CN101487474B - Blower - Google Patents
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- CN101487474B CN101487474B CN 200910005626 CN200910005626A CN101487474B CN 101487474 B CN101487474 B CN 101487474B CN 200910005626 CN200910005626 CN 200910005626 CN 200910005626 A CN200910005626 A CN 200910005626A CN 101487474 B CN101487474 B CN 101487474B
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- impeller
- blower
- stream
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Abstract
The invention provides a vortex blower, which has high efficiency by improving the pressure of the blower and the cooling performance, and can simply the sealing structure. The blower comprising: a vane wheel (4) having a vane box(4a) of a circular groove using a pivoted axis(11) as the centre and a plurality of blades crossing through the circular groove in the circular groove of the vane box and divided into the segments in the circumferential direction, and a casing(5) including stationary flow paths facing to the grooves. In the blower, the plurality of blades are combined with the stationary flow paths, the flow-out side and the suction side arranged on each level of stationary flow paths are connected to guide the gas by a guiding flow path (9); the vane wheel is a cup-shaped vane wheel for secondary boostering having the vane box with semicircular or semi-elliptic section shape.
Description
The application is that the application number that proposed on May 29th, 2006 is dividing an application of 200610084684.3 application of the same name.
Technical field
The present invention relates to provide the technology of blower.
Background technique
In patent documentation 1～3, disclose multistage turbo-fan is arranged, structure as blower, what adopt in patent documentation 1 is to carry out first class boost with single impeller, and determine the structure of progression with the quantity of impeller, and be by the structure of impeller being studied improvement, being reduced the blade number with respect to progression in patent documentation 2.In addition, in patent documentation 3, disclose the impeller that a kind of 3D shape is arranged.
Patent documentation 1: Japanese Patent Publication 46-33856 communique
Patent documentation 2: No. 2084917 communique of Japan Patent
Patent documentation 3: No. 2680136 communique of Japan Patent
What Fig. 1 represented is the structure example of turbo-fan, and wherein, label 1 represents induction motor; Label 2 represents the rotatingshaft of induction motor; Label 3 represents the static stream of housing; Label 4 represents the impeller of turbo-fan, and the blade (label is 4b) of its blade box by impeller (label is 4a) and impeller is constituted; Label 5 represents housing; Label 6 represents the side cover of turbo-fan; Label 7 represents baffler.
For turbo-fan, it is characterized in that the height as the pressure coefficient ratio centrifugal blower of the nondimensional quantity of the merit of expression per unit impeller outer diameter, therefore, can be providing the air blast of high pressure with less impeller outer diameter or under identical impeller outer diameter condition with lower revolution under the identical revolution condition, so be widely used always.This turbo-fan is required to access higher pressure, as its corresponding structure, have at same rotatingshaft a plurality of impellers that are installed in series, the multistage structure in the operation stage of can repeated multiple times boosting.
By with the impeller multipolarity, make the external diameter or the raising revolution that do not need to increase impeller just can improve pressure, thus can make the blower miniaturization, and prolong the life-span of blower.In addition, under conditions of similarity, if increase impeller outer diameter, then air quantity can increase with the ratio of impeller outer diameter 3 powers, so the high-pressure trend of realizing by multilevel hierarchy can not increase air quantity and only improves pressure.
For the efficient that improves impeller and miniaturization and propose to improve the scheme of static pressure, as its shape, the impeller that 3D shape is arranged, the sectional shape of the blade box of impeller is made semicircle or half elliptic cup type, perhaps the sectional shape of blade box is the cup type, from the radial direction inclination predetermined angular centered by rotatingshaft blade is installed, further blade itself is made curve, with (patent documentations 3) such as raising pressure coefficients.
Shape by making blade is from the tilt angle of regulation of the radiation direction centered by rotatingshaft, make the pressure coefficient raising as the nondimensional quantity of the pressure of representing per unit impeller outer diameter, revolution, with general be not 5～11 relative with the pressure coefficient of the cup type impeller of the straight radial shape of angle, the pressure coefficient of described 3D shape impeller is 10～20.
