WO2023054353A1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

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Publication number
WO2023054353A1
WO2023054353A1 PCT/JP2022/035927 JP2022035927W WO2023054353A1 WO 2023054353 A1 WO2023054353 A1 WO 2023054353A1 JP 2022035927 W JP2022035927 W JP 2022035927W WO 2023054353 A1 WO2023054353 A1 WO 2023054353A1
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WO
WIPO (PCT)
Prior art keywords
inlet
outlet
refrigerant
flow path
heat exchanger
Prior art date
Application number
PCT/JP2022/035927
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English (en)
Japanese (ja)
Inventor
健 佐藤
光春 沼田
航 寺井
信哉 田端
智己 廣川
Original Assignee
ダイキン工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Application filed by ダイキン工業株式会社 filed Critical ダイキン工業株式会社
Priority to CN202280065446.5A priority Critical patent/CN118043621A/zh
Publication of WO2023054353A1 publication Critical patent/WO2023054353A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • 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
    • F28F3/08—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning

Definitions

  • Patent Document 1 Japanese Patent Application Laid-Open No. 11-173772
  • the lower end of the heat transfer plate is provided with a third opening for guiding the water introduced from the water inlet pipe to the water flow passage, and the upper end of the heat transfer plate is provided with the water flow passage.
  • a fourth opening is provided to direct water to the water outlet tube. The third opening and the fourth opening are provided in the central portion in the width direction of the heat transfer plate.
  • the lower end of the heat transfer plate is provided with a first opening for guiding the refrigerant introduced from the refrigerant inlet pipe to the refrigerant channel, and the upper end of the heat transfer plate is provided with a refrigerant outlet pipe to direct the refrigerant in the refrigerant flow channel.
  • a second opening is provided leading to the.
  • the first opening is provided in the widthwise central portion of the heat transfer plate
  • the second opening is provided at the widthwise end portion of the heat transfer plate. Therefore, the coolant may concentrate at the end where the second opening is provided. In this case, the amount of refrigerant in each refrigerant flow passage becomes non-uniform, resulting in deterioration in performance.
  • the heat exchanger according to the first aspect comprises a plurality of stacked plates.
  • the heat exchanger allows heat exchange between the refrigerant and the heat medium.
  • a first channel and a second channel are formed between the plates.
  • a two-phase refrigerant flows through the first channel.
  • a heat medium flows through the second flow path.
  • the plate is formed with a first inlet and a first outlet.
  • the first inlet serves as an inlet for the coolant flowing through the first flow path.
  • a 1st outlet becomes an outlet of the refrigerant
  • the first inlet and the first outlet are line-symmetrical with respect to the center line in the width direction of the plates.
  • the first inlet serving as an inlet for the two-phase refrigerant and the first outlet serving as an outlet for the refrigerant are arranged along the center line in the width direction of the plates. It is formed at a line-symmetrical position. Therefore, the difference in flow path resistance due to the positional relationship between the first inlet and the first outlet can be reduced. Therefore, even if the refrigerant passing through the first flow path between the first inlet and the first outlet flows into the first flow path from the first inlet in a two-phase state, the amount of refrigerant flowing through the first flow path is reduced. Homogenization can be enhanced. Therefore, since the drift of the refrigerant can be suppressed, the performance of the heat exchanger can be improved.
  • the heat exchanger according to the second aspect is the heat exchanger according to the first aspect, and one plate is formed with one or more through holes as first inlets.
  • a plurality of plates having one or a plurality of through holes formed therein can be used as the first inlet.
  • the heat exchanger according to the third aspect is the heat exchanger according to the first aspect or the second aspect, and a first inlet header and a first outlet header are formed between the plates.
  • a first inlet header is formed between the first inlet and the first flow path.
  • a first outlet header is formed between the first outlet and the first flow path.
  • the refrigerant can be collected from the first inlet to the first inlet header and diverted from the first inlet header to the first flow path. Refrigerant can then be collected from the first flow path to the first outlet header.
  • the heat exchanger according to the fourth aspect is the heat exchanger according to the third aspect, and the first flow paths are a plurality of flow paths extending in the longitudinal direction of the plate.
  • the multiple channels are spaced apart from each other.
  • a plurality of flow paths extending in the longitudinal direction and separated from each other as the first flow paths are likely to cause uneven flow of the refrigerant.
  • the first inlet serving as the inlet of the two-phase coolant and the first outlet serving as the outlet of the coolant are positioned symmetrically with respect to the center line in the width direction of the plates. formed. Therefore, even if the first flow path has a shape that easily causes a drift of the coolant, the drift can be suppressed.
  • the heat exchanger according to the fifth aspect is the heat exchanger according to the first to fourth aspects, and the plate is further formed with a second inlet and a second outlet.
  • the second inlet serves as an inlet for the heat medium flowing through the second flow path.
  • the second outlet serves as an outlet for the heat medium flowing through the second flow path.
  • An angle between a line connecting the first inlet and the first outlet and a line connecting the second inlet and the second outlet is less than 25 degrees.
  • the angle formed by a line connecting the first inlet and the first outlet of the refrigerant and a line connecting the second inlet and the second outlet of the heat medium is less than 25 degrees. In this case, the drift of the refrigerant can be effectively suppressed.
  • the heat exchanger according to the sixth aspect is the heat exchanger according to the first to fifth aspects, and the plate is further formed with a second inlet and a second outlet.
  • the second inlet serves as an inlet for the heat medium flowing through the second flow path.
  • the second outlet serves as an outlet for the heat medium flowing through the second flow path.
  • the second inlet and the second outlet are line-symmetrical with respect to the center line in the width direction of the plates.
  • the difference in flow path resistance due to the positional relationship between the second inlet and the second outlet can be reduced. Therefore, it is possible to further improve the uniformity of the amount of the heat medium flowing through the second flow path. Therefore, the drift of the heat medium can be further suppressed, so that the performance of the heat exchanger can be further improved.
  • the heat exchanger according to the seventh aspect is the heat exchanger according to the first to sixth aspects, and the plate is further formed with a second inlet and a second outlet.
  • the second inlet serves as an inlet for the heat medium flowing through the second flow path.
