CN111059928A - Pure countercurrent modular combined heat exchanger - Google Patents
Pure countercurrent modular combined heat exchanger Download PDFInfo
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- CN111059928A CN111059928A CN201811204148.1A CN201811204148A CN111059928A CN 111059928 A CN111059928 A CN 111059928A CN 201811204148 A CN201811204148 A CN 201811204148A CN 111059928 A CN111059928 A CN 111059928A
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- UGFAIRIUMAVXCW-UHFFFAOYSA-N Carbon monoxide Chemical compound [O+]#[C-] UGFAIRIUMAVXCW-UHFFFAOYSA-N 0.000 claims description 31
- 239000003546 flue gas Substances 0.000 claims description 31
- 238000007667 floating Methods 0.000 claims description 5
- 229910000831 Steel Inorganic materials 0.000 claims description 4
- 239000010959 steel Substances 0.000 claims description 4
- 230000000087 stabilizing effect Effects 0.000 claims description 3
- 239000000428 dust Substances 0.000 abstract description 16
- 239000000779 smoke Substances 0.000 abstract description 9
- 238000005299 abrasion Methods 0.000 description 15
- 239000012530 fluid Substances 0.000 description 15
- 230000008602 contraction Effects 0.000 description 13
- 238000013461 design Methods 0.000 description 8
- 238000009991 scouring Methods 0.000 description 8
- 238000012546 transfer Methods 0.000 description 8
- 230000008021 deposition Effects 0.000 description 6
- 239000007789 gas Substances 0.000 description 5
- 238000009825 accumulation Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 239000002918 waste heat Substances 0.000 description 4
- 230000009286 beneficial effect Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 230000002349 favourable effect Effects 0.000 description 3
- 239000007788 liquid Substances 0.000 description 3
- 238000012545 processing Methods 0.000 description 3
- 238000011084 recovery Methods 0.000 description 3
- 230000003111 delayed effect Effects 0.000 description 2
- 238000005265 energy consumption Methods 0.000 description 2
- 230000002035 prolonged effect Effects 0.000 description 2
- 239000010865 sewage Substances 0.000 description 2
- 230000008646 thermal stress Effects 0.000 description 2
- 229910000746 Structural steel Inorganic materials 0.000 description 1
- 230000002238 attenuated effect Effects 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 230000001680 brushing effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000003303 reheating Methods 0.000 description 1
- 230000002787 reinforcement Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
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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
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
本发明公开了一种纯逆流模块式组合换热器，换热器采用立式或卧式方烟道管布置，包括蒸汽入口母管、入口大联箱、出口大联箱、入口小联箱、出口小联箱、若干组组合式布置的换热管组、蒸汽出口母管、收缩入口段筒体、扩张出口段筒体以及稳流直段筒体；换热管组由多根高比表面换热管组成；收缩入口段筒体与扩张出口段筒体分别设置在稳流直段筒体的两端；入口小联箱位于扩张出口段筒体内，出口小联箱位于收缩入口段筒体内；蒸汽入口母管与入口大联箱相接，蒸汽出口母管与出口大联箱相接。本换热器的体积小，且运行阻力更低；当采用立式布置时，完全可以避免烟尘堵塞现象；采用多组分别并行控制，实现负荷灵活调节。
The invention discloses a pure countercurrent modular combined heat exchanger. The heat exchanger adopts a vertical or horizontal square flue pipe arrangement, and includes a steam inlet main pipe, an inlet large header, an outlet large header and an inlet small header. , outlet small header, several groups of combined heat exchange tube groups, steam outlet main pipes, shrinking inlet section cylinders, expanding outlet section cylinders and steady flow straight section cylinders; It consists of surface heat exchange tubes; the cylinder body of the shrinking inlet section and the cylinder body of the expanding outlet section are respectively arranged at the two ends of the cylinder body of the steady flow straight section; Inside the body; the steam inlet main pipe is connected with the inlet large header, and the steam outlet main pipe is connected with the outlet large header. The heat exchanger is small in size and has lower operating resistance; when it is arranged vertically, the phenomenon of smoke and dust clogging can be completely avoided; multiple groups of parallel control are used to realize flexible load adjustment.
Description
Technical Field
The invention relates to the technical field of energy conservation and environmental protection, in particular to a pure countercurrent modular combined heat exchanger.
