CN109443061A - A kind of upper tightly lower sparse double helix finned heat exchanger - Google Patents
A kind of upper tightly lower sparse double helix finned heat exchanger Download PDFInfo
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- CN109443061A CN109443061A CN201811166613.7A CN201811166613A CN109443061A CN 109443061 A CN109443061 A CN 109443061A CN 201811166613 A CN201811166613 A CN 201811166613A CN 109443061 A CN109443061 A CN 109443061A
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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
- F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
- F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
- F28D15/04—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes with tubes having a capillary structure
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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
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/34—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely
- F28F1/36—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely the means being helically wound fins or wire spirals
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- Mechanical Engineering (AREA)
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- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
A kind of upper tightly lower sparse double helix finned heat exchanger, the spiral capillary finned tube being wrapped in including mandrel and along axial screw on mandrel, sealing shell is set with outside spiral capillary finned tube, there are the spaces for forming evaporation cavity for the mandrel lower end and shell, the spiral capillary finned tube includes the helical fin of capillary and winding on the capillary, the upper end of the sealing shell offers capillary inlet and heat exchanger exit respectively, and capillary outlet is connected with evaporation cavity；The spiral capillary finned tube is divided into upper end condensed section capillary finned tube and sparse section of lower end capillary finned tube according to helical fin spacing size.Hot fluid enters in capillary finned tube from air inlet, after flowing of from top to bottom spinning in pipe cools down, the thermic load taken away in evaporation cavity becomes cryogen, from bottom to top helically flow regime in the circular passage formed between mandrel, capillary finned tube and shell consequently as cold fluid is discharged after the hot fluid in cooling capillary finned tube through discharge pipe.
Description
Technical field
The present invention relates to a kind of heat exchanger in fields such as infrared device, cryotronics, central air-conditioning, it is specifically a kind of on
Close lower thin double helix finned heat exchanger.
Background technique
Realize that refrigeration is refrigeration & cryogenic engineering field using the throttling refrigeration effect and constant entropy expansion refrigeration effect of gas
The two ways being most widely used, and throttling refrigeration has the advantages that structure is simple, can easily be accommodated, and is commonly applied to small-sized low temperature
Refrigerator.Such as: miniature J-T throttling refrigerator because have small in size, light-weight, cooling velocity it is fast, without mechanical moving element and anti-
The advantages that electromagnetic interference and be widely used in infrared guidance system.Regenerator in micro-miniature refrigerator mainly uses double helix
Adverse current finned heat exchanger has hot and cold two kinds of fluids in double-helix heat exchanger, and hot fluid flows in stainless steel capillary, cold flow
Body flows between Dewar bottle and mandrel, and cold and hot fluid carries out heat exchange by fin.On the one hand fin structure increases biography
Heat area, so that heat exchange amount increases, to reduceLoss；But then, heat exchanger flow resistance increased, and increase
?Loss, therefore the rational design heat exchanging device of fin structureLoss appraisal is most important.Liu et al. people [Yingwen
Liu,Liu Liu,Lili Liang,Xin Liu,Jiapeng Li,2015.Thermodynamic optimization of
the recuperative heat exchanger for Joule–Thomson cryocoolers using response
Surface methodology [J] .International Journal of Refrigeration 60,155-165.] it is logical
Crossing Response surface meth od and having studied influences miniature J-T throttling refrigeratorThe factor of loss, the results showed that refrigerator length, capillary
Internal diameter, fin influence coefficient and internal diameter of outer cover pairLoss has significant impact.Fin is in traditional contra-flow heat exchanger
Away from, the equidistant finned heat exchanger after Parameters Optimal Design still existsWhat loss streamwise was seriously unevenly distributed asks
Topic, restrict double helix regenerator performance further increase or it is qualitative can under device light-weight design.This team [Chen Hui,
Double Jing Jing, Liu Yingwen, 2018. are based onAnalysis J-T throttling refrigerator local optimum design [J] Engineering Thermophysics journal, 39
(04): 724-729.] pass through the part to double-helix heat exchangerLoss is analyzed, and then double-helix heat exchanger is divided into close
Collect section and sparse section of two parts, research shows that: using upper tightly lower sparse double-helix heat exchanger structure to reduction heat exchangerLoss
Have great importance, however condensed section and sparse section each infinitesimal are all made of identical pitch in text,Loss distribution is deposited
