Patent Application
20150354641
The invention relates to a unidirectional torque coupling and a method for its operation. In particular, the invention relates to such a coupling with improved characteristics.
Unidirectional torque couplings serve for the transmission of torques in only one rotation direction, whereas they do transmit no or only significantly less torques in the other rotation direction, i.e. provide a so called “freewheel”. Such apparatuses are typically being used in drive technology, and they are known e.g. from non permanently driven two-wheeled vehicles. While in the drive phase, the drive force which is e.g. provided by means of muscles or a motor shall be transmitted by use of a coupling from the drive to the wheel, the wheel shall be able to rotate freely in phases without (or without sufficient) drive, and be decoupled from the still standing or only slower rotating drive (“coasting”).
In particular in the two wheel vehicle technology, such apparatuses are often simplifying called “freewheel”. In bicycles, they are typically mounted in the rear wheel hub. They allow to transmit the drive forces which are provided from the foot pedal over the chain onto the hub, as long as the angular velocity of the rear sprocket is equal to the angular velocity of the hub (and therefore, of the rear wheel). This equality is achieved in that in drive direction, a mechanical, form-closed and/or frictional coupling is provided between rear sprocket and hub. If, on the other hand, the angular velocity of the rear sprocket is slower than the angular velocity of the hub, the hub can rotate freely without being braked by the sprocket or the further drive train components which are connected with it, respectively.
For the transmission of the torque which is present at the rear sprocket onto the hub, spur-cut freewheel disks are being used. These have a saw tooth profile and are pressed against each other by means of spring or magnetic force. One of the freewheel disks is connected to the drive (rear sprocket), the other is connected to the output (hub). In drive direction, both freewheel disks interlock, such that the torque can be transmitted from the one to the other disk, and thus, from the drive to the output. Contrary to the drive direction, one of the both freewheel disks which is axially moveable is pressed away by the saw tooth profile from the other free wheel disk such that it slips, and no torque can be transmitted. Often, this slipping is associated with an acoustically well perceptible clicking.
The axially moveable freewheel disk is often equipped with a spline profile at its circumferential external surface. It gears form-locking with an accordingly designed toothing of the inside of the hub body. A tilting and thus cocking of the moveable freewheel disk must be avoided, just as the introduction of particles onto the spline profile, since this could otherwise result in a jamming of the free wheel disk. Thus, the repeated axial movement produces abrasion in the spline profile which on one hand continuously increases the clearance, and which can contribute to a contamination caused failure on the other. Further, the safe operation is influenced also by an ingress of dirt from the outside, as well as by the temperature variable viscosity of the imperatively necessary lubricant.
The contact force of both tooth lock disks is exclusively provided by the above mentioned springs and/or by magnetic force. If it is too high, this results in an unnecessary high friction and thus in an increased abrasion of the slipping freewheel, together with an often unpleasantly loud noise emission. If it is too weak, the result can be an undesired slipping of the toothing in drive direction. Because of the continuous aging of the freewheel, it can absolutely suddenly slip in drive direction and be rendered useless after only a few years of normal operation. Therein, injuries of the driver due to such a defect are not unlikely. In order to minimize the danger of such a defect, the saw tooth profile is manufactured with a slight undercut which is however complicated to produce, so that the toothings pull themselves against each other when the coupling is in the drive phase.
The object of the invention is to avoid the aforementioned disadvantages known from the art.
Thus, the invention shall provide a unidirectional torque coupling which does not have the disadvantages which come along with the usage of a spline profile which is arranged at the circumferential external surface for the purpose of torque transmission of an axially moveable freewheel disk.
Also, the invention shall have an improved safety against slipping contrary to the drive direction, and wear or any wear induced functional impairment shall be reduced.
The objects are solved by a torque coupling according to the main claim. Advantageous embodiments are mentioned in the dependent claims, the description, as well as the figures.
The unidirectional torque coupling (in the following, also “coupling” in short) is in principle universally usable; however, is can be used in particular for vehicles with a non-permanent drive (bicycle, motorcycle), where drive and roll phases alternate. The coupling serves for transmitting a drive torque which is provided in a drive direction e.g. onto a wheel, wherein contrary to the drive direction, no torque (or only a small, e.g. gripping, torque which is not usable for drive purposes) is transmissible.
The coupling comprises a drive body providing the drive torque, having a rotation axis around which the body is rotatably supported.
