CN104019679B - Spiral grooved tube reverse-winding formula heat exchanger and variable-flow spiral grooved tube cooling device - Google Patents
Spiral grooved tube reverse-winding formula heat exchanger and variable-flow spiral grooved tube cooling device Download PDFInfo
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- CN104019679B CN104019679B CN201410268850.XA CN201410268850A CN104019679B CN 104019679 B CN104019679 B CN 104019679B CN 201410268850 A CN201410268850 A CN 201410268850A CN 104019679 B CN104019679 B CN 104019679B
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Abstract
The present invention relates to a kind of spiral grooved tube reverse-winding formula heat exchanger, the helicla flute that the two ends comprising housing and be located at enclosure interior are fixed on tube sheet is restrained, described housing is provided with tube side import, tube side outlet, shell side import, shell-side outlet, described helicla flute tube bank forms by being wound in spiral helicine spiral grooved tube with one heart, and every helical layer barrel adopts many spiral grooved tubes to be wound around in the same way; The groove of wherein said spiral grooved tube is located at the outer surface of spiral grooved tube, and its direction of rotation is contrary with the winding direction of corresponding spiral grooved tube.Beneficial effect of the present invention is: the groove direction of rotation of described spiral grooved tube is contrary with the winding direction of corresponding spiral grooved tube, this special construction greatly changes the flow regime of fluid, tube fluid is constantly forced to change direction in advance process, do centrifugal motion, rate of flow of fluid improves, form strong turbulent flow and Secondary Flow effect, this can ensure the enhanced heat transfer in pipe.
Description
Technical field
The invention belongs to convection heat transfer' heat-transfer by convection, energy-saving and cost-reducing fluid heat transfer technical field, be specifically related to a kind ofly can regulate heat transferring medium flow in real time and the less variable-flow spiral grooved tube cooling device of convection transfer rate difference inside and outside helix tube, and a kind of spiral grooved tube reverse-winding formula heat exchanger.
Background technology
Traditional shell-and-tube heat exchanger heat exchanger tube limited length, the heat exchange area arranged in unit volume is less; The safe operation of equipment is often limited to the maximum operating temperature of heat transferring medium, and whether can go out to advise flow blind angle uniform flow sharp fall district, causes heat-transfer surface to cause thermal stress damage because Local Heat Transfer is uneven; During equipment longtime running, restrain easy fouling, and not easy cleaning.
Spiral winding tube type heat exchanger can make up above-mentioned deficiency to a certain extent, has heat exchange property good, the uniform advantage of Working fluid flow.But with regard to existing spiral winding tube type heat exchanger, on the one hand, the flow of heat transferring medium can not regulate in real time, cannot adapt to the dynamic change of cooling load, and the real-time district realizing cooling load joins; On the other hand, in existing spiral winding tube type heat exchanger tube bank, the heat exchange property difference of outer fluid is comparatively large, and the overall heat transfer effect of heat-transfer surface improves not obvious.Therefore, existing wrap-round tubular heat exchanger lacks the dynamic adaptability of heat exchange load, and performance driving economy is poor, is difficult to meet energy-saving and cost-reducing requirements at the higher level.
Summary of the invention
For the weak point existed in the problems referred to above, the invention provides a kind of can by realizing the spiral grooved tube reverse-winding formula heat exchanger of enhanced heat exchange in shell-side with spiral grooved tube, to improve the heat convection efficiency of extratubal fluid.In addition, provide a kind of variable-flow spiral grooved tube cooling device, to realize the real-time matching cooling (or heating) load.
The present invention is achieved through the following technical solutions, a kind of spiral grooved tube reverse-winding formula heat exchanger, the helicla flute that the two ends comprising housing and be located at enclosure interior are fixed on tube sheet is restrained, described housing is provided with tube side import, tube side outlet, shell side import, shell-side outlet, described helicla flute tube bank forms by being wound in spiral helicine spiral grooved tube with one heart, and every helical layer barrel adopts many spiral grooved tubes to be wound around in the same way; The groove of wherein said spiral grooved tube is located at the outer surface of spiral grooved tube, and its direction of rotation is contrary with the winding direction of corresponding spiral grooved tube.
The center of restraining at described helicla flute is provided with core body, and core body at least one end is fixed on tube sheet, for preventing from flowing in the housing short circuit, thus improving cooling effectiveness, making cooling more abundant.
The odd-level of described spiral grooved tube is preferably contrary with even level winding direction, makes fluid form turbulent flow in this gap.
Be equipped with deflection plate between described adjoining spiral barrel, deflection plate can improve the flow condition of shell-side fluid, solves the problem that tube side shell side convection transfer rate difference is larger preferably, guarantees that the overall heat transfer performance of wrap-round tubular heat exchanger significantly improves; Described deflection plate is preferably segmental baffle, and segmental baffle has perturbation action to shell-side fluid, and effectively can promote turbulent flow and strengthening shell-side heat transfer, heat transfer efficiency is high, and flow resistance is little.
