CN114993079A - Design method of printing plate type micro-channel heat exchanger and micro-channel heat exchanger - Google Patents

Design method of printing plate type micro-channel heat exchanger and micro-channel heat exchanger Download PDF

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CN114993079A
CN114993079A CN202210492203.1A CN202210492203A CN114993079A CN 114993079 A CN114993079 A CN 114993079A CN 202210492203 A CN202210492203 A CN 202210492203A CN 114993079 A CN114993079 A CN 114993079A
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channel
flow
heat exchanger
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齐宏
余智强
林鹏
于喜奎
吴建泽
任亚涛
何明键
高包海
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Harbin Institute of Technology
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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
    • F28D9/0031—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 for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0037—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 for one heat-exchange medium being formed by paired plates touching each other the conduits for the other heat-exchange medium also being formed by paired plates touching each other
    • 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
    • F28F3/08—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/04—Arrangements for sealing elements into header boxes or end plates
    • F28F9/06—Arrangements for sealing elements into header boxes or end plates by dismountable joints
    • F28F9/12—Arrangements for sealing elements into header boxes or end plates by dismountable joints by flange-type connections
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
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Abstract

A design method of a printing plate type micro-channel heat exchanger and the micro-channel heat exchanger belong to the technical field of heat exchangers. The heat exchanger aims to solve the problems that a unified design flow is not formed in the existing design method of the micro-channel heat exchanger, customized designs are often adopted for different application scenes and heat exchange requirements, a heat exchanger structure with relatively good performance is obtained through a large amount of simulation analysis and structural improvement, the production process of the heat exchanger is complex, the manufacturing cost is high, and a large amount of trial and error cost is required for the complex design flow. The invention provides a design method of a printed board type micro-channel heat exchanger, and designs a set of micro-channel heat exchanger by the method, which is suitable for the design of heat exchangers with different application scenes and heat exchange requirements, simplifies the design flow, avoids the trial and error cost for repeated model selection in the design process of a customized heat exchanger, and improves the design efficiency to a certain extent. The invention is mainly used for the design of the micro-channel heat exchanger and the heat exchange by utilizing the heat exchanger.

Description

Design method of printing plate type micro-channel heat exchanger and micro-channel heat exchanger
Technical Field
The invention belongs to the technical field of heat exchangers, and particularly relates to a design method of a printed plate type micro-channel heat exchanger and the micro-channel heat exchanger.
Background
The printed plate type microchannel heat exchanger (PCHE) is mainly applied to the fields of energy power, chemical engineering, electric machinery, aerospace and the like, and has the characteristics of high heat transfer efficiency, compact structure, strong adaptability and the like.
Printed plate microchannel heat exchangers (PCHE), are currently a new type of heat exchanger that is highly efficient and compact. The main heat exchange element is a heat exchange plate, a microchannel is processed on a metal plate by methods such as chemical etching, a cold-side heat exchange plate and a hot-side heat exchange plate are overlapped and arranged together to form a multilayer metal plate structure, all the plates are combined together by modes such as vacuum diffusion welding to form a printed plate type microchannel heat exchanger (PCHE), and cold fluid and hot fluid exchange heat through the plates to realize high-efficiency heat exchange.
The flow and heat exchange characteristics inside the printed plate type microchannel heat exchanger (PCHE) are influenced by the micro-scale effect, and the traditional calculation method is not suitable any more, so that the design method suitable for the conventional heat exchanger cannot be used for the structural design of the printed plate type microchannel heat exchanger (PCHE). At present, a unified design flow and a design method are not formed for the design of a printed board type microchannel heat exchanger (PCHE), customized designs are often adopted for different application scenes and heat exchange requirements, a heat exchanger structure with relatively good performance is obtained through a large amount of simulation analysis and structural improvement, the production process of the heat exchanger is complex, the manufacturing cost is high, and a large amount of trial and error cost is required for the complex design flow. Based on the design method, the invention provides a typical printing plate type microchannel heat exchanger (PCHE) overall structure and heat exchange plate structure suitable for a high-temperature and high-pressure heat exchange environment, and the design method is suitable for heat exchange working media with liquid on the cold side and the hot side.
Disclosure of Invention
The technical problems to be solved by the invention are as follows: the existing design method of the micro-channel heat exchanger does not form a uniform design flow, customized designs are often adopted for different application scenes and heat exchange requirements, a heat exchanger structure with relatively good performance is obtained through a large amount of simulation analysis and structural improvement, the production process of the heat exchanger is complex, the manufacturing cost is high, and a large amount of trial and error cost is required for the complex design flow; further provides a design method of the printed board type microchannel heat exchanger and the microchannel heat exchanger.
The technical scheme adopted by the invention for solving the technical problems is as follows:
a design method suitable for a printing plate type micro-channel heat exchanger comprises the following specific design steps:
step 1, structure screening: based on the whole size constraint range of the heat exchanger and the size constraint range of the internal channel, the size, the total heat exchange area, the compactness and the heat exchanger quality of the pre-designed heat exchanger are screened, an optimization method is adopted to perform circular search in the size range of geometric constraint, and the structure meeting the set conditions is output as an effective structure I;
step 2, performance screening: based on a mathematical model, calculating the heat transfer characteristic and the flow characteristic of an effective structure I meeting the structural requirements, and outputting a structure meeting the structural requirements and the performance requirements as an effective structure II;
step 3, applicability screening: establishing a full-working-condition combination according to the flow range, the temperature range and the pressure range of working media at the cold side and the hot side in the practical application process of the heat exchanger, and then carrying out the calculation of the comprehensive performance under the full working condition on the effective structure II based on a heat transfer characteristic calculation model and a flow characteristic calculation model; and (3) establishing different operation condition parameter combinations capable of covering all research ranges by taking the performance design requirements as screening conditions, calculating one by one, and screening the effective structure II with the maximum number of parameter combinations with comprehensive performance meeting the design requirements under the condition of all condition parameter combinations as a final structure.
A printed board type micro-channel heat exchanger suitable for high-pressure thermal environment comprises two heat exchange cover plates, a plurality of cold flow heat exchange core plates, a plurality of hot flow heat exchange core plates, four connecting seal heads and four connecting flanges, wherein the shapes and the sizes of the plates of the heat exchange cover plates, the cold flow heat exchange core plates and the hot flow heat exchange core plates are the same, the plurality of cold flow heat exchange core plates and the plurality of hot flow heat exchange core plates are longitudinally overlapped and arranged between the two heat exchange cover plates and form a convection heat exchange plate group with the two heat exchange cover plates, the convection heat exchange plate group comprises cold flow heat exchange channels and hot flow heat exchange channels, the four connecting seal heads are respectively connected at two opposite corners of the convection heat exchange plate group, the two connecting seal heads at one opposite corner are respectively communicated with the cold flow heat exchange channels, the two connecting seal heads at the other opposite corner are respectively communicated with the hot flow heat exchange channels, and the cold flow heat exchange channels and the hot flow heat exchange channels achieve the purpose of heat exchange, each connecting end socket is connected with a corresponding pipeline through a connecting flange.
