CN113624038A - Shell and tube heat exchanger - Google Patents
Shell and tube heat exchanger Download PDFInfo
- Publication number
- CN113624038A CN113624038A CN202011501286.3A CN202011501286A CN113624038A CN 113624038 A CN113624038 A CN 113624038A CN 202011501286 A CN202011501286 A CN 202011501286A CN 113624038 A CN113624038 A CN 113624038A
- Authority
- CN
- China
- Prior art keywords
- wall
- gas
- heat exchanger
- curved wall
- curved
- 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.)
- Withdrawn
Links
Images
Classifications
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
- F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
- F28F13/125—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation by stirring
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
- F28F2250/10—Particular pattern of flow of the heat exchange media
- F28F2250/102—Particular pattern of flow of the heat exchange media with change of flow direction
Abstract
The invention provides a shell-and-tube heat exchanger, wherein a flow guide plate extending from the inner wall of an outlet tube to the center of the outlet tube is arranged in the outlet tube, the flow guide plate comprises a first bent wall and a second bent wall extending from the inner wall, the acute angle between a first line and the inner wall between the connecting point of the first bent wall and the inner wall and the intersection point is A2, a plurality of flow guide plates are arranged on the inner wall of the outlet tube along the flowing direction of gas, and the included angle of A2 is smaller and smaller along the flowing direction of gas. The invention provides a novel shell-and-tube heat exchanger, which reduces the flow resistance by setting the acute angle A2 between the first line and the inner wall to be smaller and smaller, and achieves the basically same temperature equalizing effect on the aspects of reduced resistance and material cost saving.
Description
Technical Field
The invention relates to a heat exchanger, in particular to a shell-and-tube heat exchanger with gas participating in heat exchange.
Background
The shell-and-tube heat exchanger is widely applied to industries such as chemical industry, petroleum industry, refrigeration industry, nuclear energy industry and power industry, and due to the worldwide energy crisis, the demand of the heat exchanger in industrial production is more and more, and the quality requirement of the heat exchanger is higher and more. In recent decades, although compact heat exchangers (plate type, plate fin type, pressure welded plate type, etc.), heat pipe type heat exchangers, direct contact type heat exchangers, etc. have been rapidly developed, because the shell and tube type heat exchangers have high reliability and wide adaptability, they still occupy the domination of yield and usage, and according to relevant statistics, the usage of the shell and tube type heat exchangers in the current industrial devices still accounts for about 70% of the usage of all heat exchangers.
The gas heater may take the form of a shell and tube heat exchanger. If the gas heat exchanger has serious problems of ash blockage, corrosion, air leakage and the like under the long-term operation condition, the tangential temperature difference of the outlet gas of the gas heat exchanger is larger. Meanwhile, the temperature of the outlet gas at different positions is not uniform due to the nonuniform heat exchange inside the heat exchanger. When the gas is distributed to different occasions for use, overheating or overcooling conditions can occur due to uneven gas temperature, and the operation is affected.
Therefore, in view of the above-mentioned drawbacks, the prior patent of the applicant proposes a new shell-and-tube heat exchanger, which aims to achieve uniform outlet temperature by providing a distributor for the outlet pipe of the shell-and-tube heat exchanger, so as to meet the requirement of further heat exchange and prolong the service life of the product.
The application is an improvement to the prior application, and the temperature equalizing effect of the distributor is enabled to be optimal by improving the optimization of the structure of the prior application.
Disclosure of Invention
The present invention provides a new heat exchange tube heat exchanger to solve the foregoing technical problems.
