CN215832532U - Cross flow plate type heat exchange plate - Google Patents
Cross flow plate type heat exchange plate Download PDFInfo
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- CN215832532U CN215832532U CN202121896655.3U CN202121896655U CN215832532U CN 215832532 U CN215832532 U CN 215832532U CN 202121896655 U CN202121896655 U CN 202121896655U CN 215832532 U CN215832532 U CN 215832532U
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Abstract
The utility model belongs to the technical field of heat exchangers, and particularly relates to a cross-flow plate type heat exchange plate which comprises a heat exchange core body, a heat exchanger shell, a hot flue gas inlet, a hot flue gas outlet, a cold fluid inlet, a cold fluid outlet, a cold fluid inlet and a cold fluid outlet, wherein the left side and the right side of the heat exchanger shell are respectively connected with the hot flue gas inlet and the hot flue gas outlet; the heat exchange core body is formed by stacking a plurality of groups of heat exchange plates, each group of heat exchange plates is composed of two heat exchange plate bodies, the heat exchange plate body positioned on the upper part between the two heat exchange plate bodies of each group and the heat exchange plate body positioned on the lower part are oppositely arranged in the concave part to form a plurality of closed heat exchange tube passes, and a heat exchange shell pass is formed between every two adjacent groups of heat exchange plates, namely the upper heat exchange plate body and the lower heat exchange plate body in each group of heat exchange plates are symmetrically arranged, and the plurality of groups of heat exchange plates are positioned in the shell and are sequentially arranged in parallel from top to bottom along the interior of the shell.
Description
Technical Field
The utility model belongs to the technical field of heat exchangers, and particularly relates to a cross flow plate type heat exchange plate.
Background
With the increasing prominence of energy problems, energy conservation and consumption reduction become important targets of industrial production. In the production process of industrial furnaces such as coal furnaces, kilns, blast furnaces and the like, a large amount of high-temperature flue gas in the industrial furnaces cannot be completely recovered by the boilers, the discharged waste flue gas contains a large amount of heat energy, and the waste flue gas is discharged into the atmosphere, so that energy is wasted and the environment is polluted. In order to deeply recycle the waste heat of the industrial flue gas, a large number of flue gas heat exchangers are developed. The most common are tube type heat exchangers, heat pipe type heat exchangers, and the like. The tubular heat exchanger is composed of tube boxes, such as a tubular air preheater, and dust deposition and corrosion problems are easy to occur on the surface of the heat exchanger for heat transfer of flue gas with dust and acid condensation. The heat pipe gas-gas heat exchanger is a compact gas-gas heat exchanger, and transfers heat by evaporation and condensation of working medium sealed in the pipe. The heat pipe heat exchanger can be made into finned pipes, so that the heat exchange area is greatly increased, and the structure is more compact than that of a tube type heat exchanger. However, the working medium of the heat pipe is incompatible with metal, and special materials are needed to be matched with the working medium or special treatment is needed, so that the process is complex and the cost is high.
The plate heat exchanger is formed by mutually isolating a series of metal sheets to form an airflow channel for dividing wall type heat transfer. The heat pipe type heat exchanger has the advantages of high heat exchange efficiency, small occupied area, light weight and the like, the gap between the plates is large, the heat exchange surface is smooth, the problem that the shell and tube type heat exchanger is easy to deposit dust and corrode is solved, the structure is compact, the cost is low, the processing is simple and convenient, and the problems that the heat pipe type heat exchanger is complex in process and high in cost are solved.
However, in the design process of the plate heat exchanger, the following two aspects still need to be considered in an important way: 1) the surface heat transfer coefficient of the plate is improved. Because the heat conductivity coefficient of the gas is low, the fluid generates turbulence at a low flow speed by reasonable design of the plate, and a high surface heat transfer coefficient is obtained; 2) reducing fouling resistance. In the environment of high dust-laden flue gas, the slab still needs to be designed reasonably, so that the deposition of fly ash particles on the surface of the slab is reduced, and the scale formation of the slab is prevented.
SUMMERY OF THE UTILITY MODEL
The utility model aims to provide a cross flow plate type heat exchanger, which is characterized in that a hot flue gas channel is a corrugated channel through the innovative design of a heat exchange plate, and convex parts and concave parts in the channel are arranged in a staggered manner, so that fluid disturbance is increased, and the heat exchange effect can be effectively enhanced.
