CN102322752A - Heat exchanger - Google Patents
Heat exchanger Download PDFInfo
- Publication number
- CN102322752A CN102322752A CN201110217683A CN201110217683A CN102322752A CN 102322752 A CN102322752 A CN 102322752A CN 201110217683 A CN201110217683 A CN 201110217683A CN 201110217683 A CN201110217683 A CN 201110217683A CN 102322752 A CN102322752 A CN 102322752A
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- Prior art keywords
- heat exchanger
- heat
- shell
- fluid
- heat exchange
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- 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
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- 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 ofly be used for the surface-type coil heat exchanger that two kinds of fluids do not contact (the for example heat exchange between cold-producing medium-water).
Background technology
In commercial 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.Like the heater in the Chemical Manufacture, cooler, evaporimeter, condenser, reboiler etc.; The and for example air preheater in the 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 pipe heat exchanger (like shell-and-tube heat exchanger, coil heat exchanger, double-tube heat exchanger, spray-type heat exchanger, aerial cooler etc.) and plate type heat exchanger (like spiral heat exchanger, plate-type exchanger, plate-fin heat exchanger etc.) again.
At present; Small-sized air-cooled cold (heat) water central air-conditioning unit is because compact conformation; Employed cold-producing medium-water-to-water heat exchanger overwhelming majority is a brazing plate type heat exchanger; Through heat exchange between plate, realize the heat transmission between cold-producing medium and the water, and then utilize water pump that cold (heat) water is delivered to indoor end equipment.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, because the restriction of the liquid cold-producing medium method of salary distribution between the plate of brazing plate type heat exchanger causes the modes of emplacement of plate type heat exchanger to be restricted, thereby influenced the utilization in space in the unit.
In order to overcome the existing existing intrinsic problem of brazing plate type heat exchanger, adopt the version of counter-current tray pipe heat exchanger usually, thereby solved the problem of existing brazing plate type heat exchanger effectively.For example: Chinese patent 02204830.8 has been introduced a kind of counter-current tray pipe heat exchanger, comprises rectangular housing, is placed on coil pipe and electric heater in the housing.The serpentine fluid passage that rectangular housing inside is separated out by deflector and dividing plate; The internal face of water stream channel is equipped with flow spoiler and distributary board mount, utilizes the disturbance of the firm and hard existing water side liquid of flow spoiler and distributary, improves heat exchange property; The refrigerant side passage is to have 180 ° serpentine coil; Simultaneously electric heater has been installed in housing, the ice-melt thermal source is provided, effectively prevented the freezing problem in the housing.In order to solve because of receiving coil pipe not compact because of the structure that restriction caused of bending radius; Space waste is serious, and then has influence on the defective of heat exchange property, and Chinese patent 200910250518.X has introduced a kind of coil pipe and had the heat exchanger of this coil pipe; Form 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 said arcuation pipe and the tail end is greater than 180 degree, and the center line of two adjacent said arcuation pipe junctions is connected with the tube hub line is tangent always, and in housing, arranges guiding device; Guiding device is made up of several water conservancy diversion cylinders and connecting wall, has further realized the compactness and the miniaturization of heat exchanger.
Though the coil exchanger of above-mentioned form has solved the heat exchanger problem of existing small-sized air-cooled cold (heat) water central air-conditioning; But because the liquid form that prior art adopted is through being parallel to each other between the adjacent tube fluid passage; Two ends at the refrigerant side passage are connected with neighbouring coolant channel with the semicircle tube connector, form snakelike (U-shaped) coil pipe.This type heat exchange structure will seriously influence the heat transfer or the drag characteristic of heat exchanger; For example: the coefficient of heat transfer of the Laminar Flow under the low flow velocity is lower; Though and the coefficient of heat transfer of the turbulent flows under the high flow rate is higher,, cause resistance very big because the runner of shell fluid is long; Cause the pump merits and demerits of shell fluid big, this all is unfavorable for, and heat exchanger is realized efficiently, requirements of saving energy.In addition; Though adopted devices such as diversion column, spoiler, improved heat exchange property, further increased the resistance of system; Turn to the district at fluid easily; 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 objective of the invention is to solve prior art based on the basis that increases system flow resistance and the consumption of increase water pump pump merit; Provide a kind of through heat exchanger tube self structure arrangement form; Under the condition that does not increase external device and assurance heat exchange property, space mounting size constancy; Realization consumes than littler flow resistance of prior art and pump merit, reaches the heat exchanger of energy-conservation comprehensively practical purpose.
For achieving the above object; The technical scheme that the present invention adopts is: comprise the housing that offers heat-exchange working medium inlet and heat-exchange working medium outlet; In housing, be provided with the snakelike heat exchange tube that several layers has refrigerant inlet and refrigerant outlet; Adjacent two layers coiled pipe interlaced arrangement also is provided with the reference column that is used for fixing snakelike heat exchange tube in the housing.
