CN100427872C - Composite reinforced heat-transmission pipe with partition spilt whirl plate and method for enhancement of thermal transmission - Google Patents
Composite reinforced heat-transmission pipe with partition spilt whirl plate and method for enhancement of thermal transmission Download PDFInfo
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- CN100427872C CN100427872C CNB2006100358322A CN200610035832A CN100427872C CN 100427872 C CN100427872 C CN 100427872C CN B2006100358322 A CNB2006100358322 A CN B2006100358322A CN 200610035832 A CN200610035832 A CN 200610035832A CN 100427872 C CN100427872 C CN 100427872C
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- transfer pipe
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Abstract
The present invention provides a composite enhancement heat transfer pipe with swirl sheets which are separately arranged at intervals and a heat transfer enhancement method. The composite enhancement heat transfer pipe comprise a heat transfer pipe body and swirl sheets. The swirl sheets are short twisted strips which have rotary angles in an axial line direction, and the curved surface shapes of the short twisted strips are symmetrical in the radius direction. At least two swirl sheets are arranged in the heat transfer pipe body. Axial spacing is kept between the swirl sheets. The heat transfer enhancement method comprises: when fluid passes through one swirl sheet in the heat transfer pipe body, a spiral flow is formed; subsequently, the self-spiral flow of the spiral flow is kept in the axial spacing of the two swirl sheets by the self movement inertia of the fluid; when the fluid passes through the next swirl sheet, a spiral flow is formed again; the process of the spiral flow and the self-spiral flow of the fluid is repeated in the flow direction. The heat-transfer pipe not only can enhance the heat transfer of the center zone of the heat transfer pipe, but also can avoid the large resistance of a continuous sliver inserter to the body of the fluid. A high convective heat transfer film coefficient can be obtained under the condition of lower fluid resistance in the heat transfer pipe. The composite enhancement heat transfer pipe is suitable for being generally popularized and used in heat transfer industry.
Description
Technical field
The present invention relates to a kind of intensify heat transfer pipe, particularly a kind of interband is every the compound intensified heat-transfer pipe that splits spinning disk.
Background technology
Existing intraductal heat transfer reinforcement technique has multiple, and wherein special-shaped intensify heat transfer pipe also has polytype, the spiral grooved tube that has used in a large number in industry for example, band tube seat and convergent-divergent pipe etc.Insert in the pipe that is provided with in intensify heat transfer pipe also has various ways to strengthen heat-transfer effect, and inserting the owner in the pipe wherein will have continuous long twisted strip, helix, and the alternate flight that is cross-linked of eddy flow direction etc.
General special-shaped intensify heat transfer pipe is used for the augmentation of heat transfer of turbulent fluid more, the main turbulivity augmentation of heat transfer that relies on the rough rib face promotion limit wall fluid of tube wall, situation that this heat transfer resistance for fluid under turbulent-flow conditions mainly concentrates on the Bian Bi district of heat-transfer pipe is effectively to improve the heat transfer property of heat-transfer pipe, but the shortcoming that exists is after the convection heat transfer' heat-transfer by convection thermal resistance of tube wall reduces relatively, the convection heat transfer' heat-transfer by convection thermal resistance in tube hub district increases relatively, and the rough rib face that only relies on tube wall is difficult to the convection heat transfer' heat-transfer by convection of further enhanced tube center, so heat conduction reinforced degree is subjected to certain restriction.
Insert is used for the augmentation of heat transfer of laminar flow or transition flow fluid more in the general pipe, the effect of the eddy flow of main dependence insert convection cell is carried out place-exchange with the fluid of heat-transfer pipe center and the fluid in Bian Bi district, strengthen the convection heat transfer' heat-transfer by convection of center, situation that this heat transfer resistance for fluid under laminar flow or transition flow condition mainly concentrates on the center of heat-transfer pipe is effectively to improve the heat transfer property of heat-transfer pipe, but the shortcoming that exists is that the body resistance of rectangular continuously insert convection cell is very big, generally only be applicable to laminar flow or transition flow, and be not suitable for turbulent-flow conditions.Therefore existing intraductal heat transfer reinforcement technique also exists limitation for turbulent heat transfer.
