WO2015020050A1 - Heat exchanger and method for manufacturing heat exchanger - Google Patents

Heat exchanger and method for manufacturing heat exchanger Download PDF

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Publication number
WO2015020050A1
WO2015020050A1 PCT/JP2014/070609 JP2014070609W WO2015020050A1 WO 2015020050 A1 WO2015020050 A1 WO 2015020050A1 JP 2014070609 W JP2014070609 W JP 2014070609W WO 2015020050 A1 WO2015020050 A1 WO 2015020050A1
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WO
WIPO (PCT)
Prior art keywords
spiral
partition wall
spiral tube
heat exchanger
groove
Prior art date
Application number
PCT/JP2014/070609
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French (fr)
Japanese (ja)
Inventor
和田 博文
智規 原口
Original Assignee
サンデン株式会社
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Publication date
Application filed by サンデン株式会社 filed Critical サンデン株式会社
Publication of WO2015020050A1 publication Critical patent/WO2015020050A1/en

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28DHEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/04Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being spirally coiled
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28DHEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0041Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for only one medium being tubes having parts touching each other or tubes assembled in panel form
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28DHEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00Heat-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
    • F28D9/04Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being formed by spirally-wound plates or laminae
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28FDETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/007Auxiliary supports for elements
    • F28F9/013Auxiliary supports for elements for tubes or tube-assemblies
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28DHEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/007Condensers

