EP1243864A2 - Unité intérieure et conditionneur d'air - Google Patents

Unité intérieure et conditionneur d'air Download PDF

Info

Publication number
EP1243864A2
EP1243864A2 EP02006380A EP02006380A EP1243864A2 EP 1243864 A2 EP1243864 A2 EP 1243864A2 EP 02006380 A EP02006380 A EP 02006380A EP 02006380 A EP02006380 A EP 02006380A EP 1243864 A2 EP1243864 A2 EP 1243864A2
Authority
EP
European Patent Office
Prior art keywords
air
fan
air duct
width
casing
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.)
Granted
Application number
EP02006380A
Other languages
German (de)
English (en)
Other versions
EP1243864B1 (fr
EP1243864A3 (fr
Inventor
Kazuhiro c/o Mitsubishi Heavy Industries Suzuki
Yuuji c/o Mitsubishi Heavy Industries Okada
Kenichi/O Mitsubishi Heavy Industries Miyazawa
Hajime c/o Mitsubishi Heavy Industries Izumi
Kiyoshi c/o Mitsubishi Heavy Industries Suenaga
Tetsuo c/o Mitsubishi Heavy Industries Tominaga
Fumio c/o Mitsubishi Heavy Industries Kondou
Masashi c/o Mitsubishi Heavy Industries Maeno
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 Heavy Industries Ltd
Original Assignee
Mitsubishi Heavy Industries Ltd
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
Priority claimed from JP2001084416A external-priority patent/JP2002276585A/ja
Priority claimed from JP2001084413A external-priority patent/JP3564414B2/ja
Priority claimed from JP2001084415A external-priority patent/JP3621892B2/ja
Priority claimed from JP2001084414A external-priority patent/JP2002276975A/ja
Application filed by Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Publication of EP1243864A2 publication Critical patent/EP1243864A2/fr
Publication of EP1243864A3 publication Critical patent/EP1243864A3/fr
Application granted granted Critical
Publication of EP1243864B1 publication Critical patent/EP1243864B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • 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
    • F04D29/422—Discharge tongues
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/663—Sound attenuation
    • 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
    • F24F1/0011—Indoor units, e.g. fan coil units characterised by air outlets
    • 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
    • F24F1/0025—Cross-flow or tangential fans

