CN101033748A - Method for determining pump flow without the use of traditional sensors - Google Patents
Method for determining pump flow without the use of traditional sensors Download PDFInfo
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- CN101033748A CN101033748A CNA2007100082961A CN200710008296A CN101033748A CN 101033748 A CN101033748 A CN 101033748A CN A2007100082961 A CNA2007100082961 A CN A2007100082961A CN 200710008296 A CN200710008296 A CN 200710008296A CN 101033748 A CN101033748 A CN 101033748A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
- F04D15/0088—Testing machines
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
- F04D15/0066—Control, e.g. regulation, of pumps, pumping installations or systems by changing the speed, e.g. of the driving engine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
- F04D27/001—Testing thereof; Determination or simulation of flow characteristics; Stall or surge detection, e.g. condition monitoring
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
- F04D27/004—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids by varying driving speed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2270/00—Control
- F05D2270/30—Control parameters, e.g. input parameters
- F05D2270/335—Output power or torque
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Abstract
A technique for determining pump flow without using traditional sensors features steps and modules for creating a calibrated power curve at closed valve conditions at several speeds; calculating coefficients from a normalized power curve based on a pump's power ratio; and solving a polynomial power equation for flow at the current operating point. The calibrated power curve may be created by increasing the speed of the pump from a minimum speed to a maximum speed and operating the pump with a closed discharge valve. This data is used to correct published performance for shutoff power and best efficiency point power at rated speed in order to determine the pump's power ratio. It is also used to accurately determine closed valve power at the current operating speed. The pump's power ratio is determined by the equation: Pratio=Pshutoff @100%/PBEP<SUB2>-</SUB2>corr. The polynomial power equation may, for example, include a 3rd order polynomial equation developed using coefficients from the normalized power versus flow curve, and corrections may be made for speed, hydraulic efficiency and specific gravity in the polynomial power equation. Complex roots may be determined to solve the 3rd order polynomial equation using either Muller's method or some other suitable method, and the calculated actual flow may be determined for a specific operating point.The present invention provides protection for centrifugal pumps while differentiating between dangerous operating conditions (e.g. dry running, minimum flow and runout) and/or conditions where transient conditions (e.g. closed valve operation) may occur and the protection can be revoked once the condition clears. The methodology utilizes a calculated flow value which can be mathematically determined from a calibrated closed valve power vs speed curve and/or various pump and motor parameters such as speed, torque, power and/or differential pressure or from calibrated flow curves stored in the evaluation device.
Description
The cross reference of related application
Present patent application require to enjoy submitted on March 8th, 2006 be entitled as " Method forDetermining Pump Flow Without the Use of Traditional Sensors " temporary patent application No.60/780 (911-2.24-1/05GI003), 546 rights and interests, present patent application also relates on November 17th, 2006 submit be entitled as " Method andApparatus For Pump Protection Without the Use of TraditionalSensors " patent application No.11/601 (911-2.22-1/05GI002), 373, and being entitled as of also relating on March 8th, 2006 and submit " Method for Optimizing ValvePosition and Pump Speed in a PID Control Valve System withoutthe Use of External Sensors) " temporary patent application No.60/780 (911-2.23-1/06GI001), 547.The full content of these all patent applications is quoted by reference at this.
Technical field
The present invention relates to have the pumping system of the pump that comprises centrifugal pump; And be particularly related to the method for definite pump duty of not using traditional sensors.
Background technique
Pumping unit is known in the present technique field, and technology related with it and their shortcoming are as follows:
As everyone knows, pump controller using pump cutting law (Pump Affinity Law), these laws are how rotating speed and impeller adjustment are influenced the approximate of centrifugal pump performance (flow, pressure head, power).Though the cutting law is effectively for general estimation, the factor coefficient of power often cause based on pump running speed, size and specific rotation speeds to the overestimate of power or low excessively.This error directly has influence on and can be in the interior pump protection of programmable logic controller (PLC) (PLC), Distributed Control System (DCS) and frequency conversion drive (VFD) and the algorithm of volume forecasting.
In addition, when setting up the pump performance mapping, actual pump performance and the deviation between the standard performance curve have reduced the accuracy of flow and/or the estimation of pump condition significantly.The most general solution is the pump performance test of carrying out under multiple rotating speed to this, to confirm accurate pump performance.Yet, this solution may be timely, special-purpose with expensive.Under the circumstances, in the industry, need the error that a kind of technology can overcome the cutting law.
Authorize the U.S. Patent No. 6 of Moeller, 715,996 B2 disclose a kind of operating method of centrifugal pump, this method is being sampled to the pump power that is under the condition that valve cuts out on two kinds of rotating speeds, determine parasitic drain, and calculate at the adjustment power on other frequencies to determine whether pump operates under the condition that valve cuts out.Yet the method that such correction is in the power under the condition that valve cuts out begins to reduce in 50% o'clock precision that motor speed is lower than rated speed, has therefore limited the scope of using.This method part of carrying out interpolation between the performance number of other rotating speeds is based on the cutting law, thereby accurate inadequately.
PCT WO 2005/064167 A1 that authorizes people such as Witzel, Rolf discloses a kind of technology, this technology used through the calibration power/differential pressure to the curve of flow to rotating speed.Data through calibration store, and compare with currency, to determine the flow of pump.This Technology Need differential pressure transmitter, and require the calibration curve of power/differential pressure to flow is stored in the valuation equipment.This method is special-purpose for obtaining flow, has therefore reduced the flexibility during being provided with at the scene.It also is not easy to adjust for compensate for wear.
