Abstract:
A device for truing and regulating the tension of spoked running wheels includes a support device for stationarily clamping the hub of the running wheel, a measuring device for determining the lateral and top eccentricity of the rim, a device for fixing a motor-driven nipple wrench to the spoke nipple, a device for manually adjusting spoke tension. The hub of the running wheel is clamped for measuring symmetrical to the axial radial plane; both lateral and top eccentricity and rim anomalies on the same radial rim segment can be read out directly and electronically with or without the tires fitted. A wrench can be installed in existing devices; and is suitable for manual and motor-driven applications.

Description:
FIELD OF THE INVENTION 
       [0001]    Device for truing and regulating the tension of spoked running wheels 
         [0002]    a) with a support device for rigidly clamping the running wheel axle, 
         [0003]    b) a measurement device for determining the axial and radial runout of the rim, 
         [0004]    c) a device for fixing the motor-driven nipple wrench to the spoke nipple, 
         [0005]    d) a device for manually adjusting the spoke tension, 
         [0006]    e) a CPU control unit with interactive display, 
       BACKGROUND OF THE INVENTION 
       [0007]    Devices that rigidly clamp the running wheel centered relative to its truly axial radial plane, are known and feature the following disadvantages together or individually:
       measurements on the same radial rim segment are possible, but adjustments to the running wheel centered to the running wheel radial axis are complicated,   there is no device for fixing the lateral and vertical tracing pin for the same rim segment in the running wheel radial direction,   high production expense,   large tolerances for centering the running wheel relative to its radial center plane.       
 
       SUMMARY OF THE INVENTION 
       [0012]    The support device presented here for application eliminates these disadvantages and is distinguished by the following characteristics: 
         [0013]    It clamps the running wheel centered to its radial center plane, simultaneously indicates the axial deviations of both rim sides relative to this radial center plane, and measures the radial runout axially on the same radial rim segment, in order to allow centering without centering calibration, without time-consuming turning of the running wheel during the centering process, and without laborious allocation of measurement values obtained on different radial rim segments for axial and radial runout of the rim. 
         [0014]    The running wheel is clamped by a novel pulling-tilting movement of the two supports simultaneously centered relative to the running wheel axis center plane, wherein the measurement device guided by the running wheel supports is simultaneously adjusted relative to a radial rim segment for each rim size. 
         [0015]    The somewhat table-sized, portable construction is possible in a surface-stressed construction, which can be realized, above all, through standard industrial profiles instead of precision molded components, wherein the symmetric integration of both support sides into the overall construction also minimizes the tolerances. The support device is also designed for the fully automatic, motor-controlled centering process that can be realized in a modular way. 
         [0016]    b) Measurement devices for determining the axial and radial runout of the running wheel rim for a rigidly clamped running wheel hub are known that have the following disadvantages together or individually:
       complicated fixing of the measurement tracing pin for axial and radial runout on the running wheel rim   complicated adjustment of the measurement tracing pin for axial and radial runout for each rim size   no simultaneous axis-centered measurement of radial or axial runout of the running wheel on the same radial rim segment   high technical expense for the mechanical measurement value display   increase in the measurement error through additional mechanisms between the measurement tracing pin and measurement display   lack of measurement scales   lack of measurement scales [sic]   no true-distance display of the axial and radial deviations of the running wheel rim   no simultaneous read-out of the measurement values   no distinction between rim defects and axial/radial runout possible.       
 
         [0027]    The measurement device presented here for application eliminates these disadvantages and is distinguished by the following features: 
         [0028]    It measures different running wheel sizes, each without time-consuming, error-generating adjustment work, displays the measurement values at the ratio L 1 [sic], provides a measurement scale, is designed for running wheels with and without mounted tires, and has a simple economical construction as well as low weight. In addition, it is equipped with a simultaneously readable scale field for axial and radial runout and a quick-positioning device for the measurement tracing pin, as well as in a modular way for electronic measurement value detection and evaluation (centering computer) up to motor-controlled, no-contact measurements. 
         [0029]    The radial measurement tracing pins that can move parallel to the running wheel radial plane allow the simple fixing and detaching of the measurement tracing pins to and from the relevant running wheel rim in interaction with a quick-tensioning device for the measurement tracing pins. The measurement gap shown symmetric to the running wheel radial center plane and formed only by measurement plates, perpendicular to the appropriate measurement direction, fixed directly to the measurement tracing pins shows, relative to the radial center plane on a magnifier-enlarged scale field with, e.g., a suitable mark spacing of 0.1 mm and a suitable mark width of 0.01 mm, simultaneously both axial runouts of the running wheel rim and the radial runout at the ratio 1:1, wherein through the simultaneous display of both rim sides, a distinction between rim defects and rim runout is also possible. With a magnifier-enlarged scale mark width of, e.g., 0.01 mm, deviations of the running wheel rim from the ideal radial center plane as far as a region of, e.g., 0.01 mm, can be detected without a problem. Thus, the installation of additional precision measurement instruments is unnecessary. 
