EP2914855B1 - Fan assembly having a rotatingly driven hub - Google Patents

Description

The invention relates to a fan wheel arrangement with a rotationally driven hub according to the preamble of claim 1.

One from the US Pat. No. 1,650,776 A Known fan wheel assembly for BKM has radial to the hub of the fan and rotatably mounted in the hub shell, about their axes of rotation on axially opposite directions of delivery fan blades on. The drive of the hub via a belt drive with a pulley, which is formed by an axial extension of the hub shell. In the region of this extension, the hub is mounted axially fixed on a bearing in the hub shell portion of a stationary to the engine bearing neck.

Starting from an engine-side actuator of the fan assembly of the support neck is penetrated by a linear drive over which the fan blades for adjusting the conveying direction and the flow rate are adjustable in their angle of attack. This linear actuator has an actuator guided in the support neck spindle drive, via which an actuator in the form of a control rod guided in the control rod is axially adjustable. On the actuating rod axially spaced from the spindle drive to the hub shell is rotationally fixed supported, axially adjustable annular body, which lies in radial overlap with the adjustable in their pitch fan blades and is connected to these about eccentric to the axes of rotation engaged with supporting elements.

Another fan wheel assembly is from the EP 0361982 A2 known. In this, the fan hub is mounted on a support neck and a control rod axially slidably received in the support neck as an actuator. On the actuating rod is axially fixed in axial overlap area to the held in the hub, adjustable in its blade angle fan blades mounted an annular body. By axial adjustment of the control rod, and thus also the ring body, the wings are adjusted in their wing angle. The axial adjustment of the actuator formed by the actuating rod via an actuating element which is formed by a remote axially to the annular body pivot lever which is pivotally mounted about a transversely to the support neck and the control rod and the actuating rod radially spaced axis and through a wall opening of the support neck accesses the control rod.

Showing a corresponding linear actuator on a hydraulic basis for a fan assembly Fig. 2 of the US 2005/100444 A1 , Here, instead of the pivot lever, a hydraulic piston acting on both sides is provided lying in the supporting neck, such that the piston rod forms the actuating rod.

Another fan drive with adjustable in the blade angle fan blades and hydraulic actuator shows the US Pat. No. 6,439,850 B1 , Again, the fan hub of the fan assembly is mounted on a combustion engine side support neck. The support neck runs in the direction of the fan hub on a radial overlap to those in the Fan hub mounted fan blade lying support shaft, on which an actuator piston is guided axially displaceable as an actuator. The actuating piston is adjacent to the support axis coaxial and axially delimited cylinder chambers from and is hydraulically acted upon by corresponding hydraulic actuation via the support neck continuous line connections axially displaceable.

The invention has for its object to design a fan assembly of the type mentioned in terms of a compact design as possible, which preferably also allows the realization of different configurations of the fan wheel while maintaining its basic structure.

This is achieved with the features of claim 1, to which specify the further claims expedient, sometimes even independently expedient embodiments.

Due to the configuration according to claim 1 results in an axially very compact design with central, in the axial overlap region to the annular body and the fan blades lying and in this area to the support neck also supported actuator. This brings favorable load conditions with it, thus makes a weaker dimensioning of the components regardless of the dominant, sometimes even sudden, loads possible. In particular, in spite of lying in the region of the radial support plane of the annular body to the actuator drive connection between the actuator and actuator as parts of a linear drive, this drive connection of supporting forces at least largely relieved, since the actuator is in turn carried over the support neck on this supported axially displaceable. Is favored by such a design and a radially very compact design, since due to the relief of supporting forces the actuator in its force transmitting engaging portion to the actuator in diameter can be performed offset, with a correspondingly graduated design of the sleeve-shaped support neck for receiving the bearing connection preferably formed by a ball bearing to the support body.

The design of the fan wheel arrangement according to the invention also offers, in particular, favorable possibilities for a different design of the linear drive provided for the adjustment of the fan blades and received in the fan hub. A related possibility is the training as a spindle drive with axially fixed support in the support neck guided spindle and the spindle axially adjustable actuator, such a configuration is to make very low, in particular with an electric motor drive for the linear drive. The actuator is designed in such a configuration, in particular in the form of a sleeve-shaped, axially to the free end of the support neck cross-supporting body, which is threadedly connected to the spindle in the region of its projecting beyond the support neck end in particular by a re-entrant collar.

