CN115143818A - Novel heat exchanger made of titanium and aluminum alloy and design method thereof - Google Patents
Novel heat exchanger made of titanium and aluminum alloy and design method thereof Download PDFInfo
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- CN115143818A CN115143818A CN202211060895.9A CN202211060895A CN115143818A CN 115143818 A CN115143818 A CN 115143818A CN 202211060895 A CN202211060895 A CN 202211060895A CN 115143818 A CN115143818 A CN 115143818A
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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
- F28D9/04—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 being formed by spirally-wound plates or laminae
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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
- F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
- F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
- F28F21/081—Heat exchange elements made from metals or metal alloys
- F28F21/084—Heat exchange elements made from metals or metal alloys from aluminium or aluminium alloys
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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
- F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
- F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
- F28F21/081—Heat exchange elements made from metals or metal alloys
- F28F21/086—Heat exchange elements made from metals or metal alloys from titanium or titanium alloys
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
- F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
- F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
- F28F3/044—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being pontual, e.g. dimples
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/20—Design optimisation, verification or simulation
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
- G06F2119/08—Thermal analysis or thermal optimisation
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Abstract
The invention discloses a novel titanium and aluminum alloy heat exchanger and a design method thereof, wherein the novel titanium and aluminum alloy heat exchanger comprises a heat exchanger core, a cold side outlet end socket, a hot side inlet end socket and a hot side outlet end socket, the heat exchanger core comprises a cover plate and a bottom plate, a plurality of heat exchange clapboards which are arranged in the vertical direction are horizontally arranged between the cover plate and the bottom plate, a hot side channel support assembly and a cold side channel support assembly are alternately arranged between the heat exchange clapboards, and the hot side channel support assembly and the cold side channel support assembly respectively form a hot side fluid channel and a cold side fluid channel with the heat exchange clapboards at the upper end and the lower end of the hot side channel support assembly; the cover plate, the bottom plate, the heat exchange partition plate, the hot side channel supporting component and the cold side channel supporting component are welded into an integral structure through brazing, and the heat exchanger has a compact structure and a small volume; meanwhile, the negative pressure area at the tail part can be reduced, the overlarge pressure fluctuation is inhibited, the pressure loss of fluid flowing is reduced, the heat exchange capability is strong, and the like.
Description
Technical Field
The invention relates to the technical field of heat exchangers, in particular to a novel titanium and aluminum alloy heat exchanger and a design method thereof.
Background
Along with the rapid development of naval force in China, a large amount of equipment needs to be equipped on various ships, and because stainless steel products are easy to react with chloride in the marine environment and are easy to corrode, frequent replacement and maintenance of the stainless steel equipment are caused, and high cost is generated, an aluminum alloy heat exchanger has great advantages in heat exchange performance, manufacturing process and economic cost, but the aluminum alloy cannot resist the corrosion of the marine environment for a long time, particularly a core body of the heat exchanger is provided with heat exchange fins and partition plates which are weak places most prone to corrosion; the heat exchanger is easy to be corroded by electrochemistry in a marine environment, the accuracy of the design method of the heat exchanger is not enough, the designed heat exchanger has a large volume and is not an optimal volume, the flow rate of fluid is difficult to be matched with a system, and a lot of resource space is wasted due to overlarge allowance of the heat exchanger.
Disclosure of Invention
The invention aims to solve the technical problem of overcoming the existing defects and provides a novel heat exchanger made of titanium and aluminum alloy and a design method thereof, which have compact structure and small volume; the flow resistance is small, the pressure fluctuation is inhibited to be overlarge, the pressure loss of fluid flow is reduced, the heat exchange capability is strong, the structural strength of the heat exchanger is high, and the structure is stable; the heat exchanger has stronger electrochemical corrosion resistance and low manufacturing cost for resisting marine environment corrosion; by adopting a multi-target convergence design method, the design error of the heat exchanger is small, the self precision design of the heat exchanger is considered, the compactness and the high efficiency of the heat exchanger are further improved, the matching degree with a system where the heat exchanger is located is higher, and the problems in the background technology can be effectively solved.
