CN106461297A - Improved evaporative condenser - Google Patents
Improved evaporative condenser Download PDFInfo
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- CN106461297A CN106461297A CN201580025168.0A CN201580025168A CN106461297A CN 106461297 A CN106461297 A CN 106461297A CN 201580025168 A CN201580025168 A CN 201580025168A CN 106461297 A CN106461297 A CN 106461297A
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- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 102
- 239000003507 refrigerant Substances 0.000 claims abstract description 16
- 238000005057 refrigeration Methods 0.000 claims abstract description 16
- 238000004378 air conditioning Methods 0.000 claims abstract description 13
- 238000009833 condensation Methods 0.000 claims description 44
- 230000005494 condensation Effects 0.000 claims description 41
- 238000000034 method Methods 0.000 claims description 34
- 238000001704 evaporation Methods 0.000 claims description 14
- 230000008020 evaporation Effects 0.000 claims description 12
- 230000003134 recirculating effect Effects 0.000 claims description 10
- 239000010935 stainless steel Substances 0.000 claims description 6
- 229910001220 stainless steel Inorganic materials 0.000 claims description 6
- 239000007788 liquid Substances 0.000 claims description 5
- 238000013016 damping Methods 0.000 claims description 3
- 230000003020 moisturizing effect Effects 0.000 claims description 3
- 230000037237 body shape Effects 0.000 claims description 2
- 238000009736 wetting Methods 0.000 abstract 2
- QGZKDVFQNNGYKY-UHFFFAOYSA-N Ammonia Chemical compound N QGZKDVFQNNGYKY-UHFFFAOYSA-N 0.000 description 48
- 229910002092 carbon dioxide Inorganic materials 0.000 description 45
- 229910021529 ammonia Inorganic materials 0.000 description 23
- ATUOYWHBWRKTHZ-UHFFFAOYSA-N Propane Chemical compound CCC ATUOYWHBWRKTHZ-UHFFFAOYSA-N 0.000 description 18
- 238000001816 cooling Methods 0.000 description 16
- 238000013461 design Methods 0.000 description 13
- 239000007789 gas Substances 0.000 description 13
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- 239000001294 propane Substances 0.000 description 9
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- 229930195733 hydrocarbon Natural products 0.000 description 8
- 239000000126 substance Substances 0.000 description 7
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 6
- 229910000831 Steel Inorganic materials 0.000 description 6
- NNPPMTNAJDCUHE-UHFFFAOYSA-N isobutane Chemical compound CC(C)C NNPPMTNAJDCUHE-UHFFFAOYSA-N 0.000 description 6
- 230000008569 process Effects 0.000 description 6
- 239000010959 steel Substances 0.000 description 6
- 239000004215 Carbon black (E152) Substances 0.000 description 5
- 238000005260 corrosion Methods 0.000 description 5
- 230000007797 corrosion Effects 0.000 description 5
- 150000002430 hydrocarbons Chemical class 0.000 description 5
- -1 isobutyl Alkane Chemical class 0.000 description 5
- 230000008859 change Effects 0.000 description 4
- 238000005516 engineering process Methods 0.000 description 4
- 239000001282 iso-butane Substances 0.000 description 4
- 235000013847 iso-butane Nutrition 0.000 description 4
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- 239000007921 spray Substances 0.000 description 3
- 238000005507 spraying Methods 0.000 description 3
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- 229910001209 Low-carbon steel Inorganic materials 0.000 description 2
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- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 1
- 241001481710 Cerambycidae Species 0.000 description 1
- CBENFWSGALASAD-UHFFFAOYSA-N Ozone Chemical compound [O-][O+]=O CBENFWSGALASAD-UHFFFAOYSA-N 0.000 description 1
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Classifications
-
- 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
- F25B39/00—Evaporators; Condensers
- F25B39/04—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
- F25B39/00—Evaporators; Condensers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28B—STEAM OR VAPOUR CONDENSERS
- F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
- F28B1/02—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using water or other liquid as the cooling medium
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28C—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA COME INTO DIRECT CONTACT WITHOUT CHEMICAL INTERACTION
- F28C1/00—Direct-contact trickle coolers, e.g. cooling towers
- F28C1/14—Direct-contact trickle coolers, e.g. cooling towers comprising also a non-direct contact heat exchange
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28C—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA COME INTO DIRECT CONTACT WITHOUT CHEMICAL INTERACTION
- F28C1/00—Direct-contact trickle coolers, e.g. cooling towers
- F28C1/16—Arrangements for preventing condensation, precipitation or mist formation, outside the cooler
-
- 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
- F28D3/00—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 flows in a continuous film, or trickles freely, over the conduits
- F28D3/02—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, in which the other heat-exchange medium flows in a continuous film, or trickles freely, over the conduits with tubular conduits
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F25/00—Component parts of trickle coolers
- F28F25/02—Component parts of trickle coolers for distributing, circulating, and accumulating liquid
-
- 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
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/046—Condensers with refrigerant heat exchange tubes positioned inside or around a vessel containing water or pcm to cool the refrigerant gas
-
- 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
- F25B2339/047—Water-cooled condensers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F25/00—Component parts of trickle coolers
- F28F2025/005—Liquid collection; Liquid treatment; Liquid recirculation; Addition of make-up liquid
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Central Air Conditioning (AREA)
Abstract
An evaporative condenser (10) for use in a refrigeration or air-conditioning system comprises one or more condensing coils (12) arranged in a condensing coil zone (13). The coils condense therewithin a refrigerant of the system. The condenser also comprises a mechanism (14, 15) for wetting the one or more condensing coils (12). The condenser further comprises drift eliminators (30) arranged to remove free water from an airstream A that has flowed past the one or more condensing coils and wetting mechanism (14, 15). The condenser additionally comprises a divergent zone (40) that diverges from the condensing coil zone (13) towards the drift eliminators (30) such that, once the airstream has flowed past the one or more condensing coils (12), it flows into and through the divergent zone 40 to the drift eliminators (30).
Description
Technical field
Disclose a kind of improved evaporative condenser used in refrigeration and air conditioning system and evaporative condenser technique.Described
Condenser and technique can adopt chemical refrigerant (such as HFC) and natural refrigerant (such as hydro carbons (such as propane and isobutyl
Alkane), CO2, ammonia etc.).
Background technology
Current evaporative condenser discharges heat by the condensation of cold-producing medium in various refrigeration and air conditioning system.More
Body ground, evaporative condenser includes (for example through spraying) condenser coil of one or more moistenings, and which passes through gas above
Circulation road is condensed to cold-producing medium, and by a part of water evaporation to wherein, so as to by heat from cold-producing medium in condenser coil
Middle removing, while cause condensing agent to condense wherein.Evaporative condenser also includes dehydrater, and (or more simply, separator, will
Water " drift " is walked, and otherwise these water will be just transferred in air).Before air-flow is discharged into the atmosphere, with air-flow stream
Condensed coil pipe and water spray device, dehydrater eliminates the free water with air current flow.
In current evaporative condenser, the reserved area (plan area) of condenser coil and the reserved area of dehydrater
Match, constant to guarantee airflow rate by evaporative condenser and air velocity.