Constructive simple options are given in such a solution, for example, to realize about a collar of the spindle an axial support thereof relative to the support neck as well as an axial stop surface in the displacement of the actuator to the support neck.

Another possibility of the design of the linear drive is its training as a piston engine, wherein also in this embodiment, a very simple basic structure, the one at a Spindle drive largely corresponds, is given. With such a piston drive, a piston is expediently received in an axially displaceable manner as an actuating element in a cylinder space of the support neck. The piston as an actuating element is advantageously at least axially fixedly connected to the actuator via a piston rod received in the support neck, whereby here too the actuator, analogous to the spindle drive, can be formed via a sleeve body axially displaceable and rotationally fixed to the support neck.

Such a constructed fan assembly can be due to their axially very compact design accommodate in predetermined tight spaces between the engine and radiator, preferably the drive connection between the engine and fan is assigned to the support neck opposite side of the fan wheel, against which the spindle expires with its threaded portion, from which the support neck widens in the opposite direction to a transmission housing.

On this, for example, in a linear drive in the form of a spindle drive a drive connection of a separate drive motor leak, spaced from the transmission housing and possibly supported independently supported by this and can be connected via a shaft drive with a rigid or flexible shaft in drive connection to the spindle. In such an arrangement, the shaft preferably extends substantially parallel to the plane of the fan wheel, so that its axial length does not increase significantly.

In the context of the invention, it is also to flange the drive motor on the transmission housing. Here, the drive motor can at least partially in the radial overlap area for supporting the support neck in a projecting lid portion of the Hub of the fan wheel are placed to save space, so that also a compact overall arrangement is achieved.

Another possibility with respect to the arrangement of a separate drive motor for the spindle drive is the formation of the transmission housing as a combined motor-gear housing, in which the drive motor is arranged annularly surrounding the central support of the support neck in the projecting lid portion of the hub of the fan wheel.

In particular, in connection with such designs of the drive connection of the drive motor to the spindle, but also generally with regard to a statically favorable supporting support of the fan wheel, it proves useful to the fan, with the drive side of the fan axially opposed actuator for adjusting the angle of attack of the fan blades, axial position on both sides to support, preferably in each case to the internal combustion engine, for example, via a bridge-like interlocking, supported on the internal combustion engine support structure.

With a Lüfterradanordnung the signposted type can be realized while maintaining the basic structure different embodiments in a simple manner. For example, fan wheels, in which an air delivery is only in a conveying direction, for example, sucking through the radiator in the direction of the internal combustion engine is provided and by changing the angle of attack for the fan blades while maintaining the conveying direction only the flow rate is varied, thus the cooling performance needs is adjusted.

Such an operation is usefully limited in consideration of the aerodynamic conditions to changes in the size of the angle of attack, which are at about 30 - 50 °.

The basic structure of the fan wheel described here also makes it possible to change the position of the fan blades far beyond this range, so in particular also to pivot the fan blades while maintaining the feed direction for the actuator beyond a turnup position, in which the fan blades extend transversely to the fan blade Circumferential direction of the fan wheel extend and thus in an area in which there is a reversal of the conveying direction. This reversal of the conveying direction means in consideration of the above statements relating to an arrangement of the fan between the engine and radiator conveying the air in the direction of the radiator, so in contrast to the above-mentioned suction a blown operation.

If, in consideration of the pre-described constructional structure, it is assumed that a small angle of attack of the fan blades corresponds to the initial position for the suction mode and correspondingly required small cooling power, the actuator is enlarged by the spindle from the originally given axial end position to spindle or support neck to increase the angle of attack Move along the threaded portion of the spindle until the Umschlaglage is reached and, if a reversal of the conveying direction is intended, beyond. As a rule, only a smaller angle range is used for the angle of attack for the reversal of the conveying direction, since the angle of attack against the end position, which corresponds to the maximum extension length of the actuator to the supporting neck, decreases starting from the envelope position for conveying towards bubbles.

There are thus already two modes of operation possible, namely a merely sucking or blowing operation and a suction to blow or vice versa convertible operation.

For both modes of operation, it is possible within the scope of the invention, for example, depending on thermal conditions, to control the angle of attack for the fan blades by the given mechanical coupling to the actuator, wherein the actuator is supported axially fixed to the ring body preferably on the existing bearing connection.