In order to achieve the purpose, the technical scheme of the invention is as follows:
a shell-and-tube heat exchanger, the said heat exchanger includes upper and lower header and heat exchange tube set up between upper and lower header; the heat exchanger comprises a gas inlet and a gas outlet, gas flows in from the gas inlet, exchanges heat with fluid in the brush heat exchange tube in the heat exchanger and then flows out from the gas outlet, and the heat exchanger is characterized in that the gas outlet is connected with an outlet tube, a flow guide plate extending from the inner wall of the outlet tube to the center of the outlet tube is arranged in the outlet tube, the flow guide plate comprises a first curved wall and a second curved wall extending from the inner wall, wherein an acute angle formed by a tangent line at the joint of the first curved wall and the inner wall is smaller than an acute angle formed by a tangent line at the joint of the second curved wall and the inner wall, the first curved wall and the second curved wall are curved towards the gas flowing direction, the intersection point of the first wall and the second wall is positioned at the downstream of the joint of the first curved wall and the inner wall, and is positioned at the downstream of the joint of the second curved wall and the inner wall; the gas flow guiding device is characterized in that an acute angle between a first line and an inner wall between a connection point of the first bending wall and the inner wall and a crossing point is A2, a plurality of flow guiding plates are arranged on the inner wall of the outlet pipe along the flow direction of gas, and the included angle of A2 is smaller and smaller along the flow direction of gas.
Preferably, the included angle a2 increases in the direction of gas flow, with decreasing magnitude.
Preferably, the first curved wall and the second curved wall are arcs, wherein the arc diameter of the first curved wall is smaller than the arc diameter of the second curved wall.
Preferably, the tangent to the first curved wall at the location of the intersection forms an angle of 30-60 with the axis of the outlet tube.
Preferably, a plurality of layers of flow guide plates are arranged on the inner wall of the outlet pipe along the flowing direction of the gas, and the flow guide plates of the adjacent layers are distributed in a staggered mode.
Preferably, the distance between the intersection point and the inner wall of the outlet pipe is 0.4 to 0.5 times the diameter of the outlet pipe.
Preferably, the length of the first curved wall is greater than the length of the second curved wall.
Preferably, the total radian of the circular arcs connecting the drainage plates of the same layer with the inner wall is 150-180 degrees.
Preferably, the length L2 of the first line between the connection point and the intersection point of the first curved wall and the inner wall, the length L1 of the second line between the connection point and the intersection point of the second curved wall and the inner wall, the included angle between the first line and the inner wall is a2, the included angle between the second line and the inside is a1, the distance S between adjacent wedge-shaped structures in the flowing direction of the gas, namely the distance between the center points of the adjacent flow guide plates on the inner wall, and the center point is the midpoint of the connection line of the connection points of the first curved wall, the second curved wall and the inner wall, and the following requirements are met:
n-a-b ln (M), wherein N ═ (L1+ L2)/S, M ═ sin (a2)/sin (a 1); ln is a function of the logarithm of the number,
0.263<a<0.264，0.0829<b<0.0831；
compared with the prior art, the flat heat exchange tube has the following advantages:
1) the invention reduces the flow resistance by setting the acute angle A2 between the first line and the inner wall to be smaller and smaller, and the temperature equalizing effect achieves the same effect on the aspects of reduced resistance and material cost saving.
2) The invention provides a novel shell-and-tube heat exchanger, wherein a flow guide plate is arranged in a gas outlet pipe, so that a part of gas flows along the flow guide plate and is guided to the opposite direction, and the gas is fully mixed with the gas entering in the opposite direction, thereby realizing uniform temperature of the gas, realizing the requirement of further heat exchange and prolonging the service life of a product.
3) According to the invention, through carrying out extensive research on the heat exchange rule caused by the change of each parameter of the drainage plate, the drainage plate structure of the heat exchanger is optimized under the condition of meeting the flow resistance, so that the optimal outlet gas temperature equalizing effect is achieved.
4) According to the invention, through reasonable layout, the drainage plates of adjacent rows are arranged in a staggered manner, so that gas is further fully mixed, and the temperature is uniform.
5) The invention further promotes the full mixing by setting the distribution change of parameters such as the size, the number angle and the like of the drainage plate along the flowing direction of the fluid.
6) According to the invention, the distance of the drainage plate is widely researched, a formula of the minimum distance is designed, the temperature-equalizing mixing requirement is fully met, the problems of uneven mixing and increased flow resistance are avoided, and the optimal outlet gas temperature-equalizing effect is achieved.
