EP3450716B1 - Roue de ventilateur et module de ventilateur de refroidissement doté d'une telle roue de ventilateur - Google Patents

Roue de ventilateur et module de ventilateur de refroidissement doté d'une telle roue de ventilateur Download PDF

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Publication number
EP3450716B1
EP3450716B1 EP18190529.0A EP18190529A EP3450716B1 EP 3450716 B1 EP3450716 B1 EP 3450716B1 EP 18190529 A EP18190529 A EP 18190529A EP 3450716 B1 EP3450716 B1 EP 3450716B1
Authority
EP
European Patent Office
Prior art keywords
fan wheel
blade
relative position
fan
rotation
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
EP18190529.0A
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German (de)
English (en)
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EP3450716A1 (fr
Inventor
Christian Froh
Michael Mauss
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.)
Brose Fahrzeugteile SE and Co KG
Original Assignee
Brose Fahrzeugteile SE and Co KG
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Application filed by Brose Fahrzeugteile SE and Co KG filed Critical Brose Fahrzeugteile SE and Co KG
Priority to RS20211269A priority Critical patent/RS62490B1/sr
Publication of EP3450716A1 publication Critical patent/EP3450716A1/fr
Application granted granted Critical
Publication of EP3450716B1 publication Critical patent/EP3450716B1/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
    • F04D29/38—Blades
    • F04D29/384—Blades characterised by form
    • F04D29/386—Skewed blades
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P5/00—Pumping cooling-air or liquid coolants
    • F01P5/02—Pumping cooling-air; Arrangements of cooling-air pumps, e.g. fans or blowers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P5/00—Pumping cooling-air or liquid coolants
    • F01P5/02—Pumping cooling-air; Arrangements of cooling-air pumps, e.g. fans or blowers
    • F01P5/04—Pump-driving arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • 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
    • F04D29/321—Rotors specially for elastic fluids for axial flow pumps for axial flow compressors
    • F04D29/324—Blades
    • 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
    • F04D29/326—Rotors specially for elastic fluids for axial flow pumps for axial flow fans comprising a rotating shroud
    • 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
    • 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
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/522—Casings; Connections of working fluid for axial pumps especially adapted for elastic fluid pumps
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/663—Sound attenuation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P5/00—Pumping cooling-air or liquid coolants
    • F01P5/02—Pumping cooling-air; Arrangements of cooling-air pumps, e.g. fans or blowers
    • F01P5/04—Pump-driving arrangements
    • F01P2005/046—Pump-driving arrangements with electrical pump drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P5/00—Pumping cooling-air or liquid coolants
    • F01P5/02—Pumping cooling-air; Arrangements of cooling-air pumps, e.g. fans or blowers
    • F01P5/06—Guiding or ducting air to, or from, ducted fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/20—Rotors
    • F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05D2240/303—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor related to the leading edge of a rotor blade
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/20—Rotors
    • F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05D2240/304—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor related to the trailing edge of a rotor blade

Definitions

  • the present invention relates to a fan wheel with backward sickle blades for a cooling fan module, in particular an electrically operated cooling fan module, in particular for motor vehicles.
  • the cooling system of an internal combustion engine in particular of a motor vehicle, mainly dissipates that heat which is given off to the walls of the combustion chambers and cylinders because the combustion process is not ideal. Since excessively high temperatures would damage the engine (tearing off the lubricating film, burning the valves, etc.), the combustion engine must be actively cooled.
  • Modern internal combustion engines especially four-stroke engines in motor vehicles, are, with a few exceptions, liquid-cooled, a mixture of water, antifreeze and anti-corrosion agent being used as the coolant.
  • the coolant is pumped through hoses, pipes and / or ducts through the engine (cylinder head and engine block) and, if necessary, through thermally highly stressed engine components, such as exhaust gas turbochargers, generators or exhaust gas recirculation coolers.
  • the coolant absorbs thermal energy and removes it from the above-mentioned components.
  • the heated coolant flows on to a cooler.
  • This cooler - in the past often made of brass, now mostly made of aluminum - is usually attached to the front of the vehicle, where a stream of air absorbs heat energy from the coolant and cools it down before it flows back to the engine, which closes the coolant circuit.