In the context of the invention, however, there are also possibilities to influence the angle of attack of the angle wing regardless of the basically given forced coupling to the actuator over certain adjustment ranges, so in particular, based on conveying direction suction, by axial play in the direction of the starting position. With such a decoupling can be speed-dependent corrections of the controlled depending on thermal conditions angle of attack for the fan blades, or in the switching range rapid changes in the angle of attack, regardless of the possible via the actuator positioning speed, which optionally also come in their performance reduced actuators in use can.

With regard to such influencing possibilities, according to the invention an axial clearance in the support of the annular body to the actuator relative to actuating forces acting on the fan blades, in particular also aerodynamic actuating forces, can be provided by the, under the influence of an adjustment of the fan blades in the sense an increase in the angle of attack causing forces, an adjustment of the fan blades on a relative to the predetermined by the adjustment angle of attack larger angle is possible.

Thus, it is possible to increase the predetermined for the initial position by the adjustment angle of the fan blades to a larger angle over a - especially elastic - support, for example, depending on rising above the speed on the fan blades acting aerodynamic forces and / or on the temperature when supported by a thermocouple, so that when lowering these support forces can set as the angle of attack predetermined by the actuator angle, thus results in a lower power consumption for the fan. A preferred solution for this purpose is that the fan blades, based on their axes of rotation, counter to their pivoting direction on the given in the direction of suction suction end position in the region of the starting position via a temperature-dependent position variable stop limit, in particular an expansion element, are supported.

It also proves to be expedient if the fan blades, based on their axes of rotation, are spring-supported counter to their pivoting direction on the given in the direction of suction suction end position in the initial position, wherein the resilient support of the fan blades, based on their axes of rotation, thereby achieve in that the ring body is spring-loaded in its position corresponding to the initial position of sucking the fan blades, in particular by an axially resilient support of the ring body against the housing.

The above-mentioned basic structure for Lüfterradanordnungen with guided on the support neck and the spindle drive axially adjustable actuator and this adjustable in the pitch fan blades is not only with regard to the arrangement of the drive motor for the spindle variable, but is based on fan wheels with maintaining the direction of rotation by adjusting the fan blade reversible conveying direction to use for fan wheels, where the fan blades over a lying in the direction of rotation of the fan wheel neutral position in its conveying direction are convertible. Thus, with the same basic construction of the fan wheel arrangement, different working methods can be implemented with only minor structural changes, which leads to considerable economic advantages with regard to the rational production of fan wheel arrangements geared to respective requirements.

The rotary drive of the spindle can be done both by an electric as well as a fluidic drive motor.

Further details and features of the invention will become apparent from the claims, the drawings as well as the largely extensively to the drawings recourse subsequent description.

Fig. 1

eine stirnseitige Ansicht eines Lüfterrades gemäß der Erfindung in Richtung des Pfeiles I in Fig. 2 und 3,

Fig. 2 und 3

Schnitte entsprechend der Schnittlinie II-II oder III-III in Fig. 1, wobei die Fig. 2 und 3 schematisiert veranschaulichen, dass die Verstellung der zur Nabe des Lüfterrades radialen Flügel um ihre Drehachsen in Fig. 2 in beiden Stellrichtungen spielfrei erfolgt, während in der Ausgestaltung gemäß Fig. 3 für die Verstellung der Lüfterflügel in einer der Stellrichtungen ein Spiel vorgesehen ist,

Fig. 4

einen Schnitt gemäß Linie IV-IV in Fig. 2 oder 3,

Fig. 5

einen Schnitt gemäß Linie V-V in Fig. 2 oder 3,

Fig. 6

einen Schnitt gemäß Linie VI-VI in Fig. 5,

Fig. 7

eine der Fig. 1 entsprechende Darstellung eines Lüfterrades mit durch Verdrehung der Lüfterflügel um ihre radialen Drehachsen umkehrbarer Förderrichtung bei Verschwenken der Lüfterflügel durch eine Querebene zur Umlaufebene des Lüfterrades und mit zum Getriebegehäuse des Lüfterrades angeflanschtem Stellmotor,

Fig. 8

eine radiale Ansicht des Lüfterrades gemäß Fig. 7 in Richtung des Pfeiles VIII in Fig. 7,

Fig. 9

eine der Fig. 1 entsprechende Darstellung eines Lüfterrades mit durch Verdrehung der Lüfterflügel um ihre radialen Drehachsen umkehrbarer Förderrichtung bei Verschwenken der Lüfterflügel durch die Umlaufebene des Lüfterrades und

Fig. 10

eine radiale Ansicht des Lüfterrades gemäß Fig. 9 in Richtung des Pfeiles 10 in Fig. 9, und

Fig. 11

eine der Darstellung gemäß Fig. 2 entsprechende Teilansicht eines Lüfterrades, wobei der Stellantrieb für die Verstellung der Lüfterflügel als fluidischer, insbesondere hydraulischer Linearantrieb mit einem im Traghals als Zylinder aufgenommenen Kolben gestaltet ist.

