Vibronic measurement recorder for measuring the mass flow of a flowable medium

Abstract

The invention relates to a vibronic measurement recorder (100) for measuring mass flow, comprising a line inlet portion (18); a vibratable measuring tube line (10) which is curved in a measuring tube line plane in its resting position and has an S-shaped directrix; a line outlet portion (19); a vibration exciter (53) for exciting a bending vibration use mode; two vibration sensors for detecting measuring tube line vibrations; a carrying body (30); two bearing bodies (21; 22) which connect the measuring tube line to the carrying body (30); wherein the measuring tube line (10) has, in the bending vibration use mode, two vibration nodes; wherein the measurement recorder (100) furthermore has two stop bodies (76; 86; 88) each of which at least partially surrounds the measuring tube line (10) in order to limit deflections of the measuring tube line (10) perpendicularly to the directrix, wherein the stop bodies (76; 86; 88) each have a centre of gravity, wherein in each case a cross-sectional plane extending perpendicularly to the directrix and in which the centre of gravity is located is no further than two outer diameters of the measuring tube line (10) away from a position at which, when the measuring tube line is filled with water, the next of the vibration nodes of the bending vibration use mode is located.

Description

[0001] Vibronic sensor for measuring the mass flow of a fluid

[0002] The present invention relates to a vibronic measuring sensor for measuring the mass flow of a flowable medium, in particular a measuring sensor with an S-shaped profile.

[0003] A generic measuring sensor comprises a line inlet section; a vibratable measuring pipe for conveying the medium, wherein the measuring pipe is bent in its rest position in a measuring pipe plane, wherein the measuring pipe has a substantially S-shaped course with a twofold rotational symmetry with respect to an axis that runs perpendicular to the measuring pipe plane; a line outlet section; at least one vibration exciter for exciting bending vibrations of the measuring pipe in a bending vibration useful mode; at least two vibration sensors for detecting vibrations of the measuring pipe; a carrier body; an inlet-side bearing body and an outlet-side bearing body; wherein the measuring pipe is firmly connected to the carrier body by means of the inlet-side bearing body and by means of the outlet-side bearing body and is delimited by the bearing bodies.The measuring pipe connects to the pipe inlet section on the inlet side and to the pipe outlet section on the outlet side, and can be connected to a pipe via the latter; the measuring pipe has two vibration nodes in the useful bending vibration mode, which is an F3 bending vibration mode, spaced from the bearing bodies. The designation F3 indicates that this bending vibration mode usually has the third-lowest natural frequency of the bending vibration modes of the measuring pipe perpendicular to the plane of the measuring pipe.

[0004] Generic sensors are disclosed, for example, in European patents EP 0 518 124 B1, EP 3 631 379 B1, EP 3 631 378 B1, and the as yet unpublished patent application DE 10 2023 122 903.6. These sensors are designed to minimize the coupling of disruptive vibrations from the sensor's surroundings via its components into the measuring pipe and the dissipation of vibration energy from the measuring pipe via the sensor's components into its surroundings. However, shocks and vibrations with a high amplitude acting on the sensor, in particular, can cause significant deflections of the measuring pipe, which in extreme cases can lead to plastic deformation. Approaches are known to limit the deflection of the measuring tube by means of stiffening elements and damping elements, as described, for example, in DE 10 2021 122 030 A1 and DE 10 2021 122 031 A1.However, the stiffening and damping elements can influence the vibration behavior of the measuring tubes, particularly due to manufacturing and assembly tolerances, even during normal measuring operation, which can potentially lead to zero-point errors. Therefore, the object of the present invention is to remedy this.

[0005] The object is achieved according to the invention by the measuring sensor according to independent patent claim 1.