Definitions

  • the present invention relates to a heat exchanger for exchanging heat between a first fluid and a second fluid flowing in a spiral shape, and a method for manufacturing the same.
  • a spiral partition plate In exchanging heat between the first fluid and the second fluid having different temperatures, a spiral partition plate is provided in a cylindrical container to form a spiral passage between the partition plates, and a plurality of spiral tubes are provided in the spiral passage.
  • a spiral heat exchanger that is arranged to exchange heat by flowing a first fluid in a spiral passage and a second fluid in a spiral tube (see, for example, Patent Document 1).
  • the first fluid and the second fluid are counterflows. And according to the structure which concerns, there existed an advantage which can be set as a compact heat exchanger with high heat exchange efficiency.
  • the present invention has been made to solve the conventional technical problems, and is a heat exchanger that improves the assembly workability of a heat exchanger composed of a spiral partition wall and a spiral tube, and heat exchange It aims at providing the manufacturing method of a vessel.
  • the heat exchanger of the invention of claim 1 comprises a spiral passage between spiral partition walls provided in a container, and a plurality of spiral tubes are arranged in the spiral passage in the upper and lower stages.
  • the first fluid flowing in the spiral passage outside the lever tube and the second fluid flowing in the spiral tube are heat-exchanged, and have a groove formed in the partition wall, and the width dimension of the partition wall of the groove portion W is configured to be smaller than the spiral interval R of the spiral tube.
  • the spiral tube corresponds to the groove of the partition wall, and the partition wall and / or the spiral tube rotates about the center of the spiral. By being done, it is closely_contact
  • the heat exchanger of the invention of claim 2 is characterized in that, in the above invention, the spiral tube is detachably fitted in the groove of the partition wall.
  • a heat exchanger manufacturing method in which a spiral passage is formed between spiral partition walls provided in a container, and a plurality of spiral tubes are arranged in the spiral passage so that the outside of the spiral tube is outside.
  • a groove is formed in the partition wall, and the width dimension W of the partition wall of this groove portion is defined as the spiral tube.
  • a spiral tube is arranged corresponding to the groove of the partition wall, and the partition wall and / or the spiral tube is rotated about the center of the spiral, so that the spiral tube is placed in the groove. It is characterized by being in close contact.
  • a heat exchanger manufacturing method wherein the spiral tube is detachably fitted in a groove of the partition wall in the above invention.
  • the spiral passage is formed between the spiral partition walls provided in the container, and the spiral tubes are arranged in a plurality of upper and lower stages in the spiral passage, and the outer sides of the spiral tubes are arranged.
  • a groove is formed in the partition wall, and the width dimension W of the partition wall of the groove portion is defined as the space between the spirals of the spiral tube.
  • the spiral tube is arranged so as to be smaller than R and corresponding to the groove of the partition wall, and the partition wall and / or the spiral tube is rotated about the center of the spiral so that the spiral tube is in close contact with the groove. Therefore, the heat exchanger can be easily assembled by assembling the spiral tube to the spiral partition wall by an extremely simple operation by simply rotating the partition wall and the spiral tube.
  • the spiral tube is detachably fitted into the groove of the partition wall as in the inventions of claim 2 and claim 4, the heat that can easily decompose the partition wall portion and the spiral tube portion.
  • the exchanger can be manufactured, and dust and scale attached to the heat exchanger can be easily washed.
  • FIG. 20 is a front view of the spiral tube of FIG. 19. It is a principal part expanded sectional view of the heat exchanger comprised with the spiral tube of FIG. It is a perspective view of the spiral tube of the heat exchanger of further another Example. It is a front view of the spiral tube of FIG. It is a principal part expanded sectional view of the heat exchanger comprised with the spiral pipe of FIG. It is a principal part expanded sectional view of the heat exchanger of other Example. It is a principal part expanded sectional view of the heat exchanger of other Example. It is a principal part perspective view of the heat exchanger of FIG.
  • FIG. 29 is a layout diagram of a partition wall and a spiral tube for explaining the method of FIG. 28. It is a top view of the heat exchanger assembled by the method of FIG. It is a top view of the partition wall explaining the other Example of the manufacturing method of the heat exchanger of this invention. It is a top view of the spiral tube explaining the method of FIG. It is a layout of the partition wall and the spiral tube for explaining the method of FIG. It is a top view of the heat exchanger assembled by the method of FIG.
  • FIG. 36 is a cross-sectional view of the heat exchanger of FIG. 35 taken along line AA.
  • reference numeral 1 denotes a spiral heat exchanger which is an embodiment to which the present invention can be applied.
  • a cylindrical container 2 having an open top and bottom, and a partition wall 3 as a spiral partition wall portion.
  • a spiral tube 4 as a spiral tube portion and lids 6 and 6.
  • the container 2, the partition wall 3, the spiral tube 4 and the lid 6 are all made of metal such as aluminum, and the spiral tube 4 is arranged in a plurality of stages inside the partition wall 3 and is in close contact by welding.
  • a partition wall 3 in which the spiral tubes 4 are in close contact with each other is arranged in the container 2, and the upper and lower openings of the container 2 are closed by lids 6 and 6.
  • the upper and lower ends of the partition wall 3 are in close contact with the inner surfaces of the lids 6 and 6, and the space between them is sealed.
  • a series of spiral passages 7 are formed between the spiral partition walls 3 toward the outside while rotating from the center of the spiral.
  • the spiral tube 4 is disposed in the spiral passage 7 so as to be in contact with the space in the spiral passage 7.
  • the spiral tube 4 comes into contact with a fluid (first fluid described later) flowing in the spiral passage 7.
  • the spiral tubes 4 in a plurality of stages are spaced from each other, and as shown in FIG. 2, the outer ends of the spiral tubes 4 are communicated with each other by a header 8, and the end portion on the center side of the spiral Are also communicated by the header 9.
  • the heat exchanger 1 When the heat exchanger 1 is used as, for example, a refrigerant condenser in the Rankine cycle, cold water as the first fluid flows into the heat exchanger 1 from the center of the spiral in the spiral passage 7. Then, the spiral passage 7 flows while rotating outward from the center of the spiral as indicated by a thick arrow in FIG. 3, and flows out of the heat exchanger 1 from the side surface of the container 2. Further, for example, a high-temperature refrigerant as the second fluid flows from the header 8 and flows in each spiral tube 4 while rotating from the outside toward the center of the spiral as indicated by a thin arrow in FIG. It flows out of the heat exchanger 1.
  • the flow of the cold water (first fluid) is counterclockwise in FIG. 3, and the flow of the refrigerant (second fluid) is counterclockwise, so the flows of the cold water and the refrigerant are opposite to each other. Therefore, the temperature difference between the refrigerant flowing in the spiral tube 4 and the water flowing in the outer spiral passage 7 increases over the entire range from the header 8 on the inlet side to the header 9 on the outlet side. Will improve. In particular, since the refrigerant (second fluid) flows through the spiral tube 4, high pressure resistance design is facilitated even when a high-pressure refrigerant flows.
  • the partition wall 3 is formed by forming in parallel a plurality of curved grooves 11 that are curved and recessed in a flat plate to have a corrugated cross section, and processing the flat plate into a spiral shape.
  • each spiral tube 4 is arrange
  • the spiral tube 4 is integrated. Thereafter, the header 8 is welded to the outer end portion of each spiral tube 4, and the header 9 is welded to the end portion on the outlet side.
  • the center direction of the vortex of the partition wall 3 and the vortex tube 4 is the horizontal direction, and the vertical direction perpendicular thereto is the vertical direction.
  • a predetermined interval (flow path width PB) is formed between the upper and lower spiral tubes 4 and 4, and the partition wall 3 (in the direction of the center of the spiral) and the partition wall 3 (on the outside of the groove 11).
  • a space (flow path width PA) is also formed between the outer surface and the protruding outer surface (FIG. 4). That is, the channel width PA is the width of the spiral passage 7 in which cold water (first fluid) flows outside the spiral tube 4 in a direction (horizontal direction) parallel to the center direction of the spiral of the spiral tube 4.
  • the width PB is the width of the spiral passage 4 through which cold water (first fluid) flows outside the spiral tube 4 in the direction orthogonal to the center direction of the spiral of the spiral tube 4.
  • FIG. 5 shows the heat of the refrigerant (second fluid) and cold water (first fluid) when the ratio of the channel width PB to the channel width PA (channel width PB / channel width PA) is changed.
  • the change in the exchange amount is shown.
  • the flow path width PB is smaller than the flow path width PA
  • the cold water (first fluid) easily flows in the spiral passage 7 between the spiral tube 4 and the inner partition wall 3. This is because it becomes difficult to flow in the spiral passage 7 between the upper and lower spiral tubes 4 and the heat transfer area of the spiral tube 4 cannot be effectively used.
  • the flow path width PB becomes larger than the flow path width PA.
  • the inside of the spiral passage 7 between the spiral tube 4 and the inner partition wall 3 is cooled with cold water ( This is because it becomes difficult for the first fluid) to flow, and it becomes easy to flow in the spiral passage 7 between the upper and lower spiral tubes 4, and the heat transfer area of the spiral tube 4 cannot be effectively used.
  • the flow path width PB of the spiral passage 7 is the same, and the flow path is between the partition wall 3 that is in close contact with the outside of the spiral tube 4 and the spiral tube 4 on the outside (opposite direction to the center of the spiral).
  • the width PA is also the same.
  • the flow path width PA is equal to the flow path width PB.
  • the ratio of the flow path width PB / the flow path width PA is in the range of 0.7 to 1.3.
  • a relatively high heat exchange amount can be secured without increasing the dead space. The reason is as follows. That is, since the peak of the heat exchange amount is 1, if it is defined that 0.98 or more is a high heat exchange amount, when the ratio of the channel width PB / channel width PA is less than 0.7, Since the flow path of the first fluid (cold water) is not sufficient, the amount of heat exchange is not sufficient, and is less than 0.98. Therefore, the lower limit of the ratio of the channel width PB / channel width PA is 0.7.
  • the heat exchange amount is maintained at 0.98 or more until the ratio of the channel width PB / channel width PA is about 2.3, but when the ratio is 1.3 or more, the channel width PB is As a result, the dead space is generated in the spiral flow path 7, and the size of the heat exchanger 1 is unnecessarily enlarged, resulting in inefficiency in terms of capacity and space. Therefore, the upper limit of the ratio of the channel width PB / channel width PA is 1.3.
  • the flow path width PA of the spiral passage 7 through which the cold water (first fluid) flows outside the spiral tube 4 in the direction parallel to the spiral center direction of the spiral tube 4 and the center direction of the spiral of the spiral tube 4 is made substantially equal, so that the cold water (first fluid) flows outside the spiral tube 4.
  • the flow path width of the spiral passage 7 can be made substantially equal over substantially the entire circumference of the spiral tube 4. That is, the flow path width of the spiral passage 7 around the spiral tube 4 is drawn concentrically with the spiral tube 4 around the axis of the spiral tube 4, and cold water (first fluid) is distributed around the entire circumference of the spiral tube 4. Since it flows evenly, the heat transfer area of the spiral tube 4 can be fully utilized, and the heat exchange performance between the cold water (first fluid) and the refrigerant (second fluid) can be greatly improved.
  • the ratio of the channel width PB to the channel width PA (channel width PB / channel width PA) is set to 0.7 to 1.3 as described above, and preferably the channel width PA as in the embodiment.
  • the flow path width PB By making the flow path width PB, the flow of cold water (first fluid) outside the spiral tube 4 is effectively uniformed, and the heat exchange amount between the first fluid (cold water) and the second fluid (refrigerant) is reduced. It becomes possible to improve the heat exchange performance as a certain value or more (0.98 or more).
  • FIG. 6 shows a heat exchanger 1 of an embodiment using a partition wall 3 having another shape.
  • the partition wall 3 has a corrugated cross section.
  • X in the portion farthest from the adjacent spiral tubes 4, 4 indicated by X in FIG. 7, that is, in the portion X in the center direction of the spiral between the upper and lower spiral tubes 4, 4, Since the space between the partition wall 3 and the spiral tube 4 becomes wider, the flow path width of this portion X is inevitably increased, and more cold water (first fluid) tends to flow.
  • the partition wall 3 in the middle (in the direction of the center of the spiral) of the middle position (height) between the upper and lower spiral tubes 4, 4 is projected toward the outer spiral tubes 4, 4, A protruding portion 12 is formed, and the partition wall 3 has a corrugated cross section having the protruding portion 12.
  • the heat exchange performance can be improved by making cold water (first fluid) flow all over the circumference of the spiral tube 4 evenly.
  • FIG. 8 shows another example of the heat exchanger 1.
  • the spiral tube 4 is disposed in the spiral passage 7 between the inner and outer partition walls 3 and the partition wall 3 without contacting the partition wall 3.
  • the spiral tube 4 is held away from the partition wall 3 by using a holder (not shown) having the same structure as the holder 18 shown in FIGS. 26 and 27, for example.
  • the flow path width on the spiral side of the spiral tube 4 is PA1
  • the flow path width PA1 and the flow path width PA2 are set.
  • the relationship is channel width PA2 ⁇ channel width PA1.
  • FIGS. 9 and 10 show another embodiment.
  • the partition wall portion 13 and the spiral tube portion 14 corresponding to the partition wall 3 and the spiral tube 4 in each of the embodiments described above are integrally formed on the extruded material 15 by extrusion molding of a metal such as aluminum. It is.
  • the extruded material 15 of the embodiment is formed with a plurality of upper and lower spiral tube portions 14 having a circular passage in the inside, and the spiral tube portions 14 are connected to each other by a partition wall portion 13. ing.
  • path 7 is comprised between the inner and outer partition wall part 13 and the spiral pipe part 14 by winding the flat extrusion material 15 which concerns in a spiral shape.
  • the flow path width PA of the spiral passage 7 outside the spiral tube portion 14 in the direction parallel to the spiral center direction of the spiral tube portion 14 is in a direction orthogonal to the spiral center direction of the spiral tube portion 14.
  • the flow path width PB of the spiral passage 7 outside the spiral tube portion 14 is substantially equivalent (same in the embodiment). (FIG. 10).
  • the partition wall portion 13 and the spiral tube portion 14 are integrally extruding the partition wall portion 13 and the spiral tube portion 14, the partition wall is formed and spirally wound as in the above-described embodiment, and a plurality of spiral tubes are wound spirally.
  • the operations of turning and bringing them into close contact with a predetermined position of the partition wall are integrated into simple operations of extrusion molding and winding, so that the number of parts can be reduced and the assembly workability can be remarkably improved.
  • FIGS. 11 to 18 show another embodiment.
  • a protrusion 16 is integrally formed at the upper end of the spiral tube 4 (FIGS. 11 and 12).
  • the ridge 16 extends in the axial direction of the spiral tube 4 and is erected in a wall shape.
  • the upper end of the ridge 16 is the other spiral tube 4 above. Is in close contact with and in close contact with the lower end (FIG. 13).
  • the spiral passage 7 is formed between the inner and outer protrusions 16 and the spiral tube 4, and in this case, the partition wall portion is constituted by the spiral tube 4 and the protrusion 16.
  • the protrusion 16 is formed not only on the upper end but also on the side surface in the center direction (inner side) of the spiral.
  • the upper ridge 16 contacts the lower end of the other spiral tube 4 above, but the side ridge 16 contacts the outer side surface of the inner spiral tube 4 and partitions the spiral passage 7 vertically. Therefore, the flow in the vertical direction of the spiral passage 7 is also made uniform.
  • the flow path width PA which is the distance between the spiral tubes 4 and 4 arranged in the center direction of the spiral is substantially equal to the flow path width PB which is the distance between the upper and lower spiral tubes 4 and 4 (substantially the height of the protrusion 16). (Same dimension in the embodiment).
  • the ridge 16 extending in the axial direction of the spiral tube 4 is provided on the spiral tube 4, and the ridge 16 is brought into contact with another spiral tube 4 adjacent in the vertical direction or the center direction of the spiral.
  • the partition wall 3 is configured, it is not necessary to provide a special partition wall, and the spiral tube 4 is positioned, so that the number of parts can be significantly reduced.
  • the side protrusion 16 may be a protrusion 17 as shown in FIGS.
  • the protrusion 17 also has the effect of positioning the spiral tube 4.
  • 19 to 24 show an example in which only the protrusion 17 is formed on the spiral tube 4.
  • the partition wall 3 is required.
  • a protrusion 17 is formed to protrude at the upper end of the spiral tube 4, and the protrusion 17 contacts the lower end of the other upper spiral tube 4 when it is stacked in a plurality of stages.
  • the spiral 4 is in close contact (brazing) with the surface of the spiral partition wall 3 in the central direction of the spiral.
  • the protrusion 17 is formed only at the upper end of the spiral tube 4, but it may be formed on the side surface in the center direction of the spiral as in FIGS. 22 to 24.
  • the side projections 17 abut against the outer surface of the inner partition wall 3.
  • the flow path width PA (substantially the dimension of the protrusion 17 in the case of FIG. 24) which is the distance between the spiral tubes 4 and 4 arranged in the center direction of the spiral is the distance between the upper and lower spiral tubes 4 and 4.
  • the flow path width PB (substantially the height dimension of the protrusion 17) is substantially the same (same in the embodiment).
  • the spiral tube 4 As described above, if the spiral tube 4 is provided with the projection 17 and the projection 17 is brought into contact with another adjacent spiral tube 4 or the partition wall 3, the spiral tube 4 can be positioned more firmly and easily. It becomes.
  • the projection 17 may be provided not only on the spiral tube 4 but also on the partition wall 3 side.
  • FIG. 25 shows an example in which the projection 17 is formed on the partition wall 3.
  • a projection 17 projecting outward is formed on the outer surface side of the groove 11 of the wave-shaped partition wall 3 similar to FIG. It contacts the inner side of the outer spiral tube 4 (side surface in the center direction of the spiral).
  • the flow path width PA (substantially the dimension of the projection 17 in the case of FIG. 25) which is the distance between the spiral tubes 4 arranged in the center direction of the spiral and the partition wall 3 is the same between the upper and lower spiral tubes 4 and 4.
  • the channel width PB which is the interval, is substantially the same (same in the embodiment).
  • the spiral tube 4 can be positioned more firmly and easily. Become.
  • FIG. 26 and FIG. 27 show another example of the attachment structure of the spiral tube 4.
  • the inner surface of the partition wall 3 (the center of the spiral)
  • the holder 18 is attached to the direction surface.
  • the holder 18 extends in the vertical direction of the partition wall 3 and is provided at a plurality of locations so as to protrude from the partition wall 3.
  • the holding groove 19 is semicircular (curved) at intervals where the spiral tube 4 is disposed. A plurality of (the bottom of the groove is separated from the partition wall 3) is formed.
  • the spiral tube 4 is closely attached to the holding groove 19 and held. Accordingly, the spiral tube 4 is disposed in the spiral passage 7 between the inner and outer partition walls 3 and the partition wall 3 without contacting the partition wall 3.
  • the spiral tube 4 may be fixed to the holding groove 19 by welding, but may be detachably attached by fitting.
  • the spiral tube 4 is detachably attached to the holding groove 19 of the holder 18 provided on the partition wall 3, for example, when dust or scale in the first fluid adheres to the spiral tube 4 or the partition wall 3, the partition wall 3 and the spiral tube 4 can be easily disassembled and cleaned.
  • FIG. 28 to FIG. 31 show an embodiment of the spiral heat exchanger 1 of the present invention and the manufacturing method thereof.
  • the structure which is not shown by these figures shall be the same as that of each said Example.
  • the spiral tube 4 is attached to the inner surface of the partition wall 3 (the surface in the direction of the center of the spiral).
  • FIG. 28 shows the partition wall 3 in this case, in which a spiral planar shape is shown on the upper side and a side sectional shape is shown on the lower side.
  • the partition wall 3 of the embodiment has a corrugated cross-section in which grooves 21 and 22 are formed alternately on the outer surface and the inner surface (the surface on the side of the center of the spiral).
  • FIG. 29 shows the planar shape of the spiral tube 4.
  • the width dimension W of the groove 21 portion of the partition wall 3 is set to be smaller than the spiral interval R of the spiral tube 4.
  • the partition wall 3 is rotated 180 ° from FIG. 28, and the spiral tube 4 is meshed with the partition wall 3 in this state concentrically (the center of the spiral is the same) (FIG. 30).
  • the spiral tube 4 is disposed corresponding to the groove 21 of the partition wall 3.
  • FIG. 30 shows a plane on the top and a side section on the bottom.
  • the flow path width PA which is the distance between the spiral tube 4 and the partition wall 3 aligned in the center direction of the spiral, and the distance between the upper and lower spiral tubes 4 and 4 (interval of the groove 21 in the case of FIG. 31).
  • the channel width PB is substantially equivalent (same in the embodiment).
  • a continuous groove 21 is formed in the partition wall 3, and the width W of the partition wall 3 in the groove 21 portion is made smaller than the spiral interval R of the spiral tube 4 so as to correspond to the groove 21 of the partition wall 3. If the spiral tube 4 is disposed, and the partition wall 3 or the spiral tube 4 is rotated around the center of the spiral, the spiral tube 4 is brought into close contact with the groove 21, so that the partition wall 3 or the spiral tube 4 is rotated.
  • the heat exchanger 1 can be easily assembled by assembling the spiral tube 4 to the spiral partition wall 3 with an extremely simple operation.
  • FIGS. 32 to 36 show another embodiment of the method for manufacturing the spiral heat exchanger 1 of the present invention.
  • the spiral tube 4 is attached to the groove 24 of the hook 23 formed on the outer surface of the partition wall 3 (the surface on the side opposite to the center direction of the spiral).
  • the hook 23 is formed at a plurality of locations on the partition wall 3, and a C-shaped groove 24 is formed at the tip thereof (FIG. 32).
  • FIG. 33 shows the planar shape of the spiral tube 4. Also in this case, the width dimension W of the hook 23 (groove 24) portion of the partition wall 3 is set to be smaller than the spiral interval R of the spiral tube 4. Then, the spiral tube 4 is concentrically engaged with the partition wall 3 (the center of the spiral is the same) (FIG. 34). At this time, the spiral tube 4 is disposed corresponding to the groove 24 of the hook 23 of the partition wall 3.
  • the partition wall 3 and the spiral tube 4 are arranged as described above, the partition wall 3 is rotated clockwise in FIG. 34 around the center of the spiral (direction in which the inner end of the partition wall 3 is further wound). Since the wall 3 generally moves outward with respect to the spiral tube 4, the spiral tube 4 is detachably fitted into and closely attached to the groove 24 of the hook 23 on the outer surface of the partition wall 3 (FIG. 35, FIG. 36).
  • the spiral tube 4 when the spiral tube 4 is rotated, it may be rotated counterclockwise in FIG. Further, the relationship between the channel widths PA1, PA2 (PA) and PB in this case is the same as in FIG. In this way, the groove 24 is formed in the hook 23 of the partition wall 3, and the width W of the partition wall 3 in the hook 23 (groove 24) portion is made smaller than the spiral interval R of the spiral tube 4. If the spiral tube 4 is arranged corresponding to the groove 24 of the 23, and the partition wall 3 and the spiral tube 4 are rotated around the center of the spiral, the spiral tube 4 is brought into close contact with the groove 24.
  • the heat exchanger 1 can be easily assembled by assembling the spiral tube 4 to the spiral partition wall 3 by an extremely simple operation by simply rotating the wall 3 and the spiral tube 4.
  • the heat exchanger 1 capable of easily disassembling the partition wall 3 and the spiral tube 4 is manufactured. As a result, dust and scale attached to the heat exchanger 1 can be easily washed.
  • the Example demonstrated the heat exchanger which implement
  • the first fluid is cold water and the second fluid is a refrigerant.
  • the present invention is not limited to this, and the heat exchanger of the present invention can be used for heat exchange between various fluids having temperature differences.
  • Heat exchanger 2 Container 3 Partition wall (partition wall) 4 Spiral tube (spiral tube) 6 Lid 7 Spiral path 8, 9 Header 11, 21, 24 Groove 12 Projection 13 Partition wall 14 Spiral tube 15 Extrusion material 16 Projection 17 Projection 18 Holder 19 Holding groove 23 Hook