  • the second outlet serves as an outlet for the heat medium flowing through the second flow path.
  • a first inlet and a first outlet are located between the second inlet and the second outlet in the longitudinal direction of the plate.
  • the first inlet and the first outlet of the first flow path which tend to cause drift, are arranged more centrally than the second inlet and the second outlet of the second flow path, which tends to cause drift. Thereby, the influence of the second inlet and the second outlet on the coolant flowing through the first flow path can be reduced.
  • the heat exchanger according to the eighth aspect is the heat exchanger according to the first to seventh aspects, and the plate is further formed with a second inlet and a second outlet.
  • the second inlet serves as an inlet for the heat medium flowing through the second flow path.
  • the second outlet serves as an outlet for the heat medium flowing through the second flow path.
  • the inlets and outlets on the low pressure side of the refrigerant and heat transfer medium are located between the inlets and outlets on the high pressure side of the refrigerant and heat transfer medium.
  • the flow path through which the medium on the low pressure side flows is susceptible to pressure loss.
  • the inlet and outlet of the medium on the low-pressure side which are greatly affected by the pressure loss, are arranged more centrally than the inlet and outlet of the medium, which is small in pressure loss.
  • the effect of pressure loss can be reduced by shortening the flow path of the medium on the low pressure side.
  • the heat exchanger according to the ninth aspect is the heat exchanger according to the first to eighth aspects, in which the first inlet is formed below the first outlet.
  • a plate having a first inlet and a first outlet can be used so that the refrigerant flows from bottom to top.
  • FIG. 4 is a schematic diagram showing the flow of refrigerant in the plates of the heat exchanger according to the embodiment;
  • FIG. 4 is a schematic diagram showing the flow of heat medium in the plates of the heat exchanger according to the embodiment;
  • FIG. 11 is a perspective view showing plates of a heat exchanger according to a modification;
  • FIG. 5 is a schematic diagram showing the flow of refrigerant in plates of a heat exchanger according to a modification;
  • FIG. 11 is a schematic diagram showing the flow of a heat medium in plates of a heat exchanger according to a modification
  • FIG. 5 is a schematic diagram showing plates of a heat exchanger according to another modification
  • FIG. 11 is a perspective view showing a frame according to a modification
  • FIG. 1 shows a refrigerant cycle system 1 including a heat exchanger 100 of this embodiment.
  • a refrigerant cycle system 1 is a device that is used to cool and heat a room such as a building by performing a vapor compression refrigeration cycle operation.
  • the refrigerant cycle system 1 has one first unit 10, one cascade unit 30, and one second unit 50.
  • the first unit 10 and the cascade unit 30 are connected by two first communication pipes 61 .
  • the cascade unit 30 and the second unit 50 are connected by two second communication pipes 62 .
  • the primary side cycle 20 is a circuit that circulates refrigerant.
  • the refrigerant includes, for example, at least one of HFC-based refrigerants such as R32 and R410A and HFO-based refrigerants.
  • R32 for example, is used as the coolant that flows through the primary side cycle 20 .
  • the secondary side cycle 40 is a circuit that circulates the heat medium.
  • the heat medium may be water or the like, or may be a refrigerant.
  • a carbon dioxide refrigerant is used as the heat medium that flows through the secondary side cycle 40 .
  • First unit 10 is a heat source unit.
  • the first unit 10 includes a first compressor 11, a first four-way switching valve 12, a first heat exchanger 13, a first expansion valve 14, a first liquid closing valve 18, and a first gas closing valve. 19.
  • the first compressor 11 sucks in low-pressure gas refrigerant as refrigerant circulating in the primary cycle 20, compresses it, and discharges high-pressure gas refrigerant.
  • the first four-way switching valve 12 is connected as indicated by the solid line in FIG. 1 during cooling operation, and is connected as indicated by the broken line in FIG. 1 during heating operation.
  • the first heat exchanger 13 exchanges heat between the refrigerant and the outside air.
  • the first heat exchanger 13 functions as a condenser during cooling operation, and functions as an evaporator during heating operation.
  • the first expansion valve 14 adjusts the flow rate of refrigerant. Furthermore, the first expansion valve 14 functions as a decompression device that decompresses the refrigerant.
  • the first liquid shut-off valve 18 and the first gas shut-off valve 19 shut off the flow path through which the refrigerant circulates, such as when the first unit 10 is being installed.
  • the cascade unit 30 is for heat exchange between the refrigerant and the heat medium.
  • the cascade unit 30 includes a second compressor 31, a second four-way switching valve 32, a cascade heat exchanger 33, a primary expansion valve 34, a secondary expansion valve 35, and a second liquid closing valve 38. , and a second gas shut-off valve 39 .
  • the second compressor 31 sucks in low-pressure gas refrigerant as a heat medium circulating in the secondary side cycle 40, compresses it, and discharges supercritical high-pressure refrigerant.
  • the second four-way switching valve 32 functions as a switching device, and is connected as indicated by the solid line in FIG. 1 for cooling operation, and is connected as indicated by the broken line in FIG. 1 for heating operation.
  • the cascade heat exchanger 33 exchanges heat between the refrigerant and the heat medium.
  • the cascade heat exchanger 33 is a plate heat exchanger 100, as shown in FIG.
  • the cascade heat exchanger 33 has a first flow path 111 through which a refrigerant flows and a second flow path 112 through which a heat medium flows.
  • the first channel 111 allows the coolant to pass through.
  • the second flow path 112 allows the heat medium to pass therethrough.
  • the cascade heat exchanger 33 functions as a refrigerant evaporator and a heat medium condenser in the cooling operation, and functions as a refrigerant evaporator and a heat medium condenser in the heating operation.
  • the primary side expansion valve 34 adjusts the amount of refrigerant circulating through the primary side cycle 20 . Further, the primary side expansion valve 34 reduces the pressure of the refrigerant.
  • the secondary expansion valve 35 adjusts the amount of heat medium circulating through the secondary cycle 40 . Furthermore, the secondary expansion valve 35 reduces the pressure of the refrigerant.
  • the second liquid shut-off valve 38 and the second gas shut-off valve 39 shut off the flow path through which the heat medium circulates, such as in the case of installation work of the cascade unit 30.
