WO2024019095A1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

Info

Publication number
WO2024019095A1
WO2024019095A1 PCT/JP2023/026469 JP2023026469W WO2024019095A1 WO 2024019095 A1 WO2024019095 A1 WO 2024019095A1 JP 2023026469 W JP2023026469 W JP 2023026469W WO 2024019095 A1 WO2024019095 A1 WO 2024019095A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
flow path
joint
heat transfer
water
Prior art date
Application number
PCT/JP2023/026469
Other languages
English (en)
Japanese (ja)
Inventor
知恵 江村
拓郎 山田
智己 廣川
航 寺井
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.)
Filing date
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
Publication of WO2024019095A1 publication Critical patent/WO2024019095A1/fr

Links

Images

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
    • 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
    • F28D9/02—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 heat-exchange media travelling at an angle to one another
    • 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
    • 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
    • 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

  • a plurality of heat transfer plates are stacked at predetermined intervals to alternately form passages through which the first fluid flows and passages through which the second fluid flows in the stacking direction to perform heat exchange between the two fluids.
  • Plate heat exchangers are known.
  • Patent Document 1 Japanese Unexamined Patent Publication No. 10-1324766 discloses, as Embodiment 5, a heat transfer plate that is equipped with a heat transfer plate that can absorb the stress through elastic deformation and suppress damage even if frozen water undergoes volumetric expansion. Discloses an exchanger.
  • the present disclosure provides a heat exchanger in which leakage of refrigerant is suppressed when water freezes and expands in volume.
  • the heat exchanger of the first aspect is a heat exchanger that exchanges heat between water and a refrigerant, and includes a first flow path through which water flows and a second flow path through which the refrigerant flows. Any of the members forming the first flow path other than the partition wall separating the first flow path and the second flow path, or any of the joints where the members forming the first flow path are joined together. It functions as a weak portion having lower strength than other members forming the first flow path.
  • the first flow path and the second flow path which are members that form the first flow path and function as fragile parts before other parts, are Either one of the members other than the partition wall that separates the first flow path or a joint where the members forming the first flow path are joined is broken. Therefore, according to this heat exchanger, when water freezes and expands in volume, the member forming the second flow path, the joint forming the second flow path, or the partition wall breaks and the refrigerant leaks. It is restrained from doing so.
  • the heat exchanger according to the second aspect is the heat exchanger according to the first aspect, in which the first flow path is formed using two partition walls, an inner fin, and a spacing member.
  • the inner fin is laminated between two partition walls and has a wave-shaped cross section.
  • the spacing member is disposed at the edge of the two partition walls and separates the two partition walls.
  • the heat exchanger according to the third aspect is the heat exchanger according to the second aspect, and the fragile part is an inner fin.
  • the inner fins forming the first flow path break before other parts, so the members forming the second flow path and This prevents the joint from breaking and leaking the refrigerant.
  • the heat exchanger according to the fourth aspect is the heat exchanger according to the third aspect, in which the wall thickness of the inner fin is tw, the distance between the tops of the inner fins in contact with the same partition wall is Lw, the wall thickness of the partition wall is tR, and the inner fin When the height in the stacking direction is hw, these satisfy the following relationship. tw/Lw ⁇ tR/hw
  • the stress generated in the partition wall when water freezes and expands in volume can be made smaller than the stress generated in the inner fin.
  • the force generated by volumetric expansion can be absorbed by the inner fin, which breaks before the partition wall, so that the leakage of refrigerant due to breakage of the members and joints forming the second flow path is suppressed.
  • the heat exchanger according to the fifth aspect is the heat exchanger according to the second aspect, and the weakened portion is a spacing member.
  • the spacing member forming the first flow path breaks before other parts, so the member forming the second flow path and This prevents the joint from breaking and leaking the refrigerant.
  • the heat exchanger according to the sixth aspect is the heat exchanger according to the fifth aspect, in which the width of the spacing member in plan view is Lsp, the thickness of the inner fin is tw, and the distance between the tops of the inner fins in contact with the same partition wall is Lw. , the thickness of the partition wall is tR, and the height of the inner fin in the stacking direction is hw, these satisfy the following relationship. ((Lsp+tw)/Lw) ⁇ tR/hw
  • the stress generated in the partition wall when water freezes and expands in volume can be made smaller than the stress generated in the spacing member.
  • the force generated by the volumetric expansion can be absorbed by the spacing member that breaks before the partition wall, which prevents the members and joints forming the second flow path from breaking and leaking the refrigerant.
  • the heat exchanger according to the seventh aspect is the heat exchanger according to the first aspect, in which the first flow path is formed using two partition walls, an inner fin, and a spacing member.
  • the inner fin is laminated between two partition walls and has a wave-shaped cross section.
  • the spacing member is disposed at the edge of the two partition walls and separates the two partition walls.
  • the heat exchanger has a first joint part and a second joint part. The first joint is a location where the partition wall and the top of the inner fin are joined.
  • the second joint is a location where the partition wall and the spacing member are joined.
  • the heat exchanger according to the eighth aspect is the heat exchanger according to the seventh aspect, and the fragile part is the first joint part.
  • the first joint that joins the members forming the first flow path breaks before other parts. This prevents the refrigerant from leaking due to breakage of the members and joints forming the flow path.
  • the heat exchanger according to the ninth aspect is the heat exchanger according to the eighth aspect, and the first joint portion is joined by brazing. Assuming that the width of the first joint is bw1, the distance between the tops of inner fins that touch the same partition wall is Lw, the wall thickness of the partition wall is tR, and the height of the inner fins in the stacking direction is hw, these satisfy the following relationship. . 0.35 ⁇ bw1/(2 ⁇ Lw) ⁇ tR/hw
  • the stress generated in the partition wall when water freezes and expands in volume can be made smaller than the stress generated in the first joint. This allows the force generated by volumetric expansion to be absorbed by the first joint, which breaks before the partition wall, so that the members and joints forming the second flow path do not break and the refrigerant leaks. suppressed.
  • the heat exchanger according to the tenth aspect is the heat exchanger according to the eighth aspect, and the first joint portion is joined by diffusion bonding.
  • the width of the first joint is bw1
  • the distance between the tops of inner fins that touch the same partition wall is Lw
  • the wall thickness of the partition wall is tR
  • the height of the inner fins in the stacking direction is hw
  • the stress generated in the partition wall when water freezes and expands in volume can be made smaller than the stress generated in the first joint. This allows the force generated by volumetric expansion to be absorbed by the first joint, which breaks before the partition wall, so that the members and joints forming the second flow path do not break and the refrigerant leaks. suppressed.
  • the heat exchanger according to the eleventh aspect is the heat exchanger according to the seventh aspect, and the fragile part is the second joint part.
  • the second joint that joins the members forming the first flow path breaks before other parts. This prevents the refrigerant from leaking due to breakage of the members and joints forming the flow path.
  • the heat exchanger according to the twelfth aspect is the heat exchanger according to the eleventh aspect, and the second joint portion is joined by brazing.
  • the width of the second joint is bsp2
  • the width of the first joint is bw1
  • the interval between the tops of inner fins in contact with the same partition is Lw
  • the wall thickness of the partition is tR
  • the height of the inner fin in the stacking direction is hw.
  • the stress that occurs in the partition when water freezes and expands in volume can be made smaller than the stress that occurs in the second joint.
  • the force generated by volumetric expansion can be absorbed by the second joint, which breaks before the partition wall, so that the members and joints forming the second flow path do not break and the refrigerant leaks. suppressed.
  • the heat exchanger according to the thirteenth aspect is the heat exchanger according to the eleventh aspect, and the second joint portion is joined by diffusion bonding.
  • the width of the second joint is bsp2
  • the width of the first joint is bw1
  • the interval between the tops of inner fins in contact with the same partition is Lw
  • the wall thickness of the partition is tR
  • the height of the inner fin in the stacking direction is hw.
  • the stress that occurs in the partition when water freezes and expands in volume can be made smaller than the stress that occurs in the second joint.
  • the force generated by volumetric expansion can be absorbed by the second joint, which breaks before the partition wall, so that the members and joints forming the second flow path do not break and the refrigerant leaks. suppressed.
  • the heat exchanger according to the fourteenth aspect is the heat exchanger according to the first aspect, in which the first flow path is formed using two heat transfer plates.
  • the heat exchanger has a third joint and a fourth joint.
  • the two heat transfer plates are stacked on each other and each has a corrugated cross section.
  • the third joint is where the tops of the two heat transfer plates are joined.
  • the fourth joint is a location where the edges of the two heat transfer plates are joined.
  • the heat exchanger according to the fifteenth aspect is the heat exchanger according to the fourteenth aspect, and the weakened part is the third joint part.
  • the third joint 210d where the members forming the first flow path are joined, breaks before other parts.
  • the leakage of the refrigerant due to breakage of the members and joints forming the second flow path is suppressed.
  • the heat exchanger according to the sixteenth aspect is the heat exchanger according to the fifteenth aspect, in which the third joint portion is joined by brazing. Assuming that the width of the third joint section viewed along the normal direction is bw3 and the thickness of the heat transfer plate is t, these satisfy the following relationship. 0.35 ⁇ bw3 ⁇ 2 ⁇ t
  • the stress that occurs in the heat transfer plate when water freezes and expands in volume can be made smaller than the stress that occurs in the third joint. This allows the force generated by volumetric expansion to be absorbed by the third joint, which breaks before the heat transfer plate, so that the members and joints that form the second flow path break and the refrigerant leaks. things are suppressed.
  • the heat exchanger according to the seventeenth aspect is the heat exchanger according to the fifteenth aspect, and the third joint portion is joined by diffusion bonding. Assuming that the width of the third joint section viewed along the normal direction is bw3 and the thickness of the heat transfer plate is t, these satisfy the following relationship. bw3 ⁇ 2 ⁇ t
  • the stress that occurs in the heat transfer plate when water freezes and expands in volume can be made smaller than the stress that occurs in the third joint. This allows the force generated by volumetric expansion to be absorbed by the third joint, which breaks before the heat transfer plate, so that the members and joints that form the second flow path break and the refrigerant leaks. things are suppressed.