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

Abstract

[Problem] To provide a heat exchanger which comprises a spiral partition wall and a spiral pipe and which can be assembled with improved work efficiency. [Solution] A heat exchanger has a spiral passage which is formed between adjacent turns of a spiral partition wall (3) provided within a container, a spiral pipe (4) having turns is disposed in the spiral passage with the turns arranged in vertical tiers, and a first fluid which flows through the spiral passage outside the spiral pipe and a second fluid which flows through the inside of the spiral pipe are caused to exchange heat. A groove (21) is formed in the partition wall, the width (W) of the portion of the partition wall which corresponds to the groove is set to be less than the distance (R) between adjacent turns of the spiral pipe, the spiral pipe is provided corresponding to the groove in the partition wall, and the spiral pipe is made to be in close contact with the groove by rotating the partition wall and/or the spiral pipe about the center of the spiral.

Description

熱交換器及び熱交換器の製造方法HEAT EXCHANGER AND HEAT EXCHANGER MANUFACTURING METHOD
 本発明は、渦巻状に流れる第一流体と第二流体とを熱交換させる熱交換器及びその製造方法に関する。 The present invention relates to a heat exchanger for exchanging heat between a first fluid and a second fluid flowing in a spiral shape, and a method for manufacturing the same.
 温度の異なる第一流体と第二流体とを熱交換させるに当たり、円筒状の容器内に渦巻状の仕切板を設けて仕切板間に渦巻通路を構成し、この渦巻通路に渦巻管を複数段配置し、渦巻通路に第一流体を、渦巻管内に第二流体をそれぞれ流して熱交換させる渦巻型熱交換器が知られている(例えば、特許文献1参照)。 In exchanging heat between the first fluid and the second fluid having different temperatures, a spiral partition plate is provided in a cylindrical container to form a spiral passage between the partition plates, and a plurality of spiral tubes are provided in the spiral passage. There is known a spiral heat exchanger that is arranged to exchange heat by flowing a first fluid in a spiral passage and a second fluid in a spiral tube (see, for example, Patent Document 1).
 この場合、第一流体と第二流体とは対向流となる。そして、係る構成によれば、熱交換効率が高くコンパクトな熱交換器とすることができる利点があった。 In this case, the first fluid and the second fluid are counterflows. And according to the structure which concerns, there existed an advantage which can be set as a compact heat exchanger with high heat exchange efficiency.
特開2006-162157号公報JP 2006-162157 A
 しかしながら、渦巻状の仕切板と渦巻管とを組み付ける作業は繁雑であり、改善が望まれていた。また、渦巻通路には第一流体に含まれる塵埃やスケールが付着するようになるが、渦巻管が存在する仕切板間の渦巻通路を洗浄する作業は極めて困難なものとなっていた。 However, the work of assembling the spiral partition plate and the spiral tube is complicated, and improvement has been desired. In addition, although dust and scale contained in the first fluid are attached to the spiral passage, it is extremely difficult to clean the spiral passage between the partition plates where the spiral pipe is present.
 本発明は、係る従来の技術的課題を解決するために成されたものであり、渦巻状の仕切壁と渦巻管から成る熱交換器の組立作業性を改善した熱交換器、及び、熱交換器の製造方法を提供することを目的とする。 The present invention has been made to solve the conventional technical problems, and is a heat exchanger that improves the assembly workability of a heat exchanger composed of a spiral partition wall and a spiral tube, and heat exchange It aims at providing the manufacturing method of a vessel.
 上記課題を解決するために、請求項1の発明の熱交換器は、容器内に設けられた渦巻状の仕切壁間に渦巻通路を構成し、この渦巻通路に渦巻管を上下複数段配置してこの渦巻管外側の渦巻通路を流れる第一流体と渦巻管内を流れる第二流体とを熱交換させるものであって、仕切壁に形成された溝を備え、この溝部分の仕切壁の幅寸法Wは、渦巻管の渦巻の間隔Rより小さく構成されており、渦巻管は、仕切壁の溝に対応された状態で、仕切壁、及び/又は、渦巻管が、渦巻の中心を軸として回転されることで、溝に密着されていることを特徴とする。 In order to solve the above problems, the heat exchanger of the invention of claim 1 comprises a spiral passage between spiral partition walls provided in a container, and a plurality of spiral tubes are arranged in the spiral passage in the upper and lower stages. The first fluid flowing in the spiral passage outside the lever tube and the second fluid flowing in the spiral tube are heat-exchanged, and have a groove formed in the partition wall, and the width dimension of the partition wall of the groove portion W is configured to be smaller than the spiral interval R of the spiral tube. The spiral tube corresponds to the groove of the partition wall, and the partition wall and / or the spiral tube rotates about the center of the spiral. By being done, it is closely_contact | adhered to the groove | channel.
 請求項2の発明の熱交換器は、上記発明において渦巻管は仕切壁の溝に着脱可能に嵌合されていることを特徴とする。 The heat exchanger of the invention of claim 2 is characterized in that, in the above invention, the spiral tube is detachably fitted in the groove of the partition wall.
 請求項3の発明の熱交換器の製造方法は、容器内に設けられた渦巻状の仕切壁間に渦巻通路を構成し、この渦巻通路に渦巻管を上下複数段配置してこれら渦巻管外側の渦巻通路を流れる第一流体と渦巻管内を流れる第二流体とを熱交換させる熱交換器を製造するに当たり、仕切壁に溝を形成し、この溝部分の仕切壁の幅寸法Wを渦巻管の渦巻の間隔Rより小さくし、仕切壁の溝に対応させて渦巻管を配置し、仕切壁、及び/又は、渦巻管を、渦巻の中心を軸として回転させることで、溝に渦巻管を密着させることを特徴とする。 According to a third aspect of the present invention, there is provided a heat exchanger manufacturing method in which a spiral passage is formed between spiral partition walls provided in a container, and a plurality of spiral tubes are arranged in the spiral passage so that the outside of the spiral tube is outside. In manufacturing a heat exchanger for exchanging heat between the first fluid flowing through the spiral passage and the second fluid flowing through the spiral tube, a groove is formed in the partition wall, and the width dimension W of the partition wall of this groove portion is defined as the spiral tube. A spiral tube is arranged corresponding to the groove of the partition wall, and the partition wall and / or the spiral tube is rotated about the center of the spiral, so that the spiral tube is placed in the groove. It is characterized by being in close contact.
 請求項4の発明の熱交換器の製造方法は、上記発明において渦巻管を仕切壁の溝に着脱可能に嵌合させることを特徴とする。 According to a fourth aspect of the present invention, there is provided a heat exchanger manufacturing method, wherein the spiral tube is detachably fitted in a groove of the partition wall in the above invention.
 請求項1及び請求項3の発明によれば、容器内に設けられた渦巻状の仕切壁間に渦巻通路を構成し、この渦巻通路に渦巻管を上下複数段配置してこれら渦巻管外側の渦巻通路を流れる第一流体と渦巻管内を流れる第二流体とを熱交換させる熱交換器において、仕切壁に溝を形成し、この溝部分の仕切壁の幅寸法Wを渦巻管の渦巻の間隔Rより小さくし、仕切壁の溝に対応させて渦巻管を配置し、仕切壁、及び/又は、渦巻管を、渦巻の中心を軸として回転させることで、溝に渦巻管を密着させるようにしたので、仕切壁や渦巻管を回転させるだけの極めて簡単な操作で、渦巻状の仕切壁に渦巻管を組み付け、熱交換器を容易に組み立てることが可能となる。 According to the first and third aspects of the present invention, the spiral passage is formed between the spiral partition walls provided in the container, and the spiral tubes are arranged in a plurality of upper and lower stages in the spiral passage, and the outer sides of the spiral tubes are arranged. In the heat exchanger for exchanging heat between the first fluid flowing in the spiral passage and the second fluid flowing in the spiral tube, a groove is formed in the partition wall, and the width dimension W of the partition wall of the groove portion is defined as the space between the spirals of the spiral tube. The spiral tube is arranged so as to be smaller than R and corresponding to the groove of the partition wall, and the partition wall and / or the spiral tube is rotated about the center of the spiral so that the spiral tube is in close contact with the groove. Therefore, the heat exchanger can be easily assembled by assembling the spiral tube to the spiral partition wall by an extremely simple operation by simply rotating the partition wall and the spiral tube.
 この場合、請求項2や請求項4の発明の如く渦巻管を仕切壁の溝に着脱可能に嵌合させるようにすれば、仕切壁部と渦巻管部とを容易に分解することができる熱交換器を製造することができるようになり、熱交換器に付着した塵埃やスケールを容易に洗浄することが可能となる。 In this case, if the spiral tube is detachably fitted into the groove of the partition wall as in the inventions of claim 2 and claim 4, the heat that can easily decompose the partition wall portion and the spiral tube portion. The exchanger can be manufactured, and dust and scale attached to the heat exchanger can be easily washed.
本発明を適用する一実施例の熱交換器の分解斜視図である。It is a disassembled perspective view of the heat exchanger of one Example to which this invention is applied. 図1の熱交換器内部の平面図である。It is a top view inside the heat exchanger of FIG. 図1の熱交換器の第一流体及び第二流体の流れを説明する図である。It is a figure explaining the flow of the 1st fluid of the heat exchanger of Drawing 1, and the 2nd fluid. 図1の熱交換器の要部拡大断面図である。It is a principal part expanded sectional view of the heat exchanger of FIG. 図4中の流路幅PB/流路幅PAと熱交換量との関係を示す図である。It is a figure which shows the relationship between the flow path width PB / flow path width PA in FIG. 4, and the amount of heat exchange. 他の実施例の熱交換器の要部拡大断面図である。It is a principal part expanded sectional view of the heat exchanger of another Example. 図6に対応する位置の図1の熱交換器の要部拡大断面図である。It is a principal part expanded sectional view of the heat exchanger of FIG. 1 of the position corresponding to FIG. 更に他の実施例の熱交換器の要部拡大断面図である。It is a principal part expanded sectional view of the heat exchanger of other Example. 更に他の実施例の熱交換器の要部拡大断面図である。It is a principal part expanded sectional view of the heat exchanger of other Example. 図9の要部拡大図である。It is a principal part enlarged view of FIG. 更に他の実施例の熱交換器の渦巻管の斜視図である。It is a perspective view of the spiral tube of the heat exchanger of further another Example. 図11の渦巻管の正面図である。It is a front view of the spiral tube of FIG. 図11の渦巻管で仕切壁を構成した状態の熱交換器の要部拡大断面図である。It is a principal part expanded sectional view of the heat exchanger of the state which comprised the partition wall with the spiral pipe of FIG. 更に他の実施例の熱交換器の渦巻管の斜視図である。It is a perspective view of the spiral tube of the heat exchanger of further another Example. 図14の渦巻管の正面図である。It is a front view of the spiral tube of FIG. 図14の渦巻管で仕切壁を構成した状態の熱交換器の要部拡大断面図である。It is a principal part expanded sectional view of the heat exchanger of the state which comprised the partition wall with the spiral pipe of FIG. 更に他の実施例の熱交換器の渦巻管の斜視図である。