         [0030]    Furthermore, by detaching the fixing device of the measurement body that can move parallel to the running wheel radial center plane on the measurement body support, the two measurement tracing pins for axial runout can display, with the perpendicular measurement plate edges of the vertical tracing pins, the radial deviations relative to the scale field attached rigidly to the measurement body support through vertical tracing pins installed on these measurement tracing pins and contacting the rim top side or bottom side selectively in a spring-mounted way via the moving measurement body. In addition, for side-grooved running wheel rims, the measurement tracing pins for axial runout can be fitted in the grooves. Likewise, for a detached fixing device of the measurement body, radial deviations of the rim can be detected and displayed simultaneously by means of the lateral tracing pins. 
         [0031]    In addition, the radial runout can be displayed with the edge of another measurement plate, which is connected rigidly to a roller spring-mounted on the rim bottom side moving in the running wheel axis and which moves vertically in the measurement gap over the scale field. This measurement form can be selected, e.g., for fast use of the centering device, when the high measurement certainty given by the simultaneous, continuously equal spacing support of the measurement tracing pins for axial and radial runout is not the primary concern, as is possible with the exclusively lateral tracing pin-guided measurement method described here. 
         [0032]    In addition to this basic setup, according to the modular principle, electronic distance sensors can now also be attached to the measurement tracing pins, which can be connected, in turn, to an interactive display with a microcontroller installed, e.g., on the measurement body support, which can also be connected to an opto-electronic device at the upper end of the measurement body for counting the spokes for a hand-driven or motor-driven running wheel, which allows a unique electronic assignment of the measurement values to the measurement locations. The manually operated centering computer installed in this way has the advantage of delivering simultaneously axially centered and axis-radial measurement values and also having a technically simple, space-saving, mobile, and lightweight construction. 
         [0033]    Finally, also according to the modular principle, an additional expansion to a fully automatically operating centering device can now take place for a rigidly clamped running wheel. First, the measurement body is replaced by a measurement body of the same size. This replacement body works with no-contact, opto-electronically flat beam emitters or flat beam sensors, which are equally suitable for running wheels with and without tires and which are arranged symmetric to the running wheel radial center plane, and can be moved automatically into the optimum measurement position driven by motors on guides attached to the measurement body support. Second, a motor-driven drive roller fixed to the centering device drives the clamped running wheel via the rim bottom side or tire bottom side. Third, the motor-driven nipple wrenches on the centering body are installed in the set-up devices of the two running wheel supports and all three components also connect to the microcontroller. Manual activities during the centering process are limited to pressing on the running wheel rim. 
         [0034]    In another construction of the invention, for no-contact measurements of the axial and radial deviations of the running wheel rim, an opto-electronically flat beam device composed of two flat beam emitters arranged orthogonally at an angle of 45° symmetric to the running wheel radial plane is designed, so that the flat beam intersects the running wheel radial plane in a common line at a right angle to this plane; the flat beam sensors are arranged in parallel, symmetric to the running wheel radial center plane, so that the axial deviations of the running wheel rim located within the beam planes can be mapped at a ratio of 1:1. For unique assignment of the measured distance to radial or axial runout movements of the rim, first there is the difference between the measured left-side or right-side distance, and second the comparison with a third flat beam running orthogonal to the running wheel radial plane and penetrating the common intersection line of the other flat beam, so that the radial deviations can be uniquely calculated from the measured axial distance. The no-contact measurement with the flat beam described here has the advantage, relative to other no-contact measurement methods, first, e.g., being able to display precisely and continuously axial deviations of a total of 40 mm and more for the measurement of used running wheels, and second, being able to adapt the measurement device to the appropriate rim size or rim condition through parallel shifting along the running wheel radial plane in a simple way, as through motor control, and thus setting up the centering device for fully automatic measurement of any running wheel size with and without running-wheel tires. 
