CN1759290A - Cooling system - Google Patents
Cooling system Download PDFInfo
- Publication number
- CN1759290A CN1759290A CNA2004800068066A CN200480006806A CN1759290A CN 1759290 A CN1759290 A CN 1759290A CN A2004800068066 A CNA2004800068066 A CN A2004800068066A CN 200480006806 A CN200480006806 A CN 200480006806A CN 1759290 A CN1759290 A CN 1759290A
- Authority
- CN
- China
- Prior art keywords
- water
- storage tank
- heat exchanger
- work
- space
- 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.)
- Granted
Links
- 238000001816 cooling Methods 0.000 title description 18
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 78
- 238000002347 injection Methods 0.000 claims description 8
- 239000007924 injection Substances 0.000 claims description 8
- 239000007788 liquid Substances 0.000 claims description 7
- 230000000717 retained effect Effects 0.000 claims description 4
- 238000005507 spraying Methods 0.000 abstract 1
- 238000001704 evaporation Methods 0.000 description 8
- 230000008020 evaporation Effects 0.000 description 8
- 238000007710 freezing Methods 0.000 description 8
- 230000008014 freezing Effects 0.000 description 8
- 239000002826 coolant Substances 0.000 description 6
- 239000012530 fluid Substances 0.000 description 5
- 230000000694 effects Effects 0.000 description 4
- 238000012423 maintenance Methods 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 238000009833 condensation Methods 0.000 description 3
- 230000005494 condensation Effects 0.000 description 3
- 238000001035 drying Methods 0.000 description 3
- 239000012809 cooling fluid Substances 0.000 description 2
- 239000000284 extract Substances 0.000 description 2
- 239000003507 refrigerant Substances 0.000 description 2
- 239000007921 spray Substances 0.000 description 2
- 238000012360 testing method Methods 0.000 description 2
- 206010060904 Freezing phenomenon Diseases 0.000 description 1
- 238000004140 cleaning Methods 0.000 description 1
- 235000019628 coolness Nutrition 0.000 description 1
- 230000003203 everyday effect Effects 0.000 description 1
- 238000011990 functional testing Methods 0.000 description 1
- 238000002955 isolation Methods 0.000 description 1
- 230000003287 optical effect Effects 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 238000007665 sagging Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 238000009423 ventilation Methods 0.000 description 1
- 238000009736 wetting Methods 0.000 description 1
Images
Classifications
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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
- F28D5/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, using the cooling effect of natural or forced evaporation
- F28D5/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, using the cooling effect of natural or forced evaporation in which the evaporating medium flows in a continuous film or trickles freely over the conduits
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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
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
-
- 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
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
-
- 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
- F28D5/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, using the cooling effect of natural or forced evaporation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/041—Details of condensers of evaporative condensers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/06—Damage
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)
- Devices For Blowing Cold Air, Devices For Blowing Warm Air, And Means For Preventing Water Condensation In Air Conditioning Units (AREA)
Abstract
A closed circuit evaporative heat exchanger comprises an air distribution plenum (4), means (36) for spraying water into the plenum (4) and a collection surface (22) for collecting unevaporated water sprayed into the plenum (4). The water is arranged to drain into a sump (16) within the plenum (4) without remaining on the collection surface (22).
Description
The present invention relates to a kind of cooling system, more particularly, the present invention relates to have a kind of cooling system of the closed circuit evaporative heat exchanger of forced ventilation structure.
Closed circuit evaporative heat exchanger is used for cooling or the condensation of various commercial plants so that cold-producing medium to be provided.Very widely, provide cooling, cooling fluid draw heat from want cooled zones wherein, and it is transported in the heat exchanger, the fluid cooling of getting back in this heat exchanger by cooling fluid.Under the situation that is the condensation of refrigerant system, as the part of process of refrigerastion, the cold-producing medium evaporation enters into heat exchanger, and there, it is condensed and leaves heat exchanger as liquid.In both cases, make the blows air over heat exchanger coil, thereby from liquid or steam, remove heat.Improve cooling procedure in the coil pipe by water is ejected into, therefore a part of water evaporates by air stream.
