CN102322752B - Heat exchanger - Google Patents
Heat exchanger Download PDFInfo
- Publication number
- CN102322752B CN102322752B CN2011102176832A CN201110217683A CN102322752B CN 102322752 B CN102322752 B CN 102322752B CN 2011102176832 A CN2011102176832 A CN 2011102176832A CN 201110217683 A CN201110217683 A CN 201110217683A CN 102322752 B CN102322752 B CN 102322752B
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- China
- Prior art keywords
- heat exchanger
- shell
- heat
- fluid
- heat exchange
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
- 239000003507 refrigerant Substances 0.000 claims description 8
- 238000005452 bending Methods 0.000 claims description 4
- 238000000034 method Methods 0.000 claims description 4
- 230000001105 regulatory effect Effects 0.000 claims description 3
- 239000012530 fluid Substances 0.000 abstract description 40
- 230000005540 biological transmission Effects 0.000 abstract description 3
- 238000009826 distribution Methods 0.000 abstract description 3
- 230000000694 effects Effects 0.000 abstract description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 11
- 239000007788 liquid Substances 0.000 description 5
- 238000005219 brazing Methods 0.000 description 4
- 238000004378 air conditioning Methods 0.000 description 3
- 238000004134 energy conservation Methods 0.000 description 3
- 238000007710 freezing Methods 0.000 description 3
- 230000008014 freezing Effects 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- 239000000126 substance Substances 0.000 description 2
- 238000009825 accumulation Methods 0.000 description 1
- WYTGDNHDOZPMIW-RCBQFDQVSA-N alstonine Natural products C1=CC2=C3C=CC=CC3=NC2=C2N1C[C@H]1[C@H](C)OC=C(C(=O)OC)[C@H]1C2 WYTGDNHDOZPMIW-RCBQFDQVSA-N 0.000 description 1
- 238000004458 analytical method Methods 0.000 description 1
- 230000009172 bursting Effects 0.000 description 1
- 230000000739 chaotic effect Effects 0.000 description 1
- 239000002826 coolant Substances 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000002950 deficient Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000009776 industrial production Methods 0.000 description 1
- 238000007670 refining Methods 0.000 description 1
- 230000009897 systematic effect Effects 0.000 description 1
- 239000002699 waste material Substances 0.000 description 1
Images
Classifications
-
- 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
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/08—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being otherwise bent, e.g. in a serpentine or zig-zag
- F28D7/082—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being otherwise bent, e.g. in a serpentine or zig-zag with serpentine or zig-zag configuration
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The invention discloses a heat exchanger. The heat exchanger comprises a shell, and the shell is provided with a heat-exchange working medium inlet and a heat-exchange working medium outlet; the inside of the shell is provided with multiple layers of serpentine heat exchange tubes, each serpentine heat exchange tube is provided with a refrigrant inlet and a refrigrant outlet, and the serpentine heat exchange tubes in two adjacent layers are arranged in a staggered mode; and the inside of the shell is also provided with a positioning column for fixing the serpentine heat exchange tubes. According to the invention, the heat exchange tubes between different layers are arranged in a staggered mesh mode, so that the disturbance of fluid beside the shell is greatly increased, and even under the condition that the flow velocity of the fluid is small, the disturbance of fluid flowing around the outsides of the tubes can be effectively strengthened, thereby greatly improving the heat transmission coefficient of the fluid beside the shell and the heat transmission performance of the heat exchanger, and enabling the temperature distribution of the fluid beside the shell to be more uniform; in addition, components such as spoilers and flow guide poles and the like generally used in the prior art are removed, and a mode that the fluid alternately flows beside the shell is changed into a small-resistance mode that the fluid flows around the outsides of the tubes, so that the length of the flow path of the fluid beside the shell is reduced, thereby effectively reducing the flow resistance of the fluid beside the shell, lowering the pump power consumption of a system, and achieving an energy saving effect.
Description
Technical field
The present invention relates to a kind of heat exchanger, especially a kind of surface-type coil heat exchanger that does not contact (for example heat exchange between cold-producing medium-water) for two kinds of fluids.
