阅读说明：本技术 用于测量可流动介质的质量流量的传感器 (Sensor for measuring the mass flow of a flowable medium ) 是由 克里斯托夫·胡伯 克里斯蒂安·许策 迪特尔·蒙得兴 本杰明·施文特 泽韦林·拉姆塞耶 马克 于 2018-05-08 设计创作，主要内容包括：质量流量传感器(100)包括：振动测量管,在管平面中弯曲；振动激发器(53),其用于在弯曲振动使用模式中激发弯曲振动；以及两个振动传感器(51,52),其用于感测振动；支撑系统,其具有支撑板(30)、在入口侧上的支承体和在出口侧上的支承体；以及传感器壳体,其中：支撑系统具有支撑系统振动模式,该支撑系统振动模式包括支撑板的弹性变形；测量管(10)借助于在入口侧上的支承体(20,21)并借助于在出口侧上的支承体被固定地连接到支撑板(30),并且由所述支承体(21,22)界定；支撑板具有多个弹簧承载的轴承(31,32,33,34),多个弹簧承载的轴承通过支撑板中的切口暴露,并且支撑板通过多个弹簧承载的轴承而被安装在具有振动自由度的传感器壳体(40)上,其固有频率低于弯曲振动使用模式的使用模式固有频率；使用模式固有频率低于支撑系统振动模式的固有频率；并且支承体(20,21)被定位成使得使用模式固有频率与另一振动模式的下一固有频率保持至少2％的频率间隔。(A mass flow sensor (100) includes: a vibrating measurement tube, curved in a tube plane; a vibration exciter (53) for exciting bending vibration in a bending vibration use mode; and two vibration sensors (51, 52) for sensing vibrations; a support system having a support plate (30), a support body on an inlet side and a support body on an outlet side; and a sensor housing, wherein: the support system has a support system vibration mode that includes elastic deformation of the support plate; the measuring tube (10) is fixedly connected to a support plate (30) by means of support bodies (20, 21) on the inlet side and by means of support bodies on the outlet side and is delimited by the support bodies (21, 22); the support plate has a plurality of spring-loaded bearings (31, 32, 33, 34) exposed through cutouts in the support plate, and the support plate is mounted on a sensor housing (40) with a degree of freedom of vibration by the plurality of spring-loaded bearings, with a natural frequency lower than a use mode natural frequency of a bending vibration use mode; the natural frequency of the use mode is lower than the natural frequency of the vibration mode of the support system; and the support (20, 21) is positioned such that the use mode natural frequency remains at least 2% of the frequency separation from the next natural frequency of the other vibration mode.)

1. A vibration sensor (100) for measuring mass flow of a flowable medium, comprising:

a line inlet portion (18);

a vibrating measuring tube (10), which vibrating measuring tube (10) serves for guiding a medium, wherein the measuring tube is bent in its rest position in a tube plane;

a line outlet portion (19);

at least one vibration exciter (53), the at least one vibration exciter (53) being used to excite bending vibrations of the measuring tube (10) in a bending vibration mode;

at least two vibration sensors for detecting vibrations of the measuring tube;

a support system having a support plate (30), at least one bearing body (21) on an inlet side and at least one bearing body (22) on an outlet side; and

a sensor housing;

wherein the support system has a support system vibration mode comprising an elastic deformation of the support plate (30);

wherein the measuring tube (10) is fixedly connected to the support plate (30) by means of the support body (21) on the inlet side and by means of the support body (22) on the outlet side and is delimited by the support body,

wherein the measuring tube (10) is connected on the inlet side to the line inlet section (18) and on the outlet side to the line outlet section (19) and is connectable to a line via the line outlet section (19),

wherein the line inlet portion (18) and the line outlet portion (19) are both fixedly connected to the sensor housing (40);

wherein the support plate (30) has a plurality of, in particular, coil spring-loaded bearings (31, 32, 33, 34), wherein the spring-loaded bearings are exposed in each case through at least one cutout in the support plate,

wherein the support plate is a spring mounted relative to the sensor housing via the spring-loaded bearing or bearings so as to have three degrees of translational vibration freedom and three degrees of rotational vibration freedom,

wherein a natural frequency of vibration of the support plate with respect to the instrument housing is lower than a use mode natural frequency of a bending vibration use mode due to the translational vibration degree of freedom and the rotational vibration degree of freedom,

wherein the use mode natural frequency is lower than the natural frequency of the support system vibration mode,

wherein the measuring tube has essentially a two-fold rotational symmetry with respect to an axis extending perpendicular to the tube plane,

wherein the support (21, 22) is positioned such that there is a frequency separation between the natural frequency of the use mode and the next natural frequency of another vibration mode of the measuring tube, which frequency separation is not below a frequency separation limit value,

wherein the frequency interval limit is at least 2%, in particular at least 4%, preferably at least 8% of the natural frequency of the usage pattern.

2. Sensor according to claim 1, wherein a calibration factor (CalF) describes, to a first approximation, the proportionality between the mass flow through the measuring tube and the phase difference between the vibrations of the measuring tube vibrating in the bending vibration use mode at the location of the two vibration sensors, wherein an evaluation function proportional to the frequency interval and inversely proportional to the use mode natural frequency and the calibration factor CalF has a local maximum or an absolute maximum, wherein the support is positioned such that the evaluation function is no more than 8%, in particular no more than 4%, and preferably no more than 2% below the maximum.

3. A mass flow meter according to one of the preceding claims, wherein the usage mode is the F3 bending vibration mode.

4. A mass flow meter according to one of the preceding claims, wherein the natural frequency of vibration of the support plate relative to the meter housing due to the translational and rotational vibrational degrees of freedom is at most half the use mode natural frequency of the bending vibration use mode, and wherein the support system natural frequency is at least twice the use mode natural frequency.

5. A sensor according to claim 1 or 2, wherein the number of spring-loaded bearings is 1, 2, 3 or 4.

6. Sensor according to one of the preceding claims, wherein the measuring tube has an S-shaped course, wherein in the tube plane a longitudinal direction (z) is present, the tube axis being at an angle of not more than 85 °, in particular not more than 83 °, to the longitudinal direction at any point.

7. Sensor according to claim 6, wherein the measuring tube (10) between the two supporting bodies (21, 22) has two outer straight portions (11, 12) and one central straight portion (13), the central straight portion (13) being connected by two circular arc portions (15, 16), wherein the two supporting bodies (21, 22) are arranged on the outer straight portions in each case.

8. Sensor according to one of the preceding claims, wherein in each case a bisector (w1, w2) extends between the pipe centre axis of the central straight portion (13) and the pipe centre axis of one of the outer straight portions (11, 12), wherein the vibration sensor is mounted in each case between the point of intersection of one of the bisectors with the measuring pipe and the point on the outer straight portion of the measuring pipe which is at the radius of curvature of the circular portion from the transition from the circular portion to the outer straight portion.

9. Sensor according to one of the preceding claims, wherein, in each case, in addition to the spring or springs, the line inlet portion and the line outlet portion also contribute a degree-of-freedom-specific reference in relation to the translational and rotational vibration degrees of freedom of the support plate relative to the sensor housing, wherein the contribution of the line inlet portion deviates in each case from the corresponding contribution of the line outlet portion by no more than 10% and in particular by no more than 5% of the respective smaller contribution.

10. Sensor according to claim 9, wherein the collective contribution of the line inlet portion and the line outlet portion does not exceed 40%, in particular does not exceed 20%, preferably does not exceed 10% for any of the degree of freedom-specific reference contributions.

11. Sensor according to one of the preceding claims, wherein the line inlet portion and the line outlet portion have substantially the same pipe cross section as the measurement pipe, in particular the same pipe material as the measurement pipe, and are preferably manufactured integrally with the measurement pipe.

12. Sensor according to one of the preceding claims, wherein the natural frequency of the translational and rotational vibrational degrees of freedom of the support plate is not lower than 70Hz, in particular not lower than 100Hz, and/or not higher than 400 Hz.

13. Sensor according to claim 7 or claim dependent thereon, wherein an angle bisector (w1, w2) extends between the tube central axis of the central straight portion (13) and the tube central axis of one of the outer straight portions (11, 12), wherein a coordinate system with a z-axis extending perpendicular to the angle bisector (w1, w2) occurs in the tube plane, wherein the axes of twofold rotational symmetry form the x-axis, wherein a y-z plane spanned by the x-axis and the z-axis intersects the outer straight portion at a distance from the support body.

14. Sensor according to one of the preceding claims, wherein the vibration excitator is arranged in the center of the double rotational symmetry, and wherein the vibration excitator is set to excite bending vibrations perpendicular to the tube plane.

15. The sensor according to claim 7 or claims dependent thereon, wherein an angle bisector (w1, w2) extends in each case between the tube center axis of the central straight portion (13) and the tube center axis of one of the outer straight portions (11, 12), wherein a coordinate system with a z-axis extending parallel to the angle bisector (w1, w2) occurs in the tube plane, wherein the axes of the twofold rotational symmetry form an x-axis, wherein the y-axis extends parallel to the angle bisector through the intersection of the x-axis and the y-axis, wherein a characteristic base plane of the measuring tube is defined by a right angle, the sides of which extend in the z-direction on the one hand through the intersection of the angle bisector with the tube axis of the curved portion and in the y-direction on the other hand through the intersection of one of the support body with the tube axis of the measuring tube, wherein the ratio of the rectangular area to the inner diameter of the measuring tube is not more than 8000, in particular not more than 6000, and preferably not more than 5000.

16. Sensor according to one of the preceding claims, wherein the inner diameter of the measuring tube does not exceed 5 mm.

Technical Field

The invention relates to a sensor for measuring mass flow with a single vibrating measuring tube, wherein the measuring tube is bent in its rest position in a tube plane, wherein the measuring tube has a double rotational symmetry with respect to an axis extending perpendicular to the tube plane. Universal sensors are described, for example, in published patent application DE 03916285 a1, publication EP 518124 ° a1 and as yet unpublished patent application DE 102015122146.2. An advantage of sensors with a single measuring tube is that they do not contain any flow splitter. However, unlike sensors with two measuring tubes which vibrate symmetrically with respect to one another, in the case of sensors with only a single measuring tube, it is more difficult to avoid interaction with the surroundings by decoupling the vibration energy of the bending vibration use mode or by coupling interfering vibrations from the surroundings. For this purpose, publication DE 102010030340 a1 discloses a sensor with a single measuring tube, wherein the measuring tube has two loops which are guided in parallel and which oscillate relative to one another and are therefore balanced with one another. However, for this type of sensor, the discharge capacity of the measuring tube is in principle not included due to the course of the measuring tube in the loop, whereas sensors of the generic type can basically be designed to be dischargeable.

Background

To avoid interaction with the surroundings by decoupling the vibration energy in the bending vibration use mode or by coupling interfering vibrations from the surroundings, EP 518124 ° a1 describes a frequency separation between the vibrations of the measuring tube and the vibrations of the other components of the sensor.

Disclosure of Invention

The object of the invention is to provide a sensor which is as compact as possible and thus resistant to interference. According to the invention, this object is achieved by a sensor according to independent claim 1.

The sensor for measuring the mass flow of a flowable medium according to the invention comprises:

a line inlet portion;

a single vibrating measuring tube for guiding the medium, wherein the measuring tube is bent in its rest position in a tube plane;

a line outlet portion;

at least one vibration exciter for exciting bending vibrations of the measuring tube in bending vibration modes;

at least two vibration sensors for detecting vibrations of the measuring tube;

a support system having a support plate, at least one support body on an inlet side and at least one support body on an outlet side; and

a sensor housing;

wherein the support system has a support system vibration mode that includes elastic deformation of the support plate;

wherein the measuring tube is connected to the support plate by means of a support body on the inlet side and by means of a support body on the outlet side and is delimited by the support bodies,

wherein the measuring tube is connected on the inlet side to a line inlet portion and on the outlet side to a line outlet portion, and can be connected to the line via the latter, wherein the line inlet portion and the line outlet portion are each firmly connected to the sensor housing,

wherein the support plate has a plurality of special helical spring-loaded bearings, wherein the spring-loaded bearings are exposed in each case through at least one cutout in the support plate,

wherein the support plate is a spring mounted relative to the sensor housing via a spring-loaded bearing or bearings, so as to have three degrees of translational vibration freedom and three degrees of rotational vibration freedom,

wherein, due to the translational vibration degree of freedom and the rotational vibration degree of freedom, the natural frequency of the support plate with respect to the vibration of the instrument case is lower than the natural frequency of the use mode of the bending vibration use mode,

wherein the natural frequency of the use mode is lower than the natural frequency of the vibration mode of the support system,

wherein the measuring tube has a dual rotational symmetry with respect to an axis extending perpendicular to the tube plane,

wherein the support is positioned such that there is a frequency separation between the natural frequency of the use mode and the next natural frequency of the other vibration mode of the measuring tube, which frequency separation is not below a frequency separation limit value,

wherein the frequency interval limit is at least 2%, in particular at least 4%, preferably at least 8% of the natural frequency of the usage pattern.

In addition to the frequency separation between the vibration modes of the measuring tube on the one hand and the vibration modes of the support system or the vibration of the support plate relative to the sensor housing on the other hand, the positioning of the support body is achieved by the arrangement in such a way that the influence of disturbing vibration modes of the measuring tube on the bending vibration mode of use is at most negligible.

Although the bending vibration use mode is preferably a vibration mode in which the measuring tube vibrates perpendicularly to the tube plane, all vibration modes of the measuring tube are also important for determining the frequency interval, that is to say a vibration mode with vibrations in the tube plane and a vibration mode with vibrations perpendicularly to the tube plane.

The suitable position of the support body can be determined, for example, by a position-based determination of the natural frequency of the vibration mode of the measuring tube by means of FEM simulation.

A special coil spring-loaded bearing can easily decouple all vibration modes between the sensor housing and the support plate in the frequency range of the bending vibration mode of use, irrespective of the vibration direction. This has considerable advantages for cantilever support springs as disclosed in WO 2015/076676 a 1. This is because such cantilever support springs actually only allow displacement perpendicular to the plane of the support plate. Thus, vibrations in the plane of the plate cannot be decoupled by such cantilever supports.

In a further development of the invention, the calibration factor (CalF) describes, to a first approximation, the proportionality between the mass flow through the measuring tube and the phase difference between the vibrations of the measuring tube vibrating in the flexural vibration mode of use at the location of the two vibration sensors, wherein an evaluation function proportional to the frequency interval and inversely proportional to the natural frequency of the mode of use and to the calibration factor CalF has a local maximum, or in particular an absolute maximum, wherein the support is positioned such that the evaluation function is less than a maximum of not more than 8%, in particular not more than 4%, and preferably not more than 2%. The calibration factor CalF, which depends on the position of the carrier, can be ascertained, for example, by FEM simulation.

The evaluation function makes it possible to balance the robustness against interference vibrations on the one hand and a greater measurement sensitivity in the design of the sensor on the other hand. This is particularly noteworthy with respect to the compact sensor design, and other aspects will be mentioned below with respect to the sensor.

In a further development of the invention, the bending vibration use mode is the F3 bending vibration mode, in which the measurement tube vibrates perpendicular to the tube plane. In this vibration mode, the integral of the acceleration along the measuring tube is minimal. Since the F3 bending vibration mode also has a double symmetry of the measuring tube, no torque is still exerted on the support body as a whole. As a result, at most a negligible part of the vibration energy can thus be dissipated via the bearing block. Accordingly, the F3 bending vibration mode is hardly disturbed by external vibration.

In a further development of the invention, the natural frequency of the vibration of the support plate relative to the instrument housing is at most half the natural frequency of the use mode of the bending vibration use mode, due to the translational and rotational vibration degrees of freedom, wherein the natural frequency of the support system is at least twice the natural frequency of the use mode.

In a further development of the invention, the number of spring-loaded bearings is 1, 2, 3 or 4. The embodiment with four spring-loaded bearings is currently preferred, since in this way the mounting of the support plate corresponding to the double rotational symmetry of the measuring tube can be achieved in a simple manner by arranging the springs accordingly. In principle it is also possible to have only two springs, but in this case the manufacturing tolerances will have a greater influence when the springs in the support plate are exposed.

In a further development of the invention, the measuring tube has an S-shaped course, wherein a longitudinal direction (z) is present in the tube plane, and the angle of the line axis to the longitudinal direction at any point does not exceed 85 °, in particular does not exceed 83 °. The discharge capacity of the measuring tube is thus ensured, in particular in the case of a vertical orientation in the longitudinal direction.

In a further development of the invention, the measuring tube between the two supporting bodies has two outer straight parts and one central straight part which is connected by two (circular) arc-shaped parts, wherein in each case the two supporting bodies are arranged on the outer straight parts.

The axis of dual rotational symmetry extends through the central straight portion. The line inlet portion or the line outlet portion is connected to the outer straight portion.

By arranging the support body on the outer straight portion, a particularly compact construction in the longitudinal direction is achieved, which deviates from the sensors according to the prior art. This initially leads to a higher calibration factor (CalF) since this tends to result in an increase in the stiffness of the measurement tube relative to the Coriolis mode superimposed on the bending vibration use mode. However, the aforementioned evaluation function takes effect here, whereby the disadvantageous consequences of a compact design can be at least partially compensated.

In a further development of the invention, in each case an angle bisector extends between the tube central axis of the central straight portion and the tube central axis of one of the outer straight portions, wherein the vibratory vibration sensor is mounted in each case between the intersection point of one of the angle bisectors with the measuring tube and a point on the outer straight portion of the measuring tube at which the transition from the arc portion to the outer straight portion is located at a radius of curvature of the arc portion.

In a further development of the invention, in each case, in addition to the spring and the plurality of springs, the line inlet portion and the line outlet portion also contribute a degree-of-freedom-specific reference in relation to the translational and rotational vibration degrees of freedom of the support plate relative to the sensor housing, wherein in each case the contribution of the line inlet portion deviates from the corresponding contribution of the line outlet portion by no more than 10%, in particular by no more than 5%, of the respective smaller contribution.

In a further development of the invention, the joint contribution of the line inlet section and the line outlet section does not exceed 40%, in particular does not exceed 20%, preferably does not exceed 10%, for any degree of freedom-specific reference contribution.

In a further development of the invention, the line inlet portion and the line outlet portion have substantially the same pipe cross section as the measurement, in particular the same pipe material as the measurement pipe, and are preferably manufactured integrally with the measurement pipe.

In a further development of the invention, the natural frequency of the translational and rotational vibration degrees of freedom of the support plate is not lower than 70Hz, in particular not lower than 100Hz, and/or not higher than 400 Hz. This ensures that the typical disturbing vibrations of the technical installation do not excite the support plate to vibrate.

In a further development of the invention, an angle bisector (w1, w2) extends between the tube center axis of the central straight portion and the tube center axis of one of the outer straight portions, wherein a coordinate system with a z-axis extending perpendicular to the angle bisector (w1, w2) occurs in the tube plane, wherein the axes of the twofold rotational symmetry form an x-axis, wherein a y-z plane spanned by the x-axis and the z-axis intersects the outer straight portion at a distance from the support body.

In a further development of the invention, the vibration exciter is arranged in the center of the double rotational symmetry and wherein the vibration exciter is set to excite bending vibrations perpendicular to the tube plane.

In a further development of the invention, an angle bisector extends between the line center axis of the central straight portion and the line center axis of one of the outer straight portions, wherein a coordinate system with a z-axis extending perpendicularly to the angle bisector occurs in the tube plane, wherein the axes of the two-fold rotational symmetry form the x-axis, wherein the y-axis extends parallel to the angle bisector through the intersection of the x-axis and the y-axis, wherein the characteristic base of the measuring tube is defined by a right angle, the sides of which extend in the z-direction on the one hand through the intersection of the one angle bisector with the tube axis of the curved portion and in the y-direction on the other hand through the intersection of one support with the tube axis of the measuring tube, wherein the ratio of the rectangular area to the inner diameter of the measuring tube does not exceed 8000, in particular does not exceed 6000, and preferably does not exceed 5000.

In a further development of the invention, the inner diameter of the measuring tube does not exceed 5 mm.

Drawings

The invention will now be explained on the basis of exemplary embodiments shown in the drawings. The figures show:

FIG. 1: a plan view of a first exemplary embodiment of a sensor according to the present invention;

FIG. 2: views relating to aspects of the evaluation function;

FIG. 3: detailed view of the spring-loaded bearing of the sensor according to the invention; and

FIG. 4: detailed views of an inlet portion or an outlet portion of an exemplary embodiment of a sensor according to the present invention.

Detailed Description

The sensor 100 comprises a measurement tube 10, which measurement tube 10 has a first straight outer portion 11, a second straight outer portion 12 and a central straight portion 13, and a first curved portion 15 and a second curved portion 16. Both straight outer portions 15, 16 are connected to the central straight portion 13 by means of one of the curved portions 15, 16. The measuring tube 10 is delimited by two supporting bodies 21, 22 and is fastened to the latter on a rigid supporting plate 30. The measuring tube 10 extends substantially in a tube plane parallel to the support plate 30. The measuring tube has a two-fold rotational symmetry about an axis of symmetry which extends through the center point C2 of the central tube portion perpendicularly to a tube plane through the center point C2 of the central tube portion. The measuring tube has an inner diameter of, for example, 5mm or less. It is made of metal, in particular stainless steel or titanium. The metal support plate 30 has a thickness of, for example, 5 mm. The support plate 30 has four helical spring-loaded bearings 31, 32, 33, 34, which are cut out, in particular by means of a laser, and which have a double rotational symmetry relative to one another with respect to an axis of symmetry passing through point C2. The support plate 30 is anchored to the housing plate 40 of the sensor housing by means of bearing bolts, not shown here, which are fixed in the center of the spring-loaded bearing.

The spring-loaded bearing 32 is shown in detail in fig. 3. The effective stiffness of the spring-loaded bearing 32 is given by the length of the spiral cut 321 and its width relative to the remaining material width of the support plate 30. In the center, the spring-loaded bearing 32 has a hole 322 for receiving a bearing pin.

By means of spring-loaded bearings 31, 32, 33, 34, the support plate 30 has three degrees of translational vibration freedom and three degrees of rotational vibration freedom, the natural frequency of which is at least 70Hz in order to avoid resonance vibrations, wherein vibrations up to 50Hz are often occurring in the process plant. To not damage the spring bearingThe soft suspension of the support plate by the carrier bearings 31, 32, 33, 34, the measuring tube can be connected to the pipeline via a sufficiently soft pipeline inlet section 18 and a sufficiently soft pipeline outlet section 19. The housing has a first housing bearing 41 and a second housing bearing 42 which are firmly connected to the housing plate 40, and to which the line inlet portion 18 and the line outlet portion 19 are fixed, in order to suppress the transmission of vibrations of the line to the measuring pipe via the line inlet portion 18 and the line outlet portion 19. The translational vibration freedom and the rotational vibration freedom of the support plate 20 each have a natural frequency f_iThe natural frequency and the included reference k_iAnd an idle term m_iIs proportional to the root of the quotient of, i.e. f_iα(k_i/m_i)^1/2. In summary, the line inlet section 18 and the line outlet section are paired with respective references k_iDoes not contribute more than 10%. In fig. 1, a line inlet section 18 and a line outlet section 19 are shown substantially schematically. Fig. 4 shows a design of the line outlet portion 119, in which the rigidity, and thus the contribution to the respective datum, is reduced by the extra pipe length and bending. The line inlet section is correspondingly designed symmetrically.

As further shown in fig. 1, the sensor 100 has a first electrodynamic vibration sensor 51 and a second electrodynamic vibration sensor 52 for detecting vibrations of the measuring tube. In this case, both vibration sensors 51, 52 are arranged on one of the two straight outer portions 11, 12, not exceeding the radius of curvature of the adjacent curved portion. For exciting bending vibrations, the sensor has an electrodynamic exciter 53 which is arranged at the center C2 of the double rotational symmetry and acts in the direction of the axis of symmetry.

Center C2 is the origin of a coordinate system used to describe other aspects of the invention. The measuring tube lies in the x-z plane, wherein the y-axis extends parallel to the angle bisectors w1, w2, which each extend between the tube axis of the straight outer portions 11, 12 and the tube axis of the central straight portion 13. The z-axis extends perpendicular to the y-axis in the tube plane and defines a longitudinal axis of the sensor 100. If the longitudinal axis is arranged vertically, the sensor can be discharged optimally. Then, the inclination of the straight portion is equal to half the angle between the tube axes of the straight outer portions 11, 12 and the tube axis of the central straight portion 13. In a preferred exemplary embodiment of the invention, the inclination is 7 °.

With regard to the positioning of the support, reference is now made to fig. 2, which shows the evaluation function and its components. In order to establish the evaluation function, the natural frequencies of the measuring tube vibration modes for different support body positions are first determined by numerical simulation. The results of using mode F3 for bending vibration and bending vibration modes F3-1 and F3+1 adjacent to the natural frequency are shown here. Furthermore, calibration factors for various support body positions are determined by means of numerical simulation

Which describes the relationship between the flow effect phase difference between the sensor signals of the vibrating sensor and the mass flow. The evaluation function is then calculated as the quotient of the minimum frequency spacing from the bending vibration use mode to the adjacent vibration mode and the calibration factor CalF. The optimum position of the support, at which the evaluation function has a maximum, is used for the orientation of the actual positioning of the support. Therefore, if the value of the evaluation function is less than 2%, the optimum position may be deviated. In the exemplary embodiment shown, the position of the supporting bodies 21, 22 is defined by means of an evaluation function such that the z-axis of the measuring tube intersects the outer straight portions 11, 12 of the measuring tube at a distance from the supporting bodies 21, 22. Overall, a tamper-resistant sensor with a compactly guided measuring tube has already been realized.