Improved Evaporative Condenser
An evaporative condenser for use in a refrigeration or air-conditioning system includes one or more condensing coils arranged in a condensing coil zone. The coils condense therewithin a refrigerant of the system. The condenser also includes a mechanism for wetting the one or more condensing coils. The condenser further includes drift eliminators arranged to remove free water from an airstream A that has flowed past the one or more condensing coils and wetting mechanism. The condenser additionally includes a divergent zone that diverges from the condensing coil zone towards the drift eliminators such that, once the airstream has flowed past the one or more condensing coils, it flows into and through the divergent zone to the drift eliminators.
An improved evaporative condenser and evaporative condensation process are disclosed for use in refrigeration and air-conditioning systems. The condenser and process can be employed with both chemical refrigerants (e.g. hydrofluorocarbons) and natural refrigerants (e.g. hydrocarbons (such as propane & isobutane), CO2, ammonia, etc).
BACKGROUND ARTExisting evaporative condensers are used to reject heat in a variety of refrigeration and air-conditioning systems through the condensing of a refrigerant. More specifically, evaporative condensers comprise one or more wetted (e.g. sprayed) condensing coils for condensing the refrigerant by the passage thereover of an airstream, and into which a portion of the water is evaporated, thereby removing heat from the refrigerant in the condensing coils and causing the refrigerant to condense therein. Evaporative condensers also comprise drift eliminators (or, more simply, eliminators, “drift” being water that would otherwise pass to atmosphere). Drift eliminators remove free water that passes with the airstream as it flows through the condensing coils and water spray, prior to releasing that airstream to atmosphere.
In existing evaporative condensers the plan area of the condensing coils is matched to the plan area of the drift eliminators to ensure constant air flow rate and airstream velocity through the evaporative condenser.
In existing evaporative condensers, heat exchange efficiency is limited by the velocity of air that flows over the condensing coils. The velocity of air is in turn limited by the ability of the drift eliminators to remove free water from the air passing therethrough. In existing evaporative condensers, such removed water is recycled for reuse in wetting the condensing coils. However, any water that passes with the air flowing through the drift eliminators to atmosphere may contain bacteria, such as legionella, hence the requirement to remove as much free water from the airstream as possible.
For example, in many existing evaporative condensers, it is known to specify a maximum air velocity through the drift eliminators as high as 3.5 to 4 m/s to ensure sufficient water removal, however, it is surmised that, with such a high maximum air velocity, there is still a significant risk of bacteria (such as legionella) passing with non-eliminated free water through the drift eliminators. A safer maximum air velocity through the drift eliminators of 3.5 m/s is proposed. However, this will in turn set a limit to the velocity of air that can flow over the condensing coils.
The above references to the background art do not necessarily constitute an admission that the art forms part of the common general knowledge of a person of ordinary skill in the art. The above references are also not intended to limit the application of the condenser and process as disclosed herein.
SUMMARY OF THE DISCLOSUREDisclosed herein is an evaporative condenser for use in a refrigeration or air-conditioning system. The evaporative condenser as disclosed herein can condense chemical refrigerants (e.g. hydrofluorocarbons, hydrochlorofluorocarbons, perfluorocarbons, hydrofluoroolefins, etc) and natural refrigerants (e.g. hydrocarbons such as propane & isobutane, CO2, ammonia, etc).
The evaporative condenser as disclosed herein comprises one or more condensing coils for condensing therewithin the refrigerant of the system. The one or more condensing coils can be arranged in a condensing coil zone of the evaporative condenser. The condensing coil zone may comprise an air plenum having a constant cross-sectional area.
The evaporative condenser as disclosed herein also comprises a mechanism for wetting the one or more condensing coils (e.g. by spraying them with water).
The evaporative condenser as disclosed herein further comprises drift eliminators arranged to remove free water from an airstream that has flowed past the one or more condensing coils and wetting mechanism.
In accordance with the present disclosure, the evaporative condenser as disclosed herein comprises a divergent zone that diverges from the condensing coil zone towards the drift eliminators. The configuration of the divergent zone is such that, once the airstream has flowed past the one or more condensing coils, it flows into and through the divergent zone to the drift eliminators. For example, the divergent zone may comprise an air plenum having a progressively increasing cross-sectional area.
