CN205090857U - Internal thread evaporation heat exchange tube with two sections different spiral flute profile structures - Google Patents
Internal thread evaporation heat exchange tube with two sections different spiral flute profile structures Download PDFInfo
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- CN205090857U CN205090857U CN201520803080.4U CN201520803080U CN205090857U CN 205090857 U CN205090857 U CN 205090857U CN 201520803080 U CN201520803080 U CN 201520803080U CN 205090857 U CN205090857 U CN 205090857U
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- heat exchange
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- exchange pipeline
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Abstract
The utility model discloses an internal thread evaporation heat exchange tube with two sections different spiral flute profile structures, it includes the body, and this body internal surface setting has certain helix angle's a plurality of helical rack and the channel between helical rack, and the body comprises first heat transfer pipeline section and second heat transfer pipeline section, helical rack in the first heat transfer pipeline section with helical rack in the second heat transfer pipeline section has different rack figures, different tooth depths, the different helix angle and the different hand of spiral. The utility model discloses intraductal at same root internal thread heat exchange tube, flow direction along the refrigerant divides into two sections heat transfer sections, and each section helical tooth has not same tooth strip figure, tooth depth, different helical angle and the hand of spiral, can improve the boiling heat transfer coefficient greatly, promotion heat exchange efficiency.
Description
Technical field
The utility model relates to a kind of heat exchanger tube, and especially a kind of internal thread evaporating heat-exchanging pipe with two sections of different helical tooth type structures, is applicable to dry blowing formula evaporimeter.
Background technology
Internal thread evaporating heat-exchanging pipe is air-conditioning system dry evaporator heat exchanger tube, is commonly called as " dry blowing pipe ".Its operation principle flows through liquid refrigerant in heat exchanger tube, to the mode that it heats, cold-producing medium being seethed with excitement, undergoing phase transition by managing outer hot water, and the final steam that formed discharges heat exchanger tube.In flow of refrigerant process, constantly heated, constantly produce bubble along journey, forming vapour phase constantly increases, the process that liquid phase constantly reduces.According to liquid phase and vapour phase institute accounting row number, two phase flow roughly can be divided into the different flow pattern such as laminar flow, wave flow, bubble flow, slug flow, stirring stream, mist flow.Bottomhole pressure boiling heat transfer and two phase flow pattern have inseparable relation, and the two phase flow heat transfer coefficient difference of different flow pattern is very large.Cold-producing medium enters internal thread evaporation tube with liquid condition until be all transformed into steam discharge, is generally experienced by the Regime transition of wave flow, bubble flow, slug flow, stirring stream, mist flow, finally form steam from laminar flow.In pipe, the two phase flow of different flow pattern is different from the interactional heat-transfer mechanism of wall.In order to improve the heat transfer effect of riffled tube, technical staff is constantly had to propose improvement project to general riffled tube.Chinese patent: disclose riffled tube technology in CN02232596.4: by thread contour in pipe along cut-out ridge formula groove tooth top ridge having rule/irregular spacing.Chinese patent: the technology of riffled tube disclosed in CN02232597.2: on heat-transfer pipe inner surface, is transformed into bimodal profile of tooth by general thread, namely processes shallow slot at the top of helical tooth, profile of tooth cross section forms " M " type tooth.But in single riffled tube, single tooth-shape structure cannot adapt to the various flow patterns along journey two phase flow, thus have impact on the raising of the coefficient of heat transfer, limits the lifting of riffled tube evaporation tube heat exchange property.
Utility model content
The utility model object is: for the deficiency of above-mentioned riffled tube, proposes a kind of internal thread evaporating heat-exchanging pipe with two sections of different helical tooth type structures, to improve heat exchange efficiency further.
The technical solution of the utility model is: a kind of internal thread evaporating heat-exchanging pipe with two sections of different helical tooth type structures, comprise body, this inner surface of tube body arranges some helical racks with certain lead angle and the conduit be formed between helical rack, described body is made up of the first heat exchange pipeline section and the second heat exchange pipeline section, and the helical rack in described first heat exchange pipeline section has different tooth bar numbers, different tooth depths, different lead angles and the different hand of spiral from the helical rack in described second heat exchange pipeline section.
The utility model, on the basis of technique scheme, also comprises following preferred version:
The tooth bar number of described first heat exchange pipeline section internal screw tooth bar is less than the tooth bar number of described second heat exchange pipeline section internal screw tooth bar, the tooth depth of described first heat exchange pipeline section internal screw tooth bar is greater than the tooth depth of described second heat exchange pipeline section internal screw tooth bar, and the lead angle of described first heat exchange pipeline section internal screw tooth bar is greater than the lead angle of described second heat exchange pipeline section internal screw tooth bar.
