CN203478730U - Horizontal shell-and-tube water-cooled condenser - Google Patents
Horizontal shell-and-tube water-cooled condenser Download PDFInfo
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- CN203478730U CN203478730U CN201320567817.8U CN201320567817U CN203478730U CN 203478730 U CN203478730 U CN 203478730U CN 201320567817 U CN201320567817 U CN 201320567817U CN 203478730 U CN203478730 U CN 203478730U
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Abstract
Disclosed is a horizontal shell-and-tube water-cooled condenser. Two-dimensional low-fin tubes with the outer tube fin density larger than 50fpi and smaller than 60fpi and the fin height larger than 0.9mm are adopted as heat transfer tubes of the horizontal shell-and-tube water-cooled condenser, and a liquid drainage plate is additionally arranged in the middle of tube bundles. Different from an existing condenser in heat transfer tube selection and tube bundle arrangement mode, the horizontal shell-and-tube water-cooled condenser has the advantages that a specific type of tubes are selected, and the low-fin tubes are adopted as all tubes in the condenser instead of three-dimensional efficient tubes adopted in the existing condenser so that the heat transfer characteristic of the low-fin tubes can be exerted; a splayed liquid baffle with a special structure is arranged, and therefore the problem that the space of the tube bundles is wasted because of the angle formed when only one baffle is arranged is solved. Because all the heat transfer tubes used in the condenser are the low-fin tubes, the machining difficulty in strengthening the heat transfer tubes is reduced. Because the low-fin tubes are adopted as the cooling tubes, condensation tubes and undercooling tubes respectively in the condenser for replacing the three-dimensional heat transfer tubes used in the existing shell-and-tube condenser, the influence of condensate on the condensation heat transfer process of the condenser is reduced, and copper materials for making the heat transfer tubes of the condenser can be saved by 15% or so.
Description
Technical field
The utility model belongs to heat transmission equipment and augmentation of heat transfer technical field, relates to a kind of heat exchanger, is specifically related to a kind of horizontal tubular water condenser '.
Background technology
Shell-and-tube cooler is used widely at refrigerating and air conditioning industry, it is the crucial heat exchanger components of large-scale refrigerated air-conditioning system the inside, the heat exchange efficiency of condenser has directly affected the efficient operation of whole refrigeration unit, and therefore designing high performance condenser is the effective way that improves refrigeration system combination property.
The horizontal pipe shell tube condenser compact conformation using at present, heat-transfer pipe deployment tube row spacing is little, and condensate liquid can not be discharged as early as possible between pipe row, and lime set, as main thermal resistance, has affected pipe row's heat exchange efficiency, is unfavorable for that every heat-transfer pipe carries out high efficient heat exchanging.In the selection of cast, existing air-conditioning condenser is used three dimension high efficiency heat-transfer pipe more, the single tube superior performance of three dimension high efficiency heat-transfer pipe, but be installed to and in shell-and-tube cooler, restrain overall performance and can not effectively bring into play, because three-dimensional tube is subject to the impact of lime set large, therefore, must be by selecting suitable heat-transfer pipe, improving the combination property of different casts on horizontal pipe shell tube condenser by pipe row being carried out to the structural design of reasonable Arrangement and optimization condenser.
Utility model content
The purpose of this utility model is to overcome condenser tube row and affected greatly by lime set, arrangement is simple, and non-ferrous metal copper consumption is large, the shortcoming that heat transfer efficiency is low, a kind of copper material consumption of having saved is provided, has simplified the horizontal tubular water condenser ' of the difficulty of processing of heat-transfer pipe cast.
For achieving the above object, the technical solution adopted in the utility model is: comprise the condenser shell that offers steam inlet, lime set outlet, in condenser shell, be provided with some groups of heating surface banks, some groups of described heating surface banks are divided into heating surface bank and lower heating surface bank, in condenser shell both sides, be provided with the hydroecium being connected with heating surface bank, wherein on a side hydroecium, offer delivery port and the water inlet being connected with upper heating surface bank and lower heating surface bank respectively;
It is 50fpi～60fpi that described heating surface bank adopts pipe external fin density, and rib height is the low ribbed pipe of two dimension of 0.9mm～1.3mm, and two-dimentional low ribbed pipe individual pen internal thread number is no less than 48, the high 0.35mm that is not less than of screw thread rib.
In described condenser shell, be also provided with steam baffle, described steam baffle is between upper heating surface bank and lower heating surface bank.
