EP3114354B1 - Roue de ventilateur pour ventilateur axial - Google Patents

Roue de ventilateur pour ventilateur axial Download PDF

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Publication number
EP3114354B1
EP3114354B1 EP15706434.6A EP15706434A EP3114354B1 EP 3114354 B1 EP3114354 B1 EP 3114354B1 EP 15706434 A EP15706434 A EP 15706434A EP 3114354 B1 EP3114354 B1 EP 3114354B1
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EP
European Patent Office
Prior art keywords
blade
ramp
fan wheel
web
blades
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP15706434.6A
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German (de)
English (en)
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EP3114354A1 (fr
Inventor
Stephanie Larpent
Uwe Blass
Nikolaus Zipf
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mahle Behr GmbH and Co KG
Original Assignee
Mahle Behr GmbH and Co KG
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Publication of EP3114354A1 publication Critical patent/EP3114354A1/fr
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Publication of EP3114354B1 publication Critical patent/EP3114354B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/325—Rotors specially for elastic fluids for axial flow pumps for axial flow fans
    • F04D29/329—Details of the hub
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/38—Blades
    • F04D29/384—Blades characterised by form

Definitions

  • the present invention relates to a fan wheel for an axial fan for generating a cooling air flow through a heat exchanger of a vehicle, with the features of the preamble of claim 1.
  • the invention also relates to an axial fan equipped with such a fan wheel.
  • a fan wheel is known. It comprises a hub and a plurality of blades, each of which is connected to the hub at a blade root.
  • the blades each have a blade body, which can also be referred to as an airfoil.
  • the blade body has a front side on a suction side of the fan wheel and a rear side on a pressure side of the fan wheel. Furthermore, the blade body has a leading edge and a trailing edge.
  • the blade body is usually curved convexly on its front side, that is to say on the suction side, while on its rear side it is complementarily curved concavely on the suction side.
  • All blades of the fan wheel have a ramp on the pressure side which protrudes from the rear of the respective blade body and which starts from an initial area in which the blade root and the leading edge of the respective blade are located.
  • the respective ramp then extends from this initial region in the direction of the trailing edge and in the direction of the blade tip of the respective blade.
  • Such a ramp ensures an improved flow around the blade root in the area of the hub.
  • the respective ramp extends over approximately 50% of a blade length measured radially from the blade root to the blade tip.
  • Similar fan wheels are also from the DE 26 19 318 A1 and from the WO 01/79704 A2 known.
  • This backflow is displaced radially with the aid of the ramps arranged on the pressure side and brought together with a main flow in an end region of the ramps, which is arranged distal to the hub, which is conveyed by the blades essentially in the axial direction.
  • the axial direction runs parallel to the axis of rotation of the fan wheel.
  • the end region of the respective ramp can be found approximately in a radially inner third of the blade length, that is to say essentially proximal to the respective blade root.
  • the present invention deals with the problem of specifying an improved embodiment for a fan wheel of the aforementioned type or for an axial fan equipped with it, which is characterized in particular by an improved energy efficiency.
  • the invention is based on the general idea of moving the end region of the respective ramp radially outward in comparison to known fan wheels, in such a way that the respective ramp extends over more than 75% of the blade length.
  • the invention uses the knowledge that the main flow conveyed by the fan wheel has different main flow directions depending on the radial position along the blades.
  • the main flow direction in the area of the blade roots is approximately axial, while it has an essentially diagonal orientation in the area of the blade tips, in other words, in the area of the blade tips, an axial component and a radial component of the main flow direction are approximately the same size.
  • the main flow direction in the area of the blade tips can be oriented largely radially.
  • the main flow direction in the area of the blade tips has a significantly larger radial component than in the area of the blade feet.
  • the ramps in the conventional design end in the inner third of the blade length, there is a large difference in direction at the transition between the return flow and the main flow, as a result of which the radial return flow must be deflected comparatively strongly into the axial direction. A comparatively large amount of energy is lost here.
  • the end region of the ramps radially outward the backflow is introduced into the main flow in a region further away from the hub, in which the main flow already has a significant radial component.
  • the fan wheel according to the invention has an improved efficiency in the operation of the axial fan.
  • the improved efficiency can be used to promote a larger flow of cooling air.
  • the improved efficiency can be used to make the fan wheel or the entire axial fan smaller and lighter with the same performance. It is clear that the improved efficiency can also be used for any combination of the above options.
  • the ramp In addition to the improved return of the return flow to the main flow, the ramp also has an additional effect.
  • On the pressure side of the respective blade it acts like a type of spoiler, which deflects the flow guided by the leading edge of the blade body along the rear of the blade body in the circumferential direction. This means an increased pressure build-up for the pressure side of the fan wheel, which also improves the efficiency of the fan wheel.