  • the heat exchanger according to the 18th aspect is the heat exchanger according to the 14th aspect, and the fragile part is the fourth joint part.
  • the fourth joint 210e when water freezes and expands in volume, the fourth joint 210e, where the members forming the first flow path are joined, breaks before other parts. This prevents the refrigerant from leaking due to breakage of the members and joints forming the two flow paths.
  • the heat exchanger according to the nineteenth aspect is the heat exchanger according to the eighteenth aspect, in which the fourth joint portion is joined by brazing.
  • the width of the fourth joint seen along the normal direction is bsp4
  • the width of the third joint section viewed along the normal direction is bw3
  • the thickness of the heat transfer plate is t
  • the stress generated in the heat transfer plate when water freezes and expands in volume can be made smaller than the stress generated in the fourth joint. This allows the force generated by volumetric expansion to be absorbed by the fourth joint, which breaks before the heat transfer plate, so that the members and joints that form the second flow path break and the refrigerant leaks. things are suppressed.
  • the heat exchanger according to the 20th aspect is the heat exchanger according to the 18th aspect, and the fourth joint portion is joined by diffusion bonding.
  • the width of the fourth joint seen along the normal direction is bsp4
  • the width of the third joint seen along the normal direction is bw3
  • the thickness of the heat transfer plate is t
  • the stress generated in the heat transfer plate when water freezes and expands in volume can be made smaller than the stress generated in the fourth joint. This allows the force generated by volumetric expansion to be absorbed by the fourth joint, which breaks before the heat transfer plate, so that the members and joints that form the second flow path break and the refrigerant leaks. things are suppressed.
  • the heat exchanger according to the twenty-first aspect is the heat exchanger according to the first aspect, and includes a first heat transfer plate and a second heat transfer plate.
  • the first heat transfer plate has a first flow path formed therein.
  • the second heat transfer plate has a second flow path formed therein.
  • the weakened part is the first heat transfer plate.
  • the first heat transfer plate that forms the first flow path breaks before other parts, so the second flow path is formed. This prevents the second heat transfer plate from breaking and leaking the refrigerant.
  • the heat exchanger according to the 22nd aspect is the heat exchanger according to the 21st aspect, in which the first heat transfer plate is formed by laminating two plate-like members in which grooves forming the first flow path are formed. be done.
  • the fragile portion is a location where two plate-like members are joined.
  • the heat exchanger according to the twenty-third aspect is any of the heat exchangers according to the first aspect to the twenty-second aspect, and the refrigerant is flammable or toxic.
  • the heat exchanger according to the 24th aspect is any of the heat exchangers according to the 1st aspect to the 23rd aspect, and the fragile portion is formed to have a strength such that it breaks when water freezes.
  • FIG. 1 is a schematic configuration diagram showing a refrigerant cycle device 1 including a heat exchanger 100.
  • FIG. 1 is a perspective view of a heat exchanger 100.
  • FIG. 3 is an enlarged view of section A in FIG. 2.
  • FIG. 3 is a cross-sectional view showing a first inner fin 110 housed in a heat exchanger 100.
  • FIG. 3 is a cross-sectional view showing a second inner fin 120 housed in the heat exchanger 100.
  • FIG. FIG. 4 is a cross-sectional view of the heat exchanger 100 of FIG. 3 taken along line B-B'.
  • FIG. 2 is an exploded perspective view of a heat exchanger 200.
  • 2 is a cross-sectional view of a heat exchanger 200.
  • FIG. FIG. 3 is a perspective view of a heat exchanger 300.
  • 10 is an enlarged view of section C in FIG. 9.
  • FIG. 11 is a cross-sectional view of the heat exchanger 300 of FIG. 10 taken along line
  • a refrigerant cycle device 1 including a heat exchanger 100 heats or cools water, such as city water (tap water), that is supplied from outside the refrigerant cycle device 1 and then supplies the water.
  • the refrigerant cycle device 1 includes a water intake section 1a, a water supply section 1b, a heat exchanger 100, a refrigerant circuit 10, a water circuit 20, a water supply section 30, and a control section 40.
  • the water supply unit 30 is installed indoors, and the water circuit 20 and refrigerant circuit 10 are installed outdoors.
  • a refrigerant circulates in the refrigerant circuit 10, and water circulates in the water circuit 20.
  • the water intake section 1a takes water supplied from the outside into the refrigerant cycle device 1.
  • the water supply unit 1b supplies water heated or cooled by the refrigerant cycle device 1 to the outside.
  • the heat exchanger 100 exchanges heat between the refrigerant circulating in the refrigerant circuit 10 and the water circulating in the water circuit 20.
  • the heat exchanger 100 has first flow pipes 170a, 170b, second flow pipes 180a, 180b, a first flow path 111, and a second flow path 121.
  • the first channel 111 is a channel through which water flows.
  • the first flow path 111 is provided between the first flow pipe 170a and the first flow pipe 170b.
  • the second flow path 121 is a flow path through which the refrigerant flows.
  • the second flow path 121 is formed between the second flow pipe 180a and the second flow pipe 180b. The detailed structure of the heat exchanger 100 will be described later.
  • the refrigerant circuit 10 In the refrigerant circuit 10, refrigerant is heated or cooled.
  • the refrigerant circuit 10 includes a compressor 11 , a four-way switching valve 12 , a heat source heat exchanger 13 , an expansion valve 14 , and a second flow path 121 of the heat exchanger 100 .
  • the compressor 11, the four-way switching valve 12, the heat source heat exchanger 13, the expansion valve 14, and the second flow path 121 of the heat exchanger 100 are connected by piping, and a refrigerant circulates inside.
  • the refrigerant is propane.
  • the compressor 11 sucks the low-pressure refrigerant in the refrigerant circuit 10 from the suction part 11a, compresses it, and discharges it as high-pressure refrigerant from the discharge part 11b.
  • the four-way switching valve 12 has a first port P1, a second port P2, a third port P3, and a fourth port P4. Based on instructions from the control unit 40, the four-way switching valve 12 operates between a first state and a second state in which the communication states of the first port P1, second port P2, third port P3, and fourth port P4 are different. Switch with . In the first state, the first port P1 and the second port P2 communicate with each other, and the third port P3 and the fourth port P4 communicate with each other. In the second state, the first port P1 and the fourth port P4 communicate with each other, and the second port P2 and the third port P3 communicate with each other.
  • the first port P1 is connected to the discharge part 11b of the compressor 11.
  • the second port P2 is connected to the second flow pipe 180a of the heat exchanger 100.
  • the third port P3 is connected to the suction section 11a of the compressor 11.
  • the fourth port P4 is connected to one end of the heat source heat exchanger 13.
  • the heat source heat exchanger 13 exchanges heat between the refrigerant circulating in the refrigerant circuit 10 and a heat source (for example, outdoor air).
  • a heat source for example, outdoor air
  • the expansion valve 14 functions as a pressure reducing device that adjusts the flow rate of the refrigerant circulating through the refrigerant circuit 10 and reduces the pressure of the refrigerant.
  • One end of the expansion valve 14 is connected to the other end of the heat source heat exchanger 13.
  • the other end of the expansion valve 14 is connected to the second flow pipe 180b of the heat exchanger 100.
  • the water circuit 20 In the water circuit 20, water that has undergone heat exchange with the refrigerant circulates.
  • the water circuit 20 includes a first flow path 111 of the heat exchanger 100, a water circulation pump 21, a flow rate control valve 22, and a utilization heat exchanger 23.
  • the first flow path 111, water circulation pump 21, flow rate control valve 22, and utilization heat exchanger 23 of the heat exchanger 100 are connected by piping, and water circulates inside.
  • the water circulation pump 21 circulates water inside the water circuit 20.
  • the water circulation pump 21 sucks water inside the water circuit 20 from the suction part 21a and discharges it from the discharge part 21b.
  • the suction section 21a is connected to the first flow pipe 170a of the heat exchanger 100.
  • the discharge portion 21b is connected to one end of the flow control valve 22.
  • the flow rate control valve 22 adjusts the flow rate of water circulating in the water circuit 20.
  • the utilization heat exchanger 23 exchanges heat between the water circulating in the water circuit 20 and the water stored inside the water storage tank 31 (described later) of the water supply section 30.
  • the utilization heat exchanger 23 is arranged inside the water storage tank 31 so that the water passing therethrough can exchange heat with the water stored in the water storage tank 31.
  • One end of the utilization heat exchanger 23 is connected to the other end of the flow control valve 22.
  • the other end of the utilization heat exchanger 23 is connected to the first flow pipe 170b of the heat exchanger 100.
  • the water circuit 20 may further include a heat exchanger for heating or cooling indoor air using circulating water.
  • the water supply unit 30 exchanges heat between water supplied from outside of the refrigerant cycle device 1 and water circulating through the water circuit 20, and then supplies the water to the outside of the refrigerant cycle device 1.
  • the water supply section 30 includes a water storage tank 31, a water supply pump 32, and a mixing valve 33.
  • the water storage tank 31, the water supply pump 32, and the mixing valve 33 are connected by piping.
  • the water storage tank 31 stores water supplied from the outside.
  • the stored water exchanges heat with the water passing through the utilization heat exchanger 23.
  • the water storage tank 31 takes in water supplied from the outside from the water inlet 31a and stores it therein.
  • the stored water exchanges heat with the water passing through the utilization heat exchanger 23, and is discharged from the water outlet portion 81b.
  • the water inlet part 31a is connected to the water intake part 1a, which is supplied with water from the outside.
  • the water supply pump 32 sucks water stored in the water storage tank 31 and supplies it to the mixing valve 33.
  • the water supply pump 32 sucks water inside the water storage tank 31 through a suction portion 32a and discharges it from a discharge portion 32b.
  • the suction part 32a is connected to the water outlet part 31b.
  • the discharge portion 32b is connected to a second port 33b (described later) of the mixing valve 33.
  • the mixing valve 33 mixes water supplied from the outside and water stored in the water storage tank 31.
  • the mixing valve 33 has a first port 33a, a second port 33b, and a third port 33c.
  • the first port 33a is connected to the water intake section 1a to which water is supplied from the outside.
  • the second port 33b is connected to the discharge part 32b of the water supply pump 32.
  • the third port 33c is connected to the water supply section 1b that communicates with the outside of the refrigerant cycle device 1.
  • Control unit 40 controls the compressor 11 , the four-way switching valve 12 , the expansion valve 14 , the water circulation pump 21 , the flow control valve 22 , the water supply pump 32 , and the mixing valve 33 .
  • the control unit 40 is configured to be able to send and receive control signals to and from the compressor 11, four-way switching valve 12, expansion valve 14, water circulation pump 21, flow rate adjustment valve 22, water supply pump 32, and mixing valve 33. electrically connected to.
  • (1-6) Operation of refrigerant cycle device 1 The refrigerant cycle device 1 performs heating operation, cooling operation, and defrosting operation.
  • the heating operation is an operation in which the refrigerant cycle device 1 heats water supplied from the outside to the water intake section 1a and supplies it from the water supply section 1b.
