CN114061358A - Heat exchange tube of falling film evaporator - Google Patents
Heat exchange tube of falling film evaporator Download PDFInfo
- Publication number
- CN114061358A CN114061358A CN202010769122.2A CN202010769122A CN114061358A CN 114061358 A CN114061358 A CN 114061358A CN 202010769122 A CN202010769122 A CN 202010769122A CN 114061358 A CN114061358 A CN 114061358A
- Authority
- CN
- China
- Prior art keywords
- heat exchange
- exchange tube
- liquid guide
- guide groove
- main body
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 239000011552 falling film Substances 0.000 title claims abstract description 45
- 239000007788 liquid Substances 0.000 claims abstract description 104
- 239000012530 fluid Substances 0.000 claims 1
- 239000010408 film Substances 0.000 abstract description 15
- 238000001704 evaporation Methods 0.000 description 21
- 230000008020 evaporation Effects 0.000 description 21
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 13
- 238000012546 transfer Methods 0.000 description 8
- 239000007921 spray Substances 0.000 description 7
- 230000000694 effects Effects 0.000 description 6
- 238000009792 diffusion process Methods 0.000 description 5
- 238000001035 drying Methods 0.000 description 5
- 238000002474 experimental method Methods 0.000 description 5
- 238000000034 method Methods 0.000 description 4
- 238000009826 distribution Methods 0.000 description 3
- 239000011148 porous material Substances 0.000 description 3
- 230000002411 adverse Effects 0.000 description 2
- 230000005484 gravity Effects 0.000 description 2
- 238000011835 investigation Methods 0.000 description 2
- 230000000149 penetrating effect Effects 0.000 description 2
- 238000006467 substitution reaction Methods 0.000 description 2
- 238000009827 uniform distribution Methods 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 239000003507 refrigerant Substances 0.000 description 1
- 238000012360 testing method Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/14—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally
- F28F1/16—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally the means being integral with the element, e.g. formed by extrusion
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/14—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally
- F28F1/16—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally the means being integral with the element, e.g. formed by extrusion
- F28F1/18—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally the means being integral with the element, e.g. formed by extrusion the element being built-up from finned sections
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
- F28F1/26—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means being integral with the element
Abstract
The invention belongs to the technical field of heat exchange, and particularly provides a heat exchange tube of a falling film evaporator. The invention aims to solve the problem that the heat exchange efficiency is easily influenced due to poor arrangement mode of the T-shaped fins of the conventional heat exchange tube. Therefore, the heat exchange tube of the falling film evaporator comprises a tubular main body and a plurality of annular fins arranged on the tubular main body at intervals along the axial direction of the tubular main body, the sections of the annular fins are T-shaped, the vertical parts of the annular fins are connected with the tubular main body, so that a circumferential liquid guide groove with a T-shaped section is formed between every two adjacent annular fins, the plane of the circumferential liquid guide groove is vertical to the axis of the tubular main body, and the heat exchange tube further comprises at least one axial liquid guide groove which penetrates through the plurality of annular fins along the axial direction of the tubular main body, so that heat exchange working media of all the circumferential liquid guide grooves can flow mutually. The invention can effectively ensure that the heat exchange working medium forms a uniform and complete liquid film on the outer surface of the heat exchange tube, thereby effectively improving the heat exchange efficiency of the heat exchange tube.
Description
Technical Field
The invention belongs to the technical field of heat exchange, and particularly provides a heat exchange tube of a falling film evaporator.
Background
The falling film evaporator is a common evaporator, the heat exchange process of the falling film evaporator is mainly realized by a heat exchange tube, the heat exchange mechanism of the heat exchange tube is mainly film evaporation heat exchange, a liquid film formed on the outer surface of the heat exchange tube has high-efficiency heat exchange performance due to low thermal resistance, namely the heat exchange performance of the liquid film determines the heat exchange performance of the heat exchange tube, and therefore, the heat exchange performance of the falling film evaporator is decisive for whether the liquid film can uniformly cover the outer surface of the heat exchange tube. The formation of the liquid film mainly depends on the flowing of the heat exchange working medium sprayed by the liquid distributor on the heat exchange tube, and whether the heat exchange working medium can be uniformly distributed on the outer surface of the heat exchange tube mainly depends on two aspects of the axial distribution condition and the circumferential distribution condition of the heat exchange working medium. Specifically, a plurality of spray holes are formed in the liquid distributor, and the heat exchange working medium is sprayed onto the heat exchange tube through the spray holes, so that the larger the arrangement density of the spray holes is, the smaller the pore diameter is, the more uniform liquid distribution is facilitated; however, the arrangement density of the spray holes needs to be limited by the strength of the liquid distributor, the pore size of the spray holes needs to be limited by the viscosity of the heat exchange working medium, the normal flow of the heat exchange working medium is inevitably influenced by the undersize pore size, and even the spray holes can be blocked. Based on this, the heat transfer working medium that current liquid distributor sprayed can only fall to the surface of heat exchange tube with the dribbling or threadiness usually to because have certain clearance between the different spray holes, therefore only can be sprayed to by heat transfer working medium on the partial surface of heat exchange tube, other surfaces then can only rely on the diffusion of heat transfer working medium on the heat exchange tube surface just can be covered by the liquid film, therefore whether the surface of heat exchange tube can form even complete liquid film mainly still rely on the diffusion of heat transfer working medium, the diffusion condition of heat transfer working medium on the heat exchange tube surface has decided falling film evaporator's whole heat transfer efficiency to a great extent promptly.
