WO2012043380A1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

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Publication number
WO2012043380A1
WO2012043380A1 PCT/JP2011/071619 JP2011071619W WO2012043380A1 WO 2012043380 A1 WO2012043380 A1 WO 2012043380A1 JP 2011071619 W JP2011071619 W JP 2011071619W WO 2012043380 A1 WO2012043380 A1 WO 2012043380A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
heat transfer
transfer tube
water
longitudinal direction
Prior art date
Application number
PCT/JP2011/071619
Other languages
English (en)
Japanese (ja)
Inventor
宏二 和田
研介 遠藤
Original Assignee
東芝キヤリア株式会社
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 東芝キヤリア株式会社 filed Critical 東芝キヤリア株式会社
Priority to JP2012536393A priority Critical patent/JP5531103B2/ja
Publication of WO2012043380A1 publication Critical patent/WO2012043380A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag

Definitions

  • Embodiments of the present invention relate to a heat exchanger that performs heat exchange between a refrigerant and a heat medium such as water.
  • a water heat exchanger used for hot water supply has a heat transfer tube through which a refrigerant flows and a water heat transfer tube through which water flows are brought into direct contact with each other by brazing, or a heat transfer tube for refrigerant is installed inside the water heat transfer tube. It was inserted to promote heat transfer and exchange heat.
  • This type of technology is disclosed in, for example, Japanese Patent Application Laid-Open No. 2006-317115.
  • the present invention has an object to provide a water heat exchanger that improves heat transfer efficiency, improves manufacturing, reduces costs, and has good space efficiency.
  • a fin group includes a plurality of fins that are long in one direction, and the plurality of fins are stacked with a gap therebetween in a posture in which the longitudinal directions are aligned with each other.
  • the refrigerant heat transfer tube penetrates the fins in the laminating direction of the fins and is formed in a meandering shape in the longitudinal direction of the fins, and the refrigerant flows inside.
  • the heat transfer tube for heat medium passes through the fins in the stacking direction of the fins, is adjacent to the heat transfer tube for refrigerant, and is formed in a meandering shape in the longitudinal direction of the fins, and the water flows inside.
  • the refrigerant heat transfer tubes are installed in both side rows of the heat transfer tube along the row direction intersecting the longitudinal direction.
  • FIG. 3 is a cross-sectional view of the heat exchanger shown along line F6-F6 shown in FIG.
  • FIG. 9 is a cross-sectional view showing a state in which the refrigerant bend pipe is cut along the line F9-F9 shown in FIG.
  • the graph which shows the temperature of the refrigerant
  • FIG. 13 is a cross-sectional view showing a state in which the refrigerant bend pipe is cut along the line F13-F13 shown in FIG.
  • FIG. 1 is a schematic view schematically showing a heat pump type hot water supply apparatus 10 in which the heat exchanger 3 of the present embodiment is used.
  • the heat exchanger 3 is used for the hot water supply apparatus 10 as an example.
  • the heat exchanger 3 is not limited to being used in the hot water supply device 10.
  • the hot water supply device 10 includes a compressor 1, a heat exchanger 3, an internal heat exchanger 4, an expansion valve 5, an air heat exchanger 6, a water supply pipe unit 8, and a pump 9. And a hot water storage tank 12.
  • the compressor 1, the heat exchanger 3, the internal heat exchanger 4, the expansion valve 5, and the air heat exchanger 6 are sequentially connected via the refrigerant pipe portion 2 to constitute a refrigeration cycle 11.
  • the refrigeration cycle 11 uses carbon dioxide (CO2) as an example of a refrigerant.
  • the water supply pipe section 8 is provided in the heat exchanger 3.
  • the pump 9 is provided on one end side of the water supply pipe portion 8.
  • the hot water storage tank 12 is provided on the other end side of the water supply pipe portion 8.
  • Water W as a heat medium flows through the water supply pipe portion 8 by the pump 9.
  • the water W is stored in the hot water storage tank 12 after undergoing heat exchange through the heat exchanger 3 when passing through the water supply pipe section 8.
  • the structure of the heat exchanger 3 will be described later in detail.
  • the high-temperature and high-pressure gaseous refrigerant L discharged from the compressor 1 flows into the heat exchanger 3.
  • the refrigerant L exchanges heat with water flowing in the water supply pipe section 8 in the process of flowing in the heat exchanger 3.
  • the refrigerant L that has exited the heat exchanger 3 is in a liquid state because its temperature has decreased due to heat exchange with the water W. This refrigerant L then flows into the internal heat exchanger 4. In the process of flowing through the internal heat exchanger 4, the refrigerant L is heat-exchanged with the refrigerant L that has come out of the air heat exchanger 6 described later, and the temperature further decreases.
  • the refrigerant L exiting the internal heat exchanger 4 reaches the expansion valve 5.
  • the refrigerant L is decompressed by the expansion valve 5 and then flows into the air heat exchanger 6 to evaporate into a gaseous state.
  • the refrigerant exiting the air heat exchanger 6 flows into the internal heat exchanger 4.
  • the refrigerant that has flowed into the internal heat exchanger 4 is heated by being exchanged with the refrigerant that has exited the heat exchanger 3.
  • the refrigerant that has exited the internal heat exchanger 4 is sucked into the compressor 1.
  • the temperature of the water W supplied to the water supply pipe section 8 is increased by the above operation.
