WO2016038690A1 - Unité intérieure de dispositif de climatisation et dispositif de climatisation - Google Patents

Unité intérieure de dispositif de climatisation et dispositif de climatisation Download PDF

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Publication number
WO2016038690A1
WO2016038690A1 PCT/JP2014/073833 JP2014073833W WO2016038690A1 WO 2016038690 A1 WO2016038690 A1 WO 2016038690A1 JP 2014073833 W JP2014073833 W JP 2014073833W WO 2016038690 A1 WO2016038690 A1 WO 2016038690A1
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WO
WIPO (PCT)
Prior art keywords
indoor unit
air conditioner
centrifugal fan
main plate
shroud
Prior art date
Application number
PCT/JP2014/073833
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English (en)
Japanese (ja)
Inventor
誠治 中島
池田　尚史
敬英 田所
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to EP14901479.7A priority Critical patent/EP3196560B1/fr
Priority to JP2016547295A priority patent/JP6429887B2/ja
Priority to PCT/JP2014/073833 priority patent/WO2016038690A1/fr
Publication of WO2016038690A1 publication Critical patent/WO2016038690A1/fr

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Classifications

    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers

Definitions

  • the present invention relates to an indoor unit for an air conditioner equipped with, for example, a centrifugal fan.
  • the technology that controls the flow of the fan blowout part so far includes the following.
  • the outer diameter of the side plate or main plate of the impeller is It is formed larger than the outer diameter of the blower blade of the impeller (for example, refer to Patent Document 1).
  • the present invention has been made to solve such a problem, and provides an indoor unit for an air conditioner that has low power consumption and low noise.
  • An indoor unit for an air conditioner includes a main plate that is fixed to a rotating shaft, a shroud that has a suction port through which gas flows, and a plurality of members that are joined between the main plate and the first portion of the main plate.
  • An air conditioner indoor unit comprising a wing and a centrifugal fan having a blowout port that is formed in a second part between the wings and through which gas flows out, wherein the main plate is in a direction in which the opening height of the blowout port increases.
  • the outer peripheral portion has an expanding end portion, and an arc having a radius of curvature is formed at the end portion, and the radius of curvature is larger in the first portion than in the second portion.
  • the indoor unit for an air conditioner of the present invention by expanding the outlet in the height direction in the outer peripheral portion of the main plate, the indoor heat exchange of the gas flowing in from the inlet is higher than the height of the outlet. Can be sent evenly to the vessel. At this time, the flow of the gas flowing out from the centrifugal fan becomes easy to spread in the gas inflow direction, and spreads along the end most easily. For this reason, the inflow of the airflow to the heat exchanger can be effectively made uniform, and the indoor unit for the air conditioner can have low power consumption and low noise.
  • FIG. 1 is a top view of an air conditioner indoor unit 100 according to Embodiment 1 of the present invention.
  • FIG. 3 is a cross-sectional view of the air conditioner indoor unit 100 according to Embodiment 1 of the present invention taken along the line AA in FIG. 3 is a cross-sectional view of the indoor unit for an air conditioner 100 according to Embodiment 1 of the present invention taken along line BB in FIG. It is sectional drawing which shows the flow of the gas inside the conventional indoor unit for air conditioning apparatuses.
  • FIG. 6 is a cross-sectional view of the air conditioner indoor unit 100 according to Embodiment 2 of the present invention taken along the line AA in FIG. [Fig. 6]
  • Fig. 6 is a cross-sectional view taken along the line BB in Fig. 2 of the air conditioner indoor unit 100 according to Embodiment 2 of the present invention.
  • It is a perspective view of the centrifugal fan 1 of the indoor unit 100 for air conditioning apparatuses which concerns on Embodiment 3 of this invention.
