WO2014103233A1 - 遠心送風機及びそれを用いた消音ボックス付送風機 - Google Patents

遠心送風機及びそれを用いた消音ボックス付送風機 Download PDF

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Publication number
WO2014103233A1
WO2014103233A1 PCT/JP2013/007368 JP2013007368W WO2014103233A1 WO 2014103233 A1 WO2014103233 A1 WO 2014103233A1 JP 2013007368 W JP2013007368 W JP 2013007368W WO 2014103233 A1 WO2014103233 A1 WO 2014103233A1
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WO
WIPO (PCT)
Prior art keywords
discharge
tongue
wall surface
side wall
centrifugal blower
Prior art date
Application number
PCT/JP2013/007368
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
朗正 上原
聡 逢坂
幸司 新崎
Original Assignee
パナソニック株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by パナソニック株式会社 filed Critical パナソニック株式会社
Priority to JP2014554118A priority Critical patent/JP6295434B2/ja
Priority to US14/653,782 priority patent/US20160195106A1/en
Priority to CN201380068014.0A priority patent/CN104870827B/zh
Publication of WO2014103233A1 publication Critical patent/WO2014103233A1/ja

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Classifications

    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4226—Fan casings
    • F04D29/4233—Fan casings with volutes extending mainly in axial or radially inward direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/16—Centrifugal pumps for displacing without appreciable compression
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/422—Discharge tongues
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4226—Fan casings
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • 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
    • 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
    • F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/52—Outlet

