CN105026768A - Impeller and axial blower in which same is used - Google Patents
Impeller and axial blower in which same is used Download PDFInfo
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- CN105026768A CN105026768A CN201480012547.1A CN201480012547A CN105026768A CN 105026768 A CN105026768 A CN 105026768A CN 201480012547 A CN201480012547 A CN 201480012547A CN 105026768 A CN105026768 A CN 105026768A
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- blade
- blade angle
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- impeller
- angle
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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
- F04D29/26—Rotors specially for elastic fluids
- F04D29/32—Rotors specially for elastic fluids for axial flow pumps
- F04D29/38—Blades
- F04D29/384—Blades characterised by form
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- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
In the present invention, an impeller is provided with a boss section and a plurality of rotating blades. The boss section has a cylindrical outer shape, and the rotating blades are radially attached to the boss section. The rotating blades have a first region and a second region. The first region has a first stagger angle distribution from an inner circumferential edge to a predetermined radial position, the inner circumferential edge being connected to the boss section. The second region has a second stagger angle distribution from a predetermined radial position to an outer circumferential edge, the predetermined radial position being adjacent to the first region. The second stagger angle distribution is different from the first stagger angle distribution. The second stagger angle distribution has a distribution in which the stagger angle decreases from a maximum radial position in the second region to the outer circumferential edge, the stagger angle being greatest at the maximum radial position.
Description
Technical field
The present invention relates to for ventilation fan, aircondition impeller and employ the axial flow blower of this impeller.
Background technique
In the past, the axial flow blower for ventilation fan, aircondition etc. had following structure: form at housing the opening that periphery has horn mouth shape, and be configured with the impeller with rotation blade at opening.In this axial flow blower, mainly in order to low noise, a part for rotation blade is configured to be projected into the position higher than bell-mouthed height.In addition, when rotation blade is configured to not outstanding from flare end, by the curvature of bell-mouthed suction side is formed achieve low noise greatly.
In addition, propose by making the shape of the rotation blade of impeller be that the three-dimension curved surface shape specified realizes low noise and high efficiency (such as with reference to patent documentation 1-3).Patent Document 1 discloses following content: the lineal shape of the link position be connected with hub portion with blade by making link blade tip portion becomes the angle of regulation and the blade angle making blade-shaped become regulation carrys out restraint speckle.Patent Document 2 discloses following content: reduce to suck the top rake in direction and increase sense of rotation sweepforward angle and carry out restraint speckle.Patent Document 3 discloses a kind of axial flow blower, this axial flow blower has as lower blade: it is constant for making from hub portion to first top rake of first area of the position of regulation, and makes the second top rake be positioned at than the second area of outer circumferential side side, first area be formed larger than the first top rake.
Prior art document
Patent documentation
Patent documentation 1: Japanese Patent Publication 2-2000 publication
Patent documentation 2: Japanese Unexamined Patent Publication 11-303794 publication
Patent documentation 3: Japanese Patent No. 3203994 publication
Summary of the invention
The problem that invention will solve
Patent documentation 1-3 described above is such, by making blade shape be the three-dimensional shape specified, achieves low noise and high efficiency, but for not considering fully from the suction of blade side near leading edge periphery.
The present invention completes to solve problem as above, its object is to provide a kind of and considers the axial flow blower laterally sucking and also can realize low noise and high efficiency.
For solving the means of problem
Rotation blade of the present invention possesses: hub portion, and it has columned profile; And multiple rotation blade, it is radially installed on hub portion, and rotation blade has: first area, and it is from the inner circumference edge being connected to hub portion to radial location of regulation and have the first blade angle distribution; And second area, its radial location from the regulation adjoined with first area is to outer periphery, and there is the second different blade angle that to distribute from the first blade angle distribute, the second blade angle distribution has blade angle from second area intra vane established angle being the greatly distribution that reduces to outer periphery of radial location greatly.
The effect of invention
According to rotation blade of the present invention, the blade angle of the second area that there is the rotation blade laterally sucked is set to and there is the second blade angle being suitable for increasing corresponding angle such to the flow of horizontal intake distributes, thus the stripping of the flowing near blade periphery can be prevented, therefore, it is possible to realize reduction and high efficiency because laterally sucking the noise caused.
Accompanying drawing explanation
Figure 1A is the stereogram of the mode of execution 1 representing axial flow blower of the present invention.