  • Cooling fan module In order to force the air through the cooler, a flow direction is taken before the cooler (ie upstream) or after the cooler (ie downstream) Cooling fan module is provided, which can be driven mechanically via a belt drive or electrically via an electric motor. The following statements refer to an electrically driven cooling fan module.
  • a cooling fan module classically consists of a fan frame, which has a fan wheel recess, and a fan wheel, which is rotatably held in the fan wheel recess.
  • the geometry of the fan wheel has a decisive influence on both the amount of air conveyed and the acoustic properties of the cooling fan module.
  • Classic fan wheels (s. Figures 1A and 1B ) have an at least substantially flat or slightly curved edge geometry on the blades.
  • the present invention is based on the object of specifying an advantageous fan wheel which is particularly advantageous with regard to its air delivery properties and / or its acoustic properties.
  • the object is achieved by a fan wheel according to claim 1.
  • this is particularly advantageous since a favorable air volume flow can be achieved in this way.
  • Comparative measurements which are explained in detail in the description of the figures, have shown that a fan wheel according to the present invention can achieve, in particular, a higher air volume flow compared to an otherwise structurally identical fan wheel with a flat or curved rear edge.
  • the same air volume flow can be generated with a power saving or a slower running fan wheel according to the present invention.
  • a higher air volume flow can be achieved with the same output.
  • a "fan wheel” in the sense of the present invention is in particular a rotationally symmetrical component that connects a hub, in particular a hub pot, which connects the fan wheel to a motor, in particular via a shaft protruding from this, in such a way that the torque generated by the Motor is generated, is at least substantially completely transferred to the fan wheel.
  • the fan wheel has a plurality of blades, which are provided, in particular are set up to generate an air volume flow as soon as the fan wheel is set in a rotary motion.
  • the blades are preferably inclined with respect to the axis of rotation in an angular range of -90 ° to + 90 °.
  • a "hub pot” in the sense of the present invention is in particular a central part of the fan wheel, which is arranged at least essentially in the middle of the fan wheel, provides a connection to a drive, in particular a motor, in particular an electric motor, this drive, in particular a motor , in particular an electric motor, at least partially and which, like a classic pot, is composed of an at least substantially flat base surface and an adjoining cylinder surface.
  • the blades are arranged, in particular molded, on this cylindrical outer wall.
  • a "blade” in the sense of the present invention is a flat body which is inclined with respect to a plane on which the axis of rotation is perpendicular, which is arranged on the hub cup and which is intended, in particular set up, to generate an air volume flow as soon as the fan wheel is in a rotational movement is displaced.
  • Blade blades in the context of the present invention are also understood in particular to mean blades or rotor blades.
  • a "leading edge" of the airfoil in the sense of the present invention is in particular that edge which leads in the direction of rotation.
  • a “trailing edge” of an airfoil in the sense of the present invention is in particular that edge of the airfoil which, viewed in the direction of rotation, lags behind.
  • orthogonal projection within the meaning of the present invention is an image of a point on a plane, so that the connecting line between the point and its image forms a right angle with this plane. The image then has the shortest distance to the starting point of all points on the plane.
  • the orthogonal projection is thus a special case of a parallel projection in which the projection direction is the same as the normal direction of the plane.
  • a “relative unit radius” in the sense of the present invention describes a point or a particularly cylindrical plane at a defined distance from the axis of rotation in a standardized manner, which leads to improved comparability between different fan impellers.
  • Aperiodic in the sense of the present invention is in particular a shape which extends asymmetrically over the relative unit radius, that is to say, in other words, no axis of symmetry can be found which defines the course of the relative position of the front edge POS rel_VK (t) and / or divides the course of the relative position of the rear edge POS rel_HK (t) into two identical sub-functions.
  • the course of the relative position of the front edge POS rel_VK (t) and / or the course of the relative position of the rear edge POS rel_HK (t) is not a function whose function values are repeated at regular intervals.
  • the basic idea of the present invention is to give the leading edge and / or the trailing edge an aperiodically wavy shape, which leads to a unique design of the airfoil, as can be seen from the edge geometry (course of the relative position of the leading or trailing edge) is described.
  • this form according to the invention lies the key to increased air performance or to the power savings described above.
  • the relative position of the leading edge POS rel_VK (t) is related to a third point which, viewed in the direction of rotation of the fan wheel, is the foremost point at the transition from the hub pot to the blade and / or the relative position of the trailing edge POS rel_HK (t) is to one referring back to the fourth point, which, viewed in the direction of rotation of the fan wheel, is the rearmost point at the transition from the hub pot to the blade.
