EP2430372A1 - Appareil et systèmes pour réguler la température de l'air intérieur - Google Patents

Appareil et systèmes pour réguler la température de l'air intérieur

Info

Publication number
EP2430372A1
EP2430372A1 EP10769193A EP10769193A EP2430372A1 EP 2430372 A1 EP2430372 A1 EP 2430372A1 EP 10769193 A EP10769193 A EP 10769193A EP 10769193 A EP10769193 A EP 10769193A EP 2430372 A1 EP2430372 A1 EP 2430372A1
Authority
EP
European Patent Office
Prior art keywords
air
housing
fan
height
top end
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.)
Withdrawn
Application number
EP10769193A
Other languages
German (de)
English (en)
Inventor
Mark Clawsey
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP2430372A1 publication Critical patent/EP2430372A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F7/00—Ventilation
    • F24F7/04—Ventilation with ducting systems, e.g. by double walls; with natural circulation
    • F24F7/06—Ventilation with ducting systems, e.g. by double walls; with natural circulation with forced air circulation, e.g. by fan positioning of a ventilator in or against a conduit
    • F24F7/065—Ventilation with ducting systems, e.g. by double walls; with natural circulation with forced air circulation, e.g. by fan positioning of a ventilator in or against a conduit fan combined with single duct; mounting arrangements of a fan in a duct
    • 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
    • F24F11/46—Improving electric energy efficiency or saving
    • 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
    • F24F11/50—Control or safety arrangements characterised by user interfaces or communication
    • F24F11/52—Indication arrangements, e.g. displays
    • 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
    • F24F11/50—Control or safety arrangements characterised by user interfaces or communication
    • F24F11/56—Remote control
    • 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
    • F24F11/72—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure
    • F24F11/74—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity
    • F24F11/76—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity by means responsive to temperature, e.g. bimetal springs
    • 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
    • F24F11/72—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure
    • F24F11/74—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity
    • F24F11/77—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity by controlling the speed of ventilators
    • 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
    • F24F11/88—Electrical aspects, e.g. circuits
    • 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
    • F24F2110/00—Control inputs relating to air properties
    • F24F2110/10—Temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2221/00—Details or features not otherwise provided for
    • F24F2221/12—Details or features not otherwise provided for transportable
    • F24F2221/125—Details or features not otherwise provided for transportable mounted on wheels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F8/00—Treatment, e.g. purification, of air supplied to human living or working spaces otherwise than by heating, cooling, humidifying or drying
    • F24F8/10—Treatment, e.g. purification, of air supplied to human living or working spaces otherwise than by heating, cooling, humidifying or drying by separation, e.g. by filtering
    • F24F8/108—Treatment, e.g. purification, of air supplied to human living or working spaces otherwise than by heating, cooling, humidifying or drying by separation, e.g. by filtering using dry filter elements
    • 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
    • Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
    • Y02A50/00—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE in human health protection, e.g. against extreme weather
    • Y02A50/20—Air quality improvement or preservation, e.g. vehicle emission control or emission reduction by using catalytic converters

Definitions

  • the embodiments herein relate in general to apparatus and systems for air distribution and circulation, and in particular, to ductless apparatus and systems for circulating high volumes of low velocity air to regulate indoor air temperature.
  • HVAC Heating, ventilation and air conditioning
  • a fan assembly is housed in a unitary duct-like housing, which is open near its base to take in air.
  • the duct-like housing is capped with an outlet hood, which adjustably telescopes on the housing so that air flow from openings in the outlet hood can be adjusted for winter or summer operation.
  • Rampe discloses an apparatus for ductlessly circulating large volumes of air in industrial facilities and the like.
  • the apparatus includes an upstanding structure, which defines a vertically extending chamber. Openings are provided in lower and upper portions of the structure and communicate the chamber with lower and upper strata of ambient air.
  • a blower assembly is housed within the structure intermediate the lower and upper openings. According to Rampe, in operation the apparatus is positioned substantially centrally in a room and the blower assembly is energized to move air upwardly through the chamber.
  • the lower and upper openings are arranged such that air from the lower strata is drawn substantially radially toward the lower openings, and such that air discharging from the upper openings into the upper strata moves substantially radially outwardly toward walls of the room.
  • the effect of this type of operation is to establish a primary substantially toroidal air flow circulation beside the apparatus, and to induce the establishment of a secondary substantially toroidal air flow circulation above the apparatus.
  • These primary and secondary circulation torri promote a thorough intermixing of air from all parts of the room and promote temperature uniformity throughout the room.
  • a ductless air distribution system for amplifying and/or manipulating high volumes of low velocity air in order to circulate and regulate indoor air temperature.
  • a portable or permanent ductless air distribution system for amplifying and/or manipulating high volumes of low velocity air in order to circulate and regulate indoor air temperature within a commercial or industrial environment using one or more natural air streams.
  • the system includes a support member and a housing having a top end and a bottom end.
  • the system further includes a fan assembly mounted above the bottom end and below the top end of the housing.
  • An air intake may be positioned across the bottom end of the housing.
  • An air outlet may be positioned across the top end of the housing and may incorporate a self-regulating control system.
  • the support member supports the housing above the ground so that the air intake may be - A -
  • the system may be used in both the winter and summer. In some cases the system may change the air within an industrial environment two to four times every hour. Furthermore, the system may be sized and configured to operate such that the temperature differential between the ceiling and the ground may be within one to two degrees Fahrenheit during use.
  • Some embodiments as described herein relate to systems and methods for controlling environmental parameters within an indoor environment using methods of forced mechanical convection to induce, amplify and/or manipulate the effects of natural convection phenomena, including at least one of the air de-lamination phenomena and the Coanda effect, to provide generally complete air distribution, circulation, de- stratification, and mixing of air within an indoor environment.
  • some advantages provided by the systems and apparatus as described herein may include equalization of the temperature throughout an industrial or commercial environment (e.g. between the ceiling and ground level), elimination of hot and cold spots (e.g. for improving comfort), elimination of drafts from ceiling fans, improved air quality, reduction in energy consumption, and self-regulation.
