JP2007139214A - Fan guard for outdoor unit of air conditioner, and outdoor unit - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce generation of noise by a fan guard even when the flow of air sucked to a blower fan is uneven. <P>SOLUTION: This fan guard 12 has a plurality of radial bridges 20 radially extending from a hub 13 as a center, and an annular bridge 21 extending in the circumferential direction. An inclination angle in the circumferential direction of the radial bridges 20 within a range R1 is approximately agreed with an inclination angle in the circumferential direction of the airflow supplied to the range R1 by the blower fan 7. An inclination angle in the radial direction of the annular bridge 21 in the range R1 is approximately agreed with an inclination angle in the radial direction of the airflow supplied to the range R1 by the blower fan 7. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a fan guard used in an outdoor unit of an air conditioner and attached to a blowout port of a blower fan, and an outdoor unit equipped with the fan guard.

  Some outdoor units of an air conditioner are provided with a blower fan such as an axial fan, and are configured to blow air to a heat exchanger mounted in the outdoor unit. In this type of outdoor unit, a blowout port is formed on the downstream side of the blower fan. A fan guard is attached to the outlet so as to prevent foreign matter from entering. Although there are various types of fan guards, there are known fan guards having a large number of radial ribs arranged radially and a large number of annular ribs arranged concentrically. Yes. Here, in recent years, the amount of air blown to the heat exchanger tends to increase for the purpose of improving the efficiency of the air conditioner. When the air volume increases, noise tends to be generated when the airflow passes through the fan guard. For this reason, the development of a fan guard having a shape that hardly resists airflow has been performed (for example, see Patent Document 1).

For example, in the fan guard disclosed in Patent Document 1, the radial ribs are inclined with respect to the rotation axis of the blower fan. The inclination angle is gradually changed in the radial direction of the fan guard so as to correspond to the inclination angle of the airflow blown from the fan. Since the inclination angle of the air flow blown out from the blower fan easily matches the inclination angle of the radial rib, interference between the air flow and the radial rib is suppressed, and noise and pressure loss are easily reduced.
JP 2004-156883 A

However, the conventional fan guard reduces noise when the heat exchanger is arranged in parallel with the blower fan and the speed of the air flow and the blowing angle are symmetric about the rotation axis of the blower fan. However, depending on the configuration of the outdoor unit, the air flow sucked into the blower fan may not be symmetric with respect to the rotation axis. In this case, since the blowing angle of the air flow blown from the blower fan is not axisymmetric, the flow of the air flow and the inclination angle of the fan guard are inconsistent, and noise and pressure loss increase. In particular, when the wind flow is increased, such as at the start of operation or during high load operation, the asymmetry of the air flow becomes prominent. It was increasing.
The present invention has been made in view of such circumstances, and its main object is to reduce the generation of noise by the fan guard even when the flow of air sucked into the blower fan is uneven. .

  The present invention for solving the above-mentioned problems has a plurality of first bars extending radially with respect to the central part and a plurality of second bars connected to the first bars and extending in the circumferential direction. In the fan guard attached to the air outlet that blows out the air flow from the outdoor unit of the air conditioner with built-in, at least a part of the first crosspiece corresponds to the arrangement of the air suction port formed in the outdoor unit The second beam is inclined so as to be substantially parallel to the direction of the airflow blown from the blowout port in the circumferential direction, and to be substantially parallel to the direction of the airflow blown from the blowout port in the radial direction. A fan guard for an outdoor unit of an air conditioner characterized by being inclined to

  In the fan guard for the outdoor unit of this air conditioner, when the blowing angle in the circumferential direction of the air flow blown out from the blower fan differs depending on the place in the circumferential direction, it is parallel to such blowing angle depending on the arrangement of the suction ports. Since the inclination angle of the first crosspiece is inclined so that the air flow and the first crosspiece are not interfered with each other. In addition, since the second rail is inclined in the radial direction, interference with the airflow is also suppressed in the radial direction of the fan guard.