In order to achieve the purpose, the invention provides the following technical scheme: a novel titanium and aluminum alloy heat exchanger comprises a heat exchanger core body, a cold side outlet end socket, a hot side inlet end socket and a hot side outlet end socket, wherein the heat exchanger core body comprises a cover plate and a bottom plate, a plurality of heat exchange partition plates which are horizontally arranged and are arranged along the vertical direction are arranged between the cover plate and the bottom plate, a hot side channel supporting assembly and a cold side channel supporting assembly are alternately arranged between the heat exchange partition plates, a hot side fluid channel is formed between the hot side channel supporting assembly and the heat exchange partition plates at the upper end and the lower end of the hot side channel supporting assembly, and a cold side fluid channel is formed between the cold side channel supporting assembly and the heat exchange partition plates at the upper end and the lower end of the cold side channel supporting assembly; the hot side channel supporting assembly comprises two hot side channel edge seals arranged along the length direction of the heat exchange partition, the hot side channel edge seals are arranged on the two side edges of the heat exchange partition in the length direction, a plurality of hot side channel supporting strips parallel to the hot side channel edge seals are arranged between the hot side channel edge seals, and the heights of the hot side channel edge seals and the hot side channel supporting strips are consistent; the cold side channel support assembly comprises two cold side channel edge sealing strips arranged along the width direction of the heat exchange clapboard, the cold side channel edge sealing strips are arranged on two side edges of the heat exchange clapboard in the width direction, a plurality of cold side channel support strips parallel to the cold side channel edge sealing strips are arranged between the cold side channel edge sealing strips, and the heights of the cold side channel edge sealing strips and the cold side channel support strips are consistent; the back surface of the heat exchange partition plate is punched with turbulence protrusions protruding upwards, and the turbulence protrusions are arranged at equal intervals along the length direction and the width direction of the heat exchange partition plate; the cover plate, the bottom plate, the heat exchange partition plate, the hot side channel supporting assembly and the cold side channel supporting assembly are welded into an integral structure through brazing, the hot side inlet end socket and the hot side outlet end socket are fixedly connected with two side walls of the heat exchanger core body in the width direction respectively, and the cold side outlet end socket is fixedly connected with one side wall of the heat exchanger core body in the length direction.
Furthermore, the heat exchange partition plate is made of a titanium alloy material, and the cover plate, the bottom plate, the hot side channel supporting assembly, the cold side outlet end socket, the hot side inlet end socket and the hot side outlet end socket are made of an aluminum alloy material.
Furthermore, the turbulence protrusions are of a fish-ridge-shaped structure.
Furthermore, the height of the turbulence protrusions is not more than half of the height of the seal at the edge of the cold-side channel.
Further, cold side passageway border strip of paper used for sealing and cold side passageway support bar are right trapezoid's platelike structure, and on cold side passageway border strip of paper used for sealing and the cold side passageway support bar along its length direction's right-angle side and hypotenuse contained angle be 1.5 ~ 3, and the inclined plane of cold side passageway border strip of paper used for sealing all towards the heat transfer baffle inboard, cold side outlet head is located the terminal side of cold side passageway border strip of paper used for sealing.
Furthermore, the hot side channel support assembly further comprises hot side support fins, the two side edges of the heat exchange partition plate in the length direction are located between the hot side channel edge seal strip and the hot side channel support strip and between the hot side channel support strips, and the hot side support fins are as high as the hot side channel edge seal strip.
Furthermore, cold side passageway supporting component still includes the cold side and supports the fin, and the both sides border of heat transfer baffle width direction lies in between cold side passageway border strip of paper used for sealing and the cold side passageway support bar and between the cold side passageway support bar all is equipped with the cold side and supports the fin, and the height that the cold side supported the fin is the same with the height of cold side passageway border strip of paper used for sealing.
In order to achieve the above purpose, the invention also provides the following technical scheme: a method of designing a heat exchanger as described above, comprising the steps of:
s1, inputting technical requirement parameters including heat load Q and flow Q m Cold fluid inlet temperature t lin Hot fluid inlet temperature t rin According to
Calculating the outlet temperature of the cold fluid and the hot fluid;
s2, calculating the qualitative temperature t of the fluid according to the inlet and outlet temperatures of the fluid in the step S1 Stator Looking up the table to obtain the temperature at the qualitative temperatureThe physical property parameter of the fluid of (1);
and S3, determining the height h and the width B of the cold side fluid channel and the hot side fluid channel according to the required or assumed heat exchanger core size, and further calculating the equivalent diameter de of the cold side fluid channel and the hot side fluid channel.
