CN112179182A

CN112179182A - Spiral heat exchanger and method for manufacturing same

Info

Publication number: CN112179182A
Application number: CN202011384544.4A
Authority: CN
Inventors: 高峰; 刘在祥; 陈艳凤; 蔡园丰; 王兵; 牛争艳
Original assignee: Shanghai Xingye Material Technology Co Ltd
Current assignee: Shanghai Xingye Material Technology Co Ltd
Priority date: 2020-12-02
Filing date: 2020-12-02
Publication date: 2021-01-05
Anticipated expiration: 2040-12-02
Also published as: US20240011713A1; KR20230116867A; CN112179182B; EP4257906A1; WO2022116960A1; JP2023551878A

Abstract

The present application relates to a spiral heat exchanger and a method for manufacturing the same, the spiral heat exchanger includes: the heat conducting thin strip is spirally wound on the periphery of the core shaft for at least 3 circles; the thin band of heat conduction on arbitrary two adjacent circle layers separates the certain distance, the heat conduction on arbitrary two adjacent circle layers is taken and is all supported between and set up the fender muscle that separates that extends about the setting, each fender muscle is arranged along a radial direction of dabber in proper order, thereby form many hot-fluid flow ways and many cold fluid flow ways of arranging in turn along the radial direction of dabber, every cold fluid exit all is equipped with the first blend stop with its partial shutoff, every hot-fluid exit all is equipped with the second blend stop with its partial shutoff, each first blend stop is arranged along first radial direction in proper order, each second blend stop is arranged along the second radial direction in proper order. The spiral heat exchanger has compact and ingenious structure, small flow resistance, large heat exchange area and high heat exchange efficiency, and is very suitable for gas-gas heat exchange and gas-liquid heat exchange.

Description

Spiral heat exchanger and method for manufacturing same

Technical Field

The application relates to the field of heat exchange, in particular to a spiral heat exchanger and a manufacturing method thereof.

Background

The heat exchanger is equipment for transferring heat of hot fluid to cold fluid, the heat exchanger is mainly applied to life and industrial production, and the traditional heat exchanger generally occupies a large area due to pursuing a larger heat exchange area, so that the heat exchanger has the defects of higher requirement on installation space, inconvenience in maintenance and the like. Therefore, on the premise of ensuring that the heat exchange area is sufficient, how to reduce the size of the heat exchanger is a problem which needs to be solved urgently in the industry.

The utility model discloses a chinese utility model patent with publication number 204495135U discloses a novel spiral plate type reaction heat exchanger, including first sheet metal, the second sheet metal, intermediate bottom and outer barrel, wherein first sheet metal and second sheet metal interval winding constitution double helix shape barrel, intermediate bottom is connected with the first sheet metal and the second sheet metal tip that is close to spiral center department respectively, and separate double helix barrel into two spaces that do not mutually interfere, one of them space is the hot fluid passageway of operation hot fluid (hot-medium entering chamber), another space is the cold fluid passageway of operation cold fluid (cold-medium entering chamber), hot fluid passageway and cold fluid passageway interval distribution, hot fluid passageway and cold fluid passageway are provided with hot fluid import and cold fluid export respectively near spiral center department, hot fluid passageway and cold fluid passageway are provided with hot fluid export and cold fluid import respectively in the position of periphery, when heat exchange is carried out, the surface areas of the first thin plate and the second thin plate are the heat exchange areas of cold and hot fluids, so that the sufficiency of the heat exchange areas is ensured, and meanwhile, the size of the heat exchanger can be effectively reduced due to the arrangement of the double-spiral cylinder. However, the spiral plate type reaction heat exchanger in the patent document has the following disadvantages:

1. the flow resistance is large. The hot fluid and the cold fluid move in the hot fluid flow channel and the cold fluid flow channel respectively along the spiral curling direction, and in the moving process, the moving direction of the fluid is changed at any moment, so that a large interaction force can be generated between the thin plate and the heat exchange fluid, and the flowing resistance of the cold fluid and the hot fluid in the flow channels is large, and the cold fluid and the hot fluid are not suitable for heat exchange of gaseous fluid.

2. The maintenance frequency is high. Although the flow channel of the hot fluid is in a spiral winding shape, the hot fluid is still substantially a space, namely the hot fluid is conveyed in a single flow channel, and the cold fluid flow channel and the cold fluid are conveyed in the same way. By way of example, the single flow channel has the problems that if a certain position of the hot fluid flow channel is blocked, the conveying of the hot fluid in the whole hot fluid flow channel is influenced, the hot fluid cannot be conveyed seriously, so that the heat exchanger cannot work normally, namely, as long as the hot fluid flow channel is blocked at one position, a worker needs to maintain the heat exchanger, and the maintenance frequency is high.

The present application is hereby presented.

Disclosure of Invention

The technical problem that this application will solve is: aiming at the problems, the spiral heat exchanger which has compact and ingenious structure, small flow resistance, large heat exchange area and high heat exchange efficiency and the manufacturing method thereof are provided, and the spiral heat exchanger is very suitable for gas-gas heat exchange and gas-liquid heat exchange.

The technical scheme of the application is as follows:

a spiral heat exchanger comprising:

a mandrel having its axis extending to the left and right, an

The heat conducting thin strip is spirally wound on the periphery of the mandrel for at least 3 circles;

the heat-conducting thin strips of any two adjacent ring layers are separated by a certain distance, and a blocking rib extending leftwards and rightwards is supported and arranged between the heat-conducting thin strips of any two adjacent ring layers, each blocking rib is sequentially arranged along one radial direction of the mandrel, so that a plurality of hot fluid runners and a plurality of cold fluid runners which are alternately arranged along the radial direction of the mandrel are formed, each hot fluid runner is provided with a hot fluid inlet positioned at the left end and a hot fluid outlet positioned at the right end, and each cold fluid runner is provided with a cold fluid outlet positioned at the left end and a cold fluid inlet positioned at the right end;

each cold fluid outlet is provided with a first barrier strip for partially blocking the cold fluid outlet, each hot fluid outlet is provided with a second barrier strip for partially blocking the hot fluid outlet, each first barrier strip is sequentially arranged along the first radial direction of the mandrel, and each second barrier strip is sequentially arranged along the second radial direction of the mandrel.

On the basis of the technical scheme, the application also comprises the following preferable scheme:

every cold fluid exit all is equipped with the third blend stop with its partial shutoff, and each third blend stop is along the third radial direction of dabber arranges in proper order, the third radial direction with first radial direction is nonzero contained angle and arranges.

Every hot-fluid exit all is equipped with the fourth blend stop of its part shutoff, and each fourth blend stop is along the fourth radial direction of dabber arranges in proper order, the fourth radial direction with the second radial direction is nonzero contained angle and arranges.