  • an apparatus for circulating air includes a housing having an airflow passageway with a bottom end defining an air intake and a top end defining an air outlet, and a support member for supporting the housing and for disposing the air intake above a support surface.
  • the apparatus also includes a fan positioned within the airflow passageway of the housing substantially adjacent to the top end of the housing, and a drive coupled to the fan for operating the fan so as to blow air from the air intake to the air outlet.
  • the fan and the air outlet may be configured such that the air exiting the air outlet has a flow direction with a significant vertical component and a significant lateral component.
  • the vertical component may be between about 40% to 80% of the total airflow, and the lateral component may be between about 60% to 20% of the total flow. In some embodiments, the vertical component may be about 60% of the total airflow, and the lateral component may be about 40% of the total airflow.
  • a first height may be defined between the fan and the top end of the housing, and a second height may be defined between the bottom end of the housing and the top end of the housing.
  • the first height may be less than half of the second height.
  • the first height may be less than one third of the second height.
  • the first height may be about one tenth of the second height.
  • the fan may be positioned between about 0 inches and about
  • the apparatus may include at least one air filter for filtering air passing through the airflow passageway of the housing.
  • the air filter may be positioned at least 20 inches below the fan.
  • a second height may be defined between the bottom end of the housing and the top end of the housing, and a third height may be defined between the at least one filter and the fan.
  • the third height may be more than about half of the second height.
  • the third height may be more than about two thirds of the second height.
  • the at least one air filter may have a rectangular shape.
  • the at least one air filter may define a filtration surface area.
  • the airflow passageway of the housing may have a cross- sectional area less than the filtration surface area.
  • the apparatus includes a housing having an airflow passageway with a bottom end defining an air intake and a top end defining an air outlet, and a support member for supporting the housing and for disposing the air intake above a support surface.
  • the apparatus also includes a fan positioned within the airflow passageway of the housing, and a drive coupled to the fan for operating the fan so as to blow air from the air intake to the air outlet.
  • the fan and the air outlet are configured such that the air exiting the air outlet has a flow direction with a significant vertical component and a significant lateral component.
  • the fan may be positioned substantially adjacent to the top end of the housing.
  • the system comprises an air circulator including a housing having airflow passageway with a bottom end defining an air intake and a top end defining an air outlet, and a support member for supporting the housing and for disposing the air intake above a support surface.
  • the air circulator also includes a fan positioned within the airflow passageway of the housing, and a drive coupled to the fan for operating the fan so as to blow air from the air intake to the air outlet.
  • the system also comprises a first temperature sensor for measuring air temperature in a lower portion of a building, and a second temperature sensor for measuring air temperature in an upper portion of the building.
  • the system comprises a controller for determining a temperature differential based on measurements from the first and second temperature sensors. The controller operates the fan based on the temperature differential.
  • the controller may adjust a fan speed for the fan based on the temperature differential. Furthermore, the controller may output an AC electrical signal having a frequency for operating the fan, and wherein the controller adjusts the frequency to control the fan speed.
  • the AC electrical signal output by the controller may have a substantially constant voltage.
  • the fan may be positioned substantially adjacent to the top end of the housing.
  • Figure 1 is a perspective view of an air circulator according to one embodiment
  • Figure 2 is a cross-sectional view of the air circulator of Figure 1 taken along line 2-2;
  • Figure 3 is a schematic diagram of an airflow pattern generated by the air circulator of Figure 1 within an indoor environment
  • Figure 4 is a schematic diagram of an airflow pattern generated by a prior art air circulator within the same indoor environment as in Figure 3;
  • Figure 5 is a schematic diagram of a system for circulating air within a building according to another embodiment
  • Figure 6 is a perspective view of an air circulator according to yet another embodiment.
  • Figure 7 is a cross sectional view of the air circulator of Figure 6 taken along line 7-7.
  • De-lamination is a phenomenon whereby warm airflows and cool airflows tend to repel one another. For example, an upper layer of warm air will tend to float on top of a lower layer of cool air, generally without mixing between the layers.
  • the upper and lower layers may be referred to as "stratified layers" having stratified layer "heights”.
  • De-lamination is a result of different air temperatures, densities and turbulence intensity between cool and warm airflows, and generally results in energy waste and/or reduced efficiencies within an HVAC system.
  • the stratified layer height (e.g. the height of each layer) might be about 1.4 meters. However, if the airflow velocity is increased to about 1.6 m/s in the same environment, the stratified layer height may reduce to about 0.7 meters. Furthermore, as the airflow velocity increases beyond about 2.0 m/s, the stratified layer height will tend to decrease further, and may in fact approach zero.
  • the stratified layer height also tends to decrease. For example, if an airflow velocity of 1.2 m/s and a temperature differential of about 3O 0 F might correspond to a stratified layer height of about 1.4 meters, while if the temperature differential between the hot and cold layers was 1O 0 F, the stratified layer height might approach zero. [0041] When the stratified layer height is larger, this tends to promote repelling of hot and cold layers (e.g. mixing of the layers of hot and cold air is inhibited). Conversely, when the stratified layer height is smaller, this tends to promote mixing between the hot and cold layers. Accordingly, it has been discovered that controlling airflow velocity can influence whether hot and cold layers of air tend to repel each other, or whether the layers of air tend to mix with each other.
  • the Coanda effect is the tendency of a moving fluid jet to stay attached to an adjacent or nearby surface.
  • air-conditioning systems may exploit the Coanda effect to increase the distance traveled by cool air using a ceiling-mounted diffuser.
  • a ceiling-mounted diffuser may take advantage of the Coanda effect by discharging air near the ceiling. The discharged air will tend to "stick" to the ceiling while traveling away from the diffuser. Accordingly, the cool air may travel further along the ceiling before tending to drop down towards the ground (in comparison to mounting the diffuser in free air without the neighboring ceiling, where the cooled air will tend to fall more quickly).
