MANUFACTURING METHOD FOR A SPIRAL HEAT EXCHANGER

Description

FIELD OF THE INVENTION

[0001] The present invention application relates to the field of heat exchange, and specifically to a manufacturing method of a spiral heat exchanger.

BACKGROUND

[0002] 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.

[0003] 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. When undergoing a heat exchange, 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. However, the spiral plate reaction heat exchanger in the patent document as described above has the following disadvantages.

[0004] 1. The flow resistance is relatively large. A hot fluid and a cold fluid are moved in the spiral coil direction in a hot fluid channel and a cold fluid channel, respectively. In the movement process, the motion directions of the fluids change all the time, and a large interaction force will be generated between the thin plate and the heat exchange fluid, so that the flow resistance of the cold and the hot fluid in the fluid channels is large, which is not suitable for the heat exchange of the gaseous fluid.

[0005] 2. The maintenance frequency is high. Although the fluid channel of the hot fluid is a spiral coil shape, its essence is still a space, that is, the hot fluid is transported in a single fluid channel, and the fluid channel and the fluid transport for the hot fluid and the cold fluid are the same. In hot fluid flow channel, for example, the problem of a single channel is that if hot fluid flow a position blockage, it will affects the hot fluid in the whole hot fluid channel. Serious will directly cause the heat fluid cannot be transported, so that the heat exchanger cannot work normally, that is, as long as there is a position of the hot fluid channel blocked, the staff will need to maintain the heat exchanger, maintenance frequency is high.

[0006] The present invention application comes from this.

[0007] US2008/257534A1 relates to a heat exchanger provided with channels which are separated by separating walls, and which are cross-flown in an alternating manner to the counter flow by one or the other flow mediums (W, K).

SUMMARY

[0008] The invention is set out in the appended set of claims.

BRIEF DESCRIPTION OF THE DRAWINGS

[0009] In order to clearly illustrate the technical solution of the embodiments of the invention, the drawings of the embodiments will be briefly described in the following; it is obvious that the described drawings are only related to some embodiments of the invention and thus are not limitative of the invention.

Fig. 1 is an overall schematic diagram of the first spiral heat exchanger in an embodiment of the present invention application.

Fig. 2 is an overall schematic representation of the first spiral heat exchanger in an embodiment of the present invention application in the other view.

Fig. 3 is a schematic representation of the internal structure of the first spiral heat exchanger in an embodiment of the present invention application, where mandrel is removed and the stamping bulge is hidden.

Fig. 4 is a schematic diagram of the internal structure of the first spiral heat exchanger in an embodiment of the present invention application in another view, where mandrel is removed and the stamping bulge is hidden.

Fig. 5 is a schematic diagram of the internal section structure of the first spiral heat exchanger in an embodiment of the present invention application, where mandrel is removed and the stamping bulge and bar are hidden.

Fig. 6 is an internal structural axis view of the second spiral heat exchanger in an embodiment of the present invention application, where mandrel is removed.

Fig. 7 is an internal structural axis view of the second spiral heat exchanger in an embodiment of the present invention application in another view angle, where the mandrel is moved out.

Fig. 8 is an internal structural axis view of the third spiral heat exchanger in an embodiment of the present invention application, where mandrel is removed.

Fig. 9 is an axis view of the internal structure of third spiral heat exchanger in an embodiment of the present invention application in another view, where mandrel is moved out.

Fig. 10 is a schematic representation of the structure of heat conduction thin tape after unfolded first spiral heat exchanger in an embodiment of the present invention application.

Fig. 11 is a local structural view of Fig. 10.

Fig. 12 is a schematic representation of the local structure of the heat conduction thin tape of the first spiral heat exchanger in an embodiment of the present invention application.

Fig. 13 is a schematic representation of the axial profile of the first spiral heat exchanger in an embodiment of the present invention application.

Fig. 14 is a stereoscopic schematic of the left end cap in first spiral heat exchanger in an embodiment of the present invention application.

Fig. 15 is a stereoscopic schematic of the right-end lid in the first spiral heat exchanger in an embodiment of the present invention application.

Fig. 16 is a stereoscopic schematic of the left end lid in the first spiral heat exchanger in an embodiment of the present invention application.