In addition, the impeller shape of the blower that discloses for patent documentation shown in Figure 72, because the air-flow that boosts with each blade flows out towards centrifugal direction, so need the impeller outer circumferential side and static stream between constitute stream, make the maximum outside diameter of blower casing become big, therefore, in order to realize miniaturization and high efficiency, need improve blade shape.
And on the surface of an impeller with the back side constitutes two grade blades and the blade box carries out the impeller that secondary boosts, must seal the first order and partial air-flow, because the circumferential centrifugal direction of the impeller outer in the patent documentation 2 is open, so between the first order and the second level of impeller blade box periphery, projection must be set, to guarantee the length of sealing configuration, the sealing configuration 10 of at least three faces of the pattern of wants need to require the position of high-accuracy mechanical processing and higher assembly precision.Therefore, as above-mentioned the announcement, by a glass type is made in blade box cross section, surface and the back side at an impeller constitute two grade blades and blade box, make as shown in Figure 6, sealing configuration is lengthened, be easy to be formed on the planar sealing configuration between impeller periphery and the static ring-type stream.
In order to make impeller improve pressure, the pressure coefficient height of the 3D shape impeller that in patent documentation 3, discloses, be suitable for improving pressure, but, because blade bending in the mode that covers the blade box, so be difficult to utilize aluminium die casting etc. to carry out global formation, in addition, for surface and the back side at an impeller constitute two grade blades and blade box, make and need be divided into several different parts, so the fabricating cost of impeller uprises.Improve pressure with three-dimensional impeller, be that the entrance angle by making fluid flow into blade is that inflow angle shown in Figure 9 is carried out rectification, and utilize the outlet shape that the circumferencial direction component increase of the outlet velocity of fluid is realized.Therefore, for form can global formation shape, the pressure coefficient of centre that can become the 3D shape impeller of the impeller of the Inlet cone angle β 1 of Fig. 8, blade shown in Figure 10 and the cup type that axial Inlet cone angle γ and air-flow adapted, do not have crooked straight radial shape and patent documentation 3 is 11～16.
In addition, as the problem in realizing multistage turbo-fan, because compression at different levels is adiabatic compression, so compression ratio is subjected to the suction side Temperature Influence, exist if the problem that the temperature height then reduces.
The pressure of the situation of each grade adiabatic compression is represented with following formula (1):
P: absolute pressure
T: kelvin temperature
H
Th: the theoretical pressure head
η ad: adiabatic efficiency
R: gas constant
κ: specific heat ratio
G: gravity accleration
Subscript 1: before boosting (sucking a side)
Subscript 2: the back (flowing out a side) of boosting
According to above situation, even can be theoretic H
ThThe impeller of merit, with the preceding absolute temperature T of boosting
1Be inversely proportional to, if the temperature height, then pressure ratio reduces.
In addition, in the cycle of multistage adiabatic compression, if the fluid in the guiding stream of each inter-stage of cooling makes to flow into the preceding temperature T of boosting at different levels
1Reduce, then improve volumetric efficiency, as a whole near isothermal compression, also can make required drive than little with the one-level compression.
So the fluid that cools off in the guiding streams at different levels is important for improving pressure and raising the efficiency.As cooling means, generally be to adopt by the cooling fan cooling guiding stream outside is set, cool off the method at the fluid of intermediate flow., if adopt the method, then because fluid passes through in the guiding stream with higher speed, so the cooling fan cooling guiding stream outside guides the time of the fluid in the stream cooling flowing path short, the temperature difference is little, cooling fluid is not too effective.
So, can consider to utilize the method for the adiabatic expansion cooling of fluid.
Utilize adiabatic condition PV
κ=constant ... (2)
The equation of state PV=nRT of gas ... (3)
Utilize (2), (3) formula, TV
κ-1=constant ... (4)
V: volume
N: More (Mohr) constant
With described (4) formula, temperature reduces during expansion, and for example establishing expansivity is 1.5,
V
a/V
b＝1.5
With (3) formula, T
b=T
a(V
a/ V
b)
κ-1=0.85T
aSubscript a: (guiding stream inlet side) subscript b before the adiabatic expansion: after the adiabatic expansion (guiding flowing path outlet side), temperature reduces after the adiabatic expansion.In addition, low by the dilatant flow prompt drop, improved the heat transference efficiency in the guiding stream.
