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WO2015166581A1 - Souffleuse d'air, unité extérieure, et dispositif à cycle de réfrigération - Google Patents

Souffleuse d'air, unité extérieure, et dispositif à cycle de réfrigération Download PDF

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Publication number
WO2015166581A1
WO2015166581A1 PCT/JP2014/062163 JP2014062163W WO2015166581A1 WO 2015166581 A1 WO2015166581 A1 WO 2015166581A1 JP 2014062163 W JP2014062163 W JP 2014062163W WO 2015166581 A1 WO2015166581 A1 WO 2015166581A1
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WO
WIPO (PCT)
Prior art keywords
fan
bell mouth
air
propeller fan
outdoor unit
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2014/062163
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English (en)
Japanese (ja)
Inventor
宏樹 岡澤
敬英 田所
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to PCT/JP2014/062163 priority Critical patent/WO2015166581A1/fr
Publication of WO2015166581A1 publication Critical patent/WO2015166581A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/54—Fluid-guiding means, e.g. diffusers

Definitions

  • the present invention relates to a blower having a propeller fan and a bell mouth.
  • blower fan unit
  • a blower having such a propeller fan is used in a wide range of fields such as an outdoor unit (outdoor unit) of a refrigeration air conditioner, a cooling device such as a refrigerator, a ventilation fan, and a computer.
  • Such a blower includes, for example, a bell mouth that forms a wall surface along the rotation direction of the propeller fan.
  • a bell mouth has an enlarged opening so that air can be smoothly blown out (see, for example, Patent Document 1).
  • propeller fans have blade tip vortices due to the difference in static pressure between the pressure surface and suction surface at the outer peripheral end, which causes a decrease in fan performance.
  • the outer peripheral end has a convex shape on the pressure surface side. (For example, refer to Patent Document 2).
  • an object of the present invention is to obtain an outdoor unit or the like of a refrigeration cycle apparatus having a blower that further suppresses noise and power increase.
  • the blower of the outdoor unit according to the present invention has a winglet having a convex shape on the pressure surface side, rotates around a rotation axis along the gravity direction, and flows a gas in a direction opposite to the gravity direction.
  • Propeller fan comprising: a propeller fan having a plurality of blades to be generated; and a bell mouth for rectifying gas by forming an annular wall surface outside the outer peripheral end of the blade along the rotation direction of the blades of the propeller fan
  • the bell mouth has a sloped wall surface that is formed so that the air path on the blowout side is enlarged, and the suction side and the blowout side of the slope are provided.
  • the blower of the outdoor unit according to the present invention has a slope formed so that the air passage on the blowout side is enlarged, and further L / L 0 ⁇ 0.5, 10 ° ⁇ ⁇ 45 °, H / D ⁇ Since the fan of the outdoor unit in which the bell mouth is formed with respect to the propeller fan having a shape satisfying the relationship of 0.04 and having a winglet having a convex shape on the pressure surface side at the outer peripheral end is configured. By selecting the optimum angle ⁇ according to the points, fan input and noise can be reduced.
  • FIG. 6 is a diagram showing PQ characteristics when L / L 0 is changed. It is a diagram representing the relationship between the value of the air volume Q specific noise level K s 2 o'clock and L / L 0. It is a diagram representing the air flow rate Q A, Q B, optimal oblique section angle of each Q C theta. Is a diagram representing the main flow 7 of the air volume Q A. Is a diagram representing the main flow 7 of the air volume Q B.
  • FIG. 6 is a perspective view illustrating another shape of the bell mouth 2 according to the first embodiment. It is FIG. (1) showing the example of another shape of the diagonal part 5a of the air blower which concerns on Embodiment 1.
  • FIG. It is a figure (the 2) showing another example of the shape of the diagonal part 5a of the air blower which concerns on Embodiment 1.
  • FIG. 1 and the following drawings the same reference numerals denote the same or corresponding parts, and are common to the whole text of the embodiments described below.
  • the form of the component represented by the whole specification is an illustration to the last, Comprising: It does not limit to the form described in the specification.
  • the combination of the components is not limited to the combination in each embodiment, and the components described in the other embodiments can be applied to another embodiment.
  • the subscripts may be omitted.
  • the upper side in the figure will be described as “upper side” and the lower side will be described as “lower side”.
  • the size relationship of each component may be different from the actual one.
  • the level of temperature, pressure, etc. is not particularly determined in relation to absolute values, but is relatively determined in the state, operation, etc. of the system, apparatus, and the like.