Described steam baffle is comprised of the baffle plate of two inclinations, and the baffle plate of two inclinations and the splayed layout replacing in an overlapping inclination laterally, angle of inclination 5-30 degree.
Two baffle plates that outside tilts that are splayed layout that described steam baffle comprises the upper flat plate be arrangeding in parallel of upper end and is arranged on upper flat plate lower end, angle of inclination 5-30 degree.
The utility model pipe row all adopts the low ribbed pipe of two dimension that is easy to processing, and two-dimentional low ribbed pipe is subject to the impact of upper strata pipe condensate drain liquid less, and pipe row order is larger, and the advantage of low ribbed pipe is more obvious.As shown in Figure 4, the heat transfer coefficient of low ribbed pipe is subject to the impact of upper strata lime set less, heat transfer coefficient is not almost changed by the impact of lime set in research range, and the heat transfer coefficient of Three-dimensional Heat-transfer pipe reduces gradually with the increase of lime set amount, can predict, in lime set amount, acquire a certain degree, the pipe row of heat exchanger is more, condensation power is larger, and its heat transfer coefficient may be significantly less than two-dimentional low ribbed pipe.
The utility model utilizes this advantage of low ribbed pipe just, adopts two-dimentional low ribbed pipe as heat-transfer pipe, and pipe external fin density is 50 to 60fpi(fpi:fins per inch, per inch rib number), the high 0.9mm that is not less than of rib.Meanwhile, the internal thread of the pipe weekly number of this heat-transfer pipe is no less than 48, the high 0.35mm that is not less than of rib.By selecting such low ribbed pipe, its condensation heat transfer process overall heat-transfer coefficient is apparently higher than the heat transfer coefficient of three-dimensional tube preferably of heat transfer property on domestic market.As shown in Figure 5, optimize after the single-pipe heat-transfer coefficient ratio figure performance high 5-10% of the heat transfer coefficient left and right of three-dimensional tube preferably of low ribbed pipe.
Diabatic process in condenser comprises that overheated gas is cooled to and saturated, saturatedly condenses and spend cold three heat transfer stages.The heat transfer area of the low ribbed pipe of overheated cooling stage is large, can strengthen better single-phase convection heat-transfer.The low ribbed pipe of saturated condensation stage is not subject to the impact of lime set, can bring into play better the advantage of low ribbed pipe.Spend the cold heat exchange stage, cooled lime set is washed away tube surface, and the relative Three-dimensional Heat-transfer pipe of ratio heat transfer area of low ribbed pipe is larger, and lime set is washed away the fin on low ribbed pipe surface, better to the cooling effect of subcooling condensate.The increase of degree of supercooling, also can improve the refrigerating capacity of whole unit.
Compare with existing horizontal pipe shell tube condenser pipe row arrangement mode, this patent also has following characteristics:
1, adopt the low ribbed pipe cast of high outer wing density, be conducive to bring into play the heat transfer advantage of low ribbed pipe, improve heat exchange efficiency, simultaneously saving copper consumptive material.
2, increase lime set baffle plate, effectively reduce the impact of liquid phase refrigerant on condensation heat transfer efficiency of condensing.
Accompanying drawing explanation
Fig. 1 is overall structure schematic diagram of the present utility model;
Fig. 2 is the structural representation of the utility model heating surface bank 2;
Fig. 3 is the structural representation of the utility model steam baffle 5; Fig. 3 a is the structural representation of embodiment 1, and Fig. 3 b is the structural representation of embodiment 2;
Fig. 4 is that two dimension, Three-dimensional Heat-transfer pipe are subject to lime set to affect heat transfer coefficient variation diagram;
Fig. 5 is two-dimentional low ribbed pipe and three-dimensional tube overall heat-transfer coefficient comparison diagram.
The specific embodiment
Below in conjunction with accompanying drawing, the utility model is described in further detail.
In order to further illustrate the design considerations of the utility model scheme, first cast feature and various pipe are arranged and put superiority-inferiority analysis: after 1) vapor phase refrigerant enters shell-and-tube cooler, in intensify heat transfer pipe surface condensation, become liquid, form one deck liquid film, the film condensation on pipe row upper strata drips to Guan Pai lower floor, the just further thickening of the tube surface liquid film of pipe row below.And the main thermal resistance of cold-producing medium film condensation depends on the thickness of this liquid film layer.Current central air-conditioning shell-and-tube cooler generally all adopts three dimension high efficiency pipe as heat-transfer pipe, but research by experiment, three-dimensional intensify heat transfer pipe floods in situation and can bring into play the effect that its reducer film thickness reduces condensation heat transfer thermal resistance in less lime set, but along with the increase of pipe row below lime set thickness of liquid film, the pipe row of lower floor is difficult to the performance image tube row equally efficient condensation heat transfer effect in upper strata.Other experimental study also shows, low ribbed pipe condensation heat transfer is on the low side to the sensitiveness of pipe row, and the heat transfer coefficient of lower floor's heat-transfer pipe reduces less than the heat transfer coefficient of upper strata heat-transfer pipe.In addition, as long as select suitable pipe external fin density, also can reach the coefficient of heat transfer same with Three-dimensional Heat-transfer pipe, and low ribbed pipe is relatively simple with respect to the processing of Three-dimensional Heat-transfer pipe.
