Coil type heat exchanger and method for manufacturing the same

Abstract

The coil-type heat exchanger and its manufacturing method are provided with a mandrel (1) whose axis extends laterally, and heat conduction bars (2) wound spirally around the outer periphery of the mandrel (1) for at least three turns, with the heat conduction bars (2) of any two adjacent turn layers spaced a fixed distance apart, and a partition rib (3) extending laterally is installed between the heat conduction bars (2) of any two adjacent turn layers, and each partition rib (3) is arranged sequentially along one radial direction of the mandrel (1), and This forms a plurality of hot fluid flow paths 4 and a plurality of cold fluid flow paths 5 alternately arranged along the radial direction of the mandrel 1, with each cold fluid outlet 5b being provided with a first stop bar 6 partially blocking it, and each hot fluid outlet 4b being provided with a second stop bar 7 partially blocking it, with the first stop bars 6 arranged sequentially along the first radial direction R1 and the second stop bars 7 arranged sequentially along the second radial direction R2. This coil-type heat exchanger has a compact and elegant structure, low flow resistance, a large heat exchange area, and high heat exchange efficiency, making it highly suitable for gas-gas heat exchange and gas-liquid heat exchange.

Description

Technical Field

[0001] The present application relates to the field of heat exchange, and more specifically to a coil-type heat exchanger and a method for manufacturing the same.

Background Art

[0002] A heat exchanger refers to a device that transfers the heat of a hot fluid to a cold fluid. Heat exchangers are widely applied in life and industrial production. In order to pursue a larger heat exchange area, conventional heat exchangers generally have a larger occupied area. Therefore, they have drawbacks such as higher requirements for the installation space and inconvenient maintenance. Thus, how to reduce the volume of the heat exchanger while ensuring a sufficient heat exchange area is an urgent problem to be solved in the industry.

[0003] Utility model registration application number CN201520085162.X discloses a new type of spiral plate reaction heat exchanger, which includes a first thin plate, a second thin plate, an intermediate partition plate, and an outer cylinder. The first thin plate and the second thin plate are wound at intervals to form a double spiral cylinder. The intermediate partition plate is connected to the ends close to the spiral centers of the first thin plate and the second thin plate respectively to partition the double spiral cylinder into two non-interfering spaces. One space is a hot fluid passage (hot medium inlet chamber) for operating the hot fluid, and the other space is a cold fluid passage (cold medium inlet chamber) for operating the cold fluid. The hot fluid passage and the cold fluid passage are arranged at intervals. A hot fluid inlet and a cold fluid outlet are respectively installed at positions close to the spiral centers of the hot fluid passage and the cold fluid passage. A hot fluid outlet and a cold fluid inlet are respectively installed at the outermost peripheral positions of the hot fluid passage and the cold fluid passage. When heat exchange is performed, the surface areas of the first thin plate and the second thin plate are both the heat exchange areas of the hot and cold fluids. While ensuring a sufficient heat exchange area, the volume of the heat exchanger can be effectively reduced by the installation of the double spiral cylinder. However, the spiral plate reaction heat exchanger in this patent document has the following drawbacks.

[0004] First, the flow resistance is greater. The hot fluid and the cold fluid move along the helical bending direction in the hot fluid flow path and the cold fluid flow path respectively. During the movement process, the movement direction of the fluid is constantly changing, and a relatively large interaction force is generated between the thin plate and the heat exchange fluid, increasing the flow resistance in the flow paths of the cold and hot fluids and making it not suitable for the heat exchange of gaseous fluids.

[0005] Second, the maintenance frequency is high. Although the flow path of the hot fluid has a helical bending shape, it is essentially still one space, that is, the hot fluid is transported in a single flow path, and the same applies to the cold fluid flow path and the cold fluid transportation. Taking the hot fluid flow path as an example, the problem of a single flow path is that when the hot fluid flow path is blocked at a certain position, it affects the transportation of the hot fluid in the entire hot fluid flow path, and ultimately directly makes it impossible to transport the hot fluid and the heat exchanger cannot operate normally. That is, when a part of the hot fluid flow path is blocked, the operator needs to maintain the heat exchanger, which means a high maintenance frequency.

[0006] The present application has been made in view of the above.

Summary of the Invention

Problems to be Solved by the Invention

[0007] The technical problem to be solved by the present application is, in view of the above problems, to provide a coil-type heat exchanger with a compact and ingenious structure, small flow resistance, a large heat exchange area, and high heat exchange efficiency, and a manufacturing method thereof, which is very applicable to gas-gas heat exchange and gas-liquid heat exchange.

Means for Solving the Problems

[0008] The technical solution of the present application is as follows. In a first aspect, the present application provides a coil-type heat exchanger, a mandrel whose axis extends horizontally, and a heat conduction bar wound around the outer periphery of the mandrel in a helical shape at least three turns. The heat conduction bars of any two adjacent turn layers are separated by a certain distance, and partition ribs extending left and right are supported and installed between the heat conduction bars of any two adjacent turn layers. Each of the partition ribs is sequentially arranged along one radial direction of the mandrel, thereby forming a plurality of heat fluid channels and a plurality of cold fluid channels alternately arranged along the radial direction of the mandrel. Each of the heat fluid channels has a heat fluid inlet located at the left end and a heat fluid outlet located at the right end, and each of the cold fluid channels has a cold fluid outlet located at the left end and a cold fluid inlet located at the right end. A first stop bar that partially blocks each of the cold fluid outlets is provided, and a second stop bar that partially blocks each of the heat fluid outlets is provided. Each of the first stop bars is sequentially arranged along a first radial direction of the mandrel, and each of the second stop bars is sequentially arranged along a second radial direction of the mandrel.

[0009] In an optional design, a third stop bar that partially blocks each of the cold fluid outlets is provided, and each of the third stop bars is sequentially arranged along a third radial direction of the mandrel. The third radial direction is arranged to form a non-zero included angle with the first radial direction.

[0010] In an optional design, a fourth stop bar that partially blocks each of the heat fluid outlets is provided, and each of the fourth stop bars is sequentially arranged along a fourth radial direction of the mandrel. The fourth radial direction is arranged to form a non-zero included angle with the second radial direction.

[0011] In an optional design, a fifth stop bar that partially blocks each of the cold fluid outlets is provided, and each of the fifth stop bars is sequentially arranged along a fifth radial direction of the mandrel. The fifth radial direction is arranged to form non-zero included angles with the first radial direction and the third radial direction respectively.