  • FIG. 1 is a diagram showing an outline of a blower according to Embodiment 1 of the present invention.
  • FIG. 1 the cross section of the propeller fan 1 and the bell mouth 2 is shown.
  • the blower according to the present embodiment is mounted on an outdoor unit of the top blowing type refrigeration cycle apparatus such as an air conditioner.
  • the propeller fan 1 is an axial fan that generates a flow of air (fluid) by rotating a plurality of blades (propellers, blades) around a rotation axis by driving a motor or the like (not shown) that receives electric power.
  • the outdoor unit is configured so that the rotation axis is substantially along the gravity direction (vertical direction; hereinafter, sometimes referred to as the height direction of the blower) and blows air in the direction opposite to the gravity direction.
  • the propeller fan 1 (blower) is disposed in FIG.
  • FIG. 2 is a view showing the winglet 1a of the propeller fan 1 according to the first embodiment of the present invention.
  • the upper side of the blade is the pressure surface
  • the lower side is the suction surface.
  • the outer peripheral end portion of the blade having the winglet 1a has a convex shape on the pressure surface side.
  • FIG. 3 is a diagram showing a blade tip vortex of a propeller fan that does not have the winglet 1a at the outer peripheral edge of the blade.
  • a blade tip vortex resulting from a static pressure difference between the pressure surface and the suction surface is generated at the outer peripheral end of the blade, which causes a decrease in fan performance.
  • a winglet 1a having a convex shape on the pressure surface side is formed at the outer peripheral end portion of the blade. Since the winglet 1a provides resistance to flow for the tip vortex, generation of the tip vortex can be reduced.
  • the bell mouth 2 covers the propeller fan 1 along the circumferential direction (rotation direction) of the propeller fan 1 (surrounds the periphery of the propeller fan 1), and rectifies the air flow generated by the rotation of the propeller fan 1. For this reason, a circular wall surface is formed around the propeller fan 1.
  • the bell mouth 2 of the present embodiment covers about 50% of the rotation axis direction (height direction) of the propeller fan 1 (as shown in FIG. 1, the rotation axis direction (height direction) of the propeller fan 1.
  • the length of the suction opening 3 and the straight pipe portion 4 is about half (length L).
  • the suction opening 3 is a portion opened to suck air on the upstream side (suction side) of the bell mouth 2.
  • the distance between the rotation shaft of the propeller fan 1 and the terminal portion of the suction opening 3 (the diameter of the opening portion) is between the rotation shaft and the surface of the straight pipe portion 4. It is longer than the distance (diameter of the straight pipe portion 4) (the end of the suction opening 3 has an extension).
  • terminus of the suction opening part 3 is made into the curved surface (a cross-sectional shape becomes circular arc shape).
  • the curved surface has a radius of curvature R, and the curved surface portion of the suction opening 3 is referred to as an R portion 3a.
  • the straight pipe portion 4 is a portion where the inner wall surface of the bell mouth 2 is substantially parallel to the rotation axis of the propeller fan 1. Although it does not specifically limit, the arrangement
  • the blowout opening 5 is a portion opened to blow out air on the downstream side (blowing side) of the bell mouth 2. Also for the blowing opening 5, the distance between the rotating shaft of the propeller fan 1 and the terminal end portion of the blowing opening 5 (diameter of the opening) is the distance between the rotating shaft and the surface of the straight pipe portion 4 (straight). Longer than the diameter of the tube part 4). And the inner wall surface from the blow-off end (blow-off opening 5 suction side end) of the straight pipe portion 4 to the blow-off opening 5 blow-off end is an inclined slope, and the cross-sectional shape is tapered (trumpet shape). It is formed to become. This tapered portion is referred to as an inclined portion 5a.
  • the bell mouth 2 of this Embodiment has the straight pipe part 4, you may make it form the whole inner wall surface by the diagonal part 5a and the R part 3a.
  • FIG. 4 is a diagram showing the PQ characteristic and the K s -Q characteristic of the propeller fan 1 alone.
  • FIG. 5 is a graph showing the PQ characteristics and ⁇ -Q characteristics of the propeller fan 1 alone.
  • P is the static pressure
  • Q is the air flow
  • K s is the specific noise [dB]
  • eta represents the fan efficiency (static pressure efficiency) [%].
  • the specific noise K s and the fan efficiency ⁇ satisfy a relationship satisfying the following expressions (1) and (2) with the static pressure and the air volume.
  • SPL represents noise [dB] at a position away from propeller fan 1 by a predetermined distance
  • T represents torque [Nm]
  • ⁇ represents angular velocity [rad / s].