The divergent zone is able to cause the airstream leaving the condensing coil zone to decelerate. This means that the velocity of air passing over the condensing coils can be increased, relative to the velocity of air passing through the drift eliminators. This higher velocity can help to reduce fouling of the tube.
Further, it has been surprisingly discovered that a condensing coil bundle with a reduced plan area, relative to the drift eliminators can be employed. A further consequence of this is that less condensing coil is required for the same condenser performance. This means that a lower cost evaporative condenser can be produced, as the condensing coil bundle represents the single-most expensive component of such a condenser.
In addition, an increased flow of refrigerant can be passed through the condensing coil bundle, because the greater air velocity is able to bring about condensation of a relatively greater amount of refrigerant.
Furthermore, this means that, as an alternative to using known hot-dipped galvanized carbon steel condensing tube, a more expensive and/or stronger material (e.g. stainless steel) can be used to form the one or more condensing coils, with the result that longer life, less corrosion and, optionally, thinner wall material for the coil (tube) can be employed. Notwithstanding, and if preferred, DN 8, 10, 15, and 20 (Schedule 40) seamless, hot-dipped seamless galvanized carbon steel tube can still be used to form the one or more condensing coils.
In one embodiment, each of the one or more condensing coils may employ stainless steel tube (e.g. 304 or 316 stainless steel of 4.76-31.8 mm outside diameter and 0.5-1.6 mm thickness). The use of 304 stainless steel can offer better conductivity, whereas 316 stainless steel can offer better corrosion resistance. Such tube material can perform favourably in comparison to a known condensing coil tube of galvanized mild carbon steel. The use of very small diameter tube can be suitable for certain small-scale applications.
The use of stainless steel tube material (i.e. due to corrosion/chemical resistance, increased refrigerant pressure capacity, etc) can also allow a natural refrigerant, such as a propane and/or isobutane hydrocarbon, CO2, ammonia, etc, to be employed.
In one embodiment the one or more condensing coils can be arranged as a bundle (e.g. of two or more nested coils) in the condensing coil zone. For example, the condensing coil zone may comprise a section of the condenser of generally constant cross-sectional area (e.g. an air plenum of circular, square, rectangular, etc hollow section).
In one embodiment the divergent part of the zone can be configured to cause the airstream to decelerate in a gradually decreasing manner.
In one embodiment the divergent zone can comprise a hollow frustum (hollow air plenum) through which the airstream flows. Such a hollow frustum may be located on the air exit side of the condensing coil plenum. For example, when the condensing coil plenum is of circular section, the divergent frustum each comprise a conical frustum, or a square-to-circular frustum-like prism; when the condensing coil plenum is of square section, the divergent frustum may comprise a square frustum; etc.
In one embodiment, the drift eliminators may be immediately located at an air leaving side of the divergent zone.
In one embodiment, the condenser may comprise an air inlet chamber located at an air entry side of the condensing coil zone.
In one embodiment, the mechanism for wetting the one or more condensing coils may comprise one or more spray nozzles. The spray nozzles may be arranged with respect to the divergent zone to spray water onto the one or more condensing coils in a direction that is counter to the airstream flow through the one or more condensing coils. For example, the spray nozzles may be arranged in the divergent zone, and may spray the water generally as a liquid cone into the condensing coil zone.
Alternatively, the mechanism for wetting the one or more condensing coils may comprise water distribution channels, such as those with serrated edges, internal slots, etc.
The condenser can comprise a water collection zone (e.g. located at a base of an air inlet chamber). The collection zone can collect water that has passed through condensing coil zone.
The condenser can further comprise a recycling system for recycling the collected water to the wetting mechanism, to maximize condenser efficiency. In one embodiment the recycling system can comprise a pump for pumping the collected water via pipework to the wetting mechanism. For example, an offtake pipe can extend from the base of the air inlet chamber to the pump, and a delivery pipe can extend from the pump outlet to the wetting mechanism (e.g. to spray nozzle, distribution pipework, etc).
In one embodiment, the recycling system can further comprise, as necessary, a water make-up mechanism for maintaining a predetermined amount of water (e.g. in the water collection zone) for effective operation of the evaporative condenser. Such make-up water can include that eliminated (captured) by the drift eliminators.
In one embodiment, the evaporative condenser can further comprise a heat exchanger (e.g. a separate, laterally located discrete heat exchange unit). The collected water can be passed through the heat exchanger prior to recycling it to the wetting mechanism. In addition, the condensed refrigerant can be passed through the heat exchanger to exchange heat with the recycled collected water. Such a heat exchanger can be used to sub-cool the condensed refrigerant to further improve the operational efficiency of the evaporative condenser.