  • the control unit 40 sets the four-way switching valve 12 to the first state, drives the compressor 11, water circulation pump 21, and water supply pump 32, and controls the expansion valve 14, flow rate adjustment valve 22, and mixing valve 33. Control opening degree.
  • (1-6-1-1) Refrigerant circuit 10 The compressor 11 sucks the low-pressure gas-phase refrigerant in the refrigerant circuit 10 from the suction part 11a, and discharges it as high-pressure gas-phase refrigerant from the discharge part 11b.
  • the refrigerant in the high-pressure gas phase passes through the four-way switching valve 12 through the first port P1 and the second port P2 in this order, and reaches the second flow path 121 of the heat exchanger 100.
  • the high-pressure gas phase refrigerant is condensed to become a high-pressure liquid phase refrigerant. At this time, the refrigerant releases heat to the water passing through the first flow path 111.
  • the high-pressure liquid phase refrigerant reaches the expansion valve 14 .
  • the expansion valve 14, which is set to an appropriate opening degree, reduces the pressure of the high-pressure liquid phase refrigerant and converts it into a low-pressure gas-liquid two-phase refrigerant.
  • the low-pressure gas-liquid two-phase refrigerant is evaporated in the heat source heat exchanger 13 to become a low-pressure gas-phase refrigerant.
  • the refrigerant absorbs heat from the heat source (outside air).
  • the low-pressure gas phase refrigerant passes through the four-way switching valve 12 through the fourth port P4 and the third port P3 in this order, and is then sucked into the compressor 11 from the suction portion 11a.
  • the water circulation pump 21 sucks water circulating through the water circuit 20 from the suction part 21a and discharges it from the discharge part 21b.
  • the discharged water passes through the flow control valve 22 and reaches the utilization heat exchanger 23 .
  • the water that has reached the utilization heat exchanger 23 releases heat to the water stored in the water storage tank 31 in the utilization heat exchanger 23 .
  • the water that has reached the utilization heat exchanger 23 heats the water stored in the water storage tank 31 in the utilization heat exchanger 23 .
  • the water that has released heat in the utilization heat exchanger 23 reaches the first flow path 111 of the heat exchanger 100.
  • the water that has reached the first flow path 111 of the heat exchanger 100 absorbs heat from the refrigerant passing through the second flow path 121.
  • the water that has absorbed heat is sucked into the water circulation pump 21 from the suction section 21a.
  • (1-6-1-3) Water supply section 30 The water stored in the water storage tank 31 is heated by absorbing heat from the water passing through the utilization heat exchanger 23.
  • the water supply pump 32 sucks water heated in the water storage tank 31 from the suction part 32a.
  • the water sucked into the water supply pump 32 is discharged from the discharge portion 32b to the mixing valve 33.
  • the water discharged from the water supply pump 32 passes through the second port 33b and is mixed with water from the outside that has passed through the water intake portion 1a and reached the first port 33a.
  • the water mixed by the mixing valve 33 is supplied to the outside of the refrigerant cycle device 1 from the water supply section 1b after passing through the third port 33c.
  • the cooling operation is an operation in which the refrigerant cycle device 1 cools water supplied from the outside to the water intake section 1a and supplies it from the water supply section 1b.
  • the control unit 40 sets the four-way switching valve 12 to the second state, drives the compressor 11, water circulation pump 21, and water supply pump 32, and controls the expansion valve 14, flow rate adjustment valve 22, and mixing valve 33. Control opening degree.
  • (1-6-2-1) Refrigerant circuit 10 The compressor 11 sucks the low-pressure gas-phase refrigerant in the refrigerant circuit 10 from the suction part 11a, and discharges it as high-pressure gas-phase refrigerant from the discharge part 11b.
  • the refrigerant in the high-pressure gas phase passes through the four-way switching valve 12 through the first port P1 and the fourth port P4 in this order, and reaches the heat source heat exchanger 13.
  • the high-pressure gas phase refrigerant is condensed to become a high-pressure liquid phase refrigerant.
  • the refrigerant releases heat to the heat source (outside air).
  • the high-pressure liquid phase refrigerant reaches the expansion valve 14 .
  • the expansion valve 14 which is set to an appropriate opening degree, reduces the pressure of the high-pressure liquid phase refrigerant and converts it into a low-pressure gas-liquid two-phase refrigerant.
  • the low-pressure gas-liquid two-phase refrigerant evaporates in the second flow path 121 of the heat exchanger 100 to become a low-pressure gas-phase refrigerant.
  • the refrigerant absorbs heat from the water passing through the first flow path 111.
  • the low-pressure gas phase refrigerant passes through the four-way switching valve 12 through the second port P2 and the third port P3 in this order, and is then sucked into the compressor 11 from the suction portion 11a.
  • the water circulation pump 21 sucks water circulating through the water circuit 20 from the suction part 21a and discharges it from the discharge part 21b.
  • the discharged water passes through the flow control valve 22 and reaches the utilization heat exchanger 23 .
  • the water that has reached the utilization heat exchanger 23 absorbs heat from the water stored in the water storage tank 31 in the utilization heat exchanger 23 .
  • the water that has reached the utilization heat exchanger 23 cools the water stored in the water storage tank 31 in the utilization heat exchanger 23 .
  • the water that has absorbed heat in the utilization heat exchanger 23 reaches the first flow path 111 of the heat exchanger 100.
  • the water that has reached the first flow path 111 of the heat exchanger 100 releases heat to the refrigerant passing through the second flow path 121.
  • the water that has released heat is sucked into the water circulation pump 21 from the suction section 21a.
  • Water supply section 30 The water stored in the water storage tank 31 is cooled by releasing heat to the water passing through the utilization heat exchanger 23.
  • the water supply pump 32 sucks water cooled in the water storage tank 31 from the suction part 32a.
  • the water sucked into the water supply pump 32 is discharged from the discharge portion 32b to the mixing valve 33.
  • the water discharged from the water supply pump 32 passes through the second port 33b and is mixed with water from the outside that has passed through the water intake portion 1a and reached the first port 33a.
  • the water mixed by the mixing valve 33 is supplied to the outside of the refrigerant cycle device 1 from the water supply section 1b after passing through the third port 33c.
  • the defrost operation is an operation in which frost adhering to the surface of the heat source heat exchanger 13 during the heating operation is melted and removed by the heat of the refrigerant condensed in the heat source heat exchanger 13.
  • the operations of each part of the refrigerant cycle device 1 during the defrost operation are similar to those in the cooling operation described above. Therefore, a detailed explanation of the defrost operation will be omitted.
  • the heat exchanger 100 includes a plurality of first inner fins 110, a plurality of second inner fins 120, a plurality of partition walls 130, a first spacing member 140, The heat exchanger includes a second spacing member 150, a casing 160, a first flow pipe 170a, a first flow pipe 170b, a second flow pipe 180a, and a second flow pipe 180b.
  • the heat exchanger 100 has a first flow path 111 through which water flows and a second flow path 121 through which a refrigerant flows. Although details will be described later, the heat exchanger 100 has a fragile portion 190 that prevents the refrigerant flowing through the second flow path 121 from flowing into the first flow path 111 when the water freezes.
  • the first inner fin 110, the second inner fin 120, and the partition wall 130 are metal plate-like members having the same rectangular outer shape.
  • the first inner fin 110, the second inner fin 120, and the partition wall 130 have a rectangular shape that is elongated in the first direction.
  • the first inner fins 110 and the second inner fins 120 are alternately stacked with the partition wall 130 in between, and are housed in the casing 160.
  • the number of each of the first inner fins 110 and the second inner fins 120 is not particularly limited, and is appropriately set according to the required performance.
  • the first direction may be referred to as the longitudinal direction DL for convenience.
  • the direction perpendicular to the first direction may be referred to as the width direction DW.
  • the direction in which the first inner fins 110, the partition walls 130, and the second inner fins 120 are stacked may be referred to as a stacking direction DS.
  • the longitudinal direction DL, the width direction DW, and the stacking direction DS correspond to the directions indicated by arrows in each figure.
  • the back, front, left, and right directions used in the following description correspond to the directions shown by arrows in FIGS. 2 to 5.
  • First inner fin 110 is a wavy fin with a wavy cross section.
  • the waveform of the first inner fin 110 is formed such that the top portion 110t of the waveform extends along the longitudinal direction DL in plan view.
  • the first inner fin 110 forms a first flow path 111 together with the partition wall 130 stacked adjacent to each other and a first spacing member 140 separating the partition wall 130.
  • the first inner fin 110 is formed using, for example, press processing, although the invention is not limited thereto.
  • the "waveform" is not limited to a shape in which semicircular irregularities are periodically arranged as shown in FIG. It may also have a shape that changes periodically. This also applies to the second inner fin 120.
  • the second inner fin 120 is a wavy fin with a wavy cross section.
  • the waveform of the second inner fin 120 is formed such that the top portion 120t of the waveform extends along the width direction DW in plan view.
  • the second inner fin 120 forms a second flow path 121 together with the partition wall 130 stacked adjacent thereto.
  • the second inner fins 120 are formed using, for example, press processing, although the invention is not limited thereto.
  • Partition wall 130 is a flat plate that separates the first inner fin 110 and the second inner fin 120 in the stacking direction DS.
  • the first spacing member 140 is a member that separates two partition walls 130 in order to arrange the first inner fin 110 between adjacent partition walls 130 in the stacking direction DS.
  • the first spacing member 140 is a band-shaped member extending along the longitudinal direction DL.
  • the first spacing member 140 is arranged along both edges of the partition wall 130 in the width direction DW.
  • the height of the first spacing member 140 in the stacking direction DS is formed to be the same as the height of the first inner fin 110 in the stacking direction DS.
  • the first inner fin 110 is arranged between first spacing members 140 arranged along both edges of the partition wall 130 in the width direction DW.
  • the second spacing member 150 is a member that separates the two partition walls 130 in order to arrange the second inner fin 120 between the partition walls 130 adjacent to each other in the stacking direction DS.
  • the second spacing member 150 is a band-shaped member extending along the width direction DW.
  • the second spacing member 150 is arranged along both edges of the partition wall 130 in the longitudinal direction DL.
  • the height of the second spacing member 150 in the stacking direction DS is formed to be the same as the height of the second inner fin 120 in the stacking direction DS.
  • the first inner fin 110 is arranged between second spacing members 150 arranged along both ends of the partition wall 130 in the longitudinal direction DL.
  • the casing 160 is a substantially rectangular parallelepiped member that accommodates the first inner fin 110, the second inner fin 120, the partition 130, the first spacing member 140, and the second spacing member 150.
  • the casing 160 has two main surfaces 160a perpendicular to the stacking direction DS, two first side surfaces 160b, and two second side surfaces 160c.
  • the main surface 140a is a surface perpendicular to the stacking direction DS.