In these systems, the most of water that is ejected in the heat exchanger coil in the air distribution plenum is not evaporated, but is discharged to the storage tank that is arranged in the air distribution plenum bottom.Therefrom, it is pumped back in the injection nozzle to recycle by filter.Typical evaporation heat-exchanger product design becomes to use some common parts of closed circuit and unlimited cooling tower.Therefore, the storage tank in traditional closed circuit tower has enough big ability, thereby can be used in unlimited tower (opentower) and the closed circuit structure.
As mentioned above, by water being ejected in the coil pipe of heat exchanger, can improve the cooling that provides by heat exchanger.But, always do not need the cooling of this raising.For example, during the month in winter, do not carry out to obtain enough coolings under the situation of evaporation, promptly can carry out so-called " dry work " at water.
But dry need of work storage tank drains, because otherwise the water in the storage tank will be freezing, and owing to forced cold air flow is crossed it and damaged this system.This is debatable, because drain and the process need elapsed time of additional storage tank, needs many hours usually.In addition, during at least some drain or replenish, usually need to close cooling system, with by guaranteeing that connecting valve float, water level control etc. makes storage tank prepare dry or wet work separately.Therefore, in practice or economically, can not think that drain every day easily and additional storage tank.This means that in a short period in every year (even by day), only carry out dry work, some temperature insight in advance are enough low, therefore do not need " wetting " work.Should be understood that to save potentially and handle water pump and needed water of any sump heater and energy, consequently, cost saving widely.
In some closed circuit evaporative heat exchanger systems, what people also knew is, storage tank is provided, and this storage tank is arranged to away from air distribution plenum.At wet duration of work, most of unevaporated water are discharged from continuously or are pumped at a distance the storage tank, then in the storage tank from afar blowback to be ejected in the heat exchanger coil again.The advantage of the storage tank of this distant place is, needn't discharge all water to carry out drying work the storage tank in air distribution plenum, because have only the water of a small amount of to be retained in the air distribution plenum, and this can drain relatively quickly.Water in the remote sump can not be subjected to the cold airflow in the air distribution plenum, therefore can prevent freezing by suitable heater.
But storage tank at a distance also has many shortcomings.At first, need exceptional space that it is installed, this usually causes expense more expensive.The second, need more kinetic pump to solve the extra quiet height that pumps water is passed through.The 3rd, needed overall number of components and mounting cost have also improved.These factors lump together and have surpassed when making this system works more effectively any expense of water consumption and jet pump energy and save.But, need pump at a distance to carry out drying work, and can prevent cold in some cases.
Another problem of conventional closed circuit evaporative heat exchanger arrangements is, need make this system quit work with realize regular maintenance as some parts in the air distribution plenum are checked, functional test, cleaning etc.For the legacy system that does not have remote sump, this is a specific question, because equipment in the storage tank and water make-up system also are affected.This regular interruption of system operation obviously has destructiveness and expense expensive.
The purpose of this invention is to provide a kind of evaporation heat-exchanger, in this heat exchanger, the problems referred to above are resolved at least in part.
From first aspect, the invention provides a kind of closed circuit evaporative heat exchanger, this heat exchanger comprises: air distribution plenum; Be used for water is ejected into device in the described space; And collect the surface, and its is collected and is ejected into water in the described space, unevaporated, and therefore described water is discharged in the storage tank described space in, thereby is retained in basically on the collection surface.