Also disclosed herein is an evaporative condenser that comprises the collection zone for collecting water that has passed through condensing coil zone, and that comprises the heat exchanger through which the collected water is passed prior to recycling it to the wetting mechanism, and through which the condensed refrigerant is passed to exchange heat with the recycled collected water.
Also disclosed herein is an evaporative condensation process forming part of a refrigeration or air-conditioning cycle.
The process comprises passing refrigerant through one or more condensing coils. The process also comprises wetting the one or more condensing coils with water.
The process further comprises passing an airstream over the one or more wetted condensing coils whereby refrigerant is caused to condense within the coils, and whereby a portion of the water is caused to evaporate into the airstream. The process additionally comprises eliminating water that is present in the airstream leaving the one or more condensing coils.
In accordance with the present disclosure, the process is conducted such that the velocity of the airstream leaving the one or more condensing coils is caused to decelerate prior to eliminating the water that is present in the airstream.
As outlined above, this can lead to a reduced plan area (and hence a lesser amount) of the one or more condensing coils relative to the drift eliminators (with the attendant advantages as outlined above).
Also disclosed herein is an evaporative condensation process in which the water that passes through the one or more condensing coils is collected and recycled to wet the one or more condensing coils with water. Further, in such a process, heat can be exchanged between the condensed refrigerant and the collected water, prior to recycling it to wet the one or more condensing coils.
The process as disclosed herein can take place in an evaporative condenser as set forth above.
In the process as disclosed herein, the refrigerant condensed in the one or more condensing coils can comprise a natural refrigerant (e.g. a hydrocarbon such as propane and/or isobutane, CO2, ammonia, etc) or a chemical refrigerant (e.g. a hydrofluorocarbon, a hydrochlorofluorocarbon, a perfluorocarbon, a hydrofluoroolefin, etc).
Notwithstanding any other forms which may fall within the scope of the condenser and process as set forth in the Summary, specific embodiments will now be described, by way of example only, with reference to the accompanying drawings in which:
Specific forms of an evaporative condenser, and an evaporative condensation process that form part of a refrigeration or air-conditioning system/cycle, will now be described.
Evaporative condenser embodiments designated 10 and 100 are respectively shown in
In
The preferred evaporative condenser 10 of
The evaporative condenser 10 also comprises a mechanism in the form of spray nozzles 14 formed in a distributor tube 15 for wetting the condensing coil bundles 12 by spraying them with cones 16 of water (e.g. at a rate of 3 kg/m2 as shown). Alternatively, water distribution channels, such as those having serrated edges or internal slots, can be employed.
The spray nozzles 14 are arranged to spray water onto the condensing coil bundles 12 in a direction that is counter to the airstream flow therethrough as shown.
The evaporative condenser 10 also comprises a fan arranged in a fan housing at an upper end of the condenser. Such an arrangement is actually shown in the embodiment of
In the embodiment of
In the embodiment of
The evaporative condenser 10 further comprises drift eliminators 30 which are arranged within the condenser adjacent to an upper end thereof. The drift eliminators 30 remove free water from the airstream once it has flowed past the condensing coil bundles 12 and spray nozzles 14.
In the embodiment of
However, in the embodiment of
In the embodiment of
It will be seen that the drift eliminators 30 are arranged immediately at the air exit of the divergent airflow plenum 40, whereby the airflow is not permitted to decelerate more than is necessary.
Thus, the embodiment of
However, in the embodiment of
The convergent airflow zone 135 is configured to cause the airstream A to accelerate, such as in a gradually increasing manner. Conversely, the divergent airflow zone 140 is configured to cause the airstream to decelerate, such as in a gradually decreasing manner. This means that the velocity of air passing through the intermediate airflow zone 113 and over the condensing coil bundles 112 is increased, relative to the velocity of air that passes into the air inlet chamber 122 as well as through the drift eliminators 130. For example, in the configuration depicted, the airflow rate in the intermediate airflow zone 113 is approximately double at ˜5 m/s, (i.e. about 45% higher than) the 3.5 m/s air velocity through the drift eliminators.
