WO1994007118A1 - Circular radial force transducer - Google Patents

Circular radial force transducer Download PDF

Info

Publication number
WO1994007118A1
WO1994007118A1 PCT/SE1993/000711 SE9300711W WO9407118A1 WO 1994007118 A1 WO1994007118 A1 WO 1994007118A1 SE 9300711 W SE9300711 W SE 9300711W WO 9407118 A1 WO9407118 A1 WO 9407118A1
Authority
WO
WIPO (PCT)
Prior art keywords
radial force
force transducer
transducer according
measurement
spokes
Prior art date
Application number
PCT/SE1993/000711
Other languages
French (fr)
Inventor
Pär Gustafsson
Tomas Hidman
Magnus WÄRME
Lars Örnholmer
Original Assignee
Asea Brown Boveri Ab
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 Asea Brown Boveri Ab filed Critical Asea Brown Boveri Ab
Publication of WO1994007118A1 publication Critical patent/WO1994007118A1/en

Links

Classifications

    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
    • G01L5/00—Apparatus for, or methods of, measuring force, work, mechanical power, or torque, specially adapted for specific purposes
    • G01L5/0009—Force sensors associated with a bearing
    • G01L5/0023—Force sensors associated with a bearing by using magnetic sensors
    • 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
    • G01L1/12—Measuring force or stress, in general by measuring variations in the magnetic properties of materials resulting from the application of stress
    • G01L1/125—Measuring force or stress, in general by measuring variations in the magnetic properties of materials resulting from the application of stress by using magnetostrictive means
    • 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
    • G01L1/12—Measuring force or stress, in general by measuring variations in the magnetic properties of materials resulting from the application of stress
    • G01L1/127—Measuring force or stress, in general by measuring variations in the magnetic properties of materials resulting from the application of stress by using inductive means