Background
The flue gas waste heat recovery heat exchange equipment is widely applied in China at present. Most of traditional flue type waste heat boilers or heat exchange equipment adopt a coiled pipe heat exchanger structure, flue gas transversely erodes the heat exchange pipe, and in order to enhance the heat exchange effect, a finned pipe structure is generally adopted in flue gas/steam heat exchange or flue gas/water heat exchange occasions. But is limited by the requirements of resistance drop on the smoke side and the problem of abrasion of the heat exchange tube, and the flow velocity of smoke transversely brushing the tube is generally controlled within 10 m/s; the finned tube is easily affected by dust deposition and scaling, and the heat exchange performance of the heat exchanger is greatly attenuated in the application process; even in some occasions with higher dust content, only the light tube with poorer heat exchange performance can be adopted for heat exchange, so the equipment becomes huge and the metal consumption is high; the limitations greatly reduce the cost performance of the flue type heat exchanger and influence the application of the waste heat recovery technology.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provides a pure countercurrent modular combined heat exchanger, which is described by taking flue gas reheating steam as an example for convenience in description.
The invention is realized by the following technical scheme: a pure countercurrent modular combined heat exchanger adopts vertical or horizontal square flue pipe arrangement and comprises a steam inlet main pipe, a large header, a small header, a plurality of groups of heat exchange pipe sets arranged in a combined mode, a steam outlet main pipe, a contraction inlet section cylinder, an expansion outlet section cylinder and a steady flow straight section cylinder; the heat exchange tube group consists of a plurality of heat exchange tubes with high specific surface; the contraction inlet section cylinder and the expansion outlet section cylinder are respectively arranged at two ends of the steady flow straight section cylinder to form heat exchange cylinders, and the heat exchange tube group is positioned in the heat exchange cylinders; the large header comprises an inlet large header and an outlet large header, and the small header comprises an inlet small header and an outlet small header; the inlet of each heat exchange tube group is provided with the small inlet header, and the small inlet headers are connected to the large inlet header in parallel; the outlet of each heat exchange tube group is provided with the small outlet header, and the small outlet headers are connected to the large outlet header in parallel; the small inlet header is positioned in the expansion outlet section cylinder, and the small outlet header is positioned in the contraction inlet section cylinder; the small inlet header and the large inlet header are connected outside the expansion outlet section cylinder, and the small outlet header and the large outlet header are connected outside the contraction inlet section cylinder; the steam inlet main pipe is connected with the inlet large header, and the steam outlet main pipe is connected with the outlet large header; a smoke channel of the heat exchanger flows in from a smoke inlet at the top end of the heat exchanger and the inner circumference of the cylinder of the contraction inlet section in the circumferential direction, and flows out of the heat exchanger through the cylinder of the expansion outlet section after the steady flow straight section cylinder releases heat; the reheated steam enters the large inlet header from the steam inlet main pipe, sequentially passes through the small inlet headers of the heat exchange tube sets, enters the heat exchange tube sets for heat exchange, then converges to the large outlet header through the small outlet headers, and flows out of the heat exchanger from the steam outlet main pipe; and the top of the small outlet header facing the inlet of the flue gas channel is provided with anti-abrasion angle steel or an anti-abrasion tile.
The heat exchanger adopts pure countercurrent arrangement of flue gas and steam, can obtain the maximum heat exchange temperature difference, is favorable for reducing the heat exchange area under the condition of reaching the same heat exchange quantity, and can also obtain the lowest flue gas outflow temperature in some application occasions, thereby recovering the heat of the flue gas to the maximum extent and reducing the energy consumption of a system; the heat exchange tubes are connected in parallel, and the resistance per unit flow is far smaller than that of transverse scouring, so that fluid outside the heat exchange element can bear higher flow velocity, and the coefficient of a heat transfer film outside the tubes (or called tube shell side) is improved; the heat exchanger adopts a modular combined structure design, and can well adapt to different load requirements; the arrangement of the anti-abrasion angle steel or the anti-abrasion tile can reduce the transverse scouring abrasion of the inlet flue gas to the small outlet header; the heat exchange tube with high specific surface has good heat transfer enhancement effect, reduces pressure drop while ensuring gas flow velocity, and has stronger anti-scaling capability.
