CN202420236U - Pure counterflow tube shell type helical flat tube heat exchanger - Google Patents
Pure counterflow tube shell type helical flat tube heat exchanger Download PDFInfo
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- CN202420236U CN202420236U CN2011205584646U CN201120558464U CN202420236U CN 202420236 U CN202420236 U CN 202420236U CN 2011205584646 U CN2011205584646 U CN 2011205584646U CN 201120558464 U CN201120558464 U CN 201120558464U CN 202420236 U CN202420236 U CN 202420236U
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- tube
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- oblate
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Abstract
The utility model discloses a pure counterflow tube shell type helical flat tube heat exchanger which comprises a shell, a heat-exchange tube bundle, a fixing tube plate and a tube box. The shell is provided with a shell side inlet and a shell side outlet; the heat-exchange tube bundle is assembled in the shell; the fixing tube plate is used for fixing the heat-exchange tube bundle; the tube box is assembled on the end part of the shell and is provided with a shell side inlet and a shell side outlet; and the heat-exchange tube bundle is formed by closely arraying a plurality of helical flat tubes with same shapes. The pure counterflow tube shell type helical flat tube heat exchanger is characterized in that the helix angles on the opposite parts of every adjacent two helical flat tubes stagger each other, therefore, one parts of the helical lines on the outer edges of all the helical flat tube are inlaid in helical slots of adjacent spiral flat tubes when the helical flat tube contact closely, periodical point contact is formed in the helical slots, and mandatory flowing channel is formed hereby. Compared with the existing helical flat tube heat exchanger, the pure counterflow tube shell type helical flat tube heat exchanger has a smaller volume, higher heat exchange efficiency because the flow area of the shell side and the diameter of the shell are reduced greatly and wider range of application.
Description
Technical field
The utility model relates to a kind of shell-and-tube heat exchanger, especially a kind of pure adverse current shell-and-tube heat exchanger with oblate tube that adopts a plurality of spiral flat tubes as the heat exchanger tube tube bank.Can be widely used in industries such as petrochemical industry, metallurgy, electric power.
Background technology
Since early 1970s oil crisis outburst, be that environment, ecology and the socioeconomic problem at center increasingly sharpened with the energy.Countries in the world are fully recognized that energy-conservation significance, and the reasonable utilization of the energy has become the key problem of various countries' industry benign development.Under this background, various power-saving technologies competitively occur.Augmentation of heat transfer is rationally efficiently to utilize one of important channel of the energy, energy savings.And in actual industrial production, what application augmentation of heat transfer technology was maximum is heat exchanger.Heat exchanger is not only and is guaranteed the engineering equipment indispensable parts that run well in each industrial processes, and in the important share that all accounts for whole engineering aspect metal consumption, power consumption and the investment.
Heat exchanger with oblate is a kind of new type high efficient heat exchanger that on the basis of conventional tube shell heat exchanger, develops, and compares with the light pipe heat exchanger, and its heat flow density is high, and volume is little, is applicable to multiple heat transfer process.Yet the application of domestic heat exchanger with oblate now also seldom, has only the report of minority commerical test research.The embodiment that it is concrete, like choosing of spiral flat tube cast, comb mode etc. does not all reach desirable state, has limited its development and application.Patent announcement number uses the technical scheme of spiral flat tube as the heat exchange oil pipe for " the spiral flat tube oil cooler " of CN2867256Y discloses, but too simple to the description of the comb mode of spiral flat tube in housing, is unfavorable for technical staff's enforcement.Patent announcement number comprises the comb mode in cast size and the housing for CN101551207B " shell-and-tube heat exchanger with oblate tube " discloses a kind of suitable heat exchanger structure.This kind arrangement form is single; As shown in Figure 1; A, b are the layout drawings of two varying cross-sections in the tube bank of existing heat exchanger with oblate among the figure, and visible by figure, the tube pitch of each spiral flat tube of the tube bank of this heat exchanger is consistent with the length of the major axis of flat tube.This structure is through changing the requirement that the cast size satisfies heat transfer and pressure drop; But,, heat exchanger volume is increased because the tube pitch of each spiral flat tube of the tube bank of this heat exchanger is consistent with the length of the major axis of flat tube; Limit the design of heat exchanger, be unfavorable for its development and popularization.So the structure of existing shell-and-tube heat exchanger with oblate tube is demanded urgently improving.
