WO2018024496A1 - Bride de support servant au support mutuel d'un organe de commande et d'un mécanisme de commande et dispositif de mesure - Google Patents

Bride de support servant au support mutuel d'un organe de commande et d'un mécanisme de commande et dispositif de mesure Download PDF

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Publication number
WO2018024496A1
WO2018024496A1 PCT/EP2017/068358 EP2017068358W WO2018024496A1 WO 2018024496 A1 WO2018024496 A1 WO 2018024496A1 EP 2017068358 W EP2017068358 W EP 2017068358W WO 2018024496 A1 WO2018024496 A1 WO 2018024496A1
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WO
WIPO (PCT)
Prior art keywords
flange
deformation
actuator
spring
carrier
Prior art date
Application number
PCT/EP2017/068358
Other languages
German (de)
English (en)
Inventor
Stefan Kolbenschlag
Rainer Oberheim
Original Assignee
Samson Aktiengesellschaft
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 Samson Aktiengesellschaft filed Critical Samson Aktiengesellschaft
Publication of WO2018024496A1 publication Critical patent/WO2018024496A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K37/00—Special means in or on valves or other cut-off apparatus for indicating or recording operation thereof, or for enabling an alarm to be given
    • F16K37/0025—Electrical or magnetic means
    • F16K37/0041—Electrical or magnetic means for measuring valve parameters