Definitions

  • Figure 1 shows a radial force measuring device according to the state of the art .
  • Figures 2, 3 and 4 show different embodiments of a radial force measuring device according to the invention.
  • the radial force transducer has a circular-cylindrical shape which comprises an inner ring 1 and an outer ring 2 being concentric with the inner ring.
  • the shaft of the deflector roll is concentrically journalled in the inner ring in a bearing 4 of the roll.
  • These two rings are separated from each other by a circular-cylindrical tubular hollow space 5.
  • the rings are held together by means of a waist 6 which adjoins two parallel circular-cylindrical recesses 7 and 8 with the same radial distance from the centre of the shaft and which adjoins the tubular hollow space.
  • strain gauges 9 and 10 are mounted on the confronting parts of the envelope surface of the circular- cylindrical recesses, that is towards the waist.
  • the outer ring can be fixed to a bearing stand 11 with the feet 12 and 13 against the base via the holes 14, 15, 16 and 17, or it can be fixed in some other way.
  • the measurement practically always takes place with radial force transducers at both ends of the shaft and the arrow at FM indicates the direction of measurement.
  • the radial force transducer Independently of the direction of the force to which the shaft is subjected, the radial force transducer will measure the force to which the waist is subjected between two strain gauges. One of the transducers will thereby sense a tensile force and the other transducer will sense a compressive force depending on the direction of the force.
  • the radial force transducer is mounted such that it measures the horizontal part of the force to which the roll and the shaft are subjected.
  • the radial force transducer of HBM is largely designed in the same way as the radial force transducer of FAG, however with the difference that it is provided with two waists with strain gauges, acting diametrically to each other.
  • the force to which the shaft is subjected is generally not parallel to the feet of the bearing stand. This is due to the fact that the force emanates from the tensile stress in the material surrounding the runner or deflector roll and to the fact that the connection to the runner or deflector roll of the material is normally not parallel to the feet of the bearing stand. In certain contexts it may be even be so that the wrap angles vary while the production is in progress. With knowledge of the connection angles for the material around the roll relative to the above-mentioned plane in the centre of the waist between the strain gauges, relatively simple mathematical operations are needed to determine the tensile stress in the material.
  • Both of the above-mentioned variants also have the disadvan ⁇ tage that they are very sensitive to any moment from the deflector roll.
  • a radial force transducer according to the invention has an inner ring and an outer ring concentric with the inner ring, the inside diameter of the outer ring being larger than the outside diameter of the inner ring.
  • the force-transferring shaft is also journalled in a bearing in the same way.
  • the radial force transducer is provided with two diametrically located spokes which inter ⁇ connect the inner and outer rings.
  • the spokes are provided with specially designed measuring regions. However, contrary to the above-described designs with strain gauges, the measuring regions are formed such that the principle of magnetoelastic force measurement can be utilized.
  • the measuring regions are provided with recesses such that a diaphragm is formed in the measuring region, which diaphragm will serve as the magnetoelastic core in the force transducers used. Holes for necessary excitation and measurement windings are then made in the diaphragm.
  • the measurement direction F defining an x- direction, is perpendicular to a plane which is determined by a line through the centre of the radial force transducer and through the centre of the spokes, defining a y- direction, as well as by a line through the centre of the radial force transducer and through the centre line of the shaft defining a z-direction.
  • the hollow space between the two rings is formed in a diffe ⁇ rent way from that according to the state of the art to better adapt to the principle of magnetoelastic measurement.
  • the shape of the hollow space according to the invention is relatively difficult to define from a geometrical point of view but will be referred to below as a cable clamp shape.
  • FIG. 2 A preferred embodiment of a radial force transducer accor ⁇ ding to the invention is shown in Figure 2.
  • the radial force transducer comprises an inner ring 1 with the internal hole for the shaft of the deflector roll and an outer ring 2 whose inside diameter is larger than the outside diameter of the inner ring.
  • the two rings are interconnected by means of two diametrically located spokes 6a and 6b.
  • the cable clamp- shaped space remaining between the rings is clear from both Figures 2 and 3.
  • the largely plane foot regions 7a, 7b and 8a, 8b form the edges of the spokes.
  • the foot regions of the cable clamp-shaped space are then interconnected via the tubular and semicircular hollow spaces 5a and 5b between the two rings.
  • the outer ring 2 will there ⁇ fore, towards the cable clamp-shaped hollow spaces, have the shape of two ring halves 2a and 2b with the fixing holes 14, 15, 16 and 17.
  • the direction of the measurement force is indicated in the figure by the arrow F m and the direction of any transverse forces is indicated by the arrow F t •
  • the shaft of the deflector roll may be rotating or non- rotating.
  • a bearing is mounted in the hole of the inner ring.
  • the hole of the inner ring may have other embodi ⁇ ments.
  • the spokes are provided with specially designed measuring regions for the principle of magnetoelastic measurement used.
  • the measuring regions therefore comprise diaphragms 18a and 18b which constitute the magnetoelastic core of the used force transducers.
  • the diaphragms in an embodiment according to Figure 2 have been achieved by providing recesses in the spokes such that circular diaphragms are formed.
  • Figure 2 also shows the holes provided in the diaphragms for the excitation and measurement windings.
  • Spokes and measuring regions can be designed in a plurality of different ways within the scope of the invention. A further example is shown in Figure 3. In regions between the hollow spaces 7a-8a and 7b-8b, two gaps 19, 20 and 21, 22, respectively, have been provided towards the foot region of the cable clamp-shaped space.
  • the diaphragms of the magnetoelastic force transducers will therefore con- sist of the rectangular regions 27a and 27b between the gaps.
  • An important advantage with this embodiment is that the transducers become stiff against any moments introduced by the deflector roll.
  • a better separation is obtained between the forces acting on the diaphragms and the transverse force-absorbing beams. This reduces the influence of transverse forces on the measurement result.
  • the measuring regions can be provided with corre ⁇ sponding gaps also in this case.
  • the embodiments are symmetrical in relation to all planes which can be defined on the basis of previously defined x-, y- and z-directions, that is, the y-z plane, the x-z plane and the x-y plane.
  • the symmetry in relation to the y-z plane means that the transducer can be loaded by a measurement force FM to the same extent in posi- tive and in negative direction
  • the symmetry in the x-z plane means that the transducer can be loaded by a trans ⁇ verse force FT to the same extent in positive and in nega ⁇ tive transverse force direction.
  • the symmetry in the x-y plane causes the transducer to become insensitive to a force in the direction of the shaft.