The heat exchange tubes of the existing falling film evaporator generally include two types, namely smooth tubes and reinforced tubes, wherein the outer surfaces of the smooth tubes are smooth surfaces, and the outer surfaces of the reinforced tubes are provided with extension surfaces. Specifically, because the outer surface of the smooth pipe is smooth, the heat exchange working medium is not limited when flowing on the outer surface of the smooth pipe, so that the flow speed is high, the circulation efficiency is high, but the phenomenon of local drying is easily caused, namely, a liquid film is not formed on part of the outer surface of the heat exchange pipe, and the heat exchange efficiency of the heat exchange pipe is influenced. The outer surface of the reinforced pipe is provided with the expansion surface, so that the flow of the heat exchange working medium is guided by the expansion surface to be more easily and uniformly distributed to form a uniform and complete liquid film; of course, whether the heat exchange working medium can be uniformly distributed or not is closely related to the structure of the expansion surface. If the structure of the expansion surface is not reasonable, even if the flow of the heat exchange working medium is guided by the expansion surface, uniform distribution is difficult to realize. The expansion surface of the existing reinforced pipe is usually formed by a fin structure, the most common fin structure is a fin structure with a T-shaped cross section, the T-shaped fin structure has a very outstanding guiding effect on the heat exchange working medium, and the existing T-shaped fins are spirally distributed along the axial direction of the heat exchange pipe so as to effectively reduce the flow speed of the heat exchange working medium and prolong the heat exchange time; however, in the practical application process, the T-shaped fins distributed spirally can effectively prolong the heat exchange time, but also easily cause the drying phenomenon on part of the surface of the heat exchange tube. Because the flow of the heat exchange working medium is mainly influenced by gravity and supporting force, and the gravity is vertical downward all the time, the heat exchange working medium can be continuously attached to the side surface of the T-shaped fin to obtain more upward supports in the flowing process, and the phenomenon of drying is inevitably easily caused on the surface far away from the T-shaped fin, so that the heat exchange efficiency of the heat exchange tube is influenced, and even the heat exchange efficiency of the whole falling film evaporator is adversely affected.
Accordingly, there is a need in the art for a new heat exchange tube for a falling film evaporator to solve the above problems.
Disclosure of Invention
In order to solve the problems in the prior art, namely to solve the problem that the heat exchange efficiency of the heat exchange tube is adversely affected due to the poor arrangement mode of the T-shaped fins of the existing heat exchange tube, the invention provides a heat exchange tube of a falling film evaporator, the heat exchange tube includes a tubular body and a plurality of annular fins provided on the tubular body at intervals in an axial direction of the tubular body, the cross sections of the annular fins are T-shaped, the vertical parts of the annular fins are connected with the tubular main body, so that a circumferential liquid guide groove with a T-shaped cross section is formed between every two adjacent annular fins, the plane where the circumferential liquid guide groove is located is perpendicular to the axis of the tubular main body, and the heat exchange tube further comprises at least one axial liquid guide groove which penetrates through the plurality of annular fins along the axial direction of the tubular main body, so that heat exchange working media of all the circumferential liquid guide grooves can flow mutually.
In a preferred technical solution of the heat exchange tube of the falling film evaporator, the number of the axial liquid guiding grooves is plural, and the plural axial liquid guiding grooves are uniformly distributed along the circumferential direction of the tubular main body.
In a preferable technical scheme of the heat exchange tube of the falling film evaporator, the number of the axial liquid guide grooves is 100 to 160.
In the preferable technical scheme of the heat exchange tube of the falling film evaporator, the distance between the transverse parts of two adjacent annular fins is 0.05-0.3 mm.
In the preferable technical scheme of the heat exchange tube of the falling film evaporator, the distance between the vertical parts of two adjacent annular fins is 0.1-0.6 mm.
In a preferred technical solution of the heat exchange tube of the falling film evaporator, the height of the annular fin is set to be greater than the groove depth of the axial liquid guide groove.
In a preferable technical scheme of the heat exchange tube of the falling film evaporator, the height of the annular fin is 0.3-1 mm.