The drawings show in

Fig. 1

an end view of a fan according to the invention in the direction of arrow I in Fig. 2 and 3 .

FIGS. 2 and 3

Sections corresponding to the section line II-II or III-III in Fig. 1 , where the Fig. 2 and 3 schematized illustrate that the adjustment of the hub to the fan wheel radial wing about their axes of rotation in Fig. 2 in both directions without play, while in the embodiment according to Fig. 3 for the adjustment the fan blade is provided in one of the adjustment directions a game,

Fig. 4

a section along line IV-IV in Fig. 2 or 3 .

Fig. 5

a section along line VV in Fig. 2 or 3 .

Fig. 6

a section according to line VI-VI in Fig. 5 .

Fig. 7

one of the Fig. 1 corresponding representation of a fan with by rotation of the fan blades about their radial axes of rotation reversible conveying direction upon pivoting of the fan blades by a transverse plane to the plane of rotation of the fan and with the gearbox of the fan wheel flanged servomotor,

Fig. 8

a radial view of the fan according to Fig. 7 in the direction of the arrow VIII in Fig. 7 .

Fig. 9

one of the Fig. 1 corresponding representation of a fan with by rotation of the fan blades about their radial axes of rotation reversible conveying direction upon pivoting of the fan blades by the orbital plane of the fan and

Fig. 10

a radial view of the fan according to Fig. 9 in the direction of the arrow 10 in Fig. 9 , and

Fig. 11

one of the representation according to Fig. 2 corresponding partial view of a fan wheel, wherein the actuator for the adjustment of the fan blades is designed as a fluidic, in particular hydraulic linear drive with a piston received in the support neck as a cylinder.

The in the Fig. 1 to 3 illustrated impeller assembly 1 has a fan 2. With respect to this fan 2 is in Fig. 2 and 3 schematized illustrates its to an internal combustion engine 3 axial arrangement, as for example - is shown here - given an arrangement of the fan 2 between the engine 3 and an axially opposite radiator 47 - here schematically. The arrangement of the fan wheel 2 in this case is preferably supported supported to the engine 3, for example via a flange 4 supported by the engine 3 via a bearing 4 and, to this axially opposite, a position fixed to the engine 3 support 6. In the region of the support 6 is in one embodiment the Lüfterradanordnung according to Fig. 1 to 3 the connection of a drive source (drive motor 50) external to the hub 7 for a rotary drive 9 (FIG. Fig. 8 ), by means of which the fan blades 10 of the fan wheel 2 can be rotated about their axes of rotation 11, which are radial to the hub 7, and thus in their angle of attack 45 (FIG. Fig. 8 and 10 ) are adjustable. This is done via an acted upon by the rotary actuator 9 actuator 12, designed here as a spindle drive 13 with the hub axis 8 concentric spindle 14, via which a concentric to the spindle 14 actuator 15 is axially displaceable.

The actuator 15 as a support body is non-rotatably supported to a spindle 14 coaxial and in turn to the support 6 rotatably, preferably positionally fixed support neck 16 which merges in the direction of the support 6 in a transmission housing 17. In the gear housing 17 is provided as a drive connection from the rotary drive 9 to the spindle drive 13, a worm gear 19 with a worm gear 20 driven by a worm wheel 21 which is rotationally fixed to the spindle 14.

The spindle 14 has a guide portion 22 which is rotatably mounted to the support neck 16 and axially fixed in position and which merges via a support collar 16 axially supporting annular collar 23 in a threaded portion 24 of smaller diameter.

With this threaded portion 24, the actuator 15 is in the form of a sleeve-shaped support body via a radially inwardly projecting threaded collar 25 which engages over the annular collar 23 radially and axially adjoins a neck portion 26 of the actuator 15, which, as from the in Fig. 4 shown section according to IV-IV can be seen on the support neck 16 axially displaceable and rotatably guided in particular via a non-circular connection. The support neck 16 has in the region of the non-circular connection rectangular cross-section with rounded edges and is overlapped by the corresponding inner cross-section having a neck portion 26, in particular from Fig. 4 seen.

On the actuator 15, a ring body 28 is arranged in its threaded collar 25 radially overlapping axial region via a bearing 27, which is also axially supported via the bearing 27 to the actuator 15 and thus via the actuator 15, as explained in more detail below, according to the direction of rotation of the spindle drive 13 is axially adjustable.

The annular body 28 and lying in its connection to the spindle drive elements 13 are in the radial overlap region to the fan blades 10, which are rotatably mounted in the peripheral part of the hub shell 29 at its radial extent about its axes of rotation 11 and the axially displaceable with the hub shell 29 and rotatably supported ring body 28 are connected via drive elements. These drive elements are based on a respective fan blade 10, the over its radially inwardly projecting pin 36 and associated bearing 37 is rotatably supported in the peripheral region of the hub shell 29, by a rotation axis 11 of the fan blade 10 positionally fixed pinion 30 and a respective fixed to the annular body 28, circumferential rack section 31 formed in the direction of displacement of the Ring body 28 extends parallel to the axis of rotation 8 of the hub 7 and is at the rotational axis 11 of the fan blade 10 radial lateral offset with the respective pinion 30 in engagement.

The hub shell 29 split axially into two halves 32, 33 runs in relation to the illustrations according to FIG Fig. 1 to 3 , axially opposite to the internal combustion engine 3 on the gear housing 17 in a cover part 34, which has a neck extending to the gear housing 17 neck 35 in the coverage area to the support neck 16 of the support neck 16 to the neck 35 of the cover member 34 via a bearing 38 axially and radially is supported, whereby a supporting support of the fan wheel 2 between the internal combustion engine 3 and the axially opposite support 6 in the region of the transmission housing 17 is achieved.

In the FIGS. 7 and 8 is the appearance of a fan 2 illustrated, the pivotable about radial axes of rotation 11 fan blades 10 for reversing the conveying direction via a plane perpendicular to the orbital plane 39 of the fan 2 transverse plane, ie a transverse position are pivotable. In FIGS. 7 and 8 the fan blades 10 are illustrated in a starting position in which they are under a small, opening in the direction of rotation angle of attack - 45 in Fig. 8 - are employed to the orbital level 39 and towards the in Fig. 2 Indicated internal combustion engine 3 by the relative to the fan to the engine 3 opposite, not shown cooler suck in cooling air - suction operation of the Fan wheel 2. With increasing the angle of attack, the amount of air conveyed in the direction of suction is initially greater, but reaching a transverse position to the orbital plane 39 but a dead center is reached. Starting from the transverse position (transverse plane 48), with further adjustment of the fan blades 10 in the pivoting direction of the arrow 41 about their axes of rotation 11, there is a direction opposite to the direction of suction suction conveying direction in which the conveyed air is now conveyed against the radiator, thus the radiator of Deposits is blown - blowing operation.

Starting from the reversal position (pivoting through the transverse plane 48) takes place while maintaining the direction of rotation in the blowing operation, an adjustment of the fan blades 10 from a first large angle of attack to a small angle of attack as the end position.

Is, as in FIGS. 7 and 8 recognizable for the fan blades 10 a given to its axis of rotation 11 asymmetric structure, in which the fan blades 10 are acted upon by the aerodynamic forces in the pivoting direction arrow 41, the result is the reverse position a fan blade 10 in the sense of reversing the direction of suction on bubbles - in the pivoting direction according to arrow 41 - acting torque.

A different in the direction of rotation of the fan blades about their respective axis of rotation different loading by aerodynamic forces can also be achieved in that the fan blades are arranged offset with respect to their wing plane radially to the respective wing axis of rotation.

This can be used according to the invention in the sense of a "turning over" of the fan blades 10 via their transverse position as a "dead center" when the actuator for the fan blades 10 allows a corresponding clearance. As an enveloping, rapid reversal of the conveying direction of suction on bubbles is desirable in order to keep the associated with the reversal of the conveying direction impairment of the cooling of the internal combustion engine as short as possible, such a clearance is provided according to the invention.

This is constructive in a solution according to Fig. 3 realized in that the annular body 28 is supported to the actuator 15 in its the adjustment of the fan blades 10 from suction to blowing corresponding adjustment direction with play to the actuator 15, thus the actuator 15 can overtake in its predetermined axial position by the actuator, the overtaking is wegbegrenzt , so that after this game area again a coupling is given to the actuator.

Fig. 2 illustrated in contrast to a solution in which an axial position-fixed connection of the actuator 15 is given to the annular body 28, so that a forced coupling between actuator, actuator 15 and ring body 28 is realized.

