US3668887A - Air conditioning apparatuses - Google Patents

Air conditioning apparatuses Download PDF

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US3668887A
US3668887A US60902A US3668887DA US3668887A US 3668887 A US3668887 A US 3668887A US 60902 A US60902 A US 60902A US 3668887D A US3668887D A US 3668887DA US 3668887 A US3668887 A US 3668887A
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Prior art keywords
air
air conditioner
inlet
fan
casing
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US60902A
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English (en)
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Valerio Giordano Riello
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Riello Condizionatori SpA
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Riello Condizionatori SpA
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/20—Casings or covers
    • 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
    • F24F1/02—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing
    • F24F1/028—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing characterised by air supply means, e.g. fan casings, internal dampers or ducts
    • F24F1/0284—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing characterised by air supply means, e.g. fan casings, internal dampers or ducts with horizontally arranged fan axis
    • 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
    • F24F1/02—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing
    • F24F1/03—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing characterised by mounting arrangements
    • F24F1/031—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing characterised by mounting arrangements penetrating a wall or window
    • 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
    • F24F1/02—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing
    • F24F1/0328—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing with means for purifying supplied air
    • F24F1/035—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing with means for purifying supplied air characterised by the mounting or arrangement of filters
    • 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
    • F24F1/02—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing
    • F24F1/0358—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing with dehumidification means
    • 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
    • F24F1/02—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing
    • F24F1/037—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing with humidification means

Definitions

  • This invention concerns improvements in and to air conditioning apparatuses and devices adapted for cooling and simultaneous dehumidification and possibly for heating and simultaneous humidification of the air which is then fed to closed rooms.
  • the improvements according to the invention concern in particular air conditioning devices of relatively small size and designed for the control of humidity and temperature of air in single rooms, or possibly in a few rooms totalling a rather small volume, being such as the devices known on trade under the Italian Registered Trade Mark Rotoclima,” i.e., devices which position can be reversed by having them turned through 180", whereby same apparatus can be quickly and readily adapted by the same user either for cooling and for heating of rooms, such as in spring or autumn time, when the regular heating plant is not in operation, or is insufficiently operating.
  • the invention has also for its object the air conditioners embodying said improvements and characterized by the features, properties and advantages hereinbelow set forth.
  • Such air conditioners are well known and widely in use. They usually comprise a case, having both front and rear sides formed with opening pairs of inlet and outlet openings, each pair being in communication with the room inside and the room outside, respectively. Connected with said pairs of openings are separate spaces formed inside of said case, and wherein fans or like means, driven by one or more electric motors are fitted, said spaces being provided with passages or channels designed to form therein two separate circuits that are run through by the air coming from the room to be conditioned, and by the air drawn from the outer atmosphere and that is sent back again thereto, respectively.
  • the flows running along said circuits are compelled to pass through heat exchangers formed by the evaporator and by the condenser, respectively, of a conventionally operating refrigerating unit, enclosed within the case to remove heat from one of the air flows and to transfer same to the other flow.
  • the evaporator is obviously located on the side of openings directed toward the inside of space to be conditioned.
  • such air conditioners have a simple structure and preferably comprise a single motor for driving both fans, in the "cold and “warm” sections, respectively, inside of same air conditioner.
  • an electric motor having a shaft projecting from either ends thereof, and by which said two fans, keyed onto the ends of projecting portions of said shaft are driven.
  • the air conditioners of such type comprise a basically parallelepipedon shaped casing, which major vertical opposite sides are formed with openings arranged in pairs, and which inside is subdivided into two approximately equal chambers by a diaphragm lying in a plane parallel to said sides, acting said chambers as the warm" section, and as the "cold” sections, respectively, of air conditioner.
  • the length or depth of said sections when measured in a direction orthogonal to same sides, should be as small as possible-at any rate not greater than a few decimeters, since the horizontal dimension of the apparatusin the meaning of projection thereof inside of roomis defined by the sum of said depths.
  • fans meaning by the term fans rotary mechanical means designed to generate and to maintain a draft inside of respective chambers
  • axial-flow fans literally helical or screw fans
  • radial-flow fans with tangential outlets practically centrifugal fans or blowers, which usually are drum-shaped.
  • Said two types of fans show each their own advantages and disadvantages.