Definitions

  • Flange support for mutual support of a control armature and an actuator
  • the invention relates to a flange support for the mutual carrying of a control valve, such as a control valve, a process plant, such as a chemical or petrochemical plant, a food processing plant, in particular a brewery, a nuclear power plant or the like, and a Stellarmatur actuated actuator, such as a pneumatic actuator, in particular a pneumatic lifting or rotary actuator. Furthermore, the invention relates to a measuring device which makes use of the flange carrier according to the invention.
  • DE 38 20 838 AI discloses a device for measuring the torque of a movable actuator by a servo-valve.
  • the housing of the actuator and the housing of the control armature via a sleeve-shaped flange are connected to each other, wherein strain gauges are arranged on a weakened Flanschiva-section, which is referred to as free rotation and is formed by a thin flange wall.
  • strain gauges have a stretching or compressive, elastic Deformation detected near the surface, with smallest deformations in ⁇ - ⁇ be detected.
  • a strain gauge gives readings based on the change in electrical resistance and direct information about the voltage acting there.
  • a control armature such as a control valve of a process plant
  • a Flansch Gay for supporting a control valve, such as a control valve, a process plant, such as a petrochemical plant, a food processing plant, a nuclear power plant or the like, and a Stellarmatur actuated, pneumatic or electric actuator, such as a rotary actuator, is provided.
  • the flange supports in the mounted state by transmitting the supporting and bearing forces between the respective housings, the control valve to the actuator, so that in particular no further supporting structure is necessary. If the control valve is mounted stationary on a process plant line, the control valve carries the actuator via the flange carrier. The same applies vice versa, the actuator should be mounted on a stationary part of the process plant and the control armature should be worn freely.
  • both the control armature and the flange support may be mounted on a process equipment part such that only a portion of the support forces are actually transmitted by the flange support between the actuator armature and actuator housings.
  • the flange carrier is designed to transmit reaction forces between the actuator and actuator housings that arise when the actuator moves the actuator to the desired position.
  • the actuating forces are also referred to below as actuating actuating forces which, for example, depend on the fluid flow strength in the process plant line and / or static and sliding friction forces of the movable elements of the control valve and the actuator result.
  • the flange is also called lantern, support frame, upper part or yoke, which support structures are formed by mainly in the axial support direction extending support columns, which are arranged in, for example, equidistant circumferential distances from each other to allow access from the outside to the control rod or Stellwelle, which run inside the lantern or the yoke and be moved to allow.
  • the support structure or the flange can also form a closed tube structure which is partially opened or weakened radially, in particular to form the Abstützchulen.
  • the flange has according to its first part of the term two sides of the flange, namely the actuator side flange and the Stellarmatur sectionen flange, with a rigid, immovable attachment of the respective housing of the actuator or the control armature is to reach the flange.
  • the flange can be integrally connected to the respective housing of the control valve and the actuator.
  • a flange can have a central passage through which an actuator, such as the control rod or the control shaft, the actuator or the control valve can extend.
  • the control rod or actuating shaft has a minimum cross-section, such as a diameter, for example, from 3 mm or 5 mm to over 300 mm, depending on the design of the actuator and the control valve.
  • the actuator receives in particular in process engineering equipment an electrical or pneumatic drive energy with which an actuator force is generated to perform a lifting movement or pivotal movement of the control valve.
  • the actuator can deliver a Nennstellkraft that can be designed to overcome a mechanical spring and / or in the range of 100 N to 600 N, 800 N, 1000 N, 2000 N and optionally may be over.
  • the flange carrier is designed in such a way that it has a deformation-soft design only in a single preferred deformation direction, such as in a circumferential direction surrounding an axial support direction of the flange carrier.
  • the only preferred deformation direction is determined by the flange.
  • the flange carrier allows in the transmission of the actuator force from the actuator to the control armature elastic deformation only in this deformation preferred direction, so that an actuator-side flange relative to a Stellarmatur practiceen flange only in the predetermined Deformation preferred direction is shifted.
  • On the basis of the displacement or displacement of the respective two flange sections can be closed to the applied Nennstell mechanism of the actuator knowledge.
  • empirical values and flange carrier-specific deformation parameters can be used to calculate the nominal setting force used after detection of the elastic deformation movement in the preferred deformation direction.
  • the deformation is elastic, so that in the absence of load - with repealed force - the flange is fed back along the direction of deformation preference in the starting position / the initial state in which act exclusively static load-bearing forces.
  • the flange carrier determines a coordinate direction system starting from the actuator or the control fitting, and defines an axial support direction, which coincides in particular with the setting direction of the actuator and / or the longitudinal extension of the control rod, a radial direction perpendicular to the support direction, preferably all star-shaped from The axial support direction radially extending radial directions are meant, as well as a peripheral direction surrounding the support direction and senlcrechte to the radial direction.