It further comprises an output side body which is arranged coaxially to the rotation axis, and onto which the drive torque is transmissible. In other words, drive and output side body are located on the same rotation axis, and a torque which acts in drive direction shall be transmitted from the drive onto the output side body.
The coupling further comprises a pressure disk which is arranged coaxially to the rotation axis. It is movable in rotation axial direction, and has a first torque transmission surface on its face side being arranged for transmission of the drive torque.
The coupling comprises also a torque transmission device which is either arranged between pressure disk and output side body, or between pressure disk and drive body, and by means of which the drive torque can be transferred. It is clear that the torque transmission device must be dimensioned such that it can actually transfer the drive torque without being damaged.
Depending on the constructional variant, it couples two different components with each other. If it is designed as an element which connects the pressure disk with the output side body, it serves for transferring the torque which is transmitted (in the drive case) from the drive body to the first torque transmission surface of the pressure disk, and which is present thereon, to the output side body (first constructional variant). If it is designed as an element which connects the drive body with the pressure disk, it serves for transferring the torque which is (also in the drive case) present at the drive body onto the pressure disk, from whose first torque transmission surface it can be transmitted to the output side body (second constructional variant). “Transferring” thus always means the force flow within the torque transferring device, whereas “transmitting” always denotes a force flow which involves the first torque transmission surface (and thus, the pressure disk) and the body which interacts with it (i.e. the drive or the output side body, depending on the constructional variant, see below).
In order for the drive torque being actually transmissible, that component which is positioned in rotationally-axial direction with its face side opposite to the first torque transmission surface of the pressure disk (this can be, depending on the constructional variant, the drive or the output side body) has a second torque transmission surface. The latter is permanently in mechanical contact with the first torque transmission surface, such that the non-driven torque transmission surface can be gripped by the driven torque transmission surface by way of form-closing and/or frictional resistance, wherein however, only a gripping torque is transmissible which falls short of the drive torque. Only upon exceeding a minimal contact pressure, the drive torque can actually be transmitted. If the minimal contact pressure is not reached, the driven torque transmission surface grips the non driven one, but the drive torque can not be transmitted, the coupling “slips”.
According to the invention, the torque transmission device is characterized in that it comprises dimensionally stable (rigid) pressure transfer elements. On one hand, these rest against that side of the pressure disk which is opposite to the first torque transmission surface (“back side” of the pressure disk). On the other hand, these rest also against the component which is opposite to this (back-)side; this component is, depending on the constructional variant, the drive or the output side body. Thus, the pressure transferring devices abut against the pressure disk and the component which is positioned as described before. The pressure disk is mechanically connected with its back side by means of the pressure transferring devices with that component onto which it shall transfer the drive torque, or from which the drive torque shall be transferred onto the pressure disk, respectively. The transmission is possible just because their dimensional stability; a non rigid body such as in particular a spring would therefore not be suitable for this purpose.
According to the invention, the pressure transfer elements are loaded by compressive forces only upon a gripping of the non driven by the driven torque transmission surface which is effected by form locking of or frictional resistance between the torque transmission surfaces, and which is firstly only a minor, then a full gripping, pointing in drive direction (drive case), wherein these forces do result in no (or only insignificant) deformation of the pressure transfer elements. In other words, only in the drive phase, the pressure transfer elements are loaded with compressive forces, wherein the compressive forces result from the drive torque, the radial distance of the pressure transfer elements from the rotation axis, as well as the position and shape of the pressure transfer elements. According to the invention, the pressure transfer elements are positioned in a way that they (or their centers of gravities, respectively) are moving upon said compressive loads (at least also) in rotation coaxial direction contrary to the pressure disk (e.g. tilting), i.e. that they e.g. erect themselves, thus exerting an infeed motion onto the pressure disk which acts in direction of the second torque transmission surface.
Typically, a (viewed in axial direction) tangential and/or radial motion of the center of gravity is superimposed to this coaxial motion. This means that the center of gravity of a pressure transfer element is displaced by means of said erecting also away from the rotation axis to the outside (radially), and/or along an arc of circle which is coaxial with the rotation axis (tangentially), depending on the orientation of the longitudinal axis of the pressure transfer element.
Because of the erecting and feeding in, i.e. their motion contrary to the pressure disk, they press it in direction of the second torque transmission surface while providing a coaxially acting force. The erecting and feeding in is possible because the pressure transfer elements are substantially non deformable and rest against the other component which is in turn rotation coaxially fixed, so that they can not move in its direction or past it, respectively.
