CN109654916B - Vapor-liquid two-phase flow heat exchange tube with fins inclined towards center - Google Patents
Vapor-liquid two-phase flow heat exchange tube with fins inclined towards center Download PDFInfo
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- CN109654916B CN109654916B CN201910081865.8A CN201910081865A CN109654916B CN 109654916 B CN109654916 B CN 109654916B CN 201910081865 A CN201910081865 A CN 201910081865A CN 109654916 B CN109654916 B CN 109654916B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
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- 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
- F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
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- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The invention provides a vapor-liquid two-phase flow heat exchange tube, wherein vapor phase in vapor-liquid two-phase flow flows in the heat exchange tube, the vapor phase in the vapor-liquid two-phase flow can be condensed into liquid phase in the heat exchange process, a flow stabilizer is arranged in the heat exchange tube, the flow stabilizer comprises a central rod arranged along the central axial direction of the heat exchange tube and a plurality of radial rods extending along the central rod in the radial direction, a plurality of fins extending from the radial rods in the opposite direction of fluid flow are arranged on the radial rods, each fin is provided with a tip, the tips extend towards the opposite direction of fluid flow, and the extending direction of the tips inclines towards the center of the heat exchange tube. The heat exchange tube of the flow stabilizer with the novel structure provided by the invention has the advantages that the extending direction of the tip part faces to the center of the heat exchange tube, so that the tip part of the fin can be cut into vapor and liquid phases to the maximum extent, and the effect of the flow stabilizer is further improved.
Description
Technical Field
The invention relates to a shell-and-tube heat exchanger, in particular to a two-phase flow heat exchanger containing condensable vapor.
Background
The vapor-liquid two-phase flow heat exchange is widely applied to various heat exchange devices, and the vapor-liquid two-phase flow has low heat exchange efficiency, worsens heat exchange, is unstable in a fluid flowing process and causes water hammer in the heat exchange process due to the existence of vapor phase. When the vapor and liquid phases of the two-phase working medium are not uniformly mixed and flow discontinuously, the large-size liquid mass can occupy the air mass space at a high speed, so that the two-phase flow is unstable, equipment and a pipeline are severely impacted, strong vibration and noise are generated, and the running safety of the equipment is seriously threatened.
The inventors have also devised some flow stabilizers, such as multi-tube flow stabilizers, in the previous applications, see fig. 7. However, in operation, the device is found that the tubes are tightly combined together, so that the space a formed among the three tubes is relatively small, and the space a is formed by convex arcs of the three tubes, so that most of the space a is narrow, fluid is difficult to enter and pass through, and short circuit is caused to the fluid, thereby affecting heat exchange of the fluid, and failing to play a good role in stabilizing the flow. And also, since a plurality of tubes of the above-described structure are combined together, the manufacturing is difficult.
Therefore, in view of the above problems, the present invention provides a heat exchanger of a flow stabilizer with a new structure, so as to solve the above problems.
Disclosure of Invention
The invention aims to provide a heat exchanger of a flow stabilizer with a novel structure, which weakens the vibration in a gas-liquid two-phase flow heat exchange pipe when gas-liquid two-phase flow exists in a pipeline, reduces the noise level and strengthens heat transfer.
In order to achieve the purpose, the technical scheme of the invention is as follows:
the utility model provides a vapour-liquid two-phase flow shell and tube heat exchanger, includes the casing, the casing both ends set up the head respectively, the hookup location of head and casing sets up the tube sheet, and the tube sheet at both ends is connected to the heat exchange tube, and the vapor phase in the vapour-liquid two-phase flow can condense into the liquid phase at the heat transfer in-process, and vapour-liquid two-phase flow flows in the tube pass, set up current stabilizer in the heat exchange tube, current stabilizer includes along the central axial of heat exchange tube set up well core rod and along well core rod to radial many radial rods of extension, set up many fins that extend to the relative direction of fluid flow from radial rod on the radial rod, the fin has sharp portion, sharp portion extends towards the relative.
Preferably, the fins are triangular fins.
Preferably, one base of the triangle is located on the radial bar and the line connecting the vertex of the angle corresponding to the side and the midpoint of the side forms an angle of 75-135 deg. with the radial bar.