  • apparatus and systems for circulating air as described herein may attempt to use at least one of the de-lamination phenomenon and the Coanda effect.
  • the air circulator 20 generally includes a housing 22 and a support member 30 for supporting the housing 22 above a ground surface (e.g. the floor of a building).
  • the housing 22 generally has a bottom end 24, a top end 26, and an airflow passageway 28 located therebetween (as shown in Figure 2).
  • the bottom end 24 defines an air intake, while the top end 26 defines an air outlet.
  • the air circulator 20 also includes a fan 32 and a drive 34.
  • the fan 32 is mounted in the airflow passageway 28 of the housing 22 between the bottom end 24 and the top end 26, and generally adjacent the top end 26.
  • the drive 34 is coupled to the fan 32 for rotating the fan 32 so as to blow air through the airflow passageway 28 from the air intake (at the bottom end 24) to the air outlet (at the top end 26).
  • the drive 34 may be an electric motor having an output shaft 36 coupled to a central hub of the fan 32.
  • the drive 34 may have different configurations, for example, the drive 34 may be coupled to the fan 32 using pulleys (for example as shown in Figure 7).
  • the fan 32 and drive 34 enable the air circulator 20 to amplify and manipulate high volumes of low velocity air in order to circulate and regulate indoor air temperature, for example within a commercial or industrial environment.
  • the fan 32 and the air outlet are generally configured to discharge an airflow from the air outlet having both a significant vertical component and a significant lateral component.
  • the air circulator 20 blows air both vertically upwards and laterally outwards relative to the top end 26 of the housing 22. This configuration tends to promote air circulation and mixing of the warm and cool layers of air, as will be described below.
  • the housing 22 may include a plurality of side panels 38 (e.g. four panels as shown in the illustrated embodiment), which may be metal, plastic or another suitable material.
  • the panels 38 may be sized and shaped so that the housing 22 has a box-like shape.
  • the housing 22 may be shaped as a vertically oriented square tube, with the airflow passageway 28 extending generally vertically through the center of the tube.
  • the support member 30 generally supports the housing 22 above the support surface (e.g. a floor within a commercial or industrial building) so that the air intake is positioned at least partially within in the natural air stream generated by the air circulator 20 (as shown in Figure 3).
  • the support surface e.g. a floor within a commercial or industrial building
  • the support member 30 may include a plurality of leg members
  • leg members 40 sized and shaped to allow air to flow into the air intake.
  • the leg members 40 and cross-members 42 are sized and shaped so as to not inhibit airflow into the air intake.
  • one or more of the leg members 40 may be supported by caster wheels 44, which may allow the air circulator 20 to be moved by rolling the air circulator 20 along the ground surface (e.g. to different locations within an industrial building).
  • the support member 30 may be fixed to the ground surface.
  • the support member 30 may include leg members 40 that are bolted to the ground surface.
  • the air intake encompasses the entire bottom end 24 of the housing 22, and the air outlet encompasses the entire top end 26 of the housing 22.
  • the air intake and air outlet may encompass less than the entire bottom end 24 and top end 26, respectively, of the housing 22.
  • the housing 22 may include a lower protective grill 50 and an upper protective grill 52.
  • the grills 50, 52 generally have one or more openings that are sized and shaped to allow airflow to pass therethrough, but which prevent undesired objects, such as hands or fingers, from entering the airflow passageway 28.
  • the grills 50, 52 may be designed to minimally impede the airflow through the air intake and the air outlet.
  • one or both of the grills 50, 52 may be removably coupled to the housing 22.
  • the removable upper grill 52 is located as close as possible to the fan 32.
  • the fan 32 and the air outlet are generally configured such that air exiting the air outlet has a flow direction with both a significant vertical component and a significant lateral component. In some embodiments, this may be achieved by positioning the fan 32 substantially adjacent to the air outlet (i.e. adjacent the top end 26 of the housing 22).
  • the fan 32 may be separated from the top end 26 by a distance corresponding to a first height H1 as shown in Figure 2.
  • the first height H1 may be between about 0 inches and about 10 inches.
  • the first height H1 might be between 2 inches and 8 inches.
  • the first height H1 may be about 4 inches.
  • the distance between the bottom end 24 and the top end 26 may define a second height H2.
  • the first height H1 may be defined relative to the second height H2.
  • the first height H1 may be less than half of the second height H2.
  • the first height H1 may be less than one third of the second height H2.
  • the first height H1 may be about one tenth of the second height H2.
  • the top end 26 of the housing 22 may include a guide 54, such as a shroud or a panel with a cylindrical cut-out.
  • the guide 54 may at least partially encase the fan 32 and direct airflow from the fan 32 out of top end 26 through the air outlet (and may assist in imparting one or both of the significant vertical component and significant lateral component to the airflow).
  • the guide 54 may deflect air traveling upwards through the airflow passageway 28 to inhibit the discharged air from traveling substantially laterally at a certain height above the ground surface (e.g. at a height corresponding to the occupant head height), and to project a substantial column of air vertically towards the ceiling.
  • This configuration may provide comfort to occupants standing near the air circulator 20 (e.g. by deflecting air leaving the air circulator 20 so that it does not directly strike the occupants).
  • This configuration may also promote air circulation using the de- lamination phenomenon and the Coanda effect.
  • the guide 54 may be generally circular and may be sized slightly larger than the diameter of the fan 32. In some embodiments, the guide 54 may be up to about 2 inches larger than the diameter of the fan.
  • Figure 3 illustrates a simulated airflow induced by the air circulator 20 described herein, which discharges an airflow having both a significant vertical component and a significant horizontal component.
  • Figure 4 illustrates a simulated airflow induced by a prior art air circulator having a significant vertical component but no significant horizontal component.
  • the air circulator 20 may provide a vertical component that is between about 40% to 80% of the total airflow, and a lateral component that is between about 60% to 20% of the total airflow.
  • the vertical component may be about 60% of the total airflow and the lateral component may be about 40% of the total airflow.
  • Providing an airflow having both a significant vertical component and a significant horizontal component may tend to promote air circulation over a wider area, which tends to promote de-stratification of the surrounding air and a reduction in temperature differentials within an indoor environment.
