Elastic dog clutch

Abstract

The present invention relates to a dog clutch (1) comprising an inner ring element (12) and an outer ring element (22), between which a middle ring element (32) is arranged, wherein the inner ring element (12) and the adjacent middle ring element (32) form an inner annular gap (14), and the middle ring element (32) and the adjacent outer ring element (22) form an outer annular gap (24), wherein bearing pockets are formed on the ring elements, which form pairs of bearing spaces, in which deformable pressure bodies are arranged, and wherein bearing pocket bases (42) extend in the bearing pockets (40), against which the elastically deformable pressure bodies (50a, 50i) rest and are force-coupled therewith in such a way that the torque MX can be transmitted via said pressure bodies between the outer ring element (22) and the inner ring element (12) with the middle ring element (32) interposed, wherein the pressure bodies (50) are designed as roller elements, and wherein a plurality of bearing pocket bases (42) have a bearing pocket base section (44) which points in the radial direction RR to the respective annular gap (14, 24) and which merges into a ramp base section (46) trailing or leading in the circumferential direction RU and likewise pointing in the radial direction RR to the respective annular gap (14, 24), the geometry of which ramp base section, in particular when viewed in a coupling cross-sectional plane perpendicular to the axis of rotation AX, differs from the geometry of the bearing pocket base section.