In either embodiment, and as a result of this increased airflow rate passing over the condensing coil bundles 12, 112, it has surprisingly been discovered that a condensing coil bundle with a reduced plan area, relative to the drift eliminators 30, 130 can be employed. As a further consequence of this increased airflow rate, it has surprisingly been discovered that less condensing coil is required for the same condenser heat rejection performance.
The result is that a lower cost evaporative condenser can be produced, as the condensing coil bundle represents the single-most expensive component of the condenser. Alternatively, instead of using known thick-wall, hot-dipped galvanized carbon steel condensing tube for the coil bundle 12, 112 a more expensive and/or stronger material, such as stainless steel tube, can be used to form the coil bundle 12, 112. In such case, the result is longer coil life, less corrosion and, if desired, thinner wall material for the tube in the coil bundle. In this regard, the coil bundle 12, 112 can comprise stainless steel tube, such as 304 or 316 stainless steel of 4.76-31.8 mm outside diameter and 0.5-1.6 mm thickness. Such tube is observed to perform well in comparison to known condensing coil tube of galvanized mild carbon steel. The corrosion and chemical resistance, as well as increased refrigerant pressure capacity, that is provided by such stainless steel tube materials also allows a natural refrigerant, such as a propane and/or isobutane hydrocarbon, CO2, ammonia, etc, to be employed in the evaporative condenser 10, 100.
Another consequence of the increased airflow rate over the condensing coils is that an increased flow of refrigerant can be passed through the condensing coil bundle 12, 112 because the greater air velocity is able to bring about condensation of a relatively greater amount of refrigerant.
The condenser 10 also comprises a water collection zone in the form of a basin 50 located at a base of (i.e. adjacent to) the air inlet chamber 22. The basin 50 collects excess spray water that has passed through or from condensing coils.
To maximize condenser efficiency, the condenser 10 additionally comprises a recycling system for recycling the collected water to the distributor tube 15 for feeding to the spray nozzles 14. In this regard, the recycling system comprises a pump 52 for pumping the collected water via pipework to the distributor tube 15. The pump 52 draws water out of the basin 50 via an offtake pipe 54. A delivery pipe section 56 then extends from the pump outlet to connect with the distributor tube 15.
The recycling system also comprises water make-up 58 (e.g. at 383 kg/h) for maintaining a predetermined amount of water in the basin 50 for effective operation of the evaporative condenser. Such make-up water can include a supply of water that has been eliminated (captured) by the drift eliminators 30.
In a variation of the evaporative condenser shown in the detail of
In this variation, the condensed refrigerant in the condenser tubes can also be passed via refrigerant delivery pipe 62 to and through the heat exchange unit 60 to exchange heat with the recycled water from the basin 50. In the heat exchange unit 60 the relatively cool basin water can sub-cool the condensed refrigerant, for example, from 30° C. to around 26.5° C. This can further improve the operational efficiency of the refrigerating system. The refrigerant (e.g. CO2) leaving the heat exchange unit 60 as the stream 64 can be at a sub-cooled temperature (e.g. around 26.5° C.).
EXAMPLESNon-limiting examples of the present condenser and process will now be provided in order to illustrate the theoretical basis of the condenser and process, and to better understand the condenser and process in operation.
Example 1—Process Design ModelA design model for the application to subcritical CO2 condensing of evaporative condensers, such as those depicted in
Firstly, however, it was noted that ammonia can be condensed at 30° C. in an evaporative condenser with an entering air wet bulb temperature of 24° C. In the developed design model it was shown that an evaporative condenser for subcritical CO2 condensing at 30° C. (i.e. 1.1 K below the critical point) was able to be designed for a wet bulb of 24° C.
Secondly, it was noted that average climate conditions in much of Europe, including the warmer climates in Spain, Italy, Greece and Turkey, were suitable for evaporative condensers to condense subcritical CO2 at 30° C. Canada, large parts of the USA and China, and most of Australia below the tropic of Capricorn were also noted to have climates suitable for the application of evaporative condensers to subcritical CO2 condensing. The thermodynamic and transport properties of subcritical CO2 at 30° C. were noted to change significantly with temperature. Thus, the effect these changes have on CO2 temperature profile, heat transfer and pressure loss for a particular design was also shown.