Background technology
In industrial production, all equipment that is used for realizing the cold fluid and hot fluid exchange heat is referred to as heat exchanger.It all is widely used in many technical fields such as chemical industry, oil refining, atomic energy, building, machinery, traffic.As the heater in Chemical Manufacture, cooler, evaporimeter, condenser, reboiler etc.; The and for example air preheater in Thermal Power Station, steam superheater, condenser and cooling column etc., in order to satisfy the needs of different working conditions, each industrial department adopts diversified heat exchanger.According to the heat exchange mode between cold fluid and hot fluid, heat exchanger can be divided three classes: dividing wall type heat exchanger, contact heat exchanger and heat regenerator.Wherein, dividing wall type heat exchanger is pressed the version of heat-transfer area, is divided into again pipe heat exchanger (as shell-and-tube heat exchanger, coil heat exchanger, double-tube heat exchanger, spray-type heat exchanger, aerial cooler etc.) and plate type heat exchanger (as spiral heat exchanger, plate-type exchanger, plate-fin heat exchanger etc.).
At present, Miniature wind cold (heat) water central air-conditioning unit is due to compact conformation, the cold-producing medium that uses-water-to-water heat exchanger overwhelming majority is brazing plate type heat exchanger, by heat exchange between plate, realize the heat transmission between cold-producing medium and water, and then utilize water pump that cold (heat) water is delivered to the indoor end device.But it is that easy freezing damages that board-like heat exchanger has a fatal shortcoming, after its inner certain plate bursting by freezing, almost can't repair, and often causes scrapping of whole air-conditioning system.In addition, the restriction of the liquid cold-producing medium method of salary distribution between the plate due to brazing plate type heat exchanger causes the modes of emplacement of plate type heat exchanger to be restricted, thereby has affected the utilization in space in unit.
In order to overcome the existing existing intrinsic problem of brazing plate type heat exchanger, usually adopt the version of counterflow pipe coiled heat exchanger, thereby effectively solved the problem of existing brazing plate type heat exchanger.For example: Chinese patent 02204830.8 has been introduced a kind of counterflow pipe coiled heat exchanger, comprises rectangular case, is placed on coil pipe and electric heater in housing.The serpentine fluid passage that rectangular case inside is gone out by deflector and baffle for separating, the internal face of water stream channel is equipped with flow spoiler and distributary board mount, utilize flow spoiler and distributary plate to realize the disturbance of water side liquid, improve heat exchange property, the refrigerant side passage is to have the serpentine coil of 180 °, simultaneously electric heater has been installed in housing, the ice-melt thermal source is provided, effectively prevented the freezing problem in housing.in order to solve because being subjected to coil pipe not compact because of the structure that the restriction of bending radius causes, the space waste is serious, and then have influence on the defective of heat exchange property, Chinese patent 200910250518.X has introduced a kind of coil pipe and has had the heat exchanger of this coil pipe, formed with the arcuation pipe that tail end is connected into the continuous bend line successively mutually by several head ends, the angle of crossing between the head end of described arcuation pipe and tail end is greater than 180 degree, the center line of adjacent two described arcuation pipe junctions is connected with the tube hub line is tangent always, and arrange guiding device in housing, guiding device is comprised of several water conservancy diversion cylinders and connecting wall, compactness and the miniaturization of heat exchanger have further been realized.
Although the coil exchanger of above-mentioned form has solved the Problems In Heat Exchangers of existing Miniature wind cold (heat) water central air-conditioning, but the liquid form that adopts due to prior art is by being parallel to each other between adjacent tube fluid passage, be connected with neighbouring coolant channel with the semicircle tube connector at the two ends of refrigerant side passage, form snakelike (U-shaped) coil pipe.This class heat exchange structure will seriously affect heat transfer or the drag characteristic of heat exchanger, for example: the coefficient of heat transfer of the Laminar Flow under low flow velocity is lower, although and the coefficient of heat transfer of the turbulent flow under high flow rate is higher, but because the runner of shell fluid is long, cause resistance very large, cause the pump merits and demerits of shell fluid large, this is unfavorable for that all heat exchanger realizes efficient, energy-conservation requirement.In addition, although adopted the devices such as diversion column, spoiler, improved heat exchange property, but further increased the resistance of system, easily turn to the district at fluid, for example the dead angle of diversion column and spoiler forms accumulation of mud, and has increased the complexity of system's manufacturing and processing, further reduces systematic function.