It is a perspective view of the spiral tube of the heat exchanger of further another Example. 図17の渦巻管の正面図である。It is a front view of the spiral pipe of FIG. 更に他の実施例の熱交換器の渦巻管の斜視図である。It is a perspective view of the spiral tube of the heat exchanger of further another Example. 図19の渦巻管の正面図である。FIG. 20 is a front view of the spiral tube of FIG. 19. 図19の渦巻管で構成した熱交換器の要部拡大断面図である。It is a principal part expanded sectional view of the heat exchanger comprised with the spiral tube of FIG. 更に他の実施例の熱交換器の渦巻管の斜視図である。It is a perspective view of the spiral tube of the heat exchanger of further another Example. 図22の渦巻管の正面図である。It is a front view of the spiral tube of FIG. 図22の渦巻管で構成した熱交換器の要部拡大断面図である。It is a principal part expanded sectional view of the heat exchanger comprised with the spiral pipe of FIG. 更に他の実施例の熱交換器の要部拡大断面図である。It is a principal part expanded sectional view of the heat exchanger of other Example. 更に他の実施例の熱交換器の要部拡大断面図である。It is a principal part expanded sectional view of the heat exchanger of other Example. 図26の熱交換器の要部斜視図である。It is a principal part perspective view of the heat exchanger of FIG. 本発明の熱交換器の製造方法の一実施例を説明する仕切壁の平面図である。It is a top view of the partition wall explaining one Example of the manufacturing method of the heat exchanger of this invention. 図28の方法を説明する渦巻管の平面図である。It is a top view of the spiral tube explaining the method of FIG. 図28の方法を説明する仕切壁と渦巻管の配置図である。FIG. 29 is a layout diagram of a partition wall and a spiral tube for explaining the method of FIG. 28. 図28の方法で組み立てられた熱交換器の平面図である。It is a top view of the heat exchanger assembled by the method of FIG. 本発明の熱交換器の製造方法の他の実施例を説明する仕切壁の平面図である。It is a top view of the partition wall explaining the other Example of the manufacturing method of the heat exchanger of this invention. 図32の方法を説明する渦巻管の平面図である。It is a top view of the spiral tube explaining the method of FIG. 図32の方法を説明する仕切壁と渦巻管の配置図である。It is a layout of the partition wall and the spiral tube for explaining the method of FIG. 図32の方法で組み立てられた熱交換器の平面図である。It is a top view of the heat exchanger assembled by the method of FIG. 図35の熱交換器のA-A線断面図である。FIG. 36 is a cross-sectional view of the heat exchanger of FIG. 35 taken along line AA.
 以下、本発明の実施の形態について、図面に基づき詳細に説明する。 Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
 図1において、1は本発明を適用可能な実施例である渦巻型の熱交換器であり、図中において上下が開口した円筒状の容器2と、渦巻状の仕切壁部としての仕切壁3と、渦巻管部としての渦巻管4と、蓋6、6とから構成されている。これら容器2、仕切壁3、渦巻管4及び蓋6は何れもアルミニウム等の金属製であり、渦巻管4は仕切壁3の内側に複数段配置され、溶接により密着されている。そして、この渦巻管4が複数段密着された仕切壁3が容器2内に配置され、容器2の上下の開口を蓋6、6にて閉塞することにより構成されている。 In FIG. 1, reference numeral 1 denotes a spiral heat exchanger which is an embodiment to which the present invention can be applied. In the figure, a cylindrical container 2 having an open top and bottom, and a partition wall 3 as a spiral partition wall portion. And a spiral tube 4 as a spiral tube portion and lids 6 and 6. The container 2, the partition wall 3, the spiral tube 4 and the lid 6 are all made of metal such as aluminum, and the spiral tube 4 is arranged in a plurality of stages inside the partition wall 3 and is in close contact by welding. A partition wall 3 in which the spiral tubes 4 are in close contact with each other is arranged in the container 2, and the upper and lower openings of the container 2 are closed by lids 6 and 6.
 この場合、仕切壁3の上下端は蓋6、6の内面に密着してそれらの間が封止される。これにより、渦巻状の仕切壁3間には、渦巻の中心から回転しながら外側に向かう一連の渦巻通路7が構成される。渦巻管4はこの渦巻通路7内に位置して当該渦巻通路7内の空間と接するように配置される。これにより、渦巻管4は渦巻通路7内を流れる流体(後述する第一流体)と接することになる。また、複数段の渦巻管4は相互に間隔を存して配置されており、図2に示すように各渦巻管4の外側の端部はヘッダ8で連通され、渦巻の中心側の端部もヘッダ9で連通されている。 In this case, the upper and lower ends of the partition wall 3 are in close contact with the inner surfaces of the lids 6 and 6, and the space between them is sealed. As a result, a series of spiral passages 7 are formed between the spiral partition walls 3 toward the outside while rotating from the center of the spiral. The spiral tube 4 is disposed in the spiral passage 7 so as to be in contact with the space in the spiral passage 7. As a result, the spiral tube 4 comes into contact with a fluid (first fluid described later) flowing in the spiral passage 7. Further, the spiral tubes 4 in a plurality of stages are spaced from each other, and as shown in FIG. 2, the outer ends of the spiral tubes 4 are communicated with each other by a header 8, and the end portion on the center side of the spiral Are also communicated by the header 9.
 そして、熱交換器1が例えばランキンサイクルにおける冷媒の凝縮器として使用される場合、渦巻通路7には渦巻の中心から、第一流体としての例えば冷水が熱交換器1内に流入する。そして、渦巻通路7を図3中太矢印で示すように渦巻の中心から外側に向けて回転しながら流れ、容器2の側面から熱交換器1外に流出する。また、ヘッダ8からは第二流体としての例えば高温の冷媒が流入し、各渦巻管4内を図3中細矢印で示すように外側から渦巻の中心に向けて回転しながら流れ、ヘッダ9から熱交換器1外に流出する。 When the heat exchanger 1 is used as, for example, a refrigerant condenser in the Rankine cycle, cold water as the first fluid flows into the heat exchanger 1 from the center of the spiral in the spiral passage 7. Then, the spiral passage 7 flows while rotating outward from the center of the spiral as indicated by a thick arrow in FIG. 3, and flows out of the heat exchanger 1 from the side surface of the container 2. Further, for example, a high-temperature refrigerant as the second fluid flows from the header 8 and flows in each spiral tube 4 while rotating from the outside toward the center of the spiral as indicated by a thin arrow in FIG. It flows out of the heat exchanger 1.
 このとき、冷水(第一流体)の流れは図3中反時計回りとなり、冷媒(第二流体)の流れは逆に時計回りとなるので、冷水と冷媒の流れは相互に対向流となる。そのため、渦巻管4内を流れる冷媒と、その外側の渦巻通路7内を流れる水との温度差が入口側のヘッダ8から出口側のヘッダ9に渡る全範囲に渡って大きくなり、熱交換性能が向上する。特に、渦巻管4内を冷媒(第二流体)が流れるため、高圧冷媒が流れても高耐圧設計が容易となる。 At this time, the flow of the cold water (first fluid) is counterclockwise in FIG. 3, and the flow of the refrigerant (second fluid) is counterclockwise, so the flows of the cold water and the refrigerant are opposite to each other. Therefore, the temperature difference between the refrigerant flowing in the spiral tube 4 and the water flowing in the outer spiral passage 7 increases over the entire range from the header 8 on the inlet side to the header 9 on the outlet side. Will improve. In particular, since the refrigerant (second fluid) flows through the spiral tube 4, high pressure resistance design is facilitated even when a high-pressure refrigerant flows.
 次に、図4を参照しながら仕切壁3と渦巻通路7及び渦巻管4の構造について説明する。仕切壁3は、平板に複数条の湾曲して凹陥する溝11を平行に形成して断面波状とし、当該平板を渦巻状に加工して構成されている。そして、各渦巻管4はこの仕切壁3の各溝11の内側にそれぞれ対応して配置され、溝11の湾曲面を利用して密着された後、ろう付けすることで仕切壁3と複数段の渦巻管4が一体化される。その後、各渦巻管4の外側の端部にヘッダ8が溶接され、出口側の端部にヘッダ9が溶接されるものである。 Next, the structure of the partition wall 3, the spiral passage 7, and the spiral tube 4 will be described with reference to FIG. The partition wall 3 is formed by forming in parallel a plurality of curved grooves 11 that are curved and recessed in a flat plate to have a corrugated cross section, and processing the flat plate into a spiral shape. And each spiral tube 4 is arrange | positioned corresponding to the inner side of each groove | channel 11 of this partition wall 3, respectively, after making close_contact | adherence using the curved surface of the groove | channel 11, it braces and separates the partition wall 3 and several steps. The spiral tube 4 is integrated. Thereafter, the header 8 is welded to the outer end portion of each spiral tube 4, and the header 9 is welded to the end portion on the outlet side.
 実施例の熱交換器1では、仕切壁3及び渦巻管4の渦巻の中心方向が水平方向であり、それに直交する上下の方向が垂直方向とされる。また、上下の渦巻管4、4間には所定の間隔(流路幅PB)が構成されており、渦巻管4とその内方(渦巻の中心方向)の仕切壁3(溝11の外側に張り出した外面)との間にも間隔(流路幅PA)が構成されている(図4)。即ち、流路幅PAは、渦巻管4の渦巻の中心方向と平行となる方向(水平方向)の当該渦巻管4外側を冷水(第一流体)が流れる渦巻通路7の幅であり、流路幅PBは、渦巻管4の渦巻の中心方向と直交する方向の当該渦巻管4外側を冷水(第一流体)が流れる渦巻通路4の幅となる。 In the heat exchanger 1 of the embodiment, the center direction of the vortex of the partition wall 3 and the vortex tube 4 is the horizontal direction, and the vertical direction perpendicular thereto is the vertical direction. Further, a predetermined interval (flow path width PB) is formed between the upper and lower spiral tubes 4 and 4, and the partition wall 3 (in the direction of the center of the spiral) and the partition wall 3 (on the outside of the groove 11). A space (flow path width PA) is also formed between the outer surface and the protruding outer surface (FIG. 4). That is, the channel width PA is the width of the spiral passage 7 in which cold water (first fluid) flows outside the spiral tube 4 in a direction (horizontal direction) parallel to the center direction of the spiral of the spiral tube 4. The width PB is the width of the spiral passage 4 through which cold water (first fluid) flows outside the spiral tube 4 in the direction orthogonal to the center direction of the spiral of the spiral tube 4.
 そして、実施例の熱交換器1では、流路幅PA=流路幅PBに設定している。ここで、図5は流路幅PAに対する流路幅PBの比率(流路幅PB/流路幅PA)を変化させた場合の冷媒(第二流体)と冷水(第一流体)との熱交換量の変化を示している。この図から明らかな如く、比率=1(流路幅PB=流路幅PA)を頂点として、その前後で熱交換量は低下している。 And in the heat exchanger 1 of an Example, it sets to channel width PA = channel width PB. Here, FIG. 5 shows the heat of the refrigerant (second fluid) and cold water (first fluid) when the ratio of the channel width PB to the channel width PA (channel width PB / channel width PA) is changed. The change in the exchange amount is shown. As is apparent from this figure, the amount of heat exchange decreases before and after the ratio = 1 (flow path width PB = flow path width PA).