  • the fan wheel has one or more blades that are sickled backwards when viewed in the direction of rotation. This is particularly important because for fan impellers with forward and backward sickle blades there are fundamentally different aerodynamic conditions which, among other things, have a significant influence on the conveyed air volume flow.
  • Backward sickle in the sense of the present invention means in particular that the tip of the airfoil with the outer radius R a , viewed in the direction of rotation, lags behind the center of the airfoil.
  • the fan wheel has an at least substantially circular outer ring which connects the blade tips of the blades to one another. This is particularly advantageous because in this way an increased mechanical strength of the fan wheel is achieved and a defined, at least essentially constant, gap is provided between a frame ring and the outer ring, which in turn leads to advantageous aerodynamic and / or acoustic effects.
  • the course of the relative position of the trailing edge POS rel_HK (t) is in the range from 80% to 100%, in particular 90% to 100%, in particular 92.5% to 97.5%, of the relative unit radius t (r) of the blade ( 30) has a maximum, especially a local one.
  • a, in particular a local, maximum in the specified area contributes a substantial proportion to the increase in the air volume flow.
  • the course of the relative position of the leading edge POS rel_VK (t) in the range from 80% to 100%, in particular 90% to 100%, in particular 92.5% to 97.5%, of the relative unit radius t (r) of the blade ( 30) has an, in particular local, minimum.
  • the profile of the relative position of the trailing edge POS rel_HK (t) in the y direction has no or at most one low point after the, in particular local, maximum. This is particularly advantageous because in this way the fan wheel runs out at least essentially in a straight line, since extensive tests have shown that further waves after the, in particular local, maximum do not achieve any further significant power savings.
  • the profile of the relative position of the leading edge POS rel_VK (t) in the y direction after the, in particular local, minimum has no or at most one high point. This is particularly advantageous because in this way the fan wheel runs out at least essentially in a straight line, since extensive tests have shown that further shafts after the, in particular local, minimum do not achieve any further significant power savings.
  • the profile of the relative position of the front edge POS rel_VK (t) and the profile of the relative position of the rear edge POS rel_HK (t) are at least essentially axially symmetrical to one another, in particular the rear edge POS rel_HK (t) runs around in an area a curve of +/- 20%, in particular +/- 10%, of the value of the relative position of the front edge POS rel_VK (t), which is geometrically exactly mirrored on the axis of symmetry.
  • a curved pivot axis through the blade runs centrally or slightly eccentrically, e.g. at 40% of the blade extension in the direction of rotation, around which incremental disks of the blade, which are perpendicular to the pivot axis, are individually aligned.
  • the pivot axis there is a functional relationship between the course of the relative position of the front edge POS rel_VK (t) and the course of the relative position of the rear edge POS rel_HK (t).
  • t 0 describes an offset of the relative unit radius for setting the apex on the hub cup
  • N the number of oscillations over the axial unit radius
  • a 1 a quadratic polynomial coefficient
  • a 2 is a linear polynomial coefficient
  • a 3 is a coefficient of the axial threading, ie to set the linear course of the leading edge from the hub cup to the blade tip or to the outer ring
  • a 4 is a relative base deflection ("start" deflection) of the leading edge on the hub cup.
  • the above-mentioned function describes the aperiodically wavy shape of the course of the relative position of the leading edge POS rel_vK (t). With the help of the specified parameters, it is possible to adapt the course of the relative position of the front edge POS rel_VK (t) to the external conditions in the course of the fan wheel design in order to achieve advantageous power savings or an equivalent increase
  • t 0 describes an offset of the relative unit radius for setting the apex on the hub cup, N the number of oscillations over the axial unit radius, a an oscillation coefficient for scaling the wavelength and setting the position of the, in particular local, maximum, A 1 a quadratic polynomial coefficient, A 2 a linear polynomial coefficient, A 3 a coefficient of the axial threading, ie for setting the linear course of the trailing edge from the hub cup to the blade tip or to the outer ring and A 4 a relative base deflection ("start" deflection) of the trailing edge on the hub cup.
  • the above-mentioned function describes the aperiodically wavy shape of the course of the relative position of the rear edge POS rel_HK (t). With the help of the specified parameters, it is possible to adapt the course of the relative position of the rear edge POS rel_HK (t) to the external conditions in the course of the fan wheel design in order to achieve an advantageous power saving or an equivalent increase in air volume.
  • the fan wheel according to the invention is intended in particular for use in connection with a fan frame with front struts, i.e. the struts are in front of the fan wheel as seen in the main flow direction.
  • a “cooling fan module” within the meaning of the present invention is in particular an assembly which, viewed in the direction of flow, is arranged upstream or downstream of a radiator of a vehicle and which is provided, in particular designed, to generate an air volume flow which extends through or around the radiator extends around the cooler, the air volume flow absorbing thermal energy from the cooler.
  • a “fan frame” within the meaning of the present invention is in particular a frame in which the fan wheel is held and itself is in turn preferably arranged, in particular fastened, on or in the vicinity of a cooler.
  • a fan frame in the sense of the present invention preferably has a plastic material, in particular a plastic compound, in particular the fan frame is formed from this.
  • the fan shroud has a metal material, for example iron, steel, Aluminum, magnesium or the like, in particular is at least partially, in particular at least substantially, in particular completely, formed therefrom.
  • a fan frame can also have more than one fan wheel recess, a motor holder, a motor and a fan wheel; in particular, the present invention is suitable for use in cooling fan modules with two or more, in particular two, fan wheels.
  • the fan frame additionally has at least one closable opening, in particular at least one flap, in particular a plurality of the same. This is particularly advantageous since further air guidance properties can be implemented in this way.
  • a “fan wheel recess” in the sense of the present invention is in particular a material recess within the fan frame.
  • struts extend in the fan wheel recess which mechanically, in particular and electrically and / or electronically connect a motor holder, which is also arranged in the fan wheel recess, to the fan frame.
  • the fan wheel recess is delimited by a frame ring.
  • a "frame ring" within the meaning of the present invention delimits the fan wheel recess in a plane perpendicular to the axis of rotation of the fan wheel, the plane in particular being at least essentially identical to the direction in which the fan frame extends.
  • the frame ring can either be formed by an edge of the fan wheel recess and / or have a cylinder surface which expands in the axial direction and which is preferably formed in one piece with the fan frame.
  • a “motor holder” in the sense of the present invention is in particular a device for mechanically fastening the motor to the fan frame, in particular for providing the torque counteracting the fan wheel.
  • the motor holder is an at least substantially annular structure in which the motor is held. This is particularly advantageous since in this way an advantageous flow of cooling air through the motor is not impaired.
  • “Struts” in the sense of the present invention are in particular bar-shaped or sickle-shaped structures which provide a mechanical connection between the motor holder and the fan shroud.
  • the struts can have a teardrop-shaped cross section in order to achieve advantageous aerodynamic and / or acoustic effects.
  • a “motor” within the meaning of the present invention is in particular a machine that performs mechanical work by converting a form of energy, for example thermal / chemical or electrical energy, into kinetic energy, in particular a torque.
  • a form of energy for example thermal / chemical or electrical energy
  • kinetic energy in particular a torque.
  • An “electric motor” in the sense of the present invention is an electromechanical converter (electrical machine) which converts electrical power into mechanical power, in particular into torque.
  • the term electric motor in the context of the present invention includes but is not limited to direct current motors, alternating current motors and three-phase motors or brushed and brushless electric motors or internal rotor and external rotor motors. This is particularly advantageous since electrical energy represents a form of energy that can be easily transmitted in comparison to mechanical or chemical energy, with which the required torque for driving the fan wheel is provided.
  • the struts of the cooling fan module are arranged in front of the fan wheel, viewed in the direction of flow. This is particularly relevant because front and rear struts lead to aerodynamic framework conditions that are significantly different from one another and the fan wheel described here can be used particularly advantageously with front struts, as extensive tests have shown.
  • Another aspect of the present invention relates to the use of a fan wheel of the type described here or a cooling fan module of the type described here in a motor vehicle. This is particularly important since the type of fan wheel described here comes into play in a particularly advantageous manner with the external conditions at the installation site.
  • FIG. 11 shows a front view of a blade 30 of the known fan wheel of FIG Figure 1A with the direction of view from the reference plane in a perspective illustration, the top (corresponds to the suction side) of the fan wheel 1 pointing downwards.
  • the fan wheel 1 has according to the Figure 1A , 1B , 2A , 2 B and 3 a hub pot 10 that is rotationally symmetrical about an axis of rotation R.
  • a plurality of impeller blades 30 are arranged on the hub pot 10 and extend from a cylindrical outer wall 12 of the hub pot 10 extend outward in the radial direction.
  • a direction of rotation D is in the Figure 1A and 2A indicated by an arrow. Accordingly, the direction of rotation is counterclockwise.
  • a main flow direction of the conveyed air is marked with HSR.
  • the fan wheel 1 has an at least substantially circular outer ring 20 which connects the blade tips of the blade blades 30 to one another.
  • the airfoils 30 according to the prior art have flat or curved leading edges VK and flat or curved trailing edges HK in an orthogonal projection.
  • Figure 2A shows a fan wheel 1 according to an embodiment of the present invention in a perspective illustration and Figure 2B a front view of a blade 30 of the fan wheel of FIG Figure 2A with viewing direction from the reference plane E_REF in a perspective representation.
  • Fig. 3 shows a fan wheel 1 from the prior art in a perspective illustration for describing a reference plane E_REF.
  • a reference straight line G_REF is defined by a first point P1 on the axis of rotation R of the fan wheel 1, a radial extension E through the first point P1 and perpendicular to the axis of rotation R and a second point P2, which has an arc-shaped edge at the transition divided from the hub pot 10 to the blade 30 into two equally long sections.
  • the radius is determined which runs through the point P2.
  • Point P2 represents the midpoint of the transition edge from hub cup 10 to blade 30, in particular the edge of blade 30 facing the pot bottom
  • Auxiliary radius runs through P1 and a third point P3 of the transition edge between the cylindrical outer wall and the airfoil and a second auxiliary radius which runs through a fourth point P4 of the transition edge from the hub pot 10 to the airfoil 30 and from this angle which is enclosed between the two auxiliary radii , the bisector is formed.
  • the point at which said bisector intersects the cylindrical outer wall 12, in particular on an outer side thereof, is P2.
  • a reference plane E_REF is defined by a straight line shifted parallel to the axis of rotation R and a straight line shifted parallel to the reference straight line G_REF, the shift being such that it is located completely in front of the blade 30 when viewed in the direction of rotation D of the fan wheel 1.
  • An orthogonal projection of the front edge VK of the airfoil 10 and an orthogonal projection of the rear edge HK of the airfoil 10 are shown on the reference plane E_REF.
  • the direction of view B shows how in the Figure 1B and 2 B a blade segment of the fan wheel 1 is viewed in each case.
  • a coordinate system consisting of the z-axis and y-axis is set up in the reference plane E_REF. This is decisive for the description of the course of the relative position of the front edge POS rel_VK (t) and the course of the relative position of the rear edge POS rel_HK ( t ).
  • the z-axis is defined by an orthogonal projection of the axis of rotation R in the reference plane E_REF, which is shifted in a second step in the reference plane E_REF starting from the orthogonal projection of the axis of rotation R around an outer radius R i of the hub pot 10 in a parallel outward radial direction.
  • the orientation of the z-axis is unchanged, but is shifted in parallel in two steps, namely once by the orthogonal projection onto the reference plane E_REF and then by the shift in the reference plane E_REF by R i .
  • the y-axis is defined by an orthogonal projection of the radial extension E in the reference plane E_REF.
  • the origin this yz coordinate system is defined by the intersection of the two axes.
  • Fig. 4 shows the course of the relative position of the front edge POS rel_VK (t) and the relative position of the rear edge POS rel_HK (t) over the relative unit radius of a fan wheel according to an embodiment of the present invention.
  • the horizontal axis corresponds to the y-axis described above and the vertical axis corresponds to the z-axis described above.
  • the relative unit radius t (r) is plotted on the horizontal axis.
  • the profile of the relative position of the front edge POS rel_VK (t) and the profile of the relative position of the rear edge POS rel_HK (t) are each plotted in standardized form on the vertical axis.
  • t 0 is an offset of the relative unit radius for setting the apex on the hub cup
  • N is the number of oscillations over the axial unit radius
  • a is an oscillation coefficient for scaling the wavelength and setting the position of the, in particular local, extreme point (i.e. for the leading edge: Minimum; for the trailing edge: maximum)
  • a 1 a quadratic polynomial coefficient
  • a 2 a linear polynomial coefficient
  • a 3 a coefficient of the axial threading, ie for setting the linear course of the leading or trailing edge from the hub cup to the blade tip or to the outer ring
  • a 4 describes a relative base deflection ("start" deflection) of the front or rear edge on the hub cup.
  • start deflection
  • the course of the relative position of the rear edge POS rel_HK (t) is in the range from 80% to 100%, in particular 90% to 100%, in particular 92.5% to 97.5%, of the relative unit radius t (r ) of the blade (30) has an, in particular local, maximum and the course of the relative position of the leading edge POS rel_VK (t) in the range from 80% to 100%, in particular 90% to 100%, in particular 92.5% to 97.5 %, of the relative unit radius t (r) of the airfoil (30) has an, in particular local, minimum.
  • Fig. 4 It can also be seen that the course of the relative position of the front edge POS rel_VK (t) and the course of the relative position of the rear edge POS rel_HK (t) are at least essentially axially symmetrical to one another, in particular the rear edge POS rel_HK (t) runs in an area around one geometrically clearly determined course of a mirrored curve of +/- 20%, in particular +/- 10%, of the value of the relative position of the leading edge POS rel_VK (t).
  • the Fig. 5 shows a comparison of a previously known fan wheel 1 with a fan wheel 1 according to an embodiment of the present invention.
  • a total efficiency ⁇ which relates the input power P wel with the generated total pressure gradient ⁇ p t over the conveyed volume flow V ⁇ .
  • ⁇ ⁇ p t V p wel
  • Fig. 6 shows a cooling fan module 100 with the fan wheel 1 according to the present invention according to the second aspect of the present invention.
  • the cooling fan module 100 has a fan frame 2, a fan wheel recess 40 being formed in the fan frame 2, which is delimited by a frame ring 42.
  • a motor holder (covered by the hub cup 10) is arranged within the fan wheel recess 40 and is mechanically connected to the fan frame 2 via struts 44.
  • a motor in particular an electric motor, is at least partially held in the motor holder (also covered by the hub cup 10).
  • a fan wheel 1 is arranged in the fan wheel recess 40 and is driven in rotation by the motor.
  • the fan wheel 1 corresponds to an embodiment of a fan wheel 1 according to the present invention.
  • the struts 44 are according to the embodiment of FIG Fig. 6 Arranged in front of the fan wheel, viewed in the direction of flow, the direction of flow being perpendicular to the figure Fig. 6 shows out.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (9)

  1. Roue de ventilateur (1), en particulier pour un véhicule automobile, comprenant
    un pot de moyeu (10) en particulier à symétrie de rotation autour d'un axe de rotation (R) ; et
    une pluralité de pales (30) disposées sur le pot de moyeu (10) et s'étendant radialement vers l'extérieur depuis une paroi extérieure (12) du pot de moyeu (10), qui est en particulier au moins sensiblement cylindrique,
    dans laquelle chaque pale (30) a un bord d'attaque (VK) et un bord de fuite (HK), dans laquelle pour au moins une pale (30), en particulier certaines des pales (30), en particulier toutes les pales (30) le suivant s'applique :
    une ligne de référence (G_REF) est définie par :
    un premier point (P1) sur un axe de rotation (R) de la roue de ventilateur (1) ;
    une extension radiale (E) passant par le premier point (P1) et perpendiculaire à l'axe de rotation (R) ; et
    un deuxième point (P2), qui divise un bord arqué à la transition du pot de moyeu (10) à la pale (30) en deux sections de longueur égale,
    dans laquelle un plan de référence (E_REF) est défini par une ligne droite déplacée parallèlement à l'axe de rotation (R) et une ligne droite déplacée parallèlement à la ligne de référence (G_REF), le déplacement étant tel que, vu dans le sens de rotation (D) de la roue de ventilateur (1), il est situé entièrement devant la pale (30),
    dans laquelle une projection orthogonale du bord d'attaque (VK) de la pale (30) et une projection orthogonale du bord de fuite (HK) de la pale (30) sont cartographiées dans le plan de référence (E_REF) ;
    dans laquelle, dans le plan de référence (E_REF), un axe z est défini par une projection orthogonale de l'axe de rotation (R) dans le plan de référence (E_REF), qui est déplacé d'une manière radialement parallèle vers l'extérieur dans le plan de référence (E_REF) à partir de la projection orthogonale de l'axe de rotation (R) d'un rayon extérieur (Ri) du pot de moyeu (10);
    dans laquelle un axe y est défini dans le plan de référence par une projection orthogonale de l'extension radiale (E) dans le plan de référence (E_REF) ;
    dans laquelle un rayon unitaire relatif t(r) est tracé sur l'axe y, ledit rayon unitaire relatif t(r) étant défini comme suit : t r = r − R i R a − R i
    Figure imgb0019
     dans laquelle
    Ri est un rayon extérieur du pot de moyeu (10), qui correspond en particulier au moins sensiblement à un rayon intérieur de la pale (30) ;
    Ra est un rayon extérieur de la pale (30) ; et
    r est la distance entre l'axe de rotation (R) et le plan de coupe (S) à considérer, qui est perpendiculaire à la ligne de référence associée (G_REF) à une distance r de l'axe de rotation (R), dans laquelle s'applique : r∈[Ri ;Ra ]
    dans laquelle une position relative du bord d'attaque POSrel_VK et une position relative du bord de fuite POSrel_HK sont tracées sur l'axe z,
    dans laquelle l'évolution de la position relative du bord d'attaque POSrel_VK(t) et l'évolution de la position relative du bord de fuite POSrel_HK(t) ont une forme ondulée apériodique,
    dans laquelle la position relative du bord d'attaque POSrel_VK(t) est référencée à un troisième point (P3), qui, vu dans la direction de rotation (D) de la roue de ventilateur (1), est le point le plus en avance à la transition entre le pot de moyeu (10) et la pale (30) ; et la position relative du bord de fuite POSrel_HK(t) est référencée à un quatrième point (P4), qui est le point le plus en arrière à la transition entre le pot de moyeu (10) et la pale (30), vu dans la direction de rotation (D) de la roue de ventilateur (1),
    dans laquelle la pale (30) est une pale (30) inclinée vers l'arrière, vu dans la direction de rotation (D), de sorte que la pointe de la pale suit le centre de la pale avec le rayon extérieur (Ra), vu dans la direction de rotation.
    dans laquelle la roue de ventilateur (1) a un anneau extérieur au moins sensiblement circulaire (20), qui relie des extrémités de pale des pales (30),
    dans laquelle l'évolution de la position relative du bord de fuite POSrel_HK(t) a un maximum dans la plage de 80 % à 100 % du rayon unitaire relatif t(r) de la pale (30) ; et
    dans laquelle l'évolution de la position relative du bord d'attaque POSrel_VK(t) a un minimum dans la plage de 80 % à 100 % du rayon unitaire relatif t(r) de la pale (30).
  2. Roue de ventilateur selon l'une des revendications précédentes, dans laquelle l'évolution de la position relative du bord de fuite POSrel_HK(t) a un maximum, en particulier un maximum local, dans la plage de 90 % à 100 %, en particulier de 92,5 % à 97,5 %, du rayon unitaire relatif t(r) de la pale (30).
  3. Roue de ventilateur selon la revendication précédente, dans laquelle l'évolution de la position relative du bord de fuite POSrel_HK(t) dans la direction y après le maximum, en particulier local, n'a pas de point bas ou qu'au plus un point bas.
  4. Roue de ventilateur selon l'une des revendications précédentes, dans laquelle l'évolution de la position relative du bord d'attaque POSrel_VK(t) et l'évolution de la position relative du bord de fuite POSrel_HK(t) sont au moins sensiblement axisymétriques l'une par rapport à l'autre, en particulier le bord de fuite POSrel_HK(t) s'étend dans une zone autour d'une allure déterminée géométriquement sans ambiguïté d'une courbe en miroir de +/- 20 %, en particulier +/- 10 %, de la valeur de la position relative du bord d'attaque POSrel_VK(t).
  5. Roue de ventilateur selon l'une des revendications précédentes, dans laquelle l'évolution de la position relative du bord d'attaque POSrel_VK(t) en fonction du rayon unitaire relatif t(r) satisfait à la condition suivante : POS rel _ VK t = − A 1 t 2 + A 2 t cos 2 πN a 1 − t + 1 t + t 0 + A 3 t + A 4 R a − R i
    Figure imgb0020
     dans laquelle s'applique :
    t 0∈[0;0,5]
    N∈[1;8]
    a∈[-1,5;1,5]
    A 1∈[-10;10]
    A 2∈[-10;10]
    A 3[-10;10] et
    A 4∈[-10;10].
  6. Roue de ventilateur selon l'une des revendications précédentes, dans laquelle l'évolution de la position relative du bord de fuite POSrel_HK(t) en fonction du rayon unitaire relatif t(r) satisfait à la condition suivante : POS rel _ HK t = A 1 t 2 + A 2 t cos 2 πN a 1 − t + 1 t + t 0 + A 3 t + A 4 R a − R i
    Figure imgb0021
     dans laquelle s'applique :
    t 0∈[0;0,5]
    N∈[1;8]
    a∈[-1,5;1,5]
    A 1∈[-10;10]
    A 2∈[-10;10]
    A 3∈[-10;10] et
    A 4∈[-10;10].
  7. Module de ventilateur de radiateur (100), en particulier pour un véhicule automobile, comprenant :
    un cadre de ventilateur (2) ;
    un évidement de roue de ventilateur (40) formé dans le cadre de ventilateur (2), l'évidement de roue de ventilateur (40) étant délimité par un anneau de cadre (42) ;
    un support de moteur, qui est disposé à l'intérieur de l'évidement (40) de la roue du ventilateur et qui est relié mécaniquement au cadre (2) du ventilateur par des entretoises (44) ;
    un moteur, en particulier un moteur électrique, qui est au moins partiellement maintenu dans le support de moteur ; et
    une roue de ventilateur (1), qui est disposée dans l'évidement de roue de ventilateur (40) et qui est entraînée en rotation par le moteur,
    caractérisé en ce que
    la roue de ventilateur (1) est formée selon l'une des revendications précédentes.
  8. Module de ventilateur de radiateur selon la revendication précédente, dans laquelle les entretoises (44) sont disposées en avant de la roue de ventilateur (1), vu dans la direction de l'écoulement.
  9. Utilisation d'une roue de ventilateur selon l'une des revendications 1 à 6 ou d'un module de ventilateur de radiateur selon l'une des revendications 7 ou 8 dans un véhicule automobile.
EP18190529.0A 2017-09-05 2018-08-23 Roue de ventilateur et module de ventilateur de refroidissement doté d'une telle roue de ventilateur Active EP3450716B1 (fr)

Priority Applications (1)

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DE102017008293.6A DE102017008293A1 (de) 2017-09-05 2017-09-05 Lüfterrad und Kühlerlüftermodul mit einem solchen Lüfterrad

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KR (1) KR102208327B1 (fr)
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EP3816454A4 (fr) * 2018-05-09 2022-01-26 York Guangzhou Air Conditioning and Refrigeration Co., Ltd. Pale et turbine à flux axial utilisant celle-ci
DE102019216704A1 (de) * 2019-10-30 2021-05-06 Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg Lüfterrad für einen Kühlerlüfter eines Kraftfahrzeugs
DE102021105226A1 (de) 2020-03-10 2021-09-16 Ebm-Papst Mulfingen Gmbh & Co. Kg Ventilator und Ventilatorflügel
CN111904150B (zh) * 2020-06-15 2022-04-08 宁波大学 一种智能自动散热电脑桌
DE102021201750A1 (de) 2021-02-24 2022-08-25 Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg Kühlerlüftermodul für ein Kraftfahrzeug
US11808282B1 (en) 2022-03-02 2023-11-07 Aaon, Inc. Propeller fan assembly with silencer seeds and concentric hub and method of use
DE102023200065A1 (de) * 2023-01-04 2024-07-04 Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg Lüfterrad und Lüftervorrichtung mit einem solchen Lüfterrad

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ES2893474T3 (es) 2022-02-09
CN109424581A (zh) 2019-03-05
US11022139B2 (en) 2021-06-01
EP3450716A1 (fr) 2019-03-06
MX2018010666A (es) 2019-03-07
KR102208327B1 (ko) 2021-01-26
US20190072105A1 (en) 2019-03-07
RS62490B1 (sr) 2021-11-30
KR20190026622A (ko) 2019-03-13
DE102017008293A1 (de) 2019-03-07
CN109424581B (zh) 2021-06-11

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