CN102455139B - 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
- Publication number
- CN102455139B CN102455139B CN201110315631.9A CN201110315631A CN102455139B CN 102455139 B CN102455139 B CN 102455139B CN 201110315631 A CN201110315631 A CN 201110315631A CN 102455139 B CN102455139 B CN 102455139B
- Authority
- CN
- China
- Prior art keywords
- plume
- meets
- pipeline
- layer
- ground floor
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Images
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 present invention relates to a kind of bifilar stream low-temperature spiral winding pipe type heat exchanger with vacuum insulation, be mainly used in low-temperature gas liquefaction separation field, comprise that the liquefaction of-161 ℃ of natural gas in low temperature ,-197 ℃ of air low temperature liquefaction separate ,-197 ℃ of low temperature liquid nitrogens wash that the gas low temperatures such as technique ,-70 ℃ of low-temp methanol washing process purify, low-temperature liquefaction separation technology field.
Background technology
Spiral winding tube type heat exchanger is a kind of heat-exchange apparatus, be mainly used in low temperature caloic exchange process, with its compact conformation, unit volume has larger heat transfer area, the thermal expansion of heat-transfer pipe can automatic compensating, easily realize and maximizing, can reduce the advantages such as equipment number of units and become the visual plant in low temperature purification, the liquefaction process such as natural gas liquefaction, cryogenic air separation, low-temperature rectisol.Because spiral winding tube type heat exchanger is applied to low temperature environment mostly, volume is larger, generally with the form of heat transfer tower, occur, can reach seven, 80 meters, general heat exchanger also two, 30 meters, mainly with bifilar stream, multiple flow heat exchange, be main greatly, internal pipeline is wound around complicated, not relevant fixing design standard, also ununified method for designing, along with the feature of technological process or physical parameter has bigger difference, brought obstacle therefore to spiral winding tube type heat exchanger standardisation process.Traditional spiral tube heat exchanger tube bank winding method is a lot, has a lot of shortcomings, can not guarantee to restrain interior tube pitch and interlamellar spacing is consistent in winding process everywhere, and heat-transfer effect is poor, there is no unified theoretical calculation method, for computer aided calculation process.In addition, because cryogenic heat exchanger and environment temperature have bigger difference, environment is as high temperature heat source, constant to cryogenic heat exchanger heat supply, heat exchanger surface is accepted solar radiation, cross-ventilation heat exchange, after the interior frictional heat of environment heat radiation or pipe, internal system fluid is especially accepting can to cause serious leakage thermal phenomenon after instantaneous high heat flux heat heating, cause biphase gas and liquid flow, produce a large amount of superheated vapors, superheated vapor causes system pressure acute variation, to the heat transfer process of heat exchanger, cause and have a strong impact on and bring very large safety problem, and the method that generally adopts the thermal insulation of external capillary thermal insulation of materials layer is difficult to meet heat exchanger and extraneous problem of carrying out heat exchange under worst cold case, in heat exchanger, cryogen still can produce fierce phase transition process.Therefore, bifilar stream spiral winding tube type heat exchanger will better be applied in low temperature field, also need at present to solve better following problem: the Mathematical Modeling that provides bifilar stream spiral winding tube type heat exchanger tube bank winding method, be conducive to be wound around the standardization of tube bank, for Heat transfer numerical simulation process is prepared; Vaccum thermal insulation technique is applied to spiral winding tube type heat exchanger, solves the adiabatic problem of large-scale spiral wrap-round tubular heat exchanger under worst cold case; Solve the tower structure of bifilar stream spiral tube heat exchanger and the location problem of each critical piece with vacuum insulation of entirety.
Summary of the invention
The present invention is a kind of bifilar stream low-temperature spiral winding pipe type heat exchanger with vacuum insulation, applies a kind of new helical bundle winding method, has provided theoretical winding equation; Adopt vacuum structure, vaccum thermal insulation technique is effectively applied to bifilar stream spiral winding tube type heat exchanger, the method that adopts processing and manufacturing step by step and detect, changes traditional vacuum structure and tubular heat exchanger tube bank combination difficulty, the shortcomings such as inconvenient is installed.