  • FIG. 6 is a cross-sectional view of the air conditioner indoor unit 100 according to Embodiment 5 of the present invention taken along the line AA in FIG. It is AA sectional drawing in FIG. 2 of the indoor unit 100 for air conditioning apparatuses which concerns on Embodiment 6 of this invention. It is a figure showing the structural example of the air conditioning apparatus which concerns on Embodiment 7 of this invention.
  • FIG. 1 to 4 are diagrams for describing an air conditioner indoor unit 100 according to Embodiment 1 of the present invention.
  • FIG. 1 is a perspective view of centrifugal fan 1 of air conditioner indoor unit 100 according to Embodiment 1 of the present invention.
  • FIG. 2 is a top view of the air conditioner indoor unit 100 according to Embodiment 1 of the present invention.
  • 3 is a cross-sectional view of the air conditioner indoor unit 100 according to Embodiment 1 of the present invention taken along the line AA in FIG. 4 is a cross-sectional view taken along the line BB in FIG. 2 of the indoor unit 100 for an air-conditioning apparatus according to Embodiment 1 of the present invention.
  • the indoor unit 100 for an air-conditioning apparatus includes a centrifugal fan 1, a bell mouth 2, and an indoor heat exchanger 3.
  • the air conditioner indoor unit 100 in the present embodiment is a ceiling-embedded indoor unit.
  • the centrifugal fan 1 includes a boss 12 that rotates around an axis 11, a main plate 13 that is connected to the boss 12, a shroud 14 that has a suction port 141 through which gas (for example, air) flows, a main plate 13, and a shroud 14.
  • a plurality of (seven in the present embodiment) blades 15 are disposed between the blades 15.
  • a space between the blades 15 sandwiched between the main plate 13 and the shroud 14 becomes a blowout port 16.
  • a driving device fan motor or the like
  • gas flows in (inhales) through the bell mouth 2 from the suction port 141 facing the rotational axis direction (hereinafter referred to as the axial direction).
  • the inflowing gas flows out (blows out) from the outlet 16 facing the outer peripheral direction intersecting the rotation axis.
  • the bell mouth 2 is installed on the gas inflow side (suction side) of the centrifugal fan 1.
  • the bell mouth 2 rectifies the gas and allows it to flow into the suction port 141 of the centrifugal fan 1.
  • the indoor heat exchanger 3 is installed so that the blower outlet 16 of the centrifugal fan 1 may be enclosed.
  • the indoor heat exchanger 3 exchanges heat between the refrigerant and the gas flowing in the heat exchanger, and cools, heats, etc. the gas.
  • the height (length in the vertical direction) of the indoor heat exchanger 3 in the indoor unit 100 for an air conditioner according to the present embodiment is the height of the outlet 16 of the centrifugal fan 1 in relation to the amount of heat exchange and the like. It is configured to be higher than the length (the length between the main plate 13 and the shroud 14).
  • the gas flowing out from the outlet 16 of the centrifugal fan 1 passes through the indoor heat exchanger 3 and flows out of the indoor unit 100 for the air conditioner.
  • the outer peripheral end 131 of the main plate 13 of the centrifugal fan 1 is in the axial main plate 13 side (the inflow direction of the gas flowing into the centrifugal fan 1.
  • An enlarged portion 132 that extends in the axial direction main plate side and expands the size of the outlet 16 in the opening height direction is formed at the end of the outer peripheral portion.
  • the enlarged portion 132 is formed to have an arc shape (including a substantially arc shape, hereinafter referred to as a substantially arc shape) on the cut surface including the rotation axis.
  • the radius of curvature of the enlarged portion 132 is that of the wing portion 152 that is the first portion where the main plate 13 and the wing 15 are joined, It is formed so as to be larger than the blade interval 151 as the second portion.
  • FIG. 5 is a cross-sectional view showing a gas flow inside a conventional indoor unit for an air conditioner.
  • FIG. 6 is sectional drawing which shows the flow of the gas inside the indoor unit 100 for air conditioning apparatuses which concerns on Embodiment 1 of this invention.
