• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
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    • 专利摘要:

    公开号:NL1010324A1
    申请号:NL1010324
    申请日:1998-10-15
    公开日:1999-04-20
    发明作者:Graeme Robert Addie
    申请人:Giw Ind；
    IPC主号:
    专利说明:

    Method of controlling slurry pumps
    Background of the invention
    Figures 1-8 are performance charts of the known pumps.
    A common method of transporting solids used in the mining, dredging and other industries is to pump them as a mixture of water and solids within a pipeline using slurry pumps.
    Centrifugal slurry pumps are similar to centrifugal water pumps except that they have been modified to better suit and withstand the abrasive nature of the slurries they are to pump. These modifications are numerous, but are usually more robust structures to accommodate the higher horsepower, fewer vanes to allow passage of large solids and the construction of the wet end of the pump in thicker, hard metal (or rubber ) wear resistant materials.
    The slurries to be transported by these pumps generally consist of mixtures of water and various solids of different sizes at different concentrations. Examples of slurries are phosphate matrix, copper ore, taconite ore and crushed rock and sand as encountered in dredging.
    In order for pipeline transport of a normally crushed rock or other conventional settling slurry to occur as a mixture of water and solids, a certain minimum average mixing rate, called the deposition rate Vsm, must be exceeded.
    The deposition rate varies with the pipe size, particle size, SG of solids, particle shape and concentration. A typical slurry is made up of particles of a variety of sizes and shapes, so that the deposition rate in practice is not just one number, but a range of rates over which a bed forms.
    The head loss characteristic for most settling slurries at different delivered concentrations is normally assumed to be a U shape as shown in Figure 1, with a minimum head loss value increasing at higher and lower speeds.
    For constant speed centrifugal pump operation, operation is usually recommended at a speed slightly above the greater of the minimum head loss rate or the deposition rate shown at constant concentration in Figure 2, in order to avoid operation where this may be unstable or bed formation occurs .
    Calculated head loss in horizontal transport
    The head loss or pipeline friction along a pipe conveying a settling slurry is commonly expressed as a head in meters (or feet) of carrier fluid per meter (or feet) of the pipe, im. The corresponding head loss for the carrier liquid only at the same mixture speed will be indicated by iw. The excess head loss resulting from the presence of the solids is then {im-iw). Empirical correlations commonly attempt to predict either (ira-iw) or the relative increase in head loss (im-iw) / iw. Some of these correlations and their applications to slurries containing a wide range of particle sizes are explained by Wasp (Wasp, EJ et al. [2], 1977, Solids-liquid flow-slurry pipeline transportation, Trans. Tech. Publications.) . However, in the writer's experience, it is much more reliable to base design on tests performed on slurry representative of that to be pumped into practice.
    A method for scaling test results consists of distinguishing between different modes of solid transport and determining the contributions of the different modes to (im-iw).
    This approach is derived from Wilson's development (Wilson, KC, [3], 1992, Slurry Transport Using Centrifugal Pumps. Elsevier Applied Science, London and New York) from previous work on settling slurries by Newitt and Clift (Clift, R., et. Al. [4], 1982, A mechanistically-based method for scaling pipeline tests for settling slurries, Proc. Hydrotransport 8, BHRA Fluid Engineering, Cranfield, UK, pp. 91-101.).
    Tests have shown that a large number of heterogeneous slurries without excessive limitations and in the relevant heterogeneous region, the above can be simplified to
    (1) as described by Carstens and Addie (Addie, G.R., 1982, Slurry pipeline friction using nomographs. Froc. District 2 Meeting, (Sept lies, Quebec), Canadian Inst. Mining and Metallurgy.). Where the Uu constant is shown in Figure 3 from Addie deposited for various medium sized D50 slurries and the form of Equation 1 is the expected inverted parabola shown in Figure 1.
    The minimum head loss Vstn value in Figure 1, calculated using the above for pure (no small particles) crushed rock slurries for different constant (operating) concentrations in pipes of different diameter sizes is shown in Table 2.
    Table 2
    Minimum Head Loss (Stable) Speed (ft / sec) (Horizontal Pipe; Solids SG 2.65; Particle Form Factor 0.26) for Pure (No Small Particles) Shattered Rock Slurry
    Slurries vary considerably and while the above is true for most slurries in the noted size ranges, this does not apply to very large particles and coal where the particle shape (and SG of solids) is different from that of conventionally crushed rock.