The heat exchange tubes of the heat exchange tube set adopt spiral twisted offset tubes with high specific surface area, external longitudinal straight ribbed tubes or internal longitudinal straight ribbed tubes. The use of the high specific surface spiral twisted flat tube can strengthen the heat exchange: (1) because the fluid in the pipe spirally rises and flows, the turbulence degree of the fluid can be enhanced, and the thickness of a fluid boundary layer is reduced, so that the coefficient of a heat transfer film in the pipe can be improved to achieve the purpose of heat exchange enhancement; (2) the specific surface area of unit tube volume is improved; (3) the fluid outside the pipe spirally flows downwards, so that the coefficient of a heat transfer film outside the pipe is improved, meanwhile, the scouring abrasion of dust-containing smoke is avoided, the pipe wall abrasion is greatly delayed, and the service life of the heat exchange pipe is prolonged; (4) the spiral downward streaming of the fluid outside the tube also greatly reduces the possibility of avoiding dust accumulation and scaling, and due to the parallel flow design, the designed flow speed is higher than that of the transverse scouring, the dust raising and carrying capacity of the flue gas is greatly improved, and the deposition of the smoke dust on the outer wall surface of the heat exchange tube is avoided; the external longitudinal straight rib pipe or the internal longitudinal straight rib pipe can increase the contact area and fully realize heat exchange.
Each group of heat exchange tube sets are arranged in the same way, the cross section of a heat exchanger formed by the heat exchange tube sets is rectangular, and the tube spacing is triangular or rectangular. The same-form arrangement can ensure that the fluid on the inner side of the tube is uniformly distributed, and the combined module structure is beneficial to adjusting the heat exchanger structure according to the size of heat exchange load, so that the rapid design and the convenient processing and assembly are realized.
The heat exchanger is of a rectangular column structure, and the length-diameter ratio of the heat exchanger is greater than or equal to 2.0. The heat exchange tube group with the rectangular cylinder structure has better steady flow heat exchange performance, and the long and thin structure and the square cross section are favorable for the spatial arrangement of the field heat exchanger.
And a hollow ring fixing structure used for stabilizing the heat exchange tubes is arranged between the heat exchange tubes. When the single tube side of the heat exchange tube is long, the hollow ring fixing structure is arranged between the heat exchange tubes, so that the vibration under high flow velocity can be avoided, and the hollow ring can reduce the influence of the fixing structure on the resistance of the outer side (or called tube shell side) of the tube to the maximum extent.
The cylinder body at the contraction inlet section adopts a gradually-reduced structure, and the diameter of the cylinder body is gradually reduced from the inlet of the cylinder body to the direction of the steady flow straight section cylinder body; the expansion outlet section cylinder body adopts a gradually expanding structure, and the diameter of the steady flow straight section cylinder body is gradually expanded towards the outlet direction of the steady flow straight section cylinder body. The contraction inlet section cylinder body of the reducing structure and the expansion outlet section cylinder body of the gradually expanding structure can reduce the inlet and outlet resistance to the maximum extent and reduce the wall surface abrasion of the inlet and outlet section heat exchange tubes when high-speed flue gas enters and exits the heat exchanger.
The steam inlet main pipe adopts a fixed pipe plate structure, and the steam outlet main pipe adopts a floating structure. The steam outlet main pipe with a floating structure can meet the requirement of thermal stress release.
The external longitudinal straight ribbed tube adopts an external finned tube.
The lowest position of the heat exchanger is provided with a sewage draining outlet, and the highest position of the heat exchanger is provided with an exhaust port.
Compared with the prior art, the invention has the advantages that: compared with the traditional flue gas waste heat recovery heat exchange equipment, the volume of the heat exchanger is reduced by more than 40%, and the running resistance is lower; when the vertical arrangement (namely, the vertical arrangement) is adopted, the smoke blocking phenomenon can be completely avoided; a plurality of groups of the devices are respectively controlled in parallel, so that flexible load adjustment is realized; the combination of multiple tube groups and pure countercurrent arrangement are adopted, the maximum heat exchange temperature difference and longitudinal high-speed flow are realized, the comprehensive heat exchange performance is improved, and the possibility of dust accumulation and scale deposition of the heat exchange tubes is effectively reduced; .
Drawings
FIG. 1 is a schematic structural diagram of a front view direction according to an embodiment of the present invention;
FIG. 2 is a schematic side view of an embodiment of the present invention;
FIG. 3 is a schematic view of a local flow field of a prior art round tube;
FIG. 4 is a schematic view of a local flow field of a spirally twisted offset pipe with a high specific surface area according to an embodiment of the present invention;
FIG. 5 is a schematic structural diagram of a spiral twisted deflection pipe with a high specific surface area according to an embodiment of the present invention;
FIG. 6 is a schematic structural diagram of an exemplary finned tube;
FIG. 7 is a schematic structural view of a tube with built-in longitudinal straight ribs according to an embodiment of the present invention.
