CN115111955A - Gill bionic plate-type micro-reactor heat exchange surface structure - Google Patents
Gill bionic plate-type micro-reactor heat exchange surface structure Download PDFInfo
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- CN115111955A CN115111955A CN202210691306.0A CN202210691306A CN115111955A CN 115111955 A CN115111955 A CN 115111955A CN 202210691306 A CN202210691306 A CN 202210691306A CN 115111955 A CN115111955 A CN 115111955A
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- 239000011664 nicotinic acid Substances 0.000 title claims abstract description 22
- 239000012530 fluid Substances 0.000 claims abstract description 36
- 229910000831 Steel Inorganic materials 0.000 claims description 2
- 239000010959 steel Substances 0.000 claims description 2
- 230000001965 increasing effect Effects 0.000 abstract description 7
- 230000000694 effects Effects 0.000 abstract description 3
- 230000007547 defect Effects 0.000 abstract description 2
- 238000004088 simulation Methods 0.000 description 8
- 239000000463 material Substances 0.000 description 6
- 238000000034 method Methods 0.000 description 4
- 241000251468 Actinopterygii Species 0.000 description 3
- 238000004364 calculation method Methods 0.000 description 3
- 230000000052 comparative effect Effects 0.000 description 3
- 229910001220 stainless steel Inorganic materials 0.000 description 3
- 239000010935 stainless steel Substances 0.000 description 3
- 238000006243 chemical reaction Methods 0.000 description 2
- 239000002826 coolant Substances 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000002708 enhancing effect Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000003889 chemical engineering Methods 0.000 description 1
- 238000006396 nitration reaction Methods 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
- F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
- F28F3/048—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of ribs integral with the element or local variations in thickness of the element, e.g. grooves, microchannels
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- 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
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
- Y02P20/00—Technologies relating to chemical industry
- Y02P20/10—Process efficiency
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- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Physical Or Chemical Processes And Apparatus (AREA)
Abstract
The invention discloses a gill bionic plate type reactor heat exchange surface structure which is provided with a plurality of runner units which are arranged at equal intervals along the length direction of a heat exchange plate and have the same structure; the flow channel unit consists of two v-shaped wave crests which are symmetrically arranged, two straight wave crests which are symmetrically arranged, a herringbone wave crest and a small herringbone wave crest which is symmetrical along the axis of the plate; the gill bionic plate type reactor heat exchange surface structure provided by the invention overcomes the defect of insufficient heat exchange performance of the heat exchange design of the existing microreactor, the gill bionic structure is adopted, the heat exchange contact area of fluid in unit volume is increased, and meanwhile, fluid disturbance is introduced, so that when the heat exchange oil in a laminar flow state originally flows through a V-shaped wave crest and a herringbone wave crest, the fluid is stretched, sheared, folded and collided, a streamline is rotated, a fluid boundary layer is damaged, the turbulence degree is greatly increased, the convection heat transfer coefficient is enhanced, and the heat exchange effect can be remarkably improved.
Description
Technical Field
The invention relates to the technical field of plate-type microreactors and heat exchange, in particular to a heat exchange surface structure of a gill bionic plate-type reactor.
Background
The plate-type microreactor has excellent mass transfer and heat transfer performances due to extremely small characteristic size and extremely large specific surface area, and is widely applied to the industries of chemical engineering, pharmacy and the like. Plate-type microreactors are often used for dangerous strongly exothermic reactions such as nitration reactions, and therefore the heat exchange capability of internal reaction fluid and cooling medium is an important index for evaluating the performance of the plate-type microreactor. In the technical field of heat exchange, the heat exchange efficiency is generally improved by enhancing the heat exchange coefficient or increasing the heat exchange area.
At present, a plate-type microreactor is designed to generally adopt a straight or herringbone corrugated structure for enhancing the heat exchange capacity, and the heat exchange area of a heat exchange medium and a plate surface can be increased. However, as the use performance of the plate-type microreactor is improved, the design of a heat exchange surface needs to be further optimized, and the heat exchange capacity of the reactor is enhanced.
