CN102455139A - Double-strand-flow low-temperature spiral winding pipe type heat exchanger with vacuum heat insulation function - Google Patents
Double-strand-flow low-temperature spiral winding pipe type heat exchanger with vacuum heat insulation function Download PDFInfo
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- OKKJLVBELUTLKV-UHFFFAOYSA-N Methanol Chemical compound OC OKKJLVBELUTLKV-UHFFFAOYSA-N 0.000 abstract description 12
- 238000000926 separation method Methods 0.000 abstract description 9
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 abstract description 8
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Abstract
The invention discloses a double-strand-flow low-temperature spiral winding pipe type heat exchanger with a vacuum heat insulation function. The double-strand-flow low-temperature spiral winding pipe type heat exchanger mainly comprises two strands of spiral winding pipe bundles and a vacuum shell; and a new double-strand-flow spiral pipe bundle theoretical winding equation is adopted, and a math model is established and applied to a flow field value simulation process, so that a pipe bundle winding theoretical calculation method is obtained, and the double-strand-flow spiral winding pipe type heat exchanger can be designed and manufactured. By applying a vacuum heat insulation technology combined with the spiral winding pipe bundles, an upper end socket and a lower end socket are welded with a pipe plate, and a vacuum structure is formed by an inner pressure shell and an outer pressure shell which are borne by the pipe plate, so that the shortcomings that the conventional vacuum structure cannot be easily combined with the winding pipe type heat exchanger, and the conventional vacuum structure is not convenient to manufacture and install and the like can be overcome; the double-strand-flow low-temperature spiral winding pipe type heat exchanger can be used in the fields of -161 DEG C natural gas liquefaction, -197 DEG C air separation, -197 DEG C low-temperature liquid-nitrogen wash, -70 DEG C low-temperature methanol wash and the like, and has the advantages of high low-temperature heat exchange efficiency, compact structure, large unit volumetric heat transmission area and the like, and can be manufactured on large scale; and thermal expansion can be self-compensated, and the number of heat exchange equipment is reduced.
Description
Technical Field
The invention relates to a double-flow low-temperature spiral winding tubular heat exchanger with vacuum insulation, which is mainly applied to the field of low-temperature liquefaction and separation of gas and comprises the technical fields of low-temperature purification and low-temperature liquefaction and separation of gas, such as low-temperature liquefaction and separation of natural gas at-161 ℃, low-temperature liquefaction and separation of air at-197 ℃, low-temperature liquid nitrogen washing process at-197 ℃, low-temperature methanol washing process at-70 ℃ and the like.
Background
The spiral wound pipe heat exchanger is a heat exchange equipment, mainly used in low-temperature heat and mass exchange process, and has the advantages of compact structure, large heat transfer area per unit volume, self-compensation of heat expansion of heat transfer pipe, easy realization of large-scale, and reduced equipment number, etc., and becomes an important equipment in low-temperature purification and liquefaction processes such as natural gas liquefaction, low-temperature air separation, low-temperature methanol washing, etc. Because the spiral winding tubular heat exchanger is mostly applied to the low temperature environment, the volume is great, generally appear with the form of heat transfer tower, can reach seven, eighty meters at most, and general heat exchanger is also in two, thirty meters, mostly use double stream, the heat transfer of multiple strand flow as the main, and the inner pipe winding is complicated, does not have relevant fixed design standard, also does not have unified design method, along with the process flow or the characteristics of physical property parameter have great difference, consequently has brought the obstacle for the standardized process of spiral winding tubular heat exchanger. The traditional spiral tube type heat exchanger tube bundle winding method has many defects, the distance between inner tubes of the tube bundle and the distance between layers can not be ensured to be consistent everywhere in the winding process, the heat transfer effect is poor, and a unified theoretical calculation method is not provided and is used for the computer-aided calculation process. In addition, because the low-temperature heat exchanger has a large difference with the ambient temperature, the environment is used as a high-temperature heat source to continuously supply heat to the low-temperature heat exchanger, after the surface of the heat exchanger receives solar radiation, air convection heat exchange, ambient heat radiation or in-tube friction heat, fluid in the system can cause serious heat leakage phenomenon particularly after being heated by instant high heat flow density heat, gas-liquid two-phase flow is caused, a large amount of superheated steam is generated, the superheated steam causes severe change of system pressure, serious influence is caused to the heat exchange process of the heat exchanger, and great safety problem is brought. Therefore, the double-flow spiral-wound tubular heat exchanger is better applied to the low-temperature field, and the following problems are needed to be solved better at present: a mathematical model of a tube bundle winding method of the double-strand spiral winding tube type heat exchanger is provided, so that the standardization of the winding tube bundle is facilitated, and preparation is made for a heat transfer numerical simulation process; the vacuum heat insulation technology is applied to the spiral wound tube type heat exchanger, so that the heat insulation problem of the large spiral wound tube type heat exchanger under the low-temperature working condition is solved; the problem of the overall arrangement of the structure and all main parts of the whole tower type double-strand spiral tube type heat exchanger with the vacuum heat insulation function is solved.
