US20090075581A1 - Cooling and ventilation device - Google Patents
Cooling and ventilation device Download PDFInfo
- Publication number
- US20090075581A1 US20090075581A1 US12/160,316 US16031607A US2009075581A1 US 20090075581 A1 US20090075581 A1 US 20090075581A1 US 16031607 A US16031607 A US 16031607A US 2009075581 A1 US2009075581 A1 US 2009075581A1
- Authority
- US
- United States
- Prior art keywords
- waste
- channel
- inlet
- outlet
- flow
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
- F24F12/001—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air
- F24F12/006—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air using an air-to-air heat exchanger
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
- F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
- F24F5/0035—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning using evaporation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
- F24F12/001—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air
- F24F2012/007—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air using a by-pass for bypassing the heat-exchanger
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2110/00—Control inputs relating to air properties
- F24F2110/20—Humidity
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2110/00—Control inputs relating to air properties
- F24F2110/40—Pressure, e.g. wind pressure
-
- 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]
- Y02B30/54—Free-cooling systems
-
- 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]
- Y02B30/56—Heat recovery units
Definitions
- the present invention relates to cooling and ventilation devices and more particularly to devices incorporating evaporative heat exchangers. In particular it relates to such devices that can also operate to provide heat recovery in combination with ventilation.
- An evaporative cooler is a device that uses the latent heat of evaporation of a liquid to provide cooling.
- the principle of evaporative cooling has been known for many centuries. For example, a damp cloth placed over an object will keep the object cool by evaporation of liquid from the cloth. By continuously adding liquid to the cloth, the cooling effect may be maintained indefinitely without input of electrical energy. The lowest temperature that can be reached by evaporation of moisture in this way into an air stream defines the wet-bulb temperature for that air.
- An indirect evaporative cooler makes use of this principle.
- a primary or product air stream passing over a primary surface of a heat exchange element may be cooled by a secondary or working air stream passing over and absorbing moisture from a secondary wetted surface of the heat exchanger.
- a particularly convenient way of cooling the working air stream is to feedback a portion of the cooled product air.
- Such devices are often referred to as dew point coolers as they may lower the temperature of the product air to below its wet bulb temperature and close to the dew point.
- dew point coolers By optimising the surfaces with which the air streams exchange heat, highly effective heat transfer can be achieved. This has been found especially significant in the case of the heat transfer from the wetted secondary surface.
- the wetted secondary surface may be provided with some form of liquid supply e.g. in the form of a hydrophilic layer. The presence of such a layer can however result in increased thermal isolation of the secondary surface from the working air stream, thus reducing heat transfer.
- dew point cooler A particularly efficient form of dew point cooler is known from PCT publication WO03/091633, the contents of which are hereby incorporated by reference in their entirety. While not wishing to be bound by theory, it is believed that the success of this device is due at least in part to the presence of heat transfer elements on the primary and secondary surfaces. These heat transfer elements may be in the form of fins and are believed to improve transmission of heat from the primary surface to the secondary surface. The fins act both to directly conduct heat and also to break up the various boundary layers that develop in the flow. They also serve to increase the total area available for heat exchange on the relevant surfaces. Further important features of the wetted second surface are known from that document and also from co-pending UK patent application No 0324348.2, the contents of which are also incorporated by reference in their entirety. Accordingly, by careful choice of the material used as a water retaining layer, optimal evaporation may be achieved without thermal isolation of the secondary surface from the working air stream.
- Such a dew point cooler comprises a pair of heat conducting plates arranged in spaced, generally parallel relationship and spacing elements separating the plates from one another and defining primary and secondary flow channels between the plates. In this manner, heat transmission between the primary and secondary channels can take place primarily by conduction along the plates from the region associated with the primary channels to the regions associated with the secondary channels. This is in contrast to conventional arrangements where heat transfer between fluids takes place through a membrane separating the fluids.
- Air may be circulated through the cooler using a low-pressure fan which has low energy consumption and is relatively silent. This makes the dew point cooler ideal for domestic use, especially at night.
- the degree of cooling of the product air in an evaporative cooler is determined at least partially by the amount of liquid that can be evaporated into the working air stream. In a dew point cooler configuration, this will depend on the portion of the product air that is returned as the working air stream. This will be referred to in the following as the working fluid/product fluid ratio (WPR).
- WPR working fluid/product fluid ratio
- the WPR has been determined by the outlet configuration of the primary channels, where a baffle determines the amount of flow diverted into the secondary channels. This has generally ensured that about 30% of the product air is returned as working air. The remaining 70% is supplied to the room or space where cooling is required.
- An equal volume of air must therefore be evacuated as waste air from the room. In the past, this waste air has simply been allowed to escape by natural ventilation routes or it has been actively evacuated via a separate ventilation system.
- a cooling and ventilation device comprising: a product inlet, a product outlet, a waste inlet, a waste outlet, a waste channel connecting the waste inlet to the waste outlet, an evaporative heat exchanger having a primary channel connected between the product inlet and the product outlet and a secondary channel connected between an outlet from the primary channel and the waste channel, a flow control element effective to control flow from the secondary channel to the waste channel and a controller selectively controlling the flow control element to thereby control flow from the secondary channel to the waste channel.
- the product inlet may be connected to a suitable source of outside air and the product outlet supplied to a habitable space such as the interior of a building or vehicle.
- the waste inlet may receive expelled air from the habitable space, which is subsequently exhausted to the environment via the waste outlet.
- a device is achieved that can provide all of the benefits of evaporative cooling and ventilation while only requiring two air inlets and two air outlets.
- the flow control element is a valve located between the waste channel and the secondary channel.
- This form of flow control has been found to operate in an extremely simple and efficient manner without the extra expense and power consumption of an additional fan to control the secondary flow.
- alternative flow control elements may be provided, the function of this element being to control flow from the secondary channel to the waste channel.
- a fan, or other forced draft device may be used to as the flow control element.
- the device further comprises a sensor providing a flow signal indicative of the flow through the secondary channel and wherein the controller controls the flow control element on the basis of the flow signal.
- the flow sensor comprises pressure sensors responsive to the pressure drop across the secondary channel. These sensors may be calibrated in the factory and will then provide accurate values for control of the secondary flow, largely independently of the manner or position of installation of the device. Installation of the device is then considerably simplified and there may be less tendency for the WFR to vary with time since the flow characteristics of the secondary channel are generally constant.
- a heat recovery valve arrangement may be provided between the waste inlet and an inlet to the secondary channel. This allows switching of the source of fluid supplied to the secondary channel.
- the secondary flow may be provided as a portion of the primary flow from the outlet of the primary channel.
- the waste air from the habitable space may be supplied to the secondary channel for heat exchange with the incoming primary air.
- the device comprises a first fan unit between the product inlet and the primary channel of the evaporative heat exchanger for driving the flow of primary air through the primary channel.
- the device preferably also comprises a second fan unit in the waste channel adjacent to the waste outlet for driving the flow through the waste channel and/or the secondary channel.
- the device further comprises a suitable water distribution system for distributing water to surfaces of the secondary channel for evaporation.
- a drainage system for recovery of excess water from either the water distribution system or from condensation e.g. during heat recovery.
- the device may also comprise a recirculation channel for selectively connecting the waste channel to the product inlet.
- a recirculation channel for selectively connecting the waste channel to the product inlet.
- the waste air may be recirculated through the primary channels for subsequent reuse. This is particularly useful in circumstances where it may be desirable to limit the amount of waste air that is allowed to exhaust from the habitable space. This may be the case when the external temperature and humidity is high. For this reason it may also be desirable to keep the recirculated air separate from the fresh air entering from the product inlet. This may be achieved by having separate product channels for fresh air and recirculated air. The recirculated air may then be preferentially provided to the secondary channel for subsequent exhaust via the waste outlet.
- a heating element provided adjacent to the product outlet for heating a flow of product air prior to supplying it to the habitable space. In this manner, when used for ventilation or heat recovery purposes, additional warmth may be added to the product air to bring its temperature up to the desired value for comfort.
- a dryer may be provided for removing moisture from the air prior to supplying it to the habitable space.
- the dryer may be located between the product inlet and the primary channel in order to increase the effectiveness of the evaporative cooling device.
- the dryer may be provided at the product outlet. In this manner, only the air supplied to the habitable space is dried.
- the drier is provided with a direct supply of outside air from the product inlet and the device is operated in a recirculation mode. This has the advantageous effect that the amount of dried fresh air entering the system can be carefully controlled independently of the cooling circulation through the evaporative cooler.
- the controller comprises a memory containing a plurality of operational profiles and is active to control the device according to one or more of the operational profiles.
- the operational profiles may include: a cooling mode; a heat recovery mode; a ventilation mode; a heating mode; a recirculation mode; and a drying mode.
- the profiles may be manually selected or the device may also include an automatic mode in which the most appropriate profile or combination of profiles is selected in order to correctly condition the habitable space.
- the device also preferably comprises a plurality of environmental sensors for sensing temperature, pressure or humidity at the inlets and outlets of the device and for providing environmental signals to the controller. The controller may then select and or carry out a particular operational profile on the basis of the environmental signals.
- the invention also relates to a cooling and ventilation device comprising: a product inlet; a product outlet to a habitable space; a waste inlet from a habitable space; a waste outlet; a first evaporative heat exchanger having a primary channel and a secondary channel; a second evaporative heat exchanger having a primary channel and a secondary channel; the first evaporative heat exchanger having the primary channel connected between the product inlet and an inlet to the secondary channels of both the first and second evaporative heat exchangers; the second evaporative heat exchanger having the primary channel connected between the waste inlet and the product outlet; the waste outlet being connected to outlets from the secondary channels of both the first and second evaporative heat exchangers; and the cooling and ventilation device further comprising flow control elements effective to control a first circulation from the habitable space through the primary channel of the second evaporative heat exchanger and back to the habitable space and to control a second circulation from the product inlet, through the primary channel of the first evaporative heat exchange
- the cooling and ventilation device further comprises a fresh air feed providing a supply of fresh air from the second circulation to the first circulation.
- a quantity of fresh air may be allowed to enter the otherwise closed first circulation
- the cooling and ventilation device further comprises a waste feed providing a supply of waste air from the first circulation to the second circulation.
- the supply of waste air may be controlled to equal the fresh air feed such that the air flows are balanced.
- a dryer may be provided in fluid commination with the product inlet for drying a quantity of the air for supply to the habitable space.
- FIG. 1 is a schematic view of a conventional evaporative heat exchanger operating as a dew point cooler
- FIG. 2 is a schematic view of a cooling and ventilation device according to a first embodiment of the invention
- FIG. 3 is a schematic view of a cooling and ventilation device according to a second embodiment of the invention.