Abstract

The invention consists of a radial force transducer which comprises an inner ring (1) for axially mounting the transducer and an outer ring (2) whose inside diameter is larger than the outside diameter of the inner ring, the rings being interconnected by means of two diametrically located spokes (6a, 6b) arranged with measuring regions adapted for radial force measurement with magnetoelastic transducers.

Description

Circular radial force transducer
TECHNICAL FIELD
In connection with rolling, for example rolling of strip, foil, etc., in manufacturing and coating of paper, it is important to be able to measure the tensile stress during the manufacturing process. The quality of the finished product is highly dependent on the manufacture being per- formed with a correct and constant tension. The manufac¬ turing process in connection with this kind of rolling always means that the product in question passes or runs over a deflector roll. This allows a very good possibility of obtaining a measure of the tensile stress in the product in the course of the manufacture. The measured tensile stress can then be used to influence the manufacturing process by means of different control systems such that a correct and constant tension can be maintained. A circular radial force measuring device according to the invention can be used, in a good and simple manner, for such tensile stress measurement.
The measurement requirement mentioned above also occurs in connection with the manufacture of round material, for example cables and ropes. In these cases the deflector roll is replaced by a wheel for deflection of the round material.
BRIEF DESCRIPTION OF THE DRAWINGS
Figure 1 shows a radial force measuring device according to the state of the art .
Figures 2, 3 and 4 show different embodiments of a radial force measuring device according to the invention. BACKGROUND ART, PROBLEMS
The need of measuring the tensile stress in connection with rolling as mentioned above has existed for a long time. Several makers of radial force measuring devices are therefore active on the market. Such devices are described, inter alia, in Publ.Nr. WL 55 130/2 DA, FAG Kraftmessystem MGZ, from FAG Kugelfischer Georg Schafer KGaA, in HBM Datenblatt D 21.41.0 Radialkraftaufneh er RKl and HBM Vorlaufige Bedienungsanleitung, Radialkraftaufnehmer RK2, 265.00-01-1.ON and in Specification Sheet, ELMESS Web Tension Monitors PDV 02. Characteristic of all of these devices is that they use strain gauges as force-sensing element and that they are largely designed in the same way.
A brief summary of a radial force transducer according to the state of the art, based on the above FAG publication, will be given, starting from Figure 1.
The radial force transducer has a circular-cylindrical shape which comprises an inner ring 1 and an outer ring 2 being concentric with the inner ring. The shaft of the deflector roll is concentrically journalled in the inner ring in a bearing 4 of the roll. These two rings are separated from each other by a circular-cylindrical tubular hollow space 5. The rings are held together by means of a waist 6 which adjoins two parallel circular-cylindrical recesses 7 and 8 with the same radial distance from the centre of the shaft and which adjoins the tubular hollow space. On the confronting parts of the envelope surface of the circular- cylindrical recesses, that is towards the waist, strain gauges 9 and 10 are mounted. The outer ring can be fixed to a bearing stand 11 with the feet 12 and 13 against the base via the holes 14, 15, 16 and 17, or it can be fixed in some other way. The measurement practically always takes place with radial force transducers at both ends of the shaft and the arrow at FM indicates the direction of measurement. Independently of the direction of the force to which the shaft is subjected, the radial force transducer will measure the force to which the waist is subjected between two strain gauges. One of the transducers will thereby sense a tensile force and the other transducer will sense a compressive force depending on the direction of the force. As a rule, however, the radial force transducer is mounted such that it measures the horizontal part of the force to which the roll and the shaft are subjected.
The radial force transducer of HBM is largely designed in the same way as the radial force transducer of FAG, however with the difference that it is provided with two waists with strain gauges, acting diametrically to each other.
The force to which the shaft is subjected is generally not parallel to the feet of the bearing stand. This is due to the fact that the force emanates from the tensile stress in the material surrounding the runner or deflector roll and to the fact that the connection to the runner or deflector roll of the material is normally not parallel to the feet of the bearing stand. In certain contexts it may be even be so that the wrap angles vary while the production is in progress. With knowledge of the connection angles for the material around the roll relative to the above-mentioned plane in the centre of the waist between the strain gauges, relatively simple mathematical operations are needed to determine the tensile stress in the material.
There are certain disadvantages with the design described under the background art, in addition to the low signal level obtained in the strain gauges. The signal contribution will be influenced both by the mounting of the force trans¬ ducer if the base is uneven and by any transverse forces which may originate from the fact that the shaft and the radial force transducers are not mounted exactly perpendi¬ cular to the direction of running of the material. Another complication which arises with the above designs is connected with the use of strain gauges. To obtain a satis¬ factory signal level from such strain gauges, a relatively high mechanical stress level is needed in the material where the strain gauges are applied. This means at the same time that the area of the strain gauge, even at nominal load, is subjected to a relatively great strain. To avoid plastic deformation of measuring regions at overload, radial force transducers with strain gauges therefore always have to be provided with mechanical means for overload protection of some kind.
Both of the above-mentioned variants also have the disadvan¬ tage that they are very sensitive to any moment from the deflector roll.
SUMMARY OF THE INVENTION, ADVANTAGES