Summary of the invention
The object of the invention is to solve prior art based on increasing the system flow resistance and increasing on the basis of water pump pump merit consumption, provide a kind of by heat exchanger tube self structure arrangement form, do not increasing external device and guaranteeing under the condition of heat exchange property, space mounting size constancy, realization consumes than the less flow resistance of prior art and pump merit, reaches the heat exchanger of comprehensively energy-conservation practical purpose.
For achieving the above object, the technical solution used in the present invention is: comprise the housing that offers heat-exchange working medium entrance and heat-exchange working medium outlet, be provided with some layers with the snakelike heat exchange tube of refrigerant inlet and refrigerant outlet in housing, adjacent two layers coiled pipe interlaced arrangement also is provided with in housing for the fixing locating dowel of snakelike heat exchange tube.
The upper strata heat exchanger tube of the snakelike heat pipe of adjacent two layers of the present invention and the intersecting angle of lower floor's heat exchanger tube are 10 °～40 °.
The intersecting angle of upper strata heat exchanger tube and lower floor's heat exchanger tube is regulated according to diameter and the spacing of locating dowel.
The flow development length of snakelike heat exchange tube accounts for 70% of total length.
The bent angle of snakelike heat exchange tube is greater than 180 °.
The employing of snakelike heat exchange tube is without the one-shot forming of inner core pipe bending technique.
The present invention adopts the arrangement of multilayer coiled pipe according to the difference of the size of heat exchange amount and mounting arrangements version, heat exchanger tube between different layers forms netted interlaced arrangement, greatly increased the disturbance of shell fluid, even if under less flow velocity, also reinforced pipe streams the flow disturbance of form outward effectively, thereby greatly improve heat transfer coefficient and the heat exchanger heat-transfer performance of shell fluid, and make the Temperature Distribution of shell fluid more even; In addition, due to the version that adopts the present invention to propose, the parts such as the spoiler that prior art is commonly used, diversion column have been removed, processing and manufacturing and the assembly cost of equipment have been greatly reduced, simultaneously because the larger shell-side of steering drag loss with prior art replaces liquid form, be improved to the less pipe of resistance and stream form outward, greatly reduced in addition the shell fluid operation length of original structure than prior art, thereby effectively reduced the flow resistance of shell-side, reduced the pump merit consumption of system, realized energy-conservation.
Description of drawings
Fig. 1 is cutaway view of the present invention;
Fig. 2 is heat exchange coiled pipe structure chart of the present invention;
Fig. 3 is effect analysis figure of the present invention.
The specific embodiment
Below in conjunction with accompanying drawing, the present invention is described in further detail.
referring to Fig. 1, 2, the present invention includes the housing 4 that offers heat-exchange working medium entrance 7 and heat-exchange working medium outlet 8, being provided with some layers in housing 4 adopts without the one-time formed snakelike heat exchange tube of inner core pipe bending technique with refrigerant inlet 1 and refrigerant outlet 6, the bent angle of this snakelike heat exchange tube is greater than 180 °, its two ends elbow be close together (perhaps close proximity), greatly reduced the volume of heat exchanger from the space, flow development length accounts for 70% of total length, as everyone knows, fluid only has when flowing in straight length along journey frictional resistance not because flow to the excessive local resistance that changes and cause, so when flowing in bend loss when flowing in the fluid straight length, drag losses is much smaller.Because snakelike heat exchange tube in the present invention has very long straight length, so the flow resistance of tube fluid of the present invention reduces greatly, reduced the pump merit consumption of tube fluid, and prior art often adopts the version of complicated many bend pipes, greatly increase the pressure loss in the pipe, reduced system effectiveness.Adjacent two layers coiled pipe interlaced arrangement of the present invention, the intersecting angle of upper strata heat exchanger tube 2 and lower floor's heat exchanger tube 3 is 10 °～40 °, also be provided with in housing 4 for the fixing locating dowel 5 of snakelike heat exchange tube, the intersecting angle of upper strata heat exchanger tube 2 and lower floor's heat exchanger tube 3 is regulated according to diameter and the spacing of locating dowel 5, diameter that can be by locating dowel 5 and the various combination of spacing are realized the multiple arrangement form of different corner dimensions, make two angle theta
1And θ
2Vary in size, make the liquid flow of shell-side more unordered, disturbance is more violent.During work, be generally cold and hot two kinds of different fluid in shell-side and pipe, shell fluid is subject to the disturbance of the heat exchanger tube of interlaced arrangement in flowing, form nowed forming in great disorder, convection current and the caloic exchange of internal fluid have been promoted, make the temperature of shell fluid more even, larger with the heat transfer temperature difference of tube fluid, thus greatly improved the coefficient of heat transfer of shell fluid.