  • the second unit 50 is a utilization unit.
  • the second unit 50 has a second heat exchanger 51 and a second expansion valve 52 .
  • the second heat exchanger 51 exchanges heat between the heat medium and the indoor air.
  • the second heat exchanger 51 is, for example, a microchannel heat exchanger and has a multi-hole flat tube.
  • the second expansion valve 52 regulates the amount of heat medium circulating through the secondary side cycle 40 .
  • the second expansion valve 52 functions as a decompression device that decompresses the heat medium.
  • the first compressor 11 sucks low-pressure gas refrigerant and discharges high-pressure gas refrigerant. .
  • the high-pressure gas refrigerant reaches the first heat exchanger 13 via the first four-way switching valve 12 .
  • the first heat exchanger 13 condenses the high pressure gas refrigerant, thereby producing high pressure liquid refrigerant. At this time, the refrigerant releases heat to the outside air.
  • the high-pressure liquid refrigerant passes through the fully opened first expansion valve 14 and reaches the primary side expansion valve 34 via the first liquid closing valve 18 and the first communication pipe 61 .
  • the primary expansion valve 34 which is properly opened, decompresses the high-pressure liquid refrigerant, thereby producing a low-pressure gas-liquid two-phase refrigerant.
  • a low-pressure gas-liquid two-phase refrigerant enters the first flow path 111 of the cascade heat exchanger 33 .
  • the cascade heat exchanger 33 evaporates the low pressure gas-liquid two-phase refrigerant thereby producing low pressure gaseous refrigerant.
  • the refrigerant in the primary cycle 20 absorbs heat from the heat medium in the secondary cycle 40 .
  • the low-pressure gas refrigerant exits the first flow path 111, passes through the first communication pipe 61 and the first gas shutoff valve 19, passes through the first four-way switching valve 12, and is sucked into the first compressor 11. be.
  • the second compressor 31 sucks low-pressure gas refrigerant as a heat medium and discharges supercritical high-pressure refrigerant.
  • the high pressure refrigerant enters the second flow path 112 of the cascade heat exchanger 33 via the second four-way switching valve 32 .
  • the cascade heat exchanger 33 condenses the high pressure refrigerant by releasing heat, thereby producing high pressure liquid refrigerant.
  • the heat medium in the secondary cycle 40 releases heat to the refrigerant in the primary cycle 20 .
  • the high-pressure liquid refrigerant exits the second flow path 112 and reaches the secondary expansion valve 35 .
  • the secondary expansion valve 35 which is set to an appropriate degree of opening, decompresses the high-pressure liquid refrigerant, thereby producing a low-pressure gas-liquid two-phase refrigerant.
  • the low-pressure gas-liquid two-phase refrigerant passes through the second liquid closing valve 38 and the second communication pipe 62 and reaches the second expansion valve 52 .
  • the second expansion valve 52 which is set to an appropriate degree of opening, further reduces the pressure of the low-pressure gas-liquid two-phase refrigerant.
  • the low-pressure gas-liquid two-phase refrigerant reaches the second heat exchanger 51 .
  • the second heat exchanger 51 evaporates the low-pressure gas-liquid two-phase refrigerant, thereby producing low-pressure gaseous refrigerant.
  • the refrigerant as a heat medium absorbs heat from the indoor air.
  • the low-pressure gas refrigerant exits the second heat exchanger 51, passes through the second communication pipe 62 and the second gas shutoff valve 39, passes through the second four-way switching valve 32, and is sucked into the second compressor 31. be done.
  • the first compressor 11 sucks low-pressure gas refrigerant and discharges high-pressure gas refrigerant.
  • the high-pressure gas refrigerant passes through the first four-way switching valve 12 , the first gas shut-off valve 19 and the first connecting pipe 61 , and enters the first flow path 111 of the cascade heat exchanger 33 .
  • the cascade heat exchanger 33 condenses the high pressure gaseous refrigerant thereby creating a high pressure liquid refrigerant.
  • the refrigerant in the primary cycle 20 releases heat to the heat medium in the secondary cycle 40 .
  • the high-pressure liquid refrigerant passes through the fully opened primary expansion valve 34 , then through the first communication pipe 61 and the first liquid closing valve 18 , and reaches the first expansion valve 14 .
  • the low-pressure gas-liquid two-phase refrigerant reaches the first heat exchanger 13 .
  • the first heat exchanger 13 evaporates the low-pressure gas-liquid two-phase refrigerant, thereby producing low-pressure gaseous refrigerant. At this time, the refrigerant absorbs heat from the outside air.
  • the low-pressure gas refrigerant passes through the first four-way switching valve 12 and is sucked into the first compressor 11 .
  • the second compressor 31 sucks low-pressure gas refrigerant as a heat medium and discharges supercritical high-pressure refrigerant.
  • the high-pressure refrigerant passes through the second four-way switching valve 32 , the second gas shut-off valve 39 and the second connecting pipe 62 , and reaches the second heat exchanger 51 .
  • the second heat exchanger 51 condenses the high pressure refrigerant by releasing heat, thereby producing high pressure liquid refrigerant.
  • the refrigerant as a heat medium releases heat to the indoor air.
  • the high-pressure liquid refrigerant reaches the second expansion valve 52 .
  • the second expansion valve 52 which is set to an appropriate degree of opening, decompresses the high-pressure liquid refrigerant, thereby producing a low-pressure gas-liquid two-phase refrigerant.
  • the low-pressure gas-liquid two-phase refrigerant passes through the second communication pipe 62 and the second liquid closing valve 38 and reaches the secondary side expansion valve 35 .
  • the secondary expansion valve 35 which is set to an appropriate degree of opening, further reduces the pressure of the low-pressure gas-liquid two-phase refrigerant.
  • the low-pressure gas-liquid two-phase refrigerant enters the second flow path 112 of the cascade heat exchanger 33 .
  • the cascade heat exchanger 33 evaporates the low pressure gas-liquid two-phase refrigerant thereby producing low pressure gaseous refrigerant.
  • the heat medium in the secondary cycle 40 absorbs heat from the refrigerant in the primary cycle 20 .
  • the low-pressure gas refrigerant exits the second flow path 112 , passes through the second four-way switching valve 32 and is sucked into the second compressor 31 .