Description

[0001]P134838PC00 Centa-Antriebe Kirschey GmbH Title: Elastic claw coupling Description The present invention relates to an elastic claw coupling, and in particular to a claw coupling that is rotatable about a rotational axis AX, for transmitting a torque MX acting about this rotational axis AX from a drive means to an output means. The claw coupling has a first coupling element, comprising an inner ring element extending in particular concentrically to the rotational axis AX along a first circumference U1, and a second coupling element rotatably mounted relative to the first coupling element.also comprising an outer ring element extending, in particular, concentrically to the rotational axis AX along an outer circumference U2. The first coupling element is connected or connectable to the output means, and the second coupling element is connected or connectable to the drive means, or vice versa. The designation first and second coupling element is merely for ease of understanding and does not define which coupling element is or can be assigned to which means. Pressure bodies are force-coupled between the inner ring element and the outer ring element in such a way that a torque can be transmitted between the inner ring element and the outer ring element. Such claw couplings are known from the prior art. The respective ring elements usually have one or more claws, between which the pressure elements are force-coupled, usually without play. Different claw arrangements are possible.Claw designs as well as geometries and arrangements of the pressure bodies are conceivable. In particular, claws are usually designed in an isolated manner and arranged essentially in a ring on the coupling element. However, the very high susceptibility to wear of the claw couplings known from the prior art has proven to be a disadvantage, especially when it comes to offering claw couplings with a very soft response. In addition, there is the problem of providing couplings that have very good resonance damping or that are designed to compensate for resonances between the output and drive means to the maximum. It is also relevant that most known couplings do not succeed in generating an increasing stiffness curve of the coupling depending on the speed of the drive means. In particular, no satisfactory solution is known to provide a soft response at low speeds that then,with increasing speed, increases more or less linearly. The object of the present invention is therefore to provide a claw clutch which, with a simple design, allows a permanent power coupling between a drive means and an output means that responds in accordance with the above requirements. This object is achieved by a claw clutch according to the independent claim. In particular, this object is achieved by an elastic claw clutch rotatable about an axis of rotation AX for transmitting a torque MX acting about the axis of rotation AX from a drive means to an output means, with a first clutch element comprising an inner ring element extending in particular concentrically to the axis of rotation AX along a first circumference U1, and a second clutch element rotatably mounted relative to the first clutch element,comprising an outer ring element extending in particular concentrically to the rotation axis AX along an outer circumference U2, wherein the first coupling element is connected or connectable to the output means and the second coupling element is connected or connectable to the drive means, or vice versa, wherein the inner ring element and the outer ring element are arranged facing each other in such a way that they form a common annular space between them, wherein in this common annular space, at least one middle ring element is arranged which is rotatably mounted relative to the inner ring element and the outer ring element in the circumferential direction RU, wherein the inner ring element and the adjacent middle ring element form an inner annular gap, and the middle ring element and the adjacent outer ring element form an outer annular gap, wherein bearing pockets are formed on the ring elements, the pocket openings of which point into the respective annular gap, wherein,radially inward-facing outer bearing pockets are formed on the outer ring element, radially outward-facing outer bearing pockets and radially inward-facing inner bearing pockets are formed on the middle ring element, and radially outward-facing inner bearing pockets are formed on the inner ring element, wherein mutually facing inward and outward-facing outer bearing pockets form outer bearing spaces, and mutually facing inward and outward-facing inner bearing pockets form inner bearing spaces, wherein elastically deformable outer pressure bodies are arranged in the outer bearing spaces, and elastically deformable inner pressure bodies are arranged in the inner bearing spaces, and wherein bearing pocket bases extend in the bearing pockets, against which the elastically deformable pressure bodies rest and are force-coupled to them in such a way that the torque MX can be transmitted between the outer ring element and the inner ring element with the middle ring element interposed,wherein the pressure bodies are designed as rolling elements, in particular rollers, with a diameter øD, which are each rotatable about their rolling axis, coaxial with the rotation axis AX along the bearing pocket bottoms, and wherein a plurality of bearing pocket bottoms have a bearing pocket bottom section pointing in the radial direction RR towards the respective annular gap, which transitions into a ramp bottom section leading or trailing in the circumferential direction RU and also pointing in the radial direction RR towards the respective annular gap, the geometry of which differs from the geometry of the bearing pocket bottom section, particularly when viewed in a coupling cross-sectional plane perpendicular to the rotation axis AX. It should be noted that the designations "pointing outwards" or "inwards", "outer" or "inner", and similar specifications,from a reference point on the rotational axis AX of the coupling. For example, "pointing outwards" means "pointing outwards as viewed from the rotational axis AX." A key aspect of the invention is therefore the freely mounted and, in particular, rotatably mounted arrangement of the middle ring element between the outer and inner ring elements, particularly in combination with the bearing pocket bottoms provided with ramp bottom sections. Of course, a plurality of such middle ring elements can also be arranged here, whereby in addition to the inner and outer annular gaps, further inner and outer annular gaps are then formed with respect to the adjacent middle ring elements. The arrangement with such a plurality of middle ring elements is also encompassed by the scope of the invention. Due to the force coupling of the pressure bodies to the adjacent ring elements and arranged in the annular gaps formed by these ring elements,Torque is transmitted from the inner or outer ring element assigned to the drive means via the middle ring element to the outer or inner ring element assigned to the output means. Optionally, the intermediately mounted pressure bodies are deformed during the transmission of torque between the adjacent ring elements. Optionally, the ring gaps and in particular adjacent ring gaps are designed as rings concentric with the rotation axis AX. These rings do not necessarily have to correspond to an ideal circular shape; they can have recesses, projections, or similar geometric features. Optionally, the aforementioned circumferences U1 and U2 or circumferences of other provided, in particular middle, ring elements are of different sizes. In a special embodiment, the circumferences are so large that they allow all ring elements to be arranged concentrically with one another.wherein their respective centers lie on the rotation axis AX. The circumferences can have a circumferential region with a width extending in the radial direction, in which the ring elements are arranged. The ring elements can be integrally formed all the way around, but they can also consist of several individual components. It is conceivable for a ring element, and in particular all ring elements, to have wall surfaces facing in the radial direction, with opposite wall surfaces of two adjacent ring elements each defining an annular gap or defining partial areas of such an annular gap. Such a definition also includes wall surfaces that are not completely orthogonal to the radial direction of the claw coupling or the respective coupling element, but also inclined thereto. Optionally, the ring elements extend in a plane that is coaxial with the rotation axis. The ring elements or their wall elements are optionally arranged orthogonally to a plane,which runs perpendicular to the rotation axis AX. Bearing pocket bottoms of opposing ring elements, each of which has at least one pressure body in contact with it, are optionally designed coaxially along the rotation axis AX. Along the circumferential direction RU, it is conceivable for the wall elements to move relative to and away from each other, or even to run surface-parallel to each other. The pressure bodies are designed, as described, as rolling elements, each of which is rotatable about its rolling axis, coaxial to the rotation axis AX. Optionally, the pressure bodies are arranged in the circumferential direction RU in the respective annular gap and optionally rollable along the bearing pocket bottoms. A rotation or rolling movement occurs, for