CN204200675U - Centrifugal blower fan blade wheel, centrifugal blower and sweeper - Google Patents
Centrifugal blower fan blade wheel, centrifugal blower and sweeper Download PDFInfo
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- CN204200675U CN204200675U CN201420598952.3U CN201420598952U CN204200675U CN 204200675 U CN204200675 U CN 204200675U CN 201420598952 U CN201420598952 U CN 201420598952U CN 204200675 U CN204200675 U CN 204200675U
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Abstract
The utility model discloses a kind of sweeper, centrifugal blower and centrifugal blower fan blade wheel thereof, wherein said centrifugal blower fan blade wheel comprises the wheel cap (4) of relative spacing and is formed with the wheel disc (5) of intake grill (9), be fixed with between described wheel cap (4) and wheel disc (5) around intake grill (9) spaced apart more blades (6), thus every two adjacent blades (6), wheel cap (4) and wheel disc (5) surround the impeller air draft runner (13) be communicated with intake grill (9) jointly, impeller air draft runner (13) described in each is inner (11) outer end (12) respectively, wherein, the cross-sectional flow area that each impeller air draft runner (13) intercepts along the circumference of centrifugal blower fan blade wheel increases from inner (11) to outer end (12), thus each impeller air draft runner (13) is formed as expanding runner.Centrifugal blower fan blade wheel of the present utility model can reduce the impact strength of air-flow under the state being applied to centrifugal blower, thus reduces impact energy loss.
Description
Technical field
The utility model relates to a kind of draught fan impeller, particularly, relates to a kind of centrifugal blower fan blade wheel.In addition, the utility model also relates to a kind of centrifugal blower and sweeper.
Background technique
Centrifugal blower utilizes the motivational drive centrifugal blower fan blade wheel of input to rotate, thus rely on the mechanical energy of input, improves gas pressure and to supply gas side by side the machinery of body.Centrifugal blower is widely used in the ventilation of mine, tunnel, cooling tower, vehicle, boats and ships and building, dust discharge and cooling.Typically, such as sweeper adopts centrifugal blower to carry out dust suction, to reach cleaning object.
Fig. 1 shows a kind of typical centrifugal blower fan blade wheel in prior art, and this centrifugal blower fan blade wheel is rotatably installed in the spiral case 1a of centrifugal blower.As shown in Figure 1, described centrifugal blower fan blade wheel comprises wheel cap 4a and the wheel disc 5a of relative spacing layout, wherein the center region of wheel cap 4a is formed with intake grill, the blade 6a arranged around described intake grill uniform intervals is fixed with between wheel cap 4a and wheel disc 5a, thus form air intake district 7a in the center region of centrifugal blower fan blade wheel, and form wind outlet area 8a in the circumferential outer edge of centrifugal blower fan blade wheel.Under the state in the spiral case 1a being installed to centrifugal blower, described centrifugal blower fan blade wheel is rotatably supported on the side sidewall of spiral case 1a by the rotating shaft 2a being fixed on wheel disc 5a central part, the center region of the relative opposite side sidewall of spiral case 1a is formed with slip ring mount inlet, at this slip ring mount inlet, air intake slip ring 3a is installed, the bore of the entrance point of air intake slip ring 3a is generally greater than the bore of outlet end, wherein the entrance point of air intake slip ring 3a generally protrudes from the outside of spiral case 1a, outlet end extend in spiral case 1a, generally extend in the intake grill of wheel cap 4a, thus the air intake district 7a of centrifugal blower fan blade wheel can be entered into swimmingly by the gas of air intake slip ring 3a.
But, see Fig. 1, in existing centrifugal blower fan blade wheel (typically such as scavenging vehicle centrifugal blower fan blade wheel), wheel cap 4a and wheel disc 5a complements each other to form the runner of shrink form, runner from air intake district 7a to wind outlet area 8a is large in the runner cross-sectional flow area of air intake district 7a, and radially directional flow passage cross-sectional flow area is constantly shunk.Due to the contraction of runner cross-sectional flow area, the airspeed at 8a place, wind outlet area is increased, adds the impact dynamics of air-out air-flow and spiral case 1a internal face, increase impact loss, thus reduce the efficiency of centrifugal blower.
Because the above-mentioned shortcoming of prior art, need to provide a kind of centrifugal blower fan blade wheel that can be novel.
Model utility content
Technical problem to be solved in the utility model is to provide a kind of centrifugal blower fan blade wheel, and this centrifugal blower fan blade wheel can reduce the impact strength of air-flow under the state being applied to centrifugal blower, thus reduces impact energy loss.
On the basis of above-mentioned technical problem, the technical problem that the utility model also will solve is to provide a kind of sweeper and centrifugal blower thereof, and this centrifugal blower can reduce gas shock intensity in the course of the work, thus reduces impact energy loss.