  • the deformation preferred direction coincides with exactly one, in particular the circumferential direction of the Flanschmois, these three coordinate directions together, wherein in particular the flange is formed in the remaining directions, in particular both in the axial support direction and in the radial direction, deformation stiff.
  • the actuator-side flange of the Flanschippos and the Stellarmatur knowledgeablee flange of the Flanschys move along the predefined deformation preferred direction when, in particular beyond the static load forces, drive reaction forces between the actuator and the control armature act.
  • This deformation relative movement which is oriented in deformation preferred direction, is detected by measurement and processed in particular computationally to draw conclusions about the current, output actuator forces. With the detected actuator forces also conclusions about the functionality of the field device can be made.
  • the flange carrier has a Stellantriebssei- term flange or mounting flange body, a Stellarmatur technologyen flange or Bef Trentsungsflanschisson and the two flanges in the preferred deformation direction spring elastically movable against each other anlenlcenden spring contour section.
  • the spring contour section can act as a resilient coupling joint and in particular be designed to return the designed Befest Trentsflansch endeavor resiliently into a starting position.
  • the spring contour portion is realized by a plurality of spring webs, which in particular extend integrally between said flanges.
  • the spring mobility of the flanges by means of the spring contour section can be realized by separate, movably mounted guide or hinge elements which allow a displacement of the two flanges only in the deformation preferred direction, with additional spring elements can be provided for returning to the predetermined starting position.
  • the spring contour portion may be provided with a deformation barrier which prevents movement of the spring contour portion in another lease as the deformation preferred direction.
  • the spring contour portion is executed without guide or joint elements and without additional spring elements and weakened on the basis of a one-piece metal or plastic part and / or configured such that the flange is deformation soft only in the preferred deformation direction, preferably only in the circumferential direction, preferably deformation soft than in all other coordinate directions of the Flanschmons, as in the axial support direction and in the radial direction.
  • the deformation preferred direction defining the flange support structure is not linear, but circular, preferably concentric about the axial support direction.
  • an elastic deformation stiffness of the spring contour section in the other coordinate directions, such as in the axial support direction and in the radial direction, of the Flanschmois by at least 50%, preferably 100%, in particular by at least three times, at least four times or at least five times greater than one elastic deformation stiffness of the spring contour portion in the deformation preferential direction, such as the circumferential direction.
  • the flange carrier in particular the spring contour section, is designed to be elastically deforming soft in the preferred deformation direction such that upon transmission of an operating force, such as an operating torque, from the actuator to the control armature, an elastic deformation relative movement between see a Stellarmatur technologyen flange and an actuator-side flange is accompanied in Deformationsvorzugsraum, the deformation relative movement by means of a position detection device, such as an inductive or capacitive measuring device, can be determined.
  • an operating force such as an operating torque
  • the executed amplitude of the deformation relative movement is adjusted due to the constructional configuration of the spring contour section, so that the position detection device can also detect minimum actuating drive forces of the actuator due to a deformation displacement of the flanges in the deformation preferred direction.
  • deformation movement amplitudes between the two flanges of 0.1 mm, 0.2 mm, 0.3 mm, 0.5 mm, 0.8 mm, 1 mm, 1.5 mm, 2 mm, 3 mm, 5 mm, 10 mm or more.
  • the inductive or capacitive or potentiometric measuring device requires movement amplitudes of larger dimensions in order to generate sufficiently precise measurement results.
  • the design of the elastic deformation softness or elastic minimum deformation displacement amplitude of the flange carrier may be determined depending on the sensitivity of the selected position detection device.
  • the position detection device is formed by a magnetic field sensor and a magnetic field source, wherein the magnetic field sensor and the magnetic field source are arranged in the region of the spring contour section, that the deformation relative movement of the magnetic field sensor and the magnetic source is detected in the preferred deformation direction.
  • the magnetic field sensor is associated with the actuator armature side flange and the magnetic field source is associated with the actuator side flange, or vice versa.
  • the particular weakened spring contour section is subjected to a torsional moment upon transmission of an operating force from the actuator to the control armature, wherein the position detection device detects the elastic deformation relative pivoting movement.
  • the spring contour portion of the Flanschlichd in a plurality, preferably at least three or four, preferably rod-shaped spring bars or columns realized, which in itself a deformation-resistant, actuator-side flange or mounting terminal, and a deformation-resistant, Stellarmatur principleen flange or Mounting connection spring elastically coupled to each other.
  • the plurality of spring bars may be designed such that they act as an elastic, in particular one-piece hinge connection between the two flanges to provide the resilient deformation softness in the preferred deformation direction.
  • the orientation of elongated spring webs is arranged so that they are bendable in the preferred deformation direction.