Therefore, those of ordinary skills can see that storage tank still is arranged in the primary air allocation space, but this storage tank is not to be used for collecting unevaporated water, but are discharged to the storage tank from collecting the surface.This means that storage tank is isolated with the major part in this space is hot mutually at least in part.When atmospheric temperature during less than freezing point, it is freezing that this just can prevent that sealing carries out, and the traditional storage tank device that is exposed in this space air-flow can not be seen this freezing phenomenon.This layout has reality advantage flexibly: they can be changed as often needed between wet work and dry work fast, but the shortcoming of remote sump is not set.
This storage tank so arranges, so that can prevent that at the cold weather duration of work water-cooled from freezing.Isolate and heater is set, is preferably thermostatically controlled heater and realizes this by the heat of guaranteeing enough degree.This makes that also changing environment temperature can be resolved.
Collect the surface and can arrange simply and be discharged to the storage tank that is arranged in its below, promptly this layout is with traditional the sort of the same effective, covers or analog covers storage tank but have, and has a tap or a plurality of tap.In this case, the upper surface of lid forms and collects the surface.
But, preferably, arrange the liquid lock (liquid lock) that forms between the two at the discharge interface of collecting between surface and the storage tank, therefore between them, can keep uneven air pressure.The advantage of this feature is, storage tank can remain under the basic atmospheric pressure, and the major part of this air is in the rising pressure that forced draft produces simultaneously.Also can avoid contacting with water jet with the physical isolation between the primary air allocation space inside in storage tank inside.Even be in the work and associated fan when turning round in this system, these two factors also make and can enter at least in the storage tank to safeguard.Should be understood that this ability with respect to having to and quit work and produced tangible advantage with the prior art systems of carrying out regular maintenance.
As in the prior art, by water yield storage tank, that be used in jet circulating system be used in the identical of the storage tank that opens wide in the tower cooler system.But, these application are known, because novel storage tank formed according to the present invention, therefore the forfeiture of the common advantage between the storage tank assembly seldom, but this means, use the capacity limitation that common sump produced no longer to need to be suitable for, in fact, by using a spot of water can obtain extra advantage.
Accordingly, in a preferred embodiment, evaporative water spray system is arranged to use with respect to the wet just enough water of work and carries out work.In an example embodiment, this system carries out work with the every square metre of coil area of about 90 premium on currency.This and legacy system have formed contrast, in legacy system, use about 240L/m
2Volume (it is consistent with the storage tank that uses standard dimensions).
Not only use the water capacity that obviously reduces to save water, but also mean the storage tank of storage tank less than other situation, a heater that required power is littler prevents that it is freezing, and needed Water Treatment is less, and all these help to reduce expense.
The preferred embodiment of the present invention that proposes above should be understood to and comprises the needed least quantity of use evaporation process.In practice, the needed least quantity of pumping system when this minimum depends on the ratio of the ability of the water distribution system that comprises pipeline engineering, the water that falls by air distribution plenum and carries out proper operation on any one time.This and prior art have formed contrast, and in the prior art, the minimum of employed volume during obviously greater than wet work in fact in the prior art, do not considered this minimum demand in the past.
Should be understood that in practice of the present invention generator replenishes the water that is lost by evaporation.Can use valve, electronic sensor, optical pickocff of any device commonly known in the art such as float-operated etc.This water replenishes has some intrinsic hysteresis, and therefore the actual water capacity in this system can circulate between predetermined minimum and maximum value when any one time.
Now,, only the preferred embodiments of the present invention are described by example with reference to accompanying drawing, in these accompanying drawings:
Fig. 1 is a cutaway view for the shown conventional closed circuit evaporative heat exchanger of reference purpose; And
Fig. 2 a and 2b each sectional side view and end-view of closed circuit evaporative heat exchanger of the present invention naturally.
At first, with reference to Fig. 1, it shows the closed circuit evaporative heat exchanger of prior art.Coolant liquid is arranged among air distribution plenum (plenum) B by sealed heat exchanger coil A wherein.The fan system C that is driven by motor D is arranged on the end of space B.At the top of space B is series of nozzles, and these arrangement of nozzles are ejected into water on the heat exchanger coil A.Storage tank F is arranged on the bottom of space B, and it is 240 liters ability that this storage tank has every square metre of coil area, and pump G is provided with water upwards is pumped out to the injection nozzle E from storage tank F.Used the water make-up system H of float valve to guarantee in storage tank, to keep the water of minimum.