Disclosure of Invention
The invention relates to a double-strand low-temperature spiral winding tubular heat exchanger with vacuum heat insulation, which applies a new spiral tube bundle winding method and gives a theoretical winding equation; the vacuum structure is adopted, the vacuum heat insulation technology is effectively applied to the double-strand flow spiral winding tube type heat exchanger, and the defects that the traditional vacuum structure is difficult to combine with the tube bundle of the tube type heat exchanger, the installation is inconvenient and the like are overcome by adopting a step-by-step processing, manufacturing and detecting method.
The technical solution of the invention is as follows:
the utility model provides a take adiabatic double strand low temperature spiral winding tubular heat exchanger in vacuum, including skirt 1, take over 2, lower tube sheet 3, fluid-discharge tube 4, lower support ring 5, vacuum takeover 6, well core section of thick bamboo 7, spiral coil 8, spiral coil goes up support ring 9, takeover 10, go up external pressure head 11, takeover 12, takeover 13, go up interior pressure head 14, blast pipe 15, go up tube sheet 16, spiral coil 17, interior pressure casing 18, external pressure casing 19, pearl sand 20, takeover 21, interior pressure head 22 down, external pressure head 23 down, takeover 24, its characterized in that: the tube bundle of the spiral coil 8 and the tube bundle of the spiral coil 17 are wound layer by layer around the central core barrel 7, the wound tube cores are arranged in the internal pressure shell 18 through the lower support ring 5 and the upper support ring 9, the upper outlet of the tube bundle is connected with the tube plate 16, and the lower outlet of the tube bundle is connected with the tube plate 3; the top of the middle core barrel 7 is connected with the center of the tube plate 16, the bottom of the middle core barrel is connected with the center of the tube plate 3, and the middle of the middle core barrel is provided with a lower support ring 5 and an upper support ring 9; a vacuum interlayer is arranged between the inner pressure shell 18 and the outer pressure shell 19, the top part is provided with a shell side inlet connecting pipe 10 and an exhaust pipe 15, the bottom part is provided with a shell side outlet connecting pipe 21 and a liquid discharge pipe 4, the interlayer is filled with pearly-lustre sand 20, and the bottom part of the outer pressure shell 19 is provided with a vacuum connecting pipe 6; a vacuum interlayer is arranged between the upper outer pressure end socket 11 and the upper inner pressure end socket 14, a partition plate is arranged in the middle of the upper inner pressure end socket 14, the partition plate divides the space of the upper end socket into two pipe boxes, a left pipe box is connected with the connecting pipe 13, a right pipe box is connected with the connecting pipe 12, the bottom of the end socket 14 is welded with the pipe plate 16, and the lower edge of the pipe plate 16 is welded with the upper edge of the cylinder 18; a vacuum interlayer is arranged between the lower outer pressure seal head 23 and the lower inner pressure seal head 22, a partition plate is arranged in the middle of the lower outer pressure seal head 22, the lower seal head space is divided into two pipe boxes by the partition plate, a left pipe box is connected with the connecting pipe 24, a right pipe box is connected with the connecting pipe 2, the upper edge of the seal head 22 is welded with the pipe plate 3, and the upper edge of the pipe plate 3 is welded with the lower edge of the cylinder 18; a skirt 1 is arranged under the external pressure end enclosure 23; the upper end enclosure 11 is welded with the upper edge of the cylinder 19, and the lower end enclosure 23 is welded with the lower edge of the cylinder 19.
