WO2010089920A1 - 空気調和機の室内機、及び空気調和機 - Google Patents
空気調和機の室内機、及び空気調和機 Download PDFInfo
- Publication number
- WO2010089920A1 WO2010089920A1 PCT/JP2009/067265 JP2009067265W WO2010089920A1 WO 2010089920 A1 WO2010089920 A1 WO 2010089920A1 JP 2009067265 W JP2009067265 W JP 2009067265W WO 2010089920 A1 WO2010089920 A1 WO 2010089920A1
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- WIPO (PCT)
- Prior art keywords
- heat exchanger
- indoor unit
- side heat
- air
- air conditioner
- Prior art date
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Classifications
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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
- F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
- F24F1/0063—Indoor units, e.g. fan coil units characterised by heat exchangers by the mounting or arrangement of the heat exchangers
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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
- F24F1/0029—Axial fans
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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
- F24F1/0057—Indoor units, e.g. fan coil units characterised by mounting arrangements mounted in or on a wall
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
- F24F1/0067—Indoor units, e.g. fan coil units characterised by heat exchangers by the shape of the heat exchangers or of parts thereof, e.g. of their fins
-
- 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
- F24F1/0071—Indoor units, e.g. fan coil units with means for purifying supplied air
- F24F1/0073—Indoor units, e.g. fan coil units with means for purifying supplied air characterised by the mounting or arrangement of filters
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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
- F24F13/24—Means for preventing or suppressing noise
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
- F24F13/30—Arrangement or mounting of heat-exchangers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
- F24F13/24—Means for preventing or suppressing noise
- F24F2013/247—Active noise-suppression
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
- F28D2020/0004—Particular heat storage apparatus
- F28D2020/0013—Particular heat storage apparatus the heat storage material being enclosed in elements attached to or integral with heat exchange conduits
Definitions
- the present invention relates to an indoor unit in which a fan and a heat exchanger are housed in a casing (indoor unit), and an air conditioner including the indoor unit.
- an air conditioner in which a fan and a heat exchanger are housed in a casing.
- an air conditioner comprising a main body casing having an air inlet and an air outlet, and a heat exchanger disposed in the main body casing, wherein the air outlet includes a plurality of small propellers.
- an air conditioner in which a fan unit having a fan arranged in the width direction of the air outlet is disposed” (see, for example, Patent Document 1).
- This air conditioner is provided with a fan unit at the air outlet to facilitate airflow direction control, and a fan unit having the same configuration is also provided at the suction port to improve the heat exchanger performance due to an increase in the air volume. I am doing so.
- a heat exchanger is provided on the upstream side of a fan unit (blower). Since the movable fan unit is provided on the air outlet side, the air flow changes due to the movement of the fan and the instability of the flow due to asymmetric suction causes a decrease in the air volume and a reverse flow. Furthermore, the air whose flow is disturbed flows into the fan unit. That is, there is a problem that the flow of air flowing into the outer peripheral part of the wing (propeller) of the fan unit that increases the flow velocity is disturbed, and the fan unit itself becomes a noise source (causes noise deterioration). there were.
- the present invention has been made to solve the above-described problems, and is an indoor unit of an air conditioner that can suppress noise more than a conventional air conditioner, and an air conditioner including the indoor unit.
- the aim is to get a chance.
- An indoor unit of an air conditioner includes a casing having a suction port formed in an upper portion thereof and a blower outlet formed in a lower side of a front surface portion, and an axial flow type or a slant provided on the downstream side of the suction port in the casing.
- a flow type blower and a heat exchanger that is provided on the downstream side of the blower in the casing and upstream of the blower outlet and exchanges heat between the air blown out from the blower and the refrigerant. .
- an air conditioner according to the present invention is provided with the indoor unit described above.
- the blower since the blower is provided on the upstream side of the heat exchanger, the flow of air flowing into the blower is less disturbed. For this reason, the noise which generate
- FIG. 10 is a longitudinal sectional view showing an example of an indoor unit of an air conditioner according to Embodiment 8.
- FIG. 10 is a longitudinal sectional view showing an example of an indoor unit of an air conditioner according to Embodiment 9.
- FIG. It is a schematic block diagram which shows the main refrigerant circuit structures of the air conditioner 100 which concerns on Embodiment 11.
- FIG. 4 is a schematic diagram for explaining a configuration example of a heat exchanger 5.
- FIG. 4 is a schematic diagram for explaining a configuration example of a heat exchanger 5.
- FIG. 13 is a diagram showing an example in which the structure of the heat exchanger shown in FIG. 5 is adopted in FIG. 13. It is a figure which shows the example which employ
- FIG. 1 is a longitudinal sectional view showing an example of an indoor unit of an air conditioner according to Embodiment 1 of the present invention (hereinafter referred to as an indoor unit 40).
- FIG. 1 shows the left side of the drawing as the front side of the indoor unit 40.
- the indoor unit 40 supplies conditioned air to an air-conditioning target area such as a room by using a refrigeration cycle in which a refrigerant is circulated.
- the left side of the figure is shown as the front side of the indoor unit up to FIG. 10 (Embodiment 10) including FIG.
- the relationship of the size of each component may be different from the actual one.
- the case where the indoor unit 40 is a wall hanging type attached to the wall surface of the air-conditioning target area is shown as an example.
- the indoor unit 40 is mainly housed in the casing 1 in which a suction port 2 for sucking indoor air into the interior and a blower outlet 3 for supplying conditioned air to an air-conditioning target area are formed.
- the fan 4 sucks room air from the suction port 2 and blows out the conditioned air from the blower outlet 3, and is arranged in the air path from the suction port 2 to the fan 4 to exchange heat between the refrigerant and the room air.
- a heat exchanger 5 for producing And the air flow path (arrow A) is connected in the casing 1 by these components.
- the suction port 2 is formed in the upper part of the casing 1.
- the blower outlet 3 has an opening formed in the lower part of the casing 1 (more specifically, on the lower side of the front part of the casing 1).
- the fan 4 is disposed on the downstream side of the suction port 2 and on the upstream side of the heat exchanger 5, and is configured by, for example, an axial flow fan or a diagonal flow fan.
- the heat exchanger 5 is disposed on the leeward side of the fan 4. As this heat exchanger 5, for example, a fin tube heat exchanger or the like may be used.
- the suction port 2 is provided with a finger guard 6 and a filter 7.
- the blower outlet 3 is provided with a mechanism for controlling the blowing direction of the airflow, such as a vane (not shown).
- the fan 4 corresponds to the blower of the present invention.
- the flow of air in the indoor unit 40 will be briefly described.
- the indoor air flows into the indoor unit 40 from the suction port 2 formed in the upper part of the casing 1 by the fan 4.
- dust contained in the air is removed by the filter 7.
- This indoor air is heated or cooled by the refrigerant that is conducted through the heat exchanger 5 when passing through the heat exchanger 5 to become conditioned air.
- the conditioned air is blown out of the indoor unit 40 from the blowout port 3 formed in the lower part of the casing 1, that is, to the air-conditioning target area.
- the air that has passed through the filter 7 flows into the fan 4. That is, the air flowing into the fan 4 is less disturbed than the air flowing into the indoor unit provided in the indoor unit of the conventional air conditioner (passed through the heat exchanger). For this reason, compared with the conventional air conditioner, the air passing through the outer peripheral part of the wing part of the fan 4 is less disturbed in the flow. Therefore, the air conditioner 100 according to Embodiment 1 can suppress noise as compared with the indoor unit of the conventional air conditioner.
- the fan 4 is provided in the upstream of the heat exchanger 5, the indoor unit 40 is blown out from the blower outlet 3, compared with the indoor unit of the conventional air conditioner in which the fan is provided in the blower outlet.
- the generation of the swirling air flow and the generation of the wind speed distribution can be suppressed.
- there is no complicated structure such as a fan at the air outlet 3 it is easy to take measures against dew condensation caused by backflow or the like.
- Embodiment 2 By configuring the heat exchanger 5 as follows, noise can be further suppressed.
- the difference from the first embodiment will be mainly described, and the same parts as those in the first embodiment are denoted by the same reference numerals.
- the indoor unit is a wall-mounted type attached to the wall surface of the air-conditioning target area is shown as an example.
- FIG. 2 is a longitudinal sectional view showing an example of an indoor unit of an air conditioner (hereinafter referred to as an indoor unit 50) according to Embodiment 2 of the present invention. Based on FIG. 2, the arrangement
- the indoor unit 50 supplies conditioned air to an air-conditioning target area such as a room by using a refrigeration cycle in which a refrigerant is circulated.
- the front-side heat exchanger 9 and the back-side heat exchanger 10 constituting the heat exchanger 5 are vertically sectioned from the front side to the back side of the indoor unit 50 (that is, the indoor unit).
- the vertical section 50 is viewed from the right side (hereinafter also referred to as the right vertical section), and is divided by the symmetry line 8.
- the symmetry line 8 divides the installation range of the heat exchanger 5 in this cross section in the left-right direction at a substantially central portion. That is, the front-side heat exchanger 9 is arranged on the front side (left side of the drawing) with respect to the symmetry line 8, and the back-side heat exchanger 10 is arranged on the back side (right side of the drawing) with respect to the symmetry line 8.
- the front-side heat exchanger 9 and the rear-side heat exchanger 10 are arranged so that the distance between the front-side heat exchanger 9 and the rear-side heat exchanger 10 is narrower with respect to the air flow direction, that is, the right side longitudinal section. It is arrange
- the front side heat exchanger 9 and the back side heat exchanger 10 are arranged so as to be inclined with respect to the flow direction of the air supplied from the fan 4. Furthermore, the air path area of the back surface side heat exchanger 10 is characterized by being larger than the air path area of the front surface side heat exchanger 9.
- the length in the longitudinal direction of the back side heat exchanger 10 is longer than the length in the longitudinal direction of the front side heat exchanger 9 in the right vertical section. Thereby, the air path area of the back surface side heat exchanger 10 is larger than the air path area of the front surface side heat exchanger 9.
- the other structure (the length of the depth direction in FIG. 2, etc.) of the front side heat exchanger 9 and the back side heat exchanger 10 is the same. That is, the heat transfer area of the back side heat exchanger 10 is larger than the heat transfer area of the front side heat exchanger 9. Further, the rotating shaft 11 of the fan 4 is installed above the symmetry line 8.
- the fan 4 is provided on the upstream side of the heat exchanger 5, the same effect as in the first embodiment can be obtained.
- the quantity of air according to an air path area passes through each of the front side heat exchanger 9 and the back side heat exchanger 10.
- this merged air will bend to the front side (blower outlet 3 side).
- the indoor unit 50 according to the second embodiment can further suppress noise compared to the indoor unit 40 according to the first embodiment. Moreover, since the indoor unit 50 can reduce the pressure loss in the blower outlet 3 vicinity, it also becomes possible to reduce power consumption.
- the heat exchanger 5 shown in FIG. 2 is comprised by the substantially V type by the front side heat exchanger 9 and the back side heat exchanger 10 which were formed separately, it is not limited to this structure.
- the front-side heat exchanger 9 and the back-side heat exchanger 10 may be configured as an integrated heat exchanger (see FIG. 12).
- each of the front side heat exchanger 9 and the back side heat exchanger 10 may be configured by a combination of a plurality of heat exchangers (see FIG. 12).
- the front side is the front side heat exchanger 9 and the rear side is the back side heat exchanger 10 with respect to the symmetry line 8.
- the length in the longitudinal direction of the heat exchanger disposed on the back side of the symmetry line 8 may be longer than the length of the heat exchanger disposed on the front side of the symmetry line 8.
- the longitudinal lengths of the plurality of heat exchangers constituting the front-side heat exchanger 9 are each. Is the length of the front heat exchanger 9 in the longitudinal direction.
- the sum of the longitudinal lengths of the plurality of heat exchangers constituting the back side heat exchanger 10 is the longitudinal length of the back side heat exchanger 10.
