CN109405589B - Spherical heat exchanger with double tube-pass independent heat exchange - Google Patents
Spherical heat exchanger with double tube-pass independent heat exchange Download PDFInfo
- Publication number
- CN109405589B CN109405589B CN201811455407.8A CN201811455407A CN109405589B CN 109405589 B CN109405589 B CN 109405589B CN 201811455407 A CN201811455407 A CN 201811455407A CN 109405589 B CN109405589 B CN 109405589B
- Authority
- CN
- China
- Prior art keywords
- spiral
- heat exchange
- heat
- shell
- tube
- 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.)
- Active
Links
- 238000012546 transfer Methods 0.000 claims description 20
- 229910000831 Steel Inorganic materials 0.000 claims description 12
- 239000010959 steel Substances 0.000 claims description 12
- 230000009977 dual effect Effects 0.000 claims description 8
- 239000012774 insulation material Substances 0.000 claims description 7
- 230000003068 static effect Effects 0.000 claims description 5
- 239000012530 fluid Substances 0.000 abstract description 65
- 238000000034 method Methods 0.000 description 12
- 230000000694 effects Effects 0.000 description 10
- 230000008569 process Effects 0.000 description 9
- 238000009413 insulation Methods 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- 230000002035 prolonged effect Effects 0.000 description 3
- 230000009471 action Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 239000011810 insulating material Substances 0.000 description 2
- 238000005192 partition Methods 0.000 description 2
- 239000002918 waste heat Substances 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 239000000378 calcium silicate Substances 0.000 description 1
- 229910052918 calcium silicate Inorganic materials 0.000 description 1
- OYACROKNLOSFPA-UHFFFAOYSA-N calcium;dioxido(oxo)silane Chemical compound [Ca+2].[O-][Si]([O-])=O OYACROKNLOSFPA-UHFFFAOYSA-N 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 239000002657 fibrous material Substances 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 238000009776 industrial production Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 239000011490 mineral wool Substances 0.000 description 1
- 238000002156 mixing Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000010451 perlite Substances 0.000 description 1
- 235000019362 perlite Nutrition 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- -1 rock wool Chemical compound 0.000 description 1
- 239000013049 sediment Substances 0.000 description 1
- 229910001220 stainless steel Inorganic materials 0.000 description 1
- 239000010935 stainless steel Substances 0.000 description 1
- 230000001954 sterilising effect Effects 0.000 description 1
- 238000004659 sterilization and disinfection Methods 0.000 description 1
- 238000005728 strengthening Methods 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
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
- F28D7/0066—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
- F28D7/0075—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids with particular circuits for the same heat exchange medium, e.g. with the same heat exchange medium flowing through sections having different heat exchange capacities or for heating or cooling the same heat exchange medium at different temperatures
-
- 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
- F28D7/02—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 helically coiled
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
- F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
- F28F21/081—Heat exchange elements made from metals or metal alloys
- F28F21/082—Heat exchange elements made from metals or metal alloys from steel or ferrous alloys
Abstract
The invention discloses a spherical heat exchanger with double tube-pass independent heat exchange, which comprises a spherical shell, a spiral heat exchange tube and a direct heat exchange tube, wherein the upper end and the lower end of the shell are respectively provided with a direct heat flow input port and a direct heat flow output port, and the two ends of the direct heat exchange tube are respectively connected with the direct heat flow input port and the direct heat flow output port; the upper end of the shell is provided with a cold flow output port and a spiral hot flow input port, and the lower end of the shell is provided with a cold flow input port and a spiral hot flow output port; the spiral heat exchange tube is sleeved on the direct heat exchange tube, and two ends of the spiral heat exchange tube are respectively connected with the spiral heat flow input port and the spiral heat flow output port; the cold flow output port and the cold flow input port are both communicated with the inner cavity of the shell; the inner cavity of the shell is provided with a spiral guide plate, and the cold flow input port and the cold flow output port are communicated through the inner cavity of the shell. The invention can prolong the heat exchange time of the cold and hot fluid, and improve the heat exchange efficiency by the countercurrent of the cold and hot fluid.
Description
Technical Field
The invention relates to a heat exchanger technology, in particular to a spherical heat exchanger with double tube-pass independent heat exchange.