In order to achieve the purpose, the utility model adopts the technical scheme that: a cross flow plate type heat exchange plate comprises a heat exchange core body, a heat exchanger shell, a hot flue gas inlet, a hot flue gas outlet and a cold fluid inlet, wherein the left side and the right side of the heat exchanger shell are respectively connected with the hot flue gas inlet and the hot flue gas outlet, the front side and the rear side of the heat exchanger shell are respectively connected with the cold fluid inlet and the cold fluid outlet, and a partition plate is respectively arranged between the heat exchanger shell and the cold fluid inlet and the cold fluid outlet; the heat transfer core is piled up by the multiunit heat transfer board and forms, every group heat transfer board comprises two heat transfer board bodies, the heat transfer board body that lies in upper portion between two heat transfer board bodies of every group and the heat transfer board body that lies in the lower part set up relatively and form a plurality of confined heat transfer tube sides in the depressed part, form the heat transfer shell side between adjacent two sets of heat transfer boards, upper portion heat transfer board body and lower part heat transfer board body symmetry set up in every group heat transfer board promptly, multiunit heat transfer board is located the casing and along the inside from the top down parallel arrangement in proper order of casing.
Furthermore, a plurality of first heat exchange surfaces and second heat exchange surfaces which are sequentially and alternately arranged are arranged on the heat exchange plate body along the longitudinal direction of the heat exchange plate body, the first heat exchange surfaces and the second heat exchange surfaces are connected through third heat exchange surfaces, the longitudinal sections of the first heat exchange surfaces are in a corrugated shape formed by a plurality of concave parts and convex parts which are repeatedly and alternately arranged, the longitudinal sections of the second heat exchange surfaces are in a corrugated shape formed by a plurality of convex parts and concave parts which are repeatedly and alternately arranged, the convex parts and the concave parts of the first heat exchange surfaces and the second heat exchange surfaces on the same transverse plane are alternately arranged, the third heat exchange surfaces are planes, the horizontal plane of the concave parts is higher than the horizontal plane of the third heat exchange surfaces, and the two sides of the third heat exchange surfaces respectively form grooves with the first heat exchange surfaces and the second heat exchange surfaces in a smooth transition mode, wherein the cross sections of the grooves are inverted isosceles trapezoids.
Furthermore, the first heat exchange surface, the second heat exchange surface and the third heat exchange surface are integrally formed and repeatedly arranged to form a heat exchange plate body, and the heat exchange plate body is rectangular plate-shaped.
Furthermore, the cross section of the concave part is in an inverted isosceles trapezoid or arc shape, and the convex part is in an isosceles trapezoid or arc shape.
Furthermore, a cold fluid channel is arranged in the heat exchange tube pass, and a hot fluid channel is arranged in the heat exchange shell pass.
Furthermore, the heat exchanger shell is provided with strip-shaped supporting plates at the inlet and outlet of the hot fluid channel, the gap between the two strip-shaped supporting plates forms the inlet of the hot fluid channel, the edge of the heat exchange plate is fixedly welded with the inner wall of the cubic shell, the cubic shell is provided with a flow limiting plate at the inlet and outlet of the cold fluid channel, the flow limiting plate is provided with a plurality of hollowed-out openings, and the shape of the opening on the flow limiting plate is matched with the shape of the heat exchange tube on the cold fluid channel with one section.
The utility model has the advantages that:
1. in the utility model, through the innovative design of the heat exchange plate, the hot flue gas channel is a corrugated channel, and the convex parts and the concave parts in the channel are arranged in a staggered way, so that the fluid disturbance is increased, the heat exchange effect can be effectively strengthened, and the deposition of fly ash particles in the flue gas can be effectively reduced;
2. the upper and lower heat exchange plates between each group of heat exchange plates are reversely buckled and spliced to form a cold fluid channel, the cold fluid channel is of a scaling structure, and the periodic expansion and contraction of the cold fluid channel causes the bending of a streamline and causes the scouring of a near-wall fluid on the wall surface, so that the mixing of a core fluid and a boundary layer fluid is promoted, the convection heat transfer effect is enhanced, and the scaling is not easy to occur;
3. the problem of large difference between the flow rates of hot flue gas and cold fluid can be solved by reasonably adjusting the structural size and the distance of the plates;
4. the sheet bar is blanked once, so that the assembly requirement can be met, and the secondary cutting amount for sheet bar forming is reduced. And the heat exchanger fluid adopting the plate can form turbulent flow at a very low Reynolds, so that the heat exchange efficiency is improved, the heat exchange area is saved, the volume of the heat exchanger is reduced, and the manufacturing cost and the operation cost of equipment are reduced.