In when work, coolant liquid or refrigerant vapour supply on the heat exchanger coil A, and before it returns, thereby heat is extracted it is cooled off or condensation there, and these are commonly known in the art.In air distribution plenum B, fan C forces air to flow through heat exchanger A fast, thereby extracts heat from coolant fluid or steam.Provide the steam cooling by water injection system, wherein this water injection system uses pump G pump up water from storage tank F.Some water that ejected from nozzle E are evaporated.Remaining water is collected among the storage tank F, and therefrom, it loops back up among the injection nozzle E.The water that is lost by evaporation compensates by water make-up system H.
In order to enter storage tank F, therefore need close this system and turn off fan C, thereby can limit the frequency that can realize this in the practice to carry out examination and maintenance.In addition, no longer need this extra cooling effect of water injection system, from storage tank F, must discharge all water so, thereby prevent that it is owing to the cooling effect of forced cold air flow is carried out freezing if environment temperature makes.This will consume the so many time, thereby so that be sure of the operator that this temperature is not elevated to once more and just can realize this when enough height are long-time to need wet practice (promptly surpassing 1 day time).
In Fig. 2 a and 2b, see embodiments of the invention now.As in the device of describing at reference Fig. 1, closed circuit evaporative heat exchanger comprises heat exchanger coil 2, this coil pipe 2 is arranged in the air distribution plenum 4, and by pipe connections 6 coolant fluid or cold-producing medium are transported to and want in the cooled zones (not shown) and transport from coolant fluid or the cold-producing medium of wanting cooled zones.Fan 8 is positioned at an end of air distribution plenum 4, and this fan 8 is driven by motor 10 by belt 12.The blade of fan 8 is installed in the housing 14, therefore can not see in Fig. 2 a.
Different with system shown in Figure 1 is not have the storage tank that opens wide in the bottom of air distribution plenum 4.And limit storage tank 16 in an end bottom of air distribution plenum 4 by inclination buffer wall 18.In this embodiment, the ability of storage tank is 90 liters of every square metre of coil area, but this only is the example explanation, and this accompanying drawing for example depends on coil lengths.Buffer wall 18 from the space 4 aft bulkhead 20 sagging downwards.It delimits leaving gap between the bottom of its end and storage tank 16.Buffer wall 18 extends between two opposing sidewalls in space 4, in other words, perpendicular to the plane of Fig. 2 a, perhaps from left to right extends among Fig. 2 b.
In storage tank 16, have to be connected to and enter valve 26 in the jet pipe 28, float-operated, thereby in storage tank 16, keep minimum water level.This water level be set to the needed minimum of heat exchanger wet practice (consider in system's remainder some the pipe etc. ability).Filter 30 is arranged in the bottom of storage tank 16, draw and upwards be pumped into vertical tube 34 on the outside that is arranged in rear end, space 20 from the water of storage tank by pump 32 through this filter 30, there, it reenters in this space 4 for giving water distribution pipe 36.
Series of spray nozzles 38 is spaced along water distribution pipe 36, therefore forces water to come out with conical jet to the mode on the heat exchanger coil 2 under 32 applied pressure effects of pump.Can be clear that such nozzle 38 more in the scrap detail view above it.A series of drift eliminators 40 are positioned at water distribution pipe 36 tops, and one of them drift eliminator also is shown more clearly in the scrap detail view.These separately are entrained in the water droplet in the air stream that leaves heat exchanger, and prevent that these water droplets from losing from this system.
At last, a pair of door 42 that carries out is arranged on the bottom of space end wall 20, thereby can enter into the inside of storage tank 16 from the outside.