example, when two adjacent ring elements move relative to each other in the circumferential direction, for example, one ring element in the direction of the acting torque, while the other adjacent ring element is not yet moved or is moved to a lesser extent.The movement of one ring element causes the intermediately mounted pressure body to move along with it. Optionally, the pressure body rolls along the bearing pocket base of at least one ring element and optionally along the bearing pocket bases of both adjacent ring elements. A rolling movement can be performed either with or without deformation of the pressure bodies. It is conceivable that during a rolling movement, the pressure body initially deforms only slightly or not at all, and then increasingly, thereby increasing the deformation force and thus also the pressure between the two adjacent ring elements. Optionally, a bearing space extends coaxially to the rotation axis and optionally in such a way that it defines a bearing volume that extends along this coaxial axis. Optionally, the pressure body is inserted into this bearing space, which optionally also has a main extension axis.which extends coaxially to the axis of rotation. This is particularly conceivable when the pressure elements are designed as rolling elements. A rolling movement of the pressure element optionally occurs around an axis coaxial to the axis of rotation. Optionally, at least two mutually facing bearing pocket bottoms, each of these bearing pocket bottoms arranged on one of the adjacent ring elements, encompass at least one pressure element arranged between them in the annular gap, at least partially in a ring shape or the like. In particular, they optionally encompass the pressure element in such a way that a deformation-free radial movement of the pressure element is prevented. The same is optionally conceivable for a deformation-free movement in the circumferential direction. To prevent movement of the pressure elements in the axial direction, i.e., coaxial to the axis of rotation, it is conceivable to arrange end face bearings on the claw coupling.which prevent the thrust bodies from axially sliding out of the bearing spaces or bearing pockets in the direction of the rotation axis. Such end face bearings can optionally be arranged on the central ring element. In addition or alternatively, it is also conceivable to attach such end face bearings to the outer and / or inner ring element. Such end face bearings can, for example, be bearing plates against which the thrust bodies rest, particularly in the deformed state. The bearing pockets can be designed such that, in the event of a particularly radial deformation of the thrust bodies as a result of a torque load acting on the coupling, in addition to this radial deformation due to the force coupling with the bearing bases, there is also an axial deformation and, in particular, a change in length, in particular an increase in length, of the thrust bodies along their axial main axis. If end face bearings are provided,In this state, the pressure bodies optionally rest against these end face bearings. They can also have bearing elements for reducing friction with respect to the pressure bodies and in particular their end faces, which optionally rest against the end face bearings. Such end face bearings can, for example, have plates, plate rings, contact surfaces, etc. It is conceivable that at least two mutually facing bearing pocket bottoms, each of these bearing pocket bottoms arranged on one of the adjacent ring elements, are aligned with respect to the circumferential direction RU of the claw coupling in such a way that, upon a load movement BL of one of the ring elements due to the acting torque MX, the relative distance a measured in the radial direction RR of at least partial sections of the mutually facing bearing pocket bottoms, optionally at locations where the pressure body rests,is reduced. During a load movement BL, optionally at least partial sections of the opposing bearing pocket bottoms move towards each other. A pressure body arranged in the storage space or between the mutually facing bearing pocket bottoms can be compressed in this way. Optionally, the bearing pocket bottoms are designed and in particular shaped such that at least partial areas of opposing bearing pocket bottoms not only move towards each other, but also move relative to each other in the circumferential direction. In such an arrangement, an intermediate pressure body is optionally subjected to a shear load. Such a shear load can transfer a torque from one ring element to an adjacent ring element. In this way, a relationship can be established between occurring radial compressions and shear compressions. It is conceivable to design the bearing pocket bottoms such thatthat with increasing radial compression of the pressure bodies, an increasingly greater shear force can be transmitted in the circumferential direction. Optionally, the bearing pocket bottoms are designed as bearings for the pressure bodies in such a way that, when the torque MX is applied, they exert a circumferential force component FU, optionally a shear force component in the direction RM of the torque, and a radial force component FR in the radial direction RR on the adjacent pressure bodies. Optionally, in this context in particular, the bearing pocket bottoms have wall elements that are inclined to the circumferential and radial directions.in order to cause both a circumferential force component and a radial force component on the respective pressure body during a movement of the ring elements relative to one another. The orientation of the bearing pocket bottoms with respect to the circumferential direction and the radial direction can be designed variably. Through such a variable design, for example, the increase and decrease of the circumferential force component and / or the radial force component can be controlled. Optionally, at least two mutually facing bearing pocket bottoms, each of these bearing pocket bottoms arranged on one of the adjacent ring elements, are aligned with respect to the circumferential direction of the claw coupling in such a way that, upon a load movement BL of one of the ring elements in the direction of the acting torque MX (and in particular caused by the torque MX), the adjacent ring element deforms the pressure body mounted between the bearing pocket bottoms,optionally moved in the same direction with a time delay. In order to enable compression of the pressure bodies depending on the relative movement of the adjacent ring elements, for example, a width of at least one annular gap running in the radial direction, viewed over its circumference, is intermittently designed to be smaller and larger. In other words, this means that the width can change over the circumference of the annular gap. Such a change can then achieve compression of an intermediate pressure element during a relative movement occurring, in particular, in the circumferential direction, between adjacent ring elements and, in particular, bearing pocket bottoms of these ring elements. The bearing pockets optionally form a bearing shell for accommodating a portion of the pressure body. Different geometries of these bearing pockets are conceivable, as described in more detail below. It is conceivable,that bearing spaces for receiving at least one pressure body are formed by two opposing bearing pockets, each of these bearing pockets arranged on one of the adjacent ring elements, wherein at least one pressure body is received or can be received both in the bearing pocket of one ring element and in the bearing pocket of the adjacent ring element. The bearing pockets optionally complement each other in such a way that they fix the pressure body in a fixed position, particularly in an unloaded state of the claw coupling. As already mentioned above, it is conceivable that the pressure bodies can be rolled, particularly in the circumferential direction, in these bearing pockets, and particularly during a relative movement occurring between two opposing bearing pockets. Such a rolling movement can optionally occur with simultaneous deformation of the pressure body. It is conceivable that with two opposing bearing pockets,Each of these bearing pockets is arranged on one of the adjacent ring elements, in the circumferential direction RU and, when no torque MX is applied, is aligned with one another such that their pocket low points PT lie on a common radial axis AR. Optionally, two opposing bearing pockets define a maximum-sized bearing space for a pressure hull when no torque MX is applied to the claw coupling. It is conceivable to design bearing pockets such that the bearing space formed by the bearing pockets is reduced as soon as a torque MX is applied and, in particular, as soon as at least one ring element is moved relative to the other ring element in the circumferential direction due to the applied torque. It is conceivable to reduce the bearing space and, in particular, the volume of the bearing space in such a way that the pressure hull mounted therein is compressed. It is conceivablethat a depth T of at least one bearing pocket, extending in the radial direction RR, changes in the circumferential direction RU of the ring element on which the bearing pocket is formed, optionally changes continuously, and further optionally increases and decreases again. A linear change is conceivable in sections, but changes can also be implemented with a changing gradient. In particular, the change in depth can be