         [0035]    c) Previously known devices for fixing the motor-driven nipple wrench to the spoke nipple each feature one or more of the following disadvantages:
       complicated adjustment work for setting the working point for each rim size   complicated overall technical construction   imprecise rotation of the rotating wrench socket locking laterally onto the nipple   imprecise operation of the geared-motor control unit   slight motion of the spherical wrench socket   increased wear phenomena due to spherically moving and latching, non-positive fit wrench socket   additional measurement devices required for the spoke tensioning       
 
         [0043]    The previously known motor-driven nipple wrench devices for centering the running wheel are found in devices with and without a rigidly clamped running wheel axle. Disadvantages in both cases include very high technical expense together with complicated adjustment work in order to prepare the entire screwing mechanism for the actual screwing process and the appropriate rim size. In addition, the required fine adjustment for the exact-fitting placement of the wrench socket in the axial direction of the spoke nipple is achieved by means of additional, technically complicated sensor mechanisms. In addition, the final lateral locking of the clamping socket, which moves spherically in a small extent and which grips and turns the spoke nipple, generates a large amount of wear and also accuracy tolerances with respect to the rotational position of the spoke nipple, whereby the centering of the running wheel and also the exact measurement of the spoke tension by means of moving the clamping socket are not possible with higher accuracy. A main prior problem definitely consists in fixing the wrench socket to the spoke nipple, because here the nipple axes tilted differently relative to the running wheel radial plane achieve maximum adaptation to the appropriate “nipple relationships” for minimum technical expense and optimum work accuracy in interaction with different running wheel sizes, spoke numbers, and rim types, as well as changes to the nipple axis position during the tensioning. 
         [0044]    For reversible fixing of the motor-driven nipple wrench to the spoke nipple, at least one drive movement is directed towards and away from the running wheel radial plane. 
         [0045]    For exact, low-wear screwing, a slotted nipple wrench socket is used, which sits with small play on the spoke nipple in its axial direction and which encompasses as much as possible the four corners of this spoke nipple and which can be screwed in exact rotational angles controlled by a directly connected angle transmitter. Thus, the direct measurement of the axial tension of the spokes is also possible by means of the motor current or the motor voltage. 
         [0046]    The central element in fixing the wrench socket to the spoke nipple is formed by the sliding guide plane, which is made from close, parallel guides that are pushed onto each spoke, in this way matching their tilted position, finally forming a contact with their connection side parallel to the spoke axis, so that the socket axis of the wrench socket fixed to it coincides with the nipple axis, wherein advantageously the wrench socket is just above the spoke nipple, in order to be pushed onto this nipple in a final movement along the spoke axis. Because the socket and nipple edges must be aligned parallel to each other as much as possible and the maximum possible twisted position equals 45°, the rotating wrench socket is dropped against the nipple square, wherein an optimal matching of both movement speeds to each other together with a movement control by means of the motor currents or motor voltage and also an elastic device for the wrench socket allow the successful gripping of the spoke nipple from above. 
         [0047]    The movement for placing the wrench socket onto the spoke nipple can also be supported by means of a sensor device for the successful nipple contact of the wrench socket and also a rim contact sensor device, as described in the drawing section. The sliding guide device with attached wrench socket is first pushed onto the spokes until reaching the axis-parallel position and second is brought into the final screw position through spoke axis-parallel shifting, gripping the spoke nipple with or without a mounted geared-motor unit in various possible reversible movement sequences. 
         [0048]    For devices with externally rigidly attached motor gear units designed, possibly adjustable, for different rim sizes, the torque transfer to the wrench socket fixed to the sliding guide device takes place by means of a flexible shaft. The reversible movement sequences are constructed differently for a translating drive movement and for a rotating drive movement. 
         [0049]    For the translating drive movement, the slide-guided wrench socket device is first pushed onto the spoke in a straight line in a fixed, frontal direction relative to the running wheel radial plane, wherein the joint devices already mentioned above for the tilting axes relative to the running wheel radial plane align the slide-guided wrench socket device in a straight-line movement direction parallel to the spoke arrangement; here, by means of the device moving in a linear direction parallel to the running wheel radial plane, the deflections are guided laterally to the movement direction during the alignment of the sliding guide along the spoke due to the radial deviations from the axis center of the running wheel radial-parallel tilting axis moved by the sliding guide device. Lateral deflections are also produced during the subsequent lowering process of the slide-guided wrench socket device along the running wheel spoke, when the downwards movement is not directed axis-parallel to the spoke, but instead, e.g., perpendicular to the frontal-directed movement direction. This can be the case when both movement procedures, parallel fixing and lowering, are implemented not with two separate, but instead one single motor device. In this case, the straight-line forward movement directed frontally to the running wheel radial plane is converted into a spoke axis-parallel downwards-directed movement direction for parallel contact of the slide-guided wrench socket device on the running wheel spoke for placing the wrench socket on the spoke nipple along the spoke by means of suitable joint devices. 