In the same way as a radial force transducer according to the state of the art, a radial force transducer according to the invention has an inner ring and an outer ring concentric with the inner ring, the inside diameter of the outer ring being larger than the outside diameter of the inner ring. The force-transferring shaft is also journalled in a bearing in the same way. Further, the radial force transducer is provided with two diametrically located spokes which inter¬ connect the inner and outer rings. The spokes are provided with specially designed measuring regions. However, contrary to the above-described designs with strain gauges, the measuring regions are formed such that the principle of magnetoelastic force measurement can be utilized. To this end the measuring regions are provided with recesses such that a diaphragm is formed in the measuring region, which diaphragm will serve as the magnetoelastic core in the force transducers used. Holes for necessary excitation and measurement windings are then made in the diaphragm. This means that the measurement direction F . defining an x- direction, is perpendicular to a plane which is determined by a line through the centre of the radial force transducer and through the centre of the spokes, defining a y- direction, as well as by a line through the centre of the radial force transducer and through the centre line of the shaft defining a z-direction.
The hollow space between the two rings is formed in a diffe¬ rent way from that according to the state of the art to better adapt to the principle of magnetoelastic measurement. The shape of the hollow space according to the invention is relatively difficult to define from a geometrical point of view but will be referred to below as a cable clamp shape.
Several advantages are afforded with the above shape of a radial force transducer in relation to that described accor¬ ding to the state of the art. The signal contributions from the two measuring regions, depending on mounting on uneven base, compensate one another. The signal effect from trans¬ verse forces FT is compensated for because of opposite mechanical stress in the two measuring regions, and thus the signal is influenced to a very small extent by transverse forces. With two measuring transducers also a higher measurement signal level is obtained.
Another important advantage of a design according to the invention in relation to the state of the art is that the principle of magnetoelastic measurement provides lower nominal mechanical stress at nominal load. This means that a lower strain or deformation is obtained at nominal load than when using strain gauges. This results in such a superior overload endurance that no mechanical protection is needed.
The design described also means that a radial force trans¬ ducer according to the invention has a considerably higher resonance frequency than the prior art devices. This may be a very important advantage, especially if the rolling process has a high strip speed. DESCRIPTION OF THE PREFERRED EMBODIMENTS
A preferred embodiment of a radial force transducer accor¬ ding to the invention is shown in Figure 2. The radial force transducer comprises an inner ring 1 with the internal hole for the shaft of the deflector roll and an outer ring 2 whose inside diameter is larger than the outside diameter of the inner ring. The two rings are interconnected by means of two diametrically located spokes 6a and 6b. The cable clamp- shaped space remaining between the rings is clear from both Figures 2 and 3. The largely plane foot regions 7a, 7b and 8a, 8b form the edges of the spokes. The foot regions of the cable clamp-shaped space are then interconnected via the tubular and semicircular hollow spaces 5a and 5b between the two rings. In this embodiment, the outer ring 2 will there¬ fore, towards the cable clamp-shaped hollow spaces, have the shape of two ring halves 2a and 2b with the fixing holes 14, 15, 16 and 17. The direction of the measurement force is indicated in the figure by the arrow Fm and the direction of any transverse forces is indicated by the arrow Ft•
The shaft of the deflector roll may be rotating or non- rotating. When the shaft is rotating, a bearing is mounted in the hole of the inner ring. When the shaft is non- rotating, the hole of the inner ring may have other embodi¬ ments.
The spokes are provided with specially designed measuring regions for the principle of magnetoelastic measurement used. The measuring regions therefore comprise diaphragms 18a and 18b which constitute the magnetoelastic core of the used force transducers. The diaphragms in an embodiment according to Figure 2 have been achieved by providing recesses in the spokes such that circular diaphragms are formed. Figure 2 also shows the holes provided in the diaphragms for the excitation and measurement windings. Spokes and measuring regions can be designed in a plurality of different ways within the scope of the invention. A further example is shown in Figure 3. In regions between the hollow spaces 7a-8a and 7b-8b, two gaps 19, 20 and 21, 22, respectively, have been provided towards the foot region of the cable clamp-shaped space. This results in the creation of two beams 23, 24 and 25, 26, respectively, towards the hollow spaces. According to this embodiment, the diaphragms of the magnetoelastic force transducers will therefore con- sist of the rectangular regions 27a and 27b between the gaps. An important advantage with this embodiment is that the transducers become stiff against any moments introduced by the deflector roll. In addition, by introducing these gaps between diaphragms and beams, a better separation is obtained between the forces acting on the diaphragms and the transverse force-absorbing beams. This reduces the influence of transverse forces on the measurement result.
To achieve the same effect with an embodiment according to Figure 2, the measuring regions can be provided with corre¬ sponding gaps also in this case.
The magnitude of the measurement force is dependent on the stress level in the measuring zone. To be able to measure small forces, a third example of an embodiment of a measu¬ ring zone according to Figure 4 can be used. Here, two of the winding holes have been combined with the somewhat en¬ larged gaps 28a, 29a and 28b, 29b, respectively, in relation to those shown in Figure 3. For this reason, the measuring zones 30 and 31 will have the appearance of thin beams with the two holes 32a, 33a and 32b, 33b, respectively.
Common for all the embodiments is that they are symmetrical in relation to all planes which can be defined on the basis of previously defined x-, y- and z-directions, that is, the y-z plane, the x-z plane and the x-y plane. The symmetry in relation to the y-z plane means that the transducer can be loaded by a measurement force FM to the same extent in posi- tive and in negative direction, and the symmetry in the x-z plane means that the transducer can be loaded by a trans¬ verse force FT to the same extent in positive and in nega¬ tive transverse force direction. Finally, the symmetry in the x-y plane causes the transducer to become insensitive to a force in the direction of the shaft.
This symmetry in combination with two measuring zones also entails the important advantage relative to the prior art that forces which are no measurement forces do not influence the measurement.

