CN113804029A - Side income formula head structure suitable for small passageway plate heat exchanger - Google Patents
Side income formula head structure suitable for small passageway plate heat exchanger Download PDFInfo
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- CN113804029A CN113804029A CN202111115247.4A CN202111115247A CN113804029A CN 113804029 A CN113804029 A CN 113804029A CN 202111115247 A CN202111115247 A CN 202111115247A CN 113804029 A CN113804029 A CN 113804029A
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- 239000012530 fluid Substances 0.000 claims abstract description 84
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 10
- 230000000903 blocking effect Effects 0.000 claims description 17
- 229910052751 metal Inorganic materials 0.000 claims description 6
- 239000002184 metal Substances 0.000 claims description 6
- RTAQQCXQSZGOHL-UHFFFAOYSA-N Titanium Chemical compound [Ti] RTAQQCXQSZGOHL-UHFFFAOYSA-N 0.000 claims description 3
- 230000005484 gravity Effects 0.000 claims description 3
- 239000011148 porous material Substances 0.000 claims description 3
- 238000012545 processing Methods 0.000 claims description 3
- 239000010936 titanium Substances 0.000 claims description 3
- 229910052719 titanium Inorganic materials 0.000 claims description 3
- 238000013461 design Methods 0.000 abstract description 3
- 238000009826 distribution Methods 0.000 description 10
- 238000009827 uniform distribution Methods 0.000 description 6
- 238000001816 cooling Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 230000007613 environmental effect Effects 0.000 description 2
- 230000000704 physical effect Effects 0.000 description 2
- 238000013519 translation Methods 0.000 description 2
- 230000003044 adaptive effect Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000005219 brazing Methods 0.000 description 1
- 238000003889 chemical engineering Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000004088 simulation Methods 0.000 description 1
- 238000005482 strain hardening Methods 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
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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
- F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
- F28D9/0037—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the conduits for the other heat-exchange medium also being formed by paired plates touching each other
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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
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/0246—Arrangements for connecting header boxes with flow lines
- F28F9/0251—Massive connectors, e.g. blocks; Plate-like connectors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2260/00—Heat exchangers or heat exchange elements having special size, e.g. microstructures
- F28F2260/02—Heat exchangers or heat exchange elements having special size, e.g. microstructures having microchannels
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- 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 utility model provides a side income formula head structure suitable for small passageway plate heat exchanger, belongs to the technical field of heat exchanger equipment head structural design. The invention aims to solve the problem of overlarge internal pressure loss of the direct-entry type end socket structure of the existing optimized heat exchanger. The invention relates to a side entry type end socket structure suitable for a micro-channel plate heat exchanger, which is characterized in that the overall structure of the end socket structure is divided into a water inlet section, a divergent section and a flow guide section; the cold fluid outlet of the water inlet section is connected with the cold fluid inlet of the divergent section, and the cold fluid outlet of the divergent section is connected with the cold fluid inlet of the guide section; a cold fluid outlet of the flow guide section is connected with a cold fluid inlet of the micro channel; the whole depth of the flow guide section is gradually reduced. The invention is mainly used for connecting the micro channels of the heat exchanger and uniformly distributing cold fluid into the micro channels.
Description
Technical Field
The invention belongs to the technical field of end enclosure structure design of heat exchanger equipment, and particularly relates to a side-entry end enclosure structure suitable for a micro-channel plate heat exchanger.
Background
The micro-channel plate heat exchanger is widely applied to the fields of energy power, chemical engineering, electric machinery, aerospace and the like, and has the characteristics of high heat transfer efficiency, compact structure, strong adaptability and the like. The micro-channel is machined on a metal plate, channel plates on a cold working medium side and a hot working medium side are arranged together in a staggered mode to form a multi-layer metal plate structure, the multi-layer metal plate structure is combined together in modes of brazing and the like to form a cross-flow plate type micro-channel plate heat exchanger, and cold fluid exchanges heat with hot fluid through the plates. In the operation process of the micro-channel plate heat exchanger, due to the influence of factors such as pressure distribution, flow channel states and the like, the flow distribution of working media among all the flow channels is unbalanced, the heat conduction of the longitudinal wall surface and the uneven distribution of internal temperature are strengthened, and further the efficiency of the heat exchanger is deteriorated. Generally, the end enclosure structure of the micro-channel plate heat exchanger mainly adopts a straight-in type end enclosure structure (as shown in fig. 1 and fig. 2), but the flow rate of cold fluid in the straight-in type end enclosure structure has a global non-uniform problem, and even if structures such as baffles, guide plates or orifice plates are added at two sides of an inlet of the straight-in type end enclosure structure to improve the flow rate distribution in the end enclosure structure, the pressure loss in the straight-in type end enclosure structure is directly caused to be large.