  • FIG. 2 shows the heat exchanger 100 in an exploded state, omitting part of the plates 103 and 104 .
  • FIG. 3 shows the refrigerant inlet and outlet and the heat medium inlet and outlet at one plate 103 , 104 of the heat exchanger 100 .
  • FIG. 4 shows an image of refrigerant flow in one plate 103, 104 of the heat exchanger 100.
  • FIG. 5 shows an image of the heat medium flow in one plate 103, 104 of the heat exchanger 100.
  • FIGS. 2 to 5 schematically show the plates 103 and 104 of the heat exchanger 100, exaggerating the inlets, outlets, channels, etc., and omitting parts not used for explanation.
  • the heat exchanger 100 exchanges heat between the refrigerant and the heat medium without mixing them.
  • the heat exchanger 100 of this embodiment is the cascade heat exchanger 33 shown in FIG. Therefore, the refrigerant of the present embodiment contains, for example, at least one of an HFC-based refrigerant and an HFO-based refrigerant, and the heat medium of the present embodiment contains, for example, carbon dioxide.
  • the heat exchanger 100 is a plate (type) heat exchanger that includes a plurality of stacked plates 103 and 104 .
  • the number of plates 103 and 104 is not particularly limited, and is appropriately set according to the required performance.
  • the heat exchanger 100 includes two frames 102, a plurality of plates 103 and 104, a refrigerant inlet pipe 105, a refrigerant outlet pipe 106, a heat medium inlet pipe 107, and a heat medium outlet pipe 108.
  • a plurality of plates 103 , 104 are stacked between two frames 102 .
  • the plurality of plates 103 and 104 are composed of two types of heat transfer plates, a first plate 103 and a second plate 104 .
  • the first plates 103 and the second plates 104 are alternately stacked.
  • the frame 102 and plates 103, 104 are integrally joined by brazing.
  • the plates 103 and 104 are composed of metal flat plates. The peripheral edges of the adjacent plates 103 and 104 are in contact with each other, and between the plates 103 and 104, there is a first flow path 111 (see FIG. 4) that is a flow path for a coolant or a second flow path 112 that is a flow path for a heat medium. (see FIG. 5) are formed. The first flow paths 111 and the second flow paths 112 are provided alternately. The coolant flowing through the first channel 111 and the heat medium flowing through the second channel 112 are heat-exchanged with each other via the plates 103 and 104 .
  • a refrigerant introduction pipe 105 , a refrigerant outlet pipe 106 , a heat medium introduction pipe 107 , and a heat medium outlet pipe 108 are attached to the frame 102 .
  • the heat medium lead-out pipe 108, the coolant lead-in pipe 105, the coolant lead-out pipe 106, and the heat medium lead-in pipe 107 are provided in this order from bottom to top.
  • the plates 103 and 104 are formed with a first inlet 115, a first outlet 116, a second inlet 117, and a second outlet 118. .
  • the first inlet 115 serves as an inlet for coolant flowing through the first flow path 111 .
  • a first inlet 115 of the plurality of plates 103, 104 constitutes a coolant inflow space.
  • the refrigerant inflow space communicates with the refrigerant introduction pipe 105 . Therefore, the coolant introduced from the coolant introduction pipe 105 flows from the first inlet 115 to the first channel 111 .
  • a gas-liquid two-phase refrigerant passes through the first inlet 115 .
  • the first outlet 116 serves as an outlet for the coolant flowing through the first channel 111 .
  • a first outlet 116 of the plurality of plates 103, 104 constitutes a coolant outflow space.
  • the refrigerant outflow space communicates with the refrigerant outlet pipe 106 . Therefore, the coolant that has flowed through the first flow path 111 flows from the first outlet 116 to the coolant lead-out pipe 106 .
  • gas-phase refrigerant passes through the first outlet 116 .
  • the second inlet 117 serves as an inlet for the heat medium flowing through the second flow path 112 .
  • a second inlet 117 of the plurality of plates 103, 104 constitutes a heat medium inflow space.
  • the heat medium inflow space communicates with the heat medium introduction pipe 107 . Therefore, the heat medium introduced from the heat medium introduction pipe 107 flows into the second flow path 112 from the second inlet 117 .
  • the second outlet 118 serves as an outlet for the heat medium flowing through the second flow path 112 .
  • a second outlet 118 of the plurality of plates 103, 104 constitutes a heat medium outlet space.
  • the heat medium outflow space communicates with the heat medium outlet pipe 108 . Therefore, the heat medium that has flowed through the second flow path 112 flows from the second outlet 118 to the heat medium lead-out pipe 108 .
  • the refrigerant evaporates and the heat medium condenses in the heat exchanger 100 . Therefore, during cooling operation, the first inlet 115 is the inlet for the evaporating medium of the refrigerant and the heat medium, and the first outlet 116 is the outlet for the evaporating medium of the refrigerant and the heat medium.
  • the second inlet 117 is an inlet for condensing medium of the refrigerant and heat medium, and the second outlet 118 is an outlet for condensing medium of the refrigerant and heat medium.
  • condensation includes changing from a gas phase state to a liquid phase state and changing from a supercritical state to a liquid phase state.
  • the refrigerant is on the low pressure side and the heat medium is on the high pressure side. Therefore, during cooling operation, the first inlet 115 is the inlet for the low-pressure side medium of the refrigerant and the heat medium, the first outlet 116 is the low-pressure side outlet of the refrigerant and the heat medium, The second inlet 117 is the inlet for the high-pressure medium of the refrigerant and the heat medium, and the second outlet 118 is the outlet for the high-pressure medium of the refrigerant and the heat medium.
  • One plate 103, 104 is formed with one or more through-holes as the first inlet 115.
  • one through hole is formed as the first inlet 115 in one plate 103 , 104 .
  • One or more through-holes are formed as first outlets 116 in one plate 103 , 104 .
  • one through hole is formed as the first outlet 116 in one of the plates 103 and 104 .
  • a single plate 103, 104 is formed with one or more through-holes as a second inlet 117.
  • one through hole is formed as the second inlet 117 in one plate 103 , 104 .
  • One or more through-holes are formed as second outlets 118 in one plate 103 , 104 .