 その理由は、流路幅PAに対して流路幅PBが小さくなると、渦巻管4とその内方の仕切壁3との間の渦巻通路7内を冷水(第一流体)が流れ易くなり、上下の渦巻管4の間の渦巻通路7内は流れ難くなって、渦巻管4の伝熱面積を有効に活用できなくなるからである。また、これは流路幅PBが流路幅PAに対して大きくなる場合も同様であり、その場合は、渦巻管4とその内方の仕切壁3との間の渦巻通路7内を冷水(第一流体)が流れ難くなり、上下の渦巻管4の間の渦巻通路7内を流れ易くなって、渦巻管4の伝熱面積を有効に活用できなくなるからである。 The reason is that when the flow path width PB is smaller than the flow path width PA, the cold water (first fluid) easily flows in the spiral passage 7 between the spiral tube 4 and the inner partition wall 3. This is because it becomes difficult to flow in the spiral passage 7 between the upper and lower spiral tubes 4 and the heat transfer area of the spiral tube 4 cannot be effectively used. This also applies to the case where the flow path width PB becomes larger than the flow path width PA. In this case, the inside of the spiral passage 7 between the spiral tube 4 and the inner partition wall 3 is cooled with cold water ( This is because it becomes difficult for the first fluid) to flow, and it becomes easy to flow in the spiral passage 7 between the upper and lower spiral tubes 4, and the heat transfer area of the spiral tube 4 cannot be effectively used.
 実施例のように流路幅PAを流路幅PBを同一とすることで、渦巻管4の渦巻の中心方向(内方)の渦巻通路7の流路幅PAと、それと直交する方向(上下)の渦巻通路7の流路幅PBが同一となり、渦巻管4の外側に密着している仕切壁3とその外方(渦巻の中心方向と反対方向)の渦巻管4との間の流路幅PAも同一となる。これにより、渦巻管4の全周の外側を冷水(第一流体)が満遍なく流れるようになるので、渦巻管4の伝熱面積を最大限利用した冷媒(第二流体)と冷水(第一流体)との熱交換が行われるようになる。 By making the flow path width PA the same as the flow path width PB as in the embodiment, the flow path width PA of the spiral passage 7 in the center direction (inward) of the spiral of the spiral tube 4 and the direction (vertical) The flow path width PB of the spiral passage 7 is the same, and the flow path is between the partition wall 3 that is in close contact with the outside of the spiral tube 4 and the spiral tube 4 on the outside (opposite direction to the center of the spiral). The width PA is also the same. As a result, cold water (first fluid) flows evenly outside the entire circumference of the spiral tube 4, so that the refrigerant (second fluid) and cold water (first fluid) that make the most of the heat transfer area of the spiral tube 4 are used. ) And heat exchange.
 尚、実施例では流路幅PA=流路幅PBとしたが、図5から明らかな如く、流路幅PB/流路幅PAの比率が、0.7以上1.3以下の範囲であれば、デッドスペースを増やすことなく比較的高い熱交換量を確保できる。その理由は以下の如くである。即ち、熱交換量のピークは1であるので、0.98以上が高い熱交換量であるものと規定すると、流路幅PB/流路幅PAの比率が0.7未満の場合には、第一流体(冷水)の流路が十分ではないため、熱交換量が十分ではなく、0.98未満となる。そのため、流路幅PB/流路幅PAの比率の下限はこの0.7となる。一方、流路幅PB/流路幅PAの比率が2.3程になるまで熱交換量は0.98以上を維持しているが、比率が1.3以上となると、流路幅PBが拡大して渦巻流路7にデッドスペースが生じ、熱交換器1の寸法が無用に拡大して能力とスペースの面で非効率となる。そこで、流路幅PB/流路幅PAの比率の上限はこの1.3となる。 In the embodiment, the flow path width PA is equal to the flow path width PB. However, as is apparent from FIG. 5, the ratio of the flow path width PB / the flow path width PA is in the range of 0.7 to 1.3. Thus, a relatively high heat exchange amount can be secured without increasing the dead space. The reason is as follows. That is, since the peak of the heat exchange amount is 1, if it is defined that 0.98 or more is a high heat exchange amount, when the ratio of the channel width PB / channel width PA is less than 0.7, Since the flow path of the first fluid (cold water) is not sufficient, the amount of heat exchange is not sufficient, and is less than 0.98. Therefore, the lower limit of the ratio of the channel width PB / channel width PA is 0.7. On the other hand, the heat exchange amount is maintained at 0.98 or more until the ratio of the channel width PB / channel width PA is about 2.3, but when the ratio is 1.3 or more, the channel width PB is As a result, the dead space is generated in the spiral flow path 7, and the size of the heat exchanger 1 is unnecessarily enlarged, resulting in inefficiency in terms of capacity and space. Therefore, the upper limit of the ratio of the channel width PB / channel width PA is 1.3.
 このように、渦巻管4の渦巻の中心方向と平行となる方向の当該渦巻管4外側を冷水(第一流体)が流れる渦巻通路7の流路幅PAと、渦巻管4の渦巻の中心方向と直交する方向の当該渦巻管4外側を冷水(第一流体)が流れる渦巻通路7の流路幅PBとを略同等とすることで、渦巻管4の外側を冷水(第一流体)が流れる渦巻通路7の流路幅を、渦巻管4の略全周において略同等とすることができるようになる。即ち、渦巻管4周囲の渦巻通路7の流路幅は渦巻管4の軸を中心として、渦巻管4と同心円を描くようになり、冷水(第一流体)が渦巻管4の外側全周に満遍なく流れるようになるので、渦巻管4の伝熱面積を十分に活用し、冷水(第一流体)と冷媒(第二流体)との熱交換性能の大幅な改善を図ることができる。 Thus, the flow path width PA of the spiral passage 7 through which the cold water (first fluid) flows outside the spiral tube 4 in the direction parallel to the spiral center direction of the spiral tube 4 and the center direction of the spiral of the spiral tube 4 The flow path width PB of the spiral passage 7 through which the cold water (first fluid) flows outside the spiral tube 4 in the direction perpendicular to the spiral pipe 4 is made substantially equal, so that the cold water (first fluid) flows outside the spiral tube 4. The flow path width of the spiral passage 7 can be made substantially equal over substantially the entire circumference of the spiral tube 4. That is, the flow path width of the spiral passage 7 around the spiral tube 4 is drawn concentrically with the spiral tube 4 around the axis of the spiral tube 4, and cold water (first fluid) is distributed around the entire circumference of the spiral tube 4. Since it flows evenly, the heat transfer area of the spiral tube 4 can be fully utilized, and the heat exchange performance between the cold water (first fluid) and the refrigerant (second fluid) can be greatly improved.
 特に、流路幅PAに対する流路幅PBの比(流路幅PB/流路幅PA)を、前述の如く0.7以上1.3以下とし、好ましくは実施例のように流路幅PA=流路幅PBとすることで、渦巻管4の外側における冷水(第一流体)の流れを効果的に均一化し、第一流体(冷水)と第二流体(冷媒)との熱交換量を一定値以上(0.98以上)として熱交換性能の向上を図ることが可能となる。 In particular, the ratio of the channel width PB to the channel width PA (channel width PB / channel width PA) is set to 0.7 to 1.3 as described above, and preferably the channel width PA as in the embodiment. = By making the flow path width PB, the flow of cold water (first fluid) outside the spiral tube 4 is effectively uniformed, and the heat exchange amount between the first fluid (cold water) and the second fluid (refrigerant) is reduced. It becomes possible to improve the heat exchange performance as a certain value or more (0.98 or more).
 次に、図6は他の形状の仕切壁3を用いた実施例の熱交換器1を示している。この実施例では仕切壁3を断面波状としている。図4の実施例の場合、図7にXで示す隣接する渦巻管4、4から最も遠くなる位置の部分、即ち、上下の渦巻管4、4間の渦巻の中心方向の部分Xでは、内方の仕切壁3と渦巻管4との間隔が広くなってしまうため、この部分Xだけが流路幅がどうしても広くなり、より多くの冷水(第一流体)が流れようとする。 Next, FIG. 6 shows a heat exchanger 1 of an embodiment using a partition wall 3 having another shape. In this embodiment, the partition wall 3 has a corrugated cross section. In the case of the embodiment of FIG. 4, in the portion farthest from the adjacent spiral tubes 4, 4 indicated by X in FIG. 7, that is, in the portion X in the center direction of the spiral between the upper and lower spiral tubes 4, 4, Since the space between the partition wall 3 and the spiral tube 4 becomes wider, the flow path width of this portion X is inevitably increased, and more cold water (first fluid) tends to flow.
 そこで、この実施例では上下の渦巻管4、4の中間の位置(高さ)の内方(渦巻の中心方向)の仕切壁3を、外側の渦巻管4、4間に向けて突出させ、突出部12を形成し、仕切壁3をこの突出部12を有した断面波状と成している。これにより、部分Xの流路幅も流路幅PA=PBとし、或いは、それらに近づけることができるようになり、渦巻管4の全周において、第一流体が流れる渦巻通路7の流路幅をより一層均一化し、満遍なく渦巻管4の全周に冷水(第一流体)を流して熱交換性能の改善を図ることができるようになる。 Therefore, in this embodiment, the partition wall 3 in the middle (in the direction of the center of the spiral) of the middle position (height) between the upper and lower spiral tubes 4, 4 is projected toward the outer spiral tubes 4, 4, A protruding portion 12 is formed, and the partition wall 3 has a corrugated cross section having the protruding portion 12. As a result, the flow path width of the portion X can be set to or close to the flow path width PA = PB, and the flow path width of the spiral passage 7 through which the first fluid flows in the entire circumference of the spiral tube 4. The heat exchange performance can be improved by making cold water (first fluid) flow all over the circumference of the spiral tube 4 evenly.
 次に、図8はもう一つの他の実施例の熱交換器1を示している。この実施例では内外の仕切壁3と仕切壁3の間の渦巻通路7内に、仕切壁3と接すること無く渦巻管4を配置している。この場合、渦巻管4は例えば図26、図27に示す保持具18と同様の構造の図示しない保持具を用いて仕切壁3から離間して保持される。このような構成とすることで、渦巻管4の全周に接して冷水(第一流体)が流れることになるので、渦巻管4内を流れる冷媒(第二流体)は渦巻管4の全周を利用して渦巻通路7内を流れる冷水(第一流体)と熱交換することができるようになる。 Next, FIG. 8 shows another example of the heat exchanger 1. In this embodiment, the spiral tube 4 is disposed in the spiral passage 7 between the inner and outer partition walls 3 and the partition wall 3 without contacting the partition wall 3. In this case, the spiral tube 4 is held away from the partition wall 3 by using a holder (not shown) having the same structure as the holder 18 shown in FIGS. 26 and 27, for example. With such a configuration, since cold water (first fluid) flows in contact with the entire circumference of the spiral tube 4, the refrigerant (second fluid) that flows in the spiral tube 4 flows around the entire circumference of the spiral tube 4. It becomes possible to exchange heat with the cold water (first fluid) flowing in the spiral passage 7 by using.
 しかしながら、冷水(第一流体)は熱交換器1の中心から外側に向かって渦巻通路7内を流れるため、渦巻の中心方向とは逆方向にかかる遠心力で渦巻通路7を構成する外側の仕切壁3寄りに多く流れようとする。そのため、内外の仕切壁3、3間の渦巻通路7の中央に渦巻管4を配置すると、当該渦巻管4の内側よりも外側の仕切壁3との間の流路に多く冷水(第一流体)が流れ、渦巻管4の伝熱面積の有効活用が阻害されてしまう。 However, since the cold water (first fluid) flows in the spiral passage 7 from the center of the heat exchanger 1 to the outside, the outer partition that forms the spiral passage 7 by centrifugal force applied in the direction opposite to the center direction of the spiral. Try to flow a lot closer to wall 3. Therefore, when the spiral tube 4 is disposed in the center of the spiral passage 7 between the inner and outer partition walls 3 and 3, a large amount of cold water (first fluid) is formed in the flow path between the inner partition wall 3 and the outer partition wall 3. ) Flows and the effective use of the heat transfer area of the spiral tube 4 is hindered.