The reference numerals in the drawings mean: 1. a steam inlet header; 21. an inlet large header; 22. an outlet large header; 31. an inlet small header; 32. an outlet small header; 4. a heat exchange pipe; 5. a heat exchange tube set; 6. wear-resistant tiles; 7. a steam outlet main pipe; 8. contracting the inlet section cylinder; 9. a steady flow straight barrel; 10. expanding the outlet section cylinder.
Detailed Description
The present invention will be described in further detail with reference to the accompanying drawings and detailed description.
Examples
Referring to fig. 1, 2 and 4 to 7, the pure countercurrent modular combined heat exchanger adopts a vertical or horizontal square flue pipe arrangement, and comprises a steam inlet main pipe 1, a large header, a small header, a plurality of groups of heat exchange pipe groups 5 arranged in a combined manner, a steam outlet main pipe 7, a contraction inlet section cylinder 8, an expansion outlet section cylinder 10 and a steady flow straight section cylinder 9; the heat exchange tube set 5 consists of a plurality of high specific surface heat exchange tube sets 5; the contraction inlet section cylinder 8 and the expansion outlet section cylinder 10 are respectively arranged at two ends of the steady flow straight section cylinder 9 to form heat exchange cylinders, and the heat exchange tube group 5 is positioned in the heat exchange cylinders; the large header comprises an inlet large header 21 and an outlet large header 22, and the small header comprises an inlet small header 31 and an outlet small header 32; the inlet of each heat exchange tube set 5 is provided with a small inlet header 31, and a plurality of small inlet headers 31 are connected in parallel to the large inlet header 21; the outlet of each heat exchange tube group 5 is provided with a small outlet header 32, and a plurality of small outlet headers 32 are connected to the large outlet header 22 in parallel; the small inlet header 31 is positioned in the expanded outlet section cylinder 10, and the small outlet header 32 is positioned in the contracted inlet section cylinder 8; the small inlet header 31 and the large inlet header 21 are connected outside the expanded outlet section cylinder 10, and the small outlet header 32 and the large outlet header 22 are connected outside the contracted inlet section cylinder 8; the steam inlet main pipe 1 is connected with the inlet large header 21, and the steam outlet main pipe 7 is connected with the outlet large header 22; a flue gas channel of the heat exchanger flows in from the flue gas inlet at the top end of the heat exchanger and the inner circumference of the cylinder 8 at the contraction inlet section, and flows out of the heat exchanger through the cylinder 10 at the expansion outlet section after heat is released by the steady flow straight section cylinder 9; the reheated steam enters the inlet large header 21 from the steam inlet main pipe 1, sequentially passes through the inlet small headers 31 of each heat exchange tube set 5, enters the heat exchange tube sets 5 for heat exchange, then converges to the outlet large header 22 through the outlet small headers 32, and flows out of the heat exchanger from the steam outlet main pipe 7; the top of the small outlet header 32 facing the inlet of the flue gas channel is provided with an anti-wear angle iron or an anti-wear tile 6. The arrows in the filling diagram in fig. 1 indicate the flow direction of the flue gas, and the solid arrows in fig. 2 indicate the flow direction of the steam.
The heat exchanger adopts pure countercurrent arrangement of flue gas and steam, can obtain the maximum heat exchange temperature difference, is favorable for reducing the heat exchange area under the condition of reaching the same heat exchange quantity, and can also obtain the lowest flue gas outflow temperature in some application occasions, thereby recovering the heat of the flue gas to the maximum extent and reducing the energy consumption of a system; the heat exchange tubes 4 are connected in parallel, and the resistance per unit flow is far smaller than that of transverse scouring, so that fluid outside the heat exchange element can bear higher flow velocity, and the coefficient of a heat transfer film outside the tubes (or called tube shell side, namely the tube shell side in a tube shell type heat exchanger) is favorably improved; the heat exchanger adopts a modular combined structure design, and can well adapt to different load requirements; the arrangement of the anti-abrasion angle steel or the anti-abrasion tile 6 can reduce the transverse scouring abrasion of the inlet flue gas to the small outlet header 32; the heat exchange tube 4 with high specific surface has good heat transfer enhancement effect, reduces pressure drop while ensuring gas flow velocity, and has strong anti-scaling capability.