- FIG. 4 is a schematic view of a cooling and ventilation device according to a third embodiment of the invention.
- FIG. 1 there is shown schematically a dew point cooler 20 of the type described in WO03/091633. It comprises a primary channel 18 and a secondary channel 19 . A primary flow 21 flows through the primary channel 18 . A secondary flow 22 flows through the secondary channel 19 .
- the dew point cooler 20 further comprises a primary inlet 23 , a primary outlet 24 and a secondary outlet 25 . The inlets and outlets form part of a housing 26 .
- a first fan unit 27 drives the primary flow 21 .
- Placed in the housing is a heat-exchanging membrane 28 which separates primary channel 18 from secondary channel 19 .
- a duct 29 which can be closed and opened by means of a valve 30 , controlled by an actuator 31 .
- a selected part of primary flow 21 is branched off according to the WPR in the form of secondary flow 22 , while the remaining part continues as a product outlet flow 37 .
- the membrane 28 bears primary fins 32 and secondary fins 33 . These serve to break up the relevant boundary layers and to increase the effective surface area of membrane 28 .
- the secondary fins 33 are provided with a hydrophilic coating that can buffer a determined quantity of water. This water is supplied via a water conduit 34 and a dispensing valve 35 to distribution nozzles 36 . This ensures a continuous wetting of the coating.
- the secondary flow 22 provides evaporation of the water present on the coating, causing a cooling of fins 33 , membrane 28 and thereby fins 32 . In this manner the primary flow 21 is also cooled.
- the product outlet flow 37 thus has a smaller flow rate than primary flow 21 , but also a reduced temperature. This product outlet flow 37 is supplied for cooling a habitable space 10 .
- the secondary flow 22 entraining the water vapour is discharged to the outside.
- the evaporative cooler of FIG. 1 is an example of a suitable evaporative cooler only and that alternative evaporative coolers may be used in its place.
- an evaporative cooler may be provided which has the same features as the embodiment described in relation to FIG. 1 except that the heat-exchanging membrane 28 is replaced by a spacing element which separates the primary flow 21 and secondary flow 22 ; and the primary fins 32 and secondary fins 33 are replaced by heat-conducting plates which extend through the spacing element to form primary fins and secondary fins.
- This results in primary and secondary fins which are formed of a continuous plate of heat-conducting material.
- the heat transmission between the primary and secondary channels therefore takes place by conduction along the plates from the region associated with the primary channels to the region associated with the secondary channels.
- the spacing element may or may not be heat conducting because the primary heat conduction path across the spacing element is via the plates.
- the habitable space 10 would have doors 11 , windows 12 and passive vents 13 .
- an active waste air outlet 14 would also be provided for active ventilation of a waste outlet flow 38 from the habitable space 10 to the outside.
- This is shown in the form of a waste channel 15 having a second fan unit 16 .
- a waste inlet 17 to the waste channel 15 would be located at an upper level within the space 10 for receiving a waste inlet flow 39 . It is noted that the waste channel 15 and second fan unit 16 are not part of the dew point cooler 20 .
- a quantity of air equal to the product outlet flow 37 must be exhausted from the space 10 . This can take place either via the waste channel 14 or via doors 11 , windows 12 vents 13 or other natural openings. This quantity is determined by the WPR according to the position of the valve 30 . As a result of this configuration, any change to the pressure difference between the primary inlet 23 and the habitable space 10 would significantly affect the quantity of the secondary air flow 22 . Such changes could occur due to wind pressure differences between primary inlet and waste outlet, opening of windows or doors, changes in operation of the second fan unit or the like.
- FIG. 2 illustrates schematically a cooling and ventilation device 1 according to the present invention operable in various modes of operation. Similar features to those described in relation to FIG. 1 will be identified by like numerals.
- the device 1 comprises a housing 26 in which are located a number of components including a heat exchange element 2 .
- the heat exchange element 2 may be as used in the dew point coolers described in relation to FIG. 1 above but could also comprise different forms of heat exchange element providing similar or higher efficiency of heat transfer.
- the housing 26 has a product inlet 40 connecting to a primary inlet 23 of the heat exchange element 2 and a product outlet 42 connected to the primary outlet 24 of the heat exchange element 2 .
- the product outlet 42 is in communication with habitable space 10 .
- the heat exchange element 2 has a primary channel 18 connecting the primary inlet 23 and the primary outlet 24 . It also has a secondary channel 19 connected between a secondary inlet 44 and a secondary outlet 25 .
- the secondary inlet 44 is provided with a changeover valve 46 , which in a closed position connects it to the primary outlet 24 . In the open position of the changeover valve 46 the secondary inlet 44 is isolated from the primary outlet 24 and connected instead to the waste inlet 17 .
- the secondary outlet 25 is connected to the waste channel 15 via a flow control valve 48 .
- the water distribution system 50 comprises a water conduit 34 and a dispensing valve 35 , leading to distribution nozzles 36 .
- a drip tray 52 below the heat exchange element 2 is located a drip tray 52 .
- a drain 56 leads from the drip tray 52 via a pump 58 to the exterior of the housing 26 .
- a number of further functional components are contained within the housing 26 .
- a first fan unit 27 is provided between the product inlet 40 and the primary inlet 23 .
- a second fan unit 16 is located in the waste channel 15 adjacent to the waste outlet 14 .
- a product filter 60 is located between the product inlet 40 and the first fan unit 27 .
- a waste filter 62 is located in the waste channel 15 adjacent to the waste inlet 17 .
- a heating element 64 is located between the primary outlet 24 and the product outlet 42 .
- a product inlet temperature and humidity sensor 66 is located at the product inlet 40 .
- a product outlet temperature sensor 68 is located at the product outlet 42 .
- a waste inlet temperature sensor 70 is located at the waste inlet 17 .
- a level sensor 76 is provided for determining the level of water in the drip tray 52 . All of the sensors are operatively connected to a controller 78 .
- the controller 78 is also operatively connected to the valves 35 , 46 , 48 , 54 , beater 64 , first and second fan units 27 , 16 and pump 58 .
- the controller 78 is provided with the necessary hardware and software to operate the functional components in response to signals received from the sensors and according to predefined and user defined settings.
- the controller 78 comprises a memory (not shown) containing a plurality of operational profiles and is active to control the device 1 according to one or more of the operational profiles.
- the sensors and functional components are all located within the housing 3 . It will nevertheless be understood by the skilled person that certain of these elements could be located remotely.
- the temperature sensors 66 , 68 and 70 could be located remotely and connected to the controller 78 in any appropriate manner.
- the fan units 16 , 27 could be located at a distance from the housing although the compact embodiment as depicted is preferred. Additional sensors could be provided where appropriate to ensure the required operational control.
- the fan unit 27 is active to deliver outside air as a product inlet flow 21 to the primary channel 18 .
- Changeover valve 46 is closed, whereby a connection is provided from the primary outlet 24 to the secondary channel 19 . A part of the product inlet flow 21 is thus diverted as a secondary flow 22 into the secondary channel 19 . The remainder of the product inlet flow 21 is delivered to the habitable space 10 as product outlet flow 37 .
- Dispensing valve 35 is active to provide water (intermittently) via distribution nozzles 36 to the secondary channel 19 where it can then evaporate into the secondary flow 22 .
- Pump 58 is active to extract water from the drip tray 52 in response to signals from the level sensor 76 .
- the second fan unit 16 is also active to extract air from the habitable space 10 through waste inlet 17 .
- the waste control valve 54 is open and the waste inlet flow 39 can flow through the waste channel 15 to the waste outlet 14 .
- the waste inlet flow 39 corresponds to the product outlet flow 37 , although this need not be the case if other ducts are provided into the habitable space 10 .
- the flow control valve 48 is actively regulated by signals from the controller 78 .
- the controller 78 receives a pressure signal P 1 from the primary outlet pressure sensor 72 and a pressure signal P 2 from the secondary outlet pressure sensor 74 . It then adjusts the degree of opening of the flow control valve 48 to maintain the pressure drop P 1 -P 2 between sensors 72 , 74 at a constant value. In this manner, the secondary flow 22 can be maintained constant, since the flow rate through the secondary channel 19 is related to the pressure drop across it. Of particular importance, the secondary flow 22 is no longer dependent upon the waste inlet flow 39 .
- valve 48 may alternatively or additionally be adjusted dependent upon other factors.
- the valve 48 may be adjusted to maintain a lower pressure drop and a lower secondary flow 22 .
- the choice of level may be set manually by a user or may also be adjusted on the basis of e.g. the temperature in the habitable space 10 .
- the device 1 may operate in a ventilation mode according to the operational profile of Table 2. In this mode, fresh air is circulated to the space 10 in an amount according to the suggested levels defined in Table 2.
- the device 1 may be operated in a heat recovery mode to provide ventilation.
- Table 3 indicates the operational profile of certain functional components for this mode of operation for four different suggested levels of ventilation.
- the heat recovery valve arrangement which acts to channel the fluid of the waste channel to the secondary channel, in this manner heat exchange is carried out between the outgoing waste and the incoming product.
- the heat recovery valve arrangement comprises change over valve 46 , waste control valve 54 and flow control valve 48 .
- the changeover valve 46 is opened and the waste control valve 54 is closed.
- the flow control valve 48 is kept in the fully open position. All of the waste inlet flow 39 is now caused to pass through the secondary channel 19 of the heat exchange element 2 . Heat exchange with the product inlet flow 21 takes place causing this to be warmed as the secondary flow 22 is cooled.
- the dispensing valve 35 is inactive, the pump 58 may still operate to remove any water collecting due to condensation. Under certain circumstances it may also be desirable to add water or other humidification products to the primary channel 18 or into the product outlet flow 37 in order to increase the humidity in the habitable space 10 .
- the flow through the primary channel 18 takes place in the same direction as in the cooling mode.
- the flow through the secondary channel 19 always takes place in the direction of the waste outlet 14 such that any contamination formed in the secondary channel 19 will be directed away from the habitable space 10 .
- the device 1 may be operated in a heat recovery and beating mode to provide ventilation.
- Table 4 indicates the operational profile of certain functional components for this mode of operation for four different suggested levels of ventilation.
- This mode of operation differs from the heat recovery mode only in that the heating element 64 is active to additionally heat the product outlet flow 37 .
- the heating element 64 may be an electrical heater although hot water or other such heating elements may also be used.
- frost protection for the incoming product inlet flow to prevent humid air exiting secondary channel 19 from condensing and freezing around secondary outlet 25 . This may be achieved by a small electrical pre-heater (not shown) or similar device at the product inlet 40 .