Drawings
Fig. 1 is a schematic view of a heat exchange plate according to the present invention.
Fig. 2 is an axial view of a heat exchanger plate body according to the utility model.
Fig. 3 is an axial view of the heat exchange core of the present invention.
Fig. 4 is a sectional view of the heat exchange core of fig. 3.
Fig. 5 is a sectional view taken along the plane a-a in fig. 4.
Fig. 6 is a sectional view taken along the plane B-B in fig. 4.
Fig. 7 is a cross-sectional view taken along plane C-C of fig. 4.
Fig. 8 is a cross-sectional view taken along plane D-D of fig. 4.
Detailed Description
As shown in fig. 1, the utility model provides a cross flow plate heat exchanger, which comprises a heat exchange core 1, a heat exchanger shell 2, hot flue gas inlets and outlets 3, 3 'and cold fluid inlets and outlets 4, 4', wherein the left and right sides of the heat exchanger shell 2 are respectively connected with the hot flue gas inlets and outlets 3, 3 ', the front and rear sides of the heat exchanger shell 2 are respectively connected with the cold fluid inlets and outlets 4, 4', and partition plates 5, 5 'are respectively arranged between the heat exchanger shell 2 and the cold fluid inlets and outlets 4, 4'.
As shown in fig. 3, the heat exchange core 1 is formed by stacking a plurality of sets of heat exchange plates. Every group heat transfer board comprises two heat transfer board bodies, and the heat transfer board body that lies in upper portion between two heat transfer board bodies of every group sets up relatively at the depressed part and forms a plurality of confined heat transfer tube sides with the heat transfer board body that lies in the lower part, forms the heat transfer shell side between adjacent two sets of heat transfer boards, and upper portion heat transfer board body and lower part heat transfer board body symmetry set up in every group heat transfer board promptly, and multiunit heat transfer board is located the casing and along the inside from the top down parallel arrangement in proper order of casing. The specific transformation process is as follows, taking fig. 3 as an example, the heat exchange plate body 7 is transformed from the heat exchange plate body 6 symmetrically, and the symmetric plane is the lower bottom surface of the third heat exchange surface of the heat exchange plate body 6. The heat exchange plate body 8 and the heat exchange plate body 9 are formed by rotating the heat exchange plate bodies 6 and 7 by 180 degrees and then moving, and the rotation axis is a perpendicular line of the third heat exchange surface.
As shown in fig. 2, a plurality of first heat exchange surfaces 101 and second heat exchange surfaces 103 which are sequentially and alternately arranged are arranged on a heat exchange plate body along a longitudinal direction of the heat exchange plate body, the first heat exchange surfaces 101 and the second heat exchange surfaces 103 are connected through a third heat exchange surface 102, a longitudinal section of the first heat exchange surface 101 is in a corrugated shape formed by a plurality of convex portions 104 and concave portions 105 which are repeatedly and alternately arranged, a longitudinal section of the second heat exchange surface 103 is in a corrugated shape formed by a plurality of concave portions 105 and convex portions 104 which are repeatedly and alternately arranged, the convex portions 104 and the concave portions 105 of the first heat exchange surface 101 and the second heat exchange surface 103 on the same transverse plane are alternately arranged, the third heat exchange surface 102 is a plane, a horizontal plane of the concave portions 105 is higher than a horizontal plane of the third heat exchange surface 102, two sides of the third heat exchange surface 102 are respectively and smoothly transited with the first heat exchange surface 101 and the second heat exchange surface 103 to form grooves with an inverted cross section of an isosceles trapezoid, the heat exchange plate body is formed by integrally forming and repeatedly arranging the first heat exchange surface 101, the second heat exchange surface 103 and the third heat exchange surface 102, the heat exchange plate body is rectangular plate-shaped, the cross section of the concave part 105 is in an inverted isosceles trapezoid shape or an inverted arc shape, and the convex part 104 is in an isosceles trapezoid shape or an inverted arc shape, so that the heat exchange plate body