EP4257906A1 - Spiralwärmetauscher und herstellungsverfahren dafür - Google Patents

Spiralwärmetauscher und herstellungsverfahren dafür Download PDF

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Publication number
EP4257906A1
EP4257906A1 EP21899991.0A EP21899991A EP4257906A1 EP 4257906 A1 EP4257906 A1 EP 4257906A1 EP 21899991 A EP21899991 A EP 21899991A EP 4257906 A1 EP4257906 A1 EP 4257906A1
Authority
EP
European Patent Office
Prior art keywords
radial direction
block bars
mandrel
block
bars
Prior art date
Legal status (The legal status 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 status listed.)
Pending
Application number
EP21899991.0A
Other languages
English (en)
French (fr)
Other versions
EP4257906A4 (de
Inventor
Feng Gao
Zaixiang LIU
Yanfeng Chen
Yuanfeng CAI
Bing Wang
Zhengyan NIU
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Shanghai Xingye Material Technology Co Ltd
Original Assignee
Shanghai Xingye Material Technology Co Ltd
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 Shanghai Xingye Material Technology Co Ltd filed Critical Shanghai Xingye Material Technology Co Ltd
Publication of EP4257906A1 publication Critical patent/EP4257906A1/de
Publication of EP4257906A4 publication Critical patent/EP4257906A4/de
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-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 arranged in parallel spaced relation
    • F28D7/1684—Heat-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 arranged in parallel spaced relation the conduits having a non-circular cross-section
    • F28D7/1692—Heat-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 arranged in parallel spaced relation the conduits having a non-circular cross-section with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/04—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being formed by spirally-wound plates or laminae
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D53/00—Making other particular articles
    • B21D53/02—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers
    • B21D53/04—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers of sheet metal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/001—Casings in the form of plate-like arrangements; Frames enclosing a heat exchange core
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D11/00—Bending not restricted to forms of material mentioned in only one of groups B21D5/00, B21D7/00, B21D9/00; Bending not provided for in groups B21D5/00 - B21D9/00; Twisting
    • B21D11/06—Bending into helical or spiral form; Forming a succession of return bends, e.g. serpentine form
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • F28F2009/222—Particular guide plates, baffles or deflectors, e.g. having particular orientation relative to an elongated casing or conduit
    • F28F2009/224—Longitudinal partitions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/044—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being pontual, e.g. dimples

Definitions

  • the present invention application relates to the field of heat exchange, and specifically to a spiral heat exchanger and manufacture method therefor.
  • a heat exchanger refers to the equipment that transfers the heat of the heat fluid to the cold fluid.
  • the heat exchanger has an important application in life and industrial production. Due to the pursuit of a larger heat exchange area, the traditional heat exchanger generally covers a large area, so it has disadvantages such as higher requirements for installation space and inconvenient maintenance. Therefore, on the premise of ensuring sufficient heat exchange area, how to reduce the volume of the heat exchanger is an urgent problem to be solved in the industry.
  • the Chinese utility model patent with authorized notice number CN201520085162.X exposes a new type of spiral plate reaction heat exchanger which includes a first sheet, a second sheet, a middle partition and an outer cylinder.
  • the first and second plates are spaced apart to form a double spiral cylinder.
  • the middle partition is connected to the ends of the first and second plates near the center of the helix respectively, and separates the double spiral cylinder into two spaces without interference each other.
  • One of the spaces is a hot fluid channel (the hot medium enters the chamber) for running the hot fluid
  • the other space is a cold fluid channel (the cold medium enters the chamber) for running the cold fluid.
  • the hot and cold fluid channels are arranged into an interval distribution.
  • Hot fluid channel and cold fluid channel are located near the center of the helix with a hot fluid inlet and a cold fluid outlet, respectively, and the hot fluid channel and the cold fluid channel are provided with hot fluid outlet and cold fluid inlet, respectively.
  • the surface areas of both the first and second plates are the heat transfer area of the hot and cold fluid which ensure the sufficient heat transfer area with the setting of a double-helical cylinder, and can effectively reduce the volume of the heat exchanger.
