WO2018024496A1

WO2018024496A1 - Flange support for reciprocal carrying of an actuator part and of an actuating drive, and measurement device

Info

Publication number: WO2018024496A1
Application number: PCT/EP2017/068358
Authority: WO
Inventors: Stefan Kolbenschlag; Rainer Oberheim
Original assignee: Samson Aktiengesellschaft
Priority date: 2016-08-02
Filing date: 2017-07-20
Publication date: 2018-02-08
Also published as: DE102016114285A1; CN207848530U

Abstract

The invention relates to a flange support for reciprocal carrying of an actuator part, such as an actuating valve, of a process technology plant, such as a petrochemical plant, a food processing plant, a nuclear power plant, or the like, and of an actuating drive which actuates the actuator part, such as a pneumatic or electric lifting or slewing drive, wherein the flange support is designed to be deformation-weak in only one single preferred deformation direction, such as a circumferential direction surrounding an axial supporting direction of the flange support.

Description

Flange support for mutual support of a control armature and an actuator

and measuring equipment

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.

It is generally known to measure a torque at a rotary actuator for actuating the control valve of the process plant the dynamic, dependent on the rotational drive force Abstützgegenkraft the rotary drive on the flange, which rigidly coupled to each other, the housing of the rotary drive and the control valve. From DE 298 11 115 Ul a measuring system for detecting the spindle force of a control valve is known. With the measuring system a malfunction of the valve is to be identified, especially when increased friction due to aging or material deposition lead to very large restoring forces. It is known to mount a force sensor in the form of a force measuring ring as a washer on a connecting screw on the support flange between the control armature and the actuator.

DE 38 20 838 AI discloses a device for measuring the torque of a movable actuator by a servo-valve. In one embodiment, 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 Flanschträger-section, which is referred to as free rotation and is formed by a thin flange wall. It is known that strain gauges have a stretching or compressive, elastic Deformation detected near the surface, with smallest deformations in Γη-ΒεΓείΛ be detected. A strain gauge gives readings based on the change in electrical resistance and direct information about the voltage acting there.

It was found in the known measuring systems that no high accuracy can be reliably ensured because a variety of predictable and unpredictable disturbing forces acting on the support flange, with the known measuring concept no direct precise inference to the actual output, inner force allow.

It is an object of the invention to overcome the disadvantages of the prior art, in particular a flange support for carrying a control armature, such as a control valve of a process plant, and provide the actuator armature actuating actuator, with the one to be transmitted from the actuator to the control armature adjusting force how a torque can be precisely determined.

This object is solved by the features of claim 1.

Thereafter, a Flanschträger 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. It should be understood that 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. When the flange carrier is fixedly mounted to a plant structure, the flange carrier can carry both the control armature and the actuator as a single support member. Of course, additional additional support and support elements can be provided. In the field of field devices, 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. However, 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 Abstützsäulen. The flange has according to its first part of the term two sides of the flange, namely the actuator side flange and the Stellarmaturseitigen 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. Usually, 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. In this case, 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.

According to the invention, 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 Stellarmaturseitigen 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 Nennstellkräfte of the actuator knowledge. For this purpose, empirical values and flange carrier-specific deformation parameters, such as a modulus of elasticity of the flange carrier in the preferred deformation direction, 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.

Based on its supporting function, 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. Preferably, the deformation preferred direction coincides with exactly one, in particular the circumferential direction of the Flanschträgers, 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. According to the invention, the actuator-side flange of the Flanschträgers and the Stellarmaturseitige flange of the Flanschträgers 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.

In a preferred embodiment of the invention, the flange carrier has a Stellantriebssei- term flange or mounting flange body, a Stellarmaturseitigen flange or Befigungsungsflanschkörper 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 Befestigungsflanschkörper resiliently into a starting position. Preferably, 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. Additionally or alternatively, 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.

Preferably, 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 Flanschträgers, as in the axial support direction and in the radial direction.

In a preferred embodiment of the invention, the deformation preferred direction defining the flange support structure is not linear, but circular, preferably concentric about the axial support direction.

In a further development of the invention, 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 Flanschträgers 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.

In a preferred embodiment of the invention, 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 Stellarmaturseitigen flange and an actuator-side flange is accompanied in Deformationsvorzugsrichtung, the deformation relative movement by means of a position detection device, such as an inductive or capacitive measuring device, can be determined. 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. In this case, 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.