Referring to Fig. 3, the ratio of heat exchange amount and resistance is with angle theta
2Changing trend diagram, fixed angle θ simultaneously
1It is 32 °.As seen from Figure 3, at θ
2During=18 ° of left and right, the heat exchange amount reaches maximum with the ratio of resistance, and the pump merit that namely reaches the identical required consumption of heat exchange amount this moment is minimum, that is to say that " cost performance " of this moment is the highest.The θ of this moment
2Be about θ
1Half, shell fluid is subject to the disturbance of the heat exchanger tube of former and later two different angles, make its nowed forming very chaotic, thereby its coefficient of heat transfer is very high, and its minimum flow area is unlikely too small, therefore its flow velocity is not high, thereby its resistance neither be very high, so it is the highest with the ratio of resistance to integrate its heat exchange amount.Work as θ
2When＜18 ° (being the left side of peak in Fig. 3), due to θ
2The too small minimum flow area of shell fluid that causes is very little, thereby makes the flow resistance of shell fluid excessive, although this moment, the heat exchange amount can increase, the ratio of its heat exchange amount and resistance is still along with θ
2Reduce and reduce; Work as θ
2When＞18 ° (being the right side of peak in Fig. 3), due to θ
2Become large, and more and more close to θ
1, the disturbed periodicity of the shell fluid of this moment is more and more obvious, that is to say the back angle theta
2Two limits can not carry out further disturbance to shell fluid, so this moment along with θ
2Increase (in other words near θ
1), the heat exchange amount of heat exchanger descends rapidly, although the flow resistance of its shell fluid reduces to some extent, its heat exchange amount remains along with θ with the ratio of resistance
2Increase reduce.The heat exchange amount of the heat exchanger in 7 ° of-27 ° of scopes in the present invention much larger than traditional U-shaped heat exchange of heat pipe, and is less than traditional U-shaped heat exchange of heat pipe during greater than 29 ° with the ratio of flow resistance.This is mainly that in pipe, the flow direction of outer fluid is more and more close to following current, so convection transfer rate decreases due to the increase along with the angle of the heat exchanger tube of heat exchanger in the present invention.
Claims (5)
1. heat exchanger, comprise the housing (4) that offers heat-exchange working medium entrance (7) and heat-exchange working medium outlet (8), it is characterized in that: be provided with some layers with the snakelike heat exchange tube of refrigerant inlet (1) and refrigerant outlet (6) in housing (4), adjacent two layers snakelike heat exchange tube interlaced arrangement also is provided with in housing (4) for the fixing locating dowel of snakelike heat exchange tube (5);
The upper strata heat exchanger tube (2) of described adjacent two layers snakelike heat exchange tube and the intersecting angle of lower floor's heat exchanger tube (3) are 10 °～40 °.
2. heat exchanger according to claim 1 is characterized in that: the intersecting angle of described upper strata heat exchanger tube (2) and lower floor's heat exchanger tube (3) is regulated according to diameter and the spacing of locating dowel (5).
3. heat exchanger according to claim 1, it is characterized in that: the flow development length of described snakelike heat exchange tube accounts for 70% of total length.
4. heat exchanger according to claim 1, it is characterized in that: the bent angle of described snakelike heat exchange tube is greater than 180 °.