Background
A heat exchanger is a device that transfers a portion of the heat of a hot fluid to a cold fluid, also known as a heat exchanger. The dividing wall type heat exchanger is key equipment for ensuring stable operation of a system, reasonable process temperature and pressure drop, saving energy, recovering waste heat and waste heat in industrial production, has large specific gravity in the aspects of metal consumption, equipment investment and the like, and is widely applied to the aspects of heating, cooling, sterilization, evaporation, condensation, thermal addition and the like.
The existing novel partition type high-efficiency heat exchanger improves the heat exchange efficiency of the partition type heat exchanger through the enhanced heat transfer technology on the basis of traditional heat exchange, and reduces energy loss in the heat exchange process. In the aspect of the enhanced heat transfer technology, the novel high-efficiency dividing wall type heat exchanger aims to increase the heat transferred by a unit heat transfer area as much as possible in a unit time. The current heat transfer enhancement methods mainly comprise three methods: improving heat transfer coefficient, enlarging unit heat transfer area, and increasing heat transfer temperature difference.
The specific means for improving the heat exchange efficiency of the novel high-efficiency dividing wall type heat exchanger are as follows: the structure of the tube side and the shell side of the traditional divided wall type heat exchanger is changed, and the turbulence effect of fluid is increased, so that the thickness of a boundary layer is reduced, or the formation of the boundary layer is disturbed, and the unit heat exchange area is increased. For shell-and-tube heat exchangers, the enhanced heat transfer of the tube side is usually achieved by processing the light tube to obtain special tubes of various structures, such as spiral grooved tubes, transverse grooved tubes, corrugated tubes, low-thread finned tubes, spiral flat tubes, porous surface tubes, pin fin tubes, in-tube inserts and the like. The shell side heat transfer enhancement is realized by designing baffle plates with different shapes, such as arched baffle plates, tower-connection type spiral baffle plates, continuous spiral baffle plates and the like. However, the shell-side flow channel formed by the arched baffle plates enables the fluid to flow in a Z shape, the movement direction and the speed of the fluid are changed, and a large flow dead zone exists. The spiral curved surface of the lap-joint type spiral baffle plate has a serious triangular leakage flow area, so that the flow of the shell-side fluid deviates from the spiral flow, and the heat transfer performance of the shell side is reduced. The continuous spiral baffle plate enables the shell-side fluid to flow through the spiral curved surface in a continuous turbulence mode, the heat transfer coefficient of the shell side is improved, the power loss is reduced, and meanwhile, the continuous spiral baffle plate is of a full supporting structure, and the risk of failure of the dividing wall type heat exchanger caused by flow vibration is reduced. In order to meet the use requirements, heat exchangers with higher heat exchange efficiency and turbulence effect are increasingly required at present, and heat exchangers suitable for various working environments are also required.
Disclosure of Invention
The invention aims to overcome the defects in the prior art and provides a spherical heat exchanger with double tube-pass independent heat exchange. The spherical heat exchanger with double tube-pass independent heat exchange improves turbulence, prolongs the heat exchange time of cold and hot fluid and strengthens heat transfer.
The aim of the invention is achieved by the following technical scheme: the spherical heat exchanger with double tube-pass independent heat exchange comprises a spherical shell, a spiral heat exchange tube and a direct heat exchange tube, wherein a direct heat flow input port and a direct heat flow output port are respectively arranged at the upper end and the lower end of the shell, and the two ends of the direct heat exchange tube are respectively connected with the direct heat flow input port and the direct heat flow output port; the upper end of the shell is provided with a cold flow output port and a spiral heat flow input port, the cold flow output port and the spiral heat flow input port are respectively positioned at two sides of the direct-current heat input port, the lower end of the shell is provided with a cold flow input port and a spiral heat flow output port, and the cold flow input port and the spiral heat flow output port are respectively positioned at two sides of the direct-current heat flow output port; the spiral heat exchange tube is sleeved on the direct heat exchange tube, and two ends of the spiral heat exchange tube are respectively connected with the spiral heat flow input port and the spiral heat flow output port; the cold flow output port and the cold flow input port are both communicated with the inner cavity of the shell; the inner cavity of the shell is provided with a spiral guide plate, and the cold flow input port and the cold flow output port are communicated through the inner cavity of the shell.
Preferably, the spiral diameter of the spiral heat exchange tube is gradually reduced from the middle part of the spiral heat exchange tube to the two ends.
Preferably, the spiral heat exchange tubes are provided with a plurality of spiral heat exchange tubes, each spiral heat exchange tube is arranged in parallel, and a space is reserved between every two adjacent spiral heat exchange tubes.