- FIG. 3 A further embodiment of the invention is shown in FIG. 3 .
- the embodiment of FIG. 3 corresponds substantially to that disclosed in FIG. 2 and those features common to the earlier embodiment will not be further described.
- a recirculation bypass 80 has been added between the waste channel 15 and the product inlet channel between the product filter 60 and the first fan unit 27 .
- a waste channel diverter valve 82 is located at the junction between the recirculation bypass 80 and waste channel 15 .
- a product channel diverter valve 84 is provided at the junction between the recirculation bypass 80 and the product inlet 40 . In the closed position of diverter valves 82 , 84 , flow is diverted to flow through the recirculation bypass 80 and the flow connections with the product inlet 40 and the waste outlet 14 respectively are interrupted.
- the recirculation bypass 80 is shown internally of the housing 26 , it may also be provided as an add-on component at the product inlet side.
- flow may be re-circulated via the heating element 64 on a continuous basis and re-supplied to the habitable space 10 .
- This arrangement may be used to circulate and heat up an (unoccupied) building such as early in the morning in an office building.
- the waste inlet flow 39 is split by placing both the waste control valve 54 and the changeover valve 46 in the open position. A portion of the waste inlet flow 39 passes through the secondary channel 19 and is cooled by heat transfer to the primary channel 18 . The remainder of the waste inlet flow 39 passes through the first part of the waste channel 15 and is then returned via the recirculation bypass 80 to the primary channel 18 .
- the product channel diverter valve 84 is partly open or floating and allows mixing of fresh air from the product inlet 40 and recirculated air from the recirculation bypasss 80 . In this manner, a pre-warming of the product inlet flow may also be achieved as frost protection.
- the second fan unit 16 acts as a flow control element for the flow from the secondary channel 19 to the waste channel 15 .
- the product channel diverter valve 84 may be regulated by the pressure difference across the secondary channel 19 .
- FIG. 3 may also be operated in a recirculation mode in combination with dew point cooling according to the operational profile of Table 7.
- the operational profile of Table 7, differs from that of Table 6 in that the changeover valve 46 has been closed such that a connection is provided from the primary outlet 24 of the primary channel 18 to the secondary channel 19 . Furthermore, the heating element 64 is inactive and the dispensing valve 35 is active. In this respect, the profile corresponds to that of the cooling mode of FIG. 2 and Table 1. Contrary to that arrangement however, the waste inlet flow 39 is recirculated via the recirculation bypass 80 to the primary channel 18 . It is assumed that the temperature within the habitable space 10 is lower than the external temperature of the product inlet flow 21 . In cases of high humidity, it may also be the case that the humidity of the waste inlet flow 39 is also lower than that of the product inlet flow 21 .
- the second fan unit 16 acts as a flow control element for the flow from the secondary channel 19 to the waste channel 15 .
- the product channel diverter valve 84 may be regulated by the pressure difference P 1 -P 2 across the secondary channel 19 .
- FIG. 4 corresponds largely to FIG. 3 with the exception that the water distribution system is not shown for reasons of clarity.
- the embodiment of FIG. 4 depicts a second heat exchange element 2 ′ arranged parallel to heat exchange element 2 . Although this is shown as a separate element, it may also be in the form of a separated second set of primary and secondary channels 18 ′, 19 ′ in parallel with channels 18 , 19 .
- the outlets 25 , 25 ′ from both secondary channels 19 , 19 ′ join together for connection via flow control valve 48 to waste outlet 14 .
- first heat exchange element 2 provides the total cooling capacity for both heat exchange elements 2 , 2 ′ while the total output of the second heat exchange element 2 is available for cooling of the habitable space 10 .
- a recirculation bypass 80 is provided connected to the waste channel 15 .
- the recirculation bypass 80 is connected to a primary inlet 23 ′ of the second heat exchange element 2 ′ via a fan unit 27 ′.
- the primary outlet 24 ′ is connected to the product outlet 42 for supply of cooled air to the habitable space 10 .
- the habitable space 10 , the waste channel 15 and the primary channel 18 ′ of the second heat exchange element 2 ′ thus form an effectively closed (indoor) system.
- a fresh air valve 86 is located between the primary outlet 24 and the product outlet 42 . Furthermore, a balance valve 88 is arranged between the primary inlets 23 , 23 ′ for allowing an equal amount of flow out of the system by transfer from primary inlet 23 ′ to primary inlet 23 . Such an arrangement is most desirable in regions of high humidity where the amount of fresh air admitted to the system must be carefully regulated independently of the circulation flow for cooling.
- a dryer 90 may additionally be provided.
- the drier 90 (shown in broken lines) may be provided with a drier fan 92 connected to the product inlet 40 .
- the output from the drier 90 is connected to the product outlet 42 .
- the fresh air valve 86 may be closed.
- Fresh air enters the system via the dryer 90 for delivery to the habitable space 10 .
- the dried air is not cooled but is however mixed with the cooled primary flow 21 ′ from the second heat exchange element 2 ′.
- the amount of air entering via the drier 90 is then balanced by controlled flow through the balance valve 88 .
- the drier 90 may be a conventional dessicant wheel. More preferably, it can be provided by a further heat exchange element or channel similar to element 2 , in which the primary flow is passed through a small compressor before being returned through the secondary channel.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Sustainable Development (AREA)
- Life Sciences & Earth Sciences (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Air Conditioning Control Device (AREA)
- Duct Arrangements (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Compressor (AREA)
- Central Air Conditioning (AREA)
- Drying Of Gases (AREA)
Abstract
Description
- 1. Field of the Invention
- The present invention relates to cooling and ventilation devices and more particularly to devices incorporating evaporative heat exchangers. In particular it relates to such devices that can also operate to provide heat recovery in combination with ventilation.
- 2. Description of the Related Art
- An evaporative cooler is a device that uses the latent heat of evaporation of a liquid to provide cooling. The principle of evaporative cooling has been known for many centuries. For example, a damp cloth placed over an object will keep the object cool by evaporation of liquid from the cloth. By continuously adding liquid to the cloth, the cooling effect may be maintained indefinitely without input of electrical energy. The lowest temperature that can be reached by evaporation of moisture in this way into an air stream defines the wet-bulb temperature for that air. An indirect evaporative cooler makes use of this principle. A primary or product air stream passing over a primary surface of a heat exchange element may be cooled by a secondary or working air stream passing over and absorbing moisture from a secondary wetted surface of the heat exchanger.
- If a quantity of air is cooled by direct evaporation its absolute humidity increases due to the uptake of moisture. Its relative humidity also increases due to its lowered temperature until at the wet bulb temperature it is full saturated with water-vapour. If the air is cooled without direct evaporation however, its absolute humidity remains the same. As its temperature decreases only the relative humidity increases until full saturation of the air is reached at the so-called dew point. The dew point is thus lower than the wet bulb temperature and is in fact defined as the temperature to which a body of air must be cooled to reach saturation or 100% relative humidity. At this point, water vapour in the air condenses.
- Attempts have been made to improve on the principle of indirect evaporative cooling by cooling or drying the working air stream prior to evaporation taking place. A particularly convenient way of cooling the working air stream is to feedback a portion of the cooled product air. Such devices are often referred to as dew point coolers as they may lower the temperature of the product air to below its wet bulb temperature and close to the dew point. By optimising the surfaces with which the air streams exchange heat, highly effective heat transfer can be achieved. This has been found especially significant in the case of the heat transfer from the wetted secondary surface. In order to provide moisture to the working air stream, the wetted secondary surface may be provided with some form of liquid supply e.g. in the form of a hydrophilic layer. The presence of such a layer can however result in increased thermal isolation of the secondary surface from the working air stream, thus reducing heat transfer.
- A particularly efficient form of dew point cooler is known from PCT publication WO03/091633, the contents of which are hereby incorporated by reference in their entirety. While not wishing to be bound by theory, it is believed that the success of this device is due at least in part to the presence of heat transfer elements on the primary and secondary surfaces. These heat transfer elements may be in the form of fins and are believed to improve transmission of heat from the primary surface to the secondary surface. The fins act both to directly conduct heat and also to break up the various boundary layers that develop in the flow. They also serve to increase the total area available for heat exchange on the relevant surfaces. Further important features of the wetted second surface are known from that document and also from co-pending UK patent application No 0324348.2, the contents of which are also incorporated by reference in their entirety. Accordingly, by careful choice of the material used as a water retaining layer, optimal evaporation may be achieved without thermal isolation of the secondary surface from the working air stream.
- Another particularly efficient dew point cooler is discussed in co-pending PCT patent application No PCT/EP2006/070205, the contents of which are incorporated by reference in their entirety. Such a dew point cooler comprises a pair of heat conducting plates arranged in spaced, generally parallel relationship and spacing elements separating the plates from one another and defining primary and secondary flow channels between the plates. In this manner, heat transmission between the primary and secondary channels can take place primarily by conduction along the plates from the region associated with the primary channels to the regions associated with the secondary channels. This is in contrast to conventional arrangements where heat transfer between fluids takes place through a membrane separating the fluids.
- Such devices are extremely convenient for cooling, as they are simple to produce and require no refrigerant or compressor. Air may be circulated through the cooler using a low-pressure fan which has low energy consumption and is relatively silent. This makes the dew point cooler ideal for domestic use, especially at night.
- The degree of cooling of the product air in an evaporative cooler is determined at least partially by the amount of liquid that can be evaporated into the working air stream. In a dew point cooler configuration, this will depend on the portion of the product air that is returned as the working air stream. This will be referred to in the following as the working fluid/product fluid ratio (WPR). In prior art devices the WPR has been determined by the outlet configuration of the primary channels, where a baffle determines the amount of flow diverted into the secondary channels. This has generally ensured that about 30% of the product air is returned as working air. The remaining 70% is supplied to the room or space where cooling is required. An equal volume of air must therefore be evacuated as waste air from the room. In the past, this waste air has simply been allowed to escape by natural ventilation routes or it has been actively evacuated via a separate ventilation system.
- In setting up an evaporative cooling system using a dew point cooler, correct calibration of the system is important in order that the desired WPR is achieved. In actual practice, since most buildings are different, calibration must take place on-site and may involve considerable time. Furthermore, even when initially correctly calibrated, the performance of filters, fans and other components can change with time and cause the WPR to drift. The system may subsequently operate sub-optimally. The problems of set-up and calibration are further complicated if it is also desired to use the heat exchange unit for heat recovery or ventilation purposes or if it is operated with a separate waste air ventilation system. Adequate control of the WPR is also complicated by external factors such as wind pressure at the exterior of a building.