At last, carry out under the situation of first class boost at an impeller with patent documentation 1, if make the suction direction of impeller identical, then the thrust that produces because of the pressure reduction of the pressure in outside atmosphere and the impeller is equidirectional, the pressure of the part of boosting by impeller action to rotatingshaft, so must be can bearing thrust bearing structure.For head it off, change the pressure direction that acts on the impellers at different levels, offset the thrust that on live axle, produces because of pressure reduction generally.Surface and the back side at an impeller constitutes two grade blades and blade box, carry out in the impeller that secondary boosts, the thrust that produces when secondary is boosted reduces half, under multistage situation of boosting, as shown in figure 13, dispose the guiding stream by the direction that applies of considering thrust, and can be as shown in figure 14, it is 0 that thrust is offset.
Summary of the invention
Problem points for the above-described etc., its purpose are to provide a kind of blower of realizing high efficiency by the pressure higher than prior art, raising cooling performance.
Adopt following method in order to solve above-mentioned problem.Wherein, they can be made up more than two.
(1) with the impeller of an impeller realization secondary, the blade box sectional shape of impeller is made semicircle or half elliptic cup type, the blade shape that constitutes at impeller is rearward crooked with respect to sense of rotation.
(2) in blower, for connecting the guiding streams that are provided with at different levels, to the guiding stream of the suction port of next stage, with respect to static flowing path section area and outflow opening area, make guiding flowing path section enlarged areas at the outflow opening from static stream at different levels.
(3) in blower, the thrust that acts on the blower shaft is the summation that acts on the thrust on the impellers at different levels, and it reduces half or is 0.
(4) in the blower of described (1), the blade box is made the impeller of semicircle or half elliptic cup type, and the relative axle of shape that constitutes the blade of this impeller is radial configuration, constitutes straight line.
(5) in being connected of the machinery of the power that rotate such as motor and blower section, the final step-up side of blower section is connected on the driving device of the power that rotate such as described motor, and the cooling air that becomes driving device touches the structure of finally boost a side and the bearing part of blower section.
(6) at the driving device that the power that rotate such as above-mentioned motor are set and have under the situation of machinery of blower section, it constitutes: at driving device and the space portion that portion is set of the power that rotate such as above-mentioned motor, baffler is set, to be reduced in the noise that described blower portion produces.
Adopting these said structures, is the high efficiency that is conceived to realize comprising the pressure that improves blower, improves cooling performance etc., and the advantage of simplifying sealing configuration etc.
According to the present invention, because the improvement of formation etc. etc., and can provide Economy better blower.
Description of drawings
Fig. 1 is the explanatory drawing of the structure of expression single-stage turbo-fan.
Fig. 2 is the explanatory drawing as embodiment's a example of multistage turbo-fan structure.
Fig. 3 is the sectional view from the blower section of the A direction observation of multistage turbo-fan embodiment illustrated in fig. 2, is the explanatory drawing in the cross section of impeller and static stream and the housing that guides stream 9 formations.
Fig. 4 is to use the impeller that uses and the dynamic explanatory drawing of the air-flow on impeller in embodiment's multistage turbo-fan.
Fig. 5 is the sectional view of observing from the C direction of impeller shown in Figure 4, also constitutes the explanatory drawing of blade box and blade at opposing face.
Fig. 6 observes the impeller that uses from the C direction of Fig. 4 embodiment's multistage turbo-fan, schematically illustrate the explanatory drawing of its cross section model.
Fig. 7 is from observing the impeller that uses with Fig. 6 equidirectional multistage turbo-fan, being used for the variform cross section model that schematically illustrates it of expression and Fig. 6.
Fig. 8 is the enlarged view of observing the blade-section of impeller shown in Figure 4 from the D direction.
Fig. 9 is from the figure of blade shape shown in Figure 8 physically is described.
Figure 10 is from the figure of the blade shape of observing from the E direction of Fig. 8 physically is described.