- the heat exchanger 5 is composed of a plurality of heat exchangers (for example, when the heat exchanger 5 is composed of the front side heat exchanger 9 and the back side heat exchanger 10), the location where the arrangement gradient of the heat exchanger 5 changes ( For example, the heat exchangers do not have to be completely in contact with each other at a substantial connection point between the front-side heat exchanger 9 and the rear-side heat exchanger 10, and there may be some gaps.
- the shape of the heat exchanger 5 in the right vertical section may be partially or entirely curved (see FIG. 12).
- FIG. 12 is a schematic diagram for explaining a configuration example of the heat exchanger 5.
- This FIG. 12 has shown the heat exchanger 5 seen from the right side longitudinal cross-section.
- the whole shape of the heat exchanger 5 shown in FIG. 12 is a substantially (LAMBDA) type
- the whole shape of a heat exchanger is an example to the last.
- Fig.12 (a) you may comprise the heat exchanger 5 with a some heat exchanger.
- FIG.12 (b) you may comprise the heat exchanger 5 with an integrated heat exchanger.
- the shape of the heat exchanger 5 may be a curved shape.
- Embodiment 3 FIG.
- the heat exchanger 5 may be configured as follows.
- the difference from the above-described second embodiment will be mainly described, and the same parts as those in the second embodiment are denoted by the same reference numerals.
- the case where the indoor unit is a wall-mounted type attached to the wall surface of the air-conditioning target area is shown as an example.
- FIG. 3 is a longitudinal sectional view showing an example of an indoor unit of an air conditioner according to Embodiment 3 of the present invention (hereinafter referred to as an indoor unit 50a). Based on FIG. 3, the arrangement
- the indoor unit 50a supplies conditioned air to an air-conditioning target area such as a room by using a refrigeration cycle that circulates refrigerant.
- the arrangement of the heat exchanger 5 is different from the indoor unit 50 of the second embodiment.
- the heat exchanger 5 is composed of three heat exchangers, and each of these heat exchangers is arranged with a different inclination with respect to the flow direction of the air supplied from the fan 4. And the heat exchanger 5 becomes a substantially N type in the right side longitudinal cross-section.
- the heat exchanger 9a and the heat exchanger 9b arranged on the front side of the symmetry line 8 constitute the front side heat exchanger 9
- the heat exchanger 10b constitutes the back side heat exchanger 10.
- the heat exchanger 9b and the heat exchanger 10b are configured as an integrated heat exchanger.
- the symmetry line 8 divides the installation range of the heat exchanger 5 in the right vertical section in the left-right direction at a substantially central portion.
- the length in the longitudinal direction of the back side heat exchanger 10 is longer than the length in the longitudinal direction of the front side heat exchanger 9. That is, the air volume of the back surface side heat exchanger 10 is larger than the air volume of the front surface side heat exchanger 9.
- the comparison of the lengths is the sum of the lengths of the heat exchanger groups constituting the front-side heat exchanger 9 and the sum of the lengths of the heat exchanger groups constituting the rear-side heat exchanger 10. Should be compared.
- the air volume of the back side heat exchanger 10 is larger than the air volume of the front side heat exchanger 9.
- this merged air is the front side (air outlet 3 To the side).
- the indoor unit 50a according to the third embodiment can further suppress noise compared to the indoor unit 40 according to the first embodiment.
- the indoor unit 50a can reduce the pressure loss in the vicinity of the blower outlet 3, it also becomes possible to reduce power consumption.
- the shape of the heat exchanger 5 substantially N-shaped in the right vertical section, it is possible to increase the area through which the front side heat exchanger 9 and the back side heat exchanger 10 pass, so each passes through.
- the wind speed can be made smaller than that in the second embodiment. For this reason, compared with Embodiment 2, the pressure loss in the front side heat exchanger 9 and the back side heat exchanger 10 can be reduced, and further reduction in power consumption and noise can be achieved.
- the heat exchanger 5 shown in FIG. 3 is comprised by the substantially N type by the three heat exchangers formed separately, it is not limited to this structure.
- the three heat exchangers constituting the heat exchanger 5 may be configured as an integrated heat exchanger (see FIG. 12).
- each of the three heat exchangers constituting the heat exchanger 5 may be configured by a combination of a plurality of heat exchangers (see FIG. 12).
- the front side is the front side heat exchanger 9 and the rear side is the back side heat exchanger 10 with respect to the symmetry line 8.
- the length in the longitudinal direction of the heat exchanger disposed on the back side of the symmetry line 8 may be longer than the length of the heat exchanger disposed on the front side of the symmetry line 8.
- the longitudinal lengths of the plurality of heat exchangers constituting the front-side heat exchanger 9 are each. Is the length of the front heat exchanger 9 in the longitudinal direction.
- the sum of the longitudinal lengths of the plurality of heat exchangers constituting the back side heat exchanger 10 is the longitudinal length of the back side heat exchanger 10.
- the heat exchanger 5 it is not necessary to incline all the heat exchangers constituting the heat exchanger 5 in the right vertical section, and a part of the heat exchangers constituting the heat exchanger 5 may be arranged vertically in the right vertical section. (See FIG. 12). Further, when the heat exchanger 5 is composed of a plurality of heat exchangers, it is not necessary that the heat exchangers are completely in contact with each other at the location where the arrangement gradient of the heat exchanger 5 is changed, and there are some gaps. May be. Moreover, the shape of the heat exchanger 5 in the right vertical section may be partially or entirely curved (see FIG. 12).
- Embodiment 4 FIG. Moreover, the heat exchanger 5 may be configured as follows.
- the difference from the above-described second and third embodiments will be mainly described, and the same parts as those in the second and third embodiments are denoted by the same reference numerals. is doing.
- the case where the indoor unit is a wall-mounted type attached to the wall surface of the air-conditioning target area is shown as an example.
- FIG. 4 is a longitudinal sectional view showing an example of an indoor unit of an air conditioner according to Embodiment 4 of the present invention (hereinafter referred to as an indoor unit 50b). Based on FIG. 4, the arrangement
- the indoor unit 50b supplies conditioned air to an air-conditioning target area such as a room by using a refrigeration cycle that circulates refrigerant.
- the arrangement of the heat exchanger 5 is different from the indoor units shown in the second and third embodiments.
- the heat exchanger 5 is composed of four heat exchangers, and each of these heat exchangers is arranged with a different inclination with respect to the flow direction of the air supplied from the fan 4. And the heat exchanger 5 becomes a substantially W type in the right side longitudinal cross-section.
- the heat exchanger 9a and the heat exchanger 9b arranged on the front side of the symmetry line 8 constitute the front side heat exchanger 9
- the heat exchanger 10b constitutes the back side heat exchanger 10.
- the symmetry line 8 divides the installation range of the heat exchanger 5 in the right vertical section in the left-right direction at a substantially central portion.
- the length in the longitudinal direction of the back side heat exchanger 10 is longer than the length in the longitudinal direction of the front side heat exchanger 9. That is, the air volume of the back surface side heat exchanger 10 is larger than the air volume of the front surface side heat exchanger 9.
- the comparison of the lengths is the sum of the lengths of the heat exchanger groups constituting the front-side heat exchanger 9 and the sum of the lengths of the heat exchanger groups constituting the rear-side heat exchanger 10. Should be compared.
- the air volume of the back side heat exchanger 10 is larger than the air volume of the front side heat exchanger 9. Therefore, as in the second and third embodiments, when the air that has passed through each of the front-side heat exchanger 9 and the rear-side heat exchanger 10 merges due to the difference in air volume, It will bend to the side (air outlet 3 side). For this reason, it is no longer necessary to bend the airflow rapidly in the vicinity of the outlet 3, and the pressure loss in the vicinity of the outlet 3 can be reduced. Therefore, the indoor unit 50b according to the fourth embodiment can further suppress noise compared to the indoor unit 40 according to the first embodiment. Moreover, since the indoor unit 50b can reduce the pressure loss in the vicinity of the blower outlet 3, it also becomes possible to reduce power consumption.
- the area which passes the front side heat exchanger 9 and the back side heat exchanger 10 can be taken large by making the shape of the heat exchanger 5 into a substantially W type in the right vertical section, it passes each. It becomes possible to make a wind speed smaller than Embodiment 2 and Embodiment 3. For this reason, compared with Embodiment 2 and Embodiment 3, the pressure loss in the front side heat exchanger 9 and the back side heat exchanger 10 can be reduced, and further reduction in power consumption and noise is possible. It becomes.
- the heat exchanger 5 shown in FIG. 4 is comprised by the substantially W type
- each of the four heat exchangers constituting the heat exchanger 5 may be configured by a combination of a plurality of heat exchangers (see FIG. 12).
- the front side is the front side heat exchanger 9 and the rear side is the back side heat exchanger 10 with respect to the symmetry line 8.
- the length in the longitudinal direction of the heat exchanger disposed on the back side of the symmetry line 8 may be longer than the length of the heat exchanger disposed on the front side of the symmetry line 8.
- the longitudinal lengths of the plurality of heat exchangers constituting the front-side heat exchanger 9 are each. Is the length of the front heat exchanger 9 in the longitudinal direction.
- the sum of the longitudinal lengths of the plurality of heat exchangers constituting the back side heat exchanger 10 is the longitudinal length of the back side heat exchanger 10.
- the heat exchanger 5 it is not necessary to incline all the heat exchangers constituting the heat exchanger 5 in the right vertical section, and a part of the heat exchangers constituting the heat exchanger 5 may be arranged vertically in the right vertical section. (See FIG. 12). Further, when the heat exchanger 5 is composed of a plurality of heat exchangers, it is not necessary that the heat exchangers are completely in contact with each other at the location where the arrangement gradient of the heat exchanger 5 is changed, and there are some gaps. May be. Moreover, the shape of the heat exchanger 5 in the right vertical section may be partially or entirely curved (see FIG. 12).
- Embodiment 5 FIG. Moreover, the heat exchanger 5 may be configured as follows. In the fifth embodiment, differences from the above-described second to fourth embodiments will be mainly described, and the same parts as those in the second to fourth embodiments are denoted by the same reference numerals. is doing. Moreover, the case where the indoor unit is a wall-mounted type attached to the wall surface of the air-conditioning target area is shown as an example.
- FIG. 5 is a longitudinal sectional view showing an example of an indoor unit of an air conditioner according to Embodiment 5 of the present invention (hereinafter referred to as an indoor unit 50c). Based on FIG. 5, the method of arrangement
- the indoor unit 50c supplies conditioned air to an air-conditioning target area such as a room by using a refrigeration cycle that circulates refrigerant.
- the arrangement of the heat exchanger 5 is different from the indoor units shown in the second to fourth embodiments. More specifically, the indoor unit 50c of the fifth embodiment is configured by two heat exchangers (a front side heat exchanger 9 and a back side heat exchanger 10), as in the second embodiment. However, the arrangement of the front-side heat exchanger 9 and the rear-side heat exchanger 10 is different from the indoor unit 50 shown in the second embodiment.
- the front side heat exchanger 9 and the back side heat exchanger 10 are arranged with different inclinations with respect to the flow direction of the air supplied from the fan 4.
- a front side heat exchanger 9 is disposed on the front side of the symmetry line 8
- a back side heat exchanger 10 is disposed on the back side of the symmetry line 8.
- the heat exchanger 5 has a substantially ⁇ shape in the right vertical section.
- the symmetry line 8 divides the installation range of the heat exchanger 5 in the right vertical section in the left-right direction at a substantially central portion.
- the length in the longitudinal direction of the back side heat exchanger 10 is longer than the length in the longitudinal direction of the front side heat exchanger 9. That is, the air volume of the back surface side heat exchanger 10 is larger than the air volume of the front surface side heat exchanger 9.
- the comparison of the lengths is the sum of the lengths of the heat exchanger groups constituting the front-side heat exchanger 9 and the sum of the lengths of the heat exchanger groups constituting the rear-side heat exchanger 10. Should be compared.
- the indoor unit 50c configured as described above has the following internal air flow.
- the indoor air flows into the indoor unit 50 c from the suction port 2 formed in the upper part of the casing 1 by the fan 4.
- dust contained in the air is removed by the filter 7.