Described deflection plate adopts snap fit to be connected between adjoining spiral barrel, being specially its mounting means can adopt two ends to be welded with half-round tubular buckle and buckle both sides flange with holes, and buckle is buckled in embrace on helix tube outer wall and by the bolt that second half half-round tubular buckle and flange are installed and buckles on the coil.
Described housing adopts casting aluminium material, reduces cooling device weight, reduces production cost.
The groove of described spiral grooved tube equidistantly arranges.
In order to realize the real-time adjustment of heat exchanging load, the present invention also provides a kind of variable-flow helix tube cooling device adopting said spiral wrap-round tubular heat exchanger, comprise spiral winding tube type heat exchanger, also comprise temperature sensor, control system, variable-frequency motor and the pump driven by variable-frequency motor, described temperature sensor is arranged on the tube side export pipeline of described spiral winding tube type heat exchanger, the output of described temperature sensor is connected with the input of described control system, the input of described variable-frequency motor is connected with the output of described control system, described delivery side of pump is connected with the shell side import of described spiral winding tube type heat exchanger.
Beneficial effect of the present invention is:
1, helicla flute tube bank interlayer replaces reverse-winding, form strong turbulent flow and Secondary Flow effect, not only can promote that fluid constantly destroys boundary layer in flow process, strengthen disturbance, the turbulivity of fluid media (medium) is strengthened, reduce the deposition probability of dirt, reduce possibility and fouling tendency that outer fluid in spiral grooved tube adheres at wall; And helix tube is wound around four to six times that the length of restraining can reach shell length, greatly can increase cold and hot media for heat exchange area, improves the compactedness of cooler.
2, spiral grooved tube reverse-winding between layers, and it is contrary with the direction of rotation of every helical layer barrel groove, this special construction greatly changes the flow regime of fluid, tube fluid is constantly forced to change direction in advance process, do centrifugal motion, rate of flow of fluid improves, and form strong turbulent flow and Secondary Flow effect, this can ensure the enhanced heat transfer in pipe.
3, the fluid in spiral grooved tube outer surface groove is constantly separated and converges between adjacent heat exchanger tube, and existing rotary motion, has again longitudinal disturbance, and the turbulivity of medium is strengthened, namely can enhanced heat exchange, can reduce and deposit probability and fouling tendency.
Accompanying drawing explanation
Fig. 1 is structural representation of the present invention.
Fig. 2 is that the C-C of Fig. 1 is to sectional view.
Fig. 3 is the partial enlarged drawing of spiral grooved tube outer surface.
Fig. 4 is the flow control system schematic diagram of cooling device.
1. housing; 2. spiral grooved tube; 3. core body; 4. deflection plate; 5. groove
The import of 1-1. tube side; 1-2. tube side exports; The import of 1-3. shell side; 1-4. shell-side outlet
Detailed description of the invention
Not to be further explained the present invention with specific embodiment by reference to the accompanying drawings.
Embodiment 1:
Fig. 1 shows the structure of the preferred embodiment of a kind of spiral grooved tube reverse-winding formula heat exchanger of the present invention, for carrying out water cooling to lubrication wet goods fluid.
As shown in Figure 1, a kind of spiral grooved tube reverse-winding formula heat exchanger, the helicla flute that the two ends comprising housing 1 and be located at enclosure interior are fixed on tube sheet is restrained, described housing 1 is provided with tube side import 1-1, tube side outlet 1-2, shell side import 1-3, shell-side outlet 1-4, composition graphs 2 can be found out, helicla flute tube bank is formed by being wound in spiral helicine 6 helical layer barrels 2 with one heart, every helical layer barrel 2 all adopt many spiral grooved tubes 2 be wound around in the same way described helicla flute tube bank form by being wound in spiral helicine spiral grooved tube 2 with one heart, every helical layer barrel 2 adopts many spiral grooved tubes 2 to be wound around in the same way, the groove 5 of wherein said spiral grooved tube 2 is located at the outer surface of spiral grooved tube 2, its concrete structure can reference diagram 3, its direction of rotation is contrary with the winding direction of corresponding spiral grooved tube 2, and equidistantly arrange at spiral grooved tube outer surface, because its direction of rotation is contrary with the winding direction of corresponding spiral grooved tube 2, fluid flow direction herein can be disturbed, be forced to again change flow direction, form more strong turbulent flow and Secondary Flow, pipe outer wall fluid boundary layer by constantly thinning and destroy, finally reach the object strengthening convection heat transfer' heat-transfer by convection, thus raising heat transfer efficiency.