  • a uniform sucking action which is in addition properly distributed in a very wide intake cone is exerted by the axial-flow, or helical fans; however, they require a wide space downstream of them for the deflection through 180 of the draft, which in addition should preferably be concentrated on a portion only of the grid or opening through which the air is drawn or impelled back into the room, being also said portion, above all in the warm" section, taken-up preferably by a part of the condenser.
  • centrifugal-flow fans In the centrifugal-flow fans, a first deflection through is directly imparted to the draft which is axially sucked, and then impelled in the rotation plane of same fans.
  • the axial sucking results in a very concentrated input draft, because by the centrifugal fan a vortex is practically generated wherein the maximum vacuum occurs in the axis thereof. Therefore, when such fans are placed very near to a heat exchanger, the useful crossing path thereof is utilized in a very incomplete and improper degree only.
  • the silentness of running is substantially inversely proportional to angular speed of fan wheels, and in particular to peripheral speed of leading edges of the fan paddles.
  • the delivery, for each given angular speed is on turn approximately proportional to wheel diameter, and to the whole of wheel sectional area which is traversed by the air.
  • large diameter wheels would be preferred, running at a low RPM, which on turn require large paddles, with consequent increase in the linear length of their leading edges, across which the undesirable sound vibrations are generated at a frequency that increases with increasing peripheral speed of said leading edges.
  • the pitch of paddle portions adjacent to their lead ing edges is preferably essentially constant, whereby to impart also essentially equal linear speeds in all points of circular zone as defined by said leading edges, to air particles that are acted upon by the paddles, thus obtaining a uniform suction in all points of a wide intake cone.
  • said fan wheels comprise paddles which are supported and clamped between surfaces that are concave shaped on the paddle outside, and convex shaped on the paddle inside, thus defining therebetween an annular channel which circular inlet section is essentially plane, while the outlet section is nearly cylindrically shaped, whereby a first deflection through nearly 90 is imparted to air that flows between same surfaces.
  • the particular orientation of blades of these combined axial intake and radial delivery fans results in a tridimensional configuration of the wheel, which comprises a marked concavity on its side opposite to inlet side. Advantage is taken from such concavity to accomodate the most part of electric motor within the wheel body.
  • the wheels are fitted back to back at either ends of electric motor shaft, being the total axial length of assembly thus formed much smaller than the sum of single axial lengths of wheels and motor.
  • the combination of said features practically allows to restrict the depth of sections wherein the intake, the deflection through I80 and the delivery of air are performed, to a value close to axial dimensions of same fan wheel. Consequently, the total dimension of the improved air conditioner, as measured between their vertical sides that are directed to the outside and to the inside of room, respectivelydue account being taken of the wide intake cone of wheels-can be restricted to a value slightly larger than the sum of thicknesses of heat exchangers (evaporator and condenser), and of axial lengths of the two wheels, between which the electric motor is practically enclosed and supported by the structural wall acting as a partition diaphragm between the warm and cold sections of air conditioner.
  • heat exchangers evaporator and condenser
  • the improved air conditioner according to the invention is characterized in that it comprises, within an essentially parallelepipedon shaped casing, having two major vertical opposite sides, either of which can be associated and engaged with a pipe union, having an inlet or passage adapted to be installed in an orifice or opening as formed in a window pane or other partition wall between the room to be conditioned and the outside, and with a shielding grid adapted to be directed toward the inside of said room: two warm" and "cold zones, respectively, that are separed by a diaphragm, essentially parallel to said vertical sides and approximately equidistant therefrom; an electric motor horizontally fitted in said diaphragm in such a manner as to extend symmetrically itself from either sides thereof, and with a shaft projecting out of both of their ends; two combined axialcentrifugal flow wheels, each having a back recess at their sides opposite to their axial inlets, and fitted back to back on either shaft ends in the cold zone and warm zone, respectively, being the adjacent
  • a refrigerating unit comprising a plategrid type evaporator and an also plate-grid type condenser, fitted in front of wheel axial inlets and close to the adjacent vertical side by which the warm, and respectively the cold sections are terminated, being the sum of axial dimensions of said wheels and of said motor smaller than the distance between the planes as defined by said inlet openings of wheels.
  • FIG. I is a plan simplified view of the improved air conditioner shown in a section taken on the horizontal plane I--I in FIG. 2.
  • FIG. 2 is a vertical sectional view of same conditioner, taken on the plane II-ll in FIG. I, wherein the axis of wheels is also contained.
