Patent Application
20170328397
This application claims priority to EP App. No. 16169579.6 which was filed on May 13, 2016 and which is incorporated herein by reference.
The present application generally relates to threading indicating for a bolt, to a threading indicating system comprising a bolt and a nut, and to a method for assembling a bolted joint.
A core property for defining the strength and load bearing capacity of a bolted joint is the axial tensile force in the bolt and the corresponding axial tensile force in the nut. The axial tensile force in the bolted joint must be above a predetermined force such that a secure bolted joint is achieved. If the axial tensile force in the bolted joint is insufficient, the bolt runs a risk of becoming loose or damaged which may result in a failure of the bolted joint. Failure of a bolted joint may result in catastrophic damage to the structure secured by the bolted joint. If the object being secured is a person: damage, injury or death may result from a failed bolted joint.
A core property for a securely assembled bolted joint is the clamp force. The clamp force is the force the bolt and the nut of the bolted joint exert on a body arranged between the two. If the clamp force is not sufficient the frictional forces between the bolt/nut and the body may be too low to prevent the body from moving. Such movement may result in large shearing forces on the bolt which may result in that the bolt shears off. The clamp force may be derived from the axial tensile force in the bolted joint.
The axial tensile force in a bolted joint may be expressed as a function of an applied bolt torque. When a bolted joint comprising a nut and a bolt is assembled the nut is threaded onto the bolt until a snug fit is achieved in the bolted joint. Thereafter a torque is applied to the tool receiving portions of the nut and the bolt and the joint is torqued until the nut and the bolt are securely joined together in a bolted joint.
A plurality of methods for assembling a bolted joint exists. The previously discussed method for assembling a bolted joint is the so called torque control, wherein a torque is applied until it reaches a threshold value. However, using a torque control method may result in that the assembled bolted joint is not secure. When threading the bolt to a nut, interference, due to imperfect threads or particles between the threads of the bolt and the nut, may result in a large tool torque. If torque control is used for determining if the bolted joint is securely assembled the interference may result in that the tool falsely indicates that the bolted joint is securely assembled. If the bolted joint forms part of a seat belt assembly, forming a point for securing the seat belt to the chassis of a vehicle an incorrectly assembled bolted joint may cause serious injure in a crash event, due to the bolted joint failing.
Hence, there is still a desire to improve the state of the art to provide a secure bolted joint and a method for assembling a secure bolted joint which at least partly solves these problems.
It is an object to improve the current state of the art of threading indicating for a bolt, and to solve, or at least mitigate, some of the above problems. These and other objects are achieved by a bolt, a system and a method as defined in the accompanying claims.
According to a first aspect, a threading indicating bolt is provided, the bolt comprising: a geometrical central axis defining an axial direction; a shank and a head, the head defining a trailing end and the shank defining a leading end of the bolt, the shank comprising a threaded trailing portion having a thread pitch, and a threaded leading portion, the threaded leading portion having a thread start, wherein the threaded leading portion extends in the axial direction from the thread start to the threaded trailing portion for a length being three times the thread pitch of the threads of the trailing portion; and wherein a torque is needed to thread a matching nut onto said bolt; the threaded leading portion of the bolt comprising a mechanical threading indicating element adapted to increase the torque needed to thread a matching nut onto the bolt while said matching nut is in threaded engagement with the mechanical threading indicating element arranged on the threaded leading portion of the bolt; the increase of the torque being in comparison to a required run-down torque when the matching nut has been threaded onto the bolt past the threaded leading portion and onto the threaded trailing portion. The system is based on the realization that a more secure bolted joint may be made using a bolt comprising a mechanical threading indicating element, for indicating a point for measuring and angle from. The measured angle may then be used for determining if the bolted joint is securely assembled, by determining if the measured angle is within an angle range. The system thereby reduces the risk that the bolted joint is incorrectly assembled.
The bolt is provided with a head and a shank revolving around a geometrical central axis defining an axial direction of the bolt. When the bolt forms part of a bolted joint with a nut, the head exerts a force on a body arranged between the bolt head and the nut. The bolt may also be used with a threaded female member. The head is arranged with a tool engaging portion or interface, such that a tool may engage the tool engaging portion and exert a rotational and turning force adapted to turn the bolt around a central axis of said bolt. The tool may thus be said to exert a torque on the bolt thereby driving the bolt such that it threads into a female threaded member.
