Flange support for mutually supporting a control valve and an actuator and measuring device

Abstract

Flange support (1, 101) for transmitting load-bearing and bearing forces between a housing of a control valve of a process engineering plant and a housing of an actuator that actuates the control valve, comprising an axial through-channel (3) for an actuating rod or actuating shaft of the actuator for actuating the control valve, characterized in that the flange support (1, 101) is designed to be deformation-soft only in a single preferred deformation direction.

Description

[0001] The invention relates to a flange support for mutually supporting 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 an actuator that actuates the control valve, such as a pneumatic actuator, in particular a pneumatic lifting or pivoting actuator. Furthermore, the invention relates to a measuring device that utilizes the flange support according to the invention.

[0002] It is generally known to measure the torque of a rotary actuator used to operate the control valve of a process plant by measuring the dynamic support counterforce of the rotary actuator on the flange support, which rigidly couples the housings of the rotary actuator and the control valve, which is dependent on the rotary drive force. DE 298 11 115 U1 discloses a measuring system for detecting the spindle force of a control valve. The measuring system is intended to identify malfunctions of the valve, particularly when increased friction values ​​due to aging or material deposits lead to very high actuating 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 valve and the actuator.

[0003] DE 38 20 838 A1 discloses a device for measuring the torque of a control valve movable by an actuator. In one embodiment, the actuator housing and the control valve housing are connected to each other via a bushing-shaped flange support, with strain gauges arranged on a weakened flange support section, referred to as the free rotation, formed by a thin flange wall. Strain gauges are known to detect stretching or compressive elastic deformation close to the surface, detecting even the smallest deformations in the µm range. A strain gauge provides measured values ​​based on the change in its electrical resistance and provides direct information about the voltage acting there.

[0004] DE 10 2014 019 546 B3 relates to a spring body for a force transducer or a load cell for use in the field of process engineering.

[0005] DE 10 2014 019 547 B3 relates to a torque and angle sensor for determining a torque to be transmitted from a drive part to an output part as well as an absolute angle of rotation of the output part.

[0006] DE 36 20 122 A1 concerns an actuator.

[0007] US 8 978 480 B2 relates to a multiaxial test apparatus, methods and systems for materials testing and characterization.

[0008] It has been shown with the known measuring systems that high measuring accuracy cannot be reliably ensured because a large number of predictable and unpredictable disturbing forces acting on the support flange do not allow a direct, precise conclusion to be drawn about the actual internal actuating force delivered using the known measuring concept.

[0009] It is an object of the invention to overcome the disadvantages of the prior art, in particular to provide a flange support for supporting a control valve, such as a control valve of a process plant, and an actuator actuating the control valve, with which an actuating force to be transmitted from the actuator to the control valve, such as a torque, can be precisely determined.

[0010] This problem is solved by the features of claim 1.

[0011] According to this, a flange support is provided 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 pneumatic or electric actuator, such as a quarter-turn actuator, that actuates the control valve. In the assembled state, the flange support holds the control valve to the actuator by transferring the supporting and bearing forces between the respective housings, so that in particular no further supporting structure is necessary. If the control valve is permanently attached to a process plant line, the control valve supports the actuator via the flange support. The same applies vice versa if the actuator is mounted on a stationary component of the process plant and the control valve is freely supported on it.It should be understood that both the control valve and the flange support may be mounted on a part of the process plant, so that only a portion of the load-bearing forces are actually transmitted by the flange support between the housings of the control valve and the actuator. The flange support is designed to transmit reaction forces between the housings of the actuator and the control valve that arise when the actuator moves the control valve to the desired position. These actuating forces are also referred to below as operating actuating forces and arise, for example, depending on the fluid flow rate in the process plant line and / or the static and sliding friction forces of the moving elements of the control valve and the actuator. If the flange support is fixedly mounted to a plant structure, the flange support can support both the control valve and the actuator as a single load-bearing element.Of course, further additional carrying and support elements can be provided. In the field of field devices, the flange carrier is also called a lantern, supporting frame, upper part or yoke, whereby these supporting structures are formed by support columns extending mainly in the axial support direction and arranged at, for example, equidistant circumferential distances from one another in order to enable external access to the actuating rod or actuating shaft, which run and are moved inside the lantern or yoke. The supporting structure or the flange carrier can, however, also form a closed tubular structure which is radially open or weakened in sections, in particular to form the support columns. According to the first part of the term, the flange carrier has two flange sides, namely the actuator-side flange and the control valve-side flange, whereby a rigid, immovable fastening of the respective housing of the actuator orof the control valve to the flange carrier. The flange carrier can be connected in one piece to the respective housing of the control valve and the actuator. Typically, a flange carrier can have a central passage through which an actuating element, such as the actuating rod or the actuating shaft, of the actuator or control valve can extend. The actuating rod or actuating shaft has a minimum cross-section, such as a diameter of, for example, 3 mm or 5 mm up to over 300 mm, depending on the design of the actuator and the control valve. The actuator, particularly in process engineering plants, receives electrical or pneumatic drive energy with which an actuating force is generated in order to execute a lifting or swiveling movement of the control valve.The actuator can deliver a nominal actuating force that can be designed to overcome a mechanical actuating spring and / or can be in the range from 100 N to 600 N, 800 N, 1000 N, 2000 N and possibly even higher.

