CN115790247A - Flow equalizing part and heat exchange device - Google Patents
Flow equalizing part and heat exchange device Download PDFInfo
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- CN115790247A CN115790247A CN202310015757.7A CN202310015757A CN115790247A CN 115790247 A CN115790247 A CN 115790247A CN 202310015757 A CN202310015757 A CN 202310015757A CN 115790247 A CN115790247 A CN 115790247A
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Abstract
The application provides a part and heat transfer device flow equalize. The flow equalizing part comprises a bottom wall and a side wall, the bottom wall comprises a first port penetrating through the bottom wall along the thickness direction of the bottom wall, the side wall is connected to the peripheral side of the bottom wall and surrounds the bottom wall to form a chamber for accommodating media and a second port communicated with the chamber, and the sectional area S2 of the second port is larger than the sectional area S1 of the first port, so that the media entering from the first port diffuse to the periphery when flowing out of the second port; the surface of the side wall facing the cavity comprises a first wall surface and a second wall surface which are oppositely arranged along the first direction, at least part of the wall surfaces are cambered surfaces protruding towards the cavity direction, the sectional area of at least part of the cavity in the second direction is gradually increased, the cavity volume generated after the medium enters the horn-shaped cavity is reduced, the vortex strength in the flow equalizing component is weakened, the flow concentration phenomenon caused by the vortex phenomenon in the flow equalizing component is improved, and the flow equalizing effect of the flow equalizing component is improved.
Description
Technical Field
The application relates to the technical field of heat exchange, in particular to a flow equalizing part and a heat exchange device.
Background
A heat exchanger is a device that transfers the heat of a certain fluid to another fluid in a certain heat transfer manner. The application of heat exchangers in industrial production is very common and extends to various industrial departments such as power, metallurgy, chemical industry, petroleum, food, medicine, aerospace and the like. A printed circuit board heat exchanger (PCHE) which can withstand high temperature and high pressure, has a compact volume, a high heat exchange efficiency and an acceptable cost is a promising development direction.
The printed circuit board type heat exchanger is a compact type heat exchanger, a plurality of micro channels are arranged in the printed circuit board type heat exchanger, but the distribution of media in the heat exchanger is uneven, so that the development of the heat exchange performance of the heat exchanger is restricted.
Disclosure of Invention
In view of the above-mentioned problem, the application provides a part and heat transfer device flow equalize in order to improve the uneven problem of medium distribution in heat transfer device, improves the effect of flow equalizing of part.
In a first aspect, the present application provides a flow equalization member, including a bottom wall and a side wall, wherein the bottom wall includes a first port penetrating through the bottom wall along a thickness direction of the bottom wall; the side wall is connected to the periphery of the bottom wall and encloses with the bottom wall to form a chamber used for containing a medium, and a second port communicated with the chamber, the surface of the side wall facing the chamber comprises a first wall surface and a second wall surface which are oppositely arranged along a first direction, at least part of the first wall surface is an arc surface protruding towards the chamber direction, and/or at least part of the second wall surface is an arc surface protruding towards the chamber direction, wherein the second port and the bottom wall are oppositely arranged along a second direction, the sectional area S2 of the second port is larger than the sectional area S1 of the first port, the sectional area of at least part of the chamber is gradually increased in the second direction, and the second direction is intersected with the first direction.
In some embodiments, the sidewall further comprises a third wall and a fourth wall oppositely disposed along the third direction, the first wall and the second wall are the same in shape and size, and the third wall and the fourth wall are the same in shape and area.
In some embodiments, the extension L1 of the bottom wall in the first direction is smaller than the extension L2 of the bottom wall in the third direction.
In some embodiments, the third wall and the fourth wall are planar.
In some embodiments, the third wall surface and the fourth wall surface are cambered surfaces that are convex toward the chamber direction.
In some embodiments, the cross-sectional area of the chamber increases in the second direction.
In some embodiments, the area S1 of the first port is equal to the area of the bottom wall, and the side walls are both cambered surfaces protruding towards the chamber direction.
In some embodiments, the sidewall has at least one baffle disposed thereon that is convex toward the chamber.