The invention is inspired from the fish gill shape, designs a heat exchange surface structure of a fish gill bionic plate type reactor, not only has a great heat exchange area, but also can introduce disturbance to a cooling medium, destroy the boundary layer of fluid, increase the heat exchange coefficient and further strengthen the heat exchange.
Disclosure of Invention
Aiming at the defects of the design of the heat exchange surface of the existing plate-type microreactor, the invention provides a gill bionic plate-type reactor heat exchange surface structure, which comprises a heat exchange plate; a heat exchange medium flowing domain is arranged above the heat exchange plate, and a heat-exchanged medium domain is arranged below the heat exchange plate; the upper surface of the heat exchange plate is a heat exchange medium flowing surface, and the lower surface of the heat exchange plate is a heat-exchanged medium surface; the heat exchange medium flow surface is provided with a plurality of flow channel units which are arranged at equal intervals along the length direction of the heat exchange plate;
the flow channel unit is composed of wave crests arranged along the flow direction of a fluid and comprises two symmetrical V-shaped wave crests arranged on two sides of a central axis in the width direction of the heat exchange plate, two symmetrical straight wave crests A arranged on two sides of the central axis in the width direction of the heat exchange plate, a large herringbone wave crest taking the central axis in the width direction of the heat exchange plate as a symmetrical axis, and a small herringbone wave crest taking the central axis in the width direction of the heat exchange plate as a symmetrical axis, wherein the whole flow channel unit is symmetrical about the central axis in the width direction of the heat exchange plate.
Preferably, the cross-sectional shapes of the v-shaped peak, the straight peak A, the large herringbone peak and the small herringbone peak are rectangular, isosceles trapezoid or sine wave. The V-shaped wave crest is formed by sequentially connecting a short-edge wave crest, a connecting wave crest and a long-edge wave crest, and a V-shaped opening of the V-shaped wave crest faces to a side edge adjacent to the V-shaped opening. The included angle alpha between the short side wave crest and the length direction of the plate is 70-90 degrees, the ratio h/w between the height of the short side wave crest and the width of the cross section of the short side wave crest is 0.5-1.5, the included angle delta between the connecting wave crest and the width direction of the heat exchange plate is 45-135 degrees, the ratio h/w between the height of the connecting wave crest and the width of the cross section of the connecting wave crest is 0.5-1.5, the included angle beta between the long side wave crest and the length direction of the heat exchange plate is 50-90 degrees, and the ratio h/w between the height of the long side wave crest and the width of the cross section of the long side wave crest is 0.5-1.5.
Preferably, the included angle gamma between the straight wave crest A and the length direction of the heat exchange plate is 60-90 degrees, and the ratio h/w of the height of the straight wave crest A to the width of the cross section of the straight wave crest A is 0.5-2. The large herringbone wave crests are formed by connecting two straight wave crests which are symmetrical along the central axis in the width direction of the heat exchange plate, the included angle epsilon between each straight wave crest and the length direction of the heat exchange plate is 40-80 degrees, the ratio h/w of the height of each straight wave crest to the width of the cross section of each straight wave crest is 0.5-2, and the herringbone opening direction is consistent with the fluid flow direction. The small herringbone wave crests are formed by connecting two straight wave crests which are symmetrical along the axial line in the width direction of the heat exchange plate, the included angle zeta between the straight wave crests and the length direction of the heat exchange plate is 40-80 degrees, the ratio h/w of the height of the straight wave crests to the width of the cross section of the straight wave crests is 1-3, and the herringbone opening direction is consistent with the flow direction of fluid.
Preferably, the heat exchange surface structure of the gill bionic plate reactor is characterized in that the flow channel unit and the heat exchange plate are integrally processed and formed; the heat exchange plate is made of steel. The flow channel unit is arranged on the heat exchange medium flow surface of the heat exchange plate, and the lower heat exchange medium flow surface is a smooth surface.
