EP2619513A2

EP2619513A2 - Device for biaxial adjustment of an installation, in particular a solar panel unit

Info

Publication number: EP2619513A2
Application number: EP11718270.9A
Authority: EP
Inventors: Erich Russ; Lothar Seifert
Original assignee: IMO Holding GmbH
Current assignee: IMO Holding GmbH
Priority date: 2010-04-06
Filing date: 2011-04-06
Publication date: 2013-07-31
Also published as: WO2011124363A2; CN103180674A; DE102010014087A1; WO2011124363A3

Abstract

The invention relates to a device for biaxial adjustment of a part of an installation, in particular a solar panel unit, relative to a foundation, chassis or a second installation part, about two pivot axes which do not extend parallel to one another, by means of a respective driven or drivable pivot unit per axle, wherein each pivot unit comprises two rings which are concentric with one another, which are mounted on one another and for reciprocal relative adjustment are or can be each coupled to a drive, wherein one ring of each of the two pivot units is connected to a common mounting assembly, whereas the respective other ring is coupled both to the installation part to be adjusted and to a foundation, chassis or a second installation part.

Description

Device for biaxial adjustment of a system, in particular a solar panel unit

The invention is directed to a device for biaxial adjustment of a system part, in particular a solar panel unit relative to a foundation, chassis or a second part of the system, by two pivot axes, which do not run parallel to each other, each by means of a driven or drivable Sch venkeinheit per axis.

A generic arrangement disclosed in DE 31 00 835 A1. The local two-axle drive serves to align a heliostat with the sun. In this case, each axis of rotation is formed by a physical shaft, on each of which a ring is imprinted, on whose outer shell a toothed ring is welded in each case, while the two shaft ends are mounted in a housing by means of rolling bearings. The gears mesh with a motor-driven worm.

Such an arrangement suffers from several disadvantages: First, either very powerful and therefore heavy waves must be used, or the diameter of the bearings is relatively small, and then can be arranged on a correspondingly small circumference per row only a few rolling elements, which then large loads need to record. This results in a very large, acting on the rolling elements surface pressure, so that in the long term damage the rolling elements and / or raceways are unavoidable, especially because such tracking turn extremely slow and are always stopped, which is extremely unfavorable for a Lubricating film on the rolling elements and overall unfavorable for the bearings is to be regarded. On the other hand, due to their comparatively small diameter, such shafts do not provide optimum connection surfaces - the end faces are flat but relatively small; The lateral surface is also limited but could be extended by an axial extension however, the buckling presents a great challenge to the connection - either there is a clearance fit with a gap preventing a full surface fit, or a hollow fitting would have to be made with a transition fit and then pulled with extreme force on the shaft end , But then there is the danger that thermal stresses can cause considerable stress. Both cases therefore lead in the long term to premature fatigue of the material and thus affect the stability of such an arrangement. In addition, the production of a curved pad on a piece of equipment is considerably more expensive than the production of a flat pad.

From the disadvantages of the described prior art results the problem initiating the invention, a generic device, in particular for tracking a solar panel unit after the

Sun position, so that the base of the solar panel Einnett is always aligned perpendicular to the current position of the sun, educate in such a way that their structure is as simple and robust and thus low maintenance and therefore reaches a high operating life even under heavy loads.

The solution to this problem is achieved in that each pivot unit comprises two mutually concentric annular structures, which are mutually supported and coupled for mutual relative adjustment with one drive or coupled, each one annular structure of the two pivot units is connected to a common mounting assembly while the respective other annular structure is coupled to the plant part to be adjusted on the one hand and with a foundation, chassis or a second plant part on the other hand. The common assembly assembly itself is therefore not directly connected to the plant part to be adjusted, nor with a foundation, Chasssi or a second part of the plant, but provides a device internal It can with respect to each of the two connected to the device plant parts, foundations od. Like. Only pivot about an axis of rotation. However, by the two axes of rotation are fixed to the common mounting assembly at different angles, the overall result is the desired, two-axis adjustment.

It has proved to be favorable that the two pivot units have the same mechanical structure or even be suitable for construction. As a result, on the one hand, the overall arrangement is simplified, and for both pivoting units each spare part must be stored only in a single execution. Finally, even identical pivoting units can be loaded with about the same forces, so that at the same time there is also a good coordination of the two pivoting units.

The invention further provides that the two annular structures of a pivoting unit are arranged in a common plane radiai one inside the other. Such a coaxial and concentric arrangement contributes to a further simplification of the balance of power and leads to a particularly robust arrangement.

A similar purpose serves a development of the invention, according to which at least one annular structure of a pivoting unit has at least one flat connection surface. Level pads require only a flat plate for mounting, so that there is a particularly easy to assemble arrangement and also the common mounting assembly can be made very simple.

The invention can be further developed to the effect that at least one annular structure of a pivot unit has two preferably flat pads. The two pads can, for example, to connect two running in different directions support a Serve solar module unit. This in turn has the advantage that a solar module unit can be arranged as a whole approximately symmetrically to the device according to the invention and thus can be supported approximately in their center of gravity, so that a support structure is exposed to bending forces in free state of external forces hardly.

Preferably, the two pads are arranged on opposite end faces of the relevant annular structure. Thus, two connected thereto carrier parallel or even coaxial with the respective axis of rotation away from these pads.

This purpose is also served by a design rule according to the invention, according to which the two connection surfaces are parallel to one another, so that blunt-flanged tubes point away from the respective pivoting unit in the direction of their axis of rotation.

It is within the scope of the invention that the two pads are arranged on the driven, in particular toothed annular structure, preferably on the radially inner. This can be provided simultaneously with a toothed outer circumferential surface, for the rotary drive of the respective annular structure.

With great advantage, at least one annular structure of a pivoting unit has a plurality of annularly distributed connection elements, in particular in a flat connection surface. By a larger number of such connection elements, a pivot unit according to the invention can be stably and securely anchored to a machine or equipment part on the one hand and on the common mounting assembly on the other hand.

Advantageously, the annularly distributed connection elements are formed as bores, for example. As through-holes or as with Innerthreaded blind holes. This machine screws can be used for anchoring, and the device of the invention can therefore be disassembled as needed or for maintenance purposes with little effort, for example. To replace a pivoting unit.

Furthermore, it has been proven that an all-round gap is provided between the two annular structures of a pivoting unit. This gap creates space for storage and thus allows a virtually frictionless rotation of the two annular structures against each other.

The gap between the two annular structures of a pivoting unit can be sealed, preferably on both end faces of the respective pivoting unit. This makes it possible to fill this gap with a lubricant, in particular with grease.

The invention recommends to provide one, two or more all-round, elastic sealing elements for sealing in the region of each end face. In the case of multiple seal rings, an inner seal ring for retaining the grease, an outer seal ring for protection against penetrating particles serve.

An elastic sealing element may be fixed to an annular structure, preferably in an all-round groove of the same, and with its free longitudinal edge, which is preferably formed as a sealing lip, pressed against a surface of the other annular structure. An additional pressing of the sealing lip by means of a tension wire is not provided when using grease as a lubricant, while it would probably be necessary for a liquid lubricating oil.

At least one pivot unit should have at least one roller bearing between the respective annular structures. A Roller bearing has a negligible low static friction, so that the smallest twists can be executed with the highest precision.

In pursuit of this inventive concept, it is provided that in the context of at least one pivot unit one or more rows of rolling elements are provided. Although already a number of spherical rolling elements with cross-adapted thereto tracks may be sufficient to transmit both axial and radial forces, it is still useful to provide several rows of rolling elements, especially with axes of rotation, which are inclined relative to the ground plane of the pivot unit by different angles ,

The rolling elements of at least one row may have a roll, barrel or spherical shape.

As part of a roller bearing should be provided on one or preferably two annular structures depending on a track for rolling the rolling elements. These tracks may be adapted in cross-section to a longitudinal section through a rolling element along the axis of rotation thereof; To increase the life of such storage, the raceways can be additionally hardened.

If there is at least one raceway for rolling the rolling elements at the level of a series of connecting elements, the axial extent of the respective pivot unit is minimized in the direction of the respective bearing axis of rotation.

For active rotational adjustment of the two annular structures of a swivel unit, at least one respective annular structure of a swivel unit can have a toothing, preferably an external toothing. A preferred embodiment of the invention is characterized in that an annular structure has a toothing on its side facing the concentric ring-shaped structure. As a result, a bearing or anchoring of a drive device can be fixed to the other annular structure.

This idea of the invention can be substantiated to the effect that the radially inner, annular structure of a pivoting unit has an external toothing. An external toothing is not only suitable for the engagement of a pinion, but is also suitable for the meshing engagement of a worm.

It also makes sense that the toothing is located on the same lateral surface as the roller bearing (s), in particular on the lateral surface facing the gap.

Another measure for reducing the axial height of a pivoting unit is that the toothing is located in the axial direction between two rolling bearings.

To simplify the manufacturing process and to increase the precision can be provided that at least one pivot unit, the teeth and at least one pad are formed by processing or shaping a single body.

A similar purpose is a development to the effect that in at least one pivot unit, the teeth and the annularly distributed connection elements are formed by processing or shaping a single body.

Another design rule, according to which at least one pivot unit, the teeth and a track for rolling the Rolling elements are formed by machining or shaping a single body, serves to increase the precision. Furthermore, the toothing or the raceway or both can be hardened, preferably by a surface hardening, in particular by flame hardening or by inductive hardening. On the other hand, in certain cases prefabricated, ring-shaped or segment-shaped raceway elements can be used instead of a raceway incorporated into a basic body.

A first embodiment of the invention is characterized by a respective pinion or worm coupled or connected to a drive, which meshes with the toothing of the relevant ring. In special cases, a gear can be provided between pinion or worm and drive motor, in particular a reduction gear.

The invention further provides that a ring is formed as the toothing encompassing housing. This protects the gearing against contamination.

In the area of the drive, the ring designed as a toothing should be provided with a somewhat radial extension, in which a drive means meshing with the toothing is accommodated, while a drive motor rotatably coupled to the drive means is preferably located outside this housing widening.

Preferably, the radial extension of the ring formed as a housing surrounds a (one) with the teeth of the other ring meshing (-s) worm or pinion.

A further design provision provides that a (e) meshing with the toothing of the other ring pinion or worm is mounted in / at the radial extension of the housing formed as a ring. By a Such storage is the rotary drive of the other forces of the interlocking tooth and / or screw elements decoupled.

Further, it is within the scope of the invention that in / at the radial extension of the housing formed as a ring drive motor is attached or fastened, preferably flanged or flanged. This is therefore accessible for maintenance purposes and can be quickly replaced if necessary. As already indicated above, in special cases, a (reduction) gear can be provided between the engine and drive pinion or -Schnecke.

The invention can be further developed such that the housing or chassis or the stator of a drive is connected or coupled to the common mounting assembly. Such a motor therefore moves with respect to all connected system parts at most about a single axis, which facilitates the electrical contacting of the power lines.

A device according to the invention, in which at least one pivoting unit is equipped with a drive worm, is preferably characterized by at least one braking device, which is connected on the one hand to the worm engaging or connectable and on the other hand supported on the formed as a housing ring or a connected or connectable part , Such a braking device is primarily assigned the task of avoiding unwanted rotation of one connected part of the plant in relation to the other or with respect to the foundation in the stopped state, so that the relevant drive motor can be switched off in order to save energy.

If the braking device has no switching elements, the probability of failure can be kept within the smallest limits. It has proven to be advantageous that the braking device permanently generates a braking effect, that is never deactivated, not even when adjusting the beireffenden pivot unit. The braking device should have a passive brake, ie without supply of auxiliary power, so that it consumes no additional energy. Thus, the arrangement in the static, ie stopped state is completely energy neutral, which is important especially in solar systems in terms of good efficiency.

A simple realization of the braking device succeeds in that it has friction discs rubbing against each other with a normal force acting perpendicular to the discs, so that the generated friction torque is independent of the direction of rotation. It may be a housing fixed to the housing and a disk rotatable with the screw, or one or two packages of a plurality of disks.

The normal forces of the discs rubbing against one another preferably always act in the same, preferably in the axial direction of the worm. This can be achieved in a simple way, characterized in that the friction surfaces are arranged approximately perpendicularly penetrated by the axis of the screw.

The braking device may be a functionally separate from the worm brake, although acting on the same rotary shaft, but is not integrated with the worm, but only coupled thereto. As a result, the production of these highly different elements is decoupled from each other and thus simplified.

Further advantages can be achieved in that the braking torque from the braking device is permanently introduced into the worm shaft independently of the direction of rotation. This is an undesirable pulling through a load in any direction of rotation safely excluded, unlike, for example, when acting only in one direction of rotation freewheel.

According to the invention, it can further be provided that the braking torque is transmitted from the braking device to the worm shaft by a positive engagement acting in the tangential direction. For this purpose, for example, can be used with a drive shafts known tongue and groove principle with two extending in the axial direction of the worm shaft and with each other fleeing grooves, wherein a common keyway can be used.

Additional advantages are achieved in that the braking device is not located between, but axially outside the pivot bearing of the worm shaft, so that the distance between these pivot bearings must not be increased and thus the precision of the storage of the screw is not affected.

The invention undergoes further optimization in that the direction of the brake is arranged in the region of an end face of the worm, which is not coupled or can be coupled to a drive motor. Thus, the drive motor can be flanged directly in the region of a rotary bearing of the worm shaft to the housing, and this results in a particularly torsion-rigid arrangement, which allows a highly accurate Einsteiiung and compliance with a rotational position. If the braking torque of the braking device is on or adjustable, so it can be an optimal compromise between the desired self-locking of the worm gear on the one hand and a minimal braking effect on the other hand, to demand the drive motor for adjustment only a minimum of additional energy.

This purpose is also served by a further design specification, according to which the braking torque generated by the braking device approximately for the maximum Load case of the device is designed, reduced by the inhibitory friction torque of the worm gear and finally divided by the power transmission ratio of worm to worm or ring.

As a result, can be used in the context of a pivoting unit of the arrangement according to the invention, a worm gear, which in itself is not self-locking; the self-locking effect instead generates the brake according to the invention.

To protect against external influences, the elements of the brake, in particular friction surfaces and possibly spring elements, should be arranged in a preferably bell-shaped housing.

A particularly advantageous arrangement is characterized in that the common mounting assembly for connecting one or both pivoting units (each) has a flat pad. It has been proven that flat pads can be produced with the highest possible precision. In addition, the balance of power on such flat surfaces are particularly überschau- and manageable. Also, there can be provided perpendicular thereto connecting or connecting elements, for example. Arranged in a circle around the axis of rotation bores, which pass through the relevant pad vertically.

The invention further provides that at least one flat connection surface of the common assembly assembly for connection of a pivot unit has an opening. In this way, pads can also be provided on the mutually corresponding end faces of both annular structures, ie in the same axial direction, for connection to the common mounting assembly on the one hand and to a foundation or plant component on the other hand. The aperture should have a circular shape in a flat pad of the common mounting assembly, preferably with a diameter equal to or greater than the radially inner ring of the pivoting unit to be fixed thereto. As a result, a connection part fixed to this radially inner ring can pass through the mounting assembly and extend beyond it to a plant or machine part.

The common mounting assembly can be formed such or their pads can be aligned so that the two axes of rotation of the connected to the common mounting assembly pivot units are inclined or inclined to each other.

In this case, the common mounting assembly should be designed such or their pads to be aligned such that the two axes of rotation of the connected to the common mounting assembly pivot units lie in a common plane. If the two axes of rotation of the pivoting units connected to the common assembly assembly intersect, in particular at an angle which is not equal to zero, the free connection surface of the non-anchored pivoting unit can be moved along a spherical surface by combined adjustment of both pivoting units about their respective axes of rotation, the center thereof is defined by the intersection of both axes of rotation.

If the common mounting assembly is formed or its pads are aligned such that the two axes of rotation of the connected to the common assembly assembly pivot units intersect at a right angle, the adjustment is independent of an adjustment to each of the two axes of rotation other axis of rotation. Aligning the free pad of the non-anchored pivot unit in a desired direction is therefore particularly easy. For example. In a mounting of a solar module unit, the axis of rotation of the pivot unit connected to a foundation can be exact be set vertically, so that can be aligned by adjusting this pivoting unit, the common assembly assembly in any direction, while the axis of rotation of the second pivoting unit remains exactly horizontal at all SchwenksteHungen and thus allows the setting of the topocentric elevation angle. Thus, the course of the sun can be tracked at any time exactly if their direction or azimuth and altitude are known. These values may then be used directly as setpoints for the two pivoting units without any conversion, if necessary.

Such a decoupling of the two rotational positions can be particularly easily achieved in that the common mounting assembly has two Anschiußfiächen which are perpendicular to each other, so that in particular the axes of rotation connected thereto pivot units are perpendicular to each other.

The common mounting assembly can be further developed to the effect that one of their pads rises vertically above its other pad, so is not offset laterally beyond the edge. As a result, the center of gravity of the common assembly assembly and in particular also the center of gravity of the entire slewing mechanism lies above a pivoting unit to be connected to a foundation, and then to a support, column or other foundation as well as to the respective pivoting unit itself will not act in a free state from external forces too big overturning moments.

On the other hand, the invention recommends that the planes of the two Anschiußfiächen the common assembly assembly intersect along a line which is offset from the centers of the two pads. As a result, the center of gravity of the entire swing can be moved exactly to a vertically oriented axis of rotation of the biaxial slewing, so that on the respective pivot unit itself in From external forces free state at most minimal or ideally no tilting moments act.

A particularly simple arrangement results by forming at least one pad by a plate. A flat plate always has a flat connection surface, so that this - in addition to the cutting of a desired plate circumference - no special measures are required. The two pads of the common mounting assembly may be formed by a respective plate, which are interconnected, preferably by one or in particular by two lateral cheek (s). A particularly rigid construction is obtained, for example, by intimately welding the plates involved with each other and / or with the additional cheeks.

A maximum stability with minimum Hersteilungsaufwand results, for example, in that at least one lateral cheek is formed by one or two plates, preferably at least one plate has two mutually perpendicular edges or end faces. If the two connection plates are perpendicular to each other, then each cheek plate can be used at this right angle and / or welded, for example. In the region of the edge of both terminal plates. A lateral cheek can be formed by two plates, which are not symmetrical to each other. This design specification takes into account in particular the fact explained above that a connection plate is preferably placed eccentrically, that is to say asymmetrically, on the other connection plate. The two plates of a cheek can then support the patch plate from both sides. Preferably, the two plates of a cheek to each have the base of a preferably rectangular triangle, wherein the catheters are attached to a respective terminal plate and the hypotenuse connects the free edge of the attached terminal plate with one free edge of the other terminal plate.

It is within the scope of the invention that one or preferably both cheeks (each) has a recess for the passage of the drive housing (have). In this case, the width of a connecting plate or the distance between the two cheeks can be minimally selected, that is only slightly larger than the outer diameter of the outer ring of the respective pivoting unit.

The housing or chassis of a drive may be connected or coupled to the common mounting assembly.

Finally, it is the teachings of the invention that the housing or chassis or the stator of a drive is not connected or coupled to the common mounting assembly.

Further features, details, advantages and effects on the basis of the invention will become apparent from the following description of a preferred embodiment of the invention and from the drawing. Hereby shows:

Figure 1 is a arranged by means of a arranged at the upper end of a column, according to the invention swing mechanism biaxially adjustable solar panel unit in a perspective view.

Fig. 2 shows the swing together with its connection to the column on the one hand and to the solar panel unit in an enlarged, perspective view;

3 shows the swivel mechanism from FIGS. 1 and 2 in a again enlarged, perspective illustration, but without connected system parts; Fig. 4 is a front view of the assembly 3 of Fig. 3;

Fig. 5 is a side view of the arrangement of Fig. 3;

Fig. 6 is a rear view of the arrangement of Fig. 3;

Fig. 7 is a section along a central Grundebe e a

Swivel unit, partially broken off; such as

The solar panel unit 1 of FIG. 1 is provided with a larger number of solar panels 2, in particular solar modules, in order to obtain energy from sunlight. All solar panels 2 are arranged within a common plane, preferably contiguously contiguous, in particular juxtaposed and / or one above the other in the form of a matrix with a plurality of columns and rows. Although the solar panels 2 could also be solar modules for solar thermal energy, that is, for example, for generating hot water in the solar modules themselves, it is preferable to use photovoltaic modules which directly generate electricity from sunlight. Another alternative would be to equip the solar panel unit 1 with a heliostat rather than solar modules with mirrors as solar panels 2 directing the sunlight to a remote stationary unit for converting the sunlight into heat.

To support the solar panels 2 - so in particular photovoltaic modules, mirrors and / or hot water modules - is a substantially flat support structure 3, on the front of the solar panels 2 befesiigt, so for example. Are screwed.

The support structure 3 comprises a frame 4 with a circumferential, preferably rectangular enclosure 5, consisting of upper and one lower crossbar 6, 7 and two lateral frame beams 8, 9, wherein in each corner of the frame 4, the there coinciding beams 6-9 are connected together at their ends. Between the two side frame beams 8, 9 also extend within the enclosure 5 a plurality of transverse struts 10, preferably parallel to the crossbars 6, 7. Two central cross struts 10 are preferably connected by two further struts 11, which in turn preferably parallel to the two lateral Zargenbalken 8, 9 run. The beams 6-9 and struts 10, 11 are preferably profiled, for example. With an i-cross section. The bars 6-9 and struts 10, 11 may, for example, be welded together, but if necessary also screwed or riveted or the like.

For large-scale support and secure attachment of the solar panels 2, a plurality of mounting rods 12 may be provided at the front of this support structure 3, in particular parallel to each other, in particular parallel to the side frame beams 8, 9 and connected to the crossbars 6, 7 and cross struts 10. At the front These fastening rods 12 may be fasteners, for example. Screws and / or tabs, provided or anchored to securely set the solar panels 2.

The solar panel unit 1 is supported by a pillar 13, which in turn is anchored in or on the ground or on some other, preferably flat base. To connect the support structure 3 with the column is at two central, parallel to the side frame beams 8.9 struts 11 each one approximately perpendicular to the plane of the solar panels 2 rearwardly directed support tabs 14 attached, for example. Welded or flanged. Between these two support tabs 14 extend two aligned support tubes 15, 16, which, however, do not meet in the middle between the two support tabs 14, but terminate at a mutual distance. These support tubes 15 direct the weight of the support structure 13 together with solar panels 2 attached thereto - as well as possibly an occurring wind load - to the upper end of the column 13, from where they are introduced into the bottom-side anchoring of the column 13.

The solar radiation power absorbed by the solar panel unit 1 is maximum when the plane of the solar panel 2 is always aligned perpendicular to the current position of the sun with respect to the azimuth or the compass direction as well as the elevation angle of the sun in the topocentric, horizontal coordinate system. To effect this, a biaxial adjustment of the solar panel unit 1 is required. There are several ways to do this:

Preferably, a first axis is vertically aligned to adjust the current azimuth of the sun, and a second axis is oriented horizontally to adjust the current elevation angle of the sun (azimuthal mount).

In another variant, a first axis (hour axis or right ascension axis) could be aligned parallel to the earth axis; the second axis (declination axis) would then stand perpendicular to it and point to the celestial equator (parallactic or equatorial mount).

Although the second variant could be simpler in terms of readjustment, it has the disadvantage that the inclination of the right ascension axis depends on the location and therefore can not be predefined at the factory. Therefore, in general, the first variant of the tracking is preferred, which requires no location-dependent modifications.

However, the following statements, which refer to the first variant, are equally applicable to arrangements in which the second variant of the tracking is applied. In order to track the solar panel unit 1 to the day bow of the position of the sun, the support tubes 15, 16 at the upper end of the column 13 are not rigidly fixed, but by means of a pivot mechanism 17 according to the invention. This has three outer, respectively annular and preferably flat pads 18, 19th , 20, for connection to the upper end of the preferably tubular column 13, in particular on a local flange 21 on the one hand and on one end-side end face or an end-side flange 22 of the two support tubes 5, 16 on the other. The flanges 21, 22 could each have the same (outer) diameter; In this case, the pads 18-20 should each have the same (outer) diameter. However, preferably, the pillar 13 is thicker than the support tubes 15, 16, so that the end-side flanges 22 on the support tubes 15, 16 have smaller (outer) diameter than the top-side flange 21 of the pillar 13.

For connecting each of a flange 21, 22, each with a connection surface 18-20 are each a plurality, in each case aligned with each other, annularly the longitudinal axis of the respective tube 13, 15, 16 surrounding arranged holes 23-25 for passing or screwing of machine screws. Preferably, the holes in the flanges 21, 22 are formed as through holes without internal thread, while the holes 23-25 may be formed in the pads 18-20 either as blind holes with internal thread or as through holes without internal thread.

The slewing gear 17 is shown in Fig. 3 ff. In dismounted state. It consists essentially of two individual pivoting units 26, 27, which are connected to each other via a common mounting assembly 28. Preferably, the two pivot units 26, 27 have the same structure or structure or may even be completely identical. This structure is shown in Fig. 7: It can be seen a first circular ring 29 with a toothing 30 on the radially outer surface. The toothing 30 is surrounded on the outside by a housing 31. The housing 31 is also of annular shape, but not completely rotationally symmetrical, but has at least one point, preferably at two diametrically opposite points to (each) a housing extension 32 for receiving a meshing with the toothing 30 drive means. In the illustrated embodiment, the drive means is a worm 33. For this purpose, the housing extension 32 has the Gestait of a longitudinal axis of the worm 33 coaxial cylinder. At the point of contact of the cylindrical housing extension 32 with the circular main part of the housing 31 is a relatively large opening, which allows engagement of the screw 33 in the toothing 33 of the ring 29. As a result, causes a rotation of the screw 33 about the longitudinal axis thereof a proportional rotation of the ring 29 relative to the housing 31st

The worm 33 is mounted in the region of the two end faces 34, 35 of the cylindrical housing widening 32, for example by means of rolling bearings 36, in particular by means of needle bearings. On the end faces 34, 35 of the cylindrical housing extension 32 are also located annularly arranged mounting holes for attachment of each another housing part 37, 38, in particular by means of screws. While the one housing part 37 is closed approximately bell-shaped, the other housing part should have an approximately cylindrical shell-shaped, which is open at both ends. The screw 33 has at its two end faces 39, 40 each have a connection option, in particular via a coaxial Elnsenkung 41, 42, in particular with a groove for inserting a spring or with a polygonal, for example. Hexagonal cross-section. Since the end faces 34, 35 of the cylindrical housing extension 32 in the region of these depressions each have an opening, the connection possibilities are accessible from the outside.

While in the bell-shaped closed housing part 37, a brake 43 is arranged, the cylinder jacket-shaped Gehäuseteii 38 serves as an adapter for connecting a drive motor 44 or an intermediate transmission, eg. A reduction and / or angular gear 45th

The brake 43 on the one hand as well as a drive motor 44 or gear 45 on the other hand, via an inner adapter 46, 47 with the respective recess 41, 42 of the screw 33 rotatably coupled. Each adapter 46, 47 in turn has a recess 48, 49 coaxial with its axis of rotation. In the recess 49 of the adapter 47, for example, the output shaft of a drive motor 44 or transmission 45 can be inserted in a rotationally fixed manner, its housing on the free end face of the cylinder jacket-shaped housing part 38 flanged non-rotatably. The drive motor 44 is preferably a - precisely controllable - electric motor, for example, a stepper motor or an electric motor with a position sensor and a position control or regulation.

The actual brake 43 has two mutually coaxial ports 50, 51, one of which is rotatably connected to the adapter 46 and the other with the bell-shaped housing part 37. Preferably, the brake 43 has two packets of brake discs, each of which is rotatably coupled to a terminal 50, 51. By the brake discs of different packages are frictionally pressed against each other, resulting in a braking torque. This may optionally be adjustable from the outside, for example. By means of a screw. The brake 43 generates a constant, Direction of rotation independent braking torque, which is adjusted so that the entire pivot unit 26, 27 thereby self-locking properties, even if the pairing of worm 33 and gear 30 itself is actually not self-locking. By these self-locking properties, an actively controllable brake is not required, and the brake 43 requires no auxiliary power. As soon as the drive motor 44 is stopped in a desired position, it is permanently maintained due to the self-locking properties. The control of the two pivoting units 26, 27 is therefore particularly simple.

