• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    AXIAL FAN. The present invention relates to an axial fan for transporting cooled air especially for an internal combustion engine of a motor vehicle, comprising fan blades (13, 14, 15) attached to a hub (12), presenting a side of pressure and a suction side, a rear edge (16, 17, 18) and a blade depth (t), on the respective pressure side of which a hub ramp (13a, 14a, 15a) is arranged upwards against the direction of rotation (D) of the axial fan (11), the rear edge (16, 17, 18) having an outer region (16a, 17a, 18a), located radially outside the hub ramp (13a, 14a, 15a) and an interior region (16b, 17b, 18b), located radially within the hub ramp (13a, 14a, 15a).
    公开号:BR112013015751B1
    申请号:R112013015751-8
    申请日:2011-12-01
    公开日:2020-10-20
    发明作者:Uwe Aschermann；Uwe Blass；Frederic Guilbaud
    申请人:MAHLE Behr GmbH & Co. KG；
    IPC主号:
    专利说明:

    [001] The invention relates to an axial fan for transporting cooled air especially for an internal combustion engine of a motor vehicle according to the preamble of claim 1.
    [002] An axial fan according to gender is described in the Depositor's previous patent application under official process number 10 2010 042 325.4. The axial fan has fan blades attached to a hub ring, which have on their pressure side a hub ramp and on their suction side air-conducting elements, also called stabilizers, which serve to influence the flow of the fan. The fan blades have, respectively, a front edge, also called a flow inlet edge, as well as a rear edge, also called a flow outlet edge. The rear edge of the fan blade essentially has two segments extending radially, namely, an outer segment disposed outside the hub ramp and an inner segment disposed within the hub ramp. The inner segment of the rear edge, for reasons of weight saving, is angled inwards, that is, towards the hub ring, so that a banding to the rear edge results and, thus, a reduction of the blade width the fan. It was found that, due to this receding of the rear edge, a transverse and / or return flow of the fan blade flow results, which produces an unfavorable influence of the flow on the pressure side of the neighboring fan blade. Due to this return and / or transverse flow, a swirl structure results in a drop in the region of the hub ramp, which results in a decrease in the degree of effectiveness.
    [003] By EP 0 515 839 A1 an axial fan with fan blades became known, on whose pressure side an upward ramp ramp is arranged against the flow direction. The cube ramp fills almost the entire area of standing water in the region of the root of the blades and thus prevents a whirlpool flow associated with losses.
    [004] From DE 199 29 978 B4 it became known an axial fan with fan blades, on whose suction side there are air conducting elements and on whose pressure side there are hub ramps. Thus a flow channel is formed, which produces a stable flow conduction in the region of the blade roots.
    [005] It is an objective of the present invention to improve the flow conditions in an axial fan of the type mentioned at the beginning and especially to avoid a whirlpool formation associated with losses.
    [006] The purpose of the invention is achieved by independent claim 1. Advantageous configurations result from the sub-claims. According to the claim, the fan blade has a rear edge with two segments, the first outer segment being located radially outside the hub ramp and the second inner segment being located radially inside the hub ramp. According to the invention, it is advantageous that the rear edge presents in the outer region radially outside the hub ramp a course that proceeds essentially unchanged by the radial position of the hub ramp radially inward to the inner region and in the innermost region extends to the hub . Thus, according to the invention, stabilization of the fan blade flow is achieved in the region of the hub ramp, that is, a transverse and / or return flow around the rear edge of the fan blade is at least reduced or prevented. This leads to a significant increase in the efficiency of the fan and a considerable increase in the volume flow conveyor through the fan at the fan's working point. In addition, the specific noise pressure level is reduced.
    [007] It is also advantageous that the radially innermost region is the radially inner fraction of the radius of the radially inner region.
    [008] It is also advantageous for this fraction to account for approximately one third, approximately one quarter or preferably less than approximately one fifth of the radius of the inner region of the rear edge.
    [009] It can thus also be understood that there are three regions, the outer region and the inner region, and the inner region is again divided into a so-called intermediate region and the innermost region itself.
    [0010] According to the invention, it is therefore advantageous for the rear edge to have a course radially outside the hub ramp outside the hub ramp radically inward towards the so-called intermediate region of the hub ramp. inner region and extends in the radially innermost region for the cube. This stroke for the cube can mean curved or angled, etc.
    [0011] The fan blade advantageously also has essentially the same blade depth in the inner region as in the outer region, that is, especially the rear edge of the blade passes from the outer segment essentially straight to the inner segment, so that in the The total result is a straight rear edge up to the root of the blades. Thus, it does not affect a certain curvature of the front edge, which in this regard, for greater clarity, was assumed to be straight, and a curved front edge that is not straight would be equally permissible.
    [0012] In front of the fan of the previous patent application, thus, the blade depth and also the blade width in the region within the hub ramp are advantageously increased.
    [0013] The terms fan blade and fan blade are used in the context of this application as synonyms. The term blade depth means the axial extension of the fan blade. The depth of the blade is the projection of the width of the blade in the peripheral direction, with the width of the blade being the distance between the front edge of the blade and the rear edge of the blade, measured in the direction of the rope.
    [0014] According to a preferred embodiment, the rear edge is rounded in the innermost region. This allows a transition with less tension from the rear blade edge to the hub region.
    [0015] According to another preferred form of execution, the rear edge of the blade presents in its innermost region - by rounding - transition to the free edge of the hub ramp. This results in an increase in resistance in the root region of the blades or blades for connecting the fan blade to the hub. In addition, a favorable flow channel results between the suction side and the pressure side in the foot region of the blades and hub ramp. The free edge of the hub ramp means the edge of the hub ramp opposite the fan blade and protruding from the fan blade.
    [0016] According to another preferred embodiment, stabilizers are located on the suction side of the fan blades, which are preferably located radially inside the hub ramp. The stabilizer region located downstream thus flows into the inner segment of the rear blade edge. Through the stabilizers, in connection with the hub ramps between both blades, greater stabilization of the flow in the region of the feet of the blades is obtained.
    [0017] According to another preferred form of execution, the hub is executed as a hub ring, which has an axial extension essentially smaller than the fan blades. Therefore, there is no longer a cylindrical cube in the classic sense. The axial extension of the fan blades - as mentioned above - is referred to as the blade depth, which represents a projection of the blade width in a peripheral direction. The fan blades protrude both with its front edge and with its rear edge through the front areas of the hub ring. In this measure, the rear edge extending in a straight line to the innermost region forms an axial protrusion of the fan blade with respect to the hub ring.
    [0018] According to another preferred embodiment, the axial fan has a Di / Da hub region greater than 42%, the hub ratio being the quotient of the hub diameter and the outer diameter of the fan blades. The axial protrusion of the rear blade edge in the inner region acts especially advantageously on fans with a relatively large hub ratio, as this acts disadvantageously on the degree of efficiency and the volumetric flow carried by the fan, thus resulting in compensation. The larger hub ratio can then result due to a smaller outside diameter, when the fan blades are shortened due to power scaling.
    [0019] According to another preferred form of execution, the axial fan is firmly joined by its hub ring with a liquid friction coupling, which in turn is driven by the internal combustion engine and drives the fan with a number of revolutions of regulated output. With higher powers, it increases the diameter of the liquid friction coupling and thus the hub diameter, which can lead to a higher hub ratio.
    [0020] The blade protrusion according to the invention, which leads to an increase in the degree of efficiency and volumetric flow, has a particularly positive effect here.
    [0021] According to another preferred form of execution, the fan blades are angled in the region of the blade root, resulting in the shape of a blade for the fan blade. Therefore, a small increase in material in the region of the fan blade and hub ring connection is advantageous as well as greater resistance.
    [0022] Examples of implementation of the invention are shown in the drawing and will be described in detail below, with the description and / or the drawing showing other characteristics and / or advantages. Show:
    [0023] Fig. 1 - a fan blade execution according to the state of the art,
    [0024] Fig. 2 - a fan blade according to the invention with stabilized flow,
    [0025] Fig. 3 - a cutout of a fan according to the invention in 3D representation,
    [0026] Fig. 4 - a radial section through the fan hub,
    [0027] Fig. 5 - a partial view of the axial fan with a cutting plane VI-VI, and
    [0028] Fig. 6 - the sectional representation according to the cutting plan VI-VI in Fig. 5.
    [0029] Fig. 1 shows an arrangement of fan blades 1, 2 of an axial fan according to the state of the art. The direction of rotation of the fan is characterized by an arrow D. The fan blades 1, 2 have hub ramps 3, 4 on their pressure side as well as rear blade edges 1a, 2a. The rear edges or flow exit edges 1a, 2a mentioned, present in their region located radially internally, that is, within the hub ramp 3, 4, respectively notches or ribs 5, 6. These grooves and width shortenings fan blades were performed in the state of the art, because, on the one hand, they mean weight savings and, on the other hand, there was the view that the fan blade no longer brings any power gain in the root region of shovel. However, a transverse and / or return flow, which is indicated by the arrow W, proved to be disadvantageous. The surrounding flow of the rear blade edge in the region of the groove 5 results in a whirlwind drag represented by the arrow W, which leads to a reduction in the degree efficiency, reduced volumetric flow and greater noise generation.
    [0030] Fig. 2 shows, schematically, an execution according to the invention of fan blades 7, 7 and their rear edges of blade 7a, 8a. The direction of rotation of the axial fan is, in turn, characterized by an arrow D. On the pressure sides of the fan blades 7, 8, hub ramps 9, 10 are arranged, which subdivide the rear blade edges 7a, 8a in a radially outer region and a radially inner region. According to the invention, the radially inner region of the rear blade edge 7a extends essentially straight, that is, from the transition from the outer region to the inner region, an essentially straight course takes place.
    [0031] In other words, the blade width of the fan blade 7 compared to the blade width of the fan blade 1 according to the state of the art is increased in the radially interior region, so that there is no banding.
    [0032] This enlarged region is highlighted by a contour 7b represented in full line. The effect of the increased blade width in region 7b is a blocking of the transverse flow and / or return associated with losses, shown in Fig. 1. Especially the flow represented by the arrow S is largely unimpeded radially outside the hub ramp 10 on the blade of fan 8. On the other hand, also below the hub ramp 10, a relatively stable and non-eddy flow is formed, indicated by the arrow P. The extension of the rear blade edge in the radially inner region 7b, that is, the increase in width blade provides a significant increase in volumetric flow and efficiency as well as noise reduction.
    [0033] In terms of blade width or blade width, the distance between the front edge and the rear edge or the length of the rope of the blade or blade must be understood. The blade depth (blade depth) is the projection of the blade width in the peripheral direction.
    [0034] Fig. 3 shows a section of an axial fan 11 according to the invention in 3D representation. The representation shows a hub ring 12, in which fan blades 13, 14, 15 are attached, that is, injected in one piece. The fan blades 13, 14, 15 have hub ramps 13a, 14a, 15a on their pressure sides, which ascend against the direction of rotation indicated by an arrow D. Hub ramps 13a, 14a, 15a are slatted from resistance units with the hub ring on its inner side. The fan blades 13, 14, 15 have rear edges 16, 17, 18 respectively, also called flow outlet edges 16, 17, 18, which essentially extend in a straight line from radially externally to radially internally. At the end of the hub ramps 13, 14a, 15a positioned downstream the rear edges 16, 17, 18 are subdivided into two segments, namely, radially outer segments or regions 16a, 17a, 18a as well as radially inner segments or regions 16b , 17b, 18b. The inner segments 16, 17b, 18b of the rear blade edges 16, 17, 18 show a transition by a radius or rounding R to the free edges of the hub ramps 13a, 14a, 15a, the reference lines of references 13a , 14a, 15a start from the free edges. Thus, a fan structure optimized in relation to the resistance is provided, which is able to absorb the forces that occur when the fan operates, especially centrifugal forces. The suction sides of the fan blades have side stabilizers 19.
    [0035] Fig. 4 shows a radial section (core in a radial plane) through the hub ring 12 of the axial fan 11, and for equal parts equal references are used as in Fig. 3. The air flow direction is represented by an arrow L. The hub ring 12 has an axial extension a and the fan blade 14 has a depth t, which - as mentioned above - is defined as a projection of the blade width in the peripheral direction. From the drawing, it is clear that the blade depth t is considerably greater than the axial extension a of the hub ring 12. The depth t in a preferred embodiment is approximately twice the axial extension a of the hub ring. 12. The rear edge 17 of the fan blade 14 extends essentially in a radial direction in a straight line, the innermost segment of the rear edge 17 being rounded. The cube ramp appears as a sectioned area, which is characterized by 14a.
    [0036] Fig. 5 shows a view of an axial fan 20 shown incomplete with a view towards its front side or the suction sides of the fan blades 21, in which air conducting elements 22 are arranged. The axial fan 20 it comprises a metal support ring 23, which is joined on one side with the plastic hub of the axial fan 20 and, on the other hand, can be attached to a coupling not shown, preferably a liquid propulsion coupling. The fan blades designated with references 21a, 21b, 21c are cut in the cutting plane VI-VI.
    [0037] Fig. 6 shows a sectional representation of the axial fan 20 according to the cutting plane VI-VI. The representation shows two distinct cutting areas of the fan blades 21a, 21b, 21c. As shown in the cutting plane VI-VI in Fig. 5, the fan blades 21a, 21b, 21c, are cut with respect to their radial central line in different planes, the cutting plane for the central blade 21b can be considered as a tangential cut and is located radially within the hub ramp. The cutting area of the blade 21c in Fig. 6 is located above the hub ramp, which is designated here with reference 24 and cannot be seen in Fig. 5, as it is arranged on the rear side of the fan blades 21 The blade width b, ie the distance between the front and rear edge, can be removed from the cutting area of the central fan blade 21b. The projection of the blade width b in the peripheral direction results in the blade depth 7 (not designated), which is approximately constant throughout the radial region, namely, with the rear blade edge extending approximately in a straight line.
    [0038] Other characteristics and preferred forms of execution can be seen from the Depositor's previous patent application, mentioned at the beginning, with the official process number 2010 042 325.4. This earlier patent application is fully incorporated into the descriptive content of the present application. According to him, it may then be advantageous to bend the fan blades towards their blade roots and pull the angled region, located internally, under the hub ring. By angling, a fan blade shape and a transition between fan blade and hub ring optimized in terms of fixation are obtained.
    权利要求:
    Claims (11)
    [0001]
    1. Axial fan for transporting cooled air especially for an internal combustion engine in a motor vehicle, comprising fan blades (13, 14, 15) attached to a hub (12), presenting a pressure side and a suction side , a rear edge (16, 17, 18) and a blade depth (t), on the respective pressure side of which a hub ramp (13a, 14a, 15a) is arranged upwards against the direction of rotation (D) of the fan axial (11), the rear edge (16, 17, 18) having an outer region (16a, 17a, 18a), located radially outside the hub ramp (13a, 14a, 15a) and a region (16b, 17b , 18b) interior, located radially inside the hub ramp (13a, 14a, 15a), characterized by the fact that the rear edge presents in the outer region radially outside the hub ramp, a course that proceeds essentially unchanged by the radial position of the ramp cube radially inward to the inner region and in the innermost region it extends of for the cube, where the radially innermost region is the radially inner fraction of the radially inner region, where the fraction matters in approximately one third, approximately one quarter, or preferably less than approximately one fifth of the region radius inside the rear edge.
    [0002]
    2. Axial fan according to claim 1, characterized by the fact that the blade depth (t) in the region (16b, 17b, 18b) corresponds to the depth of blade (t) in the region (16a, 17a, 18a) outside.
    [0003]
    Axial fan according to claim 1 or 2, characterized in that the rear edge (16, 17, 18) in the outer region and in the inner region (16a, 16b, 17a, 17b, 18a, 18b) is, however, performed without the innermost region essentially as a straight edge.
    [0004]
    Axial fan according to one of claims 1 to 3, characterized in that the rear edge (16, 17, 18) in the innermost region is rounded and presents a transition to the hub (12).
    [0005]
    Axial fan according to one of claims 1 to 4, characterized by the fact that the rear edge (16, 17, 18) presents in its region radially more interior by a rounding (R) in the transition to the free edge of the ramp cube (14a, 15a).
    [0006]
    Axial fan according to one of claims 1 to 5, characterized in that the air blades (22) are arranged on the suction side of the fan blades (22), which are used as stabilizers.
    [0007]
    Axial fan according to claim 6, characterized by the fact that the stabilizers (22) extend to the interior region (16b, 17b, 18b) of the rear edges (16, 17, 18).
    [0008]
    Axial fan according to one of claims 1 to 7, characterized in that the hub is made as a hub ring (12) with an axial extension (a), which is essentially less than the depth of the fan blade ( t).
    [0009]
    9. Axial fan according to any of claims 1 to 8, characterized by the fact that the axial fan (11) has a Di / Da hub ratio greater than 42%, with Di being the outer diameter of the hub ( 12) and Da the outside diameter of the fan blades (14).
    [0010]
    An axial fan according to any one of claims 1 to 9, characterized in that a liquid friction coupling is arranged inside the hub ring (12) and firmly connected with the hub ring (12).
    [0011]
    Axial fan according to one of claims 1 to 10, characterized by the fact that the fan blades (13, 14, 15) are angled towards their blade root, the angled region of the fan blade ( 13, 14, 15) the hub ring (12) is at least partially pulled from under the hub respectively.
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    法律状态:
    2018-12-18| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|
    2019-11-26| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|
    2020-06-02| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|
    2020-10-20| B16A| Patent or certificate of addition of invention granted|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 01/12/2011, OBSERVADAS AS CONDICOES LEGAIS. |
    2020-10-20| B25D| Requested change of name of applicant approved|Owner name: MAHLE BEHR GMBH AND CO. KG (DE) |
    优先权:
    申请号 | 申请日 | 专利标题
    DE102010062301A|DE102010062301A1|2010-12-01|2010-12-01|Axial|
    DE102010062301.6|2010-12-01|
    PCT/EP2011/071579|WO2012072779A1|2010-12-01|2011-12-01|Axial fan|
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