[0006] The vibronic measuring sensor according to the invention for measuring the mass flow of a flowable medium comprises: a line inlet section; an oscillating measuring pipe for guiding the medium, wherein the measuring pipe is bent in its rest position in a measuring pipe plane, wherein the measuring pipe essentially has an S-shaped guide curve with a twofold rotational symmetry with respect to an axis that runs perpendicular to the measuring pipe plane; a line outlet section; at least one vibration exciter for exciting bending vibrations of the measuring pipe in a bending vibration useful mode; at least two vibration sensors for detecting vibrations of the measuring pipe; a carrier body; an inlet-side bearing body and an outlet-side bearing body;wherein the measuring pipe is firmly connected to the support body by means of the inlet-side bearing body and by means of the outlet-side bearing body and is delimited by the bearing bodies; wherein the measuring pipe connects to the pipe inlet section on the inlet side and to the pipe outlet section on the outlet side and can be connected to a pipe via the latter; wherein the measuring pipe has two vibration nodes in the useful bending vibration mode, which is an F3 bending vibration mode, which are spaced apart from the bearing bodies;wherein the measuring sensor according to the invention further comprises two stop bodies, which each at least partially surround the measuring pipe in order to at least limit deflections of the measuring pipe perpendicular to the guide curve at the location of the stop body in the measuring pipe plane, wherein the stop bodies each have a center of gravity, wherein in each case a cross-sectional plane running perpendicular to the guide curve, in which the center of gravity lies, is not more than two outer diameters of the measuring pipe, for example not more than one outer diameter of the measuring pipe and in particular not more than half an outer diameter of the measuring pipe from a position at which the next of the vibration nodes of the bending vibration useful mode is located when the measuring pipe is filled with water.

[0007] In a further development of the invention, the stop bodies are dimensioned such that when the measuring tube is deflected in the bending vibration useful mode due to excitation by means of the vibration exciter up to a maximum strain of the measuring tube of 0.1% without external interference, the stop body is not touched by the vibrating measuring tube.

[0008] In a further development of the invention, the stop bodies are dimensioned such that the deflection of the measuring pipe in the measuring pipe plane is limited by the stop on the stop body to a degree at which no plastic deformation of the measuring pipe occurs, wherein in particular the maximum elongation of the measuring pipe is not more than 0.2%.

[0009] In a further development of the invention, the stop body comprises a bent part which is joined to the carrier body.

[0010] In a further development of the invention, the measuring pipe comprises damper mass bodies, each of which has a center of gravity that is no more than two outer diameters of the measuring pipe, for example, no more than one outer diameter of the measuring pipe, and in particular no more than half an outer diameter of the measuring pipe, from a position at which the nearest vibration node of the useful bending vibration mode is located when the measuring pipe is filled with water. Investigations of the generic measuring sensors have shown that sound waves propagating through the medium into the measuring pipe influence the vibration behavior of the latter and can thus cause a zero-point error in the flow measurement. This is why the as yet unpublished patent application DE 10 2023 122 903 teaches this.6 a measuring sensor in which the measuring pipe has such absorber mass bodies at the vibration nodes of the bending vibration useful mode.

[0011] The damper masses serve to cancel out, and thus largely suppress, disturbing vibrations introduced into the measuring pipes at the location of the vibration nodes. However, the damper masses cannot effectively counteract vibrations caused by external impacts, since in extreme cases the inertia of the masses can even lead to increased relative movement between the measuring pipe and the support body.

[0012] In a further development of the invention, the stop bodies each have an opening through which one of the damper mass bodies extends. The stop bodies are designed to limit a deflection of the measuring pipe in the measuring pipe plane by the damper mass body striking an edge of the opening or striking the stop body outside the opening. This has the particular advantage of preventing a direct collision between the thin pipe wall of the measuring pipe and the stop body. This prevents collision-induced deformation of the measuring pipe wall.

[0013] In a further development of the invention, at least one of the stop bodies has a bridge section and two parallel legs that extend perpendicular to the plane of the measuring pipe and are connected to each other by the bridge section at their ends facing away from the support body. The parallel, vertical legs allow for slight lateral deflection in the direction of the transverse plane of the measuring pipe, whereby the forces occurring during a collision between the measuring pipe and the stop body are lower than in the case of a non-deflector stop body.

[0014] In a further development of the invention, at least one of the stop bodies has a bridge section and two diverging legs connected by the bridge section. In this embodiment, the stop body is stiffer due to its shape, so that in this case, the desired strength can be achieved with a lower material thickness of the stop body.