exponential, parabolic, or in the shape of a clothoid. It is conceivable that, due to the correspondingly reduced depth of the bearing pockets, an increasing compression of the pressure body mounted therein occurs. It is conceivable to design the reduction in depth in such a way that, depending on a load movement around the rotation axis of the ring element, a linearly increasing compression of the pressure body occurs; however, it is also conceivable to design the change in depth in such a way that a different increase in compression,for example, an exponential compression. It is conceivable to arrange bearing pockets in such a way that with a small load movement, especially when low torques are applied, a much lower compression occurs than with a larger load movement, e.g., due to an increasing torque. This guarantees, among other things, that the claw coupling responds very smoothly during initial deflections of the ring element. With increasing deflection, the coupling then becomes harder. It is conceivable that during a relative movement of the ring elements relative to one another in the circumferential direction, the bearing pocket bottoms of the adjacent ring elements move past one another in such a way that, due to bearing pocket bottom areas that are arranged at an angle to the circumferential direction, their relative distance decreases.which leads to compression of the pressure hulls. The pressure hull can have a cylindrical shape or a similar rotationally symmetrical shape. Its rotational symmetry axis optionally extends coaxially to the rotational axis of the coupling. Starting from this rotational symmetry axis, at least one radius of the pressure hull optionally extends co-planar to the coupling cross-sectional plane perpendicular to the rotational axis AX. It is conceivable that the elastically deformable inner pressure hulls arranged in the inner bearing spaces, optionally in the undeformed state, have a larger diameter ØDi than the elastically deformable outer pressure hulls arranged in the outer bearing spaces, and optionally a diameter ØDi in the range between 1.02-1.2 times larger, further optionally 1.05-1.15 times larger. In a pressure hull,which is designed as a rotational body deviating from a cylindrical shape and having different radii around its rotational symmetry axis, the above relationship can be determined from a comparison of the mean values ​​of the radii of the pressure bodies. It is conceivable that the elastically deformable inner pressure bodies arranged in the inner bearing spaces, optionally in the undeformed state, have a larger volume than the elastically deformable outer pressure bodies arranged in the outer bearing spaces. It is conceivable that the material used in the elastically deformable outer pressure bodies and the elastically deformable inner pressure bodies has essentially the same degree of hardness. It is conceivable that the elastically deformable outer pressure bodies and the elastically deformable inner pressure bodies are made of the same material. It is conceivablethat a majority of the storage pocket base sections and / or ramp base sections extend straight in the direction of the rotation axis AX. It is conceivable that a majority of the storage spaces extend in the direction of the rotation axis AX with a constant volume and / or straight. It is conceivable that at least one storage pocket base section and / or at least one ramp base section extend in a circular arc, viewed in the coupling cross-sectional plane perpendicular to the rotation axis AX, wherein the radius RL of the storage pocket base section is optionally smaller than the radius RR of the adjoining ramp base section. Circular arc can be understood in particular as a circular segment arc, i.e., an arc shape that is part of a fully encircling circular arc. The circular segment arc shape of the storage pocket base section can optionally have a circumferential angle between 50° and 120°.further optionally 60° and 110°. The circular segment arc shape of the ramp floor section can optionally have a circumferential angle of less than 70°, further optionally less than 70°. It is conceivable that the radius RLa of at least one storage pocket floor section of at least one outer storage space and / or the radius RLi of at least one storage pocket floor section of at least one inner storage space is substantially equal to the radius, optionally in the undeformed state, of the pressure hull stored therein. It is conceivable that the radius RRa of at least one ramp floor section of at least one outer storage space and / or the radius RRi of at least one ramp floor section of at least one inner storage space is greater than the radius, optionally in the undeformed state, of the pressure hull stored therein. It is conceivable,that at least one storage pocket base section of at least one outer storage space and at least one storage pocket base section of at least one inner storage space, viewed in the coupling cross-sectional plane perpendicular to the rotation axis AX, each extend in a circular arc. It is conceivable that the radius RLa of the storage pocket base section of the outer storage space is smaller than the radius RLi of the storage pocket base section of the inner storage space, and / or at least one ramp base section of at least one outer storage space and at least one ramp base section of at least one inner storage space, viewed in the coupling cross-sectional plane perpendicular to the rotation axis AX, each extend in a circular arc. It is conceivable that the radius RRa of the ramp base section of the outer storage space is smaller than the radius RRi of the ramp base section of the inner storage space. It is conceivable,that a ramp floor section and a storage pocket floor section of at least one outer storage space extend in the coupling cross-sectional plane perpendicular to the rotation axis AX, each in a circular arc, wherein the radius RRa of the (particularly inwardly facing outer) ramp floor section is 1.5 - 4.0 times, optionally 2.0 - 3.5 times greater than the radius RLa of the (particularly inwardly facing outer) storage pocket floor section, and / or a ramp floor section and a storage pocket floor section of at least one inner storage space extend in the coupling cross-sectional plane perpendicular to the rotation axis AX, each in a circular arc, wherein the radius RRi of the (particularly inwardly facing inner) ramp floor section is 1.0 - 3.0 times, optionally 1.5 - 2.5 times greater than the radius RLi of the (particularly inwardly facing inner) Storage bag bottom section. It is conceivableThe radii of the inner bearing spaces are designed to be complementary to the above radii and in proportion to the sizes, in particular the radii of the inner and outer pressure bodies. It is conceivable that at least one bearing pocket base section extends in the coupling cross-sectional plane perpendicular to the rotation axis AX and extends concavely with respect to the adjacent inner or outer annular gap. It is conceivable that at least one bearing pocket base, viewed in the coupling cross-sectional plane perpendicular to the rotation axis AX, is designed as a trough in which the pressure body mounted therein is fixedly guided in the unloaded state of the coupling. It is conceivable that at least one bearing pocket base, comprising a bearing pocket base section and a ramp base section, extends curvedly, viewed in the coupling cross-sectional plane perpendicular to the rotation axis AX.wherein its extension curve, with respect to a distance from the rotation axis AX, has a vertex PS with a maximum distance Amax or a minimum distance Amin from the rotation axis AX, wherein the vertex PS lies in the bearing pocket base section (44). The vertex PS can have such a maximum distance Amax, in particular in the case of an inwardly facing inner and / or outer bearing pocket. The vertex PS can have such a minimum distance Amin, in particular in the case of an outwardly facing inner and / or outer bearing pocket. If it is assumed that the vertex PS lies on a radial axis through the rotation axis AX, and the center of the circular segment arc defining the bearing base section also lies on this radial axis, then optionally the circular arc of the bearing base section extending in the direction of the adjoining ramp base section is bent by a partial angle of 2° - 20°.optionally extends 3° - 10° beyond this radial axis and the vertex PS. At the end of this circular arc lies the transition point PÜ to the arc and in particular the circular arc, in particular the circular segment arc of the ramp arc section. The ramp floor section and the storage pocket floor section optionally merge continuously into one another at a transition point PÜ. It is conceivable that, viewed in the coupling cross-sectional plane perpendicular to the rotation axis AX, opposite ramp floor sections forming a common storage space are essentially, in particular exactly, the same length. The length of the ramp floor section is optionally, viewed in the coupling cross-sectional plane perpendicular to the rotation axis AX, the length from the vertex PS or the transition point PÜ and the free end of the ramp floor section,located on the outer or inner annular gap. In particular, all ramp floor sections of the inner storage spaces and / or the outer storage spaces can optionally be of the same length. It is conceivable that, viewed in the coupling cross-sectional plane perpendicular to the rotation axis AX, a segment arc center point of a circular arc-shaped storage