S4, determining the number N of layers and the number N of processes of a cold side fluid channel and a hot side fluid channel of the heat exchanger according to the size of the core body of the heat exchanger in the step S3;
s5, calculating the heat exchange area F and the free flow area F of the heat exchanger according to the heat exchanger core parameters determined in the step S3 and the step S4 Circulation of fluids ；
S6, calculating the fluid flow velocity V, and returning to the step S3 and the step S4 to readjust the parameters of the equivalent diameter de, the number N of layers and the flow number N of the cold-side fluid channel and the hot-side fluid channel when the fluid flow velocity V is larger than or equal to 30m/S or less than or equal to 5 m/S; when the fluid flow speed V is less than or equal to 30m/S and is less than or equal to 5m/S, calculating in the step S7;
s7, calculating a Reynolds number Re, a friction factor f, a heat transfer factor j and a heat supply coefficient alpha, wherein when the heat supply coefficient meets the following conditions: -20% alpha Cold side ≤α Hot side ≤20%α Cold side The calculation of step S8 may be performed if the condition is satisfied; when the heat supply coefficient satisfies: alpha (alpha) ("alpha") Hot side ≤-20%α Cold side Or alpha Hot side ≥20%α Cold side Returning to the step S3 and the step S4 when the condition is met, and readjusting the parameters of the equivalent diameter de, the number of layers N and the flow number N of the cold-side fluid channel and the hot-side fluid channel;
s8, calculating the heat exchange efficiency eta and the effective heat exchange area F of the heat exchanger Is effective Thermal fusion ratio C and NTU;
s9, calculating the actual fluid outlet temperature, performing the next calculation when the fluid outlet temperature is lower than the required fluid outlet temperature, and returning to the step S3 and the step S4 to readjust the parameters of the equivalent diameter de, the number N of layers and the number N of the processes of the cold-side fluid channel and the hot-side fluid channel when the fluid outlet temperature is higher than the required fluid outlet temperature;
s10, calculating the actual heat exchange quantity Q of the heat exchanger Practice of When the actual heat exchange amount Q Practice of When the heat load is more than 10%, carrying out the next flow resistance accounting; when the actual heat exchange quantity Q Practice of Returning to the step S3 and the step S4 when the heat load is less than 10%, and readjusting the parameters of the equivalent diameter de, the number N of layers and the flow number N of the cold-side fluid channel and the hot-side fluid channel;
s11, calculating flow resistance delta P, and finishing the design of the heat exchanger core when the actual flow resistance delta P is smaller than-10% of a required value; returning to the step S3 and the step S4 to readjust the parameters of the equivalent diameter de, the number N of layers and the flow number N of the cold-side fluid channel and the hot-side fluid channel when the actual flow resistance delta P is larger than the required value;
further, the equivalent diameter de of the cold-side fluid channel and the hot-side fluid channel in the step S3 is related to the height h and the width B thereof, and when h/B is less than or equal to 0.01, de =2 h/(1+h/B); when h/B > 0.01, de =2h.
Compared with the prior art, the invention has the beneficial effects that: according to the novel titanium and aluminum alloy heat exchanger and the design method thereof, no heat exchange fin is arranged in the heat exchanger, and all heat exchange areas are primary surfaces of hot side and cold side in fluid contact, so that the space can be effectively saved, the flow resistance is small, more other equipment is equipped, the structure is compact, and the heat exchange capacity is strong; the turbulent flow bulges arranged on the heat exchange partition plate can effectively destroy the boundary layer of fluid flow, further enhance the heat exchange capability, reduce the negative pressure area at the tail part, inhibit overlarge pressure fluctuation and reduce the pressure loss of the fluid flow; the heat exchanger has high structural strength and stable structure; the titanium alloy material adopted by the heat exchange partition plate has stronger electrochemical corrosion resistance, so that the corrosion problem of the marine environment can be effectively solved, and the other materials are all made of aluminum alloy materials, so that the manufacturing cost of the marine environment corrosion resistant heat exchanger is reduced; by adopting a multi-target convergence design method, the design error of the heat exchanger is small, the self precision design of the heat exchanger is considered, the compactness and the high efficiency of the heat exchanger are further improved, and meanwhile, the matching degree of the heat exchanger with a system where the heat exchanger is located is higher.
Drawings
FIG. 1 is a schematic view of a heat exchanger according to the present invention;
FIG. 2 is an exploded view of the heat exchanger of the present invention;
FIG. 3 is a schematic diagram of a heat exchanger core of the present invention;
FIG. 4 is an enlarged view of a portion of the core structure of the heat exchanger of the present invention;
FIG. 5 is a top view of a hot side passage support assembly of the present invention;
FIG. 6 is a top view of a cold side channel support assembly of the present invention;
FIG. 7 is a flow chart of the heat exchanger design of the present invention.