Figure 11 is the sectional view from the blower section of the B direction observation of multistage turbo-fan embodiment illustrated in fig. 2, is the explanatory drawing in the cross section of impeller and static stream and the housing that guides stream 9 formations.
Figure 12 is the figure that uses in embodiment's explanation, and the sectional view of the blower section of observing from the A direction of multistage turbo-fan embodiment illustrated in fig. 2 is the explanatory drawing in the cross section of the housing that constitutes of impeller and static stream and guiding stream.
Figure 13 observes the impeller that uses from the C direction of Fig. 4 embodiment's multistage turbo-fan, schematically illustrate the explanatory drawing of its cross section model.
Figure 14 is the figure that Figure 13 is described physically.
Figure 15 is the figure that uses in the explanation of embodiments of the invention, is to observe the impeller that uses from the C direction of Fig. 4 embodiment's multistage turbo-fan, schematically illustrates the explanatory drawing of its cross section model.
Figure 16 is the figure that uses in embodiment's explanation, and the blade box is made semicircle or half elliptic cup type, and the relative axle of shape that constitutes the blade of its impeller is the explanatory drawing of radial configuration.
Figure 17 constitutes the sectional view of the embodiment under the situation of final voltage-boosting stage and outflow opening in motor one side.
Figure 18 is the sectional view that is illustrated in configuration baffler situation under the situation of Fig. 2.
Embodiment
Describe being used for implementing best mode of the present invention.
Below, utilize accompanying drawing that the blower structure of the embodiment of the invention is elaborated.
Embodiment 1 is described.Fig. 2 represents that two impellers by the multistage turbo-fan structure of present embodiment carry out an example under 4 grades of situations of boosting.Fig. 3 is the sectional view from the blower section of the A direction observation of Fig. 2, the cross section of the impeller that expression is made of blade 4b and blade box 4a, static stream 3 and guiding stream 9.In the embodiment that Fig. 2 represents, because the multipolarity of a plurality of impellers makes rotatingshaft 11 elongated, form by power transfering parts such as coupling and connect structure as the rotatingshaft 11 of the motor 1 of power source and blower.As long as the intensity of axle is enough, also can directly be connected with motor reel and driven.In addition, drive portion is not only motor 1, also can with other rotary machine combination such as motor.And impeller as shown in Figure 3, blade 4b and blade box 4a in that surface and the back side of an impeller constitute secondary carry out secondary to boost, with the periphery of impeller and the sealing configuration of a face of housing formation.Fluid after at different levels boosting is directed into next stage by guiding stream 9, and is further boosted.For this multistage formation, till from one-level to level Four, sequentially be directed under the situation of stream 9 connections, the surface of an impeller and the back side constitute the first order and the second level, because the direction of the power of the thrust that produces with the pressure reduction of outside atmosphere reduces half mutually on the contrary, so act on half that the summation of the thrust on the rotatingshaft 11 becomes power that the pressure that boosts because of blower produces.
Fig. 4 is the impeller that uses in embodiment's multistage turbo-fan, and Fig. 5 is the sectional view of observing from the C direction of impeller shown in Figure 4.Fig. 6 is the enlarged view of observing from the C direction of Fig. 4, and Figure 10 schematically illustrates the blade 4b shape of observing from the E direction of Fig. 8.As shown in Figure 4, the blade box 4a of impeller makes semicircle or half elliptic cup type, as shown in Figure 5, has adopted the blade 4b and the blade box 4a that constitute secondary at surface and the back side of an impeller, carries out the structure that secondary boosts.At this moment, the configuration of the first order, partial blade 4b, the phase place that formation will be staggered by the interval between entrance and exit is interfered by the pressure that produces during the pressure difference largest portion between static stream entrance 13 (suction port) 13 and outlet (outflow opening) 14 and is reduced sound for reducing blade 4b.As shown in Figure 8, the blade 4b of impeller is crooked backward with respect to sense of rotation, and Inlet cone angle β 1 is the angle that is fit to the regulation of fluid inflow with respect to the vertical surface of rotatingshaft 11.As shown in figure 10, the entrance shape of blade 4b is also to tilt with respect to axially being adapted at axially going up the mode that flows into angle.
