CN117628946B - Heat exchanger and heat exchange system - Google Patents
Heat exchanger and heat exchange system Download PDFInfo
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- CN117628946B CN117628946B CN202410093673.XA CN202410093673A CN117628946B CN 117628946 B CN117628946 B CN 117628946B CN 202410093673 A CN202410093673 A CN 202410093673A CN 117628946 B CN117628946 B CN 117628946B
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- 239000012530 fluid Substances 0.000 claims abstract description 150
- 238000005452 bending Methods 0.000 claims description 21
- 230000001154 acute effect Effects 0.000 claims description 5
- 230000000903 blocking effect Effects 0.000 abstract description 22
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 16
- 238000004891 communication Methods 0.000 description 13
- 238000010586 diagram Methods 0.000 description 12
- 229910002092 carbon dioxide Inorganic materials 0.000 description 8
- 239000001569 carbon dioxide Substances 0.000 description 8
- 238000000034 method Methods 0.000 description 8
- 230000008569 process Effects 0.000 description 8
- 238000006243 chemical reaction Methods 0.000 description 6
- 238000009792 diffusion process Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000009835 boiling Methods 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 238000010992 reflux Methods 0.000 description 2
- 244000126211 Hericium coralloides Species 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 230000008094 contradictory effect Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000011010 flushing procedure Methods 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 238000004064 recycling Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Classifications
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
- F01D15/10—Adaptations for driving, or combinations with, electric generators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
- F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
- F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
- F01K25/103—Carbon dioxide
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/32—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines using steam of critical or overcritical pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The application discloses a heat exchanger and a heat exchange system, wherein the heat exchanger comprises a tube box and a heat exchange core body, wherein a high-temperature fluid medium inlet, a high-temperature fluid medium outlet, a low-temperature fluid medium inlet and a low-temperature fluid medium outlet are formed in the tube box; the heat exchange core body is used for transferring heat of the high-temperature fluid medium flowing through the high-temperature fluid medium inlet, the first heat exchange plate and the high-temperature fluid medium outlet to the low-temperature fluid medium flowing through the low-temperature fluid medium inlet, the second heat exchange plate and the low-temperature fluid medium outlet; the first heat exchange plate and the second heat exchange plate are respectively provided with a heat exchange channel and an airfoil fin which is positioned in the heat exchange channels, and the airfoil fin and the heat exchange channels are used for carrying out forward diversion and reverse flow blocking on high-temperature fluid medium or low-temperature fluid medium flowing through the heat exchange channels. The heat exchanger with the reverse flow blocking function is used for replacing a check valve, and the problems of loose equipment space arrangement and low heat exchange efficiency in a heat exchange system based on a sCO2 Brayton cycle system are solved.
Description
Technical Field
The application relates to the technical field of heat exchange, in particular to a heat exchanger and a heat exchange system.
Background
Supercritical carbon dioxide (Supercritical CO) 2 ，sCO 2 ) Can be used forThe quantity conversion system is used as a common heat exchange system which combines carbon dioxide with the Brayton cycle and adopts CO in a supercritical state 2 The steam Rankine cycle is used as a working medium, and the boiling critical phenomenon existing in the steam Rankine cycle is solved.
Currently, common sCO 2 The Brayton cycle system includes a turbine and a compressor, the direction of rotation of the impellers of the turbine and the compressor being fixed. In order to prevent the fluid medium from counter-current flushing the impeller during operation of the system, check valves are provided on both the turbine and compressor outlets.
However, the existing check valve has a large volume, resulting in sCO 2 The equipment space arrangement in the Brayton cycle system is loose, and the heat exchange efficiency is low.
The foregoing is merely provided to facilitate an understanding of the principles of the present application and is not admitted to be prior art.
Disclosure of Invention
The main purpose of the application is to provide a heat exchanger and a heat exchange system, which aim to solve the problem of sCO by replacing a check valve with a heat exchanger with forward diversion and reverse flow blocking functions 2 The problems of loose equipment space arrangement and low heat exchange efficiency in the Brayton cycle system are solved.
To achieve the above object, the present application provides a heat exchanger including: the pipe box is provided with a high-temperature fluid medium inlet, a high-temperature fluid medium outlet, a low-temperature fluid medium inlet and a low-temperature fluid medium outlet; the heat exchange core body comprises a first cover plate, a second cover plate, a first heat exchange plate and a second heat exchange plate; the first heat exchange plates and the second heat exchange plates are alternately laminated and distributed to form a porous core body, and the first cover plate and the second cover plate are correspondingly arranged on two sides of the porous core body so as to cover the porous core body; the high-temperature fluid medium inlet is communicated with the high-temperature fluid medium outlet through the first heat exchange plate so as to circulate high-temperature fluid medium, the low-temperature fluid medium inlet is communicated with the low-temperature fluid medium outlet through the second heat exchange plate so as to circulate low-temperature fluid medium, and the heat exchange core exchanges heat between the passing high-temperature fluid medium and low-temperature fluid medium through the first heat exchange plate and the second heat exchange plate; the first heat exchange plate and the second heat exchange plate are respectively provided with a heat exchange channel and an airfoil fin positioned in the heat exchange channels, the airfoil fins are provided with blunt surface heads and tip tails which are oppositely arranged, and the blunt surface heads of the airfoil fins are positioned at one side of the tip tails close to a fluid medium inlet; the orthographic projection of the wing-shaped fin on the plane where the first cover plate is located is an arc-shaped structure, the arc-shaped structure has a first curvature at a position corresponding to the blunt surface head part and a second curvature at a position corresponding to the tip tail part, and the first curvature is smaller than the second curvature.
Optionally, the heat exchange channel comprises a plurality of channel parts which are sequentially connected, and the channel parts comprise a first micro-flow channel, a second micro-flow channel and a third micro-flow channel; wherein, in the same channel part, the channel inlet of the third microfluidic channel is respectively communicated with the channel outlet of the second microfluidic channel and the channel outlet of the first microfluidic channel; in the adjacent two channel parts, the channel outlet of the third micro-flow channel in the former channel part is communicated with the channel inlet of the second micro-flow channel in the latter channel part and the channel inlet of the first micro-flow channel.
Optionally, in the same channel part, a first bending angle is formed between the channel inlet of the third microfluidic channel and the channel outlet of the second microfluidic channel, the first bending angle is greater than or equal to 90 °, and the angle between the channel inlet of the third microfluidic channel and the channel outlet of the first microfluidic channel is 180 °; in the two adjacent channel parts, a second bending angle and a third bending angle are respectively arranged between a channel outlet of a third micro-flow channel in the front channel part and a channel inlet of a second micro-flow channel in the rear channel part and between the channel inlets of the first micro-flow channels, wherein the second bending angle is an obtuse angle smaller than or equal to 270 degrees, and the third bending angle is an acute angle.
Optionally, a comb structure is disposed on a side wall of the channel inlet of the third microfluidic channel near the channel outlet of the second microfluidic channel.
Optionally, the airfoil fins are located in the third microfluidic channel and the second microfluidic channel, and the airfoil fins are uniformly distributed at intervals in the third microfluidic channel and the second microfluidic channel.
Optionally, the path length of the second microfluidic channel is smaller than the path length of the first microfluidic channel.