The shank has a cylindrical shape and at least a portion of the shank is threaded, thereby comprising a thread. The shank is defining a leading end of the bolt, e.g. the end of the bolt adapted to be inserted to a female threaded member. The head of the bolt is defining a trailing end of the bolt. The shank of the bolt comprises a trailing threaded portion and a leading threaded portion. The threads of the trailing threaded portion and the threads of the leading threaded portion have a respective thread pitch. The respective threads may have the same pitch or may have different pitches. The thread and the diameter of the shank of the bolt are arranged corresponding to a thread standard and a thread size. For instance, a bolt having an Isometric M10 size thread has clearly defined thread parameters such as nominal diameter, thread pitch and thread shape to name a few of said parameters. An Isometric M10 sized bolt is adapted to cooperate with a female threaded member having matching thread properties. Naturally, an M10 bolt is not able to threadingly cooperate with an M8 nut due to non-matching thread properties.
The threaded leading portion comprises a thread start, e.g. a starting point for threading a female threaded member, such as a bolt.
The thread start of the leading threaded portion may be arranged at the leading end of the bolt or it may be arranged at a distance from the leading end of the bolt. In other words, a part of the bolt may be arranged not comprising a thread, and the thread start may be arranged at a distance from the leading end.
The threaded leading portion has an axial length being three times the thread pitch of the threads of the trailing portion. A rule of thumb when dimensioning and designing bolted joints using bolt and a female threaded member, such as a nut, is that the first three turns of the threads of the bolt, from the thread start towards the head of the bolt, are not to be loaded or exerted to forces when the bolted joint is assembled. The threaded leading portion may be said to comprise “incomplete threads”. Hence the thread properties of the threaded leading portion may be altered slightly without affecting the security of a bolted joint comprising the bolt.
The torque needed to thread a matching nut onto the bolt, when the bolt and nut are unloaded, in other words not exerting a clamping force on a body arranged between the nut and bolt, may be referred to as a run-down torque, run-in torque, or run-on torque. The run-down torque may also be referred to as the torque needed to run a nut down the shank of a bolt, towards the head of the bolt. Hence a torque is needed to thread the matching nut to the bolt. The run-down torque does not include the torque needed for the final tightening of the bolted joint. Naturally, the torque is a variable that may vary depending on various parameters. However, in the ideal case when the nut is threaded onto a matching bolt, and the thread surfaces are well lubricated and free from particles and dirt, there is none to very small resistance resulting in that a very low and constant run-down torque is needed to thread the nut onto the bolt. When the nut has been threaded onto the bolt and the clamping force is starting to build up the run-down torque is increased as axial forces build up in the bolt and the nut.
The inventive bolt is provided with a mechanical threading indicating element. The mechanical threading indicating element is adapted to increase the run-down torque when a female threaded member such as a nut is being threaded onto the bolt and the nut is in threaded contact with the mechanical threading indicating element. By “mechanical” it is meant that the threading indicating element is comprised in the bolt, and may in other words be said to be a part of the bolt, made in the same material as the bolt. Hence, the mechanical threading indicating element may be formed when the bolt is being manufactured by cold forging. It may be manufactured when the threads of the bolt are being rolled. The mechanical threading indicating element may also be said to be formed from the same blank the bolt is cold forged from.
The mechanical threading indicating element may also be said to be a mechanical thread friction increasing means, adapted to increase the friction between the mechanical thread friction increasing means and a matching nut or female threaded member being threaded onto the bolt, thereby at least temporarily increasing the run-down torque. The mechanical threading indicating element is arranged on the threaded leading portion of the bolt such that the increase in run-down torque only occurs when the nut or female threaded member is in threaded contact with the threaded leading portion of the bolt. Hence, when the nut is threaded past the threaded leading portion onto the threaded trailing portion a decrease in run-down torque will occur. Such an arrangement is advantageous in that the mechanical threading indicating element is not engaged when the bolt has been tightened. Both the run-down torque increase and decrease may be detected.
The increase in run-down torque may be detected by a torque sensor, or by measuring the torque applied by the tool driving the bolt or nut. If the increase is above a predetermined threshold value the increase may be used as a starting point for counting or measuring an angle of rotation, or rotational angle. Such an angle may be measured in degrees and may be larger than 360°. In order to determine if the increased run-down torque is above a predetermined threshold the increased run-down torque may be compared to the run-down torque needed for threading the nut onto the bolt, when the nut is determined to have been threaded past the threaded leading portion. In such a case both an increase and a decrease in run-down torque may be used for counting or measuring an angle.