In the figure: 1 hot side inlet head, 2 hot side outlet head, 3 heat exchanger core, 31 heat exchange partition, 311 turbulence protrusion, 32 hot side channel support assembly, 321 hot side channel edge seal, 322 hot side channel support strip, 323 hot side support fin, 33 cold side channel support assembly, 331 cold side channel edge seal, 332 cold side channel support strip, 333 cold side support fin, 34 hot side fluid channel, 35 cold side fluid channel, 36 cover plate, 37 bottom plate, 4 cold side outlet head.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
Example one
Referring to fig. 1-6, the present invention provides a technical solution: a novel titanium and aluminum alloy heat exchanger comprises a heat exchanger core body 3, a cold side outlet end socket 4, a hot side inlet end socket 1 and a hot side outlet end socket 2, wherein the heat exchanger core body 3 comprises a cover plate 36 and a bottom plate 37, a plurality of horizontally arranged heat exchange partition plates 31 which are arranged along the vertical direction are arranged between the cover plate 36 and the bottom plate 37, a hot side channel support assembly 32 and a cold side channel support assembly 33 are alternately arranged between the heat exchange partition plates 31, a hot side fluid channel 34 is formed between the hot side channel support assembly 32 and the heat exchange partition plates 31 at the upper end and the lower end of the hot side channel support assembly, and a cold side fluid channel 35 is formed between the cold side channel support assembly 33 and the heat exchange partition plates 31 at the upper end and the lower end of the cold side channel support assembly; the hot side channel support assembly 32 comprises two hot side channel edge seals 321 arranged along the length direction of the heat exchange separator 31, the hot side channel edge seals 321 are arranged at the two side edges of the length direction of the heat exchange separator 31, a plurality of hot side channel support bars 322 parallel to the hot side channel edge seals 321 are arranged between the hot side channel edge seals 321, and the heights of the hot side channel edge seals 321 and the hot side channel support bars 322 are consistent; the cold-side channel support component 33 comprises two cold-side channel edge seals 331 arranged along the width direction of the heat exchange separator 31, the cold-side channel edge seals 331 are arranged on the two side edges of the heat exchange separator 31 in the width direction, a plurality of cold-side channel support bars 332 parallel to the cold-side channel edge seals 331 are arranged between the cold-side channel edge seals 331, and the heights of the cold-side channel edge seals 331 and the cold-side channel support bars 332 are consistent; the back surface of the heat exchange partition plate 31 is punched with turbulence protrusions 311 protruding upwards, and the turbulence protrusions 311 are arranged at equal intervals along the length direction and the width direction of the heat exchange partition plate 31; the cover plate 36, the bottom plate 37, the heat exchange partition plate 31, the hot side channel support assembly 32 and the cold side channel support assembly 33 are welded into an integral structure through brazing, the hot side inlet end socket 1 and the hot side outlet end socket 2 are fixedly connected with two side walls in the width direction of the heat exchanger core 3 respectively, and the cold side outlet end socket 4 is fixedly connected with one side wall in the length direction of the heat exchanger core 3; the heat exchange partition plate 31 is made of titanium alloy materials, and the cover plate 36, the bottom plate 37, the hot side channel supporting assembly 32, the cold side channel supporting assembly 33, the cold side outlet seal head 4, the hot side inlet seal head 1 and the hot side outlet seal head 2 are made of aluminum alloy materials.
The working principle is as follows: cold fluid flows along the width direction of the heat exchange partition plate 31 through the cold side fluid channel 35, the cold fluid flows out through the cold side outlet end socket 4, hot fluid flows into the heat side fluid channel 34 through the hot side inlet end socket 1, the hot fluid flows along the length direction of the heat exchange partition plate 31, the hot fluid flows out through the hot side outlet end socket 2, the cold fluid and the hot fluid exchange heat through the heat exchange partition plate 31, namely the cold fluid absorbs the heat of the hot fluid, the temperature of the hot fluid is increased, the heat exchange partition plate 31 is made of a titanium alloy material and has high electrochemical corrosion resistance, meanwhile, the cover plate 36, the bottom plate 37, the hot side channel support assembly 32, the cold side channel support assembly 33, the cold side outlet end socket 4, the hot side inlet end socket 1 and the hot side outlet end socket 2 are made of aluminum alloy materials, and the manufacturing cost of the heat exchanger resistant to marine environmental corrosion is reduced.