  • the spiral plate reaction heat exchanger in the patent document as described above has the following disadvantages.
  • the present invention application comes from this.
  • a spiral heat exchanger which comprises:
  • third block bars are disposed at each of the cold fluid outlets for partially blocking thereof, each of the third block bars is sequentially arranged along a third radial direction of the mandrel, the third radial direction and the first radial direction are arranged at a non-zero clip angle.
  • fourth block bars are disposed at each of the hot fluid outlets for partially blocking thereof, each of the fourth block bars is sequentially arranged along a fourth radial direction of the mandrel, the fourth radial direction and the second radial direction are arranged at a non-zero clip angle.
  • fifth block bars are disposed at each of the cold fluid outlets for partially blocking thereof, each of the fifth block bars is sequentially arranged along a fifth radial direction of the mandrel; the fifth radial direction is arranged at a non-zero clip angle with the first radial direction and the third radial direction, respectively.
  • sixth block bars are disposed at each of the cold fluid inlets for partially blocking thereof
  • seventh block bars are disposed at each of the hot fluid inlets for partially blocking thereof
  • each of the sixth block bars are sequentially arranged along a sixth radial direction of the mandrel
  • each of the seventh block bars are sequentially arranged along a seventh radial direction of the mandrel
  • the sixth radial direction is arranged at a non-zero clip angle with the second radial direction and the fourth radial direction, respectively
  • the seventh radial direction is arranged at a non-zero clip angle with the third radial direction, the first radial direction and the fifth radial direction, respectively.
  • eighth block bars are disposed at each of the cold fluid inlets for partially blocking thereof
  • ninth block bars are disposed at each of the hot fluid inlets for partially blocking thereof
  • each of the eighth block bars is sequentially arranged alone an eighth radial direction of the mandrel
  • each of the ninth block bars is sequentially arranged along a ninth radial direction of the mandrel
  • the eighth radial direction is arranged at a non-zero clip angle with the sixth radial direction, the second radial direction and the fourth radial direction, respectively
  • the ninth radial direction, and the seventh radial direction, the third radial direction, the first radial direction and the fifth radial direction are respectively arranged at a non-zero clip angle.
  • tenth block bars are disposed at each of the hot fluid outlets for partially blocking thereof, each of the tenth block bars is sequentially arranged along a tenth radial direction of the mandrel; the tenth radial direction is arranged at a non-zero clip angle with the eighth radial direction, the sixth radial direction, the fourth radial direction and the second radial direction, respectively.
  • the sixth radial direction and the first radial direction are arranged at a non-zero clip angle
  • the seventh radial direction and the second radial direction are arranged at a non-zero clip angle
  • both the first block bars and the second block bars are an arc block bar
  • a manufacturing method of the spiral heat exchanger as described in the first aspect of the present invention application which comprises: winding a heat conduction thin tape around the periphery of a mandrel to have a spiral shape; coating an adhesive on the left and right of the heat conduction thin tape for forming first block bars and second block bars on the corresponding position with a certain length at a certain interval, in the process of the winding the heat conduction thin tape, meanwhile, coating an adhesive on a surface of the heat conduction thin tape for forming the baffle ribs at a certain interval.
  • a spiral heat exchanger which comprises:
  • eighth block bars are disposed at each of the cold fluid inlets for partially blocking thereof
  • ninth block bars are disposed at each of the hot fluid inlets for partially blocking thereof
  • each of the eighth block bars is sequentially arranged along a eighth radial direction of the mandrel
  • each of the ninth block bars is sequentially arranged along a ninth radial direction of the mandrel
  • the eighth radial direction and the sixth radial direction are arranged at a non-zero clip angle
  • the ninth radial direction and the seventh radial direction are arranged at a non-zero clip angle.
  • the sixth block bars and the seventh block bars are arc block bars.
  • the lengths of the sixth block bars increase sequentially, the lengths of the seventh block bars increase sequentially, and so that the sixth block bars are fan-distributed, the seventh block bars are fan-distributed.