- this indoor air passes through the heat exchanger 5 (the front-side heat exchanger 9 and the back-side heat exchanger 10), it is heated or cooled by the refrigerant that is conducted through the heat exchanger 5 to become conditioned air.
- the air passing through the front side heat exchanger 9 flows from the front side to the back side of the indoor unit 50c.
- the air which passes the back side heat exchanger 10 flows from the back side of the indoor unit 50c to the front side.
- the conditioned air that has passed through the heat exchanger 5 (the front-side heat exchanger 9 and the back-side heat exchanger 10) passes from the outlet 3 formed in the lower part of the casing 1 to the outside of the indoor unit 50c, that is, the air-conditioning target area. Blown out.
- the air volume of the back side heat exchanger 10 is larger than the air volume of the front side heat exchanger 9. Therefore, as in the second to fourth embodiments, when the air that has passed through each of the front-side heat exchanger 9 and the rear-side heat exchanger 10 joins due to the difference in air volume, It will bend to the side (air outlet 3 side). For this reason, it is no longer necessary to bend the airflow rapidly in the vicinity of the outlet 3, and the pressure loss in the vicinity of the outlet 3 can be reduced. Therefore, the indoor unit 50c according to the fifth embodiment can further suppress noise compared to the indoor unit 40 according to the first embodiment. Moreover, since the indoor unit 50c can reduce the pressure loss in the vicinity of the blower outlet 3, it also becomes possible to reduce power consumption.
- the flow direction of the air flowing out from the back side heat exchanger 10 is the flow from the back side to the front side.
- the indoor unit 50c according to the fifth embodiment can more easily bend the air flow after passing through the heat exchanger 5. That is, the indoor unit 50c according to the fifth embodiment can more easily control the airflow of the air blown out from the outlet 3 than the indoor unit 50 according to the second embodiment. Therefore, compared to the indoor unit 50 according to the second embodiment, the indoor unit 50c according to the fifth embodiment further eliminates the need to bend the airflow in the vicinity of the air outlet 3, and further reduces power consumption and noise. Is possible.
- the heat exchanger 5 shown in FIG. 5 is comprised by the substantially (LAMBDA) type
- the front-side heat exchanger 9 and the back-side heat exchanger 10 may be configured as an integrated heat exchanger (see FIG. 12).
- each of the front side heat exchanger 9 and the back side heat exchanger 10 may be configured by a combination of a plurality of heat exchangers (see FIG. 12).
- the front side is the front side heat exchanger 9 and the rear side is the back side heat exchanger 10 with respect to the symmetry line 8.
- the length in the longitudinal direction of the heat exchanger disposed on the back side of the symmetry line 8 may be longer than the length of the heat exchanger disposed on the front side of the symmetry line 8.
- the longitudinal lengths of the plurality of heat exchangers constituting the front-side heat exchanger 9 are each. Is the length of the front heat exchanger 9 in the longitudinal direction.
- the sum of the longitudinal lengths of the plurality of heat exchangers constituting the back side heat exchanger 10 is the longitudinal length of the back side heat exchanger 10.
- the heat exchanger 5 it is not necessary to incline all the heat exchangers constituting the heat exchanger 5 in the right vertical section, and a part of the heat exchangers constituting the heat exchanger 5 may be arranged vertically in the right vertical section. (See FIG. 12). Further, when the heat exchanger 5 is composed of a plurality of heat exchangers, it is not necessary that the heat exchangers are completely in contact with each other at the location where the arrangement gradient of the heat exchanger 5 is changed, and there are some gaps. May be. Moreover, the shape of the heat exchanger 5 in the right vertical section may be partially or entirely curved (see FIG. 12).
- Embodiment 6 FIG. Moreover, the heat exchanger 5 may be configured as follows. In the sixth embodiment, the differences from the above-described second to fifth embodiments will be mainly described, and the same parts as those in the second to fifth embodiments are denoted by the same reference numerals. ing. Moreover, the case where the indoor unit is a wall-mounted type attached to the wall surface of the air-conditioning target area is shown as an example.
- FIG. 6 is a longitudinal sectional view showing an example of an indoor unit of an air conditioner according to Embodiment 6 of the present invention (hereinafter referred to as an indoor unit 50d). Based on FIG. 6, the arrangement
- the indoor unit 50d supplies conditioned air to an air-conditioning target area such as a room by using a refrigeration cycle that circulates refrigerant.
- the arrangement of the heat exchanger 5 is different from the indoor units shown in the second to fifth embodiments. More specifically, the indoor unit 50d of the sixth embodiment is composed of three heat exchangers as in the third embodiment. However, the arrangement of these three heat exchangers is different from the indoor unit 50a shown in the third embodiment.
- each of the three heat exchangers constituting the heat exchanger 5 is arranged with a different inclination with respect to the flow direction of the air supplied from the fan 4.
- the heat exchanger 5 has a substantially ⁇ type in the right vertical section.
- the heat exchanger 9a and the heat exchanger 9b arranged on the front side of the symmetry line 8 constitute the front side heat exchanger 9
- the heat exchanger 10b constitutes the back side heat exchanger 10. That is, in the sixth embodiment, the heat exchanger 9b and the heat exchanger 10b are configured as an integrated heat exchanger.
- the symmetry line 8 divides the installation range of the heat exchanger 5 in the right vertical section in the left-right direction at a substantially central portion.
- the length in the longitudinal direction of the back side heat exchanger 10 is longer than the length in the longitudinal direction of the front side heat exchanger 9. That is, the air volume of the back surface side heat exchanger 10 is larger than the air volume of the front surface side heat exchanger 9.
- the comparison of the lengths is the sum of the lengths of the heat exchanger groups constituting the front-side heat exchanger 9 and the sum of the lengths of the heat exchanger groups constituting the rear-side heat exchanger 10. Should be compared.
- the air volume of the back side heat exchanger 10 is larger than the air volume of the front side heat exchanger 9. Therefore, as in the second to fifth embodiments, when the air that has passed through each of the front-side heat exchanger 9 and the rear-side heat exchanger 10 joins due to the difference in air volume, It will bend to the side (air outlet 3 side). For this reason, it is no longer necessary to bend the airflow rapidly in the vicinity of the outlet 3, and the pressure loss in the vicinity of the outlet 3 can be reduced. Therefore, the indoor unit 50d according to the sixth embodiment can further suppress noise compared to the indoor unit 40 according to the first embodiment. Moreover, since the indoor unit 50d can reduce the pressure loss in the vicinity of the blower outlet 3, the power consumption can also be reduced.
- the flow direction of the air flowing out from the back side heat exchanger 10 is the flow from the back side to the front side.
- the indoor unit 50d according to the sixth embodiment can bend the air flow after passing through the heat exchanger 5 more easily. That is, the indoor unit 50d according to the sixth embodiment can more easily control the airflow of the air blown from the outlet 3 than the indoor unit 50a according to the third embodiment. Therefore, the indoor unit 50d according to the sixth embodiment does not need to bend the airflow in the vicinity of the air outlet 3 more rapidly than the indoor unit 50a according to the third embodiment, thereby further reducing power consumption and noise. Is possible.
- the area passing through the front side heat exchanger 9 and the back side heat exchanger 10 can be increased, so that each passes through.
- the wind speed can be made smaller than that in the fifth embodiment. For this reason, compared with Embodiment 5, the pressure loss in the front side heat exchanger 9 and the back side heat exchanger 10 can be reduced, and further reduction in power consumption and noise can be achieved.
- the heat exchanger 5 shown in FIG. 6 is comprised by the substantially ⁇ type
- the three heat exchangers constituting the heat exchanger 5 may be configured as an integrated heat exchanger (see FIG. 12).
- each of the three heat exchangers constituting the heat exchanger 5 may be configured by a combination of a plurality of heat exchangers (see FIG. 12).
- the front side is the front side heat exchanger 9 and the rear side is the back side heat exchanger 10 with respect to the symmetry line 8.
- the length in the longitudinal direction of the heat exchanger disposed on the back side of the symmetry line 8 may be longer than the length of the heat exchanger disposed on the front side of the symmetry line 8.
- the longitudinal lengths of the plurality of heat exchangers constituting the front-side heat exchanger 9 are each. Is the length of the front heat exchanger 9 in the longitudinal direction.
- the sum of the longitudinal lengths of the plurality of heat exchangers constituting the back side heat exchanger 10 is the longitudinal length of the back side heat exchanger 10.
- the heat exchanger 5 it is not necessary to incline all the heat exchangers constituting the heat exchanger 5 in the right vertical section, and a part of the heat exchangers constituting the heat exchanger 5 may be arranged vertically in the right vertical section. (See FIG. 12). Further, when the heat exchanger 5 is composed of a plurality of heat exchangers, it is not necessary that the heat exchangers are completely in contact with each other at the location where the arrangement gradient of the heat exchanger 5 is changed, and there are some gaps. May be. Moreover, the shape of the heat exchanger 5 in the right vertical section may be partially or entirely curved (see FIG. 12).
- Embodiment 7 FIG. Moreover, the heat exchanger 5 may be configured as follows. In the seventh embodiment, the difference from the above-described second to sixth embodiments will be mainly described. The same parts as those in the second to sixth embodiments are denoted by the same reference numerals. ing. Moreover, the case where the indoor unit is a wall-mounted type attached to the wall surface of the air-conditioning target area is shown as an example.
- FIG. 7 is a longitudinal sectional view showing an example of an air conditioner indoor unit (hereinafter, referred to as an indoor unit 50e) according to Embodiment 7 of the present invention. Based on FIG. 7, the arrangement
- the indoor unit 50e supplies conditioned air to an air-conditioning target area such as a room by using a refrigeration cycle that circulates refrigerant.
- the arrangement of the heat exchanger 5 is different from the indoor units shown in the second to sixth embodiments. More specifically, the indoor unit 50e according to the seventh embodiment includes four heat exchangers as in the fourth embodiment. However, the arrangement of these four heat exchangers is different from the indoor unit 50b shown in the fourth embodiment.
- each of the four heat exchangers constituting the heat exchanger 5 is arranged with a different inclination with respect to the flow direction of the air supplied from the fan 4.
- the heat exchanger 5 has a substantially M shape in the right vertical section.
- the heat exchanger 9a and the heat exchanger 9b arranged on the front side of the symmetry line 8 constitute the front side heat exchanger 9
- the heat exchanger 10b constitutes the back side heat exchanger 10.
- the symmetry line 8 divides the installation range of the heat exchanger 5 in the right vertical section in the left-right direction at a substantially central portion.
- the length in the longitudinal direction of the back side heat exchanger 10 is longer than the length in the longitudinal direction of the front side heat exchanger 9. That is, the air volume of the back surface side heat exchanger 10 is larger than the air volume of the front surface side heat exchanger 9.
- the comparison of the lengths is the sum of the lengths of the heat exchanger groups constituting the front-side heat exchanger 9 and the sum of the lengths of the heat exchanger groups constituting the rear-side heat exchanger 10. Should be compared.
- the air volume of the back side heat exchanger 10 is larger than the air volume of the front side heat exchanger 9. Therefore, as in Embodiments 2 to 6, when the air that has passed through each of the front-side heat exchanger 9 and the rear-side heat exchanger 10 joins due to the difference in air volume, It will bend to the side (air outlet 3 side). For this reason, it is no longer necessary to bend the airflow rapidly in the vicinity of the outlet 3, and the pressure loss in the vicinity of the outlet 3 can be reduced. Therefore, the indoor unit 50e according to the seventh embodiment can further suppress noise compared to the indoor unit 40 according to the first embodiment. Moreover, since the indoor unit 50e can reduce the pressure loss in the vicinity of the blower outlet 3, it also becomes possible to reduce power consumption.
- the indoor unit 50e according to the seventh embodiment the flow direction of the air flowing out from the back side heat exchanger 10 is the flow from the back side to the front side. For this reason, the indoor unit 50e which concerns on this Embodiment 7 becomes easier to bend the flow of the air after passing the heat exchanger 5.
- FIG. That is, the indoor unit 50e according to the seventh embodiment can more easily control the airflow of the air blown from the outlet 3 than the indoor unit 50b according to the fourth embodiment. Therefore, in the indoor unit 50e according to the seventh embodiment, compared with the indoor unit 50b according to the fourth embodiment, it is no longer necessary to bend the airflow in the vicinity of the air outlet 3 and further reduce power consumption and noise. Is possible.
- the area which passes the front side heat exchanger 9 and the back side heat exchanger 10 can be taken large by making the shape of the heat exchanger 5 into a substantially M type in the right-side vertical cross section, it passes each. It becomes possible to make a wind speed smaller than Embodiment 5 and Embodiment 6. FIG. For this reason, compared with Embodiment 2 and Embodiment 6, the pressure loss in the front side heat exchanger 9 and the back side heat exchanger 10 can be reduced, and further power consumption and noise can be reduced. It becomes.
- the heat exchanger 5 shown in FIG. 7 is comprised by the substantially M type
- each of the four heat exchangers constituting the heat exchanger 5 may be configured by a combination of a plurality of heat exchangers (see FIG. 12).
- the front side is the front side heat exchanger 9 and the rear side is the back side heat exchanger 10 with respect to the symmetry line 8.
- the length in the longitudinal direction of the heat exchanger disposed on the back side of the symmetry line 8 may be longer than the length of the heat exchanger disposed on the front side of the symmetry line 8.
- the longitudinal lengths of the plurality of heat exchangers constituting the front-side heat exchanger 9 are each. Is the length of the front heat exchanger 9 in the longitudinal direction.
- the sum of the longitudinal lengths of the plurality of heat exchangers constituting the back side heat exchanger 10 is the longitudinal length of the back side heat exchanger 10.
- the heat exchanger 5 it is not necessary to incline all the heat exchangers constituting the heat exchanger 5 in the right vertical section, and a part of the heat exchangers constituting the heat exchanger 5 may be arranged vertically in the right vertical section. (See FIG. 12). Further, when the heat exchanger 5 is composed of a plurality of heat exchangers, it is not necessary that the heat exchangers are completely in contact with each other at the location where the arrangement gradient of the heat exchanger 5 is changed, and there are some gaps. May be. Moreover, the shape of the heat exchanger 5 in the right vertical section may be partially or entirely curved (see FIG. 12).
- Embodiment 8 FIG. Moreover, the heat exchanger 5 may be configured as follows.
- the difference from the above-described second to seventh embodiments will be mainly described, and the same parts as those in the second to seventh embodiments are denoted by the same reference numerals. ing.
- the case where the indoor unit is a wall-mounted type attached to the wall surface of the air-conditioning target area is shown as an example.
- FIG. 8 is a longitudinal sectional view showing an example of an indoor unit of an air conditioner according to Embodiment 7 of the present invention (hereinafter referred to as an indoor unit 50f). Based on FIG. 8, the method of arrangement
- the indoor unit 50f supplies conditioned air to an air-conditioning target area such as a room by using a refrigeration cycle in which a refrigerant is circulated.
- the arrangement of the heat exchanger 5 is different from the indoor units shown in the second to seventh embodiments. More specifically, the indoor unit 50f of the eighth embodiment is composed of two heat exchangers (a front-side heat exchanger 9 and a rear-side heat exchanger 10), as in the fifth embodiment, and has a right vertical cross section. In FIG. However, in Embodiment 8, the pressure loss of the front side heat exchanger 9 and the pressure loss of the back side heat exchanger 10 are made different from each other, whereby the air volume of the front side heat exchanger 9 and the back side heat exchange are changed. The air volume of the vessel 10 is different.
- the front side heat exchanger 9 and the back side heat exchanger 10 are arranged with different inclinations with respect to the flow direction of the air supplied from the fan 4.
- a front side heat exchanger 9 is arranged on the front side of the symmetry line 8
- a back side heat exchanger 10 is arranged on the back side of the symmetry line 8.
- the heat exchanger 5 has a substantially ⁇ shape in the right vertical section.
- the length in the longitudinal direction of the back side heat exchanger 10 and the length in the longitudinal direction of the front side heat exchanger 9 are the same. And the specifications of the front side heat exchanger 9 and the back side heat exchanger 10 are determined so that the pressure loss of the back side heat exchanger 10 becomes smaller than the pressure loss of the front side heat exchanger 9.
- the length in the short side direction (fin width) of the back side heat exchanger 10 in the right vertical section is set to the right side.
- the distance between the fins of the right rear heat exchanger 10 may be larger than the distance between the fins of the front heat exchanger 9.
- the pipe diameter of the right rear heat exchanger 10 may be smaller than the pipe diameter of the front heat exchanger 9.
- the number of pipes of the right rear side heat exchanger 10 may be smaller than the number of pipes of the front side heat exchanger 9.
- the symmetry line 8 divides the installation range of the heat exchanger 5 in the right vertical section in the left-right direction at a substantially central portion.
- the same effect as in the first embodiment can be obtained.
- an amount of air corresponding to the pressure loss passes through each of the front-side heat exchanger 9 and the rear-side heat exchanger 10. That is, the air volume of the back surface side heat exchanger 10 is larger than the air volume of the front surface side heat exchanger 9. And when the air which passed each of the front side heat exchanger 9 and the back side heat exchanger 10 merges by this air volume difference, this merged air will bend to the front side (blower outlet 3 side).
- the indoor unit 50f according to the eighth embodiment suppresses noise further than the indoor unit 40 according to the first embodiment without increasing the length of the rear side heat exchanger 10 in the right vertical section. Is possible. Moreover, since the indoor unit 50f can reduce the pressure loss in the vicinity of the blower outlet 3, the power consumption can also be reduced.
- the heat exchanger 5 shown in FIG. 8 is configured in a substantially ⁇ shape by the front side heat exchanger 9 and the back side heat exchanger 10 formed separately, but is not limited to this configuration.
- the shape of the heat exchanger 5 in the right vertical section may be configured to be approximately V-shaped, approximately N-shaped, approximately W-shaped, approximately ⁇ -shaped, approximately M-shaped, or the like.
- each of the front side heat exchanger 9 and the back side heat exchanger 10 may be configured by a combination of a plurality of heat exchangers (see FIG. 12).
- the front side is the front side heat exchanger 9 and the rear side is the back side heat exchanger 10 with respect to the symmetry line 8. That is, the length in the longitudinal direction of the heat exchanger disposed on the back side of the symmetry line 8 may be longer than the length of the heat exchanger disposed on the front side of the symmetry line 8.
- the longitudinal lengths of the plurality of heat exchangers constituting the front-side heat exchanger 9 are each. Is the length of the front heat exchanger 9 in the longitudinal direction.
- the sum of the longitudinal lengths of the plurality of heat exchangers constituting the back side heat exchanger 10 is the longitudinal length of the back side heat exchanger 10.
- the heat exchanger 5 is composed of a plurality of heat exchangers (for example, when the heat exchanger 5 is composed of the front side heat exchanger 9 and the back side heat exchanger 10), the location where the arrangement gradient of the heat exchanger 5 changes ( For example, the heat exchangers do not have to be completely in contact with each other at a substantial connection point between the front-side heat exchanger 9 and the rear-side heat exchanger 10, and there may be some gaps.
- the shape of the heat exchanger 5 in the right vertical section may be partially or entirely curved (see FIG. 12).
- Embodiment 9 FIG. Further, in Embodiments 2 to 8 described above, fan 4 may be arranged as follows. In the ninth embodiment, differences from the above-described second to eighth embodiments will be mainly described, and the same parts as those in the second to eighth embodiments are denoted by the same reference numerals. ing. Moreover, the case where the indoor unit is a wall-mounted type attached to the wall surface of the air-conditioning target area is shown as an example.
- FIG. 9 is a longitudinal sectional view showing an example of an indoor unit of an air conditioner according to Embodiment 9 of the present invention (hereinafter, referred to as an indoor unit 50g). Based on FIG. 9A to FIG. 9C, a method of arranging the fan 4 in the indoor unit 50g will be described.
- the indoor unit 50g supplies conditioned air to an air-conditioning target area such as a room by using a refrigeration cycle that circulates refrigerant.
- the heat exchanger 5 of the indoor unit 50g according to the ninth embodiment has the same arrangement as the indoor unit 50c of the fifth embodiment.
- the indoor unit 50g according to the ninth embodiment is different from the indoor unit 50c according to the fifth embodiment in the manner in which the fan 4 is arranged. That is, in the indoor unit 50g according to the ninth embodiment, the arrangement position of the fan 4 is determined according to the air volume and the heat transfer area of the front side heat exchanger 9 and the back side heat exchanger 10.
- the heat transfer area is larger than that of the front heat exchanger 9.
- the air volume of the large rear side heat exchanger 10 may be insufficient.
- the heat exchanger 5 (the front surface side heat exchanger 9 and the back surface side heat exchanger 10) may not be able to exhibit desired heat exchange performance.
- the arrangement position of the fan 4 may be moved in the back direction.
- the air volume of the back side heat exchanger 10 may be insufficient, such as when the pressure loss of the back side heat exchanger 10 is large.
- the air volume adjustment by the configuration of the front side heat exchanger 9 and the back side heat exchanger 10 passed through the front side heat exchanger 9 and the back side heat exchanger 10.
- the air that has joined later cannot be adjusted to a desired angle.
- the air merged after passing through each of the front surface side heat exchanger 9 and the back surface side heat exchanger 10 may not bend more than a desired angle.
- the arrangement position of the fan 4 may be moved in the back direction.
- the heat transfer area of the front side heat exchanger 9 may be larger than the heat transfer area of the back side heat exchanger 10.
- FIG.8 (c) it is good to move the arrangement position of the fan 4 to a front direction.
- the heat exchanger 5 the front side heat exchanger 9 and the back side heat exchanger 9.
- the heat exchange performance of the vessel 10) is improved.
- the air volume of the front heat exchanger 9 may be larger than necessary.
- the air volume adjustment by the configuration of the front side heat exchanger 9 and the back side heat exchanger 10 passed through the front side heat exchanger 9 and the back side heat exchanger 10.
- the air which joined after passing each of the front side heat exchanger 9 and the back side heat exchanger 10 may bend more than a desired angle. In such a case, the arrangement position of the fan 4 may be moved in the front direction as shown in FIG.
- the heat exchanger 5 shown in FIG. 9 is configured in a substantially ⁇ shape by the front side heat exchanger 9 and the back side heat exchanger 10 formed separately, it is not limited to this configuration.
- the shape of the heat exchanger 5 in the right vertical section may be configured to be approximately V-shaped, approximately N-shaped, approximately W-shaped, approximately ⁇ -shaped, approximately M-shaped, or the like.
- each of the front side heat exchanger 9 and the back side heat exchanger 10 may be configured by a combination of a plurality of heat exchangers (see FIG. 12).
- the front side is the front side heat exchanger 9 and the rear side is the back side heat exchanger 10 with respect to the symmetry line 8. That is, the length in the longitudinal direction of the heat exchanger disposed on the back side of the symmetry line 8 may be longer than the length of the heat exchanger disposed on the front side of the symmetry line 8.
- the longitudinal lengths of the plurality of heat exchangers constituting the front-side heat exchanger 9 are each. Is the length of the front heat exchanger 9 in the longitudinal direction.
- the sum of the longitudinal lengths of the plurality of heat exchangers constituting the back side heat exchanger 10 is the longitudinal length of the back side heat exchanger 10.
- the heat exchanger 5 is composed of a plurality of heat exchangers (for example, when the heat exchanger 5 is composed of the front side heat exchanger 9 and the back side heat exchanger 10), the location where the arrangement gradient of the heat exchanger 5 changes ( For example, the heat exchangers do not have to be completely in contact with each other at a substantial connection point between the front-side heat exchanger 9 and the rear-side heat exchanger 10, and there may be some gaps.
- the shape of the heat exchanger 5 in the right vertical section may be partially or entirely curved (see FIG. 12).
- Embodiment 10 FIG. Further, in Embodiments 2 to 8 described above, fan 4 may be arranged as follows. In the tenth embodiment, the difference from the above-described second to ninth embodiments will be mainly described. The same parts as those in the second to ninth embodiments are denoted by the same reference numerals. ing. Moreover, the case where the indoor unit is a wall-mounted type attached to the wall surface of the air-conditioning target area is shown as an example.
- FIG. 10 is a longitudinal sectional view showing an example of an indoor unit of an air conditioner according to Embodiment 10 of the present invention (hereinafter, referred to as an indoor unit 50h). Based on FIG. 9, the arrangement
- the indoor unit 50h supplies conditioned air to an air-conditioning target area such as a room by using a refrigeration cycle in which a refrigerant is circulated.
- the heat exchanger 5 of the indoor unit 50h according to the tenth embodiment has the same arrangement as the indoor unit 50c of the fifth embodiment.
- the indoor unit 50g according to the ninth embodiment is different from the indoor unit 50c according to the fifth embodiment in the manner in which the fan 4 is arranged. That is, in the indoor unit 50h according to the tenth embodiment, the inclination of the fan 4 is determined according to the air volume and the heat transfer area of the front side heat exchanger 9 and the back side heat exchanger 10.
- the air volume of the back side heat exchanger 10 having a larger heat transfer area than the front side heat exchanger 9 may be insufficient.
- the fan 4 cannot be moved in the front-rear direction to adjust the air volume.
- the heat exchanger 5 (the front surface side heat exchanger 9 and the back surface side heat exchanger 10) may not be able to exhibit desired heat exchange performance.
- the fan 4 may be inclined toward the back side heat exchanger 10 in the right vertical section.
- the air volume of the back side heat exchanger 10 may be insufficient.
- the fan 4 may be moved in the front-rear direction and the air volume adjustment may not be performed.
- the air merged after passing through each of the front surface side heat exchanger 9 and the back surface side heat exchanger 10 may not bend more than a desired angle.
- the fan 4 may be inclined toward the back side heat exchanger 10 in the right vertical section.
- the heat exchanger 5 shown in FIG. 10 is configured in a substantially ⁇ shape by the front side heat exchanger 9 and the back side heat exchanger 10 formed separately, but is not limited to this configuration.
- the shape of the heat exchanger 5 in the right vertical section may be configured to be approximately V-shaped, approximately N-shaped, approximately W-shaped, approximately ⁇ -shaped, approximately M-shaped, or the like.
- each of the front side heat exchanger 9 and the back side heat exchanger 10 may be configured by a combination of a plurality of heat exchangers (see FIG. 12).
- the front side is the front side heat exchanger 9 and the rear side is the back side heat exchanger 10 with respect to the symmetry line 8. That is, the length in the longitudinal direction of the heat exchanger disposed on the back side of the symmetry line 8 may be longer than the length of the heat exchanger disposed on the front side of the symmetry line 8.
- the longitudinal lengths of the plurality of heat exchangers constituting the front-side heat exchanger 9 are each. Is the length of the front heat exchanger 9 in the longitudinal direction.
- the sum of the longitudinal lengths of the plurality of heat exchangers constituting the back side heat exchanger 10 is the longitudinal length of the back side heat exchanger 10.
- the heat exchanger 5 is composed of a plurality of heat exchangers (for example, when the heat exchanger 5 is composed of the front side heat exchanger 9 and the back side heat exchanger 10), the location where the arrangement gradient of the heat exchanger 5 changes ( For example, the heat exchangers do not have to be completely in contact with each other at a substantial connection point between the front-side heat exchanger 9 and the rear-side heat exchanger 10, and there may be some gaps.
- the shape of the heat exchanger 5 in the right vertical section may be partially or entirely curved (see FIG. 12).
- FIG. FIG. 11 is a schematic configuration diagram showing a main refrigerant circuit configuration of the air conditioner 100 according to Embodiment 11 of the present invention. Based on FIG. 11, the structure and operation
- the air conditioner 100 includes any one of the indoor unit 40 according to the first embodiment to the indoor unit 50h according to the tenth embodiment.
- the air conditioner 100 may be an apparatus that uses a refrigeration cycle, and can be applied to, for example, a room air conditioner installed in a house or a building.
- An indoor heat exchanger 64 described later is the heat exchanger 5 mounted on any of the indoor units 40 to 50h.
- the air conditioner 100 is configured by sequentially connecting a compressor 61, an outdoor heat exchanger 62, an expansion device 63, and an indoor heat exchanger 64 through a refrigerant pipe 65.
- the compressor 61 sucks the refrigerant flowing through the refrigerant pipe 65 and compresses the refrigerant to bring it into a high temperature / high pressure state.
- the outdoor heat exchanger 62 functions as a condenser (or a radiator) or an evaporator, and performs heat exchange between the refrigerant and the fluid (air, water, refrigerant, etc.) conducted through the refrigerant pipe 65, thereby exchanging the indoor heat.
- the cooler is supplied to the vessel 64.
- the expansion device 63 decompresses and expands the refrigerant that is conducted through the refrigerant pipe 65.
- the throttling device 63 may be composed of, for example, a capillary tube or a solenoid valve.
- the indoor heat exchanger 64 functions as a condenser (or a radiator) or an evaporator, and performs heat exchange between the refrigerant and the fluid that are conducted through the refrigerant pipe 65.
- the refrigerant that has been compressed by the compressor 61 and has become high temperature and high pressure flows into the indoor heat exchanger 64.
- the refrigerant exchanges heat with the fluid to condense, and becomes a low-temperature / high-pressure liquid refrigerant or a gas-liquid two-phase refrigerant.
- the indoor air is heated to become heating air.
- the air for heating is adjusted by the air direction control mechanism of the indoor unit 50 and the air direction deflection is adjusted, and is sent from the air outlet 3 to the air conditioning target area.
- the refrigerant flowing out of the indoor heat exchanger 64 is decompressed by the expansion device 63 and flows into the outdoor heat exchanger 62 as a low-temperature / low-pressure liquid refrigerant or a gas-liquid two-phase refrigerant.
- the refrigerant exchanges heat with the fluid and evaporates to become a high-temperature / low-pressure refrigerant gas, which is sucked into the compressor 61 again.
- the refrigerant that has been compressed by the compressor 61 and has become high temperature and high pressure flows into the outdoor heat exchanger 62.
- the refrigerant exchanges heat with the fluid and condenses to become a low-temperature / high-pressure liquid refrigerant or a gas-liquid two-phase refrigerant.
- the refrigerant flowing out of the outdoor heat exchanger 62 is decompressed by the expansion device 63 and flows into the indoor heat exchanger 64 as a low-temperature / low-pressure liquid refrigerant or a gas-liquid two-phase refrigerant.
- the refrigerant exchanges heat with the fluid and evaporates to become a high-temperature / low-pressure refrigerant gas.
- the room air is cooled to become air for cooling.
- the cooling air is sent out from the air outlet 3 to the air-conditioning target area after the air direction deflection is adjusted by the air direction control mechanism of the indoor unit 50. Then, the refrigerant that has flowed out of the indoor heat exchanger 64 is sucked into the compressor 61 again.
- the air conditioner 100 has the effect of the indoor unit depending on the installed indoor unit (any one of the indoor unit 40 to the indoor unit 50h). That is, since the indoor unit mounted on the air conditioner 100 can improve the heat exchange performance of the heat exchanger 5 as described above, the performance of the air conditioner 100 is improved accordingly. Moreover, since the indoor unit mounted in the air conditioner 100 can suppress generation
- Embodiment 12 FIG. The following configurations may be added to the air conditioners (more specifically, indoor units) according to the first to eleventh embodiments.
- the air conditioners more specifically, indoor units
- the same reference numerals are given to the same portions as those in the first to eleventh embodiments. is doing.
- FIG. 13 is a cross-sectional view when the front view of the air conditioner shown in FIG. 14 is cut along a cross section X, and is a view showing a configuration of the air conditioner according to the twelfth embodiment.
- the air conditioner 100 in FIG. 13 constitutes an indoor unit, and an air inlet 2 is opened at the upper part of the air conditioner 100 and an outlet 3 is opened at the lower end.
- the air conditioner 100 is formed with an air flow path that connects the suction port 2 and the blower port 3, and an axial flow fan having a vertical rotation axis is provided below the suction port 2 of the air flow channel.
- the fan 4 is provided, and a heat exchanger 5 for cooling or heating the air by exchanging heat is disposed below the fan 4.
- the air in the room is sucked into the air flow path in the air conditioner 100 from the suction port 2 by the operation of the fan 4, and the suction air is cooled or heated by the heat exchanger 5 at the lower part of the fan 4. It comes to blow out indoors.
- a noise detection microphone 71 is attached to the wall below the fan 4 as noise detection means for detecting the operation sound (noise) of the air conditioner 100 including the blowing sound of the fan 4.
- a control speaker 72 is arranged as a control sound output means for outputting a control sound for noise so as to face the center of the air flow path from the wall, and the noise detection microphone 71 and the control speaker 72 are arranged. Is attached between the fan 4 and the heat exchanger 5.
- the noise detection microphone 71 corresponds to the first sound detection device of the present invention
- the control speaker 72 corresponds to the control sound output device of the present invention.
- noise reduction effect detection microphone 73 is detected as noise reduction effect detection means for detecting noise from the outlet 3 on the wall at the lower end of the air conditioner and detecting the noise reduction effect, It is installed in a position that avoids wind currents.
- the muffling effect detection microphone 73 corresponds to the second sound detection apparatus of the present invention.
- the output signals of the noise detection microphone 71 and the silencing effect detection microphone 73 are input to a signal processing means 80 which is a control sound generation means for generating a signal (control sound) for controlling the control speaker 72.
- the signal processing means 80 corresponds to the control sound generator of the present invention.
- FIG. 15 shows a configuration diagram of the signal processing means 80.
- Electric signals input from the noise detection microphone 71 and the muffler effect detection microphone 73 are amplified by the microphone amplifier 81 and converted from an analog signal to a digital signal by the A / D converter 82.
- the converted digital signal is input to the FIR filter 88 and the LMS algorithm 89.
- the FIR filter 88 generates a control signal that has been corrected so that the noise detected by the noise detection microphone 71 has the same amplitude and opposite phase as the noise when the noise reduction effect detection microphone 73 is installed.
- After being converted from a digital signal to an analog signal by the D / A converter 84 it is amplified by the amplifier 85 and emitted from the control speaker 72 as a control sound.
- the wind flow sent by the fan 4 passes through the air flow path and is sent to the heat exchanger 5.
- the heat exchanger 5 is supplied with refrigerant from a pipe connected to an outdoor unit (not shown in FIG. 13), and air is cooled by the flow of air through the heat exchanger 5 to become cold air. Then, it is discharged into the room from the outlet 3 as it is.
- the air conditioner 100 is provided with a water receiver or the like for preventing water droplets from coming out of the air outlet 3 in the vicinity of the air outlet 3.
- region where the noise detection microphone 71 and the control speaker 72 which are the upstream of the heat exchanger 5 are arrange
- region used as cold air dew condensation does not arise.
- the operation sound (noise) including the blowing sound of the fan 4 in the air conditioner 100 is detected by the noise detection microphone 71 attached between the fan 4 and the heat exchanger 5, and the microphone amplifier 81 and the A / D converter. It becomes a digital signal via 82 and is input to the FIR filter 88 and the LMS algorithm 89.
- the tap coefficient of the FIR filter 88 is sequentially updated by the LMS algorithm 89.
- the coefficient is updated.
- h is a tap coefficient of the filter
- e is an error signal
- x is a filter input signal
- ⁇ is a step size parameter.
- the step size parameter ⁇ controls a filter coefficient update amount for each sampling.
- the digital signal that has passed through the FIR filter 88 whose tap coefficient has been updated by the LMS algorithm 89 is converted into an analog signal by the D / A converter 84, amplified by the amplifier 85, and the fan 4 and the heat exchanger 5.
- the digital signal that has passed through the FIR filter 88 whose tap coefficient has been updated by the LMS algorithm 89 is converted into an analog signal by the D / A converter 84, amplified by the amplifier 85, and the fan 4 and the heat exchanger 5.
- the muffler effect detection microphone 73 attached in the direction of the outer wall of the air outlet 3 so that the wind emitted from the air outlet 3 does not hit is passed through the air flow path from the fan 4.
- the noise detection microphone 71 and the control speaker 72 are arranged between the fan 4 and the heat exchanger 5, and the silencing effect detection microphone 73 is connected to the air outlet 3. Since it is not necessary to attach a member for active silencing to the region B where condensation occurs, it is possible to prevent water droplets from adhering to the control speaker 72, the noise detection microphone 71, and the silencing effect detection microphone 73. Therefore, it is possible to prevent deterioration of the silencing performance and failure of the speaker and the microphone.
- the muffling effect detection microphone 73 is installed at the lower end of the air conditioner 100 at a location where the wind discharged from the outlet 3 is not hit.
- the case where the fan 4 is an axial fan has been described as an example, but any fan that blows air by rotating an impeller like a line flow fan may be used.
- the microphone is exemplified as a means for detecting the silencing effect after the noise is canceled by the noise or the control sound, it may be constituted by an acceleration sensor or the like that detects the vibration of the casing.
- sound may be regarded as air flow disturbance, and the noise reduction effect after the noise is canceled by noise or control sound may be detected as air flow disturbance. That is, a flow rate sensor, a hot wire probe, or the like that detects an air flow may be used as a means for detecting a silencing effect after noise is canceled by noise or control sound. It is also possible to detect the air flow by increasing the gain of the microphone.
- the FIR filter 88 and the LMS algorithm 89 are used in the signal processing means 80.
- any adaptive signal processing circuit that brings the sound detected by the mute effect detection microphone 73 close to zero can be used.
- a filtered-X algorithm generally used in the mute method may be used.
- the signal processing means 80 may be configured to generate the control sound by a fixed tap coefficient instead of the adaptive signal processing.
- the signal processing means 80 may be an analog signal processing circuit instead of digital signal processing.
- the present invention is applicable even when the heat exchanger 5 that does not cause condensation is disposed. Therefore, it is possible to prevent the performance deterioration of the noise detection microphone 71, the control speaker 72, the silencing effect detection microphone 73, and the like without considering the presence or absence of condensation due to the heat exchanger 5.
- the fan 4, the heat exchanger 5 installed downstream of the fan 4, and installed between the fan 4 and the heat exchanger 5, are noisy.
- a noise detection microphone 71 that is a noise detection means for detecting noise
- a control speaker 72 that is installed between the fan 4 and the heat exchanger 5 and outputs a control sound that silences the noise
- the signal processing means 80 which is a control sound generation means for generating a control sound, from the detection results of the noise reduction effect detection microphone 9, which is a noise reduction effect detection means for detecting the noise reduction effect, and the noise detection microphone 71 and the noise reduction effect detection microphone 73.
- the silencing effect detection microphone 73 as the silencing effect detection means is installed between the fan 4 and the heat exchanger 5 so that the silencing It is possible to prevent water droplets from being attached to the effect detection microphone 73 due to dew condensation, and to prevent deterioration of the silencing performance and failure of the microphone, speaker, and the like. Further, considering that noise is transmitted along the air flow, more effective silencing is possible.
- the silencing effect detection microphone 73 as the silencing effect detection means is installed downstream of the heat exchanger 5 and at a position avoiding the wind flow.
- FIG. 17 is a cross-sectional view when the front view of the air conditioner 100 shown in FIG. 14 is cut by a cross section X, and is a view showing the configuration of the air conditioner in the thirteenth embodiment.
- the noise and silencing effect detection microphone 86 corresponds to the sound detection device of the present invention.
- the air conditioner 100 constitutes an indoor unit, and an air inlet 2 is opened at the upper part of the air conditioner 100, and an air outlet 3 is opened at the lower end.
- the air conditioner 100 is formed with an air flow path that connects the suction port 2 and the blower port 3, and an axial flow fan having a vertical rotation axis is provided below the suction port 2 of the air flow channel.
- the fan 4 is provided, and a heat exchanger 5 for cooling or heating the air by exchanging heat is disposed below the fan 4.
- the air in the room is sucked into the air flow path in the air conditioner 100 from the suction port 2 by the operation of the fan 4, and the suction air is cooled or heated by the heat exchanger 5 at the lower part of the fan 4. It comes to blow out indoors.
- the air conditioner 100 described in the twelfth embodiment includes two microphones, a noise detection microphone 71 and a silencing effect detection microphone 73 for active silencing.
- the noise and the silencing effect detecting microphone 86 are replaced with one microphone.
- the signal processing method is different, the contents of the signal processing means 87 are different.
- a control speaker 72 that outputs a control sound for noise is disposed on the lower wall portion of the fan 4 so as to face the center of the air flow path from the wall, and further, the air flow path from the fan 4 to the lower side thereof.
- a noise and muffling effect detection microphone 86 for detecting the sound that has propagated through and is caused to interfere with the control sound emitted from the control speaker 72 to the noise that comes out of the outlet 3 is disposed.
- the control speaker 72 and the noise and silencing effect detection microphone 86 are attached between the fan 4 and the heat exchanger 5.
- the output signal of the noise and silencing effect detection microphone 86 is input to a signal processing means 87 which is a control sound generation means for generating a signal (control sound) for controlling the control speaker 72.
- FIG. 18 shows a configuration diagram of the signal processing means 87.
- the electric signal converted from the sound signal by the noise and muffler effect detection microphone 86 is amplified by the microphone amplifier 81 and converted from an analog signal to a digital signal by the A / D converter 82.
- the converted digital signal is input to the LMS algorithm 89, and the difference signal from the signal obtained by convolving the FIR filter 90 with the output signal of the FIR filter 88 is input to the FIR filter 88 and the LMS algorithm 89.
- the difference signal is subjected to a convolution operation by the tap coefficient calculated by the LMS algorithm 89 by the FIR filter 88, converted from a digital signal to an analog signal by the D / A converter 84, and amplified by the amplifier 85.
- the sound is emitted from the control speaker 72 as a control sound.
- the wind flow sent by the fan 4 passes through the air flow path and is sent to the heat exchanger 5.
- the heat exchanger 5 is supplied with refrigerant from a pipe connected to an outdoor unit (not shown in FIG. 17), and the air is cooled by the flow of air through the heat exchanger 5 to become cold air. Then, it is discharged into the room from the outlet 3 as it is.
- the air conditioner 100 is provided with a water receiver or the like for preventing water droplets from coming out of the air outlet 3 in the vicinity of the air outlet 3.
- region where the noise and the silencing effect detection microphone 86 and the control speaker 72 which are upstream of the heat exchanger 5 are located upstream of the area
- the detected noise and silencing effect detection microphone 86 detects the noise and converts it into a digital signal via the microphone amplifier 81 and the A / D converter 82.
- noise to be silenced is input to the FIR filter 88, and the LMS algorithm 89 is input as shown in Equation 1. It is necessary to input a sound after causing the noise to be silenced as a signal to interfere with the control sound as an error signal. However, since the noise and the silencing effect detection microphone 86 can detect only the sound after the control sound interferes, it is necessary to create the noise to be silenced from the noise and the sound detected by the silencing effect detection microphone 86.
- FIG. 20 shows a path in which a control signal output from the FIR filter 88 is output as a control sound and output from the control speaker 72, and then detected by the noise and muffler effect detection microphone 86 and input to the signal processing means 87.
- the FIR filter 90 in FIG. 18 estimates this transfer characteristic H.
- the control sound can be estimated as the signal b detected by the noise and silencing effect detection microphone 86, and after the interference detected by the noise and silencing effect detection microphone 86
- the noise c to be silenced is generated by taking the difference from the sound a.
- the noise c to be silenced generated in this way is supplied as an input signal to the LMS algorithm 89 and the FIR filter 88.
- the digital signal that has passed through the FIR filter 88 whose tap coefficient has been updated by the LMS algorithm 89 is converted to an analog signal by the D / A converter 84, amplified by the amplifier 85, and between the fan 4 and the heat exchanger 5.
- a control sound is emitted from the attached control speaker 72 to the air flow path in the air conditioner 100.
- the noise and silencing effect detection microphone 86 attached to the lower side of the control speaker 72 propagates through the air flow path from the fan 4 and is emitted from the control speaker 72 to the noise coming out from the outlet 3.
- the sound after the control sound is interfered is detected.
- the error signal of the LMS algorithm 89 described above is input with the sound detected by the noise and muffler effect detection microphone 86, so the tap coefficient of the FIR filter 88 is updated so that the sound after the interference approaches zero. Will be.
- noise in the vicinity of the air outlet 3 can be suppressed by the control sound that has passed through the FIR filter 88.
- the noise and silencing effect detection microphone 86 and the control speaker 72 are disposed between the fan 4 and the heat exchanger 5, thereby causing a region B where condensation occurs. Since it is not necessary to attach a member that requires active silencing, it is possible to prevent water droplets from adhering to the control speaker 72, the noise and the silencing effect detection microphone 86, and to prevent degradation of the silencing performance and failure of the speaker and microphone.
- the noise and silencing effect detection microphone 86 is arranged on the upstream side of the heat exchanger 5, but when the wind discharged from the outlet 3 hits the lower end of the air conditioner 100 as shown in FIG. It may be installed in a place where there is no air flow (position avoiding wind flow).
- the case where the fan 4 is an axial fan has been described as an example, but any fan that blows air by rotating an impeller like a line flow fan may be used.
- the microphone is exemplified as a means for detecting the silencing effect after the noise is canceled by the noise or the control sound, it may be constituted by an acceleration sensor or the like that detects the vibration of the casing.
- sound may be regarded as air flow disturbance, and the noise reduction effect after the noise is canceled by noise or control sound may be detected as air flow disturbance. That is, a flow rate sensor, a hot wire probe, or the like that detects an air flow may be used as a means for detecting a silencing effect after noise is canceled by noise or control sound. It is also possible to detect the air flow by increasing the gain of the microphone.
- the FIR filter 88 and the LMS algorithm 89 are used as the adaptive signal processing circuit in the thirteenth embodiment in the signal processing means 87, the adaptive signal processing circuit that brings the noise detected by the noise and muffler effect detection microphone 86 close to zero. I just need it.
- the signal processing means 87 may be configured to generate the control sound by a fixed tap coefficient instead of the adaptive signal processing.
- the signal processing means 87 may be an analog signal processing circuit instead of digital signal processing.
- the present invention is applicable even when the heat exchanger 5 that does not cause condensation is disposed. Therefore, there is an effect that it is possible to prevent the performance deterioration of the noise and silencing effect detection microphone 16, the control speaker 72, and the like without considering the presence or absence of the occurrence of condensation by the heat exchanger 5.
- the fan 4, the heat exchanger 5 installed downstream of the fan 4, and installed between the fan 4 and the heat exchanger 5, are noisy.
- the noise and muffler effect detection microphone 16 which is a noise and muffler effect detection means for detecting the noise and the muffler effect of the control sound that mutes the noise.
- the noise and silencing effect detection microphone 16 as the noise and silencing effect detection means is located downstream of the heat exchanger 5 and at a position avoiding the wind flow.
- the noise and silencing effect detection microphone 16 is located downstream of the heat exchanger 5 and at a position avoiding the wind flow.
- FIG. 13 to 21 show the structure of the heat exchanger 5 shown in FIG. 1 as the structure of the heat exchanger 5, but naturally the structure of the heat exchanger 5 shown in FIGS.
- the structure of the heat exchanger 5 as shown in each of FIGS. 2 to 8 may be adopted.
- FIG. 22 is a diagram illustrating a case where the structure of the heat exchanger 5 shown in FIG. 5 is adopted as the structure of the heat exchanger 5 shown in FIG. 13, and
- FIG. 23 is a diagram showing the heat exchanger shown in FIG. 6 is a diagram illustrating a case where the structure of the heat exchanger 5 shown in FIG.
- Air volume distribution may be performed according to the heat transfer area.
Abstract
Description
実施の形態1.
図1は、本発明の実施の形態1に係る空気調和機の室内機の一例(以下、室内機40と称する)を示す縦断面図である。この図1は、図の左側を室内機40の前面側として示している。図1に基づいて、室内機40の構成、特に熱交換器の配置の仕方について説明する。この室内機40は、冷媒を循環させる冷凍サイクルを利用することで室内等の空調対象域に空調空気を供給するものである。なお、図1を含め、以下の図10(実施の形態10)までは、図の左側を室内機の前面側として示している。また、以下の図面では各構成部材の大きさの関係が実際のものとは異なる場合がある。また、室内機40が空調対象域の壁面に取り付けられる壁掛け型である場合を例に示している。
まず、室内空気は、ファン4によってケーシング1の上部に形成されている吸込口2から室内機40内に流れ込む。このとき、フィルター7によって空気に含まれている塵埃が除去される。この室内空気は、熱交換器5を通過する際に熱交換器5内を導通している冷媒によって加熱又は冷却されて空調空気となる。そして、空調空気は、ケーシング1の下部に形成されている吹出口3から室内機40の外部、つまり空調対象域に吹き出されるようになっている。
熱交換器5を以下のように構成することにより、さらに騒音を抑制することが可能となる。なお、本実施の形態2では上述した実施の形態1との相違点を中心に説明するものとし、実施の形態1と同一部分には、同一符号を付している。また、室内機が空調対象域の壁面に取り付けられる壁掛け型である場合を例に示している。
また、本実施の形態2に係る室内機50によれば、前面側熱交換器9及び背面側熱交換器10のそれぞれには、風路面積に応じた量の空気が通過する。つまり、背面側熱交換器10の風量は前面側熱交換器9の風量よりも大きくなる。そして、この風量差により、前面側熱交換器9及び背面側熱交換器10のそれぞれを通過した空気が合流した際、この合流した空気は前面側(吹出口3側)へ曲がることとなる。このため、吹出口3近傍で気流を急激に曲げる必要が無くなり、吹出口3近傍での圧力損失を低減することができる。したがって、本実施の形態2に係る室内機50は、実施の形態1に係る室内機40と比べ、騒音をさらに抑制することが可能となる。また、室内機50は、吹出口3近傍での圧力損失を低減することができるので、消費電力を低減させることも可能となる。
また、熱交換器5を複数の熱交換器で構成する場合(例えば前面側熱交換器9と背面側熱交換器10で構成する場合)、熱交換器5の配置勾配が変局する箇所(例えば前面側熱交換器9と背面側熱交換器10との実質的な接続箇所)で各熱交換器が完全に接触している必要はなく、多少の隙間があってもよい。
また、右側縦断面における熱交換器5の形状は、一部又は全部が曲線形状となっていてもよい(図12参照)。
図12(a)に示すように、熱交換器5を複数の熱交換器で構成してもよい。図12(b)に示すように、熱交換器5を一体型の熱交換器で構成してもよい。12(c)に示すように、熱交換器5を構成する熱交換器を、さらに複数の熱交換器で構成してもよい。また、図12(c)に示すように、熱交換器5を構成する熱交換器の一部を、垂直に配置してもよい。図12(d)に示すように、熱交換器5の形状を曲線形状としてもよい。
熱交換器5は、以下のように構成されてもよい。なお、本実施の形態3では上述した実施の形態2との相違点を中心に説明するものとし、実施の形態2と同一部分には、同一符号を付している。また、室内機が空調対象域の壁面に取り付けられる壁掛け型である場合を例に示している。
熱交換器5は、3つの熱交換器で構成されており、これら各熱交換器は、ファン4から供給される空気の流れ方向に対して異なる傾斜を有して配置されている。そして、熱交換器5は、右側縦断面において略N型となっている。ここで、対称線8よりも前面側に配置された熱交換器9a及び熱交換器9bが前面側熱交換器9を構成し、対称線8よりも背面側に配置された熱交換器10a及び熱交換器10bが背面側熱交換器10を構成する。つまり、本実施の形態3では、熱交換器9b及び熱交換器10bが一体型の熱交換器で構成されている。なお、対称線8は、右側縦断面における熱交換器5の設置範囲を、略中央部において左右方向に分断するものである。
また、熱交換器5を複数の熱交換器で構成する場合、熱交換器5の配置勾配が変局する箇所において各熱交換器が完全に接触している必要はなく、多少の隙間があってもよい。
また、右側縦断面における熱交換器5の形状は、一部又は全部が曲線形状となっていてもよい(図12参照)。
また、熱交換器5は以下のように構成されてもよい。なお、本実施の形態4では上述した実施の形態2及び実施の形態3との相違点を中心に説明するものとし、実施の形態2及び実施の形態3と同一部分には、同一符号を付している。また、室内機が空調対象域の壁面に取り付けられる壁掛け型である場合を例に示している。
熱交換器5は、4つの熱交換器で構成されており、これら各熱交換器は、ファン4から供給される空気の流れ方向に対して異なる傾斜を有して配置されている。そして、熱交換器5は、右側縦断面において略W型となっている。ここで、対称線8よりも前面側に配置された熱交換器9a及び熱交換器9bが前面側熱交換器9を構成し、対称線8よりも背面側に配置された熱交換器10a及び熱交換器10bが背面側熱交換器10を構成する。なお、対称線8は、右側縦断面における熱交換器5の設置範囲を、略中央部において左右方向に分断するものである。
また、熱交換器5を複数の熱交換器で構成する場合、熱交換器5の配置勾配が変局する箇所において各熱交換器が完全に接触している必要はなく、多少の隙間があってもよい。
また、右側縦断面における熱交換器5の形状は、一部又は全部が曲線形状となっていてもよい(図12参照)。
また、熱交換器5は以下のように構成されてもよい。なお、本実施の形態5では上述した実施の形態2~実施の形態4との相違点を中心に説明するものとし、実施の形態2~実施の形態4と同一部分には、同一符号を付している。また、室内機が空調対象域の壁面に取り付けられる壁掛け型である場合を例に示している。
より詳しくは、本実施の形態5の室内機50cは、実施の形態2と同様に、2つの熱交換器(前面側熱交換器9及び背面側熱交換器10)で構成されている。しかしながら、前面側熱交換器9及び背面側熱交換器10の配置の仕方が実施の形態2に示す室内機50と相違している。
なお、対称線8は、右側縦断面における熱交換器5の設置範囲を、略中央部において左右方向に分断するものである。
まず、室内空気は、ファン4によってケーシング1の上部に形成されている吸込口2から室内機50c内に流れ込む。このとき、フィルター7によって空気に含まれている塵埃が除去される。この室内空気は、熱交換器5(前面側熱交換器9及び背面側熱交換器10)を通過する際、熱交換器5内を導通している冷媒によって加熱又は冷却されて空調空気となる。このとき、前面側熱交換器9を通過する空気は、室内機50cの前面側から背面側に流れる。また、背面側熱交換器10を通過する空気は、室内機50cの背面側から前面側に流れる。
熱交換器5(前面側熱交換器9及び背面側熱交換器10)を通過した空調空気は、ケーシング1の下部に形成されている吹出口3から室内機50cの外部、つまり空調対象域に吹き出される。
また、熱交換器5を複数の熱交換器で構成する場合、熱交換器5の配置勾配が変局する箇所において各熱交換器が完全に接触している必要はなく、多少の隙間があってもよい。
また、右側縦断面における熱交換器5の形状は、一部又は全部が曲線形状となっていてもよい(図12参照)。
また、熱交換器5は以下のように構成されてもよい。なお本実施の形態6では上述した実施の形態2~実施の形態5との相違点を中心に説明するものとし、実施の形態2~実施の形態5と同一部分には、同一符号を付している。また、室内機が空調対象域の壁面に取り付けられる壁掛け型である場合を例に示している。
より詳しくは、本実施の形態6の室内機50dは、実施の形態3と同様に、3つの熱交換器で構成されている。しかしながら、これら3つの熱交換器の配置の仕方が実施の形態3に示す室内機50aと相違している。
また、熱交換器5を複数の熱交換器で構成する場合、熱交換器5の配置勾配が変局する箇所において各熱交換器が完全に接触している必要はなく、多少の隙間があってもよい。
また、右側縦断面における熱交換器5の形状は、一部又は全部が曲線形状となっていてもよい(図12参照)。
また、熱交換器5は以下のように構成されてもよい。なお本実施の形態7では上述した実施の形態2~実施の形態6との相違点を中心に説明するものとし、実施の形態2~実施の形態6と同一部分には、同一符号を付している。また、室内機が空調対象域の壁面に取り付けられる壁掛け型である場合を例に示している。
より詳しくは、本実施の形態7の室内機50eは、実施の形態4と同様に、4つの熱交換器で構成されている。しかしながら、これら4つの熱交換器の配置の仕方が実施の形態4に示す室内機50bと相違している。
また、熱交換器5を複数の熱交換器で構成する場合、熱交換器5の配置勾配が変局する箇所において各熱交換器が完全に接触している必要はなく、多少の隙間があってもよい。
また、右側縦断面における熱交換器5の形状は、一部又は全部が曲線形状となっていてもよい(図12参照)。
また、熱交換器5は以下のように構成されてもよい。なお本実施の形態8では上述した実施の形態2~実施の形態7との相違点を中心に説明するものとし、実施の形態2~実施の形態7と同一部分には、同一符号を付している。また、室内機が空調対象域の壁面に取り付けられる壁掛け型である場合を例に示している。
より詳しくは、本実施の形態8の室内機50fは、実施の形態5と同様に、2つの熱交換器(前面側熱交換器9及び背面側熱交換器10)で構成され、右側縦断面において略Λ型となっている。しかしながら、本実施の形態8では、前面側熱交換器9の圧力損失と及び背面側熱交換器10の圧力損失とを異ならせることにより、前面側熱交換器9の風量と及び背面側熱交換器10の風量とを異ならせている。
なお、対称線8は、右側縦断面における熱交換器5の設置範囲を、略中央部において左右方向に分断するものである。
また、本実施の形態8に係る室内機50fによれば、前面側熱交換器9及び背面側熱交換器10のそれぞれには、圧力損失に応じた量の空気が通過する。つまり、背面側熱交換器10の風量は前面側熱交換器9の風量よりも大きくなる。そして、この風量差により、前面側熱交換器9及び背面側熱交換器10のそれぞれを通過した空気が合流した際、この合流した空気は前面側(吹出口3側)へ曲がることとなる。このため、吹出口3近傍で気流を急激に曲げる必要が無くなり、吹出口3近傍での圧力損失を低減することができる。したがって、本実施の形態8に係る室内機50fは、右側縦断面における背面側熱交換器10の長さを長くすることなく、実施の形態1に係る室内機40よりもさらに騒音を抑制することが可能となる。また、室内機50fは、吹出口3近傍での圧力損失を低減することができるので、消費電力を低減させることも可能となる。
また、熱交換器5を複数の熱交換器で構成する場合(例えば前面側熱交換器9と背面側熱交換器10で構成する場合)、熱交換器5の配置勾配が変局する箇所(例えば前面側熱交換器9と背面側熱交換器10との実質的な接続箇所)で各熱交換器が完全に接触している必要はなく、多少の隙間があってもよい。
また、右側縦断面における熱交換器5の形状は、一部又は全部が曲線形状となっていてもよい(図12参照)。
また、上述した実施の形態2~実施の形態8において、ファン4を以下のように配置してもよい。なお本実施の形態9では上述した実施の形態2~実施の形態8との相違点を中心に説明するものとし、実施の形態2~実施の形態8と同一部分には、同一符号を付している。また、室内機が空調対象域の壁面に取り付けられる壁掛け型である場合を例に示している。
すなわち、本実施の形態9に係る室内機50gは、前面側熱交換器9及び背面側熱交換器10の風量や伝熱面積に応じて、ファン4の配置位置が決定されている。
このように構成することにより、前面側熱交換器9及び背面側熱交換器10の伝熱面積に応じた風量分配が可能となり、熱交換器5(前面側熱交換器9及び背面側熱交換器10)の熱交換性能が向上する。
このように構成することにより、前面側熱交換器9及び背面側熱交換器10の伝熱面積に応じた風量分配が可能となり、熱交換器5(前面側熱交換器9及び背面側熱交換器10)の熱交換性能が向上する。
また、熱交換器5を複数の熱交換器で構成する場合(例えば前面側熱交換器9と背面側熱交換器10で構成する場合)、熱交換器5の配置勾配が変局する箇所(例えば前面側熱交換器9と背面側熱交換器10との実質的な接続箇所)で各熱交換器が完全に接触している必要はなく、多少の隙間があってもよい。
また、右側縦断面における熱交換器5の形状は、一部又は全部が曲線形状となっていてもよい(図12参照)。
また、上述した実施の形態2~実施の形態8において、ファン4を以下のように配置してもよい。なお本実施の形態10では上述した実施の形態2~実施の形態9との相違点を中心に説明するものとし、実施の形態2~実施の形態9と同一部分には、同一符号を付している。また、室内機が空調対象域の壁面に取り付けられる壁掛け型である場合を例に示している。
すなわち、本実施の形態10に係る室内機50hは、前面側熱交換器9及び背面側熱交換器10の風量や伝熱面積に応じて、ファン4の傾斜が決定されている。
このように構成することにより、ファン4を前後方向に移動させられない場合でも、前面側熱交換器9及び背面側熱交換器10の伝熱面積に応じた風量分配が可能となり、熱交換器5(前面側熱交換器9及び背面側熱交換器10)の熱交換性能が向上する。
また、熱交換器5を複数の熱交換器で構成する場合(例えば前面側熱交換器9と背面側熱交換器10で構成する場合)、熱交換器5の配置勾配が変局する箇所(例えば前面側熱交換器9と背面側熱交換器10との実質的な接続箇所)で各熱交換器が完全に接触している必要はなく、多少の隙間があってもよい。
また、右側縦断面における熱交換器5の形状は、一部又は全部が曲線形状となっていてもよい(図12参照)。
図11は、本発明の実施の形態11に係る空気調和機100の主な冷媒回路構成を示す概略構成図である。図11に基づいて、空気調和機100の構成及び動作について説明する。この空気調和機100は、実施の形態1の室内機40~実施の形態10の室内機50hのいずれかを備えているものである。この空気調和機100は、冷凍サイクルを使用した装置であればよく、例えば家屋やビル等に設置されるルームエアコン等に適用することが可能なものである。なお、後述の室内熱交換器64が室内機40~室内機50hのいずれかに搭載されている熱交換器5である。
[暖房運転]
圧縮機61で圧縮されて高温・高圧となった冷媒は、室内熱交換器64に流入する。この室内熱交換器64では、冷媒が流体と熱交換して凝縮し、低温・高圧の液冷媒又は気液二相冷媒となる。このとき、室内空気は、加熱されて暖房用空気となる。この暖房用空気は、室内機50の風向制御機構で風向偏向が調整されて吹出口3から空調対象域に送出される。室内熱交換器64から流出した冷媒は、絞り装置63で減圧され、低温・低圧の液冷媒又は気液二相冷媒となって室外熱交換器62に流入する。室外熱交換器62では、冷媒が流体と熱交換して蒸発し、高温・低圧の冷媒ガスとなり、圧縮機61に再度吸入される。
圧縮機61で圧縮されて高温・高圧となった冷媒は、室外熱交換器62に流入する。この室外熱交換器62では、冷媒が流体と熱交換して凝縮し、低温・高圧の液冷媒又は気液二相冷媒となる。室外熱交換器62から流出した冷媒は、絞り装置63で減圧され、低温・低圧の液冷媒又は気液二相冷媒となって室内熱交換器64に流入する。室内熱交換器64では、冷媒が流体と熱交換して蒸発し、高温・低圧の冷媒ガスとなる。このとき、室内空気は、冷却されて冷房用空気となる。この冷房用空気は、室内機50の風向制御機構で風向偏向が調整されて吹出口3から空調対象域に送出される。そして、室内熱交換器64から流出した冷媒は、圧縮機61に再度吸入される。
実施の形態1~実施の形態11の空気調和機(より詳しくは室内機)に以下のような構成を付加してもよい。なお、本実施の形態12では上述した実施の形態1~実施の形態11との相違点を中心に説明するものとし、実施の形態1~実施の形態11と同一部分には、同一符号を付している。
図13は、図14に示した空気調和機の前面図を断面Xで切った時の断面図であり、本実施の形態12における空気調和機の構成を示した図である。
次に空気調和機100の動作について説明する。空気調和機100が動作すると、ファン4の羽根車が回転し、ファン4上側から室内の空気が吸い込まれ、ファン4下側へと空気が送られることにより風流が発生する。
本発明にかかる実施の形態12によれば、空気調和機において、ファン4と、ファン4の下流に設置される熱交換器5と、ファン4と熱交換器5との間に設置され、騒音を検出する騒音検出手段である騒音検出マイクロホン71と、ファン4と熱交換器5との間に設置され、騒音を消音する制御音を出力する制御音出力手段である制御スピーカ72と、制御音の消音効果を検出する消音効果検出手段である消音効果検出マイクロホン9と、騒音検出マイクロホン71と消音効果検出マイクロホン73とにおける検出結果から、制御音を生成する制御音生成手段である信号処理手段80とを備えることで、騒音検出マイクロホン71、制御スピーカ72等への結露による水滴の付着を防止し、消音性能の劣化やマイクロホン、スピーカ等の故障を防ぐことが可能となる。また、騒音が空気の流れに沿って伝わることを考慮すると、より効果的な消音が可能となる。
<B-1.構成>
本実施の形態13では、実施の形態12における騒音検出マイクロホン71と消音効果検出マイクロホン73とを集約した騒音及び消音効果検出手段として騒音及び消音効果検出マイクロホン86を配置した空気調和機について説明する。図17は、図14に示した空気調和機100の前面図を断面Xで切った時の断面図であり、本実施の形態13における空気調和機の構成を示す図である。
次に空気調和機100の動作について説明する。空気調和機100が動作すると、ファン4の羽根車が回転し、ファン4上側から室内の空気が吸い込まれ、ファン4下側へと空気が送られることにより風流が発生する。
本発明にかかる実施の形態13によれば、空気調和機において、ファン4と、ファン4の下流に設置される熱交換器5と、ファン4と熱交換器5との間に設置され、騒音の検出と、騒音を消音する制御音の消音効果の検出とを行う騒音及び消音効果検出手段である騒音及び消音効果検出マイクロホン16と、ファン4と熱交換器5との間に設置され、制御音を出力する制御音出力手段である制御スピーカ72と、騒音及び消音効果検出マイクロホン16における検出結果から、制御音を生成する制御音生成手段である信号処理手段87とを備えることで、騒音及び消音効果検出マイクロホン16、制御スピーカ72等への結露による水滴の付着を防止し、消音性能の劣化やマイクロホン、スピーカ等の故障を防ぐことが可能となる。また、マイクロホンの数が減少し、より安価にシステムを構成することができる。
Claims (16)
- 上部に吸込口が形成され、前面部下側に吹出口が形成されたケーシングと、
前記ケーシング内の前記吸込口の下流側に設けられた軸流型又は斜流型の送風機と、
前記ケーシング内の前記送風機の下流側であって、前記吹出口の上流側に設けられ、前記送風機から吹き出された空気と冷媒とが熱交換する熱交換器と、
を備えた空気調和機の室内機。 - 前記熱交換器は、
前面側に配置された前面側熱交換器と、
背面側に配置された背面側熱交換器と、
を有し、
前記前面側熱交換器を流れる空気の流量は、前記背面側熱交換器を流れる空気の流量よりも小さくなるよう構成されていることを特徴とする請求項1に記載の空気調和機の室内機。 - 前記前面側熱交換器の風路面積は、前記背面側熱交換器の風路面積よりも小さいことを特徴とする請求項2に記載の空気調和機の室内機。
- 側面視において、
前記前面側熱交換器の長手方向の長さは、前記背面側熱交換器の長手方向の長さよりも短いことを特徴とする請求項3に記載の空気調和機の室内機。 - 前記前面側熱交換器の圧力損失は、前記背面側熱交換器の圧力損失よりも大きいことを特徴とする請求項2~請求項4のいずれか一項に記載の空気調和機の室内機。
- 前記前面側熱交換器は、空気が前面側から背面側に流れるように配置され、
前記背面側熱交換器は、空気が背面側から前面側に流れるように配置されたことを特徴とする請求項2~請求項5のいずれか一項に記載の空気調和機の室内機。 - 前記送風機は、
前記前面側熱交換器の伝熱面積及び前記背面側熱交換器群の伝熱面積に応じた風量を、前記前面側熱交換器群及び前記背面側熱交換器に供給するように配置されたことを特徴とする請求項1~請求項6のいずれか一項に記載の空気調和機の室内機。 - 前記送風機の回転軸は、
前記前面側熱交換器群及び前記背面側熱交換器のうち、伝熱面積の大きい方の上方に配置されたことを特徴とする請求項7に記載の空気調和機の室内機。 - 前記送風機の回転軸は、
前面側熱交換器群及び背面側熱交換器群のうち、伝熱面積の大きい方へ向かうように配置されたことを特徴とする請求項7に記載の空気調和機の室内機。 - 前記送風機と前記熱交換器との間に設置され、当該位置の音を検出する第1の音検出装置と、
前記送風機と前記熱交換器との間に設置され、制御音を出力する制御音出力装置と、
前記送風機の下流側に設置され、当該位置の音を検出する第2の音検出装置と、
前記第1の音検出装置の検出結果及び前記第2の音検出装置の検出結果から、前記制御音を生成する制御音生成装置と、
を備えたことを特徴とする請求項1~請求項9のいずれか一項に記載の空気調和機の室内機。 - 前記第2の音検出装置は、前記送風機と前記熱交換器との間に配置されたことを特徴とする請求項10に記載の空気調和機の室内機。
- 前記第2の音検出装置は、前記熱交換器の下流側に配置されたことを特徴とする請求項10に記載の空気調和機の室内機。
- 前記送風機と前記熱交換器との間に設置され、制御音を出力する制御音出力装置と、
前記送風機の下流側に設置され、当該位置の音を検出する音検出装置と、
前記音検出装置の検出結果から前記制御音を生成する制御音生成装置と、
を備えたことを特徴とする請求項1~請求項9のいずれか一項に記載の空気調和機の室内機。 - 前記音検出装置は、前記送風機と前記熱交換器との間に設置されたことを特徴とする請求項13に記載の空気調和機の室内機。
- 前記音検出装置は、前記熱交換器の下流側に設置されたことを特徴とする請求項13に記載の空気調和機の室内機。
- 請求項1~請求項15のいずれか一項に記載の室内機を備えたことを特徴とする空気調和機。
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Cited By (23)
Publication number | Priority date | Publication date | Assignee | Title |
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Also Published As
Publication number | Publication date |
---|---|
CN102308153A (zh) | 2012-01-04 |
AU2009339555A1 (en) | 2011-08-04 |
RU2013124171A (ru) | 2014-12-10 |
CN102308153B (zh) | 2015-03-04 |
JPWO2010089920A1 (ja) | 2012-08-09 |
US9982898B2 (en) | 2018-05-29 |
EP2395290B1 (en) | 2020-03-18 |
JP5425106B2 (ja) | 2014-02-26 |
EP2395290A1 (en) | 2011-12-14 |
US20120018117A1 (en) | 2012-01-26 |
RU2493497C2 (ru) | 2013-09-20 |
RU2011136705A (ru) | 2013-03-10 |
ES2784491T3 (es) | 2020-09-28 |
EP2395290A4 (en) | 2015-08-05 |
JP2013137192A (ja) | 2013-07-11 |
RU2542553C2 (ru) | 2015-02-20 |
AU2009339555B2 (en) | 2013-01-10 |
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