In the preferable technical scheme of the heat exchange tube of the falling film evaporator, the groove depth of the axial liquid guide groove is greater than or equal to 0.3 mm.
In a preferable technical scheme of the heat exchange tube of the falling film evaporator, the width of the axial liquid guide groove is 0.05-0.15 mm.
In a preferable technical scheme of the heat exchange tube of the falling film evaporator, the outer diameter of the heat exchange tube is 15.8-25.4 mm.
The heat exchange tube of the falling film evaporator comprises a tubular main body and a plurality of annular fins arranged on the tubular main body at intervals along the axial direction of the tubular main body, the cross sections of the annular fins are T-shaped, the vertical parts of the annular fins are connected with the tubular main body, so that a circumferential liquid guide groove with a T-shaped cross section is formed between every two adjacent annular fins, the plane of the circumferential liquid guide groove is vertical to the axis of the tubular main body, and the heat exchange tube further comprises at least one axial liquid guide groove penetrating through the plurality of annular fins along the axial direction of the tubular main body, so that heat exchange working mediums of all the circumferential liquid guide grooves can flow mutually. According to the invention, the plurality of annular fins are arranged at intervals along the axial direction of the tubular main body to form a plurality of circumferential liquid guide grooves with T-shaped sections, the planes of the circumferential liquid guide grooves are vertical to the axis of the tubular main body, so that heat exchange working media can be uniformly distributed in the circumferential direction through the circumferential liquid guide grooves, the phenomenon of drying of the surface of the heat exchange tube is effectively avoided, and meanwhile, the arrangement mode can effectively accelerate the flow speed of the heat exchange working media, and further the circulation efficiency of the heat exchange tube is effectively improved; and this application still through setting up at least one axial liquid guide groove is in order to guarantee that heat transfer working medium can be in the axial direction evenly distributed. Through the structure setting, this application can effectively guarantee that the heat transfer working medium is in form even complete liquid film on the surface of heat exchange tube, and then effectively promote the heat exchange efficiency of heat exchange tube.
Furthermore, the plurality of axial liquid guide grooves are uniformly distributed along the circumferential direction of the tubular main body, so that heat exchange working media can better circulate in all the circumferential liquid guide grooves through the axial liquid guide grooves, the heat exchange working media can be effectively ensured to better flow under the guidance of the axial liquid guide grooves and the circumferential liquid guide grooves, a liquid film formed by the heat exchange working media can be effectively ensured to uniformly and completely cover the outer surface of the whole heat exchange tube, and the heat exchange efficiency of the heat exchange tube is further ensured to the maximum extent.
Furthermore, the invention also ensures that the heat exchange working medium can be uniformly distributed on the outer surface of the heat exchange tube to the maximum extent by strictly limiting the sizes of all parts, thereby further improving the heat exchange efficiency of the heat exchange tube to the maximum extent.
Drawings
FIG. 1 is a schematic view of the overall construction of a heat exchange tube of the present invention;
FIG. 2 is a side view of a heat exchange tube of the present invention;
FIG. 3 is a cross-sectional view taken at A-A of FIG. 2;
FIG. 4 is a front view of a heat exchange tube of the present invention;
FIG. 5 is a cross-sectional view taken at B-B of FIG. 4;
reference numerals: 11. a tubular body; 111. a circumferential liquid guide groove; 112. an axial liquid guide groove; 12. an annular fin; 121. a vertical portion; 122. a transverse portion.
Detailed Description
Preferred embodiments of the present invention are described below with reference to the accompanying drawings. It should be understood by those skilled in the art that these embodiments are only for explaining the technical principle of the present invention, and are not intended to limit the scope of the present invention. And can be adjusted as needed by those skilled in the art to suit particular applications. For example, it should be noted that in the description of the present invention, the terms of direction or positional relationship indicated by the terms "upper", "lower", "left", "right", "vertical", "lateral", "inner", "outer", etc. are based on the directions or positional relationships shown in the drawings, which are merely for convenience of description, and do not indicate or imply that the device or element must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first" and "second" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
Furthermore, it should be noted that, in the description of the present invention, unless otherwise explicitly specified or limited, the terms "connected" and "connected" should be interpreted broadly, e.g., as being fixedly connected, detachably connected, or integrally connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
Referring to fig. 1 to 5, wherein fig. 1 is a schematic view of the overall structure of the heat exchange tube of the present invention; FIG. 2 is a side view of a heat exchange tube of the present invention; FIG. 3 is a cross-sectional view taken at A-A of FIG. 2; FIG. 4 is a front view of a heat exchange tube of the present invention; fig. 5 is a sectional view at B-B in fig. 4. As shown in fig. 1 to 5, the heat exchange tube of the present invention includes a tubular main body 11 and a plurality of annular fins 12 arranged on the tubular main body 11 at intervals along the axial direction of the tubular main body 11, the tubular main body 11 forms a tube cavity, water (of course, other working media may be possible, and no limitation is provided herein, as long as heat exchange can be achieved) generally flows through the tube cavity, and the water flowing through the tube cavity of the tubular main body 11 exchanges heat with a heat exchange working medium (so-called refrigerant, the present invention does not make any limitation on specific components thereof, and a technician can select according to actual use requirements) flowing through the outside of the heat exchange tube; the annular fins 12 are fin structures formed by surrounding along the circumferential direction of the tubular main body 11, and the plurality of annular fins 12 are arranged at intervals along the axial direction of the tubular main body 11, so that gaps between two adjacent annular fins 12 can form an annular circumferential liquid guide groove 111, and heat exchange working media can be distributed circumferentially through the circumferential liquid guide groove 111.