Preferably, the included angle is 90 °.
Preferably, the triangular fins are isosceles triangular fins, and the bottom edges of the isosceles triangles are located on the radial rods.
Preferably, the size of the vertex angle of the isosceles triangle is a, the length of the base of the isosceles triangle is Y, and the distance between adjacent isosceles triangles is J, then the following requirements are met:
Y/J= d-a*sin(A)3-b*sin(A)2-c sin (a); wherein sin is a trigonometric function and a, b, c, d are parameters;
0.353<a<0.358,
0.485<b<0.486,
0.082<c<0.083，
0.403<d<0.404， 4<A<33°，
0.1765<Y/J <0.4118。
preferably, a =0.3559, b = 0.4859, c =0.08294, and d = 0.4033.
Preferably, the number of the radial rods is 5-10, and the included angles between the radial rods are equal.
Preferably, the number of radial rods is 8.
Preferably, the length of the bottom side of the isosceles triangle is 0.02-0.03 times of the inner diameter of the heat exchange tube.
Compared with the prior art, the invention has the following advantages:
1) the heat exchange tube of the flow stabilizer with the novel structure provided by the invention has the advantages that the extending direction of the tip part faces to the center of the heat exchange tube, so that the tip part of the fin can be cut into vapor and liquid phases to the maximum extent, and the effect of the flow stabilizer is further improved.
2) The invention provides a flow stabilizer with a novel structure, which separates a two-phase fluid into a liquid phase and a gas phase through the flow stabilizer, divides the liquid phase into small liquid masses, divides the gas phase into small bubbles, inhibits the backflow of the liquid phase, promotes the smooth flow of the gas phase, plays a role in stabilizing the flow and has the effects of vibration reduction and noise reduction. Compared with a rod-fin type flow stabilizer, the flow stabilizer further improves the flow stabilizing effect, strengthens heat transfer and is simple to manufacture.
3) By arranging the rod-fin type flow stabilizing device, the invention equivalently increases the internal heat exchange area in the heat exchange tube, strengthens the heat exchange and improves the heat exchange effect.
4) The invention divides the vapor phase and the liquid phase on the whole cross section of the heat exchange tube, thereby avoiding the division of only the inner wall surface of the heat exchange tube in the prior art, realizing the enlargement of the contact area of the vapor-liquid interface and the vapor phase boundary layer with the cooling wall surface on the whole cross section of the heat exchange tube, enhancing the disturbance, reducing the noise and the vibration and strengthening the heat transfer.
5) According to the invention, the distance between adjacent flow stabilizers, the length of the flow stabilizer, the size of the fin and other parameters are regularly changed in the height direction of the heat exchange tube, so that the flow stabilizing effect is further achieved, the noise is reduced, and the heat exchange effect is improved.
6) According to the invention, the regular change of the size of parameters such as the size and the spacing of the phase fins is arranged in the radial direction, so that the flow stabilizing effect is further achieved, the noise is reduced, and the heat exchange effect is improved.
7) According to the invention, the heat exchange rule caused by the change of each parameter of the rod-fin type flow stabilizer is widely researched, and the optimal relational expression of the vibration and noise reduction effects is realized under the condition of meeting the flow resistance.
Drawings
FIG. 1 is a schematic structural view of a two-phase flow shell-and-tube heat exchanger of the present invention;
FIG. 2 is a schematic view of the heat exchange tube structure of the two-phase flow shell-and-tube heat exchanger of the present invention;
FIG. 3 is a schematic view of a flow stabilizer of the present invention;
FIG. 4 is a schematic view of the arrangement of the flow stabilizers of the present invention within the heat exchange tubes;
fig. 5 is another schematic view of the arrangement of the flow stabilizer of the present invention within a heat exchange tube.
Fig. 6 is a schematic cross-sectional view of the arrangement of the flow stabilizer of the present invention within a heat exchange tube.
FIG. 7 is a schematic view of the structure of a two-phase flow shell-and-tube heat exchanger of the background art.