The coaxially acting force is of a magnitude so high that the above mentioned minimal contact pressure is reached or exceeded and the (full) drive torque is transmissible; the coupling “takes up”. On the other hand, upon a contrary to the drive direction acting drive of the non driven by the driven torque transmission surface (freewheel case), the pressure transfer elements—once again without any significant change in shape—are relieved, so that they move away from the pressure disk and the minimal contact pressure is not met, so that also, no more drive torque is transmissible, and the drive body substantially rotates free with respect to the output side body.
Thus, the construction according to the invention dispenses with a spline or comparable outside profile known from the art, because presently, transferring of the torque is effected by means of the torque transmission device, and in particular, by the pressure transfer elements which are comprised by it. These do only slightly erect upon engagement which results in only negligible friction and accordingly little wear in the torque transmission device. The actual force transmission of the drive torque is effected via the two torque transmission surfaces which provide a significantly larger area compared to latching pawls, so that here as well wear is minimized. The height of individual teeth which are preferably used for transmission can be smaller with respect to latching pawls because of this larger area which is available for transmission, resulting in a lower working stroke and thus, in a faster response of the coupling. An undercut is mandatory not any more, since the axial compressive force which can be provided by the pressure transfer elements can be so high that even torque transmission surfaces without undercuts and even without the teeth which are known from freewheels can be used for torque transmission.
According to one embodiment of the torque coupling, the pressure transfer elements are designed as push rods. Push rods are typically oblong components with two ends.
With respect to the above described first constructional variant, the push rods rest against the back side of the pressure disk with a drive side end, and against the output side body with an output side end.
With respect to the above described second constructional variant, the push rods rest against the drive with a drive side end, and against the back side of the pressure disk with an output side end.
Always in the drive state, and preferably in the drive as well as in the freewheel state, the push rods are inclined with their “pitch line” in an erecting angle contrary to the drive direction. This means that at least in the drives state, a certain inclination of the pitch lines is present which must not be present during the freewheel state, but which automatically sets itself during the transition from the freewheel to the drive state. This can e.g. be effected by means of springs or the same, as discussed in detail further below.
In other words with regard to the case of the first constructional variant, at least in the drive case, the push rods have in rotation axial direction, measured from the pressure disk, a smaller distance to the pressure disk on the drive side than on the output side. The pitch line can be regarded as an imaginary line along which the axis of the push rod would run if it would be indefinitely thin and have indefinitely small ends. For an axially symmetric designed push rod, the pitch line runs just through the longitudinal axis of the push rod. As a result, there exists a positive erecting angle between the longitudinal axis of the pitch line and the pressure disk as well as the output side body (first constructional variant), or the drive body (second constructional variant), respectively.
As a result of this inclination, this erecting angle of the push rods further increases upon compressive load due to the permanently present inclination (=erecting); thus, the push rods press the pressure disk in direction of the component which has the second torque transmission surface. In this manner, the contact pressure of both torque transmission surfaces increases more and more, until the minimal contact pressure, from which a transmission of the drive torque by means of the both torque transmission surfaces is possible, is reached or exceeded.
It is clear that the erecting angle and the geometry of the push rods are adapted to each other such that the resulting stroke is at least slightly larger than the teeth height of a possibly present spur gearing of the torque transmission surfaces. In the case of a frictional torque transmission, the stroke can be even smaller.
The push rods can also e.g. be designed as small plates which can also erect themselves, but which have larger areas at the ends than bar shaped push rods. Such small plates provide a “pitch plane” instead of a pitch line. It is clear that the small plates can have a rounded shape at one or both edges in order to provide the maximal mating surface in every position.
It is clear that the push rods must not have a linear and/or symmetric shape. They must only have a shape which can change between a more lying and a more erected position, wherein this shape has, viewed in rotation axial direction, a smaller dimension in the lying position than in the erected position. Thus, only spheres are not suitable for this embodiment, since they do not have a pitch line.
Particularly preferred, the push rods have a ball head at their drive side end and/or at their output side end. The ball head must not be symmetric with respect to the possibly present longitudinal axis of the respective push rod. The support area provided for the resting of the respective end has a suitable pocket (joint socket, ball socket) for housing this ball head.
One of the support areas is always arranged at the back side of the pressure disk; the other support area is situated with its face side at the component which is located opposite to this back side, i.e. either the output side body or the drive body.