Composition graphs 2 can be found out, in this embodiment, every helical layer barrel 2 quantity is from outside to inside 14,12,10,8,6,4.
The layout of each group deflection plate as shown in Figure 2, is provided with polylith deflection plate 4 between layers at spiral grooved tube 2.In embodiment shown in Fig. 2, spiral grooved tube totally 6 layers from outside to inside, forms gap between 5 layers of ring pipe between 6 helical layer pipes, therefore deflection plate 4 totally 5 layers from outside to inside, and in this embodiment, every layer of deflection plate 4 has 4 pieces, and therefore often group has 20 pieces of deflection plates 4.The dispersed arrangement form that this deflection plate breaks the whole up into parts solves the problem adopting traditional structure deflection plate and mounting means thereof can not be applied to spiral winding tube type heat exchanger.
If all spiral grooved tube winding directions are identical, its guide functions can make shell-side fluid flow trace be spirality, and its effect is better than traditional shell heat exchanger traverse baffle.The present invention is as preferred forms, and odd-level is contrary with the winding direction of even level spiral grooved tube 2, and such as odd-level is left-handed, even level dextrorotation.Such odd-level is contrary to the guide direction of fluid with even level, and improve the flow-disturbing effect of fluid flowing further, form turbulent flow, pipe outer wall fluid boundary layer is thinned and destroys, and reaches than being wound around better strengthening convection heat transfer' heat-transfer by convection effect in the same way.
Because adjacent layer spiral grooved tube 2 winding direction is contrary, therefore the buckle at deflection plate two ends deflects certain angle mutually, and deflection plate adopts to reverse and forms twisted shape (with the hand of spiral consistent) covering of the fan the same with screw accordingly.So not only produce flow-disturbing effect to shell-side fluid along heat exchanger length direction, also to the raw flow-disturbing effect of radial direction miscarriage, disturbance is more violent.
Owing in the middle part of innermost layer spiral grooved tube 2 being a hole being roughly circle, and due to processing problems innermost layer helix tube coiling diameter unsuitable too small, the middle circular tube shaped runner formed is unfavorable for convection heat transfer' heat-transfer by convection, therefore as shown in Fig. 1-2,1-3, described helical bundle center is provided with core body 3, and core body 3 one or both ends are fixed on tube sheet.Core body 3 prevents from flowing within the case 1 short circuit, thus improves cooling effectiveness, makes cooling more abundant.
Comparative example 1:
Do not have the helix tube of groove to contrast under the same conditions the present invention and surface, find that heat transfer efficiency of the present invention does not comparatively have the helix tube of groove to significantly improve, improve 70%;
Comparative example 2:
Have the spiral tube seat of groove to contrast under the same conditions the present invention and surface, lower be that the direction of rotation of groove is consistent with the winding direction of spiral tube seat, find that heat transfer efficiency of the present invention improves compared with the spiral grooved tube consistent with groove direction of rotation, improve 40%.
The project organization of spiral grooved tube improves heat transfer efficiency largely by above comparative example 1 and 2 also sufficient proof, saves financial cost.
Embodiment 2 variable-flow helix tube reverse-winding formula cooling device
As shown in Figure 4, be a kind of variable-flow spiral grooved tube cooling device, Spiral-tube Heat Exchanger adopts the structure of embodiment 1.
The pump that cooling device comprises spiral tube exchanger, temperature sensor, control system, variable-frequency motor and driven by variable-frequency motor, temperature sensor is arranged on the tube side export pipeline of described spiral winding tube type heat exchanger, the output of described temperature sensor is connected with the input of described control system, the input of described variable-frequency motor is connected with the output of described control system, and described delivery side of pump is connected with the shell side import of described spiral winding tube type heat exchanger.
The temperature of wrap-round tubular heat exchanger tube side outlet is measured by temperature sensor, temperature sensor is uploaded to control system after temperature being measured, control system controls the rotating speed of variable-frequency motor, and variable-frequency motor regulates the output water yield of pump, and the inflow of wrap-round tubular heat exchanger is changed.Like this, can the temperature of field monitoring fluid, according to the dynamic change of cooling load in running, by frequency-converting speed-governing control system realization to the monitoring of cooling medium consumption and adjustment, the flow of real-time matching cooling medium, realize energy-saving and cost-reducing, reach object that is efficient, reliable, stable operation.
Only as described above, be only preferred embodiment of the present invention, such as professional who are familiar with this art.After understanding technological means of the present invention, natural energy, according to actual needs, is changed under the teachings of the present invention.Therefore all equal changes of doing according to the present patent application the scope of the claims and modification, all should still remain within the scope of the patent.