  • the first side surface 160b is a surface perpendicular to the longitudinal direction DL.
  • the second side surface 160c is a surface perpendicular to the width direction DW.
  • the casing 160 has a first header 141, a second header 142, a third header 143, a fourth header 144, and a fifth header 145 formed therein.
  • the first header 141 is a space that divides the water that has entered the casing 160 into the plurality of first channels 111.
  • the first header 141 is formed along the first side surface 160b on the back side.
  • the second header 142 is a space in which water that has passed through the first flow path 111 joins together.
  • the second header 142 is formed along the first side surface 160b on the near side.
  • the third header 143 is a space that divides the refrigerant that has entered the casing 160 into the plurality of second flow paths 121.
  • the third header 143 is formed along the back side of the second side surface 160c on the right side.
  • the fourth header 144 is a space where the refrigerant that has passed through the second flow path 121 joins together.
  • the fourth header 144 is formed along the front side of the second side surface 160c on the right side.
  • the fifth header 145 is a space in which the refrigerant that has passed through the second flow path 121 is merged, changes the flow direction, and is diverted to the second flow path 121 again.
  • the fifth header 145 includes a fifth header 145a, a fifth header 145b, and a fifth header 145c. As shown in FIG. 5, the fifth header 145a is formed along the back side of the second side surface 160c on the left side.
  • the fifth header 145b is formed along between the fourth header 144 and the fifth header 145 on the second side surface 160c on the right side.
  • the fifth header 145c is formed along the front side of the second side surface 160c on the left side.
  • First flow pipe 170a and first flow pipe 170b The first flow pipe 170a is a pipe that allows water to flow through the first flow path 111.
  • the first flow pipe 170a is provided in the casing 160 so as to pass through the first side surface 160b on the near side and communicate with the first header 141.
  • the first flow pipe 170b is a pipe that allows water to flow through the first flow path 111.
  • the first flow pipe 170b is provided in the casing 160 so as to penetrate through the first side surface 160b on the back side and communicate with the second header 142.
  • Second flow pipe 180a and second flow pipe 180b The second flow pipe 180a is a pipe that allows the refrigerant to flow through the second flow path 121.
  • the second flow pipe 180a is provided in the casing 160 so as to pass through the second right side surface 160c and communicate with the third header 143.
  • the second flow pipe 180b is a pipe that allows water to flow through the second flow path 121.
  • the second flow pipe 180b is provided in the casing 160 so as to penetrate through the second right side surface 160c and communicate with the fourth header 144.
  • the first flow path 111 includes a space extending in the longitudinal direction DL surrounded by the first inner fin 110 and the partition wall 130 and a space extending in the longitudinal direction DL surrounded by the first inner fin 110, the partition wall 130, and the first spacing member 140. This is a space extending to DL.
  • first inner fin 110, the partition wall 130, and the first spacing member 140 are joined by brazing. More specifically, the corrugated top portion 110t of the first inner fin 110 is joined to the partition wall 130 by brazing.
  • the first spacing member 140 has a surface perpendicular to the stacking direction DS joined to the partition wall 130 by brazing.
  • first joint portion 110c the portion where the top portion 110t and the partition wall 130 are joined
  • second joint portion 140c the portion where the partition wall 130 and the first spacing member 140 are joined.
  • the first joint 110c and the second joint 140c are examples of joints.
  • the second inner fin 120 is accommodated in a space surrounded by two partition walls 130 adjacent to each other in the stacking direction DS and two second spacing members 150 arranged between these partition walls 130, so that the longitudinal direction A plurality of second channels 121 are formed in line with the DL.
  • the second flow path 121 includes a space extending in the width direction DW surrounded by the second inner fin 120 and the partition wall 130 and a space extending in the width direction DW surrounded by the second inner fin 120, the partition wall 130, and the second spacing member 150. This is a space extending to DW.
  • the plurality of first inner fins 110 and the plurality of second inner fins 120 are stacked alternately with the partition wall 130 in between, so that the plurality of first flow channels 111 are arranged in the width direction DW and the plurality of first flow channels 111 are arranged in the longitudinal direction DL.
  • a plurality of second channels 121 are stacked in a parallel grid shape in the stacking direction DS.
  • the heat exchanger 100 has a weak portion 190 that has lower strength than other parts and breaks when water freezes and expands in volume.
  • the fragile portion 190 is any member other than the partition wall 130 that forms the first flow path 111 and separates the first flow path 111 and the second flow path 121.
  • the first inner fin 110 and the first spacing member 140 function as the fragile portion 190.
  • the first inner fins 110 and the first spacing member 140 are arranged so that when the volume of water expands beyond a certain level, the first inner fin 110 breaks first, and then the first spacing member 140 breaks. Preferably, it is formed.
  • the dimensions of each part forming the first flow path 111 satisfy the following relationship (Equation 1).
  • the thickness of the first inner fin 110 is tw
  • the interval between the top portions 110t in contact with the same partition 130 is Lw
  • the thickness of the partition 130 is tR
  • the height of the first inner fin in the stacking direction DS is hw.
  • tw is, for example, 0.15 mm.
  • Lw is, for example, 2 mm.
  • tR is, for example, 0.15 mm.
  • hw is, for example, 1 mm.
  • the dimensions of each portion forming the first flow path 111 satisfy the following relationship (Equation 2).
  • the width of the first spacing member 140 in plan view is assumed to be Lsp. ((Lsp+tw)/Lw) ⁇ tR/hw...(Formula 2)
  • Lsp is, for example, 0.1 mm.
  • the water that has reached the front side passes through the first header 141 and is led out from the first flow pipe 170a. In either case, the water flowing through the first channel 111 exchanges heat with the refrigerant in the adjacent second channel 121 via the partition wall 130 .
  • the refrigerant introduced from the second flow pipe 180a of the heat exchanger 100 passes through the third header 143 and flows into the second flow path 121.
  • the refrigerant that has entered the second flow path 121 flows from the right side to the left side along the width direction DW in the second flow path 121.
  • the refrigerant that has reached the left side merges at the fifth header 145a, flows toward the front side along the longitudinal direction DL, and branches into the plurality of second flow paths 121 again.
  • the refrigerant that has flowed into the second flow path 121 from the fifth header 145a flows from the left side to the right side in the second flow path 121 along the width direction DW.
  • the refrigerant flows through the fifth header 145b, the second flow path 121, the fifth header 145c, and the second flow path 121, repeating branching and merging, and then flows through the fourth header 144. It passes through and is led out from the second flow pipe 180b. Further, the refrigerant introduced from the second flow pipe 180b of the heat exchanger 100 passes through the fourth header 144 and flows into the second flow path 121. The refrigerant that has entered the second flow path 121 flows from the right side to the left side along the width direction DW in the second flow path 121.
  • the refrigerant that has reached the left side merges at the fifth header 145c, flows toward the back front side along the longitudinal direction DL, and branches into the plurality of second flow paths 121 again.
  • the refrigerant that has flowed into the second flow path 121 from the fifth header 145c flows through the second flow path 121 from the left side to the right side along the width direction DW.
  • the refrigerant flows through the fifth header 145b, the second flow path 121, the fifth header 145a, and the second flow path 121, repeating branching and merging, and then flows through the third header 143. It passes through and is led out from the second flow pipe 180a.
  • the water flowing through the second flow path 121 exchanges heat with the water in the adjacent first flow path 111 via the partition wall 130 to condense (during heating operation) or evaporate (during cooling operation and defrost operation). )do.
  • the heat exchanger 100 is a heat exchanger that exchanges heat between water and a refrigerant, and includes a first flow path 111 through which water flows and a second flow path 121 through which a refrigerant flows. Any of the members forming the first flow path 111 other than the partition wall 130 that separates the first flow path 111 and the second flow path 121 has a lower height than the other members forming the first flow path 111. It functions as a strong weak part 190.
  • the first flow path 111 that functions as the fragile portion 190 is formed before other parts. Then, any member other than the partition wall 130 separating the first flow path 111 and the second flow path 121 is broken. Therefore, according to the heat exchanger 100, when water freezes and expands in volume, the member forming the second flow path 121, the joint forming the second flow path 121, or the partition wall 130 breaks. Leakage of refrigerant is suppressed.
  • the refrigerant cycle device 1 it is assumed that water passing through the first flow path 111 freezes due to, for example, cooling operation, defrost operation, and a drop in temperature at the installation location of the refrigerant circuit 10.
  • the refrigerant passing through the second flow path 121 in the heat exchanger 100 evaporates and absorbs heat from the water passing through the first flow path 111 (cooling the water), so that the water freezes. There is a risk.
  • the air temperature at the location where the refrigerant circuit 10 is installed drops, the water may freeze because the heat exchanger 100 is cooled as the surrounding temperature drops.
  • a first flow path 111 is formed using two partition walls 130, a first inner fin 110, and a first spacing member 140.
  • the first inner fin 110 is stacked between two partition walls 130 and has a wave-shaped cross section.
  • the first spacing member 140 is disposed at the edge of the two partition walls 130 and separates the two partition walls 130 from each other.
  • the fragile portion 190 is the first inner fin 110.
  • the first inner fins 110 forming the first flow path 111 break before other parts, so the second flow path 121 This prevents the refrigerant from leaking due to breakage of the members and joints that form the refrigerant.
  • the thickness of the first inner fin 110 is tw
  • the interval between the tops 110t of the first inner fins 110 that are in contact with the same partition 130 is Lw
  • the thickness of the partition 130 is tR
  • the height of the first inner fin 110 in the stacking direction DS is hw
  • the stress generated in the partition wall 130 when water freezes and expands in volume is reduced to the first inner fin 110 when water freezes and expands in volume. It can be made smaller than the stress generated.
  • the force generated by the volumetric expansion can be absorbed by the first inner fins 110, which break before the partition walls 130, so that the members and joints forming the second flow path 121 break and the refrigerant leaks.
  • the fragile portion 190 is the first spacing member 140.
  • the first spacing member that forms the first flow path 111 is formed before other parts. Since the member 140 is broken, the leakage of the refrigerant due to the breakage of the members and joints forming the second flow path 121 is suppressed.
  • the width of the first spacing member 140 in a plan view is Lsp
  • the thickness of the first inner fin 110 is tw
  • the distance between the tops 110t of the first inner fins 110 that are in contact with the same partition 130 is Lw
  • the thickness of the partition 130 is tR
  • hw the height of the first inner fin 110 in the stacking direction