  • FIG. 3 is a side elevational view of the inside of the air conditioner shown in FIG. 1, and
  • FIG. 4 is a diagrammatic diametral section of one of wheels.
  • FIGS. 4A, 4B and 4C are enlarged sections of a wheel paddle taken on the planes lVa-lVa, lVb-IVb and IVc-IVc, respectively, in FIG. 4.
  • FIG. 5 shows the reversible components of air conditioner, in a position reversed in respect of operating position as shown in FIG. 2, and
  • FIG. 6 is an exploded sectional view of the main components of the air conditioner.
  • the air conditioner basically consists, on its whole, of a parallelepipedon shaped casing, having two major opposite sides, and subdivided into two approximately symmetric portions by a middle vertical diaphragm I0, parallel to said major sides, and by which two sections are defined inside of said casing.
  • Such sections may be appropriately called, on the basis of their function, by the terms cold section I4 and warm section 12.
  • the side wall perpendicular to diaphragm 10 of said sections are spiral shaped, as clearly shown in FIG. 3, to serve as delivery conveyors for the fan wheels (as described later on), having said conveyors their outlets in upper spaces 16 and 18 respectively, which as clearly shown in FIG. 2, are shaped in such a manner as to deflect through 90 to the outside, the air blasts delivered by the wheels into said conveyors.
  • the side walls 20 and 22 respectively of said parallelepipedon casing are formed with circular openings 24 and 26 respectively, juxtaposed to wheel axial inlets.
  • an electric motor 28 Fitted in said diaphragm I0 is an electric motor 28 having preferably a relatively low rating (e.g., a six-pole asynchronous motor) and extending in part into one and in part into the other of said sections.
  • the two wheels are keyed on and driven by the shaft of said motor, which extends out of both ends thereof.
  • Such exchangers consist of condenser 30 and evaporator 32 of refrigerating unit, which refrigeration compressor 34 already per se known is fitted in a recess 36 of air conditioner casing, sidewise to said warm and cold sections.
  • Such heat exchangers are of the already well known flat design and are fitted parallel and close to said walls 20, 22.
  • Said condenser 30 preferably extends also in front of space 16 to be thereby crossed in part by the induced draught and in part by the delivered blast.
  • the two fan wheels indicated generally by the reference numerals 38 and 40 are of properly diversified sizes, to obtain the required proportionality between the flow rates of air blasts that are impelled through the condenser and the evaporator, respectively, and their distinctive diametral sections are shown in FIG. 2, while their operating features are outlined in FIGS. 4 4C (wherein the wheel 40 only is exemplified, which description therefore holds also for the exactly corresponding-apart from the larger sizeswheel 38).
  • said wheels are preferably titted with paddle rims 42, which paddles are clamped between an inwardly convex annular front member 44 having an inside diameter smaller than the outer diameter, and a centrally flattened back member 46 having an inwardly concave perimetral portion, thereby forming on the back a recess wherein a substantial part of axial dimension of frame of motor 28 is accomodated. Consequently, the spacing between the wheel backs is remarkably smaller than the axial dimension of motor, as shown in particular in FIG. 2, while the interval between the planes as defined by the intake orifices 24, 26 is much smaller than the sum of axial dimensions of motor 28 and of the two wheels 38 and 40.
  • the outside diameter of back portion 46 is only slightly smaller than the outer diameter of fore annular portion 44, while the inside diameter of concave perimetral rim of said back portion 46 is smaller than the inside diameter of said annular front portion 44.
  • the width of annular channel as defined by said portions 44, 46 is preferably gradually decreasing toward the outside, being same channel also bent, whereby to deflect the air blast from the axial direction of inlet, to a plane orthogonal to wheel axes.
  • each of wheel paddles extends between the outer borders of said two portions 44, 46, while the preferably convex leading edge extends between the inner contours of said portion 44 and of concave rim of back portion 46.
  • the paddles are bent so that a spiral lead is formed by their intake portions or leading edges 50 in respect of wheel axes, while their trailing edges 48 are essentially parallel to same axes.
  • this latter shows and angle of incidence a and B, 7 respectively which gradually increases proportionally to decreasing of radial value a and b, c respectively of their points, as clearly shown by a comparison of FIGS. 4A 4C.
