• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a device for compensating a torque, which is due to a force, in particular the weight force acting on an eccentrically about a horizontal shaft (7) deflected mass point, the mass point in particular the center of gravity of a tool of a machine tool (1). and a pedestal, against which the shaft (7) is rotatable, and a balancing spring (13), wherein the balancing spring (13) is configured and arranged such that the shaft (7) counteracts rotation relative to the pedestal Counter torque can be acted upon comprises.
    公开号:AT14047U1
    申请号:TGM50133/2013U
    申请日:2013-09-26
    公开日:2015-03-15
    发明作者:
    申请人:Emco Maier Gmbh；
    IPC主号:
    专利说明:

    description
    TECHNICAL AREA
    The present invention relates to a device for compensating a Drehmo¬ments, which is due to a force, in particular the weight force, which acts on a eccentrically deflected about a horizontal shaft mass point, wherein the mass point in particular the center of gravity a tool of a machine tool is.
    STATE OF THE ART
    Generally arises due to a frequently not present coaxiality of the center of gravity of a rotating about a shaft tool of a machine tool with respect to the axis of rotation of the shaft in a movement or positioning a predominantly horizontally arranged shaft of the machine tool generated by gravity, winkelab¬ pendent torque. In order to maintain the necessary torque balance in each position of the tool, a drive for rotation about the shaft must generate a corre sponding counter-torque. Firstly, this requires energy and, secondly, leads to a reduced machining accuracy. The reduced machining accuracy is due to an increased heating of the components and consequently higher thermoelastic deformations of individual or several components of the machine tools. Furthermore, there may be a need to size the drive for the rotation of the tool around the shaft, thereby requiring additional space.
    For the purpose of balancing mass forces in machine tools, a number of different concepts are already known. These are essentially based on the build-up of counter forces with the use of fluids, counterweights or springs. Regardless of the physical operating principle, the potential energy of the moving mass is stored by the mechanism during a movement in a first direction and made available again in the case of a (back) movement opposite to the first direction and the external energy requirement for the return movement is thereby reduced.
    From DE 100 25 355 A1 a device for weight balance of vertically or obliquely movable components of a machine tool is known which includes a plurality of parallel nebenei¬nander arranged coil springs whose inner ends on a fixed axis and whose outer ends on a concentric to the axis, rotatable mounted housing drum are attached. Via a flexible belt or toothed belt, the housing drum is further connected to the moving parts of the machine. During a travel movement in the direction of the acting gravitational acceleration or obliquely thereto, a rotational relative movement takes place between the axis and the housing drum and a part of the potential energy of the moving components is stored in the spiral springs. With a reversal of motion, the energy is removed from the spring accumulator and thus supports the movement.
    The system described in DE 10 2005 024 038 A1 for compensating an uneven mass distribution on a rocker is likewise based on the use of springs as an energy store, the memory being arranged linearly. The necessary conversion of the rotational movement into a translational movement takes place, for example, by means of an eccentric on the rotating axis and a connecting element connected thereto. A special feature of this design is that the energy conversion takes place completely within a housing, whereby no lateral forces on the storage of the oscillating effect.
    In DE 37 14 637 A1 a torque compensation system is presented, which also causes a transformation of a rotational movement into a translatory movement. This function is realized by means of a crank drive and a push rod. Upon rotation of the crank, the rotational movement is converted via a push rod into a translational movement. On the basis of the coupling of the rectilinear motion to a spring which moves in a housing, the rotational energy of the axis of rotation can be transformed into spring energy and intermediately stored. A particular feature of the system described is a device which causes a radial displacement of the articulation point of the push rod and thus the effective force application point. Thereby, the course of the available torque in dependence on the angular position of the axis of rotation can be adjusted.
    The device described in DE 697 22 036 T2 solves the task according to the invention of a cam disc and a sprung spring sprung thereto. When the rotation axis is moved from a neutral position, a cam plate connected to the rotation axis also rotates. In accordance with the shape of the cam disk, the rotation movement forces a translatory movement of tappets sprung onto the cam disk via rollers. Since the plungers mounted in a piston are pressed against the cam plate by a spring, a reaction force dependent on the cam shape results, which in turn results in a counter torque to the torque resulting from the rotational movement.