  • each part By forming the dimensions of each part to satisfy the above relationship, stress generated in the partition wall 130 when water freezes and expands in volume can be reduced to the first spacing member 140 when the water freezes and expands in volume. It can be made smaller than the stress generated. As a result, the force generated by the volumetric expansion can be absorbed by the first spacing member 140, which breaks before the partition wall 130, so that the members and joints forming the second flow path 121 break and the refrigerant leaks. It is restrained from doing so.
  • the member forming the first flow path 111 functions as the weakened portion 190, but the weakened portion 190 is any joint where the members forming the first flow path 111 are joined.
  • the fragile portion 190 may be the first joint portion 110c.
  • the fragile portion 190 may be the first joint portion 110c and the second joint portion 140c. In this case, it is preferable that the first joint portion 110c is first broken, and then the second joint portion 140c is formed, when the volume of water expands beyond a certain level.
  • the heat exchanger 100 is a heat exchanger that exchanges heat between water and a refrigerant, and includes a first flow path 111 through which water flows and a second flow path 121 through which the refrigerant flows.
  • the first joint part 110c or the second joint part 140c which is a joint part where members forming the first flow path 111 are joined, is a weak part having lower strength than other members forming the first flow path 111. Function.
  • the dimensions of each part forming the first flow path 111 satisfy the following relationship (Equation 3).
  • the width of the first joint portion 110c in plan view is assumed to be bw1. 0.35 ⁇ bw1/(2 ⁇ Lw) ⁇ tR/hw (Formula 3)
  • bw1 is, for example, 0.035 mm.
  • each part By forming the dimensions of each part to satisfy the above relationship, stress generated in the partition wall 130 when water freezes and expands in volume can be reduced to the first joint 110c when the water freezes and expands in volume. It can be made smaller than the stress generated. As a result, the force generated by the volumetric expansion can be absorbed by the first joint 110c, which breaks before the partition wall 130, so that the members and joints forming the second flow path 121 break and the refrigerant leaks. It is restrained from doing so.
  • the dimensions of each part forming the first flow path 111 satisfy the following relationship (Equation 4).
  • the width of the second joint portion 140c in plan view is assumed to be bsp2. 0.35 ⁇ (2 ⁇ bsp2+bw1)/Lw ⁇ 2 ⁇ tR/hw (Formula 4)
  • bsp2 is, for example, 0.1 mm.
  • each part By forming the dimensions of each part to satisfy the above relationship, stress generated in the partition wall 130 when water freezes and expands in volume can be reduced to the second joint 140c when the water freezes and expands in volume. It can be made smaller than the stress generated. As a result, the force generated by the volumetric expansion can be absorbed by the second joint 140c, which breaks before the partition wall 130, so that the members and joints forming the second flow path 121 break and the refrigerant leaks. It is restrained from doing so.
  • each part By forming the dimensions of each part to satisfy the above relationship, stress generated in the partition wall 130 when water freezes and expands in volume can be reduced to the first joint 110c when the water freezes and expands in volume. It can be made smaller than the stress generated. As a result, the force generated by the volumetric expansion can be absorbed by the first joint 110c, which breaks before the partition wall 130, so that the members and joints forming the second flow path 121 break and the refrigerant leaks. It is restrained from doing so.
  • each portion forming the first flow path 111 satisfy the following relationship (Equation 6). (2 ⁇ bsp2+bw1)/Lw ⁇ 2 ⁇ tR/hw (Formula 6)
  • each part By forming the dimensions of each part to satisfy the above relationship, stress generated in the partition wall 130 when water freezes and expands in volume can be reduced to the second joint 140c when the water freezes and expands in volume. It can be made smaller than the stress generated. As a result, the force generated by the volumetric expansion can be absorbed by the second joint 140c, which breaks before the partition wall 130, so that the members and joints forming the second flow path 121 break and the refrigerant leaks. It is restrained from doing so.
  • the refrigerant used was propane, but the refrigerant used is not limited to this, and is a well-known refrigerant such as HC, HFC (R410A, etc.), HCFC (R22, R32, etc.), natural refrigerant, etc. can be used.
  • the heat exchanger 100 even when a flammable or toxic refrigerant is used, it is possible to suppress leakage of the refrigerant due to breakage of the members and joints forming the second flow path 121.
  • the flammable refrigerant refers to a refrigerant classified as 2L or higher according to the American ANSI/ASHRAE34 standard.
  • Heat Exchanger A heat exchanger 200 according to a second embodiment of the present disclosure will be described.
  • the main difference between heat exchanger 100 and heat exchanger 200 is that heat exchanger 100 forms a flow path by laminating inner fins and partition walls, whereas heat exchanger 200 forms a flow path by laminating inner fins and partition walls.
  • heat transfer plates are stacked to form a flow path.
  • the refrigerant cycle device 1 can include a heat exchanger 200 instead of the heat exchanger 100.
  • the configuration and operation of the refrigerant cycle device 1 including the heat exchanger 200 are the same as those of the heat exchanger 100, so detailed explanations will be omitted.
  • the longitudinal direction DL, the width direction DW, and the stacking direction DS correspond to the directions indicated by arrows in each figure.
  • the back, front, top, bottom, left, and right directions used in the following description correspond to the directions shown by arrows in FIGS. 7 and 8.
  • the heat exchanger 200 includes a plurality of first heat transfer plates 210, a plurality of second heat transfer plates 220, a first frame 230, a second frame 240, and a first flow pipe 250a.
  • This is a heat exchanger including a first flow pipe 250b, a second flow pipe 260a, and a second flow pipe 260b.
  • the heat exchanger 200 is provided with a first flow path 211 and a second flow path 221 inside. Although details will be described later, the heat exchanger 200 has a fragile portion 290 that prevents the refrigerant flowing through the second flow path 221 from flowing into the first flow path 211 when the water freezes.
  • the first heat transfer plate 210 and the second heat transfer plate 220 are metal plate members having the same rectangular outer shape.
  • the first heat transfer plate 210 and the second heat transfer plate 220 have the same thickness.
  • the outer shapes of the first heat transfer plate 210, the second heat transfer plate 220, the first frame 230, and the second frame 240 are arranged in the first direction (longitudinal direction DL). It is formed into a long rectangle.
  • the plurality of first heat transfer plates 210 and the plurality of second heat transfer plates 220 are alternately stacked.
  • the number of each of the plurality of first heat transfer plates 210 and the plurality of second heat transfer plates 220 is not particularly limited, and is appropriately set according to the required performance.
  • First heat transfer plate 210 is a corrugated fin having a corrugated cross section.
  • the waveform of the first heat transfer plate 210 is formed such that the top portion 210t draws a convex herringbone pattern upward in plan view.
  • the first heat transfer plate 210 forms a first flow path 211 and a second flow path 221 together with a second heat transfer plate 220 stacked adjacent to each other.
  • the first heat transfer plate 210 has a first joint region 210a, two first communication holes 210b, two first through holes 210c, a first surface 210sa, and a second surface 210sb.
  • the first bonding region 210a is a region where the first heat transfer plate 210 and the second heat transfer plate 220 are bonded to each other.
  • the first bonding area 210a is a band-shaped area with an edge of a predetermined width bent toward the front side.
  • the first flow hole 210b is a hole that allows water to flow to the first flow path 211.
  • the first communication holes 210b are formed on the upper right side and the lower left side.
  • the first through hole 210c is a hole through which the refrigerant passes in the stacking direction DS.
  • the first through hole 210c is formed on the upper left side and the lower right side.
  • the first surface 210sa is the front surface of the first heat transfer plate 210.
  • the first surface 210sa is a surface that faces a second surface 220sb of the second heat transfer plate 220, which will be described later, when the first heat transfer plate 210 and the second heat transfer plate 220 are stacked.
  • the second surface 210sb is the back surface of the first heat transfer plate 210.
  • the second surface 210sb is a surface that faces a first surface 220sa of the second heat transfer plate 220, which will be described later, when the first heat transfer plate 210 and the second heat transfer plate 220 are stacked.
  • the first heat transfer plate 210 is formed using, for example, but not limited to, press working.
  • the "waveform" is not limited to a shape in which semicircular irregularities are periodically arranged as shown in FIG. It may be a shape that changes periodically. This also applies to the second heat transfer plate 220.
  • the second heat transfer plate 220 is a corrugated fin having a corrugated cross section.
  • the waveform of the second heat transfer plate 220 is formed such that the top portion 220t draws a downwardly convex herringbone pattern when viewed from above.
  • the second heat transfer plate 220 forms a first flow path 211 and a second flow path 221 together with the first heat transfer plate 210 stacked adjacent to each other.
  • the second heat transfer plate 220 has a second bonding area 220a, two second communication holes 220b, two second through holes 220c, a first surface 220sa, and a second surface 220sb.
  • the second bonding region 220a is a region where the first heat transfer plate 210 and the second heat transfer plate 220 are bonded to each other.
  • the second joining area 220a is a band-shaped area with an edge of a predetermined width bent toward the front side.
  • the second flow hole 220b is a hole that allows the refrigerant to flow to the second flow path 221.
  • the second communication hole 220b is formed on the upper right side and the lower left side.
  • the second communication hole 220b is formed at a position that overlaps and communicates with the first through hole 210c when the first heat transfer plate 210 and the second heat transfer plate 220 are stacked.
  • the size and shape of the second communication hole 220b are the same as the first through hole 210c.
  • the second through hole 220c is a hole that allows water to pass in the stacking direction DS.
  • the second through hole 220c is formed on the upper left side and the lower right side.
  • the second through hole 220c is formed at a position that overlaps and communicates with the first communication hole 210b when the first heat transfer plate 210 and the second heat transfer plate 220 are stacked.
  • the size and shape of the second through hole 220c are the same as the first communication hole 210b.
  • the first surface 220sa is the front surface of the second heat transfer plate 220.
  • the first surface 220sa is a surface that faces the second surface 210sb of the first heat transfer plate 210 when the first heat transfer plate 210 and the second heat transfer plate 220 are stacked.
  • the second surface 220sb is the back surface of the second heat transfer plate 220.
  • the second surface 220sb is a surface that faces the first surface 210sa of the first heat transfer plate 210 when the first heat transfer plate 210 and the second heat transfer plate 220 are stacked.
  • the second heat transfer plate 220 is formed using, for example, but not limited to, press working.
  • First frame 230 and second frame 240 are metal plate-like members that sandwich the plurality of first heat transfer plates 210 and the plurality of second heat transfer plates 220, which are stacked alternately, at both ends in the stacking direction DS. be.
  • the first flow pipe 250a is a pipe that allows water to flow through the first flow path 211.