Preferably, the pipe diameter of the spiral heat exchange pipe is gradually reduced from the middle part of the spiral heat exchange pipe to the two ends.
Preferably, a spoiler is inserted into the straight heat exchange tube.
Preferably, the turbulence member is any one of a torsion belt, a spiral coil, a spiral sheet and a static mixer.
Preferably, the straight heat exchange tubes are provided with a plurality of straight heat exchange tubes, each straight heat exchange tube is arranged in parallel, and a space is reserved between every two adjacent straight heat exchange tubes.
Preferably, the shell is of a double-layer steel structure, and a high-temperature-resistant heat insulation material is filled between the two layers of steel in the shell.
Preferably, the housing comprises an upper half housing and a lower half housing, and the upper half housing and the lower half housing are fixedly connected through a clamp assembly.
Preferably, the width of the spiral guide plate gradually decreases from the middle part of the spiral guide plate to two ends, a gap is arranged between the outer edge of the spiral guide plate and the inner wall of the shell, and the size of the gap is 0.2 mm-0.5 mm.
Compared with the prior art, the invention has the following advantages:
1. and the heat exchange time of the cold and hot fluid is prolonged, the cold and hot fluid is in countercurrent flow, and the heat exchange efficiency is improved. The spiral heat exchange tube and the straight heat exchange tube are adopted to form a tube pass, wherein the spiral heat exchange tube can prolong the time of hot fluid in the tube pass, and meanwhile, a continuous spiral guide plate is arranged in the inner cavity of the shell so as to start a spiral shell pass in the shell, the spiral shell pass prolongs the time of cold fluid in the shell pass, and meanwhile, cold fluid in the shell pass and hot fluid in the tube pass flow in opposite directions, so that the heat exchange efficiency between the cold fluid and the hot fluid can be greatly improved. Meanwhile, the turbulence degree of fluid can be improved by the shell side formed by the inner cavity of the shell and the spiral flow guide pipe and the tube side formed by the spiral heat exchange pipe, and the heat exchange efficiency is further improved.
2. The branch pipes exchange heat, and have the double functions of a spiral heat exchange pipe and a direct heat exchange pipe. In the invention, the spiral heat exchange tube and the straight heat exchange tube are independent in tube pass, and when the use environment is a hot fluid, the same fluid with different temperatures can be obtained due to different heat exchange time. When the use environment is two different hot fluids, the cold fluid can exchange heat with the two different hot fluids at the same time, so that the utilization rate of the cold fluid can be improved, the use of different heat exchangers can be reduced, and the industrial design is simplified.
3. The heat transfer coefficient is improved, the heat exchange effect is good, and the self-descaling capability is achieved. Because the turbulent flow piece and the spiral heat exchange tube are inserted into the straight heat exchange tube, the flow of fluid can form secondary circulation, and the pipe diameter and the spiral diameter of the spiral heat exchange tube are gradually changed, the spiral heat exchange tube can obtain higher turbulence degree under a lower Reynolds number, the thickness of a boundary layer is reduced, the heat transfer coefficient is improved, and the heat exchange effect is enhanced. The tube side and the shell side have high turbulence, so that dirt is easy to wash away, and the maintenance is very convenient.
4. The pressure-resistant steel plate is uniform in stress and strong in pressure resistance, can be used in high-temperature and high-pressure occasions, and has the largest specific surface area of a unit body. Compared with the common cylindrical heat exchanger, under the condition of the same diameter, the internal stress of the spherical heat exchanger is minimum, the stress is uniform, and the capacity of bearing fluid is twice as high as that of the cylindrical heat exchanger, so that the thickness of the spherical heat exchanger shell is only half that of the common cylindrical heat exchanger. At the same volume and the same pressure, the surface area of the spherical heat exchanger is the smallest, so the area of the required steel is small. The spherical heat exchanger can greatly reduce the consumption of steel, generally saves 30% -45%, and in addition, the spherical heat exchanger has small occupied area and small foundation engineering, and can save the land area.
5. Can be placed at any angle and any space, and has wide application range. The common heat exchanger generally has a certain length-width ratio and also has a specific support, and when in use, the space position and the occupied area conforming to the size of the common heat exchanger are required, so that the application range of the common heat exchanger is limited to a certain extent. In contrast, because the ball body and the heat exchanger are designed to have high symmetry, a specific support is not needed, and the ball body can rotate at any angle to meet the requirements of certain use occasions, and even can normally work in a space away from the ground, so that the ball body has a very wide application range.
6. The thermal expansion stress of the tube bundle is small. The two ends of the tube bundles of the spiral heat exchange tube and the straight heat exchange tube are provided with certain free sections which can be expanded by themselves, so that when the temperature difference of two fluids for heat exchange is large, thermal expansion stress does not exist.
7. The heat loss through the shell is reduced, and the manufacturing cost is saved. The shell of the spherical heat exchanger is of a double-layer steel structure, and the middle of the spherical heat exchanger is filled with high-temperature resistant heat insulation materials. Compared with the vacuumizing heat insulation method, the filling heat insulation mode is more economical, and is beneficial to reducing the manufacturing cost of the spherical heat exchanger of the spiral pipeline.
Drawings
Fig. 1 is a schematic structural view of a dual-tube independent heat exchange spherical heat exchanger of the present invention.
Fig. 2 is a cross-sectional view of a dual tube pass independent heat exchanging spherical heat exchanger of the present invention.
Fig. 3 is a schematic structural view of the spiral heat exchange tube of the present invention.
Fig. 4 is a schematic structural view of the direct heat exchange tube of the present invention.
Fig. 5 is a schematic view of the structure of the spiral baffle of the present invention.
Fig. 6 is a schematic structural view of the upper half shell of the present invention.
Fig. 7 is a schematic structural view of the lower half shell of the present invention.
Fig. 8 is a schematic structural view of the straight tube fixing plate of the present invention.
Fig. 9 is a schematic structural view of the coil fixing plate of the present invention.
Fig. 10 is a perspective view of the straight heat exchange tube of embodiment 1.
Fig. 11 is a perspective view of the straight heat exchange tube of embodiment 2.
Fig. 12 is a perspective view of the straight heat exchange tube of embodiment 3.
Fig. 13 is a schematic view of the clip assembly of the present invention.
Wherein, 1 is the casing, 2 is the spiral heat exchange tube, 3 is the straight heat exchange tube, 4 is the straight heat flow input port, 5 is the straight heat flow output port, 6 is the cold flow output port, 7 is the cold flow input port, 8 is the spiral heat flow input port, 9 is the spiral heat flow output port, 10 is the spiral guide plate, 11 is the vortex piece, 12 is the clamp subassembly, 13 is the snap ring, 14 is the bolt, 15 is the straight tube fixed plate, 16 is the spiral pipe fixed plate, 17 is the first half casing, 18 is the second half casing.
Detailed Description
The invention is further described below with reference to the drawings and examples.
Example 1
The spherical heat exchanger with double tube-pass independent heat exchange as shown in fig. 1 to 5 comprises a spherical shell, a spiral heat exchange tube and a direct heat exchange tube, wherein the upper end and the lower end of the shell are respectively provided with a direct heat flow input port and a direct heat flow output port, and the two ends of the direct heat exchange tube are respectively connected with the direct heat flow input port and the direct heat flow output port; the upper end of the shell is provided with a cold flow output port and a spiral heat flow input port, the cold flow output port and the spiral heat flow input port are respectively positioned at two sides of the direct-current heat input port, the lower end of the shell is provided with a cold flow input port and a spiral heat flow output port, and the cold flow input port and the spiral heat flow output port are respectively positioned at two sides of the direct-current heat flow output port; the spiral heat exchange tube is sleeved on the direct heat exchange tube, and two ends of the spiral heat exchange tube are respectively connected with the spiral heat flow input port and the spiral heat flow output port; the cold flow output port and the cold flow input port are both communicated with the inner cavity of the shell; the inner cavity of the shell is provided with a spiral guide plate, and the cold flow input port and the cold flow output port are communicated through the inner cavity of the shell. Specifically, the direct heat exchange tube forms a direct tube pass, and the spiral heat exchange tube forms a spiral tube pass, that is, the spherical heat exchanger in the embodiment adopts double tube pass heat exchange, and the direct tube pass and the spiral tube pass are mutually independent. The shell side of the spherical heat exchanger in the embodiment is formed by the inner cavity of the shell and the spiral guide plate, wherein the spiral guide plate is a continuous plate, and the shell side is also spiral. Therefore, the spherical heat exchanger in the embodiment is provided with the spiral tube pass and the spiral shell pass, so that the turbulence of the fluid can be improved, the time of the fluid in the shell pass can be prolonged, the heat exchange efficiency can be improved, and the heat exchange effect can be enhanced. In order to ensure the installation stability of the straight heat exchange tube and the spiral heat exchange tube, as shown in fig. 2, 4 and 8, straight tube fixing plates are arranged at the straight heat flow input port and the straight heat flow output port, and two ends of the straight heat exchange tube are fixedly connected with the corresponding straight tube fixing plates respectively. As shown in fig. 3 and 9, spiral pipe fixing plates are arranged at the spiral heat flow output port and the spiral heat flow input port, and two ends of the spiral heat exchange pipe are respectively connected with the corresponding spiral pipe fixing plates.