Summary of the invention
The utility model provides a kind of pure adverse current shell-and-tube heat exchanger with oblate tube, can fundamentally solve the problem that shell side flow dead, shell side pressure that the arc heat exchanger of conventional tube shell-type exists are fallen big, easy scale formation and the tube bank induced vibration is taken place easily.Compare with existing heat exchanger with oblate, whole heat exchanger volume is dwindled, and can significantly reduce the circulation area and the diameter of the housing of shell side, improve heat exchange efficiency, the scope of application is more extensive.
The utility model solves the technical scheme that its technical problem adopted: a kind of pure adverse current shell-and-tube heat exchanger with oblate tube, comprise the housing that is provided with the shell side entrance and exit, be assembled in heat exchanger tube tube bank in the housing, be used for fixing tube bank fixed tube sheet, be assembled in shell end and be provided with the bobbin carriage of tube side gateway; Said tube bank is closely arranged by the identical spiral flat tube of some shapes and is constituted; Be characterized in: the angle of the lead angle at the relative position of two whenever adjacent spiral flat tubes staggers; Make each spiral flat tube when each spiral flat tube closely contacts the outer rim helix some be embedded in the helicla flute of adjacent spiral flat tube; In helicla flute, form the periodic points contact, force to stream passage thereby outside pipe, form.
Above-mentioned pure adverse current shell-and-tube heat exchanger with oblate tube, wherein: when each spiral flat tube closely contacted, the tube pitch between adjacent two spiral flat tubes was less than the length of the major axis of each spiral flat tube.
Above-mentioned pure adverse current shell-and-tube heat exchanger with oblate tube, wherein: the angle that the lead angle at relative position staggers between described adjacent two spiral flat tubes is for extremely spending less than 180 greater than 0 degree.
Above-mentioned pure adverse current shell-and-tube heat exchanger with oblate tube, wherein: the angle that the lead angle at relative position staggers between described adjacent two spiral flat tubes is identical.
Above-mentioned pure adverse current shell-and-tube heat exchanger with oblate tube, wherein: the angle that the lead angle between described adjacent two spiral flat tubes staggers is 90 when spending, and the cross section of the major axis of each adjacent spiral flat tube is orthogonal in the arbitrary section of said tube bank.
Above-mentioned pure adverse current shell-and-tube heat exchanger with oblate tube, wherein: the angle that the lead angle between described adjacent two spiral flat tubes staggers is 60 when spending: the cross section of the major axis of each adjacent spiral flat tube is mutual state triangular in shape in the arbitrary section of said tube bank.
Above-mentioned pure adverse current shell-and-tube heat exchanger with oblate tube, wherein: the angle that the lead angle at relative position staggers between described adjacent two spiral flat tubes is incomplete same.
Above-mentioned pure adverse current shell-and-tube heat exchanger with oblate tube, wherein: the import and export of described shell side and tube side are arranged according to countercurrent heat exchange method.
Because the utility model has adopted above technical scheme; The technique effect of its generation is tangible: because each spiral flat tube adopts alternate angle to arrange, making respectively, therefore the tube pitch between the pipe makes structure compact more less than the length of flat tube major axis; Can reduce heat exchanger volume; Increased the surface film thermal conductance of shell side, improved heat exchange efficiency, also made the design of spiral flat tube cast more flexible; Owing to adopt the arrangement form of pure adverse current, can increase effective heat transfer temperature difference greatly, improve heat exchange efficiency.
Description of drawings
Fig. 1 is the cross sectional arrangement figure of existing heat exchanger with oblate tube bank, and wherein a is the sketch map in a cross section, and b is the sketch map in another cross section.
Fig. 2 is the general structure sketch map (part is analysed and observe) of the pure adverse current shell-and-tube heat exchanger with oblate tube of the utility model.
Fig. 3 has shown the wherein structural representation of a spiral flat tube that constitutes the tube bank of the pure adverse current shell-and-tube heat exchanger with oblate tube of the utility model.
Fig. 4 is the structural representation of a kind of embodiment that adjacent spiral flat tube is arranged in the tube bank of the pure adverse current shell-and-tube heat exchanger with oblate tube of the utility model.
Fig. 5 is the tube bank cross sectional arrangement figure of an embodiment of the pure adverse current shell-and-tube heat exchanger with oblate tube of the utility model, and wherein a is the sketch map in a cross section, and b is the sketch map in another cross section.
Fig. 6 is the tube bank cross sectional arrangement figure of another embodiment of the pure adverse current shell-and-tube heat exchanger with oblate tube of the utility model, and wherein a is the sketch map in a cross section, and b is the sketch map in another cross section.
The specific embodiment
Below in conjunction with concrete embodiment and accompanying drawing the structure of the utility model is done further to specify.
