WO2016199195A1 - Ventilateur axial - Google Patents

Ventilateur axial Download PDF

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Publication number
WO2016199195A1
WO2016199195A1 PCT/JP2015/066501 JP2015066501W WO2016199195A1 WO 2016199195 A1 WO2016199195 A1 WO 2016199195A1 JP 2015066501 W JP2015066501 W JP 2015066501W WO 2016199195 A1 WO2016199195 A1 WO 2016199195A1
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WO
WIPO (PCT)
Prior art keywords
stationary blade
blade
stationary
axial
motor
Prior art date
Application number
PCT/JP2015/066501
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English (en)
Japanese (ja)
Inventor
新井　俊勝
千景 門井
Original Assignee
三菱電機株式会社
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Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2015/066501 priority Critical patent/WO2016199195A1/fr
Publication of WO2016199195A1 publication Critical patent/WO2016199195A1/fr

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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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/54—Fluid-guiding means, e.g. diffusers

Definitions

  • the present invention relates to an axial blower.
  • Axial fans are used for ventilation fans, air conditioners, cooling fans, and the like.
  • An axial blower has a larger air volume but a lower static pressure rise than other types of blowers of the same size.
  • cooling applications such as switchboards in which electronic devices are incorporated.
  • Patent Documents 1 to 4 propose a method of increasing the static pressure by arranging a stationary blade or a static pressure increasing member upstream or downstream of the rotor blade.
  • a motor fixing member for fixing a motor and a stationary blade are integrated.
  • Patent Document 1 defines a curved shape of a stationary blade.
  • Patent Document 2 defines the angle between the rotating blade and the stationary blade, and
  • Patent Document 3 defines the distance in the rotation axis direction between the rotating blade and the stationary blade.
  • Patent document 4 is disclosing mounting the static pressure raising member without a stationary blade downstream of a rotary blade.
  • Patent Documents 1 to 3 the effect of increasing static pressure can be obtained, but since the motor fixing member and the stationary blade are integrated, the stationary blade is removed from the axial blower and the large air volume mode is set. It cannot be returned. That is, Patent Documents 1 to 3 cannot be easily changed between the large air volume mode and the static pressure increase mode in which the static pressure increase is large, depending on the use of the axial blower. Therefore, it becomes necessary to use different types of axial blowers depending on the application, which is troublesome during manufacturing and handling. In Patent Document 4, since the static pressure increasing member does not have a stationary blade, there is a possibility that the effect of increasing the static pressure cannot be sufficiently obtained with an axial blower having a large air volume.
  • the present invention has been made in view of the above, and can be easily changed between the large air volume mode and the static pressure increase mode, and can further increase the static pressure in the static pressure increase mode. It aims at obtaining the axial flow fan which can be performed.
  • the present invention is an axial blower that includes a stationary part and a rotating part that rotates in one direction about a rotating shaft with respect to the stationary part.
  • a rotating blade that is fixed to the rotating portion of the motor, rotates together with the rotating portion, and rotates in the one direction to form an air flow, and a flow direction that is a direction in which the air flows more than the rotating blade.
  • a stationary blade that is detachable from a stationary member and that connects the inner end and the outer end in a direction perpendicular to the rotation axis.
  • the straight line has a plurality of blades inclined in a direction opposite to a rotation direction of the rotary blade with respect to a direction orthogonal to the rotation axis.
  • the present invention it is possible to easily change between the large air volume mode and the static pressure increase mode, and to increase the static pressure in the static pressure increase mode.
  • FIG. 4 is a view of the axial blower of FIG. 4 as viewed from the base end side of the bell mouth duct. 4 is a cross-sectional view taken along the line VV in FIG. 4, showing the configuration of the axial blower before the stationary blade is arranged.
  • FIG. 4 is a view of the axial blower of FIG. 4 as viewed from the base end side of the bell mouth duct. 4 is a cross-sectional view taken along the line VV in FIG. 4, showing the configuration of the axial blower before the stationary blade is arranged.
  • the perspective view which shows the structure of the stationary blade used for a 1st comparative example The figure which looked at the axial blower concerning the 1st comparative example from the base end side of a bell mouth duct
  • the perspective view which shows the structure of the stationary blade which has a function of the motor fixing member used for the 2nd comparative example The figure which looked at the axial flow fan concerning the 2nd comparative example from the base end side of a bell mouth duct
  • the perspective view which shows an example of the structure of the stationary blade used for Embodiment 2 The figure which looked at an example of the axial blower concerning Embodiment 2 from the base end side of a bell mouth duct XX-XX sectional view of FIG. 19 showing an example of the configuration of the axial blower according to the second embodiment.
  • FIG. 1 The figure which shows the static pressure characteristic of the axial-flow fan of two examples of Embodiment 1, Embodiment 2, and a 2nd comparative example, when there is no stator blade
  • FIG. 2nd comparative example The figure which shows the fan efficiency of the axial-flow fan of two examples of Embodiment 1, Embodiment 2, and a 2nd comparative example, when there is no stationary blade.
  • Sectional drawing which shows the structure of the axial flow fan which concerns on Embodiment 3.
  • FIG. 1 is a view of the axial flow fans 110 and 120 according to the first embodiment when viewed from the base end side of the bell mouth duct 7.
  • 2 is a cross-sectional view taken along the line II-II in FIG. 1, showing an example of the configuration of the axial blower 110 according to the first embodiment.
  • FIG. 3 is a perspective view showing the axial blower 100 before the stationary blade 10 is arranged.
  • FIG. 4 is a view of the axial blower 100 of FIG. 3 as viewed from the base end side of the bell mouth duct 7.
  • 5 is a cross-sectional view taken along the line VV of FIG. 4 showing the configuration of the axial blower 100 before the stationary blade 10 is arranged.
  • FIG. 1 is a view of the axial flow fans 110 and 120 according to the first embodiment when viewed from the base end side of the bell mouth duct 7.
  • 2 is a cross-sectional view taken along the line II-II in FIG. 1, showing an example of the configuration of the axial blower 110 according
  • FIG. 6 is a perspective view showing the structure of the stationary blade 10 used in the first embodiment.
  • FIG. 7 is a cross-sectional view illustrating a configuration of an axial blower 120 that is another example of the axial blower according to the first embodiment.
  • FIG. 8 is a plan view showing the structure of the stationary blade 10 of FIG. 9 is a cross-sectional view taken along the line IX-IX in FIG. 10 is a cross-sectional view taken along the line XX of FIG.
  • FIG. 11 is a diagram showing a distribution of the solidity ⁇ in the radial direction of the stationary blade 10 of FIG.
  • FIG. 12 is a perspective view showing the structure of the stationary blade 13 used in the first comparative example.
  • FIG. 13 is a view of the axial blower 130 according to the first comparative example as viewed from the base end side of the bell mouth duct 7.
  • FIG. 14 is a perspective view showing a structure of a stationary blade 14 having a function of a motor fixing member used in the second comparative example.
  • FIG. 15 is a view of the axial blower 140 according to the second comparative example as viewed from the base end side of the bell mouth duct 7.
  • FIG. 16 shows the static pressure of the axial flow fan 100 when there is no stationary blade, the axial flow fan 110 according to Embodiment 1, the axial flow fan 130 of the first comparative example, and the axial flow blower 140 of the second comparative example. It is a figure which shows a characteristic.
  • FIG. 17 shows the fan efficiency of the axial flow fan 100 when there is no stationary blade, the axial flow fan 110 according to Embodiment 1, the axial flow fan 130 of the first comparative example, and the axial flow blower 140 of the second comparative example.
  • the axial-flow fan 110 includes a rotary blade 1, a motor 2, a motor fixing member 6, a bell mouth duct (duct) 7, and a stationary blade 10.
  • the rotary blade 1, the motor 2, the motor fixing member 6, and the stationary blade 10 are arranged inside the bell mouth duct 7, and from the upstream side to the downstream side in the flow direction (air blowing direction) described later.
  • the rotating blade 1, the motor 2, the motor fixing member 6, and the stationary blade 10 are arranged in this order.
  • Rotating blade 1 rotates around rotating shaft 3.
  • the rotary blade 1 has a plurality of blades arranged around the rotation axis 3 (circumferential direction).
  • the blades of the rotary blade 1 have a three-dimensional solid shape.
  • the rotary blade 1 has five blades formed radially from the outer periphery of a cylindrical boss portion 5 that houses the motor 2.
  • the rotary blade 1 of Embodiment 1 has five blades at equal intervals in the rotation direction 4, the number of blades is not limited to five. Any number of blades may be used, and this is the same in other embodiments.
  • the motor 2 has a stationary part 2a and a rotating part 2b that rotates relative to the stationary part 2a.
  • the rotating blade 1 is fixed to the rotating part 2b.
  • the motor 2 rotates the rotating blade 2 about the rotating shaft 3 by rotating the rotating portion 2b about the rotating shaft 3.
  • the rotating portion 2 b protrudes in the axial direction of the rotating shaft 3 with respect to the stationary portion 2 a.
  • the rotary blade 1 is fixed to a portion protruding from the stationary portion 2a of the rotating portion 2b. That is, in the rotating part 2b, the rotating blade 1 is fixed to the distal end side, and the proximal end side is inserted into the stationary part.
  • the rotation direction of the motor 2 is fixed in one direction.
  • the motor 2 rotates the rotor blade 1 in one direction of rotation 4 to form a wind flow in a predetermined direction (the direction of arrow A in FIG. 3).
  • the direction of arrow A is called the flow direction.
  • the upstream side in the flow direction is the distal end side (also simply referred to as the distal end side) of the rotating portion of the motor 2, and the downstream side in the flow direction is also referred to as the proximal end side (also simply referred to as the proximal end side) of the rotating portion of the motor 2. )
  • the bell mouth duct 7 is a cylindrical duct, and has a pipe line 7 a provided on the distal end side and a flat portion 7 b provided on the proximal end side.
  • the pipe line 7a has a bell mouth shape in which the cross-sectional area of the inner peripheral surface continuously decreases from the distal end side to the proximal end side, that is, from the upstream side to the downstream side in the flow direction.
  • the flat portion 7b is a portion where the cross-sectional area of the inner peripheral surface does not change in the axial direction.
  • the bell mouth duct 7 has a large flat portion 7b with respect to the pipe line 7a, and the boundary is a stepped portion 7c.
  • An upstream R portion 9a is provided at the distal end of the conduit 7a, and a downstream R portion 9b is provided at the proximal end.
  • the central axis of the pipe line 7 a coincides with the rotation axis 3.
  • the bell mouth duct 7 forms an air flow path for airflow generated by the rotation of the rotary blade 1.
  • the motor fixing member 6 has four pillar members 6a and two arc members 6b as shown in FIG.
  • the four column members 6 a are arranged at intervals in the circumferential direction of the rotation shaft 3, in this embodiment, at intervals of 90 °, and extend in the radial direction of the rotation shaft 3, that is, in the direction orthogonal to the rotation shaft 3.
  • the four pillar members 6 a have radially inner ends in contact with the stationary portion 2 a of the motor 2 and radially outer ends fixed to the flat portion 7 b of the bell mouth duct 7.
  • the four column members 6 a extend radially from the stationary portion 2 a of the motor 2.
  • the two arc members 6b are provided in an arc shape along the stationary portion 2a of the motor 2, and are connected to the adjacent two column members 6a.
  • the arc member 6b one end of the arc is fixed to the column member 6a, and the other end of the arc is fixed to the adjacent column member 6a.
  • the fixing member 6 two arc members 6b are fixed with the stationary portion 2a of the motor 2 interposed therebetween, and the two arc members 6b are fixed to the bell mouth duct 7 with four column members 6a.
  • the motor fixing member 6 fixes the motor 2 at a predetermined position with respect to the bell mouth duct 7.
  • the motor fixing member 6 is an internal space of the bell mouth duct 7 (a space surrounded by the inner peripheral surface), and a position where the central axis of the bell mouth duct 7 and the rotation shaft 3 coincide with each other.
  • the motor 2 is fixed.
  • the axial flow fan 110 is configured such that the motor 2 is fixed to the internal space of the bell mouth duct 7 by the motor fixing member 6, so that the rotary blade 1 rotates in the internal space of the bell mouth duct 7. 3 is supported so as to be rotatable around 3.
  • the rotary blade 1 is housed so that the outer peripheral tip 8 of the rotary blade is inside the bell mouth duct 7.
  • the rotor blade 1 is the upstream tip in the axial direction, and the rotor blade outer peripheral tip 8 that is the outer tip in the radial direction is closer to the base end (downstream side) than the upstream R portion 9a. Is arranged.
  • the stationary blade 10 is disposed on the proximal end side with respect to the motor fixing member 6.
  • the stationary blade 10 is fixed to the bell mouth duct 7 in a detachable state. As shown in FIG. 2, the stationary blade 10 is positioned by being fitted inside the stepped portion 7 c of the flat portion 7 b of the bell mouth duct 7 in the axial blower 110.
  • the stationary blade 10 is detachably provided on the base end side opposite to the drive shaft of the motor 2, and has a plurality of blades 11 having an advancing shape opposite to the rotation direction 4 of the rotating blade 1.
  • the stationary blade 10 includes an inner ring 10 a and an outer ring 10 b arranged concentrically, and eight blades 11 provided between the inner ring 10 a and the outer ring 10 b.
  • the blade 11 has an advancing shape in the direction opposite to the rotation direction 4 of the rotary blade 1. Specifically, in the blade 11, a straight line connecting the inner end and the outer end in the radial direction of the rotary shaft 3 is in the rotational direction 4 of the rotary blade 1 with respect to the radial direction of the rotary shaft 3.
  • the stationary blade 10 of Embodiment 1 has eight blades 11, the number of the blades 11 is not limited, and may be seven or less or nine or more.
  • the inner ring 10 a is disposed around the stationary portion 2 a of the motor 2, and a concave portion in contact with the column member 6 a is formed on the surface on the tip side in the axial direction.
  • the outer peripheral ring 10b has a larger diameter than the downstream R portion 9b and is fixed to the bell mouth duct 7 in a detachable state.
  • the stationary blade 10 two blades 11 are disposed between each of the four column members 6 a of the motor fixing member 6 in the circumferential direction when viewed from the direction of the rotating shaft 3. That is, since the stationary blade 10 has a structure in which the eight blades 11 are arranged so as to avoid the four column members 6a in the circumferential direction, the interference with the motor fixing member 6 is minimized. Therefore, the stationary blade 10 can minimize the influence of the restriction of the shape such as the outer peripheral portion being cut due to the presence of the motor fixing member 6.
  • the stationary blade 10 of the first embodiment is disposed at a position where the central axes of the inner ring 10a and the outer ring 10b coincide with the rotation axis 3. Further, the stationary blade 10 is slidable with respect to the rotating blade 1 in the direction in which the rotating shaft 3 extends.
  • the direction in which the rotation shaft 3 extends is appropriately referred to as an axial direction.
  • the stationary blade 10 can adjust the position in the axial direction with respect to the rotary blade 1 by arranging a distance adjusting member between the stationary blade 10 and the bell mouth duct 7.
  • the distance adjustment member is exemplified by a shim, but is not limited thereto. Since the axial blower 110 can be installed by adjusting the distance from the rotary blade 1 in the axial direction of the rotary shaft 3, the influence of interference received from the rotary blade 1 can be adjusted to be small, and the noise can be adjusted to be small. it can.
  • the stationary blade 10 when the installation position of the stationary blade 10 is adjusted, the stationary blade 10 can be rotated around the rotation shaft 3 in the rotation direction 4 and in the opposite direction, and the eight blades 11 are four in the circumferential direction. It adjusts so that it may arrange
  • the stationary blade 10 is adjusted and installed in the axial direction, the rotation direction 4 and the opposite direction, and then fixed to the bell mouth duct 7 by a fixing mechanism.
  • the fixing mechanism is a screw, it is not limited to this.
  • the stationary blade 10 may be fixed to the bell mouth duct 7 by a removable mechanism other than a screw.
  • the stationary blade 10 shown in FIG. 2 is fixed to the bell mouth duct 7, but may be fixed to the stationary portion 2 a of the motor 2.
  • the stationary blade 10 is fixed to the stationary portion 2 a of the motor 2 in a detachable state.
  • the axial flow fan 120 is installed with the stationary blade 10 having a sufficient distance from the rotary blade 1 in the axial direction, so that it is possible to reduce the influence of interference from the wake of the rotary blade 1. Can reduce noise.
  • the stationary blade 10 has a forward angle ⁇ that is a parameter representing the forward shape of 40 ° in all of the eight blades 11.
  • the stagger angle ⁇ that is a parameter indicating the mounting angle of each blade 11 is 35 ° in all eight blades 11.
  • the stagger angle ⁇ is constant from the inner peripheral portion that is the innermost peripheral portion in the radial direction of the rotating shaft 3 to the outer peripheral portion that is the outermost peripheral portion in the radial direction. Therefore, the stationary blade 10 is accommodated in the bell mouth duct 7 in the direction of the rotating shaft 3 as shown in FIG.
  • the stationary blade 10 has a forward tilt angle ⁇ z, which is a parameter representing the inclination of each blade 11 toward the base end side of the bell mouth duct 7, of 3.75 °. is there.
  • the stationary blade 10 preferably has a forward angle ⁇ within a range of 0 ° to 45 °.
  • a value ⁇ obtained by subtracting the stagger angle ⁇ th of the blade 11 of the stationary blade 10 from the stagger angle ⁇ th of the outer peripheral portion of the blade of the rotary blade 1 is in a range of 15 ° to 40 °. preferable.
  • the stationary blade 10 preferably has a forward tilt angle ⁇ z in the range of 0 ° to 15 °.
  • the stator blade 10 has a blade pitch t and a blade chord length L, which are parameters representing the shape of the eight blades 11.
  • the inter-blade pitch t and the chord length L are determined as a solidity ⁇ that is a ratio of the inter-blade pitch t and the chord length L.
  • the inter-blade pitch t and the chord length L both have a radial distribution from the inner periphery to the outer periphery. Therefore, the solidity ⁇ has a radial distribution from the inner periphery to the outer periphery. If the inter-blade pitch t is not constant, the solidity ⁇ is calculated using the average value of the inter-blade pitch t in Equation (1).
  • the stationary blade 10 has a solidity ⁇ of all eight blades 11 in a radial direction from the inner ring 10 a to the outer ring 10 b in a radial direction, not a distribution according to a linear function, but a convex 2
  • the distribution follows the following function.
  • the vane 10 has a solidity ⁇ of 0.25 at the outer peripheral portion.
  • the stationary blade 10 of the first embodiment is accommodated in the bell mouth duct 7 in the direction of the rotation shaft 3 because the radial distribution of the solidity ⁇ gradually decreases from the inner periphery to the outer periphery. Therefore, the axial blower 110 does not change the axial length regardless of whether the stationary blade 10 is attached or detached, and the volume does not change.
  • the stationary blade 10 has a shape satisfying the solidity of distribution according to a downward convex quadratic function, so that interference with the rotary blade 1 is suppressed and the stationary blade 10 is housed inside the bell mouth duct 7.
  • the blade area can be increased.
  • the stationary blade 13 of the axial blower 130 shown in FIGS. 12 and 13 includes eight inner rings 10a and outer rings 10b arranged concentrically, and eight sheets provided between the inner rings 10a and 10b. And blades 13a.
  • the stationary blade 13 has a forward angle ⁇ of 0 ° in all of the eight blades 13a. That is, in the stationary blade 13, the eight blades 13 a do not have the advance shape in the direction opposite to the rotation direction 4 of the rotary blade 1.
  • the stationary blade 13 has a blade area equivalent to that of the stationary blade 10 in a state of being housed inside the bell mouth duct 7.
  • the axial blower 140 shown in FIGS. 14 and 15 is a second comparative example of the axial blower 110 according to the first embodiment.
  • the stationary blade 14 of the axial blower 140 shown in FIGS. 14 and 15 includes nine inner ring 14b and outer ring 14c arranged concentrically, and nine sheets provided between the inner ring 14b and outer ring 14c. And a blade 14a.
  • the stationary blade 14 has an advance angle ⁇ of 40 ° in all nine blades 14a.
  • the stator blade 14 has an inner ring 14 b fixed to the stationary part 2 a and an outer ring 14 c fixed to the flat part 7 b of the bell mouth duct 7.
  • the stationary blade 14 also has a function equivalent to that of the motor fixing member 6.
  • the axial flow fan 140 cannot be used as an axial flow fan when the stationary blade 14 is not incorporated because the stationary blade 14 fixes the motor 2.
  • the stationary blade 14 has a blade area equivalent to that of the stationary blade 10 in a state of being housed inside the bell mouth duct 7.
  • the axial flow fan 110 according to the first embodiment can increase the static pressure more than the axial flow fan 100 in which the stationary blade 10 is not incorporated and the axial flow fan 130 in which the stationary blade 13 is incorporated. it can.
  • the axial flow fan 110 according to Embodiment 1 has a lower static pressure than the axial flow fan 140 incorporating the stationary blade 14. That is, the stationary blade 10 reduces the increase in static pressure compared to the stationary blade 14, but improves the increase in static pressure when applying static pressure compared to the stationary blade 13.
  • the axial fan 110 according to the first embodiment has higher fan efficiency than the axial fan 100 in which the stationary blade 10 is not incorporated and the axial fan 130 in which the stationary blade 13 is incorporated. Further, the axial fan 110 according to the first embodiment has a slightly lower fan efficiency than the axial fan 140 incorporating the stationary blade 14. That is, the stationary blade 10 reduces the fan efficiency as compared with the stationary blade 14, but improves the fan efficiency when a static pressure is applied as compared with the stationary blade 13.
  • the axial blower 110 can be used as the large flow rate mode in which the static pressure rise is low as the axial blower 100 when the stationary blade 10 is not incorporated.
  • the axial flow fan 110 incorporates the stationary blade 10 configured such that the plurality of blades 11 are arranged between the motor fixing members 6 in the circumferential direction
  • the axial flow fan 130 incorporating the stationary blade 13 is incorporated. It can be used as a static pressure increase mode in which the static pressure increase is further improved and the efficiency is improved as compared with the axial flow fan 140 incorporating the stationary blade 14.
  • the stationary blade 10 can be detached from the base end side of the bell mouth duct 7 with respect to the motor fixing member 6 by a simple method, and the stationary blade 10 can be easily assembled and removed. Therefore, it can be easily changed between the large air volume mode and the static pressure increase mode.
  • the axial flow fan 110 since the stationary blade 10 is accommodated in the bell mouth duct 7 in the direction of the rotating shaft 3, the axial flow fan 100 in which the stationary blade 10 is not incorporated regardless of the mode. Since the length in the direction of the rotating shaft 3 does not change and the volume does not change, it is easy to use.
  • FIG. FIG. 18 is a perspective view showing a structure of a stationary blade 15 which is an example of a stationary blade used in the second embodiment.
  • FIG. 19 is a view of an axial blower 150 as an example of the axial blower according to the second embodiment when viewed from the base end side of the bell mouth duct 7.
  • 20 is a cross-sectional view taken along the line XX-XX in FIG. 19, showing the configuration of the axial blower 150 according to the second embodiment.
  • FIG. 21 is a perspective view showing a structure of a stationary blade 16 which is another example of the stationary blade used in the second embodiment.
  • FIG. 22 is a view of an axial-flow fan 160 as another example of the axial-flow fan according to the second embodiment when viewed from the base end side of the bell mouth duct 7.
  • FIG. 23 is a cross-sectional view taken along the line XXIII-XXIII in FIG. 22 showing the configuration of the axial blower 160 according to the second embodiment.
  • FIG. 24 shows an axial flow fan 100 without a stationary blade, an axial flow fan 110 according to the first embodiment, an axial flow blower 140 of the second comparative example, and two examples of the axial flow blower of the second embodiment. It is a figure which shows the static pressure characteristics of 150,160.
  • FIG. 25 shows an axial flow fan 100 without a stationary blade, an axial flow fan 110 according to the first embodiment, an axial flow blower 140 according to the second comparative example, and two examples of the axial flow blower according to the second embodiment. It is a figure which shows the fan efficiency of 150,160.
  • the stationary blade 10 is changed from the first embodiment to the stationary blade 15 shown in FIGS. 18 to 20 or the stationary blade 16 shown in FIGS. It has been done.
  • the axial flow fans 150 and 160 according to the second embodiment use the same code group as that of the first embodiment in the same configuration as that of the first embodiment, and a detailed description thereof will be omitted.
  • the stationary blade 15 is incorporated on the base end side of the bell mouth duct 7.
  • the stationary blade 16 is incorporated on the base end side of the bell mouth duct 7.
  • the stationary blade 15 includes an inner ring 15b and an outer ring 15c arranged concentrically, and eight blades 15a provided between the inner ring 15b and the outer ring 15c.
  • the vane 15 has a solidity ⁇ of 0.5 in all the eight blades 15a, and the forward inclination angle ⁇ z is increased when the blade 15a is inclined in the direction A as compared with the blade 11 of the vane 10. It is larger than the stationary blade 10.
  • the inner ring 15 b and the outer ring 15 c have an adjustment space 17.
  • the vane 15 has an increased blade area as compared with the vane 10 due to the fact that the solidity ⁇ at the outer peripheral portion is approximately twice that of the vane 11 of the vane 10. Improve the air blowing characteristics of the flow fan. Since the vane 15 has a larger forward tilt angle ⁇ z than the vane 10, the axial distance from the rotor blade 1, that is, the gap can be secured to the same extent as in the first embodiment. On the other hand, when the stationary blade 15 is detachably incorporated in the base end side of the motor fixing member 6, as shown in FIG. 20, it is not completely accommodated in the bell mouth duct 7, and the base end side of the bell mouth duct 7. Protrude from.
  • the axial blower 150 has a length HS1 in the direction of the rotating shaft 3 when the stationary blade 15 is incorporated and the stationary blade 15 protrudes from the base end side of the bell mouth duct 7 and the stationary blade 15 is not incorporated.
  • HS1 / H which is a ratio to the length H in the direction of the rotation axis 3, is 0.29.
  • the adjustment space 17 has a structure that avoids the motor fixing member 6, and reduces interference between the blade 15 a and the motor fixing member 6 that increases as the solidity ⁇ increases.
  • the stationary blade 16 includes an inner ring 15b and an outer ring 15c arranged concentrically, and eight blades 16a provided between the inner ring 15b and the outer ring 15c.
  • the vane 16 has a solidity ⁇ of 1.0 in all of the eight blades 16a, and the vane 16a is inclined in the direction A as compared with the blades 11 of the vane 10, so that the forward inclination angle ⁇ z is increased. It is larger than the stationary blade 10.
  • the stationary blade 16 has an inner circumferential ring 15 b and an outer circumferential ring 15 c having an adjustment space 17.
  • the stationary blade 16 has an increased blade area as compared with the stationary blade 10, because the solidity ⁇ at the outer peripheral portion is about four times that of the stationary blade 10.
  • the air blowing characteristics of the flow blower 160 are improved. Since the vane 16 has a forward tilt angle ⁇ z larger than that of the vane 10, the distance in the direction of the rotary shaft 3 with respect to the rotary blade 1, that is, the gap can be secured to the same extent as in the first embodiment.
  • the stationary blade 16 is detachably incorporated in the base end side of the motor fixing member 6, as shown in FIG. 23, it is not completely stored in the bell mouth duct 7, and the base end side of the bell mouth duct 7 Protrude from.
  • the axial blower 160 has a length HS2 in the direction of the rotating shaft 3 when the stationary blade 16 is incorporated and the stationary blade 16 protrudes from the base end side of the bell mouth duct 7 and the stationary blade 16 is not incorporated.
  • HS2 / H which is a ratio to the length H in the direction of the rotary shaft 3, is 1.06.
  • the adjustment space 17 has a structure that avoids the motor fixing member 6, and reduces interference between the blade 16 a and the motor fixing member 6 that increases as the solidity ⁇ increases.
  • FIGS. 24 and 25 the axial blower 150 is represented as the embodiment 2-1
  • the axial blower 160 is represented as the embodiment 2-2.
  • the measurement results of the static pressure and fan efficiency for the axial fan 140 shown in FIG. 15 are also shown.
  • the axial flow fan 150 in which the stationary blade 15 is incorporated includes the axial flow fan 100 in which the stationary blade is not incorporated, the axial flow fan 140 in which the stationary blade 14 is incorporated, and the stationary blade 10.
  • the static pressure can be made larger than that of the axial flow fan 110. That is, the stationary blade 15 further improves the increase in static pressure when a static pressure is applied, as compared with the stationary blade 10 and the stationary blade 14.
  • the axial flow fan 160 incorporating the stationary blade 16 can further increase the static pressure as compared with the axial flow fan 150 incorporating the stationary blade 15. That is, the stationary blade 16 further improves the static pressure increase when the static pressure is applied, as compared with the stationary blade 15.
  • the axial flow fan 150 in which the stationary blade 15 is incorporated includes the axial flow fan 100 in which the stationary blade is not incorporated, the axial flow fan 140 in which the stationary blade 14 is incorporated, and the stationary blade 10.
  • the fan efficiency can be made larger than that of the axial fan 110. That is, the stationary blade 15 further improves the fan efficiency when static pressure is applied, as compared with the stationary blade 10 and the stationary blade 14.
  • the axial fan 160 incorporating the stationary blade 16 can further increase fan efficiency than the axial fan 150 incorporating the stationary blade 15. That is, the stationary blade 16 further improves the fan efficiency when a static pressure is applied, as compared with the stationary blade 15.
  • HS / H which is a ratio of the length HS in the direction 3 and the length H in the direction of the rotating shaft 3 excluding the stationary blade is 0.29 to 1.06.
  • FIG. 26 is a cross-sectional view illustrating a configuration of an axial flow fan 170 according to the third embodiment.
  • FIG. 27 is a perspective view showing the structure of a stationary blade used in the third embodiment.
  • the axial blower 170 according to Embodiment 3 is obtained by stacking two stationary blades 10 in the direction of the rotating shaft 3 in Embodiment 1 as shown in FIGS. 26 and 27.
  • the axial flow fan 170 according to the third embodiment uses the same code group as that of the first embodiment in the same configuration as that of the first embodiment, and a detailed description thereof is omitted.
  • the stationary blade 10 has a fixing mechanism for fixing the stationary blade 10 itself and another stationary blade 10 stacked on the stationary blade 10 to the inner ring 10a or the outer ring 10b. 10 are stacked and fixed. As shown in FIG. 27, the stationary blade 10 is arranged in the direction 18 of adjusting the other stationary blade 10 with respect to one stationary blade 10 stacked on the inner ring 10 a or the outer ring 10 b provided with the fixing mechanism. It has an adjustment mechanism that rotates and adjusts. As in the second embodiment, the stacked stationary blades 10 further improve the static pressure rise and fan efficiency when applying the static pressure of the axial blower. In particular, the stacked stationary blade 10 is adjusted by the adjusting mechanism so that the two blades 11 to be stacked overlap each other like a single blade, and then fixed by the fixing mechanism. Increases static pressure and improves fan efficiency.
  • the third embodiment includes the case where three or more stationary blades 10 are stacked.
  • the static pressure increase and fan efficiency can be adjusted by stacking a plurality of one type of stationary blades 10.
  • a plurality of static pressure increase modes can be provided, and can be easily changed between the plurality of static pressure increase modes.
  • the configuration described in the above embodiment shows an example of the contents of the present invention, and can be combined with another known technique, and can be combined with other configurations without departing from the gist of the present invention. It is also possible to omit or change the part.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne un ventilateur axial (110), lequel ventilateur comporte : une aube rotative (1) ; un moteur (2) ; et une aube de stator (10). Le moteur (2) a des parties fixes (2a) et une partie rotative (2b) qui tourne par rapport aux parties fixes (2a). L'aube rotative (1) est fixée à la partie rotative (2b) dans le moteur (2). Le moteur (2) fait tourner la partie rotative (2b) autour d'un axe de rotation (3), de façon à faire ainsi tourner l'aube rotative (1) autour de l'axe de rotation (3) dans une direction. Le moteur (2) fait tourner l'aube rotative (1) dans une direction, de façon à former ainsi un écoulement d'air dans une direction prédéterminée. L'aube de stator (10) est disposée en un emplacement qui est plus proche d'un côté aval dans la direction dans laquelle s'écoule l'air que ne l'est l'aube rotative (1), et est fixée amovible à un élément côté fixe. L'aube de stator (10) a une pluralité de pales (11) dans chacune desquelles une ligne droite reliant une extrémité interne et une extrémité externe dans une direction perpendiculaire à l'axe de rotation (3) est inclinée dans la direction opposée vis-à-vis d'une direction de rotation (4) de l'aube rotative (1), par rapport à une direction perpendiculaire à l'axe de rotation (3).
PCT/JP2015/066501 2015-06-08 2015-06-08 Ventilateur axial WO2016199195A1 (fr)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110595031A (zh) * 2019-10-30 2019-12-20 广东美的制冷设备有限公司 风道部件及落地式空调室内机
WO2021181024A1 (fr) * 2020-03-13 2021-09-16 Valeo Systemes Thermiques Bras de maintien pour armature de support

Citations (8)

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Publication number Priority date Publication date Assignee Title
JPS57105593A (en) * 1980-12-19 1982-07-01 Sanyo Electric Co Ltd Fan
JPS5947394U (ja) * 1982-09-20 1984-03-29 三洋電機株式会社 送風機
JP2000130809A (ja) * 1998-10-21 2000-05-12 Toshiba Corp 換気扇
US20020159883A1 (en) * 2001-04-30 2002-10-31 Simon Glenn C. Combination airflow straightener and finger guard for use with a fan
JP2004132300A (ja) * 2002-10-11 2004-04-30 Minebea Co Ltd 軸流送風装置
JP2008196504A (ja) * 2008-05-21 2008-08-28 Sanyo Denki Co Ltd 軸流送風機
JP2009197593A (ja) * 2008-02-19 2009-09-03 Nippon Densan Corp ファン装置
JP2012026291A (ja) * 2010-07-20 2012-02-09 Hitachi Ltd 軸流ファン

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57105593A (en) * 1980-12-19 1982-07-01 Sanyo Electric Co Ltd Fan
JPS5947394U (ja) * 1982-09-20 1984-03-29 三洋電機株式会社 送風機
JP2000130809A (ja) * 1998-10-21 2000-05-12 Toshiba Corp 換気扇
US20020159883A1 (en) * 2001-04-30 2002-10-31 Simon Glenn C. Combination airflow straightener and finger guard for use with a fan
JP2004132300A (ja) * 2002-10-11 2004-04-30 Minebea Co Ltd 軸流送風装置
JP2009197593A (ja) * 2008-02-19 2009-09-03 Nippon Densan Corp ファン装置
JP2008196504A (ja) * 2008-05-21 2008-08-28 Sanyo Denki Co Ltd 軸流送風機
JP2012026291A (ja) * 2010-07-20 2012-02-09 Hitachi Ltd 軸流ファン

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110595031A (zh) * 2019-10-30 2019-12-20 广东美的制冷设备有限公司 风道部件及落地式空调室内机
CN110595031B (zh) * 2019-10-30 2024-04-26 广东美的制冷设备有限公司 风道部件及落地式空调室内机
WO2021181024A1 (fr) * 2020-03-13 2021-09-16 Valeo Systemes Thermiques Bras de maintien pour armature de support
FR3108147A1 (fr) * 2020-03-13 2021-09-17 Valeo Systemes Thermiques Bras de maintien pour armature de support

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