Definitions

  • the present invention relates to a centrifugal blower and a blower with a sound deadening box using the centrifugal blower.
  • FIG. 10A is a side view of a centrifugal blower of Patent Document 1
  • FIG. 10B is a side view of a conventional general centrifugal blower.
  • the centrifugal fan 101a includes a casing 106a and an impeller 109 built in the casing 106a.
  • the casing 106 a includes a side plate 104 having a suction port 103 and a scroll 105.
  • a discharge duct 107a is provided at the discharge port 102a of the casing 106a.
  • the suction port 103 is provided with a suction duct 108.
  • the blowing direction of the discharge duct 107a (the air flow 111a in the discharge duct) is parallel to a plane orthogonal to the rotation axis of the impeller 109. Further, the air flow (discharge port air flow 110a) blown out from the discharge port 102a is bent toward the opposite tongue side in the vicinity of the tongue portion 112 by the discharge duct 107a to become an air flow 111a in the discharge duct.
  • the airflow blown out from the opposite tongue side of the casing 106a does not flow along the wall surface of the discharge duct 107a.
  • the blowing direction of the airflow is a central portion between the upper side and the lower side in FIG. 10A of the discharge duct 107a.
  • FIG. 10B shows a connection form between a general centrifugal blower 101b and a discharge duct 107b.
  • the same reference numerals are the same components.
  • the end of the casing 106b and the discharge duct 107b are substantially horizontal.
  • the discharge duct 107b is fixed so that the direction of the discharge port air flow 110b at the discharge port 102b is the same as the direction of the air flow 111b in the discharge duct.
  • the discharge port airflow 110b blown out from the casing 106b travels through the discharge duct 107b so as to go straight as it is.
  • the discharge port airflow 110b is faster on the outer peripheral side of the casing 106b. Accordingly, in the discharge duct 107b, the wind speed on the upper side is faster than the central portion between the upper side and the lower side of the discharge duct 107b. Therefore, when the discharge duct 107b is bent in the same direction as the rotation direction 114 in the downstream portion, an airflow having a high wind speed passes through the outer peripheral side of the bent portion, and the airflow flows smoothly along the bending of the discharge duct 107b.
  • the casing 106 a is rotated in the rotation direction 114 of the impeller 109. Therefore, out of the discharge port air flow 110a, the discharge port air flow 110a having a high wind speed on the outer peripheral side of the casing 106a flows into the vicinity of the center between the upper side and the lower side of the discharge duct 107a. In the vicinity of the center of the discharge duct 107a, the discharge port airflow 110a is diffused throughout the discharge duct 107a and flows through the discharge duct 107a.
  • the centrifugal blower 101a By collecting the quick discharge port airflow 110a at the center of the discharge duct 107a, the pressure loss due to the bending of the discharge duct 107a is reduced regardless of which direction the discharge duct 107a is bent. Therefore, the centrifugal blower 101a has a small pressure loss without depending on the bending direction of the discharge duct 107a.
  • the scroll 105 is interrupted in the middle.
  • the scroll air passage enlargement portion from the vicinity of the tongue portion 112 of the scroll 105 to the discharge port 102a, the flow rate of the gas pressurized by the impeller 109 is reduced by the air passage enlargement. That is, the scroll air passage expanding portion is a portion that converts gas from dynamic pressure to static pressure and flows it into the discharge duct 107a.
  • the centrifugal blower of the present invention has a casing provided with a scroll and an impeller built in the casing.
  • the casing includes a side plate having a suction port
  • the scroll includes a discharge port
  • a discharge duct is connected to the casing.
  • the discharge port airflow which blows off from a discharge port is parallel to the surface orthogonal to the rotating shaft of an impeller.
  • at least one of a tongue side wall surface on the tongue side extending from the casing outlet of the casing and an anti-tongue side wall surface on the opposite side of the tongue extending from the casing outlet protrudes into the discharge duct. Then, when viewed from the direction orthogonal to the suction port, the air flow at the discharge port bends at a predetermined angle from the tongue side toward the side opposite the tongue, and becomes an air flow in the discharge duct flowing through the discharge duct.
  • the scroll air passage enlarged portion is enlarged by the tongue side wall surface, the anti-tongue side wall surface, or both, the flow velocity of the discharge port airflow is sufficiently reduced, and the flow is smoothly guided to the discharge duct. Therefore, the discharge airflow is sufficiently converted from dynamic pressure to static pressure, pressure loss is prevented, and performance degradation of the centrifugal blower is prevented.
  • FIG. 1 is a side view of the centrifugal blower according to Embodiment 1 of the present invention.
  • FIG. 2 is a performance comparison graph between the centrifugal blower and a conventional centrifugal blower.
  • FIG. 3A is a side view of the centrifugal blower according to Embodiment 2 of the present invention.
  • FIG. 3B is a front view of the centrifugal blower.
  • FIG. 4 is a side view of the centrifugal blower provided with a sound absorbing material in the discharge adapter.
  • FIG. 5 is a perspective view of the casing when a small hole is provided in the tongue side wall surface and the counter tongue side wall surface of the centrifugal blower.
  • FIG. 6 is a side view illustrating duct connection of the centrifugal blower.
  • FIG. 7 is a side view of a blower with a sound deadening box using the centrifugal blower of Embodiment 3 of the present invention.
  • FIG. 8 is a top view of a blower with a sound deadening box using the centrifugal blower.
  • FIG. 9 is an installation diagram of the fan with the sound deadening box.
  • 10A is a side view of the centrifugal blower of Patent Document 1.
  • FIG. 10B is a side view of a conventional general centrifugal fan.
  • FIG. 1 is a side view of the centrifugal blower according to Embodiment 1 of the present invention.
  • the centrifugal fan 1 includes a casing 6 and an impeller 9 built in the casing 6.
  • the casing 6 includes a side plate 4 having a suction port 3 and a scroll 5 having a discharge port 2.
  • a discharge duct 7 is connected to the casing outlet 6 a of the casing 6, and a suction duct 8 is connected to the suction port 3.
  • the tongue side wall surface 14 on the side of the tongue 13b of the scroll 5 and the tongue side wall surface 15 on the tongue 13a are formed so as to protrude into the discharge duct 7.
  • the tongue side wall surface 14 does not reach the center of the discharge duct 7 and has an end portion at the upper half position of the discharge duct 7 in FIG.
  • the tongue side wall surface 15 makes the tongue side wall surface tip 15a contact the discharge duct wall surface 7a.
  • the tongue side wall surface 14 and the tongue side wall surface 15 extend from the casing outlet 6a.
  • the discharge port airflow 10 flowing through the discharge port 2 is discharged so as to be parallel to a surface orthogonal to the rotation shaft 24 of the impeller 9 and to the opposite tongue 13b side of the scroll 5 opposite to the tongue 13a.
  • the duct 7 is connected to the discharge port 2. That is, when viewed from the direction orthogonal to the suction port 3, the discharge port airflow 10 bends at a predetermined angle ⁇ ′ from the tongue portion 13 a side to the opposite tongue portion 13 b side, and flows in the discharge duct 7. It becomes.
  • the predetermined angle ⁇ ′ is larger than 0 degree and smaller than 45 degrees, preferably 20 degrees or more and 30 degrees or less.
  • the angle ⁇ is greater than 135 degrees and less than 180 degrees, and is preferably between 150 degrees and 160 degrees.
  • the tongue-facing position 13c is a position where a perpendicular line extending from the tongue 13a to the anti-tongue side wall surface 14 intersects with the anti-tongue side wall surface 14.
  • the connecting portion 26 on the side opposite to the tongue portion 13b between the casing 6 and the discharge duct 7 is provided closer to the impeller 9 side than the tongue portion facing position 13c.
  • the discharge port airflow 10 that has collided with the tongue 13 a is guided into the discharge duct 7 along the tongue side wall surface 15. In this way, the discharge port airflow 10 is smoothly guided to the discharge duct 7 by the tongue side wall surface 15, thereby preventing pressure loss due to a sudden expansion of the air passage from the tongue 13 a to the discharge duct 7.
  • the tongue side wall surface 15 projected into the discharge duct 7 has the tongue side wall surface tip 15a in contact with the discharge duct wall surface 7a.
  • the tongue side wall surface tip 15a is not necessarily in contact with the discharge duct wall surface 7a.
  • the discharge port airflow 10 is faster on the outer peripheral side of the casing 6, that is, on the side opposite to the tongue 13b.
  • the discharge port airflow 10 on the side of the tongue portion 13b is bent in the direction of the airflow 11 in the discharge duct at the central portion of the discharge duct 7.
  • the flow velocity of the discharge port airflow 10 in the center portion is increased. Therefore, in the bent portion on the downstream side of the discharge duct 7, an increase in pressure loss can be suppressed regardless of which direction the discharge duct 7 is bent. That is, the distance from the discharge port 2 to the bent portion of the discharge duct 7 can be made smaller in the first embodiment than in the case where the discharge port airflow 10 goes straight and becomes the discharge duct airflow 11.
  • the centrifugal blower 1 is reduced in size.
  • the centrifugal blower 1 is downsized.
  • the discharge duct 7 is connected so that the central axis of the discharge duct 7 passes through the rotating shaft 24 (or the vicinity) of the impeller 9.
  • FIG. 2 is a performance comparison graph between the centrifugal blower of Embodiment 1 of the present invention and a conventional centrifugal blower.
  • FIG. 2 shows the flow rate of the centrifugal blower of the first embodiment of the graph (c), the centrifugal blower of the graph (b) shown in FIG. 10A, and the centrifugal blower of the graph (a) shown in FIG. 10B.
  • the comparison graph of is shown.
  • the horizontal axis shows the air volume, and the vertical axis shows the static pressure.
  • Graph (a) shows the case where the air flow at the discharge port advances straight in the centrifugal blower of FIG.
  • Graph (b) shows the case where the air flow in the discharge port is bent toward the opposite side of the tongue in the centrifugal blower shown in FIG. 10A.
  • the graph (c) shows that in the centrifugal blower 1 of the first embodiment, the side wall surface 14 of the tongue portion and the side wall surface 15 of the tongue portion protrude into the discharge duct 7, and the discharge airflow 10 is directed to the side of the tongue portion 13 b. This is a case where the airflow 11 in the discharge duct is bent.
  • the centrifugal blower of FIG. 10A has a smaller scroll air passage enlargement portion than the centrifugal blower of FIG. 10B, and the air passage suddenly expands to the discharge duct at the tongue portion, so that the static pressure is reduced overall. ing.
  • the centrifugal blower 1 of Embodiment 1 has substantially the same performance as the general centrifugal blower of FIG. 10B.
  • the centrifugal blower 1 can reduce pressure loss due to bending of the discharge duct 7, regardless of where the discharge duct 7 is bent, while suppressing a decrease in performance (static pressure).
  • the casing 6 is reduced in size.
  • two types of parts such as a clockwise part and a counterclockwise part are not necessary for the parts such as the casing 6 in accordance with the bending direction of the discharge duct 7, and the pressure loss is reduced without depending on the bending direction of the discharge duct 7. Is suppressed.
  • both the tongue side wall surface 14 on the tongue 13b side and the tongue side wall surface 15 on the tongue 13a side of the casing 6 protrude into the discharge duct 7. Only one of them needs to protrude into the discharge duct 7. In that case, it has only one action and effect.
  • FIG. 3A is a side view of the centrifugal blower according to Embodiment 2 of the present invention
  • FIG. 3B is a front view of the centrifugal blower.
  • the centrifugal blower 1 shown in FIGS. 3A and 3B is provided with a round discharge adapter 17 covering the outer periphery of the casing outlet 6a when the round discharge duct 7 is connected to the casing outlet 6a.
  • a round discharge duct 7 is connected to the discharge adapter 17.
  • An anti-tongue side wall surface 14 and a tongue side wall surface 15 protrude into the discharge adapter 17.
  • the tongue side wall surface width 15c is the same as the impeller width 9a.
  • a gap 21 is provided between the tongue side wall surface side portion 15b and both the left and right discharge adapters 17.
  • the wind speed of the side plate side outlet airflow 23 on the side plate 4 side of the impeller 9 is slow. That is, the side-plate-side discharge port airflow 23 is less affected by a suddenly enlarged portion of the air passage formed in the gap 21 portion, flows into the lower side of the discharge adapter 17 and is guided to the discharge duct 7.
  • the impeller outlet airflow 22 having a high wind speed and the side plate side outlet airflow 23 having a low wind speed collide smoothly into the discharge duct 7 by the gap 21, and the impeller outlet airflow 22. And the pressure loss between the side plate side discharge port air flow 23 is prevented.
  • the discharge adapter 17 connects the rectangular casing outlet 6 a and the round discharge duct 7 in a shape along the extension of the scroll 5.
  • the discharge adapter 17 has a circular shape on the scroll 5 side, and the circular cross-sectional area gradually decreases toward the discharge duct 7 side.
  • the discharge port airflow 10 flows into the casing 6 through the impeller 9 and is boosted in the casing 6 to reach the casing outlet 6a.
  • the discharge port airflow 10 is smoothly guided from the casing outlet 6 a to the discharge duct 7 by the discharge adapter 17.
  • the outlet airflow 10 is directed toward the center of the discharge duct 7. Therefore, the diameter of the discharge duct 7 can be reduced.
  • the discharge duct 7 is inserted into the discharge adapter 17 for installation. Moreover, since a part of casing 6 is inserted in the discharge adapter 17, the centrifugal blower 1 is reduced in size.
  • the casing 6 is downsized, the discharge duct 7 is downsized, and the workability is improved while suppressing the performance (static pressure) reduction.
  • the tongue side wall surface 15 has a flat plate shape.
  • the tongue side wall surface side portion 15b with respect to the blowing direction may be raised to the opposite tongue portion 13b side, or conversely bent to the tongue portion 13a side direction.
  • FIG. 4 is a side view of the centrifugal blower according to the second embodiment of the present invention in which a sound absorbing material is provided in the discharge adapter.
  • a sound absorbing material 19 is disposed between the discharge adapter inner surface 17 a, the anti-tongue side wall surface 14, and the tongue side wall surface 15.
  • the operation and effect of the centrifugal blower 1 shown in FIG. 4 will be described.
  • the air flow boosted in the casing 6 flows out to the discharge duct 7 from the casing outlet 6a.
  • air current noise is generated by the discharge airflow 10 colliding with the discharge adapter 17.
  • This airflow noise is absorbed by the sound absorbing material 19 provided between the discharge adapter 17 and the casing outlet 6 a of the scroll 5.
  • FIG. 5 is a perspective view of the casing when a small hole is provided in the tongue side wall surface and the anti-tongue side wall surface of the centrifugal blower according to Embodiment 2 of the present invention. As shown in FIG. 5, a plurality of small holes 20 are provided in the side wall surface 14 of the tongue and the side wall surface 15 of the tongue.
  • the energy of the airflow noise passes through the small holes 20 and is provided between the scroll 5 and the discharge adapter 17 shown in FIG.
  • the sound is transmitted and absorbed in the spaces A and B or the sound absorbing material 19.
  • the sound absorption rate in the discharge adapter 17 increases.
  • FIG. 6 is a side view for explaining duct connection of the centrifugal fan according to the second embodiment of the present invention. As shown in FIG. 6, the central axis 25 of the opening of the discharge adapter 17 passes through the rotation axis 24 of the impeller 9 which is the center of the suction port 3.
  • the height of the discharge duct 7 and the suction duct 8 can be the same. Therefore, when the discharge duct 7 and the suction duct 8 are fixed by using members from the floor or the ceiling, the lengths of the members are unified.
  • the gap 21 is between the tongue side wall surface side portion 15b and the discharge adapter 17.
  • the gap 21 may be between the tongue side wall surface side portion 15 b and the discharge duct 7.
  • FIG. 7 is a side view of a blower with a sound deadening box using the centrifugal blower of Embodiment 3 of the present invention
  • FIG. 8 is a top view of the blower with a sound deadening box using the centrifugal blower.
  • the blower with a sound deadening box includes any one of the centrifugal blowers 1 described in the first and second embodiments, and a box-shaped body 50 incorporating the centrifugal blower 1.
  • the machine body 50 includes a discharge panel 53, a suction panel 56, and a side panel 58.
  • the discharge panel 53 is provided with a fuselage outlet 51 and a discharge adapter 52.
  • the suction panel 56 is provided with a body suction port 54 and a suction adapter 55.
  • An inspection panel 57 is fixed to the side panel 58.
  • the casing outlet 6 a is connected to the discharge duct 59 by connecting the discharge adapter 52 to the discharge duct 59.
  • the discharge adapter 52 is provided at the center of the discharge panel 53, and the suction adapter 55 is provided at the center of the suction panel 56.
  • the anti-tongue side wall surface 14 and the tongue side wall surface 15 are arranged inside the discharge adapter 52, but only one of them is the same as in the first or second embodiment. It may be provided.
  • the top panel 60, the bottom panel 61, and the side panel 58 are located between the discharge panel 53 and the suction panel 56.
  • the top panel 60 and the bottom panel 61 are panels of the machine body 50 that cover the top and bottom surfaces of the centrifugal blower 1, respectively.
  • An inspection panel 57 that is detachably fixed to the side panel 58 faces the side plate 4 of the centrifugal blower 1. Therefore, after the inspection panel 57 is removed from the side panel 58, a person entering the wall inspection port 63 can see the impeller 9 and the motor 62 fixed to the side plate 4 through the inspection panel opening 64. it can.
  • the air outlet 51 is provided at the center of the discharge panel 53, and the discharge panel 53 faces the casing outlet 6 a of the centrifugal blower 1.
  • the discharge panel 53 and the centrifugal blower 1 are connected and fixed close to each other, but may be connected via an intermediate member.
  • Airframe inlet airflow 66 of airframe inlet 54 flows out through centrifugal blower 1 as airframe outlet airflow 67 through discharge duct 59 connected to discharge adapter 52 and suction duct 65 connected to suction adapter 55.
  • the discharge adapter 52 and the suction adapter 55 are disposed at the centers of the discharge panel 53 and the suction panel 56 and face each other. Therefore, the discharge duct 59 and the suction duct 65 are constructed on the same central axis 68. Note that it is desirable that the airframe suction port 54 is provided at the center of the suction panel 56 because the airflow 66 from the air intake duct 65 flows smoothly into the air intake port 54.
  • FIG. 9 is an installation diagram of the blower with a sound deadening box according to the third embodiment of the present invention.
  • the centrifugal blower 1 shown in FIG. 9 When the centrifugal blower 1 shown in FIG. 9 is operated, the air in the room 70 is sucked from the wall surface suction port 71 and is exhausted from the wall surface discharge port 72 to the outdoor 73 through the suction duct 65, the machine body 50, and the discharge duct 59. .
  • the wall inspection port 63 is provided in the vicinity of the inspection panel 57, and the centrifugal blower 1 can be inspected. Moreover, since the airframe 50 is installed in the ceiling back 74, downsizing of the centrifugal blower 1 leads to downsizing of the airframe 50, and the airframe 50 can be easily installed even when the ceiling back 74 is narrow.
  • the discharge adapter 52 is provided at the center of the discharge panel 53, and the suction adapter 55 is provided at the center of the suction panel 56. Therefore, when the top surface and bottom surface of the machine body 50 are constructed in reverse, the relative positions of the discharge adapter 52 and the suction adapter 55 with respect to the machine body 50 do not change, and the workability is improved.
  • the reverse construction of the top and bottom surfaces of the airframe 50 is when the interior of the ceiling 74 shown in FIG. 9 is narrow and the position of the inspection panel 57 with respect to the airframe 50 is reversed, that is, the position of the wall surface inspection port 63 is reversed. This is effective.
  • the airframe outlet 51 is provided at the center of the discharge panel 53. Therefore, the airframe outlet airflow 67 from the airframe outlet 51 is directed smoothly to the discharge adapter 52 at the center of the discharge panel 53 and the airflow does not collide, and pressure loss is suppressed.
  • the distance between the discharge panel 53 and the centrifugal blower 1 is minimized, and the body 50 is downsized. Therefore, although it is desirable that the discharge panel 53 contacts the casing outlet 6a of the centrifugal blower 1, the discharge panel 53 does not necessarily need to contact the casing outlet 6a.
  • the blower with a sound deadening box using the centrifugal blower 1 according to the third embodiment of the present invention has good workability while reducing the performance (static pressure), and the body 50 is downsized.
  • the present invention is applied to a centrifugal blower used for a ventilation blower such as a duct fan or an air conditioner. Moreover, this invention is applicable also to the cooling of the installation apparatus using the ventilation from a body blower outlet other than the objectives of air conveyance, such as a ventilation ventilation apparatus.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
PCT/JP2013/007368 2012-12-25 2013-12-16 遠心送風機及びそれを用いた消音ボックス付送風機 WO2014103233A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2014554118A JP6295434B2 (ja) 2012-12-25 2013-12-16 遠心送風機及びそれを用いた消音ボックス付送風機
US14/653,782 US20160195106A1 (en) 2012-12-25 2013-12-16 Centrifugal fan, and fan equipped with sound-muffling box and using centrifugal fan
CN201380068014.0A CN104870827B (zh) 2012-12-25 2013-12-16 离心风机和使用其的带消音箱的风机

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
JP2012280667 2012-12-25
JP2012-280667 2012-12-25
JP2013-059528 2013-03-22
JP2013059528 2013-03-22
JP2013-191426 2013-09-17
JP2013191426 2013-09-17

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WO2014103233A1 true WO2014103233A1 (ja) 2014-07-03

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PCT/JP2013/007368 WO2014103233A1 (ja) 2012-12-25 2013-12-16 遠心送風機及びそれを用いた消音ボックス付送風機

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US (1) US20160195106A1 (zh)
JP (1) JP6295434B2 (zh)
CN (1) CN104870827B (zh)
WO (1) WO2014103233A1 (zh)

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CN104653479B (zh) * 2013-11-22 2017-05-10 珠海格力电器股份有限公司 离心式压缩机及具有其的冷水机组
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JPWO2014103233A1 (ja) 2017-01-12

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