[0012] According to the invention, the flange support is designed such that it is deformably flexible only in a single preferred deformation direction, such as a circumferential direction surrounding an axial support direction of the flange support. The only preferred deformation direction is defined by the flange support. When the actuator force is transmitted from the actuator to the control valve, the flange support permits elastic deformation only in this preferred deformation direction, so that a flange section on the actuator side is displaced relative to a flange section on the control valve side only in the predetermined preferred deformation direction. Based on the displacement or shift of the respective two flange sections, the applied nominal actuating forces of the actuator can be determined.For this purpose, empirical values ​​and flange-beam-specific deformation parameters, such as the elastic modulus of the flange beam in the preferred deformation direction, can be used to calculate the applied nominal actuating force after recording the elastic deformation movement in the preferred deformation direction. The deformation is elastic, so that in the absence of load – when the actuating force is removed – the flange beam is returned along the preferred deformation direction to its initial position / state, in which, in particular, exclusively static load-bearing forces act.

[0013] Based on its supporting function, the flange support defines a coordinate system originating from the actuator or the control valve, and defines an axial support direction, which in particular coincides with the actuating direction of the actuator and / or the longitudinal extension of the actuating rod, a radial direction perpendicular to the support direction, preferably meaning all radial directions extending radially from the axial support direction in a star shape, and a circumferential direction surrounding the support direction and perpendicular to the radial direction. Preferably, the preferred deformation direction coincides with exactly one of these three coordinate directions, in particular the circumferential direction of the flange support, wherein the flange support is designed to be more deformation-resistant in the remaining directions, in particular both in the axial support direction and in the radial direction.According to the invention, the actuator-side flange of the flange support and the control valve-side flange of the flange support move along the predefined preferred deformation direction when drive reaction forces act between the actuator and the control valve, particularly in excess of the static load-bearing forces. This relative deformation movement, which is oriented in the preferred deformation direction, is measured and, in particular, processed computationally to draw conclusions about the current output actuator forces. The measured actuator forces can also be used to draw conclusions about the functionality of the field device.

[0014] In a preferred embodiment of the invention, the flange support has a flange or mounting flange body on the actuator side, a flange or mounting flange body on the control valve side, and a spring contour section that connects the two flanges to one another in a resiliently movable manner in the preferred deformation direction. The spring contour section can function as a resilient coupling joint and, in particular, be designed to resiliently return the deployed mounting flange body to an initial position. The spring contour section is preferably implemented by a plurality of spring webs, which extend, in particular, integrally between the aforementioned flanges.The spring movement of the flanges by means of the spring contour section can be achieved by separate, movably mounted guide or joint elements that allow displacement of the two flanges only in the preferred deformation direction. Additional spring elements can be provided for returning to the predetermined starting position. Additionally or alternatively, the spring contour section can be provided with a deformation lock that prevents movement of the spring contour section in a direction other than the preferred deformation direction.

[0015] Preferably, the spring contour section is designed without guide or joint elements and without additional spring elements and is weakened and / or designed on the basis of a one-piece metal or plastic part in such a way that the flange carrier is deformation-soft only in the preferred deformation direction, preferably only in the circumferential direction, preferably more deformation-soft than in all other coordinate directions of the flange carrier, such as in the axial support direction and in the radial direction.

[0016] In a preferred embodiment of the invention, the preferred deformation direction defining the flange support structure is not linear, but circular, preferably concentric around the axial support direction.

[0017] 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 flange carrier is at least 50%, preferably 100%, in particular at least three times, at least four times or at least five times greater than an elastic deformation stiffness of the spring contour section in the preferred deformation direction, such as the circumferential direction.

[0018] In a preferred embodiment of the invention, the flange support, in particular the spring contour section, is designed to be elastically deformable in the preferred deformation direction such that upon transmission of an operating actuating force, such as an operating torque, from the actuator to the control valve, an elastic relative deformation movement occurs between a flange on the control valve side and a flange on the actuator side in the preferred deformation direction, wherein the relative deformation movement can be determined by means of a position detection device, such as an inductive or capacitive measuring device. The executed amplitude of the relative deformation movement is set due to the structural design of the spring contour section, so that the position detection device can also detect minimum actuating forces of the actuator due to a deformation displacement of the flanges in the preferred deformation direction.Deformation movement amplitudes between the two flanges can be 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.

[0019] In particular, inductive, capacitive, or potentiometric measuring devices require larger movement amplitudes to generate sufficiently precise measurement results. The design of the elastic deformation softness or the elastic minimum deformation displacement amplitude of the flange carrier can be determined depending on the sensitivity of the selected position detection device.