Every cold fluid exit all is equipped with the fifth blend stop of its partial shutoff, and each fifth blend stop is along the fifth radial direction of dabber arranges in proper order, the fifth radial direction respectively with first radial direction the third radial direction is nonzero contained angle and arranges.

Every cold fluid import department all is equipped with the sixth blend stop with its partial shutoff, and every hot fluid import department all is equipped with the seventh blend stop with its partial shutoff, and each sixth blend stop along the sixth radial direction of dabber arranges in proper order, and each seventh blend stop along the seventh radial direction of dabber arranges in proper order, the sixth radial direction with the second radial direction is nonzero contained angle and arranges, the seventh radial direction with first radial direction is nonzero contained angle and arranges.

Every cold fluid import department all is equipped with the eighth blend stop with its partial shutoff, and every hot fluid import department all is equipped with the ninth blend stop with its partial shutoff, and each eighth blend stop along the eighth radial direction of dabber arranges in proper order, and each ninth blend stop along the ninth radial direction of dabber arranges in proper order, the eighth radial direction respectively with the sixth radial direction the second radial direction is nonzero contained angle and arranges, the ninth radial direction respectively with the seventh radial direction first radial direction is nonzero contained angle and arranges.

And each hot fluid outlet is provided with a tenth barrier strip for partially blocking the hot fluid outlet, each tenth barrier strip is sequentially arranged along the tenth radial direction of the mandrel, and the tenth radial direction is arranged at a nonzero included angle with the eighth radial direction, the sixth radial direction and the second radial direction.

The sixth radial direction with first radial direction is nonzero contained angle and arranges, the seventh radial direction with the second radial direction is nonzero contained angle and arranges.

The area of each cold fluid outlet outside the seventh radial direction is entirely blocked by the first barrier ribs, and the area of each hot fluid outlet outside the sixth radial direction is entirely blocked by the second barrier ribs.

The regions of each cold fluid inlet outside the second radial direction are all blocked by the sixth barrier, and the regions of each hot fluid inlet outside the first radial direction are all blocked by the seventh barrier.

The first barrier strip and the second barrier strip are both arc barrier strips;

in the radial direction from inside to outside of dabber, the length of each first blend stop increases progressively in proper order, and the length of each second blend stop increases progressively in proper order to make each first blend stop be fan-shaped distribution, each second blend stop is fan-shaped distribution.

The sixth barrier strip and the seventh barrier strip are both arc barrier strips;

in the radial direction from inside to outside of the mandrel, the length of each sixth barrier strip is sequentially increased in an increasing manner, the length of each seventh barrier strip is sequentially increased in an increasing manner, and the sixth barrier strips are distributed in a fan shape, and the seventh barrier strips are distributed in a fan shape.

The first blocking strip, the second blocking strip and the blocking ribs are adhesives fixedly bonded with the heat-conducting thin belt.

The third barrier strip and the fourth barrier strip are both adhesives fixedly bonded with the heat-conducting thin strip.

And a plurality of supporting platforms which are arranged at intervals are supported and arranged between the heat conducting thin strips of any two adjacent ring layers.

The heat conduction thin strip is a metal thin strip, and the support table is a stamping bulge formed on the metal thin strip in a stamping mode.

Each stamping bulge is formed on the outer side face of the heat-conducting thin strip.

And one part of the stamping bulge is formed on the outer side surface of the heat-conducting thin strip, and the other part of the stamping bulge is formed on the inner side surface of the heat-conducting thin strip.

The heat conducting thin strip is an aluminum foil.

The thickness of the hot fluid flow channel and the thickness of the cold fluid flow channel in the radial direction of the mandrel are 2-10 mm.

The mandrel is sleeved with a left end cover arranged on the left side of the heat-conducting thin belt in an abutting mode and a right end cover arranged on the right side of the heat-conducting thin belt in an abutting mode, and hot fluid concentrated introducing holes located at the first barrier strips are formed in the left end cover.

And the right end cover is provided with a hot fluid concentrated leading-out hole positioned at each sixth barrier strip.

And the left end cover is also provided with another hot fluid centralized introduction hole positioned at each third baffle bar.

The another hot fluid concentration introduction hole is located at both each of the first barrier ribs and each of the fifth barrier ribs.

And the right end cover is provided with cold fluid centralized introduction holes positioned at the second stop bars.

And cold fluid concentrated leading-out holes positioned at the seventh barrier strips are formed in the left end cover.

The left end cap includes:

a cold fluid collecting groove which is recessed towards the left from the right end surface of the left end cover and is positioned at the seventh barrier strip, an

A cold fluid lead-out connector communicated with the cold fluid collecting groove;

the right end cap includes:

a cold fluid buffer groove recessed rightwards from the left end face of the right end cover and located at the second barrier strip, an

And the cold fluid introduction joint is communicated with the cold fluid buffer groove.

The mandrel is a hollow tube or a solid rod.

And a fan is arranged on one axial side of the heat-conducting thin strip.

The heat conducting thin strip is spirally wound on the periphery of the core shaft in a circular shape.

The heat conducting thin strip is wound on the periphery of the core shaft in a non-circular spiral shape.

The heat-conducting thin strip is spirally wound on the periphery of the core shaft in an oval shape.

The manufacturing method of the spiral heat exchanger comprises the following steps:

and spirally winding the heat-conducting thin strip around the mandrel, coating adhesives with corresponding lengths and used for forming the first barrier strip and the second barrier strip at intervals on the left side edge and the right side edge of the heat-conducting thin strip in the process of winding the heat-conducting thin strip, and coating adhesives used for forming the blocking ribs at intervals on the surface of the heat-conducting thin strip.

In the process of winding the heat-conducting thin strip, punching a plurality of punching bulges which are arranged at intervals are punched on the section to be wound of the heat-conducting thin strip.

The beneficial effect of this application:

1. according to the spiral heat exchanger, the hot fluid flow channels and the cold fluid flow channels extend axially instead of spirally, cold fluid and hot fluid flow in the cold and hot flow channels in a convection mode along the axial direction of the heat exchanger respectively during working, flowing resistance of heat exchange fluid is small, and the spiral heat exchanger is very suitable for gas-gas exchange and gas-liquid exchange.

2. This application is through taking the spiral to coil around the dabber periphery with the heat conduction of individual layer to set up between the heat conduction of adjacent circle layer takes and separate the fender muscle, still take width both sides relevant position in the heat conduction and set up the blend stop, thereby form many hot-fluid runners and the cold fluid runner of crisscross arranging, the import of each hot-fluid runner and cold fluid runner concentrates the different positions that distribute at the heat exchanger respectively, has made things convenient for the leading-in of cold and hot fluid to each runner of this heat exchanger greatly.