Drawings
FIG. 1 is a schematic diagram of the construction of a heat exchanger according to the present invention;
FIG. 2 is an axial cut view of an outlet tube with a flow guide plate according to the present invention;
figure 3 is a schematic diagram of the size of the outlet tube-containing baffle of the present invention.
FIG. 4 is a perspective view of 1 drainage plate per layer.
FIG. 5 is a perspective view of 3 drainage plates per layer.
FIG. 6 is a perspective view of 1 drainage plate per layer.
Fig. 7 is an exploded perspective view of one side of the outlet tube of fig. 6.
The reference numbers are as follows:
1 heat exchange tube, 2 flow guide plates, 21 first curved wall, 22 second curved wall, 23 intersection point, 3 inlet tube, 4 outlet tube, 5 outlet tube, 6 gas inlet, 7 gas outlet, 8 upper header and 9 lower header
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.
Fig. 1 discloses a shell and tube heat exchanger for making the outlet gas temperature uniform. As shown in fig. 1, the heat exchanger includes an upper header 8, a lower header 9, and a heat exchange tube 1 disposed between the upper and lower headers; the heat exchanger comprises a gas inlet 6 and a gas outlet 7, wherein gas flows in from the gas inlet 6, exchanges heat with fluid in the heat exchange tube 1 in the heat exchanger and then flows out from the gas outlet 7.
As a modification, the gas outlet 7 is connected with the outlet pipe 5, as shown in fig. 2, a flow guide plate 2 extending from the inner wall 51 of the outlet pipe to the center of the outlet pipe is arranged in the outlet pipe 5, the flow guide plate 2 comprises a first curved wall 21 and a second curved wall 22 extending from the inner wall, wherein the acute angle formed by the tangent at the junction of the first curved wall 21 and the inner wall 51 and the inner wall is smaller than the acute angle formed by the tangent at the junction of the second curved wall 22 and the inner wall and the acute angle formed by the tangent at the junction of the first curved wall 21 and the inner wall 51 and the inner wall are smaller than the acute angle formed by the second curved wall 22 and the inner wall, the first curved wall 21 and the second curved wall 22 are curved and extend in the gas flow direction, and the intersection 23 of the first curved wall 21 and the second curved wall 22 is located downstream of the junction of the first curved wall 21 and the inner wall 51 and the second curved wall 22. The shape of the flow guide plate 2 is that of the first and second curved walls 21, 22 and the inner wall rotated along the outlet tube axis.
The invention provides a method for improving the heat exchange efficiency of a gas heat exchanger, which is characterized in that the flow guide plate is arranged in the gas outlet pipe, so that a part of gas flows along the flow guide plate and is guided to the opposite direction, and the gas is fully mixed with the gas entering in the opposite direction, thereby realizing the uniform temperature of the gas, realizing the further heat exchange requirement and prolonging the service life of the product.
According to the invention, the drainage plate is respectively provided with the first bending wall and the second bending wall, and the two bending walls are arranged, so that the disturbance effect of gas is better, the area of the drainage plate contacting the inner wall is increased, and the stability is improved. And through setting up the second crooked wall for the gas that comes from opposite direction water conservancy diversion also can be along the crooked direction motion of second crooked wall direction, increases the buffering, reduces flow resistance.
Preferably, the first curved wall 21 and the second curved wall 22 are circular arcs, wherein the circular arc diameter of the first curved wall 21 is smaller than the circular arc diameter of the second curved wall 22.
The first wall and the second wall are in the shape of circular arcs, so that the gas flow resistance is smaller, and the gas flows to the opposite side easily to be mixed.
Preferably, the tangent to the first curved wall 21 at the location of the intersection point 23 forms an angle of 30-60 deg., preferably 45 deg., with the axis of the outlet tube. By providing this angle, fluid can be quickly directed to the opposite downstream location, and flow resistance can be further reduced.
