JP2010255450A - Centrifugal blower - Google Patents

Abstract

An object of the present invention is to provide a centrifugal blower that can be used for a ventilation blower or the like to effectively mute a low-frequency main sound source and reduce noise without changing the dimensions of a main body.
An electric motor 8 in which an impeller 7 is connected to be rotatable about a rotating shaft 6 and a scroll casing 12 that surrounds the impeller 7 and has a bell mouth-like suction port 9 are provided in an outer frame 5. A centrifugal blower provided with a spiral second scroll casing 21 so as to form a cavity 19 around the scroll casing 12. The second scroll casing 21 includes an opening 20 facing the suction port 9. In this way, resonance silencing due to air column resonance occurs, and a centrifugal blower that effectively silences the low-frequency main sound source to reduce noise can be obtained.
[Selection] Figure 1

Description

  The present invention relates to a centrifugal blower used for a ventilation blower or the like.

  Conventionally, this type of centrifugal blower is used for a centrifugal blower or the like, and is known to have an orifice on one surface of an outer shell that is different from a suction casing having a bell mouth-like suction port (for example, a patent) Reference 1).

  Hereinafter, the centrifugal blower will be described with reference to FIG.

  As shown in the drawing, an outer casing 101 having an opening on one surface, an electric motor 104 having an impeller 103 fixed to a top surface 102 in the outer casing 101, a casing 105 surrounding the periphery of the impeller 103, and a suction casing having a suction port 106 The centrifugal fan provided with 107 has an orifice 109 having a suction hole 108 that is equal to or smaller than the suction port 106 with a predetermined gap h from the suction casing 107, and a gap dimension between the lower end 110 of the suction casing 107 and the end 111 of the orifice 109. A resonance space 112 is formed by providing i apart. Further, a grill 113 and a discharge port 114 provided on one side of the outer shell 101 are provided on one surface of the orifice 109.

  In the above configuration, when the impeller 103 rotates, the intake air passes from the grill 113 through the suction hole 108 of the orifice 109, enters the impeller 103 through the suction port 106 of the suction casing 107, and is pressurized by the impeller 103. And discharged from the discharge port 114. At this time, rotational noise generated when the pressure is increased by the impeller 103, turbulent noise due to vortex generated when passing through the casing 105, and sound waves of noise generated in the casing 105 are radiated from the suction port 106, and A part of the light enters the resonance space 112 from the entrance 115 having the gap size i. Among sound waves of incident noise, sound waves of a frequency specified by the volume and shape of the resonance space 112 cause air column resonance in the resonance space 112, or the inlet 115 and the resonance space 112 are the Helmholtz resonator. The sound wave having a frequency specified by the volume and shape of the sound absorbing structure is simultaneously resonated by the sound absorbing structure acting as a Helmholtz resonator.

Japanese Patent No. 3479835

  In such a conventional centrifugal blower, it is possible to mute relatively low frequency noise of approximately 1 kHz or less due to the resonance muffling effect, but by combining the frequency range of the main sound source of the centrifugal blower with the frequency range where the muffling effect appears, It is required to reduce a lot of noise.

  The frequency value that can be silenced depends on the dimensions of the resonance space. The larger the resonance space size, the lower the frequency, and if you want to enhance the noise reduction effect on the low frequency side, the frequency value depends on the size of the centrifugal fan body. There is a problem that there is a limit, and it is required to move the silencing effect to the low frequency side while suppressing an increase in the body size.

  The present invention solves such a conventional problem, and while suppressing an increase in the size of the main body, the frequency that can be silenced is moved to the low frequency side, and the frequency range of the main sound source and the frequency range in which the silencing effect appears are obtained. The object is to provide a centrifugal blower that reduces noise by combining them.

  In order to achieve this object, the present invention includes a spiral second scroll casing so as to form a cavity around the scroll casing, and resonance silencing due to air column resonance occurs in the cavity. Thus, the intended purpose is achieved.

  According to the present invention, a centrifugal blower that can reduce noise by moving the frequency that can be silenced to the low frequency side while suppressing the increase in the body size and combining the frequency range of the main sound source and the frequency range in which the silencing effect appears is provided. Can be provided.

