EP1623199A1 - Element dynamometrique - Google Patents

Element dynamometrique

Info

Publication number
EP1623199A1
EP1623199A1 EP04719910A EP04719910A EP1623199A1 EP 1623199 A1 EP1623199 A1 EP 1623199A1 EP 04719910 A EP04719910 A EP 04719910A EP 04719910 A EP04719910 A EP 04719910A EP 1623199 A1 EP1623199 A1 EP 1623199A1
Authority
EP
European Patent Office
Prior art keywords
force
measuring element
force measuring
element according
spring
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Withdrawn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
EP04719910A
Other languages
German (de)
English (en)
Inventor
Michael Munz
Kurt Weiblen
Andreas Stratmann
Anton Dukart
Helmut Grutzeck
Johann Wehrmann
Conrad Haeussermann
Klaus Kasten
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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
Priority claimed from DE10333992.2A external-priority patent/DE10333992B4/de
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1623199A1 publication Critical patent/EP1623199A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60N—SEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
    • B60N2/00—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles
    • B60N2/002—Seats provided with an occupancy detection means mounted therein or thereon
    • 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
    • G01L1/005—Measuring force or stress, in general by electrical means and not provided for in G01L1/06 - G01L1/22
    • 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
    • G01L1/04—Measuring force or stress, in general by measuring elastic deformation of gauges, e.g. of springs
    • G01L1/044—Measuring force or stress, in general by measuring elastic deformation of gauges, e.g. of springs of leaf springs
    • 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 invention is based on a force measuring element according to the type of the independent claim.
  • the advantage is that the bending element has a double bending beam, which realizes a spring shape for each beam, the double bending beam being clamped on one side and the force being introduced perpendicular to the longitudinal direction of the double bending beam.
  • the strain distribution is optimal under load in the direction of force measurement.
  • the design is also minimized.
  • the force measuring element is insensitive to destruction by loads that do not act in force measuring directions due to the selected shape.
  • the spring shape is designed so that the expansion distribution and force measurement direction is optimal. This means that a large deflection can be achieved without the material failing mechanically.
  • the elastic expansion limit or the fatigue strength can be used as a failure criterion.
  • the double bending beam can be made from square or rectangular or circular or semi-circular original materials.
  • the spring shape can be produced with an opening and with a wedge tapering towards the center of the spring.
  • the spring shape itself is optimized so that
  • the spring shape is designed in the form of a double wedge tapering towards the center, which causes an even distribution of the stretching maxima.
  • the shape of the connecting radii is adapted and represents a curve shape optimized in its distribution of expansion, which enables a particularly smooth transition from the highly stressed area to the slightly stretched original material.
  • the double wedge-shaped spring shape results in a very even distribution of the maximum strains acting in the spring area. In this way, in particular in the case of force measurement in which the deflection or the path is measured, a maximum path is achieved for a predetermined force without the elongation permissible in the material being exceeded.
  • the geometric parameters of the force measuring element must be coordinated. For example, finite element calculations can be used.
  • the external tapering can be omitted. It is essential that the spring tapers uniformly in the middle area. Slight deviations from the straight shape can bring about a further, if only slight improvement in the stress distribution. Transitions can also be adjusted accordingly. It is essential here that this shape approximately corresponds to an elliptical shape which merges into the spring or into the base of the original material with little or no change in the slope.
  • a displacement sensor is advantageously used as the measuring system.
  • the displacement sensor can advantageously be arranged in the pivot point of the tilting movement. This enables the sensor to be rotated only around the x-axis when the bending beam is loaded with a moment in the x-direction, but there is no deflection in the z-direction and therefore there is no undesired measurement signal when the bending beam is loaded with a torque around the x-axis.
  • the double bending beam itself enables the lateral forces Fx and Fy and the moments Mz and My to be suppressed, as it is considerably stiffer under these loads.
  • An inductive measurement can be used as the displacement sensor, for example by using a Hall element, it being possible to use a magnetic field generating reference and the Hall element as the magnetic field sensitive element. Alternatively, it is still possible to measure optically or capacitively.
  • the force can preferably be introduced via a sleeve. Otherwise, it is advantageous to apply the force at the end of the bending beam.
  • the displacement sensor can be guided from the bar ends to the optimal measuring location by means of rod-shaped extensions. However, it is also possible to guide the displacement sensor to the optimal measuring location via a fastening on the sleeve and a rod at the clamped beam start.
  • the embodiment of the bending beam can also be a different spring shape in the measuring principle, not necessarily a double spring, so that a single or three or more parallel springs are possible with this measuring principle according to the invention.
  • the described torque insensitivity to Mx also exists in these cases due to the selection of the optimal location for the position measuring system.
  • FIG. 1 shows a first schematic illustration of the force measuring element according to the invention
  • FIG. 2 shows a first schematic representation of the force measuring element according to the invention in perspective
  • FIG. 3 shows a second perspective illustration of the force measuring element
  • FIG. 4 different cross-sectional shapes of the force measuring element
  • FIG. 6 shows a shape of the transition of the spring shape
  • FIG. 7 shows a perspective view of the force measuring element with highlights of
  • FIG. 8 shows a further side view of the force measuring element with a displacement sensor
  • FIG. 9 shows a side view of the force measuring element with a sleeve
  • FIG. 10 shows a triple spring system
  • FIG. 11 shows a single spring system. description
  • strain gauges or piezoresistive structures for measuring the elongation of the bending element are applied, or the deflection of bending elements is recorded with path-measuring systems.
  • Known forms of the bending elements are s-shaped or rod-shaped elements. However, these elements have a constant cross section. A disadvantage of these shapes is the uneven distribution of strain under load in the measuring direction and the large design associated with this.