  • the air circulator 20 can take advantage of at least one of the de- lamination phenomenon and the Coanda effect.
  • the lateral component of the discharged airflow tends to have a lower temperature in comparison to adjacent air because the air circulator 20 takes cooler air near the floor and blows it into warmer air that is located higher up above the floor.
  • the discharge airflow has a sufficiently low velocity to avoid de-stratification for a given temperature differential between the cool air and warm air
  • the cool air and the warm air tend to repel each other such that one floats on the other with limited heat and mass transfer therebetween. Since the cool and warm air repel each other, the cool airflow tends to travel further laterally outward before mixing with the warm air (thus extending the effective mixing range of the air circulator 20).
  • the present air circulator 20 takes advantage of the repelling effect between warm and cool airflows and enables discharged air to travel further laterally outwards from the air circulator 20 and cover a substantially broader lateral area.
  • the vertical component of the airflow is generally configured to impinge the ceiling such that the airflow spreads out laterally along the ceiling. Due to the Coanda effect, this component of the discharged airflow tends to stay attached to, or at least adjacent to, the ceiling and thus tends to spread out laterally further from the vertical component of the airflow before falling down and mixing with the warmer air below.
  • the outward spreading along the ceiling is further enhanced by the de-lamination phenomenon, since the discharged airflow that moves along the ceiling is cooler than the warmer air it replaced. Accordingly, the cooler discharged air tends to repel the warmer air in the same way as described previously so as to increase the lateral distance traveled along the ceiling by the cooler air.
  • the combined effect of the significant vertical component and the significant horizontal component means the discharged airflow tends to spread out over greater lateral distances in comparison to prior art systems. Accordingly, the air circulator 20 tends to promote de-stratification over a wider interior space in comparison to known prior art air circulators.
  • Another benefit of the present air circulator 20 is that the air discharged generally does not require ducting. Ducting tends to be costly to ship and install and also introduces frictional losses due to interactions between the airflow and the interior surfaces of the ducting (and which tend to increase the power requirements for circulating air).
  • the air circulator 20 also utilizes the Coanda effect at the air intake of the housing 22. For example, air discharged from the air circulator 20 eventually pushes warmer air downward toward a lower portion of the indoor environment (e.g. towards the floor). The air circulator 20 then draws this air in through the air inlet at the bottom end 24, which tends to induce an air current that travels across the floor. This air current along the floor tends to stay attached to the floor (according to the Coanda effect).
  • the air circulator 20 works to gently pull cool air across the floor.
  • the air circulator 20 may pull air from over two hundred feet away. Discharged air is propelled upward and outward across the upper level (e.g. ceiling). At the same time, drawing cool air from the floor into the air circulator 20 creates a low-pressure layer, which pulls the warmer air near the ceiling back down to the ground.
  • the air circulator 20 tends to create a natural rolling airflow pattern, which mixes the cool air with the warm air and reduces the temperature gradient within the building. [0079] Furthermore, placing the air circulator 20 within this natural rolling air stream and exposing the air stream to at least a portion of the air intake at the bottom end 24 of the air circulator 20 tends to increase the efficiency of the air circulator 20, which enables the air circulator 20 to de- stratify the air and reduce temperature gradients faster. As a result, the air circulator 20 tends to quickly de-stratify the air and equalize the temperature differential within a few degrees Fahrenheit.
  • the air circulator 20 can equalize temperatures within a building during both the summer and winter.
  • the warm air from the building heating system tends to collect at the top of a building (e.g. in an atrium).
  • the air circulator 20 can bring this warm air down to floor level or occupant level.
  • the cool air or conditioned air may have difficulty reaching the top portion of an atrium because it tends to settle at the bottom of the building near the floor.
  • the air circulator 20 can distribute the cool air that is collected near the floor back up to the top. Accordingly, the air circulator 20 may be used to maintain overall improved comfort levels in operation during both summer and winter seasons.
  • the air circulator 20 can increase the overall efficiency of existing HVAC systems by 20% or more.
  • the air circulator 20 may also reduce the short cycling on/off of the existing HVAC rooftop units and unit heaters (e.g. by stabilizing the on and off cycles). Accordingly, the air circulator 20 may reduce electrical power consumption and may allow a building to downsize HVAC rooftop blower motors, which may result in energy savings.
  • the air circulator 20 may be used to replace ceiling fans.
  • the present air circulator 20 may also have the ability to capture and distribute latent heat produced by manufacturing equipment, which can further enhance efficiencies. For example, the natural rolling airflow that passes along the floor tends to pick up heat generated by manufacturing equipment. This heat capture ability can reduce operator fatigue by sweeping the heat from their work areas and generally equalizing temperatures throughout an indoor work environment.
  • the air circulator 20 may also reduce heat losses through the ceiling and walls of a building. For example, heat losses occur when warm air within the building transfers heat to the cooler air outside the building through the walls and ceiling. These heat losses tend to increase as the temperature differential between the inside air and the outside air increases.
  • the air circulator described herein circulates air within the building and inhibits the formation of a stratified layer of warm air by mixing it with cooler air closer to the floor. Accordingly, the air circulator may reduce the air temperature near the ceiling, which may reduce both the temperature differential and heat losses.
  • the height of the air intake above the ground can be important because it sets the height at which incoming air is drawn into the fluid passageway 28. For example, when the height of the air intake is lowered, incoming air is drawn from a lower height, which generally corresponds to cooler air. Drawing in cooler air tends to provide more efficient air circulation and de-stratification because it tends to utilize the maximum (or at least a significant) temperature differential between the air near the ground and the air near the ceiling. However, the air intake should be set above the ground some minimum height, otherwise static pressure increases and tends to reduces the efficiency of the air circulator 20.
  • the height of the air intake above the ground corresponds to a clearance height C.
  • the clearance height C of the air intake may be between one foot and four feet above the ground.
  • the clearance height C of the air intake above the ground may be about two feet.
