WO2016038690A1 - Indoor unit for air conditioning device, and air conditioning device - Google Patents
Indoor unit for air conditioning device, and air conditioning device Download PDFInfo
- 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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- WIPO (PCT)
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- indoor unit
- air conditioner
- centrifugal fan
- main plate
- shroud
- Prior art date
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
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.
Abstract
Description
図1~図4は、本発明の実施の形態1に係る空気調和装置用室内機100を説明する図である。具体的には、図1は本発明の実施の形態1に係る空気調和装置用室内機100の遠心ファン1の斜視図である。また、図2は本発明の実施の形態1に係る空気調和装置用室内機100の上面図である。さらに、図3は本発明の実施の形態1に係る空気調和装置用室内機100の図2におけるA-A断面図である。そして、図4は本発明の実施の形態1に係る空気調和装置用室内機100の図2におけるB-B断面図である。
1 to 4 are diagrams for describing an air conditioner
より一層の空気調和装置用室内機100の低消費電力化および低騒音化を実現するために、本実施の形態の空気調和装置用室内機100を以下のような構成にするのが望ましい。図7および図8は、本発明の実施の形態2に係る空気調和装置用室内機100を説明するための図である。具体的には、図7は本発明の実施の形態2に係る空気調和装置用室内機100の図2におけるA-A断面図である。また、図8は本発明の実施の形態2に係る空気調和装置用室内機100の図2におけるB-B断面図である。
In order to further reduce the power consumption and the noise of the air conditioner
より一層の空気調和装置用室内機100の低消費電力化および低騒音化を実現するために、本実施の形態の空気調和装置用室内機100を以下のような構成にするのが望ましい。図9および図10は、本発明の実施の形態3に係る空気調和装置用室内機100を説明するための図である。具体的には、図9は本発明の実施の形態3に係る空気調和装置用室内機100の遠心ファン1の斜視図である。また、図10は本発明の実施の形態3に係る空気調和装置用室内機100の図2におけるA-A断面図である。
In order to further reduce the power consumption and the noise of the air conditioner
より一層の空気調和装置用室内機100の低消費電力化、低騒音化を実現するためには、以下のような構成にするのが望ましい。図12は本発明の実施の形態4に係る空気調和装置用室内機100の遠心ファン1の斜視図である。
In order to realize further reduction in power consumption and noise in the
より一層の空気調和装置用室内機100の低消費電力化、低騒音化を実現するためには、以下のような構成にするのが望ましい。図13は本発明の実施の形態5に係る空気調和装置用室内機100の図2におけるA-A断面図である。 Embodiment 5 FIG.
In order to realize further reduction in power consumption and noise in the
より一層の空気調和装置用室内機100の低消費電力化、低騒音化を実現するためには、以下のような構成にするのが望ましい。図14は本発明の実施の形態6に係る空気調和装置用室内機100の図2におけるA-A断面図である。 Embodiment 6 FIG.