Structurally, both possibilities according to the invention can be achieved while maintaining the basic structure in that the bearing 27 in the case of Fig. 2 to the annular body 28 is firmly supported, in the case of Fig. 3 but, as previously described, with axial play. Both solutions can be realized with little effort in each case via a snap ring support, wherein a snap ring 42 in the solution according to Fig. 2 the bearing 27 to the ring body 28 free of play by engagement in a rear side provided for bearing 27 groove 43 of the ring body 28 determines. A corresponding engagement groove 44 is in the solution according to Fig. 3 provided with axial distance to the bearing 27, which in the solution according to Fig. 3 aspired axial clearance wegbegrenzt results. The corresponding grooves 43, 44 can be in common without affecting the respective solution a ring body 28 may be provided so that the same parts can be used for both solutions.

Thus, it is also possible according to the invention, with respect to the actuator and its drive connection to the fan blades 10 via the ring body 28 of the same, or at least substantially the same structure, fan wheels 10 according to FIGS. 7 and 8 or fan wheels 10 according to FIGS. 9 and 10 to operate, based on the reversal of the conveying direction by switching the fan blades 10 differ in that the fan blades 10 in the solution according to FIGS. 7 and 8 about a transverse position and the solution according to FIGS. 9 and 10 be switched over a neutral position in which the planes of the fan blades 10 extend in the orbital plane 39 of the fan 2. Such a solution requires a positive guidance of the fan blades 10 with respect to their pivotal position about their respective axis of rotation 11, as in an axially positionally fixed support of the actuator 15 to the annular body 18 in the solution according to Fig. 2 is illustrated.

To the Fig. 2 and 3 are as with the ring body 28 for the implementation of its axial movements in corresponding rotational movements of the fan blades 10 cooperating drive elements rack sections 31 and pinion 30 addressed. The pinions 30 are rotationally fixed to the pins 36 of the fan blades 10, the rack sections 31 extend tangentially to the pinions 30 in the direction of displacement of the annular body 28 and are arranged circumferentially fixed to the annular body 28. Fig. 8 and 10 illustrate that, depending on the required pivoting direction (arrow 41 or 49) of the fan blade 10 with respect to the feed direction of the annular body 28, the rack portions 31 to the pinion 30 laterally offset, so are relative to the pinion 30 to be arranged on opposite sides. This makes it possible for the fan variants according to Fig. 7 and 9 to design the drive connection of the annular body 28 to the fan blades 10 with identical parts, wherein the annular body 28 with respect to the staggered arrangement and attachment of the rack portion 31 is constructive, so for example by corresponding plug-in receptacles for a respective rack section 31st

In a solution according to FIGS. 7 and 8 the given axial, wegbegrenzte clearance between the actuator 15 and the annular body 28 can also be used to superimposed to the actuator for the fan blades 10 to raise the given in the starting position angle 45 via a temperature-dependent actuator 46 if necessary, if, for example, to be cooled internal combustion engine 3 is operated under high load at low speed and accordingly a operated at a correspondingly low speed impeller 10 would remain in its cooling performance compared to the requirements of the internal combustion engine 3. As a temperature-dependent actuator 46 can, for example, as in Fig. 8 indicated, a thermo-wax element may be provided, the circumferentially to the hub shell 29 lying and supported a respective fan blades 10 back acted upon in the sense of increasing the angle of attack 45.

In the FIGS. 7 and 8 is based on solutions according to the invention, a drive solution to the actuator 12 illustrated, in which a drive motor 50 in the form of an electric motor - is also possible a hydraulic motor - is provided. This is flanged in direct association with the fixed, fixed on the support 6 gear housing 17 flanged to this shown, namely at a radial extent to the axis of rotation 8 of the hub 7, so that for the Lüfterradanordnung 1 gives a flat structure. Fig. 8 also illustrates that around the neck 35 of the cover member 34 of the hub shell 29 in such a solution an annular space remains as a free space 51, which would be suitable for the placement of a drive motor 50, so that in addition to the solution shown also further drive concepts with a total flat design the fan wheel assembly are possible. The space 51 is indicated by dashed lines.

The representation according to Fig. 11 corresponds largely to those according to Fig. 2 , so that with regard to the preceding description, in particular to the comments on Fig. 2 reference is made and reference is made, according to this reference, the same reference numerals are used for the same parts.

Deviating from the illustration according to Fig. 2 Although the actuator 12 is in turn designed as a linear drive, but now in the form of a piston drive 52 and provided in coordination therewith, the support neck 53 for receiving the piston 54 of the piston drive 52 with a cylinder chamber 55. The piston 54 passes into a piston rod 56 which passes through the cylinder space 55 and starting from the cylinder chamber 55 through a guide bore 57 of the support neck 53 terminates on an end portion 58 which is axially overlapping a collar 59 of the actuator 15 and with this at least axially , but preferably axially and radially fixed position is connected, for example, which is not shown here, by a corresponding threaded connection.

By appropriate pressurization of the piston 54, this, as indicated by the arrow 60, axially adjustable and in this case takes the actuator 15 respectively with, so that apart from the different configuration of Actuator 12 once as piston and the other spindle drive same function sequences with respect to the adjustment of the fan blades 10 are given.

To adjust the fan blades 10 by axial adjustment of the piston drive 52 is in Fig. 11 schematically illustrates a hydraulic control, starting from a pressure source 61 in the form of a pump or storage arrangement, in its place a connection can be made to existing pressure sources. Via the pressure source 61, a valve arrangement 62 is acted upon, from which via the supply line 63, the feeding of the working medium takes place on the cylinder space portion 64 demarcated via the piston 54. The valve assembly 62 operates in a known manner with a view to a finely tuned as possible compressed pressurization of the cylinder space portion 64 in a known manner clocked, wherein the control of the valve assembly 62, and optionally also the control of the pressure source 61 via a control line 66 from the controller 65, which is dependent on the each given wing angle position of the fan blades 10 and in consideration of the respective given cooling power requirement, and possibly other parameters, the valve assembly 62 responds.

For detecting the respective wing angle of the fan blades 10 is in Fig. 11 a sensor arrangement 67, for example in the form of a Hall sensor indicated, which communicates with the control unit 65 via a control line 68, wherein in the control unit 65, a corresponding processing of said parameters, optionally in conjunction with other parameters, via a control line 69, for example be made available from an engine control unit. Of course, instead of the control unit 65 via an engine control unit, not shown here, an immediate control of the valve arrangement 62 take place.

The clocked control of the valve assembly 62 in consideration of corresponding operating parameters, such as the wing angle, for example, by the date of the Applicant German Patent Application 10th 2011 101 494 , as well as other documents known. It is also within the scope of the invention to implement the hydraulic control as a function of the respective parameters to be taken into account via a proportionally operating valve arrangement 62, in particular a proportional valve.

In Fig. 11 is shown only one-sided pressurization of the piston 54, shown in conjunction with a schematically indicated spring support in the opposite direction by a spring 70. A two-sided pressurization and thus the opposite adjustment of the piston 54, as indicated by the arrow 60, can be realized in a corresponding manner.

Analogous to in Fig. 11 shown arrangement of the spring support via a spring 70, but instead of such, not shown here spring support axially opposite between the actuator 15 and cover 34, in particular to the cover part 34 positionally fixed support neck 53 may be provided on the fan blades 10 - by acting on the ring body 28th - Are supported resiliently in the region of the initial position counter to their pivoting direction on the given in the conveying direction suction end position.

Claims (15)