Technical solution of the present invention:
A kind of bifilar stream low-temperature spiral winding pipe type heat exchanger with vacuum insulation, comprise skirt 1, the first plume entrance sleeve 2, lower perforated plate 3, discharging tube 4, lower support ring 5, vacuum takes over 6, SMIS cylinder 7, first strand of spiral coil 8, upper support ring 9, shell side entrance sleeve 10, upper outside press seal head 11, the first plume discharge connection 12, the second plume discharge connection 13, press seal head 14 in upper, blast pipe 15, upper perforated plate 16, second strand of spiral coil 17, interior pressure shell body 18, external pressure shell 19, pearlife 20, shell side discharge connection 21, press seal head 22 in lower, lower outside press seal head 23, the second plume entrance sleeve 24, it is characterized in that: first burst of spiral coil 8 tube bank restrained around SMIS cylinder 7 and be wound around layer by layer with second strand of spiral coil 17, tube core after winding is installed in interior pressure shell body 18 by lower support ring 5 and upper support ring 9, tube bank upper outlet connects upper perforated plate 16, the lower outlet of tube bank connects lower perforated plate 3, SMIS cylinder 7 tops are connected with upper perforated plate 16 centers, and bottom is connected with lower perforated plate 3 centers, middle lower support ring 5 and the upper support ring 9 installed, between interior pressure shell body 18 and external pressure shell 19, be vacuum interlayer, top is shell side entrance sleeve 10 and blast pipe 15, and bottom is shell side discharge connection 21 and discharging tube 4, fills pearlife 20 in interlayer, and external pressure shell 19 bottoms are installed vacuum and taken over 6, between upper outside press seal head 11 and upper interior press seal head 14, it is vacuum interlayer, dividing plate is housed in the middle of press seal head 14 in upper, dividing plate is divided into two bobbin carriages by upper cover space, left pipe box connects the second plume discharge connection 13, right pipe box connects the first plume discharge connection 12, in upper, press seal head 14 bottoms and upper perforated plate 16 weld, upper perforated plate 16 lower limbs and the 18 top edge welding of interior pressure shell body, between lower outside press seal head 23 and lower interior press seal head 22, it is vacuum interlayer, dividing plate is housed in the middle of press seal head 22 in lower, dividing plate is divided into two bobbin carriages by lower interior press seal head 22 spaces, left pipe box connects the second plume entrance sleeve 24, right pipe box connects the first plume entrance sleeve 2, in lower, press seal head 22 top edges and lower perforated plate 3 weld, lower perforated plate 3 top edges and the 18 lower limb welding of interior pressure shell body, under lower outside press seal head 23, skirt 1 is installed, upper outside press seal head 11 and external pressure shell 19 top edge welding, lower outside press seal head 23 and external pressure shell 19 lower limb welding.
Heat exchanger tube is wound around the helical curve that in the interior first strand of spiral coil 8 of section and second strand of spiral coil 17, arbitrary single helix tube center line forms and meets following curve representation formula:
x
ni 2+y
ni 2=r
ni 2
z
ni=2πr
nik
nitgb
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
An1=[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, z is coordinate variable, r is base radius, and k is the rising number of turns, and d is every layer increases pipe radical, b is elevating screw angle, l is basic circle girth, and m is ground floor pipe radical, and n is the number of plies, i is i root pipe in layer, j is that in n layer, two strands of spiral coil pipelines are counted ratio variable, and e is that in layer, two fluid streams pipelines are counted ratio independent variable, and α is first helix tube initial angle of ground floor, β is initial angle, θ is helical angle size, and t is arbitrary layer of pipe radical, and S is whole Tube Sheet of Heat Exchanger radical, A is the first fluid streams, and B is the second fluid streams; Initial angle β is specifically expressed as follows:
e
n＝1，2，3……j……；
……………………………………………………………………………………
e
n＝m
An/m
Bn＝j；
j＝1；
First pipeline of ground floor the first plume meets β
a11=-α;
Second pipeline of ground floor the first plume meets β
a12=-(α+2 × 2 π/m);
The 3rd pipeline of ground floor the first plume meets β
a13=-(α+2 × 2 π/m+2 × 2 π/m);
The 4th pipeline of ground floor the first plume meets β
a14π/m+2 × 2, π/m+2 × 2 ,=-(α+2 × 2 π/m);
Ground floor the first plume h root pipeline meets β
a1h=-(α+2 (h-1) × 2 π/m);
First pipeline of ground floor the second plume meets β
b11=-(α+2 π/m);
Second pipeline of ground floor the second plume meets β
b12=-(α+2 π/m+2 × 2 π/m);
The 3rd pipeline of ground floor the second plume meets β
b13π/m+2 × 2, π/m+2 × 2 ,=-(α+2 π/m);
The 4th pipeline of ground floor the second plume meets β
b14π/m+2 × 2, π/m+2 × 2 ,=-(α+2 π/m+2 × 2 π/m);
…………
Ground floor the second plume h root pipeline meets β
b1h=-(α+2 π/m+2 (h-1) × 2 π/m);
First pipeline of the second layer the first plume meets β
a21=α+π/m;
Second pipeline of the second layer the first plume meets β
a22=α+π/m+2 × 2 π/m;
The 3rd pipeline of the second layer the first plume meets β
a23π/m+2 × 2 ,=α+π/m+2 × 2 π/m;
The second layer the first plume h root pipeline meets β
a2h=α+π/m+2 (h-1) × 2 π/m;
First pipeline of the second layer the second plume meets β
b21=α+π/m+2 π/m;
Second pipeline of the second layer the second plume meets β
b22=α+π/m+2 π/m+2 × 2 π/m;
The 3rd pipeline of the second layer the second plume meets β
b23=α+π/m+2 π/m+2 × 2 π/m+2 × 2 π/m;
…………
The second layer the second plume h root pipeline meets β
b2h=α+π/m+2 π/m+2 (h-1) × 2 π/m;
First pipeline of n layer the first plume meets:
β
An1=[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))]×(-1)
n
Second pipeline of n layer the first plume meets:
β
An2=[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+2×2/m]×(-1)
n
The 3rd pipeline of n layer the first plume meets:
β
An3=[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+2×2π/m+2×2/m]×(-1)
n
…………