Disclosure of Invention
The technical problems to be solved by the invention are as follows: the problem of overlarge internal pressure loss of the existing optimized heat exchanger direct-entering type end socket structure is solved; further provides a side entry type end enclosure structure suitable for the micro-channel plate heat exchanger.
The technical scheme adopted by the invention for solving the technical problems is as follows:
the side entry type end socket structure suitable for the micro-channel plate heat exchanger is characterized in that the overall structure of the end socket structure is divided into a water inlet section, a divergent section and a flow guide section; the cold fluid outlet of the water inlet section is connected with the cold fluid inlet of the divergent section, and the cold fluid outlet of the divergent section is connected with the cold fluid inlet of the guide section; a cold fluid outlet of the flow guide section is connected with a cold fluid inlet of the micro channel; the whole depth of the flow guide section is gradually reduced.
Furthermore, the end enclosure structure comprises two side vertical plates, an upper top plate, a lower bottom plate and a rear blocking plate, wherein the two side vertical plates are vertically arranged oppositely, and the upper top plate and the lower bottom plate are vertically arranged oppositely and are respectively welded between the two side vertical plates; the rear blocking plate is fixedly arranged at the tail end of a flow channel formed by the two side vertical plates and the upper top plate; the front end surfaces of the two side vertical plates, the front end surface of the upper top plate and the front end surface of the lower bottom plate form an inlet of cold fluid, the lower end surfaces of the two side vertical plates, the lower end surface of the lower bottom plate and the lower end surface of the rear blocking plate form an outlet of the cold fluid, and the outlet of the cold fluid is connected to the inlet of the micro channel of the heat exchanger;
the upper top plate comprises a horizontal section, an inclined section and a streamline section; establishing a plane rectangular coordinate system for a curve of the streamline section of the upper top plate projected to the paper surface, wherein the origin of the coordinate system is the end point of the tail end of the curve, and the direction of the x axis is the inflow direction of the cold fluid; the parameterized equation of the curve structure of the streamline section projected to the paper surface is as follows:
wherein n is a variable parameter.
Furthermore, a guide plate is obliquely arranged between the divergent section and the flow guide section of the end enclosure structure or at the front end of the flow guide section, a first gap is reserved between the upper end surface of the guide plate and the inner wall of the divergent section of the end enclosure structure, and a second gap is reserved between the lower end surface of the guide plate and the inlet of the micro channel of the heat exchanger.
Furthermore, the guide plate is a pore plate, and a plurality of guide holes are arranged on the guide plate in an array form.
Further, the distance from the gravity center position of the guide plate to the inlet of the seal head structure is set to be L, and the value range of the L is 15-25 mm.
Further, an included angle between the guide plate and the vertical surface is set as alpha, and the value range of alpha is 0< alpha <90 degrees.
Furthermore, the distance between the centers of two transversely adjacent guide holes is R, the value of R is 3mm, the aperture of each guide hole is phi, and the value range of phi is 0.5mm < phi <2.5 mm.
Furthermore, the thickness of the guide plate is 1 mm.
Further, rounding treatment with the radius of 0.5mm is carried out on the junction of the two side wall surfaces of the contact part of the guide plate and the fluid; and rounding with the radius of 0.2mm is carried out at the intersection line of the side wall surface of the flow guide hole and the surface of the flow guide plate.
Furthermore, the two side vertical plates, the upper top plate, the lower bottom plate, the rear blocking plate and the guide plate are all manufactured by processing metal titanium.