Summary of the invention
The objective of the invention is to overcome existing coarse ribbed pipe only relies on the rough rib face of tube wall to be difficult to the shortcoming of the convection heat transfer' heat-transfer by convection of further enhanced tube center, a kind of convection heat transfer' heat-transfer by convection film coefficient (more than 10%) that further improves tube fluid under lower fluid resistance condition is provided, obtains the heat-transfer pipe of better heat conduction reinforced effect.
Technical purpose of the present invention can be achieved through the following technical solutions:
Interband is every the compound intensified heat-transfer pipe that splits spinning disk, comprise heat transfer body and spinning disk, described heat transfer body is to have the periodically coarse heat transfer body of concavo-convex rough rib face, it is characterized in that, spinning disk is a kind ofly to have the anglec of rotation and at the short twisted strip of radial direction curve form symmetry along axis direction, be provided with at least 2 spinning disks in the described heat transfer body, keep axial spacing between the spinning disk; The described spinning disk anglec of rotation is 45 degree, 90 degree, 180 degree or 270 degree.
For further realizing purpose of the present invention:
Useful is that with the finer wire connection, steel wire one end is fixed on tube fluid inlet termination between the described spinning disk.
Useful is that described spinning disk is welded on the heat-transfer pipe inwall.
Useful is that the method that described spinning disk compresses with mechanical rolling is fixed on the heat-transfer pipe inwall.
Useful is that described coarse heat transfer body is the spiral grooved tube body, band tube seat body or convergent-divergent pipe body.
Axial spacing between the described spinning disk is 150～1500mm, preferred 400mm.
The relative prior art of the present invention has following advantage and effect: shorter owing to its length by the be separated by spinning disk that splits of certain axial spacing in pipe, the resistance of convection cell is less, and the spin current body resistance at spinning disk tract fluid that utilizes spinning disk to produce is very little, can avoid continuously the body resistance of rectangular insert convection cell very big, generally only be applicable to laminar flow or transition flow, and be not suitable for the disadvantage of turbulent-flow conditions, the fluid spin current that is produced by spinning disk has the effect of enhanced tube inner fluid center convection heat transfer' heat-transfer by convection simultaneously, can overcome special-shaped intensify heat transfer pipe only relies on rough rib face to be difficult to the shortcoming of the convection heat transfer' heat-transfer by convection of further enhanced tube center, can under lower fluid resistance condition, further improve the convection heat transfer' heat-transfer by convection film coefficient (more than 10%) of tube fluid, obtain better heat conduction reinforced effect.
Description of drawings
Fig. 1 is the front view of spinning disk;
Fig. 2 is the shaft side figure of spinning disk;
Fig. 3 is the vertical view of spinning disk;
Fig. 4 is the left view of spinning disk;
Fig. 5 is that embodiment 1 interband is every the compound intensified heat-transfer pipe schematic diagram that splits spinning disk;
Fig. 6 is that embodiment 2 interbands are every the compound intensified heat-transfer pipe schematic diagram that splits spinning disk;
Fig. 7 is that embodiment 3 interbands are every the compound intensified heat-transfer pipe schematic diagram that splits spinning disk.
The specific embodiment
The present invention is described in further detail below in conjunction with embodiment and accompanying drawing, but embodiments of the invention are not limit therewith.