  • said wheels practically act as axial-flow fans having an essentially constant pitch on their intake side, and as centrifugal fans on their delivery side, thereby imposing the required deflection through 90 to the air blast that flows along said annular channel, in the zone wherein said air blast is acted upon by the dynamic action as exerted by the paddles.
  • both wheels are preferably fitted with a pretty large number of paddles, as shown in FIG. 3, in order that the peripheral spacing of trailing edges 48 of adjacent paddles be preferably not greater than the axial dimension of same edge.
  • wheels having a rather large diameter without increasing the overall sizes, and in particular the axial dimension of rotary assembly, thereby ensuring large flow rates at advantageously low RPM.
  • the drafts are deflected through 90 by at least three times (between the axial inlet and the tangential outlet of wheels, then upwardly along the spiral or scroll shaped conveyors and finally to the outside in the conveying components 16, 18 under very gradual and uniform conditions, without substantial perturbation and whirling phenomena, to great advantage of a high aerodynamic efficiency as well as of silent running.
  • the induced draft occurs the form of a very wide cone as diagrammatically shown in FIG. 4 by a plurality of small arrows.
  • the operation of said wheels can be additionally pre-set in such a manner as to obtain a sharp differentiation between the inlet and the outlet speeds of air blasts.
  • the inlet sides of same wheels may be compared to airscrews having a diameter equal to that of annular portions 44 thereof, and which pitch is established by the angle of incidence of their leading edges 50, as previously outlined.
  • each given RPM is obviously associated with a given flow rate and a given linear speed of air threads on the inlet side, which speed is reduced already at a small distance from the inlet openings of wheels, owing to the width of induction cone.
  • the annular outlet of wheel can be pre-set in such a manner as to show a free area much smaller than that of circular inlet opening. The paddles therefore, at their trailing edges act as centrifugating blades.
  • Said acceleration also allows to obtain a further important advantage, which will be dealt with in more detail later on, ensuing from said differentiation in the speeds, without any head loss and therefore with a high aerodynamic efficiency, due account being taken, in particular, of the not negligible resistances that are encountered by the air blast in the passages through the heat exchangers, the grids, the filters and at any rate in the whole travel inside of the air conditioner.
  • the structural and operating components which have been previously described both individually and as a whole, will form the proper air conditioner, which is capable to absorb heat on one of its sides, and specifically on the evaporator side 32 and to give it back into the (outer or inner) surrounding at the condenser side 30.
  • the component 60 which is directed toward the room to be conditioned, is to be fitted with suitably oriented and distributed grids, thus forming a panel by which the air conditioner is aesthetically completed.
  • the component 61 is to be formed with an opening 62 that, to facilitate the operations of preparation and installation, is preferably-but not necessarily-circular shaped, and that is designed to be inserted through a window pane 63 or the like.
  • said components comprise an essentially box-like structure, generally indicated by 64 and 65 respectively, and having equal sizes and configuration, in order to be indifferently associated with either opposite vertical sides of air conditioner.
  • the proper conditioner shall be turned through 180 about a vertical axis, or at any rate about an axis parallel to window pane 63 or other partition wall by which the room is separed from the outside. From a comparison of FIGS. 2 and 5, the reversal of air conditioner in respect of components 60, 6] which are left in place, is manifest.
  • the component 60 usually comprises two outer grilles 66, 67 fitted to inlet and outlet openings, respectively, of drafts.
  • the grille of outlet opening 67 that is located in front of portion 16 or of portion 18 is conveniently positioned, whereby to direct the draft upwardly and thus to prevent any trouble in the room to be conditioned.
  • the component 61 is preferably formed with a single circular opening 62, that is connected by a nonsymmetrical coneshaped tubular fitting 70 with the related side of air conditioner, and is parted by a diaphragm 71 into its inlet and outlet sections.
  • the use of a single opening is obviously advantageous from the installation viewpoint. In fact, when recourse is made to separate inlet and outlet openings, conditions of precise mutual spacing and positioning of the openings, to be formed in the window pane or panes 63, are to be strictly observed, while with a single opening such requirements can be obviated.
  • the above danger is prevented by taking advantage of the already stated sharp difference in the speeds of incoming and outcoming air threads, and by subdividing the opening 62 and the inner front grillage of air conditioner by means of diaphragm 71 and of component 68, respectively, into inlet ports 72 and outlet ports 73, and into inlet grilled passages 66 and outlet grilled passages 67, respectively, in such a manner that the free area of passage of inlet ports be at least twice the amount of that of outlet ports, whereby to obtain that the speed of outflowing air threads be at least twice of that of inflowing air threads,
  • the outwardly directed outlet port 73 is dimensioned in such a manner that the speed of outflowing air be at least of 4-6 m/sec.
