened so that the wave end portion 9 (end of the bottom ridgeline) is located on the inner side of the plate from the end portion 10 (end of the top ridgeline) of the lower plate. Form. Thereby, the flow path of the area
  • the flow path width can be reduced by aggregation of rows between the outer peripheral edge and the “joining point of the upper and lower plates having the shortest dimension in the short axis direction”. Can be avoided.
  • one plate is a waveform, pressure loss can be reduced, maintaining the heat-transfer promotion effect by the stirring action of a flow.
  • the region c is formed on both outer peripheral sides in the minor axis direction of the plate. However, the region c is formed only on one outer peripheral side so that the differential pressure distribution in the plate becomes uniform according to the fluid inlet / outlet direction. It may be provided.
  • Embodiment 4 FIG. Next, a fourth embodiment will be described with reference to FIG. In the third embodiment, the case where the wave ridgeline of one of the upper and lower plates is shortened has been described. In this Embodiment 4, the case where the ridgeline of the wave of both upper and lower plates is shortened is demonstrated.
  • FIG. 5 is a front view of the heat transfer plate in the fourth embodiment.
  • a flow path in a region d surrounded by a broken line in the figure is formed.
  • Such a channel is formed on the outer peripheral edge side to prevent the channel width from being reduced due to the aggregation of the wax.
  • a fluid containing scale and fiber tends to be the starting point of the flow path blockage at the junction of the upper and lower plates, but the configuration of FIG. 5 is effective because the scale and fiber flow from the flow path in the region d.
  • At least one of the adjacent heat transfer plate 2 and lower heat transfer plate 3 is the outer peripheral edge portion 2 along the long side.
  • Dimension L extending from one short side to the other short side only within a range of a predetermined distance W (FIGS. 4 and 5) in a direction (z direction) from 3 to the other long side Only the region c or the region d where the waveform is not processed is provided.
  • FIG. 6 is a front view of the heat transfer plate in the fifth embodiment.
  • the wave ridgelines of the upper heat transfer plate 2 and the lower heat transfer plate 3 are shortened for each wave. In this way, the joint point 11 of the upper and lower plates having the shortest dimension in the minor axis direction (Z direction) with respect to the outer peripheral edge 2-3 is not formed.
  • the junction point is not formed at a position of an inconvenient dimension b (dimension b in the first embodiment) where the rows are aggregated. For this reason, there is no aggregation of the wax between the outer peripheral edge 2-3 and the joint point of the upper and lower plates, and the ridge line size is different for each wave. Therefore, heat transfer is promoted by the stirring effect of the flow in the short axis direction. If it is the structure of FIG. 6, the plate type heat exchanger which improved heat transfer performance, suppressing the increase in pressure loss can be provided. In FIG. 6, the ridgeline dimension is shortened for each wave, but the same effect can be obtained by changing the ridgeline dimension according to the design conditions such as heat transfer and pressure loss and the fluid flow mode.
  • the direction of the plurality of bottom ridge lines is directed to the outer peripheral edge 2-3 along the long side.
  • the ends of the plurality of bottom ridge lines with respect to the “outer peripheral edge portion 2-3 along the long side” are alternately positioned at the nearest position T and the nearest position T of the “outer peripheral edge portion 2-3 along the long side”. It is formed at a position S, which is farther from the outer peripheral edge 2-3.
  • the ridges of the wave of the plates are moved one wave at a time in the fluid flow direction.
  • Embodiment 6 will be described with reference to FIG.
  • the upper heat transfer plate is equivalent to the joint point of the upper and lower plates (there is no gap between them) in the shortest axis direction (Z direction) with respect to the outer peripheral edge of the upper and lower plates.
  • a gap of 0.2 mm or more is provided between the wave trough (bottom) of 2 and the wave crest (top) of the lower heat transfer plate 3 will be described.
  • FIG. 7 is a schematic view corresponding to a cross-sectional view of the heat transfer plate.
  • FIG. 7 is a diagram useful in explaining a gap dimension e described later.
  • the upper and lower plate joint points that are the shortest dimension in the minor axis direction (Z direction) with respect to the outer peripheral edge 2-3 of the plate (there is a gap as described above, and precisely the joint point corresponding to the joint point)
  • a gap between the wave part of the upper plate and the peak part of the lower plate in dimension b (similar to FIG. 3) is defined as dimension e.
  • the dimension e is set to 0.2 mm or more to eliminate the joining of the upper and lower plates, and the aggregation of the wax due to the outer peripheral edge 2-3 and the joining point of the upper and lower plates is prevented.
  • the adjacent upper heat transfer plate 2 and lower heat transfer plate 3 are defined as “the outer peripheral edge portion along the long side” of the intersections on one bottom ridge line in the upper heat transfer plate 2.
  • a gap is formed between the bottom of the wave indicated by the bottom ridge line and the top of the wave indicated by the top ridge line of the lower heat transfer plate 3. Then, at the intersection other than the intersection of the ends, the bottom of the wave indicated by the bottom ridge line is in contact with the top of the wave indicated by the top ridge line.
  • the plate heat exchanger formed by laminating a plurality of plates provided with passage holes serving as fluid inlets and outlets at the four corners, the shortest dimension in the minor axis direction with respect to the outer peripheral edge portions of the upper and lower plates.
  • the plate heat exchanger in which a gap of 0.2 mm or more is provided between the corrugation valley and the crest of the plate at the junction point corresponding to the upper and lower plates in FIG.
  • the heat transfer plate described in the first to sixth embodiments can be used for many industrial and household devices equipped with a plate heat exchanger, such as air conditioning, power generation, and food sterilization processing equipment.
  • a plate heat exchanger such as air conditioning, power generation, and food sterilization processing equipment.
  • the present invention can be used for the radiator, the evaporator, or any of the heat pump device in which a compressor, a radiator, an expansion mechanism, and an evaporator are connected by piping.