In some embodiments, the height of the interfering fluid does not exceed 5mm.
In some embodiments, the plurality of interfering fluids extend linearly from the first port to the second port on the sidewall and/or the plurality of interfering fluids extend helically from the first port to the second port on the sidewall.
In some embodiments, at least one baffle is arranged in the chamber, the baffle covers at least part of the chamber, and at least one opening for circulating the medium is arranged on the baffle.
In some embodiments, the area of the opening increases gradually from the center of the spoiler to the edge of the spoiler.
In some embodiments, n spoiler areas (n is larger than or equal to 2) are sequentially arranged from the center of the spoiler to the edge of the spoiler, and the area of the opening in each spoiler area is the same.
In some embodiments, an area of the spoiler at the central position of the spoiler is not less than half of the area of the spoiler.
In some embodiments, in the second direction, the at least one spoiler is no less than one third of the length of the chamber from the second port.
In a second aspect, the present application provides a heat exchange device comprising any one of the flow equalization members of the first aspect described above.
In some embodiments, the heat exchange device comprises a plurality of heat exchange flow channels, the heat exchange flow channels are communicated with the flow equalizing part, and the non-uniformity S:
wherein Q i Is a measured value of the flow at the ith heat exchange flow channel, Q ave The flow average value of the heat exchange flow channels is shown, and N is the number of the heat exchange flow channels.
In some embodiments, the heat exchange efficiency coefficient η of the heat exchange device is:
wherein S is the unevenness of the heat exchange device.
Compared with the prior art, the method has the following beneficial effects:
the flow equalizing component comprises a bottom wall and a side wall, wherein the bottom wall comprises a first port which penetrates through the bottom wall along the thickness direction of the bottom wall, the side wall is connected to the peripheral side of the bottom wall and surrounds the bottom wall to form a chamber for accommodating media and a second port which is communicated with the chamber, and the sectional area S2 of the second port is larger than the sectional area S1 of the first port, so that the media entering from the first port diffuse to the periphery when flowing out from the second port, and the flow equalizing effect of the flow equalizing component is improved;
the surface of the side wall facing the cavity comprises a first wall surface and a second wall surface which are oppositely arranged along a first direction, at least part of the first wall surface is a cambered surface protruding towards the cavity direction, and/or at least part of the second wall surface is a cambered surface protruding towards the cavity direction, the sectional area of at least part of the cavity is gradually increased in a second direction, the cavity volume generated after a medium enters the horn-shaped cavity is reduced, the centrifugal force and the pressure gradient strength after the medium enters the flow equalizing part are reduced, the eddy strength in the flow equalizing part is weakened, the flow concentration phenomenon caused by the eddy phenomenon in the flow equalizing part is improved, and the flow equalizing effect of the flow equalizing part is improved.
Drawings
In order to more clearly illustrate the technical solutions in the embodiments of the present application, the drawings needed to be used in the embodiments or the prior art descriptions will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present application, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without inventive exercise.
FIG. 1 is a schematic structural diagram of a conventional current equalizing component;
FIG. 2 is a schematic structural diagram of a current equalizing component in an embodiment of the present application;
FIG. 3 is a side view of a flow equalization member of an embodiment of the present application;
FIG. 4 is a top view of a flow equalization member in an embodiment of the present application;
FIG. 5 is a schematic diagram of a flow equalization component in another embodiment of the present application;
FIG. 6 is a schematic diagram of a flow equalization component in another embodiment of the present application;
FIG. 7 is a schematic diagram of a flow equalization component in another embodiment of the present application;
FIG. 8 is a side view of a flow equalization member in another embodiment of the present application;
FIG. 9 is a top view of a flow equalization member in another embodiment of the present application.
The reference numbers in the detailed description are as follows:
1. a flow equalizing component; 11. a bottom wall; 111. a first port; 12. a side wall; 121. a first wall surface; 122. a second wall surface; 123. a third wall surface; 124. a fourth wall surface; 125. a second port; 13. a chamber; 14. a fluid-disturbing body; 15. a spoiler; 151. opening a hole;
2. a medium line;
1', a conventional flow equalization component; 13', conventional chamber.