Preferably, as shown in fig. 2, a plurality of layers of flow guide plates 2 are arranged on the inner wall of the outlet pipe 5 along the flowing direction of the gas, and the flow guide plates of the adjacent layers are staggered. Through the staggered distribution of the drainage plates of adjacent rows, the gas can fully move to the opposite position in the outlet pipe, and the full and uniform mixing is ensured. FIG. 2 shows one drainage plate per layer. Of course, each layer of drainage plate can be provided with a plurality of drainage plates, for example, two drainage plates with each angle of 90 degrees or four drainage plates with each angle of 45 degrees can be provided.
Preferably, the distance between the intersection point and the inner wall of the outlet pipe is 0.3 to 0.5 times, preferably 0.4 times the diameter of the outlet pipe. With this arrangement, the air has less flow resistance on thorough mixing.
Preferably, the length of the first curved wall is greater than the length of the second curved wall.
Preferably, the total radian of the circular arcs connecting the drainage plates of the same layer with the inner wall is 150-180 degrees. This parameter set ensures thorough mixing while meeting the resistance requirements. For example, FIGS. 2, 4, and 6 show one drainage plate per layer, with the total arc of one plate being 150 and 180. Of course, multiple drainage plates can be arranged on each layer, for example, three drainage plates are arranged on each layer in the angle of 150 and 180 degrees in total in FIG. 5.
As preferablely, A layer drainage plate sets up the polylith, sets up the interval between the A drainage plate, and the equidistant setting of A drainage plate, B layer are the adjacent row on A layer, follow the direction of flow and observe, and B layer drainage plate sets up the interval position department on A layer. Through the complementation of the positions of the drainage plates of the adjacent layers, the gas can fully move to the opposite position in the outlet pipe, and the full and uniform mixing is ensured. It should be noted that the layer a and the layer B are not specifically and explicitly specified, and A, B is only used as a distinction and is used as an adjacent layer.
Preferably, a plurality of flow guide plates are arranged on the inner wall of the outlet pipe along the flowing direction of the gas, and the distribution density of the flow guide plates is smaller and smaller along the flowing direction of the gas. Because the mixing degree of the gas is better and better along with the continuous movement of the gas, the distribution density is required to be set to be smaller and smaller so as to reduce the flow resistance, and the temperature equalizing effect achieves the basically same effect on the aspects of reducing the resistance and saving the material cost.
Preferably, the distribution density of the flow guide plates is increased along the flowing direction of the gas in a smaller and smaller range. The effect is obtained through a large number of numerical simulation and experimental research results, and the research finds that the rule accords with the rule of gas motion, and the temperature equalizing effect achieves the basically same effect on the aspects of further reduction of resistance and saving of material cost.
Preferably, a plurality of flow guiding plates are arranged on the inner wall of the outlet pipe along the flowing direction of the gas, and the size of the flow guiding plates is smaller along the flowing direction of the gas. Because the mixing degree of the gas is better and better along with the continuous movement of the gas, the size is required to be smaller and smaller so as to reduce the flow resistance, and the temperature equalizing effect achieves the same effect in the aspects of reducing the resistance and saving the material cost.
Preferably, a plurality of flow guiding plates are arranged on the inner wall of the outlet pipe along the flowing direction of the gas, and the size of the flow guiding plates is gradually reduced along the flowing direction of the gas. The effect is obtained through a large number of numerical simulation and experimental research results, and the research finds that the rule accords with the rule of gas motion, and the temperature equalizing effect achieves the basically same effect on the aspects of further reduction of resistance and saving of material cost.
Through a large amount of numerical simulation and experimental study discovery, the angle and the size of drainage plate have very big influence to heat transfer and misce bene, drainage plate and inner wall contained angle are on the small side, can lead to mixing effect variation, and lead to the drainage plate size too big, influence the flow resistance, the contained angle is on the large side, it is not good to lead to stirring fluid effect, the resistance grow, mixing effect variation, the interval of drainage plate is too big, can lead to the vortex effect not good, the interval undersize can lead to increasing the movement resistance, consequently, this application has obtained nearest drainage plate structure size optimization relation through a large amount of data simulation and experiments.
Preferably, the length L2 of the first line between the connection point of the first curved wall and the inner wall and the intersection point 23, the length L1 of the second line between the connection point of the second curved wall and the inner wall and the intersection point 23, the acute angle between the first line and the inner wall is a2, the acute angle between the second line and the inner wall is a1, and the distance S between adjacent flow guide plates on the same side along the flow direction of the gas (for example, the distance between two adjacent flow guide plates on the upper side in fig. 2 is S), that is, the distance between the center points of the inner walls of the adjacent flow guide plates, and the center point is the midpoint of the connection point of the first curved wall and the second curved wall and the inner wall, satisfy the following requirements:
n-a-b ln (M), wherein N ═ (L1+ L2)/S, M ═ sin (a2)/sin (a 1); ln is a function of the logarithm of the number,
0.263<a<0.264，0.0829<b<0.0831；
preferably, 0.25< M <0.75,0.28< N <0.35,45< a1<75 °, 15< a2<45 °,400< S <500mm, 70< L2<130mm, 30< L1<90 mm.
The optimal design requirements of the drainage plate structure can be met by the various types. The structural optimization formula is a main improvement point of the invention, is the most optimized formula which is researched by a large number of numerical simulations and experiments, and is not common knowledge in the field.
More preferably, a is 0.2634 and b is 0.0830.
It is found in data simulation and experiment that the interval between the drainage plate must be greater than certain distance, otherwise can lead to the fluid to guide to opposite direction through last drainage plate, but if the interval undersize between the drainage plate, can lead to gaseous flowing opposite, not fully filled with whole pipeline yet, set up the drainage plate this moment, play not can not play the mixed effect, the drainage plate only plays a baffling board effect, does not guide the effect of mixing, can only increase the flow resistance. Therefore, the design scheme of the minimum spacing of the drainage plate is provided through a great deal of research, and the design of the drainage plate has certain guiding significance.
The vertical point of the intersection point 23 on the inner wall, the line formed by the intersection point and the vertical point is a third line, the distance between the connecting point of the first bending wall and the inner wall and the vertical point is H, the acute angle formed by the first line and the third line is A3, the acute angle formed by the tangent of the first bending wall at the intersection point and the axis of the outlet pipe is A4, the inner pipe diameter of the outlet pipe is R, and the distance S is designed in the following way:
(S/H)>a+b*Ln(T)，(S/R)2>c+d*Ln(T)；
wherein T ═ sin (A3)/sin (a4), 2.74< a <2.75,17.4< b <17.5, 1.998< c <1.999, 3.431< d <3.432,
30< A3<70 °, 20< a4<60 °; preferably 1.07< T < 1.30;
preferably, a is 2.743, b is 17.47, c is 1.9984, d is 0.4316;
according to the invention, through a large number of experiments and numerical simulation, the minimum design distance of the drainage plate is obtained, the resistance is reduced through the design distance, and meanwhile, the full mixing can be realized.
Preferably, a plurality of flow guide plates are arranged on the inner wall of the outlet pipe along the flowing direction of the gas, and the included angle of A2 is smaller along the flowing direction of the gas. Because along with the continuous motion of gas, gaseous mixture degree is more and more good, consequently need set up the contained angle and diminishes to alleviate flow resistance, in the degree that resistance reduces and material cost saves, the samming effect reach basically the same effect.
Preferably, the included angle a2 increases in the direction of gas flow, with decreasing magnitude. The effect is obtained through a large number of numerical simulation and experimental research results, and the research finds that the rule accords with the rule of gas motion, and the temperature equalizing effect achieves the basically same effect on the aspects of further reduction of resistance and saving of material cost.
Preferably, a plurality of flow guide plates are arranged on the inner wall of the outlet pipe along the flowing direction of the gas, and the included angle of A4 is smaller along the flowing direction of the gas. Because along with the continuous motion of gas, gaseous mixture degree is more and more good, consequently need set up the contained angle and diminishes to alleviate flow resistance, in the degree that resistance reduces and material cost saves, the samming effect reach basically the same effect.
