EP2345852B1 - Indoor unit of floor-type air conditioner - Google Patents
Indoor unit of floor-type air conditioner Download PDFInfo
- Publication number
- EP2345852B1 EP2345852B1 EP09816001.3A EP09816001A EP2345852B1 EP 2345852 B1 EP2345852 B1 EP 2345852B1 EP 09816001 A EP09816001 A EP 09816001A EP 2345852 B1 EP2345852 B1 EP 2345852B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- extension portion
- impeller
- centrifugal fan
- impeller disk
- indoor unit
- 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.)
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Links
- 239000003507 refrigerant Substances 0.000 description 15
- 239000011810 insulating material Substances 0.000 description 4
- 230000000052 comparative effect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 230000000452 restraining effect Effects 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 238000007664 blowing Methods 0.000 description 1
- 230000001143 conditioned effect Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 239000000428 dust Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 238000009413 insulation Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/288—Part of the wheel having an ejecting effect, e.g. being bladeless diffuser
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
- F04D29/442—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps rotating diffusers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- 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
- F24F1/0014—Indoor units, e.g. fan coil units characterised by air outlets having two or more outlet openings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- 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
- F24F1/005—Indoor units, e.g. fan coil units characterised by mounting arrangements mounted on the floor; standing on the floor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- 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
- F24F1/0022—Centrifugal or radial fans
-
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
- F24F13/20—Casings or covers
- F24F2013/205—Mounting a ventilator fan therein
Definitions
- the present invention relates to an indoor unit of a floor-type air conditioner having a centrifugal fan generating an air flow in centrifugal direction.
- KR 2003 0089142 discloses an indoor unit of an air conditioner which aims to improve efficiency and noise reduction of a turbo fan by preventing back flow phenomenon generated between a bell mouth and a shroud.
- a back flow preventing rib is placed on a blow guiding plate of an indoor unit of an air conditioner to prevent back flow phenomenon by cutting off air flowing back between a bell mouth and a shroud.
- the back flow preventing rib is formed annularly, and extended from a rear side of the blow guiding plate on an outside of the bell mouth to an outside of a turbo fan.
- An end of the back flow preventing rib is formed within 15-30% of width of a blade of the turbo fan to cover some of the outlet of the turbo fan.
- Air passed through the turbo fan by the back flow preventing rib is stopped from flowing back between the bell mouth and the shroud to be smoothly discharged into a room through a discharge port. Air volume discharged from the indoor unit is increased by prevention of back flow phenomenon to improve efficiency of the turbo fan and reduce noise of the indoor unit.
- a known indoor unit of an air conditioner is arranged such that, by using a centrifugal fan housed in a casing, air sucked through an inlet port on the front of the casing is arranged to be an air flow in centrifugal direction, and the air flow is blown out from an inlet port provided around the outlet port (see e.g. Patent Document 1).
- the air flow blown out from the centrifugal fan in centrifugal direction collides a guide wall (fan casing) which is radially outside the centrifugal fan, so that the air flow is guided to the outlet port.
- Patent Document 1 Japanese Unexamined Patent Publication No. 2007-183013
- Patent Document 1 The indoor unit of Patent Document 1, however, is disadvantageous in that noise is generated because the air flow blown out from the centrifugal fan in centrifugal direction collides the guide wall (fan casing).
- the present invention was done to solve this problem and hence an object of the present invention is to provide an indoor unit of a floor-type air conditioner which is capable of restraining noise caused by the collision of air blown out from a centrifugal fan onto a casing or the like.
- An indoor unit of a floor-type air conditioner includes: a centrifugal fan which generates an air flow in centrifugal direction; a fan motor which has a motor shaft attached to the centrifugal fan and is configured to rotate the centrifugal fan; and a casing which stores the centrifugal fan and has an inlet port sucking air from outside to supply the air to the centrifugal fan and an outlet port which blows out an air flow generated by the centrifugal fan to the outside, wherein, the centrifugal fan includes an impeller disk (main blade), an impeller shroud (sub blade) on the inlet port side of the impeller disk (main blade), and a plurality of blades provided between the impeller disk (main blade) and the impeller shroud (sub blade), the impeller disk (main blade) has a first extension portion which extends from an outer periphery of the impeller disk (main blade) toward the outside of outer peripheries of the blades and is linearly inclined toward the in
- This indoor unit of the floor-type air conditioner arranges, by means of the first extension portion and the second extension portion, an air flow blown out in centrifugal direction from the space between the impeller disk (main blade) and the impeller shroud (sub blade) to be an air flow toward the outlet ports.
- the indoor unit is able to form a smooth air flow which moves from the centrifugal fan to the outlet ports in the casing without colliding the casing or the like. As a result, it is possible to restrain the noise caused by the collision of an air flow blown out from the centrifugal fan onto the casing or the like.
- the angle of inclination of the first extension portion on the impeller disk (main blade) side where the air flow blown out from the centrifugal fan is fast is arranged to be smaller than that of the second extension portion, the fast air flow on the impeller disk (main blade) side is directed toward the outlet ports without being sharply diverted.
- the indoor unit of the floor-type air conditioner includes: a centrifugal fan which generates an air flow in centrifugal direction; and a casing which stores the centrifugal fan and has an inlet port which sucks air from outside to supply the air to the centrifugal fan and outlet port which blows out an air flow generated by the centrifugal fan to the outside, wherein the centrifugal fan includes an impeller disk (main blade), an impeller shroud (sub blade) on the inlet port side of the impeller disk (main blade), and a plurality of blades provided between the impeller disk (main blade) and the impeller shroud (sub blade), the impeller disk (main blade) has a first extension portion which extends from an outer periphery of the impeller disk (main blade) toward the outside of outer peripheries of the blades and curves toward the inlet port, the impeller shroud (sub blade) includes a second extension portion which extends from an outer periphery of the
- the indoor unit of the floor-type air conditioner is arranged so that the second extension portion on the impeller shroud (sub blade) side, where the air flow is slow, is curved. This facilitates airflow to the outlet ports.
- the indoor unit of the floor-type air conditioner according to any one of the first to second aspects of the invention is arranged so that the external diameter of the first extension portion is identical with the external diameter of the second extension portion.
- the first extension portion and the second extension portion are efficiently extended in the casing which defines the maximum size of the external diameter of the centrifugal fan.
- the indoor unit of the floor-type air conditioner according to any one of the first to third aspects of the invention is arranged so that the first extension portion is formed along the entire outer periphery of the impeller disk (main blade), and the second extension portion is formed along the entire outer periphery of the impeller shroud (sub blade).
- This indoor unit of the floor-type air conditioner allows the air flow blown out in centrifugal direction to be equally directed to the outlet ports from the entire outer peripheries of the impeller disk (main blade) and the impeller shroud (sub blade).
- an air flow blown out in centrifugal direction from the space between the impeller disk (main blade) and the impeller shroud (sub blade) are arranged to be an air flow toward the outlet ports. Therefore, the indoor unit is able to form a smooth air flow which moves from the centrifugal fan to the outlet ports in the casing without colliding the casing or the like. As a result, it is possible to restrain the noise caused by the collision of an air flow blown out from the centrifugal fan onto the casing or the like.
- the angle of inclination of the first extension portion on the impeller disk (main blade) side where the air flow blown out from the centrifugal fan is fast is arranged to be smaller than that of the second extension portion, the fast air flow on the impeller disk (main blade) side is directed toward the outlet ports without being sharply diverted.
- the second extension portion on the impeller shroud (sub blade) side, where the air flow is slow is curved. This facilitates airflow to the outlet ports.
- the first extension portion and the second extension portion are efficiently extended in the casing which defines the maximum size of the external diameter of the centrifugal fan.
- the first extension portion is formed along the entire outer periphery of the impeller disk (main blade), and the second extension portion is formed along the entire outer periphery of the impeller shroud (sub blade).
- Fig. 1 is a circuit diagram of a refrigerant circuit of an air conditioner according to the present invention.
- Fig. 2 is an oblique perspective showing the appearance of the floor-type indoor unit.
- Fig. 3 is a cross section of the floor-type indoor unit shown in Fig. 2 according to a Reference Example.
- Fig. 4 is an elevation view showing the internal structure of the floor-type indoor unit shown in Fig. 2 .
- an air conditioner according to the present invention will be described with reference to Fig. 1 to Fig. 4 .
- An air conditioner 100 is an apparatus for supplying conditioned air into a room, and includes, as shown in Fig. 1 , a floor-type indoor unit (hereinafter, indoor unit) 1 disposed in the room, an outdoor unit 2 disposed outside the room, and a connection pipe 3 connecting the indoor unit 1 with the outdoor unit 2.
- the components and valves housed in the indoor unit 1 and the outdoor unit 2 and the connection pipe 3 are connected with one another and constitute a refrigerant circuit.