Figure 11 is the sectional view from the blower section of the B direction observation of multistage turbo-fan embodiment illustrated in fig. 2, Figure 12 is the sectional view from the blower section of the A direction observation of multistage turbo-fan embodiment illustrated in fig. 2, be the housing cross section that impeller and static stream and guiding stream 9 constitute, also expression is arranged on the cross section of the cooling fan between the second level and the third level.Figure 11 is illustrated in the secondary structure at the surface of an impeller and the back side, fluid after the first order is boosted is directed to the shape of partial guiding stream 9, and Figure 12 represents to be directed to from the second level shape of the guiding stream 9 of the third level that constitutes at another impeller.Both sides' guiding stream 9 all constitutes: the section area of guiding stream 9 is all big with the outflow opening area that is connected on the guiding stream 9 than static flowing path section area, as illustrated in above-mentioned " summary of the invention ", static stream with respect to front and back, the cross section that connects guiding stream 9 at different levels is enlarged, utilize adiabatic expansion, make by the fluid temperature (F.T.) behind the guiding stream 9 and reduce, prevent from reducing in the pressure ratio of next stage.In addition, by cause the deceleration of fluid because of expansion, make that the heat transfer time in guiding stream 9 is elongated, thereby can more effectively cool off with cooling fan.Therefore can improve cooling effect.
Figure 13, the 14th, it is the additional embodiments of 0 structure that expression makes the summation that acts on the thrust on the blower rotatingshaft 11.In Figure 13, at two impeller intermediate configurations motor 1, utilize the configuration of guiding stream 9, making thrust is 0.In addition, in this embodiment, owing to rotatingshaft 11 shortens, so be easy to constitute the multistage turbo-fan that directly is connected on the motor reel.Embodiment with Fig. 2 in Figure 14 is identical, and motor 1 is configured in the opposite side of multistage blowers portion, utilizes the configuration of guiding stream 9, and making thrust is 0.
Figure 16 represents to change another embodiment under the situation of impeller shape.In Figure 16, with constituting the shape of blade 4b that blade box 4a be the impeller of cup type, be arranged in relative and be radial.
Be illustrated by above embodiment, and the blower of other mode of executions 1 of the present invention, the impeller and the housing that comprise turbo-fan, wherein, described impeller comprises: have the blade box of the annular slot centered by rotatingshaft and cross this annular slot in the annular slot of this blade box, the a plurality of blades that are divided into section at circumferencial direction, described housing is provided with the static stream in the face of described annular slot, in the blower that constitutes like this, combination to a plurality of described impellers and static stream is connected, and the outflow opening that will be arranged on the static streams at different levels by the guiding stream is connected to come steering flow with suction port; Each impeller carries out secondary with one and boosts, and, be the impeller that the sectional shape of blade box is made semicircle or half elliptic cup type.
The blower of other mode of executions 2 of the present invention, for described impeller, the blade shape that constitutes this impeller is rearward crooked with respect to sense of rotation.
The blower of other mode of executions 3 of the present invention, for described impeller, the blade shape that constitutes this impeller is radial arrangement with respect to rotatingshaft, and is straight line.
The blower of other mode of executions 4 of the present invention, above-mentioned blade are configured to the phase place that staggers by the intervals at different levels between the entrance and exit.
The blower of other mode of executions 5 of the present invention, the impeller and the housing that comprise turbo-fan, wherein, described impeller comprises: have the blade box of the annular slot centered by rotatingshaft and cross this annular slot in the annular slot of this blade box, the a plurality of blades that are divided into section at circumferencial direction, described housing is provided with the static stream in the face of described annular slot, in the blower that constitutes like this, the suction port of guiding stream from the outflow opening on the static streams at different levels to next stage that is used for the connection of level and arranges, with respect to static flowing path section area and outflow opening area, will guide the flowing path section enlarged areas.
The blower of other mode of executions 6 of the present invention, above-mentioned blade are configured to the phase place that staggers by the intervals at different levels between the entrance and exit.