The work of this device is described now.As in the prior art systems, fan 8 forces air to flow through heat exchanger coil 2, thereby extracts heat from the coolant fluid thing.When needs additionally cooled off, pump 32 carried out work drawing water from storage tank 16 by filter 30, and forces it to pass through nozzle 38, thereby formed meticulous injection on heat exchanger coil.Can obtain tangible cooling effect by some water of evaporation.Unevaporated water falls towards the bottom of air distribution plenum 4, and falls by on buffer wall 18 or the 22 formed collection surfaces, tilting bottom.The water of falling in these parts can not remain there, but is discharged in the little gap 24 between them.
As from known to Fig. 2 a, the water level in the storage tank is such, so that gap 24 is filled with water at least in part.This has formed sluice (water lock) between air distribution plenum 4 and storage tank 16.Sluice allows to keep different air pressures between the major part in space 4 and storage tank 16, thereby can enter in the storage tank 16, thereby for example carries out examination and maintenance, and main fan 8 still carries out work in running and this system simultaneously.
At dry duration of work, pump 32 cuts out and remaining water is discharged in the storage tank 16 by gap 24.In storage tank 16, water no longer directly contacts with the air stream that fan 12 is produced.Therefore, should be appreciated that, promptly contact, so the possibility that it is frozen has obviously reduced with cold airflow owing to there is not water to be retained in the major part of air distribution plenum 4.
Although in Fig. 2 a, do not illustrate, thermostatically controlled warmer is set the water temperature in the storage tank 16 is kept greater than cryogenic temperature.But owing to compare with allocation space 4, storage tank 16 is less relatively, and separates mutually with cold air stream by buffer wall 18, so these heater desired power are less relatively.
Should be appreciated that also the water yield in the storage tank 16 is significantly less than the storage tank F among Fig. 1.This has not only saved the needed water yield of this equipment of filling, but also has saved needed chemically treated expense and prevented its freezing needed heat.
The foregoing description has produced such overall advantage: as required, be operated in fully neatly in wet or the drying mode, and can change very apace between these patterns.
Example
The structure and the test and with reference to Fig. 2 a and described in the above those the similar exemplary device of 2b.The sump water volume of testing arrangement is 860 liters, and fan produces the air stream of 27 cubic metres of per seconds on heat exchanger coil.But, keep normal atmospheric pressure by sluice in storage tank inside.
When the pump of evaporative cooling system cuts out and atmospheric temperature is reduced to-10 ℃ when spending,, make storage tank and sluice keep fully not ice by from the sump heater of moderate 4KW, carrying out the heat input.
Claims (4)
1. closed circuit evaporative heat exchanger, this heat exchanger comprises: air distribution plenum; Be used for water is ejected into device in the described space; And collect the surface, and its is collected and is ejected into water in the described space, unevaporated, and therefore described water is discharged in the storage tank described space in, thereby is retained in basically on the collection surface.
2. heat exchanger as claimed in claim 1, it comprises that at the discharge interface of collecting between surface and the storage tank described interface is arranged and formed the liquid lock of collecting between surface and the storage tank, therefore can keep uneven air pressure between them.
3. as claim 1 or 2 described heat exchangers, it is characterized in that, be used for the described device of injection water to be arranged to use the water just enough to carry out work with respect to the described wet work of heat exchanger.