3. The maintenance frequency is low. Spiral heat exchanger in this application is taking to be the heliciform through the individual layer heat conduction and winds and make on the dabber, the heat conduction of arbitrary two adjacent circle layers is taken and is all supported the setting and control the fender muscle that separates that extends, a plurality of fender muscle separates into a plurality of hot fluid runners and cold fluid runner of mutual independence with the space that forms between two adjacent circle layers, every hot fluid runner of mutual independence all has respective hot fluid import and hot fluid outlet, every cold fluid runner of mutual independence all has respective cold fluid import and cold fluid outlet, when wherein certain hot fluid runner or cold fluid runner block up, only this fluid passage can't carry, fluid carries out the heat exchange in not influencing other fluid passages, only when a plurality of fluid passages appear simultaneously and block up the condition, just need maintain, thereby the maintenance frequency to the heat exchanger has been reduced.

4. The first radial direction, the sixth radial direction, the third radial direction, the eighth radial direction and the fifth radial direction are arranged at non-zero included angles between every two radial directions, and the second radial direction, the seventh radial direction, the fourth radial direction, the ninth radial direction and the tenth radial direction are arranged at non-zero included angles between every two radial directions, so that the flow stroke of cold and hot fluids in the heat exchanger is improved, and the heat exchange efficiency is further improved.

5. Because the heat-conducting thin strip is spirally wound on the periphery of the mandrel, the heat-conducting thin strips of adjacent layers can be attached during winding or using, and the stamping protrusions are used for separating the adjacent heat-conducting thin strips, determining the distance between the adjacent heat-conducting thin strips and further forming gaps for forming fluid flow passages.

6. When the hot fluid flows in the hot fluid flow channel, the temperature of the hot fluid at the position, in the radial direction of the mandrel, in contact with the heat-conducting thin strip is lower than that of the hot fluid at the position not in contact with the heat-conducting thin strip, and the heat of the hot fluid at the position not in contact with the heat-conducting thin strip cannot be effectively released; the stamping bulge is located on a path when the hot fluid flows, the hot fluid (and the cold fluid) can generate turbulence at the position of the stamping bulge, so that the hot fluid in the hot runner is mixed with each other in the radial direction in the flowing process, the temperature of the hot fluid at the position of contact with the heat-conducting thin strip is increased, the temperature difference between the hot fluid and the cold fluid on the other side of the heat-conducting thin strip is increased, heat exchange is accelerated, and the heat exchange rate is increased.

Meanwhile, the contact area between the heat-conducting thin strip and the fluid is increased by the stamping protrusions, so that heat exchange is better carried out on hot fluid and cold fluid on two sides of the heat-conducting thin strip, and further the heat exchange rate is improved.

7. The heat conducting thin strip is a metal thin strip, the heat conducting coefficient of metal is large, the metal thin strip is used as an excellent heat conducting conductor to carry out heat exchange on hot fluid and cold fluid on two sides, and the heat conducting efficiency is high.

8. The aluminium foil has good heat conductivity, structural strength and ductility, and on the basis of guaranteeing certain structural strength, very thin that can do, the heat conduction thin area is thinner more, and heat conduction efficiency is higher, because its ductility is good simultaneously, is favorable to the bellied preparation of punching press.

9. The manufacturing process is simple. First sheet metal and second sheet metal interval winding constitute two spiral barrels among the background art, need control the relative position of first sheet metal and second sheet metal respectively during spiral winding, and the position that the single-deck heat conduction thin strip heliciform was convoluteed in the dabber in this application, only need control the heat conduction thin strip can.

Drawings

In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings of the embodiments will be briefly introduced below, and it is apparent that the drawings in the following description only relate to some embodiments of the present application and are not limiting on the present application.

FIG. 1 is a schematic overall view of a first spiral heat exchanger in an embodiment of the present application;

FIG. 2 is a general schematic view of a first spiral heat exchanger from another perspective in an embodiment of the present application;

FIG. 3 is a schematic diagram of the internal structure of a first spiral heat exchanger in an embodiment of the present application, in which the mandrel is removed and the stamped projection is hidden;

FIG. 4 is a schematic internal view of the first spiral heat exchanger from another perspective in an embodiment of the present application, wherein the mandrel is removed and the stamped projection is hidden;

FIG. 5 is a schematic cross-sectional view of the interior of a first spiral heat exchanger in an embodiment of the present application, with the mandrel removed and the stamped projections and bars hidden;

FIG. 6 is an axial view of the internal construction of a second spiral heat exchanger in an embodiment of the present application with the mandrel removed;

FIG. 7 is an axial view of the internal construction of a second spiral heat exchanger in an alternate view of an embodiment of the present application with the mandrel removed;

FIG. 8 is an axial view of the internal construction of a third spiral heat exchanger in an embodiment of the present application with the mandrel removed;

FIG. 9 is an axial view of the internal construction of a third spiral heat exchanger of the present embodiment from another perspective with the mandrel removed;

fig. 10 is a schematic structural diagram of the first spiral heat exchanger after the thin heat-conducting strip is unfolded in the embodiment of the present application.

Fig. 11 is a partial perspective view of fig. 10.

Fig. 12 is a partial structural schematic diagram of a thin heat-conducting strip of a first spiral heat exchanger in an embodiment of the present application.

Fig. 13 is a schematic axial cross-sectional view of a first spiral heat exchanger in an embodiment of the present application.

Fig. 14 is a perspective view of the left end cap of the first spiral heat exchanger in the embodiment of the present application.

Fig. 15 is a perspective view of the right end cap of the first spiral heat exchanger in the embodiment of the present application.

Fig. 16 is a schematic perspective cross-sectional view of a left end cap in the first spiral heat exchanger in the embodiment of the present application.

Fig. 17 is a schematic perspective cross-sectional view of a right end cover in the first spiral heat exchanger in the embodiment of the present application.

Wherein:

1-mandrel, 2-heat conducting thin strip, 3-separating barrier rib, 4-hot fluid channel, 5-cold fluid channel, 6-first barrier strip, 7-second barrier strip, 8-third barrier strip, 9-fourth barrier strip, 10-fifth barrier strip, 11-sixth barrier strip, 12-seventh barrier strip, 13-eighth barrier strip, 14-ninth barrier strip, 15-tenth barrier strip, 16-left end cover, 17-right end cover and 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;

2 a-support table, 4 a-hot fluid inlet, 4 b-hot fluid outlet, 5 a-cold fluid inlet, 5 b-cold fluid outlet, 16 a-hot fluid centralized inlet hole, 16 b-cold fluid confluence groove, 16 c-cold fluid outlet joint, 17 a-hot fluid centralized outlet hole, 17 b-cold fluid buffer groove and 17 c-cold fluid inlet joint.

Detailed Description

In order to make the objects, technical solutions and advantages of the embodiments of the present application clearer, the technical solutions of the embodiments of the present application will be clearly and completely described below with reference to the drawings of the embodiments of the present application. It should be apparent that the described embodiments are only some of the embodiments of the present application, and not all embodiments. All other embodiments, which can be derived by a person skilled in the art from the described embodiments of the application without any inventive step, are within the scope of protection of the application.

