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EP1873461B1 - Ceiling embedded air conditioner - Google Patents

Ceiling embedded air conditioner Download PDF

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Publication number
EP1873461B1
EP1873461B1 EP06712972A EP06712972A EP1873461B1 EP 1873461 B1 EP1873461 B1 EP 1873461B1 EP 06712972 A EP06712972 A EP 06712972A EP 06712972 A EP06712972 A EP 06712972A EP 1873461 B1 EP1873461 B1 EP 1873461B1
Authority
EP
European Patent Office
Prior art keywords
motor
air
hub
conditioning apparatus
ceiling
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.)
Expired - Lifetime
Application number
EP06712972A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1873461A1 (en
EP1873461A4 (en
Inventor
Takashi Ikeda
Atsushi Edayoshi
Kazutaka Suzuki
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.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to EP10009996.9A priority Critical patent/EP2273207B1/en
Priority to EP11177128.3A priority patent/EP2390590B1/en
Publication of EP1873461A1 publication Critical patent/EP1873461A1/en
Publication of EP1873461A4 publication Critical patent/EP1873461A4/en
Application granted granted Critical
Publication of EP1873461B1 publication Critical patent/EP1873461B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/08—Units comprising pumps and their driving means the working fluid being air, e.g. for ventilation
    • F04D25/082—Units comprising pumps and their driving means the working fluid being air, e.g. for ventilation the unit having provision for cooling the motor
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/5806—Cooling the drive system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0018—Indoor units, e.g. fan coil units characterised by fans
    • F24F1/0033—Indoor units, e.g. fan coil units characterised by fans having two or more fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0043—Indoor units, e.g. fan coil units characterised by mounting arrangements
    • F24F1/0047—Indoor units, e.g. fan coil units characterised by mounting arrangements mounted in the ceiling or at the ceiling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/24—Means for preventing or suppressing noise
    • 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
    • F24F13/02—Ducting arrangements
    • F24F13/06—Outlets for directing or distributing air into rooms or spaces, e.g. ceiling air diffuser
    • F24F2013/0616—Outlets that have intake openings

Definitions

  • the present invention relates to a ceiling-embedded-type air conditioning apparatus, and, more specifically, relates to an apparatus structure for motor cooling ability improvement and noise reduction.
  • a known ceiling-embedded-type air conditioning apparatus includes a turbo fan having a ceiling-embedded-type air conditioning apparatus body having a chassis top panel, a motor disposed inside the ceiling-embedded-type air conditioning apparatus body in a manner such that the rotary shaft is arranged at right angle to the chassis top panel, a downward-protruding hub covering the motor and fixing the rotary shaft of the motor, a main plate extending from the periphery of an upper opening surface of the hub opposite to the top panel and having a plurality of blades attached to one surface of the main plate opposite to the other surface opposing the top panel, and a shroud opposing the main plate and forming a guiding channel for the blades, a motor-side air passage defined by the hub, the main plate and the shroud and provided on the motor side of the hub, a fan inner air passage provided opposite to the motor-side air passage, and a turbo fan to blow out air taken in from the shroud side through the fan inner air passage, see e.
  • AU-A1-2003 284610 part of the air blown out from the turbo fan is guided through a gap between the chassis top panel and the main plate into the motor-side air passage on the inner side of the hub to cool the motor. Then, the air used for cooling the motor is emitted from openings provided in the hub in the vicinity of the motor-side surface into the fan inner air passage at the outer side of the hub.
  • the openings in the hub are positioned at the lower side of the hub (in the vicinity of fixed portion of the motor rotary shaft and the hub) instead of positioning them in the vicinity of the motor-side surface and an auxiliary fan having a plurality of blades is provided on the outer side of the hub in a manner such that the lower-side openings are covered (see, e.g. JP-B-3270567 ).
  • the cooling rate of the motor is improved by increasing the air volume flowing around the motor and operating noise of the motor leaking from the lower-side openings is reduced by covering the lower-side openings with the auxiliary fan.
  • the openings provided in the hub are side surface openings provided in the vicinity of the side surface of the hub instead of the lower-side openings, and an auxiliary hub protruding downward substantially in line with the hub and being provided on the outer side of the hub so as to cover the side-surface openings is provided instead of the auxiliary fan (see e.g. JP-B-3275474 ).
  • AU-A1-2003 284610 discloses a ceiling-embedded-type air conditioning apparatus on which the precharacterizing portion of claim 1 is based.
  • the openings provided in the hub are covered with the auxiliary fan or the auxiliary hub.
  • the auxiliary fan or the auxiliary hub do not cover the entire hub but only cover part of the hub. Therefore, similar to the above-described prior art, there is a possibility in that the flow from the openings interferes with the intake flow of the turbo fan to worsen the noise.
  • a first object of the present invention is to provide a highly reliable, low-noise ceiling-embedded-type air conditioning apparatus capable of preventing damaging of the motor by improving the motor cooling efficiency.
  • a second object of the present invention is to provide a ceiling-embedded-type air conditioning apparatus being capable of preventing the fan from being damaged during transportation and having high product reliability.
  • the present invention provides a ceiling-embedded-type air conditioning apparatus as defined in claim 1.
  • an air guiding cover is provided on the inner side of a hub and this air guiding cover is formed so that the height position of the lower edge openings of a circumferential surface portion is lower than the lower edge surface of the motor, the air flown into the motor-side air passage can reliably guide the air to the lower edge surface of the motor.
  • the motor cooling efficiency is improved and damaging of the motor due to generated heat can be prevented, enabling a highly reliable ceiling-embedded-type air conditioning apparatus to be obtained.
  • openings for emitting air into the fan inner air passage are provided in the circumferential surface portion of.the hub in the vicinity of a main plate, the air flowing out from the openings into the fan inner air passage can be prevented from interfering with a fan intake air flow. Therefore, shear distortion of the fan intake flow is suppressed, and noise caused by blades passing through turbulent air can be reduced. Furthermore, an increase in noise accompanying deterioration in air supply efficiency caused by interference with the air flowing out from the openings and the fan intake flow can be prevented.
  • the entire hub is substantially a double structure and the openings are provided on the circumferential surface portion of the hub in the vicinity of a main plate, as described above, the distance from the motor-side air passage of the hub to the fan inner air passage is extended, and the noise is damped. As a result, the leakage of motor operating noise, such as abnormal electromagnetic noise and bearing rotating noise generated at the motor, to the outside can be prevented. Furthermore, a low-noise ceiling-embedded-type air conditioning apparatus providing a comfortable environment for residents can be obtained.
  • reinforcement ribs are provided on a chassis top panel and radially disposed air guiding passages for guiding part of the blow-off air flow from the turbo fan to the motor by a top-panel-side heat-insulating material and the reinforcement ribs provided on the inner side of the chassis top panel are formed. Then, first, the strength of the chassis top panel can be increased by the reinforcement ribs so as to enable reduction in the thickness and the weight of the chassis top panel 1b and the flow of air from the radially disposed air guiding passages to the motor can be increased so as to improve the cooling efficiency. As a result, damaging of the motor can be prevented.
  • FIG. 1 illustrates an external perspective view of the air conditioning apparatus according to the present invention.
  • Fig. 2 illustrates a longitudinal cross-sectional view of the inside of the air conditioning apparatus shown in Fig. 1 .
  • Fig. 3 illustrates a horizontal cross-sectional view taken along line X-X in Fig. 2 viewed from the top panel side and illustrates the inside of the air conditioning apparatus body 1 shown in Fig. 1 .
  • Fig. 4 illustrates an enlarged cross-sectional view of a turbo fan 3 and its vicinity shown in Fig. 2 .
  • FIG. 5 illustrates a perspective view of the turbo fan 3 mounted on the ceiling-embedded-type air conditioning apparatus body 1 according the present invention.
  • Fig. 6 illustrates a perspective view of the turbo fan 3 shown in Fig. 5 shown upside-down.
  • Fig. 7 illustrates a perspective view of an air guiding cover 18 disposed on the turbo fan 3.
  • the air conditioning apparatus body 1 is embedded in the ceiling of a room 15 in a manner such that a substantially square decorative panel 2 provided at the lower portion of the air conditioning apparatus body 1 can be seen.
  • the ceiling-embedded-type air conditioning apparatus includes substantially square suction grills 2a communicating with an air inlet 11a (refer to Fig. 2 ) for sucking air into the air conditioning apparatus body 1, and panel outlets 2b communicating with a body outlet 16a (refer to Fig. 2 ) aligned with the sides of the decorative panel 2, both provided in the central area of the decorative panel 2, and further includes air flow direction vanes 2c provided in the panel outlets 2b.
  • the chassis of the air conditioning apparatus body 1 is constituted of chassis side panels 1a and a chassis top panel 1b attached to the area surrounded by the chassis side panels 1a.
  • the chassis side panels 1a and the chassis top panel 1b are composed of sheet metal members.
  • a heat-insulating material 1c is attached to at least part of the surfaces of the chassis side panels 1a and the chassis top panel 1b, on the inner side of the air conditioning apparatus body 1, so as to form the sidewalls of an air passage.
  • a motor 4 disposed in a manner such that its rotary shaft 4a is arranged at right angles to the chassis top panel 1b, a centrifugal air blower including the turbo fan 3 rotationally driven by the motor 4, and a substantially C-shaped heat exchanger 6 disposed vertically so as to surround the turbo fan 3 are provided.
  • a drain pan 12 composed of foamed material and an electric component box 13 accommodating electronic components, such as a control substrate, are disposed.
  • Two end portions 6a of the substantially C-shaped heat exchanger 6 are connected with a heat exchanger connecting plate 7 in a manner such that the heat exchanger 6 and the heat exchanger connecting plate 7, as a whole, form a substantially square shape.
  • a gap is provided between the heat exchanger connecting plate 7 and a side panel-side heat-insulating material 1d.
  • a piping accommodating space 10 is formed by covering the upper end and the lower end of the gap with the chassis top panel 1b and the drain pan 12, respectively.
  • a header 8 connected to a heat exchanger tube 6b extending from one of the end portions 6a and a distributor 9 are disposed.
  • the centrifugal air blower includes the turbo fan 3 and a bellmouth 5 constituting an intake air passage 23a to the turbo fan 3.
  • the turbo fan 3 includes a downward-protruding hub 3c covering the motor 4 and fixing the rotary shaft 4a of the motor 4 in place, a substantially ring-shaped main plate 3b extending from the periphery of the upper opening of the hub 3c so as to oppose the chassis top panel 1b and including a plurality of blades 3a attached to the surface opposite to the surface opposing the chassis top panel 1b, a shroud 3g opposing the main plate 3b and constituting a guiding channel to the blades 3a.
  • the upper edge of the hub 3c is formed as a single unit with the main plate 3b, and the lower edge of the hub 3c is fixed to the rotary shaft 4a of the motor 4.
  • the hub 3c is constituted as a single unit integrating a hollow cone-shaped circumferential surface portion 3ca whose diameter decreases from the inner circumferential surface portion of the main plate 3b to the lower portion of the circumferential surface portion 3ca, a flat surface portion 3cb extending from the lower edge opening of the circumferential surface portion 3ca to the rotary shaft 4a, and a cylindrical portion 3cc extending from the inner circumference of the flat surface portion 3cb to the motor shaft 4a.
  • a plurality of openings 3d is formed along a concentric circle in the vicinity of the main plate 3b.
  • the hub 3c having the above-described structure is fixed to the motor shaft 4a with the cylindrical portion 3cc.
  • the dimensions of the hub 3c are designed so that, in this fixed position, a gap E1 between the main plate 3b formed as a single unit with the hub 3c and a top-panel-side heat-insulating material 1e has a predetermined interval.
  • an air guiding cover 18 On the inner side (motor 4 side) of the hub 3c of the turbo fan 3, an air guiding cover 18 is provided. A motor-side air passage 3f is formed between the air guiding cover 18 and the motor 4. The air guiding cover 18 guides air, flowing from the gap E1 formed between the chassis top panel 1b and the main plate 3b into the motor-side air passage f, to the motor 4. As shown in Fig. 7 , the air guiding cover 18 includes a ring-shaped flange portion 18a and a hollow cone-shaped circumferential surface portion 18c whose diameter decreases so that the cross-sectional area of the motor-side air passage 3f decreases from the inner circumferential surface portion of the flange portion 18a to the lower edge of an opening 18b.
  • the circumferential surface portion 18c is provided at substantially the same angle as the circumferential surface portion 3ca of the hub 3c and in a manner such that a gap E2 between the circumferential surface portion 18c and the circumferential surface portion 3ca has a predetermined interval.
  • the air guiding cover 18 is formed so that the height of the lower edge opening 18b of the circumferential surface portion 18c is lower than a lower edge surface 4b of the motor 4.
  • the air guiding cover 18 guides air flowing into the motor-side air passage 3f to the entire motor 4.
  • the air guiding cover 18 having the above-described structure is composed of metal members, such as aluminum and plated steel plates, having high heat conductivity.
  • the air guiding cover 18 is fixed to the main plate 3b by the flange portion 18a in a suspended position by melting and rotates together with the turbo fan 3 by the rotation of the motor 4.
  • the motor 4 is driven and the turbo fan 3 rotates in the direction indicated by an arrow A (refer to Figs. 3 , 5 , and 6 ). Then, air in the room 15 is taken in from the intake grills 2a as indicated by an arrow B. After dust is removed at a filter 14, the air is taken into the turbo fan 3 through the bellmouth 5. Subsequently, blow-off air C1 from an outlet 3i of the turbo fan 3 is heated or cooled as it passes through the heat exchanger 6.
  • air conditioning is carried out by blowing out the air C1 from the panel outlet 2b into the room 15 while controlling the flow direction of the air with the air flow direction vane 2c rotated by a vane motor, not shown in the drawings.
  • condensed water generated by condensing air in the room 15 at the heat exchanger 6 is drained outside the air conditioning apparatus body 1 by a drain pump 17.
  • the flow B taken into the turbo fan 3 splits into an air flow C1 flowing from the turbo fan 3 to the heat exchanger 6 and a flow C2 flowing through the gap E1 between the main plate 3b and the top-panel-side heat-insulating material 1e, flowing into the motor-side air passage 3f around the motor 4, flowing through the lower edge opening 18b of the air guiding cover 18, flowing through the gap E2 between the hub 3c and the air guiding cover 18, emitted from the openings 3d to the fan inner air passage 3e, and joining the fan intake air flow B.
  • the air flowing into the motor-side air passage 3f (side of the motor 4) of the inner side of the air guiding cover 18 through the gap E1 generates an air flow directed to the lower edge opening 18b.
  • the air guiding cover 18 is formed so that the height of the lower edge opening 18b of the circumferential surface portion 18c is lower than the lower edge surface of the motor 4, the air flowing into the motor-side air passage 3f can be reliably guided to the lower edge surface 4b of the motor 4. In this way, the entire surface of the motor 4 can be cooled, and the heat of the coils and the elements inside the motor 4 can be radiated.
  • the air used to cool the motor 4 surface flows out from the lower edge opening 18b of the air guiding cover 18 and comes in contact with the flat surface portion 3cb of the hub 3c. Subsequently, the air is guided upward through the gap E2 and is emitted from the openings 3d to the fan inner air passage 3e.
  • the openings 3d are formed in the circumferential surface portion 3ca of the hub 3c on the main plate 3b side (in the vicinity of the main plate 3b), the air flowing out from the openings 3d to the fan inner air passage 3e can be prevented from interfering with the fan intake air flow B.
  • the length of the air passage from the motor-side air passage 3f of the hub 3c to the fan inner air passage 3e is greater than that in the case where the hub is in a single structure and the openings for emitting air from the inner side of the hub to the outside is provided in the vicinity of the side surface of the motor or where part of the hub is in a double structure and the position of the openings are low. Therefore, noise is damped, and operational noise, such as abnormal electromagnetic noise or bearing rotating noise generated at the motor 4, is reduced.
  • the flow speed of the air flowing out from the openings 3d to the fan inner air passage 3e is also damped. Accordingly, reduction in the flow rate of the fan blow-off air flow C1 caused by the air flowing out from the openings 3d into the fan inner air passage 3e and interfering with the fan intake air flow B can be reliably prevented, and an increase in noise accompanying degradation of air supply efficiency can be prevented. Furthermore, due to the effect of preventing a reduction in the fan blow-off air flow C1, an air volume sufficient for cooling the motor can be obtained and the motor 4 can be efficiently cooled.
  • Relevant dimensions include the minimum gap spacing k between the air guiding cover 18 and the motor 4 lower edge (the distance between the lower edge of the motor 4 and the surface of the circumferential surface portion 18c along a perpendicular line extended from the lower edge of the motor 4 to the surface of the circumferential surface portion 18c of the air guiding cover 18), an area G5 of the outlet 3i of the turbo fan 3, a circular opening area G1 at the gap E2 between the air guiding cover 18 and the hub 3c (i.e., the opening area obtained by taking a circular cross-section of the air guiding cover 18 and the hub 3c along a plane orthogonal to the circumferential surface portion 3ca), and an total opening area G4 of the openings 3d (total area of all of the openings 3d).
  • Fig. 8 illustrates the relationship between the minimum gap spacing k between the air guiding cover 18 and the motor 4 lower edge and the motor cooling efficiency.
  • the motor cooling efficiency is represented by the proportion of (h1-h2) in h1, where h1 represents the motor temperature when the openings 3d are provided and h2 represents the motor temperature when the openings 3d are not provided.
  • sufficient air flows on the motor surface so that stable motor cooling efficiency can be achieved and damage caused by heat generated at the motor can be prevented.
  • Fig. 9 illustrates the relationship between G4/G1 (the proportion of the total opening area G4 in the circular opening area G1) and the motor cooling efficiency. As shown in Fig. 9 , if G4/G1 is 40% or more, the flow resistance at the passage from the gap E2 between the air guiding cover 18 and the hub 3c to the openings 3d of the hub 3c is not too great, and minimum air flows so that stable, high motor cooling efficiency is achieved and damage caused by heat generated at the motor 4 can be prevented.
  • Fig. 10(a) illustrates the relationship between G4/G5 (the proportion of the total opening area G4 in the turbo fan outlet area G5) and noise values.
  • Fig. 10(b) illustrates the relationship between G4/G5 (the proportion of the total opening area G4 in the turbo fan outlet area G5) and the motor cooling efficiency.
  • G4/G5 the proportion of the total opening area G4 in the turbo fan outlet area G5
  • the motor cooling efficiency As shown in Fig. 10(a) , if G4/G5 is 10% or less, the air flow emitted from the openings 3d does not interfere with the fan intake air flow B and, thus, the noise value is small.
  • G4/G5 is 0.5% or more, stable motor cooling efficiency is obtained. In this way, by setting G4/G5 between 0.5% and 10%, stable motor cooling efficiency can be achieved with low noise.
  • Fig. 11 illustrates the frequency characteristics of the air conditioning apparatus according to the present invention in operation and illustrates the comparative results to a known air conditioning apparatus.
  • the horizontal axis represents frequency
  • the longitudinal axis represents the noise value SPL.
  • the experimental result shows a comparison of the structure according to the present invention and a known structure (a single structure hub having openings formed in the vicinity of the motor side surface of the hub, for emitting the air inside the hub to outside of the hub). As shown in Fig. 11 , it can be confirmed that abnormal electromagnetic noise or bearing rotating noise generated at the motor 4 can be reduced.
  • Fig. 12 illustrates the relationship between the air supply volume and noise during operation of the air conditioning apparatus according to the present invention and illustrates the comparative result with that of a known air conditioning apparatus.
  • the horizontal axis represents the air supply volume
  • the longitudinal axis represents the noise value.
  • the air guiding cover 18 is provided on the inner side (motor 4 side) of the hub 3c and this air guiding cover 18 is formed so that the height of the lower edge opening 18b of the circumferential surface portion 18c is lower than the lower edge surface 4b of the motor 4, air flown into the motor-side air passage 3f can be reliably guided to the lower edge surface 4b of the motor 4.
  • the entire surface of the motor 4 can be cooled, and the heat of the coils and the elements inside the motor 4 can be radiated.
  • the motor cooling efficiency is improved and damage of the motor caused by heat generation can be prevented, and a highly reliable ceiling-embedded-type air conditioning apparatus can be obtained.
  • the openings 3d for emitting air to the fan inner air passage 3e are provided on the main plate 3b side of the circumferential surface portion 3ca of the hub 3c, the air emitted from the openings 3d to the fan inner air passage can be prevented from interfering with the fan intake air flow B. Therefore, shearing distortion of the fan intake air flow B can be suppressed, and noise caused by the blades 3a passing through turbulent air can be reduced. Furthermore, an increase in noise accompanying deterioration in air supply efficiency caused by interference of the emitted air with the air flowing out from the openings and the fan intake air flow B can be prevented.
  • the hub 3c is substantially a double structure as a whole and the openings 3d are provided on the main plate 3b side of the circumferential surface portion 3ca of the hub 3c, as described above, the distance from the motor-side air passage 3f of the hub 3c to the fan inner air passage 3e is extended, and noise is damped.
  • motor operating noise such as abnormal electromagnetic noise or bearing rotating noise generated the motor 4
  • a low-noise ceiling-embedded-type air conditioning apparatus providing a comfortable environment for residents can be provided.
  • the flow speed of the air flowing out from the openings 3d into the fan inner air passage 3e is also damped. Consequently, a reduction in the flow rate of the fan flow-off air flow C1, which is caused by interference between the air flowing out from the openings 3d into the fan inner air passage 3e and the fan intake air flow B can be reliably prevented, and an increase in noise accompanying degradation in air supply efficiency can be prevented. Furthermore, because of the effect of preventing the reduction in flow volume of the fan blow-off air flow C1, a sufficient volume of air for cooling the motor can be ensured, and the motor 4 can be cooled efficiently.
  • the circumferential surface portion 18c of the air guiding cover 18 is hollow cone-shaped and its diameter decreases so that the cross-sectional area of the motor-side air passage 3f gradually decreases toward the lower edge of an opening 18b, the air flow inside the motor-side air passage 3f rises toward the lower edge opening 18b.
  • each of the components so that the minimum gap spacing k is between 8 mm or more and 25 mm or less, G4/G1 is 40% or more, and G4/G5 is between 0.5% or more and 10% or less, damage caused by heat generated at the motor 4 can be prevented at low noise and a quiet, high quality ceiling-embedded-type air conditioning apparatus body can be obtained.
  • the air guiding cover 18 is composed of metal members, such as aluminum and plated steel plates, having high heat conductivity, heat from the heated air around the motor is transmitted to the air guiding cover 18. Also, since the air guiding cover 18 rotates together with the turbo fan 3, the volume of air passing by in contact with the surface of the air guiding cover 18 is increased compared with that in the case where the air guiding cover 18 is so formed as to not rotate, and heat radiation is promoted. In this way, a high motor cooling effect can be achieved. As a result, damage due to heat generation of the motor 4 can be prevented at low noise and a highly reliable ceiling-embedded-type air conditioning apparatus body can be obtained.
  • the openings formed in the fixing member of the motor 4 i.e., the openings 3d of the hub 3c
  • the openings 3d of the hub 3c are provided at the bottom edge side (i.e., main plate 3b side) instead of the tip side of the truncated cone
  • the area of the members (hub 3c) between adjacent openings 3d is great compared with that in the case where the openings 3d having the same opening area are provided at the lower side surface or in the vicinity of the lower edge, as in a known hub. For this reason, great strength against torque generated by the motor 4 is achieved.
  • the circumferential surface portion 18c of the air guiding cover 18 and the circumferential surface portion 3ca of the hub 3c are substantially parallel to each other.
  • a cylindrical portion 18d may be provided by bending the circumferential surface portion 18c of the air guiding cover 18 along the outer peripheral surface on the motor 4 side.
  • FIG. 14 illustrates a longitudinal cross-sectional view of the inside of the air conditioning apparatus according to the second embodiment of the present invention.
  • Fig. 15 illustrates a horizontal cross-sectional view of the inside of the air conditioning apparatus body 1 shown in Fig. 14 viewed from the top panel.
  • Fig. 16 illustrates an enlarged view of a turbo fan 3 and its vicinity shown in Fig. 14 .
  • Fig. 14 illustrates a longitudinal cross-sectional view of the inside of the air conditioning apparatus according to the second embodiment of the present invention.
  • Fig. 15 illustrates a horizontal cross-sectional view of the inside of the air conditioning apparatus body 1 shown in Fig. 14 viewed from the top panel.
  • Fig. 16 illustrates an enlarged view of a turbo fan 3 and its vicinity shown in Fig. 14 .
  • FIG. 17 illustrates a schematic view of a turbo fan 3 coming in contact with a top-panel-side heat-insulating material 1e by pivoting on a supporting point at a fixed point of the hub 3c and the rotary shaft 4a during transportation.
  • the same components as those according to the first embodiment shown in Figs. 1 to 4 are represented by the same reference numerals, and descriptions thereof are omitted.
  • the second embodiment is the same as the first embodiment shown in Fig. 2 except that, on the top-panel-side heat-insulating material 1e, a rectifying section 1g for limiting the flow volume flowing from the gap E1 to the motor 4 side is provided in a ring-shaped fan main plate-corresponding area 1f opposing the main plate 3b. In this way, the flow volume emitted from openings 3d to the fan inner air passage 3e is reduced to lower noise.
  • the rectifying section 1g is provided as a single unit with the top-panel-side heat-insulating material 1e.
  • Fig. 18 illustrates a perspective view from the portion corresponding to the fan side of the heat-heat-insulating material 1c.
  • the rectifying section 1g is substantially a ring-shaped, and the distance from the main plate 3b in the height direction is reduced from the outer circumferential portion toward the inner circumferential portion.
  • the minimum gap E1 between the rectifying section 1g and the main plate 3b and a gap D1 between the main plate 3b and the top-panel-side heat-insulating material 1e in the height direction are set to establish a predetermined relationship.
  • a side surface 1h of the rectifying section 1g as shown in Fig.
  • the shape of the inclined side surface 1h is a polygonal shape so that the hub comes into line contact or surface contact with the outer circumferential edge of the turbo fan 3, as shown in Fig. 18 .
  • a flow C2 blown out from an outlet 3i of the turbo fan 3 and reversed in a direction toward the gap E1 between the main plate 3b and the top-panel-side heat-insulating material 1e is prevented from excessively flowing into a motor-side air passage 3f. Therefore, the flow volume of air flowing out from the openings 3d to the fan inner air passage 3e can be reduced, the air is prevented from interfering with the fan intake air flow B and the generation of shear distortion is suppressed. In this way, noise can be reduced.
  • Fig. 19(a) illustrates the change in the noise value corresponding to E1/D1 (proportion of the minimum gap E1 between the rectifying section 1g and the main plate 3b in the gap D1 between the top-panel-side heat-insulating material 1e and the main plate 3b in the height direction) uner the condition that the air supply volumes are the same.
  • Fig. 19(b) illustrates the motor cooling efficiency corresponding to E1/D1 when the air supply volumes are the same.
  • E1/D1 is set between 0.3 and 0.7 to balance the motor 4 cooling effect and the noise reduction effect. In this way, the motor cooling efficiency is increased, and, thus, damage due to heat generated at the motor 4 can be prevented and the noise values can be reduced.
  • the same advantages as those according to the first embodiment are achieved. Also, according to the second embodiment, since the rectifying section 1g having the above-described shape is provided, the air flow C2 blown out of the outlet 3i of the turbo fan 3 and reversed in a direction toward the gap E1 between the main plate 3b and the top-panel-side heat-insulating material 1e is prevented from excessively flowing into a motor-side air passage 3f. Therefore, the flow volume of air flowing out from the openings 3d to the fan inner air passage 3e can be reduced, the air is prevented from interfering with the fan intake air flow B, and the generation of shear distortion is suppressed. In this way, noise can be reduced.
  • the manner of contact is not point contact as in the case of a known apparatus but is line contact or surface contact, as indicated by J in Fig. 17 , stress concentration to the main plate 3b due to impact can be avoided, and damaging of the turbo fan 3 can be prevented.
  • the rectifying section 1g can be formed as a single unit using the heat-heat-insulating material 1, which constitutes the air passage, when molding the heat-insulating material 1c.
  • other components do not have to be composed and the assembling process can be simplified.
  • a highly reliable, low-noise ceiling-embedded-type air conditioning apparatus capable of preventing motor damage by improving the motor cooling efficiency and providing a comfortable environment for a resident can be obtained.
  • E1/D1 is set between 0.3 and 0.7, a ceiling-embedded air conditioning apparatus having both a motor 4 cooling effect and a noise reduction effect can be obtained.
  • the side surface of rectifying section 1g is formed in a polygonal shape.
  • the shape is not limited so long as the side surface of rectifying section 1g is shaped so that the outer circumferential edge of the turbo fan 3 can be brought into line contact or surface contact.
  • the shape may be that illustrated in Fig. 20 as described below.
  • Fig. 20 illustrates a perspective view of another example of the rectifying section 1g having different shape.
  • the side surface 1h of the rectifying section 1g is shaped as the inclined surface of a truncated cone.
  • stress concentration due to impact imposed on the main plate 3b can be avoided and damaging of the turbo fan 3 can be prevented.
  • E1/D1 is 0.3 to 0.7, a ceiling-embedded air conditioning apparatus having both a motor 4 cooling effect and a noise reduction effect can be obtained.
  • the rectifying section 1g is formed of the top-panel-side heat-insulating material 1e.
  • the rectifying section 1g may be formed by deforming a section of the fan main plate-corresponding area 1f of the chassis top panel 1b. In such a case, even if the top-panel-side heat-insulating material 1e is not provided inside the air passage of the top panel 1b, the rectifying section 1g can be provided as a single unit with the chassis top panel 1b without the top-panel-side heat-insulating material 1e, so that cost can be reduced
  • FIG. 22 illustrates a longitudinal cross-sectional view of the inside of the air conditioning apparatus according to the third embodiment of the present invention.
  • Fig. 23 illustrates a perspective view of a rectifying plate 19 shown in Fig. 22 .
  • the same components as those according to the first embodiment shown in Figs. 1 to 4 are represented by the same reference numerals, and descriptions thereof are omitted.
  • the third embodiment is the same as the second embodiment shown in Fig. 14 , except that, instead of forming the rectifying section 1g on the top-panel-side heat-insulating material 1e, a rectifying plate 19 having a shape corresponding to the rectifying section 1g and functioning in the same way as the rectifying section 1g is detachably installed.
  • the rectifying plate 19 is composed of a sheet metal member or a plastic member and is fixed to the top-panel-side heat-insulating material 1e and the chassis top panel 1b with screws.
  • the same advantages as those according to the first and second embodiments are achieved and the rectifying plate 19 is made replaceable. Therefore, the flow resistance changes because of partial change of the specifications of the structural components, such as the heat exchanger 6 and the filter 14, the flow volume of the gap E2 between the main plate 3b and the rectifying plate 19 can be adjusted appropriately according to the model by simply changing the rectifying plate 19.
  • the shape of the rectifying plate 19, similar to the above-described rectifying section 1g, is not limited to the shape illustrated in the drawings and the shape may be that illustrated in following Fig. 24 .
  • the side surface 1h of the rectifying plate 19 is shaped as the inclined surface of a truncated cone.
  • stress concentration due to impact imposed on the main plate 3b can be avoided and damaging of the turbo fan 3 can be prevented.
  • FIG. 25 is a longitudinal cross-sectional view of the inside of an air conditioning apparatus according to the fourth embodiment of the present invention.
  • Fig. 26 illustrates a z-z cross-sectional view.
  • Fig. 27 illustrates the exterior of a top panel viewed from an arrow S in Fig. 25 .
  • Fig. 28 illustrates a partially enlarged view of the turbo fan 3 and its vicinity illustrated in Fig. 25 .
  • Fig. 29 illustrates a cross-sectional perspective view taken along line V-V in Fig. 26 .
  • Fig. 30 illustrates a partial cross-sectional side view of a motor 4.
  • Fig. 25 is a longitudinal cross-sectional view of the inside of an air conditioning apparatus according to the fourth embodiment of the present invention.
  • Fig. 26 illustrates a z-z cross-sectional view.
  • Fig. 27 illustrates the exterior of a top panel viewed from an arrow S in Fig. 25 .
  • Fig. 28 illustrates a partially
  • FIG. 31 illustrates a schematic view of a driving substrate built-in the motor 4.
  • Fig. 32 illustrates the measurement experiment results of the motor surface temperature and the noise value corresponding to the positional relationship between the radially positioned air guiding passage 1k and the turbo fan 3 shown in Fig. 25 .
  • the same components as those according to the first embodiment shown in Figs. 1 to 4 are represented by the same reference numerals, and descriptions thereof are omitted.
  • the fourth embodiment is the same as the first embodiment shown in Fig. 1 except that, a plurality of reinforcement ribs 1i is provided on the chassis top panel 1b so as to improve the strength of the chassis top panel 1b and a top-panel-side heat-insulating material 1ea is provided on the reinforcement ribs 1i and the chassis top panel 1b so as to form radially positioned air guiding passage 1k for guiding a flow C2 to the motor 4 in order to improve the motor 4 cooling efficiency.
  • a plurality of the reinforcement ribs 1i is provided on the chassis top panel 1b in an area corresponding to the inner side of the heat exchanger 6 in a manner such that the reinforcement ribs 1i extend from the outer peripheral portion of an area opposing the motor 4 toward the chassis side panels 1a and protrude toward the inner side of the body.
  • a heat-insulating material 1ca having a substantially overall box shape is disposed constituting an air passage wall surface.
  • the heat-insulating material 1ca includes the top-panel-side heat-insulating material 1ea disposed flush with part of or the entire inner surface of the chassis top panel 1b and a side panel-side heat-insulating material 1d that is the same as the above-described one. Since the fourth embodiment is characterized by the top-panel-side heat-insulating material 1ea, the shape of the top-panel-side heat-insulating material 1ea will be described in detail below.
  • the top-panel-side heat-insulating material 1ea is disposed flush with part of or the entire inner surface of the chassis top panel 1b, but, according to this embodiment, the top-panel-side heat-insulating material 1ea is disposed flush with part of the inner surface of the chassis top panel 1b.
  • the reinforcement ribs 1i are provided on the chassis top panel 1b in a manner such that the reinforcement ribs 1i protrude toward the inner side of the body, and the top-panel-side heat-insulating material 1ea is formed so that it is disposed flush with the entire protruding surface 1ia on the basis of the protruding surface 1ia (refer to Fig. 29 ).
  • the top-panel-side heat-insulating material 1ea is formed flush with part (several) of radially positioned areas 1ib among a plurality of radially positioned areas (i.e., the triangular area (one of which is a longitudinal area) 1ib positioned outside from the protruding surface 1ia and located between adjacent reinforcement ribs 1i on the chassis top panel 1b) in a protruding manner.
  • the triangular area one of which is a longitudinal area
  • the top-panel-side heat-insulating material 1ea is disposed flush with four of the radially positioned areas 1ib, and, for the other areas, the top-panel-side heat-insulating material 1ea is provided flat without being disposed flush with the radially positioned areas 1ib. Therefore, as shown in Figs. 26 and 29 , the other radially positioned areas 1ib than the four radially positioned areas 1ib are hidden by being covered with the flat portion of the top-panel-side heat-insulating material 1ea.
  • the top-panel-side heat-insulating material 1ea having such a structure forms an area corresponding to the radially positioned areas 1ib (refer to Fig. 29 ) so that the radially positioned air guiding passage 1k having a gap distance to the main plate 3b that is greater than the gap distance between the reinforcement ribs 1i and the main plate 3b.
  • the motor 4 is so constituted as to have an in-motor substrate 4h having a driver circuit 4d and a control circuit 4e mounted inside of the motor on the chassis top panel side (opposite side to the turbo fan) or, more specifically, is constituted of a DC motor.
  • the in-motor substrate 4h is fixed to the inside of the motor 4.
  • the rotor 4g is fixed to the rotary shaft 4a.
  • a stator 4f including a coil and a core is disposed around the rotor 4g.
  • the stator 4f is molded and formed as a single unit with a molding material 4k.
  • the DC motor is formed by disposing the rotor 4g in a hollow portion formed in the stator 4f and holding the rotor 4g in a freely rotatable manner by the edge of the hollow portion and a bearing 4i press fit into a bracket 4L. Furthermore, the rotor 4g is formed by molding a plastic magnetic material into a cylindrical shape and has magnetic fields having N and S poles at the outer periphery.
  • a hole element 4j for detecting the magnetic field of the rotor 4g and generating a revolution signal, the control circuit 4e for receiving the revolution signal and transmitting a revolution instructing signal voltage, and the driver circuit 4d for controlling the electrical power applied to the magnetic field of the stator 4f on the basis of the revolution instructing signal are mounted.
  • a power element 4M is mounted and is in contact with the bracket 4L with intervention of an insulating plate and a heat radiating silicone.
  • the in-motor substrate 4h is connected to an electronic substrate 25 inside an electric component box 24, as illustrated in Fig. 25 , via wiring.
  • an AC/DC converter 25a for converting a voltage (e.g., 200 V) of an AC power supply 26 into a DC voltage and boosting it to supply this DC voltage to the driver circuit 4d and a control circuit power supply 25b for supplying power to the control circuit 4e are mounted.
  • the temperature of the heat generated at the power element 4M becomes higher than other components, such as the coil of the stator 4f, and, thus, heat is transmitted via the heat-radiating silicone so as to increase the temperature of the bracket 4L and a side surface 4c on the chassis top panel side of the motor 4. Therefore, if the bracket 4L and the side surface 4c on the chassis top panel side of the motor 4 does not radiate heat, the power element 4M will be damaged by the generated heat, and the motor 4 will fail. In other words, to prevent the damaging of the motor 4, it is necessary to mainly cool the bracket 4L and the side surface 4c on the chassis top panel side of the motor 4.
  • the motor 4 As another example of the motor 4, if the motor 4 is a DC motor indicating the driver circuit 4d and the control circuit 4e mounted on the electronic substrate 25 accomodated in the electric component box 24 outside the motor, the rotary shaft 4a is heated by heat transmitted from the stator 4f having the highest temperature in the motor 4, lubricant oil of the bearing 4i is degraded by the high temperature, and the bearing 4i seizes, causing the motor 4 to be damaged. In other words, for this case also, to prevent damaging of the motor 4, it is necessary to mainly cool a bearing-corresponding portion 4P (refer to Fig. 28 ) on the surface of the motor and the bracket 4L in contact with the bearing 4i.
  • the bearing-corresponding portion 4P is a portion of the outer surface of the bearing 4i of the motor 4.
  • the cooling effect on the motor 4 by proving the radially positioned air guiding passages 1k will be described.
  • the portion being disposed flush with the radially positioned areas 1ib and constituting the radially positioned air guiding passages 1k has a greater gap distance E1 compared with other portions (i.e., the flat portion formed in accordance with the protruding surface 1ia of the reinforcement ribs 1i). Therefore, the flow volume and speed of part of the blow-off air flow C2 from the turbo fan 3 can be increased when the air is drawn to the motor 4. Consequently, the cooling effect on the motor 4 is increased.
  • the direction of the flow C2 which rotates between the main plate 3b and the top-panel-side heat-insulating material 1ea and is drawn toward the motor 4 is changed by coming into contact with a side surface 1ka of the radially positioned air guiding passage 1k, as shown in Fig. 29 .
  • a side surface 1ka of the radially positioned air guiding passage 1k as shown in Fig. 29 .
  • the side surface 4c of the motor 4 on the chassis top panel side and the bracket 4L on the top surface of the motor 4 on the chassis top panel side are cooled.
  • the top-panel-side heat-insulating material 1ea is disposed flush only with part of the radially positioned areas 1ib among all of the radially positioned areas 1ib.
  • the top-panel-side heat-insulating material 1ea is not disposed flush with all of the radially positioned areas 1ib because, if the top-panel-side heat-insulating material 1ea is disposed flush with all of the radially positioned areas lib, noise may increase.
  • the bearing-corresponding portion 4P can be cooled.
  • the bearing-corresponding portion 4P can be sufficiently cooled. Since the motor 4 can be sufficiently cooled in this way, the turbo fan 3 can be rotated until the limit temperature of the power element 4M is reached. In this way, the air supply volume can be increased, and the heat-exchange ability of the heat exchanger 6 can be improved.
  • inner circuit loss of the power element 4M can be reduced, motor efficiency is improved and energy can be conserved.
  • the blow-off flow C1 instead of the flow C2 passing through the gap E1 and being directed toward the motor-side air passage 3f, directly collides with the side surface 1ka of the radially positioned air guiding passage 1k, causing an increase in noise.
  • the blow-off flow C1 directly collides with the side surface 1ka of the radially positioned air guiding passage 1k and its direction is changed toward the motor 4, the flow volume toward the motor 4 side increases, whereas the flow volume toward the heat exchanger 6 decreases. Therefore, the air flow must be increased to increase the heat exchanging ability, and, as a result, noise worsens.
  • Fig. 32(a) illustrates the relationship between the position of the inner circumferential edge 1kb of the radially positioned air guiding passage 1k and the surface temperature T1 of the bracket 4L disposed on the chassis top panel side of the motor 4 after being operated for the same amount of time.
  • Fig. 32(b) illustrates the relationship between the position of the outer circumferential edge 1kc of the radially positioned air guiding passage 1k and the noise value SP at the same flow volumes.
  • Fig. 32(c) illustrates the relationship between the position of the outer circumferential edge 1kc of the radially positioned air guiding passage 1k and the surface temperature T1 of the bracket 4L disposed on the chassis top panel side of the motor 4 after being operated for the same amount of time.
  • the reinforcement ribs 1i are formed on the chassis top panel 1b in a manner such that they protrude toward the inside of the body, strength can be increased without increasing the height of the body. In this way, the thickness and the weight of the chassis top panel 1b can be reduced. Moreover, since the radially positioned air guiding passage 1k having the ability to change the direction of the flow C2 toward the motor 4 is formed with the top-panel-side heat-insulating material 1ea provided on the inner side of the chassis top panel 1b, the motor 4 can be effectively cooled and damaging of the motor can be prevented.
  • top-panel-side heat-insulating material 1ea is provided on the inner surface of chassis top panel 1b, even when the heat exchanger 6 is cooled during cooling operation, the atmosphere inside the body is also cooled, and the humidity of the area under roof where the air conditioning apparatus body 1 is installed is high, dew condensation on the surface of the chassis top panel 1b can be prevented. In this way, drew does not drop on the floor of the room to cause the floor to get dirty, and the cleanliness of the floor can be maintained.
  • a low-noise, high quality ceiling-embedded air conditioning apparatus capable of both improving the motor 4 cooling efficiency and suppressing the worsening of the noise value and capable of preventing damaging by heat generated at the motor 4.
  • the size of the electric component box 24 can be reduced compared with the size of an electric component box 24 including the driver circuit 4d and the control circuit 4e. In this way, the bellmouth 5 and the body intake air passage 11 are not partially blocked. Therefore, reduction of flow resistance and prevention of an intake drift are possible, and noise reduction is possible.
  • the height of the top surface (surface of the bracket 4L of the motor 4) of the motor 4on the chassis top panel 1b side of the motor 4 is lower (closer to the turbo fan 3) than the height of the surface of the top-panel-side heat-insulating material 1ea, shown in a dotted line in Fig. 28 , a space is formed in the vicinity of the bracket 4L, allowing the flow C2 to easily flow into the bracket 4L. Therefore, the cooling effect can be improved, and, as a result, the motor efficiency is improved, enabling a high quality ceiling-embedded air conditioning apparatus capable of excellent energy saving to be obtained.
  • a ceiling-embedded-type air conditioning apparatus according to a fifth embodiment of the present invention will be described below with reference to Figs. 33 to 35 .
  • Figs. 33 and 34 illustrate the same body according to the fourth embodiment, except that the radially disposed reinforcement ribs 1i protrude toward the outside of the body.
  • Fig. 33 illustrates the chassis top panel 1b viewed from the side of a top-panel-side heat-insulating material 1eb.
  • a Y-Y cross-sectional view of Fig. 33 is substantially the same as Fig. 28 .
  • Fig. 34 illustrates a plan view of the exterior of the chassis top panel 1b.
  • Fig. 35 illustrates a cross-sectional perspective view taken along line V-V in Fig. 33 .
  • the same components as those according to the first embodiment shown in Figs. 1 to 4 and those according to the fourth embodiment shown in Figs. 25 to 32 are represented by the same reference numerals, and descriptions thereof are omitted.
  • the fifth embodiment is the same as the fourth embodiment, except that the radially disposed reinforcement ribs 1i protrude toward the outside of the body instead of the inside of the body.
  • a substantially box-shaped heat-insulating material 1cb is disposed to form an air passage side surface.
  • the heat-insulating material 1cb includes a top-panel-side heat-insulating material 1ea disposed flush with part of or the entire inner surface of the chassis top panel 1b and a side panel-side heat-insulating material 1d, which is the same as the above-described one. Since the fifth embodiment is characterized by the top-panel-side heat-insulating material 1eb, the shape of the top-panel-side heat-insulating material 1eb will be described in detail below.
  • the top-panel-side heat-insulating material 1eb is disposed flush with part of the chassis top panel 1b instead of flush with the entire chassis top panel 1b. More specifically, on the chassis top panel 1b, the reinforcement ribs 1i protruding toward the outside of the body are formed, as shown in Fig. 34 , and the top-panel-side heat-insulating material 1eb are formed so that they are disposed flush with the entire surface 1ic based on the protruding surface 1ic (refer to Fig. 35 ).
  • the top-panel-side heat-insulating material 1eb is formed flush with part (several) of the reinforcement ribs 1i among all the reinforcement ribs 1i protruding further outward than the surface 1ic, in a protruding manner.
  • the top-panel-side heat-insulating material 1eb is disposed flush with four of the reinforcement ribs 1i, and, for the other areas, the top-panel-side heat-insulating material 1eb is provided flat without being disposed flush with the reinforcement ribs 1i. Therefore, as shown in Fig. 33 , the reinforcement ribs 1i, except for the four reinforcement ribs 1i, are hidden by being covered with the flat portion of the top-panel-side heat-insulating material 1eb.
  • the area formed flush with the reinforcement ribs 1i constitutes a radially positioned air guiding passages 1k' having a gap distance to the main plate 3b that is greater than the gap distance between the area formed flat and not flush with the reinforcement ribs 1i and the main plate 3b.
  • the bearing-corresponding portion 4P can be sufficiently cooled and prevented from being damage. Since the motor 4 is sufficiently cooled in this way, the turbo fan 3 can be rotated until the limit temperature of the power element 4M is reached. In this way, the air supply volume can be increased, and the heat-exchange ability of the heat exchanger 6 can be improved.
  • inner circuit loss of the power element 4M can be reduced, motor efficiency is improved, and energy can be saved.
  • a dimensions satisfying 0.5 ⁇ L1 ⁇ L0 ⁇ 0.6 ⁇ L1 and 0 ⁇ L2 ⁇ 0.3 ⁇ L1 is effective for cooling the motor 4 and reducing noise.
  • the same advantages are also achieved in the fifth embodiment.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Air-Conditioning Room Units, And Self-Contained Units In General (AREA)
  • Motor Or Generator Frames (AREA)

Abstract

　モータ冷却効率向上によりモータの故障を防止することできて信頼性が高く、また、低騒音の天井埋込型空気調和機を得る。モータ４を覆いモータ４の回転軸４ａを固定する下に凸形状のハブ３ｃのモータ側に、モータ４との間にモータ側風路３ｆを形成し、筐体天板１ｂと主板３ｂとの間に形成された隙間からモータ側風路３ｆに流れ込んだ空気を、モータ４に向けて導風する導風カバー１８を設ける。導風カバー１８は、主板３ｂ側から下方に向かって延出された周面部１８ｃを備え、周面部１８ｃの下端開口１８ｂの高さ位置がモータ４の下端表面４ｂよりも下方に位置するように形成されており、ハブ３ｃは、隙間からモータ側風路３ｆに流れ込み、導風カバー１８の下端開口１８ｂから流れ出て導風カバー１８とハブ３ｃとの隙間に流入した空気をファン内部風路３ｅに流出させる開口穴３ｄを複数有する。
EP06712972A 2005-02-24 2006-02-03 Ceiling embedded air conditioner Expired - Lifetime EP1873461B1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP10009996.9A EP2273207B1 (en) 2005-02-24 2006-02-03 Ceiling-embedded-type air conditioning apparatus
EP11177128.3A EP2390590B1 (en) 2005-02-24 2006-02-03 Ceiling-embedded-type air conditioning apparatus

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2005049354 2005-02-24
JP2005334856A JP4684085B2 (ja) 2005-02-24 2005-11-18 天井埋込型空気調和機
PCT/JP2006/301829 WO2006090564A1 (ja) 2005-02-24 2006-02-03 天井埋込型空気調和機

Related Child Applications (4)

Application Number Title Priority Date Filing Date
EP10009996.9A Division EP2273207B1 (en) 2005-02-24 2006-02-03 Ceiling-embedded-type air conditioning apparatus
EP11177128.3A Division EP2390590B1 (en) 2005-02-24 2006-02-03 Ceiling-embedded-type air conditioning apparatus
EP10009996.9 Division-Into 2010-09-20
EP11177128.3 Division-Into 2011-08-10

Publications (3)

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EP1873461A1 EP1873461A1 (en) 2008-01-02
EP1873461A4 EP1873461A4 (en) 2010-07-14
EP1873461B1 true EP1873461B1 (en) 2011-10-05

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Application Number Title Priority Date Filing Date
EP06712972A Expired - Lifetime EP1873461B1 (en) 2005-02-24 2006-02-03 Ceiling embedded air conditioner
EP10009996.9A Expired - Lifetime EP2273207B1 (en) 2005-02-24 2006-02-03 Ceiling-embedded-type air conditioning apparatus
EP11177128.3A Expired - Lifetime EP2390590B1 (en) 2005-02-24 2006-02-03 Ceiling-embedded-type air conditioning apparatus

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EP10009996.9A Expired - Lifetime EP2273207B1 (en) 2005-02-24 2006-02-03 Ceiling-embedded-type air conditioning apparatus
EP11177128.3A Expired - Lifetime EP2390590B1 (en) 2005-02-24 2006-02-03 Ceiling-embedded-type air conditioning apparatus

Country Status (5)

Country Link
EP (3) EP1873461B1 (ja)
JP (1) JP4684085B2 (ja)
CN (2) CN1942716B (ja)
ES (2) ES2623875T3 (ja)
WO (1) WO2006090564A1 (ja)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US12145092B2 (en) 2020-11-11 2024-11-19 Samsung Electronics Co., Ltd. Air conditioner

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CN1942716A (zh) 2007-04-04
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CN101907325B (zh) 2012-06-13
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EP2390590A3 (en) 2014-06-04
WO2006090564A1 (ja) 2006-08-31
ES2623875T3 (es) 2017-07-12
EP2390590B1 (en) 2017-03-22
EP2273207B1 (en) 2017-03-22
EP1873461A1 (en) 2008-01-02
EP1873461A4 (en) 2010-07-14
EP2273207A3 (en) 2014-06-18
EP2273207A2 (en) 2011-01-12
ES2623606T3 (es) 2017-07-11
JP4684085B2 (ja) 2011-05-18
CN101907325A (zh) 2010-12-08

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