CN109163586B - Spiral runner printed circuit board heat exchanger - Google Patents
Spiral runner printed circuit board heat exchanger Download PDFInfo
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- CN109163586B CN109163586B CN201810897783.6A CN201810897783A CN109163586B CN 109163586 B CN109163586 B CN 109163586B CN 201810897783 A CN201810897783 A CN 201810897783A CN 109163586 B CN109163586 B CN 109163586B
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- 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
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D9/04—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being formed by spirally-wound plates or laminae
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Abstract
The invention discloses a spiral flow channel printed circuit board heat exchanger, which comprises an upper shell, a lateral shell and a lower shell, wherein a heat exchanger core body is arranged in a cavity formed by the upper shell, the lower shell and the lateral shell, the heat exchanger core body is formed by diffusion welding of a plurality of layers of heat exchange plates, a spiral flow channel is arranged on each heat exchange plate for a working medium to act, a heat medium inlet and a cold medium inlet are arranged on the lateral shell and are respectively communicated with a heat medium inlet and a cold medium inlet on the heat exchange plates, a heat medium outlet and a cold medium outlet are arranged on each heat exchange plate, and after heat exchange is carried out on the heat medium and the cold medium through the corresponding spiral flow channels, the heat medium and the cold medium are respectively output out of the upper. The invention has compact structure and small occupied volume, enhances the heat exchange effect, leads the pressure change to present stable transition, avoids the cavitation effect caused by the occurrence of a reverse flow zone and prolongs the service life of the heat exchanger.
Description
Technical Field
The invention relates to a heat exchanger, in particular to a spiral flow channel printed circuit board heat exchanger.
Background
In the 80 s of the 20 th century, the university of sydney, australia, invented a Printed Circuit board Heat Exchanger (PCHE), and then the british company, Heatric, produced products for use in the refrigeration and petrochemical industries. The heat exchange core body of the PCHE is formed by laminating a plurality of heat exchange plates, a micro-channel is processed on the surface of each heat exchange plate by using a chemical etching or laser corrosion process, the heat exchange plates are tightly connected by a diffusion welding technology, and the performance of a welding seam after diffusion welding can reach the standard consistent with that of a base material. The size of a flow channel of the PCHE is millimeter level, compared with the traditional heat exchanger, the PCHE has larger heat exchange area to volume ratio, Natesan et al compares the PCHE which is used as an intermediate heat exchanger with a shell-and-tube heat exchanger, the volume of the PCHE under the same heat transfer rate is only 1/30 of the shell-and-tube heat exchanger, and the compactness of the PCHE is very visible. Secondly, the printed circuit board heat exchanger has the advantages of high temperature resistance and high pressure resistance, and can be used as a heater, a preheater, a superheater, an evaporator and the like, so that the printed circuit board heat exchanger is very widely applied, is developed or applied in the aspects of solar power generation, nuclear energy utilization, industrial waste heat power generation and the like, and has potential application possibility in the fields of geothermal power generation, fuel cells, gas heating, gas turbines, ship waste heat power generation, aerospace and the like.
The heat exchange plate of traditional printed circuit board heat exchanger core is the direct current way form, although complicated runner heat exchangers such as Z style of calligraphy, wave type, airfoil section have also appeared in the later stage, but its compactness and heat transfer ability still can promote, and the backward flow district appears easily for the corner of complicated runner, influences heat exchanger comprehensive properties. Particularly, when the PCHE works at a high-temperature and high-pressure state, the PCHE generates reverse flow and simultaneously generates cavitation phenomenon, cavitation corrosion can be generated after a long time, the surface of the heat exchange plate is damaged, the heat exchange effect is influenced, and the service life of the heat exchanger is also shortened. The heat exchange plates connected together by diffusion welding cannot be repaired or replaced, and the cost is too high. Therefore, to avoid the above problems and achieve the purpose of enhancing the heat exchange performance, further improvement of the flow channel structure is required.
Disclosure of Invention
The technical problem to be solved by the present invention is to provide a spiral flow channel printed circuit board heat exchanger with improved heat exchange performance, aiming at the defects existing in the prior art.