Compared with the prior art, the invention has the following beneficial effects:
1. the invention provides a design method of a printed board type micro-channel heat exchanger, which is suitable for designing heat exchangers with different application scenes and heat exchange requirements, simplifies the design process, avoids trial and error cost for repeated model selection of a customized heat exchanger in the design process, and improves the design efficiency to a certain extent.
2. The invention designs a set of micro-channel heat exchanger by utilizing the design method of the printing plate type micro-channel heat exchanger, the arrangement and the trend of the flow channels of the completely overlapped part of the cold flow heat exchange channel and the heat flow heat exchange channel in the micro-channel heat exchanger are completely consistent, and the flow channel arrangement of the partially overlapped part has the staggered phenomenon.
3. In the microchannel heat exchanger, the whole cold flow microchannel set or the heat flow microchannel set only has two turning points in the design process of the channels, so that the pressure loss generated by the working medium in the process of flowing through the turning points can be reduced;
4. compared with the traditional heat exchanger, the heat transfer efficiency of the invention can reach more than 93 percent, and the compactness is not less than 1500m 2 /m 3 (ii) a The application temperature range is-200 ℃ to 800 ℃, and the highest bearing pressure exceeds 4 MPa; under the condition that the heat exchange quantity is the same as that of the traditional heat exchanger, the volume of the printed plate type micro-channel heat exchanger can be reduced by 3 to 5 times, and the weight is light by 1 to 2 times; the application scene is complex, and the method can be used for both gaseous working media and liquid working media.
Drawings
The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this application, illustrate embodiment(s) of the invention and together with the description serve to explain the invention without limiting the invention to its proper form.
FIG. 1 is a schematic flow diagram of the design of the structural core of a printed plate microchannel heat exchanger;
FIG. 2 is a schematic structural diagram of the calculation of the Heat Transfer characteristics of an effective structure I, wherein Hot Side represents the Cold Side, Fouling Layer represents the Fouling Layer, Heat Transfer Surface represents the Heat Transfer Surface, and Cold Side represents the Hot Side;
FIG. 3 is a schematic diagram of the flow behavior calculation for "effective Structure I";
FIG. 4 is a schematic flow chart of calculating heat transfer characteristics and flow characteristics based on a mathematical model of heat transfer characteristics and a mathematical model of flow characteristics;
FIG. 5 is an isometric view of a printed plate microchannel heat exchanger;
FIG. 6 is a schematic diagram of working medium flow and heat exchange of the printing plate type microchannel heat exchanger;
FIG. 7 is an exploded view of the overall structure of a printed plate type microchannel heat exchanger;
FIG. 8 is a schematic diagram of a printed plate microchannel heat exchanger assembly construction;
FIG. 9 is a schematic view of a cold flow heat exchange core plate engraved with "straight" cold flow microchannels;
FIG. 10 is a schematic view of a heat flow heat exchange core plate engraved with "straight" heat flow microchannels;
FIG. 11 is a schematic view of a cold flow heat exchange channel and a hot flow heat exchange channel stacked alternately;
FIG. 12 is a schematic view of the fusiform cross-over overlap of the cold and hot heat exchange channels;
FIG. 13 is an enlarged view of a portion of FIG. 9 at A;
FIG. 14 is a cross-sectional view taken at B-B of FIG. 10;
FIG. 15 is an enlarged view of a portion of FIG. 14 at C;
FIG. 16 is a schematic view of a cold flow heat exchange core plate of "sinusoidal" cold flow microchannels;
FIG. 17 is a schematic view of a heat flow heat exchange core plate of a "sinusoidal" heat flow microchannel;
FIG. 18 is an enlarged view of a portion of FIG. 16 at D;
fig. 19 is a three-dimensional schematic view of a connection head and a connection flange.
In the figure: 1-a heat exchange cover plate; 2-cold flow heat exchange core plate; 2-1-cold flow microchannels; 3-heat flow heat exchange core plate; 3-1-heat flow microchannels; 4-connecting a seal head; 5-a connecting flange; 6-rectangular plate; 7-hexagonal plate pieces; 8-a flow splitting section; 9-intermediate overlap section; 10-turning transition section; 10-1-turning section one; 10-2-turning section two; 11-an inlet section; 12-an outlet section; 13-a first connection; 14-a second connection.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and the following embodiments are used for illustrating the present invention and are not intended to limit the scope of the present invention.
In the description of the present invention, it should be noted that the terms "upper", "lower", "inside", "outside", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience in describing the present invention and simplifying the description, but do not indicate or imply that the referred device or element must have a specific orientation, be constructed in a specific orientation, and be operated, and thus, should not be construed as limiting the present invention.