The central line of any spiral pipeline in the winding section of the double-flow low-temperature spiral winding pipe type heat exchanger tube bundle meets the following pipeline curve expression:
x ni 2+y ni 2=r ni 2
z ni =2πr ni k ni tg b ni
b ni ＝θ ni
l n =2πr ni [m+(n-1)d]/m
m＝m 1＝m A1+m B1
e n ＝m An /m Bn ＝j
d＝e n +1
β An 1 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))]×(-1) n
β Ani –β An i(-1) =((1+(-1) i )/2×2π/m+(1+(-1) i+1) /2×j×2π/m)×(-1) n =(j+1-(j-1))×(-1) i ×π/m×(-1) n
β Bni =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+j×2/m+(i-1)×(j+1)×2 /m]×(-1) n
t n =m+(n-1)/2
S＝nm+dn 2/2-dn/2
wherein,x，y，zas a coordinate variable, the number of the coordinate variables,ris the radius of the base circle,kin order to raise the number of turns,dthe number of the tubes is increased for each layer,bin order to increase the helix angle,lis the length of the circumference of the base circle,m＝m 1the number of the first layer of the tubes is,nthe number of layers is the number of layers,iis the first layer in the layeriThe root canal is provided with a plurality of holes,αthe starting angle of the first spiral tube of the first layer,βis the starting angle of the angle,θthe size of the spiral angle is the size of the spiral angle,tthe number of the tubes in any layer is,Sthe number of the tubes of the whole heat exchanger,ethe ratio of the number of the two fluid pipes in the layer,Athe first stream of the fluid is the first stream of the fluid,Bis a second stream; initial angleβThe concrete expression is as follows:
……………………………………………………………………………………
e n ＝m An /m Bn ＝1；
the first layer of the first stream and the first pipeline meetβ A11＝-α；
The first layer of the first stream and the second pipeline meetβ A12＝-(α+2×2π/m)；
The first layer of the first flow and the third pipeline meet the requirementβ A13＝-(α+2×2π/m+2×2π/m)；
The first layer of the first stream and the fourth pipeline meetβ A14＝-(α+2×2π/m+2×2π/m+2×2π/m)；
First layer first streamhRoot canal satisfiesβ A h1＝-(α+2(h-1)×2π/m)；
First layer second streamARoot canal satisfiesβ B11＝-(α+2π/m)；
The second pipeline of the first layer and the second stream meets the requirementβ B12＝-(α+2π/m+2×2π/m)；
The third pipeline of the first layer, the second stream and the third stream meets the requirementβ B13＝-(α+2π/m+2×2π/m+2×2π/m)；
The fourth pipeline of the second strand of the first layer meets the requirement of the first layerβ B14＝-(α+2π/m+2×2π/m+2×2π/m+2×2π/m)；
…………
First layer second streamhRoot canal satisfiesβ B h1＝-(α+2π/m+2(h-1)×2π/m)；
The first pipeline of the first flow of the second layer meets the requirement of the first pipelineβ A21＝α+π/m；
The second layer of the first stream and the second pipeline meetβ A22＝α+π/m+2×2π/m；
The second layer of the first flow and the third pipe meetβ A23＝α+π/m+2×2π/m+2×2π/m；
Second layer first stream secondhRoot canal satisfiesβ A h2＝α+π/m+2(h-1)×2π/m；
The first pipeline of the second layer and the second strand meetsβ B21＝α+π/m+2π/m；
The second layer of the second flow and the second pipeline meetβ B22＝α+π/m+2π/m+2×2π/m；
The third pipe of the second layer, the second strand and the third flow meets the requirementsβ B23＝α+π/m+2π/m+2×2π/m+2×2π/m；
…………
Second layer second streamhRoot canal satisfiesβ B h2＝α+π/m+2π/m+2(h-1)×2π/m；
First, thenThe first flow of the layer and the first pipeline meet the following conditions:
β An 1 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))]×(-1) n
first, thenThe first layer flow and the second pipeline meet the following conditions:
β An 2 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d)) +2×2 /m]×(-1) n
first, thenThe third pipeline of the first flow of the layer meets the following conditions:
β An 3 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d)) +2×2π/m+2×2 /m]×(-1) n
…………
first, thenLayer first streamiThe root canal satisfies:
β Ani =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d)) +2(i-1)×2 /m]×(-1) n
first, thenThe first pipeline of the layer second flow meets the following conditions:
β Bn 1 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+2 /m]×(-1) n
first, thenThe second pipeline of the layer second flow meets the following conditions:
β Bn 2 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d)) +2π/m+2×2 /m]×(-1) n
first, thenThe third pipeline of the layer second flow meets the following conditions:
β Bn 3 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d)) +2π/m+2×2π/m+2×2 /m]×(-1) n
first, thenLayer two streamiThe root canal satisfies:
β Bni =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d)) +2π/m+2(i-1)×2 /m]×(-1) n
……………………………………………………………………………………
e n ＝m An /m Bn ＝2；
the first layer of the first stream and the first pipeline meetβ A11＝-α；
The first layer of the first stream and the second pipeline meetβ A12＝-(α+2π/m)；
The first layer of the first flow and the third pipeline meet the requirementβ A13＝-(α+2π/m+2×2π/m)；
The first layer of the first stream and the fourth pipeline meetβ A14＝-(α+2π/m+2×2π/m+2π/m)；
…………
First layer first streamhRoot canal satisfies
β A h 1–β A h1(-1)＝–((1+(-1) h )/2×2π/m+(1+(-1) h+1) /2×2×2π/m)＝-(3-(-1) h )π/m
First layer second streamARoot canal satisfiesβ B11＝-(α+2×2π/m)；
The second pipeline of the first layer and the second stream meets the requirementβ B12＝-(α+2×2π/m+3×2π/m)；
The third pipeline of the first layer, the second stream and the third stream meets the requirementβ B13＝-(α+2×2π/m+3×2π/m+3×2π/m)；