Compared with the prior art, the invention has the following beneficial effects:
1. according to the invention, a side-entry type end socket structure is adopted, the shell part of the end socket structure is designed based on a cubic spline curve, the depth of the end socket structure is gradually reduced, the pressure loss generated by huge internal vortexes is reduced, and the huge pressure drop caused by the huge internal vortexes of the end socket is weakened; the phenomenon of cold fluid jet impact is weakened by adding the porous guide plate in the end socket, so that the problem of a vortex dead zone of cold fluid at the inlet of a micro channel at the inlet side of the end socket is solved, and the approximately uniform distribution of fluid entering the inlet of a flow channel is realized;
2. the position, the inclination angle and the aperture of the guide plate which are arranged oppositely are changed according to the actual working condition, and the three parameters are adjusted to adapt to different operating environments, so that the overall efficiency of the heat exchanger is improved to the greatest extent;
3. rounding off the juncture of the two side wall surfaces of the contact part of the guide plate and the fluid and the intersection line of the side wall surface of the guide hole and the side wall of the guide plate respectively to reduce the local pressure loss in the seal head structure;
4. the invention solves the problem of uniform distribution of cold fluid in the micro channel of the heat exchanger, and also solves the problems of local turbulence, pressure loss and uneven temperature distribution in the micro channel caused by uneven flow distribution before the cold fluid enters the micro channel, thereby finally solving the problem of performance reduction of the heat exchanger.
Drawings
FIG. 1 shows an inlet of a straight-in type head structure;
FIG. 2 is a schematic view of a straight-in head structure and a general flow trajectory of a flow channel after entering the head structure;
FIG. 3 is a schematic structural view of the side entry type end socket of the present invention;
FIG. 4 is a schematic view of a side entry type end socket structure and a schematic view of a flow path according to the present invention;
FIG. 5 is a schematic view of the side entry seal head structure housing "spline curve" of the present invention;
FIG. 6 is a schematic view of a baffle configuration; fig. 6(a) is a schematic structural view when the inner diameter of the diversion hole on the diversion plate is 0.5 mm; fig. 6(b) is a schematic structural view when the inner diameter of the diversion hole on the diversion plate is 2.5 mm;
FIG. 7 is a schematic view of the baffle tilt angle;
FIG. 8 is a schematic view of the relative positions of baffles;
FIG. 9 is a schematic diagram showing the dimensions of the head structure and the dimensions of the micro-channel in example 1 of the present invention; FIG. 9(a) is a front view of the present invention; FIG. 9(b) is a left side view of the present invention; FIG. 9(C) is a partial enlarged view at C in FIG. 9 (b); FIG. 9(d) is a top view of the present invention with the top plate removed; FIG. 9(e) is a partial enlarged view at B in FIG. 9 (d);
fig. 10 is a numerical simulation diagram of an adaptive structure of the side entry type end socket structure provided in the embodiment of the present invention under a certain working condition; FIG. 10(a) is a schematic diagram of the fluid velocity at the first gap, the second gap and the baffle immediately after the cold fluid enters the header structure; fig. 10(b) is a schematic view of the fluid states of the first gap, the second gap and the baffle when the cold fluid completely enters the end enclosure structure and then keeps a stable state.