The heat exchange tubes 4 of the heat exchange tube group 5 adopt high specific surface spiral twisted offset tubes, external longitudinal straight ribbed tubes or internal longitudinal straight ribbed tubes. The three types of high specific surface spiral twisted inclined tubes, external longitudinal straight ribbed tubes or internal longitudinal straight ribbed tubes are high specific surface reinforced heat exchange tubes, the high specific surface tubes are one of the main measures for heat exchange reinforcement of the heat exchange tubes, and the three types of tubes suitable for the heat exchanger are selected. The use of the high specific surface spiral twisted flat tube can strengthen the heat exchange: (1) because the fluid in the pipe spirally rises and flows, the turbulence degree of the fluid can be enhanced, and the thickness of a fluid boundary layer is reduced, so that the coefficient of a heat transfer film in the pipe can be improved to achieve the purpose of heat exchange enhancement; (2) the specific surface area of unit tube volume is improved; (3) the fluid outside the pipe spirally flows downwards, so that the coefficient of a heat transfer film outside the pipe is improved, meanwhile, the scouring abrasion of dust-containing smoke is avoided, the pipe wall abrasion is greatly delayed, and the service life of the heat exchange pipe 4 is prolonged; (4) the spiral downward streaming of the fluid outside the pipe also greatly reduces the possibility of avoiding dust accumulation and scaling, and due to the parallel flow design, the designed flow speed is higher than that of the transverse scouring, the dust raising and carrying capacity of the flue gas is greatly improved, and the dust is prevented from being deposited; the external longitudinal straight rib pipe or the internal longitudinal straight rib pipe can increase the contact area and fully realize heat exchange.
Each group of heat exchange tube sets 5 are arranged in the same way, the cross section of the heat exchanger formed by the plurality of groups of heat exchange tube sets 5 is rectangular, and the tube spacing is triangular or rectangular. The same-form arrangement can ensure that the fluid on the inner side of the tube is uniformly distributed, and the combined module structure is beneficial to adjusting the heat exchanger structure according to the size of heat exchange load, so that the rapid design and the convenient processing and assembly are realized.
The heat exchanger is a rectangular column structure, and the length-diameter ratio of the heat exchanger is greater than or equal to 2.0. The heat exchange tube group 5 with the rectangular cylinder structure has better steady flow heat exchange performance, and the long and thin structure and the square section are beneficial to the spatial arrangement of the field heat exchanger.
A hollow ring fixing structure for stabilizing the heat exchange tubes 4 is arranged between the heat exchange tubes 4. When the heat exchange tubes 4 are long in single tube pass, a hollow ring fixing structure is arranged between the heat exchange tubes 4, vibration under high flow velocity can be avoided, and the hollow ring can reduce the influence of the fixing structure on resistance of the outer sides of the tubes (or called tube shell sides) to the maximum extent.
The cylinder 8 at the contraction inlet section adopts a gradually-reduced structure, and the diameter of the cylinder is gradually reduced from the inlet of the cylinder to the direction of the steady flow straight section cylinder 9; the cylinder 10 at the expansion outlet section adopts a gradually expanding structure, and the diameter of the cylinder is gradually expanded from the steady flow straight section cylinder 9 to the outlet direction of the cylinder. The contraction inlet section cylinder 8 of the reducing structure and the expansion outlet section cylinder 10 of the gradually expanding structure, the structural design can reduce the inlet and outlet resistance to the maximum extent, and can reduce the wall surface abrasion of the inlet and outlet section heat exchange tubes 4 when high-speed flue gas enters and exits the heat exchanger.
The steam inlet main pipe 1 adopts a fixed pipe plate structure, and the steam outlet main pipe 7 adopts a floating structure. The steam outlet main pipe 7 with a floating structure can meet the requirement of thermal stress release.
The external longitudinal straight ribbed tube adopts an external finned tube.
The lowest position of the heat exchanger is provided with a sewage draining outlet, and the highest position of the heat exchanger is provided with an exhaust port.
The working medium flow of the embodiment is as follows:
the flue gas enters the heat exchanger from the top and around the cylinder 8 at the contraction inlet section from the flue gas inlet at the top end of the heat exchanger, then enters the steady flow straight section cylinder 9, and flows out of the heat exchanger through the cylinder 10 at the expansion outlet section after releasing heat. Reheated steam enters the inlet large header 21 from the steam inlet main pipe 1 at the bottom end of the heat exchanger, sequentially passes through the inlet small header 31 and the heat exchange pipe 4 of each pipe group, converges to the outlet large header 22 through the pipe group outlet small header 32, and then converges to the outlet steam main pipe to flow out of the heat exchanger.