In the description of the present invention, it should be noted that, unless otherwise explicitly specified or limited, the terms "mounted" and "connected" are to be construed broadly, e.g., as being fixed or detachable or integrally connected; can be mechanically or electrically connected; may be directly connected or indirectly connected through an intermediate. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
Referring to fig. 1, fig. 2, fig. 3 and fig. 4, an embodiment of the present application provides a design method for a printed plate type microchannel heat exchanger, the core of the design method includes three parts, namely, a structure screening, a performance screening and a suitability screening, and the specific design steps are as follows:
step 1, structure screening: based on the whole size constraint range of the heat exchanger and the size constraint range of an internal channel, the actual requirements such as the volume, the total heat exchange area, the compactness and the heat exchanger quality of a pre-designed heat exchanger are screened, an optimization method such as an exhaustion method, an ant colony optimization algorithm or a genetic algorithm can be adopted to carry out cyclic search in the size range of the geometric constraint, the circular search is carried out by the exhaustion method, a structure meeting the set conditions (the volume, the total heat exchange area, the compactness and the heat exchanger quality of the heat exchanger) is output as an effective structure I, and if the effective structure I is not output, the geometric constraint is readjusted due to the fact that the geometric constraint is input and the design requirement are unbalanced;
step 2, performance screening: based on a mathematical model, calculating the heat transfer characteristic and the flow characteristic of the 'effective structures I' meeting the structural requirements, namely screening the pressure loss and heat exchange quantity conditions of each 'effective structure I', and outputting the structure meeting the structural requirements and the performance requirements as an 'effective structure II';
the heat transfer characteristics of the "effective structure i" were obtained by the following three part calculation:
for the calculation of the convective heat transfer coefficient h, solving is carried out based on the relation between the convective heat transfer coefficient h and the Nusselt number, the Nusselt number is solved by taking the square root of the sectional area as a characteristic size, and the solving correlation formula is as follows:
Figure RE-GDA0003782454350000041
Figure RE-GDA0003782454350000051
Figure RE-GDA0003782454350000052
Figure RE-GDA0003782454350000053
m＝2.27+1.65Pr 1/3 ,0.1＜Pr＜∞,
Figure RE-GDA0003782454350000054
Figure RE-GDA0003782454350000055
Figure RE-GDA0003782454350000056
in the formula (I), the compound is shown in the specification,
Figure RE-GDA0003782454350000057
denotes the number of Nusselt by taking the square root of the cross-sectional area as the characteristic dimension,
Figure RE-GDA0003782454350000058
representing the Reynolds number with the square root of the cross-sectional area as the characteristic dimension, Pr representing the Prandtl number, C 1 ～C 4 Represents a correlation coefficient, m c B and B
Figure RE-GDA0003782454350000059
16, 425 and 1700, respectively;
Figure RE-GDA00037824543500000510
representing dimensionless mean wall shear stress, K td Represents a correction coefficient, and TC represents a thermal correction coefficient;
Figure RE-GDA00037824543500000511
the dimensionless thermal length with the square root of the cross-sectional area as the characteristic dimension is shown, epsilon indicates the channel aspect ratio, and gamma indicates the shape factor. The subscript s represents the solid side, f the fluid side,
Figure RE-GDA00037824543500000512
indicating the characteristic dimension as the square root of the cross-sectional area, L the channel length, m; the subscripts Lam, Tur denote Laminar (Laminar) and turbulent (Turbulence), respectively;
for the calculation of the total heat transfer coefficient UA, considering that the PCHE channel is narrow and the heat exchange working medium has high cleanliness, the fouling thermal resistance R can be ignored d So it is mainly influenced by convective thermal resistance and thermal conductive thermal resistance, and the expression is:
Figure RE-GDA00037824543500000513
Figure RE-GDA0003782454350000061
in the formula eta o Expressing the thermal efficiency of the fin assembly, eta fin Fin efficiency; h represents the convective heat transfer coefficient, W/(m) 2 K); a represents the total heat exchange area, m 2 (ii) a K represents the material thermal conductivity, W/(m.K); a represents the inter-channel grid thickness, m; subscript total denotes total, fin denotes a fin portion, s denotes a solid side, wall denotes a wall surface;
for the calculation of the total heat exchange quantity q, because the PCHE mostly adopts a counter-flow structure to carry out convection heat exchange, the calculation of the total heat exchange quantity is calculated based on the logarithmic mean temperature, and the definition formula is as follows:
q＝UA·ΔT LMTD
Figure RE-GDA0003782454350000062
Figure RE-GDA0003782454350000063
Figure RE-GDA0003782454350000064
wherein q represents the total heat exchange amount, W; delta T LMTD Represents the log mean temperature, K; UA represents the total heat transfer coefficient of the heat exchanger, W/(m) 2 K); c is the heat capacity of the heat exchange working medium, W/(s.K); epsilon represents the heat exchanger efficiency, NTU represents the heat exchange unit; t represents a temperature;
Figure RE-GDA0003782454350000065
represents the mass flow rate, kg/s; c. C p J/(kg. K) represents a constant-pressure specific heat capacity; c represents the heat capacity of the heat exchange working medium at the hot side; the subscripts h, c represent the hot and cold sides, respectively, and in represents the inlet side.
The flow characteristics of the heat exchanger are influenced by the flow pressure drop Δ p in the core of the heat exchanger core Pressure drop Δ p at the inlet and outlet of the channel contraction 、Δp expansion Pressure drop Δ p in the inlet and outlet flow distribution headers heade The flow characteristics of the "effective structure i" are thus obtained by the following three-part calculation:
for the flow pressure drop Δ p in the core of the heat exchanger core The pressure loss in the heat exchanger core is mainly composed of three parts, respectively the pressure loss Δ p due to friction friction Pressure loss Δ p due to change in momentum ratio acceleration And pressure loss Δ p due to channel break angle angle The expression is as follows:
Figure RE-GDA0003782454350000066
in the formula, D h Represents the channel equivalent diameter, m; l represents the channel length, m; the subscript out denotes the exit side.
Pressure loss Δ p caused by friction in the core of the heat exchanger friction Considering both the surface friction and the shape resistance effect, if any additional losses due to internal contraction and expansion caused by the change in the flow area of the flowing working medium also need to be taken into the heat exchange core friction loss term, the friction pressure drop in the heat exchange core is given by:
Figure RE-GDA0003782454350000071
Figure RE-GDA0003782454350000072
wherein G represents the mass velocity in the micro-channel of the heat exchanger, kg/s; τ represents the channel aspect ratio; rho represents the density of the working medium, kg/m 3 ；
Figure RE-GDA0003782454350000073
Square root based on cross-sectional area
Figure RE-GDA0003782454350000074
Dimensionless hydrodynamic length of (a);
pressure loss Δ p due to momentum change in heat exchange core acceleration Due to the fact that the fluid is heated or cooled, resulting in momentum rate changes or flow acceleration or deceleration effects within the heat exchanging core, positive values indicate a pressure drop at flow acceleration and negative values indicate a pressure rise at flow deceleration, the resulting pressure drop being given by:
Figure RE-GDA0003782454350000075
when fluid passes through a bent channel, an inward radial force is inevitably acted on the fluid, the pressure on the outer wall surface is increased, the pressure loss is generated on the inner wall surface, and due to the existence of flow inertia, a vortex area formed by separating a streamline is generated towards the inner side of the bent pipe and the bent pipe, so that the pressure loss delta p is locally generated angle The expression is as follows:
Figure RE-GDA0003782454350000076
Figure RE-GDA0003782454350000077
in the formula, ζ angle Representing the local resistance coefficient in the folded pipe; phi represents the angle of the channel turning angle, °;
pressure drop Δ p for inlet and outlet flare portions of a channel contraction 、Δp expansion The pressure loss in the inlet and outlet sections of the channel is mainly caused by two factors, namely: the pressure drop due to the change in cross-sectional flow area, the pressure loss due to irreversible free expansion and momentum change without considering friction, is given by:
Figure RE-GDA0003782454350000078
in the formula, σ represents the ratio of the free flow area and the windward area of the core, namely porosity, also called the contraction ratio; k c And K e A function representing the geometry of the contraction and expansion segments;
for pressure drop Δ p in inlet and outlet flow distribution header The flow distribution and collection are completed through the end socket structures on the inlet side and the outlet side, the pressure loss in the end socket structures is a part of the total pressure drop of the heat exchanger, the part of calculation belongs to macroscopic pressure loss calculation, and the expression of the part of pressure loss is as follows:
Figure RE-GDA0003782454350000081
Figure RE-GDA0003782454350000082
in the formula, ζ expansion Denotes the local pressure loss coefficient, ζ contraction A local pressure loss coefficient; k con,1 、 K con,2 Coefficients associated with head taper are θ and F 2 /F 1 A function of (a); f 1 、F 2 Cross-sectional areas of circular and rectangular ends of the head structure, respectively (F) 1 <F 2 )；c 0 ＝λl/D h λ represents the Darcy friction coefficient, D h A characteristic dimension for closure head configuration; c. C 1 Is l/D o Is the length of the closure head, D o The diameter of the round tube of the transport channel, m.