The spiral diameter of the spiral heat exchange tube is gradually reduced from the middle part of the spiral heat exchange tube to the two ends. The pipe diameter of the spiral heat exchange pipe is gradually reduced from the middle part of the spiral heat exchange pipe to the two ends. The spiral diameter and the pipe diameter of the spiral heat exchange pipe are of gradual change structures, so that the time of hot fluid in the spiral tube side can be further prolonged, and the heat exchange efficiency is further improved.
The spiral heat exchange tubes are provided with a plurality of spiral heat exchange tubes, each spiral heat exchange tube is arranged in parallel, and a space is reserved between every two adjacent spiral heat exchange tubes. The straight heat exchange tubes are arranged in parallel, and a space is reserved between every two adjacent straight heat exchange tubes. The spiral heat exchange tubes and the direct heat exchange tubes are not contacted with each other, so that the hot fluid in the corresponding spiral heat exchange tubes and the direct heat exchange tubes are not affected with each other, and the heat exchange efficiency of the hot fluid in the tube pass and the cold fluid in the shell pass is ensured.
And a turbulence piece is inserted into the straight heat exchange tube. The turbulence piece is any one of a torsion belt, a spiral coil, a spiral sheet and a static mixer. As shown in fig. 10, the spoiler in the present embodiment employs a spiral coil. The structure can make the heat fluid rotate in the direct heat exchange tube and cause secondary circulation, thereby strengthening heat transfer and having the function of descaling.
The shell is of a double-layer steel structure, and a high-temperature-resistant heat insulation material is filled between the two layers of steel in the shell. Specifically, the heat conductivity coefficient of the high-temperature-resistant heat insulation material is 0.5-0.8W/(m) 2 K) specifically, one of porous heat insulating materials such as microporous calcium silicate, fibrous materials such as rock wool, and granular heat insulating materials such as expanded perlite can be used. The double-layer steel structure and the high-temperature-resistant heat insulation material can enable the shell to have good heat insulation effect, avoid heat loss and save manufacturing cost.
The shell comprises an upper half shell and a lower half shell, and the upper half shell is fixedly connected with the lower half shell through a clamp assembly. As shown in fig. 2, 6 and 7, after the upper half shell and the lower half shell are well butted, the butted part between the upper half shell and the lower half shell is locked and fixed through the clamp assembly. As shown in fig. 13, and the clip assembly is comprised of a snap ring and a bolt. The structure is simple, and the installation is convenient.
The width of the spiral guide plate gradually becomes smaller from the middle part of the spiral guide plate to the two ends. A gap is formed between the outer edge of the spiral guide plate and the inner wall of the shell, and the size of the gap is 0.2mm. The spiral guide plate also adopts a gradual change structure, so that the fit degree of the spiral guide plate and the shell is higher, cold fluid flows along the continuous spiral guide plate to form spiral fluid, the turbulence degree is further improved, and the heat exchange efficiency is improved.
Specifically, in this embodiment, the following parameters are adopted for each component in the spherical heat exchanger:
the specific working process of the spherical device with the double pipelines for independent heat exchange is as follows:
the heat fluid is respectively input from the spiral heat flow input port and the straight pipe heat flow input port, and the flows of the heat fluid in the spiral heat exchange pipe and the straight heat exchange pipe are mutually independent and mutually noninterfere. Simultaneously, cold fluid is input from a cold fluid input port, flows in a spiral line on a shell side formed by the shell and the spiral guide plate under the guide action of the continuous spiral guide plate, and the flowing direction of the cold fluid and the flowing direction of the hot fluid are opposite, namely the cold fluid and the hot fluid form countercurrent. The heat exchange is carried out between the hot fluid and the cold fluid through the pipe walls of the respective heat exchange pipes (spiral heat exchange pipes or straight heat exchange pipes). The heat-exchanged hot fluid is discharged from the spiral hot fluid outlet and the straight pipe hot fluid outlet respectively, and the cold fluid is discharged from the cold fluid outlet.