The technical scheme adopted by the invention is as follows: the utility model provides a spiral flow channel printed circuit board heat exchanger, includes casing, side casing, lower casing, is equipped with the heat exchanger core in the cavity that casing and side casing formed from top to bottom, its characterized in that: the heat exchanger core body is formed by diffusion welding a plurality of layers of heat exchange plates, each heat exchange plate is provided with a spiral flow channel for a working medium to act, a heat medium inlet and a cold medium inlet which are respectively communicated with a heat medium inlet and a cold medium inlet on each heat exchange plate are arranged on the lateral shell, each heat exchange plate is provided with a heat medium outlet and a cold medium outlet which are respectively communicated with the flow channels arranged on the upper shell and the lower shell, and the heat medium and the cold medium are respectively output out of the upper shell and the lower shell through the heat medium outlets and the cold medium outlets after heat exchange is carried out through the corresponding spiral flow channels.
According to the technical scheme, the heat exchange plates are all of a circular structure, and spiral flow channels are processed on the surfaces of the heat exchange plates by means of a chemical etching technology or a laser corrosion technology to allow working media to circulate.
According to the technical scheme, the spiral flow channel in the spiral direction is arranged on the surface of the heat exchange plate, and the medium flow inlets of the spiral flow channels of the adjacent heat exchange plates are staggered by a certain angle, so that the cold medium inlet and the hot medium inlet are staggered by a certain angle.
According to the technical scheme, the medium inlets of the spiral flow channels of the adjacent heat exchange plates are staggered by 180 degrees, so that the cold medium inlets and the hot medium inlets are staggered by 180 degrees, and the medium outlets of the adjacent heat exchange plates are also staggered by 180 degrees, so that different working media flow out separately.
According to the technical scheme, the surface of the heat exchange plate is provided with two spiral flow channels in the spiral direction, namely the heat medium spiral flow channel and the cold medium spiral flow channel, and the inflow ports of the two medium spiral flow channels are arranged in a staggered mode at a certain angle, so that the heat medium inlet and the cold medium inlet arranged on the lateral shell are arranged in a staggered mode at a certain angle.
According to the technical scheme, the inflows of the two medium spiral flow channels are arranged in a staggered mode at an angle of 180 degrees, so that the cold medium inlet and the hot medium inlet are arranged in a staggered mode at an angle of 180 degrees.
According to the technical scheme, the heat medium outlet and the cold medium outlet are respectively semicircular and are symmetrically arranged relative to the center of the heat exchange plate.
According to the technical scheme, the cold medium inlet is a pit communicated with the corresponding spiral flow channel, and the hot medium inlet is a pit communicated with the corresponding spiral flow channel.
According to the technical scheme, the upper end and the lower end of the heat exchanger core body are respectively provided with the top cover plate and the bottom cover plate, the top cover plate and the bottom cover plate are respectively provided with a channel for outflow, and cold medium or heat medium flows out, and the centers of the upper shell and the lower shell are respectively provided with an output channel for outflow of the cold medium or the heat medium.
According to the technical scheme, the cross section of the flow channel is semicircular, rectangular, triangular, elliptical or trapezoidal, and is not limited to the above.
Generally, the heat exchange area per unit volume is used for evaluationCompactness of heat exchanger, denoted by j, in mm2/mm3. Taking heat exchange units of a straight flow channel and a spiral flow channel respectively, as shown in fig. 8(a), wherein r is the radius of the flow channel, L is the distance between adjacent flow channels, h is the thickness of a hot plate, and L is the length of the straight flow channel; in FIG. 8(b), l is the distance between adjacent channels, l0The radius of the spiral flow channel is the inner diameter (radius) of the area where the section of spiral flow channel is located, and alpha is a central angle corresponding to the spiral flow channel.
The calculation shows that the heat exchange area and the volume ratio of the two heat exchange units are consistent, but generally, the rectangular heat exchange units and the circular heat exchange units with the same area are stretched to have the same thickness, and the cuboids are always larger than the cylinders, so that the heat exchanger core body formed by the circular heat exchange plates of the spiral flow channels is more compact than the core body formed by the rectangular heat exchange plates of the linear flow channels.
Generally, the Knoop number Nu is used for representing the heat exchange performance of the heat exchanger, and the fanning friction coefficient f is used for representing the pressure drop performance of the heat exchanger, and is calculated according to the following formulas:
wherein k is the coefficient of thermal conductivity of the working medium, DhIs the hydraulic diameter of the flow channel, and q is the heat exchange coefficient;
in the formula, delta P is inlet-outlet pressure drop, L is runner length, rho is working medium density, and V is working medium flow velocity;
the calculation results are shown in fig. 9 and fig. 10, the working medium is supercritical carbon dioxide, under the specified working condition, the actual lengths of the linear flow channel and the spiral flow channel are the same, that is, the heat exchange areas are kept the same, along with the increase of the reynolds number, the heat exchange performance of the heat exchanger of the spiral flow channel is increased by 67% -155%, and the effect is very obvious.