The U.S. Patent No. 6,591,697 of authorizing Henyan discloses uses motor torque to measure the method for the flow velocity of determining pump, and it has illustrated torque and rotating speed is adjusted the ability that the centrifugal pump rotating speed is regulated pump duty to the relation and the use frequency conversion drive (VFD) of flow rate pump.Yet, this technology utilization for the flow calibrated on the rotating speed of some special uses to torque curve, therefore reduced the flexibility during being provided with at the scene.It also is not easy to adjust for compensate for wear.
U.S. Patent No. 6,464,464 B2 that authorize people such as Sabini disclose a kind of being used for based on using VFD to regulate the equipment and the method for the control pump system of the control of flow, pressure or rotating speed of centrifugal pump and pump protection algorithm.Yet this Technology Need uses auxiliary instrumentation, and this has increased the cost and the complexity of drive system, and has added possible fault point and unnecessary cost.It also utilizes the flow of calibrating on the rotating speed of some special uses to the TDH curve, has therefore reduced the flexibility during being provided with at the scene.
In addition, in the present invention being carried out the patentability search, find to have following patent.The summary of these patents is as follows.
Patent No.4,358,821 disclose a kind of in process variable control the method and apparatus in conjunction with variable flow, wherein the flow that passes through is measured, by the measurement result integration being determined the amount of substance of the process that flows through.
Patent No.5,213,477 disclose a kind of equipment that pump transmits flow speed control that is used for, and wherein maximum permission flow is determined based on the relation between the available and needed net positive suction head (NPSH).
Patent No.6,424,873 disclose a kind of method and system, are used for not comprising the integral and calculating assembly of main PID controller or including only its a part of technology based on calculating at PID the integral and calculating assembly in the restriction PID controller.
Patent No.6,546,295 disclose a kind of in industrial process the method for tuning process control loop, wherein by determining the Control Parameter fine tuning field apparatus and the process controller of interactional controller, so that desirable process variability to be provided.
Patent No.6,554,198 disclose a kind of being used for based on the technology that relates to the error between calculated gas flow setting value and the measured air-flow, control at the slope predication control and the digital PID of pressure-independent variable air flow (VAV) temperature control system inner control VAV box.
System and method are disclosed for patent disclosure No.2004/0267395, be used for based on certain technology, the optimization of dynamic multi-object is carried out in machine choice, integration and use, wherein in described technology, revised the utilization of resources in the industrial automation system based on the function of diagnosis of being analyzed and machine data.
Patent disclosure No.2005/0237021 discloses a kind of rotational driving device of construction plant of the method and apparatus with constant mean velocity suction fluid.
Top patent of mentioning or the open technology that does not all have prompting or advise illustrated definite pump duty of not using traditional sensors here.
Summary of the invention
The invention provides the method for pump duty in a kind of novel unique definite centrifugal pump, centrifugal blender, centrifugal blower or centrifugal compressor of not using traditional sensors, the characterization step of this method is: the power curve that is created in the calibration that is in the condition that valve cuts out under some rotating speeds; According to the power ratio of pump from power to the flow curve design factor; And for to separate power equation at the flow of current operating point.
Can be by when making pump close under the situation of bleeder valve operation, the rotating speed of pump being incremented to maximum (top) speed from minimum speed and being captured in rotating speed under some rotating speeds and power curve that power data is created calibration.These data are used for proofreading and correct when rated speed for the performance of being announced of closing power and best efficiency point power, to determine the power ratio of pump.It also is used for accurately determining the power that the valve when current operating speed cuts out.This is essential, because the performance data of being announced is usually owing to sealing loss, wearing and tearing, casting deviation etc. are different with real data.
The power ratio of pump is calculated with following formula:
P
ratio＝P
shutoff@100％/P
BEP_corr。
Power equation for example can comprise the three rank polynomial equations that use forms the coefficient of flow curve from normalized power, and can proofread and correct for the rotating speed in the multinomial power equation and hydraulic efficiency.In addition, complex root can be determined, separating three rank polynomial equations, and the actual flow that is calculated can be determined in particular point of operation with Muller method or some other suitable method.
Each step of this method can go up at the frequency conversion drive (VFD) of the module with one or more functions that are implemented in here to be proposed and programmable logic controller (PLC) (PLC) and carry out.
The present invention can also comprise the controller of the module with one or more functions that are configured to be implemented in here and proposed and the pumping system with such controller.
Description of drawings
This specification comprises the following drawings, wherein:
Fig. 1 is the skeleton diagram according to basic pumping system of the present invention;
Fig. 2 is according to the flow chart of the present invention by the basic step of controller execution shown in Figure 1;
Fig. 3 carries out the skeleton diagram of the controller of basic step shown in Figure 2 for being used to shown in Fig. 1;
Fig. 4 is the % error (HP) of using the whole bag of tricks such as three interpolations, method X and cutting laws the plotted curve to rotating speed (RPM);
Fig. 5 under the condition that valve cuts out for the power (HP) of actual driving power, tune power and cutting method plotted curve to rotating speed (RPM);
Fig. 6 be power (BHP) for actual driving power to the plotted curve of flow (GPM), wherein also show the data of quotation (pricebook) (the band sealing) announcement and with the data of the tune power correction of polynomial curve fitting for each data array;
Fig. 7 at RPM be 1700,2200,2800,3570 o'clock reality and as the normalized curve figure of the % power (HP) that is calculated to % flow (RPM); And
Fig. 8 is for the tune power (BHP) of actual flow and the institute's calculated flow rate plotted curve to flow (GPM).