pocket floor section of at least one storage pocket floor lies on a radial axis through the rotation axis AX, and a segment arc center point of a circular arc-shaped ramp floor section of the same storage pocket floor lies on a parallel axis orthogonal to the radial axis offset by a value X. Optionally, at least in a plurality,Optionally, only one pressure body is arranged in all storage spaces. In a special embodiment, instead of the circular arc shape of the storage pocket section and / or the ramp floor section, a similar continuous arc shape can also be provided. Within the scope of the invention, this is then also understood to mean a "circular arc shape" or "circular arc-shaped." Optionally, the shape of the storage pocket is designed, at least in sections, to be complementary to the shape of the pressure body and, in particular, such that the pressure body rests against it without play. At least one ramp floor section optionally differs from the geometry of the remaining storage pocket or a section thereof, in particular the geometry in an area in which the pressure body is arranged when no torque is applied to the claw coupling.This is optionally the bearing base section. The response behavior of the claw coupling can be determined via the geometry of a ramp base section. The ramp base section can optionally have a continuous gradient and / or an increasing gradient in the radial direction toward the annular gap. In addition to a continuous (increasing) gradient, the gradient can also increase discontinuously. An increase in the gradient means, as soon as a pressure hull is moved and, in particular, rolled along this ramp base section, a correspondingly increasing compression of the pressure hull.where optionally the forces that can be transmitted in the circumferential direction increase. With the same pitch, the compression increases evenly. Such a (rolling) movement can occur during a relative movement of two adjacent ring elements. Optionally, in adjacent ring elements, opposite ramp base sections of bearing pockets are designed as trailing ramp base sections on one ring element and as leading ramp base sections on the adjacent ring element with respect to the torque direction RM. Leading here optionally means that they are designed at the front end of the bearing pocket in the direction of the torque. Trailing optionally means that they are designed at the rear end of the bearing pocket with respect to the torque direction. It is conceivable that in the ring element connected or connectable to the drive means,Ramp base sections are designed as trailing ramp base sections with respect to the torque direction RM, and optionally opposite ramp base sections of the adjacent ring element are designed as leading ramp base sections. Optionally, viewed in a coupling cross-sectional plane perpendicular to the rotation axis AX, two bearing pockets define a bearing space, wherein an inwardly facing bearing pocket has a bearing pocket base section and a subsequent ramp base section viewed in a direction of rotation about the rotation axis, and an outwardly facing bearing pocket has a bearing pocket base section and a leading ramp base section viewed in the same direction of rotation about the rotation axis. It is also conceivable that bearing pocket sections, optionally ramp base sections, formed on a ring element, extend in the circumferential direction RU such that on the adjacent ring element,At least in a state in which no torque MX acts, no bearing pocket sections are formed opposite one another in the radial direction RR. It is conceivable, particularly in this context, that opposing bearing pockets of adjacent ramp floor sections extend offset from one another in the circumferential direction. Bearing pockets can begin on one ring element, while the opposite bearing pocket begins somewhat later or earlier. The same naturally applies to the ends of these bearing pockets. It is possible that all bearing pockets of a ring element are identical. It is conceivable that opposing bearing pockets of adjacent ring elements are identical. However, it is also conceivable that bearing pockets of a ring element located further outward radially are somewhat larger and, in particular, longer in the circumferential direction than bearing pockets located further inward, in particular of the adjacent ring element. It is conceivable,Opposite bearing pockets of two adjacent ring elements are designed to be identical, smaller, or larger, but with the same geometry, but rotated by 180° around an axis, optionally by 160° - 200° coaxially to the rotation axis. Further embodiments of the invention emerge from the subclaims. The invention is described below with reference to exemplary embodiments.which are explained in more detail in the accompanying drawings. The following schematically show: Figs. 1 and 2 are isometric views of an embodiment of the claw coupling from different viewing angles; Figs. 3 and 4 are views according to Figs. 1 and 2 without end bearings (rings); Fig. 5A is a cross-section through the embodiment according to Fig. 1; Fig. 5B is a detailed view of the view according to Fig. 5A; Fig. 5C is a further detailed view of the view according to Fig. 5A; Fig. 6 is a longitudinal section through the embodiment according to Fig. 6; Figs. 7 to 9 are different load and deflection states of the embodiment according to Fig. 1; Figs. 10 to 13 are further embodiments of the invention with differently acting moments. In the following, the same reference numerals are used for identical and identically acting components, with prime indices sometimes being used to distinguish them. Position indices a and i are also used.which can be used in conjunction with a component to further define its position. It should be noted that the designation of a component with a reference symbol without the further specifications "a" and "i" does not exclude the possibility that it is a correspondingly specified or specifiable component. Rather, this is included unless otherwise defined. Unless otherwise defined, all terms used herein (including technical and scientific terms) have the same meaning, and in particular a meaning as generally understood by a person of ordinary skill in the art when interpreted in the context of the description and the drawings. It is further understood that terms, such as those defined in commonly used dictionaries, are to be interpreted with reference to the technical field relevant here.and not in an idealized or overly formal sense, unless explicitly defined as such. In certain cases, a detailed description of well-known devices and methods may be omitted to avoid redundancy of the description. The description of specific embodiments and the terminology used therein is not intended to limit the invention. The singular forms "a," "an," "the," and "the" may also include the plural forms unless the context clearly indicates otherwise. The term "and / or" includes any and all combinations of one or more of the associated listed items. It is understood that the terms "comprises" and / or "comprising" indicate the presence of recited features, but do not preclude the presence or addition of one or more other features. Furthermore, it is understoodthat when a particular step of a method is stated to follow another step, it may follow that other step directly, or one or more intermediate steps may be performed before the particular step is performed, unless otherwise stated. In the same way, it is understood that when a connection between structures or components is described, that connection may be made directly or via intermediate structures or components, unless otherwise specified. The disclosure of all publications, patent applications, patents, and other literature mentioned herein is incorporated by reference in its entirety. In the event of a conflict, this specification, including its definitions, shall prevail. The invention is described herein with reference to the accompanying drawings,in which embodiments of the invention are shown. The invention may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein. Rather, the embodiments are provided herein so that this disclosure will be thorough and complete, and will fully but exemplarily convey the scope of the invention to those skilled in the art. The description of the exemplary embodiments should be read in conjunction with the accompanying drawings, which are incorporated herein by reference and are intended to be a part of the entire written description. In the drawings, the absolute and relative sizes of systems, components, layers, and regions may be exaggerated for clarity. Embodiments may be illustrated by schematic and / or cross-sectional illustrations.idealized embodiments and intermediate structures of the invention. Relative terms, as well as their derivatives, should be understood to refer to the orientation as described or shown therein in the drawing just discussed. These relative terms are used for convenience of description and do not require that the system be constructed or operated in a particular orientation unless explicitly stated otherwise. Any of the disclosed devices or parts thereof may be combined together or divided into further parts unless specifically stated otherwise. The mere fact that particular measures are recited in different sections or claims is not intended to indicatethat a combination of these measures cannot be advantageously undertaken. In particular, all conceivable combinations of the claims are to be considered as inherently