JP5494088B2 - Multi-blade blower - Google Patents

Description

  The present invention relates to a multiblade blower used for ventilation air conditioning equipment such as a ceiling-embedded ventilation fan.

  Conventionally, as shown in FIG. 8, this type of multiblade blower drives a fan casing 102 having a bell mouth 101, an impeller 103 that is rotatably installed in the fan casing 102, and an impeller 103. The motor 104 is configured. The impeller 103 has a plurality of blades 106 on the outer peripheral side of the main plate 105, and an outer peripheral ring 107 having a larger outer diameter than the outer periphery of the blade 106 is provided at the suction side end portion 108 of the impeller 103 (for example, Patent Documents). 1).

  In this configuration, when the frequency of the electromagnetic vibration generated from the electric motor 104 and the frequency of the natural vibration mode of the impeller 103 coincide with each other, a resonance phenomenon is excited, the vibration of the impeller 103 is amplified, and noise is generated. Since the excitation force of electromagnetic vibration acts in the circumferential direction of the rotating shaft, the natural vibration mode of the impeller 103 is changed between the main plate 105 and the suction side end by bending deformation of the blade 106 with the main plate 105 and the outer peripheral ring 107 as supporting points. When the part 108 has a behavior that is twisted to the opposite phase in the circumferential direction, it is easy to respond to the vibration, and the impeller 103 acts as a diaphragm of the speaker, so that excessive noise tends to occur. Further, since the frequency of the natural vibration mode depends on the distance between the main plate 105 and the outer peripheral ring 107, that is, the length of the blade 106, the length of the blade 106 can be changed to suppress the resonance phenomenon. Most effective. However, the length of the blade is determined by the blowing performance as a multiblade fan, and cannot be significantly shortened or lengthened.

  In view of this, a structure in which vibration from an electric motor is insulated to suppress excitation of a resonance phenomenon and prevent generation of noise is widely known (see, for example, Patent Document 2).

  Hereinafter, the multiblade fan will be described with reference to FIG.

  The inner diameter of the blade boss 110 of the impeller 109 is made larger than the outer diameter of the rotating shaft 111 of the electric motor, the recess 113 into which the rubber ring 112 is inserted is provided on both ends of the blade boss 110, and the blade boss 110 is inserted into the rotating shaft 111. The impeller 109 is pressed by the washer 114 and the screw 115 and is lifted from the rotating shaft 111 by applying the washer 114 and stopping with the screw 115. Since electromagnetic vibration from the rotating shaft 111 is insulated by the ring 112 and is not transmitted to the impeller 109, it does not resonate with the natural frequency of the impeller 109, and noise can be prevented.

JP 2001-173596 A (FIG. 2) Japanese Utility Model Publication No. 5-1899 (Fig. 2)

  In such a conventional multiblade fan, another part made of a material having a large loss factor such as a rubber ring is required to insulate vibration, so that the structure is complicated and the cost is increased. In addition, when the rubber deteriorates due to long-term use and the effect of insulating the vibration is reduced, the vibration from the motor is transmitted to the impeller, the resonance phenomenon is excited, and noise is generated.

  The present invention solves such a conventional problem, and provides a multiblade fan that is simple in structure, can suppress excitation of a resonance phenomenon at low cost, and can stably prevent generation of noise for a long period of time. With the goal.

In order to achieve this object, the present invention provides a main plate and a plurality of blades arranged in a ring on the front side and the back side of the main plate , respectively, on a plane whose end face positions are perpendicular to the rotation axis. A resin impeller provided uniformly, an electric motor connected to the rotating shaft , a casing including the impeller and including a suction port and a blowout port, and a natural vibration mode caused by twisting of the impeller plate The main plate is divided into a plurality of portions in the circumferential direction so that the position of the outer peripheral side in the rotation axis direction is non-uniform, and the length of the blade plate in the rotation axis direction is set to the front side of the main plate and It is characterized in that it is made uneven on the back side, thereby achieving the intended purpose.

  According to the present invention, since the frequency of the natural vibration mode in which the opening ends of the main plate and the blade plate are twisted in the opposite phase in the circumferential direction by bending deformation of the blade plate can be made different for each blade plate, the frequency of the natural vibration mode is It is possible to suppress the excitation of resonance phenomenon with the frequency of the vibration force in the circumferential direction that is distributed and generated from the electric motor, the structure is simple and low cost, and the generation of noise can be stably prevented for a long time A multi-blade fan can be provided.