  • the air conditioner is completed by suitable feeding, control and other means which are per se already known, whereby they have been neither described, nor shown.
  • the air conditioner is fitted with suitable switches, thermostats and the like, which controls are preferably positioned on the top side of conditioner casing, in order to allow an easy accessibility thereto in either positions that can be taken by the reversible air conditioner.
  • the air conditioner can be fitted with valve means 80, 81, that can be controlled from the outside, as well as with passages 82, 83 respectively, whereby to bring the high pressure on delivery side of either warm and cold zones into communication with the low pressure or sucking side or the other zone or section, being thereby possible to ensure a supply of fresh air from the outside, or a discharge of stagnant air into the outside, being in the former case the inflowing air previously conditioned (i.e., cooled or heated).
  • valve means 80, 81 that can be controlled from the outside, as well as with passages 82, 83 respectively, whereby to bring the high pressure on delivery side of either warm and cold zones into communication with the low pressure or sucking side or the other zone or section, being thereby possible to ensure a supply of fresh air from the outside, or a discharge of stagnant air into the outside, being in the former case the inflowing air previously conditioned (i.e., cooled or heated).
  • An air conditioner apparatus particularly of the reversible type for the air-conditioning of a single room or a small group of rooms, comprising a casing having two substantially parallel faces; an evaporator contained in said casing adjoining one of said faces; a condenser unit contained in said casing adjoining the other of said faces; passage means associated with said units for the intake of air from and the expulsion of air to the outside of said casing; a partition wall dividing said easing into two sections; and two rotary fans fitted back to back on either side of said partition wall and adjacent to one or the other of said faces respectively, both said fans being of the axial-tangential flow type having a plurality of curved blades having an intake portion of helical configuration screwly acting on the in-flowing air; an outlet portion tangentially acting on the air, and intermediate portion progressively evolving from helical to radial, said blades forming channels therebetween wherein the flow is progressively deviated from axial to radial while being acted upon said blades.
  • An improved air conditioner according to claim 1 comprising fans formed with a recess on their backs, and keyed on either ends of the shaft of a motor that is fitted in said partition wall and extending in either sections and into said fan recesses, the sum of axial dimensions of said fans and of said motor being smaller than the distance between the planes defined by the fan inlets.
  • An improved air conditioner according to claim I wherein a scroll conveyor, circumscribing the related fan wheel is provided in both warm and cold sections, leading said scroll, through a plane essentially tangential to same wheel into a space comprising a baffle plate, by which the air blast, coming from said scroll, is deflected toward the adjacent face of the conditioner.
  • An improved air conditioner according to claim 1, comprising components including tubular fittings and grilles and designed to be indifferently connected with said opposite major faces and formed with separate openings, positioned to juxtapose on the inlet and outlet passages for the air flows provided in either warm and cold sections.
  • each one of said components is formed with inlet and outlet ports for the air flows, being the passage sectional area of inlet port twice as great than that of outlet port, whereby to impart to outflowing air flow a speed at least twice as great that ofair flow sucked into the conditioner,
  • the improved air conditioner according to claim 6, comprising a component indifferently connectable to either major faces of the air conditioner casing and designed to fit into a single opening formed on a partition by which the room to be conditioned is separed from the external, said component comprising an essentially rectangular frame, adapted to match with the contour of either said major faces; an inlet port adapted to be engaged with said opening in said partition, a middle portion by which said rectangular frame is connected with said port, and an inner partition wall that extends from a line crossing said frame, in coincidence with the separation line between the air inlet and outlet ports formed on either said casing faces, to a line by which said opening is subdivided into two inlet and outlet ports, having the inlet port a passage area twice as great that of outlet port.