Unless defined otherwise, technical or scientific terms used herein shall have the ordinary meaning as understood by one of ordinary skill in the art to which this application belongs. The use of the terms "a" or "an" and the like in the description and in the claims of the present application do not denote a limitation of quantity, but rather denote the presence of at least one.

In the description of the present specification and claims, the terms "upper", "lower", "horizontal", and the like indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of describing the present application and simplifying the description, but do not indicate or imply that the referred device or unit must have a specific direction, be constructed in a specific orientation, and be operated, and thus, should not be construed as limiting the present application.

Specific embodiments of the present application will now be described with reference to the accompanying drawings.

The spiral heat exchanger of the embodiment mainly comprises a mandrel 1 and a heat conducting thin strip 2, wherein the heat conducting thin strip 2 is spirally wound on the periphery of the mandrel 1, and the number of winding turns of the heat conducting thin strip 2 is 10. In order to be able to describe the specific structure of the spiral heat exchanger more conveniently, the longitudinal direction of the mandrel 1 is defined as a left-right direction, that is, the axis of the mandrel 1 extends left and right (extends from left to right).

In the present embodiment, the heat conducting thin strips 2 of any two adjacent coil layers are separated by a certain distance, so as to form a spiral gap. And, support and set up the spacer rib 3 that extends from side to side between the thin heat conduction strip of any two adjacent circles layers, thus separate the aforesaid large spiral space into 9 small quasi-circular spaces separated each other by these spacer ribs 3. Further, the blocking ribs 3 are sequentially arranged along a radial direction of the mandrel 1, so that the 9 circular-like gaps are sequentially arranged along the radial direction of the mandrel 1. In the present embodiment, in the radial direction from the inside to the outside of the mandrel 1, the circular-like gaps of the odd-numbered layers, i.e., the first, third, fifth, seventh and ninth layers, are hot fluid flow passages 4 for flowing hot fluid, and the circular-like gaps of the even-numbered layers, i.e., the second, fourth, sixth and eighth layers, are cold fluid flow passages 5 for flowing cold fluid. The hot fluid flow passages 4 and the cold fluid flow passages 5 are alternately arranged in sequence along the radial direction of the mandrel 1. Each hot fluid flow passage 4 has a hot fluid inlet 4a at the left end and a hot fluid outlet 4b at the right end, and each cold fluid flow passage 5 has a cold fluid outlet 5b at the left end and a cold fluid inlet 5a at the right end. In practical application, hot fluid flows from left to right in each hot fluid channel 4, cold fluid flows from right to left in each cold fluid channel 5, and the hot fluid and the cold fluid perform heat convection.

Because the hot fluid inlet 4a of each hot fluid channel 4 and the cold fluid outlet 5b of each cold fluid channel 5 are on the same side (left side) of the heat exchanger and are alternately and closely arranged with each other, the cold fluid inlet 5a of each cold fluid channel 5 and the hot fluid outlet 4b of each hot fluid channel 4 are on the same side (right side) of the heat exchanger and are alternately and closely arranged with each other. If hot fluid and cold fluid are directly fed to the heat exchanger from the left and right sides, respectively, a problem arises in that part of the hot fluid enters the cold fluid flow passage 5 and part of the cold fluid enters the hot fluid flow passage 4. Based on this, the following optimization design is adopted in this embodiment to more conveniently introduce the hot fluid and the cold fluid into each hot fluid channel 4 and each cold fluid channel 5, so as to avoid the mutual series flow of the hot fluid and the cold fluid:

referring to fig. 3, 4, 6 to 9, each of the cold fluid outlets 5b is provided with a first barrier 6 for partially blocking the cold fluid outlet (i.e., the first barrier does not block all of the cold fluid outlets, but blocks only a part of the cold fluid outlets). Each hot fluid outlet 4b is provided with a second stop 7 which partially blocks the hot fluid outlet. Furthermore, the first bars 6 are arranged in sequence along the first radial direction R1 of the mandrel 1, and the second bars 7 are arranged in sequence along the second radial direction R2 of the mandrel 1.

It can be seen that, with the above design, at least a portion of the hot fluid inlet 4a of each hot fluid flow channel 4 is arranged in a concentrated manner in the first radial direction R1 — for convenience of description, the concentrated arrangement region is referred to as a first region. In the first region position, the cold fluid outlet 5b of each cold fluid flow passage 5 is blocked by the first blocking strip 6. In practical use, the hot fluid is only fed to the first region, so that the hot fluid can flow into each hot fluid channel 4 without flowing into the cold fluid channel 5.

At least a part of the cold fluid inlet 5a of each of the cold fluid channels 5 is arranged concentrically in the second region of the above-mentioned second radial direction R2. And, at the aforementioned second area position, the hot fluid outlet 4b of each hot fluid flow path 4 is blocked by the second dam 7. In practical applications, the cold fluid is only sent to the second region, so that the cold fluid can flow into each cold fluid flow channel 5 without flowing into the cold fluid flow channels 5.

If in practical application, all the hot fluid and the cold fluid are only fed into the heat exchanger from the first area and the second area respectively, the areas of the first area and the second area are preferably increased, otherwise the inflow areas of the cold fluid and the hot fluid are small, which is not beneficial to improving the heat exchange efficiency. However, the area of the first and second regions cannot be set to be large due to various factors, and in this case, the inflow area of the cold and hot fluids can be increased by increasing the number of the regions where the cold and hot fluids are collected as shown in fig. 6 and 7, thereby increasing the heat exchange efficiency:

in fig. 6 and 7, each of the cold fluid outlets 5b is further provided with a third barrier 8 for partially blocking the cold fluid outlet, the third barrier 8 are sequentially arranged along the third radial direction R3 of the mandrel 1, and the third radial direction R3 is arranged at a non-zero angle with respect to the first radial direction R1. Each hot fluid outlet 4b is provided with a fourth bar 9 for partially blocking the hot fluid outlet 4b, the fourth bars 9 are arranged in sequence along a fourth radial direction R4 of the mandrel 1, and the fourth radial direction R4 is arranged at a non-zero included angle with the second radial direction R2.

It can be understood that, after the solutions of fig. 6 and 7 are adopted, the heat exchanger has at least two hot fluid collecting areas on the left side thereof and two cold fluid collecting areas on the right side thereof, and the inflow areas of the cold and hot fluids are increased by increasing the number of the cold and hot fluid collecting areas, so as to improve the heat exchange efficiency.

Of course, a larger number of hot and cold fluid collection areas can be provided, such as in the manner shown in fig. 3 and 4: each cold fluid outlet 5b is also provided with a fifth bar 10 partially blocking it, each fifth bar 10 being arranged in succession along a fifth radial direction R5 of the mandrel 1, and the fifth radial direction R5 being arranged at a non-zero angle with respect to the aforementioned first and third radial directions R1 and R3, respectively. In this way, a total of three mutually offset hot fluid intake regions are formed on the left side of the heat exchanger, and a total of two mutually offset cold fluid intake regions are formed on the right side of the heat exchanger.