  According to the present invention, by optimizing the inclination angle of the first rail and the inclination angle of the second rail so as to correspond to the flow of the air flow of the outdoor unit, Since interference with the first and second rails is suppressed, noise and pressure loss are reduced. As a result, a quiet outdoor unit with a small blowing sound can be obtained, and power consumption can be reduced.

The best mode for carrying out the invention will be described in detail with reference to the drawings.
(First embodiment)
1 and 2 show the configuration of an outdoor unit equipped with a fan guard according to the present embodiment. The outdoor unit 1 is pipe-connected to an indoor unit (not shown) and constitutes an air conditioner. In the outdoor unit 1, the inside of the cabinet 2 is divided into a blower chamber 4 and a machine chamber 5 by a partition plate 3, and a heat exchanger 6 and a blower fan 7 are disposed in the blower chamber 4. .

  A large number of suction ports 10 are formed in the back surface portion 2A of the cabinet 2 and the first side surface portion 2B which is one side surface portion. The machine room 5 is formed in a space partitioned by the partition plate 3 on the second side surface portion 2C side which is the other side surface portion of the cabinet 2, and accommodates a compressor, various electric components, and the like. Yes. The suction port 10 is not formed in the second side surface portion 2 </ b> C and the partition plate 3. An end portion 3A of the partition plate 3 fixed to the back surface portion 2A side of the cabinet 2 is gently curved so as to open toward the second side surface portion 2C. The heat exchanger 6 is bent into a substantially L shape in plan view so as to extend from the first side surface portion 2B of the cabinet 2 to the back surface portion 2A. The end portion of the heat exchanger 6 enters the portion where the blower chamber 4 is widened because the end portion 3A of the partition plate 3 is curved.

  The blower fan 7 includes a wing 7A and a motor 7B that rotates the wing 7A. The motor 7 </ b> B is supported by a bracket (not shown) on the front surface portion 2 </ b> D side facing the back surface portion 2 </ b> A of the cabinet 2 at the center of the blower chamber 4. The axis C1 of the blower fan 7 is orthogonal to the back surface portion 2A of the cabinet 2 and is parallel to the side surface portions 2B and 2C, and is disposed horizontally in this embodiment. For this reason, such a ventilation fan 7 may be called a horizontal blowing type ventilation fan. In addition, as shown in FIG. 1, the rotation direction of this ventilation fan 7 is a direction shown by arrow C2.

  A blowout port 11 is formed in the front surface portion 2D of the cabinet 2. A fan guard 12 is attached to the outlet 11. The fan guard 12 has an outer diameter that can be attached to the air outlet 11, and a circular hub (center portion) 13 is provided at the center. The fan guard 12 has a plurality of radial bars (first bars) 20 extending radially from the hub 13, and the plurality of radial bars 20 are circular or circular circular bars (second bars) in the circumferential direction. ) 21. In FIG. 1, the radial beam 20 has a radial beam extending from the hub 13 to the outer edge portion of the fan guard 12, and has a length that bisects the radial direction, and each radial beam is arranged so as to be shifted in the circumferential direction. Although it has a radial crosspiece, the arrangement and the length of the radial crosspiece 20 are not limited to this.

  Here, the radial crosspiece 20 is inclined so as to be parallel to the air flow blown from the blower fan 7. For example, as shown in FIG. 4, in a range R1 including a radial bar 20A extending in a direction orthogonal to the second side surface portion 2C (or the partition plate 3) as viewed in the direction of the axis C1, the circumferential direction of the radial bar 20A The inclination angle is constant at a large angle. Further, in the range R2 including the radial bars 20B extending in a direction orthogonal to the upper surface portion 2E of the cabinet 2 as viewed in the direction of the axis C1, the circumferential inclination angle of the radial bars 20B is constant at an angle smaller than the range R1. ing. Similarly, the range R3 including the radial bars 20C extending in a direction orthogonal to the lower surface portion 2F of the cabinet 2 is constant at substantially the same inclination angle as the same range R2. The upper surface portion 2E and the lower surface portion 2F of the cabinet 2 are side surface portions that are parallel to the axis C1 and do not have the suction port 10.

  The inclination angle of the radial beam 20 in each range between the range R1 and the range R2 and between the range R1 and the range R3 is an intermediate inclination angle between the inclination angle of the radial beam 20A and the inclination angle of the radial beam 20B. In the remaining range (on the first side face 2B side, between the range R3 and the range R2 in the circumferential direction), the inclination angle of the radial rail 20 is larger than the range R2 and the range R3 and smaller than the range R1.

The range R1 is an area where the extended line of the radial beam 20A intersects the partition plate 3 and the second side surface portion 2C, includes the radial beam 20A, and is an angle indicated by N × 360 × H / Q × A at the maximum in the circumferential direction. (°) region. Here, N is the rotational speed (rps) of the blower fan 7, H is the height of the blower fan 7 (m, see FIG. 2), Q is the air volume (m ³ / s), and A is the fan flow path area (m ^2). ). Note that including the radial beam 20A may be the range R1 in the rotation direction C2 of the blower fan 7 starting from the radial beam 20A, or the range R1 in the direction opposite to the rotation direction C2 of the blower fan starting from the radial beam 20A. The range R1 may be set between them. More preferably, the range R1 can be set to a range of 0 to 45 ° in the rotational direction of the blower fan 7 including the radial crosspiece 20A.

  Ranges R2 and R3 are regions where the extended lines of the radial rails 20 do not intersect with the partition plate 3 and the second side surface portion 2C, that is, regions where the upper surface portion 2E and the lower surface portion 2F intersect, and include the radial rails 20B and 20C, respectively. This is a region having an angle (°) indicated by N × 360 × H / Q × A at the maximum in the circumferential direction. Note that each of the radial bars 20B and 20C includes, for example, the range R2 from the radial bar 20B as the starting point to the range R2 in the rotational direction C2 of the blower fan 7, and the radial fan 20B as the starting point. The direction of rotation C2 is meant to include all regions between the range R2 in the opposite direction. More preferably, the range R2 can be set to a range of 0 to 45 ° in the rotation direction of the blower fan 7 including the radial bars 20B and 20C.

  As shown in FIG. 4, the cross section of the radial crosspiece 20 </ b> A in the range R <b> 1 has an inclination angle α <b> 1 with respect to the axis line (horizontal direction) C <b> 1 of the blower fan 7. As shown in FIG. 5, the cross sections of the radial bars 20 </ b> B and 20 </ b> C in the ranges R <b> 2 and R <b> 3 have an inclination angle β <b> 1 with respect to the axis C <b> 1 of the blower fan 7. The inclination angle α1 is larger than the inclination angle β1. In the range R4, the inclination angle of the radial beam 20 changes from the inclination angle α1 of the radial beam 20A in the range R1 to the inclination angle β1 of the radial beams 20B and 20C in the ranges R2 and R3. As a method of changing the inclination angle of the range R4, it may be gradually changed one by one or may be changed stepwise for each of the plurality of radial bars 20.

  The relationship between the inclination angles α1, β1 and the airflow blowing angle will be described with reference to FIGS. 6 to 8, suction speeds Vin1, Vin2, and Vin3 are vectors indicating the wind speed and direction of the air flow sucked into the blower fan 7. The blowing speeds Vout1, Vout2, and Vout3 are vectors indicating the wind speed and direction of the airflow blown from the blower fan 7.

  The suction speed Vin1 and the blowout speed Vout1 shown in FIG. 6 are within the range R1. In this range R1, since the partition plate 3 is close to the blower fan 7, the suction of the blower fan 7 is hindered and the air volume is slightly small, so the suction speed Vin1 is small. The direction of the suction speed Vin1 is parallel to the axis C1 of the blower fan 7. The blowing speed Vout1 is a combination of the suction speed Vin1 and the rotational speed Vf of the blower fan 7. The inclination angle α1 is determined so that the blowing speed Vout1 substantially coincides with the angle θ1 formed with the axis C1.

  The suction speed Vin2 and the blowing speed Vout2 shown in FIG. 7 are within the range R2. Since the airflow flowing through the range R2 is larger than the range R1, the suction speed Vin1 is larger than the suction speed Vin1. The direction of the suction speed Vin2 is substantially parallel to the axis C1 of the blower fan 7. The blowing speed Vout2 is a combination of the suction speed Vin2 and the rotational speed Vf of the blower fan 7. The inclination angle β1 is determined so that the blowing speed Vout2 substantially coincides with the angle θ2 formed with the axis C1.

  Similarly, the suction speed Vin3 and the blowing speed Vout3 shown in FIG. 8 are within the range R3. The component (Vin3 ′) in the direction of the axis C1 of the air flow flowing through the range R3 is a pre-swirl flow due to the influence of the air flow blown from the side surface portion 2B, and thus is smaller than the blowing speed Vin2, but the rotational speed Vf Since ′ (= Vf−Vin3 ″) is also reduced, the direction of the blowing speed Vout3 is substantially equal to the angle θ2. For this reason, the inclination angle of the range R3 is β1. The inclination angles α1 and β1 are determined based on the case where the rotational speed of the blower fan 7 is high and the air volume is large. This is because noise and pressure loss at this time tend to increase.

  As shown in FIG. 9, the annular crosspiece 21 is inclined so as to open outward. The inclination angles γ1, γ2, and γ3 with respect to the direction of the axis C1 are small on the inner peripheral side near the hub 13 and larger on the outer peripheral side. The inclination angles γ1, γ2, and γ3 are in the range of 5 to 25 °. In FIG. 9, the inclination angle γ1, the inclination angle γ2, and the inclination angle γ3 are set for each of the four annular bars 21. The inclination angles γ1, γ2, and γ3 of the annular bars may be changed one by one. In this case, the inclination angle gradually changes from γ1 to γ3. The reason why the annular crosspiece 21 is inclined in this way is that the airflow is once throttled at the outlet 11 and then flows so as to be released to the outside, so that the airflow is inclined outward in the radial direction of the fan guard 12. This is because the angle of inclination is larger toward the outer periphery of the fan guard 12. That is, the inclination angles γ1, γ2, and γ3 are determined so as to be substantially parallel to the radial blow-out angle of the air flow that varies from place to place in the radial direction.

Next, the operation of this embodiment will be described.
When the air conditioner is operated, the blower fan 7 rotates. Air is sucked into the cabinet 2 from the respective inlets 10 of the back surface portion 2 </ b> A and the first side surface portion 2 </ b> B of the cabinet 2 by the suction force of the blower fan 7. Air is blown out from the outlet 11 through the heat exchanger 6. The suction port 10 is formed in the back surface portion 2A and the first side surface portion 2B of the cabinet 2, and further, since the partition plate 3 is close to the suction port 10, as shown in FIG. The air volume is reduced, and the air volume on the first side surface portion 2B side is relatively increased. In the region on the side of the partition plate 3, the blower fan 7 blows out from the blower fan 7 while being swung in the rotation direction by a range R <b> 1 at the maximum from the suction position into the blower fan 7 by the rotation of the blower fan 7. Since the circumferential angle θ1 of the blowing speed Vout1 at this time is substantially equal to the circumferential inclination angle α1 of the radial beam 20A, the air flow is discharged with little interference with the radial beam 20B in the circumferential direction. The air flow is blown out while inclining also in the radial direction of the fan guard 12. However, since the annular crosspiece 21 is inclined so as to open outward in accordance with the blowing angle of the air flow, the air flow is in the radial direction. It is discharged almost without interfering with the annular crosspiece 21.