  • the first flow pipe 250a is provided to pass through the upper left side of the first frame 230 and communicate with the first flow path 211. More specifically, the first flow pipe 250a is a first flow hole formed on the upper left side that communicates with each other when the first heat transfer plate 210, the second heat transfer plate 220, and the first frame 230 are stacked. 210b and the second through hole 220c.
  • the first flow pipe 250b is a pipe that allows water to flow through the first flow path 211.
  • the first flow pipe 250a is provided to penetrate the lower right side of the first frame 230 and communicate with the first flow path 211. More specifically, the first flow pipe 250a is a first flow hole formed on the lower right side that communicates with each other when the first heat transfer plate 210, the second heat transfer plate 220, and the first frame 230 are stacked. 210b and the second through hole 220c.
  • first flow pipe 250a corresponds to the first flow pipe 170a of the heat exchanger 100.
  • the first flow pipe 250b corresponds to the first flow pipe 170b of the heat exchanger 100.
  • Second flow pipe 260a and second flow pipe 260b The second flow pipe 260a is a pipe that allows the refrigerant to flow through the second flow path 221.
  • the second flow pipe 260a is provided to pass through the upper right side of the first frame 230 and communicate with the second flow path 221. More specifically, the second flow pipe 260a is a second flow hole formed on the upper right side that communicates with each other when the first heat transfer plate 210, the second heat transfer plate 220, and the first frame 230 are stacked. 220b and the first through hole 210c.
  • the second flow pipe 260b is a pipe that allows the refrigerant to flow through the second flow path 221.
  • the second flow pipe 260a is provided to penetrate the lower left side of the first frame 230 and communicate with the second flow path 221. More specifically, the second flow pipe 260a is a second flow hole formed on the lower left side that communicates with each other when the first heat transfer plate 210, the second heat transfer plate 220, and the first frame 230 are stacked. 220b and the first through hole 210c.
  • the second flow pipe 260a corresponds to the second flow pipe 180a of the heat exchanger 100.
  • the second flow pipe 260b corresponds to the second flow pipe 180b of the heat exchanger 100.
  • first flow channels 211 and second flow channels 221 are alternately formed in the stacking direction DS. More specifically, the first heat transfer plate 210 and the second heat transfer plate 220 are stacked alternately, so that the first surface 210sa of the first heat transfer plate 210 and the second surface of the second heat transfer plate 220 are stacked alternately. The space where 220sb faces becomes the first flow path 211.
  • the second surface 210sb of the first heat transfer plate 210 and the first surface 220sa of the second heat transfer plate 220 are The opposing space becomes the first flow path 211.
  • first flow path 211 corresponds to the first flow path 111 of the heat exchanger 100.
  • the second flow path 221 corresponds to the second flow path 121 of the heat exchanger 100.
  • the first heat transfer plate 210 and the second heat transfer plate 220 are joined by brazing. More specifically, in the first heat transfer plate 210 and the second heat transfer plate 220, the first bonding area 210a and the second bonding area 220a are bonded to each other by brazing, and the first heat transfer plate 210 is The top portion 210t and the top portion 220t of the second heat transfer plate 220 are joined to each other by brazing.
  • the portion where the first surface 210sa side of the top portion 210t of the first heat transfer plate 210 and the second surface 220sb side of the top portion 220t of the second heat transfer plate 220 are joined will be referred to as a third joint portion 210d.
  • a portion where the first surface 210sa side of the first bonding region 210a and the second surface 220sb side of the second bonding region 220a are bonded is called a fourth bonding portion 210e.
  • the heat exchanger 200 has a weak portion 290 that has lower strength than other parts and breaks when water freezes and expands in volume.
  • the fragile portion 290 is any joint where members forming the first flow path 211 are joined.
  • the third joint portion 210d and the fourth joint portion 210e function as the fragile portion 290.
  • the third bonding portion 210d and the fourth bonding portion 210e are arranged such that when the water expands in volume beyond a certain level, the third bonding portion 210d breaks first, and then the fourth bonding portion 210e breaks. Preferably, it is formed.
  • the dimensions of each part forming the first flow path 211 satisfy the following relationship (Equation 7).
  • the width of the third joint portion 210d viewed along the normal direction is bw3
  • the thickness of the first heat transfer plate 210 and the second heat transfer plate is t. 0.35 ⁇ bw3 ⁇ 2 ⁇ t...(Formula 7)
  • bw3 is, for example, 1 mm.
  • t is 2 mm.
  • the dimensions of each part forming the first flow path 211 satisfy the following relationship (Equation 8).
  • the width of the fourth joint portion 210e viewed along the normal direction is assumed to be bsp4. 0.35 ⁇ (bsp4+bw3/2) ⁇ 2 ⁇ t...(Formula 8)
  • bsp4 is, for example, 1 mm.
  • the water that has flowed into the first flow path 211 flows through the first flow path 211 toward the upper first flow hole 210b.
  • the water that has reached the first flow hole 210b on the upper side passes through the second through hole 220c on the upper side and is led out from the first flow pipe 250a.
  • the water flowing through the first flow path 211 exchanges heat with the refrigerant in the adjacent second flow path 221 via the first heat transfer plate 210 or the second heat transfer plate 220.
  • the refrigerant introduced from the second flow pipe 260a of the heat exchanger 200 passes through the upper first through hole 210c and the second flow hole 220b and flows into the second flow path 221.
  • the refrigerant that has entered the second flow path 221 flows through the second flow path 221 toward the second flow hole 220b on the lower side.
  • the refrigerant that has reached the second flow hole 220b on the lower side passes through the first through hole 210c on the lower side and is led out from the second flow pipe 260b.
  • the refrigerant introduced from the second flow pipe 260b of the heat exchanger 200 flows into the second flow path 221 through the first through hole 210c and the second flow hole 220b on the lower side.
  • the refrigerant that has entered the second flow path 221 flows through the second flow path 221 toward the upper second circulation hole 220b.
  • the refrigerant that has reached the upper second circulation hole 220b passes through the upper first through hole 210c and is led out from the second circulation pipe 260a.
  • the water flowing through the second flow path 221 exchanges heat with the water in the adjacent first flow path 211 via the first heat transfer plate 210 or the second heat transfer plate 220 to condense (heating operation ) or evaporates (during cooling and defrosting operations).
  • the first flow path 211 includes a first heat transfer plate 210, a second heat transfer plate 220, a third joint portion 210d, and a fourth joint portion 210e.
  • the first heat transfer plate 210 and the second heat transfer plate 220 are stacked on each other.
  • Each of the first heat transfer plate 210 and the second heat transfer plate 220 has a wave-shaped cross section.
  • the third joint is a place where the top portions 210t and 220t of the first heat transfer plate 210 and the second heat transfer plate 220 are bonded.
  • the fourth joint portion 210e is a portion where the edges of the first heat transfer plate 210 and the second heat transfer plate 220 are joined.
  • the weak portion 290 is the third joint portion 210d.
  • the third joint 210d where the members forming the first flow path 211 are joined breaks before other parts. , the leakage of the refrigerant due to breakage of the members and joints forming the second flow path 221 is suppressed.
  • the third joint portion 210d is joined by brazing. Assuming that the width of the third joint portion 210d viewed along the normal direction is bw3, and the thickness of the first heat transfer plate 210 and the second heat transfer plate 220 is t, these satisfy the following relationship. 0.35 ⁇ bw3 ⁇ 2 ⁇ t...(Formula 7)
  • the stress that occurs in the first heat transfer plate 210 and the second heat transfer plate 220 when water freezes and expands in volume can be reduced by freezing and expanding the volume.
  • the stress can be made smaller than the stress generated in the third joint portion 210d when it expands.
  • the force generated by the volumetric expansion can be absorbed by the third joint portion 210d, which breaks before the first heat transfer plate 210 and the second heat transfer plate 220, so that the second flow path 221 is formed. This prevents refrigerant from leaking due to breakage of members or joints.
  • the fragile portion 290 is the fourth joint portion 210e.
  • the fourth joint 210e when water freezes and expands in volume, the fourth joint 210e, where the members forming the first flow path 211 are joined, breaks before other parts. , the leakage of the refrigerant due to breakage of the members and joints forming the second flow path 221 is suppressed.
  • the fourth joint portion 210e is joined by brazing.
  • the width of the fourth joint 210e as seen along the normal direction is bsp4
  • the width of the third joint as seen along the normal direction is bw3
  • the thickness of the first heat transfer plate 210 and the second heat transfer plate 220 is When the thickness is t, these satisfy the following relationship. 0.35 ⁇ (bsp4+bw3/2) ⁇ 2 ⁇ t...(Formula 8)
  • the stress that occurs in the first heat transfer plate 210 and the second heat transfer plate 220 when water freezes and expands in volume can be reduced by freezing and expanding the volume.
  • the stress can be made smaller than the stress generated in the fourth joint portion 210e when it expands.
  • the force generated by the volumetric expansion can be absorbed by the fourth joint 210e, which breaks before the first heat transfer plate 210 and the second heat transfer plate 220, so that the second flow path 221 is formed. This prevents the refrigerant from leaking due to breakage of members or joints.
  • the part when water freezes and causes volumetric expansion, the part functions as the fragile part 290 before other parts.
  • the third joint portion 210d or the fourth joint portion 210e is broken. Therefore, according to the heat exchanger 200 according to Modification Example 2B, when water freezes and expands in volume, the members and joints forming the second flow path 221 are prevented from breaking and the refrigerant is prevented from leaking. be done.
  • the stress that occurs in the first heat transfer plate 210 and the second heat transfer plate 220 when water freezes and expands in volume can be reduced by freezing and expanding the volume. This can be made smaller than the stress generated in the third joint portion 210d when it expands. As a result, the force generated by the volumetric expansion can be absorbed by the third joint portion 210d, which breaks before the first heat transfer plate 210 and the second heat transfer plate 220, so that the second flow path 221 is formed. This prevents the refrigerant from leaking due to breakage of members or joints.
  • each part forming the first flow path 211 satisfy the following relationship (Equation 10). (bsp4+bw3/2) ⁇ 2 ⁇ t...(Formula 10)
  • the stress that occurs in the first heat transfer plate 210 and the second heat transfer plate 220 when water freezes and expands in volume can be reduced by freezing and expanding the volume.
  • the stress can be made smaller than the stress generated in the fourth joint portion 210e when it expands.
  • the force generated by the volumetric expansion can be absorbed by the fourth joint 210e, which breaks before the first heat transfer plate 210 and the second heat transfer plate 220, so that the second flow path 221 is formed. This prevents the refrigerant from leaking due to breakage of members or joints.
  • Heat Exchanger A heat exchanger 300 according to a third embodiment of the present disclosure will be described.
  • the main difference between heat exchanger 100 and heat exchanger 300 is that heat exchanger 100 forms a flow path by laminating inner fins and partition walls, whereas heat exchanger 300 forms a flow path by laminating inner fins and partition walls.
  • the point is that heat transfer plates are stacked to form a flow path.
  • the refrigerant cycle device 1 can include a heat exchanger 300 instead of the heat exchanger 100.