The reference numbers are as follows: the heat exchanger comprises a front end enclosure 1, an end enclosure flange 2, a front tube plate 3, a shell 4, a flow stabilizer 5, a heat exchange tube 6, a rear tube plate 7, an end enclosure flange 8, a rear end enclosure 9, a support 10, a support 11, a tube side inlet tube 12, a tube side outlet tube 13, a shell side inlet tube 14, a shell side outlet tube 15, a central rod 51, radial rods 52 and fins 53.
Detailed Description
The following detailed description of embodiments of the invention refers to the accompanying drawings.
In this document, "/" denotes division and "×", "denotes multiplication, referring to formulas, if not specifically stated.
It should be noted that, if not specifically stated, the two-phase flow referred to in the present invention is a vapor-liquid two-phase flow where the vapor phase can be condensed into a liquid phase during heat exchange.
As shown in fig. 1, the shell-and-tube heat exchanger includes a shell 4, a heat exchange tube 6, a tube-side inlet tube 12, a tube-side outlet tube 13, a shell-side inlet connecting tube 14 and a shell-side outlet connecting tube 15; a heat exchange tube bundle consisting of a plurality of heat exchange tubes 6 arranged in parallel is connected on the front tube plate 3 and the rear tube plate 7; the front end of the front tube plate 3 is connected with the front seal head 1, and the rear end of the rear tube plate 7 is connected with the rear seal head 9; the tube pass inlet pipe 12 is arranged on the rear seal head 9; the tube pass outlet pipe 13 is arranged on the front seal head 1; the shell side inlet connecting pipe 14 and the shell side outlet connecting pipe 15 are both arranged on the shell 4; the two-phase flow enters from the tube side inlet tube 12, exchanges heat through the heat exchange tube and exits from the tube side outlet tube 13.
As shown in fig. 3-5, a rod-fin flow stabilizer 5 is disposed within the heat exchange tube 6. The structure of the rod-fin flow stabilizer 5 is shown in figures 3-4. As shown in fig. 3, a flow stabilizer 5 is disposed in the heat exchange tube 6, the flow stabilizer comprises a central rod 51 disposed along the central axial direction of the heat exchange tube 6 and a plurality of radial rods 52 extending radially along the central rod 51, a plurality of fins 53 extending from the radial rods 52 in the opposite direction to the fluid flow are disposed on the radial rods 52, and the fins 53 have tip portions extending in the opposite direction to the fluid flow.
The rod-fin flow stabilizer is arranged in the heat exchange tube, and mainly separates the liquid phase and the gas phase in the two-phase fluid through the tip of the rod-fin flow stabilizer, divides the liquid phase into small liquid clusters, divides the gas phase into small bubbles, inhibits the backflow of the liquid phase, promotes the smooth flow of the gas phase, plays a role in stabilizing the flow and has the effects of vibration reduction and noise reduction. Compared with the current stabilizer applied in the prior art, the current stabilizer further improves the current stabilizing effect, strengthens heat transfer and is simple to manufacture.
By arranging the rod-fin type flow stabilizing device, the invention equivalently increases the internal heat exchange area in the heat exchange tube, strengthens the heat exchange and improves the heat exchange effect.
The invention divides the gas phase and the liquid phase at all cross section positions of all heat exchange tubes, thereby realizing the contact area between the division of a gas-liquid interface and a gas phase boundary layer and a cooling wall surface on the whole heat exchange tube section and enhancing the disturbance, greatly reducing the noise and the vibration and strengthening the heat transfer.
Preferably, the fins 53 are triangular fins, as shown in fig. 4-6. Because the triangular fin is provided with three tips, the tips can be fully utilized to carry out the flow stabilizing effect downwards.
The radial rod and the triangular fins extending outwards along the radial rod are arranged, so that the heat exchange area can be further increased, the heat exchange effect is improved, and due to the triangular fins, turbulence can be further increased through the triangular tips of the triangular fins similar to the needle-shaped structure, so that fluid is fully mixed, the increase and aggregation of bubbles can be further destroyed, and the heat exchange effect is improved.
Further preferably, the radial bars are rectangular, preferably square, in cross-section.
Further preferably, the radial rod is circular in cross-section.