Figure 1B is the stereogram of the mode of execution 1 representing axial flow blower of the present invention.
Fig. 2 is the schematic top plan view of the mode of execution 1 representing impeller of the present invention.
Fig. 3 is the schematic side view of the mode of execution 1 representing impeller of the present invention.
Fig. 4 is the cylinder section unfolded drawing of rotation blade in the radial position of regulation of the impeller of Fig. 2.
Fig. 5 is the chart of the blades installation angle distribution of the rotation blade representing Fig. 2.
Fig. 6 is the cylinder section unfolded drawing of rotation blade at the radial location R1 place of first area of Fig. 2.
Fig. 7 is the cylinder section unfolded drawing of rotation blade at the radial location R2 place of second area of Fig. 2.
Fig. 8 is the schematic side view of an example of the impeller representing comparative example.
Fig. 9 represents the schematic diagram when not considering relative velocity vector when laterally sucking.
Figure 10 represents the schematic diagram when considering relative velocity vector when laterally sucking.
Figure 11 is the schematic diagram of the relation between the relative velocity vector of the impeller representing Fig. 2 and air-flow.
Figure 12 is the schematic diagram of the relation between the relative velocity vector of the impeller of the comparative example representing Fig. 8 and air-flow.
Figure 13 is the chart of the ratio noise characteristic represented when the impeller of the comparative example of the impeller and Fig. 8 employing Fig. 2.
Figure 14 is the chart of the fan efficiency characteristic represented when the impeller of the comparative example of the impeller and Fig. 8 employing Fig. 2.
Figure 15 is the chart of the minimum difference than noise represented when the impeller of the comparative example of the impeller and Fig. 8 employing Fig. 2.
Figure 16 is the chart of the difference of the highest fan efficiency represented when the impeller of the comparative example of the impeller and Fig. 8 employing Fig. 2.
Figure 17 is when the impeller of the comparative example of the impeller and Fig. 8 employing Fig. 2, uses the expansion sectional view by different leaves established angle of outer periphery to carry out the chart of the comparison of height.
Figure 18 is the chart of the blades installation angle distribution of the rotation blade of the mode of execution 2 representing impeller of the present invention.
Figure 19 is the cylinder section unfolded drawing of rotation blade at the radial location R1 place of first area of Figure 18.
Figure 20 is the chart of the fan efficiency characteristic represented when employing the impeller of the impeller of Fig. 2, the impeller of the comparative example of Fig. 8 and Figure 18.
Figure 21 is the chart of the fan efficiency characteristic represented when employing the impeller of the impeller of Fig. 2, the impeller of the comparative example of Fig. 8 and Figure 18.
Embodiment
Below, with reference to accompanying drawing, impeller of the present invention be described and employ the mode of execution of axial flow blower of this impeller.Fig. 1 is the stereogram of the mode of execution 1 representing axial flow blower of the present invention, with reference to Fig. 1, axial flow blower 1 is described.In addition, Figure 1A represents the stereogram observing axial flow blower from front, and Figure 1B represents the stereogram observing axial flow blower 1 from the back side.The axial flow blower 1 of Fig. 1 possesses: housing 2; Impeller 10, it is configured at suction port in rotatable mode; And motor M, its drives impeller makes it rotate.Housing 2 is received impeller 10 in the mode that impeller 10 is rotatable and is formed with opening 3, and this opening 3 is the wind paths passed through for the air-flow that produced by impeller, is formed with diameter expands such horn mouth 4 towards the upstream side of air stream in the edge of opening 3.
Impeller 10 possesses: the roughly columned hub portion 11 of profile; And multiple rotation blade 12, it is set to the periphery being radially installed on hub portion 11.Hub portion 11 is connected to the motor M being held in housing 2 on running shaft CL, is driven by motor M, and hub portion 11 is rotated up in arrow RR side centered by running shaft CL, produces the air-flow of arrow A direction (with reference to Fig. 3).In addition, the impeller 10 exemplified with Fig. 1 has the situation of 5 rotation blades 12, but the sheet number of rotation blade 12 also can be the multi-disc of 3 or other quantity.