    Fluidic solutions for balancing the mass forces of translationally or rotatorily moving machine parts are described for example in DE 33 12 971 C2, DE 102 20617 A1, US 4 904 150 A and in EP 1 880 797 B1. As a further mechanical solution, which provides for compensation of the mass forces via cables with deflection rollers and with counterweights, supplemental to the already described approaches DE 12 37 403 B is mentioned.
    The aforementioned concepts have a number of disadvantages.
    Solutions balance the mass forces by counterweights and optionally cables andUmlenkrollen are space-consuming and limit due to the additional masses and the risk of lifting the acceleration of the respective axes. As a consequence, a larger dimensioning of the drives is necessary or productivity losses of the machines must be accepted in order to ensure damage to the device for mass balance and the functional safety.
    Fluid engineering solutions require a complicated structure and in particular a costly pressure medium supply and complex control devices. Since in such systems the fluid hydraulic oil, compressed air or gas, such as nitrogen, typically oscillates back and forth between a balancing cylinder and a fluid reservoir, negligible power losses occur, which have to be compensated by the drive or the fluid supply device ,
    The known concepts, which are based on the use of springs as energy storage, require a variety of components with appropriate space requirements. Since these have to move to fulfill the function partially at the contact surfaces relative to each other, erge¬ben increased wear and friction forces. Particularly in machine tools, the friction in the reversal of motion leads to hysteresis errors in the movement of the machine, which can lead to machining inaccuracies on the component.
    Furthermore, the known solutions to compensate for induced by inertia torques in waves as a common feature have the disadvantage that the Drehbewe¬gung the shaft must first be converted into a translational movement, before the energy is cached. In the case of motion reversal, the reverse principle applies to the transformation of a translational motion into a rotational motion. The described property also results in the consequence that the working range of the corresponding solutions is restricted.
    PRESENTATION OF THE INVENTION
    Against the background of the above-outlined prior art, the object of the present invention is to further develop a device for balancing a torque of the obi¬gen technical field such that a particularly simple structure and a space-saving compact design of the device is possible. For this purpose, a further object of the invention is to avoid the transformation of a rotational movement into a translational movement during energy storage and the disadvantages occurring in the prior art due to friction between individual parts or due to large masses, in particular additional masses prevent.
    The object is achieved by a device according to claim 1.Other advantageous embodiments of the invention will become apparent from the dependent claims.
    The inventive device for compensating a torque, which is due to a force, in particular the weight force, which acts on an eccentrically deflected about a hori¬ zontale shaft mass point, wherein the mass point is particularly the focus of a tool of a machine tool, comprises a base against which the shaft is rotatable and a balancing spring. In this case, the compensating spring is embodied and arranged such that the shaft can be acted upon by a torque which counteracts rotation relative to the base.
    Under a "horizontal wave " in this application is also understood to mean a shaft which is not exactly horizontal, but oblique and aligned with a horizontal alignment component. With "wave" is meant any element which is suitable for the transmission of Rotationskräf¬ten, in particular therefore also a pin and a cardan shaft.
    As an example of a "tool". However, other tools are to be understood by this reference, namely those that are usually located on a machine tool and can be ver¬schwend to a horizontal shaft. The invention can also be applied to a ver-pivotable about a shaft workpiece. The "milling spindle" preferably comprises all around the Wellerotierbaren parts of the machine tool.
    Under the term "socket " In this application, for example, a housing is understood, in which the shaft is rotatably mounted. However, it may also be an object deviating from the housing as long as it can serve as a reference point for the rotation of the shaft, in particular displaceable only by translational movements, but can not rotate.
    Under a "compensating spring " is to be understood in the context of the invention, a device which comprises a single compensating spring or a plurality of sub-springs, which can optionally coupled and / or parallel with each other. In addition, the term "balancing spring" may be used. comprise further components to clamp individual springs at different positions or to connect or ver¬ span with other springs or other components.