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 the diameter and the spacing of reference column.
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 does not have the one-shot forming of inner core pipe bending technique.
The present invention is according to the different mining of the size of heat and the mounting arrangements version arrangement with the multilayer coiled pipe; Heat exchanger tube between the 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 improve the heat transfer coefficient and the heat exchanger heat-transfer performance of shell fluid greatly, and make that the Temperature Distribution of shell fluid is more even; In addition; Because the version that adopts the present invention to propose has been removed parts such as the spoiler that prior art is used always, diversion column, has significantly reduced the processing and manufacturing and the assembly cost of equipment; Because being lost bigger shell-side, the steering drag of prior art replaces liquid form simultaneously; Be improved to the less pipe of resistance and stream form outward, significantly reduced the shell fluid flow process length of original structure in addition than prior art, thereby reduced the flow resistance of shell-side effectively; Reduced the pump merit consumption of system, realized energy-conservation.
Description of drawings
Fig. 1 is a cutaway view of the present invention;
Fig. 2 is a 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 done further explain.
Referring to Fig. 1; 2; The present invention includes the housing 4 that offers heat-exchange working medium inlet 7 and heat-exchange working medium outlet 8, in housing 4, be provided with several layers and have refrigerant inlet 1 and the one-time formed snakelike heat exchange tube of the refrigerant outlet 6 no inner core pipe bending techniques of employing, the bent angle of this snakelike heat exchange tube is greater than 180 °; Its two ends elbow be close together (perhaps close proximity); From the space, reduced heat exchanger volume greatly, flow development length accounts for 70% of total length, and is well-known; Fluid has only when in straight length, flowing along journey frictional resistance not because flow to the excessive local resistance that changes and cause, so drag losses is much little when in bend loss, flowing when flowing in the fluid straight length.Because snakelike heat exchange tube has very long straight length among the present invention; 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, has greatly increased the pressure loss in the pipe, has 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 the reference column 5 that is used for fixing snakelike heat exchange tube in the housing 4; The intersecting angle of upper strata heat exchanger tube 2 and lower floor's heat exchanger tube 3 is according to the diameter and spacing adjusting of reference column 5, and the diameter that can be through reference column 5 and the various combination of spacing are realized the multiple arrangement form of different corner dimensions, makes two angle theta
1And θ
2Vary in size, make that the liquid flow of shell-side is more unordered, disturbance is more violent.During work; Be generally cold and hot two kinds of different fluid in shell-side and the pipe, shell fluid receives the disturbance of the heat exchanger tube of interlaced arrangement in flowing, form nowed forming in great disorder; Convection current and caloic exchange that fluid is inner have been promoted; Make that the temperature of shell fluid is more even, bigger with the heat transfer temperature difference of tube fluid, thus improved the coefficient of heat transfer of shell fluid greatly.
Referring to Fig. 3, the ratio of heat and resistance is with angle theta
2Changing trend diagram, fixed angle θ simultaneously
1It is 32 °.Can find out by Fig. 3, at θ
2Heat reaches maximum with the ratio of resistance during=18 ° of left and right sides, and the pump merit that promptly reaches the identical required consumption of heat 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 the; Shell fluid receives 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; So 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.Work as θ
2When＜18 ° (being the left side of peak among Fig. 3), because θ
2The too small minimum flow area of shell fluid that causes is very little, thereby makes that the flow resistance of shell fluid is excessive, although this moment, heat can increase, the ratio of its heat and resistance is still along with θ
2Reduce and reduce; Work as θ
2When＞18 ° (being the right side of peak among Fig. 3), because θ
2Become big, and more and more approach 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 of heat exchanger descends rapidly, although the flow resistance of its shell fluid reduces to some extent, its heat remains along with θ with the ratio of resistance
2Increase reduce.The heat of the heat exchanger in 7 ° of-27 ° of scopes among the present invention and the ratio of flow resistance be much larger than traditional U type heat exchange of heat pipe, and be less than traditional U type heat exchange of heat pipe during greater than 29 °.This mainly is because along with the increase of the angle of the heat exchanger tube of heat exchanger among the present invention, the flow direction of outer fluid more and more approaches following current in the pipe, so convection transfer rate decreases.
Claims (6)
1. heat exchanger; Comprise the housing (4) that offers heat-exchange working medium inlet (7) and heat-exchange working medium outlet (8); It is characterized in that: in housing (4), be provided with the snakelike heat exchange tube that several layers has refrigerant inlet (1) and refrigerant outlet (6); Adjacent two layers coiled pipe interlaced arrangement also is provided with the reference column (5) that is used for fixing snakelike heat exchange tube in the housing (4).
2. heat exchanger tube according to claim 1 is characterized in that: the upper strata heat exchanger tube (2) of the snakelike heat pipe of described adjacent two layers and the intersecting angle of lower floor's heat exchanger tube (3) are 10 °～40 °.