Embodiment 1
Fig. 5 shows interband of the present invention every a kind of version of compound intensified heat-transfer pipe that splits spinning disk.As shown in Figure 3, interband comprises heat transfer body 2 every the compound intensified heat-transfer pipe that splits spinning disk, spinning disk 1, finer wire 3, and heat transfer body 2 is the plain tube body.As Fig. 1,2,3, shown in 4, spinning disk 1 has the 45 degree anglecs of rotation and at the short twisted strip of radial direction curve form symmetry for a kind of along axis direction, in heat transfer body 2, keep axial spacing between the spinning disk, specifically be, spinning disk 1 splits installation at interval in the pipe of heat transfer body 2, have 4 spinning disks, the heat-transfer pipe body diameter is 20mm, and internal diameter of tube body is 16mm, and body is long to be 2m, the spinning disk spacing distance is all 400mm, spinning disk length is 30mm, and width is 15.5mm, and thickness is 1mm, spinning disk adopts φ 1mm finer wire 3 to be connected each other, and fixation with steel wire is at the arrival end 4 of tube fluid.During application, fluid enters from heat transfer body 2 arrival ends 4, in heat transfer body 2, during through a spinning disk 1, form spiral flow, afterwards, spiral flow relies on the motional inertia of fluid self to keep spin current in the spacing of two spinning disks 1, fluid forms spiral flow again during through next spinning disk 1 again, and the fluid streamwise repeats the process of described spiral flow and spin current, at last, fluid flows out from the heat-transfer pipe port of export.After testing, this interband improves 6% every the heat conduction reinforced multi-stress of the compound intensified heat-transfer pipe that splits spinning disk than normal optical slip pipe
Fig. 6 shows another kind of interband of the present invention every the compound intensified heat-transfer tubular construction form that splits spinning disk.As shown in Figure 6, interband comprises heat transfer body 2 (for the convergent-divergent body), spinning disk 1 every the compound intensified heat-transfer pipe that splits spinning disk.Spinning disk is a kind ofly to have the 60 degree anglecs of rotation and at the short twisted strip of radial direction curve form symmetry, keep axial spacing between each spinning disk in convergent-divergent body 2 along axis direction.Specifically be, spinning disk 1 splits installation at interval in the pipe of convergent-divergent body 2, and spinning disk 1 has 8, spinning disk 1 adopts the method for welding to fix with the convergent-divergent inboard wall of tube body, and convergent-divergent body external diameter is 20mm, and the bore that does not have coarse rib section is 16mm, the bore that coarse rib section is arranged is 16/14mm, wherein the minimum tube internal diameter of fin point is 14mm, and rib spacing is 12mm, and pipe range is 2m, the spinning disk spacing distance is 200mm, spinning disk length is 30mm, and width is 14mm, and thickness is 1mm.After testing, this interband has improved 15% every the heat conduction reinforced multi-stress of the compound intensified heat-transfer pipe that splits spinning disk than convergent-divergent pipe.Application process is with embodiment 1.
Embodiment 3
Fig. 7 shows interband of the present invention another version every the compound intensified heat-transfer pipe that splits spinning disk.As shown in Figure 7, this interband comprises heat transfer body 2 (for the band body) every the compound intensified heat-transfer pipe that splits spinning disk, and spinning disk 1, spinning disk 1 split installation at interval in the pipe of band body 2.Shown in Fig. 1,2,3,4, spinning disk is a kind ofly to have the 45 degree anglecs of rotation and at the short twisted strip of radial direction curve form symmetry along axis direction.Band body external diameter is 20mm, the bore that does not have coarse rib section is 16mm, the bore that coarse rib section is arranged is 16/14mm, and wherein the minimum tube internal diameter of fin point is 14mm, and rib spacing is 8mm, pipe range is 2m, the spinning disk spacing distance is 400mm, and spinning disk length is 30mm, and width is 14mm, thickness is 1mm, and the method that spinning disk and inside pipe wall adopt mechanical rolling to compress is fixed.After testing, this interband has improved more than 10% than band pipe every the heat conduction reinforced multi-stress of the compound intensified heat-transfer pipe that splits spinning disk.Application process is with embodiment 1.
Claims (6)
1, interband is every the compound intensified heat-transfer pipe that splits spinning disk, comprise heat transfer body and spinning disk, described heat transfer body is to have the periodically coarse heat transfer body of concavo-convex rough rib face, it is characterized in that, spinning disk is a kind ofly to have the anglec of rotation and at the short twisted strip of radial direction curve form symmetry along axis direction, be provided with at least 2 spinning disks in the described heat transfer body, keep axial spacing between the spinning disk; The described spinning disk anglec of rotation is 45 degree, 90 degree, 180 degree or 270 degree.
2, interband according to claim 1 is characterized in that every the compound intensified heat-transfer pipe that splits spinning disk, connects with finer wire between the described spinning disk, and steel wire one end is fixed on tube fluid inlet termination.
3, interband according to claim 1 is characterized in that every the compound intensified heat-transfer pipe that splits spinning disk, and described spinning disk is welded on the heat-transfer pipe inwall.
4, interband according to claim 1 is characterized in that every the compound intensified heat-transfer pipe that splits spinning disk, and the method that described spinning disk compresses with mechanical rolling is fixed on the heat-transfer pipe inwall.
5, interband according to claim 1 is characterized in that every the compound intensified heat-transfer pipe that splits spinning disk, and described coarse heat transfer body is helicla flute body, band tube seat body or convergent-divergent pipe body.