Definitions

  • the present invention relates to an indoor unit and an air-conditioner that provides a comfortable indoor environment by heating or cooling, and more particularly, to a technology that is suitable for use in an indoor unit and air-conditioner that is capable of reducing the operating noise generated in the air blowing system of an indoor unit that uses a tangential fan.
  • Air-conditioners are composed of two large constituent elements in the form of an indoor unit and outdoor unit. Each of these units is equipped with an indoor heat exchanger and outdoor heat exchanger that perform heat exchange between a refrigerant and the indoor air and between refrigerant and the outside air.
  • indoor and outdoor heat exchangers are elements that compose a refrigerant circuit in addition to elements such as a compressor and expansion valve.
  • indoor cooling and heating are realized by following a circulation process of thermal changes in state consisting of high-temperature, high-pressure gas, low-temperature, low-pressure gas, high-temperature, high-pressure liquid and low-temperature, low-pressure liquid.
  • this indoor cooling and heating is realized directly by heat exchange between refrigerant within the indoor heat exchanger and indoor air.
  • gaseous refrigerant transformed into a high-temperature, high-pressure gas with a compressor is sent to an indoor heat exchanger, and as a result of heat exchange between this refrigerant and indoor air, the refrigerant condenses, realizing a transformation to a high-temperature, high-pressure liquid refrigerant.
  • a high-temperature, high-pressure gaseous refrigerant is sent to an outdoor heat exchanger, where a high-temperature, high-pressure liquid refrigerant is formed as a result of heat exchange with the outside air.
  • the shape of the casing of the indoor unit has conventionally been determined empirically.
  • a tangential fan cross flow fan
  • a typical fan provided in the indoor unit for example, among those widely popular for home use, a tangential fan (cross flow fan) has conventionally been employed as a typical fan provided in the indoor unit.
  • an object of the present invention is to provide indices that facilitate design for improving aerodynamic performance by optimizing the shape of the air blowing system formed in the indoor unit of an air-conditioner, and particularly the shape of the air inflow back wall provided above the inlet of the air duct, and forms of the inflow and discharge of air in the fan air blowing system and the shape of the stabilizer.
  • the present invention provides an indoor unit comprising a tangential fan that suctions in indoor air from an intake port and blows out that air from a blower outlet, an indoor heat exchanger that performs heat exchange between the above indoor air and refrigerant supplied from an outdoor unit, an indoor unit controller composed of various electrical circuit elements, and a casing that houses each of these devices, and provides the following constitution for solving the above problems.
  • a first aspect of the present invention is characterized by f/D being within the range of 0.002 to 0.003 (0.002 ⁇ f/D ⁇ 0.003) when the fan diameter of the above tangential fan is taken to be D, and the width of the intake diaphragm provided on the upstream side of the air duct inlet inside the above casing is taken to be f.
  • a second aspect of the present invention is characterized by g/D being 0.06 or more (0.06 ⁇ g/D) when the fan diameter of the above tangential fan is taken to be D, and the width of the inverted portion of incoming air flow provided on the upstream side of the air duct inlet inside the above casing is taken to be g.
  • a third aspect of the present invention is characterized by e/D being within the range of 0.25 to 0.3 (0.25 ⁇ e/D ⁇ 0.3), and ⁇ being within the range of 80 degrees to 90 degrees (80 degrees ⁇ 90 degrees) when the fan diameter of the above tangential fan is taken to be D, the length of the auxiliary intake path provided on the upstream side of the air duct inlet inside the above casing is taken to be e, and the intake diaphragm angle is taken to be ⁇ .
  • first through third aspects may be designed in combination in a single indoor unit.
  • a concave portion may be formed in the surface that forms width g of the above inverted portion.
  • a fourth aspect of the present invention is characterized by designing such that Wo/D is 0.55 or less (Wo/D ⁇ 0.55) when the fan diameter D of the above tangential fan is taken to be D, and the width of the outlet of the air duct formed between the outer peripheral surface of the above tangential fan and the air duct wall surface of the above casing is taken to be Wo.
  • a fifth aspect of the present invention is characterized by being designed such that the upstream opening angle ⁇ 2, which becomes the negative pressure region on the air upstream side of the above tangential fan, is 180 degrees or more ( ⁇ 2 ⁇ 180 degrees).
  • the upstream opening angle ⁇ 2 which becomes the negative pressure region on the air upstream side of the tangential fan, is ⁇ 2 ⁇ 180 degrees, a reduction in the noise level of the fan air blowing system can be achieved for the same air quantity.
  • a sixth aspect of the present invention is characterized by the stabilizer tongue end angle ⁇ , which is formed between the surface of the stabilizer opposing the above tangential fan and an extended line a, being within the range of 50 degrees to 60 degrees (50 degrees ⁇ 60 degrees) when the fan diameter of the above tangential fan is taken to be D, and a line extending in the direction of flow along the upper surface that forms the discharge port serving as the air duct outlet in the above casing is taken to be a.
  • the stabilizer tongue end angle a is 50 degrees ⁇ 60 degrees, a reduction in the noise level of the fan air blowing system can be achieved for the same air quantity.
  • a seventh aspect of the present invention is characterized by being designed so that the ratio of stabilizer actual height h to fan diameter D is 25% or less (h/D ⁇ 25%) when the fan diameter of the above tangential fan is taken to be D, and the actual height of the stabilizer provided on the upstream side of the above tangential fan is taken to be h.
  • An eighth aspect of the present invention is characterized by providing a guide in the indoor air inflow portion of the stabilizer provided on the upstream side of the above tangential fan that leads the flow of the above indoor air in the direction of roughly the center of the above tangential fan.
  • sixth through eighth aspects may also be designed in combination in a single indoor unit.
  • a ninth aspect of the present invention is characterized by d/D being within the range of -0.2 to 0.2 (-0.2 ⁇ d/D ⁇ 0.2) when the fan diameter of the above tangential fan is taken to be D, and the distance between extended line a in the direction of flow along the upper surface that forms the discharge port serving as the air duct outlet inside the above casing, and the tangent b of the above fan diameter D parallel to said extended line a, is taken to be d.
  • a tenth aspect of the present invention is characterized by the angle ⁇ 1 opening towards the downstream side formed by the line that passes through fan center C perpendicular to the above tangent b, and the line that passes through origin K of the casing coil and fan center C, being within the range of 115 degrees to 125 degrees (115 degrees ⁇ 1 ⁇ 125 degrees) when the fan diameter of the above tangential fan is taken to be D, and the tangent of the above fan diameter D that is parallel to or coincides with extended line a in the direction of flow along the upper surface that forms the discharge port serving as the air duct outlet inside the above casing is taken to be b.