It should be noted that the present invention does not limit any structure at two ends of the tubular main body 11 and any connection manner of the heat exchange tube and other components, and the present invention does not limit any number of the ring fins 12 and any length of the tubular main body 11, and the technician can set the length according to the actual use requirement. The specific structure can be modified without departing from the basic principle of the invention, and the invention belongs to the protection scope.
As a preferred embodiment, the outer diameter D (see the label in fig. 3 for details) of the heat exchange tube is set to be 15.8mm to 25.4mm, and a technician can take any value within the value range, so that the water flow can fully fill the tube cavity of the whole tubular main body 11, thereby effectively ensuring that the water flow in the heat exchange tube can fully exchange heat with the heat exchange working medium flowing through the outside of the heat exchange tube, and further effectively improving the heat exchange efficiency. Of course, as a preferred embodiment, the value of the outer diameter of the heat exchange tube is also related to the length of the heat exchange tube, the longer the length of the heat exchange tube is, the smaller the outer diameter of the heat exchange tube is, and the shorter the length of the heat exchange tube is, the larger the outer diameter of the heat exchange tube is, so as to ensure the heat exchange efficiency of water flow and heat exchange working medium to the maximum extent.
Further, the cross sections of the ring fins 12 are all T-shaped and the vertical portions 121 of the ring fins 12 are connected to the tubular body 11 so that the cross section of the circumferential liquid guide groove 111 formed between each adjacent two ring fins 12 is all T-shaped, and the plane where the circumferential liquid guide groove 111 is located is perpendicular to the axis of the tubular body 11. As shown in fig. 3, each of the ring fins 12 is composed of a vertical portion 121 and a lateral portion 122 based on the cross section of the ring fin 12, and the width of the vertical portion 121 is smaller than the width of the lateral portion 122 so that the cross section of the ring fin 12 is T-shaped; it will be understood that the vertical portion 121 and the transverse portion 122 are both substantially annular in overall shape, the annular fin 12 being connected to the tubular body 11 by the vertical portion 121. The vertical parts 121 and the horizontal parts 122 of the two adjacent annular fins 12 jointly form the circumferential liquid guide groove 111, because the gap between the vertical parts 121 of the two adjacent annular fins 12 is larger than the gap between the horizontal parts 122 of the two adjacent annular fins 12, the cross section of the circumferential liquid guide groove 111 formed between the two adjacent annular fins 12 is also T-shaped, and the T-shaped cross section makes the circumferential liquid guide groove 111 narrow outside and wide inside, so that the heat exchange working medium entering the circumferential liquid guide groove 111 is not easy to flow out easily, thereby effectively ensuring that all the heat exchange working media can be better used for forming a liquid film to cover the outer surface of the heat exchange tube without early dripping, and further effectively ensuring the heat exchange efficiency of the heat exchange tube.
With continued reference to fig. 4 and 5, as shown in fig. 4 and 5, the heat exchange tube further includes a plurality of axial liquid guiding grooves 112 penetrating the plurality of annular fins 12 in the axial direction of the tubular body 11 so as to enable the heat exchange working mediums of all the circumferential liquid guiding grooves 111 to flow mutually. The axial liquid guiding grooves 112 are arranged along the axial direction of the tubular body 11, that is, the axis of the axial liquid guiding groove 112 is parallel to the axis of the tubular body 11, and each axial liquid guiding groove 112 is arranged to penetrate all the annular fins 12 along the axial direction of the tubular body 11, that is, each axial liquid guiding groove 112 can communicate all the circumferential liquid guiding grooves 111 to enable the heat exchange working medium to better circulate. It should be noted that, the invention does not limit the specific number of the axial liquid guiding slots 112, and the technician can set the number according to the actual use requirement; as an optimal arrangement scheme, the number of the axial liquid guide grooves 112 is multiple, so that heat exchange working media in all the circumferential liquid guide grooves 111 can flow mutually better, and the uniform distribution effect of the heat exchange working media is effectively improved. Further preferably, the plurality of axial liquid guiding grooves 112 are uniformly distributed along the circumferential direction of the tubular main body 11, and the number of the axial liquid guiding grooves 112 is set to be 100 to 160, so as to maximally improve the communication effect among the circumferential liquid guiding grooves 111, thereby effectively improving the heat exchange efficiency. It should be noted that, in order to show the various structures of the heat exchange tubes more clearly, the drawings used in the preferred embodiment do not depict so many axial liquid guiding grooves 112, i.e. the various structures in the drawings are only schematic and do not limit the scope of the present invention in any way.