In particular, 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.

In a preferred embodiment of the invention, 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. Preferably, 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.

Preferably, 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.

In a preferred embodiment of the invention, the spring contour portion of the Flanschträgers 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, Stellarmaturseitigen 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. Preferably, the orientation of elongated spring webs is arranged so that they are bendable in the preferred deformation direction. Upon application of operating reaction forces transmitted by the flange carrier, they press on the spring bars, which allow a displacement of the actuator drive side flange relative to the Stellarmaturseitigen flange only in the preferred deformation direction.

In a further development of the invention, the plurality of spring bars coupling a Stellarmaturseitigen Befestigungsflanschkörper elastically to an actuator side mounting body, the spring bars are structured / shaped and / or arranged such that the Federkonturabschnitt 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.

Preferably, the plurality of spring bars and the Stellarmaturseitige flange and the drive-side flange are made of one piece, such as a plastic piece or piece of metal.

In a further development of the invention, each spring bar extends at a certain circumferential position in particular only axially (perpendicular to contact surface of the stellarmaturseitigen and Stellantriebsseitigen 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. In this way, 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 Flanschträgers and its components, flange, spring contour section, spring bars, despite the deformation in one direction. Preferably, in particular in a one-piece design with the flanges, 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- turseitigen flange and goes there. In one embodiment, 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.

In a preferred embodiment of the invention, 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.

In an alternative or combinable embodiment of the invention, 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.

In a further development of the invention, the flange carrier comprises an actuator-side and a Stellarmaturseitigen Befestigungsflanschkörper or flange. This Befestigungs- 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- Sßenanlagenflächen 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.

In a further development of the invention, 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. In this way, the respective Befestigungsflanschkörper has the sleeve-like or sleeve-shaped basic shape.

The flange has the weakened Federkonturabschnitt 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. According to the invention, 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 Federkontoabschnitts and a Stellarmaturseitigen 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 greater the detected deformation deformation or the deformation amplitude, which allows the elastically yielding spring contour section, the greater the effective actual operating force, from which conclusions can be drawn, inter alia, on the state of wear of the actuator and the control valve. 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. In particular, it is to be understood that 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.

According to the invention, 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. In particular, 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. According to the invention, 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. If 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 Federkonturabschnitt at a force transmission in normal operation. In the case of an actuator of 20 mm, with a 0.5% deformation path component, an absolute deformation path of at least 1 mm must also be assumed, which is already established at normal, in particular low operating forces.

It was found that a deformation path of at least 0.1 mm is sufficient in particular to use commercial capacitive or inductive or potentiometric position measuring methods. With 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.

In contrast to the prior art, 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 Stellarmaturseitigen 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.

Furthermore, 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.

Preferred embodiments are specified in the subclaims.

Further characteristics, merlanals and advantages of the invention will become apparent from the following description of preferred embodiments of the invention with reference to the accompanying drawings, in which:

Fig. La is a perspective view of a erfmdungs contemporary flange of a first

Execution;

Fig. Lb is an end view of the flange of Figure la on the Stellarmaturseitige end side of the flange.

Fig. Lc is a side view of the flange according to Fig. La and lb

2 a is a perspective view of a flange carrier according to the invention of a second

Execution; 2b shows an end view of the flange carrier of Figure 2a on the Stellarmaturseitige end side of the flange. and

Fig. 2c is a side view of the flange according to Fig. 2a and 2b.

In Fig. La to lc 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. Through the cylindrical passage 3 extends and moves in the assembled state of the Flanschträgers 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. Around 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 Stellarmaturseitigen Befestigungsflanschkörper 7. In the plate-shaped and substantially square Befestigungsflanschkörpern 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 Befestigungsflanschkörper 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. As a further main component of the Flanschträgers 1, a cylindrical inner bushing 61 is arranged centrally, coaxially to Abstützrichtungsachse 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. Carrier 1 of Fig. 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. Stellarmaturseitig the cylindrical inner sleeve 61 extends into a square, centrally disposed passage opening 65 and is received engaging.