  • the unit of static pressure in the formula (1) is [mmAq]
  • the unit of air volume is [m 3 / min].
  • the PQ characteristic represents the relationship between the static pressure P, which is the draft resistance, and the air volume Q, with the fan rotation speed of the propeller fan 1 being constant.
  • the low air volume and high static pressure side is referred to as a cutoff side
  • the high air volume and low static pressure side is referred to as an open side.
  • the smaller the draft resistance the easier the wind will flow (the lower the static pressure, the greater the air volume)
  • the greater the draft resistance the less likely the wind will flow (the higher the static pressure, the less the quantity of air).
  • the relationship between the air volume and the static pressure does not always have this relationship, and there is a region where the change in the static pressure is small with respect to the air volume. Referred to as a surging area deadline side of this region, the propeller fan 1 having a winglet 1a on the outer peripheral end, the specific noise K s a little the open side than the surging area is minimized, the fan efficiency ⁇ becomes maximum. Note that the air volume at the minimum specific noise point and the maximum fan efficiency point are substantially the same.
  • FIG. 6 is a diagram showing the relationship between the PQ characteristic and the K s -Q characteristic and the fan diameter of the propeller fan 1.
  • FIG. 7 is a graph showing the relationship between the PQ characteristic and the ⁇ -Q characteristic and the diameter of the propeller fan 1.
  • the minimum specific noise point and the maximum fan efficiency point move to the open side when the fan diameter is increased.
  • the slope of the PQ characteristic becomes gentler in the open side area than the minimum specific noise point and the maximum fan efficiency point, and conversely, when the fan diameter is reduced, the open side is further out than the surging area. In the region, the slope of the PQ characteristic becomes steep.
  • the minimum specific noise is reduced and the maximum fan efficiency is increased.
  • the fan diameter is decreased, the minimum specific noise is increased and the maximum fan efficiency is decreased.
  • the values of minimum specific noise and maximum fan efficiency mainly depend on the fan diameter.
  • the fan rotation speed of the propeller fan 1 is N 0 when the outdoor unit has a predetermined air volume Q 0 . Then, from the PQ characteristics of the propeller fan 1 alone at the fan rotation speed N 0 , the static pressure P 0 at the air volume Q 0 / M is obtained, and (Q 0 / M, P 0 ) is used as the operating point. .
  • the specific noise K s at the operating point is larger than the specific noise at the minimum specific noise point, and the fan efficiency ⁇ is the maximum fan efficiency point. It becomes smaller than the fan efficiency.
  • the minimum specific noise point and maximum fan efficiency point move to the open side as described above, and the minimum specific noise point and maximum fan efficiency point approach the operating point.
  • the noise K s and the fan efficiency ⁇ approach the specific noise at the minimum specific noise point and the fan efficiency at the maximum fan efficiency point, and can suppress noise and fan input.
  • the specific noise K s and fan efficiency ⁇ at the operating point are set to the minimum specific noise and maximum fan efficiency.
  • it is preferable to increase the static pressure on the open side by making the gradient of the PQ characteristic gentler in the open side region than the minimum specific noise point and the maximum fan efficiency point. Increasing the static pressure, the formula (1), from (2), K s is reduced, since the ⁇ is increased, it is possible to reduce noise, the fan input.
  • the slope of the PQ characteristic is gradually reduced in the open area rather than the surging area. It is good to do. In this case, the slopes of the K s -Q characteristics and ⁇ -Q characteristics also become gentler, and the specific noise K s at the operating point, the fan efficiency ⁇ , and the specific noise at the minimum specific noise point, compared to the case where the slope is steep, Since the difference between the maximum fan efficiency point and the fan efficiency is reduced, noise and fan input can be suppressed.
  • an air conditioner including the propeller fan 1 may have a setting that changes the air volume in a plurality of stages.
  • the fan diameter cannot be increased, the operating point at the maximum air volume operation, the minimum specific noise point, and the maximum fan efficiency point in the K s -Q characteristics and ⁇ -Q characteristics will deviate, and noise and fan input are likely to increase. Become. This is because when the fan diameter cannot be made sufficiently large as described above, the minimum specific noise point and the maximum fan efficiency point are on the cutoff side, and the operating point during the maximum air flow operation is on the open side.
  • FIG. 8 is a diagram illustrating an example of a dimension parameter of the bell mouth 2.
  • D the fan diameter of the propeller fan 1.
  • L the length in the rotation axis direction of the bell mouth 2 from the end of the suction opening 3 to the outlet side end of the straight pipe portion 4
  • L the length of the blades in the axial direction (fan height) and L 0.