With continued reference to fig. 3, and through numerous experiments and investigations, the present invention gives the following preferred ranges for the distance c between the transverse portions 122 and the distance d between the vertical portions 121 of two adjacent annular fins 12: the distance c between the lateral portions 122 of two adjacent annular fins 12 is 0.05mm to 0.3 mm; the distance d between the vertical portions 121 of two adjacent ring fins 12 is 0.1mm to 0.6 mm. The technical staff can take any value within the preferable value range so as to effectively ensure that the circumferential flow guiding function of the circumferential liquid guiding groove 111 can be best exerted, and further effectively ensure that the heat exchange working medium can be uniformly distributed in the circumferential direction.
Further, as a preferred embodiment, the height of the annular fin 12 is set to be greater than the groove depth of the axial liquid guiding groove 112, that is, the groove bottom of the circumferential liquid guiding groove 111 is lower than the groove bottom of the axial liquid guiding groove 112, and the difference depth between the height of the annular fin 12 and the groove depth of the axial liquid guiding groove 112 is the difference between the height of the annular fin and the groove depth of the axial liquid guiding groove 112, which is to effectively ensure that a certain thickness of heat exchange working medium is always accumulated in each circumferential liquid guiding groove 111, so as to further effectively avoid the problem of local dryness of the outer surface of the heat exchange tube. Preferably, the viscosity of the heat exchange working medium determines the difference between the height of the annular fins 12 and the groove depth of the axial liquid guide groove 112; the method specifically comprises the following steps: the larger the viscosity of the heat exchange working medium is, the smaller the difference between the height of the annular fin 12 and the groove depth of the axial liquid guide groove 112 is, so that the good flowing effect of the heat exchange working medium is effectively ensured; the smaller the viscosity of the heat exchange working medium is, the larger the difference between the height of the annular fin 12 and the groove depth of the axial liquid guide groove 112 is, so that the problem that the heat exchange working medium with a certain thickness can be accumulated to avoid local drying is effectively solved.
After a lot of experiments and investigations, the present invention gives the following preferred ranges for the height h of the ring fins 12, the groove depth L and the groove width b of the axial liquid guiding groove 112: the height h of the annular fin 12 is set to 0.3mm to 1 mm; the groove depth L of the axial liquid guide groove 112 is set to be greater than or equal to 0.3 mm; the groove width b of the axial liquid guide groove 112 is set to be 0.05mm to 0.15 mm. The technical staff can take any value within the above preferred value range so as to effectively ensure that the axial flow guiding function of the axial liquid guiding groove 112 can be best exerted, and further effectively ensure that the heat exchange working medium can be uniformly distributed in the axial direction.
Based on the contents described in the above preferred embodiments, in order to effectively verify the technical effects brought by the above preferred numerical value range, especially the outstanding effect on the heat exchange efficiency of the heat exchange tube when the distance c between the transverse portions 122 of two adjacent annular fins 12 and the distance d between the vertical portions 121 of two adjacent annular fins 12 are within the above preferred range, the present preferred embodiment performs a plurality of heat exchange experiments on two heat exchange tubes with different sizes and obtains relevant experimental data on the heat exchange coefficient.
The data for the first heat exchange tube is as follows: the length of first heat exchange tube is 2.5m, the external diameter D of first heat exchange tube is 25.4mm, distance c between the horizontal part 122 of two adjacent ring fins 12 is 0.4mm, distance D between the vertical part 121 of two adjacent ring fins 12 is 0.65mm, the height h of ring fin 12 is 0.9mm, the groove depth L of axial liquid guide groove 112 is 0.25mm, the groove width b of axial liquid guide groove 112 is 0.1mm, the quantity that sets up of axial liquid guide groove 112 is 120.
The data for the second heat exchange tube are as follows: the length of the second heat exchange tube is 2.5m, the outer diameter D of the second heat exchange tube is 25.4mm, the distance c between the transverse parts 122 of two adjacent annular fins 12 is 0.25mm, the distance D between the vertical parts 121 of two adjacent annular fins 12 is 0.5mm, the height h of each annular fin 12 is 0.9mm, the groove depth L of the axial liquid guide groove 112 is 0.6mm, the groove width b of the axial liquid guide groove 112 is 0.1mm, and the number of the axial liquid guide grooves 112 is 120.