  • Setting the air intake height to about two feet may be useful when using the air circulator 20 near a loading dock door area. For example, air above the two-foot level tends to remain at the existing temperature set point for the HVAC system (e.g. 70 degrees Fahrenheit or some other set point).
  • the air circulator 20 tends to force the air from outside the loading dock door to remain below the two-foot level. Accordingly, in the winter, loading dockworkers will tend not to feel the cold air from outside the loading dock because it is kept at a low height.
  • the air circulator 20 can reduce the heat recovery time for that area. For example, in some cases, the temperature of the area may be brought back up to the desired temperature within minutes by circulating air in the loading dock area with air throughout the rest of the building.
  • the air circulator 20 may include an outlet adjustment mechanism for adjusting the size of the air outlet.
  • the outlet adjustment mechanism may increase or decrease the radius of the circular guide 54. Adjusting the size of the air outlet enables the air circulator 20 to alter the vertical and/or lateral components of the airflow, for example, to manipulate the de-lamination phenomenon and/or the Coanda effect depending on the particular configuration of the building, or the air temperatures within the building.
  • the outlet adjustment mechanism may adjust the size of the air outlet between a first size and a second size, with the second size being smaller than the first size.
  • the larger first size allows the fan to blow more air laterally outward relative to the housing 22 in comparison to the second size. Accordingly, the larger first size may utilize the de-lamination phenomenon to a greater extent.
  • the smaller second size may allow the fan to blow more air upward relative to the housing in comparison to the first size. Accordingly, the smaller second size may utilize the Coanda effect to a greater extent.
  • Adjusting the size of the air outlet may be beneficial when dealing with varying ceiling heights. If the ceiling height is low in relation to the discharge of the air circulator 20, the radius of the guide 54 could be increased to allow for more lateral airflow.
  • the adjustment mechanism may include louvers
  • the louvers could be positioned to direct airflow around the obstacle. An example of this would be when the air circulator 20 is located within proximity to an interior partition or wall and the louvers could direct airflow around the wall.
  • the louvers could also be used to adjust the vertical and lateral components of the airflow.
  • each upper grill 52 could provide a different diffusion pattern for the discharged air, which may be used to alter or manipulate the de-lamination phenomenon and/or Coanda effect.
  • the air circulator 20 may include a different diffusion pattern for summer and winter applications (e.g. the summer diffuser could take advantage of the Coanda Effect in an effort to distribute the cooler air-conditioned air over a larger area by keeping the cooler air attached or adjacent to the ceiling plane).
  • the air circulator 20 might also reduce the actual volume of air being serviced by effectively decreasing the size of the building such that warm air near the ceiling remains un-serviced during the summer months. This may be desirable because servicing the warmer air near the ceiling might actually increase the load on the air conditioning unit.
  • the air circulator 20 uses a 36-inch diameter fan 32.
  • any size fan 32 will work depending on the size of the area being serviced. For example, in a large area a large fan (or multiple fans) can be used, while in a small area the fan size can be reduced.
  • the housing 22 for the fan 32 may be a few inches larger than the diameter of the fan 32.
  • the air circulator 20 may be effective in a space that is about 10,000 square feet or more.
  • an air circulator 20 with a 36-inch fan 32 may work effectively within a 10,000 square foot building having a twenty foot high ceiling such that air changes occur two to four times per hour.
  • the air circulator 20 may work well in a 10,000 square foot building, the air circulator 20 may be effective in a variety of different building sizes (e.g. larger than 10,000 square feet, smaller than 10,000 square feet, and so on). In some embodiments, multiple air circulators 20 can be used in larger spaces.
  • a plurality of smaller air circulators can be used to replace one large air circulator, or visa versa.
  • the number and size of air circulators utilized may depend upon desired aesthetics, fan noise levels, floor space, and the size of fan that can be used within a predetermined amount of space.
  • the sizing calculation is based on the total volume of air within a space divided by the flow rate (e.g. cubic feet per hour) that the air circulator can move. The calculation determines the time it takes the air circulator to theoretically service all of the air within the space.
  • a similar sizing calculation utilizes the flow rate divided by the volume of air within the space so as to determine the theoretical number of air changes per hour within the building.
  • the amount of air circulation may change between summer and winter operation.
  • the winter it might be desirable to lower the number of air changes per hour and corresponding air velocity in an effort to reduce the chilling effect and increase occupant comfort. Accordingly, the sizing calculation may take into account the air changes per hour desired for both summer and winter operation.
  • the air circulator 20 may include a self- regulator or controller 70 for controlling the air circulator 20.
  • the controller 70 may be operatively coupled to the drive 34 for controlling the speed of the fan 32.
  • the controller 70 may provide electrical power to the drive 34 through a cable 72 and may adjust the amount of power supplied to control the speed of the fan 32.
  • the controller 70 may receive electrical power from a source such as a 120V wall socket through a plug 74 on the outside of the housing 22 as shown in Figure 1.
  • the controller 70 may control other aspects of the air circulator 20, such as the air outlet adjustment mechanism.
  • the controller 70 may include a touch screen 76 for adjusting parameters.
  • the touch screen 76 may enable a user to select the desired temperature for the indoor environment.
  • the touch screen 76 may allow the user to select other parameters such as the fan speed or the horizontal or vertical components of the discharge airflow.
  • the user may select these setting using one of several presets. In generally, these parameters can help the user regulate the temperature throughout the indoor environment.
  • FIG. 5 illustrated therein is an air circulation system 100 made in accordance with another embodiment.
  • the system 100 is generally used to circulate air within an indoor environment such as a building 102, which may be a commercial building or an industrial building.
  • the system 100 includes an air circulator 120, which may be similar to the air circulator 20 described previously, and similar elements are given similar reference numerals incremented by one hundred.
  • the air circulator 120 includes a housing 122, a support 130, a fan 132 and a drive 134.
  • the system 100 also includes two temperatures sensors 160, 162 and a controller 170 in communication with the temperature sensors 160, 162.