  • the component designed to cover the inwardly directed casing face is formed with essentially coplanar inlet and outlet openings, lying on a plane essentially parallel to heat exchanger (evaporator or condenser) adjacent to the major face of air conditioner casing with which said component is associated, an air-pervious filtering layer being provided to span over both inlet and outlet openings, through which the air is sucked from and delivered back, respectively, into the conditioned room,
  • An improved air conditioner according to claim 1, comprising passages and operator controlled valve means, by which a space upstream of fan of cold section can be selectively and alternately put in communication with a space downstream of fan of warm section, and respectively a space upstream of fan of warm section can be put in communication with a space downstream of fan of cold section for controlledly providing the intake of air from the outside and the delivery thereof, after having been heated (or cooled) into a conditioned room.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning Room Units, And Self-Contained Units In General (AREA)
  • Separation By Low-Temperature Treatments (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US60902A 1969-08-07 1970-08-04 Air conditioning apparatuses Expired - Lifetime US3668887A (en)

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IT2067169 1969-08-07

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US3668887A true US3668887A (en) 1972-06-13

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US (1) US3668887A (de)
AT (1) AT312876B (de)
CH (1) CH512703A (de)
DE (1) DE2039026A1 (de)
ES (1) ES382501A1 (de)
FR (1) FR2057825A5 (de)
GB (1) GB1312517A (de)
NL (1) NL7011753A (de)

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US4265593A (en) * 1978-09-14 1981-05-05 Hatton C W Stall stabilizer for a centrifugal rotor
US4274810A (en) * 1977-06-29 1981-06-23 Kawasaki Jukogyo Kabushiki Kaisha Diagonal-flow fan wheel with blades of developable surface shape
US4358244A (en) * 1977-01-28 1982-11-09 Kawasaki Jukogyo Kabushiki Kaisha Single curvature fan wheel of a diagonal flow fan
US4641502A (en) * 1985-01-09 1987-02-10 The Duo-Therm Corporation Roof mount air conditioner
US4682384A (en) * 1983-10-05 1987-07-28 The Scott & Fetzer Company Vacuum generating system for hand-held vacuum cleaner
US4748827A (en) * 1987-06-29 1988-06-07 Chang Dick Y K Coil support structure
US4936101A (en) * 1989-04-24 1990-06-26 Carrier Corporation Fan arrangement for thru-the-wall unit
US5336050A (en) * 1993-05-06 1994-08-09 Penn Ventilator Co. Inc. Ventilator fan device
US6339935B1 (en) * 2001-05-16 2002-01-22 Carrier Corporation Evaporator scroll for blower wheel
US6443010B1 (en) * 1999-12-16 2002-09-03 Lucent Technologies Inc. Audible air flow detector for air filters
US6725915B2 (en) 2000-01-20 2004-04-27 Vent-Rite Valve Corp. Method of adjusting room air temperature
US20050056038A1 (en) * 2003-09-16 2005-03-17 Park Hae Yong Integral type air conditioner and air guide structure thereof
US20050056037A1 (en) * 2003-09-16 2005-03-17 Park Hae Yong Integral type air conditioner and front panel thereof
US20050186077A1 (en) * 2004-02-25 2005-08-25 Lg Electronics Inc. Blower fan structure
US20050196282A1 (en) * 2004-03-05 2005-09-08 Lg Electronics Inc. Blower fan
US20070221061A1 (en) * 2006-03-10 2007-09-27 Hamilton Beach/Proctor-Silex, Inc. Air purifier
US20120063899A1 (en) * 2009-06-11 2012-03-15 Takashi Ikeda Turbo fan and air conditioning apparatus
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US20130319778A1 (en) * 2012-05-29 2013-12-05 Don MacGregor Windrower Tractor with Parallel Heat Exchangers for Cooling of Engine and Associated Fluids
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US4358244A (en) * 1977-01-28 1982-11-09 Kawasaki Jukogyo Kabushiki Kaisha Single curvature fan wheel of a diagonal flow fan
US4218190A (en) * 1977-06-29 1980-08-19 Kawasaki Jukogyo Kabushiki Kaisha Flat-bladed fan wheel of diagonal-flow fan