In order to obtain an elastically deformable connection, movable in a preferred deformation direction U, between the two mounting flange bodies 5, 7, 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 Befestigungsflanschkörper 5, 7 have a base plate shape with Durchgangsöffnun- gene 63, 65 for the passage 3. The Stellarmaturseitige Befestigungsflanschkörper 7 is formed both in the radial direction R and in the axial direction A stronger than the actuator drive-side Befestigungsflanschkörper 5. As in particular in Fig. La it can be seen, 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 Stellarmaturseitigen Befestigungsflanschkörpers 7, wherein the actuator side Befestigungsflanschkörpers 5 through the inner sleeve 61 in an always constant axial distance (in the axial support direction A) to the stellarmaturseitigen Befestigungsflanschkörper 7. An end portion of the inner sleeve 61 is completely surrounded by the flange plate 53 in the circumferential direction U.

In order to realize the weakened, elastically yielding spring contour portion 21 between the inner sleeve 61 (13) integrally formed with the actuator side flange plate 51 and the actuator side flange plate 53 of the mounting flange body 7, 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 Erstteckungsrichtungskomponente 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 ).

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. In the other coordinate directions A, R, 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.

Due to the arrangement of the spring bars 17 and their areal extent both in the radial direction R and in the axial support direction A, 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.

In the embodiment of the flange carrier 1 shown in FIG. 1, 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. In this respect, 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.

It is clear that three or more spring webs 17, in particular at equidistant circumferential distances from one another, can be provided in order to form the desired spring contour section 21. 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 Stellarmaturseitigen 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. In the case of different actuators, 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.

The movement amplitude is so great that 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. Preferably, the position detection device is provided on an actuator-side or Stellarmaturseitigen end of the spring contour portion 21 in order to detect the maximum Relatiwerlagerung can.

In the embodiment illustrated in FIGS. 1 a and 1 b, 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. As can be seen in FIG. 1a, the magnetic field source 25 is stationary with the deformation-resistant, adjusting armature-side fastening. tigungsmontagekörper 7 coupled while the magnetic field sensor 23 is fixedly secured to the deformation-resistant, actuator-side mounting flange 5. In a deformation movement in the circumferential direction of at least 0.1 mm, 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. Based on empirical values and stored data with regard to the modulus of elasticity of the spring contour section, 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.

Preferably, the entire flange 1 is in one piece, in particular a piece of plastic or a piece of metal, injected or molded. The two Befestigungsflanschkörper 5, 7 and the spring contour portion 21 together with spring bars 17 are made of a piece of material.

Preferably, 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 Axialabstützrichtung 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. Preferably, all four spring bars have such a plate plate pair construction.

If the flange carrier 1 is used in combination with the magnetic field sensor 23, an actuator force measuring device according to the invention 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.

In Fig. 2a to 2c, another embodiment of a Flanschträgers invention is shown. For ease of reading the figure description, the same reference numerals are used for similar or identical components of the Flanschträgers 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 Stellarmaturseitigen Befestigungsflanschkörper 107, in particular their flange 151, 153. In this way, similar to the embodiment of FIG. 1 (spring bars 17) a hinge-like connection of the spring bars to the Befestigungsflansch- 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).

As already stated, 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. However, in order to force an exclusive deformation movement in the circumferential direction U, the flange carrier 101 according to FIG. 2 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 Flanschträgers 101 occurs in the action of the actuator forces in the radial direction. In this way, 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. In the circumferential direction adjacent to the spring bars 117 Ausweichaussparungen 145 are formed in a wide slot shape in the inner sleeve 161 in order to achieve the weakening of the Flanschträgers 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.

In the flange carrier 101, 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 Stellarmaturseitigen Befestigungsflanschkörpers 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. In the embodiment according to FIGS. 2 a to 2 c, 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.

The features disclosed in the foregoing description, the figures and the claims may be of importance both individually and in any combination for the realization of the invention in the various embodiments.

Samson AG

LIST OF REFERENCE NUMBERS

1, 101 flange carrier

3, 103 through-channel

5, 105 actuator side mounting flange body

7, 107 Stellarmaturseitiger mounting flange body

17, 117 Spring bar

21, 121 Spring contour section

23, 123 Magnetic field sensor

25, 125 magnetic field source

51, 53, 151, 153 flange plate

55, 57, 155, 157 mounting holes

61, 161 inner bush

63, 65, 163, 165 passage opening

141 head of the spring bar

143 arm section

145 alternate recesses

171 overload stop

A support direction

D passage diameter

Ri, R ₂ , R Radial direction

U circumferential direction

Claims

claims

1. flange support (1, 101) for mutual support of a control valve, such as a control valve, a process engineering plant, such as a petrochemical plant, a food processing plant, a nuclear power plant or the like, and an actuating armature actuating actuator, such as a pneumatic o- electric Lifting or swivel drive, characterized in that the flange (1, 101) only in a single deformation preferred direction, such as an axial support direction (A) of the Flanschträgers (1, 101) surrounding the circumferential direction (U), deformed soft.

Second flange (1, 101) according to claim 1, characterized in that it has an axial supporting direction (A), a support direction (A) perpendicular radial direction (R) and a support direction (A) surrounding and perpendicular to the radial direction (R) Defined circumferential direction, wherein the preferred deformation direction coincides with exactly one, in particular the circumferential direction (U), the three directions (A, R, U), wherein the flange (1, 101) in the other directions, in particular both in the axial support direction (A) as well as in Radia direction (R), deformation is more rigid.

3. flange carrier (1, 101) according to claim 1 or 2, characterized in that it has an actuator-side flange (5, 105) of the Flanschträgers (1, 101) and a Stellarmaturseitigen flange (7, 107) of the Flanschträgers (1, 101 ) in resilient deformation deflecting Federkonturabschnitt (21, 121), which is weakened and / or configured such that the flange is deformation soft only in the preferred deformation direction, preferably in the circumferential direction (U), preferably smoother than in the other coordinate directions, as in axial support direction (A) and in the radial direction (R), the Flanschträgers (1, 101).

4. flange carrier (1, 101) according to claim 3, characterized in that a deformation stiffness of the spring contour portion (21, 121) in the other Coordinate directions, such as in the axial supporting direction (A) and in the radial direction (R), the Flanschträgers (1, 101) by at least 50%, preferably 100%, in particular by three, four or five times greater than a deformation stiffness of the spring contour section (21, 121) in a deformation preferential direction, such as the circumferential direction.

5. flange (1, 101) according to any one of the preceding claims, characterized in that it, in particular the spring contour portion (21, 121), so deformed soft in the deformation preferred direction is that upon transmission of an operating force, such as an operating torque, from the actuator an elastic deformation relative movement between a Stellarmaturseitigen flange (7, 107) and a stellantriebsseiti- flange (5, 105) in Deformationsvorzugsrichtung goes on the control armature, wherein the deformation relative movement by means of a position detection device, such as an inductive or capacitive or potentiometric measuring device, can be determined.

6. flange carrier (1, 101) according to claim 5, characterized in that the position detecting means by a magnetic field sensor (23, 123) and a magnetic source (25, 125) is formed, wherein the magnetic field sensor (23, 123) and the magnetic source (25 , 125) are arranged in the region of the spring contour section (21, 121) in such a way that the deformation relative movement of the magnetic field sensor (23, 123) and the magnetic field source (25, 125) in the deformation preferred direction is detected.

7. flange carrier (1, 101) according to any one of the preceding claims, characterized in that a spring contour portion (21, 121) of the Flanschträgers (1, 101) by a plurality, preferably at least three or four spring bars (17, 117) is realized, the an actuator-side flange (5, 105) and a Stellarmaturseitigen flange (7, 107) resiliently coupled to each other, in particular the spring bars (17, 117) are aligned such that they make the flange (1, 101) elastic deformation deformation in the direction of deformation ,

8. flange carrier (1, 101) according to claim 7, characterized in that the plurality of spring bars (21, 121) a Stellarmaturseitigen Befestigungsflanschkörper (5, 105) elastically coupled to an actuator-side Befestigungsfianssch- body (7, 107), wherein the spring bars structured in such a way and / or that the spring contour section (21, 121) is soft in deformation only in the deformation preferred direction and is more resistant to deformation in the other directions, wherein the plurality of spring webs (17, 117) and the stellar maturseitige flange (7, 107) and the actuator-side flange (5, 105) are made in one piece and / or each spring bar (17, 117) extends at a certain circumferential position exclusively axially, radially outwards, without circumferential direction component and / or on the one hand in a sleeve-shaped connection portion the actuator-side flange (5, 105) and on the other hand in a sleeve-shaped Anbi transition section of the stellarmaturseitigen flange (7, 107).

9. flange (1, 101) according to claim 7 or 8, dadurchgekennzeic et hn, that the plurality of spring bars (17, 117) are column-shaped or plate-shaped, in particular the plate-shaped spring webs (17, 117) by a lamellar pair extending parallel Platelets are realized, which are arranged in particular in a circumferential distance (U), in particular less than 2 mm.

10. flange carrier (1, 101) according to one of claims 7 to 9, dadurchgeken nz eichnet that the plurality of spring bars (17, 117) coupling a Stellarmaturseitigen Befestigungsflanschkörper elastically to an actuator side mounting flange body, wherein the spring bars (17, 117) structured and in that the spring contour section (21, 121) is deformingly soft in the preferred deformation direction and at least one further direction, wherein the spring contour section (21, 121) additionally comprises a deformation barrier, such as a stop or an encompassing sleeve (147), which comprises a Deformation of the spring contour portion (21, 121) in the at least one further direction (R) locks such that a relative deformation movement is accompanied exclusively in the deformation preferred direction.

11. flange carrier (1, 101) according to any one of the preceding claims, characterized in that an actuator side and a Stellarmaturseitiger Befestigungsflanschkörper (5, 105, 7, 107) of the Flanschträgers (1, 101) each have a plate shape, said plate-shaped flange ( 5, 105, 7, 107) have axially opposed inner surfaces on which a magnetic field source (25, 125) and a magnetic field sensor (23, 123) are arranged axially diametrically opposite, and / or these plate-shaped mounting terminals facing away from each other outer contact surfaces, the are formed such that a flat contact with a correspondingly shaped housing of the actuator or the control valve is allowed.

12. flange carrier (1, 101) according to any one of the preceding claims, characterized in that an actuator side and a Stellarmaturseitiger Beigungsflanschkörper (5, 7, 105, 107) each have a through hole (63, 65, 163, 165) in particular concentric to axial support direction (A) through which an actuator of the actuator and / or the control armature can extend, wherein the Befestigungsflanschkörper (5, 7, 105, 107) by a particular cylindrical inner sleeve (61, 161) with a through-channel (3, 103) which is substantially at least partially congruent with the passage openings (63, 65, 163, 165) and / or along which the actuator is displaced, wherein the spring contour portion (21, 121) for elastic deformation soft coupling of the mounting flange body ( 5, 7, 105, 107) with the inner bush (61, 161) is provided.

13. flange carrier (1, 101) according to any one of the preceding claims, characterized in that the spring contour portion (21, 121) is configured such that by the spring contour portion (21, 121) upon transmission of an operating force, such as an operating torque, of the actuator on the control armature an elastic deformation movement, in particular between a Stellan- drive-side starting point of the spring contour portion (21, 121) and a stellar- maturity end of the spring contour portion (21, 121), with a deformation of at least 0.1 mm or at least 0.5 % or 1% of a minimum cross-sectional thickness, such as a diameter, an actuating rod or actuating shaft of the actuator is associated.

14. flange carrier (1, 101) according to claim 13, characterized in that the spring contour portion (21, 121) is weakened such that in a normal operation of the control valve, in particular at normal operating friction, for providing the control armature, the Federkonmrabschnitt (21, 121) an elastic deformation movement with a deformation path of over 0.1 mm, 0.2 mm, 0.5 mm or 1.0 mm or of at least 0.5%, 1%, 2%, 5% or 10% of the cross-sectional thickness, such as the diameter, the adjusting rod or actuating shaft of the actuator is accompanied, wherein in particular the spring contour portion (21, 121) permits an elastic deformation movement with a maximum deformation of at least 1 mm, 2 mm, 3 mm and in particular of at most 5 mm, 7 mm or 10 mm and / or an elastic deformation path amplitude of up to 3 mm, preferably up to 2.5 mm or up to 2 mm.

15. A device for measuring an operating force of an actuating armature of a process-technical plant actuated actuator comprising a trained according to one of the claims flange (1, 101) on which the control armature and the actuator are mounted and / or mounted, wherein the flange (1 , 101) is associated with a position detection device such that the elastic deformation, which is caused by the spring contour portion, is detected in the deformation preferred direction.