Fig. 17 is a stereoscopic schematic of the right end lid in the first spiral heat exchanger in an embodiment of the present invention application.

explanation of the reference symbols:

[0010] 

1-mandrel, 2-heat conduct thin tape, 3-baffle ribs, 4-hot fluid flow channels, 5-cold fluid flow channels, 6-first block bars, 7-second block bars, 8-third block bars, 9-fourth block bars, 10-fifth block bars, 11-sixth block bars, 12-seventh block bars, 13-eighth block bars, 14-ninth block bars, 15-tenth block bars, 16-left end cover, 17-right end cover, 18-shell;

R1-first radial direction, R2-second radial direction, R3-third radial direction, R4-fourth radial direction, R5-fifth radial direction, R6-sixth radial direction, R7-seventh radial direction, R8-eighth radial direction, R9-ninth radial direction, R10-tenth radial direction;

2a-hold table, 4a-hot fluid inlet, 4b-hot fluid outlet, 5a-cold fluid inlet, 5b-cold fluid outlet, 16a-hot fluid lead hole, 16b-cold fluid flow tank, 16c-cold fluid lead joint, 17a-hot fluid lead hole, 17b-cold fluid buffer tank, 17c-cold fluid into the joint.

DETAILED DESCRIPTION

[0011] In order to clearly illustrate the technical solution of the embodiments of the invention, the drawings of the embodiments will be briefly described in the following; it is obvious that the described drawings are only related to some embodiments of the invention and thus are not limitative of the invention.

[0012] Unless otherwise defined, all the technical and scientific terms used herein have the same meanings as commonly understood by one of ordinary skill in the art to which the present invention belongs. The terms "first," "second," etc., which are used in the description and the claims of the present application for invention, are not intended to indicate any sequence, amount or importance, but distinguish various components. Also, the terms such as "a," "an," etc., are not intended to limit the amount, but indicate the existence of at least one. The terms "comprise," "comprising," "include," "including," etc., are intended to specify that the elements or the objects stated before these terms encompass the elements or the objects and equivalents thereof listed after these terms, but do not preclude the other elements or objects. The phrases "connect", "connected", etc., are 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.

[0013] Now, embodiments of the present invention application will be described with reference to the drawings.

[0014] 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. In order to more conveniently describe the specific structure of the spiral heat exchanger, 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).

[0015] In this embodiment, the heat conduction thin tape 2 of any two adjacent circle layers are separated by a certain distance to form a spiral void. Moreover, 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). Further, the aforementioned baffle ribs 3 are arranged along a radial direction of mandrel1 so that the aforementioned nine circular voids are arranged along the radial direction of the mandrel 1. In this embodiment, in the radial direction of the mandrel 1 from inside to outside, the circular spaces of the first, third, fifth, seventh and ninth layers are hot fluid flow channels 4 for the hot fluid, and 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, and 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. In practical application, 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.

[0016] Since the hot fluid inlet 4a of 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.

[0017] Referring to Fig. 3, Fig. 4, Fig. 6 to Fig. 9, 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. Moreover, each first block bars 6 are sequentially arranged along the first radial direction R1 of the mandrel 1, and each second block bars 7 are sequentially arranged along the second radial direction R2 of the mandrel 1.

[0018] It is not difficult to see that after adopting the above design, at least part of the hot fluid inlet 4a of 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.

[0019] 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.

[0020] If, in practical application, all the hot fluid and cold fluid are only fed into the heat exchanger from the first region and the second region respectively, then it is best to increase the area of the first region and the second region, otherwise the inflow area of the hot fluid is small, which is not conducive to the improvement of heat transfer efficiency. However, due to the influence of various factors, the area of the first and second regions usually cannot be set very large. In this case, 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.

[0021] In Figs. 6 and 7, 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.

[0022] It is not difficult to understand that after adopting the scheme of Figs. 6 and 7, 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.

[0023] Of course, we can also set up even more amounts of cold, hot fluid integration area, for example, Figs. 3 and 4, 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.

[0024] 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. However, in other environments, we hope that the cold fluid derived from the heat exchanger should not be mixed with hot fluid, and that the hot fluid derived from the heat exchanger should not be mixed with cold fluid. Thus, we can do the following further optimization of the heat exchanger.

[0025] In the first embodiment shown in Figs. 3 and 4, the second embodiment shown in Figs. 6 and 7, the third embodiment shown in Figs. 8 and 9, the sixth block bars 11 blocking the cold fluid inlet at each cold fluid inlets 5a, and 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, and each seventh block bars 12 are along a seventh radial direction R7 of mandrel 1. Moreover, 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, and 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.

[0026] After adopting the above design, at least part of the hot fluid outlet 4b of 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.

[0027] 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.