In the process of heat exchange between the hot fluid and the cold fluid, the spherical shell is filled with the high-temperature-resistant heat insulation material between the double-layer stainless steel, so that unnecessary heat loss in the heat exchange process is effectively reduced. When the hot fluid flows in the spiral heat exchange pipeline with the variable diameter, secondary circulation perpendicular to the main flow direction can be generated due to the action of centrifugal force, so that disturbance of a boundary layer in the pipe is enhanced, and a turbulence effect is generated; when the straight pipe heat exchange pipeline flows, the fluid is rotated by the insert in the straight pipe to cause secondary flow, so that radial mixing is promoted, and heat transfer is enhanced. Simultaneously, cold fluid flows in a spiral line, so that the turbulence of a stagnant layer on a heat transfer interface of the fluid is promoted. The above processes all make the fluid raise the flow velocity, eliminate dead zone and avoid the generation of sediment. Because the spiral heat exchange tube and the straight heat exchange tube are mutually independent and the heat exchange process and the heat exchange effect are different, when the input heat fluid is of the same type, the heat fluid with different temperatures is respectively obtained at the spiral tube heat flow output port and the straight tube heat flow output port; when different hot fluids are input, the two hot fluids exchange heat simultaneously without affecting each other. Therefore, different heat exchange modes can be adopted in industry according to different requirements. Compared with the traditional heat exchange process, the heat exchange process reduces heat loss by 55%, prolongs the heat exchange time by 2 times, improves the heat transfer coefficient by 5 times, improves the pressure endurance capacity by 2 times, reduces the consumption of steel by 35% and saves the space by 50%.
Example 2
The bulb with double pipelines for independent heat exchange is the same as in example 1 except the following technical characteristics: and a turbulence piece is inserted into the straight heat exchange tube. As shown in fig. 11, the turbulence member is a spiral piece. The spiral sheets and the spiral coils have the same effect, and can also enable the hot fluid to generate secondary circulation in the direct heat exchange tube, so that the heat exchange efficiency is improved.
Example 3
The bulb with double pipelines for independent heat exchange is the same as in example 1 except the following technical characteristics: and a turbulence piece is inserted into the straight heat exchange tube. As shown in fig. 12, the turbulence member is a static mixer. The static mixer and the spiral coil have the same effect, and can also enable the hot fluid to generate secondary circulation in the direct heat exchange tube, thereby improving the heat exchange efficiency.
The above embodiments are preferred examples of the present invention, and the present invention is not limited thereto, and any other modifications or equivalent substitutions made without departing from the technical aspects of the present invention are included in the scope of the present invention.
Claims (8)
1. The utility model provides a spherical heat exchanger of independent heat transfer of double-barrelled journey which characterized in that: the heat exchange device comprises a spherical shell, a spiral heat exchange tube and a direct heat exchange tube, wherein the upper end and the lower end of the shell are respectively provided with a direct heat flow input port and a direct heat flow output port, and the two ends of the direct heat exchange tube are respectively connected with the direct heat flow input port and the direct heat flow output port; the upper end of the shell is provided with a cold flow output port and a spiral heat flow input port, the cold flow output port and the spiral heat flow input port are respectively positioned at two sides of the direct-current heat input port, the lower end of the shell is provided with a cold flow input port and a spiral heat flow output port, and the cold flow input port and the spiral heat flow output port are respectively positioned at two sides of the direct-current heat flow output port; the spiral heat exchange tube is sleeved on the direct heat exchange tube, and two ends of the spiral heat exchange tube are respectively connected with the spiral heat flow input port and the spiral heat flow output port; the cold flow output port and the cold flow input port are both communicated with the inner cavity of the shell; the inner cavity of the shell is provided with a spiral guide plate, the cold flow input port and the cold flow output port are communicated through the inner cavity of the shell, the spiral diameter of the spiral heat exchange tube gradually becomes smaller from the middle part of the spiral heat exchange tube to two ends, the spiral heat exchange tube is provided with a plurality of spiral heat exchange tubes, each spiral heat exchange tube is arranged in parallel, and a space is reserved between every two adjacent spiral heat exchange tubes.