For example, an examination of average climate conditions revealed that much of Europe, including Spain, Italy, Greece and Turkey, has a climate where evaporative condensers may be applied for the condensing of CO2 at subcritical conditions at a condensing temperature of 30° C. or lower 100% of the time in many locations. For example, the only location in Europe where the 5% design Wet Bulb temperature incidence exceeded 24° C. was Adana in Turkey (where the 1 and 2.5% wet bulb incidence design levels are at 26° C.). At Thessaloniki in Greece the 1% wet bulb design incidence is at 25° C., but the 2.5% and 5% wet bulb design incidence levels are at 24° C. The next highest 1% wet bulb design incidence level of 24° C. occurred at Gibraltar, Barcelona, Valencia, Milan, Istanbul and Izmir.
Finally, it was concluded that the use of evaporative condensers for CO2 in temperate and many subtropical climates could make CO2 refrigeration as ubiquitous as any chemical refrigerant and would compete successfully with ammonia when it needed to be used in an indirect application (such as the heating and cooling of office buildings and hospitals for example).
When CO2 refrigeration was revived about 20 years ago, air cooled gas cooling (some with adiabatic assistance by spraying water onto the air inlet face of the finned coil gas cooler) was applied almost universally. It was noted that this resulted in virtually all CO2 refrigeration systems needing to run in trans-critical mode because the air cooling temperature is close to, or exceeds, the CO2 critical temperature of 31.1° C.
More often than not the summer design CO2 exit temperatures from an air cooled gas cooler were higher than the critical temperature, and this resulted in the compressors needing to operate at a pressure of 90 bar or higher to ensure a reasonable COP. The summer design COPs of trans-critical CO2 compressors were generally lower than those of air cooled HFC or evaporatively cooled ammonia systems.
It was therefore proposed to reduce the temperature of the condenser cooling medium to a level which would allow a complete subcritical CO2 refrigeration cycle. This was accomplished with an evaporative condenser, where the ambient air Wet Bulb (WB) temperature was the effective cooling medium temperature, rather than the ambient air Dry Bulb (DB) temperature in the case of an air cooled condenser or gas cooler.
Issues noted included the need for a water supply, water consumption and water treatment, and control of a minimum condensing temperature as currently mandated by some compressor suppliers. Another issue was the control strategies to handle inadvertent trans-critical conditions. Recommendations were made to address these issues.
A Rating Model for a CO2 Evaporative Condenser Rating ExampleThe specified parameters were: (a) air velocity and wet and dry bulb temperatures, (b) spray water flow rate, (c) bundle dimensions, and (d) leaving CO2 comprising saturated liquid at 30° C. and 7.2 MPa.
Mass and Energy Balances in Evaporative CoolersQureshi (2006) and Heyns (2009) published five simultaneous non-linear differential equations describing air-water-process fluid interactions in evaporative cooling.
The equations were solved by writing a program using a fourth order Runge-Kutta routine written in Microsoft's VBA behind a Microsoft Excel spreadsheet with pass length divided into forty intervals. The solution was trial and error because the basin water temperature at air entry was guessed and adjusted iteratively until it was the same as the calculated water temperature at the air exit.
The solution proceeded “backwards” along a tube pass from CO2 exit to entry, starting at the air inlet with saturated liquid refrigerant at 30° C., and proceeded up, as if heating, ending with superheated vapour at a calculated discharge temperature. The program allowed for both two-phase condensation and single phase vapour de-superheating.
Verifying the Model.There was no analytical solution to the five equations by which the numerical solution can be validated. However, two findings were noted: when the leaving and entering water temperatures were equal; (a) the CO2 enthalpy change was equal to the moist air enthalpy change, and (b) the heat duty calculated for ammonia condensing at 30° C. was within 9% of duty computed using the simplified Merkel model (Merkel, 1926) which is based on constant condensing temperature.
Model PredictionsThe model predicted that 67% of exchanger surface would be needed for sensible cooling. Enthalpy data for CO2 at 30° C., close to the critical point, showed that 68% of the rejection was sensible cooling, unlike ammonia where it is only 10%.
Water temperature profile was skewed to the left, compared to profiles where sensible cooling was relatively small, reflecting the larger proportion of sensible cooling for CO2 near the critical point.
Water EvaporationIn the model 0.845 was used for the Lewis number in equation (3). With a Lewis number of 1.00, the surface area required for the same heat duty was reduced by only 1.4%.