  • the length (height, hereinafter referred to as an oblique portion height) of the oblique portion 5a in the blowout opening 5 in the rotation axis direction of the propeller fan 1 is denoted by H, and the length in the fan diameter D direction (hereinafter, the oblique portion length). Is called W).
  • the angle which the direction which makes the taper shape of the diagonal part 5a makes with the rotating shaft direction of the propeller fan 1 is set as diagonal part angle (theta).
  • FIG. 9 is a diagram showing the PQ characteristics for the dimensional parameters shown in FIG.
  • the air volume Q 1 represents the air volume in the vicinity of the minimum specific noise point and the maximum fan efficiency point
  • the air volume Q 2 represents the air volume at the operating point that is sufficiently open from the surging area.
  • blower having a structure in which the static pressure at the operating point on the open side of the surging area is increased and the slope on the open side of the PQ characteristic is gentler than that of the surging area.
  • open side refers to an operating point on the open side with respect to the surging region.
  • FIG. 10 is a graph showing the PQ characteristics when L / L 0 is changed.
  • the fan height L 0 is fixed, and the bell mouth height L is changed to change L / L 0 .
  • the static pressure is almost the same.
  • L / L 0 is larger, at the operating point of the air volume Q 2 that is on the open side than the air volume Q 1, the static pressure increases when L / L 0 ⁇ 0.5 and L / L 0 ⁇ In the case of 0.5, the static pressure is almost the same.
  • Figure 11 is a graph depicting the relationship of the fan rotation speed N A, a specific noise level K s [dB] in the air volume Q 2 o'clock blower to the value of L / L 0.
  • L / L 0 ⁇ 0.5 the larger the value of L / L 0 is, the more the specific noise K s on the open side can be reduced.
  • L / L 0 ⁇ 0.5 the specific noise K s on the open side is almost unchanged.
  • Figure 12 is a fan speed as N 0, the air volume Q A, Q B, varying the oblique portion angle ⁇ for each Q C, K s is the minimum, eta is a diagram representing the optimum oblique section angle ⁇ which maximizes is there.
  • Air volume Q A minimum ratio noise point, air flow in the vicinity of the maximum fan efficiency point, the air volume Q C is the air volume which is a static pressure 0, the air flow Q B is the air volume of the middle of the air flow Q A and the air volume Q C. From FIG. 12, ⁇ that minimizes noise and fan input differs for each operating point. Next, the reason will be described.
  • Figure 16 is a graph showing a P-Q characteristic at the time of the fan rotation speed as N A, changing the value of H / D.
  • FIG. 17, when the fan rotational speed N A, the air volume Q 2, is a diagram showing the relationship between the value of the static pressure and H / D.
  • FIG. 18 is a diagram illustrating the relationship between the fan rotation speed N A , the fan efficiency ⁇ at the air volume Q 2 , the specific noise K s and H / D.
  • the fan efficiency ⁇ and the specific noise K s are almost the same in the vicinity of the surging region regardless of the value of H / D.
  • H / D ⁇ 0.04 if the value of H / D is small, the fan efficiency ⁇ decreases and the specific noise K s increases.
  • H / D ⁇ 0.04 the effect of improving the open-side fan efficiency ⁇ and the specific noise K s becomes relatively small as the value of H / D increases.
  • the reason for the improvement in fan efficiency and specific noise on the open side compared to the case of H / D ⁇ 0.04 is that the area of the blowout air passage is expanded and blown out. This is because the speed of the air is decreased and the static pressure is increased. Since the blowout opening 5 has an expansion, the blowout air passage functions as a diffuser. At this time, when H / D ⁇ 0.04, the function as a diffuser is efficiently performed.
  • the minimum specific noise point and the maximum fan efficiency point move to the cutoff side. Therefore, it is necessary to ensure a predetermined size for the fan diameter D. (For example, in an outdoor unit, it is desirable to be 600 mm or more). For this reason, when trying to increase the value of H / D, the height H of the oblique portion is increased, but the size is increased on the downstream side of the bell mouth 2.
  • the setting conditions H / D ⁇ 0.04, 10 ° ⁇ ⁇ 45 °, L / L 0 ⁇ 0.5
  • the propeller fan 1 and the bell mouth 2 are formed so as to satisfy the parameter).
  • the blower is formed based on the setting conditions including the respective relationships, it is possible to achieve an effect of suppressing an increase in noise and power (fan input).