  • An eleventh aspect of the present invention is characterized by air duct width W formed between the outer peripheral surface of the above tangential fan and the air duct wall surface of the above casing having an enlarged linear portion, which increases from the origin to outlet width Wo in proportion to the extended length of the casing air duct center line, and a curved portion on the inlet side that gradually increases from inlet width Wi serving as the above origin and leads to the above enlarged linear portion, and said air duct width W changing.
  • air duct width W has an enlarged linear portion on the outlet side that increases from the origin to outlet width Wo in proportion to the extended length of the casing air duct center line, and a curved portion on the inlet side that gradually increases from inlet width Wi serving as the above origin and leads to the above enlarged linear portion, and allowing said air duct width W to change, a reduction in the noise level of the fan air blowing system can be achieved for the same air quantity.
  • a twelfth aspect of the present invention is characterized by air duct width W formed between the outer peripheral surface of the above tangential fan and the air duct wall surface of the above casing being such that inlet width Wi serving as the origin is within the range of 0.7% to 0.8% of fan diameter D (0.7% ⁇ Wi/D ⁇ 0.8%) when the fan diameter of the above tangential fan is taken to be D.
  • the above ninth through twelfth aspects may be designed in combination in a single indoor unit.
  • the present invention provides an air-conditioner comprising an outdoor heat exchanger, a compressor that feeds a high-temperature, high-pressure gaseous refrigerant to the heat exchanger, an outdoor unit provided with an outdoor unit controller comprised of various electrical circuit elements, and the above indoor unit.
  • an air-conditioner as a result of comprising an indoor unit capable of easily achieving a reduction in the noise level for the same air quantity, an air-conditioner can be provided having superior aerodynamic performance and a high degree of product appeal.
  • the indoor unit and air-conditioner of the present invention described above demonstrate the remarkable effect of improving product appeal by being able to significantly and easily reduce the operating noise of the fan air blowing system in the indoor unit to a greater extent than the prior art, thereby lowering the noise levels of the indoor unit and an air-conditioner that has said indoor unit as a constituent feature.
  • Fig. 1 is an explanatory drawing showing the overall constitution of the air-conditioner.
  • the air-conditioner is composed of indoor unit 10 and outdoor unit 20.
  • This indoor unit 10 and outdoor unit 20 are connected by refrigerant lines 21, through which refrigerant passes, and electrical wiring and so forth not shown.
  • refrigerant lines 21 There are two refrigerant lines 21 provided, and refrigerant flows from indoor unit 10 to outdoor unit 20 through one of the lines, and from outdoor unit 20 to indoor unit 10 through the other.
  • Indoor unit 10 is integrally composed of base 11 serving as a casing and front panel 12.
  • Base 11 is equipped with various equipment including a plate fin tube type of indoor heat exchanger 13 and a roughly cylindrical tangential fan (to be simply referred to as a "fan") 14.
  • Base 11 is also equipped with indoor unit controller 15 composed of various electrical circuit elements and so forth for performing various operational controls relating to indoor unit 10.
  • Indoor unit controller 15 is equipped with a suitable indicator 15a for displaying the operating status and error modes. This indicator 15a can be confirmed visually from the outside through window 12a provided on front panel 12.
  • installation plate 16 is provided on the back of base 11, and this enables indoor unit 10 to be installed on the wall and so forth of a room.
  • Intake grilles (intake ports) 12b are respectively formed in the front and top surfaces of front panel 12. Air inside a room (indoor air) is suctioned into indoor unit 10 from multiple directions by these intake grilles 12b.
  • air filters 17 are equipped behind intake grilles 12b, and act to remove dust in the air and so forth that is suctioned in.
  • blower outlet 12c is formed below front panel 12, and is designed so that warmed air or cooled air (namely, air-conditioned air) is blown out therefrom. Furthermore, this suctioning of air and blowing of air is performed due to the operation of fan 14.
  • the above-mentioned indoor unit 10 is equipped with a remote controller serving as a controller that performs control of various operations.
  • a remote controller serving as a controller that performs control of various operations.
  • switches, a liquid crystal display and so forth are provided on this remote controller 30, and various operation control signals, temperature settings and so forth of the air-conditioner can be transmitted in the form of, for example, infrared signals, towards the receiving unit (not shown) of indoor unit controller 15.
  • partial operational control of the air-conditioner can also be performed by switches not shown provided at appropriate locations on the indoor unit.
  • Outdoor unit 20 is equipped with outdoor heat exchanger 20b, propeller fan 20c, compressor 20f and outdoor unit controller 20g in housing 20a.
  • Outdoor heat exchanger 20b is composed of a refrigeration line equipped with a large number of blade-shaped fins around its periphery, and is for realizing heat exchange between the refrigerant and outside air.
  • Propeller fan 20c continuously brings in fresh air to housing 20a by generating an air flow that escapes from the back to the front inside housing 20a, and is provided to improve the heat exchange efficiency in outdoor heat exchanger 20b.
  • fin guard 20d and fin guard 20e are respectively provided on the sides of housing 20a on which the above outdoor heat exchanger 20b and propeller fan 20c are facing the outside.
  • Fan guard 20d is provided so as to prevent the above blade-shaped fins from being damaged by unexpected impacts from the outside.
  • Fin guard 20e is also similarly provided for the purpose of protecting propeller fan 20c from external impacts.
  • Compressor 20f discharges low-temperature, low-pressure gaseous refrigerant by converting to a high-temperature, high-pressure gaseous refrigerant, and plays the most important role among the components that compose the refrigerant circuit.
  • the refrigerant circuit refers to that which is roughly composed of this compressor 20f as well as the above-mentioned indoor heat exchanger 13, outdoor heat exchanger 20b, refrigerant lines 21, an expansion valve, a four-way valve that determines the direction of refrigerant flow (both the expansion valve and four-way valve are not shown) and so forth, and allows refrigerant to circulate between indoor unit 10 and outdoor unit 20.
  • Outdoor unit controller 20g performs operational control relating to the above-mentioned propeller fan 20c, compressor 20f and various other equipment provided in outdoor unit 20, and is composed of various electrical circuit elements.
  • outdoor unit 20 is also equipped with a base plate 20h to avoid the effects of external vibrations and so forth while also supporting housing 20a.
  • a removable panel 20i for performing maintenance and so forth on the above compressor 20f is provided in the wall of case 20 near the above compressor 20f.
  • the following provides an explanation of the action of the air-conditioner composed of these components, dividing into an explanation of that during heating operation and that during cooling operation.
  • refrigerant that has been transformed into a high-temperature, high-pressure gas in compressor 20f is sent through refrigerant line 21 to indoor heat exchanger 13 of indoor unit 10.
  • indoor heat exchanger 13 Inside indoor unit 10, heat from the high-temperature, high-pressure gaseous refrigerant that passes through indoor heat exchanger 13 is imparted to indoor air taken in from intake grilles 12 by fan 14. As a result, warm air is blown out from blower outlet 12c below front panel 12.