N layer the first plume i root pipeline meets:
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 pipeline of n layer the second plume meets:
β
Bn1=[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+2/m]×(-1)
n
Second pipeline of n layer the second plume meets:
β
Bn2=[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+2π/m+2×2/m]×(-1)
n
The 3rd pipeline of n layer the second plume meets:
β
Bn3=[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
N layer the second plume i root pipeline meets:
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＝j；
j＝2；
First pipeline of ground floor the first plume meets β
a11=-α;
Second pipeline of ground floor the first plume meets β
a12=-(α+2 π/m);
The 3rd pipeline of ground floor the first plume meets β
a13=-(α+2 π/m+2 × 2 π/m);
The 4th pipeline of ground floor the first plume meets β
a14π/m+2 × 2 ,=-(α+2 π/m+2 π/m);
…………
Ground floor the first plume h root pipeline meets
β
A1h–β
A1(h-1)＝–((1+(-1)
h)/2×2π/m+(1+(-1)
h+1)/2×2×2π/m)＝-(3-(-1)
h)π/m
First pipeline of ground floor the second plume meets β
b11=-(α+2 × 2 π/m);
Second pipeline of ground floor the second plume meets β
b12=-(α+2 × 2 π/m+3 × 2 π/m);
The 3rd pipeline of ground floor the second plume meets β
b13π/m+3 × 2, π/m+3 × 2 ,=-(α+2 × 2 π/m);
The 4th pipeline of ground floor the second plume meets β
b14π/m+3 × 2, π/m+3 × 2 ,=-(α+2 × 2 π/m+3 × 2 π/m);
…………
Ground floor the second plume h root pipeline meets β
b1h=-(α+2 × 2 π/m+ (h-1) × 3 × 2 π/m);
First pipeline of the second layer the first plume meets β
a21=α+π/m;
Second pipeline of the second layer the first plume meets β
a22=α+π/m+2 π/m;
The 3rd pipeline of the second layer the first plume meets β
a23=α+π/m+2 π/m+2 × 2 π/m;
The 4th pipeline of the second layer the first plume meets β
a24=α+π/m+2 π/m+2 × 2 π/m+2 π/m;
…………
The second layer the first plume h root pipeline meets
β
A2h–β
A2(h-1)＝(1+(-1)
h)/2×2π/m+(1+(-1)
h+1)/2×2×2π/m＝(3-(-1)
h)π/m
First pipeline of the second layer the second plume meets β
b21=α+π/m+2 × 2 π/m;
Second pipeline of the second layer the second plume meets β
b22π/m+3 × 2 ,=α+π/m+2 × 2 π/m;
The 3rd pipeline of the second layer the second plume meets β
b23π/m+3 × 2 ,=α+π/m+2 × 2 π/m+3 × 2 π/m;
The 4th pipeline of the second layer the second plume meets β
b24π/m+3 × 2, π/m+3 × 2, π/m+3 × 2 ,=α+π/m+2 × 2 π/m;
The second layer the second plume h root pipeline meets β
b2h=α+π/m+2 × 2 π/m+ (h-1) × 3 × 2 π/m;
First pipeline of n layer the first plume meets:
β
An1=[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))]×(-1)
n
Second pipeline of n layer the first plume meets:
β
An2=[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+2/m]×(-1)
n
The 3rd pipeline of n layer the first plume meets:
β
An3=[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+2/m+2×2/m]×(-1)
n
N layer the first plume i root pipeline meets:
β
Ani–β
An(i-1)=(3-(-1)
i)π/m×(-1)
n
First pipeline of n layer the second plume meets:
β
Bn1=[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+2×2/m]×(-1)
n
Second pipeline of n layer the second plume meets:
β
Bn2=[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+2×2/m+3×2/m]×(-1)
n
The 3rd pipeline of n layer the second plume meets:
β
Bn3=[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
N layer the second plume i root pipeline meets:
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＝j；
j＝3；
N layer the first plume i root pipeline meets:
β
An1=[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))]×(-1)
n
β
An2=[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+2/m]×(-1)
n
β
An3=[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)
N layer the second plume i root pipeline meets:
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；
N layer the first plume i root pipeline meets:
β
An1=[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))]×(-1)
n
β
An2=[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+2/m]×(-1)
n
β
An3=[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)
N layer the second plume i root pipeline meets:
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 Principle Problems that scheme is related:
With the bifilar stream low-temperature spiral winding pipe type heat exchanger of vacuum insulation, being mainly used in low-temperature gas liquefaction separates and gas purification field, as technical fields such as gas low temperature purification, low-temperature liquefaction separation such as natural gas in low temperature liquefaction, air low temperature liquefaction separation, low-temperature rectisols, so there is low-temperature heat exchange characteristic, multiple gases mixed heat transfer, often there is multiphase flow, heat transfer temperature difference is large, in heat transfer process, having phase transformation, is calculating in current cryogenic high pressure heat transmission equipment, design, heat exchanger that manufacture difficulty is larger.The present invention proposes a kind of bifilar stream low-temperature spiral winding pipe type heat exchanger that is mainly used in low temperature environment with vacuum heat-insulating layer, and provided respective tube wrapping around Mathematical Modeling, the winding method of spiral winding tube type heat exchanger can be applied to process of mathematical modeling, and built Mathematical Modeling and corresponding three-dimensional physical model are applied to Field Flow Numerical Simulation process, obtain flow field parameter distributed model and the relevant heat transfer model of bifilar stream spiral winding tube type heat exchanger, with this, design whole spiral winding tube type heat exchanger, make bifilar stream spiral winding tube type heat exchanger have a definite method for designing, application vacuum and low temperature adiabatic method, it is the effective method that solves at present that Environmental Heat Source in low-temperature heat exchange process internally conducts heat, can effectively stop the diabatic process of Environmental Heat Source take heat conduction, heat convection, heat radiation as main heat transfer path, it is more conventional method in current low temperature field, more traditional capillary materials thermal insulation, performance has improved a nearly magnitude.In order to adapt to spiral winding heat exchange of heat pipe vacuum insulation needs, should vacuum insulation, facilitate again processing and manufacturing process, the present invention to adopt first processing and manufacturing tube core, then assemble inner casing simultaneously, finally manufacture and install vacuum casting and adopt overall adiabatic form, be that cylindrical shell 19 forms unified vacuum castings with upper cover 11, low head 23, integral weld forming, realizes the vacuum insulation process of overall heat exchange device, make processing and manufacturing convenient, corresponding detection can be processed and carry out to each vacuum component step by step.Tube bank 17, tube bank 8 are installed and are manufactured, also can detect separately, and detect after qualified and be installed in inner casing 18, more above low head of docking.The object of adding pearlife 20 in vacuum layer is the Radiant exothermicities that reduce in vacuum layer.