In order to realize further reduction in power consumption and noise in the
図15は本発明の実施の形態7に係る空気調和装置の構成例を表す図である。図15の空気調和装置は、室外機(室外ユニット)200と室内機(室内ユニット)100とをガス冷媒配管300、液冷媒配管400により配管接続する。室外機200は、圧縮機201、四方弁202、室外熱交換器203、膨張弁204および室外送風機205を有している。また、空気調和装置用室内機100は室内熱交換器3を有している。 Embodiment 7 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
遠心ファン1は、前述したように、例えば空調対象となる空気を室内熱交換器3に送り込む。本実施の形態の遠心ファン1は、主板13に拡大部132を形成している。 Further, as described above, the
As described above, the
Claims (7)
- 回転軸に固定される主板、気体が流入する吸い込み口を有するシュラウドおよび前記主板と前記シュラウドとの間に配置され、前記主板の第一部分とそれぞれ接合する複数の翼および該翼間となる第二部分に形成されて前記気体が流出する吹き出し口を有する遠心ファンと
を備える空気調和装置用室内機であって、
前記主板は、前記吹き出し口の開口高さが拡大する方向に拡がる端部を外周部分に有し、前記端部は、曲率半径を有する円弧が形成され、前記曲率半径は前記第二部分よりも前記第一部分の方が大きい空気調和装置用室内機。 A main plate fixed to the rotating shaft, a shroud having a suction port through which gas flows, and a plurality of blades arranged between the main plate and the shroud and respectively joined to the first portion of the main plate, and a second between the blades An indoor unit for an air conditioner comprising a centrifugal fan having a blowout port formed in a portion and outflowing the gas,
The main plate has an end portion that extends in a direction in which the opening height of the blowout opening increases in the outer peripheral portion, and the end portion is formed with an arc having a radius of curvature, and the radius of curvature is larger than that of the second portion. The indoor unit for an air conditioner having a larger first part. - 前記翼間の前記端部において、前記遠心ファンの外周端部と、前記吹き出し口の開口高さより高く、前記吹き出し口を囲むように設置される室内熱交換器との距離が最も近接する位置における接線が、前記室内熱交換器の下端部を通過するように構成する請求項1記載の空気調和装置用室内機。 In the end portion between the blades, the outer peripheral end portion of the centrifugal fan is higher than the opening height of the air outlet, and the distance between the indoor heat exchanger installed so as to surround the air outlet is closest. The indoor unit for an air conditioner according to claim 1, wherein the tangent passes through a lower end of the indoor heat exchanger.
- 前記遠心ファンは、前記シュラウドの上流側面に小翼を有する請求項1又は請求項2記載の空気調和装置用室内機。 3. The indoor unit for an air conditioner according to claim 1, wherein the centrifugal fan has a small blade on an upstream side surface of the shroud.
- 前記小翼は、前記翼と同一枚数で、かつ、前記回転軸方向から見たときに前記翼に対して同一となるような位置に付設されている請求項3に記載の空気調和装置用室内機。 4. The air conditioner chamber according to claim 3, wherein the number of the small blades is the same as the number of the blades, and is attached to a position that is the same as the blades when viewed from the rotation axis direction. Machine.
- 前記小翼の高さは、前記シュラウドの外周端部と前記遠心ファンの気体流入側に設置されるベルマウスとの前記回転軸の方向における距離の1/2以下である請求項3又は請求項4に記載の空気調和装置用室内機。 The height of the winglet is ½ or less of the distance in the direction of the rotation axis between the outer peripheral end of the shroud and the bell mouth installed on the gas inflow side of the centrifugal fan. 4. The indoor unit for an air conditioning apparatus according to 4.
- 前記遠心ファンの外周端部と前記室内熱交換器とが最も近接する位置での半径方向距離をL、前記遠心ファンのシュラウド外周端部と熱交換器の上端部との軸方向距離、および前記遠心ファンの前記主板の外周端部と前記熱交換器の下端部との軸方向距離のうち、短い方の距離をL1、長い方の距離をL2とするとき、L1<L<L2となる関係を有する構成であることを特徴とする請求項1~請求項4のいずれか一項に記載の空気調和装置用室内機。 L is the radial distance at the position where the outer peripheral end of the centrifugal fan and the indoor heat exchanger are closest to each other, the axial distance between the outer peripheral end of the shroud of the centrifugal fan and the upper end of the heat exchanger, and Of the axial distances between the outer peripheral end of the main plate of the centrifugal fan and the lower end of the heat exchanger, when L1 is the shorter distance and L2 is the longer distance, L1 <L <L2 The indoor unit for an air conditioner according to any one of claims 1 to 4, wherein the indoor unit is an air conditioner.
- 請求項1~6のいずれか一項に記載の空気調和装置用室内機と、室外機とを備えて空気調和を行うことを特徴とする空気調和装置。 An air conditioner comprising the indoor unit for an air conditioner according to any one of claims 1 to 6 and an outdoor unit to perform air conditioning.