  • the first temperature sensor 160 is for measuring a first air temperature T1 in a lower portion of the building 102
  • the second temperature sensor 162 is for measuring a second air temperature T2 in an upper portion of the building 102.
  • the controller 170 controls the air circulator 120 based on the first and second temperatures T1 and T2.
  • the controller 170 may be similar to the controller 70 described previously.
  • the controller 170 may be part of the air circulator 120.
  • the controller 170 may be located separately from the air circulator 120.
  • the controller 170 may control multiple air circulators and the controller 170 may be in remote communication with each of the air circulators.
  • Operation of the system 100 commences by detecting a first air temperature T1 from the first temperature sensor 160 near the ground level of the building 102 and detecting a second air temperature T2 from the second temperature sensor 162 near the ceiling of the building 102.
  • the controller 164 calculates a temperature differentia! based on the first and second temperatures T1 and T2, and then operates the air circulator 120 based on the calculated temperature differential. For example, if the temperature differential is above a threshold value, which indicates the air within the building is stratified, the controller 170 might turn on the air circulator 120 by sending a signal to the drive 134.
  • the controller 170 may continue monitoring the temperature differential so that once the temperature differential is below a threshold value, the controller turns off the air circulator 120.
  • the controller 170 may operate other aspects of the air circulator 120 based on the temperature differential. For example, the controller 170 may adjust the speed of the fan 132 based on the temperature differential. For example, if the temperature differential is high, the controller 164 may operate the drive 134 at a higher speed. If the temperature differential is low, the controller 164 may operate the drive 134 at a lower speed. In some embodiments, the controller 64 may operate the drive 134 at one of several preset speeds. In other embodiments, the controller 164 may operate the drive 134 using an analogue type signal that allows a continuous range of speeds, as will be described below.
  • the controller 164 may also adjust the operating speed of the drive 134 based on other events. For example, if there is a change in the indoor environment such as a door opening, the controller 164 may increase the speed of the drive 134, for example, up to full speed. When the door closes, the controller 164 may decrease the speed back down to the previous speed.
  • the controller 170 may also control the outlet adjustment mechanism or other aspects of the air circulator 120 so as to adjust the vertical and lateral components of the airflow discharged from the air circulator 120.
  • the system 100 may control the speed of the fan 132 by adjusting the frequency of a signal sent to the drive 134.
  • the controller 170 may receive a 120VAC two-phase signal and convert it to a three-phase AC signal that is output to the drive 134.
  • the controller 164 may use the three-phase AC signal to control the speed of the drive 134 by adjusting the frequency of the three-phase AC signal. This method of control may have advantages over the prior art.
  • Prior art systems tend to control the speed of the drive by adjusting the voltage using a rheostat, which has numerous drawbacks.
  • the rheostat in these systems often produces a noticeable motor hum, in part, due to the size of the drive (e.g. motor) required to produce the optimal amount of air-changes-per-hour.
  • utilizing the system 100 described above to adjust fan speed based on frequency tends to reduce motor hum and noise and allows the user to tune the system 100 (e.g. by adjusting fan speed) for a specific application or building environment.
  • the self-regulating control system 100 may continue operating even after an industrial or a commercial facility is de- stratified, for example, such that the fan 132 operates at a reduced speed. Operating the fan 132 at reduced speed can help maintain de-stratification within the building, for example, to within a temperature differential of about 1 0 F to 2 0 F for some buildings. Once the air current is induced in a building, it is easy to maintain using discharged air with less velocity.
  • the system 100 may adjust the fan speed for other purposes.
  • the system 100 can to be tuned to meet the desired effects for occupants.
  • An example would be to vary the fan speed between summer and winter to produce a wind chill effect induced by higher speed air currents. By speeding the current up in the summer it allows for an occupant to perceive the temperature as being cooler than it actually is, for example, by as much as three or more degrees Fahrenheit. In the winter, the current speed can be reduced to reduce the wind chill effect so as to increase the perceived temperature felt by occupants.
  • the system 100 may also turn the air circulator 120 off during the night when the space is un-occupied.
  • Another reason for adjusting the fan speed is to create "vertical air curtains" at loading bay doors. For example, during the winter, it may be desirable to increase the speed of the fan, which may keep colder air outside the building below the air intake of the air circulator 120, and may prevent loading dock workers from feeling the cold air. Accordingly, when the loading bay door is opened, the system 100 automatically increases the fan speed. When the loading bay door is closed, the system 100 automatically slows the fan 132 down.
  • FIGS. 6 and 7, illustrated therein is an air circulator 220 made in accordance with an embodiment of the present invention.
  • the air circulator 220 is similar in many respects to the air circulator 20 described previously and similar elements are given similar reference numerals incremented by two hundred.
  • the air circulator 220 includes a housing 222, a support 230, a fan 232, and a drive 234.
  • the housing 222 has a bottom end 224 defining an air intake and a top end 226 defining an air outlet.
  • the fan 232 is positioned further away from the top end 226 in comparison to the air circulator 20 described previously.
  • the height H1 between the top end 226 and the fan 232 is approximately 8 inches.
  • the housing 222 also includes a guide 254 encasing the fan 232.
  • the guide 254 has a slopped profile that narrows as it gets closer to the air outlet. This may help direct the airflow out of the air circulator 220, for example, so that the discharged air has a significant vertical component and a significant lateral component.
  • the drive 234 is coupled to fan 232 through a series of pulleys and a belt.
  • one pulley 280 is coupled to the drive 234, which is in turn coupled to a second pulley 282 through a belt 284.
  • the second pulley 282 is also coupled to a shaft 236, which is coupled to the hub of the fan 232.
  • the air circulator 220 also includes a controller 270, however, the controller 270 is located behind a plate 271 that is removably attached to the housing 222 for concealing the control panel 270.
  • the controller 270 receives power from a power source through a power cord 274, which extends outward from the rear of the housing 222.
  • the air circulator 220 also includes one or more filters 280 that remove particulates from the air.