- Conventional heat recovery, ventilation and air conditioning systems do no presently provide adequate solutions to these problems as they are not concerned with the practicalities of a partial air-flow through the secondary channels of a dew point cooler. It should be noted that a conventional air-conditioning device operates to cool recirculated air without requiring direct connection to the outside air. A dew point cooler however could not work without such a connection.
- It would therefore be desirable to provide a cooling and ventilation device capable of operating according to the dew point cooling principle, in which calibration and installation are simplified. Preferably, this should be achieved using only the inlets and outlets required by conventional ventilation systems.
- According to the present invention, there is provided a cooling and ventilation device comprising: a product inlet, a product outlet, a waste inlet, a waste outlet, a waste channel connecting the waste inlet to the waste outlet, an evaporative heat exchanger having a primary channel connected between the product inlet and the product outlet and a secondary channel connected between an outlet from the primary channel and the waste channel, a flow control element effective to control flow from the secondary channel to the waste channel and a controller selectively controlling the flow control element to thereby control flow from the secondary channel to the waste channel. The product inlet may be connected to a suitable source of outside air and the product outlet supplied to a habitable space such as the interior of a building or vehicle. The waste inlet may receive expelled air from the habitable space, which is subsequently exhausted to the environment via the waste outlet. In this manner, a device is achieved that can provide all of the benefits of evaporative cooling and ventilation while only requiring two air inlets and two air outlets.
- According to a first embodiment of the invention, the flow control element is a valve located between the waste channel and the secondary channel. This form of flow control has been found to operate in an extremely simple and efficient manner without the extra expense and power consumption of an additional fan to control the secondary flow. Of course, the person skilled in the art will understand that alternative flow control elements may be provided, the function of this element being to control flow from the secondary channel to the waste channel. For example, although such embodiment suffers from disadvantages as discussed, a fan, or other forced draft device, may be used to as the flow control element.
- According to a further aspect of the invention, the device further comprises a sensor providing a flow signal indicative of the flow through the secondary channel and wherein the controller controls the flow control element on the basis of the flow signal. By determining the secondary flow into the waste channel, careful control of the WFR can be achieved, either to maintain it at a constant value or alternatively to regulate it on the basis of desired flow parameters.
- In a preferred embodiment, the flow sensor comprises pressure sensors responsive to the pressure drop across the secondary channel. These sensors may be calibrated in the factory and will then provide accurate values for control of the secondary flow, largely independently of the manner or position of installation of the device. Installation of the device is then considerably simplified and there may be less tendency for the WFR to vary with time since the flow characteristics of the secondary channel are generally constant.
- According to an additional advantage of the invention, a heat recovery valve arrangement may be provided between the waste inlet and an inlet to the secondary channel. This allows switching of the source of fluid supplied to the secondary channel. In a cooling mode, the secondary flow may be provided as a portion of the primary flow from the outlet of the primary channel. In a heat recovery mode, the waste air from the habitable space may be supplied to the secondary channel for heat exchange with the incoming primary air.
- Preferably, the device comprises a first fan unit between the product inlet and the primary channel of the evaporative heat exchanger for driving the flow of primary air through the primary channel. The device preferably also comprises a second fan unit in the waste channel adjacent to the waste outlet for driving the flow through the waste channel and/or the secondary channel.
- According to the preferred embodiment of the invention, the device further comprises a suitable water distribution system for distributing water to surfaces of the secondary channel for evaporation. There may also be provided a drainage system for recovery of excess water from either the water distribution system or from condensation e.g. during heat recovery.
- According to a yet further embodiment of the invention, the device may also comprise a recirculation channel for selectively connecting the waste channel to the product inlet. In this manner, at least some of the waste air may be recirculated through the primary channels for subsequent reuse. This is particularly useful in circumstances where it may be desirable to limit the amount of waste air that is allowed to exhaust from the habitable space. This may be the case when the external temperature and humidity is high. For this reason it may also be desirable to keep the recirculated air separate from the fresh air entering from the product inlet. This may be achieved by having separate product channels for fresh air and recirculated air. The recirculated air may then be preferentially provided to the secondary channel for subsequent exhaust via the waste outlet.
- According to a yet further aspect of the invention, there is further provided a heating element provided adjacent to the product outlet for heating a flow of product air prior to supplying it to the habitable space. In this manner, when used for ventilation or heat recovery purposes, additional warmth may be added to the product air to bring its temperature up to the desired value for comfort.
- According to a still further embodiment of the invention, a dryer may be provided for removing moisture from the air prior to supplying it to the habitable space. The dryer may be located between the product inlet and the primary channel in order to increase the effectiveness of the evaporative cooling device. Alternatively, the dryer may be provided at the product outlet. In this manner, only the air supplied to the habitable space is dried. In a particularly advantageous alternative, the drier is provided with a direct supply of outside air from the product inlet and the device is operated in a recirculation mode. This has the advantageous effect that the amount of dried fresh air entering the system can be carefully controlled independently of the cooling circulation through the evaporative cooler.
- According to the preferred embodiment of the invention, the controller comprises a memory containing a plurality of operational profiles and is active to control the device according to one or more of the operational profiles. The operational profiles may include: a cooling mode; a heat recovery mode; a ventilation mode; a heating mode; a recirculation mode; and a drying mode. The profiles may be manually selected or the device may also include an automatic mode in which the most appropriate profile or combination of profiles is selected in order to correctly condition the habitable space. The device also preferably comprises a plurality of environmental sensors for sensing temperature, pressure or humidity at the inlets and outlets of the device and for providing environmental signals to the controller. The controller may then select and or carry out a particular operational profile on the basis of the environmental signals.
- The invention also relates to a cooling and ventilation device comprising: a product inlet; a product outlet to a habitable space; a waste inlet from a habitable space; a waste outlet; a first evaporative heat exchanger having a primary channel and a secondary channel; a second evaporative heat exchanger having a primary channel and a secondary channel; the first evaporative heat exchanger having the primary channel connected between the product inlet and an inlet to the secondary channels of both the first and second evaporative heat exchangers; the second evaporative heat exchanger having the primary channel connected between the waste inlet and the product outlet; the waste outlet being connected to outlets from the secondary channels of both the first and second evaporative heat exchangers; and the cooling and ventilation device further comprising flow control elements effective to control a first circulation from the habitable space through the primary channel of the second evaporative heat exchanger and back to the habitable space and to control a second circulation from the product inlet, through the primary channel of the first evaporative heat exchanger and subsequently through the secondary channels of both the first and second evaporative heat exchangers to the waste outlet. In this manner, the cooling effect can be maintained substantially separate from the ventilation effect.
- According to a preferred arrangement of this embodiment the cooling and ventilation device further comprises a fresh air feed providing a supply of fresh air from the second circulation to the first circulation. In this manner, a quantity of fresh air may be allowed to enter the otherwise closed first circulation
- According to a further advantageous form of this embodiment, the cooling and ventilation device further comprises a waste feed providing a supply of waste air from the first circulation to the second circulation. The supply of waste air may be controlled to equal the fresh air feed such that the air flows are balanced.
- Also in this embodiment, a dryer may be provided in fluid commination with the product inlet for drying a quantity of the air for supply to the habitable space.
- Embodiments of the invention will now be described in further detail by way of example only with reference to the accompanying figures, in which:
-
FIG. 1 is a schematic view of a conventional evaporative heat exchanger operating as a dew point cooler; -
FIG. 2 is a schematic view of a cooling and ventilation device according to a first embodiment of the invention; -
FIG. 3 is a schematic view of a cooling and ventilation device according to a second embodiment of the invention; and -
FIG. 4 is a schematic view of a cooling and ventilation device according to a third embodiment of the invention. - The following is a description of certain embodiments of the invention, given by way of example only and with reference to the drawings. Referring to