The beneficial effects obtained by the invention are as follows:
(1) compared with a cubic heat exchange core body formed by linear runner heat exchange plates with the same area, the heat exchange core body formed by the spiral linear runner heat exchange plates is smaller in volume;
(2) the spiral flow channel heat exchanger can save the space of a collecting pipe (positioned at the inlet and the outlet of the heat exchange plate and used for distributing working media and collecting the working media respectively) of a linear flow channel, and further improves the compactness of equipment;
(3) when the same material is used, the heat exchange core body of the spiral flow channel is lighter in weight;
(4) enhancing the heat exchange efficiency: the curvature of the spiral flow channel is changed constantly, and compared with a linear flow channel printed circuit board heat exchanger with the same length, the spiral flow channel has larger local head loss, so that the action time of a medium in the flow channel is longer, and the heat exchange effect is better;
(5) the service life is prolonged: compared with the zigzag flow channel form with angle change, such as a trapezoid flow channel form and the like, the spiral line enables the pressure and the speed of the medium in the flowing process to realize stable transition, a reverse flow area can not appear, the generation of cavitation effect is inhibited, the heat exchange plate is protected, and the service life of the heat exchanger is prolonged.
Drawings
FIG. 1 is an overall assembly diagram of the present invention.
Fig. 2 is an exploded view of the present invention.
Fig. 3 shows a first embodiment of the heat exchanger plate according to the invention.
Fig. 4 is a side view of fig. 3.
Fig. 5 is a partially enlarged view of fig. 4 at II.
Fig. 6 shows a second embodiment of a heat exchanger plate according to the invention.
FIG. 7 is an embodiment of the cross-sectional shape of the flow channels of the heat exchanger plate of the present invention, wherein 7(a) is semi-circular; 7(b) rectangular; 7(c) a triangle; 7(d) elliptical; 7(e) trapezoid.
FIG. 8 is a comparison of the sizes of heat exchange units with different flow channels, wherein 8(a) is a straight flow channel; 8(b) is a spiral flow channel.
FIG. 9 is a comparison of the thermal performance of linear and spiral flow channels.
FIG. 10 is a comparison of linear and spiral flow channel cooling performance.
Detailed Description
The invention will be further explained with reference to the drawings.
As shown in the figure, the present embodiment provides a spiral flow channel printed circuit board heat exchanger, which includes an upper casing 1, a lateral casing 2, and a lower casing, wherein a flow channel 1-1 is formed in the center of the upper casing 1 and the center of the lower casing 1 for a medium to pass through. The heat exchanger comprises an upper shell, a lower shell, a side shell, a heat exchanger core body 4, a plurality of layers of heat exchange plates 4-2, a spiral flow channel, a circular structure and a heat exchanger core body 1, wherein the heat exchanger core body 4 is arranged in a cavity formed by the upper shell, the lower shell and the side shell, the heat exchanger core body 1 is formed by diffusion welding the plurality of layers of heat exchange plates 4-2, the spiral flow channel is arranged on each heat exchange plate and is used for a working medium to act, the heat. A heat medium inlet 3-1 and a cold medium inlet 3-2 are arranged on the lateral shell 2 and are respectively communicated with a heat medium inlet and a cold medium inlet on the heat exchange plates, a heat medium outlet and a cold medium outlet are arranged on each heat exchange plate 4-2 and are respectively communicated with flow channels arranged on the upper shell 1 and the lower shell, and after heat exchange is carried out on the heat medium and the cold medium through corresponding spiral flow channels, the heat medium and the cold medium are respectively output out of the upper shell and the lower shell through the heat medium outlet and the cold medium outlet.