Detailed Description
Embodiments of the present invention will be described in detail below with reference to the accompanying drawings. The following examples are only used to illustrate the technical solutions of the present application more clearly, and therefore are only used as examples, and the protection scope of the present application is not limited thereby.
It should be noted that technical terms or scientific terms used in the embodiments of the present application should be understood as having a common meaning as understood by those skilled in the art to which the embodiments of the present application belong, unless otherwise specified.
The exchanger is an important part for energy recycling in modern industry. With the higher requirements of the fields of petrochemical engineering, ocean engineering, nuclear energy, photothermal and the like on the efficiency, high temperature resistance and high pressure resistance of the heat exchanger, the micro-channel compact heat exchanger (PCHE) combining a chemical etching micro-channel forming technology and a diffusion welding technology gradually becomes hot
The PCHE utilizes chemical etching to etch a micro flow passage with the diameter of 0.5mm to 2.0mm on the heat exchange plate, so that the density of the heat exchange surface of the PCHE can reach 2500m 2 /m 3 However, the uneven distribution of the working medium flow caused by the dense microchannel arrangement becomes a great important factor for restricting the efficiency of the heat exchanger.
Referring to fig. 1, fig. 1 is a schematic diagram of a conventional current sharing component.
As shown in fig. 1, in order to make the working medium uniformly enter the heat exchanger in the prior art, a conventional flow equalizing part 1' is usually added at the inlet end of the medium pipeline 2 and the heat exchanger, the conventional flow equalizing part 1' has a semi-cylindrical conventional chamber 13', and the medium pipeline 2 is connected to the curved surface of the semi-cylindrical chamber, so as to improve the flow equalizing effect of the medium.
The inventor of the present application has noticed that the conventional flow equalizing part 1' does not achieve the theoretical flow equalizing effect. The inventor finds that in the conventional flow equalizing part, after the medium enters the semi-cylindrical cavity, the convex semi-cylindrical curved surface can form a large cavity, when the medium flows to the cavity, a vortex can be generated at the position due to the action of pressure difference, and the vortex can cause flow to be concentrated, so that the flow equalizing effect of the flow equalizing part is reduced.
Based on the above problems discovered by the inventors, through intensive research, in order to improve the current sharing performance of the current sharing component, the inventors improve the current sharing component, and the technical solution described in the embodiment of the present application is applicable to the current sharing component and various devices using the current sharing component.
Referring to fig. 2 to 4, fig. 2 is a schematic structural diagram of a current equalizing component 1 in the embodiment of the present application, fig. 3 is a side view of the current equalizing component 1 in the embodiment of the present application, and fig. 4 is a top view of the current equalizing component 1 in the embodiment of the present application.
In some alternative embodiments, as shown in fig. 2 to 4, a flow equalizing member includes a bottom wall 11 and a side wall 12, where the bottom wall 11 includes a first port 111 penetrating through the bottom wall in a thickness direction; the side wall 12 is connected to the peripheral side of the bottom wall 11 and encloses with the bottom wall 11 to form a chamber 13 for accommodating a medium, and a second port 125 communicated with the chamber 13, the surface of the side wall 12 facing the chamber 13 includes a first wall surface 121 and a second wall surface 122 oppositely arranged along a first direction X, at least a part of the first wall surface 121 is an arc surface protruding towards the chamber 13, and/or at least a part of the second wall surface 122 is an arc surface protruding towards the chamber 13, wherein the second port 125 and the bottom wall 11 are oppositely arranged along a second direction Y, the sectional area S2 of the second port 125 is larger than the sectional area S1 of the first port 111, the sectional area of at least a part of the chamber 13 in the second direction Y is gradually increased, and the second direction Y intersects with the first direction X.
Optionally, the first direction is an X direction in fig. 2, and the second direction intersecting the first direction X is a Y direction.
Optionally, the material of the current equalizing part 1 may be any one of stainless steel, copper alloy, titanium alloy or composite material.
Optionally, the central angle of the arc surface protruding towards the chamber 13 is not less than 90 °, so as to avoid that the arc surface protrudes too much to block the flow of the medium in the chamber 13.