  • each of the sixth block bars has a radiant 180°
  • each of the seventh block bars has a radian ⁇ 180°.
  • connection is not intended to define a physical connection or mechanical connection, but may include an electrical connection, directly or indirectly.
  • "On,” “under,” “right,” “left” and the like are only used to indicate relative position relationship, and when the position of the object which is described is changed, the relative position relationship may be changed accordingly.
  • the spiral heat exchanger of this embodiment mainly includes a mandrel 1 and a heat conduction thin tape 2, where the heat conduction thin tape 2 is coiled around the periphery of the mandrel 1, and the coil number of heat conduction thin tape 2 is 10 circles.
  • the length direction of mandrel 1 is now defined as the left and right direction, that is, the axis of mandrel 1 extends in left-right direction (extending from left to right).
  • the heat conduction thin tape 2 of any two adjacent circle layers are separated by a certain distance to form a spiral void.
  • the left and right extended baffle ribs 3 are configured to support between any adjacent two circle layers of the heat conduction thin tape, thereby these baffle ribs 3 are used to separate the large helical voids into nine small class round voids(circular spaces).
  • the aforementioned baffle ribs 3 are arranged along a radial direction of mandrel 1 so that the aforementioned nine circular voids are arranged along the radial direction of the mandrel 1.
  • the circular spaces of the first, third, fifth, seventh and ninth layers are hot fluid flow channels 4 for the hot fluid
  • the even circular spaces of the second, fourth, sixth and eighth layers are cold fluid flow channels 5 for the cold fluid.
  • Hot fluid flow channels 4 and cold fluid flow channels 5 are sequentially arranged alternately along the radial direction of the mandrel 1.
  • Each of the hot fluid flow channels 4 has a hot fluid inlet 4a located on the left and a hot fluid outlet4 b located on the right
  • each of the cold fluid flow channels 5 has a cold fluid outlet 5b located on the left and a cold fluid inlet 5a on the right.
  • the hot fluid flows from left to right in each hot fluid flow channels 4, and the cold fluid flows from right to left in each cold fluid flow channels 5, both convective heat exchange.
  • each hot fluid flow channels 4 and the cold fluid outlet 5b of each cold fluid flow channels 5 are on the same side of the heat exchanger (left side), and alternately closely arranged with each other, the cold fluid inlet 5a of each cold fluid flow channels 5 is on the same side as the hot fluid outlets 4b of each hot fluid flow channels 4 (right side), and alternately closely arranged. If the heat fluid and cold fluid are directly fed to the heat exchanger from the left and right side respectively, part of the heat fluid into the cold fluid flow channels 5 and some cold fluid into the hot fluid flow channels 4 will occur. Based on this, the present embodiment adopts the following optimization design to more conveniently introduce the hot fluid and the cold fluid into each hot fluid flow channels 4 and each cold fluid flow channels 5, respectively, to avoid the hot and cold fluid crosstalk.
  • first block bars 6 are disposed at each cold fluid outlets 5b to block part of the hot fluid inlet (i.e. first block bars does not block all the cold fluid outlets, block only part of the cold fluid outlet).
  • Second block bars 7 are disposed at each hot fluid outlets 4b to block part of the hot fluid outlet.
  • each first block bars 6 are sequentially arranged along the first radial direction R1 of the mandrel 1
  • each second block bars 7 are sequentially arranged along the second radial direction R2 of the mandrel 1.
  • each hot fluid flow channels 4 is centrally arranged - on the above first radial direction R1 for convenient description, and the centralized arrangement area becomes the first region. Moreover, in the first region, the cold fluid outlet 5b of each cold fluid flow channels 5 is blocked by first block bars 6. Therefore, in practical application, only need to send the hot fluid to the first region, it can flow into each hot fluid flow channels 4, without string into the cold fluid flow channels 5.
  • At least a part of the cold fluid inlet 5a of each cold fluid flow channels 5 is centrally arranged in the second region of the above second radial direction R2. Moreover, in the second region, the hot fluid outlet 4b of each hot fluid flow channels 4 is blocked by second block bars 7. Therefore, in practical application, only need to send the cold fluid to the aforementioned second region, it can flow into each cold fluid flow channels 5, but not into cold fluid flow channels 5.