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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)

Abstract

L'invention concerne un échangeur de chaleur du type à plaques présentant une perte basse pression d'un fluide et un excellent rendement de conversion thermique, et une configuration simple. Une plaque de transfert de chaleur de côté supérieur (2) et une plaque de transfert de chaleur de côté inférieur (3) qui sont adjacentes présentent un traitement ondulé qui se déplace dans la direction stratifiée. Dans les plaques, lorsque l'on regarde depuis la direction stratifiée, une pluralité de lignes de bord inférieures virtuelles (21) qui indiquent le fond de l'ondulation de la plaque de transfert de chaleur de côté supérieur (2) et qui s'étendent dans des directions différentes depuis la direction de côté long, et une pluralité de lignes de bord supérieures virtuelles (22) qui indiquent le sommet de l'ondulation de la plaque de transfert de chaleur de côté inférieur (3) et qui s'étendent dans des directions différentes depuis la direction de côté long se croisent pour créer des points d'intersection, et le fond de l'ondulation indiqué par les lignes de bord inférieures et le sommet de l'ondulation indiqué par les lignes de bord supérieures viennent en contact l'un avec l'autre au niveau des points d'intersection pour former des points de connexion. La plaque de transfert de chaleur de côté supérieur (2) et la plaque de transfert de chaleur de côté inférieur (3) sont formées en une position au niveau de laquelle un point de connexion (11) correspondant à un point d'intersection (23) au niveau de l'extrémité la plus proche d'une section de bord périphérique externe (2-3) le long du côté long parmi des points d'intersection existant sur les lignes de bord inférieures (21) correspond approximativement à la section de bord périphérique externe le long du côté long.
PCT/JP2010/070192 2009-11-19 2010-11-12 Echangeur de chaleur du type à plaques et dispositif de pompe à chaleur WO2011062118A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US13/510,633 US20120227438A1 (en) 2009-11-19 2010-11-12 Plate heat exchanger and heat pump apparatus
EP10831513.6A EP2503277B1 (fr) 2009-11-19 2010-11-12 Échangeur de chaleur du type à plaques et dispositif de pompe à chaleur
CN201080052178.0A CN102667391B (zh) 2009-11-19 2010-11-12 板式热交换器及热泵装置
HK12112886.8A HK1172080A1 (zh) 2009-11-19 2012-12-13 板式熱交換器及熱泵裝置

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2009263598A JP2011106764A (ja) 2009-11-19 2009-11-19 プレート式熱交換器及びヒートポンプ装置
JP2009-263598 2009-11-19

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Publication Number Publication Date
WO2011062118A1 true WO2011062118A1 (fr) 2011-05-26

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PCT/JP2010/070192 WO2011062118A1 (fr) 2009-11-19 2010-11-12 Echangeur de chaleur du type à plaques et dispositif de pompe à chaleur

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US (1) US20120227438A1 (fr)
EP (1) EP2503277B1 (fr)
JP (1) JP2011106764A (fr)
CN (1) CN102667391B (fr)
HK (1) HK1172080A1 (fr)
WO (1) WO2011062118A1 (fr)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
WO2020136863A1 (fr) * 2018-12-28 2020-07-02 三菱電機株式会社 Échangeur de chaleur à plaques et dispositif de pompe à chaleur

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US8544294B2 (en) * 2011-07-11 2013-10-01 Palo Alto Research Center Incorporated Plate-based adsorption chiller subassembly
US10690421B2 (en) 2012-03-28 2020-06-23 Modine Manufacturing Company Heat exchanger and method of cooling a flow of heated air
EP2657636B1 (fr) 2012-04-23 2015-09-09 GEA Ecoflex GmbH Echangeur thermique à plaques
WO2015082348A1 (fr) * 2013-12-05 2015-06-11 Swep International Ab Plaque d'échange de chaleur à pas variable
EP4166880A1 (fr) * 2021-10-12 2023-04-19 Valeo Autosystemy SP. Z.O.O. Plaque pour échangeur de chaleur
RS20221182A1 (sr) 2022-12-26 2024-06-28 Euro Heat Doo Izmenjivač toplote sa zavarenim unutrašnjim izmenjivačkim pločama

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EP2503277A1 (fr) 2012-09-26
EP2503277A4 (fr) 2014-08-13
JP2011106764A (ja) 2011-06-02
CN102667391B (zh) 2016-03-02
EP2503277B1 (fr) 2019-09-04
US20120227438A1 (en) 2012-09-13
HK1172080A1 (zh) 2013-04-12
CN102667391A (zh) 2012-09-12

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