  • a spring shape which enables an optimal distribution of strain under load in the direction of force measurement. This minimizes the design, while in the other directions the force measuring element is insensitive to destruction by loads due to the selected shape.
  • the force measuring element is to be used in particular in motor vehicles.
  • use as weight measurement sensors in the vehicle seats is preferably intended.
  • FIG. 1 shows a side view of the force measuring element 14 according to the invention
  • Force measuring element 14 has an opening 16, which is surrounded in the longitudinal direction by two springs 12 and 13, which are bending beams here.
  • the force is introduced at the end of the bending beam at location 15 in the z direction.
  • 1 shows in a coordinate system that the z direction is transverse to the bending beam 14, while the longitudinal direction is represented by the y axis.
  • the double bending beam 14 is clamped on one side on a wall 17, for example by a joining technique or by a screw connection.
  • Two opposing half bars are arranged in the opening on which the measuring system 10 sits.
  • a displacement sensor is used here by way of example, in which, for example, a Hall sensor is used as the measuring element and a magnet as the reference. Other sensors are alternatively or additionally possible.
  • strain gauges include, for example, strain gauges.
  • FIG. 2 shows a schematic representation of the double bending beam according to the invention.
  • the double bending beam 21 is clamped in place 20, either as shown above by a thread or by material joining or by continuing the round material from which the bending beam is made.
  • the spring shapes 23 and 24 around the opening are wedge-shaped here and taper towards their center.
  • the double bending beam here has a circular cross section 22.
  • the displacement sensor arrangement is omitted here as well for the sake of simplicity.
  • Figure 3 shows a further schematic representation of the double bending beam according to the invention.
  • the double bending beam 30 is in turn clamped in place 31 and here has a rectangular or square cross section 32.
  • the spring shapes 34 and 35 are in turn arranged, which here also taper in a wedge shape towards the center.
  • Figure 4 captures the different cross sections for the double bending beam.
  • 4a shows the rectangular cross section, the square cross section being a special form of this cross section.
  • the circular cross section is indicated in FIG. 4b and the elliptical one in FIG. 4c.
  • Figure 4d is a semicircular
  • the cross section has arcs, but also straight boundary lines.
  • Figure 5a shows a further side view of the bending beam according to the invention. Another is also shown in Figure 5b. Through the side views are here
  • Axes of symmetry 50 drawn.
  • the shape of the spring is discussed and the parameters with which the spring shape is determined.
  • External tapers I and II as well as internal tapers III and IV are given here. These tapers run towards the center of the springs.
  • the center points on the upper spring are identified by R1 for the outer and R2 for the inner. Also the
  • Transitions 54, 55 in the corners of the opening 53 are optimized here in such a way that the stress distribution is distributed evenly.
  • the transitions are identified here with S1, S2, S3 and S4, the details in FIG. 6 being discussed.
  • Figure 5b shows the double bending beam again in the side view, with others here
  • Parameters for determining the double bending beam, especially the spring shape are specified.
  • dl the diameter of the spring is given at the thinnest point in the middle, where it has tapered to the maximum.
  • d2 denotes a diameter in the outer area of the spring, where it is as thick as possible.
  • ⁇ l denotes a taper angle as well as ⁇ 2.
  • the parameter hl shows the maximum distance from the inside of the opening at the thinnest point to the axis of symmetry.
  • Optimization takes place by means of an optimization on the computer, in particular with the aid of a finite element calculation.
  • FIG. 6 now shows the shape of the transition of the spring shape.
  • the transitions S1, S2, S3 and S4 are optimized in such a way that at point 60 the transition to the
  • the transition is optimized in such a way that at point 61 the transition into the spring, ie into the beam, also takes place without a slope jump. This results in an overall elliptical shape of the opening with the diameters A and B. The fact that an ellipse is formed requires the diameter A to be smaller than the diameter
  • the shape can be approximated mathematically as a spline, polynomial, parabolic, using two radii of different sizes, possibly with small straight lines in between, or directly as an elliptical function.
  • the design without a slope jump enables a space-saving design, since there are no stress concentrations due to excessive stretching.
  • FIG. 7 shows a perspective view of the double bending beam 70 with the stress distributions shown when a force has been introduced.
  • Force 71 is introduced at the end of the bending beam at the free end.
  • the bending beam is clamped on one side at location 74.
  • the point 73 shows an example of a transition from
  • FIG. 8 shows the independence of the double bending beam 80 when the moment is introduced around the x-axis, that is into the paper surface, since the bending beam moves in position 81 under this torque without an offset occurring at the measuring location 85. This is achieved through the appropriate positioning of the
  • Measurement site 85 reached.
  • the measuring location 85 is positioned by means of a rod 83 attached to the bar end in such a way that a momentary deflection at the bar end does not produce an offset at the measuring location. This means that the displacement sensor will not generate a signal in the breakthrough. There is therefore a decoupling from the moment Mx.
  • rod shapes instead of rod shapes, other structural shapes can also be selected, which ensure appropriate positioning of the measuring location.
  • the position of the tapered spring can be found using FEM simulations. For simple spring shapes, this can be done using analytical calculations.
  • Figure 9 shows a further embodiment in side view.
  • a sleeve is used here.
  • the double bending beam 90 here has an additional sleeve 92 for the introduction of force.
  • the force F 2 is applied to the sleeve region 93.
  • Force signals are independent of the position of the force Fz, as long as this is perpendicular to the Sleeve axis works. Of course, this only applies if the measuring location has been placed in the location using FEM or analytical calculations, which is insensitive to the moment M x replacement .
  • Figure 10 shows that the measuring principle with the displacement sensor also works with a triple spring.
  • the force Fz is applied to the bending beam at the free end.
  • the middle spring there is a free working of the displacement sensor 100 with the rods described in FIG. 8, which can be used here as well as with a simple spring, which is shown in FIG. 11.
  • the measuring system 100 for measuring the deflection in the z direction is a free working in the middle spring.
  • Figure 1 1 shows the use of a simple spring 110, which also here has the measuring system 111 with rods, as described for FIG. 8, in free working.
  • Figure 11 shows the side view and the top view.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Measurement Of Force In General (AREA)
  • Force Measurement Appropriate To Specific Purposes (AREA)

Abstract

L'invention concerne un élément dynamométrique qui mesure une force déclenchée au moyen d'une double barre de flexion et d'un capteur de course. La double barre de flexion permet d'avoir une forme de ressort elliptique qui optimise la répartition de l'extension.
EP04719910A 2003-05-07 2004-03-12 Element dynamometrique Withdrawn EP1623199A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10320575 2003-05-07
DE10333992.2A DE10333992B4 (de) 2003-05-07 2003-07-25 Kraftmesselement
PCT/DE2004/000493 WO2004099746A1 (fr) 2003-05-07 2004-03-12 Element dynamometrique

Publications (1)

Publication Number Publication Date
EP1623199A1 true EP1623199A1 (fr) 2006-02-08

Family

ID=33435960

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04719910A Withdrawn EP1623199A1 (fr) 2003-05-07 2004-03-12 Element dynamometrique

Country Status (3)

Country Link
US (1) US7437943B2 (fr)
EP (1) EP1623199A1 (fr)
WO (1) WO2004099746A1 (fr)

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Publication number Priority date Publication date Assignee Title
JP5376859B2 (ja) * 2007-08-28 2013-12-25 キヤノン株式会社 磁気式力センサ及び磁気式力センサを有するロボットアーム
US8151638B2 (en) * 2008-12-07 2012-04-10 Robert Bosch Gmbh Spring force component tester
EP2629068B1 (fr) * 2010-10-15 2019-12-11 Yamato Scale Co., Ltd. Cellule de charge ayant un mécanisme de prévention de surcharge
JP5795908B2 (ja) * 2011-01-07 2015-10-14 Ntn株式会社 電動ブレーキ装置
JP5877134B2 (ja) 2012-07-11 2016-03-02 Ntn株式会社 磁気式荷重センサおよび電動ブレーキ装置
AT515508A1 (de) * 2014-03-11 2015-09-15 Franz Dipl Ing Braunschmid Konstruktionselemente zur Erfassung von messgrößenverursachten Gestalts- oder Torsionsveränderungen
EP3123144A4 (fr) * 2014-03-28 2017-12-13 United Technologies Corporation Appareil et procédé de test de matériau
US20180311468A1 (en) * 2017-04-27 2018-11-01 The Regents Of The University Of California Force sensor and monitoring device

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Also Published As

Publication number Publication date
US7437943B2 (en) 2008-10-21
WO2004099746A1 (fr) 2004-11-18
US20070107531A1 (en) 2007-05-17

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