Technical characterstic of the present invention:
A kind of global design model and model concrete structure of the bifilar stream low-temperature spiral winding pipe type heat exchanger with vacuum insulation have been provided; The Mathematical Modeling that a kind of bifilar stream wrap-round tubular heat exchanger tube bank is wound around has been proposed, can apply this Mathematical Modeling the winding method of bifilar stream spiral winding tube type heat exchanger is applied to process of mathematical modeling, and built Mathematical Modeling and corresponding three-dimensional physical model are applied to Field Flow Numerical Simulation process, can obtain flow field parameter distributed model and the relevant heat transfer model of bifilar stream spiral winding tube type heat exchanger, with this, design whole bifilar stream spiral winding tube type heat exchanger, make bifilar stream spiral winding tube type heat exchanger have a definite method for designing; Monoblock type vacuum structure is applied to bifilar stream spiral winding tube type heat exchanger, i.e. the internals such as first processing and manufacturing tube core, then assemble inner casing and detect, detect qualified after, finally manufacture and install vacuum casting, realize overall vacuum adiabatic process of heat exchanger.Each vacuum component can substep processing and manufacturing detecting accordingly, makes spiral winding tube type heat exchanger processing, manufacture process convenient, has overcome the former vaccum thermal insulation technique shortcoming that can not combine with large-scale wrap-round tubular heat exchanger.
Accompanying drawing explanation
Figure 1 shows that a kind of critical piece and installation site relation of the bifilar stream low-temperature spiral winding pipe type heat exchanger with vacuum insulation.
The specific embodiment
The present invention is wound around Mathematical Modeling according to the tube bank having established, application Heat transfer numerical simulation method, first determine the theoretical winding method of tube bank in bifilar stream spiral winding tube type heat exchanger, and the relevant parameter such as the tube pitch in tube bank winding process and interlamellar spacing, application heat transfer and Field Flow Numerical Simulation method are determined the inside optimal arrangement structure of wrap-round tubular heat exchanger, and then definite helical angle, tube pitch, the important parameters such as interlamellar spacing, finally, according to known parameters, determine complete arrangement mode, can obtain definite tube bank design, carry out the processing and manufacturing process of Related product.The helical bundle processing 8, helical bundle 17 are wound in the upper annular on central tube 7 between bracing ring 9 and lower support circle 5 by Mathematical Modeling of the present invention, and tube bank two ends connect tube sheet fixing again; Upper perforated plate 16 and lower perforated plate 3 are welded between upper cover 14, low head 22, cylindrical shell 18; By lower tube box left side connecting tubes 24, right side connecting tubes 2, upper tube box left side connecting tubes 13, right side connecting tubes 12; Adapter 2 is communicated with tube bank 8, adapter 12, takes over 24 and is communicated with tube bank 17, adapter 13.During adverse current, the fluid that flows into bottom right bobbin carriage from lower linking tube 2 flows into winding tube bank 8 each arms after lower perforated plate 3, it is interior mobile that fluid is wound around tube bank 8 in layering, and with from taking over 10 fluids that enter shell side, in housing 18, carry out complicated exchange heat, after exchange, through upper perforated plate 16, along upper right bobbin carriage through taking over 12 outflows; The fluid that flows into bottom left bobbin carriage from lower linking tube 24 flows into winding tube bank 17 each arms after lower perforated plate 3, it is interior mobile that fluid is wound around tube bank 17 in layering, and with from taking over 10 fluids that enter shell side, in housing 18, carry out complicated exchange heat, after exchange, through upper perforated plate 16, along upper left bobbin carriage through taking over 13 outflows; Shell-side fluid flows out along lower linking tube 23.And while flowing, the fluid that flows into upper right bobbin carriage from upper connecting tube 12 flows into winding tube bank 8 each arms after upper perforated plate 16, it is interior mobile that fluid is wound around tube bank 8 in layering, and with from taking over 10 fluids that enter shell side, in housing 18, carry out complicated exchange heat, after exchange, through lower perforated plate 3, along bottom right bobbin carriage through taking over 2 outflows; The fluid that flows into upper left bobbin carriage from upper connecting tube 13 flows into winding tube bank 17 each arms after upper perforated plate 16, it is interior mobile that fluid is wound around tube bank 17 in layering, and with from taking over 10 fluids that enter shell side, in housing 18, carry out complicated exchange heat, after exchange, through lower perforated plate 3, along bottom left bobbin carriage through taking over 24 outflows; Shell-side fluid flows out along lower linking tube 21.