FIG. 1 , there is shown schematically a dew point cooler 20 of the type described in WO03/091633. It comprises aprimary channel 18 and asecondary channel 19. Aprimary flow 21 flows through theprimary channel 18. Asecondary flow 22 flows through thesecondary channel 19. The dew point cooler 20 further comprises aprimary inlet 23, aprimary outlet 24 and asecondary outlet 25. The inlets and outlets form part of ahousing 26. Afirst fan unit 27 drives theprimary flow 21. Placed in the housing is a heat-exchangingmembrane 28 which separatesprimary channel 18 fromsecondary channel 19. Situated close to theprimary outlet 24 is aduct 29 which can be closed and opened by means of avalve 30, controlled by anactuator 31. In the open position of thevalve 30, a selected part ofprimary flow 21 is branched off according to the WPR in the form ofsecondary flow 22, while the remaining part continues as aproduct outlet flow 37. - The
membrane 28 bearsprimary fins 32 andsecondary fins 33. These serve to break up the relevant boundary layers and to increase the effective surface area ofmembrane 28. Thesecondary fins 33 are provided with a hydrophilic coating that can buffer a determined quantity of water. This water is supplied via awater conduit 34 and a dispensingvalve 35 todistribution nozzles 36. This ensures a continuous wetting of the coating. - The
secondary flow 22 provides evaporation of the water present on the coating, causing a cooling offins 33,membrane 28 and therebyfins 32. In this manner theprimary flow 21 is also cooled. Theproduct outlet flow 37 thus has a smaller flow rate thanprimary flow 21, but also a reduced temperature. Thisproduct outlet flow 37 is supplied for cooling ahabitable space 10. Thesecondary flow 22 entraining the water vapour is discharged to the outside. - It will be clear to the skilled person that the evaporative cooler of
FIG. 1 is an example of a suitable evaporative cooler only and that alternative evaporative coolers may be used in its place. For example, an evaporative cooler may be provided which has the same features as the embodiment described in relation toFIG. 1 except that the heat-exchangingmembrane 28 is replaced by a spacing element which separates theprimary flow 21 andsecondary flow 22; and theprimary fins 32 andsecondary fins 33 are replaced by heat-conducting plates which extend through the spacing element to form primary fins and secondary fins. This results in primary and secondary fins which are formed of a continuous plate of heat-conducting material. The heat transmission between the primary and secondary channels therefore takes place by conduction along the plates from the region associated with the primary channels to the region associated with the secondary channels. The spacing element may or may not be heat conducting because the primary heat conduction path across the spacing element is via the plates. - According to conventional arrangements, the
habitable space 10 would havedoors 11,windows 12 andpassive vents 13. Often, an activewaste air outlet 14 would also be provided for active ventilation of awaste outlet flow 38 from thehabitable space 10 to the outside. This is shown in the form of awaste channel 15 having asecond fan unit 16. For cooling, it is preferable that the warmest air layers are exhausted and for this purpose awaste inlet 17 to thewaste channel 15 would be located at an upper level within thespace 10 for receiving awaste inlet flow 39. It is noted that thewaste channel 15 andsecond fan unit 16 are not part of thedew point cooler 20. - For operation of the dew point cooler, a quantity of air equal to the
product outlet flow 37 must be exhausted from thespace 10. This can take place either via thewaste channel 14 or viadoors 11,windows 12vents 13 or other natural openings. This quantity is determined by the WPR according to the position of thevalve 30. As a result of this configuration, any change to the pressure difference between theprimary inlet 23 and thehabitable space 10 would significantly affect the quantity of thesecondary air flow 22. Such changes could occur due to wind pressure differences between primary inlet and waste outlet, opening of windows or doors, changes in operation of the second fan unit or the like. -
FIG. 2 illustrates schematically a cooling andventilation device 1 according to the present invention operable in various modes of operation. Similar features to those described in relation toFIG. 1 will be identified by like numerals. - Referring to
FIG. 2 , thedevice 1 comprises ahousing 26 in which are located a number of components including aheat exchange element 2. Theheat exchange element 2 may be as used in the dew point coolers described in relation toFIG. 1 above but could also comprise different forms of heat exchange element providing similar or higher efficiency of heat transfer. Thehousing 26 has aproduct inlet 40 connecting to aprimary inlet 23 of theheat exchange element 2 and aproduct outlet 42 connected to theprimary outlet 24 of theheat exchange element 2. Theproduct outlet 42 is in communication withhabitable space 10. There is also provided awaste inlet 17 in communication with thehabitable space 10.Waste inlet 17 communicates further with awaste channel 15, leading to awaste outlet 14. - The
heat exchange element 2 has aprimary channel 18 connecting theprimary inlet 23 and theprimary outlet 24. It also has asecondary channel 19 connected between asecondary inlet 44 and asecondary outlet 25. Thesecondary inlet 44 is provided with achangeover valve 46, which in a closed position connects it to theprimary outlet 24. In the open position of thechangeover valve 46 thesecondary inlet 44 is isolated from theprimary outlet 24 and connected instead to thewaste inlet 17. Thesecondary outlet 25 is connected to thewaste channel 15 via aflow control valve 48. There is also provided awaste control valve 54 in thewaste channel 15, between thechangeover valve 46 and the point where thewaste channel 15 connects to thesecondary outlet 25. - In order for the
heat exchange element 2 to function as an evaporative cooler, there is provided awater distribution system 50. Thewater distribution system 50 comprises awater conduit 34 and a dispensingvalve 35, leading todistribution nozzles 36. Below theheat exchange element 2 is located adrip tray 52. Adrain 56 leads from thedrip tray 52 via apump 58 to the exterior of thehousing 26. - A number of further functional components are contained within the
housing 26. Afirst fan unit 27 is provided between theproduct inlet 40 and theprimary inlet 23. Asecond fan unit 16 is located in thewaste channel 15 adjacent to thewaste outlet 14. Aproduct filter 60 is located between theproduct inlet 40 and thefirst fan unit 27. Awaste filter 62 is located in thewaste channel 15 adjacent to thewaste inlet 17. Aheating element 64 is located between theprimary outlet 24 and theproduct outlet 42. - Also located within the
housing 26 are a number of sensors and other components for control and regulation of the operation of the cooling andventilation device 1. A product inlet temperature andhumidity sensor 66 is located at theproduct inlet 40. A productoutlet temperature sensor 68 is located at theproduct outlet 42. A wasteinlet temperature sensor 70 is located at thewaste inlet 17. Furthermore, there are provided a primaryoutlet pressure sensor 72 at theprimary outlet 24 and a secondaryoutlet pressure sensor 74 at thesecondary outlet 25. Alevel sensor 76 is provided for determining the level of water in thedrip tray 52. All of the sensors are operatively connected to acontroller 78. Thecontroller 78 is also operatively connected to thevalves beater 64, first andsecond fan units pump 58. Thecontroller 78 is provided with the necessary hardware and software to operate the functional components in response to signals received from the sensors and according to predefined and user defined settings. In particular, thecontroller 78 comprises a memory (not shown) containing a plurality of operational profiles and is active to control thedevice 1 according to one or more of the operational profiles. According toFIG. 2 , the sensors and functional components are all located within the housing 3. It will nevertheless be understood by the skilled person that certain of these elements could be located remotely. Thus thetemperature sensors controller 78 in any appropriate manner. Similarly, thefan units - Operation of the cooling and
ventilation device 1 in a cooling mode will now be described with reference to Table 1, which indicates the operational profile of certain functional components for this mode of operation for four different suggested levels of cooling. -
TABLE 1 Ref Value No. Process/Referenced Part State Level 1 Level 2Level 3 Level 4 21 Product inlet flow Active 150 m3/h 300 m3/h 450 m3/h 600 m3/ h 37 Product outlet flow Active 100 m3/h 200 m3/h 300 m3/h 400 m3/ h 38 Waste outletflow Active 150 m3/h 300 m3/h 450 m3/h 600 m3/ h 39 Waste inlet flow Active 100 m3/h 200 m3/h 300 m3/h 400 m3/ h 22 Secondary flow Active 50 m3/h 100 m3/h 150 m3/h 200 m3/ h 46 Changeover valve Closed 54 Waste control valve Open 48 Flow control valve Regulated by P1- P2 15 Pa 30 Pa 45 Pa 60 Pa 27 First fan unit Set to 150 m3/h 300 m3/h 450 m3/h 600 m3/ h 16 Second fan unit Set to 150 m3/h 300 m3/h 450 m3/h 600 m3/ h 64 Heating element Inactive 60 Product inlet temperature/humidity Active sensor 68 Product outlet temperature sensor Active 70 Waste inlet temperature sensor Active 72 Primary outlet pressure sensor Active 74 Secondary outlet pressure sensor Active 60 Product inlet filter Active 62 Waste inlet filter Active 35 Dispensing valve Active 58 Pump Active - In the cooling mode, the
fan unit 27 is active to deliver outside air as aproduct inlet flow 21 to theprimary channel 18.Changeover valve 46 is closed, whereby a connection is provided from theprimary outlet 24 to thesecondary channel 19. A part of theproduct inlet flow 21 is thus diverted as asecondary flow 22 into thesecondary channel 19. The remainder of theproduct inlet flow 21 is delivered to thehabitable space 10 asproduct outlet flow 37. Dispensingvalve 35 is active to provide water (intermittently) viadistribution nozzles 36 to thesecondary channel 19 where it can then evaporate into thesecondary flow 22.Pump 58 is active to extract water from thedrip tray 52 in response to signals from thelevel sensor 76. - The
second fan unit 16 is also active to extract air from thehabitable space 10 throughwaste inlet 17. Thewaste control valve 54 is open and thewaste inlet flow 39 can flow through thewaste channel 15 to thewaste outlet 14. According to Table 1, thewaste inlet flow 39 corresponds to theproduct outlet flow 37, although this need not be the case if other ducts are provided into thehabitable space 10. - According to the invention, the