- the refrigerant circuit is chiefly made up of an indoor heat exchanger 10, an outdoor heat exchanger 20, an accumulator 21, a compressor 22, a four-pass switching valve 23, and an electric expansion valve 24.
- the four-pass switching valve 23 is switched to the position indicated by the solid line, when heating.
- a hot high-pressure refrigerant discharged from the compressor 22 flows into the indoor heat exchanger 10 via the four-pass switching valve 23.
- the refrigerant condensed in the indoor heat exchanger (condenser) 10 is depressurized by the electric expansion valve 24 and then flows into the outdoor heat exchanger 20.
- the refrigerant evaporated in the outdoor heat exchanger (evaporator) 20 returns to the sucking side of the compressor 22 via the four-pass switching valve 23 and the accumulator 21.
- the air around the indoor heat exchanger 10 is heated and hot air is supplied into the room.
- the four-pass switching valve 23 is switched to the position indicated by a dotted line.
- the hot high-pressure refrigerant discharged from the compressor 22 flows into the outdoor heat exchanger 20 via the four-pass switching valve 23.
- the refrigerant condensed in the outdoor heat exchanger (condenser) 20 is depressurized by the electric expansion valve 24, and then flows into the indoor heat exchanger 10.
- the refrigerant evaporated in the indoor heat exchanger (evaporator) 10 returns to the sucking side of the compressor 22 via the four-pass switching valve 23 and the accumulator 21.
- the air around the indoor heat exchanger 10 is cooled and cool air is supplied to the room.
- the outdoor unit 2 includes the compressor 22, the four-pass switching valve 23 connected to the discharging side of the compressor 22, the accumulator 21 connected to the sucking side of the compressor 22, the outdoor heat exchanger 20 connected to the four-pass switching valve 23, the electric expansion valve 24 connected to the outdoor heat exchanger 20, and an outdoor fan 25 attached to the outdoor heat exchanger 20.
- the electric expansion valve 24 is connected to a liquid refrigerant pipe 31, and is further connected to one end of the indoor heat exchanger 10 via the liquid refrigerant pipe 31.
- the four-pass switching valve 23 is connected to a gas refrigerant pipe 32, and is further connected to the other end of the indoor heat exchanger 10 via the gas refrigerant pipe 32.
- the refrigerant pipes 31 and 32 are equivalent to the above-described connection pipe 3.
- the indoor unit 1 is, as shown in Fig. 2 and Fig. 3 , a floor-type indoor unit and chiefly includes a casing unit 50, an indoor heat exchanger 10 housed in the casing unit 50, a fan unit 60, and a shutter unit 70.
- the casing unit 50 constituting the contour of the indoor unit 1 includes a front panel 51, a front grill 52, a bottom frame 53, and a back heat-insulating material 54. These components are disposed in the order of, from the front side of the indoor unit 1, the front panel 51, the front grill 52, the bottom frame 53, and the back heat-insulating material 54.
- the space formed inside the casing unit 50 is, as shown in Fig. 4 , divided into a fan chamber 50A in which the indoor heat exchanger 10, the fan unit 60 and the like are provided, and a pipe chamber 50B in which electric units or the like are provided.
- the front panel 51 is, as shown in Fig. 2 and Fig. 3 , attached to cover a filter 55 which is attached to the front grill 52.
- At the top of this front panel 51 is provided an upper inlet port 51a, whereas at the bottom of the front panel 51 is provided a lower inlet port 51b.
- Furthermore, on the both sides of the front panel 51 are formed side inlet ports 51c.
- the upper inlet port 51a and the lower inlet port 51b are long in the width directions (X directions) whereas the side inlet ports 51c are long in the vertical directions (Z directions). These ports allow the unit to suck indoor air in four directions, i.e. from above, from below, from left, and from right, and the air sucked through the inlet ports 51a, 51b, and 51c are evenly passes through the indoor heat exchanger 10.
- the front grill 52 is, as shown in Fig. 2 and Fig. 3 , provided between the front panel 51 and the indoor heat exchanger 10.
- At the top of the front grill 52 is provided an upper outlet port 52a, whereas at the bottom of the front grill 52 is provided a lower outlet port 52b.
- These upper outlet port 52a and the lower outlet port 52b are both long in the width directions (X directions).
- At the center of the front grill 52 is formed a substantially rectangular parallelepiped opening 52c. This opening 52c is provided with a filter 55 to catch the dust in the air sucked through the inlet ports 51a, 51b, and 51c of the front panel 51.
- the bottom frame 53 is, as shown in Fig. 3 , disposed between the later-described fan unit 60 and the back heat-insulating material 54.
- This bottom frame 53 includes a bottom portion 53a forming the bottom of the indoor unit 1 and a standing portion 53b standing on the bottom portion 53a.
- the bottom portion 53a is provided with a pipe introducing hole 53c to introduce the connection pipe 3 into the pipe chamber 50B (see Fig. 4 ).
- Substantially at the center of the standing portion 53b is provided a fan attaching portion 53d for attaching the fan unit 60 thereto.
- the back heat-insulating material 54 is provided on the back side of the bottom frame 53 for heat insulation.
- an upper air duct 50a is formed to connect a later-described turbofan 62 with the upper outlet port 52a.
- This upper air duct 50a is formed along the inner wall surface of the bottom frame 53.
- This duct 50a curves and extends forward and upward from the turbofan 62 to the upper outlet port 52a.
- a vertical flap 40 by which the direction of air flow blown out from the upper outlet port 52a is controlled in regard to the horizontal direction and a horizontal flap 41 by which the direction of air flow is controlled in regard to the vertical direction.
- a lower air duct 50b is formed to connect the turbofan 62 with the lower outlet port 52b.
- the lower air duct 50b curves and extends forward and downward from the turbofan 62 to the lower outlet port 52b. Above this lower air duct 50b is provided a vertical flap 42 by which the direction of air flow blown out from the lower outlet port 52b is controlled in regard to the horizontal direction. On the windward side of the vertical flap 42 is provided a later-described shutter 72.
- the indoor heat exchanger 10 is provided for conducting heat exchange with the indoor air.
- This indoor heat exchanger 10 is, as shown in Fig. 3 , provided between the fan unit 60 and the front grill 52 and conducts heat exchange on the windward side of the fan unit 60.
- a bell-mouth 11 guides the air having passed through the indoor heat exchanger 10 to the later-described turbofan 62 (opening 64a).
- Fig. 5 is a Reference Example of a schematic cross section of an unclaimed fan unit and bottom frame.
- Fig. 6 turbofan shown in is an oblique perspective of the turbofan shown in Fig.5
- Fig. 7 is an elevation of the turbofan shown in Fig. 5
- Fig. 8 is a cross section taken along the A-A line in Fig. 7 .
- the fan unit 60 will be detailed with reference to drawings such as Fig. 5 to Fig. 8 , and is provided for background information.
- the fan unit 60 includes a fan motor 61 which is a drive source and provided on the leeward side of the indoor heat exchanger 10 and the turbofan 62 which is a type of centrifugal fan generating an air flow in centrifugal direction.
- the air flow generated by this fan unit 60 is blown out from the upper outlet port 52a via the above-described upper air duct 50a and from the lower outlet port 52b via the lower air duct 50b.
- the fan motor 61 is attached to the fan attaching portion 53d (see Fig. 3 ) of the standing portion 53b of the bottom frame 53.
- the motor shaft 61a of this fan motor 61 extends in the front-back directions (Y directions), and rotates about a rotational axis extending in the front-back directions.
- the turbofan 62 is attached to the motor shaft 61a of the fan motor 61 and rotates in accordance with the rotation of the motor shaft 61a.
- This turbofan 62 includes, as shown in Fig. 5 to Fig. 8 , a impeller disk (main blade) 63, a impeller shroud (sub blade) 64 opposing the impeller disk (main blade) 63, and seven blades 65 provided between the impeller disk (main blade) 63 and the impeller shroud (sub blade) 64.
- the impeller disk (main blade) 63 is substantially disc-shaped in elevation, and a protrusion 63a protruding toward the impeller shroud (sub blade) 64 is formed at its center.
- This protrusion 63a is formed to correspond to the fan motor 61, and is attached to the above-described motor shaft 61a.
- a flat portion 63b is formed to extend along the plane orthogonal to the above-described motor shaft 61a.
- the impeller disk (main blade) 63 further has an extension portion 63c which linearly extends from the outer periphery of the impeller disk (main blade) 63 toward the outside of the outer peripheries of the seven blades 65.
- This extension portion 63c is inclined for an angle of theta (see Fig. 5 ) toward the impeller shroud (sub blade) 64, with respect to the flat portion 63b.
- the extension portion 63c is arranged to be close to the impeller shroud (sub blade) 64 toward its leading end.
- the impeller shroud (sub blade) 64 is spaced apart from the impeller disk (main blade) 63 and is on the port 52a side and on the port 52b side of the impeller disk (main blade) 63.