[0015] In a further development of the invention, the opening extends at least through the bridge section of the stop body.

[0016] In a further development of the invention, the bridge section runs at least partially above the measuring tube guide curve at the center of gravity of the stop body.

[0017] In a further development of the invention, at least one of the stop bodies and the damper mass body associated with it is designed in such a way that the collision between the damper mass body and the stop body occurs in an edge section of the opening when the measuring pipe is deflected in the measuring pipe plane, wherein the edge section runs essentially in the measuring pipe plane.

[0018] In a further development of the invention, the two absorber mass bodies each have an extension in the direction of the direction vector of the measuring tube guide curve which is not more than four, for example not more than two, measuring tube diameters.

[0019] In a further development of the invention, the two absorber mass bodies each have a mass which is not less than eight times, in particular not less than twelve times, the mass of a section of the measuring pipe which has a length of one measuring pipe diameter.

[0020] In a further development of the invention, the two absorber mass bodies are arranged according to the twofold rotational symmetry.

[0021] In a further development of the invention, the line inlet section and the line outlet section have substantially the same pipe cross-section as the measuring pipe, in particular the same pipe material as the measuring pipe, and are preferably manufactured in one piece with the measuring pipe.

[0022] In a further development, the measuring tube has an outer diameter of not more than 20 mm, in particular not more than 10 mm. In a further development of the invention, the measuring tube has an outer diameter of not less than 0.5 mm, in particular not less than 1.0 mm.

[0023] In a further development, the useful bending vibration mode, which corresponds to the second symmetrical bending vibration mode, has a natural frequency of not less than 100 Hz, in particular not less than 400 Hz, when the measuring pipe is filled with water.

[0024] In a further development, the useful bending vibration mode, which corresponds to the second symmetrical bending vibration mode, has a natural frequency of not more than 1200 Hz, in particular not more than 900 Hz, when the measuring pipe is filled with water.

[0025] In a further development of the invention, the carrier body has a carrier plate which runs essentially parallel to the measuring pipe plane.

[0026] The invention will now be explained in more detail with reference to the exemplary embodiments illustrated in the drawings. It shows:

[0027] Fig. 1a: a plan view of a first embodiment of a measuring sensor according to the invention;

[0028] Fig. 1 b: a detailed cross-section through a stop body of the embodiment of the first embodiment of a measuring sensor according to the invention from Fig. 1 a;

[0029] Fig. 2a: a perspective view of a second embodiment of a measuring sensor according to the invention;

[0030] Fig. 2b: a detailed cross-section through a first embodiment of a

[0031] Stop body of the embodiment of the second embodiment of a measuring sensor according to the invention from Fig. 2a;

[0032] Fig. 2c: a detailed view of the first embodiment of a stop body

[0033] Fig. 2a; Fig. 2d: a detailed cross-section through a second embodiment of a

[0034] Stop body of the embodiment of the second embodiment of a measuring sensor according to the invention from Fig. 2a; and

[0035] Fig. 2e: a detailed view of the second embodiment of a

[0036] Stop body Fig. 2d.

[0037] The measuring sensor 100 shown in Fig. 1a comprises a measuring pipe 10 with a first straight outer section 11, a second straight outer section 12 and a central straight section 13 as well as a first bent section 15 and a second bent section 16. The two straight outer sections 11, 12 are each connected to the central straight section 13 by means of one of the bent sections 15, 16. The measuring pipe 10 is delimited by two bearing bodies 21, 22 and is fastened by the latter to a rigid support plate 30. The measuring pipe 10 runs essentially in a pipe plane parallel to the support plate 30. The measuring pipe has a twofold rotational symmetry about an axis of symmetry that runs perpendicular to the pipe plane through a point C2 in the middle of the central pipe section. The measuring pipe has an inner diameter of, for example, 5 mm or less.It is made of a metal, in particular stainless steel or titanium. The metallic carrier plate 30 has a thickness of, for example, 5 mm. The carrier plate 30 has four spiral-shaped spring bearings 31, 32, 32, 33, 34, which are cut out in particular by means of a laser, and which also have twofold rotational symmetry with respect to the axis of symmetry through point C2. The carrier plate 30 is anchored to a housing plate 40 of a sensor housing by bearing bolts (not shown here) that are fixed in the center of the spring bearings. The effective stiffness of the spring bearings results from the length of the spiral-shaped cut and its width in relation to the width of the remaining material of the carrier plate 30. In the center, the spring bearings have a bore (not shown here) for receiving a bearing bolt each.Thanks to the spring bearings 31, 32, 33, 34, the support plate 30 has three degrees of freedom for translational vibration and three degrees of freedom for rotational vibration, whose natural frequencies are at least 70 Hz to avoid resonance vibrations with vibrations of up to 50 Hz, which are frequently encountered in process plants. In order not to impair the soft suspension of the support plate achieved by the spring bearings 31, 32, 33, 34, the measuring pipe can be connected to a pipeline via a sufficiently soft pipe inlet section 18 and a sufficiently soft pipe outlet section 19. The housing has a first and second housing bearing 41, 42 which are fixedly connected to the housing plate 40 and to which the line inlet section 18 and the line outlet section 19 are fixed in order to suppress transmission of vibrations of the pipeline to the measuring pipeline via the line inlet section 18 and the line outlet section 19.The translational and rotational vibration degrees of freedom of the carrier plate 30 each have natural frequencies fi which are proportional to the root of a quotient of a reference quantity ki and an inertia term mi, i.e. fi a (k / mi). 1 / 2. The line inlet section 18 and the line outlet section contribute a total of no more than 10% to the respective reference value ki. In Fig. 1a, the line inlet section 18 and the line outlet section 18, 19 are shown essentially schematically. They can have reduced rigidity by means of additional pipe length and bends, whereby their contribution to the respective reference values ​​is reduced. As further shown in Fig. 1a, the measuring sensor 100 for detecting the vibrations of the measuring pipe 10 has a first electrodynamic vibration sensor 51 and a second electrodynamic vibration sensor 52, each of which has a magnet on the measuring pipe 10 and a coil on the carrier plate 30. The two vibration sensors 51, 52 are each arranged on one of the two straight outer sections 11, 12 not more than one radius of curvature of the curved sections 15, 16 from the adjacent curved section.To excite bending vibrations, the sensor has an electrodynamic exciter 53, which is arranged at the center C2 of the twofold rotational symmetry and acts in the direction of the symmetry axis. The electrodynamic exciter 53 comprises a magnet on the measuring pipe 10 and an excitation coil on the support plate 30. The center C2 is the origin of a coordinate system for describing an advantageous aspect of a sensor according to the invention. The directrix of the measuring pipe, i.e., the trajectory of the centers of all measuring pipe cross-sections, lies in an xz-plane, with the y-axis running parallel to angle bisectors w1, w2, which each run between a pipe axis of the straight outer sections 11, 12 and the pipe axis of the central straight section 13. The z-axis runs perpendicular to the y-axis in the pipe plane and defines a longitudinal axis of the sensor 100.If this longitudinal axis is arranged vertically, the sensor can be optimally drained. The inclination of the straight sections is then equal to half the angle between a tube axis of the straight outer sections 11, 12 and the tube axis of the central straight section 13. In this embodiment of the invention, this inclination is 7°.

[0038] The measuring pipe 10 has a preferred symmetrical bending vibration mode with two vibration nodes between the bearing bodies 21, 22, which is also referred to as the second symmetrical bending vibration mode. This symmetrical bending vibration mode has a higher natural frequency than the symmetrical fundamental bending vibration mode, which has no vibration nodes. However, it differs from the fundamental bending vibration mode in that the center of gravity of the measuring pipe 10 has a lower vibration amplitude for the same exciter deflection, so that less vibration energy of the bending vibration mode can be dissipated in this way.Together with the previously described mounting of the carrier plate 30 in the spring bearings and the associated frequency separations between the bending vibration useful mode and the vibration of the carrier plate, the sensor 100 is very well protected against unwanted mechanical coupling or decoupling of vibrations via structural elements of the sensor.

[0039] The measuring sensor 100 according to the invention is further characterized in that two stop bodies 76 are provided to limit deflections of the measuring pipe due to external disturbances to the elastic range. This applies in particular in the measuring pipe plane. The stop bodies 76 partially surround the measuring pipe 10, whereby a minimum distance is maintained between the measuring pipe and the stop body, which allows elastic deflections of the measuring pipe 10, for example up to a maximum expansion of 0.1%. Furthermore, the maximum distance, at least in the measuring pipe plane, can be selected such that plastic deformation of the measuring pipe due to deflections in the measuring pipe plane is avoided by the measuring pipe 10 striking the stop body 76, for example by limiting the maximum expansion of the measuring pipe due to this deflection to 0.2%.

[0040] In order not to endanger the vibrations of the bending vibration useful mode during normal measuring operation of the measuring sensor 100 by the stop bodies 76, the latter can be arranged, with respect to the measuring tube guide curve, in particular in the region of vibration nodes of the bending vibration useful mode.

[0041] As shown in Fig. 1 b, the stop bodies 76 are manufactured as bent parts and comprise a central, semicircularly curved bridge section 762 to which legs 764 extend on both sides perpendicular to the plane of the measuring pipe, each of which has an angled foot 766 at its carrier-side end, which is connected to the carrier body 30, for example, by spot welding or brazing. The bridge section 762 here runs approximately concentrically to the measuring pipe guide curve of the measuring pipe 10, with a distance of approximately 1 mm remaining between the measuring pipe and the bridge section 762. In this respect, the measuring pipe can move freely up to a deflection corresponding to this distance, until it strikes the stop body. This prevents further deflection.

[0042] The second embodiment of a sensor 200 according to the invention shown in Figs. 2a to 2e corresponds in essential features to the first embodiment, with the same reference numerals as in the discussion of the first embodiment being used for equivalent components. And the description of the first embodiment applies accordingly here, unless expressly stated otherwise.

[0043] The essential difference between the second embodiment and the first embodiment is that the measuring pipe 10 of the second embodiment of the measuring sensor 200 according to the invention has two damper mass bodies 56, the centers of gravity of which ideally each coincide with one of the vibration nodes of the symmetrical bending vibration useful mode. The two damper mass bodies 56 are structurally identical and can, for example, comprise polygons, in particular rectangles or squares, as well as circular plates with a central bore through which the fluid-carrying line extends, as shown in the example of one of the damper mass bodies 58 in Fig. 1b, 1c and 1d. The damper mass bodies 56 are fixed in their position on the line by joining, for example, brazing. Insofar as the masses of the damper mass bodies 56 act in vibration nodes of the bending vibration useful mode, they hardly influence their vibration properties.In particular, the absorber mass bodies 56 at most cause a reduction in the natural frequency of the useful bending vibration mode by less than 2%. This means that the dynamics of the density measurement are hardly affected by the absorber mass bodies 56. The effect of the absorber mass bodies 56 is discussed in detail in the as yet unpublished patent application DE 10 2023 122 903.6. Essentially, the absorbers minimize zero-point fluctuations that can be triggered by sound waves coupled into the measuring pipe. However, if external mechanical shocks or vibrations act on the measuring transducer 200, which result, among other things, in an acceleration of the bearing bodies 21, 22 in which the measuring pipe is held, the increased inertia of the measuring pipe caused by the absorber mass bodies 56 can lead to a greater deflection of the same. This entails an increased risk of plastic deformation of the measuring pipe.To counteract this, the damper bodies 56 are surrounded by stop bodies 86, 88, which limit the deflection of the measuring pipe. Two different stop bodies 86, 88 are shown in Fig. 2a to illustrate the variety of possible designs. For a specific sensor, however, two identical stop bodies are preferably used.

[0044] A first embodiment of a stop body 86 is shown in Figs. 2b and 2c. This stop body 86 is made as a bent part from sheet steel. It comprises a bridge section 862 running parallel to the measuring pipe plane and two parallel straight legs 864, which adjoin the bridge section 862 at right angles and are joined by their base 866 to the support body 30. The bridge section 862 has an opening 862—here essentially rectangular—through which the damper mass body 56 extends, wherein, in a direction parallel to the measuring pipe plane and perpendicular to the measuring pipe guide curve in the center of the damper mass body 56, the distance between the damper mass body 56 and an edge of the opening 863 is not less than 0.5 mm and not more than 2 mm.This, on the one hand, leaves sufficient space for vibrations of the measuring pipe 10 in the elastic range, and on the other hand, reliably prevents plastic deformation of the measuring pipe 10 when the damper mass body 56 strikes the stop body 86. The parallel legs 864 of the stop body 86 also allow for slight yielding, thus reducing a force peak during a collision between the damper mass body 56 and the stop body.

[0045] A second embodiment of a stop body 88 is shown in Figs. 2d and 2e. This stop body 88 is also manufactured as a bent part from sheet steel. It comprises an arcuate bridge section 882, two diverging straight legs 864 that connect to the bridge section 862, and two coplanar mounting sections 886, each of which connects to one of the legs 884. The mounting sections are joined to the support body 30. The stop body 88 has an opening 883—here essentially rectangular—through which the damper mass body 56 extends. In a direction parallel to the measuring pipe plane and perpendicular to the measuring pipe guide curve in the center of the damper mass body 56, the distance between the damper mass body 56 and an edge of the opening 883 is not less than 0.5 mm and not more than 2 mm.This, on the one hand, leaves sufficient free space for vibrations of the measuring pipe 10 in the elastic range, and on the other hand, plastic deformations of the measuring pipe 10 are reliably prevented when the damper mass body 56 strikes the stop body 88. In this exemplary embodiment, the design parameters for the design of the stop body 88 are, in particular, the radius of curvature of the curved bridge section 882, the arc angle of the bridge section, the length of the opening 883 and the length of the legs 884. By selecting the parameters accordingly, the edge of the opening 883 serving as a stop can be placed in the measuring pipe plane, so that in the event of a collision between the damper body 56 and the stop body, no torsional moments are introduced into the pipe.

Claims

Patent claims 1. A vibronic measuring sensor (100) for measuring the mass flow rate of a flowable medium, comprising: a line inlet section (18); a vibratable measuring pipe (10) for guiding the medium, wherein the measuring pipe (10) is bent in its rest position in a measuring pipe plane, wherein the measuring pipe (10) has an essentially S-shaped guide curve with a twofold rotational symmetry with respect to an axis that runs perpendicular to the measuring pipe plane; a line outlet section (19); at least one vibration exciter (53) for exciting bending vibrations of the measuring pipe (10) in a bending vibration useful mode; at least two vibration sensors for detecting vibrations of the measuring pipe; a support body (30); an inlet-side bearing body (21) and an outlet-side bearing body (22);wherein the measuring pipe (10) is firmly connected to the support body (30) by means of the inlet-side bearing body (21) and by means of the outlet-side bearing body (22) and is delimited by the bearing bodies; wherein the measuring pipe (10) connects to the pipe inlet section (18) on the inlet side and to the pipe outlet section (19) on the outlet side and can be connected to a pipe via the latter; wherein the measuring pipe (10) has two vibration nodes in the useful bending vibration mode, which is an F3 bending vibration mode, which vibration nodes are spaced from the bearing bodies; characterized in that; the measuring sensor (100) further comprises two stop bodies (76; 86; 88), each of which at least partially surrounds the measuring pipe (10) in order to at least limit deflections of the measuring pipe (10) perpendicular to the guide curve at the location of the stop body in the measuring pipe plane, wherein the stop bodies (76; 86; 88) each have a center of gravity, wherein a cross-sectional plane running perpendicular to the guide curve, in which the center of gravity lies, is not more than two outer diameters of the measuring pipe (10), for example not more than one outer diameter of the measuring pipe (10) and in particular not more than half an outer diameter of the measuring pipe (10) away from a position at which the next of the vibration nodes of the useful bending vibration mode is located when the measuring pipe is filled with water.

2. Vibronic measuring sensor (100) according to claim 1, wherein stop bodies (76; 86; 88) are dimensioned such that when the measuring tube is deflected in the bending vibration useful mode due to excitation by means of the vibration exciter up to a maximum strain of the measuring tube of 0.1% without external interference, the stop body is not touched by the vibrating measuring tube.

3. Vibronic measuring sensor (100) according to claim 1 or 2, wherein the stop bodies are dimensioned such that the deflection of the measuring pipe in the measuring pipe plane is limited by abutment against the stop body to a degree at which no plastic deformation of the measuring pipe occurs, wherein in particular the maximum elongation of the measuring pipe is not more than 0.2%.

4. Vibronic measuring sensor (100) according to claim 1, 2 or 3, wherein the stop bodies each comprise a bent part which is joined to the carrier body.

5. Vibromic measuring sensor (100) according to one of the preceding claims, wherein the measuring pipe (100) has absorber mass bodies (56), wherein the absorber mass bodies (56) each have a center of gravity which is not more than two outer diameters of the measuring pipe (10), for example not more than one outer diameter of the measuring pipe and in particular not more than half an outer diameter of the measuring pipe (10) away from a position at which the nearest of the vibration nodes of the bending vibration useful mode is located when the measuring pipe (10) is filled with water.

6. Vibromic measuring sensor (100) according to claim 5, wherein the stop bodies (86; 88) each have an opening (863; 883) through which one of the damper mass bodies (56) extends, wherein the stop bodies (86; 88) are designed to limit a deflection of the measuring pipe (10) in the measuring pipe plane in that the damper mass body (56) strikes an edge of the opening (863; 883) or outside the opening against the stop body (86; 88).

7. Vibromic measuring sensor (100) according to claims 5 and 6, wherein at least one of the stop bodies and the damper mass body associated therewith are designed such that the collision between the damper mass body and the stop body occurs in an edge section of the opening upon deflection of the measuring pipe in the measuring pipe plane, wherein the edge section extends substantially in the measuring pipe plane.

8. Vibromic measuring sensor (100) according to one of the preceding claims, wherein at least one of the stop bodies (86) has a bridge section (86) and two parallel legs which extend perpendicular to the measuring pipe plane and which are connected to one another by the bridge section at their end facing away from the carrier body (30).

9. Vibromic measuring sensor (100) according to one of claims 1 to 7, wherein at least one of the stop bodies (88) has a bridge section (882) and two diverging legs (884) connected by the bridge section.

10. Vibromic measuring sensor (100) according to one of claims 8 to 9, wherein the opening (863; 883) extends at least through the bridge portion (862; 882) of the stop body (86; 88).

11. Vibromic measuring sensor (100) according to one of claims 7 to 10, wherein the bridge section extends at least partially above the measuring tube guide curve, in particular in a cross section through the measuring tube in which the center of gravity of the stop body is located.

12. Vibromic measuring sensor (100) according to one of claims 5 to 11, wherein the two absorber mass bodies each have an extension in the direction of the direction vector of the measuring tube guide curve which is not more than four, for example not more than two, measuring tube diameters.

13. Vibromic measuring sensor (100) according to one of claims 5 to 12, wherein the two absorber mass bodies (56) each have a mass which is not less than eight times, in particular not less than twelve times, the mass of a section of the measuring pipe which has a length of one measuring pipe diameter.

14. Vibromic measuring sensor (100) according to one of claims 5 to 13, wherein the two damper mass bodies (56) are arranged according to the twofold rotational symmetry of the measuring pipe (10).

15. Vibromic measuring sensor (100) according to one of the preceding Claims, wherein the measuring tube of the measuring pipe (10) has an outer diameter of not more than 20 mm, in particular not more than 10 mm, and / or wherein the measuring tube has an outer diameter of not less than 0.5 mm, in particular not less than 1.0 mm.

16. Vibromic measuring sensor (100) according to one of the preceding claims, wherein the useful bending vibration mode, which corresponds to the second symmetrical bending vibration mode, has a natural frequency of not less than 100 Hz, in particular not less than 400 Hz, when the measuring pipe is filled with water, and / or wherein the useful bending vibration mode, which corresponds to the second symmetrical bending vibration mode, has a natural frequency of not more than 1200 Hz, in particular not more than 900 Hz, when the measuring pipe is filled with water.

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