  • This spoiler that is to say the ramp, can be positioned radially outwards, the stronger the pressure-building effect, since the peripheral speeds of the blades are higher radially on the outside when the fan wheel is in operation.
  • the respective ramp can extend essentially over the entire blade length according to an advantageous embodiment.
  • the expression “essentially” is to be understood in such a way that the respective ramp extends at least over 90% of the blade length. It is also conceivable that the respective ramp extends over the entire length of the blade. As stated above, the further the return flow can be directed radially outwards, the more the efficiency improves before it meets the main flow. However, there may be other reasons for not providing the ramp in full along the entire blade length. Manufacturing-related restrictions and / or stability requirements are conceivable, for example. It is also conceivable that a ramp that extends completely over the entire length of the blade or that extends to the tip of the blade can lead to noise.
  • At least one channel open to the pressure side can be formed between the ramp and the trailing edge of the blade body.
  • Such a channel causes the return flow to be channeled along the ramp, as a result of which the return flow is guided from radially inside to radially outside.
  • the respective channel is located on the outflow side of the respective ramp and on the back of the respective blade body. Since the respective channel is open on the pressure side, the backflow can easily enter the channel.
  • At least one such channel can extend to a radially outer end of the ramp.
  • the return flow in the respective channel is thus guided to the outer end of the ramp, which improves a controlled return of the return flow into the main flow.
  • the ramp is arranged at a distance from the starting area to its end in the circumferential direction to the trailing edge of the blade body.
  • the outer end of the ramp can be designed to be radially closed.
  • the outer end of the ramp can be located directly on the trailing edge of the blade body.
  • at least one such channel is open radially on the outside.
  • the ramp ends free-standing radially on the outside, whereby the channel extending to the outer end of the ramp is radially open.
  • the ramp has a crossbar at its outer end, which connects the ramp to the trailing edge. In order to open the channel ending at the crosspiece radially, a corresponding opening can then be formed in this crosspiece.
  • At least one such radially open channel can be configured as a diffuser in a radially outer outlet area.
  • a diffuser of this type is characterized in that its cross-section through which flow can flow first decreases in the direction of flow and then increases again. With the aid of such a diffuser, the flow velocity of the backflow conducted in the respective channel can be reduced, which simplifies the deflection of the backflow in the main flow and accordingly requires less energy.
  • a plurality of channels can be arranged parallel to one another on the respective blade, adjacent channels being separated from one another by a common separating web which protrudes from the blade body between the ramp and the trailing edge on the rear side.
  • the ramp can be concavely curved toward the leading edge. It has been shown that such a concave curvature on the inflow side is particularly expedient in order to improve the pressure increase on the pressure side on the one hand and to improve the flow guidance of the return flow on the other hand.
  • an outflow edge of the ramp distal to the blade body along the ramp can lie essentially in an exit plane running perpendicular to the axis of rotation of the fan wheel.
  • the trailing edges of the blade bodies can also lie in this exit plane.
  • the ramp can have an outflow edge which is distal to the blade body and has at least one section which extends along the ramp and is spaced apart from an exit plane running perpendicular to the axis of rotation of the fan wheel.
  • the outflow edge in said section is spaced toward the suction side from the exit plane, as a result of which the ramp has a reduced overall height or ramp height in relation to the blade body in said section.
  • Such a section with a reduced ramp height can be located in a radially outer half, preferably in a radially outer third, or in a radially inner half, preferably in a radially inner third, of the ramp length measured in the longitudinal direction of the blade.
  • Such sections with a reduced ramp height enable the flows from the pressure and suction sides to be brought together better, which can be used to increase the efficiency.
  • the ramp can extend into an end region in which the trailing edge and the blade tip are located, wherein the blade body is arched outwards in this end region towards the suction side in relation to the rest of the front side.
  • the suction-side contour of the blade body is varied in order to improve the transition between the backflow and the main flow.
  • the ramp enables a certain decoupling between the suction-side contour of the blades defined by the front of the blade body and the pressure-side contour of the blades, which is determined from the leading edge to the ramp by the back of the respective blade body and by the ramp.
  • a suitable choice of the geometry of the ramp can thus be used to influence the geometry and thus the aerodynamic effect of the pressure side of the respective blade without impairing the geometry or aerodynamics of the suction side of the blade.
  • the respective blade and thus the entire fan wheel remain relatively easy to manufacture.
  • At least one such channel can extend into said end region, in which the section of the blade body that is curved outwards is located. The return flow can thus be returned in a targeted manner in this end region.
  • the respective ramp begins at the blade root and / or at the hub. This ensures that the backflow can be essentially completely recorded.
  • the respective ramp is preferably formed integrally on the respective blade body. As a rule, it is a one-piece injection molded part.
  • the blades are preferably integrally formed on the hub. In particular, it is an injection molded part produced in one piece.
