WO2011107070A1 - Arbre de mesure de couple - Google Patents

Arbre de mesure de couple Download PDF

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Publication number
WO2011107070A1
WO2011107070A1 PCT/DE2011/000170 DE2011000170W WO2011107070A1 WO 2011107070 A1 WO2011107070 A1 WO 2011107070A1 DE 2011000170 W DE2011000170 W DE 2011000170W WO 2011107070 A1 WO2011107070 A1 WO 2011107070A1
Authority
WO
WIPO (PCT)
Prior art keywords
torque
measuring
measuring shaft
torque measuring
spring
Prior art date
Application number
PCT/DE2011/000170
Other languages
German (de)
English (en)
Inventor
Herbert Meuter
Ulrich Rohs
Original Assignee
GIF Gesellschaft für Industrieforschung mbH
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 GIF Gesellschaft für Industrieforschung mbH filed Critical GIF Gesellschaft für Industrieforschung mbH
Priority to DE112011100722T priority Critical patent/DE112011100722A5/de
Publication of WO2011107070A1 publication Critical patent/WO2011107070A1/fr

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Classifications

    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
    • G01L3/00—Measuring torque, work, mechanical power, or mechanical efficiency, in general
    • G01L3/02—Rotary-transmission dynamometers
    • G01L3/04—Rotary-transmission dynamometers wherein the torque-transmitting element comprises a torsionally-flexible shaft
    • G01L3/10—Rotary-transmission dynamometers wherein the torque-transmitting element comprises a torsionally-flexible shaft involving electric or magnetic means for indicating
    • G01L3/108—Rotary-transmission dynamometers wherein the torque-transmitting element comprises a torsionally-flexible shaft involving electric or magnetic means for indicating involving resistance strain gauges
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
    • G01L3/00—Measuring torque, work, mechanical power, or mechanical efficiency, in general
    • G01L3/02—Rotary-transmission dynamometers
    • G01L3/14—Rotary-transmission dynamometers wherein the torque-transmitting element is other than a torsionally-flexible shaft
    • G01L3/1407—Rotary-transmission dynamometers wherein the torque-transmitting element is other than a torsionally-flexible shaft involving springs
    • G01L3/1428—Rotary-transmission dynamometers wherein the torque-transmitting element is other than a torsionally-flexible shaft involving springs using electrical transducers
    • G01L3/1457—Rotary-transmission dynamometers wherein the torque-transmitting element is other than a torsionally-flexible shaft involving springs using electrical transducers involving resistance strain gauges