The fourth pipeline of the second strand of the first layer meets the requirement of the first layerβ B14＝-(α+2×2π/m+3×2π/m+3×2π/m+3×2π/m)；
…………
First layer second streamhRoot canal satisfiesβ B h1＝-(α+2×2π/m+ (h-1)×3×2π/m)；
The first pipeline of the first flow of the second layer meets the requirement of the first pipelineβ A21＝α+π/m；
The second layer of the first stream and the second pipeline meetβ A22＝α+π/m+2π/m；
The second layer of the first flow and the third pipe meetβ A23＝α+π/m+2π/m+2×2π/m；
The fourth pipeline of the first flow of the second layer meets the requirement of the second layerβ A24＝α+π/m+2π/m+2×2π/m+2π/m；
…………
Second layer first stream secondhRoot canal satisfies
β A h 2–β A h2 (-1)＝(1+(-1) h )/2×2π/m+(1+(-1) h+1) /2×2×2π/m＝(3-(-1) h )π/m
Second layer second streamARoot canal satisfiesβ B21＝α+π/m+2×2π/m；
The second layer of the second flow and the second pipeline meetβ B22＝α+π/m+2×2π/m+3×2π/m；
The third pipe of the second layer, the second strand and the third flow meets the requirementsβ B23＝α+π/m+2×2π/m+3×2π/m+3×2π/m；
The fourth pipeline of the second layer of the second flow meets the requirementβ B24＝α+π/m+2×2π/m+3×2π/m+3×2π/m+3×2π/m；
Second layer second streamhRoot canal satisfiesβ B h2＝α+π/m+2×2π/m+ (h-1)×3×2π/m；
First, thenThe first flow of the layer and the first pipeline meet the following conditions:
β An 1 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))]×(-1) n
first, thenThe first layer flow and the second pipeline meet the following conditions:
β An 2 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d)) +2/m]×(-1) n
first, thenThe third pipeline of the first flow of the layer meets the following conditions:
β An 3 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d)) +2 /m+2×2 /m]×(-1) n
first, thenLayer first streamiThe root canal satisfies:
β Ani –β An i(-1) =(3-(-1) i )π/m×(-1) n
first, thenThe first pipeline of the layer second flow meets the following conditions:
β Bn 1 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+2×2/m]×(-1) n
first, thenThe second pipeline of the layer second flow meets the following conditions:
β Bn 2 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+2×2/m+3×2/m]×(-1) n
first, thenThe third pipeline of the layer second flow meets the following conditions:
β Bn 3 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d)) +2×2/m+3×2/m+3×2/m]×(-1) n
first, thenLayer two streamiThe root canal satisfies:
β Bni =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+2×2/m+(i-1)×3×2 /m]×(-1) n
……………………………………………………………………………………
e n ＝m An /m Bn ＝3；
first, thenLayer first streamiThe root canal satisfies:
β An 1 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))]×(-1) n
β An 2 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d)) +2/m]×(-1) n
β An 3 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d)) +2/m+2/m]×(-1) n
β Ani –β An i(-3) =2π/m×(-1) n ×(e n +1) (i＞3)
first, thenLayer two streamiThe root canal satisfies:
β Bni =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+3×2/m+(i-1)×4×2 /m]×(-1) n
……………………………………………………………………………………
e n ＝m An /m Bn ＝j；
first, thenLayer first streamiThe root canal satisfies:
β An 1 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))]×(-1) n
β An 2 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d)) +2/m]×(-1) n
β An 3 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d)) +2/m+2/m]×(-1) n
…………
β Anj =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d)) +(j-1)×2/m]×(-1) n
β Ani –β An i j(-) =2π/m×(-1) n ×(j+1) (i＞j)
first, thenLayer two streamiThe root canal satisfies:
β Bni =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+j×2/m+(i-1)×(j+1)×2 /m]×(-1) n 。
the scheme involves the following principle problems:
the double-strand low-temperature spiral winding tubular heat exchanger with the vacuum thermal insulation is mainly applied to the fields of low-temperature liquefaction and separation of gas and purification of gas, such as the technical fields of low-temperature purification of gas, low-temperature liquefaction and separation of natural gas, low-temperature liquefaction and separation of air, low-temperature methanol washing and the like, so that the double-strand low-temperature spiral winding tubular heat exchanger has a low-temperature heat exchange characteristic, multiple gases are mixed for heat exchange, multiphase flow is often achieved, the heat exchange temperature difference is large, phase change exists in the heat exchange process, and the double-strand low-temperature spiral winding. The invention provides a double-flow low-temperature spiral winding tubular heat exchanger with a vacuum heat insulation layer, which is mainly applied to a low-temperature environment, provides a corresponding tube bundle winding mathematical model, can apply a winding method of the spiral winding tubular heat exchanger to a mathematical modeling process, and applies a built mathematical model and a corresponding three-dimensional physical model to a flow field numerical simulation process to obtain a flow field parameter distribution model and a related heat transfer model of the double-flow spiral winding tubular heat exchanger, so as to design the whole spiral winding tubular heat exchanger, and the double-flow spiral winding tubular heat exchanger has a determined design method; the application of a vacuum low-temperature heat