Preferably, the engineering diameter of the radial rod is 0.21 to 0.42 times, preferably 0.32 times the engineering diameter of the central rod.
Preferably, the radial rod is a rod-shaped object and extends from the center of the circle to the inner wall of the condensation pipe along the radial direction.
Preferably, a plurality of triangular fins are provided on each radial rod, said plurality of triangular fins being of similar shape. Namely, the three mutually corresponding internal angles of different triangular fins are the same.
Preferably, the radial rods are round rods with a diameter of 0.7-1.1 mm, preferably 0.8 mm.
Preferably, the fins extend downwardly from the centerline of the round bar. The fins are of a flat plate structure. The planar structure extension surface passes through the center line of the central rod, and the planar structure extension surface passes through the center line of the radial rod.
Preferably, as shown in fig. 4 and 5, a plurality of fins 53 are arranged on the same radial rod, the fins 53 are similar (i.e. the fins have the same shape), and the size of the fins on the same radial rod is larger and larger in the radial extending direction from the central rod 51 of the heat exchange tube 6. I.e., a distance S1 from the central rod 51 (i.e., from the central axis of the heat exchange tube), and a fin size C1, C1 being a function of the distance S1, i.e., C1= F4(S1), satisfying the following requirements:
c1 '> 0, where C1' is the first derivative of C1.
Because the heat exchange mainly takes place at the heat exchange tube pipe wall, consequently through the fin 53 size of increase heat exchange tube pipe wall for the ability reinforcing of cutting vapour phase and liquid phase near the pipe wall, through the cutting ability near the key enhancement pipe wall, can be pointed to the specific case and make an uproar shock attenuation of falling, thereby further realize the shock attenuation effect of falling an uproar, also can further strengthen heat transfer simultaneously.
Further preferably, the size of the fins on the same radial rod is increased continuously from the central rod of the heat exchange tube to the radial extension direction. I.e., C1 "> 0, where C1" is the reciprocal of the second order of C1, respectively.
Numerical simulation and experimental research show that the change of the increase amplitude can further realize noise reduction and shock absorption, and the effect can be improved by nearly 8%.
Preferably, a plurality of fins 53 are arranged on the same radial rod 52, and the spacing between the fins 53 is continuously reduced in the radial extending direction from the central rod 51 of the heat exchange tube 6. The continuous reduction amplitude of the spacing between the fins is continuously increased.
I.e. a distance S1 from the central rod, a fin pitch J1, J1= F5(S1), satisfying the following requirements:
j1 '< 0, J1 "> 0, wherein J1', J1" are the first and second reciprocal of J1, respectively.
The specific principle is the same as the above. Because the heat exchange mainly takes place at the heat exchange tube pipe wall, consequently through the distribution of increase heat exchange tube pipe wall's fin 53 for the ability reinforcing of cutting vapour phase and liquid phase near the pipe wall, through the shock attenuation of making an uproar that falls near the reinforcing pipe wall, thereby further realize the shock attenuation effect of making an uproar that falls, also can further strengthen heat transfer simultaneously.
Preferably, one base of the triangle is located on the radial bar 52 and the line connecting the apex of the angle corresponding to that side and the midpoint of that side makes an angle of 75-135 deg. with the radial bar. Mainly through the setting of the angle, the tip of the fin can be cut into vapor and liquid phases to the maximum extent, so that the effect of the invention is further improved.
Preferably, an angle formed by a line connecting a vertex of an angle corresponding to the side and a midpoint of the side and the radial rod is 90 °
Preferably, as shown in fig. 5, the triangular fins are isosceles triangular fins, and the bottom sides of the isosceles triangles are located on the radial rods.
Analysis and experiments show that the spacing between the fins 43 cannot be too large, the damping and noise reduction effect is poor if the spacing is too large, the resistance is too large if the spacing is too small, and the resistance is too small if the spacing is too small, and similarly, the height of the fins cannot be too large or too small, and the damping and noise reduction effect is poor or the resistance is too large, so that the damping and noise reduction can be optimized under the condition that normal flow resistance (the total pressure bearing is less than 2.5Mpa or the on-way resistance of a single ascending pipe is less than or equal to 5 Pa/M) is preferentially met through a large number of experiments, and the optimal relation of each parameter is arranged.