flow control valve 48 is actively regulated by signals from thecontroller 78. Thecontroller 78 receives a pressure signal P1 from the primaryoutlet pressure sensor 72 and a pressure signal P2 from the secondaryoutlet pressure sensor 74. It then adjusts the degree of opening of theflow control valve 48 to maintain the pressure drop P1-P2 betweensensors secondary flow 22 can be maintained constant, since the flow rate through thesecondary channel 19 is related to the pressure drop across it. Of particular importance, thesecondary flow 22 is no longer dependent upon thewaste inlet flow 39. - Although not shown in Table 1, the position of
valve 48 may alternatively or additionally be adjusted dependent upon other factors. Thus, if theproduct inlet flow 21 is particularly dry, the temperature of theproduct outlet flow 37 may become too low. In this case, thevalve 48 may be adjusted to maintain a lower pressure drop and a lowersecondary flow 22. The choice of level may be set manually by a user or may also be adjusted on the basis of e.g. the temperature in thehabitable space 10. - If the temperature in the
habitable space 10 is comfortable and cooling is not required, thedevice 1 may operate in a ventilation mode according to the operational profile of Table 2. In this mode, fresh air is circulated to thespace 10 in an amount according to the suggested levels defined in Table 2. -
TABLE 2 Ref Value No. Process/Referenced Part State Level 1 Level 2Level 3 Level 4 21 Product inlet flow Active 150 m3/h 300 m3/h 450 m3/h 600 m3/ h 37 Product outlet flow Active 150 m3/h 300 m3/h 450 m3/h 600 m3/ h 38 Waste outletflow Active 150 m3/h 300 m3/h 450 m3/h 600 m3/ h 39 Waste inlet flow Active 150 m3/h 300 m3/h 450 m3/h 600 m3/ h 22 Secondary flow Inactive 0 m3/h 0 m3/h 0 m3/h 0 m3/ h 46 Changeover valve Closed 54 Waste control valve Open 48 Flow control valve Closed 27 First fan unit Set to 150 m3/h 300 m3/h 450 m3/h 600 m3/ h 16 Second fan unit Set to 150 m3/h 300 m3/h 450 m3/h 600 m3/ h 64 Heating element Inactive 60 Product inlet temperature/humidity Active sensor 68 Product outlet temperature sensor Active 70 Waste inlet temperature sensor Active 72 Primary outlet pressure sensor Active 74 Secondary outlet pressure sensor Active 60 Product inlet filter Active 62 Waste inlet filter Active 35 Dispensing valve Inactive 58 Pump Active - According to Table 2, in the ventilation mode, the
flow control valve 48 has been closed and the dispensingvalve 35 is inactive such that supply of water to theheat exchange element 2 is stopped. Thepump 58 is still active should the level in thedrip tray 52 rise. Theproduct inlet flow 21 is now equal to thewaste inlet flow 39 and thesecondary channel 19 is inactive. This has the advantage that thesecondary channel 19 retains moisture for subsequent evaporation should the mode be changed to cooling. - During cold periods, the
device 1 may be operated in a heat recovery mode to provide ventilation. Table 3 indicates the operational profile of certain functional components for this mode of operation for four different suggested levels of ventilation. -
TABLE 3 Ref Value No. Process/Referenced Part State Level 1 Level 2Level 3 Level 4 21 Product inlet flow Active 100 m3/h 150 m3/h 200 m3/h 250 m3/ h 37 Product outlet flow Active 100 m3/h 150 m3/h 200 m3/h 250 m3/ h 38 Waste outletflow Active 100 m3/h 150 m3/h 200 m3/h 250 m3/ h 39 Waste inlet flow Active 100 m3/h 150 m3/h 200 m3/h 250 m3/ h 22 Secondary flow Inactive 0 m3/h 0 m3/h 0 m3/h 0 m3/ h 46 Changeover valve Open 54 Waste control valve Closed 48 Flow control valve Open 27 First fan unit Set to 100 m3/h 150 m3/h 200 m3/h 250 m3/ h 16 Second fan unit Set to 100 m3/h 150 m3/h 200 m3/h 250 m3/ h 64 Heating element Inactive 60 Product inlet temperature/humidity Active sensor 68 Product outlet temperature sensor Active 70 Waste inlet temperature sensor Active 72 Primary outlet pressure sensor Active 74 Secondary outlet pressure sensor Active 60 Product inlet filter Active 62 Waste inlet filter Active 35 Dispensing valve Inactive 58 Pump Active - In this mode there is provided a heat recovery valve arrangement which acts to channel the fluid of the waste channel to the secondary channel, in this manner heat exchange is carried out between the outgoing waste and the incoming product. In the specific example of
FIG. 2 , the heat recovery valve arrangement comprises change overvalve 46,waste control valve 54 andflow control valve 48. Thechangeover valve 46 is opened and thewaste control valve 54 is closed. Theflow control valve 48 is kept in the fully open position. All of thewaste inlet flow 39 is now caused to pass through thesecondary channel 19 of theheat exchange element 2. Heat exchange with theproduct inlet flow 21 takes place causing this to be warmed as thesecondary flow 22 is cooled. Although the dispensingvalve 35 is inactive, thepump 58 may still operate to remove any water collecting due to condensation. Under certain circumstances it may also be desirable to add water or other humidification products to theprimary channel 18 or into theproduct outlet flow 37 in order to increase the humidity in thehabitable space 10. - Of significance, it should be noted that during heat recovery use, the flow through the
primary channel 18 takes place in the same direction as in the cooling mode. The same applies for thesecondary channel 19. In particular the flow through thesecondary channel 19 always takes place in the direction of thewaste outlet 14 such that any contamination formed in thesecondary channel 19 will be directed away from thehabitable space 10. - During even colder periods or if additional comfort is required, the
device 1 may be operated in a heat recovery and beating mode to provide ventilation. Table 4 indicates the operational profile of certain functional components for this mode of operation for four different suggested levels of ventilation. -
TABLE 4 Ref Value No. Process/Referenced Part State Level 1 Level 2Level 3 Level 4 21 Product inlet flow Active 100 m3/h 150 m3/h 200 m3/h 250 m3/ h 37 Product outlet flow Active 100 m3/h 150 m3/h 200 m3/h 250 m3/ h 38 Waste outletflow Active 100 m3/h 150 m3/h 200 m3/h 250 m3/ h 39 Waste inlet flow Active 100 m3/h 150 m3/h 200 m3/h 250 m3/ h 22 Secondary flow Inactive 0 m3/h 0 m3/h 0 m3/h 0 m3/ h 46 Changeover valve Open 54 Waste control valve Closed 48 Flow control valve Open 27 First fan unit Set to 100 m3/h 150 m3/h 200 m3/h 250 m3/ h 16 Second fan unit Set to 100 m3/h 150 m3/h 200 m3/h 250 m3/ h 64 Heating element Active 500 W 1 KW 1.5 KW 2 KW 60 Product inlet temperature/humidity Active sensor 68 Product outlet temperature sensor Active 70 Waste inlet temperature sensor Active 72 Primary outlet pressure sensor Active 74 Secondary outlet pressure sensor Active 60 Product inlet filter Active 62 Waste inlet filter Active 35 Dispensing valve Inactive 58 Pump Active - This mode of operation differs from the heat recovery mode only in that the
heating element 64 is active to additionally heat theproduct outlet flow 37. Theheating element 64 may be an electrical heater although hot water or other such heating elements may also be used. For extremely low external temperature operation, it is also possible to provide frost protection for the incoming product inlet flow to prevent humid air exitingsecondary channel 19 from condensing and freezing aroundsecondary outlet 25. This may be achieved by a small electrical pre-heater (not shown) or similar device at theproduct inlet 40. - A further embodiment of the invention is shown in
FIG. 3 . The embodiment ofFIG. 3 corresponds substantially to that disclosed inFIG. 2 and those features common to the earlier embodiment will not be further described. According toFIG. 3 , arecirculation bypass 80 has been added between thewaste channel 15 and the product inlet channel between theproduct filter 60 and thefirst fan unit 27. A wastechannel diverter valve 82 is located at the junction between therecirculation bypass 80 andwaste channel 15. A productchannel diverter valve 84 is provided at the junction between therecirculation bypass 80 and theproduct inlet 40. In the closed position ofdiverter valves recirculation bypass 80 and the flow connections with theproduct inlet 40 and thewaste outlet 14 respectively are interrupted. It is noted that although therecirculation bypass 80 is shown internally of thehousing 26, it may also be provided as an add-on component at the product inlet side. - Operation of the embodiment of
FIG. 3 in a recirculation heating mode will be described with reference to Table 5 which shows four different levels of circulation. -
TABLE 5 Ref Value No. Process/Referenced Part State Level 1 Level 2Level 3 Level 4 21 Product inlet flow Inactive 0 m3/h 0 m3/h 0 m3/h 0 m3/ h 37 Product outlet flow Active 100 m3/h 150 m3/h 200 m3/h 250 m3/ h 38 Waste outletflow Inactive 0 m3/h 0 m3/h 0 m3/h 0 m3/ h 39 Waste inlet flow Active 100 m3/h 150 m3/h 200 m3/h 250 m3/ h 22 Secondary flow Inactive 0 m3/h 0 m3/h 0 m3/h 0 m3/ h 46 Changeover valve Open 54 Waste control valve Closed 48 Flow control valve Open 82 Waste channel diverter valve Closed 84 Product channel diverter valve Closed 27 First fan unit Set to 100 m3/h 150 m3/h 200 m3/h 250 m3/ h 16 Second fan unit Inactive 0 m3/h 0 m3/h 0 m3/h 0 m3/ h 64 Heating element Active 500 W 1 KW 1.5 KW 2 KW 60 Product inlet temperature/humidity Active sensor 68 Product outlet temperature sensor Active 70 Waste inlet temperature sensor Active 72 Primary outlet pressure sensor Active 74 Secondary outlet pressure sensor Active 60 Product inlet filter Active 62 Waste inlet filter Active 35 Dispensing valve Inactive 58 Pump Active - In this manner, flow may be re-circulated via the
heating element 64 on a continuous basis and re-supplied to thehabitable space 10. This arrangement may be used to circulate and heat up an (unoccupied) building such as early in the morning in an office building. - Operation of the embodiment of
FIG. 3 in a recirculation heat recovery mode will be described with reference to Table 6 which shows four different levels of circulation. -
TABLE 6 Ref Value No. Process/Referenced Part State Level 1 Level 2Level 3 Level 4 21 Product inlet flow Active 50 m3/h 100 m3/h 150 m3/h 200 m3/ h 37 Product outlet flow Active 100 m3/h 150 m3/h 200 m3/h 250 m3/ h 38 Waste outletflow Active 50 m3/h 100 m3/h 150 m3/h 200 m3/ h 39 Waste inlet flow Active 100 m3/h 150 m3/h 200 m3/h 250 m3/ h 22 Secondary flow Active 50 m3/h 100 m3/h 150 m3/h 200 m3/ h 46 Changeover valve Open 54 Waste control valve Open 48 Flow control valve Open 82 Waste channel diverter valve Closed 84 Product channel diverter valve Partly open 27 First fan unit Set to 100 m3/h 150 m3/h 200 m3/h 250 m3/ h 16 Second fan unit Inactive 50 m3/h 100 m3/h 150 m3/h 200 m3/ h 64 Heating element Active 500 W 1 KW 1.5 KW 2 KW 60 Product inlet temperature/humidity Active sensor 68 Product outlet temperature sensor Active 70 Waste inlet temperature sensor Active 72 Primary outlet pressure sensor Active 74 Secondary outlet pressure sensor Active 60 Product inlet filter Active 62 Waste inlet filter Active 35 Dispensing valve Inactive 58 Pump Active - According to the operational profile for recirculation and heat recovery, the