- This impeller shroud (sub blade) 64 is substantially ring-shaped in elevation and an opening 64a formed at its center functions as an air inlet.
- the impeller shroud (sub blade) 64 has an extension portion 64b which curves and extends from the outer periphery of the impeller shroud (sub blade) 64 toward the outside of the outer peripheries of the seven blades 65. This extension portion 64b is inclined away from the impeller disk (main blade) 63.
- extension portion 64b is arranged to be close to the outlet ports 52a and 53b toward its leading end.
- the impeller shroud (sub blade) 64 is further provided with an extension portion 64c which curves and extends inward from its inner periphery. This extension portion 64c is inclined away from the impeller disk (main blade) 63 in the same manner as the extension portion 64b described above. More specifically, the extension portion 64c is arranged to be close to the outlet ports 52a and 52b toward its leading end.
- the extension portion 63c of the above-described impeller disk (main blade) 63 is formed along the entirety of the outer periphery, and the extension portion 64b of the impeller shroud (sub blade) 64 is formed along the entirety of the outer periphery. Furthermore, as shown in Fig. 5 , the external diameter R1 of the extension portion 63c is identical with the external diameter R2 of the extension portion 64b.
- the seven blades 65 are, as shown in Fig. 7 , provided at predetermined intervals and angles along the direction of the rotation of the turbofan 62.
- the turbofan 62 rotates, the air having passed through the indoor heat exchanger 10 is sucked into the turbofan 62 via the opening 64a, with the result that an air flow in centrifugal direction is generated.
- This air flow in centrifugal direction is directed toward the outlet ports 52a and 52b of the indoor unit 1 by the extension portion 63c of the impeller disk (main blade) 63 and the extension portion 64b of the impeller shroud (sub blade) 64.
- the air flow blown out from the upper part of the turbofan 62 progresses along the upper air duct 50a and is then blown out from the casing unit 50 through the upper outlet port 52a.
- the air flow blown out from the lower part of the turbofan 62 progresses along the lower air duct 50b and is then blown out from the casing unit 50 through the lower outlet port 52b.
- FIG. 9 and Fig. 10 are an oblique perspective when the shutter unit is viewed from the back side.
- Fig. 11 is a cross section of the shutter unit when the shutter is open.
- Fig. 12 is a cross section of the shutter unit when the shutter is closed.
- the shutter unit 70 will be detailed with reference to drawings such as Fig. 9 to Fig. 12 .
- the shutter unit 70 is provided around the lower outlet port 52b and determines whether the air flow from the turbofan 62 to the lower outlet port 52b is allowed to be blown to the outside, by opening or closing a port 50c on the lower air duct 50b which connects the turbofan 62 with the lower outlet port 52b.
- This shutter unit 70 is provided with a shutter driving motor 71 which is a drive source, the shutter 72, and a shutter casing 73 which rotatably supports the shutter 72.
- the shutter casing 73 includes, as shown in Fig. 4 , Fig. 9, and Fig. 10 , a shutter supporter 73a to which the shutter driving motor 71 and the shutter 72 are attached and a drain pan 73b provided above the shutter supporter 73a.
- the shutter supporter 73a is a tubular member functioning as a part of the above-described lower air duct 50b as shown in Fig. 9 and Fig. 10 , and its longitudinal end is attached to a mounting portion 73c to which the shutter driving motor 71 is mounted.
- This mounting portion 73c has a through hole 73d (see Fig. 10 ) through which the motor shaft 71a of the shutter driving motor 71 penetrates.
- the other longitudinal end of the shutter supporter 73a is attached to a bearing portion 73e which rotatably supports a later-described shaft 72b of the shutter 72.
- the drain pan 73b is, as shown in Fig. 4 , disposed along the lower edge of the indoor heat exchanger 10 and receives water drained from the indoor heat exchanger 10. This drain pan 73b is arranged to be inclined downward toward the pipe chamber 50B. At the bottom of the drain pan 73b on the pipe chamber 50B side, a drain pipe 73f is provided to drain the water in the drain pan to the outside.
- the shutter driving motor 71 is a stepper motor and is provided outside the shutter casing 73 so as not to obstruct the air flow in the lower air duct 50b.
- the motor shaft 71a of this shutter driving motor 71 is, as shown in Fig. 10 , attached to the shutter 72 via the through hole 73d penetrating the shutter casing 73.
- the shutter driving motor 71 rotates the shutter 72 in the direction of the arrow G about a rotational axis extending along the longitudinal directions of the shutter 72.
- the shutter 72 therefore moves from the open position shown in Fig. 11 to the close position show in Fig. 12 or moves from the close position shown in Fig. 12 to the open position shown in Fig. 11 .
- the shutter 72 is provided around the lower outlet port 52b. This shutter 72 is able to take a position to close the port 50c on the lower air duct 50b and a position to open the port 50c.
- the shutter 72 is, as shown in Fig. 9 and Fig. 10 , arranged to be long in the width directions (X directions) of the indoor unit 1.
- a fitting hole 72a At one longitudinal end of the shutter 72 is provided a fitting hole 72a to which the motor shaft 71a of the shutter driving motor 71 is fit, whereas at the other longitudinal end is provided the shaft 72b which is rotatably supported by the bearing portion 73e.
- the floor-type indoor unit 1 of the Reference Example has the features described below.
- the indoor unit 1 of the present embodiment is arranged so that the impeller disk (main blade) 63 and the impeller shroud (sub blade) 64 of the turbofan 62 have the extension portions 63c and 64b, respectively.
- the air flow in centrifugal direction which is blown out through the space between the impeller disk (main blade) 63 and the impeller shroud (sub blade) 64, is directed to the upper outlet port 52a and the lower outlet port 52b by the extension portion 63c and the extension portion 64b.
- the indoor unit 1 is able to form a smooth air flow which heads for the upper outlet port 52a and the lower outlet port 52b from the turbofan 62 in the casing unit 50, before colliding the bottom frame 53. This makes it possible to restrain the generation of noise on account of the collision of an air flow blown out from the turbofan 62 onto the bottom frame 53.
- the indoor unit 1 of the Reference Example is arranged so that the extension portion 64b on the impeller shroud (sub blade) 64 side, where the air flow is slow, is curved. This facilitates airflow to the upper outlet port 52a and the lower outlet port 52b.
- the indoor unit 1 of the Reference Example is arranged so that the external diameter R1 of the extension portion 63c is identical with the external diameter R2 of the extension portion 64b. This allows the extension portion 63c and the extension portion 64b to be efficiently extended in the casing unit 50 which defines the maximum size of the external diameter of the turbofan 62.
- the indoor unit 1 of the Reference Example is arranged so that the extension portion 63c is formed along the entirety of the outer periphery of the impeller disk (main blade) 63 and the extension portion 64b is formed along the entirety of the outer periphery of the impeller shroud (sub blade) 64.
- This structure allows the air flow blown out in centrifugal direction to be equally directed to the upper outlet port 52a and the lower outlet port 52b from the entire outer peripheries of the impeller disk (main blade) 63 and the impeller shroud (sub blade) 64.
- Fig. 13 is a graph showing the relationship between an angle of inclination of the extension portion of the impeller disk (main blade) of Reference Example and noise.
- Fig. 14 is a graph showing the relationship between an angle of inclination of the extension portion of the impeller disk (main blade) of Reference Example and an input to the fan motor.
- Example 1 the angle theta of inclination (see Fig. 5 ) of the extension portion of the impeller disk (main blade) was about 9 degrees.
- the generation of noise caused by the collision of wind blown out from the turbofan onto the casing or the like was restrained in Example 1, as compared to a comparative example of the conventional structure in which the impeller disk (main blade) does not have the extension portion.
- the input to the fan motor was slightly restrained as shown in Fig. 14 .
- Example 2 the angle theta of inclination (see Fig. 5 ) of the extension portion of the impeller disk (main blade) was arranged to be about 18 degrees.
- the generation of noise caused by the collision of wind blown out from the turbofan onto the casing or the like was restrained in Example 2, as compared to the comparative example of the conventional structure in which the impeller disk (main blade) does not have the extension portion.
- the input to the fan motor was slightly restrained as shown in Fig. 14 .
- both the noise reduction and the reduction in the input of the fan motor were less effective than Example 1. This is presumably because the increase in the angle of inclination of the extension portion narrowed the blowing path of the turbofan and hence the channel loss was increased.
- Fig. 15 is a schematic cross section of a turbofan according to the First Embodiment of the present invention.
- the following will describe the turbofan according to the First Embodiment of the present invention with reference to Fig. 15 .
- the turbofan 162 of First Embodiment is different from the turbofan 62 of the Reference Example in the shape of an extension portion 164b of a impeller shroud (sub blade) 164. It is noted that the components other than the turbofan 162 in First Embodiment are identical with those recited in Reference Example, and hence the same reference numerals are assigned to them and the descriptions thereof are not repeated.