In summary, the mathematical model calculation correlation for the flow behavior of "effective Structure I" is as follows:
Figure RE-GDA0003782454350000083
step 3, applicability screening: establishing a full working condition combination according to the flow range, the temperature range and the pressure range of the working media at the cold side and the hot side in the practical application process of the heat exchanger, and then carrying out the calculation of the comprehensive performance under the full working condition on the effective structure II based on the calculation model; and (3) establishing different operation condition parameter combinations capable of covering all research ranges by taking the performance design requirements as screening conditions, and calculating one by one. And screening the effective structure II with the maximum number of parameter combinations with comprehensive performance meeting the design requirements under the condition of all-working-condition parameter combination as a final structure.
Through the three screening steps, two situations exist: firstly, a structural parameter set of an effective structure II can be obtained theoretically, the effective structure II comprises one or more heat exchanger structures meeting conditions, and then the most appropriate structure is screened out according to actual needs; secondly, in the screening process, if none of the structures meets the screening condition, the screening process needs to return to the previous step or the initial structure part, review whether the defined structure range, working condition conditions, screening requirements and the like are unreasonable, and reset for screening calculation.
Referring to fig. 5 to 19, the embodiment of the present application provides a printed plate type microchannel heat exchanger suitable for high pressure thermal environment, which includes two heat exchange cover plates 1, a plurality of cold flow heat exchange core plates 2, a plurality of hot flow heat exchange core plates 3, four connecting seal heads 4 and four connecting flanges 5, wherein the heat exchange cover plates 1, the cold flow heat exchange core plates 2 and the hot flow heat exchange core plates 3 have the same plate shape and size, the plurality of cold flow heat exchange core plates 2 and the plurality of hot flow heat exchange core plates 3 are longitudinally overlapped and arranged between the two heat exchange cover plates 1 and form a convective heat exchange plate assembly with the two heat exchange cover plates 1, the convective heat exchange plate assembly includes a cold flow heat exchange channel and a hot flow heat exchange channel, the four connecting seal heads 4 are respectively connected to two opposite corners of the convective heat exchange plate assembly, the two connecting seal heads 4 at one opposite corner are respectively communicated with the cold flow heat exchange channel, the two connecting seal heads 4 at the other opposite corner are respectively communicated with the hot flow heat exchange channel, the cold flow heat exchange channel and the hot flow heat exchange channel exchange heat in a convection mode to achieve the purpose of heat exchange, and each connecting end socket 4 is connected with a corresponding pipeline through one connecting flange 5.
In this embodiment, the heat exchange cover plate 1 is two relatively thick metal plates, the width of the connection portion reserved on the two sides of the cold flow heat exchange core plate 2 and the hot flow heat exchange core plate 3 is basically kept consistent, the thickness of the heat exchange cover plate 1 can be increased along with the increase of the operating pressure, and generally, when the design pressure of the printed plate type microchannel heat exchanger is 4MPa, the thickness of the heat exchange cover plate 1 is about 12 mm. The heat exchange cover plates 1 are arranged above and below a heat exchange core composed of the cold flow heat exchange core plate 2 and the heat flow heat exchange core plate 3, the purpose is to provide strength support for the heat exchange core of the printed plate type micro-channel heat exchanger PCHE, and the stability and the strength of the printed plate type micro-channel heat exchanger in working under a certain pressure environment are realized.
In this embodiment, as shown in fig. 5 to 8, the connecting end enclosure 4 and the connecting flange 5 are divided into two groups, wherein one group of the connecting end enclosure 4 and the connecting flange 5 corresponds to a cold flow heat exchange channel for connecting the cold flow heat exchange channel with an inlet pipeline and an outlet pipeline of a low-temperature working medium, respectively, and the other group of the connecting end enclosure 4 and the connecting flange 5 corresponds to a hot flow heat exchange channel for connecting the hot flow heat exchange channel with an inlet pipeline and an outlet pipeline of a high-temperature working medium, respectively; because two connecting seal heads 4 and connecting flanges 5 in each group are arranged in an oblique diagonal manner, and two groups of connecting seal heads 4 and connecting flanges 5 are arranged in a cross manner, low-temperature working media in a cold flow heat exchange channel and high-temperature working media in a hot flow heat exchange channel are overlapped in the flowing process, and the purpose of heat exchange is achieved. Meanwhile, the connecting end socket 4 also realizes the purpose of uniformly distributing the flow of the heat exchange working medium entering the heat exchange channel. As shown in fig. 3, a low-temperature working medium (or a high-temperature working medium) enters from an inlet of one connecting end enclosure 4 of the heat exchanger, passes through a cold-flow heat exchange channel (or a hot-flow heat exchange channel) and flows out from the other connecting end enclosure at the opposite angle, a high-temperature working medium (or a low-temperature working medium) enters from an inlet of one connecting end enclosure 4 of the heat exchanger, passes through a hot-flow heat exchange channel (or a cold-flow heat exchange channel) and flows out from the other connecting end enclosure at the opposite angle, heat exchange is realized in a middle convection heat exchange plate set, it can be seen from fig. 3 that the internal flow of the heat exchanger is quasi-countercurrent convection heat exchange, and after heat exchange is completed, the heat exchange working medium flows out from respective outlets. The mode of countercurrent heat exchange is adopted, so that the total heat exchange quantity of heat exchange is favorably improved, and the balance of the whole temperature distribution of the heat exchanger is realized.
In the embodiment, the cold flow heat exchange core plates 2 and the hot flow heat exchange core plates 3 can be designed in an alternating mode, so that the uniformity and the efficiency of heat exchange are ensured; the number of the cold flow heat exchange core plates 2 and the number of the hot flow heat exchange core plates 3 which are overlapped up and down can be changed according to working conditions, and if the heat exchange requirement of the hot flow heat exchange channel is strong and the heat carrying capacity of the cold flow heat exchange channel is insufficient, the number of the cold flow heat exchange core plates which are arranged at intervals can be increased to two or three; conversely, the number of heat flow heat exchange core plates can be increased.