In the embodiment, the hot side fluid channel 34 and the cold side fluid channel 35 which are alternately arranged are formed by alternately arranging the hot side channel support assembly 32 and the cold side channel support assembly 33 between the multiple layers of heat exchange clapboards 31, the hot side fluid channel 34 and the cold side fluid channel 35 share one heat exchange clapboard 31, no heat exchange fin is arranged in the hot side fluid channel 34 and the cold side fluid channel 35, and all heat exchange areas are primary surfaces of the hot side and the cold side fluid which are in contact with each other, namely the heat exchange clapboard 31; the hot side fluid and the cold side fluid are enabled to flow and exchange heat vertically through the hot side fluid channel 34 and the cold side fluid channel 35, the heat exchange efficiency is high, the hot side fluid channel 34 and the cold side fluid channel 35 are respectively divided into a plurality of circulation channels through the hot side channel support bar 322 and the cold side channel support bar 332, the fluid flows more uniformly, and the heat exchange efficiency is improved; the turbulent flow protrusions 311 arranged on the heat exchange partition plate 31 can effectively destroy the boundary layer of fluid flow, further enhance the heat exchange capacity, reduce the negative pressure area at the tail part, inhibit overlarge pressure fluctuation and reduce the pressure loss of fluid flow; the titanium alloy material adopted by the heat exchange partition plate 31 has strong electrochemical corrosion resistance, the corrosion problem of the marine environment can be effectively solved, and the other materials are all made of aluminum alloy materials, so that the manufacturing cost of the marine environment corrosion resistant heat exchanger is reduced.
Furthermore, the turbulence protrusion 311 is a ridge-shaped structure, and the turbulence protrusion 311 of the ridge-shaped structure improves the turbulence effect, reduces the flow resistance of the fluid, has a good effect of suppressing pressure fluctuation, and reduces the pressure loss of the fluid flow.
Further, the height of the burbling protrusion 311 is not more than half of the height of the cold-side channel edge seal 331.
Further, cold side passageway border strip 331 and cold side passageway support bar 332 are right trapezoid's platelike structure, and the right-angle side and the hypotenuse contained angle of following its length direction on cold side passageway border strip 331 and the cold side passageway support bar 332 are 1.5 ~ 3, and the inclined plane of cold side passageway border strip 331 all is inboard towards heat transfer baffle 31, cold side outlet head 4 is located the terminal side of cold side passageway border strip 331, because the heat exchanger is vertical installation, is convenient for the rainwater to derive through the special construction of cold side passageway border strip 331 and cold side passageway support bar 332, prevents to appear ponding phenomenon, reduces the corrosion influence.
Further, the hot side channel support assembly 32 further includes a hot side support fin 323, both side edges of the heat exchange spacer 31 in the length direction are located between the hot side channel edge seal 321 and the hot side channel support bar 322 and between the hot side channel support bar 322, and the hot side support fin 323 is disposed, and the height of the hot side support fin 323 is the same as that of the hot side channel edge seal 321, the cold side channel support assembly 33 further includes a cold side support fin 333, both side edges of the heat exchange spacer 31 in the width direction are located between the cold side channel edge seal 331 and the cold side channel support bar 332 and between the cold side channel support bars 332, and the height of the cold side support fin 333 is the same as that of the cold side channel edge seal 331, and the edges of both ends of the heat exchange spacer 31 supported by the hot side support fin 323 and the cold side support fin 333 are placed in a sunken position, so that the heat exchanger has high structural strength and stable structure.
Example two
Referring to fig. 7, the present invention further provides a technical solution: a method of designing a heat exchanger as described above, comprising the steps of:
s1, inputting technical requirement parameters including heat load Q and flow Q m Cold fluid inlet temperature t lin Hot fluid inlet temperature t rin According to
Calculating the outlet temperature t of the cooling body lout Hot fluid outlet temperature t rout ；
Wherein
The specific heat capacity is obtained by looking up a table according to the qualitative temperature.
S2, calculating the qualitative temperature t of the fluid according to the inlet and outlet temperatures of the fluid in the step 1 Stator Looking up a table to obtain the physical property parameters of the fluid at the qualitative temperature;
cold side qualitative temperature
；
Qualitative temperature of hot side
；
S3, determining the height h and width B of the cold side fluid channel 35 and the hot side fluid channel 34 according to the required or assumed heat exchanger core 3 size, and further calculating the equivalent diameter de of the cold side fluid channel 35 and the hot side fluid channel 34.