insulation mode is the most effective method for solving the problem of internal heat transfer of an environmental heat source in the low-temperature heat exchange process at present, can effectively avoid the heat transfer process of the environmental heat source which takes heat conduction, convective heat exchange and heat radiation as main heat transfer ways, is a more common method in the low-temperature field at present, and has the advantages of heat insulation and performance improvement by nearly one magnitude compared with the traditional capillary material. In order to meet the requirement of vacuum heat insulation of the spiral winding pipe heat exchanger, the heat exchanger needs to have vacuum heat insulation and is convenient to process and manufacture, the pipe core is processed and manufactured firstly, then the inner shell is assembled, finally the vacuum outer shell is manufactured and installed and adopts an integral heat insulation mode, namely the barrel 19, the upper end enclosure 11 and the lower end enclosure 23 form a unified vacuum outer shell which is integrally welded and formed, the vacuum heat insulation process of the integral heat exchanger is realized, the processing and the manufacturing are more convenient, and each vacuum component can be processed step by step and correspondingly detected. The tube bundle 17 and the tube bundle 8 are well installed and manufactured, can be independently detected, are installed in the inner shell 18 after being detected to be qualified, and are butted with the upper end enclosure and the lower end enclosure. The purpose of adding the pearlite sand 20 in the vacuum layer is to reduce the radiation heat exchange amount in the vacuum layer.
The invention has the technical characteristics that:
the overall design model and the specific model structure of the double-strand low-temperature spiral wound tubular heat exchanger with vacuum heat insulation are provided; the mathematical model can be applied to apply the winding method of the double-flow spiral winding tube type heat exchanger to a mathematical modeling process, and apply the established mathematical model and a corresponding three-dimensional physical model to a flow field numerical simulation process, so that a flow field parameter distribution model and a related heat transfer model of the double-flow spiral winding tube type heat exchanger can be obtained, and the whole double-flow spiral winding tube type heat exchanger is designed, so that the double-flow spiral winding tube type heat exchanger has a determined design method; the integral vacuum structure is applied to the double-strand spiral winding tube type heat exchanger, namely, internal components such as tube cores and the like are firstly processed and manufactured, then the inner shell is assembled and detected, and finally the vacuum outer shell is manufactured and installed after the detection is qualified, so that the integral vacuum heat insulation process of the heat exchanger is realized. Each vacuum component can be processed and manufactured step by step and correspondingly detected, so that the processing and manufacturing processes of the spiral wound tube type heat exchanger are more convenient, and the defect that the original vacuum heat insulation technology cannot be combined with a large wound tube type heat exchanger is overcome.
Drawings
Fig. 1 shows the main components and the installation position relationship of a double-flow low-temperature spiral winding tube type heat exchanger with vacuum heat insulation.
Detailed Description
According to the established tube bundle winding mathematical model, the invention applies a heat transfer numerical simulation method, firstly determines a theoretical winding method of the tube bundle in the double-flow spiral winding tube type heat exchanger and relevant parameters such as tube spacing, layer spacing and the like in the tube bundle winding process, determines an internal optimal arrangement structure of the winding tube type heat exchanger by applying the heat transfer and flow field numerical simulation method, further determines important parameters such as spiral angle, tube spacing, layer spacing and the like, and finally determines a complete arrangement mode according to the known parameters, so that a determined tube bundle design scheme can be obtained, and the processing and manufacturing processes of relevant products can be carried out. Winding the processed spiral tube bundle 8 and the processed spiral tube bundle 17 between an upper annular upper supporting ring 9 and a lower supporting ring 5 on a central cylinder 7 according to the mathematical model of the invention, and connecting and fixing the tube plates at the two ends of the tube bundles; welding an upper tube plate 16 and a lower tube plate 3 among the upper seal head 14, the lower seal head 22 and the cylinder 18; connecting the left side of the lower pipe box with a connecting pipe 24, connecting the right side of the lower pipe box with a connecting pipe 2, connecting the left side of the upper pipe box with a connecting pipe 13 and connecting the right side of the upper pipe box with a connecting pipe 12; nozzle 2 is in communication with tube bundle 8 and nozzle 12, and nozzle 24 is in communication with tube bundle 17 and nozzle 13. During countercurrent, fluid flowing into