[0028] Similarly, if in practical application, all the hot and cold fluids only lead from the sixth and seventh regions respectively, then it is best to improve the area of the sixth and seventh regions, otherwise, the outflow area of the hot fluid is small, which is not conducive to the improvement of heat transfer efficiency. However, due to the influence of various factors, 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.

[0029] In Figs. 6 and 7, 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.

[0030] It is not difficult to understand that after adopting the scheme of Figs. 6 and 7, 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.

[0031] Of course, we can also adopt the setting scheme shown in Figs. 3 and 4 for more amounts of cold and fluid collection regions. In the first embodiment shown in Figs. 3 and 4, 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. Thus, 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.

[0032] In the first embodiment shown in Figs. 3 and 4, in the first radial direction R1, 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, and 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. Thus, this can lift flow stroke of the cold and hot fluid in this heat exchanger, then improve the heat transfer efficiency.

[0033] As mentioned above, in addition to increasing the numbers of cold and hot fluid, and the inflow and outflow area of hot fluid, and then improving the heat transfer efficiency, 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.

[0034] In Figs. 8 and 9, the area of 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.

[0035] In the first embodiment shown in Figs. 3 and 4, 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. Moreover, in the radial direction of mandrel 1, 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, and the lengths of each fourth block bars 8 increase sequentially. In turn, 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. By the above fan-shaped distribution, the inlet and the outlet of each cold and hot fluid flow channels are arranged in the corresponding multiple fan areas, which is conducive to the concentrated introduction of the cold and hot fluids.

[0036] In the first embodiment shown in Figs. 3 and 4, mentioned above 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. When manufacturing, with the mandrel1 as the support center, coil the heat conduction thin tape 2 around the periphery of the mandrel 1, and during the winding of the heat conduction thin tape 2, with a certain interval in the length of the left and right sides of the heat conduction thin tape 2, 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, 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. After the winding is completed, part of the adhesive is removed to form the inlet and outlet for the cold and hot fluid.

[0037] It is not difficult to understand that 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.

[0038] Because there is only a block structure on the left and the right side of the heat conduction thin tape 2 in the width direction, the support strength of the block for different circles layer heat conduction thin tape 2 is limited. If the width of the heat conduction thin tape 2 is large, the heat conduction thin tape 2 of adjacent circles layer will easily be close to each other, leading to the blockage of the fluid flow channel. Based on this, in the present embodiment, 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.

[0039] In the first embodiment shown in Figs. 3 and 4, the above heat conduction thin tape 2 is a metal thin strip, and the support platform 2a is a stamping bump formed to stamp on the metal thin strip. When manufacturing, 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. In the process of winding heat conduction thin tape 2, 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.

[0040] In the first embodiment shown in Figs. 3 and 4, each stamping bump is formed on the outer side - of heat conduction thin tape 2, i.e., the side departing from mandrel 1.

[0041] Of course, it is also possible to set the stamping bumps on both the inner and outer sides of the heat conduction thin tape 2.

[0042] In another embodiment of the present invention application, the above support platform 2a may be a welded bump. The shapes of the stamping bulges and bulges can be hemispherical or cylindrical.

[0043] In the first embodiment shown in Figs. 3 and 4, 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.

[0044] When the thermal fluid flow in hot fluid flow channels, in the radial direction of the mandrel, the thermal fluid at the contact position with heat conduction thin tape is lower than the thermal fluid not in contact with heat conduction thin tape, and the heat of the hot fluid not in contact with heat conduction thin tape cannot be effectively released; 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. At the same time, 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.

[0045] In this embodiment, 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. In some other embodiments of the present invention application, 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. Generally speaking, 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.

[0046] In the first embodiment shown in Figs. 3 and 4, 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.

[0047] Since 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.

[0048] 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.

[0049] Of course, we can also open the cold fluid concentration drawing hole at a position of the seventh block bars 12 and the cold fluid concentration drawing hole at a position of each seventh block bars 12 in the second block bars 2, respectively, to make the cold fluid introduce and draw from right to left along the axis of the mandrel 1, but this design is not adopted in this embodiment. As shown in Figs. 16 and 17, 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.

[0050] In practical application, 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.

[0051] 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.

[0052] For ease of illustration, the 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.

[0053] In order to fully heat exchange between cold fluid and hot fluid, 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.

[0054] What are described above is related to the illustrative embodiments of the disclosure only and not limitative to the scope of the disclosure; the scopes of the disclosure are defined by the accompanying claims.