And S4, determining the layer number N and the flow number N of the cold side fluid channel 35 and the hot side fluid channel 34 of the heat exchanger according to the size of the heat exchanger core 3 in the step S3.
S5, calculating the heat exchange area F and the free flow area F of the heat exchanger according to the parameters of the heat exchanger core body 3 determined in the step S3 and the step S4 Circulation of fluids ；
Free flow area:
；
heat exchange area:
；
wherein: b is the channel width, B is the support strip width, h is the channel height, n is the number of layers, and S is the hot side channel or cold side channel length;
s6, calculating the fluid flow velocity V, and returning to the step S3 and the step S4 to readjust the parameters of the equivalent diameter de, the number of layers N and the flow number N of the cold-side fluid channel 35 and the hot-side fluid channel 34 when the fluid flow velocity V is larger than or equal to 30m/S or the fluid flow velocity V is smaller than or equal to 5 m/S; when the fluid flow speed V is less than or equal to 30m/S and is less than or equal to 5m/S, calculating in the step S7; when the flow velocity is too low, the heat exchange efficiency of the heat exchanger is lower, when the flow velocity is too high, the generated flow resistance is larger, and when the flow velocity is 5-30 m/s, the heat exchanger has smaller flow resistance and larger heat exchange efficiency;
wherein: q. q.s m ρ is the fluid density;
s7, calculating a Reynolds number Re, a friction factor f, a heat transfer factor j and a heat supply coefficient alpha, wherein when the heat supply coefficient meets the following conditions: -20% alpha Cold side ≤α Hot side of the furnace ≤20%α Cold side The calculation of step S8 may be performed if the condition is satisfied; when the heat supply coefficient satisfies: alpha is alpha Hot side ≤-20%α Cold side Or alpha Hot side ≥20%α Cold side Returning to the step S3 and the step S4 to readjust the parameters of the equivalent diameter de, the number N of layers and the number N of the processes of the cold-side fluid channel 35 and the hot-side fluid channel 34 under the condition; only when the difference between the heat supply heat exchange coefficients of the cold side and the hot side is smaller, the total heat exchange coefficient K of the heat exchanger is the maximum, and the actual heat exchange amount is the maximum;
reynolds number:
，
heat transfer factor:
friction factor:
heat supply coefficient:
wherein: cp is the specific heat capacity of the fluid at constant pressure, pr is the Plantt number (which can be obtained by looking up a table according to the qualitative temperature)
S8, calculating the heat exchange efficiency eta and the effective heat exchange area F of the heat exchanger Is effective Thermal fusion ratio C and NTU;
heat exchanger efficiency:
(branched flow)
Hot melting ratio:
wherein: heat capacity:
，W min the lower of the cold and hot sides, W max The larger of the cold and hot sides;
the thickness of the titanium alloy partition plate is,
is the heat conductivity coefficient of the titanium alloy partition plate, F L is effective Is the effective heat transfer area of the cold side, F r is effective For the effective heat transfer area of the hot side, n L Number of cold side channels, n r The number of layers of the hot side channel is. Fouling resistance was neglected for gaseous fluids.
S9, calculating the actual fluid outlet temperature, performing the next calculation when the fluid outlet temperature is lower than the required fluid outlet temperature, and returning to the step S3 and the step S4 to readjust the parameters of the equivalent diameter de, the number N of layers and the number N of the processes of the cold-side fluid channel 35 and the hot-side fluid channel 34 when the fluid outlet temperature is higher than the required fluid outlet temperature;
actual cold-side fluid outlet temperature:
actual hot side fluid outlet temperature:
wherein: w is a group of L Heat capacity on the cold side, W r Thermal capacity at the hot side;
s10, calculating the actual heat exchange quantity Q of the heat exchanger Practice of When the actual heat exchange amount Q In fact When the heat load Q is more than 10%, carrying out the next flow resistance accounting; when actual heat exchange quantity Q In fact When the heat load is less than 10%, returning to the step S3 and the step S4 to readjust the parameters of the equivalent diameter de, the number N of layers and the flow number N of the cold side fluid channel 35 and the hot side fluid channel 34;
s11, calculating the actual flow resistance delta P, and finishing the design of the heat exchanger core body 3 when the actual flow resistance delta P is smaller than-10% of a required value; and returning to the step S3 and the step S4 to readjust the parameters of the equivalent diameter de, the number N of layers and the number N of the processes of the cold-side fluid channel 35 and the hot-side fluid channel 34 when the actual flow resistance delta P is larger than the required value of-10%.