waste inlet flow 39 is split by placing both thewaste control valve 54 and thechangeover valve 46 in the open position. A portion of thewaste inlet flow 39 passes through thesecondary channel 19 and is cooled by heat transfer to theprimary channel 18. The remainder of thewaste inlet flow 39 passes through the first part of thewaste channel 15 and is then returned via therecirculation bypass 80 to theprimary channel 18. The productchannel diverter valve 84 is partly open or floating and allows mixing of fresh air from theproduct inlet 40 and recirculated air from therecirculation bypasss 80. In this manner, a pre-warming of the product inlet flow may also be achieved as frost protection. It is furthermore noted that in this mode, thesecond fan unit 16 acts as a flow control element for the flow from thesecondary channel 19 to thewaste channel 15. Additionally or alternatively, the productchannel diverter valve 84 may be regulated by the pressure difference across thesecondary channel 19. - The embodiment of
FIG. 3 may also be operated in a recirculation mode in combination with dew point cooling according to the operational profile of Table 7. -
TABLE 6 Ref Value No. Process/Referenced Part State Level 1 Level 2Level 3 Level 4 21 Product inlet flow Active 50 m3/h 100 m3/h 150 m3/h 200 m3/ h 37 Product outlet flow Active 100 m3/h 200 m3/h 300 m3/h 400 m3/ h 38 Waste outletflow Active 50 m3/h 100 m3/h 150 m3/h 200 m3/ h 39 Waste inlet flow Active 100 m3/h 200 m3/h 300 m3/h 400 m3/ h 22 Secondary flow Active 50 m3/h 100 m3/h 150 m3/h 200 m3/ h 46 Changeover valve Closed 54 Waste control valve Open 48 Flow control valve Open 82 Waste channel diverter valve Closed 84 Product channel diverter valve Partly open 27 First fan unit Set to 150 m3/h 300 m3/h 450 m3/h 600 m3/ h 16 Second fan unit Set to 50 m3/h 100 m3/h 150 m3/h 200 m3/ h 64 Heating element Inactive 60 Product inlet temperature/humidity Active sensor 68 Product outlet temperature sensor Active 70 Waste inlet temperature sensor Active 72 Primary outlet pressure sensor Active 74 Secondary outlet pressure sensor Active 60 Product inlet filter Active 62 Waste inlet filter Active 35 Dispensing valve Active 58 Pump Active - The operational profile of Table 7, differs from that of Table 6 in that the
changeover valve 46 has been closed such that a connection is provided from theprimary outlet 24 of theprimary channel 18 to thesecondary channel 19. Furthermore, theheating element 64 is inactive and the dispensingvalve 35 is active. In this respect, the profile corresponds to that of the cooling mode ofFIG. 2 and Table 1. Contrary to that arrangement however, thewaste inlet flow 39 is recirculated via therecirculation bypass 80 to theprimary channel 18. It is assumed that the temperature within thehabitable space 10 is lower than the external temperature of theproduct inlet flow 21. In cases of high humidity, it may also be the case that the humidity of thewaste inlet flow 39 is also lower than that of theproduct inlet flow 21. In such circumstances, it is a waste of cooling capacity to allow thewaste inlet flow 39 to be exhausted directly. Instead, by recirculating it, it may be assured that onlysecondary flow 22 is exhausted, having a temperature close to the external temperature and being fully saturated. As in the operational profile of Table 6, thesecond fan unit 16 acts as a flow control element for the flow from thesecondary channel 19 to thewaste channel 15. Additionally or alternatively, the productchannel diverter valve 84 may be regulated by the pressure difference P1-P2 across thesecondary channel 19. - The advantages of recirculation may be further exploited according to the embodiment of
FIG. 4 . According toFIG. 4 , a number of further components are added to the cooling andventilation device 2 as previously described.FIG. 4 corresponds largely toFIG. 3 with the exception that the water distribution system is not shown for reasons of clarity. The embodiment ofFIG. 4 depicts a secondheat exchange element 2′ arranged parallel to heatexchange element 2. Although this is shown as a separate element, it may also be in the form of a separated second set of primary andsecondary channels 18′, 19′ in parallel withchannels outlets secondary channels flow control valve 48 towaste outlet 14. Only theprimary outlet 24 fromheat exchange element 2 however is joined to thesecondary inlets secondary channels heat exchange element 2 provides the total cooling capacity for bothheat exchange elements heat exchange element 2 is available for cooling of thehabitable space 10. As inFIG. 3 , arecirculation bypass 80 is provided connected to thewaste channel 15. In this case however therecirculation bypass 80 is connected to aprimary inlet 23′ of the secondheat exchange element 2′ via afan unit 27′. Theprimary outlet 24′ is connected to theproduct outlet 42 for supply of cooled air to thehabitable space 10. Thehabitable space 10, thewaste channel 15 and theprimary channel 18′ of the secondheat exchange element 2′ thus form an effectively closed (indoor) system. - In order to also allow entry of fresh air into the system for delivery to the
habitable space 10, afresh air valve 86 is located between theprimary outlet 24 and theproduct outlet 42. Furthermore, a balance valve 88 is arranged between theprimary inlets primary inlet 23′ toprimary inlet 23. Such an arrangement is most desirable in regions of high humidity where the amount of fresh air admitted to the system must be carefully regulated independently of the circulation flow for cooling. - For complete humidity control, a
dryer 90 may additionally be provided. InFIG. 4 , the drier 90 (shown in broken lines) may be provided with adrier fan 92 connected to theproduct inlet 40. The output from the drier 90 is connected to theproduct outlet 42. In this case, thefresh air valve 86 may be closed. Fresh air enters the system via thedryer 90 for delivery to thehabitable space 10. The dried air is not cooled but is however mixed with the cooledprimary flow 21′ from the secondheat exchange element 2′. The amount of air entering via the drier 90 is then balanced by controlled flow through the balance valve 88. It is noted that the manner in which the drier 90 is connected is open to variation although for maximum efficiency, only the air that is finally supplied to thehabitable space 10 need be dried. It will be noted that further sensors and control and regulation valves may be provided to ensure correct control of the embodiment ofFIG. 4 . The drier 90 may be a conventional dessicant wheel. More preferably, it can be provided by a further heat exchange element or channel similar toelement 2, in which the primary flow is passed through a small compressor before being returned through the secondary channel. - Thus, the invention has been described by reference to certain embodiments discussed above. It will be recognized that these embodiments are susceptible to various modifications and alternative forms well known to those of skill in the art. Many modifications in addition to those described above may be made to the structures and techniques described herein without departing from the spirit and scope of the invention. Accordingly, although specific embodiments have been described, these are examples only and are not limiting upon the scope of the invention.
Claims (20)
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GB0600274.5 | 2006-01-09 | ||
GBGB0600274.5A GB0600274D0 (en) | 2006-01-09 | 2006-01-09 | Cooling and ventilation device |
PCT/EP2007/050164 WO2007080162A2 (en) | 2006-01-09 | 2007-01-09 | Cooling and ventilation device |
Publications (1)
Publication Number | Publication Date |
---|---|
US20090075581A1 true US20090075581A1 (en) | 2009-03-19 |
Family
ID=35911520
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US12/160,316 Abandoned US20090075581A1 (en) | 2006-01-09 | 2007-01-09 | Cooling and ventilation device |
Country Status (16)
Country | Link |
---|---|
US (1) | US20090075581A1 (en) |
EP (1) | EP1977171B1 (en) |
JP (1) | JP5175219B2 (en) |
KR (1) | KR20080104270A (en) |
CN (1) | CN101384859B (en) |
AT (1) | ATE537411T1 (en) |
AU (1) | AU2007204360A1 (en) |
BR (1) | BRPI0706453A2 (en) |
CA (1) | CA2646393A1 (en) |
GB (1) | GB0600274D0 (en) |
IL (1) | IL192704A0 (en) |
MY (1) | MY146212A (en) |
RU (1) | RU2008132733A (en) |
TW (1) | TW200732607A (en) |
WO (1) | WO2007080162A2 (en) |
ZA (1) | ZA200806324B (en) |
Cited By (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20110269388A1 (en) * | 2009-01-18 | 2011-11-03 | Matthijs Dirk Meulenbelt | Cooling Device |
US20120024000A1 (en) * | 2010-07-28 | 2012-02-02 | Lg Electronics Inc. | Ice making machine |
US20120260739A1 (en) * | 2011-04-13 | 2012-10-18 | Yang Seung Duk | Bidirectional wind pressure detecting apparatus |
US20130211600A1 (en) * | 2012-02-14 | 2013-08-15 | Honeywell International Inc. | Hvac controller with ventilation boost control |
US20140260372A1 (en) * | 2013-03-13 | 2014-09-18 | Alliance For Sustainable Energy, Llc | Control methods and systems for indirect evaporative coolers |
US20140260398A1 (en) * | 2013-03-13 | 2014-09-18 | Alliance For Sustainable Energy, Llc | Indirect evaporative coolers with enhanced heat transfer |
US9518784B2 (en) | 2008-01-25 | 2016-12-13 | Alliance For Sustainable Energy, Llc | Indirect evaporative cooler using membrane-contained, liquid desiccant for dehumidification |
RU2692180C1 (en) * | 2018-07-03 | 2019-06-21 | Акционерное общество "Группа Машиностроительных Заводов "Химмаш" | Indirect evaporative cooling method and device for its implementation |
CN110584237A (en) * | 2019-09-23 | 2019-12-20 | 中国人民解放军空军特色医学中心 | Air cooling source simulation equipment matched with ventilation suit |
US20210364173A1 (en) * | 2018-07-03 | 2021-11-25 | Akcionernoe Obshchestvo "Gruppa Mashinostroitel'nyh Zavodov "Himmash" | Method of indirect evaporative cooling of air and device for implementation thereof |
US20210381773A1 (en) * | 2018-09-17 | 2021-12-09 | Omius Inc. | Evaporative cooling system |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2948751A1 (en) | 2009-07-29 | 2011-02-04 | Aldes Aeraulique | CONTROLLED MECHANICAL VENTILATION INSTALLATION WITH DOUBLE FLOW OF A BUILDING |
FI20096397A0 (en) * | 2009-12-23 | 2009-12-23 | Enervent Oy Ab | VENTILATION DEVICE |