  • the water W whose temperature has risen in the heat exchanger 3 is stored in the hot water storage tank 12.
  • FIG. 2 is a perspective view showing a state in which a refrigerant bend pipe 32 and a water bend pipe 42 described later are removed from the heat exchanger 3.
  • a heat insulating material 50 described later is indicated by a two-dot chain line.
  • FIG. 3 is a front view showing the heat exchanger 3 viewed from the direction F3 shown in FIG.
  • FIG. 3 shows a state in which the refrigerant bend pipe 32 and the water bend pipe 42 are removed from the heat exchanger 3.
  • the heat exchanger 3 includes a fin group 20, a refrigerant heat transfer tube 30, a water heat transfer tube 40, and a heat insulating material 50.
  • the fin group 20 includes a plurality of plate fins 21.
  • the plate fin 21 is an example of a fin.
  • the plate fins 21 may all have the same structure.
  • the plate fins 21 are plate members that are long in one direction, and are rectangular as an example.
  • the plate fin 21 is formed of an aluminum material as an example.
  • the plate fin 21 is not limited to an aluminum material, and may be formed of, for example, copper, and is preferably formed of a material having good heat conductivity.
  • the longitudinal direction of the plate fin 21 is indicated by an arrow X.
  • a direction orthogonal to the longitudinal direction X is defined as a width direction Y.
  • the width direction Y is an example of a column direction.
  • Each plate fin 21 is laminated
  • the plate fins 21 have the same posture in the stacking direction, and have the longitudinal direction X aligned and the width direction Y aligned.
  • the refrigerant heat transfer tube 30 constitutes a part of the refrigerant tube portion 2, and the refrigerant flows inside.
  • the refrigerant heat transfer tube 30 is connected to the compressor 1 through, for example, a tube member 2a, and is connected to the internal heat exchanger 4 through, for example, a tube member 2b.
  • These pipe members 2 a and 2 b are also part of the refrigerant pipe portion 2.
  • the refrigerant heat transfer tube 30 is a portion that passes through the fin group 20 in the refrigerant tube portion 2 described above.
  • the refrigerant heat transfer tube 30 is a single flow path that does not branch, and passes through one end 22 in the width direction Y of each plate fin 21 and the other end 23 in the width direction Y of each plate fin 21. It is provided in a meandering manner and in a meandering manner in the longitudinal direction.
  • FIG. 4 is a plan view showing the heat exchanger 3.
  • the heat insulating material 50 is indicated by a two-dot chain line.
  • the fin group 20 shown in FIG. 4 some of the plate fins 21 are illustrated, and the illustration of the plate fins 21 within the range Z indicated by the two-dot chain line is omitted. However, actually, the plate fins 21 are also laminated in the range Z.
  • FIG. 4 shows a state in which the portion of the refrigerant heat transfer tube 30 provided at the one end 22 passes through the fin group 20.
  • a water heat transfer tube 40 described later is omitted.
  • the water heat transfer tube 40 is an example of a heat transfer tube for a heat medium.
  • the other part of the refrigerant heat transfer tube 30 is provided at the other end.
  • the refrigerant heat transfer tube 30 includes a plurality of refrigerant heat transfer tube bodies 31 and a plurality of refrigerant bend tubes 32.
  • the structure of the refrigerant heat transfer tube body 31 is the same.
  • the structure of the refrigerant bend pipe 32 is the same.
  • the refrigerant heat transfer tube body 31 includes a pair of straight portions 33 and a connecting portion 34 that connects the straight portions 33.
  • the straight portion 33 is an example of a straight portion for refrigerant.
  • the straight portion 33 is straight, and as shown in FIG. 3, the cross-sectional shape perpendicular to the direction in which the straight portion 33 extends is circular for both the inner edge 33a and the outer edge 33b.
  • One of the linear portions 33 is disposed at the one end portion 22 and the other is disposed at the other end portion 23, and is disposed in parallel to each other.
  • One straight line portion 33 and the other straight line portion face each other in the width direction Y.
  • the connecting portion 34 connects one end of one straight portion 33 and one end of the other straight portion 33 so as to communicate with each other.
  • the connection part 34 is U-shaped.
  • the pair of linear portions 33 and the connecting portion 34 are integrally formed, and are formed, for example, by bending a single pipe member. For this reason, as for the heat exchanger tube main body 31 for refrigerant
  • each plate fin 21 is formed with a refrigerant insertion hole 24 through which the straight portion 33 of the refrigerant heat transfer tube body 31 passes.
  • the refrigerant insertion hole 24 has a shape in which the straight portion 33 of the refrigerant heat transfer tube main body 31 is fitted, and the entire area of the edge of the refrigerant insertion hole 24 is in close contact with the peripheral surface of the straight portion 33 of the refrigerant heat transfer tube main body 31. is doing.
  • the heat transfer tube main body 31 for refrigerant is expanded. For this reason, the heat of the refrigerant L passing through the refrigerant heat transfer tube 30 is efficiently transmitted to each plate fin 21.
  • the diameter of the refrigerant insertion hole 24 and the outer diameter d of the linear portion 33 are the same value.
  • each straight portion 33 passing through the plate fin 21 is a posture in which each straight portion 33 is parallel to a direction orthogonal to the longitudinal direction X and the width direction Y. That is, the direction in which the center of each linear portion 33 extends is orthogonal to the directions X and Y. That is, the center of the straight portion 33 is the axis of the straight portion 33. For this reason, all the linear parts 33 are mutually parallel.