Further, the equivalent diameter de of the cold-side fluid channel 35 and the hot-side fluid channel 34 in step S3 is related to the height h and the width B thereof, and when h/B is less than or equal to 0.01, de =2 h/(1+h/B); when h/B > 0.01, de =2h.
The design method disclosed by the embodiment adopts a design method of multi-target convergence such as fluid flow rate, heat supply coefficient, fluid outlet temperature, actual heat exchange quantity and flow resistance of the heat exchanger, the design error of the heat exchanger is small, the self-precision design of the heat exchanger is considered, the compactness and the high efficiency of the heat exchanger are further improved, and meanwhile, the matching degree of the heat exchanger with a system where the heat exchanger is located is higher.
Although embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that changes, modifications, substitutions and alterations can be made in these embodiments without departing from the principles and spirit of the invention, the scope of which is defined in the appended claims and their equivalents.
Claims (9)
1. The utility model provides a novel heat exchanger of titanium, aluminum alloy, includes heat exchanger core, cold side outlet head, hot side inlet head and hot side outlet head, its characterized in that: the heat exchanger core comprises a cover plate and a bottom plate, a plurality of heat exchange partition plates which are horizontally arranged and are arranged along the vertical direction are arranged between the cover plate and the bottom plate, a hot side channel supporting component and a cold side channel supporting component are alternately arranged between the heat exchange partition plates, a hot side fluid channel is formed between the hot side channel supporting component and the heat exchange partition plates at the upper end and the lower end of the hot side channel supporting component, and a cold side fluid channel is formed between the cold side channel supporting component and the heat exchange partition plates at the upper end and the lower end of the cold side channel supporting component; the hot side channel supporting assembly comprises two hot side channel edge sealing strips arranged along the length direction of the heat exchange partition plate, the hot side channel edge sealing strips are arranged on the two side edges of the heat exchange partition plate in the length direction, a plurality of hot side channel supporting strips parallel to the hot side channel edge sealing strips are arranged between the hot side channel edge sealing strips, and the heights of the hot side channel edge sealing strips and the hot side channel supporting strips are consistent; the cold side channel support assembly comprises two cold side channel edge sealing strips arranged along the width direction of the heat exchange clapboard, the cold side channel edge sealing strips are arranged on two side edges of the heat exchange clapboard in the width direction, a plurality of cold side channel support strips parallel to the cold side channel edge sealing strips are arranged between the cold side channel edge sealing strips, and the heights of the cold side channel edge sealing strips and the cold side channel support strips are consistent; the back surface of the heat exchange partition plate is punched with turbulence protrusions protruding upwards, and the turbulence protrusions are arranged at equal intervals along the length direction and the width direction of the heat exchange partition plate; the cover plate, the bottom plate, the heat exchange partition plate, the hot side channel supporting assembly and the cold side channel supporting assembly are welded into an integral structure through brazing, the hot side inlet end socket and the hot side outlet end socket are respectively and fixedly connected with two side walls of the heat exchanger core in the width direction, and the cold side outlet end socket is fixedly connected with one side wall of the heat exchanger core in the length direction.
2. The novel titanium-aluminum alloy heat exchanger as recited in claim 1, wherein: the heat exchange partition plate is made of a titanium alloy material, and the cover plate, the bottom plate, the hot side channel supporting assembly, the cold side outlet end socket, the hot side inlet end socket and the hot side outlet end socket are made of an aluminum alloy material.
3. The novel titanium-aluminum alloy heat exchanger as recited in claim 1, wherein: the turbulence protrusions are of a fish-ridge-shaped structure.
4. The novel titanium-aluminum alloy heat exchanger as recited in claim 1, wherein: the height of the turbulence protrusions does not exceed half of the height of the edge seal of the cold-side channel.
5. The novel titanium and aluminum alloy heat exchanger as recited in claim 1, wherein: the cold side channel edge seal strip and the cold side channel support strip are of right trapezoid plate-shaped structures, the right-angle side and the bevel edge included angle along the length direction of the cold side channel edge seal strip and the cold side channel support strip are 1.5-3 degrees, the inclined plane of the cold side channel edge seal strip faces the inner side of the heat exchange partition plate, and the cold side outlet end socket is located at the tail end side of the cold side channel edge seal strip.
6. The novel titanium-aluminum alloy heat exchanger as recited in claim 1, wherein: the hot side channel supporting component further comprises hot side supporting fins, the two side edges of the heat exchange partition in the length direction are located between the hot side channel edge sealing strip and the hot side channel supporting strips, and the hot side supporting fins are arranged between the hot side channel edge sealing strips, and the height of each hot side supporting fin is the same as that of each hot side channel edge sealing strip.