In this way, the push rods are joined or at least joinable in a ball joint manner with the component which provides the first and/or second torque transmission surface. Depending on the design and support of the ball joint, it can carry not only compressive forces, but it also secures the push rod against lifting off from the joint socket which is present in the support area. Thus, one unit is formed which firmly connects the pressure disk with the component which is located opposite to its back side. A free rotation of the pressure disk relatively to the component which is attached to is not possible. In particular, these two bodies are only slightly rotatable against each other (e.g. a few degrees). The erecting which is effected by a relative rotation is stopped when both torque transmission surfaces rest against each other. The shorter the possible stroke, the smaller the relative remaining rotatability.
Instead of a ball joint, a cardan joint or a swivel joint (hinge) can be used as well.
Naturally, the stroke is also influenced by the above described erecting angle; a pressure transfer element with a most possible flat running pitch line will erect itself faster or, with the same rotation angle, further up than one with an already rather steep running pitch line. In the borderline case of an erecting angle of 90 degrees, no further erecting takes place; thus, this borderline case must therefore always be avoided.
A preferred erecting angle amounts to less than approx. 10 degrees in the freewheel case, and not more than approx. 30 degrees in the drive case. Particularly preferred is an erecting angle of less than approx. 5 degrees in the freewheel case, and of not more than approx. 10 degrees in the drive case. Most preferred is an erecting angle of less than approx. 3 degrees in the freewheel case, and of not more than approx. 6 degrees in the drive case.
According to a further embodiment, the output side body is designed being fixedly joinable with the hub body of e.g. a wheel hub, and/or the drive body is designed being fixedly joinable with the freewheel body of e.g. a wheel hub. In other words, the drive or the output side body are e.g. designed as a ring which can be screwed in, and which can be inserted in, and fixed to, the hub or freewheel body of a wheel hub, respectively. The advantage of this embodiment is that the torque coupling according to the invention can be fabricated separately and then be subsequently installed with no or only little reworking into a preferably commercially available wheel hub.
According to another embodiment, the output side body is designed as the hub body of a wheel hub, and/or the drive body is designed as the freewheel body of a wheel hub. In other words, the drive or output side body, respectively, is integral with the freewheel or hub body, respectively, of the wheel hub. This embodiment has the advantage of less weight and needs less individual parts.
Basically, all surface structures which are known in the art and which are suitable for frictional resistance and/or form-closed transmission of torque can be considered as the torque transmission surfaces. For example, at least one of the two torque transmission surfaces has a spur gearing (axial gearing), whereby an undercut is possible, but not necessary. A symmetric or asymmetric wave profile can be used for the torque transmission as well. Eventually, at least one of the torque transmission surfaces can be designed as frictional surface, so that a frictional coupling is formed which can, upon reaching the above mentioned minimal contact pressure, transmit the drive torque.
As already mentioned further above, it must be ensured according to the invention that at least in the drive state a permanent mechanical contact of the two torque transmission surfaces is present. This can be effected e.g. by means of gravity, in that the rotation axis is approximately vertically oriented, and in that the first torque transmission surface is being positioned above the second one, so that both torque transmission surfaces rest onto each other.
However, for ensuring, an approaching means for approaching of both torque transmission surfaces is preferably present. By means of one or several mechanical springs or by means of magnetic forces, the approaching means can exert little pressure onto the back side of the pressure disk which is however sufficiently high for the approaching; such solutions are well known in the art. One or preferably several springs can be arranged between the back side of the pressure disk and the component which is opposite to this back side, being compressively loaded; instead of the springs, accordingly polarized magnets can be used. It is also possible to use attracting magnets, provided that according mounting positions are used within or close to the torque transmission surfaces.
By use of an approaching means it is also possible to orient the pitch line of push rods flat, i.e. parallel to the rotation plane of the component which is arranged opposite to the pressure disk, in the freewheel case. Then, in the drive case, the approaching means makes sure that an erecting angle of more than 0 degrees is set, as long as the pressure disk which moves in rotation axial direction does grip the ends of the push rods that rest against the disk.
It is further possible that the ensuring is effected by means of centrifugal force, or by means of fluidic force. Fluidic forces are exerted by liquids which flow through channels in a suitable manner upon rotation, and which build up pressure which acts onto the pressure disk.
Subsequently, the method according convention for the operation of a unidirectional torque coupling is described. The torque coupling has a drive body such as e.g. the freewheel of a wheel hub, an output side body such as e.g. the hub body of a wheel hub, a pressure disk which is arranged rotation coaxially to both and which is movable in this direction, and a torque transmission device which is either arranged between pressure disk and output side body or between pressure disk and drive body and which respectively comprises rigid pressure transfer elements. In order to avoid repetition, reference is made to the above explanations regarding the torque coupling according to the invention.
