EP0185709A1 - Appareil de mesure de la densite et de la vitesse de debit-masse - Google Patents

Appareil de mesure de la densite et de la vitesse de debit-masse

Info

Publication number
EP0185709A1
EP0185709A1 EP85902919A EP85902919A EP0185709A1 EP 0185709 A1 EP0185709 A1 EP 0185709A1 EP 85902919 A EP85902919 A EP 85902919A EP 85902919 A EP85902919 A EP 85902919A EP 0185709 A1 EP0185709 A1 EP 0185709A1
Authority
EP
European Patent Office
Prior art keywords
loop
recited
flow meter
detection
velocity
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP85902919A
Other languages
German (de)
English (en)
Other versions
EP0185709A4 (fr
Inventor
Erik B. Dahlin
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Exac Corp
Original Assignee
Exac Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Exac Corp filed Critical Exac Corp
Publication of EP0185709A1 publication Critical patent/EP0185709A1/fr
Publication of EP0185709A4 publication Critical patent/EP0185709A4/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01F—MEASURING VOLUME, VOLUME FLOW, MASS FLOW OR LIQUID LEVEL; METERING BY VOLUME
    • G01F1/00—Measuring the volume flow or mass flow of fluid or fluent solid material wherein the fluid passes through a meter in a continuous flow
    • G01F1/76—Devices for measuring mass flow of a fluid or a fluent solid material
    • G01F1/78—Direct mass flowmeters
    • G01F1/80—Direct mass flowmeters operating by measuring pressure, force, momentum, or frequency of a fluid flow to which a rotational movement has been imparted
    • G01F1/84—Coriolis or gyroscopic mass flowmeters
    • G01F1/8409—Coriolis or gyroscopic mass flowmeters constructional details
    • G01F1/8413—Coriolis or gyroscopic mass flowmeters constructional details means for influencing the flowmeter's motional or vibrational behaviour, e.g., conduit support or fixing means, or conduit attachments
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01F—MEASURING VOLUME, VOLUME FLOW, MASS FLOW OR LIQUID LEVEL; METERING BY VOLUME
    • G01F1/00—Measuring the volume flow or mass flow of fluid or fluent solid material wherein the fluid passes through a meter in a continuous flow
    • G01F1/76—Devices for measuring mass flow of a fluid or a fluent solid material
    • G01F1/78—Direct mass flowmeters
    • G01F1/80—Direct mass flowmeters operating by measuring pressure, force, momentum, or frequency of a fluid flow to which a rotational movement has been imparted
    • G01F1/84—Coriolis or gyroscopic mass flowmeters
    • G01F1/8409—Coriolis or gyroscopic mass flowmeters constructional details
    • G01F1/8422—Coriolis or gyroscopic mass flowmeters constructional details exciters
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01F—MEASURING VOLUME, VOLUME FLOW, MASS FLOW OR LIQUID LEVEL; METERING BY VOLUME
    • G01F1/00—Measuring the volume flow or mass flow of fluid or fluent solid material wherein the fluid passes through a meter in a continuous flow
    • G01F1/76—Devices for measuring mass flow of a fluid or a fluent solid material
    • G01F1/78—Direct mass flowmeters
    • G01F1/80—Direct mass flowmeters operating by measuring pressure, force, momentum, or frequency of a fluid flow to which a rotational movement has been imparted
    • G01F1/84—Coriolis or gyroscopic mass flowmeters
    • G01F1/8409—Coriolis or gyroscopic mass flowmeters constructional details
    • G01F1/8427—Coriolis or gyroscopic mass flowmeters constructional details detectors
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01F—MEASURING VOLUME, VOLUME FLOW, MASS FLOW OR LIQUID LEVEL; METERING BY VOLUME
    • G01F1/00—Measuring the volume flow or mass flow of fluid or fluent solid material wherein the fluid passes through a meter in a continuous flow
    • G01F1/76—Devices for measuring mass flow of a fluid or a fluent solid material
    • G01F1/78—Direct mass flowmeters
    • G01F1/80—Direct mass flowmeters operating by measuring pressure, force, momentum, or frequency of a fluid flow to which a rotational movement has been imparted
    • G01F1/84—Coriolis or gyroscopic mass flowmeters
    • G01F1/8409—Coriolis or gyroscopic mass flowmeters constructional details
    • G01F1/8436—Coriolis or gyroscopic mass flowmeters constructional details signal processing
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01F—MEASURING VOLUME, VOLUME FLOW, MASS FLOW OR LIQUID LEVEL; METERING BY VOLUME
    • G01F1/00—Measuring the volume flow or mass flow of fluid or fluent solid material wherein the fluid passes through a meter in a continuous flow
    • G01F1/76—Devices for measuring mass flow of a fluid or a fluent solid material
    • G01F1/78—Direct mass flowmeters
    • G01F1/80—Direct mass flowmeters operating by measuring pressure, force, momentum, or frequency of a fluid flow to which a rotational movement has been imparted
    • G01F1/84—Coriolis or gyroscopic mass flowmeters
    • G01F1/845—Coriolis or gyroscopic mass flowmeters arrangements of measuring means, e.g., of measuring conduits
    • G01F1/8468—Coriolis or gyroscopic mass flowmeters arrangements of measuring means, e.g., of measuring conduits vibrating measuring conduits
    • G01F1/8481—Coriolis or gyroscopic mass flowmeters arrangements of measuring means, e.g., of measuring conduits vibrating measuring conduits having loop-shaped measuring conduits, e.g. the measuring conduits form a loop with a crossing point
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01F—MEASURING VOLUME, VOLUME FLOW, MASS FLOW OR LIQUID LEVEL; METERING BY VOLUME
    • G01F1/00—Measuring the volume flow or mass flow of fluid or fluent solid material wherein the fluid passes through a meter in a continuous flow
    • G01F1/76—Devices for measuring mass flow of a fluid or a fluent solid material
    • G01F1/78—Direct mass flowmeters
    • G01F1/80—Direct mass flowmeters operating by measuring pressure, force, momentum, or frequency of a fluid flow to which a rotational movement has been imparted
    • G01F1/84—Coriolis or gyroscopic mass flowmeters
    • G01F1/845—Coriolis or gyroscopic mass flowmeters arrangements of measuring means, e.g., of measuring conduits
    • G01F1/8468—Coriolis or gyroscopic mass flowmeters arrangements of measuring means, e.g., of measuring conduits vibrating measuring conduits
    • G01F1/8481—Coriolis or gyroscopic mass flowmeters arrangements of measuring means, e.g., of measuring conduits vibrating measuring conduits having loop-shaped measuring conduits, e.g. the measuring conduits form a loop with a crossing point
    • G01F1/8486—Coriolis or gyroscopic mass flowmeters arrangements of measuring means, e.g., of measuring conduits vibrating measuring conduits having loop-shaped measuring conduits, e.g. the measuring conduits form a loop with a crossing point with multiple measuring conduits
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01N—INVESTIGATING OR ANALYSING MATERIALS BY DETERMINING THEIR CHEMICAL OR PHYSICAL PROPERTIES
    • G01N9/00—Investigating density or specific gravity of materials; Analysing materials by determining density or specific gravity
    • G01N9/002—Investigating density or specific gravity of materials; Analysing materials by determining density or specific gravity using variation of the resonant frequency of an element vibrating in contact with the material submitted to analysis
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01N—INVESTIGATING OR ANALYSING MATERIALS BY DETERMINING THEIR CHEMICAL OR PHYSICAL PROPERTIES
    • G01N9/00—Investigating density or specific gravity of materials; Analysing materials by determining density or specific gravity
    • G01N9/002—Investigating density or specific gravity of materials; Analysing materials by determining density or specific gravity using variation of the resonant frequency of an element vibrating in contact with the material submitted to analysis
    • G01N2009/006—Investigating density or specific gravity of materials; Analysing materials by determining density or specific gravity using variation of the resonant frequency of an element vibrating in contact with the material submitted to analysis vibrating tube, tuning fork

