EP1671090A1 - Dispositif de mesure de force - Google Patents

Dispositif de mesure de force

Info

Publication number
EP1671090A1
EP1671090A1 EP04790147A EP04790147A EP1671090A1 EP 1671090 A1 EP1671090 A1 EP 1671090A1 EP 04790147 A EP04790147 A EP 04790147A EP 04790147 A EP04790147 A EP 04790147A EP 1671090 A1 EP1671090 A1 EP 1671090A1
Authority
EP
European Patent Office
Prior art keywords
force
measuring device
mandrel
springs
force measuring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP04790147A
Other languages
German (de)
English (en)
Inventor
Jürgen HERHAUS
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Honigmann Industrielle Elektronik GmbH
Original Assignee
Honigmann Industrielle Elektronik GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Honigmann Industrielle Elektronik GmbH filed Critical Honigmann Industrielle Elektronik GmbH
Publication of EP1671090A1 publication Critical patent/EP1671090A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
    • G01L1/00—Measuring force or stress, in general
    • G01L1/20—Measuring force or stress, in general by measuring variations in ohmic resistance of solid materials or of electrically-conductive fluids; by making use of electrokinetic cells, i.e. liquid-containing cells wherein an electrical potential is produced or varied upon the application of stress
    • G01L1/22—Measuring force or stress, in general by measuring variations in ohmic resistance of solid materials or of electrically-conductive fluids; by making use of electrokinetic cells, i.e. liquid-containing cells wherein an electrical potential is produced or varied upon the application of stress using resistance strain gauges
    • G01L1/2206—Special supports with preselected places to mount the resistance strain gauges; Mounting of supports
    • G01L1/2243—Special supports with preselected places to mount the resistance strain gauges; Mounting of supports the supports being parallelogram-shaped