Optionally, the channel part further includes a fourth microfluidic channel, and the fourth microfluidic channel and the first microfluidic channel are respectively located at two sides of the third microfluidic channel; the channel inlets of the fourth microfluidic channels are respectively communicated with the channel inlets of the third microfluidic channels and the channel outlets of the second microfluidic channels in the same channel part, and the channel outlets of the fourth microfluidic channels are respectively communicated with the channel outlets of the third microfluidic channels in the same channel part, the channel inlets of the second microfluidic channels in adjacent channel parts and the channel inlets of the first microfluidic channels; a fourth bending angle is arranged between the channel inlet of the fourth micro-flow channel and the channel inlet of the third micro-flow channel, the fourth bending angle is an obtuse angle, and the angle between the channel outlet of the fourth micro-flow channel and the channel inlet of the second micro-flow channel in the adjacent channel part is 180 degrees.
Optionally, in the same channel part, a first included angle is formed between the channel inlet of the first microfluidic channel and the channel inlet of the second microfluidic channel, a second included angle is formed between the channel outlet of the first microfluidic channel and the channel outlet of the second microfluidic channel, and the first included angle is larger than the second included angle; in the same channel part, a third included angle is formed between the channel inlet of the fourth microfluidic channel and the channel inlet of the third microfluidic channel, a fourth included angle is formed between the channel outlet of the fourth microfluidic channel and the channel outlet of the third microfluidic channel, and the third included angle is larger than the fourth included angle.
Optionally, the first included angle and the third included angle are obtuse angles, the second included angle and the fourth included angle are acute angles, the first included angle is the same as the third included angle, and the second included angle is the same as the fourth included angle.
In addition, in order to achieve the above object, the present application further provides a heat exchange system, including: the heat exchanger of any embodiment of the present application; the heat exchange system also comprises a heat source, a turbine, a generator, a cooler and a compressor; the heat source comprises a heat source, a heat exchanger, a heat generator, a cooler, a compressor, a turbine, a heat source, a heat exchanger, a heat source, a heat generator and a generator, wherein the first output end of the heat exchanger is connected with the input end of the heat source, the output end of the heat source is connected with the input end of the turbine, the output end of the turbine is connected with the second input end of the heat exchanger, the second output end of the heat exchanger is connected with the input end of the cooler, the output end of the cooler is connected with the input end of the compressor, the output end of the compressor is connected with the first input end of the heat exchanger, and the generator is connected with the turbine.
According to the heat exchanger and the heat exchange system provided by the embodiment of the application, on one hand, a high-temperature fluid medium is guided into a heat exchange core body through a high-temperature fluid medium inlet on a pipe box; the high-temperature fluid medium is guided out of the heat exchange core body through a high-temperature fluid medium outlet on the pipe box; introducing a low-temperature fluid medium into the heat exchange core through a low-temperature fluid medium inlet on the tube box; guiding the low-temperature fluid medium out of the heat exchange core body through a low-temperature fluid medium outlet on the pipe box; the high-temperature fluid medium transfers heat to the low-temperature fluid medium through the first heat exchange plate and the second heat exchange plate in the heat exchange core body, so that a heat exchange function is realized;
on the other hand, the wing-shaped fins in the heat exchange channel are used for shunting the fluid medium flowing in the forward direction in the heat exchange channel, so that the heat exchange efficiency of the heat exchanger can be effectively ensured; through the lateral wall and the wing type fin of heat exchange channel, flow blocking is carried out to the fluid medium of reverse flow in the heat exchange channel, prevents the fluid medium of refluence from flowing out the heat exchange core, so makes the heat exchanger have the function of forward water conservancy diversion and reverse flow blocking, has replaced the check valve in the traditional heat transfer system based on sCO2 Brayton cycle system to simplified system equipment has improved the compactibility of system equipment space arrangement, has improved the heat exchange efficiency of system to a certain extent.
Drawings
FIG. 1 is a schematic diagram of a circulation flow of a heat exchange system based on a supercritical carbon dioxide energy conversion system according to the related art;
FIG. 2 is a schematic diagram of a circulation flow of a heat exchange system based on a supercritical carbon dioxide energy conversion system according to an embodiment of the present disclosure;
FIG. 3 is an overall schematic diagram of a heat exchanger provided in an embodiment of the present application;
FIG. 4 is an exploded view of a heat exchanger according to an embodiment of the present disclosure;
fig. 5 is a schematic structural diagram of a first heat exchange plate according to an embodiment of the present disclosure;
FIG. 6 is a schematic illustration of the forward flow of a high temperature fluid medium through section A of FIG. 5;
FIG. 7 is a schematic diagram showing the reverse flow of a high temperature fluid medium through section A of FIG. 5;
FIG. 8 is a schematic flow diagram of a high temperature fluid medium flowing positively through an airfoil fin;
FIG. 9 is a flow schematic of a high temperature fluid medium counter-current flow through an airfoil fin;
FIG. 10 is a schematic flow diagram of a high temperature fluid medium flowing positively through a comb structure;
FIG. 11 is a schematic flow diagram of a high temperature fluid medium flowing in reverse through a comb structure;
FIG. 12 is a schematic view of a heat exchange channel according to another embodiment of the present disclosure;
FIG. 13 is a schematic diagram of a second heat exchange channel according to another embodiment of the present disclosure;
Fig. 14 is a schematic structural diagram of a second heat exchange plate according to an embodiment of the present disclosure.
Wherein, 1, a heat source; 2. a turbine; 3. a generator; 4. a regenerator; 5. a cooler; 6. a compressor; 7. a first check valve; 8. a second check valve; 9. a heat exchanger; 91. a tube box; 911. a high temperature fluid medium inlet; 912. a high temperature fluid medium outlet; 913. a cryogenic fluid medium inlet; 914. a cryogenic fluid medium outlet; 92. a heat exchange core; 921. a first heat exchange plate; 922. a second heat exchange plate; 923. a first cover plate; 924. a second cover plate; 93. an airfoil fin; 94. a heat exchange channel; 941. a channel portion; 9411. a first microfluidic channel; 9412. a second microfluidic channel; 9413. a third microfluidic channel; 9414. a fourth microfluidic channel; 95. a comb structure; 96. an air inlet; 97. and an air outlet.
The realization, functional characteristics and advantages of the present application will be further described with reference to the embodiments, referring to the attached drawings.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and fully with reference to the accompanying drawings, in which it is evident that the embodiments described are only some, but not all embodiments of the invention. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
It should be noted that all directional indicators (such as up, down, left, right, front, and rear … …) in the embodiments of the present invention are merely used to explain the relative positional relationship, movement, etc. between the components in a particular posture (as shown in the drawings), and if the particular posture is changed, the directional indicator is changed accordingly.
In the present invention, unless specifically stated and limited otherwise, the terms "connected," "affixed," and the like are to be construed broadly, and for example, "affixed" may be a fixed connection, a removable connection, or an integral body; can be mechanically or electrically connected; either directly or indirectly, through intermediaries, or both, may be in communication with each other or in interaction with each other, unless expressly defined otherwise. The specific meaning of the above terms in the present invention can be understood by those of ordinary skill in the art according to the specific circumstances.