[0012] In a selectable design, each cold fluid inlet is provided with a sixth stop bar that partially blocks it, each hot fluid inlet is provided with a seventh stop bar that partially blocks it, each sixth stop bar is sequentially arranged along a sixth radial direction of the mandrel, each seventh stop bar is sequentially arranged along a seventh radial direction of the mandrel, the sixth radial direction is arranged to form a non-zero included angle with each of the second radial direction and the fourth radial direction, and the seventh radial direction is arranged to form a non-zero included angle with each of the third radial direction, the first radial direction, and the fifth radial direction.

[0013] In a selectable design, each cold fluid inlet is provided with an eighth stop bar that partially blocks it, each hot fluid inlet is provided with a ninth stop bar that partially blocks it, each eighth stop bar is sequentially arranged along an eighth radial direction of the mandrel, each ninth stop bar is sequentially arranged along a ninth radial direction of the mandrel, the eighth radial direction is arranged to form a non-zero included angle with each of the sixth radial direction, the second radial direction, and the fourth radial direction, and the ninth radial direction is arranged to form a non-zero included angle with each of the seventh radial direction, the third radial direction, the first radial direction, and the fifth radial direction.

[0014] In a selectable design, each hot fluid outlet is provided with a tenth stop bar that partially blocks it, each tenth stop bar is sequentially arranged along a tenth radial direction of the mandrel, and the tenth radial direction is arranged to form a non-zero included angle with each of the eighth radial direction, the sixth radial direction, the fourth radial direction, and the second radial direction.

[0015] In a selectable design, the sixth radial direction is arranged to form a non-zero included angle with the first radial direction, and the seventh radial direction is arranged to form a non-zero included angle with the second radial direction. All regions other than the seventh radial direction of each cold fluid outlet are blocked by the first stop bar, and all regions other than the sixth radial direction of each hot fluid outlet are blocked by the second stop bar. All regions other than the second radial direction of each cold fluid inlet are blocked by the sixth stop bar, and all regions other than the first radial direction of each hot fluid inlet are blocked by the seventh stop bar.

[0016] In an optional design, both the first stop bar and the second stop bar are arc-shaped stop bars, In the radial direction from the inside to the outside of the mandrel, the length of each first stop bar increases sequentially, the length of each second stop bar increases sequentially, and each first stop bar is arranged in a fan shape, and each second stop bar is arranged in a fan shape.

[0017] Both the sixth stop bar and the seventh stop bar are arc-shaped stop bars, In the radial direction from the inside to the outside of the mandrel, the length of each sixth stop bar increases sequentially, the length of each seventh stop bar increases sequentially, and each sixth stop bar is arranged in a fan shape, and each seventh stop bar is arranged in a fan shape.

[0018] In a second aspect, the present application provides a method for manufacturing the coil type heat exchanger described in the first aspect, The heat conduction bar is spirally wound around the outer circumference of the mandrel, and in the winding process of the heat conduction bar, adhesives with corresponding lengths for forming the first stop bar and the second stop bar are applied at predetermined intervals on the left and right edges of the heat conduction bar, and further adhesives for forming the partition ribs are applied at predetermined intervals on the surface of the heat conduction bar.

[0019] In a third aspect, the present application provides a coil type heat exchanger, a mandrel whose axis extends left and right, a heat conduction bar spirally wound around the outer circumference of the mandrel at least three turns, The heat conduction bars of any two adjacent turn layers are separated by a certain distance, and partition ribs extending left and right are supported and installed between the heat conduction bars of any two adjacent turn layers. Each of the partition ribs is sequentially arranged along one radial direction of the mandrel, thereby forming a plurality of heat fluid channels and a plurality of cold fluid channels that are alternately arranged along the radial direction of the mandrel. Each heat fluid channel has a heat fluid inlet located at the left end and a heat fluid outlet located at the right end, and each cold fluid channel has a cold fluid outlet located at the left end and a cold fluid inlet located at the right end. A sixth stop bar that partially blocks each cold fluid inlet is provided, and a seventh stop bar that partially blocks each heat fluid inlet is provided. Each sixth stop bar is sequentially arranged along the sixth radial direction of the mandrel, and each seventh stop bar is sequentially arranged along the seventh radial direction of the mandrel.

[0020] In an optional design, an eighth stop bar that partially blocks each cold fluid inlet is provided, and a ninth stop bar that partially blocks each heat fluid inlet is provided. Each eighth stop bar is sequentially arranged along the eighth radial direction of the mandrel, and each ninth stop bar is sequentially arranged along the ninth radial direction of the mandrel. The eighth radial direction is arranged to form a non-zero included angle with the sixth radial direction, and the ninth radial direction is arranged to form a non-zero included angle with the seventh radial direction.

[0021] In an optional design, both the sixth stop bar and the seventh stop bar are arc-shaped stop bars. In the radial direction from the inside to the outside of the mandrel, the length of each sixth stop bar increases sequentially, the length of each seventh stop bar increases sequentially, and each sixth stop bar is arranged in a fan shape, and each seventh stop bar is arranged in a fan shape.

[0022] In an optional design, the radian of each sixth stop bar is ≥180°, and the radian of each seventh stop bar is ≥180°.

Advantages of the Invention

[0023] The beneficial effects of the present application are as follows. First, in the coil-type heat exchanger according to the first and third aspects of the present application, each of the hot fluid flow path and the cold fluid flow path does not extend in a spiral shape but extends in the axial direction. During operation, the hot and cold fluids respectively convect and flow along the axial direction of the heat exchanger in the hot and cold flow paths. The flow resistance of the heat exchange fluid is small, and it is very suitable for gas-gas exchange and gas-liquid exchange.

[0024] Second, in the coil-type heat exchanger according to the first aspect of the present application, the heat conduction bars are wound spirally around the outer periphery of the mandrel, and partition ribs are installed between the heat conduction bars of adjacent turn layers. Further, stop bars are installed at corresponding positions on both sides of the width of the heat conduction bars, thereby forming a plurality of hot fluid flow paths and cold fluid flow paths arranged in an intersecting manner. The inlets of each of the hot fluid flow path and the cold fluid flow path are concentrated and arranged at different positions of the heat exchanger, which greatly contributes to the introduction of the hot and cold fluids into each flow path of the heat exchanger.

[0025] Third, in the coil-type heat exchanger according to the third aspect of the present application, the heat conduction bars are wound spirally around the outer periphery of the mandrel, and partition ribs are installed between the heat conduction bars of adjacent turn layers. Further, stop bars are installed at corresponding positions on both sides of the width of the heat conduction bars, thereby forming a plurality of hot fluid flow paths and cold fluid flow paths arranged in an intersecting manner. The outlets of each of the hot fluid flow path and the cold fluid flow path are concentrated and arranged at different positions of the heat exchanger, which greatly contributes to the concentrated derivation of the hot and cold fluids from each flow path of the heat exchanger.