    The term of the compensating spring means any type of spring, which is claimed to torsion about its spring axis. Examples of a compensating spring are a tortuous spiral spring, preferably a helical spring configured as a leg spring, a spiral spring or a torsion bar, preferably a limb spring or spiral spring.
    Under a "counter torque". In this application, that torque is understood which is opposed to the torque exerted by the force of gravity acting on the tool and countered by the lever arm, via which the center of gravity of the tool is connected to the shaft, in order to move the tool in a predetermined deflection position hold. The counter-torque does not have to be equal in magnitude to the torque caused by the force of gravity, but must be counteracted, that is to say, to weaken the torque of the gravitational force.
    Advantageously, the compensating spring is at least partially arranged around the shaft. This means that the compensating spring, which can be configured, for example, as a leg spring and thus a screw-shaped spring, surrounds the shaft on the circumferential side and thus has in particular the same longitudinal axis as the shaft , Preferably, the balance spring is attached to both the base and the shaft.
    The compensating spring can be braced to build up the counter torque with a relative movement between the shaft and the base. For this purpose, it is preferable to connect the compensating spring to the base at at least one point and to the shaft at at least one point. Accordingly, the compensating spring preferably also includes suitably shaped structural elements which enable the production of such a detachable or non-detachable connection. For example, such a connection can be made by means of a tensioning set, which produces a frictional connection of the compensating spring with the base and / or the shaft. Alternatively, however, other types of connection are conceivable, such as a positive connection by means of a splined shaft profile or a screw connection.
    To be able to fulfill the function according to the invention, the compensating spring must at least contain a spring which is suitable to be dimensioned. This can be done, for example, by adapting the winding diameter and / or the wire diameter of a spring designed as a leg spring to the intended machine tool, in particular the mass, the lever arm and the deflection angle of the tool. Another possibility for adaptation to the available installation space, the torque to be compensated and the necessary deflection range of the shaft consists in the combination of a plurality of springs connected in series or in parallel with respect to the base and the shaft.
    The nature and sequence of the arrangement of individual springs in the form of elementary series and / or series circuits in combination with the location of the connection points on the base and on the shaft will be¬ referred to in the further course of the description as a spring arrangement.
    In a preferred embodiment, the shaft is rotatable from a zero position in two mutually opposite directions of rotation and the counter torque counteracts a rotation of the shaft in each of the two directions of rotation respectively.
    Under the "zero position" is a position of the tool and thus to understand the shaft in which the compensating spring exerts no counter torque on the shaft relative to the base. Assuming that the reaction torque counteracts a rotation of the shaft in each of the two directions of rotation, it is to be understood that a deflection of the shaft from the zero position, which is initiated for example by a separate drive and reinforced by gravity, leads to a restoring torque is constructed by the preferred device.
    In a preferred embodiment, the counter torque is proportional to a deflection angle of the shaft. With the deflection angle while the angle is meant by which the shaft is deflected from the zero position.
    Advantageously, the compensating spring is designed as a helical spring, in particular as Schen¬kelfeder, which extends surrounding the shaft along the shaft. A first recovery of the helical spring along the shaft means that the cylinder axis of the helical spring is parallel to the central axis of the shaft. Further preferably, the compensating spring on one or more bending springs, which is preferably designed as a leg spring, or designed as leg springs. More preferably, the compensation spring can be attached to the shaft and / or to the base by a clamping connection.
    In principle, however, other embodiments of the invention are also possible which allow direct storage of the energy without transformation of the rotational movement into a translatory movement. The term bending spring here refers to the primary internal load type of the spring used.
    Leg springs are associated with the bending springs and correspond in shape in the
    Essentially helical springs. They consist of a cylindrically wound wire, with the individual windings touching each other or being able to have a certain distance from one another. The torsional force acting on the compensating spring is directed around the cylinder axis of the leg spring.
    The described shape makes it possible to build a compact balance spring constructed extremely compact and to save space between the base and the shaft to inteie¬ren. Corresponding space is typically present in shafts of machine tools, since on the one hand for the storage of the respective modules sufficient space is necessary and on the other hand, a simple assembly and disassembly of the system must be made possible. The preferred embodiment of the invention thus uses the already existing Bau¬raum in a particularly efficient manner.
    Advantageously, the compensating spring is in several parts, in particular formed in two parts. This means that the compensating spring can also be composed of a plurality of individual springs in order to form an overall acting on the shaft and the base compensating spring.
    Advantageously, the compensating spring is biased. To this end, the system consisting of one or more equalizers is preferably retained at one end of the spring assembly by suitably shaped clamping members and rotated at a second end opposite the first end by a defined angle coaxially about the longitudinal axis of the spring assembly. The second end opposite the first end is then also clamped by means of a clamping element and the two clamping elements are further connected to each other by means of a yoke, so that the compensating spring is already preloaded in the unloaded state.
    The connection of the spring with the shaft is advantageously carried out in a neutral position (zero position), in which no or only a minimal compensation torque (counter torque) is erforder¬.
    Preferably, in this position, the yoke is connected to the base. The connection of the compensating spring on the shaft is preferably carried out in the neutral position and mit¬tels a suitably shaped clamping system. This is connected between the two ends of the balance spring with the balance spring and fixed to the shaft.
    It can also be realized a different connection of the balance spring to the base and the shaft, for example, by connecting the yoke to the shaft, while the clamping system positioned at a location between the two ends of the balancing spring is connected to the balancing spring and the base.
    In a preferred embodiment, the shaft is rotatable relative to the pedestal by a drive, in particular an electric motor, to deflect the mass point. This is executed in a particularly preferred embodiment of the invention as a direct drive and integrated directly between the base and the shaft.
    Advantageously, the compensating spring between the shaft and the base is integrated. This means that the compensating spring is installed in the space between shaft and base.
    In a further preferred embodiment, the compensating spring is provided with a profile sleeve or a plurality of profile sleeves. It is additionally possible to apply the compensating spring through the one profiled sleeve or the plurality of profiled sleeves to the shaft and / or the base.
    In this advantageous embodiment of the invention, a variation of the stiffness of the compensating, in particular leg spring used allows almost any adaptation of the available counter torque as a function of the angular position of the shaft relative to the base. For this purpose, the fact is used that the spring used at a defined rotation about its longitudinal axis also changes its Außen¬ diameter or inner diameter defined. By suitably shaped profiled sleeves are applied from the outside to the spring or inserted into the spring, it can be selectively controlled which portions of the spring are effectively effective.
    If, for example, due to the rotation of a leg spring enforces a reduction of the winding diameter, so an inner profile sleeve can be formed so that with increasing rotation angle parts of the spring rest against the profile sleeve and thus these parts of the spring are no longer effective. As a result, the rigidity of the still effective part of the spring is increased, whereby a disproportionate increase in the available torque takes place with increasing rotation angle. An analogous situation applies to an externally applied to the spring profile sleeve, if due to the rotation of the spring an enlargement of the spring diameter is enforced.
    In an already biased spring and a decrease in the effective spring stiffness can be achieved. If, for example, due to the rotation of a spring, a reduction of the spring diameter is enforced, then an outer profile sleeve can be so shaped that, as the angle of rotation increases, parts of the spring resting on the profile sleeve become free again and these parts of the spring become effective again. In the following, the rigidity of the effective part of the spring is reduced, whereby a disproportionate increase in the available torque takes place with increasing rotational angle. An analogous situation applies to a profile sleeve lying on the inside of the spring, when an enlargement of the spring diameter is forced due to the rotation of the spring.
    Further advantages and features of the invention will become apparent from the following description of the figures and the totality of the claims.
    BRIEF FIGURE DESCRIPTION
    FIG. 1a shows a perspective view of a machine tool with a horizontally arranged shaft and a tool rotatable about this shaft.