Preferably, the included angle a4 increases in the direction of gas flow, with decreasing magnitude. The effect is obtained through a large number of numerical simulation and experimental research results, and the research finds that the rule accords with the rule of gas motion, and the temperature equalizing effect achieves the basically same effect on the aspects of further reduction of resistance and saving of material cost.
Preferably, a plurality of flow guide plates are arranged on the inner wall of the outlet pipe along the flowing direction of the gas, and the total radian of the arc connecting the flow guide plates on the same layer with the inner wall is smaller and smaller along the flowing direction of the gas. Because the mixing degree of the gas is better and better along with the continuous movement of the gas, the flow space which needs to be arranged is larger and larger so as to reduce the flow resistance, and the temperature equalizing effect achieves basically the same effect on the aspects of reducing the resistance and saving the material cost.
Preferably, the total radian of the arcs connecting the drainage plates and the inner wall of the same layer in the flow direction of the gas is gradually reduced and increased along the flow direction of the gas. The effect is obtained through a large number of numerical simulation and experimental research results, and the research finds that the rule accords with the rule of gas motion, and the temperature equalizing effect achieves the basically same effect on the aspects of further reduction of resistance and saving of material cost.
Preferably, a plurality of flow guide plates are arranged on the inner wall of the outlet pipe along the flowing direction of the gas, and the included angle of A1 is larger along the flowing direction of the gas. Because the mixing degree of the gas is better and better along with the continuous movement of the gas, the included angle needs to be set to be larger and larger so as to reduce the size, so that the flow resistance is reduced, and the temperature equalizing effect achieves the basically same effect on the aspects of reducing the resistance and saving the material cost.
Preferably, the included angle a1 increases with increasing magnitude in the direction of flow of the gas. The effect is obtained through a large number of numerical simulation and experimental research results, and the research finds that the rule accords with the rule of gas motion, and the temperature equalizing effect achieves the basically same effect on the aspects of further reduction of resistance and saving of material cost.
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 (4)
1. A shell-and-tube heat exchanger, the said heat exchanger includes upper and lower header and heat exchange tube set up between upper and lower header; the heat exchanger comprises a gas inlet and a gas outlet, gas flows in from the gas inlet, exchanges heat with fluid in the brush heat exchange tube in the heat exchanger and then flows out from the gas outlet, and the heat exchanger is characterized in that the gas outlet is connected with an outlet tube, a flow guide plate extending from the inner wall of the outlet tube to the center of the outlet tube is arranged in the outlet tube, the flow guide plate comprises a first curved wall and a second curved wall extending from the inner wall, wherein an acute angle formed by a tangent line at the joint of the first curved wall and the inner wall is smaller than an acute angle formed by a tangent line at the joint of the second curved wall and the inner wall, the first curved wall and the second curved wall are curved towards the gas flowing direction, the intersection point of the first wall and the second wall is positioned at the downstream of the joint of the first curved wall and the inner wall, and is positioned at the downstream of the joint of the second curved wall and the inner wall; the gas flow guiding device is characterized in that an acute angle between a first line and an inner wall between a connection point of the first bending wall and the inner wall and a crossing point is A2, a plurality of flow guiding plates are arranged on the inner wall of the outlet pipe along the flow direction of gas, and the included angle of A2 is smaller and smaller along the flow direction of gas.
2. The heat exchanger of claim 1, wherein the included angle a2 increases in magnitude with decreasing magnitude along the direction of flow of the gas.
3. The heat exchanger of claim 1, wherein the first curved wall and the second curved wall are arcs, wherein the diameter of the arc of the first curved wall is less than the diameter of the arc of the second curved wall.