Optionally, the bottom wall 11 and the side walls 12 are integrally formed, which ensures that the flow equalizing member 1 has sufficient strength.
Optionally, the flow equalizing part 1 is machined, forged and welded.
In the flow equalizing component 1 provided in the embodiment of the present application, the flow equalizing component 1 includes a bottom wall 11 and a side wall 12, the bottom wall 11 includes a first port 111 penetrating through the bottom wall in the thickness direction, the side wall 12 is connected to the peripheral side of the bottom wall 11 and encloses with the bottom wall 11 to form a chamber 13 for accommodating a medium, and a second port 125 communicating with the chamber 13, and a sectional area S2 of the second port 125 is larger than a sectional area S1 of the first port 111, so that the medium entering from the first port 111 diffuses around when flowing out from the second port 125, thereby improving the flow equalizing effect of the flow equalizing component 1; the surface of the sidewall 12 facing the chamber 13 includes a first wall surface 121 and a second wall surface 122 which are oppositely arranged along the first direction X, at least a part of the first wall surface 121 is a cambered surface protruding towards the direction of the chamber 13, and/or at least a part of the second wall surface 122 is a cambered surface protruding towards the direction of the chamber 13, the sectional area of at least a part of the chamber 13 is gradually increased in the second direction Y, the cavity volume generated after the medium enters the trumpet-shaped chamber 13 is reduced, the centrifugal force and pressure gradient strength after the medium enters the flow equalizing part 1 are reduced, the eddy strength in the flow equalizing part 1 is weakened, the flow concentration phenomenon caused by the eddy phenomenon in the flow equalizing part 1 is improved, and the flow equalizing effect of the flow equalizing part 1 is improved.
In some alternative embodiments, as shown in fig. 2 and 3, the sidewall further includes a third wall 123 and a fourth wall 124 opposite to each other along the third direction Z, the first wall 121 and the second wall 122 have the same shape and size, and the third wall 123 and the fourth wall 124 have the same shape and area.
Optionally, the third direction is a Z direction in fig. 2.
Alternatively, the first wall 121, the second wall 122, the third wall 123 and the fourth wall 124 are the same in shape and size.
In these alternative embodiments, the first wall 121 and the second wall 122 have the same shape and size, and the third wall 123 and the fourth wall 124 have the same shape and size, so that the manufacturing process is simplified and the industrial applicability is improved.
In some alternative embodiments, as shown in fig. 2 and 3, an extension length L1 of the bottom wall 11 in the first direction is smaller than an extension length L2 of the bottom wall 11 in the third direction Z.
In these alternative embodiments, the strength of the vortex generated in the third direction Z is smaller than that in the first direction X, and the extension length L1 of the bottom wall 11 in the first direction X is smaller than the extension length L2 of the bottom wall 11 in the third direction Z, so that the cross-sectional area of the chamber 13 is increased, the medium can be distributed to a larger area, the size of the cavity in the chamber 13 in the first direction X is prevented from being increased, and the strength of the vortex in the chamber 13 is reduced.
In some alternative embodiments, as shown in fig. 2 and 3, the third wall 123 and the fourth wall 124 are planar.
In these alternative embodiments, the third wall surface 123 and the fourth wall surface 124 which are arranged in a plane reduce the difficulty in processing the flow equalizing part 1, and the third wall surface 123 and the fourth wall surface 124 which are arranged in a plane also play a role in supporting the first wall surface 121 and the second wall surface 122, thereby enhancing the stability of the flow equalizing part 1.
Referring to fig. 5, fig. 5 is a schematic structural diagram of a current equalizing component 1 according to another embodiment of the present application.
In some alternative embodiments, as shown in fig. 5, the third wall 123 and the fourth wall 124 are curved surfaces protruding toward the chamber 13.
In these alternative embodiments, the third wall 123 and the fourth wall 124 are curved surfaces that are convex toward the chamber 13, reducing the cavity size and attenuating the intensity of the vortex in the chamber 13.
In some alternative embodiments, as shown in fig. 5, the cross-sectional area of the chamber 13 is gradually increased in the second direction Y.