US4274810A (en) * 1977-06-29 1981-06-23 Kawasaki Jukogyo Kabushiki Kaisha Diagonal-flow fan wheel with blades of developable surface shape
US4265593A (en) * 1978-09-14 1981-05-05 Hatton C W Stall stabilizer for a centrifugal rotor
US4682384A (en) * 1983-10-05 1987-07-28 The Scott & Fetzer Company Vacuum generating system for hand-held vacuum cleaner
US4641502A (en) * 1985-01-09 1987-02-10 The Duo-Therm Corporation Roof mount air conditioner
US4748827A (en) * 1987-06-29 1988-06-07 Chang Dick Y K Coil support structure
US4936101A (en) * 1989-04-24 1990-06-26 Carrier Corporation Fan arrangement for thru-the-wall unit
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US6443010B1 (en) * 1999-12-16 2002-09-03 Lucent Technologies Inc. Audible air flow detector for air filters
US6725915B2 (en) 2000-01-20 2004-04-27 Vent-Rite Valve Corp. Method of adjusting room air temperature
US6742582B1 (en) 2000-01-20 2004-06-01 Vent-Rite Valve Corp. Modular climate control unit
US6339935B1 (en) * 2001-05-16 2002-01-22 Carrier Corporation Evaporator scroll for blower wheel
US20050056038A1 (en) * 2003-09-16 2005-03-17 Park Hae Yong Integral type air conditioner and air guide structure thereof
US20050056037A1 (en) * 2003-09-16 2005-03-17 Park Hae Yong Integral type air conditioner and front panel thereof
US20050186077A1 (en) * 2004-02-25 2005-08-25 Lg Electronics Inc. Blower fan structure
US7163374B2 (en) * 2004-02-25 2007-01-16 Lg Electronics Inc. Blower fan structure
US7214033B2 (en) * 2004-03-05 2007-05-08 Lg Electronics Inc. Blower fan
US20050196282A1 (en) * 2004-03-05 2005-09-08 Lg Electronics Inc. Blower fan
US20070221061A1 (en) * 2006-03-10 2007-09-27 Hamilton Beach/Proctor-Silex, Inc. Air purifier
US9651056B2 (en) 2009-06-11 2017-05-16 Mitsubishi Electric Corporation Turbo fan and air conditioning apparatus
US20120063899A1 (en) * 2009-06-11 2012-03-15 Takashi Ikeda Turbo fan and air conditioning apparatus
US8834121B2 (en) * 2009-06-11 2014-09-16 Mitsubishi Electric Corporation Turbo fan and air conditioning apparatus
US20120137716A1 (en) * 2010-12-07 2012-06-07 Tai-Her Yang Air conditioning device utilizing temperature differentiation of exhausted gas to even temperature of external heat exchanger
US8381541B2 (en) * 2010-12-07 2013-02-26 Tai-Her Yang Air conditioning device utilizing temperature differentiation of exhausted gas to even temperature of external heat exchanger
US20130319778A1 (en) * 2012-05-29 2013-12-05 Don MacGregor Windrower Tractor with Parallel Heat Exchangers for Cooling of Engine and Associated Fluids
US8936122B2 (en) * 2012-05-29 2015-01-20 Macdon Industries Ltd. Windrower tractor with parallel heat exchangers for cooling of engine and associated fluids
US20170058914A1 (en) * 2015-08-26 2017-03-02 Lg Electronics Inc. Centrifugal fan
US10132328B2 (en) * 2015-08-26 2018-11-20 Lg Electronics Inc. Centrifugal fan
US11525584B2 (en) 2017-04-13 2022-12-13 Giovanni D. Volo Method of modifying air conditioner for heating
US20190145657A1 (en) * 2017-11-14 2019-05-16 Regal Beloit America, Inc. Blower assembly for use in an air handling system and method for assembling the same
US11255335B2 (en) * 2017-11-14 2022-02-22 Regal Beloit America, Inc. Blower assembly for use in an air handling system and method for assembling the same
US20190298286A1 (en) * 2018-04-03 2019-10-03 Siemens Healthcare Gmbh Cooling system for an imaging apparatus having a gantry
US10856824B2 (en) * 2018-04-03 2020-12-08 Siemens Healthcare Gmbh Cooling system for an imaging apparatus having a gantry
US20220146213A1 (en) * 2020-11-11 2022-05-12 B/E Aerospace, Inc. Heat transfer systems
EP4012275A1 (de) * 2020-11-11 2022-06-15 B/E Aerospace, Inc. Wärmeübertragungssysteme
US11946701B2 (en) * 2020-11-11 2024-04-02 B/E Aerospace, Inc. Heat transfer systems

Also Published As

Publication number Publication date
FR2057825A5 (de) 1971-05-21
CH512703A (it) 1971-09-15
NL7011753A (de) 1971-02-09
ES382501A1 (es) 1972-12-01
DE2039026A1 (de) 1971-02-18
AT312876B (de) 1974-01-25
GB1312517A (en) 1973-04-04

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