The blower of other mode of executions 7 of the present invention, the impeller and the housing that comprise turbo-fan, wherein, described impeller comprises: have the blade box of the annular slot centered by rotatingshaft and cross this annular slot in the annular slot of this blade box, the a plurality of blades that are divided into section at circumferencial direction, described housing is provided with the static stream in the face of described annular slot, simultaneously, combination to a plurality of described impellers and static stream is connected, to be arranged on the structure that outflow opening and suction port on the static stream at different levels is connected to come steering flow by the guiding stream, wherein, in the blower that boosts that carries out more than the level Four, the thrust that acts on the blower rotatingshaft is the summation that acts on the thrust on the impellers at different levels, and it becomes below half.
The blower of other mode of executions 8 of the present invention, the thrust that acts on the blower rotatingshaft is the summation that acts on the thrust on the impeller at different levels, it reduces half.
The blower of other mode of executions 9 of the present invention, the thrust that acts on the blower rotatingshaft is the summation that acts on the thrust on the impeller at different levels, it is inoperative.
In addition, Figure 17 represents other embodiments of the invention.
Figure 17 carries out example under the situation that level Four boosts with two impellers, is the figure of section constitution of structure of the multistage turbo-fan of explanation present embodiment, and Figure 18 is the formation that is illustrated in the situation lower section of Fig. 2.
In Figure 17, from the rotatory force of motor 1, be delivered to blower portion 15 by power transfering part 12.Be with the difference of Figure 18: in Figure 17, joint one side at motor 1 and blower 15 disposes the final voltage-boosting stage 53 of blower portion 15, to constitute by fluid 58 mode that 1 one effluents go out from outflow opening to motor in the blower portion.The suction port 55 of blower portion 15 and the voltage-boosting stage of the first order are arranged on the power transfering part 12 opposite sides with motor 1 and blower portion 15.
As shown in figure 17, opposite side at the live axle of motor 1, be provided with the cooling fan 51 of motor 1, it constitutes the shell that not only can arrive motor 1 from the cooling air 57 of fan 51, and can reach power transfering part 12, load side bearing portion, the final voltage-boosting stage 53 of blower portion 15, outflow opening 52, therefore can cool off by the air cooling of cooling air 57.
Utilize the rotatory force of motor 1, rotate by blower portion 15, the suction port 55 suction gases from blower portion through impeller 4, static guiding stream 9, boost at each voltage-boosting stage, from outflow opening 52 outputs.
In this process, because turbo-fan utilizes the frictional force of fluid, that carries out rotating in impeller 4 boosts, so the temperature at the fluid 58 of blower inside raises significantly, the temperature of final voltage-boosting stage and the temperature of load side bearing 54 raise significantly, the lubricating grease lifetime of bearing 54 reduces because the high temperature of housing 5 causes the strength of materials.
In addition, under the situation of the combination of multistage connection impeller and static stream, owing to support and make the rotatingshaft of blower of a plurality of wheel rotation elongated, therefore, sometimes can be by the power transfering part of coupling etc., be connected with the live axle of the driving device of motor etc.
In this case, become high temperature based on the blower portion of housing 5, create a difference as the live axle of the rotatingshaft of blower portion, driving device, the expansivity that connects both relative temperatures such as power transfering part, just might become problem.For fear of this problem, the complexity of the dimensional accuracy of requirement each several part, configuration, bindiny mechanism, formation etc. when it is contemplated that design.
In contrast, by adopting the structure of Figure 17, be cooled by fan 51 around the final voltage-boosting stage 53 of blower portion 15, outflow opening 52 and the load side bearing 54, can improve the cooling performance of final voltage-boosting stage 53 and load side bearing 54, can solve described problem points etc.According to this structure, special-purpose cooling fan can be set in addition and utilize the cooling air 57 of motor 1.
In addition, the temperature of present embodiment reduces, because the T1 of described formula (1) reduction, so pressure ratio P2/P1 increases.In other words, compare with the formation of prior art, the temperature of bringing because of the formation that adopts present embodiment reduces, and has improved pressure ratio.