  • the filters 280 may be MERV 8 filters, HEPA filters or another suitable air filter. As shown in the illustrated embodiment, the filters 280 are positioned on the support 230 between leg members 240 and cross-members 242 along the vertical sides of the support 230 and along the bottom side of the support 230 (shown in FIG. 7).
  • the filters 280 may be rectangular filters. Furthermore, the filters 280 may be of a standard rectangular size used in filtration industry.
  • the filters 280 may have a cumulative filtration surface area that is larger then the cross-sectional area of the airflow passageway 228.
  • the filters 280 on the vertical sides of the support 230 increase the surface area tend to increase the filtration surface area in comparison to using one filter along the air intake 224 at the bottom of the housing 222.
  • the filtration surface area is approximately three times larger than the cross-section of the airflow passageway 28. Increasing the filtration surface area tends to reduce the velocity of the air flowing through the filters 280, which may improve the effectiveness of the filters 280.
  • the filters 280 may be located in different positions.
  • one filter may be positioned at the bottom end of the housing 222.
  • the fan 232 is generally spaced apart from the filters 280. Positioning the fan 232 closer to the top end 226 of the housing 222 tends to improve filtration. In particular, when the fan 232 is positioned closer to the bottom end 224, the speed of the air coming through the filters 280 tends to increase, which reduces the effectiveness of the filters 280. By placing the fan 232 further away from the bottom end 224, the speed of the air coming through the filters 280 decreases, which may improve the effectiveness of the filters 280.
  • the distance between the fan 232 and the filters 280 generally corresponds to a third height H3 between the fan 232 and the bottom end 224 of the housing 222.
  • the third height H3 is at least about 20-inches. In the illustrated embodiment, the third height H3 is about 24-inches.
  • the height of the fan 232 above the filters 280 may be defined in relative terms.
  • the third height H3 may be defined relative to the second height H2 between the bottom end 224 and the top end 226 of the housing 222.
  • the third height H3 may be more than about half of the second height H2, or the third height H3 may be more than about two thirds of the second height H2.
  • third height H3 is about nine tenths of the second height H2.
  • the inventor has determined that the air circulator 220 as described above and having a 36 inch fan 232, and using a 0.5 horsepower drive 234 provides an air speed between about 200 to 500 feet-pet-minute at about 10,000 cubic-feet-per-minute.
  • the filtration provided by the air circulator 220 is comparable to other prior art systems, but the air circulator 220 uses about one third of the energy compared to the other prior art systems.
  • the air filters 280 can help reduce odours.
  • the air filters may incorporate charcoal cartridges that reduce or eliminate odours and chemical particulates from cleaning/sanitizing agents, or from other manufacturing processes.
  • the air filters 280 may also reduce airborne allergens.
  • the air circulator 220 may be adapted to provide fresh-air or "make-up air" capabilities, for example, by providing a length of ducting between the air intake and a source of fresh air (e.g. outside air).
  • the air circulator 220 may also be fitted with a heating source so as to heat air being circulated within an indoor environment.
  • the heating source may include a solar heating coil or a hydronic heating coil, or a heat source fueled by natural gas, oil, or electricity.
  • the air circulator 220 may also be fitted with a cooling device such as an air conditioner.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
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Abstract

La présente invention concerne un dispositif de circulation d'air destiné à amplifier et à manipuler des volumes importants d'air à faible vitesse afin de faire circuler l'air et de réguler la température de l'air intérieur dans un environnement commercial ou industriel. Le dispositif de circulation d'air comprend un boîtier et un élément de support. Le boîtier présente un passage de flux d'air présentant une extrémité inférieure qui définit une entrée d'air, et une extrémité supérieure qui définit une sortie d'air. Le dispositif de circulation d'air comprend un ventilateur disposé dans le passage de flux d'air du boîtier en étant sensiblement adjacent à son extrémité supérieure. L'élément de support assure le maintien du boîtier pour que l'entrée d'air se trouve au dessus du sol. Le ventilateur et la sortie d'air sont conçus pour émettre de l'air dans une direction ayant une composante verticale significative et une composante latérale significative.
EP10769193A 2009-05-01 2010-05-03 Appareil et systèmes pour réguler la température de l'air intérieur Withdrawn EP2430372A1 (fr)

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US17459709P 2009-05-01 2009-05-01
PCT/CA2010/000661 WO2010124388A1 (fr) 2009-05-01 2010-05-03 Appareil et systèmes pour réguler la température de l'air intérieur

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Families Citing this family (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8157892B2 (en) 2010-05-17 2012-04-17 Enverid Systems, Inc. Method and system for improved-efficiency air-conditioning
US8690999B2 (en) 2011-02-09 2014-04-08 Enverid Systems, Inc. Modular, high-throughput air treatment system