[0026] Fourthly, the coil-type heat exchanger according to the first and third aspects of the present application is formed by spirally winding a heat conduction bar around a mandrel. Partition ribs extending left and right are supported and installed between the heat conduction bars of any two adjacent turn layers. A plurality of partition ribs partition the space formed between two adjacent turn layers into a plurality of independent heat fluid flow paths and cold fluid flow paths. Each independent heat fluid flow path has its own heat fluid inlet and heat fluid outlet, and each independent cold fluid flow path has its own cold fluid inlet and cold fluid outlet. When a certain heat fluid flow path or cold fluid flow path is blocked, only that fluid passage becomes non-transportable and does not affect the heat exchange of the fluid in other fluid passages. Maintenance is only required when a plurality of fluid passages are blocked simultaneously, thereby reducing the maintenance frequency of the heat exchanger.

[0027] Fifthly, the first radial direction, the sixth radial direction, the third radial direction, the eighth radial direction, and the fifth radial direction are arranged such that there is a non-zero included angle for every two of them, and the second radial direction, the seventh radial direction, the fourth radial direction, the ninth radial direction, and the tenth radial direction are arranged such that there is a non-zero included angle for every two of them. This improves the process of the cold and hot fluids flowing through the heat exchanger and further improves the heat exchange efficiency.

Brief Description of the Drawings

[0028] To more clearly explain the technical solution of the embodiment of the present application, the drawings of the embodiment will be briefly described below. Obviously, the drawings described below are only related to a part of the embodiment of the present application and do not limit the present application.

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Embodiments for Carrying Out the Invention

[0029] To make the objectives, 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. Obviously, the described embodiments are part of the embodiments of the present application, rather than all of them. Based on the described embodiments of the present application, any other embodiments obtained by those skilled in the art without inventive labor all belong to the protection scope of the present application.

[0030] In the description of the specification and claims of the present application, terms such as "first" and "second" are for distinguishing the objects to be described, and have no order or technical meaning. Thus, the objects limited by "first", "second", etc. may explicitly or implicitly include one or more of such objects. And similar terms such as "one" or "a" do not indicate a limitation on the number, but indicate that there is at least one, and "a plurality" indicates two or more.

[0031] In the description of the specification and claims of the present application, unless otherwise specified, terms such as "connection", "attachment", "fixation", "accommodation", etc. should be understood in a broad sense. For example, "connection" may be separable connection, integral connection, direct connection, indirect connection through an intermediate element, non-removable connection, or removable connection. Further, for example, "accommodation" does not necessarily mean that the whole is completely accommodated, and this concept further includes a partial accommodation situation where a part protrudes from the outside. Those skilled in the art can understand the specific meaning of the above terms in the present application according to the specific situation.

[0032] In the description of the specification and claims of the present application, the orientation or positional relationship indicated by terms such as "upper", "lower", "horizontal", etc. is the orientation or positional relationship shown in the drawings, and is merely for clearly and simply explaining the present application, and does not indicate or imply that the element pointed to must have a specific direction and must be configured and operated in a specific orientation. These directional terms are relative concepts and are used for relative description and clarification, and may change as the placement orientation of the members in the drawings changes. For example, when the device in the figure is inverted, an element located "below" another element is positioned "above" the other element.

[0033] In the description of the specification and claims of the present application, the orientation or positional relationship indicated by terms such as "upper", "lower", "horizontal", etc. is the orientation or positional relationship shown in the drawings, and is merely for making it easier to explain the present application and simplifying the description, and does not indicate or imply that the device or unit pointed to must have a specific direction and must be configured and operated in a specific orientation. Therefore, it should not be understood as limiting the present application.

[0034] Now, specific embodiments of the present application will be described with reference to the drawings.

[0035] The coil type heat exchanger of this embodiment mainly includes a mandrel 1 and a heat conduction bar 2, the heat conduction bar 2 is spirally wound around the outer periphery of the mandrel 1, and the number of winding turns of the heat conduction bar 2 is 10 turns. To more easily explain the specific structure of the coil type heat exchanger, the length direction of the mandrel 1 is defined as the left-right direction below, that is, the axis of the mandrel 1 extends left and right (extends from left to right).

[0036] In this embodiment, the heat conduction bars 2 of any two adjacent turn layers are separated by a certain distance, thereby forming a spiral gap. Moreover, partition ribs 3 extending left and right are supported and installed between the heat conduction bars of any two adjacent turn layers, and these partition ribs 3 partition the large spiral gap into nine small quasi-elliptical gaps separated from each other. Further, each of these partition ribs 3 is sequentially arranged along one radial direction of the mandrel 1, thereby arranging the nine quasi-elliptical gaps sequentially along the radial direction of the mandrel 1. In this embodiment, in the radial direction from the inside to the outside of the mandrel 1, the quasi-elliptical gaps of the odd-numbered layers, namely the first, third, fifth, seventh, and ninth layers, are heat fluid flow paths 4 for allowing the heat fluid to flow, and the quasi-elliptical gaps of the even-numbered layers, namely the second, fourth, sixth, and eighth layers, are cold fluid flow paths 5 for allowing the cold fluid to flow. The heat fluid flow path 4 and the cold fluid flow path 5 are alternately arranged in sequence along the radial direction of the mandrel 1. Each heat fluid flow path 4 has a heat fluid inlet 4a located at the left end and a heat fluid outlet 4b located at the right end, and each cold fluid flow path 5 has a cold fluid outlet 5b located at the left end and a cold fluid inlet 5a located at the right end. When actually applied, the heat fluid flows through each heat fluid flow path 4 from left to right, and the cold fluid flows through each cold fluid flow path 5 from right to left, and both perform heat exchange by convection.

[0037] Since the heat fluid inlet 4a of each heat fluid flow path 4 and the cold fluid outlet 5b of each cold fluid flow path 5 are located on the same side (left side) of the heat exchanger and are closely arranged alternately with each other, the cold fluid inlet 5a of each cold fluid flow path 5 and the heat fluid outlet 4b of each heat fluid flow path 4 are located on the same side (right side) of the heat exchanger and are closely arranged alternately with each other. If the heat fluid and the cold fluid are directly sent to the heat exchanger from the left side and the right side respectively, a problem will occur that part of the heat fluid enters the cold fluid flow path 5 and part of the cold fluid enters the heat fluid flow path 4. Based on this, this embodiment uses the following optimized design to introduce the heat fluid and the cold fluid into each heat fluid flow path 4 and each cold fluid flow path 5 respectively to avoid the cold and hot fluids becoming turbulent with each other.

