Patent ID: 12228440

DETAILED DESCRIPTION

FIGS.1-7and the following description depict specific examples to teach those skilled in the art how to make and use the best mode of embodiments of determining a vapor pressure using a vapor pressure meter factor. For the purpose of teaching inventive principles, some conventional aspects have been simplified or omitted. Those skilled in the art will appreciate variations from these examples that fall within the scope of the present description. Those skilled in the art will appreciate that the features described below can be combined in various ways to form multiple variations of determining the vapor pressure using the vapor pressure meter factor. As a result, the embodiments described below are not limited to the specific examples described below, but only by the claims and their equivalents.

FIG.1shows a vibratory meter5. As shown inFIG.1, the vibratory meter5comprises a meter assembly10and meter electronics20. The meter assembly10responds to mass flow rate and density of a process material. The meter electronics20is connected to the meter assembly10via leads100to provide density, mass flow rate, temperature information over path26, and/or other information.

The meter assembly10includes a pair of manifolds150and150′, flanges103and103′ having flange necks110and110′, a pair of parallel conduits130and130′, driver180, resistive temperature detector (RTD)190, and a pair of pickoff sensors1701and170r. Conduits130and130′ have two essentially straight inlet legs131,131′ and outlet legs134,134′, which converge towards each other at conduit mounting blocks120and120′. The conduits130,130′ bend at two symmetrical locations along their length and are essentially parallel throughout their length. Brace bars140and140′ serve to define the axis W and W′ about which each conduit130,130′ oscillates. The legs131,131′ and134,134′ of the conduits130,130′ are fixedly attached to conduit mounting blocks120and120′ and these blocks, in turn, are fixedly attached to manifolds150and150′. This provides a continuous closed material path through meter assembly10.

When flanges103and103′, having holes102and102′ are connected, via inlet end104and outlet end104′ into a process line (not shown) which carries the process material that is being measured, material enters inlet end104of the meter through an orifice101in the flange103and is conducted through the manifold150to the conduit mounting block120having a surface121. Within the manifold150the material is divided and routed through the conduits130,130′. Upon exiting the conduits130,130′, the process material is recombined in a single stream within the mounting block120′ having a surface121′ and the manifold150′ and is thereafter routed to outlet end104′ connected by the flange103′ having holes102′ to the process line (not shown).

The conduits130,130′ are selected and appropriately mounted to the conduit mounting blocks120,120′ so as to have substantially the same mass distribution, moments of inertia and Young's modulus about bending axes W-W and W′-W′, respectively. These bending axes go through the brace bars140,140′. Inasmuch as the Young's modulus of the conduits change with temperature, and this change affects the calculation of flow and density, RTD190is mounted to conduit130′ to continuously measure the temperature of the conduit130′. The temperature of the conduit130′ and hence the voltage appearing across the RTD190for a given current passing therethrough is governed by the temperature of the material passing through the conduit130′. The temperature dependent voltage appearing across the RTD190is used in a well-known method by the meter electronics20to compensate for the change in elastic modulus of the conduits130,130′ due to any changes in conduit temperature. The RTD190is connected to the meter electronics20by lead195.

Both of the conduits130,130′ are driven by driver180in opposite directions about their respective bending axes W and W′ and at what is termed the first out-of-phase bending mode of the flow meter. This driver180may comprise any one of many well-known arrangements, such as a magnet mounted to the conduit130′ and an opposing coil mounted to the conduit130and through which an alternating current is passed for vibrating both conduits130,130′. A suitable drive signal is applied by the meter electronics20, via lead185, to the driver180.

The meter electronics20receives the RTD temperature signal on lead195, and the left and right sensor signals appearing on leads100carrying the left and right sensor signals1651,165r, respectively. The meter electronics20produces the drive signal appearing on lead185to driver180and vibrate conduits130,130′. The meter electronics20processes the left and right sensor signals and the RTD signal to compute the mass flow rate and the density of the material passing through meter assembly10. This information, along with other information, is applied by meter electronics20over path26as a signal.

A mass flow rate measurement {dot over (m)} can be generated according to the equation:
{dot over (m)}=FCF[Δt−Δt0]  [1]

The Δt term comprises an operationally-derived (i.e., measured) time delay value comprising the time delay existing between the pick-off sensor signals, such as where the time delay is due to Coriolis effects related to mass flow rate through the vibratory meter5. The measured Δt term ultimately determines the mass flow rate of the flow material as it flows through the vibratory meter5. The Δt0term comprises a time delay at zero flow calibration constant. The Δt0term is typically determined at the factory and programmed into the vibratory meter5. The time delay at zero flow Δt0term will not change, even where flow conditions are changing. The flow calibration factor FCF is proportional to the stiffness of the vibratory meter5.

Pressures in a Fluid in a Vibratory Meter

Assuming an incompressible liquid under steady conditions, the rate at which mass enters a control volume (e.g., a pipe) at an inlet ({dot over (m)}1) equals the rate at which it leaves at an outlet ({dot over (m)}3). This principle that the inlet mass flow rate ({dot over (m)}1) must be equal to the outlet mass flow rate ({dot over (m)}3) is illustrated by equation [2] below. Moving from the inlet to the outlet, the mass flow rate is conserved at each point along the pipe. However, there may be a reduction in a flow area midway between the inlet and the outlet. This reduction in the flow area requires that the velocity of the fluid increase (ν↑) to maintain the same mass flow rate and obey conservation of mass principles.
{dot over (m)}1=ρ1ν1A1=ρ2ν2A2={dot over (m)}2={dot over (m)}3;  [2]
where:{dot over (m)} is a mass flow rate of the fluid;ν is an average fluid velocity;ρ is a density of the fluid;A is a total cross-sectional area;subscript 1 indicates the inlet;subscript 3 indicates the outlet; andsubscript 2 indicates midway between the inlet and the outlet.

Additionally, the total pressure in a flow system is equal to the sum of both the dynamic pressure and the static pressure:
Ptotal=Pstatic+Pdynamic[3]

The dynamic pressure Pdynamicmay be defined as:

Pdynamic=ρ⁢v22;[4]
where the terms ρ and ν are defined above with respect to equation [2].

Assuming steady, incompressible, inviscid, irrotational flow, the Bernoulli equation gives:

Constant=ρ⁢v22+ρ⁢g⁢z+P;[5]
Where P refers to the static pressure and the pgz term accounts for hydrostatic head due to elevation changes. More specifically, g is a gravitational constant and z is a height. The viscous portion of pressure drop can be handled with a separate loss term in the Bernoulli equation.

Δ⁢Pviscous=-ρ⁢v22⁢f⁢LD;[6]

where;f is a friction factor;L is a length of a pipe; andD is a diameter of the pipe.

The below equation [7] is a version of the Bernoulli equation that accounts for frictional losses associated with traveling through a pipe. As fluid travels through the pipe, the fluid dissipates energy and the pressure drops across a given length of pipe. This loss in pressure is unrecoverable because energy from the fluid has been consumed through frictional losses. Accordingly, the following equation may account for this loss:

P1+ρ⁢v122+ρ⁢g⁢z1+Δ⁢Pviscous=P2+ρ⁢v222+ρ⁢g⁢z2[7]

This relationship can be applied to the exemplary pipe described above with reference to equation [2]. When the fluid moves from the inlet to midway between the inlet and the outlet, there is a change in velocity to conserve the mass flow rate. Therefore, in maintaining the relationship shown in equation [7], the dynamic pressure

ρ⁢v22
increases, causing the static pressure to decrease. As the fluid moves to the outlet from midway between the inlet and outlet, the static pressure is recovered through the same principles. That is, moving to the outlet from midway between the inlet and the outlet, the flow area is increased; therefore, the fluid velocity is decreased, causing the dynamic pressure to decrease while recovering part of the initial static pressure. However, the static pressure at the outlet will be lower due to unrecoverable viscous losses.

This can cause the static pressures at the inlet and outlet to be greater than a vapor pressure of the fluid, while a static pressure between the inlet and outlet is less than the vapor pressure of the fluid. As a result, although the static pressures at the inlet and the outlet are both greater than the vapor pressure of the fluid, flashing or outgassing may still occur in the pipe. Additionally, a vibratory meter, such as a Coriolis meter, may be inserted into a pipeline that has a diameter that is different than a diameter of a conduit or conduits in the vibratory meter. As a result, when outgas sing is detected in the vibratory meter, the pressure measured in the pipeline may not be a vapor pressure of the fluid in the vibratory meter.

Meter Electronics—Drive Gain

FIG.2is a block diagram of the meter electronics20of vibratory meter5. In operation, the vibratory meter5provides various measurement values that may be outputted including one or more of a measured or averaged value of mass flow rate, volume flow rate, individual flow component mass and volume flow rates, and total flow rate, including, for example, both volume and mass flow of individual flow components.

The vibratory meter5generates a vibrational response. The vibrational response is received and processed by the meter electronics20to generate one or more fluid measurement values. The values can be monitored, recorded, saved, totaled, and/or output. The meter electronics20includes an interface201, a processing system203in communication with the interface201, and a storage system204in communication with the processing system203. Although these components are shown as distinct blocks, it should be understood that the meter electronics20can be comprised of various combinations of integrated and/or discrete components.

The interface201is configured to communicate with the meter assembly10of the vibratory meter5. The interface201may be configured to couple to the leads100(seeFIG.1) and exchange signals with the driver180, pickoff sensors1701and170r, and RTDs190, for example. The interface201may be further configured to communicate over the communication path26, such as to external devices.

The processing system203can comprise any manner of processing system. The processing system203is configured to retrieve and execute stored routines in order to operate the vibratory meter5. The storage system204can store routines including a flowmeter routine205, a valve control routine211, a drive gain routine213, and a vapor pressure routine215. The storage system204can store measurements, received values, working values, and other information. In some embodiments, the storage system stores a mass flow (m)221, a density (p)225, a density threshold226, a viscosity (μ)223, a temperature (T)224, a pressure209, a drive gain306, a drive gain threshold302, a gas entrainment threshold244, a gas entrainment fraction248, and any other variables known in the art. The routines205,211,213,215may comprise any signal noted and those other variables known in the art. Other measurement/processing routines are contemplated and are within the scope of the description and claims.

As can be appreciated, more or fewer values may be stored in the storage system204. For example, a vapor pressure may be determined without using the viscosity223. For example, estimate viscosity based on a pressure drop, or a function relating friction as a function of flow rate. However, the viscosity223may be used to calculate a Reynolds number which can then be used to determine a friction factor. The Reynolds number and friction factor can be employed to determine a viscous pressure drop in a conduit, such as the conduits130,130′ described above with reference toFIG.1. As can be appreciated, the Reynolds number may not necessarily be employed.

The flowmeter routine205can produce and store fluid quantifications and flow measurements. These values can comprise substantially instantaneous measurement values or can comprise totalized or accumulated values. For example, the flowmeter routine205can generate mass flow measurements and store them in the mass flow221storage of the storage system204, for example. The flowmeter routine205can generate density225measurements and store them in the density225storage, for example. The mass flow221and density225values are determined from the vibrational response, as previously discussed and as known in the art. The mass flow and other measurements can comprise a substantially instantaneous value, can comprise a sample, can comprise an averaged value over a time interval, or can comprise an accumulated value over a time interval. The time interval may be chosen to correspond to a block of time during which certain fluid conditions are detected, for example a liquid-only fluid state, or alternatively, a fluid state including liquids and entrained gas. In addition, other mass and volume flow and related quantifications are contemplated and are within the scope of the description and claims.

A drive gain threshold302may be used to distinguish between periods of flow, no flow, a monophasic/biphasic boundary (where a fluid phase change occurs), and gas entrainment/mixed-phase flow. Similarly, a density threshold226applied to the density reading225may also be used, separately or together with the drive gain306, to distinguish gas entrainment/mixed-phase flow. Drive gain306may be utilized as a metric for the sensitivity of the vibratory meter's5conduit vibration to the presence of fluids of disparate densities, such as liquid and gas phases, for example, without limitation.

As used herein, the term drive gain refers to a measure of the amount of power needed to drive the flow tubes to specified amplitude, although any suitable definition may be employed. For example, the term drive gain may, in some embodiments, refer to drive current, pickoff voltage, or any signal measured or derived that indicates the amount of power needed to drive the flow conduits130,130′ at a particular amplitude. The drive gain may be used to detect multi-phase flow by utilizing characteristics of the drive gain, such as, for example, noise levels, standard deviation of signals, damping-related measurements, and any other means known in the art to detect mixed-phase flow. These metrics may be compared across the pick-off sensors1701and170rto detect a mixed-phase flow.

Detecting a Phase Change of a Fluid

FIG.3shows a graph300illustrating a relationship between a drive gain and a gas-liquid ratio that can be used to determine a vapor pressure using a vapor pressure meter factor. As shown inFIG.3, the graph300includes an average void fraction axis310and a drive gain axis320. The average void fraction axis310and the drive gain axis320are incremented in percentages, although any suitable units and/or ratios may be employed.

The graph300includes plots330that are relationships between drive gains and gas-liquid ratios for various flow rates. As shown, the gas-liquid ratio is an average void fraction value of the plots330, although any suitable gas-liquid ratio, such as a gas volume fraction (“GVF”) or a gas entrainment fraction, may be employed, and may be based on volume, cross-sectional area, or the like. As can be appreciated, the plots330are similar despite being associated with different flow rates. Also shown is a drive gain threshold line340that intersects with the plots330at about 0.20 percent average void fraction, which may be a reference average void fraction330athat corresponds to a 40% drive gain. Also shown is a true vapor pressure drive gain332, which is about 10%. The true vapor pressure drive gain332corresponds to the fluid in the meter assembly that has a static pressure at which a fluid phase change occurs and has a gas-liquid ratio of zero.

As can be seen, the plots330vary from a drive gain of about 10 percent to drive gain of about 100 percent over a range of average void fractions from 0.00 percent to about 0.60 percent. As can be appreciated, a relatively small change in the average void fraction results in a significant change in the drive gain. This relatively small change can ensure that the onset of vapor formation can be accurately detected with the drive gain.

Although the drive gain of 40% is shown as corresponding to an average void fraction of 0.20 percent, the correspondence may be specific to a process. For example, the drive gain of 40% may correspond to other average void fractions in other process fluids and conditions. Different fluids may have different vapor pressures and therefore onset of vapor formation for the fluids may occur at different flow rates. That is, a fluid with a relatively low vapor pressure will vaporize at higher flow rates and a fluid with relatively high vapor pressure may vaporize at lower flow rates.

As can also be appreciated, the drive gain threshold line340may be at alternative/other drive gains. However, it may be beneficial to have the drive gain at 40% to eliminate false detections of entrainment/mixed phase flow while also ensuring that the onset of vapor formation is correctly detected.

Also, the plots330employ a drive gain, but other signals may be used, such as a measured density, or the like. The measured density may increase or decrease due to the presence of voids in the fluid. For example, the measured density may, counterintuitively, increase due to voids in relatively high frequency vibratory meters because of a velocity-of-sound effect. In relatively low frequency meters, the measured density may decrease due to the density of the voids being less than the fluid. These and other signals may be used alone or in combination to detect the presence of the vapor in the meter assembly.

As discussed above, the 0.20 percent average void fraction value may be the reference average void fraction330athat corresponds to the 40 percent drive gain value, which may be where the drive gain threshold line340intersects with the drive gain axis320. Accordingly, when a measured drive gain is at 40 percent for a fluid in a meter assembly, such as the meter assembly10described above, then an average void fraction of the fluid may be about 0.20 percent. The void fraction of about 0.20 percent may correspond to a pressure of the fluid due to gas present in the fluid. For example, the void fraction of about 0.20 percent may correspond to, for example, a static pressure value.

Due to the previously determined relationship between the drive gain, or other signal, such as density, and the reference average void fraction330a, which may be a reference gas-liquid ratio, a vapor pressure value may be associated with a vapor pressure meter factor. For example, the meter assembly may be vibrated while a static pressure is increased or decreased until a fluid phase change is detected. A vapor pressure value may then be determined from the static pressure, as will be described in more detail in the following with reference toFIG.4. The determined vapor pressure value may correspond to, for example, the static pressure at the drive gain threshold line340. This determined vapor pressure value may be adjusted by the vapor pressure meter factor to correspond to the true vapor pressure drive gain332, which is where a phase change occurs, or the monophasic/biphasic boundary is encountered. Accordingly, although the presence of gas in the fluid may be detected at a static pressure that is different than the true vapor pressure of the fluid, the true vapor pressure value may nevertheless be determined.

Using the reference average void fraction330aas an example, the static pressure in the meter assembly may be reduced until the drive gain reaches 40 percent, thereby indicating that the fluid in the meter assembly has an average void fraction of 0.20 percent. A processing system, such as the processing system203described above, may determine that the fluid began to vaporize at a static pressure that is, for example, proportionally higher than the static pressure corresponding to the 40 percent drive gain. For example, a true vapor pressure value may be associated with a drive gain of about 10%. As can be appreciated, due to uncertainties involved in calculating the static pressure (e.g., errors from a pressure sensor, flow rate measurement errors, etc.) a true vapor pressure may be proportionally lower than the calculated static pressure that is associated with the 40% drive gain. True vapor pressure corresponds to a static pressure of the fluid where a fluid phase change occurs, but the gas-liquid ratio is zero.

Thus, the measured drive gain can be used to detect gas, yet still may result in a highly accurate true vapor pressure value. With more particularity, at the instant that outgassing first occurs, with a few tiny bubbles present, drive gain may not increase past the drive gain threshold line340for detection. A dynamic pressure may be increased by, for example, a pump that continues to increase a flow rate until the static pressure drops such that drive gain passes the drive gain threshold line340. Depending on the application, this calculated static pressure (e.g., an uncorrected vapor pressure) could be corrected (e.g., adjusted—decreased or increased) by a vapor pressure meter factor of, for example, 1 psi, to account for the delay in detecting the fluid phase change. That is, the vapor pressure meter factor could be determined and applied to the uncorrected vapor pressure measurement as a function of drive gain to account for the difference in the drive gain at which the gas is detected and the true vapor pressure so as to detect tiny amounts of gas.

Referring toFIG.3by way of example, the measured drive gain of 40 percent may correspond to a static pressure of the fluid in the meter assembly that is, for example, 1 psi less than a static pressure corresponding to the drive gain associated with the true vapor pressure. Accordingly, the vibratory meter5, or meter electronics20, or any suitable electronics, can determine that the vapor pressure meter factor is 1 psi and add this value to the static pressure associated with the 40 percent drive gain. As a result, the vibratory meter5may accurately detect the phase change of the fluid and, therefore, also accurately determine a vapor pressure of the fluid using the drive gain.

However, other means of detecting the phase change may be employed that do not use a drive gain. For example, the phase change may be detected by acoustic measurement, x-ray-based measurements, optical measurements, etc. Also, combinations of the above implementations could be considered. For example, a bypass line that extends vertically in a loop with acoustic and/or optical measurements distributed vertically to determine where the gas first outgasses. This height would then provide the needed input to calculate a vapor pressure of the fluid in the vibratory meter5, as the following explains.

Pressure Drop in a Vibratory Meter

FIG.4shows a graph400illustrating how a static pressure of a fluid in a vibratory meter may be used to determine a vapor pressure. As shown inFIG.4, graph400includes a position axis410and a static pressure axis420. The position axis410is not shown with any particular units of length, but could be in units of inches, although any suitable unit may be employed. The static pressure axis420is in units of pounds-per-square inch (psi), although any suitable unit may be employed. The position axis410ranges from an inlet (“IN”) to an outlet (“OUT”) of the vibratory meter.

Accordingly, the position from IN to OUT may correspond to fluid in, for example, the meter assembly10shown inFIG.1. In this example, the region from IN to about A may correspond to a portion of the meter assembly10between the flange103to the conduit mounting block120. The region from about A to about G may correspond to the conduits130,130′ between the mounting blocks120,120′. The region from G to OUT may correspond to the portion of the meter assembly10from the mounting block120′ to the flange103′. Accordingly, the fluid in the meter assembly10(e.g., in the position ranging from IN to OUT) may not include fluid in, for example, the pipeline in which the meter assembly10is inserted. The fluid in the meter assembly10may be the fluid in the conduits130,130′.

The graph400also includes a zero dynamic pressure plot430and a dynamic pressure change plot440. The zero dynamic pressure plot430shows no change in the dynamic pressure—the pressure is assumed to decrease linearly from an inlet to an outlet of a vibratory meter. The dynamic pressure change plot440may represent an actual pressure in the vibratory meter inserted into the pipeline wherein the diameter of the conduit or conduits of the vibratory meter is less than the diameter of the pipeline. An exemplary vibratory meter5is shown inFIG.1, although any suitable vibratory meter may be employed. Accordingly, the fluid in the meter assembly, such as the meter assembly10described above, may have a reduced static pressure due to an increase in dynamic pressure. Also shown is a vapor pressure line450representing a vapor pressure of the fluid in the vibratory meter.

The dynamic pressure change plot440includes a static pressure drop section440a, a viscous loss section440b, and a static pressure increase section440c. The dynamic pressure change plot440also includes a minimum static pressure440d. The static pressure drop section440amay be due to an increase in fluid velocity causing a corresponding increase in the dynamic pressure of this section of the vibratory meter. The viscous loss section440bmay correspond to a constant diameter portion of the conduit or conduits in the vibratory meter. Accordingly, the viscous loss section440bmay not reflect an increase in fluid velocity and, therefore, may not reflect an increase in a dynamic pressure. The static pressure increase section440cmay be due to a decrease in fluid velocity and, therefore, the static pressure decrease during the static pressure drop section440amay be recovered. The static pressure drop section440aand the static pressure increase section440cmay be static pressure changes in the meter assembly.

The portion of the dynamic pressure change plot440lying below the vapor pressure line450, which includes the minimum static pressure440d, may correspond to positions (e.g., from about position E to slightly after position G) where a fluid phase change occurs in a fluid in a meter assembly, such as the meter assembly10described above. As can be seen inFIG.4, the minimum static pressure440dis below the vapor pressure line450. This indicates that the dynamic pressure change plot440may be shifted upwards by increasing the static pressure of the fluid in the meter assembly. However, if the static pressure were to be increased by about 5 psi so as to shift the dynamic pressure change plot440up until the minimum static pressure440dlies on the vapor pressure line450, a fluid phase change may be detected. Because the static pressure is increased, gas or vapor in the fluid in the meter assembly may become a liquid. Conversely, if the dynamic pressure change plot440were above the vapor pressure line450and the static pressure of the fluid in the meter assembly were decreased until the minimum static pressure440dlies on the vapor pressure line, then the fluid phase change may be the formation of gas or vapor in the fluid.

As can be seen inFIG.4, the viscous loss section440bdecreases from a static pressure of about 68 psi at position A to a static pressure of about 55 psi at position G. As can be appreciated, the static pressure of about 55 psi at the position G is less than the vapor pressure line450, which is about 58 psi. As a result, even though the static pressures at the inlet and outlet are greater than the vapor pressure line450, the fluid in the vibratory meter may still flash or outgas.

Accordingly, the static pressure at the inlet and outlet do not directly correspond to the vapor pressure of the fluid. In other words, the vapor pressure of the fluid may not be directly determined from a static pressure of the fluid in the pipeline or external of the meter assembly. The static pressure in the meter assembly10or, more specifically, the conduits130,130′, can be accurately determined by, for example, using the pressure measurements at the inlet and the outlet and inputting the dimensions of the vibratory meter5(e.g., diameter and length of the conduit130,130′). However, to accurately determine the vapor pressure, a phase change in the fluid in the vibratory meter5may need to be induced, which may be caused by varying the static pressure of the fluid in the vibratory meter5.

Varying a Static Pressure of a Fluid

FIG.5shows a system500for determining a vapor pressure of a fluid. As shown inFIG.5, the system500is a bypass that includes a bypass inlet and a bypass outlet that are coupled to a pipeline501. The system500includes a pump510in fluid communication with an outlet of a vibratory meter5, illustrated as a Coriolis meter, and the bypass outlet. An inlet pressure sensor520is in fluid communication with an inlet of the vibratory meter5and the bypass inlet. An outlet pressure sensor530is disposed between the outlet of the vibratory meter5and the pump510and is in configured to measure a static pressure of the fluid at the outlet of the vibratory meter5. A flow control device540, which is shown as a valve, is disposed between the bypass inlet and the inlet pressure sensor520.

The pump510may be any suitable pump that can, for example, increase a velocity of the fluid in the vibratory meter5. The pump510may, for example, include a variable frequency drive. The variable frequency drive may allow the pump510to control a fluid velocity of the fluid in the system500. For example, the variable frequency drive may increase the fluid velocity of the fluid through the vibratory meter5, although the fluid velocity may be increased by any suitable pump. By increasing the fluid velocity, the pump510can increase a dynamic pressure of the fluid in the vibratory meter5by increasing the fluid velocity.

Accordingly, the static pressure of the fluid in the vibratory meter5may decrease. By way of illustration, with reference toFIG.4, the pump510may cause the dynamic pressure change plot440to shift downward. Accordingly, although not shown inFIG.4, should the dynamic pressure change plot440be above the vapor pressure line450, the pump510may induce flashing or outgassing by causing the dynamic pressure change plot440to shift downward. Similarly, by shifting the dynamic pressure change plot440up to or above the vapor pressure line450, gas or vapor in the fluid may become a liquid.

The inlet pressure sensor520and the outlet pressure sensor530may be any suitable pressure sensor configured to measure any pressure of the fluid. For example, the inlet pressure sensor520and the outlet pressure sensor530may measure a static pressure of the fluid in the system500. Additionally, or alternatively, the inlet pressure sensor520and the outlet pressure sensor530may measure a total pressure of the fluid in the system500. In one example, a dynamic pressure of the fluid may be determined by taking a difference between the total pressure and the static pressure of the fluid in the system500according to equation [3] above. For example, the inlet pressure sensor520may measure the total pressure and the static pressure of the fluid proximate to, or at, an inlet of the vibratory meter5. The inlet pressure sensor520and/or the meter electronics20in the vibratory meter5may determine the dynamic pressure at the inlet of the vibratory meter5.

The flow control device540may increase the fluid velocity of the fluid in the system500, when the flow control device540's position is moved from a partially closed position to a fully open position. For example, by decreasing the flow restriction of the system500at the inlet of the vibratory meter5, the velocity of the fluid may increase in accordance with equation [2] above. This can shift the dynamic pressure change plot440down so as to induce flashing or outgassing. Conversely, the flow control device540can reduce the fluid velocity of the fluid in the system500thereby shifting the dynamic pressure change plot440up, thereby causing gas or vapors to condense.

As the flow control device540is opened, the fluid velocity will increase, but so will a static pressure at the vibratory meter5inlet, and vice versa. The combination of the flow control device540with the pump510may provide a preferred process condition by partially closing the flow control device540(e.g., to restrict a flow and lower pressure downstream of the flow control device540) and increasing pump speed (e.g., increasing flow rate) to obtain a desirably lower static pressure and higher velocity.

Although the static pressure of the fluid in the vibratory meter5, or, more particularly, the meter assembly10in the vibratory meter5, may be varied by using the pump510or the flow control device540, or a combination of both, described above, other means of varying the static pressure may be employed. For example, a height z of the vibratory meter5may be varied. To reduce the static pressure of the fluid in the vibratory meter5, the height z may be increased. To increase the static pressure of the fluid in the vibratory meter5, the height z may be decreased. The height z of the vibratory meter5may be varied by any suitable means, such as a motorized lift between the vibratory meter5and the pipeline501and bellows between the vibratory meter5, for example, the flow control device540and the pump510. Other means may be employed, as well as a combination of various means (e.g., the pump510, flow control device540, and/or the motorized lift).

For example, if the flow rate through a bypass is sufficient, a pump may not necessarily be employed. Only the flow control device540may be used. The flow control device540may be installed in other locations, such as downstream of the vibratory meter5. Alternatively, the flow control device540may not be employed, such as where the pump510and/or motorized lift is used. In another alternative example, the meter may be installed in the main line, rather than a bypass. Additionally, or alternatively, only a single pressure sensor may be employed. For example, only the outlet pressure sensor530may be employed. The inlet and/or outlet pressure sensors520,530may be located at alternative locations. The outlet pressure sensor530and its location may be beneficial because the static pressure at the location of the outlet pressure sensor530may substantially stabilize with respect to fluid velocity once the fluid in the meter assembly10is at the vapor pressure. That is, any additional increase in the fluid velocity may not cause a substantial decrease in the static pressure measured by the outlet pressure sensor530.

True Vapor Pressure and Reid Vapor Pressure

As discussed above, the Coriolis-meter-based system may provide a true vapor pressure at a gas-liquid ratio of 0:1, which may be a more useful parameter for engineering calculations. Additionally, the Coriolis-based system may measure a “live sample,” which may still have a component with a low vapor pressure (“light-ends”). This may be a potential benefit when compared to methods that measure using “dead sample” where light-ends are evaporated and lost during sampling. Additionally, safety benefits of eliminating the need of transporting sample containers full of vapor for laboratory analysis may be realized.

As to other vapor pressure measurements, a meter electronics20can be configured to back-calculate the Reid vapor pressure at 4:1, or some other V/L ratio using other correlations. For example, to obtain a Reid vapor pressure from true vapor pressure measurements for gasoline, the following equations can be used:

A=-A1-A2⁢ln⁡(TVP)[8]B=B1-B2⁢ln⁡(TVP)[9]RVP=exp⁡(A-BT+C)[10]

Similarly, to a obtain Reid vapor pressure from true vapor pressure measurements for crude oil, the following equations may be used:

A=A1-A2⁢ln⁡(TVP)-A3⁡(T+C)[11]B=B1-B2⁢ln⁡(TVP)-B3⁡[ln⁡(TVP)]2[12]RVP=exp⁡(A-BT+C)[13]
Where:T is temperature (° C.);TVP is a true vapor pressure (kPa);RVP is a Reid vapor pressure (kPa); andA1, A2, A3, B1, B2, B3, and C are parameters for converting between the Reid vapor pressure and the true vapor pressure, and depend on the composition of the fluid.
By way of example, the conversion parameters A1, A2, A3, B1, B2, B3, and C may have the following values (for SI units):

ParameterGasolineCrude OilA19.467416.62A2−0.94450.9875B15211.05339B216.014675.7C459.67273.15

An example of the benefit of measuring the vapor pressure at a gas-liquid ratio close to zero can be seen in rail transportation of crude oil. Most vapor pressure testing methods require a gas-liquid ratio of 4:1 and a measuring temperature of 37.8° C. However, crude oil can be transported at 80° C. and gas-liquid ratios close to 0:1. Under these conditions, light-ends might begin to evaporate even in “dead” crude oil and produce a gaseous mixture with exponential pressure increase. This may not be foreseen if the vapor pressure is measured at a gas-liquid ratio of 4:1 and a temperature of 37.8° C. For safety calculations, it may be important to measure the vapor pressure transported in pipelines at process temperature and a gas-liquid ratio close to 0:1, which can be accomplished using a method consistent with the description ofFIG.6, an exemplary one of which is described below.

Using a Vapor Pressure Meter Factor

FIG.6shows a method600of determining a vapor pressure using a vapor pressure meter factor. As shown inFIG.6, the method600begins with step610, which provides a drive signal to a meter assembly having a fluid. The meter assembly employed by the method600may be the meter assembly10described above although any suitable meter assembly may be employed. In step620, a drive gain of the drive signal provided to the meter assembly is measured. A vapor pressure of the fluid is determined based on a previously determined relationship between the drive gain and a reference gas-liquid ratio in step630.

The method600may include additional steps. For example, a static pressure may be determined when the drive gain is measured. For example, the static pressure may be determined contemporaneous to when the drive gain is measured. As described above with reference toFIG.3, the measured drive gain may be associated with a drive gain threshold for detecting a phase change, such as the drive gain threshold line340. When the drive gain is measured at the drive gain threshold, the method600may also determine a static pressure of the fluid in the meter assembly. Accordingly, the measured static pressure may be an uncorrected vapor pressure. This uncorrected vapor pressure may be adjusted using a vapor pressure meter factor to determine a true vapor pressure.

In step610, the drive signal may be provided by the meter electronics20described above, although any suitable electronics may be employed. The fluid may or may not have a gas or vapor, such as entrained gas, bubbles, slug flow, or the like. A velocity of the fluid may vary due to, for example, a pump in line with the vibratory meter5although any suitable configuration may be employed. By varying the velocity of the fluid in the meter assembly, the static pressure of the fluid in the meter assembly may increase or decrease. For example, increasing the velocity of the fluid may decrease the static pressure of the fluid in the meter assembly.

The previously determined relationship between the drive gain and the reference gas-liquid ratio may be a direct relationship or an indirect relationship. For example, a direct previously determined relationship between the drive gain and the reference gas-liquid ratio may be a linear relationship that relates a drive gain to a gas-liquid ratio over a range. The range may be from a drive gain associated with a true vapor pressure to a drive gain of 100 percent. In an example, the drive gain associated with the true vapor pressure may be about 10 percent, although any suitable value may be employed.

In an exemplary indirect relationship, the reference gas-liquid ratio may be associated with a static pressure, which is subtracted from by the vapor pressure meter factor. The vapor pressure meter factor may therefore also be associated with a drive gain threshold associated with an uncorrected vapor pressure. Accordingly, a value of the gas-liquid ratio may not necessarily be used to calculate the vapor pressure, such as a true vapor pressure, but the previously determined relationship between the drive gain and the gas liquid-ratio may nevertheless be a basis for determining a vapor pressure.

FIG.7shows a method700of determining a vapor pressure meter factor for determining a vapor pressure. As shown inFIG.7, the method700, in step710, determines a static pressure of a fluid in a meter assembly. In step720, the method700determines a difference between the static pressure and a true vapor pressure of the fluid.

The method700may further include providing a signal to the meter assembly, measuring a drive gain of the drive signal provided to the meter assembly, and/or associating the static pressure of the fluid in the meter assembly with the drive gain. Additionally or alternatively, the method700may include associating a drive gain threshold for detecting a phase change in the fluid with a measured drive gain, and associating the difference with the drive gain threshold.

The above describes the vibratory meter5, in particular the meter electronics20, and method600that determine a vapor pressure using a vapor pressure meter factor. By using the vapor pressure meter factor, a threshold, such as the drive gain threshold line340, may be accounted for. More specifically, a vapor pressure value associated with the drive gain threshold line340may be corrected by the vapor pressure meter factor to obtain a true vapor pressure value. The true vapor pressure value may correspond to where a phase change occurs in a fluid, but there is no vapor in the fluid. Accordingly, the determined vapor pressure may be more accurate. As a result, the operation of the vibratory meter5and the meter electronics20is improved because the values provided by the vibratory meter5and meter electronics20are more accurate. More accurate measurements in the technical field of vapor pressure measurements can improve other technical fields, such as fluid process controls, or the like.

The detailed descriptions of the above embodiments are not exhaustive descriptions of all embodiments contemplated by the inventors to be within the scope of the present description. Indeed, persons skilled in the art will recognize that certain elements of the above-described embodiments may variously be combined or eliminated to create further embodiments, and such further embodiments fall within the scope and teachings of the present description. It will also be apparent to those of ordinary skill in the art that the above-described embodiments may be combined in whole or in part to create additional embodiments within the scope and teachings of the present description.

Thus, although specific embodiments are described herein for illustrative purposes, various equivalent modifications are possible within the scope of the present description, as those skilled in the relevant art will recognize. The teachings provided herein can be applied to other ways of determining the vapor pressure using the vapor pressure meter factor and not just to the embodiments described above and shown in the accompanying figures. Accordingly, the scope of the embodiments described above should be determined from the following claims.