(A) is a sectional side view of the centrifugal fan according to Embodiment 1 of the present invention, and (b) is a bottom view of the centrifugal fan. (A) is a bottom view of the centrifugal blower according to Embodiment 2 of the present invention, and (b) is a cross-sectional view of the centrifugal blower at the cut surface A. (A) is a bottom view of the centrifugal blower according to Embodiment 3 of the present invention, and (b) is a cross-sectional view of the centrifugal blower at the cut surface B. Side sectional view of the centrifugal blower of Embodiment 4 of the present invention Side sectional view of the centrifugal blower of Embodiment 5 of the present invention A perspective view of a scroll casing and a second scroll casing according to a sixth embodiment of the present invention. Lower sectional view of centrifugal blower according to Embodiment 7 of the present invention Side sectional view of the centrifugal blower of the eighth embodiment of the present invention. Side sectional view of the centrifugal blower of Embodiment 9 of the present invention A bottom view of the centrifugal fan according to the tenth embodiment of the present invention. Side sectional view showing a conventional centrifugal blower The figure which shows the resonance space cross section of the conventional centrifugal blower

  The centrifugal blower according to claim 1 of the present invention is an impeller that is formed of a top plate and a side plate, and that can be rotated around a rotation shaft inside an outer frame provided with an opening at a position facing the top plate. And a centrifugal blower having a spiral scroll casing surrounding the impeller and having a bell mouth-shaped suction port, and a spiral second scroll casing is formed so as to form a cavity around the scroll casing. The second scroll casing includes an opening facing the suction port, and has a configuration in which resonance silencing due to air column resonance occurs in the cavity. Thereby, in the resonance space formed by the scroll casing and the second scroll casing, the cross-sectional shape by a plane perpendicular to the scroll casing is a pipe shape. At this time, the pipe shape is formed along the scroll casing in order to make the pipe length as long as possible, and the sound wave that is resonated by the air column resonance of the pipe line is in a low frequency region. The noise of the frequency is effectively reduced and the noise is reduced.

  In addition, it is preferable that the thickness of the cavity surrounded by the scroll casing and the second scroll casing is constant. As a result, the flow path width of the cross-sectional shape of the cavity becomes a uniform pipe shape, and when sound waves propagate through the cavity, it is possible to minimize the hindrance to propagation due to changes in the cavity shape, so that air column resonance occurs strongly. And the effect of reducing noise.

  In addition, it is preferable that the thickness of the cavity surrounded by the scroll casing and the second scroll casing is configured such that the thickness in the rotation axis direction is lower than the radial thickness. Thereby, since the size in the vertical direction is reduced, there is an effect that noise is reduced by resonance silence due to air column resonance of the cavity while suppressing the height of the product.

  Further, it is preferable that the thickness of the cavity surrounded by the scroll casing and the second scroll casing is configured such that the thickness in the radial direction is lower than the thickness in the rotation axis direction. As a result, the size in the horizontal direction is reduced and the space between the outer frame and the second scroll casing can be widened. Therefore, it is easy to secure the space for the control board, wiring, etc. There is an effect that noise is reduced by resonance mute.

  Moreover, it is preferable that the upper end portion of the second scroll casing is bent so that a cavity on the top surface side is formed between the top plate and the second scroll casing. Accordingly, the cavity formed by the scroll casing and the second scroll casing is extended by the space of the cavity on the top surface side, so that the silencing effect is greatly moved to the low frequency side without changing the outer frame size. It is possible to effectively reduce low-frequency noise and reduce noise.

  Moreover, it is preferable that the thickness of the cavity on the top surface side is sufficiently larger than the cavity thickness. As a result, the structure is the same as the Helmholtz resonator with the cavity on the top side as the volume and the thickness of the cavity as the gap. Therefore, the silencing effect by the Helmholtz resonator is added to the silencing by the air column resonance, and the noise is reduced. There is an effect.

  In addition, it is preferable that a second cavity is formed between the second scroll casing and the outer frame, and a communication hole that communicates the cavity and the second cavity is provided. Thereby, since the second cavity and the communication hole have the same structure as the Helmholtz resonator, the silencing effect by the Helmholtz resonator is added to the silencing by the air column resonance, and the noise is reduced.

  Further, it is preferable that the communication hole is provided near the tongue portion of the second scroll casing. As a result, there is a large space in the vicinity of the tongue part between the outer frame and the Helmholtz resonator structure formed by the communication hole and the second cavity, so that the volume part can be made large, so that the silencing effect is reduced to the low frequency side. By moving it, the low frequency noise is effectively reduced and the noise is reduced.

  Further, it is preferable that the communication hole is a slit, and the slit is provided below the suction port. As a result, there is a slit at the position where the sound wave enters from the intrusion position, and the sound wave easily enters the second cavity from the slit, so that the silencing effect by the Helmholtz resonator structure becomes easy to work and the noise is reduced. Play.

  Further, it is preferable that the communication holes are a plurality of holes and the holes are distributed over the entire wall surface sandwiched between the cavity and the second cavity. Thereby, resonance silencing by the Helmholtz resonator structure formed by the hole and the second cavity is generated in a wide range, so that a strong silencing effect can be obtained and the noise can be reduced.