Claims (2)
1. the bifilar stream low-temperature spiral winding pipe type heat exchanger with vacuum insulation, comprises skirt (1), the first plume entrance sleeve (2), lower perforated plate (3), discharging tube (4), lower support ring (5), vacuum is taken over (6), SMIS cylinder (7), first strand of spiral coil (8), upper support ring (9), shell side entrance sleeve (10), upper outside press seal head (11), the first plume discharge connection (12), the second plume discharge connection (13), press seal head (14) in upper, blast pipe (15), upper perforated plate (16), second strand of spiral coil (17), interior pressure shell body (18), external pressure shell (19), pearlife (20), shell side discharge connection (21), press seal head (22) in lower, lower outside press seal head (23), the second plume entrance sleeve (24), it is characterized in that: first strand of spiral coil (8) tube bank is wound around around SMIS cylinder (7) layer by layer with second strand of spiral coil (17) tube bank, tube core after winding is installed in interior pressure shell body (18) by lower support ring (5) and upper support ring (9), tube bank upper outlet connects upper perforated plate (16), and the lower outlet of tube bank connects lower perforated plate (3), SMIS cylinder (7) top is connected with upper perforated plate (16) center, and bottom is connected with lower perforated plate (3) center, middle lower support ring (5) and the upper support ring (9) installed, between interior pressure shell body (18) and external pressure shell (19), it is vacuum interlayer, top is shell side entrance sleeve (10) and blast pipe (15), bottom is shell side discharge connection (21) and discharging tube (4), in interlayer, fill pearlife (20), external pressure shell (19) bottom is installed vacuum and is taken over (6), between upper outside press seal head (11) and upper interior press seal head (14), it is vacuum interlayer, dividing plate is housed in the middle of press seal head (14) in upper, dividing plate is divided into two bobbin carriages by upper cover space, left pipe box connects the second plume discharge connection (13), right pipe box connects the first plume discharge connection (12), press seal head (14) bottom and upper perforated plate (16) welding in upper, upper perforated plate (16) lower limb and the welding of interior pressure shell body (18) top edge, between lower outside press seal head (23) and lower interior press seal head (22), it is vacuum interlayer, dividing plate is housed in the middle of press seal head (22) in lower, dividing plate is divided into two bobbin carriages by lower interior press seal head (22) space, left pipe box connects the second plume entrance sleeve (24), right pipe box connects the first plume entrance sleeve (2), press seal head (22) top edge and lower perforated plate (3) welding in lower, lower perforated plate (3) top edge and the welding of interior pressure shell body (18) lower limb, skirt (1) is installed under lower outside press seal head (23), upper outside press seal head (11) and the welding of external pressure shell (19) top edge, lower outside press seal head (23) and the welding of external pressure shell (19) lower limb.