is convenient to press process or punch process. The first heat exchange surface 102, the second heat exchange surface 103 and the third heat exchange surface 102 are formed integrally and repeatedly to form a heat exchange plate body, and the heat exchange plate body is rectangular plate-shaped. The cross section of the concave part is in an inverted isosceles trapezoid or arc shape, and the convex part is in an isosceles trapezoid or arc shape. A cold fluid channel is arranged in the heat exchange tube pass, and a hot fluid channel is arranged in the heat exchange shell pass. Fig. 4 is a sectional position view of the heat exchange core 1, in which section a-a and section B-B are schematic views of a hot flue gas flow passage. The difference between the A-A section and the B-B section results from the staggered arrangement of the high convex parts and the low convex parts, so that the hot flue gas channel is in a corrugated flow passage. The C-C and D-D sections are schematic views of the cold fluid flow channel. The difference of the C-C section and the D-D section is caused by the fact that high bulges and low bulges are sequentially and alternately arranged, so that a cold runner is a convergent-divergent runner, strip-shaped supporting plates are arranged at the inlet and the outlet of a hot fluid channel of the heat exchanger shell, the gap between the two strip-shaped supporting plates forms the inlet of the hot fluid channel, the edge of the heat exchange plate is fixedly welded with the inner wall of a cubic shell, a flow limiting plate is arranged at the inlet and the outlet of the cold fluid channel of the cubic shell, a plurality of hollowed-out openings are formed in the flow limiting plate, and the shape of the opening in the flow limiting plate is matched with the shape of a heat exchange tube on the cold fluid channel with one section.
According to the requirement of heat exchange quantity, the flow speed of hot flue gas flow and cold fluid can be adjusted by changing the structural size of the plate. As shown in fig. 5 and 6, the flue gas flow area can be adjusted by changing the distance between the heat exchange plate body 7 and the heat exchange plate body 8, the corrugation angle of the hot flue gas corrugation flow channel can be adjusted by changing the height, inclination angle and longitudinal width of the high convex portion and the low convex portion, and the disturbance degree of the hot flue gas can be adjusted by changing the width of the convex portion in the transverse direction. Meanwhile, as shown in fig. 7 and 8, the degree of scaling of the cold fluid is adjusted by changing the width and the inclination angle of the protrusion in the transverse direction, so that the degree of turbulence of the fluid is increased, and the heat transfer is enhanced.
The cross flow plate heat exchanger provided by the utility model is suitable for gas-gas and gas-liquid heat exchangers, such as air coolers, air preheaters, coal economizers and the like.
Claims (6)
1. The utility model provides a cross flow plate formula heat transfer board which characterized in that: the heat exchanger comprises a heat exchange core body, a heat exchanger shell, a hot flue gas inlet, a hot flue gas outlet and a cold fluid inlet, wherein the left side and the right side of the heat exchanger shell are respectively connected with the hot flue gas inlet and the hot flue gas outlet, the front side and the rear side of the heat exchanger shell are respectively connected with the cold fluid inlet and the cold fluid outlet, and a partition plate is respectively arranged between a heat exchanger shell and the cold fluid inlet and the cold fluid outlet; the heat transfer core is piled up by the multiunit heat transfer board and forms, every group heat transfer board comprises two heat transfer board bodies, the heat transfer board body that lies in upper portion between two heat transfer board bodies of every group and the heat transfer board body that lies in the lower part set up relatively and form a plurality of confined heat transfer tube sides in the depressed part, form the heat transfer shell side between adjacent two sets of heat transfer boards, upper portion heat transfer board body and lower part heat transfer board body symmetry set up in every group heat transfer board promptly, multiunit heat transfer board is located the casing and along the inside from the top down parallel arrangement in proper order of casing.