5. heat exchanger according to claim 1, it is characterized in that: the employing of described snakelike heat exchange tube is without the one-shot forming of inner core pipe bending technique.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011102176832A CN102322752B (en) | 2011-08-01 | 2011-08-01 | Heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011102176832A CN102322752B (en) | 2011-08-01 | 2011-08-01 | Heat exchanger |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102322752A CN102322752A (en) | 2012-01-18 |
| CN102322752B true CN102322752B (en) | 2013-05-22 |
Family
ID=45450549
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011102176832A Expired - Fee Related CN102322752B (en) | 2011-08-01 | 2011-08-01 | Heat exchanger |
Country Status (1)
| Country | Link |
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| CN (1) | CN102322752B (en) |
Families Citing this family (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102645058A (en) * | 2012-05-04 | 2012-08-22 | 太仓市弧螺机电有限公司 | Efficient condenser |
| JP6180338B2 (en) * | 2014-01-29 | 2017-08-16 | ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド | Air conditioner |
| CN103808185B (en) * | 2014-02-21 | 2015-11-25 | 杭州沈氏节能科技股份有限公司 | A kind of efficient heat-exchanging pipe and evaporative condenser thereof |
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| CN105486123B (en) * | 2015-12-24 | 2018-06-26 | 上海理工大学 | A kind of snakelike heat exchange tube beam |
| CN107869833B (en) * | 2016-09-23 | 2024-08-16 | 青岛海尔智能技术研发有限公司 | Tubular heat exchanger and heat pump system |
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| CN108344205A (en) * | 2018-02-05 | 2018-07-31 | 东南大学 | Beach source heat pump system for aquaculture |
| CN108645246A (en) * | 2018-06-27 | 2018-10-12 | 广州航海学院 | A kind of heat exchanger |
| CN110608622B (en) * | 2019-05-20 | 2020-12-18 | 无锡蓝海工程设计有限公司 | Tower type tube bundle heat exchanger |
| CN110813034B (en) * | 2019-11-13 | 2021-08-24 | 上海交通大学 | S-shaped tube bundle falling film absorber |
| CN111442589A (en) * | 2020-03-13 | 2020-07-24 | 青岛海尔电冰箱有限公司 | Refrigerating device |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5507340A (en) * | 1995-05-19 | 1996-04-16 | Alston; Gerald A. | Multiple circuit cross-feed refrigerant evaporator for static solutions |
| CN101259388A (en) * | 2007-03-09 | 2008-09-10 | 苏舍化学技术有限公司 | Device for heat exchange and mixing treatment of fluid mediums |
| CN101506609A (en) * | 2006-08-08 | 2009-08-12 | 苏舍化学技术有限公司 | An apparatus for combined carrying out of heat exchange and static mixing using a liquid |
| CN101738122A (en) * | 2009-12-14 | 2010-06-16 | 杭州沈氏换热器有限公司 | Coiled tube and heat exchanger applying same |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS597887A (en) * | 1982-07-06 | 1984-01-17 | Mitsubishi Heavy Ind Ltd | Production of meandering pipe type heat-transmitting pipe |
| JPH11294973A (en) * | 1998-04-14 | 1999-10-29 | Tokyo Gas Co Ltd | Heat exchanger of absorption water cooler/heater |
| CN202254497U (en) * | 2011-08-01 | 2012-05-30 | 西安交通大学 | Heat exchanger |
-
2011
- 2011-08-01 CN CN2011102176832A patent/CN102322752B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5507340A (en) * | 1995-05-19 | 1996-04-16 | Alston; Gerald A. | Multiple circuit cross-feed refrigerant evaporator for static solutions |
| CN101506609A (en) * | 2006-08-08 | 2009-08-12 | 苏舍化学技术有限公司 | An apparatus for combined carrying out of heat exchange and static mixing using a liquid |
| CN101259388A (en) * | 2007-03-09 | 2008-09-10 | 苏舍化学技术有限公司 | Device for heat exchange and mixing treatment of fluid mediums |
| CN101738122A (en) * | 2009-12-14 | 2010-06-16 | 杭州沈氏换热器有限公司 | Coiled tube and heat exchanger applying same |
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| Publication number | Publication date |
|---|---|
| CN102322752A (en) | 2012-01-18 |
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