While the pivoting unit 26 fixed to the column 13 has only at least two connecting surfaces 18, 52 - one for connection to the column 13, the other for connecting the common assembly 28 - the other pivoting unit 27 to be connected to the supporting structure 3 requires its three a pad 53 serves to connect to the common mounting assembly 28; at the other two pads 19, 20 each have a support tube 15, 16 flanged.

The two pads 18, 52 of the pivot unit connected to the column 13 are located on opposite end faces of the toothed ring 29 on the one hand and the housing 31 on the other. These pads 18, 52 are flat and parallel to each other. Both pads 18, 52 have annularly arranged fastening means in the form of holes 23, which are preferably designed as threaded Sachklochbohrungen. Preferably, the pad 18 to be connected to the column flange 21 is disposed on the radially outer annular structure, namely the housing 31 of the pivot unit 26, while the pad 52 for the common mounting assembly 28 is preferably on the other annular structure, namely the toothed ring 29 the pivoting unit 26, is located. The other, to be connected to the support tubes 15, 16 pivot unit 27 has three flat, preferably mutually parallel pads 19, 20, 53. Of which is to be connected to the common mounting assembly 28 pad 52 at the radially outer annular structure, namely arranged on one end face of the housing 31 of the pivoting unit 27, while the other two connecting surfaces 19, 20 are provided on opposite end faces of the other annular structure, namely the toothed ring 29 of the pivoting unit 27. All pads 19, 20, 53 have a ring-shaped fastening means in the form of holes 24, 25. These can be formed as through holes, but also as a threaded Sachklochbohrungen.

It is not shown that one or more rows of rolling elements are arranged in the gap 54 between the housing 31 and the ring 29 enclosed therefrom, preferably each on one raceway per annular one

Structure, i. Housing 31 on the one hand and ring 29 on the other hand, roll.

Further, the gap 54 in the region of one or preferably both

Mouths be sealed, so that of the housing 31 on the one hand, the ring 29 on the other hand and this preferably annular

Sealing elements enclosed gap cavity with a lubricant, in particular grease, may be filled.

Since both end faces of the ring 29 serve as connection surfaces 19, 20 in the pivoting unit 27, the ring 29 of this pivoting unit 28 can not be encompassed by the housing 31 on the front side, in contrast to the pivoting unit 26 whose ring 29 has a connection surface 18 only on one end side has, so that the ring 29 may be encompassed on the other or this pad 18 opposite end of the housing 31, so that possibly the housing 31 could even extend along the radially inner circumferential surface of the ring 29 - in this case would be the two Mouths of the gap 54 on the underside of the pivot unit 27 and would therefore be optimally protected against rain, for example.

The common mounting assembly 28 connects the two pivoting units 26, 27 to a common pivoting mechanism 17. For reasons of stability, it is constructed from rigid metal plates, for example with a thickness of 10 mm or more, which can simultaneously serve as connection surfaces. In the embodiment shown in the drawing, there are a total of six interconnected, preferably welded plates:

A base plate 55 and five perpendicular plates, namely a holding plate 56 and four lateral support plates 57, 58th

As can be seen from Fig. 3, the base plate 55 preferably has a square base and has a plurality of annularly arranged around the center of this plate holes 59. These holes 59 serve to connect the base plate 55 with the pad 52 of the first pivot unit 26th In the case of the azimuthal mounting, this ensures that the base plate 59 is and remains completely horizontal in each rotational position of the lower pivoting unit 26 fixed to the upper end of the column 13.

Above this horizontal base plate 55 then rise the other five support and support plates 56-58:

The holding plate 56 stands on the base plate 55 and rises above this vertically upwards; the contact surface extends transversely across the horizontal base plate 55, preferably from one edge 60 thereof to the opposite one, and parallel to two further, mutually opposite edges 61 thereof, but preferably off-center, ie such that their distance to an edge 61 is smaller than to the other edge 61 of the base plate 55.

The support plate 56 preferably has the same width as the base plate 55 and is limited by a horizontal lower edge 62, two vertical side edges 63 and an upper edge 64, which may be straight, but may also have corners or even follow a curved course.

The support plate 56 carries on the one hand the second Sichwenkeinheit 27 and is in turn held in the vertical orientation by the four support plates 57, 58. These each have a triangular or trapezoidal base, but also have two perpendicular meeting one another edges 65, 66, respectively one on the base plate 55 and the other on the holding plate 56 rests, preferably in each case along the local (side) edges 60, 63rd

As a result of the off-center or asymmetrical arrangement of the holding plate 56 above the base plate 55 are each two support plates 57 slightly larger than the other two support plates 58th

Preferably, all of the plates 55-58 are welded together at their respective abutment surfaces 62, 65, 66 so that the common mounting assembly 28 is given maximum stability.

For connection of the pivoting unit 27 to the handle plate 56 this has a plurality of annularly arranged mounting holes 65, which are each aligned with a mounting hole in the pad 53 of the housing 31 of the second pivot unit 27 and allow fixing them by means of screws.

A central recess 66 in the holding plate 56 has a diameter which approximately corresponds to the outer diameter of the toothed ring 29 of the Swivel unit 27 corresponds. As a result, the two, serving as pads 19, 20 of the second pivot unit 27 end faces of this ring 29 are accessible and can each be screwed with a flange 22 of the two support tubes 15, 16.

The lateral offset of the holding plate 56 can be selected such that the two Anschiußflächen 19, 20 of the pivot unit 27 are symmetrical to the center of the base plate 55 and the (vertical) axis of rotation of the pivot unit 26; In this case, the two support tubes 15, 16 can be selected to be the same length, and the overall result is a symmetrical arrangement.

Another design rule provides to select the lateral offset of the holding plate 55 such that the center of gravity of the entire swing mechanism 17 is exactly on the axis of rotation of the lower (horizontally oriented) pivot unit 26 - so that there is no or only a negligible small imbalance - or vertically above the center of the base plate - so that one gets in free state of external forces no or only a negligible tilting moment. In practice, however, it has been shown that all three design rules are not or only slightly different.