  • the configuration and operation of the refrigerant cycle device 1 including the heat exchanger 300 are the same as those of the heat exchanger 100, so detailed description thereof will be omitted.
  • the longitudinal direction DL, the width direction DW, and the stacking direction DS correspond to the directions indicated by arrows in each figure.
  • the back, front, top, bottom, left, and right directions used in the following description correspond to the directions shown by arrows in FIGS. 9 and 10. Note that features similar to or corresponding to those in the first embodiment are given the same reference numerals, and description thereof will be omitted as appropriate.
  • the heat exchanger 300 includes a plurality of first heat transfer plates 310, a plurality of second heat transfer plates 320, a casing 160, a first flow pipe 170a, and a first flow pipe 170b. , a second flow pipe 180a, and a second flow pipe 180b.
  • the heat exchanger 300 includes a first heat transfer plate instead of the first inner fin 110, second inner fin 120, partition wall 130, first spacing member 140, and second spacing member 150 of the heat exchanger 100. 310 and a second heat transfer plate 320.
  • the heat exchanger 300 has a first flow path 311 through which water flows and a second flow path 321 through which a refrigerant flows. Although details will be described later, the heat exchanger 300 has a weakened portion 390 that prevents the refrigerant flowing through the second flow path 321 from flowing into the first flow path 311 when the water freezes.
  • the first heat transfer plate 310 and the second heat transfer plate 320 are metal plate members having the same rectangular outer shape. In the present embodiment, as shown in FIGS. 9 and 10, the first heat transfer plate 310 and the second heat transfer plate 320 are the It is formed in a rectangular shape that is long in one direction (longitudinal direction DL).
  • the first heat transfer plates 310 and the second heat transfer plates 320 are alternately stacked along the stacking direction DS and housed in the casing 160.
  • the number of each of the first heat transfer plates 310 and the second heat transfer plates 320 is not particularly limited, and is appropriately set according to the required performance.
  • the first heat transfer plate 310 is a plate-like member in which a plurality of first channels 311 are formed.
  • the first flow path 311 is formed to extend along the longitudinal direction DL in plan view.
  • the plurality of first flow paths 311 are formed side by side at predetermined intervals in the width direction DW.
  • the first flow path 311 has a rectangular cross-sectional shape cut along a plane perpendicular to the direction in which water flows.
  • the first flow path 311 is formed using etching, for example, but not limited thereto.
  • the first heat transfer plate 310 is formed by laminating a plate member 310a and a plate member 310b in the stacking direction DS. Grooves 311a and 311b, which face each other to form the first flow path 311 when stacked, are formed in the plate members 310a and 310b by etching.
  • the plate-like member 310a and the plate-like member 310b are joined by brazing.
  • a fifth joint portion 310c the portion where the plate-like member 310a and the plate-like member 310b are joined, and which is located between the adjacent first channels 311 in plan view, will be referred to as a fifth joint portion 310c.
  • the first flow path 311 is formed at the end of the first heat transfer plate 310 in the width direction DW and closest to this end, where the plate-like member 310a and the plate-like member 310b are joined.
  • the portion located between the two is called the sixth joint portion 310d.
  • the fifth joint 310c and the sixth joint 310d are examples of joints.
  • first flow path 311 corresponds to the first flow path 111 of the heat exchanger 100.
  • the second heat transfer plate 320 is a plate-like member in which a plurality of second channels 321 are formed.
  • the second flow path 321 is formed to extend along the width direction DW in plan view.
  • the plurality of second flow paths 321 are formed side by side at predetermined intervals in the longitudinal direction DL.
  • the second flow path 321 is formed using etching, for example, but not limited thereto.
  • the second flow path 321 corresponds to the second flow path 121 of the heat exchanger 100.
  • the heat exchanger 300 has a weak portion 390 that has lower strength than other parts and breaks when water freezes and expands in volume.
  • the first heat transfer plate 310 which is a member forming the first flow path 311, functions as the weakened portion 390.
  • the dimensions of each part of the first heat transfer plate 310 satisfy the following relationship (Equation 11).
  • the interval in the width direction DW of the first passage 311 formed in the first heat transfer plate 310 is tw3
  • the sum of the interval tw3 and the width in the width direction DW of the first passage 311 is Lw3
  • the stacking direction DS Let the interval between the first flow path 311 and the second flow path 321 be tR3, and the height of the first flow path 311 in the stacking direction DS be hw3.
  • tw3 is, for example, 0.15 mm.
  • Lw3 is, for example, 2 mm.
  • tR3 is, for example, 0.15 mm.
  • hw3 is, for example, 1 mm.
  • the dimensions of each part forming the first heat transfer plate 310 further satisfy the following relationship (Equation 12).
  • the distance in the width direction DW between the end of the first heat transfer plate 310 in the width direction DW and the first flow path 311 formed closest to this end is defined as Lsp3. ((Lsp3+tw3/2)/Lw3) ⁇ tR3/hw3...(Formula 12)
  • Lsp3 is, for example, 0.1 mm.
  • Heat exchanger 300 includes a first heat transfer plate 310 and a second heat transfer plate 320.
  • the first heat transfer plate 310 has a first flow path 311 formed therein.
  • the second heat transfer plate 320 has a second flow path 321 formed therein.
  • the weakened part 390 is the first heat transfer plate 310.
  • the first heat transfer plate 310 that forms the first flow path 311 breaks before other parts, so the second flow path This prevents the second heat transfer plate 320 forming the second heat transfer plate 321 from breaking and leaking the refrigerant.
  • the member forming the first flow path 311 functions as the weakened portion 390, but the weakened portion 390 may be a portion where the members forming the first flow path 311 are joined together.
  • the fragile portion 390 may be the fifth joint portion 310c.
  • the fragile portion 190 may be the fifth joint portion 310c and the sixth joint portion 310d. In this case, it is preferable that the fifth bonding portion 310c is first broken, and then the sixth bonding portion 310d is formed, when the volume of water expands beyond a certain level.
  • the heat exchanger 300 according to modification example 3A when water freezes and causes volumetric expansion, the fifth joint 310c or the sixth joint 310d, which functions as the fragile portion 390, breaks before other parts. do. Therefore, according to the heat exchanger 300 according to Modification Example 3A, when water freezes and expands in volume, the member (second heat transfer plate 320) forming the second flow path 321 breaks and the refrigerant flows out. Leakage is suppressed.
  • the dimensions of each part of the first heat transfer plate 310 forming the first flow path 311 satisfy the following relationship (Equation 13).
  • the width of the fifth joint portion 310c in plan view is assumed to be bw5. 0.35 ⁇ bw5/(2 ⁇ Lw3) ⁇ tR3/hw3 (Formula 13)
  • bw5 is, for example, 0.035 mm.
  • each part of the first heat transfer plate 310 By forming the dimensions of each part of the first heat transfer plate 310 to satisfy the above relationship, when water freezes and expands in volume, a phenomenon occurs between the first flow path 311 and the second flow path 321.
  • the stress can be made smaller than the stress generated in the fifth joint 310c when water freezes and expands in volume.
  • the force generated by the volumetric expansion can be absorbed by the fifth joint 310c, which breaks earlier than between the first flow path 311 and the second flow path 321, so that the second flow path 321 is formed. This prevents the refrigerant from leaking due to breakage of the member.
  • the dimensions of each part of the first heat transfer plate 310 forming the first flow path 311 satisfy the following relationship (Equation 14).
  • the width of the sixth joint portion 310d in plan view is assumed to be bsp6. 0.35 ⁇ (2 ⁇ bsp6+bw5)/Lw3 ⁇ 2 ⁇ tR3/hw3 (Formula 14)
  • bsp6 is, for example, 0.1 mm.
  • each part of the first heat transfer plate 310 By forming the dimensions of each part of the first heat transfer plate 310 to satisfy the above relationship, when water freezes and expands in volume, a phenomenon occurs between the first flow path 311 and the second flow path 321.
  • the stress can be made smaller than the stress that occurs in the sixth joint 310d when water freezes and expands in volume.
  • the force generated by the volumetric expansion can be absorbed by the sixth joint 310d, which breaks earlier than between the first flow path 311 and the second flow path 321, so that the second flow path 321 is formed. This prevents the member (second heat transfer plate 320) from breaking and leaking the refrigerant.
  • the first heat transfer plate 310 is formed by laminating two plate-like members 310a and 310b in which grooves 311a and 312b forming the first flow path 311 are formed.
  • the weak portion 390 is a portion where the two plate-like members 310a and 310b are joined.
  • the heat exchanger 300 when water freezes and expands in volume, the area where the two plate-like members 310a and 310b forming the first heat transfer plate 310 are joined ( Since the fifth joint portion 310c and the sixth joint portion 310d are fractured, the second heat transfer plate 320 forming the second flow path is prevented from being fractured and the refrigerant is prevented from leaking.
  • the heat exchanger 300 according to the modification example 3B in which the fifth joint part 310c and the sixth joint part 310d are joined by diffusion bonding, water freezes and causes volumetric expansion, similarly to the heat exchanger 300 according to the modification example 3A.
  • the fifth joint portion 310c or the sixth joint portion 310d which functions as the fragile portion 390, breaks before the breakage occurs between the first flow path 311 and the second flow path 321. Therefore, according to the heat exchanger 300 according to Modification Example 3B, when water freezes and expands in volume, the member (second heat transfer plate 320) forming the second flow path 321 breaks, and the refrigerant flows out. Leakage is suppressed.
  • each part of the first heat transfer plate 310 forming the first flow path 311 satisfy the following relationship (Equation 15). bw5/(2 ⁇ Lw3) ⁇ tR3/hw3 (Formula 15)
  • the stress generated between the first flow path 311 and the second flow path 321 when the water freezes and expands in volume can be absorbed by the water.
  • the stress can be made smaller than the stress generated in the fifth joint portion 310c when volumetric expansion occurs.
  • the force generated by the volumetric expansion can be absorbed by the fifth joint 310c, which breaks earlier than between the first flow path 311 and the second flow path 321, so that the second flow path 321 is formed. This prevents the refrigerant from leaking due to breakage of the connecting parts and joints.
  • each portion of the first heat transfer plate 310 forming the first flow path 111 satisfy the following relationship (Equation 16). (2 ⁇ bsp6+bw5)/Lw3 ⁇ 2 ⁇ tR3/hw3 (Formula 16)
  • the stress generated between the first flow path 311 and the second flow path 321 when the water freezes and expands in volume can be absorbed by the water.
  • the stress can be made smaller than the stress generated in the sixth joint portion 310d when the volume expands.
  • the force generated by the volumetric expansion can be absorbed by the sixth joint 310d, which breaks earlier than between the first flow path 311 and the second flow path 321, so that the second flow path 321 is formed. This prevents the refrigerant from leaking due to breakage of the connecting parts and joints.
  • Refrigerant cycle device 100, 200, 300 Heat exchanger 110 First inner fin 110c First joint 110t Top 111, 211, 311 First flow path 130 Partition 140 Spacing member 140c Second joint 210, 310 First heat transfer Plate 210d Third joint 210e Fourth joint 220, 320 Second heat transfer plate 121, 221, 321 Second flow path 190, 290, 390 Weak portion 310a, 310b Plate member 310c Fifth joint 310d Sixth joint Part 311a, 311b Groove