The invention provides a spiral flow channel printed circuit board heat exchanger, the flow channel form of the heat exchange plate can be various:
in the first embodiment, a spiral flow channel 4-5 in a spiral direction is arranged on the surface of a heat exchange plate, and the arrow direction indicates the flowing direction of a medium; the medium inlets of the spiral flow channels of the adjacent heat exchange plates are staggered by 180 degrees, so that the cold medium inlet and the hot medium inlet of the lateral shell 2 are staggered by 180 degrees. Pits are processed near the edges of the heat exchange plates and connected with the spiral flow passages to form medium flow inlets 4-4. The medium inlets of the spiral flow channels of the adjacent heat exchange plates are staggered by 180 degrees, so that the cold medium inlet and the hot medium inlet are staggered by 180 degrees. The medium outflow channels 4-6 and the medium outflow ports 4-7 are respectively semicircular and are symmetrically arranged relative to the center of the heat exchange plate, wherein the medium outflow ports 4-7 are communicated with the spiral flow channel for outputting the medium on the heat exchange plate. While the medium outflow channels 4-6 are not in communication with the spiral flow channel for serving as an output channel for another medium. 4-6 and 4-7 can make the cold and hot working mediums on the heat exchange plates arranged at intervals freely flow without mutual interference. When the heat exchange plates are selected, medium flow inlets 4-4 of adjacent heat exchange plates are separated by 180 degrees, low-temperature medium and high-temperature medium enter a spiral flow channel at 180 degrees, naturally enter corresponding semicircular channels at outlets respectively and do not interfere with each other, a top cover plate 4-1 and a bottom cover plate 4-3 which are only provided with a semicircular through hole are arranged at the top and the bottom of a heat exchanger core respectively, the top cover plate and the bottom cover plate can be used as a closed port of one channel and an opening of the other channel, and finally the two semicircular channels are respectively connected with the channels of the upper shell and the lower shell to respectively output the media in the two channels.
In the second embodiment, the surface of the heat exchange plate is provided with two spiral flow channels in a spiral direction, namely a heat medium spiral flow channel and a cold medium spiral flow channel, wherein the heat medium and the cold medium flow on the same surface of the heat exchange plate, and the solid line arrow and the dotted line arrow represent the flow directions of the heat medium and the cold medium respectively; two grooves are arranged on the edge of the heat exchange plate 4-2 and are respectively connected with the two spiral flow channels to be used as medium inlets, the relative positions of the grooves are determined according to the processing or installation convenience or (not limited to 180 degrees), the embodiment is explained by taking the arrangement that the inlets of the two spiral flow channels are staggered by an angle of 180 degrees as an example, and the cold medium inlet and the hot medium inlet are staggered by an angle of 180 degrees. The heat medium outlet and the cold medium outlet are respectively semicircular and are symmetrically arranged relative to the center of the heat exchange plate. Are respectively communicated with the two spiral flow channels to be used as medium outlets. When the heat exchange plate is selected, only the inlets of the high-temperature medium or the low-temperature medium are ensured to be aligned respectively. Similarly, the top and the bottom of the core body part of the heat exchanger are provided with cover plates only provided with a semicircular through hole, the semicircular through holes at the top and the bottom are respectively connected with semicircular outlets of a high-temperature medium and a low-temperature medium, and simultaneously play a role of blocking another working medium so as to respectively output the high-temperature medium and the low-temperature medium.
The spiral flow channel printed circuit board heat exchanger provided by the invention has various flow channel section forms, as shown in fig. 6: as examples, the cross-sectional form of the flow channel may be semicircular, rectangular, triangular, oval, and trapezoidal, but is not limited to the above-mentioned forms.
Claims (8)
1. The utility model provides a spiral flow channel printed circuit board heat exchanger, includes casing, side casing, lower casing, is equipped with the heat exchanger core in the cavity that casing and side casing formed from top to bottom, its characterized in that: the heat exchanger core body is formed by diffusion welding a plurality of layers of heat exchange plates, each heat exchange plate is provided with a spiral flow passage for the action of a working medium, the side shell is provided with a heat medium inlet and a cold medium inlet which are respectively communicated with the heat medium inlet and the cold medium inlet on the heat exchange plate, each heat exchange plate is provided with a heat medium outlet and a cold medium outlet which are respectively communicated with the flow channels arranged on the upper shell and the lower shell, the heat medium and the cold medium respectively output out of the upper shell and the lower shell through the heat medium outlet and the cold medium outlet after heat exchange is carried out through the corresponding spiral flow channels, the surface of the heat exchange plate is provided with two spiral flow channels in a spiral direction, namely a heat medium spiral flow channel and a cold medium spiral flow channel, and the inflow inlets of the two medium spiral flow channels are arranged in a staggered mode at a certain angle, so that the heat medium inlet and the cold medium inlet arranged on the lateral shell are arranged in a staggered mode at a certain angle.