  • high-temperature, high-pressure gaseous refrigerant condenses and liquefies in the above indoor heat exchanger 13 and becomes a high-temperature, high-pressure liquid refrigerant.
  • This high-temperature, high-pressure liquid refrigerant is sent again through refrigerant line 21 to outdoor heat exchanger 20b in outdoor unit 20.
  • outdoor unit 20 In outdoor unit 20, it passes through an expansion valve not shown where its pressure is reduced and it becomes a low-temperature, low-pressure liquid refrigerant.
  • This low-temperature, low-pressure liquid refrigerant that passes through outdoor heat exchanger 20b then takes the heat from fresh outside air that has been taken into housing 20a by propeller fan 20c.
  • This low-temperature, low-pressure liquid refrigerant evaporates to a gas as a result of this, becoming a low-temperature, low-pressure gaseous refrigerant. This is then again sent to compressor 20f where the above process is repeated.
  • the refrigerant flows through the refrigerant circuit in the opposite direction from that described above. Namely, after being transformed into a high-temperature, high-pressure gas in compressor 20f, the refrigerant is sent to outdoor heat exchanger 20b through refrigerant line 21 where it imparts heat to the outside air and condenses and liquefies to become a high-temperature, high-pressure liquid refrigerant.
  • This high-temperature, high-pressure liquid refrigerant passes through an expansion valve not shown and becomes a low-temperature, low-pressure liquid refrigerant, after which it is sent to indoor heat exchanger 13 again through refrigerant line 21.
  • the low-temperature, low-pressure liquid refrigerant takes the heat from the indoor air and together with cooling said indoor air, the refrigerant itself evaporates and vaporizes resulting in the formation of a low-temperature, low-pressure gaseous refrigerant. This is again sent out to compressor 20f where the above process is then repeated.
  • indoor unit controller 15 housed in indoor unit 10
  • outdoor unit controller 20g housed in outdoor unit 20.
  • Fig. 2 used in this explanation is a cross-section taken along arrows A-A of Fig. 1 that shows fan 14 and its air blowing system.
  • a fan air blowing system is provided inside the above-mentioned indoor unit 10 for suctioning in indoor air through intake grilles 12b by operating fan 14, passing that air through indoor heat exchanger 13, and blowing out the air-conditioned air that has undergone heat exchange from blower outlet 12c.
  • Air duct 40 that guides air-conditioned air to blower outlet 12c is provided in this fan air blowing system.
  • Air duct 40 is a space formed between outer peripheral surface 14a of cylindrical fan 14 and air duct wall surface 41 provided in base 11 serving as a constituent member of the casing.
  • Inlet 42 of air duct 40 is on a line that connects fan center C that serves as the axial center during rotation of fan 14 and point K on air duct wall surface 41, and the width of this inlet is represented with Wi.
  • Point K serves as the origin of the casing coil (concave curved surface in the direction of flow of air duct wall surface 41), and when viewed from the side of front panel 12 of indoor unit 10, is roughly positioned behind the upper portion of fan 14 (wall side).
  • Air duct 40 is formed to outlet 43 in the direction of rotation of fan 14 (clockwise direction in the example shown in the drawing) with inlet 42 serving as the origin.
  • the width of air duct 40 namely air duct width W, gradually increases from inlet width Wi of inlet 42 to outlet width Wo of outlet 43.
  • Outlet width Wo is the distance covered by a line perpendicular to air duct center line 44 extending from end point M of the casing coil on casing wall surface 41 to outlet upper surface 45.
  • Front panel 12 is arranged to the front of the direction of flow of outlet 43 (front side of indoor unit 10), and blower outlet 12c of said panel 12 is open facing into the room.
  • louvers (not shown) are arranged near outlet 43 that adjust the blowing direction to the left and right, and flaps (not shown) are arranged in blower outlet 12c that adjust the blowing direction upward and downward.
  • fan 14 is also provided with stabilizer 70, and air inflow back wall 50 located in the upper portion of air duct 40.
  • Air inflow back wall 50 is a portion that is located above inlet 42 of air duct 40 and provided in continuation from air duct wall surface 41, and inverted portion 52 is provided on the end (upper end) of auxiliary intake path 51.
  • Auxiliary intake path 51 is a wall surface that forms a concave portion continuing from origin K of air duct wall surface 41 to wall surface starting point N, and the depth of the concave portion serving as auxiliary intake path 51 (depth from the line connecting origin K and wall surface starting point N to the deepest part of the concave portion) is hereinafter to be referred to as intake diaphragm width f.
  • inverted portion 52 is a portion that is arranged behind air duct wall surface 41 and air inflow back wall 50 that inverts the flow of air-conditioned air so as to guide air-conditioned air that has passed through indoor heat exchanger 13 to air duct 40, and its end shape is composed by providing a first flat portion 53, which forms a roughly vertical surface extending upward from wall surface starting point N to peak P, and a second flat portion 54, which forms a roughly horizontal surface extending backward (back side) from peak P to inverted portion starting point Q. Furthermore, back portion 55 is provided on the back side of auxiliary intake path 51 that forms an inclined surface facing downward on an angle from inverted portion starting point Q.
  • inverted portion width (inverted thickness) g distance KN from origin K to wall surface starting point N is to hereinafter be referred to as auxiliary intake path length e
  • intake diaphragm angle ⁇ the angle from the line connecting fan center C and origin K to line KN that defines auxiliary intake path length e.
  • intake diaphragm width f of the shape of air inflow back wall 50 is defined in the manner explained below in a first embodiment.
  • Intake diaphragm width f is a value indicating the concave depth of the concave wall surface provided in continuation facing upward from inlet 42 (origin K) of air duct wall surface 41 that forms air duct 40, namely auxiliary intake path 51, and indicates the vertical distance from line KN to the deepest part.
  • intake diaphragm width f provided on the upstream side of the air duct inlet inside the casing is set so that the ratio to fan diameter D (f/D) is within the range of 0.002 to 0.003 (0.002 ⁇ f/D ⁇ 0.003).
  • Fig. 3 shows the results of respectively measuring noise level based on the same air quantity by suitably changing the above-mentioned f/D.
  • the noise level was the lowest when f/D was roughly 0.025, and when intake diaphragm width f was increased or decreased from the value corresponding to this minimum noise level, the noise level was found to increase in both cases. Therefore, the range over which ⁇ dB increases 1 dB (A) from f/D at which the noise level is the lowest based on the same air quantity was determined to be the proper design range of intake diaphragm width f, and according to the results shown in Fig. 3, the range of f/D was defined as 0.002 ⁇ f/D ⁇ 0.003.
  • inverted portion width g of the shape of air inflow back wall 50 in the above-mentioned fan air blowing system is defined as explained below.
  • Inverted portion width (inverted thickness) g is the distance NQ from wall surface starting point N to inverted portion starting point Q that indicates the width of inverted portion 52.
  • inverted portion width g of intake air flow provided on the upstream side of the air duct inlet inside the casing is set so that the ratio to fan diameter D (g/D) is 0.06 ⁇ g/D.
  • Fig. 4 shows the results of respectively measuring noise levels based on the same air quantity by suitably changing the above-mentioned g/D.
  • inverted portion width g is made to make the ratio to fan diameter D as described above greater than or equal to 0.06, increasing g/D means that the inverted portion width g becomes thicker.
  • wall thickness of inverted portion 52 which is a plastic molded part integrally formed with base 11, becomes thicker, there is greater susceptibility to strain caused by thermal deformation as a result of being greatly subjected to the effects of thermal contraction during molding. Consequently, the upper limit of inverted portion width g is subject to restriction due to problems in terms of production engineering in the form of the occurrence of thermal deformation.
  • inverted portion 52 that ensures an inverted portion width g capable of reducing noise levels while also increasing resistance to the occurrence of thermal deformation during molding.
  • Fig. 7 shows a variation of inverted portion 52 in which concave portion 56 having a rectangular cross-section is provided on first flat portion 53.
  • the formation of thick walled portion in inverted portion 52 can be prevented while maintaining inverted portion width g.
  • the shape of concave portion 56 is not limited to this, but rather other variations are also effective, including the forming of surface 56a into a concave curved surface.
  • auxiliary intake path length e and intake diaphragm angle ⁇ of air inflow back wall 50 are defined in the manner explained below in a third embodiment in the fan air blowing system described above.
  • Auxiliary intake path length e is the distance KN from origin K to wall surface starting point N
  • intake diaphragm angle ⁇ is the angle from line CK that connects fan center C and origin K to line KN that defines auxiliary intake path length e.
  • the ratio of auxiliary intake path length e provided on the upstream side of the air duct inlet inside the casing to fan diameter D (e/D) is set so as to be within the range of 0.25 ⁇ e/D ⁇ 0.3.
  • intake diaphragm angle ⁇ is set so as to be within the range of 80 degrees ⁇ 90 degrees.
  • Fig. 5 shows the results of respectively measuring noise levels for the same air quantity by suitably changing the above-mentioned angle ⁇ .
  • the noise level is the lowest when e/D is roughly 0.275, and when auxiliary intake path length e is increased or decreased from the value corresponding to this minimum noise level, the noise level was determined to increase in both cases. Therefore, similar to the intake diaphragm width f described above, the range over which ⁇ dB increases 1 dB (A) from e/D for which the noise level is the lowest based on the same air quantity was judged to be the proper design range of intake diaphragm width f, and according to the results shown in Fig. 5, the range of e/D was defined as 0.25 ⁇ e/D ⁇ 0.3.
  • Fig. 6 shows the results of respectively measuring noise levels based on the same air quantity by suitably changing the above-mentioned ⁇ .
  • each of the above embodiments allows the obtaining of the action and effect of improving aerodynamic performance even if each is used alone, if each embodiment is suitably used in combination, namely by using a suitable combination of at least two of the above embodiments, reduction in noise levels of air inflow back wall 50 and the fan air blowing system for the same air quantity can be further promoted due to mutual synergistic effects.
  • indoor unit 10 which is equipped with air inflow back wall 50 having a shape designed using the above-mentioned stipulations, has superior aerodynamic performance with respect to low noise levels of the fan air blowing system and so forth, and is able to improve the product appeal of an air-conditioner having this for its constituent element.
  • outlet width Wo of air duct 40 of the fan air blowing system equipped with air duct 40 described above is defined as explained below in a fourth embodiment. Furthermore, outlet width Wo relates to the discharge form of air-conditioned air flowing out of the fan air blowing system.
  • the ratio of outlet width Wo to fan diameter D is set to be 0.55 or less (Wo/D ⁇ 0.55).
  • Fig. 9 shows the results of respectively measuring noise levels based on the same air quantity by suitably changing the above Wo/D.
  • upstream opening angle ⁇ 2 of the fan air blowing system equipped with the above air duct 40 is defined in the manner explained below in a fifth embodiment. Furthermore, upstream opening angle ⁇ 2 relates to air inflow of air-conditioned air that is introduced into fan 14 in the fan air blowing system.
  • upstream opening angle ⁇ 2 is defined.
  • This upstream opening angle 02 refers to the angle of the negative pressure region on the air inflow side of fan 14, and this upstream opening angle ⁇ 2 is set to be ⁇ 2 ⁇ 180 degrees.
  • upstream opening angle ⁇ it refers to the angle from the line connecting the peak of effective end height h in stabilizer 70 and fan center C to the line connecting origin K of the casing coil and fan center C.
  • stabilizer 70 may have a corrugated shape in which there are peaks and valleys in the end portion of stabilizer 70 as shown in Fig. 11A, or it may have a linear shape in which the end portion has a constant or roughly constant height as shown in Fig. 11B.
  • the effective end height h of stabilizer 70 is defined as the effective stabilizer height from extended line a, and thus, in the case of a corrugated shape, is the height from extended line a to valley 70a, and in the case of a linear shape, the height from extended line a to end portion 70c becomes the actual height h.
  • reference symbol 70b in Fig. 11A indicates a peak of the corrugated shape.
  • Fig. 10 shows the results of respectively measuring noise levels for the same air quantity by suitably changing the above upstream opening angle ⁇ 2.
  • an indoor unit 10 equipped with outlet width Wo and upstream opening angle ⁇ 2 having a shape designed using the above stipulations has superior aerodynamic performance with respect to low noise levels of the fan air blowing system and so forth, and is able to improve the product appeal of an air-conditioner having this for its constituent element.
  • stabilizer 70 and particularly stabilizer tongue end angle ⁇ , in the above fan air blowing system equipped with air duct 40 is defined in the manner explained below in a sixth embodiment.
  • the angle ⁇ formed by stabilizer surface 71 opposing fan 14 and extended line a is referred to as the stabilizer tongue end angle, and this tongue end angle is set to be within the range of 50 degrees to 60 degrees (50 degrees ⁇ 60 degrees).
  • Fig. 13 shows the results of respectively measuring noise levels based on the same air quantity by suitably changing the above stabilizer tongue end angle ⁇ .
  • the noise levels were the lowest when stabilizer tongue end angle ⁇ was set to the vicinity of 57 degrees, and even if this angle was changed in the decreasing direction or increasing direction from this value, the noise level was found to increase. Therefore, the angle over the range in which ⁇ dB increases 1 dB (A) from a reference value based on the noise level corresponding to the stabilizer tongue end angle ⁇ at which noise level is the lowest based on the same air quantity was judged to be the proper design range of stabilizer tongue end angle ⁇ , and according to the results of Fig. 13, the range of stabilizer tongue end angle ⁇ was defined as 50 degrees ⁇ ⁇ 60 degrees.
  • stabilizer 70 shape of stabilizer 70, and particularly the actual height h of stabilizer 70, in the above fan air blowing system equipped with air duct 40 is defined in the manner explained below in a seventh embodiment.
  • Stabilizer 70 may have a corrugated shape in which there are peaks and valleys in the end of stabilizer 70 as shown in Fig. 15A, or a linear shape in which the end has a constant or roughly constant height as shown in Fig. 15B.
  • the actual height h of stabilizer 70 is defined as the effective stabilizer height from extended line a, and thus, the height from extended line a to valley 71a becomes actual height h in the case of the corrugated shape, while the height from extended line a to end 71c becomes actual height h in the case of the linear shape.
  • the above actual height h of stabilizer 70 is set so that h/D is 25% or less (h/D ⁇ 25%) in the case the ratio to fan diameter D of fan 14 is represented as a percentage.
  • Fig. 14 shows the results of respectively measuring noise levels based on the same air quantity by suitably changing the above actual height h.
  • noise level is the lowest in the case h is set to lower than roughly 15%, and when h is increased or decreased from the value of h corresponding to this minimum value, noise level was found to increase in both cases. Therefore, the region within the range over which ⁇ dB increases 1 dB (A) based on this minimum value was judged to be the proper design range, and according to the results shown in Fig. 14, the range of h/D is defined as h/D ⁇ 25%.
  • the lower limit of the actual height h of stabilizer 70 is determined according to the required water receiving height H that is a value higher (larger) than h corresponding to h/D ⁇ 15% at which noise level is the lowest. Furthermore, the required water receiving height H is the value required to prevent outflow of condensed water that has formed in indoor heat exchanger 14.
  • Guide 60 is provided on the indoor air inflow portion of the stabilizer provided on the upstream side of fan 14 so as to introduce the flow of indoor air in the direction of roughly the center of fan 14.
  • This guide 60 is located on the upstream side of stabilizer 70, namely on the side of front panel 12 from stabilizer 70, and is provided in the axial direction of fan 14 and lengthwise direction of stabilizer 70 so as to form air guiding surface 61 that is continuous with the above actual height h of stabilizer 70.
  • each of the above embodiments allows the obtaining of the action and effect of improving aerodynamic performance even if each is used alone, if each embodiment is suitably used in combination, namely by using a suitable combination of at least two of the above embodiments, reduction in noise levels of stabilizer 70 and the fan air blowing system for the same air quantity can be further promoted due to mutual synergistic effects.
  • indoor unit 10 which is equipped with stabilizer 70 having a shape designed using the above-mentioned stipulations, has superior aerodynamic performance with respect to low noise levels of the fan air blowing system and so forth, and is able to improve the product appeal of an air-conditioner having this for its constituent element.
  • the fan diameter of fan 14 is taken to be D
  • the extended line in the direction of flow along outlet upper surface 45 that forms a discharge port in the form of outlet 43 of air duct 40 inside the casing is taken to be a
  • the distance between tangent b of fan diameter D parallel to extended line a and extended line a is taken to be d
  • the ratio of distance d to fan diameter D (d/D) is set to be within the range of -0.2 to 0.2 (-0.2 ⁇ d/D ⁇ 0.2).
  • Fig. 18 shows the results of respectively measuring noise levels based on the same air quantity by suitably changing the above d/D.
  • downstream downward angle ⁇ 1 of the shape of the above air duct 40 is defined in the manner explained below in a tenth embodiment.
  • downstream downward angle ⁇ 1 is defined.
  • the extended line in the direction of flow along outlet upper surface 45 that forms a discharge port in the form of outlet 43 of air duct 40 inside the casing is taken to be a
  • the tangent of fan diameter D that is parallel or coincides with extended line a is taken to be b
  • the angle on the side of air duct wall surface 41 formed by line 81 that is perpendicular to this tangent b and passes through fan center C, and by line 82 that passes through origin K of the casing coil that forms air duct wall surface 41 and fan center C is downstream opening angle ⁇ 1
  • this downstream downward angle ⁇ 1 is set to be within the range of 115 degrees to 125 degrees (115 degrees ⁇ 1 ⁇ 125 degrees).
  • Fig. 19 shows the results of respectively measuring noise levels based on the same air quantity by suitably changing the above ⁇ 1.
  • air duct width W that is formed between outer peripheral surface of fan 14 and air duct wall surface 41 of the shape of the above air duct 40 is defined in the manner explained below in an eleventh embodiment.
  • Air duct width W gradually increases in the direction of flow corresponding to extended length L of casing air duct center line 44 from inlet 42 to outlet 43, and the following provides a discussion of the optimum shape of this increase in width.
  • the change in air duct width W that increases from inlet 42 to outlet 43 consists of (1) a convex shape in which the change on the inlet side is large, (2) a straight line in which the change increases from the inlet to the outlet at a constant rate, and (3) a concave shape in which the change on the outlet side is large.
  • Measurement of noise level based on the same air quantity for each of these three kinds of air duct shapes yielded the results shown in Fig. 21.
  • inlet 42 is required to have inlet width Wi (Wi ⁇ 0), as shown in Fig. 22, it is necessary that air duct width W have a curved portion that increases gradually and smoothly from the origin of inlet width Wi, preferably increasing in the form of the concave curved line shown in (3) of Fig. 20, and is connected to the above-mentioned straight line portion (proportionally increasing portion).
  • the optimum shape of air duct width W should be formed so that air duct width W changes having an expanding linear portion 61 on the side of outlet 43, in which it increases from inlet 42 as the origin to outlet width Wo in proportion to extended length L of air duct center line 44, and curved portion 62 on the side of inlet 42 that is connected to expanding linear portion 61, in which it increases gradually from inlet width Wi as the origin.
  • inlet width Wi of the shape of the above air duct 40 is defined in the manner explained below in a twelfth embodiment.
  • the ratio of inlet width Wi to fan diameter D (Wi/D) in terms of a percentage is set to be within the range of 0.7% to 0.8% (0.7% ⁇ Wi/D ⁇ 0.8%).
  • Fig. 23 shows the results of respectively measuring noise levels based on the same air quantity by suitably changing the above Wi/D.
  • the case of setting Wi/D to about 0.75% results in the lowest noise level, and it was found that noise level tends to increase when this ratio is either increased or decreased. Therefore, similar to distance d previously described, the range over which ⁇ dB increases 1 dB (A) from inlet width Wi for which the noise level is the lowest based on the same air quantity was judged to be the proper design range of inlet width Wi, and according to the results shown in Fig. 23, the range of Wi/D was defined as 0.7% ⁇ Wi/D ⁇ 0.8%.
  • each of the above embodiments allows the obtaining of the action and effect of improving aerodynamic performance even if each is used alone, if each embodiment is suitably used in combination, namely by using a suitable combination of at least two of the above embodiments, reduction in noise levels of air duct 40 and the fan air blowing system for the same air quantity can be further promoted due to mutual synergistic effects.
  • indoor unit 10 which is equipped with air duct 40 having a shape designed using the above-mentioned stipulations, has superior aerodynamic performance with respect to low noise levels of the fan air blowing system and so forth, and is able to improve the product appeal of an air-conditioner having this for its constituent element.
  • the constitution of the present invention is not limited to the above-mentioned embodiments, but rather may be suitably changed within a range that does not deviate from the gist of the present invention.