Definitions

  • the invention relates to a torque measuring shaft.
  • AI torque measuring shafts which have cylindrical shaft sections, in which pocket-shaped recesses or membranes are incorporated and in which strain gauges (DMS) for measuring a voltage proportional to the applied torque be applied in this membrane.
  • Torque shafts according to this prior art usually have a defined linear measuring range and are designed for a specific maximum torque applied to the torque measuring shaft.
  • a disadvantageous side effect of a torque measuring shaft designed for a large measuring range was the fact that in the range of very small torques to be measured, the resolution of the electrical or electronic signal generated via the strain gauge is very small.
  • torque measuring shafts for example from DE 10 2007 005 894 A1
  • diaphragms with different, preferably two, wall thicknesses are formed.
  • sensors with different sensitivities are available in accordance with the applied torque and the angle of rotation associated therewith.
  • the disadvantage of such torque measuring waves is the fact that, at high angles of rotation, the thinner and more sensitive diaphragms are likewise further loaded when the load or the applied torque is further increased.
  • the membranes set aside for small measuring ranges can be subjected to an excessive load, whereby these membranes may already be plastically stretched and a reproducible measurement of the applied torque is no longer possible.
  • a torque measuring shaft is proposed, which is characterized by at least two measuring ranges, a first measuring range with a high sensitivity and a low torsional stiffness and a second measuring range with a low sensitivity and a high torsional stiffness.
  • the advantage of this proposed torque measuring shaft is that the torque measuring shaft has two measuring ranges with different torsional stiffnesses, whereby the torsion angle occurring at the torque measuring shaft is limited and thus the first measuring range with the high sensitivity is no longer loaded unduly high.
  • the means for detecting the torque which may consist of resilient elements or membranes, are designed for the respectively intended measuring range.
  • the design can then be such that the resilient elements can each have linear characteristics and are not claimed in a non-linear or plastic range.
  • torque measuring shafts have resilient elements that allow under torque movement, which then ultimately lead to a proportional to the torque measurement signal. These spring-acting elements will ultimately have non-linear characteristics, which - at least before a break - rise sharply.
  • the measuring ranges of such torque measuring shafts are designed for such small rotational angles that these regions of the resilient elements are not reached.
  • a linear relationship between torque and measurement signal can be assumed, which can then be used for example by a corresponding equation for interpolation purposes.
  • the loads on the resilient elements occurring in the two measuring ranges are proportional, preferably linearly proportional, to a torque applied to the torque measuring shaft. Since the applied torque to the torque measuring shaft generates a torque angle or torsion angle proportional to this torque, it is further proposed that the torque measuring shaft be exceeded by means for increasing the rotational stiffness when a defined rotational angle is exceeded is, excels.
  • the first measuring range can be delimited to the second measuring range by using a defined angle of rotation for demarcation and, on the other hand, starting from this defined rotational angle, the rotational stiffness is increased to such an extent that the means for measuring the torque in the first measuring range not be exposed to an unduly high load.
  • the torsional rigidity increasing means comprise a stop.
  • the entire measuring range can be divided into two measuring ranges, wherein preferably the first measuring range has a linear characteristic and the second measuring range has a linear characteristic and thus the entire measuring range has an overall characteristic with partially linear dependencies.
  • the torsional stiffness increasing means comprise a plant.
  • a system as a torsional stiffness enhancer has the advantage that the change in the overall characteristic of the torque shaft may have a steady course, wherein the dependence of the rotational angle of the applied torque no longer necessarily have to have a linear course.
  • the profile of the angle of rotation of the applied torque in a range of smaller torques can have a high sensitivity and thus a high rotational angle change as a function of the torque change and in a second measuring range for higher torques have a smaller rotational angle change in response to the torque change.