In current evaporative condenser, heat exchanger effectiveness is limited by the air velocity institute for flowing through condenser coil.Air speed
Degree is subject to the ability that dehydrater removing flows through free water in air-flow therein to be limited in turn again.In current evaporative condenser
In, the water recirculation of this removing is to be re-used for moistening condenser coil.However, flowing through dehydrater to appointing in air with air
He Shuizhong may contain antibacterial, such as Legionnella, it is therefore desirable to remove free water as much as possible from air-flow.
For example, in many current evaporative condensers, it is known that the maximum air velocity of dehydrater need to be set by
Up to 3.5 to 4m/s, to guarantee fully to remove water, however, it is assumed that under so high maximum air velocity, however it remains
Antibacterial (such as Legionnella) is by the notable risk of dehydrater together with the free water not removed.Suggestion is by dehydrater more
The maximum air velocity of safety is 3.5m/s.However, this air velocity again in turn to flowing through condenser coil is arranged and is limited.
Above-mentioned the technology segment for not necessarily constituting to those of ordinary skill in the art's common knowledge is quoted to background technology
Accreditation.Above-mentioned list of references is not intended to limit the application of condenser disclosed herein and technique.
Content of the invention
The invention discloses a kind of evaporative condenser for freezing with air conditioning system.Evaporative condenser as disclosed herein
Condensable chemical refrigerant (such as HFC, HCFC, perfluocarbon, HF hydrocarbon etc.) and natural refrigerant is (for example
Hydro carbons (such as propane and iso-butane), CO2, ammonia etc.).
Evaporative condenser includes the one or more condenser coils for cold-producing medium among condenser system as disclosed herein.
One or more of condenser coils are may be provided in the condenser coil region of evaporative condenser.The condenser coil region Ke Bao
Include the air chamber with constant cross-sectional area.
Evaporative condenser is also included for moistening (for example, by being sprayed to them with water) as disclosed herein
Or the device of multiple condenser coils.
Evaporative condenser further includes the dehydrater for arranging as disclosed herein, has been flowed through with removing one or more cold
Free water in the air-flow of solidifying coil pipe and damping device.
According to disclosed in this invention, evaporative condenser disclosed herein includes to shunt from condenser coil to dehydrater
Shunting zone.The construction of the shunting zone is such, once air-flow has passed through one or more condenser coils, which flows into and leads to
Cross shunting zone and enter dehydrater.For example, the shunting zone may include the air chamber being gradually increased with cross-sectional area.
The shunting zone enables to leave the flow slowing down in condenser coil region.This means to flow through the sky of condenser coil
Gas speed can be increased with respect to the air velocity for flowing through dehydrater.This higher speed can help reduce the dirt in pipe
Dirt.
In addition, it has therefore been surprisingly found that the condenser coil that can be reduced using the reserved area having with respect to dehydrater
Bundle.Less condenser coil is needed to reach identical condensation performance in this regard, further result of this is that.This means to produce
More inexpensive evaporative condenser, because condensate pans tube bank is equivalent to the part of unique most expensive in this condenser.
Additionally, increased cold-producing medium stream can be restrained by condensate pans, because higher air velocity can cause relatively more
Most condensing agent condensation.
Additionally, it means that replacement as the known hot dipping galvanized carbon steel condensing tube for using, can use more expensive
And/or firmer material (such as rustless steel) is constituting one or more condenser coils, so as to obtain longer life-span, less
Corrosion and, optionally, the thinner pipe wall material for coil pipe (pipe) can be used.Even so, if preferred, still
So can be seamless using DN 8,10,15 and 20 (subordinate list 40), hot dipping is seamless carbon electroplating steel pipe to be forming one or more condensations
Coil pipe.
In one embodiment, each Cai Yong the stainless steel tube in one or more condenser coils is (for example, outward
Footpath is 4.76-31.8mm, thickness is 304 or 316 rustless steels of 0.5-1.6mm).Can be provided using 304 rustless steels and preferably lead
Electrically, and 316 rustless steels can provide more preferable corrosion resistance.Compared with known plating mild steel condenser coil, such pipe
Material preferably can run.Go for some small-scale applications using the pipe of very minor diameter.
Can also be permitted using stainless steel tube material (that is, according to corrosion-resistant/chemical resistance, elevated refrigerant pressure capacity etc.)
Perhaps using natural refrigerant, such as propane and/or iso-butane Hydrocarbon, CO2, ammonia etc..
In one embodiment, one or more condenser coils can arrange bunchy (for example, two in condensate pans area under control
Or multiple nesting coil bundles).For example, the condensate pans area under control can containing the condenser of one section of cross-sectional area constant (for example,
Circle, the air chamber of the hollow section such as square, rectangle).
In one embodiment, the shunting part in region can be configured to makes air-flow slow down in the way of being gradually reduced.
In one embodiment, the shunting zone can containing make hollow frustum that air stream circulated wherein (in
Absolutely empty air chamber).Such hollow frustum may be located at the air outlet slit side of condenser coil air compartment.For example, when condensate pans manage-style
When room is circular cross-section, each self-contained conical frustum of frustum or square subcircular (square-to- is shunted
Circular frustum-shaped prism)；When condenser coil air compartment is square-section, shunting frustum can include square
Frustum, etc..
In one embodiment, the dehydrater can be close proximity to the air of shunting zone and leave away side.
In one embodiment, the condenser may include the air intake of the air inlet side positioned at condensate pans area under control
Room.
In one embodiment, for the part of the one or more condenser coils of moistening, one or more sprays may include
Mouth.The nozzle can be arranged with respect to shunting zone, with the rightabout of the air-flow for flowing through one or more condenser coils on will
Water is ejected on one or more condenser coils.For example, the nozzle is may be provided in shunting zone, and generally can by water with
Liquid taper is ejected in condensate pans area under control.
Or, moisture circulation road is may include for the part of the one or more condenser coils of moistening, for example those have saw
Toothed edge, with inside groove, etc..
The condenser may include a water collecting region (for example, positioned at the bottom of air intake room).The collecting region can
To collect the water for having passed through condensate pans area under control.
The condenser can further include the recirculating system for the water of collection to be recycled to wetted part, so that
Condenser efficiency is maximized.In one embodiment, the recirculating system may include one for will collect water via
Pipeline is pumped into the pump of wetted part.For example, discharge pipe can extend to pump from air intake room, and delivery pipe can be from pump discharge
Extend to wetted part (for example, to nozzle, arriving shunt conduit etc.).
In one embodiment, recirculating system can further include the water (example for maintaining scheduled volume as required
Such as, in water collecting region) moisturizing part, for effective operation of evaporative condenser.This moisturizing may include what dehydrater was removed
(capture) water.
In one embodiment, (for example, individually, laterally the evaporative condenser can further include heat exchanger
The discrete heat exchange unit of positioning).The water of collection can first pass through heat exchanger before wetted part is recycled to.Additionally, cold
Solidifying cold-producing medium can flow through heat exchanger to carry out heat exchange with collected recirculation water.This heat exchanger can be used for cold
Solidifying cold-producing medium carries out sub-cooled, to improve the operational efficiency of evaporative condenser further.