    FIG. 1b shows an enlarged partial view of the shaft of the machine tool, partly in section, in a preferred embodiment of a device according to the invention.
    FIG. 2 a shows a perspective view of a compensating spring in a preferred embodiment.
    2b shows a perspective view of a clamping set for connecting a shaft with a compensating spring in a preferred embodiment.
    Figures 3a-3f show some exemplary embodiments of a spring arrangement of
    Balancing spring against a shaft and a base.
    FIG. 4a shows a schematic sectional view of a preferred embodiment of the device according to the invention with integrated profile sleeves for adapting the available counter-torque profile to a neutral position.
    FIG. 4b shows a schematic sectional illustration of the preferred embodiment of FIG. 4a in a position deviating from the neutral position.
    WAYS FOR CARRYING OUT THE INVENTION
    As a typical application example for the use of a first, preferred embodiment of the device according to the invention, FIG. 1a shows a perspective view of a machine tool 1 with a horizontally arranged rotation axis 8 and a tool designed as a milling spindle 6, which has an eccentric load relative to the rotation axis 8 forms.
    The machine tool 1 has a horizontally movable stand 2, which wiede¬rum carries a vertically movable carriage 3. The carriage 3 holds and in turn guides a housing 4, which can also be moved in the horizontal direction relative to the carriage 3 along a translational movement axis, this being arranged perpendicular to the two superimposed movement axes. On a front side 5 of the housing 4 is the milling spindle 6, which is rotatably mounted in the housing 4 via a shaft 7, wherein the Rotati¬onsachse 8 is horizontal and thus parallel to the translational axis of movement of the Gehäuse4. The milling spindle 6 is rotatable about the shaft 7 by an angle ß to edit a workpiece to be processed (not shown) from different directions.
    1b shows an enlarged partial view of the horizontally movable housing 4, the shaft 7, the milling spindle 6 and other components according to a first preferred embodiment of the invention in a sectional view. The rotary bearing 9, 10 allows the milling spindle 6 from the illustrated "vertical". Turn clockwise or counterclockwise more than ninety degrees about the axis of rotation 8, thereby enabling the execution of complex milling operations. The "vertical" Position is therefore referred to as so, because the center of gravity 11 of the milling spindle 6 is arranged in this position on the Rotations¬ axis 8 and the direct connection between the center of gravity 11 and the rotation axis 8 thus extends vertically.
    The center of gravity 11 of the milling spindle 6 and its attachments is therefore not coaxial on the axis of rotation 8, but with respect to this axis of rotation 8 eccentric. In order to rotate the milling spindle 6 about its vertical position about the axis of rotation 8, an electric motor 12 integrated in the housing 4, which in the described example of application is in the form of a torque motor, is used which rotates the shaft 7 by the desired deflection angle.
    Once the milling spindle is no longer in its vertical position, a torque caused by the weight of the center of gravity 11 acts on the shaft 7. The amount of this torque is proportional to the mass of the milling spindle 6, the lever arm of the center of gravity 11 and the sine of the deflection angle. This torque is balanced by the electric motor 12 and a compensating spring 13 to move the milling spindle 6 to a desired position, i. at a desired deflection angle with respect to the vertical position.
    In Figure 2a, a first preferred embodiment of the balancing spring 13 is shown in a perspective view. A trained as a leg spring 14 balancing spring is provided at both ends with clamping elements 15, 16. The two clamping elements 15, 16 are attached to a yoke 17, which connects the clamping elements 15, 16 and thus the two ends of the leg spring 14 together. By the leg spring 14 is rotated by the yoke 17 by a defined angle about its longitudinal axis 18 before Ver¬binden the two clamping elements 15, 16, the compensating spring 13 can be biased. This can be done in particular before installing the compensating spring 13 in the machine tool 1 and thus simplify this installation.
    2b shows a preferred embodiment of a compound of the leg spring with the shaft 7 in the form of a clamping set 19. This consists of a conical inner ring 20 and a likewise conical outer ring 21, which are clamped against each other via a screw 22 against each other and a frictional connection to Produce shaft 7.