  • the highest suppression effect on noise and power increase among the conditions is when H / D ⁇ 0.04 is satisfied.
  • the order is 10 ° ⁇ ⁇ 45 ° and L / L 0 ⁇ 0.5. For this reason, even if it is a case where not all the setting conditions can be satisfied, the effect which concerns on this invention can be show
  • FIG. 19 is a perspective view showing another shape of the bell mouth 2 according to the first embodiment.
  • the bell mouth 2 when the diameter of the bell mouth 2 (particularly the blowout opening 5) is longer than at least one of the width and depth of the casing of the outdoor unit, the bell mouth 2 protrudes from the other unit.
  • the bell mouths 2 are in contact with each other, and it may be difficult to install a plurality of outdoor units in close proximity. Therefore, the shape of the bell mouth 2 may be partially changed so that the length of the diameter of the bell mouth 2 is shorter than the width and depth of the casing of the outdoor unit.
  • the oblique portion angle ⁇ is not constant over the entire circumference, but is partially different. Thus, the setting condition is satisfied while preventing the bell mouth 2 from protruding.
  • FIG. 20 and 21 are diagrams illustrating another shape example of the oblique portion 5a of the blower according to the first embodiment.
  • the oblique portion 5a is formed to be a straight line in cross-sectional shape.
  • it may not be straight due to reasons such as manufacturing, design, and dimensional constraints.
  • the angle formed by the straight line connecting both ends of the oblique portion 5a is about 10 ° ⁇ ⁇ 45 °, the same effect as when the oblique portion 5a is a straight line can be exhibited.
  • it can be a concave substantially arc shape shown in FIG. 20, a convex substantially arc shape shown in FIG.
  • FIG. 22 and 23 are diagrams showing the configuration of the top blowing type outdoor unit.
  • FIG. 22 shows an outdoor unit in which the outdoor heat exchanger 104 that performs heat exchange between the refrigerant and air in the housing is arranged in a U-shape.
  • FIG. 23 shows an outdoor unit in which the outdoor heat exchanger 104 is arranged in a V shape and a W shape.
  • the top blowing type outdoor unit has a multi-stage bending arrangement such as a U-shape, a V-shape, and a W-shape. The blower blows air in the direction opposite to the direction of gravity (upward blowing direction).
  • FIG. 24 and FIG. 25 are diagrams showing the configuration of a horizontal blowing type outdoor unit.
  • the blower of the lateral blowing outdoor unit blows out air in a direction perpendicular to the direction of gravity.
  • the outdoor heat exchanger 104 has an L-shaped arrangement in the lateral blow type outdoor unit.
  • the outdoor heat exchanger 104 is arranged by multi-stage bending of the top blowing type as shown in FIG. 23, the heat exchanger is arranged in a V-shape when considered per propeller fan 1 (blower). . At this time, suction is performed on the same two surfaces as the L-shaped arrangement. The two heat exchangers have the same length.
  • the heat exchanger is arranged in an L shape like a side-blowing outdoor unit, the length of the heat exchanger on one suction surface is shortened. For this reason, the V-shaped arrangement in the top-blowing type outdoor unit is easier to secure the mounting capacity of the heat exchanger than the L-shaped arrangement.
  • the top blow type does not have the sheet metal 6 that covers the periphery of the compressor, which flows unevenly near the propeller fan 1 as in the side blow type, and causes large ventilation resistance. It almost coincides with the single unit characteristics.
  • a loss coefficient ⁇ as an index indicating whether the operating point is on the cutoff side or the open side.
  • the operating point is closer to the open side as ⁇ is smaller and closer to the cutoff side as ⁇ is larger.
  • the air blowing resistance of the heat exchanger is generally smaller in the top blowing type outdoor unit than in the side blowing type outdoor unit, so the loss coefficient ⁇ is small, and the operating point is located on the open side. To do. For this reason, in order to bring the minimum specific noise point and the maximum fan efficiency point closer to the operating point, the upper blow type requires a larger fan diameter D than the side blow type. If the fan diameter D cannot be increased due to design restrictions on the outdoor unit size due to the installation area, etc., the operating point is located on the open side of the minimum specific noise point and maximum fan efficiency point, and the specific noise K s Increases and the fan efficiency ⁇ also decreases.
  • the configuration of the present invention for bringing the operating point closer to the minimum specific noise point and the maximum fan efficiency point without increasing the fan diameter D is an upper blow type outdoor unit as compared with a side blow type outdoor unit.
  • the configuration is more necessary, and the effect can be further exhibited.
