Patent Application
20240011713
The present invention application relates to the field of heat exchange, and specifically to a spiral heat exchanger and manufacture method therefor.
A heat exchanger refers to the equipment that transfers the heat of the heat fluid to the cold fluid. The heat exchanger has an important application in life and industrial production. Due to the pursuit of a larger heat exchange area, the traditional heat exchanger generally covers a large area, so it has disadvantages such as higher requirements for installation space and inconvenient maintenance. Therefore, on the premise of ensuring sufficient heat exchange area, how to reduce the volume of the heat exchanger is an urgent problem to be solved in the industry.
The Chinese utility model patent with authorized notice number CN201520085162.X exposes a new type of spiral plate reaction heat exchanger which includes a first sheet, a second sheet, a middle partition and an outer cylinder. The first and second plates are spaced apart to form a double spiral cylinder. The middle partition is connected to the ends of the first and second plates near the center of the helix respectively, and separates the double spiral cylinder into two spaces without interference each other. One of the spaces is a hot fluid channel (the hot medium enters the chamber) for running the hot fluid, the other space is a cold fluid channel (the cold medium enters the chamber) for running the cold fluid. The hot and cold fluid channels are arranged into an interval distribution. Hot fluid channel and cold fluid channel are located near the center of the helix with a hot fluid inlet and a cold fluid outlet, respectively, and the hot fluid channel and the cold fluid channel are provided with hot fluid outlet and cold fluid inlet, respectively. When undergoing a heat exchange, the surface areas of both the first and second plates are the heat transfer area of the hot and cold fluid which ensure the sufficient heat transfer area with the setting of a double-helical cylinder, and can effectively reduce the volume of the heat exchanger. However, the spiral plate reaction heat exchanger in the patent document as described above has the following disadvantages.
The present invention application comes from this.
The technical problems to be solved in this application are: in view of the above problems, a spiral heat exchanger and its manufacturing method with compact structure, small flow resistance, a large heat transfer area and high heat transfer efficiency is proposed, which is very suitable for gas-gas heat exchange and gas-liquid heat exchange.
The technical solution of this application is as follows.
In the first aspect of the present invention application, there is provided a spiral heat exchanger, which comprises:
In an optional design, third block bars are disposed at each of the cold fluid outlets for partially blocking thereof, each of the third block bars is sequentially arranged along a third radial direction of the mandrel, the third radial direction and the first radial direction are arranged at a non-zero clip angle.
In an optional design, fourth block bars are disposed at each of the hot fluid outlets for partially blocking thereof, each of the fourth block bars is sequentially arranged along a fourth radial direction of the mandrel, the fourth radial direction and the second radial direction are arranged at a non-zero clip angle.
In an optional design, fifth block bars are disposed at each of the cold fluid outlets for partially blocking thereof, each of the fifth block bars is sequentially arranged along a fifth radial direction of the mandrel; the fifth radial direction is arranged at a non-zero clip angle with the first radial direction and the third radial direction, respectively.
In an optional design, sixth block bars are disposed at each of the cold fluid inlets for partially blocking thereof, seventh block bars are disposed at each of the hot fluid inlets for partially blocking thereof, each of the sixth block bars are sequentially arranged along a sixth radial direction of the mandrel, each of the seventh block bars are sequentially arranged along a seventh radial direction of the mandrel; the sixth radial direction is arranged at a non-zero clip angle with the second radial direction and the fourth radial direction, respectively; the seventh radial direction is arranged at a non-zero clip angle with the third radial direction, the first radial direction and the fifth radial direction, respectively.
In an optional design, eighth block bars are disposed at each of the cold fluid inlets for partially blocking thereof, ninth block bars are disposed at each of the hot fluid inlets for partially blocking thereof, each of the eighth block bars is sequentially arranged alone an eighth radial direction of the mandrel, each of the ninth block bars is sequentially arranged along a ninth radial direction of the mandrel; the eighth radial direction is arranged at a non-zero clip angle with the sixth radial direction, the second radial direction and the fourth radial direction, respectively; the ninth radial direction, and the seventh radial direction, the third radial direction, the first radial direction and the fifth radial direction are respectively arranged at a non-zero clip angle.