The scheme solves the problem of how to conveniently feed the cold fluid and the hot fluid into the heat exchanger without considering how to more conveniently lead the cold fluid and the hot fluid in the heat exchanger out independently, which does not influence the use of the heat exchanger in some specific environments. However, in other use environments, we prefer that the cold fluid exiting the heat exchanger not be mixed with the hot fluid and that the hot fluid exiting the heat exchanger not be mixed with the cold fluid, and we can further optimize the heat exchanger as follows:

in the first embodiment shown in fig. 3 and 4, the second embodiment shown in fig. 6 and 7, and the third embodiment shown in fig. 8 and 9, a sixth barrier strip 11 for partially blocking the cold fluid inlet is provided at each cold fluid inlet 5a, and a seventh barrier strip 12 for partially blocking the hot fluid inlet is provided at each hot fluid inlet 4 a. The sixth bars 11 are arranged in sequence along the sixth radial direction R6 of the mandrel 1 and the seventh bars 12 are arranged in sequence along the seventh radial direction R7 of the mandrel 1. The sixth radial direction R6 is disposed at a non-zero angle with respect to the second radial direction R2 and the fourth radial direction R4, respectively, and the seventh radial direction R7 is disposed at a non-zero angle with respect to the third radial direction R3, the first radial direction R1, and the fifth radial direction R5, respectively.

With the above design, at least a part of the hot fluid outlets 4b of the respective hot fluid flow passages 4 are arranged in a concentrated manner in the sixth radial direction R6 — for convenience of description, the concentrated arrangement region is referred to as a sixth region. In the sixth area position, the cold fluid inlet 5a of each cold fluid flow passage 5 is blocked by the sixth stopper 11. Therefore, in practical application, a large hot fluid outlet hole can be arranged in the sixth area so as to intensively lead out the hot fluid after heat exchange and not mix with the cold fluid.

At least a part of the cold fluid outlets 5b of the respective cold fluid flow passages 5 are arranged concentrically in the seventh radial direction R7 described above — for convenience of description, the concentrically arranged region is referred to as a seventh region. And, at the seventh area position, the hot fluid inlet 4a of each hot fluid flow path 4 is blocked by the seventh barrier rib 12. Therefore, in practical application, a large cold fluid outlet hole can be arranged in the seventh area so as to intensively lead out the cold fluid after heat exchange, and the hot fluid is not mixed.

Similarly, if in practical application, all the hot fluid and the cold fluid are only led out from the sixth area and the seventh area respectively, it is better to increase the areas of the sixth area and the seventh area, otherwise, the outflow areas of the cold fluid and the hot fluid are small, which is not beneficial to increase the heat exchange efficiency. However, the areas of the sixth and seventh regions cannot be set to be large, which is influenced by various factors, in this case, the outflow areas of the cold and hot fluids can be increased by increasing the number of the collecting regions of the cold and hot fluids as shown in fig. 6 and 7, so as to improve the heat exchange efficiency:

in fig. 6 and 7, each of the cold fluid inlets 5a is further provided with an eighth barrier 13 for partially blocking the cold fluid inlet, the eighth barriers 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 angle with respect to the sixth radial direction R6, the second radial direction R2 and the fourth radial direction R4. Each hot fluid inlet 4a is further provided with a ninth bar 14 for partially blocking the hot fluid inlet, the ninth bars 14 are sequentially arranged along a ninth radial direction R9 of the mandrel 1, and the ninth radial direction R9 is arranged at a non-zero included angle with the seventh radial direction R7, the third radial direction R3, the first radial direction R1 and the fifth radial direction R5.

It can be understood that, after the solutions of fig. 6 and fig. 7 are adopted, the heat exchanger has at least two cold fluid collecting areas located on the left side thereof and two hot fluid collecting areas located on the right side thereof, and the outflow areas of the cold fluid and the hot fluid are increased by increasing the number of the cold fluid collecting areas and the hot fluid collecting areas, so as to improve the heat exchange efficiency.

Of course, we can also adopt the scheme of setting more cold and hot fluid collecting areas as shown in fig. 3 and 4: in the first embodiment shown in fig. 3 and 4, each cold fluid inlet 5a is further provided with a tenth barrier strip 15 partially blocking it, each tenth barrier strip 15 being arranged in sequence along a tenth radial direction R10 of the mandrel 1, and the tenth radial direction R10 being arranged at a non-zero angle with respect to the aforementioned eighth radial direction R8, sixth radial direction R6, fourth radial direction R4, and second radial direction R2, respectively. In this way, a total of three mutually offset hot fluid collecting areas are formed on the right side of the heat exchanger, and a total of two mutually offset cold fluid collecting areas are formed on the left side of the heat exchanger.

In the first embodiment shown in fig. 3 and 4, the first radial direction R1, the sixth radial direction R6, the third radial direction R3, the eighth radial direction R8 and the fifth radial direction R5 are arranged with a non-zero included angle therebetween, and the second radial direction R2, the seventh radial direction R7, the fourth radial direction R4, the ninth radial direction R9 and the tenth radial direction R10 are arranged with a non-zero included angle therebetween, so that the flow strokes of the cold and hot fluids in the heat exchanger can be increased, and further the heat exchange efficiency can be increased.

As described above, in addition to increasing the inflow and outflow areas of the cold and hot fluids by increasing the number of the cold and hot fluid collecting and discharging areas, thereby increasing the heat exchange efficiency, the heat exchange efficiency of the heat exchanger may be increased by increasing the areas of the first, second, sixth and seventh areas, such as the embodiment shown in fig. 8 and 9:

in fig. 8 and 9, the area of each cold fluid outlet 5b outside the seventh radial direction R7 is entirely blocked by the first bars 6 to obtain a sufficiently large hot fluid collection area. The area of each hot fluid outlet 4b outside the sixth radial direction R6 is entirely blocked by the second bars 7 to obtain a sufficiently large cold fluid collection area. The area of each cold fluid inlet 5a outside the second radial direction R2 is entirely blocked by the sixth bars 11 to obtain a sufficiently large hot fluid collection area. The area of each hot fluid inlet 4a outside the first radial direction R1 is totally blocked by the seventh bars 12 to obtain a sufficiently large cold fluid collection area.