The size of the vertex angle of the isosceles triangle is A, the length of the bottom edge of the isosceles triangle is Y, and the distance between the adjacent isosceles triangles is J, so that the following requirements are met:
Y/J= d-a*sin(A)3-b*sin(A)2-c sin (a); wherein sin is a trigonometric function and a, b, c, d are parameters;
0.353<a<0.358,
0.485<b<0.486,
0.082<c<0.083，
0.403<d<0.404， 4<A<33°，
0.1765<Y/J <0.4118。
wherein the distance J between adjacent isosceles triangles is the distance between the midpoints of the bases of adjacent triangles.
Preferably, a =0.3559, b = 0.4859, c =0.08294, and d = 0.4033.
Preferably, 5< a <30 °.
Preferably, the number of the radial rods is 5-10, and the included angles between the radial rods are equal.
Preferably, the number of radial rods is 8.
Preferably, the length of the base of the isosceles triangle is 0.02 to 0.03 times the inner diameter of the ascending tube.
Preferably, a plurality of flow stabilizers are arranged in the heat exchange tube along the flowing direction of the fluid in the heat exchange tube, and the distance between every two adjacent flow stabilizers is longer and longer from the inlet of the heat exchange tube to the outlet of the heat exchange tube. The distance from the inlet of the heat exchange tube is X, the distance between adjacent flow stabilizers is S, S = F1(X), S' is the first derivative of S, and the following requirements are met:
S’>0;
the main reason is that along the flowing direction of the fluid, the gas is condensed due to the heat release of the fluid in the heat exchange tube, and is condensed into a liquid phase, so that along the flowing direction of the fluid in the heat exchange tube, the gas is less and less, the vapor phase in the vapor-liquid two-phase flow is less and less, the heat exchange capacity in the heat exchange tube is continuously increased along with the conversion of the vapor phase into the liquid phase, and the vibration and the noise thereof are also continuously reduced along with the conversion of the vapor phase into the liquid phase. Therefore, the distance between the flow stabilizers can be increased, so that the flow resistance can be reduced, the low noise and the low vibration can be kept, the heat exchange uniformity of the whole heat exchange tube can be kept because the flow stabilizers are distributed less and less as the inner fins, and the materials can be saved.
Experiments show that through the arrangement, vibration and noise can be reduced to the maximum extent, and meanwhile, the flow resistance of the fluid can be guaranteed to be reduced.
Further preferably, the distance between adjacent flow stabilizers from the inlet of the heat exchange tube to the outlet of the heat exchange tube is increased continuously. I.e. S "is the second derivative of S, the following requirements are met:
S”>0;
through experiments, the vibration and noise of about 8% can be further reduced, and the resistance of about 6% of flowing can be reduced.
Preferably, the length of each flow stabilizer remains constant.
Preferably, other parameters of the flow stabilizers (e.g., length, tube diameter, etc.) are maintained, except for the distance between adjacent flow stabilizers.
Preferably, a plurality of flow stabilizers 5 are arranged in the heat exchange tube 6 along the flowing direction of the fluid in the heat exchange tube 6, and the size of the fins of the flow stabilizers 5 is increased from the inlet of the heat exchange tube 6 to the outlet of the heat exchange tube 6. I.e. the fin size of the flow stabilizer is C, C = F2(X), C' is the first derivative of C, and meets the following requirements:
C’>0;
further preferably, the size of the fins of the flow stabilizer is increased from the inlet of the heat exchange tube to the outlet of the heat exchange tube. I.e., C "is the second derivative of C, the following requirement is satisfied:
C”>0;
for example, the distance between adjacent flow stabilizers may vary equally.
Preferably, the distance between adjacent flow stabilizers remains constant.
Preferably, other parameters of the flow stabilizer (e.g., adjacent spacing, tube diameter, etc.) are maintained, other than the length of the flow stabilizer.