There is disclosed herein a kind of evaporative condenser, which includes collecting region, and the collecting region is used for collection and has flowed through condensation
The water in coil pipe area, and including heat exchanger, collected water can first pass through heat exchanger before wetted part is recycled to, and
And, the cold-producing medium stream of condensation carries out heat exchange through heat exchanger with collected recirculation water.
There is disclosed herein a kind of evaporative condenser technique for the part for forming refrigeration or Air-conditioning Cycle.
The technique includes to make cold-producing medium stream through one or more condenser coils.The technique is also included with water-wet one
Or multiple condenser coils.The technique further includes to cause air flow through the condenser coil of one or more moistenings, so that
Cold-producing medium in disk in-tube condensation, whereby so that a part of water evaporation is entered in air-flow.The technique comprise additionally in from one or
Water that leave in multiple condenser coils, existing in the gas flow is removed.
According to present disclosure, remove present in air-flow before water, caused from one or many using the technique
The air velocity that leaves in individual condenser coil is minimized.
As mentioned previously, this can cause the reserved area (and therefore reduce) of one or more condenser coils with respect to
Dehydrater (thing followed advantage as described above) has been reduced.
There is disclosed herein a kind of steam condensation process, wherein, the water for flowing through one or more condenser coils is collected simultaneously
Recirculation is with the one or more condenser coils of water-wet.Additionally, in the process, in collected water recirculation with moistening one
Before individual or multiple condenser coils, between the cold-producing medium and collected water of condensation, heat can be exchanged.
Processes disclosed herein can be carried out in evaporative condenser as above.
In process disclosed herein, the cold-producing medium for condensing in one or more condenser coils can include natural system
Cryogen (for example, hydro carbons, such as propane and/or iso-butane, CO2, ammonia etc.), or chemical refrigerant (for example, HFC, hydrogen chlorine fluorine
Hydrocarbon, perfluocarbon, HF hydrocarbon etc.).
Brief Description Of Drawings
Although there may be any other form in the range of condenser and the technique for falling into as illustrated in summary, existing
Only by way of example and specific embodiment will be described with reference to the drawings：
Fig. 1 shows the cross-sectional side view of evaporative condenser, its have be provided with one or more condenser coils condensation
Coil pipe area, and the shunting zone for extending out from condensate pans area under control.
Fig. 2 shows Fig. 1 details, illustrates a kind of version of evaporative condenser, and which further includes side heat exchange
Device；With
The evaporation that Fig. 3 A and 3B are respectively illustrated with contraction-breathing space (being provided with one or more condenser coils) is cold
The cross-sectional view of condenser and side view；
Fig. 4 shows the cross-sectional side schematic diagram of the evaporative condenser similar to Fig. 1, but is suitable for according to embodiment different
Technological parameter；
Fig. 5 shows the CO according to embodiment2With coolant-temperature gage curve chart；
Fig. 6 shows the CO according to embodiment2Thermal capacitance curve chart；
Fig. 7 shows the curve chart of the water for flowing downward according to embodiment along tube bank；
Fig. 8 shows the curve chart of the overall heat-transfer coefficient according to embodiment and the pressure loss；
Fig. 9 is shown according to embodiment, based on commercially available supercritical CO2Compressor is under 5 DEG C of saturation suction, and 5K has
The CO of suction superheat and 5 DEG C2Heat extraction curve chart under temperature of liquid；
Figure 10 is shown according to embodiment, commercially available supercritical CO2Compressor is in 50Hz.30kW/27.2m3Under/h
Performance map；With
Figure 11 is shown according to embodiment, NH3, the performance demands of R22R507A, propane and R134a under saturation condensation temperature
Number (COP) variation diagram.
Specific embodiment is described in detail
It is described below the concrete form of evaporative condenser, and the composition portion for forming refrigeration or air conditioning system/circulation
The evaporative condenser technique that divides.
The evaporative condenser embodiment for being labeled as 10 and 100 is shown in Fig. 1 and Fig. 2 and Fig. 3 A and 3B.Evaporation is cold
Condenser embodiment 10 and 100 can use chemical refrigerant and natural refrigerant (as described above).Fig. 4 is related to embodiment to 11
Described in embodiment.
In Fig. 1 to Fig. 3, the similar assembly of evaporative condenser 10 and 100 is similarly numbered, but the embodiment party of Fig. 3
100 are with the addition of in formula.It is to be further understood that for simplicity, below describe and do not redescribe those and reappear
Similar or identical component in Fig. 3 embodiment, therefore should be considered as had been noted above.
Fig. 1 includes two or more nested condensate pans tube banks 12, the condensation with preferred evaporative condenser 10 in Fig. 2
System refrigerant selected by (for condensing) with flowing in coil pipe bundle.The condensate pans tube bank 12 is with rectangular airflow air chamber 13
Form is arranged in condensate pans area under control.
Evaporative condenser 10 also includes the device of 14 form of nozzle, and the nozzle 14 is formed in isocon 15, for leading to
Cross and sprayed (for example, with shown 3kg/m with the water of vertebral body 162Speed) condensation tube bank 12 with moistening they.Or, can make
Use moisture circulation road, for example those have jagged edge or internal slot.
Nozzle 14 is arranged along the direction contrary with shown air current flow and ejects water in condensate pans tube bank 12.
Evaporative condenser 10 also includes the fan being arranged in the fan hub in upper end of condenser portion.Embodiment in Fig. 3
In, this set actual displayed is the fan 118 (referring to Fig. 3 A) in the fan hub 120 of condenser the top.In Fig. 1 and
Same or similar setting can be adopted in the embodiment of Fig. 2.In this respect, fan bypasses air through air intake 21 and is inhaled
Enter in air intake room 22, the air intake room 22 is towards the lower end of condenser 10.
In the embodiment of Fig. 1 and Fig. 2, air-flow A is with such as 8.1m3The volume flow rate of/s is entered, and passes through screen cloth first
Filter, subsequently into air intake room 22, causes air-flow to flow up by fan afterwards and restrains 12 by condensate pans.By wind
The air pressure difference that fan is obtained can maintain such as 160Pa.
In the embodiment of fig. 3, air-flow A is entered with the wet bulb temperature of the speed of such as 3m/s and such as 23 DEG C, first
According to atmospheric pollution by optional granular membrane 124 and air inlet duct 126, subsequently into inlet plenum 122, afterwards by fan
118 cause air-flow to flow up and restrain 112 by condensate pans.
Evaporative condenser 10 further includes dehydrater 30, and the dehydrater is placed in condenser adjacent to upper end of condenser
Interior.Once air-flow flows through condensate pans tube bank 12 and nozzle 14, dehydrater 30 just eliminates the free water in air-flow.
In the embodiment of Fig. 1 and Fig. 2, the evaporative condenser 10 includes rectangular airflow air chamber 13, followed by with
The splitting streams room of 40 form of frustum air chamber.Rectangular airflow air chamber 13 can be foursquare, rectangle etc. hollow section
Face (for example, bending or welding plastics or sheet metal/sheet material).Shunting air chamber 40 can also be hollow section (for example,
Bending or welding plastics or sheet metal/sheet material), but define the frustum as defined.When for example air chamber 13 has
During square-section, shunting air chamber 40 includes square or rectangle frustum.