[0020] 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 in such a way that the relative deformation movement of the magnetic field sensor and the magnetic source is detected in the preferred deformation direction. Preferably, the magnetic field sensor is assigned to the flange on the control valve side, and the magnetic field source is assigned to the flange on the actuator side, or vice versa.

[0021] Preferably, the particularly weakened spring contour section is exposed to a torsional moment when an operating actuating force is transmitted from the actuator to the actuating valve, wherein the position detection device detects the elastic deformation relative pivoting movement.

[0022] In a preferred embodiment of the invention, the spring contour section of the flange support is realized in several, preferably at least three or four, preferably rod-shaped spring bars or columns, which elastically and movably couple an inherently deformation-resistant, actuator-side flange or mounting connection to a deformation-resistant, control valve-side flange or mounting connection. The plurality of spring bars can be designed such that they act as an elastic, in particular one-piece, hinge joint between the two flanges in order to create the spring-elastic deformation flexibility in the preferred deformation direction. The orientation of elongated spring bars is preferably configured such that they are flexible in the preferred deformation direction.When operating reaction forces transmitted by the flange carrier are applied, these forces press on the spring bars, which only allow displacement of the actuator-side flange relative to the control valve-side flange in the preferred deformation direction.

[0023] In a further development of the invention, the plurality of spring bars elastically couple a fastening flange body on the control valve side to a fastening body on the actuator side, wherein the spring bars are structured / shaped and / or arranged such that the spring contour section is elastically deformation-flexible only in the preferred deformation direction and, in particular, is more deformation-resistant in the other directions, in particular without requiring an additional guide device or deformation lock. Due to the design of the spring contour section itself, the elastic deformation flexibility is achieved only in the preferred deformation direction, so that a relative displacement of the two flanges to one another is predictably and measurably accompanied only in one preferred deformation direction.

[0024] Preferably, the plurality of spring bars and the control valve-side flange and the actuator-side flange are made of one piece, such as a plastic piece or a metal piece.

[0025] In a further development of the invention, each spring bar extends at a specific circumferential position, in particular flatly, exclusively axially (perpendicular to the contact surface of the flange on the control valve side and the actuator side) and radially outward (from a connection section of one flange to a connection section of the other flange), in particular without a circumferential component. In this way, the desired elastic deformation flexibility in the circumferential direction as well as the desired deformation stiffness in the radial and axial directions are achieved. Due to the one-piece design, a structural unit of the flange carrier and its components, flange, spring contour section, spring bars, remains intact despite the deformation in one direction.

[0026] Preferably, especially in a one-piece design with the flanges, the spring bar opens into a sleeve-shaped connecting section of the actuator-side flange on the one hand and into a sleeve-shaped connecting section of the control valve-side flange on the other, where it merges. In one embodiment, the respective connecting sections are diametrically opposed radially. In the transition area, the spring bar is reinforced to achieve a desired hinge pivot effect with only one degree of freedom of movement through the spring bar, with each spring bar, in particular, defining the same hinge pivot direction.

[0027] 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 of less than 2 mm.

[0028] In an alternative or combinable embodiment of the invention, the plurality of spring webs which elastically couple the fastening flange body on the control valve side to the fastening flange body on the actuator side are structured and / or arranged such that the spring contour section is designed to be elastically deformation-soft in the preferred deformation direction and at least one further direction, wherein in this case the spring contour section additionally comprises a deformation lock, such as a stop or an encompassing sleeve, which is designed and mounted in particular as a separate additional component to the spring contour section or the flange carrier, and / or blocks a deformation of the spring contour section only in the at least one further direction such that a relative deformation movement occurs exclusively in the preferred deformation direction according to the invention.

[0029] In a further development of the invention, the flange support comprises a mounting flange body or flange on the actuator side and a control valve side. This mounting flange body has a plate shape, which is provided with several mounting holes near the edge to realize the rigid connection to the actuator or control valve. The plate-shaped flanges define axially opposing inner surfaces on which a magnetic field source or a magnetic field sensor is arranged axially diametrically opposite one another. The plate-shaped flanges define mutually opposite outer contact surfaces, which are shaped in such a way that a flat contact with a particularly correspondingly shaped, complementary housing section of the actuator or control valve is permitted.

[0030] In a further development of the invention, the mounting flange body on the actuator side and the control valve side each have a through-hole, particularly concentric with the axial support direction. An actuator of the actuator and / or the control valve can extend through the through-hole without contact. In this way, the respective mounting flange body has a bushing-like or sleeve-like basic shape.