In catastrophe, and there are still the lower device light-weight designs of qualitative energy for existing two-part upper tightly lower sparse double helix finned heat exchanger
Difficult problem.At the same time, the physical characteristic under fluid different conditions generates great influence to finned heat exchanger performance.Fluid
Different variations are presented according to its temperature, pressure difference in characteristic: in low-pressure area, enthalpy is only related with temperature；In high pressure area, enthalpy
With temperature, pressure variation and change, at identical temperature, pressure rise, enthalpy is increased, and under uniform pressure, temperature is increased, enthalpy
Value increases.In higher-pressure region, enthalpy is the complicated function of temperature and pressure, and under uniform pressure, temperature is increased, and enthalpy increases, but phase
Under synthermal, pressure rise, enthalpy reduces instead；Using the equidistant double-helix heat exchanger of tradition, fluid outlet state may be implemented
In higher-pressure region, but the acquisition of high heat transfer to be to increase heat exchange area as cost, and therefore pressure drop also increases.In conjunction with higher-pressure region fluid
Characteristic and the hot device performance of fin structure parameters on shift influence, by reasonable distribution structural parameters, to reduce high pressure heat exchange
It, can be while obtaining low pressure drop, high heat transfer for the purpose of the pressure drop of device, the light-weight design of realization device.
Summary of the invention
It is an object of the invention to solve the light-weight design of the lower device of the qualitative energy of upper tightly lower sparse double helix finned heat exchanger
The problems such as hardly possible, low efficiency, material can be saved by providing one kind, reduce heat exchangerLoss, the upper tightly lower sparse for enhancing heat exchange are double
Spiral fin heat exchanger.
In order to achieve the above objectives, the technical solution adopted by the present invention is that: be wrapped in core including mandrel and along axial screw
Spiral capillary finned tube on axis, be set with outside spiral capillary finned tube sealing shell, the mandrel lower end and shell there are
The space of evaporation cavity is formed, the spiral capillary finned tube includes the helical fin of capillary and winding on the capillary,
The upper end of the sealing shell offers capillary inlet and heat exchanger exit respectively, and capillary outlet is connected with evaporation cavity；
The spiral capillary finned tube is divided into upper end condensed section capillary finned tube and sparse section of lower end according to helical fin spacing size
Capillary finned tube.
The capillary outlet end is also equipped with throttle valve.
The condensed section capillary finned tube is located at hot fluid inlet, and sparse section of capillary finned tube is located at hot fluid outlet ports
Section.
The screw pitch of the helical fin of the winding on the capillary is calculated by following formula (1):
By entire heat exchanger along being divided axially into n infinitesimal, the length of each infinitesimal by winding capillary screw pitch integer
Times, i indicates that i-th of the infinitesimal divided since thermal fluid inlet, m are condensed section or sparse section of infinitesimal number, and n-m is sparse section
Infinitesimal number, d be capillary outer diameter, α, β, γ be correction factor, condensed section infinitesimal number m=0.4n~0.5n, α=0.1~
0.3, β=1~11, γ=0.2~0.5, and α < γ < β.The condensed section capillary finned tube and sparse section of capillary finned tube
Each infinitesimal identical screw pitch is used using different screw pitch or multiple infinitesimals using identical screw pitch, each infinitesimal.
Every two infinitesimal uses identical fin spiral shell in the condensed section capillary finned tube and sparse section of capillary finned tube
Away from then screw pitch is determined by following formula (2)-(3):
Each infinitesimal uses different pitch of fin in the condensed section capillary finned tube and sparse section of capillary finned tube,
Pitch of fin is in hyperbola consecutive variations, then screw pitch is determined by following formula (4):
The mandrel material is monel metal, and sealing shell material is Dewar, and capillary material is stainless steel, spiral
Fin material is copper.
Present invention combination shooting flow bulk properties, it is matched based on fin structure form and warm areaDamage the design of minimum
Theory furthers investigate regenerator working characteristics with structure optimization from local optimum parameter angle.Spiral capillary finned tube
By the non-special construction for being equally spacedly wrapped in capillary periphery and forming " upper tightly lower sparse " of helical fin, condensed section capillary finned tube
The helical fin screw pitch of upper winding is small, and the helical fin screw pitch wound on sparse section of capillary finned tube is big.Hot fluid is in spiral hair
Movement of spinning from top to bottom in thin finned tube becomes super cooled fluid.Cold fluid is in mandrel, spiral capillary finned tube and outer hull shape
At annular space in helically flow from bottom to top, the hot fluid in spiral capillary finned tube is cooled down.