Preferably, the pivot unit 27 is flanged to the support plate 56 of the common mounting assembly 28 such that the worm 33 extends horizontally, preferably in the lower region of the support plate 56, which is preferably higher than it is wide for this purpose. The larger support plates 57 each have a recess 67 for the passage of the housing parts 37, 38 connected to the end face of the cylindrical housing extension 32.

As shown in FIGS. 2 and 3, the drive motors 44 can each be arranged in coaxial arrangement with respect to the cylinder jacket-shaped housing parts 38 be flanged, or - as indicated in Fig. 1 - via a respective angular gear 45, so that the axes of rotation of the drive motors 44 are aligned vertically. In this case, in order to exclude a conflict between the two pivoting units 26, 27, it is advisable in this case, the drive motor 44 of the lower pivot unit 26 to project vertically downwardly projecting the drive motor 44 of the upper pivot unit 27 vertically upwards.

LIST OF REFERENCES 1 solar panel unit 26 pivoting unit 2 solar panel 27 pivoting unit 3 support structure 28 mounting assembly 4 frame 29 ring

5 surround 30 toothing

6 upper crossbar 31 housing

7 lower crossbar 32 housing extension 8 side frame beam 33 worm

9 side frame beams 34 front side

10 cross struts 35 front side

11 struts 36 rolling bearings

12 mounting rods 37 housing part

13 column 38 housing part

14 support tab 39 front side

15 support tube 40 front side

16 support tube 41 depression

17 Swing mechanism 42 depression

18 pad 43 brake

19 Pad 44 Drive motor 20 Contact surface 45 Gear

21 flange 46 adapter

22 flange 47 adapter

23 bore 48 depression

24 bore 49 depression

25 bore 50 connection 51 terminal 52 pad 53 pad 54 gap

55 base plate

56 holding plate

57 support plate

58 support plate

59 bore

60 edge

61 edge

62 lower edge

63 side edge

64 top edge

65 mounting hole 66 recess

67 recess

Claims

claims

1. Device (17) for biaxial adjustment of a system part, in particular a solar panel unit (1) relative to a foundation, chassis or a second system part (13), about two pivot axes which are not parallel to each other, each by means of a driven or driven pivoting unit (26,27) per axis, characterized in that each Schwenkeinheii (26,27) each comprise two mutually concentric annular structures (29; 31, 32), which are mutually supported and coupled for mutual Reiativversteüung with a drive (44) or can be coupled, wherein each an annular structure of both pivoting units (26,27) with a common mounting assembly (28) is connected, while the respective other annular structure (29; 31, 32) with the system part to be adjusted (1) on the one hand and with a Foundation, chassis or a second system part (13) on the other hand is coupled.

2. Device (17) according to claim 1, characterized in that the two pivoting units (26, 27) have the same structure or are of construction type.

3. Device (7) according to claim 1 or 2, characterized in that the two annular structures (29; 31, 32) of a

, Swivel unit (26,27) are arranged in a common plane radiai one inside the other.

4. Device (17) according to one of claims 1 to 3, characterized in that at least one annular structure (29; 31, 32) of a pivoting unit (26,27) has at least one flat connection surface.

5. Device (17) according to any one of the preceding claims, characterized in that at least one annular structure (29; 31, 32) of a pivoting unit (26,27) has two preferably flat pads (19,20).

6. Device (17) according to claim 5, characterized in that the two connection surfaces (19,20) on the radially inner annular structure (29; 31, 32) are arranged,

7. Device (17) according to claim 5 or 6, characterized in that the two connection surfaces (19.20) on opposite end sides of the respective annular structure (29; 31, 32) are arranged.

8. Device (17) according to one of claims 5 to 7, characterized in that the two connection surfaces (19,20) are parallel to each other. 9. Device (17) according to any one of the preceding claims, characterized in that at least one annular structure (29; 31, 32) of a pivoting unit (26,27) has a plurality of annularly distributed connecting elements, in particular in a flat pad (18- 20).

10. Device (17) according to claim 9, characterized in that the annularly distributed connection elements (18-20) are formed as bores (23-25), for example. As through-holes or as provided with internal thread blind holes. 1. Device (17) according to any one of the preceding claims, characterized in that between the two annular structures (29; 31, 32) of a pivoting unit (26, 27), an all-round gap (54) is provided.

12. Device (17) according to claim 11, characterized in that the gap (54) between the two annular structures (29;

Swivel unit (26,27) is sealed, preferably at both end sides. 3. Device (7) according to any one of the preceding claims, characterized in that at least one pivoting unit (26,27) at least one rolling bearing between the respective annular

14. Device (17) according to claim 13, characterized in that in the context of at least one pivot unit (26,27) one or more

Rows of rolling elements are provided, in particular with roller, barrel or spherical rolling elements.

15. Device (17) according to any one of claims 13 or 14, characterized in that in the context of a rolling bearing on one or preferably two annular structures (29; 31, 32) each have a raceway for rolling the rolling elements is provided.

16. Device (17) according to any one of claims 9 or 10 in conjunction with one of claims 13 to 15, characterized in that there is at least one raceway for rolling the rolling elements at the level of a number of connecting elements.

17. Device (17) according to any one of the preceding claims, characterized in that at least one annular structure

(29; 31, 32) of a pivoting unit (26, 27) has a toothing (30), preferably an external toothing. 18. Device (17) according to one of the preceding claims, characterized in that an annular structure (29; 31, 32) on its concentric annular structure (29; 31, 32) facing side has a toothing (30).

19. Device (17) according to one of the preceding claims, characterized in that the radially inner, annular structure (29) of a pivoting unit (26,27) has an external toothing.

20. Device (17) according to any one of the preceding claims, characterized in that the toothing (30) is located on the same lateral surface as the roller bearing (s).