2. a kind of bifilar stream low-temperature spiral winding pipe type heat exchanger with vacuum insulation according to claim 1, is characterized in that: heat exchanger tube is wound around the helical curve that in the interior second strand of spiral coil (17) of section and first strand of spiral coil (8), arbitrary single helix tube center line forms and meets following curve representation formula:
x
ni 2+y
ni 2=r
ni 2
z
ni=2πr
nik
nitgb
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
An1=[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, z is coordinate variable, r is base radius, and k is the rising number of turns, and d is every layer increases pipe radical, b is elevating screw angle, l is basic circle girth, and m is ground floor pipe radical, and n is the number of plies, i is i root pipe in layer, j is that in n layer, two strands of spiral coil pipelines are counted ratio variable, and e is that in layer, two fluid streams pipelines are counted ratio independent variable, and α is first helix tube initial angle of ground floor, β is initial angle, θ is helical angle size, and t is arbitrary layer of pipe radical, and S is whole Tube Sheet of Heat Exchanger radical, A is the first fluid streams, and B is the second fluid streams; Initial angle β is specifically expressed as follows:
e
n＝1，2，3……j……；
……………………………………………………………………………………
e
n＝m
An/m
Bn＝j；
j＝1；
First pipeline of ground floor the first plume meets β
a11=-α;
Second pipeline of ground floor the first plume meets β
a12=-(α+2 × 2 π/m);
The 3rd pipeline of ground floor the first plume meets β
a13=-(α+2 × 2 π/m+2 × 2 π/m);
The 4th pipeline of ground floor the first plume meets β
a14π/m+2 × 2, π/m+2 × 2 ,=-(α+2 × 2 π/m);
Ground floor the first plume h root pipeline meets β
a1h=-(α+2 (h-1) × 2 π/m);
First pipeline of ground floor the second plume meets β
b11=-(α+2 π/m);
Second pipeline of ground floor the second plume meets β
b12=-(α+2 π/m+2 × 2 π/m);
The 3rd pipeline of ground floor the second plume meets β
b13π/m+2 × 2, π/m+2 × 2 ,=-(α+2 π/m);
The 4th pipeline of ground floor the second plume meets β
b14π/m+2 × 2, π/m+2 × 2 ,=-(α+2 π/m+2 × 2 π/m);
…………
Ground floor the second plume h root pipeline meets β
b1h=-(α+2 π/m+2 (h-1) × 2 π/m);
First pipeline of the second layer the first plume meets β
a21=α+π/m;
Second pipeline of the second layer the first plume meets β
a22=α+π/m+2 × 2 π/m;
The 3rd pipeline of the second layer the first plume meets β
a23π/m+2 × 2 ,=α+π/m+2 × 2 π/m;
The second layer the first plume h root pipeline meets β
a2h=α+π/m+2 (h-1) × 2 π/m;
First pipeline of the second layer the second plume meets β
b21=α+π/m+2 π/m;
Second pipeline of the second layer the second plume meets β
b22=α+π/m+2 π/m+2 × 2 π/m;
The 3rd pipeline of the second layer the second plume meets β
b23=α+π/m+2 π/m+2 × 2 π/m+2 × 2 π/m;
…………
The second layer the second plume h root pipeline meets β
b2h=α+π/m+2 π/m+2 (h-1) × 2 π/m;
First pipeline of n layer the first plume meets:
β
An1=[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))]×(-1)
n
Second pipeline of n layer the first plume meets:
β
An2=[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+2×2/m]×(-1)
n
The 3rd pipeline of n layer the first plume meets:
β
An3=[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+2×2π/m+2×2/m]×(-1)
n
…………
N layer the first plume i root pipeline meets:
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 pipeline of n layer the second plume meets:
β
Bn1=[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+2/m]×(-1)
n
Second pipeline of n layer the second plume meets:
β
Bn2=[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+2π/m+2×2/m]×(-1)
n
The 3rd pipeline of n layer the second plume meets:
β
Bn3=[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
N layer the second plume i root pipeline meets:
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＝j；
j＝2；
First pipeline of ground floor the first plume meets β
a11=-α;
Second pipeline of ground floor the first plume meets β
a12=-(α+2 π/m);
The 3rd pipeline of ground floor the first plume meets β
a13=-(α+2 π/m+2 × 2 π/m);
The 4th pipeline of ground floor the first plume meets β
a14π/m+2 × 2 ,=-(α+2 π/m+2 π/m);
…………
Ground floor the first plume h root pipeline meets
β
A1h–β
A1(h-1)＝–((1+(-1)
h)/2×2π/m+(1+(-1)
h+1)/2×2×2π/m)＝-(3-(-1)
h)π/m
First pipeline of ground floor the second plume meets β
b11=-(α+2 × 2 π/m);
Second pipeline of ground floor the second plume meets β
b12=-(α+2 × 2 π/m+3 × 2 π/m);
The 3rd pipeline of ground floor the second plume meets β
b13π/m+3 × 2, π/m+3 × 2 ,=-(α+2 × 2 π/m);
The 4th pipeline of ground floor the second plume meets β
b14π/m+3 × 2, π/m+3 × 2 ,=-(α+2 × 2 π/m+3 × 2 π/m);
…………
Ground floor the second plume h root pipeline meets β
b1h=-(α+2 × 2 π/m+ (h-1) × 3 × 2 π/m);
First pipeline of the second layer the first plume meets β
a21=α+π/m;
Second pipeline of the second layer the first plume meets β
a22=α+π/m+2 π/m;
The 3rd pipeline of the second layer the first plume meets β
a23=α+π/m+2 π/m+2 × 2 π/m;