[0038] As shown in FIGS. 3, 4, 6 to 9, a first stop bar 6 is provided at each cold fluid outlet 5b to partially block the hot fluid inlet (that is, the first stop bar does not completely block the cold fluid outlet, but only blocks a part of the cold fluid outlet). A second stop bar 7 is provided at each hot fluid outlet 4b to partially block the hot fluid outlet. Moreover, the first stop bars 6 are sequentially arranged along the first radial direction R1 of the mandrel 1, and the second stop bars 7 are sequentially arranged along the second radial direction R2 of the mandrel 1.

[0039] Obviously, after using the above design, at least a part of the hot fluid inlets 4a of the respective hot fluid flow paths 4 of each book are concentratedly arranged in the first radial direction R1, and for the sake of easy explanation, the concentrated arrangement region is referred to as the first region. And at the position of the first region, the cold fluid outlets 5b of the respective cold fluid flow paths 5 of each book are blocked by the first stop bar 6. Therefore, when actually applied, by simply sending the hot fluid to the first region, it can flow into the respective hot fluid flow paths 4 without entering the cold fluid flow path 5.

[0040] At least a part of the cold fluid inlets 5a of the respective cold fluid flow paths 5 of each book are concentratedly arranged in the second region of the second radial direction R2. And at the position of the second region, the hot fluid outlets 4b of the respective hot fluid flow paths 4 of each book are blocked by the second stop bar 7. Therefore, when actually applied, by simply sending the cold fluid to the second region, it can flow into the respective cold fluid flow paths 5 without entering the cold fluid flow path 5.

[0041] In actual application, when all the hot fluid and cold fluid are simply sent to the heat exchanger from the first region and the second region respectively, it is optimal to increase the areas of the first region and the second region. Otherwise, the inflow area of the cold and hot fluids is small, which is disadvantageous for improving the heat exchange efficiency. However, affected by various factors, the areas of the first region and the second region generally cannot be set large. In such a case, by increasing the number of concentrated inflow regions of the cold and hot fluids shown in FIGS. 6 and 7, the inflow area of the cold and hot fluids can be increased, and further the heat exchange efficiency can be improved. In FIGS. 6 and 7, each of the cold fluid outlets 5b is further provided with a third stop bar 8 that partially blocks the cold fluid outlet. The third stop bars 8 are sequentially arranged along the third radial direction R3 of the mandrel 1, and the third radial direction R3 is arranged to form a non-zero included angle with the first radial direction R1. Each of the hot fluid outlets 4b is provided with a fourth stop bar 9 that partially blocks the hot fluid outlet 4b. The fourth stop bars 9 are sequentially arranged along the fourth radial direction R4 of the mandrel 1, and the fourth radial direction R4 is arranged to form a non-zero included angle with the second radial direction R2.

[0042] As can be understood, after using the solutions in FIGS. 6 and 7, the heat exchanger has at least two hot fluid concentrated inflow regions located on its left side and two cold fluid concentrated inflow regions located on its right side. By increasing the number of cold and hot fluid concentrated inflow regions, the inflow area of the cold and hot fluids is increased, and further the heat exchange efficiency is improved.

[0043] Naturally, even more cold and hot fluid concentrated inflow regions can be provided. For example, as shown in FIGS. 3 and 4, each of the cold fluid outlets 5b is further provided with a fifth stop bar 10 that partially blocks it. The fifth stop bars 10 are sequentially arranged along the fifth radial direction R5 of the mandrel 1, and the fifth radial direction R5 is arranged to form a non-zero included angle with the first radial direction R1 and the third radial direction R3 respectively. In this way, a total of three hot fluid concentrated inflow regions that are shifted from each other are formed on the left side of the heat exchanger, and a total of two cold fluid concentrated inflow regions that are shifted from each other are formed on the right side of the heat exchanger.

[0044] The above solutions solve how to easily send the cold and hot fluids to the heat exchanger, but do not consider how to more easily independently guide the cold and hot fluids out of the heat exchanger from each other. This does not affect the use of the heat exchanger in some specific environments. However, in other use environments, it is not only desired that the hot fluid is not mixed into the cold fluid derived from the heat exchanger, but also that the cold fluid is not mixed into the hot fluid derived from the heat exchanger. In response to this, the following further optimization can be performed on the heat exchanger. In the first embodiment shown in FIGS. 3 and 4, the second embodiment shown in FIGS. 6 and 7, and the third embodiment shown in FIGS. 8 and 9, a sixth stop bar 11 that partially blocks each cold fluid inlet 5a is provided at each cold fluid inlet 5a, and a seventh stop bar 12 that partially blocks each hot fluid inlet 4a is provided at each hot fluid inlet 4a. Each sixth stop bar 11 is sequentially arranged along a sixth radial direction R6 of the mandrel 1, and each seventh stop bar 12 is sequentially arranged along a seventh radial direction R7 of the mandrel 1. Moreover, the sixth radial direction R6 is arranged so as to form a non-zero included angle with the second radial direction R2 and the fourth radial direction R4 respectively, and the seventh radial direction R7 is arranged so as to form a non-zero included angle with the third radial direction R3, the first radial direction R1, and the fifth radial direction R5 respectively.

[0045] After using the above design, at least a part of the hot fluid outlets 4b of each hot fluid flow path 4 is concentratedly arranged in the sixth radial direction R6, and for the sake of easy explanation, the concentrated arrangement region is referred to as the sixth region. Moreover, at the position of the sixth region, the cold fluid inlet 5a of each cold fluid flow path 5 is blocked by the sixth stop bar 11. Therefore, when actually applied, one large hot fluid outlet hole may be installed in the sixth region so that the hot fluid after heat exchange can be concentratedly led out from this location without mixing the cold fluid.

[0046] At least a part of the cold fluid outlets 5b of each cold fluid flow path 5 is concentratedly arranged in the seventh radial direction R7, and for the sake of easy explanation, the concentrated arrangement region is referred to as the seventh region. Moreover, at the position of the seventh region, the hot fluid inlet 4a of each hot fluid flow path 4 is blocked by the seventh stop bar 12. Therefore, when actually applied, one large cold fluid outlet hole may be installed in the seventh region so that the cold fluid after heat exchange can be concentratedly led out from this location without mixing the hot fluid.