In these optional embodiments, the sectional area of the chamber 13 is gradually increased, so that a phenomenon that a medium generates a larger vortex due to a pressure difference and a centrifugal force which are suddenly increased after entering the chamber 13 is improved, a flow beam concentration phenomenon caused by the vortex phenomenon is reduced, and a flow equalizing effect is improved.
In some alternative embodiments, as shown in fig. 4 and 5, the area S1 of the first port 111 is equal to the area of the bottom wall (not shown), and the side walls 12 are all arc surfaces protruding toward the chamber 13.
The area S1 of the first port 111 is equal to the area of the bottom wall, that is, the bottom wall of the flow equalizing member 1 is set to be the first port 111. Intuitively, in the solution of this embodiment, the side wall 12 is directly connected to the medium line 2, without providing a bottom wall.
Optionally, the flow equalizing part 1 is horn-shaped, and the first port 111 and the second port 125 are both circular.
In these alternative embodiments, the side walls 12 are all curved surfaces protruding towards the chamber 13, and the cross-sectional area of the chamber 13 gradually increases, so that the size of the cavity generated after the medium enters the chamber 13 is reduced, and the strength of the vortex in the first direction X and the third direction Z is weakened.
Referring to fig. 6, fig. 6 is a schematic structural diagram of a current equalizing component according to another embodiment of the present application.
In some alternative embodiments, as shown in fig. 6, at least one baffle 14 protruding toward the cavity 13 is disposed on the sidewall 12.
Alternatively, the turbulence bodies 14 can be formed integrally with the flow equalizing member 1.
In these alternative embodiments, the sidewall 12 is provided with at least one spoiler 14 protruding toward the chamber 13, which increases the friction of the sidewall 12, and the spoiler 14 has a spoiler effect, which can weaken the strength of the vortex.
In some alternative embodiments, as shown in fig. 6, the height of the turbulent flow 14 is not more than 5mm.
In these alternative embodiments, the height of the interfering fluid 14 does not exceed 5mm, preventing the interfering fluid 14 from excessively impeding the flow of the medium in the chamber 13.
In some alternative embodiments, as shown in fig. 6, the plurality of baffle bodies 14 extend linearly from the first port 111 to the second port 125 on the sidewall 12, and/or the plurality of baffle bodies 14 extend helically from the first port 111 to the second port 125 on the sidewall 12.
Optionally, a plurality of baffle members 14 are attached end-to-end on the side wall 12 to form a rib.
Optionally, a plurality of turbulators 14 are arranged in a ring on the sidewall 12.
In these alternative embodiments, the plurality of turbulent fluid 14 extends linearly from the first port 111 to the second port 125, and/or, on the sidewall 12, the plurality of turbulent fluid 14 extends spirally from the first port 111 to the second port 125, so that the friction force of the inner wall of the chamber 13 is enhanced, the viscous force of the medium in the chamber 13 is increased, and the strength of the vortex generated when the medium enters the chamber 13 is reduced.
Referring to fig. 7 to 9, fig. 7 is a schematic structural diagram of a current equalizing component 1 in another embodiment of the present application, fig. 8 is a side view of the current equalizing component 1 in another embodiment of the present application, and fig. 9 is a top view of the current equalizing component 1 in another embodiment of the present application.
In some alternative embodiments, as shown in fig. 7 to 9, at least one spoiler 15 is disposed in the chamber 13, the spoiler 15 covers at least a portion of the chamber 13, and at least one opening 151 is disposed in the spoiler 15 for flowing a medium therethrough.
Optionally, the spoiler 15 may be made of any one of stainless steel, copper alloy, titanium alloy or composite material; optionally, the spoiler 15 is made of the same material as the flow equalizing member 1.
Optionally, a spoiler 15 is positioned in a cross-section of the chamber in the first direction X to obtain a maximum effective spoiler area.
Optionally, all edges of the spoiler 15 are connected to the chamber 13 to obtain a maximum spoiler area.
Optionally, the openings 151 in the spoiler 15 are identical in shape; optionally, the opening 151 of the spoiler 15 is a circular hole.
Optionally, only one spoiler 15 is arranged in the chamber 13 to avoid an excessive pressure drop of the medium.