- the turbofan 162 of the present embodiment includes, as shown in Fig. 15 , a impeller disk (main blade) 163, a impeller shroud (sub blade) 164 opposing the impeller disk (main blade) 164, and a plurality of blades 165 provided between the impeller disk (main blade) 163 and the impeller shroud (sub blade) 164.
- the impeller disk (main blade) 163 and the blade 165 will not be described in the present embodiment because they are identical with the impeller disk (main blade) 63 and the blade 65 of Reference Example, respectively.
- the impeller shroud (sub blade) 164 is provided with an extension portion 164b which linearly extends from the outer periphery of the impeller shroud (sub blade) 164 toward the outside of the outer peripheries of the blades 165.
- First Embodiment is arranged so that both of the extension portion 163c of the impeller disk (main blade) 163 and the extension portion 164b of the impeller shroud (sub blade) 164 linearly extend.
- the extension portion 164b is inclined away from the impeller disk (main blade) 163. More specifically, the extension portion 164b is arranged to be close to the outlet ports 52a and 52b (see Fig. 3 ) toward its leading end.
- the angle theta of inclination 101 of this extension portion 164b of the impeller shroud (sub blade) 164 is larger than the angle theta of inclination 102 of the extension portion 163c of the impeller disk (main blade) 163.
- Fig. 16 is a schematic cross section of a turbofan according to Second Embodiment of the present invention.
- the following will describe the turbofan according to Second Embodiment of the present invention with reference to Fig. 16 .
- the turbofan 262 of Second Embodiment is arranged so that both of an extension portion 263c of a impeller disk (main blade) 263 and an extension portion 264b of a impeller shroud (sub blade) 264 are curved.
- the components other than the turbofan 262 in Second Embodiment are identical with those recited in Reference Example, and hence the same reference numerals are assigned to them and the descriptions thereof are not repeated.
- the turbofan 262 of the present embodiment includes, as shown in Fig. 16 , a impeller disk (main blade) 263, a impeller shroud (sub blade) 264 opposing the impeller disk (main blade) 263, and a plurality of blades 265 provided between the impeller disk (main blade) 263 and the impeller shroud (sub blade) 264.
- the blades 265 will not be described because they are identical with the blades 65 of Reference Example.
- the impeller disk (main blade) 263 is provided with an extension portion 263c which curves and extends from the outer periphery of the impeller disk (main blade) 263 toward the outside of the outer peripheries of the blades 265.
- This extension portion 263c is arranged to be close to the impeller shroud (sub blade) 264 toward its leading end.
- the impeller shroud (sub blade) 264 is provided with an extension portion 264b which curves and extends from the outer periphery of the impeller shroud (sub blade) 264 toward the outside of the outer peripheries of the blades 265.
- both of the extension portion 263c of the impeller disk (main blade) 263 and the extension portion 264b of the impeller shroud (sub blade) 264 are curved.
- the extension portion 264b is inclined away from the impeller disk (main blade) 263. More specifically, the extension portion 264b is arranged to be close to the outlet ports 52a and 52b (see Fig. 3 ) toward its leading end.
- the curvature of this extension portion 264b of the impeller shroud (sub blade) 264 is greater that that of the extension portion 263c of the impeller disk (main blade) 263.
- the present invention is applicable for integrated air conditioners.
- the Reference Example is arranged so that the extension portion of the impeller disk (main blade) is linear whereas the extension portion of the impeller shroud (sub blade) is curved
- First Embodiment is arranged so that the extension portions of the impeller disk (main blade) and the impeller shroud (sub blade) are both linear
- Second Embodiment is arranged so that the extension portions of the impeller disk (main blade) and the impeller shroud (sub blade) are both curved.
- the present invention may be arranged such that the extension portion of the impeller disk (main blade) is curved whereas the extension portion of the impeller shroud (sub blade) is linear.
- the present invention makes it possible to realize an indoor unit of a floor-type air conditioner, which is capable of restraining noise caused by the collision of air blown out from a centrifugal fan (turbofan) onto a casing or the like.
Description
- The present invention relates to an indoor unit of a floor-type air conditioner having a centrifugal fan generating an air flow in centrifugal direction.
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KR 2003 0089142 - A known indoor unit of an air conditioner is arranged such that, by using a centrifugal fan housed in a casing, air sucked through an inlet port on the front of the casing is arranged to be an air flow in centrifugal direction, and the air flow is blown out from an inlet port provided around the outlet port (see e.g. Patent Document 1). In this indoor unit of
Patent Document 1, the air flow blown out from the centrifugal fan in centrifugal direction collides a guide wall (fan casing) which is radially outside the centrifugal fan, so that the air flow is guided to the outlet port. - [Patent Document 1] Japanese Unexamined Patent Publication No.
2007-183013 - The indoor unit of
Patent Document 1, however, is disadvantageous in that noise is generated because the air flow blown out from the centrifugal fan in centrifugal direction collides the guide wall (fan casing). - The present invention was done to solve this problem and hence an object of the present invention is to provide an indoor unit of a floor-type air conditioner which is capable of restraining noise caused by the collision of air blown out from a centrifugal fan onto a casing or the like.
- An indoor unit of a floor-type air conditioner according to the first aspect of the invention includes: a centrifugal fan which generates an air flow in centrifugal direction; a fan motor which has a motor shaft attached to the centrifugal fan and is configured to rotate the centrifugal fan; and a casing which stores the centrifugal fan and has an inlet port sucking air from outside to supply the air to the centrifugal fan and an outlet port which blows out an air flow generated by the centrifugal fan to the outside, wherein, the centrifugal fan includes an impeller disk (main blade), an impeller shroud (sub blade) on the inlet port side of the impeller disk (main blade), and a plurality of blades provided between the impeller disk (main blade) and the impeller shroud (sub blade), the impeller disk (main blade) has a first extension portion which extends from an outer periphery of the impeller disk (main blade) toward the outside of outer peripheries of the blades and is linearly inclined toward the inlet port with respect to a plane orthogonal to the motor shaft, and the impeller shroud (sub blade) includes a second extension portion which extends from an outer periphery of the impeller shroud (sub blade) toward the outside of outer peripheries of the blades and is linearly inclined toward the inlet port with respect to a plane orthogonal to the motor shaft, and an angle of inclination of the first extension portion with respect to a plane orthogonal to the motor shaft is smaller than an angle of inclination of the second extension portion.
- This indoor unit of the floor-type air conditioner arranges, by means of the first extension portion and the second extension portion, an air flow blown out in centrifugal direction from the space between the impeller disk (main blade) and the impeller shroud (sub blade) to be an air flow toward the outlet ports. In other words, the indoor unit is able to form a smooth air flow which moves from the centrifugal fan to the outlet ports in the casing without colliding the casing or the like. As a result, it is possible to restrain the noise caused by the collision of an air flow blown out from the centrifugal fan onto the casing or the like.
- Furthermore, since the angle of inclination of the first extension portion on the impeller disk (main blade) side where the air flow blown out from the centrifugal fan is fast is arranged to be smaller than that of the second extension portion, the fast air flow on the impeller disk (main blade) side is directed toward the outlet ports without being sharply diverted.
- According to the second aspect of the invention, the indoor unit of the floor-type air conditioner includes: a centrifugal fan which generates an air flow in centrifugal direction; and a casing which stores the centrifugal fan and has an inlet port which sucks air from outside to supply the air to the centrifugal fan and outlet port which blows out an air flow generated by the centrifugal fan to the outside, wherein the centrifugal fan includes an impeller disk (main blade), an impeller shroud (sub blade) on the inlet port side of the impeller disk (main blade), and a plurality of blades provided between the impeller disk (main blade) and the impeller shroud (sub blade), the impeller disk (main blade) has a first extension portion which extends from an outer periphery of the impeller disk (main blade) toward the outside of outer peripheries of the blades and curves toward the inlet port, the impeller shroud (sub blade) includes a second extension portion which extends from an outer periphery of the impeller shroud (sub blade) toward the outside of outer peripheries of the blades and curves toward the inlet port, and the second extension portion is more curved than the first extension portion.
- The indoor unit of the floor-type air conditioner is arranged so that the second extension portion on the impeller shroud (sub blade) side, where the air flow is slow, is curved. This facilitates airflow to the outlet ports.
- According to the third aspect of the invention, the indoor unit of the floor-type air conditioner according to any one of the first to second aspects of the invention is arranged so that the external diameter of the first extension portion is identical with the external diameter of the second extension portion.
- According to this indoor unit of the floor-type air conditioner, the first extension portion and the second extension portion are efficiently extended in the casing which defines the maximum size of the external diameter of the centrifugal fan.
- According to the fourth aspect of the invention, the indoor unit of the floor-type air conditioner according to any one of the first to third aspects of the invention is arranged so that the first extension portion is formed along the entire outer periphery of the impeller disk (main blade), and the second extension portion is formed along the entire outer periphery of the impeller shroud (sub blade).