  • FIG. 5 is given the same reference numerals as those of the members in the indoor unit 100 for an air conditioner of the present embodiment. The effects obtained by the configuration of the air conditioner indoor unit 100 in the present embodiment will be described with reference to FIGS. 1, 5, and 6.
  • the gas flowing out from the outlet 16 of the centrifugal fan 1 flows into the indoor heat exchanger 3.
  • the indoor heat exchanger 3 is connected to the indoor heat exchanger 3. Inflow becomes uneven.
  • the amount of gas flowing into the region that becomes the top surface decreases.
  • the indoor unit 100 for an air conditioner has a substantially arc shape so that the outlet 16 extends toward the axial main plate at the outer peripheral end 131 of the main plate 13.
  • An enlarged portion 132 is provided. For this reason, the gas flowing out of the centrifugal fan 1 is likely to spread to the top surface side.
  • the flow of the gas flowing out from the centrifugal fan 1 has a large blowing flow velocity in the blade portion 152 that gives work to the airflow, and the space between the blades between the blade portion 152 and the blade portion 152 is increased.
  • the blowout flow rate decreases.
  • the radius of curvature of the substantially arc-shaped enlarged portion 132 is formed large in the blade portion 152 having a large blowing flow velocity, and the curvature radius is formed small in the blade interval 151 having a small blowing flow velocity.
  • the gas is allowed to expand to the axial main plate side while following the substantially arc-shaped enlarged portion 132 of the outer peripheral end portion 131 of the main plate 13 without any difficulty. For this reason, the inflow of the gas to the indoor heat exchanger 3 can be made uniform effectively. Therefore, the air conditioner indoor unit 100 can be configured with low power consumption and low noise.
  • FIG. 7 and 8 are diagrams for explaining an air conditioner indoor unit 100 according to Embodiment 2 of the present invention. Specifically, FIG. 7 is a cross-sectional view of the air conditioner indoor unit 100 according to Embodiment 2 of the present invention taken along the line AA in FIG. FIG. 8 is a cross-sectional view taken along the line BB in FIG. 2 of the indoor unit 100 for an air-conditioning apparatus according to Embodiment 2 of the present invention.
  • the tangent at the outer peripheral end 131 of the substantially arc-shaped enlarged portion 132 toward the axial main plate of the outer peripheral end 131 of the main plate 13 of the centrifugal fan 1 is the centrifugal fan. 1 is configured to pass through the lower end portion 31 of the indoor heat exchanger 3 at a position where the distance between the outer peripheral end portion 131 and the indoor heat exchanger 3 is closest.
  • the outer peripheral end 131 of the main plate 13 spreads along the substantially arc-shaped enlarged portion 132 toward the axial main plate.
  • the blowout flow from the centrifugal fan 1 flows into the indoor heat exchanger 3 without excess or deficiency in order to expand at an optimal expansion angle. Therefore, the inflow of the airflow into the indoor heat exchanger 3 can be made even more effectively, and the air conditioner indoor unit 100 can be reduced in power consumption and noise.
  • FIG. 9 and 10 are diagrams for explaining an air conditioner indoor unit 100 according to Embodiment 3 of the present invention. Specifically, FIG. 9 is a perspective view of centrifugal fan 1 of air conditioner indoor unit 100 according to Embodiment 3 of the present invention. FIG. 10 is a cross-sectional view of the air conditioner indoor unit 100 according to Embodiment 3 of the present invention taken along the line AA in FIG.
  • the air conditioner indoor unit 100 according to Embodiment 3 of the present invention has a small blade 17 attached to the upstream side surface of the shroud 14 of the centrifugal fan 1.
  • FIG. 11 is a cross-sectional view showing a gas flow inside the air conditioner indoor unit 100 according to Embodiment 3 of the present invention. The effect obtained by configuring the indoor unit 100 for an air conditioner according to Embodiment 3 will be described with reference to FIG.