However, in the embodiment of fig. 3, evaporative condenser 100 includes the middle square of condensate pans tube bank 112 using being located at
Air-flow accumulation regions 135 and airflow diversion area 140 on 113 either side of shape air-flow air chamber.The air chamber 113 is with constant transversal
Face area, and air-flow accumulation regions 135 and airflow diversion area 140 are interconnected.The middle air flow air chamber 113 still can be for just
Square, rectangle etc. hollow section (such as thin plate/sheet material).During air-flow accumulation regions 135 and airflow diversion area 140 still can be
(the such as thin plate/sheet material) in empty section, but each is formed as the frustum as defined.For example, when mesozone 113 has side
During tee section, aggregation air chamber and shunting air chamber each may include square or rectangle frustum.
In the embodiment of Fig. 1 and Fig. 2, fan operation causes air-flow A with respect to dehydrater at condensate pans tube bank 12
30 already at higher speed.After air-flow A flows through gel coil pipe bundle 12, splitting streams air chamber 40 is flowed into by water vertebral body 16.
Due to the cross section that splitting streams air chamber 40 is gradually increased, air-flow can be decelerated to before which travels to and through dehydrater 30 can
The speed of acceptance.Evaporative condenser 10, the speed being particularly built into splitting streams air chamber 40 is in and can remove from air-flow
Meet the level of the free water of environmental requirement, minimum.At this point, the airflow rate at dehydrater 30 can be decelerated to about
3.5m/s.
As can be seen that dehydrater 30 is arranged in against 40 exit of splitting streams air chamber, thus air-flow does not allow to carry out not
Necessary deceleration.
Therefore, the embodiment of Fig. 1 and Fig. 2 does not adopt air-flow collecting region.Conversely, from air intake room 22 and by cold
The air velocity of solidifying coil pipe bundle 12 is about 5m/s, until air-flow reaches splitting streams air chamber 40, therefore air-flow is in dehydrater 30
Place is gradually decelerated to about 3.5m/s.
However, in the embodiment of fig. 3, condensate pans tube bank 112 is placed in middle air flow area 113.Build these areas
Domain causes air-flow A to flow through, and air-flow accelerates (for example, about 5m/s) in air-flow collecting region 135 and reaches positioned at middle air flow gas
Condensate pans tube bank 112 in room 113.After condensate pans tube bank 112 is flowed through, air-flow A flows into splitting streams area 140, by water vertebra
Body 16, and reach the front reduction gear of dehydrater 130.Again, dehydrater 130 is arranged in against 140 exit of splitting streams air chamber.
Air-flow collecting region 135 is built into and air-flow A can be caused for example to accelerate in the way of being gradually increased.On the contrary, air-flow divides
Stream area 140 is built into and air-flow A can be caused for example to slow down in the way of being gradually lowered.It means that with respect to air inlet import
Room 122 is also by the air velocity of dehydrater 130, by middle air flow area 113 and fast by the air of condensate pans tube bank 112
Degree increases.For example, in shown construction, the air speed in middle air flow area 113 is about the 3.5m/s sky by dehydrater
The twice of gas speed, is～5m/s (i.e. about high 45%).
In any embodiment, and the result of the airflow rate as the increase by condensate pans tube bank 12,112,
It has surprisingly been found that can adopt that there is with respect to dehydrater 30,130 the condensate pans tube bank for reserving that area reduces.Make
Further result for the airflow rate of this increase, it has therefore been surprisingly found that need less condenser coil to can reach phase
Same condenser heat dispersion.
As a result, it is possible to more inexpensive evaporative condenser is produced, because condensate pans are restrained equivalent to this condenser only
The part of one most expensive.Or, except being used for coil pipe bundle 12,112 using known heavy wall hot dipping galvanized carbon steel condensing tube, permissible
Coil pipe bundle 12,112 is formed using more expensive and/or firmer material (such as stainless steel tube).In this case, as a result
Longer coil pipe life-span, less corrosion is obtained, and if desired, obtains the tube wall material thin for coil pipe Shu Zhonggeng
Material.In this respect, coil pipe bundle 12,112 may include stainless steel tube, and such as external diameter is 4.76-31.8mm and thickness is 0.5-1.6mm
304 or 316 rustless steels.Observation shows this kind of pipe compared with known plating mild steel condenser coil, functional.By so
The corrosion resistance that provides of stainless steel tube material and the refrigerant pressure capacity of chemical resistance and increase also allow for natural system
Cryogen such as propane and/or iso-butane Hydrocarbon, CO2, ammonia etc. be used for evaporative condenser 10,100.
The cold-producing medium that is to increase of another result of the airflow rate for increasing on condenser coil can pass through condensate pans restrain 12,
112, because larger air velocity can result in the condensation of relatively large amount of cold-producing medium.
Condenser 10 also includes that the water of 50 form of pond of the base portion (that is, adjacent) positioned at air intake room 22 is collected
Area.The excess water spray for having passed through or from condenser coil is collected in the pond 50.
In order to maximize condenser efficiency, condenser 10 also additionally includes a recirculating system, the recirculating system
For the water of collection is recycled to isocon 15 with supply nozzle 14.In this respect, recirculating system includes pump 52, for inciting somebody to action
The water of collection is pumped via pipes into isocon 15.Water is extracted out from pond 50 by pump 52 via discharge pipe 54.Then pipeline section 56 is conveyed
Extend from pump discharge to be connected with isocon 15.
The recirculating system also includes water replensiher 58 (for example, with 383kg/h), for keeping predetermined in pond 50
The water of amount is so as to effective operation of evaporative condenser.This supplementary water may include to be removed the confession of the water of (capture) by dehydrater 30
Should.
In the version of the evaporative condenser shown in the details in Fig. 2, condenser 10 can also further include that side is changed
Hot cell 60.Water in pond 50 can be pumped via pump 52 and enter into and through heat exchange unit 60, then before being recycled
Isocon 15 is recycled to by delivery pipe section 56.This unit can also be assembled in the embodiment of Fig. 3.
In the version, in condenser tube condense cold-producing medium can also transmit via conveying pipe of refrigerant 62 and
By heat exchange unit 60, to carry out heat exchange with recirculation water in pond 50.In heat exchange unit 60, relatively cool
But the water in pond can sub-cooled condensation cold-producing medium, for example, be cooled to about 26.5 DEG C from 30 DEG C.This can carry further
The operating efficiency of high refrigeration system.Cold-producing medium (for example, the CO of heat exchange unit 60 is left with current 642) can be at one supercool
Temperature (for example, 26.5 DEG C or so).
Embodiment
The non-limiting example of the condenser and technique will be provided now, to describe the theoretical base of condenser and technique
Plinth, and more fully understand the condenser in work and technique.
Embodiment 1- process planning model
Develop subcritical CO2The Application Design model of condensation evaporation condenser, as shown in Fig. 1 to 3.More specifically,
To by evaporative condenser technology in subcritical CO2Benefit in condensation application is checked.This benefit includes：Grasp with Trans-critical cycle
Compare operation and the operation cost of the design pressure, the energy consumption for reducing and reduction of reduction.It is clear that hot gas defrosting also may be used
To become subcritical CO2The standard feature of refrigeration plant operation.