  Further, it is preferable that a partition plate standing in the direction of the rotation axis for dividing the cavity is provided, and the partition plate has a second gap between the partition plate and the top plate. As a result, the cavity formed by the casing and the second scroll casing is folded and extended on the top plate side by the partition plate, so that the silencing effect can be greatly moved to the low frequency side without changing the outer frame size. It is possible to effectively reduce low-frequency noise and reduce noise.

  Moreover, it is preferable to make it the structure that a cavity is divided so that thickness may become equal by a partition plate. As a result, the thickness of the cavity, including the cavity that is folded back and extended, becomes constant, so that it is possible to minimize the hindrance to propagation due to the change in the cavity shape, and the air column resonance is strongly generated. There is an effect of reducing.

  In addition, it is preferable that the second gap dimension is smaller than the thickness of the space surrounded by the second scroll casing and the partition plate. As a result, the relationship between the space surrounded by the second scroll casing and the partition plate and the gap becomes the same structure as that of the Helmholtz resonator, so that the silencing effect by the Helmholtz resonator structure is added to the silencing effect by the air column resonance. There is an effect of reducing.

  Moreover, it is preferable to provide a partition plate standing in the direction of the rotation axis that divides the cavity, and the partition plate includes a second gap between the partition plate and the second scroll casing. Thereby, since the cavity is divided into two types of cavities, the sound wave having a new frequency is silenced by the air column resonance, and the noise is reduced.

  Further, it is preferable that the cavity is divided by the partition plate so that the thickness is equal, and the cavity thickness in the rotation axis direction between the scroll casing and the second scroll casing is equal to the divided cavity thickness. As a result, the thicknesses of the cavities formed by each wall surface are all equal, so that the noise reduction effect that was previously provided before the division and the noise reduction effect that is newly added by the division of the cavity can be demonstrated in a balanced manner. There is an effect of reducing.

  Moreover, it is preferable to make it the structure that the lower end of a partition plate is lower than the lower end of a scroll casing. As a result, the second gap is smaller than the thickness of the cavity, and the structure is equivalent to a Helmholtz resonator whose volume is the space outside the partition plate. Therefore, the silencing effect by the Helmholtz resonator structure is in addition to the silencing effect by the air column resonance. It is added and produces the effect of reducing noise.

  Moreover, it is preferable to make it the structure that an opening part and a suction inlet are concentric circles. Thereby, since air can be smoothly guided into the scroll casing, an effect of reducing noise can be achieved.

  Moreover, it is preferable that the opening is larger than the suction port. Thereby, when air flows in, since the opening is larger than the suction port, the opening flows smoothly without being inflow resistance, so that the noise is reduced.

  Moreover, it is preferable that the opening is smaller than the suction port. As a result, the noise radiated from the suction port is less likely to be radiated to the outside through the opening, and the sound wave of the noise is more easily guided to the cavity. The effect of doing.

  In addition, it is preferable that the opening and the suction port have the same diameter. As a result, the resistance at the time of air inflow is suppressed as much as possible, and the sound wave of noise is relatively easily guided to the cavity, so that the air is smoothly guided into the scroll casing, and resonance silencing due to air column resonance is suppressed. Since it becomes easy to work, there is an effect of reducing noise.

  Moreover, it is preferable to make it the structure that the distance from the approach position of a sound wave to the innermost position reflected is uniform. As a result, the frequency at which air column resonance occurs, which is determined by the length of the deepest position reflected from the incident position of the sound wave, is constant, so that resonance silencing due to air column resonance occurs strongly at a single frequency, Since the sound wave of a frequency is strongly silenced, there exists an effect of reducing noise.

  Further, it is preferable that the distance from the sound wave intrusion position to the innermost position to be reflected is non-uniform. As a result, the frequency at which air column resonance occurs, which is determined by the length of the innermost position reflected from the incident position of the sound wave, varies, so that resonance muting due to air column resonance occurs at various frequencies, and sound waves in a wide range of frequencies. As a result, the noise is reduced.

  Moreover, it is preferable to provide a configuration in which a dividing plate that divides the cavity into a plurality along the scroll is provided. As a result, the cavity is divided into several types by the dividing plate, and each has a unique silencing effect, so that noises of various frequencies are silenced and the noise is reduced.

  Further, it is preferable that the dividing plates are provided at equal intervals along the scroll. As a result, a plurality of spaces of the same size are formed by the divided plates, so that the silencing characteristics of the divided spaces can be generated strongly, and the effect of reducing noise can be achieved.

  Further, it is preferable that the dividing plates are provided at equal intervals along the scroll with a space thickness. As a result, the cavities are subdivided and pipes having a square cross section are arranged along the scroll, so that silencing due to air column resonance occurs in the individual pipes, resulting in strong resonance muting and reducing noise. There is an effect.