         [0050]    For the reversible rotating drive movement, the spoke axis-parallel setting of the sliding-device-guided wrench socket and also the placement on the spoke nipple is realized in the most favorable case from a rotating movement. By means of a tilted, motor-driven radial joint, which is aligned parallel to the running wheel radial plane approximately at the height of the nipple and which is also guided with slide bearings in a linear direction in a plane orthogonal to the running wheel radial plane both parallel and perpendicular to the running wheel radial plane with elastic movement devices, a rod-like holding device is first moved orthogonal to the running wheel radial plane onto the spoke and finally aligned axis-parallel to this spoke. For sliding-device-guided shifting onto the spoke, the tilting movements already generated in the translating movement case and lateral displacements are absorbed this time by means of the tilting bearing and also the two elastic guided slide bearing devices of the radial axle. 
         [0051]    After contacting the spoke, the sliding-device-guided wrench socket is then pushed along the spoke axis onto the spoke nipple by continuing the rotating movement, wherein the radial axle is pushed backward by means of its corresponding linear joint and in this way exerts slight pressure on the running wheel spoke. By lifting the wrench socket from the spoke nipple by beginning the rearward rotational movement, this contact pressure guarantees a tilt-free detachment of the wrench socket in the nipple axis direction. In addition, by means of a fine-adjustment device, the working position of the radial joint can be set relative to the running wheel radial plane, e.g., for long-term operation with axial runout tolerances of ca. +/−8 mm according to requirements. The shifting of the radial joint parallel and perpendicular to the running wheel radial plane can be realized manually or be motor driven for the purpose of adapting to different running wheel sizes. 
         [0052]    d) Devices for manual adjustment of the spoke tension are known, which are limited, however, to merely manual tightening or loosening of the spoke nipple. However, because knowledge of the spoke tension is also required, not least of all, for operating centering computers and because torsion of the spoke must be avoided for each tightening of the nipple, the work-saving, space-saving, and cost-saving unification of all three processes, nipple tensioning, spoke tensioning, measuring and torsion control, into one device is advantageous. Even for measuring the spoke tension, known devices, such as 3-point measurements on the spoke wire, mechanical tension measurements, or acoustic measurements through the selection of the measurement point and/or the crossing of the spokes is necessarily inexact. In contrast, in the device presented here for filing, the axial tensile stress of the spoke is measured. 
         [0053]    The device is composed of a cylindrical base body with nipple wrench socket, spoke guide, and pressure sensors, a center rotating body and also a head unit with power supply, display, signal transmitter, and torsion display. The rotating movements of the wrench socket can also be driven by a motor, wherein the controlled drive unit is used on the spoke in a manually operated way for the motor-driven nipple screw device presented here for filing at another location. Embodiments of the invention are shown in the drawings and described in more detail below. 
     
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         [0054]      FIG. 1 , an oblique representation of the structural elements of the centering stand, 
           [0055]      FIG. 2 , a view of the symmetric tensioning/tilting mechanism of the centering stand, 
           [0056]      FIG. 3   a, b, c , a representation of the measurement body and its elements, 
           [0057]      FIG. 4   a, b, c, d, e , oblique representation, side view, and components of a construction of the nipple wrench moved with a translating motion and also a representation of the nipple wrench moved with a rotating motion, 
           [0058]      FIG. 5 , setup and components of the manual nipple wrench. 
       
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 
       [0059]      FIG. 1 . The sketch shows the outer trapezoidal support plates, which are arranged symmetric to each other and which are defined by the lines  1 ,  2 ,  3  and  3 ,  4 ,  5 , respectively. The lines  5  and  6  form, via the tube guides  7 , a base that is fixed vertically and can move in the rigid body  9  between the lines  8 . Here, the lines  1 ,  3 ,  5  represent sliding guides that move in the radial direction. Line  10  designates a rod device for lifting and lowering the base  5 ,  6  in the body  9 . Item  11  designates the holding devices, which can also move in the radial direction, for the running wheel hub. The lines  12 ,  13 ,  14 , and  15  designate the symmetric support plate, which is u-shaped in the upper half, with the sliding guides  16  for the measurement body  17 , which contacts the holding device  19  attached to the two outer supports  1 ,  2 ,  3  from the radial rotating joint  12  running over the entire width of the support construction outwards to its two upper points  18  symmetric to each other. The control unit with display  20  is attached to the bottom end of the holding support. The outer and inner support plates and also the base of the support construction can be designed with devices for installing the motor-driven nipple wrench. 