disclosed. In this description, words such as "substantially," "approximately," or "generally / generally" are to be interpreted to include at least deviations of a measure of 10% or less, preferably 5% or less, or deviations from a form that would still fall within the scope of the respective definition for a person skilled in the art, unless otherwise specified. For the sake of clarity and in the interests of a stringent description, features are usually described herein as part of one or separate embodiments; however, it is to be understood that the scope of the invention may also include embodimentswhich have combinations of all or some of the described features. The illustrations according to Figs. 1 to 6 show an embodiment of the elastic claw coupling 1, with features as previously described in detail. All of the aforementioned embodiments are optionally present in this embodiment shown here. This applies both in combination and taken individually. In this respect, explicit reference is made to the previously described passages and these are transferred to the embodiments shown here. The embodiment shown here has a first coupling element 10 and a second coupling element 20. The first coupling element 10 is exemplarily connected to an output means, for example a transmission, and the second coupling element 20 is exemplarily connected to a drive means 2,for example, a motor. The first coupling element 10 and the second coupling element 20 are arranged so as to be rotatable relative to one another, this rotation being defined and controlled by force-coupling pressure bodies 50, as described in more detail below. The first coupling element 10 comprises an inner ring element 12, which runs particularly concentrically to the rotational axis AX along a first circumference U1. The second coupling element 20, on the other hand, comprises an outer ring element 22, which runs particularly concentrically to the rotational axis AX along an outer circumference U2. Of course, depending on the embodiment of the first and second coupling elements, the ring element of the second coupling element can be arranged as the inner ring element and the ring element of the first coupling element as the outer ring element. The definition of "first" and "second" is merely illustrative and does not constitute a restrictive,This particularly represents a defining position indication. The first coupling element is rotatably mounted relative to the second coupling element and, in particular, rotatably mounted along the rotational axis AX, around which the torque MX runs. The claw coupling 1 has a circumference that is also defined by a radius running through the rotational axis AX. The circumferential line of the claw coupling can be annular, but it can of course also have recesses and projections or similar geometric irregularities. The same applies to the geometries of the inner ring element and the outer ring element. The inner ring element 12 and the outer ring element 22 are arranged facing each other in such a way that they form a common annular space 60 between them. This annular space 60 is shown as an example in Figs. 5 and 5a. A central ring element 32 is arranged in this common annular space 60,which is rotatably mounted relative to the inner ring element 12 and the outer ring element 22. Optionally, the middle ring element is fundamentally mounted exclusively via pressure bodies 50 in the common annular space 60, at least with respect to movements along the sectional plane shown in Fig. 5A. The inner ring element 12 and the adjacent middle ring element 32 form an inner annular gap 14. The middle ring element 32 and the adjacent outer ring element 22 form an outer annular gap 24. As shown in detail in Fig. 5B, bearing pockets 40 are formed on the ring elements 12, 22, 32, the pocket openings 43 of which point into the respective annular gap 14, 24, wherein on the outer ring element 22 there are radially inwardly facing outer bearing pockets 40ai, on the middle ring element 32 there are radially outwardly facing outer bearing pockets 40aa and radially inwardly facing inner bearing pockets 40ii, and on the inner ring element 12 there are radially outwardly facing inner bearing pockets 40ia,are formed. Outer bearing pockets 40ai, 40aa facing inwards and outwards form outer bearing spaces 41a, and inner bearing pockets 40ii, 40ia facing inwards and outwards form inner bearing spaces 41i. Elastically deformable outer pressure bodies 50a are arranged in the outer bearing spaces 41a, and elastically deformable inner pressure bodies 50i are arranged in the inner bearing spaces 41i. The pressure bodies 50 are designed as rolling elements, in particular rollers, with a diameter ØD, each of which is rotatable about its rolling axis Aw coaxially to the rotation axis AX along bearing pocket bottoms 42. In the bearing pockets 40, these bearing pocket bottoms 42 are designed such that the elastically deformable pressure bodies 50a, 50i rest against them and are force-coupled to them in such a way thatthat the torque MX can be transmitted between the outer ring element 22 and the inner ring element 12 with the interposition of the middle ring element 32. A plurality of bearing pocket bottoms 42 have a bearing pocket bottom section 44 pointing in the radial direction RR towards the respective annular gap 14, 24, which merges into a ramp bottom section 46 trailing or leading in the circumferential direction RU and also pointing in the radial direction RR towards the respective annular gap 14, 24, the geometry of which, in particular viewed in a coupling cross-sectional plane perpendicular to the rotation axis AX,differs from the geometry of the bearing pocket bottom section 44. To distinguish between trailing and leading, one and the same direction of rotation RU must be taken as a basis. For example, with a clockwise direction of rotation RU assumed in Fig. 5B, a “leading ramp bottom section” 46aa is arranged counterclockwise offset in front of the associated bearing pocket bottom section 44aa, and a “trailing ramp bottom section” 46ai is arranged clockwise offset behind an associated bearing pocket bottom section 44ai. The pressure bodies 50 are designed as rolling elements, each of which is rotatable about its rolling axis AW, which runs coaxially to the rotation axis AX. As will be explained in more detail below, particularly with reference to Figs. As described in Figures 7 to 9, these pressure bodies 50 are arranged in a rollable manner in the circumferential direction RU in the respective annular gap 14, 24 and optionally along the bearing pocket bottoms 42. As described in detail below,This rolling movement occurs here, for example, with simultaneous deformation of the pressure bodies 10 upon application of the torque MX and upon execution of a load movement BL, as shown in Figs. 7 to 9. Opposing bearing pocket bottoms 42, each arranged on adjacent ring elements 12, 32 or 32, 22, form a common bearing space for at least, optionally exactly one of these pressure bodies 50. The bearing pocket bottoms 42 or the bearing pockets are optionally arranged and designed relative to one another in such a way that upon a load movement BL of one of the ring elements 12, 22, 32, here for example the outer ring element 20, as a result of the acting torque MX, the relative distance a measured in the radial direction RR is reduced at least by partial sections of the mutually facing bearing pocket bottoms 42. This means,that a pressure body arranged therein is compressed at least in the radial direction. This can occur particularly at locations where the pressure body rests against the bearing pocket bottoms. This process is shown in detail in Figs. 7 to 9. It can be seen that during a load movement BL of the outer ring element 22, as a result of the torque MX acting on it, the relative distance a1 to a3 shown in Figs. increases the further the outer ring element is moved in the moment direction RM or circumferential direction RU. It is fundamentally conceivable that the moment direction RM corresponds to the circumferential direction RU. It can also be seen that during this movement of the outer ring element, a deformation of the pressure bodies 50 arranged between the outer ring element 22 and the middle ring element 32 occurs.which, during the load movement of the outer ring element, then leads to a load movement of the middle ring element 32 (see Figs. 8 and 9). Here, too, a deformation of the pressure bodies mounted further inside occurs and ultimately to a torque transfer to the first coupling element mounted inside here or the inner ring element (not shown). It can also be seen in Figs. 7 to 9 that during the load movement of the individual ring elements 12, 22, 32, a rolling movement of the pressure bodies 50 occurs within the bearing pockets. As shown in particular in Fig. 5A, the bearing pocket bottoms can be designed as bearings for the pressure bodies 50 such that, when the torque MX and optionally the resulting load movement BL are applied, they generate a circumferential force component FU in the direction RM of the torque MX,and a radial force component FR acting in the radial direction RR on the adjacent pressure bodies 50. These two force components cause compression of the pressure body and, in addition, a torque transmission acting in the moment direction. The resulting radial force component can optionally define the response behavior of the claw clutch. It is conceivable, with the individual components again being shown in detail in Fig. 5a, that the elastically