The 4th pipeline of the second layer the first plume meets β
a24=α+π/m+2 π/m+2 × 2 π/m+2 π/m;
…………
The second layer the first plume h root pipeline meets
β
A2h–β
A2(h-1)＝(1+(-1)
h)/2×2π/m+(1+(-1)
h+1)/2×2×2π/m＝(3-(-1)
h)π/m
First pipeline of the second layer the second plume meets β
b21=α+π/m+2 × 2 π/m;
Second pipeline of the second layer the second plume meets β
b22π/m+3 × 2 ,=α+π/m+2 × 2 π/m;
The 3rd pipeline of the second layer the second plume meets β
b23π/m+3 × 2 ,=α+π/m+2 × 2 π/m+3 × 2 π/m;
The 4th pipeline of the second layer the second plume meets β
b24π/m+3 × 2, π/m+3 × 2, π/m+3 × 2 ,=α+π/m+2 × 2 π/m;
The second layer the second plume h root pipeline meets β
b2h=α+π/m+2 × 2 π/m+ (h-1) × 3 × 2 π/m;
First pipeline of n layer the first plume meets:
β
An1=[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))]×(-1)
n
Second pipeline of n layer the first plume meets:
β
An2=[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+2/m]×(-1)
n
The 3rd pipeline of n layer the first plume meets:
β
An3=[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+2/m+2×2/m]×(-1)
n
N layer the first plume i root pipeline meets:
β
Ani–β
An(i-1)=(3-(-1)
i)π/m×(-1)
n
First pipeline of n layer the second plume meets:
β
Bn1=[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+2×2/m]×(-1)
n
Second pipeline of n layer the second plume meets:
β
Bn2=[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+2×2/m+3×2/m]×(-1)
n
The 3rd pipeline of n layer the second plume meets:
β
Bn3=[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
N layer the second plume i root pipeline meets:
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＝j；
j＝3；
N layer the first plume i root pipeline meets:
β
An1=[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))]×(-1)
n
β
An2=[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+2/m]×(-1)
n
β
An3=[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)
N layer the second plume i root pipeline meets:
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；
N layer the first plume i root pipeline meets:
β
An1=[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))]×(-1)
n
β
An2=[α+π(1/m+1/(m+d)+1/(m+2d)+…+1/(m+(n-2)d))+2/m]×(-1)
n
β
An3=[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)
N layer the second plume i root pipeline meets:
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?。
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110315631.9A CN102455139B (en) | 2011-10-18 | 2011-10-18 | Double-strand-flow low-temperature spiral winding pipe type heat exchanger with vacuum heat insulation function |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110315631.9A CN102455139B (en) | 2011-10-18 | 2011-10-18 | Double-strand-flow low-temperature spiral winding pipe type heat exchanger with vacuum heat insulation function |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102455139A CN102455139A (en) | 2012-05-16 |
| CN102455139B true CN102455139B (en) | 2014-04-16 |
Family
ID=46038575
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201110315631.9A Expired - Fee Related CN102455139B (en) | 2011-10-18 | 2011-10-18 | Double-strand-flow low-temperature spiral winding pipe type heat exchanger with vacuum heat insulation function |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN102455139B (en) |
Families Citing this family (21)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102980199A (en) * | 2012-11-14 | 2013-03-20 | 辽宁省电力有限公司电力科学研究院 | Special system for interface of medium temperature flue gas pipeline and heating surface in middle storage type bituminous coal boiler |
| CN102999707A (en) * | 2012-12-07 | 2013-03-27 | 张周卫 | Low-temperature methanol-methanol winding tubular heat exchanger design and calculation method |
| CN103017573B (en) * | 2012-12-25 | 2015-06-17 | 张周卫 | Low-temperature spiral wound heat exchanger for non-converted gas cooler |
| CN103033074B (en) * | 2013-01-04 | 2015-07-15 | 张周卫 | Low-temperature wound-tube heat exchanger used for converted gas cooler |
| CN103063057B (en) * | 2013-01-30 | 2015-11-25 | 张周卫 | Feed gas chiller three plume low temperature wrap-round tubular heat exchangers |
| CN103148732A (en) * | 2013-03-26 | 2013-06-12 | 牛玉振 | Gas/liquid-phase fluid uniform distribution device of high-pressure wound-tube type heat exchanger |
| CN103438667B (en) * | 2013-08-16 | 2015-08-12 | 张周卫 | Low temperature liquid nitrogen three grades of backheat multiple flows are wound around pipe type heat transfer equipment |
| CN103438736B (en) * | 2013-08-19 | 2015-05-27 | 张周卫 | Two-stage back heating multi-strand winding pipe type heat exchange device for low-temperature liquid nitrogen |
| CN103438666B (en) * | 2013-08-21 | 2015-05-20 | 张周卫 | Multi-strand winding pipe type main back heating and heat exchange device for low-temperature liquid nitrogen |
| CN103438733B (en) * | 2013-08-31 | 2015-07-01 | 张周卫 | Primary heat-regeneration multi-flow heat exchange device for low-temperature liquid nitrogen |