  • each refrigerant heat transfer tube main body 31 is arranged such that the opening 35 at the other end of the linear portion 33 is aligned in the longitudinal direction X.
  • the opening 35 at the other end of the linear portion 33 is an opening to which the connecting portion 34 is not connected.
  • the opening 35 disposed at one end in the longitudinal direction X and at one end in the width direction Y is a refrigerant inlet 36.
  • An opening 35 disposed at the other end in the longitudinal direction X and at one end in the width direction Y is a refrigerant outlet 37.
  • the refrigerant inlet 36 is connected to the pipe member 2a and the refrigerant L flows in.
  • the refrigerant outlet 37 is connected to the pipe member 2b and the refrigerant L flows out.
  • FIG. 5 is a front view showing the heat exchanger 3 with the heat insulating material 50 omitted and a state in which the heat exchanger 3 is viewed from the opening 35 side of the other end of the linear portion 33.
  • the refrigerant bend pipe 32 is connected so as to communicate with the opening 35 of the linear portion 33 of the refrigerant heat transfer pipe main body 31 adjacent in the longitudinal direction X.
  • the pair of straight portions 33 of each heat transfer tube body 31 for each refrigerant are connected to each other in the width direction Y by a connecting portion 34.
  • the refrigerant heat transfer tube forms one line, that is, one flow path, that is, one path, that does not branch from the refrigerant inlet 36 to the refrigerant outlet 37.
  • tube 32 which connects the linear parts 33 of the refrigerant
  • the refrigerant inlet 36 and the refrigerant outlet 37 are communicated with each other by the plurality of refrigerant heat transfer tube bodies 31 and the plurality of refrigerant bend tubes 32. Therefore, the refrigerant heat transfer tube 30 is connected to the refrigerant inlet. From the 36 to the refrigerant outlet 37, the fin group 20 is arranged to meander.
  • the water heat transfer tube 40 is provided in the fin group 20 so as to meander through the fin group 20 like the refrigerant heat transfer tube 30.
  • the water heat transfer pipe 40 is a part of the water supply pipe section 8, and is connected to the pump 9 through, for example, a pipe member 8a, and is connected to the hot water storage tank 12 through, for example, the pipe member 8b.
  • the water heat transfer tubes 40 are provided so as to pass between the refrigerant heat transfer tubes 30 provided at one end 22 and the other end 23 in the width direction Y in each plate fin 21. .
  • FIG. 6 is a sectional view of the heat exchanger 3 taken along line F6-F6 shown in FIG.
  • FIG. 6 is a plan view of the water heat transfer tube 40 as viewed in the width direction Y as it passes through the fin group 20. A part of the fin group 20 is omitted from the two-dot chain line. Further, from FIG. 6, the refrigerant heat transfer tube 30 provided at the other end 23 is omitted for explanation.
  • the water heat transfer tube 40 includes a plurality of water heat transfer tube main bodies 41 and a plurality of water bend tubes 42.
  • the water heat transfer tube main body 41 has a pair of straight portions 43 and a connecting portion 44 that connects the straight portions 43.
  • the straight line portion 43 is an example of a straight line portion for water.
  • the straight portion 43 is straight, and as shown in FIG. 3, the cross-sectional shape perpendicular to the direction in which the straight portion 43 extends is a circle for both the inner edge 43 a and the outer edge 43 b.
  • the connecting part 44 is U-shaped. Each linear part 43 is arrange
  • the straight line portion 43 and the connecting portion 44 are formed integrally with each other, and are formed by bending a single pipe member, for example. For this reason, as for the heat exchanger tube main body 41 for water, while each linear part 43 is connected via the connection part 44, the planar shape is U shape.
  • the water heat transfer tube main body 41 is provided in the fin group 20 so that each straight portion 43 passes through all the plate fins 21. For this reason, each plate fin 21 is formed with a water insertion hole 25 through which the straight portion 43 of the water heat transfer tube body 41 passes.
  • the water insertion hole 25 has a shape in which the straight portion 43 of the water heat transfer tube main body 41 is fitted. Therefore, the entire area of the edge of the water insertion hole 25 is the circumference of the straight portion 43 of the water heat transfer tube main body 41. It is in close contact with the surface. In order to make it adhere, for example, the heat transfer tube main body 41 for water is expanded. For this reason, the heat of each plate fin 21 is efficiently transmitted to the heat transfer tube 40 for water.
  • the diameter of the water insertion hole 25 and the outer diameter D of the linear portion 43 are the same value.
  • the posture of the straight portion 43 passing through the plate fin 21 is, for example, a posture in which the straight portion 43 is parallel to a direction orthogonal to the longitudinal direction X and the width direction Y. That is, the center of the straight line portion 43 extends in a direction orthogonal to the directions X and Y and is parallel to the straight line portion 33. The center of the straight line portion 43 is the axis.
  • the water heat transfer tube 40 is arranged so that the other opening 45 of the straight portion 43 of each water heat transfer tube main body 41 is aligned in the longitudinal direction X.
  • the other opening 45 of the straight portion 43 of the water heat transfer tube body 41 is an opening to which the connecting portion 44 is not connected.