[0047] Similarly, in actual applications, when all hot and cold fluids are simply derived from the above-mentioned sixth and seventh regions respectively, it is optimal to increase the areas of the sixth and seventh regions. Otherwise, the outflow areas of the cold and hot fluids are small, which is also disadvantageous for improving the heat exchange efficiency. However, due to the influence of various factors, the areas of the above-mentioned sixth and seventh regions generally cannot be set large. In such cases, by increasing the number of concentrated outflow regions of the cold and hot fluids shown in FIGS. 6 and 7, the outflow areas of the cold and hot fluids can be increased, and further the heat exchange efficiency can be improved. In FIGS. 6 and 7, each of the cold fluid inlets 5a is further provided with an eighth stop bar 13 that partially blocks the cold fluid inlet. Each eighth stop bar 13 is sequentially arranged along the eighth radial direction R8 of the mandrel 1, and the eighth radial direction R8 is arranged to form a non-zero included angle with each of the above-mentioned sixth radial direction R6, second radial direction R2, and fourth radial direction R4. Each of the hot fluid inlets 4a is further provided with a ninth stop bar 14 that partially blocks the hot fluid inlet. Each ninth stop bar 14 is sequentially arranged along the ninth radial direction R9 of the mandrel 1, and the ninth radial direction R9 is arranged to form a non-zero included angle with each of the above-mentioned seventh radial direction R7, third radial direction R3, first radial direction R1, and fifth radial direction R5.

[0048] As can be understood, after using the solutions in FIGS. 6 and 7, the heat exchanger has at least two cold fluid concentrated outflow regions located on its left side and two hot fluid concentrated outflow regions located on its right side. By increasing the number of cold and hot fluid concentrated outflow regions, the outflow areas of the cold and hot fluids can be increased, and further the heat exchange efficiency can be improved.

[0049] Of course, solutions for installing a larger number of cold and hot fluid concentrated outflow regions shown in FIGS. 3 and 4 may also be used. In the first embodiment shown in FIGS. 3 and 4, each cold fluid inlet 5a is further provided with a tenth stop bar 15 that partially blocks it. Each tenth stop bar 15 is sequentially arranged along the tenth radial direction R10 of the mandrel 1, and the tenth radial direction R10 is arranged so as to form a non-zero included angle with each of the eighth radial direction R8, the sixth radial direction R6, the fourth radial direction R4, and the second radial direction R2 at 0°. In this way, a total of three hot fluid concentrated outflow regions that are shifted from each other are formed on the right side of the heat exchanger, and a total of two cold fluid concentrated outflow regions that are shifted from each other are formed on the left side of the heat exchanger.

[0050] In the first embodiment shown in FIGS. 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 in pairs so as to form a non-zero included angle, 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 in pairs so as to form a non-zero included angle. In this way, the process of the cold and hot fluids flowing through the heat exchanger can be improved, and the heat exchange efficiency can be further improved.

[0051] As described above, in addition to increasing the heat exchange efficiency by increasing the number of cold and hot fluid concentrated inflow and concentrated outflow regions to increase the inflow and outflow areas of the cold and hot fluids, the heat exchange efficiency of the heat exchanger can be improved by further increasing the areas of the first region, the second region, the sixth region, and the seventh region. For example, in the embodiments shown in FIGS. 8 and 9, In FIGS. 8 and 9, the regions other than the seventh radial direction R7 of each cold fluid outlet 5b are all blocked by the first stop bar 6, thereby obtaining a sufficiently large hot fluid concentrated inflow region. The regions other than the sixth radial direction R6 of each hot fluid outlet 4b are all blocked by the second stop bar 7, thereby obtaining a sufficiently large cold fluid concentrated inflow region. The regions other than the second radial direction R2 of each cold fluid inlet 5a are all blocked by the sixth stop bar 11, thereby obtaining a sufficiently large hot fluid concentrated outflow region. The regions other than the first radial direction R1 of each hot fluid inlet 4a are all blocked by the seventh stop bar 12, thereby obtaining a sufficiently large cold fluid concentrated outflow region.

[0052] In the first embodiment shown in FIGS. 3 and 4, each of the above stop bars, namely the first stop bar 6, the second stop bar 7, the third stop bar 8, the fourth stop bar 9, the fifth stop bar 10, the sixth stop bar 11, the seventh stop bar 12, the eighth stop bar 13, the ninth stop bar 14, and the tenth stop bar 17, is an arc-shaped stop bar. And in the radial direction from the inside to the outside of the mandrel 1, the length of each first stop bar 6 increases sequentially, the length of each second stop bar 7 increases sequentially, the length of each third stop bar 8 increases sequentially, and the length of each fourth stop bar 8 increases sequentially. Further, each first stop bar 6 is arranged in a sector shape, each second stop bar 7 is arranged in a sector shape, each third stop bar 8 is arranged in a sector shape, each fourth stop bar 9 is arranged in a sector shape, each fifth stop bar 10 is arranged in a sector shape, each sixth stop bar 11 is arranged in a sector shape, each seventh stop bar 12 is arranged in a sector shape, each eighth stop bar 13 is arranged in a sector shape, each ninth stop bar 16 is arranged in a sector shape, and each tenth stop bar 17 is arranged in a sector shape. Each stop bar arranged in a sector shape is arranged corresponding to a plurality of sector regions corresponding to the inlets and outlets of each cold and hot fluid flow path, contributing to the concentrated introduction and derivation of cold and hot fluids.

[0053] In the first embodiment shown in FIGS. 3 and 4, the partition rib 3 and each stop bar, namely the first stop bar 6, the second stop bar 7, the third stop bar 8, the fourth stop bar 9, the fifth stop bar 10, the sixth stop bar 11, the seventh stop bar 12, the eighth stop bar 13, the ninth stop bar 14, and the tenth stop bar 17 are all adhesives that are adhesively fixed to the heat conduction bar 2. During manufacturing, with the mandrel 1 as the support center, the heat conduction bar 2 is wound around the outer periphery of the mandrel 1 in a spiral shape. And during the winding process of the heat conduction bar 2, adhesives of corresponding lengths for forming stop bars are applied at predetermined intervals on the left and right edges of the heat conduction bar 2, and adhesives for forming the partition rib 3 are applied on the surface of the heat conduction bar 2 at predetermined intervals. On this day, the left and right edges of the heat conduction bar 2 may be coated with adhesives completely. After the winding is completed, a part of the adhesive is removed to form the inlets and outlets of the cold and hot fluids.

[0054] As can be understood, each of the above stop bars can not only block the inlets and outlets of the flow paths so as to concentrate the inlets and outlets of each cold fluid flow path and each hot fluid flow path at different positions, but also support the heat conduction bars 2 of different turn layers. Thereby, the heat conduction bars 2 of each turn layer are made to form flow paths at a certain distance apart.

[0055] Since the stop bar structure is installed only on the left and right sides in the width direction of the heat conduction bar 2, the support strength of the heat conduction bars 2 of different turn layers by the stop bars is limited. When the width of the heat conduction bar 2 is larger, the heat conduction bars 2 of adjacent turn layers are likely to approach each other and the flow path is easily blocked. Based on this, in this embodiment, a plurality of support bases 2a that are arranged at intervals between any two adjacent turn layers of the heat conduction bar 2 are supported and installed. The support bases 2a arranged without gaps support the heat conduction bars 2 of adjacent turn layers, thereby ensuring the stability of the structure of each cold and hot fluid flow path.