  • a bell mouth related to the top blowing type for example, a bell mouth having a shape as shown in FIG. 23 can be integrally formed of resin and can be integrally formed regardless of L / L 0 in FIG.
  • a bell mouth is generally manufactured by integrally molding a bell mouth sheet metal 10 as shown in FIG.
  • the blower of the outdoor unit is configured with L / L 0 ⁇ 0.5, 10 ° ⁇ ⁇ 45 °, and H / D ⁇ 0.04 as setting conditions. Therefore, the specific noise and fan efficiency on the open side can be brought close to the minimum specific noise and the maximum fan efficiency without increasing the fan diameter D, and the fan efficiency ⁇ and the specific noise K s are improved. be able to. For this reason, it is possible to reduce fan input and noise.
  • FIG. FIG. 26 is a diagram illustrating the relationship between the shape of the bell mouth 2 and the air flow according to the second embodiment of the present invention.
  • the flow of air is represented by streamlines.
  • the air blown from the blowout opening 5 on the downstream side of the bell mouth 2 flows in an oblique direction along the oblique portion 5a as it is closer to the wall surface of the oblique portion 5a.
  • a plurality of outdoor units such as an air conditioner are installed on the roof of a building, for example, the air blows off in an oblique direction due to the suction force of the propeller fan 1 of the adjacent outdoor unit or the influence of the outside wind.
  • FIG. 27 is a diagram illustrating the shape of the bell mouth 2 and the air flow according to the second embodiment.
  • the downstream outlet portion (terminal portion) of the blowout opening 5 is a straight pipe portion 5b.
  • the oblique portion 5a satisfies the setting condition (parameter) in the first embodiment.
  • the air in the outer peripheral portion flows along the oblique portion 5a and the straight pipe portion 5b and is blown upward (in a direction opposite to the gravitational direction) Short cycles to the unit can be suppressed.
  • a lattice-shaped fan guard that covers the blowout opening 5 may be provided.
  • the fan guard can be easily fixed by setting the end portion downstream of the bell mouth 2 as the straight pipe portion 5b.
  • the straight pipe portion 5b is formed at the outlet (end portion) on the downstream side of the blowout opening 5, so that there is no influence on the adjacent outdoor unit. Since air can be sent out, a short cycle can be suppressed. In addition, the lattice-shaped fan guard can be easily fixed.
  • FIG. 28 is a diagram illustrating the relationship between the bell mouth 2 of the blower and the fan guard 11 installed in the blower according to Embodiment 3 of the present invention.
  • the fan guard 11 covers the blowout opening 5 with a lattice-like mesh, and protects the propeller fan 1, equipment in the outdoor unit housing, and the like.
  • the lattice also has a length in the height direction. For this reason, depending on the angle, the blown out air hits the side surface.
  • an angle formed by the lattice of the fan guard 11 and the fan rotation axis is ⁇ .
  • the angle ⁇ formed by the lattice of the fan guard 11 and the fan rotation axis is 0 °, and is parallel to the rotation axis.
  • FIG. 30 is a diagram illustrating the radius of curvature R of the R portion 3a in the suction opening 3 of the bell mouth 2 according to Embodiment 4 of the present invention.
  • FIG. 30 shows the shapes of the two suction openings 3 having different radii of curvature R.
  • FIG. 31 is a diagram showing the relationship between the PQ characteristic and R / D.
  • the fan diameter D and the fan rotational speed N 0 is constant, while fixing the end position of the suction opening 3 of the bell mouth 2, R when went changing the size of the radius of curvature R of the R portion 3a Based on the value of / D (hereinafter referred to as R / D).
  • R / D the value of / D
  • FIG. 8 with respect to the PQ characteristic, R / D in the air volumes Q 1 and Q 2 is represented.
  • Figure 32 is a graph depicting the relationship of specific noise K s and R / D in the air volume Q 2. Further, FIG. 33 is a graph depicting the relationship of the fan efficiency ⁇ and R / D in the air volume Q 2.
  • Embodiment 5 FIG.
  • the radius of curvature R in the R portion 3a of the suction opening 3 the fan efficiency ⁇ is improved, the specific noise K s is small.
  • the radius of curvature R of the R portion 3a cannot be increased without limitation in the suction opening 3 of the bell mouth 2 due to, for example, size restrictions of the outdoor unit.
  • the curvature radius R of the R portion 3a is generally It gets smaller.
  • the fan center is point O
  • the two points on the outer diameter of the bell mouth 2 are points A and B
  • the point A is fixed
  • the angle between OA and OB is ⁇
  • the curvature radius R is determined over the entire circumference so that the value based on the following equation (3) is maximized.