See also Fig. 2, Fig. 2 is the structural representation (part is analysed and observe) of the utility model.The utility model comprises bobbin carriage 1, fixed tube sheet 2, shell side inlet 3, housing 4, heat exchanger tube tube bank 5, cranse 6, tube side inlet 7, tube side outlet 8, shell side outlet 9.Bobbin carriage 1 is assembled in the end of housing 4, and housing 4 is provided with shell side inlet 3 and shell side outlet 9, and bobbin carriage is provided with tube side import 7 and tube side outlet 8, presses reflux type and arranges.Described tube bank 5 places in the housing 4, and said tube bank is closely arranged by a plurality of spiral flat tubes and constituted, and the tube bank two ends are fixed on the fixed tube sheet 2, and tube bank is peripheral with some cranse 6 bandings.Said heat exchanger with oblate shell side is not provided with deflector, and the import and export of shell side and tube side are according to reverse layout, and arrangement form satisfies complete countercurrent flow; Said tube bank from peripheral banding, can effectively prevent vibration by some cranses.
See also Fig. 3, Fig. 3 has shown the wherein structural representation of a spiral flat tube 100 that constitutes the tube bank of the utility model heat exchanger.Be connected with fixed tube sheet for ease, the two ends of spiral flat tube respectively keep a segment length and for example are the pipe section 101 of 200mm.Visible by figure, along with the difference of the helical angle of spiral flat tube, the angle of inclination of the major axis that this cross section, place shows is also different, and A is a major axis among the figure, and B is a minor axis.
See also Fig. 4, Fig. 4 is the structural representation of a kind of embodiment of the adjacent spiral flat tube arrangement of the utility model.Three spiral flat tubes 201,202,203 have only been shown among the figure; Second spiral flat tube 202 and adjacent two spiral flat tubes 201, helical angle certain angle that staggered wherein at relative position between 203; Make each spiral flat tube when each spiral flat tube closely contacts the outer rim helix some be embedded in the helicla flute of adjacent spiral flat tube; In helicla flute, form the periodic points contact, force to stream passage thereby outside pipe, form.When each spiral flat tube closely contacted, the tube pitch between adjacent two spiral flat tubes was less than the length of the major axis of each spiral flat tube.The angle that the lead angle at relative position staggers between described adjacent two spiral flat tubes is for extremely spending less than 180 greater than 0 degree.
See also Fig. 5, Fig. 5 is the tube bank cross sectional arrangement figure of an embodiment of the pure adverse current shell-and-tube heat exchanger with oblate tube of the utility model.For example be made up of a plurality of spiral flat tubes, each spiral flat tube is by one
φThe 19mm pipe processes, its pitch
SWith equivalent diameter
d e The ratio
S/
d e Span be 6～12, wherein the span of major axis A is 22～26mm, the scope of the ratio B/A of short major axis is 0.25～0.63.The spiral flat tube of selecting among this embodiment is of a size of: major axis A=25mm, minor axis B=8.5mm, pitch
S=150mm, the ratio B/A=0.34 of short major axis, pitch
SWith equivalent diameter
d e The ratio
S/
d e =11.37.During arrangement; The helical angle at each relative position of described every adjacent two said spiral flat tubes staggers; The angle that staggers is identical, make each spiral flat tube when each spiral flat tube closely contacts the outer rim helix some be embedded in the helicla flute of adjacent spiral flat tube.In this embodiment, on any cross section, the major axis of adjacent tube bank is vertical each other, is 90 ° of angles.Lean on a point of major axis to contact to form between the spiral flat tube and support, make tube pitch between adjacent two spiral flat tubes less than the length of the major axis of each spiral flat tube.Tube pitch is less than major axis.Among this embodiment, compare with existing heat exchanger with oblate, under the constant situation of tube side area, make the shell side circulation area reduce 35%, the structure of heat exchanger is also compact more, and the diameter of heat exchanger reduces 15%.
See also Fig. 6, Fig. 6 is the tube bank cross sectional arrangement figure of another embodiment of the pure adverse current shell-and-tube heat exchanger with oblate tube of the utility model.In this embodiment, said spiral flat tube by
φThe pipe of 25mm is processed into, and the span of each its major axis A of spiral flat tube is 28～34mm, and the scope of the ratio B/A of short major axis is 0.27～0.7.In the present embodiment, on any cross section that constitutes tube bank, between two adjacent arbitrarily pipes, the direction of major axis is all inequality, is 60 ° of angles in twos and intersects, and arranges for equilateral triangle, and among this embodiment, tube pitch is less than major axis.This instance can make the shell side circulation area reduce 15% under the constant situation of tube side area, and the diameter of heat exchanger reduces 8%.