 そこで、この実施例では渦巻管4の渦巻の中心側の流路幅をPA1、渦巻の外側の流路幅をPA2とし(PA1+PA2=PA=PB)、更に流路幅PA1と流路幅PA2の関係を、流路幅PA2<流路幅PA1としている。これにより、遠心力により多く流れようとする渦巻管4の外側の冷水(第一流体)と、渦巻の中心側の冷水(第一流体)の流れを均一化することができるようになり、熱交換性能の改善が図られる。 Therefore, in this embodiment, the flow path width on the spiral side of the spiral tube 4 is PA1, the flow path width outside the spiral is PA2 (PA1 + PA2 = PA = PB), and further, the flow path width PA1 and the flow path width PA2 are set. The relationship is channel width PA2 <channel width PA1. As a result, the flow of the cold water (first fluid) outside the spiral tube 4 that tends to flow more due to centrifugal force and the flow of the cold water (first fluid) on the center side of the spiral can be made uniform. The exchange performance is improved.
 次に、図9、図10はもう一つの他の実施例を示している。この実施例は、上述した各実施例における仕切壁3及び渦巻管4に相当する仕切壁部13及び渦巻管部14を、アルミニウム等の金属の押出成形により、押出材15に一体に構成した例である。実施例の押出材15には、内部に断面円形の流路を有する渦巻管部14が上下複数段形成されており、各渦巻管部14が仕切壁部13により相互に接続された構成とされている。 Next, FIGS. 9 and 10 show another embodiment. In this embodiment, the partition wall portion 13 and the spiral tube portion 14 corresponding to the partition wall 3 and the spiral tube 4 in each of the embodiments described above are integrally formed on the extruded material 15 by extrusion molding of a metal such as aluminum. It is. The extruded material 15 of the embodiment is formed with a plurality of upper and lower spiral tube portions 14 having a circular passage in the inside, and the spiral tube portions 14 are connected to each other by a partition wall portion 13. ing.
 そして、係る平板状の押出材15を渦巻状に巻回することにより、内外の仕切壁部13及び渦巻管部14の間に渦巻通路7を構成する。そしてこの場合も、渦巻管部14の渦巻の中心方向と平行となる方向の渦巻管部14外側の渦巻通路7の流路幅PAは、渦巻管部14の渦巻の中心方向と直交する方向の渦巻管部14外側の渦巻通路7の流路幅PB(実質的に上下の渦巻管部14、14を接続する仕切壁部13の高さ寸法)と略同等(実施例では同一)とされている(図10)。 And the spiral channel | path 7 is comprised between the inner and outer partition wall part 13 and the spiral pipe part 14 by winding the flat extrusion material 15 which concerns in a spiral shape. Also in this case, the flow path width PA of the spiral passage 7 outside the spiral tube portion 14 in the direction parallel to the spiral center direction of the spiral tube portion 14 is in a direction orthogonal to the spiral center direction of the spiral tube portion 14. The flow path width PB of the spiral passage 7 outside the spiral tube portion 14 (substantially the height dimension of the partition wall portion 13 connecting the upper and lower spiral tube portions 14, 14) is substantially equivalent (same in the embodiment). (FIG. 10).
 このように、仕切壁部13と渦巻管部14を一体に押出成形することにより、前述の実施例のように仕切壁を成形して渦巻状に巻回し、複数の渦巻管を渦巻状に巻回し、それらを仕切壁の所定位置に密着させるという作業が、押出成形と巻回という単純な作業に集約されるので、部品点数の削減と組立作業性の著しい改善を図ることが可能となる。 Thus, by integrally extruding the partition wall portion 13 and the spiral tube portion 14, the partition wall is formed and spirally wound as in the above-described embodiment, and a plurality of spiral tubes are wound spirally. The operations of turning and bringing them into close contact with a predetermined position of the partition wall are integrated into simple operations of extrusion molding and winding, so that the number of parts can be reduced and the assembly workability can be remarkably improved.
 次に、図11乃至図18はもう一つの他の実施例を示している。この実施例では、渦巻管4の上端に突条16が一体に形成されている(図11、図12)。突条16は渦巻管4の軸方向に延在して壁状に起立形成されており、渦巻管4を上下に複数段重ねたときに、突条16の上端は上方の他の渦巻管4の下端に当接し、密着されている(図13)。これによって内外の突条16及び渦巻管4の間に渦巻通路7が形成されるので、この場合は渦巻管4とその突条16により仕切壁部が構成されることになる。 Next, FIGS. 11 to 18 show another embodiment. In this embodiment, a protrusion 16 is integrally formed at the upper end of the spiral tube 4 (FIGS. 11 and 12). The ridge 16 extends in the axial direction of the spiral tube 4 and is erected in a wall shape. When the spiral tube 4 is stacked in a plurality of stages, the upper end of the ridge 16 is the other spiral tube 4 above. Is in close contact with and in close contact with the lower end (FIG. 13). As a result, the spiral passage 7 is formed between the inner and outer protrusions 16 and the spiral tube 4, and in this case, the partition wall portion is constituted by the spiral tube 4 and the protrusion 16.
 また、図14乃至図16は係る突条16を上端のみならず、渦巻の中心方向(内側)の側面にも突出形成した例を示している。この場合も上端の突条16は上方の他の渦巻管4の下端に当接するが、側面の突条16は内方の渦巻管4の外側の側面に当接し、渦巻通路7を上下に仕切ることになるので、渦巻通路7の上下方向における流れも均一化される。 14 to 16 show an example in which the protrusion 16 is formed not only on the upper end but also on the side surface in the center direction (inner side) of the spiral. In this case as well, the upper ridge 16 contacts the lower end of the other spiral tube 4 above, but the side ridge 16 contacts the outer side surface of the inner spiral tube 4 and partitions the spiral passage 7 vertically. Therefore, the flow in the vertical direction of the spiral passage 7 is also made uniform.
 この場合も渦巻の中心方向で並ぶ渦巻管4、4相互の間隔である流路幅PAが、上下の渦巻管4、4相互の間隔である流路幅PB(実質的に突条16の高さ寸法)と略同等(実施例では同一)とされる。 Also in this case, the flow path width PA which is the distance between the spiral tubes 4 and 4 arranged in the center direction of the spiral is substantially equal to the flow path width PB which is the distance between the upper and lower spiral tubes 4 and 4 (substantially the height of the protrusion 16). (Same dimension in the embodiment).
 このように、この実施例では渦巻管4の軸方向に延在する突条16を当該渦巻管4に設け、突条16を上下や渦巻の中心方向で隣接する他の渦巻管4に当接させることにより、仕切壁3を構成するようにしたので、格別な仕切壁を設ける必要が無くなると共に、渦巻管4の位置決めも成されるので、著しい部品点数の削減を図ることが可能となる。 Thus, in this embodiment, the ridge 16 extending in the axial direction of the spiral tube 4 is provided on the spiral tube 4, and the ridge 16 is brought into contact with another spiral tube 4 adjacent in the vertical direction or the center direction of the spiral. Thus, since the partition wall 3 is configured, it is not necessary to provide a special partition wall, and the spiral tube 4 is positioned, so that the number of parts can be significantly reduced.
 尚、側面の突条16は図17、図18のような突起17でもよい。係る突起17によっても渦巻管4の位置決め効果を奏する。 The side protrusion 16 may be a protrusion 17 as shown in FIGS. The protrusion 17 also has the effect of positioning the spiral tube 4.
 そして、図19乃至図24は係る突起17のみを渦巻管4に形成する例を示している。この場合は、仕切壁3が必要となる。そして、渦巻管4の上端に突起17が突出形成され、上下に複数段重ねたときに突起17が上方の他の渦巻管4の下端に当接する。尚、渦巻4は渦巻条の仕切壁3の渦巻の中心方向の面に密着(ろう付け)されている。 19 to 24 show an example in which only the protrusion 17 is formed on the spiral tube 4. In this case, the partition wall 3 is required. Then, a protrusion 17 is formed to protrude at the upper end of the spiral tube 4, and the protrusion 17 contacts the lower end of the other upper spiral tube 4 when it is stacked in a plurality of stages. The spiral 4 is in close contact (brazing) with the surface of the spiral partition wall 3 in the central direction of the spiral.
 図19乃至図21では渦巻管4の上端にのみ突起17を形成したが、図22乃至図24のように渦巻の中心方向の側面にも形成してもよい。側面の突起17は内方の仕切壁3の外側面に当接する。 19 to 21, the protrusion 17 is formed only at the upper end of the spiral tube 4, but it may be formed on the side surface in the center direction of the spiral as in FIGS. 22 to 24. The side projections 17 abut against the outer surface of the inner partition wall 3.
 この場合も渦巻の中心方向で並ぶ渦巻管4、4相互の間隔である流路幅PA(図24の場合には実質的に突起17の寸法)が、上下の渦巻管4、4相互の間隔である流路幅PB(実質的に突起17の高さ寸法)と略同等(実施例では同一)とされる。 Also in this case, the flow path width PA (substantially the dimension of the protrusion 17 in the case of FIG. 24) which is the distance between the spiral tubes 4 and 4 arranged in the center direction of the spiral is the distance between the upper and lower spiral tubes 4 and 4. The flow path width PB (substantially the height dimension of the protrusion 17) is substantially the same (same in the embodiment).
 このように渦巻管4に突起17を設け、この突起17を隣接する他の渦巻管4や仕切壁3に当接させれば、渦巻管4の位置決めをより一層強固且つ容易に行うことが可能となる。 As described above, if the spiral tube 4 is provided with the projection 17 and the projection 17 is brought into contact with another adjacent spiral tube 4 or the partition wall 3, the spiral tube 4 can be positioned more firmly and easily. It becomes.
 この突起17は渦巻管4のみならず、仕切壁3側に設けても良い。図25は係る突起17を仕切壁3に形成する例を示している。この場合は、図4と同様の波形状の仕切壁3の溝11の外面側に、外方(渦巻の中心方向とは反対側)に突出した突起17が形成されており、この突起17は外方の渦巻管4の内側(渦巻の中心方向の側面)の側面に当接する。 The projection 17 may be provided not only on the spiral tube 4 but also on the partition wall 3 side. FIG. 25 shows an example in which the projection 17 is formed on the partition wall 3. In this case, a projection 17 projecting outward (opposite to the direction of the center of the spiral) is formed on the outer surface side of the groove 11 of the wave-shaped partition wall 3 similar to FIG. It contacts the inner side of the outer spiral tube 4 (side surface in the center direction of the spiral).
 この場合も渦巻の中心方向で並ぶ渦巻管4と仕切壁3の間隔である流路幅PA(図25の場合には実質的に突起17の寸法)が、上下の渦巻管4、4相互の間隔である流路幅PBと略同等(実施例では同一)とされる。 Also in this case, the flow path width PA (substantially the dimension of the projection 17 in the case of FIG. 25) which is the distance between the spiral tubes 4 arranged in the center direction of the spiral and the partition wall 3 is the same between the upper and lower spiral tubes 4 and 4. The channel width PB, which is the interval, is substantially the same (same in the embodiment).
 このように仕切壁3に突起17を設け、この突起17を外方で隣接する他の渦巻管4に当接させれば、渦巻管4の位置決めをより一層強固且つ容易に行うことが可能となる。 Thus, if the projection 17 is provided on the partition wall 3 and this projection 17 is brought into contact with the other spiral tube 4 adjacent to the outside, the spiral tube 4 can be positioned more firmly and easily. Become.
 次に、図26、図27は渦巻管4の取付構造の他の例を示している。前述した図8の場合の如く内外の仕切壁3と仕切壁3の間の渦巻通路7内に、仕切壁3と接すること無く渦巻管4を配置する場合、仕切壁3の内面(渦巻の中心方向の面)に保持具18を取り付ける。この保持具18は仕切壁3の上下に延在し、且つ、当該仕切壁3から突出するかたちで複数箇所設けられており、渦巻管4を配置する間隔で半円形(湾曲)の保持溝19(溝の底は仕切壁3から離間する)が複数形成されている。 Next, FIG. 26 and FIG. 27 show another example of the attachment structure of the spiral tube 4. When the spiral tube 4 is disposed in the spiral passage 7 between the inner and outer partition walls 3 and the partition wall 3 without contacting the partition wall 3 as in the case of FIG. 8 described above, the inner surface of the partition wall 3 (the center of the spiral) The holder 18 is attached to the direction surface. The holder 18 extends in the vertical direction of the partition wall 3 and is provided at a plurality of locations so as to protrude from the partition wall 3. The holding groove 19 is semicircular (curved) at intervals where the spiral tube 4 is disposed. A plurality of (the bottom of the groove is separated from the partition wall 3) is formed.