    The outer ring 21 of the clamping set 19 has on the outside via a schrauben¬förmig formed cutout 23, which is tuned to the pitch and the diameter of the Schenkelfe¬der 14. The connection of the clamping set 19 with the leg spring 14 takes place in the middle of the spring assembly, by a clamping piece 24 with a likewise helically cut-out 25 and a screw connection 26.
    The connection of the balance spring 13 to the housing 4 (the "pedestal") is accomplished in the first preferred embodiment by screwing the yoke 17 to the housing 4.
    Figures 3a to 3f show by way of example some possible arrangements of the springs in a balancing spring. The arrangement which is preferred for the respective application is determined by the available installation space and the torque to be compensated / the counter-torque to be applied and the required pivoting range of the milling spindle 6.
    The arrangement shown in Figure 3a is a spring assembly according to the inscribed first preferred embodiment of the invention of Figure 2. It comprises a single spring which at its two ends 27, 28 and at an intermediate position 29 via one or more auxiliary elements with the housing 4 and the shaft 7 is connected.
    The arrangement shown in Figure 3b shows a combination of two identical springs 30a and 30b, which have a magnitude equal in stiffness c.
    In contrast, in FIG. 3c, the spring arrangement comprises two different springs 31, 32 which have different dimensions but also a stiffness C of equal magnitude in terms of magnitude.
    The spring arrangement shown in Figure 3d corresponds in structure to the arrangement of Figure 3c. In contrast to this, however, the individual springs have a different magnitude of stiffness c.
    Figure 3e shows a combination of a single spring 33 and a Parallelschal¬tung two springs 34, 35, wherein the parallel connected part of the spring assembly with the springs 34 and 35 and the second part of the spring assembly with the spring 33 a moderate amount have the same rigidity q.
    The arrangement shown in Figure 3f comprises a single spring 36 which, however, is not connected in an intermediate position to the housing 4 or the shaft 7, but at their respective ends 37, 38th
    Figure 4a shows a sectional view of another preferred embodiment of the inventive device with an integrated, inner profile sleeve 39 and an additional outer profile sleeve 40 for adjusting the available Gegendrehmo¬ments.
    The spring arrangement is implemented according to the concept shown in Figure 3f and not biased. It accordingly comprises, in this embodiment of the invention, a single leg spring 14 which is connected at its respective ends 41, 42 to the housing 4 and the shaft 7, respectively (connection not shown). The inner profile sleeve 39 has an outer profile surface 43 which is shaped such that the leg spring 14 in the neutral position of the axis of rotation 8, i. the vertical position of the milling spindle 6, on a defined length U to the profile surface 43 of the profile sleeve 39 applies and thus is not effective on this length.
    The outer profile sleeve 40, however, has an inner profile surface 44, which is also formed such that the leg spring 14 in the neutral position of the axis of rotation 8 on a defined length L2 to the profile surface 44 of the profile sleeve 40anlegt and thus on this length is not effective. The stiffness of the spring arrangement is thus determined by the free effective length LWirko of the leg spring 14.
    FIG. 4b shows a sectional illustration of the preferred embodiment of the invention according to FIG. 4a in a position deviating from the neutral position, in which the axis of rotation is at a defined angle β with respect to the neutral position of the axis and thus the vertical position of the milling spindle 6 is twisted.
    Upon rotation of the shaft 7 in a first direction, the diameter of the leg spring 14 increases and thus it releases depending on the rotation angle ß on a certain length L ^ ß) of the profile surface 43 of the inner profile sleeve 39. At the same time, the leg spring 14 depending on the rotation angle ß on a certain length I_2 (ß) to the profile surface 44 of the outer profile sleeve 40 at.