In addition, if there is a description of "first", "second", etc. in the embodiments of the present invention, the description of "first", "second", etc. is for descriptive purposes only and is not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include at least one such feature. In addition, the meaning of "and/or" as it appears throughout includes three parallel schemes, for example "A and/or B", including the A scheme, or the B scheme, or the scheme where A and B are satisfied simultaneously. In addition, the technical solutions of the embodiments may be combined with each other, but it is necessary to base that the technical solutions can be realized by those skilled in the art, and when the technical solutions are contradictory or cannot be realized, the combination of the technical solutions should be considered to be absent and not within the scope of protection claimed in the present invention.
In the prior art, supercritical carbon dioxide (sCO 2) energy conversion systems are commonly used as heat exchange systems, which combine carbon dioxide with Brayton cycle and use CO in Supercritical state 2 The steam Rankine cycle is used as a working medium, the boiling critical phenomenon existing in the steam Rankine cycle is solved, and the safety of the system is improved.
The supercritical carbon dioxide energy conversion system is shown in fig. 1, and mainly comprises a heat source 1, a turbine 2, a generator 3, a heat regenerator 4, a cooler 5, a compressor 6, a first check valve 7 and a second check valve 8, wherein a first output end of the heat regenerator 4 is connected with an input end of the heat source 1, an output end of the heat source 1 is connected with an input end of the turbine 2, the turbine 2 is connected with the generator 3, an output end of the turbine 2 is connected with a second input end of the heat regenerator 4 through the first check valve 7, a second output end of the heat regenerator 4 is connected with an input end of the cooler 5, an output end of the cooler 5 is connected with an input end of the compressor 6, and an output end of the compressor 6 is connected with a first input end of the heat regenerator 4 through the second check valve 8.
During operation, sCO 2 Compressed by a compressor 6 and passed through a regenerator 4, and heated by a heat source 1 to become high-temperature high-pressure sCO 2 sCO at high temperature and high pressure 2 Expansion work is carried out in a turbine 2, and the expanded sCO 2 Reduced pressure sCO exiting turbine 2 2 Enters a cooler 5 for cooling through a heat regenerator 4, and the cooled sCO2 enters a compressor 6 again to realize sCO 2 Is recycled.
The turbine 2 and the compressor 6 in the above system are both high-speed rotating machines, and the rotation direction of the impeller is fixed. To prevent the counter-flow of the fluid medium against the counter-rotating impeller, a first check valve 7 is provided at the outlet of the turbine 2 and a second check valve 8 is provided at the outlet of the compressor 6.
However, the first check valve 7 and the second check valve 8 are relatively bulky, resulting in sCO 2 The equipment space arrangement in the Brayton cycle system is loose, and the heat exchange efficiency is low.
In order to solve the technical problems, embodiments of the present application provide a vortex generator and a heat exchange system, which aim to replace a check valve by a heat exchanger with forward flow guiding and reverse flow blocking functions, so as to solve the sCO 2 The problems of loose equipment space arrangement and low heat exchange efficiency in a heat exchange system formed by the Brayton cycle system.
Referring to fig. 2, which is a schematic diagram of a circulation flow of a heat exchange system based on a supercritical carbon dioxide energy conversion system according to an embodiment of the present application, fig. 3 is a schematic diagram of a heat exchanger according to an embodiment of the present application.
The heat exchange system includes: a heat source 1, a turbine 2, a generator 3, a cooler 5, a compressor 6 and a heat exchanger 9.
Specifically, the first output end of the heat exchanger 9 is connected with the input end of the heat source 1, the output end of the heat source 1 is connected with the input end of the turbine 2, the output end of the turbine 2 is connected with the second input end of the heat exchanger 9, the second output end of the heat exchanger 9 is connected with the input end of the cooler 5, the output end of the cooler 5 is connected with the input end of the compressor 6, and the output end of the compressor 6 is connected with the first input end of the heat exchanger 9 and is connected with the turbine 2.
During operation, sCO2 is compressed by the compressor 6 and is heated by the heat source 1 to become high-temperature and high-pressure sCO2 after passing through the heat exchanger 9, the high-temperature and high-pressure sCO2 expands in the turbine 2 to do work, the pressure of the expanded sCO2 is reduced, sCO2 flowing out of the turbine 2 enters the cooler 5 through the heat exchanger 9 to be cooled, and the cooled sCO2 enters the compressor 6 again to realize recycling of the sCO 2.
When the heat exchange system works, the heat exchanger 9 can be used for transmitting heat of a high-temperature fluid medium to a low-temperature fluid medium to realize a heat exchange function; on the other hand, the high-temperature fluid medium or the low-temperature fluid medium flowing backwards in the heat exchanger 9 can be blocked, so that the heat exchanger 9 has the functions of forward flow guiding and reverse flow blocking, and replaces a check valve in the traditional sCO2 Brayton cycle system, thereby simplifying system equipment, improving the compactness of equipment space arrangement in the heat exchange system, and further improving the heat exchange efficiency of the heat exchange system.
The composition and working principle of the heat exchange system are described in detail, and the heat exchanger 9 in the heat exchange system is described in detail.
Referring to fig. 3 and 4, the heat exchanger 9 includes a tube box 91 and a heat exchange core 92.
Specifically, the tube box 91 is provided with a high-temperature fluid medium inlet 911, a high-temperature fluid medium outlet 912, a low-temperature fluid medium inlet 913, and a low-temperature fluid medium outlet 914. The heat exchange core 92 includes a first cover plate 923, a second cover plate 924, a first heat exchange plate 921, and a second heat exchange plate 922; the first heat exchange plates 921 and the second heat exchange plates 922 are alternately stacked and distributed to form a porous core, and the first cover plate 923 and the second cover plate 924 are correspondingly arranged at two sides of the porous core to cover the porous core.
The high temperature fluid medium inlet 911 is connected to the high temperature fluid medium outlet 912 through the first heat exchange plate 921 to circulate the high temperature fluid medium, the low temperature fluid medium inlet 913 is connected to the low temperature fluid medium outlet 914 through the second heat exchange plate 922 to circulate the low temperature fluid medium, and the heat exchange core 92 exchanges heat with the passing high temperature fluid medium and low temperature fluid medium through the first heat exchange plate 921 and the second heat exchange plate 922, that is, the high temperature fluid medium and the low temperature fluid medium in the present application exchange heat through the isolated first heat exchange plate 921 and the second heat exchange plate 922. Wherein the temperature range of the high-temperature fluid medium is 200-500 ℃, and the temperature range of the low-temperature fluid medium is 30-200 ℃.
The first heat exchange plate 921 and the second heat exchange plate 922 are both provided with a heat exchange channel 94 and an airfoil fin 93 positioned in the heat exchange channel 94, the airfoil fin 93 is provided with a blunt surface head and a sharp end which are oppositely arranged, the blunt surface head of the airfoil fin 93 is positioned at one side of the sharp end close to the fluid medium inlet, namely, in the first heat exchange plate 921, one side of the airfoil fin 93 close to the high temperature fluid medium inlet 911 is the blunt surface head, and one side of the airfoil fin 93 close to the high temperature fluid medium outlet 912 is the sharp end; in the second heat exchange plate 922, the side of the airfoil fin 93 close to the low-temperature fluid medium inlet 913 is a blunt head, and the side of the airfoil fin 93 close to the low-temperature fluid medium outlet 914 is a pointed tail, so that when the fluid medium flows forward, the fluid medium flows in through the blunt head of the airfoil fin 93 and then flows out from the pointed tail.