The lead angle of described first heat exchange pipeline section internal screw tooth bar is 30 ~ 40 degree, and the lead angle of described second heat exchange pipeline section internal screw tooth bar is 10 ~ 18 degree.
The tooth depth of described first heat exchange pipeline section internal screw tooth bar is 0.2 ~ 0.35mm, and the tooth depth of described second heat exchange pipeline section internal screw tooth bar is 0.15 ~ 0.25mm.
The tooth bar number of described first heat exchange pipeline section internal screw tooth bar is 35 ~ 50, and the tooth bar number of described second heat exchange pipeline section internal screw tooth bar is 50 ~ 80.
The hand of spiral of described first heat exchange pipeline section internal screw tooth bar is dextrorotation, and the hand of spiral of described second heat exchange pipeline section internal screw tooth bar is left-handed.
The outer surface of described body is smooth surface.
Principle of the present utility model is as follows: in the first heat exchange pipeline section of refrigerant inlet, because mass dryness fraction is lower, under gravity, liquid is below pipe, gas is in the top of pipe, and two phase flow signals is laminar flow or wave flow, in this case, liquid can not cover heat-transfer surface completely, have impact on boiling heat transfer effect.In order to increase the area that liquid covers, need to rely on the conduit on wall to produce the liquid of larger siphonage lifting tube bottom.Siphonage produces under the radius of curvature effect due to the liquid in conduit and the surface tension in gas interface and vapour-liquid interface, generally, surface tension is larger, radius of curvature is less, then siphonage is stronger, in pipe, the liquid level hoisting depth of bottom is higher, and the heat exchange area of covering is also larger.The radius of curvature at vapour-liquid interface is determined by the geometry of conduit.According to hydromechanical theory, on wall, corresponding conduit cross section is triangle, and conduit wants dark, capillary pressure reduction in groove can be caused larger, produce stronger siphonage; The helical angle of helical rack is larger simultaneously, and under same capillary force effect, in conduit, lifting liquid height is higher, and obtain larger liquid wetted area in inner helix pipe, the increase of wetted area causes the raising of heat transfer effect.Along with continuous in Working fluid flow process is heated, produce increasing gas, liquid is fewer and feweri, two phase flow pattern experience slug flow, stirs stream equal flow type and changes, and progressively develops into annular flow.The feature of annular flow is heat exchanger tube central area is gas, liquid film is distributed in the wall place of pipe, form thin layer, this layer of thin liquid film can have rotation to a certain extent along gear rack helix angle, there is radial velocity component, cause liquid film surface to produce fluctuation, add the disturbance to liquid film, cause the strengthening of liquid film heat exchange.Experiment shows, the more rotary speed components of wall liquid film that can cause of number of starts are larger, and heat transfer effect is better; Lead angle is less, and the flow resistance of tube fluid is less, and flowing velocity is larger, and heat transfer effect is better.Under annular flow flow pattern, the liquid film at wall place is very thin, and therefore the height of tooth can not be too high, otherwise helical rack can protrude outside liquid film, does not have the effect of boiling heat transfer.So the tooth depth of the second heat exchange pipeline section will lower than the tooth depth of the first heat exchange pipeline section.In addition, the hand of spiral of the helical tooth of the first heat exchange pipeline section is different from the hand of spiral of the second heat exchange pipeline section, namely become left-handed by dextrorotation, then can produce violent disturbance to the flow field of downstream flow pattern and near wall, accelerate the flow regime transition of two phase flow, make it to enter into annular flow as early as possible, and annular flow is in various flow pattern, the one of good effect of heat exchange.According to criteria equation or the classical two phase flow signals figure of two phase flow pattern conversion, as Taitei-Dukler, Baker equal flow type figure, by parameter computing, determine the boundary position of laminar flow or wave flow and other flow pattern, in this, as the foundation of the utility model riffled tube segmentation position.
The utility model has the advantages that: riffled tube is the widely used thermoexcell of current air conditioner industry.Pipe internal surface arranges many protruding tooth bars, and form conduit between tooth bar, tooth bar distributes vertically twist.The boiling heat transfer coefficient of riffled tube improves more than 80% than plain tube.At present, for single riffled tube, tooth bar number, tooth depth, helical angle and the hand of spiral are all single fixing.The utility model, in same internal thread heat exchange tube, along the flow direction of cold-producing medium, is divided into two sections of heat exchanging segments, and each section of helical tooth has different tooth bar number, tooth depth, different helical angle and the hand of spiral, greatly can improve boiling heat transfer coefficient.
