CN101832297A - Axial flow fan and air valve thereof as well as cooling tower and air cooler - Google Patents
Axial flow fan and air valve thereof as well as cooling tower and air cooler Download PDFInfo
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- CN101832297A CN101832297A CN 201010178851 CN201010178851A CN101832297A CN 101832297 A CN101832297 A CN 101832297A CN 201010178851 CN201010178851 CN 201010178851 CN 201010178851 A CN201010178851 A CN 201010178851A CN 101832297 A CN101832297 A CN 101832297A
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Abstract
The invention discloses an air valve for an axial flow fan, the axial flow fan with the air valve and a cooling tower or an air cooler with the axial flow fan. The disclosed air valve for the axial flow fan comprises a valve body and a plurality of blades, wherein each blade comprises a blade shaft and a main blade; the inner edges of the main blades are fixed with the blade shafts; the valve body comprises an outer barrel and a central seat which are relatively fixed, and the central seat is arranged in the outer barrel; the outer end and the inner end of the blade shaft are respectively and rotatably arranged on the outer barrel and the central seat; and the plurality of blades are radially distributed on the periphery of the central seat. In the disclosed air valve for the axial flow fan, the blades can be matched with the pressure distribution of an air outlet of the axial flow fan, the blade arrangement area corresponds to a positive pressure air exhaust area of the air outlet, and the opening degree of each blade can be better matched with the pressure of the area to reduce the air exhaust resistance of the air outlet so as to reduce the vibration of the blades, lower the noise and the opening pressure of the air valve and improve the working reliability of the air valve.
Description
Technical field
The present invention relates to a kind of blower fan technology, particularly a kind of axial fan air-valve, and have the axial fan of this air-valve, also relate to a kind of air-cooler that has the cooling tower of this axial fan and have this axial fan.
Background technique
Axial fan is one of general blower fan of current application.Axial fan mainly comprises blower fan body and impeller, and casing generally has cylindrical structure to form the air port, and impeller is installed in the exhaust outlet; Impeller can rotate in exhaust outlet under suitable dynamic mechanism drives, and after gas enters from the exhaust outlet front end, can obtain energy by the impeller of rotation, and pressure and flow velocity increase, and discharge from the exhaust outlet rear end then, realize flowing of air-flow.
Current, a lot of equipment need be provided with axial fan, and require according to the needs of concrete operating mode the running state of axial fan to be regulated.Wherein, the cooling tower of mechanical ventilation type adopts axial fan to carry out forced ventilation usually.
The cooling tower of mechanical ventilation type is widely used in HVAC or/and in the air-conditioning system of refrigeration.In comprising the big load air-conditioning system of a plurality of main frames, often dispose many cooling towers cooling medium is cooled off.The cooling tower of this class air-conditioning system has two kinds of operating modes: a kind of is independent operation mode, and another kind is to be communicated with operating mode.
In independent operation mode, each main frame water-cooling tube by separately respectively connects the cooling tower that is complementary with its amount of cooling water; If the amount of cooling water demand of individual host is bigger, also several cooling towers can be assembled into cooling tower group and same main frame coupling, but the cooling tower or the cooling tower group that are complementary with each main frame are uncorrelated mutually.When one or more main frames quit work, stop using cooling tower corresponding or cooling tower group with it; At this moment, can't make full use of the heat radiation filler in cooling tower or the cooling tower group, therefore, when independent operation mode, there is the low deficiency of cooling effectiveness in cooling tower.
In being communicated with operating mode, all cooling towers of air-conditioning system are assembled into the cooling tower group, and the All hosts of air-conditioning system is by same cooling water pipeline, and all cooling towers that cooling water is transported in the cooling tower group cool off.The assembly form of cooling tower group has two kinds: a kind of is the dividing plate of cancellation or each cooling tower junction plane of partial cancellation, and the wind path between each cooling tower is connected; Another kind is the dividing plate that keeps junction plane, and the wind path of each cooling tower is separate.This pattern can make full use of the heat radiation filler in each cooling tower, has the high advantage of operational efficiency.
Because there is the low deficiency of operational efficiency in independent operation mode, and is current, the cooling tower of the air-conditioning system of big load is usually to be communicated with mode operation.
In actual use, air-conditioning system is often moved under sub load.With the connection mode operation time, the operation quantity that the blower fan of the part cooling tower of stopping using is usually regulated cooling tower is to cut down the consumption of energy.When the junction plane between each cooling tower kept dividing plate, the cooling water that enters the inactive cooling tower of blower fan can't effectively be cooled off, thereby is difficult to realize cooling purpose; When the junction plane of each cooling tower does not have dividing plate, owing to interconnect between the wind path of each cooling tower, when the blower fan running of other cooling towers, the wind path of the cooling tower of inactive blower fan can form negative pressure, and then outer gas stream may enter by the exhaust outlet of this cooling tower in the wind path of cooling tower group, and then the air-flow short circuit takes place, cause the useful horsepower of cooling tower group to reduce.Simultaneously, the air-flow that sucks from exhaust outlet also can make inactive blower fan counter-rotating, and then influences the life-span of this blower fan machine driven system; In addition, when starting the counter-rotating blower fan, be easy to cause this fan starting power excessive and cause overload, damage the power mechanisms such as motor of this blower fan.
Equally, in the air-conditioning system and other air-cooling apparatuses of air-cooled multi fan module, also have the air-flow short circuit, cooling unit useful horsepower reduces, problems such as blower fan counter-rotating.
For solving the problems of the technologies described above, another publication number of claimant is in the disclosed technological scheme of patent application of CN100504269C, exhaust outlet at blower fan also is provided with air-valve, this air-valve can be when its corresponding blower fan be stopped using, automatically exhaust outlet is closed, to avoid the useful horsepower of air-flow short circuit, maintenance cooling tower group, the blower fan counter-rotating prevents to stop using.
Current air-valve is a louvered blade valve, comprises valve body and blade, and valve body is installed in the exhaust outlet outside, and blade is divided into two groups, and the blade two ends are rotatably installed on the valve body, and a plurality of blades are along a secant symmetric arrays across exhaust outlet.But this air-valve can not be complementary with the pressure distribution of axial fan exhaust outlet, thereby has produced a lot of problems.
As shown in Figure 1, this figure is the pressure distribution schematic representation of axial fan exhaust outlet.Among the figure, transverse axis is the radius R of exhaust outlet, vertical pivot is a pressure value P, and as can be seen from Figure, exhaust outlet pressure is the wave band formula and distributes, be that pressure increases earlier from the exhaust outlet outer, reduce, O is reduced to minimum to the axle center again, even can form negative value, pressure be on the occasion of outer peripheral portion form the malleation exhaust zone, air-flow discharges from this zone; Be the central core region of negative value even can form the negative pressure recirculating zone that in this zone, the outer air-flow of exhaust outlet may enter in the exhaust outlet under the effect of negative pressure pressure at pressure.As shown in Figure 2, this figure is the pressure span schematic representation at axial fan exhaust outlet place.At the exhaust outlet place, according to its pressure difference, pressure can be called zone of high pressure Z1 greater than the zone of P1, pressure is lower than P1 and is called low pressure area Z2 greater than zero zone, the malleation exhaust zone is divided into zone of high pressure Z1 and low pressure area Z2; The negative pressure recirculating zone that central core region forms is Z3.
According to above-mentioned axial fan pressure distribution characteristics, can determine: when adopting the air-valve of existing louvered blade valve, the pressure that the two end portions of every blade and intermediate portion bear is also inequality, and the power that different parts bears is also inequality.With the blade that is positioned at the exhaust outlet neutral position is example, and the intermediate portion of this blade is in the negative pressure recirculating zone, and two end portions is positioned at the malleation exhaust zone; The comprehensive function of negative pressure recirculating zone and malleation exhaust zone pressure makes this blade reach balance at certain opening angle, and the angle that this opening angle needs less than the air draft of malleation exhaust zone stops the needed angle that refluxes greater than the negative pressure recirculating zone simultaneously; Like this, under this opening angle, can align on the one hand and press exhaust zone to form very big exhaust resistance, can make air communication cross the negative pressure recirculating zone on the other hand refluxes, the comprehensive result in two aspects increases exhaust resistance, has reduced the ventilation efficiency of blower fan, improves the energy consumption of blower fan.Simultaneously, be between the wave band formula distribution air-flow and also can produce frictional force, thereby increase the exhaust resistance of exhaust outlet.
In addition, have the wind-guiding effect when opening owing to each blade, can be by the air-flow of each face of blade to the certain pressure of reverse side generation of its front blade; Like this, all have a forward and reverse opposite pressure between the every blade, the discharge that this has also influenced air-flow increases the exhaust resistance of exhaust outlet.
When the stroke linkage mechanism being set guaranteeing that each vane travels is kept strokes, though can realize the basically identical of each blade opening angle, but it is same because each vane stress is inequality, also can make the opening angle of each blade not to be complementary, have the bigger problem of exhaust outlet exhaust resistance equally with the presumptive area stream pressure.
Because the exhaust outlet exhaust resistance is bigger, not only can makes blade produce vibration, and then produce very big noise; Also can improve the air-valve cracking pressure, and then hour, just can't guarantee that air-valve opens with the blower fan running, reduce the reliability of fan operation at the exhaust outlet stream pressure.
In addition, current blade is the planar blade, and at the horizontal arrangement air-valve, opening angle is under the state of 90 degree, can't form moment between the gravity of blade and its shaft axis, is difficult to satisfy the needs that air-valve cuts out automatically.
Summary of the invention
Therefore, first purpose of the present invention is, a kind of axial fan air-valve is provided, to reduce the exhaust resistance of exhaust outlet.
Second purpose of the present invention is, a kind of axial fan is provided, to reduce the blower fan exhaust resistance.
The 3rd purpose of the present invention is, a kind of cooling tower with above-mentioned axial fan is provided.
The 4th purpose of the present invention is, a kind of air-cooler with above-mentioned axial fan is provided.
In order to realize above-mentioned first purpose, axial fan provided by the invention comprises valve body and a plurality of blade with air-valve, described blade comprises sharf and main lobe, described main lobe inner edge and sharf are fixed, difference with the prior art is that described valve body comprises relatively-stationary urceolus and center base, and described center base is positioned at urceolus, the outer end of described sharf and the inner are rotatably installed in respectively on urceolus and the center base, and a plurality of described blades are distributed in the center base periphery radially.
Preferably, described center base is with the central core region sealing of urceolus.
Optionally, described blade also comprises inner edge and the fixing accessory lobes of sharf, and the extension direction of described accessory lobes is opposite with the extension direction of main lobe, and the extension area of described main lobe is greater than the extension area of described accessory lobes.
Optionally, described main lobe and accessory lobes are respectively near outer end and the inner of described sharf.
Optionally, on described sharf bearing of trend, described main lobe and described accessory lobes are overlapped at least.
Preferably, the outside of described main lobe is or/and extend to its reverse side direction deflection in the outside of accessory lobes.
Preferably, in the air-valve full-gear, has predetermined distance between the vertical line by described blade center of gravity and the axis of described sharf.
Preferably, described air-valve also comprises linking mechanism, and described linking mechanism comprises elastic mechanism, pressure disk and a plurality of driving rocking handle; Described center base comprises central tube and guide rod, and described guide rod is arranged in central tube; A plurality of described sharfs the inner is passed the central tube barrel respectively, and links to each other with the outer end of the driving rocking handle that is positioned at central tube respectively, and the axis of sharf is departed from the inner of described driving rocking handle; Described pressure disk is enclosed within outside the guide rod, and described elastic mechanism two ends are supported on respectively on pressure disk and the guide rod, and described pressure disk compresses the inner of described driving rocking handle.
Preferably, described guide rod comprises slide bar and the spring pressure pad that links to each other by screw-thread fit, and described elastic mechanism two ends are supported on respectively on pressure disk and the spring pressure pad.
Optionally, described air-valve also comprises linking mechanism, and described linking mechanism comprises gear ring and a plurality of driving wheel; Described center base comprises central tube; A plurality of described sharfs the inner is passed the central tube barrel respectively, and links to each other the dead in line of described driving wheel axis and described sharf respectively with the driving wheel that is positioned at central tube; Described gear ring meshes with described a plurality of driving wheels simultaneously.
In order to realize above-mentioned second purpose, axial fan provided by the invention comprises blower fan body and impeller, and described blower fan body forms exhaust outlet, and described exhaust outlet place is provided with above-mentioned any described axial fan air-valve.
In order to realize above-mentioned the 3rd purpose, cooling tower provided by the invention comprises cooling tower body and blower fan, and described blower fan is above-mentioned axial fan.
In order to realize above-mentioned the 4th purpose, air-cooler provided by the invention comprises cooler body and blower fan, and described blower fan is above-mentioned axial fan.
Compared with prior art, axial fan provided by the invention is with in the air-valve, and a plurality of blades are distributed in the center base periphery radially, and the sharf of each blade is rotatably installed on the valve body respectively.In this technological scheme, the layout of blade can be complementary with the pressure distribution of axial fan exhaust outlet, make the vane collocation zone corresponding, and then blade opening angle and malleation exhaust zone stream pressure are complementary, reduce the exhaust resistance of exhaust outlet with the malleation exhaust zone of exhaust outlet; Simultaneously, because the opening angle of each blade can be realized better coupling with this regional pressure, this just can reduce the pressure of rear blade water conservancy diversion air-flow to front vane greatly, reduces the exhaust resistance of exhaust outlet further; In addition, utilize axial fan air-valve provided by the invention, a plurality of blades are divided into the air-flow of exhaust outlet in the air-flow of a plurality of parts, and the air-flow of a plurality of parts is outwards penetrated respectively in straight mode to jet, and then can reduce resistance between the exhaust outlet eddy current, reduce the frictional force between the air-flow, promote air-flow directly to the jet effect.Because the exhaust outlet exhaust resistance reduces, can reduce blade vibration on the one hand, reduce noise, reduce the cracking pressure of air-valve, improve the functional reliability of air-valve; Can increase the pressure difference of draught fan impeller front and back on the other hand, and then can provide prerequisite for total air-out flow and the usefulness that increases axial fan.
In further technological scheme, make the central core region sealing of center base with the valve body urceolus, the negative pressure recirculating zone of at least a portion can be sealed like this, and then reduce the throughput of passing through the backflow of negative pressure recirculating zone, improve the ventilation efficiency of air-valve.
In further technological scheme, described blade also comprises inner edge and the fixing accessory lobes of sharf, and the extension direction of described accessory lobes is opposite with the extension direction of main lobe, and described main lobe extension area is greater than described accessory lobes extension area.This technological scheme can guarantee to open on the one hand, air draft and closed needs, and on the other hand, the gravity that accessory lobes can the balance main lobe reduces the opening resistance of blade, improves the functional reliability of air-valve.
In further technological scheme, described main lobe and accessory lobes are fixed with inner near the outer end of sharf respectively, can make accessory lobes be positioned at the low pressure area of exhaust outlet, reduce the exhaust resistance that accessory lobes are caused as much as possible.
Further in the technological scheme, the outside of described main lobe is or/and extend to its reverse side direction deflection in the outside of accessory lobes.The air-valve that utilizes this technological scheme to provide, the outside of main lobe can improve the positive air-out water conservancy diversion effect of main lobe, and reverse side forms the jet flow negative pressure district, increase main lobe obverse and reverse pressure difference, increase the air-valve air-out flow; Simultaneously, the air-flow eddy flow that this structure can also form with the exhaust outlet of axial fan adapts, and the actual opening angle that makes main lobe is greater than 90 degree, further to reduce the exhaust resistance of air-valve.
In further technological scheme, in the air-valve full-gear, make between the axis of vertical line by described blade center of gravity and described sharf and have predetermined distance, can make the moment of the gravity formation of blade like this with respect to the sharf axis, when blower fan shuts down, blade can be improved automatically close, that improves air-valve closes performance automatically.
In further technological scheme, also comprise linking mechanism, the conformity that this linking mechanism can be realized each blade action on the one hand realizes rectification, reduces the noise of air-valve generation, improves the stability of air-valve work; On the other hand, the elastic mechanism two ends are supported on pressure disk and the spring pressure pad respectively, the moment that can balance blade forms with respect to the sharf axis is adjusted the cracking pressure of air-valve easily, improves the functional reliability of air-valve.In further technological scheme, guide rod comprises slide bar and the spring pressure pad that links to each other by screw-thread fit, can adjust the elastic force of elastic device by the rotating spring pressure pad, can adjust the air-valve cracking pressure easily like this, improves the conformability of air-valve.
Providing above-mentioned axial fan with on the basis of air-valve, provided by the inventionly comprising the axial fan of this air-valve and comprise that the cooling tower of this axial fan also has the corresponding techniques effect.
Description of drawings
Fig. 1 is the pressure distribution schematic representation of axial fan exhaust outlet;
Fig. 2 is the pressure span schematic representation at axial fan exhaust outlet place;
Fig. 3 is the structural representation of the axial fan that provides of the embodiment of the invention one with air-valve, shows the profile diagram of axial fan among the figure with double dot dash line;
Fig. 4 is that A among Fig. 3 is to view;
Fig. 5 is in the air-valve that provides of embodiment one, the structural representation of blade.
Fig. 6 be the B of Fig. 5 to view, the position when also showing blade and be in open mode among this figure with double dot dash line;
Fig. 7 is the structural representation of air-valve when being in open mode:
Fig. 8 is an I-I part enlarged view among Fig. 3;
Fig. 9 is an II-II part enlarged view among Fig. 7;
Figure 10 is among the embodiment one, the axial fan vane stress principle signal power of air-valve;
Figure 11 is the top view structural representation of the axial fan that provides of the embodiment of the invention two with air-valve;
Figure 12 is an III-III part enlarged view among Figure 11.
Embodiment
Describe the present invention below in conjunction with accompanying drawing, the description of this part only is exemplary and explanatory, should any restriction not arranged to protection scope of the present invention.
Please refer to Fig. 3 and Fig. 4, Fig. 3 is the structural representation of the axial fan that provides of the embodiment of the invention one with air-valve, shows the profile diagram of axial fan among the figure with double dot dash line; Fig. 4 is that A among Fig. 3 is to view.
The axial fan that embodiment one provides comprises urceolus 1, center base 2 and a plurality of blade 3 with air-valve; The quantity of blade 3 can determine according to actual needs that in general, blade 3 quantity are relevant with installation conditions, and under the identical situation of blade diameter, blade 3 is few more, and requirements of installation space is big more, and blade 3 is many more, and requirements of installation space is more little.Center base 2 is positioned at urceolus 1, and passes through support beam 4 relative fixed with urceolus 1, forms the valve body of air-valve.In this example, urceolus 1 is a cylindrical drum, and the blower fan body of its lower end and axial fan 10 is fixed; Center base 2 comprises central tube 21 and guide rod 22, and central tube 21 is the cylindrical drum of lower end closed, and guide rod 22 is positioned at the center region of the central tube 21 of tubular, and the space in the urceolus 1 is corresponding with the exhaust outlet of blower fan; Preferably, the central lines of urceolus 1, central tube 21 and guide rod 22.As shown in Figure 4, a plurality of blades 3 are distributed in the periphery of center base 2 radially, and in this example, a plurality of blades 3 are in the annular space that circumferentially is evenly arranged between urceolus 1 and the center base 2.
Please refer to Fig. 5, this figure is in the air-valve that provides of embodiment one, the structural representation of blade.Blade 3 comprises sharf 31, main lobe 32 and accessory lobes 33.In conjunction with shown in Figure 3, sharf 31 the inners and outer end are rotatably installed on urceolus 1 and the central tube 21 by bearing 5 and bearing 6 respectively, and in order to prevent blade 3 along sharf 31 axial direction plaies, bearing 5 is a thrust bearing; Main lobe 32 inner edges and sharf 31 are fixing, and accessory lobes 33 inner edges and sharf 31 are fixing, and the extension direction of accessory lobes 33 is opposite with the extension direction of main lobe 32.In this example, main lobe 32 extension areas are greater than described accessory lobes 33 extension areas, and the two is fixing near outer end and the inner of sharf 31 respectively, be that a plurality of main lobves 32 are corresponding with the zone of high pressure Z1 of axial fan 10 exhaust outlets, a plurality of accessory lobes 33 are corresponding with the low pressure area Z2 of exhaust outlet, and central tube 21 lower ends are corresponding with negative pressure recirculating zone Z3.
The working principle of above-mentioned air-valve is as follows:
Please refer to Fig. 6 and Fig. 7, Fig. 6 be the B of Fig. 5 to view, in addition, the position when also showing blade and be in open mode among this figure with double dot dash line; Fig. 7 is the structural representation of air-valve when being in open mode.
When blower fan 10 work, the impeller rotation of blower fan 10 makes air communication cross exhaust outlet and outwards flows.Main lobe 32 is subjected to the Z1 stream pressure effect of exhaust outlet zone of high pressure, accessory lobes 33 are subjected to the effect of exhaust outlet low pressure area Z2 stream pressure, because the extension area of accessory lobes 33 is less than the extension area of main lobe 32, and low pressure area Z3 stream pressure is less than zone of high pressure Z1 stream pressure, the main lobe 32 of the official post blade 3 of the active force that main lobe 32 and accessory lobes 33 are subjected to outwards overturns, make blade 3 be transformed into open mode from closed state, make exhaust outlet become open mode, make air-flow waltz through exhaust outlet and discharge by closed state.According to blower fan 10 exhaust outlet stream pressure differences, blade 3 may have different opening angles, when Fig. 7 is in maximum opening angle for blade 3, and position when promptly being in full-gear.Excessive in order to prevent blade 3 opening angles, the angle position-limit mechanism can also be set on central tube 21, when blade 3 opening angles reach predetermined angle, continue rotation by angle position-limit mechanism limit blade 3.
In this example, the air-valve level is installed, can under its deadweight effect, close automatically in order to make blade 3, as shown in Figure 6, blade 3 is in maximum opening angle, be air-valve when being in full-gear, have predetermined distance L between the vertical line by blade 3 center of gravity G and the axis of sharf 31, be about to blade 3 and be set to the off-axis structure.The working environment of this intended distance and air-valve, blade 3 gravity, sharf 31 two ends frictional force and that air-valve cuts out performance demands automatically is relevant, those skilled in the art can select suitable size according to actual needs, with under full-gear, make the gravity of blade 3 can form enough moment, blade 3 is closed under the deadweight effect automatically, and that improves air-valve closes performance automatically.
When blower fan quit work, under blade 3 actions of gravity, blade 3 turned back to closed state from open mode, and exhaust outlet is sealed.
Compared with prior art, in the air-valve provided by the invention, a plurality of blades 3 are distributed in center base 2 peripheries radially, the layout of blade 3 can be complementary with the pressure distribution of the exhaust outlet of axial fan 10, not only can make blade 3 layout area corresponding with the malleation exhaust zone of exhaust outlet, each blade 3 opening angle and malleation exhaust zone stream pressure coupling can also be made, and then the exhaust outlet exhaust resistance can be reduced; Simultaneously, because the opening angle of each blade 3 can be realized better coupling with this regional pressure, the air-flow that each blade 3 front water conservancy diversion are formed is reduced to minimum to the influence of its place ahead blade 3, this has also reduced the exhaust resistance of exhaust outlet further, and can make the air-flow of discharge even more, stable; Stream pressure is evenly distributed on each blade 3, a plurality of blades 3 are divided into the air-flow of exhaust outlet in the air-flow of a plurality of parts, and the air-flow of a plurality of parts is outwards penetrated respectively in straight mode to jet, and then can reduce resistance between the exhaust outlet eddy current, reduce the frictional force between the air-flow, promote air-flow directly to the jet effect, improve the air draft layout.Because the exhaust outlet exhaust resistance reduces, can reduce blade 3 vibrations on the one hand, reduce the air-valve noise, reduce the cracking pressure of air-valve, improve the functional reliability of air-valve; Can increase the pressure difference of draught fan impeller front and back on the other hand, and then can provide prerequisite for total air-out flow and the usefulness that increases axial fan.
In this example, make main lobe 32 corresponding, make accessory lobes 33 corresponding with low pressure area Z2 with zone of high pressure Z1.This structure can be utilized the gravity of accessory lobes 33 balance main lobves 32 on the one hand, improves the sensitive performance of unlatching of blade 3, reduces the cracking pressure of air-valve, satisfies unlatching, air draft and closed needs; Can reduce the exhaust resistance that accessory lobes 33 are caused as much as possible on the other hand, guarantee the whole air draft performance of air-valve.In order to improve the overall performance of air-valve, can also make according to actual needs between the extension area of main lobe 32 and the accessory lobes 33 extension areas and have predetermined ratio, the determining and to determine according to factors such as the size of the environment of air-valve, main lobe 32 and blade 3 weight of predetermined ratio, when less or weight is light in main lobe 32 sizes, what accessory lobes 33 can be provided with is smaller, under specific circumstances, also accessory lobes 33 can be set.In addition, experiment showed, in the optimized technical scheme, on sharf 31 bearing of trends, main lobe 32 and accessory lobes 33 are overlapped at least, help keeping the working stability and the reliability of blade 3.
In this example, central tube 21 is corresponding with negative pressure recirculating zone Z3, in order to reduce or to avoid the outer air communication of exhaust outlet to cross negative pressure recirculating zone Z3 and reflux, and can also be with the lower end closed of central tube 21, so that negative pressure recirculating zone Z3 is sealed; Certainly, also the upper end closed of central tube 21 can be able to be realized the purpose of closed negative pressure recirculating zone Z3 equally.In the optimized technical scheme, the top and bottom sealing of central tube 21 can be entered in the central tube 21 to avoid moisture.
Refer again to Fig. 6, in this example, extend to its reverse side direction deflection in the outside of main lobe 32, and described reverse side is the opposing side of main lobe 32 guide faces, makes main lobe 32 form the wing blade structure on the whole.The benefit of this structure is: the main lobe 32 of this structure can adapt with the air-flow eddy flow that axial fan 10 exhaust outlets form, and can improve the positive air-out water conservancy diversion effect of main lobe 32; Simultaneously, make its reverse side form the jet flow negative pressure district together, make between main lobe 32 fronts and the reverse side and produce pressure difference, reduce the cracking pressure of air-valve, improve the sensitive performance of unlatching of air-valve; In addition, as shown in Figure 6, this structure can also make the actual opening angle a of main lobe 32 greater than 90 degree, and then reduces the exhaust resistance of air-valve.Equally, extended in accessory lobes 33 outsides to its reverse side deflection, form the wing blade structure, also can improve its positive water conservancy diversion effect, reduce the exhaust resistance of exhaust outlet.
Refer again to Fig. 7, in this example, the support beam 4 that connects urceolus 1 and center base 2 is positioned at blade 3 outsides, experimental results show that, be arranged on blade 3 outsides and will more help reducing the exhaust outlet exhaust resistance, being arranged on then obviously influences the air draft air-flow between blade 3 and the blower fan 10, and influences the flow stability of air-flow.Therefore, when between urceolus 1 and center base 2, linking to each other, preferably be arranged on blade 3 outsides by miscellaneous part.
In order to strengthen discharging the rectified action of air-flow, the air-valve that embodiment one provides also is provided with linking mechanism, so that each blade 3 has identical opening angle, and helps reducing or avoiding the shake of blade 3.
Please refer to Fig. 8 and Fig. 9, Fig. 8 is an I-I part enlarged view among Fig. 3, and Fig. 9 is an II-II part enlarged view among Fig. 7.Linking mechanism 7 comprises helical spring 71, pressure disk 72 and a plurality of driving rocking handle 73; Guide rod 22 comprises spring pressure pad 221 and the slide bar 222 that links to each other by screw-thread fit, also is provided with handwheel on the spring pressure pad 221, the center line of preferred slide bar 222, between spring pressure pad 221 and the slide bar 222 center line of screw thread all with the central lines of central tube 21.A plurality of driving rocking handles 73 are corresponding one by one with the sharf 31 of a plurality of blades 3, a plurality of sharfs 31 the inners are passed central tube 21 barrels respectively, each sharf 31 the inner links to each other with an outer end that drives rocking handle 73 that is positioned at central tube 21 respectively, driving rocking handle 73 is a knee, and the axis of sharf 31 is departed from its inner.Helical spring 71 is enclosed within outside the slide bar 222, and pressure disk 72 also is enclosed within outside the slide bar 222, and can slide along slide bar 222.On helical spring 71 two ends difference abutment pressure dish 72 upsides and the spring pressure pad 221, pressure disk 72 downsides form press face and are pressed against on the inner that drives rocking handle 73.Under the effect of helical spring 71, pressure disk 72 can apply predetermined force to a plurality of driving rocking handles 73, make and respectively drive rocking handle 73 the inners and have identical phase angle with respect to its corresponding sharf 31, make the main lobe 32 of each blade 3 have essentially identical opening angle, realize the conformity of each blade 3 action and opening angle.Spring pressure pad 221 and slide bar 222 link to each other by screw thread, can pass through handwheel rotating spring pressure pad 221 like this, spring pressure pad 221 is moved up and down with respect to slide bar 222, and then adjust the decrement of helical spring 71, adjust 72 pairs of pressure disk and drive the active force that rocking handle 73 applies.Not needing to adjust under the situation of helical spring 71 decrements, also guide rod 22 can be set to integrative-structure, and make helical spring 71 1 end bearings in the relevant position of guide rod 22, also can realize making the purpose of each blade 3 interlock.
In this example, make helical spring 71 two ends can also adjust the cracking pressure of air-valve respectively on abutment pressure dish 72 upsides and the spring pressure pad 221 easily.Its principle is as follows: with reference to Figure 10, and among this figure embodiment one, the axial fan vane stress principle signal power of air-valve.When the opening angle of blade 3 was a, the gravity of blade 3 formed running torque M1=G * L1 with respect to the axis with sharf 31; If the active force that the outer end of 72 pairs of single driving rocking handles 73 of pressure disk applies is F, moment M2=F * L2 that 72 pairs of blades of pressure disk 3 produce.From diagram as can be seen, when opening angle a is zero, the M1 maximum, this moment helical spring 71 the decrement maximum, F is also maximum.By adjusting the decrement of helical spring 71, just can change the difference between M1 and the M2, make blade 3 when being subjected to being scheduled to blast, upwards upset realizes the adjustment to the air-valve cracking pressure; Simultaneously, along with the continuous increase of opening angle a, M1 reduces; Make to drive the phase angle suitable, rocking handle 73 the inners, reduce gradually, M2 is constantly reduced, keep difference between M1 and the M2 within prespecified range, keep the stable of blade 3 opening processes in the decrement of helical spring 71 with respect to sharf 31.Certainly, can also pass through to select the helical spring 71 of suitable elasticity system, to obtain suitable cracking pressure and to open performance or/and drive the phase angle of rocking handle 73.
In order to prevent that driving rocking handle 73 separates with pressure disk 72, also can on the press face of pressure disk 72, corresponding structure be set, make the inner that drives rocking handle 73 keep being connected with pressure disk 72, such as, can make driving rocking handle 73 inner hinged with pressure disk 72, also can on the press face of pressure disk 72, be provided with and drive the groove that matches in rocking handle 73 the inners, to inlay the inner of driving rocking handle 73.In this example, the press face that pressure disk 72 downsides form is the plane, and therefore, each drives rocking handle 73 the inners and has identical phase angle with respect to its main lobe 32; Drive rocking handle 73 inner contact position height when inequality in pressure disk 72 and each, also can make respectively to drive rocking handle 73 the inners and have different phase angles with respect to its main lobe 32.
In the present embodiment, helical spring 71 is separately positioned on pressure disk 72 both sides with driving rocking handle 73, the compression that depends on helical spring 71 realizes applying predetermined active force to driving rocking handle 73; It will be understood by those skilled in the art that also and helical spring 71 can be arranged on pressure disk 72 the same sides with driving rocking handle 73, the elongation that depends on helical spring 71 realizes driving the purpose that rocking handle 73 applies predetermined effect.Certainly, helical spring 71 can also can be substituted by the elastic mechanism of other kinds, and elastic mechanism is connected between pressure disk 72 and the guide rod 22 by other class springs.
The embodiment of the invention two also provides the air-valve that comprises another kind of linking mechanism.Please refer to Figure 11 and Figure 12, Figure 11 is the top view structural representation of the axial fan that provides of the embodiment of the invention two with air-valve, and Figure 12 is an III-III part enlarged view among Figure 11.
Compare with the air-valve that embodiment one provides, the air-valve that embodiment two provides comprises another kind of linking mechanism, and this linking mechanism comprises a gear ring 82 and a plurality of driving wheel 81.A plurality of sharfs 31 the inners are passed central tube 21 barrels respectively, and link to each other the dead in line of driving wheel 81 axis and sharf 31 respectively with the driving wheel 81 that is positioned at central tube 21; Gear ring 82 meshes with all driving wheels 81 simultaneously, and driving wheel 81 meshes with gear ring 82 for convenience, and in the preferred version, the actuation gear 81 and gear ring 82 gear teeth are the awl tooth; Gear ring 82 is rotatably installed in the central tube 21.Utilize this linking mechanism, when gear ring 82 rotation predetermined angles, the identical angle of each actuation gear 81 rotation, each blade 3 can keep synchronization motion, realizes the interlock of each blade 3; In addition, can also be provided with as motor or other mechanisms as driving mechanism, and this drive mechanism gear ring 82 is rotated, can realize adjustment like this to blade 3 opening angles, the adjustable air-valve of angulation, satisfy the vertical setting of air-valve or other more many-sided demands, can also provide prerequisite for the telecontrol of blade 3 opening angles simultaneously.
Providing on the basis of above-mentioned air-valve, a kind of axial fan also is provided, this axial fan comprises the blower fan body, driving mechanism and impeller, described blower fan body forms exhaust outlet, and impeller is installed in the blower fan body, the rotation of drive mechanism impeller, described exhaust outlet place is provided with above-mentioned any air-valve.Because air-valve has above-mentioned technique effect, the axial fan that has this air-valve also has corresponding technique effect.In addition, the present invention also provides a kind of cooling tower and air-cooler, and the cooling tower that provides comprises cooling tower body and blower fan, and blower fan is above-mentioned axial fan, and the air-cooler that provides comprises cooler body and above-mentioned axial fan.Because good seal performance when axial fan has closure, the cooling tower with this axial fan can be avoided airflow reflux and blower fan counter-rotating, improves the cooling effectiveness of cooling tower and air-cooler.Certainly, above-mentioned axial fan also can be applied in other cooling units, also can produce the corresponding techniques effect.
The above only is a preferred implementation of the present invention, should be understood that, for those skilled in the art, under the prerequisite that does not break away from the principle of the invention, can also make some improvements and modifications, such as, under the not high particular condition of performance requirement, also blade 3 can be set to non-off-axis structure, or the like; These improvements and modifications also should be considered as protection scope of the present invention.
Claims (13)
1. axial fan air-valve, comprise valve body and a plurality of blade, described blade comprises sharf and main lobe, described main lobe inner edge and sharf are fixed, it is characterized in that described valve body comprises relatively-stationary urceolus and center base, described center base is positioned at urceolus, the outer end of described sharf and the inner are rotatably installed in respectively on urceolus and the center base, and a plurality of described blades are distributed in the center base periphery radially.
2. axial fan air-valve according to claim 1 is characterized in that, described center base is with the central core region sealing of urceolus.
3. axial fan air-valve according to claim 1, it is characterized in that, described blade also comprises inner edge and the fixing accessory lobes of sharf, and the extension direction of described accessory lobes is opposite with the extension direction of main lobe, and the extension area of described main lobe is greater than the extension area of described accessory lobes.
4. axial fan air-valve according to claim 3 is characterized in that, described main lobe and accessory lobes are outer end and the inner of close described sharf respectively.
5. axial fan air-valve according to claim 4 is characterized in that, on described sharf bearing of trend, described main lobe and described accessory lobes are overlapped at least.
6. axial fan air-valve according to claim 3 is characterized in that, the outside of described main lobe is or/and extend to its reverse side direction deflection in the outside of accessory lobes.
7. axial fan air-valve according to claim 3 is characterized in that, in the air-valve full-gear, has predetermined distance between the vertical line by described blade center of gravity and the axis of described sharf.
8. according to any described axial fan air-valve of claim 1-7, it is characterized in that also comprise linking mechanism, described linking mechanism comprises elastic mechanism, pressure disk and a plurality of driving rocking handle; Described center base comprises central tube and guide rod, and described guide rod is arranged in central tube; A plurality of described sharfs the inner is passed the central tube barrel respectively, and links to each other with the outer end of the driving rocking handle that is positioned at central tube respectively, and the axis of sharf is departed from the inner of described driving rocking handle; Described pressure disk is enclosed within outside the guide rod, and described elastic mechanism two ends are supported on respectively on pressure disk and the guide rod, and described pressure disk compresses the inner of described driving rocking handle.
9. axial fan air-valve according to claim 8 is characterized in that, described guide rod comprises slide bar and the spring pressure pad that links to each other by screw-thread fit, and described elastic mechanism two ends are supported on respectively on pressure disk and the spring pressure pad.
10. according to any described axial fan air-valve of claim 1-7, it is characterized in that also comprise linking mechanism, described linking mechanism comprises gear ring and a plurality of driving wheel; Described center base comprises central tube; A plurality of described sharfs the inner is passed the central tube barrel respectively, and links to each other the dead in line of described driving wheel axis and described sharf respectively with the driving wheel that is positioned at central tube; Described gear ring meshes with described a plurality of driving wheels simultaneously.
11. an axial fan comprises blower fan body and impeller, described blower fan body forms exhaust outlet, it is characterized in that described exhaust outlet place is provided with each described axial fan air-valve of claim 1-10.
12. a cooling tower comprises cooling tower body and blower fan, it is characterized in that described blower fan is the described axial fan of claim 11.
13. an air-cooler comprises cooler body and blower fan, it is characterized in that, described blower fan is the described axial fan of claim 11.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010101788517A CN101832297B (en) | 2010-05-21 | 2010-05-21 | Axial flow fan and air valve thereof as well as cooling tower and air cooler |
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| Application Number | Priority Date | Filing Date | Title |
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| CN2010101788517A CN101832297B (en) | 2010-05-21 | 2010-05-21 | Axial flow fan and air valve thereof as well as cooling tower and air cooler |
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| CN101832297A true CN101832297A (en) | 2010-09-15 |
| CN101832297B CN101832297B (en) | 2012-07-18 |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103352859A (en) * | 2013-06-25 | 2013-10-16 | 上海易源节能科技有限公司 | Axial flow fan and air valve thereof |
| CN103498945A (en) * | 2013-10-21 | 2014-01-08 | 南京凯盛国际工程有限公司 | Automatic air flow adjusting valve |
| CN105179773A (en) * | 2015-08-24 | 2015-12-23 | 石磊 | Flow control valve |
| CN108916095A (en) * | 2018-08-24 | 2018-11-30 | 珠海格力电器股份有限公司 | Grid structure and air outlet equipment |
| CN111141029A (en) * | 2018-11-05 | 2020-05-12 | 宁波方太厨具有限公司 | Chimney anti-downdraft structure and gas water heater |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2362288A1 (en) * | 1976-08-18 | 1978-03-17 | Gebhardt Gmbh Wilhelm | VARIABLE STEP PROPELLER REGULATOR TO MODIFY THE AXIAL FLOW THROUGH FANS AND OTHER SIMILAR DEVICES |
| DE8507738U1 (en) * | 1985-03-15 | 1985-10-10 | Siemens AG, 1000 Berlin und 8000 München | Swirl regulator |
| EP0196450A1 (en) * | 1985-03-15 | 1986-10-08 | Siemens Aktiengesellschaft | Drag adjuster |
| FR2614369A1 (en) * | 1987-04-23 | 1988-10-28 | Tagnon Luc | Variable-pitch stator |
| EP0391006A1 (en) * | 1988-02-24 | 1990-10-10 | TAGNON, ClaudeJean-Marie | Air heater with a vertical axis |
| EP1974973A1 (en) * | 2007-03-30 | 2008-10-01 | Kunststoff Schwanden AG | Blind for motor vehicles |
| CN201753704U (en) * | 2010-05-21 | 2011-03-02 | 上海理工大学 | Axial flow fan and air valve, cooling tower and air cooler thereof |
-
2010
- 2010-05-21 CN CN2010101788517A patent/CN101832297B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2362288A1 (en) * | 1976-08-18 | 1978-03-17 | Gebhardt Gmbh Wilhelm | VARIABLE STEP PROPELLER REGULATOR TO MODIFY THE AXIAL FLOW THROUGH FANS AND OTHER SIMILAR DEVICES |
| DE8507738U1 (en) * | 1985-03-15 | 1985-10-10 | Siemens AG, 1000 Berlin und 8000 München | Swirl regulator |
| EP0196450A1 (en) * | 1985-03-15 | 1986-10-08 | Siemens Aktiengesellschaft | Drag adjuster |
| FR2614369A1 (en) * | 1987-04-23 | 1988-10-28 | Tagnon Luc | Variable-pitch stator |
| EP0391006A1 (en) * | 1988-02-24 | 1990-10-10 | TAGNON, ClaudeJean-Marie | Air heater with a vertical axis |
| EP1974973A1 (en) * | 2007-03-30 | 2008-10-01 | Kunststoff Schwanden AG | Blind for motor vehicles |
| CN201753704U (en) * | 2010-05-21 | 2011-03-02 | 上海理工大学 | Axial flow fan and air valve, cooling tower and air cooler thereof |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103352859A (en) * | 2013-06-25 | 2013-10-16 | 上海易源节能科技有限公司 | Axial flow fan and air valve thereof |
| CN103352859B (en) * | 2013-06-25 | 2015-10-21 | 上海艾客制冷科技有限公司 | A kind of axial-flow blower and air-valve thereof |
| CN103498945A (en) * | 2013-10-21 | 2014-01-08 | 南京凯盛国际工程有限公司 | Automatic air flow adjusting valve |
| CN105179773A (en) * | 2015-08-24 | 2015-12-23 | 石磊 | Flow control valve |
| CN108916095A (en) * | 2018-08-24 | 2018-11-30 | 珠海格力电器股份有限公司 | Grid structure and air outlet equipment |
| CN111141029A (en) * | 2018-11-05 | 2020-05-12 | 宁波方太厨具有限公司 | Chimney anti-downdraft structure and gas water heater |
Also Published As
| Publication number | Publication date |
|---|---|
| CN101832297B (en) | 2012-07-18 |
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Address after: 200093 Shanghai military road, Yangpu District, No. 516 Patentee after: University of Shanghai for Science and Technology Patentee after: SHANGHAI ACEC REFRIGERATION TECHNOLOGY CO., LTD. Address before: 200093 Shanghai military road, Yangpu District, No. 516 Patentee before: University of Shanghai for Science and Technology Patentee before: Shanghai Yiyuan Energy Saving Technology Co., Ltd. |
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Effective date of registration: 20160812 Address after: 200433, room 3, building 128, No. 104 Xiang Yin Road, Shanghai, Yangpu District Patentee after: SHANGHAI ACEC REFRIGERATION TECHNOLOGY CO., LTD. Address before: 200093 Shanghai military road, Yangpu District, No. 516 Patentee before: University of Shanghai for Science and Technology Patentee before: SHANGHAI ACEC REFRIGERATION TECHNOLOGY CO., LTD. |