  • a small blade 17 is attached to the upstream side surface of the shroud 14 of the centrifugal fan 1, so that a space formed between the shroud 14, the bell mouth 2, and the indoor heat exchanger 3 is obtained.
  • the generated shroud vicinity vortex 4 can be strengthened.
  • the gas flowing out from the centrifugal fan 1 easily spreads to the bell mouth 2 side (axial bell mouth side) in the axial direction due to the airflow attraction effect by the action of the strong shroud vicinity vortex 4. Therefore, the inflow of the airflow into the indoor heat exchanger 3 can be made even more effectively, and the indoor unit 100 for the air conditioner can be reduced in power consumption and noise.
  • FIG. 12 is a perspective view of centrifugal fan 1 of air conditioner indoor unit 100 according to Embodiment 4 of the present invention.
  • the small blade 17 attached to the upstream side surface of the shroud 14 of the centrifugal fan 1 is disposed between the main plate 13 and the shroud 14. It is the same number as the plurality of blades 15 to be formed.
  • Each winglet 17 is attached at a position that is the same as the wing 15 when viewed from the axial direction.
  • the flow rate of the gas flowing out of the centrifugal fan 1 increases in the blowing flow velocity at the blade portion 152 that imparts work to the air flow, and decreases in the blade interval 151 between the blade portions 152 and 152.
  • a strong shroud vicinity vortex 4 is generated in the small wing portion 172 which is a space near the small blade 17 provided on the upstream surface side of the shroud 14.
  • a weak shroud vicinity vortex 4 is generated in the small blade inter-blade portion 171 which is a space between the small blade 17 and the small blade 17.
  • a small blade is provided on the upstream side surface of the shroud 14 of the centrifugal fan 1 so that the same number and the same number of blades 15 are disposed between the main plate 13 and the shroud 14.
  • a relatively strong shroud vicinity vortex 4 is generated in the wing portion 152 having a large blowing flow velocity, and the blowing flow having a large flow velocity is expanded toward the axial shroud side by an attraction effect.
  • a relatively weak shroud vicinity vortex 4 is generated between the blades 151 having a small blowing flow velocity so that the blowing flow having a small flow velocity is expanded toward the axial shroud side by an attraction effect.
  • size of blowing flow velocity can be exhibited. Therefore, the inflow of the airflow into the indoor heat exchanger 3 can be made even more effective, and the air conditioner indoor unit 100 can be reduced in power consumption and noise.
  • FIG. 13 is a cross-sectional view of the air conditioner indoor unit 100 according to Embodiment 5 of the present invention taken along the line AA in FIG.
  • Embodiment 5 of the present invention the differences from Embodiments 1 to 4 will be described.
  • the axial height from the shroud outer peripheral end portion 142 to the small blade outer peripheral upper end portion 173 is h, and the shroud outer periphery
  • the axial height from the end 142 to the bell mouth 2 is H.
  • h is configured to be 1/2 or less of H.
  • the size of the shroud vicinity vortex 4 generated by the small blades 17 is not excessive and interferes with the bell mouth 2. do not do. For this reason, the flow of the gas flowing out from the centrifugal fan 1 can be effectively expanded to the axial shroud side by the attraction effect while suppressing the flow loss to the minimum. Therefore, the inflow of the airflow to the indoor heat exchanger 3 can be made uniform, and the air conditioner indoor unit 100 can have low power consumption and low noise.
  • Embodiment 6 FIG. 14 is a cross-sectional view of the air conditioner indoor unit 100 according to Embodiment 6 of the present invention taken along the line AA in FIG.
  • Embodiments 1 to 5 portions different from Embodiments 1 to 5 will be described.
  • L be a radial distance at a position where the blowout port 16 in the outer peripheral end 131 of the centrifugal fan 1 and the indoor heat exchanger 3 are closest to each other.
