JP2012251494A - Air blower - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an air blower which can suppress weight increase caused by a weight.SOLUTION: The air blower comprises: fans 1, 2 which impart motion amounts to air by rotation; a shaft 32 being a rotating shaft of the fans 1, 2; a bearing 314 which supports the shaft 32 outside the fans 1, 2; and a weight 61 which can move in rotational directions of the fans 1, 2. The weight 61 is located at the opposite side of the bearing 314 rather than ends 13, 22 at the side of the bearing 314 out of the fans 1, 2. For example, the fans 1, 2 have a boss 24 connected with the shaft 32, and the weight 61 is arranged at the boss 24.

Description

  The present invention relates to a blower including a weight for balance adjustment.

  Conventional blowers perform balance adjustment by adding a balance weight to the fan (plus balance adjustment) or removing excess weight (minus balance adjustment) in order to cancel vibrations of the fan and motor that are rotating bodies. It was. For example, Patent Literature 1 describes a centrifugal blower that adjusts minus balance.

  On the other hand, Patent Document 2 describes an electric blower that automatically adjusts the balance by disposing a weight so as to be movable between a fan and a washer that fixes the fan.

JP 2009-30588 A Japanese Patent Laid-Open No. 2005-94983

  According to the prior art of Patent Document 2, there is an advantage that the labor for balance adjustment in the manufacturing process is reduced. However, since the weight of the rotating body is increased by the weight, there is a problem that the efficiency of the blower is deteriorated.

  An object of this invention is to provide the air blower which can suppress the weight increase by a weight in view of the said point.

In order to achieve the above object, in the invention according to claim 1, the fans (1, 2) that give the momentum to the air by rotating,
A shaft (32) serving as a rotation axis of the fans (1, 2);
A bearing (314) that supports the shaft (32) outside the fans (1, 2);
A weight (61, 63, 65) movable in the rotation direction of the fans (1, 2),
The weights (61, 63, 65) are located on the opposite side of the bearing (314) from the ends (13, 22) of the fan (1, 2) on the bearing (314) side. .

  According to this, from the bearing (314) to the weight (61, 63, 65) compared with the case where the weight (61, 63, 65) is located between the fan (1, 2) and the bearing (314). Therefore, the balance adjustment effect by the weights (61, 63, 65) can be effectively exhibited. For this reason, the weight increase by a weight (61, 63, 65) can be suppressed.

In the invention of claim 2, in the invention of claim 1, the fans (1, 2) have a boss (24) to which the shaft (32) is coupled,
The weights (61, 63) are provided on the boss (24).

  Here, “the weight is provided on the boss” in the present invention does not only mean that the weight is provided on the boss itself, but also includes that the weight is provided in the vicinity of the boss. belongs to.

  According to this, since the weights (61, 63) are provided in a region where the air flow is relatively weak, the weights (61, 63) disturb the air flow by the fans (1, 2) and blow noise. Can be prevented from increasing.

  The invention according to claim 3 is characterized in that, in the invention according to claim 1, the weights (61, 63, 65) are arranged on the opposite side of the bearing (314) with the fan (2) interposed therebetween. And

  Thereby, since the distance from a bearing (314) to a weight (61, 63, 65) can be taken still larger, the weight increase by a weight (61, 63, 65) can be suppressed further.

According to a fourth aspect of the present invention, in the first or second aspect of the present invention, the fan (1) includes a plurality of blade portions (11) and a main plate (13) connecting the blade portions (11). A centrifugal multiblade fan having
The weights (61, 63, 65) are arranged inside the fan (1).

  Thereby, the weights (61, 63, 65) can be efficiently arranged.

  The invention according to claim 5 is characterized in that, in the invention according to claim 4, the weights (61, 63) are accommodated in a groove formed in the main plate (13).

  Thereby, the weights (61, 63) can be arranged more efficiently.

The invention according to claim 6 is the invention according to claim 4, further comprising a weight accommodating portion (62, 64) for accommodating the weight (61, 63),
The weight housing parts (62, 64) are characterized by protruding from the main plate (13) toward the air suction side of the fan (1).

  Accordingly, it is possible to suppress the weights (61, 63) from disturbing the air flow by the fan (1) and increasing the blowing noise, and to effectively utilize the space inside the fan to reduce the weight (61, 63). 63) can be arranged efficiently.

  The invention described in claim 7 is characterized in that, in the invention described in claim 6, the weight accommodating portion (62) is tapered toward the air suction side of the fan (1).

  Thereby, the flow of air by the fan (1) can be adjusted by the weight accommodating part (62), and blowing noise can be suppressed.

In the invention according to claim 8, in the invention according to claim 1, the fan (1) includes a plurality of blade portions (11) disposed around the rotation shaft and the plurality of blade portions. A centrifugal multiblade fan having a side plate (12) connecting (11) from a radially outer side of the fan (1);
The weight (61) is housed in a groove formed in the side plate (12).

  According to this, since the weight (61) is provided in a region where the air flow is relatively weak, it is possible to prevent the weight (61) from disturbing the air flow by the fan (1) and increasing the blowing noise. can do.

According to a ninth aspect of the invention, in the first aspect of the invention, the fan (1, 2) connects a plurality of blade portions (11, 21) and the blade portions (11, 21). A centrifugal multiblade fan having a main plate (13, 23);
The weight (65) is slidable in a groove (64) formed in the main plate (13, 23).

  According to this, since the weight (65) is provided in a region where the air flow is relatively weak, the weight (65) disturbs the air flow by the fans (1, 2) and increases the blowing noise. Can be suppressed.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

It is sectional drawing which shows the air blower in 1st Embodiment. It is AA sectional drawing of FIG. FIG. 3 shows the configuration of the blower of FIG. 1 with a simple model. It is a graph which shows the vibration reduction effect by 1st Embodiment. It is sectional drawing which shows the air blower in 2nd Embodiment. It is sectional drawing which shows the air blower in 3rd Embodiment. It is sectional drawing which shows the air blower in 4th Embodiment. It is sectional drawing which shows the air blower in 5th Embodiment. It is sectional drawing which shows the air blower in 6th Embodiment. It is sectional drawing etc. which show the air blower in 7th Embodiment.

(First embodiment)
Hereinafter, the first embodiment will be described. The blower shown in FIG. 1 is used in an indoor unit (not shown) of a vehicle air conditioner, sucks outside air and inside air introduced by an inside / outside air switching box of the indoor unit, and uses the sucked air as an air conditioning unit of the indoor unit. Vent toward The up and down arrows shown in FIG. 1 indicate directions in the vehicle mounted state.

  The blower is an internal / external air two-layer blower that can inhale and suck both vehicle exterior air (outside air) and vehicle interior air (inside air), and includes a first fan 1, a second fan 2, an electric motor 3, and a casing 4. Etc.

  The first fan 1 and the second fan 2 are centrifugal multiblade fans that are driven to rotate by the electric motor 3 and blow out air in the centrifugal direction. The first fan 1 and the second fan 2 are arranged coaxially. In the vehicle mounted state of the blower, the first fan 1 is located above the second fan 2. In this example, the first fan 1 and the second fan 2 are integrally formed of resin.

  The electric motor 3 includes a motor main body 31 and a shaft 32 protruding from the motor main body 31. The shaft 32 forms a rotation axis of the first fan 1 and the second fan 2, and extends in the vertical direction when the blower is mounted on the vehicle. The motor main body 31 is located below the first fan 1 and the second fan 2 when the blower is mounted on the vehicle.

  The casing 4 has a first scroll part 41 that houses the first fan 1, a second scroll part 42 that houses the second fan 2, and a motor housing part 43 that houses the motor body 31 of the electric motor 3. is doing.

  The first scroll portion 41 is formed with a first suction port 411 that opens toward one end side in the fan axial direction (opposite side of the electric motor 3). A bell mouth extending toward the inside of the first fan 1 is formed at the outer edge of the first suction port 411. Inside the first scroll part 41, a spiral flow path for collecting air blown from the first fan 1 is formed.

  The second scroll portion 42 is formed with a second suction port 421 that opens toward the other end side in the fan axial direction (electric motor 3 side). A bell mouth extending toward the inside of the second fan 2 is formed at the outer edge of the second suction port 421. Inside the second scroll part 42, a spiral flow path for collecting air blown from the first fan 1 is formed.

  In the casing 4, an introduction passage 44 that guides air to the second suction port 421 is formed outside the second scroll portions 41 and 42.

  The motor housing portion 43 is formed by denting the wall surface of the casing 4 toward the second suction port 421 side.

  The first fan 1 has a configuration in which a large number of plate-like wing parts 11 (blades) are arranged around a rotation axis. The multiple blades 11 are connected at the first suction port 411 side end by the side plate 12 and at the opposite end by the main plate 13.

  The side plate 12 is formed in an annular shape so as to serve as a hook that fastens a large number of blade portions 11 from the outer peripheral side of the first fan 1. The main plate 13 is formed in a disk shape that covers a large number of blade portions 11 from the bottom surface side (anti-air intake side) of the first fan 1.

  In this example, the side plate 12 has a linear cross-sectional shape parallel to the fan axial direction. The side plate 12 has a substantially arc shape along the main stream line flowing between the wing parts 11 so that the cross-sectional area of the air flow path between the wing parts 11 decreases from the inside to the outside in the fan radial direction. It may have a cross-sectional shape.

  Similarly to the first fan 1, the second fan 2 has a configuration in which a large number of plate-like wing portions 21 (blades) are arranged around the rotation axis. The blade 21 of the second fan 2 is connected at its second suction port 421 side end by a bowl-shaped side plate 22 and at the opposite end by a disk-shaped main plate 23.

  A cylindrical boss 24 to which the shaft 32 of the electric motor 3 is coupled is formed at the center of the main plate 23. The boss 24 is connected to the central portion of the main plate 13 of the first fan 1.

  The motor main body 31 of the electric motor 3 includes a core 311, a rotor 312, a magnet 313, a bearing 314, a center piece 315, and the like. The core 311 is fixed to the casing 4 via the center piece 315. Two bearings 314 are fixed to the center piece 315. The two bearings 314 support the shaft 32 outside the first and second fans 1 and 2. The rotor 312 is fixed to the shaft 32, and the magnet 313 is fixed to the rotor 312.

  A motor cover 5 is attached to the casing 4 in order to protect motor components such as the shaft 32, the bearing 314, and a circuit unit (not shown) from external dust and dirt.

  When the core 311 is energized by an external power source (not shown), a change in magnetic flux occurs and a force that attracts the magnet 313 is generated, so that the magnet 313, the rotor 312, the shaft 32, and the fans 1 and 2 are integrated around the central axis of the shaft 32. And rotate.

  In the vicinity of the boss 24 (fan boss portion), a balancer 6 for reducing vibration due to rotation is provided. Specifically, the balancer 6 is provided inside the first fan 1 and at the center of the main plate 13. In other words, the balancer 6 is disposed on the side farther from the electric motor 3 than the boss 24 (on the side opposite to the motor). The balancer 6 is disposed on the side farther from the electric motor 3 than the second fan 2 (on the side opposite to the motor).

  The balancer 6 is a ball balancer having a ball 61 (spherical weight) movable in the rotation direction of the fans 1 and 2 and a ball housing portion 62 (weight housing portion) for housing the ball 61. The balance is automatically adjusted by moving an annular housing space 621 formed in the housing portion 62. The accommodation space 621 is formed coaxially with the fans 1 and 2.

  The ball housing portion 62 projects in a tapered manner from the main plate 13 toward the first suction port 411 side (the air suction side of the first fan 1). In the example of FIG. 1, the ball housing portion 62 has a truncated cone shape, but may have a shape with a rounded corner (R chamfering, C chamfering).

  In this example, the ball housing portion 62 is configured by making the central portion of the main plate 13 thick, forming an annular groove in the thick portion, and covering the annular groove with a cover member.

  FIG. 2 is a cross-sectional view taken along the line AA of FIG. The ball 61 can freely move (roll) in the accommodation space 621. 2A shows an example when there are two balls 61, FIG. 2B shows an example when there are three balls 61, and FIG. 2C shows an example when there are four balls 61. Yes.

  Next, the operation in the above configuration will be described. When the electric motor 3 rotationally drives the fans 1 and 2, the wings 11 and 21 of the fans 1 and 2 give momentum to the air. As a result, air is sucked from the suction ports 41 and 42 of the scroll portions 41 and 42, and air is sent out from the outer peripheral portions of the fans 1 and 2. The sent air is collected in the spiral flow paths of the scroll portions 41 and 42 and sent out from the discharge ports (not shown) of the scroll portions 41 and 42 to the air conditioning unit (not shown).

  Here, the rotation balance of the fans 1 and 2 will be described. FIG. 3 shows the above configuration with a simple model. 3A shows a stationary state (rotational speed ω = 0) of the rotating body R including the fans 1, 2, the shaft 32, the rotor 312 and the magnet 313, and FIG. The state where the rotational speed ω is lower than the critical speed ωc (ω <ωc) is shown, and FIG. 3C shows the state where the rotational speed ω of the rotating body R is higher than the critical speed ωc (ω> ωc).

  As shown in FIG. 3A, the inertia main axis A of the rotating body R including the fans 1, 2, the shaft 32, the rotor 312, and the magnet 313 has a slight deviation from the central axis of the shaft 32. This small deviation is caused by manufacturing errors and the like.

  Therefore, as shown in FIGS. 3B and 3C, a moment is generated by the centrifugal force Fc generated by the rotation of the rotating body R, and the support member that supports the bearing 314 (in the example of FIG. 1, the center piece 315). ) Is deformed, and the central axis of the shaft 32 tilts and swings around a specific point C between the two bearings 314.

  As shown in FIG. 3 (b), the rotating body R has a center of gravity G and an inertial spindle A as the shaft because the moment due to the centrifugal force Fc is larger than the gyro moment Mg at a rotational speed ω (rotational speed) lower than the critical speed ωc. Swing around the center axis of 32. In other words, the center of gravity G and the principal axis of inertia A are the center axis of the virtual shaft 32 when it is not tilted at the rotational speed ω = 0 with respect to the center axis of the actual tilted shaft 32 (FIG. 3B ) Is located on the opposite side of the dashed line.

  On the other hand, as shown in FIG. 3C, the rotating body R has a center of gravity G and an inertial spindle because the gyro moment Mg is larger than the moment due to the centrifugal force Fc at a rotational speed ω (number of revolutions) greater than the critical speed ωc. A falls inside the central axis of the shaft 32. In other words, the center of gravity G and the principal axis of inertia A are the actual center axis of the tilted shaft 32 and the center axis of the virtual shaft 32 when it is not tilted at the rotational speed ω = 0 (in FIG. 3C). It is located between the one-dot chain line).

  At this time, since the ball 61 of the balancer 6 is automatically arranged at a position that balances with the center of gravity G by centrifugal force, the ball 61 of the balancer 6 and the center of gravity G and the inertia main axis A are in a balanced positional relationship. Therefore, the vibration can be reduced by reducing the swing width of the shaft 32.

  In addition, since the balancer 6 is disposed at the fan boss portion away from the bearing 314, the distance from the tilt center C of the shaft 32 to the ball 61 can be increased. For this reason, the balance adjustment effect by the ball | bowl 61 can be exhibited effectively.

  Further, since the weight is increased by the balancer 6, the moment of inertia around the tilt center C is increased and the gyro moment Mg is also increased. For this reason, it is possible to further reduce the vibration at the rotational speed equal to or higher than the critical speed. In addition, since the balancer 6 is disposed at the fan boss portion away from the bearing 314, the moment of inertia can be efficiently increased with a small amount of weight increase.

  An example of the vibration reduction effect according to this embodiment is shown in FIG. The comparative example of FIG. 4 shows vibration in a blower without the balancer 6. As can be seen from FIG. 4, in the present embodiment, the critical speed is reduced as compared with the comparative example, and vibration at a rotational speed ω greater than the critical speed ωc is reduced.

  Furthermore, in the present embodiment, the balancer 6 is disposed in the fan boss portion (region where the air flow is relatively weak), so that the balancer 6 uses the first fan 1 and the second fan 2 for the air flow (suction port 41). The air flow from the fan 42 to the outer periphery of the fan) can be suppressed as much as possible, and the balancer 6 can be efficiently arranged by effectively utilizing the space inside the fan. Can do.

  Furthermore, since the ball accommodating portion 62 is formed in a truncated cone shape that becomes narrower toward the air suction portion 24 side of the first fan 1, the air flow by the first fan 1 is adjusted by the ball accommodating portion 62 and blown. Noise can be suppressed.

(Second Embodiment)
In the first embodiment, the balancer 6 is provided in the fan boss portion (near the boss 24). However, in the second embodiment, the balancer 6 is provided on the side plate 12 (an upper outer periphery of the fan) as shown in FIG. Is provided. Specifically, the ball accommodating portion 62 of the balancer 6 is configured by forming an annular groove in the side plate 12. The annular groove is provided with a return shape that prevents the ball 61 from falling off.

  According to the present embodiment, the distance from the tilt center C of the shaft 32 to the ball 61 can be further increased as compared with the first embodiment. Therefore, the balance adjustment effect by the balls 61 can be more effectively exhibited, and the moment of inertia can be further increased, so that vibration can be reduced more efficiently.

  Further, it is possible to suppress as much as possible that the balancer 6 increases the blowing noise by disturbing the air flow (the air flow from the inlets 41 and 42 toward the fan outer peripheral side) by the first fan 1 and the second fan 2. In addition, the balancer 6 can be efficiently arranged by effectively utilizing the space inside the casing.

(Third embodiment)
In the third embodiment, as shown in FIG. 6, the accommodation space 621 is partitioned in the circumferential direction of the fan into the same number of spaces as the balls 61 by the partition portions 622, and one ball 61 is accommodated in each partitioned space. The elastic body 623 is attached to the wall surface of the partition portion 622.

  According to the present embodiment, the impact caused by the collision of the balls 61 can be reduced by the partition portion 622 and the elastic body 623. Therefore, when the balls 61 exhibit unstable behavior at the critical speed, the balls 61 or the balls 61 are separated from each other. The vibration can be prevented from increasing due to the collision of the portion 622.

(Fourth embodiment)
In the third embodiment, the accommodation space 621 is partitioned in the fan circumferential direction. In the fourth embodiment, as shown in FIG. 7, the accommodation space 621 is partitioned in the fan radial direction. Thereby, it is possible to prevent the balls 61 from colliding with each other.

(Fifth embodiment)
In the third and fourth embodiments, the accommodation space 621 is partitioned in the fan circumferential direction or the fan radial direction. However, in the fifth embodiment, as shown in FIG. 8, the accommodation space 621 is arranged in the fan axial direction. It is partitioned. Thereby, it is possible to prevent the balls 61 from colliding with each other.

(Sixth embodiment)
In the first to fifth embodiments, the balancer 6 is a ball balancer. However, in the sixth embodiment, as shown in FIG. 9, the balancer 6 includes a fluid 63 that forms a weight, and a fluid 63. It is comprised with the fluid balancer which has the fluid accommodating part 64 (weight accommodating part) to accommodate.

  The fluid 63 automatically adjusts the balance by moving in a cylindrical accommodation space 641 formed in the fluid accommodation portion 64. The accommodation space 641 is formed coaxially with the fans 1 and 2.

  In this example, the ball housing portion 62 is formed by forming a cylindrical portion at the center of the main plate 13 and covering the opening of the cylindrical portion with a cover member. Further, an O-ring 642 for sealing the accommodation space 641 is disposed on the cover member.

  Also in this embodiment, the vibration can be reduced by the balance adjustment effect of the balancer 6.

(Seventh embodiment)
In the seventh embodiment, as shown in FIG. 10, the balancer 6 includes a groove 64 formed in the main plates 13 and 23 and a weight 65 that can slide in the groove 64.

  In this example, a plurality of grooves 64 are formed, and one weight 65 is arranged in each groove 64. The groove 64 is formed in an arc shape coaxial with the fans 1 and 2.

  Further, in this example, the central portion of the main plate 13 of the first fan 1 is recessed toward the second fan 2 and is integrated with the main plate 23 of the second fan 2, and the main plates 13 and 23 are integrated. A groove 64 is formed in the region.

  According to the present embodiment, the balance adjustment effect can be exhibited by the weight 65 moving in the formation range of the groove 64.

  Also in the present embodiment, the balancer 6 disturbs the air flow (the air flow from the suction ports 41 and 42 toward the fan outer peripheral side) by the first fan 1 and the second fan 2 to increase the blowing noise. Can be suppressed as much as possible, and the balancer 6 can be efficiently arranged by effectively utilizing the space inside the fan.

  In the present embodiment, a cover that covers the balancer 6 may be provided, and the air flow (air flow from the suction ports 41 and 42 toward the fan outer peripheral side) may be adjusted by the cover.

(Other embodiments)
The weight of the balancer 6 may be a fine particle (sand particle or the like). However, it is preferable that the microparticles are free-flowing materials that do not adhere to each other (those that do not have moisture or stickiness).

  The balancer 6 may be a pendulum type balancer. That is, the weight of the balancer 6 may be constituted by a pendulum that rotates around the central axis of the shaft 32.

  The fans 1 and 2 are not limited to the centrifugal multiblade fan, and may be various types of fans such as an axial fan and a cross-flow fan. That is, even in various types of fans other than the centrifugal multiblade fan, a large distance from the bearing to the weight can suppress the weight increase due to the weight, and the air flow is relatively weak. By providing a weight in the vicinity of the boss, an increase in blowing noise due to the weight can be suppressed.

  Further, the blower is not limited to the inside / outside air two-layer blower including two fans, and the single fan may be a single fan.

1 First fan (fan)
2 Second fan (fan)
13 Main plate 24 Boss 32 Shaft 61 Ball (weight)
62 Ball housing part (weight housing part)
314 Bearing

Claims (9)

Fans (1, 2) that give momentum to the air by rotating,
A shaft (32) serving as a rotation axis of the fans (1, 2);
A bearing (314) for supporting the shaft (32) outside the fans (1, 2);
A weight (61, 63, 65) movable in the rotational direction of the fans (1, 2),
The weight (61, 63, 65) is located on the opposite side of the bearing (314) from the end (13, 22) of the fan (1, 2) on the bearing (314) side. Blower characterized by. The fan (1, 2) has a boss (24) to which the shaft (32) is coupled,
The blower according to claim 1, wherein the weight (61, 63) is provided on the boss (24).   The blower according to claim 1, wherein the weight (61, 63, 65) is arranged on the opposite side of the bearing (314) with the fan (2) interposed therebetween. The fan (1) is a centrifugal multiblade fan having a large number of blade portions (11) and a main plate (13) connecting the blade portions (11).
The blower according to claim 1 or 2, wherein the weight (61, 63, 65) is arranged inside the fan (1).   The blower according to claim 4, wherein the weight (61, 63) is accommodated in a groove formed in the main plate (13). A weight housing portion (62, 64) for housing the weight (61, 63);
The blower according to claim 4, wherein the weight housing part (62, 64) protrudes from the main plate (13) toward the air suction side of the fan (1).   The blower according to claim 6, wherein the weight housing part (62) is tapered toward the air suction side of the fan (1). The fan (1) includes a plurality of blades (11) arranged around the rotation shaft, and a side plate that connects the plurality of blades (11) from the outside in the radial direction of the fan (1). 12) a centrifugal multiblade fan having
The blower according to claim 1, wherein the weight (61) is accommodated in a groove formed in the side plate (12). The fans (1, 2) are centrifugal multiblade fans having a large number of blade portions (11, 21) and main plates (13, 23) connecting the blade portions (11, 21).
The blower according to claim 1, wherein the weight (65) is slidable in a groove (64) formed in the main plate (13, 23).

Images