The drive case in which the drive torque shall be transmitted is firstly characterized in a relative rotation between drive body and output side body in drive direction. Upon this rotation which points in drive direction of at least the drive body, eventually, a taking up of the coupling takes place, so that, from the moment of this taking up, the relative rotation becomes zero, but never negative. In other words, the angular velocity of the drive body is greater than the one of the output side body which also rotates in drive direction until the coupling has taken up and both angular velocities become equal due to the mechanical coupling.
According to the invention, said pressure transfer elements are loaded by compressive forces, so that their center of gravity moves contrary to the back side of the pressure disk, onto which they then exert pressure. In other words, due to the loading with compressive forces, the orientation and/or position of the pressure transfer elements, which rest against the back side of the pressure disk as well as against the component which is opposite to this back side, changes. The displacement of the center of gravity can be effected by a change in position or orientation, which will be discussed further below. Therein, typically, a radial and/or tangential displacement takes place as well; reference is made to the above explanations.
The motion contrary to the back side of the pressure disk results in an (at least also) rotation axial motion of the pressure disk in direction of the drive body or the output side body, respectively; the (according to the invention desired) rotation coaxial motion of the pressure disk is typically superimposed with a rotational motion of the same.
The motion eventually leads to a frictional and/or form-closed connection between a first torque transmission surface arranged at the pressure disk and a second torque transmission surface which is arranged at the drive body or at the output side body, respectively. By pressing the pressure disk with its first torque transmission surface against the second torque transmission surface which is, depending on the constructional variant, arranged either at the drive body, providing the drive torque, or at the output side body, serving for the “leading off” of the drive torque, the coupling is thus “engaged” and actuated.
As a consequence, the relative rotation becomes zero, the drive body drives the output side body via the pressure disk, and transmission of the drive torque from the drive body to the pressure disk, and from there, to the output side body, is the result. Therein, the pressure load onto the torque transmission devices is permanently kept up, such that these really ensure the permanent pressing of both torque transmission surfaces. In other words, the compressive load results in a change of position of the pressure transfer elements, eventually leading to a self-retention (cocking).
In contrary, the freewheeling case is characterized in a permanent relative rotation between drive body and output side body contrary to the drive direction. In other words, the difference between the angular velocity of the drive and output side body is non-zero and negative, i.e. points contrary to the drive direction. Rephrased, the drive body is stationary in relative terms, and only the output side body rotates contrary to the drive direction.
Said pressure transfer elements are pressure relieved in the freewheeling case, so that their center of gravity moves away from the back side of the pressure disk, such that they do not exert pressure onto the same (no more); if applicable, a radial and/or tangential displacement is also reversed. This in turn results in a rotation axial increase of the distance of the pressure disk from the drive body or the output side body, respectively, resulting in a release of a connection between the first and second torque transmission surface. The form-closed and/or frictional resistance connection is separated; at least so much that the drive torque can not be transmitted any more. A gripping torque can still be transmissible, as long as both torque transmission devices touch each other without significant pressure. Thus, contrary to the drive direction, no drive torque is transmitted from the drive body to the output side body, but drive and output side body substantially rotate free with respect to each other.
According to one embodiment, the motion of the centers of gravity of the pressure transfer elements is effected in that the pressure transfer elements have a longitudinal, i.e. at least non-spherical, shape with a “pitch line”. They can e.g. have the shape of oblong push rods, reference is made to the above explanations in this matter. Further, the push rods are, viewed in drive direction, fixed to the back of the pressure disk as well as to the component which is opposite to this back side. This means that the pressure transfer elements result in a cocking between drive body and output side body upon a relative rotation which points in drive direction, such that eventually, both bodies can not rotate against one another any more. Since the pressure transfer elements have an oblong shape and are supported in drive direction, they erect upon compressive loads and require more space in rotation axial direction. It is clear that the pressure transfer elements are preferably (pre-)inclined such that they further erect upon compressive loads. If their “pitch line” would run parallel to the back side of the pressure disk, they would still carry compressive loads, but they would not try to erect themselves. Thus, at least a little erecting angle must be present between their pitch line and the pressure disk at any time which further increases upon compressive loads. Alternatively, an approaching means must be provided which makes sure that said erecting angle is present at least in the drive case, here as well reference is made to the above explanations.