2. The dual tube independent heat exchanging spherical heat exchanger according to claim 1, wherein: the pipe diameter of the spiral heat exchange pipe is gradually reduced from the middle part of the spiral heat exchange pipe to the two ends.
3. The dual tube independent heat exchanging spherical heat exchanger according to claim 1, wherein: and a turbulence piece is inserted into the straight heat exchange tube.
4. A dual tube independent heat exchanging spherical heat exchanger according to claim 3, wherein: the turbulence piece is any one of a torsion belt, a spiral coil, a spiral sheet and a static mixer.
5. The dual tube independent heat exchanging spherical heat exchanger according to claim 1, wherein: the straight heat exchange tubes are arranged in parallel, and a space is reserved between every two adjacent straight heat exchange tubes.
6. The dual tube independent heat exchanging spherical heat exchanger according to claim 1, wherein: the shell is of a double-layer steel structure, and a high-temperature-resistant heat insulation material is filled between the two layers of steel in the shell.
7. The dual tube independent heat exchanging spherical heat exchanger according to claim 1, wherein: the shell comprises an upper half shell and a lower half shell, and the upper half shell is fixedly connected with the lower half shell through a clamp assembly.
8. The dual tube independent heat exchanging spherical heat exchanger according to claim 1, wherein: the width of the spiral guide plate is gradually reduced from the middle part of the spiral guide plate to the two ends; and a gap is arranged between the outer edge of the spiral guide plate and the inner wall of the shell, and the size of the gap is 0.2 mm-0.5 mm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811455407.8A CN109405589B (en) | 2018-11-30 | 2018-11-30 | Spherical heat exchanger with double tube-pass independent heat exchange |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811455407.8A CN109405589B (en) | 2018-11-30 | 2018-11-30 | Spherical heat exchanger with double tube-pass independent heat exchange |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109405589A CN109405589A (en) | 2019-03-01 |
| CN109405589B true CN109405589B (en) | 2023-10-27 |
Family
ID=65456629
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201811455407.8A Active CN109405589B (en) | 2018-11-30 | 2018-11-30 | Spherical heat exchanger with double tube-pass independent heat exchange |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN109405589B (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110057084A (en) * | 2019-03-26 | 2019-07-26 | 淮南市知产创新技术研究有限公司 | A kind of multiple branch heat exchange device for air and heat change method |
| CN111779550B (en) * | 2020-06-19 | 2023-03-24 | 武汉第二船舶设计研究所(中国船舶重工集团公司第七一九研究所) | Regulating device for supercritical carbon dioxide turbine |
| CN113432454B (en) * | 2021-07-14 | 2022-12-06 | 哈尔滨锅炉厂有限责任公司 | Non-circular cross-section double-tube-pass spiral heat exchanger tube bundle structure |
| CN114353556B (en) * | 2021-12-31 | 2024-03-01 | 无锡市张华医药设备有限公司 | Large-scale belt-wound spiral micro-channel heat exchanger and brazing process thereof |
| CN114636326B (en) * | 2022-03-10 | 2023-11-21 | 南京理工大学 | Wheel-like efficient heat exchanger |
| CN114705063B (en) * | 2022-03-29 | 2024-04-02 | 张家港氢云新能源研究院有限公司 | High-efficiency heat exchange vaporizer |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1492520A (en) * | 1975-04-16 | 1977-11-23 | Daido Steel Co Ltd | Heat exchanger for industrial furnaces |
| EP0080161A2 (en) * | 1981-11-19 | 1983-06-01 | Kioteru Takayasu | Heat exchanger |
| JPH07280468A (en) * | 1994-04-11 | 1995-10-27 | Suzuki Motor Corp | Water-cooled oil cooler |
| CN201637310U (en) * | 2010-03-05 | 2010-11-17 | 赛普斯天宇试验设备(成都)有限责任公司 | Drum-type heat exchanger with liquid storage function |
| CN102538507A (en) * | 2010-12-15 | 2012-07-04 | 太仓南极风能源设备有限公司 | Heat exchanger for fluidizing type water heater |