7. The novel titanium-aluminum alloy heat exchanger as recited in claim 1, wherein: the cold side channel supporting component further comprises a cold side supporting fin, the two side edges of the width direction of the heat exchange clapboard are located between the cold side channel edge sealing strip and the cold side channel supporting strip and between the cold side channel supporting strips, the cold side supporting fin is arranged, and the height of the cold side supporting fin is the same as that of the cold side channel edge sealing strip.
8. A method of designing a heat exchanger according to any one of claims 1 to 7, comprising the steps of:
s1, inputting technical requirement parameters including heat load Q and flow Q m Cold fluid inlet temperature t lin Hot fluid inlet temperature t rin According to
Calculating the outlet temperature t of the cold body lout Hot fluid outlet temperature t rout ；
S2, calculating flow according to the temperature of the fluid inlet and the fluid outlet in the step S1Qualitative temperature t of body Stator Looking up a table to obtain the physical property parameters of the fluid at the qualitative temperature;
s3, determining the height h and the width B of a cold-side fluid channel and a hot-side fluid channel according to the required or assumed heat exchanger core size, and further calculating the equivalent diameter de of the cold-side fluid channel and the hot-side fluid channel;
s4, determining the number N of layers and the number N of processes of a cold side fluid channel and a hot side fluid channel of the heat exchanger according to the size of the core body of the heat exchanger in the step S3;
s5, calculating the heat exchange area F and the free flow area F of the heat exchanger according to the heat exchanger core parameters determined in the step S3 and the step S4 Circulation of fluids ；
S6, calculating the flow rate of the fluid, and returning to the step S3 and the step S4 to readjust the parameters of the equivalent diameter de, the number N of layers and the flow number N of the cold-side fluid channel and the hot-side fluid channel when the flow rate V is larger than or equal to 30m/S or smaller than or equal to 5 m/S; when the fluid flow rate is less than or equal to 30m/S and less than or equal to 5m/S, calculating in the step S7;
s7, calculating a Reynolds number Re, a friction factor f, a heat transfer factor j and a heat supply coefficient alpha, wherein when the heat supply coefficient meets the following conditions: -20% alpha Cold side ≤α Hot side ≤20%α Cold side The calculation of step S8 may be performed if the condition is satisfied; when the heat supply coefficient satisfies: alpha is alpha Hot side ≤-20%α Cold side Or alpha Hot side ≥20%α Cold side Returning to the step S3 and the step S4 to readjust the parameters of the equivalent diameter de, the number N of layers and the flow number N of the cold-side fluid channel and the hot-side fluid channel when the conditions are met;
s8, calculating the heat exchange efficiency eta and the effective heat exchange area F of the heat exchanger Is effective Thermal fusion ratio C and NTU;
s9, calculating the actual fluid outlet temperature, performing the next calculation when the fluid outlet temperature is lower than the required fluid outlet temperature, and returning to the step S3 and the step S4 to readjust the parameters of the equivalent diameter de, the number N of layers and the number N of the processes of the cold-side fluid channel and the hot-side fluid channel when the fluid outlet temperature is higher than the required fluid outlet temperature;
s10, calculating the actual heat exchange quantity Q of the heat exchanger In fact When the actual heat exchange amount Q In fact Greater than thermal loadWhen 10%, carrying out the next flow resistance calculation; when actual heat exchange quantity Q In fact Returning to the step S3 and the step S4 when the heat load is less than 10%, and readjusting the parameters of the equivalent diameter de, the number N of layers and the flow number N of the cold-side fluid channel and the hot-side fluid channel;
s11, calculating the actual flow resistance delta P, and finishing the design of the heat exchanger core when the actual flow resistance delta P is smaller than-10% of a required value; and returning to the step S3 and the step S4 to readjust the parameters of the equivalent diameter de of the cold-side fluid channel and the hot-side fluid channel, the number N of layers and the number N of processes when the actual flow resistance delta P is larger than the required value.
9. The design method of the novel titanium and aluminum alloy heat exchanger as claimed in claim 8, wherein: the equivalent diameter de of the cold side fluid channel and the hot side fluid channel in the step S3 is related to the height h and the width B of the cold side fluid channel and is de =2 h/(1+h/B) when h/B is less than or equal to 0.01; when h/B > 0.01, de =2h.
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