In the first embodiment shown in fig. 3 and 4, the barrier ribs, i.e., the first barrier rib 6, the second barrier rib 7, the third barrier rib 8, the fourth barrier rib 9, the fifth barrier rib 10, the sixth barrier rib 11, the seventh barrier rib 12, the eighth barrier rib 13, the ninth barrier rib 14 and the tenth barrier rib 15 are all arc-shaped barrier ribs. Moreover, in the radial direction from the inside to the outside of the mandrel 1, the length of each first barrier strip 6 increases progressively, the length of each second barrier strip 7 increases progressively, the length of each third barrier strip 8 increases progressively, and the length of each fourth barrier strip 8 increases progressively. And then make each first blend stop 6 be fan-shaped and distribute, each second blend stop 7 is fan-shaped and distributes, and each third blend stop 8 is fan-shaped and distributes, and each fourth blend stop 9 is fan-shaped and distributes, and each fifth blend stop 10 is fan-shaped and distributes, and each sixth blend stop 11 is fan-shaped and distributes, and each seventh blend stop 12 is fan-shaped and distributes, and each eighth blend stop 13 is fan-shaped and distributes, and each ninth blend stop 14 is fan-shaped and distributes, and each tenth blend stop 15 is fan-shaped and distributes. The blocking strips distributed in a fan shape enable the inlets and outlets of the cold and hot fluid flow passages to be correspondingly distributed in a plurality of corresponding fan-shaped areas, and the concentrated introduction and the concentrated extraction of the cold and hot fluids are facilitated.

In the first embodiment shown in fig. 3 and 4, the barrier rib 3 and the barrier ribs, i.e., the first barrier rib 6, the second barrier rib 7, the third barrier rib 8, the fourth barrier rib 9, the fifth barrier rib 10, the sixth barrier rib 11, the seventh barrier rib 12, the eighth barrier rib 13, the ninth barrier rib 14, and the tenth barrier rib 15, are all adhesives that are adhesively fixed to the heat-conductive thin strip 2. During manufacturing, the core shaft 1 is taken as a supporting center, the heat-conducting thin strip 2 is spirally wound on the periphery of the core shaft 1, in the process of winding the heat-conducting thin strip 2, adhesives with corresponding lengths and used for forming barrier strips are coated on the left side edge and the right side edge of the heat-conducting thin strip 2 at intervals, and meanwhile, adhesives used for forming the barrier ribs 3 are coated on the surface of the heat-conducting thin strip 2 at intervals. Of course, the left and right sides of the heat-conducting thin strip 2 may be fully coated with the adhesive, and after the winding is completed, part of the adhesive is removed to form the inlet and outlet for the cold and hot fluids.

It is understood that the barrier strips can not only block the inlet and outlet of the flow channel to concentrate the inlet and outlet of each cold fluid flow channel and hot fluid flow channel at different positions, but also support the heat-conducting thin strips 2 of different ring layers, so that the heat-conducting thin strips 2 of each ring layer are separated by a certain distance to form the flow channel.

Because the barrier strip structures are only arranged on the left side and the right side of the width direction of the heat-conducting thin strip 2, the support strength of the barrier strips to the heat-conducting thin strips 2 of different circle layers is limited, and if the width of the heat-conducting thin strip 2 is large, the heat-conducting thin strips 2 of adjacent circle layers are easy to be close to each other, so that the flow channel is blocked. Based on this, in this embodiment, a plurality of supporting platforms 2a arranged at intervals are supported and disposed between the heat conducting thin strips 2 of any two adjacent ring layers, and the heat conducting thin strips 2 of the adjacent ring layers are supported by the densely distributed supporting platforms 2a, so as to ensure the structural stability of each cold and hot fluid flow channel.

In the first embodiment shown in fig. 3 and 4, the heat conductive thin strip 2 is a metal thin strip, and the support stand 2a is a press-formed protrusion formed by pressing the metal thin strip. When manufacturing, the heat conducting thin strip 2 may be punched to be the stamping protrusion of the support platform 2a in advance, and then the heat conducting thin strip 2 with the stamping protrusion is wound outside the mandrel 1. In the process of winding the heat-conducting thin strip 2, a plurality of punching protrusions arranged at intervals may be punched on the segment to be wound of the heat-conducting thin strip 2, that is, the heat-conducting thin strip 2 may be wound while punching the punching protrusions.

In the first exemplary embodiment shown in fig. 3 and 4, each punch protrusion is formed on the outer side of the heat conducting strip 2, i.e. the side facing away from the mandrel 1.

Of course, the punched protrusions may be provided on both the inner side and the outer side of the thin heat-conducting strip 2.

In another embodiment of the present application, the supporting platform 2a may be a soldered bump. The shapes of the stamping protrusions and the salient points can be hemispheric and cylindrical.

In the first embodiment shown in fig. 3 and 4, the heat conducting thin strip 2 is made of aluminum foil with a thickness less than one millimeter. The distance between the adjacent layers of the thin heat conducting strips 2 is 2-10 mm, namely the thickness of the hot fluid flow channel 4 and the cold fluid flow channel 5 in the radial direction of the mandrel 1 is 2-10 mm. The thin heat-conducting thin strip and the thin fluid flow channel improve the heat exchange area and the heat exchange efficiency of cold and hot fluid.

In the embodiment, the heat conducting thin strip 2 is spirally wound on the periphery of the mandrel 1 in a circular shape, that is, the heat conducting thin strip 2 is in a circular spiral shape, and the heat exchanger in the shape is easier to process and manufacture. In some other embodiments of the present application, the heat conductive thin strip 2 is in a non-circular spiral shape, i.e. the heat conductive thin strip 2 may also be wound around the mandrel 1 in a non-circular spiral shape. Generally, the non-circular spiral is preferably an elliptical spiral, and the heat exchanger with the shape is flat in appearance, more attractive in appearance and capable of being arranged in a flat space, and the flat space is fully utilized to exert the heat exchange performance of the heat exchanger to the maximum extent.

In the first embodiment shown in fig. 3 and 4, a left end cap 16 and a right end cap 17 are sleeved on the mandrel 1. The left end cover 16 and the right end cover 17 are both bolted to the mandrel 1, the left end cover 16 abuts against the left side of the thin heat-conducting strip 2, and the right end cover 17 abuts against the right side of the thin heat-conducting strip 2. The left end cover 16 is provided with two hot fluid centralized inlet holes 16a, and the right end cover 17 is provided with two hot fluid centralized outlet holes 17 a.

Since each of the first bars 6 is disposed closely to each of the fifth bars 10 with only a narrow barrier rib 3 interposed therebetween in this embodiment, the first of the two hot fluid-concentrating introduction holes 16a is simultaneously disposed at the position of each of the first bars 6 and each of the fifth bars 10, and the hot fluid fed from the first hot fluid-concentrating introduction hole 16a can simultaneously flow to each of the hot fluid inlets 4a at the first radial direction R1 and the fifth radial direction R5. The second hot fluid concentrated introduction hole 16a is disposed only at the position of the third barrier 8, and the hot fluid fed from the second hot fluid concentrated introduction hole 16a flows only to the respective hot fluid inlets 4a at the third radial direction R3.

