WO2010057634A1 - Capteur de force pour éléments de support - Google Patents

Capteur de force pour éléments de support Download PDF

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Publication number
WO2010057634A1
WO2010057634A1 PCT/EP2009/008238 EP2009008238W WO2010057634A1 WO 2010057634 A1 WO2010057634 A1 WO 2010057634A1 EP 2009008238 W EP2009008238 W EP 2009008238W WO 2010057634 A1 WO2010057634 A1 WO 2010057634A1
Authority
WO
WIPO (PCT)
Prior art keywords
force transducer
flange portion
piston
working cylinder
measuring system
Prior art date
Application number
PCT/EP2009/008238
Other languages
German (de)
English (en)
Inventor
Otto Pfeffer
Original Assignee
Brosa Ag
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 Brosa Ag filed Critical Brosa Ag
Publication of WO2010057634A1 publication Critical patent/WO2010057634A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C23/00—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
    • B66C23/62—Constructional features or details
    • B66C23/72—Counterweights or supports for balancing lifting couples
    • B66C23/78—Supports, e.g. outriggers, for mobile cranes
    • B66C23/80—Supports, e.g. outriggers, for mobile cranes hydraulically actuated
    • 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
    • G01L1/26—Auxiliary measures taken, or devices used, in connection with the measurement of force, e.g. for preventing influence of transverse components of force, for preventing overload
    • 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
    • G01L5/0061—Force sensors associated with industrial machines or actuators