| CN103486877B (en) * | 2013-09-23 | 2015-11-04 | 上海交通大学 | The micro-channel flat coiled heat exchanger of variable-flow-path |
| DE102014103691A1 (en) * | 2014-03-18 | 2015-09-24 | Basf Se | Heat exchanger, reactor assembly comprising this heat exchanger and method for controlling the temperature of a reactor |
| CN103822505A (en) * | 2014-03-19 | 2014-05-28 | 明圣化工机械（南通）有限公司 | Heat exchanger |
| CN104359335A (en) * | 2014-11-05 | 2015-02-18 | 镇海石化建安工程有限公司 | Novel multi-strand flow heat exchanger |
| CN105841517A (en) * | 2015-11-18 | 2016-08-10 | 瞿云亮 | Multipurpose temperature difference conversion device |
| CN106437874A (en) * | 2016-08-30 | 2017-02-22 | 南京工业大学 | Novel liquid air energy storage system using phase change energy storage |
| CN106152514A (en) * | 2016-09-27 | 2016-11-23 | 郑州大学 | Novel bifilar stream central flame flame vacuum boiler |
| CN107504840A (en) * | 2017-09-18 | 2017-12-22 | 湖北迪峰船舶技术有限公司 | A kind of LNG high pressures wound tube heat exchanger peculiar to vessel |
| CN108709436A (en) * | 2018-05-08 | 2018-10-26 | 中国科学院近代物理研究所 | A kind of low temperature, negative pressure heat exchanger |
| CN111426215B (en) * | 2020-05-21 | 2021-08-27 | 山东九泽换热系统有限公司 | High-efficient spiral winding tubular heat exchanger |
| CN112066763B (en) * | 2020-09-03 | 2022-02-15 | 无锡市申京化工设备有限公司 | Double-channel high-heat-conduction type tubular heat exchanger |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4296713A (en) * | 1979-02-07 | 1981-10-27 | General Atomic Company | Vapor generator |
| CN2128728Y (en) * | 1992-07-10 | 1993-03-24 | 苏州市振兴动力设备辅件厂 | Efficient cylindrical spiral conduit flow cooling unit |
| CN2190276Y (en) * | 1994-04-19 | 1995-02-22 | 刘少怀 | Spiral vibrating heat-exchanger |
| CN201373690Y (en) * | 2008-12-18 | 2009-12-30 | 西安市三桥机电设备有限公司 | Tube-shell helical flow heat exchanger |
-
2011
- 2011-10-18 CN CN201110315631.9A patent/CN102455139B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4296713A (en) * | 1979-02-07 | 1981-10-27 | General Atomic Company | Vapor generator |
| CN2128728Y (en) * | 1992-07-10 | 1993-03-24 | 苏州市振兴动力设备辅件厂 | Efficient cylindrical spiral conduit flow cooling unit |
| CN2190276Y (en) * | 1994-04-19 | 1995-02-22 | 刘少怀 | Spiral vibrating heat-exchanger |
| CN201373690Y (en) * | 2008-12-18 | 2009-12-30 | 西安市三桥机电设备有限公司 | Tube-shell helical flow heat exchanger |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102455139A (en) | 2012-05-16 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102455139B (en) | Double-strand-flow low-temperature spiral winding pipe type heat exchanger with vacuum heat insulation function | |
| CN102564167B (en) | Single-flow low-temperature spiral winding tube type heat exchanger with vacuum heat-insulation effect | |
| CN102954726B (en) | Composite phase-change heat storage device | |
| CN102810128A (en) | Design calculation method for single-strand spiral wound heat exchanger | |
| CN103822510B (en) | Muitishell tubular heat exchanger | |
| CN105289440A (en) | Hydrogen storage reactor and system with fin and spiral coil type heat exchanger coupled | |
| CN102538388B (en) | Three-stream spiral wound type heat exchange equipment for secondary refrigeration and low-temperature liquefaction of LNG (liquefied natural gas) | |
| CN107664450A (en) | A kind of electric heating coil heat pipe | |
| CN103063057B (en) | Feed gas chiller three plume low temperature wrap-round tubular heat exchangers | |
| CN102980422B (en) | Wound tube type heat exchanger for low-temperature circulating methanol coolers | |
| CN103033074B (en) | Low-temperature wound-tube heat exchanger used for converted gas cooler | |
| CN204043451U (en) | A kind of chuck material heat exchanger | |
| CN103486877B (en) | The micro-channel flat coiled heat exchanger of variable-flow-path | |
| CN201653249U (en) | Dividing wall spiral titanium tube heat exchanger | |
| CN105444591A (en) | Heat exchange jetting device eliminating heat stratification in low-temperature propellant storage box | |
| CN203869557U (en) | Liquid-nitrogen evaporator for X-ray single-crystal diffractometer | |
| CN104368282B (en) | The water bed reactor of beam tube type | |
| CN103983129B (en) | A kind of liquid nitrogen evaporator for X-ray single crystal diffractometer | |
| CN102999707A (en) | Low-temperature methanol-methanol winding tubular heat exchanger design and calculation method | |
| CN103411451A (en) | Rectification type tube-shell type heat exchanger | |
| CN106369272A (en) | Efficient heat exchange tube for LNG vaporizer and open rack vaporizer | |
| CN203550682U (en) | Multi-medium tube-and-shell heat exchanger | |
| CN202709814U (en) | Water-cooled heat exchanger for compressive refrigeration equipment | |
| CN203274537U (en) | Novel uranium hexafluoride condenser | |
| CN113148948A (en) | Magnesium hydride solid hydrogen energy storage system and method for improving hydrogen storage and release efficiency |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20140416 Termination date: 20141018 |
|
| EXPY | Termination of patent right or utility model |