deformable inner pressure bodies 50i arranged in the inner bearing spaces 44i, optionally in the undeformed state, have a larger diameter ØDi than the elastically deformable outer pressure bodies 50a arranged in the outer bearing spaces 44a, and optionally a diameter ØDi in the range between 1.02-1.2 times larger, further optionally 1.05-1.15 times larger. Also shown here is,that at least one bearing pocket bottom section 44 and / or at least one ramp bottom section 46 extend in the shape of a circular arc when viewed in the coupling cross-sectional plane perpendicular to the rotation axis AX, wherein optionally the radius RL of the bearing pocket bottom section 44 is smaller than the radius RR of the ramp bottom section 46. It is conceivable that the radius RLa of at least one bearing pocket bottom section 44a of at least one outer bearing space 41a and / or the radius RLi of at least one bearing pocket bottom section 44i of at least one inner bearing space 41i is substantially equal to the radius, optionally in the non-deformed state, of the pressure body 50a or 50i mounted therein. It is conceivable that at least one bearing pocket bottom section 44a of at least one outer storage space 41a and at least one bearing pocket bottom section 44i of at least one inner storage space 41i are viewed in the coupling cross-sectional plane perpendicular to the rotation axis AX,each extend in a circular arc, wherein the radius RLa of the bearing pocket bottom section 44a of the outer storage space 41a is smaller than the radius RLi of the bearing pocket bottom section 44i of the inner storage space 41i, and / or at least one ramp bottom section 46a of at least one outer storage space 41a and at least one ramp bottom section 46i of at least one inner storage space 41i, viewed in the coupling cross-sectional plane perpendicular to the rotation axis AX, each extend in a circular arc, wherein the radius RRa of the ramp bottom section 46a of the outer storage space 41a is smaller than the radius RRi of the ramp bottom section 46i of the inner storage space 41i. It is conceivable that a ramp floor section 46a and a storage pocket floor section 44a of at least one outer storage space 41a extend in the coupling cross-sectional plane perpendicular to the rotation axis AX, each in a circular arc,wherein the radius RRa of the inwardly facing outer ramp base section 46ai is 1.5 - 4.0 times, optionally 2.0 - 3.5 times greater than the radius RLa of the inwardly facing outer bearing pocket base section 44ai. It is also conceivable for a ramp base section 46i and a bearing pocket base section 44i of at least one inner bearing space 41i to each extend in a circular arc in the coupling cross-sectional plane perpendicular to the rotation axis AX, wherein the radius RRi of the inwardly facing inner ramp base section 46ii is 1.0 - 3.0 times, optionally 1.5 - 2.5 times greater than the radius RLi of the inwardly facing inner bearing pocket base section 44ii. It is possible that at least one bearing pocket bottom 42, viewed in the coupling cross-sectional plane perpendicular to the rotation axis AX, is designed as a trough,in which the pressure body mounted therein is guided in a fixed position in the unloaded state of the coupling. It is conceivable that at least one bearing pocket base 42, comprising a bearing pocket base section 44 and a ramp base section 46, extends in a curved manner when viewed in the coupling cross-sectional plane perpendicular to the rotation axis AX, and its extension curve with respect to a distance from the rotation axis AX has a vertex PS (see Figs. 5B and 5C) with a maximum distance Amax from the rotation axis AX, wherein the vertex PS lies in the bearing pocket base section 44. The ramp base section 46 and the bearing pocket base section 44 merge into one another at a point PÜ. It is conceivable that the transition point PÜ corresponds to the vertex PS. It is conceivable (see Fig. 5C), viewed in the coupling cross-sectional plane perpendicular to the rotation axis AX,that a segment arc center point PML of a circular arc-shaped bearing pocket base section 44 of at least one bearing pocket base 42 lies on a radial axis AR through the rotation axis AX, and a segment arc center point PMR of a circular arc-shaped ramp base section 46 of the same bearing pocket base 42 lies on a parallel axis ARP offset by a value X, orthogonal to the radial axis. Fig. 5b shows in detail the circular segments emanating from the respective segment arc center points PML and PMR, the arcs of which, viewed in the coupling cross-sectional plane perpendicular to the rotation axis AX, define the geometry of the bearing pocket base sections 44 and the ramp base sections 46. If the bearing pocket base sections 44 and the ramp base sections 46 extend straight in the axial direction, geometric troughs with a circular radius result. It is conceivable that with adjacent ring elements 12, 32; 32,22 opposite ramp base sections 46 of bearing pockets 40, with respect to the torque direction RM on one ring element 12; 32 are designed as trailing ramp base sections 46b and on the adjacent ring element 32; 22 as leading ramp base sections 46a. This is shown in particular in Fig. 5A. In this embodiment, bearing spaces 41 for receiving at least one pressure body 50 are formed by two opposing bearing pockets, wherein this bearing pocket 40 is arranged on one of the adjacent ring elements 12, 22 or 32, 22. The bearing pockets or their bearing pocket openings face one another in this embodiment. At least one pressure body 50 is accommodated or can be accommodated in a bearing pocket 40 of one ring element 12, 32 as well as in the bearing pocket 40 of the adjacent ring element 32, 22. It can also be seen (see Fig. 5A),that optionally, in the case of the two opposing bearing pockets, the pocket low points PT of the bearing pockets can lie on a common radial axis AR when the torque MX is not applied. It can also be seen that when the torque MX is not applied, the pressure bodies mounted in the bearing pockets cannot be deformed. Only when the torque MX and the resulting load movement BL are applied do the opposing bearing pockets shift relative to each other, thereby deforming the pressure bodies with resulting force coupling in the radial and circumferential directions and thus leading to a torque transfer between the individual ring elements. The bearing pockets are defined in such a way that their depth changes along the circumferential direction RU and, in particular, changes continuously. The depth of these bearing pockets first increases and then decreases again in the circumferential direction. It is optionally possible,to determine the response behavior or load transfer capacity of the claw clutch via the gradient of the decrease or increase. As shown in detail in Figs. 5, 10 to 13, in adjacent ring elements 12, 32 or 32, 22, opposite ramp bottom sections 46 of bearing pockets 40 can be designed as trailing ramp bottom sections 46a on one ring element 12, 32 and as leading ramp bottom sections 46b on the adjacent ring element 32, 22 with respect to the torque direction RM. In the embodiments shown in Figs. 1 and 10, the outer ring element 22 connected to the drive means 2 has trailing ramp bottom sections 46b with respect to the torque direction RM. The adjacent ring element 32 has opposite ramp floor sections 46, which are designed as leading ramp floor sections 46a. As shown by way of example in Fig. 5C, it is conceivable that,Viewed in the coupling cross-sectional plane perpendicular to the rotation axis AX, opposite ramp floor sections (46) forming a common storage space have a substantially, in particular exactly, equal length LRBA. The length LRBA of the ramp floor section is optionally, viewed in the coupling cross-sectional plane perpendicular to the rotation axis AX, the length from the vertex Ps or transition point PÜ (as shown in Fig. 5C) and the free end of the ramp floor section, located at the outer or inner annular gap. In particular, all ramp floor sections of the inner storage spaces and / or the outer storage spaces can optionally be designed with the same length LRBA. Different embodiments are shown in Figs. 10 to 13.which differ in the direction of the applied torques MX as well as in the termination of the drive or output means. In Figs. 10 and 11, the drive means is connected to the outer ring element 22 or coupling element 20, whereby it acts on the second coupling element 20 counterclockwise in Fig. 10 and clockwise in Fig. 11. In Figs. 12 and 13, however, the first coupling element and thus the inner ring element 12 is the actively driven element connected to the drive means 2. Here, too, two different torque directions are shown (counterclockwise in Fig. 12 and clockwise in Fig. 13). Depending on the driven component and the torque direction, the coupling has different orientations of the trailing and leading ramp floor sections. In the embodiment shown here, optional storage pocket sections and in particular the ramp floor sections 46,formed on a ring element 12, 32, in the circumferential direction RU such that, at least in a state in which no torque MX is acting (see, for example, Fig. 5A and Figs. 10 to 13), no bearing pocket sections are formed opposite each other in the radial direction RR on the adjacent ring element 32, 22. It is conceivable that only after the load movement BL (see Figs. 7 to 9) has been carried out do the respective bearing pocket sections come into alignment, thus compressing the intermediately mounted pressure body.