  • the inflow area of the cold and hot fluid can be increased by increasing the number of integrated areas shown in Figs. 6 and 7 , thus increasing the heat transfer efficiency.
  • each cold fluid outlets 5b mentioned above also has third block bars 8 to block part of the cold fluid outlet, each third block bars 8 are sequentially arranged along a third radial direction R3 of the mandrel 1, and each hot fluid outlets 4b of third radial direction R3 and first radial direction R1 are arranged at a non-zero clip angle.
  • Each hot fluid outlets 4b have fourth block bars 9 partially blocking the hot fluid outlets 4b, each fourth block bars 9 are sequentially arranged along a fourth radial direction R4 of the mandrel 1, and the fourth radial direction R4 and the second radial direction R2 are arranged at a non-zero clip angle.
  • the heat exchanger has at least two hot fluid integration areas on the left and two cold fluid integration areas on the right, which improves the inflow area of the cold and hot fluid by increasing the number of cold and hot fluid integration areas, and then improves the heat transfer efficiency.
  • each cold fluid outlets 5b also has fifth block bars 10 to partially blocks it, each fifth block bars 10 are sequentially arranged along the fifth radial direction R5 of the mandrel 1, and the fifth radial direction R5 is arranged at a non-zero clip angle with the aforementioned first radial direction R1 and the third radial direction R3. Therefore, there are three staggered hot fluid integration areas on the left side of the heat exchanger, and two staggered cold fluid areas are formed on the right side of the heat exchanger.
  • the above solution solves how to bring the cold and heat fluid into the heat exchanger, without considering how to draw the heat fluid independently of each other, which does not affect the use of the heat exchanger in some specific environments.
  • each hot fluid inlets 4a has the seventh block bars 12 blocking the hot fluid inlet.
  • Each sixth block bars11 is sequentially arranged along a sixth radial direction R6 of mandrel 1
  • each seventh block bars 12 are along a seventh radial direction R7 of mandrel 1.
  • the sixth radial direction R6 is arranged at a non-zero clip angle with the aforementioned second radial direction R2 and the fourth radial direction R4 respectively
  • the seventh radial direction R7 is arranged at a non-zero clip angle with the third radial direction R3, the first radial direction R1 and the fifth radial direction R5 respectively.
  • each hot fluid flow channels 4 is arranged - on the above sixth radial direction R6 for convenient description, and the centralized arrangement area becomes the sixth region. Moreover, at the location of the sixth region, the cold fluid inlet 5a of each cold fluid flow channels 5 is blocked by the sixth block bars 11. Therefore, in practical application, a large hot fluid draw out hole can be provided in the aforementioned sixth region to draw out the heat fluid without incorporating cold fluid.
  • At least part of the cold fluid outlet 5b of each cold fluid flow channels 5 is arranged - on the above seventh radial direction R7 for convenient description, and the centralized arrangement area becomes the seventh area. Moreover, in the seventh area, the hot fluid inlet 4a of each hot fluid flow channels 4 is blocked by the seventh block bars 12. Therefore, in practical application, a large cold fluid draw out hole can be provided in the aforementioned seventh region to concentrate the heat-exchanged cold fluid from the place without incorporating the hot fluid.
  • the outflow area of the hot fluid is small, which is not conducive to the improvement of heat transfer efficiency.
  • the area of the sixth and seventh areas usually cannot be set very large. In this case, the outflow area of the cold and hot fluid can be increased by increasing the number of the areas in the sets of cold and hot fluid, thus improving the heat transfer efficiency.
  • each above cold fluid inlets 5a also have an eighth block bars 13 to blocking part of the cold fluid inlet.
  • Each eighth block bars 13 are sequentially arranged along an eighth radial direction R8 of the mandrel 1, and the eighth radial direction R8 is arranged at a non-zero clip angle with the aforementioned sixth radial direction R6, the second radial direction R2 and the fourth radial direction R4.