Fig. 2 is the schematic top plan view of the mode of execution 1 representing impeller of the present invention, and Fig. 3 is the schematic side view of the mode of execution 1 representing impeller of the present invention, and the rotation blade 12 of impeller 10 is described with reference to Fig. 2 and Fig. 3.In addition, in figs. 2 and 3 exemplified with 1 rotation blade 12, and other the rotation blade 12 being installed on hub portion 11 is also of similar shape.The rotation blade 12 of Fig. 2 has the three-dimensional shape of regulation, be formed with leading edge 12a, trailing edge 12b, these four limits of inner circumference edge 12c and outer periphery 12d, this leading edge 12a is positioned at the forward side of sense of rotation RR, this trailing edge 12b is positioned at the opposite direction side of sense of rotation RR, this inner circumference edge 12c is connected to hub portion 11, and this outer periphery 12d is positioned at housing 2 side.
Rotation blade 12 has: first area AR1, and it is from hub portion 11 to radial location (boundary position) Rd of regulation and have the first blade angle distribution D ξ 1; And second area AR2, it is from boundary position Rd to outer periphery 12d and have the second different blade angle of the D ξ 1 that to distribute from the first blade angle and to distribute D ξ 2.This boundary position Rd is set as, such as, relative to the length from the radial direction the position Rt on the position Rb to outer periphery 12d on inner circumference edge 12c, and boundary position Rd=0.7 × (Rt-Rb).At this, the expansion sectional view of the arbitrary point that Fig. 4 is rotation blade 12 on the line of the mid point of the mid point linking leading edge 12a and trailing edge 12b.As shown in Figure 4, blade angle ξ refers to angle ξ formed by blade string of a musical instrument SL and vertical line HL, and this blade string of a musical instrument SL links leading edge 12a and trailing edge 12b, and this vertical line HL extends abreast with running shaft CL from the leading edge 12a of rotation blade 12.
Fig. 5 is the chart of an example of the blade angle distribution of the rotation blade 12 representing Fig. 2.In addition, in the line segment of the distribution of the expression blade angle ξ of Fig. 5, the left end of line segment is the blade angle ξ b at the radial location Rb place of the inner circumference edge 12c being connected to hub portion 11, and right-hand member represents the blade angle ξ t at the radial location Rt place of outer periphery 12d.In Figure 5, the first blade angle distribution D ξ 1 of first area AR1 has blade angle ξ and becomes distribution so greatly gradually in continuous print mode smoothly, particularly, the first blade angle distribution D ξ 1 is blade angle ξ with the distribution that increases of constant increment rate linarity (linear function) ground.First blade angle distribution D ξ 1 is such as following distribution: the blade angle ξ b=58 ° being set as the radial location Rb of inner circumference edge 12c, be set as the blade angle ξ d=64.46 ° at boundary position Rd place, increase to the first area AR1 Leaf established angle ξ linarity between radial location Rb and boundary position Rd.
The second blade angle distribution D ξ 2 of second area AR2 has following distribution: blade angle ξ becomes large from boundary position Rd in the mode that the increment rate of blade angle ξ reduces gradually, be very big blade angle ξ 2max at very big radial location R2max place, blade angle ξ reduces from very big radial location R2max gradually to outer periphery 12d, and the blade angle ξ t of the outer periphery 12d of second area AR2 is less than very big blade angle ξ 2max (ξ t< ξ 2max).In other words, the second blade angle distribution D ξ 2 of second area AR2 has the distribution of following quadratic function: in second area AR2, blade angle ξ is that greatly radial location R2max reduces to outer periphery 12d greatly from blade angle ξ.In addition, second area AR2 become the maximum value that great blade angle ξ 2max also becomes the blade angle ξ of whole rotation blade 12.Second blade angle distribution D ξ 2 is such as, blade angle ξ is increased to the very big blade angle ξ 2max of very big radial location R2max from the blade angle ξ d=64.46 ° of boundary position Rd, blade angle ξ reduces from very big radial location R2max to outer periphery 12d, reaches the blade angle ξ t=63.5 ° of outer periphery 12d.In addition, on the boundary position Rd of first area AR1 and second area AR2, blade angle distribution has continuous print curve or the such distribution of straight line.
Like this, be arranged in the second area AR2 of outer circumferential side of rotation blade 12, there is the second blade angle distribution D ξ 2 that the blade angle ξ t of outer periphery 12d is less like this than the blade angle ξ 2max of very big radial location R2max, therefore blade angle can be set as that the flow be suitable for the horizontal intake produced at outer periphery 12d increases corresponding angle, and prevent the stripping of the flowing at outer periphery 12d place, therefore, it is possible to realize the reduction of noise that caused by turbulent flow and the high efficiency of fan efficiency.