A first one of the foregoing two hot fluid concentrated drawing holes 17a is disposed at the position of each sixth barrier 11, and the hot fluid coming out of each hot fluid outlet 4b at the position of the sixth radial direction R6 is entirely led out from the first hot fluid concentrated drawing hole 17 a. The second hot fluid concentrated drawing hole 17a is disposed at the position of the eighth barrier 13, and all of the hot fluid coming out of the respective hot fluid outlets 4b at the position of the eighth radial direction R6 is led out from the second hot fluid concentrated drawing hole 17 a.

Of course, the left end cover and the right end cover may be respectively provided with a cold fluid concentrated outlet hole located at each seventh stop strip 12 and a cold fluid concentrated inlet hole located at each second stop strip 2, so that the cold fluid is introduced and extracted from right to left along the axial direction of the mandrel 1, but this design is not adopted in this embodiment. As shown in fig. 16 and 17, the left end cap 16 of the present embodiment includes: two cold fluid collecting grooves 16b recessed to the left from the right end surface of the left end cover and respectively located at the seventh barrier rib 12 and the ninth barrier rib 14, and a cold fluid leading-out joint 16c communicated with the two cold fluid collecting grooves 16 b. The right end cover 17 of the present embodiment includes: two cold fluid buffer grooves 17b recessed rightward from the left end surface of the right end cover, and a cold fluid inlet joint 17c communicating with the two cold fluid buffer grooves 17 b. One of the cold fluid buffer grooves 17b is located at both the second bar 7 and the tenth bar 15, and the other is located at the fourth bar 9.

In practical application, the cold fluid inlet connector 17c and the cold fluid outlet connector 16c may be respectively connected to a supply end and a return end of an external cold fluid circulation unit (usually circulating water), and a fan fixed to the left end cap or the right end cap is disposed on one axial side of the spiral heat-conducting thin strip 2 to promote air (hot fluid) to flow in each hot fluid flow channel. The cold fluid flows into the cold fluid collecting groove 16b from the cold fluid inlet joint 17c, then flows into the cold fluid inlets 5a of the cold fluid flow channels 5 from the cold fluid collecting groove 16b, and after heat exchange is performed between the cold fluid flow channels 5 and the hot fluid (air) flowing in the hot fluid flow channels in the opposite direction, flows into the cold fluid collecting groove 16b from the cold fluid outlets 5b, then flows into the cold fluid outlet joint 16c from the cold fluid collecting groove 16b, and flows back to the external cold fluid circulating unit.

The mandrel 1 of the embodiment is a hollow pipe, and cold fluid or hot fluid can be introduced into the central through hole of the mandrel during use, so that the heat exchange capacity of the heat exchanger is enhanced.

For convenience of explanation, the spiral wound cross section is set to be approximately circular in this embodiment, but in actual practice, a heat conductive thin strip having a cross section of various shapes such as an oval shape or a rectangle with rounded corners is also included in the protection scope.

In order to ensure that the cold fluid and the hot fluid can fully exchange heat, the axial length can be increased by adopting a series or parallel connection mode through a plurality of groups of heat exchangers, so that the heat exchange time is prolonged, and the heat exchange between the cold fluid and the hot fluid is more sufficient.

Claims

1. A spiral heat exchanger, comprising:

a mandrel (1) with an axis extending to the left and right, and

a heat conducting thin strip (2) spirally wound on the periphery of the mandrel for at least 3 circles;

the heat-conducting thin strips (2) of any two adjacent ring layers are separated by a certain distance, and a blocking rib (3) extending leftwards and rightwards is supported and arranged between the heat-conducting thin strips of any two adjacent ring layers, each blocking rib (3) is sequentially arranged along one radial direction of the mandrel (1) so as to form a plurality of hot fluid runners (4) and a plurality of cold fluid runners (5) which are alternately arranged along the radial direction of the mandrel (1), each hot fluid runner (4) is provided with a hot fluid inlet (4 a) positioned at the left end and a hot fluid outlet (4 b) positioned at the right end, and each cold fluid runner (5) is provided with a cold fluid outlet (5 b) positioned at the left end and a cold fluid inlet (5 a) positioned at the right end;

each cold fluid outlet (5 b) is provided with a first barrier strip (6) for partially blocking the cold fluid outlet, each hot fluid outlet (4 b) is provided with a second barrier strip (7) for partially blocking the hot fluid outlet, the first barrier strips (6) are sequentially arranged along the first radial direction (R1) of the mandrel (1), and the second barrier strips (7) are sequentially arranged along the second radial direction (R2) of the mandrel (1).

2. Spiral heat exchanger according to claim 1, wherein at each cold fluid outlet (5 b) a third bar (8) is provided partially blocking it, each third bar (8) being arranged in sequence along a third radial direction (R3) of the mandrel (1), the third radial direction (R3) being arranged at a non-zero angle to the first radial direction (R1).

3. A spiral heat exchanger according to claim 2, wherein at each hot fluid outlet (4 b) there is provided a fourth bar (9) partially blocking it, each fourth bar (9) being arranged in sequence along a fourth radial direction (R4) of the mandrel (1), the fourth radial direction (R4) being arranged at a non-zero angle to the second radial direction (R2).

4. A spiral heat exchanger according to claim 3, wherein at each cold fluid outlet (5 b) there is provided a fifth bar (10) partially blocking it, each fifth bar (10) being arranged in sequence along a fifth radial direction (R5) of the mandrel (1), the fifth radial direction (R5) being arranged at a non-zero angle to the first radial direction (R1), respectively the third radial direction (R3).

5. Spiral heat exchanger according to claim 1, wherein at each cold fluid inlet (5 a) a sixth bar (11) partially blocking it is provided, at each hot fluid inlet (4 a) a seventh bar (12) partially blocking it is provided, each sixth bar (11) being arranged in sequence along a sixth radial direction (R6) of the mandrel (1), each seventh bar (12) being arranged in sequence along a seventh radial direction (R7) of the mandrel (1), the sixth radial direction (R6) being arranged at a non-zero angle to the second radial direction (R2), the seventh radial direction (R7) being arranged at a non-zero angle to the first radial direction (R1).

6. Spiral heat exchanger according to claim 5, wherein at each cold fluid inlet (5 a) an eighth bar (13) is provided, which partially blocks it, and at each hot fluid inlet (4 a) a ninth bar (14) is provided, which partially blocks it, each eighth bar (13) being arranged in sequence along an eighth radial direction (R8) of the mandrel (1), each ninth bar (14) being arranged in sequence along a ninth radial direction (R9) of the mandrel (1), the eighth radial direction (R8) being arranged at a non-zero angle to the sixth radial direction (R6), respectively the second radial direction (R2), respectively, and the ninth radial direction (R9) being arranged at a non-zero angle to the seventh radial direction (R7), respectively the first radial direction (R1).