- This indoor unit of the floor-type air conditioner allows the air flow blown out in centrifugal direction to be equally directed to the outlet ports from the entire outer peripheries of the impeller disk (main blade) and the impeller shroud (sub blade).
- As described above, the following effects are obtained from the present invention.
- According to the first aspect of the invention, by means of the first extension portion and the second extension portion, an air flow blown out in centrifugal direction from the space between the impeller disk (main blade) and the impeller shroud (sub blade) are arranged to be an air flow toward the outlet ports. Therefore, the indoor unit is able to form a smooth air flow which moves from the centrifugal fan to the outlet ports in the casing without colliding the casing or the like. As a result, it is possible to restrain the noise caused by the collision of an air flow blown out from the centrifugal fan onto the casing or the like.
- Furthermore, since the angle of inclination of the first extension portion on the impeller disk (main blade) side where the air flow blown out from the centrifugal fan is fast is arranged to be smaller than that of the second extension portion, the fast air flow on the impeller disk (main blade) side is directed toward the outlet ports without being sharply diverted.
- According to the second aspect of the invention, the second extension portion on the impeller shroud (sub blade) side, where the air flow is slow, is curved. This facilitates airflow to the outlet ports.
- According to the third aspect of the invention, the first extension portion and the second extension portion are efficiently extended in the casing which defines the maximum size of the external diameter of the centrifugal fan.
- According to the fourth aspect of the invention, the first extension portion is formed along the entire outer periphery of the impeller disk (main blade), and the second extension portion is formed along the entire outer periphery of the impeller shroud (sub blade).
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Fig. 1 is a circuit diagram of a refrigerant circuit of an air conditioner in accordance with the present invention. -
Fig. 2 is an oblique perspective showing the appearance of the floor-type indoor unit. -
Fig. 3 is a cross section of the floor-type indoor unit shown inFig. 2 according to a Reference Example. -
Fig. 4 is an elevation view showing the internal structure of the floor-type indoor unit shown inFig. 2 . -
Fig. 5 is a schematic cross section of a fan unit and the bottom frame according to a Reference Example. -
Fig. 6 is an oblique perspective of the turbofan shown inFig.5 . -
Fig. 7 is an elevation of the turbofan shown inFig.5 . -
Fig. 8 is a cross section taken along the A-A line inFig. 7 . -
Fig. 9 is an oblique perspective when the shutter unit is viewed from the back side. -
Fig. 10 is an oblique perspective when the shutter unit is viewed from the back side. -
Fig. 11 is a cross section of the shutter unit when the shutter is open. -
Fig. 12 is a cross section of the shutter unit when the shutter is closed. -
Fig. 13 is a graph showing the relationship between an angle of inclination of the extension portion of the impeller disk (main blade) of Reference Example and noise. -
Fig. 14 is a graph showing the relationship between an angle of inclination of the extension portion of the impeller disk (main blade) of Reference Example and an input to the fan motor. -
Fig. 15 is a schematic cross section of a turbofan according to First Embodiment of the present invention. -
Fig. 16 is a schematic cross section of a turbofan according to Second Embodiment of the present invention. - The following will describe an embodiment of an air conditioner having a floor-type indoor unit according to the present invention, with reference to figures.
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Fig. 1 is a circuit diagram of a refrigerant circuit of an air conditioner according to the present invention.Fig. 2 is an oblique perspective showing the appearance of the floor-type indoor unit.Fig. 3 is a cross section of the floor-type indoor unit shown inFig. 2 according to a Reference Example.Fig. 4 is an elevation view showing the internal structure of the floor-type indoor unit shown inFig. 2 . Now, an air conditioner according to the present invention will be described with reference toFig. 1 to Fig. 4 . - An
air conditioner 100 according to an embodiment of the present invention is an apparatus for supplying conditioned air into a room, and includes, as shown inFig. 1 , a floor-type indoor unit (hereinafter, indoor unit) 1 disposed in the room, anoutdoor unit 2 disposed outside the room, and aconnection pipe 3 connecting theindoor unit 1 with theoutdoor unit 2. The components and valves housed in theindoor unit 1 and theoutdoor unit 2 and theconnection pipe 3 are connected with one another and constitute a refrigerant circuit. The refrigerant circuit is chiefly made up of anindoor heat exchanger 10, anoutdoor heat exchanger 20, anaccumulator 21, acompressor 22, a four-pass switching valve 23, and anelectric expansion valve 24. - In the
air conditioner 100 arranged as above, the four-pass switching valve 23 is switched to the position indicated by the solid line, when heating. As a result, a hot high-pressure refrigerant discharged from thecompressor 22 flows into theindoor heat exchanger 10 via the four-pass switching valve 23. The refrigerant condensed in the indoor heat exchanger (condenser) 10 is depressurized by theelectric expansion valve 24 and then flows into theoutdoor heat exchanger 20. Thereafter, the refrigerant evaporated in the outdoor heat exchanger (evaporator) 20 returns to the sucking side of thecompressor 22 via the four-pass switching valve 23 and theaccumulator 21. As such, the air around theindoor heat exchanger 10 is heated and hot air is supplied into the room. - On the other hand, when cooling, the four-
pass switching valve 23 is switched to the position indicated by a dotted line. Upon switching, the hot high-pressure refrigerant discharged from thecompressor 22 flows into theoutdoor heat exchanger 20 via the four-pass switching valve 23. The refrigerant condensed in the outdoor heat exchanger (condenser) 20 is depressurized by theelectric expansion valve 24, and then flows into theindoor heat exchanger 10. Thereafter, the refrigerant evaporated in the indoor heat exchanger (evaporator) 10 returns to the sucking side of thecompressor 22 via the four-pass switching valve 23 and theaccumulator 21. As such, the air around theindoor heat exchanger 10 is cooled and cool air is supplied to the room. - The
outdoor unit 2 includes thecompressor 22, the four-pass switching valve 23 connected to the discharging side of thecompressor 22, theaccumulator 21 connected to the sucking side of thecompressor 22, theoutdoor heat exchanger 20 connected to the four-pass switching valve 23, theelectric expansion valve 24 connected to theoutdoor heat exchanger 20, and anoutdoor fan 25 attached to theoutdoor heat exchanger 20. Theelectric expansion valve 24 is connected to a liquidrefrigerant pipe 31, and is further connected to one end of theindoor heat exchanger 10 via the liquidrefrigerant pipe 31. The four-pass switching valve 23 is connected to agas refrigerant pipe 32, and is further connected to the other end of theindoor heat exchanger 10 via thegas refrigerant pipe 32. Therefrigerant pipes connection pipe 3. - The
indoor unit 1 is, as shown inFig. 2 andFig. 3 , a floor-type indoor unit and chiefly includes acasing unit 50, anindoor heat exchanger 10 housed in thecasing unit 50, afan unit 60, and ashutter unit 70. - The
casing unit 50 constituting the contour of theindoor unit 1 includes afront panel 51, afront grill 52, abottom frame 53, and a back heat-insulatingmaterial 54. These components are disposed in the order of, from the front side of theindoor unit 1, thefront panel 51, thefront grill 52, thebottom frame 53, and the back heat-insulatingmaterial 54. The space formed inside thecasing unit 50 is, as shown inFig. 4 , divided into afan chamber 50A in which theindoor heat exchanger 10, thefan unit 60 and the like are provided, and apipe chamber 50B in which electric units or the like are provided. - The
front panel 51 is, as shown inFig. 2 andFig. 3 , attached to cover afilter 55 which is attached to thefront grill 52. At the top of thisfront panel 51 is provided anupper inlet port 51a, whereas at the bottom of thefront panel 51 is provided alower inlet port 51b. Furthermore, on the both sides of thefront panel 51 are formedside inlet ports 51c. Theupper inlet port 51a and thelower inlet port 51b are long in the width directions (X directions) whereas theside inlet ports 51c are long in the vertical directions (Z directions). These ports allow the unit to suck indoor air in four directions, i.e. from above, from below, from left, and from right, and the air sucked through theinlet ports indoor heat exchanger 10. - The front grill 52is, as shown in
Fig. 2 andFig. 3 , provided between thefront panel 51 and theindoor heat exchanger 10. At the top of thefront grill 52 is provided anupper outlet port 52a, whereas at the bottom of thefront grill 52 is provided alower outlet port 52b. Theseupper outlet port 52a and thelower outlet port 52b are both long in the width directions (X directions). At the center of thefront grill 52 is formed a substantiallyrectangular parallelepiped opening 52c. Thisopening 52c is provided with afilter 55 to catch the dust in the air sucked through theinlet ports front panel 51. - The