  • Each hot fluid inlets 4a also have ninth block bars 14 for partially blocking the hot fluid inlet, each ninth block bars14 are sequentially arranged along the ninth radial direction R9 of the mandrel 1, and the ninth radial direction R9 is arranged at a non-zero clip angle with the aforementioned seventh radial direction R7, the third radial direction R3, the first radial direction R1 and the fifth radial direction R5.
  • the heat exchanger has at least two cold fluid outlet areas on the left and two hot fluid outlet areas on the right, which increases the number of outlet areas of cold and hot fluid, and then improves the heat transfer efficiency.
  • each cold fluid inlets 5a are also provided with tenth block bars15 to partially block it, Each tenth block bars 15 are sequentially arranged along a tenth radial direction R10 of the mandrel1, and the tenth radial direction R10 is arranged at a non-zero clip angle with the aforementioned eighth radial direction R8, the sixth radial direction R6, the fourth radial direction R4 and the second radial direction R2.
  • three staggered hot fluid regions are formed on the right side of the heat exchanger, and two staggered cold fluid regions are formed on the left side of the heat exchanger.
  • the sixth radial direction R6, the third radial direction R3, the eighth radial direction R8, the fifth radial direction R5, between two pairs, are arranged at a non-zero clip angle
  • the second radial direction R2 the seventh radial direction R7, the fourth radial direction R4, the ninth radial direction R9, the tenth radial direction R10, between two pairs, are arranged at a non-zero clip angle.
  • the heat transfer efficiency of the heat exchanger may also be increased by increasing the area of the first, the second, the sixth and the seventh regions the second area, the sixth heat region and the seventh heat exchanger regions, such as the embodiment shown in Figs. 8 and 9 .
  • each cold fluid outlets 5b out of the seventh radial direction R7 is completely blocked by the first block bars 6 to obtain a sufficiently large hot fluid influx area.
  • All regions of each hot fluid outlets 4b out of the sixth radial direction R6 were blocked by the second block bars 7 to obtain a sufficiently large cold fluid sink area.
  • All regions of each cold fluid inlets 5a outside the second radial direction R2 were blocked by the sixth block bars 11 to obtain a sufficiently large hot fluid set region.
  • All regions of each hot fluid inlets 4a out of the first radial directionr1 were blocked by the seventh block bars 12 to obtain a sufficiently large cold fluid set region.
  • the above various blocks in other words, all of the first block bars 6, the second block bars 7, the third block bars 8, the fourth block bars 9, the fifth block bars 10, the sixth block bars 11, the seventh block bars 12, the eighth block bars 13, the ninth block bars 14 and the tenth block bars 17 are arc block bars.
  • the length of each first block bars 6 increases sequentially
  • the lengths of each second block bars 7 increase sequentially
  • the lengths of each third block bars 8 increase sequentially
  • the lengths of each fourth block bars 8 increase sequentially.
  • each first block bars 6 have a scalloped distribution
  • each second block bars 7 show a scalloped distribution
  • each third block bars 8 show a scalloped distribution
  • each fourth block bars 9 show a scalloped distribution
  • each fifth block bars 10 show a scalloped distribution
  • each sixth block bars 11 show a scalloped distribution
  • each seventh block bars 12 show a scalloped distribution
  • each eighth block bars13 show a scalloped distribution
  • each ninth block bars16 show a scalloped distribution
  • each tenth block bars17 show a scalloped distribution.
  • baffle ribs 3 and each block bars all of the first block bars 6, the second block bars 7, the third block bars 8, the fourth block bars 9, the fifth block bars 10, the sixth block bars 11, the seventh block bars 12, the eighth block bars 13, the ninth block bars 14, the tenth block bars 17 are adhesive adhered with the heat conduction thin tape 2.
  • the above barriers can not only block the inlet and outlet of the flow channels, so that the inlet and outlet of each cold fluid flow channels and hot fluid flow channels are concentrated in different positions, but also support the heat conduction thin tape 2 of different circles, so that the heat conduction thin tape 2 of each circle can form the flow channels at a certain distance.