4. A shell-and-tube heat exchanger, the said heat exchanger includes upper and lower header and heat exchange tube set up between upper and lower header; the heat exchanger comprises a gas inlet and a gas outlet, gas flows in from the gas inlet, exchanges heat with fluid in the brush heat exchange tube in the heat exchanger and then flows out from the gas outlet, and the heat exchanger is characterized in that the gas outlet is connected with an outlet tube, a flow guide plate extending from the inner wall of the outlet tube to the center of the outlet tube is arranged in the outlet tube, the flow guide plate comprises a first curved wall and a second curved wall extending from the inner wall, wherein an acute angle formed by a tangent line at the joint of the first curved wall and the inner wall is smaller than an acute angle formed by a tangent line at the joint of the second curved wall and the inner wall, the first curved wall and the second curved wall are curved towards the gas flowing direction, the intersection point of the first wall and the second wall is located at the downstream of the joint of the first curved wall and the inner wall, and is located at the downstream of the joint of the second curved wall and the inner wall.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011501286.3A CN113624038A (en) | 2020-12-18 | 2020-12-18 | Shell and tube heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011501286.3A CN113624038A (en) | 2020-12-18 | 2020-12-18 | Shell and tube heat exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN113624038A true CN113624038A (en) | 2021-11-09 |
Family
ID=78377787
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202011501286.3A Withdrawn CN113624038A (en) | 2020-12-18 | 2020-12-18 | Shell and tube heat exchanger |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN113624038A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114489168A (en) * | 2022-03-21 | 2022-05-13 | 上海淳禧应用技术股份有限公司 | High-precision humidity calibration device and humidity calibration method |
-
2020
- 2020-12-18 CN CN202011501286.3A patent/CN113624038A/en not_active Withdrawn
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114489168A (en) * | 2022-03-21 | 2022-05-13 | 上海淳禧应用技术股份有限公司 | High-precision humidity calibration device and humidity calibration method |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| KR20110083996A (en) | Double-piped heat exchanger | |
| CN201517899U (en) | Pipe shell type heat exchanger | |
| CN103411454A (en) | Tube type heat exchanger with outer-protruding-type corrugated tubes arranged in staggering mode | |
| CN104913663A (en) | Tube shell pass volume-adjustable longitudinal turbulence oil cooler | |
| CN1283972C (en) | Shell-and-tube heat exchanger | |
| CN113624038A (en) | Shell and tube heat exchanger | |
| CN210689299U (en) | Efficient energy-saving tubular heat exchanger | |
| CN113804021B (en) | Shell-and-tube heat exchanger with linear drainage plate with total radian changing along length | |
| CN113624039A (en) | Shell-and-tube heat exchanger with arc-shaped drainage plates changing in radian | |
| CN113776364A (en) | Shell-and-tube heat exchanger for heating air | |
| CN113624037A (en) | Linear temperature-equalizing flow-guiding shell-and-tube heat exchanger | |
| CN113790618A (en) | Shell and tube heat exchanger | |
| CN113686177A (en) | Linear temperature-equalizing flow-guiding shell-and-tube heat exchanger | |
| CN114076301A (en) | Linear temperature-uniforming plate steam boiler | |
| CN111692896B (en) | Hot melt type gas-liquid two-phase heat exchange core structure | |
| CN209926938U (en) | Heat exchanger | |
| CN100467993C (en) | Helical baffles support dimpled pipe bundle heat exchanger | |
| CN209978658U (en) | Shell and tube heat exchanger and air conditioning unit | |
| CN206037815U (en) | Spiral baffling board for heat exchanger | |
| CN207035905U (en) | A kind of macroporous plate convergent-divergent pipe efficient heat exchanger | |
| CN205192299U (en) | Novel all -welded lamella heat exchanger | |
| CN113623628B (en) | Steam boiler with arc plates | |
| CN219829593U (en) | Novel external flow-guiding efficient heat exchanger | |
| CN219301352U (en) | Coiled pipe type heat exchanger | |
| CN220583157U (en) | Double-tube heat exchanger structure |
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 | ||
| WW01 | Invention patent application withdrawn after publication | ||
| WW01 | Invention patent application withdrawn after publication |
Application publication date: 20211109 |