In an optional design, tenth block bars are disposed at each of the hot fluid outlets for partially blocking thereof, each of the tenth block bars is sequentially arranged along a tenth radial direction of the mandrel; the tenth radial direction is arranged at a non-zero clip angle with the eighth radial direction, the sixth radial direction, the fourth radial direction and the second radial direction, respectively.
In an optional design, the sixth radial direction and the first radial direction are arranged at a non-zero clip angle, the seventh radial direction and the second radial direction are arranged at a non-zero clip angle;
In an optional design, both the first block bars and the second block bars are an arc block bar;
In the second aspect of the present invention application, there is provided a manufacturing method of the spiral heat exchanger as described in the first aspect of the present invention application, which comprises:
In the third aspect of the present invention application, there is provided a spiral heat exchanger, which comprises:
In an optional design, eighth block bars are disposed at each of the cold fluid inlets for partially blocking thereof, ninth block bars are disposed at each of the hot fluid inlets for partially blocking thereof, each of the eighth block bars is sequentially arranged along a eighth radial direction of the mandrel, each of the ninth block bars is sequentially arranged along a ninth radial direction of the mandrel, the eighth radial direction and the sixth radial direction are arranged at a non-zero clip angle, the ninth radial direction and the seventh radial direction are arranged at a non-zero clip angle.
In an optional design, the sixth block bars and the seventh block bars are arc block bars.
In a radial direction of the mandrel from inside to outside, the lengths of the sixth block bars increase sequentially, the lengths of the seventh block bars increase sequentially, and so that the sixth block bars are fan-distributed, the seventh block bars are fan-distributed.
In an optional design, each of the sixth block bars has a radian ≥180≥, each of the seventh block bars has a radian ≥180°.
Beneficial effects of the present invention application are as follows.
In order to clearly illustrate the technical solution of the embodiments of the invention, the drawings of the embodiments will be briefly described in the following; it is obvious that the described drawings are only related to some embodiments of the invention and thus are not limitative of the invention.
In order to clearly illustrate the technical solution of the embodiments of the invention, the drawings of the embodiments will be briefly described in the following; it is obvious that the described drawings are only related to some embodiments of the invention and thus are not limitative of the invention.
Unless otherwise defined, all the technical and scientific terms used herein have the same meanings as commonly understood by one of ordinary skill in the art to which the present invention belongs. The terms “first,” “second,” etc., which are used in the description and the claims of the present application for invention, are not intended to indicate any sequence, amount or importance, but distinguish various components. Also, the terms such as “a,” “an,” etc., are not intended to limit the amount, but indicate the existence of at least one. The terms “comprise,” “comprising,” “include,” “including,” etc., are intended to specify that the elements or the objects stated before these terms encompass the elements or the objects and equivalents thereof listed after these terms, but do not preclude the other elements or objects. The phrases “connect”, “connected”, etc., are not intended to define a physical connection or mechanical connection, but may include an electrical connection, directly or indirectly. “On,” “under,” “right,” “left” and the like are only used to indicate relative position relationship, and when the position of the object which is described is changed, the relative position relationship may be changed accordingly.
Now, embodiments of the present invention application will be described with reference to the drawings.
The spiral heat exchanger of this embodiment mainly includes a mandrel 1 and a heat conduction thin tape 2, where the heat conduction thin tape 2 is coiled around the periphery of the mandrel 1, and the coil number of heat conduction thin tape 2 is 10 circles. In order to more conveniently describe the specific structure of the spiral heat exchanger, the length direction of mandrel 1 is now defined as the left and right direction, that is, the axis of mandrel 1 extends in left-right direction (extending from left to right).