Alternatively, the chamber 13 may include a plurality of spoilers 15 arranged alternately in the chamber 13 along the first direction X, and the area of the spoilers 15 is smaller than the cross-sectional area of the chamber 13.
In these alternative embodiments, at least one spoiler 15 is disposed in the chamber 13, and the spoiler 15 plays a role of spoiler, so as to reduce the strength of vortex and improve the flow equalizing effect of the flow equalizing component 1; the spoiler 15 is provided with at least one opening 151 for medium circulation, so that the problem that the heat exchange effect of the medium is influenced due to overlarge medium pressure drop caused by the arrangement of the spoiler 15 is solved.
In some alternative embodiments, as shown in fig. 7 to 9, the area of the opening 151 gradually increases from the center of the spoiler 15 to the edge of the spoiler 15.
Optionally, the diameter of the opening 151 is between 5mm and 50 mm.
Alternatively, the diameter of the opening 151 increases in an equal ratio series or an equal difference series from the center of the spoiler 15 to the edge of the spoiler 15.
In these alternative embodiments, since the medium is more concentrated in the central position of the chamber 13, the flow area of the edge region of the chamber 13 is increased by increasing the area of the opening 151 in the edge region of the spoiler 15, the medium flow rate in the edge region of the chamber 13 is increased, and the flow equalizing effect of the flow equalizing member 1 is improved.
In some alternative embodiments, as shown in fig. 7 to 9, n spoiler areas (n ≧ 2) are sequentially disposed on the spoiler 15 from the center of the spoiler 15 to the edge of the spoiler 15, and the area of the opening 151 is the same in each spoiler area.
Optionally, the shape of each turbulent flow region is the same; optionally, the shape of the spoiler 15 is the same as the shape of the spoiler.
Optionally, the shape and area of the opening 151 are the same in each turbulent flow region.
In these optional embodiments, n spoiler regions are arranged on the spoiler 15 in the direction from the center of the spoiler 15 to the edge of the spoiler 15, and the areas of the openings 151 in each spoiler region are the same, thereby reducing the operation difficulty of the opening 151 process and improving the production efficiency.
In some alternative embodiments, as shown in fig. 7 to 9, the area of the spoiler 15 at the central position thereof is not less than half of the area of the spoiler 15.
Optionally, three spoiler regions are arranged on the spoiler 15, and the area ratio of the three spoiler regions is 2 in the direction from the center of the spoiler 15 to the edge of the spoiler 15: 1:1.
in these alternative embodiments, since the medium is more concentrated in the central position of the chamber 13, the area of the turbulent flow region in the central position of the turbulent flow plate 15 is not less than half of the area of the turbulent flow plate 15, so as to achieve a greater flow equalizing effect.
In some alternative embodiments, as shown in fig. 7 to 9, the distance L3 from the spoiler 15 to the second port 125 in the second direction Y is not less than one third of the length L4 of the chamber 13.
In these alternative embodiments, the spoiler 15 is prevented from being too close to the second port 125, which results in too much obstruction of the medium by the spoiler 15, and thus too much pressure drop of the medium, which affects the heat exchange effect of the heat exchange device.
The embodiment of the application also provides a heat exchange device, which comprises the flow equalizing part provided by any one of the embodiments.
The heat exchange device provided by the embodiment of the application has the same technical effect due to the adoption of the flow equalizing part provided by any one of the embodiments, and the details are not repeated herein.
In some embodiments, the heat exchange device comprises a plurality of heat exchange flow channels, the heat exchange flow channels are communicated with the flow equalizing part, and the non-uniformity S:
wherein Q i Is a measured value of the flow at the ith heat exchange flow channel, Q ave The flow average value of the heat exchange flow channels is shown, and N is the number of the heat exchange flow channels.
In other embodiments, the heat exchange efficiency coefficient η of the heat exchange device is:
wherein S is the unevenness of the heat exchange device.
The embodiment of the application provides a parameter for representing the nonuniformity of flow distribution of a heat exchange device, namely nonuniformity S. The formula is as follows:
in the formula: q i For each heat exchange flow channel, m 3 /h；
Q ave Is the average value of the flow of each heat exchange flow passage, m 3 /h；
N is the number of heat exchange flow channels;
i is the channel number.