Claims

1. A radial force transducer comprising an inner ring (1) with a hole for a shaft (3) and an outer ring (2) whose inside diameter is larger than the outside diameter of the inner ring, characterized in that the rings are inter¬ connected by means of two diametrically located spokes (6a, 6b) arranged with measuring regions adapted for radial force measurement with magnetoelastic transducers.
2. A radial force transducer according to claim 1, characterized in that its measurement direction FM, defi¬ ning an x-direction, is perpendicular to a plane determined by a line through the centre of the radial force transducer and through the centre of the spokes, defining a y-direc- tion, as well as by a line through the centre of the radial force transducer and through the centre line of the shaft defining a z-direction.
3. A radial force transducer according to claims 1 and 2, characterized in that it is symmetrical around the planes which are defined by the x-z, y-z and x-y directions.
4. A radial force transducer according to claim 1, characterized in that a bearing (4) is mounted in the hole of the inner ring for accomodating the shaft.
5. A radial force transducer according to claim 1, characterized in that the remaining hollow space between the two rings is shaped as a cable clamp and that the foot region (7a, 7b, 8a, 8b) of the cable clamp-shaped hollow space forms the edges of the spokes.
6. A radial force transducer according to claim 1, characterized in that the measuring regions of the spokes comprise circular diaphragms (18a, 18b) which constitute the core of the magnetoelastic transducers and are arranged with holes for both excitation and measurement windings.
7. A radial force transducer according to claim 1, characterized in that the measuring regions of the spokes comprise rectangular diaphragms (27a, 27b) which constitute the core of the magnetolelastic transducers and are arranged with holes for both excitation and measurement windings.
8. A radial force transducer according to claim 1, characterized in that the measuring regions of the spokes comprise gaps (19, 20, 21, 22) arranged between the diaph- ragms and the edges of the spokes.
9., A radial force transducer according to claims 1 and 6, characterized in that in the rectangular diaphragms between the gaps, only holes (32a, 32b, 33a, 33b) for the measurement windings of the magnetoelastic transducers are provided.
10. A radial force transducer according to claim 1, characterized in that the outer ring is arranged with holes (14, 15, 16, 17) for external fixing and that the measurement force is applied to the inner ring.
11. A radial force transducer according to claim 1, characterized in that the inner ring is arranged with holes for internal fixing and that the measurement force is applied to the outer ring.
12. A radial force transducer according to claims 1 and 9, characterized in that the measurement force applied to the outer ring is transferred via a bearing arranged around the outer ring.
PCT/SE1993/000711 1992-09-24 1993-08-30 Circular radial force transducer WO1994007118A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE9202755-6 1992-09-24
SE9202755A SE9202755L (en) 1992-09-24 1992-09-24 Round radial force meter

Publications (1)

Publication Number Publication Date
WO1994007118A1 true WO1994007118A1 (en) 1994-03-31

Family

ID=20387256

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/SE1993/000711 WO1994007118A1 (en) 1992-09-24 1993-08-30 Circular radial force transducer

Country Status (2)

Country Link
SE (1) SE9202755L (en)
WO (1) WO1994007118A1 (en)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2733592A1 (en) * 1995-04-25 1996-10-31 Abs Pump Prod Ab METHOD FOR DETERMINING THE INSTANTANEOUS WORKING CONDITIONS OF A CENTRIFUGAL PUMP
DE19623741A1 (en) * 1996-06-14 1997-12-18 Wittenstein Motion Contr Gmbh Device for recording and evaluating the operating force acting on a spindle drive
WO2004027366A1 (en) * 2002-09-20 2004-04-01 Ecole Polytechnique Federale De Lausanne (Epfl) Device for measuring the amplitude of a force produced on an axis and a vehicle provided with said device
WO2012080570A1 (en) * 2010-12-13 2012-06-21 Konecranes Plc Arrangement for measuring radial forces in bearing
WO2015145313A1 (en) 2014-03-28 2015-10-01 Consiglio Nazionale Delle Ricerche Transducer of radial forces, in particular for rotating shafts
WO2019115513A3 (en) * 2017-12-11 2019-08-29 Otto Bock Healthcare Products Gmbh Linear force-measuring device and hydraulic actuator

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3258962A (en) * 1963-02-14 1966-07-05 Asea Ab Magneto-elastic force measuring device
GB1146656A (en) * 1965-07-13 1969-03-26 Asea Ab Strip tension measuring device in a strip mill
DE2729699A1 (en) * 1977-06-07 1978-12-21 Heinrich Gruenbaum Measurement of radial force acting on bearing - using double ring linked with strain-gauge carrying arms
CH631013A5 (en) * 1978-09-20 1982-07-15 Schmid Roost J Sro Kugellagerw MEASURING DEVICE.
WO1989008826A1 (en) * 1988-03-10 1989-09-21 Stefan Valdemarsson Device for measuring and/or registering mechanical forces, and a method of manufacturing a measuring body for use in the device
DE3838810A1 (en) * 1988-11-17 1990-05-23 Inova Vyzkumny A Vyvojovy Podn Measuring element of a loading transmitter for testing machines
EP0376019A1 (en) * 1988-12-21 1990-07-04 Siemag Transplan Gmbh Cable load measuring device

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3258962A (en) * 1963-02-14 1966-07-05 Asea Ab Magneto-elastic force measuring device
GB1146656A (en) * 1965-07-13 1969-03-26 Asea Ab Strip tension measuring device in a strip mill
DE2729699A1 (en) * 1977-06-07 1978-12-21 Heinrich Gruenbaum Measurement of radial force acting on bearing - using double ring linked with strain-gauge carrying arms
CH631013A5 (en) * 1978-09-20 1982-07-15 Schmid Roost J Sro Kugellagerw MEASURING DEVICE.
WO1989008826A1 (en) * 1988-03-10 1989-09-21 Stefan Valdemarsson Device for measuring and/or registering mechanical forces, and a method of manufacturing a measuring body for use in the device
DE3838810A1 (en) * 1988-11-17 1990-05-23 Inova Vyzkumny A Vyvojovy Podn Measuring element of a loading transmitter for testing machines
EP0376019A1 (en) * 1988-12-21 1990-07-04 Siemag Transplan Gmbh Cable load measuring device

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2733592A1 (en) * 1995-04-25 1996-10-31 Abs Pump Prod Ab METHOD FOR DETERMINING THE INSTANTANEOUS WORKING CONDITIONS OF A CENTRIFUGAL PUMP
DE19623741A1 (en) * 1996-06-14 1997-12-18 Wittenstein Motion Contr Gmbh Device for recording and evaluating the operating force acting on a spindle drive
WO1997047953A1 (en) * 1996-06-14 1997-12-18 Wittenstein Motion Control Gmbh Device for detecting and evaluating the motive power acting on a linear drive
US6189391B1 (en) 1996-06-14 2001-02-20 Wittenstein Motion Control Gmbh Linear drive having a device for sensing and evaluating an operational force acting thereon
WO2004027366A1 (en) * 2002-09-20 2004-04-01 Ecole Polytechnique Federale De Lausanne (Epfl) Device for measuring the amplitude of a force produced on an axis and a vehicle provided with said device
WO2012080570A1 (en) * 2010-12-13 2012-06-21 Konecranes Plc Arrangement for measuring radial forces in bearing
WO2015145313A1 (en) 2014-03-28 2015-10-01 Consiglio Nazionale Delle Ricerche Transducer of radial forces, in particular for rotating shafts
WO2019115513A3 (en) * 2017-12-11 2019-08-29 Otto Bock Healthcare Products Gmbh Linear force-measuring device and hydraulic actuator
US11872145B2 (en) 2017-12-11 2024-01-16 Otto Bock Healthcare Products Gmbh Linear force-measuring device and hydraulic actuator

Also Published As

Publication number Publication date
SE9202755D0 (en) 1992-09-24
SE9202755L (en) 1993-11-15

Similar Documents

Publication Publication Date Title
US4864851A (en) Sensor and system for continuous determination of sheet strength
FI80522B (en) FOERFARANDE OCH ANORDNING FOER MAETNING AV SPAENNINGEN I EN BANA.
US3031152A (en) Improved apparatus for measuring, indicating, and controlling web tension
EP1468258B1 (en) Method of manufacturing a high sensitivity fibre optic vibration sensing device
US4530245A (en) Strain measuring apparatus and method of making same
WO1994007118A1 (en) Circular radial force transducer
US4784004A (en) Web tension transducer
US6422096B1 (en) Load cell
US5925832A (en) Torsional sensing load cell
US7612886B2 (en) Fiber-optic seismic sensor
USRE31312E (en) Tension monitor means
EP0501351A2 (en) Load cell
US4453422A (en) Strain gage load cell having improved sensitivity
JPS63106556A (en) Device and method of determining strength of sheet material
EP1247081A1 (en) Load cell
CA2815715C (en) Roll arrangement
US5837910A (en) Method and a device for two-shaft force measurement and its application to the determination of tensile force in a continuous web
US3866157A (en) Load cell
GB2052078A (en) Load Cell
US5394756A (en) Three-dimensional magnetoelastic force transducer
US20150101413A1 (en) Microelectromechanical pressure sensors
US2837620A (en) Strain gauges and load weighing cells
US4936149A (en) Internal strain measuring system
US20030144119A1 (en) Measuring sensor in a paper machine
US6786444B2 (en) Web winding method and apparatus and contact roller thereof

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): JP US

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): AT BE CH DE DK ES FR GB GR IE IT LU MC NL PT SE

DFPE Request for preliminary examination filed prior to expiration of 19th month from priority date (pct application filed before 20040101)
121 Ep: the epo has been informed by wipo that ep was designated in this application
122 Ep: pct application non-entry in european phase