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
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EP14901479.7A EP3196560B1 (en) | 2014-09-09 | 2014-09-09 | Indoor unit for air conditioning device, and air conditioning device |
PCT/JP2014/073833 WO2016038690A1 (en) | 2014-09-09 | 2014-09-09 | Indoor unit for air conditioning device, and air conditioning device |
JP2016547295A JP6429887B2 (en) | 2014-09-09 | 2014-09-09 | Indoor unit for air conditioner and air conditioner |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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PCT/JP2014/073833 WO2016038690A1 (en) | 2014-09-09 | 2014-09-09 | Indoor unit for air conditioning device, and air conditioning device |
Publications (1)
Publication Number | Publication Date |
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WO2016038690A1 true WO2016038690A1 (en) | 2016-03-17 |
Family
ID=55458481
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/JP2014/073833 WO2016038690A1 (en) | 2014-09-09 | 2014-09-09 | Indoor unit for air conditioning device, and air conditioning device |
Country Status (3)
Country | Link |
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EP (1) | EP3196560B1 (en) |
JP (1) | JP6429887B2 (en) |
WO (1) | WO2016038690A1 (en) |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH02166323A (en) * | 1988-12-20 | 1990-06-27 | Daikin Ind Ltd | Airconditioning device |
JPH0593523A (en) * | 1990-11-07 | 1993-04-16 | Daikin Ind Ltd | Air conditioner |
JPH05172097A (en) * | 1991-12-25 | 1993-07-09 | Mitsubishi Electric Corp | Air conditioner |
JPH05231392A (en) * | 1992-02-17 | 1993-09-07 | Nippondenso Co Ltd | Multiblade blower fan |
JP2001173595A (en) * | 1999-12-15 | 2001-06-26 | Hitachi Ltd | Centrifugal impelelr |
JP2007198268A (en) * | 2006-01-27 | 2007-08-09 | Hitachi Ltd | Centrifugal fan and air conditioning device equipped with it |
JP2010185456A (en) * | 2009-02-12 | 2010-08-26 | Ebm - Papst Mulfingen Gmbh & Co Kg | Impeller for use in centrifugal blower or diagonal flow blower |
-
2014
- 2014-09-09 WO PCT/JP2014/073833 patent/WO2016038690A1/en active Application Filing
- 2014-09-09 EP EP14901479.7A patent/EP3196560B1/en active Active
- 2014-09-09 JP JP2016547295A patent/JP6429887B2/en active Active
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH02166323A (en) * | 1988-12-20 | 1990-06-27 | Daikin Ind Ltd | Airconditioning device |
JPH0593523A (en) * | 1990-11-07 | 1993-04-16 | Daikin Ind Ltd | Air conditioner |
JPH05172097A (en) * | 1991-12-25 | 1993-07-09 | Mitsubishi Electric Corp | Air conditioner |
JPH05231392A (en) * | 1992-02-17 | 1993-09-07 | Nippondenso Co Ltd | Multiblade blower fan |
JP2001173595A (en) * | 1999-12-15 | 2001-06-26 | Hitachi Ltd | Centrifugal impelelr |
JP2007198268A (en) * | 2006-01-27 | 2007-08-09 | Hitachi Ltd | Centrifugal fan and air conditioning device equipped with it |
JP2010185456A (en) * | 2009-02-12 | 2010-08-26 | Ebm - Papst Mulfingen Gmbh & Co Kg | Impeller for use in centrifugal blower or diagonal flow blower |
Also Published As
Publication number | Publication date |
---|---|
EP3196560B1 (en) | 2020-09-09 |
JPWO2016038690A1 (en) | 2017-06-01 |
EP3196560A1 (en) | 2017-07-26 |
JP6429887B2 (en) | 2018-11-28 |
EP3196560A4 (en) | 2018-05-09 |
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