The present invention is based on upper tightly lower sparse double helix finned heat exchangers can reduce heat exchangerLoss, promotes heat exchanger performance
Feature further studies the spy of upper tightly lower sparse double-helix heat exchanger condensed section and sparse section of pitch of fin under different variation tendencies
Property, propose that upper tightly lower sparse double-helix heat exchanger condensed section and sparse section of pitch of fin press the novel knot of different trend consecutive variations
Structure.Exist compared to upper tightly lower sparse double-helix heat exchanger, the present invention in documentIn the case that loss is held essentially constant, heat exchanger is whole
Body fin area greatly reduces, and raw material are reduced, and realizes the light-weight design of the lower device of qualitative energy；Loss distribution is more equal
It is even, no catastrophe；And pitch of fin consecutive variations, so that thermal stress distribution is uniform, to guarantee the peace of heat exchange equipment work
Quan Xingyu durability.It is high compared to traditional double-helix heat exchanger if heat exchanger high-voltage side liquid is under supercritical, high pressure state
The acquisition of heat transfer is to increase heat exchange area as cost, and pressure drop increases accordingly, the present invention can obtain low pressure drop, high heat transfer it is same
When, the light-weight design of realization device；There is the higher coefficient of heat transfer, while heat exchanger using the heat exchanger of spiral winding arrangement
Interior thermal stress distribution is uniform, to guarantee safety and the durability of heat exchange equipment work.The non-equidistant double-helix heat exchanger
Structure design philosophy is particularly suitable for overcritical working medium heat exchange.Overcritical working medium has in corresponding state region when temperature is kept
It is constant, the characteristics of enthalpy is reduced with pressure rise, make full use of the feature and can in conjunction with the double helix finned heat exchanger
While obtaining high heat exchange amount and consumptive material reduces.
Detailed description of the invention
Fig. 1 is structural schematic diagram described in present example.
Fig. 2 a is partial enlarged view at heat exchanger main part separation described in present example.
Fig. 2 b is the partial enlarged view of spiral capillary finned tube.
Fig. 3 a is heat transferLose the schematic diagram changed from top to bottom along axial direction.
Fig. 3 b is flowingLose the schematic diagram changed from top to bottom along axial direction.
Fig. 3 c is totalLose the schematic diagram changed from top to bottom along axial direction.
Fig. 4 is the schematic diagram that novel reverse flow tube arranges formula dividing wall type heat exchanger.
Fig. 5 a is the schematic diagram of novel microchannel contra-flow heat exchanger.
Fig. 5 b is the schematic diagram of intensive fin and sparse fin in novel microchannel contra-flow heat exchanger.
Fig. 6 a is fluid (by taking argon gas as an example) p-h performance profile.
Fig. 6 b is non-equidistant, equidistant structural fins heat exchanger inlet and outlet state p-h figure.
In figure: capillary 1, mandrel 2, spiral capillary finned tube 3, sealing shell 4, helical fin 5, condensed section capillary fin
Pipe 6, sparse section of capillary finned tube 7, throttle valve 8, evaporation cavity 9.
Specific embodiment
The present invention is described in further detail with reference to the accompanying drawings and embodiments.