4. heat exchanger as claimed in claim 3, this heat exchanger carries out work with the every square metre of coil area of about 90 premium on currency.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GBGB0303195.2A GB0303195D0 (en) | 2003-02-12 | 2003-02-12 | Cooling system |
| GB0303195.2 | 2003-02-12 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1759290A true CN1759290A (en) | 2006-04-12 |
| CN100398972C CN100398972C (en) | 2008-07-02 |
Family
ID=9952888
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2004800068066A Expired - Lifetime CN100398972C (en) | 2003-02-12 | 2004-02-06 | Cooling system |
Country Status (14)
| Country | Link |
|---|---|
| US (1) | US20060168981A1 (en) |
| EP (1) | EP1592936B1 (en) |
| JP (1) | JP4238263B2 (en) |
| KR (1) | KR100731834B1 (en) |
| CN (1) | CN100398972C (en) |
| AU (1) | AU2004211510B2 (en) |
| BR (1) | BRPI0407423A (en) |
| CA (1) | CA2515736C (en) |
| DE (1) | DE602004006719T2 (en) |
| ES (1) | ES2285424T3 (en) |
| GB (1) | GB0303195D0 (en) |
| MX (1) | MXPA05008542A (en) |
| MY (1) | MY137660A (en) |
| WO (1) | WO2004072569A1 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101903714B (en) * | 2008-01-11 | 2012-08-15 | 江森自控科技公司 | Vapor compression system |
| CN103353243A (en) * | 2013-07-03 | 2013-10-16 | 无锡宇吉科技有限公司 | Spraying-type heat exchanger |
| CN103890526A (en) * | 2011-09-30 | 2014-06-25 | 豪威株式会社 | Ice thermal storage tank and water cooler having the same |
Families Citing this family (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7698906B2 (en) * | 2005-12-30 | 2010-04-20 | Nexajoule, Inc. | Sub-wet bulb evaporative chiller with pre-cooling of incoming air flow |
| US20080041087A1 (en) * | 2006-08-18 | 2008-02-21 | Jaeggi/Guntner (Schweiz) Ltd. | Hybrid dry cooler heat exchange with water-droplet slit and water-droplet splitting louver for heat exchangers with primarily latent heat transfer |
| MX2011009109A (en) | 2009-03-03 | 2011-10-19 | Harol Dean Curtis | Direct forced draft fluid cooler/cooling tower and liquid collector therefor. |
| US20110048051A1 (en) * | 2009-08-27 | 2011-03-03 | Duffy Robert D | Heating Ventilation Air Conditioner (HVAC) Compressor Efficiency Enhancement Apparatus |
| US9546804B2 (en) * | 2009-12-16 | 2017-01-17 | Heatcraft Refrigeration Products Llc | Microchannel coil spray system |
| CN103134343B (en) * | 2011-11-25 | 2015-02-25 | 北京紫荆信达节能科技有限公司 | Heat source tower with solution capable of regeneration function |
| US9207018B2 (en) | 2012-06-15 | 2015-12-08 | Nexajoule, Inc. | Sub-wet bulb evaporative chiller system with multiple integrated subunits or chillers |
| US10107001B2 (en) | 2014-03-28 | 2018-10-23 | Syntech Towers, L.L.C. | CMU cooling tower and method of construction |
| CN105466246B (en) * | 2015-12-31 | 2018-02-16 | 广州爱高空调设备有限公司 | Falling film type evaporation cooling coil, the method and falling-film heat exchanger for manufacturing the coil pipe |
| EP3306246B1 (en) * | 2016-10-06 | 2020-09-30 | Jaeggi HybridTechnologie AG | Heat exchange device |
| US10852079B2 (en) | 2017-07-24 | 2020-12-01 | Harold D. Curtis | Apparatus for cooling liquid and collection assembly therefor |
| US11609051B2 (en) | 2020-04-13 | 2023-03-21 | Harold D. Revocable Trust | Apparatus for cooling liquid and collection assembly therefor |