[0056] In the first embodiment shown in FIGS. 3 and 4, the heat conduction bar 2 is a metal bar, and the support base 2a is a press-formed protrusion formed by press-forming on the metal bar. During manufacturing, the press-formed protrusion as the support base 2a may be press-formed in advance on the heat conduction bar 2, and then the heat conduction bar 2 with the press-formed protrusion may be wound around the outside of the mandrel 1. In the winding process of the heat conduction bar 2, a plurality of press-formed protrusions arranged at intervals may be press-formed on the portion of the heat conduction bar 2 to be wound, that is, the heat conduction bar 2 is wound while press-forming the press-formed protrusions.

[0057] In the first embodiment shown in FIGS. 3 and 4, each press-formed protrusion is formed on the outer surface of the heat conduction bar 2, that is, the surface away from the mandrel 1.

[0058] Naturally, press-formed protrusions may be provided on both the inner surface and the outer surface of the heat conduction bar 2.

[0059] In other embodiments of the present application, the support base 2a may be a welding bump. The shapes of the press-formed protrusions and the bumps may be hemispherical or columnar.

[0060] In the first embodiment shown in FIGS. 3 and 4, the heat conduction bar 2 uses an aluminum foil with a thickness of 1 millimeter or less. The distance between the heat conduction bars 2 of adjacent turn layers is 2 to 10 mm, that is, the thickness in the radial direction of the mandrel 1 of the heat fluid flow path 4 and the cold fluid flow path 5 is 2 to 10 mm. The thin heat conduction bar and the thin fluid flow path improve the heat exchange area and heat exchange efficiency of the cold and hot fluids.

[0061] When the hot fluid flows in the hot fluid flow path, in the radial direction of the mandrel, the temperature of the hot fluid at the location where it contacts the heat conduction bar is lower than that of the hot fluid at the location where it does not contact the heat conduction bar. The heat of the hot fluid at the location where it does not contact the heat conduction bar cannot be effectively released. The die pressing protrusion is located in the path where the hot fluid flows, and turbulence occurs at the location of the die pressing protrusion for the hot fluid (and cold fluid), causing the hot fluid in the heat flow path to be mixed with each other in the radial direction during the flowing process, further increasing the temperature of the hot fluid at the location where it contacts the heat conduction bar, increasing the temperature difference with the cold fluid on the other side of the heat conduction bar, accelerating the heat exchange, and further improving the heat exchange rate. At the same time, the die pressing protrusion increases the contact area between the heat conduction bar and the fluid, enabling better heat exchange between the hot fluid and the cold fluid on both sides of the heat conduction bar, and further improving the heat exchange rate.

[0062] In this embodiment, the heat conduction bar 2 is wound around the outer periphery of the mandrel 1 in a circular spiral shape, that is, the heat conduction bar 2 has a circular spiral shape. Such a heat exchanger can be more easily processed and manufactured. In some other embodiments of the present application, the heat conduction bar 2 has a non-circular spiral shape, that is, the heat conduction bar 2 may be wound around the outer periphery of the mandrel 1 in a non-circular spiral shape. Generally, it is preferable that the non-circular spiral is an elliptical spiral. Such a heat exchanger has a flat outer shape, is more beautiful, and is arranged in a flat space to make full use of the flat space and maximize the heat exchange performance of the heat exchanger.

[0063] In the first embodiment shown in FIGS. 3 and 4, one left end cover 16 and one right end cover 17 are sleeved on the mandrel 1. Both the left end cover 16 and the right end cover 17 are bolt-fixed to the mandrel 1, and the left end cover 16 is arranged in contact with the left side of the heat conduction bar 2, and the right end cover 17 is arranged in contact with the right side of the heat conduction bar 2. Two hot fluid concentrated introduction holes 16a are opened in the left end cover 16, and two hot fluid concentrated discharge holes 17a are opened in the right end cover 17.

[0064] In this embodiment, each first stop bar 6 and each fifth stop bar 10 are arranged at a short distance and separated by the narrow stop bar 3. Therefore, the first of the two hot fluid concentrated introduction holes 16a is arranged at the positions of each first stop bar 6 and each fifth stop bar 10 at the same time, and the hot fluid sent from the first hot fluid concentrated introduction hole 16a can flow into each hot fluid inlet 4a in the first radial direction R1 and the fifth radial direction R5 at the same time. The second hot fluid concentrated introduction hole 16a is arranged only at the position of the third stop bar 8, and the hot fluid sent from the second hot fluid concentrated introduction hole 16a flows only into each hot fluid inlet 4a in the third radial direction R3.

[0065] The first of the two hot fluid concentrated discharge holes 17a is arranged at the position of each sixth stop bar 11, and all the hot fluid flowing out from each hot fluid outlet 4b at the position in the sixth radial direction R6 is discharged from the first hot fluid concentrated discharge hole 17a. The second hot fluid concentrated discharge hole 17a is arranged at the position of the eighth stop bar 13, and all the hot fluid flowing out from each hot fluid outlet 4b at the position in the eighth radial direction R6 is discharged from the second hot fluid concentrated discharge hole 17a.

[0066] Naturally, in order to introduce and discharge the cold fluid from right to left along the axial direction of the mandrel 1, cold fluid concentrated discharge holes at the positions of each seventh stop bar 12 and cold fluid concentrated introduction holes at the positions of each second stop bar 2 may be opened in the left end cover and the right end cover respectively. However, this design is not used in this embodiment. As shown in FIGS. 16 and 17, the left end cover 16 of this embodiment includes two cold fluid confluence grooves 16b recessed to the left from the right end face of the left end cover and located at the seventh stop bar 12 and the ninth stop bar 14 respectively, and a cold fluid discharge connector 16c communicating with the two cold fluid confluence grooves 16b. The right end cover 17 of this embodiment includes two cold fluid surge tanks 17b recessed to the right from the left end face of the right end cover, and a cold fluid introduction connector 17c communicating with the two cold fluid surge tanks 17b. One of the cold fluid surge tanks 17b is located at the second stop bar 7 and the tenth stop bar 15 at the same time, and the other is located at the fourth stop bar 9.