However, being pointed out initially that, under 24 DEG C of air inlet wet bulb temperature, ammonia can be in evaporative condenser, at 30 DEG C
Condensation.In designing a model for exploitation, as a result show, for subcritical CO under 30 DEG C (being less than critical point 1.1K)2Condensation
Evaporative condenser can be designed for 24 DEG C of wet bulb.
Secondly, it is noted that the average weather conditions in most of Europe area, including Spain, Italy, Greece and soil
Its temperature climate condition of ear, is suitable for evaporative condenser and condenses supercritical CO at 30 DEG C2.We also noted that, Canada,
The U.S. and the most area of China and the major part Australia area below the tropic of Capricorn also have and are suitable for super facing
Boundary CO2The weather of condensation evaporation condenser application.Supercritical CO2Thermodynamics and transport property at 30 DEG C significantly become with temperature
Change.Therefore, these changes also show to CO in particular design2The impact of temperature curve, heat transfer and the pressure loss.
For example, the investigation to average weather conditions shows, most of Europe area, including Spain, Italy, Greece and
Turkey, in many places, under 30 DEG C or lower of condensation temperature, has in 100% time and evaporates under critical condition
Condenser can be used to condense CO2Weather.For example, unique 5% design position of the wet bulb temperature incidence rate more than 24 DEG C in Europe
For osmanli Ya Dana (wherein, 1 and 2.5% wet bulb incidence rate design level be 26 DEG C).In the Salonika of Greece,
1% wet bulb design incidence rate is at 25 DEG C, but 2.5% and 5% wet bulb design incidence rate is at 24 DEG C.Following highest
1% wet bulb design incidence rate level is for occurring in Gibraltar, Barcelona, Valencia, Milan, Istanbul and Yi Zi
24 DEG C of Mill.
Finally, it was concluded that, in temperate zone and many subtropical climates, using CO2Evaporative condenser can make
Obtain CO2Cold-producing medium generally existing as chemical refrigerant, and when need used in indirect application when, can successfully with
Ammonia competition (the warm refrigeration of the confession of such as office building and hospital).
Worked as CO before about 20 years2When refrigeration is recovered, air cooling gas cooling is almost commonly used (by water to be sprayed onto
Heat-insulated auxiliary on the gas-cooled air intlet surface of finned coil).It should be noted that this causes actually all CO2System
Cooling system is needed with Trans-critical cycle mode operation, because air chilling temperature is near or above 31.1 DEG C of CO2Critical temperature.
Generally, the summer from air cooling gas cooler designs CO2Discharge temperature is higher than critical temperature, and this causes
Compressor needs to run under the pressure of 90bar or higher, to guarantee rational COP.Trans-critical cycle CO2The summer design of compressor
COP is usually less than the COP of air cooling HFC or evaporation cooling ammonia system.
Therefore, it is suggested that the temperature of condenser cooling medium is reduced to the completely subcritical CO of permission2The level of kind of refrigeration cycle.
This is realized by evaporative condenser, wherein in the case of air cooling condenser or gas cooler, surrounding air wet bulb
Temperature (WB) is effective coolant temperature, rather than surrounding air dry bulb (DB) temperature.
Produced problem includes to supply water, with the needs of water and water process, and according to current by some compressors supplier
Regulation control that minimum condensation temperature is carried out.Another problem is the control strategy to accidental Trans-critical cycle condition.For solution
These problems of determining propose suggestion.
CO
2
The evaluation model of evaporative condenser
Evaluate embodiment
Fig. 4 shows the schematic flow diagram of the evaporative condenser that will be described with now.In the flow chart of figure 4, water
Recirculation in tube bank so that spraying coolant-temperature gage is identical with tank water temperature.
The parameter of regulation is：(a) air velocity and wet bulb and dry-bulb temperature；(b) spraying rate of flow of water；(c) beam tube size, and
(d) CO that leaves away comprising saturated liquid under 30 DEG C and 7.2MPa2.
Quality and the energy balance in vapotron
Qureshi (2006) and Heyns (2009) disclose the Nonlinear differential eguations of five simultaneous, describe evaporation
Air-Water in cooler-process liquids interact.
By using quadravalence Runge-Kutta programming used in the VBA of the Excel electrical form of Microsoft
These equations of program solution, the electrical form have be divided into 40 interval transmission length.This method for solving is examination
The property tested and error, because the pond water temperature at air intake is conjecture and adjusts with being iterated, until itself and air
The calculating water temperature in exit is identical.
Solution is along pipeline from CO2Exporting to import " backward " is carried out, with the saturated liquid at 30 DEG C at air intake
Cold-producing medium starts, and proceeds, and as be heated, is terminated with superheated steam under the discharge temperature for calculating.The program permits
Perhaps biphase condensation and single-phase steam desuperheating.
Checking model
Do not have to verify five equation analytic solutions of numerical solution.However, it was noted that two discoveries：When leaving away and enter
When the water temperature that enters is equal；(a)CO2Enthalpy changes equal to humid air enthalpy change, and (b) thermic load that ammonia condensing is calculated at 30 DEG C makes
With the Merkel model (Merkel, 1926) for simplifying, the load for being calculated based on constant condensation temperature 9% within.
Model prediction
Fig. 5 and Fig. 6 show CO2With coolant-temperature gage curve chart.CO2The shape of temperature curve (Fig. 5) is beat all
It is more flat than expection.In about more than 37% exchanger surfaces, CO2Vapor (steam) temperature is only reduced to 30 in space-number 29 from 32
℃.This is the result (Fig. 6) of the very high thermal capacity just above 30 DEG C (Fig. 6).
The exchanger surfaces of the model prediction 67% will need dominant cooling.The CO of critical point is close to when 30 DEG C2Enthalpy data
The heat extraction of display 68% is dominant cooling, unlike ammonia only has 10%.
Compared with the curve relatively small with sensible heat cooling, water temperature curve is offset to the left, reflects the CO in Near The Critical Point2
The larger proportion of dominant cooling.
Moisture evaporation
Fig. 7 shows the current downward along tube bank.Another is not it was unexpectedly determined that water is evaporated to the sky of tube bundle top
In gas.Here, although rising, water temperature is low, and water is to contact higher than the humidity ratio in air-water interface humidity ratio
, therefore there are some condensations in air, current increase.
The impact of performance change
Fig. 8 illustrates thermal capacity, density, viscosity and thermal conductivity variation with temperature on each solution interval
Number and the impact of the pressure loss.Where 0th interval is the entrance of hot discharge gas.With CO2Temperature is close to 32 DEG C, total heat transfer
Coefficient has sizable rising, when gas phase transition for biphase when, per meter of the pressure loss is accordingly reduced.
In a model, 0.845 is used for the lewis number in equation (3).When lewis number is 1.00, identical thermic load
Required surface area only reduces by 1.4%.
Comment
The situation of simulation is extreme, CO at 30 DEG C2Condensation closely its critical point.It is noted that relatively low
Condensation temperature under, the ratio of sensible heat cooling will reduce, and performance variation with temperature will substantially reduce.Referring to Fig. 9.
