CN105715584A

CN105715584A - Blade

Info

Publication number: CN105715584A
Application number: CN201510821041.1A
Authority: CN
Inventors: 丹尼尔·格伯特; 索斯滕·皮萨尔奇克; 奥利弗·哈弗; 埃哈德·格鲁伯
Original assignee: Ebm Papst Mulfingen GmbH and Co KG
Current assignee: Ebm Papst Mulfingen GmbH and Co KG
Priority date: 2014-12-17
Filing date: 2015-11-23
Publication date: 2016-06-29
Also published as: DE102015200361A1; DE202015100246U1

Abstract

The invention relates to a blade, and the blade is used for a fan impeller. In addition, the invention relates to a geometric shape of the blade in a tail region opposite to a hub. Moreover, the invention also relates to the fan impeller. According to the invention, the blade is provided with the tail region opposite to the hub. There is at least one rib in the tail region opposite to the hub, and the rib is provided with an external contour similar to a flow profile.

Description

A kind of blade

Technical field

The present invention relates to the blade of a kind of draught fan impeller, in particular it relates to a kind of side is towards the geometry of the blade of hub.The invention still further relates to a kind of draught fan impeller.

Background technology

On axial flow blower, the rotating shaft rotation direction of impeller is parallel or axially to airflow direction.On radial fan, the airflow direction of radial the phase outlet side of rotating shaft rotation direction of impeller.Blade-carrying impeller rotates around hub, thus transfers a gas medium.Particularly at internal impeller of blower modular manufacture in an equipment or the like and/or during installing, dangerous stress produces, and it may damaged blade.When draught fan impeller works, the air-flow around the gas medium of impeller of blower blade enters the axle being attached in fan hub by fan hub, produces the power being dissipated, and like this, draught fan impeller can be brought problem by the pressure produced due to centrifugal force.

Prior art is so to solve this problem.Such as, the wall thickness of the blade connecting hub and leaf area is increased.But so certainly will increasing the weight of draught fan impeller, this improves material consumption, cause that manufacturing cost increases.Draught fan impeller is typically made of a plastic, and increases wall thickness and can extend the manufacturing cycle of impeller, for instance, in the cooling procedure of thermoplastic spray casting, wall thickness has a quadratic effect.

Another is known can the method for reinforced blade be arrange a bead at the cross section of blade.So can also increase wall thickness.In addition United States Patent (USP) 5,066,196 proposes in the region that blade and wheel hub connect at least provided with a reinforcement.US publication application documents 2004/0013526A1 proposes to preset at least two muscle at the subzone of fan impeller blade simultaneously.

But, air-flow can be had a negative impact by these means increasing intensity.Work efficiency and operating noise can be had a negative impact by the air-flow separation in hub region.Additionally, when rotating shaft is in vertical position, particularly when axial flow type fan impeller remains static, liquid cannot be completely exhausted out.Water gathering in fan impeller blade can cause draught fan impeller uneven and frost damages, particularly in winter.

Summary of the invention

It is an object of the invention to provide a kind of blade for draught fan impeller, it, according to strength demand, materials'use and product produceability aspect, has the attribute of optimization, at least remain the attribute of air-flow, and operating noise and work efficiency will not be carried out technology compromise.

The feature of the fan impeller blade described in independent claims 1 can realize the purpose of the present invention.

Dependent claims 2 to 14 provides the feature improving blade further.

Further object is that a kind of draught fan impeller of offer, it, according to strength demand, materials'use and product produceability aspect, has the attribute of optimization, at least remains the attribute of air-flow, and operating noise and work efficiency will not be carried out technology compromise.

The feature of another draught fan impeller described in independent claims 15 can realize another object of the present invention.Dependent claims 16 and 17 provides the feature improving draught fan impeller further.

According to the present invention, a fan impeller blade, there is a stub area towards hub, blade is having at least a muscle towards the stub area of wheel whereby, and muscle has the external shape of similar flow profile whereby.Herein, the shape of leaf cross-section is referred to as term " flow profile ", because its special blade shape, and because air-flow creates the power of impacted object.Such as, this can be the plano-convex profile with convex first blade-side peace the second blade-side, or it can be the concavo-convex profile with convex first blade-side and recessed second blade-side.Here, leaf cross-section forms an external shape, and whereby in the region of muscle, outer layer forms the profile of external shape.Additionally, the blade of the present invention has at the bottom of a muscle, in the starting point towards the muscle in the stub area of hub, it is positioned at higher axial direction than at the bottom of the contrary muscle of the end at muscle.Therefore, being positioned at the bottom of the muscle of the end of muscle at the bottom of lower than the muscle of the starting point of the muscle in the stub area towards hub of flow direction.Therefore, the water of the blade of the fixing draught fan impeller of any impact can be discharged, especially when draught fan impeller is set to substantially rotating shaft vertical orientation, result as this setting, even if when ambient temperature is below the freezing point, ice cube is removed, and because of without producing imbalance and/or frost damage.

The present invention is based on one and is surprisingly found that, when similar for the external shape of muscle one-tenth flow profile, although the intensity of flow of carrying through muscle and blade profile improves, wherein medium fluid is interrupted on blade profile, but the air-flow through blade will not be had a negative impact by muscle.When medium fluid is interrupted for several times by the muscle on multiple blades on blade profile, this effect yet suffers from.But, muscle has booster action.Therefore, the blade of the present invention has the strength character of optimization, at least ensures mobile performance, and causes that the technology of noise and efficiency is traded off, and the wall thickness of blade will not increase whereby, has a negative impact thus without to consumption and the produceability of material.

In a preferred embodiment of blade of the present invention, the ratio between thickest and the maximum sectional thickness of blade of blade is 0.1 to 0.9, and wherein preferred ratio is 0.2 to 0.6.

The certified preferred embodiment of another one is, the ratio between thickness and the wall thickness of blade of muscle is 0.1 to 2, and wherein preferred ratio is between 0.5 to 1.5.

In another preferred embodiment of blade of the present invention, at the shoulder place of hub, the angular range that muscle is formed in radial direction is between-80 ° to+80 °, and wherein preferred scope is between-45 ° to+45 °.

The motion path of muscle can be designed to straight line.Or, it is also possible to it is designed to counterclockwise radially curvature movement to the left, or is designed to footpath curvature movement to the right clockwise.

In another preferred embodiment of blade of the present invention, muscle has an end solid in appearing areas, the end solid of muscle is designed to zigzag fashion whereby, whereby between end solid and the external shape of muscle formed angular range be 45 ° to+45 °, it is particularly preferred to range for 30 ° to+30 °.The design of such zigzag fashion makes the air-flow separating the end of muscle will not pass through from the flaunching part of muscle.

Additionally, another advantage is that of blade, having at least two muscle towards the blade end region of hub, two is 0.2 to 5 with the proportion between the space between muscle and the thickness of muscle whereby, it is particularly preferred to proportion be 0.5 to 1.5.In addition on one piece of blade, the thickness of all muscle can be identical, and for the same reason, and on blade, the space between a plurality of or all muscle can also be identical.But the size in independent muscle and space can also be different.

Draught fan impeller of the present invention at least includes a blade of the present invention.In addition this draught fan impeller can be axial flow type fan impeller, the impeller of radial fan impeller or other fan design.Here, it is impossible to this term of fan is done restriction and understands, and ventilation blower should be included, aerator, also include rotor and propeller, so that protection scope of the present invention extends to all of blade and draught fan impeller it is envisioned that the application that obtains.

Dependent claims, it is preferred that embodiment and accompanying drawing will be further described the more advantage of the present invention, feature and progressive part.In preferred embodiment, relate to axial flow type fan impeller, but limited understanding can not be done.The impeller of radial fan impeller or other draft types can also be construed to.

Accompanying drawing explanation

Fig. 1 is the top view of the axial flow type fan impeller of prior art；

Fig. 2 is the profile of the axial flow type fan impeller of prior art；

Fig. 3 is the profile of the first embodiment of the fan impeller blade of the axial flow type fan impeller of the present invention；

Fig. 4 is the profile of the second embodiment of the fan impeller blade of the axial flow type fan impeller of the present invention；

Fig. 5 is the profile of the 3rd embodiment of the fan impeller blade of the axial flow type fan impeller of the present invention；

Fig. 6 is the profile of the 4th embodiment of the fan impeller blade of the axial flow type fan impeller of the present invention；

Fig. 7 is the profile of the 5th embodiment of the fan impeller blade of the axial flow type fan impeller of the present invention；

Fig. 8 is the partial top view of the axial flow type fan impeller of the present invention.

Reference number list

100 draught fan impellers

110 take turns

120 blades

121 muscle

122 spaces

The end solid of 123 muscle

124 towards the blade end region of hub

125 first blade-side

126 second blade-side

127 first muscle sidewalls

128 second muscle sidewalls

A external structure

At the bottom of the muscle of P1 muscle starting point

At the bottom of the muscle of P2 muscle end

The maximum sectional thickness of t_max

T_w wall thickness

The thickness of b muscle

R radial direction

The width of s space L

The α gradient (zigzag)

β angle between the muscle and radial direction of shoulder place guiding wheel hub.

Detailed description of the invention

Fig. 1 is illustrated that the draught fan impeller 100 of prior art.Hub 110 is provided with 4 fan impeller blade 120.Having a muscle 121 in its region being connected with hub 110 in each fan impeller blade 120, muscle 121 is molded on hub 110 by same, and in mounted fan impeller blade 120.The centrifugal force produced in fan impeller blade 120 is transmitted in fan impeller blade 120 not only by connection, also can pass through muscle 121 and be transmitted on wheel 110.

Fig. 2 is illustrated that the partial sectional view of the draught fan impeller 100 identical with in Fig. 1.Wherein, in the region being connected with hub 110, fan impeller blade 120 is shown as profile type.The flow profile of fan impeller blade 120 has the second blade-side 126 of the first convexly curved blade-side 125 and plane.First blade-side 125 has a muscle 121, in the second blade-side 126, has two muscle 121 simultaneously.Muscle 121 is arranged in blade-side 125,126, and this has interrupted flow profile, and this can cause the efficiency that fluid is even worse in axial flow type fan impeller work process and the noise emission increased.

Fig. 3 is the profile of the first embodiment of the fan impeller blade 120 of the axial flow type fan impeller 100 of the present invention.Exterior contour A shows the first blade-side 125 of a convex and slightly concave second blade-side 126.In other words, the flow profile of fan impeller blade 120 is concavo-convex.In the second blade-side 126, there are 7 muscle 121, between muscle and muscle, form space 122.In addition showing the thickest t_w and maximum sectional thickness t_max of fan impeller blade 120, wherein the ratio between thickest t_w and maximum sectional thickness t_max is approximately 0.5.Additionally, also show the thickness b of muscle 121, wherein the ratio between thickness b and wall thickness t_w is approximately 0.63.Additionally, the width s in the space 122 displayed that in Fig. 3 between two muscle 121.Wherein the ratio between width s and thickness b is approximately 1.25.Such geometric proportion makes the exterior contour A of muscle 121 be flow profile.

Fig. 4 is the profile of the second embodiment of the fan impeller blade 120 of the axial flow type fan impeller 100 of the present invention.In the present embodiment, exterior contour A displays that the first blade-side 125 of a convex and slightly concave second blade-side 126.Second blade-side 126 has 3 muscle 121, between muscle and muscle, forms space 122.Additionally, there are 3 muscle 121 in the first blade-side 125 equally, between muscle and muscle, form space 122.Also show the thickest t_w of fan impeller blade 120 and maximum sectional thickness t_max in Fig. 4, wherein the ratio between thickest t_w and maximum sectional thickness t_max is approximately 0.4.Additionally, also show the thickness b of muscle 121, wherein the ratio between thickness b and wall thickness t_w is approximately 1.5.Additionally, the width s in the space 122 that also show in Fig. 4 between two muscle 121.Wherein the ratio between width s and thickness b is approximately 0.5.Such geometric proportion makes the similar flow profile of exterior contour A of muscle 121.

Fig. 5 is the profile of the 3rd embodiment of the fan impeller blade 120 of the axial flow type fan impeller 100 of the present invention.In the present embodiment, exterior contour A displays that the first blade-side 125 of a convex and slightly concave second blade-side 126.The same with in the first embodiment of Fig. 3, the second blade-side 126 has 7 muscle 121, between muscle and muscle, forms space 122.Muscle 121 has the first muscle sidewall 127 and the second vein sidewall 128, has an end solid 123 at muscle head.End solid 123 indentation, wherein, forms the angle of about 30 °, say, that form tangent plane with the surface profile of the second blade-side 126 between end solid 123 and the exterior contour A of muscle 121.In the present embodiment, the similar flow profile of external structure A of muscle 121.Because the contour shape of such a sawtooth, the air-flow that the end at muscle separates needs not move through the raised brim of muscle 121, and this is favorably improved work efficiency and reduces operating noise.

Fig. 6 is the profile of the 4th embodiment of the fan impeller blade 120 of the axial flow type fan impeller 100 of the present invention.In the present embodiment, exterior contour A displays that the first blade-side 125 of a convex and slightly concave second blade-side 126.The same with in the 3rd embodiment of the first embodiment of Fig. 3 and Fig. 5, the second blade-side 126 has 7 muscle, between muscle and muscle, forms space 122.Having the first muscle sidewall 127 and the second muscle sidewall 128 on muscle 121, wherein, muscle sidewall 127 and 128 converges at muscle head, and forms a saw-toothed profile.The inclination angle of one about 30 ° is formed, say, that with the plane tangent of the second blade-side 126 between first muscle sidewall and exterior contour A.In this embodiment, the ratio between the wall thickness t_w and the maximum sectional thickness t_max of fan impeller blade 120 of fan impeller blade 120 is about 0.5, it is preferred that range for 0.2 to 0.6.Additionally, the ratio between the thickness b and the wall thickness t_w of fan impeller blade 120 of muscle 121 is about 0.8, it is preferred that range for 0.5 to 1.5.Additionally, the ratio between the width s and the thickness b of muscle 121 in space 122 between two muscle 121 is approximately 1.0, it is preferred that range for 0.5 to 1.5.In the present embodiment, muscle 121 forms an exterior contour A, is similar to flow profile.Because such a jagged contour shape, the air-flow that the end at muscle separates needs not move through the raised brim of muscle 121, and this is favorably improved work efficiency and reduces operating noise.

Fig. 7 is the profile of the 5th embodiment of the fan impeller blade 120 of the axial flow type fan impeller 100 of the present invention.Fan impeller blade is made up of waveform profiles, and wherein, waveform formation exterior contour A is envelope wire, and exterior contour has been similarly formed a flow cross section.Here, profile waveform can be interpreted muscle 121 and the space 122 between muscle and muscle, also adopts these given solid proportionate relationships whereby in the present embodiment.

Fig. 8 is the partial top view of the axial flow type fan impeller 100 of the present invention.Merely illustrate a fan impeller blade 120 herein, on wheel 110, have multiple fan impeller blade 120 whereby, for instance four fan impeller blade 120.There are 9 muscle 121 in top view it can be seen that in fan impeller blade 120, between muscle and muscle 121, have ten spaces 122 whereby.Muscle 121 and radial direction r form the angle β of about 45 °, and radial direction, at the shoulder of fan impeller blade 120, guides to wheel hub 110.Muscle 121 continues counterclockwise to turn left from hub 110, and bends away from radial direction.In the starting point of muscle 121, fan impeller blade 120 connects P1 at the bottom of the muscle at wheel hub 110 place, than being oppositely arranged on P2 at the bottom of the muscle of muscle 121 end, has the axial direction of higher axial flow type fan impeller blade 120.Therefore, the flow direction that P1 at the bottom of the muscle of muscle 121 end looks at P2 at the bottom of the muscle of initiating terminal, connects wheel hub 110 in P2 place fan impeller blade 120 lower than muscle 121.Its result is, any water being likely to impact axial flow type fan impeller blade 120 can be discharged, especially when axial flow type fan impeller is set to substantially rotating shaft vertical orientation, result as this setting, even if when ambient temperature is below the freezing point, ice cube is removed, and because of without producing imbalance and/or frost damage.

The foregoing is only preferred embodiment of the present invention; not thereby restriction embodiments of the present invention and protection domain; to those skilled in the art; the equivalent replacement done by all utilizations description of the present invention and diagramatic content and the obtained scheme of apparent change should be can appreciate that, all should be included in the protection domain of invention.

Claims

1. the blade (120) for draught fan impeller (100), there is a stub area (124) towards wheel (110), it is characterized in that, described blade (120) is having at least a muscle (121) towards the stub area of wheel (110), muscle (121) has an exterior contour (A) whereby, it is similar to a flow profile, and at least one muscle described has at the bottom of a muscle (P1) in the starting point of muscle in the stub area towards wheel (110), and it has at the bottom of a muscle (P2) at the relative end of muscle (121), at the bottom of muscle, (P1) is positioned at than the axial direction higher at (P2) at the bottom of the end muscle of muscle (121) whereby.

2. blade according to claim 1 (120), it is characterized in that, the ratio between thickest (t_w) and the maximum sectional thickness (t_max) of blade (120) of blade (120) range for 0.1 to 0.9.

3. blade according to claim 2 (120), it is characterized in that, the ratio between thickest (t_w) and the maximum sectional thickness (t_max) of blade (120) of blade (120) range for 0.2 to 0.6.

4. according to the blade (120) one of aforementioned claim Suo Shu, it is characterized in that, the ratio between thickness (b) and the wall thickness (t_w) of described blade (120) of described muscle (121) range for 0.1 to 2.

5. blade according to claim 4 (120), it is characterised in that the ratio between thickness (b) and the wall thickness (t_w) of described blade (120) of described muscle (121) range for 0.5 to 1.5.

6. according to the blade (120) one of aforementioned claim Suo Shu, it is characterized in that, shoulder place at directive wheel (110), described muscle (121) and radial direction (r) shape () at an angle, the scope of angle () is between-80 ° to+80 °.

7. blade according to claim 6 (120), it is characterised in that described muscle (121) and radial direction (r) shape () at an angle, the scope of angle () is between-45 ° to+45 °.

8. the blade (120) according to claim 6 or 7, it is characterised in that the further route of described muscle (121) is designed to straight line.

9. the blade (120) according to claim 6 or 7, it is characterised in that the further route of described muscle (121) is designed to the counter clockwise direction motion of the left-end bent to radial direction (r).

10. the blade (120) according to claim 6 or 7, it is characterised in that the further route of described muscle (121) is designed to moving clockwise that the right-hand member of radial direction (r) bends.

11. according to the blade (120) one of aforementioned claim Suo Shu, it is characterized in that, described muscle (121) has an end solid (123) in the region of exterior contour (A), end solid (123) forms a zigzag fashion, forms one whereby and range for the angle () from 45 ° to+45 ° between end solid (123) and the exterior contour (A) of muscle (121).

12. blade according to claim 11 (120), it is characterized in that, form one between end solid (123) and the exterior contour (A) of described muscle (121) and range for the angle () from 30 ° to+30 °.

13. according to the blade (120) one of aforementioned claim Suo Shu, it is characterized in that, described blade (120) has at least two muscle (121) in the stub area towards wheel (110), between at least two muscle (121), have a space (122), the ratio between width (s) and the thickness (b) of a muscle (121) of space (122) range for 0.2 to 5.

14. blade according to claim 13 (120), it is characterized in that, blade (120) has at least two muscle (121) in the stub area towards wheel (110), between at least two muscle (121), have a space (122), the ratio between the thickness (b) of the width (s) in space and a muscle (121) range for 0.5 to 1.5.

15. a draught fan impeller (100), there is a hub (110), it is characterised in that draught fan impeller (100) has according at least one blade (120) one of aforementioned claim Suo Shu.

16. draught fan impeller according to claim 15 (100), it is characterised in that described draught fan impeller (100) is an axial flow type fan impeller.

17. draught fan impeller according to claim 15 (100), it is characterised in that described draught fan impeller (100) is radial fan impeller.