  • the expression (3) represents an integrated value at the radius of curvature R of the R portion 3 a over the entire circumference of the suction opening 3.
  • FIG. 34 is a configuration diagram of a refrigeration air conditioning apparatus according to Embodiment 6 of the present invention.
  • a refrigeration air conditioner will be described as an example of a refrigeration cycle apparatus having the above-described blower.
  • the refrigerated air conditioner of FIG. 34 includes the outdoor unit (outdoor unit) 100 and the load unit (indoor unit) 200 described in Embodiments 1 to 5, and these are connected by a refrigerant pipe, and are the main refrigerant circuit. (Hereinafter referred to as a main refrigerant circuit) to circulate the refrigerant.
  • a main refrigerant circuit to circulate the refrigerant.
  • a pipe through which a gaseous refrigerant (gas refrigerant) flows is referred to as a gas pipe 300
  • a pipe through which a liquid refrigerant (liquid refrigerant, which may be a gas-liquid two-phase refrigerant) flows is referred to as a liquid pipe 400.
  • the outdoor unit 100 includes a compressor 101, an oil separator 102, a four-way valve 103, an outdoor heat exchanger 104, an outdoor fan 105, an accumulator (gas-liquid separator) 106, and an outdoor throttle device. (Expansion valve) 107, the inter-refrigerant heat exchanger 108, the bypass expansion device 109, and the outdoor side control device 110 (means).
  • Compressor 101 compresses and discharges the sucked refrigerant.
  • the compressor 101 includes an inverter device or the like, and can arbitrarily change the capacity of the compressor 101 (the amount of refrigerant sent out per unit time) by arbitrarily changing the operation frequency.
  • the oil separator 102 separates the lubricating oil discharged from the compressor 101 mixed with the refrigerant.
  • the separated lubricating oil is returned to the compressor 101.
  • the four-way valve 103 switches the refrigerant flow between the cooling operation and the heating operation based on an instruction from the outdoor control device 110.
  • the outdoor heat exchanger 104 performs heat exchange between the refrigerant and air (outdoor air). For example, during the heating operation, it functions as an evaporator, performs heat exchange between the low-pressure refrigerant and air that have flowed in through the outdoor expansion device 107, and evaporates and vaporizes the refrigerant.
  • the outdoor heat exchanger 104 is provided with the outdoor blower 105 serving as the blower described in the first to fifth embodiments in order to efficiently exchange heat between the refrigerant and the air.
  • the rotational speed of the propeller fan 1 may be finely changed by arbitrarily changing the operating frequency of the fan motor by the inverter device.
  • the inter-refrigerant heat exchanger 108 exchanges heat between the refrigerant flowing in the main flow path of the refrigerant circuit and the refrigerant branched from the flow path and adjusted in flow rate by the bypass expansion device 109 (expansion valve). .
  • the bypass expansion device 109 expansion valve
  • the refrigerant is supercooled and supplied to the load unit 200.
  • the liquid flowing through the bypass throttle device 109 is returned to the accumulator 106 through the bypass pipe.
  • the accumulator 106 is means for storing, for example, liquid excess refrigerant.
  • the outdoor side control device 110 is composed of, for example, a microcomputer. It is possible to perform wired or wireless communication with the load-side control device 204.
  • the load unit 200 includes a load side heat exchanger 201, a load side expansion device (expansion valve) 202, a load side blower 203, and a load side control device 204.
  • the load side heat exchanger 201 performs heat exchange between the refrigerant and air. For example, it functions as a condenser during heating operation, performs heat exchange between the refrigerant flowing in from the gas pipe 300 and air, condenses and liquefies the refrigerant (or gas-liquid two-phase), and moves to the liquid pipe 400 side. Spill.
  • the load unit 200 is provided with a load-side blower 203 for adjusting the flow of air for heat exchange.
  • the operating speed of the load-side fan 203 is determined by, for example, user settings.
  • the load side expansion device 202 is provided to adjust the pressure of the refrigerant in the load side heat exchanger 201 by changing the opening degree.
  • the load-side control device 204 is also composed of a microcomputer or the like, and can communicate with the outdoor-side control device 110, for example, by wire or wirelessly. Based on an instruction from the outdoor control device 110 and an instruction from a resident or the like, each device (means) of the load unit 200 is controlled so that the room has a predetermined temperature, for example. Further, a signal including data related to detection by the detection means provided in the load unit 200 is transmitted.