bottom frame 53 is, as shown inFig. 3 , disposed between the later-describedfan unit 60 and the back heat-insulatingmaterial 54. Thisbottom frame 53 includes abottom portion 53a forming the bottom of theindoor unit 1 and a standingportion 53b standing on thebottom portion 53a. Thebottom portion 53a is provided with apipe introducing hole 53c to introduce theconnection pipe 3 into thepipe chamber 50B (seeFig. 4 ). Substantially at the center of the standingportion 53b is provided afan attaching portion 53d for attaching thefan unit 60 thereto. - The back heat-insulating
material 54 is provided on the back side of thebottom frame 53 for heat insulation. - In the
casing unit 50 structured as above, as shown inFig. 3 , anupper air duct 50a is formed to connect a later-describedturbofan 62 with theupper outlet port 52a. Thisupper air duct 50a is formed along the inner wall surface of thebottom frame 53. Thisduct 50a curves and extends forward and upward from theturbofan 62 to theupper outlet port 52a. Above theupper air duct 50a are provided avertical flap 40 by which the direction of air flow blown out from theupper outlet port 52a is controlled in regard to the horizontal direction and ahorizontal flap 41 by which the direction of air flow is controlled in regard to the vertical direction. In thecasing unit 50, furthermore, alower air duct 50b is formed to connect theturbofan 62 with thelower outlet port 52b. Thelower air duct 50b curves and extends forward and downward from theturbofan 62 to thelower outlet port 52b. Above thislower air duct 50b is provided avertical flap 42 by which the direction of air flow blown out from thelower outlet port 52b is controlled in regard to the horizontal direction. On the windward side of thevertical flap 42 is provided a later-describedshutter 72. - The
indoor heat exchanger 10 is provided for conducting heat exchange with the indoor air. Thisindoor heat exchanger 10 is, as shown inFig. 3 , provided between thefan unit 60 and thefront grill 52 and conducts heat exchange on the windward side of thefan unit 60. - In addition to the above, between the
indoor heat exchanger 10 and thefan unit 60 is provided a bell-mouth 11. This bell-mouth 11 guides the air having passed through theindoor heat exchanger 10 to the later-described turbofan 62 (opening 64a). -
Fig. 5 is a Reference Example of a schematic cross section of an unclaimed fan unit and bottom frame.Fig. 6 turbofan shown in is an oblique perspective of the turbofan shown inFig.5 ,Fig. 7 is an elevation of the turbofan shown inFig. 5 , andFig. 8 is a cross section taken along the A-A line inFig. 7 . Now, thefan unit 60 will be detailed with reference to drawings such asFig. 5 to Fig. 8 , and is provided for background information. - The
fan unit 60 includes afan motor 61 which is a drive source and provided on the leeward side of theindoor heat exchanger 10 and theturbofan 62 which is a type of centrifugal fan generating an air flow in centrifugal direction. The air flow generated by thisfan unit 60 is blown out from theupper outlet port 52a via the above-describedupper air duct 50a and from thelower outlet port 52b via thelower air duct 50b. - The
fan motor 61 is attached to thefan attaching portion 53d (seeFig. 3 ) of the standingportion 53b of thebottom frame 53. Themotor shaft 61a of thisfan motor 61 extends in the front-back directions (Y directions), and rotates about a rotational axis extending in the front-back directions. - As shown in
Fig. 3 , theturbofan 62 is attached to themotor shaft 61a of thefan motor 61 and rotates in accordance with the rotation of themotor shaft 61a. Thisturbofan 62 includes, as shown inFig. 5 to Fig. 8 , a impeller disk (main blade) 63, a impeller shroud (sub blade) 64 opposing the impeller disk (main blade) 63, and sevenblades 65 provided between the impeller disk (main blade) 63 and the impeller shroud (sub blade) 64. - The impeller disk (main blade) 63 is substantially disc-shaped in elevation, and a
protrusion 63a protruding toward the impeller shroud (sub blade) 64 is formed at its center. Thisprotrusion 63a is formed to correspond to thefan motor 61, and is attached to the above-describedmotor shaft 61a. Around theprotrusion 63a formed substantially at the center of the impeller disk (main blade) 63, aflat portion 63b is formed to extend along the plane orthogonal to the above-describedmotor shaft 61a. In the Reference Example, as shown inFig. 5 andFig. 8 , the impeller disk (main blade) 63 further has anextension portion 63c which linearly extends from the outer periphery of the impeller disk (main blade) 63 toward the outside of the outer peripheries of the sevenblades 65. Thisextension portion 63c is inclined for an angle of theta (seeFig. 5 ) toward the impeller shroud (sub blade) 64, with respect to theflat portion 63b. Theextension portion 63c is arranged to be close to the impeller shroud (sub blade) 64 toward its leading end. - The impeller shroud (sub blade) 64 is spaced apart from the impeller disk (main blade) 63 and is on the
port 52a side and on theport 52b side of the impeller disk (main blade) 63. This impeller shroud (sub blade) 64 is substantially ring-shaped in elevation and anopening 64a formed at its center functions as an air inlet. In the Reference Example, furthermore, the impeller shroud (sub blade) 64 has anextension portion 64b which curves and extends from the outer periphery of the impeller shroud (sub blade) 64 toward the outside of the outer peripheries of the sevenblades 65. Thisextension portion 64b is inclined away from the impeller disk (main blade) 63. More specifically, theextension portion 64b is arranged to be close to theoutlet ports extension portion 64c which curves and extends inward from its inner periphery. Thisextension portion 64c is inclined away from the impeller disk (main blade) 63 in the same manner as theextension portion 64b described above. More specifically, theextension portion 64c is arranged to be close to theoutlet ports - In the Reference Example, as shown in
Fig. 6 , theextension portion 63c of the above-described impeller disk (main blade) 63 is formed along the entirety of the outer periphery, and theextension portion 64b of the impeller shroud (sub blade) 64 is formed along the entirety of the outer periphery. Furthermore, as shown inFig. 5 , the external diameter R1 of theextension portion 63c is identical with the external diameter R2 of theextension portion 64b. - The seven
blades 65 are, as shown inFig. 7 , provided at predetermined intervals and angles along the direction of the rotation of theturbofan 62. - As shown in
Fig. 3 andFig. 5 , as thefan motor 61 is activated, theturbofan 62 rotates, the air having passed through theindoor heat exchanger 10 is sucked into theturbofan 62 via theopening 64a, with the result that an air flow in centrifugal direction is generated. This air flow in centrifugal direction is directed toward theoutlet ports indoor unit 1 by theextension portion 63c of the impeller disk (main blade) 63 and theextension portion 64b of the impeller shroud (sub blade) 64. In other words, the air flow blown out from the upper part of theturbofan 62 progresses along theupper air duct 50a and is then blown out from thecasing unit 50 through theupper outlet port 52a. The air flow blown out from the lower part of theturbofan 62 progresses along thelower air duct 50b and is then blown out from thecasing unit 50 through thelower outlet port 52b. - Each of
Fig. 9 and Fig. 10 is an oblique perspective when the shutter unit is viewed from the back side.Fig. 11 is a cross section of the shutter unit when the shutter is open.Fig. 12 is a cross section of the shutter unit when the shutter is closed. Now, theshutter unit 70 will be detailed with reference to drawings such asFig. 9 to Fig. 12 . - The
shutter unit 70 is provided around thelower outlet port 52b and determines whether the air flow from theturbofan 62 to thelower outlet port 52b is allowed to be blown to the outside, by opening or closing aport 50c on thelower air duct 50b which connects theturbofan 62 with thelower outlet port 52b. Thisshutter unit 70 is provided with ashutter driving motor 71 which is a drive source, theshutter 72, and ashutter casing 73 which rotatably supports theshutter 72. - The
shutter casing 73 includes, as shown inFig. 4 ,Fig. 9, and Fig. 10 , ashutter supporter 73a to which theshutter driving motor 71 and theshutter 72 are attached and adrain pan 73b provided above theshutter supporter 73a. Theshutter supporter 73a is a tubular member functioning as a part of the above-describedlower air duct 50b as shown inFig. 9 and Fig. 10 , and its longitudinal end is attached to a mountingportion 73c to which theshutter driving motor 71 is mounted. This mountingportion 73c has a throughhole 73d (seeFig. 10 ) through which themotor shaft 71a of theshutter driving motor 71 penetrates. The other longitudinal end of theshutter supporter 73a is attached to a bearingportion 73e which rotatably supports a later-describedshaft 72b of theshutter 72. Thedrain pan 73b is, as shown inFig. 4 , disposed along the lower edge of theindoor heat exchanger 10 and receives water drained from theindoor heat exchanger 10. Thisdrain pan 73b is arranged to be inclined downward toward thepipe chamber 50B. At the bottom of thedrain pan 73b on thepipe chamber 50B side, adrain pipe 73f is provided to drain the water in the drain pan to the outside. - The
shutter driving motor 71 is a stepper motor and is provided outside theshutter casing 73 so as not to obstruct the air flow in thelower air duct 50b. Themotor shaft 71a of thisshutter driving motor 71 is, as shown inFig. 10 , attached to theshutter 72 via the throughhole 73d penetrating theshutter casing 73. Theshutter driving motor 71 rotates theshutter 72 in the direction of the arrow G about a rotational axis extending along the longitudinal directions of theshutter 72. Theshutter 72 therefore moves from the open position shown inFig. 11 to the close position show inFig. 12 or moves from the close position shown inFig. 12 to the open position shown inFig. 11 . - The