Claims

1. A manufacturing method for a spiral heat exchanger, the spiral heat exchanger comprising:

a mandrel (1) having an axis extending in left- right direction, and

a heat conduction thin tape (2) having a spiral shape wound around the periphery of the mandrel for at least three circles;

any adjacent circles of the heat conduction thin tape (2) are separated by a certain distance, and baffle ribs (3) extending in left-right direction are configured to support between any adjacent two circles of the heat conduction thin tape, each of the baffle ribs (3) is sequentially arranged along a radial direction of the mandrel (1), thereby forming a plurality of hot fluid flow channels (4) and a plurality of cold fluid flow channels (5) 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 at its left end and a hot fluid outlet (4b) located at its right end, each of the cold fluid flow channels (5) has a cold fluid outlet (5b) located at its left end and a cold fluid inlet (5a) located at its right end;

first block bars (6) are disposed at each of the cold fluid outlet (5b) for partially blocking thereof, second block bars (7) are disposed at each of the hot fluid outlet (4b) for partially blocking thereof, each of the first block bars (6) is sequentially arranged along a first radial direction (R1) of the mandrel (1), each of the second block bars (7) is sequentially arranged along a second radial direction (R2) of the mandrel (1);

the manufacturing method comprising:

winding a heat conduction thin tape (2) around the periphery of a mandrel (1) to have a spiral shape;

the manufacturing method characterized by further comprising:
coating an adhesive on the left and right of the heat conduction thin tape (2) for forming first block bars (6) and second block bars (7) on the corresponding position with a certain length at a certain interval, in the process of the winding the heat conduction thin tape (2); meanwhile, coating an adhesive on a surface of the heat conduction thin tape (2) for forming the baffle ribs (3) at a certain interval.

2. The manufacturing method according to claim 1, wherein:

both the first block bars (6) and the second block bars (7) are an arc block bars;

in a radial direction of the mandrel (1) from inside to outside, the length of each of the first block bars (6) increases sequentially, the length of each of the second block bars (7) increases sequentially, and so that the first block bars (6) are fan-distributed, the second block bars (7) are fan-distributed.

Ansprüche

1. Herstellungsverfahren für einen Spiralwärmetauscher, wobei der Spiralwärmetauscher umfasst:

einen Dorn (1), der eine sich in Links-Rechts-Richtung erstreckende Achse aufweist, und

ein Wärmeleit-Dünnband (2), das eine Spiralform aufweist und um den Umfang des Dorns um mindestens drei Umläufe gewickelt ist;

wobei jeweils benachbarte Umläufe des Wärmeleit-Dünnbands (2) durch einen bestimmten Abstand voneinander getrennt sind, und wobei sich in Links-Rechts-Richtung erstreckende Trennrippen (3) dazu eingerichtet sind, zwischen jeweils zwei benachbarten Umläufen des Wärmeleit-Dünnbands abzustützen, wobei die Trennrippen (3) entlang einer radialen Richtung des Dorns (1) der Reihe nach angeordnet sind, wodurch eine Mehrzahl von Heißfluid-Strömungskanälen (4) und eine Mehrzahl von Kaltfluid-Strömungskanälen (5) gebildet werden, die abwechselnd entlang der radialen Richtung des Dorns (1) angeordnet sind, wobei jeder der Heißfluid-Strömungskanäle (4) einen an seinem linken Ende angeordneten Heißfluid-Einlass (4a) und einen an seinem rechten Ende angeordneten Heißfluid-Auslass (4b) aufweist, wobei jeder der Kaltfluid-Strömungskanäle (5) einen an seinem linken Ende angeordneten Kaltfluid-Auslass (5b) und einen an seinem rechten Ende angeordneten Kaltfluid-Einlass (5a) aufweist;

wobei erste Sperrleisten (6) jeweils an dem Kaltfluid-Auslass (5b) zum teilweisen Sperren desselben angeordnet sind, wobei zweite Sperrleisten (7) jeweils an dem Heißfluid-Auslass (4b) zum teilweisen Sperren desselben angeordnet sind, wobei die ersten Sperrleisten (6) entlang einer ersten radialen Richtung (R1) des Dorns (1) der Reihe nach angeordnet sind, wobei die zweiten Sperrleisten (7) entlang einer zweiten radialen Richtung (R2) des Dorns (1) der Reihe nach angeordnet sind;

wobei das Herstellungsverfahren umfasst:

Wickeln eines Wärmeleit-Dünnbands (2) um den Umfang eines Dorns (1), so dass es eine Spiralform aufweist;

wobei das Herstellungsverfahren dadurch gekennzeichnet ist, dass es ferner umfasst:
Aufbringen eines Klebstoffs auf die linke und rechte Seite des Wärmeleit-Dünnbands (2), um während des Wickelns des Wärmeleit-Dünnbands (2) an entsprechenden Positionen erste Sperrleisten (6) und zweite Sperrleisten (7) mit einer bestimmten Länge und in einem bestimmten Abstand zu bilden; gleichzeitig Aufbringen eines Klebstoffs auf eine Oberfläche des Wärmeleit-Dünnbands (2), um die Trennrippen (3) in einem bestimmten Abstand zu bilden.

2. Herstellungsverfahren nach Anspruch 1, wobei:

sowohl die ersten Sperrleisten (6) als auch die zweiten Sperrleisten (7) bogenförmige Sperrleisten sind;

wobei in einer radialen Richtung des Dorns (1) von innen nach außen die Länge jeder der ersten Sperrleisten (6) der Reihe nach zunimmt und die Länge jeder der zweiten Sperrleisten (7) der Reihe nach zunimmt, so dass die ersten Sperrleisten (6) fächerförmig verteilt sind und die zweiten Sperrleisten (7) fächerförmig verteilt sind.

Revendications

1. Procédé de fabrication d'un échangeur de chaleur en spirale, l'échangeur de chaleur en spirale comprenant :

un mandrin (1) ayant un axe s'étendant dans la direction gauche-droite, et

une bande mince thermoconductrice (2) ayant une forme en spirale enroulée autour de la périphérie du mandrin sur au moins trois spires ;

toutes spires adjacentes de la bande mince thermoconductrice (2) sont séparés par une certaine distance, et des nervures de déflecteur (3) s'étendant dans la direction gauche-droite sont configurées pour supporter entre deux spires adjacentes quelconques de la bande mince thermoconductrice, chacune des nervures de déflecteur (3) est agencée séquentiellement le long d'une direction radiale du mandrin (1), formant ainsi une pluralité de canaux d'écoulement de fluide chaud (4) et une pluralité de canaux d'écoulement de fluide froid (5) disposés alternativement le long de la direction radiale du mandrin (1), chacun des canaux d'écoulement de fluide chaud (4) a une entrée de fluide chaud (4a) située à son extrémité gauche et une sortie de fluide chaud (4b) située à son extrémité droite, chacun des canaux d'écoulement de fluide froid (5) a une sortie de fluide froid (5b) située à son extrémité gauche et une entrée de fluide froid (5a) située à son extrémité droite ;

des premières barres de blocage (6) sont disposées à chaque sortie de fluide froid (5b) pour la bloquer partiellement, des deuxièmes barres de blocage (7) sont disposées à chaque sortie de fluide chaud (4b) pour la bloquer partiellement, chacune des premières barres de blocage (6) est agencée séquentiellement le long d'une première direction radiale (R1) du mandrin (1), chacune des deuxièmes barres de blocage (7) est agencée séquentiellement le long d'une deuxième direction radiale (R2) du mandrin (1) ;

le procédé de fabrication comprenant :

l'enroulement d'une bande mince thermoconductrice (2) autour de la périphérie d'un mandrin (1) pour avoir une forme en spirale ;

le procédé de fabrication caractérisé en ce qu'il comprend en outre :
l'application d'un adhésif sur la gauche et la droite de la bande mince thermoconductrice (2) pour former des premières barres de blocage (6) et des deuxièmes barres de blocage (7) sur la position correspondante avec une certaine longueur à un certain intervalle, dans le processus de l'enroulement de la bande mince thermoconductrice (2) ; en même temps, l'application d'un adhésif sur une surface de la bande mince thermoconductrice (2) pour former les nervures de déflecteur (3) à un certain intervalle.

2. Procédé de fabrication selon la revendication 1, dans lequel :

les premières barres de blocage (6) et les deuxièmes barres de blocage (7) sont toutes deux des barres de blocage en arc ;

dans une direction radiale du mandrin (1) de l'intérieur vers l'extérieur, la longueur de chacune des premières barres de blocage (6) augmente séquentiellement, la longueur de chacune des deuxièmes barres de blocage (7) augmente séquentiellement, et de sorte que les premières barres de blocage (6) sont distribuées en éventail, les deuxièmes barres de blocage (7) sont distribuées en éventail.

Drawing