Embodiment 1: referring to Fig. 1, 2, 3a, in view of above analysis, the utility model proposes horizontal pipe shell tube condenser heat-transfer pipe and select two-dimentional intensify heat transfer pipe, the utility model comprises and offers steam inlet 4, the condenser shell 1 of lime set outlet 7, in condenser shell 1, be provided with some groups of heating surface banks 2, some groups of described heating surface banks are divided into heating surface bank 2-1 and lower heating surface bank 2-2, in condenser shell 1 both sides, be provided with the hydroecium 6 being connected with heating surface bank 2, wherein on a side hydroecium 6, offer delivery port 9 and the water inlet 8 being connected with upper heating surface bank 2-1 and lower heating surface bank 2-2 respectively, it is 50fpi～60fpi that described heating surface bank 2 adopts pipe external fin 10 density, and rib height is the low ribbed pipe of two dimension of 0.9mm～1.3mm, and two-dimentional low ribbed pipe individual pen internal thread 11 numbers are no less than 48, the high 0.35mm that is not less than of screw thread rib.In condenser shell 1, be also provided with steam baffle 5, described steam baffle 5 is between upper heating surface bank 2-1 and lower heating surface bank 2-2.
Referring to Fig. 3 b, the steam baffle 5 of the present embodiment is comprised of baffle plate 5-1 and the 5-2 of two inclinations, and the baffle plate 5-1 of two inclinations and splayed that 5-2 replaces are in an overlapping arranged and tilt laterally, angle of inclination 5-30 degree.
Referring to Fig. 3 b, the baffle plate 5-1 and the 5-2 that are two inclinations that outside that splayed arranges tilts that the steam baffle 5 of the present embodiment comprises the upper flat plate 5-3 be arrangeding in parallel of upper end and is arranged on upper flat plate 5-3 lower end, angle of inclination 5-30 degree.
By the experiment of 2500kW condenser, only two-dimentional low ribbed pipe is replaced Three-dimensional Heat-transfer pipe and can be saved the copper material of 15% left and right, and heat exchange amount can meet original heat exchange requirement and can slightly be improved, after the application with concrete case and measured data.Consider various composite factors, method for designing heat exchange amount of the present utility model can meet the heat exchange requirement of original heat exchanger, but copper consumption is comparable, has originally reduced nearly 15%.
Scheme one: whole Exchanger Tubes adopts three dimension high efficiency pipe, heat-transfer pipe, pipe external fin density 43fpi, manages the high 0.98mm of outer fin, and rib number is 48 weekly, interior tooth depth 0.37mm, whole heat exchanger uses 530 of heat-transfer pipes, and wherein supercooling tube is 21.
Scheme two: whole Exchanger Tubes adopts two-dimentional low ribbed pipe, pipe external fin density 56fpi, manages the high 1.0mm of outer fin, interior tooth depth 0.35mm, rib number is 48 weekly, and whole heat exchanger uses 450 of heat exchanger tubes, and wherein supercooling tube is 21.
In identical operating mode, the heat exchange property of two units is as following table, and test operating mode is according to standard GB/T/T18430.1-2001 vapor-compression cycle cold water (heat pump) unit---and industry and commerce is used and cold water (heat pump) unit of similar applications carries out:
| Test operating mode | Scheme one | Scheme two |
| Cooling water resistance/kPa | 95.1 | 110.7 |
| Refrigerating capacity/kW | 1727.5 | 1755.4 |
| Condensation saturation temperature/℃ | 36.9 | 36.9 |
| Power input to machine/kW | 402.4 | 402.3 |
Under identical operating mode, the whole unit refrigerating capacity of scheme two (being present patent application content) improves 27kW.Compressor power input is identical, and condensation saturation temperature is identical, and each unit is saved 80 of copper pipes, the every long 4m of copper pipe, and copper pipe wall thickness 1.15mm, the density of copper is 8930kg/m
3, each unit condenser of this model unit can saving copper 656.73kg.