Accompanying drawing explanation
Fig. 1 is the structural representation of this internal thread evaporating heat-exchanging pipe of the utility model embodiment, and in figure, arrow represents the flow direction of its fluid when practical application;
Fig. 2 is that the A-A of Fig. 1 is to sectional view;
Wherein: 1-body, 2-helical rack, 1a-first heat exchange pipeline section, 1b-second heat exchange pipeline section.
Detailed description of the invention
Below in conjunction with the drawings and specific embodiments, illustrate the utility model further, these embodiments should be understood and be only not used in restriction scope of the present utility model for illustration of the utility model, after having read the utility model, the amendment of those skilled in the art to the various equivalent form of value of the present utility model has all fallen within the application's claims limited range.
Fig. 1 and Fig. 2 shows a specific embodiment of this internal thread evaporating heat-exchanging pipe of the utility model, identical with traditional internal thread evaporating heat-exchanging pipe is, it also comprises body 1, this body 1 inner surface arranges some helical racks 2 with certain lead angle and the conduit be formed between helical rack 2, and the outer surface of described body 1 is smooth surface.
The key improvements of the present embodiment is: described body 1 is made up of the first heat exchange pipeline section 1a and the second heat exchange pipeline section 1b two pipeline sections, and the helical rack 2 in described first heat exchange pipeline section 1a has different tooth bar numbers, different tooth depths, different lead angles and the different hand of spiral from the helical rack 2 in described second heat exchange pipeline section 1b.In this example, the tooth bar number of the first heat exchange pipeline section 1a inside spin tooth bar 2 is less than the tooth bar number of the second heat exchange pipeline section 1b inside spin tooth bar 2, the lead angle of the first heat exchange pipeline section 1a inside spin tooth bar 2 is greater than the lead angle of the second heat exchange pipeline section 1b inside spin tooth bar 2, the tooth depth of the first heat exchange pipeline section 1a inside spin tooth bar 2 is greater than the tooth depth of the second heat exchange pipeline section 1b inside spin tooth bar 2, the hand of spiral of the first heat exchange pipeline section 1a inside spin tooth bar 2 is dextrorotation, the hand of spiral of the second heat exchange pipeline section 1b inside spin tooth bar 2 is left-handed, certainly, also can the first heat exchange pipeline section be left-handed, second heat exchange pipeline section is dextrorotation.
Test through designer:
The lead angle of the first heat exchange pipeline section 1a inside spin tooth bar 2 is generally good with 30 ~ 40 degree, and this example is specially 40 degree.The lead angle of the second heat exchange pipeline section 1b inside spin tooth bar 2 is generally good with 10 ~ 18 degree, and this example is specially 15 degree.
The tooth depth of the first heat exchange pipeline section 1a inside spin tooth bar 2 is good with 0.2 ~ 0.35mm, and this example is specially 0.35mm.The tooth depth of the second heat exchange pipeline section 1b inside spin tooth bar 2 is good with 0.15 ~ 0.25mm, and body is specially 0.2mm.
The tooth bar number of the first heat exchange pipeline section 1a inside spin tooth bar 2 is good with 35 ~ 50, and this example is specially 35.The tooth bar number of the second heat exchange pipeline section 1b inside spin tooth bar 2 is good with 50 ~ 80, and this example is specially 75.
In addition, as shown in Figure 2, the cross section of the conduit be formed between helical rack 2 is arranged to triangle by this example, to promote the heat exchange efficiency of this heat exchanger tube further.
Described first heat exchange pipeline section 1a and the second heat exchange pipeline section 1b can be one-piece integrated structure, and also can be split-type structural, this example be monolithic construction.When practical application, the first heat exchange pipeline section 1a is refrigerant inlet, and the second heat exchange pipeline section 1b is refrigerant outlet, and cold-producing medium flows to the second heat exchange pipeline section by the first heat exchange pipeline section in body 1.
In brief, the internal thread evaporating heat-exchanging pipe of the present embodiment is copper material riffled tube, its diameter 15.88mm, the first heat exchanger tube segment length 300mm, and remaining part is the second heat exchange pipeline section.The internal thread tooth depth 0.35mm of the first heat exchange pipeline section, tooth bar number is 35, helical angle 40 degree, and the hand of spiral is dextrorotation; The internal thread tooth depth of the second heat exchanger tube is 0.2mm, and tooth bar number is 75, helical angle 15 degree, and the hand of spiral is left-handed.
Claims (8)
1. one kind has the internal thread evaporating heat-exchanging pipe of two sections of different helical tooth type structures, comprise body (1), this body (1) inner surface arranges some helical racks (2) with certain lead angle and the conduit be formed between helical rack (2), it is characterized in that: described body (1) is made up of the first heat exchange pipeline section (1a) and the second heat exchange pipeline section (1b), helical rack (2) in described first heat exchange pipeline section (1a) has different tooth bar numbers from the helical rack (2) in described second heat exchange pipeline section (1b), different tooth depths, different lead angles and the different hand of spiral.