Preferably, alongThe flow direction of the fluid in the heat exchange tube 6, a plurality of flow stabilizers are arranged in the heat exchange tube 6, and the distribution density of fins in different flow stabilizers 5 is increased from the inlet of the heat exchange tube 6 to the outlet of the heat exchange tube 6. That is, the fin distribution density of the flow stabilizer is D, D = F3(X), D' is the first derivative of D, and the following requirements are met:
D’>0;
preferably, the fin distribution density of the flow stabilizer is increased from the inlet of the heat exchange tube to the outlet of the heat exchange tube. Namely, it is
D' is the second derivative of D, and meets the following requirements:
D”>0。
for example, the distance between adjacent flow stabilizers may vary equally.
Preferably, the length of the flow stabilizers and the distance between adjacent flow stabilizers remain constant.
Preferably, other parameters of the flow stabilizers (e.g., length, distance between adjacent flow stabilizers, etc.) are maintained, in addition to fin distribution density of the flow stabilizers.
The distance between adjacent flow stabilizers is S, the inner diameter of the heat exchange tube is W, and the distance S between the flow stabilizers is the distance between the central axes of the adjacent radial rods of the adjacent flow stabilizers.
34mm<W<58mm；
50mm<S<80mm。
Preferably, the length L of the heat exchange tube is between 3000-5500 mm. More preferably, 3500-4500 mm.
Further preferred, 40mm < W <50 mm;
55mm<S<60mm。
preferably, S is greater than 1.4 times the height of the fin.
For other parameters, such as the wall thickness of the pipe and the wall thickness of the shell, the parameters are set according to normal standards.
Preferably, the shell-side fluid is water.
Preferably, the flow rate of the fluid in the tube side is 3-5 m/S.
Preferably, the ratio of the length L of the heat exchange tube to the shell diameter of the heat exchanger is 6-10.
Although the present invention has been described with reference to the preferred embodiments, it is not limited thereto. Various changes and modifications may be effected therein by one skilled in the art without departing from the spirit and scope of the invention as defined in the appended claims.
Claims (2)
1. A vapor-liquid two-phase flow heat exchange tube is provided, wherein vapor phase in vapor-liquid two-phase flow flows in the heat exchange tube and can be condensed into liquid phase in the heat exchange process, a flow stabilizer is arranged in the heat exchange tube and comprises a central rod and a plurality of radial rods, the central rod is axially arranged along the center of the heat exchange tube, the radial rods extend along the central rod in the radial direction, a plurality of fins extending from the radial rods in the opposite direction of fluid flow are arranged on the radial rods, each fin is provided with a tip part, the tip parts extend towards the opposite direction of fluid flow, a plurality of fins are arranged on the same radial rod, the fins are similar, and the size of the fins on the same radial rod is larger and larger in the radial direction from the central rod of the heat exchange; characterized in that the extension direction is inclined toward the center of the heat exchange tube.
2. A heat exchange tube according to claim 1, wherein the fin is a triangle, one base of the triangle is located on the radial rod, and a line connecting a vertex of an angle corresponding to the side and a midpoint of the side forms an angle of 75 ° with the radial rod.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201910081865.8A CN109654916B (en) | 2017-08-02 | 2017-08-02 | Vapor-liquid two-phase flow heat exchange tube with fins inclined towards center |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201910081865.8A CN109654916B (en) | 2017-08-02 | 2017-08-02 | Vapor-liquid two-phase flow heat exchange tube with fins inclined towards center |
| CN201710652542.0A CN108332580B (en) | 2017-08-02 | 2017-08-02 | A kind of vehicle repair major flow tube shell type heat exchanger |
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| GB1003013A (en) * | 1962-05-28 | 1965-09-02 | Patterson Kelley Co | Heat exchange device |
| CN2854484Y (en) * | 2005-12-15 | 2007-01-03 | 苏州新太铜高效管有限公司 | Heat-exchange pipe for evaporimeter |
| CN106767007B (en) * | 2016-11-25 | 2017-09-15 | 中国核动力研究设计院 | The heat exchanger of pointed structures is set outside a kind of pipe |
| CN106969652B (en) * | 2017-05-09 | 2019-03-19 | 山东大学 | A kind of condensable annular and separation device heat exchanger of length variation |
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