Claims (4)
1. a horizontal tubular water condenser ', it is characterized in that: comprise and offer steam inlet (4), the condenser shell (1) of lime set outlet (7), in condenser shell (1), be provided with some groups of heating surface banks (2), some groups of described heating surface banks are divided into heating surface bank (2-1) and lower heating surface bank (2-2), in condenser shell (1) both sides, be provided with the hydroecium (6) being connected with heating surface bank (2), wherein on a side hydroecium (6), offer delivery port (9) and the water inlet (8) being connected with upper heating surface bank (2-1) and lower heating surface bank (2-2) respectively,
It is 50fpi～60fpi that described heating surface bank (2) adopts pipe external fin (10) density, and rib height is the low ribbed pipe of two dimension of 0.9mm～1.3mm, and two-dimentional low ribbed pipe individual pen internal thread (11) number is no less than 48, the high 0.35mm that is not less than of screw thread rib.
2. horizontal tubular water condenser ' according to claim 1, it is characterized in that: in described condenser shell (1), be also provided with steam baffle (5), described steam baffle (5) is positioned between heating surface bank (2-1) and lower heating surface bank (2-2).
3. horizontal tubular water condenser ' according to claim 2, it is characterized in that: described steam baffle (5) forms by the baffle plate (5-1) of two inclinations with (5-2), and the splayed that the baffle plate of two inclinations (5-1,5-2) replaces is in an overlapping arranged and is tilted laterally, angle of inclination 5-30 degree.
4. horizontal tubular water condenser ' according to claim 1, it is characterized in that: the baffle plate (5-1,5-2) that is two inclinations that outside that splayed arranges tilts that described steam baffle (5) comprises the upper flat plate be arrangeding in parallel (5-3) of upper end and is arranged on upper flat plate (5-3) lower end, angle of inclination 5-30 degree.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320567817.8U CN203478730U (en) | 2013-09-12 | 2013-09-12 | Horizontal shell-and-tube water-cooled condenser |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320567817.8U CN203478730U (en) | 2013-09-12 | 2013-09-12 | Horizontal shell-and-tube water-cooled condenser |
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| CN203478730U true CN203478730U (en) | 2014-03-12 |
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| CN201320567817.8U Expired - Fee Related CN203478730U (en) | 2013-09-12 | 2013-09-12 | Horizontal shell-and-tube water-cooled condenser |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105758033A (en) * | 2016-04-29 | 2016-07-13 | 北京天云动力科技有限公司 | Energy-efficient cooling system and method for data center |
| CN105823353A (en) * | 2016-03-23 | 2016-08-03 | 东华大学 | High-efficiency condenser |
| CN108981242A (en) * | 2018-08-15 | 2018-12-11 | 天津商业大学 | Heat exchanger tube water cooled condenser |
| CN110195994A (en) * | 2019-04-29 | 2019-09-03 | 西安交通大学 | A kind of high efficiency composition bilateral augmentation of heat transfer pipe |
| US11098934B2 (en) | 2018-01-16 | 2021-08-24 | Carrier Corporation | Guiding panel for condenser, condenser and refrigeration system |
-
2013
- 2013-09-12 CN CN201320567817.8U patent/CN203478730U/en not_active Expired - Fee Related
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105823353A (en) * | 2016-03-23 | 2016-08-03 | 东华大学 | High-efficiency condenser |
| CN105758033A (en) * | 2016-04-29 | 2016-07-13 | 北京天云动力科技有限公司 | Energy-efficient cooling system and method for data center |
| US11098934B2 (en) | 2018-01-16 | 2021-08-24 | Carrier Corporation | Guiding panel for condenser, condenser and refrigeration system |
| US11821665B2 (en) | 2018-01-16 | 2023-11-21 | Carrier Corporation | Guiding panel for condenser, condenser and refrigeration system |
| CN108981242A (en) * | 2018-08-15 | 2018-12-11 | 天津商业大学 | Heat exchanger tube water cooled condenser |
| CN110195994A (en) * | 2019-04-29 | 2019-09-03 | 西安交通大学 | A kind of high efficiency composition bilateral augmentation of heat transfer pipe |
| CN110195994B (en) * | 2019-04-29 | 2021-07-13 | 西安交通大学 | High-efficiency composite double-side reinforced heat transfer pipe |
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| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20140312 Termination date: 20150912 |
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| EXPY | Termination of patent right or utility model |