In order to solve the problems of the technologies described above, the utility model provides a kind of centrifugal blower fan blade wheel, it comprises wheel cap and wheel disc, the side card of this wheel disc and a side surface relative spacing of described wheel cap are arranged, the middle section of this wheel cap is formed with the intake grill of this wheel cap thickness through, be fixed with around the spaced apart more blades of described intake grill between described wheel cap and wheel disc, thus every two adjacent described blades, wheel cap and wheel disc surround the impeller air draft runner be communicated with described intake grill jointly, impeller air draft runner described in each has the inner and outer end of being positioned at described centrifugal blower fan blade wheel middle section and peripheral edge regions respectively, wherein, impeller air draft runner described in each increases to described outer end along the sectional area of the passage section that the circumference of described centrifugal blower fan blade wheel intercepts from described the inner, thus impeller air draft runner is formed as expanding runner described in each.
Preferably, described in each, the sectional area of the passage section of impeller air draft runner increases from described the inner continuously to described outer end.
Concrete selectively it is the circumferentially same of R5 that the inner of blade described in each is in radius, and the outer end of blade described in each is in radius is the circumferentially same of R6, wherein 0.261≤R5/R6≤0.522; And the radius of the described intake grill of described centrifugal blower fan blade wheel is L1, the radius of described centrifugal blower fan blade wheel is L2, wherein 2.946≤L2/L1≤3.38.
Preferably, the inner port of impeller air draft runner described in each and outer end port are respectively h and H, wherein 0.865≤h/H≤1.26 along the width of the central rotation axis of described centrifugal blower fan blade wheel.
More preferably, a described side surface relative with described wheel disc of described wheel cap comprises and rotates by the central rotation axis of centrifugal blower fan blade wheel described in the first type wound the wheel cap surface of revolution formed, and this first molded line at least comprises arc; And the described side card relative with described wheel cap of described wheel disc comprises and rotate by the central rotation axis of centrifugal blower fan blade wheel described in Second-Type wire-wound the wheel disc surface of revolution formed, this second molded line at least comprises arc.
Further, described first molded line comprises the first circular arc line that radius is R1 and radius and is R2 and relative to described first circular arc line more near the second circular arc line of described central rotation axis, one end of described second circular arc line and described central rotation axis interval, the other end is connected with one end of described first circular arc line with seamlessly transitting, wherein 0.985≤R1/R2≤1.4; And the three-arc line that described second molded line comprises straightway, radius is R3 and radius are R4 and relative to described three-arc line more away from the 4th circular arc line of described central rotation axis, described straightway is perpendicular to described central rotation axis, one end of this straightway is connected to described central rotation axis, the other end of this straightway is connected to one end of described three-arc line, the other end of this three-arc line is connected with one end of described 4th circular arc line with seamlessly transitting, wherein 0.267≤R3/R4≤0.52.
Further preferably, the radius R 2 of described second circular arc line and the radius R 3 of described three-arc line also meet: 1.5≤R2/R3≤2.4.
Preferably, described first molded line and the described second molded line part being at least positioned at described centrifugal blower fan blade wheel outer edge region is separately formed as described arc, under described centrifugal blower fan blade wheel is placed as and makes state that described central rotation axis is vertical with vertical direction, the tangent line at outer end points place and the angle of described vertical direction of described first molded line are α, the tangent line at outer end points place and the angle of described vertical direction of described second molded line are β, wherein meet 5 °≤α=β≤12 °.
Especially preferably, in the Normal direction of any point of the described arc of described first molded line, the width of described impeller air draft runner is bi, and the distance between this point and described central rotation axis is Li, meet as 35<Li<82.527, bi=0.153Li+27.319; As 82.527≤Li<110, bi=0.011Li+39.079, wherein the dimensional units of bi with Li is identical.
On the basis of the technique scheme of centrifugal blower fan blade wheel of the present utility model, the utility model also provides a kind of centrifugal blower, comprise spiral case and be rotatably installed in the centrifugal blower fan blade wheel in this spiral case, wherein, described centrifugal blower fan blade wheel is above-mentioned arbitrary centrifugal blower fan blade wheel.
In addition, the utility model also provides a kind of sweeper, and wherein, the dust collecting system of this sweeper comprises above-mentioned centrifugal blower.
Pass through technique scheme, the impeller air draft runner formed between the wheel cap of the utility model centrifugal blower fan blade wheel and wheel disc is formed as the expanding runner that cross-sectional flow area is expanded from the inner to outer end, when this centrifugal blower fan blade wheel is installed on centrifugal blower, this makes in the impeller air draft runner of centrifugal blower fan blade wheel of the present utility model, when air-flow flow to outer end along impeller air draft runner from the inner, due to the increase of the cross-sectional flow area of described impeller air draft runner, the flow velocity of air-flow can suitably reduce, this effectively reduces the impact strength of impeller outlet fluid and spiral case, reduce impact loss, significantly improve the efficiency of centrifugal blower.
In preferred implementation of the present utility model, the utility model is by optimizing the parameters of structural dimension of centrifugal blower fan blade wheel, especially the profile surface molded line of wheel cap and wheel disc (i.e. the first molded line and the second molded line) is made to comprise arc, this make it possible to the air-flow that makes to enter described impeller air draft runner evenly, air-flow is little along impeller air draft runner adverse pressure gradient outwardly, suffered flow resistance is little, not easily there is boundary layer separation and produce swirl flow, in impeller air draft runner, velocity distribution is even, this can reduce fan noise effectively, improve fan efficiency.
Especially, in the further optimal way of the utility model, the utility model provides about impeller discharge air flow Dow process is to the optimizing structure design of cross-sectional width, it has comprehensively taken into account the diffusion degree of impeller air draft runner of the present utility model, the design of the cross-sectional flow area of impeller air draft runner is made to ensure that blower fan makes impeller channel diffusion best results when obtaining enough negative pressure, reduce air current flow drag losses, thus obtain good aeroperformance.
Other features and advantages of the utility model are described in detail in embodiment part subsequently.
Accompanying drawing explanation
Following accompanying drawing is used to provide further understanding of the present utility model; and form a part for specification; itself and following embodiment one are used from explanation the utility model, but protection domain of the present utility model is not limited to following the drawings and the specific embodiments.In the accompanying drawings:
Fig. 1 is the structural representation of a kind of typical centrifugal blower fan blade wheel in prior art, wherein said centrifugal blower fan blade wheel is arranged in the spiral case of centrifugal blower, and in order to the structure of the described centrifugal blower fan blade wheel of clear display, spiral case is adopted and cuts display format open and broken section has been carried out to centrifugal blower fan blade wheel.
Fig. 2 is the agent structure schematic perspective view of the centrifugal blower of the utility model embodiment, is provided with centrifugal blower fan blade wheel of the present utility model in the spiral case of wherein this centrifugal blower.
Fig. 3 is the cross-sectional schematic of the centrifugal blower of the radial direction cutting along centrifugal blower fan blade wheel shown in Fig. 2, wherein because the thickness of shell of spiral case and air intake slip ring is less and eliminate its hatching.
Fig. 4 is the sectional structure schematic diagram of the centrifugal blower fan blade wheel of the utility model embodiment;
Fig. 5 is the wheel cap of the centrifugal blower fan blade wheel shown in Fig. 4 and the layout cross-sectional schematic of wheel disc, wherein eliminates the blade between wheel cap and wheel disc;
Fig. 6 is the layout schematic diagram of the blade of the centrifugal blower fan blade wheel shown in Fig. 4, wherein in order to the setting type of clear display blade eliminates wheel cap.
The utility model description of reference numerals:
1 spiral case; 2 rotating shafts;
3 air intake slip rings; 4 wheel caps;
5 wheel discs; 6 blades;
7 air intake districts; 8 wind outlet areas;
9 intake grills; 10 wheel shaft joints;
11 is inner; 12 outer ends;
13 impeller air draft runners;
A airintake direction; B outgassing direction;
R radial direction; L central rotation axis.
Embodiment
Below in conjunction with accompanying drawing, embodiment of the present utility model is described in detail; should be understood that; embodiment described herein is only for instruction and explanation of the utility model, and protection domain of the present utility model is not limited to following embodiment.
First it should be noted that, in the description of technical solutions of the utility model, in order to clearly limit the implication of the correlation technique feature of the utility model centrifugal blower fan blade wheel, some involved nouns of locality, such as " the inner ", " outer end ", " middle section ", " center region ", " peripheral edge regions " and " outer edge region " etc., all the restrictions carried out according to the art-recognized meanings that the technician in centrifugal blower field is usually known, know ground for those skilled in the art, centrifugal blower fan blade wheel belongs to the device carrying out forcing air draft by rotating generation centrifugal force on the whole, therefore it has central rotation axis, with regard to each technical characteristics (such as each component or impeller air draft runner etc.) of centrifugal blower fan blade wheel, so-called " the inner " refers in radial directions relatively near one end of central rotation axis, " outer end " refers to relatively away from the other end of central rotation axis, the region that " middle section " and " center region " i.e. center steering axis passes, " peripheral edge regions " and " outer edge region " refer to the relative part away from central rotation axis of centrifugal blower fan blade wheel.
See Fig. 2 to Fig. 6, centrifugal blower of the present utility model adopts a kind of centrifugal blower fan blade wheel of uniqueness, and this centrifugal blower fan blade wheel has the impeller air draft runner 13 of expanding.Particularly, the centrifugal blower fan blade wheel of the utility model basic embodiment comprises wheel cap 4 and the wheel disc 5 of relative spacing layout, the side card of this wheel disc 5 and a side surface relative spacing of wheel cap 4 are arranged, the middle section of wheel cap 4 is formed with the intake grill 9 of this wheel cap 4 thickness through, be fixed with around the spaced apart blade 6 of intake grill 9 between wheel cap 4 and wheel disc 5, thus form air intake district 7 in the center region of centrifugal blower fan blade wheel, and form wind outlet area 8 in the peripheral edge regions of centrifugal blower fan blade wheel.Correspondingly, see Fig. 6, every two adjacent described blades 6, wheel cap 4 and wheel disc 5 surround the impeller air draft runner 13 be communicated with intake grill 9 jointly, each impeller air draft runner 13 has the inner 11 and outer end 12 of being positioned at centrifugal blower fan blade wheel middle section and peripheral edge regions respectively, wherein, as shown in Figure 5 and Figure 6, the sectional area of the passage section that each impeller air draft runner 13 intercepts along the circumference of centrifugal blower fan blade wheel increases from inner 11 to described outer end 12 and (preferably can increase continuously, such as linear or along level and smooth curve corresponding relation increase), thus each impeller air draft runner 13 is formed as expanding runner.
Although the art-recognized meanings of " circumferential cross-section " is know ground for routine techniques personnel, but still supplemental instruction is given to this herein, so-called " passage section that the circumference along centrifugal blower fan blade wheel intercepts " refers to the different concentric column outer circumferential face of each radius that the central rotation axis L around centrifugal blower fan blade wheel is rotarily formed and the coincidence face that formed crossing with the diverse location of impeller air draft runner 13, such as in figure 6, different concentric circles is made around the center of circle in Fig. 6, the central rotation axis L of these concentric circles along centrifugal blower is moved thus cutting impeller air draft runner 13, thus form the passage section that circumferentially intercept of impeller air draft runner 13 on the diverse location of its bearing of trend.Also it should be noted that herein; any centrifugal blower fan blade wheel; regardless of the specific constructive form of its each impeller air draft runner 13; as long as the expanding runner that the sectional area that impeller air draft runner 13 is formed as the passage section intercepted along the circumference of centrifugal blower fan blade wheel increases from inner 11 to outer end 12, then all belong to protection domain of the present utility model.
In above-mentioned basic embodiment, because the impeller air draft runner 13 formed between the wheel cap 4 of the utility model centrifugal blower fan blade wheel and wheel disc 5 is formed as the expanding runner that cross-sectional flow area expands from inner 11 to outer end 12, when this centrifugal blower fan blade wheel is installed on centrifugal blower, when air-flow flow to outer end 12 along impeller air draft runner 13 from inner 11, due to the increase of the cross-sectional flow area of described impeller air draft runner 13, the flow velocity of air-flow can reduce, this can reduce the impact strength of impeller outlet fluid and spiral case 1 effectively, reduce impact loss, significantly improve the efficiency of centrifugal blower.
In the scope that the general technical of the utility model centrifugal blower fan blade wheel is conceived, as integrally-built a kind of preferred arrangement form of centrifugal blower fan blade wheel, as shown in Figure 6, the layout parameter can following optimization around intake grill 9 more blades 6 (being 12 blades 6 in such as Fig. 6) be fixed between wheel cap 4 and wheel disc 5 is arranged, particularly, it is the circumferentially same of R5 that the inner (i.e. entrance point) of each blade 6 can be in radius, and the outer end of each blade 6 (i.e. outlet end) can be in radius is the circumferentially same of R6, wherein 0.261≤R5/R6≤0.522.As shown in Figure 6, each blade 6 can be single arc-shaped structure, also can be multistage arcuate structure or arc and rectilinear composite structure, the radius of the entrance point (namely inner) of blade 6 is R5, the radius of outlet end (i.e. outer end) is R6, wherein meet 0.261≤R5/R6≤0.522, under this optimized arrangement structure, there is corresponding relation in the radius scale relation of circumference and the radial through-flow length of impeller air draft runner residing for the inner of blade and outer end, this is not only convenient to the layout of the blade of centrifugal blower fan blade wheel, and practice confirms the more excellent performance at this optimized arrangement structure form centrifugal blower fan blade wheel.In addition, as the typical structure of blade, each blade 6 can adopt single circular arc vane, and around above-mentioned intake grill 9, multiple blade shroud is arranged so that the arc surface of each blade 6 protrudes along identical sense of rotation.Like this, multiple blade 6 is arranged as a kind of structure being similar to helical fan on the whole, is so more conducive to carrying out supercharging to air-flow, makes the centrifugal function of increasing pressure of centrifugal blower fan blade wheel more excellent.Certainly, blade 6 also can be multistage arcuate structure, the protrusion direction of arc surface can be arranged as and protrude forward (namely forward direction is arranged) along the sense of rotation of impeller, also can be arranged as and protrude backward (i.e. backward layout) etc. against the sense of rotation of impeller.
Further, see Fig. 5, as a kind of global optimization structural type, the radius of the above-mentioned intake grill 9 of centrifugal blower fan blade wheel is L1, the radius (namely centrifugal blower fan blade wheel is as the radius of parts) of centrifugal blower fan blade wheel is L2, can meet 2.946≤L2/L1≤3.38.In this preferred arrangements structural type, because the radius L1 of intake grill 9 represents air intake ability, in the flow-path-length of centrifugal blower fan blade wheel after the roughly corresponding air-flow of radius L2 of centrifugal blower fan blade wheel enters, test confirms, when the radius L1 of the intake grill 9 of the centrifugal blower fan blade wheel of the present utility model and integral radius L2 of centrifugal blower fan blade wheel arranges according to aforementioned proportion relation, the air intake of centrifugal blower fan blade wheel, air draft and boost performance coupling are good, reliable operation, which improves the service behaviour of centrifugal blower fan blade wheel.
As mentioned above, within the scope of technical conceive of the present utility model, each impeller air draft runner 13 is formed as expanding runner, the opposite arrangement structure of wheel cap 4 and wheel disc 5 can carry out certain improvement for this reason, participate in Fig. 5, preferably, the inner port (i.e. air intake port) of each impeller air draft runner 13 and outer end port (i.e. air draft port) are respectively h and H, wherein 0.865≤h/H≤1.26 along the width of the central rotation axis L of centrifugal blower fan blade wheel.In this case, the interval between the side card of wheel disc 5 of arranging due to relative spacing and a side surface of wheel cap 4 is increases from the center region of centrifugal blower fan blade wheel to peripheral edge regions, therefore, it is possible to more easily formation expanding runner.Especially, this preferred implementation has comprehensively taken into account the diffusion degree of impeller air draft runner 13.If diffusion degree is too small, do not have diffusion effect, the exit flow of impeller air draft runner 13 and the impact loss of spiral case 1 still very large; If diffusion degree is excessive, the total head of centrifugal blower can decline, thus is difficult to provide enough negative pressure, affects the service behaviour of centrifugal blower.Actual experiment is verified, the above-mentioned optimal way of the utility model can ensure that centrifugal blower makes impeller air draft runner diffusion effect relatively good when obtaining enough negative pressure, centrifugal blower fluid resistance losses is relatively little, thus obtains good aeroperformance.
Within the scope of technical conceive of the present utility model, especially innovative, the utility model is theoretical and design the structural type of the inner surface (i.e. the side card of wheel disc 5 of relative spacing layout and a side surface of wheel cap 4) of wheel cap 4 and wheel disc 5 in conjunction with CFD emulation technology (i.e. computation fluid dynamics emulation technology) based on fluid mechanics Three-dimensional Flow.Briefly, see Fig. 4 and Fig. 5, a side surface relative with wheel disc 5 of wheel cap 4 comprises and rotates by the central rotation axis L of the first type wound centrifugal blower fan blade wheel the wheel cap surface of revolution formed, and this first molded line at least comprises arc.Meanwhile, the side card relative with wheel cap 4 of wheel disc 5 also comprises and rotates by the central rotation axis L of Second-Type wire-wound centrifugal blower fan blade wheel the wheel disc surface of revolution formed, and this second molded line also comprises arc.The wheel cap 4 of this cambered surface form and wheel disc 5 make the air-flow in working procedure near wheel cap 4 and wheel disc 5 can against wheel cap inner surface relatively goodly and wheel disc inner disc surface current moves, make the air-flow in impeller air draft runner 13 can transfer Radial Flow to by axial flow smoothly, make air-flow more smooth and easy, thus reduction flow losses, improve centrifugal blower pneumatic efficiency.
Such as, described in Fig. 4 and Fig. 5, the first molded line of wheel cap 4 and wheel disc 5 and the second molded line can be made up of two sections of tangent circular arcs respectively.Particularly, see Fig. 5, above-mentioned first molded line of wheel cap 4 can comprise the first circular arc line that radius is R1 and radius and be R2 and relative to the first circular arc line more near second circular arc line of central rotation axis L, one end of described second circular arc line and central rotation axis L interval (center region due to wheel cap 4 is formed with intake grill 9), the other end is connected with one end of the first circular arc line with seamlessly transitting (being specifically as follows tangent relation), wherein preferably 0.985≤R1/R2≤1.4.In addition, above-mentioned second molded line of wheel disc 5 comprises straightway (the wheel shaft joint 10 that the central part of wheel disc 5 is the plane shape for connection rotating shaft 2 shown in Fig. 3), radius is that the three-arc line of R3 and radius are R4 and relative to three-arc line more away from the 4th circular arc line of central rotation axis L, described straightway is perpendicular to central rotation axis L, one end of this straightway is connected to central rotation axis L, the other end of this straightway is connected to one end of three-arc line, the other end of this three-arc line is connected (being specifically as follows tangent relation) with one end of the 4th circular arc line with seamlessly transitting, wherein preferably 0.267≤R3/R4≤0.52.Under above-mentioned preferred size relationship, centrifugal blower fan blade wheel of the present utility model not only makes the interior surface smooth transition of impeller air draft runner 13, makes the air-flow in impeller channel can transfer Radial Flow to by axial flow smoothly, reduces flow losses; And the radius of arc relation of shaping molded line due to wheel cap 4 and wheel disc 5, the streamlined expansionary channel that inner surface is smooth can be formed, thus make that centrifugal blower reduces impact loss, the technique effect of raising the efficiency is optimized more.
Further, the centrifugal blower fan blade wheel of the utility model embodiment can also meet: 1.5≤R2/R3≤2.4, this makes to there is certain matching relationship between the shaping molded line of wheel cap 4 and wheel disc 5, it more effectively can ensure that impeller channel forms flaring pattern, airspeed is reduced gradually, thus more effectively weaken the impact of impeller outlet air-flow to spiral case wall, improve the efficiency of blower fan, also reduce the noise of blower fan simultaneously.
Certainly; need at this be annotatedly; wheel cap 4 of the present utility model and wheel disc 5 are also confined to above-mentioned specific constructive form; it is not limited to have the turning surface of shape shown in Fig. 5; and the shaping molded line of wheel cap 4 and wheel disc 5 is also not only limited as two sections of circular arcs to be formed; can also be the multi-section circular arc formation of more than two sections, these all belong within protection domain of the present utility model.
Comprise on the mode of execution basis of arcuate segment at above-mentioned first molded line and the second molded line, analyzed and fluid mechanics Three-dimensional Flow theoretical test by CFD analogue simulation, more preferably, as shown in Figure 5, in the Normal direction of any point of the described arc of described first molded line, the width of impeller air draft runner 13 is bi, and the distance between this point and central rotation axis L is Li, meet as 35<Li<82.527, bi=0.153Li+27.319; As 82.527≤Li<110, bi=0.011Li+39.079, wherein the dimensional units of bi with Li is identical, the unit of such as Li is cm, the unit of the bi obtained also is cm, and regardless of the dimensional units of bi and Li, bi and Li can preferably mate according to above-mentioned relation formula.Under this preferred implementation, because impeller channel adopts flaring pattern, simulation test confirms, the adverse pressure gradient that radially flows in now impeller air draft runner is little, suffered flow resistance is little, not easily boundary layer separation occur and produce swirl flow, velocity field is more evenly distributed, and thus flow effect reaches optimized degree.
The further preferred embodiment of the centrifugal blower fan blade wheel of arc is comprised respectively as above-mentioned first molded line and the second molded line, see Fig. 5, above-mentioned first molded line and the second molded line part being at least positioned at described centrifugal blower fan blade wheel outer edge region is separately formed as arc, in this case, under centrifugal blower fan blade wheel be placed as make state that central rotation axis L is vertical with vertical direction, the tangent line at outer end points place and the angle of vertical direction of described first molded line are α, the tangent line at outer end points place and the angle of vertical direction of described second molded line are β, 5 °≤α=β≤12 ° can be made.This more optimal refined structure improves and ensure that the exit flow of the impeller air draft runner 13 of centrifugal blower fan blade wheel is along wheel cap, wheel disc flowing, make flowing more smooth and easy, thus it is further perfect that the performance of centrifugal blower fan blade wheel of the present utility model is obtained.
The foregoing describe basic embodiment and the preferred implementation of the utility model centrifugal blower fan blade wheel, further, see Fig. 2 and Fig. 3, the utility model also provides a kind of centrifugal blower, it centrifugal blower fan blade wheel comprising spiral case 1 and be rotatably installed in this spiral case 1, wherein, described centrifugal blower fan blade wheel can adopt above-mentioned centrifugal blower fan blade wheel.More specifically, such as, the central part (i.e. wheel shaft joint 10) of the opposite side card of the wheel cap dorsad 4 of wheel disc 5 is connected with rotating shaft 2, and centrifugal blower fan blade wheel be can be rotated to support on the side sidewall of spiral case 1 by this rotating shaft 2 and is arranged in this spiral case 1.Be provided with air intake slip ring 3 in the opening of the relative opposite side sidewall of spiral case 1, the entrance point of this air intake slip ring 3 protrudes from outside spiral case 1, and outlet extend in the intake grill 9 of the centrifugal blower fan blade wheel in spiral case 1.
In addition, as mentioned above, centrifugal blower is widely used in multiple occasion, such as, be applied to the dust pelletizing system of sweeper.For this reason, the utility model also provides a kind of sweeper, and the dust collecting system of this sweeper can adopt centrifugal blower of the present utility model.
The centrifugal blower comprising described centrifugal blower fan blade wheel below in conjunction with the utility model preferred implementation shown in Fig. 2 to Fig. 9 simply describes its working procedure.
As shown in Figures 2 to 6, in centrifugal blower working procedure, air-flow enters from the intake grill 9 of centrifugal blower fan blade wheel along airintake direction A (substantially vertically), then flows out along outgassing direction B (roughly along radial direction R).When air-flow enters air intake district 7 by air inlet slip ring 3 and arrives blade inner, can produce by axially turning to radial, centrifugal blower fan blade wheel of the present utility model is due to the appropriate design of the shaping molded line of wheel cap 4 and wheel disc 5, passage section area along impeller air draft runner 13 is increased gradually, airspeed reduces gradually, the exit flow reducing impeller ventilation channel 13, to the impact of spiral case 1 internal face, improves the efficiency of blower fan, also reduces the noise of blower fan simultaneously.Find to adopt above-mentioned centrifugal fan impeller structure of the present utility model by CFD analysis of experiments, press close to wheel cap 4 and the mobility status near the relative inner surface of wheel disc 5 be improved significantly, inhibit the generation of separated flow, eddy-currents from source.Wheel cap 4 and wheel disc 5 place fluid are by axially corner loss is radially less, and the exit flow of impeller air draft runner 13 and the impact loss of spiral case 1 reduce, and the internal flow of impeller air draft runner is more smooth and easy, and the performance of centrifugal blower increases.By the verification experimental verification of preferred implementation of the present utility model, under the prerequisite that other working condition is identical, fan efficiency of the present utility model improves 6 ~ 9 percentage points, and noise significantly reduces, and has certain noise reduction.
As can be seen from upper description, the utility model advantage is:
First, the impeller air draft runner 13 formed between the wheel cap 4 of the utility model centrifugal blower fan blade wheel and wheel disc 5 is formed as the expanding runner that cross-sectional flow area is expanded from inner 11 to outer end 12, this reduces the outlet fluid of impeller air draft runner 13 and the impact loss of spiral case 1 to greatest extent, make to enter the air-flow of spiral case 1 evenly, centrifugal blower performance is better.
Second, in preferred implementation of the present utility model, the utility model is by optimizing the parameters of structural dimension of centrifugal blower fan blade wheel, especially the profile surface molded line of wheel cap 4 and wheel disc 5 (i.e. the first molded line and the second molded line) is made to comprise arc, this make it possible to the air-flow that makes to enter described impeller air draft runner 13 evenly, air-flow is little along impeller air draft runner 13 adverse pressure gradient outwardly, suffered flow resistance is little, not easily there is boundary layer separation and produce swirl flow, in impeller air draft runner, velocity distribution is even, this can reduce fan noise effectively, improve fan efficiency.
Especially, in the further optimal way of the utility model, the utility model provides the optimizing structure design about impeller air draft runner 13 normal direction cross-sectional width, it has comprehensively taken into account the diffusion degree of impeller air draft runner of the present utility model, the design of the cross-sectional flow area of impeller air draft runner is made to ensure that blower fan makes impeller channel diffusion best results when obtaining enough negative pressure, reduce air current flow drag losses, thus obtain good aeroperformance.
Below preferred implementation of the present utility model is described by reference to the accompanying drawings in detail; but; the utility model is not limited to the detail in above-mentioned mode of execution; within the scope of technical conceive of the present utility model; can carry out multiple simple variant to the technical solution of the utility model, these simple variant all belong to protection domain of the present utility model.
It should be noted that in addition, each the concrete technical characteristics described in above-mentioned embodiment, in reconcilable situation, can be combined by any suitable mode.Especially; each dimension scale relation or calculation relational expression involved in the description of each embodiment above-mentioned of the present utility model; not conflicting with under prerequisite that is that run counter to the utility model object, can mutually combinationally use, this also belongs to protection domain of the present utility model.In order to avoid unnecessary repetition, the utility model illustrates no longer separately to various possible compound mode.
In addition, also can carry out combination in any between various different mode of execution of the present utility model, as long as it is without prejudice to thought of the present utility model, it should be considered as content disclosed in the utility model equally.
Claims (11)
1. centrifugal blower fan blade wheel, comprise wheel cap (4) and wheel disc (5), the side card of this wheel disc (5) and a side surface relative spacing of described wheel cap (4) are arranged, the middle section of this wheel cap (4) is formed with the intake grill (9) of through this wheel cap (4) thickness, be fixed with between described wheel cap (4) and wheel disc (5) around described intake grill (9) spaced apart more blades (6), thus every two adjacent described blades (6), wheel cap (4) and wheel disc (5) surround the impeller air draft runner (13) be communicated with described intake grill (9) jointly, impeller air draft runner (13) described in each has the inner (11) and outer end (12) of being positioned at described centrifugal blower fan blade wheel middle section and peripheral edge regions respectively, it is characterized in that,
The sectional area from described the inner (11) to described outer end (12) of the passage section that impeller air draft runner (13) described in each intercepts along the circumference of described centrifugal blower fan blade wheel increases, thus described in each, impeller air draft runner (13) is formed as expanding runner.
2. centrifugal blower fan blade wheel according to claim 1, is characterized in that, described in each, the sectional area of the described passage section of impeller air draft runner (13) increases from described the inner (11) continuously to described outer end (12).
3. centrifugal blower fan blade wheel according to claim 1, it is characterized in that, it is the circumferentially same of R5 that the inner of blade described in each (6) is in radius, and the outer end of blade described in each is in radius is the circumferentially same of R6, wherein 0.261≤R5/R6≤0.522; And
The radius of the described intake grill (9) of described centrifugal blower fan blade wheel is L1, and the radius of described centrifugal blower fan blade wheel is L2, wherein 2.946≤L2/L1≤3.38.
4. centrifugal blower fan blade wheel according to claim 1, it is characterized in that, the inner port of impeller air draft runner (13) described in each and outer end port are respectively h and H, wherein 0.865≤h/H≤1.26 along the width of the central rotation axis (L) of described centrifugal blower fan blade wheel.
5. centrifugal blower fan blade wheel according to any one of claim 1 to 4, is characterized in that,
A described side surface relative with described wheel disc (5) of described wheel cap (4) comprises and rotates by the central rotation axis (L) of centrifugal blower fan blade wheel described in the first type wound the wheel cap surface of revolution formed, and this first molded line at least comprises arc; And
The described side card relative with described wheel cap (4) of described wheel disc (5) comprises and rotates by the central rotation axis (L) of centrifugal blower fan blade wheel described in Second-Type wire-wound the wheel disc surface of revolution formed, and this second molded line at least comprises arc.
6. centrifugal blower fan blade wheel according to claim 5, it is characterized in that, described first molded line comprises the first circular arc line that radius is R1 and radius and is R2 and relative to described first circular arc line more near the second circular arc line of described central rotation axis (L), one end of described second circular arc line and described central rotation axis (L) interval, the other end is connected with one end of described first circular arc line with seamlessly transitting, wherein 0.985≤R1/R2≤1.4; And
The three-arc line that described second molded line comprises straightway, radius is R3 and radius are R4 and relative to described three-arc line more away from the 4th circular arc line of described central rotation axis (L), described straightway is perpendicular to described central rotation axis (L), one end of this straightway is connected to described central rotation axis (L), the other end of this straightway is connected to one end of described three-arc line, the other end of this three-arc line is connected with one end of described 4th circular arc line with seamlessly transitting, wherein 0.267≤R3/R4≤0.52.
7. centrifugal blower fan blade wheel according to claim 6, is characterized in that, the radius R 2 of described second circular arc line and the radius R 3 of described three-arc line also meet: 1.5≤R2/R3≤2.4.
8. centrifugal blower fan blade wheel according to claim 5, it is characterized in that, described first molded line and the described second molded line part being at least positioned at described centrifugal blower fan blade wheel outer edge region is separately formed as described arc, under being placed as at described centrifugal blower fan blade wheel the state making described central rotation axis (L) vertical with vertical direction, the tangent line at outer end points place and the angle of described vertical direction of described first molded line are α, the tangent line at outer end points place and the angle of described vertical direction of described second molded line are β, wherein meet 5 °≤α=β≤12 °.
9. centrifugal blower fan blade wheel according to claim 5, it is characterized in that, in the Normal direction of any point of the described arc of described first molded line, the width of described impeller air draft runner (13) is bi, and the distance between this point and described central rotation axis (L) is Li, meet as 35<Li<82.527, bi=0.153Li+27.319; As 82.527≤Li<110, bi=0.011Li+39.079, wherein the dimensional units of bi with Li is identical.
10. centrifugal blower, the centrifugal blower fan blade wheel comprising spiral case (1) and be rotatably installed in this spiral case (1), is characterized in that, described centrifugal blower fan blade wheel is centrifugal blower fan blade wheel according to any one of claim 1 to 9.
11. sweepers, is characterized in that, the dust collecting system of this sweeper comprises centrifugal blower according to claim 10.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420598952.3U CN204200675U (en) | 2014-10-16 | 2014-10-16 | Centrifugal blower fan blade wheel, centrifugal blower and sweeper |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201420598952.3U CN204200675U (en) | 2014-10-16 | 2014-10-16 | Centrifugal blower fan blade wheel, centrifugal blower and sweeper |
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| CN204200675U true CN204200675U (en) | 2015-03-11 |
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| CN108533511A (en) * | 2018-05-09 | 2018-09-14 | 青岛海尔空调器有限总公司 | Air-supply assembly and cabinet type air conditioner indoor set with the air-supply assembly |
| CN110769912A (en) * | 2017-06-02 | 2020-02-07 | 北欧水产品公司 | Filter disc |
| CN113153811A (en) * | 2021-05-30 | 2021-07-23 | 台州学院 | Volute-free centrifugal ventilator adopting shaft disc to reduce static pressure loss |
| CN114458617A (en) * | 2022-01-24 | 2022-05-10 | 广东顺威精密塑料股份有限公司 | Centrifugal fan |
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2014
- 2014-10-16 CN CN201420598952.3U patent/CN204200675U/en not_active Expired - Fee Related
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| CN110769912A (en) * | 2017-06-02 | 2020-02-07 | 北欧水产品公司 | Filter disc |
| CN110769912B (en) * | 2017-06-02 | 2022-02-08 | 北欧水产品公司 | Filter disc, filter cartridge for use in a filter disc and method of reducing disturbances in a filter disc |
| CN108533511A (en) * | 2018-05-09 | 2018-09-14 | 青岛海尔空调器有限总公司 | Air-supply assembly and cabinet type air conditioner indoor set with the air-supply assembly |
| CN108533511B (en) * | 2018-05-09 | 2024-05-03 | 青岛海尔空调器有限总公司 | Air supply assembly and cabinet air conditioner indoor unit with same |
| CN113153811A (en) * | 2021-05-30 | 2021-07-23 | 台州学院 | Volute-free centrifugal ventilator adopting shaft disc to reduce static pressure loss |
| CN113153811B (en) * | 2021-05-30 | 2022-05-27 | 台州学院 | Volute-free centrifugal ventilator adopting shaft disc to reduce static pressure loss |
| CN114458617A (en) * | 2022-01-24 | 2022-05-10 | 广东顺威精密塑料股份有限公司 | Centrifugal fan |
| CN114458617B (en) * | 2022-01-24 | 2024-05-07 | 广东顺威精密塑料股份有限公司 | Centrifugal fan |
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