6, interband according to claim 1 is characterized in that every the compound intensified heat-transfer pipe that splits spinning disk, and the axial spacing between the described spinning disk is 150～1500mm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2006100358322A CN100427872C (en) | 2006-06-07 | 2006-06-07 | Composite reinforced heat-transmission pipe with partition spilt whirl plate and method for enhancement of thermal transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2006100358322A CN100427872C (en) | 2006-06-07 | 2006-06-07 | Composite reinforced heat-transmission pipe with partition spilt whirl plate and method for enhancement of thermal transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1865830A CN1865830A (en) | 2006-11-22 |
| CN100427872C true CN100427872C (en) | 2008-10-22 |
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| Application Number | Title | Priority Date | Filing Date |
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| CNB2006100358322A Expired - Fee Related CN100427872C (en) | 2006-06-07 | 2006-06-07 | Composite reinforced heat-transmission pipe with partition spilt whirl plate and method for enhancement of thermal transmission |
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| CN (1) | CN100427872C (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100498180C (en) * | 2007-07-11 | 2009-06-10 | 华南理工大学 | Rectangular tube bundle heat exchanger adopting swirl plate support and its intensified heat-conduction method |
| US20100307729A1 (en) * | 2009-06-04 | 2010-12-09 | Rocky Research | Firetube heat exchanger |
| CN102759294B (en) * | 2011-04-29 | 2014-07-16 | 中国石油化工股份有限公司 | Reinforced heat transfer pipe with spinning disks |
| CN102706180A (en) * | 2012-05-25 | 2012-10-03 | 南京白云化工环境监测有限公司 | Immersive coil type heat-exchanger |
| CN105571372A (en) * | 2016-02-22 | 2016-05-11 | 大震锅炉工业（昆山）有限公司 | Improved and strengthened heat transfer equipment |
| JP2020016339A (en) * | 2016-10-18 | 2020-01-30 | 株式会社エコラ・テック | Radiator, condenser unit, and refrigeration cycle |
Citations (7)
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|---|---|---|---|---|
| JPS5640095A (en) * | 1979-09-10 | 1981-04-16 | Toyobo Co Ltd | Heat conducting pipe |
| JPS59231397A (en) * | 1983-06-10 | 1984-12-26 | Matsushita Refrig Co | Turbulator |
| CN2089155U (en) * | 1990-08-02 | 1991-11-20 | 上海市红光锅炉厂 | Inserting twist-belt type turbolator for forced heat transfer in pipe |
| US5307867A (en) * | 1992-08-10 | 1994-05-03 | Noritake Co., Limited | Heat exchanger |
| CN1102704A (en) * | 1993-11-10 | 1995-05-17 | 周森泉 | Rotational flow heat exchanger |
| US20030188850A1 (en) * | 2002-04-09 | 2003-10-09 | Honeywell International Inc., | Tubular catalytic aircraft precooler |
| CN1133862C (en) * | 1998-09-16 | 2004-01-07 | 中国石油化工集团公司 | Heat exchange pipe and its manufacture method and application |
-
2006
- 2006-06-07 CN CNB2006100358322A patent/CN100427872C/en not_active Expired - Fee Related
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5640095A (en) * | 1979-09-10 | 1981-04-16 | Toyobo Co Ltd | Heat conducting pipe |
| JPS59231397A (en) * | 1983-06-10 | 1984-12-26 | Matsushita Refrig Co | Turbulator |
| CN2089155U (en) * | 1990-08-02 | 1991-11-20 | 上海市红光锅炉厂 | Inserting twist-belt type turbolator for forced heat transfer in pipe |
| US5307867A (en) * | 1992-08-10 | 1994-05-03 | Noritake Co., Limited | Heat exchanger |
| CN1102704A (en) * | 1993-11-10 | 1995-05-17 | 周森泉 | Rotational flow heat exchanger |
| CN1133862C (en) * | 1998-09-16 | 2004-01-07 | 中国石油化工集团公司 | Heat exchange pipe and its manufacture method and application |
| US20030188850A1 (en) * | 2002-04-09 | 2003-10-09 | Honeywell International Inc., | Tubular catalytic aircraft precooler |
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| CN1865830A (en) | 2006-11-22 |
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