Detailed Description
The technical scheme of the invention is further explained by the specific implementation mode in combination with the attached drawings:
as shown in fig. 3 and 4, the side-in type end enclosure structure suitable for the micro-channel plate heat exchanger includes two side vertical plates 1, an upper top plate 2, a lower bottom plate 3 and a rear blocking plate 4, the two side vertical plates 1 are vertically arranged oppositely, the upper top plate 2 and the lower bottom plate 3 are arranged oppositely up and down and are respectively welded between the two side vertical plates 1, that is, two side end surfaces of the upper top plate 2 are respectively welded with upper end surfaces of the two side vertical plates 1, and two side end surfaces of the lower bottom plate 3 are respectively welded with lower end surfaces of the two side vertical plates 1; the rear blocking plate 4 is fixedly arranged at the tail end of a flow channel formed by the two side vertical plates 1 and the upper top plate 2, namely two side end surfaces opposite to the rear blocking plate 4 are respectively welded on the rear end surfaces of the two side vertical plates 1, and the upper end surface of the rear blocking plate 4 is welded on the rear end surface of the upper top plate 2;
the front end surfaces of the two side vertical plates 1, the front end surface of the upper top plate 2 and the front end surface of the lower bottom plate 3 form an inlet of cold fluid, the lower end surfaces of the two side vertical plates 1, the lower end surface of the lower bottom plate 3 and the lower end surface of the rear blocking plate 4 form an outlet of the cold fluid, and the outlet of the cold fluid is connected to the inlet of the heat exchanger micro channel 5; as shown in fig. 5, the overall configuration of the end socket structure is divided into a water inlet section 6, a divergent section 7 and a flow guide section 8; the cold fluid outlet of the water inlet section 6 is connected with the cold fluid inlet of the divergent section 7, and the cold fluid outlet of the divergent section 7 is connected with the cold fluid inlet of the guide section 8; the integral depth of the flow guide section 8 is gradually reduced; namely, the two side vertical plates 1, the upper top plate 2 and the lower bottom plate 3 are all special-shaped plates, and the upper top plate 2 comprises a horizontal section 2-1, an inclined section 2-2 and a streamline section 2-3; as shown in fig. 3, a plane rectangular coordinate system is established for the curve of the streamline section 2-3 of the upper top plate projected to the paper surface, the origin of the coordinate system is the end point of the tail end of the curve, and the direction of the x axis is the direction of the cold fluid inflow; the parameterized equation of the curve structure of the streamline section 2-3 projected to the paper surface is as follows:
wherein n is a variable parameter, and the variable guide curve is changed to a certain extent, so that different shell structures are formed.
The shell structure of the end socket structure adopts a structural design of a cubic spline curve to form a streamline shell structure, the structural appearance of the streamline shell structure is changed according to an actual application scene, namely the streamline shell structure is determined according to the flow velocity of working media at an inlet of the end socket, basic physical properties (viscosity) of the working media, environmental pressure and other factors, and a proper streamline structure is selected to adapt to different working conditions; the streamlined shell structure gradually reduces the depth, reduces the pressure loss generated by the huge vortex in the end socket structure, and weakens the huge pressure drop caused by the huge vortex in the end socket.
As an optional embodiment, in order to uniformly distribute the cold fluid into the micro channels 5 of each heat exchanger, as shown in fig. 4 and 6, a guide plate 9 is further obliquely arranged between the divergent section 7 and the guide section 8 of the head structure or at the front end of the guide section 8, a first gap is left between the upper end surface of the guide plate 9 and the inner wall of the divergent section of the head structure, a second gap is left between the lower end surface of the guide plate 9 and the inlet of the micro channel of the heat exchanger, the guide plate 9 is a hole plate, and a plurality of guide holes 9-1 are arranged on the guide plate 9 in an array form; as shown in fig. 7, the flow guide holes 9-1, the first gap and the second gap all realize the flow guide effect, and because the first gap and the second gap are not subjected to the resistance of the flow guide plate, the cold fluid has high flow velocity and high flow rate, the cold fluid flowing through the first gap flows to the tail end of the seal head structure flow guide section 8 under the action of the streamline section 2-3 of the upper top plate 2, the cold fluid flowing through the flow guide plate 9 flows to the middle and the middle rear positions of the seal head structure flow guide section 8, and the cold fluid flowing through the second gap flows to the front end and the middle front positions of the seal head structure flow guide section 8; it can be clearly seen from fig. 7 that the cold fluid enters from the inlet of the end enclosure structure, and the cold fluid weakens the jet impact phenomenon of the cold fluid at the inlet of the end enclosure through the guide holes on the guide plate and the gaps left above and below the guide holes, so that the range of the vortex dead zone at the inlet of the micro channel 5 of the heat exchanger is reduced, and then the cold fluid uniformly flows into each micro channel 5 under the action of the shell of the end enclosure structure, and the uniform distribution of the flow of the end enclosure structure is realized; the cold fluid enters the micro channel, exchanges heat with the hot fluid on the other side and then flows out; the invention solves the problem of uniform distribution of cold fluid in the micro channel of the heat exchanger, and also solves the problems of local turbulence, pressure loss and uneven temperature distribution in the micro channel caused by uneven flow distribution before the cold fluid enters the micro channel, thereby finally solving the problem of performance reduction of the heat exchanger.