  • the axial distance between the shroud outer peripheral end 142 of the centrifugal fan 1 and the upper end 32 of the heat exchanger, and the axial distance between the outer peripheral end 131 of the main plate 13 of the centrifugal fan 1 and the lower end 31 of the heat exchanger let L1 be the smaller one and L2 the larger one.
  • the air conditioner indoor unit 100 of the present embodiment is configured to satisfy L1 ⁇ L ⁇ L2.
  • the axial distance between the outer peripheral end 131 of the main plate 13 of the centrifugal fan 1 and the lower end 31 of the heat exchanger is L1, the shroud outer end 142 of the centrifugal fan 1 and the upper end of the heat exchanger.
  • L2 the case where the axial direction distance to 32 is set to L2 is shown as an example, it is not limited to this.
  • the distance between the air outlet 16 at the outer peripheral end 131 of the centrifugal fan 1 and the indoor heat exchanger 3 is appropriately set. Can be maintained.
  • the outer peripheral end 131 of the main plate 13 is formed with a substantially arc-shaped enlarged portion 132 toward the axial main plate, and the radius of curvature of the substantially arc-shaped enlarged portion 132 is large in the blade portion 152 where the blowing flow velocity is large.
  • the flow between the blades 151 having a small flow velocity is small, and the blowout flow of the centrifugal fan 1 spread by attaching the small blades 17 to the upstream side of the shroud 14 of the centrifugal fan 1 is the most effective in the indoor heat exchanger 3.
  • the air conditioner indoor unit 100 can be reduced in power consumption and noise.
  • FIG. FIG. 15 is a diagram illustrating a configuration example of an air-conditioning apparatus according to Embodiment 7 of the present invention.
  • the air conditioner of FIG. 15 connects an outdoor unit (outdoor unit) 200 and an indoor unit (indoor unit) 100 with a gas refrigerant pipe 300 and a liquid refrigerant pipe 400.
  • the outdoor unit 200 includes a compressor 201, a four-way valve 202, an outdoor heat exchanger 203, an expansion valve 204, and an outdoor blower 205.
  • the indoor unit 100 for an air conditioner has an indoor heat exchanger 3.
  • Compressor 201 compresses and discharges the sucked refrigerant.
  • the capacity of the compressor 201 (the amount of refrigerant sent out per unit time) is changed by arbitrarily changing the operating frequency of the compressor 201 by, for example, an inverter circuit. You may be able to.
  • the four-way valve 202 is, for example, a valve for switching the refrigerant flow between the cooling operation and the heating operation.
  • the outdoor heat exchanger 203 performs heat exchange between the refrigerant and air (outdoor air). For example, it functions as an evaporator during heating operation, evaporating and evaporating the refrigerant. Moreover, it functions as a condenser during the cooling operation, and condenses and liquefies the refrigerant.
  • the outdoor blower 205 sends gas to the outdoor heat exchanger 203.
  • An expansion valve 204 such as a throttle device (flow rate control means) expands the refrigerant by depressurizing it. For example, in the case of an electronic expansion valve or the like, the opening degree is adjusted based on an instruction from a control means (not shown) or the like.
  • the indoor heat exchanger 3 performs heat exchange between gas (for example, air to be air-conditioned) and refrigerant. During heating operation, it functions as a condenser and condenses and liquefies the refrigerant. Moreover, it functions as an evaporator during cooling operation, evaporating and evaporating the refrigerant. As described above, the centrifugal fan 1 sends air to be air-conditioned, for example, into the indoor heat exchanger 3.
  • the centrifugal fan 1 of the present embodiment has an enlarged portion 132 formed on the main plate 13.
  • the air flow to the indoor heat exchanger 3 can be effectively achieved by using the air conditioner indoor unit 100 described in the first to sixth embodiments. Can be made uniform, and the entire apparatus can achieve low power consumption and low noise.
  • the indoor units of the first to third embodiments can be used for other refrigeration cycle apparatuses such as a refrigeration apparatus.