The smaller S is, the more uniform the flow of each heat exchange flow channel in the heat exchange device is, and the more excellent the flow distribution performance of the flow equalizing part is.
The average Reynolds number of the flow channel is:
in the formula: rho is the density of the medium, kg/m 3 ；
d is the hydraulic diameter of the heat exchange flow channel, m;
μ is the dielectric dynamic viscosity, kg/(m · s);
and u is the average speed of the medium in the heat exchange flow channel, and m/s.
In the formula, A i Is the inlet area of the ith heat exchange channel, m 2 ；
A o Is the total flow area of the heat exchange flow passage m 2 ；
u i Is the inlet flow velocity of the ith heat exchange flow channel in m/s.
On-way resistance in the flow passage of f
Through calculation and experiments, the relationship between the flow distribution unevenness S and the on-way resistance f in the heat exchange device is obtained as follows:
S 1 =1−0.005f，S 1 the unevenness of the heat exchange device when the flow equalizing part shown in the attached figure 1 is used;
S 2 =1−0.078f，S 2 the unevenness of the heat exchange device when the flow equalizing part shown in the attached figure 2 is used;
S 5 =1−0.092f，S 5 the non-uniformity of the heat exchange device when using the flow equalization part shown in figure 5;
S 6 =1−0.099f，S 6 the unevenness of the heat exchange device when the flow equalizing part shown in the attached figure 6 is used;
S 7 =1−0.112f，S 7 the non-uniformity of the heat exchange device when using the flow equalization means shown in figure 7.
In the heat exchange device, a cold side runner and a hot side runner are periodically overlapped and arranged, and a heat transfer chain of the heat exchange device consists of convective heat exchange of the cold side and the hot side and heat conduction of an intermediate wall. Dispersing the heat exchanger into a plurality of heat exchange units along the flow direction, wherein the heat exchange amounts of the hot side fluid, the cold side fluid and the intermediate wall in the heat exchange units are respectively as follows:
wherein Q is h Is the total heat exchange power of the hot-side fluid, h h Is the convective heat transfer coefficient of the hot side fluid, A h Heat exchange area for hot side fluid, T h,b Is the temperature of the main fluid in the hot side fluid, T h,w Temperature of wall surface in hot side fluid, Q c Total heat exchange power of cold side fluid, h c Is the convective heat transfer coefficient of the cold side fluid, A c Is the heat exchange area of the cold side fluid, T c,w Temperature of wall in cold-side fluid, T c,b Temperature of main fluid in cold-side fluid, Q w The total heat exchange power of the wall surface, lambda is the heat conductivity of the wall surface, A is the heat exchange area, and t is the thickness of the intermediate wall.
The heat transfer coefficient h of convection in the formula is related to the flow velocity of the working medium, and the unevenness in the heat exchange device is essentially caused by different flow velocities among the heat exchange flow channels, and the patent provides the unevenness of the heat exchange device corresponding to the flow equalizing part of the patent and the corresponding heat exchange efficiency coefficient.
Where η is a coefficient of heat exchange efficiency and is related to the unevenness. P t The theoretical heat exchange power of the heat exchange device.
In these embodiments, the heat exchanger is composed of a plurality of heat exchange channels, the uneven flow among the heat exchange channels can reduce the heat exchange efficiency and safety, the purpose of using the flow equalizing part is to make the heat exchanger have better flow distribution performance under corresponding working conditions, and the distribution performance can be represented by distribution unevenness S. The unevenness S provided by the invention can effectively represent the flow distribution performance of the flow equalizing part under a certain working condition, and is beneficial to model selection and calculation in engineering application.
Under rated working condition, each heat exchange device has corresponding designed heat exchange power P t The uneven flow distribution may cause the actual power P to be less than the design power P t . The patent provides the heat exchange efficiency coefficient eta of the heat exchange device using the flow equalizing part in the patent on the basis of sufficient experiment and calculation, and the heat exchange efficiency coefficient eta can be used as a key technical parameter when the heat exchange device is designed and optimized.