Side sectional view showing the multiblade fan of Embodiment 1 of the present invention (A) Top view (b) Perspective view of the impeller of the multiblade fan Side sectional view of the impeller of the multiblade fan (A) Perspective view (b) Side sectional view of the impeller of the multiblade fan of Embodiment 2 of the present invention (A) Top view (b) Perspective view of impeller of multiblade fan of Reference Example 1 of the present invention (A) Top view (b) Perspective view of impeller of multiblade fan of Reference Example 2 of the present invention (A) Top view (b) Perspective view of impeller of multiblade fan of Reference Example 3 of the present invention Side sectional view showing a conventional multiblade fan A perspective view of an impeller of a conventional multiblade fan Partial sectional view of an impeller of a conventional blade fan

The multiblade fan according to claim 1 of the present invention is characterized in that the main plate and a plurality of blades arranged in a ring on the outer side of the front side and the back side of the main plate are uniformly arranged on a plane whose end face positions are perpendicular to the rotation axis. and a resin impeller equipped with the, an electric motor connected to said rotary shaft, and a casing having a containing and inlet and outlet of the impeller, the natural vibration mode by twisting of the blades The main plate is divided into a plurality of portions in the circumferential direction so that the frequency is distributed, the position of the outer peripheral side in the direction of the rotation axis is uneven, and the length of the blade plate in the direction of the rotation axis is set to the front side and the back side Each has a non-uniform configuration.

  As a result, the frequency of the natural vibration mode of the slats in which the opening ends of the main plate and the slats are twisted in the opposite phase in the circumferential direction by bending deformation of the slats can be made different for each slat. Thus, the frequency of the natural vibration mode is dispersed, the excitation of the resonance phenomenon with the frequency of the circumferential excitation force generated from the motor can be suppressed, and the generation of noise can be prevented stably for a long period of time. There is an effect.

In particular, the main plate is divided into a plurality in the circumferential direction, and the configuration of the position of the outer periphery of the main plate in the direction of the rotation axis is non-uniform, so that the length of the blades can be greatly varied in the rotation direction, The frequency of natural vibration mode is greatly dispersed, and the excitation of resonance phenomenon with the frequency of the circumferential excitation force generated from the motor can be suppressed, the structure is simple and low cost, stable for a long time This produces the effect of preventing noise generation.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

(Embodiment 1)
As shown in FIGS. 1 to 3, the multiblade blower 1 includes a fan casing 4 having a single inlet 2 and an outlet 3, an impeller 5 disposed inside the fan casing 4, an impeller 5, and a rotating shaft. 6 is provided, and an electric motor 7 fixed to the side of the fan casing 4 facing the suction port 2 is provided.

  The impeller 5 includes a plurality of (for example, 47) front blades 9a arranged in a ring on the suction port 2 side (hereinafter referred to as the front side) and the motor 7 side (hereinafter referred to as the back side) of the main plate 8 (for example, 100 mm in diameter). And a rear blade 9b.

  The front blade end face 10a, which is the end face of the front blade 9a, is uniform on the front flat surface Sa perpendicular to the rotary shaft 6 located 40 mm from the center position of the main plate 8 in the direction of the suction port 2, and the rear blade 9b. The rear blade end surface 10b, which is the end surface of the main plate 8, is uniform on the back side plane Sb perpendicular to the rotary shaft 6 located 25 mm in the direction of the electric motor 7 from the center position of the main plate 8, and the outer shape of the impeller 5 is cylindrical. ing. On the outer periphery of the front blade end face 10a, there is provided an outer ring 11 that connects the front blade 9a.

  The main plate 8 includes a main plate hub portion 12 and a main plate outer peripheral portion 13 that is equally divided into six pieces in the rotational direction. The main plate outer peripheral portions 13 are each perpendicular to the rotary shaft 6 and have an interval of 10 mm in the rotary shaft direction. Alternately positioned in the rotational direction, a main plate opening 14 is provided between the main plate hub portion 12 and the main plate outer peripheral portion 13 of the main plate 8.

  In the above configuration, when the impeller 5 is rotated by driving the electric motor 7, the air is boosted by the action of the front-side vane plate 9a and the back-side vane plate 9b. Passes through the front blade 9a, and the remainder flows into the back side of the main plate 8 because the main plate 8 has the main plate opening 14, passes through the back blade 9b, is sent out from the impeller 5 into the fan casing 4, and is blown out from the outlet 3. Air is blown out from.

  At this time, for example, when a DC brushless motor is used as the electric motor 7, an excitation force is generated in the circumferential direction of the rotary shaft 6 during operation, and the excitation frequency changes in proportion to the rotational speed. It has been known. For example, when the excitation frequency is Fm (Hz), the rotation speed is Rm (1 / min), and the coefficient is α, it can be expressed as Fm = α × Rm / 60 (Hz). The coefficient α is determined by the structure of the motor and the drive control method. In the case of a DC brushless motor having a coefficient α of 18, the excitation frequency Fm is 220 (Hz) when the rotational speed Rm is 740 (1 / min).

  The impeller 5 is an integrally injection-molded product made of resin, and the material thereof is, for example, polypropylene (PP), but other thermoreversible resins such as acrylonitrile, butadiene, styrene (ABS) may be used. Because it is made of resin, it has a high vibration damping rate and it is difficult to generate excessive vibration and noise radiation even if the excitation force is transmitted. However, when the resonance phenomenon is excited, it produces a large response to the excitation force and causes excessive vibration. May occur.

  For example, in a conventional impeller 103 as shown in FIG. 9, a plurality of blades 106 having a constant length are arranged annularly only on the front side from the main plate 105, and the main plate 105 side and the suction side end of each blade 106. Since the natural vibration mode in which 108 is twisted to the opposite phase in the circumferential direction is the same for all the blades 106, when the excitation frequency of the motor 7 and Fm overlap with the natural vibration mode, an excellent resonance phenomenon is excited. The

  However, in the impeller 5 of the present embodiment, the position of the main plate outer peripheral portion 13 of the main plate 8 is not uniform in the rotation direction and the outer shape of the impeller 5 is cylindrical. The lengths of the back blades 9b are non-uniform in the rotational direction, and the frequencies of the natural vibration modes in which the front blades 9a and the back blades 9b are twisted in the opposite phase in the circumferential direction with respect to the main plate 8 are dispersed. The excitation of the resonance phenomenon is suppressed, and the generation of noise can be prevented.

  Further, since the outer shape of the impeller 5 is cylindrical, the total length of the front blade 9a and the rear blade 9b of the main plate 8 is uniform in the rotational direction, the balance of the impeller 5 is improved, and the rotational direction The variation of work with respect to the air of the impeller 5 is suppressed, the generation of vibration of the impeller 5 can be suppressed, and the generation of noise due to vibration can be suppressed.

  Further, since the main plate 8 is equally divided in the rotation direction, the balance of the impeller can be improved, the generation of vibration of the impeller 5 can be suppressed, and the generation of noise due to vibration can be suppressed.

  In addition, since the main plate outer peripheral portion 13 of the main plate 8 is perpendicular to the rotation axis, it is possible to suppress deterioration of the rotational balance of the impeller 5 due to air colliding with the front side or the back side of the main plate 8. Generation of vibration of the vehicle 5 can be suppressed, and generation of noise due to vibration can be suppressed.

  Further, since no separate parts such as rubber that insulates vibration are used, the effect of suppressing the resonance phenomenon stably for a long time without deterioration can be obtained.

  In addition, the impeller 5 is a resin-integrated molded product and does not need to be manufactured by separate parts or complicated divided molds. Further, if the outer peripheral ring 11 is only in one direction, it can be molded by a general upper and lower two-side mold, and the cost can be reduced.

(Embodiment 2)
4, the same components as those in FIGS. 1 to 3 are denoted by the same reference numerals, and detailed description thereof is omitted.

  As shown in FIG. 4, the main plate outer peripheral portion 13 of the main plate 8 that is equally divided is inclined in a direction in which air hits the back side of the main plate 8 when the impeller 5 rotates uniformly. (For example, the degree of inclination (inclination angle) is 10 degrees).

  By the said structure, the main-plate outer peripheral part 13 of the inclined main plate 8 can accelerate | stimulate the flow of the air of the direction from the front side of the main plate 8 to a back side, and can improve ventilation efficiency.

  Moreover, since the inclination of each main plate outer peripheral portion 13 is uniform, the rotation balance of the impeller 5 is suppressed from being deteriorated, the vibration of the impeller 5 is suppressed, and the generation of noise due to the vibration is suppressed. be able to.

( Reference Example 1 )
5, the same components as those in FIGS. 1 to 3 are denoted by the same reference numerals, and detailed description thereof is omitted.

As shown in FIG. 5, the main plate 8 of the impeller 5 is disk-shaped, and the number of front side blades 9a and back side blades 9b is 48, respectively. Each of the front blade 9a and the back blade 9b has a configuration in which eight sheets having different thicknesses are arranged in a group and are periodically arranged in the rotation direction. (E.g., eight forming a group may have a thickness, increasing the thickness by 0.15mm from 0.8mm to reverse rotation direction until 1.85 mm).

  With the above configuration, the thicknesses of the front and rear blades 9a and 9b are not uniform in the rotational direction, and the front and rear blades 9a and 9b are twisted in the opposite phase in the circumferential direction with respect to the main plate 8. The frequency of the vibration mode is dispersed and the excitation of the resonance phenomenon is suppressed, so that the generation of noise can be prevented.

  In addition, since a group of non-uniform thicknesses of the front blade 9a and the rear blade 9b is periodically arranged in the rotation direction, the balance of the impeller 5 can be improved, and the vibration of the impeller 5 can be improved. Generation | occurrence | production can be suppressed and there exists an effect that generation | occurrence | production of the noise by vibration can be suppressed.

( Reference Example 2 )
In FIG. 6, the same components as those in FIGS. 1 to 3 are denoted by the same reference numerals, and detailed description thereof is omitted.

  As shown in FIG. 6, the main plate 8 of the impeller 5 has a disk shape, and the number of front side blades 9a and back side blades 9b is 48, respectively. The front blade 9a has a structure in which eight front blade inner diameters Da differ from each other in a group, and is periodically arranged in the rotation direction. Similarly, the rear blade 9b also has eight rear blade inner diameters Db different from each other. As a group, they are arranged periodically in the rotational direction.

  With the above configuration, the front blade inner diameter Da and the rear blade inner diameter Db are non-uniform in the rotational direction, and the natural vibration mode in which the front blade 9a and the rear blade 9b are twisted in the opposite phase in the circumferential direction with respect to the main plate 8. Are dispersed and the excitation of the resonance phenomenon is suppressed, so that the generation of noise can be prevented.

  In addition, since a group of non-uniform front blade inner diameter Da and rear blade inner diameter Db is periodically arranged in the rotation direction, the balance of the impeller 5 can be improved, and the occurrence of vibration of the impeller 5 is suppressed. In addition, generation of noise due to vibration can be suppressed.

( Reference Example 3 )
In FIG. 7, the same components as those in FIGS. 1 to 3 are denoted by the same reference numerals, and detailed description thereof is omitted.

  As shown in FIG. 7, the main plate 8 of the impeller 5 has a disk shape, and the number of front side blades 9a and back side blades 9b is 48, respectively. The front blade 9a has a configuration in which eight sheets having different cross-sectional shapes perpendicular to the rotation shaft 6 are grouped in a group in a rotational direction, and the rear blade 9b is similarly different in cross-section. It is the structure which arrange | positioned the sheet | seat as a group periodically in the rotation direction.

  With the above configuration, the cross-sectional shapes of the front and rear blades 9a and 9b are non-uniform in the rotational direction, and the front and rear blades 9a and 9b are twisted in the opposite phase in the circumferential direction with respect to the main plate 8. The frequency of the natural vibration mode is dispersed and the excitation of the resonance phenomenon is suppressed, so that the generation of noise can be prevented.

  Further, a group of non-uniform cross-sectional shapes of the front blade plate 9a and the back blade plate 9b is periodically arranged in the rotation direction, so that the balance of the impeller 5 can be improved, and the vibration of the impeller 5 can be improved. The generation of noise can be suppressed and the generation of noise due to vibration can be suppressed.

  The multiblade fan according to the present invention is useful as an application for use in a ceiling-embedded ventilation fan used for indoor ventilation. Moreover, it is useful also as a use as air blowers, such as an air conditioning apparatus and an air cleaner.

DESCRIPTION OF SYMBOLS 1 Multiblade blower 2 Intake port 3 Outlet 4 Fan casing 5 Impeller 6 Rotating shaft 7 Electric motor 8 Main plate 9a Front side blade 9b Back side blade 10a Front side blade end surface 10b Back side blade end surface Sa Front side plane Sb Back side plane 11 Outer ring 12 Main plate hub portion 13 Main plate outer peripheral portion 14 Main plate opening portion Fm Excitation frequency Rm Rotational speed α Coefficient Da Front blade inner diameter Db Back blade inner diameter

Claims (1)

A resin impeller comprising a main plate, and a plurality of blades arranged in a ring on the outer peripheral side of the front side and the back side of the main plate, each end face position being uniform on a plane perpendicular to the rotation axis; and the rotation An electric motor connected to a shaft , and a casing including the impeller and including a suction port and a blower outlet, and the main plate is arranged in a circumferential direction so that the frequency of the natural vibration mode due to torsion of the blade plate is dispersed The multi-blade is divided into a plurality of portions, the position of the outer peripheral side in the direction of the rotational axis is made uneven, and the length of the blade plate in the direction of the rotational axis is made uneven on the front side and the back side of the main plate, respectively. Blower.

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