  • one through-hole is formed as the second outlet 118 in one of the plates 103 and 104 .
  • the first inlet 115, the first outlet 116, the second inlet 117 and the second outlet 118 may have the same shape or different shapes.
  • the first inlet 115, the first outlet 116, the second inlet 117 and the second outlet 118 are circular through holes of approximately the same size.
  • the first inlet 115 and the first outlet 116 are arranged with respect to the center line L in the width direction (horizontal direction in FIG. 3) of the plates 103 and 104. It is line symmetrical.
  • the line symmetry means that the distance between the center line L and the centroid of the first inlet 115 and the distance between the center line L and the centroid of the first outlet 116 are the distances between the plates 103 and 104 when viewed in the stacking direction. It is 10% or less of the width dimension W.
  • the plurality of plates 103 and 104 are rectangular when viewed in the stacking direction.
  • the corners of the rectangle may be composed of straight lines, or may be composed of curved lines such as an R shape. Therefore, the plates 103 and 104 have a longitudinal direction and a lateral direction, and the width direction is the lateral direction.
  • the center line L is specified by connecting the centers of the plates 103 and 104 in the width direction.
  • the first inlet 115 is symmetrical with respect to the center line L.
  • the first outlet 116 is symmetrical with respect to the center line L.
  • the centers of the first inlet 115 and the first outlet 116 are located on the centerline L.
  • the center of the first inlet 115 and the first outlet 116 of the present disclosure may be shifted left or right with respect to the center line L within a range of 10% or less of the width dimension W of the plates 103 and 104. good.
  • the second inlet 117 and the second outlet 118 are located with respect to the center line L in the width direction (horizontal direction in FIG. 3) of the plates 103 and 104. is line symmetrical.
  • the second inlet 117 is symmetrical with respect to the center line L.
  • the second outlet 118 is symmetrical with respect to the centerline L.
  • the centers of the second inlet 117 and the second outlet 118 are located on the centerline L.
  • the center of the second inlet 117 and the second outlet 118 of the present disclosure may be shifted left or right with respect to the center line L within a range of 10% or less of the width dimension W of the plates 103 and 104. good.
  • a first inlet 115 and a first outlet 116 are located between the second inlet 117 and the second outlet 118 in the longitudinal direction of the plates 103 and 104 (vertical direction in FIG. 3). In other words, first inlet 115 and first outlet 116 are closer to the longitudinal center than second inlet 117 and second outlet 118 .
  • first inlet 115 is closer to the center in the longitudinal direction than the second inlet 117.
  • the first outlet 116 is closer to the longitudinal center than the second outlet 118 .
  • first inlet 115, the first outlet 116, the second inlet 117 and the second outlet 118 are positioned on one straight line in the longitudinal direction.
  • first inlet 115 , the first outlet 116 , the second inlet 117 and the second outlet 118 are located on the widthwise center line L of the plates 103 , 104 .
  • a first inlet 115 is formed below the first outlet 116 .
  • a second inlet 117 is formed above the second outlet 118 .
  • the second outlet 118, the first inlet 115, the first outlet 116, and the second inlet 117 are formed in this order from bottom to top.
  • the angle between the line connecting the first inlet 115 and the first outlet 116 and the line connecting the second inlet 117 and the second outlet 118 is less than 25 degrees.
  • the line connecting the first inlet 115 and the first outlet 116 is the center line L
  • the line connecting the second inlet 117 and the second outlet 118 is the center line L. Therefore, the angle between the line connecting the first inlet 115 and the first outlet 116 and the line connecting the second inlet 117 and the second outlet 118 is 0 degree.
  • Concavities and convexities such as a herringbone shape and a corrugated shape are formed on the front and back surfaces of the plates 103 and 104 .
  • the first plate 103 and the second plate 104 are stacked such that one surface faces the other back surface.
  • a first channel 111 through which the coolant flows is formed.
  • a two-phase refrigerant flows through the first channel 111 .
  • a gas-liquid two-phase refrigerant flows through the first flow path 111 during cooling operation.
  • a gas-liquid two-phase refrigerant flows through at least a portion of the first channel 111 .
  • a gas-liquid two-phase refrigerant flows in the vicinity of the first inlet 115 of the first channel 111 . Therefore, the gas-phase or liquid-phase coolant may flow through the remaining portion of the first flow path 111 .
  • a vapor-phase refrigerant flows in the vicinity of the first outlet of the first flow path 111 .
  • a heat medium in a supercritical state flows through the second flow path 112 during cooling operation.
  • the refrigerant flows from bottom to top, and the heat medium flows from top to bottom. Therefore, the refrigerant and the heat medium flow countercurrently.
  • a first inlet header 113 and a first outlet header 114 are formed between the plates 103 and 104.
  • a first inlet header 113 is formed between the first inlet 115 and the first channel 111 .
  • a first outlet header 114 is formed between the first outlet 116 and the first channel 111 .
  • the first inlet header 113 forms a header space for diverting the coolant to the first flow path 111 .
  • the first inlet header 113 is provided upstream of the first flow path 111 .
  • the first outlet header 114 forms a header space for gathering the coolant that has flowed through the first flow path 111 .
  • the first outlet header 114 is provided downstream of the first flow path 111 .
  • the first channels 111 are multiple channels extending in the longitudinal direction of the plates 103 and 104 .
  • the multiple channels are spaced apart from each other.
  • the plurality of channels that make up the first channel 111 do not separate from each other and join together from the first inlet header 113 to the first outlet header 114 .
  • the plurality of flow paths may meander, but here they extend in a straight line parallel to each other.
  • a second inlet header and a second outlet header are further formed between the plates 103 and 104 (not shown).
  • a second inlet header is formed between the second inlet 117 and the second flow path 112 .
  • a second outlet header is formed between the second outlet 118 and the second flow path 112 .
  • the second channels 112 are a plurality of channels extending in the longitudinal direction of the plates 103 and 104 (not shown).
  • the multiple channels are spaced apart from each other.
  • the plurality of channels that make up the second channel 112 do not separate and merge with each other from the second inlet 117 to the second outlet 118 .