the lower right tube box from the lower tube 2 flows into each branch tube of the winding tube bundle 8 after passing through the lower tube plate 3, flows in the layered winding tube bundle 8 and performs complex heat exchange with fluid entering the shell pass from the connecting tube 10 in the shell 18, and flows out along the upper right tube box through the connecting tube 12 after the heat exchange is finished through the upper tube plate 16; the fluid flowing into the lower left channel box from the lower connecting pipe 24 flows into each branch pipe of the winding pipe bundle 17 after passing through the lower pipe plate 3, flows in the layered winding pipe bundle 17, and performs complex heat exchange with the fluid entering the shell pass from the connecting pipe 10 in the shell 18, and after the heat exchange is finished, the fluid flows out along the upper left channel box through the connecting pipe 13 through the upper pipe plate 16; the shell-side fluid exits along the lower connecting pipe 23. During parallel flow, fluid flowing into the upper right tube box from the upper connecting tube 12 flows into each branch tube of the winding tube bundle 8 after passing through the upper tube plate 16, flows in the layered winding tube bundle 8, performs complex heat exchange with fluid entering the shell pass from the connecting tube 10 in the shell 18, and flows out through the connecting tube 2 along the lower right tube box through the lower tube plate 3 after the heat exchange is finished; the fluid flowing into the upper left tube box from the upper connecting tube 13 flows into each branch tube of the winding tube bundle 17 after passing through the upper tube plate 16, flows in the layered winding tube bundle 17, and performs complex heat exchange with the fluid entering the shell pass from the connecting tube 10 in the shell 18, and after the heat exchange is finished, flows out along the lower left tube box through the connecting tube 24 through the lower tube plate 3; the shell-side fluid flows out along the lower connecting pipe 21.
Claims (2)
1. The utility model provides a take adiabatic single strand low temperature spiral winding tubular heat exchanger in vacuum, including skirt (1), take over (2), lower tube sheet (3), fluid-discharge tube (4), lower support ring (5), vacuum takeover (6), well core section of thick bamboo (7), spiral coil (8), support ring (9) on the spiral coil, takeover (10), go up outer pressure head (11), takeover (12), takeover (13), interior pressure head (14) on, blast pipe (15), go up tube sheet (16), spiral coil (17), interior pressure casing (18), outer pressure casing (19), pearly-lustre sand (20), takeover (21), interior pressure head (22) down, outer pressure head (23) down, takeover (24), its characterized in that: a tube bundle of a spiral coil (8) and a tube bundle of a spiral coil (17) are wound layer by layer around a central core cylinder (7), the wound tube cores are arranged in an internal pressure shell (18) through a lower support ring (5) and an upper support ring (9), an upper outlet of the tube bundle is connected with a tube plate (16), and a lower outlet of the tube bundle is connected with a tube plate (3); the top of the middle core barrel (7) is connected with the center of the tube plate (16), the bottom of the middle core barrel is connected with the center of the tube plate (3), and the middle of the middle core barrel is provided with a lower support ring (5) and an upper support ring (9); a vacuum interlayer is arranged between the inner pressure shell (18) and the outer pressure shell (19), the top part is provided with a shell side inlet connecting pipe (10) and an exhaust pipe (15), the bottom part is provided with a shell side outlet connecting pipe (21) and a liquid discharge pipe (4), the interlayer is filled with pearlife (20), and the bottom part of the outer pressure shell (19) is provided with a vacuum connecting pipe (6); a vacuum interlayer is arranged between the upper outer pressure end enclosure (11) and the upper inner pressure end enclosure (14), a partition plate is arranged in the middle of the upper inner pressure end enclosure (14), the space of the upper end enclosure is divided into two pipe boxes by the partition plate, a left pipe box is connected with a connecting pipe (13), a right pipe box is connected with a connecting pipe (12), the bottom of the end enclosure (14) is welded with a pipe plate (16), and the lower edge of the pipe plate (16) is welded with the upper edge of a cylinder (18); a vacuum interlayer is arranged between the lower outer pressure seal head (23) and the lower inner pressure seal head (22), a partition plate is arranged in the middle of the lower outer pressure seal head (22), the space of the lower pressure seal head is divided into two pipe boxes by the partition plate, a left pipe box is connected with a connecting pipe (24), a right pipe box is connected with a connecting pipe (2), the upper edge of the seal head (22) is welded with the pipe plate (3), and the upper edge of the pipe plate (3) is welded with the lower edge of the cylinder (18); a skirt (1) is arranged under the outer pressure seal head (23); the upper end enclosure (11) is welded with the upper edge of the cylinder body (19), and the lower end enclosure (23) is welded with the lower edge of the cylinder body (19).