| US11761707B2 (en) * | 2020-12-23 | 2023-09-19 | Alfa Laval Corporate Ab | Evaporative wet surface air cooler |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2890864A (en) * | 1956-04-18 | 1959-06-16 | Niagara Blower Co | Heat exchanger |
| US3784171A (en) * | 1968-02-16 | 1974-01-08 | Baltimore Aircoil Co Inc | Evaporative heat exchange apparatus |
| US3677029A (en) * | 1970-12-03 | 1972-07-18 | Frick Co | Evaporative condenser |
| US4519450A (en) * | 1983-05-04 | 1985-05-28 | Niagara Blower Company | Vacuum producing condenser |
| CN2144287Y (en) * | 1992-11-24 | 1993-10-20 | 山东建筑工程学院 | Closed cooling tower |
| CN2304095Y (en) * | 1997-01-15 | 1999-01-13 | 李永光 | Tightly-closed cooling tower |
| US6213200B1 (en) * | 1999-03-08 | 2001-04-10 | Baltimore Aircoil Company, Inc. | Low profile heat exchange system and method with reduced water consumption |
-
2003
- 2003-02-12 GB GBGB0303195.2A patent/GB0303195D0/en not_active Ceased
-
2004
- 2004-01-29 MY MYPI20040255A patent/MY137660A/en unknown
- 2004-02-06 US US10/545,240 patent/US20060168981A1/en not_active Abandoned
- 2004-02-06 ES ES04708825T patent/ES2285424T3/en not_active Expired - Lifetime
- 2004-02-06 CA CA2515736A patent/CA2515736C/en not_active Expired - Lifetime
- 2004-02-06 MX MXPA05008542A patent/MXPA05008542A/en active IP Right Grant
- 2004-02-06 DE DE602004006719T patent/DE602004006719T2/en not_active Expired - Lifetime
- 2004-02-06 KR KR1020057014990A patent/KR100731834B1/en active IP Right Grant
- 2004-02-06 AU AU2004211510A patent/AU2004211510B2/en not_active Ceased
- 2004-02-06 CN CNB2004800068066A patent/CN100398972C/en not_active Expired - Lifetime
- 2004-02-06 JP JP2006502245A patent/JP4238263B2/en not_active Expired - Fee Related
- 2004-02-06 WO PCT/GB2004/000459 patent/WO2004072569A1/en active IP Right Grant
- 2004-02-06 BR BR0407423-8A patent/BRPI0407423A/en not_active IP Right Cessation
- 2004-02-06 EP EP04708825A patent/EP1592936B1/en not_active Expired - Lifetime
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101903714B (en) * | 2008-01-11 | 2012-08-15 | 江森自控科技公司 | Vapor compression system |
| CN103890526A (en) * | 2011-09-30 | 2014-06-25 | 豪威株式会社 | Ice thermal storage tank and water cooler having the same |
| US10451343B2 (en) | 2011-09-30 | 2019-10-22 | Coway Co., Ltd | Ice thermal storage tank and water cooler having the same |
| CN103353243A (en) * | 2013-07-03 | 2013-10-16 | 无锡宇吉科技有限公司 | Spraying-type heat exchanger |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2006517647A (en) | 2006-07-27 |
| EP1592936A1 (en) | 2005-11-09 |
| KR20050100399A (en) | 2005-10-18 |
| WO2004072569A1 (en) | 2004-08-26 |
| JP4238263B2 (en) | 2009-03-18 |
| AU2004211510A1 (en) | 2004-08-26 |
| US20060168981A1 (en) | 2006-08-03 |
| AU2004211510B2 (en) | 2008-01-17 |
| MY137660A (en) | 2009-02-27 |
| BRPI0407423A (en) | 2006-01-24 |
| EP1592936B1 (en) | 2007-05-30 |
| DE602004006719D1 (en) | 2007-07-12 |
| KR100731834B1 (en) | 2007-06-25 |
| CA2515736C (en) | 2010-07-13 |
| GB0303195D0 (en) | 2003-03-19 |
| CA2515736A1 (en) | 2004-08-26 |
| ES2285424T3 (en) | 2007-11-16 |
| MXPA05008542A (en) | 2005-10-20 |
| CN100398972C (en) | 2008-07-02 |
| DE602004006719T2 (en) | 2008-01-31 |
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