Definitions

  • the present invention relates to a force measuring device according to the preamble of the main claim.
  • Such a force measuring device is known from EP 0 621 469 B1.
  • a special feature of this force measuring device is that a pair of measuring springs which are parallel and spaced apart from one another is provided for measuring the force to be expected from a predetermined direction.
  • This arrangement is referred to as a "double bending beam", but is not intended to limit the arrangement of measuring springs of this type to the present invention. All possible measuring spring arrangements are considered for the measurement of these forces, including single benders, shear force sensors, torsion sensors, etc.
  • measuring rollers can also be produced very well with such a force measuring device, which are characterized in particular by the fact that the roller bearing is also always displaced parallel to itself under load.
  • the invention solves this problem with the features of the main claim.
  • the advantage of the invention is that in relation to the stiffnesses of the known force measuring devices for transverse force directions with comparable cross-sectional dimensions, a stiffness that is four times higher is achieved. This increase in stiffness therefore follows the requirement to achieve only small deflections in the transverse direction and thus to maintain a high lateral load resistance. The ability to absorb high side loads is not paired with a waiver to achieve high nominal measuring forces.
  • This advantage is achieved in that two mutually parallel and spaced bending springs are provided in the transverse direction, which deform under the transverse load just as - in the case of the known force measuring device - the double bending beams provided for the measuring direction.
  • each of the transverse bending springs is deformed in an S-shape under the transverse load and thus has a bending line with two turning points, the force measuring device according to the invention opposes the transverse force with a correspondingly high resistance, which leads exactly to the comparably small deformations despite correspondingly high transverse forces.
  • the force measuring device is furthermore also excellently suitable for combination with roller bearings which can be arranged on corresponding bearing seats of the yoke.
  • the exactly parallel movement of the rolling bearing is e.g. Necessary for measuring tasks on rollers when it is important to move the measuring roller without constraint. In such cases, it must be ensured under the influence of transverse forces that the web edges of the belt do not run out of their intended track due to an undesired displacement of the measuring roller.
  • the spiral springs which are provided for absorbing the transverse forces, as well as the at least one measuring spring which serves to detect the force-related deformation, extend between the base and the yoke.
  • the further spiral springs can therefore be connected in one piece to the yoke and base.
  • the transverse bending springs are worked out of the measuring spring (s) by appropriate measures, which serve to record the force to be measured.
  • the bending springs can also be used for the qualitative recording of the transverse forces or, depending on the installation situation, “only” for the geometrical parallel guidance of the yoke under the influence of transverse forces the stiffness of the bending springs for each measuring task is produced without leaving the advantages of the double bending beam known in a special design from the prior art, which only has two or more parallel and S-shaped bending springs in the direction of the force to be measured ,
  • the position of the transverse direction relative to the direction of the predetermined force is arbitrary as long as the transverse direction and agreed force to make an angle between them that is greater than 0 (except 180 degrees) degrees.
  • measuring spring (s) provided for force measurement have slots which, on the one hand, extend in the longitudinal direction of the measuring springs and, on the other hand, are perpendicular to the transverse direction with their slot plane.
  • the base in a ring shape and to fix it on the machine frame by means of a mandrel which pierces the annular recess in the base, the mandrel on its side facing away from the machine frame having a head which is attached to the outside of the base.
  • This development has the advantage that the mandrel can be fixed in any desired rotational position within a 360 degree angle range on the machine frame.
  • the dome is advantageously fixed in a clamping base which can be rigidly connected to the machine frame.
  • This terminal base has a fitting hole for the Mandrel, which is cut by a clamp hole.
  • a pair of jaws sits in the clamp bore and engages the mandrel from two sides. This is achieved in that a clamping jaw sits on one side of the fitting bore and the other clamping jaw sits on the other side of the fitting bore.
  • An advantageous further development provides for actuating the pair of clamping jaws by means of a clamping screw which sits with its shaft in a through hole in one clamping jaw, while the other clamping jaw has a threaded hole corresponding to the thread of the clamping screw.
  • This development of the invention offers the advantage that the clamping screw can run completely inside the clamping base and thus spring back behind the envelope of the clamping base.
  • the force measuring device according to the present invention in particular also permits a modular structure.