It should be understood by those skilled in the art that the above embodiments are illustrative and not restrictive. Different features which are present in different embodiments may be combined to advantage. Other variations to the disclosed embodiments can be understood and effected by those skilled in the art upon studying the drawings, the specification, and the claims. In the claims, the term "comprising" does not exclude other means or steps; the indefinite article "a" does not exclude a plurality; the terms "first" and "second" are used to denote a name and not to denote any particular order. Any reference signs in the claims shall not be construed as limiting the scope. The functions of the parts appearing in the claims may be implemented by one single hardware or software module. The mere fact that certain measures are recited in mutually different dependent claims does not indicate that a combination of these measures cannot be used to advantage.
Claims (16)
1. A flow equalization component for increasing distribution uniformity of a medium after entering a heat exchange device, the flow equalization component comprising:
a bottom wall including a first port provided therethrough in a thickness direction thereof;
the side wall is connected with the peripheral side of the bottom wall and surrounds the bottom wall to form a chamber used for containing a medium and a second port communicated with the chamber, the surface of the side wall facing the chamber comprises a first wall surface and a second wall surface which are oppositely arranged along a first direction, at least part of the first wall surface is a cambered surface protruding towards the direction of the chamber, and/or at least part of the second wall surface is a cambered surface protruding towards the direction of the chamber,
the second port and the bottom wall are oppositely arranged along a second direction, the sectional area S2 of the second port is larger than the sectional area S1 of the first port, the sectional area of at least part of the chamber is gradually increased in the second direction, the second direction is intersected with the first direction, and at least one fluid disturbing body protruding towards the chamber is arranged on the side wall.
2. The flow straightener element of claim 1, wherein the side walls further comprise a third wall and a fourth wall that are oppositely disposed in a third direction, the first wall and the second wall are the same in shape and size, and the third wall and the fourth wall are the same in shape and area.
3. The flow straightener element of claim 2, characterized in that the extension L1 of the bottom wall in the first direction is smaller than the extension L2 of the bottom wall in the third direction.
4. The flow equalization component of claim 2 wherein the third wall and the fourth wall are planar.
5. The flow straightener of claim 2, wherein the third wall and the fourth wall are arcs that are convex towards the chamber.
6. The flow equalization member of claim 1 wherein the chamber has a cross-sectional area that increases in the second direction.
7. The flow straightener of claim 6, wherein the area S1 of the first port is equal to the area of the bottom wall, and the side walls are both cambered surfaces protruding towards the chamber.
8. The flow straightener of claim 1, wherein a plurality of the turbulent flow bodies extend linearly from a first port to the second port on the side wall and/or spirally from a first port to the second port on the side wall.
9. The flow straightener of claim 1, wherein at least one baffle is arranged in the chamber, wherein the baffle covers at least a part of the chamber, and wherein at least one opening is arranged in the baffle for the medium to flow through.
10. The flow straightener of claim 9, wherein the openings increase in area from the center of the spoiler to the edge of the spoiler.
11. The flow straightener of claim 10, wherein n turbulence areas (n ≧ 2) are provided in sequence from the center of the spoiler to the edge of the spoiler, and the area of the opening is the same in each turbulence area.
12. The flow equalizing member of claim 11, wherein the area of the spoiler at the center of the spoiler is not less than half of the area of the spoiler.
13. The flow straightener of claim 9, wherein in the second direction the distance from the at least one baffle to the second port is not less than one third of the length of the chamber.
14. A heat exchange device comprising a flow equalization member as claimed in any one of claims 1 to 13.
15. The heat exchange device of claim 14, comprising a plurality of heat exchange flow channels in communication with the flow equalization member, wherein the non-uniformity S:
wherein Q i For the flow measurement at the ith heat exchange channel, Q ave And N is the flow average value of each heat exchange flow channel, and is the number of the heat exchange flow channels.
16. The heat exchange device of claim 15, wherein the heat exchange efficiency coefficient η:
wherein S is the unevenness of the heat exchange device.
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| CN202310015757.7A CN115790247B (en) | 2023-01-06 | 2023-01-06 | Flow equalizing component and heat exchange device |
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