In the embodiment, two adjacent heat exchange core plates are connected by vacuum diffusion welding, the upper end of a connecting end enclosure 4 is connected to the heat exchange cover plate 1 above the connecting end enclosure 4 by welding, the lower end of the connecting end enclosure 4 is connected to the heat exchange cover plate 1 below the connecting end enclosure 4 by welding, and two sides of the connecting end enclosure 4 are connected to the end faces of two ends of the superposed heat exchange core plates forming the cold flow heat exchange channel or the hot flow heat exchange channel by welding;
in this embodiment, the invention provides a printed plate type microchannel heat exchanger (PCHE) which is safe and reliable and is suitable for a high-pressure heat exchange environment, so as to provide an available structure type in a design process of the printed plate type microchannel heat exchanger (PCHE), so as to solve the problem that the design of the printed plate type microchannel heat exchanger (PCHE) is not systematized, simplify the design flow to a certain extent, avoid trial and error cost paid by repeated model selection in the design process, and improve the design efficiency to a certain extent.
In a possible embodiment, a plurality of cold flow microchannels 2-1 arranged side by side at equal intervals are arranged on the upper surface of the cold flow heat exchange core plate 2 and form a cold flow microchannel group, and the cold flow microchannel group on the cold flow heat exchange core plate 2 and the lower surface of the upper plate sheet adjacent to the cold flow microchannel group form a cold flow heat exchange channel; the ports at the two ends of the cold flow heat exchange channel are respectively flush with the ends at the two ends of the cold flow heat exchange core plate 2; a plurality of heat flow micro-channels 3-1 which are arranged side by side at equal intervals are arranged on the upper surface of the heat flow heat exchange core plate 3 and form a heat flow micro-channel group, and the heat flow micro-channel group on the heat flow heat exchange core plate 3 and the lower surface of the adjacent upper plate form a heat flow heat exchange channel; the ports of the two ends of the heat flow heat exchange channel are respectively flush with the ends of the two ends of the heat flow heat exchange core plate 3; the cold flow micro-channel set on the cold flow heat exchange core plate 2 and the hot flow micro-channel set on the hot flow heat exchange core plate 3 are arranged in an axial symmetry manner; the overlapped part of the cold flow heat exchange channel and the hot flow heat exchange channel is in a spindle shape.
In this embodiment, as shown in fig. 11 and 12, the arrangement and the trend of the flow channels of the completely overlapped portions of the cold flow heat exchange channel and the hot flow heat exchange channel are completely consistent, and the flow channels of the partially overlapped portions are arranged in a staggered manner, so that the heat exchange area of the cold flow heat exchange channel and the heat flow heat exchange channel can be increased, and the heat exchange efficiency of the heat exchanger can be increased within a limited space range.
In a possible embodiment, the cold flow micro-channel set and the hot flow micro-channel set are arranged in a zigzag manner, the cold flow micro-channel set and the hot flow micro-channel set each include a middle overlapping section 9, two turning transition sections 10, two shunt sections 8, an inlet section 11 and an outlet section 12, the working medium outlet end of the inlet section 11 is communicated with the working medium inlet end of one of the turning transition sections 10, the working medium outlet end of one of the turning transition sections 10 is communicated with the working medium inlet end of one of the shunt sections 8, the working medium outlet end of one of the shunt sections 8 is communicated with the working medium inlet end of the middle overlapping section 9, the working medium outlet end of the middle overlapping section 9 is communicated with the working medium inlet end of the other turning transition section 10, the working medium outlet end of the other turning transition section 10 is communicated with the working medium inlet end of the other shunt section 8, the working medium outlet end of the other section of the flow distribution section 8 is communicated with the working medium inlet end of the outlet section 12; each section of the shunting section 8 and the middle overlapping section 9 are arranged in an obtuse angle.
In the embodiment, the cold flow micro-channel set and the hot flow micro-channel set are arranged in a multi-section mode, on one hand, the cold flow heat exchange channel and the hot flow heat exchange channel are connected with pipelines of respective working media; on the other hand, the heat exchange efficiency is submitted in order to ensure that the low-temperature working medium and the high-temperature working medium form quasi-countercurrent convection heat exchange in the heat exchange process.
In one possible embodiment, as shown in FIGS. 9 and 10, the intermediate overlapping sections 9, the two diverging sections 8, the inlet section 11 and the outlet section 12 of the cold and hot microchannel arrays are all linear channels, the transition section 10 comprises a first transition section 10-1 and a second transition section 10-2 which are arranged in an axial symmetry way, one end port of the first turning section 10-1 is communicated with one end port of the middle overlapping section 9, the other end port of the first turning section 10-1 is communicated with one end port of the second turning section 10-2, the other end port of the second turning section 10-2 is communicated with one end port of the shunt section 8, the connection point of the first turning section 10-1 and the second turning section 10-2 is the central axis of the first turning section 10-1 and the second turning section 10-2; the extending direction of the channel of the first turning section 10-1 is the same as that of the channel of the middle overlapping section 9, and the extending direction of the channel of the second turning section 10-2 is the same as that of the channel of the shunting section 8; the first turning section 10-1 and the second turning section 10-2 are both linear type grooves.
In this embodiment, as shown in fig. 9 and 10, there is only one turning point between the middle overlapping section 9 and the splitting sections 8 at the two ends, that is, there are only two turning points in the design process of the whole cold flow micro-channel set or the whole hot flow micro-channel set, so that the pressure loss generated during the process of the working medium flowing through the turning points can be reduced.
In one possible embodiment, as shown in fig. 16 and 17, the intermediate overlapping segments 9 and the two diverging segments 8 of the cold and hot sets of microchannels are sinusoidal channels, the inlet section 11 and the outlet section 12 are both linear type channels, the turning transition section 10 comprises a first turning section 10-1 and a second turning section 10-2 which are arranged in an axial symmetry manner, one end port of the first turning section 10-1 is communicated with one end port of the middle overlapping section 9, the other end port of the first turning section 10-1 is communicated with one end port of the second turning section 10-2, the other end port of the second turning section 10-2 is communicated with one end port of the shunt section 8, the connection point of the first turning section 10-1 and the second turning section 10-2 is the central axis of the first turning section 10-1 and the second turning section 10-2; the extending direction of the channel of the first turning section 10-1 is the same as that of the channel of the middle overlapping section 9, and the extending direction of the channel of the second turning section 10-2 is the same as that of the channel of the shunting section 8; the first turning section 10-1 and the second turning section 10-2 are linear channels.
