CN107255425B - Heat exchange plate, machining method and heat exchanger - Google Patents
Heat exchange plate, machining method and heat exchanger Download PDFInfo
- Publication number
- CN107255425B CN107255425B CN201710498151.8A CN201710498151A CN107255425B CN 107255425 B CN107255425 B CN 107255425B CN 201710498151 A CN201710498151 A CN 201710498151A CN 107255425 B CN107255425 B CN 107255425B
- Authority
- CN
- China
- Prior art keywords
- flow
- flow channel
- heat exchange
- channel
- branch
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Classifications
-
- 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)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The invention discloses a heat exchange plate, a processing method and a heat exchanger, and relates to the field of heat exchange equipment. Be equipped with two collection grooves and flute profile runner on the first surface of heat transfer board, two collection grooves are located the heat transfer board both ends respectively, and the flute profile runner includes: the grading flow channel is communicated from one flow collecting groove to the other flow collecting groove and comprises two main flow channels which are respectively communicated with the two flow collecting grooves, and the two main flow channels are communicated through at least two first branch flow channels; the reticular flow channels are arranged between the adjacent first branch flow channels and are communicated with the first branch flow channels in a fluid mode; meanwhile, the cross section area of the reticular flow passage is smaller than that of the first branch flow passage, and the grading flow passage and the reticular flow passage form a vein-shaped fluid distribution structure. The invention effectively improves the fluid distribution uniformity and increases the effective heat transfer area through the combined action of the main driving force of the grading flow channel and the capillary force of the reticular flow channel, so that the flow velocity of the fluid is reduced under the same flow rate, and the resistance is reduced.
Description
Technical Field
The invention relates to the field of heat exchange equipment, in particular to a heat exchange plate, a processing method and a heat exchanger.
Background
With the rapid development of the fourth-generation high-temperature reactor technology and the clean thermal power technology, the highly matched supercritical fluid Brayton cycle becomes a hot point of domestic and foreign research, and has a tendency of replacing the existing steam Rankine cycle. Because the Brayton cycle has the characteristic of high heat regeneration and is under the condition of gas-gas heat exchange, the supercritical fluid heat exchanger becomes the equipment with the largest volume in the power system, the volume of the supercritical fluid heat exchanger accounts for more than 90 percent of the total equipment volume of the power system, and meanwhile, the performance of the supercritical fluid heat exchanger has important significance on the integration level, the stability, the controllability and the safety of the power system.
The traditional tube-fin shell-and-tube heat exchanger is formed by combining heat exchange tubes and fins in a brazing mode, is suitable for heat exchange of conventional gas or liquid working media, does not meet the heat exchange requirement of high-temperature and high-pressure supercritical fluid media, is easy to lose effectiveness due to internal deformation caused by thermal expansion stress and creep deformation of the fins, and is easy to leak due to corrosion of brazing materials. Due to the physical characteristics of high temperature and high pressure, high density and low viscosity of the supercritical fluid, the micro-channel heat exchanger utilizes the characteristic that the volume flow and the frictional resistance of the supercritical fluid are correspondingly small, so that the heat exchange efficiency is higher, and the economy and the safety are better. For example, the basic element of a printed circuit board heat exchanger proposed by Heatric corporation is a microchannel plate, channels with various configurations, such as a straight channel, a herringbone channel and an S-shaped channel, are formed on the plate by chemical etching, and the heat exchanger formed by alternately overlapping cold and hot plates layer by layer has the advantages of good pressure bearing capacity, high heat exchange efficiency and the like, and the volume of the heat exchanger is reduced by 85% compared with that of a shell-and-tube heat exchanger under the same thermal load condition. However, the highly compact arrangement of the printed circuit board microchannel heat exchanger and the microscale channel can cause the practical problems of the heat exchanger such as the sharp increase of resistance, the uneven flow distribution, the over-high local temperature of the plate sheet and the like while the size of the heat exchanger is greatly reduced, and the problems not only cause the increase of compression power consumption, but also affect the efficiency and the economy of the whole system.
Disclosure of Invention
In view of the defects in the prior art, the main object of the present invention is to provide a heat exchange plate, and another object of the present invention is to provide a processing method and a heat exchanger, which can effectively improve the uniformity of flow distribution, prevent local channel blockage, and increase the effective heat transfer area by the combined action of the main driving force of the staged flow channels in the vein-like fluid distribution structure and the capillary force of the mesh flow channels, so as to reduce the flow velocity of the fluid working medium under the same flow rate, and contribute to reducing the resistance.
The invention provides a heat exchange plate, wherein two collecting grooves and a groove-shaped flow passage are arranged on a first surface of the heat exchange plate, the two collecting grooves are respectively positioned at two ends of the heat exchange plate, and the groove-shaped flow passage comprises:
the grading flow channel is communicated from one flow collecting groove to the other flow collecting groove and comprises two main flow channels respectively communicated with the two flow collecting grooves, and the two main flow channels are communicated through at least two first branch flow channels;
the reticular flow channels are arranged between the adjacent first branch flow channels and are communicated with the first branch flow channels in a fluid mode; at the same time, the user can select the desired position,
the cross-sectional area of the reticular flow passage is smaller than that of the first branch flow passage, and the grading flow passage and the reticular flow passage form a vein-shaped fluid distribution structure.
On the basis of the technical scheme, at least one secondary flow channel is further arranged between the adjacent first branch flow channels, the secondary flow channel is communicated with the mesh flow channel between the adjacent first branch flow channels in a fluid mode, and the cross section area of the secondary flow channel is smaller than that of the first branch flow channel and larger than that of the mesh flow channel.
On the basis of the technical scheme, the cross sections of the grading flow channel, the reticular flow channel and the secondary flow channel are all semicircular.
On the basis of the technical scheme, the sum of the diameters of the at least two first branch flow passages is equal to the diameter of the main flow passage.
On the basis of the technical scheme, the diameter D of the reticular flow passagewComprises the following steps: dw＝aDzWherein D iszThe diameter of the first branch flow channel is 1/3-1/10.
On the basis of the technical scheme, one end of the main flow channel, which is far away from the flow collecting groove, and at least two first branch flow channels form a branched structure, and the included angle between each first branch flow channel and the main flow channel is not less than 0 and not more than α and not more than 90.
On the basis of the technical scheme, at least two second branch flow passages are further arranged in the middle of the first branch flow passage, the first branch flow passage and the at least two second branch flow passages form a branched structure, and the included angle range between the second branch flow passages and the first branch flow passage is greater than or equal to 0 and less than or equal to α and less than 90.
On the basis of the technical scheme, the second surface of the heat exchange plate is provided with two flow collecting grooves and a groove-shaped flow passage, the flow collecting grooves on the first surface are provided with first outlets, the flow collecting grooves on the second surface are provided with second outlets, and the positions of the first outlets and the second outlets are different.
The invention also provides a processing method of the heat exchange plate, which comprises the following steps:
s1, polishing treatment of machining is carried out on the heat exchange plate so as to improve the smoothness of the heat exchange plate;
s2, processing a grading flow channel on the heat exchange plate by a chemical etching method;
and S3, processing the reticular flow channel by adopting a laser etching method.
The invention also provides a heat exchanger, which comprises a plurality of heat exchange plates, wherein the heat exchange plates are stacked, the surface of one heat exchange plate, which is provided with the other heat exchange plate, is provided with the flow collecting groove and the groove-shaped flow passage, and the flow collecting groove and the groove-shaped flow passage of the adjacent heat exchange plates are spliced to form a fluid passage.
Compared with the prior art, the collecting tank is communicated with the first branch runners through the main runner, and the first branch runners are communicated through the reticular runners to form the vein-shaped fluid distribution structure, so that the invention has the following advantages:
(1) improving the flow uniformity: the main driving force of the grading flow channel in the vein-shaped fluid distribution structure and the capillary force of the reticular flow channel are combined, so that the uniformity of fluid distribution can be effectively improved, and local channel blockage is prevented.
(2) Increase effective heat transfer area, reduce runner resistance: the total area of the cross section of circulation is greatly increased through the grading flow channel and the reticular flow channel, so that the effective heat transfer area can be increased, the flow speed of the fluid working medium under the same flow is reduced, the resistance is reduced, the power consumption is saved, and the flow heat exchange efficiency is improved.
(3) Reducing the thermal stress: the mesh-shaped flow channel is adopted to enable the distribution range of the fluid working medium in the heat exchange plate to be larger, so that the temperature distribution of the heat exchange plate surface is more uniform, and the thermal stress caused by local high temperature gradient can be effectively reduced.
Drawings
FIG. 1 is a schematic diagram of the microchannel structure on the front side of a heat exchange plate according to an embodiment of the present invention;
FIG. 2 is an enlarged view of a portion of the staging channel of FIG. 1;
FIG. 3 is a schematic view of two embodiments of the reticulated flow passage of the present invention;
FIG. 4 is a schematic view of a microchannel configuration on the opposite side of a heat exchange plate according to an embodiment of the invention;
FIG. 5 is a schematic structural view of a microchannel heat exchanger according to an embodiment of the invention;
FIG. 6 is a side view A of FIG. 5;
fig. 7 is a side view B of fig. 5.
Reference numerals:
1-a collecting channel, 101-a first outlet, 102-a second outlet, 2-a grading channel, 21-a main channel, 22-a first branch channel, 221-a lateral extension section, 222-a horizontal extension section, 3-a reticular channel, 4-a secondary channel and 5-a miniature secondary channel.
Detailed Description
In the embodiment of the invention, the vein-shaped fluid distribution structure comprising the grading flow channel 2, the secondary flow channel 4 and the reticular flow channel 3 positioned between the grading flow channel 2 and the secondary flow channel 4 is formed on the front surface and the back surface of the same heat exchange plate through machining, chemical etching and laser etching and is used as a fluid heat transfer micro-channel for heat exchange of fluid (such as supercritical fluid), and the positions of the vein-shaped heat transfer micro-channels on the front surface and the back surface of the same heat exchange plate are corresponding, so that the heat transfer micro-channel with the vein-shaped fractal characteristics generates more and more branches, the convection heat exchange area is greatly increased, the convection heat exchange effect is enhanced, the flow resistance of a working medium is reduced by utilizing the vein bionic structure, the working medium is conveyed to each part of the heat exchange plate under the premise of minimum energy consumption, and the heat transfer performance of a.
The invention is described in further detail below with reference to the figures and the embodiments.
Referring to fig. 1, an embodiment of the present invention provides a heat exchange plate, which has no limitation on the shape, and for example, the heat exchange plate may be a rectangular or circular plate, a first surface of the heat exchange plate is provided with two flow collecting grooves 1 and groove-shaped flow channels, the first surface may be a front surface or a back surface, the heat exchange plate may also be a three-dimensional solid body with any shape for heat exchange, and at least one surface (for example, an outer surface) of the solid body is provided with two flow collecting grooves 1 and groove-shaped flow channels. The runner structure on the front and/or back of the heat exchange plate mainly comprises an inlet part, a heat exchange area and an outlet part, wherein two collecting grooves 1 respectively positioned at two ends of the heat exchange plate form the inlet part and the outlet part, and the groove-shaped runner forms the heat exchange area. The fluid flowing into the inlet part is firstly divided into the groove-shaped flow channels, flows into the outlet part after being converged, and then leaves the heat exchange plate, and the fluid can enter the heat exchange area without being bent after entering the heat exchange plate.
The channel-shaped flow channels comprise at least one classifying flow channel 2, a reticular flow channel 3 and at least one secondary flow channel 4. The grading flow channels 2 are communicated from one collecting groove 1 to another collecting groove 1, and the number of the grading flow channels 2 is determined according to the size of the heat exchange area of the heat exchange plate, for example, 3 grading flow channels 2 are shown in fig. 1. Referring to fig. 2, each of the classifying channels 2 includes two main channels 21 respectively communicating with the two collecting channels 1, and the two main channels 21 communicate with each other through at least two first branch channels 22. The reticulated flow channels 3 and the secondary flow channels 4 are both disposed between adjacent first sub-flow channels 22, and the reticulated flow channels 3, the secondary flow channels 4 and the adjacent first sub-flow channels 22 are in fluid communication with each other.
The total area of the cross section of circulation can be greatly increased through the grading flow channel 2, the reticular flow channel 3 and the secondary flow channel 4, so that the effective heat transfer area can be increased, the flow speed of the fluid working medium under the same flow is reduced, the flow channel resistance is reduced, the power consumption is saved, and the flow heat exchange efficiency is improved.
The cross-sectional area of the reticular flow channel 3 is smaller than that of the first branch flow channel 22, the cross-sectional area of the secondary flow channel 4 is smaller than that of the first branch flow channel 22 and larger than that of the reticular flow channel 3, and the grading flow channel 2, the secondary flow channel 4 and the reticular flow channel 3 form a vein-shaped fluid distribution structure. The fluid in the collecting channel 1 as an inlet portion flows into the main channel 21, is first divided into at least two first branch channels 22, then flows into the collecting channel 1 as an outlet portion, and at the same time, the fluid in the first branch channels 22 near the inlet portion enters the secondary channels 4 and the reticular channels 3, merges into the first branch channels 22 near the outlet portion, flows into the collecting channel 1 as an outlet portion through the main channel 21, and finally exits the heat exchange plate.
The main driving force of the fluid in the main flow channel 21 and the first branch flow channel 22 and the capillary force of the reticular flow channel 3 act together, so that the uniformity of flow distribution can be effectively improved, the local channel blockage is prevented, and the flow uniformity is improved.
The cross sections of the grading flow channel 2, the reticular flow channel 3 and the secondary flow channel 4 are all semicircular, the central lines connected with the semicircular circle centers of all the main flow channels 21 are all positioned on the same plane, and similarly, for the first branch flow channel 22, the reticular flow channel 3 or the secondary flow channel 4, the central lines connected with the semicircular circle centers are all positioned on the same plane, so that the uniformity of fluid distribution can be further improved, the local channel blockage is prevented, and the flow uniformity is improved.
The length of the main flow passage 21 is L1One end of the main flow channel 21 is communicated with the collecting groove 1, one end of the main flow channel 21, which is far away from the collecting groove 1, and at least two first branch flow channels 22 form a branching structure, the number of the first branch flow channels 22 is s, s is a positive integer, s is 2, 3, 4 … …, the included angle range between the first branch flow channels 22 and the main flow channel 21 is 0- α < 90, the diameter range of the first branch flow channels 22 is 500-1500 micrometers, and the sum of the diameter cubes of the s sections of the first branch flow channels 22 is equal to the cube of the diameter of the main flow channel 21, so that the uniform distribution of the flow of a fluid working medium is facilitated, the phenomenon that the flow velocity of individual flow channels is too high is avoided, the flow velocity can be ensured not to have obvious mutation when the fluid flows through the main flow channel 21 and the first branch.
Fig. 2 illustrates an example of a branching structure, in which one end of the main flow channel 21 away from the header 1 is branched into 3 first branch flow channels 22, wherein the middle 1 first branch flow channel 22 is parallel to the main flow channel 21, the other 2 first branch flow channels 22 are expanded to both sides at a proper angle α (0 ≦ α ≦ 90), the first branch flow channel 22 includes a lateral extension section 221 and a horizontal extension section 222, both ends of the lateral extension section 221 are respectively communicated with the main flow channel 21 and the horizontal extension section 222, and an included angle between the lateral extension section 221 and the main flow channel 21 ranges from 0 ≦ α ≦ 90. s, diameters of the first branch flow channels 22 may be the same or slightly different, and a sum of the diameters of the cubes of the first branch flow channels 22 in the s section is equal to a cube of the diameter of the main flow channel 21.
The secondary flow passage 4 communicates with the horizontally extending section 222 in the adjacent first branch flow passage 22 and is perpendicular to the horizontally extending section 222 in the first branch flow passage 22, so that the uniformity of fluid distribution can be further improved, local passage blockage is prevented, and the flow uniformity is improved.
Referring to fig. 1, the stepped flow channel 2, the mesh flow channel 3 and the secondary flow channel 4 have at least 3 stages and are spread out in a planar manner, the main flow channel 21, the first branch flow channel 22 and the second branch flow channel 23 form a main vein channel, the adjacent first branch flow channels 22 form a secondary vein channel through the perpendicular secondary flow channel 4, the main vein channels are distributed in a radial manner on one side far away from the collecting channel 1, a plurality of polygonal areas are formed between the main vein channels and the secondary vein channels, and the mesh flow channels 3 are arranged in the polygonal areas to jointly form a vein-shaped heat transfer channel, so that the ratio of the main vein channels, the secondary vein channels and the whole heat exchange plate can be improved, and the problems of excessive heating and excessive local temperature caused by local channel blockage can be avoided.
Referring to fig. 3, the mesh-shaped flow channel 3 may adopt a triangular mesh structure, a quadrangular mesh structure, a pentagonal mesh structure, a hexagonal mesh structure, or even an irregular polygonal mesh structure, and the side length of the polygonal structure is not greater than 1/5 of the size of the polygonal area, so as to ensure that the mesh-shaped flow channel 3 has a certain distribution density in the whole heat exchange area. The fluid working medium is distributed in a wider range in the heat exchange plate by adopting the reticular flow passage 3, thereby ensuring that the heat exchange is carried outThe temperature distribution of the plate surface is more uniform, and the thermal stress caused by local high temperature gradient can be effectively reduced. Diameter D of the reticular flow passage 3wComprises the following steps: dw＝aDzWherein D iszThe diameter of the first branch flow passage 22 is 1/3-1/10.
The middle part of the first branch flow passage 22 is also provided with at least two second branch flow passages 23, the first branch flow passage 22 and the at least two second branch flow passages 23 form a branching structure, and the fluid working medium dispersedly flows into the second branch flow passages 23 from one end of the first branch flow passage 22 and then converges and flows out from the other end of the first branch flow passage 22.
Referring to FIG. 2, fluid flows into the first branch flow passage 22 over a length L2The formation of the diverging structure, i.e., the second branch flow path 23, may then continue. The number of the second branch flow passages 23 is also s, s is a positive integer, and s is 2, 3, 4 … …, for example, in fig. 2, the second branch flow passages 23 are 2 sections, specifically, at least two second branch flow passages 23 are further provided in the middle of each horizontal extension section 222, and the fluid working medium flows into the second branch flow passages 23 dispersedly from one end of the horizontal extension section 222 and then flows out from the other end of the horizontal extension section 222 in a converging manner. The diameters of the second branch flow passages 23 in the s section can be the same or slightly different, and the sum of the diameters and the cubes of at least two second branch flow passages 23 is equal to the cube of the diameter of the first branch flow passage 22 before branching. The adjacent second branch runners 23 can also be communicated through the micro secondary runner 5, the micro secondary runner 5 is perpendicular to the second branch runners 23, and the reticular runners 3, the micro secondary runner 5 and the adjacent second branch runners 23 are mutually communicated in a fluid manner, so that the uniformity of flow distribution is further improved, the local channel blockage is prevented, and the flow uniformity is improved. The second branch flow path 23 may continue to form a similar new diverging structure.
Referring to fig. 1, the collecting groove 1 on the first surface of the heat exchange plate is provided with a first outlet 101, referring to fig. 4, two collecting grooves 1 and groove-shaped flow passages are arranged on the second surface of the heat exchange plate, the collecting groove 1 on the second surface is provided with a second outlet 102, and the positions of the first outlet 101 and the second outlet 102 are different. The first surface and the second surface are respectively the front surface and the back surface of the heat exchange plate, and the positions of the collecting grooves 1 and the groove-shaped flow passages on the first surface and the second surface are the same, namely the positions of all stages of veins and reticular vein channels in the heat exchange areas on the front surface and the back surface of the heat exchange plate are completely overlapped.
The vein-shaped channel structures are respectively arranged on the front side and the back side of the single heat exchange plate, so that the space can be fully utilized, and the purposes of compact structure and high-efficiency heat exchange of the heat exchanger are achieved. But the front and back surfaces differ as follows: (1) in order to keep the hot fluid and the cold fluid in countercurrent heat exchange, the inlet part and the outlet part on the back surface of the heat exchange plate are opposite to the inlet part and the outlet part on the front surface of the heat exchange plate; the two collecting grooves 1 on the front surface of the heat exchange plate are respectively connected with the inlet and the outlet of a fluid working medium through a first outlet 101, the two collecting grooves 1 on the back surface of the heat exchange plate are respectively connected with the inlet and the outlet of the heat exchange working medium through a second outlet 102, and the positions of the first outlet 101 and the second outlet 102 are different. (2) Due to the limitation of the inlet and outlet positions, the inlet part and the outlet part of the front surface of the heat exchange plate are positioned at the left side and the right side of the plate sheet, and the inlet part and the outlet part of the back surface of the heat exchange plate are positioned at the upper side and the lower side of the plate sheet.
The embodiment of the invention also provides a processing method of the heat exchange plate, which comprises the following steps:
s1, polishing treatment of machining is carried out on a heat exchange plate to improve the smoothness of a plate;
s2, processing a grading flow channel 2 on the heat exchange plate by a chemical etching method;
and S3, processing the reticular flow channel 3 by adopting a laser etching method.
The processing method further comprises the following steps:
and S4, aligning the two heat exchange plates and then performing diffusion welding to enable the grading flow channel 2 and the reticular flow channel 3 to be combined into a circular channel.
Specifically, firstly, polishing treatment of machining is carried out on the single-layer heat exchange plate, so that the smoothness of the plate is improved, and a good effect is obtained in later welding; secondly, processing a main vein channel and a secondary vein channel on the heat exchange plate by a chemical etching method, for example, the main vein channel is formed by a main channel 21, a first branch channel 22 and a second branch channel 23, the secondary vein channels are formed by a secondary channel 4 between adjacent first branch channels 22 and a micro secondary channel 5 between adjacent second branch channels 23, and the main vein channel and the secondary vein channels with semicircular sections are processed on both sides of the heat exchange plate by chemical etching; thirdly, after the main vein channel and the secondary vein channel are processed, a laser etching method is adopted to process a reticular flow channel 3 existing between the main vein channel and the secondary vein channel on the board; finally, after finishing the processing of the fluid channel, the channels of the two layers of heat exchange plates which are contacted up and down are completely matched, the two layers of plate sheets are aligned and diffusion welded, finally the fluid channel is combined into a circular channel with the minimum flow resistance, the cold side channel and the hot side channel are alternately arranged, and the heat exchanger is wholly in countercurrent heat exchange.
The heat exchange plates adopt bilateral etching channels except for the top layer and the bottom layer, the channel processing mode and the structure of the heat exchange plates between the top layer and the bottom layer are completely the same, batch mode processing can be adopted, and the processing difficulty and the cost can be effectively reduced.
Referring to fig. 5, an embodiment of the present invention further provides a heat exchanger, where the heat exchanger includes a plurality of heat exchange plates as described above, and the plurality of heat exchange plates are stacked, a flow collecting groove 1 and a groove-shaped flow channel are arranged on a surface of one of the heat exchange plates on which another heat exchange plate is arranged, and the flow collecting groove 1 and the groove-shaped flow channel of adjacent heat exchange plates are spliced to form a fluid channel.
The heat exchange plates are combined through a pressure diffusion welding technology to form a main body structure of the heat exchanger, wherein the back fluid channel of the first heat exchange plate and the back fluid channel of the second heat exchange plate are spliced to form a fluid channel with a circular section, a low-temperature side fluid channel is assumed, the front flow channel of the second heat exchange plate and the front flow channel of the third heat exchange plate are spliced to form a heat exchange channel corresponding to the other side channel, namely a high-temperature side fluid channel. Referring to fig. 6 and 7, the front and rear sides of the heat exchanger body are respectively a high temperature side inlet cross section and a high temperature side outlet cross section, which are completely the same, the high temperature fluid enters the circular inlet channel through the inlet branch connecting box, and the left and right sides of the heat exchanger body have a low temperature fluid outlet and outlet, so that it can be seen that the high temperature side inlet is adjacent to the low temperature side outlet, and the high temperature side outlet is adjacent to the low temperature side inlet. The working process of the heat exchanger is as follows: supercritical fluid enters each layer of heat exchange plate of the heat exchanger from the inlet part connecting box, flows into the other side fluid which is separated from the heat exchange plates in each stage of vein channel for heat exchange, and finally flows out of the heat exchanger after passing through the outlet connecting box.
The present invention is not limited to the above-described embodiments, and it will be apparent to those skilled in the art that various modifications and improvements can be made without departing from the principle of the present invention, and such modifications and improvements are also considered to be within the scope of the present invention. Those not described in detail in this specification are within the skill of the art.
Claims (8)
1. A heat exchange panel, characterized in that: the heat exchange plate is used for heat exchange of supercritical fluid, be equipped with two collection groove (1) and flute profile runner on the first surface of heat exchange plate, two collection groove (1) are located respectively the heat exchange plate both ends, the flute profile runner includes:
the grading flow channel (2) is communicated from one flow collecting groove (1) to the other flow collecting groove (1), the grading flow channel (2) comprises two main flow channels (21) respectively communicated with the two flow collecting grooves (1), and the two main flow channels (21) are communicated through at least two first branch flow channels (22);
a reticulated flow channel (3) disposed between adjacent first branch flow channels (22) and in fluid communication with the first branch flow channels (22); at the same time, the user can select the desired position,
the cross-sectional area of the reticular flow channel (3) is smaller than that of the first branch flow channel (22), and the grading flow channel (2) and the reticular flow channel (3) form a vein-shaped fluid distribution structure;
the cross sections of the grading flow channel (2) and the reticular flow channel (3) are semicircular, and central lines formed by connecting semicircular centers of the main flow channel (21), the first branch flow channel (22) and the reticular flow channel (3) are all positioned on the same plane;
the sum of the diameters cube of at least two first branch flow channels (22) is equal to the cube of the diameter of the main flow channel (21);
the diameter D of the reticular flow passage (3)wComprises the following steps: dw＝aDzWherein D iszThe diameter of the first branch flow passage (22) is 1/3-1/10.
2. A heat exchanger plate as claimed in claim 1, wherein: at least one secondary flow channel (4) is further arranged between the adjacent first branch flow channels (22), the secondary flow channel (4) is communicated with the mesh-shaped flow channel (3) between the adjacent first branch flow channels (22) in a fluid mode, and the cross section area of the secondary flow channel (4) is smaller than that of the first branch flow channel (22) and larger than that of the mesh-shaped flow channel (3).
3. A heat exchanger plate as claimed in claim 2, wherein: the cross sections of the grading flow channel (2), the reticular flow channel (3) and the secondary flow channel (4) are all semicircular.
4. A heat exchange plate according to claim 1, characterized in that the end of the main flow channel (21) far from the header tank (1) and at least two of the first branch flow channels (22) form a branched structure, and the included angle between the first branch flow channels (22) and the main flow channel (21) is 0- α -90.
5. A heat exchange plate according to claim 1, characterized in that at least two second branch flow passages (23) are further arranged in the middle of the first branch flow passage (22), the first branch flow passage (22) and the at least two second branch flow passages (23) form a branched structure, and the included angle between the second branch flow passage (23) and the first branch flow passage (22) is 0- α -90.
6. A heat exchanger plate according to any one of claims 1 to 5, wherein: the second surface of the heat exchange plate (10) is provided with two collecting grooves (1) and a groove-shaped flow passage, the collecting grooves (1) on the first surface are provided with first outlets (101), the collecting grooves (1) on the second surface are provided with second outlets (102), and the positions of the first outlets (101) and the positions of the second outlets (102) are different.
7. A method of processing a heat exchanger plate according to any of claims 1-6, characterised in that the method of processing comprises:
s1, polishing treatment of machining is carried out on the heat exchange plate so as to improve the smoothness of the heat exchange plate;
s2, processing a grading flow channel (2) on the heat exchange plate by a chemical etching method;
and S3, processing the reticular flow channel (3) by adopting a laser etching method.
8. A heat exchanger, characterized by: the heat exchanger comprises a plurality of heat exchange plates according to any one of claims 1 to 6, wherein the plurality of heat exchange plates are stacked, the flow collecting groove (1) and the groove-shaped flow channel are arranged on the surface of one heat exchange plate, which is provided with another heat exchange plate, and the flow collecting groove (1) and the groove-shaped flow channel of the adjacent heat exchange plate are spliced to form a fluid channel.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710498151.8A CN107255425B (en) | 2017-06-27 | 2017-06-27 | Heat exchange plate, machining method and heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710498151.8A CN107255425B (en) | 2017-06-27 | 2017-06-27 | Heat exchange plate, machining method and heat exchanger |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107255425A CN107255425A (en) | 2017-10-17 |
| CN107255425B true CN107255425B (en) | 2020-05-05 |
Family
ID=60023359
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710498151.8A Active CN107255425B (en) | 2017-06-27 | 2017-06-27 | Heat exchange plate, machining method and heat exchanger |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN107255425B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2022182877A1 (en) * | 2021-02-26 | 2022-09-01 | Teradyne, Inc. | Thermal plate having a fluid channel |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108180779B (en) * | 2017-12-29 | 2019-11-26 | 中国科学院工程热物理研究所 | Structure at a kind of printed circuit board heat exchanger entrance shunting |
| CN108339504B (en) * | 2018-03-12 | 2020-03-31 | 宋梓钰 | Microstructure reactor |
| CN109443056B (en) * | 2018-09-14 | 2020-08-11 | 中国科学院工程热物理研究所 | Double-sided staggered printed circuit board type heat exchange plate and heat exchanger |
| BE1026909B1 (en) * | 2018-12-21 | 2020-07-22 | Safran Aero Boosters Sa | FUEL OIL HEAT EXCHANGER |
| CN111189339B (en) * | 2020-01-22 | 2023-05-05 | 航天海鹰(哈尔滨)钛业有限公司 | Spliced microchannel heat exchanger |
| WO2023115230A1 (en) * | 2021-12-22 | 2023-06-29 | Universidad Técnica Federico Santa María | Plate heat exchanger based on the hilbert curve |
| CN115060108B (en) * | 2022-06-23 | 2024-10-18 | 西安热工研究院有限公司 | Bionic vein runner structure heat exchange plate and heat exchanger with same |
| CN115325717B (en) * | 2022-10-14 | 2023-01-31 | 中国核动力研究设计院 | Heat exchange device and Brayton cycle system |
Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1128506A (en) * | 1993-07-05 | 1996-08-07 | 帕金诺克斯公司 | Process and apparatus for controlling reaction temperatures |
| US6688381B2 (en) * | 2000-06-05 | 2004-02-10 | The State Of Oregon Acting By And Through The State Board Of Higher Education On Behalf Of Oregon State University | Multiscale transport apparatus and methods |
| CN1892163A (en) * | 2005-06-29 | 2007-01-10 | 株式会社聚源 | Heat exchange unit |
| CN101309573A (en) * | 2007-05-18 | 2008-11-19 | 富准精密工业(深圳)有限公司 | Even heating board and heat radiating device |
| CN201688739U (en) * | 2010-05-31 | 2010-12-29 | 甘肃蓝科石化高新装备股份有限公司 | Novel corrugated plate sheet for a welded plate type heat exchanger |
| CN102003899A (en) * | 2010-12-01 | 2011-04-06 | 杭州沈氏换热器有限公司 | Microchannel heat exchanger |
| CN102645117A (en) * | 2012-05-02 | 2012-08-22 | 西安交通大学 | Microchannel cooler |
| CN102812321A (en) * | 2010-04-09 | 2012-12-05 | 英格索尔-兰德公司 | Formed microchannel heat exchanger |
| CN102997026A (en) * | 2012-11-08 | 2013-03-27 | 西安智拓精密焊接科技有限公司 | Automobile oil cooler |
| CN203083407U (en) * | 2012-11-06 | 2013-07-24 | 董永梅 | Novel heat exchanger with double-side micro-channel heat exchange plates |
| CN103542749A (en) * | 2013-10-15 | 2014-01-29 | 华南理工大学 | Simulated liquid absorbing core for heat uniformizing plate |
| CN103954162A (en) * | 2014-05-16 | 2014-07-30 | 中国科学院工程热物理研究所 | Low resistance hydraulic cavitation structure with microchannel heat exchange enhancing function |
-
2017
- 2017-06-27 CN CN201710498151.8A patent/CN107255425B/en active Active
Patent Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1128506A (en) * | 1993-07-05 | 1996-08-07 | 帕金诺克斯公司 | Process and apparatus for controlling reaction temperatures |
| US6688381B2 (en) * | 2000-06-05 | 2004-02-10 | The State Of Oregon Acting By And Through The State Board Of Higher Education On Behalf Of Oregon State University | Multiscale transport apparatus and methods |
| CN1892163A (en) * | 2005-06-29 | 2007-01-10 | 株式会社聚源 | Heat exchange unit |
| CN101309573A (en) * | 2007-05-18 | 2008-11-19 | 富准精密工业(深圳)有限公司 | Even heating board and heat radiating device |
| CN102812321A (en) * | 2010-04-09 | 2012-12-05 | 英格索尔-兰德公司 | Formed microchannel heat exchanger |
| CN201688739U (en) * | 2010-05-31 | 2010-12-29 | 甘肃蓝科石化高新装备股份有限公司 | Novel corrugated plate sheet for a welded plate type heat exchanger |
| CN102003899A (en) * | 2010-12-01 | 2011-04-06 | 杭州沈氏换热器有限公司 | Microchannel heat exchanger |
| CN102645117A (en) * | 2012-05-02 | 2012-08-22 | 西安交通大学 | Microchannel cooler |
| CN203083407U (en) * | 2012-11-06 | 2013-07-24 | 董永梅 | Novel heat exchanger with double-side micro-channel heat exchange plates |
| CN102997026A (en) * | 2012-11-08 | 2013-03-27 | 西安智拓精密焊接科技有限公司 | Automobile oil cooler |
| CN103542749A (en) * | 2013-10-15 | 2014-01-29 | 华南理工大学 | Simulated liquid absorbing core for heat uniformizing plate |
| CN103954162A (en) * | 2014-05-16 | 2014-07-30 | 中国科学院工程热物理研究所 | Low resistance hydraulic cavitation structure with microchannel heat exchange enhancing function |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2022182877A1 (en) * | 2021-02-26 | 2022-09-01 | Teradyne, Inc. | Thermal plate having a fluid channel |
Also Published As
| Publication number | Publication date |
|---|---|
| CN107255425A (en) | 2017-10-17 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN107255425B (en) | Heat exchange plate, machining method and heat exchanger | |
| CN102881957B (en) | battery cooler | |
| CN112097552A (en) | Combined compact heat exchanger core | |
| CN109163586B (en) | Spiral runner printed circuit board heat exchanger | |
| CN105371684B (en) | A kind of heat exchanger plate chip architecture | |
| CN103363829A (en) | Heat pipe | |
| CN105452794A (en) | Heat exchanger, and heat pump device | |
| CN101922870B (en) | Dividing wall type heat exchanger | |
| CN201059904Y (en) | Asymmetric slit finned tube heat exchanger | |
| CN105157455A (en) | Flow-area-variable backflow plate-fin heat exchanger and control method thereof | |
| CN203758089U (en) | Micro-channel heat exchanger and air conditioner with micro-channel heat exchanger | |
| CN105387741B (en) | A kind of heat exchanger plate group of Novel asymmetric channel design | |
| CN112880444A (en) | Printed circuit board heat exchanger and core for heat exchange of variable-property fluid | |
| CN109141085B (en) | A kind of optimum design method of heat pipe | |
| JP2017129335A (en) | Heat exchanger and heat exchange method | |
| CN204963623U (en) | Variable flow area's adverse current finned plate heat exchanger | |
| CN105333757A (en) | Heat exchanger of variable-volume channel structure | |
| CN108548326A (en) | Water heater water tank and air can water heater | |
| CN209857688U (en) | Novel little logical board, and possess radiator and air conditioner end equipment of this little logical board | |
| CN114623720B (en) | Printed circuit board heat exchange plate structure, heat exchanger and heat exchange method | |
| CN205300358U (en) | Heat exchanger sheet structure | |
| CN105157253B (en) | Solar phase-change heat storage system | |
| CN112066601A (en) | Heat exchanger and air conditioning system | |
| CN114111115A (en) | Heat exchanger and air conditioner | |
| CN103791741B (en) | A kind of phase transformation plate type heat exchanger |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |