JP2012159034A - Vibration control boss for fan - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vibration control boss for a fan capable of enhancing vibration control effect making spring property in a twisting direction soft and capable of effectively stabilizing the rotation of a fan body by and making spring properties in a direction perpendicular to a shaft and a prying direction hard.SOLUTION: In the vibration control boss 14 for the fan having a rigid cylindrical member 18, a rigid connecting plate 20 rotating integrally with the fan body, an elastomer 22 elastically coupling the cylindrical member 18 and the connecting plate 20 and arranged in a center part of the rotational fan and preventing vibration, the cylindrical member 18 is arranged while totally dislocating the same in an axial direction to a position not overlapping the connecting plate 20 in a radial direction, and the cylindrical member 18 and the connecting plate 20 are coupled in the axial direction by the elastomer 22.

Description

  The present invention relates to a vibration isolating boss for a fan that is provided in a central portion of a rotary fan and that performs vibration isolation between a rotary shaft and a fan body by elastic deformation of an elastic body.

  Conventionally, a cross flow fan that sucks air from a radial range of a long cylindrical fan body as a rotary fan, and blows out the sucked air from another radial range while flowing in the transverse direction inside the fan body ( However, it is widely used as a rotating fan for an air conditioner (air conditioner) because it can blow out a wide range of wind.

FIG. 6 shows an example.
In the figure, reference numeral 200 denotes a casing, 202 denotes a fan body, and 204 denotes a motor that rotationally drives the fan body 202.
The casing 200 has a pair of side plates 206 on the left and right sides, and the fan body 202 has a plurality of blades 208 provided along the circumferential direction and end plates 210 at the left and right ends.
Reference numeral 212 denotes a vibration isolating boss for vibration isolation, which is interposed between the rotary shaft 214 and the fan main body 202, specifically, the end plate 210.
In the case of this cross flow fan, air is sucked in from above as indicated by an arrow, and the wind is sent forward in a band shape.

In recent years, inverter control is mainly used for air conditioners in response to growing global environmental awareness and increasing needs for energy saving and comfort improvement.
Under this inverter control, the air conditioner can maintain the set temperature by low power operation after rapid cooling, for example, and can consume power economically.
On the other hand, under inverter control, frequent torque fluctuations are caused by the DC motor, and vibrations and noises are likely to occur due to the torque fluctuations.

  The anti-vibration boss 212 suppresses vibration transmission from the rotation shaft 214 to the fan body 202 and vibration transmission from the fan body 202 to the rotation shaft 214, that is, vibration isolation between the rotation shaft 214 and the fan body 202. It is provided for the purpose.

A typical example of the anti-vibration boss for the crossflow fan is disclosed in Patent Document 1 below.
FIG. 7 shows a specific example thereof.
In the figure, reference numeral 216 denotes an anti-vibration boss, which has a cylindrical shape and is fitted with a rotating shaft 214 in an inner fitting hole 218 and receives a driving force from the rotating shaft 214 to rotate integrally with the rotating shaft 214. A cylindrical member (inner side member) 220, a rigid disc-shaped connection plate (outer side member) 222 that is joined to the fan main body 202, specifically the end plate 210 and rotates integrally with the fan main body 202, And an elastic body 224 that is elastically connected in the radial direction.
Here, the inner cylinder member 220 is fixed to the rotary shaft 214 in an integrally rotated state by a male screw member 226.

  In the anti-vibration boss 216, the rotational movement of the inner cylinder member 220 is transmitted to the connection plate 222 via the elastic body 224, that is, the fan main body 202 to rotate the inner cylinder member 220. Vibration transmission from the member 220, that is, the rotation shaft 214 to the fan main body 202 and vibration transmission from the fan main body 202 to the rotation shaft 214 are suppressed.

  In the anti-vibration boss 216 shown in FIG. 7, the radial distance between the connecting plate 222 and the inner cylinder member 220 is increased, that is, the size of the elastic body 224 between them is increased. The softening of the spring characteristics in the torsional direction 224 (the spring characteristics in the direction in which the connecting plate 222 rotates with respect to the inner cylinder member 220) suppresses the vibration suppression effect between the rotating shaft 214 and the fan main body 202, that is, vibration isolation. The performance can be increased.

  However, by doing so, the spring characteristic in the direction perpendicular to the axis of the elastic body 224 and the spring characteristic in the twisting direction (as shown in FIG. 7B, the spring in the direction in which the connecting plate 222 is tilted with respect to the inner cylinder member 220). At the same time, the characteristics are also softened.

If the spring characteristics in the direction perpendicular to the axis and the direction of twisting become soft, the fan main body 202 is violated during product (fan) transportation (the fan main body 202 tilts or irregularly moves with respect to the casing 200), and the fan main body 202 moves into the casing. There arises a problem of hitting 200.
Even when the fan is used in a horizontal position, the fan main body 202 is inclined with respect to the casing 200, and in some cases, the fan main body 202 may be damaged by contact with the casing 200 or may generate noise.

  In addition, when the fan is used in a horizontal position, if the spring characteristic of the elastic body 224 in the direction perpendicular to the axis is soft, the amount of deformation in the same direction increases. In this case, the axis of the fan main body 202 with respect to the axis of the rotating shaft 214 is increased. As a result, the fan main body 202 rotates irregularly, which causes problems such as vibration and abnormal noise.

  Further, in the case of the anti-vibration boss 216 shown in FIG. 7, since the fan main body 202 (specifically, the end plate 210) is joined to the connection plate 222, the radial projection dimension a of the connection plate 222 from the elastic body 224 A certain dimension or more is required, and a dimension b for embedding the connecting plate 222 in the elastic body 224 is required to be a certain dimension or more, and in order to soften the torsion spring characteristics, The dimension c between the inner cylinder member 220 and the inner cylinder member 220 is also required to be greater than a certain value, and the thickness of the inner cylinder member 220 in the radial direction is added, so that the outer diameter of the connection plate 222 is inevitably increased. There is a problem that 216 becomes larger.

  When the vibration isolating boss 216 is enlarged, when the vibration isolating boss 216 is molded in a state where the inner cylinder member 220 and the connection plate 222 are coupled by the elastic body 224, the number of products to be taken per die is reduced. As a result, the manufacturing cost of the anti-vibration boss 216 increases accordingly.

  In addition, if the dimension c of the elastic body 224 is increased, the amount of deformation described above is also increased, and this is also a factor that increases the deviation of the axis of the fan main body 202.

The above is an example of the anti-vibration boss for the cross flow fan, but the same kind of problem can occur in common in other various anti-vibration bosses for the fan.
In general, a vibration isolating boss for a rotary fan is composed of a rigid inner side member that rotates integrally with the rotary shaft, a rigid outer side member that rotates integrally with the fan body, and an elastic body that elastically connects them. While the effect of reducing vibration is enhanced by softening the spring characteristics in the torsional direction of the elastic body, the problem is that the spring characteristics in the direction perpendicular to the axis and in the twisting direction become soft at the same time. As a result, there is a problem that the holding and rotation of the fan body becomes unstable.

Japanese Patent Laid-Open No. 7-155854

  In the present invention, against the background described above, the spring characteristics in the torsional direction can be softened to increase the vibration suppression effect, while the spring characteristics in the direction perpendicular to the axis and in the twisting direction are hardened to maintain the fan body. The purpose of the present invention is to provide a vibration isolating boss for a fan that can effectively stabilize the rotation.

  Thus, according to the first aspect of the present invention, (a) a rotating shaft is inserted into the inner fitting hole in the form of a cylinder, and the driving shaft receives a driving force from the rotating shaft to rotate integrally with the rotating shaft. An inner side member, (b) a rigid outer side member joined to the fan body of the rotary fan and rotated integrally with the fan body, and (c) joined to the inner side member and the outer side member. An elastic body that elastically connects the side member and the outer side member, and is provided at a central portion of the rotary fan, and is provided with an anti-vibration function between the rotary shaft and the fan body by elastic deformation of the elastic body. An anti-vibration boss for a fan, wherein the inner side member is arranged so as to be shifted in the axial direction as a whole to a position where the inner side member is not overlapped in the radial direction with respect to the outer side member, and the inner side member and the outer side member And the outer A first support portion that supports a rotational force applied to the member; and is non-joined to the rotary shaft, and is interposed between the outer side member and the rotary shaft in a radial direction, and is radially directed to the outer side member The inner side member and the outer side member are integrally elastically connected by the elastic body including a second support portion that supports a force applied inward by contact with the rotating shaft.

  According to a second aspect of the present invention, in the first aspect, the elastic body is formed in an annular shape around the rotating shaft.

  According to a third aspect of the present invention, in the second aspect, the elastic body is fitted to the rotary shaft in an externally fitted state, and the elastic body is slid with respect to the outer peripheral surface of the rotary shaft. It is possible to move relative to the rotating shaft in the rotational direction.

  According to a fourth aspect of the present invention, in any one of the second and third aspects, an inner diameter of the outer side member is smaller than an outer diameter of the inner side member, and an inner peripheral position of the outer side member is the inner side member. It is characterized in that it is located radially inward from the outer peripheral position.

  According to a fifth aspect of the present invention, in any one of the first to fourth aspects, the outer side member has a disc shape.

  According to a sixth aspect of the present invention, in the fifth aspect, the elastic body has an embedded portion that embeds an inner peripheral portion of the outer side member.

Effects and effects of the invention

  As described above, the present invention arranges the inner side member and the outer side member so that the inner side member is displaced in the axial direction as a whole until the position where the inner side member does not overlap with the outer side member in the radial direction. A first support portion that is coupled in the direction and supports the rotational force applied to the outer side member, and is non-joined to the rotating shaft, and is interposed between the outer side member and the rotating shaft in the radial direction, On the other hand, the inner side member and the outer side member are integrally elastically connected by an elastic body including a second support portion that supports a force applied radially inward by contact with the rotating shaft.

  In the present invention, the second support portion of the elastic body which is not joined to the rotating shaft and is interposed between the outer side member and the rotating shaft in the radial direction hardly affects the spring characteristics in the torsional direction. The spring characteristic in the torsional direction is determined by the axial distance between the outer side member and the inner side member, that is, mainly by the axial length of the first support portion in the elastic body.

  In the anti-vibration boss of the present invention, the inner side member is not located at the radially inner position of the outer side member, and the second support portion of the elastic body located at the radially inner side is not joined to the rotating shaft. Therefore, when the outer side member rotates around the rotating shaft, the second support portion rotates integrally with the outer side member, and does not become an elastic resistor against the rotation of the outer side member, that is, the movement in the torsional direction. , Does not develop a torsional spring.

That is, in the present invention, the spring characteristics in the torsional direction can be independently adjusted freely by changing the length of the first support portion.
On the other hand, the spring characteristic in the direction perpendicular to the axis is mainly determined by the radial dimension of the second support portion. In addition, the spring characteristics in the twisting direction are also determined by the radial dimension of the second support portion.

In the present invention, in order to soften the spring characteristics in the torsional direction, it is not necessary to increase the radial dimension of the second support portion of the elastic body, that is, the portion located on the radially inner side of the outer side member. Can be set.
Thus, if the radial dimension of the same portion can be reduced, the spring characteristics in the direction perpendicular to the axis and in the twisting direction can be made harder.
That is, according to the present invention, it is possible to independently adjust the spring characteristics in the torsional direction and the spring characteristics in the direction perpendicular to the axis and in the twisting direction.

  In the present invention, the spring characteristics in the direction perpendicular to the axis and the twisting direction can be hardened while softening the spring characteristics in the torsion direction, so that the product (rotating fan) can be transported while ensuring the high anti-vibration performance of the anti-vibration boss. It is possible to solve the problem that the fan body sometimes tilts or irregularly hits the casing and is damaged.

  Furthermore, when using a rotating fan, the fan body hits the casing and damages or generates abnormal noise, especially when the rotating fan is a cross-flow fan and when it is used horizontally, It is possible to satisfactorily solve the problem of tilting with respect to the casing and causing damage due to contact with the casing or generating abnormal noise.

  Furthermore, the amount of deformation of the elastic body in the direction perpendicular to the axis can be reduced by stiffening the spring characteristics in the direction perpendicular to the axis of the second support part and by reducing the radial dimension. The problem that the fan main body rotates irregularly or generates abnormal noise can be solved together by causing a deviation from the axial center of the fan.

  Further, in the present invention, since there is no inner side member on the radially inner side at a position overlapping with the outer side member in the radial direction, at least the radial thickness of the inner side member, the outer diameter size of the elastic body, and It is possible to reduce the outer diameter of the outer side member, and in addition, since the radial dimension of the second support portion can be reduced in the present invention, the overall radial dimension of the vibration isolating boss can be effectively reduced, The vibration-proof boss can be reduced in size.

Thus, if the vibration-proof boss can be miniaturized, the number of products to be taken per die can be increased, and the productivity can be increased while the manufacturing cost can be reduced.
Further, since the radial dimension of the second support portion can be reduced, the deformation amount of the elastic body in the same direction can be suppressed to a small amount.

  In this invention, the said elastic body can be made into the shape which makes | forms a ring around a rotating shaft (Claim 2).

  In this case, the elastic body is fitted to the rotating shaft in an externally fitted state, and the elastic body can be moved relative to the rotating shaft in the rotational direction while sliding the inner peripheral surface of the elastic body with respect to the outer peripheral surface of the rotating shaft. (Claim 3).

In the present invention, the inner diameter of the outer side member is made smaller than the outer diameter of the inner side member, and the inner peripheral position of the outer side member is positioned radially inward from the outer peripheral position of the inner side member. (Claim 4).
In the case of the conventional anti-vibration boss shown in FIG. 7, such a thing cannot be realized, but according to the anti-vibration boss of the present invention, it can be realized. The spring characteristics of the second support portion in the direction perpendicular to the axis and the twisting direction can be effectively increased, and further, the vibration-proof boss can be more effectively downsized.

In this invention, the said outer side member can be made into disk shape (Claim 5).
In this case, the elastic body may have an embedded portion that embeds an inner peripheral portion of the outer side member (claim 6).

It is principal part sectional drawing at the time of applying the anti-vibration boss | hub which is one Embodiment of this invention for crossflow fans. It is a figure of the vibration isolating boss of the embodiment. It is a figure at the time of applying the anti-vibration boss of this invention as an anti-vibration boss for propeller fans. It is the figure which showed the anti-vibration boss of the conventional structure for the comparison. It is explanatory drawing of the method of the spring measurement of a vibration isolating boss. It is a figure of a cross flow fan. It is the figure which showed an example of the conventional vibration isolating boss.

Next, embodiments of the present invention will be described in detail with reference to the drawings.
In FIG. 1, 10 is a cross-flow fan, 12 is an end plate of the fan main body 11, 14 is a central portion of the fan main body 11, more specifically, a vibration-proof boss provided at the central portion of the end plate 12, and 16 is a motor. A rotating shaft protruding from the side.
The anti-vibration bosses 14 are respectively joined to the inner cylindrical member 18 as the inner side member, the disk-shaped connecting plate 20 as the outer side member, and the inner cylindrical member 18 and the connecting plate 20, and elastically integrate them. And an elastic body 22 to be connected.

Here, the inner cylinder member 18 and the connection plate 20 are both metallic rigid members. However, the inner cylinder member 18 and the connection plate 20 can be rigid members made of resin.
On the other hand, the elastic body 22 is made of a rubber elastic body here. However, this may be composed of a thermoplastic elastomer.

The inner cylinder member 18 is a cylindrical member and has a fitting hole 24 in the center thereof, and the rotary shaft 16 is fitted therein.
The inner cylinder member 18 is provided with a female screw hole 25 penetrating in the radial direction, and a male screw member 26 is screwed therein. The inner cylinder member 18 is fixed to the rotary shaft 16 in an integrally rotated state by screwing the male screw member 26.
As shown in FIG. 2B, the inner cylinder member 18 is provided with a notch 28 for positioning in the rotational direction at a predetermined position in the circumferential direction of the outer peripheral portion.

As shown in FIG. 2, the connecting plate 20 is a thin disk-shaped member having a circular opening 30 in the center, and has a plurality of connecting holes 32 and 34 penetrating in the plate thickness direction. Yes.
The end plate 12 shown in FIG. 1 is formed integrally with the connection plate 20 so as to wrap around the outer peripheral portion of the connection plate 20 exposed in the radial direction from the elastic body 22.
At this time, the end plate 12 made of resin is integrated by connecting a portion located on the right side in FIG. 1 of the connecting plate 20 and a portion located on the left side through a connecting hole 32.

In this embodiment, the inner cylinder member 18 is disposed so as to be displaced in the axial direction (right direction in the figure) as a whole until the position where it does not overlap with the connection plate 20 in the radial direction. The cylindrical member 18 and the connection plate 20 are elastically connected by an elastic body 22.
Here, the inner cylinder member 18, the connecting plate 20, and the elastic body 22 are integrally joined by vulcanization adhesion.

In this embodiment, the elastic body 22 has an annular shape around the rotary shaft 16 shown in FIG. 1, and its central portion is a fitting hole that extends substantially linearly in the axial direction to the fitting hole 24 of the inner cylinder member 18. 36.
The hole diameter of the fitting hole 36 is substantially the same as the outer diameter of the rotary shaft 16, specifically, a large diameter by a minute dimension (here, 0.1 mm on one side in the radial direction), that is, the state shown in FIG. In the state where the rotary shaft 16 is fitted in the fitting hole 24 and the fitting hole 36 of the elastic body 22, the inner peripheral surface of the elastic body 22 has a minute gap (0.1 mm) with respect to the outer peripheral surface of the rotary shaft 16. It is in the state fitted via.

  The elastic body 22 connects the inner cylinder member 18 as the inner side member and the connection plate 20 as the outer side member in the axial direction, and supports a first support portion G1 that supports the rotational force applied to the connection plate 20. In addition, it is non-joined to the rotating shaft 16 and is interposed between the connecting plate 20 and the rotating shaft 16 in the radial direction, and supports the force applied to the connecting plate 20 radially inward by contact with the rotating shaft 16. And a second support portion G2.

The elastic body 22 also has an embedded portion G3 for embedding the left end portion of the inner cylindrical member 18 in the figure, an embedded portion G4 for embedding the inner peripheral side portion of the connecting plate 20, and a protruding portion G5 to the left in the drawing. is doing.
In the vibration isolating boss 14 of this embodiment, when the connection plate 20 is rotated, the first support portion G1 mainly generates an elastic resistance. That is, mainly the first support portion G1 functions as a torsion spring.

At this time, the second support part G2 rotates integrally with the connecting plate 20 while sliding the inner peripheral surface with respect to the outer peripheral surface of the rotating shaft 16, and particularly provides elastic resistance against the rotating motion of the connecting plate 20. Do not generate.
That is, in this embodiment, the second support portion G2 does not substantially function as a torsion spring.

On the other hand, the connection plate 20 is moved in the direction perpendicular to the axis under the state shown in FIG. Then, the second support part G2 is compressed and elastically deformed in the direction perpendicular to the axis, and a large elastic resistance force is generated. That is, at this time, the second support portion G2 mainly functions as an axially perpendicular spring.
At that time, the smaller the radial dimension (diameter thickness dimension) of the second support part G2, the larger the axially perpendicular spring.

In the vibration isolating boss 14 of this embodiment, when the connecting plate 20 is tilted, the entire elastic body 22 generates an elastic resistance force and acts as a twisting direction spring.
However, the twisting direction spring becomes larger in the same manner as the axially perpendicular direction spring as the radial dimension of the second support portion G2 is smaller, that is, as the position of the inner peripheral end of the connecting plate 20 is closer to the rotary shaft 16.

  That is, in this embodiment, the spring constant of the torsion spring can be adjusted by changing the axial length of the first support portion G1 substantially. By changing the radial thickness of the second support portion G2, the spring constant in those directions can be adjusted.

In this embodiment, the inner diameter d1 of the inner cylindrical member 18 is d1 = φ8 mm and the outer diameter d2 = φ16 mm, which is the same diameter as the rotary shaft 16.
Here, as described above, the diameter of the fitting hole 36 in the elastic body 22 is larger by 0.1 mm than the outer diameter of the rotating shaft 16 on one side in the radial direction.
The inner diameter d3 of the connecting plate 20 is φ12 mm, and thus the radial thickness d7 of the second supporting portion G2 is 1.9 mm, and the axial direction between the connecting plate 20 and the inner cylindrical member 18 in the first supporting portion G1. Here, the dimension (diameter dimension) of the overlapping portion is 2 mm on one side in the radial direction and 4 mm on both sides.

A portion of the first support portion G1 sandwiched in the axial direction between the connection plate 20 and the inner cylinder member 18 has a great influence on the torsion spring.
The axial dimension d4 of the first support part G1 is 1.7 mm, the outer diameter d5 of the connecting plate 20 is 61 mm, and the thickness d6 of the connecting plate 20 is 1.0 mm.

In the present embodiment as described above, the spring characteristics in the torsional direction can be independently adjusted by changing the axial length of the first support portion G1.
On the other hand, the spring characteristic in the direction perpendicular to the axis is mainly determined by the radial dimension of the second support part G2. In addition, the spring characteristic in the twisting direction is also determined by the radial dimension of the second support portion G2.

In the present embodiment, in order to soften the spring characteristics in the torsional direction, it is not necessary to increase the radial dimension of the second support portion G2 of the elastic body 22, that is, the portion located on the radially inner side of the connection plate 20, and the same The dimensions can be set small.
Thus, by reducing the radial dimension of the same portion, the spring characteristics of the elastic body 22 in the direction perpendicular to the axis and in the twisting direction can be hardened.
That is, according to the present embodiment, the spring characteristics in the torsional direction and the spring characteristics in the direction perpendicular to the axis and the twisting direction can be adjusted independently.

  In this embodiment, the spring characteristics in the direction perpendicular to the axis and the twisting direction can be hardened while softening the spring characteristics in the torsion direction, so that the product (fan) It is possible to solve the problem that the fan main body 40 is tilted or irregularly moved during transportation and the fan main body 40 hits the casing and is damaged.

  Further, when the fan is used, it is possible to satisfactorily solve the problem that the fan body 40 hits the casing and is damaged or generates abnormal noise.

  Further, by reducing the radial dimension of the second support part G2, the spring characteristic in the direction perpendicular to the axis is hardened, so that the amount of deformation of the elastic body 22 in the direction perpendicular to the axis can be reduced, and the axis of the fan body 40 rotates. By causing a deviation with respect to the axis of the shaft 16, it is possible to solve the problem that the fan body 40 irregularly rotates or generates abnormal noise.

  Further, in the present embodiment, since the cylindrical member 18 does not exist on the radially inner side at the position overlapping with the connection plate 20 in the radial direction, at least the thickness of the cylindrical member 18 in the radial direction is equal to the outer diameter of the elastic body 22. The dimensions and the outer diameter of the connection plate 20 can be reduced. In addition, in the present embodiment, the radial dimension of the second support portion G2 can be reduced. Can be effectively reduced, and the vibration-proof boss 14 can be reduced in size.

By reducing the size of the vibration isolating boss 14, the number of products per mold can be increased, and the productivity can be increased and the manufacturing cost can be reduced.
Moreover, since the radial direction dimension of the 2nd support part G2 can be made small, the deformation amount of the elastic body 22 in the same direction can be suppressed few.

In this embodiment, the inner diameter of the connection plate 20 is made smaller than the outer diameter of the cylindrical member 18, and the inner peripheral position of the connection plate 20 is positioned radially inward from the outer peripheral position of the cylindrical member 18. .
In the case of the conventional anti-vibration boss 14A shown in FIG. 7, such a thing cannot be realized, but according to the anti-vibration boss 14 of the present embodiment, it can be realized, and by doing so, the elastic body The spring characteristics in the direction perpendicular to the axis 22 and the twisting direction can be effectively increased, and the vibration isolating boss 14 can be further downsized more effectively.

The anti-vibration boss 14 can be applied as an anti-vibration boss for other rotary fans other than the cross flow fan, for example, a propeller fan and a turbo fan.
FIG. 3 shows an example in which the vibration isolating boss 14 is applied as a vibration isolating boss for a propeller fan.

In the figure, reference numeral 40 denotes a fan body in the propeller fan 38.
The fan body 40 includes a hub 42, a plurality of blades 44 extending radially from the hub 42, and a joint portion 46 with the vibration proof boss 14.
The joint 46 is integrally formed with the anti-vibration boss 14 so as to enclose the connection plate 20.
The fan main body 40 including the joint portion 46, the hub 42, and the blades 44 is made of resin.
In the figure, reference numeral 48 denotes a motor.
Further, 16A in the figure is a male engaging portion of the rotary shaft 16 having a D-shaped cross section, and here, the fitting hole 24 of the inner cylindrical member 18 forms a corresponding D-shaped female engaging portion. Yes.
Reference numeral 58 denotes a male screw shaft protruding from the rotary shaft 16, and reference numeral 60 denotes a nut screwed therein.

<Spring measurement>
The spring measurements in the torsional direction, the axis perpendicular direction, and the twisting direction in the vibration isolating boss 14 of the present embodiment were performed as follows.
For comparison, the spring measurement of the vibration isolating boss 14A having the conventional structure shown in FIG. 4B and the vibration isolating boss 14B having the conventional structure shown in FIG. 4A used for the propeller fan are also shown. went.
The vibration-proof boss 14A shown in FIG. 4B has the same basic structure as that shown in FIG. 7, but is an example different from that shown in FIG.
In the figure, 18A indicates an inner cylinder member, 20A indicates a disk-shaped connecting plate, and 22A indicates a rubber elastic body.

On the other hand, an anti-vibration boss 14B of the conventional example used for the propeller fan shown in FIG. 4 (A) includes a cylindrical inner cylinder member 50B, a cylindrical outer cylinder member 52B, and an integral part thereof. And a rubber elastic body 54B having a cylindrical shape which is vulcanized and bonded.
In the case of the anti-vibration boss 14B shown in FIG. 4A, the cylindrical joint portion 55B of the fan body of the propeller fan is joined to the outer peripheral surface of the outer cylinder member 52B.

The dimensional relationship is as follows.
In the vibration isolating boss 14A shown in FIG. 4B, d8 = φ50 mm, d9 = φ27 mm, d10 = 7 mm, d11 = 20 mm.
4A, d12 = 14 mm, d13 = 24 mm, d14 = (d13−d12 / 2) = 5 mm, d15 = 30 mm, and d16 = φ46.2 mm.

Each spring measurement in the twist direction, the direction perpendicular to the axis, and the twist direction was performed as shown in FIG.
FIG. 5 shows a spring measurement method using the anti-vibration boss 14 </ b> A of FIG. 4B used as a conventional anti-vibration boss for a crossflow fan as a representative.
Here, the shaft 56 is inserted into the inner cylinder member 18A, the inner cylinder member 18A is fixed thereto, and the connecting plate 20A is fixed, and a torsion torque is applied from the shaft 56 to the inner cylinder member 18A in the direction indicated by the arrow. The spring constant in the torsional direction was derived from the displacement and load at that time.
The displacement angle was in the range of 0 to 10 °.

On the other hand, FIG. 5B shows a method of measuring the spring in the direction perpendicular to the axis. Here, the connecting plate 20A is fixed, and a load in the direction perpendicular to the axis is applied from the shaft 56 to the inner cylinder member 18A. And the spring constant was derived from the load.
Here, the amount of displacement was set to 0 to 0.4 mm.

On the other hand, FIG. 5C shows a method of measuring the spring in the twisting direction. Here, a torque is applied from the shaft 56 to the inner cylinder member 18A in the twisting direction indicated by the arrow in the drawing, and the spring is determined from the displacement and load at that time. Derived a constant.
Here, the displacement angle is in the range of 0 to 6 °.
These measurement results are shown in Table 1.
The rubber hardness in Table 1 was measured according to JIS K6253.

  As shown in Table 1, in the case of the vibration isolating boss 14 of the present embodiment, the spring constant in the torsional direction is equivalent to that of the vibration isolating boss 14A shown in FIG. Both the spring constant in the direction perpendicular to the axis and the spring constant in the twisting direction are significantly larger than those of the vibration isolating boss 14A shown in FIG.

Compared with the vibration isolating boss 14B shown in FIG. 4A, the ratio of the spring constant in the direction perpendicular to the axis / torsion direction spring constant and the ratio of the twist direction spring constant / torsion direction spring constant is significantly increased.
From this, it can be seen that the present embodiment can effectively increase the spring constant in the direction perpendicular to the axis and the spring constant in the twisting direction as compared with the spring constant in the twisting direction.

  Although the embodiment of the present invention has been described in detail above, this is merely an example, and the vibration isolating boss of the present invention has various forms other than the above examples of the inner side member, the outer side member, and the elastic body. The present invention can be configured in various forms without departing from the gist of the present invention, such as being able to be applied as an anti-vibration boss for various rotary fans.

14 Anti-vibration boss 16 Rotating shaft 18 Inner cylinder member (inner side member)
20 Connection plate (outer side member)
22 Elastic body 24 Fitting hole 40 Fan body G1 1st support part G2 2nd support part

Claims (6)

(a) a rigid inner member that is cylindrical and has a rotating shaft inserted into an inner fitting hole, and receives a driving force from the rotating shaft and rotates integrally with the rotating shaft; and (b) a rotating fan. A rigid outer side member that is joined to the fan main body and rotates integrally with the fan main body; and (c) the inner side member and the outer side member that are joined together and elastically connect the inner side member and the outer side member. An anti-vibration boss for a fan that is provided at a central portion of the rotary fan and vibrates between the rotary shaft and the fan body by elastic deformation of the elastic body,
The inner side member is disposed so as to be displaced in the axial direction as a whole to a position where the inner side member does not overlap in the radial direction with respect to the outer side member, and the inner side member and the outer side member are connected in the axial direction. A first support portion that supports a rotational force applied to the side member; and is non-joined to the rotary shaft, and is interposed between the outer side member and the rotary shaft in a radial direction, and has a diameter relative to the outer side member. The inner side member and the outer side member are integrally elastically connected by the elastic body including a second support portion that supports a force applied inward in the direction by contact with the rotating shaft. Anti-vibration boss for fans.   The anti-vibration boss for a fan according to claim 1, wherein the elastic body is formed in an annular shape around the rotary shaft.   3. The elastic body according to claim 2, wherein the elastic body is fitted onto the rotating shaft in an externally fitted state, and the elastic body is rotated with respect to the rotating shaft while sliding the inner peripheral surface of the elastic body with respect to the outer peripheral surface of the rotating shaft. Anti-vibration boss for fan, characterized in that it can be moved relative to the direction.   4. The outer side member according to claim 2, wherein an inner diameter of the outer side member is smaller than an outer diameter of the inner side member, and an inner peripheral position of the outer side member is more radial than an outer peripheral position of the inner side member. Anti-vibration boss for fans, characterized by being located inside.   5. The fan anti-vibration boss according to claim 1, wherein the outer side member has a disk shape.   6. The anti-vibration boss for a fan according to claim 5, wherein the elastic body has an embedded portion for embedding a portion on the inner peripheral side of the outer side member.

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