It can be seen that the first heat exchange tube and the second heat exchange tube only differ in the distance c between the transverse portions 122 of the two adjacent annular fins 12, the distance d between the vertical portions 121 of the two adjacent annular fins 12 and the groove depth L of the axial liquid guide groove 112, wherein the distance c between the transverse portions 122 of the two adjacent annular fins 12, the distance d between the vertical portions 121 and the groove depth L of the axial liquid guide groove 112 of the first heat exchange tube all exceed the preferred value range given in the preferred embodiment, and the distance c between the transverse portions 122 of the two adjacent annular fins 12, the distance d between the vertical portions 121 and the groove depth L of the axial liquid guide groove 112 of the second heat exchange tube all exceed the preferred value range given in the preferred embodiment.
It should be noted that, the groove depth of the axial liquid guide groove of the heat exchange tube of the existing falling film evaporator is set between 0.1mm and 0.3mm, however, it is found through many times of experiments that the axial diffusion of the heat exchange working medium cannot be well realized at all in the groove depth range, especially under the condition that the groove width is also small, the heat exchange working medium can only flow between two groove walls almost and cannot enter the circumferential liquid guide groove, thereby causing the problem that the axial diffusion of the heat exchange working medium cannot be realized, and further causing the liquid film to be unable to be formed.
Making a real object based on the size characteristics of the two heat exchange tubes, and under the condition that other experimental conditions are the same, performing an experiment of exchanging heat between a heat exchange working medium outside the heat exchange tube and water in the heat exchange tube by using a falling film evaporator with a heat exchange working medium R1234ze (E), wherein under the conditions that the flow density q of the heat exchange working medium is 23 KW/square meter, the evaporation temperature t of the heat exchange working medium is 5 ℃, and the Reynolds number Re of a liquid film outside the heat exchange tube is 1400, the water flow velocity v in the heat exchange tube is changed for testing, so as to obtain experimental data shown in the following table (it needs to be explained that the following experimental results adopt the average value of multiple experimental results, so as to effectively eliminate the influence caused by accidental errors):
based on the data in the table above, at a water flow rate of 1.0 m/s: the falling film evaporation heat exchange coefficient ho1 of the first heat exchange tube is 14398W/((square meter)), the falling film evaporation heat exchange coefficient ho2 of the second heat exchange tube is 16220W/((square meter)), and the falling film evaporation heat exchange coefficient of the second heat exchange tube is improved by 12.7 percent compared with the falling film evaporation heat exchange coefficient of the first heat exchange tube;
measured at a water flow rate of 1.5 m/s: the heat exchange coefficient ho1 of the falling film evaporation of the first heat exchange tube is 14096W/((square meter)), the heat exchange coefficient ho2 of the falling film evaporation of the second heat exchange tube is 16199W/((square meter)), and the heat exchange coefficient of the falling film evaporation of the second heat exchange tube is improved by 15.0 percent compared with the heat exchange coefficient of the falling film evaporation of the first heat exchange tube;
measured at a water flow rate of 2.0 m/s: the heat exchange coefficient ho1 of the falling film evaporation of the first heat exchange tube is 14011W/((square meter)), the heat exchange coefficient ho2 of the falling film evaporation of the second heat exchange tube is 16628W/((square meter)), and the heat exchange coefficient of the falling film evaporation of the second heat exchange tube is improved by 18.9 percent compared with the heat exchange coefficient of the falling film evaporation of the first heat exchange tube;
measured at a water flow rate of 2.5 m/s: the falling film evaporation heat exchange coefficient ho1 of the first heat exchange tube is 14383W/((square meter)), the falling film evaporation heat exchange coefficient ho2 of the second heat exchange tube is 16127W/((square meter)), and the falling film evaporation heat exchange coefficient of the second heat exchange tube is improved by 12.1 percent compared with that of the first heat exchange tube;
measured at a water flow rate of 3.0 m/s: the heat exchange coefficient ho1 of the falling film evaporation of the first heat exchange tube is 14403W/((square meter)), the heat exchange coefficient ho2 of the falling film evaporation of the second heat exchange tube is 16173W/((square meter)), and the heat exchange coefficient of the falling film evaporation of the second heat exchange tube is improved by 12.3% compared with the heat exchange coefficient of the falling film evaporation of the first heat exchange tube.
Therefore, under different water flow speeds, the heat exchange performance of the second heat exchange tube is greatly improved compared with that of the first heat exchange tube, so that the values of the distance between the transverse parts 122 of two adjacent annular fins 12 and the distance between the vertical parts 121 of two adjacent annular fins 12 are very important, and when the values of the distance between the transverse parts 122 of two adjacent annular fins 12 and the distance between the vertical parts 121 of two adjacent annular fins 12 are within the preferred value range provided by the preferred embodiment, the heat exchange performance of the heat exchange tube can be greatly improved.