  • the outdoor blower 105 that is the blower described in the first to fifth embodiments is used for the outdoor unit 100 so that air is blown out in the direction opposite to the direction of gravity.
  • the air volume can be increased while realizing low noise, and energy saving of the refrigeration air conditioner (refrigeration cycle apparatus) can be achieved.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

　L'invention porte sur une souffleuse d'air, laquelle souffleuse comporte : un ventilateur à hélice (1) comprenant une ailette convexe (1a) dans l'extrémité périphérique externe d'un côté de surface de pression, et comprenant une pluralité de pales pour créer un écoulement d'air dans la direction opposée à celle de la gravité ; et une embouchure en cloche (2) formant une surface de paroi annulaire dans un côté plus éloigné vers l'extérieur que ne le sont les extrémités périphériques externes des pales du ventilateur à hélice (1). L'embouchure en cloche (2) présente une surface de paroi dans une partie inclinée (5a) qui est une surface inclinée, la paroi étant formée de telle sorte que la trajectoire d'air sur le côté décharge s'élargit, quand le point de fonctionnement du ventilateur à hélice (1) est positionné davantage vers le côté ouvert que ne l'est une zone d'afflux, et l'embouchure en cloche (2) est formée de telle sorte que les relations suivantes sont satisfaites, à titre de conditions : la relation H/D ≥ 0,04 entre la longueur (H) dans la direction d'axe de rotation entre les extrémités terminales du côté admission et du côté décharge de la surface inclinée, et le diamètre de ventilateur (D) du ventilateur à hélice ; la relation 10º < θ ≤ 45º de l'angle (θ) qui est formé, par rapport à l'axe de rotation, par une ligne droite entre les extrémités terminales de la surface inclinée ; et la relation L/L0 ≥ 0,5 entre la longueur L dans la direction d'axe de rotation à partir de la partie ouverte sur le côté admission jusqu'à la partie d'extrémité terminale sur le côté admission de la surface inclinée, et la longueur L0 de chacune des pales du ventilateur à hélice (1) dans la direction d'axe de rotation.
PCT/JP2014/062163 2014-05-02 2014-05-02 Souffleuse d'air, unité extérieure, et dispositif à cycle de réfrigération Ceased WO2015166581A1 (fr)

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PCT/JP2014/062163 WO2015166581A1 (fr) 2014-05-02 2014-05-02 Souffleuse d'air, unité extérieure, et dispositif à cycle de réfrigération

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017145370A1 (fr) * 2016-02-26 2017-08-31 三菱電機株式会社 Dispositif de soufflage
EP3739271A4 (fr) * 2018-02-19 2021-03-17 Daikin Industries, Ltd. Unité de ventilateur et unité extérieure de climatiseur comprenant une unité de ventilateur
CN115654587A (zh) * 2022-10-09 2023-01-31 青岛海信日立空调系统有限公司 一种空调室外机以及空调系统

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04269400A (ja) * 1991-02-22 1992-09-25 Nippondenso Co Ltd 押込式軸流ファン
JP2010236372A (ja) * 2009-03-30 2010-10-21 Daikin Ind Ltd 軸流送風機、空気調和機及び換気扇
JP2012136941A (ja) * 2010-12-24 2012-07-19 Mitsubishi Electric Corp 送風機、室外ユニット及び冷凍サイクル装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04269400A (ja) * 1991-02-22 1992-09-25 Nippondenso Co Ltd 押込式軸流ファン
JP2010236372A (ja) * 2009-03-30 2010-10-21 Daikin Ind Ltd 軸流送風機、空気調和機及び換気扇
JP2012136941A (ja) * 2010-12-24 2012-07-19 Mitsubishi Electric Corp 送風機、室外ユニット及び冷凍サイクル装置

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017145370A1 (fr) * 2016-02-26 2017-08-31 三菱電機株式会社 Dispositif de soufflage
GB2562000A (en) * 2016-02-26 2018-10-31 Mitsubishi Electric Corp Blower Apparatus
JPWO2017145370A1 (ja) * 2016-02-26 2018-11-22 三菱電機株式会社 送風装置
GB2562000B (en) * 2016-02-26 2021-05-19 Mitsubishi Electric Corp Blower Apparatus
EP3739271A4 (fr) * 2018-02-19 2021-03-17 Daikin Industries, Ltd. Unité de ventilateur et unité extérieure de climatiseur comprenant une unité de ventilateur
CN115654587A (zh) * 2022-10-09 2023-01-31 青岛海信日立空调系统有限公司 一种空调室外机以及空调系统

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