  Further, the air flow sucked into the blower fan 7 through the upper region of the blower fan 7 is blown out from the blower fan 7 while being swung in the rotation direction by the range R2 at the maximum by the rotation of the blower fan 7. Since the circumferential inclination angle β1 of the radial beam 20B is substantially equal to the angle θ2 of the blowing speed Vout2 at this time, the air flow is discharged with almost no interference with the radial beam 20B. Similarly, the airflow blown into the blower fan 7 through the lower region of the blower fan 7 is blown out from the blower fan 7 while being swung in the rotation direction by the range R2 at the maximum by the rotation of the blower fan 7. . At this time, since the angle θ3 of the blowing speed Vout3 and the circumferential inclination angle β1 of the radial beam 20B are substantially equal, the air flow is discharged with almost no interference with the radial beam 20B.

  Between the range R1 and the ranges R2 and R3, the blowing angle of the airflow blown from the blower fan 7 takes a value between the respective angles of the blowing speeds Vout1 and Vout2 between the range R1 and the range R2. Since the inclination angle of the radial crosspiece 20 in this range is also inclined in the circumferential direction in accordance with this, the air flow is discharged without almost interfering with the radial crosspiece 20. About a radial direction, it discharges, hardly interfering with the annular crosspiece 21 similarly to the above.

  In this embodiment, in the configuration in which the outdoor unit 1 is biased toward the partition plate 3 and the air flows, the inclination angle α1 of the radial beam 20A in the range R1 on the partition plate 3 side is set to the inclination angle of the radial beam 20B near the vertical direction. Since it is set to be larger than β1 and is substantially parallel to the airflow passing through the range R1 in the circumferential direction, interference between the radial beam 20A and the airflow can be suppressed. Further, in the vertical range R2 that is not orthogonal to the first side surface 2B and the partition plate 3, the inclination angle β1 of the radial crosspiece 20B is set to be small, and the airflow passing through the range R2 is set in the circumferential direction. Since it is made substantially parallel, interference with the radial crosspiece 20B and an airflow can be suppressed. Between the range R1 and the ranges R2 and R3, the portion close to the partition plate 3 has the inclination angle of the radial beam 20 set to an intermediate angle between the range R1 and the ranges R2 and R3. Interference with 20 can be suppressed. From these things, generation | occurrence | production of noise and generation | occurrence | production of pressure loss can be prevented. In addition, since the annular crosspiece 21 is inclined so as to open outward and is made substantially parallel to the radial blowout direction of the airflow, interference between the annular crosspiece 21 and the airflow is suppressed, noise, etc. Occurrence is prevented. The air volume also changes depending on the rotational speed of the blower fan 7, and the rotational speed increases at the time of high load or at the start of operation. Thus, when the rotational speed is increasing, noise and pressure loss generated can be particularly reduced.

  Here, the measurement results of the power consumption and the blowing sound when the conventional fan guard is attached and when the fan guard 12 of the present embodiment is attached are shown in FIGS. Compared with the conventional fan guard shown by the broken line in FIGS. 10 and 11, the fan guard 12 of the present embodiment shown by the solid line consumes less power and the blowing sound is lower. That is, when this fan guard 12 is used, the power loss can be reduced by reducing the pressure loss. Furthermore, the quiet outdoor unit 1 with a small blowing sound can be obtained.

(Second embodiment)
12 and 13 show an outdoor unit equipped with a fan guard according to the second embodiment. In addition, the description which overlaps with a 1st form is abbreviate | omitted.
The outdoor unit 51 has a hollow cabinet 52. A large number of suction ports 60 are formed in the three side surfaces 52A, 52B, and 52C of the cabinet 52. A heat exchanger 56 is bent and arranged along the side surfaces 52A, 52B, and 52C on the inner side of these side surfaces 52A, 52B, and 52C. The end portion of the heat exchanger 56 does not reach the side surface portion (first side surface portion) 52D that does not have the suction port 60. Further, the height of the heat exchanger 56 is lower than the height of the cabinet 52. A blowout port 61 is formed at substantially the center of the ceiling surface 52E of the cabinet 52, and a motor 57B of the blower fan 57 is fixed by a bracket (not shown) so that the wings 57A face the blowout port 61. The blower fan 57 is fixed so that the axis C3 coincides with the vertical direction of the cabinet 52 and is parallel to each of the side surfaces 52A, 52B, 52C, 52D. A fan guard 62 is attached to the outlet 61. A machine room (not shown) is disposed on the bottom surface portion 52F of the cabinet 52.