It is further noted that the CO that the heat exhaust ratio of Merkel simplified model prediction is condensed at 30 DEG C2Differential pattern is low
About 22%, it is contemplated that the notable ratio of sensible heat cooling, this is not unexpected.
CO
2
The subcritical energy characteristics of compressor
Impact of the condensation temperature to cycle performance
In Fig. 10, five commercially available, semiclosed Trans-critical cycle CO are generated2The COP curve of compressor, which has
The swept volume of 27.2m3/h under 50Hz and 30kW four-pole motor.
With reference to curve 1, the COP in Figure 10 under+10 DEG C of saturated suction temperature (SST), from+30 DEG C of saturation condensation temperatures
(SCT) under 6.27 to+16 DEG C of saturation condensation temperatures 18.0 under.+ 10 DEG C of SST will allow+11 DEG C of evaporating temperature (ET),
The suction pressure drop having corresponding to the suppression of 1K boiling point.11 DEG C is considered as to cool down the rationally effective of air-conditioning (AC) air for direct
Evaporating temperature, it is allowed to relatively large diffusion in the air themperature on cooling coil, so as to suppress need circulation air
Volume, and thus reduce fan energy and resulting parasitism thermic load.This causes to be input to compressor in turn
In required energy reduce, so as to improve the total energy efficiency of whole system.
Curve 2 shows under+5 DEG C of SST, and under 30 DEG C to 16 DEG C SCT, COP is from 4.45 to 11.67.This will allow empty
The chilled water of tune is used for transforming existing structure and is applied to new building.
In above-mentioned two situations, compressor of air conditioner is also used as the compression in parallel of the cooling load under -5 DEG C of SST
Machine, for example, keep stored frozen temperature about at 0 DEG C, and the two benches CO for being applied to cold preservation and bleed type freezing2System
High-stage load.
In this case, high pressure compressor is by with+5 DEG C and+10 DEG C of virtual CO2Gas cooler exit temperature is transported
OK, this causes COP curve 3 and 4 respectively.The virtual gas cooler outlet of the SCT in the range of from+30 to+16 DEG C and+5 DEG C
At a temperature of, COP curve 3 is changing under -5 DEG C of SST from the range of 4.7 to 7.88.COP curve 4 is shown at+10 DEG C
The outlet of virtual gas cooler, under -5 DEG C of SST, and the SCT in the range of from+30 to+16 DEG C, COP scope from 4.45 to
7.04.It is noted that this can pass through to improve compressor suction pressure in suction heat exchanger (SHEX), so that performance is more
It is close to curve 3.
Impact of the ambient wet bulb temperature to condenser performance
Fig. 4 shows CO2, air and water general details.Impact of the ambient wet bulb temperature to condenser performance is shown in down
In result listed by table：
NB. refrigeration tube bank：84 loops, 8 paths, 146.2m2
Ammonia, R22, R507A, the relative energy efficiency of propane and R134a
These cold-producing mediums COP under identical operating conditions shows in fig. 11.As a result, it was confirmed that ammonia is wherein best system
Cryogen.The unexpectedly low COP of R134a.Under 16 and 35 DEG C of SCT, the COP of R134a is respectively than low 42 He of ammonia
31%.Additionally, the COP of the R134a compressor under+16 DEG C of SCT is 3.84, under identical suction condition and under+35 DEG C of SCT
Ammonia compressor COP roughly the same.Which demonstrate R134a and there is high global warming potential directly or indirectly
(Global Warming Potential, GWP).Under 25 to 35 DEG C of SCT, the performance lower than R22 efficiency 11 of R507A to
16%.HFC R507A does not have ozone depletion potential as HCFC R22, but the 100 of R507A years GWP are 3,895, are R22
100 years GWP value 1810 twice.
Overall heat-transfer coefficient, Uo
Fig. 8, Uo are referred again to apparently higher than the common Uo in the case of ammonia condensing, wherein in the apparent sky of 2.6 to 3.05m/s
Under gas speed, Uo scope is about 450 to 550w/m2.K.The apparent air velocity of 3m/s is selected in a model as maximum, with
Guarantee that dehydrater can capture the most of free water being suspended in ascending air.
CO in Fig. 42Evaporative condenser average Uo value in fig. 8 is for about 1050w/m2.K.This is considered as to enter condensation
Under the almost identical apparent air velocity of tube bank, more than the twice of the meansigma methodss of ammonia.It is readily apparent that at considering 30 DEG C
The heat to be removed of condensation 68% is significantly overheated, and only 32% is actually the condensation latent heat at 30 DEG C shown in Fig. 9.High
Total heat transfer factor owing to the high CO in 76 55 meters long of equivalent length loop2Mass flux is 338.7kg/m2.s, this makes
The calculating pressure drop of 15kPa is become.This is acceptable maximum, to promote the CO being operated in parallel2Condenser, without too big
Down-comer, to avoid when a condenser does not work, liquid holdup in the condenser of operation.
As vaporizer, CO2High Δ P/ Δ T ratio allow condenser circuit in high-quality flux, to provide height
Heat transfer rate, it is allowed to less longer loop, this also cause restrain manufacture more economical.
It is to be noted that the ammonia mass flux in evaporative condenser is in about 25 to 40kg/m2In the range of, and often
Less than 25.The pressure drop is the problem of ammonia condenser, because the excessive pressure drops in ammonia evaporative condenser improve discharge pressure, so as to
Saturation condensation temperature (SCT) is improve, causes energy consumption to increase.
Minimum air flow affects
Fig. 4 is referred again to, the air dry-bulb temperature of leaving away of calculating is 29.3 DEG C under 100%RH, therefore leaves wet bulb temperature
Degree is also 29.3 DEG C.This only 0.7 ° K lower than 30 DEG C of SCT.This is possible to, because head tube temperature is 77 DEG C, and
A high proportion of dominant overheated ensure that high 47.7 ° K leaves away approach.Should be noted, in ammonia evaporative condenser this be not
Possible, wherein under design condition, ammonia evaporative condenser leave away temperature very positioned at ammonia SCT and the minimum that leaves away between wet bulb
Less less than 3K and not less than 2.5K.Little airflow also results in minimum fan energy.
Conclusion
Meeting full-scale prototype CO2On the premise of the performance test of evaporative condenser, it was therefore concluded that, wet in design maximum
Ball (WB) temperature is that used in 24 to 25 DEG C of relatively high latitude subtropical zones, evaporative condenser shows huge prospect.In environment WB
Lower more gentle of temperature and feel nice and cool to the area of cold climate, CO2Evaporative condenser shows huger prospect.
According to above-mentioned conclusion, almost all of European Region (including mediterranean country), except with Gulf of Mexico and big
Southern US continent and many Midwest states such as Minnesota State as far as the north that the West connects, are suitable for evaporative condenser
Device is applied to subcritical CO2Compression exhaust.
Experiment is it is also shown that ambient wet bulb temperature is 28 to 29 DEG C of boil-off gas cooling and surrounding air WB to CO2Go out
It is feasible that mouth temperature is close to 3K.This attribution on the fact that, under Trans-critical cycle pattern, without condensation phase (Fig. 9)
Only have dominant heat transfer under larger LMTD, and of a relatively high Trans-critical cycle fluid density is accompanied by high heat capacity, similar to Fig. 6.