[0067] When actually applied, the cold fluid inlet connector 17c and the cold fluid outlet connector 16c may be respectively connected to the supply end and the return end of an external cold fluid circulation unit (generally circulating water). On one side in the axial direction of the helical heat conduction bar 2, a fan fixed to the left end cover or the right end cover is installed to allow air (hot fluid) to flow through each hot fluid flow path. The cold fluid flows from the cold fluid inlet connector 17c into the cold fluid confluence groove 16b, and then from the cold fluid confluence groove 16b into the cold fluid inlets 5a of each cold fluid flow path 5. After exchanging heat with the hot fluid (air) flowing in the opposite direction to the hot fluid flow path in the cold fluid flow path 5, it flows from each cold fluid outlet 5b into the cold fluid confluence groove 16b, and then from the cold fluid confluence groove 16b into the cold fluid outlet connector 16c and flows back to the external cold fluid circulation unit.

[0068] The mandrel 1 of this embodiment is a hollow tube, and in order to enhance the heat exchange capacity of the heat exchanger, cold fluid or hot fluid may be passed through its central through hole during use.

[0069] For ease of explanation, in this embodiment, the helical winding cross-section is installed as approximately circular. However, when actually operating, heat conduction bars with cross-sections of a plurality of shapes such as elliptical or rectangular with fillets are also included within the protection scope.

[0070] In order to sufficiently exchange heat between the cold fluid and the hot fluid, a plurality of sets of heat exchangers can be connected in series or in parallel to increase the axial length, thereby extending the heat exchange time and making the heat exchange between the cold fluid and the hot fluid more sufficient.

Description of Reference Numerals

[0071] 1 Mandrel 2 Introduction Bar 3 Partition Rib 4 Hot Fluid Flow Path 5 Cold Fluid Flow Path 6 First Stop Bar 7 Second Stop Bar 8 Third Stop Bar 9 Fourth Stop Bar 10 Fifth stop bar 11 Sixth stop bar 12 Seventh stop bar 13 Eighth stop bar 14 Ninth stop bar 15 Tenth stop bar 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 Support platform 4a Hot fluid inlet 4b Hot fluid outlet 5a Cold fluid inlet 5b Cold fluid outlet 16a Hot fluid concentrated introduction hole 16b Cold fluid confluence groove 16c Cold fluid outlet connector 17a Hot fluid concentrated outlet hole 17b Cold fluid surge tank 17c Cold fluid inlet connector

Claims

1. A coil-type heat exchanger comprising: a mandrel (1) having an axis extending horizontally; a heat conduction bar (2) wound around the outer periphery of the mandrel in a spiral shape for at least three turns; the heat conduction bars (2) of any two adjacent turn layers are spaced apart by a certain distance, and partition ribs (3) extending horizontally are supported and installed between the heat conduction bars of any two adjacent turn layers. Each of the partition ribs (3) is sequentially arranged along one radial direction of the mandrel (1), thereby forming a plurality of hot fluid flow paths (4) and a plurality of cold fluid flow paths (5) alternately arranged along the radial direction of the mandrel (1). Each of the hot fluid flow paths (4) has a hot fluid inlet (4a) located at the left end and a hot fluid outlet (4b) located at the right end. Each of the cold fluid flow paths (5) has a cold fluid outlet (5b) located at the left end and a cold fluid inlet (5a) located at the right end. A first stop bar (6) that partially blocks each of the cold fluid outlets (5b) is provided, and a second stop bar (7) that partially blocks each of the hot fluid outlets (4b) is provided. Each of the first stop bars (6) is sequentially arranged along a first radial direction (R1) of the mandrel (1), and each of the second stop bars (7) is sequentially arranged along a second radial direction (R2) of the mandrel (1). The heat conduction bar (2) is formed using an aluminum foil with a thickness of 1 millimeter or less, and the distance between the heat conduction bars (2) of adjacent turn layers is 2 to 10 mm. The heat exchanger further includes a left end cover (16) and a right end cover (17) fixedly connected to the mandrel (1). The left end cover (16) is provided with two hot fluid concentrated introduction holes (16a) corresponding to the hot fluid inlet (4a), and the right end cover (17) is provided with two hot fluid concentrated discharge holes (17a) corresponding to the hot fluid outlet (4b). The right end face of the left end cover is recessed to the left to form two cold fluid confluence grooves (16b) corresponding to the cold fluid outlets (5b), and the left end cover is provided with a cold fluid discharge connector (16c) communicating with the cold fluid confluence grooves (16b). The left end face of the right end cover is recessed to the right to form two cold fluid surge tanks (17b) corresponding to the cold fluid inlets (5a). The coil-type heat exchanger is characterized in that a cold-fluid introduction connector (17c) communicating with a cold-fluid surge tank (17b) is provided in the right end cover.

2. A third stop bar (8) that partially blocks each cold-fluid outlet (5b) is provided, and each third stop bar (8) is sequentially arranged along a third radial direction (R3) of the mandrel (1), and the third radial direction (R3) is arranged so as to form a non-zero included angle with the first radial direction (R1). The coil-type heat exchanger according to claim 1, characterized in that.

3. A fourth stop bar (9) that partially blocks each hot-fluid outlet (4b) is provided, and each fourth stop bar (9) is sequentially arranged along a fourth radial direction (R4) of the mandrel (1), and the fourth radial direction (R4) is arranged so as to form a non-zero included angle with the second radial direction (R2). The coil-type heat exchanger according to claim 2, characterized in that.

4. A fifth stop bar (10) that partially blocks each cold-fluid outlet (5b) is provided, and each fifth stop bar (10) is sequentially arranged along a fifth radial direction (R5) of the mandrel (1), and the fifth radial direction (R5) is arranged so as to form non-zero included angles with the first radial direction (R1) and the third radial direction (R3), respectively. The coil-type heat exchanger according to claim 3, characterized in that.

5. A sixth stop bar (11) that partially blocks each cold-fluid inlet (5a) is provided, and a seventh stop bar (12) that partially blocks each hot-fluid inlet (4a) is provided. Each sixth stop bar (11) is sequentially arranged along a sixth radial direction (R6) of the mandrel (1), and each seventh stop bar (12) is sequentially arranged along a seventh radial direction (R7) of the mandrel (1). The sixth radial direction (R6) is arranged so as to form non-zero included angles with the second radial direction (R2) and the fourth radial direction (4), respectively, and the seventh radial direction (R7) is arranged so as to form non-zero included angles with the third radial direction (R3), the first radial direction (R1), and the fifth radial direction (R5), respectively. The coil-type heat exchanger according to claim 4, characterized in that.