  In the outdoor unit 51, the air volume is the largest in the range R11 close to the side surface portion 52D where the suction port 60 is not formed, and the air volume decreases as it deviates in the circumferential direction from here, and the side surface portion 52A side facing the side surface portion 52D. The air volume is the smallest in the region R12. Accordingly, the range R11 has a relatively small circumferential component and a large upward velocity component because the air flows from the three side surfaces 52A, 52B, and 52C merge, so the upward velocity component becomes large. The inclination angle becomes smaller. In the range R13 in the vicinity of the two side surface portions 52B and 52C substantially orthogonal to the side surface portion 52D, the upward velocity component of the air flow is smaller than the range R11. Therefore, the inclination angle of the blowing speed with respect to the axis C3 is within the range R11. It becomes larger than the inclination angle. The blowing speed in the range R12 has the largest inclination angle since the circumferential speed component is dominant. In addition, each range R11, R12, R13 is only an angle (°) of N × 360 × H / Q × A at the maximum with respect to the suction side by the rotation of the blower fan 7 as in the first embodiment. The position is preferably shifted in the rotational direction of the blower fan 7. More preferably, the position may be shifted by 0 to 45 ° from the position orthogonal to each of the side surfaces 52A, 52B, 52C, and 52D. Note that such a blower fan 57 may be referred to as a top blower type blower.

  The fan guard 62 has a plurality of radial bars (first bars) 70 extending from the hub (center part) 63, and these radial bars 70 are connected by an arc-shaped or annular ring-shaped bar (second bar) 71. ing. The radial crosspiece 70 in the range R11 has an inclination angle α2 as shown in FIG. The radial crosspiece 70 in the range R13 has an inclination angle β2 as shown in FIG. The radial crosspiece 70 in the range R12 has an inclination angle ε2 as shown in FIG. These inclination angles α2, β2, and ε2 are approximately equal to the inclination angles of the blowing speeds of the respective airflows in the ranges R11, R12, and R13 when the blower fan 57 is operated at the highest load. In addition, the inclination angle of the radial beam 70 between the range R11 and the range R13, and between the range R12 and the range R13 is gradually changed one by one or every plurality. As in the first embodiment, the annular crosspiece 71 is inclined so as to open upward.

The operation of this embodiment will be described.
When the air conditioner is operated, the blower fan 57 rotates. Air is sucked into the cabinet 52 from the respective inlets 60 of the three side surfaces 52A, 52B, 52C by the suction force of the blower fan 57. The air is blown out from the outlet 61 through the heat exchanger 56. As shown in FIG. 12, the air volume in the region R <b> 11 near the side surface portion 52 </ b> D where the suction port 60 is not formed increases, and the airflow here is blown out from the blowout port 61 by the rotation of the blower fan 57. At this time, the air is blown out while being swung in the rotation direction C4 by an angle (°) of N × 360 × H / Q × A at the maximum from the suction position into the blower fan 57. Since the circumferential inclination angle of the radial beam 70 is substantially equal to the blowing angle in the circumferential direction of the air flow at this time, the air flow is discharged with almost no interference with the radial beam 70 in the circumferential direction. Further, due to the radial inclination of the annular crosspiece 71, the air flow is discharged with little interference with the annular crosspiece 71 in the radial direction.