The angle that the lead angle at relative position staggers between described adjacent two spiral flat tubes of the utility model also can be incomplete same.
The utlity model has the advantage that heat exchanger volume is little, heat transfer efficiency is high, less scaling and applied widely.
Claims (8)
1. pure adverse current shell-and-tube heat exchanger with oblate tube, comprise the housing that is provided with the shell side entrance and exit, be assembled in heat exchanger tube tube bank in the housing, be used for fixing tube bank fixed tube sheet, be assembled in shell end and be provided with the bobbin carriage of tube side gateway; Said tube bank is closely arranged by the identical spiral flat tube of some shapes and is constituted; It is characterized in that: the angle of the lead angle at the relative position of two whenever adjacent spiral flat tubes staggers; Make each spiral flat tube when each spiral flat tube closely contacts the outer rim helix some be embedded in the helicla flute of adjacent spiral flat tube; In helicla flute, form the periodic points contact, force to stream passage thereby outside pipe, form.
2. pure adverse current shell-and-tube heat exchanger with oblate tube according to claim 1 is characterized in that: when each spiral flat tube closely contacted, the tube pitch between adjacent two spiral flat tubes was less than the length of the major axis of each spiral flat tube.
3. pure adverse current shell-and-tube heat exchanger with oblate tube according to claim 1 is characterized in that: the angle that the lead angle at relative position staggers between described adjacent two spiral flat tubes is for extremely spending less than 180 greater than 0 degree.
4. pure adverse current shell-and-tube heat exchanger with oblate tube according to claim 1 is characterized in that: the angle that the lead angle at relative position staggers between described adjacent two spiral flat tubes is identical.
5. according to claim 3 or 4 described pure adverse current shell-and-tube heat exchanger with oblate tube; It is characterized in that: the angle that the lead angle between described adjacent two spiral flat tubes staggers is 90 when spending, and the cross section of the major axis of each adjacent spiral flat tube is orthogonal in the said tube bank cross section.
6. according to claim 3 or 4 described pure adverse current shell-and-tube heat exchanger with oblate tube, it is characterized in that: the angle that the lead angle between described adjacent two spiral flat tubes staggers is 60 when spending: the cross section of the major axis of each adjacent spiral flat tube is mutual state triangular in shape in the cross section of said tube bank.
7. pure adverse current shell-and-tube heat exchanger with oblate tube according to claim 1 is characterized in that: the angle that the lead angle at relative position staggers between described adjacent two spiral flat tubes is incomplete same.
8. pure adverse current shell-and-tube heat exchanger with oblate tube according to claim 1, it is characterized in that: the import and export of described shell side and tube side are arranged according to countercurrent heat exchange method.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011205584646U CN202420236U (en) | 2011-12-28 | 2011-12-28 | Pure counterflow tube shell type helical flat tube heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011205584646U CN202420236U (en) | 2011-12-28 | 2011-12-28 | Pure counterflow tube shell type helical flat tube heat exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202420236U true CN202420236U (en) | 2012-09-05 |
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ID=46744993
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011205584646U Expired - Lifetime CN202420236U (en) | 2011-12-28 | 2011-12-28 | Pure counterflow tube shell type helical flat tube heat exchanger |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN202420236U (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103925812A (en) * | 2014-04-25 | 2014-07-16 | 北京迪威尔石油天然气技术开发有限公司 | Core-pulling pure counterflow heat exchanger and heat exchange method using same |
| CN105674770A (en) * | 2016-04-05 | 2016-06-15 | 中国科学院上海高等研究院 | Shell and tube heat exchanger for exchanging heat of fused salts with different temperatures |
| CN105841522A (en) * | 2016-04-05 | 2016-08-10 | 中国科学院上海高等研究院 | Molten salt heat exchanger for intelligently controlling heat exchange flowing speed |
| CN107941048A (en) * | 2017-11-22 | 2018-04-20 | 江苏迈克化工机械有限公司 | A kind of heat exchanger suitable for the heat exchange of high/low temperature lye |