 そして、この保持溝19に渦巻管4を密着して取り付け、保持させる。これによって渦巻管4は内外の仕切壁3と仕切壁3の間の渦巻通路7内に、仕切壁3と接すること無く配置されることになる。 Then, the spiral tube 4 is closely attached to the holding groove 19 and held. Accordingly, the spiral tube 4 is disposed in the spiral passage 7 between the inner and outer partition walls 3 and the partition wall 3 without contacting the partition wall 3.
 このとき、渦巻管4は保持溝19に溶接して固定してもよいが、嵌合により着脱可能に取り付けてもよい。仕切壁3に設けた保持具18の保持溝19に渦巻管4を着脱可能に取り付けることにより、例えば第一流体中の塵埃やスケールが渦巻管4や仕切壁3に付着した場合に、仕切壁3と渦巻管4とを容易に分解して洗浄することができるようになる。 At this time, the spiral tube 4 may be fixed to the holding groove 19 by welding, but may be detachably attached by fitting. When the spiral tube 4 is detachably attached to the holding groove 19 of the holder 18 provided on the partition wall 3, for example, when dust or scale in the first fluid adheres to the spiral tube 4 or the partition wall 3, the partition wall 3 and the spiral tube 4 can be easily disassembled and cleaned.
 次に、図28乃至図31は本発明の渦巻型の熱交換器1及びその製造方法の一実施例を示している。尚、これらの図に示されない構成は前記各実施例と同様であるものとする。また、この実施例では渦巻管4は仕切壁3の内面(渦巻の中心方向の側の面)に取り付けられる。図28はこの場合の仕切壁3であり、上に渦巻状の平面形状が示され、下に側断面形状が示されている。実施例の仕切壁3は外面と内面(渦巻の中心方向の側の面)に連続した溝21、22が交互に形成された断面波状とされている。 Next, FIG. 28 to FIG. 31 show an embodiment of the spiral heat exchanger 1 of the present invention and the manufacturing method thereof. In addition, the structure which is not shown by these figures shall be the same as that of each said Example. In this embodiment, the spiral tube 4 is attached to the inner surface of the partition wall 3 (the surface in the direction of the center of the spiral). FIG. 28 shows the partition wall 3 in this case, in which a spiral planar shape is shown on the upper side and a side sectional shape is shown on the lower side. The partition wall 3 of the embodiment has a corrugated cross-section in which grooves 21 and 22 are formed alternately on the outer surface and the inner surface (the surface on the side of the center of the spiral).
 図29は渦巻管4の平面形状を示している。この場合、仕切壁3の溝21部分の幅寸法Wは、渦巻管4の渦巻の間隔Rより小さく設定する。そして、仕切壁3を図28とは180°回転させ、その状態の仕切壁3に渦巻管4を同心状(渦巻の中心を同一とする)に噛み合わせる(図30)。このとき、渦巻管4は仕切壁3の溝21に対応して配置する。 FIG. 29 shows the planar shape of the spiral tube 4. In this case, the width dimension W of the groove 21 portion of the partition wall 3 is set to be smaller than the spiral interval R of the spiral tube 4. Then, the partition wall 3 is rotated 180 ° from FIG. 28, and the spiral tube 4 is meshed with the partition wall 3 in this state concentrically (the center of the spiral is the same) (FIG. 30). At this time, the spiral tube 4 is disposed corresponding to the groove 21 of the partition wall 3.
 このように仕切壁3と渦巻管4とを配置した状態で、仕切壁3を渦巻の中心を軸として図30中時計回り(仕切壁3の内端を更に巻く方向)に回転させると、仕切壁3が渦巻管4に対して総体的に外側に移動するかたちとなるので、渦巻管4は仕切壁3の外面の溝21内に進入して密着される(図31)。この図31も上に平面が、下に側断面が示されている。 When the partition wall 3 and the spiral tube 4 are arranged as described above, the partition wall 3 is rotated clockwise in FIG. 30 (the direction in which the inner end of the partition wall 3 is further wound) about the center of the spiral as a partition. Since the wall 3 generally moves outward with respect to the spiral tube 4, the spiral tube 4 enters into and closely contacts the groove 21 on the outer surface of the partition wall 3 (FIG. 31). FIG. 31 also shows a plane on the top and a side section on the bottom.
 尚、渦巻管4を回転させる場合には、図30の反時計回りに回転させればよい。また、この場合も渦巻の中心方向で並ぶ渦巻管4と仕切壁3の間隔である流路幅PAと、上下の渦巻管4、4相互の間隔(図31の場合には溝21の間隔)である流路幅PBとは略同等(実施例では同一)とされる。 In addition, what is necessary is just to rotate counterclockwise of FIG. Also in this case, the flow path width PA, which is the distance between the spiral tube 4 and the partition wall 3 aligned in the center direction of the spiral, and the distance between the upper and lower spiral tubes 4 and 4 (interval of the groove 21 in the case of FIG. 31). The channel width PB is substantially equivalent (same in the embodiment).
 このように仕切壁3に連続した溝21を形成し、この溝21部分の仕切壁3の幅寸法Wを渦巻管4の渦巻の間隔Rより小さくし、仕切壁3の溝21に対応させて渦巻管4を配置し、仕切壁3や渦巻管4を、渦巻の中心を軸として回転させることで、溝21に渦巻管4を密着させるようにすれば、仕切壁3や渦巻管4を回転させるだけの極めて簡単な操作で、渦巻状の仕切壁3に渦巻管4を組み付け、熱交換器1を容易に組み立てることが可能となる。 In this way, a continuous groove 21 is formed in the partition wall 3, and the width W of the partition wall 3 in the groove 21 portion is made smaller than the spiral interval R of the spiral tube 4 so as to correspond to the groove 21 of the partition wall 3. If the spiral tube 4 is disposed, and the partition wall 3 or the spiral tube 4 is rotated around the center of the spiral, the spiral tube 4 is brought into close contact with the groove 21, so that the partition wall 3 or the spiral tube 4 is rotated. The heat exchanger 1 can be easily assembled by assembling the spiral tube 4 to the spiral partition wall 3 with an extremely simple operation.
 次に、図32乃至図36は本発明の渦巻型の熱交換器1の製造方法の他の実施例を示している。尚、この実施例では渦巻管4は仕切壁3の外面(渦巻の中心方向とは反対方向の側の面)に形成されたフック23の溝24に取り付けられる。この場合、フック23は仕切壁3に複数箇所突出形成されており、その先端にC形状の溝24が形成されている(図32) Next, FIGS. 32 to 36 show another embodiment of the method for manufacturing the spiral heat exchanger 1 of the present invention. In this embodiment, the spiral tube 4 is attached to the groove 24 of the hook 23 formed on the outer surface of the partition wall 3 (the surface on the side opposite to the center direction of the spiral). In this case, the hook 23 is formed at a plurality of locations on the partition wall 3, and a C-shaped groove 24 is formed at the tip thereof (FIG. 32).
 図33は渦巻管4の平面形状を示している。この場合も、仕切壁3のフック23(溝24)部分の幅寸法Wは、渦巻管4の渦巻の間隔Rより小さく設定する。そして、仕切壁3に渦巻管4を同心状(渦巻の中心を同一とする)に噛み合わせる(図34)。このとき、渦巻管4は仕切壁3のフック23の溝24に対応して配置する。 FIG. 33 shows the planar shape of the spiral tube 4. Also in this case, the width dimension W of the hook 23 (groove 24) portion of the partition wall 3 is set to be smaller than the spiral interval R of the spiral tube 4. Then, the spiral tube 4 is concentrically engaged with the partition wall 3 (the center of the spiral is the same) (FIG. 34). At this time, the spiral tube 4 is disposed corresponding to the groove 24 of the hook 23 of the partition wall 3.
 このように仕切壁3と渦巻管4とを配置した状態で、仕切壁3を渦巻の中心を軸として図34中時計回り(仕切壁3の内端を更に巻く方向)に回転させると、仕切壁3が渦巻管4に対して総体的に外側に移動するかたちとなるので、渦巻管4は仕切壁3の外面のフック23の溝24内に着脱可能に嵌合して密着される(図35、図36)。 When the partition wall 3 and the spiral tube 4 are arranged as described above, the partition wall 3 is rotated clockwise in FIG. 34 around the center of the spiral (direction in which the inner end of the partition wall 3 is further wound). Since the wall 3 generally moves outward with respect to the spiral tube 4, the spiral tube 4 is detachably fitted into and closely attached to the groove 24 of the hook 23 on the outer surface of the partition wall 3 (FIG. 35, FIG. 36).
 尚、渦巻管4を回転させる場合には、図34の反時計回りに回転させればよい。また、この場合の流路幅PA1、PA2(PA)とPBの関係も図8のときと同様とする。このように仕切壁3のフック23に溝24を形成し、このフック23(溝24)部分の仕切壁3の幅寸法Wを渦巻管4の渦巻の間隔Rより小さくし、仕切壁3のフック23の溝24に対応させて渦巻管4を配置し、仕切壁3や渦巻管4を、渦巻の中心を軸として回転させることで、溝24に渦巻管4を密着させるようにすれば、仕切壁3や渦巻管4を回転させるだけの極めて簡単な操作で、渦巻状の仕切壁3に渦巻管4を組み付け、熱交換器1を容易に組み立てることが可能となる。 Incidentally, when the spiral tube 4 is rotated, it may be rotated counterclockwise in FIG. Further, the relationship between the channel widths PA1, PA2 (PA) and PB in this case is the same as in FIG. In this way, the groove 24 is formed in the hook 23 of the partition wall 3, and the width W of the partition wall 3 in the hook 23 (groove 24) portion is made smaller than the spiral interval R of the spiral tube 4. If the spiral tube 4 is arranged corresponding to the groove 24 of the 23, and the partition wall 3 and the spiral tube 4 are rotated around the center of the spiral, the spiral tube 4 is brought into close contact with the groove 24. The heat exchanger 1 can be easily assembled by assembling the spiral tube 4 to the spiral partition wall 3 by an extremely simple operation by simply rotating the wall 3 and the spiral tube 4.
 特に、この実施例では渦巻管4が仕切壁3のフック23の溝24に着脱可能に嵌合するので、仕切壁3と渦巻管4とを容易に分解することができる熱交換器1を製造することができるようになり、熱交換器1に付着した塵埃やスケールを容易に洗浄することが可能となる。 In particular, in this embodiment, since the spiral tube 4 is detachably fitted into the groove 24 of the hook 23 of the partition wall 3, the heat exchanger 1 capable of easily disassembling the partition wall 3 and the spiral tube 4 is manufactured. As a result, dust and scale attached to the heat exchanger 1 can be easily washed.
 尚、実施例ではランキンサイクルで冷水と冷媒との熱交換を実現する熱交換器を例に説明したが、それに限らず、あらゆる用途の渦巻型の熱交換器に本発明は有効である。また、実施例では第一流体を冷水、第二流体を冷媒としたが、それに限らず、温度差のある種々の流体相互の熱交換に本発明の熱交換器は利用可能である。 In addition, although the Example demonstrated the heat exchanger which implement | achieves heat exchange with cold water and a refrigerant | coolant by Rankine cycle as an example, it is not restricted to this, This invention is effective for the spiral heat exchanger of all uses. In the embodiments, the first fluid is cold water and the second fluid is a refrigerant. However, the present invention is not limited to this, and the heat exchanger of the present invention can be used for heat exchange between various fluids having temperature differences.
 1 熱交換器
 2 容器
 3 仕切壁(仕切壁部)
 4 渦巻管(渦巻管部)
 6 蓋
 7 渦巻通路
 8、9 ヘッダ
 11、21、24 溝
 12 突出部
 13 仕切壁部
 14 渦巻管部
 15 押出材
 16 突条
 17 突起
 18 保持具
 19 保持溝
 23 フック
1 Heat exchanger 2 Container 3 Partition wall (partition wall)
4 Spiral tube (spiral tube)
6 Lid 7 Spiral path 8, 9 Header 11, 21, 24 Groove 12 Projection 13 Partition wall 14 Spiral tube 15 Extrusion material 16 Projection 17 Projection 18 Holder 19 Holding groove 23 Hook