RemarksThe case modelled was extreme in the respect that CO2 condensing at 30° C. was very close to its critical point. It was noted that at lower condensing temperatures the proportion of sensible cooling would reduce and the variation of properties with temperature would be much reduced. Reference was made to
It was further noted that heat rejection predicted by the Merkel simplified model was about 22% lower than the differential model with CO2 condensing at 30° C., which was not unexpected given the significant proportion of sensible cooling.
CO2 Compressor Subcritical Energy Performance Effect of Condensing Temperature on Cycle PerformanceIn
Referring to curve 1 in
Curve 2 showed the COP ranging from 4.45 to 11.67 at 30° C. to 16° C. SCT at an SST of +5° C. This would allow chilled water production for AC for retrofitting into existing buildings and application to new buildings.
In both the above two cases the AC compressors could act also as parallel compressors for refrigeration duties at −5° C. SST, such as maintaining chill storage temperatures at around 0° C. and high stage duties for two stage CO2 systems applied to cold storage and blast freezing applications.
In such cases the high stage compressors would operate with virtual CO2 gas cooler exit temperatures of +5° C. and +10° C., which resulted in COP curves 3 and 4 respectively. COP curve 3 ranged from 4.7 to 7.88 at an SST of −5° C. at SCTs ranging from +30 to +16° C. and a virtual gas cooler exit of +5° C. COP curve 4 showed the COP ranging 4.45 to 7.04 with a virtual gas cooler exit of +10° C., and SST of −5° C. and the SCT ranging from +30 to +16° C. It was noted that this could be improved with a Suction Heat Exchanger (SHEX) in the compressor suction to bring the performance closer to curve 3.
Effect of Ambient Wet Bulb Temperature on Condenser Performance
The COPs for these refrigerants at identical operating conditions were shown in
Referring again to
The average Uo in
As with evaporators, the high ΔP/ΔT ratio of CO2 allowed high mass fluxes in the condenser circuits giving high rates of heat transfer, allowing fewer longer circuits, which also made for more economical manufacture of the tube bundle.
It was noted that ammonia mass fluxes in evaporative condensers range from about 25 to 40 kg/m2·s and are frequently lower than 25. The pressure drop was a concern with ammonia condensers, as excessive pressure drop in an ammonia evaporative condenser lifts the discharge pressure, and thus the Saturated Condensing Temperature (SCT), resulting in increased energy consumption.
Consequences of Minimum AirflowAgain referring to
Subject to satisfactory performance testing of a full scale prototype CO2 evaporative condenser, it was concluded that the application of the evaporative condensers in the higher latitude subtropics with maximum design Wet Bulb (WB) temperatures of 24 to 25° C. showed a great deal of promise. The CO2 evaporative showed even more promise in areas with more temperate and cool to cold climates where ambient WB temperatures are lower.
According to the above conclusion, suitable areas for the application of evaporative condensers to the condensing of subcritical CO2 compressor discharge gases was thus feasible in virtually all of Europe (including the Mediterranean countries), the USA except for the Southern States bordering the Gulf of Mexico and the Atlantic Ocean, and many of the Mid West States as far North as Minnesota.
Experimentation also showed that evaporative gas cooling with ambient Wet Bulb temperatures of 28 to 29° C. and ambient air WB to CO2 exit temperature approaches of 3 K were entirely feasible. This was ascribed to the fact that, in trans-critical mode, there was only sensible heat transfer at a larger LMTD without the condensing phase (
The application of evaporative cooling to both the condensing of CO2 at subcritical and gas cooling at trans-critical CO2 resulted in efficient refrigeration at high COPs which were comparable to, and in many cases higher than, the COPs achieved with conventional refrigerants operating below their critical points. This opened the way for the worldwide application of CO2 refrigeration. This is particularly true in applications where CO2 is used for Air Conditioning duties at +5 and +10° C. compressor Saturated Suction Temperature for chilled water, and DX or pumped CO2 AC applications respectively.