In this embodiment, the heat conduction thin tape 2 of any two adjacent circle layers are separated by a certain distance to form a spiral void. Moreover, the left and right extended baffle ribs 3 are configured to support between any adjacent two circle layers of the heat conduction thin tape, thereby these baffle ribs 3 are used to separate the large helical voids into nine small class round voids (circular spaces). Further, the aforementioned baffle ribs 3 are arranged along a radial direction of mandrel so that the aforementioned nine circular voids are arranged along the radial direction of the mandrel 1. In this embodiment, in the radial direction of the mandrel 1 from inside to outside, the circular spaces of the first, third, fifth, seventh and ninth layers are hot fluid flow channels 4 for the hot fluid, and the even circular spaces of the second, fourth, sixth and eighth layers are cold fluid flow channels 5 for the cold fluid. Hot fluid flow channels 4 and cold fluid flow channels 5 are sequentially arranged alternately along the radial direction of the mandrel 1. Each of the hot fluid flow channels 4 has a hot fluid inlet 4a located on the left and a hot fluid outlet 4b located on the right, and each of the cold fluid flow channels 5 has a cold fluid outlet 5b located on the left and a cold fluid inlet 5a on the right. In practical application, the hot fluid flows from left to right in each hot fluid flow channels 4, and the cold fluid flows from right to left in each cold fluid flow channels 5, both convective heat exchange.
Since the hot fluid inlet 4a of each hot fluid flow channels 4 and the cold fluid outlet 5b of each cold fluid flow channels 5 are on the same side of the heat exchanger (left side), and alternately closely arranged with each other, the cold fluid inlet 5a of each cold fluid flow channels 5 is on the same side as the hot fluid outlets 4b of each hot fluid flow channels 4 (right side), and alternately closely arranged. If the heat fluid and cold fluid are directly fed to the heat exchanger from the left and right side respectively, part of the heat fluid into the cold fluid flow channels 5 and some cold fluid into the hot fluid flow channels 4 will occur. Based on this, the present embodiment adopts the following optimization design to more conveniently introduce the hot fluid and the cold fluid into each hot fluid flow channels 4 and each cold fluid flow channels 5, respectively, to avoid the hot and cold fluid crosstalk.
Referring to
It is not difficult to see that after adopting the above design, at least part of the hot fluid inlet 4a of each hot fluid flow channels 4 is centrally arranged on the above first radial direction R1 for convenient description, and the centralized arrangement area becomes the first region. Moreover, in the first region, the cold fluid outlet 5b of each cold fluid flow channels 5 is blocked by first block bars 6. Therefore, in practical application, only need to send the hot fluid to the first region, it can flow into each hot fluid flow channels 4, without string into the cold fluid flow channels 5.
At least a part of the cold fluid inlet 5a of each cold fluid flow channels 5 is centrally arranged in the second region of the above second radial direction R2. Moreover, in the second region, the hot fluid outlet 4b of each hot fluid flow channels 4 is blocked by second block bars 7. Therefore, in practical application, only need to send the cold fluid to the aforementioned second region, it can flow into each cold fluid flow channels 5, but not into cold fluid flow channels 5.
If, in practical application, all the hot fluid and cold fluid are only fed into the heat exchanger from the first region and the second region respectively, then it is best to increase the area of the first region and the second region, otherwise the inflow area of the hot fluid is small, which is not conducive to the improvement of heat transfer efficiency. However, due to the influence of various factors, the area of the first and second regions usually cannot be set very large. In this case, the inflow area of the cold and hot fluid can be increased by increasing the number of integrated areas shown in
In
It is not difficult to understand that after adopting the scheme of
Of course, we can also set up even more amounts of cold, hot fluid integration area, for example,
The above solution solves how to bring the cold and heat fluid into the heat exchanger, without considering how to draw the heat fluid independently of each other, which does not affect the use of the heat exchanger in some specific environments. However, in other environments, we hope that the cold fluid derived from the heat exchanger should not be mixed with hot fluid, and that the hot fluid derived from the heat exchanger should not be mixed with cold fluid. Thus, we can do the following further optimization of the heat exchanger.