Definitions

  • the present invention relates to a combinable with a working force transducer for the determination of tensile and / or compressive forces exerted by the working cylinder, preferably a hydraulic cylinder, in particular in the form of supporting forces. Furthermore, the present invention relates to a working cylinder with a corresponding load cell, which is mounted on the piston side. Moreover, the present invention relates to a support leg with a corresponding hydraulic cylinder.
  • measuring axes which in a joint of a support arm for heavy work equipment, such as a load trolley with integrated concrete pump, between a horizontally oriented shear beam and a vertically oriented support cylinder are arranged.
  • Such measuring axes are prone to parasitic forces, in particular at a force introduction obliquely to the longitudinal axis of the support cylinder.
  • a measuring axis is described in EP 1 675 760 B1.
  • a monitoring device comprises evaluation electronics, which can be acted upon in given scanning cycles with supporting foot-related supporting load measured values as well as their comparison with at least one predetermined stability-determining threshold value. This makes it possible to provide a real-time monitoring of the vertical load in the area of the individual support feet in a tight time frame, so that also dynamic effects and inertial effects in the operation of the implement can be included in the monitoring.
  • a ring-shaped force transducer with integrated, electrical measuring system is mounted below a conventional foot plate. Below the annular force transducer turn another foot plate is mounted.
  • This first variant is used to retrofit conventional support legs.
  • the second variant has mounted the annular force transducer between a piston-receiving element and the foot plate in an integrated manner, so that the force transducer is secured against environmental influences.
  • a force transducer for the determination of tensile and / or compressive forces, which can be exercised by a working cylinder, preferably a hydraulic cylinder, in particular in the form of supporting forces, wherein the force transducer has a body which is a substantially spherical , adapted to be received in a socket of a support plate formed portion and a substantially annular flange portion, wherein the flange portion is adapted to be connected to a piston of the working cylinder, wherein a, in particular the piston facing inner surface of the annular flange portion, which adjoins a transition region connecting between the flange portion and the spherical portion is adapted to receive an electrical measuring system.
  • the force introduction direction is oriented substantially coaxially to the longitudinal axis of the force transducer or the working cylinder.
  • the power cylinder has its longitudinal axis aligned coaxially with the longitudinal axis of the force transducer. Even if a support plate of a support arm is on a sloped surface, the force introduction direction is always the same.
  • the support plate preferably has a socket-like recess for receiving the spherical body of the force transducer.
  • an outer diameter of the annular flange portion is substantially equal to an outer diameter of the piston.
  • the flange portion extends perpendicular to a longitudinal axis of the working cylinder, and thus to the central axis of the force transducer.
  • the flange portion is formed in several parts and has an outer flange and an inner, preferably formed with a T-shaped cross-section, stamp member, which is fixed in an inner cavity of the flange, preferably by means of a counter-holder, that one, in one assembled Condition of the flange substantially axially oriented support member of the punch member centrally, preferably flush, abuts a bottom of the interior and that a substantially radially oriented diaphragm member of the punch member to which the support member connects centrally and substantially perpendicular to a circumferentially extending, inwardly projecting step of the flange mantle, wherein the electrical measuring system is attached to the diaphragm member.
  • This embodiment has the advantage that the DMS sit protected inside the Stützfußadapters that connects the cylinder with the Abductiveeller.
  • the introduction of force is centered in the area of the stamp element.
  • the membrane of the stamp element can make smallest changes detectable.
  • the measuring system is protected against external environmental influences and nevertheless easy to maintain and interchangeable. Even oblique force discharges can be detected well and lead to few or no parasitic disturbances.
  • the spherical portion and the flange portion define a half-open space, which is substantially closed by the piston in a cylinder-mounted state.
  • the electrical measuring system is preferably hermetically sealed off from the outside world. Nevertheless, maintenance or replacement of the electrical metering system can be done easily, for example, when the load cell is bolted to the piston rod. To replace or maintain the electrical measuring system, only the corresponding screws need to be solved to release the spherical load cell from the piston rod. Thereafter, the electrical measuring system is freely accessible.
  • the spherical portion has a recess in the interior about a central axis of the force transducer.
  • the material thickness can be chosen and shaped arbitrarily, in particular in the region of the transition region.
  • the material thickness in this expanding and / or accumulating region of the force transducer has an influence on the linearity and the hysteresis of the measuring signal.
  • the spherical portion and the flange portion are integrally formed.
  • an electrical force measuring system preferably comprising strain gauges, the measuring system being mounted on an inside surface of the annular flange portion oriented perpendicular to a central axis of the body, in a region preferably outside of Transition diameter is.
  • the flange portion may comprise a cylindrical body having at least two openings extending in the axial direction for receiving the electrical measuring system.
  • any number of measuring zones can be integrated into the body of the flange section.
  • the strain gauges which are attached to the inner wall of the measuring zones, are protected against external influences.
  • the force transducer is preferably constructed in several parts, which is noticeable in a simpler production of the individual components.
  • the electrical measuring system can be easily attached from the outside to the inner walls of the measuring zones.
  • the shape of a centrally located core piece of the flange section can be varied, with which the size of the measuring signal can be influenced.
  • the force transducer on the piston side to a working cylinder in particular a hydraulic cylinder mounted.
  • such a hydraulic cylinder is used in a support leg for a provided with Stauerauslegern working device.
  • this support leg further comprises a support plate having a socket which is adapted to receive the spherical body, wherein the force transducer is the only connection between a piston rod and the support plate.
  • Fig. 1 is a perspective view of a first force transducer according to the present invention, which is coupled to a working cylinder;
  • Fig. 2 is a side view of the insulated force transducer of Fig. 1;
  • Fig. 3 is a sectional view taken along a line III-III of Fig. 2;
  • FIG. 5 shows a cross section of a bottle section of the second force transducer according to FIG. 4;
  • FIG. 6 shows a cross section through a further embodiment of a force transducer according to the present invention.
  • Fig. 7 is a perspective view of another, partially cut illustrated force transducer according to the present invention.
  • Fig. 1 shows a schematic perspective view of a force transducer according to the present invention, which is generally designated 10 below.
  • identical features will be denoted by like reference characters. Similar features are provided with similar reference numerals.
  • the first embodiment of the force transducer 10 according to the invention is adapted to be mounted on a support arm of a mobile working device, as exemplified in the German patent application DE 101 10 176 Al entitled "Mobile work tool with Standsi- DE 101 10 176 discloses a support arm of a mobile working implement, for example a concrete pump, which is operated with a hydraulic cylinder, however, the present invention is is not limited to this application, for example, the present invention is also applicable to support arms for truck cranes and the like.
  • the force transducer 10 of Figure 1 is here formed in one piece and comprises a body having a substantially spherical portion 12, preferably of solid material (e.g., stainless steel), to which an annular flange portion 14 couples. Between the spherical portion 12 and the annular flange portion 14 is provided with the reference numeral 16 transition region which extends substantially parallel to a longitudinal axis 18.
  • the Flanschanites 14 in turn coupled either directly or indirectly to a here generally designated 20 piston or to a piston rod of a working cylinder, not shown here, such as a hydraulic cylinder to.
  • the force transducer 10 rests when used as an end piece of a piston rod of a support arm usually in a pan element, not shown here (support plate), as shown by way of example in DE 101 10 176 Al.
  • the pan element in turn coupled to a support plate, also not shown here, which is usually sold directly on the ground.
  • the counterforce exerted by the bottom is identified by the reference symbol F.
  • the force introduction usually takes place essentially along the longitudinal axis or central axis 18 of the force transducer 10.
  • the force F is preferably oriented coaxially to the central axis 18. Depending on the surface, the force can also be introduced at an angle.
  • passage openings 22 are shown in FIG. 1, preferably with an internal thread are provided, for example, to screw screws for the purpose of connection with the piston rod 20 can.
  • the transition region 16 has a length L parallel to the central axis 18.
  • the transition region 16 extends substantially parallel to the central axis 18.
  • the diameter of the transition region 18 is provided with U via D in Fig. 2 designates.
  • Fig. 3 shows a sectional view taken along the line III-III of Fig. 2.
  • the flange portion 14 is formed substantially annular or cylindrical and here has an inner diameter Dmnen and an outer diameter Dausen on.
  • the force transducer 10 has a single recess 26 on the inside, which defines an interior 28 for receiving an electrical measuring system 30.
  • the electrical measuring system 30 is mounted on an inner side 31 of the flange portion 14, which is opposite to the piston rod 22 in the installed state of the force transducer 10.
  • the inner surface 31 is oriented perpendicular to the central axis 18 here. An oblique orientation is also possible.
  • the electrical measurement system 30 may include one or more strain gauges 32 (DMS) that are either glued or sputtered.
  • the DMS 32 are located locally with respect to the radius of preferably between the transition diameter D u via and the inner diameter D ln NEN.
  • This region of the force transducer 10 is web-shaped between the flange portion 14 and the spherical portion 12 is formed. It can be seen that the force transducer 10 has a comparatively small material thickness at this point, so that when forces are exerted, in particular parallel to the central axis 18, this region can be deformed particularly strongly or easily deformed. In this area both strains and compressions occur. In this way it is possible with to measure 32 tensile and compressive forces on a DMS.
  • the signal is linear at high resolution and has low hysteresis.
  • the material thickness - and thus the power flow - in this area of the force transducer 10 can also be changed by further recesses 34, 36. Any number of deep recesses can be provided in the direction of the interior of the spherical part 12. Preferably, a cylindrical recess is provided, which is indicated in FIG. 3 with a dashed line 38.