In the case of an (viewed in axial direction) only radially running pitch line, the center of gravity will be displaced axially and besides, radially as well. In the case of an only tangentially running pitch line, the center of gravity will be displaced axially and besides, tangentially as well. Apart from that, typically, a combination of these motions (radial and tangential component of the pitch line) takes place.
As shown, the invention solves the problems which are known from the art as mentioned at the beginning. A spline profile which is arranged at the circumferential external surface of the pressure disk can be omitted. Safety against slipping of the coupling contrary to the drive direction is improved, and wear or any wear induced functional impairment are reduced.
In the following, exemplary embodiments of the invention are described by aid of the figures.
In
A first torque transmission surface 4A is arranged on that side of the pressure disc 3 which points in direction of the drive body 1. A second torque transmission surface 4B is arranged at that end of the drive body 1 which is facing the pressure disk 3. Presently, both torque transmission surfaces 4A, 4B have a spur gearing.
For the sake of better visibility, the drive body 1 is shown apart from the pressure disk 3. In the operational state, the first torque transmission surface 4A and the second torque transmission surface 4B touch each other at any time at least slipping by frictional resistance (in the freewheel case) or catching by form-closing (in the drive state), respectively.
In
Opposite to the latter, the first torque transmission surface 4A with the pressure disk 3 is arranged. The pressure disk 3 is not fixed in rotation axial direction. In contrast, the drive body 1 is immobile in this direction, since it is fixed by means of not depicted bearings; the same is true for the output side body 2 which is presently designed as screw-in ring in order to provide the possibility of being fixed in the hub body 9B (not shown) which is also fixed in rotation coaxial direction.
Pressure transfer elements 6 are evenly distributed between the back side of the pressure disk 3 and that side of the output side body 2 which faces the pressure disk 3. They are presently designed as push rods 7. They are designed in shape of a spherical segment at their drive side end 7A and their output side end 7B. These ends 7A, 7B rest in pockets 8A, 8B (not visible in
The push rods 7 form, together with the pockets 8A, 8B, the torque transmission device 5. Since they are loaded upon rotation of the drive body 1 in drive direction A with compressive force, and since they are fixed in drive direction A, the drive torque is transferred from the back side of the pressure disk 3 via the pockets 8A, the pressure transfer elements 6 (push rods 7) and the pockets 8B onto the output side body 2, as long as the drive torque is transmitted by means of frictional resistance and/or form-closing via both torque transmission surfaces 4A, 4B. It is clear that the pressure transfer elements 6 must be designed rigid, since otherwise, the transmission of the typically high drive torque which is transferred through the pressure transfer elements 6 in form of compressive forces would not be possible.
In
Also well visible is the fact that each push rod 7 has an erecting angle α. Presently, the same is measured between the plane of the screw-in ring and the “pitch line” W. The pitch line W is the imaginary line to which the push rod could be reduced if having an indefinitely small thickness. Also other, not depicted, differently shaped bodies, with the exception of spheres, have such a pitch line. According to the depicted embodiment, viewed in axial direction, the pitch line runs tangentially.
When the push rods 7 are compressively loaded, i.e. pushed into the pockets 8A, 8B (the latter not shown), they will try to further erect themselves due to the upwards (in direction of the non depicted pressure disk) pointing pitch line W. Thus, their center of gravity M is moved in direction of the back side of the pressure disk 3. Due to the tangential orientation (see above), an erecting of the push rod 7 will presently result not only in an axial, but also in a tangential motion of its center of gravity M. Since the push rod 7 is a rigid structure, its drive side end 7A moves accordingly further in this, but in particular, in the axial direction, while the output side end 7B remains in its joint socket in which it rotates. As a result, the push rods have in rotation axial direction, measured from the output side bodies' 2 rotation plane which is perpendicular to the rotation axis (not drawn), at any time a smaller drive side distance to this plane than an output side distance. Synonymously, the push rods have in rotation axial direction, measured from the non depicted pressure disk, at any time a smaller drive side distance than an output side distance.
As well,
In
Since the pressure disk 3 does only insignificantly rotate relative to the output side body 2 upon erecting of the push rods 7, this rotation can be tolerated by the springs with no problems, without them being pulled or pushed out of the seats 10B.
Eventually,
| Number | Date | Country | Kind |
|---|---|---|---|
| 102014108087.4 | Jun 2014 | DE | national |