It was further noted that the AC compressors may also act as parallel compressors for any remaining refrigeration duties in a facility such as a supermarket where both chilling and freezing duties are required at high to very high COPs as shown in
Indeed, when comparing
At a high Wet Bulb temperature of e.g. 28° C. conventional evaporative condensers would be able to operate at 40° C. SCT resulting in COPs of 3.37, 3.34, 2.71, 2.96 and 2.38 for NH3, R22, R507A, propane and R134a respectively as shown in
In the Examples:
-
- 1. NIST (2011) data were used for thermodynamic and transport properties of saturated and superheated CO2;
- 2. hw in equation (6) was calculated from Mizushima and Miyasita (1967), equation (A.8) in Qureshi and Zubair (2006);
- 3. hd in equation (3) was calculated from Mizushima and Miyasita (1967), equation (A.13) in Qureshi and Zubair (2006);
- 4. For two phase CO2 flow, hi in equation (6) was calculated from Shah's (2009), Qureshi and Zubair (2006) equations (A.6) and (A.7); pressure loss was calculated from Müller-Steinhagen and Heck correlation (ASHRAE, 2005);
- 5. For single phase CO2 vapour flow, hi in equation (6) was calculated from the Dittus-Boelter correlation Nu=0.023Re0.8Pr0.3; pressure loss was calculated from a friction factor=0.079Re−0.25;
- 6. Air pressure drop across the tube bank was calculated from Mills (1999), section 4.5.1, p. 316.
- 1. ASHRAE, 2005, 2005 Fundamentals, page 4.12-13
- 2. Heyns J, Kroger D, 2009, 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, Vol. 70, pp. 123-128
- 4. Mills A. F., 1999, Basic Heat & Mass Transfer, 2nd ed., A. F., Prentice Hall.
- 5. Mizushima, T., R. Ito and H. Miyasita, 1967, Experimental study of an evaporative cooler, International Chemical Engineering, Vol. 7, pp. 727-732
- 6. NIST 2011, http://webbook.nist.gov/chemistry/fluid/ Thermophysical Properties of Fluid Systems
- 7. Qureshi B, Zubair S, 2006, A comprehensive design and rating study of evaporative coolers and condensers. Part I Performance evaluation, Int. J. Refrigeration, 29: 645-658.
- 8. Shah M, 2009, An improved and extended general correlation for heat transfer during condensation in plain tubes, HVAC&R Research, 15 (5)
- 9. Pearson, S. Forbes, 2010, Use of carbon dioxide for air conditioning and general refrigeration, IIR-IOR 1st Cold Chain Conference, Cambridge, UK.
The following data points were produced by the design model to illustrate condenser capacity variation with the superficial air velocity:
Whilst a number of condenser and process embodiments and models have been described, it should be appreciated that the condenser and process may be embodied in many other forms.
For example, the plenum 13 could be of circular section, whereby the divergent plenum 40 comprises a conical frustum, or a square to circular frustum-like prism. However, such a configuration is less favoured, as it does not promote free drainage of water within the condenser.
In the claims which follow, and in the preceding description, except where the context requires otherwise due to express language or necessary implication, the word “comprise” and variations such as “comprises” or “comprising” are used in an inclusive sense, i.e. to specify the presence of the stated features but not to preclude the presence or addition of further features in various embodiments of the condenser and process as disclosed herein.
Claims
1.-19. (canceled)
20. An evaporative condenser for use in a refrigeration or air-conditioning system, the condenser comprising:
- one or more condensing coils arranged in a condensing coil zone, the coils for condensing therewithin a refrigerant of the system;
- a mechanism for wetting the one or more condensing coils;
- drift eliminators arranged to remove free water from an airstream that has flowed past the one or more condensing coils and wetting mechanism;
- a divergent zone that diverges from the condensing coil zone towards the drift eliminators such that, once the airstream has flowed past the one or more condensing coils, it flows into and through the divergent zone to the drift eliminators.
21. The condenser according to claim 20, wherein the one or more condensing coils are arranged as a bundle in the condensing coil zone.
22. The condenser according to claim 21, wherein the condensing coil zone comprises a section of the condenser of generally constant cross-sectional area.
23. The condenser according to claim 20, wherein the divergent zone is configured to cause the airstream flowing therein to decelerate before reaching the drift eliminators.
24. The condenser according to claim 21, wherein the divergent zone comprises a hollow frustum through which the airstream flows.
25. The condenser according to claim 21, wherein the drift eliminators are immediately located at an air leaving side of the divergent zone.
26. The condenser according to claim 21, further comprising an air inlet chamber located at an air entry side of the condensing coil zone.
27. The condenser according to claim 21, wherein the mechanism for wetting the one or more condensing coils comprises spray nozzles that are arranged with respect to the divergent zone to spray water into the one or more condensing coils in a direction counter to the airstream flow through the one or more condensing coils.