KR101036705B1 (en) * | 2010-08-26 | 2011-05-24 | 신상철 | A building ventilation system for using a carrying out device of the ground |
NL2006314C2 (en) * | 2010-12-24 | 2012-06-27 | Optimair Holding B V | SYSTEM FOR DRYING AND / OR COOLING A AIR FLOW. |
ES2668804T3 (en) * | 2011-04-08 | 2018-05-22 | Zehnder Group International Ag | Ventilation equipment |
EP2620715B1 (en) * | 2012-01-26 | 2014-01-22 | STIEBEL ELTRON GmbH & Co. KG | Method for operating a ventilation heating device and ventilation heating device |
EP2821727B1 (en) | 2013-07-05 | 2016-03-16 | Stiebel Eltron GmbH & Co. KG | Method for operating a ventilation heating device and ventilation heating device |
DE102017003355A1 (en) | 2017-04-06 | 2018-10-11 | Stiebel Eltron Gmbh & Co. Kg | heat pump system |
WO2019145024A1 (en) * | 2018-01-24 | 2019-08-01 | Luwa Air Engineering Ag | Air conditioning system and method based on evaporative heat transfer with air supersaturation |
EP4379282A1 (en) * | 2022-11-30 | 2024-06-05 | Vero Duco N.V. | Hybrid ventilation system and method for controlling such a ventilation system |
Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4407185A (en) * | 1982-02-23 | 1983-10-04 | Borg-Warner Corporation | Return air flow control for variable air volume system |
US5024263A (en) * | 1987-12-18 | 1991-06-18 | Ilmatera Oy | Method and apparatus for the control of air flows and pressures in air-conditioning |
US5179998A (en) * | 1992-01-24 | 1993-01-19 | Champs Nicholas H Des | Heat recovery ventilating dehumidifier |
US5800595A (en) * | 1994-08-30 | 1998-09-01 | William Allen Trusts Pty Ltd | Spaced evaporative wicks within an air cooler |
US6779735B1 (en) * | 2003-09-24 | 2004-08-24 | Onstott Richard S | Air ventilation control system |
US20050236136A1 (en) * | 2002-03-11 | 2005-10-27 | Level Holding B.V. | Heat recuperator with frost protection |
US7007740B2 (en) * | 2003-01-22 | 2006-03-07 | Nutech R. Hldgs Inc. | Adjustable flow heat recovery ventilator and method |
US20060086058A1 (en) * | 2002-04-26 | 2006-04-27 | Reinders Johannes Antonius M | Dewpoint cooler designed as a frame or part thereof |
US7231967B2 (en) * | 1994-01-31 | 2007-06-19 | Building Performance Equipment, Inc. | Ventilator system and method |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
NL8401778A (en) * | 1984-06-04 | 1986-01-02 | Vapochill Bv | DEW POINT COOLER. |
US5170633A (en) * | 1991-06-24 | 1992-12-15 | Amsted Industries Incorporated | Desiccant based air conditioning system |
JPH0712382A (en) * | 1993-06-22 | 1995-01-17 | Kubota Corp | Heat exchanger for ventilation |
JPH0861752A (en) * | 1994-08-18 | 1996-03-08 | Matsushita Electric Ind Co Ltd | Controller for ventilator |
US6006142A (en) * | 1997-07-14 | 1999-12-21 | Seem; John E. | Environmental control system and method |
US6176305B1 (en) * | 1998-11-09 | 2001-01-23 | Building Performance Equipment Inc. | Ventilator system and method |
NL1021812C1 (en) * | 2002-04-26 | 2003-10-28 | Oxycell Holding Bv | Dew point cooler. |
JP2004019966A (en) * | 2002-06-12 | 2004-01-22 | Toshiba Kyaria Kk | Ventilation equipment |
CH697104A5 (en) * | 2004-01-30 | 2008-04-30 | Polybloc Ag | A method of cooling a supply air flow for a room. |
-
2006
- 2006-01-09 GB GBGB0600274.5A patent/GB0600274D0/en not_active Ceased
-
2007
- 2007-01-08 TW TW096100625A patent/TW200732607A/en unknown
- 2007-01-09 MY MYPI20082533A patent/MY146212A/en unknown
- 2007-01-09 KR KR1020087019536A patent/KR20080104270A/en not_active Application Discontinuation
- 2007-01-09 CN CN2007800060087A patent/CN101384859B/en not_active Expired - Fee Related
- 2007-01-09 EP EP07703715A patent/EP1977171B1/en not_active Not-in-force
- 2007-01-09 US US12/160,316 patent/US20090075581A1/en not_active Abandoned
- 2007-01-09 WO PCT/EP2007/050164 patent/WO2007080162A2/en active Application Filing
- 2007-01-09 JP JP2008549022A patent/JP5175219B2/en not_active Expired - Fee Related
- 2007-01-09 BR BRPI0706453-5A patent/BRPI0706453A2/en not_active IP Right Cessation
- 2007-01-09 CA CA002646393A patent/CA2646393A1/en not_active Abandoned
- 2007-01-09 AT AT07703715T patent/ATE537411T1/en active
- 2007-01-09 RU RU2008132733/06A patent/RU2008132733A/en not_active Application Discontinuation
- 2007-01-09 AU AU2007204360A patent/AU2007204360A1/en not_active Abandoned
-
2008
- 2008-07-08 IL IL192704A patent/IL192704A0/en unknown
- 2008-07-21 ZA ZA200806324A patent/ZA200806324B/en unknown
Patent Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4407185A (en) * | 1982-02-23 | 1983-10-04 | Borg-Warner Corporation | Return air flow control for variable air volume system |
US5024263A (en) * | 1987-12-18 | 1991-06-18 | Ilmatera Oy | Method and apparatus for the control of air flows and pressures in air-conditioning |
US5179998A (en) * | 1992-01-24 | 1993-01-19 | Champs Nicholas H Des | Heat recovery ventilating dehumidifier |
US7231967B2 (en) * | 1994-01-31 | 2007-06-19 | Building Performance Equipment, Inc. | Ventilator system and method |
US5800595A (en) * | 1994-08-30 | 1998-09-01 | William Allen Trusts Pty Ltd | Spaced evaporative wicks within an air cooler |
US20050236136A1 (en) * | 2002-03-11 | 2005-10-27 | Level Holding B.V. | Heat recuperator with frost protection |
US20060086058A1 (en) * | 2002-04-26 | 2006-04-27 | Reinders Johannes Antonius M | Dewpoint cooler designed as a frame or part thereof |
US7007740B2 (en) * | 2003-01-22 | 2006-03-07 | Nutech R. Hldgs Inc. | Adjustable flow heat recovery ventilator and method |
US6779735B1 (en) * | 2003-09-24 | 2004-08-24 | Onstott Richard S | Air ventilation control system |
Cited By (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9518784B2 (en) | 2008-01-25 | 2016-12-13 | Alliance For Sustainable Energy, Llc | Indirect evaporative cooler using membrane-contained, liquid desiccant for dehumidification |
US20110269388A1 (en) * | 2009-01-18 | 2011-11-03 | Matthijs Dirk Meulenbelt | Cooling Device |
US9829207B2 (en) * | 2009-01-18 | 2017-11-28 | Lux Et Libertas B.V. | Cooling device |
US20120024000A1 (en) * | 2010-07-28 | 2012-02-02 | Lg Electronics Inc. | Ice making machine |
US20120260739A1 (en) * | 2011-04-13 | 2012-10-18 | Yang Seung Duk | Bidirectional wind pressure detecting apparatus |
US8667850B2 (en) * | 2011-04-13 | 2014-03-11 | Seung Duk YANG | Bidirectional wind pressure detecting apparatus |
US20130211600A1 (en) * | 2012-02-14 | 2013-08-15 | Honeywell International Inc. | Hvac controller with ventilation boost control |
US9804611B2 (en) * | 2012-02-14 | 2017-10-31 | Honeywell International Inc. | HVAC controller with ventilation boost control |
US9140460B2 (en) * | 2013-03-13 | 2015-09-22 | Alliance For Sustainable Energy, Llc | Control methods and systems for indirect evaporative coolers |
US9140471B2 (en) * | 2013-03-13 | 2015-09-22 | Alliance For Sustainable Energy, Llc | Indirect evaporative coolers with enhanced heat transfer |
US20140260398A1 (en) * | 2013-03-13 | 2014-09-18 | Alliance For Sustainable Energy, Llc | Indirect evaporative coolers with enhanced heat transfer |
US20140260372A1 (en) * | 2013-03-13 | 2014-09-18 | Alliance For Sustainable Energy, Llc | Control methods and systems for indirect evaporative coolers |
RU2692180C1 (en) * | 2018-07-03 | 2019-06-21 | Акционерное общество "Группа Машиностроительных Заводов "Химмаш" | Indirect evaporative cooling method and device for its implementation |
WO2020009598A1 (en) * | 2018-07-03 | 2020-01-09 | Акционерное общество "Группа Машиностроительных Заводов "Химмаш" | Method of indirect evaporative cooling of air and device for implementation thereof |
US20210364173A1 (en) * | 2018-07-03 | 2021-11-25 | Akcionernoe Obshchestvo "Gruppa Mashinostroitel'nyh Zavodov "Himmash" | Method of indirect evaporative cooling of air and device for implementation thereof |
US20210381773A1 (en) * | 2018-09-17 | 2021-12-09 | Omius Inc. | Evaporative cooling system |
CN110584237A (en) * | 2019-09-23 | 2019-12-20 | 中国人民解放军空军特色医学中心 | Air cooling source simulation equipment matched with ventilation suit |
Also Published As
Publication number | Publication date |
---|---|
EP1977171B1 (en) | 2011-12-14 |
AU2007204360A1 (en) | 2007-07-19 |
RU2008132733A (en) | 2010-02-20 |
CN101384859A (en) | 2009-03-11 |
WO2007080162A2 (en) | 2007-07-19 |
JP2009522536A (en) | 2009-06-11 |
CN101384859B (en) | 2011-11-23 |
EP1977171A2 (en) | 2008-10-08 |
IL192704A0 (en) | 2009-02-11 |
GB0600274D0 (en) | 2006-02-15 |
CA2646393A1 (en) | 2007-07-19 |
KR20080104270A (en) | 2008-12-02 |
MY146212A (en) | 2012-07-31 |
BRPI0706453A2 (en) | 2011-03-29 |
JP5175219B2 (en) | 2013-04-03 |
ZA200806324B (en) | 2009-05-27 |
ATE537411T1 (en) | 2011-12-15 |
WO2007080162A3 (en) | 2007-08-30 |
TW200732607A (en) | 2007-09-01 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US20090075581A1 (en) | Cooling and ventilation device | |
US6176305B1 (en) | Ventilator system and method | |
EP2274557B1 (en) | Combined heat exchange unit | |
KR102641608B1 (en) | Rooftop liquid desiccant systems and methods | |
JP5925004B2 (en) | Air conditioning ventilation system | |
JP4207166B2 (en) | Dehumidifying air conditioner | |
US4841733A (en) | Dri-Pc humidity and temperature controller | |
US7093452B2 (en) | Air conditioner | |
KR100463550B1 (en) | cooling and heating system | |
JP4816251B2 (en) | Air conditioner and building | |
KR101825873B1 (en) | Heat pipe air conditioning plant using by-pass | |
JP2008506090A (en) | Heat exchanger | |
JP2008545113A (en) | Device and method for humidifying air flow | |
GB2540139B (en) | Combined ventilation, cooling and humidification system and method | |
JP3942820B2 (en) | Humidification method for air conditioning | |
US6523359B1 (en) | Environmental control device | |
JP3614775B2 (en) | Heat pump air conditioner | |
CN111750461B (en) | Air conditioning system | |
JP4816252B2 (en) | Air conditioner and building | |
KR101563696B1 (en) | Humidifying and Ventilating Apparatus | |
JP4816253B2 (en) | Air conditioner and building | |
JP2021018000A (en) | Separately installed air conditioning system | |
JP2005283036A (en) | Heat pump type air conditioner |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: OXYCOM BEHEER B.V., NETHERLANDS Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:VAN HEESWIJK, FREDERIK SIMON, MR.;NIJSEN, ANDREAS JACOBUS LOUIS, MR.;REEL/FRAME:021534/0402;SIGNING DATES FROM 20080901 TO 20080908 |
|
AS | Assignment |
Owner name: HEEMAK B.V., NETHERLANDS Free format text: SECURITY AGREEMENT;ASSIGNOR:OXYCOM BEHEER B.V.;REEL/FRAME:023421/0089 Effective date: 20090408 |
|
AS | Assignment |
Owner name: HEEMAK B.V., NETHERLANDS Free format text: SECURITY AGREEMENT;ASSIGNOR:OXYCOM BEHEER B.V.;REEL/FRAME:023499/0850 Effective date: 20071012 Owner name: HEEMAK B.V., NETHERLANDS Free format text: SECURITY AGREEMENT;ASSIGNOR:OXYCOM BEHEER B.V.;REEL/FRAME:023499/0826 Effective date: 20071012 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |