EP0945626B1 - Ventilateur en particulier pour un système de refroidissement des machines à combustion - Google Patents

Ventilateur en particulier pour un système de refroidissement des machines à combustion Download PDF

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Publication number
EP0945626B1
EP0945626B1 EP99105936A EP99105936A EP0945626B1 EP 0945626 B1 EP0945626 B1 EP 0945626B1 EP 99105936 A EP99105936 A EP 99105936A EP 99105936 A EP99105936 A EP 99105936A EP 0945626 B1 EP0945626 B1 EP 0945626B1
Authority
EP
European Patent Office
Prior art keywords
fan wheel
fan
actuating
fan blades
wheel according
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.)
Expired - Lifetime
Application number
EP99105936A
Other languages
German (de)
English (en)
Other versions
EP0945626A3 (fr
EP0945626A2 (fr
Inventor
Karl Hägele
Gebhard Munz
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.)
Hagele GmbH
Haegele GmbH
Original Assignee
Hagele GmbH
Haegele GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from DE19813372A external-priority patent/DE19813372C2/de
Priority claimed from DE19840843A external-priority patent/DE19840843B4/de
Application filed by Hagele GmbH, Haegele GmbH filed Critical Hagele GmbH
Publication of EP0945626A2 publication Critical patent/EP0945626A2/fr
Publication of EP0945626A3 publication Critical patent/EP0945626A3/fr
Application granted granted Critical
Publication of EP0945626B1 publication Critical patent/EP0945626B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04D19/00—Axial-flow pumps
    • F04D19/002—Axial flow fans
    • F04D19/005—Axial flow fans reversible fans
    • 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
    • F04D29/34—Blade mountings
    • F04D29/36—Blade mountings adjustable
    • F04D29/362—Blade mountings adjustable during rotation
    • F04D29/364—The blades having only a predetermined number of possible positions

Definitions

  • the invention relates to a fan wheel, in particular a Cooling system of internal combustion engine usable fan wheel, according to the preamble of claim 1.
  • Fan wheels that can be used in cooling systems of internal combustion engines are also known from DE 4438995 A1.
  • starting point is a motor cooling system for the known solution heavy construction machines that are used both in driving and in Stand operation can be used and where the fan wheel turns higher when driving than when stationary.
  • Corresponding are the cooling capacities achieved via the fan wheel larger when driving than when stationary. For stand operation such an interpretation can then result in inadequate Cooling capacities result when the internal combustion engine is heavily loaded during stationary work.
  • the known solution is kept constant the speed of the fan wheel its conveying direction vice versa, once towards the internal combustion engine and to promote it in the opposite direction.
  • the fan wheel inside its hub with an adjusting device provided, through which the wings of the fan wheel as far can be rotated so that the conveying direction is reversed, so that a forward blowing direction and a backward blowing direction can be realized in relation to the Cooling the internal combustion engine cooling performance by reversing adapt the conveying direction to the respective cooling requirement to be able to.
  • the invention has the design of a fan wheel type mentioned at the beginning to the task, with the objective to a simple, small and flat building basic construction for the fan wheel to come which allows it to be related on the direction of rotation with the same direction of rotation reversible fan wheel instead of conventional fan wheels in use existing constructions, what by the characteristics of claim 1 is achieved.
  • the actuator can, with only a short-term connection the compressed air source to build the required Signal pressure and then shutdown, time-controlled switching from the backward blowing direction as a short-time working position to the normal working position as the forward blowing direction can already be realized in that the pressure reduction time-delayed or time-controlled.
  • the holding time of the pressure, and thus the determination of one Time period in which the so-called short-time working position is maintained is obtained before the changeover is initiated by pressure reduction can be controlled in a simple manner by both pneumatic and hydraulic Actuation that in the inlet from the work area on the throttle Check valve is arranged, for example a 2/2 way valve, that blocks the process in one switch position and in the other switching position the flow on the throttle releases.
  • the fan blades in their respective end position via one of the actuating device independent, arbitrary towards the end position Holding force, especially those acting on the fan blades Air resistance is applied, it is connected with a prescribed, time-controlled pressure reduction possible to design the actuator so that a quasi sudden change between the two end positions not only when switching from the regular work position to the short-time working position, but also when changing over to the reverse Direction.
  • a switch from the regular work position to the short-time position is essentially related to the switchover time only from the capacity of the pressure source or one corresponding storage volume as a supply source.
  • the backward blowing direction characterized above to maintain as a short-time position over a longer period of time, for example in that the throttle related to the amount of compressed air supplied is adjusted so that at a slightly higher actuation pressure, a state of equilibrium sets, or that in the inlet on the throttle Check valve is arranged.
  • a simple structure also contributes in particular if based on the axial conveying direction of the fan wheel, the the eccentric pins assigned to the fan blades in their two, the standard work position and the short-time position corresponding end positions about the same, but preferred in the same through the axis of rotation of the fan wheel Radial plane. This results in the two end positions the same position of the fan blades, and therefore also one equally large self-holding power in both end positions.
  • the eccentric pin it is also possible to adjust the wing positions to influence in the end positions so that these for the two working positions are not symmetrical to one Axis of rotation of the fan wheel vertical radial plane, with following the change in the corresponding self-holding forces and the flow rates.
  • the fan blades are - seen radially from the outside - each curved opposite to the conveying direction, so that in Cut for the fan blades against the conveying direction Directional convex curvature results, which in the conveying direction forward end of the respective shovel one predominantly has axial extension, and that related to the direction of conveyance rearward end is largely radial Extent shows.
  • For the changeover between the funding directions proves to be a rotation of the wings around their respective central axis as expedient, with an angle of preferably more than 90 °, in particular with an angle of the order of about 110 °, both due to the shape of the wing profile, and / or the angle of attack and / or the axial distance of the in the conveying direction at the front of the respective wing edge
  • the axis of rotation of the fan blade is the size of the self-holding force can be influenced.
  • the starting point for this is that for a variety of purposes, especially for work machines, such as agricultural and stationary machines, as well as commercial vehicles, and here in particular agricultural vehicles like tugs the internal combustion engine mostly inside operated in a relatively narrow working area is so that for a continuous adjustment of the fan blades there is no need.
  • the mentioned work area is usually one below the maximum speed Area of the internal combustion engine in which related to the maximum torque achievable for this range or maximum performance achievable for this area is a high, there is in particular maximum cooling power requirement. outgoing from this area the grows with increasing speed Air flow rate and the cooling capacity that can be achieved via this usually more than the respective maximum cooling capacity requirement.
  • This can be done by the configuration according to the invention Are taken into account in which the angle of attack of the Fan blades - in the sense of a reduction in cooling capacity-in Direction of smaller air flow is adjusted, whereby this can happen directly depending on the speed.
  • Such a speed-dependent adjustment can be independent inventive solution can be achieved via the actuating force, those acting on the fan blades depending on the air resistance Power results, which increases with the speed, so that, based on the working area mentioned, maximum Cooling power requirement, an adjustment can be made can, in which the air resistance dependent actuating force to a resilient support is in balance. If this work area is exited upwards, i.e. the RPM increased further, so with the increased Speed a correspondingly higher air resistance dependent Positioning force, and there will be the fan blades against the elastic Support swiveled to a smaller angle of attack, where it is expedient, the allowable minimum angle of attack limit by a fixed stop.
  • the temperature-dependent adjustability according to the invention if appropriate also combined as temperature and speed dependent Adjustability carried out also gives the security, that in the case of a higher cooling capacity requirement in Speed range above the specified working range there is no cooling capacity deficit, as with increased Temperature and corresponding repercussions on the temperature-dependent working stop element in the fan blades above, i.e. beyond the work area mentioned adjusted speed range in their angle of attack or can be set to an angle of attack that corresponds to the maximum delivery rate if this is temperature-dependent working stop element is designed so that it also occur depending on the speed, higher depending on the air resistance Withstands actuating forces.
  • Springs in particular, can be used as elastic stop elements Coil springs as temperature-dependent stop elements in particular expansion elements are used.
  • the hub 4 comprises a cup-shaped hub body 5, which comprises a bottom part 6 and the cup wall 7, the cup wall serving as the peripheral wall of the hub body 5 7 via a cover 8 opposite the bottom part 6 is covered so that the hub 4 has a bottom part 6, Cup wall 7 and cover 8 has limited interior 9.
  • the interior 9 takes an actuating piston 11, the one adjacent to the bowl wall 7, cylindrical Piston wall 12 and a piston crown 13 comprises, piston wall 12 and piston crown 13 delimit the piston interior 14, which is open against the bottom part 6 of the hub 4.
  • the piston crown 13 of the actuating piston 11 in the area of the piston crown 13 via ring seals 15 is sealed against the bowl wall 7, a work space 16 from a supply opening 17 to a Pressure source, which is not shown here, to connect is.
  • There is also an outflow opening 19 in the cover 8 arranged in the context of the invention as a throttle bore is trained.
  • the control piston is in the direction of the cover 8 11 resiliently loaded, this support in the exemplary embodiment according to FIG Coil spring 20 takes place as a support element, the diameter about the diameter of the piston interior accommodating them 14 corresponds.
  • a positioning pin 24 comprises, which in a provided in the piston wall 12 Recess engages 25, which is preferably a receiving bore, especially as the blind pin 24 leading the adjusting pin is trained.
  • the connecting part is not shown in the exemplary embodiment 3 associated to cover the bearing 21, circumferential Hub cover 4.
  • FIG. 2 corresponds to that according to Figure 1 very largely. Accordingly find for same Parts use the same reference numerals.
  • the actuating piston designated 31 in this exemplary embodiment are as resilient supports - support elements - But several coil springs 32 over the circumference distributed assigned, each in support against the bottom part 6 of the cup-shaped hub body in one in the back of the actuating piston 31 provided recess 33 are.
  • FIGS. 3 and 4 show in highly schematic representation of the assignment of the fan wheel 1 to the cooler of an internal combustion engine only indicated 18, this cooler being designated 40 and being for the respective fan wheel 1 shown only one fan blade 42 is.
  • This is the fan blade 42 that is shown in FIG View with respect to its adjustment axis of rotation 23 in one perpendicular to the plane of the drawing, the axis of rotation 10 of the fan wheel 1 containing level, so that in the bowl wall 7 provided receiving hole 43 for the storage of Connection part 3 of the respective fan blade 42 symmetrical to this level.
  • FIG. 3 corresponds to a conveying direction of the fan wheel 1, as indicated by arrow 46 so that air through the cooler 40 is sucked in.
  • the result is with the axial displacement of the actuating piston 11 or 31 a rotation of the adjusting pin 24 about the respective bearing axis 23 of the associated fan blade, and therefore due the non-rotatable connection between the eccentric Adjustment pin 24 and the respective fan blades a twist of the fan blade.
  • the axial adjustment path of the actuating piston 11 or 31 is dimensioned that by interacting with the eccentric Adjustment pin 24 a rotation of the fan blade 42, in Embodiment results in a rotation (arrow 56) over 110 °, the fan blade 42 in its two end positions one to the plane of symmetry through the axis of rotation 23 of the fan blade 42, which is perpendicular to the axis of rotation 10 of the fan wheel 1 stands, assumes a symmetrical position. Accordingly is the delivery behavior of the fan wheel in the embodiment 1 in both conveying directions, arrows 46 and 47 the same.
  • the angle of rotation for the fan blades 42 can, even if a Angle of 110 ° is particularly advantageous, and an angle of 110 ° in particular with the blade configuration described proves to be particularly advantageous, especially for arched blade cross sections may also be smaller, with also angles of less than 90 °, approximately 70-90 ° according to the invention can be realized especially if in a Delivery direction a smaller delivery rate than in the other Direction is accepted, which is partly also sought can be.
  • a particularly high output for the short-time position is sought to e.g. if the Cooler 40 to achieve a quick blow-out, which for the Regulating work position required funding however comparatively is low.
  • the fan blades 42 are each plane of symmetry arched opposite to the respective conveying direction, whereby the curved curve 49 formed by the fan blade 42 and the chord 48 connecting the ends of the fan blades Describe a segment of a circle, its chord 48 at an angle 52 of about 50-60 °, in the exemplary embodiment about 55 ° to the to the axis of rotation 10 parallel conveying direction.
  • the chord 48 and the curved curve 49 of the fan blade are currently lying 42 on different sides of the axis of rotation 23 extending straight line 50, the line given by the chord 48 Width of the fan blade essentially its radius of curvature equivalent.
  • the center of curvature 53 for the Curved curve 49 lies on a perpendicular to the chord 48 Straight 51 through the axis 23, to which the curved curve 49 is symmetrical lies.
  • the circumferential angle 54 of the curved curve 49 is in the embodiment between 55 and 75 °, preferred about 65 °.
  • the configuration of the fan blade 42 described enables for both end positions and regardless of the Position of the fan blade 42 constant direction of rotation 55 of the fan wheel 1 in a simple manner, i.e. without additional mechanical effort the realization of a self-holding effect due to the effect on the fan blade 42 Air resistance.
  • the fan blade is in both end positions 42 through the air resistance towards the end position applied. Accordingly, within the framework of solution according to the invention no other special security this end position, e.g. a flapping of the wings to avoid.
  • a fan wheel 1 can thus be realized according to the invention, in which the actuating piston 11, 31 of the actuating device in the Forward blowing direction 46, which corresponds to the normal working position only via the resilient resetting device is loaded by the spring 20 or the springs 32 is formed. There are high preloads not necessary, since the wing 2 or 42 in this normal working position corresponding position according to Figure 3 also over the air resistance they are subjected to, so that there are no fluttering movements for the fan blades.
  • the actuating piston 11 or 31 is pressurized, so is in the solution according to the invention, in which the control piston 11 or 31 is axially pressurized and one of the hub surface largely corresponding, and thus very large exposure area has only a low signal pressure required and the system can therefore be operated at low pressure operate.
  • the piston 11 or 31 against the resilient support (springs 20, 32) and the fan blades 42 reach it a position according to Figure 4, in the direction of the cooler 40 is blown (reverse blowing direction 47 or short-time working position).
  • the pressurization is what is not shown here is, by switching on a pump or a compressor same can be done, but also by connecting to a low-pressure storage system, interrupted, so takes place Pressure reduction due to the air flowing out through the discharge opening 19, which in training as a throttle opening depending of the throttle cross-section offers a possibility of reducing pressure time-controlled.
  • the throttle opening of course also elsewhere in the work room outgoing drain path can be arranged.
  • the throttle a check valve assign, be it upstream, downstream or in the throttle integrated to the holding time via this valve to determine the pressure in the working chamber, and thus independently from the connection of the working chamber to the pressure source, as soon as in the Chamber of Labor for the switch to the Short-time working position required pressure is built up.
  • hydraulic actuation of the control piston is advisable and advantageous, especially with hydraulic actuation in many Cases, such as with tugs on existing ones hydraulic systems and their pressure supply can be.
  • a pressure accumulator in particular a pressure bladder accumulator provided such that after switching off the pressure source Maintain pressure in the work area even with certain leaks can be.
  • a choke in the drain the actual switching time also to be determined for a hydraulic system, since according to Release of the process of pressure medium from the pressure accumulator in the work area is moved up and from there via the throttle flows out, while reducing the Pressure in the pressure accumulator and working chamber System, so that the switch to the normal working position can also happen almost suddenly if this System pressure has dropped to a value at which the the actuating force acting on the piston is smaller than that on the Spring-applied restoring force.
  • Fan wheel created the use of such a fan wheel particularly useful in the cooling system of internal combustion engines does, especially when the short-time position with reversal of the conveying direction the normal working position is to be used, the cooler, or the inflow path to the fan wheel, based on the direction of air flow in the normal work position by reversal to blow the direction of flow. See Figure 9.
  • the changeover to the short-time working position for cleaning purposes can depend on air resistance or other appropriate parameters, such as changes the cooling water temperature and the like take place automatically, or manually, with only a short-term Formwork of the pressure source is required to the To switch to the short-time position. Accordingly is also the energy requirement for the operation of the invention Fan wheel extremely low, especially, as explained, the reversal in the opposite direction without active Actuators is carried out.
  • FIG. 6 shows a structure corresponding to that of FIG. 1 Illustration shows and use the same reference numerals Find.
  • deviant 1 is the actuating piston 11 starting from the working space 16 with receiving openings 75, 76 provided, which penetrates the piston crown 13 closed are executed and in which stop elements 77 and 78 are to be arranged are that are supported against the cover 8.
  • a support spring is provided as a stop element 78 an expansion element, as may be commercially available is to be acquired.
  • the stop elements 77, 78 form speed or temperature dependent position-adjustable stop limits to which the Piston 11 in the opposite direction to the coil spring 32 as elastic resilient support element is supported, the Piston 11 has an edge 79 which, when in contact with cover 8 acts as a fixed stop.
  • Figure 7 shows the schematic representation of the actuating piston 11 when viewed in the direction of arrow 80 in FIG. 6, for example, possible arrangements for the stop elements 77, 78 and those acting in the opposite direction Coil springs 32, the one shown on the left in FIG Design a radially staggered arrangement for the stop elements 77 or 78 indicates, while the right-hand side Representation of this with an arrangement offset in the circumferential direction shows.
  • the resilient acting from the opposite side Support symbolized by the coil spring 32 to set gap, for example in the left-hand side Representation near the piston wall, and in the right-hand side Representation close to the center. This way you can get an even one Reach the piston support from both sides of the piston, so that the piston is not subjected to tilting forces.
  • FIG. 8 shows, starting from a position of the hub 4 according to FIG 6, and thus based on an arrangement of the fan wheel 1 according to Figure 9, the position for a fan blade 42 in in Direction of the internal combustion engine 18 given conveying direction 46, the direction of rotation of the fan wheel 1 by the Arrow 81 is symbolized, corresponding to a direction of rotation 55th
  • the axis of rotation 10 of the fan wheel 1 contained level lies so that the receiving bore provided in the cup wall 7 43 for the storage 21 of the connector 3 symmetrical to this level.
  • the fan blade 42 promotes in the 8 in the direction of arrow 46, ie in Direction to the internal combustion engine 18, and that in solid lines shown position of the fan blade 42 corresponds to a Position of the adjusting pin 24 according to FIG. 6.
  • the adjusting pin 24 is only indicated schematically in FIG. 8.
  • A corresponds to the work area mentioned above certain cooling capacity requirements, and therefore also a certain one Temperature level to which the hub 4 is exposed.
  • a temperature-dependent expansion element as a stop element, indicated in Figure 6 with 78, can a position in relation to the addressed temperature of the piston 11 by appropriate deflection of the expansion element 78 reach, in the sense of the description above a position of the fan blade 42 corresponds to how it is shown in full lines in FIG. 8 and in turn corresponds to a maximum cooling capacity requirement.
  • stop elements spring-elastic stop elements (Spring 77) and temperature-dependent stop elements (Expansion element 78) used, so complete the corresponding functions and it is dependent on the temperature working, especially as an expansion element 78 trained stop element ensures that with appropriate Cooling power requirement independent of the speed via the temperature-dependent stop element Angle of attack for the fan blade 42 is controlled, which takes into account the increased cooling capacity requirement, whereby relatively small travel ranges for the respective support elements are given and needed.
  • FIG. 9 shows a preferred one for a fan wheel 1 according to the invention Can be used in conjunction with a tractor, the tractor being designated 82 overall and has a frame part 83, the front in the area of Front axle is supported via wheels 84.
  • the front axle between the wheels 84 is the internal combustion engine 18, the cooler 40 is structurally upstream, wherein the fan wheel between the cooler 40 and the internal combustion engine 18 1, for example one according to the invention equipped fan wheel 1, which on the crankshaft of the Internal combustion engine 18 is driven in the usual way.
  • a connection frame 85 is provided at the front end of the frame 83, on which devices or the like, for example Have it attached using a three-point lifting device.

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Claims (15)

  1. Ventilateur (1), notamment ventilateur pouvant être utilisé dans le système de refroidissement de moteurs à combustion interne, comprenant un moyeu (4) et des pales de ventilateur (2) réglables, qui sont guidées de manière rotative dans la paroi périphérique du moyeu et qui peuvent être réglées par un entraínement de commande situé dans le moyeu en forme de cuvette, qui comprend un élément de réglage sollicité par ressort dans une position de départ et un excentrique de réglage situé dans sa transition aux pales du ventilateur, qui peuvent être sollicités par l'élément de réglage, l'élément de réglage étant formé par un vérin se raccordant de manière hermétique contre la paroi en forme de cuvette et disposé concentriquement et guidé sur celle-ci,
    caractérisé en ce que
    la paroi (12) du vérin (11) se situe sous forme de bague de réglage pour la réception de tourillons de réglage (24) de l'excentrique de réglage en recouvrement axial par rapport aux pales du ventilateur (2) et en ce que les pales du ventilateur (2, 42) peuvent être commutées par la sollicitation du vérin (11) avec du fluide sous pression dans un sens d'écoulement (47) opposé au sens d'écoulement(46) dans la position de départ et peuvent être sollicitées dans les deux sens d'écoulement opposés l'une à l'autre (46, 47) dans le sens de la position des pales correspondant au sens d'écoulement respectif (46, respectivement 47).
  2. Ventilateur selon la revendication 1,
    caractérisé en ce que
    les pales de ventilateur (2, 42) sont sollicitées dans le sens de position des pales correspondant au sens d'écoulement respectif (46, respectivement 47) par le biais de la force de la résistance de l'air.
  3. Ventilateur selon la revendication 1 ou 2,
    caractérisé en ce que
    les pales du ventilateur (2, 42) sont sollicitées dans leur position extrême respective par la force de la résistance de l'air en tant que force de retenue automatique indépendante du dispositif de réglage, agissant dans le sens de sa position extrême respective, laquelle est plus petite que la force de rappel qui agit par la force de ressort à l'opposé de la sollicitation par le fluide sous pression sur le vérin (11).
  4. Ventilateur selon l'une quelconque des revendications 1 à 3,
    caractérisé en ce que
    par rapport au sens d'écoulement axial du ventilateur (1), les tourillons de réglage (24) se situent dans les deux positions extrêmes correspondant aux sens d'écoulement opposés (46, respectivement 47) du même côté d'un plan radial contenant l'axe de rotation (10) du ventilateur (2, 42).
  5. Ventilateur selon l'une quelconque des revendications précédentes,
    caractérisé en ce que les pales du ventilateur (2, 42) - en vue radiale - sont courbées dans leurs deux positions extrêmes correspondant aux sens d'écoulement opposés (46, respectivement 47) à chaque fois à l'opposé du sens d'écoulement (46, respectivement 47).
  6. Ventilateur selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    les pales du ventilateur (2, 42) sont tournées l'une vers l'autre entre leurs positions extrêmes par rapport à leur axe de rotation (23) sur plus de 90°, notamment sur environ 110°.
  7. Ventilateur selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    les pales du ventilateur (2, 42), en vue radiale et par rapport au sens de rotation (55) du ventilateur (1) sont courbées à chaque fois à l'opposé du sens de rotation (55).
  8. Ventilateur selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    les pales du ventilateur (2, 42) - en vue radiale et par rapport au sens de rotation (55) du ventilateur (1) - s'étendent avec leur extrémité arrière obliquement par rapport au sens d'écoulement respectif (46, respectivement 47) à l'encontre du sens de rotation (55) du ventilateur (1) vers l'arrière et avec leur extrémité avant essentiellement dans le sens périphérique du ventilateur (1).
  9. Ventilateur selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    la position de départ du vérin (11, 31) pouvant être atteinte par le support élastique (ressort 20) à l'encontre du sens de réglage par sollicitation avec un fluide sous pression correspond à une position de travail normale (sens d'écoulement 46) et la position extrême du vérin (11, respectivement 31) pouvant être atteinte par le biais de la sollicitation avec un fluide sous pression correspond à une position de travail momentanée (sens d'écoulement 47).
  10. Ventilateur selon la revendication 9,
    caractérisé en ce que
    la position des pales de ventilateur (2, 42) de la position de travail momentanée (sens d'écoulement 47) à la position de travail normale (sens d'écoulement 46) peut être commutée notamment par diminution commandée dans le temps de la pression existant après la déconnexion de la source de pression.
  11. Ventilateur selon l'une quelconque ou plusieurs des revendications précédentes,
    caractérisé en ce que
    la position de départ sollicitée par ressort du vérin (11, 31) est limitée par une butée à l'encontre de la force du ressort et la position de la limitation par butée peut être modifiée en fonction du régime et/ou de la température.
  12. Ventilateur selon la revendication 11,
    caractérisé en ce que
    la position de départ correspond à une position des pales (42) du ventilateur (1) dans laquelle une puissance d'écoulement plus importante, notamment dans la région du maximum, est fournie et en ce que la position de départ est associée à une plage de travail du moteur à combustion interne (18) dans laquelle un régime se trouvant sous le régime maximal du moteur à combustion interne (18) et un besoin en puissance de refroidissement supérieur, notamment dans la région du maximum, sont donnés.
  13. Ventilateur selon l'une quelconque des revendications 11 ou 12,
    caractérisé en ce que
    la limitation par butée est formée par le vérin (11, 31) de manière élastiquement flexible dans le sens d'éléments de butée sollicitant la position de départ (élément en matériau extensible 27, ressort 28).
  14. Ventilateur selon la revendication 13,
    caractérisé en ce que
    le support servant de limitation de butée est formé par au moins un ressort (28) et/ou par au moins un élément se composant de matériau élastique, en particulier de matériau en plastique élastomère et/ou par au moins un élément de support de longueur variable en fonction de la température, notamment un élément en matériau extensible.
  15. Ventilateur selon la revendication 13 ou 14,
    caractérisé en ce que
    les éléments de butée (27, 28) servant de limitation de butée peuvent être déplacés de leur position correspondant à la position de départ de la pale du ventilateur (1) par la force de réglage sollicitant la pale de ventilateur, dépendant de la résistance de l'air, de telle sorte que les pales de ventilateur (1) puissent être déplacées en fonction de la force de commande dépendant de la résistance de l'air dans une position de puissance d'écoulement réduite.
EP99105936A 1998-03-26 1999-03-24 Ventilateur en particulier pour un système de refroidissement des machines à combustion Expired - Lifetime EP0945626B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE19813372A DE19813372C2 (de) 1998-03-26 1998-03-26 Lüfterrad, insbesondere im Kühlsystem von Brennkraftmaschinen einsetzbares Lüfterrad
DE19813372 1998-03-26
DE19840843A DE19840843B4 (de) 1998-09-07 1998-09-07 Stellvorrichtung für ein im Kühlsystem von Brennkraftmaschinen einsetzbares Lüfterrad
DE19840843 1998-09-07

Publications (3)

Publication Number Publication Date
EP0945626A2 EP0945626A2 (fr) 1999-09-29
EP0945626A3 EP0945626A3 (fr) 2001-04-04
EP0945626B1 true EP0945626B1 (fr) 2004-12-08

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EP99105936A Expired - Lifetime EP0945626B1 (fr) 1998-03-26 1999-03-24 Ventilateur en particulier pour un système de refroidissement des machines à combustion

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DE (1) DE59911215D1 (fr)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
US9086076B2 (en) 2009-12-18 2015-07-21 Flexxaire Inc. Variable pitch fan having a pitch sensor

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Publication number Priority date Publication date Assignee Title
US6439850B1 (en) 1998-07-15 2002-08-27 Flexxaire Manufacturing Inc. Variable pitch fan
DE19959893B4 (de) * 1999-12-11 2004-07-08 Hägele GmbH Angetriebenes Lüfterrad, insbesondere für Brennkraftmaschinen
DE10153099B4 (de) * 2001-10-30 2006-12-14 Hägele GmbH Axiallüfter, insbesondere im Kühlsystem einer Brennkraftmaschine einsetzbarer Axiallüfter
CA2403632C (fr) 2002-09-17 2011-04-05 Flexxaire Manufacturing Inc. Ventilateur a pas variable
DE102004035631B4 (de) * 2004-07-22 2006-04-13 Hägele GmbH Lüfterrad, insbesondere im Kühlsystem von Brennkraftmaschinen einsetzbares Lüfterrad
DE102007039422B4 (de) * 2007-08-21 2009-05-28 Daimler Ag Sitzbelüftungseinrichtung eines Polsters eines Fahrzeugsitzes
DE102008008275A1 (de) 2008-02-07 2009-08-20 Hägele GmbH Lüfterflügel für Lüfterräder
DE102011001426A1 (de) 2011-03-21 2012-09-27 Hägele GmbH Brennkraftmaschine mit einem Lüftersystem
DE102018114534B4 (de) * 2018-06-18 2020-10-08 Ie Assets Gmbh & Co. Kg In nur einer Drehrichtung angetriebenes Lüfterrad

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9086076B2 (en) 2009-12-18 2015-07-21 Flexxaire Inc. Variable pitch fan having a pitch sensor

Also Published As

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EP0945626A3 (fr) 2001-04-04
EP0945626A2 (fr) 1999-09-29
DE59911215D1 (de) 2005-01-13

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