Claims (4)

  1.  容器内に設けられた渦巻状の仕切壁間に渦巻通路を構成し、該渦巻通路に渦巻管を上下複数段配置して該渦巻管外側の前記渦巻通路を流れる第一流体と前記渦巻管内を流れる第二流体とを熱交換させる熱交換器において、
     前記仕切壁に形成された溝を備え、
     該溝部分の前記仕切壁の幅寸法Wは、前記渦巻管の渦巻の間隔Rより小さく構成されており、
     前記渦巻管は、前記仕切壁の前記溝に対応された状態で、前記仕切壁、及び/又は、渦巻管が、渦巻の中心を軸として回転されることで、前記溝に密着されていることを特徴とする熱交換器。
    A spiral passage is formed between the spiral partition walls provided in the container, and a plurality of spiral tubes are arranged in the spiral passage in the upper and lower stages, and the first fluid flowing in the spiral passage outside the spiral tube and the inside of the spiral tube are disposed. In a heat exchanger that exchanges heat with the flowing second fluid,
    Comprising a groove formed in the partition wall;
    A width dimension W of the partition wall of the groove portion is configured to be smaller than a spiral interval R of the spiral tube,
    The spiral tube is in close contact with the groove by rotating the partition wall and / or the spiral tube around the center of the spiral in a state corresponding to the groove of the partition wall. A heat exchanger characterized by
  2.  前記渦巻管は前記仕切壁の溝に着脱可能に嵌合されていることを特徴とする請求項1に記載の熱交換器。 The heat exchanger according to claim 1, wherein the spiral tube is detachably fitted in a groove of the partition wall.
  3.  容器内に設けられた渦巻状の仕切壁間に渦巻通路を構成し、該渦巻通路に渦巻管を上下複数段配置して該渦巻管外側の前記渦巻通路を流れる第一流体と前記渦巻管内を流れる第二流体とを熱交換させる熱交換器において、
     前記仕切壁に溝を形成し、
     該溝部分の前記仕切壁の幅寸法Wを前記渦巻管の渦巻の間隔Rより小さくし、
     前記仕切壁の前記溝に対応させて前記渦巻管を配置し、
     前記仕切壁、及び/又は、渦巻管を、渦巻の中心を軸として回転させることで、前記溝に前記渦巻管を密着させることを特徴とする熱交換器の製造方法。
    A spiral passage is formed between the spiral partition walls provided in the container, and a plurality of spiral tubes are arranged in the spiral passage in the upper and lower stages, and the first fluid flowing in the spiral passage outside the spiral tube and the inside of the spiral tube are disposed. In a heat exchanger that exchanges heat with the flowing second fluid,
    Forming a groove in the partition wall;
    The width W of the partition wall of the groove portion is made smaller than the spiral interval R of the spiral tube,
    The spiral tube is arranged corresponding to the groove of the partition wall,
    A method of manufacturing a heat exchanger, comprising: rotating the partition wall and / or the spiral tube around the center of the spiral to bring the spiral tube into close contact with the groove.
  4.  前記渦巻管を前記仕切壁の溝に着脱可能に嵌合させることを特徴とする請求項3に記載の熱交換器の製造方法。 The method for manufacturing a heat exchanger according to claim 3, wherein the spiral tube is detachably fitted in a groove of the partition wall.
PCT/JP2014/070609 2013-08-08 2014-08-05 Heat exchanger and method for manufacturing heat exchanger WO2015020050A1 (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104807350A (en) * 2015-05-05 2015-07-29 宁波德业科技集团有限公司 Heat exchanger of air conditioner

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6174777U (en) * 1984-10-20 1986-05-20
DE19606201A1 (en) * 1996-02-21 1997-08-28 Balcke Duerr Gmbh Device for holding parallel pipes in heat exchanger
JP2004176949A (en) * 2002-11-25 2004-06-24 Denso Corp Heat exchanger
WO2008113714A1 (en) * 2007-03-12 2008-09-25 Valeo Systemes Thermiques Heat exchanger and built-in assembly including such exchanger

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6174777U (en) * 1984-10-20 1986-05-20
DE19606201A1 (en) * 1996-02-21 1997-08-28 Balcke Duerr Gmbh Device for holding parallel pipes in heat exchanger
JP2004176949A (en) * 2002-11-25 2004-06-24 Denso Corp Heat exchanger
WO2008113714A1 (en) * 2007-03-12 2008-09-25 Valeo Systemes Thermiques Heat exchanger and built-in assembly including such exchanger

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104807350A (en) * 2015-05-05 2015-07-29 宁波德业科技集团有限公司 Heat exchanger of air conditioner

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