In the first embodiment shown in
After adopting the above design, at least part of the hot fluid outlet 4b of each hot fluid flow channels 4 is arranged—on the above sixth radial direction R6 for convenient description, and the centralized arrangement area becomes the sixth region. Moreover, at the location of the sixth region, the cold fluid inlet 5a of each cold fluid flow channels 5 is blocked by the sixth block bars 11. Therefore, in practical application, a large hot fluid draw out hole can be provided in the aforementioned sixth region to draw out the heat fluid without incorporating cold fluid.
At least part of the cold fluid outlet 5b of each cold fluid flow channels 5 is arranged—on the above seventh radial direction R7 for convenient description, and the centralized arrangement area becomes the seventh area. Moreover, in the seventh area, the hot fluid inlet 4a of each hot fluid flow channels 4 is blocked by the seventh block bars 12. Therefore, in practical application, a large cold fluid draw out hole can be provided in the aforementioned seventh region to concentrate the heat-exchanged cold fluid from the place without incorporating the hot fluid.
Similarly, if in practical application, all the hot and cold fluids only lead from the sixth and seventh regions respectively, then it is best to improve the area of the sixth and seventh regions, otherwise, the outflow area of the hot fluid is small, which is not conducive to the improvement of heat transfer efficiency. However, due to the influence of various factors, the area of the sixth and seventh areas usually cannot be set very large. In this case, the outflow area of the cold and hot fluid can be increased by increasing the number of the areas in the sets of cold and hot fluid, thus improving the heat transfer efficiency.
In
It is not difficult to understand that after adopting the scheme of
Of course, we can also adopt the setting scheme shown in
In the first embodiment shown in
As mentioned above, in addition to increasing the numbers of cold and hot fluid, and the inflow and outflow area of hot fluid, and then improving the heat transfer efficiency, the heat transfer efficiency of the heat exchanger may also be increased by increasing the area of the first, the second, the sixth and the seventh regions the second area, the sixth heat region and the seventh heat exchanger regions, such as the embodiment shown in
In
In the first embodiment shown in
In the first embodiment shown in
It is not difficult to understand that the above barriers can not only block the inlet and outlet of the flow channels, so that the inlet and outlet of each cold fluid flow channels and hot fluid flow channels are concentrated in different positions, but also support the heat conduction thin tape 2 of different circles, so that the heat conduction thin tape 2 of each circle can form the flow channels at a certain distance.
Because there is only a block structure on the left and the right side of the heat conduction thin tape 2 in the width direction, the support strength of the block for different circles layer heat conduction thin tape 2 is limited. If the width of the heat conduction thin tape 2 is large, the heat conduction thin tape 2 of adjacent circles layer will easily be close to each other, leading to the blockage of the fluid flow channel. Based on this, in the present embodiment, a plurality of supports 2a are configured to support between any adjacent two layers of the heat conduction thin tape 2, and supports the heat conduction thin tape 2 of the adjacent layer, so as to ensure the structural stability of the cold and hot fluid flow channels.
In the first embodiment shown in
In the first embodiment shown in
Of course, it is also possible to set the stamping bumps on both the inner and outer sides of the heat conduction thin tape 2.
In another embodiment of the present invention application, the above support platform 2a may be a welded bump. The shapes of the stamping bulges and bulges can be hemispherical or cylindrical.
In the first embodiment shown in
When the thermal fluid flow in hot fluid flow channels, in the radial direction of the mandrel, the thermal fluid at the contact position with heat conduction thin tape is lower than the thermal fluid not in contact with heat conduction thin tape, and the heat of the hot fluid not in contact with heat conduction thin tape cannot be effectively released; stamping bulge is located in the path of the hot fluid flow, hot fluid (and cold fluid) in the position of stamping bulge will produce turbulence, making the hot flow in the flow process in the radial direction mixing, thus increasing the hot fluid temperature at the contact position with heat conduction thin tape up, increasing the temperature difference with the other side of heat conduction thin tape cold fluid, accelerating the heat exchange, and then improving the heat exchange rate. At the same time, the stamping bulge increases the contact area between heat conduction thin tape and the fluid, so that the hot and cold fluids on both sides of the heat conduction thin tape can exchange heat better, and thus improves the heat exchange rate.