As an optional embodiment, in order to uniformly distribute the cold fluid into the micro channels, reduce local turbulence in the end enclosure, and uniformly distribute the temperature in the micro channels, as shown in fig. 8, the position of the guide plate 9 is adjusted according to different working conditions, the distance from the gravity center position of the guide plate 9 to the inlet of the end enclosure structure is L, and the value range of L is 15mm to 25 mm;
the initial position that guide plate 9 originally set up is 25mm departments apart from the seal head structure entrance, and guide plate 9 is according to the operating mode of difference, and the translation is 10mm to seal head structure entrance gradually, and the biggest translation distance.
As an optional implementation manner, in order to uniformly distribute the cooling working medium into the micro channel, reduce the local turbulence in the end socket, and uniformly distribute the temperature in the micro channel, as shown in fig. 7, the inclination angle of the guide plate 9 may be adjusted according to different working conditions, the included angle between the guide plate 9 and the vertical surface is set to α, and the value range of α is 0< α <90 °.
As an optional implementation manner, in order to uniformly distribute the cooling working medium into the micro channel, reduce the local turbulence in the end socket and uniformly distribute the temperature in the micro channel, the aperture size of the flow guide holes 9-1 is adjusted according to different working conditions, that is, the distance between the centers of two transversely adjacent flow guide holes 9-1 is R, the value of R is 3mm, the aperture of the flow guide hole 9-1 is Φ, and the value range of Φ is 0.5mm < Φ <2.5 mm.
As an optional implementation mode, in order to reduce local pressure loss in the end socket structure as much as possible, rounding processing is respectively performed on the edge of the side wall of the guide plate and the edge of the hole wall of the guide hole; namely, when the guide plate 9 is processed, the fillet treatment with the radius of 0.5mm is carried out on the boundary of the two side wall surfaces of the contact part of the guide plate and the fluid; when the guide hole 9-1 is processed, rounding with radius of 0.2mm is carried out at the intersection line of the side wall surface of the guide hole and the side wall of the guide plate.
According to the invention, the position, the inclination angle and the aperture of the guide plate which are oppositely arranged are respectively adjusted according to the influence of actual working conditions such as the flow velocity of the cooling working medium at the end socket inlet, the basic physical property (viscosity) of the working medium, the environmental pressure and the like, the three parameters are adjusted to adapt to different operating environments, and the overall efficiency of the heat exchanger is improved to the maximum extent.
As an optional embodiment, the two side vertical plates 1, the upper top plate 2, the lower bottom plate 3, the rear blocking plate 4 and the guide plate 9 are all made of titanium metal, and are consistent with the whole material of the heat exchanger, so as to improve the power-weight ratio (power-mass ratio) of the light heat exchanger.
In embodiment 1, the side-in type end enclosure structure suitable for the micro-channel plate heat exchanger comprises two side vertical plates 1, an upper top plate 2, a lower bottom plate 3, a rear blocking plate 4 and a guide plate 9, wherein the two side vertical plates 1 are vertically arranged oppositely, the upper top plate 2 and the lower bottom plate 3 are arranged oppositely, two side end surfaces of the upper top plate 2 are respectively welded with the upper end surfaces of the two side vertical plates 1, and two side end surfaces of the lower bottom plate 3 are respectively welded with the lower end surfaces of the two side vertical plates 1; two opposite side end surfaces of the rear plugging plate 4 are respectively welded on the rear end surfaces of the two side vertical plates 1, and the upper end surface of the rear plugging plate 4 is welded on the rear end surface of the upper top plate 2;
the front end surfaces of the two side vertical plates 1, the front end surface of the upper top plate 2 and the front end surface of the lower bottom plate 3 form a cold fluid inlet, the inner diameter of the cold fluid inlet is 30mm, the inner diameter of the outlet of the divergent section is 50mm, the lower end surfaces of the two side vertical plates 1, the lower end surface of the lower bottom plate 3 and the lower end surface of the rear blocking plate 4 form a cold fluid outlet, the length of the cold fluid outlet is 150mm, and the width of the cold fluid outlet is 39 mm; the height of the rear blocking plate 4 is 10mm, the outlet of the cold fluid is connected to the inlet of the heat exchanger micro channel 5, the space between the heat exchange tubes of the micro channel 5 is 3.5mm, and the inner diameter of the heat exchange tube is 2.5 mm;