  • the other opening 45 of the water heat transfer tube 40 opens to the same side as the opening 35 of the refrigerant heat transfer tube body 31.
  • the opening 45 disposed at the other end in the longitudinal direction X serves as a water inlet 46
  • the opening 45 disposed at one end serves as a water outlet 47.
  • the pipe member 8a is connected to the water inlet 46
  • the pipe member 8b is connected to the water outlet 47.
  • the water bend pipe 42 is substantially U-shaped in plan view.
  • the water bend pipe 42 connects the openings 45 excluding the water inlet 46 and the water outlet 47 adjacent to each other in the longitudinal direction X.
  • the water inlet 46 and the water outlet 47 are communicated with each other by the plurality of water heat transfer pipe bodies 41 and the plurality of water bend pipes 42. Therefore, the water heat transfer pipe 40 is connected to the water inlet.
  • the fin group 20 is provided to meander from the water outlet 46 to the water outlet 47.
  • the inner diameter of the water heat transfer tube 40 is larger than the inner diameter of the refrigerant heat transfer tube 30, and the outer diameter of the water heat transfer tube 40 is larger than the outer diameter of the refrigerant heat transfer tube 30.
  • FIG. 7 is a front view of the heat exchanger 3 showing a state in which the heat insulating material 50 and the bend pipes 32 and 42 are omitted and partially omitted.
  • each refrigerant heat transfer tube main body 31 one linear portion 33 disposed at one end 22 and the other linear portion 33 disposed at the other end 23 are arranged in the width direction Y.
  • the lines that face each other and connect the center P ⁇ b> 1 of the linear portion 33 are parallel to the width direction Y.
  • the line connecting the centers P1 of the linear portions 33 arranged in the longitudinal direction X at the one end portion 22 is parallel to the longitudinal direction X.
  • a line connecting the centers P ⁇ b> 1 of the linear portions 33 aligned in the longitudinal direction X is parallel to the longitudinal direction X.
  • the linear portions 33 of the refrigerant heat transfer tube main body 31 adjacent to each other in the longitudinal direction X are arranged at equal intervals in the longitudinal direction X at the one end portion 22 and the other end portion 23.
  • the pipe pitch between the linear portions 33 adjacent to each other in the longitudinal direction X at the one end portion 22 and the other end portion 23 is the length B.
  • the distance between the centers P1 of the linear portions 33 adjacent in the longitudinal direction X is the length B.
  • the inter-pitch distance B has the same value.
  • the line connecting the centers P2 of the straight portions 43 of the water heat transfer tube main bodies 41 arranged in the longitudinal direction X is parallel to the longitudinal direction X.
  • the straight line portion 43 is disposed between the straight line portions 33 of the refrigerant heat transfer tube body 31 adjacent to each other in the longitudinal direction X.
  • the center P2 of the straight line portion 43 has the straight line portion 43 in the longitudinal direction X. It arrange
  • the straight portions 33 and 43 are arranged in a staggered manner with respect to each other. For this reason, the length of the width direction Y of each plate fin 21 can be shortened. Further, because of the arrangement structure, the water heat transfer tube 40 is disposed adjacent to the refrigerant heat transfer tube 30.
  • the plurality of linear portions 43 are arranged at equal intervals in the longitudinal direction X.
  • the pipe pitch between the straight portions 43 adjacent in the longitudinal direction X is the length A.
  • the distance between the centers P2 of the linear portions 43 adjacent in the longitudinal direction X is the length A.
  • the inter-pitch distance A has the same value.
  • a heat blocking means is provided between the adjacent straight portions 33.
  • a heat blocking means is provided between the straight portions 33 adjacent to each other in the longitudinal direction X and the width direction Y.
  • the heat blocking means has a function of suppressing heat exchange between the straight portions 33 via the plate fins 21.
  • a cut 26 is formed as an example between the straight portions 33 adjacent to each other in each plate fin 21.
  • Each notch 26 formed between the linear portions 33 adjacent to each other in the longitudinal direction X extends in the width direction Y.
  • Each notch 26 formed between the linear portions 33 adjacent in the width direction Y is provided between the linear portions 43 adjacent in the longitudinal direction X and extends in the longitudinal direction X.
  • Each cut 26 penetrates the plate fin 21.
  • the cuts 26 suppress heat exchange between the linear portions 33 adjacent to each other via the plate fins 21.
  • the notch 26 does not reach the water insertion hole 25 of the plate fin 21.
  • the shortest distance E between the refrigerant insertion holes 24 through which the pair of straight portions 33 facing in the width direction Y is passed is shorter than the outer diameter D of the water heat transfer tube body 41.
  • the outer diameter D of the water heat transfer tube main body 41 is the inner diameter D of the water insertion hole 34. Therefore, it is considered that the refrigerant bend tube 32 does not contact the water heat transfer tube 40 and the water bend tube 42 does not contact the refrigerant heat transfer tube 30.
  • FIG. 8 is a plan view showing the range of F8 shown in FIG. FIG. 8 shows a part of the refrigerant bend pipe 32 and a pair of linear portions 33 adjacent to each other in the longitudinal direction X.
  • the refrigerant bend pipes 32 are all the same as the structure shown in FIG. 8, and therefore the refrigerant bend pipe 32 shown in FIG. 8 will be described as a representative.
  • FIG. 9 is a cross-sectional view showing a state in which the refrigerant bend pipe 32 is cut along the line F9-F9 shown in FIG.
  • the refrigerant bend pipe 32 has a flat shape in which the maximum width lr ⁇ b> 1 in the width direction Y is smaller than the outer diameter d of the refrigerant heat transfer pipe body 31.
  • the maximum width lr1 is set so that the refrigerant bend pipe 32 does not contact the water bend pipe.
  • the water bend pipe 42 has a flat shape in which the maximum width lr ⁇ b> 2 in the width direction Y is smaller than the outer diameter D of the linear portion 43.
  • the maximum width lr2 is set in consideration so that the water bend pipe 42 does not contact the refrigerant bend pipe 32.
  • the width lr1 of the refrigerant bend pipe 32 and the width lr2 of the water bend pipe 42 are set in consideration of each other as described above. Large changes to the outer diameters d and D are suppressed.
  • the refrigerant bend pipe 32 connects a pair of linear portions 33 adjacent to each other in the longitudinal direction X so as to avoid the water heat transfer pipe 40, that is, so as not to contact.
  • the water bend pipe 42 connects the pair of linear portions 43 adjacent to each other in the longitudinal direction X so as to avoid the refrigerant heat transfer pipe 30, that is, so as not to contact.
  • each refrigerant heat transfer tube main body 31 one end of the linear portion 33 facing the width direction Y is connected to each other by a connecting portion 34.
  • the connecting portion 34 is set to have a maximum width smaller than the outer diameter d of the linear portion 33 in the longitudinal direction X so as not to contact the water heat transfer tube 40 like the refrigerant bend tube 32, and is flat. It is.
  • the heat insulating material 50 is provided so as to cover the entire outer surface of the heat exchanger 3. Furthermore, as shown in FIG. 2, the heat insulating material 50 has a size that covers the heat transfer pipe 30 for refrigerant and the heat transfer pipe 40 for water.
  • the heat insulating material 50 is sectioned so that the openings 35 and 45 can be seen in the heat exchanger 3.
  • the heat insulating material 50 is formed of a material having low thermal conductivity.
  • the heat insulating material 50 is not limited to being comprised so that all the surfaces of the heat exchanger 3 may be covered.
  • the heat exchanger 3 may have a shape that opens so that a side surface on the side where the bend pipes 32 and 42 are provided and a side surface on the side where the connecting portions 34 and 44 are provided can be seen from the outside.
  • the refrigerant L that has flowed into the heat exchanger 3 flows into the refrigerant heat transfer tube 30 from the refrigerant inlet 36 and flows in the refrigerant heat transfer tube 30 toward the refrigerant outlet 37. Since the refrigerant heat transfer tube 30 is a single flow path, the refrigerant L alternately flows through the one end 22 and the other end 23 of each plate fin 21. At this time, the heat of the refrigerant L is transmitted to the fin group 20, that is, each plate fin 21.
  • the water W that has flowed into the heat exchanger 3 flows into the water heat transfer tube 40 from the water inlet 46 and flows in the water heat transfer tube 40 toward the water outlet 47.
  • the refrigerant inlet 36 and the water outlet 47 are provided adjacent to each other, and the refrigerant outlet 37 and the water inlet 46 are provided adjacent to each other, the flow of the refrigerant L and the water W The flows are opposite to each other.
  • the heat of the refrigerant L transmitted to each plate fin 21 is transmitted to the water W.
  • the refrigerant L that has exited the refrigerant outlet 37 is then guided to the internal heat exchanger 4.
  • the water W exiting the water outlet 47 is guided to the hot water storage tank 12.
  • FIG. 10 is a graph showing the temperature of the refrigerant L between the refrigerant inlet 36 and the refrigerant outlet 37 and the temperature of the water W between the water inlet 46 and the water outlet 47 in the heat exchanger 3. Show.
  • the graph G shows the temperature gradient between the refrigerant L and the water W.
  • the horizontal axis indicates the position in the refrigerant heat transfer tube 30 and the water heat transfer tube 40, and the vertical axis indicates the temperature.
  • the temperature of the refrigerant inlet 36 is T1
  • the temperature of the refrigerant outlet 37 is T2.
  • the temperature of the water inlet 46 is t1
  • the temperature of the water outlet 47 is t2.
  • the temperature of the refrigerant L decreases in the process of flowing from the refrigerant inlet 36 to the refrigerant outlet 37, that is, T1> T2.
  • the temperature of the water W rises in the process of flowing from the water inlet 46 to the water outlet 47, that is, t2> t1.
  • the refrigerant heat transfer tube 30 is connected to the fin group 20, that is, each plate fin 21, and the water heat transfer tube 40 is connected to the fin group 20, that is, each plate fin 21.
  • heat transfer from the refrigerant L to the water W is performed via the fin group 20.
  • the pipe pitch B between the straight portions 33 arranged side by side in the longitudinal direction X is larger than the length C between the straight portions 33 arranged in the width direction Y. For this reason, since the distance between the linear parts 33 arranged in the width direction Y becomes smaller than the distance between the linear parts 33 adjacent to each other in the longitudinal direction X, the heat transfer efficiency is improved. The same effect can be obtained even when B ⁇ C.
  • the productivity in producing the heat exchanger 3 can be improved and the cost can be reduced.
  • the ratio between the heat capacity flow rate of the refrigerant L and the heat capacity flow rate of the water W is approximately 1: 1 so that the total area in the tube of the refrigerant heat transfer tube 30 and the total area in the tube of the heat transfer tube for refrigerant are
  • the outer diameter of the refrigerant heat transfer tube 30 is made smaller than the outer diameter of the water heat transfer tube 40 by taking advantage of the characteristic that the pressure loss of the refrigerant L is low so that the ratio is approximately 1: 1. Is sandwiched in the width direction Y by a pair of refrigerant heat transfer tubes 30.
  • the heat exchanger 3 has a structure in which the balance of the heat transfer amount is improved, and therefore, the heat transfer amount. Thermal efficiency is increased.
  • coolant heat exchanger tube 30 when the connection part 34 of the refrigerant
  • the refrigerant bend pipe 32 and the water bend pipe 42 are flat, the refrigerant bend pipe 32 does not interfere with the water heat transfer pipe 40 and does not interfere with the water bend pipe. Since 42 does not interfere with contact with the refrigerant heat transfer tube 30 or the like, the efficiency of attaching the refrigerant bend tube 32 and the water bend tube 42 is improved. Furthermore, since the refrigerant heat transfer tube 30 and the water heat transfer tube 40 can be brought closer to each other, the heat transfer efficiency is improved.
  • the refrigerant heat transfer tube 30 has a structure having a single flow that alternately flows through the one end portion 22 and the other end portion 23 of each plate fin 21, and therefore, the one end portion 22 across the water heat transfer tube 40.
  • the amount of refrigerant L flowing through the other end 23 is the same. For this reason, heat exchange is performed efficiently.
  • the refrigerant inlet 36 and the water outlet 47 are provided at one end in the longitudinal direction X of the fin group 20 so as to be adjacent to each other, and the refrigerant outlet 37 and the water inlet 46 are arranged in the longitudinal direction X of the fin group 20.
  • the refrigerant flow and the water flow are opposite to each other. For this reason, heat transfer from the refrigerant L to the water W can be efficiently promoted.
  • each plate fin 21 the linear part 33 of the refrigerant
  • the one linear part 43 comes to oppose the two linear parts 33 by arrange
  • the slits 26 are formed in each plate fin 21 between the linear portions 43 adjacent to each other in the longitudinal direction X and between the linear portions 33 adjacent to each other in the width direction Y, whereby the condensation latent heat of the refrigerant L is Since heat is efficiently transferred only to the water heat transfer tube 40, the heat exchange performance is improved.
  • the heat insulating material 50 suppresses heat exchange between the fin group 20 and the surrounding air. For this reason, heat exchange between the refrigerant L and the water W via the fin group 20 is efficiently performed.
  • FIG. 11 is a front view showing a state in which the heat insulating material 50, the refrigerant bend pipe 32, and the water bend pipe 42 are removed in the heat exchanger 3 of the present embodiment.
  • the relative positional relationship between the linear portion 33 and the linear portion 43 is D ⁇ Cd instead of the relative positional relationship where B ⁇ C.
  • the linear portion 33 When the relative positional relationship between the linear portion 33 and the linear portion 43 satisfies D ⁇ Cd, the linear portion 33 approaches the water heat transfer tube 40. For this reason, in this embodiment, the same operation and effect as those of the first embodiment can be obtained. Further, the relative positional relationship between the straight line portion 33 and the straight line portion 43 may be satisfied simultaneously with B ⁇ C described in the first embodiment and D ⁇ Cd described in the present embodiment.
  • the refrigerant bend pipe 32, the water bend pipe 42, and the connecting portion 34 are different from those of the first embodiment.
  • Other structures may be the same as those in the first embodiment. The different structure will be specifically described.
  • FIG. 12 is a plan view showing a part of the straight portion 33 and the refrigerant bend pipe 32 in the refrigerant heat transfer pipe 30 of the present embodiment.
  • FIG. 12 shows a part of the straight portion 33 and the refrigerant bend pipe 32 as in FIG. 8 used in the first embodiment.
  • FIG. 13 is a cross-sectional view showing a state in which the refrigerant bend pipe 32 is cut along the line F13-F13 shown in FIG.
  • the refrigerant bend pipe 32 is not flat but has a circular cross section.
  • the outer diameter dr1 of the bend pipe 32 for refrigerant is smaller than the outer diameter d of the straight portion 33. That is, d> dr1.
  • the outer diameter dr1 of the refrigerant bend pipe 32 is set in consideration so that the refrigerant bend pipe 32 does not contact the water heat transfer pipe 40.
  • the water bend pipe 42 has a circular cross section.
  • the outer diameter dr ⁇ b> 2 of the water bend pipe 42 is smaller than the outer diameter D of the linear portion 43.
  • the outer diameter dr ⁇ b> 2 of the water bend pipe 42 is set in consideration so that the water bend pipe 42 does not contact the refrigerant heat transfer pipe 30.
  • the connecting portion 34 that connects one end of the linear portion 33 facing in the width direction Y has a circular cross section.
  • the outer diameter of the connecting portion 34 is set in consideration so that the refrigerant bend pipe 32 does not contact the water heat transfer pipe 40.
  • the structure of the refrigerant bend pipe 32, the water bend pipe 42, and the connecting portion 34 described in the present embodiment may be used in the heat exchanger 3 described in the second embodiment. In this case, the same operation and effect as in the second embodiment can be obtained.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

Ce mode de réalisation de l'invention se rapporte à un groupe d'ailettes, à des tubes de transfert de chaleur pour fluide frigorigène et à des tubes de transfert de chaleur pour milieu chauffant. Le groupe d'ailettes se compose d'une pluralité d'ailettes qui sont stratifiées. Les tubes de transfert de chaleur pour fluide frigorigène traversent les ailettes dans la direction de stratification et se présentent sous une forme sinueuse dans la direction longitudinale des ailettes, et le fluide frigorigène s'écoule à l'intérieur. Les tubes de transfert de chaleur pour milieu chauffant traversent les ailettes dans la direction de stratification et sont adjacents aux tubes de transfert de chaleur pour fluide frigorigène, et se présentent sous une forme sinueuse dans la direction longitudinale des ailettes et le milieu chauffant s'écoule à l'intérieur. Les tubes de transfert de chaleur pour fluide frigorigène sont alignés en colonne de part et d'autre des tubes de transfert de chaleur pour milieu chauffant. Lorsque l'espacement entre tubes des tubes de transfert de chaleur pour fluide frigorigène qui sont alignés dans la direction longitudinale est défini par B, et que la distance entre les centres des tubes de transfert de chaleur pour fluide frigorigène de part et d'autre des tubes de transfert de chaleur pour milieu chauffant dans la direction longitudinale est définie par C, B est réglé pour être supérieur ou égal à C.
PCT/JP2011/071619 2010-09-29 2011-09-22 Échangeur de chaleur WO2012043380A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2012536393A JP5531103B2 (ja) 2010-09-29 2011-09-22 熱交換器

Applications Claiming Priority (2)

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JP2010219903 2010-09-29
JP2010-219903 2010-09-29

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WO2012043380A1 true WO2012043380A1 (fr) 2012-04-05

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PCT/JP2011/071619 WO2012043380A1 (fr) 2010-09-29 2011-09-22 Échangeur de chaleur

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JP (1) JP5531103B2 (fr)
WO (1) WO2012043380A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016130597A (ja) * 2015-01-13 2016-07-21 東芝キヤリア株式会社 プレート式熱交換器及び冷凍サイクル装置
FR3071901A1 (fr) * 2017-10-03 2019-04-05 Naval Group Dispositif deprimogene compact a coudes

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000213814A (ja) * 1999-01-25 2000-08-02 Matsushita Electric Ind Co Ltd １缶２回路式熱源装置
JP2003240457A (ja) * 2002-02-08 2003-08-27 Toyo Radiator Co Ltd 給湯用熱交換器

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000213814A (ja) * 1999-01-25 2000-08-02 Matsushita Electric Ind Co Ltd １缶２回路式熱源装置
JP2003240457A (ja) * 2002-02-08 2003-08-27 Toyo Radiator Co Ltd 給湯用熱交換器

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016130597A (ja) * 2015-01-13 2016-07-21 東芝キヤリア株式会社 プレート式熱交換器及び冷凍サイクル装置
FR3071901A1 (fr) * 2017-10-03 2019-04-05 Naval Group Dispositif deprimogene compact a coudes

Also Published As

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JPWO2012043380A1 (ja) 2014-02-06
JP5531103B2 (ja) 2014-06-25

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