  • the recess according to the dashed line 38 essentially allows a constant material thickness in the region of the flange portion 14 and of the transition 16, so that the force flux density in this region is relatively homogeneous. Small forces then cause large signal strengths.
  • FIG. 3 an internal thread of the passage opening 22 is schematically indicated in FIG. 3. It should be understood that the force transducer 10 of the present invention may be connected to the piston 20, not shown in FIG. 3, in any other manner (e.g., by welding).
  • a second embodiment of a force transducer 10 'according to the invention is shown, which is formed here in several pieces.
  • the force transducer 10 'of Fig. 4 has a hemispherical portion 12', to which a transition region 16 'integrally connected.
  • the transitional region 16 'itself has a flange-shaped section at its end opposite the (semi-) spherical section 12'. This flange-shaped section has an outer diameter Dober.
  • the flange portion 14 ' has a cylindrical body which has at its one longitudinal end a cylindrical recess 40 which is designed to receive the flange-shaped end of the transition region 16'. Both the recess 40 and the flange-shaped end of the transitional region 16 'may be formed with corresponding threads to connect the portion 12' to the flange portion 14 'frictionally and positively.
  • the recess 40 in the flange portion 14 ' has to a depth To, which corresponds substantially to the height of the flange-shaped end of the transition region 16'.
  • the flange portion 14 'of Fig. 4 further comprises at least two measuring openings 42 having a respective depth T M relative to the recess 40.
  • the measuring openings 42 are located radially outward relative to the central axis of the flange portion 14 'and extend substantially in the longitudinal direction (ie vertically in Fig. 4) of the flange portion 14'.
  • the measuring openings 42 define a core 44 between them.
  • the measuring openings 42 are preferably arranged symmetrically to the central axis of the flange portion 14 '.
  • the measuring openings 42 serve to receive the strain gages 32. For this purpose, the strain gages are attached to the inner walls of the measuring openings 42.
  • the inner walls of the measuring openings 42 extend substantially along the central axis M of the flange portion 14 '.
  • the measuring openings 42 here have a circular cross-section. Other cross-sectional shapes can be chosen. Outwardly, the measuring openings 42 are bounded by outer walls 46 of the flange portion 14 '.
  • the flange portion 14 ' has at its other, the piston 20 end facing a centrally disposed, sleeve-shaped projection 48.
  • the projection 48 protrudes from a lid-like, substantially flat surface 50 of the flange portion 14 '.
  • the surface 50 is usually flush with the piston and serves the preferably planar power transmission from the piston in the direction of the spherical portion 12 '.
  • the sleeve-shaped projection 48 may have an outer circumferential thread 52. Other connection types are possible.
  • the sleeve-shaped projection 48 is in particular hollow on the inside. This cavity 54 has space for receiving a measuring amplifier 56, which can be electrically connected via channels not shown here through the flange portion 14 'with the DMS 32.
  • the measuring amplifier 56 is shown in FIG. 4 with a dashed line.
  • the piston 20, which is not shown in FIG. 4, is non-positively connected to the flange section 14 'of FIG. through the core 44 onto the spherical portion 12 'via the transition region 16'.
  • the core 44 is in the assembled state of the force transducer 10 'preferably flat on the transition region 16'.
  • FIG. 5 a view is shown of an underside of the isolated flange portion 14 'of FIG. 4.
  • the flange portion 14 'of Fig. 4 is here viewed from the direction of the spherical portion 12' from "bottom", without the spherical portion 12 'is shown.
  • the flange portion 14 has the circumferential wall 46 radially outermost lying on. Further inside, in the area of the recess 40 (see Fig. 4), four measuring openings 42 arranged symmetrically to the central axis of the force transducer 10 are shown by way of example here.
  • the strain gauges 32 are fourfold per Provided measuring port 42 and are preferably arranged symmetrically on the inner walls. Usually, the compression of the core portion 44 is measured.
  • Fig. 6 is a cross-section through another embodiment of a power take 10 "is shown according to the present invention.
  • the force transducer 10 also has a flange portion 14", a transition region 16 "and a spherical portion 12" on.
  • the portions 12 "to 16" are formed integrally with each other.
  • the flange portion 14 is in turn made of several parts, and the flange portion 14" has an outer flange jacket 60 and an inner punch member 62.
  • the flange jacket 60 is integrally formed with the transition region 16 "and the spherical portion 12".
  • the punch member 62 may have a T-shaped cross-section which is formed essentially of a vertical support member 64 and a horizontal diaphragm member 66.
  • the membrane member 66 has here a substantially circular cross-section.
  • the support member 64 is cylindrical.
  • the support member 64 is preferably oriented coaxially with the central axis M in the installed state.
  • the membrane member 66 is then oriented substantially perpendicular to the central axis M.
  • the support member can be centered, screwed in, taped, etc, with a thread.
  • the punch element 62 can be fixed in the flange jacket 60 by means of a counter-holder 68.
  • the counter-holder 68 may have a thread 70, which can be brought into the interior 74 with a thread 72 (not shown in FIG. 6).
  • the punch element 62 can be fixed directly to the flange jacket 60 without a counter holder 68, for example by welding.
  • the counter-holder embodiment 68 is more advantageous because the punch member 62 is easier to remove, for example, to replace one of the strain gages 32 attached to the diaphragm member 66.
  • the internal space 74 of the force transducer 10 has a step-shaped profile, the radius of which tapers abruptly with increasing depth relative to the flange section 14" or the transitional region 16 ".
  • the profile has at least one step 76 which is in the circumferential direction Circumferential stop for the diaphragm member 66 of the punch member 62.
  • the counter-holder 68 forces the punch member 62 preferably against the step 76 in the shell 60th
  • the lower, free end of the support member 64 is in the assembled state, preferably flat, on a projection 78 in the bottom 79 of the interior 74 at.
  • the projection has in particular the same cross-section as the support member 64 in order to ensure the best possible and centered power transmission.
  • the projection 78 and the support member 64 form a kind of power transmission column which is free in the lower part of the Innraums 74 and in the case of a force application (in the longitudinal direction of the force transducer 10 ") causes a deflection or deformation of the diaphragm member 66, similar to the first 1.
  • This deflection of the diaphragm can be registered by the strain gauges 32 and converted into a measuring signal
  • the signal lines are not shown in FIG. 6 for reasons of clarity
  • the strain gages 32 can also be seen on the support member 64 Side of the membrane member 66. In both variants of the arrangement, the strain gages 32 are protected from the outside environment.
  • the projection 78 is not mandatory. Also, the cross section of the projection 78 need not necessarily be equal to the cross section of the support member 64. Also, the interior 74 defining recess can be varied. It can e.g. 6 can also be provided only in the flange section 14 "The stamp element 62 can be designed in several parts. The step 62 can be interrupted in the circumferential direction.
  • Fig. 7 shows a perspective sectional view of another force transducer 10 according to the present invention.
  • the force transducer 10 of Fig. 7 is here again integrally formed and has a spherical portion 12, a flange portion 14 and a transition portion 16.
  • the body of the force transducer 10 extends substantially in the axial direction 18.
  • the flange portion 14 here again comprises a (one-piece) flange jacket 80.
  • the flange portion 14 and the transition portion 16 define in their respective radially inner regions a revolver drum-like trained core element 80th ,
  • the core member 80 extends in the axial direction 18 within the flange jacket 60 in the direction of the spherical portion 12, starting from the inner space 28 and 74, respectively.
  • An upper surface of the turret-like core member 80 corresponds to the inner surface 31 of FIG.
  • the electrical measuring system 30, here consisting of DMS 32, is attached to the inner surface 31, ie the upper side of the core element 80.
  • the upper side of the core element 80 lies above a contact surface of the flange section 14 with the working cylinder or piston 20, which is indicated in FIG. 7 by two dashed lines.
  • the inner surface 31 is thus set back relative to the contact plane between the force transducer 10 and the working cylinder or piston 20 in the direction of the arrow 84 in an interior of the working cylinder or piston 20.
  • the electrical measuring system 30 is offset in the direction of the working cylinder 20.
  • the working cylinder 20 when used in a mobile work implement, is oriented vertically in the extended working condition and connected to a horizontally oriented boom. Therefore, when a supporting force is applied, the working cylinder tends to swerve in the horizontal direction, ie, laterally. This tendency to evade laterally usually results in bending moments in the region of the force transducer 10, where the contact with the substrate takes place.
  • the electrical measuring system 30 is arranged here between blind holes 86.
  • the blind holes 86 extend in the axial direction 18, starting from the upper side 31 of the core element 80.
  • the blind holes 86 are arranged in a radially outer region of the upper side 31.
  • the top surface 31 acts as a diaphragm upon application of a support force, as the core member 80 tends to move toward the power cylinder 20, whereas the power cylinder 20 initiates movement in the opposite direction over the outer edge of the flange portion 14. In the area of the electrical measuring system 30, there is a bending of the upper side 31, which is measured.
  • Fig. 7 shows a further aspect of the present invention, as it shows a force transducer 10, which is suitable for determining tensile and / or compressive forces exerted by the working cylinder 20 in the form of supporting forces, wherein the Force transducer 10 has an axially oriented body having a substantially spherical, formed for receiving in a support plate portion 12 and a substantially annular flange portion 14, wherein the flange portion 14 is adapted to be connected to the piston 20 of the working cylinder, wherein the, in particular the piston facing, inner surface 31 of the annular flange portion 14, which adjoins the transition region 16 between the flange portion 14 and the spherical portion 12 is adapted to receive the electrical measuring system 30.
  • the flange portion 14 extends in a state mounted on the working cylinder 20 in the axial direction 18 in the working cylinder 20, so that the inner surface 31 is disposed with the attached electrical measuring system 30 within the working cylinder 20.
  • the spherical section 12, the transition section 16 and the flange section 14 are integrally formed, wherein the flange section 14 and the transition section 16 have a radially inwardly arranged cylindrical section.
  • beautiful core element 80 having axially extending blind holes 86 which are formed in the inner surface 31.
  • the blind holes 86 are formed in the circumferential direction in a radially outer region of the inner surface 31.
  • the electrical measuring system 30, preferably centrally, is arranged between the blind holes 86.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Measurement Of Force In General (AREA)

Abstract

L'invention concerne un capteur de force (10) pouvant être accouplé à un vérin de travail, destiné à déterminer des forces de traction et/ou de pression (F) pouvant être exercées par un vérin de travail, de préférence un vérin hydraulique, en particulier sous la forme de forces d'appui, le capteur de force (10) présentant une section (12), conçue de manière sensiblement sphérique de façon à être reçue dans une cavité de rotule. Sur un côté orienté vers un piston (20), la section sphérique (12) se transforme en une section de rebord (14) sensiblement annulaire, appropriée pour être montée sur un piston (20) du vérin, une surface intérieure de la section de rebord annulaire (14), qui est orientée vers le piston (20) et contiguë à une zone de transition (16) entre la section de rebord et la section sphérique (12), étant adaptée pour recevoir un système de mesure électrique (30).
PCT/EP2009/008238 2008-11-19 2009-11-19 Capteur de force pour éléments de support WO2010057634A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008058758A DE102008058758A1 (de) 2008-11-19 2008-11-19 Kraftaufnehmer für mit einem Hydraulikzylinder betätigten Stützausleger
DE102008058758.3 2008-11-19

Publications (1)

Publication Number Publication Date
WO2010057634A1 true WO2010057634A1 (fr) 2010-05-27

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PCT/EP2009/008238 WO2010057634A1 (fr) 2008-11-19 2009-11-19 Capteur de force pour éléments de support

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DE (2) DE102008058758A1 (fr)
WO (1) WO2010057634A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016104592A1 (de) 2016-03-14 2017-09-14 Weber-Hydraulik Gmbh Stützenbauteil mit integriertem Kraftsensor
CN111122038A (zh) * 2019-12-27 2020-05-08 中联重科股份有限公司 传感器组件、作用力检测设备和方法以及工程机械
CN113464214A (zh) * 2021-05-25 2021-10-01 内蒙古蒙达发电有限责任公司 一种汽轮机汽缸载荷测量装置

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009002188A1 (de) * 2009-04-03 2010-10-14 Tecsis Gmbh Kraftaufnehmer zur Messung von Stützkräften in einem Abstützelement
EP3096119B1 (fr) * 2014-01-17 2022-03-02 Tecsis GmbH Système de mesure permettant de déterminer une force de support
DE102019106580A1 (de) * 2019-03-14 2020-09-17 Wobben Properties Gmbh Flanschverbindung, Windenergieanlage mit selbiger, und Verfahren zur Überwachung selbiger
CN111122037B (zh) * 2019-12-27 2020-12-15 中联重科股份有限公司 传感器组件、作用力检测设备和工程机械
DE102020101615A1 (de) 2020-01-23 2021-07-29 Weber-Hydraulik Gmbh Zylinderkolbenaggregat mit integriertem Kraftmesssystem

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3711142A (en) * 1970-04-07 1973-01-16 Demag Ag Suction operated lifting device
DE2609631A1 (de) * 1976-03-09 1977-09-15 Metz Gmbh Carl Kraftfahrzeug
US4319766A (en) * 1980-06-25 1982-03-16 General Motors Corporation Vehicle trailer hitch
DE3933575A1 (de) * 1989-10-07 1991-04-18 Hartmut Prof Dr Janocha Tasteinrichtung
EP0736755A1 (fr) * 1995-04-06 1996-10-09 Metz Feuerwehrgeräte Gmbh Dispositif pour mesurer la force de pression
WO2006042537A1 (fr) * 2004-10-21 2006-04-27 Zf Friedrichshafen Ag Systeme dynamometrique comprenant au moins une articulation a rotule
WO2009141193A1 (fr) * 2008-05-21 2009-11-26 Putzmeister Concrete Pumps Gmbh Engin de travail mobile à surveillance de la stabilité statique

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10110176A1 (de) 2001-03-02 2002-09-05 Putzmeister Ag Mobiles Arbeitsgerät mit Standsicherheitsüberwachung
DE10349234A1 (de) 2003-10-20 2005-05-19 Putzmeister Ag Mobiles Arbeitsgerät mit Stützauslegern

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3711142A (en) * 1970-04-07 1973-01-16 Demag Ag Suction operated lifting device
DE2609631A1 (de) * 1976-03-09 1977-09-15 Metz Gmbh Carl Kraftfahrzeug
US4319766A (en) * 1980-06-25 1982-03-16 General Motors Corporation Vehicle trailer hitch
DE3933575A1 (de) * 1989-10-07 1991-04-18 Hartmut Prof Dr Janocha Tasteinrichtung
EP0736755A1 (fr) * 1995-04-06 1996-10-09 Metz Feuerwehrgeräte Gmbh Dispositif pour mesurer la force de pression
WO2006042537A1 (fr) * 2004-10-21 2006-04-27 Zf Friedrichshafen Ag Systeme dynamometrique comprenant au moins une articulation a rotule
WO2009141193A1 (fr) * 2008-05-21 2009-11-26 Putzmeister Concrete Pumps Gmbh Engin de travail mobile à surveillance de la stabilité statique

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016104592A1 (de) 2016-03-14 2017-09-14 Weber-Hydraulik Gmbh Stützenbauteil mit integriertem Kraftsensor
CN111122038A (zh) * 2019-12-27 2020-05-08 中联重科股份有限公司 传感器组件、作用力检测设备和方法以及工程机械
CN113464214A (zh) * 2021-05-25 2021-10-01 内蒙古蒙达发电有限责任公司 一种汽轮机汽缸载荷测量装置
CN113464214B (zh) * 2021-05-25 2022-10-14 内蒙古蒙达发电有限责任公司 一种汽轮机汽缸载荷测量装置

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