US9683748B2 (en) * 2011-03-11 2017-06-20 Carrier Corporation Rooftop hydronic heating unit
WO2012158911A2 (fr) 2011-05-17 2012-11-22 Enverid Systems Inc. Sorbants pour diminuer la concentration en dioxyde de carbone contenu dans l'air intérieur
CN107255324A (zh) * 2011-11-17 2017-10-17 恩弗里德系统公司 用于以分布式空气循环系统调节封闭环境中的空气的方法和系统
CN104254741B (zh) 2012-01-10 2017-07-07 恩弗里德系统公司 用于管理空调系统中的空气质量和能量使用的方法和系统
CN108096991A (zh) 2012-05-22 2018-06-01 恩沃德系统公司 对室内空气的洗涤的吸附剂的高效利用
US9950290B2 (en) 2012-07-18 2018-04-24 Enverid Systems, Inc. Systems and methods for regenerating adsorbents for indoor air scrubbing
US9399187B2 (en) 2012-09-24 2016-07-26 Enverid Systems, Inc. Air handling system with integrated air treatment
WO2014078708A1 (fr) 2012-11-15 2014-05-22 Enverid Systems, Inc. Procédé et système de réduction de la quantité de gaz non désirés dans l'air intérieur
EP2946146B1 (fr) * 2013-01-21 2019-12-25 Carrier Corporation Terminal d'air avancé
CN105745004B (zh) 2013-09-17 2018-05-29 恩弗里德系统公司 用于有效加热室内空气洗涤器中的吸着剂的系统和方法
WO2016004399A1 (fr) * 2014-07-02 2016-01-07 Free Air, Inc. Systèmes de purificateur d'air ambiant des et procédés associés
US10473348B2 (en) * 2014-11-10 2019-11-12 Internal Air Flow Dynamics, Llc Method and system for eliminating air stratification via ductless devices
US20180147526A1 (en) 2015-05-11 2018-05-31 Enverid Systems, Inc. Method and system for reduction of unwanted gases in indoor air
ITUB20150759A1 (it) * 2015-05-21 2016-11-21 Saipem Spa Dispositivo soffiatore per erogare un flusso di aria a portata amplificata e unita’ modulare di raffreddamento
US10792608B2 (en) 2015-08-24 2020-10-06 Enverid Systems, Inc. Scrubber for HVAC system
US11207633B2 (en) 2016-04-19 2021-12-28 Enverid Systems, Inc. Systems and methods for closed-loop heating and regeneration of sorbents
WO2018089856A1 (fr) 2016-11-10 2018-05-17 Enverid Systems, Inc. Épurateur d'air intérieur monté au plafond et à faible bruit
JP2019190806A (ja) * 2018-04-18 2019-10-31 充 本間 床置型暖房機器の暖熱気体を真上天井に吹き上げ送風する暖房方法
US11268537B2 (en) 2018-08-06 2022-03-08 Johnson Controls Technology Company Interface for a plenum fan
KR200495704Y1 (ko) * 2020-08-14 2022-07-29 (주)한별시스템 세이프티 에어서큘레이터
CN117073083B (zh) * 2023-08-18 2024-06-04 湖南省湘能舒适环境科技有限责任公司 全效空调

Family Cites Families (34)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1958768A (en) * 1932-12-27 1934-05-15 Frederick N Ross Air circulator
US2177129A (en) * 1937-11-22 1939-10-24 Bronson C Skinner Fruit curing room
US2500007A (en) * 1947-03-26 1950-03-07 Igor B Polevitzky Air sterilizer and lamp
BE557578A (fr) * 1956-07-12
US2875316A (en) * 1957-12-09 1959-02-24 Emerson Pryne Company Combined heating and ventilating unit
GB914391A (en) * 1961-06-27 1963-01-02 Richard Rowe Cook Air purifier
US3299620A (en) * 1964-03-09 1967-01-24 Charles E Hollingworth Gas treatment device
US3347025A (en) * 1965-08-12 1967-10-17 Wiley Mannie Air circulation system
US3421687A (en) * 1967-01-20 1969-01-14 Buddy Z Daily Vertical air circulation fan
US3827342A (en) * 1973-10-11 1974-08-06 G Hughes Air circulating device
US4103146A (en) * 1975-09-02 1978-07-25 Rampe Research Methods and apparatus for ductlessly circulating and selectively supplementally heating large volumes of air in industrial facilities
US4185545A (en) * 1977-01-10 1980-01-29 Martin David A Air circulator
US4184415A (en) * 1978-07-14 1980-01-22 General Connector Corporation Air circulation apparatus
US4287872A (en) * 1979-10-05 1981-09-08 Rampe Research Methods and apparatus for ductlessly distributing and circulating heated air from a gas-fired heater to heat large volumes of air in industrial facilities
US4347782A (en) * 1979-11-13 1982-09-07 Enercon Systems, Incorporated Telescopable winter/summer air recirculator
US4339250A (en) * 1980-07-17 1982-07-13 Thut Timothy T Fresh air fountain air filter arrangement
GB2135046A (en) * 1983-01-29 1984-08-22 Peter Ashworth Webb Space heating
US4738188A (en) * 1984-02-25 1988-04-19 Nishida Tekko Corporation Room air circulating apparatus
US4570532A (en) * 1984-06-28 1986-02-18 Labelle Raymond R Ventilating unit for animal buildings
DE3532820A1 (de) * 1985-09-13 1987-03-26 Gas & Wasserleitungsgeschaeft Vorrichtung zum gleichmaessigen erwaermen von raeumen
US5000079A (en) * 1990-05-17 1991-03-19 Mardis Michael C Noise-attenuating ventilation pedestal for an electronic enclosure
US5078574A (en) * 1990-11-19 1992-01-07 Olsen George D Device for minimizing room temperature gradients
JP3476899B2 (ja) * 1994-04-12 2003-12-10 東芝キヤリア株式会社 空気調和機
US5588830A (en) * 1995-01-13 1996-12-31 Abb Paint Finishing, Inc. Combined radiant and convection heating oven
US5616172A (en) * 1996-02-27 1997-04-01 Nature's Quarters, Inc. Air treatment system
JP3913334B2 (ja) * 1996-11-20 2007-05-09 三菱電機株式会社 換気送風装置および換気送風システム
JP2918536B2 (ja) * 1997-07-23 1999-07-12 三星電子株式会社 冷蔵庫の冷気吐出口の開閉作動制御方法
US6019677A (en) * 1997-08-22 2000-02-01 York International Corporation Modular integrated terminals and associated systems for heating and cooling
US5997619A (en) * 1997-09-04 1999-12-07 Nq Environmental, Inc. Air purification system
US7028506B2 (en) * 2001-10-15 2006-04-18 Lg Electronics Inc. Indoor unit of packaged air conditioner
US7459002B2 (en) * 2004-08-31 2008-12-02 Airistar Technologies Llc Modular presentation apparatus having integral air processing apparatus
PL1867932T3 (pl) * 2005-01-06 2009-07-31 Oy Halton Group Ltd Automatyczny system wentylacji wyporowej z trybem ogrzewania
US7205740B1 (en) * 2006-03-17 2007-04-17 Delta Elctronics, Inc. Fan control device for frequency converter
JP5268317B2 (ja) * 2007-09-28 2013-08-21 株式会社日立産機システム 油冷式空気圧縮機

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2010124388A1 *

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