  • the fan wheel can be equipped with a fan ring which extends closed in the circumferential direction and which connects the blade tips of the blades to one another.
  • a fan ring can significantly improve the stability of the fan wheel.
  • the end of the fan ring is expediently axially spaced from the trailing edges of the blade bodies. If the ramps extend essentially to the tip of the blade, the fan ring extends at most to the ramp. Furthermore, the fan ring can protrude axially beyond the leading edges of the blade bodies.
  • the fan ring can also be integrally formed on the fan wheel.
  • At least one web can be provided at least in one of the blades, which projects from the back of the blade body, begins at the ramp and extends in the direction of the trailing edge.
  • the respective web leads to a stiffening of the respective blade body. If a channel of the type described above is provided between the ramp and the trailing edge, the respective web extends within this channel and has a flow guiding function in order to divert the radially outward-oriented flow in the channel towards the trailing edge. All blades are preferably equipped with such webs.
  • exactly two or at least two such webs can be provided, namely an outer web arranged radially further out and an inner web arranged radially further inside. It can also be expediently provided that a web end of the inner web which is distant with respect to the ramp lies in a region less than 50% of the blade length, while a web end which is distant with respect to the ramp lies in a region greater than 50% of the blade length. In particular it can be provided that the web end of the inner web is approximately 33% ⁇ 5% of the blade length, while the web end of the outer web is approximately 66% ⁇ 5% of the blade length.
  • Such a distribution of the webs has proven to be particularly advantageous for the efficiency of the paddle wheel with regard to delivery capacity and reduction of oscillation and vibrations.
  • the respective web can advantageously have a web end that is spaced apart from the ramp and that is spaced apart from the trailing edge.
  • the aforementioned channel in particular remains radially flowable.
  • the respective web on the ramp that is to say at a transition point between the ramp and web, has a web height measured perpendicular to the rear, which is smaller than a ramp height measured perpendicular to the rear, which the ramp on the web or at said transition point.
  • At least one rib can be provided on the pressure side of the hub, which begins at a transition between two adjacent blades in the circumferential direction, runs at an incline to the circumferential direction and connects the trailing edge of one blade to the leading edge of the other blade at this transition , This results in an intense Bracing and stabilization of the blades in the area of the hub. In particular, this can reduce vibration excitation.
  • the respective rib is designed as an extension of such a ramp that extends at least partially over the hub. This extends the flow control function of the respective ramp into the hub and improves it accordingly.
  • a variant is particularly advantageous in which the respective rib ends radially on the inside on a radially inner edge of the hub.
  • the flow control function of the respective ramp can thus be extended radially over the entire hub.
  • At least one of the blades has a blade profile, at least on its blade tip, which has exactly one in an outflow region having the trailing edge outflow-side turning point. Additionally or alternatively, it can be provided that at least one of the blades has, at least at its blade tip, a blade profile which has exactly one upstream turning point in an inflow region having the leading edge. In particular, it can be provided that at least one of the blades has at least at its blade tip a blade profile that has exactly two turning points.
  • the aforementioned turning points are preferably only to be found in the blade profile of an end section of the respective blade body which has the blade tip, while the blade has, moreover, a blade profile which is convexly curved on the suction side and free of suction points.
  • At least one of the blades on the suction side of the fan wheel has a guide rib which protrudes from the front of the blade body and which extends from the starting area in the direction of the trailing edge and the blade tip of the respective blade, wherein the respective guide rib extends over approximately 50% or less than 50% of the blade length.
  • the respective guide rib preferably extends over a maximum of 40% of the blade length. In particular, the respective guide rib ends at approximately 33% of the blade length.
  • An axial fan according to the invention comprises a fan wheel of the type described above and a fan cover which surrounds the fan wheel on the outer circumference.
  • the fan cover is arranged in a stationary manner, while the fan wheel rotates relative to it.
  • the fan hood essentially causes the air flow to be channeled.
  • the fan cover can be connected to the heat exchanger to be flowed through in order to form a flow channel leading from the heat exchanger to the fan wheel.
  • FIG. 1 . 2 . 12 . 14 and 16 comprises a fan wheel 1, which for a in Fig. 18 indicated axial fan 2 is provided, a hub 3 and a plurality of blades 4, which start from the hub 3.
  • the fan wheel 1 is preferably an injection molded part made of plastic, in which the hub 3 and the blades 4 are made of one piece from the same material.
  • Each blade 4 has a blade root 5, with which it is connected to the hub 3, and a blade tip 6, which is arranged distally to the hub 3. Furthermore, each blade 4 has a blade body 7, which can also be referred to as an airfoil.
  • the blade body 7 has one in the Figures 3, 4 . 17 and 18 recognizable suction side 8 of the fan wheel 1 a front 9 and on a pressure side 10 of the fan wheel 1 a rear 11. Furthermore, there is a leading edge 12 and a trailing edge 13 of the respective blade 4 on the blade body 7.
  • the axial views of the Figures 1 . 2 and 12 as well as the isometric views of the Figures 5 to 11 and 14 and 15 are directed to the pressure side 10 of the fan wheel 1. This means that in these views the pressure side 10 faces the viewer, while the suction side 8 faces away from the viewer. In contrast, the isometric views of the 16 and 17 directed to the suction side 8 of the fan wheel 1, so that this suction side 8 faces the viewer.
  • all blades 4 each have a ramp 14 on the pressure side of the fan wheel 1.
  • the ramp 14 protrudes from the blade body 7 towards the pressure side 10.
  • the respective ramp 14 starts from an initial region 15 in which the blade root 5 and the leading edge 12 are located. Starting from this initial region 15, the respective ramp 14 then extends in the direction of the trailing edge 13 and in the direction of the blade tip 6 of the respective blade 4.
  • a blade length 16 is entered for one of the blades 4 and extends radially from the blade root 5 to the blade tip 6.
  • the ramps 14 in the preferred embodiments shown here extend essentially over the entire blade length 16, that is to say from the blade root 5 to the blade tip 6, in particular in the views of FIGS Figures 5 to 10 and 12 to 15 can be seen that the respective ramp 14 expediently does not extend completely to a radially outer outer edge 19 of the blade tip 6, but rather remains radially behind it. Accordingly, one remains in the Figures 5 to 10 and 12 to 15 designated gap 17 between a radially outer end 18 of the ramp 14 and said outer edge 19 of the blade tip 6.
  • This radial gap 17 is very small in the preferred embodiments shown here, in particular less than 10% of the blade length 16. In other embodiments, this gap can 17 may however be larger. According to the invention, for a sufficient improvement in the efficiency of the fan wheel 1, the ramp 14 is dimensioned such that it extends over at least 75% of the blade length 16.
  • the respective ramp 14 extends over at least 90% of the respective blade length 16.
  • the blade tip 6 and the outer end 18 of the ramp 14 are located in an end region 34 of the respective ramp 14.
  • the respective ramp 14 extends in its end region 34 at least up to the vicinity of the trailing edge 13, so that in the end region 34 also the trailing edge 13 is included.
  • the ramp 14 extends to the trailing edge 13.
  • FIGS Figures 2 to 17 The ramp 14 remains in the at least in the Figures 2 . 12 . 14 and 16 removed by a double arrow indicated circumferential direction 21 from the trailing edge 13.
  • At least one channel 20 is formed between the ramp 14 and the trailing edge 13 on the respective blade 4 and on the rear 11 of the respective blade body 7, which channel is open to the pressure side 10.
  • three such channels 20 are provided per blade 4.
  • two channels 20 are provided per blade 4.
  • only one such channel 20 is ever Bucket 4 provided.
  • At least one of the channels 20, which is designated 20 ′ below, extends to the radially outer end 18 of the ramp 14 Figure 1 In the embodiment shown, the ramp 14 is guided in the end region 34 to the trailing edge 13, the channel 20 ′ extending into the end 18 of the ramp 14 is radially closed.
  • the channel 20 ′ extending into the end region 34 is open radially, as a result of which it has a radial outlet opening 22.
  • the ramp 14 is also spaced in its end region 34 in the circumferential direction 21 from the trailing edge 13.
  • a plurality of channels 20 are provided per blade 4, the channels 20 preferably run parallel to one another.
  • adjacent channels 20 are each separated from one another by a common separating web 23.
  • the respective separating web 23 is arranged on the rear side 11 of the respective blade body 7, where it projects from the blade body 7 between the ramp 14 and the trailing edge 13.
  • the dividers 23 at their radially outer end each pass into the ramp 14.
  • the ramp 14 is designed, for example, as a web which projects from the blade body 7. It is noteworthy here that the web-shaped ramp 14 does not protrude from the blade body 7 perpendicularly to the rear 11, but is inclined with respect to a perpendicular direction 41. An angle of inclination of approximately 45 ° is indicated here. As a result, the respective channel 20 or 20 'has a V-profile in a cross section measured transversely to the radial direction. By changing a web height or ramp height, the flow around the respective blade 4 can be influenced, as shown in the figures 3 and 4 is indicated by corresponding flow arrows 24 and 25.
  • the ramp 14 is concavely curved toward the leading edge 12. It has been shown that such a concave curvature is particularly advantageous for guiding a backflow 29 and for building up pressure on the pressure side 10 in the region of a main flow 30. In principle, however, other geometries for the ramp 14 are also conceivable. Accordingly, in Fig. 10 purely by way of example, a slightly convex ramp 14 is indicated toward the leading edge 12. The originally concave curved ramp 14 is in Figure 10 indicated by a broken line. It is also conceivable to design the respective ramp 14 in a straight line.
  • the shape of the ramp 14 also makes it possible to influence a flow direction of the backflow 29 in the region of the outlet opening 22 of the respective axially open channel 20 '.
  • the following are purely exemplary Figures 7 to 9 three different options are shown.
  • the direction of flow of the backflow 29 in the outlet opening 22 is inclined toward the trailing edge 13.
  • the direction of flow of the backflow 29 in the outlet opening 22 is largely radially oriented.
  • the direction of flow of the backflow 29 in the outlet opening 22 is inclined toward the leading edge 23.
  • the radially outer open channel 20 ' is designed as a diffuser 32 in a radially outer outlet region 31 which contains the outlet opening 22.
  • the flow-through cross-section of the radially open channel 20 'in the flow direction of the backflow 29 conducted therein between the ramp 14 and the blade body 7 initially decreases and then increases again.
  • Figure 11 shows a further special embodiment, in which the blade body 7 in the end region 34 of the ramp 14 is curved toward the suction side with respect to the rest of the front side 9 outwards.
  • This outwardly bulging section is in Fig. 11 designated 33.
  • the original contour of this section 33 is shown with a broken line, which results when the contour of the remaining front side 9 of the blade body 7 at the blade tip 6 is extended from the leading edge 12 to the trailing edge 13 and at the trailing edge 13 from the blade root 5 to Blade tip 6 is extended.
  • the in Fig. 11 recognizable, axially open channel 20 'extends into the end region 34.
  • the blades 4 each have at least one web 42 on their rear side 11 which projects from the blade body 7.
  • the respective web 42 begins at the ramp 14 and extends in the direction of the trailing edge 13.
  • the respective web 42 leads to a stiffening of the respective blade body 7.
  • a channel 20 of the type described above is provided between the ramp 14 and the trailing edge 13 the respective web 42 within this channel 20 and has a flow guiding function in order to deflect the radially outwardly oriented flow in the channel 20 at least partially in the direction of the trailing edge 13.
  • exactly two such webs 42 are provided, namely an outer web 42 ′ arranged radially further out and an inner web 42 ′′ arranged radially further inward.
  • of the inner web 42 lies in a region smaller than 50% of the blade length 16, while a web end 43 'of the outer web 42' which is removed with respect to the ramp 14 lies in a region larger than 50% of the blade length 16.
  • the example shows that the web end 43 "of the inner web 42" is approximately 33% ⁇ 5% of the blade length 16, while the web end 43 'of the outer web 42' is approximately 66% ⁇ 5% of the blade length 16.
  • Such a distribution of the webs 42 has proven to be particularly advantageous for the efficiency of the paddle wheel 1 with regard to delivery capacity and reduction of oscillation and vibrations.
  • the respective web 42 is spaced from the ramp 14 and has the said web end 43, which is spaced from the trailing edge 13.
  • the aforementioned channel 20 in particular remains radially flowable.
  • the respective web 42 on the ramp 14, that is to say at a transition point 55 between the ramp 14 and web 42 has a web height 44 measured, for example, perpendicular to the rear side 11, which is smaller than a ramp height 45 then also measured perpendicular to the rear side 11 , which has the ramp 14 on the web 42 or at said transition point 55.
  • At least one rib 46 may be provided on the hub 3 on the pressure side 8, which begins at a transition 47 between two adjacent blades 4 in the circumferential direction, which runs inclined to the circumferential direction 21 and which at this transition 47 has the trailing edge 13 of the one blade 4 ( in Fig. 15 left) with the leading edge 12 of the other blade 4 (in Fig. 15 right) connects.
  • the respective rib 46 is designed as an extension of such a ramp 14 that extends completely over the hub 3.
  • the flow control function of the respective ramp 14 extended into the hub 3 and improved accordingly.
  • the continuous structure of ramp 14 is best seen in the axial views of the Fig. 12 and 13 to recognize.
  • Fig. 1 and 2 are also such ribs 46, which also extend the respective ramp 14 there and also the respective separating webs 23 into the hub 3.
  • a variant is particularly advantageous in which the respective rib 46 ends radially on the inside on a radially inner edge 48 of the hub 3.
  • the flow control function of the respective ramp 14 can thereby be extended radially over the entire hub 3.
  • the blades 4 have at least on their blade tip 6, in particular on their outer edge 19, a blade profile 49 which has exactly one outflow-side turning point 51 in an outflow region 50 having the outflow edge 13.
  • the blade profile 49 of the blades 4 has exactly one upstream turning point 53 at least on the blade tip 6, in particular on its outer edge 19, in an inflow region 52 having the leading edge 12.
  • the blades 4 thus have at least on the blade tip 6 or on the outer edge 19 a blade profile 49 which has exactly two turning points 51, 53.
  • the aforementioned turning points 51, 53 can only be found in the blade profile 49 of an end section of the respective blade body 7 which has the blade tip 6, while the blade 4 also has a different blade profile, for example a turning point-free, convexly curved blade side.
  • the blades 4 on the suction side 8 of the fan wheel 1 each have a guide rib 54 which protrudes from the front side 9 of the blade body 7 and which, starting from the starting region 15 in the direction of the trailing edge 13 and the blade tip 6 of the respective blade 4, wherein the respective guide rib 54 extends over approximately 50% or over less than 50% of the blade length 16.
  • the respective guide rib 54 preferably extends over a maximum of 40% of the blade length 16.
  • the respective guide rib 54 ends at approximately 33% of the blade length 16.
  • one end of the respective guide rib 54 projecting beyond the trailing edge 13 can be seen, whereby its position along the blade length 16 can also be seen.
  • the axial fan 2 comprises a fan hood 35 which surrounds the fan wheel 1 on the outer circumference.
  • the fan cover 35 is in the example of Figure 18 attached to a heat exchanger 36 and forms a flow channel 37 which leads from the heat exchanger 36 to the fan wheel 1.
  • the axial fan 2 generates a cooling air flow 38, which flows through the heat exchanger 36, using the fan wheel 1 during operation.
  • the fan wheel 1 is arranged axially between the heat exchanger 36 and an engine block 39 of an internal combustion engine, not shown, in particular a vehicle.
  • the fan wheel 1 promotes a main flow 30 largely axially, with deflection in the radial direction already taking place within the fan wheel 1, so that a diagonal flow is present in particular in the area of the blade tips 6.
  • the fan wheel 1 is purely exemplary equipped with a fan ring 40 which is fixedly connected to the blades 4 and accordingly rotates with the fan wheel 1.
  • the fan ring 40 can be an integral part of the injection molded fan wheel 1. As can be seen, the fan ring 40 extends axially on the suction side 8 beyond the leading edges 12 of the blades 4, while on the pressure side 10 the trailing edges 13 project axially beyond the fan ring 40.

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  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (15)

  1. Roue de ventilateur pour un ventilateur axial (2) pour la génération d'un courant d'air de refroidissement (38) à travers un échangeur de chaleur (36) d'un véhicule,
    - avec un moyeu (3) et plusieurs aubes (4), qui sont reliées au moyeu (3) respectivement au niveau d'un pied d'aube (5),
    - dans laquelle les aubes (4) présentent respectivement un corps d'aube (7), qui dispose sur un côté aspiration (8) de la roue de ventilateur (1), d'un côté avant (9) et sur un côté pression (10) de la roue de ventilateur (1), d'un côté arrière (11) et qui présente un bord d'attaque (12) ainsi qu'un bord de fuite (13),
    - dans laquelle au moins une des aubes (4) présente sur le côté pression (10) de la roue de ventilateur (1) une rampe (14), qui fait saillie du côté arrière (11) du corps d'aube (7) et qui s'étend à partir d'une zone de début (15), dans laquelle se trouvent le pied d'aube (5) et le bord d'attaque (12) de l'aube respective (4), en direction du bord de fuite (13) et d'une pointe d'aube (6) de l'aube respective (4),
    - dans laquelle la rampe (14) respective commence au niveau du pied d'aube (5) et/ou au niveau du moyeu (3),
    caractérisée en ce
    que la rampe (14) respective s'étend sur au moins 75% d'une longueur d'aube (16) mesurée radialement du pied d'aube (5) à la pointe d'aube (6).
  2. Roue de ventilateur selon la revendication 1,
    caractérisée en ce
    que la rampe (14) respective s'étend sensiblement sur toute la longueur d'aube (16).
  3. Roue de ventilateur selon la revendication 1 ou 2,
    caractérisée en ce
    qu'au moins un canal (20, 20') ouvert vers le côté pression (10) est réalisé entre la rampe (14) et le bord d'attaque (13) du corps d'aube (14).
  4. Roue de ventilateur selon la revendication 3,
    caractérisée en ce
    - qu'au moins un tel canal (20') s'étend jusqu'à une extrémité située radialement à l'extérieur (18) de la rampe (14), et/ou
    - qu'au moins un tel canal (20') est ouvert radialement à l'extérieur, et/ou
    - qu'au moins un tel canal ouvert radialement vers l'extérieur (20') est conçu dans une zone de sortie située radialement à l'extérieur (31) en tant que diffuseur (32).
  5. Roue de ventilateur selon la revendication 3 ou 4,
    caractérisée en ce
    que plusieurs canaux (20, 20') sont agencés parallèlement l'un à côté de l'autre, dans laquelle des canaux adjacents (20, 20') sont séparés les uns des autres par une traverse de séparation commune (23), qui fait saillie au niveau du côté arrière (11) du corps d'aube (7) entre la rampe (14) et le bord de fuite (13).
  6. Roue de ventilateur selon l'une quelconque des revendications 1 à 5,
    caractérisée en ce
    - qu'un bord de fuite (26) de la rampe (14) distal par rapport au corps d'aube (7) se situe le long de la rampe (14) sensiblement dans un plan de sortie s'étendant perpendiculairement à l'axe de rotation (27) de la roue de ventilateur (1), ou
    - que la rampe (14) présente un bord de fuite (26) distal par rapport au corps d'aube (7), qui dispose d'au moins une section (28) s'étendant le long de la rampe (14), qui est espacée d'un plan de sortie s'étendant perpendiculairement à l'axe de rotation (27) de la roue de ventilateur (1).
  7. Roue de ventilateur selon l'une quelconque des revendications 1 à 6,
    caractérisée en ce
    que la rampe (14) s'étend jusque dans une zone d'extrémité (34), dans laquelle se trouvent le bord de fuite (13) et la pointe d'aube (6), dans laquelle le corps d'aube (7) est incurvé vers l'extérieur dans cette zone d'extrémité (34) vers le côté aspiration (8) par rapport au reste du côté avant (9).
  8. Roue de ventilateur selon les revendications 7 et 3,
    caractérisée en ce
    qu'au moins un tel canal (20') s'étend jusque dans la zone d'extrémité (34).
  9. Roue de ventilateur selon l'une quelconque des revendications 1 à 8,
    caractérisée en ce
    qu'au moins pour une des aubes (4) au moins une traverse (42) est prévue, qui fait saillie au niveau du côté arrière (11) du corps d'aube (7), commence au niveau de la rampe (14) et s'étend en direction du bord de fuite (13).
  10. Roue de ventilateur selon la revendication 9,
    caractérisée en ce
    qu'au moins deux traverses (42) de ce genre sont prévues, à savoir une traverse extérieure agencée radialement plus à l'extérieur (42') et une traverse intérieure agencée radialement plus à l'intérieur (42"), dans laquelle une extrémité de traverse (43") de la traverse intérieure (42") éloignée par rapport à la rampe (14) se situe dans une zone inférieure à 50% de la longueur d'aube (16), pendant qu'une extrémité de traverse (43') de la traverse extérieure (42') éloignée par rapport à la rampe (14) se situe dans une zone supérieure à 50 % de la longueur d'aube (16).
  11. Roue de ventilateur selon la revendication 9 ou 10,
    caractérisée en ce
    - que la traverse respective (42) espacée de la rampe (14) présente une extrémité de traverse (43), qui est espacée du bord de fuite (13), dans laquelle l'extrémité de traverse (43') de la traverse extérieure (42') se situe de préférence plus près du bord de fuite (13) que l'extrémité de traverse (43") et la traverse intérieure (42"),
    - que la traverse respective (42) présente au niveau de la rampe (14) une hauteur de traverse (44), qui est inférieure à une hauteur de rampe (45), que la rampe (14) présente au niveau de la traverse (42).
  12. Roue de ventilateur selon l'une quelconque des revendications 1 à 11,
    caractérisée en ce
    - qu'au niveau du moyeu (3) sur le côté pression (10), au moins une nervure (46) est prévue, qui commence à une transition (47) entre deux aubes (4) adjacentes dans la direction circonférentielle (21), s'étend de manière inclinée par rapport à la direction circonférentielle (21) et relie au niveau de cette transition (47) le bord de fuite (13) de l'une aube (4) au bord d'attaque (12) de l'autre aube (4),
    - que la nervure respective (46) est conçue en tant que prolongement s'étendant au moins en partie sur le moyeu (3) d'une telle rampe (14).
  13. Roue de ventilateur selon l'une quelconque des revendications précédentes,
    caractérisée en ce
    - qu'au moins une des aubes (4) présente au moins au niveau de sa pointe d'aube (6) un profil d'aube (49), qui dispose dans une zone de fuite (50) présentant le bord de fuite (13) exactement d'un tournant côté fuite (51),
    - qu'au moins une des aubes (4) présente au moins au niveau de sa pointe d'aube (6) un profil d'aube (49), qui dispose dans une zone d'attaque (52) présentant le bord d'attaque (12) exactement d'un tournant côté attaque (53),
    - qu'au moins une des aubes (4) présente au moins au niveau de sa pointe d'aube (6) un profil d'aube (49), qui dispose exactement de deux tournants (51, 53).
  14. Roue de ventilateur selon l'une quelconque des revendications précédentes,
    caractérisée en ce
    qu'au moins une des aubes (4) présente sur le côté aspiration (8) de la roue de ventilateur (1) une nervure de guidage (54), qui fait saillie du côté avant (9) du corps d'aube (7) et qui s'étend à partir de la zone de début (15) en direction du bord de fuite (13) et de la pointe d'aube (6) de l'aube respective (4), dans laquelle la nervure de guidage respective (54) s'étend sur moins de 50 % de la longueur d'aube (16).
  15. Ventilateur axial pour la génération d'un courant d'air de refroidissement (38) pour la traversée d'un échangeur de chaleur (36) d'un véhicule,
    - avec une roue de ventilateur (1) selon l'une quelconque des revendications 1 à 14,
    - avec un capot de ventilateur (35), qui entoure la roue de ventilateur (1) au niveau de la circonférence extérieure.
EP15706434.6A 2014-03-05 2015-02-19 Roue de ventilateur pour ventilateur axial Active EP3114354B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014204043.4A DE102014204043A1 (de) 2014-03-05 2014-03-05 Lüfterrad eines Axiallüfters
PCT/EP2015/053537 WO2015132077A1 (fr) 2014-03-05 2015-02-19 Roue de ventilateur pour ventilateur axial

Publications (2)

Publication Number Publication Date
EP3114354A1 EP3114354A1 (fr) 2017-01-11
EP3114354B1 true EP3114354B1 (fr) 2020-01-08

Family

ID=52589369

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15706434.6A Active EP3114354B1 (fr) 2014-03-05 2015-02-19 Roue de ventilateur pour ventilateur axial

Country Status (3)

Country Link
EP (1) EP3114354B1 (fr)
DE (1) DE102014204043A1 (fr)
WO (1) WO2015132077A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USD860427S1 (en) 2017-09-18 2019-09-17 Horton, Inc. Ring fan
WO2020028010A1 (fr) 2018-08-02 2020-02-06 Horton, Inc. Ventilateur de refroidissement de véhicule à faible plénitude
DE102019214822A1 (de) * 2019-09-27 2021-04-01 Siemens Aktiengesellschaft Lüfterschaufel mit Radialflügel

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19929978B4 (de) 1999-06-30 2006-02-09 Behr Gmbh & Co. Kg Lüfter mit Axialschaufeln
US6375427B1 (en) * 2000-04-14 2002-04-23 Borgwarner Inc. Engine cooling fan having supporting vanes
ES2269274T3 (es) 2001-01-02 2007-04-01 BEHR GMBH & CO. KG Ventilador con palas axiales.
DE102010042325A1 (de) 2010-10-12 2012-04-12 Behr Gmbh & Co. Kg Lüfter mit Lüfterschaufeln
DE102010062301A1 (de) 2010-12-01 2012-06-06 Behr Gmbh & Co. Kg Axiallüfter

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
WO2015132077A1 (fr) 2015-09-11
DE102014204043A1 (de) 2015-09-10
EP3114354A1 (fr) 2017-01-11

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