7. Spiral heat exchanger according to claim 6, wherein at each hot fluid outlet (4 b) a tenth bar (15) is provided, partially blocking it, each tenth bar (15) being arranged in sequence along a tenth radial direction (R10) of the mandrel (1), the tenth radial direction (R10) being arranged at a non-zero angle to the eighth radial direction (R8), the sixth radial direction (R6), the second radial direction (R2).

8. A spiral heat exchanger according to claim 5, wherein the sixth radial direction (R6) is arranged at a non-zero angle to the first radial direction (R1) and the seventh radial direction (R7) is arranged at a non-zero angle to the second radial direction (R2).

9. Spiral heat exchanger according to claim 5, wherein the areas of each cold fluid outlet (5 b) outside the seventh radial direction (R7) are all blocked by the first bars (6) and the areas of each hot fluid outlet (4 b) outside the sixth radial direction (R6) are all blocked by the second bars (7).

10. Spiral heat exchanger according to claim 9, wherein the regions of each cold fluid inlet (5 a) outside the second radial direction (R2) are all blocked by the sixth bars (11) and the regions of each hot fluid inlet (4 a) outside the first radial direction (R1) are all blocked by the seventh bars (12).

11. A spiral heat exchanger according to claim 1,

the first barrier strip (6) and the second barrier strip (7) are both arc barrier strips;

in the radial direction from inside to outside of dabber (1), the length of each first blend stop (6) increases progressively in proper order, and the length of each second blend stop (7) increases progressively in proper order to make each first blend stop (6) be fan-shaped distribution, each second blend stop (7) are fan-shaped distribution.

12. A spiral heat exchanger according to claim 5,

the sixth barrier strip (11) and the seventh barrier strip (12) are both arc barrier strips;

in the radial direction from inside to outside of the mandrel (1), the lengths of the sixth barrier strips (11) are sequentially increased in an increasing mode, the lengths of the seventh barrier strips (12) are sequentially increased in an increasing mode, the sixth barrier strips (11) are distributed in a fan shape, and the seventh barrier strips (12) are distributed in a fan shape.

13. The spiral heat exchanger according to claim 1, wherein the first barrier rib (6), the second barrier rib (7) and the barrier rib (3) are all adhesives that are adhesively fixed to the thin heat-conducting strip (2).

14. Spiral heat exchanger according to claim 4, wherein the third barrier strips (8) and the fourth barrier strips (9) are both adhesives adhesively fixed to the thin, thermally conductive strip (2).

15. A spiral heat exchanger according to claim 1, wherein a plurality of supporting platforms (2 a) arranged at intervals are supported and arranged between the heat conducting thin strips (2) of any two adjacent circle layers.

16. A spiral heat exchanger according to claim 15, wherein the thin, heat-conducting strip (2) is a thin metal strip and the brace (2 a) is a stamped projection stamped into the thin metal strip.

17. Spiral heat exchanger according to claim 16, wherein each stamped projection is formed on an outer side face of the thin, heat-conducting strip (2).

18. Spiral heat exchanger according to claim 16, wherein a part of the punched protrusions is formed on the outer side of the thin heat conducting strip (2) and another part of the punched protrusions is formed on the inner side of the thin heat conducting strip (2).

19. Spiral heat exchanger according to claim 16, wherein the thin, heat-conducting strip (2) is an aluminium foil.

20. The spiral heat exchanger according to claim 1, wherein the hot fluid flow channel (4) and the cold fluid flow channel (5) have a thickness of 2-10 mm in a radial direction of the mandrel (1).

21. The spiral heat exchanger according to any one of claims 1 to 20, wherein the mandrel (1) is sleeved with a left end cover (16) abutting against the left side of the thin heat-conducting strip (2) and a right end cover (17) abutting against the right side of the thin heat-conducting strip (2), and the left end cover (16) is provided with a hot fluid concentration introduction hole (16 a) located at each first barrier strip (6).

22. A spiral heat exchanger according to claim 21, when claim 22 is appended to claim 6, wherein the right end cap (17) is formed with a hot fluid concentration lead-out hole (17 a) at each sixth barrier (11).

23. A spiral heat exchanger according to claim 21, when claim 22 is appended to claim 2, wherein the left end cap (16) is further provided with another hot fluid concentrated introduction hole (16 a) at each third baffle (8).

24. A spiral heat exchanger according to claim 23, when claim 22 is appended to claim 4, wherein one of the hot fluid concentration introduction holes (16 a) is located at both the respective first bars (6) and the respective fifth bars (10).

25. A spiral heat exchanger according to claim 21, wherein the right end cap (17) is provided with a cold fluid concentrated introduction hole at each second louver (7).

26. The spiral heat exchanger according to claim 25, when claim 22 is appended to claim 6, wherein the left end cap (16) is provided with a cold fluid concentrated outlet hole at each seventh baffle (12).

27. A spiral heat exchanger according to claim 21, when claim 22 is appended to claim 6,

the left end cap (16) includes:

a cold fluid collecting groove (16 b) recessed to the left from the right end surface of the left end cap and located at the seventh barrier rib (12), an

A cold fluid leading-out joint (16 c) communicated with the cold fluid collecting groove (16 b);

the right end cap (17) comprises:

a cold fluid buffer groove (17 b) which is recessed rightwards from the left end surface of the right end cover and is positioned at the second barrier strip (7), an

A cold fluid introduction joint (17 c) communicated with the cold fluid buffer groove (17 b).

28. A spiral heat exchanger according to claim 1, wherein the mandrel (1) is a hollow tube or a solid rod.

29. Spiral heat exchanger according to claim 1, wherein one axial side of the thin, heat conducting strip (2) is provided with a fan.

30. A spiral heat exchanger according to claim 1, wherein the thin heat conducting strip (2) is spirally wound around the mandrel (1) in a circular shape.

31. A spiral heat exchanger according to claim 1, wherein the thin, heat-conducting strip (2) is wound in a non-circular spiral around the periphery of the mandrel (1).

32. A spiral heat exchanger according to claim 31, wherein the thin, heat-conducting strip (2) is spirally wound in an elliptical shape around the mandrel (1).

33. A method of making a spiral heat exchanger as claimed in any one of claims 1 to 32, comprising:

the method comprises the steps of spirally winding a heat-conducting thin strip (2) on the periphery of a mandrel (1), coating adhesives with corresponding lengths and used for forming a first blocking strip (6) and a second blocking strip (7) at intervals on the left side edge and the right side edge of the heat-conducting thin strip (2) in the process of winding the heat-conducting thin strip (2), and coating the adhesives used for forming a blocking rib (3) at intervals on the surface of the heat-conducting thin strip (2).

34. The method according to claim 33, characterized in that a plurality of punching protrusions arranged at intervals are punched on the section of the heat-conducting strip (2) to be wound during the winding of the heat-conducting strip (2).