WO2009130891A1 - Centrifugal fan and method of reducing noise of centrifugal fan - Google Patents
Centrifugal fan and method of reducing noise of centrifugal fan Download PDFInfo
- Publication number
- WO2009130891A1 WO2009130891A1 PCT/JP2009/001819 JP2009001819W WO2009130891A1 WO 2009130891 A1 WO2009130891 A1 WO 2009130891A1 JP 2009001819 W JP2009001819 W JP 2009001819W WO 2009130891 A1 WO2009130891 A1 WO 2009130891A1
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- centrifugal blower
- suction port
- protrusions
- outer shell
- protrusion
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- 238000000034 method Methods 0.000 title claims description 5
- 230000001603 reducing effect Effects 0.000 title description 5
- 230000001154 acute effect Effects 0.000 claims description 4
- 239000011358 absorbing material Substances 0.000 claims description 3
- 238000010276 construction Methods 0.000 abstract 1
- 230000000694 effects Effects 0.000 description 37
- 230000001788 irregular Effects 0.000 description 13
- 230000001965 increasing effect Effects 0.000 description 4
- 230000004048 modification Effects 0.000 description 4
- 238000012986 modification Methods 0.000 description 4
- 230000000052 comparative effect Effects 0.000 description 3
- 230000007423 decrease Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000009423 ventilation Methods 0.000 description 2
- 241000135309 Processus Species 0.000 description 1
- 230000005534 acoustic noise Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000002708 enhancing effect Effects 0.000 description 1
- 230000030279 gene silencing Effects 0.000 description 1
- 239000011491 glass wool Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000009751 slip forming Methods 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/663—Sound attenuation
- F04D29/664—Sound attenuation by means of sound absorbing material
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/663—Sound attenuation
- F04D29/665—Sound attenuation by means of resonance chambers or interference
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- G—PHYSICS
- G10—MUSICAL INSTRUMENTS; ACOUSTICS
- G10K—SOUND-PRODUCING DEVICES; METHODS OR DEVICES FOR PROTECTING AGAINST, OR FOR DAMPING, NOISE OR OTHER ACOUSTIC WAVES IN GENERAL; ACOUSTICS NOT OTHERWISE PROVIDED FOR
- G10K11/00—Methods or devices for transmitting, conducting or directing sound in general; Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
- G10K11/16—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
- G10K11/172—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general using resonance effects
Definitions
- the present invention relates to a centrifugal blower used for a ventilation blower and the like, and a noise reduction method for a centrifugal blower that reduces noise generated by the operation of the centrifugal blower.
- 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).
- the centrifugal blower 100 includes an outer shell 101 that is open on one surface, an impeller 103 that is rotatably supported by the top surface 102 in the outer shell 101, and an impeller 103 that is fixed to the top surface 102.
- An electric motor 104 that rotates the motor, a scroll casing 105 that surrounds the impeller 103, and a suction casing 107 that has a suction port 106.
- the centrifugal blower 100 includes 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.
- the orifice 109 is provided with the lower end 110 of the suction casing 107 and the end 111 of the orifice 109 separated by a gap dimension i.
- the resonance space 112 communicated with the suction port 106 through the inlet portion 115 between the lower end 110 of the suction casing 107 and the end portion 111 of the orifice 109 is defined by the outer shell 101, the scroll casing 105, and the orifice 109.
- the centrifugal blower 100 includes a grill 113 disposed on one surface of the orifice 109 and a discharge port 114 provided on one side surface of the outer shell 101.
- a relatively low frequency noise of approximately 1 kHz or less can be reduced by the resonance silence effect, but a relatively low frequency noise reduction effect of approximately 1 kHz or more such as noise caused by turbulent flow is low. . Therefore, there is a problem that the amount of noise reduction is small when high-frequency noise is dominant, such as when the amount of air blown by the centrifugal blower is large. Therefore, the centrifugal blower is required to enhance the noise reduction effect in the high frequency range and reduce noise in a wide frequency range from low frequency to high frequency.
- the present invention solves such a conventional problem, and in a centrifugal blower, the noise reduction effect in the high frequency range can be enhanced, noise can be reduced in a wide frequency range from low frequency to high frequency, and noise can be reduced. It aims at providing the centrifugal blower which reduces.
- the present invention is configured as follows.
- the outer shell having the opening, the impeller supported rotatably in the outer shell, the electric motor that rotationally drives the impeller, the first suction port, and the blade It is arranged at the opening of the outer shell so as to have a gap between the casing disposed in the outer shell so as to surround the periphery of the vehicle and the first suction port of the casing, and the opening of the outer shell and the first of the casing A bell mouth-shaped orifice having a second suction port communicating with the suction port, and communicated with the first suction port through a gap between the first suction port and the second suction port.
- a centrifugal blower in which a resonance space that resonates and muffles noise emitted from one suction port is defined with an orifice, a casing, and an outer wall as a defining wall, and a plurality of protrusions are provided on the defining wall of the resonance space.