2. the internal thread evaporating heat-exchanging pipe with two sections of different helical tooth type structures according to claim 1, it is characterized in that: the tooth bar number of described first heat exchange pipeline section (1a) inside spin tooth bar (2) is less than the tooth bar number of described second heat exchange pipeline section (1b) inside spin tooth bar (2), the tooth depth of described first heat exchange pipeline section (1a) inside spin tooth bar (2) is greater than the tooth depth of described second heat exchange pipeline section (1b) inside spin tooth bar (2), the lead angle of described first heat exchange pipeline section (1a) inside spin tooth bar (2) is greater than the lead angle of described second heat exchange pipeline section (1b) inside spin tooth bar (2).
3. the internal thread evaporating heat-exchanging pipe with two sections of different helical tooth type structures according to claim 1 and 2, the lead angle that it is characterized in that described first heat exchange pipeline section (1a) inside spin tooth bar (2) is 30 ~ 40 degree, and the lead angle of described second heat exchange pipeline section (1b) inside spin tooth bar (2) is 10 ~ 18 degree.
4. the internal thread evaporating heat-exchanging pipe with two sections of different helical tooth type structures according to claim 1 and 2, it is characterized in that: the tooth depth of described first heat exchange pipeline section (1a) inside spin tooth bar (2) is 0.2 ~ 0.35mm, the tooth depth of described second heat exchange pipeline section (1b) inside spin tooth bar (2) is 0.15 ~ 0.25mm.
5. the internal thread evaporating heat-exchanging pipe with two sections of different helical tooth type structures according to claim 1 and 2, it is characterized in that: the tooth bar number of described first heat exchange pipeline section (1a) inside spin tooth bar (2) is 35 ~ 50, the tooth bar number of described second heat exchange pipeline section (1b) inside spin tooth bar (2) is 50 ~ 80.
6. the internal thread evaporating heat-exchanging pipe with two sections of different helical tooth type structures according to claim 1 and 2, it is characterized in that: the hand of spiral of described first heat exchange pipeline section (1a) inside spin tooth bar (2) is dextrorotation, the hand of spiral of described second heat exchange pipeline section (1b) inside spin tooth bar (2) is left-handed.
7. the internal thread evaporating heat-exchanging pipe with two sections of different helical tooth type structures according to claim 1 and 2, is characterized in that: the cross section of described conduit is triangular in shape.
8. the internal thread evaporating heat-exchanging pipe with two sections of different helical tooth type structures according to claim 1 and 2, is characterized in that: the outer surface of described body (1) is smooth surface.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520803080.4U CN205090857U (en) | 2015-10-16 | 2015-10-16 | Internal thread evaporation heat exchange tube with two sections different spiral flute profile structures |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520803080.4U CN205090857U (en) | 2015-10-16 | 2015-10-16 | Internal thread evaporation heat exchange tube with two sections different spiral flute profile structures |
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| CN205090857U true CN205090857U (en) | 2016-03-16 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201520803080.4U Expired - Fee Related CN205090857U (en) | 2015-10-16 | 2015-10-16 | Internal thread evaporation heat exchange tube with two sections different spiral flute profile structures |
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| CN (1) | CN205090857U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105202961A (en) * | 2015-10-16 | 2015-12-30 | 苏州新太铜高效管有限公司 | Inner-thread evaporation heat exchange pipe with two sections of different spiral tooth-shaped structures |
| CN112052550A (en) * | 2019-06-05 | 2020-12-08 | 无锡化工装备股份有限公司 | Design method of shell side boiling spiral wound tube type heat exchanger |
-
2015
- 2015-10-16 CN CN201520803080.4U patent/CN205090857U/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105202961A (en) * | 2015-10-16 | 2015-12-30 | 苏州新太铜高效管有限公司 | Inner-thread evaporation heat exchange pipe with two sections of different spiral tooth-shaped structures |
| CN112052550A (en) * | 2019-06-05 | 2020-12-08 | 无锡化工装备股份有限公司 | Design method of shell side boiling spiral wound tube type heat exchanger |
| CN112052550B (en) * | 2019-06-05 | 2023-09-19 | 无锡化工装备股份有限公司 | Design method of shell-side boiling spiral coiled tube heat exchanger |
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| Date | Code | Title | Description |
|---|---|---|---|
| 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: 20160316 Termination date: 20201016 |
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| CF01 | Termination of patent right due to non-payment of annual fee |