  • the term "two measuring ranges with different torsional stiffness" in the present context does not necessarily have to provide a discontinuous transition between the two measuring ranges, as will usually be the case in a stop.
  • the invention proposes a torque measuring shaft, which is characterized by at least one arranged between two flanges spring element with an effective spring length and means for changing the spring length in response to the rotation angle to provide different measuring ranges.
  • This solution has the advantage that the rotation angle of the torque measuring shaft, in contrast to the above solution or other known solutions is no longer dependent only on the torsional stiffness of the torque measuring shaft, but that the torque dependent on the rotational angle of the torque measuring shaft is a function of can be free spring length of a spring element, in which case the spring stiffness of this spring element can remain substantially constant over the entire measuring range.
  • the change of the spring length can be made depending on the specific requirements substantially continuously or even at certain points discontinuous.
  • a torque measuring shaft is accordingly proposed, which is characterized in that the spring length is shortened with increasing angle of rotation.
  • This has the advantage that the rotation angle change in a measurement range with low torque has a higher sensitivity to a torque change and that the rotation angle change in a measurement range with higher torque has a lower sensitivity to a torque increase.
  • the spring stiffness does not have to remain constant over the length of the spring. It is also possible, for example, the use of a spring with variable torsional or bending stiffness as a function of the free spring length.
  • the object of the present invention is also achieved by a torque measuring shaft, which is characterized by a centrally disposed between two flanges and a measuring rod by a radially outside of the measuring rod between the flanges effective spring arrangement.
  • a torque measuring shaft can advantageously be provided in which the means for measuring the angle of rotation are provided independently of the means for generating a torque-rotational angle characteristic.
  • the means for measuring the angle of rotation are provided independently of the means for generating a torque-rotational angle characteristic.
  • the torque / rotation angle characteristic curve can be selected such that the transducers can operate optimally.
  • the radially inner arrangement of the measuring rod has the advantage that the load on the transducers on the one hand by small Verwarn, due to the small radius on which the Measurements must be effective, and on the other hand by low centrifugal forces, also due to the small radius can be minimized.
  • the spring arrangement comprises at least two axially aligned spring elements.
  • This implements the advantage that the spring elements used can be distributed uniformly on the circumference, so that by the torsion of the torque measuring shaft no skewed bend outside the axis of symmetry, on the torque measuring shaft itself, can arise, and so that the spring elements by their axial orientation as Bending springs can be used with a linear in a large range spring characteristic.
  • torque measuring shafts according to the prior art generally use a cylindrical tube which is subjected to torsion.
  • the measuring rod itself also influences the torque / rotation angle characteristic or is correspondingly resiliently resetting accordingly.
  • this influence can be determined as desired by the suitable choice of the springs and by the relatively small radius of the measuring rod.
  • this torque measuring shaft can have a circumferential direction with at least one spring element arranged system.
  • the axially aligned spring rest against the system such that by means of the system, the free spring length of the spring, instead of the bending or torsional stiffness of the spring, is changed.
  • beam springs can be used as spring elements.
  • This embodiment offers the further advantage that in a torque measuring shaft with axially arranged spring elements, which are pronounced as bar springs, preferably uniaxial tensile or compressive stresses occur instead of possibly multiaxial stresses.
  • the mechanical characteristic of the torque measuring shaft can be favorably influenced, which in turn increases the accuracy of the torque measuring shaft as a whole, since electronic adjustment parameters no longer have to be used to the same extent as in torque measuring shafts according to the prior art.
  • the beam spring is radially wider than in the circumferential direction.
  • the torque measuring shaft can be designed very rigid in total constant torsional stiffness.