  Further, the air flow sucked into the blower fan 52 through the regions in the vicinity of the side portions 52A, 52B, and 52C and blown out from the ranges R12 and R13 has a circumferential blowing angle in the circumferential direction of the radial beam 70. Since the inclination angles β2 and ε2 are approximately equal to each other, the air flow is discharged with almost no interference with the radial beam. Also in the range between the ranges R11 to R13, since the circumferential inclination angle of each radial crosspiece 70 is substantially equal to the circumferential inclination angle of the air flow, there is almost no interference. Then, in the radial direction, the radial inclination angle of the annular crosspiece 71 is substantially equal to the blowing angle in the radial direction of the air flow, and therefore, it is discharged with almost no interference.

  In this embodiment, the suction port 60 is formed in the three side surfaces 52A, 52B, and 52C, so that the air flow sucked into the blower fan 57 is different for each location, and the radial crosspiece 70 in the region R11 is different. The inclination angle α2 is made smaller than the inclination angle β2 of the radial beam 70 in the region R13 so as to be substantially parallel to the flow of the air flow blown into these ranges R11 and R13. Interference with 70 can be suppressed. In addition, since the inclination angle ε2 of the radial crosspiece 70 in the region R12 is maximized so as to be substantially parallel to the flow of the air flow blown into the range R12, in the region where the circumferential velocity component is dominant. Interference between the radial beam 70 and the airflow can be suppressed. From these things, generation | occurrence | production of noise and generation | occurrence | production of pressure loss can be prevented. In addition, since the annular crosspiece 71 is inclined so as to open outward so as to be substantially parallel to the blowing direction in the radial direction of the airflow, interference between the annular crosspiece 71 and the airflow is suppressed, noise, etc. Is prevented from occurring.

Note that the present invention can be widely applied without being limited to the above-described embodiment.
For example, the arrangement of the machine room 5 and the arrangement of the suction ports 10 and 60 and the heat exchangers 6 and 56 are not limited to those described above, and may be an arrangement in which the air flow sucked into the blower fans 7 and 57 is biased. It ’s fine. In these configurations, the radial bars 20 and 70 having the optimum inclination angle are used in accordance with the air volume in the directions of the axes C1 and C3 and the speed component in the circumferential direction.
The circular bars 21 and 71 may be arc-shaped bars that are partially cut off in the circumferential direction.
In the first embodiment, the range R3 may be smaller than the range R2. In the range R2, the air flow and the axis C1 of the blower fan 7 substantially coincide with each other, whereas in the range R3, the air flow and the axis C1 of the blower fan 7 do not coincide with each other. And the rotational direction C2 of the blower fan 7 are reversed, and the movement amount of the air flow moved in the circumferential direction while passing through the blower fan 7 is reduced, so that the range R3 can be narrowed. is there.
The side surface portions 2B, 2C, 52A, 52B, 52C, the upper surface portion 2E, and the lower surface portion 2F, which are the side surface portions, may be substantially parallel to the axes C1 and C3, and a part thereof may be curved or the like. It is good also considering the partition plate 3 as a side part.

It is the fan guard and outdoor unit which concern on embodiment of this invention. It is sectional drawing along the AA line of FIG. It is a figure explaining a range. It is sectional drawing along the BB line of FIG. It is sectional drawing along the CC line of FIG. It is sectional drawing along the DD line of FIG. 1, Comprising: It is a figure which shows the relationship between a part of fan wing | blade and airflow in the range R1. It is sectional drawing of the same position as FIG. 6 in the range R2, and is a figure which shows a part of fan blade | wing body and the relationship of an air flow. It is sectional drawing of the same position as FIG. 6 in range R3, and is a figure which shows a part of fan blade | wing body and the relationship of an air flow. It is sectional drawing along the EE line of FIG. It is a figure which compares power consumption. It is a figure which compares ventilation sound. It is sectional drawing of the fan guard and outdoor unit which concern on embodiment of this invention. It is F arrow line view of FIG. It is sectional drawing along the GG line of FIG. It is sectional drawing along the II line | wire of FIG. It is sectional drawing along the JJ line of FIG.