  • a plurality of flow paths extend from the second inlet header to the second outlet header to avoid the first inlet 115 and the first outlet 116 .
  • the high-pressure supercritical heat medium introduced from the heat medium introduction pipe 107 of the heat exchanger 100 passes through the second inlet 117 and flows into the second flow path 112 .
  • This heat medium flows through the second flow paths 112, exchanges heat with the refrigerant in the adjacent first flow paths 111, condenses, and is cooled.
  • the cooled liquid phase heat medium is discharged from the heat medium lead-out pipe 108 through the second outlet 118 .
  • This vapor-phase refrigerant flows through the first flow path 111, exchanges heat with the heat medium in the adjacent second flow path 112, condenses, and heats the heat medium.
  • the condensed liquid-phase refrigerant is discharged from the refrigerant outlet pipe 106 through the first outlet 116 .
  • the low-pressure gas-liquid two-phase heat medium introduced from the heat medium introduction pipe 107 of the heat exchanger 100 flows into the second flow path 112 through the second inlet 117 .
  • This heat medium flows through the second flow paths 112, exchanges heat with the refrigerant in the adjacent first flow paths 111, evaporates, and is heated.
  • the heated vapor-phase heat medium is discharged from the heat medium lead-out pipe 108 through the second outlet 118 .
  • a heat exchanger 100 includes a plurality of stacked plates 103 and 104 .
  • the heat exchanger 100 allows heat exchange between the refrigerant and the heat medium.
  • a first channel 111 and a second channel 112 are formed between the plates 103 and 104 .
  • a two-phase refrigerant flows through the first flow path 111 .
  • a heat medium flows through the second flow path 112 .
  • a first inlet 115 and a first outlet 116 are formed in the plates 103 , 104 .
  • the first inlet 115 serves as an inlet for coolant flowing through the first flow path 111 .
  • the first outlet 116 serves as an outlet for the coolant flowing through the first flow path 111 .
  • the first inlet 115 and the first outlet 116 are line-symmetrical with respect to the central line L of the plates 103 and 104 in the width direction.
  • the first inlet 115 serving as an inlet for the two-phase refrigerant and the first outlet 116 serving as an outlet for the refrigerant are located on the plates 103 and 104 when viewed from the stacking direction of the plates 103 and 104. It is formed at a line-symmetrical position with respect to the center line L in the width direction. As a result, the difference in flow path resistance due to the positional relationship between the first inlet 115 and the first outlet 116 can be reduced.
  • the first flow path Uniformity of the amount of refrigerant flowing through 111 can be enhanced. Therefore, since the drift of the refrigerant can be suppressed, the heat exchange between the refrigerant and the heat medium can be promoted, so the performance of the heat exchanger 100 can be improved.
  • one through-hole is formed as the first inlet 115 in each of the plates 103 and 104 .
  • a plurality of plates 103 and 104 with one through hole can be used as the first inlet 115 .
  • a first inlet header 113 and a first outlet header 114 are preferably formed between the plates 103 and 104 in the heat exchanger 100 according to this embodiment.
  • a first inlet header 113 is formed between the first inlet 115 and the first channel 111 .
  • a first outlet header 114 is formed between the first outlet 116 and the first channel 111 .
  • the refrigerant can be collected from the first inlet 115 to the first inlet header 113 and diverted from the first inlet header 113 to the first flow path 111 . Then, the refrigerant can be collected from the first flow path 111 to the first outlet header 114 .
  • the first channels 111 are a plurality of channels extending in the longitudinal direction of the plates 103 and 104 .
  • the multiple channels are spaced apart from each other.
  • first flow path 111 As the first flow path 111, a plurality of flow paths that extend in the longitudinal direction and are separated from each other are more likely to cause uneven flow of the refrigerant.
  • a first inlet 115 serving as an inlet for two-phase refrigerant and a first outlet 116 serving as an outlet for the refrigerant are aligned with the center line L of the plates 103 and 104 in the width direction. is formed at a line-symmetrical position with respect to Therefore, even if the first flow path 111 has a shape that easily causes a drift of the refrigerant, the drift can be effectively suppressed.
  • the plates 103 and 104 are further formed with a second inlet 117 and a second outlet 118 .
  • the second inlet 117 serves as an inlet for the heat medium flowing through the second flow path 112 .
  • the second outlet 118 serves as an outlet for the heat medium flowing through the second flow path 112 .
  • the angle between the line connecting the first inlet 115 and the first outlet 116 and the line connecting the second inlet 117 and the second outlet 118 is less than 25 degrees.
  • the second inlet 117 and the second outlet 118 are aligned with respect to the center line L in the width direction of the plates 103 and 104 when viewed in the stacking direction of the plates 103 and 104. Symmetrical.
  • the difference in flow path resistance due to the positional relationship between the second inlet 117 and the second outlet 118 can be reduced.
  • the uniformity of the amount of the heat medium flowing through the second flow path 112 can be further enhanced. Therefore, even if the heat medium flows into the second flow path 112 from the second inlet 117 in a two-phase state, the amount of heat medium flowing through the second flow path 112 can be made more uniform. Therefore, the uneven flow of the heat medium can be further suppressed, and heat exchange between the refrigerant and the heat medium can be further promoted, so that the performance of the heat exchanger 100 can be further improved.
  • the first inlet 115 and the first outlet 116 are located between the second inlet 117 and the second outlet 118 in the longitudinal direction of the plates 103 , 104 .
  • the first channel 111 in which the two-phase refrigerant flows, is more susceptible to drift than the second channel 112, in which the heat medium flows.
  • the first inlet 115 and the first outlet 116 of the first flow path 111 which tend to cause drift, are positioned more centrally than the second inlet 117 and the second outlet 118 of the second flow path 112, which tend to cause drift. Deploy.
  • the influence of the second inlet 117 and the second outlet 118 on the coolant flowing through the first flow path 111 can be reduced. Therefore, the drift of the coolant flowing through the first flow path 111 can be suppressed.
  • the inlet (second inlet 117 in this embodiment) and the outlet (second inlet 117 in this embodiment) on the high pressure side of the refrigerant and heat medium 118), the low-pressure side inlet (first inlet 115 in this embodiment) and outlet (first outlet 116 in this embodiment) of the refrigerant and heat medium are located.