  • a torque measuring shaft is proposed, which is characterized by two flanges, which are arranged rotatable within the intended measuring range by more than 0.5 ° against each other. This has the advantage that the large rotation angle allows both a good resolution and a large measuring range, in particular if the characteristic of the torque measuring shaft increases sharply at larger angles of rotation, thus in particular also leaves the linear characteristic range.
  • a high resolution can be achieved in a lower measuring range by means of a large gradient and higher torques can be measured in an upper measuring range, in which the further rotation of the shaft is limited due to a smaller gradient of the characteristic.
  • Figure 1 shows a first torque measuring shaft in a schematic view in which a first measuring rod is more sensitive and is bridged from a certain angle of rotation, by stops over the entire spring length is shortened;
  • Figure 2 shows a second torque measuring shaft in a schematic view in which a first measuring rod is more sensitive and is bridged from a certain angle of rotation by stops over the entire spring length is shortened;
  • Figure 3 is a spring characteristic (torque angle of rotation) of the measuring rods of the second
  • FIG. 4 shows a third rotary measuring measuring shaft in a schematic view, in which a
  • Measuring rod is more sensitive than a measuring sleeve and is bridged at a certain angle of rotation, by stops the entire spring length is shortened;
  • Figure 5 is a spring characteristic (torque angle of rotation) of the dipstick and the
  • FIG. 6 shows a fourth torque measuring shaft in a schematic view, in which a centrally arranged measuring rod and externally arranged, first from a certain angle of rotation via stops effective spring rods are provided;
  • FIG. 7 shows a spring characteristic (torque angle of rotation) of the fourth torque measuring shaft
  • FIG. 8 shows a fifth torque measuring shaft in a schematic view, in which a centrally arranged measuring rod as well as externally arranged, at a certain angle of rotation via stops influenced spring rods are provided, which run against equipment;
  • FIG. 9 shows a spring characteristic (torque angle of rotation) of the fifth torque measuring shaft
  • FIG. 10 shows a sixth torque measuring shaft in a schematic view in which a centrally arranged measuring rod and externally arranged round spring rods are provided, which run against systems which are already arranged very close to the spring rods.
  • Figure 1 shows a torque measuring shaft 10 with a flange 1 1 and a flange 12 by means of which the torque measuring shaft 10 can be integrated in an existing drive train.
  • the torque measuring shaft 10 shown also has an intermediate flange 15 and a further intermediate flange 16, which divides the overall arrangement into two subregions.
  • a first measuring rod 13 is arranged in a first portion of the torque measuring shaft 10, between the flange 1 1 and the intermediate flange 16, a first measuring rod 13 is arranged.
  • This first measuring rod 13 has a substantially smaller diameter than the second measuring rod 14 located in the second partial region of the torque measuring shaft 10. Accordingly, the smaller diameter of the first measuring rod 13 provides a higher sensitivity to torque on the first measuring rod 13, as a result of which preferably small sensors are provided on this measuring rod Torques with high resolution can be measured.
  • the stops 17 and 18 which rest upon reaching a defined angle of rotation to each other, so that a rotation of the first measuring rod 13 is prevented in a further increase in torque and thus the first portion of the torque measuring shaft 10 between the flange 1 1 and the Intermediate flange 16 has a substantially higher, preferably infinitely high, torsional stiffness than the second portion of the torque measuring shaft 10 between the flange 12 and the intermediate flange 15.
  • the second portion of the torque measuring shaft 10 between the flange 12 and the intermediate flange 15 has by the second measuring rod 14, which has a substantially larger diameter than the measuring rod 13, a relation to the first measuring rod 13 substantially higher torsional rigidity. Due to this higher torsional rigidity of the second measuring rod 14, the second portion of the torque measuring shaft 10 is suitable for measuring high torques at a low resolution.
  • the second portion of the torque measuring shaft 10 between the flange 12 and the intermediate flange 15 thus has a linear over the entire measuring range characteristic curve, by means of which the rotation angle is related to the applied torque.
  • FIG. 2 shows a torque measuring shaft 20 as a further embodiment with a flange 21 and a flange 22, by means of which the torque measuring shaft 20 can be inserted in an existing drive train.