The orthographic projection of the airfoil fin 93 on the plane of the first cover plate 923 is an arc structure, the arc structure has a first curvature at a position corresponding to the blunt surface head and a second curvature at a position corresponding to the tip tail, and the first curvature is smaller than the second curvature. Wherein the first curvature is less than the second curvature, indicating that the rate of change of curvature of the arcuate structure at the blunt tip is less than the rate of change of curvature at the tip tail, and therefore the sidewalls of the airfoil fins 93 form a greater angle at the blunt tip than at the tip tail. In this way, through the structural cooperation of the airfoil fins 93 and the heat exchange channels 94, the high-temperature fluid medium or the low-temperature fluid medium flowing in the heat exchange channels 94 can be positively guided and reversely choked.
It should be understood that the fluid forward flow as described herein refers to the direction of fluid flow from the media inlet to the media outlet. For example, in the first heat exchange plate, the high-temperature fluid flows from the high-temperature fluid medium inlet to the high-temperature fluid medium outlet, that is, the high-temperature fluid flows forward.
As an alternative embodiment, referring to fig. 3, the tube box 91 includes a first tube box, a second tube box, a third tube box, and a fourth tube box. The first tube box 91 and the second tube box 91 are arranged at two ends of the heat exchange core 92 along the length direction of the heat exchange core 92, wherein the first tube box 91 is provided with a high-temperature fluid medium inlet 911, and the second tube box 91 is provided with a high-temperature fluid medium outlet 912. The third tube box 91 and the fourth tube box 91 are arranged on two sides of the heat exchange core 92 along the width direction of the heat exchange core 92, the third tube box 91 is arranged close to the first tube box 91, and the fourth tube box 91 is arranged close to the second tube box 91; the third tube box 91 is provided with a low-temperature fluid medium inlet 913, and the fourth tube box 91 is provided with a low-temperature fluid medium outlet 914.
Referring to fig. 4, the heat exchange core 92 may include a first cover plate 923, a second cover plate 924, a first heat exchange plate 921, and a second heat exchange plate 922. The first heat exchange plates 921 and the second heat exchange plates 922 are provided with a plurality of first heat exchange plates 921 and second heat exchange plates 922 which are alternately distributed, and porous cores are formed between the adjacent first heat exchange plates 921 and second heat exchange plates 922 through diffusion welding. The first cover plate 923 is diffusion welded to one side of the porous core and the second cover plate 924 is diffusion welded to the other side of the porous core such that the first cover plate 923 and the second cover plate 924 cover the outside of the porous core.
In combination with the above-described embodiment, in operation in the present embodiment, the high-temperature fluid medium enters the heat exchange passages 94 of the respective first heat exchange plates 921 of the heat exchange core 92 from the high-temperature fluid medium inlet 911 of the first tube box 91, flows through the heat exchange passages 94 of the first heat exchange plates 921, and then flows out from the high-temperature fluid medium outlet 912 of the second tube box 91; the low-temperature fluid medium enters the heat exchange channels 94 of the second heat exchange plates 922 of the heat exchange core 92 from the low-temperature fluid medium inlet 913 of the third tube box 91, flows through the heat exchange channels 94 of the second heat exchange plates 922, and flows out from the low-temperature fluid medium outlet 914 of the fourth tube box 91. In the heat exchange core 92, during the process that the high-temperature fluid medium flows through the heat exchange channel 94 of the first heat exchange plate 921 and the low-temperature fluid medium flows through the heat exchange channel 94 of the second heat exchange plate 922, the high-temperature fluid medium transfers heat to the low-temperature fluid medium through the first heat exchange plate 921 and the second heat exchange plate 922, so as to realize a heat exchange function.
In other words, in the process of introducing the scco 2 flowing out of the turbine 2 into the cooler 5 through the heat exchanger 9, referring to fig. 2, the scco 2 is a high-temperature fluid medium, and the high-temperature scco 2 enters the heat exchange core 92 from the high-temperature fluid medium inlet 911, flows through the first heat exchange plate 921, and flows out from the high-temperature fluid medium outlet 912; in the process that the sCO2 is compressed by the compressor 6 and enters the turbine 2 through the heat exchanger 9, the sCO2 is a low-temperature fluid medium, the low-temperature sCO2 enters the heat exchange core 92 from the low-temperature fluid medium inlet 913, flows through the second heat exchange plate 922 and flows out from the low-temperature fluid medium outlet 914, so that in the heat exchange core 92, the heat of the high-temperature sCO2 is transferred to the low-temperature sCO2 through the first heat exchange plate 921 and the second heat exchange plate 922, and the heat exchange work is realized.
And, in the heat exchange core 92, the flow directions of the high temperature scco 2 and the low temperature scco 2 are relatively reversed. That is, referring to fig. 4, as indicated by the arrow on the first heat exchange plate 921, the flow direction of the high temperature scco 2 on the first heat exchange plate 921 is from the right side to the left side; as indicated by the arrow on the second heat exchanger plate 922, the flow direction of the low temperature scco 2 on the second heat exchanger plate 922 is from left to right. The flow directions of the high-temperature sCO2 and the low-temperature sCO2 are in opposite flow, so that the heat exchange effect of the heat exchanger 9 can be effectively improved.
And, in the heat exchange core 92, the side wall of the heat exchange channel 94 opened on the first heat exchange plate 921 and the wing fins 93 provided on the heat exchange channel 94 perform forward flow guiding and reverse flow blocking on the high temperature scco 2 flowing in the heat exchange channel 94, so as to prevent part of the high temperature fluid medium flowing reversely from flowing out of the heat exchange core 92. That is, in the process that the high temperature sCO2 flowing out of the turbine 2 enters the cooler 5 through the heat exchanger 9, the heat exchange channel 94 arranged on the first heat exchange plate 921 and the wing fins 93 positioned in the heat exchange channel 94 guide the high temperature sCO2 flowing in the heat exchange channel 94 to the cooler 5, block the high temperature sCO2 flowing in the heat exchange channel 94 to the turbine 2, so that the high temperature sCO2 cannot flow from the heat exchanger 9 to the turbine 2, and prevent the backflow of the high temperature sCO2 from reversely rushing the impeller of the turbine 2, so that the heat exchanger 9 has the functions of forward flow guide and reverse flow blocking, thereby realizing the purpose of replacing the first check valve 7;
And, in the heat exchange core 92, the side wall of the heat exchange channel 94 opened on the second heat exchange plate 922 and the wing fin 93 arranged on the heat exchange channel 94 perform forward flow guiding and reverse flow blocking on the low temperature sCO2 flowing in the heat exchange channel 94, so as to prevent part of the low temperature fluid medium flowing reversely from flowing out of the heat exchange core 92. That is, in the process that the low temperature sCO2 flowing out of the compressor 6 enters the heat source 1 through the heat exchanger 9, the heat exchange channel 94 opened on the second heat exchange plate 922 and the wing fin 93 positioned in the heat exchange channel 94 guide the low temperature sCO2 flowing into the heat source 1 in the heat exchange channel 94, block the low temperature sCO2 flowing into the compressor 6, so that the low temperature sCO2 cannot flow into the compressor 6 from the heat exchanger 9, and prevent the backflow of the low temperature sCO2 from reversely rushing to the impeller of the compressor 6, so that the heat exchanger 9 has the functions of forward flow guide and reverse flow blocking, thereby achieving the purpose of replacing the second check valve 8.