| CN109506488A (en) * | 2018-12-28 | 2019-03-22 | 广东万和热能科技有限公司 | Burnt gas wall hanging furnace and condensing heat exchanger |
| CN109579566A (en) * | 2019-01-17 | 2019-04-05 | 西安交通大学 | A kind of spiral flat tube cast deflection rod heat exchanger |
| CN110657691A (en) * | 2019-10-23 | 2020-01-07 | 华南理工大学 | Anti-freezing and anti-blocking LNG cold energy utilization enhanced heat transfer device |
-
2011
- 2011-12-28 CN CN2011205584646U patent/CN202420236U/en not_active Expired - Lifetime
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103925812A (en) * | 2014-04-25 | 2014-07-16 | 北京迪威尔石油天然气技术开发有限公司 | Core-pulling pure counterflow heat exchanger and heat exchange method using same |
| CN103925812B (en) * | 2014-04-25 | 2016-06-29 | 北京迪威尔石油天然气技术开发有限公司 | A kind of pure contra-flow heat exchanger loosed core and the heat-exchange method applying this heat exchanger |
| CN105674770A (en) * | 2016-04-05 | 2016-06-15 | 中国科学院上海高等研究院 | Shell and tube heat exchanger for exchanging heat of fused salts with different temperatures |
| CN105841522A (en) * | 2016-04-05 | 2016-08-10 | 中国科学院上海高等研究院 | Molten salt heat exchanger for intelligently controlling heat exchange flowing speed |
| CN107941048A (en) * | 2017-11-22 | 2018-04-20 | 江苏迈克化工机械有限公司 | A kind of heat exchanger suitable for the heat exchange of high/low temperature lye |
| CN109506488A (en) * | 2018-12-28 | 2019-03-22 | 广东万和热能科技有限公司 | Burnt gas wall hanging furnace and condensing heat exchanger |
| CN109506488B (en) * | 2018-12-28 | 2024-02-13 | 广东万和热能科技有限公司 | Gas wall-mounted furnace and condensing heat exchanger |
| CN109579566A (en) * | 2019-01-17 | 2019-04-05 | 西安交通大学 | A kind of spiral flat tube cast deflection rod heat exchanger |
| CN110657691A (en) * | 2019-10-23 | 2020-01-07 | 华南理工大学 | Anti-freezing and anti-blocking LNG cold energy utilization enhanced heat transfer device |
| CN110657691B (en) * | 2019-10-23 | 2024-04-12 | 华南理工大学 | Anti-freezing and anti-blocking LNG cold energy utilization enhanced heat transfer device |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| ASS | Succession or assignment of patent right |
Owner name: SHANGHAI QIYAO TECHNOLOGY GROUP CO., LTD. Free format text: FORMER OWNER: THE 711TH RESEARCH INSTITUTE OF CHINA SHIPBUILDING INDUSTRIAL CORPORATION(CSIC) Effective date: 20150318 |
|
| C41 | Transfer of patent application or patent right or utility model | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20150318 Address after: 201108 Shanghai city Minhang District Huaning Road No. 3111 building second Patentee after: SHANGHAI QIYAO TECHNOLOGY GROUP CO., LTD. Address before: 201108 Shanghai city Minhang District Huaning Road No. 3111 Patentee before: The 711th Research Institute of China Shipbuilding Industrial Corporation(CSIC) |
|
| EE01 | Entry into force of recordation of patent licensing contract |
Assignee: SHANGHAI QIYAO THERMAL ENGINEERING CO., LTD. Assignor: SHANGHAI QIYAO TECHNOLOGY GROUP CO., LTD. Contract record no.: 2015990000233 Denomination of utility model: Pure counterflow tube shell type helical flat tube heat exchanger Granted publication date: 20120905 License type: Exclusive License Record date: 20150511 |
|
| LICC | Enforcement, change and cancellation of record of contracts on the licence for exploitation of a patent or utility model | ||
| ASS | Succession or assignment of patent right |
Owner name: SHANGHAI QIYAO THERMAL POWER ENGINEERING CO., LTD. Free format text: FORMER OWNER: SHANGHAI QIYAO TECHNOLOGY GROUP CO., LTD. Effective date: 20150715 |
|
| C41 | Transfer of patent application or patent right or utility model | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20150715 Address after: 201108 Shanghai city Minhang District Huaning Road No. 3111 Building 1 floor 2 Patentee after: SHANGHAI QIYAO THERMAL ENGINEERING CO., LTD. Address before: 201108 Shanghai city Minhang District Huaning Road No. 3111 building second Patentee before: SHANGHAI QIYAO TECHNOLOGY GROUP CO., LTD. |
|
| EC01 | Cancellation of recordation of patent licensing contract |
Assignee: SHANGHAI QIYAO THERMAL ENGINEERING CO., LTD. Assignor: SHANGHAI QIYAO TECHNOLOGY GROUP CO., LTD. Contract record no.: 2015990000233 Date of cancellation: 20150702 |
|
| LICC | Enforcement, change and cancellation of record of contracts on the licence for exploitation of a patent or utility model | ||
| CX01 | Expiry of patent term |
Granted publication date: 20120905 |
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| CX01 | Expiry of patent term |