2. According to claim1The single-flow low-temperature spiral winding tube type heat exchanger with vacuum heat insulation is characterized in that: the central lines of the spiral coil (17) and the spiral coil (8) in the winding section of the heat exchanger tube bundle meet the pipeline curve expression
x ni 2+y ni 2=r ni 2
z ni =2πr ni k ni tg b ni
b ni ＝θ ni
l n =2πr ni [m+(n-1)d]/m
m＝m 1＝m A1+m B1
e n ＝m An /m Bn ＝j
d＝e n +1
β An 1 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))]×(-1) n
β Ani –β An i(-1) =((1+(-1) i )/2×2π/m+(1+(-1) i+1) /2×j×2π/m)×(-1) n =(j+1-(j-1))×(-1) i ×π/m×(-1) n
β Bni =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+j×2/m+(i-1)×(j+1)×2 /m]×(-1) n
t n =m+(n-1)/2
S＝nm+dn 2/2-dn/2
Wherein,x，y，zas a coordinate variable, the number of the coordinate variables,ris the radius of the base circle,kin order to raise the number of turns,dthe number of the tubes is increased for each layer,bin order to increase the helix angle,lis the length of the circumference of the base circle,mthe number of the first layer of the tubes is,nthe number of layers is the number of layers,iis the first layer in the layeriThe root canal is provided with a plurality of holes,αthe starting angle of the first spiral tube of the first layer,βis the starting angle of the angle,θthe size of the spiral angle is the size of the spiral angle,tthe number of the tubes in any layer is,Sthe number of the tubes of the whole heat exchanger,ethe ratio of the number of the two fluid pipes in the layer,Athe first stream of the fluid is the first stream of the fluid,Bis a second stream; initial angleβThe concrete expression is as follows:
……………………………………………………………………………………
e n ＝m An /m Bn ＝1；
the first layer of the first stream and the first pipeline meetβ A11＝-α；
The first layer of the first stream and the second pipeline meetβ A12＝-(α+2×2π/m)；
The first layer of the first flow and the third pipeline meet the requirementβ A13＝-(α+2×2π/m+2×2π/m)；
The first layer of the first stream and the fourth pipeline meetβ A14＝-(α+2×2π/m+2×2π/m+2×2π/m)；
First layer first streamhRoot canal satisfiesβ A h1＝-(α+2(h-1)×2π/m)；
First layer second streamARoot canal satisfiesβ B11＝-(α+2π/m)；
First layer second stream second rootPipeline satisfiesβ B12＝-(α+2π/m+2×2π/m)；
The third pipeline of the first layer, the second stream and the third stream meets the requirementβ B13＝-(α+2π/m+2×2π/m+2×2π/m)；
The fourth pipeline of the second strand of the first layer meets the requirement of the first layerβ B14＝-(α+2π/m+2×2π/m+2×2π/m+2×2π/m)；
…………
First layer second streamhRoot canal satisfiesβ B h1＝-(α+2π/m+2(h-1)×2π/m)；
The first pipeline of the first flow of the second layer meets the requirement of the first pipelineβ A21＝α+π/m；
The second layer of the first stream and the second pipeline meetβ A22＝α+π/m+2×2π/m；
The second layer of the first flow and the third pipe meetβ A23＝α+π/m+2×2π/m+2×2π/m；
Second layer first stream secondhRoot canal satisfiesβ A h2＝α+π/m+2(h-1)×2π/m；
The first pipeline of the second layer and the second strand meetsβ B21＝α+π/m+2π/m；
The second layer of the second flow and the second pipeline meetβ B22＝α+π/m+2π/m+2×2π/m；
The third pipe of the second layer, the second strand and the third flow meets the requirementsβ B23＝α+π/m+2π/m+2×2π/m+2×2π/m；
…………
Second layer second streamhRoot canal satisfiesβ B h2＝α+π/m+2π/m+2(h-1)×2π/m；
First, thenThe first flow of the layer and the first pipeline meet the following conditions:
β An 1 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))]×(-1) n
first, thenThe first layer flow and the second pipeline meet the following conditions:
β An 2 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d)) +2×2 /m]×(-1) n
first, thenThe third pipeline of the first flow of the layer meets the following conditions:
β An 3 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d)) +2×2π/m+2×2 /m]×(-1) n
…………
first, thenLayer first streamiThe root canal satisfies:
β Ani =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d)) +2(i-1)×2 /m]×(-1) n
first, thenThe first pipeline of the layer second flow meets the following conditions:
β Bn 1 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+2 /m]×(-1) n
first, thenLayer twoThe second pipeline satisfies:
β Bn 2 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d)) +2π/m+2×2 /m]×(-1) n
first, thenThe third pipeline of the layer second flow meets the following conditions:
β Bn 3 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d)) +2π/m+2×2π/m+2×2 /m]×(-1) n
first, thenLayer two streamiThe root canal satisfies:
β Bni =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d)) +2π/m+2(i-1)×2 /m]×(-1) n
……………………………………………………………………………………
e n ＝m An /m Bn ＝2；
the first layer of the first stream and the first pipeline meetβ A11＝-α；
The first layer of the first stream and the second pipeline meetβ A12＝-(α+2π/m)；
The first layer of the first flow and the third pipeline meet the requirementβ A13＝-(α+2π/m+2×2π/m)；
The first layer of the first stream and the fourth pipeline meetβ A14＝-(α+2π/m+2×2π/m+2π/m)；
…………
First layer first streamhRoot canal satisfies
β A h 1–β A h1(-1)＝–((1+(-1) h )/2×2π/m+(1+(-1) h+1) /2×2×2π/m)＝-(3-(-1) h )π/m
First layer second streamARoot canal satisfiesβ B11＝-(α+2×2π/m)；
The second pipeline of the first layer and the second stream meets the requirementβ B12＝-(α+2×2π/m+3×2π/m)；
The third pipeline of the first layer, the second stream and the third stream meets the requirementβ B13＝-(α+2×2π/m+3×2π/m+3×2π/m)；
The fourth pipeline of the second strand of the first layer meets the requirement of the first layerβ B14＝-(α+2×2π/m+3×2π/m+3×2π/m+3×2π/m)；
…………
First layer second streamhRoot canal satisfiesβ B h1＝-(α+2×2π/m+ (h-1)×3×2π/m)；
The first pipeline of the first flow of the second layer meets the requirement of the first pipelineβ A21＝α+π/m；
The second layer of the first stream and the second pipeline meetβ A22＝α+π/m+2π/m；
The second layer of the first flow and the third pipe meetβ A23＝α+π/m+2π/m+2×2π/m；
The fourth pipeline of the first flow of the second layer meets the requirement of the second layerβ A24＝α+π/m+2π/m+2×2π/m+2π/m；
…………
Second layer first stream secondhRoot canal satisfies
β A h 2–β A h2 (-1)＝(1+(-1) h )/2×2π/m+(1+(-1) h+1) /2×2×2π/m＝(3-(-1) h )π/m
Second layer second streamARoot canal satisfiesβ B21＝α+π/m+2×2π/m；
The second layer of the second flow and the second pipeline meetβ B22＝α+π/m+2×2π/m+3×2π/m；
The third pipe of the second layer, the second strand and the third flow meets the requirementsβ B23＝α+π/m+2×2π/m+3×2π/m+3×2π/m；
The fourth pipeline of the second layer of the second flow meets the requirementβ B24＝α+π/m+2×2π/m+3×2π/m+3×2π/m+3×2π/m；
Second layer second streamhRoot canal satisfiesβ B h2＝α+π/m+2×2π/m+ (h-1)×3×2π/m；
First, thenThe first flow of the layer and the first pipeline meet the following conditions:
β An 1 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))]×(-1) n
first, thenThe first layer flow and the second pipeline meet the following conditions:
β An 2 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d)) +2/m]×(-1) n
first, thenThe third pipeline of the first flow of the layer meets the following conditions:
β An 3 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d)) +2 /m+2×2 /m]×(-1) n
first, thenLayer first streamiThe root canal satisfies:
β Ani –β An i(-1) =(3-(-1) i )π/m×(-1) n
first, thenThe first pipeline of the layer second flow meets the following conditions:
β Bn 1 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+2×2/m]×(-1) n
first, thenThe second pipeline of the layer second flow meets the following conditions:
β Bn 2 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+2×2/m+3×2/m]×(-1) n
first, thenThe third pipeline of the layer second flow meets the following conditions:
β Bn 3 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d)) +2×2/m+3×2/m+3×2/m]×(-1) n
first, thenLayer two streamiThe root canal satisfies:
β Bni =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+2×2/m+(i-1)×3×2 /m]×(-1) n
……………………………………………………………………………………
e n ＝m An /m Bn ＝3；
first, thenLayer first streamiThe root canal satisfies:
β An 1 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))]×(-1) n
β An 2 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d)) +2/m]×(-1) n
β An 3 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d)) +2/m+2/m]×(-1) n
β Ani –β An i(-3) =2π/m×(-1) n ×(e n +1) (i＞3)
first, thenLayer two streamiThe root canal satisfies:
β Bni =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+3×2/m+(i-1)×4×2 /m]×(-1) n
……………………………………………………………………………………
e n ＝m An /m Bn ＝j；
first, thenLayer first streamiThe root canal satisfies:
β An 1 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))]×(-1) n
β An 2 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d)) +2/m]×(-1) n
β An 3 =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d)) +2/m+2/m]×(-1) n
…………
β Anj =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d)) +(j-1)×2/m]×(-1) n
β Ani –β An i j(-) =2π/m×(-1) n ×(j+1) (i＞j)
first, thenLayer two streamiThe root canal satisfies:
β Bni =[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+j×2/m+(i-1)×(j+1)×2 /m]×(-1) n 。
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