US3805542A - Air conditioning apparatus - Google Patents

Air conditioning apparatus Download PDF

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Publication number
US3805542A
US3805542A US00294803A US29480372A US3805542A US 3805542 A US3805542 A US 3805542A US 00294803 A US00294803 A US 00294803A US 29480372 A US29480372 A US 29480372A US 3805542 A US3805542 A US 3805542A
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United States
Prior art keywords
blower
housing
air
disposed
air intake
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Expired - Lifetime
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US00294803A
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English (en)
Inventor
T Hosoda
H Ogawa
A Sakazume
K Ogata
H Uzuhashi
Y Sekine
K Fujie
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Hitachi Ltd
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Hitachi Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4226—Fan casings
    • F04D29/4246—Fan casings comprising more than one outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • 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
    • F24F1/022—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing comprising a compressor cycle
    • F24F1/027—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing comprising a compressor cycle mounted in wall openings, e.g. in windows

Definitions

  • the present invention relates to an improvement in an air conditioning apparatus.
  • An object of the present invention is to provide an air conditioning apparatus which is compact and has a lower noise level.
  • the air conditioning apparatus in accordance with the present invention is of such a type that comprises a housing having an air passage opening, a heat exchanger disposed in the housing and a blower for directing air to the heat exchanger.
  • This type of heat exchanger is advantageous in that, since the heat exchanger and the blower are enclosed in the housing, it
  • the apparatus of this type has widely been used in homes, however, a serious problem encountered in this type of air conditioning apparatus is a relatively high level noise.
  • This type of air conditioning apparatus generally uses an axial flow type as turbo blowenThe blowerof thistype operates with a high efficiency and produces less noise when flow resistance in air flow passage is very small, but the efficiency is remarkably reduced and a high level noise is produced when the air flow resistance is high.
  • the air conditioning apparatus of the aforementioned type since the flow resistance at the air flow I passage opening in the housing is generally high, the
  • axial flow blower used therein operates with a low efficiency and produces a high level noise.
  • centrifugal flow type blower in lieu of the axial flow type blower, because it has been found that a centrifugal flow type blower has a higher operating efficiency and produces less noise under a relatively high flow resistance as compared with an axial flow type blower.
  • the use of a centrifugal flow type blower in an air conditioning apparatus may be effective to reduce noise level, however, in order to provide a sufficient. amount of flow byusing this type of blower, it is required to. provide aspiral casing of a substantial di mension for this blower to direct airflow from the blower to the air flow passage opening of the housing.
  • the present invention has an important feature in that the spiral casing is divided into a plurality of segments so as to provide a plurality of discharge ports.
  • a centrifugal type blower it is essential in reducing noise level to decrease the flow speed in the passage provided by the spiral casing.
  • the cross-sectional area of the passage in the spiral casing is gradually increasedalong the three quarter circumferential extent of the blower,
  • an air conditioning apparatus comprising a housing having an air intake opening and a plurality of air discharge openings, a centrifugal flow type blower disposed in the housing, and a spiral casing disposed about said centrifugal type blower and comprising a plurality of spiral segments to provide a plurality of discharge ports, and a heat exchanger disposed in an air flow passage of said centrifugal blower.
  • FIG. 1 is a longitudinal sectional view of an air conditioning apparatus in accordance with the present invention
  • FIG. 2 is a sectional view taken along the line II-II in FIG. 1;
  • FIG. 3 is a sectional view taken along the line III-III in FIG. 2;
  • FIG. 4 is a fragmentary enlarged view of the segment shown in FIG. 3;
  • FIG. 5 is a longitudinal sectional view 'of another embodiment of the present invention.
  • FIG. 6 is a sectional view taken along the line VI-VI in FIG. 5;
  • FIG. 7 is a sectional view taken along the line VII- -VII in FIG. 6;
  • FIG. 8 is a longitudinal sectional view of a further embodiment of the present invention.
  • FIG. 9 is a sectional view taken along the line IX-IX in FIG. 8;
  • FIG. 10 is a sectional view taken along the line X-X in FIG. 9;
  • FIG. 11 is a longitudinal sectional view of a further embodiment of the present invention.
  • FIG. 12 is a sectional view taken along the line XII- -XII in FIG. 11;
  • FIG. 13 is a sectional view taken along the line XIII- -XIII in FIG. 12.
  • the reference numeral (1) designates a housing of an air conditioning apparatus having an air intake opening (la) at the front surface thereof and air discharge openings (lb) and (10) at the opposite side surfaces thereof.
  • the numeral (2) designates a centrifugal flow type blower such as a multi-blade type centrifugal blower which takes air thereinto at the front surface thereof and discharges from the sides thereof.
  • a circumferentially extending spiral casing (3) which comprises a mouth ring (3a) disposed at the front side, a back plate (3b) and a pair of spiral segments (3c) and (3d) which are disposed at the opposite sides of the blower.
  • the mouth ring (3a) has an intake port (3e) for the centrifugal blower (2), and the spiral segments (30) and (3d) are so arranged to provide air outlet ports (3]) and (3g) which communicate with the air discharge openings (1b) and (1c).
  • the spiral segments (30) and (3d) are positioned symmetrically with respect to the axis of the blower (2).
  • the reference numeral (4) designates a blower motor having an output shaft connected to the centrifugal blower (2) and disposed in a shielded chamber (5) defined by the housing (1) and the back plate (3b) of the spiral casing (3).
  • the numeral (6) designates a heat exchanger which provides a portion of cooling cycle together with a compressor (7) and serves as an evaporator when the apparatus is operated for cooling purpose, and as a condenser when the apparatus is operated for heating purpose.
  • compressed refrigerant is discharged outside the apparatus from the compressor (7) through a discharge line, not shown, and is cooled into liquified refrigerant in a suitable manner by cold water supplied from a source, which liquified refrigerant is fed to the evaporator (6) through a fed line, not shown. Since means for cooling compressed refrigerant by utilizing cold water and the conduits including the discharge and fed lines do not constitute a part of this invention, they are not shown nor disclosed herein in detail.
  • liquified refrigerant is discharged outside the apparatus from the condenser (6) through a discharge line, not shown, and is heated into volatized refrigerant in a suitable manner by hot water supplied from a source, which volatized refrigerant is fed to the compressor (7) through a fed line, not shown.
  • the compressor (7) is housed in the shielded chamber (5).
  • the shielded chamber (5) is connected to the inlet passage of the blower (2) by means of a conduit (8) and vented to the atmosphere through a vent hole (9).
  • air is taken into the apparatus through the air intake opening (la) by means of the centrifugal blower (2), cooled or heated as the case may be by the heat exchanger (6) and introduced into the blower (2). Then, the air is discharged from the blower (2) and directed through the spiral segments (30) and (3d) to the discharge ports (3]) and (3g) to be discharged therefrom. Finally, the air is passed through the discharge openings (1b) and (1c) in the housing (1) to the room where the air conditioning apparatus is positioned.
  • the spiral casing comprises two spiral segments (3c) and (3d)
  • the spiral casing (3) since the spiral casing comprises two spiral segments (3c) and (3d), it is possible to decrease the increase in the flow resistance due to the provision of the spiral casing (3) to one-fourth as compared with an arrangement in which a single outlet spiral casing is used, because the illustrated arrangement is effective to reduce the air flow speed to one-half of that in a known arrangement.
  • the noise level without increasing the dimension of the housing (1).
  • the spiral casing (3) has a pair of discharge ports (3]) and (33) at the opposite sides thereof for corresponding with the discharge openings (lb) and (1c) in the housing (1 it is possible to obtain a smooth air flow even with a small housing.
  • the spiral segments (3c) and (3d) are disposed symmetrically with respect to the axis of the blower (2), it is possible to further decrease the noise level as compared with an asymmetrical arrangement.
  • the illustrated arrangement is also desirable in that the load on the rotating blower shaft is well balanced and vibration of the blower can be remarkably decreased. Since the heat exchanger (6) is disposed in the intake passage of the centrifugal blower (2), turbulence of air flow can be decreased as compared with an arrangement in which the heat exchanger is disposed in the discharge passage of the blower and thus the noise level of the apparatus can be further reduced. Since the compressor (7 is disposed in the shielded chamber (5), the noise produced by the compressor 7) is not transmitted outside the apparatus.
  • the air conduit (8) and the vent hole (9) serve to provide a sufficient cooling air flow for the compressor (7).
  • the shielded chamber (5) for the compressor (7 is formed by the back plate (3b) of the blower casing (3) without adding any member.
  • the conduit (8) may be omitted and the cooling air may be introduced into the shielded chamber (5) through a passage formed in the shaft of the blower motor (4).
  • the reference character (3h) designates the leading portion of the spiral segment (3d), and (3i) the leading portion of the segment (3c), both being bent radially outwardly of the centrifugal blower (2) in order to provide smooth air entrances.
  • the trailing end portion of each spiral segment forms the air discharge port (3g) or (3f) with the leading portion (3h) or (3i) of the other segment.
  • the character D designates the external diameter of the blower (2), Ad and Ac the distances from the blower (2) to the leading portions (3h) and (3i), Ed and Be the distances from the outer periphery of the blower (2) to the inner surfaces of the spiral segments (3d) and (3c), respectively at the trailing portions thereof.
  • the characters 0d and 6c designate angular distances from the leading ends of the portions (3h) and (3i) to the horizontal center line of the blower (2).
  • the ratio Ad to Ac is determined 1 4 or below and the values of Ad/D and Ac/D are between 0.02 and 0.2, preferable results can be obtained in respect to the air flow and the operating efficiency of the blower and the apparatus can be operated with less noise.
  • the ratio Ad/D or Ac/D is below 0.02
  • a piping noise is produced and, when the ratio is over 0.2, a portion of blower output air flows from either the discharge ports (3f) or (3g) to the adjacent intake port Ad or Ac producing a noise and resulting in a reduced air pressure.
  • the ratio of Be to Ed when the ratio of Be to Ed is below 1 to 4 and the ratio Bd/D and Bc/D are between 0.1 and 0.4, preferable results can be obtained in respect of the air flow and the blower efficiency, with less operating noise.
  • the ratio Bd/D or Bc/D is less than 0.1, the air flow speed is so increased that noise is remarkably increased and the amount of air flow is decreased due to an increase in flow resistance. Thus, the operating efficiency is decreased.
  • the spiral segment (3d) or (30) do not serve its purpose and the discharged air is allowed to flow back around the centrifugal blower (2) resulting in an increased noise and a reduced discharge pressure.
  • the ratio of Rd to Ad or Bc to Ac should preferably be 2 to 10. If the ratio is out of this range, the spiral segment does not serve its purpose anymore and the performance of the blower is remarkably decreased and noise level is increased to an unacceptable value.
  • the ratio of angle ad to ac or ac to ad should preferably be 1 to 3 and a preferable range of each of the angle ad and ac is between 45 and 135. If the angle is less than 45 or over l35, a decrease in performance will be encountered.
  • the angle d or (is should be between 45 and +30 as measured from the horizontal center line in order to provide a preferable result in respect of the amount of air flow, the blower operating efficiency and the noise level. When the angle is out of this range, a piping noise is produced or the amount of airflow and the discharge air pressure are decreased.
  • the air conditioning apparatus includes a housing (1 1) having an air intake port (110) at the rear surface, air discharge ports (11b) and (110) at the opposite sides thereof, and an air vent hole (11d) at the front surface thereof.
  • a centrifugal flow type blower (12) which having larger blades and smaller blades at opposite sides of a partition disc as shown in FIGS. 5 and 6, takes air thereinto from the front and reat surfaces and discharges it from the periphery thereof.
  • a spiral casing (13) which comprises a pair of mouth rings (13a) and (13b) respectively disposed at the rear and front surfaces of the blower, and a pair of spiral segments (13c) and (13d) disposed along the periphery of the blower (12).
  • the mouth ring (13a) is provided with an air intake port (13c) for the blower (12) and the mouth ring (1317) is provided with an airintake port (13]) and also defines a shielded chamber (14) together with the housing (11). In this arrangement, air is'allowed to flow from the air vent hole (11d) through the shielded chamber (14) into the air intake port (13]).
  • the spiral segments (13c) and (13d) are provided with air discharge ports (13g) .and(l3h), respectively, which are positioned in confronting relationship with the air discharge openings (11b) and (11c) of the housing (11).
  • the air discharge ports (13g) and (13h) are positioned in symmetrical relation with respect to the axis of the blower (12).
  • a blower motor (15) is disposed in the shielded chamber (14) and operatively connected to the centrifugal blower (12).
  • a compressor (16) is also disposed in the shielded chamber (14) with a side-by-side relation with the blower motor (15).
  • the reference numeral (17) designates a heat exchanger which constitutes a portion of a cooling cycle together with the compressor (16). When the apparatus is used for cooling purpose, the heat exchanger serves as an evaporator, while when the apparatus is used for heating purpose, it serves as a condenser.
  • the apparatus as constructed above has advantageous features as in the embodiment shown in FIGS. 1 through 3.
  • the apparatus has the following advantages. Namely, the use of a dual-intake type centrifugal blower (12) is effective to compensate the decrease in air flow passage for the blower which is caused by the provision of the shielded chamber (14) for preventing the noise of the compressor (16) from being transmitted outside the apparatus. Further, since the air in the shielded chamber (14) is directly introduced into the blower, the compressor cooling air passage construction can be made very simple. Still further, the provision of a dual-intake type blower is effective to have axially balanced loads on the blower, resulting in a reduced vibration.
  • FIGS. 7 through 9 show a window type air conditioning apparatus comprising a housing (21) which is adapted to be mounted through a wall (22).
  • the housing (21) has an open front end to which a decorating cover (23) is attached.
  • the cover (23) is provided with an air intake port (23a) and an air discharge port (23b).
  • the portion of the housing 21) that is disposed outside the room has a rear surface which is provided with an air intake opening (21a) and side surfaces which are provided with air discharge openings (21b) and (21c).
  • the reference numerals (24) and (25) designate partition plates for separating the interior space of the housing (21) into an inboard space (26), an outboard space (27) and a shielded chamber (28), the plate (24) separating the space (26) and the shielded chamber (28) and the plate (25) separating the shielded chamber (28) and the space (27).
  • a centrifugal flow type blower (29) which takes air thereinto from the front .side and discharges the air from the periphery thereof.
  • a spiral casing comprising a mouth ring (30a) disposed at the front surface of the blower, and a spiral segment (30b) at the periphery of the blower.
  • the partition plate (24) also constitute a portion of the spiral casing (30).
  • the mouth ring (30a) is formed with an air-intake port (30c) for the blower (29) and the spiral segment (30b) is formed with an air discharge port(30d) which is positioned in confronting relation with the air discharge opening (23b) in the housing (21).
  • an evaporator (31) which serves to cool the air in the room.
  • a second centrifugal type-blower (32) is provided in. the space (27) of the housing (21) which serves to take air thereinto from the rear side and discharge from the periphery thereof.
  • a second spiral casing (33) is disposed around the second blower (32) and comprises a mouth ring (33a) at the rear side thereof and a pair of spiral segments (33b) and (33c) at the peripheral portion thereof.
  • the partition plate (25) also takes-a part of the spiral casing (33).
  • the mouth ring (33a) is formed with an air intake port (33d) for the centrifugal blower (32) and the spiral segments (33b) and (33c) are formed with air discharge ports (33c) and (33)), respectively, which are in communication with the air discharge openings (21b) and (21c) in the housing (21
  • the spiral segements (33b) and (330) are positioned in symmetrical relation with respect to the axis of the blower (32).
  • a condenser (34) is disposed at the inlet side of the blower (32) for cooling the air from the compressor.
  • a blower motor (35) is-provided in the shielded chamber (28) and operatively connected to the blowers (29) and (32).
  • the reference numeral (36) designates a compressor disposed in the shielded chamber (28) and constituting a cooling cycle together with the evaporator (31) and the condenser (34).
  • the numeral (37) designates a dew tray disposed directly beneath the evaporator (31) for receiving water dipping from the evaporator (31).
  • a conduit (38) is connected to the dew tray (37) for directing the water in the tray (37) to the bottom of the space (27). [n the space (27), there is provided a slinger ring (39) which is driven by the centrifugal blower (32) for spattering the water collected in the space (27) toward the condenser.
  • the air conditioning apparatus as described above can provide advantages as in theembodiment shown in FIGS. 1 through 3.
  • the apparatus provides further advantages in that the noise from the second centrifugal blower (32) is shielded by two partition plates (24) and (25), so that the noise level can be remarkably reduced. Since the compressor (36) and the blower motor (35) are disposed at the longitudinal outer portion of the housing, and the partition plates (24) and (25), the blowers (29) and (32), and the heat exchangers (3]) and (34) are arranged in symmetrical relationship with respect to the compressor (36) and the blower motor (35), the window type air conditioning apparatus can be stably positioned on the wall.
  • the operating efficiency can be further increased by the arrangement in which the condensed water is spattered to the condenser (34). It is of course possible to decrease the noise level of the room blower (29) by using a centrifugal flow type blower as the room blower (29) and providing a spiral casing comprising a plurality of spiral segments for forming a plurality of discharge ports.
  • FIGS. 11 through 13 show a further embodiment of the present invention which is obtained by combining the arrangement of FIG. 5 through 7 with that of FIGS. 8 through 10. 7
  • An air conditioning apparatus comprising a housing having an air intake opening at the rear surface thereof and a plurality of air discharge openings at the opposite side surfaces thereof; a dual-inlet type centrifugal blower disposed in said housing, said blower including a partition disc and a plurality of larger and smaller blades, said larger blades being provided at a rear side of said partition disc and said smaller blades being provided at the front side of said disc; a spiral casing comprising a pair of spiral segments disposed along the periphery of said blower, said spiral segments providing two air discharge ports which are positioned in confronting relationship with said air discharge openings at the opposite side surfaces of said housing, a rear plate disposed at the rear side of said blower for separating an air intake flow passage from air discharge passages provided with an air intake port for said blower, and a front plate disposed at the front side of said blower for separating the interior space of said housing into two spaces, said front plate being provided with an intake port for said blower; a heat exchanger disposed in an air intake flow
  • An air conditioning apparatus comprising a housing separating the interior space thereof into an inboard space and an outboard space by means of first and second partition plates, said housing having an air intake port and an air discharge port at the front surface thereof, an air intake opening at the rear surface thereof, and air discharge openings at the opposite side surfaces thereof; a first single-inlet type centrifugal blower disposed within said inboard space of said housing taking air thereinto from said front side thereof; an evaporator disposed at said inlet side of said first blower; a second dual-inlet type centrifigual blower disposed within said outboard space of said housing, said second blower including a partition disc, and a plurality of large and small blades, said large blades being provided at a rear side of said partition disc and said small blades being provided at the front side of said disc; a spiral casing comprising a pair of spiral segments disposed along the periphery of said second blower, said spiral segments providing two air discharge ports which are positioned in confronting relationship with said air discharge openings at

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Air-Conditioning Room Units, And Self-Contained Units In General (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Soundproofing, Sound Blocking, And Sound Damping (AREA)
US00294803A 1972-02-18 1972-10-04 Air conditioning apparatus Expired - Lifetime US3805542A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP1972019501U JPS4896748U (it) 1972-02-18 1972-02-18

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US3805542A true US3805542A (en) 1974-04-23

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ID=12001108

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US00294782A Expired - Lifetime US3805541A (en) 1972-02-18 1972-10-04 Window-mounted air conditioning apparatus
US00294803A Expired - Lifetime US3805542A (en) 1972-02-18 1972-10-04 Air conditioning apparatus

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US00294782A Expired - Lifetime US3805541A (en) 1972-02-18 1972-10-04 Window-mounted air conditioning apparatus

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US (2) US3805541A (it)
JP (1) JPS4896748U (it)
DE (1) DE2248550A1 (it)
GB (2) GB1401834A (it)
IT (2) IT975152B (it)

Cited By (16)

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US5065596A (en) * 1990-05-11 1991-11-19 Whirlpool Corporation Dual louvered side air discharge openings for room air conditioner
US5065597A (en) * 1990-05-11 1991-11-19 Whirlpool Corporation Dual side discharge air housing for room air conditioner
US5085057A (en) * 1990-05-11 1992-02-04 Whirlpool Corporation Dual side discharge room air conditioner with foamed insulation air passage walls
US5299634A (en) * 1991-09-26 1994-04-05 Mitsubishi Denki Kabushiki Kaisha Indoor unit of a ventilation system, ventilation and air conditioner
GB2289314A (en) * 1994-05-05 1995-11-15 Bentone Electro Oil Ab Fan housing arrangement in an oil burner
US6196013B1 (en) * 1998-02-19 2001-03-06 Samsung Electronics Co., Ltd. Fan casing of window type air conditioner
WO2001066952A1 (en) * 2000-03-09 2001-09-13 Pm-Luft Ab Air conditioning apparatus
US20030228213A1 (en) * 2002-06-11 2003-12-11 Valeo Climate Control Corporation Center console dual centrifugal fan blower
US20050115262A1 (en) * 2003-11-21 2005-06-02 John Stanko Compact chassis room air conditioner
US20050163607A1 (en) * 2004-01-23 2005-07-28 Airex Inc. Blower with double inlet wheel
US20070051121A1 (en) * 2003-10-23 2007-03-08 Yoon-Seob Eom Window type air conditioner
US20070056305A1 (en) * 2003-10-23 2007-03-15 Yoon-Seob Eom Window type air conditioner
US20070209385A1 (en) * 2004-03-31 2007-09-13 Tomohiro Yabu Humidity Control System
US20110008161A1 (en) * 2007-11-16 2011-01-13 Lg Electronics Inc. Fan
US20180105012A1 (en) * 2015-04-28 2018-04-19 Denso Corporation Air conditioner for vehicle
US20180298914A1 (en) * 2015-04-28 2018-10-18 Denso Corporation Blower

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JPS5287848A (en) * 1976-01-19 1977-07-22 Hitachi Ltd Room air conditioner
US4586349A (en) * 1983-11-02 1986-05-06 Mitsubishi Denki Kabushiki Kaisha Unitary air conditioner
DE3438710C2 (de) * 1984-10-23 1986-11-27 Wilhelm Gebhardt Gmbh, 7112 Waldenburg Dachventilator
GB2199126A (en) * 1986-12-10 1988-06-29 Albert John Amor Combined flue and ventilator
IT210218Z2 (it) * 1987-04-17 1988-12-06 Delchi Carrier Spa Apparecchio trasferibile per la climatizzazione di ambienti.
DE3926293A1 (de) * 1988-12-17 1990-06-21 Samsung Electronics Co Ltd Klimaanlage zum fensteranbau
US5293758A (en) * 1991-08-29 1994-03-15 American Standard Inc. Outside section for split system air conditioning unit
US5253485A (en) * 1992-03-27 1993-10-19 White Consolidated Industries, Inc. Low profile room air conditioner
BE1011636A3 (nl) * 1997-12-23 1999-11-09 Atlas Copco Airpower Nv Compressor met ingebouwde ventilator.
HK1025475A2 (en) * 1999-07-29 2000-10-13 Gree Electric Appliances Inc Separation type air conditioner and its installation method
US6880354B2 (en) * 2003-05-05 2005-04-19 Carrier Corporation Condensate pump for rooftop air conditioning unit
RU2490560C2 (ru) * 2009-09-30 2013-08-20 Василий Иванович Мазий Устройство и способ воздушного отопления воздушного охлаждения и вентиляции помещений
CN104358603A (zh) * 2014-12-10 2015-02-18 马根昌 恒速离心排气管消声器
CN104696282B (zh) * 2014-12-30 2018-04-27 博耐尔汽车电气系统有限公司 一种离心风机蜗壳设计方法
EP3749900A4 (en) * 2018-02-06 2022-03-23 Scientific Environmental Design, Inc. HVAC SYSTEM FOR IMPROVED SOURCE-TO-LOAD MATCHING IN LOW LOAD STRUCTURES
CN108224598A (zh) * 2018-03-20 2018-06-29 广东美的制冷设备有限公司 整体式空调器
CN108224596A (zh) * 2018-03-20 2018-06-29 广东美的制冷设备有限公司 整体式空调器
CN108469075A (zh) * 2018-03-20 2018-08-31 广东美的制冷设备有限公司 整体式空调器
US11236762B2 (en) * 2019-04-26 2022-02-01 Johnson Controls Technology Company Variable geometry of a housing for a blower assembly
WO2022052568A1 (zh) * 2020-09-10 2022-03-17 广东美的制冷设备有限公司 一体式空调器

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US5065596A (en) * 1990-05-11 1991-11-19 Whirlpool Corporation Dual louvered side air discharge openings for room air conditioner
US5065597A (en) * 1990-05-11 1991-11-19 Whirlpool Corporation Dual side discharge air housing for room air conditioner
US5085057A (en) * 1990-05-11 1992-02-04 Whirlpool Corporation Dual side discharge room air conditioner with foamed insulation air passage walls
US5299634A (en) * 1991-09-26 1994-04-05 Mitsubishi Denki Kabushiki Kaisha Indoor unit of a ventilation system, ventilation and air conditioner
GB2260576B (en) * 1991-09-26 1995-05-03 Mitsubishi Electric Corp Indoor unit of a ventilation system,ventilator and air conditioner
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Also Published As

Publication number Publication date
DE2248550A1 (de) 1973-08-30
GB1401834A (en) 1975-07-30
GB1400550A (en) 1975-07-16
JPS4896748U (it) 1973-11-16
DE2248549B2 (de) 1976-04-29
IT975152B (it) 1974-07-20
DE2248549A1 (de) 1973-08-30
IT975151B (it) 1974-07-20
US3805541A (en) 1974-04-23

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