as shown in fig. 5, the overall configuration of the end socket structure is divided into a water inlet section 6, a divergent section 7 and a flow guide section 8; a guide plate 9 is also obliquely arranged between the divergent section 7 and the flow guide section 8 of the end enclosure structure, a first gap is reserved between the upper end surface of the guide plate 9 and the inner wall of the divergent section of the end enclosure structure, a second gap is reserved between the lower end surface of the guide plate 9 and the inlet of the micro channel of the heat exchanger, the guide plate 9 is a pore plate, and a plurality of guide holes 9-1 are distributed on the guide plate 9 in an array form; the length of the water inlet section 6 is 10mm, and the inner diameter of the divergent section 7 is 50 mm; the thickness of the guide plate 9 is 1mm, the side length of the guide plate 9 is 30mm, and the circle center distance R of two transversely adjacent guide holes 9-1 is 3 mm;
when the flow velocity of the working medium at the inlet side of the end socket is between 0.21m/s and 1.03m/s, the inclination angle alpha of the guide plate is 45 degrees, the position L of the guide plate, which is away from the inlet, is 22.7mm, the aperture phi of the guide plate is 2.5mm, and the side wall of the guide plate is subjected to fillet treatment with the radius of 0.5 mm; rounding the hole wall of the flow guide hole 9-1 with a radius of 0.2 mm;
establishing a plane rectangular coordinate system for a curve projected to a paper surface by the streamline section 2-3 of the upper top plate, wherein the origin of the coordinate system is the end point of the tail end of the curve, and the direction of the x axis is the inflow direction of the cold fluid; the parameterized equation of the curve structure of the streamline section 2-3 projected to the paper surface is as follows:
the variable parameter n is 5;
as shown in fig. 7, the flow guide holes 9-1, the first gap and the second gap all realize the flow guide effect, and because the first gap and the second gap are not subjected to the resistance of the flow guide plate, the cold fluid has high flow velocity and high flow rate, the cold fluid flowing through the first gap flows to the tail end of the seal head structure flow guide section 8 under the action of the streamline section 2-3 of the upper top plate 2, the cold fluid flowing through the flow guide plate 9 flows to the middle and the middle rear positions of the seal head structure flow guide section 8, and the cold fluid flowing through the second gap flows to the front end and the middle front positions of the seal head structure flow guide section 8; it can be clearly seen from fig. 7 that the cold fluid enters from the inlet of the end enclosure structure, and the cold fluid weakens the jet impact phenomenon of the cold fluid at the inlet of the end enclosure through the guide holes on the guide plate and the gaps left above and below the guide holes, so that the range of the vortex dead zone at the inlet of the micro channel 5 of the heat exchanger is reduced, and then the cold fluid uniformly flows into each micro channel 5 under the action of the shell of the end enclosure structure, and the uniform distribution of the flow of the end enclosure structure is realized; the cold fluid enters the micro channel, exchanges heat with the hot fluid on the other side and then flows out; the invention solves the problem of uniform distribution of cold fluid in the micro channel of the heat exchanger, and also solves the problems of local turbulence, pressure loss and uneven temperature distribution in the micro channel caused by uneven flow distribution before the cold fluid enters the micro channel, thereby finally solving the problem of performance reduction of the heat exchanger.
It is to be understood that the disclosed embodiments are merely exemplary of the invention, and that it is not intended to limit the invention to the particular embodiments disclosed. The embodiment of the present invention may have other embodiments, and all other embodiments obtained by researchers with different skills in the field without creative efforts based on the embodiment of the present invention belong to the protection scope of the present invention without any creative work on the premise of not departing from the novel spirit and the structural essence of the embodiment of the present invention.