In this embodiment, the inlet section 11 and the outlet section 12 are linear channels, so as to ensure that the heat exchange working medium can smoothly flow into the channel, and pressure loss is not increased due to the phenomena of backflow, vortex and the like; the first turning section 10-1 and the second turning section 10-2 are linear channels, and the purpose of the linear channels is to ensure that the flow channels of the overlapped parts of the upper and lower heat exchange plates can fully correspond to each other, avoid the phenomenon of staggering from influencing the heat exchange characteristic, and then reduce the processing difficulty of the bent part of the channel to a certain extent.
As shown in fig. 16 and 17, the micro-channels are in a wave-shaped radial development structure, so that a heat exchange common system generates local disturbance in a flow process, and the development of a flow boundary layer and a thermal boundary layer is damaged, thereby promoting heat exchange and improving the heat exchange characteristics of the heat exchanger.
In the present embodiment, the cold flow microchannels 2-1 and the hot flow microchannels 3-1 may be disposed in a zigzag shape.
In a possible embodiment, the cold flow heat exchange core plate 2 and the hot flow heat exchange core plate 3 are dumbbell-shaped heat exchange core plates which are arranged in an axisymmetric manner, each dumbbell-shaped heat exchange core plate comprises a rectangular plate 6 and two hexagonal plates 7, and the two hexagonal plates 7 are oppositely arranged at two ends of the rectangular plate 6 and are integrally manufactured with the rectangular plate 6;
the middle overlapping section 9 in the cold flow micro-channel set and the hot flow micro-channel set is positioned on the rectangular plate 6, one of the flow dividing sections 8, one of the turning transition sections 10 and one of the inlet sections 11 are positioned on one of the hexagonal plates 7, and the other of the flow dividing sections 8, the other of the turning transition sections 10 and the outlet section 12 are positioned on the other hexagonal plate 7.
In this embodiment, the cold flow heat exchange core plate 2 and the hot flow heat exchange core plate 3 are disposed as dumbbell-shaped heat exchange core plates, so that the four end enclosure structures can be better installed and welded, and the cold side and the hot side flow channels of the heat exchanger can be kept similar in arrangement, so that the local pressure losses of the working mediums at two sides are basically consistent when the working mediums flow, that is, the working mediums at two sides have similar flow characteristics, and the overlapped parts of the cold and hot flow channels can be increased as much as possible, thereby promoting the heat exchange characteristics.
In a possible embodiment, first connecting parts 13 are left between two sides of the cold flow micro-channel sets and two sides of the cold flow heat exchange core plate 2, and the cold flow heat exchange core plate 2 is connected with the adjacent plate above the first connecting parts 13 through vacuum diffusion welding; and second connecting parts 14 are reserved between the two sides of the heat flow micro-channel group and the two sides of the heat flow heat exchange core plate 3, and the heat flow heat exchange core plate 3 is connected with the adjacent plate sheets above the heat flow heat exchange core plate through the second connecting parts 14 by vacuum diffusion welding.
In this embodiment, the widths of the first connecting portion 13 and the second connecting portion 14 are the same as the thickness of the heat exchange cover plate, so that the high pressure resistance between two adjacent heat exchange core plates is ensured.
In the embodiment, the core plates are connected through vacuum diffusion welding, the welding seam is small, and the strength of the welding part can be higher.
In a possible embodiment, the cold flow heat exchange core plate 2 and the hot flow heat exchange core plate 3 are both metal plate sheets, and the thickness of each plate sheet is 0.4 mm-1.0 mm; the cold flow micro-channel 2-1 or the hot flow micro-channel 3-1 is a micro-channel with a semicircular section etched on a metal sheet by a chemical etching method.
In this embodiment, as shown in fig. 15, the thicknesses of the cold flow heat exchange core plate 2 and the hot flow heat exchange core plate 3 are selected according to a metal thin plate with a standard thickness formed by the existing processing technology, the general thicknesses of the metal plate for processing the microchannel are 0.4mm, 0.6mm, 0.8mm and 1.0mm, and microchannels are etched on the metal plate by a chemical etching method on the selected plate; because the processing process adopts the chemical etching method, the method can only control the depth of the processed micro-channel, and is difficult to control the shape of the cross section of the micro-channel generated in the processing process.
In a possible embodiment, the connecting end of the connecting end enclosure 4 and the convection heat exchange plate group is a square port, the connecting end of the connecting end enclosure 4 and the connecting flange 5 is a circular port, and the connecting end enclosure 4 is gradually expanded from the circular port to the square port; four top corners of the inner wall of the connecting seal head 4 are designed to be chamfered.
In this embodiment, as shown in fig. 19, the connecting end enclosure 4 is an integral gradually-expanding structure, the cross-sectional shapes of the ports at the two sides of the connecting end enclosure 4 are different, the cross-sectional shape of the port at the connecting part with the connecting flange 5 is circular, the cross-sectional shape of the port at the connecting part with the microchannel heat exchange intermediate structure is square, and the connecting end enclosure 4 is a circular port structure and gradually transits to a square port in a smooth manner; in the design process of the printed plate type microchannel heat exchanger (PCHE), the port part of the convection heat exchange plate group is generally designed into a port with a square cross section, so that in order to match the shape of the port of the convection heat exchange plate group, the connecting port of the connecting end enclosure 4 and the convection heat exchange plate group is also designed into a square port, and the pressure loss generated by the circular cross section channel during fluid transportation is less, so that the circular heat exchange plate is an optimal structure, and the similarity exists between the circular cross section and the square cross section, so that the connecting port of the connecting end enclosure 4 and the connecting flange 5 is designed into a circle, and the circular port of the connecting end enclosure 4 is smoothly transited to the square port, so that the flow distribution can be realized, and meanwhile, less pressure loss is generated.
In this embodiment, flange 5 choose for use the flange of standard according to the demand of reality, often adopt neck butt welding flange (MN type) to high pressure thermal environment, when choosing, flange 5's latus rectum is close as far as possible and slightly less than the latus rectum of the square connection port of heat convection bank group, is favorable to making the divergent angle of connecting head 4 reach the minimum like this to can shorten the length of connecting head 4 to a certain extent, reduce the pressure loss that working medium flow produced through connecting head 4.
In the embodiment, four top corners of the inner wall of the connecting seal head 4 adopt chamfer design, so that the pressure loss can be reduced.
Compared with the traditional heat exchanger, the heat exchanger has the advantages that the heat transfer efficiency can reach more than 93 percent, and the compactness is not less than 1500m 2/m 3; the application temperature range is-200 ℃ to 800 ℃, and the highest bearing pressure exceeds 4 MPa; under the condition that the heat exchange quantity is the same as that of the traditional heat exchanger, the volume of the printed plate type micro-channel heat exchanger can be reduced by 3 to 5 times, and the weight is light by 1 to 2 times; the application scene is complex, and the method can be used for both gaseous working media and liquid working media.