2. The cross flow plate heat exchanger plate of claim 1, wherein: the heat exchange plate comprises a heat exchange plate body and is characterized in that a plurality of first heat exchange surfaces and second heat exchange surfaces which are sequentially and alternately arranged are arranged on the heat exchange plate body along the longitudinal direction of the heat exchange plate body, the first heat exchange surfaces and the second heat exchange surfaces are connected through third heat exchange surfaces, the longitudinal sections of the first heat exchange surfaces are in a corrugated shape formed by a plurality of repeated and alternately arranged concave parts and convex parts, the longitudinal sections of the second heat exchange surfaces are in a corrugated shape formed by a plurality of repeated and alternately arranged convex parts and concave parts, the convex parts and the concave parts of the first heat exchange surfaces and the second heat exchange surfaces on the same transverse plane are alternately arranged, the third heat exchange surfaces are planes, the horizontal plane of the concave parts is higher than the horizontal plane of the third heat exchange surfaces, and the two sides of the third heat exchange surfaces are respectively in smooth transition with the first heat exchange surfaces and the second heat exchange surfaces to form grooves with cross sections of inverted isosceles trapezoids.
3. The cross flow plate heat exchanger plate of claim 2, wherein: the first heat exchange surface, the second heat exchange surface and the third heat exchange surface are integrally formed and repeatedly arranged to form a heat exchange plate body, and the heat exchange plate body is rectangular plate-shaped.
4. A cross flow plate heat exchanger plate according to claim 3, wherein: the cross section of the concave part is in an inverted isosceles trapezoid or arc shape, and the convex part is in an isosceles trapezoid or arc shape.
5. The cross flow plate heat exchanger plate of claim 4, wherein: a cold fluid channel is arranged in the heat exchange tube pass, and a hot fluid channel is arranged in the heat exchange shell pass.
6. The cross flow plate heat exchanger plate of claim 5, wherein: the heat exchanger shell is provided with strip-shaped supporting plates at the inlet and outlet of a hot fluid channel, the gap between the two strip-shaped supporting plates forms the inlet of the hot fluid channel, the edge of the heat exchange plate is fixedly welded with the inner wall of a cubic shell, the cubic shell is provided with a flow limiting plate at the inlet and outlet of a cold fluid channel, the flow limiting plate is provided with a plurality of hollowed-out openings, and the shape of the opening on the flow limiting plate is matched with the shape of a heat exchange tube on the cold fluid channel with one section.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202121896655.3U CN215832532U (en) | 2021-08-13 | 2021-08-13 | Cross flow plate type heat exchange plate |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202121896655.3U CN215832532U (en) | 2021-08-13 | 2021-08-13 | Cross flow plate type heat exchange plate |
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| CN215832532U true CN215832532U (en) | 2022-02-15 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202121896655.3U Active CN215832532U (en) | 2021-08-13 | 2021-08-13 | Cross flow plate type heat exchange plate |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115752040A (en) * | 2022-12-23 | 2023-03-07 | 宁波连通设备集团有限公司 | Plastic plate heat exchanger |
| CN116182179A (en) * | 2023-05-04 | 2023-05-30 | 南京宜热纵联节能科技有限公司 | Flue gas cooler |
| CN116592674A (en) * | 2023-07-19 | 2023-08-15 | 南京宜热纵联节能科技有限公司 | Efficient heat exchanger |
| CN116907239A (en) * | 2023-09-14 | 2023-10-20 | 山东大华环境节能科技有限公司 | Air cooler tube bundle |
-
2021
- 2021-08-13 CN CN202121896655.3U patent/CN215832532U/en active Active
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115752040A (en) * | 2022-12-23 | 2023-03-07 | 宁波连通设备集团有限公司 | Plastic plate heat exchanger |
| CN115752040B (en) * | 2022-12-23 | 2023-08-15 | 宁波连通设备集团有限公司 | Plastic plate heat exchanger |
| CN116182179A (en) * | 2023-05-04 | 2023-05-30 | 南京宜热纵联节能科技有限公司 | Flue gas cooler |
| CN116592674A (en) * | 2023-07-19 | 2023-08-15 | 南京宜热纵联节能科技有限公司 | Efficient heat exchanger |
| CN116592674B (en) * | 2023-07-19 | 2023-09-19 | 南京宜热纵联节能科技有限公司 | Efficient heat exchanger |
| CN116907239A (en) * | 2023-09-14 | 2023-10-20 | 山东大华环境节能科技有限公司 | Air cooler tube bundle |
| CN116907239B (en) * | 2023-09-14 | 2023-11-17 | 山东大华环境节能科技有限公司 | Air cooler tube bundle |
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