Specific embodiment
Fig. 1 show totally be designated as 2 according to basic pumping system of the present invention, it has controller 4, motor 6 and pump 8.In operation, according to the present invention, controller 4 is used under the situation of not using traditional sensors, and based on determining pump duty with shown here and illustrated certain consistent technology, wherein said technology is created in the power curve that is in the condition calibration that valve cuts out under some rotating speeds; Based on the power ratio of pump from power to the flow curve design factor; And for to separate power equation at the flow of current operating point.
Fig. 2 shows in the mode of example and totally is designated as 10 flow chart, and it has basic step 10a, 10b, the 10c that can be determined algorithm by the pump duty that controller 4 is realized according to the present invention.Determined flow value can also come control flow rate as the input to pid control circuit, and does not need external flow meter or traditional instrumentation.Flow determines that algorithm can embed frequency conversion drive or programmable logic controller (PLC), as above to the controller among Fig. 14 illustrated.
According to the present invention, can be by when making pump close under the situation of bleeder valve operation, the rotating speed of pump being incremented to the power curve that maximum (top) speed is created calibration from minimum speed.These data are used for proofreading and correct the performance of being announced of closing power and best efficiency point power in rated speed, to determine the power ratio of pump.It also is used for accurately determining the power of closing at the valve of current operating speed.
The power ratio of pump can be calculated with following formula:
P
ratio＝P
shutoff@100％/P
BEP_corr.
Power equation for example can comprise the three rank polynomial equations that use forms the coefficient of flow curve from normalized power, can carry out some corrections for the rotating speed in the multinomial power equation and hydraulic efficiency.In addition, complex root can be determined, separating this three rank polynomial equation, thereby the actual flow that is calculated can be determined in particular point of operation with Muller method or some other proper method.
An advantage of the invention is by under the condition of closing the power of each rotating speed being sampled to have overcome the error of cutting law, thereby can generate the power curve that is in the condition of closing accurately at valve.By using three times exclusive interpolating methods, just can in wide speed range, accurately determine to be in the pump power of the condition that valve cuts out.See the curve shown in the Figure 4 and 5.
Because the linear pump seal loss that changes uses the power of the pump performance curve data of being announced different with actual power usually.Can be used to the power that curve that biasing (adjustments) announced is located at the best efficiency point (BEP) of pump in the difference of the actual power of the condition of closing and the power of being announced, is constant because seal loss for given rotating speed.This approach has been eliminated pump performance curve (for example, factory testing) or the comparatively needs of complicated field calibration process highly accurately.This process has been created more accurately to P
BEPAnd P
SOEstimation at different rotating speeds.So these data can be used for according to minimum external data pump performance being carried out advanced modeling.
Integrating the method for normalized power coefficient in three rank power equations has eliminated carry out the needs of traffic alignment at the parameter such as torque, power or pressure at different rotating speeds, eliminated needs, and the application flexibility during the on-the-spot setting is provided external sender.The present invention can be below periodically carrying out the illustrated tuning wear compensation that provides in steps A.
Fig. 3: controller 4
Fig. 3 shows basic module 4a, 4b, 4c, the 4d of controller 4.Known in this technical field have many dissimilar and controller and control modules kind can be used for pump is controlled.Based on to the such known control device and the understanding of control module, according to the present invention, those skilled in the art will realize that the control module such as 4a, 4b, 4c carries out and illustrated consistent function with they are configured to here, comprise: the power curve that is created in the calibration that is in the condition that valve cuts out under some rotating speeds; Power ratio according to pump is calculated the normalized power curve coefficients; And for to separate the multinomial power equation at the flow of current operating point, all as shown in Figure 2 with discussed above.For instance, the function of module 4a, 4b, 4c can use hardware, software, firmware or their combination to realize, though scope of the present invention is not limited to any specific embodiment of the present invention.In typical software was realized, a kind of like this module can be one or more architectures with microprocessor, random-access memory (ram), ROM (read-only memory) (ROM), input-output apparatus and the control that is connected them, data and address bus based on microprocessor.Those skilled in the art does not need too many experience and just can programme to carry out illustrated function here to such realization based on microprocessor.Scope of the present invention is not limited to any specific embodiment that uses technology known or that develop in the future.
Controller also has at other controller modules 4d known in the art, and these modules do not form substantial section of the present invention, therefore here just they is not elaborated.
Motor 6 and pump 8
Motor 6 and pump 8 are well-known in the present technique field, here do not elaborate.In addition, scope of the present invention is not limited to any particular type now known or that develop in the future or the motor and the pump of kind.In addition, scope of the present invention should comprise that also use is according to the operation relevant technology of the present invention with control centrifugal pump, centrifugal stirrer, centrifugal blower or centrifugal compressor.
Implementation
This flow rate calculation method has two basic steps:
Steps A is the power curve that is created in the calibration that is in the condition that valve cuts out under some rotating speeds.
Step B is according to the power ratio calculating normalized power curve coefficients of pump with for to separate three rank multinomial power equations at the flow of current operating point.
Steps A:
Make when pump moves under the situation that bleeder valve is closed according to logic of the present invention the rotating speed of pump is incremented to higher rotation speed (for example 60% of maximum (top) speed) from predetermined minimum speed (for example 30% of maximum (top) speed).Rotating ratio should be about 2: 1.Then, under these rotating speeds and maximum speed, measure power, and proofreaied and correct for the situation of proportion=1 100%.
So the power of closing at any rotating speed can be definite with three times exclusive interpolating methods:
Coefficient A-F is calculated as follows:
A＝(P
SO_30％)/(N
30％)
B＝(P
SO_60％-P
SO_30％)/(N
60％-N
30％)
C＝(B-A)/(N
60％-N
30％)
D＝(P
SO_100％-P
SO_60％)/(N
100％-N
60％)
E＝(D-B)/(N
100％-N
30％)
F＝(E-C)/(N
100％)
Any rotating speed to close power calculation as follows:
P
SO_N％＝A(N
ACT)+C(N
ACT)(N
ACT-N
30％)+F(N
ACT)(N
ACT-N
30％)(N
ACT-N
60％)，
Wherein:
P
SO_30%=P
Meas_30%The power of/SG under motor rated speed, measuring 30% through proofreading and correct by proportion=1,
P
SO_60%=P
Meas_60%The power of/SG under motor rated speed, measuring 60% through proofreading and correct by proportion=1, and
P
SO_100%=P
Meas_100%The power of/SG under motor rated speed, measuring 100% through proofreading and correct by proportion=1.
It is to be noted that for some embodiment, for example unprssurized pump must be deducted eddy current loss from measured closing and estimate the performance number.
Should be noted also that for some embodiment such as acting on the little hp pump that proportion is not 1.0 liquid, superincumbent closing in the power equation can be done following compensation to mechanical loss (MechLoss) (for example sealing and bearing):
P
SO_N＝[(P
Meas_N％-(Mech Loss×N
Act/N
Rated))/SG]+(Mech Loss×N
Act/N
Rated)，
Wherein
SG=proportion,
N
30%The rotating speed of=30% motor rated speed,
N
60%The rotating speed of=60% motor rated speed, and
N
100%The rotating speed of=100% motor rated speed.
Fig. 5 illustrates tune power to the cutting law capability correction of speed curves and (closing) condition of closing at the valve plotted curve to the situation of comparing of actual power.
In the higher pump of power, must limit rotating speed at stand-by period, overheated to prevent pump.In this case, the power at 100% rotating speed can calculate with following formula:
P
SO_100％＝(N
100％/N
60％)
KSO×P
SO_60％，
Wherein, KSO is for closing index, and representative value is 3.0.
Last step according to logic of the present invention is the power of estimating at best efficiency point (BEP).Though this functional dependence is in the P of any given pump
BEPAnd P
SOActual value may significantly depart from the performance curve of being announced but the slope of power curve keeps geostationary observation.
Wherein:
P
SO=from the curve of being announced be in 100% rotating speed the time the pump power of the condition of closing, and
P
BEP=from the curve of being announced be in 100% rotating speed the time the pump power of BEP.
Fig. 6 illustrates tune power to the curve of flow and the diagrammatic sketch of the relation of the quotation curve of being announced.Notice that these two slope of a curves are identical.
Can also adopt other comparatively coarse approximate, to obtain factor coefficient " K
SO", it can be estimated with the ratio of the natural logarithm of rotating ratio by the natural logarithm of getting power ratio as follows:
KSO＝LN(P
so1/P
so2)/LN(N
1/N
2)
Wherein:
P
So1The measured power of closing when=rotating speed is N1, and
P
So2=rotating speed is measured during for N2 closes power.
So closing power and can be defined as when any rotating speed:
P
SOxrpm＝P
SOyrpm×(N
xrpm/N
yrpm)
KSO
Wherein:
P
SOxrpm=rotating speed is N
XrpmThe time close power, and
P
SOyrpm=rotating speed is N
YrpmThe time close power.
Step B:
For the flow value of determining to be calculated, calculate the normalized power curve according to the power ratio of pump, wherein:
P
Ratio＝P
SO_100％/P
BEPcorr.
Normalized curve is specific for the power ratio and the concrete rotating speed of pump.Concrete rotating speed is the numerical value relevant with the hydraulic performance of centrifugal pump.
Fig. 7 illustrates in the mode of example has P
Ratio=0.45 and concrete rotating speed be the plotted curve of the normalized curve of drawing for some rotating speeds of 2 * 3-13 end aspiration pump of 836.
Following table show 2 * 3-13 pump when 3570rpm flow and the reality of power to normalized test data.
| Flow (Gpm) | The flow of normalization | Power (HP) | The power of |
| 0 | 0.00 | 79.8 | 0.45 |
| 188 | 0.24 | 102.7 | 0.58 |
| 398 | 0.51 | 129.2 | 0.73 |
| 590 | 0.76 | 154.5 | 0.87 |
| The 775Bep flow | 1.00 | 177.2BepHP | 1.00 |
| 960 | 1.24 | 198.7 | 1.12 |
Three rank multinomial power equations are used from normalized power the coefficient of flow curve are derived.In power equation, done correction for rotating speed and hydraulic efficiency.
Normalized power to coefficient a, the b of flow curve and c as the shape of normalized curve of having given a definition:
0＝[(P
BEPCORR(a))/((Q
BEP)
3(η
HBEP_CORR))](Q
Act)
3+[((N
Act)(P
BEPCORR)(b))/((N
Rated)(Q
BEP)
2(η
HBEP_CORR))](Q
Act)
2+[((N
Act)
2(P
BEPCORR)(c))/((N
Rated)
2(Q
BEP)(η
HBEP_CORR))](Q
Act)+(P
SO_N％-(P
ACT/S.G.))，
Wherein:
P
BEPCORR=as in rated speed from the determined calibrated pump power that is in BEP of tune power curve,
Q
BEP=when rated speed, be in the pump duty of BEP,
η
HBEP_CORR=hydraulic efficiency is proofreaied and correct,
The value of being announced usually in the scope of 0.7-0.95,
N
Act=practical operation rotating speed,
N
Rated=rated speed,
P
SO_N%=pump when the practical operation rotating speed cuts out power (determining according to the tune power curve),
P
ACT=actual pump power,
S.G.=proportion, and
Q
Act=the actual flow that when current operating speed, calculated.
Should also be noted that for some embodiment for example being used for proportion is the little hp pump of the liquid outside 1.0,, can pass through following adjustment P in the superincumbent power equation in order to improve precision
ACTMechanical loss (such as sealing and bearing) is compensated:
P
ACTCORR＝[((P
ACT-(Mech Loss×N
Act/N
Rated))/S.G.)+(Mech Loss×N
Act/N
Rated)]
It should be appreciated that once more,, must from the actual power reading, deduct eddy current loss in the superincumbent power equation and estimate for some embodiment such as unprssurized pump.
Then, determine complex root, so that use Muller method or other equivalent methods to separate three rank multinomials.Then, for the definite actual flow that is calculated of specific operation point.It is that the power of the three rank multinomial power equations calculating of being drawn is to the comparison of flow curve with the actual flow data that obtained by meter readings that Fig. 8 shows.
Because the pump wearing and tearing will influence the pump power requirement, thereby reduce flow accuracy, so power calculation can regularly be compensated as calibrating at the another kind shown in the steps A by carrying out.
The application that other are possible
Other possible application comprise following at least listed:
Pump load monitors: pump load monitors the accurate modeling of depending on the pump power curve, to discern minimum discharge and to close condition.Though most of loads monitor the power that just monitors when a kind of rotating speed, this logic can monitor for the speed variable operation provides comparatively accurate load.
The flow rate calculation of no sensor: the flow of no sensor estimates to depend on that the accurate power curve is to estimate the flow of pump.Use basic cutting law may damage the precision of flow when rotating speed reduces.Become more outstanding and can not be particularly like this according to cutting the miniature pump that law turns to the factor for for example sealing and the loss of bearing.
Pump protection algorithm: the flow measurement of no sensor can provide the reliable indication of operational condition; point out it is, be lower than under the condition of minimum pump duty (flow is low excessively) and operate, still operate closing under the condition of bleeder valve in operation under the condition of overload (flow is too high).
Scope of the present invention
Unless it should be understood that has explanation here in addition, here to the illustrated any feature of specific embodiment, characteristic, substitute or revise and also can be applied to or be used for any other illustrated embodiment here or combine with these embodiments.In addition, these accompanying drawings are not here drawn in proportion.
Its exemplary embodiment describes though the invention relates to, and can carry out aforementioned and various other and increase and omit in these exemplary embodiments, and not deviate from the spirit and scope of the present invention.
Claims (57)
1. the method for the pump duty in a definite centrifugal pump, centrifugal stirrer, centrifugal blower or the centrifugal compressor comprises:
Be created in the power curve of the calibration that is in the condition that valve cuts out under some rotating speeds;
According to the power ratio of pump from power to the flow curve design factor; And
For the flow at current operating point is separated power equation.
2. in accordance with the method for claim 1, wherein the power curve of this calibration is to create by the rotating speed and the power data that when making this pump close under the situation of bleeder valve operation the rotating speed of this pump are incremented to maximum (top) speed from minimum speed and be captured under some rotating speeds.
3. in accordance with the method for claim 2, wherein this valve power data of closing equals 1 by proportion and proofreaies and correct.
4. wherein, in the power reading that the valve of measuring cuts out, can following mechanical loss (for example sealing and bearing) be compensated in accordance with the method for claim 2, for being applied to the little hp pump that proportion is not 1.0 liquid:
P
SO_N＝[(P
Meas_N％-(Mech Loss×N
Act/N
Rated))/SG]+(Mech Loss×N
Act/N
Rated)，
Wherein
SG=proportion.
5. in accordance with the method for claim 2, wherein must deduct eddy current loss for unprssurized pump from the power reading that actual valve is closed estimates.
6. in accordance with the method for claim 2,, can calculate the power of closing when 100% rotating speed from following formula to the heating minimum of the liquid that is subjected to this pumping action in order to make wherein for the higher pump of power:
P
SO_100％＝(N
100％/N
60％)
KSO×P
SO_60％，
Wherein, KSO is for closing index, and representative value is 3.0.
7. in accordance with the method for claim 2, wherein the power of closing of the valve when any rotating speed can accurately be determined by following three interpolating methods:
A＝(P
SO_30％)/(N
30％)，
B＝(P
SO_60％-P
SO_30％)/(N
60％-N
30％)，
C＝(B-A)/(N
60％-N
30％)，
D＝(P
SO_100％-P
SO_60％)/(N
100％-N
60％)，
E=(D-B)/((N
100%-N
30%), and
F=(E-C)/(N
100%); And
Wherein, when any rotating speed to close power calculation as follows:
P
SO_N％＝A(N
ACT)+C(N
ACT)(N
ACT-N
30％)+F(N
ACT)(N
ACT-N
30％)(N
ACT-N
60％)，
Wherein:
P
SO_30%=P
Meas_30%/ SG is the power of closing of measuring when 30% the motor rated speed of proofreading and correct by proportion=1,
P
SO_60%=P
Meas_60%/ SG is the power of closing of measuring when 60% the motor rated speed of proofreading and correct by proportion=1, and
P
SO_100%=P
Meas_100%/ SG is the power of closing of measuring when 100% the motor rated speed of proofreading and correct by proportion=1.
8. in accordance with the method for claim 2, wherein being in the power data that this power of announcing of this best efficiency point closes according to actual valve when rated speed proofreaies and correct.
9. in accordance with the method for claim 8, this power announced that wherein is in best efficiency point is proofreaied and correct according to following formula:
Wherein:
P
SO=from the curve of being announced be in the pump power of closing when 100% rotating speed,
P
BEP=from the pump power that is in BEP when 100% rotating speed of the curve of being announced,
And
10. in accordance with the method for claim 1, wherein the power ratio of this pump is determined by following formula:
P
ratio＝P
shutoff@100%/P
BEP_corr。
11. in accordance with the method for claim 1, wherein this power equation is to use the polynomial equation of the coefficient of flow curve being derived from this power.
12. in accordance with the method for claim 11, wherein this multinomial power equation is:
0＝[(P
BEP CORR(a))/((Q
BEP)
3(η
HBEP_CORR))](Q
Act)
3
+f((N
Act)(P
BEP CORR)(b))/((N
Rated)(Q
BEP)
2(η
HBEP_CORR))](Q
Act)
2
+[((N
Act)
2(P
BEP CORR)(c))/((N
Rated)
2(Q
BEP)(η
HBEP_CORR))](Q
Act)
+(P
SO_N％-(P
ACT/S.G.))，
Wherein:
P
BEP CORP=as in rated speed from the determined calibrated pump power that is in BEP of tune power curve,
Q
BEP=when rated speed, be in the pump duty of BEP,
η
HBEP_CORR=hydraulic efficiency is proofreaied and correct,
The value of being announced usually in the scope of 0.7-0.95,
N
Act=practical operation rotating speed,
N
Rated=rated speed,
P
SO_N%=pump when the practical operation rotating speed cuts out power (determining according to the tune power curve),
P
ACT=actual pump power,
S.G.=proportion, and
Q
Act=the actual flow that when current operating speed, calculated.
13. in accordance with the method for claim 12, wherein, can in this multinomial power equation, pass through following adjustment P for being used for the precision that proportion is the little hp pump of the liquid outside 1.0
ACTMechanical loss (for example sealing and bearing) is compensated:
P
ACT CORR＝[((P
ACT-(Mech Loss×N
Act/N
Rated))/S.G.)+(Mech Loss×N
Act/N
Rated)]。
14. in accordance with the method for claim 12, wherein must deduct the eddy current loss estimation this actual power reading in this multinomial power equation for unprssurized pump.
15. wherein rotating speed, hydraulic efficiency and proportion in this multinomial power equation are proofreaied and correct in accordance with the method for claim 11.
16. in accordance with the method for claim 15, wherein determine complex root, separate this polynomial equation to use Muller method or some other suitable method.
17. in accordance with the method for claim 16, wherein determine the actual flow that this calculates for particular point of operation.
18. in accordance with the method for claim 1, wherein each step of this method goes up execution in frequency conversion drive (VFD) or programmable logic controller (PLC) (PLC).
19. in accordance with the method for claim 1, wherein this determined flow value can come control flow rate as the input to the PID controller, and does not need flowmeter or other externally measured instrument.
20. a controller that is used for determining the pump duty in centrifugal pump, centrifugal stirrer, centrifugal blower or the centrifugal compressor comprises:
Be configured to be created in the module of the power curve of the calibration that is in the condition that valve cuts out under some rotating speeds;
Be configured to power ratio according to pump from the module of power to the flow curve design factor; And
Be configured as the module of separating power equation at the flow of current operating point.
21. according to the described controller of claim 20, wherein the power curve of this calibration is to create by the rotating speed and the power data that when making this pump close under the situation of bleeder valve operation the rotating speed of this pump are incremented to maximum (top) speed from minimum speed and be captured under some rotating speeds.
22. according to the described controller of claim 21, wherein this valve power data of closing equals 1 by proportion and proofreaies and correct.
23., wherein, in the power reading that the valve of measuring cuts out, can following mechanical loss (such as sealing and bearing) be compensated for being applied to the little hp pump that proportion is the liquid outside 1.0 according to the described controller of claim 21:
P
SO_N＝[(P
Meas_N％-(Mech Loss×N
Act/N
Rated))/SG]+(Mech Loss×N
Act/N
Rated)，
Wherein
SG=proportion.
24., wherein must from the power reading that actual valve is closed, deduct eddy current loss and estimate for unprssurized pump according to the described controller of claim 21.
25.,, can calculate when 100% rotating speed this from following formula to the heating minimum of the liquid that is subjected to this pumping action and close power in order to make wherein for the higher pump of power according to the described controller of claim 21:
P
SO_100％＝(N
100％/N
60％)
KSO×P
SO_60％，
Wherein, KSO is for closing index, and representative value is 3.0.
26. according to the described controller of claim 21, wherein the power of closing of this valve when any rotating speed can accurately be determined by following three interpolating methods:
A＝(P
SO_30％)/(N
30％)，
B＝(P
SO_60％-P
SO_30％)/(N
60％-N
30％)，
C＝(B-A)/(N
60％-N
30％)，
D＝(P
SO_100％-P
SO_60％)/(N
100％-N
60％)，
E=(D-B)/(N
100%-N
30%), and
F=(E-C)/(N
100%); And
Wherein, to close power calculation as follows for this when any rotating speed:
P
SO_N％＝A(N
ACT)+C(N
ACT)(N
ACT-N
30％)+
F(N
ACT)(N
ACT-N
30％)(N
ACT-N
60％)，
Wherein:
P
SO_30%=P
Meas_30%/ SG is the power of closing of measuring when 30% the motor rated speed of proofreading and correct by proportion=1,
P
SO_60%=P
Meas_60%/ SG is the power of closing of measuring when 60% the motor rated speed of proofreading and correct by proportion=1, and
P
SO_100%=P
Meas_100%/ SG is the power of closing of measuring when 100% the motor rated speed of proofreading and correct by proportion=1.
27., wherein when rated speed, be in the power data that this power of announcing of this best efficiency point closes according to actual valve and proofread and correct according to the described controller of claim 21.
28. according to the described controller of claim 27, this power announced that wherein is in best efficiency point is proofreaied and correct according to following formula:
Wherein:
P
SO=from the curve of being announced be in the pump power of closing when 100% rotating speed,
P
BEP=from the pump power that is in BEP when 100% rotating speed of the curve of being announced, and
29. according to the described controller of claim 20, wherein the power ratio of this pump is determined by following formula:
P
ratio＝P
shutoff@100％/P
BEP_corr。
30. according to the described controller of claim 20, wherein this power equation is to use the polynomial equation of the coefficient of flow curve being derived from this power.
31. according to the described controller of claim 30, wherein this multinomial power equation is:
0＝[(P
BEP CORR(a))/((Q
BEP)
3(η
HBEP_CORR))](Q
Act)
3
+[((N
Act)(P
BEP CORR)(b))/((N
Rated)(Q
BEP)
2(η
HBEP_CORR))](Q
Act)
2
+[((N
Act)
2(P
BEP CORR)(c))/((N
Rated)
2(Q
BEP)(η
HBEP_CORR))](Q
Act)
+(P
SO_N％-(P
ACT/S.G.))，
Wherein:
P
BEP CORR=as in rated speed from the determined calibrated pump power that is in BEP of tune power curve,
Q
BEP=when rated speed, be in the pump duty of BEP,
η
HBEP_CORR=hydraulic efficiency is proofreaied and correct,
The value of being announced usually in the scope of 0.7-0.95,
N
Act=practical operation rotating speed,
N
Rated=rated speed,
P
SO_N%=pump when the practical operation rotating speed cuts out power (determining according to the tune power curve),
P
ACT=actual pump power,
S.G.=proportion, and
Q
Act=the actual flow that when current operating speed, calculated.
32., wherein, can in this multinomial power equation, pass through following adjustment P for being used for the precision that proportion is the little hp pump of the liquid outside 1.0 according to the described controller of claim 30
ACTMechanical loss (for example sealing and bearing) is compensated:
P
ACT CORR＝[((P
ACT-(Mech Loss×N
Act/N
Rated))/S.G.)+(Mech Loss×N
Act/N
Rated)]。
33., wherein must deduct the eddy current loss estimation this actual power reading in this multinomial power equation for unprssurized pump according to the described controller of claim 30.
34., wherein rotating speed, hydraulic efficiency and proportion in this multinomial power equation are proofreaied and correct according to the described controller of claim 30.
35. according to the described controller of claim 34, wherein determine complex root, separate this polynomial equation to use Muller method or some other suitable method.
36., wherein determine the actual flow that this calculates for particular point of operation according to the described controller of claim 35.
37. according to the described controller of claim 20, wherein this controller comprises frequency conversion drive (VFD) or programmable logic controller (PLC) (PLC) or forms the part of this frequency conversion drive or this programmable logic controller (PLC).
38. according to the described controller of claim 20, wherein this determined flow value can come control flow rate as the input to the PID controller, and does not need flowmeter or other externally measured instrument.
39. the pumping system with the controller that is used for the pump duty in definite centrifugal pump, centrifugal stirrer, centrifugal blower or the centrifugal compressor, described controller comprises:
Be configured to be created in the module of the power curve of the calibration that is in the condition that valve cuts out under some rotating speeds;
Be configured to power ratio according to pump from the module of power to the flow curve design factor; And
Be configured as the module of separating power equation at the flow of current operating point.
40. according to the described pumping system of claim 39, wherein the power curve of this calibration is to create by the rotating speed and the power data that when making this pump close under the situation of bleeder valve operation the rotating speed of this pump are incremented to maximum (top) speed from minimum speed and be captured under some rotating speeds.
41. according to the described pumping system of claim 40, wherein this valve power data of closing equals 1 by proportion and proofreaies and correct.
42., wherein, in the power reading that the valve of measuring cuts out, can following mechanical loss (such as sealing and bearing) be compensated for being applied to the little hp pump that proportion is the liquid outside 1.0 according to the described pumping system of claim 40:
P
SO_N＝[(P
Meas_N％-(Mech Loss×N
Act/N
Rated))/SG]+(Mech Loss×N
Act/N
Rated)，
Wherein
SG=proportion.
43., wherein must from the power reading that actual valve is closed, deduct eddy current loss and estimate for unprssurized pump according to the described pumping system of claim 40.
44.,, can calculate when 100% rotating speed this from following formula to the heating minimum of the liquid that is subjected to this pumping action and close power in order to make wherein for the higher pump of power according to the described pumping system of claim 40:
P
SO_100％＝(N
100％/N
60％)
KSO×P
SO_60％，
Wherein, KSO is for closing index, and representative value is 3.0.
45. according to the described pumping system of claim 40, wherein the power of closing of this valve when any rotating speed can accurately be determined by following three interpolating methods:
A＝(P
SO_30％)/(N
30％)，
B＝(P
SO_60％-P
SO_30％)/(N
60％-N
30％)，
C＝(B-A)/(N
60％-N
30％)，
D＝(P
SO_100％-P
SO_60％)/(N
100％-N
60％)，
E=(D-B)/(N
100%-N
30%), and
F=(E-C)/(N
100%); And
Wherein, to close power calculation as follows for this when any rotating speed:
P
SO_N％＝A(N
ACT)+C(N
ACT)(N
ACT-N
30％)+
F(N
ACT)(N
ACT-N
30％)(N
ACT-N
60％)，
Wherein:
P
SO_30%=P
Meas_30%/ SG is the power of closing of measuring when 30% the motor rated speed of proofreading and correct by proportion=1,
P
SO_60%=P
Meas_60%/ SG is the power of closing of measuring when 60% the motor rated speed of proofreading and correct by proportion=1, and
P
SO_100%=P
Meas_100%/ SG is the power of closing of measuring when 100% the motor rated speed of proofreading and correct by proportion=1.
46., wherein when rated speed, be in the power data that this power of announcing of best efficiency point closes according to actual valve and proofread and correct according to the described pumping system of claim 40.
47. according to the described pumping system of claim 46, this power announced that wherein is in best efficiency point is proofreaied and correct according to following formula:
Wherein:
P
SO=from the curve of being announced be in the pump power of closing when 100% rotating speed,
P
BEP=from the pump power that is in BEP when 100% rotating speed of the curve of being announced,
And
48. according to the described pumping system of claim 39, wherein the power ratio of this pump is determined by following formula:
P
ratio＝P
shutoff@100％/P
BEP_corr。
49. according to the described pumping system of claim 39, wherein this power equation is to use the polynomial equation of the coefficient of flow curve being derived from this power.
50. according to the described pumping system of claim 49, wherein this multinomial power equation is:
0＝[(P
BEP CORR(a))/((Q
BEP)
3(η
HBEP_CORR))](Q
Act)
3
+[((N
Act)(P
BEP CORR)(b))/((N
Rated)(Q
BEP)
2(η
HBEP_CORR))](Q
Act)
2
+[((N
Act)
2(P
BEP CORR)(c))/((N
Rated)
2(Q
BEP)(η
HBEP_CORR))](Q
Act)
+(P
SO_N％-(P
ACT/S.G.))，
Wherein:
P
BEP CORR=as in rated speed from the determined calibrated pump power that is in BEP of tune power curve,
Q
BEP=when rated speed, be in the pump duty of BEP,
η
HBEP_CORR=hydraulic efficiency is proofreaied and correct,
The value of being announced usually in the scope of 0.7-0.95,
N
Act=practical operation rotating speed,
N
Rated=rated speed,
P
SO_N%=pump when the practical operation rotating speed cuts out power (determining according to the tune power curve),
P
ACT=actual pump power,
S.G.=proportion, and
Q
Act=the actual flow that when current operating speed, calculated.
51., wherein, can in this multinomial power equation, pass through following adjustment P for being used for the precision that proportion is the little hp pump of the liquid outside 1.0 according to the described pumping system of claim 49
ACTMechanical loss (for example sealing and bearing) is compensated:
P
ACT CORR＝[((P
ACT-(Mech Loss×N
Act/N
Rated))/S.G.)+(Mech Loss×N
Act/N
Rated)]。
52., wherein must deduct the eddy current loss estimation this actual power reading in this multinomial power equation for unprssurized pump according to the described pumping system of claim 49.
53., wherein rotating speed, hydraulic efficiency and proportion in this multinomial power equation are proofreaied and correct according to the described pumping system of claim 49.
54. according to the described pumping system of claim 53, wherein determine complex root, separate this polynomial equation to use Muller method or some other suitable method.
55., wherein determine the actual flow that this calculates for particular point of operation according to the described pumping system of claim 54.
56. according to the described pumping system of claim 39, wherein this controller comprises frequency conversion drive (VFD) or programmable logic controller (PLC) (PLC) or forms the part of this frequency conversion drive or this programmable logic controller (PLC).
57. according to the described pumping system of claim 39, wherein this determined flow value can come control flow rate as the input to the PID controller, and does not need flowmeter or other externally measured instrument.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US78054606P | 2006-03-08 | 2006-03-08 | |
| US60/780,546 | 2006-03-08 |
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|---|---|
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
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| Country | Link |
|---|---|
| CN (1) | CN101033748B (en) |
| DE (1) | DE102007009302B4 (en) |
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| CN109578262A (en) * | 2018-12-13 | 2019-04-05 | 保定申辰泵业有限公司 | A kind of control method, device and the peristaltic pump of peristaltic pump transmission viscous liquid |
| CN114667395A (en) * | 2019-12-31 | 2022-06-24 | 哈里伯顿能源服务公司 | Predicting brake horsepower for a viscous application pump |
| US11668594B2 (en) | 2020-06-26 | 2023-06-06 | Saudi Arabian Oil Company | Methods for controlling pump flow rate based on pump flow rate estimation using pump head and performance curves and pump control systems having the same |
| CN113157023A (en) * | 2020-12-31 | 2021-07-23 | 佛山市顺德区美的饮水机制造有限公司 | Control method and device for water dispenser, storage medium and processor |
Also Published As
| Publication number | Publication date |
|---|---|
| FI20070181A (en) | 2007-09-09 |
| FI121858B (en) | 2011-05-13 |
| DE102007009302B4 (en) | 2012-04-05 |
| FI20070181A0 (en) | 2007-03-02 |
| CN101033748B (en) | 2013-07-24 |
| DE102007009302A1 (en) | 2007-09-13 |
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