Evaporation cooling is to subcritical CO2Condensation and Trans-critical cycle CO2Gas-cooled application causes the efficient system under high COP
Cold, which operates realized COP suitable and higher under many circumstances with conventional refrigerant under less than critical temperature.This is
Whole world application CO2Refrigeration opens road.Respectively with chilled water, DX or pumping CO2In the application of air-conditioning, by CO2For+5 and
Especially true in the application of+10 DEG C of compressor saturation inlet temperature.
It is further noted that compressor of air conditioner is also used as any residue cooling load in the facilities such as supermarket
Parallel connection compressor, wherein as shown in Figure 10, height need to very high COP under cool down and freezing load.
In fact, when Figure 10 and 11 is compared, it is clear that in subcritical condensation phase, CO2Performance better than routinizing length of schooling
Cryogen, such as R22, R507A and R134a, are also found just like Pearson (2010).Additionally, in most of operating conditions
Under, particularly in the case of parallel compression is related to, CO2Can compete with ammonia and propane or win.
At a temperature of high wet bulb, such as 28 DEG C, conventional evaporative condenser is possible to operate under 40 DEG C of SCT, as Fig. 9 institute
Show, for NH3, R22, R507A, propane and R134a generate respectively 3.37,3.34,2.71,2.96 and 2.38 COP value.Cause
This, in order to develop efficient CO2Cold-producing medium, needs bigger compressor, for example, the modified version of CNG dyestuff compressor.
Term
In embodiment：
A exterior surface area m2
maAir rate kg dry air s-1
mwRate of flow of water kg s-1
mrCO2Flow rate kg s-1
imaswThe saturated air enthalpy J kg of air-water interface-1Dry air
haAir enthalpy J kg-1Dry air
hdMass tranfer coefficient kg
ivVapor enthalpy J kg-1
TwWater temperature DEG C
Le lewis number-
TrCO2Temperature DEG C
CpwThe thermal capacitance J kg of aqueous water-1K-1
CpaThe thermal capacitance J kg of humid air-1K-1
UoOverall heat-transfer coefficient W m-2K-1
W air humidity is than kg water kg-1Dry air
WintThe air humidity of air-water interface is than kg water kg-1Dry air
hwWater pipe heat transfer coefficient W m-2K-1
hiCO2Heat transfer coefficient W m-2K-1
diBore m
doPipe external diameter m
Ff sealing factor K m2W-1
Model parameter
1. using NIST (2011) data, saturation and overheated CO to be used for2Macroscopic property and transport property；
2. the h in equation (6)wBy Mizushima and Miyasita (1967), Qureshi and Zubair (2006)
Equation (A.8) is calculated；
3. the h in equation (3)dBy Mizushima and Miyasita (1967), Qureshi and Zubair (2006) etc.
Formula (A.13) is calculated；
4. for biphase CO2Stream, the h in equation (6)iBy Shah ' s (2009), Qureshi and Zubair (2006) equation
(A.6) calculate with (A.7)；Pressure loss by M ü ller-Steinhagen and Heck correlation (ASHRAE,
2005) calculate；
5. for single-phase CO2Steam stream, the h in equation (6)iBy Dittus-Boelter dependency Nu=
0.023Re0.8Pr0.3Calculate；Pressure loss is by friction factor=0.079Re-0.25Calculate；
6. the air-pressure drop in tube bank is calculated by Mills (1999), 4.5.1 section, page 316.
It is used for formulating model below with reference to document：
1.ASHRAE, 2005,2005Fundamentals, 4.12-13 page
2.Heyns J,D, 2009, ventilation type steam condenser merges the performance spy of mixing (dry/wet) rectifier
Point (Performance characteristics of an air-cooled steam condenser incorporating
A hybrid (dry/wet) dephlegmator), appendix A, PIER Report, CEC-500-2013-065-APA
3.Merkel, F., 1926, Verdunstungskuling, VDI Zeitschrift, rolls up page 70,123 128
4.Mills A.F., 1999, basis is conducted heat and mass transfer (Basic Heat＆Mass Transfer), second edition,
A.F.,Prentice Hall.
5.Mizushima, T., R.Ito and H.Miyasita, 1967, the experimentation of vapotron
(Experimental study of an evaporative cooler),International Chemical
Engineering, rolls up page 7,727 732
6.NIST 2011,http://webbook.nist.gov/chemistry/fluid/Thermophysical
Properties of Fluid Systems
7.Qureshi B, Zubair S, 2006, the comprehensive Design of vapotron and condenser studies (A with grading
comprehensive design and rating study of evaporative coolers and
condensers.Part I Performance evaluation),Int.J.Refrigeration,29:645-658.
8.Shah M, 2009, in plain tube, condensation process is used for the improvement of heat transfer and the general correction (An of extension
improved and extended general correlation for heat transfer during
condensation in plain tubes),HVAC&R Research,15(5)
9.Pearson, S.Forbes, 2010, are used for air-conditioning and general refrigeration (Use of carbon using carbon dioxide
dioxide for air conditioning and general refrigeration),IIR-IOR 1st Cold
Chain Conference,Cambridge,UK.
Embodiment 2 designs a model output
Data below point is produced by modelling, so that the change with superficial air velocity with condenser capacity to be described：
Although it have been described that the embodiment and model of multiple condensers and technique, but it is to be understood that, condenser
Can be realized with many other forms with technique.
For example, pumping chamber 13 can be with circular cross-section, and thus shunting pumping chamber 40 includes conical frustum or square
The prism of subcircular vertebral body shape.However, this construction is less popular, because which can not promote freely arranging for water in condenser
Go out.
In description in following claims and above, unless context is due to representation language or necessary implicit,
The otherwise implication use of word " including " and its variant such as "comprising" or " including " to include, i.e. to specify the feature
Presence, but be not excluded for existing in the various embodiments of condenser as described herein and technique or add other features.
Claims (19)
1. a kind of for refrigeration or the evaporative condenser of air conditioning system, the condenser includes：
- it is arranged on one or more condenser coils in condensate pans area under control, the cold-producing medium having in the coil pipe in condenser system；
- for the one or more of condenser coils of moistening device；
The dehydrater of-setting is to remove the free water in the air-flow for flowing through one or more condenser coils and damping device；
- shunting zone from condenser coil to dehydrater that shunt from, once air-flow flows through one or more condenser coils, which flows into and leads to
Cross shunting zone and enter dehydrater.
2. condenser as claimed in claim 1, it is characterised in that one or more condenser coils are arranged in condensate pans area under control
Tube bank.
3. condenser as claimed in claim 2, it is characterised in that the condensate pans area under control include one section total with cross-sectional area
The constant condenser of body.
4. the condenser as described in aforementioned any claim, it is characterised in that the shunting zone is configured to cause and removes in arrival
Before hydrophone, flow slowing down therein is flowed into.
5. the condenser as described in aforementioned any claim, it is characterised in that the shunting zone includes so that air stream flows through
Hollow frustum therein.
6. the condenser as described in aforementioned any claim, it is characterised in that the dehydrater can be located at shunting zone adjacent to each other
Air leave side.