In the present embodiment, on the one hand, a high-temperature fluid medium is introduced into the heat exchange core 92 through the high-temperature fluid medium inlet 911 on the tube box 91; high temperature fluid medium is led out of the heat exchange core 92 through a high temperature fluid medium outlet 912 on the tube box 91; the low-temperature fluid medium is introduced into the heat exchange core 92 through the low-temperature fluid medium inlet 913 on the tube box 91; the cryogenic fluid medium is directed out of the heat exchange core 92 through a cryogenic fluid medium outlet 914 on the tube box 91; in the heat exchange core 92, the high temperature fluid medium transfers heat to the low temperature fluid medium through the first heat exchange plate 921 and the second heat exchange plate 922, realizing a heat exchange function; on the other hand, the flow of the fluid medium flowing forward in the heat exchange channel 94 is split through the wing fins 93 in the heat exchange channel 94, so that the heat exchange efficiency of the heat exchanger 9 can be effectively ensured; through the side wall of the heat exchange channel 94 and the wing-shaped fins 93, the flow of the fluid medium flowing reversely in the heat exchange channel 94 is blocked, and the fluid medium flowing reversely is prevented from flowing out of the heat exchange core 92, so that the heat exchanger 9 has the functions of forward flow guiding and reverse flow blocking, the first check valve 7 and the second check valve 8 in the traditional sCO2 Brayton cycle system are replaced, the system equipment is simplified, the space arrangement compactness of the system equipment is improved, and the heat exchange efficiency of the system is improved to a certain extent.
As an alternative embodiment, an embodiment of the present application provides a specific structure of the first heat exchange plate 921.
Referring to fig. 5, the first heat exchange plate 921 is provided with heat exchange channels 94 and airfoil fins 93.
The heat exchange channel 94 may include a plurality of channel portions 941 connected in sequence, the channel portions 941 including a first microfluidic channel 9411, a second microfluidic channel 9412, and a third microfluidic channel 9413; wherein, in the same channel portion 941, the channel inlet of the third microfluidic channel 9413 communicates with the channel outlet of the second microfluidic channel 9412 and the channel outlet of the first microfluidic channel 9411, respectively; in the adjacent two channel portions 941, the channel outlet of the third microfluidic channel 9413 in the preceding channel portion communicates with the channel inlet of the second microfluidic channel 9412 in the succeeding channel portion 941 and the channel inlet of the first microfluidic channel 9411.
It should be understood that, the channel inlet of a microfluidic channel described herein refers to a port on one side of the microfluidic channel into which fluid enters when the fluid flows in the forward direction; accordingly, the channel outlet of a microfluidic channel refers to a port on one side of the microfluidic channel from which fluid flows when the fluid flows in the forward direction. In addition, the previous microfluidic channel of a microfluidic channel refers to the previous microfluidic channel through which fluid flows when the fluid flows through the two connected microfluidic channels in the forward direction, and correspondingly, the next microfluidic channel through which fluid flows in the backward direction.
In the example embodiment, the first heat exchange plate 921 has an air inlet 96 formed in one side wall thereof along the length direction of the first heat exchange plate 921, and an air outlet 97 formed in the other side wall thereof. One end of the heat exchange channel 94 is communicated with the air inlet 96 of the first heat exchange plate 921, and the other end is communicated with the air outlet 97 of the first heat exchange plate 921. The heat exchange channels 94 include a plurality of sets of channel portions 941, and each set of channel portions 941 includes a first microfluidic channel 9411, a second microfluidic channel 9412, and a third microfluidic channel 9413. Specifically, the third micro-fluidic channels 9413 of the first group are in communication with the air inlet 96 of the first heat exchange plate 921, the second micro-fluidic channels 9412 of the first group are in communication with the third micro-fluidic channels 9413 of the second group, and so on until the second micro-fluidic channels 9412 of the last group are in communication with the air outlet 97 of the first heat exchange plate 921.
For example, in fig. 5, six air inlets 96 and six air outlets 97 are uniformly provided along both side walls of the first heat exchange plate 921 in the longitudinal direction thereof, respectively; six heat exchange channels 94 are uniformly arranged on the first heat exchange plate 921 along the length direction at intervals, and the six heat exchange channels 94 are communicated with the six air outlets 97 and the six air inlets 96 in a one-to-one correspondence manner. The six heat exchange channels 94 each include 11 sets of channel portions 941, each set of channel portions 941 includes a first microfluidic channel 9411, a second microfluidic channel 9412, and a third microfluidic channel 9413, and the third microfluidic channel 9413 of each set communicates with the second microfluidic channel 9412, and the second microfluidic channel 9412 communicates with the first microfluidic channel 9411. And the first set of second microfluidic channels 9412 communicates with the second set of third microfluidic channels 9413, the second microfluidic of the second set communicates with the third microfluidic channels 9413 of the third set, and so on until the second microfluidic of the last set communicates with the air outlet 97 of the first heat exchange plate 921.
Further, airfoil fins 93 are located in each group of the third microfluidic channel 9413 and the second microfluidic channel 9412, and the airfoil fins 93 are uniformly distributed at random intervals in the third microfluidic channel 9413 and the second microfluidic channel 9412.
As can be appreciated in connection with the above embodiments, airfoil fins 93 are distributed within each set of third and second microfluidic channels 9413, 9412. For example, referring to fig. 6 and 7, four airfoil fins 93 are distributed in the third microfluidic channel 9413 of each group, the intervals between the four airfoil fins 93 are uniform, four airfoil fins 93 are distributed in the second microfluidic channel 9412 of each group, and the intervals between the four airfoil fins 93 are uniform.
Further, in order to provide the heat exchanger 9 with the functions of forward flow guiding and reverse flow blocking, the leading edge of the airfoil fin 93 is located at the rear side of the trailing edge of the airfoil fin 93 in the forward flow direction of the high temperature fluid medium in the heat exchange passage 94.
In an exemplary embodiment, referring to fig. 6 and 8, during the flow of high temperature scco 2 exiting turbine 2 into cooler 5 via heat exchanger 9, the forward flow direction of high temperature scco 2 is the direction indicated by the arrow in fig. 6, along which the tip tail of airfoil fin 93 is on the left and the blunt tip is on the right, during which high temperature scco 2 flows in from the blunt tip (near a) of airfoil fin 93; the high-temperature sCO2 flows out from the tail parts of the tips of the wing-shaped fins, is well attached to the wall surfaces of the wing-shaped fins 93, and does not break away from the boundary layer, so that the reflux blocking effect is avoided, and the function of guiding the high-temperature sCO2 flowing in the forward direction is realized.
Referring to fig. 7 and 9, during the process of flowing out high temperature scco 2 of the turbine 2 into the cooler 5 via the heat exchanger 9, a backflow of part of the high temperature scco 2 occurs in the heat exchange channel 94, that is, the flow direction of part of the high temperature scco 2 is the direction indicated by the arrow in fig. 7, and at this time, the backflow of the high temperature scco 2 flows in from the tip tail of the airfoil fin 93; from the blunt tip of the winged fin (near a). When flowing out, the high-temperature sCO2 can be separated from a flowing boundary layer at the blunt surface head (near a) of the wing fin 93, so that the high-temperature sCO2 is cut off, then the high-temperature sCO2 at other positions in the heat exchange channel 94 flows back to the blunt surface head (near a) of the wing fin 93 under the action of a reverse pressure gradient to form a backflow area, and the kinetic energy of the high-temperature sCO2 is consumed due to the existence of a large amount of vortexes in the backflow area, so that the resistance of the high-temperature sCO2 is increased, the flowing of the high-temperature sCO2 is blocked, and the function of blocking the flow of the reversely flowing high-temperature sCO2 is realized.