3. heat exchanger tube according to claim 2 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 the diameter and the spacing of reference column (5).
4. heat exchanger tube according to claim 1 is characterized in that: the flow development length of described snakelike heat exchange tube accounts for 70% of total length.
5. heat exchanger tube according to claim 1 is characterized in that: the bent angle of described snakelike heat exchange tube is greater than 180 °.
6. heat exchanger tube according to claim 1 is characterized in that: the employing of described snakelike heat exchange tube does not have 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 true CN102322752A (en) | 2012-01-18 |
| CN102322752B CN102322752B (en) | 2013-05-22 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011102176832A Active CN102322752B (en) | 2011-08-01 | 2011-08-01 | Heat exchanger |
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Cited By (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 |
| CN103808185A (en) * | 2014-02-21 | 2014-05-21 | 杭州沈氏换热器有限公司 | Efficient heat exchange tube and evaporative condenser |
| CN104209381A (en) * | 2014-09-12 | 2014-12-17 | 张家港市华机环保新能源科技有限公司 | Equipment for carburetor pipe bending |
| CN105486123A (en) * | 2015-12-24 | 2016-04-13 | 上海理工大学 | S-shaped heat exchange pipe bundle |
| CN106643235A (en) * | 2016-12-08 | 2017-05-10 | 沈阳航空航天大学 | Recuperative heat exchanger and manufacturing method thereof |
| CN107650412A (en) * | 2017-10-27 | 2018-02-02 | 合肥燕庄食用油有限责任公司 | A kind of squeezer for cold pressing sesame oil |
| CN107702549A (en) * | 2017-11-14 | 2018-02-16 | 朝阳镔鑫环保设备有限公司 | A kind of sintering machine Two-way Cycle cooling unit and cooling device |
| CN107869833A (en) * | 2016-09-23 | 2018-04-03 | 青岛海尔智能技术研发有限公司 | Pipe heat exchanger and heat pump |
| 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 |
| CN109059113A (en) * | 2014-01-29 | 2018-12-21 | 日立江森自控空调有限公司 | Air-conditioning |
| CN110608622A (en) * | 2019-05-20 | 2019-12-24 | 无锡蓝海工程设计有限公司 | Tower type tube bundle heat exchanger |
| CN110813034A (en) * | 2019-11-13 | 2020-02-21 | 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 |
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| 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 |
| 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 active Active
Patent Citations (7)
| 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 |
| US5507340A (en) * | 1995-05-19 | 1996-04-16 | Alston; Gerald A. | Multiple circuit cross-feed refrigerant evaporator for static solutions |
| JPH11294973A (en) * | 1998-04-14 | 1999-10-29 | Tokyo Gas Co Ltd | Heat exchanger of absorption water cooler/heater |
| 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 |
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Cited By (18)
| 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 |
| CN109059113A (en) * | 2014-01-29 | 2018-12-21 | 日立江森自控空调有限公司 | Air-conditioning |
| CN103808185A (en) * | 2014-02-21 | 2014-05-21 | 杭州沈氏换热器有限公司 | Efficient heat exchange tube and evaporative condenser |
| 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 |
| CN104209381A (en) * | 2014-09-12 | 2014-12-17 | 张家港市华机环保新能源科技有限公司 | Equipment for carburetor pipe bending |
| CN105486123A (en) * | 2015-12-24 | 2016-04-13 | 上海理工大学 | S-shaped heat exchange pipe bundle |
| CN105486123B (en) * | 2015-12-24 | 2018-06-26 | 上海理工大学 | A kind of snakelike heat exchange tube beam |
| CN107869833A (en) * | 2016-09-23 | 2018-04-03 | 青岛海尔智能技术研发有限公司 | Pipe heat exchanger and heat pump |
| CN106643235B (en) * | 2016-12-08 | 2018-07-27 | 沈阳航空航天大学 | A kind of recuperative heat exchanger and preparation method thereof |
| CN106643235A (en) * | 2016-12-08 | 2017-05-10 | 沈阳航空航天大学 | Recuperative heat exchanger and manufacturing method thereof |
| CN107650412A (en) * | 2017-10-27 | 2018-02-02 | 合肥燕庄食用油有限责任公司 | A kind of squeezer for cold pressing sesame oil |
| CN107702549A (en) * | 2017-11-14 | 2018-02-16 | 朝阳镔鑫环保设备有限公司 | A kind of sintering machine Two-way Cycle cooling unit and cooling device |
| 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 |
| CN110608622A (en) * | 2019-05-20 | 2019-12-24 | 无锡蓝海工程设计有限公司 | Tower type tube bundle 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 |
| CN110813034A (en) * | 2019-11-13 | 2020-02-21 | 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 |
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|---|---|
| CN102322752B (en) | 2013-05-22 |
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