Definitions

  • the present invention relates generally to mass flow rate and density measuring apparatus and more particularly to an improved means for measuring the mass flow rate of a flowing mass using the effects of Coriolis forces and centrifugal forces upon an oscillatorially translated or deflected portion of one or more loops of conduit through which the mass flow is caused to pass.
  • Prior art flow meters of the type including the present invention have in the past been embodied as gyroscopic mass flow meters or Coriolis type mass flow meters and the like.
  • a U-shaped conduit is mounted in a cantilevered manner at the leg ends thereof, and an oscillating means is mounted on a spring arm having a natural frequency substantially equal to that of the U-shaped conduit and is used to provide up and down motion to the center of the bight end thereof .
  • Measuring sensors (flags and photodete ⁇ tors) are provided which detect the leading and trailing portions of the legs of the U-shaped conduit as they pass through a plane defined by the U-shaped conduit at substantially the mid-point of its oscillation. The time differential of passage of the legs through the midplane is measured as an indication of mass flow rate.
  • a pair of velocity sensors are substituted for the photodetectors, and conditioning electronics are provided for developing signals corresponding to the passage of the side legs through the midplane.
  • this reference is the narrowing of the separation of the legs of each U- shaped tube proximate the support ends thereof so as to improve the freedom of torsional twist that may be imposed upon the respective tubes by the Coriolis reactance forces.
  • This reference also illustrates a looped tube configuration in Fig. 5 thereof, but fails to teach or suggest how such configuration might be used to provide enhanced flow measurement. It is therefore not believed to anticipate the present invention.
  • a disadvantage of the Smith and Cox type of flow measuring devices, as well as those of others in the prior art, is that they are highly sensitive to to external vibrations which cause the measuring tube or tubes to be subjected to twisting forces other than those imparted by Coriolis reaction forces, and such forces interfere with the accurate measurement of mass flow.
  • Coriolis type devices are not capable of providing accurate flow data over a wide range of flow due to limitations in sensitivity in the flow structure used.
  • Still another disadvantage of the prior art devices is that they are not provided with dynamic damping means to reduce the sensitivity to external vibrations.
  • a further object of the present invention is to provide means for measuring mass flow rate and density of a mass flowing through a conduit without introducing perturbing objects or mechanisms into the fluid flow path.
  • a preferred embodiment of the present invention includes at least one helically configured loop of conduit, means for causing oscillatory movement of a portion of the loop in a direction normal to the direction of flow through the conduit portion and generally parallel to the central axis of the loop, and means for detecting the Coriolis forces exerted on other portions of the loop as a result of the mass flow therethrough and the oscillatory translation thereof.
  • a strain gage and associated processing electronics are also used in combination with the mass flow rate information to determine the density of the flow.
  • An important advantage of the present invention is that it enables true mass flow measurement to be made independent of variations of the properties of the material flowing through the measuring apparatus.
  • Fig. 1 is a schematic diagram used to illustrate theoretical operation of the present invention
  • Fig. 2 is a diagram schematically illustrating a simplified embodiment of one form of the present invention
  • Fig. 3 is a diagram schematically illustrating a first alternative embodiment of the present invention.
  • Fig. 4 is a diagram schematically illustrating a multi loop embodiment in accordance with the present invention.
  • Figs. 5 and 6 illustrate parallel flow multilooped embodiments of the present invention
  • Fig. 7 is a diagram schematically illustrating one method of applying oscillatory energy to the loop or loops in accordance with the present invention.
  • Fig. 8 is a diagram schematically illustrating a damping technique used in accordance with the present invention.
  • Fig. 9 is a diagram schematically illustrating a method of detecting the coriolis influence on multiple loops in accordance with the present invention.
  • Fig. 10 is a set of wave forms illustrating operation of the present invention.
  • Fig. 11 is a diagram schematically illustrating an alternative embodiment of the present invention modified to allow increased sensitivity to measurement
  • Fig. 12 illustrates a further alternative embodiment of the present invention modified to have increased sensitivity to measurement and reduced sensitivity to outside vibrations
  • Fig. 13 illustrates an alternative method of detecting Coriolis forces in accordance with the present invention
  • Fig. 14 illustrates an embodiment including a strain gage and electronic processing apparatus in accordance with the present invention
  • Fig. 15 is a block diagram illustrating computational algorithms used in accordance with the present invention.
  • the present invention is based upon the principle that a mass flowing through a looped tube or other conduit and experiencing a velocity gradient transverse to the flow path will interact with the wall of the conduit with a force directly related to the transverse velocity gradient and the mass flow rate.
  • the reaction is known as a Coriolis force.
  • the magnitude and direction of the reaction force depends upon the magnitude and direction of the transverse velocity change and the magnitude and direction of the mass flow. If two portions of the loop have the same transverse velocity gradient but have opposite directions of flow, a force couple consisting of equal and opposite reaction forces will result. In accordance with the present invention this force couple is measured as a means of determining the mass flow rate through the conduit.
  • Fig. 1 of the drawings for purposes of illustration there is shown an example of a generalized helical loop of conduit 10, with its crossed ends mounted to a base structure 12 and 14.
  • the following general theory of the present invention applies for any shape of helical structure and any shape of tube cross-section.
  • the loop 10 may thus be considered to lie substantially in the X-Y plane for purposes of simplified mathematical analysis; deviation of the tube in the Z direction (normal to the X-Y plane) required to permit crossover is ignored.
  • F mass is the fluid mass flow
  • each half loop has a certain "participating mass".
  • the center of action is the point where the resultant force of the distributed force for a half loop is applied and can be computed from the particu lar tube geometry and the general Coriolis force formula for individual mass elements.
  • Participating mass is approximately the weight of the tubing and the fluid in each half loop but ignores the section between the X-axis and the suspension point. This concept takes into account that the motion is not uniform for different points on the half loop.
  • the participating mass can be experimentally determined by measuring the natural frequency of the bending mode of oscillation around the X-axis and by comparing it with the theoretical natural frequency of the differential equation to be presented. The participating mass is determined so that the two natural frequencies agree.
  • A is the damping factor including both natural damping in the material and damping introduced by a damping coil as described hereinbelow;
  • B is the spring factor describing the restoring force from the spring action due to fixed attachment of the ends of the tube 10;
  • Z D is the motion of the center of action point due to drive motion alone
  • Z is the motion due to drive motion and Coriolis force at the center of action point.
  • the spring factor B can be determined by static application of a force couple at the center of action points (working in opposite directions approximately at the points 24 and 26 of the two sides of the loop 10) in the Z direction, and measuring the deflection of the center of action points.
  • Equation (1) determines approximately the magnitude of the Coriolis force where v D has a sinusoidal time variation.
  • the amount of damping in this example results from the application of a certain amount of damping force to the loop as will be explained further below. With a different amount of damping, or a different selection of drive frequency w, but the same natural frequency in the Coriolis mode, a different amount of phase shift would occur.
  • the natural frequency of the coriolis mode will change and the phase shift at the drive frequency will also change somewhat.
  • the density change can be ignored.
  • Af ter Laplace transformation G may be expr es sed as
  • K 1 /K 2 By selection of the ratio K 1 /K 2 , an arbitrary positive phase shift between 0 degrees and 90 degrees can be introduced relating the new function G to the measurement of ⁇ . This ratio is selected so that it creates a positive phase shift equal to the negative phase shift resulting from the inertia of movement as approximately described by the differential equation (2).
  • K 1 /K 2 there will be no significant phase shift between the computed variable G and the drive point velocity v D in equation (1) as long as the drive velocity is approximately a sinusoidal function.
  • some deviation from a single sinewave (harmonic free) waveform is permissible; for example, as caused by disturbing mechanical vibrations. Indeed, the insensitivity to this type of disturbance is a strong advantage of the present invention.
  • variable G and the velocity of the drive point v D are sampled periodically.
  • the rate would typically be 20 times for each full cycle of application of the drive force. However, in the presence of high frequency disturbing vibration of strong magnitude, a much higher frequency would be more suitable.
  • a lower sampling rate speeds up the signal analysis and may be desirable if the flow meter is used for fast acting flow control.
  • K 2 is selected as equal to 1/K3 and
  • G g + (K 1 '/K' 2 ) ⁇ (11)
  • ⁇ may then be determined by linear regression analysis of sample population of G i and V i .
  • the solution to this expression is for one of the two regression lines related to equation (14a).
  • a circular loop 30 of conduit is mounted to a base 32 by means of two standards 34 and 36. Note that loop 30 is deformed upwardly away from the pipe line axis 37 at 38 and downwardly at 40 to provide clearance at the crossover point 41. Alternatively, the pipe line matching deformations could have taken place outside the standards 34 and 36.
  • a loop actuating mechanism 42 is mounted to base 32 and has its force applying armature, or the like, electromagnetically coupled to loop 30 at 44.
  • Actuating means 42 is of any suitable type which is capable of causing reciprocating motion of the engaged loop portion along the Z-axis as defined in equation (2) above.
  • Suitable sensors 46 and 48 Disposed on each side of the loop 30 are suitable sensors 46 and 48 which simultaneously detect the mo tion of the loop points 50 and 52 relative to base 32 and communicate such measurement to a suitable computing circuit and indicator means 54 which will provide a measurement of the Coriolis moment and thus the mass flow though loop 30.
  • indicator 54 could be coupled to a suitable means 56 coupled to the crossing portions of loop 30 at the cross-over point 41 and operative to output a signal indicative of the loop separation, relative velocity or relative acceleration; such signal also serving to cause indicator 54 to indicate the mass flow through tube 30.
  • any vibrational motion transmitted from the pipe line to the base 32 will likewise be transmitted to the drive mechanism 42 and the loop position detectors 46 and 48. Accordingly, vibrational disturbances will not normally affect the accuracy of the measurement.
  • a modification of the Fig. 2 embodiment is illustrated wherein instead of mounting the drive means directly to the base, the drive means 60 is mounted to a counter balancing structure 62 which is rigidly attached to the standards 64 and 66.
  • the counter balancing arm 62 is configured to have the same natural frequency about its support axis as that of the loop 68, and is further provided with an adjustment slide weight 70 for allowing it to be adjusted to match different densities of the mass expected to flow in loop 68. Accordingly, in this embodiment, even though rigid end mounts are required, the base does not need to be vibration resistant since the drive mechanism 60 is not attached directly to the base. Using this alternative, another possible source of error is also avoided in that vibrations generated by the flow meter drive 60 are effectively prevented from influencing the attached pipe line which might reflect energy back into the subject apparatus.
  • a feature of the present invention that should be noted from the embodiments of Figs. 2 and 3 is that stresses induced in the tube at its attachment points to standards 34 (64) and 36 (66) due to actuation by the drive means 42 (60), i.e., drive mode stresses, are torsional rather than bending.
  • stresses at such points caused by Coriolis forces, i.e., Coriolis mode stresses are primarily bending in nature.
  • serial combinations of cross-over loops such as are illustrated in Fig. 4-6 of the drawing, may be utilized.
  • a drive force might be applied between the two loops 70 and 72 at 74 causing deflection of the two loops in opposite directions.
  • Means provided at 76 and 78 could detect changes in separation, i.e., relative position, velocity or acceleration between the loops, with the dynamic difference in separation being used as an indication of mass flow rate.
  • detection of the loop separations at 80 and 82, or the difference therebetween could be used as mass flow rate indicators.
  • detection of separation between the loops at 84 could likewise be utilized.
  • both loops are wound spirally in the same direction, while in the Fig. 6 embodiment, the upper loop is wound spirally advancing downwardly while the lower loop is wound spirally advancing upwardly.
  • measurements could be taken of the top gap l ⁇ (114 in Fig. 6) or the bottom gap 102 (116) , or the difference between the top gap 100 (114) and bottom gap 102 (116) could be measured.
  • the differential loop characteristics of separation at 108 (118) , 110 (120) , 112 (122) could be taken as indicators, as could the differences between 110 and 112, (120 and 122) . Measuring the position difference, or velocity of relative motion or acceleration between the upper and lower loops on opposite sides of the loons, and then calculating the differences between these distances (or velocities or accelerations) is the measurement mode which is believed to be the most sensitive to mass flow.
  • the difference in phase angle ⁇ measured at a given signal level for the position, velocity or acceleration signals produced by sensors 46 and 48 in Fig. 2 can be used. If velocity sensors are used, F mass would be calculated by computational electronics fro the e uation
  • w c is the actual natural frequency of the mode excited by the Coriolis forces (the Coriolis mode) and corresponds to the theoretical value W th in equation (3); and z c is the actual damping coefficient for the Coriolis mode (correspoinds to the theoretical value z in equation (4)).
  • phase angle difference ⁇ is equal to the drive frequency w D times the time difference between the waveforms developed by the detectors operating at left and right positions such as 46 and 48 respectively in Fig. 2, 76 and 78 in Fig. 4, or 110 and 112 in Fig. 5. See Electronic and Radio Engineering by Frederick E. Terman, McGraw-Hill (1955) .
  • Equation (19) is different from and more accurate than the equations presented and implemented in the prior art.
  • Fig. 7 of the drawing one possible implementation of a drive system of the type depicted at 42 in Fig. 2 is illustrated in detail.
  • a standoff 131 Mounted to one tube 130 by means of a standoff 131 is a permanent magnet 132.
  • a double coil mechanism 133 including an upper winding 136 and a lower winding 138 which are mechanically attached to each other by a member 140, but are electrically isolated from each other.
  • the assembly 133 is mounted relative to magnet 132 such that as current is input to winding 136 a motive force will be applied the magnet which will tend to drive the loop segment 130 relative to the loop segment 132.
  • a signal will be induced therein which is proportional to the velocity of the magnet with respect to the velocity of the coil as it moves along the axis of the assembly 133.
  • This signal illustrated as the current i 1 is proportional to the velocity difference between the tubes 130 and 134.
  • the voltage created by i 1 in the resistor R1 is input to a differential amplifier A 1 , which in turn will generate a voltage signal V 1 that is also proportional to the velocity difference.
  • the voltage V 1 is then fed through an amplifier A 3 whose output V is subtracted by an analog computing device 142 from an input voltage V 0 generated by an oscillator 144 that generates a suitable periodic voltage signal V 0 in a form such as a sign wave.
  • the purpose of the velocity feedback loop is to control the amplitude of the tube oscillation at a desirable magnitude, even if the oscillator is operated at or near the natural frequency of the tube. Without this velocity feedback, or some other means for applying damping force to the tubes, should the oscillatory frequency be set at the natural frequency of the tubes it would cause the tubes to be driven to their elastic limit and perhaps failure.
  • the behavior of the closed feedback loop illustrated in Fig. 7 can be approximately described by the transfer function
  • K 1 is the gain factor (V 1 /I 1 )
  • K 2 is the gain factor (I 2 /V 2 )
  • K 3 is the force between drive coil 136 Fig. 7 and magnet 132 per unit current I 2
  • K 4 is the magnitude of current I 1 per unit velocity difference between drive coil 136 and permanent magnet 132
  • s is the Laplace operator symbol
  • m is the mass of both tubes 130 and 134 and the fluid contained therein including only the circular portion of the loops
  • a is the damping constant of the structure for the drive motion
  • b is the spring constant of the structure for the drive motion.
  • Any flow tube will exhibit a natural mode of vibration with low damping.
  • Artificial damping and control of the drive may of course be achieved as illustrated in Fig. 7.
  • a similar system such as is illustrated in Fig. 8, can also be used.
  • Such a device would be a valuable addition to any type of Coriolis flow sensor, but would be an important improvement over the apparatus shown in the above-referenced Smith patents.
  • a permanent magnet 150 is attached to the center loop portion 152 of a double serial loop device that is driven by an actuating assembly 154 such as was previously described at 133 in Fig. 7.
  • the magnet 150 is disposed to move vertically within a damping coil 156 which is rigidly attached to a device base 158.
  • a variable load resistor R Connected across the winding of coil 156 is a variable load resistor R.
  • the current induced in coil 156 by motion of the magnet 150 therewithin creates a current which passes through resistor R and which is proportional to the velocity of the motion of the magnet relative to coil 156. Energy generated by motion of the magnet within coil 156 will be absorbed by energy dissipated in the resistor R. Accordingly, by selection of coil size, number of turns, permanent magnet strength, and the value of resistor R, the extent of damping achieved by such device can be selected to accomodate a particular application.
  • damping coils 160 and 162 can be physically tied to velocity sense coils 164 and 166 in a double loop serial or parallel device configuation.
  • the velocity sense coils 164 and 166 are wound in opposite directions and connected together serially so that when both gaps close at the same rate, the total induced EMF is 0.
  • the output currents developed by coils 164 and 166 in this embodiment are passed through a resistor R to develope a voltage that is fed into a differential amplifier 168 which in turn generates an output signal S 1 that is proportional to the velocity difference between the relative motions of tube portions 161 and 165, and 163 and 167 respectively.
  • the amplifiers 170 and 172, and the potentiometers P 1 and P 2 perform a phase-shifting function to compensate for the phaseshift between the Coriolis and the related motion of the flow tubes as described mathematically by the equations (2)-(8).
  • This compensation is an alternative design feature which is especially useful with digital signal analysis schemes such as described by equations (9)- (18).
  • the signal S 1 is fed through the variable potentiometer P 1 to generate a proportional voltage that is fed into one side of the difference amplifier 170. Simultaneously, S 1 is also fed through the integrator 172 to develop a corresponding position signal S 0 , and this signal is passed through the second potentiometer P 2 to generate a proportional voltage that is fed into the other side of amplifier 170.
  • the resultant output signal S 2 generated is described by equation (8) where the coefficients K 1 . and K 2 correspond to the settings of the potentiometers P 1 and P 2 respectively.
  • Position information may be obtained in this embodiment by integration of velocity (or double integration of acceleration if such sensors are used), and difference in position can be computed by integration of the velocity difference (or double integration of the acceleration difference) as shown in Fig. 9, velocity data is equivalent to position information for the purpose of measurement.
  • the effect of initial conditions associated with integration disappear quickly since the analysis of amplitude is made during many cycles of periodic excitation of the loop for each point of measurement of mass flow rate.
  • the 164 and 166 are connected serially so that, as suggested above, parallel motion of the tube portions 165-167 will produce opposing currents in the resistor R, thus resulting in a net voltage drop across R of 0. Under influence of flow through the tubes, induced Coriolis forces in the portions 165 and 167 will cause relative movement of these tube sections in opposite directions, and a net current resulting from the sum of the induced voltages in the sense coils 164 and 166 will be delivered through the resistor R. As indicated above, the voltage developed across resistor R is then fed into the differential amplifier 168 and the output thereof is integrated by 172 to convert the signal S 1 , which represents the velocity difference between the relative motion between the tubes 161 and
  • Fig. 10 the relationship between steady state signals with sinusoidal drive velocity is illustrated. More particularly, in part (a) of Fig. 10, the drive position of tube 130 is shown by the solid line 174, while the velocity curve corresponding thereto is shown by the dashed line 175. It will be noted that the velocity is the derivative of the driving motion and is therefore 90 degree out-of-phase therewith. If there were no flow in the illustrated tube, it will be appreciated that the position of the tube segments 165 and 167 would be in phase with the position of tube segment 130. These positions are illustrated by the drive component curves 176 in part (c) and 177 in part (b) of Fig. 10.
  • any Coriolis induced deflection will be nearly inphase with the velocity component of the drive motion, and will be positive with respect to tube segment 167 and negative with respect to tube segment 165. Accordingly, by summing the Coriolis components and the drive components, the Coriolis induced positional displacements of tube segments 167 and 165 can be derived, and such displacements are respectively illustrated in parts (b) and (c) by the indicated waveforms 178 and 179.
  • Figs. 11 and 12 such extensions are illustrated wherein the loop sides 182 and 183 are lengthened.
  • two potential problems may be encountered, i.e., "wobble" and "roll”.
  • Fig. 11 the problem of wobble due to bending of the lengthened tube sections in the vertical direction, as illustrated by the dashed lines 184, as the loop is driven.
  • stiffening plates 185 to each side 182 so that the sides are no longer free to bow.
  • Fig. 12 The second problem that is encountered with such modification, the problem of rolling, is illustrated in Fig. 12 by the dashed lines 186.
  • the loop 182 In this situation there is a tendency for the loop 182 to deflect in the plane of the loop, or in effect to "roll", either leftwardly or rightwardly (parallel to the X-Y plane).
  • roll restraint arms such as those illustrated at 187 and 188 may be utilized.
  • the restraint, arms may be in the form of rigid or semi-rigid rods or bars welded directly to the tube at either end.
  • these members could also be in the form of flexible cables since the restraint imposed is tensil in nature.
  • a combination of the two solutions shown in Figs. 11 and 12 might also be utilized to avoid both roll and wobble deformation.
  • a fiber optic sensor may be utilized instead of utilizing an electromagnetic sensing means to sense relative motion between adjacent tube segments, or a tube segment and a base.
  • a fiber optic bundle 190 is attached to the upper tube 192 and a reflective plate 195 is attached to the lower tube 194 (or to a base).
  • the fiber optic sensor apparatus 196 then causes a beam of light to pass through a portion of the optical bundle 190, be reflected by the surface 195 and be returned through a different portion of the bundle 190 to the sensor 196 to effect positional detection.
  • any other suitable means of detecting relative position or relative velocity or acceleration information may also be used in accordance with the present invention.
  • Fig. 14 The inclusion of density measurement as part of this invention is illustrated in Fig. 14 wherein for simplicity the Coriolis measuring apparatus is not shown.
  • This feature utilizes the fact that the centrifugal forces acting upon each element of the fluid flowing in the looped portion 202 of tube 200 is directed from the center of curvature for the element perpendicular to the tube section the element is in. Since the loop is relatively flat, the centrifugal forces for the elements are not far removed from the plane of the drawing. Thus, the centrifugal force is inversely proportional to the radius of curvature for the element, proportional to the mass within the element and proportional to the square of the fluid velocity.
  • the centrifugal forces on the output half 204 of the loop will cause a pull to the left at point 205 and the forces on the input half 206 of the loop will cause a pull to the right at point 205.
  • the opposing forces at 205 will thus cause a strain in the material that is related to the aggregate of the centrifugal forces on the whole test section. Since the Coriolis forces cause no strain at the point 205, measurement of the strain at that point 204 may be accomplished using a simple strain gauge
  • a strain gauge measurement taken anywhere along the loop will furnish information permitting the accomplishment of a density measurement in conjunction with the Coriolis mass flow rate measurement although the calibration relationship will be more complex.
  • the ratio of the total centrifugal force for the half circle 204 acting in the horizontal direction at the point 205, and the total Coriolis force acting upon the same half circle is directly proportional to the velocity of the material in the fluid and is independent of all other characteristics of the fluid.
  • the density of the material in the conduit is directly proportional to the square of the measured mass flow rate divided by the centrifugual force acting upon the half loop.
  • One circuit by which such information may be developed is illustrated in Fig. 15 and includes a means 210 for sampling the drive signal V 1 (from Fig. 7) and signal S 2 (from Fig. 9), and strain gauge signal C (from Fig. 14), a means 212 for computing the mass flow rate F mass from the sampled signals V 1 and S 1 , a means 214 for calculating the centrifugal force Pcentr. from the strain gauge signal C, and a means 216 for calculating the density from mass flow rate and centrifugal force.

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  • General Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
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  • Life Sciences & Earth Sciences (AREA)
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Abstract

Un appareil de mesure par effet de Coriolis de la vitesse de débit-masse comprend au moins une boucle (30) de conduite à configuration helicoïdale, un mécanisme d'entraînement (42) pour imprimer à une partie de la boucle un mouvement d'oscillation perpendiculaire à la direction du débit à travers la partie de la conduite et généralement parallèle à l'axe de la boucle, et un ou plusieurs détecteurs (46), (48), (56) pour détecter les forces de Coriolis qui s'exercent sur d'autres parties de la boucle en conséquence du débit-masse qui les traverse et de leur mouvement d'oscillation. Une jauge de contrainte (208) et des dispositifs électroniques associés de traitement sont également utilisés en combinaison avec l'information concernant la vitesse du débit-masse pour déterminer la densité du débit.
EP19850902919 1984-06-04 1985-06-03 Appareil de mesure de la densite et de la vitesse de debit-masse. Withdrawn EP0185709A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US61680884A 1984-06-04 1984-06-04
US616808 1984-06-04

Publications (2)

Publication Number Publication Date
EP0185709A1 true EP0185709A1 (fr) 1986-07-02
EP0185709A4 EP0185709A4 (fr) 1987-11-02

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EP19850902919 Withdrawn EP0185709A4 (fr) 1984-06-04 1985-06-03 Appareil de mesure de la densite et de la vitesse de debit-masse.

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EP (1) EP0185709A4 (fr)
JP (1) JPH0718734B2 (fr)
AU (1) AU584903B2 (fr)
WO (1) WO1985005677A1 (fr)

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DE4016907A1 (de) * 1990-05-25 1991-11-28 Krohne Messtechnik Massametron Massendurchflussmessgeraet
DE4124296A1 (de) * 1990-07-28 1992-02-06 Krohne Messtechnik Massametron Massendurchflussmessgeraet

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WO1986000699A1 (fr) * 1984-07-11 1986-01-30 Exac Corporation Appareil pour mesurer la densite et la vitesse du debit-masse
DE3526297A1 (de) * 1985-07-23 1987-01-29 Fischer & Porter Gmbh Vorrichtung zur messung des masseflusses eines stroemenden mediums
DE3534288A1 (de) * 1985-09-26 1987-04-02 Danfoss As Massendurchfluss-messgeraet nach dem coriolis-prinzip
US4747312A (en) * 1986-02-21 1988-05-31 Fischer & Porter Co. Double-loop Coriolis type mass flowmeter
US4691578A (en) * 1986-02-21 1987-09-08 Fischer & Porter Company Coriolis-type mass flowmeter
US4730501A (en) * 1986-05-19 1988-03-15 Exac Corporation Single tube parallel flow coriolis mass flow sensor
US4781069A (en) * 1986-06-05 1988-11-01 Exac Corporation Mode selection apparatus for multiple tube coriolis type mass flow meters
DE3788425T2 (de) * 1986-10-09 1994-05-19 Micro Motion Inc Verfahren und vorrichtung zur messung der dicke einer unbekannten flüssigkeit mit einem coriolis-messgerät.
US4911020A (en) * 1986-10-28 1990-03-27 The Foxboro Company Coriolis-type mass flowmeter circuitry
US5271281A (en) * 1986-10-28 1993-12-21 The Foxboro Company Coriolis-type mass flowmeter
US5343764A (en) * 1986-10-28 1994-09-06 The Foxboro Company Coriolis-type mass flowmeter
US5050439A (en) * 1986-10-28 1991-09-24 The Foxboro Company Coriolis-type mass flowmeter circuitry
KR960000099B1 (ko) * 1986-10-28 1996-01-03 더폭스보로 컴패니 코리올리 유형의 질량유량계
US4777833A (en) * 1986-11-12 1988-10-18 Micro Motion, Inc. Ferromagnetic drive and velocity sensors for a coriolis mass flow rate meter
US5027662A (en) * 1987-07-15 1991-07-02 Micro Motion, Inc. Accuracy mass flow meter with asymmetry and viscous damping compensation
JP2557098B2 (ja) * 1987-07-27 1996-11-27 サン ルー、ヒョク 対流慣性力流量計
US4949583A (en) * 1987-11-20 1990-08-21 Flowtec Ag Method of mass flow measurement by the coriolis principle and mass flow meter operating by the coriolis principle
US5115683A (en) * 1988-09-27 1992-05-26 K-Flow Division Of Kane Steel Co., Inc. Coriolis mass flow meter adapted for low flow rates
FR2645272B1 (fr) * 1989-03-30 1991-07-19 Instrulab Capteur de densimetre a vibrations
DE3916285A1 (de) * 1989-05-19 1990-11-22 Krohne Messtechnik Massametron Massendurchflussmessgeraet
US5448921A (en) * 1991-02-05 1995-09-12 Direct Measurement Corporation Coriolis mass flow rate meter
US5497665A (en) * 1991-02-05 1996-03-12 Direct Measurement Corporation Coriolis mass flow rate meter having adjustable pressure and density sensitivity
US5753827A (en) * 1995-10-17 1998-05-19 Direct Measurement Corporation Coriolis meteR having a geometry insensitive to changes in fluid pressure and density and method of operation thereof
US5907104A (en) * 1995-12-08 1999-05-25 Direct Measurement Corporation Signal processing and field proving methods and circuits for a coriolis mass flow meter
US5827979A (en) * 1996-04-22 1998-10-27 Direct Measurement Corporation Signal processing apparati and methods for attenuating shifts in zero intercept attributable to a changing boundary condition in a Coriolis mass flow meter
DE29609624U1 (de) * 1996-05-30 1997-10-02 Bopp & Reuther Messtechnik GmbH, 68305 Mannheim Meßgerät zur Messung des Masseflusses eines strömenden Mediums
US6227059B1 (en) 1999-01-12 2001-05-08 Direct Measurement Corporation System and method for employing an imaginary difference signal component to compensate for boundary condition effects on a Coriolis mass flow meter
JP4254966B2 (ja) * 2006-03-14 2009-04-15 株式会社オーバル 振動方向規制手段を有するコリオリ流量計
JP5033755B2 (ja) * 2008-10-14 2012-09-26 株式会社オーバル 振動方向規制手段を有するコリオリ流量計
US9341059B2 (en) * 2009-04-15 2016-05-17 Schlumberger Technology Corporation Microfluidic oscillating tube densitometer for downhole applications
EP2771656B1 (fr) * 2011-10-26 2018-01-24 Micro Motion, Inc. Capteur co-implanté pour un débitmètre vibrant
DE102013113689B4 (de) 2013-12-09 2018-02-01 Endress + Hauser Flowtec Ag Dichte-Meßgerät
WO2015090776A1 (fr) 2013-12-20 2015-06-25 Endress+Hauser Flowtec Ag Bobine
DE102013114731A1 (de) 2013-12-20 2015-06-25 Endress+Hauser Flowtec Ag Spule
AT515778B1 (de) * 2014-07-18 2015-12-15 Anton Paar Gmbh Biegeschwinger
AT516421B1 (de) 2014-10-31 2016-07-15 Anton Paar Gmbh Verfahren und Messgerät zur Dichtemessung von fluiden Medien
JP6178033B1 (ja) * 2017-04-03 2017-08-09 株式会社アツデン コリオリ式質量流量計
DE102017121157A1 (de) 2017-08-09 2019-02-14 Endress+Hauser Flowtec Ag Spule sowie Meßwandler mit einer solchen Spule
DE102017131199A1 (de) 2017-12-22 2019-06-27 Endress + Hauser Flowtec Ag Coriolis-Massendurchfluß-Meßgerät
US20220099543A1 (en) 2018-12-20 2022-03-31 Endress+Hauser Flowtec Ag Coriolis mass flow meter
EP3899447B1 (fr) 2018-12-20 2023-09-20 Endress + Hauser Flowtec AG Débitmètre massique à effet coriolis
DE102018133117A1 (de) 2018-12-20 2020-06-25 Endress+Hauser Flowtec Ag Coriolis-Massendurchfluß-Meßgerät
EP3899448B1 (fr) 2018-12-21 2024-03-27 Endress + Hauser Flowtec AG Débitmètre massique à effet coriolis muni d'un détecteur de champ magnétique
DE102019133610A1 (de) 2019-12-09 2021-06-10 Endress + Hauser Flowtec Ag Vibronisches Meßsystem zum Messen eines Massestroms eines fluiden Meßstoff
DE102020127382A1 (de) 2020-10-16 2022-04-21 Endress+Hauser Flowtec Ag Verfahren zum Überprüfen eines vibronischen Meßsystems
DE102022112523A1 (de) 2022-05-18 2023-11-23 Endress+Hauser Flowtec Ag Vibronisches Meßsystem
DE102022116111A1 (de) 2022-06-28 2023-12-28 Endress+Hauser Flowtec Ag Vibronisches Meßsystem

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US4127028A (en) * 1977-06-07 1978-11-28 Halliburton Company Coriolis mass flow rate metering means
EP0109218A2 (fr) * 1982-11-03 1984-05-23 Micro Motion Incorporated Débitmètre Coriolis pour masses avec conduites parallèles

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DE4016907A1 (de) * 1990-05-25 1991-11-28 Krohne Messtechnik Massametron Massendurchflussmessgeraet
DE4016907C3 (de) * 1990-05-25 1998-06-10 Krohne Ag Massendurchflußmeßgerät
DE4124296A1 (de) * 1990-07-28 1992-02-06 Krohne Messtechnik Massametron Massendurchflussmessgeraet

Also Published As

Publication number Publication date
AU584903B2 (en) 1989-06-08
JPS61502281A (ja) 1986-10-09
EP0185709A4 (fr) 1987-11-02
JPH0718734B2 (ja) 1995-03-06
WO1985005677A1 (fr) 1985-12-19
AU4409585A (en) 1985-12-31

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