Embodiment 1:
Such as Fig. 1, shown in Fig. 2 a, Fig. 2 b, the present embodiment includes mandrel 2 and is wrapped in the spiral shell on mandrel 2 along axial screw
Capillary finned tube 3 is revolved, sealing shell 4 is set with outside spiral capillary finned tube 3, there are formation with shell 4 for 2 lower end of mandrel
The space of evaporation cavity 9, the spiral capillary finned tube 3 include capillary 1 and the helical fin 5 being wrapped on capillary 1,
The upper end of the sealing shell 4 offers capillary inlet and heat exchanger exit respectively, and the outlet of capillary 1 is connected with evaporation cavity 9
It is logical, and throttle valve 8 is also equipped in exit；The spiral capillary finned tube 3 is divided into according to 5 spacing size of helical fin
Condensed section capillary finned tube 6 and sparse section of lower end capillary finned tube 7 are held, forms the structure of " upper tightly lower sparse ", wherein condensed section hair
Thin finned tube 6 is located at hot fluid inlet, and sparse section of capillary finned tube 7 is located at hot fluid outlet ports section, and the spacing of helical fin is pressed
Hyperbola consecutive variations are calculated by following formula (5):
By entire heat exchanger along being divided axially into n infinitesimal, the length of each infinitesimal by winding capillary screw pitch integer
Times, i indicates that i-th of the infinitesimal divided since thermal fluid inlet, m are condensed section or sparse section of infinitesimal number, and d is capillary
Outer diameter, n=50, m=0.4n=20.2 material of mandrel of the present embodiment is monel metal, and 4 material of sealing shell is Dewar, hair
3 material of tubule is stainless steel, and 5 material of helical fin is copper.
Hot fluid is spinned movement from top to bottom in spiral capillary finned tube 3.Cold fluid is in mandrel 2, capillary finned tube 3
Helical flow is ultimately discharged into the hot fluid cooling in capillary finned tube 3 from bottom to top in the annular space formed with shell 4
Atmosphere.
The present invention compares two-part upper tightly lower sparse double-helix heat exchanger,In the case that loss is held essentially constant, change
Hot device integral fins area greatly reduces, and raw material are reduced, and realizes the light-weight design of the lower device of qualitative energy；Loss distribution
It is more uniform, no catastrophe；And pitch of fin consecutive variations, so that thermal stress distribution is uniform, to guarantee heat exchange equipment work
The safety of work and durability.
As shown in Figure 3a, the pitch of fin used in the embodiment of the present invention is tied with " upper tightly lower sparse " of hyperbola consecutive variations
In structure, heat transfer of the condensed section to sparse section of transition portionLose the biography compared to two-part " upper tightly lower sparse " structure in document
HeatLoss greatly reduces.As shown in Figure 3b, after using " upper tightly lower sparse " structure, in structure size and physical properties of fluids joint effect
Under, the flowing of condensed sectionLoss greatly reduces, compared with two-part " upper tightly lower sparse " structure (document), overall flowLoss
Be distributed it is more uniform, and flowLoss reduces 0.4%.As shown in Figure 3c, the pitch of fin that the embodiment of the present invention 1 uses with
In " upper tightly lower sparse " structure of hyperbola consecutive variations, changeover portionLoss greatly reduces, to entiretyLoss distribution plays
" disappear peak effect ", so thatLoss distribution is more evenly." upper tightly lower sparse " structure and two-part used in specific embodiment 1 "
Upper tightly lower sparse " structure is compared: totalLoss is held essentially constant, and material consumption reduces 26%.
Embodiment 2:
It is identical with 1 basic parameter of embodiment, but the screw pitch of condensed section and sparse section of each infinitesimal of spiral capillary according to
Linear continuous variation.Shown in its screw pitch calculating formula such as equation (6):
In formula: n=50, m=0.4n=20, α=0.3, β=1.By being tied to " upper tightly lower sparse " in specific embodiment 2
Structure calculate and with two-part " upper tightly lower sparse " Structure Comparison: totalLose NdIt is held essentially constant, material consumption reduces
24%.
Embodiment 3:
The present embodiment is a kind of Novel adverse current heat exchanger, specially countercurrent tube bundle type wall-type heat exchanger, be by base tube 10,
Intensive fin 11, sparse fin 12 form, as shown in Figure 4.Intensive fin 11 is located at hot fluid inlet section, and sparse fin 12 is located at
The separation of hot fluid outlet ports section, intensive fin 11 and sparse fin 12 is located at the position apart from thermal fluid inlet 40%~50%
It sets.Hot fluid backflows dynamic in 10 infolding of base tube, carries out heat exchange by fin and cold fluid, while cooling down to itself.It adopts
With the structure of " upper tightly lower sparse ", so that the heat exchange of cold fluid and hot fluid is stronger at intensive fin 11, to hot fluid
Cooling effect it is more preferable；And the resistance that cold fluid is subject at sparse fin 12 is smaller, flowingLoss greatly reduces.Using
" upper tightly lower sparse " new structural countercurrent tube bundle type wall-type heat exchanger, hasLoss reduces, saves the advantages of material.