So far, the technical solutions of the present invention have been described in connection with the preferred embodiments shown in the drawings, but it is easily understood by those skilled in the art that the scope of the present invention is obviously not limited to these specific embodiments. Equivalent changes or substitutions of related technical features can be made by those skilled in the art without departing from the principle of the invention, and the technical scheme after the changes or substitutions can fall into the protection scope of the invention.
Claims (10)
1. A heat exchange tube of a falling film evaporator, comprising a tubular body and a plurality of annular fins arranged on the tubular body at intervals along the axial direction of the tubular body,
the cross sections of the annular fins are T-shaped, the vertical parts of the annular fins are connected with the tubular main body, so that a circumferential liquid guide groove with a T-shaped cross section is formed between every two adjacent annular fins, the plane of the circumferential liquid guide groove is vertical to the axis of the tubular main body,
the heat exchange tube also comprises at least one axial liquid guide groove which penetrates through the plurality of annular fins along the axial direction of the tubular main body, so that heat exchange working mediums of all the circumferential liquid guide grooves can flow mutually.
2. The heat exchange tube of claim 1, wherein the number of the axial liquid guiding grooves is plural, and the plural axial liquid guiding grooves are uniformly distributed along the circumferential direction of the tubular body.
3. The heat exchange tube of claim 2, wherein the number of axial fluid guide slots is 100 to 160.
4. The heat exchange tube according to claim 1, wherein the distance between the lateral portions of adjacent two of the ring fins is 0.05 to 0.3 mm.
5. The heat exchange tube of claim 4, wherein the distance between the vertical portions of adjacent two of the ring fins is 0.1 to 0.6 mm.
6. The heat exchange tube of claim 1, wherein the height of the annular fin is set to be greater than the groove depth of the axial liquid guide groove.
7. The heat exchange tube of claim 6, wherein the height of the annular fin is 0.3 to 1 mm.
8. The heat exchange tube of claim 7, wherein the groove depth of the axial liquid guide groove is greater than or equal to 0.3 mm.
9. The heat exchange tube of claim 8, wherein the width of the axial liquid guide groove is 0.05 to 0.15 mm.
10. A heat exchange tube according to any one of claims 1 to 9, wherein the heat exchange tube has an outer diameter of 15.8 to 25.4 mm.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010769122.2A CN114061358A (en) | 2020-08-03 | 2020-08-03 | Heat exchange tube of falling film evaporator |
| PCT/CN2021/099551 WO2021228276A1 (en) | 2020-08-03 | 2021-06-11 | Heat exchange tube of falling film type evaporator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010769122.2A CN114061358A (en) | 2020-08-03 | 2020-08-03 | Heat exchange tube of falling film evaporator |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN114061358A true CN114061358A (en) | 2022-02-18 |
Family
ID=78525210
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010769122.2A Pending CN114061358A (en) | 2020-08-03 | 2020-08-03 | Heat exchange tube of falling film evaporator |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN114061358A (en) |
| WO (1) | WO2021228276A1 (en) |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001153580A (en) * | 1999-11-29 | 2001-06-08 | Furukawa Electric Co Ltd:The | Heat transfer pipe |
| CN1731066A (en) * | 2005-08-09 | 2006-02-08 | 江苏萃隆铜业有限公司 | Heat exchange tube of evaporator |
| CN101556125A (en) * | 2009-04-29 | 2009-10-14 | 金龙精密铜管集团股份有限公司 | Heat-transfer pipe of evaporator |
| CN105066761A (en) * | 2015-09-22 | 2015-11-18 | 烟台恒辉铜业有限公司 | Evaporating pipe with narrow-gap steam exhaust opening |
| CN108801034A (en) * | 2018-05-02 | 2018-11-13 | 珠海格力电器股份有限公司 | Heat exchanger tube, heat exchanger and heat pump unit |
| CN208780005U (en) * | 2018-08-16 | 2019-04-23 | 上海欧贡制冷科技有限公司 | A kind of evaporating heat-exchanging pipe |
Family Cites Families (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR0134557B1 (en) * | 1993-07-07 | 1998-04-28 | 가메다카 소키치 | Heat exchanger tube for falling film evaporator |