6. A first stop bar (13) that partially blocks each cold fluid inlet (5a) is provided, and a ninth stop bar (14) that partially blocks each hot fluid inlet (4a) is provided. Each first stop bar (13) is sequentially arranged along an eighth radial direction (R8) of the mandrel (1), and each ninth stop bar (14) is sequentially arranged along a ninth radial direction (R9) of the mandrel (1). The eighth radial direction (R8) is arranged so as to form a non-zero included angle with each of the sixth radial direction (R6), the second radial direction (R2), and the fourth radial direction (4), and the ninth radial direction (R9) is arranged so as to form a non-zero included angle with each of the seventh radial direction (R7), the third radial direction (R3), the first radial direction (R1), and the fifth radial direction (R5). The coil type heat exchanger according to claim 5, characterized in that.

7. A tenth stop bar (15) that partially blocks each hot fluid outlet (4b) is provided, and each tenth stop bar (15) is sequentially arranged along a tenth radial direction (R10) of the mandrel (1). The tenth radial direction (R10) is arranged so as to form a non-zero included angle with each of the eighth radial direction (R8), the sixth radial direction (R6), the fourth radial direction (R4), and the second radial direction (R2). The coil type heat exchanger according to claim 6, characterized in that.

8. The sixth radial direction (R6) is arranged so as to form a non-zero included angle with the first radial direction (R1), and the seventh radial direction (R7) is arranged so as to form a non-zero included angle with the second radial direction (R2). All regions other than the seventh radial direction (R7) of each cold fluid outlet (5b) are blocked by the first stop bar (6), and all regions other than the sixth radial direction (R6) of each hot fluid outlet (4b) are blocked by the second stop bar (7). All regions other than the second radial direction (R2) of each cold fluid inlet (5a) are blocked by the sixth stop bar (11), and all regions other than the first radial direction (R1) of each hot fluid inlet (4a) are blocked by the seventh stop bar (12). The coil type heat exchanger according to claim 5, characterized in that.

9. Both the first stop bar (6) and the second stop bar (7) are arc-shaped stop bars. In the radial direction from the inside to the outside of the mandrel (1), the length of each first stop bar (6) increases sequentially, the length of each second stop bar (7) increases sequentially, and each first stop bar (6) is arranged in a fan shape, and each second stop bar (7) is arranged in a fan shape. The coil-type heat exchanger according to claim 1, characterized in that.

10. Both the sixth stop bar (11) and the seventh stop bar (12) are arc-shaped stop bars, In the radial direction from the inside to the outside of the mandrel (1), the length of each sixth stop bar (11) increases sequentially, the length of each seventh stop bar (12) increases sequentially, and each sixth stop bar (11) is arranged in a fan shape, and each seventh stop bar (12) is arranged in a fan shape. The coil-type heat exchanger according to claim 5, characterized in that.

11. A method for manufacturing a coil-type heat exchanger according to any one of claims 1 to 10, The heat conduction bar (2) is spirally wound around the outer periphery of the mandrel (1), and in the winding process of the heat conduction bar (2), adhesives of corresponding lengths for forming the first stop bar (6) and the second stop bar (7) are applied at predetermined intervals on the left and right edges of the heat conduction bar (2). At the same time, adhesives for forming the partition ribs (3) are applied on the surface of the heat conduction bar (2) at predetermined intervals. The method for manufacturing a coil-type heat exchanger according to any one of claims 1 to 10, characterized in that.

12. A coil-type heat exchanger, A mandrel (1) whose axis extends left and right, A heat conduction bar (2) wound around the outer periphery of the mandrel at least three times in a spiral shape, and The heat conduction bars (2) of any two adjacent turn layers are separated by a certain distance, and partition ribs (3) extending left and right are supported and installed between the heat conduction bars of any two adjacent turn layers. Each of the partition ribs (3) is sequentially arranged along one radial direction of the mandrel (1), thereby forming a plurality of heat fluid flow paths (4) and a plurality of cold fluid flow paths (5) arranged alternately along the radial direction of the mandrel (1). Each heat fluid flow path (4) has a heat fluid inlet (4a) located at the left end and a heat fluid outlet (4b) located at the right end, and each cold fluid flow path (5) has a cold fluid outlet (5b) located at the left end and a cold fluid inlet (5a) located at the right end. Each cold fluid inlet (5a) is provided with a sixth stop bar (11) that partially blocks it, and each hot fluid inlet (4a) is provided with a seventh stop bar (12) that partially blocks it. Each sixth stop bar (11) is sequentially arranged along the sixth radial direction (R6) of the mandrel (1), and each seventh stop bar (12) is sequentially arranged along the seventh radial direction (R7) of the mandrel (1). The heat conduction bar (2) is formed using an aluminum foil with a thickness of 1 millimeter or less, and the distance between the heat conduction bars (2) of adjacent turn layers is 2 to 10 mm. It further includes a left end cover (16) and a right end cover (17) that are fixedly connected to the mandrel (1). The left end cover (16) is provided with two hot fluid concentrated introduction holes (16a) corresponding to the hot fluid inlets (4a), and the right end cover (17) is provided with two hot fluid concentrated discharge holes (17a) corresponding to the hot fluid outlets (4b). The right end face of the left end cover is recessed to the left to form two cold fluid confluence grooves (16b) corresponding to the cold fluid outlets (5b), and the left end cover is provided with a cold fluid discharge connector (16c) communicating with the cold fluid confluence grooves (16b). The left end face of the right end cover is recessed to the right to form two cold fluid surge tanks (17b) corresponding to the cold fluid inlets (5a). The right end cover is provided with a cold fluid inlet connector (17c) communicating with the cold fluid surge tank (17b), and the coil type heat exchanger is characterized by this.

13. Each cold fluid inlet (5a) is provided with an eighth stop bar (13) that partially blocks it, and each hot fluid inlet (4a) is provided with a ninth stop bar (14) that partially blocks it. Each eighth stop bar (13) is sequentially arranged along the eighth radial direction (R8) of the mandrel (1), and each ninth stop bar (14) is sequentially arranged along the ninth radial direction (R9) of the mandrel (1). The eighth radial direction (R8) is arranged so as to form a non-zero included angle with the sixth radial direction (R6), and the ninth radial direction (R9) is arranged so as to form a non-zero included angle with the seventh radial direction (R7). The coil type heat exchanger according to claim 12 is characterized by this.

14. Both the sixth stop bar (11) and the seventh stop bar (12) are arc-shaped stop bars. In the radial direction from the inside to the outside of the mandrel (1), the length of each sixth stop bar (11) sequentially increases, the length of each seventh stop bar (12) sequentially increases, and each sixth stop bar (11) is arranged in a sector shape, and each seventh stop bar (12) is arranged in a sector shape. The coil type heat exchanger according to claim 12, characterized in that.

15. The coil type heat exchanger according to claim 14, characterized in that the radian of each sixth stop bar (11) ≧ 180°, and the radian of each seventh stop bar (12) ≧ 180°.

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