  • the plurality of spring bars coupling a Stellarmatur practiceen Befest Trentsflansch phenomena elastically to an actuator side mounting body are structured / shaped and / or arranged such that the Federkonturabites is elastic deformation soft only in the deformation preferred direction and is particularly resistant to deformation in the other directions, in particular without having to start with an additional guide device or deformation barrier. Due to the design of the spring contra-section itself, the elastic deformation softness is achieved only in the preferred deformation direction, so that a relative displacement of the two flanges is predictably measurably accompanied only in a deformation preferred direction.
  • the plurality of spring bars and the Stellarmatur facede flange and the drive-side flange are made of one piece, such as a plastic piece or piece of metal.
  • each spring bar extends at a certain circumferential position in particular only axially (perpendicular to contact surface of the stellarmatur textbooken and Stellantriebs claimeden flange) and radially outward (from a connection portion of a flange to a connection portion of the other flange), in particular without circumferential direction component.
  • the desired elastic deformation softness in the circumferential direction as well as the desired deformation stiffness in the radial direction and axial direction is achieved. Due to the one-piece construction remains a structural unit of the Flanschschdes and its components, flange, spring contour section, spring bars, despite the deformation in one direction.
  • the spring bar opens into a sleeve-shaped connection portion of the actuator-side flange on the one hand and on the other hand in a sleeve-shaped connecting portion of the stellarma- tur practiceen flange and goes there.
  • the respective attachment sections are diametrically opposed radially.
  • In the transition region of the spring bar is reinforced to achieve a desired hinge pivot effect with only one degree of freedom of movement through the spring bar, in particular each spring bar sets the same hinge pivoting.
  • the plurality of spring bars are column-shaped and / or plate-shaped, wherein in particular the plate-shaped spring bars are each realized by a lamellar pair of two parallel extending plates, which are arranged in particular at a circumferential distance preferably less than 2 mm.
  • the plurality of spring bars which elastically couple the actuator arm side mounting flange body to the actuator side mounting flange body are structured and / or arranged such that the spring contour portion is resiliently deformed in the preferred deformation direction and at least one other direction
  • Case of the spring contour section additionally includes a deformation barrier, such as a stop or a recapturing sleeve, which is designed and mounted in particular as a separate additional component to the spring contour section or the flange and / or a deformation of the spring contour section only in the at least one further direction so locks, that a deformation relative movement erfmdungs accrued exclusively in the deformation preferred direction.
  • the flange carrier comprises an actuator-side and a Stellarmatur practiceen Befest Trentsflanschianu or flange.
  • This Befest Trents- flange body has a plate shape, which is provided close to the edge with a plurality of mounting holes to realize the rigid connection to the actuator or to the control valve.
  • the plate-shaped flanges define axially opposed inner surfaces on which a magnetic field source or a magnetic field sensor are arranged axially diametrically opposite one another.
  • the plate-shaped flanges define mutually remote au- S Hanlagen lake that are shaped so that a flat contact with a particular suitably shaped, complementary shape housing portion of the actuator or the control valve is allowed.
  • the actuator-side and the stellarmatursei- term mounting flange each have a passage opening in particular concentric to the axial support direction. Through the passage opening, an actuator of the actuator and / or the control armature can extend without contact.
  • the respective Befest Trentsflansch analyses has the sleeve-like or sleeve-shaped basic shape.
  • the flange has the weakened Federkonturabrough to make metrological statements about operating forces that are delivered in field operation of the actuator to the control armature.
  • the spring contour section is an elastic nominal deformation section of the otherwise in particular rigid and stiff flange carrier and, when the actuating force is applied, causes an elastic deformation in a predetermined direction, which can be scanned in particular by means of a position sensor.
  • the spring contour section or desired deformation section is designed such that upon transmission of the operating force, such as the operating torque, from the actuator to the control armature elastic deformation movement, in particular between an actuator side of the Federfeldabitess and a Stellarmatur principleen body of the spring contour section, with a Deformationsweg of at least 0.1 mm, 0.2 mm, 0.3 mm, 0.4 mm, 0.5 mm or 1 mm or at least 0.5% of the minimum cross-section of the actuator control rod / actuator stem.
  • the spring contour section can be so weakened that a still measurable minimum deformation deformation already occurs when normal (defect-free, without wear, without increased coefficient of friction) minimum operating forces act from the actuator to the control armature.
  • the measurable relative displacement of at least 0.1 mm or 0.5% of the minimum cross section of the control rod should already occur when operating forces are overcome just to overcome the internal friction of the control valve and actuator. It is clear that even with large-sized actuators a Relatiwerlagerung should be excluded by more than 5 mm.
  • An optimal displacement amplitude rich lies between 0.1 mm and 2 mm or 3 mm.
  • the flange carrier and its spring contour section are designed to be elastically deformation-soft in the preferred deformation direction so that the deformation in the preferred deformation direction remains elastic even at high operating forces and the yield point in the region of the spring contour section is not reached.
  • the flange carrier is designed to be elastically deformable, in the preferred or desired deformation direction, in which operating counterforces act which are expended on account of the usual operating forces of the actuator and the control valve.
  • a desired elastic deformation amplitude should be at least 0.1 mm and a maximum extension of up to 1 mm, 2 mm or 3 mm to 5 mm should not be exceeded.
  • the minimum deformation path allowed by the spring contour portion may be at least 0.3% or 0.5%, preferably 1%, 2%, 3%, 5%, or even 10% of the minimum thickness, such as the diameter, of the control rod or the adjusting shaft of the actuator or the control valve.
  • the respective actuator of the actuator and the control valve has a minimum cross-sectional dimension or a diameter of 10 mm, so should a deformation amplitude of at least 1%, preferably up to 10% or 20%, the minimum cross-sectional dimension are allowed by the Federkonturabêt at a force transmission in normal operation.
  • an absolute deformation path of at least 1 mm must also be assumed, which is already established at normal, in particular low operating forces.
  • a deformation path of at least 0.1 mm is sufficient in particular to use commercial capacitive or inductive or potentiometric position measuring methods.
  • the measurement data on the elastic deformation of the flange can be made, for example, from experience, flange support individual structural constants, such as modulus of elasticity, etc., a statement about the effective actual operating forces between the control valve and the control valve. It is advantageous to allow greater motion amplitudes of one or more millimeters through the spring contour portion to increase positional accuracy.
  • a position measurement in the area of the weakened spring contour section with only one preferred deformation direction is referred to, for example.
  • lent the elastic relative movement between an actuator side portion of the spring contour portion and a Stellarmaturpracticen area of the spring contour section provided in order to obtain conclusions about the absolute restoring forces that result in transmission of the drive actuating force on the control armature. In this way, precise statements about the actual restoring forces can be obtained.
  • the invention relates to a device for measuring an operating force, such as an operating torque, an actuating armature of a process plant actuated actuator according to claim 15 or as described above.
  • the measuring device comprises a flange carrier according to the invention, as described above.
  • the adjusting armature and the actuator can be mounted and / or mounted on the flange carrier, the flange carrier being combined with a position detection device in order to detect the elastic deformation which is forced and caused by the spring contour section in the direction of deformation.
  • Fig. La is a perspective view of a erfmdungs contemporary flange of a first
  • Fig. Lb is an end view of the flange of Figure la on the Stellarmatur workede end side of the flange.
  • Fig. Lc is a side view of the flange according to Fig. La and lb
  • FIG. 2 a is a perspective view of a flange carrier according to the invention of a second
  • Fig. 2c is a side view of the flange according to Fig. 2a and 2b.
  • a flange according to the invention is generally provided with the reference numeral 1.
  • the flange 1 assumes in its basic form a socket shape and defines an axial support direction A and an axial passage 3, which is cylindrical and extending in the axial support direction A.
  • the cylindrical passage 3 extends and moves in the assembled state of the Flanschismes 1, the control rod or the actuating shaft of an actuator, not shown, with the control rod / actuating shaft not shown in detail control armature, such as a control valve operated by the actuator forces of the Actuator to be transferred non-positively to the control valve.
  • the cylindrical passage 3 is formed concentrically to the axial support direction A.
  • the bush-shaped flange 1 defines Radia ments, wherein two mutually perpendicular radial directions Ri and R 2 in Fig. Lb are indicated.
  • the axial support direction A around the circumferential or torsion U is defined.
  • the flange carrier 1 comprises an actuator-side mounting flange body 5 and a Stellarmatur principleen Befest onlysflanschianu 7.
  • a Stellarmatur principleen Befest onlysflanschisson 7 In the plate-shaped and substantially square Befest onlysflanschianun 5, 7 four mounting holes 55, 57 incorporated to the housing of the actuator, not shown, or the housing of the control armature, not shown, rigidly, immovable with the flange 1 to mount.
  • Both Befest Trentsflansch stresses 5, 7 have a top view square or at least rectangular flange plate 51, 53, at the corners of the mounting holes 55, 57 are introduced to realize the rigid attachment to the housing, not shown, of the actuator or the control valve.
  • a cylindrical inner bushing 61 is arranged centrally, coaxially to Abstütziquessachse A.
  • the inner bush 61 defines on the inside the through-channel 3 over the entire axial length of the flange carrier 1.
  • the inner bush 61 is substantially cylindrical on the outside and inside and bridges the axial distance between the two flange plates 51, 53.
  • La to lc is the cylindrical inner sleeve 61 integrally into the flange plate 51, without forming a recess on the circumference of the connection.
  • the actuator-side flange plate 51 and the inner sleeve 61 are made of one piece, in particular of a piece of metal.
  • the flange plate 51 of the actuator side mounting flange body 5 has a through hole 63 which opens into the cylindrical passage 3 in the inner bushing 61.
  • Stellarmatur proved the cylindrical inner sleeve 61 extends into a square, centrally disposed passage opening 65 and is received engaging.
  • a spring contour offset 21 of the flange carrier 1 is realized by four spring webs 17. From the outside of the cylindrical inner bushing 61, the spring webs 17 extend radially.
  • Both Befest onlysflansch analyses 5, 7 have a base plate shape with fürgangsöffnun- gene 63, 65 for the passage 3.
  • the Stellarmatur difficulte Befest onlysflanschMech 7 is formed both in the radial direction R and in the axial direction A stronger than the actuator drive-side Befest onlysflanschMech 5.
  • the centrally disposed, square passage opening 65 in the mounting flange body 7 is larger than the cylindrical inner sleeve 61 of the actuator-side mounting flange body 5 measured.
  • the inner sleeve 61 is inserted (non-contact) concentrically (except for spring bars 17) in the through hole 65 of the Stellarmatur principleen Befest onlysflanschianus 7, wherein the actuator side Befest onlysflansch stressess 5 through the inner sleeve 61 in an always constant axial distance (in the axial support direction A) to the stellarmatur principleen Befest onlysflanschianu 7.
  • An end portion of the inner sleeve 61 is completely surrounded by the flange plate 53 in the circumferential direction U.
  • the four spring bars 17 are provided, which are substantially flat or lamellar exclusively in the radial directions Ri and R 2 and extend in the axial direction A, without having a Mutteckungslegiskomponente in the circumferential direction U.
  • Two Spring webs 17 lie diametrically opposite each other and extend in the same radial direction plane (Ri or R 2 ).
  • the spring bars 17 There are four spring bars 17 arranged at a 12 o'clock, 3 o'clock, 6 o'clock and 9 o'clock position, in particular according to the front view of FIG. Lb, so that equidistant circumferential distances are provided, which in the in Fig 1 are approximately 90 °.
  • the spring bars 17 have a thickness of a few millimeters or less in order to be elastically bendable in the circumferential direction U.
  • the design of the spring contour portion 21 by means of the four spring bars 17 and their arrangement cause the flange 1 is only in one direction (of the three coordinate directions: circumferential direction U, radial direction R, axial direction A), namely the circumferential direction U, elastic deformation soft.
  • the flange carrier 1 in particular the spring contour section 21, is much more resistant to deformation by a multiple. This causes reaction actuating forces to be diverted into the flange carrier 1 when actuating actuator forces are transmitted from the actuator to the control armature, the torsion component of which leads to significantly greater deformation of the flange carrier 1 in the circumferential direction U than the forces in the axial direction A or radial direction R.
  • the two deformation-resistant mounting mounting body 5, 7 in the circumferential direction U elastically displaced coupled to each other.
  • the elasticity of the spring contour section 21 should be adjusted such that a minimum displacement amplitude of 0.1 mm between the two fastening mounting bodies 5, 7 is achieved during normal operation of the actuator, in particular at the lowest actuator force.
  • This minimum displacement amplitude can be determined by conventional position detection devices, wherein in the examples given a magnetic field sensor arrangement is provided.
  • the spring contour section 21 itself reaches the one-dimensional elastic deformation property only in the circumferential direction U. No separate guide device on the flange carrier or deformation barriers is required, which would prevent a displacement in the other direction A, R.
  • the embodiment according to FIG. 1 represents a particularly simple, space-saving de Structure that can be used as a lantern and yoke in the field of field device technology.
  • the spring contour section 21 renders the flange carrier 1 deformation-soft in the torsional or circumferential direction U, but the flange carrier 1, in particular the spring contour section 21, is deformation-resistant in all radial directions R and in the axial section direction A.
  • the elastic deformation stiffness in the axial support direction and in the radial directions is significantly greater, namely preferably twice as large or a multiple as large as compared to the elastic deformation softness in the circumferential direction U.
  • Torsional forces acting between the Stellarmatur matteren mounting mounting body 7 and the actuator drive-side mounting mounting body 5, with an inductive or capacitive position measuring device, such as a production detection device, can be determined.
  • the spring contour section 21 is designed in a deformation-soft circumferential direction U such that a deformation path of at least 0.1 mm, preferably 0.5 mm or 1 mm is achieved.
  • different minimum deformation paths can be provided in each case, which the respective spring contour section 21 determines. For example, for an actuator with a 10 mm diameter actuator shaft, a minimum deformation path of 0.5% or 1% of the diameter of the actuator shaft through the spring contour section may be permitted.
  • a position detection device such as an inductive or capacitive measuring device, such as a magnetic field sensor, can measure the relative bearing due to elastic deformation of the spring contour section.
  • the position detection device is provided on an actuator-side or Stellarmaturpracticen end of the spring contour portion 21 in order to detect the maximum Relatiwerlagerung can.
  • a magnetic field sensor is provided which bears the reference numeral 23.
  • the magnetic field sensor 23 is associated with a magnetic field source, such as a permanent magnet, which is designated by the reference numeral 25.
  • the magnetic field source 25 is stationary with the deformation-resistant, adjusting armature-side fastening.
  • t Trentsmontage redesign 7 coupled while the magnetic field sensor 23 is fixedly secured to the deformation-resistant, actuator-side mounting flange 5.
  • the magnetic field sensor can detect the elastic deformation movement and forward this to a microcontroller of a positioner (not shown in detail), not shown.
  • the latter can calculate how the actuator forces, in particular a torsional moment, of the actuator, such as a pivoting drive, actually are. It has been found that with the flange carrier 1 according to the invention and the desired deformation structure, namely the spring contour section 21, a deformation movement, even visible from the outside, is generated between the actuator and the control armature, which can easily be detected with an inductive and capacitive measuring method. In this way, only the actuator forces are calculated and other special static disturbance forces can be filtered out easily. Even a visual plausibility check can be achieved with the visible displacement by the flange carrier 1 according to the invention.
  • the entire flange 1 is in one piece, in particular a piece of plastic or a piece of metal, injected or molded.
  • the two Befest Trentsflansch stresses 5, 7 and the spring contour portion 21 together with spring bars 17 are made of a piece of material.
  • the spring bars 17 are not formed by a single plate or arm structure, but each formed by two parallel slightly spaced lamellae to ensure a sufficiently high rigidity of the spring contour portion 21 in both the radial directions R ⁇ , R 2 and the Axialabstützraum A.
  • the lamella plates may have a cross section of 0.2 mm to 1.5 mm and have a circumferential distance from each other of substantially the thickness of the plate lamella.
  • all four spring bars have such a plate plate pair construction.
  • an actuator force measuring device is provided. However, this is not positioned in the area of the actuator, but distally, outside the actuator housing There, it is easily accessible, whereby its operation can be reliably checked.
  • FIG. 2a to 2c another embodiment of a Flanschchis invention is shown.
  • the same reference numerals are used for similar or identical components of the Flanschafters compared to the first embodiment of FIG. La to lc, wherein the reference numerals are increased by 100.
  • the object of the flange carrier 101 according to FIGS. 2a to 2c differs from the flange carrier 1 according to FIGS. 1a to 1c mainly by the spring contour section 121, which is in two parts and forms a weakened structure in the cylindrical inner bushing 161 and the fastening flange bodies 105, 107 with one another deformation soft in the circumferential direction U, but also in the radial direction R, connects.
  • the spring contour section 121 also has four spring webs 117 which extend according to the main extension in the axial support direction A at equidistant circumferential positions (12 o'clock, 3 o'clock, 6 o'clock, 9 o'clock), wherein they have an arm or rod shape.
  • the spring bars 117 open integrally into the actuator side mounting flange 105 and the Stellarmatur practiceen Befest whysflanschianu 107, in particular their flange 151, 153.
  • spring bars 17 a hinge-like connection of the spring bars to the Befest whysflansch- bodies 105 and 107 implemented, wherein in contrast to the embodiment of FIG. 1 pivot axes is aligned in the radial direction (in the embodiment of FIG. 1, the pivot axes in the axial support direction A are effective).
  • the spring contour portion 21 has the desired elastic deformation softness in the circumferential direction U, so that the position means can detect a deformation movement in this direction.
  • the flange carrier 101 in order to force an exclusive deformation movement in the circumferential direction U, has an additional, rigid recapturing sleeve 147 which avoids deflection of the spring webs 117 from their axial extent direction in the radial direction R, so that the radial direction components directly occur when an operational reaction force is introduced be accommodated in the Umgreifhülse 147 without a deformation of the Flanschyess 101 occurs in the action of the actuator forces in the radial direction.
  • a flange carrier 101 is created with a single preferred deformation direction, in the circumferential direction U, whereby the desired predetermined deformation direction is fixed and use as part of a measuring device is possible.
  • the respective spring bar 117 is made reinforced at the foot 141 at the transition to the actuator side mounting flange body 107 to axially form a weakened arm portion 143, for example, at a passage diameter D of 25 mm, a thickness of less than 5 mm, preferably between 1 mm and May have 3 mm. Also at the opposite end portion, which merges into the actuator-side mounting flange 105, the spring bar 117 is reinforced.
  • Ausweichaussparungen 145 are formed in a wide slot shape in the inner sleeve 161 in order to achieve the weakening of the Flanschlichlichenstein 101 and thus the deformation softness in the circumferential direction U.
  • Such a flange support 101 has a high dimensional stability and dimensional stability in the axial support direction A, wherein the deformation in the circumferential direction is significantly lower.
  • the flange plates 151, 153 of the mounting flange body 105, 107 are coupled together by the inner sleeve 161 (without engagement with the through hole 165).
  • the inner sleeve 161 has the radial-passage slot recesses 145, which cause the deformation capability in the circumferential direction U, wherein the vast foot portion of the inner sleeve 61 is integral with the flange plate 153 of the Stellarmatur practiceen Befest Trentsflansch stressess 107 executed.
  • the head portion of the inner bushing 161 opposite the integrally formed foot portion extends only partially into the through hole 163 of the flange plate 151 of the actuator side mounting flange body 105. Only the spring webs 117 of the inner bush 161 constitute the structural elastic force transmitting connection between the two flange plates 151, 153 of the mounting flange body ,
  • the magnetic field sensor 125 is accommodated in the flange plate 153 while the magnetic field source 125 is housed or disposed on the sleeve end portion 159 which is at a gap distance to the inside of the flange plate 153. Also, the flange carrier 101 is part of a measuring device and becomes such when the position measuring device is combined with it.
  • the magnetic field sensor 23, 123 may be connected to a positioner, not shown, to calculate and output functional test statements, maintenance statements, etc. based on the measurement data of the position measuring device.
  • the elastic deformation softness in deformation preferred direction (U) may be limited by a movement stop, which is formed for example by the through hole 13 in the embodiment of FIG. 2a to 2c.
  • This movement limitation of the flange carrier 1, 101 in the deformation preferred direction (circumferential direction U) is provided in order to avoid a deformation of the flange carrier beyond the yield strength or the like.
  • such an overload stop is designated by the reference numeral 171, the maximum amplitude of movement of the flange carrier 101 being determined by the axial dimension gap on the overload stop 171.

Abstract

L'invention concerne une bride de support servant au support mutuel d'un organe de commande, par exemple une soupape de commande d'une installation technique, par exemple une installation pétrochimique, une installation de traitement de produits alimentaires, une installation nucléaire ou similaire, et d'un mécanisme de commande actionnant l'organe de commande, par exemple un mécanisme pneumatique ou électrique de levage ou de pivotement. La bride de support n'est déformable que dans une seule direction préférentielle de déformation, par exemple une direction périphérique entourant la direction d'appui axiale de la bride de support.
PCT/EP2017/068358 2016-08-02 2017-07-20 Bride de support servant au support mutuel d'un organe de commande et d'un mécanisme de commande et dispositif de mesure WO2018024496A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016114285.9 2016-08-02
DE102016114285.9A DE102016114285A1 (de) 2016-08-02 2016-08-02 Flanschträger zum gegenseitigen Tragen einer Stellarmatur und eines Stellantriebs und Messeinrichtung

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WO2018024496A1 true WO2018024496A1 (fr) 2018-02-08

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CN (1) CN207848530U (fr)
DE (1) DE102016114285A1 (fr)
WO (1) WO2018024496A1 (fr)

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Publication number Priority date Publication date Assignee Title
DE202022104260U1 (de) 2022-07-27 2022-09-12 Samson Aktiengesellschaft Messeinrichtung

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GB2133885A (en) * 1983-01-20 1984-08-01 Simmonds Precision Products Torque measurement
DE3820838A1 (de) 1988-06-21 1990-01-04 Bbc Reaktor Gmbh Einrichtung zum messen des drehmomentes einer durch einen stellantrieb bewegbaren armatur
WO1992001212A1 (fr) * 1990-07-09 1992-01-23 Westinghouse Electric Corporation Procede et apprareil de mesure de charges exercees sur une tige de vanne dans un ensemble a vanne motorisee
EP0656500A1 (fr) * 1993-12-03 1995-06-07 Westinghouse Electric Corporation Dispositif de mesure du couple et de la vitesse d'un robinet entraîné par moteur
US5454273A (en) * 1994-02-09 1995-10-03 Westinghouse Electric Corporation Motor operated valve actuator diagnostic system and test stand
WO1997008527A1 (fr) * 1995-08-31 1997-03-06 Snr Roulements Dispositif de mesure de couple de torsion d'un arbre tournant
DE29811115U1 (de) 1998-06-22 1999-10-28 Istec Gmbh Meßsystem zur Erfassung der Spindelkraft an Armaturen
US20040050178A1 (en) * 2002-09-13 2004-03-18 Gastops Ltd. Apparatus for detecting torque, axial position and axial alignment of a rotating shaft
US20160178458A1 (en) * 2014-12-23 2016-06-23 Samson Aktiengesellschaft Spring body for a force transducer, such as a torque-and/or tension/compression-force measuring cell

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DE3620122A1 (de) * 1985-06-21 1987-01-02 Teldix Gmbh Stellantrieb
US8978480B2 (en) * 2011-08-02 2015-03-17 The United States Of America, As Represented By The Secretary Of The Navy Recursive hexapod system and method for multiaxial mechanical testing
DE102014019547B3 (de) * 2014-12-23 2016-05-12 Samson Ag Drehmoment- und Winkelsensor und Stellantrieb

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Publication number Priority date Publication date Assignee Title
GB2133885A (en) * 1983-01-20 1984-08-01 Simmonds Precision Products Torque measurement
DE3820838A1 (de) 1988-06-21 1990-01-04 Bbc Reaktor Gmbh Einrichtung zum messen des drehmomentes einer durch einen stellantrieb bewegbaren armatur
US4977782A (en) * 1988-06-21 1990-12-18 Abb Reaktor Gmbh Device for measuring the torque of a valve moved by an actuator
WO1992001212A1 (fr) * 1990-07-09 1992-01-23 Westinghouse Electric Corporation Procede et apprareil de mesure de charges exercees sur une tige de vanne dans un ensemble a vanne motorisee
EP0656500A1 (fr) * 1993-12-03 1995-06-07 Westinghouse Electric Corporation Dispositif de mesure du couple et de la vitesse d'un robinet entraîné par moteur
US5454273A (en) * 1994-02-09 1995-10-03 Westinghouse Electric Corporation Motor operated valve actuator diagnostic system and test stand
WO1997008527A1 (fr) * 1995-08-31 1997-03-06 Snr Roulements Dispositif de mesure de couple de torsion d'un arbre tournant
DE29811115U1 (de) 1998-06-22 1999-10-28 Istec Gmbh Meßsystem zur Erfassung der Spindelkraft an Armaturen
US20040050178A1 (en) * 2002-09-13 2004-03-18 Gastops Ltd. Apparatus for detecting torque, axial position and axial alignment of a rotating shaft
US20160178458A1 (en) * 2014-12-23 2016-06-23 Samson Aktiengesellschaft Spring body for a force transducer, such as a torque-and/or tension/compression-force measuring cell

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202022104260U1 (de) 2022-07-27 2022-09-12 Samson Aktiengesellschaft Messeinrichtung
WO2024023226A1 (fr) 2022-07-27 2024-02-01 Samson Aktiengesellschaft Dispositif de mesure

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CN207848530U (zh) 2018-09-11

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