  Moreover, it is preferable that the opening has a bell mouth shape. Thereby, since air is smoothly guide | induced into a scroll casing, there exists an effect of reducing a noise.

  In addition, the space from the opening to the lower end of the second scroll casing is provided with an orifice having a bell mouth-shaped opening at a position facing the opening, closing the opening of the outer frame, It is preferable that a third gap be provided between the scroll casing and the scroll casing. As a result, the resonance space enclosed by the orifice and the second scroll casing and the third gap add silence due to air column resonance and resonance silence due to the Helmholtz resonator structure. Are generated at the same time, which has the effect of reducing noise.

  In addition, it is preferable that a sound absorbing material is provided in the space from the opening to the lower end of the second scroll casing. Thereby, since the sound absorbing material is provided in the vacant space, a noise reduction effect by the sound absorbing material is newly added, and an effect of reducing noise is achieved.

  In addition, it is preferable to employ a configuration in which a sound deadening mechanism using active noise control (hereinafter abbreviated as ANC) is provided in a space from the opening to the lower end of the second scroll casing. Thereby, since the silencing effect by ANC is added, there exists an effect of reducing a noise.

  In addition, it is preferable that a sound absorbing material is provided inside the cavity. Thereby, since the silencing effect by the air column resonance and the silencing effect by the sound absorbing material act on the sound wave entering the inside of the cavity, there is an effect of reducing noise.

  In addition, it is preferable that a sound absorbing material is provided in a space between the second scroll casing and the outer frame. Thereby, since the silencing effect by a sound-absorbing material is added, there exists an effect of reducing a noise.

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

(Embodiment 1)
FIG. 1A is a side sectional view of the centrifugal blower according to Embodiment 1 of the present invention, FIG. 1B is a bottom view of the centrifugal blower, and as shown in FIG. 1A and FIG. A centrifugal blower 1 used as a built-in ventilation fan is formed by a top plate 2 and a side plate 3, and can be rotated around a rotation shaft 6 in an outer frame 5 having an opening 4 in a lower portion facing the top plate 2. An electric motor 8 having a multi-blade type impeller 7 connected thereto, and a spiral scroll casing 12 which surrounds the periphery of the impeller 7 and has a bell mouth-like suction port 9 and a discharge port 11 on a side wall 10 are provided. The scroll casing 12 and the discharge port 11 communicate with the discharge adapter 14 via a discharge opening 13 provided on one side surface of the outer frame 5.

  There is a flange portion 15 on the outer periphery of the lower surface of the outer frame 5, and the outer frame 5 is fixed to the ceiling material 17 with a screw or the like through a hole 16 provided in the flange portion 15, and is arranged on the ceiling and communicates with the outside. Is joined to the discharge port 11 via the discharge adapter 14. Further, a bell mouth-shaped opening is formed in a position that is concentric with the inlet 9 inside the outer frame so as to form a cavity 19 between the scroll casing 12 and a position spaced apart from the scroll casing 12. A second scroll casing 21 having a portion 20 is provided. The cavity 19 is formed along the circumference of the scroll casing 12, and becomes a pipe cross-sectional cavity having a shape of an elongated pipe having a pipe length L1. Further, since the distance between the scroll casing 12 and the second scroll casing 21 is constant, the cavity thickness D1 of the cavity 19 is constant. In the pipe cross section of the cavity 19, corner portions of the scroll casing 12 and the second scroll casing 21 where the pipe is bent are each subjected to fillet processing, and the cavity thickness is also D1 in this part.

  In the above configuration, when the impeller 7 is rotated by the electric motor 8, the intake air passes through the opening 20 of the second scroll casing 21 from the opening 4 and enters the impeller 7 through the suction port 9 of the scroll casing 12. The pressure is increased, passes through the inside of the scroll casing 12, is discharged from the discharge adapter 14 to the exhaust duct 18, and is discharged outdoors.

  Furthermore, rotational noise generated when the pressure is increased by the impeller 7, turbulent noise caused by vortices generated when passing through the inside of the scroll casing 12, and sound waves of noise amplified by resonance in the scroll casing 12, Radiated downward from the suction port 9.

  According to such a configuration, a part of the sound wave of the noise radiated from the suction port 9 of the scroll casing 12 is transmitted from the gap portion 22 formed between the opening 20 of the second scroll casing 21 and the scroll casing 12. The light enters the cavity 19. The incident sound wave becomes an anti-phase sound wave by reflection at the fixed end of the cavity 19 at the innermost end 23 of the cavity 19 and returns to the gap portion 22, and resonance silence due to air column resonance that cancels a part of the sound wave emitted from the suction port 9 occurs. Here, as shown in FIG. 12, in the sectional view of the resonance space 112 in the centrifugal blower of the conventional example, the part where the noise reduction due to the air column resonance in the hollow of the pipe cross-sectional shape occurs is the pipe length L2. . On the other hand, the pipe length formed by the second scroll casing 21 is L1, which is longer than the conventional example by the length on the lower surface side of the scroll casing 12.

  In addition, since the length L1 of the pipe line varies depending on the position of the cross section of the lower surface side of the scroll casing 12, the distance from the sound wave entry position to the innermost reflection position is not uniform. At this time, in resonance silencing by air column resonance, the frequency of the sound wave in which resonance silencing occurs is lower as the length of the pipe is longer. Therefore, low frequency noise is effectively reduced and noise is reduced. be able to.

  Further, since the cavity thickness D1 of the cavity 19 is constant, when the sound wave entering from the gap portion 22 propagates through the cavity 19, it is possible to suppress the hindrance to propagation due to the change in the shape of the cavity 19 as much as possible. Is strongly generated and noise can be reduced.

  Note that the thickness of the cavity 19 may be configured such that the thickness in the direction of the rotation axis 6 is lower than the thickness in the radial direction. As a result, the size of the second scroll casing 21 in the direction of the rotation axis 6, that is, in the vertical direction is reduced, and noise can be reduced by suppressing the height of the product, and by resonance silence due to air column resonance of the cavity.

  Note that the thickness of the cavity 19 may be configured such that the radial thickness is lower than the thickness in the direction of the rotation axis 6. Thereby, the size of the second scroll casing 21 in the radial direction, that is, the horizontal direction is reduced, and the space between the outer frame 5 and the second scroll casing 21 can be widened, and the space for the control base, wiring, etc. can be secured. While facilitating the noise, the noise can be reduced by resonance silencing by the air column resonance of the cavity 19.

  Moreover, since the opening part 20 is concentric with the suction inlet 9, air can be smoothly guide | induced into the scroll casing 12 and a noise can be reduced.

  Further, since the opening 20 and the suction port 9 have the same diameter, the resistance at the time of air inflow is suppressed as much as possible, and sound waves of noise are relatively easily guided to the cavity 19, and noise can be reduced.

  The opening 20 may be configured to be larger than the suction port 9. Thereby, when air flows in, since the opening 20 is larger than the suction port 9, the opening 20 smoothly flows in without being inflow resistance, so that noise can be reduced.

  The opening 20 may be smaller than the suction port 9. Thereby, the noise radiated from the suction port 9 is blocked by the opening 20 and is not easily radiated to the outside. Further, since the sound wave of the noise is easily guided to the cavity 19, the noise can be reduced.

  In addition, since the distance from the sound wave intrusion position to the innermost reflection position is non-uniform, the frequency at which air column resonance occurs depends on the length of the innermost reflection position from the sound wave incident position varies. Therefore, resonance silence due to air column resonance occurs at various frequencies, and sound waves in a wide range of frequencies are silenced, so that noise can be reduced.

  Further, since the opening 20 has a bell mouth shape, air can be smoothly guided into the scroll casing 12, and noise can be reduced.

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

  2 (a) is a bottom view of the centrifugal blower according to Embodiment 2 of the present invention, (b) is a cross-sectional view of the centrifugal blower at the cut surface A, and in FIG. 2 (b), the second scroll casing 21 is The top surface plate 2 side is bent so as to be parallel to the top surface plate 2, and a top surface side cavity 19 is formed between the top surface plate 2 and the top surface plate 2. Further, since the cavity thickness D2 on the top surface side of the cavity 19 on the top surface side is larger than the cavity thickness D1, it is equivalent to a Helmholtz resonator having a cavity thickness D1 portion as a gap and the top surface side cavity 19 as a volume. A structure is formed.

  In the above configuration, since the cavity 19 formed by the scroll casing 12 and the second scroll casing 21 is extended by the space of the cavity 19 on the top surface side, the silencing effect is reduced without changing the dimensions of the outer frame 5. It can be moved greatly to the frequency side, low frequency noise can be effectively reduced, and noise can be reduced.

  Moreover, since the structure is the same as that of a Helmholtz resonator with the cavity 19 on the top surface as a volume and the thickness of the cavity 19 as a gap, the silencing effect by the Helmholtz resonator is added to the silencing by the air column resonance, thereby reducing noise. can do.

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

  3A is a bottom view of the centrifugal blower according to Embodiment 3 of the present invention, FIG. 3B is a cross-sectional view of the centrifugal blower B taken along the cut surface B, and in FIG. An additional plate 25 is provided so as to form a second cavity 24 between the outer frame 5 and a slit 26 communicating the cavity 19 and the second cavity 24. The slit 26 is provided in the vicinity of the tongue portion 28 and below the suction port 9. As shown in FIG. 3A, in the vicinity of the tongue portion 28, there is a large space between the outer frame 5 and the second scroll casing 21, and the second cavity 24 can be formed larger than other places. it can.

  Since the second cavity 24 and the slit 26 have the same structure as that of the Helmholtz resonator in the above configuration, the silencing effect by the Helmholtz resonator is added to the silencing by the air column resonance, and the noise can be reduced.

  Further, since the slit 26 is provided in the vicinity of the tongue portion 28, the volume portion can be increased in the Helmholtz resonator structure. The frequency of the sound wave that is resonated and muffled by the Helmholtz resonator becomes lower as the volume is larger. Therefore, the muffling effect can be moved to the low frequency side, effectively reducing low frequency noise and reducing noise. Can be reduced.

  Further, since the slit 26 is provided below the suction port 9, the sound wave that has entered the cavity 19 from the gap portion 22 reaches the slit 26 only by going straight, so that the sound wave is easily guided to the slit 26. Therefore, the resonance muffling by the Helmholtz resonator composed of the slit 26 and the second cavity 24 is strongly generated, so that the noise can be reduced.

  Instead of the slits 26, a plurality of holes 27 may be distributed over the entire wall surface sandwiched between the cavities 19 and the second cavities 24. As a result, resonance silencing by the Helmholtz resonator structure formed by the hole 27 and the second cavity 24 is generated in a wide range, so that a strong silencing effect can be obtained and noise can be reduced.

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

  FIG. 4 is a side sectional view of a centrifugal blower according to Embodiment 4 of the present invention. In FIG. 4, a partition plate 29 standing in the direction of the rotary shaft 6 is provided in the cavity 19, and the lower end of the partition plate 29 is the second. Connected to the scroll casing 21, the upper end is provided with a second gap portion 30 between the top plate 2. In addition, the cavity 19 divided by the partition plate 29 has a constant thickness of the cavity 19.

  In the above configuration, the partition plate 29 causes the cavity 19 formed by the scroll casing 12 and the second scroll casing 21 to be folded back on the top plate 2 side, and is extended by the length of the folded back. Without changing the size of the frame 5, the silencing effect can be greatly moved to the low frequency side, and noise can be reduced.

  In addition, since the thickness of the cavity 19 is constant, when the sound wave propagates through the cavity 19, it is possible to prevent the propagation of the sound due to the change in the shape of the cavity 19 as much as possible, so that air column resonance is strongly generated and noise is reduced. can do.

  In addition, you may make it the structure that the dimension of the 2nd gap | interval part 30 is small enough with respect to the thickness of the space enclosed by the 2nd scroll casing 21 and the partition plate 29. FIG. As a result, the relationship between the space surrounded by the second scroll casing 21 and the partition plate 29 and the second gap 30 is the same as that of the Helmholtz resonator. An effect is added and noise can be reduced.

(Embodiment 5)
5, the same components as those in FIG. 1 are denoted by the same reference numerals, and detailed description thereof is omitted.

  5 is a side sectional view of a centrifugal blower according to Embodiment 5 of the present invention. In FIG. 5, a partition plate 29 standing in the direction of the rotary shaft 6 is provided in the cavity 19, and the upper end of the partition plate 29 is a top plate. 2, and the lower end is provided with a second gap 30 between the second scroll casing 21. Further, the partition plate 29 divides the cavity 19 equally, and the thickness of the cavity 19 between the scroll casing 12 and the second scroll casing 21 in the rotation axis direction and the dimension of the second gap 30 are divided. The thickness of the cavity 19 is generally constant.

  In the above-described configuration, a new cavity 19 having different pipe lengths is formed by being divided by the partition plate 29, so that two types of cavities are formed. Can be reduced.

  Moreover, since all the thicknesses of the cavities 19 formed by the respective wall surfaces are equal, it is possible to exert a good balance between the silencing effect that is conventionally provided before the division and the silencing effect that is newly added by the division of the cavities 19, Noise can be reduced.

  Note that the lower end of the partition plate 29 may be lower than the lower end of the scroll casing 12. As a result, the second gap portion 30 becomes smaller than the thickness of the cavity and becomes a structure equivalent to a Helmholtz resonator whose volume is the space outside the partition plate 29. Therefore, the silencing effect by air column resonance is due to the Helmholtz resonator structure. Noise reduction effect is added and noise can be reduced.

(Embodiment 6)
6, the same components as those in FIG. 1 are denoted by the same reference numerals, and detailed description thereof is omitted.

  FIG. 6 is a perspective view of the scroll casing 12 and the second scroll casing 21 according to the sixth embodiment of the present invention. In FIG. 6, the pipe length is constant with respect to the cavity 19 having a pipe cross-sectional shape. The position of the cavity innermost end 23 changes in a slope shape along the scroll portion.

  In the above configuration, the frequency at which air column resonance occurs, which is determined by the length of the innermost end 23 of the cavity reflected from the incident position of the sound wave, is constant, so that resonance silencing due to air column resonance is strongly generated at a single frequency. And since the sound wave of a single frequency is strongly silenced, noise can be reduced.

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

  FIG. 7 shows a lower cross-sectional view of the centrifugal fan according to the seventh embodiment of the present invention. In FIG. 7, a split plate 31 is provided in the cavity 19 to divide the cavity 19 into a plurality along the scroll. The dividing plates 31 are provided at equal intervals along the scroll, and are provided at intervals equivalent to the thickness of the cavity 19. The divided cavities have a square cross-sectional shape by a plane perpendicular to the direction of the rotation axis 6. It has the same shape as

  In the above configuration, the cavity 19 is divided into several types by the dividing plate 31, and each has a unique silencing effect. Therefore, noises of various frequencies can be silenced and noise can be reduced.

  In addition, since a plurality of spaces of the same size are formed by the dividing plate 31, it is possible to strongly generate the silencing characteristics of the divided spaces and to reduce noise.

  In addition, since the cavity 19 is subdivided and a pipe having a square cross section is arranged along the scroll, noise suppression due to air column resonance occurs in each pipe, and strong resonance noise reduction is obtained and noise is reduced. be able to.

(Embodiment 8)
8, the same components as those in FIG. 1 are denoted by the same reference numerals, and detailed description thereof is omitted.

  FIG. 8 is a side sectional view of the centrifugal blower according to the eighth embodiment of the present invention. In FIG. 8, the opening 4 of the outer frame 5 is closed in the space from the opening 4 to the lower end of the second scroll casing 21. An additional orifice 32 having a bell mouth-shaped second opening 34 is provided at an opposing position, and a third gap 33 is provided between the bell mouth-shaped end portion and the second scroll casing 21.

  In the above configuration, the resonance space surrounded by the additional orifice 32 and the second scroll casing 21 and the third gap 33 form a structure equivalent to the Helmholtz resonator. Therefore, the air column resonance caused by the cavity 19 between the scroll casing 12 and the second scroll casing 21 and the resonance silence due to the Helmholtz resonator structure formed by the additional orifice 32 and the second scroll casing 21 are simultaneously generated, thereby reducing noise. can do.

  In addition, you may make it the structure of providing a sound absorption material in the space from the opening 4 to the 2nd scroll casing 21 lower end. Thereby, the silencing effect by the sound absorbing material is added, and the noise can be reduced.

  A space from the opening 4 to the lower end of the second scroll casing 21 may be provided with an ANC silencer mechanism using active noise control (hereinafter abbreviated as ANC). Thereby, the silencing effect by ANC is added, and noise can be reduced.

(Embodiment 9)
9, the same components as those in FIG. 1 are denoted by the same reference numerals, and detailed description thereof is omitted.

  FIG. 9 is a side sectional view of a centrifugal blower according to Embodiment 9 of the present invention. In FIG. 9, a sound absorbing material 35 is provided inside the cavity 19.

  In the above configuration, since the sound deadening effect by the air column resonance and the sound deadening effect by the sound absorbing material act on the sound wave that has entered the inside of the cavity 19, noise can be reduced.

(Embodiment 10)
10, the same components as those in FIG. 1 are denoted by the same reference numerals, and detailed description thereof is omitted.

  FIG. 10 is a bottom view of the centrifugal blower according to the tenth embodiment of the present invention. In FIG. 10, a sound absorbing material is provided in the space between the second scroll casing 21 and the outer frame 5.

  In the said structure, since the silencing effect by the sound-absorbing material 35 is added, there exists an effect of reducing a noise.

  The centrifugal blower according to the present invention reduces the noise by moving the frequency that can be muffled to the low frequency side while suppressing an increase in the size of the main body, and combining the frequency range of the main sound source and the frequency range where the mute effect appears. Therefore, it can be used particularly for air-conditioning equipment and ventilation / air-blowing equipment.

DESCRIPTION OF SYMBOLS 1 Centrifugal blower 2 Top plate 3 Side plate 4 Opening 5 Outer frame 6 Rotating shaft 7 Impeller 8 Electric motor 9 Suction port 10 Side wall 11 Discharge port 12 Scroll casing 13 Discharge opening 14 Discharge adapter 15 Flange part 16 Hole 17 Ceiling material 18 Exhaust duct 19 cavity 20 opening 21 second scroll casing 22 gap 23 cavity innermost end 24 second cavity 25 additional plate 26 slit 27 hole 28 tongue 29 partition plate 30 second gap 31 split plate 32 additional orifice 33 third gap Part 34 Second opening 35 Sound absorbing material L1 Pipe length L2 Pipe length D1 Cavity thickness D2 Cavity thickness on the top side

Claims (31)

An electric motor formed by a top plate and a side plate, and having an impeller connected to the inside of an outer frame having an opening at a position facing the top plate, and capable of rotating about a rotation shaft, and the periphery of the impeller A centrifugal blower having a spiral scroll casing having a bell mouth-like suction port, and having a spiral second scroll casing so as to form a cavity around the scroll casing, the second scroll casing is A centrifugal blower comprising an opening facing the suction port, wherein resonance silencing due to air column resonance occurs in the cavity. The centrifugal blower according to claim 1, wherein a thickness of a cavity surrounded by the scroll casing and the second scroll casing is constant. 2. The centrifugal blower according to claim 1, wherein the thickness of the cavity surrounded by the scroll casing and the second scroll casing is set to be smaller in the rotation axis direction than in the radial direction. 2. The centrifugal blower according to claim 1, wherein a thickness of a cavity surrounded by the scroll casing and the second scroll casing is reduced in a radial thickness as compared with a thickness in a rotation axis direction. The centrifugal blower according to any one of claims 1 to 4, wherein an upper end portion of the second scroll casing is bent so that a cavity on the top surface side is formed between the top plate and the second scroll casing. . The centrifugal blower according to claim 5, wherein the thickness of the cavity on the top surface side is sufficiently larger than the thickness of the cavity. The centrifugal blower according to claim 1, further comprising a communication hole that forms a second cavity between the second scroll casing and the outer frame and communicates the cavity with the second cavity. The centrifugal blower according to claim 8, wherein the communication hole is provided in the vicinity of the tongue portion of the second scroll casing. The centrifugal blower according to claim 7 or 8, wherein the communication hole is a slit, and the slit is provided below the suction port. The centrifugal blower according to claim 7, wherein the communication holes are a plurality of holes, and the holes are distributed over the entire wall surface sandwiched between the cavity and the second cavity. The centrifugal blower according to any one of claims 1 to 10, further comprising a partition plate erected in a direction of a rotation axis that divides the cavity, wherein the partition plate includes a second gap between the partition plate and the top plate. The centrifugal blower according to claim 11, wherein the cavity is divided by the partition plate so as to have the same thickness. The centrifugal blower according to claim 11, wherein the second gap dimension is smaller than the thickness of the space surrounded by the second scroll casing and the partition plate. The centrifugal separator according to any one of claims 1 to 10, further comprising: a partition plate erected in a rotation axis direction that divides a cavity, wherein the partition plate includes a second gap between the partition plate and the second scroll casing. Blower. The cavity is divided by the partition plate so as to have the same thickness, and the cavity thickness in the rotation axis direction between the scroll casing and the second scroll casing is equal to the divided cavity thickness. The centrifugal blower described in The centrifugal blower according to claim 14, wherein the lower end of the partition plate is lower than the lower end of the scroll casing. The centrifugal blower according to claim 1, wherein the opening and the suction port are concentric circles. The centrifugal blower according to any one of claims 1 to 17, wherein the opening is larger than the suction port. The centrifugal blower according to any one of claims 1 to 17, wherein the opening is smaller than the suction port. The centrifugal blower according to claim 1, wherein the opening and the suction port have the same diameter. The centrifugal blower according to any one of claims 1 to 20, wherein a distance from a sound wave entrance position to a deepest position to be reflected is uniform. The centrifugal blower according to any one of claims 1 to 20, wherein a distance from a sound wave intrusion position to a deepest position to be reflected is non-uniform. The centrifugal blower according to any one of claims 1 to 22, further comprising a dividing plate that divides the cavity into a plurality along the scroll. The centrifugal blower according to claim 23, wherein the divided plates are provided at equal intervals along the scroll. The centrifugal blower according to claim 25, wherein the dividing plates are provided at equal intervals along the scroll with a space thickness. The centrifugal blower according to any one of claims 1 to 28, wherein the opening has a bell mouth shape. In the space from the opening to the lower end of the second scroll casing, the opening of the outer frame is closed, and an orifice having a bell mouth-shaped opening is provided at a position facing the opening, the bell mouth-shaped end, and the second scroll casing A centrifugal blower according to any one of claims 1 to 28, further comprising a third gap therebetween. The centrifugal blower according to any one of claims 1 to 28, further comprising a sound absorbing material in a space from the opening to the lower end of the second scroll casing. The centrifugal blower according to any one of claims 1 to 28, further comprising a silencer mechanism using active noise control in a space from the opening to the lower end of the second scroll casing. The centrifugal blower according to any one of claims 1 to 31, wherein a sound absorbing material is provided inside the cavity. The centrifugal blower according to any one of claims 1 to 31, further comprising a sound absorbing material in a space between the second scroll casing and the outer frame.

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