According to at least one exemplary embodiment, the mechanical threading indicating element is a change of at least one thread property of at least a portion of one thread turn of the threads of the leading portion of the bolt. The mechanical threading indicating element is arranged such that it results in a clear and detectable run-down torque increase, and at the same time does not result in an unwontedly large run-down torque increase such that the threads of the bolt or nut are plastically and permanently deformed.
According to at least one exemplary embodiment, the mechanical threading indicating element is a partial deformation of at least a portion of at least one thread turn of the thread of said leading portion. A deformation may, for instance, be a deformation to a thread crest, a deformation making the distance between two adjacent thread crest smaller than the corresponding distance according to the thread standard. The partial deformation increases the interference between a thread on the nut and partial deformation of the thread resulting in an increased frictional force. Thus, an increased run-down torque is needed to thread the bolt to a nut and said increased run-down torque is detectable and indicate a starting point for counting or measuring and angle.
According to at least one exemplary embodiment, the change of at least one thread property is at least one of the following thread properties: a thread angle, a pitch, a lead, a major diameter, a minor diameter, a top radius, a bottom radius or a thread depth. The change in thread property may be a change to a single thread property, or it may be a combination of changes to a plurality of thread properties. As an example changing one thread property may indirectly change an additional thread property. The combination achieved when changing more than one thread property allows for customization of the run-down torque increased depending on the application of the bolt.
According to at least one exemplary embodiment the mechanical threading indicating element is arranged on at least a portion of the third thread turn of the bolt counting from said thread start of said threaded leading portion. When the mechanical threading indicating element is arranged on at least a portion of the third thread turn of the bolt the mechanical threading indicating element is not in contact when the bolt is used in a bolted joint. This is due to the rule of thumb that the first three thread turns of a bolt comprise “incomplete threads” not arranged to support load.
Advantageously the run-down torque increase due to the mechanical threading indicating element is a factor times a normal, nominal, run-down torque needed to thread a standard nut to a matching bolt. Such a mechanical threading indicating element is advantageous in that a system using the bolt for indicating a starting point for counting or measuring an angle from, may be setup by only inputting the factor value. The factor may be a value or a range of values. The torquing tool may then only need to detect when the run-down torque is above the inputted range value for determining the starting point for counting or measuring the angle. Such a system reduces the risk for errors linked to when an operator needs to input a plurality of variables when setting up the torque tool.
According to at least one exemplary embodiment, the mechanical threading indicating element comprises an altered thread pitch of at least a portion of the thread of the leading portion. Altering the thread pitch of at least a portion of the thread of the leading portion will result in a slight interference when a nut is threaded onto the leading portion. The slightly larger interference will result in lager frictional forces and an increased run-down torque is needed to thread the nut past the threaded leading portion. A change in thread pitch of at least a portion of the threaded leading portion may be done when the threads are rolled thus not needing any additional manufacturing steps as compared to a standard bolt. Once the nut is threaded past the threaded leading portion, the run-down torque will decrease and be essentially equal to the run-down torque needed for threading a standard nut to a matching standard bolt.
According to a second aspect, a threading indicating system is provided, the system comprising a threaded bolt according to the first aspect, and a matching threaded nut, the system characterized in that: a first torque is required when the nut is threading onto the threaded trailing portion; and the mechanical threading indicating element is a torque increasing element; and wherein a second torque is required when the nut is threading onto the threaded leading portion bolt and the nut is in threaded contact with the torque increasing element; and
wherein the second torque is larger than the first torque. The system comprises a bolt comprising a mechanical threading indicating element in the form of a torque increasing element. When the nut is being threaded onto the trailing threaded portion of the bolt a first torque is required. A second torque is required when the nut is threaded onto the bolt and is determined to be in threaded contact with the torque increasing element. Hence, the increase in torque when the nut is coming into contact with the torque increasing element may be detected. Additionally the decrease in torque when the nut is coming out of contact with the torque increasing element may be detected. The second torque due to the torque increasing element is larger than the first torque.