7. the condenser as described in aforementioned any claim, it is characterised in that the condenser is further included positioned at condensation
The air intake room of the air inlet side in coil pipe area.
8. the condenser as described in aforementioned any claim, it is characterised in that for the one or more condenser coils of moistening
Part, including nozzle, the nozzle is arranged with respect to shunting zone, contrary with the air-flow for flowing through one or more condenser coils
Eject water on direction on one or more condenser coils.
9. condenser as claimed in claim 8, it is characterised in that the nozzle is arranged in shunting zone, by water substantially with liquid
Body shape is ejected on one or more condensate pans areas under control.
10. the condenser as described in aforementioned any claim, it is characterised in that further include for collect passed through cold
The collecting region of the water in solidifying coil pipe area, and for the water of collection to be recycled to the recirculating system of wetted part.
11. condensers as claimed in claim 10, it is characterised in that the recirculating system include one for by collect
Water is pumped into the pump of wetted part via pipeline, and, as required, a moisturizing part for being used for maintaining the water of scheduled volume,
Effective operation for evaporative condenser.
12. condensers as described in claim 10 or 11, it is characterised in that further include heat exchanger, wherein, collection
Water passed through the heat exchanger before wetted part is recycled to, and, the cold-producing medium stream of condensation through heat exchanger with follow again
The collection water of ring carries out heat exchange.
13. condensers as described in aforementioned any claim, it is characterised in that wherein one or more condenser coils are each wrapped
Include stainless steel tube.
14. is a kind of for refrigeration or the evaporative condenser of air conditioning system, and the condenser includes：
- it is arranged on one or more condenser coils in condensate pans area under control, the cold-producing medium having in the coil pipe in condenser system；
- for the one or more of condenser coils of moistening device；
The dehydrater of-setting is to remove the free water in the air-flow for flowing through one or more condenser coils and damping device；
- for collecting the collecting region of the water for having passed through condensate pans area under control；
- for the water of collection to be recycled to the recirculating system of wetted part；And
- heat exchanger, wherein, the water of collection passed through the heat exchanger before wetted part is recycled to, and, condensation
Collection water of the cold-producing medium stream through heat exchanger with recirculation carries out heat exchange.
15. condensers as claimed in claim 14, it is characterised in that the condenser is also in addition as claim 1-13 is arbitrary
Described.
A kind of 16. forming part refrigeration or the evaporative condenser technique of Air-conditioning Cycle, it is characterised in that the technique includes：
- cold-producing medium stream is through one or more condenser coils；
- use the one or more condenser coils of water-wet；
- condenser coil of one or more moistenings is caused air flow through, so that cold-producing medium is in disk in-tube condensation so that a part
Water evaporation is entered in air-flow；
- remove the water being present in the air-flow for leaving one or more condenser coils；
Wherein, remove before being present in the water in air-flow, cause to leave the air-flow of one or more condenser coils using the technique
Speed be minimized.
A kind of 17. forming part refrigeration or the evaporative condenser technique of Air-conditioning Cycle, the technique includes：
- cold-producing medium stream is through one or more condenser coils；
- use the one or more condenser coils of water-wet；
- water for flowing through one or more condenser coils is collected, and by water recirculation with the one or more condenser coils of moistening；
- air-flow is by the condenser coil of one or more moistenings, and wherein cold-producing medium is in disk in-tube condensation, and part water evaporation enters gas
In stream；
- remove the water being present in the air-flow for leaving one or more condenser coils；
- collect water be recycled for the one or more condenser coils of moistening before, by condensation cold-producing medium and collect water it
Between carry out heat exchange.
18. techniques as described in claim 16 or 17 is arbitrary, it is characterised in that the technique is appointed in such as front claim 1-15
Carry out in evaporative condenser described in one.
19. techniques as described in claim 16 to 18 is arbitrary, it is characterised in that condensation in one or more condenser coils
Cold-producing medium includes foregoing chemistry or natural refrigerant.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| AU2014901764A AU2014901764A0 (en) | 2014-05-13 | Improved evaporative condenser | |
| AU2014901764 | 2014-05-13 | ||
| PCT/AU2015/000277 WO2015172180A1 (en) | 2014-05-13 | 2015-05-13 | Improved evaporative condenser |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN106461297A true CN106461297A (en) | 2017-02-22 |
Family
ID=54479035
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201580025168.0A Pending CN106461297A (en) | 2014-05-13 | 2015-05-13 | Improved evaporative condenser |
Country Status (9)
| Country | Link |
|---|---|
| US (1) | US20170153048A1 (en) |
| EP (1) | EP3146279A4 (en) |
| JP (1) | JP2017519182A (en) |
| KR (1) | KR20170005047A (en) |
| CN (1) | CN106461297A (en) |
| AU (1) | AU2015258758A1 (en) |
| CA (1) | CA2947774A1 (en) |
| WO (1) | WO2015172180A1 (en) |
| ZA (1) | ZA201607964B (en) |
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| CN108644800A (en) * | 2018-05-31 | 2018-10-12 | 中国石油化工股份有限公司胜利油田分公司现河采油厂 | Condensing steam injection boiler flue gas waste heat recovering device for oil field and method |
| CN109724429A (en) * | 2018-12-21 | 2019-05-07 | 江苏格陵兰传热科技有限公司 | Heat reclamation energy-saving-type gas cooling device |
| CN111256487A (en) * | 2020-01-17 | 2020-06-09 | 浙江大学 | Steam cooling device and method for forming circulation loop |
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| WO2018148534A1 (en) * | 2017-02-09 | 2018-08-16 | Evapco, Inc. | Evaporative refrigerant condenser heat exchanger |
| AU2018373496A1 (en) | 2017-11-27 | 2020-06-18 | Glaciem Cooling Technologies Pty Ltd. | Refrigeration system |
| TWI732153B (en) * | 2018-11-15 | 2021-07-01 | 國立臺北科技大學 | Integrated water-cooled air conditioning device |
| CN112539576B (en) * | 2020-11-30 | 2021-09-14 | 浙江万享科技股份有限公司 | Circulating quick-cooling efficient condenser |
| CN113587497B (en) * | 2021-07-12 | 2023-04-07 | 浙江国祥股份有限公司 | Double-cooling composite efficient evaporative condenser |
| CN113530620A (en) * | 2021-07-16 | 2021-10-22 | 江苏奥喜埃化工有限公司 | Improved structure of chlorine cooling system of turbine |
| WO2024106286A1 (en) * | 2022-11-15 | 2024-05-23 | 一男 中野 | Film heat exchange device |
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Also Published As
| Publication number | Publication date |
|---|---|
| EP3146279A4 (en) | 2018-02-14 |
| EP3146279A1 (en) | 2017-03-29 |
| WO2015172180A1 (en) | 2015-11-19 |
| US20170153048A1 (en) | 2017-06-01 |
| KR20170005047A (en) | 2017-01-11 |
| AU2015258758A1 (en) | 2016-11-17 |
| ZA201607964B (en) | 2019-04-24 |
| JP2017519182A (en) | 2017-07-13 |
| CA2947774A1 (en) | 2015-11-19 |
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