Landscapes

  • 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)
  • Air-Flow Control Members (AREA)
EP02006380A 2001-03-23 2002-03-21 Unité intérieure et conditionneur d'air Expired - Lifetime EP1243864B1 (fr)

Applications Claiming Priority (8)

Application Number Priority Date Filing Date Title
JP2001084416A JP2002276585A (ja) 2001-03-23 2001-03-23 室内機ユニット及び空気調和機
JP2001084413 2001-03-23
JP2001084413A JP3564414B2 (ja) 2001-03-23 2001-03-23 室内機ユニット及び空気調和機
JP2001084415A JP3621892B2 (ja) 2001-03-23 2001-03-23 室内機ユニット及び空気調和機
JP2001084415 2001-03-23
JP2001084416 2001-03-23
JP2001084414A JP2002276975A (ja) 2001-03-23 2001-03-23 室内機ユニット及び空気調和機
JP2001084414 2001-03-23

Publications (3)

Publication Number Publication Date
EP1243864A2 true EP1243864A2 (fr) 2002-09-25
EP1243864A3 EP1243864A3 (fr) 2003-01-02
EP1243864B1 EP1243864B1 (fr) 2007-10-10

Family

ID=27482133

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02006380A Expired - Lifetime EP1243864B1 (fr) 2001-03-23 2002-03-21 Unité intérieure et conditionneur d'air

Country Status (5)

Country Link
EP (1) EP1243864B1 (fr)
CN (1) CN1282853C (fr)
AT (1) ATE375483T1 (fr)
DE (1) DE60222823D1 (fr)
ES (1) ES2291387T3 (fr)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009054588A1 (fr) 2007-10-22 2009-04-30 Lg Electronics Inc. Climatiseur
EP2664799A1 (fr) * 2004-10-01 2013-11-20 Mitsubishi Electric Corporation Climatiseur
EP3088806A4 (fr) * 2013-12-27 2017-03-01 Daikin Industries, Ltd. Climatiseur intérieur
US9803340B2 (en) 2016-03-17 2017-10-31 Komatsu Ltd. Control system for work vehicle, control method, and work vehicle
CN107490066A (zh) * 2017-08-25 2017-12-19 武汉凌达压缩机有限公司 室内机和空调系统
CN107490064A (zh) * 2017-08-25 2017-12-19 重庆凌达压缩机有限公司 室内机和空调系统
CN111997936A (zh) * 2020-08-27 2020-11-27 华中科技大学 一种可调节蜗舌装置及贯流风机
CN112253541A (zh) * 2020-09-25 2021-01-22 宁波方太厨具有限公司 一种离心风机的蜗壳型线生成方法、蜗壳和离心风机
CN112432355A (zh) * 2020-12-03 2021-03-02 珠海格力电器股份有限公司 蜗壳组件、送风组件和空调系统
CN114636197A (zh) * 2022-03-31 2022-06-17 广东美的白色家电技术创新中心有限公司 贯流风机及空调器
WO2023236680A1 (fr) * 2022-06-07 2023-12-14 珠海格力电器股份有限公司 Ensemble conduit d'air, ventilateur à flux transversal et dispositif de climatisation
EP4310404A4 (fr) * 2021-03-19 2024-04-10 Mitsubishi Electric Corporation Unité intérieure et dispositif de climatisation

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100343595C (zh) * 2003-05-20 2007-10-17 乐金电子(天津)电器有限公司 空调器室内机的风扇罩
CN103486661B (zh) * 2012-06-13 2016-08-03 珠海格力电器股份有限公司 风管室内机
CN103486664B (zh) * 2012-06-13 2015-12-09 珠海格力电器股份有限公司 室内机
US11396879B2 (en) * 2016-09-30 2022-07-26 Daikin Industries, Ltd. Cross-flow blower and indoor unit of air-conditioning device equipped with same
CN107490067B (zh) * 2017-08-25 2022-11-15 珠海凌达压缩机有限公司 室内机和空调系统

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4014625A (en) * 1973-08-20 1977-03-29 Teruo Yamamoto Transverse flow fan
JPH0771781A (ja) * 1993-08-31 1995-03-17 Mitsubishi Heavy Ind Ltd 空気調和機
JPH07305695A (ja) * 1995-04-14 1995-11-21 Sanyo Electric Co Ltd 空気調和機
EP0930472A2 (fr) * 1998-01-19 1999-07-21 Mitsubishi Denki Kabushiki Kaisha Ventilateur à courant transversal
US5943878A (en) * 1998-05-22 1999-08-31 American Standard Inc. Tangential fan scroll and discharged diffuser design
JP2000009098A (ja) * 1998-06-22 2000-01-11 Pacific Ind Co Ltd 壁掛け式の浴室暖房乾燥機
JP2000291594A (ja) * 1999-04-05 2000-10-17 Sharp Corp クロスフローファン

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4014625A (en) * 1973-08-20 1977-03-29 Teruo Yamamoto Transverse flow fan
JPH0771781A (ja) * 1993-08-31 1995-03-17 Mitsubishi Heavy Ind Ltd 空気調和機
JPH07305695A (ja) * 1995-04-14 1995-11-21 Sanyo Electric Co Ltd 空気調和機
EP0930472A2 (fr) * 1998-01-19 1999-07-21 Mitsubishi Denki Kabushiki Kaisha Ventilateur à courant transversal
US5943878A (en) * 1998-05-22 1999-08-31 American Standard Inc. Tangential fan scroll and discharged diffuser design
JP2000009098A (ja) * 1998-06-22 2000-01-11 Pacific Ind Co Ltd 壁掛け式の浴室暖房乾燥機
JP2000291594A (ja) * 1999-04-05 2000-10-17 Sharp Corp クロスフローファン

Non-Patent Citations (4)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 1995, no. 06, 31 July 1995 (1995-07-31) & JP 07 071781 A (MITSUBISHI HEAVY IND LTD), 17 March 1995 (1995-03-17) *
PATENT ABSTRACTS OF JAPAN vol. 1996, no. 03, 29 March 1996 (1996-03-29) & JP 07 305695 A (SANYO ELECTRIC CO LTD), 21 November 1995 (1995-11-21) *
PATENT ABSTRACTS OF JAPAN vol. 2000, no. 04, 31 August 2000 (2000-08-31) & JP 2000 009098 A (PACIFIC IND CO LTD;OSAKA GAS CO LTD), 11 January 2000 (2000-01-11) *
PATENT ABSTRACTS OF JAPAN vol. 2000, no. 13, 5 February 2001 (2001-02-05) -& JP 2000 291594 A (SHARP CORP), 17 October 2000 (2000-10-17) *

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2664799A1 (fr) * 2004-10-01 2013-11-20 Mitsubishi Electric Corporation Climatiseur
WO2009054588A1 (fr) 2007-10-22 2009-04-30 Lg Electronics Inc. Climatiseur
EP2203688A1 (fr) * 2007-10-22 2010-07-07 Lg Electronics Inc. Climatiseur
EP2203688A4 (fr) * 2007-10-22 2011-06-29 Lg Electronics Inc Climatiseur
EP3088806A4 (fr) * 2013-12-27 2017-03-01 Daikin Industries, Ltd. Climatiseur intérieur
US10443214B2 (en) 2016-03-17 2019-10-15 Komatsu Ltd. Control system for work vehicle, control method, and work vehicle
US9803340B2 (en) 2016-03-17 2017-10-31 Komatsu Ltd. Control system for work vehicle, control method, and work vehicle
CN107490066A (zh) * 2017-08-25 2017-12-19 武汉凌达压缩机有限公司 室内机和空调系统
CN107490064A (zh) * 2017-08-25 2017-12-19 重庆凌达压缩机有限公司 室内机和空调系统
CN111997936A (zh) * 2020-08-27 2020-11-27 华中科技大学 一种可调节蜗舌装置及贯流风机
CN111997936B (zh) * 2020-08-27 2021-04-06 华中科技大学 一种可调节蜗舌装置及贯流风机
CN112253541A (zh) * 2020-09-25 2021-01-22 宁波方太厨具有限公司 一种离心风机的蜗壳型线生成方法、蜗壳和离心风机
CN112432355A (zh) * 2020-12-03 2021-03-02 珠海格力电器股份有限公司 蜗壳组件、送风组件和空调系统
EP4310404A4 (fr) * 2021-03-19 2024-04-10 Mitsubishi Electric Corporation Unité intérieure et dispositif de climatisation
CN114636197A (zh) * 2022-03-31 2022-06-17 广东美的白色家电技术创新中心有限公司 贯流风机及空调器
CN114636197B (zh) * 2022-03-31 2023-09-08 广东美的白色家电技术创新中心有限公司 贯流风机及空调器
WO2023236680A1 (fr) * 2022-06-07 2023-12-14 珠海格力电器股份有限公司 Ensemble conduit d'air, ventilateur à flux transversal et dispositif de climatisation

Also Published As

Publication number Publication date
CN1376878A (zh) 2002-10-30
ATE375483T1 (de) 2007-10-15
CN1282853C (zh) 2006-11-01
DE60222823D1 (de) 2007-11-22
ES2291387T3 (es) 2008-03-01
EP1243864B1 (fr) 2007-10-10
EP1243864A3 (fr) 2003-01-02

Similar Documents

Publication Publication Date Title
EP1243864A2 (fr) Unité intérieure et conditionneur d'air
CN109891155B (zh) 室内机及空调装置
JP5805214B2 (ja) 室外機及びこの室外機を備えた冷凍サイクル装置
EP2618066A1 (fr) Soufflante pour unité extérieure, unité extérieure et dispositif à cycle de réfrigération
EP2757268B1 (fr) Ventilateur sirocco et appareil de climatisation
US20110127019A1 (en) Bell-mouth structure of air blower
US11029058B2 (en) Air conditioner
US20190101131A1 (en) Centrifugal Blower, Air Conditioner, and Refrigeration Cycle Apparatus
CN210772705U (zh) 室内机以及空调机
JP3593106B2 (ja) 室内ユニット及び空気調和機
KR100441101B1 (ko) 일체형 공기조화기의 전선고정구조
JP3564414B2 (ja) 室内機ユニット及び空気調和機
EP2096365B1 (fr) Unité de source de chaleur installée dans un bâtiment
AU2019448451B2 (en) Indoor unit of air-conditioning apparatus
JP3621892B2 (ja) 室内機ユニット及び空気調和機
CN116391097A (zh) 室内机和制冷循环装置
CN116490736B (zh) 壁挂式空调室内机及空调装置
JP7209844B2 (ja) 吹出グリル、室内機及び空気調和装置
WO2022195834A1 (fr) Unité intérieure et dispositif de climatisation
CN213300271U (zh) 窗式空调器
CN221570669U (zh) 空调室内机
WO2024189871A1 (fr) Unité intérieure pour climatiseur et climatiseur équipé de celle-ci
JP2010216750A (ja) 空気調和機
KR20040020709A (ko) 일체형 공기조화기
JP6056471B2 (ja) 冷凍空調装置

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20020321

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

RIC1 Information provided on ipc code assigned before grant

Free format text: 7F 24F 1/00 A, 7F 24F 13/24 B, 7F 04D 17/04 B

AKX Designation fees paid

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

17Q First examination report despatched

Effective date: 20051108

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RIN1 Information on inventor provided before grant (corrected)

Inventor name: KONDOU, FUMIO,C/O MITSUBISHI HEAVY INDUSTRIES

Inventor name: SUZUKI, KAZUHIRO,C/O MITSUBISHI HEAVY INDUSTRIES

Inventor name: SUENAGA, KIYOSHI,C/O MITSUBISHI HEAVY INDUSTRIES

Inventor name: IZUMI, HAJIME,C/O MITSUBISHI HEAVY INDUSTRIES

Inventor name: MAENO, MASASHI,C/O MITSUBISHI HEAVY INDUSTRIES

Inventor name: TOMINAGA, TETSUO,C/O MITSUBISHI HEAVY INDUSTRIES

Inventor name: MIYAZAWA, KENICHI/O MITSUBISHI HEAVY INDUSTRIES

Inventor name: OKADA, YUUJI,C/O MITSUBISHI HEAVY INDUSTRIES

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Ref country code: GB

Ref legal event code: 746

Effective date: 20071024

REF Corresponds to:

Ref document number: 60222823

Country of ref document: DE

Date of ref document: 20071122

Kind code of ref document: P

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2291387

Country of ref document: ES

Kind code of ref document: T3

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080110

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20071010

Ref country code: LI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20071010

Ref country code: CH

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20071010

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080310

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20071010

EN Fr: translation not filed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20071010

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20071010

26N No opposition filed

Effective date: 20080711

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080725

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080331

Ref country code: DE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080111

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080111

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080321

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20071010

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20071010

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080321

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20071010

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150321

REG Reference to a national code

Ref country code: GB

Ref legal event code: 732E

Free format text: REGISTERED BETWEEN 20171214 AND 20171222

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150321

PGRI Patent reinstated in contracting state [announced from national office to epo]

Ref country code: IT

Effective date: 20180516

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20190320

Year of fee payment: 18

Ref country code: IT

Payment date: 20190326

Year of fee payment: 18

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 20190402

Year of fee payment: 18

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20200321

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200321

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20210804

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200322

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210331