Embodiment 4:
The present embodiment is a kind of novel microchannel contra-flow heat exchanger, as shown in figure 5 a and 5b, including it is microchannel 13, intensive
Fin 14, sparse fin 15, sealing strip 16.The runner direction of the microchannel 14 and the intensive fin 14, dilute on the outside of microchannel
The runner direction for dredging fin 15 is parallel, forms contra-flow heat exchanger.Working medium in microchannel 13 is cold fluid, 13 outside of microchannel
Working medium is hot fluid.Using the structure of " upper tightly lower sparse ", i.e., spacing of fin is small at thermal fluid inlet, at hot fluid outlet ports between fin
Away from big.As shown in Figure 5 b, the separation of intensive fin 14 and sparse fin 15 is located at apart from thermal fluid inlet 40%~50%
Position.Compared to traditional equidistant fin micro-channel heat exchanger, the flowing of hot fluid outlet ports sectionLoss greatly reduces, heat transferLoss
It greatly reduces；The fin dense arrangement of thermal fluid inlet section, on the one hand can increase heat exchange amount, make up end heat exchange amount reduce into
And meet heat exchanger integrally cooling amount, end is on the other hand reduced indirectlyLoss.The microchannel changed using spacing of fin
Finned heat exchanger hasLose it is small, save material the advantages of.
Embodiment 5:
The present embodiment is a kind of using argon gas as the overcritical miniature non-equidistant finned heat exchanger of working medium, argon gas characteristic such as Fig. 6 a
It is shown, including low-pressure area 16, higher-pressure region 17 and high pressure area 18.Different changes are presented according to its temperature, pressure difference in argon gas characteristic
Change, under low-pressure area, identical temperature, as the raising enthalpy of pressure is basically unchanged；Under higher-pressure region, identical temperature, pressure liter
Height, enthalpy reduce；Under high pressure area, identical temperature, pressure rise, enthalpy is increased.Using argon gas as working medium, be respectively adopted " on
It is close lower to dredge " non-equidistant fin structure heat exchanger and the equidistant fin structure heat exchanger of tradition, p-h characteristic is as shown in Figure 6 b, ab,
Cd is that (a is thermal fluid inlet to traditional equidistant structural fins heat exchanger state point, and b is hot fluid outlet ports, and c is cold fluid inlet, d
For cold fluid outlet)；Ab ', cd ' it is that (a is thermal fluid inlet to non-equidistant structural fins heat exchanger state point, and b ' goes out for hot fluid
Mouthful, c is cold fluid inlet, and d ' is cold fluid outlet).After " upper tightly lower sparse " non-equidistant fin structure heat exchanger, hot fluid
B ' is exported compared to the raising of traditional structure hot fluid outlet ports b temperature, pressure rise, and hot fluid outlet ports state is in higher-pressure region,
The beneficial effect of high heat exchange amount and low flow resistance can be obtained simultaneously.If hot fluid outlet ports are in low-pressure area, as state point 12,
Shown in 12 ', 2 ' temperature of hot fluid outlet temperature is increased, pressure rise, but enthalpy increases (i.e. heat exchange amount reduction).Therefore reasonable distribution
Pitch of fin, using upper tightly lower sparse non-equidistant finned heat exchanger, and it is low to combine supercritical, high pressure area fluid behaviour that can obtain simultaneously
The beneficial effect of pressure drop height heat exchange, at the same time, heat exchanger materials consumption also greatly reduce.
Claims (8)
1. a kind of upper tightly lower sparse double helix finned heat exchanger, it is characterised in that: be wrapped in including mandrel (2) and along axial screw
Spiral capillary finned tube (3) on mandrel (2) is set with sealing shell (4), the mandrel outside spiral capillary finned tube (3)
(2) there are the space for forming evaporation cavity (9), the spiral capillary finned tube (3) includes capillary (1) for lower end and shell (4)
And it is wrapped in the helical fin (5) on capillary (1), the upper end of the sealing shell (4) offers capillary inlet respectively
And heat exchanger exit, capillary (1) outlet are connected with evaporation cavity (9)；The spiral capillary finned tube (3) is according to spiral wing
Piece (5) spacing size is divided into upper end condensed section capillary finned tube (6) and sparse section of lower end capillary finned tube (7).