  • a first measuring rod 23 and a second measuring rod 24 which merge into one another and thus represent two series-connected torsion springs.
  • the torque measuring shaft 20 or the second measuring rod 24 has an intermediate piece 26, which in turn is connected to an intermediate flange 25.
  • the flange 21 includes a plurality of stops 27, to which the intermediate flange 25 can strike, provided that a corresponding angle of rotation between the flanges 21 and 22 of the torque measuring shaft 20 is present.
  • the measuring rods 23 and 24 are rotated on the torque measuring shaft 20 with an applied torque in linear dependence on the applied torque.
  • the measuring rod 23 has a much smaller diameter than the measuring rod 24, whereby the measuring rod 23 has a much greater sensitivity to an applied torque, and the measuring rod 23 can be used for small torques at a very high measurement resolution. If a rotation of the torque measuring shaft 20 by a higher applied torque, the intermediate flange 25 abuts against the stop 27, whereby further rotation of the first measuring rod 23 is prevented and the entire applied torque only over the second dipstick 24 is passed. High torques are detected in this measuring range via the second measuring rod 24 and fed to a corresponding measuring device.
  • This torque measuring shaft 20 can also be designed in such a way that the characteristic curves of the individual measuring rods, of the first measuring rod 23 and of the second measuring rod 24, are embodied in sections linearly or proportionally to the applied torque.
  • FIG. 3 shows a characteristic curve for a torque measuring shaft according to FIGS. 1 and 2.
  • the torsion angle ⁇ is plotted against the applied torque T.
  • the first measuring rod 23 has a characteristic curve 23A divided into two sections, in which the first section has a very high gradient, ie a high sensitivity to an applied torque, and a gradient of 0 in a second partial section. It is clear that the first measuring rod 23 is not further loaded from a certain applied torque and thus the measuring device located on this dipstick is not subjected to overloading.
  • the measuring rod 24 has a characteristic curve 24A which, although having a substantially lower slope, that is to say a substantially lower sensitivity to torque, is also suitable for measuring high torques.
  • the characteristic curve 24A of the second measuring rod 24 runs continuously and linearly over the entire measuring range.
  • FIG. 4 shows a torque measuring shaft 30 with a flange 31 and a flange 32, by means of which the torque measuring shaft 30 can be integrated into an existing drive train.
  • the flange 31 is operatively connected to a measuring sleeve 34, which in turn has stops 37 and opens into the second flange 32 by means of these.
  • a measuring sleeve 34 which in turn has stops 37 and opens into the second flange 32 by means of these.
  • an intermediate piece 36 is further connected, which has an intermediate flange 35 at its end opposite the stop 37.
  • the torque measuring shaft 30 also has a measuring rod 33 which effectively connects the intermediate flange 35 and the flange 32.
  • the measuring rod 33 is, similar to the previous embodiments, intended to measure a small torque applied to the torque measuring shaft 30 over the rotation angle caused by this torque.
  • the measuring rod 33 is further connected via the flange 35 and the intermediate piece 36 in series with the measuring sleeve 34. Now reaches the torque applied to the torque measuring shaft 30 a defined Value, the stop 37 abuts against the flange 32, whereby the measuring rod 33 is bridged and the applied torque is transmitted only via the measuring sleeve 30.
  • the torque measuring shaft 30 shown in this figure also has two measuring ranges, wherein a first measuring range has a characteristic curve with a high gradient for low torques at a high measuring resolution and a second measuring range has a characteristic curve with a low gradient, ie also a lower sensitivity has high torques.
  • the dependencies of the angles of rotation of the measuring rod 33 and the measuring sleeve 34 with respect to the torque applied to the torque measuring shaft 30 are shown in the diagram shown in FIG.
  • the characteristic curve 33A is associated with the measuring rod 33, in which a first region with a high sensitivity to torque and a second region with a non-increasing rotation angle can be seen.
  • the measuring rod 33 is preferably used for a measurement of low applied torques.
  • the measuring range for high torques is represented by the characteristic 34A associated with measuring sleeve 34.
  • the characteristic curve 34A in contrast to the characteristic curve 33A, has a gradient which is lower than the one of a certain torque, but which is generally continuous, and which runs linearly over the entire measuring range.
  • the measuring sleeve 34 thus has, similar to the embodiments explained above, a large torque measuring range at a low resolution, in which case both partial characteristics 33A and 33B are additively superimposed.
  • FIG. 6 Another torque measuring shaft 40 is shown in Figure 6, which in turn has a flange 41 and a flange 42, by means of which the torque measuring shaft 40 can be integrated into an existing drive train.
  • the torque measuring shaft 40 includes only a single central measuring rod 43.
  • the central measuring rod 43 connects directly the flange 41 with the flange 42 and thus measures the entire torque applied to the torque measuring shaft 40.
  • the torque measuring shaft 40 also has spring bars 48 arranged axially relative to the torque measuring shaft.
  • the spring rods 48 are arranged radially on the outside of the torque measuring shaft 40 and each have a stop 47, which engage in the flange 42.
  • FIG. 7 shows by way of example a characteristic curve 40A of the torque measuring shaft 40.
  • a first subregion is visible, in which the slope, ie the sensitivity of the torque measuring shaft to torque, is very high and a second subregion in which the sensitivity is due to the low Slope is lower.
  • the entire measuring range can be represented by a characteristic curve, since only one measuring transducer is used in the torque measuring shaft 40.
  • no device for superimposing or evaluating two individual measured values is required.
  • the possibility of erroneous measurement is reduced, since a shift or drift of the measured value and thus a necessary calibration of the torque measuring shaft 40 is only required at a measuring device.
  • the torque measuring shaft 50 is shown with the flange 51 and flange 52, by means of which the torque measuring shaft can be integrated into an existing drive train.
  • a central measuring rod 53 Between the flange 51 and the flange 52 there is in turn a central measuring rod 53, which actively connects the flange 52 and the flange 51 and detects the entire torque applied to the torque measuring shaft 50.
  • These torque measuring shaft 50 also has axial and parallel to the central measuring rod 53 arranged spring rods 58, which are also disposed between the flange 51 and the flange 52, and on the voltage applied to the torque measuring shaft 50 torque against a torsional resistance.
  • the acting as a beam spring spring rods 58 bend under an applied torque and start with increasing deformation of the system 59.
  • the spring bars 58 Due to the gradual contact with the system 59, the spring bars 58 experience a shortening of their effective spring length, which leads to a stiffening of the torque Measuring shaft 50 is coming. The rising with increasing applied torque stiffening of the torque measuring shaft 50 has a degressive rotational angle-torque characteristic of the torque measuring shaft 50 result. Since the spring rods 58 have a small distance to the systems 59 in a relaxed state, these systems 59 initially form stops at the moment in which a first contact occurs. The relatively small distance and the low angle at which this contact takes place require that the slope at this point changes only slightly discontinuous.
  • FIG. 9 shows a diagram with a characteristic curve 50A of the torque measuring shaft 50. It becomes clear that with a very small applied torque T, the characteristic curve of the torque measuring shaft 50 has a high pitch and by means of this a high resolution of the rotational angle ⁇ is possible. With increasing applied torque T, the sensitivity of the torque measuring shaft gradually decreases due to the falling slope of the characteristic 50A. The degressive change of the characteristic curve 50A thus has a continuous characteristic in contrast to the previous embodiments.
  • FIG. 10 shows a further embodiment of a torque measuring shaft according to the invention. The torque measuring shaft 50 shown has, as the embodiments described above, a flange 61 and a flange 62 for integrating the torque measuring shaft 60 in a drive strnature on.
  • the measuring rod 63, the spring rods 68 and the system body 69B are arranged axially to the axis of rotation of the torque measuring shaft.
  • the spring bars 68 which are arranged in a radially outer region of the torque measuring shaft 60, deform under a force acting tangentially to the axis of the torque measuring shaft 60 and cause by their resistance to bending of the torque measuring shaft 60 associated characteristic. [40] Due to the resulting deformation of the spring rods resulting from the applied torque, these begin to apply to the systems 69, which are arranged on an outer surface of the system body 69B. This results in a shortening of the free spring length of the spring rods 68 and consequently a stiffening of the entire torque measuring shaft 60, whereby • the characteristic curve shown in Figure 9 results. LIST OF REFERENCE NUMBERS

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)
  • Investigating Strength Of Materials By Application Of Mechanical Stress (AREA)

Abstract

L'invention concerne un arbre de mesure de couple qui, d'une part, permet une grande sensibilité de mesure pour une grande largeur de bande et, d'autre part, est configuré de manière à préserver les matériaux. Ledit arbre comporte au moins deux plages de mesure, une première plage de mesure présentant une haute sensibilité et une faible rigidité à la torsion, et une seconde plage de mesure présentant une faible sensibilité et une haute rigidité à la torsion.
PCT/DE2011/000170 2010-03-03 2011-02-22 Arbre de mesure de couple WO2011107070A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112011100722T DE112011100722A5 (de) 2010-03-03 2011-02-22 Drehmomentmesswelle

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102010010232 2010-03-03
DE102010010232.6 2010-03-03
DE102010034638.1 2010-08-17
DE102010034638A DE102010034638A1 (de) 2010-03-03 2010-08-17 Drehmomentmesswelle

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WO2011107070A1 true WO2011107070A1 (fr) 2011-09-09

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PCT/DE2011/000170 WO2011107070A1 (fr) 2010-03-03 2011-02-22 Arbre de mesure de couple

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DE (2) DE102010034638A1 (fr)
WO (1) WO2011107070A1 (fr)

Cited By (4)

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WO2012093134A1 (fr) * 2011-01-05 2012-07-12 Avl List Gmbh Dispositif de mesure de couple
DE102011116561A1 (de) 2011-03-11 2012-09-13 GIF Gesellschaft für Industrieforschung mbH Drehmomentmesswelle und Verfahren zur Messung eines Drehmomentes
DE102013005967A1 (de) 2012-05-18 2013-11-21 GIF Gesellschaft für Industrieforschung mbH Drehmomentmesseinrichtung bzw. -vorrichtung
US9857254B2 (en) 2012-05-18 2018-01-02 Atesteo Gmbh Torque-measuring device or jig

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DE102014201450A1 (de) 2013-02-21 2014-08-21 Ford Global Technologies, Llc Kraftfahrzeug-Lenkvorrichtung und Verfahren zum Erfassen eines Lenkmoments
AT513125B1 (de) * 2013-10-31 2015-05-15 Avl List Gmbh Messerweiterung in Wellenverbänden
DE102014017410A1 (de) 2014-11-06 2016-05-12 GIF Gesellschaft für Industrieforschung mbH Drehmomentmesswelle
DE202014105432U1 (de) 2014-11-12 2016-01-25 Kuka Systems Gmbh Pressschweißvorrichtung
DE102017004378A1 (de) * 2017-05-05 2018-11-08 Hottinger Baldwin Messtechnik Gmbh Doppelflansch-Drehmomentaufnehmer
DE102017004587A1 (de) * 2017-05-12 2018-11-15 Hottinger Baldwin Messtechnik Gmbh Doppelflansch-Drehmomentaufnehmer mit Korrektursensorik
DE102017004680A1 (de) * 2017-05-16 2018-11-22 Hottinger Baldwin Messtechnik Gmbh Doppelflansch-Drehmomentaufnehmer mit Korrektursensorik

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Publication number Priority date Publication date Assignee Title
US4503713A (en) * 1982-04-22 1985-03-12 Nippon Soken, Inc. Dual sensitivity torque detector
DE4009286A1 (de) 1990-03-22 1991-09-26 Wiegand Gmbh & Co Alexander Verfahren zum messen der torsion eines stabfoermigen koerpers sowie messelement zur durchfuehrung des verfahrens
EP0451613A1 (fr) * 1990-04-12 1991-10-16 Look S.A. Dispositif pour mesurer un couple moteur
EP1074826B1 (fr) 1999-08-02 2008-03-05 Hottinger Baldwin Messtechnik Gmbh Capteur de couple
US20020050177A1 (en) * 2000-11-02 2002-05-02 Hisashi Honjo Torque detector
DE102007005894A1 (de) 2006-06-14 2007-12-20 GIF Gesellschaft für Industrieforschung mbH Drehmomentmessflansch

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012093134A1 (fr) * 2011-01-05 2012-07-12 Avl List Gmbh Dispositif de mesure de couple
DE102011116561A1 (de) 2011-03-11 2012-09-13 GIF Gesellschaft für Industrieforschung mbH Drehmomentmesswelle und Verfahren zur Messung eines Drehmomentes
DE102013005967A1 (de) 2012-05-18 2013-11-21 GIF Gesellschaft für Industrieforschung mbH Drehmomentmesseinrichtung bzw. -vorrichtung
US9857254B2 (en) 2012-05-18 2018-01-02 Atesteo Gmbh Torque-measuring device or jig

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DE112011100722A5 (de) 2013-01-10

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