Landscapes

  • 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 qui empêche toute fuite de fluide frigorigène lorsque l'eau gèle et que le volume augmente. L'échangeur de chaleur (100) échange la chaleur entre l'eau et un fluide frigorigène. L'échangeur de chaleur (100) comprend : une première voie d'écoulement (111) à travers laquelle circule l'eau ; et une seconde voie d'écoulement (121) à travers laquelle circule le fluide frigorigène. Les éléments formant la première voie d'écoulement (111), ou les parties au niveau desquelles les éléments formant la première voie d'écoulement (111) sont assemblés, fonctionnent chacun comme une partie fragile (190) dont la résistance est inférieure à celle des autres parties. Dans l'échangeur de chaleur (100), lorsque l'eau gèle et que le volume augmente, les éléments formant la première voie d'écoulement (111) ou les parties au niveau desquelles les éléments formant la première voie d'écoulement (111) sont assemblés, jouent le rôle de partie fragile (190) se rompant plus tôt que les autres parties. Par conséquent, dans l'échangeur de chaleur (100), lorsque l'eau gèle et que le volume augmente, la fuite du fluide frigorigène causée par la rupture d'un élément formant la seconde voie d'écoulement (121) ou d'une partie de raccordement est évitée.
PCT/JP2023/026469 2022-07-19 2023-07-19 Échangeur de chaleur WO2024019095A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2022114817 2022-07-19
JP2022-114817 2022-07-19

Publications (1)

Publication Number Publication Date
WO2024019095A1 true WO2024019095A1 (fr) 2024-01-25

Family

ID=89617833

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2023/026469 WO2024019095A1 (fr) 2022-07-19 2023-07-19 Échangeur de chaleur

Country Status (2)

Country Link
JP (2) JP7454733B2 (fr)
WO (1) WO2024019095A1 (fr)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03500861A (ja) * 1987-03-20 1991-02-28 ケルンフオルシユングスツエントルム、カールスルーエ、ゲゼルシヤフト、ミツト、ベシユレンクテル、ハフツング 微細構造体の製造方法
JP2003294380A (ja) * 2002-03-29 2003-10-15 Hisaka Works Ltd 熱交換器
JP2005061778A (ja) * 2003-08-19 2005-03-10 Calsonic Kansei Corp 蒸発器
WO2019176566A1 (fr) * 2018-03-15 2019-09-19 三菱電機株式会社 Échangeur de chaleur de type plaque, dispositif de pompe à chaleur comprenant un échangeur de chaleur de type plaque et système d'alimentation en eau chaude de chauffage/refroidissement de type pompe à chaleur comprenant un dispositif de pompe à chaleur
WO2020245876A1 (fr) * 2019-06-03 2020-12-10 三菱電機株式会社 Échangeur de chaleur du type à plaques et dispositif de transfert de chaleur
CN113432461A (zh) * 2021-05-13 2021-09-24 江苏远卓设备制造有限公司 用于板式换热器的换热片组以及板式换热器

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005177921A (ja) 2003-12-19 2005-07-07 Zexel Valeo Climate Control Corp チューブの製造方法、熱交換チューブ、及び熱交換器
JP6843012B2 (ja) 2017-07-14 2021-03-17 株式会社日本クライメイトシステムズ 熱交換器用チューブ

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03500861A (ja) * 1987-03-20 1991-02-28 ケルンフオルシユングスツエントルム、カールスルーエ、ゲゼルシヤフト、ミツト、ベシユレンクテル、ハフツング 微細構造体の製造方法
JP2003294380A (ja) * 2002-03-29 2003-10-15 Hisaka Works Ltd 熱交換器
JP2005061778A (ja) * 2003-08-19 2005-03-10 Calsonic Kansei Corp 蒸発器
WO2019176566A1 (fr) * 2018-03-15 2019-09-19 三菱電機株式会社 Échangeur de chaleur de type plaque, dispositif de pompe à chaleur comprenant un échangeur de chaleur de type plaque et système d'alimentation en eau chaude de chauffage/refroidissement de type pompe à chaleur comprenant un dispositif de pompe à chaleur
WO2020245876A1 (fr) * 2019-06-03 2020-12-10 三菱電機株式会社 Échangeur de chaleur du type à plaques et dispositif de transfert de chaleur
CN113432461A (zh) * 2021-05-13 2021-09-24 江苏远卓设备制造有限公司 用于板式换热器的换热片组以及板式换热器

Also Published As

Publication number Publication date
JP2024036686A (ja) 2024-03-15
JP2024013229A (ja) 2024-01-31
JP7454733B2 (ja) 2024-03-22

Similar Documents

Publication Publication Date Title
JP6012857B2 (ja) 積層型ヘッダー、熱交換器、及び、空気調和装置
US6308527B1 (en) Refrigerant evaporator with condensed water drain structure
JP6005267B2 (ja) 積層型ヘッダー、熱交換器、及び、空気調和装置
US20130292098A1 (en) Heat exchanger and air conditioner
WO2014184912A1 (fr) Collecteur stratifié, échangeur thermique, et climatiseur
JP5859022B2 (ja) プレート式熱交換器およびこの熱交換器を備えた冷凍サイクル装置
US9546823B2 (en) Heat exchanger, method of manufacturing same, and refrigeration cycle apparatus
WO2013015186A1 (fr) Appareil échangeur de chaleur
JP6767637B2 (ja) 熱交換器およびそれを用いた冷凍システム
JP6767620B2 (ja) 熱交換器およびそれを用いた冷凍システム
WO2022166236A1 (fr) Échangeur de chaleur, boîtier de commande électrique et système de climatisation
EP3060868A2 (fr) Échangeur de chaleur et plaque latérale
WO2014184918A1 (fr) Colonne stratifiée, échangeur de chaleur, et climatiseur
JP2018066536A (ja) 熱交換器およびそれを用いた冷凍システム
WO2024019095A1 (fr) Échangeur de chaleur
JP2004069228A (ja) 熱交換器
JP2024036686A5 (fr)
JP3658677B2 (ja) プレート式熱交換器および冷凍システム
JP2004325023A (ja) 冷凍装置
JP3423981B2 (ja) 熱交換器および冷凍空調装置
CN113874674B (zh) 板式热交换器以及导热装置
JP7301224B2 (ja) プレート式熱交換器、冷凍サイクル装置および伝熱装置
JP5490160B2 (ja) 加熱器及び冷凍サイクル装置
EP4080150A1 (fr) Échangeur de chaleur, unité d'échange de chaleur, et dispositif à cycle frigorifique
WO2021234954A1 (fr) Échangeur de chaleur, unité extérieure et dispositif à cycle de réfrigération

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 23843018

Country of ref document: EP

Kind code of ref document: A1