Referring to fig. 3, which is a schematic view of a circular tube of a conventional inverter in the prior art, fig. 4 is a schematic view of a circular tube with a high specific surface area manufactured by processing a circular tube with the same diameter as the circular tube in fig. 3, and it can be seen from the two views that the high specific surface area tube has no vortex due to the change of its shape, is not easy to generate dust deposition and is not easy to be worn by dust.
In the embodiment, the combination of multiple pipe groups and the pure countercurrent arrangement are adopted, so that the maximum heat exchange temperature difference and the longitudinal high-speed flow are realized, the comprehensive heat exchange performance is improved, and the possibility of dust accumulation and scale deposition of the heat exchange pipe 4 is effectively reduced; the design of a pure countercurrent structure is adopted, so that the maximum heat exchange temperature difference is ensured; the parallel flow structure can greatly reduce the flow resistance of a unit flow, or greatly improve the flow velocity of a medium under the same flow resistance, reduce the degree of dust and scale deposition on a heat exchange surface and reduce the influence of surface scaling on the heat exchange performance to the greatest extent; the embodiment is particularly suitable for flue type heat exchangers for flue gas/air heat exchange, flue gas/steam heat exchange and the like and other dividing wall type heat exchange occasions among fluids such as gas/gas, gas/liquid, liquid/liquid and the like.
The above detailed description is specific to possible embodiments of the present invention, and the embodiments are not intended to limit the scope of the present invention, and all equivalent implementations or modifications that do not depart from the scope of the present invention are intended to be included within the scope of the present invention.
Claims (8)
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811204148.1A CN111059928B (en) | 2018-10-16 | 2018-10-16 | Pure countercurrent modular combined heat exchanger |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811204148.1A CN111059928B (en) | 2018-10-16 | 2018-10-16 | Pure countercurrent modular combined heat exchanger |
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| Publication Number | Publication Date |
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| CN111059928A true CN111059928A (en) | 2020-04-24 |
| CN111059928B CN111059928B (en) | 2024-05-03 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201811204148.1A Active CN111059928B (en) | 2018-10-16 | 2018-10-16 | Pure countercurrent modular combined heat exchanger |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113465414A (en) * | 2021-07-06 | 2021-10-01 | 包头华鼎铜业发展有限公司 | Low pressure drop corrosion resistant shell-and-tube heat exchanger |
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|---|---|---|---|---|
| CN103884209A (en) * | 2014-03-10 | 2014-06-25 | 中国科学院过程工程研究所 | Split combined type flue heat exchanger |
| CN205784740U (en) * | 2016-05-31 | 2016-12-07 | 中冶焦耐工程技术有限公司 | A self-supporting zoom tube heat exchanger |
| US20170016678A1 (en) * | 2015-07-14 | 2017-01-19 | Holtec International | Tubular heat exchanger |
| CN107543434A (en) * | 2017-08-16 | 2018-01-05 | 重庆大学 | Removable modularization abrasionproof ash disposal three-dimensional ribbed pipe heat exchanger |
| CN209570045U (en) * | 2018-10-16 | 2019-11-01 | 中国科学院广州能源研究所 | Pure countercurrent modular combined heat exchanger |
-
2018
- 2018-10-16 CN CN201811204148.1A patent/CN111059928B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103884209A (en) * | 2014-03-10 | 2014-06-25 | 中国科学院过程工程研究所 | Split combined type flue heat exchanger |
| US20170016678A1 (en) * | 2015-07-14 | 2017-01-19 | Holtec International | Tubular heat exchanger |
| CN205784740U (en) * | 2016-05-31 | 2016-12-07 | 中冶焦耐工程技术有限公司 | A self-supporting zoom tube heat exchanger |
| CN107543434A (en) * | 2017-08-16 | 2018-01-05 | 重庆大学 | Removable modularization abrasionproof ash disposal three-dimensional ribbed pipe heat exchanger |
| CN209570045U (en) * | 2018-10-16 | 2019-11-01 | 中国科学院广州能源研究所 | Pure countercurrent modular combined heat exchanger |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113465414A (en) * | 2021-07-06 | 2021-10-01 | 包头华鼎铜业发展有限公司 | Low pressure drop corrosion resistant shell-and-tube heat exchanger |
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| CN111059928B (en) | 2024-05-03 |
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