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

Abstract

Cette unité intérieure (100) destinée à un dispositif de climatisation est pourvue d'un ventilateur centrifuge (1), comportant : une plaque principale (13) fixée à un arbre tournant ; une enveloppe (14) comportant une ouverture d'aspiration (141) dans laquelle s'écoule du gaz ; une pluralité d'aubes (15) agencées entre la plaque principale (13) et l'enveloppe (14) et jointes respectivement à des premières parties de la plaque principale (13) ; et des ouvertures d'évacuation (16) formées dans des secondes parties, qui se trouvent entre les aubes (15), et évacuent le gaz. La plaque principale (13) présente des sections de détente (132) au niveau de sa partie périphérique extérieure, les sections de détente (132) s'étendant dans la direction dans laquelle la hauteur des ouvertures d'évacuation (16) augmente. Les sections de détente (132) comportent des arcs circulaires ayant un rayon de courbure, et les premières parties présentent un rayon de courbure supérieur à celui des secondes parties.
PCT/JP2014/073833 2014-09-09 2014-09-09 Unité intérieure de dispositif de climatisation et dispositif de climatisation WO2016038690A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP14901479.7A EP3196560B1 (fr) 2014-09-09 2014-09-09 Unité intérieure de dispositif de climatisation et dispositif de climatisation
JP2016547295A JP6429887B2 (ja) 2014-09-09 2014-09-09 空気調和装置用室内機および空気調和装置
PCT/JP2014/073833 WO2016038690A1 (fr) 2014-09-09 2014-09-09 Unité intérieure de dispositif de climatisation et dispositif de climatisation

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2014/073833 WO2016038690A1 (fr) 2014-09-09 2014-09-09 Unité intérieure de dispositif de climatisation et dispositif de climatisation

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WO2016038690A1 true WO2016038690A1 (fr) 2016-03-17

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WO (1) WO2016038690A1 (fr)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02166323A (ja) * 1988-12-20 1990-06-27 Daikin Ind Ltd 空気調和装置
JPH0593523A (ja) * 1990-11-07 1993-04-16 Daikin Ind Ltd 空気調和装置
JPH05172097A (ja) * 1991-12-25 1993-07-09 Mitsubishi Electric Corp 空気調和機
JPH05231392A (ja) * 1992-02-17 1993-09-07 Nippondenso Co Ltd 多翼送風ファン
JP2001173595A (ja) * 1999-12-15 2001-06-26 Hitachi Ltd 遠心型羽根車
JP2007198268A (ja) * 2006-01-27 2007-08-09 Hitachi Ltd 遠心ファンとそれを備えた空気調和装置
JP2010185456A (ja) * 2009-02-12 2010-08-26 Ebm - Papst Mulfingen Gmbh & Co Kg 遠心式送風機または斜流送風機に用いられるインペラ

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02166323A (ja) * 1988-12-20 1990-06-27 Daikin Ind Ltd 空気調和装置
JPH0593523A (ja) * 1990-11-07 1993-04-16 Daikin Ind Ltd 空気調和装置
JPH05172097A (ja) * 1991-12-25 1993-07-09 Mitsubishi Electric Corp 空気調和機
JPH05231392A (ja) * 1992-02-17 1993-09-07 Nippondenso Co Ltd 多翼送風ファン
JP2001173595A (ja) * 1999-12-15 2001-06-26 Hitachi Ltd 遠心型羽根車
JP2007198268A (ja) * 2006-01-27 2007-08-09 Hitachi Ltd 遠心ファンとそれを備えた空気調和装置
JP2010185456A (ja) * 2009-02-12 2010-08-26 Ebm - Papst Mulfingen Gmbh & Co Kg 遠心式送風機または斜流送風機に用いられるインペラ

Also Published As

Publication number Publication date
JP6429887B2 (ja) 2018-11-28
EP3196560B1 (fr) 2020-09-09
EP3196560A4 (fr) 2018-05-09
EP3196560A1 (fr) 2017-07-26
JPWO2016038690A1 (ja) 2017-06-01

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