Further, in order to increase the path of the high-temperature fluid medium flowing through the first heat exchange plate 921, the path length of each set of the second microfluidic channels 9412 is smaller than the path length of the first microfluidic channels 9411 to increase the heat exchange effect.
In an exemplary embodiment, referring again to fig. 6 and 7, in the same channel portion 941, a first bending angle is formed between the channel inlet of the third micro-channel 9413 and the channel outlet of the second micro-channel 9412, the first bending angle is an obtuse angle, and an angle between the channel inlet of the third micro-channel 9413 and the channel outlet of the first micro-channel 9411 is 180 °, in two adjacent channel portions 941, a second bending angle is formed between the channel outlet of the third micro-channel 9413 in the front channel portion 941 and the channel inlet of the second micro-channel 9412 in the rear channel portion 941, a third bending angle is formed between the channel outlet of the third micro-channel 9413 in the front channel portion 941 and the channel inlet of the first micro-channel 9411, and the second bending angle is an obtuse angle. The flow is converged into the third microfluidic channel 9413 through the second microfluidic channel 9412 and the first microfluidic channel 9411 in the forward flow direction of the flow, and then flows out into the channel portion 941 of the next stage through the third microfluidic channel 9413, and the above-described steps are repeated.
For example, the third micro-fluidic channel 9413, the second micro-fluidic channel 9412 may be a straight line segment, and the third micro-fluidic channel 9413 and the second micro-fluidic channel 9412 are connected in a folded line shape, such that a first folded angle is formed between a channel inlet of the third micro-fluidic channel 9413 and a channel outlet of the second micro-fluidic channel 9412, and a second folded angle is formed between a channel outlet of the third micro-fluidic channel 9413 and a channel inlet of the second micro-fluidic channel 9412 in the subsequent channel portion 941, the first folded angle may be the same as the second folded angle, and a folded direction between the second micro-fluidic channel 9412 and the third micro-fluidic channel 9413 in the same channel portion is opposite to a folded direction between the third micro-fluidic channels 9413 in an adjacent channel portion, such that the heat exchange channel extends along a straight line direction as a whole.
It should be understood that, the angle between a certain structure a and a structure B described in the present application means an angle formed between two outer side walls of the structure a and the structure B.
The first micro-channel 9411 may be arc-shaped, and in the same channel portion 941, a first included angle is formed between the channel inlet of the first micro-channel 9411 and the channel inlet of the second micro-channel 9412, a second included angle is formed between the channel outlet of the first micro-channel 9411 and the channel outlet of the second micro-channel 9412, and the first included angle is greater than the second included angle, so that the arc-shaped first micro-channel 9411 is equivalent to forming an eccentric structure, and is inclined towards one side of the channel portion of the previous stage to form the eccentric structure. As such, the second microfluidic channel 9412 has a path length that is less than the path length of the first microfluidic channel 9411.
As can be appreciated in connection with the above embodiments, any two adjacent sets of channel portions 941, the third microfluidic channel 9413 and the second microfluidic channel 9412 of each set are connected in a folded line shape, and a first folded angle is formed, and a first folded angle area c is adjacent to the first folded angle; the second microfluidic channels 9412 of the first group are connected to the third microfluidic channels 9413 of the adjacent second group in a folded line shape, a second folded angle is formed, a second folded angle region b is provided near the second folded angle, one end of the first microfluidic channel 9411 of the first group is connected to the first folded angle region b, and the other end is connected to the second folded angle region c.
Referring to fig. 7, in the process that the high temperature scco 2 flowing out of the turbine 2 enters the first heat exchange plate 921 of the heat exchanger 9, the side wall of the heat exchange channel 94 is combined with the airfoil fins 93 to block the flow of the high temperature scco 2 flowing backward to the turbine 2. That is, when the high temperature scco 2 flows backward through the first corner region b, the high temperature scco 2 is separated from the fluid boundary layer at the blunt surface head of the airfoil fin 93 to generate a reverse difference, so that the high temperature scco 2 flowing backward at other positions flows backward, and a vortex is generated in the first corner region b, thereby consuming kinetic energy of the high temperature scco 2 flowing backward, reducing the flow velocity of the high temperature scco 2 flowing backward, and realizing flow blocking of the high temperature scco 2 flowing backward.
When the high-temperature scco 2 flows back through the second corner region c, since the high-temperature scco 2 generates a vortex in the first corner region b, a part of the flowing direction of the high-temperature scco 2 flowing back is deflected, and flows along the second microfluidic channel 9412 or flows forward along the third microfluidic channel 9413; the other part flows along the first micro-flow channel 9411, the flow direction deflects to a large extent, and two high temperature scco 2 collide in the second corner region c, so that the fluid kinetic energy of the high temperature scco 2 is further consumed, and the flow direction of the high temperature scco 2 deflects, and flows forward along the second micro-flow channel 9412 or flows along the third micro-flow channel 9413 of the adjacent group.
It should be noted that, since the high temperature scco 2 flowing out of the third micro-channel has a velocity component opposite to the flow direction of the high temperature scco 2 flowing out of the second micro-channel 9412, the high temperature scco 2 flowing out of the third micro-channel may have a trapping effect on the high temperature scco 2 flowing out of the second micro-channel 9412, so as to weaken the flow velocity of the high temperature scco 2 flowing back in the second micro-channel 9412, and achieve the purpose of reverse flow blocking.
In the present application, the included angle formed between the microfluidic channel a and the microfluidic channel B refers to the included angle between the microfluidic channel a and the microfluidic channel B in the forward flow direction of the fluid.
Further, each set of second microfluidic channels 9412 and/or first microfluidic channels 9411 is semi-circular or rectangular in cross-section.
In an example embodiment, referring again to fig. 6 or 7, the second microfluidic channel 9412 is a through groove having a semicircular cross section along the M-M line or a through groove having a rectangular cross section. And the first microfluidic channel 9411 is a through groove having a semicircular cross section along the H-H line or a through groove having a rectangular cross section.
Further, in order to further block the high-temperature fluid medium flowing backward in the first heat exchange plate 921, a comb structure 95 is disposed on a side wall of the channel inlet of each group of third micro-channels 9413 near the channel outlet of the second micro-channel 9412.
As can be appreciated in connection with the above embodiments, the first corner region b is formed at the connection between each group of third micro-fluidic channels 9413 and the second micro-fluidic channels 9412, the comb structures 95 are disposed on the side walls of the third micro-fluidic channels 9413 near the second micro-fluidic channels 9412 in the same channel portion 941, and the comb structures 95 are located in the first corner region b.