Claims (10)
1. The utility model provides a side income formula head structure suitable for small passageway plate heat exchanger which characterized in that: the integral structure of the end enclosure structure is divided into a water inlet section (6), a divergent section (7) and a flow guide section (8); a cold fluid outlet of the water inlet section (6) is connected with a cold fluid inlet of the divergent section (7), and a cold fluid outlet of the divergent section (7) is connected with a cold fluid inlet of the flow guide section (8); a cold fluid outlet of the flow guide section (8) is connected with a cold fluid inlet of the micro channel (5); the whole depth of the diversion section (8) is gradually reduced.
2. The side entry type end socket structure suitable for the micro-channel plate heat exchanger in claim 1 is characterized in that: the end enclosure structure comprises two side vertical plates (1), an upper top plate (2), a lower bottom plate (3) and a rear blocking plate (4), wherein the two side vertical plates (1) are vertically arranged oppositely, the upper top plate (2) and the lower bottom plate (3) are vertically arranged oppositely and are respectively welded between the two side vertical plates (1); the rear blocking plate (4) is fixedly arranged at the tail end of a flow channel formed by the two side vertical plates (1) and the upper top plate (2); the front end surfaces of the two side vertical plates (1), the front end surface of the upper top plate (2) and the front end surface of the lower bottom plate (3) form an inlet of cold fluid, the lower end surfaces of the two side vertical plates (1), the lower end surface of the lower bottom plate (3) and the lower end surface of the rear blocking plate (4) form an outlet of the cold fluid, and the outlet of the cold fluid is connected to the inlet of the heat exchanger micro channel (5);
the upper top plate (2) comprises a horizontal section (2-1), an inclined section (2-2) and a streamline section (2-3); establishing a plane rectangular coordinate system for a curve projected to a paper surface by the streamline section (2-3) of the upper top plate, wherein the origin of the coordinate system is the end point of the tail end of the curve, and the direction of the x axis is the flowing direction of the cold fluid; the parameterized equation of the curve structure of the streamline section (2-3) projected to the paper surface is as follows:
wherein n is a variable parameter.
3. The side entry type end socket structure suitable for the micro-channel plate heat exchanger as claimed in claim 2, wherein: a guide plate (9) is obliquely arranged between the divergent section (7) and the flow guide section (8) of the end enclosure structure or at the front end of the flow guide section (8), a first gap is reserved between the upper end face of the guide plate (9) and the inner wall of the divergent section (7) of the end enclosure structure, and a second gap is reserved between the lower end face of the guide plate (9) and the inlet of the micro channel (5) of the heat exchanger.
4. The side entry type end socket structure suitable for the micro-channel plate heat exchanger as claimed in claim 3, wherein: the guide plate (9) is a pore plate, and a plurality of guide holes (9-1) are arranged on the guide plate (9) in an array form.
5. The side entry type end socket structure suitable for the micro-channel plate heat exchanger as claimed in claim 4, wherein: and the distance from the gravity center position of the guide plate (9) to the inlet of the seal head structure is set to be L, and the value range of the L is 15-25 mm.
6. The side entry type end socket structure suitable for the micro-channel plate heat exchanger as claimed in claim 5, wherein: the included angle between the guide plate (9) and the vertical surface is alpha, and the value range of alpha is 0< alpha <90 degrees.
7. The side entry type end socket structure suitable for the micro-channel plate heat exchanger as claimed in claim 6, wherein: the distance between the centers of two transversely adjacent guide holes (9-1) is R, the value of R is 3mm, the aperture of each guide hole (9-1) is phi, and the value range of phi is 0.5mm < phi <2.5 mm.
8. The side entry type end socket structure suitable for the micro-channel plate heat exchanger of claim 7, wherein: the thickness of the guide plate (9) is 1 mm.
9. The side entry type end socket structure suitable for the micro-channel plate heat exchanger of claim 7, wherein: rounding the boundary of two side wall surfaces of the contact part of the guide plate and the fluid to a radius of 0.5 mm; and rounding with the radius of 0.2mm is carried out at the intersection line of the side wall surface of the guide hole (9-1) and the surface of the guide plate.
10. The side entry type end socket structure suitable for the micro-channel plate heat exchanger of claim 7, wherein: the two side vertical plates (1), the upper top plate (2), the lower bottom plate (3), the rear blocking plate (4) and the guide plate (9) are all manufactured by processing metal titanium.
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|---|---|
| CN113804029B (en) | 2023-12-26 |
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