Compared with the prior art, the invention has the following beneficial effects:
on the one hand, adopt fish gill bionic structure, increased the heat transfer area of contact of unit volume fluid, on the other hand, introduced fluid disturbance, when the heat transfer oil that originally was in laminar flow state flows through v font crest and chevron shape crest, the fluid is stretched, sheared, folded, collided, makes the streamline take place to rotate, and the fluid boundary layer is destroyed, turbulence degree greatly increased to strengthen the convection heat transfer coefficient, promoted to the heat transfer effect and had apparent effect.
Drawings
FIG. 1 is a schematic view of a gill bionic plate-type reactor heat exchange surface structure (referred to as gill corrugation for short);
FIG. 2 is a schematic cross-sectional view of a peak;
FIG. 3 is a schematic diagram of a non-isothermal flow simulation model of gill corrugation;
FIG. 4 is a schematic view of a non-isothermal flow simulation model of straight corrugations;
FIG. 5 is a schematic diagram of a smooth non-corrugated non-isothermal flow simulation model;
FIG. 6 is a flow chart of non-isothermal flow simulation results of three structures, namely gill corrugation, straight corrugation and smooth non-corrugation;
FIG. 7 is a graph comparing temperature rise at the outlet of heat exchange oil in non-isothermal flow simulation results of three structures of gill corrugation, straight corrugation and smooth non-corrugation;
in the figure: 1. a v-shaped peak; 2. a straight wave crest A; 3. big herringbone crest, 4, little herringbone crest.
Detailed Description
The invention will be further illustrated and described with reference to specific embodiments. The described embodiments are merely exemplary of the disclosure and are not intended to limit the scope thereof. The technical features of the embodiments of the present invention can be combined correspondingly without mutual conflict.
As shown in the attached figure 1, the method provides a gill bionic plate type reactor heat exchange surface structure, which comprises a heat exchange plate; a heat exchange medium flowing domain is arranged above the heat exchange plate, and a heat-exchanged medium domain is arranged below the heat exchange plate; the upper surface of the heat exchange plate is a heat exchange medium flowing surface, and the lower surface of the heat exchange plate is a heat-exchanged medium surface; the heat exchange medium flow surface of the heat exchange plate is provided with a plurality of flow channel units which are arranged at equal intervals along the length direction of the heat exchange plate;
the flow channel unit consists of wave crests arranged along the flow direction of the fluid; the heat exchange plate comprises two symmetrical V-shaped wave crests 1 arranged on two sides of a central axis in the width direction of the heat exchange plate, two symmetrical straight wave crests A2 arranged on two sides of the central axis in the width direction of the heat exchange plate, a large herringbone wave crest 3 taking the central axis in the width direction of the heat exchange plate as a symmetrical axis, and a small herringbone wave crest 4 taking the central axis in the width direction of the heat exchange plate as a symmetrical axis; the whole flow passage unit is symmetrical about the central axis in the width direction of the heat exchange plate; the wave crests are structures on the flow surface of the heat exchange medium of the heat exchange plate, the wave crests are integrally formed with the heat exchange plate and are part of the heat exchange plate, the flow channel unit is arranged on the upper side of the heat exchange plate, namely the flow surface of the heat exchange medium, and the flow surface of the heat-exchanged medium is a smooth surface on the lower side.
As shown in fig. 2, the cross-sectional shapes of the v-shaped peak 1, the straight peak a2, the big herringbone peak 3 and the small herringbone peak 4 are rectangles, and the width of the cross-section of the peaks is w; the spacing distance d between two adjacent wave crests can be 1-4 times the cross-sectional width w of the wave crest.
The v-shaped peak 1 is formed by sequentially connecting a short-edge peak, a connecting peak and a long-edge peak, wherein an included angle alpha between the short-edge peak and the length direction of the heat exchange plate is 85 degrees, the height h of the short-edge peak is 0.75 peak cross section width w, an included angle delta between the connecting peak and the length direction of the heat exchange plate is 90 degrees, the height h of the connecting peak is 0.75 peak cross section width w, the included angle beta between the long-edge peak and the length direction of the heat exchange plate is 65 degrees, and the height h of the long-edge peak is 0.75 peak cross section width w; the v-shaped opening faces the side adjacent thereto;
an included angle gamma between the straight wave crest A2 and the length direction of the heat exchange plate is 75 degrees, and the height h of the straight wave crest A2 is equal to the width w of the cross section of the wave crest;
the large herringbone wave crests 3 are formed by connecting two sections of straight wave crests which are symmetrical along the central axis of the heat exchange plate, the included angle epsilon between the straight wave crests and the length direction of the heat exchange plate is 60 degrees, the height h of the straight wave crests is equal to the width w of the cross section of the wave crests, and the herringbone opening direction is consistent with the fluid flow direction;
the small herringbone wave crests 4 are formed by connecting two sections of straight wave crests which are symmetrical along the central axis in the width direction of the heat exchange plate, the included angle zeta between the straight wave crests and the length direction of the heat exchange plate is 60 degrees, the height h of the straight wave crests is equal to 1.5 wave crest cross section width w, and the herringbone opening direction is consistent with the fluid flow direction.
Example 1: gill corrugation design
Referring to the attached figure 3, the heat exchange performance of the gill corrugation is tested by adopting COMSOL Multiphysics software to perform non-isothermal flow simulation on fluid, wherein the fluid material is heat exchange oil and the density is 900kg/m 3 The heat conductivity coefficient is 0.45W/(m.k), the constant-pressure heat capacity is 1809.1J/(kg.k), the dynamic viscosity is 0.006 Pa.s, the heat exchange plate material is stainless steel 316L, and the density is 7980kg/m 3 The thermal conductivity is 16.2W/(m.k), and the constant-pressure heat capacity is 502J/(kg.k). The calculation model adopts a non-isothermal flow model to couple the flow and heat transfer processes, the inlet speed of the heat exchange oil at the left end is 0.04m/s, the inlet temperature of the heat exchange oil is 15 ℃, and the isothermal domain of the plate is set to be 40 ℃, which means that the temperature of the plate is always constant at 40 ℃, the heat exchange performance is judged by comparing the outlet temperature of the heat exchange oil, and the higher the outlet temperature of the heat exchange oil represents the stronger the heat exchange performance. The result shows that as shown in fig. 6, when the heat exchange oil in the originally laminar state flows through the v-shaped wave crest and the herringbone wave crest, the fluid is stretched, sheared, folded and collided to generate a very complicated rotating flow line, the fluid boundary layer is damaged, the fluid close to the wall surface is heated and then convects to the two sides and the upper part along the extending direction of the corrugation, the unheated fluid is filled in, a good internal circulation of the fluid is formed, and the turbulence degree is greatly increased. As shown in fig. 7, the heat exchange oil outlet temperature rise was 14.793 ℃.
Comparative example 2: smooth no-ripple design
Referring to FIG. 4, the non-isothermal flow simulation of fluid using COMSOL Multiphysics software to test the smooth and ripple-free heat exchange performance was performed with the fluid material being heat exchange oil and the density being 900kg/m 3 The thermal conductivity coefficient is 0.45W/(m.k), the constant-pressure heat capacity is 1809.1J/(kg.k), the dynamic viscosity is 0.006 Pa.s, the heat exchange plate material is stainless steel 316L, and the density is 7980kg/m 3 A thermal conductivity of 162W/(m.k), constant pressure heat capacity 502J/(kg.k). The calculation model adopts a non-isothermal flow model to couple the flow and heat transfer processes, the inlet speed of the heat exchange oil at the left end is 0.04m/s, the inlet temperature of the heat exchange oil is 15 ℃, and the isothermal region adopted by the plate is set to be 40 ℃. The results show that the heat exchange oil flow lines are parallel, the flow state is always laminar, the temperature of the fluid near the wall surface is heated to be higher, and the temperature of the fluid far from the wall surface is still lower, as shown in figure 6. As shown in fig. 7, the heat exchange oil outlet temperature rise was 9.062 ℃.
Comparative example 3: straight corrugated design
Referring to FIG. 4, the heat exchange performance of straight corrugations was tested by non-isothermal flow simulation of fluid using COMSOL Multiphysics software, the fluid material being heat exchange oil and having a density of 900kg/m 3 The thermal conductivity coefficient is 0.45W/(m.k), the constant-pressure heat capacity is 1809.1J/(kg.k), the dynamic viscosity is 0.006 Pa.s, the heat exchange plate material is stainless steel 316L, and the density is 7980kg/m 3 The thermal conductivity is 16.2W/(m.k), and the constant-pressure heat capacity is 502J/(kg.k). The calculation model adopts a non-isothermal flow model to couple the flow and heat transfer processes, the inlet speed of the heat exchange oil at the left end is 0.04m/s, the inlet temperature of the heat exchange oil is 15 ℃, and the isothermal region adopted by the plate is set to be 40 ℃. The results show that the heat exchange oil flow lines are substantially parallel, slightly curved flow lines are generated, the heat exchange oil is slightly disturbed when passing through the straight corrugations, the flow state is still kept laminar, the temperature of the fluid close to the wall surface is heated to be higher, and the temperature of the fluid far away from the wall surface is lower, as shown in figure 6. As shown in fig. 7, the heat exchange oil outlet temperature rise was 12.317 ℃.
As shown in fig. 7, the comparison between example 1 and comparative examples 1 and 2 shows that the heat exchange performance of straight corrugations is better than that of smooth non-corrugated heat exchange performance, and the heat exchange performance of gill corrugations is significantly improved compared with that of the other two structures, because in the gill corrugation design, the heat exchange oil flows through the gill corrugations and is greatly disturbed, so that the gill corrugations have stronger turbulence degree and good internal heat circulation of the fluid, and the convection heat exchange coefficient is further enhanced. Under the combined action of high convection heat transfer coefficient and high unit fluid heat transfer area, the heat transfer performance of the gill corrugated structure is obviously improved.
Claims (10)
1. A gill bionic plate type reactor heat exchange surface structure is characterized by comprising a heat exchange plate; the upper surface of the heat exchange plate is a heat exchange medium flowing surface, and the lower surface of the heat exchange plate is a heat-exchanged medium surface; the heat exchange medium flow surface is provided with a plurality of flow channel units which are arranged at equal intervals along the length direction of the heat exchange plate;
the flow channel unit is composed of wave crests arranged along the flow direction of a fluid, and comprises two V-shaped wave crests (1) which are arranged on two sides of a central axis in the width direction of the heat exchange plate and are symmetrical, two straight wave crests A (2) which are arranged on two sides of the central axis in the width direction of the heat exchange plate and are symmetrical, a big herringbone wave crest (3) which takes the central axis in the width direction of the heat exchange plate as a symmetrical axis, and a small herringbone wave crest (4) which takes the central axis in the width direction of the heat exchange plate as a symmetrical axis, wherein the whole flow channel unit is symmetrical about the central axis in the width direction of the heat exchange plate.
2. The gill bionic plate type reactor heat exchange surface structure according to claim 1, wherein the cross-sectional shapes of the v-shaped wave crest (1), the straight wave crest A (2), the herringbone wave crest (3) and the herringbone wave crest (4) are rectangular, isosceles trapezoid or sine wave.
3. The gill bionic plate reactor heat exchange surface structure according to claim 1, wherein the v-shaped wave crests (1) are formed by connecting short-side wave crests, connecting wave crests and long-side wave crests in sequence, and v-shaped openings of the v-shaped wave crests (1) face to the side edges adjacent to the v-shaped wave crests.
4. The gill bionic plate reactor heat exchange surface structure of claim 3, wherein an included angle α between the short side wave crest and the plate length direction is 70-90 °, a ratio h/w between the height of the short side wave crest and the cross section width of the short side wave crest is 0.5-1.5, an included angle δ between the connection wave crest and the heat exchange plate width direction is 45-135 °, a ratio h/w between the height of the connection wave crest and the cross section width of the connection wave crest is 0.5-1.5, an included angle β between the long side wave crest and the heat exchange plate length direction is 50-90 °, and a ratio h/w between the height of the long side wave crest and the cross section width of the long side wave crest is 0.5-1.5.
5. The gill bionic plate reactor heat exchange surface structure according to claim 1, wherein the included angle γ between the straight wave crest A (2) and the length direction of the heat exchange plate is 60-90 °, and the ratio h/w between the height of the straight wave crest A (2) and the cross-sectional width of the straight wave crest A (2) is 0.5-2.
6. The gill bionic plate type reactor heat exchange surface structure of claim 1, wherein the large herringbone wave crest (3) is formed by connecting two straight wave crests which are symmetrical along the central axis in the width direction of the heat exchange plate, the included angle epsilon between the straight wave crest and the length direction of the heat exchange plate is 40-80 degrees, the ratio h/w between the height of the straight wave crest and the width of the cross section of the straight wave crest is 0.5-2, and the herringbone opening direction is consistent with the fluid flow direction.
7. The gill bionic plate reactor heat exchange surface structure according to claim 1, wherein the small herringbone peaks (4) are formed by connecting two straight peaks which are symmetrical along the axial line in the width direction of the heat exchange plate, the included angle zeta between the straight peaks and the length direction of the heat exchange plate is 40-80 degrees, the ratio h/w between the height of the straight peaks and the width of the cross section of the straight peaks is 1-3, and the herringbone opening direction is consistent with the fluid flow direction.
8. The gill bionic plate type reactor heat exchange surface structure of claim 1, wherein the flow passage unit and the heat exchange plate are integrally formed.
9. The gill bionic plate reactor heat exchange surface structure of claim 1, wherein the heat exchange plate is made of steel.
10. The heat exchange surface structure of the gill bionic plate reactor according to claim 1, wherein the heat exchange medium flow surface of the heat exchange plate is provided with a flow channel unit, and the heat exchange medium flow surface is smooth.
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| CN202210691306.0A CN115111955B (en) | 2022-06-17 | 2022-06-17 | Heat exchange surface structure of fish gill bionic plate-type microreactor |
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| CN202210691306.0A CN115111955B (en) | 2022-06-17 | 2022-06-17 | Heat exchange surface structure of fish gill bionic plate-type microreactor |
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| CN215930667U (en) * | 2021-08-12 | 2022-03-01 | 珠海格力电器股份有限公司 | Heat exchange plate sheet of plate heat exchanger and plate heat exchanger |
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2022
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| GB1272285A (en) * | 1969-04-29 | 1972-04-26 | Kyffhauserhutte Arten Veb Masc | Plate-type heat exchanger |
| JPH0989482A (en) * | 1995-09-26 | 1997-04-04 | Hisaka Works Ltd | Plate-type heat exchanger |
| JP2002102974A (en) * | 2000-09-11 | 2002-04-09 | Valeo Engine Cooling Ab | Fluid transportation tube, manufacturing method and device therefor |
| CN201225852Y (en) * | 2008-05-04 | 2009-04-22 | 郑州凯乐生物能有限公司 | Wide channel plate heat exchanger with detachable intensified element on one side |
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| CN215003090U (en) * | 2021-03-26 | 2021-12-03 | 广州番禺新速能板式热交换器有限公司 | Large and small channel plate heat exchanger |
| CN215930667U (en) * | 2021-08-12 | 2022-03-01 | 珠海格力电器股份有限公司 | Heat exchange plate sheet of plate heat exchanger and plate heat exchanger |
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| Title |
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| 吴私;李春兰;王森;李占英;朱海舟;: "不同波纹夹角的人字形板式热交换器数值模拟", 化工机械, no. 06, 15 December 2016 (2016-12-15), pages 770 - 775 * |
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| CN115111955B (en) | 2024-04-26 |
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