2. The spiral flow channel printed circuit board heat exchanger of claim 1, wherein: the heat exchange plates are all of circular structures, and spiral flow channels are processed on the surfaces of the heat exchange plates by means of a chemical etching technology or a laser corrosion technology to allow working media to circulate.
3. The spiral flow channel printed circuit board heat exchanger of claim 1, wherein: the medium inlets of the spiral flow channels of the adjacent heat exchange plates are staggered by 180 degrees, so that the cold medium inlet and the hot medium inlet are staggered by 180 degrees.
4. The spiral flow channel printed circuit board heat exchanger of claim 1, wherein: the inlets of the two medium spiral channels are arranged in a staggered way at an angle of 180 degrees, so that the cold medium inlet and the hot medium inlet are staggered at an angle of 180 degrees.
5. The spiral flow channel printed circuit board heat exchanger of claim 1, wherein: the heat medium outlet and the cold medium outlet are respectively semicircular and are symmetrically arranged relative to the center of the heat exchange plate.
6. The spiral flow channel printed circuit board heat exchanger of claim 1, wherein: the cold medium inlet is a pit which is communicated with the corresponding spiral flow channel and has the same depth, and the hot medium inlet is a pit which is communicated with the corresponding spiral flow channel.
7. The spiral flow channel printed circuit board heat exchanger of claim 1, wherein: the upper end and the lower end of the heat exchanger core body are respectively provided with a top cover plate and a bottom cover plate, the top cover plate and the bottom cover plate are respectively provided with a channel for outflow, and a cooling medium or a heat medium flows out, and the centers of the upper shell and the lower shell are respectively provided with an output channel for outflow of the cooling medium or the heat medium.
8. The spiral flow channel printed circuit board heat exchanger of claim 1, wherein: the cross section of the flow channel is semicircular, rectangular, triangular, elliptical or trapezoidal.
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| CN201810897783.6A CN109163586B (en) | 2018-08-08 | 2018-08-08 | Spiral runner printed circuit board heat exchanger |
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| CN201810897783.6A CN109163586B (en) | 2018-08-08 | 2018-08-08 | Spiral runner printed circuit board heat exchanger |
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Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN110686550A (en) * | 2019-11-18 | 2020-01-14 | 西安热工研究院有限公司 | Compact uniform transition interface of printed circuit board heat exchanger and preparation process thereof |
| CN112179172A (en) * | 2020-09-02 | 2021-01-05 | 东南大学 | Plate-type diffusion welding compact heat exchanger with cold and hot fluids arranged on same layer |
| CN111998553B (en) * | 2020-09-22 | 2024-06-18 | 陈安祥 | Solar water heating system |
| CN112629295B (en) * | 2020-12-30 | 2022-07-12 | 大连海事大学 | Novel printed circuit board type heat exchanger core body of three-dimensional spiral winding type runner |
| CN115031423B (en) * | 2022-06-10 | 2023-04-11 | 浙江青风环境股份有限公司 | Water chilling unit with vortex disc type micro-channel heat exchanger |
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| US705614A (en) * | 1901-03-01 | 1902-07-29 | Julien W Mathis | Radiator. |
| GB450665A (en) * | 1935-03-28 | 1936-07-22 | Curt Fredrik Rosenblad | Improvements in plate heat-exchangers for fluids |
| US2131265A (en) * | 1937-03-01 | 1938-09-27 | Dow Chemical Co | Spiral heat interchanger and method of making same |
| CN203053281U (en) * | 2013-01-16 | 2013-07-10 | 台州恒之泰医化设备有限公司 | Spiral-plate heat exchanger |
-
2018
- 2018-08-08 CN CN201810897783.6A patent/CN109163586B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US705614A (en) * | 1901-03-01 | 1902-07-29 | Julien W Mathis | Radiator. |
| GB450665A (en) * | 1935-03-28 | 1936-07-22 | Curt Fredrik Rosenblad | Improvements in plate heat-exchangers for fluids |
| US2131265A (en) * | 1937-03-01 | 1938-09-27 | Dow Chemical Co | Spiral heat interchanger and method of making same |
| CN203053281U (en) * | 2013-01-16 | 2013-07-10 | 台州恒之泰医化设备有限公司 | Spiral-plate heat exchanger |
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