    Upon rotation of the shaft 7 in a direction opposite to the first direction second direction reduces the diameter of the leg spring 14 against it, and thus this applies depending on the rotation angle ß on a certain length U (ß) to the profile surface 43 of the inner profile sleeve 39 at , At the same time, the leg spring 14 releases depending on the angle of rotation ß on a certain length L2 (ß) of the profile surface 44 of the outer profile sleeve 40th
    In summary, it can be stated for this preferred embodiment that the effective length LWirk (β) of the leg spring 14 and thus its rigidity is determined by the shaping of the profile surfaces 43, 44 of the two profile sleeves 39, 40. By adapted to the respective application design and design of the leg spring 14 and the two profile sleeves 39, 40 so that the rotation angle-dependent course of the available counter torque of the device according to the invention can be adjusted individually.
    权利要求:
    Claims (17)
    [1]
    Claims 1. A device for compensating a torque which is caused by a force, in particular the weight, acting on a mass point eccentrically deflected about a horizontal shaft (7), the mass point in particular being the center of gravity of a tool of a machine tool ( 1), comprising: a pedestal, opposite which the shaft (7) is rotatable, and a balance spring (13), wherein the balance spring (13) is configured and arranged such that the shaft (7) rotates with respect to the pedestal counteracting counter torque is acted upon.
    [2]
    2. Apparatus according to claim 1, wherein the mass point of gravity of a milling spindle (6) of a machine tool (1).
    [3]
    3. Device according to claim 1 or 2, wherein the compensating spring (13) is at least partially disposed around the shaft (7) around.
    [4]
    4. Device according to one of the preceding claims, wherein the compensating spring (13) connected to both the base and with the shaft (7), preferably attached to this ange¬bracht.
    [5]
    5. Device according to one of the preceding claims, wherein the shaft (7) is rotatable from a zero position in two opposite directions of rotation and wherein the counter-torque of a rotation of the shaft (7) in each of the two directions of rotation respectively counteracts.
    [6]
    6. Device according to one of the preceding claims, wherein the counter torque is proportional to a deflection angle of the shaft (7).
    [7]
    A device according to any one of the preceding claims, wherein the compensating spring (13) is in the form of a helical spring, in particular a leg spring (14), which extends around the shaft (7) surrounding the shaft (7).
    [8]
    8. Device according to one of the preceding claims, wherein the compensating spring (13) comprises a bending spring or a plurality of bending springs, which is preferably designed as a leg spring (14) or designed as leg springs (14).
    [9]
    9. Device according to one of the preceding claims, wherein the compensating spring (13) on the shaft (7) and / or the base is attached by a clamping connection.
    [10]
    10. Device according to one of the preceding claims, wherein the compensating spring (13) is formed in several parts, in particular in two parts.
    [11]
    11. Device according to one of the preceding claims, wherein the compensating spring (13) is biased.
    [12]
    12. Device according to one of the preceding claims, wherein the base comprises a shaft (7) surrounding the housing (4).
    [13]
    A device according to any one of the preceding claims, wherein the shaft (7) is rotatable relative to the base by a drive, in particular an electric motor (12), for deflecting the center of mass.
    [14]
    14. Device according to one of the preceding claims, wherein the compensating spring (13) between the shaft (7) and the base is integrated.
    [15]
    15. Device according to one of the preceding claims, wherein with at least one profile sleeve (39, 40) is a stiffness modulation of the compensating spring (13), which is preferably designed as a small spring (14) is generated.
    [16]
    16. The apparatus of claim 15, wherein the compensating spring (13) force and / or formschlüs¬sig on the at least one profile sleeve (39, 40) is mounted.
    [17]
    17. The apparatus of claim 15 or 16, wherein the compensating spring (13) is non-positively and / or formschlüssig attached to the shaft (7) and / or the base. For this 7 sheets drawings
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    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
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    法律状态:
    2016-10-15| HC| Change of the firm name or firm address|Owner name: EMCO GMBH, AT Effective date: 20160825 |
    2019-05-15| MM01| Lapse because of not paying annual fees|Effective date: 20180930 |
    优先权:
    申请号 | 申请日 | 专利标题
    DE202012009295.2U|DE202012009295U1|2012-09-27|2012-09-27|Device for balancing a torque|
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