In this embodiment, the heat conduction thin tape 2 is coiled around the periphery of mandrel 1 in a spiral shape, that is, the heat conduction thin tape 2 is a circular spiral shape, which is easier to manufacture. In some other embodiments of the present invention application, the heat conduction thin tape 2 is of a non-circular helical shape, or the heat conduction thin tape 2 may also be coiled around the periphery of mandrel 1 in a non-circular helix. Generally speaking, the aforementioned non-circular spiral is preferably an oval spiral. The heat exchanger of this shape is flat, more beautiful, and can be arranged in a flat space to make full use of the flat space to maximize the heat transfer performance of the heat exchanger.
In the first embodiment shown in
Since each first block bars 6 are arranged in close proximity to each fifth block bars 10 in the present embodiment, there is only a very narrow baffle ribs 3 between them. Therefore, the first one of the two hot fluid concentration introduction holes 16a is simultaneously arranged at the position of each of the first block bars 6 and the fifth block bars 10. The second thermal fluid concentration introduction hole 16a from the first thermal fluid concentration may flow simultaneously to each hot fluid inlets 4a in a first radial direction R1 and a fifth radial direction R5. The second thermal fluid concentration introduction hole 16a is arranged only at the third block bars 8, and the thermal fluid from the second thermal fluid concentration introducing hole 16a flows only to the hot fluid inlet 4a in the third radial direction R3.
The first one of the two hot fluid concentration holes 17a is arranged at the position of each sixth block bars 11, and the thermal fluid from each hot fluid outlets 4b at a position in the sixth radial direction R6 is derived from the first hot fluid concentration hole 17a. The second hot fluid concentration hole 17a is arranged at the position of the eighth block bars 13 and the hot fluid emerging from each hot fluid outlets 4b at a position in the eighth radial direction R6 is derived from the second hot fluid concentration hole 17a.
Of course, we can also open the cold fluid concentration drawing hole at a position of the seventh block bars 12 and the cold fluid concentration drawing hole at a position of each seventh block bars 12 in the second block bars 2, respectively, to make the cold fluid introduce and draw from right to left along the axis of the mandrel 1, but this design is not adopted in this embodiment. As shown in
In practical application, the cold fluid inlet joint 17c and the cold fluid outlet joint 16c can be connected to the supply end and return end of the external cold fluid circulation unit (usually circulating water), respectively, to the axial side of the coil and the heat conduction thin tape 2, prompting the air (hot fluid) to flow in each hot fluid flow channels. The cold fluid flows from the cold fluid inlet joint 17c into the cold fluid collecting tray 16b, from the cold fluid flow channel 16b into the cold fluid inlets 5a of each cold fluid flow channels 5, after heat exchange in cold fluid flow channels 5 with the thermal fluid (air) in hot fluid flow channels, from each cold fluid outlets 5b into the cold fluid sink groove 16b, then flows from the cold fluid collecting tray 16b to the cold fluid outlet joint 16c, return to the external cold fluid circulation unit.
The mandrel 1 of this embodiment is a hollow tube, in which a cold or hot fluid can be fed into the central through hole to enhance the heat transfer capacity of the heat exchanger.
For ease of illustration, the spiral winding section in this embodiment is approximately circular, but in practice, a heat conduction thin tape of an oval or a rectangle with rounded corners is also included in the claimed range.
In order to fully heat exchange between cold fluid and hot fluid, the axial length can be increased by series or parallel with multiple sets of heat exchanger, so as to increase the heat transfer time and make the heat transfer between cold fluid and hot fluid more sufficient.
What are described above is related to the illustrative embodiments of the disclosure only and not limitative to the scope of the disclosure; the scopes of the disclosure are defined by the accompanying claims.
| Number | Date | Country | Kind |
|---|---|---|---|
| 202011384544.4 | Dec 2020 | CN | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/CN2021/134289 | 11/30/2021 | WO |