         [0060]      FIG. 2 . The frontal view in a representation without measurement body support  12 ,  13 ,  14 ,  15 , measurement body  17 , and display control unit  20  shows a construction with the high-precision tubes  1 ,  3 ,  5 ,  10 ,  19 ,  21 ,  22  and also the rectangular tubes  2 ,  4 ,  6 ,  8 . Item  7  designates the tube guides arranged symmetric to the running wheel axis center plane  23 , wherein the body  9  is constructed here by rectangular tubes  8  arranged one behind the other in a plane, simultaneously [verb apparently omitted] the articulated tubes  1 , the movement rod tube  10 , and also the two tubes  21  arranged symmetric to the axis  23  to contribute to the stability and dimensional accuracy of the entire construction, because, as can be seen from  FIG. 1 , here the tubes  1 ,  10 , and  21  and also the stick-slip tubes  19  form the basis for the dimensionally accurate assembly of the measurement support  12 ,  13 ,  14 ,  15 . Here, the holding device for the running wheel hub  11  is shown in more detail than in  FIG. 1  by the radial cardan joint  24 , which runs above the articulated tube  3  and which is used as a holding device  11  connected rigidly to a v-shaped plate for the running wheel axle. It can be seen that the stick-slip devices  19  must move on circular lines during the pulling/tilting movement. The measurement body support  12 ,  13 ,  14 , supported so that it can move in its radial joint  12  and forming a stick-slip contact at each of its ends with its two U-flanks in the axis radial parallel direction is previously oriented for an optimum average height of the stick-slip devices  19 , so that its higher measurement tracing pins can minimize the running-wheel radial directional deviations produced for a minimum to maximum running wheel hub width, wherein the resulting error on the radial rim segment lies within the tracing pin sensor cross sections, and thus a simultaneous, running wheel axis radially directed measurement of the axial and radial runout of the running wheel is possible. 
         [0061]      FIG. 3   a, b, c . The sketch shows the measurement body support  12 ,  13 ,  14 ,  15 , the display control unit  20  with the control fields  25  and display  26 . To be seen further is the sliding guide  16 , on which the measurement body  17  is fixed so that it can move by means of the sliding devices  50 . The spoke  27 , the rim sides  28 , and also the running wheel tire  29  are shown centered relative to the radial wheel axis center plane  23 . The tracing pins  31 , moving in the slide bearings  30 , provided with contact pressure devices  35  guide the display plates  32  rigidly with them, which in turn appear in the scale field  34  and feature a gap size dependent on the rim width centered relative to the running wheel radial plane  23 . The display plates  32  can also simultaneously display the radial runout of the rim in the scale field  34 , on the one hand, when the probe tip is guided in the lateral groove of a rim side  28  and simultaneously the sliding guide brakes  37  are released by means of the setting button  36 , so that the measurement body  17  is guided along with vertical deflections by means of the slide bearing  30 , so that these deflections can be displayed in the scale field above the lower edge of the display plates  32 . On the other hand, a sticking contact can be formed on the rim top or bottom side by means of the contact pressure devices  42  or  43  by means of the pivot support  40  that can be locked using precision boreholes  39  by means of a similarly rotating tracing pin  41 . The last two methods have the advantage that the measurement tracing pin is always carried along in a mutual way and therefore always measures at the same rim position. 
         [0062]    In principle, however, there is also the possibility of measuring the axial and radial runouts independently from each other, in that the measurement roller  44  moving by means of the slide guides  45  and spring mounted by means of pressure devices  46  on the running wheel  29  or the rim bottom side displays the radial runout in the scale field  34  simultaneously with the measurement plates  32  for axial runout by means of the measurement plates  48  that can be displaced with the setting button  47 . A magnifying glass  49  is fixed above the scale field for increasing the read-out accuracy. 
         [0063]    In addition, electronic distance sensors, whose measurement data can be retrieved on the display  26  by means of the operating fields  25  of the control unit  20 , can be attached between the sliding guides  51  or  30  of the measurement body. For this purpose, an adjustable electro-optical counting device  50 , with whose help a microcontroller unit assigns unique rim locations to the measurement values and calculates the necessary processing steps for centering relative to the running wheel center axis, is also attached to the upper ends. 
         [0064]    Furthermore, the measurement body  17  is constructed so that it can be removed from the support plate  12 ,  13 ,  14 ,  15 , so that a flat beam measurement body  59  with an opto-electronic measurement unit for flat beam measurements can be installed in its position, wherein this body is made from the flat beam emitters  52 ,  54 ,  56  and the flat beam receivers  53 ,  55 ,  57  in connection with a microcontroller and the display  26  with the control device  25  of the control unit  20 . Here, the beam units  52 ,  53  and also  54 ,  55  are arranged at an angle of 45° orthogonal to the running wheel center axis  23 . In contrast, the beam unit  56 ,  57  is 90° orthogonal to the running wheel center axis  23 . The angular position of 45° is preferred, because here deviations of the rim orthogonal to the axis  23  are mapped 1:1 to the flat beam receivers  53 ,  55  oriented parallel and orthogonal to the axis  23 . The flat beam unit  56 ,  57  detects spokes, valves, and the radial deviations of the running wheel rim. Thus, a unique assignment of the detected deviations in  53 ,  55  is possible by comparing with the measurement values in the microcontroller. In principle, one of the two flat beam units  52 ,  53  or  54 ,  55  is unnecessary; the two-fold use shown here is suitable for higher operating reliability of the measurement body and also for minimizing errors. Thus, a completely no-contact measurement of the axial and radial runouts of the running wheel is possible. Obviously, the automatic adjustment of the measurement body for the appropriate rim size can be achieved by a motor-driven device, moving the measurement body  59  along the guide devices  16 , in coordination with the microcontroller. In coordination with a drive roller for the running wheel similarly controlled by the microcontroller, the fully automatic measurement process of the running wheel is now possible. 
         [0065]      FIG. 4   a, b, c, d, e . The sketch in  FIG. 4   a  shows the perspective view of an embodiment of the motorized screw body with moving support unit. Here, on a base plate  60  is the support construction  61  moving in the running wheel axial direction towards the running wheel radial plane with the two-sided holding device  62 , on which a cardan joint is oriented by the device  63  moving in the axial and radial directions with holding support  64  and radial joint  65 , on which the screw body  67  and also the sliding guide device  68  are rigidly attached above the mounting body  66 . For movement of the support construction on the running wheel radial plane towards the appropriate spoke, the screw body adapts with the help of the sliding guide device to the inclined position of the appropriate spoke by means of a simultaneous tilting of the cardan joint in the running wheel axial plane and orthogonal to this plane, and finally contacts the spoke  75 , so that a centered position of the wrench socket  72  above the spoke nipple is achieved in its axial direction by means of the devices  69 ,  70 , and  71 . The holding devices  69  are equipped with devices for sliding, reversible adhesion to the spoke. The device  70  is also designed with a torsion measurement device for the spoke. 
         [0066]    Placing the wrench socket  72  on the spoke nipple  74  is realized through displacements centered relative to the nipple axis longitudinal to the spoke by means of a drive  73 , which is oriented in the mounting body  66 . Here, the wrench socket turns at 8 rpm, slow enough to be able to slide over the spoke nipple after detection with the help of the nipple position sensor  76 ; this movement is then stopped by means of the rim contact sensor  77  and the nipple wrench can change to a screwing process. Here, an angle sensor  87  housed in the screw body  67  directly measures the rotation of the wrench socket calculated in advance by the microcontroller. When removing the spoke nipple, the wrench socket slot is reversibly rotated into the starting position. In the opposite movement direction, the drive  73  lifts the wrench socket from the spoke nipple and the support construction  61  moves back into its starting position. 
         [0067]    In  FIG. 4   c , a construction of the torsion measurement device  70  with the running wheel spoke  75  clamped between two spring-guided balls  79  and the angle transmitter  80  is shown in a top view. The angle transmitter  80  pressed against the spoke  75  receives its rotating movements. In addition, the nipple position sensor  76  shown in top view is provided with the tracing pin arm  81  installed within the body  79 , the radial bearing  82 , the restoring spring  83 , and also the electrical contact device  84 . During the simultaneously lowering and rotating movement of the wrench socket  72 , the tracing pin arm  81  tapering downward initially lies with the narrow bottom side on an arbitrary rotationally positioned spoke nipple  78  and turns with the wrench socket  72  set at a right angle to its contact position up to the contact position parallel to one of the spoke-nipple square sides. Furthermore, in the top view, the lower plane of the screw body  67  is drawn with the wrench socket  72 , the drive wheel  86  connected to the gear shaft  85 , an angle transmitter  87 , and also transmission wheels  88  or stabilization wheels  89 . In principle, the placement movement of the nipple wrench on the spoke nipple can be performed within the slide-guided forward movement with the help of additional joint devices. Likewise, the sensor elements described in  FIG. 4   c  for contacting the nipple wrench or for stopping the placement movement are not absolutely necessary. Similarly, here, e.g., suitable spring devices are also possible in combination with the control of the wrench socket position by means of the measured current flow change due to the increased torque when the spoke nipple is seized, not least of all due to the slow and very precise rotating movement of the nipple wrench. Consequently, with the help of the angle transmitter  87 , the spoke tension within the combination of a tightening movement of the spoke nipple with a subsequent, opposite loosening movement through the motor current values measured at the same position of the angle transmitter  87  and the respective torque can be stored by the microcontroller unit and also calculated there by means of the simple, general, readable relationship* for screw connections under tensile stress as follows: 
         [0068]    Mt=tangential torque 
         [0069]    Fu=circumferential force 
         [0070]    Fa=axial tensile force in the threads 
         [0071]    α=pitch angle of the threads 
         [0072]    ρ=angle of friction, each formed with the resultant—from the normal force and the friction force opposite the respective movement—and the normal force 
         [0073]    r=flank radius of the threading. 
         [0074]    For tightening the spoke nipple, the following applies: 
         [0000]        Mt↑=r*Fu↑=r*Fa *tan(ρ+α)  I 
         [0075]    For loosening the spoke nipple: the following applies: 
         [0000]        M↓=r*Fu↓=r*Fa *tan(ρ−α)  II 
         [0076]    Because the axial spoke tension force Fa is sought, the second unknown, causing an interference but not exactly parametrizable, namely thread friction given by the angle of friction ρ can be solved here for ρ based on the thread friction acting equally in both measurements, and due to the measurement of Fa in the same nipple position in equation I and II, with the help of known addition theorems, simplified, and solved for Fa in the simple and exactly programmable relationship 
         [0000]        Fa=Mt↑−Mt↓/ 2*tan α,  III 
         [0077]    Because the total of 3 possible thread pitches for spoke threads according to DIN 79012 can be programmed into the microcontroller as pre-selected constants and thus an approximately linear relationship of the torque Mt↑ or Mt↓ measured directly via motor current and/or motor voltage or motor rotational speed is available for measurement evaluation, wherein for further error reduction, repeated measurements are possible. The advantage of this spoke tension measurement relative to a tension measurement through an acoustic measurement or by placing a suitable measurement device on the spoke lies both in the prevention of spoke crossing effects and also selection of the placement point, which is prone to errors, for the tension measurement. 
         [0078]      FIG. 4   d  shows the rotating drive movement in side view. Movements possible in the plane of the paper are shown by arrows. What is new is the radial joint  90  with the radial joint  92 , which is attached to its moving, rod-like holding device  91  and which simultaneously holds the sliding guide device  68  so that it can move in the radial direction. Furthermore,  93  describes the rotational path followed by the radial joint  92  through the motor-driven movement via the radial joint  90 . The tilting bearing of the radial joint  90  is described in  FIG. 4   e  by the support device  99  with linearly displaceable  101  radial bearings  98 , which are supported so that they can move by means of the linear guides  101 . Furthermore, the adhesion point  94  of the radial joint  92  on the spoke  75  is shown on the rotating track  93 , wherein the wrench socket  71  guided by sliding-device  68  contacts the spoke axis parallel for the first time, together with the holding devices  69 , the wrench socket guide device  72 , and also the torsion device  70 . From this it can be seen that the radial joint  92  in its position  95  with the sliding-device-guided wrench socket sitting on the nipple pushes  96  the tilting joint  90 , supported elastically and in a translational way in  97 , somewhat away from the running wheel radial plane  23 , which allows, for the inverse movement, a pulling away of the wrench socket from the nipple in the nipple axis direction along the spoke axis based on the restoring forces generated in  97 . 
         [0079]      FIG. 5 . Shown are the manual nipple wrench  102  in side view and also its 3 main components, one, the base body  103  composed of the spoke guiding device  104  with wrench socket  105 , contact web  106 , and also two-sided pressure sensor  107  and rotary head guide  108 , second, the rotary head  109  with spoke slot  112  [sic;  110 ], contact pressure flanks  111 , and pressure contact slot  112 , and finally the cover device  113 , with measurement display  114 , the signal devices  115 ,  116 , and also the spoke adhesion device  117 . By bringing the manual nipple wrench  102  in the axial direction against the running wheel spoke, the fixed cover device  113  moving with the base body  103  via an axis radial sliding guide device  105  [sic] contacts the spoke with the spoke adhesion device  117 , so that the cover device  113  forms a fixed base relative to rotating movements of the base body  103  by means of the rotary head  109 , and on the other hand, displays the torsion of the spoke via the wedge-shaped vertical tip  106  [sic] when the nipple wrench socket  105  sits on and turns the spoke nipple. For measuring the spoke tension with the nipple wrench  102 , the measurement of the torque when tightening or loosening the spoke nipple under tensile stress is required in the same nipple position. The torque is calculated via the force effect on the pressure sensors arranged radial to the spoke axis by means of a microchip  119  mounted in the cover device  113  with the help of the characteristic lines of the pressure sensor and also the linear relationship M=F×r. For this purpose, the cover device  113  is installed on its bottom side  120  by means of the sliding contact  121  of the base body  103  with two point-contact devices arranged at an angular position of ca. +/−75° relative to the spoke slot  110 . For optimum measurement results on the measurement contact, the base body is turned with the rotary button past the 75° position by ca. 25°. At these positions there are also point contacts, so that a “green light” for the second measurement and also for an overall successful measurement is given to the signal transmitter  115 ,  116  via the microchip. The linear formulas for the tightening torque and the loosening torque of the spoke nipple each contain, in addition to these parameters, the spoke tension, the thread pitch, the flank radius, and also the friction between the spoke and nipple thread. Because the same thread friction occurs for both tightening and loosening of the nipple, this can be eliminated by solving both equations, and thus the second unknown in both equations, the spoke tension, can be calculated directly without additional linearization by the microchip  119 , and can be displayed on the display  114 . To supply power and set up the current loop, the cover device  113  is provided with a DC battery  122  and is also connected on its bottom side to the rotary cap top side via a permanent sliding contact  123 . The rotary head  109  installed with bearing play relative to the base body conducts the current to the sliding contact  121  via one of the two pressure sensors  107  for pressure contact. Up to the measurement of the torque with the manually contacted pressure sensors  107 , the physics of the screwing process is the same as that already described for the motor-driven nipple screwing measurement. In addition to the pressure sensors  107  described here, the manual nipple wrench  102  can also be installed with other electronic devices suitable for measuring torque. 
         [0080]    Achieved Advantages 
         [0081]    Centering Stand 
         [0082]    All of the work procedures and measurement errors occurring due to the adjustment work of measurement devices are prevented. Arbitrary running wheel or rim sizes from 24-29 inches with hub installation widths of &gt;90 mm to &lt;160 mm are positioned for the axial and radial runout measurement of the rim measurement simultaneously in a radial plane of the running wheel and centered relative to the running wheel axis center plane. Positioning the measurement body and attachment of the measurement tracing pin are performed in a single mechanically guided movement sequence. Can be equipped according to the modular principle as a basic model up to a fully automatically controlled centering device. Due to the modular principle of the entire construction, the centering stand is provided with devices for installing the motor-driven nipple wrench, a motor-controlled drive roller, and also opto-electronic distance sensors. 
         [0083]    Measurement Body 
         [0084]    Simultaneous attachment of the two side tracing pins, radial and axial runout measurement possible for grooved rim sides just by means of the side tracing pins. Increased measurement accuracy through direct measurement value display without intermediate mechanical elements. Simultaneous read-out of the radial and axial runout relative to the running wheel axis center plane on a scale field. Measurement accuracy :9 [sic] 0.05 mm without additional equipment possible by means of a magnifying glass over the scale field. Detecting of measurement affects due to unevenness of the rim surfaces possible due to the reduction/enlargement of the measurement gap of the parallel measurement plates displayed relative to the running wheel axis center plane. Additional installation of electronic distance sensors, graphical display, and also centering computer according to the modular principle possible. 
         [0085]    Motor-Driven Nipple Wrench 
         [0086]    The exact orientation of the tension socket in the nipple axis with exact-fit positioning over the spoke nipple is possible through the moving sliding guide body of the nipple wrench. Therefore, minimal mechanical wear and small overall size. High positioning accuracy of the spoke nipple due to slower nipple movements measured directly via the position of the drive pinion. Exact fatigue-free work also in high spoke tension ranges. Direct measurement of the spoke tension without additional equipment. Use of a geared motor wrench socket CPU small display combination as a handheld device for exact tightening/loosening of the spoke nipple or measuring of the spoke tension with simultaneous torsion control. Prevention of measurement errors occurring in the spoke tension measurement due to crossed spokes and the selection of the spoke measurement point. Spoke tension of the running wheel can be pre-selected arbitrarily through high nipple wrench operation accuracy with microcontroller use. Low technical expense for rotational and translational movement sequence. Multipurpose use possible due to small overall size. 
         [0087]    IV. Manual Nipple Wrench 
         [0088]    1. Unification of the following processing steps previously performed separately into one work device: 
         [0089]    a) measuring the tension of the running wheel spokes 
         [0090]    b) torsion control of the spoke during the nipple rotation 
         [0091]    c) manual turning of the spoke nipple. 
         [0092]    2. The associated time and cost savings. 
         [0093]    3. Increase of the measurement accuracy by preventing previously unavoidable error sources, e.g., due to crossed spokes and the selection of the spoke measurement point.