    Other methods for calculating the head loss characteristic of heterogeneous slurries exist. This gives roughly comparable values or, at least, produces the same characteristics.
    Regardless of this, most settling slurries have a horizontal pipe head loss characteristic with a U shape with a minimal head loss which can be called the minimum stable operating speed.
    Centrifugal slurry pump performance
    If a given pump is driven at a constant shaft speed (which is fixed N), a series of readings of Q, H and P can be obtained at several orifices of the throttle located downstream of the pump. The head is plotted directly against delivery, as shown in Figure 4. This curve is known as the head delivery characteristic, or the head quantity (or head capacity) relationship, or simply the H-Q curve. The required power and efficiency are also plotted against Q, as shown in Figure 4, which shows representative pump characteristic curves.
    With N constant, efficiency 17 varies only with the ratio HQ / T, where T is always greater than zero. Thus, η will be zero at the condition of no current (Q = 0) and again when the H-Q curve intersects the release axis (here H = 0). Between these extremes, the efficiency curve shows a maximum, as shown in the figure. This maximum determines the "best efficiency" or BEP, and the associated release and head are often identified as QBEP and HBEP.
    The curves shown in Figure 4 refer to a single angular velocity, but if the tests were repeated with a different value of N, all the points shift. This behavior can be plotted as a series of H-Q curves for various angular velocities, with contours of efficiency and power added as shown in Figure 5. Figure 5 is a pump performance chart. Test data is not required for every curve; instead, the various constant velocity curves are constructed based on the following simple scale relationships. All releases (including both QBEP and the release at H = 0) shift in direct proportion to N, while all heads (including both the non-flow head and Hbep) shift in proportion to N2.
    The power output of the pump is determined by the product of Q and H, and is given by (Power) out = PfgQH = P «fg» Q * H (2) where Pf is the fluid density.
    This relationship holds true in any consistent unit system. Thus, SI units give the output power in watts, which is usually divided by 1000 to obtain kilowatts. With the units most commonly used in the United States of America, Q is expressed in US gallons per minute, and H in feet. Pump output power is expressed as water horsepower, and a numerical coefficient is required in the equation.
    With the overall pump efficiency included r P and the head H expressed in units of liquid (as mixture) produced (feet)
    The pump input power
    (3) where SG is the relative density of the mixture.
    Effects of Solids on Performance The presence of solids in the stream tends to produce adverse effects on pump performance.
    The effects on pump characteristics are shown schematically in Figure 6, which is a definition sketch for showing the reduction in head and efficiency of a centrifugal pump operating at a constant rotational speed and processing a solid-water mixture. In this sketch, ηη represents the pump efficiency in slurry service and r W is the pure water equivalent. Analogously, Pro and Pw are the power requirements for slurry service and water service, respectively. The head Hm is developed in slurry service measured in slurry height, while Η "represents the head developed in water service, in water height. The head ratio Hr and efficiency ratio 7 R are defined as Η ,,, / Η * 7 respectively. The fractional reduction in head (the head reduction factor) is denoted by R 'and defined as 1-Hr; for efficiency reduction efficiency (ef fiency reduction factor) is R77, given by l-r / r.
    Values of RH and jr range from zero to 10% for most heterogeneous slurries, but may be higher as the size and concentration of the solid increases. Fairly accurate values for R „and ηζ can be predicted from maps in Wasp and Wilson.
    Stability consideration
    Figure 7 shows typical "system characteristics" for a settling slurry at three released concentrations, in two forms. In Figure 7 (a), the frictional gradient is expressed as the head of carrier liquid, im, while Figure 7 (b) gives the same information in terms of head of slurry, jra. For simplicity, only the friction contribution is considered here, which is the discussion referring to horizontal transport.
    The total developed head measured in terms of delivered slurry density (Figure 7 (b)) decreases slightly with increasing concentration, due to the effect of solids on pump performance as discussed in Wasp and Wilson. As a result, the pump delivery head, measured as the water column equivalent to the pump delivery pressure, increases with slurry concentration. This increase is a little less than directly proportional to S ^. For the case shown in Figure 7, where the pump is selected to operate at the "standard speed" at point A, the system may record variations in solids concentration from zero up to the maximum shown: there will be some reduction in the average speed when Cvd increases, due to the effect of the solids on the pump characteristic (Figure 7 (a)), but the variation in stable condition operating conditions is small.
    However, the transient behavior is more interesting. Consider the case where the system has been operating stably at concentration 2, and the slurry presented to the pump suddenly changes to the higher concentration 3. Referring to Figure 7 (a), the system characteristic is now as 2, but the pump is processing a material with higher density so that its delivery pressure increases to characteristic 3. Thus, the immediate effect is to shift the system operating conditions to point B, increasing both the average slurry speed and the power drawn by the pump. As the higher concentration solid continues along the line, the system resistance moves up to characteristic 3, decreasing the speed and returning system operation to point C. By contrast, if the system has been operating continuously at point A and the slurry entering the pump suddenly reduced in concentration to 1, the mixing speed is reduced as the system goes to point D. As before, the system resistance now gradually returns to characteristic 1, and operation returns to point E.
    Figure 8 shows the operation of the same system but with pumps selected to further work back on the system characteristics, giving a rate below the "standard" value at concentration 2. The result of increasing solids concentration to characteristic 3 is now considered. As before, the effect on the pump occurs before the new concentration has progressed along the pipeline, so that the immediate effect is shifting action from A 'to B'. The system reacts more slowly again, and the pipe speed consequently decreases from the maximum at B '. In this case, however, stable operation at concentration 3 is not possible with fixed speed pumps as they cannot generate sufficient head. Thus, when the system achieves a characteristic corresponding to 3a, the speed decreases abruptly back into the deposition region. In other words, the line is provided with a "plug". Figure 8 (a) shows that reducing the solid concentration even after the point of pumping water only cannot purify the plug; higher pumping rates are needed, or alternatively slurry or fine particles may shift the deposit. If variable speed pumps or clay slurries are not available, the only tool will be to open the line at an intermediate point and pump out the solids.
    Two general conclusions can be drawn from the previous discussion. Comparing the system and pump characteristics is essential as it allows for a qualitative but very informative determination of operating stability. For systems driven by centrifugal pumps, operation at speeds below the "standard" speed is only possible for relatively fine slurries (see below) or for systems where the solids concentration is not subject to wide variations.
    Figure 8 also shows why the velocity at the boundary of the deposit is often unimportant for slurry settling; although operation resulted in a "plug-in line", the cause of which was poor adjustment (or control) of the pump and system characteristics, rather than working too close to deposit. This also shows why field data often indicate deposition rates (so-called) far above the calculated values; in reality they correspond to the limit of stable operation with centrifugal pumps, rather than the limit of operation without a stationary deposit. In practice, centrifugal pumps allow operation near the deposition point only for relatively fine particles.
    Where the pipeline head includes a large static component such as a mill cyclone supply and other circuits, the system characteristic is flatter and the above behavior may be more present.
    Analog (but different) effects are seen in Ref. 5 for the effect of particle size. Here, the effect of solids on the pump plays a major role.
    Operation of the prior art in the field
    Operation in an unstable manner as described results in plugging a line or in the case of a system where the suction collector level is significant with respect to the overall head, it may just result in large variations in flow through the pump when the pump stops pumping and then restarts when the sump level increases and the system characteristic drops back to that below the pump.
    Cyclone supply service is a good example here. Often the mill's orders and grinding process force operation at a current that is unstable. Here, the pump is often forced to work with the sump that empties and fills with the flow rocking back and forth. It is possible that the average current will meet the needs of the mill. However, the result on the pump is excessive wear and tear due to the wide variation in percentage of BEP quantity flow operation.
    As noted earlier, the operating point should always be where the pressure produced by the pump is equal to that of the system, where the resistance of the system is a function of the SG of the mixture, the elevation (or static head) change, the friction in the pipeline and a cyclone pressure.
    These (system values) can usually be measured or calculated using magnetic, venturi or Doppler flow meters; with nuclear "U" loop or other density gauges and a variety of different pressure gauges noting that where the static head is large with respect to friction, a current and SG measurement with calculated pipeline friction and elevation (from measured level differences) can be used.
    It should be noted here that the slurry is not compressible for all practical purposes and the flow is the same in the pump and pipeline. The density dimensions of solids, etc., may alternatively vary along the pipeline. However, if we average the readings over the average time it takes the slurry to pass through the entire system (normally in cyclone feed service about 10 seconds) then we can find a good overall average of the pipeline resistance at a given time .
    The equilibrium pressure (or not equilibrium pressure depending on the case) produced by the pump is directly related to the pump, its speed, the flow and the density or SG of fluid in the pump at a given time. The performance of the pump at pure water at a given speed and flow is usually known in terms of its tested water performance for the head produced and the power consumed.
    Pump input power is normally available either as watts or amperes from an electric motor driver, possibly a measured torque or even pressures and / or rack position for a diesel motor driver.
    Regardless of how it is collected, the pump input power can be calculated using one or more of the above methods using the readings noted and, if necessary, known or determinable motor, gear or other efficiencies. It should be noted here that in almost all cases the power reading can be obtained over a short period of time (or instantaneous) if necessary.
    Using the pump input power and the known pump characteristics with the known calculated or measured solids effect corrections for the slurry effect or the performance with respect to its water performance, an instantaneous pressure produced by the pump and SG in the pump can be determined.
    SUMMARY OF THE INVENTION The present invention therefore relates to a way of determining the instantaneous pressure produced by the pump (and the internal SG associated therewith) and how it can be used with respect to the overall total pipeline resistance to control the pump performance. and / or adjust to better operate the pump and / or reduce or eliminate the previously described unsuitable unstable operation, as well as any adverse cavitation, wear and other effects on the pump and pipeline associated therewith.
    DETAILED DESCRIPTION In particular, this invention relates to using the measured pump input power, the known or measured speed, the previously known pump performance (either for slurry or with solid effect corrections related to water) to instantaneous pump drive pressure (and SG) and use this to better control the pump so that it works in balance with the system and in a stable manner.
    The system pressure used for comparison here would be the pressure normally determined on a continuous average basis. This can be the calculated sum of the system static head, cyclone pressure and pipe friction using conventional flow and SG meter measurements or could even come from a system pressure sensor.
    Stable operation would, in principle, have the purpose of balancing the instantaneous pump pressure with the continuous average system pressure, while simultaneously meeting input flow and sump level restrictions.
    As noted earlier, for the determination of the instantaneous pump pressure and SG, we use the commonly accepted relationship of
    (3) where P = pump input power in horsepower Q = USgpm flow units
    Hra = pump head in base of slurry mixture SG = relative density of the mixture in the pump.
    77P = pump efficiency.
    Noting that the term r P mainly depends on the pump quantity Q at a given rotational speed N but must also be corrected or set for the effect of solid size, SG, etc.
    The ηρ and H value partly depends on the SG initially known only in the combined term H x SG. However, initial values of 7 P and H used can be found from the previously determined water performance test values for the pump at the measured speed and rpm to determine an initial SG. The final values of r P and H can then be determined using a solid effect correction and resubstitution of the SG value until the difference in the SG used in the correlation is close to the value as determined in the combined term lies.
    In the former case, therefore, knowing the instantaneous pump input power, rpm and the system flow and SG of the system, we can use the pump tested or estimated water performance, in the former case to determine the pump efficiency without solid effect.
    In this case (at this stage), the term Hm x SG represents an approximate value of the instantaneous pump pressure in pressure units commonly in feet H20.
    Now, using the known pump size, approximate slurry size, and average system slurry SG, a solid effect value is determined for Hr and T7p in Wilson's equations.
    HR = Hm / Hw and r P = and again using the tested and estimated water performance curve a more accurate instantaneous value of slurry SG can be calculated using equation 3.
    If the values of HR and r P are set to reflect the new instantaneous SG and the above is repeated because the changes in SG are small, then an accurate estimate of the instantaneous pump pressure and internal concentration (SG) can be determined for use in controlling the pump.
    In the above, the value for P is usually determined by instantaneous reading of the actuator input power. In the case of an electric actuator, it may be from a watt meter or motor efficiency correction or it may be using the instantaneous amperes. Using the commonly known relationship
    where E = volts I = amperes cos0 = motor power factor usually 0.8 for a 3 phase motor and 77ra = motor and / or acceleration efficiency
    The instantaneous relative density or SG here is the unknown or determined value which, in turn, depending on the slurry, can be used with a correction (as described) to determine the pump pressure produced in units of feet H20.
    Pressure = SG. Hm (pump)
    In a control system, therefore, the instantaneous pump pressure can be used to compare with the resistance pressure of the system usually determined using the measured overall elevation differences, an SG measurement taken over the time (approximately) the slurry needs to pass through the system. and a calculated value for the pipe friction component using
    H system (vt H20) = elevation fresh. X SG + pipe friction + cyclone pressure As previously described.
    The difference between the value of the gap pressure (pump) above and the HeyBteem value (and also alternatively the pump and system SG values) represents the instantaneous destabilizing drive pressure.
    This difference can then be used in a control circuit (with approximate timing and averaging) or other method to correct the imbalance by known conventional methods. This would set the pump speed using the conventionally known affinity laws
    where H = pump head N = pump speed 1 = initial 2 = eventually a likely method but if possible a quick change of incoming SG, sump level (special additives) or others could be used.
    The invention provides a method of comparing the instantaneous internal pump pressure of SG with the system pressure that can be used to control slurry pump operation in a slurry pipeline.
    The instantaneous driving force or pressure controlled (and destabilized) by the incoming change in slurry SG solid size, etc., (with respect to the system) can be determined and then used with respect to overall system head for instability reduce or eliminate in operation.
    The measured input power of a pump along with its known performance can be used to calculate an instantaneous pump pressure and internal density that when compared to an overall system resistance calculated from the elevations, flow, relative density and friction head component can be used to measure the pump performance in to minimize or eliminate unstable operation.
    By using this technique or method, operation and a so-called unstable area will be more stable and uniform, providing benefits during mining and for other customers whose processes and systems require it.
    By using this technique or method, operation in an unstable area will be possible with the instability, damage and increased wear on the pump associated with it being reduced or eliminated.
    The effective instantaneous pressure produced by a slurry pump can be determined from the instantaneous pump input power, rpm, flow and other parameters.
    The effective instantaneous mixture relative density in a slurry pump can be determined from the instantaneous pump input power, rpm, flow and other parameters.
    The effective internal pressure of a working slurry pump can be used to control or stabilize operation of that pump or pumps in a pipeline system.
    权利要求:
    Claims (9)
    [1]
    Method for controlling the operation of a slurry pump of the type comprising an electric motor, a centrifugal pump driven by the motor, the pump comprising an inlet for communication with a slurry, and an outlet for communication with a delivery line who develops a back pressure; characterized by using the instantaneous drive power supplied by the engine in accordance with:

    [2]
    The method of claim 1 and wherein the initial value of H and ηρ in the expression

    [3]
    The method of claim 1 and wherein the step of varying the performance of the pump comprises varying the particle size of the slurry.
    [4]
    The method of claim 1 and wherein the step of varying the performance of the pump comprises varying the level of the receptacle at the inlet of the pump.
    [5]
    The method of claim 1 and wherein the step of varying the performance of the pump comprises varying the speed of the pump.
    [6]
    A method of controlling the operation of a slurry pump of the type containing a motor, a centrifugal pump driven by the motor, the pump comprising an inlet for communicating with a slurry, and an outlet for communicating with a delivery line who develops a back pressure; characterized by using the instantaneous drive power supplied by the engine in accordance with:

    [7]
    The method of claim 6 and wherein the step of varying the performance of the pump comprises varying the particle size of the slurry.
    [8]
    The method of claim 6 and wherein the step of varying the performance of the pump comprises varying the level of the receptacle at the inlet of the pump.
    [9]
    The method of claim 6 and wherein the step of varying the performance of the pump comprises varying the speed of the pump.
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    同族专利:
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    法律状态:
    1999-07-01| AD1A| A request for search or an international type search has been filed|
    2000-03-01| EDI| The registered patent application has been withdrawn|
    优先权:
    申请号 | 申请日 | 专利标题
    US08/953,135|US6033187A|1997-10-17|1997-10-17|Method for controlling slurry pump performance to increase system operational stability|
    US95313597|1997-10-17|
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