Although the invention herein has been described with reference to particular embodiments, it is to be understood that these embodiments are merely illustrative of the principles and applications of the present invention. It is therefore to be understood that numerous modifications may be made to the illustrative embodiments and that other arrangements may be devised without departing from the spirit and scope of the present invention as defined by the appended claims. It should be understood that features described in different dependent claims and herein may be combined in ways different from those described in the original claims. It is also to be understood that features described in connection with individual embodiments may be used in other described embodiments.

Claims (10)

1. A design method suitable for a printing plate type micro-channel heat exchanger is characterized by comprising the following steps: the specific design steps are as follows:
step 1, structure screening: based on the whole size constraint range of the heat exchanger and the size constraint range of the internal channel, the size, the total heat exchange area, the compactness and the heat exchanger quality of the pre-designed heat exchanger are screened, an optimization method is adopted to perform circular search in the size range of geometric constraint, and the structure meeting the set conditions is output as an effective structure I;
step 2, performance screening: based on a mathematical model, calculating the heat transfer characteristic and the flow characteristic of an effective structure I meeting the structural requirements, and outputting a structure meeting the structural requirements and the performance requirements as an effective structure II;
step 3, applicability screening: establishing a full-working-condition combination according to the flow range, the temperature range and the pressure range of working media at the cold side and the hot side in the practical application process of the heat exchanger, and then carrying out the calculation of the comprehensive performance under the full working condition on the effective structure II based on a heat transfer characteristic calculation model and a flow characteristic calculation model; and (3) establishing different operation condition parameter combinations capable of covering all research ranges by taking the performance design requirements as screening conditions, calculating one by one, and screening the effective structure II with the maximum number of parameter combinations with comprehensive performance meeting the design requirements under the condition of all condition parameter combinations as a final structure.
2. The design method of a printed plate microchannel heat exchanger as claimed in claim 1, wherein: in the step 2, the heat transfer characteristic of the effective structure I is obtained by the following calculation:
the convective heat transfer coefficient h is obtained based on the Nusselt number, and the calculation process is as follows:
Figure RE-FDA0003782454340000011
Figure RE-FDA0003782454340000012
Figure RE-FDA0003782454340000013
Figure RE-FDA0003782454340000014
m＝2.27+1.65Pr 1/3 ,0.1＜Pr＜∞,
Figure RE-FDA0003782454340000016
Figure RE-FDA0003782454340000015
Figure RE-FDA0003782454340000021
in the formula (I), the compound is shown in the specification,
Figure RE-FDA0003782454340000027
denotes the number of Nusselt by taking the square root of the cross-sectional area as the characteristic dimension,
Figure RE-FDA0003782454340000028
representing the Reynolds number with the square root of the cross-sectional area as the characteristic dimension, Pr representing the Prandtl number, C 1 ～C 4 Represents a correlation coefficient, m c B and B
Figure RE-FDA0003782454340000029
16, 425, and 1700, respectively;
Figure RE-FDA00037824543400000210
representing dimensionless mean wall shear stress, K td Represents a correction coefficient, and TC represents a thermal correction coefficient;
Figure RE-FDA00037824543400000211
representing a dimensionless thermal length with the square root of the cross-sectional area as the characteristic dimension, epsilon representing the channel aspect ratio, and gamma representing the shape factor; the subscript s represents the solid side,f denotes the fluid side and,
Figure RE-FDA00037824543400000212
indicating the characteristic dimension as the square root of the cross-sectional area, the subscripts Lam, Tur respectively indicating laminar flow;
calculating the total heat transfer coefficient UA according to the convective heat transfer coefficient h, wherein the calculation process is as follows:
Figure RE-FDA0003782454340000022
Figure RE-FDA0003782454340000023
in the formula eta o Expressing the thermal efficiency of the fin assembly, eta fin Fin efficiency; h represents the convective heat transfer coefficient; a represents the total heat exchange area; k represents the material thermal conductivity; a represents the inter-channel grid thickness; subscript total denotes total, fin denotes a fin portion, s denotes a solid side, wall denotes a wall surface;
obtaining the total heat exchange quantity q of the heat exchanger based on the logarithmic mean temperature, wherein the calculation process is as follows:
q＝UA·ΔT LMTD
Figure RE-FDA0003782454340000024
Figure RE-FDA0003782454340000025
Figure RE-FDA0003782454340000026
in the formula, q represents the total heat exchange amount; delta T LMTD Represents the log mean temperature; UA represents the total heat transfer coefficient of the heat exchanger; c is to changeThermal capacity of the hot working medium; epsilon represents the heat exchanger effectiveness, NTU represents the heat exchange unit; t represents a temperature; m represents a mass flow rate; c. C p Represents the specific heat capacity at constant pressure; c represents the heat capacity of the heat exchange working medium at the hot side; the subscripts h, c represent the hot and cold sides, respectively, and in represents the inlet side.
3. The design method of the printed plate type microchannel heat exchanger as claimed in claim 2, wherein: in the step 2, the calculation formula of the flow characteristic of the effective structure I is as follows:
Figure RE-FDA0003782454340000031
wherein G represents the mass velocity in the microchannel of the heat exchanger; rho represents the density of the working medium; l represents the channel length; d h Represents the channel equivalent diameter; ζ represents a unit angle Representing the local resistance coefficient in the folded pipe; σ represents the ratio of the core free flow area to the frontal area; k c And K e A function representing the geometry of the contraction and expansion segments; zeta expansion Representing a local pressure loss coefficient; zeta contraction The local pressure loss coefficient is expressed.
4. A printed plate type microchannel heat exchanger adapted to a high pressure thermal environment designed based on the design method of claim 3, characterized in that: the heat exchange plate comprises two heat exchange cover plates (1), a plurality of cold flow heat exchange core plates (2), a plurality of hot flow heat exchange core plates (3), four connecting seal heads (4) and four connecting flanges (5), wherein the shapes and the sizes of the plates of the heat exchange cover plates (1), the cold flow heat exchange core plates (2) and the hot flow heat exchange core plates (3) are the same, the plurality of cold flow heat exchange core plates (2) and the plurality of hot flow heat exchange core plates (3) are longitudinally overlapped and arranged between the two heat exchange cover plates (1) and form a convection heat exchange plate group with the two heat exchange cover plates (1), the convection heat exchange plate group comprises a cold flow heat exchange channel and a hot flow heat exchange channel, the four connecting seal heads (4) are respectively connected at two opposite corners of the convection heat exchange plate group, the two connecting seal heads (4) at one opposite corner are respectively communicated with the cold flow heat exchange channel, and the two connecting seal heads (4) at the other opposite corner are respectively communicated with the heat exchange channel, the cold flow heat exchange channel and the hot flow heat exchange channel exchange heat in a convection mode to achieve the purpose of heat exchange, and each connecting end socket (4) is connected with a corresponding pipeline through one connecting flange (5).