Explanation of symbols

1,51 Outdoor unit 2B, 52D 1st side surface part 2C 2nd side surface part 7,57 Blower fan 10,60 Inlet port 11,61 Outlet port 12,62 Fan guard 13,63 Hub (central part)
20,70 Radial beam (first beam)
21,71 Annular cross (second cross)
52A, 52B, 52C Side part α1, α2, β1, β2, γ1, γ2, γ3, ε2 Inclination angle

Claims (12)

Air from an outdoor unit of an air conditioner having a plurality of first bars extending radially with respect to the center and a second bar connected to the first bars and extending in the circumferential direction. In the fan guard attached to the outlet that blows out the flow,
At least a part of the first crosspiece is inclined so as to be substantially parallel to the direction of the airflow blown out from the blowout port corresponding to the arrangement of the air suction port formed in the outdoor unit. A fan guard for an outdoor unit of an air conditioner, wherein the second beam is inclined so as to be substantially parallel in the radial direction to the direction of the airflow blown from the blowout port.   The second side surface portion facing the first side surface portion corresponding to the suction port formed only in the first side surface portion among the side surface portions of the outdoor unit substantially parallel to the axis of the blower fan. 2. The air conditioner according to claim 1, wherein an inclination angle of at least a part of the first rail extending in the direction with respect to an axis of the blower fan is larger than an inclination angle of the other first rail. Fan guard for outdoor units.   The first crosspiece that includes substantially the first crosspiece orthogonal to the second side surface portion and has a large inclination angle of the first crosspiece is in a range of 0 to 45 ° in the circumferential direction. The fan guard for an outdoor unit of an air conditioner according to claim 2, wherein the inclination angle of the crosspiece is constant.   At least a part of the first beam extending in a direction not intersecting the first side surface part is the first beam extending at an inclination angle with respect to the axis of the blower fan in the direction of the second side surface part. 3. The fan guard for an outdoor unit of an air conditioner according to claim 2, wherein the fan guard is smaller than one having an increased inclination angle.   Including the first crosspiece substantially parallel to the first side surface portion, a range of 0 to 45 ° in the circumferential direction is a range in which the inclination angle of the first crosspiece is small, and the first crosspiece is within this range. 5. The fan guard for an outdoor unit of an air conditioner according to claim 4, wherein the inclination angle of the crosspiece is constant.   The fan guard for an outdoor unit of an air conditioner according to claim 2 or 4, wherein an inclination angle of at least a part of the first crosspiece is changed along a circumferential direction.   Of the side surface portions of the outdoor unit substantially parallel to the axis of the blower fan, the suction port is not formed in the first side surface portion, but the suction port is formed in each of the other three side surface portions. Corresponding to the outdoor unit, at least a part of the first bar extending from the central portion toward the first side surface portion has an inclination angle with respect to the axis of the blower fan other than the first The fan guard for an outdoor unit of an air conditioner according to claim 1, wherein the fan guard is smaller than an inclination angle of the crosspiece.   At least a part of the first beam extending in a direction not intersecting with the first side surface part is an inclination angle of the first beam whose inclination angle with respect to the axis of the blower fan is directed toward the first side surface part. The fan guard for an outdoor unit of an air conditioner according to claim 7, wherein the fan guard is larger than a smaller one.   8. The first crosspieces including the first crosspieces that are substantially orthogonal to the side surface portions, respectively, wherein the inclination angle of the first crosspieces in the range of 0 to 45 ° in the circumferential direction is made constant. Or the fan guard for the outdoor units of the air conditioner according to claim 8.   The second crosspiece is inclined so as to open from the inside to the outside of the outdoor unit, and the inclination angle is within a range of 5 to 25 ° with respect to the axis of the blower fan. The fan guard for an outdoor unit of an air conditioner according to any one of claims 1 to 9.   11. The outdoor unit of an air conditioner according to claim 10, wherein an inclination angle of the second beam on the inner peripheral side close to the central portion is smaller than an inclination angle of the second beam on the outer peripheral side. Fan guard. The outdoor unit equipped with the fan guard for outdoor units of the air conditioner as described in any one of Claims 1-11.

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