According to at least one embodiment, the run-down torque is decreased when said nut is threaded past said leading portion, and is determined not to be in threaded contact with said threads of said leading portion of said bolt. When the run-down torque decreases when the nut is threaded past the leading portion, the decrease in run-down torque may be detected and a starting point for counting or measuring an angle from may be determined.
According to a third aspect, there is provided a method for assembling a bolted joint, the bolted joint comprising a bolt according to the first aspect and a matching nut. The method comprises the steps of: detecting a change in run-down torque when threading said bolt to said nut, said change in run-down torque being above a predetermined threshold value and due to said mechanical threading indicating element, determining, based on the step of detecting said change in run-down torque, a starting point for measuring an angle from; and assembling said bolted joint by applying a torque and performing one of the method steps A and B: A. torquing said nut to said bolt until said measured angle is within an angle range; and B. torquing said nut to said bolt until said applied torque is above a predetermined torque threshold value and said measured angle is within an angle range; wherein said angle being within said angle range is indicative that said bolted joint is securely assembled. The method for assembling a bolt comprising a mechanical threading indicating element and a matching nut comprises the step of detecting a change in run-down torque when the nut is threaded onto the bolt and the change in run-down torque is due to the nut coming in threaded contact with the mechanical threading indicating element. The change in run-down torque may be an increase or a decrease. Further the change in run-down torque may be an increase followed by a subsequent decrease. The detected change in run-down torque may be compared to a threshold value and if the run-down torque is above the threshold value a starting point for counting or measuring an angle may be determined. Hence, the step of determining the starting point is based on the comparison of the change in run-down torque to the predetermined threshold value. After determining the starting point the bolted joint may be assembled by further applying a torque preferably by using a torque tool such as an impact wrench. In addition to assembling the bolted joint by a torque tool, one of the following steps is additionally performed: torquing the bolted joint until the counted or measured angle is within an angle range; or torquing the bolted joint until the applied torque is above a threshold value, or within a torque threshold range, and the counted or measured angle is within an angle range and the angle being within said angle range is indicative that the bolted joint is securely assembled. Hence, the bolted joint may be assembled by torquing the bolt and joint until the angle is within an angle range. The angle range is then indicative of both the position and indirectly the axial forces of the bolt and nut, and thus also the torque of the bolted joint. For example if the angle range is determined to be 7.5-8 revolutions or 2700°-2880°, the bolt and nut may be threaded until the counted or measured angle is within the 2700°-2880°. Once within the range the bolted joint may be concluded to be securely assembled.
Alternatively the bolt and nut may be torqued until a predetermined tool torque is achieved or the tool torque is within a torque range. The counted or measured angle may thereafter be compared to a predetermined angle range or angle value and if the measured angle is within the angle range or above the angle range, it may be determined that the bolted joint is securely assembled.
According to at least one embodiment of the third aspect, the method further comprises the steps of: comparing said measured angle to said predetermined angle range, and based on said comparison and if said measured angle is within said angle range: determining that said bolted joint is securely assembled. Advantageously the measured or counted angle may be used for checking/controlling that the bolted joint is securely assembled.
According to at least one exemplary embodiment of the third aspect the method further comprises the steps of: if said measured angle is determined to not be within said predetermined angle range: determining that said bolted joint is not securely assembled; and indicating to an operator that the bolted joint is not securely assembled. Advantageously if the measured or counted angle is determined to not be within the angle range or above an angle value the bolted joint may be determined to not be securely assembled and an indication may be done to the operator of the tool. Such an indication may be done using sound, or by displaying an indication on a display or using indication lights. The indication may also be done by controlling the tool itself by controlling the torque motor of the tool. For instance the tool may rapidly switch from threading the bolt onto the nut to unthreading the bolt from the nut. Indicating to the operator of the tool that the bolted joint is not securely assembled increases the manufacturing security.
According to at least one exemplary embodiment of the third aspect, the step of detecting a change in run-down torque comprises detecting an increase in run-down torque resulting from the nut threadingly engaging the mechanical threading indicating element of the bolt, or a decrease in run-down torque resulting from the nut threadingly disengaging the mechanical threading indicating element of the bolt, when the nut is threading onto the bolt. Advantageously the change in run-down torque may be an increase or a decrease both being detectable using the present system. Hence the starting point for counting or measuring and angle may be determined based on detecting the increase or decrease in run-down torque or a combination of the increase and decrease in run-down torque.
Generally, all terms used in the claims are to be interpreted according to their ordinary meaning in the technical field, unless explicitly defined otherwise herein. All references to “a/an/the [element, device, component, means, step, etc.]” are to be interpreted openly as referring to at least one instance of said element, device, component, means, step, etc., unless explicitly stated otherwise.
The above objects, as well as additional objects, features and advantages of the present inventive concept, will be more fully appreciated by reference to the following illustrative and non-limiting detailed description of preferred embodiments of the present inventive concept, when taken in conjunction with the accompanying drawings, wherein:
All the figures are highly schematic, not necessarily to scale, and they show parts which are appropriate for elucidating the invention as set forth in the appended claims, other parts being omitted or merely suggested.
Embodiments of the bolt and system will be described in more detail in the following with reference to the accompanying drawings.
The angle α denotes the angle of rotation between the nut and the bolt. Hence one full revolution between the nut and the bolt is 360 ° or 2π. Naturally in order to assemble a nut and bolt joint, a plurality of full rotations is required. Hence the angle is larger than 360°. For example, if seven and a half rotations (7.5) are needed to assemble the bolted joint the resulting angle is 2700°.
In a point P1, the bolt enters the nut. From point P1 to a point P2, no very low frictional forces are present in the threading contact between the nut and the bolt. Hence, between the points P1 and P2, the torque is constant and approximately 0 Nm. At a point P2, the nut and the bolt have been threaded until contact, direct or indirect, is achieved between the nut, the bolt and the body being clamped between the nut and bolt. After point P2, the resistance from frictional forces in the threads of the nut and the bolt will start to build up and increase as the nut and bolt are rotated. Between point P2 and a point P3, an exponential and non-linear torque increase occurs. After point P3 and before a point P4 a linear torque increase occurs. During this linear torque increase the rotational angle of the nut and bolt will result in increased axial forces in the nut and bolt. The axial forces in turn results in normal forces which in turn results in frictional forces in the threads. Hence increased axial forces result in that an increased torque is needed to be applied in order to tighten the bolted joint. Between points P3 and P4 elastic, and no plastic, deformation is present in the nut, bolt and body being clamped.
At a point P4, the nut and the bolt start to experience plastic deformation due to the axial forces in the two. Hence, point P4 may be referred to as a yield point. Plastic deformation normally occurs in the weaker one of the nut and bolt, preferably designed and dimensioned to be the bolt.
After point P4 where plastic deformation has been initiated, the torque will start to level out. At a point P5, the torque is constant and will start to decrease slightly.
In a point P1′, the bolt enters the nut. Between entering the nut in point P1′ and a point P2′, where the patch comes into contact with the threads of the nut, the torque is constant and approximately 0 Nm. When the patch comes into contact with the threads of the nut the frictional forces, due to the smearing of the patch in the threads of the nut and the bolt, increase approximately linearly. The point P2′, indicates that the patch of the bolt has entered the nut. When the patch is smeared between the threads, the patch is moved from its original placement on the bolt and spread out on a larger portion of the bolt. The patch will thus increase the torque needed to thread the bolt to the nut or “steal torque” from the tool applying the torque to the bolted joint.
In a point P3′ the torque decreases slightly before starting to increase once more in point P4′. After point P4′ and before point P5′ a linear torque increase occurs due to increased axial forces and friction between the thread of the nut and the bolt. At point P5′, the yield point, the bolt will start to plastically deform and the torque start to flatten out. Between point P5′ and a point P6′ only minor change in torque occurs.
After being constant between point P20 and a point P30 the torque is decreased due to the mechanical threading indicating element leaving the nut or coming out of contact with the nut. Since the mechanical threading indicating element is arranged on a small portion of the bolt, the decrease of torque is sudden, or almost instant, and occurs during a small angular range. When the nut is threaded completely past the mechanical threading indicating element the torque needed to thread the bolt onto the nut will be low or approximately 0 Nm. Hence, contrary to using a thread locking patch the mechanical threading indicating element will not “steal torque” from the tool applying the torque to the bolted joint when the mechanical threading indicating element is threaded past the nut. Further, the mechanical threading indicating element is fixed in position on the bolt and does not move or smear like a patch.
In a point P40 the linear torque has decreased and is approximately 0 Nm. From point P40 the torque will start to increase. However, and depending on the design of the bolt, after the decrease in torque from point P30 to point P40 the torque may remain constant and approximately 0 Nm for an angle until the bolt and nut fit snuggly. Between the point P40 and a point P60 the bolt will function as a normal bolt. This may be seen when comparing the torque curve shape between points P3 to P6 of
The length of the phase P20 to P30 of the curve in
Ideally point P20, the first torque increase, is used for counting or measuring an angle from, however, additionally or alternatively point P30 may be used for the counting or measuring the angle.
The shank 3 comprises a threaded trailing portion 6 and a threaded leading portion 7. The threaded trailing portion 6 is arranged between the threaded leading portion 7 and the head 2 of the bolt 1 and comprises a thread pitch 1P. The threaded leading portion 7 is arranged adjacent the leading end 5 of the bolt 1. The threaded leading portion 7 comprises a thread start 11 defining a starting point 11 of the thread of the threaded leading portion 7, being arranged adjacent the leading end 5 of the bolt 1. The threaded trailing portion 6 of may be threaded all the way up to the head 3 of the bolt 1 or there may be a non-threaded portion 60 between the threaded trailing portion 6 and the head 3 of the bolt 1. The threaded leading portion 7 comprises a mechanical threading indicating element 10 in the form of an altered thread pitch compared to the thread pitch 1P of the threaded trailing portion 6. The altered thread pitch is adapted to alter the fit between the bolt 1 and a nut being threaded onto the threaded leading portion 7. The result is that the fit will be slightly off with increased interference between the threads of the bolt 1 and a nut. This will result in larger frictional forces that need to be overcome by the applied tool torque in order for the nut to be threaded onto the bolt 1. Hence when the nut is threaded onto the bolt the increased torque is detectable and a point for counting or measuring an angle from may be determined. Only minor change to the thread pitch may be needed in order to increase the frictional forces between the threads.
The threaded leading portion 7 is arranged such that the axial length of the threaded leading portion 7 is three times 3P the thread pitch of the threaded trailing portion 6. A rule of thumb when dimensioning bolted joints is that the first three thread turns of a bolt are not to be loaded when the bolted joint is assembled. Hence, when arranging the mechanical threading indicating element 10, in the form of an altered thread pitch 10, the threading indicating application does not void or alter the structural integrity of the bolt 1.
Arranged adjacent the threaded leading portion 7 on the leading end 5 of the bolt 1 is an extended unthreaded end 8. The extended unthreaded end 8 may help guide the bolt 1 into a threaded hole or nut when assembling a bolted joint comprising said bolt 1 and a matching nut or threaded hole.
In a first step S1, a change in run-down torque when threading a bolt 1, 1′, 1″ comprising the mechanical threading indicating element 10, 10′, 10″ is detected. The change in run-down torque is due to the threads of the nut being in threaded contact with the mechanical threading indicating element 10, 10′, 10″ of the bolt 1, 1′, 1″. When a nut is being threaded onto a bolt 1, 1′, 1″ a run-down torque is needed in order to overcome the frictional forces between the threads of the nut and the bolt 1, 1′, 1″. Normally when the threads are clean and lubricated the run-down torque is low or approximately 0 Nm. However, when due to the mechanical threading indicating element 10, 10′, 10″ the run-down torque will change when the mechanical threading indicating element 10, 10′, 10″ comes into contact, or comes out of contact, with the threads of a nut being threaded onto the bolt 1, 1′, 1″. A change in run-down torque being above a predetermined torque threshold is indicative of that the mechanical threading indicating element 10, 10′, 10″ is in contact with the threads of the nut.
In a step S2, and based on the detected run-down torque change a starting point for counting or measuring an angle α from is determined. A device for measuring the rotation of the tool driving the bolt may be used for continuously measuring the rotation angle of the tool. In addition the tool may measure the torque applied to the bolt. When a torque increase above a threshold is detected, the angle from which to count or measure may be determined in an almost instantaneous manner.
In a step S3, the bolted joint is assembled by applying a torque to the bolted joint. The step of assembling the bolted joint is performed by either performing a method step A or B, referred to as step S41 or S42 in
The invention has mainly been described above with reference to a few embodiments. However, as is readily appreciated by a person skilled in the art, other embodiments than the ones disclosed above are equally possible within the scope of the invention, as defined by the appended patent claims.
| Number | Date | Country | Kind |
|---|---|---|---|
| 16169579.6 | May 2016 | EP | regional |