shutter 72 is provided around thelower outlet port 52b. Thisshutter 72 is able to take a position to close theport 50c on thelower air duct 50b and a position to open theport 50c. Theshutter 72 is, as shown inFig. 9 and Fig. 10 , arranged to be long in the width directions (X directions) of theindoor unit 1. At one longitudinal end of theshutter 72 is provided afitting hole 72a to which themotor shaft 71a of theshutter driving motor 71 is fit, whereas at the other longitudinal end is provided theshaft 72b which is rotatably supported by the bearingportion 73e. - The floor-type
indoor unit 1 of the Reference Example has the features described below. - As stated above, the
indoor unit 1 of the present embodiment is arranged so that the impeller disk (main blade) 63 and the impeller shroud (sub blade) 64 of theturbofan 62 have theextension portions upper outlet port 52a and thelower outlet port 52b by theextension portion 63c and theextension portion 64b. In other words, theindoor unit 1 is able to form a smooth air flow which heads for theupper outlet port 52a and thelower outlet port 52b from theturbofan 62 in thecasing unit 50, before colliding thebottom frame 53. This makes it possible to restrain the generation of noise on account of the collision of an air flow blown out from theturbofan 62 onto thebottom frame 53. - In addition to the above, the
indoor unit 1 of the Reference Example is arranged so that theextension portion 64b on the impeller shroud (sub blade) 64 side, where the air flow is slow, is curved. This facilitates airflow to theupper outlet port 52a and thelower outlet port 52b. - In addition to the above, the
indoor unit 1 of the Reference Example is arranged so that the external diameter R1 of theextension portion 63c is identical with the external diameter R2 of theextension portion 64b. This allows theextension portion 63c and theextension portion 64b to be efficiently extended in thecasing unit 50 which defines the maximum size of the external diameter of theturbofan 62. - In addition to the above, the
indoor unit 1 of the Reference Example is arranged so that theextension portion 63c is formed along the entirety of the outer periphery of the impeller disk (main blade) 63 and theextension portion 64b is formed along the entirety of the outer periphery of the impeller shroud (sub blade) 64. This structure allows the air flow blown out in centrifugal direction to be equally directed to theupper outlet port 52a and thelower outlet port 52b from the entire outer peripheries of the impeller disk (main blade) 63 and the impeller shroud (sub blade) 64. -
Fig. 13 is a graph showing the relationship between an angle of inclination of the extension portion of the impeller disk (main blade) of Reference Example and noise.Fig. 14 is a graph showing the relationship between an angle of inclination of the extension portion of the impeller disk (main blade) of Reference Example and an input to the fan motor. - In Example 1, the angle theta of inclination (see
Fig. 5 ) of the extension portion of the impeller disk (main blade) was about 9 degrees. In this case, as shown inFig. 13 , the generation of noise caused by the collision of wind blown out from the turbofan onto the casing or the like was restrained in Example 1, as compared to a comparative example of the conventional structure in which the impeller disk (main blade) does not have the extension portion. Furthermore, in Example 1, the input to the fan motor was slightly restrained as shown inFig. 14 . - In Example 2, the angle theta of inclination (see
Fig. 5 ) of the extension portion of the impeller disk (main blade) was arranged to be about 18 degrees. In this case, as shown inFig. 13 , the generation of noise caused by the collision of wind blown out from the turbofan onto the casing or the like was restrained in Example 2, as compared to the comparative example of the conventional structure in which the impeller disk (main blade) does not have the extension portion. Furthermore, in Example 2, the input to the fan motor was slightly restrained as shown inFig. 14 . In Example 2, however, both the noise reduction and the reduction in the input of the fan motor were less effective than Example 1. This is presumably because the increase in the angle of inclination of the extension portion narrowed the blowing path of the turbofan and hence the channel loss was increased. -
Fig. 15 is a schematic cross section of a turbofan according to the First Embodiment of the present invention. The following will describe the turbofan according to the First Embodiment of the present invention with reference toFig. 15 . Theturbofan 162 of First Embodiment is different from theturbofan 62 of the Reference Example in the shape of anextension portion 164b of a impeller shroud (sub blade) 164. It is noted that the components other than theturbofan 162 in First Embodiment are identical with those recited in Reference Example, and hence the same reference numerals are assigned to them and the descriptions thereof are not repeated. - The
turbofan 162 of the present embodiment includes, as shown inFig. 15 , a impeller disk (main blade) 163, a impeller shroud (sub blade) 164 opposing the impeller disk (main blade) 164, and a plurality ofblades 165 provided between the impeller disk (main blade) 163 and the impeller shroud (sub blade) 164. The impeller disk (main blade) 163 and theblade 165 will not be described in the present embodiment because they are identical with the impeller disk (main blade) 63 and theblade 65 of Reference Example, respectively. - In First Embodiment, the impeller shroud (sub blade) 164 is provided with an
extension portion 164b which linearly extends from the outer periphery of the impeller shroud (sub blade) 164 toward the outside of the outer peripheries of theblades 165. In other words, First Embodiment is arranged so that both of theextension portion 163c of the impeller disk (main blade) 163 and theextension portion 164b of the impeller shroud (sub blade) 164 linearly extend. Theextension portion 164b is inclined away from the impeller disk (main blade) 163. More specifically, theextension portion 164b is arranged to be close to theoutlet ports Fig. 3 ) toward its leading end. The angle theta of inclination 101 of thisextension portion 164b of the impeller shroud (sub blade) 164 is larger than the angle theta of inclination 102 of theextension portion 163c of the impeller disk (main blade) 163. -
Fig. 16 is a schematic cross section of a turbofan according to Second Embodiment of the present invention. The following will describe the turbofan according to Second Embodiment of the present invention with reference toFig. 16 . Theturbofan 262 of Second Embodiment is arranged so that both of anextension portion 263c of a impeller disk (main blade) 263 and anextension portion 264b of a impeller shroud (sub blade) 264 are curved. It is noted that the components other than theturbofan 262 in Second Embodiment are identical with those recited in Reference Example, and hence the same reference numerals are assigned to them and the descriptions thereof are not repeated. - The
turbofan 262 of the present embodiment includes, as shown inFig. 16 , a impeller disk (main blade) 263, a impeller shroud (sub blade) 264 opposing the impeller disk (main blade) 263, and a plurality ofblades 265 provided between the impeller disk (main blade) 263 and the impeller shroud (sub blade) 264. Theblades 265 will not be described because they are identical with theblades 65 of Reference Example. - According to Second Embodiment, as shown in
Fig. 16 , the impeller disk (main blade) 263 is provided with anextension portion 263c which curves and extends from the outer periphery of the impeller disk (main blade) 263 toward the outside of the outer peripheries of theblades 265. Thisextension portion 263c is arranged to be close to the impeller shroud (sub blade) 264 toward its leading end. - The impeller shroud (sub blade) 264 is provided with an
extension portion 264b which curves and extends from the outer periphery of the impeller shroud (sub blade) 264 toward the outside of the outer peripheries of theblades 265. In other words, in Second Embodiment both of theextension portion 263c of the impeller disk (main blade) 263 and theextension portion 264b of the impeller shroud (sub blade) 264 are curved. Theextension portion 264b is inclined away from the impeller disk (main blade) 263. More specifically, theextension portion 264b is arranged to be close to theoutlet ports Fig. 3 ) toward its leading end. The curvature of thisextension portion 264b of the impeller shroud (sub blade) 264 is greater that that of theextension portion 263c of the impeller disk (main blade) 263. - While the present invention has been described in conjunction with the specific embodiments outlined above, it is evident that many alternatives, modifications and variations will be apparent to those skilled in the art. Accordingly, the preferred embodiments of the invention as set forth above are intended to be illustrative, not limiting.
- For example, while the embodiments above describe the separated air conditioner including the outdoor unit and the indoor unit, the present invention is applicable for integrated air conditioners.
- Also, the Reference Example is arranged so that the extension portion of the impeller disk (main blade) is linear whereas the extension portion of the impeller shroud (sub blade) is curved, First Embodiment is arranged so that the extension portions of the impeller disk (main blade) and the impeller shroud (sub blade) are both linear, and Second Embodiment is arranged so that the extension portions of the impeller disk (main blade) and the impeller shroud (sub blade) are both curved. In addition to this, the present invention may be arranged such that the extension portion of the impeller disk (main blade) is curved whereas the extension portion of the impeller shroud (sub blade) is linear.
- The present invention makes it possible to realize an indoor unit of a floor-type air conditioner, which is capable of restraining noise caused by the collision of air blown out from a centrifugal fan (turbofan) onto a casing or the like.
-
- 1 INDOOR UNIT
- 50 CASING UNIT (CASING)
- 51a UPPER INLET PORT (INLET PORT)
- 51b LOWER INLET PORT (INLET PORT)
- 52a UPPER OUTLET PORT (OUTLET PORT)
- 52b LOWER OUTLET PORT (OUTLET PORT)
- 62, 162, 262 TURBOFAN (CENTRIFUGAL FAN)
- 63, 163, 263 MAIN BLADE
- 63c, 163c, 263c EXTENSION PORTION (FIRST EXTENSION PORTION)
- 64, 164, 264 SUB BLADE
- 64b, 164b, 264b EXTENSION PORTION (SECOND EXTENSION PORTION)
- 65, 165, 265 BLADE
Claims (4)
- An indoor unit (1) of a floor-type air conditioner, comprising:a centrifugal fan (162) which generates an air flow in centrifugal direction;a fan motor (61) which has a motor shaft (61a) attached to the centrifugal fan (162) and is configured to rotate the centrifugal fan (162); anda casing (53) which stores the centrifugal fan (162) and has an inlet port (51a, b, c) which sucks air from outside to supply the air to the centrifugal fan and an outlet port (52a, b) which blows out an air flow generated by the centrifugal fan to the outside, wherein,the centrifugal fan (162) includes an impeller disk (163), an impeller shroud (164) on the inlet port side of the impeller disk, and a plurality of blades (165) provided between the impeller disk and the impeller shroud, and characterised in thatthe impeller disk (163) has a first extension portion (163c) which extends from an outer periphery of the impeller disk toward the outside of outer peripheries of the blades (165) and is linearly inclined toward the inlet port (51a, b, c) with respect to a plane orthogonal to the motor shaft,the impeller shroud (164) includes a second extension portion (164b) which extends from an outer periphery of the impeller shroud toward the outside of outer peripheries of the blades (165) and is linearly inclined toward the inlet port (51a, b, c) with respect to a plane orthogonal to the motor shaft, andan angle of inclination (θ 102) of the first extension portion (163c) with respect to a plane orthogonal to the motor shaft is smaller than an angle of inclination (θ 101) of the second extension portion (164b).
- An indoor unit (1) of a floor-type air conditioner, comprising:a centrifugal fan (262) which generates an air flow in centrifugal direction; anda casing (53) which stores the centrifugal fan (262) and has an inlet port (51a, b, c) which sucks air from outside to supply the air to the centrifugal fan (262) and an outlet port (52a, b) which blows out an air flow generated by the centrifugal fan (262) to the outside, wherein,the centrifugal fan (262) includes an impeller disk (263), an impeller shroud (264) on the inlet port side of the impeller disk, and a plurality of blades (265) provided between the impeller disk and the impeller shroud, and characterised in thatthe impeller disk (263) has first extension portion (263c) which extends from an outer periphery of the impeller disk toward the outside of outer peripheries of the blade (265) and curves toward the inlet port (51a, b, c),the impeller shroud (264) includes a second extension portion (264b) which extends from an outer periphery of the impeller shroud toward the outside of outer peripheries of the blades (65, 265) and curves towards the inlet port (51a, b, c), andthe second extension portion (264b) is more curved than the first extension portion (263c).
- The indoor unit (1) of the floor-type air conditioner according to any one of claims 1 to 2, wherein,
the external diameter of the first extension portion (163c, 263c) is identical with the external diameter of the second extension portion (164b, 264b). - The indoor unit (1) of the floor-type air conditioner according to any one of claims 1 to 3, wherein,
the first extension portion (163c, 263c) is formed along the entire outer periphery of the impeller disk (163, 263), and the second extension portion (164b, 264b) is formed along the entire outer periphery of the impeller shroud (164, 264).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2008250077A JP4502057B2 (en) | 2008-09-29 | 2008-09-29 | Indoor unit of floor type air conditioner |
PCT/JP2009/064166 WO2010035584A1 (en) | 2008-09-29 | 2009-08-11 | Indoor unit for floor mounted air conditioner |
Publications (3)
Publication Number | Publication Date |
---|---|
EP2345852A1 EP2345852A1 (en) | 2011-07-20 |
EP2345852A4 EP2345852A4 (en) | 2015-03-04 |
EP2345852B1 true EP2345852B1 (en) | 2017-05-10 |
Family
ID=42059591
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP09816001.3A Active EP2345852B1 (en) | 2008-09-29 | 2009-08-11 | Indoor unit of floor-type air conditioner |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP2345852B1 (en) |
JP (1) | JP4502057B2 (en) |
AU (1) | AU2009297727B2 (en) |
ES (1) | ES2626129T3 (en) |
WO (1) | WO2010035584A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN112797486A (en) * | 2020-12-28 | 2021-05-14 | 珠海格力电器股份有限公司 | Air conditioner indoor unit, control method and air conditioner |
Families Citing this family (11)
Publication number | Priority date | Publication date | Assignee | Title |
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JP5522306B1 (en) * | 2012-12-21 | 2014-06-18 | ダイキン工業株式会社 | Centrifugal fan |
FR3007086B1 (en) * | 2013-06-18 | 2015-07-03 | Cryostar Sas | CENTRIFUGAL WHEEL |
KR101625061B1 (en) * | 2014-03-27 | 2016-05-27 | 엘지전자 주식회사 | Centrifugal fan |
CN105091284B (en) * | 2015-08-24 | 2018-01-23 | 珠海格力电器股份有限公司 | Air-out component and air conditioner |
CN106091111A (en) * | 2016-06-17 | 2016-11-09 | 青岛海尔空调电子有限公司 | Wall hanging machine indoor set |
JP2018100603A (en) * | 2016-12-19 | 2018-06-28 | 三菱電機株式会社 | Centrifugal Pump |
DE102017100684A1 (en) * | 2017-01-16 | 2018-07-19 | Ebm-Papst Mulfingen Gmbh & Co. Kg | Fan wheel with predefined discharge direction |
JP6982302B2 (en) * | 2017-10-23 | 2021-12-17 | フルタ電機株式会社 | Impeller |
WO2019144736A1 (en) * | 2018-01-29 | 2019-08-01 | 美的集团股份有限公司 | Impeller, fan assembly and electrical appliance |
WO2019235423A1 (en) * | 2018-06-05 | 2019-12-12 | 株式会社村田製作所 | Blowing device and fluid control device |
IT201800010686A1 (en) * | 2018-11-29 | 2020-05-29 | Aermec Spa | FAN COIL |
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JP2956317B2 (en) * | 1990-11-07 | 1999-10-04 | ダイキン工業株式会社 | Air conditioner |
JP2000074410A (en) * | 1998-09-03 | 2000-03-14 | Daikin Ind Ltd | Double suction centrifugal fan and air supplying apparatus provided therewith |
JP2000120582A (en) * | 1998-10-15 | 2000-04-25 | Matsushita Seiko Co Ltd | Centrifugal blower |
KR100468468B1 (en) * | 2002-05-16 | 2005-01-27 | 삼성전자주식회사 | An air conditioning system |
FR2874241A1 (en) * | 2004-08-16 | 2006-02-17 | Max Sardou | Centrifugal impeller for pump and centrifugal blower, has hub and ring including trailing edge radii greater than trailing edge radii of truncated blade for closing of slipstream and detent of circulating fluid |
JP4123276B2 (en) * | 2006-01-04 | 2008-07-23 | ダイキン工業株式会社 | Air conditioner indoor unit |
JP3992063B2 (en) | 2006-01-04 | 2007-10-17 | ダイキン工業株式会社 | Air conditioner indoor unit |
-
2008
- 2008-09-29 JP JP2008250077A patent/JP4502057B2/en active Active
-
2009
- 2009-08-11 EP EP09816001.3A patent/EP2345852B1/en active Active
- 2009-08-11 WO PCT/JP2009/064166 patent/WO2010035584A1/en active Application Filing
- 2009-08-11 ES ES09816001.3T patent/ES2626129T3/en active Active
- 2009-08-11 AU AU2009297727A patent/AU2009297727B2/en active Active
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN112797486A (en) * | 2020-12-28 | 2021-05-14 | 珠海格力电器股份有限公司 | Air conditioner indoor unit, control method and air conditioner |
Also Published As
Publication number | Publication date |
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JP4502057B2 (en) | 2010-07-14 |
AU2009297727B2 (en) | 2013-01-24 |
AU2009297727A1 (en) | 2010-04-01 |
WO2010035584A1 (en) | 2010-04-01 |
EP2345852A1 (en) | 2011-07-20 |
ES2626129T3 (en) | 2017-07-24 |
EP2345852A4 (en) | 2015-03-04 |
JP2010078274A (en) | 2010-04-08 |
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