2. upper tightly lower sparse double helix finned heat exchanger according to claim 1, it is characterised in that: the capillary (1)
Outlet end is also equipped with throttle valve (8).
3. upper tightly lower sparse double helix finned heat exchanger according to claim 1, it is characterised in that: the condensed section capillary
Finned tube (6) is located at hot fluid inlet, and sparse section of capillary finned tube (7) is located at hot fluid outlet ports section.
4. upper tightly lower sparse double helix finned heat exchanger according to claim 1, it is characterised in that: described to be wrapped in capillary
(1) screw pitch of the helical fin (5) on is calculated by following formula (1):
By entire heat exchanger along being divided axially into n infinitesimal, the length of each infinitesimal by winding capillary screw pitch integral multiple, i
Indicate that i-th of the infinitesimal divided since thermal fluid inlet, m are condensed section or sparse section of infinitesimal number, n-m is sparse section micro-
First number, d are the outer diameter of capillary, and α, β, γ are correction factor, condensed section infinitesimal number m=0.4n~0.5n, α=0.1~0.3, β
=1~11, γ=0.2~0.5, and α < γ < β.
5. upper tightly lower sparse double helix finned heat exchanger according to claim 1, it is characterised in that: the condensed section capillary
Finned tube (6) and each infinitesimal of sparse section of capillary finned tube (7) use identical screw pitch, each infinitesimal to use different spiral shells
Away from or multiple infinitesimals use identical screw pitch.
6. upper tightly lower sparse double helix finned heat exchanger according to claim 1, it is characterised in that: the condensed section capillary
Every two infinitesimal uses identical pitch of fin in finned tube (6) and sparse section of capillary finned tube (7), then screw pitch is by following formula (2)-
(3) it determines:
7. upper tightly lower sparse double helix finned heat exchanger according to claim 1, it is characterised in that: the condensed section capillary
Each infinitesimal uses different pitch of fin in finned tube (6) and sparse section of capillary finned tube (7), and pitch of fin connects in hyperbola
Continuous variation, then screw pitch is determined by following formula (4):
8. upper tightly lower sparse double helix finned heat exchanger according to claim 1, it is characterised in that: described mandrel (2) material
Material is monel metal, and sealing shell (4) material is Dewar, and capillary (3) material is stainless steel, and helical fin (5) material is
Copper.
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| CN201811166613.7A CN109443061B (en) | 2018-10-08 | 2018-10-08 | Double-spiral fin heat exchanger with dense upper part and sparse lower part |
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| CN109443061B CN109443061B (en) | 2020-06-26 |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN112013695A (en) * | 2020-06-10 | 2020-12-01 | 湖北雷迪特冷却系统股份有限公司 | Core body assembly with non-uniform wave pitch structure |
| CN112173722A (en) * | 2020-08-05 | 2021-01-05 | 宁波诺丁汉大学 | Fluid conveying device |
| CN114087810A (en) * | 2021-11-16 | 2022-02-25 | 西安交通大学 | Throttling refrigerator |
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| CN108131963A (en) * | 2017-12-13 | 2018-06-08 | 西安交通大学 | A kind of ellipse cast wrap-round tubular heat exchanger |
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| CN202770269U (en) * | 2012-09-26 | 2013-03-06 | 江苏中圣高科技产业有限公司 | Tube bundle winding type heat exchanger |
| US20180283796A1 (en) * | 2016-02-05 | 2018-10-04 | Hamilton Sundstrand Corporation | Counter spiral tube and shell heat exchanger |
| CN105737639A (en) * | 2016-05-10 | 2016-07-06 | 郑州大学 | Afterheat utilization cyclone separator |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN112013695A (en) * | 2020-06-10 | 2020-12-01 | 湖北雷迪特冷却系统股份有限公司 | Core body assembly with non-uniform wave pitch structure |
| CN112173722A (en) * | 2020-08-05 | 2021-01-05 | 宁波诺丁汉大学 | Fluid conveying device |
| CN114087810A (en) * | 2021-11-16 | 2022-02-25 | 西安交通大学 | Throttling refrigerator |
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| CN109443061B (en) | 2020-06-26 |
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