- each of the plurality of protrusions has an inclined surface that is inclined with respect to the defining wall surface of the resonance space at each of the formation positions.
- the centrifugal blower according to the first aspect is provided, in which a slope of another projection adjacent to the projection is connected to each other, and a recess is formed between the projections by each slope.
- centrifugal blower according to the second aspect, wherein an angle of a connection portion of each inclined surface in the recess is an acute angle.
- the protruding portion provides the centrifugal blower according to the second aspect, which has a flat surface at the top.
- the centrifugal blower according to the second aspect wherein the protrusion has a shape whose depth is long with respect to its height and width.
- the plurality of protrusion groups in which the plurality of protrusions are arranged with the depth direction parallel to each other are arranged such that the depth directions of adjacent protrusion groups intersect each other.
- the centrifugal blower according to the fifth aspect is provided.
- a plurality of protrusion groups in which a plurality of protrusions are arranged in parallel in the depth direction are arranged so that each depth direction is different.
- the plurality of recesses formed between the plurality of protrusions are formed so as to extend along the defining wall surface, and are at least in the radial direction, the circumferential direction, and the axial direction of the impeller.
- the centrifugal blower according to the fifth aspect is provided in which the extending directions of the respective recesses are arranged differently with respect to one direction.
- any of the first to eighth aspects has the same shape of the plurality of protrusions and the same shape of the plurality of recesses formed between the plurality of protrusions.
- a centrifugal blower according to claim 1 is provided.
- any one of the first to eighth aspects there are a plurality of types of protrusions and a plurality of types of recesses formed between the plurality of protrusions.
- a centrifugal blower as described is provided.
- the centrifugal blower according to any one of the first to eighth aspects, wherein a plurality of protrusions are provided on the orifice in the resonance space.
- the plurality of protrusions are formed integrally with an orifice, a casing, or a demarcating wall of the outer shell, and the centrifuge according to any one of the first to eighth aspects.
- the centrifugal blower according to any one of the first to eighth aspects, wherein the protrusion is detachably installed on the defining wall.
- the centrifugal blower according to the thirteenth aspect, wherein the protrusion is formed of a sound absorbing material.
- any one of the first to eighth aspects is provided, wherein the protrusion is formed with a hollow inside, and a hole communicating the cavity and the resonance space is formed in the protrusion.
- a centrifugal blower according to claim 1 is provided.
- the outer shell having the opening, the impeller rotatably supported in the outer shell, the first suction port, and surrounding the periphery of the impeller Is disposed in the opening of the outer shell so as to have a gap between the casing disposed in the casing and the first suction port of the casing, and the second opening for communicating the opening of the outer shell and the first suction port of the casing.
- a centrifugal blower including a bell mouth-shaped orifice having a suction port
- the first suction port is communicated with the first suction port through a gap between the first suction port and the second suction port to define the orifice, the casing, and the outer shell.
- a sound wave of noise generated in the casing as the impeller is driven to rotate is incident through a gap between the first suction port and the second suction port into the resonance space defined as a wall, Incident on
- the level of the sound wave of the sound as well as to reduce the air column resonance, thereby reducing the level of acoustic noise by diffused reflection of the acoustic waves of noise at the resonant space, provides a noise reduction method of the centrifugal blower.
- a resonance space communicating with the first suction port of the casing is provided, and a configuration in which a plurality of protrusions are provided in the resonance space is employed.
- noise generated by the operation of the centrifugal blower is incident on the resonance space communicated with the first suction port of the casing of the centrifugal blower to enter the resonance space.
- the sound wave level of the incident noise can be reduced by air column resonance.
- the sound wave level can be reduced by irregularly reflecting the sound wave of noise in the resonance space. Therefore, the two effects of air column resonance and irregular reflection can enhance the noise reduction effect in the high frequency range of noise associated with the operation of the centrifugal blower, and reduce the noise in a wide frequency range from low frequency to high frequency.
- FIG. 2A It is a model perspective view which shows the shape of the permite
- FIG. 1A A schematic cross-sectional view of the centrifugal blower 1 according to the first embodiment of the present invention is shown in FIG. 1A, and a partially enlarged view of a portion X in FIG. 1A is shown in FIG. 1B.
- a centrifugal blower 1 used as a ceiling-embedded ventilation fan has a multi-blade impeller that can rotate around a rotating shaft 4 in an outer shell 3 having an opening 2 on a lower surface.
- a casing 10 having a bell mouth-like suction port 7 (first suction port) in the opening and a discharge port 9 in the side wall 8. ing.
- the discharge port 9 of the casing 10 communicates with the discharge adapter 12 through a discharge opening 11 provided on one side surface of the outer shell 3.
- a flange portion 13 is provided on the outer periphery of the lower surface of the outer shell 3, and the outer shell 3 is fixed to the ceiling material 15 with screws or the like through a hole 14 provided in the flange portion 13, and a duct 16 disposed on the ceiling and communicating with the outside is discharged. It is joined to the discharge port 9 via the adapter 12.
- an orifice 18 that is concentric with the suction port 7 of the casing 10 and includes a bell mouth-shaped suction port 17 (second suction port) is disposed in the opening 2 of the outer shell 3. That is, the opening 2 of the outer shell 3 communicates with the suction port 7 of the casing 10 through the suction port 17 of the orifice 18. 1A and 1B, the end portion 20 of the orifice 18 is located at a gap dimension j from the lower surface of the suction port 7 of the casing 10, and the gap portion is provided between the orifice 18 and the casing 10. A (gap) 21 is formed.
- a resonance space 19 defined by being surrounded by the orifice 18, the casing 10, and the outer shell 3 is defined.
- the resonance space 19 communicates with the suction port 7 of the casing 10 through a gap 21 between the orifice 18 and the casing 10.
- each protrusion 22 and the orifice 18 are one part integrally molded.
- the protrusion 22 has a shape that is longer in the depth direction (one direction in the plane) than the width in plan view.
- the protrusions 22 having such a long shape in the depth direction are arranged on the orifice 18 as a plurality of protrusion groups (protrusion part groups) 30 arranged in a set of three with the depth direction being parallel. As shown in FIG. 2A, the adjacent protrusion groups 30 are arranged so that the depth directions thereof are substantially orthogonal to each other.
- the protrusion 22 has a shape in which the protrusion depth L (the length in the Y direction in the drawing) is longer than the protrusion height ho (the height in the Z direction in the drawing). Further, the protrusion 22 has a trapezoidal cross-sectional shape (XZ cross-sectional shape) perpendicular to the depth direction (Y direction).
- the top of the projection 22 is a flat surface 31, and the top flat surface 31 having a width a is spread on both sides by a width c as it goes downward, on both side surfaces (both side surfaces in the X direction) of the projection 22.
- An inclined surface 32 inclined with respect to the Z direction is formed.
- a recess 23 having a substantially V-shaped cross section is formed by two inclined surfaces 32 between two protrusions 22 arranged in parallel in the depth direction.
- the opening width of the upper portion of the recess 23 is b, and gradually decreases toward the lower side in the Z direction, and the two inclined surfaces 32 intersect at the recess angle ⁇ .
- the depression angle ⁇ is an acute angle.
- the centrifugal blower 1 having such a configuration, an operation of reducing noise generated by the rotational drive of the impeller 5 by the resonance space 19 and the plurality of protrusions 22 provided in the resonance space 19 will be described.
- the intake air passes from the main body opening 2 through the suction port 17 of the orifice 18, enters the impeller 5 through the suction port 7 of the casing 10, and is boosted by the impeller 5. , Passes through the inside of the casing 10 and is discharged from the discharge adapter 12 to the duct 16 and discharged to the outdoors.
- each recess 23 has a substantially V-shaped cross section, and the width of the recess 23 is set to be narrow.
- the sound wave incident on the depression 23 is reflected more times, causing irregular reflection, and the sound reduction effect is strong and noise can be reduced.
- the relationship of ho ⁇ b is preferable with respect to the protrusion height ho and the recess opening width b.
- the protrusion 22 has a trapezoidal cross-sectional shape perpendicular to the depth direction of the protrusion 22, and the shape of the recess 23 formed by the protrusion 22 is gradually narrowed toward the lower side. Therefore, the sound wave incident on the depression 23 is diffusely reflected, and the time interval at which the reflection occurs becomes shorter as the sound wave travels to the lower side of the depression 23. Thereby, since the frequency
- the trapezoidal shape of the cross section of the protrusion 22 preferably has a relationship of ho ⁇ c with respect to the protrusion height ho and the width c of the inclined surface 32.
- the same effect can be expected when the cross-sectional shape of the protrusion 22 is triangular.
- the volume of the recess 23 is adjusted by adjusting the width a of the top flat surface 31 of the protrusion 22 while keeping the angle of the inclined surface 32 at an optimum angle by making the cross-sectional shape of the protrusion 22 trapezoidal. can do.
- the same effect can be expected when the inclined surface of the protrusion 22 forming the recess 23 is not only formed as a flat surface but also when the inclined surface is a curved surface.
- the dent angle ⁇ of the dent 23 is an acute angle, irregular reflection is likely to occur even for a sound wave having a shallow incident angle with respect to the dent 23, so that a sound reduction effect can be easily obtained and noise can be effectively obtained. Can be reduced.
- the protrusion 22 has a shape that is long in depth with respect to the height and width of the protrusion 22, the recess 23 formed by the protrusion 22 has a slit shape. Therefore, irregular reflection can be generated even for a sound wave having a shallow (small) incident angle with respect to the depth direction of the protrusion 23 and the slit direction (that is, the Y direction (see FIG. 3)). As a result, a sound reduction effect can be easily obtained, and noise can be reduced.
- L 1.5ho or L> 1.5a.
- each protrusion 22 is the same and the shape of the recess 23 formed by each protrusion 22 is the same, the frequency of the sound wave reduced by the irregular reflection at the recess 23 is Since it depends on the shape, the sound reduction effect works strongly for a specific frequency, and noise can be reduced.
- the sound wave entering the resonance space 19 from the gap 21 tends to be diffracted toward the orifice 18 in the resonance space 19 by the end 20 of the orifice 18 (see FIGS. 1A and 1B). Therefore, the possibility that the sound wave collides with the orifice 18 is increased. Therefore, by forming the plurality of protrusions 22 and the depressions 23 on the orifice 18, sound waves can be effectively incident on the depressions 23, and noise can be reduced by the sound reducing action of the depressions 23.
- the protrusion 22 and the orifice 18 are formed as a single component, the plurality of protrusions 22 and the recesses 23 are formed in the resonance space 19 without increasing the number of components. Can be provided.
- FIG. 2B by making the cross-sectional shape of the orifice 18 a shape that can be manufactured by a die with one direction removed, the manufacturing is easy and the manufacturing cost can be reduced.
- the slit-like depressions 23 arranged in parallel by one projection group 30 are maximized.
- Four can be formed. There is a characteristic that the incidence rate of irregular reflection by the depression 23 becomes higher as the sound wave in a direction near to the longitudinal direction of the slit-like depression 23 becomes higher, and for example, by combining four or more protrusions 22, the characteristic is further improved. Become stronger.
- the projection groups 30 that form a set of four depressions 23 in the orifice 18 are arranged alternately vertically and horizontally. By doing so, it is possible to compensate for the low occurrence rate between adjacent sets. Therefore, irregular reflection by the depression 23 can be effectively generated, and a sound reduction effect can be obtained.
- the inner dimension of the outer shell 3 is 264 mm square, the height is 195 mm, the diameter of the impeller 5 is 183.5 mm, the inner diameter Di of the suction port 7 is 152 mm, and the suction port 17
- FIG. 4 shows a graph of noise characteristic values of the centrifugal blower of the comparative example in which 22 is not provided (the other conditions are the same as those of the example).
- the solid line is the noise characteristic value of the centrifugal fan of the example having the protrusions 22 and the depressions 23, and the dotted line is the noise characteristic value of the centrifugal fan of the comparative example having no protrusions and depressions.
- the noise characteristics of the embodiment are reduced in sound pressure levels at various frequencies, particularly in the relatively high frequency ranges of 1 kHz to 1.4 kHz and 2.6 kHz to 3.4 kHz. It can be seen that the sound is more prominent than the comparative example. Therefore, it has been confirmed that by adopting the configuration of the centrifugal blower of the first embodiment, a noise reduction effect of 1 dB can be obtained in overall.
- the depth direction of the protrusion 22 of each protrusion group 30 is arranged in a direction parallel to the radial direction of the impeller 5 and in a direction inclined from the orthogonal direction.
- the protrusion group 30 can also be arranged. Even in such a configuration, the same effect as the above-described configuration can be expected.
- An arbitrary angle can be adopted as the inclination angle in the inclined direction.
- the sound reduction effect by air column resonance and the sound reduction effect by diffuse reflection are used together to enhance the sound reduction effect in the high frequency range and reduce the noise in a wide frequency range from low frequency to high frequency.
- a centrifugal blower can be obtained.
- FIG. 7A shows a schematic perspective view of the orifice 18 included in the centrifugal blower of the second embodiment
- FIG. 7B shows a cross-sectional view taken along the line BB in the orifice 18 of FIG. 7A.
- a plurality of protrusions 22 are provided discontinuously on the inner side of the resonance space 19 of the orifice 18, that is, the side surfaces of the protrusions 22 are not directly connected to the side surfaces of the adjacent protrusions 22.
- a recess 23 formed by a side surface and a bottom surface of each adjacent protrusion 22 is provided between the protrusions 22.
- the protrusion 22 and the orifice 18 are formed as a single molded part.
- the individual protrusions 22 have different shapes, and the protrusions 22 having a plurality of types of shapes are provided. For this reason, there are a plurality of types of shapes of the recesses 23 formed by the protrusions 22.
- the plurality of protrusions 22 are discontinuously provided at intervals without directly connecting the respective side surfaces.
- the recesses 23 are arranged at arbitrary intervals in the radial direction of the impeller 5.
- each hollow 23 is arrange
- the sound wave of the noise that has entered from the gap portion 21 has various directions due to diffraction and reflection inside the resonance space 19.
- the respective recesses 23 are arranged with the slit-like longitudinal direction as various directions, a sound reduction effect can be obtained even for sound waves in various directions, and noise can be reduced. Can do.
- the frequency of the sound wave reduced by the irregular reflection at the depression 23 depends on the shape of the depression 23, there are a plurality of types of the projections 22, and there are a plurality of types of the depressions 23 formed by the projections 22.
- Configuration is adopted. With such a configuration, a sound reduction effect can be obtained at various frequencies as compared with the configuration of the first embodiment, and noise can be reduced in a wider frequency range.
- each protrusion 22 and the hollow 23 are arranged so that the longitudinal direction is different from at least one of the radial direction, the circumferential direction, and the axial direction of the impeller 5, various directions can be provided. A sound reduction effect for sound waves can be obtained.
- the sound reduction effect by air column resonance and the sound reduction effect by diffuse reflection are used together to enhance the sound reduction effect in the high frequency range and reduce noise in a wide frequency range from low frequency to high frequency.
- a centrifugal blower that can be obtained is obtained.
- FIG. 8 shows a schematic perspective view of the orifice 18 included in the centrifugal blower of the third embodiment.
- the projections 22 having the same shape are formed as a set of projection groups 30 in the same manner as the arrangement of the projections 22 of the first embodiment shown in FIG. 2A.
- the plurality of protrusion groups 30 are alternately arranged in the vertical and horizontal directions.
- the configuration in which the plurality of projection groups 30 are formed integrally with the orifice 18 is employed.
- the unit 24 to which the projection group 30 can be attached and detached is provided. In the point comprised as follows, the structure different from the said 1st Embodiment is employ
- the unit 24 (corresponding to the protrusion group 30) includes three protrusions 22 arranged in parallel in the depth direction, and a slit-like depression 23 formed by these protrusions 22 is parallel to the depth direction. Two are provided. On the inner side of the resonance space 19 of the orifice 18, a plurality of units 24 are arbitrarily arranged vertically and horizontally so that the depth directions of the adjacent units 24 intersect each other. Each unit 24 is fixed to the orifice 18 by a fixing means such as a screw, so that it can be detached from the orifice 18.
- each unit 24 can be changed into various forms, and various arrangements of the recesses 23 can be created with one type of unit 24. Further, since the unit 24 is detachable, the frequency at which the sound can be reduced can be adjusted by changing the arrangement of the recesses 23.
- the unit 24 as a sound absorbing material such as glass wool, the gradual decrease of energy due to irregular reflection at the recess 23 becomes stronger, so that the sound reduction effect works strongly and noise can be reduced.
- the sound reduction effect by air column resonance and the sound reduction effect by diffuse reflection are used together to enhance the sound reduction effect in the high frequency range, and reduce the noise in a wide frequency range from low frequency to high frequency.
- a centrifugal blower in which the frequency of the noise to be reduced can be adjusted.
- FIGS. 9A and 9B are schematic cross-sectional views showing the structures of the protrusions 22 and the recesses 23 provided in the centrifugal blower of the fourth embodiment.
- the protrusion 22 of the fourth embodiment has a plate thickness of 1 mm, for example, and has a hollow 25 inside thereof, and further has a hole 27 of ⁇ 1.5 mm on the protrusion tip surface 26, for example. .
- the protrusion 22 forms a Helmholtz resonance structure in which the cavity 25 is a volume part and the hole 27 is a throat part.
- FIG. 9B such a structure of the projection 22 is formed by forming the orifice 18 with a thin plate to form the upper surface of each projection 22 and attaching a plate part 28 from the lower side of the orifice 18 in the figure.
- the cavity 25 can be easily formed inside each projection 22.
- the inside is a cavity 25 and a hole 27 is formed.
- centrifugal blower capable of enhancing the noise reduction effect in the high frequency range and reducing noise in a wide frequency range from low frequency to high frequency.
- the present invention provides a centrifugal blower that enhances a sound reduction effect in a high frequency range, can reduce noise in a wide frequency range from low frequency to high frequency, and reduces noise. Is available.
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Abstract
Description
本発明の第1の実施形態にかかる遠心送風機1の模式断面図を図1Aに示し、図1AのX部分の部分拡大図を図1Bに示す。図1Aに示すように、例えば、天井埋込型換気扇として用いられる遠心送風機1は、下面に開口2を備えた外郭3内に、回転軸4を中心に回動可能に多翼型の羽根車5を連結した電動機6と、羽根車5の周囲を囲み、開口にベルマウス状の吸込み口7(第1の吸込み口)を有し、かつ側壁8に吐出口9を有するケーシング10とを備えている。ケーシング10の吐出口9は外郭3の一側面に設けられた吐出開口11を介して、吐出アダプタ12と連通している。外郭3の下面の外周にはフランジ部13があり、フランジ部13に備えた穴14を通して、ねじ等で天井材15に外郭3が固定され、天井に配され屋外に連通するダクト16が、吐出アダプタ12を介して吐出口9に接合されている。 (First embodiment)
A schematic cross-sectional view of the
次に、本発明の第2の実施形態にかかる遠心送風機について説明する。以下の説明において、上記第1実施形態と同じ構成部材には同じ参照番号を付して、その説明を省略する。本第2実施形態の遠心送風機が備えるオリフィス18の模式斜視図を図7Aに示し、図7Aのオリフィス18におけるB-B線断面図を図7Bに示す。 (Second Embodiment)
Next, a centrifugal blower according to a second embodiment of the present invention will be described. In the following description, the same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted. FIG. 7A shows a schematic perspective view of the
次に、本発明の第3の実施形態にかかる遠心送風機について説明する。以下の説明において、上記第1実施形態と同じ構成部材には同じ参照番号を付して、その説明を省略する。本第3実施形態の遠心送風機が備えるオリフィス18の模式斜視図を図8に示す。 (Third embodiment)
Next, a centrifugal blower according to a third embodiment of the present invention will be described. In the following description, the same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted. FIG. 8 shows a schematic perspective view of the
次に、本発明の第4の実施形態にかかる遠心送風機について説明する。以下の説明において、上記第1実施形態と同じ構成部材には同じ参照番号を付して、その説明を省略する。本第4実施形態の遠心送風機に設けられた突起22および窪み23の構造を示す模式断面図を図9Aおよび図9Bに示す。 (Fourth embodiment)
Next, a centrifugal blower according to a fourth embodiment of the present invention will be described. In the following description, the same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted. 9A and 9B are schematic cross-sectional views showing the structures of the
Claims (16)
- 開口部を備える外郭と、
外郭内にて回転可能に支持された羽根車と、
羽根車を回転駆動する電動機と、
第1の吸込み口を有し、羽根車の周囲を囲むように外郭内に配置されたケーシングと、
ケーシングの第1の吸込み口との間に隙間を有するように外郭の開口部に配置され、外郭の開口部とケーシングの第1の吸込み口とを連通させる第2の吸込み口を有するベルマウス状のオリフィスとを備え、
第1の吸込み口と第2の吸込み口との間の隙間を通じて第1の吸込み口と連通されて、第1の吸込み口から放出される騒音を共鳴消音する共鳴空間が、オリフィス、ケーシング、および外郭を画定壁として画定され、共鳴空間の画定壁に複数の突起部が設けられている、遠心送風機。 An outer shell with an opening,
An impeller supported rotatably in the outer shell;
An electric motor for rotationally driving the impeller;
A casing having a first suction port and disposed in the outer shell so as to surround the periphery of the impeller;
A bell mouth shape having a second suction port which is disposed in an opening of the outer shell so as to have a gap between the first suction port of the casing and communicates the opening of the outer shell and the first suction port of the casing. With an orifice,
A resonance space that communicates with the first suction port through a gap between the first suction port and the second suction port to resonate and muffle noise emitted from the first suction port. A centrifugal blower, wherein the outer wall is defined as a defining wall, and the plurality of protrusions are provided on the defining wall of the resonance space. - 複数の突起部は、各々の形成位置において共鳴空間の画定壁面に対して傾斜された傾斜面を有し、
1つの突起部の傾斜面と、この1つの突起部に隣接する別の1つの突起部の傾斜面とが互いに接続されて、それぞれの傾斜面により両突起部間に凹部が形成されている、請求項1に記載の遠心送風機。 The plurality of protrusions have inclined surfaces that are inclined with respect to the defining wall surface of the resonance space at each forming position,
An inclined surface of one protruding portion and an inclined surface of another protruding portion adjacent to the one protruding portion are connected to each other, and a concave portion is formed between the protruding portions by each inclined surface. The centrifugal blower according to claim 1. - 凹部におけるそれぞれの傾斜面の接続部分の角度が鋭角である、請求項2に記載の遠心送風機。 The centrifugal blower according to claim 2, wherein an angle of a connecting portion of each inclined surface in the recess is an acute angle.
- 突起部は、その頂部に平坦面を有する、請求項2に記載の遠心送風機。 The centrifugal blower according to claim 2, wherein the protrusion has a flat surface at the top.
- 突起部は、その高さおよび幅に対してその奥行きが長い形状を有する、請求項2に記載の遠心送風機。 The centrifugal blower according to claim 2, wherein the protrusion has a shape whose depth is long with respect to its height and width.
- その奥行き方向を平行にして複数の突起部が配列された複数の突起部群が、隣接する突起部群同士の奥行き方向が互いに交差するように配置されている、請求項5に記載の遠心送風機。 The centrifugal blower according to claim 5, wherein the plurality of protrusion groups in which the plurality of protrusions are arranged in parallel with each other in the depth direction are arranged so that the depth directions of adjacent protrusion groups intersect each other. .
- その奥行き方向を平行にして複数の突起部が配列された複数の突起部群が、各々の奥行き方向が異なるように配置されている、請求項5に記載の遠心送風機。 The centrifugal blower according to claim 5, wherein a plurality of protrusion groups in which a plurality of protrusions are arranged in parallel in the depth direction are arranged so that each of the depth directions is different.
- 複数の突起部の間に形成される複数の凹部が、画定壁面沿いに延在するように形成され、羽根車の径方向、周方向および軸方向の少なくとも1つの方向に対して、それぞれの凹部の延在方向が異なるように配列されている、請求項5に記載の遠心送風機。 A plurality of recesses formed between the plurality of protrusions are formed so as to extend along the demarcating wall surface, and each recess is provided in at least one of the radial direction, the circumferential direction, and the axial direction of the impeller. The centrifugal blower according to claim 5, wherein the extending directions are different from each other.
- 複数の突起部の形状が同じであり、複数の突起部の間に形成される複数の凹部の形状が同じである、請求項1から8のいずれか1つに記載の遠心送風機。 The centrifugal blower according to any one of claims 1 to 8, wherein the plurality of protrusions have the same shape, and the plurality of recesses formed between the plurality of protrusions have the same shape.
- 突起部の形状が複数種類あり、複数の突起部の間に形成される凹部の形状が複数種類ある、請求項1から8のいずれか1つに記載の遠心送風機。 The centrifugal blower according to any one of claims 1 to 8, wherein there are a plurality of types of protrusions, and there are a plurality of types of recesses formed between the plurality of protrusions.
- 共鳴空間内において、オリフィス上に複数の突起部が設けられている、請求項1から8のいずれか1つに記載の遠心送風機。 The centrifugal blower according to any one of claims 1 to 8, wherein a plurality of protrusions are provided on the orifice in the resonance space.
- 複数の突起部は、オリフィス、ケーシング、または外郭の画定壁と一体的に形成されている、請求項1から8のいずれか1つに記載の遠心送風機。 The centrifugal blower according to any one of claims 1 to 8, wherein the plurality of protrusions are integrally formed with an orifice, a casing, or a demarcation wall of the outer shell.
- 突起部は、画定壁に着脱可能に設置されている、請求項1から8のいずれか1つに記載の遠心送風機。 The centrifugal blower according to any one of claims 1 to 8, wherein the protrusion is detachably installed on the defining wall.
- 突起部が、吸音材にて形成されている、請求項13に記載の遠心送風機。 The centrifugal blower according to claim 13, wherein the protrusion is formed of a sound absorbing material.
- 突起部はその内部を空洞として形成され、この空洞と共鳴空間とを連通する孔部が突起部に形成されている、請求項1から8のいずれか1つに記載の遠心送風機。 The centrifugal blower according to any one of claims 1 to 8, wherein the protrusion is formed with a hollow inside, and a hole communicating with the cavity and the resonance space is formed in the protrusion.
- 開口部を備える外郭と、外郭内にて回転可能に支持された羽根車と、第1の吸込み口を有し、羽根車の周囲を囲むように外郭内に配置されたケーシングと、ケーシングの第1の吸込み口との間に隙間を有するように外郭の開口部に配置され、外郭の開口部とケーシングの第1の吸込み口とを連通させる第2の吸込み口を有するベルマウス状のオリフィスとを備える遠心送風機において、第1の吸込み口と第2の吸込み口との間の隙間を通じて第1の吸込み口と連通され、オリフィス、ケーシング、および外郭を画定壁として画定される共鳴空間内に、羽根車の回転駆動に伴ってケーシングにて発生した騒音の音波を第1の吸込み口と第2の吸込み口との間の隙間を通じて入射させ、
共鳴空間内にて入射された騒音の音波のレベルを気柱共鳴により低減させるとともに、共鳴空間内にて騒音の音波を乱反射させることにより騒音の音波のレベルを低減させる、遠心送風機の騒音低減方法。 An outer shell having an opening, an impeller rotatably supported in the outer shell, a casing having a first suction port and being arranged in the outer shell so as to surround the periphery of the impeller, A bell mouth-shaped orifice having a second suction port which is disposed in an opening of the outer shell so as to have a gap between the first suction port and communicates the opening of the outer shell and the first suction port of the casing; In a resonance space defined by the orifice, the casing, and the outer shell as a demarcated wall, and communicated with the first suction port through a gap between the first suction port and the second suction port. The sound wave of the noise generated in the casing as the impeller rotates is incident through the gap between the first suction port and the second suction port,
A noise reduction method for a centrifugal blower that reduces the sound wave level of noise incident in the resonance space by air column resonance and reduces the sound wave level of noise by irregularly reflecting the sound wave of noise in the resonance space. .
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Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
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Families Citing this family (35)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2468312A (en) | 2009-03-04 | 2010-09-08 | Dyson Technology Ltd | Fan assembly |
GB2468322B (en) | 2009-03-04 | 2011-03-16 | Dyson Technology Ltd | Tilting fan stand |
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GB2532557B (en) | 2012-05-16 | 2017-01-11 | Dyson Technology Ltd | A fan comprsing means for suppressing noise |
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GB2503907B (en) | 2012-07-11 | 2014-05-28 | Dyson Technology Ltd | A fan assembly |
US9388731B2 (en) * | 2013-03-15 | 2016-07-12 | Kohler Co. | Noise suppression system |
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US9169750B2 (en) * | 2013-08-17 | 2015-10-27 | ESI Energy Solutions, LLC. | Fluid flow noise mitigation structure and method |
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US20150140344A1 (en) * | 2013-11-20 | 2015-05-21 | Covidien Lp | Coated medical devices |
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WO2016066213A1 (en) * | 2014-10-31 | 2016-05-06 | Arcelik Anonim Sirketi | Improved suction muffler for use in a hermetically sealed compressor of a refrigeration appliance |
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JP2020109259A (en) * | 2018-12-28 | 2020-07-16 | 日本電産株式会社 | Blower |
KR102082666B1 (en) * | 2019-02-08 | 2020-02-28 | 주식회사 힘펠 | Blast Apparatus |
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Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS4868201A (en) * | 1971-12-15 | 1973-09-18 | ||
JPS4997514U (en) * | 1972-12-09 | 1974-08-22 | ||
JPH0178292U (en) * | 1987-11-13 | 1989-05-25 | ||
JPH02139212U (en) * | 1989-04-25 | 1990-11-21 | ||
JPH0894146A (en) * | 1994-09-21 | 1996-04-12 | Matsushita Seiko Co Ltd | Ceiling embedded type ventilating fan |
JP3066804U (en) * | 1999-07-19 | 2000-03-07 | インダストリアル テクノロジー リサーチ インスティテュート | Low noise fan filter device |
JP2003091286A (en) * | 2001-09-17 | 2003-03-28 | Fumihiro Nakagawa | Sound absorbing member |
JP2006145657A (en) * | 2004-11-17 | 2006-06-08 | Sasakura Engineering Co Ltd | Method for mounting sound absorbing wedges for anechoic room |
JP2007065901A (en) * | 2005-08-30 | 2007-03-15 | Nec Fielding Ltd | Silent computer structure |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3035657A (en) * | 1959-12-22 | 1962-05-22 | Sidney Roofing & Paper Company | Acoustic panel |
FR2191025B1 (en) * | 1972-07-04 | 1975-03-07 | Aerospatiale | |
US4303144A (en) * | 1979-12-21 | 1981-12-01 | Lockheed Corporation | Apparatus for the retroreflection of sound |
US5803721A (en) * | 1996-10-29 | 1998-09-08 | Enviroflex, Inc. | Clean room fan unit |
CN2367806Y (en) * | 1999-05-20 | 2000-03-08 | 财团法人工业技术研究院 | Low-noise fan-filter net machine set |
JP4873845B2 (en) * | 2004-10-01 | 2012-02-08 | 三菱電機株式会社 | Air conditioner |
US8123468B2 (en) * | 2006-11-02 | 2012-02-28 | Panasonic Corporation | Centrifugal fan |
-
2008
- 2008-04-22 JP JP2008111032A patent/JP2009264121A/en active Pending
-
2009
- 2009-04-21 US US12/920,163 patent/US20110002775A1/en not_active Abandoned
- 2009-04-21 CN CN2009801069514A patent/CN101965461A/en active Pending
- 2009-04-21 WO PCT/JP2009/001819 patent/WO2009130891A1/en active Application Filing
Patent Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS4868201A (en) * | 1971-12-15 | 1973-09-18 | ||
JPS4997514U (en) * | 1972-12-09 | 1974-08-22 | ||
JPH0178292U (en) * | 1987-11-13 | 1989-05-25 | ||
JPH02139212U (en) * | 1989-04-25 | 1990-11-21 | ||
JPH0894146A (en) * | 1994-09-21 | 1996-04-12 | Matsushita Seiko Co Ltd | Ceiling embedded type ventilating fan |
JP3066804U (en) * | 1999-07-19 | 2000-03-07 | インダストリアル テクノロジー リサーチ インスティテュート | Low noise fan filter device |
JP2003091286A (en) * | 2001-09-17 | 2003-03-28 | Fumihiro Nakagawa | Sound absorbing member |
JP2006145657A (en) * | 2004-11-17 | 2006-06-08 | Sasakura Engineering Co Ltd | Method for mounting sound absorbing wedges for anechoic room |
JP2007065901A (en) * | 2005-08-30 | 2007-03-15 | Nec Fielding Ltd | Silent computer structure |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN102192194A (en) * | 2010-03-17 | 2011-09-21 | 广东松下环境系统有限公司 | Structure for reducing noise of ventilating fan |
US9441642B2 (en) | 2010-03-17 | 2016-09-13 | Panasonic Ecology Systems Guangdong Co., Ltd. | Structure for reducing noise of ventilating fan |
CN109595652A (en) * | 2017-09-30 | 2019-04-09 | 宁波方太厨具有限公司 | A kind of near-suction type oil smoke suction machine |
CN109595652B (en) * | 2017-09-30 | 2024-01-16 | 宁波方太厨具有限公司 | Near-suction type range hood |
CN112061365A (en) * | 2020-08-10 | 2020-12-11 | 上海外高桥造船有限公司 | Indoor noise reduction device for ocean passenger ship |
CN113847810A (en) * | 2021-10-11 | 2021-12-28 | 成都新仪征环保科技有限公司 | Low-noise air-cooled heat dissipation device |
CN113847810B (en) * | 2021-10-11 | 2024-03-08 | 成都新仪征环保科技有限公司 | Low-noise air-cooled heat dissipation device |
Also Published As
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---|---|
JP2009264121A (en) | 2009-11-12 |
US20110002775A1 (en) | 2011-01-06 |
CN101965461A (en) | 2011-02-02 |
WO2009130891A8 (en) | 2010-03-11 |
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