5. The printed plate microchannel heat exchanger of claim 4, adapted for use in a high pressure thermal environment, wherein: a plurality of cold flow micro-channels (2-1) which are arranged side by side at equal intervals are arranged on the upper surface of the cold flow heat exchange core plate (2) to form a cold flow micro-channel set, and the cold flow micro-channel set on the cold flow heat exchange core plate (2) and the lower surface of the upper plate sheet adjacent to the cold flow micro-channel set form a cold flow heat exchange channel; the ports at the two ends of the cold flow heat exchange channel are respectively flush with the end parts at the two ends of the cold flow heat exchange core plate (2); a plurality of heat flow micro-channels (3-1) which are arranged side by side at equal intervals are arranged on the upper surface of the heat flow heat exchange core plate (3) and form a heat flow micro-channel group, and the heat flow micro-channel group on the heat flow heat exchange core plate (3) and the lower surface of the upper plate sheet adjacent to the heat flow micro-channel group form a heat flow heat exchange channel; the ports of the two ends of the heat flow heat exchange channel are respectively flush with the ends of the two ends of the heat flow heat exchange core plate (3); the cold flow micro-channel set on the cold flow heat exchange core plate (2) and the heat flow micro-channel set on the heat flow heat exchange core plate (3) are arranged in an axial symmetry manner; the overlapped part of the cold flow heat exchange channel and the hot flow heat exchange channel is in a spindle shape.
6. The printed plate microchannel heat exchanger of claim 5, adapted for use in a high pressure thermal environment, wherein: the cold flow micro-channel set and the heat flow micro-channel set are integrally arranged in a Z shape, the cold flow micro-channel set and the heat flow micro-channel set respectively comprise a middle overlapping section (9), two turning transition sections (10), two shunt sections (8), an inlet section (11) and an outlet section (12), the working medium outlet end of the inlet section (11) is communicated with the working medium inlet end of one turning transition section (10), the working medium outlet end of one turning transition section (10) is communicated with the working medium inlet end of one shunt section (8), the working medium outlet end of one shunt section (8) is communicated with the working medium inlet end of the middle overlapping section (9), the working medium outlet end of the middle overlapping section (9) is communicated with the working medium inlet end of the other turning transition section (10), the working medium outlet end of the other turning transition section (10) is communicated with the working medium inlet end of the other shunt section (8), the working medium outlet end of the other section of the flow distribution section (8) is communicated with the working medium inlet end of the outlet section (12); each section of the shunting section (8) and the middle overlapping section (9) are arranged in an obtuse angle;
7. the printed plate microchannel heat exchanger of claim 6, adapted for use in a high pressure thermal environment, wherein: the middle overlapping section (9), the two flow dividing sections (8), the inlet section (11) and the outlet section (12) in the cold flow micro-channel set and the hot flow micro-channel set are all linear channels, the turning transition section (10) comprises a first turning section (10-1) and a second turning section (10-2) which are arranged in an axial symmetry way, one end port of the first turning section (10-1) is communicated with one end port of the middle overlapping section (9), the other end port of the first turning section (10-1) is communicated with one end port of the second turning section (10-2), the other end port of the second turning section (10-2) is communicated with one end port of the shunt section (8), the connection point of the first turning section (10-1) and the second turning section (10-2) is the central axis of the first turning section (10-1) and the second turning section (10-2); the extending direction of the channel of the first turning section (10-1) is the same as that of the channel of the middle overlapping section (9), and the extending direction of the channel of the second turning section (10-2) is the same as that of the channel of the shunting section (8); the first turning section (10-1) and the second turning section (10-2) are linear channels.
8. A printed plate microchannel heat exchanger adapted for use in a high pressure thermal environment according to claim 6, wherein: the middle overlapping section (9) and the two shunting sections (8) in the cold flow micro-channel set and the hot flow micro-channel set are both sine-shaped channels, and the inlet section (11) and the outlet section (12) are both linear channels; the transition section (10) comprises a first transition section (10-1) and a second transition section (10-2) which are arranged in an axial symmetry manner, one end port of the first transition section (10-1) is communicated with one end port of the middle overlapping section (9), the other end port of the first transition section (10-1) is communicated with one end port of the second transition section (10-2), the other end port of the second transition section (10-2) is communicated with one end port of the shunt section (8), and the connection point of the first transition section (10-1) and the second transition section (10-2) is the central axis of the first transition section (10-1) and the second transition section (10-2); the extending direction of the channel of the first turning section (10-1) is the same as that of the channel of the middle overlapping section (9), and the extending direction of the channel of the second turning section (10-2) is the same as that of the channel of the shunting section (8); the first turning section (10-1) and the second turning section (10-2) are linear channels.
9. A printed plate microchannel heat exchanger suitable for use in high pressure thermal environments according to claim 7 or 8, wherein: the cold flow heat exchange core plate (2) and the hot flow heat exchange core plate (3) are dumbbell-shaped heat exchange core plates which are arranged in an axisymmetric manner, each dumbbell-shaped heat exchange core plate comprises a rectangular plate (6) and two hexagonal plates (7), and the two hexagonal plates (7) are oppositely arranged at two ends of the rectangular plate (6) and are integrally manufactured with the rectangular plate (6); the cold flow micro-channel set and the hot flow micro-channel set are characterized in that the middle overlapping section (9) is positioned on the rectangular plate (6), one section of the flow distribution section (8), one section of the turning transition section (10) and one section of the inlet section (11) are positioned on one hexagonal plate (7), and the other section of the flow distribution section (8), the other section of the turning transition section (10) and the outlet section (12) are positioned on the other hexagonal plate (7).
10. A printed plate microchannel heat exchanger suitable for use in high pressure thermal environments according to claim 9, wherein: the connecting end of the connecting end enclosure (4) and the convection heat exchange plate set is a square port, the connecting end of the connecting end enclosure (4) and the connecting flange (5) is a circular port, and the connecting end enclosure (4) is transited from the circular port to the square port in a gradually expanding manner; four vertex angles of the inner wall of the connecting seal head (4) are designed by adopting chamfers.
CN202210492203.1A 2022-05-07 2022-05-07 Design method of printing plate type micro-channel heat exchanger and micro-channel heat exchanger Pending CN114993079A (en)

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