1. Fan impeller assembly having a hub (7) that can be driven in rotation, having radial fan blades (10) that can be pivoted with respect to the hub housing (29), having a central, positionally fixed support neck (16, 53), on which the hub housing (29) is retained in an axially fixed and rotatably mounted manner, and having an adjustment drive (12) for the fan blades (10) which has a linear drive with an actuating element (14) guided concentrically in the support neck (16), and has an adjustment member (15) that can be displaced axially by means of the actuating element (14), wherein, mounted radially with respect to the adjustment member (15), there is retained an annular body (28) which is secured in rotation with the hub housing (29) and is connected to the fan blades (10), that are adjustable in terms of their incidence (45), via drive elements that engage eccentrically with respect to the axes of rotation (11) of the blades,
   characterized in that
   the adjustment member (15) consists of a support body which overlaps the support neck (16, 53) and is guided in an axially displaceable and rotationally fixed manner with respect thereto.
2. Fan impeller assembly according to Claim 1,
   characterized in that
   the linear drive is formed as a spindle drive (13) by, as the actuating element, a spindle (14) which is guided in a retained manner with a fixed axial position in the support neck (16), and an adjustment member (15), that is axially displaceable via the spindle (14), in the form of the in particular sleeve-shaped support body which overlaps the free end of the support neck (16).
3. Fan impeller assembly according to Claim 2,
   characterized in that
   the spindle (14) which is retained with a fixed axial position has a guide section (22) which is retained axially and radially with respect to the support neck (16), and a thread section (24) that is reduced, in particular radially and axially, with respect to the guide section.
4. Fan impeller assembly according to Claim 2 or 3,
   characterized in that
   the support neck (16) is widened, at the opposite end from the thread section (24), to give a gear housing (17).
5. Fan impeller assembly according to one of Claims 2 to 4,
   characterized in that
   the drive for the spindle (14) is provided, with respect to the hub axis (8), axially opposite the drive for the hub (7).
6. Fan impeller assembly according to one of Claims 2 to 5,
   characterized in that
   the fan impeller (2) is respectively retained, in the region of the axially mutually opposite drive-side connections to the spindle (14) and to the hub (7), in a positionally fixed, supporting manner.
7. Fan impeller assembly according to Claim 1,
   characterized in that
   the linear drive is designed as a piston drive (52) having, as actuating element, a piston (54) received in an axially displaceable manner in a cylinder space (55) of the support neck (53), and an adjustment member (15), that is retained at least in an axially positionally fixed manner with respect to a piston rod (56) received in the support neck (53), in the form of the in particular sleeve-shaped support body which overlaps the free end of the support neck (53).
8. Fan impeller assembly according to one of Claims 1 to 7,
   characterized in that
   the adjustment member (25) is retained in a rotationally fixed manner and is guided axially by means of a non-circular cross section on the support neck (16, 53).
9. Fan impeller assembly according to one of Claims 1 to 8,
   characterized in that
   when changing the delivery direction from suction to blowing and vice versa, the adjustable-incidence (45) fan blades (10) can be switched via a neutral position that lies in the direction of rotation of the fan impeller, proceeding from, as starting position, a high incidence (45) of the fan impeller (10) in the suction delivery direction, via the neutral position, to, as end position, a high incidence in the blowing delivery direction.
10. Fan impeller assembly according to one of the preceding claims,
    characterized in that
    the annular body (28) is retained in an axially fixed position with respect to the adjustment member (15)
11. Fan impeller assembly according to one of Claims 1 to 9,
    characterized in that
    the annular body (28) is retained, with respect to the adjustment member (15), in an axially fixed position in an adjustment direction and, in the opposite direction, with a limited path with an axial clearance.
12. Fan impeller assembly according to Claim 11,
    characterized in that
    the fan impeller (2) is provided with fan blades (10) which are adjustable from a starting position and low incidence (45) to higher incidence, and in that the annular body (28) is retained with a limited path with respect to the adjustment member (15) and with an axial clearance counter to the adjustment direction, which corresponds to adjusting the incidence (45) of the fan blades (10) to a higher incidence.
13. Fan impeller assembly according to Claim 11 or 12,
    characterized in that
    in the case of an annular body (28) that can be adjusted axially between a starting position and an end position, and an incidence (45) of the fan blades (10) that increases from the starting position to the end position of the annular body (28), the annular body (28) is retained, with respect to the adjustment member (15), in an axially fixed position in the adjustment direction towards the end position and with axial play in the adjustment direction from the end position to the starting position.
14. Fan impeller assembly according to one of Claims 11 to 13,
    characterized in that
    when changing the delivery direction from suction to blowing, the adjustable-incidence (45) fan blades (10) can be switched via a changeover plane (48), which is perpendicular to the plane of rotation (39) of the fan impeller (10), proceeding from a small incidence of the fan blades (10) in the suction delivery direction as starting position - via the changeover plane with fan blades (10) lying perpendicular to the plane of rotation of the fan impeller (2) - to a small incidence in the blowing delivery direction as end position - and vice versa - and in that the fan blades (10) are positively guided, in terms of their incidence (45), in the direction of the rotational displacement towards their given end position in the blowing delivery direction and, in the direction of the opposite rotational displacement towards their given starting position in the suction delivery direction, have a rotation angle play of predefined magnitude.
15. Fan impeller assembly according to one of the preceding claims,
    characterized in that
    the fan blades (10) each have, in relation to their axes of rotation (11) that are radial with respect to the hub (7), in particular in the case of asymmetric design, unequal aerodynamic loading, and the effect of the aerodynamic forces acting counter to the direction of rotation is to urge them in the direction of reducing their incidence (45) in the direction of rotation of the fan impeller (10).

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