  • the flow path (the first flow path 111 in the present embodiment) through which the medium on the low pressure side (refrigerant in the present embodiment) flows is susceptible to pressure loss.
  • the inlet and outlet of the medium on the low pressure side which is greatly affected by pressure loss, are arranged more centrally than the inlet and outlet of the medium on the high pressure side (heat medium in this embodiment), which is small in pressure loss.
  • the medium flow path on the low-pressure side can be shortened. Therefore, the pressure loss in the medium flow path on the low pressure side can be reduced.
  • the first inlet 115 is formed below the first outlet 116 .
  • plates 103 and 104 formed with first inlets 115 and first outlets 116 may be used so that the coolant flows from bottom to top.
  • the first inlet 115 and the first outlet 116 are symmetrical with respect to the center line L.
  • the first inlet 115 of this modified example is positioned lower than the embodiment, and the first outlet 116 of this modified example is positioned higher than the embodiment.
  • the second inlet 117 is formed on one side in the width direction (left side in FIG. 6) with respect to the center line L.
  • the second outlet 118 is formed on the other widthwise side (the right side in FIG. 6) with respect to the center line L. As shown in FIG. Here, the second inlet 117 and the second outlet 118 are symmetrical with respect to the center O of the plates 103,104.
  • the first inlet 115 and the second outlet 118 are at the same position in the longitudinal direction (vertical direction in FIG. 6).
  • the first outlet 116 and the second inlet 117 are at the same position in the longitudinal direction.
  • the angle ⁇ between the line connecting the first inlet 115 and the first outlet 116 (here, the center line L) and the line L1 connecting the second inlet 117 and the second outlet 118 exceeds 0 degrees and is 25 degrees. is less than
  • FIG. 7 shows an image of refrigerant flow in one plate 103, 104 of the heat exchanger according to this modification.
  • the first flow path 111 flows from bottom to top as in the embodiment.
  • the first channels 111 are a plurality of channels extending in the longitudinal direction of the plates 103, 104 and spaced apart from each other.
  • FIG. 8 shows an image of the heat medium flow in one plate 103, 104 of the heat exchanger according to this modification.
  • the second flow path 112 flows from upper left to lower right.
  • the second channels 112 are a plurality of channels extending in a direction that crosses the longitudinal direction of the plates 103, 104 at less than 25 degrees and are spaced apart from each other.
  • the heat exchanger of this modified example is suitable for use in a cascade heat exchanger of a cooling-only refrigerant cycle system.
  • a two-phase refrigerant flows through the first channel 111 .
  • the first inlet 115 and the first outlet 116 are symmetrical about the center line L. Therefore, it is possible to suppress the drift of the two-phase refrigerant flowing from the first inlet 115 to the first flow path 111 .
  • the heat medium flowing into the second flow path 112 from the second inlet 117 is in a gaseous state. For this reason, the heat medium does not enter a two-phase state in the second flow path 112, and thus drifting is less likely to occur than with the refrigerant. Therefore, the influence of the fact that the second inlet 117 and the second outlet 118 are not symmetrical with respect to the center line L is small.
  • the heat exchanger of this modified example can also be used in a cascade heat exchanger that performs cooling operation and heating operation as in the above embodiment.
  • the first flow path 111 formed between the first inlet 115 and the first outlet 116 located symmetrically with respect to the center line L is used during one operation ( In the above-described embodiment, the refrigerant flows in a two-phase state during the cooling operation.
  • one plate 103, 104 is formed with one through-hole as the first inlet 115, the first outlet 116, the second inlet 117 and the second outlet 118, but is limited to this. not.
  • one through-hole is formed as the first inlet 115 and the second inlet, and a plurality of through-holes are formed as the first outlet 116 and the second outlet 118.
  • FIG. 9 shows an image of the refrigerant inlet and outlet, the heat medium inlet and outlet, and the flow of the refrigerant and heat medium in one plate 103, 104 of the heat exchanger according to this modification.
  • the first entrance 115 is positioned on the center line L, as in the embodiment.
  • the first outlet 116 consists of two through holes 116a, 116b.
  • the two through-holes 116a and 116b are symmetrical with respect to the central line L.
  • the centroids of the two through holes 116a and 116b are located on the center line L.
  • the midpoint of the line connecting the centers of the two through holes 116a and 116b is located on the center line L.
  • the two through holes 116a and 116b have the same shape and size.
  • the distance between the centroids of the two through-holes 116a and 116b and the center line L is 10% or less of the width W of the plates 103 and 104, at least one of the two through-holes 116a and 116b is positioned laterally. They may be misaligned, and the two through holes 116a and 116b may differ in size and shape.
  • the second entrance 117 is positioned on the center line L, as in the embodiment.
  • the second outlet 118 consists of two through holes 118a, 118b.
  • the two through-holes 118a and 118b are symmetrical with respect to the central line L.
  • the centroids of the two through holes 118a and 118b are located on the center line L.
  • the midpoint of the line connecting the centers of the two through holes 118a and 118b is located on the center line L.
  • the two through holes 118a and 118b have the same shape and size.
  • the distance between the centroids of the two through-holes 118a and 118b and the center line L is 10% or less of the width W of the plates 103 and 104, at least one of the two through-holes 118a and 118b is positioned horizontally. They may be misaligned, and the two through holes 118a and 118b may differ in size and shape.
  • a line connecting the first inlet 115 and the first outlet 116 and a line connecting the second inlet 117 and the second outlet 118 in the embodiment are the first inlet 115, the first outlet 116, and the second inlet 117. and when a plurality of second outlets 118 are formed, the line connecting the centroids thereof.
  • the line connecting the first inlet 115 and the first outlet 116 is the line connecting the first inlet 115 and the centroids of the two through holes 116a and 116b. matches.
  • the line connecting the second inlet 117 and the second outlet 118 is the line connecting the second inlet 117 and the centroids of the two through-holes 118a and 118b, and thus coincides with the center line L here. Therefore, in this modified example, as in the embodiment, the angle between the line connecting the first inlet 115 and the first outlet 116 and the line connecting the second inlet 117 and the second outlet 118 is 0 degree. is.