It will be appreciated that referring to fig. 10, when the scco 2 flowing out of the turbine 2 enters the heat exchanger 9, the scco 2 at this time is a high-temperature fluid medium, and the high-temperature scco 2 enters the heat exchange channel 94 of the first heat exchange plate 921 from the high-temperature fluid medium inlet 911, and the high-temperature scco 2 first contacts the blunt surface head portion of the airfoil fin 93, flows in from the blunt surface head portion of the airfoil fin 93, and then flows out from the tip tail portion of the airfoil fin 93. The high temperature sCO2 is well attached to the wall surface of the wing-shaped fin 93, and the boundary layer of the high temperature sCO2 is not separated, so that the reflux blocking effect is avoided. Meanwhile, the comb tooth structure 95 can not block high-temperature sCO2 flowing in the forward direction, so that the high-temperature sCO2 can pass smoothly.
Referring to fig. 11, when the high temperature scco 2 in the heat exchanger 9 flows reversely to the turbine 2, the high temperature scco 2 flows in from the blunt surface tips of the wing fins and flows out from the tip tails of the wing fins, and the high temperature scco 2 flowing reversely generates a vortex in the first corner region b, which retards the reverse flow of the high temperature scco 2. At the same time, the comb structure 95 further blocks the flow of high temperature scco 2 in the first fold angle region b. That is, when the high temperature scco 2 flowing backward flows through the first corner region b, the comb structure 95 breaks the boundary layer near the wall surface of the third micro-channel 9413, so that the high temperature scco 2 is separated from the near wall surface of the third micro-channel 9413, the flow velocity of the vortex in the first corner region b is enhanced, and the blocking of the high temperature scco 2 flowing backward is realized.
Further, in order to further improve the heat exchange efficiency, the channel portion 941 of the embodiment of the present application may further include a fourth microfluidic channel 9414.
In an example embodiment, the heat exchange channels 94 on the first heat exchange plate 921 may include a third microfluidic channel 9413, a second microfluidic channel 9412, a first microfluidic channel 9411, and a fourth microfluidic channel 9414, and the fourth microfluidic channel 9414 and the first microfluidic channel 9411 are located at both sides of the third microfluidic channel 9413, respectively; the channel inlets of the fourth microfluidic channel 9414 are respectively communicated with the channel inlets of the third microfluidic channel 9413 and the channel outlets of the second microfluidic channel 9412 in the same channel portion 941, and the channel outlets of the fourth microfluidic channel 9414 are respectively communicated with the channel outlets of the third microfluidic channel 9413 in the same channel portion 941 and the channel inlets of the second microfluidic channel 9412 and the channel inlets of the first microfluidic channel 9411 in adjacent channel portions 941; the channel inlet of the fourth microfluidic channel 9414 and the channel inlet of the third microfluidic channel 9413 have a fourth bending angle therebetween, the fourth bending angle is an obtuse angle, and the angle between the channel outlet of the fourth microfluidic channel 9414 and the channel inlet of the second microfluidic channel 9412 in the adjacent channel portion 941 is 180 °.
As can be appreciated, for example, referring to fig. 12 and 13, a first set of third microfluidic channels 9413 is shown in communication with the air inlet 96, the second microfluidic channels 9412, and the second microfluidic channels 9412 are in communication with the first microfluidic channels 9411; the third microfluidic channel 9413 of the second set is in communication with the second microfluidic channel 9412 of the first set, the second microfluidic channel 9412 of the second set, the fourth microfluidic channel 9414 of the second set, the second microfluidic channel 9412 of the second set is in communication with the first microfluidic channel 9411 of the second set; similarly, the third microfluidic channel 9413, the second microfluidic channel 9412, the first microfluidic channel 9411, and the fourth microfluidic channel 9414 that realize a plurality of sets of communication communicate with the air inlet 96 and the air outlet 97 of the first heat exchange plate 921. In this connection manner, the first micro-fluidic channel 9411 is located on one side of the second micro-fluidic channel 9412, and the fourth micro-fluidic channel 9414 is located on the other side of the second micro-fluidic channel 9412, so that the heat exchange efficiency of the heat exchanger 9 can be effectively improved. And the third microfluidic channel 9413 communicating with the fourth microfluidic channel 9414 may be all channel portions 941 after the first set of channel portions 941.
The arrow shown in fig. 12 indicates the forward flow direction of high temperature scco 2 in the channel portion 941, and the arrow shown in fig. 13 indicates the reverse flow direction of high temperature scco 2 in the channel portion 941.
In an exemplary embodiment, in the same channel portion 941, a third included angle is formed between the channel inlet of the fourth microfluidic channel 9414 and the channel inlet of the third microfluidic channel 9413, and a fourth included angle is formed between the channel outlet of the fourth microfluidic channel 9414 and the channel outlet of the third microfluidic channel 9413, where the third included angle is greater than the fourth included angle. In this way, the fourth microfluidic channel 9414 also has an eccentric structure, and is inclined toward the channel portion side of the preceding stage.
On the basis of the above embodiment, the first included angle and the third included angle are obtuse angles, the second included angle and the fourth included angle are acute angles, the first included angle is the same as the third included angle, and the second included angle is the same as the fourth included angle.
As an alternative embodiment, an embodiment of the present application provides a specific structure of the second heat exchange plate 922.
Referring to fig. 14, unlike the first heat exchange plate 921, the air inlet 96 on the second heat exchange plate 922 is located at one end of the second heat exchange plate 922 in the own length direction, and the air outlet 97 on the second heat exchange plate 922 is located at the other end of the second heat exchange plate 922 in the own length direction. And the heat exchange channels 94 on the second heat exchange plate 922 are distributed along the width direction of the second heat exchange plate 922 near both ends of the air inlet 96 and the air outlet 97.
For example, in fig. 14, six air inlets 96 are formed along the upper wall of the second heat exchange plate 922 in the width direction, six air outlets 97 are formed along the lower wall of the second heat exchange plate 922 in the width direction, six heat exchange channels 94 are formed along the width direction of the second heat exchange plate 922, and the six heat exchange channels 94 are respectively in one-to-one correspondence with the six air outlets 97 and the six air inlets 96. The heat exchange channels 94 near both ends of the air inlet 96 and the air outlet 97 are distributed along the width direction of the second heat exchange plate 922; the heat exchange passages 94 located at the middle region of the second heat exchange plate 922 are distributed along the length direction of the second heat exchange plate 922.
Further, the heat exchange channels 94 on the second heat exchange plate 922 may include several sets of channel portions 941, and each set of heat exchange channels 94 may include a third microfluidic channel 9413, a second microfluidic channel 9412, and a first microfluidic channel 9411. Wherein the third microfluidic channel 9413 communicates with the second microfluidic channel 9412, and the first microfluidic channel 9411 communicates with the third microfluidic channel 9413.
Further, the heat exchange channels 94 on the second connection plate may further include a fourth micro-channel 9414, the first set of third micro-channels 9413 is in communication with the second micro-channel 9412 and the first micro-channel 9411, the second set of third micro-channels 9413 is in communication with the first set of second micro-channels 9412 and the second set of first micro-channels 9411, the second set of second micro-channels 9412 is in communication with the fourth micro-channel 9414, and so on until the last set of second micro-channels 9412 is in communication with the air outlet 97 of the second heat exchange plate 922. And the first microfluidic channel 9411 is located on one side of the second microfluidic channel 9412, and the fourth microfluidic channel 9414 is located on the other side of the second microfluidic channel 9412.
It should be noted that, the third micro-flow channel 9413 on the second heat exchange plate 922 is communicated with the second micro-flow channel 9412 in a folded line shape, and the first micro-flow channel 9411 is in an arc shape; and the cross-section of each set of the second micro-fluid channels 9412 and/or the first micro-fluid channels 9411 is semicircular or rectangular, which is consistent with the principle of the first heat exchange plate 921 described above, specifically please refer to the above embodiment.
Further, the wing fins 93 on the second heat exchange plate 922 are located in the third micro-flow channel 9413 and the second micro-flow channel 9412 in the heat exchange channel 94, wherein the wing fins 93 are combined with the side wall of the heat exchange channel 94 to guide the low temperature sCO2 flowing forward to the turbine 2, and block the low temperature sCO2 flowing backward to the compressor 6, so that the low temperature sCO2 cannot flow into the compressor 6 from the heat exchanger 9, and the low temperature sCO2 prevented from flowing backward reversely impacts and turns the impeller of the compressor 6, so that the heat exchanger 9 has the functions of forward guide and reverse flow blocking, and replaces the second check valve 8.
It should be noted that the principles of the forward flow guiding and reverse flow blocking of the airfoil fins 93 on the second heat exchange plate 922 are identical to the principles of the forward flow guiding and reverse flow blocking of the airfoil fins 93 on the first heat exchange plate 921 for the high temperature scco 2. Please refer to the embodiment of the first heat exchange plate 921, which is not described in detail in this embodiment.
The foregoing description is only of the preferred embodiments of the present application, and is not intended to limit the scope of the claims, and all equivalent structures or equivalent processes using the descriptions and drawings of the present application, or direct or indirect application in other related technical fields are included in the scope of the claims of the present application.
Claims (9)
1. A heat exchanger, the heat exchanger comprising:
the pipe box is provided with a high-temperature fluid medium inlet, a high-temperature fluid medium outlet, a low-temperature fluid medium inlet and a low-temperature fluid medium outlet;
the heat exchange core body comprises a first cover plate, a second cover plate, a first heat exchange plate and a second heat exchange plate; the first heat exchange plates and the second heat exchange plates are alternately laminated and distributed to form a porous core body, and the first cover plate and the second cover plate are correspondingly arranged on two sides of the porous core body so as to cover the porous core body;
the high-temperature fluid medium inlet is communicated with the high-temperature fluid medium outlet through the first heat exchange plate so as to circulate high-temperature fluid medium, the low-temperature fluid medium inlet is communicated with the low-temperature fluid medium outlet through the second heat exchange plate so as to circulate low-temperature fluid medium, and the heat exchange core exchanges heat between the passing high-temperature fluid medium and low-temperature fluid medium through the first heat exchange plate and the second heat exchange plate;
The first heat exchange plate and the second heat exchange plate are respectively provided with a heat exchange channel and an airfoil fin positioned in the heat exchange channels; the heat exchange channel comprises a plurality of channel parts which are connected in sequence, wherein each channel part comprises a first micro-flow channel, a second micro-flow channel and a third micro-flow channel; wherein, in the same channel part, the channel inlet of the third microfluidic channel is respectively communicated with the channel outlet of the second microfluidic channel and the channel outlet of the first microfluidic channel; in two adjacent channel parts, the channel outlet of the third micro-flow channel in the former channel part is communicated with the channel inlet of the second micro-flow channel and the channel inlet of the first micro-flow channel in the latter channel part;
the wing-shaped fin is provided with a blunt head and a sharp tail which are oppositely arranged, and the blunt head of the wing-shaped fin is positioned at one side of the sharp tail close to the fluid medium inlet; the orthographic projection of the wing-shaped fin on the plane where the first cover plate is located is an arc-shaped structure, the arc-shaped structure has a first curvature at a position corresponding to the blunt surface head part and a second curvature at a position corresponding to the tip tail part, and the first curvature is smaller than the second curvature.
2. The heat exchanger of claim 1, wherein in the same channel portion, a first bend angle is provided between a channel inlet of the third microfluidic channel and a channel outlet of the second microfluidic channel, the first bend angle being 90 ° or more, and an angle between the channel inlet of the third microfluidic channel and the channel outlet of the first microfluidic channel is 180 °;
in the two adjacent channel parts, a second bending angle and a third bending angle are respectively arranged between a channel outlet of a third micro-flow channel in the front channel part and a channel inlet of a second micro-flow channel in the rear channel part and between the channel inlets of the first micro-flow channels, wherein the second bending angle is an obtuse angle smaller than or equal to 270 degrees, and the third bending angle is an acute angle.
3. The heat exchanger of claim 1, wherein the third microfluidic channel has a channel inlet provided with a comb structure on a side wall adjacent to the channel outlet of the second microfluidic channel.
4. The heat exchanger of claim 1, wherein the airfoil fins are located within the third and second microfluidic channels and the airfoil fins are evenly spaced within the third and second microfluidic channels.
5. The heat exchanger of claim 1, wherein the path length of the second microfluidic channel is less than the path length of the first microfluidic channel.
6. The heat exchanger of claim 2, wherein the channel portion further comprises a fourth microfluidic channel, and the fourth microfluidic channel and the first microfluidic channel are located on either side of a third microfluidic channel, respectively;
the channel inlets of the fourth microfluidic channels are respectively communicated with the channel inlets of the third microfluidic channels and the channel outlets of the second microfluidic channels in the same channel part, and the channel outlets of the fourth microfluidic channels are respectively communicated with the channel outlets of the third microfluidic channels in the same channel part, the channel inlets of the second microfluidic channels in adjacent channel parts and the channel inlets of the first microfluidic channels;
a fourth bending angle is arranged between the channel inlet of the fourth micro-flow channel and the channel inlet of the third micro-flow channel, the fourth bending angle is an obtuse angle, and the angle between the channel outlet of the fourth micro-flow channel and the channel inlet of the second micro-flow channel in the adjacent channel part is 180 degrees.
7. The heat exchanger of claim 6, wherein in the same channel section, a first included angle is formed between the channel inlet of the first microfluidic channel and the channel inlet of the second microfluidic channel, a second included angle is formed between the channel outlet of the first microfluidic channel and the channel outlet of the second microfluidic channel, and the first included angle is greater than the second included angle;
In the same channel part, a third included angle is formed between the channel inlet of the fourth microfluidic channel and the channel inlet of the third microfluidic channel, a fourth included angle is formed between the channel outlet of the fourth microfluidic channel and the channel outlet of the third microfluidic channel, and the third included angle is larger than the fourth included angle.
8. The heat exchanger of claim 7, wherein the first angle and the third angle are obtuse angles, the second angle and the fourth angle are acute angles, and the first angle and the third angle are the same, and the second angle is the same as the fourth angle.
9. A heat exchange system, comprising:
the heat exchanger of any one of claims 1-8;
the heat exchange system also comprises a heat source, a turbine, a generator, a cooler and a compressor;
the heat source comprises a heat source, a heat exchanger, a heat generator, a cooler, a compressor, a turbine, a heat source, a heat exchanger, a heat source, a heat generator and a generator, wherein the first output end of the heat exchanger is connected with the input end of the heat source, the output end of the heat source is connected with the input end of the turbine, the output end of the turbine is connected with the second input end of the heat exchanger, the second output end of the heat exchanger is connected with the input end of the cooler, the output end of the cooler is connected with the input end of the compressor, the output end of the compressor is connected with the first input end of the heat exchanger, and the generator is connected with the turbine.
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