  • the counter flange of an extension axis can be attached to the outside of the head of the Do via a screw-on flange provided there.
  • a further counter flange can be provided, which is used to attach a mirror-image arranged force measuring device.
  • both embodiments of the invention can be advantageous, depending on whether the transverse force is significant and / or must be taken into account.
  • the cables can be guided out of the force measuring device to the machine frame via these communicating holes.
  • the extension axis should also be drilled hollow so that the measuring line can be led out to the machine frame via this axis hole.
  • the mandrel has a key contact surface, which should preferably be concentric to the mandrel axis.
  • Fig. 1 a first embodiment of the invention
  • Fig. 2 shows an embodiment of the invention on a measuring roller
  • Fig. 3 shows a section along the line III-III from Fig. 2
  • Fig. 5 shows another embodiment 6, the embodiment according to the invention.
  • Figure 7 shows the embodiment.
  • the figures show a force measuring device 1 for measuring a force 2.
  • the force 2 acts from a predetermined direction 3 on the force introduction point 4 of the force measuring device 1.
  • the force introduction point 4 is connected via a yoke 5 to the unidirectional free ends 8 - here - two measuring springs 6, 7 which are parallel to one another. It can also be a single or more than two parallel measuring springs.
  • the measuring springs 6,7 are provided for force measurement.
  • the connection between measuring springs 6, 7 and yoke 5 is designed as a rigid connection.
  • the other end 9 of the measuring springs 6, 7 is seated on a base 10 which is designed so as to be rigidly connectable to the machine frame 50.
  • the force-related deformation, ie the deformation under the force 2 to be measured, of the spiral springs 6, 7 is detected at predetermined measuring points 11 a1 and evaluated.
  • the detection is expediently carried out via strain gauges. If four identical stretchers used measuring strips, the measuring circuit is in the form of a Wheatstone's bridge.
  • FIGS. 1 to 4 The difference between the embodiments of FIGS. 1 to 4 and FIGS. 5 to 8 lies in the fact that in the case of FIGS. 1 to 4 the measuring springs 6, 7 are always designed as so-called pure double bending beams.
  • FIGS. 5 to 7 show another embodiment.
  • the measuring springs 6, 7 are connected to one another via a so-called shear force transducer 6 'in their common longitudinal center plane.
  • the shear force transducer 6 ' is formed by a hole made on both sides in the force measuring device 1, which leaves a kind of elastically deformable membrane, since the holes on both sides do not completely pass through the force measuring device 1. This also results in two mutually parallel measuring springs 6, 7, which, however, can no longer be referred to as double bending beams.
  • the bending line of these measuring springs 6, 7 is shown in FIG. 6 below.
  • the bending line has a qualitative course with basically two turning points. However, it does not correspond to the course of a double bending beam, because over the centrally arranged shear force transducers, overlay effects like those of a single bender are inevitable.
  • the yoke 5 is guided in parallel via at least one (further) pair of mutually parallel bending springs 12, 13, 14 in a transverse direction 15 which is transverse to the direction 3 of the predetermined force 2.
  • the yoke also receives a parallel guidance in a direction that is transverse to the direction 3 of the force 2 to be measured, so that the yoke 5 is practically parallel to itself in two directions.
  • the transverse direction 15 can assume any direction that is transverse to the line of action of the force 2 to be measured.
  • the yoke is expediently guided in parallel
  • the parallel guidance of the yoke 5 in its two directions of movement can therefore take place by an additional arrangement of paired spiral springs, the deflection plane of which lies in the transverse direction to be expected.
  • the basic idea of the invention is to provide measuring springs or bending springs at least in pairs, both in the direction of the force 2 to be measured and in the transverse direction 15, which guide the yoke in parallel in the two directions according to the principle of the respective double bending beam.
  • each double bending beam is known to deform in the form of an S-stroke, a correspondingly high deformation work must be performed to deflect the yoke under the respectively acting force, which gives the entire sensor or the entire force measuring device 1 an outstanding rigidity in two directions.
  • the basic idea of the invention is therefore based on providing a pair of double bending beams in each of the deformation or loading directions to be expected, so that a correspondingly high output signal is generated even with a small stroke, while at the same time the entire sensor has an outstandingly good rigidity. For the sake of completeness, however, it should be said that it is not absolutely necessary to also measure the transverse forces that occur in the transverse direction.
  • FIG. 1 shows a system of three mutually parallel bending springs 12, 13, 14, which are all deformed together in parallel under the transverse load and, as a result, also require a correspondingly high amount of deformation work.
  • transverse direction 15 can be at any angle to the direction 3 of the force 2 to be measured, as long as this angle is not 180 degrees.
  • the respective conditions depend on the machine requirements. These can be specified in particular to the relationships between the direction of gravity and the direction of the resultant of the force to be measured when deflecting an endless material so that there are also angles of unequal to 90 degrees between the parasitic transverse direction due to the dead weight and the line of action of the force to be measured.
  • the measuring springs 6, 7 provided for force measurement are penetrated by slots 16, 17 which extend in the longitudinal direction of the measuring springs 6, 7.
  • the slot plane of the slots 16, 17 is practically perpendicular to the transverse direction 15, so that in this way the measuring springs 6, 7 provided for measuring the force 2 to be measured are now also used for parallel guidance of the yoke 5 in the transverse direction.
  • the slot planes of the slots 16, 17 do not in any case have to extend perpendicular to the transverse direction 15, but that other oblique directions are theoretically also possible.
  • 2 shows in particular that the yoke 5 has an annular receiving zone 18 for a roller bearing 19.
  • the force to be measured can thus be introduced into the yoke 5 via the roller bearing 19 even in the case of deflection rollers, deflection rollers or the like.
  • the inner diameter of the annular receiving zone 18 is, however, larger in the exemplary embodiments shown than the outer diameter of a Do s 20 passing through the yoke 5, so that the yoke 5 has a clearance for deformation of the spiral springs 6, 7, while at the same time in contact between the inner diameter of the annular ones Receiving zone 18 and the outer circumference of the dome 20 a reliable overload stop is guaranteed.
  • This measure offers advantages in particular if the base 10 is annular and is penetrated by a mandrel 20 which can be rigidly connected to the machine frame 50.
  • the mandrel 20 has a head on the outside of the base 10, which in turn can be rigidly connected to the base 10.
  • This measure alone or in conjunction with the other bending springs 13, 14, 15, serves in particular the modular construction possibility of a sensor system consisting of several force measuring devices 1 in connection with the requirement for a deflection roller mounted on the fly, for example for web-like material.
  • the mandrel 20 can be fixed continuously in any number of different rotational positions on the machine frame 50 in a 360-degree angular range.
  • the clamping base 22 has a fitting bore 23 which can be brought into a suction fit with the outer diameter of the mandrel 20.
  • the fitting bore 23 is cut here by a clamp bore 24 within which a pair of jaws acting on the mandrel 20 is seated.
  • the mandrel 20 Upon delivery of the pair of jaws, of which each jaw engages on one of two opposite sides of the mandrel 20, the mandrel 20 is clamped against rotation, and additionally a slight relative rotation of the mandrel 20 is eliminated during the clamping process because the pair of jaws 25, 26 symmetrically on the mandrel 20 attacks.
  • the pair of clamping jaws 25, 26 be acted upon by a clamping screw 27, with the aid of which the two clamping jaws 25, 26 are brought towards one another in the direction of the mandrel 20. So that the clamping screw 27 springs back completely within the outer surface line of the clamping base 22, it is additionally proposed to make a through hole 29 in one clamping jaw 25 or the other clamping jaw 26, while the other clamping jaw 26 or 25 then has one with the thread of the clamping screw Has 27 corresponding threaded bore.
  • the head 21 of the mandrel 20 is provided with a screw-on flange 33, this offers the advantage that an extension axis 35 in the sense of a freely cantilevered roller bearing according to FIG. 2 can also be attached via a counter flange 34 attached at the end.
  • the extension axis 35 should have at its end facing away from the counter flange 34 a further counter flange 36, on which a further force measuring device can be attached in mirror image to the force measuring device 1 provided on the machine side.
  • the mandrel 20 should have a cable entry opening 37 in the longitudinal region of the measuring springs 6, 7, which opening is cut by a mandrel longitudinal bore 38. Since the longitudinal mandrel bore 38 extends at least to one end of the mandrel 20, the measuring lines can be easily led out in this way.
  • the mandrel 20 responsible for the left force measuring device 1 is completely drilled, since it also serves to lead the measuring lines out of the further force measuring device 1 shown in the right part of the figure.
  • the entire length of the extension axis 35 is drilled through such that the axis bore 39 is aligned with the longitudinal mandrel bores 38.
  • the mandrel 20 which can be seen in the right part of the picture does not, however, need to be completely drilled through since the measuring lines expediently only have to be led out in the direction of the machine frame 50.
  • the mandrel 20 provided in the right part of the image according to FIG. 2 shows a key engagement surface 40, with the aid of which, when the clamping jaw pair 25, 26 is released, the force measuring device 1 can be aligned such that the measuring axis corresponds to the direction 3 of the force 2 to be measured coincides.
  • FIGS. 4, 6 and 7 also show that the deformation of the further bending beams 12, 13, 14 can also be detected by sensors 11la-d.
  • the sensors llla-d are attached in a known manner at the locations of the greatest elongation of the bending beams, that is to say where they assume their S-shaped deformation, and are wired accordingly.
  • Tapped hole 1 first inclined surface 2 second inclined surface 3 screw-on flange 34 counter flange

Landscapes

  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Force Measurement Appropriate To Specific Purposes (AREA)

Abstract

Dispositif de mesure de force pour la mesure d'une force qui est appliquée à partir d'une direction prédéterminée sur le site d'introduction de force du dispositif de mesure de force. Pour la mesure de la force, ledit dispositif comporte deux doubles ressorts de flexion à l'aide desquels le site d'introduction de force est guidé de manière parallèle sous l'influence de la force à mesurer. En outre, selon la présente invention, le site d'introduction de force est également guidé de manière parallèle dans une direction transversale par rapport à la direction de la force à mesurer, par l'intermédiaire d'au moins une autre paire de ressorts de flexion parallèles l'un à l'autre.
EP04790147A 2003-10-06 2004-10-06 Dispositif de mesure de force Withdrawn EP1671090A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10346811.0A DE10346811B4 (de) 2003-10-06 2003-10-06 Kraftmeßvorrichtung
PCT/EP2004/011162 WO2005036117A1 (fr) 2003-10-06 2004-10-06 Dispositif de mesure de force

Publications (1)

Publication Number Publication Date
EP1671090A1 true EP1671090A1 (fr) 2006-06-21

Family

ID=34428251

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04790147A Withdrawn EP1671090A1 (fr) 2003-10-06 2004-10-06 Dispositif de mesure de force

Country Status (4)

Country Link
US (1) US7698963B2 (fr)
EP (1) EP1671090A1 (fr)
DE (1) DE10346811B4 (fr)
WO (1) WO2005036117A1 (fr)

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Publication number Priority date Publication date Assignee Title
DE102006031635A1 (de) * 2006-07-06 2008-01-17 Werthschützky, Roland, Prof. Dr.-Ing. Minaturisierbarer Kraftsensor zum Erfassen eines Kraftvektors
ATE498830T1 (de) * 2006-11-20 2011-03-15 Texmag Gmbh Vertriebsges Vorrichtung zum messen einer zugkraft innerhalb einer materialbahn oder eines materialstranges
DE102009002188A1 (de) * 2009-04-03 2010-10-14 Tecsis Gmbh Kraftaufnehmer zur Messung von Stützkräften in einem Abstützelement
GB2498755A (en) * 2012-01-26 2013-07-31 Michael John Hearn Idler roller for a belt conveyor including load cell
WO2016044094A1 (fr) * 2014-09-16 2016-03-24 Thorlabs, Inc. Actionneur piézo-électrique amplifié avec vis de réglage motorisée
DE102017210289A1 (de) * 2016-06-29 2018-01-04 Aktiebolaget Skf Rolle mit integrierter Lastdruckzelle
WO2019049099A1 (fr) * 2017-09-08 2019-03-14 Alemnis Ag Capteur de force
FR3075367B1 (fr) * 2017-12-19 2021-04-09 Centre Technique Des Industries Mec Et Du Decolletage Module de mesure d'efforts, porte-plaquette et extremite de bras de robot pourvus d'un tel module de mesure d'efforts
DE102018200047A1 (de) * 2018-01-03 2019-07-04 Aktiebolaget Skf Sensorrolle
EP3578942B1 (fr) * 2018-06-07 2024-05-01 Amazonen-Werke H. Dreyer SE & Co. KG Appareils et procedes pour mesurer des forces
EP3892967B1 (fr) * 2020-04-06 2022-08-03 FMS Force Measuring Systems AG Dispositif de mesure de force permettant de détecter des tractions de bande d'une bande de matière continue

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Also Published As

Publication number Publication date
US7698963B2 (en) 2010-04-20
DE10346811A1 (de) 2005-05-19
US20070051190A1 (en) 2007-03-08
DE10346811B4 (de) 2018-07-12
WO2005036117A1 (fr) 2005-04-21

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