| CN201885619U (en) * | 2010-12-02 | 2011-06-29 | 珠海格力电器股份有限公司 | Heat exchange tube and air-conditioning heat exchanger including same |
| CN102121805A (en) * | 2011-04-07 | 2011-07-13 | 金龙精密铜管集团股份有限公司 | Enhanced heat transfer tube used for falling film evaporator |
| CN202221261U (en) * | 2011-08-16 | 2012-05-16 | 江苏萃隆精密铜管股份有限公司 | Heat exchange pipe for evaporator |
| CN203100513U (en) * | 2013-01-10 | 2013-07-31 | 江苏萃隆精密铜管股份有限公司 | Heat-exchanger tube |
| CN103063072A (en) * | 2013-01-10 | 2013-04-24 | 江苏萃隆精密铜管股份有限公司 | Heat-exchange tube |
| JP6738593B2 (en) * | 2015-07-13 | 2020-08-12 | 株式会社コベルコ マテリアル銅管 | Boiling heat transfer tube |
| CN206959678U (en) * | 2017-06-30 | 2018-02-02 | 中国石油天然气股份有限公司 | The T-shaped finned tube combination exchanger of cavity ring |
| CN208901686U (en) * | 2018-09-20 | 2019-05-24 | 苏州新太铜高效管有限公司 | A kind of evaporating heat-exchanging pipe |
| CN211400919U (en) * | 2019-12-10 | 2020-09-01 | 珠海格力电器股份有限公司 | Falling film heat exchange tube, falling film heat exchanger and air conditioner |
| CN112944977A (en) * | 2019-12-10 | 2021-06-11 | 珠海格力电器股份有限公司 | Falling film heat exchange tube, falling film heat exchanger and air conditioner |
-
2020
- 2020-08-03 CN CN202010769122.2A patent/CN114061358A/en active Pending
-
2021
- 2021-06-11 WO PCT/CN2021/099551 patent/WO2021228276A1/en active Application Filing
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001153580A (en) * | 1999-11-29 | 2001-06-08 | Furukawa Electric Co Ltd:The | Heat transfer pipe |
| CN1731066A (en) * | 2005-08-09 | 2006-02-08 | 江苏萃隆铜业有限公司 | Heat exchange tube of evaporator |
| CN101556125A (en) * | 2009-04-29 | 2009-10-14 | 金龙精密铜管集团股份有限公司 | Heat-transfer pipe of evaporator |
| CN105066761A (en) * | 2015-09-22 | 2015-11-18 | 烟台恒辉铜业有限公司 | Evaporating pipe with narrow-gap steam exhaust opening |
| CN108801034A (en) * | 2018-05-02 | 2018-11-13 | 珠海格力电器股份有限公司 | Heat exchanger tube, heat exchanger and heat pump unit |
| CN208780005U (en) * | 2018-08-16 | 2019-04-23 | 上海欧贡制冷科技有限公司 | A kind of evaporating heat-exchanging pipe |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2021228276A1 (en) | 2021-11-18 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101858698A (en) | Microchannel heat exchanger | |
| US11454448B2 (en) | Enhanced heat transfer surface | |
| CN105020940A (en) | Microchannel heat exchanger capable of uniformly distributing refrigerant flow | |
| CN202614060U (en) | Condenser pipe with pyramidal fins | |
| RU146877U1 (en) | HEAT EXCHANGER | |
| CN105571209A (en) | Heat exchanger provided with area-varying communication holes | |
| CN114061358A (en) | Heat exchange tube of falling film evaporator | |
| CN105486116A (en) | Heat exchanger with vertex angles of isosceles triangular through holes changeable | |
| CN209341919U (en) | A kind of support device of shell-and-tube exchanger heat exchanger tube | |
| CN209295733U (en) | A kind of heat exchanger internal channel structure and heat exchanger | |
| CN102654372B (en) | Pyramid-shaped finned condensing tube | |
| CN105674629A (en) | Microchannel heat exchanger and heat-pump water heater | |
| CN102401598A (en) | Falling film evaporation heat exchange pipe | |
| CN211400919U (en) | Falling film heat exchange tube, falling film heat exchanger and air conditioner | |
| CN112944977A (en) | Falling film heat exchange tube, falling film heat exchanger and air conditioner | |
| CN105627789B (en) | A kind of heat exchanger of intercommunicating pore number change | |
| CN210674258U (en) | Horizontal falling film liquid distributor | |
| EP3859263B1 (en) | Heat exchanger | |
| CN208382635U (en) | A kind of Falling Film Evaporator of Horizontal Tube heat exchanger | |
| CN108895864B (en) | Baffle assembly and shell-and-tube heat exchanger comprising such an assembly | |
| KR101315648B1 (en) | Plate-type heat exchanger | |
| CN208223234U (en) | A kind of radiator | |
| CN102636068B (en) | Asymmetric fin condenser pipe | |
| CN114234700B (en) | Collecting pipe assembly, micro-channel heat exchanger and air conditioning system | |
| CN110736378A (en) | Micro-channel heat exchanger flat tube, micro-channel heat exchanger and heat exchange equipment |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20220218 |
|
| RJ01 | Rejection of invention patent application after publication |