28. The condenser according to claim 27, wherein the nozzles are arranged in the divergent zone so as to spray the water generally as a liquid cone onto the one or more condensing coils.
29. The condenser according to claim 20, further comprising a collection zone for collecting water that has passed through condensing coil zone, and a recycling system for recycling collected water to the wetting mechanism.
30. The condenser according to claim 29, wherein the recycling system comprises a pump for pumping the collected water via pipework to the wetting mechanism and, as necessary, a water make-up mechanism for maintaining a predetermined amount of water for effective operation of the evaporative condenser.
31. The condenser according to claim 29, further comprising a heat exchanger through which the collected water is passed prior to recycling it to the wetting mechanism, and through which the condensed refrigerant is passed to exchange heat with the recycled collected water.
32. The condenser according to claim 20, wherein each of the one or more condensing coils comprises stainless steel tube.
33. An evaporative condenser for use in a refrigeration or air-conditioning system, the condenser comprising:
- one or more condensing coils arranged in a condensing coil zone, the coils for condensing therewithin a refrigerant of the system;
- a mechanism for wetting the one or more condensing coils;
- drift eliminators arranged to remove free water from an airstream that has flowed past the one or more condensing coils and wetting mechanism;
- a collection zone for collecting water that has passed through condensing coil zone;
- a recycling system for recycling collected water to the wetting mechanism; and
- a heat exchanger through which the collected water is passed prior to recycling it to the wetting mechanism, and through which the condensed refrigerant is passed to exchange heat with the recycled collected water.
34. The condenser according to claim 33, further comprising a divergent zone that diverges from the condensing coil zone towards the drift eliminators such that, once the airstream has flowed past the one or more condensing coils, it flows into and through the divergent zone to the drift eliminators.
35. An evaporative condensation process forming part of a refrigeration or air-conditioning cycle, the process comprising:
- passing refrigerant through one or more condensing coils;
- wetting the one or more condensing coils with water;
- passing an airstream over the one or more wetted condensing coils whereby refrigerant is caused to condense within the coils, and whereby a portion of the water is caused to evaporate into the airstream;
- eliminating water that is present in the airstream leaving the one or more condensing coils;
- wherein the velocity of the airstream leaving the one or more condensing coils is caused to decelerate prior to eliminating the water that is present in the airstream.
36. An evaporative condensation process forming part of a refrigeration or air-conditioning cycle, the process comprising:
- passing refrigerant through one or more condensing coils;
- wetting the one or more condensing coils with water;
- collecting the water that passes through the one or more condensing coils and recycling it to wet the one or more condensing coils with water;
- passing an airstream over the one or more wetted condensing coils whereby refrigerant is caused to condense within the coils, and whereby a portion of the water is caused to evaporate into the airstream;
- eliminating water that is present in the airstream leaving the one or more condensing coils; and
- exchanging heat between the condensed refrigerant and the collected water prior to recycling it to wet the one or more condensing coils.
37. The process according to claim 35, wherein the process takes place in an evaporative condenser that comprises:
- one or more condensing coils arranged in a condensing coil zone, the coils for condensing therewithin a refrigerant of the system;
- a mechanism for wetting the one or more condensing coils;
- drift eliminators arranged to remove free water from an airstream that has flowed past the one or more condensing coils and wetting mechanism; and
- a divergent zone that diverges from the condensing coil zone towards the drift eliminators such that, once the airstream has flowed past the one or more condensing coils, it flows into and through the divergent zone to the drift eliminators.
38. A process as claimed in claim 36, wherein the process takes place in an evaporative condenser that comprises:
- one or more condensing coils arranged in a condensing coil zone, the coils for condensing therewithin a refrigerant of the system;
- a mechanism for wetting the one or more condensing coils;
- drift eliminators arranged to remove free water from an airstream that has flowed past the one or more condensing coils and wetting mechanism; and
- a divergent zone that diverges from the condensing coil zone towards the drift eliminators such that, once the airstream has flowed past the one or more condensing coils, it flows into and through the divergent zone to the drift eliminators.
39. The process according to claim 35, wherein the refrigerant condensed in the one or more condensing coils comprises a chemical or natural refrigerant.
Type: Application
Filed: May 13, 2015
Publication Date: Jun 1, 2017
Inventor: Klaas Visser (Kangaroo Flat, Victoria)
Application Number: 15/310,001