  • a plurality of supports 2a are configured to support between any adjacent two layers of the heat conduction thin tape 2, and supports the heat conduction thin tape 2 of the adjacent layer, so as to ensure the structural stability of the cold and hot fluid flow channels.
  • the above heat conduction thin tape 2 is a metal thin strip
  • the support platform 2a is a stamping bump formed to stamp on the metal thin strip.
  • the stamping bump can be made as the support platform 2a on the heat conduction thin tape 2 in advance, and then wrap the heat conduction thin tape 2 with the stamping bump on the outside of the mandrel 1.
  • multiple intervals of stamping bumps can be flushed on the section to be rolled in heat conduction thin tape 2. That is, punching the stamping bumps at one side and winding heat conduction thin tape 2 at the same time.
  • each stamping bump is formed on the outer side - of heat conduction thin tape 2, i.e., the side departing from mandrel 1.
  • stamping bumps on both the inner and outer sides of the heat conduction thin tape 2.
  • the above support platform 2a may be a welded bump.
  • the shapes of the stamping bulges and bulges can be hemispherical or cylindrical.
  • the above heat conduction thin tape 2 is an aluminum foil with a thickness of less than one mm.
  • the distance between the adjacent circle layers of the heat conduction thin tape 2 is 2 ⁇ 10mm, that is, the thicknesses of the hot fluid flow channels 4 and the cold fluid flow channels 5 in the radial direction of the mandrel 1 are 2 ⁇ 10mm.
  • the thin heat conduction thin tape and the thin fluid flow channel improve the heat transfer area and heat transfer efficiency of the hot and hot fluid.
  • stamping bulge is located in the path of the hot fluid flow, hot fluid (and cold fluid) in the position of stamping bulge will produce turbulence, making the hot flow in the flow process in the radial direction mixing, thus increasing the hot fluid temperature at the contact position with heat conduction thin tape up, increasing the temperature difference with the other side of heat conduction thin tape cold fluid, accelerating the heat exchange, and then improving the heat exchange rate.
  • the stamping bulge increases the contact area between heat conduction thin tape and the fluid, so that the hot and cold fluids on both sides of the heat conduction thin tape can exchange heat better, and thus improves the heat exchange rate.
  • the heat conduction thin tape 2 is coiled around the periphery of mandrel 1 in a spiral shape, that is, the heat conduction thin tape 2 is a circular spiral shape, which is easier to manufacture.
  • the heat conduction thin tape 2 is of a non-circular helical shape, or the heat conduction thin tape 2 may also be coiled around the periphery of mandrel 1 in a non-circular helix.
  • the aforementioned non-circular spiral is preferably an oval spiral.
  • the heat exchanger of this shape is flat, more beautiful, and can be arranged in a flat space to make full use of the flat space to maximize the heat transfer performance of the heat exchanger.
  • a left end cover 16 and a right end cover 17 are provided to set on the mandrel 1.
  • the left end cover 16 and the right end cover 17 are fixed with the mandrel 1 by bolt and nut, and the left end cover 16 is disposed against the left side of the heat conduction thin tape 2 and the right end cover 17 against the right side of the heat conduction thin tape 2.
  • Two hot fluid concentration lead holes 16a are provided in the left end cover 16, and two hot fluid concentration lead holes 17a are provided in the right end cover 17.
  • each first block bars 6 are arranged in close proximity to each fifth block bars 10 in the present embodiment, there is only a very narrow baffle ribs 3 between them. Therefore, the first one of the two hot fluid concentration introduction holes 16a is simultaneously arranged at the position of each of the first block bars 6 and the fifth block bars 10.
  • the second thermal fluid concentration introduction hole 16a from the first thermal fluid concentration may flow simultaneously to each hot fluid inlets 4a in a first radial direction R1 and a fifth radial direction R5.
  • the second thermal fluid concentration introduction hole 16a is arranged only at the third block bars 8, and the thermal fluid from the second thermal fluid concentration introducing hole 16a flows only to the hot fluid inlet 4a in the third radial direction R3.
  • the first one of the two hot fluid concentration holes 17a is arranged at the position of each sixth block bars 11, and the thermal fluid from each hot fluid outlets 4b at a position in the sixth radial direction R6 is derived from the first hot fluid concentration hole 17a.
  • the second hot fluid concentration hole 17a is arranged at the position of the eighth block bars 13 and the hot fluid emerging from each hot fluid outlets 4b at a position in the eighth radial direction R6 is derived from the second hot fluid concentration hole 17a.
  • the left end cover 16 of this embodiment includes two cold fluid collecting tray 16b from the right end facing the left recess, respectively, and the cold fluid lead joint 16 c communicating with the two cold fluid flow sinks 16b.
  • the right end cover 17 of this embodiment includes two cold fluid buffer grooves 17b facing from the left end of the right end cover, and a cold fluid introduction joint 17 c communicating with the two cold fluid buffer grooves 17b.
  • One of the cold fluid buffer grooves 17b is located at both second block bars 7 and tenth block bars15, and the other at fourth block bars 9.
  • the cold fluid inlet joint 17c and the cold fluid outlet joint 16c can be connected to the supply end and return end of the external cold fluid circulation unit (usually circulating water), respectively, to the axial side of the coil and the heat conduction thin tape 2, prompting the air (hot fluid) to flow in each hot fluid flow channels.
  • the cold fluid flows from the cold fluid inlet joint 17c into the cold fluid collecting tray 16b, from the cold fluid flow channel 16b into the cold fluid inlets 5a of each cold fluid flow channels 5, after heat exchange in cold fluid flow channels 5 with the thermal fluid (air) in hot fluid flow channels, from each cold fluid outlets 5b into the cold fluid sink groove 16b, then flows from the cold fluid collecting tray 16b to the cold fluid outlet joint 16c, return to the external cold fluid circulation unit.
  • the mandrel 1 of this embodiment is a hollow tube, in which a cold or hot fluid can be fed into the central through hole to enhance the heat transfer capacity of the heat exchanger.
  • spiral winding section in this embodiment is approximately circular, but in practice, a heat conduction thin tape of an oval or a rectangle with rounded corners is also included in the claimed range.
  • the axial length can be increased by series or parallel with multiple sets of heat exchanger, so as to increase the heat transfer time and make the heat transfer between cold fluid and hot fluid more sufficient.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP21899991.0A 2020-12-02 2021-11-30 Spiralwärmetauscher und herstellungsverfahren dafür Pending EP4257906A4 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN202011384544.4A CN112179182B (zh) 2020-12-02 2020-12-02 螺旋换热器及其制法
PCT/CN2021/134289 WO2022116960A1 (zh) 2020-12-02 2021-11-30 螺旋换热器及其制法

Publications (2)

Publication Number Publication Date
EP4257906A1 true EP4257906A1 (de) 2023-10-11
EP4257906A4 EP4257906A4 (de) 2025-01-01

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US (1) US20240011713A1 (de)
EP (1) EP4257906A4 (de)
JP (1) JP7704858B2 (de)
KR (1) KR20230116867A (de)
CN (1) CN112179182B (de)
WO (1) WO2022116960A1 (de)

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CN112179182B (zh) * 2020-12-02 2021-03-02 上海兴邺材料科技有限公司 螺旋换热器及其制法

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JP3090915B1 (ja) * 1999-04-16 2000-09-25 株式会社カンキョー 熱交換器、その製造方法及びそれを含む除湿機
JP2000329484A (ja) * 1999-05-14 2000-11-30 Matsushita Seiko Co Ltd 熱交換素子とその製造方法
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CN214199794U (zh) * 2020-12-02 2021-09-14 上海兴邺材料科技有限公司 一种螺旋换热器

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KR20230116867A (ko) 2023-08-04
CN112179182B (zh) 2021-03-02
WO2022116960A1 (zh) 2022-06-09
JP2023551878A (ja) 2023-12-13
JP7704858B2 (ja) 2025-07-08
EP4257906A4 (de) 2025-01-01
US20240011713A1 (en) 2024-01-11
CN112179182A (zh) 2021-01-05

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