Claims (8)
1. a spiral grooved tube reverse-winding formula heat exchanger, it is characterized in that: the helicla flute that the two ends comprising housing and be located at enclosure interior are fixed on tube sheet is restrained, described housing is provided with tube side import, tube side outlet, shell side import, shell-side outlet, described helicla flute tube bank forms by being wound in spiral helicine spiral grooved tube with one heart, and every helical layer barrel adopts many spiral grooved tubes to be wound around in the same way; The groove of wherein said spiral grooved tube is located at the outer surface of spiral grooved tube, and its direction of rotation is contrary with the winding direction of corresponding spiral grooved tube; Also deflection plate is equipped with between described adjoining spiral barrel.
2. spiral grooved tube reverse-winding formula heat exchanger as claimed in claim 1, it is characterized in that: the center of restraining at described helicla flute is provided with core body, core body at least one end is fixed on tube sheet.
3. spiral grooved tube reverse-winding formula heat exchanger as claimed in claim 1, is characterized in that: the odd-level of described spiral grooved tube is contrary with even level winding direction.
4. spiral grooved tube reverse-winding formula heat exchanger as claimed in claim 1, is characterized in that: described deflection plate is segmental baffle.
5. spiral grooved tube reverse-winding formula heat exchanger as claimed in claim 1, is characterized in that: described deflection plate adopts snap fit to be connected between adjoining spiral barrel.
6. spiral grooved tube reverse-winding formula heat exchanger as claimed in claim 1, is characterized in that: described housing adopts casting aluminium material.
7. spiral grooved tube reverse-winding formula heat exchanger as claimed in claim 1, is characterized in that: the groove of described spiral grooved tube equidistantly arranges.
8. one kind adopts the variable-flow spiral grooved tube cooling device of above spiral grooved tube reverse-winding formula heat exchanger arbitrarily described in claim, it is characterized in that, comprise spiral grooved tube reverse-winding formula heat exchanger, temperature sensor, control system, variable-frequency motor, by the water pump that variable-frequency motor drives, described temperature sensor is positioned on the tube side export pipeline of described spiral grooved tube reverse-winding formula heat exchanger, the output of described temperature sensor is connected with the input of described control system, the input of affiliated variable-frequency motor is connected with the output of described control system, described delivery side of pump is connected with the shell side import of described spiral grooved tube reverse-winding formula heat exchanger.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201410268850.XA CN104019679B (en) | 2014-06-16 | 2014-06-16 | Spiral grooved tube reverse-winding formula heat exchanger and variable-flow spiral grooved tube cooling device |
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| CN201410268850.XA CN104019679B (en) | 2014-06-16 | 2014-06-16 | Spiral grooved tube reverse-winding formula heat exchanger and variable-flow spiral grooved tube cooling device |
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| CN104019679B true CN104019679B (en) | 2016-03-23 |
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| CN109876561A (en) * | 2019-03-18 | 2019-06-14 | 合肥合意环保机电装备制造有限公司 | A kind of deduster water cooled pipeline |
| CN115183602A (en) * | 2022-07-18 | 2022-10-14 | 中国矿业大学 | Spiral winding structure and external application type heat exchange device |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| GB1116537A (en) * | 1965-08-05 | 1968-06-06 | Cvi Corp | Heat exchangers |
| JPS59118223A (en) * | 1982-12-23 | 1984-07-07 | Mitsubishi Heavy Ind Ltd | Manufacture of heat-transmitting tube |
| CN201032427Y (en) * | 2007-04-10 | 2008-03-05 | 新疆昌晟源换热设备有限公司 | Winding type screwed conduit casing heat exchanger |
| CN102478371A (en) * | 2010-11-29 | 2012-05-30 | 李文涛 | Automatic control system of heat exchanger |
| CN103267434A (en) * | 2013-05-23 | 2013-08-28 | 山东豪迈机械制造有限公司 | Detachable spiral winding heat exchanger |
| CN203550678U (en) * | 2013-09-13 | 2014-04-16 | 海安天润机械科技有限公司 | Reverse spiral winding tubular cooler |
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Effective date of registration: 20160205 Address after: 226600, Haiphong Road, Chengdong Town, Haian County, Jiangsu, Nantong, 33 Applicant after: HAIAN TIANRUN MACHINERY TECHNOLOGY CO., LTD. Address before: Eleven Ge Village East of the town of Haian County of Jiangsu Province, Nantong City, 226600 Applicant before: Haian Tianrun Mechanical Technology Co., Ltd. |
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Address after: No.33 Haifang Road, Chengdong Town, Haian City, Nantong City, Jiangsu Province Patentee after: Jiangsu Yuling Machinery Technology Co., Ltd Address before: 226600, Haiphong Road, Chengdong Town, Haian County, Jiangsu, Nantong, 33 Patentee before: HAIAN YU LING MACHINERY TECHNOLOGY Co.,Ltd. |