Claims

Claims 1. An elastic claw coupling (1) rotatable about a rotational axis AX for transmitting a torque MX acting about the rotational axis AX from a drive means (2) to an output means (4), comprising: a first coupling element (10), comprising an inner ring element (12) extending in particular concentrically to the rotational axis AX along a first circumference U1, and a second coupling element (20) rotatably mounted relative to the first coupling element (10), comprising an outer ring element (22) extending in particular concentrically to the rotational axis AX along an outer circumference U2, wherein the first coupling element (10) is connected or connectable to the output means (4) and the second coupling element (20) is connected or connectable to the drive means (2), or vice versa, wherein the inner ring element (12) and the outer ring element (22) are arranged facing each other in such a way that they form a common annular space (60) between them,wherein in this common annular space (60), at least one middle ring element (32) is arranged, which is mounted rotatably relative to the inner ring element (12) and the outer ring element (22) in the circumferential direction RU, wherein the inner ring element (12) and the adjacent middle ring element (32) form an inner annular gap (14), and the middle ring element (32) and the adjacent outer ring element (22) form an outer annular gap (24), wherein bearing pockets (40) are formed on the ring elements (12, 22, 32), the pocket openings (43) of which point into the respective annular gap (14, 24), wherein on the outer ring element (22) there are radially inwardly facing outer bearing pockets (40ai), on the middle ring element (32) there are radially outwardly facing outer bearing pockets (40aa) and radially inwardly facing inner bearing pockets (40ii), and on the inner ring element (12) radially outwardly facing inner bearing pockets (40ia), wherein mutually facing inwardly and outwardly facing outer bearing pockets (40ai, 40aa) form outer bearing spaces (41a), and mutually facing inwardly and outwardly facing inner bearing pockets (40ii, 40ia) form inner bearing spaces (41i), wherein elastically deformable outer pressure bodies (50a) are arranged in the outer bearing spaces (41a), and elastically deformable inner pressure bodies (50i) are arranged in the inner bearing spaces (41i), and wherein bearing pocket bottoms (42) are formed in the bearing pockets (40), against which the elastically deformable pressure bodies (50a, 50i) rest and are force-coupled to them in such a way that the torque MX can be transmitted between the outer ring element (22) and the inner ring element (12) with the interposition of the middle ring element (32), wherein the pressure bodies (50) are designed as rolling elements, in particular rollers, with a diameter ØD, which each around its rolling axis,coaxial with the rotation axis AX along the bearing pocket bottoms (42), and wherein a plurality of bearing pocket bottoms (42) have a bearing pocket bottom section (44) pointing in the radial direction RR towards the respective annular gap (14, 24), which merges into a ramp bottom section (46) trailing or leading in the circumferential direction RU and also pointing in the radial direction RR towards the respective annular gap (14, 24), the geometry of which differs from the geometry of the bearing pocket bottom section (44), in particular viewed in a coupling cross-sectional plane perpendicular to the rotation axis AX, characterized in that the elastically deformable inner pressure bodies (50i) arranged in the inner bearing spaces (44i) have, in the undeformed state, a larger diameter ØDi than the elastically deformable outer pressure bodies arranged in the outer bearing spaces (44a). (50a), 2. Claw coupling according to one of claims 1,characterized in that the elastically deformable inner pressure bodies (50i) arranged in the inner bearing spaces (44i) have, in the undeformed state, a diameter ØDi which is in the range between 1.02 - 1.2 times larger than the elastically deformable outer pressure bodies (50a) arranged in the outer bearing spaces (44a).

3. Claw coupling according to one of claims 1 and 2, characterized in that the material used in the elastically deformable outer pressure body (50a) and the elastically deformable inner pressure body (50i) has a substantially identical degree of hardness.

4. Claw coupling according to one of the preceding claims, characterized in that the elastically deformable outer pressure bodies (50a) and the elastically deformable inner pressure bodies (50i) are made of the same material.

5. Claw coupling according to one of the preceding claims, characterized in that at least one bearing pocket base section (44) and / or at least one ramp base section (46) extend in a circular arc when viewed in the coupling cross-sectional plane perpendicular to the rotation axis AX, wherein the radius RL of the bearing pocket base section (44) is optionally smaller than the radius RR of the ramp base section (46).

6. Claw coupling according to one of the preceding claims, characterized in that the radius RLa of at least one bearing pocket bottom section (44a) of at least one outer bearing space (41a) and / or the radius RLi of at least one bearing pocket bottom section (44i) of at least one inner bearing space (41i) is substantially equal to the radius, optionally in the non-deformed state, of the pressure body (50a or 50i) mounted therein.

7. Claw coupling according to one of the preceding claims, characterized in that at least one bearing pocket bottom section (44a) of at least one outer bearing space (41a) and at least one bearing pocket bottom section (44i) of at least one inner bearing space (41i) each extend in the shape of a circular arc when viewed in the coupling cross-sectional plane perpendicular to the rotation axis AX, wherein the. Radius RLa of the storage pocket bottom section (44a) of the outer storage space (41a) is smaller than the radius RLi of the storage pocket bottom section (44i) of the inner storage space (41i), and / or at least one ramp bottom section (46a) of at least one outer storage space (41a) and at least one ramp bottom section (46i) of at least one inner storage space (41i) each extend in a circular arc when viewed in the coupling cross-sectional plane perpendicular to the rotation axis AX, wherein the radius RRa of the ramp bottom section (46a) of the outer storage space (41a) is smaller than the radius RRi of the ramp bottom section (46i) of the inner storage space (41i).

8. Claw coupling according to one of the preceding claims, characterized in that a ramp bottom section (46a) and a bearing pocket bottom section (44a) of at least one outer bearing space (41a) extend in the coupling cross-sectional plane perpendicular to the rotation axis AX, each in a circular arc,wherein the radius RRa of the (particularly inwardly facing outer) ramp floor section (46ai) is 1.5 - 4.0 times, optionally 2.0 - 3.5 times greater than the radius RLa of the (particularly inwardly facing outer) bearing pocket floor section (44a), and / or a ramp floor section (46i) and a bearing pocket floor section (44i) of at least one inner storage space (41i) each extend in a circular arc in the coupling cross-sectional plane perpendicular to the rotation axis AX, wherein the radius RRi of the (particularly inwardly facing inner) ramp floor section (46i) is 1.0 - 3.0 times, optionally 1.5 - 2.5 times greater than the radius RLi of the (particularly inwardly facing inner) bearing pocket floor section (44i).

9. Claw coupling according to one of the preceding claims, characterized in that at least one bearing pocket bottom (42) is viewed in the coupling cross-sectional plane perpendicular to the rotation axis AX,is designed as a trough in which the pressure body mounted therein is fixed in place when the coupling is unloaded.

10. Claw coupling according to one of the preceding claims, characterized in that at least one bearing pocket base (42), comprising a bearing pocket base section (44) and a ramp base section (46), extends in a curved manner when viewed in the coupling cross-sectional plane perpendicular to the rotation axis AX, and its extension curve, with respect to a distance from the rotation axis AX, has a vertex PS with a maximum distance Amax from the rotation axis AX, wherein the vertex PS lies in the bearing pocket base section (44). 11.Claw coupling according to one of the preceding claims, characterized in that, viewed in the coupling cross-sectional plane perpendicular to the rotation axis AX, a segment arc center point of a circular arc-shaped bearing pocket base section (44) of at least one bearing pocket base (42) lies on a radial axis through the rotation axis AX, and a segment arc center point of a circular arc-shaped ramp base section (46) of the same bearing pocket base (42) lies on a parallel axis offset orthogonally to the radial axis by a value X. 12.Claw coupling according to one of the preceding claims, characterized in that, in adjacent ring elements (12, 32; 32, 22), opposite ramp base sections (46) of bearing pockets (40) are designed as trailing ramp base sections (46b) with respect to the torque direction RM on one ring element (12; 32) and as leading ramp base sections (46a) on the adjacent ring element (32; 22).

13. Claw coupling according to one of the preceding claims, characterized in that, in the ring element (22; 12) connected or connectable to the drive means (2), ramp base sections (46) are designed as trailing ramp base sections (46b) with respect to the torque direction RM, and optionally. Opposite ramp base sections (46) of the adjacent ring element (32) are designed as leading ramp base sections (46a).

14. Claw coupling according to one of the preceding claims, characterized in that, viewed in the coupling cross-sectional plane perpendicular to the rotation axis AX, opposite ramp base sections (46) forming a common bearing space (41i; 41a) have the same length LRBA.

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