[0031] The flange support has a weakened spring contour section to provide measurement-based information about the operating actuating forces transmitted by the actuator to the control valve during field operation. The spring contour section is an elastic target deformation section of the otherwise particularly rigid and stiff flange support and, when actuating forces are applied, causes an elastic deformation in a predetermined direction, which can be sensed, in particular, by a position sensor.According to the invention, the spring contour section or desired deformation section is designed such that when the operating actuating force, such as the operating torque, is transmitted from the actuator to the actuating valve, an elastic deformation movement, in particular between a point of the spring contour section on the actuator side and a point of the spring contour section on the actuating valve side, is accompanied by a deformation path of at least 0.1 mm, 0.2 mm, 0.3 mm, 0.4 mm, 0.5 mm or 1 mm or of at least 0.5% of the minimum cross-section of the actuating rod / actuating shaft of the actuator. The spring contour section can be weakened in such a way that a still measurable minimum deformation already occurs when normal (defect-free, without wear, without increased coefficient of friction) minimum operating actuating forces act from the actuator to the actuating valve. The greater the detected deformation deformation orThe greater the deformation amplitude permitted by the elastically yielding spring contour section, the greater the effective operating actuating force, from which conclusions can be drawn, among other things, about the wear condition of the actuator and the control valve. A measurable relative displacement of at least 0.1 mm or 0.5% of the minimum cross-section of the actuating rod should already occur when operating actuating forces are being overcome to overcome the internal friction of the control valve and actuator. It should be understood that even with large-sized actuators, a relative displacement of more than 5 mm should be excluded. The optimal displacement amplitude range is between 0.1 mm and 2 mm or 3 mm.In particular, it is clear that the flange support and its spring contour section are designed to be elastically deformable in the preferred deformation direction so that even at high operating forces, the deformation in the preferred deformation direction remains elastic and the yield point is not reached in the area of ​​the spring contour section.

[0032] According to the invention, the flange support is designed to be elastically deformable in the preferred or desired deformation direction, in which operating counterforces act, which are exerted due to 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 permitted by the spring contour section can 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 actuating rod or the actuating shaft of the actuator or the control valve.If the respective actuator element of the actuator and the control valve has a minimum cross-sectional dimension or diameter of 10 mm, a deformation amplitude of at least 1%, preferably up to 10% or 20%, of the minimum cross-sectional dimension through the spring contour section should be permitted for actuating force transmission during normal operation. For an actuator of 20 mm, with a 0.5% deformation travel component, an absolute deformation travel of at least 1 mm can also be assumed, which already occurs at normal, particularly low operating actuating forces.

[0033] It was shown that a deformation travel of at least 0.1 mm is sufficient, especially for the use of commercially available capacitive, inductive, or potentiometric position measurement methods. Using the measurement data on the elastic deformation of the flange support, a statement can be made about the actual operating forces acting between the control valve and the control element based on empirical values, flange support-specific structural constants such as the modulus of elasticity, etc. It is advantageous to allow larger movement amplitudes of one or more millimeters through the spring contour section to increase position measurement accuracy.

[0034] In contrast to the prior art, a position measurement is provided in the area of ​​the weakened spring contour section with only one preferred deformation direction, for example, with respect to the elastic relative movement between an actuator-side area of ​​the spring contour section and an actuating valve-side area of ​​the spring contour section. This allows for conclusions to be drawn about the absolute actuating forces that result when the drive actuating force is transferred to the actuating valve. This allows for precise statements about the actual actuating forces.

[0035] Furthermore, the invention relates to a device for measuring an operating actuating force, such as an operating actuating torque, of an actuator actuating a control valve of a process plant according to claim 15 or as described above. The measuring device comprises a flange support according to the invention, as described above. The control valve and the actuator are mountable and / or mounted on the flange support, wherein the flange support is combined with a position detection device to detect the elastic deformation, which is forced and induced by the spring contour section, in the preferred direction of deformation.

[0036] Preferred embodiments are specified in the subclaims.

[0037] Further properties, features and advantages of the invention will become clear from the following description of preferred embodiments of the invention with reference to the accompanying drawings, in which: Fig. 1a a perspective view of a flange support according to the invention of a first embodiment; Fig. 1b a front view of the flange support according to Fig. 1a on the front side of the flange support on the control valve side; Fig. 1c a side view of the flange support according to Fig. 1a and Fig. 1b Fig. 2a a perspective view of a flange support according to the invention of a second embodiment; Fig. 2b a front view of the flange support according to Fig. 2a on the front side of the flange support on the control valve side; and Fig. 2c a side view of the flange support according to Fig. 2a and Fig. 2b.

[0038] In Fig. 1a to 1c, a flange support according to the invention is generally provided with the reference numeral 1. The flange support 1 takes on a bushing shape in its basic form and defines an axial support direction A and an axial through-channel 3 which is cylindrical and extends in the axial support direction A. In the assembled state of the flange support 1, the actuating rod or the actuating shaft of an actuator (not shown in detail) extends and moves through the cylindrical through-channel 3, wherein the actuating rod / actuating shaft actuates a control valve (not shown in detail), such as a control valve, by transmitting the actuating forces from the actuator to the control valve in a force-fitting manner. The cylindrical through-channel 3 is formed concentrically to the axial support direction A.

[0039] The bush-shaped flange carrier 1 defines radial directions, with two mutually perpendicular radial directions R1 and R2 in Fig. 1b. The circumferential or torsional direction U is defined around the axial support direction A.

[0040] The flange support 1 comprises a mounting flange body 5 on the actuator side and a mounting flange body 7 on the control valve side. Four mounting holes 55, 57 are machined into the plate-shaped and essentially square mounting flange bodies 5, 7 in order to rigidly and immovably mount the housing of the actuator (not shown) or the housing of the control valve (not shown) to the flange support 1.

[0041] Both fastening flange bodies 5, 7 have a square or at least rectangular flange plate 51, 53 when viewed from above, at the corners of which the mounting holes 55, 57 are made in order to realize the rigid attachment to the housing of the actuator or the control valve (not shown). As a further main component of the flange carrier 1, a cylindrical inner bushing 61 is arranged centrally, coaxially to the support direction axis A. The inner bushing 61 defines the through-channel 3 on the inside over the entire axial length of the flange carrier 1. The inner bushing 61 is essentially cylindrical on the outside and inside and bridges the axial distance between the two flange plates 51, 53. In the flange carrier 1 made of Fig. 1a to 1c, the cylindrical inner bushing 61 merges 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 from a single piece, in particular from a single piece of metal. The flange plate 51 of the actuator-side mounting flange body 5 has a through-opening 63 that opens into the cylindrical through-channel 3 in the inner bushing 61. On the control valve side, the cylindrical inner bushing 61 extends into a square, centrally located through-opening 65 and is received in an engaging manner.

[0042] In order to obtain an elastically deformable connection between the two fastening flange bodies 5, 7 that is movable in a preferred deformation direction U, a spring contour section 21 of the flange support 1 is realized by four spring bars 17. The spring bars 17 extend radially from the outside of the cylindrical inner bushing 61.

[0043] Both mounting flange bodies 5, 7 have a base plate shape with through holes 63, 65 for the through channel 3. The mounting flange body 7 on the control valve side is stronger in both the radial direction R and the axial direction A than the mounting flange body 5 on the actuator side. As can be seen in particular in Fig. 1a, the centrally arranged, square through-opening 65 in the mounting flange body 7 is larger than the cylindrical inner bushing 61 of the actuator-side mounting flange body 5. The inner bushing 61 is inserted (without contact) concentrically (except for spring webs 17) into the through-opening 65 of the control valve-side mounting flange body 7, whereby the actuator-side mounting flange body 5 is located at a constant axial distance (in the axial support direction A) from the control valve-side mounting flange body 7 due to the inner bushing 61. An end section of the inner bushing 61 is completely surrounded by the flange plate 53 in the circumferential direction U.

[0044] In order to realize the weakened, elastically yielding spring contour section 21 between the inner bushing 61 (13), which is formed integrally with the actuator-side flange plate 51, and the actuator-side flange plate 53 of the fastening flange body 7, the four spring webs 17 are provided, which extend essentially in a plate-like or lamellar manner exclusively in the radial directions R1 and R2 and in the axial direction A, without having an extension direction component in the circumferential direction U. Two spring webs 17 are located diametrically opposite one another and extend in the same radial direction plane (R1 and R2).

[0045] There are four spring bars 17 arranged at 12 o'clock, 3 o'clock, 6 o'clock and 9 o'clock positions, in particular according to the front view according to Fig. 1b, so that equidistant circumferential distances are provided, which are in the Fig. 1 are approximately 90°. The spring bars 17 have a thickness of a few millimeters or less in order to be elastically flexible in the circumferential direction U. The design of the spring contour section 21 by means of the four spring bars 17 and their arrangement ensure that the flange support 1 is elastically deformation-flexible only in one direction (of the three coordinate directions: circumferential direction U, radial direction R, axial direction A), namely the circumferential direction U. In the other coordinate directions A, R, the flange support 1, in particular the spring contour section 21, is many times more deformation-resistant. This means that when actuating forces are introduced from the actuator to the control valve, reaction actuating forces are diverted into the flange support 1, wherein the torsional component thereof leads to a significantly greater deformation of the flange support 1 in the circumferential direction U than the force components in the axial direction A or radial direction R.

[0046] Due to the arrangement of the spring bars 17 and their planar extension both in the radial direction R and in the axial support direction A, the two deformation-resistant fastening mounting bodies 5, 7 are elastically displaceably coupled to one another in the circumferential direction U. The elasticity of the spring contour section 21 should be adjusted such that a minimum displacement amplitude of 0.1 mm is achieved between the two fastening mounting bodies 5, 7 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, with a magnetic field sensor arrangement being provided in the examples given.

[0047] At the Fig. 1, the spring contour section 21 itself achieves the inventive, one-dimensional elastic deformation property only in the circumferential direction U. No separate guide device on the flange support or deformation locks are 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 structure that can be used as a lantern and yoke in the field of field device technology.

[0048] It should be understood that three or more spring webs 17, in particular at equidistant circumferential distances from one another, can also be provided to form the desired spring contour section 21. The spring contour section 21 makes the flange support 1 deformation-flexible in the torsional or circumferential direction U, but the flange support 1, in particular the spring contour section 21, is deformation-rigid in all radial directions R as well as in the axial section direction A. The elastic deformation stiffness in the axial support direction as well as in radial directions is significantly greater, namely preferably twice as great or several times as great, compared to the elastic deformation-flexibility in the circumferential direction U.

[0049] Torsional forces acting between the fastening assembly body 7 on the control valve side and the fastening assembly body 5 on the actuator side can be determined using an inductive or capacitive position measuring device, such as a production detection device. The spring contour section 21 is designed to be deformation-flexible in the circumferential direction U such that a deformation path of at least 0.1 mm, preferably 0.5 mm or 1 mm, is achieved. Different actuators can be provided with different minimum deformation paths, which are determined by the respective spring contour section 21. For example, in an actuator with an actuating shaft with a diameter of 10 mm, a minimum deformation path of 0.5% or 1% of the diameter of the actuating shaft can be permitted by the spring contour section.

[0050] The movement amplitude is so large that a position detection device, such as an inductive or capacitive measuring device, such as a magnetic field sensor, can measure the relative displacement due to elastic deformation of the spring contour section. The position detection device is preferably provided at an actuator-side or actuator-side end of the spring contour section 21 in order to be able to detect the maximum relative displacement.

[0051] At the Fig. 1a and Fig. 1b, a magnetic field sensor is provided, which bears the reference number 23. The magnetic field sensor 23 is associated with a magnetic field source, such as a permanent magnet, which is provided with the reference number 25. As in Fig. As can be seen in Figure 1a, the magnetic field source 25 is fixedly coupled to the deformation-resistant, control valve-side mounting body 7, while the magnetic field sensor 23 is fixedly attached to the deformation-resistant, actuator-side mounting flange body 5. In the event of a deformation movement in the circumferential direction of at least 0.1 mm, the magnetic field sensor can detect the elastic deformation movement and transmit it to a microcontroller (not shown in detail) of a position controller (not shown in detail). Based on empirical values ​​and stored data regarding the elastic modulus of the spring contour section, the microcontroller can calculate the actual actuator forces, in particular a torsional moment, of the actuator, such as a rotary actuator.It was found that the flange support 1 according to the invention and the desired deformation structure arranged therein, namely the spring contour section 21, generates a deformation movement between the actuator and the control valve that is even visible from the outside and can be easily measured using an inductive and capacitive measuring method. In this way, only the actuator forces are calculated, and other specific static disturbance forces can be easily filtered out. Even a visual plausibility check is achievable with the visible displacement provided by the flange support 1 according to the invention.

[0052] Preferably, the entire flange support 1 is injection-molded or molded from a single piece, in particular a piece of plastic or metal. The two mounting flange bodies 5, 7 as well as the spring contour section 21 including spring bars 17 are made from a single piece of material.

[0053] Preferably, the spring bars 17 are not formed by a single plate or arm structure, but rather by two parallel lamellae arranged at a slight distance apart, in order to ensure sufficiently high rigidity of the spring contour section 21 both in the radial directions R1, R2 and the axial support direction A. The lamella plates can have a cross-section of 0.2 mm to 1.5 mm and are spaced circumferentially apart from one another by substantially the thickness of the plate lamella. Preferably, all four spring bars have such a plate-lamella pair structure.

[0054] If the flange support 1 is used in combination with the magnetic field sensor 23, an actuator force measuring device according to the invention is created. However, this device is not positioned in the area of ​​the actuator, but rather distally, outside the actuator housing, on the flange support 1. There, it is easily accessible, allowing its functionality to be reliably checked.

[0055] In Fig. 2a to 2c illustrate a further embodiment of a flange support according to the invention. For ease of reading of the description of the figures, the same reference numerals are used for similar or identical components of the flange support compared to the first embodiment according to Fig. 1a to 1c, wherein the reference numerals are increased by 100. The subject of the flange support 101 according to Fig. 2a to 2c differs from the flange support 1 according to Fig. 1a to 1c, primarily by the spring contour section 121, which is two-part and forms a weakened structure in the cylindrical inner bushing 161 and connects the fastening flange bodies 105, 107 to one another in a deformation-soft manner in the circumferential direction U, but also in the radial direction R. 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), having an arm or rod shape.

[0056] The spring bars 117 end integrally in the actuator-side fastening flange body 105 and the control valve-side fastening flange body 107, in particular their flange plates 151, 153. In this way, similar to the design according to Fig. 1 (spring bars 17) a hinge-like connection of the spring bars to the fastening flange bodies 105 and 107 is realized, whereby in contrast to the design according to Fig. 1 swivel axes are aligned in the radial direction (in the design according to Fig. 1 the swivel axes are effective in the axial support direction A).

[0057] As already explained, the spring contour section 21 has the desired elastic deformation softness in the circumferential direction U so that the positioning device 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 has Fig. 2 an additional, rigid gripping sleeve 147, which prevents the spring bars 117 from deviating from their axial extension direction in the radial direction R, so that when an operating reaction force is introduced, the radial direction components are directly absorbed in the gripping sleeve 147, without deformation of the flange carrier 101 occurring when the actuator forces act in the radial direction. In this way, a flange carrier 101 with a single preferred deformation direction, in the circumferential direction U, is created, whereby the desired predetermined deformation direction is established and use as part of a measuring device is possible.

[0058] The respective spring bar 117 is reinforced at the base 141 at the transition to the actuator-side mounting flange body 107 in order to form a weakened arm section 143 in the axial direction, which, for example, with a through diameter D of 25 mm, can have a thickness of less than 5 mm, preferably between 1 mm and 3 mm. The spring bar 117 is also reinforced at the opposite end section, which transitions into the actuator-side mounting flange body 105. Adjacent to the spring bars 117 in the circumferential direction, escape recesses 145 in the form of a wide slot are formed in the inner bushing 161 in order to achieve the weakening of the flange carrier 101 and thus the deformation flexibility in the circumferential direction U.

[0059] Such a flange support 101 has a high dimensional stability and rigidity in the axial support direction A, whereby the deformation rigidity in the circumferential direction is significantly lower.

[0060] In the flange support 101, the flange plates 151, 153 of the mounting flange body 105, 107 are coupled to each other by the inner sleeve 161 (without engaging the through-hole 165). The inner sleeve 161 has the radially continuous slotted recesses 145, which provide the deformability in the circumferential direction U. The majority of the base region of the inner sleeve 61 is formed integrally with the flange plate 153 of the control valve-side mounting flange body 107. The head region of the inner bushing 161, opposite the integrally formed foot region, 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 bushing 161 represent the structural elastic force-transmitting connection between the two flange plates 151, 153 of the mounting flange body.

[0061] The magnetic field sensor 125 is housed in the flange plate 153, while the magnetic field source 125 is housed or arranged at the sleeve end region 159, which is located at a gap distance from the inside of the flange plate 153.

[0062] The flange carrier 101 is also part of a measuring device and becomes one when the position measuring device is combined with it.

[0063] The magnetic field sensor 23, 123 can be connected to a position controller (not shown in detail) in order to calculate and output functional test statements, maintenance statements, etc. based on the measurement data of the position measuring device.

[0064] The elastic deformation softness in the preferred deformation direction (U) can be limited by a movement stop, which for example is formed by the through opening 13 in the embodiment according to Fig. 2a to 2c. This limitation of movement of the flange support 1, 101 in the preferred deformation direction (circumferential direction U) is provided to prevent deformation of the flange support beyond the yield point or the like. In the design according to Fig. 2a to 2c, such an overload stop is provided with the reference number 171, wherein the maximum movement amplitude of the flange carrier 101 is determined by the axial dimensional gap at the overload stop 171.

[0065] The features disclosed in the above description, the figures and the claims may be important both individually and in any combination for the realization of the invention in the various embodiments. List of reference symbols 1, 101 flange supports 3, 103 Through channel 5, 105 actuator-side mounting flange body 7, 107 control valve side 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 bushing 63, 65, 163, 165 passage opening 141 Head of the spring bar 143 arm section 145 escape cutouts 171 Overload stop A Support direction D passage diameter R1, R2, R radial direction U circumferential direction

Claims

[1] Flange support (1, 101) for transmitting load-bearing and bearing forces between a housing of a control valve of a process plant and a housing of an actuator actuating the control valve, comprising an axial through-channel (3) for an actuating rod or actuating shaft of the actuator for actuating the control valve, characterized by that the flange support (1, 101) is designed to be deformation-soft only in a single preferred deformation direction. [2] Flange support (1, 101) according to claim 1, characterized by in that it defines an axial support direction (A), a radial direction (R) perpendicular to the support direction (A) and a circumferential direction (U) surrounding the support direction (A) and perpendicular to the radial direction (R), wherein the preferred deformation direction coincides with exactly one of the three directions (A, R, U), wherein the flange support (1, 101) is designed to be more deformation-resistant in the other directions. [3] Flange support (1, 101) according to claim 1 or 2, characterized by in that it has a spring contour section (21, 121) which elastically links an actuator-side flange body (5, 105) of the flange carrier (1, 101) and an actuating valve-side flange body (7, 107) of the flange carrier (1, 101) in the preferred deformation direction, which is weakened and / or designed in such a way that the flange carrier (1, 101) is deformation-softer only in the preferred deformation direction than in the other coordinate directions of the flange carrier (1, 101). [4] Flange support (1, 101) according to claim 3, characterized by that a deformation stiffness of the spring contour section (21, 121) in the other coordinate directions of the flange support (1, 101) is at least 50% greater than a deformation stiffness of the spring contour section (21, 121) in the preferred deformation direction. [5] Flange support (1, 101) according to one of claims 3 or 4, characterized bythat the spring contour section (21, 121) is designed to be deformation-soft in the preferred deformation direction such that when an operating actuating force is transmitted from the actuator to the actuating valve, an elastic relative deformation movement occurs between a flange body (7, 107) on the actuating valve side and a flange body (5, 105) on the actuator side in the preferred deformation direction, wherein the relative deformation movement can be determined by means of a position detection device. [6] Flange support (1, 101) according to claim 5, characterized by in that the position detection device is formed by a magnetic field sensor (23, 123) and a magnetic field source (25, 125), wherein the magnetic field sensor (23, 123) and the magnetic field source (25, 125) are arranged in the region of the spring contour section (21, 121) in such a way that the relative deformation movement of the magnetic field sensor (23, 123) and the magnetic field source (25, 125) is detected in the preferred deformation direction. [7] Flange support (1, 101) according to one of the preceding claims, characterized by that a spring contour section (21, 121) of the flange carrier (1, 101) is realized by a plurality of spring webs (17, 117) which elastically couple a flange body (5, 105) on the actuator side and a flange body (7, 107) on the control valve side. [8] Flange support (1, 101) according to claim 7, characterized bythat the plurality of spring bars (17, 117) elastically couple a flange body (5, 105) on the control valve side to a flange body (7, 107) on the actuator side, wherein the spring bars (17, 117) are structured and / or arranged in such a way that the spring contour section (21, 121) is deformation-soft only in the preferred deformation direction, wherein the plurality of spring bars (17, 117) and the flange body (7, 107) on the control valve side and the flange body (5, 105) on the actuator side are made from one piece and / or each spring bar (17, 117) extends at a specific circumferential position exclusively axially, radially outwards, without a circumferential direction component and / or on the one hand into a sleeve-shaped connecting section of the flange body (5, 105) on the actuator side and on the other hand into a sleeve-shaped Connection section of the control valve-side flange body (7, 107). [9] Flange support (1, 101) according to claim 7 or 8, characterized bythat the plurality of spring bars (17, 117) are plate-shaped, wherein the plate-shaped spring bars (17, 117) are realized by a lamellar pair of parallel extending plates which are arranged at a circumferential distance. [10] Flange support (1, 101) according to one of claims 7 to 9, characterized byin that the plurality of spring webs (17, 117) elastically couple a flange body (5, 105) on the control valve side to a flange body (7, 107) on the actuator side, wherein the spring webs (17, 117) are structured and / or arranged in such a way that the spring contour section (21, 121) is deformation-soft in the preferred deformation direction and at least one further direction, wherein the spring contour section (21, 121) additionally comprises a deformation lock which blocks deformation of the spring contour section (21, 121) in the at least one further direction (R) in such a way that a relative deformation movement occurs exclusively in the preferred deformation direction. [11] Flange support (1, 101) according to one of the preceding claims, characterized byin that a flange body (5, 105, 7, 107) on the actuator side and a control valve side of the flange carrier (1, 101) each have a plate shape, wherein these plate-shaped flange bodies (5, 105, 7, 107) have axially opposite inner surfaces on which a magnetic field source (25, 125) and a magnetic field sensor (23, 123) are arranged axially diametrically opposite one another, and / or these plate-shaped mounting connections have outer contact surfaces facing away from one another, which are shaped in such a way that a flat contact with a correspondingly shaped housing of the actuator or the control valve is permitted. [12] Flange support (1, 101) according to one of claims 3 to 11, characterized byin that a flange body (5, 7, 105, 107) on the actuator side and a flange body (5, 7, 105, 107) on the control valve side each have a through-opening (63, 65, 163, 165) through which an actuator of the actuator and / or the control valve can extend, wherein the flange bodies (5, 7, 105, 107) are coupled by an inner bushing (61, 161) to a through-channel (3, 103) which is arranged at least partially congruent with the through-openings (63, 65, 163, 165) and / or along which the actuator is displaced, wherein the spring contour section (21, 121) is provided for the elastic, deformation-soft coupling of the flange bodies (5, 7, 105, 107) to the inner bushing (61, 161). [13] Flange support (1, 101) according to one of claims 3 to 12, characterized bythat the spring contour section (21, 121) is designed such that, when an operating actuating force is transmitted from the actuator to the actuating valve, the spring contour section (21, 121) causes an elastic deformation movement with a deformation path of at least 0.1 mm or of at least 0.5% or 1% of a smallest cross-sectional thickness of an actuating rod or actuating shaft of the actuator. [14] Flange support (1, 101) according to claim 13, characterized by that the spring contour section (21, 121) is weakened in such a way that during normal operation of the control valve for adjusting the control valve, the spring contour section (21, 121) undergoes an elastic deformation movement with a deformation path of more than 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, of the control rod or control shaft of the actuator. [15] Device for measuring an operating actuating force of an actuator actuating a control valve of a process plant, comprising a control valve and an actuator actuating the control valve with an actuating rod or actuating shaft which extends through the cylindrical through-channel (3), and a flange carrier (1, 101) designed according to one of claims 3 to 14, on which the control valve and the actuator are mounted, wherein the flange carrier (1, 101) is assigned a position detection device such that the elastic deformation caused by the spring contour section (21, 121) is detected in the preferred direction of deformation.

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