  • the first inlet 115 is located above the second outlet 118 in the vertical direction of the plates 103 and 104 . Also, the first outlet 116 is located above the second inlet 117 in the vertical direction of the plates 103 and 104 .
  • the first flow path 111 is formed so that the coolant flows from the first inlet 115 toward the through holes 116 a and 116 b that are the two first outlets 116 .
  • the second flow path 112 is formed such that the heat medium flows from the second inlet 117 toward the through holes 118 a and 118 b that are the two second outlets 118 .
  • the length of the first channel 111 and the length of the second channel 112 are substantially the same.
  • a plurality of through holes are formed as the first inlets 115 in the single plates 103 and 104 .
  • a plurality of plates 103 and 104 with one through hole can be used as the first inlet 115 .
  • the coolant introduction pipe 105 attached to the frame 102 and the first inlets 115 of the plates 103 and 104 are located at the same position in the vertical direction and the horizontal direction.
  • the refrigerant lead-out pipe 106 and the first outlets 116 of the plates 103 and 104 are located at the same positions in the vertical and horizontal directions, and the heat medium lead-in pipe 107 attached to the frame 102 and the second inlets of the plates 103 and 104 117 is the same position in the vertical direction and the horizontal direction, and the heat medium outlet pipe 108 attached to the frame 102 and the second outlet 118 of the plates 103 and 104 are the same position in the vertical direction and the horizontal direction. , but not limited to.
  • FIG. 10 shows a frame according to this modified example.
  • the frame 102 is formed with a bulging portion 102a.
  • the bulging portion 102a is a convex portion formed on a part of the surface of the frame 102 opposite to the surface facing the plates 103 and 104 .
  • the bulging portion 102a is formed by, for example, pressing.
  • a refrigerant inlet pipe 105, a refrigerant outlet pipe 106, a heat medium inlet pipe 107, and a heat medium outlet pipe 108 are attached to the bulging portion 102a.
  • the refrigerant introduction pipe 105, the refrigerant outlet pipe 106, the heat medium introduction pipe 107, and the heat medium outlet pipe 108 are not positioned on a straight line with respect to the center line of the frame 102 in the width direction. Therefore, in this modified example, the degree of difficulty in connecting the refrigerant introduction pipe 105, the refrigerant outlet pipe 106, the heat medium introduction pipe 107, and the heat medium outlet pipe 108 to the frame 102 can be alleviated.
  • R32 was exemplified as the refrigerant and carbon dioxide was exemplified as the heat medium, but the present invention is not limited to these.
  • refrigerant As the refrigerant, R32, HFO refrigerant, mixed refrigerant of R32 and HFO refrigerant, carbon dioxide, ammonia, propane, or the like can be used.
  • heat medium As the heat medium, R32, HFO-based refrigerant, mixed refrigerant of R32 and HFO-based refrigerant, refrigerants such as carbon dioxide, ammonia, propane, water, antifreeze, and the like can be used.
  • HFO-based refrigerant for example, HFO-1234yf, HFO-1234ze, etc. can be used.
  • the same refrigerant or different media may be used for the refrigerant and the heat medium, but the heat medium has a lower global warming potential (GWP) than the refrigerant, It preferably has at least one of a low delaminating modulus (ODP), low flammability, and low toxicity.
  • GWP global warming potential
  • ODP delaminating modulus
  • heat exchangers 103, 104 plate 111: first channel 112: second channel 113: first inlet header 114: first outlet header 115: first inlet 116: first outlets 116a, 116b, 118a, 118b: through hole 117: second inlet 118: second outlet L: center line ⁇ : angle

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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

Cet échangeur de chaleur (100) comprend une pluralité de plaques empilées (103, 104). L'échangeur de chaleur (100) réalise un échange de chaleur entre un fluide frigorigène et un milieu caloporteur. Un premier trajet d'écoulement (111) et un second trajet d'écoulement (112) sont formés entre les plaques (103, 104). Un fluide frigorigène à deux phases s'écoule dans le premier trajet d'écoulement (111). Le milieu caloporteur s'écoule dans le second trajet d'écoulement (112). Une première entrée (115) et une première sortie (116) sont formées dans les plaques (103, 104). La première entrée (115) sert d'entrée pour le fluide frigorigène s'écoulant dans le premier trajet d'écoulement (111). La première sortie (116) sert de sortie pour le fluide frigorigène s'écoulant dans le premier trajet d'écoulement (111). Lorsqu'elles sont observées dans la direction d'empilement des plaques (103, 104), la première entrée (115) et la première sortie (116) présentent une symétrie axiale par rapport à une ligne centrale dans la direction de la largeur (L) des plaques (103, 104).
PCT/JP2022/035927 2021-09-30 2022-09-27 Échangeur de chaleur WO2023054353A1 (fr)

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10339590A (ja) * 1997-06-10 1998-12-22 Daikin Ind Ltd プレート式熱交換器
JPH11173772A (ja) 1997-12-10 1999-07-02 Daikin Ind Ltd プレート式熱交換器
JP2012127541A (ja) * 2010-12-13 2012-07-05 Hisaka Works Ltd プレート式熱交換器
JP2012229880A (ja) * 2011-04-27 2012-11-22 Hisaka Works Ltd プレート式熱交換器
JP2015152229A (ja) * 2014-02-14 2015-08-24 株式会社日阪製作所 プレート式熱交換器
JP2018189352A (ja) * 2017-04-28 2018-11-29 株式会社前川製作所 熱交換器

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10339590A (ja) * 1997-06-10 1998-12-22 Daikin Ind Ltd プレート式熱交換器
JPH11173772A (ja) 1997-12-10 1999-07-02 Daikin Ind Ltd プレート式熱交換器
JP2012127541A (ja) * 2010-12-13 2012-07-05 Hisaka Works Ltd プレート式熱交換器
JP2012229880A (ja) * 2011-04-27 2012-11-22 Hisaka Works Ltd プレート式熱交換器
JP2015152229A (ja) * 2014-02-14 2015-08-24 株式会社日阪製作所 プレート式熱交換器
JP2018189352A (ja) * 2017-04-28 2018-11-29 株式会社前川製作所 熱交換器

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US20240247875A1 (en) 2024-07-25

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