In addition, in the structure of Figure 17, because compared with the existing, can make the position of the outflow opening 52 of blower portion 15 and baffler 56 more approaching, so compared with the existing, connecting the outflow opening 52 of blower portion 15 and the piping length of baffler 56 can shorten.Length as this pipe arrangement shortens, and compared with the existing, can be reduced in the drag losses that the pipe arrangement inwall produces, and more is conducive to improve the efficient of machinery.
But, baffler 56 is being arranged under the situation of suction port 55, also can baffler be set at motor shown in Figure 17 1 and the space portion that arranges between the portion.
As described above baffler 56 is arranged on motor 1 and the space portion that portion is set, use the cooling air from fan 51 to cool off by air, can cool off baffler 56, as the temperature that can make baffler 56 temperature range in certain regulation, can implement to reduce the noise that described blower portion produces sometimes effectively.What account for very big weight in the sound that is produced by the blower with impeller is the pressure disturbances sound that frequency that the number of blade and revolution by impeller 4 multiply each other produces, and eliminate this characteristic frequency sound, and the resonance type baffler that utilizes the length of wavelength is effective.As previously mentioned, temperature rises significantly under the situation of turbo-fan, the pressure difference that this external cause uses, and the length of wavelength changes, and the effect of resonance type baffler reduces.As previously mentioned, as can making the length change of described wavelength in certain scope in the scope of baffler 56 cooling duct set points of temperature, can keep certain to the reduction noise result of resonance type baffler.
In the embodiment of above-mentioned Figure 17, figured and illustrated that blower portion 15 is the combinations that connect a plurality of impellers and static stream, even primary structure is fine certainly in enforcement of the present invention.
According to the embodiment based on the present invention, in having the multistage turbo-fan that carries out the impeller that secondary boosts with an impeller, pressure by improving blower can be provided, improve cooling performance etc. and realize high efficiency and the multistage turbo-fan of simplifying sealing configuration.
Claims (8)
1. a blower is characterized in that, comprising:
The impeller of turbo-fan and housing,
The impeller of described turbo-fan comprises: have the blade box of the annular slot centered by rotatingshaft and cross this annular slot in the annular slot of this blade box, be divided into the multi-disc blade of section at circumferencial direction, and described housing is provided with the static stream in the face of described annular slot, wherein
Combination to a plurality of described impellers and static stream is connected,
Be by the guiding stream, the outflow opening that is arranged on the static stream at different levels be connected with suction port, with the structure of steering flow;
The sectional area of described guiding stream, than the sectional area of described static stream and to be connected the area of the outflow opening on the guiding stream big,
Each impeller carries out secondary and boosts at blade and blade box that surface and the back side of an impeller constitute secondary, and the sectional shape of blade box is formed semicircle or half elliptic cup type,
The suction port of guiding stream from the outflow opening on the static stream at different levels to next stage that is used for the connection of level and arranges with respect to static flowing path section area and outflow opening area, will guide the flowing path section enlarged areas.
2. blower as claimed in claim 1 is characterized in that:
In described impeller, the shape of blade that constitutes this impeller is rearward crooked with respect to sense of rotation.
3. blower as claimed in claim 1 is characterized in that:
In described impeller, the shape that constitutes the blade of this impeller relatively rotates axle and is radial arrangement, and is straight line.
4. blower as claimed in claim 1 is characterized in that:
Described blade is configured to the phase place that staggers by the interval at different levels between the entrance and exit of described static stream.
5. blower as claimed in claim 1 is characterized in that:
The suction port of guiding stream from the outflow opening on the static stream at different levels to next stage that is used for the connection of level and arranges with respect to static flowing path section area and outflow opening area, will guide the flowing path section enlarged areas;
Described blade is configured to the phase place that staggers by the interval at different levels between the entrance and exit of described static stream.
6. a blower is characterized in that, comprising:
The impeller of turbo-fan and housing,
The impeller of described turbo-fan comprises: have the blade box of the annular slot centered by rotatingshaft and cross this annular slot in the annular slot of this blade box, be divided into the multi-disc blade of section at circumferencial direction, and described housing is provided with the static stream in the face of described annular slot
Simultaneously, the combination of a plurality of described impellers and static stream is connected,
Be by the guiding stream, the outflow side that is arranged on the static stream at different levels is connected with the suction side, with the structure of steering flow, wherein,
The surface of an impeller and the back side constitute blade and the blade box of secondary, carrying out secondary boosts, impeller periphery and housing constitute the sealing configuration of a face, fluid after at different levels boosting is directed into next stage by described guiding stream, further boosted, carry out thus in the above blower that boosts of level Four
The sectional area of described guiding stream, than the sectional area of described static stream and to be connected the area of the outflow opening on the guiding stream big,
Because the direction of the power of the thrust that produces with the pressure reduction of outside atmosphere is opposite, the thrust that acts on the blower rotatingshaft is the summation that acts on the thrust on the impeller at different levels, and it becomes below half of power that pressure that blower boosts produces.
7. blower as claimed in claim 6 is characterized in that:
The thrust that acts on the blower rotatingshaft is the summation that acts on the thrust on the impeller at different levels, half of the power that the pressure that its minimizing blower boosts produces.
8. blower as claimed in claim 6 is characterized in that:
The thrust that acts on the blower rotatingshaft is the summation that acts on the thrust on the impeller at different levels, considers that the direction that applies of thrust disposes described guiding stream, makes that the thrust that acts on the blower rotatingshaft is inoperative.
Applications Claiming Priority (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2005156305 | 2005-05-27 | ||
| JP2005156305 | 2005-05-27 | ||
| JP2005-156305 | 2005-05-27 | ||
| JP2005341366 | 2005-11-28 | ||
| JP2005341366A JP4671844B2 (en) | 2005-05-27 | 2005-11-28 | Blower |
| JP2005-341366 | 2005-11-28 |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2006100846843A Division CN1869449B (en) | 2005-05-27 | 2006-05-29 | Blower |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101487474A CN101487474A (en) | 2009-07-22 |
| CN101487474B true CN101487474B (en) | 2013-07-10 |
Family
ID=37443196
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200910005626 Expired - Fee Related CN101487474B (en) | 2005-05-27 | 2006-05-29 | Blower |
| CN2006100846843A Expired - Fee Related CN1869449B (en) | 2005-05-27 | 2006-05-29 | Blower |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2006100846843A Expired - Fee Related CN1869449B (en) | 2005-05-27 | 2006-05-29 | Blower |
Country Status (1)
| Country | Link |
|---|---|
| CN (2) | CN101487474B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2931214B1 (en) * | 2008-05-15 | 2013-07-26 | Turbomeca | COMPRESSOR WHEEL BLADE WITH EVOLVING CONNECTION |
| CN107044434B (en) * | 2017-05-09 | 2019-01-22 | 福建东亚环保科技股份有限公司 | A kind of minitype high voltage centrifugal blower |
| CN212318344U (en) * | 2020-09-23 | 2021-01-08 | 台州瑞晶机电有限公司 | Impeller and vortex type air pump |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2193448Y (en) * | 1994-06-21 | 1995-03-29 | 吴加兴 | Swirl pump |
| CN2490338Y (en) * | 2001-07-23 | 2002-05-08 | 井得江 | Centfifugal blowing machine set |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2105580U (en) * | 1991-07-06 | 1992-05-27 | 上海交通大学 | High-temp. axial-flow fan |
| CN2527751Y (en) * | 2001-04-26 | 2002-12-25 | 李明贤 | Superhigh speed multistage centrifugal blower |
| CN2651489Y (en) * | 2003-10-31 | 2004-10-27 | 黄伟文 | Middle pressure draught fan |
-
2006
- 2006-05-29 CN CN 200910005626 patent/CN101487474B/en not_active Expired - Fee Related
- 2006-05-29 CN CN2006100846843A patent/CN1869449B/en not_active Expired - Fee Related
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2193448Y (en) * | 1994-06-21 | 1995-03-29 | 吴加兴 | Swirl pump |
| CN2490338Y (en) * | 2001-07-23 | 2002-05-08 | 井得江 | Centfifugal blowing machine set |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1869449B (en) | 2011-06-08 |
| CN101487474A (en) | 2009-07-22 |
| CN1869449A (en) | 2006-11-29 |
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