Below, while comparing with comparative example, impeller 10 is described.In addition, as mode of execution 1 shown below, the rotation blade 12 with above-mentioned blade angle distribution (with reference to Fig. 5) is used.On the other hand, Fig. 8 is the schematic diagram of an example of the rotation blade 112 represented as comparative example, and the rotation blade 112 of comparative example is described with reference to Fig. 8.In the same manner as the rotation blade 12 of Fig. 2 and Fig. 3, the rotation blade 112 of comparative example also has the three-dimensional shape of regulation, and has: leading edge 112a, and it is positioned at the forward side of sense of rotation RR; Trailing edge 112b, it is positioned at the opposite direction side of sense of rotation RR; Inner circumference edge 112c, it is connected to hub portion 111; And outer periphery 112d, it is positioned at housing 2 side.Rotation blade 112 has the tilting distribution increased to such, that blade angle ξ is from the position of inner circumference edge 112c to outer periphery 112d position linarity (linear function) as shown in dash-dot lines in fig. 5.Specifically, rotation blade 112 is set as diameter Rt=260 (mm), the blade angle ξ t=67.5 ° of outer periphery 112d side, the blade angle ξ b=58 ° of side, hub portion 111, the blade angle ξ between outer periphery 112d and hub portion 111 have and distribute with the blade diameter blade angle that linarity increases accordingly.
At this, in Figure 5, mode of execution 1 is consistent with the blade angle ξ b of the position Rb at inner circumference edge 12c of comparative example.And go to outer peripheral side along with from inner circumference edge 12c, the blade angle ξ of the rotation blade 12 of mode of execution 1 increases with the increment rate that the increment rate of the blade angle of the rotation blade 112 than comparative example is large.Fig. 6 represents the rotation blade 12 of mode of execution 1 and the blade profile unfolded drawing of the rotation blade 112 of comparative example at the arbitrary radial location R1 place of first area AR1.As shown in Figure 6, in the AR1 of first area, compared with the blade angle ξ c1 of the rotation blade 112 of comparative example, the blade angle ξ 1 large (ξ 1> ξ c1) of the rotation blade 12 of mode of execution 1 is little relative to sense of rotation RR slope.
In the second area AR2 of Fig. 5, the increment rate of the blade angle ξ of the rotation blade 12 of mode of execution 1 reduces gradually, move closer to the blade angle ξ of the rotation blade 112 of comparative example, in the position than very big radial location R2max outer circumferential side side (outer periphery 12d), the blade angle ξ of the rotation blade 12 of mode of execution 1 becomes less than the blade angle ξ of the rotation blade 112 of comparative example.Fig. 7 represents the rotation blade 12 of mode of execution 1 and the blade profile unfolded drawing of the rotation blade 112 of comparative example at the radial location R2 place of the very big radial location R2max outer circumferential side side than second area AR2.As shown in Figure 7, at the radial location R2 than very big radial location R2max outer circumferential side side, compared with the blade angle ξ c2 of the rotation blade 112 of comparative example, the blade angle ξ 2 of the rotation blade 12 of mode of execution 1 is little (ξ 2< ξ c2), large relative to sense of rotation RR slope.
Fig. 9 and Figure 10 is the schematic diagram of the relation represented between blade cylinder sectional view near outer periphery 12d and velocity triangle.In addition, Fig. 9 represents the situation not considering laterally to suck, Figure 10 represents the situation considering and laterally suck, in the drawings, the velocity vector on running shaft direction (the arrow A direction with reference to Fig. 3) is represented with V, V10, represent the horizontal vector corresponding with the rotational speed of rotation blade 12 with U, represent synthesis flow velocity vector V, V10 and horizontal vector U and the relative velocity vector that obtains with W, W10.As shown in Figure 8, in the rotation blade 112 of comparative example, based on when supposing that air-flow is along the velocity vector V not considering when blade factor mobility as the line feature in the same radius of blade face laterally to suck and horizontal vector U, has carried out two-dimentional optimal design.Thus, under the flow of design, represent that the direction of the relative velocity vector W of the flowing flowed into rotation blade 112 is roughly mated with leading edge 112a.
But in fact, owing to existing from the air stream of outer periphery 112d side, so the air-flow sucked from the transverse direction of blade side adds the air-flow flowed into from leading edge 112a, thus flow change is many, becomes velocity vector V10 (>V).Therefore, as shown in Figure 10, the direction of relative velocity vector W10 is not mated with the angle of the leading edge 112a side of rotation blade 112.
Figure 11 is the schematic diagram of the state of air stream in the unmatched situation of angle representing the direction of relative velocity vector W10 and the leading edge 112a of rotation blade 112.As shown in figure 11, except before rotation blade 112 (the arrow A direction of Fig. 3) inflow except, exist in leading edge 112a side and suck from the transverse direction of horn mouth 4 side.Therefore, air occurs in the leading edge 112a side of blade suction surface 112f and peels off AC1 etc., the flowing of air-flow is not mated with the shape of rotation blade 112, becomes disorder and to trailing edge 112b sidesway stream, the scale of vortex wake AC2 also becomes large.The loss of these flowings becomes large, and therefore air-supply-noise characteristic is deteriorated.
The schematic diagram of the state of air stream when Figure 12 is the angle automatching representing the direction of relative velocity vector W10 and the leading edge 12a of rotation blade 12.Rotation blade 12 has blade angle distribution (with reference to Fig. 6) of regulation, therefore has the distribution that blade angle ξ near the large outer periphery 12d of the impact that laterally sucks is corresponding with flow increasing amount.Therefore, even if when there is laterally suction, the direction of relative velocity vector W10 also becomes the direction of mating with the angle of leading edge 12a.Thus, air-flow flows along blade shape, and stripping diminishes, and the loss of therefore flowing diminishes, and the deterioration of air-supply-noise characteristic also diminishes.
Figure 13 is the chart compared ratio noise characteristic and the fan efficiency characteristic of the rotation blade 112 that the rotation blade 12 of the blade angle distribution D ξ with mode of execution 1 distributes with the blade angle with comparative example.In addition, setting air quantity as Q [m
3/ min], set static pressure as P
s[Pa], set noise characteristic (A sound level) as SPL
atime [dB], than noise K
s[dB] can represent with following formula (1).
[formula 1]
K
S＝SPL
A－10Log(Q·P
s 2.5)···(1)
As shown in figure 13, compared with there is the blade of linear blade angle characteristic, than noise K
sin the air quantity band of wider scope, achieve low noise, the low noise of maximum-5 (dB) can be realized.
Figure 14 is the chart compared the fan efficiency characteristic of the rotation blade 112 that the rotation blade 12 of the blade angle distribution D ξ with mode of execution 1 distributes with the blade angle with comparative example.In addition, setting axle power as P
wtime [W], fan efficiency E
s[%] can represent with following formula (2).
[formula 2]
E
S＝(P
s·Q)/(60·P
w)···(2)
As shown in figure 14, for fan efficiency, the high efficiency of maximum+1 (percent point) also can be realized.
Figure 15 be to represent in the rotation blade 12 of the blade angle distribution D ξ with Fig. 4, when making the blade angle ξ t of outer periphery 12d be changed to 57.5 ~ 66.5 ° blade angle ξ t with minimum than noise K
sbetween the chart of relation.In fig .15, in the scope of 57.5 °≤ξ t≤66.5 °, all low noise can be realized.Figure 16 be to represent in the rotation blade 12 of the blade angle distribution D ξ with Fig. 4, the chart of blade angle when making the blade angle of outer periphery 12d change in the scope of 57.5 °≤ξ t≤66.5 ° and the relation between the peak of fan efficiency.As shown in figure 16, in the blade with blade angle of the present invention distribution, in the scope of this research, all high efficiency can be realized.It is further preferred that as learnt from the chart of Figure 15 and Figure 16, when 60 °≤ξ t≤63 °, the generation of noise can be suppressed to inferior limit and axial flow blower 1 efficiency is operated well.In addition, the aspect ratio of rotation blade 12 can be made to have the blade of the blade angle distribution of comparative example at the outer circumferential side of rotation blade 12 low, and the joint etc. between motor M becomes easy.
Figure 17 is the chart using the expansion sectional view by different blade angle ξ t of outer periphery 12d to carry out the comparison of height.In addition, the comparison of the height when aligned in position has been carried out in the position (such as leading edge 12a side) specified is represented in fig. 17.Blade angle ξ t is less, more can produce the difference of height between leading edge 12a side and trailing edge 12b side, thus makes the height of rotation blade 12 higher, and in mode of execution 1, rotation blade 12 is higher than the rotation blade 112 of comparative example.The height of rotation blade 12 is subject to the restriction of the relation in the gap between the height restriction of product and motor bracket etc. etc.Due to different and different along with the relation between each product form from other parts according to product of restriction of this height, therefore in general cannot determine.On the other hand, as long as blade angle ξ t is in the scope of 57.5 ~ 66.5 °, just can fall in the scope of above-mentioned height restriction, and, above-mentioned low noise can be provided and high efficiency rotation blade 12.Particularly, if 60 °≤ξ t≤63 °, the generation of noise can be suppressed to inferior limit and axial flow blower 1 efficiency is operated well.
Mode of execution 2
Figure 18 is the chart of the mode of execution 2 of the blade angle distribution of the rotation blade representing impeller of the present invention.In addition, there is the impeller of the blade angle distribution of Figure 18 also for having the structure in hub portion 11 as shown in FIG. 1 to 3 and multiple rotation blade 12.In addition, blade angle distribution and the blade angle of Fig. 5 of Figure 18 different point that distributes is that first blade angle of first area AR1 distributes D ξ 11.In addition, in figure 18, in the same manner as Fig. 5, boundary position Rd is set in the position of Rd=0.7 × (Rt-Rb), is divided into the first area AR1 with the first blade angle distribution D ξ 11 and second area AR2 with the second blade angle distribution D ξ 2 by boundary position Rd.In addition, the blade angle ξ t of outer periphery 12d is set in the scope of 57.5 °≤ξ t≤66.5 °.
In the first area AR1 of Figure 18, blade angle ξ reduces gradually from the blade angle ξ 2b of the radial location Rb of inner circumference edge 12c, being minimum blade angle ξ 1min at minimum radial location R1min place, increasing gradually along with going to the blade angle ξ d of boundary position Rd from minimum radial location R1min.In addition, the blade angle ξ 2b at radial location Rb place becomes the maximum value of the blade angle ξ of whole rotation blade 12.Specifically, the first blade angle distribution D ξ 1, such as, be set as the blade angle ξ 2b=72 ° of the radial location Rb of inner circumference edge 12c, be set as the blade angle ξ t=63.5 ° of the radial location Rt of outer periphery 12d.
Figure 19 is the cross section unfolded drawing of rotation blade at the arbitrary radial location R1 of first area AR1 of the blade angle distribution of the mode of execution 2 with Figure 18.As shown in figure 19, at radial location R1, compared with the blade distributed with the blade angle had in the past, the slope of rotation blade 12 is little.
Figure 20 is to the rotation blade 12 of the blade angle distribution D ξ with mode of execution 2 and has the chart that the ratio noise characteristic of rotation blade 112 of blade angle distribution of comparative example and fan efficiency characteristic compare, and Figure 21 is the chart compared the rotation blade 12 of the blade angle distribution D ξ with mode of execution 2 and the fan efficiency characteristic of rotation blade 112 of blade angle distribution with comparative example.In Figure 20 and Figure 21, there is the part of properties deteriorate in Wind Volume side, but on the percent point in middle air quantity region using region as reality, low noise, high efficiency can be realized further, compared with the blade distributed with the blade angle had in the past, the low noise of maximum-6 (dB) can be realized.For fan efficiency, the high efficiency of maximum+2.4 (percent points) also can be realized.
Like this, when blade angle distribution D ξ 1 with first area AR1 as shown in figure 18, also in the same manner as mode of execution 1, due to the second blade angle distribution D ξ 2 that the blade angle ξ t with outer periphery 12d is less like this than the blade angle ξ t of very big radial location R2max, therefore blade angle can be set as that the flow be suitable for the horizontal intake produced at outer periphery 12d increases corresponding angle, the stripping of the flowing at outer periphery 12d place can be prevented, therefore, it is possible to the reduction of noise realized because turbulent flow causes and the high efficiency of fan efficiency.In addition, at the outer circumferential side of rotation blade 12, the blade that the blade angle that the aspect ratio of rotation blade 12 can be made to have comparative example distributes is low, and the joint etc. between motor M becomes easy.Further, for first area AR1, by being the first blade angle distribution D ξ 11 shown in Figure 18, can be continuous with the blade angle ξ of second area AR2 smoothly, also can realize slimming.
Embodiments of the present invention are not limited to above-mentioned mode of execution.Such as in above-mentioned mode of execution 1,2, exemplified with first area AR1, there is the first blade angle distribution D ξ 1 of regulation, the situation of D ξ 11, as long as but the second blade angle distribution D ξ 2 of second area AR2 to have at second area AR2 intra vane established angle ξ from blade angle ξ be that greatly radial location R2max reduces such distribution to outer periphery 12d greatly, then can adopt arbitrary first blade angle distribution.
In addition, exemplified with the situation of the blade angle ξ b=58 of inner circumference edge 12c ° in above-mentioned mode of execution 1, exemplified with the situation of the blade angle ξ 20b=72 of inner circumference edge 12c ° in mode of execution 2, preferably blade angle ξ b, the ξ 20b of inner circumference edge 12c are in the scope of 58 ° ~ 72 °.This is because, in rotation blade 12, the scope contributing to most wind pushing performance is the region of the outer circumferential side of the position of 0.7 times ~ 1.0 times being positioned at radius, and the contribution degree of inner circumference edge 12c is less than outer circumferential side, but according to the relation between inner circumferential side and hub portion 11, the little this point of rotation blade 12 slope is constructively favourable.
Description of reference numerals
1: axial flow blower, 2: housing, 3: opening, 4: horn mouth, 10: impeller, 11, 111: hub portion, 12, 112: rotation blade, 12a, 112a: leading edge, 12b, 112b: trailing edge, 12c, 112c: inner circumference edge, 12d, 112d: outer periphery, 112f: blade suction surface, AC1: air is peeled off, AC2: vortex wake, AR1: first area, AR2: second area, CL: running shaft, D ξ, D ξ 1, D ξ 11: the first blade angle distributes, and D ξ 2: the first blade angle distributes, HL: vertical line, M: motor, R1: the radial location of first area, R2: the radial location of second area, RR: sense of rotation, Rb: the radial location of inner circumference edge, Rd: boundary position (radial location of regulation), Rt: the radial location of outer periphery, SL: the blade string of a musical instrument, U: horizontal vector, V, V10: velocity vector, W, W10: relative velocity vector, ξ: blade angle, ξ b, ξ 20b: the blade angle of inner circumference edge, ξ d: the blade angle of boundary position, ξ t: the blade angle of outer periphery.
Claims (12)
1. an impeller, is characterized in that, possesses:
Hub portion, it has columned profile; And
Multiple rotation blade, it is radially installed on described hub portion,
Described rotation blade has:
First area, it is from the inner circumference edge being connected to described hub portion to radial location of regulation and have the first blade angle distribution; And
Second area, it has the second different blade angle that to distribute with described first blade angle from from the radial location of the regulation that described first area adjoins distribute to outer periphery,
Described second blade angle distribution has blade angle from described second area intra vane established angle being the distribution that great greatly radial location reduces to described outer periphery.
2. impeller according to claim 1, is characterized in that,
The described second blade angle distribution increment rate had from the radial location of described regulation to described very big radial location, blade angle reduces and blade angle becomes large distribution.
3. impeller according to claim 2, is characterized in that,
The blades installation angle distribution that described second blade angle distribution changes with having curve-like in quadratic function.
4. the impeller according to any one of claims 1 to 3, is characterized in that,
The blade angle of described outer periphery is in the scope of 57.5 ° ~ 66.5 °.
5. the impeller according to any one of Claims 1 to 4, is characterized in that,
Described first blade angle distribution has the distribution that blade angle increases from described hub portion to periphery.
6. impeller according to claim 5, is characterized in that,
Described first blade angle distributes the distribution increased with having blade angle linarity.
7. the impeller according to any one of claim 1 ~ 6, is characterized in that,
Described first blade angle distributes the minimum minimum blade established angle had in described rotation blade.
8. the impeller according to any one of Claims 1 to 4, is characterized in that,
Described first blade angle distribution has following distribution: from described inner circumference edge to the minimum radial location described first area, the mode that blade angle reduces with the reduction rate of blade angle diminishes, from the minimum radial location described first area to the radial location of described regulation, blade angle becomes large gradually.
9. impeller according to claim 8, is characterized in that,
The blade angle of the described inner circumference edge of described rotation blade is maximum in the blade angle of described rotation blade.
10. impeller according to claim 8 or claim 9, is characterized in that,
The blades installation angle distribution that described first blade angle distribution changes with having curve-like in quadratic function.
11. impellers according to any one of claim 1 ~ 10, it is characterized in that, the blade angle of described inner circumference edge is in the scope of 58 ° ~ 72 °.
12. 1 kinds of blowers, is characterized in that possessing:
Impeller according to any one of claim 1 ~ 11;
Motor, it drives the described hub portion of described impeller to make it rotate; And
Housing, it receives described impeller in described vane rotary mode freely, and passes through for the air-flow produced by described impeller.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2013/057135 WO2014141417A1 (en) | 2013-03-14 | 2013-03-14 | Impeller and axial blower in which same is used |
| JPPCT/JP2013/057135 | 2013-03-14 | ||
| PCT/JP2014/056617 WO2014142225A1 (en) | 2013-03-14 | 2014-03-13 | Impeller and axial blower in which same is used |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105026768A true CN105026768A (en) | 2015-11-04 |
| CN105026768B CN105026768B (en) | 2017-03-15 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201480012547.1A Active CN105026768B (en) | 2013-03-14 | 2014-03-13 | Impeller and the axial flow blower of the impeller is used |
Country Status (6)
| Country | Link |
|---|---|
| JP (1) | JP6005256B2 (en) |
| KR (1) | KR101788431B1 (en) |
| CN (1) | CN105026768B (en) |
| MY (1) | MY180269A (en) |
| TW (1) | TWI529308B (en) |
| WO (2) | WO2014141417A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111133201A (en) * | 2017-10-03 | 2020-05-08 | 三菱电机株式会社 | Propeller fan and axial flow blower |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5905985B1 (en) * | 2015-08-18 | 2016-04-20 | 山洋電気株式会社 | Axial flow fan and serial type axial flow fan |
| WO2017077564A1 (en) * | 2015-11-02 | 2017-05-11 | 三菱電機株式会社 | Axial fan and air-conditioning device having said axial fan |
| CN110513329A (en) * | 2019-09-30 | 2019-11-29 | 广东美的制冷设备有限公司 | Axial-flow windwheel and air conditioner with it |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5783696A (en) * | 1980-11-14 | 1982-05-25 | Nippon Denso Co Ltd | Fan |
| JPH08284887A (en) * | 1995-04-11 | 1996-10-29 | Toyo Radiator Co Ltd | Fan |
| JPH1144432A (en) * | 1997-07-24 | 1999-02-16 | Hitachi Ltd | Air conditioner |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2590514B2 (en) * | 1987-03-13 | 1997-03-12 | 日本電装株式会社 | Blower fan |
| US6899526B2 (en) * | 2003-08-05 | 2005-05-31 | General Electric Company | Counterstagger compressor airfoil |
-
2013
- 2013-03-14 WO PCT/JP2013/057135 patent/WO2014141417A1/en active Application Filing
- 2013-06-13 TW TW102120854A patent/TWI529308B/en active
-
2014
- 2014-03-13 JP JP2015505544A patent/JP6005256B2/en active Active
- 2014-03-13 WO PCT/JP2014/056617 patent/WO2014142225A1/en active Application Filing
- 2014-03-13 CN CN201480012547.1A patent/CN105026768B/en active Active
- 2014-03-13 MY MYPI2015703055A patent/MY180269A/en unknown
- 2014-03-13 KR KR1020157027510A patent/KR101788431B1/en active IP Right Grant
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5783696A (en) * | 1980-11-14 | 1982-05-25 | Nippon Denso Co Ltd | Fan |
| JPH08284887A (en) * | 1995-04-11 | 1996-10-29 | Toyo Radiator Co Ltd | Fan |
| JPH1144432A (en) * | 1997-07-24 | 1999-02-16 | Hitachi Ltd | Air conditioner |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111133201A (en) * | 2017-10-03 | 2020-05-08 | 三菱电机株式会社 | Propeller fan and axial flow blower |
| CN111133201B (en) * | 2017-10-03 | 2021-10-08 | 三菱电机株式会社 | Propeller fan and axial flow blower |
Also Published As
| Publication number | Publication date |
|---|---|
| MY180269A (en) | 2020-11-26 |
| JPWO2014142225A1 (en) | 2017-02-16 |
| KR20150125006A (en) | 2015-11-06 |
| JP6005256B2 (en) | 2016-10-12 |
| KR101788431B1 (en) | 2017-10-19 |
| CN105026768B (en) | 2017-03-15 |
| TWI529308B (en) | 2016-04-11 |
| WO2014142225A1 (en) | 2014-09-18 |
| WO2014141417A1 (en) | 2014-09-18 |
| TW201435215A (en) | 2014-09-16 |
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