21. Device (17) according to one of the preceding claims, characterized in that the toothing is located in the axial direction between two rolling bearings.

22. Device (17) according to any one of claims 4 to 8 in conjunction with one of claims 17 to 21, characterized in that at least one pivot unit (26,27), the toothing (30) and at least one pad (18-20, 52, 53) are formed by machining or shaping a single basic body.

23. Device (17) according to claim 9 or 10 in conjunction with one of claims 17 to 22, characterized in that at least one Schwenkeinhejt (26,27), the toothing (30) and the annularly distributed connection elements (23-25) through Machining or shaping of a single body are formed.

24. Device (17) according to any one of claims 15 or 16 in conjunction with one of claims 17 to 23, characterized in that at at least one pivot unit (26,27), the toothing (30) and a raceway for rolling the rolling elements by machining or shaping of a single body are formed.

25. Device (17) according to any one of claims 17 to 24, characterized by in each case one with a drive (44) coupled or connected pinion or worm, which (s) meshes with the toothing (30) of the respective ring.

26. Device (17) according to any one of claims 17 to 25, characterized in that a ring as the toothing (30) on both sides encompassing housing (31) is formed.

27. Device (17) according to claim 26, characterized in that as the toothing (30) encompassing housing (31) formed ring in the region of the drive (44) with a slightly radial extension (32) is provided.

28. Vornchtung (17) according to claim 27, characterized in that the radial extension (32) of the housing (31) formed ring (e) with the teeth of the other ring (29) meshing pinion or screw (33) surrounds.

29. Device (17) according to claim 27 or 28, characterized in that in / on the radial extension (32) of the housing (31) formed as a ring drive motor (44) is fastened or fastened, preferably flanged or flanged.

30. Device (17) according to any one of claims 28 to 29, characterized in that in / on the radial extension (32) of the housing (31) formed as a ring (e) with the toothing (30) of the other ring meshing pinion or screw (33) is stored.

31. Device (17) according to any one of the preceding claims, characterized in that the housing or chassis or the stator of a drive (44) relative to the common mounting assembly (28) is fixed immovably. 32. Device (17) according to any one of the preceding claims, wherein at least one pivoting unit (26,27) is equipped with a drive screw (33), characterized by at least one braking device (43), on the one hand connected to the screw (33) attacking or connected and on the other hand on the housing (31) formed ring or a connected or connectable part (37) is supported. 33. Device (17) according to claim 32, characterized in that the braking device (43) has no switching elements, so that the probability of failure can be kept within the smallest limits. 34. Device (17) according to claim 32 or 33, characterized in that the braking device (43) permanently generates a braking effect.

Device (17) according to any one of claims 32 to 34, characterized in that the braking device (43) has friction discs rubbing against each other with a normal force acting in the axial direction, so that the generated friction torque is independent of the direction of rotation. 36. Device (17) according to any one of claims 32 to 35, characterized in that the braking device (43) is one of the worm (33) functionally separate brake.

37. Device (17) according to any one of claims 32 to 36, characterized in that the braking torque of the braking device (43) is permanently and rotationally independent of the worm shaft (33) introduced.

38. Device (17) according to any one of claims 32 to 37, characterized in that the braking device (43) is not between, but axially outside of the rotary bearing (36) of the Schneckenweiie (33) is arranged.

39. Device (17) according to any one of claims 32 to 38, characterized in that the braking device (43) in the region of an end face (39,40) of the screw (33) is arranged, which is not coupled to a drive motor (44) or can be coupled.

40. Device (17) according to one of claims 32 to 39, characterized in that the braking torque of the braking device (43) is switched on or adjustable.

41. Device (17) according to one of claims 32 to 40, characterized in that the brake device (43) generated braking torque is designed approximately for the maximum load case of the device (17), reduced by the inhibiting friction torque of the worm gear (26, 27) and finally divided by the force transmission ratio of worm (33) to worm wheel or ring (29).

42. Device (17) according to any one of the preceding claims, characterized in that the common mounting assembly (28) for connecting one or both pivoting units (26,27) (each) has a flat pad.

43. Device (17) according to claim 42, characterized in that at least one flat connection surface of the common assembly assembly (28) for connection of a pivoting unit (26,27) has an opening (66).

44. Device (17) according to claim 43, characterized in that the

Opening (66) in a flat pad of the common

Mounting assembly (28) has a circular shape, preferably with a diameter which is equal to or greater than the radially inner ring (29) of the thereto to be determined pivoting unit (26, 27)

45. Device (17) according to any one of claims 42 to 44, characterized by two pads of the common mounting assembly (28) which are perpendicular to each other.

46. Device (17) according to claim 45, characterized in that the common mounting assembly (28) is designed such that one of its pads vertically rises above its other pad.

47. Device (17) according to claim 45 or 46, characterized in that the common mounting assembly (28) is formed such that intersect the planes of its two pads along a line which is offset from the centers of the two pads.

48. Device (17) according to any one of claims 44 to 47, characterized in that at least one connection surface is formed by a plate (55, 56).

49. Device (17) according to any one of claims 44 to 48, characterized in that the two connecting surfaces by a respective plate. (55,56) are formed, which are interconnected, preferably by two lateral cheek (s). 50. Device (17) according to claim 49, characterized in that at least one lateral cheek by one or two plates (57,58) are formed, wherein preferably at least one plate (57,58) has two mutually perpendicular edges or end faces , 51. Device (17) according to claim 49 or 50, characterized in that a lateral cheek is formed by two plates (57,58), which are not symmetrical to each other. 52. Device (17) according to one of the preceding claims, characterized in that the housing or chassis or stator of a drive (44) relative to the common mounting assembly (28) is fixed against rotation. 53. Device (17) according to any one of the preceding claims, characterized in that the housing or chassis or stator of a drive (44) is not connected or coupled to the common mounting assembly (28).