| CN102538562A (en) * | 2012-02-17 | 2012-07-04 | 西安交通大学 | Shell-and-tube heat exchanger with combined type one-shell-pass continuous spiral baffles |
| CN203100489U (en) * | 2012-12-12 | 2013-07-31 | 刘精华 | Tank type heat exchanger with synchronous spiral flow deflector |
| CN105823348A (en) * | 2016-05-19 | 2016-08-03 | 郑州大学 | Double-flow mixed tube bundle shell and tube heat exchanger |
| CN209279723U (en) * | 2018-11-30 | 2019-08-20 | 华南理工大学 | A kind of spherical heat exchanger with Dual heat exchange effect |
-
2018
- 2018-11-30 CN CN201811455407.8A patent/CN109405589B/en active Active
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1492520A (en) * | 1975-04-16 | 1977-11-23 | Daido Steel Co Ltd | Heat exchanger for industrial furnaces |
| EP0080161A2 (en) * | 1981-11-19 | 1983-06-01 | Kioteru Takayasu | Heat exchanger |
| JPH07280468A (en) * | 1994-04-11 | 1995-10-27 | Suzuki Motor Corp | Water-cooled oil cooler |
| CN201637310U (en) * | 2010-03-05 | 2010-11-17 | 赛普斯天宇试验设备(成都)有限责任公司 | Drum-type heat exchanger with liquid storage function |
| CN102538507A (en) * | 2010-12-15 | 2012-07-04 | 太仓南极风能源设备有限公司 | Heat exchanger for fluidizing type water heater |
| CN102538562A (en) * | 2012-02-17 | 2012-07-04 | 西安交通大学 | Shell-and-tube heat exchanger with combined type one-shell-pass continuous spiral baffles |
| CN203100489U (en) * | 2012-12-12 | 2013-07-31 | 刘精华 | Tank type heat exchanger with synchronous spiral flow deflector |
| CN105823348A (en) * | 2016-05-19 | 2016-08-03 | 郑州大学 | Double-flow mixed tube bundle shell and tube heat exchanger |
| CN209279723U (en) * | 2018-11-30 | 2019-08-20 | 华南理工大学 | A kind of spherical heat exchanger with Dual heat exchange effect |
Also Published As
| Publication number | Publication date |
|---|---|
| CN109405589A (en) | 2019-03-01 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN109405589B (en) | Spherical heat exchanger with double tube-pass independent heat exchange | |
| WO2017101235A1 (en) | Enhanced high-efficiency spiral tube heat exchanger | |
| CN101349514B (en) | Internal and external fins intubatton type high temperature heat exchanger | |
| CN102620587B (en) | Tube shell type pulsating heat pipe heat exchanger | |
| CN102278907B (en) | External-convex-type asymmetrical wave node pipe heat exchanger | |
| CN103047882A (en) | Deflecting fence type square heat exchanger with waved tube | |
| CN103411454A (en) | Tube type heat exchanger with outer-protruding-type corrugated tubes arranged in staggering mode | |
| CN101033922B (en) | Pipeline type micro-channels heat exchanger | |
| CN104913663A (en) | Tube shell pass volume-adjustable longitudinal turbulence oil cooler | |
| CN103017570A (en) | Self-support type heat exchanger with micro wavy tubes and straight tubes mixedly arranged | |
| CN104197760A (en) | Pipeline type pulse heat pipe heat exchanger | |
| CN103743269A (en) | Non-isometric double-spiral baffle-plate tube shell heat exchanger | |
| CN101726195B (en) | Stainless steel finned tube heat exchanger for residual heat recovery | |
| CN203893704U (en) | Non-isometric dual helical baffle plate tubular heat exchanger | |
| CN105202950A (en) | Shell-and-tube type heat exchanger | |
| CN202216587U (en) | Heat exchanger adopting oval flat spiral heat exchange tube | |
| CN207797806U (en) | A kind of special pipe wing heat exchanger | |
| RU2386096C2 (en) | Honeycomb heat exchanger with flow swirling | |
| CN209279723U (en) | A kind of spherical heat exchanger with Dual heat exchange effect | |
| CN109612312B (en) | Spherical heat exchanger with wave-shaped plate lantern structure | |
| CN206974246U (en) | A kind of tubular heat exchange device | |
| CN105698583A (en) | Novel heat exchange tube | |
| CN216482406U (en) | Heat exchanger and air conditioning unit | |
| CN202614040U (en) | Needle wing sleeve type strengthening heat transfer element | |
| CN107246813A (en) | Tubular heat exchange device |
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 | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |