CN118056075A

CN118056075A - System and method for monitoring pump vibration

Info

Publication number: CN118056075A
Application number: CN202280067780.4A
Authority: CN
Inventors: 蒂姆·桑德斯特罗伊姆
Original assignee: SPM Instrument AB
Current assignee: SPM Instrument AB
Priority date: 2021-10-09
Filing date: 2022-10-10
Publication date: 2024-05-17

Abstract

A method of operating a centrifugal pump (10) having a housing (62) with a rotatable impeller (20) disposed therein, the rotatable impeller (20) having a plurality (L) of blades for pressing fluid material (30) from a pump inlet (66) into a volute (75) as the rotatable impeller (20) rotates, the method comprising receiving a vibration signal (S _EP;S_EA,S_MD, se (i), S (j), S (q)) in accordance with a fluid material pulsation (V _p); receiving a signal (E _p, P (i), P (j), P (q)) indicative of a rotational position of the rotatable impeller (20) relative to the housing; information indicating an internal state of the centrifugal pump (10) is generated based on the vibration signal and the position signal.

Description

System and method for monitoring pump vibration

Technical Field

The present invention relates to the field of centrifugal pumps and monitoring of centrifugal pumps. The invention also relates to the field of control of centrifugal pumps. The invention also relates to a device for monitoring the internal state of a centrifugal pump. The invention also relates to a device for controlling the internal state of a centrifugal pump. The invention also relates to a computer program for monitoring the internal state of a centrifugal pump. The invention also relates to a computer program for controlling the internal state of a centrifugal pump.

Background

In certain industries, such as the paper industry, it is desirable to deliver fluid materials such as pulp. The mining industry also requires the delivery of fluid materials. Other industries (such as the dairy industry) also require transportation of fluids (such as dairy products). Furthermore, in many cases of modern society, there is also a need to transport fluid materials such as water, such as water for water towers and/or for agricultural irrigation.

Centrifugal pumps can achieve the delivery of fluid materials. For this purpose, centrifugal pumps have a rotatable part which is equipped with blades and is called an impeller. The impeller produces motion as the fluid passes through the pump. The fluid is accelerated by centrifugation in the rotating impeller to create pressure to achieve the desired head. Fluid may flow axially toward the impeller, be deflected by the impeller, and exit through the holes between the blades. Thus, the fluid changes direction and is accelerated. This results in an increase in pressure at the pump outlet. The fluid exits from the impeller and enters the volute, which collects the fluid and directs it out of the pump. The volute is the gradually widening portion of the volute of the pump. Alternatively, as the fluid leaves the impeller, it may first pass through a ring of fixed vanes surrounding the impeller, and is commonly referred to as a diffuser, and then enter the volute and flow to the pump outlet. The operation of centrifugal pumps is generally discussed in terms of pump operating point concepts.

US2003/0129062 (ITT Fluid Technology) discloses that the operating point of a pump is generally considered to be the flow rate and Total Dynamic Head (TDH) delivered by the pump. US2003/0129062 also discloses a method of determining an operating point of a centrifugal pump based on motor torque and motor speed. According to US2003/0129062, a method of determining whether a centrifugal pump is operating within a normal flow operating range comprises the steps of: determining a motor torque/TDH relationship within a speed range of a minimum flow rate to obtain a minimum flow operating range of the centrifugal pump; determining a motor torque/TDH relationship within a speed range of a maximum flow rate to obtain a maximum flow operating range of the centrifugal pump; determining actual running motor torque and TDH of the centrifugal pump at a given running point; and determining whether the actual operating motor torque and TDH of the centrifugal pump are within the minimum flow and maximum flow operating ranges of the centrifugal pump.

US 9,416,787 B2 (ABB Technology Oy) discloses that the flow rate-head curve (QH curve) and flow rate-power curve (QP curve) of the pump are provided by the pump manufacturer and are available for all pumps. US 9,416,787 B2 also discloses a method for determining the flow rate (Q) produced by a pump, which frequency converter estimates the rotational speed and torque of the pump when the pump is controlled by the frequency converter, and the pump characteristics are known. The method includes determining a shape of a QH curve of the pump, dividing the QH curve into two or more regions according to the shape of the QH curve, determining which region of the QH curve the pump is operating in, and determining a flow rate (Q) of the pump using the determined operating region of the characteristic curve.

Disclosure of Invention

In view of one aspect of the prior art, one problem that needs to be addressed is how to provide an improved way to identify the internal state of a centrifugal pump during operation. This problem is solved by way of example (such as by a method and/or system and/or pump as disclosed in the present disclosure).

In view of one aspect of the prior art, one problem that needs to be addressed is how to provide an improved way of optimizing the operation of a centrifugal pump. This problem is solved by way of example (such as by a method and/or system and/or pump as disclosed in the present disclosure).

In view of one aspect of the prior art, one problem that needs to be addressed is how to increase the efficiency of the pumping process of a centrifugal pump. This problem is solved by way of example (such as by a method and/or system and/or pump as disclosed in the present disclosure).

In view of one aspect of the prior art, it is a problem to be solved how to provide an improved way to identify and/or visualize and/or control the internal state of a centrifugal pump during operation, thereby improving the pumping process of the centrifugal pump. This problem is solved by way of example (such as by a method and/or system and/or pump as disclosed in the present disclosure).

Drawings

For a simple understanding of the invention, the invention will be described by way of example and with reference to the accompanying drawings, in which,

Fig. 1A shows a schematic side view of a system comprising a centrifugal pump.

Fig. 1B shows another schematic side view of a system including a centrifugal pump.

Fig. 2A is a diagram of the centrifugal pump 10.

Fig. 2B is a schematic diagram of the operating point of the pump of fig. 2A.

Fig. 2C is a block diagram illustrating a centrifugal pump as a block 10B that receives multiple inputs U1.

Fig. 2D is a diagram of an example of the centrifugal pump 10.

Fig. 2E is a diagram of another example of the centrifugal pump 10.

Fig. 3 is a schematic block diagram of an example of the analysis device 150 shown in fig. 1.

Fig. 4 is a simplified diagram of program memory 360 and its contents.

Fig. 5 is a block diagram showing an example of the analysis device 150.

Fig. 6A is a diagram of the signal pairs S (i) and P (i) delivered by the a/D converter 330.

Fig. 6B is a diagram of the sequence of signal pairs S (i) and P (i) delivered by the a/D converter 330.

Fig. 7 is a block diagram illustrating an example of a portion of a state parameter extractor 450.

Fig. 8 is a simplified diagram of an example of memory 460 and its contents.

Fig. 9 is a flowchart illustrating an example of a method of operation of the state parameter extractor 450 of fig. 7.

Fig. 10 is a flowchart showing an example of a method for performing step s#40 of fig. 9.

Fig. 11 is a flowchart showing another example of the method.

Fig. 12 is a flowchart showing an example of a method for performing step s#40 of fig. 9.

Fig. 13 is a graph showing a series of temporally successive position signals, each indicating a complete revolution of the monitored impeller.

Fig. 14A, 14B, and 14C illustrate another example of a cross-sectional view of a pump during operation.

Fig. 14D, 14E and 14F show another aspect of the flow and pressure patterns in the pump.

Fig. 14G is another illustration of the example pump 10 of any of fig. 1A, 1B, 2A, 2B, 2D, 2E, or 14A-14F.

Fig. 15A is a block diagram showing an example of the state parameter extractor 450.

FIG. 16 is a diagram of an example of a visual indication of analysis results.

Fig. 17 and 18 are diagrams of another example of visual indications of analysis results.

Fig. 19A is another example of a visual indication of the analysis results concerning the internal state of the centrifugal pump 10.

19B, 19C and 19D are diagrams of a number of internal status indicating objects relating to pumps having flow below BEP and flow above BEP.

Fig. 19E is a diagram of a first time chart of the amplitude of the detected fluid pressure pulsations in a centrifugal pump having four impeller blades.

Fig. 19F is another illustration of a second time plot of the amplitude of detected fluid pressure pulsations in the same centrifugal pump as discussed in connection with fig. 19E.

Fig. 20 is a block diagram of an example of a compensation decimator.

FIG. 21 is a flow chart illustrating one embodiment of a method of operation of the compensation decimator of FIG. 20.

22A, 22B and 22C are flowcharts of one embodiment of a method of operation of the compensation decimator of FIG. 20.

Fig. 23 is a block diagram showing another example of a state parameter extractor.

Fig. 24 shows a pump with an adaptive volute and sensor.

Fig. 25A illustrates another example system including a pump with an adaptive volute and sensor.

Fig. 25B is a cross-sectional top view of the pump shown in fig. 25A.

Fig. 26 shows a schematic diagram of yet another embodiment of a system including a pump with an adaptive volute and a sensor.

FIG. 27 shows a schematic block diagram of a distributed process monitoring system.

FIG. 28 shows a schematic block diagram of yet another embodiment of a distributed process monitoring system.

FIG. 29 shows a schematic block diagram of yet another embodiment of a distributed process control system.

Detailed Description

Hereinafter, similar features in different examples will be denoted by the same reference numerals.

Fig. 1A shows a system 5 comprising a centrifugal pump 10 for delivering a fluid 30 through a tubing 40 to a fluid material consumer 50. The fluid system to which the pump is coupled, including tubing 40 and fluid material consumer 50, is referred to herein as fluid system 52.

The fluid 30 may include a fibrous slurry 30A for use in papermaking production on a paper machine in the pulp and paper industry, with high volume papermaking at high speeds. The fluid material consumers 50 may include a headbox 50A, also known as a head tank, which is intended to maintain a constant head (i.e., constant pressure) of the fiber slurry 30A. The fluid material consumer 50 may include a metering valve (not shown) that functions to regulate the flow of the fluid 30A as the fluid 30A mixes with the white water to the headbox 50A and to regulate the flow of the forming wire where the sheet begins to form. Basis weight of paper is calculated from the weight of a given unit area. Accurate control of the metering valve is required to produce high quality paper. Fluctuations in paper layer thickness or basis weight can lead to uneven drying, poor quality of finished products and/or waste, as such fluctuations may require removal of the produced paper. Therefore, it is necessary to achieve a constant flow rate Q _OUT as delivered from the centrifugal pump 10 in order to produce high quality paper.

In the field of fluid dynamics, bernoulli's principle states that an increase in fluid velocity occurs simultaneously with a decrease in static pressure or a decrease in fluid potential. Thus, when a certain amount of fluid flows horizontally from the high pressure first region 54 to the low pressure second region 56, the rear pressure is greater than the front pressure. This creates a net force on the volume to accelerate the flow along the streamline. In the example shown in fig. 1, the tubing 40 that directs the fluid 30 from the first region 54 of high pressure to the second region 56 of low pressure includes a tubing component 58, which tubing component 58 may include a filter 58A.

The Bernoulli principle, for a volume of fluid flowing horizontally from the first region 54 of the high pressure P _H to the second region 56 of the low pressure P _L at a velocity v, can be expressed in mathematical terms as follows:

P+1/2×d×v=constant, (equation 1)

Wherein,

P = pressure of fluid material

D = density of fluid material

V = speed of fluid material flow

Thus, referring to fig. 1, when the bernoulli principle is applied to the volume of fluid flowing horizontally at a velocity v ₅₄ in the first region 54 of high pressure P ₅₄ to the second region 56 of low pressure P ₅₆, the fluid will flow at a velocity v ₅₆ in the second region 56, as shown in equation 2 below:

P ₅₄+1/2*D*v₅₄*v₅₄＝P₅₆+1/2*D*v₅₆*v₅₆ (equation 2)

Wherein,

P ₅₄ = pressure of fluid material in first region 54

D = density of fluid material

V ₅₄ = speed of fluid material flow in the first region 54

P ₅₆ = pressure of the fluid material in the second region 56,

V ₅₆ = speed of fluid material flow in the second region 56

Fig. 1B shows another schematic diagram of a system 325 including a centrifugal pump 10. Accordingly, reference numeral 325 refers to a system comprising a pump 10 having a rotatable impeller 20, as described herein. The system 325 in fig. 1B may include and be configured as described above with respect to fig. 1A and 2A and/or elsewhere herein.

In the example shown in fig. 1A, the pump user input/output interface 250 is coupled to the regulator 240, and the HCI 210 is a separate input/output interface coupled to the analysis device 150 or the monitoring module 150A, the system shown in fig. 1B may provide integrated HCIs 210, 250, 210S. Accordingly, input/output interface 210 of FIG. 1B may be configured to enable all of the inputs and/or outputs described above with interfaces 210 and 250.

Fig. 2A is an illustration of an example of a centrifugal pump 10. The pump 10 includes a housing 62, and the rotatable impeller 20 is disposed in the housing 62 so as to be rotatable about a rotational axis 60. The housing 62 defines a pump inlet 64 of the fluid material 30 and an outlet 66 of the fluid material 30. The housing also defines a volute 75. Scroll 75 may be a curved funnel that increases the cross-sectional area of scroll 75 as fluid material 30 flowing therein approaches outlet 66 (which may also be referred to as discharge port 66).

Volute 75 of centrifugal pump 10 is a portion of a housing that receives fluid 30 pumped by impeller 20. Impeller 20 has a number L of blades 310 for forcing fluid material 30 from pump inlet 64 into volute 75 as impeller 20 rotates. The impeller shown in fig. 1 has 6 blades 310. Vane 310 defines a plurality of impeller channels 320 for flowing fluid material 30 from pump inlet 64 into volute 75. In other words, the L blades 310 define L impeller channels 320, which in the example shown in fig. 2A, has the number l=6.

The housing 62 has an outlet portion 63 separating a first portion 77 of the volute 75 from a second portion 78 of the volute. The cross-sectional area of the first portion 77 is smaller and the cross-sectional area of the second portion 78 is larger. The outlet portion of the pump shown in fig. 2A has a volute tongue 65. The sensors 70, 70 ₇₈ of the example pump 10 of fig. 2A may be connected to the housing 62 at the second volute portion 78 by a larger cross-sectional area near the outlet 66 of the pump 10.

As the fluid progresses along the volute, more and more fluid 30 flows out of the rotating impeller passage 320, but as the cross-sectional area of the volute increases, the speed v75 remains the same if the pump operating speed approaches the pump design flow Q _OUT. In this manner, fluid 30 is forced out of pump outlet 66, thereby causing fluid material to flow out of outlet 66, Q _OUT. In this case, "design flow rate of the pump Q _OUT" may also be referred to as flow rate Q _OUTBEP, i.e., the flow rate of the pump at the point of Best Efficiency (BEP).

The design flow Q _OUT of the pump, i.e., the design flow, may also be referred to as a design point or design operating point. The design point is commonly referred to as the best efficiency point BEP for operation. Referring to fig. 2A, as fluid material 30 flows therein and approaches outlet 66, the cross-sectional area of volute 75 increases. The volute receives fluid from the impeller passage 320 such that the fluid velocity v ₇₅ in the volute remains constant during the design operating point operation. This is because more and more fluid is received from impeller passage 320 as it travels along volute 75, but as the cross-sectional area of the volute increases, speed v ₇₅ remains the same as the pump operates at the design operating point.

However, if the pump flow rate is low, the fluid velocity v ₇₅ will decrease along the volute and the fluid pressure will increase along the volute. Conversely, if the pump flow is higher than the design flow, the speed of the fluid on the volute will increase and the pressure will decrease. This is the result of the continuity equation and is also the result of the bernoulli principle. This is also the result of the first law of thermodynamics.

Fig. 2B is a graph of flow versus pressure at operating point 205 of the pump of fig. 2A. Referring to fig. 2B and 1, the operating point 205 of the pump 10 is represented by the intersection of the pump curve 207 and the system curve 209 of the particular system 52, 40, 50 to which the pump 66 is connected (see fig. 2B and 1).

Pump curve 207 indicates how pump pressure varies with flow. In fluid systems 52, 40, 50 where pressure and flow fluctuate over time, the system curve 209 may change over the life and operation of the system 52. Thus, the operating point 205 of the pump 10 may move along the pump curve 207. As the operating point 205 moves away from the point of Best Efficiency (BEP), fluid pressure pulsations typically increase.

Pressure pulsation is a fluctuation in fluid pressure. During operation, centrifugal pumps may cause such pressure pulsations. Some pressure pulsations are fluctuations in the fluid pressure generated by the pump at pump outlet 66. Thus, fluid 30 exiting pump outlet 66 may exhibit a fluid material flow rate Q _OUT with pressure pulsation P _FP. The repetition frequency f _R of the fluid pressure pulses P _FP depends on the rotational speed f _ROT of the impeller 20.

Referring to fig. 2A, a sensor 70 may be mounted on the housing 62 for generating vibration signals S _EA、S_MD, se (i), S (j), S (q) that depend on the fluid material pressure pulsation P _FP.

For example, the sensor 70 may be embodied by an accelerometer. Examples of accelerometers include microelectromechanical systems (abbreviated MEMS).

Thus, the sensor 70 may comprise a semiconductor silicon substrate configured as a MEMS accelerometer.

The sensor 70 may also be constituted by a piezoelectric accelerometer.

Alternatively, the sensor 70 may also be constituted by a piezoresistive sensor 70. The piezoresistive sensor 70 may be used as a strain gauge configured to measure stress. The piezoresistive sensor 70 may include a piezoresistive material that is configured to deform when a force is applied thereto, the deformation resulting in a change in sensor resistance.

Another example of a sensor 70 is a speed sensor. The speed sensor 70 includes a coil and magnet arrangement configured to measure speed.

The pump may also be provided with a position sensor 170 for generating position signals EP, PS, P (i), P (j), P (q) indicative of the rotational position of said impeller 20 relative to the housing 62. As shown in fig. 2A, a position-marking device 180 associated with the impeller 20 may be provided, with the position-marking device 180 passing the position sensor 170 once per revolution of the impeller 20 about the rotational axis 60, such that the position sensor 170 generates a rotational-marking signal value PS.

Although fig. 2A shows a single position marker 180 that may be provided in association with the impeller 20, the position marker 180 causes the position sensor 170 to generate one revolution mark signal value P _S per revolution, it should be noted that more than one position signal value P _S、P_C per revolution may be generated. For example, by providing more than one position marker 180 associated with the impeller 20, more than one position signal value Ps, pc may be generated per revolution. Alternatively, the position signal value P _S、P_C may be generated by an encoder 170 that is mechanically coupled to the rotary pump impeller 20. Thus, the position sensor 170 may be formed of an encoder 170, the encoder 170 being mechanically coupled to the rotary pump impeller 20 such that during rotation of the impeller 20, the encoder generates, for example, a signature signal P _S for each blade 310 in the rotary impeller 20. In this way, the encoder 170 may deliver L marking signals P _S per revolution of the impeller 20.

Alternatively, the position sensor 170 for generating the position signals EP, PS, P (i), P (j), P (q) may for example comprise a light source 170, such as a laser, in combination with a light detector 170 in combination with a position marking device 180 in the form of a reflective strip 180 on the rotating member.

Alternatively, the position sensor 170 for generating the position signals EP, PS, P (i), P (j), P (q) may comprise an inductive probe 170 configured to detect the presence of a metal or magnetic component 180 on the rotating shaft. The metal or magnetic component 180 may be constituted by a bolt or a wedge, for example. The advantage of the inductive probe 170 position detector is that it can operate effectively also in a dirty environment. Yet another example of a position sensor 170 and position-marking device 180 arrangement includes a hall effect sensor 170 that is used in conjunction with a magnet 180 mounted on a rotating component. The hall effect sensor 170 has the advantage of being insensitive to dust and dirt.

Regarding the physical location where the position sensor 170 and the position-marking device 180 are arranged, the following points may be considered:

When the rotating shaft is at risk of torsional movement, for example if the shaft is too weak compared to the torque, it is preferable to mount the position marking device 180 as close as possible to the impeller 20, in order to avoid that the torsional movement has an adverse effect on the measurement.

Although the above examples relate to pulp, the fluid pumped by the pump 10 may be any fluid material 30. The fluid material 30 may be water. The density of water is approximately 997 kg per cubic meter. Sometimes, the fluid to be pumped comprises fragments of solid material. For example, the fluid material 30 may include a mixture of water and a solid having a density greater than water, such as sand or crushed stone material, also known as mud.

Mud is a mixture of solids suspended in a liquid that have a density greater than water. The density of the solid material may be different from the density of water. In addition, sometimes the compressibility of the fluid material 30 is also different from water.

The fluid material 30 may also be oil.

Table 1 provides some examples of fluid materials and solid materials that may be suspended in fluid 30. Table 1 also provides some material properties, including density.

TABLE 1

Materials in fluids	Density (kg/cubic meter)	Toughness of	Compressive strength (MPa)
				Water and its preparation method	997
Oil (oil)	840-950
				Aluminum (Al)	2700	Plastic material	30-280
Granite	2700	Brittleness of the glass	Above 200
				Hematite (Fe ₂O₃)	5150	Brittleness of the glass	About 155 of about
Magnetic ore (Fe ₃O₄)	5180	Brittleness of the glass	About 100
				Zinc alloy	7130	Brittleness of the glass	75-160
Iron (Fe)	7870	Plastic material	110-220
				Silver (Ag)	10500	Plastic material	45-300
Gold alloy	19320	Toughness of	20-205

The outlet of the centrifugal pump 10 may include or be coupled to a filter 58 (see fig. 1 and 2A).

The pumping process is expected to achieve high efficiency. One aspect of the efficiency of the pumping process is the amount of pulsation of the flowable material 30 exiting the pump 10. Accordingly, it is desirable to maximize the flow rate Q _OUT of fluid material out of the pump while minimizing pulsations in the pumped fluid.

The efficiency of the pumping process in the centrifugal pump 10 depends on a number of variables affecting the internal state of the centrifugal pump 10. One variable that affects the efficiency of the pumping process of the centrifugal pump 10 is the operating point of the centrifugal pump 10. It is therefore desirable to control the operating point to achieve an optimal pumping process.

Therefore, in order to maximize the amount of output material 95 of the centrifugal pump 10, it is desirable to maintain an optimal state of the centrifugal pump process.

In this case, it is noted that the power consumption per pumping volume of the centrifugal pump increases when the centrifugal pump 10 operates away from the BEP.

Another variable that has an impact on the pumping process efficiency of the centrifugal pump 10 is the system pressure, also known as back pressure. The back pressure of the system may vary, for example, if there is a valve in the flow path of the tubing 40 (see FIG. 1). Alternatively, when the plumbing 40 includes a filter 58, the back pressure of the system may also vary and the filter 58 may be clogged to varying degrees. The clogging of the filter 58 may be due to particulate clogging in the filter, thereby progressively reducing the cross-sectional effective flow area through the filter 58. Thus, increased clogging may result in a decrease in the effective flow area, which in turn may result in an increase in the pressure drop across the filter 58.

In this regard, it is noted that because the composition of certain fluid materials 30 (such as pulp or paper pulp) may change over time, certain fluids 30 (such as pulp or paper pulp) may exhibit characteristics that are not constant over time. The change in the characteristics of the fluid material 30 may affect the pumping process efficiency of the centrifugal pump 10. Thus, the efficiency of the pumping process may vary over time.

Referring to fig. 1A and 1B, the system 5, 325 may include a control room 220 that allows a pump operator 230 to operate the centrifugal pump 10. The analysis device 150 may be configured to generate information indicative of an internal state of the centrifugal pump 10. The analysis device 150 further includes a human-machine interface (HCI) 210 for enabling user input and user output. The HCI 210 may include a display or screen 210S for providing a visual indication of the analysis results. The displayed analysis results may include information indicative of the internal state of the centrifugal pump process so that the operator 230 controls the centrifugal pump.

The centrifugal pump controller 240 may be configured to communicate the impeller speed set point value U1 _SP、F_ROTSP to control the rotational speed f _ROT of the impeller 20. According to certain embodiments, the setpoint value U1 _SP、f_ROTSP is set by the operator 230.

In the example shown in fig. 1A, the pump user input/output interface 250 is coupled with the regulator 240, and the HCI 210 is coupled with the analysis device 150 or the monitoring module 150A, which is configured to generate information indicative of the internal state of the centrifugal pump 10. Thus, when only coupled with the monitoring module 150A as shown in fig. 1A, the HCI 210 may advantageously be added in the control room 220 without modifying any of the pre-existing input/output interfaces 250 and regulators 240 that the pump operator 230 uses to operate the centrifugal pump 10.

One object to which the solutions and examples disclosed in this document are directed is to describe a method and a system for improved monitoring of the internal state X of a centrifugal pump 10 during operation. Another object to be solved by the solutions and examples disclosed in this document is to describe a method and a system for improved control of the internal state X of the centrifugal pump 10 during operation. Furthermore, it is an object of the solutions and examples disclosed in this document to describe a method and a system of an improved human-computer interaction interface (HCI) related to useful information for conveying the internal state X of a centrifugal pump during operation. Another object addressed herein is to describe a method and system of an improved graphical user interface relating to a pumping process in a centrifugal pump 10.

When pump 10 is coupled to fluid system 52, certain aspects of fluid system 52 may be affected by internal state X of the pump. For example, if the pump delivers a pulsating flow, such pulsation may cause some component of fluid system 52 to resonate. According to certain examples, certain aspects of fluid system 52 may be measured or estimated with parameters Y1, Y2, Y3..

Accordingly, one object to which some of the solutions and examples disclosed in this document address is to describe methods and systems for improved control of parameters Y1, Y2, Y3..

Another object to be solved by the solutions and examples disclosed in this document is to describe an improved method and system of a human-machine interaction interface (HCI) related to useful information for conveying parameters Y1, Y2, Y3...yn related to the fluid system 52 during operation of the centrifugal pump 10.

In this respect, the solutions and examples disclosed in this document also achieve the object of conveying useful information about the parameters Y1, Y2, Y3. about the fluid system 52 during operation of the centrifugal pump 10, while also conveying useful information about the corresponding internal state X during operation of the centrifugal pump 10.

Fig. 2C is a block diagram showing a centrifugal pump as block 10B, the centrifugal pump receiving a plurality of inputs U1. The internal state X of the pump may be described or represented by a plurality of internal state parameters X1, X2, X3.

Likewise, one or more aspects Y of the system 52 coupled to the pump 10 may also be monitored. Thus, the system 52 coupled to receive fluid from the pump 10 may display an output system state Y, which may be described by a plurality of output parameters Y1, Y2, Y3, and..once. Referring to fig. 1C, it should be noted that for ease of analysis, the centrifugal pump 10 may be considered as a block 10B having a plurality of input variables, referred to as input parameters U1, U2, U3, respectively.

Using linear algebraic terms, the input variables U1, U2, U3.. Internal state parameters X1, X2, X3.. Xm may be collectively referred to as an internal state vector X; output parameters Y1, Y2, Y3..

The internal state X of the pump 10 may be referred to as X (r) at a point in time referred to as r. The internal state X (r) may be described or indicated by a plurality of parameter values defining different aspects of the internal state X (r) of the pump 10 at time r.

The internal state X (r) of the black frame centrifugal pump 10B depends on the input vector U (r), and the output vector Y (r) depends on the internal state vector X (r).

Thus, during operation of pump 10, internal state X (r) may be considered as a function of input U (r):

x (r) =f ₁ (U (r)), wherein,

X (r) represents the internal state X of the pump 10 at a time called r; and

U (r) represents the input vector of the pump 10 at a time called r.

Likewise, the output Y of the black box 10B can also be considered as a function of the internal state X:

Y(r)＝f₂(X(r))

Fig. 2D is a diagram of an example of the centrifugal pump 10. The pump 10 of fig. 2D may include and be configured with the components described above with respect to fig. 1A and 2A and/or elsewhere herein. However, the example of the centrifugal pump 10 in fig. 2D may include sensors 70, 70 ₇₇ connected to the housing 62 at the first volute section 77 by a narrower cross-sectional area near the volute tongue 65.

Thus, the sensor 70 ₇₈ of the example pump of FIG. 2A is connected to the housing 62 at the second volute portion 78 by a larger cross-sectional area near the pump outlet, while the sensor 70 ₇₇ of the example pump of FIG. 2D is also connected to the housing 62 at the first volute portion 77 by a narrower cross-sectional area near the volute tongue 65. Alternatively, sensor 70 ₇₇ connected to housing 62 at first volute portion 77 replaces sensor 70 ₇₇. One or more sensors 70 may be positioned to detect vibrations generated by fluid pressure pulsations P _FP that depend on the rotational speed f _ROT of impeller 20.

Fig. 2E is a diagram of another example of the centrifugal pump 10. The pump of fig. 2E has a housing that includes a plurality of stationary vanes 312 positioned between the volute 75 and the impeller 20.

Fig. 3 is a schematic block diagram of an example of the analysis device 150 shown in fig. 1. The analysis device 150 has an input 140 for receiving the analog vibration signal S _EA from the vibration sensor 70. The input 140 is connected to an analog-to-digital (a/D) converter 330. The a/D converter 330 samples the received analog vibration signal S _EA at a specific sampling frequency f _S in order to transmit a digital measurement data signal S _MD having said specific sampling frequency f _S, and wherein the amplitude of each sample depends on the amplitude of the analog signal received at the sampling instant. The digital measurement data signal S _MD is transmitted on a digital output 340 coupled to the data processing device 350.

Referring to fig. 3, a data processing device 350 is coupled to a computer readable medium 360 for storing program code. The computer-readable medium 360 may also be referred to as memory 360. Program memory 360 is preferably a non-volatile memory. The memory 360 may be a read/write memory, i.e. capable of reading data from the memory and capable of writing new data to the memory 360. According to one example, program memory 360 is implemented by flash memory. The program memory 360 may comprise a first memory segment 370 for storing a first set of program code 380 that is executable to control the analysis device 150 to perform basic operations. Program memory 360 may also include a second memory segment 390 for storing a second set of program code 394. The second set of program code in the second memory segment 390 may include program code for causing the analysis device 150 to process the detection signal. The signal processing may include processing for generating information indicative of the internal state of the centrifugal pump, as discussed elsewhere in this document. Furthermore, the signal processing may include control of the internal state of the centrifugal pump, as discussed elsewhere in this document. Thus, the signal processing may include generating data indicative of the internal state of the centrifugal pump, as disclosed in connection with embodiments of the state parameter extractor 450 of fig. 5, 15 and/or 24, for example.

The memory 360 may also include a third memory segment 400 for storing a third set of program code 410. The set of program code 410 in the third memory segment 400 may comprise program code for causing the analysis device to perform the selected analysis function. The analysis function, when executed, may cause the analysis device to present the corresponding analysis results on the user interface 210, 210S or to communicate the analysis results on the port 420.

The data processing device 350 is also coupled to a read/write memory 430 for data storage. Accordingly, the analysis device 150 includes a data processor 350 and program code for causing the data processor 350 to perform certain functions, including digital signal processing functions. When it is stated in this document that the apparatus 150 performs a certain function or a certain method, the statement may mean that a computer program is running in the data processing device 350 to cause the apparatus 150 to perform a method or a function of the kind described in this document.

Processor 350 may be a digital signal processor. The digital signal processor 350 may also be referred to as a DSP. Alternatively, the processor 350 may be a field programmable gate array circuit (FPGA). Thus, the computer program may be executed by a field programmable gate array circuit (FPGA). Alternatively, the processor 350 may comprise a combination of a processor and an FPGA. Thus, the processor may be configured to control the operation of the FPGA.

Fig. 4 is a simplified illustration of program memory 360 and its contents. The simplified illustration is intended to convey an understanding of the general idea of storing different program functions in the memory 360 and is not necessarily the correct technical teaching of the way in which programs will be stored in real memory circuits. The first memory segment 370 stores program code for controlling the analysis means 150 to perform basic operations. Although the simplified illustration of fig. 4 shows pseudo code, it should be understood that the program code may be comprised of machine code or any level of program code that may be executed or interpreted by data processing apparatus 350 (fig. 3).

The second memory segment 390 shown in FIG. 4 stores a second set of program code 394. When run on the data processing device 350, the program code 394 in section 390 will cause the analysis means 150 to perform functions, such as digital signal processing functions. The function may include advanced digital processing of the digital measurement data signal S _MD.

A computer program for controlling the functions of the analysis device 150 may be downloaded from the server computer 830 (see fig. 27 and or 29). This means that the program to be downloaded is transmitted through the communication network 810 (see fig. 27 and or fig. 29). This may be achieved by modulating a carrier wave carrying the program over the communication network 810. Thus, the downloaded program may be loaded into a digital memory, such as memory 360 (see fig. 3 and 4). Accordingly, program 380 and/or signal processing program 394 and/or analysis function program 410 may be received via a communication port, such as port 420 (fig. 1 and 3) or port 920 (see fig. 27) or port 800B (see fig. 27) or port (see fig. 27), for loading into program memory 360.

Accordingly, this document also relates to a computer program product, such as program code 380 and/or program code 394 and/or program code 410, that may be loaded into a digital memory of a device, such as memory 360 (see fig. 3 and 4). The computer program product comprises software code portions for performing the signal processing method and/or the analysis function when said product is run on the data processing unit 350 of the device 150. The term "running on a data processing unit" means that the computer program plus the data processing device 350 performs the method described in this document.

The phrase "computer program product loadable into a digital memory of an analysis device" means that a computer program can be introduced into the digital memory of the analysis device 150 in order to implement an analysis device 150 programmed to be able or adapted to perform a method of the kind described herein. The term "loaded into a digital memory of a device" means that the device programmed in this way is capable or adapted to perform the functions described herein and/or the methods described in this document. The computer program product described above may also be a program 380, 394, 410 loadable onto a computer readable medium, such as an optical disk or DVD. Such computer readable media may be used to communicate the programs 380, 394, 410 to a client. As described above, the computer program product may alternatively comprise a carrier wave modulated to carry the computer programs 380, 394, 410 over a communication network. Thus, the computer programs 380, 394, 410 may be transmitted from the provider server to the client with the analysis device 150 via an internet download.

Fig. 5 is a block diagram showing an example of the analysis device 150. In the example of fig. 5, some of the functional blocks represent hardware, and some of the functional blocks may represent hardware, or may represent functions implemented by running program code on data processing device 350, as discussed in connection with fig. 3 and 4.

The apparatus 150 in fig. 5 illustrates an example of the analysis apparatus 150 shown in fig. 1 and/or 3. To simplify understanding, fig. 5 also shows some peripheral devices coupled to device 150. The vibration sensor 70 is coupled to the input 140 of the analysis device 150 to transmit an analog measurement signal S _EA (also referred to as a vibration signal S _EA) to the analysis device 150.

Further, a position sensor 170 is coupled to the second input 160. Thus, the position sensor 170 transmits a position signal E _p, which depends on the rotational position of the impeller 20, to the second input 160 of the analysis device 150.

The input 140 is connected to an analog-to-digital (a/D) converter 330. The a/D converter 330 samples the received analog vibration signal SEA at a specific sampling frequency f _S in order to transmit a digital measurement data signal S _MD having said specific sampling frequency f _S, and wherein the amplitude of each sample depends on the amplitude of the analog signal received at the sampling instant. The digital measurement data signal S _MD is transmitted on a digital output 340, which is coupled to a data processing unit 440. The data processing unit 440 includes functional blocks showing the functions performed. In terms of hardware, the data processing unit 440 may include a data processing unit 350, a program memory 360, and a read/write memory 430, as described above in connection with fig. 3 and 4. Accordingly, the analysis device 150 of fig. 5 may comprise a data processing unit 440 and program code for causing the analysis device 150 to perform certain functions.

The digital measurement data signal S _MD is processed in parallel with the position signal E _P. Accordingly, the a/D converter 330 may be configured to sample the position signal E _P while sampling the analog vibration signal S _EA. The sampling of the position signal E _P may be performed using the same sampling frequency f _S in order to generate the digital position signal E _PD, wherein the amplitude of each sample P (i) depends on the amplitude of the received analog position signal E _P at the sampling instant. As described above, the analog position signal E _P may have a signature signal value P _S, for example in the form of an electrical pulse, which has an amplitude edge that can be accurately detected and indicates the particular rotational position of the impeller 20 being monitored. Thus, although the analog position-marker signal P _S has an amplitude edge that can be accurately detected, the digital position signal E _PD will switch from a first value (e.g., "0" (zero)) to a second value (e.g., "1" (one)) at a different time.

Thus, the a/D converter 330 may be configured to transmit a series of measurement pairs S (i) associated with corresponding position signal values P (i). The letter "i" in S (i) and P (i) indicates a point in time, i.e., a sample number. Thus, the time of occurrence of the rotational reference position of the rotating impeller 20 may be detected by analyzing the time series of position signal values P (i) and identifying samples P (i) that indicate that the digital position signal E _PD has switched from a first value (e.g., "0" (zero) to a second value (e.g., "1" (one)).

Fig. 6A is a diagram of the signal pair S (i) and P (i) transmitted by the a/D converter 330.

Fig. 6B is a diagram of the sequence of signal pairs S (i) and P (i) transmitted by the a/D converter 330. The first signal pair comprises a first vibration signal amplitude value S (n) associated with a sampling instant "n", which is transmitted simultaneously with the first position signal value P (n), associated with a sampling instant "n". Followed by a second signal pair comprising a second vibration signal amplitude value S (n+1) associated with the sampling instant "n+1", which is transmitted simultaneously with a second position signal value P (n+1) associated with the sampling instant "n+1", and so on.

Referring to fig. 5, the signal pairs S (i) and P (i) are transferred to the state parameter extractor 450. The example state parameter extractor 450 of fig. 5 is configured to generate an amplitude peak S _P (r) based on a time series of measured sample values S (i).

The state parameter extractor 450 is further configured to generate a time relation value R _T (j), also referred to as R _T (R), based on the length of time (T _D) between the occurrence time of the amplitude peak S _P (R) and the occurrence time of the rotational reference position of the rotating impeller. As described above, the time of occurrence of the rotational reference position of the rotating impeller may be detected by analyzing the time series of position signal values P (i) and identifying a signal indicating that the digital position signal E _PD has switched from a first value (e.g., "0" (zero)) to a second value (e.g., "1" (one)).

Fig. 7 is a block diagram illustrating an example of a portion of a state parameter extractor 450. According to one example, state parameter extractor 450 includes memory 460. The state parameter extractor 450 is adapted to receive the sequence of measured values S (i) and the signal sequence of positions P (i) and the time relation between them, and the state parameter extractor 450 is adapted to provide the time-coupled value sequences S (i), f _ROT (i) and P (i). Thus, a single measurement value S (i) is associated with a corresponding speed value f _ROT (i), the speed value f _ROT (i) being indicative of the rotational speed of the impeller 20 at the time of detection of the associated single measurement value S (i). This will be described in detail below with reference to fig. 8-13.

Fig. 8 is a simplified illustration of an example of the memory 460 and its contents, and the memory 460 illustrates columns #01, #02, #03, #04, and #05 on the left-hand side, providing illustrative images intended to show the temporal relationship between the detection time of the encoder pulse signal P (i) (see column # 02) and the corresponding vibration measurement value S (i) (see column # 03).

As described above, the analog-to-digital converter 330 samples the analog electrical measurement signal S _EA at the initial sampling frequency f _S to generate the digital measurement data signal S _MD. The encoder signal P may also be detected at approximately the same initial temporal resolution f _S, as shown in column #02 of fig. 8.

Column #01 shows the time course as a series of time slots, each time slot having a duration dt=l/f _Sample; where f _Sample is a sampling frequency having an integer relationship with the initial sampling frequency f _S at which the analog electrical measurement signal S _EA is sampled. According to a preferred example, the sampling frequency f _Sample is the initial sampling frequency f _S. According to another example, the sampling frequency f _Sample is a first reduced sampling frequency f _SR1, which is reduced by an integer multiple M compared to the initial sampling frequency f _S.

In column #02 of fig. 8, each positive edge of the encoder signal P is represented by a "1". In this example, the positive edge of the encoder signal P is detected in slots 3, 45, 78 and 98, as shown in column # 02. According to another example, a negative edge of the position signal is detected, which provides an equivalent result as detecting a positive edge. According to yet another example, both positive and negative edges of the position signal are detected in order to obtain redundancy by allowing later selection of whether to use the positive or negative edge.

Column #03 shows a sequence of vibration sample values S (i). Column #05 shows the corresponding sequence of the vibration sample values S (j) when integer decimation is performed. Therefore, when the integer decimation is performed by this stage, it may be set to provide an integer decimation factor m=10, for example, and as shown in fig. 8, one vibration sample value S (j) will be provided for every ten samples S (i) (see column #03 in fig. 8) (see column #05 in fig. 8). According to one example, by setting the position time (PositionTime) signal in column #04 to the value pt=3, very accurate position and time information PT related to the extracted vibration sample value S (j) is maintained to indicate that a positive edge is detected in slot #03 (see column # 02). Thus, the value of the position time signal after the integer decimation indicates the detection time of the position signal edge P relative to the sample value S (l).

In the example of fig. 8, the magnitude value of the position time signal at sample i=3 is pt=3, and the sample S (l) is transmitted in the slot 10 due to the decimation factor m=10, which means that an edge is detected in M-pt=10-3=7 slots before the slot of the sample S (l).

Thus, the apparatus 150 is operable to process information about the positive edge of the encoder signal P (i) in parallel with the vibration sample S (i) in order to maintain the temporal relationship between the positive edge of the encoder signal P (i) and the corresponding vibration sample value S (i) and/or the integer extracted vibration sample value S (j) by the above-described signal processing from detecting the analog signal to establishing the speed value f _ROT.

Fig. 9 is a flowchart illustrating an example of a method of operating the state parameter extractor 450 of fig. 7.

According to one example, the state parameter extractor 450 analyzes (step s#10) the time relationship between three consecutively received position signals in order to determine whether the monitored rotating impeller 20 is in a constant speed phase or in an acceleration phase. As described above, the analysis may be performed based on information in memory 460 (see fig. 8).

If the analysis shows that there are the same number of time slots between the position signals, the state parameter extractor 450 concludes (at step # 20) that the speed is constant, in which case step S #30 is performed.

In step s#30, the state parameter extractor 450 may calculate a duration between two consecutive position signals by multiplying the duration of the time slot dt=1/fs by the number of time slots between the two consecutive position signals. The rotational speed may be calculated as when the monitored impeller 20 provides a position signal once per full revolution

V＝1/(n_diff*dt)，

Where n _diff = the number of time slots between two consecutive position signals. During the constant speed phase, all sample values S (j) associated with the three analyzed position signals (see column #05 in fig. 8) may be assigned the same speed value f _ROT＝V＝1/(n_diff x dt, as described above. Thereafter, step s#10 may be performed again for the next three consecutively received position signals. Alternatively, when step s#10 is repeated, the previous third position signal P3 will be used as the first position signal P1 (i.e., P1: =p3) to determine whether the speed is about to change.

If the analysis (step S#10) shows that the number of time slots between the first and second position signals is different from the number of time slots between the second and third position signals, the state parameter extractor 450 concludes (at step S#20) that the monitored rotating impeller 20 is in an acceleration phase. The acceleration may be positive, i.e. an increase in rotational speed, or the acceleration may be negative, i.e. a decrease in rotational speed, also referred to as deceleration.

In a next step s#40, the state parameter extractor 450 operates to establish an instantaneous speed value during the acceleration phase and to associate each measured data value S (j) with an instantaneous speed value Vp indicative of the rotational speed of the impeller monitored upon detection of a sensor signal (S _EA) value corresponding to the data value S (j).

According to one example, the state parameter extractor 450 operates to establish the instantaneous speed value by linear interpolation. According to another example, the state parameter extractor 450 operates to establish the instantaneous speed value by nonlinear interpolation.

Fig. 10 is a flowchart showing an example of a method for performing step s#40 of fig. 9. According to one example, it is assumed that the acceleration has a constant value for the duration between two mutually adjacent position indicators P (see column #02 in fig. 8). Thus, when

Transmitting the position indicator P once per revolution, and

The gear ratio is 1/1, then

The angular distance travelled by the rotating impeller 20 between two mutually adjacent position indicators P is one (1) turn, also denoted 360 degrees, and

The duration is t=n _diff x dt,

■ Where n _diff is the number of time slots of duration dt between two mutually adjacent position indicators P.

Referring to fig. 8, a first position indicator P is detected in a slot il+# 03, and a next position indicator P is detected in a slot i 2+# 45. Thus, the duration is n _diff1 = i2-i1 = 45-3 = 42 slots.

Thus, in step s#60 (see fig. 10 in conjunction with fig. 8), the state parameter extractor 450 operates to establish a first number of time slots n _diff1 between the first two consecutive position signals P1 and P2, i.e. between the position signal P (i=3) and the position signal P (i=45).

In step s#70, the state parameter extractor 450 operates to calculate a first rotation speed value VT1. The first rotation speed value VTL may be calculated as

VT1＝1/(n_diff1*dt)，

Wherein VT1 is the speed in revolutions per second,

N _diff1 = number of time slots between two consecutive position signals; and

Dt is the duration of one time slot expressed in seconds.

Since it is assumed that the acceleration has a constant value for the duration between two position indicators P adjacent to each other, the calculated first velocity value VT1 is assigned to the middle time slot between two consecutive position signals (step s#80).

Thus, in this example, where the first position indicator P1 is detected in time slot i _P1 = #03 and the next position indicator P2 is detected in time slot i _P2 = # 45; the first intermediate time slot is:

Time slot i _P1-2＝i_P1+(i_P2-i_P1)/2=3+ (45-3)/2=3+21) =24.

Therefore, in step s#80, the first rotation speed value VT1 can be assigned to a slot (for example, slot i=24) indicating a point of time earlier than a point of time when the second position signal edge P (i=45) is detected, see fig. 8.

The retrospective assignment of velocity values to time slots representing points in time between two successive position signals advantageously results in a substantial improvement, since the inaccuracy of the velocity values is significantly reduced, as explained in fig. 13. While the prior art method of obtaining an instantaneous rotational speed value of the centrifugal pump impeller 20 may be satisfactory for establishing a constant speed value at several mutually different rotational speeds, the prior art solution seems unsatisfactory when used for establishing a speed value of the rotating centrifugal pump impeller 20 during the acceleration phase. In this regard, it should be noted that impeller speed may be affected by changes in fluid pressure in the fluid system.

In contrast, the method according to the example disclosed in this document enables the establishment of a speed value with advantageously small inaccuracy even during the acceleration phase.

In a subsequent step s#90, the state parameter extractor 450 operates to establish a second number of time slots n _diff2 between the next two consecutive position signals. In the example of fig. 8, this is the number of slots n _diff2 between slot 45 and slot 78, i.e., n _diff2 =78-45=33.

In step s#100, the state parameter extractor 450 calculates a second rotation speed value VT2. The second rotation speed value VT2 may be calculated as:

VT2＝Vp61＝1/(n_diff2*dt)，

Where n _diff2 = the number of time slots between the next two consecutive position signals P2 and P3. Thus, in the example of fig. 8, n _diff2 = 33, the number of slots between instant 45 and slot 78.

Since it can be assumed that the acceleration has a constant value for the duration between two position indicators P adjacent to each other, the calculated second velocity value VT2 is assigned (step s#110) to the middle time slot between two consecutive position signals.

Thus, in the example of fig. 8, the calculated second speed value VT2 is assigned to the time slot 61, because 45+ (78-45)/2= 61,5. Thus, the speed at time slot 61 is set to:

V(61):＝VT2。

thus, in this example, where one position indicator P is detected in time slot i2= #45 and the next position indicator P is detected in time slot i3= # 78; the second intermediate slot is an integer part of:

i_P2-3＝i_P2+(i_P3-i_P2)/2＝45+(78-45)/2＝45+33/2＝61,5

Thus, slot 61 is the second intermediate slot i _P2-3.

Thus, in step s#110, the second speed value VT2 can advantageously be assigned to a time slot (e.g., time slot i=61) representing a point in time earlier than the point in time of detecting the third position signal edge P (i=78), see fig. 8. This feature enables a slightly delayed real-time monitoring of the rotational speed while achieving a higher accuracy of the detection speed.

In the next step s#120, a first acceleration value of the relevant time period is calculated. The first acceleration value may be calculated as:

a12＝(VT2-VT1)/((i_VT2-i_VT1)*dt)

In the example of fig. 8, the second speed value VT2 is assigned to slot 61, so i _VT2 =61, and the first speed value VT1 is assigned to slot 24, so i _VT1 =24.

Therefore, since dt=1/fs, the acceleration value may be set to:

a12＝fs*(VT2-VT1)/(i_VT2-i_VT1)

for the time period between time slot 24 and time slot 60, in the example of fig. 8.

In a next step s#130, the state parameter extractor 450 operates to associate the established first acceleration value a11 with a time slot in which the established acceleration value a12 is valid. This may be all time slots between the time slots of the first speed value VT1 and the time slots of the second speed value VT 2. Thus, the established first acceleration value a12 may be associated with each time slot of the duration between the time slot of the first velocity value VT1 and the time slot of the second velocity value VT 2. In the example of fig. 8, are time slots 25 through 60. This is shown in column #07 of fig. 8.

In a next step s#140, the state parameter extractor 450 operates to establish a velocity value of the measured value S (j) associated with the duration for which the established acceleration value is valid. Thus, a speed value is established for each time slot

Associated with the measured value s (j), and

Associated with the established first acceleration value a 12.

During linear acceleration, i.e. when the acceleration a is constant, the velocity at any given point in time is given by the following equation:

V (i) =v (i-1) +a×dt, (equation 3)

Wherein,

V (i) is the instantaneous speed at the point in time of slot i,

V (i-1) is the instantaneous speed at the time point of the slot immediately preceding the slot i,

A is the acceleration rate of the vehicle,

Dt is the duration of the time slot.

According to one example, the speed of each of the slots 25 through 60 may be continuously calculated in this manner, as shown in column #08 in fig. 8. Thus, the instantaneous velocity values Vp associated with the detected measured values Se (25), se (26), se (27)..se (59) and Se (60) can be established in this way, the detected measured values being associated with the acceleration value a12 (see column #08 in fig. 8 together with column #03 and time slots 25 to 60 in column # 07).

Thus, the instantaneous speed values S (j) [ see column #05] associated with the detected measurement values S (3), S (4), S (5), and S (6) associated with the acceleration value a12 can be established in this way.

According to another example, the instantaneous speed of the time slot 30 associated with the first measurement S (j) =s (3) can be calculated as:

V(i＝30)＝Vp30＝VT1+a*(30-24)*dt＝Vp24+a*6*dt

the instantaneous speed of the time slot 40 associated with the first measurement S (j) =s (4) can be calculated as:

V(i＝40)＝Vp40＝VT1+a*(40-24)*dt＝Vp40+a*16*dt

or calculated as:

V(i＝40)＝Vp40＝V(30)+(40-30)*dt＝Vp30+a*10*dt

The instantaneous speed of the time slot 50 associated with the first measurement S (j) =s (5) can then be calculated as:

V(i＝50)＝Vp50＝V(40)+(50-40)*dt＝Vp40+a*10*dt

And the instantaneous speed of the time slot 60 associated with the first measurement S (j) =s (6) can then be calculated as:

V(i＝60)＝Vp50+a*10*dt

As described above, when the measured sample value S (i) [ see column #03 in fig. 8 ] associated with the established acceleration value has been associated with an instantaneous velocity value, a data array comprising a time series of measured sample values S (i), each value being associated with a velocity value V (i), f _ROT (i), may be transmitted at the output of the state parameter extractor 450.

Alternatively, if a decimated sample rate is desired, this may be done as follows: as described above, when the measured sample value S (j) associated with the established acceleration value [ see column #05 in fig. 8 ] has been associated with an instantaneous velocity value, a data array comprising a time series of measured sample values S (j), each value being associated with a velocity value V (j), f _ROT (j), may be transmitted on the output of the state parameter extractor 450.

Referring to fig. 11, another example of a method is described. According to this example, the state parameter extractor 450 operates to record (see step s#160 in fig. 11) a time sequence of position signal values P (i) of the position signal (E _P) such that a first time relation n _diff1 exists between at least some of the recorded position signal values (P (i)), e.g., between the first position signal value P1 (i) and the second position signal value P2 (i). According to one example, the second position signal value P2 (i) is received and recorded in a time slot (i) that arrives n _diffl time slots after the reception of the first position signal value P1 (i) (see step s#160 in fig. 11). Then, the third position signal value P3 (i) is received and recorded (see step s#170 in fig. 11) in the slot (i) which arrives ndiff2 slots after the second position signal value P2 (i) is received.

As shown in step S #180 of fig. 11, the state parameter extractor 450 may operate to calculate a relationship value

a12＝ndiff1/ndiff2

If the relationship value a12 is equal to one (unity) or approximately equal to one, then the state parameter extractor 450 operates to determine that the velocity is constant and may continue to calculate the velocity according to the constant velocity phase method.

If the relationship value a12 is greater than one, the relationship value indicates a percentage speed increase.

If the relationship value a12 is less than one, the relationship value indicates a percentage speed decrease.

The relation value a12 may be used to calculate the velocity V2 at the end of the time series based on the velocity VI at the beginning of the time series, e.g. as

V2＝a12*V1

Fig. 12 is a flowchart showing an example of a method for performing step s#40 of fig. 9. According to one example, it is assumed that the acceleration has a constant value for the duration between two position indicators P adjacent to each other (see column #02 in fig. 8). Thus, when

Transmitting the position indicator P once per revolution, and

The gear ratio is 1/1, then

The angular distance of movement between two position indicators P adjacent to each other is 1 turn, also denoted 360 degrees, and

The duration is t=n x dt,

■ Where n is the number of time slots of duration dt between the first two adjacent position indicators P1 and P2.

In step s#200, a first rotation speed value VT1 may be calculated as:

VT1＝1/(n_diff1*dt)，

Wherein VT1 is the speed in revolutions per second,

Ndiff1 = the number of time slots between two consecutive position signals; and

Dt is the duration of the time slot expressed in seconds. The value of dt may be, for example, the inverse of the initial sampling frequency f _S.

Since the acceleration is assumed to have a constant value for the duration between two position indicators P adjacent to each other, the calculated first velocity value VT1 is assigned to the first intermediate time slot in the middle between two consecutive position signals P (i) and P (i+ndiff 1).

In step s#210, the second velocity value VT2 may be calculated as:

VT2＝1/(ndiff2*dt)，

Wherein VT2 is the speed in revolutions per second,

Ndiff2 = the number of time slots between two consecutive position signals; and

Since it is assumed that the acceleration has a constant value for the duration between two position indicators P adjacent to each other, the calculated second velocity value VT2 is assigned to the second intermediate time slot in the middle between two consecutive position signals P (i+ndiff 1) and P (i+ndiff 1+ndiff 2).

Thereafter, the speed difference V _Delta can be calculated as:

V_Delta＝VT2-VT1

the speed difference V _Delta value may be divided by the number of slots between the second intermediate slot and the first intermediate slot. The resulting value indicates the speed difference dV between adjacent time slots. Of course, as described above, this assumes that the acceleration is constant.

An instantaneous speed value associated with the selected time slot may then be calculated from the first speed value VT1 and a value indicative of a speed difference between adjacent time slots.

As described above, when the measured sample value S (i) associated with the time slot between the first intermediate time slot and the second intermediate time slot has been associated with an instantaneous speed value, a data array comprising a time series of measured sample values S (i), each value being associated with a speed value V (i), is transmitted at the output of the state parameter extractor 450. The instantaneous velocity value V (i) may also be referred to as f _ROT (i).

In summary, according to some examples, the first instantaneous speed value VT1 may be established according to the following factors:

The angular distance δ -FI _p1-p2 between the first position signal P1 and the second position signal P2, and is dependent on:

Corresponding duration delta-T _p1-p2＝t_P2-t_P1.

Thereafter, a second instantaneous speed value VT2 may be established according to the following factors:

The angular distance δ -FI _P2-P3 between the second position signal P2 and the third position signal P3, and is dependent on:

corresponding duration delta-T _p2-p3＝t_P2-t_P1.

Thereafter, an instantaneous speed value of the rotating impeller 20 may be established by interpolation between the first instantaneous speed value VT1 and the second instantaneous speed value VT 2.

In other words, according to an example, two instantaneous speed values VT1 and VT2 may be established based on the angular distance δ -FI _p1-p2、δ-FI_P2-P3 and the corresponding duration between three consecutive position signals, and thereafter, the instantaneous speed value of the rotating impeller 20 may be established by interpolation between the first instantaneous speed value VT1 and the second instantaneous speed value VT 2.

Fig. 13 is a diagram showing a series of temporally successive position signals P1, P2, P3, each indicating a complete revolution of the impeller 20 being monitored. Thus, the time value in seconds increases rightward along the horizontal axis.

The vertical axis indicates rotational speed, graded in Revolutions Per Minute (RPM).

Referring to fig. 13, the effect of a method according to one example is shown. The first instantaneous speed value V (t ₁) =vt1 may be established according to:

Corresponding duration delta-T _1-2＝t_P2-t_P1. The velocity value obtained by dividing the angular distance δ -FI _p1-p2 by the corresponding duration (t _P2-t_P1) represents the velocity V (t ₁), also called mtp (intermediate time point), of the rotating impeller 20 at the first intermediate time point t ₁, as shown in fig. 13.

Thereafter, a second instantaneous speed value V (t ₂) =vt2 may be established according to:

the angular distance δ -FI between the second position signal P2 and the third position signal P3, and is dependent on:

The corresponding duration δ -T2-3=t _P3-t_P2.

As shown in fig. 13, a speed value obtained by dividing the angular distance δ -FI by the corresponding duration (t _P3-t_P2) represents the speed V (t ₂) of the rotating impeller 20 at the second intermediate time point t ₂ (second mtp).

Thereafter, an instantaneous speed value of the time value between the first intermediate point in time and the second intermediate point in time may be established by interpolation between the first instantaneous speed value VT1 and the second instantaneous speed value VT2, as shown by the curve f _ROTint.

Mathematically, this can be expressed by the following equation:

v (t 12) =v (t 1) +a (t 12-t 1) (equation 4)

Therefore, if the speed of the impeller 20 can be detected at two time points (t 1 and t 2) and the acceleration a is constant, the instantaneous speed at an arbitrary time point can be calculated. In particular, the housing speed V (t 12) at time t12 (a point in time before t ₂ after t ₁) can be calculated by:

V (t 12) =v (t ₁)+a*(t12–t₁) (equation 4)

Wherein,

A is acceleration, and

T ₁ is the first intermediate time point t ₁ (see fig. 13).

The establishment of the speed values as described above and the compensation extraction described with reference to fig. 20, 21 and 22 can be achieved by performing the corresponding method steps and this can be achieved by a computer program 94 stored in the memory 60 as described above. The computer program may be executed by the DSP 50. Alternatively, the computer program may be executed by a field programmable gate array circuit (FPGA).

The establishment of the velocity values f _ROT (i) as described above may be performed by the analysis device 150 when the processor 350 executes the respective program code 380, 394, 410, as discussed above in connection with fig. 4. The data processor 350 may include a central processing unit 350 for controlling the operation of the analysis device 14. Alternatively, the processor 50 may include a Digital Signal Processor (DSP) 350. According to another example, processor 350 includes a field programmable gate array circuit (FPGA). The operation of a field programmable gate array circuit (FPGA) may be controlled by a central processing unit 350, which may include a Digital Signal Processor (DSP) 350.

Identification of data relating to the operating point of a centrifugal pump

During operation of the centrifugal pump 10, pressure fluctuations P _FP may occur in the pumped fluid material 30. Pressure fluctuations in the fluid material 30 may cause mechanical vibrations V _FP (see fig. 2A, 2D, and/or 14A-14G) in the pump housing 62.

As described above, the centrifugal pump impeller 20 has a plurality of blades 310. The number L of blades 310 is an important factor related to analysis of vibration caused by rotation of the pump impeller 20. According to some embodiments, the number L of blades 310 may be any number greater than l=1. According to some embodiments, the number L of blades 310 may be any value in the range of l=2 to l=60. According to some embodiments, the number L of blades 310 may be any value in the range of l=2 to l=35.

The presence of the vibration signal signature S _FP, which is dependent on the vibration movement V _FP of the housing, can thus provide information about the instantaneous internal state of the pumping process in the pump. The repetition frequency f _R of the fluid pressure fluctuations depends on the number L of blades 310 and the rotational speed f _ROT of the impeller 20.

The inventors have appreciated that some of the mechanical vibration of the housing 62 is caused by pressure fluctuations in the fluid material 30. The repetition frequency f _R of the pressure fluctuations depends on the number L of blades 310 and the rotational speed f _ROT of the impeller 20.

Such repetition frequency f _R may be discussed in terms of repetitions per time unit or in terms of repetitions per revolution of the monitored housing, without distinguishing between the two, when the monitored centrifugal pump impeller 20 is rotating at a constant rotational speed. However, if the centrifugal pump impeller 20 rotates at a variable rotational speed, the matter may be more complex, as discussed elsewhere in this disclosure, for example, in connection with fig. 20, 21, 22A, 22B, and 22C. In fact, even very small changes in the rotational speed of the pump housing appear to have a significant adverse effect on the detected signal quality in terms of blurring of the detected vibration signal. Therefore, a very accurate detection of the rotational speed f _ROT of the pump impeller 20 is crucial.

Furthermore, the inventors have realized that not only the amplitude of the mechanical vibration V _FP, but also the time of occurrence of the mechanical vibration V _FP, may be indicative of data related to the operating point 205 in the centrifugal pump. Thus, the measurement signal S _MD (see, e.g., fig. 5) may include at least one vibration signal amplitude component S _FP that is dependent on the vibration motion;

Wherein the vibration signal amplitude component S _FP has a repetition frequency f _R, which is:

the rotational speed f _ROT of the centrifugal pump impeller 20, which is dependent on the rotational movement, and also

Depending on the number L of blades 310 provided on the impeller 20; and

Wherein there is a temporal relationship between:

Occurrence of the amplitude component S _FP of the repetitive vibration signal, and

The occurrence of the position signal P (i) with the second repetition frequency f _P, which frequency depends on the rotational speed f _ROT of the centrifugal pump impeller 20 of the rotary motion.

Regarding a constant rotational speed, the inventors have concluded that if the rotational speed f _ROT is constant, the time-series digital measurement signal S _MD comprising the vibration sample value S (i) has a repetition frequency f _R, which depends on the number L of blades 310 provided.

The state parameter extractor 450 may optionally include a Fast Fourier Transform (FFT) coupled to receive the digital measurement signal S _MD or a signal that depends on the digital measurement signal S _MD (see fig. 15A). Regarding analysis of a centrifugal pump having a rotating impeller 20, it may be of interest to analyze signal frequencies above the rotational frequency f _ROT of the rotating impeller 20. In this case, the rotation frequency f _ROT of the impeller 20 may be referred to as "1 st order". If the signal of interest occurs ten times per revolution of the housing, the frequency may be referred to as the 10 th order, i.e. the repetition frequency f _R (measured in Hz) divided by the rotational speed f _ROT (measured in revolutions per second rps) is equal to 10Hz/rps, i.e. oi=fr/f _ROT =10 th order.

The maximum order is called O _MAX and the total number of frequency bins in the FFT is used as B _n, the inventors conclude that according to one example, the following equation applies:

Oi*B_n＝N_R*O_MAX。

In contrast, N _R＝Oi*B_n/O_MAX, wherein,

O _MAX is the maximum order; and

B _n is the number of frequency bins in the FFT generated spectrum, and

Oi is the number L of blades 310 in the centrifugal pump housing being monitored.

The variables O _MAX、B_n and Oi described above should be set so that the variable N _R is a positive integer. In connection with the above example, it should be noted that the FFT analyzer is configured to receive a reference signal, i.e., the position marker signal value PS or E _P, once per revolution of the rotating impeller 20. As described in connection with fig. 2, the position-marking device 180 may be disposed on an outer wall surface of the impeller 20 such that, upon each revolution of the housing as the impeller 20 rotates about the rotation axis 60, the position-marking device 180 passes the position sensor 170 once, thereby causing the position sensor 170 to generate the rotation-marking signal values PS, E _P.

Incidentally, referring to the above example of the FFT analyzer setting, the resulting integer N _B may indicate the number of revolutions of the centrifugal pump impeller 20 being monitored, during which the digital signal S _MD is analyzed. According to one example, the variables O _MAX、B_n and Oi described above may be set by the human-machine interfaces HCI 210, 210S (see, e.g., fig. 1 and/or fig. 5 and/or fig. 15A).

Consider the case when the digital measurement signal S _MD is transmitted to an FFT analyzer: in this case, when the FFT analyzer is set for 10 blades, i.e., l=10, and B _n =160 frequency bins, and the user pays attention to analyzing frequencies up to the order O _MAX =100, the value of N _B becomes N _R＝Oi*B_n/O_MAX =10×160/100=16.

Thus, when B _n = 160 frequency bins are required, measurements need to be made during 16 housing rotations (N _R = 16), the number of blades being L = 10; and the user is concerned with analyzing frequencies up to order O _MAX = 100. In conjunction with the setting of the FFT analyzer, the order value O _MAX may indicate the highest frequency to be analyzed in the digital measurement signal S _MD.

According to some embodiments, when the FFT analyzer is configured to receive one reference signal, i.e. the position marker signal value PS, per revolution of the rotating impeller 20, the FFT analyzer should be set up to meet the following criteria:

the integer value Oi is set equal to L, i.e. the number of blades in the impeller 20, and

The settable variables O _MAX and B _n are selected such that the mathematical expression Oi B _n/O_MAX becomes a positive integer. In other words: when the integer value Oi is set equal to L, then settable variables O _MAX and B _n should be set to integer values, so that variable N _R is a positive integer,

Wherein N _R＝Oi*B_n/O_MAX.

According to one example, the number of bins B _n may be set by selecting a value B _n from a set of values. The set of selectable values for frequency resolution B _n may include:

B_n＝200

B_n＝400

B_n＝800

B_n＝1600

B_n＝3200

fig. 14A, 14B and 14C show another example of a cross-sectional view of the pump during operation.

According to the example of fig. 14A, 14B and 14C, the centrifugal pump impeller 20 has six blades 310, i.e., the number l=6.

For the purposes of this example, the sampling frequency is: at the rotational speed f _ROT of the impeller 20, there are n=7680 sampling points per revolution, or multiples of the sampling points. Thus, n may be 768 samples per revolution or 76800 samples per revolution. The actual number of samples per revolution is not critical, but it may vary depending on system conditions and system settings.

As described above, the impeller 20 is rotatable, so the position sensor 170 may generate a position signal Ep for indicating the instantaneous rotational position of the impeller 20. The position marker 180 may be used in conjunction with the impeller 20 such that the position marker 180 passes the position sensor 170 once per revolution of the impeller 20, causing the position signal Ep to display the position marker signal value P _S. Each position-marker signal value P _S represents a fixed position, i.e. a certain rotational position of the impeller 20 relative to the fixed stator.

As illustrated in fig. 2A, the pump delivery outlet flow rate Q _OUT, the sensors 70, ₅₄ may be mounted on the housing 62 beside the outlet for generating vibration signals S _EA、S_MD, se (i), S (j), S (Q) that depend on the pressure pulsation P _FP in the fluid material delivered by the pump.

According to the bernoulli principle, an increase in fluid velocity occurs simultaneously with a decrease in fluid pressure (see equations 1 and 2 above). Therefore, in analyzing the outflow pattern of the pump 10, attention needs to be paid to the instantaneous pressure P ₅₄ of the outlet region and its relation to the fluid velocity v ₅₄ (refer to part I of fig. 14A). The continuity equation for the fluid means that the total flow into and out of the enclosed volume must be zero. In other words, the sum of the flow into the enclosed volume and the flow out of the enclosed volume must be zero. Thus, for incompressible fluid in a flow tube (e.g., the outlet of pump 10), the continuity equation can be written as:

v₁ A₁＝v₂ A₂

wherein,

A ₁ =inflow region

V ₁ = velocity of fluid through inflow region a ₁

A ₂ =outflow region

V ₂ = velocity of fluid through outflow region a ₂

When the cross-sectional area of the outlet is constant, the pulsating flow Q _OUT necessarily results in a pulsating fluid velocity v ₅₄. According to bernoulli's principle, pulsating fluid velocity v ₅₄ occurs simultaneously with pulsating fluid pressure P ₅₄.

Fig. 14A shows an explanation of the flow pattern, i.e., the flow of the design points, during BEP operation.

Part I of fig. 14A shows the rotational position of the rotating impeller 20, wherein the blade tips 310A pass just past the tangs 65. Here, the vane tip 310A is located closest to the vane tongue, with minimal passage opening between the narrow volute section 77 and the wide volute section 78. Blade 310A is followed by an adjacent blade 310B.

When the pump is operated with the total output flow Q _OUT of the outlet 66 being the pump design flow (i.e., the pump point of best efficiency flow Q _OUTBEP), the pressure pulsations in the fluid exhibit minimal pulsation amplitude (see 550BEP in fig. 19A in combination with fig. 14A).

As shown in fig. 14A, the position of the position marker 180 relative to the impeller may be such that the position signal Ep displays a position marker signal value PS when the blade tip 310A is located closest to the volute tongue 65. In this case, the minimum pulse amplitude displayed appears to occur at a zero degree phase angle. The instantaneous flow from the outlet 66 at the time shown in FIG. 14AI is referred to herein as Q _OUTBEPI.

Part II of fig. 14A shows another rotational position of the rotary impeller 20, slightly later than the rotational position shown in part I of fig. 14A. In section II of fig. 14A, adjacent vane 310B is closer to the volute tongue 65, vane 310A is now located in the narrow volute section 77, and vane 310B is located in the larger volute section 78. Thus, at this point, the impeller passageway 320 between the vane 310A and the vane 310B provides a larger passageway opening between the narrow volute portion 77 and the wide volute portion 78. When the impeller 20 is in the rotated position shown in section II of FIG. 14A during BEP operation, a portion of the water flow from the inlet 64 flows through the passage 320 between the vanes 310A and 310B to the larger volute section and another portion of the water flow from the inlet 64 flows through the passage 320 between the vanes 310A and 310B to the narrower volute section. It is believed that there is no "leakage flow" between the narrow and wide volute portions during BEP operation, or, that there is substantially no "leakage flow" between the narrow and wide volute portions during BEP operation. Thus, at the time shown in section II of FIG. 14A, when the passage 320 between the vanes 310A and 310B is open to the same extent as the large volute section, then during BEP operation, approximately half of the flow from the inlet 64 flows through the passage between the vanes 310A and 310B to the large volute section, and approximately half of the flow from the inlet 64 flows through the passage between the vanes 310A and 310B to the narrow volute section. The instantaneous flow from the outlet 66 at the time indicated by AII in FIG. 14 is referred to herein as Q _OUTBEPII. The instantaneous flow Q _OUTBEPII appears to be approximately the same size as the instantaneous flow Q _OUTBEPI (fig. 14 AI). It is believed that the deviation of instantaneous flow Q _OUTBEPII from instantaneous flow Q _OUTBEPI may be very small, thereby producing relatively small pulsations during BEP operation.

Part III of fig. 14A shows the rotational position of the impeller 20, wherein the blade tips 310B pass right through the volute tongue 65. Here, the vane tip 310B is located closest to the volute tongue 65, so that the vane tip 310B substantially closes the passage opening between the narrow volute section and the wide volute section. Blade 310B is followed by an adjacent blade 310C. Thus, portion III of fig. 14A corresponds to portion I of fig. 14A. Thus, the instantaneous flow (referred to herein as Q _OUTBEPIII) at the time shown in fig. 14AIII at outlet 66 is the same size as instantaneous flow _QOUTBEPI (fig. 14 AI).

Fig. 14B shows the flow pattern when operating with the total output flow Q _OUT below the design point (i.e., below the BEP). The low instantaneous flow at the outlet 66 shown in section I of fig. 14B is referred to herein as Q _OUTLoI.

As shown in part II of fig. 14B, there appears to be leakage flow q3' from the large volute section 78 to the narrow volute section 77. Thus, the instantaneous flow rate (referred to herein as Q _OUTLoII) of outlet 66 at the time shown in part II of fig. 14B appears to be lower than instantaneous flow rate Q _OUTLoI.

It is believed that the instantaneous outlet flow Q _OUTLoII has a magnitude of Q _OUTLoI -Q3'.

It is believed that the leakage flow q3' from the large volute section 78 to the narrow volute section 77 is caused by the pressure differential between the large volute section 78 and the narrow volute section 77 when operating at a flow below the design point. This is because the pressure P ₇₈ in the large volute portion 78 is higher than the pressure P ₇₇ in the narrow volute portion 77 during operation at a flow rate below the design point.

From the point of view of flow through the pump, the moment shown in section III of fig. 14B corresponds to the moment shown in section I of fig. 14B from the pump inlet to the pump outlet. Thus, the instantaneous flow (referred to herein as Q _OUTLoIII) out of outlet 66 at the time shown in fig. 14BIII is the same size as instantaneous flow Q _OUTLoI (fig. 14 BI).

Thus, the flow periods shown in section I of FIG. 14B, section II of FIG. 14B, and section III of FIG. 14B appear to exhibit pulsations, the magnitude of which depends on the magnitude of the maximum leakage flow rate q 3'. When the impeller has l=6 blades, the pulsation will show l=6 such flow cycles when the impeller makes one revolution.

The above-described flow pulsations are believed to produce pulsatile fluid velocity v ₅₄ in region 54 (see fig. 1 and 2A and 14B). Thus, the fluid pressure P ₅₄ in this region 54 also pulsates according to Bernoulli's principle. Thus, the repetition frequency f _R of the fluid pressure pulsation P _FP in this region 54 is related to the rotational speed f _ROT of the impeller 20.

More specifically, the pressure P ₅₄ detected by the vibration sensors 70, 70 ₅₄, which are positioned to detect pressure fluctuations in the outlet fluid of the pump 10, appear to exhibit the following cycle:

When the impeller moves from the position shown in part I of fig. 14B to the position shown in part II of fig. 14B, the flow decreases from Q _OUTLoI to Q _OUTLoI -Q3', and thus the velocity v ₅₄ decreases and the pressure P54 increases. Conversely, as the impeller moves from the position shown in section II of FIG. 14B to the position shown in section III of FIG. 14B, the flow increases from Q _OUTLoI -Q3' to Q _OUTLoI, and thus the fluid velocity v ₅₄ increases and the pressure P54 decreases.

Thus, the phase of the detected pressure pulsation P ₅₄ depends on the current operating point 205 and impeller position relative to the BEP (see FIG. 2B). The following table summarizes the instantaneous outlet fluid pressure P ₅₄ as a function of impeller position when the pump is operating at an outlet flow rate that is lower than the BEP flow rate.

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The amplitude and phase values of the detected pressure pulsation P ₅₄ appear to indicate the relationship of the current operating point 205 to the BEP.

Therefore, it seems significant to determine the impeller position at which the highest peak P ₅₄ occurs. Another expression is that it seems necessary to determine at which position between two adjacent blade tips the highest peak P ₅₄ occurs in terms of the distance between two adjacent blade tips 310A and 310B. In this regard, reference may also be made to the discussion below in table 5 regarding the detected pressure pulsation phase values.

Fig. 14C shows the flow pattern when operating with the total output flow Q _OUT above the design point (i.e., above the BEP).

The instantaneous flow at the time outlet 66 shown in part I of fig. 14C is relatively high, referred to herein as Q _OUTHiI.

As shown in part II of fig. 14C, there appears to be leakage flow q3 from the narrow volute section 77 to the large volute section 78. Thus, at the time shown in part II of fig. 14C, the instantaneous flow rate of the outlet 66 (referred to herein as Q _OUTHiII) appears to be higher than the instantaneous flow rate Q _OUTHiI.

It is believed that the instantaneous outlet flow Q _OUTHiII has a size of Q _OUTHiI +q3.

It is believed that during operation at flow levels above the design point, leakage flow q3 from the narrow volute section 77 to the large volute section 78 is caused by the pressure differential between the narrow volute section 77 and the large volute section 78. This is because during operation with flow above the design point, the pressure P ₇₈ in the large volute portion 78 is lower than the pressure P ₇₇ in the narrow volute portion 77.

From the point of view of flow through the pump, the moment shown in section III of fig. 14C corresponds to the moment shown in section I of fig. 14C from the pump inlet to the pump outlet. Thus, it is believed that the instantaneous flow (referred to herein as Q _OUTHiIII) out of outlet 66 at the time shown in section III of fig. 14C is the same size as instantaneous flow Q _OUTHiI (section I of fig. 14C).

Thus, the flow periods shown in section I of FIG. 14C, section II of FIG. 14C, and section III of FIG. 14C appear to exhibit pulsations, the magnitude of which depends on the magnitude of the maximum leakage flow rate q 3. When the impeller has l=6 blades, the pulsation will show l=6 such flow cycles when the impeller makes one revolution. As described above in fig. 14B, the fluid pressure P ₅₄ in the region 54 near the pump outlet 66 shows a fluid pressure pulsation P _FP according to the bernoulli principle.

More specifically, the pressure P ₅₄ detected by the vibration sensor 70, 70 ₅₄ positioned to detect pressure fluctuations from the outlet fluid species of the pump 10 shows the following cycle:

When the impeller moves from the position shown in part I of fig. 14C to the position shown in part II of fig. 14C, the flow increases from Q _OUTHiI to Q _OUTHiI +q3, and thus the fluid velocity v ₅₄ increases and the pressure P ₅₄ decreases.

In contrast, when the impeller moves from the position shown in part II of fig. 14C to the position shown in part III of fig. 14C, the flow decreases from Q _OUTHiI +q3 to Q _OUTHiI, and thus the fluid velocity v ₅₄ decreases and the pressure P ₅₄ increases.

Thus, the phase of the detected pressure pulsation P ₅₄ depends on the current operating point 205 and the impeller position associated with the BEP (see FIG. 2B). The following table summarizes the instantaneous outlet fluid pressure P ₅₄ as a function of impeller position when the pump is operating at an outlet flow rate higher than the BEP flow rate.

Impeller position (higher than BEP flow)	Pressure P ₅₄
		I	At the highest peak
I towards II	The pressure P ₅₄ is continuously decreased
		At or near II	Decrease, pass through the lowest peak P ₅₄, then increase
II towards III	The pressure P ₅₄ is continuously increased
		IIII＝I	At the highest peak

Therefore, it seems significant to determine the impeller position at which the lowest peak P ₅₄ occurs. Another expression is that it seems necessary to determine at which position between two adjacent blade tips the lowest peak P ₅₄ occurs in terms of the distance between two adjacent blade tips 310A and 310B. In this regard, reference may also be made to the discussion below in table 5 regarding the detected pressure pulsation phase values.

According to one explanation, the flow patterns shown in fig. 14A-14C provide a cause for the detected phase values, as described in fig. 16-19D. It is particularly noted that the first polar angle (X1 (r), FI (r), Φ (r), T _D、T_D1) may be phase shifted by about 180 degrees when the operating point 205 changes from below to above the BEP and/or when the operating point 205 changes from above to below the BEP. Therefore, this phase shift should be kept in mind when viewing fig. 14B and 14C. In this regard, please refer to an internal status indication object 550, which will be discussed in other portions of the present disclosure (e.g., fig. 16-19D).

Thus, it appears desirable to control the pump to move the current internal state 550 (r) toward the origin reference point (O, 530) in the polar plots of fig. 16-19B, or to a position as close as possible to the reference point (O, 530), so that the flow pattern is as close as possible to that shown in fig. 14A.

Fig. 14D, 14E and 14F show another example of a cross-sectional view of the pump during operation, showing flow and pressure patterns in the pump and another aspect of its detection. According to the example of fig. 14D, 14E and 14F, the centrifugal pump 10 may include a sensor 70, 70 ₇₇ connected to the housing 62 at the first volute section 77 by a narrower cross-sectional area near the volute tongue 65 (see also fig. 2D). The pump 10 of fig. 14D, 14E, and 14F may include and be configured as described above with respect to fig. 1A, 2A, and 2D and/or elsewhere herein. However, the example of the centrifugal pump 10 of fig. 14D, 14E, and 14F may include sensors 70, 70 ₇₇ connected to the housing 62 at the first volute section 77 by a narrower cross-sectional area near the volute tongue 65.

As shown in fig. 14D, 14E and 14F, the positioning of the sensor 70 ₇₇ appears to be advantageous because the sensor is relatively close to the passing blade tip, which appears to exhibit detectable localized high and low pressures when the pump is operated away from BEP flow, as will be discussed in detail below in connection with fig. 14E and 14F.

Portions I, II and III of fig. 14D show an explanation of flow and pressure patterns during BEP operation, i.e., flow at the design point.

As described above, fluid may flow axially toward the inlet 64 at the center of the impeller 20, rotating the impeller blades 310 deflects the fluid so that it exits through the holes 320 between the blades 310. Rotating the impeller blades 310 causes centrifugal acceleration of the fluid, which changes direction and accelerates. When the pump is operating at BEP flow Q _OUTBEP, the accelerated fluid has reached tangential velocity v ₇₅ when it reaches the blade tip and enters volute 75 from orifice 320, while tangential fluid velocity v ₇₅ remains the same when the fluid flows along volute 75 to outlet 66 when the pump is operating at BEP flow Q _OUTBEP.

Thus, when the pump is operating at BEP flow Q _OUTBEP, the tangential velocity component v ₇₅ of the accelerating fluid 30 corresponds to the tangential velocity of the blade tips 310A, 310B, 310C. In fact, if the pump is operating at exactly BEP flow Q _OUTBEP, the fluid tangential velocity component v ₇₅ appears to be the same as the tangential velocity v _310T of the blade tips. In this way, as fluid flows along volute 75, more and more fluid 30 flows out of rotating impeller passage 320, but as the cross-sectional area of the volute increases, tangential fluid velocity v ₇₅ remains the same when the pump is operated at BEP flow rate Q _OUTBEP.

Incidentally, when the pump is operated at BEP flow rate Q _OUTBEP, the radial velocity component v _75R of the accelerating fluid 30 also corresponds to the progressively increasing volute cross-sectional area. The gradual widening of the cross-sectional area of the volute is such that the amount of fluid added to the volute per unit time balances the widening of the cross-sectional area per unit time when the pump is operating at BEP flow rate Q _OUTBEP. Thus, according to the continuity equation, the tangential fluid velocity v75 remains unchanged when the pump is operating at the BEP flow rate Q _OUTBEP. In this way, when the pump is operated at BEP flow rate Q _OUTBEP, the fluid appears to exhibit laminar or substantially laminar flow in the volute.

Part I of fig. 14D shows the rotational position of the rotating impeller 20, wherein the blade tips 310A pass just past the tangs 65. Here, the blade tip 310A is located closest to the blade tongue, with minimal passage opening between the narrow blade portion 77 and the wide blade portion 78. Blade 310A is followed by an adjacent blade 310B. The instantaneous flow from outlet 66 at the time shown in fig. 14DI is referred to herein as Q _OUTBEPI.

Part II of fig. 14D shows another rotational position of the rotary impeller 20, which is slightly later than the rotational position shown in part I of fig. 14D. In section II of fig. 14D, adjacent vane 310B is located closer to the volute tongue 65, the vane tip 310A is now located in the narrower volute section 77, and the vane 310B is located in the larger volute section 78.

Thus, as shown in section II of FIG. 14D, the blade tip 310A is now relatively close to the vibration sensor 70 ₇₇. This appears to be advantageous, as will be discussed in more detail below in connection with fig. 14E and 14F.

When the pump is operating at BEP flow Q _OUTBEP, the tangential fluid velocity component v ₇₇ of the accelerating fluid 30 at the blade tip 310A corresponds to the tangential velocity v _310T of the blade tip 310A. As fluid 30 flows along volute 75, more and more fluid 30 exits rotating impeller passage 320, but as the cross-sectional area of the volute increases, tangential fluid velocity v ₇₅ remains the same when the pump is operating at BEP flow rate Q _OUTBEP, and tangential fluid velocity component v ₇₈ in wide volute portion 78 is the same or substantially the same as tangential fluid velocity component v ₇₇ in narrow volute portion 77.

Part III of fig. 14D shows the rotational position of the impeller 20, wherein the blade tips 310B pass just past the volute tongue 65. Here, the vane tip 310B is located closest to the volute tongue 65, and thus the vane tip 310B substantially closes the passage opening between the narrow and wide portions of the volute. Blade 310B is followed by an adjacent blade 310C. Thus, the instantaneous flow and pressure pattern at the instant shown in section III of fig. 14D is the same as the flow and pressure pattern at the instant shown in section I of fig. 14D.

Blade tip local pressure region during operation at flow rates lower than BEP flow rates

Portions I, II and III of fig. 14E show the flow and pressure patterns when the total output flow Q _OUTLo is below the design point (i.e., below the BEP flow). The low instantaneous flow at outlet 66 at the time shown in section I of fig. 14E is referred to herein as Q _OUTLoI.

As described above, fluid may flow axially toward the inlet 64 at the center of the impeller 20, and the rotating impeller 20 deflects the fluid to exit through the holes 320 between the blades 310 (see fig. 2D, in conjunction with fig. 14D, 14E, 14F). The rotating impeller causes centrifugal acceleration of the fluid, and thus the fluid changes direction and accelerates. When the pump is operated at an output flow rate Q _OUTLo below the design point, i.e., below the BEP flow rate, the accelerated fluid, as it reaches the vane tips and exits from the orifice 320 into the volute 75, has a radial velocity component v _75R that is low relative to the progressively widening volute cross-sectional area. Because of the lower radial velocity component v _75R, the amount of fluid entering volute 75 from aperture 320 between two adjacent vanes 310 is such that when the pump is operating at an output flow rate Q _OUTHi above the design point, the amount of fluid added to the volute per unit time is less than the amount of widening of the cross-sectional area per unit time. Thus, according to the continuity equation, the tangential fluid velocity v ₇₅ gradually decreases when the pump is operated at an output flow rate Q _OUTHi below the design point. Thus, referring to section II of fig. 14E, when the pump is operating at an output flow rate below the design point, the tangential fluid velocity v ₇₈ in the volute wide portion 78 is lower than the tangential fluid velocity v ₇₇ in the narrow portion 77.

Thus, the effect of the pump operating below the design flow is that the tangential fluid velocity v ₇₅ becomes lower than the tangential velocity of the blade tips. Now, when we observe a single blade tip, the speed deviation between the higher tangential velocity of the blade tip at the inner edge of the volute and the lower tangential fluid velocity v ₇₅ causes a localized high-pressure zone on the front side of the blade tip, indicated by the plus sign "+" in sections I, II and III of fig. 14F, and a localized low-pressure zone on the rear side of the blade tip, indicated by the minus sign "-" in sections I, II and III of fig. 14F.

Part I of fig. 14E shows the rotational position of the rotating impeller 20, wherein the blade tips 310A pass just past the volute tongue 65. Thus, at this point the localized high pressure region (indicated by the plus sign "+" in section I of FIG. 14E) on the front side of blade tip 310A is approaching sensor 70 ₇₇, which is believed to result in an increase in the instantaneous fluid pressure in the fluid region near sensor 70 ₇₇.

Part II of fig. 14E shows another rotational position of the rotary impeller 20, slightly later than the rotational position shown in part I of fig. 14E. In section II of fig. 14E, the blade tip 310A is located in the narrow volute section 77 and just past the sensor 70 ₇₇. Thus, as shown in section II of FIG. 14E, where blade tip 310A is relatively close to vibration sensor 70 ₇₇, the instantaneous fluid pressure in the fluid region near sensor 70 ₇₇ drops from a high pressure on the front side of blade tip 310A to a low pressure on the rear side of blade tip 310A, indicated by the minus sign "-" in section II of FIG. 14E. Thus, at the time shown in part II of FIG. 14E, sensor 70 ₇₇ appears to detect a negative pressure derivative.

Part III of fig. 14E shows the rotational position of impeller 20 slightly later than shown in part II of fig. 14E, with blade tip 310B just past volute tongue 65. Thus, at the time shown in section III of FIG. 14E, sensor 70 ₇₇ is considered to detect a positive pressure derivative because the local low pressure on the trailing side of blade tip 310A is offset from the fluid region near sensor 70 ₇₇, while the local high pressure on the leading side of blade tip 310B is approaching the fluid region near sensor 70 ₇₇.

Thus, the phase of the detected pressure pulsation P ₇₇ depends on the current operating point 205 and the impeller position associated with the BEP (see FIG. 2B). The following table summarizes the instantaneous fluid pressure P ₇₇ as a function of impeller position when the pump is operated at an outlet flow rate that is lower than the BEP flow rate.

Impeller position (below BEP flow)	Pressure P ₇₇
		I	Increase in size
I towards II	Continue to increase, pass through the highest peak, and then decrease
		II	Descent down
II towards III	Continue to descend, pass through the lowest peak, and then increase
		IIII＝I	Increase in size

From this, the amplitude and phase values of the detected pressure pulsation P ₇₇ indicate the relationship of the current operating point 205 to the BEP. In this regard, please refer to the discussion below in table 5 regarding the detected pressure pulsation phase values.

Because of the higher tangential velocity of the blade tips and the lower tangential velocity v ₇₅ of the fluid, a localized high pressure region occurs on the front side of the blade tips (indicated by positive sign "+" in sections I, II and III of fig. 14E) and a localized low pressure region occurs on the rear side of the blade tips (indicated by negative sign "-" in sections I, II and III of fig. 14E), turbulence in the volute, i.e., below BEP flow, occurs when the pump is operated at an output flow Q _OUTLo below the design point, i.e., below BEP flow. Thus, the occurrence of turbulence appears to result in a decrease in the energy efficiency of the pumping process, as part of the energy fed to the impeller by the drive motor may result in swirling motion of the fluid and a rise in temperature of the fluid caused by the swirling.

In this way, when the pump is operated at an output flow rate Q _OUTLo below the design point, i.e., below the BEP flow rate, turbulence of the fluid in the volute may occur.

From the point of view of flow through the pump, the moment shown in section III of fig. 14E corresponds to the moment shown in section I of fig. 14E, section I of fig. 14B, and section III of fig. 14B from the pump inlet to the pump outlet. Thus, it is believed that the instantaneous flow (referred to herein as Q _OUTLoIII) out of the outlet 66 at the time shown in section III of fig. 14E is the same size as the instantaneous flow Q _OUTLoI (see section I of fig. 14E and section I of fig. 14B). In contrast, it is believed that the instantaneous flow out of the outlet 66 at the time shown in part II of fig. 14E (referred to herein as Q _OUTLoII) is lower than the instantaneous flows Q _OUTLoI and Q _OUTLoIII (part I of fig. 14E and part III of fig. 14E). Instantaneous flow Q _OUTLoII (part II of fig. 14E) corresponds to flow Q _OUTLoII in part II of fig. 14B. Thus, when the pump is operated at an output flow rate below the design point, the output flow rate Q _OUTLo appears to pulsate, with the magnitude of the pulsation being dependent on the magnitude of the maximum leakage flow rate Q3', as discussed above with respect to section I, section II, and section III of fig. 14B. Further, experiments appear to show that the amplitude of the vibrations detected by the sensors 70, 70 ₇₇ attached to the first narrower volute portion 77 of the housing 62 increases when the pump is operated further from the design point. Further, experiments appear to show that when the pump is operating at an output flow rate Q _OUTLo below the design point, i.e. below the BEP flow rate, the amplitude of the vibrations detected by the sensors 70, 70 ₇₇ attached to the housing 62 of the first narrower volute portion 77 corresponds to the amplitude of the pulsations of the outlet flow rate Q _OUTLo. When the impeller has l=6 blades, the pulsation will show l=6 such flow cycles when the impeller makes one revolution.

Blade tip local pressure region during operation at flow rates above BEP flow

Portions I, II and III of fig. 14F show the flow and pressure patterns when the total output flow Q _OUTHi is above the design point (i.e., above the BEP flow). The instantaneous high flow at the outlet 66 shown in section I of fig. 14F is referred to herein as Q _OUTHiI.

As described above, fluid may flow axially toward the inlet 64 at the center of the impeller 20 and the rotating impeller 20 may deflect the fluid to exit through the holes 320 between the blades 310. The impeller blades 310 exert a centrifugal acceleration on the fluid, so that the fluid changes direction and is accelerated. When the pump is operated at an output flow rate Q _OUTHi above the design point, i.e., above the BEP flow rate, the radial velocity component v _75R of the accelerated fluid is high compared to the progressively widening volute cross-sectional area as it reaches the vane tips and exits from the orifice 320 into the volute 75. Because of the higher radial velocity component v _75R, the amount of fluid entering volute 75 from aperture 320 between two adjacent vanes 310 is such that when the pump is operating at an output flow rate Q _OUTHi above the design point, the amount of fluid added to the volute per unit time exceeds the amount of widening of the cross-sectional area per unit time. Thus, according to the continuity equation, the tangential fluid velocity v ₇₅ gradually increases when the pump is operated at an output flow rate Q _OUTHi above the design point. Referring to section II of fig. 14F, when the pump is operating at an output flow rate above the design point, the tangential fluid velocity v ₇₈ in the volute wide portion 78 is higher than the tangential fluid velocity v ₇₇ in the narrow portion 77.

Thus, when the pump is operating above the design point, the tangential fluid velocity v ₇₅ will be higher than the tangential velocity of the blade tips. Now, when we observe a single blade tip, the velocity deviation between the higher tangential fluid velocity v ₇₅ and the lower tangential velocity of the blade tip causes a localized high pressure zone at the rear side of the blade tip, indicated by the plus sign "+" in sections I, II and III of fig. 14F, and a localized low pressure zone at the front side of the blade tip, indicated by the minus sign "-" in sections I, II and III of fig. 14F.

Part I of fig. 14F shows the rotational position of the rotating impeller 20, wherein the blade tips 310A pass just past the volute tongue 65. Thus, at this point, it is believed that a localized low pressure region (indicated by the minus sign "-" in section I of FIG. 14F) on the front side of blade tip 310A is approaching sensor 70 ₇₇, resulting in a pressure drop in the fluid region near sensor 70 ₇₇.

Part II of fig. 14F shows another rotational position of the rotary impeller 20, slightly later than the rotational position shown in part I of fig. 14F. In section II of fig. 14E, the blade tip 310A is located in the narrow volute section 77 and just past the sensor 70 ₇₇. Thus, as shown in section II of FIG. 14F, where blade tip 310A is relatively close to vibration sensor 70 ₇₇, the instantaneous fluid pressure in the fluid region near sensor 70 ₇₇ increases from a low pressure on the front side of blade tip 310A to a high pressure on the rear side of blade tip 310A, indicated by the minus sign "+" in section II of FIG. 14F. Thus, at the time shown in part II of FIG. 14F, sensor 70 ₇₇ appears to detect a positive pressure derivative.

Part III of fig. 14F shows the rotational position of the impeller 20 slightly later than the rotational position shown in part II of fig. 14F, with the blade tip 310B just past the volute tongue 65. Thus, at the time shown in section III of FIG. 14F, sensor 70 ₇₇ is considered to detect a negative pressure derivative because the local low pressure on the rear side of blade tip 310A is offset from the fluid region near sensor 70 ₇₇, while the local high pressure on the front side of blade tip 310B is approaching the fluid region near sensor 70 ₇₇.

Thus, the phase of the detected pressure pulsation P ₇₇ depends on the current operating point 205 and the impeller position associated with the BEP (see FIG. 2B). The following table summarizes the instantaneous fluid pressure P ₇₇ as a function of impeller position when the pump is operating at an outlet flow rate that is higher than the BEP flow rate.

Impeller position (higher than BEP flow)	Pressure P ₇₇
		I	Descent down
I towards II	Continue to descend, pass through the lowest peak, and then increase
		II	Increase in size
II towards III	Continue to increase, pass through the highest peak, and then decrease
		IIII＝I	Descent down

Since the tangential velocity of the blade tips is high and the tangential velocity v ₇₅ of the fluid is low, resulting in a localized high pressure region on the rear side of the blade tips (indicated by positive sign "+" in sections I, II and III of fig. 14F) and a localized low pressure region on the rear side of the blade tips (indicated by negative sign "-" in sections I, II and III of fig. 14F), turbulence in the volute, i.e., higher than BEP flow, occurs when the pump is operated at an output flow rate Q _OUTHi above the design point, i.e., higher than BEP flow. Thus, the occurrence of turbulence appears to result in a decrease in the energy efficiency of the pumping process, as part of the energy fed to the impeller by the drive motor may result in swirling motion of the fluid and a rise in temperature of the fluid caused by the swirling.

In this way, when the pump is operated at an output flow rate Q _OUTHi above the design point, i.e., above the BEP flow rate, turbulence of the fluid in the volute may occur.

From the point of view of flow through the pump, the moment shown in section III of fig. 14F corresponds to the moment shown in section I of fig. 14F, section I of fig. 14C, and section III of fig. 14C from the pump inlet to the pump outlet. Thus, it is believed that the instantaneous flow (referred to herein as Q _OUTHiIII) out of the outlet 66 at the time shown in section III of fig. 14F is the same size as the instantaneous flow Q _OUTHiI (see section I of fig. 14F and section I of fig. 14C). In contrast, it is believed that the instantaneous flow from the outlet 66 at the time shown in fig. 14F II (referred to herein as Q _OUTHiII) is higher than the instantaneous flows Q _OUTHiI and Q _OUTHiIII (part I of fig. 14F and part III of fig. 14F). Instantaneous flow Q _OUTHiII (part II of fig. 14F) corresponds to flow Q _OUTHiII in part II of fig. 14C. Thus, when the pump is operated at an output flow rate above the design point, the output flow rate Q _OUTHi appears to pulsate, with the magnitude of the pulsation being dependent on the magnitude of the maximum leakage flow rate Q3, as discussed above with respect to section I, section II, and section III of fig. 14C. Further, experiments appear to show that the amplitude of the vibrations detected by the sensors 70, 70 ₇₇ attached to the first narrower volute portion 77 of the housing 62 increases when the pump is operated further from the design point. Further, experiments appear to show that when the pump is operating at an output flow rate Q _OUTHi above the design point, i.e. above the BEP flow rate, the amplitude of the vibrations detected by the sensors 70, 70 ₇₇ attached to the housing 62 of the first narrower volute portion 77 corresponds to the amplitude of the pulsations of the outlet flow rate Q _OUTHi. When the impeller has l=6 blades, the pulsation will show l=6 such flow cycles when the impeller makes one revolution.

According to one explanation, the flow and pressure patterns shown in fig. 14D-14F provide a cause for the detected phase values, as described in fig. 16-19D.

In particular, it is noted that the first polar angles X1 (r), FI (r), Φ (r), T _D、T_D1 exhibit a phase shift of about 180 degrees when the operating point 550 changes from below to above the BEP, or vice versa. Thus, this phase shift should be kept in mind when viewing fig. 14E and 14F. In this regard, reference is made to an internal status indication object 550, which is discussed elsewhere in this disclosure, e.g., in connection with fig. 16-19D.

Furthermore, the analysis appears to show that the detected pressure signal 70 ₇₇ shows a different phase compared to the detected pressure signal 70 ₅₄. Accordingly, the internal state of the centrifugal pump 10 can be estimated or detected based on the mutual occurrence sequence of the vibration signal detected by the sensor 70 ₅₄ and the vibration signal detected by the sensor 70 ₇₇.

Method for identifying current operating point

Fig. 14G is another illustration of the example pump 10 of any of fig. 1A, 1B, 2A, 2B, 2D, 2E, or any of fig. 14A-14F. The disclosure related to fig. 14G may be related to any pump discussed in this disclosure. In the interest of clarity, the example pump shown in fig. 14G does not show all of the features of pump 10. For example, fig. 14G shows one wall of the pump outlet, but the wall portion near the volute tongue 65 is omitted in fig. 14G to more clearly show an example of the stator positions P1, P _S.

As shown in fig. 14G, the example pump 10 includes a housing 62, with the rotatable impeller 20 disposed in the housing 62 so as to be rotatable about a rotational axis 60. Housing 62 forms volute 75 and the pump includes volute tongue 65, separating one portion 77 of the volute from another portion 78. The volute tongue 65 has a tongue tip 65T. The whirlpool tongue 65 may have an elongated shape, wherein the tongue tip 65T may form an edge. Thus, the volute tongue 65 may separate the outlet tube 66 from the narrow volute section 77.

In other words, the housing 62 may include a volute tongue 65 having an elongated shape, wherein the elongated tip 65T may form an edge separating the outlet 66 from the narrow volute portion 77. During pump operation, at the point of optimum efficiency operation (BEP), the fluid proximate the tongue tip 65T is preferably split into two portions so as to flow from the elongated tongue tip 65T to the outlet 66 and from the elongated tongue tip 65T to the narrow volute portion 77 (see fig. 14G and 14A and/or 14D).

The pump shown in fig. 14G is designed with the impeller rotated in a clockwise direction. As shown in fig. 14G, a position-marking device 180 may be used in conjunction with the impeller 20, such that when the impeller 20 rotates about the rotational axis 60, the position-marking device 180 passes the position sensor 170 once per revolution of the impeller, thereby causing the position sensor 170 to generate a rotation-marking signal value PS. Additionally, the position signal values PS, PC may be generated by the encoder 170, as described elsewhere in this disclosure.

When there is one position-marker signal value P _S per revolution and the rotational speed f _ROT is constant or substantially constant, there will be a constant or substantially constant number of vibration sample values S (i) per revolution of the pump impeller 20. For the purpose of this example, the position signal P (0) indicates a vibration sample i=0, as shown in table 2 (see below). For purposes of illustration, the position of the position signal P (0) relative to the impeller 20 may not be important, so long as the repetition frequency f _P is dependent on the rotational speed f _ROT of the rotating centrifugal pump impeller 20. Thus, if the position signal E _P had a pulse Ps per revolution of the impeller 20, the digital position signal would also have a position signal value P (i) =1 per revolution, with the remaining position signal values being zero.

TABLE 2

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Thus, at a certain constant speed f _ROT, there may be n slots per revolution, as shown in Table 2, n may be a positive integer. In the example of table 2, n=7680.

There is one position signal P _S per revolution, which we know will repeat every n time slots, since the rotational speed f _ROT is constant. Thus, a plurality of virtual position signals P _C can be generated by calculation. In one example, consider generating virtual position signal P _C. Providing each blade 310 with L virtual position signals P _C, i.e., one virtual position signal P _C, may be used to establish a temporal relationship between:

The position signals P _C, P (i) occur with a second repetition frequency f _P, which depends on the rotational speed f _ROT of the rotating centrifugal pump impeller 20.

There are L equidistant blades 310 in the pump housing and one position signal P _S and constant speed f _ROT per revolution, one virtual position signal P _C can be generated for each blade, so that the total number of position signals P _S、P_C is evenly distributed. Each such position-marker signal value P _S and P _C indicates a rest position, i.e., the position of stationary housing 62, as shown by "P _S" and "P _C" in fig. 14G. The housing 62 may also be referred to as a stator 62 because the housing is stationary or motionless.

Thus, as shown in Table 3, when n slots are provided per revolution, the position signal P _S or P _C will occur at every n/L sample value positions. In table 3, n=7680, l=6, thus providing one position signal P _C per 1280 samples, the calculated position signal being denoted 1C.

As shown in the example of fig. 14G, the position-marker signal values P _S and P _C indicate L fixed positions P1, P2, P3, P4, P5 and PL, where l=6, because there are 6 blades 310, 310 ₁、310₂、310₃、310₄、310₅、310₆、310_L in the illustrated impeller 20.

It may be assumed that the operating point of the pump is substantially constant during a single rotation of the impeller 20. In other words, the location of the pulsation event in the fluid is substantially fixed during a single rotation of the impeller 20.

Since the vibration signal amplitude component S _FP、S_P is generated by a pulsation event in the fluid (see fig. 14A-14F), it will be repeated at the frequency of one vibration signal amplitude component S _FP、S_p per blade 310. Thus, it can be assumed that:

occurrence of the amplitude component S _FP、S_p of the repetitive vibration signal, and

The time relationship between the occurrence of the position signal P, PC is approximately constant for each of the L data blocks, in this example, l=6.

Table 3 shows the principle of time course of the position signal value P (i), the calculated position signal value P (i) being denoted as "1C".

TABLE 3 Table 3

TABLE 4 Table 4

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TABLE 5

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As described above, the impeller 20 may rotate about the rotational axis 60, and thus the fixedly mounted position sensor 170 may generate a position signal Ep having a series of housing position signal values P _S for indicating the instantaneous rotational position of the impeller 20. As shown in fig. 2A, the position marker 180 may be mechanically coupled to the impeller 20 such that when the impeller 20 rotates about the rotational axis 60, the position marker 180 passes the position sensor 170 during one rotation of the impeller 20, thereby causing the position sensor 170 to generate a rotation marker signal value P _S.

As described above, the position sensor 170 may generate a position signal Ep having a series of housing position signal values P _S for indicating the instantaneous rotational position of the impeller 20 as the impeller 20 rotates. Referring to tables 2-4 in this document, such a flag signal value P _S is shown as "1" in column #2 of tables 2-4.

When the rotating impeller is provided with a position marker 180, a marker signal value P _S will be provided once per revolution. In tables 2-4, the flag signal value P _S is shown as "1" in column # 2. There are L equidistant blades 310 in the pump housing and one position signal value P _S and constant rotational speed f _ROT per revolution, it is possible to generate one virtual position signal P _C for each blade, such that the total number of position signal values P _S、P_C is evenly distributed, as described above (see fig. 14G). Thus, as shown in Table 3, when n slots are provided per revolution, the position signal P _S or P _C will occur at every n/L sample value positions. In table 3, n=7680 and l=6, so one position signal P _C is provided every 1280 samples, the calculated position signal being indicated as 1C.

It is believed that when the marker signal value P _S (indicated as "1" in column #2 of tables 2-4) is provided once per revolution and the virtual position signal value P _C is generated in an evenly distributed manner, for some embodiments of the present disclosure, the equidistant positions of the blades 310 from each other are important, such that when n time slots are provided per revolution in the housing position signal value sequence for indicating the instantaneous rotational position of the impeller 20, the position signal P or P _C will occur at every n/L sample value positions, as shown in table 3. In table 3, the actually detected rotation flag signal value P _S is reflected as "1" (see column #2, slot "0" and slot "7680" in table 3), and the virtual position signal value P _C is reflected as "1C" (see column #2, slot "0" and slot "7680" in table 3).

This is believed to be important for some embodiments of the present disclosure, because the position marker 180 results in the generation of a position reference signal value, and the blade 310 participates in causing a signal event, e.g., an amplitude peak in the vibration signal (see, e.g., references S _EA、S_MD, se (i), S (j), S (q) in fig. 1 and 15). Further, the duration between the occurrence of the position reference signal value and the occurrence of the signal event in the vibration signal may be indicative of the internal state of the pump in operation, as discussed elsewhere in this disclosure, the duration being caused by pulsations in the fluid material 30.

Table 4 is a schematic diagram of a first block of data (i.e., associated with channel I) having n/l=7680/6=1280 consecutive slots. It will be appreciated that if there is a constant speed phase (see fig. 9) for the duration of a complete rotation of the impeller 20, each of the channels I to VI (see table 3) will have the same appearance as the channel I shown in table 4.

According to an embodiment of the present disclosure, referring to column #03 in table 4, a vibration sample value S (i) is analyzed for detecting a vibration signal characteristic S _FP. The vibration signal characteristic S _FP may be represented as a peak amplitude sample value S _P. According to one example, referring to column #03 in table 4, the vibration sample value S (i) is analyzed by a peak detector for detecting the peak sample value S _P. Referring to table 5, the peak analysis results in the detection of the highest vibration sample amplitude value S (i). In the example shown, the vibration sample amplitude value S (i=760) is detected as maintaining the highest peak S _P.

Having detected that peak S _P is located in time slot 760, a temporal relationship between the occurrence of the repetitive vibration signal amplitude component S _P and the occurrence of the position signal P (i) may be established. In table 5, the time slots transmitting the position signal P (i) are denoted as 0% and 100%, respectively, and all time slots therebetween may be marked with their corresponding positions, as shown in column #02 in table 5. As shown in the example in column #02 of table 5, the time position of the slot number i=760 is a position of 59% of the time distance between the slot i=0 and the slot i=1280. In other words 760/1280=0.59=59%.

Thus, the inventors concluded that:

The temporal relationship between the occurrence of the repetitive vibration signal amplitude component S _FP and the occurrence of the position signal P (i) may be used as an indication of the physical location of the event signature between two adjacent blades 310 in the rotating impeller 20, e.g., between the blades 310A and 310B. In this regard, reference is made to fig. 14A-14C and 14D-14F for a discussion of the amplitude and phase values of the detected pressure pulsations P ₅₄ and P ₇₇, respectively. As described herein, it appears that the amplitude and phase values of the detected pressure pulsations P ₅₄ and/or P ₇₇ indicate the current operating point 205 associated with the BEP (see also fig. 2B).

Thus, it seems to be meaningful to determine the impeller position at which peak P ₅₄ and/or P ₇₇ occur. Another expression is: in terms of the distance between two adjacent blade tips 310A and 310B, it appears to be meaningful to determine where the highest peak P ₅₄ and/or P ₇₇ occurs between two adjacent blade tips. This is because this location (i.e. where the highest peak occurs) appears to be indicative of the current operating state of the pump. More specifically, the location where the highest peak occurs appears to be indicative of the operational operating state of the pump relative to the optimal operating point.

Thus, the position of the detected event signature 205, expressed as a percentage of the distance between the tips of two adjacent blades 310A, 310B (see FIGS. 14A-14C and 14D-14F and Table 5), may be obtained by:

Count the total number of samples (N _B-N₀＝N_B-0＝N_B =1280) from the first reference signal occurrence in sample number N ₀ =0 to the second reference signal occurrence in sample number N _B =1280, and

Count another number of samples (N _P-N₀＝N_P-0＝N_P) from the occurrence of the first reference signal at N ₀ = 0 to the occurrence of the peak amplitude value S _P at sample number N _P, and

The first time relation (R _T(r);T_D; FI (R)) is generated based on the another number N _P and the total number N _B. This can be summarized as:

R_T(r)＝R_T(760)＝(N_P-N₀)/(N_B-N₀)＝(760-0)/(1280-0)＝0.59＝59％

thus, information identifying the instantaneous operating point 205 may be generated by:

count the total number of samples (N _B) from the first reference signal generation to the second reference signal generation, and

Count another number of samples (N _P) from the occurrence of the first reference signal to the occurrence of the peak amplitude value S _P at sample number N _P, and

The first temporal relationship (R _T(r);T_D; FI (R)) is generated based on a relationship between the number of samples N _P and the total number of samples (i.e., N _B).

Because s=v×t, where s=distance, v=constant speed, t is time, the time relationship can be directly converted to distance. Thus, column #02 of table 5 may be considered the physical location of the event signature at a location 59% of the distance between blade 310A and blade 310B (see fig. 14E, 14F, and/or 14B, 14C along with column #02 of table 5). Additionally, column #02 of table 5 may be considered to indicate the physical location of the event signature at a percentage of the distance between the first and second static locations P1, P2 (see fig. 14G in combination with column #02 of table 5 and in view of fig. 14E, 14F and/or 14B, 14C).

According to another example, referring to table 6, the time relationship between the occurrence of the repetitive vibration signal amplitude component S _P and the occurrence of the position signal P (i) may be regarded as a phase deviation or a phase value FI in degrees.

TABLE 6

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In fact, by using the position signal as a reference signal for the digital measurement signals S _MD, S (i), S (j) and adjusting the settings of the fast fourier transformer in some way, the fast fourier transformer can be used to extract the amplitude peak as well as the phase value as described below. Thus, when the total distance between blade 310A and blade 310B is considered 360 degrees, column #02 of table 6 may be considered to indicate the location of the detected event signature 205, and/or to indicate the physical location of the internal state indicating object 550 at location 213.75 degrees of the distance between blade 310A and blade 310B (see fig. 14A-14F together with column #02 of table 6).

When the phase angle parameter values FI, X1 have values exceeding 180 degrees, they may be converted into phase deviation values FI _DEV, wherein,

FI_DEV＝FI-360

In this case, when

FI (r) =360×760/1280= 213.75 degrees

The corresponding phase deviation value F _IDEV will be

FI _DEV = FI-360 = 213.75-360 = -146.25 degrees

This is shown in fig. 19A.

Referring to fig. 19A in conjunction with column #02 of table 6, the phase angle FI appears to represent the current operating point associated with the optimal efficiency point. In other words, the phase angle phi (r) =fi (r) may exhibit a predetermined value when the pump is operating under BEP flow conditions. When the phase angle Φ (r) =fi (r) deviates from a predetermined value, the deviation appears to indicate operation away from BEP flow conditions. In the example shown in fig. 19A, the predetermined value is zero (0) degrees, so the status indication object 550 _BEP, which indicates that the pump is operating under BEP flow conditions, exhibits a zero degree phase angle. Thus, the state indicating object 550 _BEP =550 (p+4) has a phase angle Φ (r) =fi (r) =Φ (p+4) =0 degrees.

When expressed as a portion of the distance between two adjacent blades 310, the physical location of the pulsation peak 205 may be referred to as information identifying the instantaneous operating point 205 (compare FIG. 2B). In other words, the present disclosure provides a way to identify information that identifies the instantaneous operating point 205 in the centrifugal pump. Thus, when expressed as a ratio of the distance between two adjacent blades 310 in the rotating impeller 20, the present disclosure provides a way to generate information indicative of the location of the detected event signature 205. Referring to fig. 15A and 16, the internal state indicating object 550 and/or the operating points 205, 550 may be represented as a phase angle F1 (r), as discussed below in connection with fig. 15 and 16. According to embodiments of the present disclosure, the internal status indication object 550 and/or the operation points 205, 550 may be presented in a percentage form (see column #02 of table 5 above). Further, according to embodiments of the present disclosure, the internal status indication object 550 and/or the operating points 205, 550 may be presented as a period of time, or as part of a period of time. As described above, in connection with table 5, since s=v _310T ×t, where s=distance, v _310T =tangential velocity of the blade tip, t is time, the time relationship can be directly converted into distance. It is noted herein that the tangential velocity v _310T of the blades depends on the angular velocity f _ROT of the impeller 20 and the radius R _MIC of the impeller 20 (see part II of fig. 14D).

Fig. 15A is a block diagram showing an example of the state parameter extractor 450. The state parameter extractor 450 of fig. 15A includes an impeller speed detector 500 that receives the number vibration signals S _MD, S (i) and the number position signal (Pi). Impeller speed detector 500 may also be referred to as a housing speed value generator 500. The impeller speed detector 500 may generate three signals S (j), P (j), and f _ROT (j) based on the received number of vibration signals S _MD, S (i), and the digital position signal (Pi). This may be achieved, for example, in the manner described above with respect to fig. 7-13. In this respect, it should be noted that three signals S (j), P (j) and f _ROT (j) may be transmitted simultaneously, i.e. all related to the same time slot j. In other words, three signals S (j), P (j), and f _ROT (j) may be provided in a synchronized manner. Providing signals such as S (j), P (j) and ROT (j) in a synchronized manner advantageously provides accurate information about the time relationship between the signal values of the respective signals. Thus, for example, the speed value f _ROT (j) transmitted by the housing speed value generator 500 indicates the instantaneous rotational speed of the impeller 20 at the time of detecting the amplitude value S (j).

It should be noted that the signals S (j) and P (j) transmitted by the housing speed value generator 500 are delayed relative to the signals S (i) and (Pi) received by the housing speed value generator 500. It should also be noted that signals S (j) and P (j) are equally delayed with respect to signals S (i) and (Pi), thus maintaining a temporal relationship between the two. In other words, signals S (j) and P (j) are synchronously delayed.

The impeller speed detector 500 may transmit a signal indicating whether the rotational speed is maintained constant for a sufficiently long time, in which case the signals S (j) and P (j) may be transmitted to the fast fourier transformer 510.

As described above, the variables O _MAX、B_n and L should be set such that the variable N _R is a positive integer. According to one example, the variables O _MAX、B_n and L described above may be set by the human-machine interfaces HCI 210, 210S (see, e.g., fig. 1 and/or fig. 5 and/or fig. 15A). As described above, the resulting integer X may be indicative of the number of revolutions of the centrifugal pump impeller 20 being monitored, during which the digital signals S (j) and P (j) are analyzed by the FFT 510. Accordingly, based on the settings of variables O _MAX、B_n and L, FFT 510 may generate a value N _R that indicates the analysis duration of the measurement session, and after the measurement session, FFT 510 transmits a set of state values Sp (r) and FI (r).

The concept "r" in the state values Sp (r) and FI (r) indicates a point in time. It should be noted that there may be a time delay from receiving the first pair of input signals S (j), P (j) at the input of the FFT 510 until transmitting the corresponding pair of state values Sp (r) and FI (r) from the FFT 510. The pair of state values Sp (r) and FI (r) may be based on a time sequence of the input signal pairs S (j), P (j). The duration of the time series of input signal pairs S (j), P (j) should comprise at least two consecutive position signal values P (j) =1 and corresponding vibration input signal values S (j).

As described below, the state values Sp (r) and FI (r) may also be referred to as C _L and Φl, respectively.

To convey an intuitive understanding of this signal processing, it may be helpful to consider the principle of superposition and repeated signals such as sinusoidal signals. The sinusoidal signal may exhibit amplitude values and phase values. In short, the principle of superposition is also known as superposition nature, indicating that for all linear systems, the net response caused by two or more stimuli at a given location and time is the sum of the responses caused by each stimulus individually.

Acoustic waves are one such stimulus. Also, vibration signals, such as vibration signals S _EA、S_MD, S (j), S (r) including signal signatures, are one such stimulus. In fact, the vibration signals S _EA、S_MD, S (j), S (r) comprising the signal signature S _FP may be considered as a sum of sinusoidal signals, each of which exhibits an amplitude value and a phase value. In this regard, reference is made to fourier series (see equation 5 below):

wherein,

N=0, the average value of the signal over a period of time (which may be, but need not be,

N=1 corresponds to the fundamental frequency of the signal F (t),

N=2 corresponds to the first harmonic portion of the signal F (t),

Ω=angular frequency, i.e. (2 x pi f _ROT),

F _ROT = housing speed in cycles per second,

T=time and,

Φ _n =phase angle of nth partials, and

C _n =amplitude of nth partials.

From the above fourier series, it follows that the time signal can be considered to consist of a superposition of a plurality of sinusoidal signals.

An overtone is any frequency greater than the fundamental frequency of the signal.

In the above example, it should be noted that the fundamental frequency will be f _ROT, i.e. the housing rotational speed, when the FFT 510 receives the marker signal value P (j) =1 only once per revolution of the impeller 20 (see for example fig. 14G together with fig. 5 and 15A).

Using fourier analysis models, the fundamental and overtones are together called partials (partials). A harmonic or more precisely a harmonic subtone is a subtone whose frequency is an integer multiple of the fundamental frequency (including the fundamental frequency, which itself is 1-fold).

Referring to fig. 15A and equation 5 above, fft 510 may transmit an amplitude value C _n (r) of n=l, i.e., C _L (r) =sp (r). FFT 510 may also transmit the phase angle of partials (n=l), i.e., Φ _L (r) =fi (r).

Consider now an example where the housing has ten (10) blades 310 when the housing is rotated at a speed of 10 revolutions per minute (rpm). A speed of 10rpm means one revolution every 6 seconds, i.e. f _ROT =0.1667 revolutions/second. The housing having ten blades (i.e., l=10) and operating at a speed of f _ROT =0.1667 revolutions per second results in a repetition frequency f _R of the signal associated with blade 310 of 1.667Hz, since repetition frequency f _R is a 10 th order frequency.

The position signals P (j), P (q) (see fig. 15A) may be used as reference signals for the digital measurement signals S (j), S (r). According to some embodiments, when the FFT analyzer is configured to receive the reference signal, i.e. the position signals P (j), P (q), once per revolution of the rotating impeller 20, the settings of the FFT analyzer should meet the following criteria:

The settable variables O _MAX and B _n are selected such that the mathematical expression Oi B _n/O_MAX becomes a positive integer. In other words: when the integer value Oi is set equal to L, then the settable variables O _MAX and B _n should be set to integer values, so that the variable N _R is a positive integer,

Wherein, N _R＝Oi*B_n/O_MAX is used for preparing the N-type nano-meter,

O _MAX is the maximum order; and

B _n is the number of bins in the spectrum generated by the FFT, and

Oi is the frequency of interest, expressed as an integer of order, and where f _ROT is the frequency of order 1, i.e., the fundamental frequency. In other words, the rotational speed f _ROT of the impeller 20 is the fundamental frequency, and L is the number of blades in the impeller 20.

Using the above setting, i.e., the integer value Oi is set equal to L, and referring to fig. 15A and equation 5 above, fft 510 may transmit an amplitude value C _n of n=l, i.e., C _L =sp (r). FFT 510 may also transmit the phase angle of the portion (n=l), i.e., Φ _L =fi (r). Thus, according to embodiments of the present disclosure, when the FFT 510 receives the position reference signals P (j), P (q) once per revolution of the rotating impeller 20, then the FFT analyzer may be configured to generate a peak amplitude value C _L of the signal, the repetition frequency f _R of which is an L-order frequency, where L is the number of equally positioned blades 310 in the rotating impeller 20.

Referring to the discussion above regarding equation 5 in this disclosure, the amplitude of a signal whose repetition frequency f _R is an L-order frequency may be referred to as C _n, where n=l, i.e., C _L. Referring to equation 5 and fig. 15A, an amplitude value C _L, denoted as Sp (r) in fig. 15A, may be transmitted as a peak amplitude value.

Referring again to equation 5 above, in the present disclosure, the phase angle value Φ _L of a signal whose repetition frequency f _R is an L-order frequency may be transmitted as a time indication value indicating the duration T _D1 between the detection of the occurrence of a frontal event signature and the occurrence of a rotational reference position of the rotating impeller.

Thus, according to embodiments of the present disclosure, when the FFT 510 receives the position reference signals P (j), P (q) once per revolution of the rotating impeller 20, then the FFT analyzer may be configured to generate the phase angle value Φ _L of the signal having the repetition frequency f _R as the L-order frequency, where L is the number of equally positioned blades 310 in the rotating impeller 20.

Thus, using the above setting, i.e., the integer value Oi is set equal to L, and referring to fig. 15A and equation 5 above, fft 510 can generate phase angle value Φ _L.

Referring to fig. 15A in conjunction with fig. 1, the state values Sp (r) =c _L and FI (r) =Φ _L may be transmitted to a human-machine interface (HCI) 210 for providing a visual indication of the analysis results. As described above, the displayed analysis results may include information indicating the internal state of the centrifugal pump process for enabling the operator 230 to control the centrifugal pump.

Fig. 16 is an illustration of an example of a visual indication of analysis results. According to one example, the visual indication of the analysis results may include providing a polar coordinate system 520. The polar coordinate system is a two-dimensional coordinate system in which each point on the plane is determined by a distance from the reference point 530 and an angle from the reference direction 540. The reference point 530 (similar to the origin of a cartesian coordinate system) is called the pole 530, and the ray from the pole in the reference direction is the polar axis. The distance to the pole is called radial coordinate, radial distance or simply radius, and the angle is called angular coordinate, polar angle or azimuth angle.

According to one example, the amplitude value Sp (r) is used as radius and the time relation values FI (r), Φ (r), T _D are used as angular coordinates.

In this way, by providing an internal status indicating object 550 on the display 210S, the internal status of the centrifugal pump being monitored can be displayed (fig. 16 in combination with fig. 1). Fig. 16 in combination with fig. 1 and 14 may be helpful in understanding the following examples.

Accordingly, one example relates to an electronic centrifugal pump monitoring system 150, 210S for generating and displaying information related to a pumping process in a centrifugal pump 10, the centrifugal pump 10 having an impeller 20, the housing rotating about a shaft 60 at a rotational speed f _ROT for urging material 30 out of a pump outlet 66. The example monitoring system 150 includes:

a computer-implemented method of representing the internal state of the pumping process in the centrifugal pump on a screen display 210S,

The method comprises the following steps:

displaying on the screen display 210S:

A polar coordinate system 520, the polar coordinate system 520 having

Reference point (O, 530), and

Reference direction (0 °,360 °,540 °); and

A first internal state indicating object (550, S _P1,T_D1) indicating the internal state of the pumping process, having a first radius (Sp (r), S _P1) from the reference point (O), and having a first polar angle (FI (r), Φ (r), T _D,T_D1) with respect to the reference direction (0, 360, 540),

The first radius (X2 (r), sp (r), S _P1) indicates the magnitude of the detected fluid pulsation, an

The first polar angle (X1 (r), F1 (r), Φ (r), TD 1) indicates the direction in which the current operating point 205 deviates from the current best efficiency operating point.

The first polar angle (X1 (r), F1 (r), Φ (r), T _D,T_D1) also indicates the location of the detected event signature 205 between two blades 310 in the rotating impeller 20.

As described above, the state parameter extractor 450 may be configured to generate successive pairs of state values Sp (r) and FI (r). The state parameter extractor 450 may also generate time derivative values for the state values Sp (r) and FI (r), respectively. This may be done, for example, by subtracting the most recent previous state value Sp (r-1) from the last state value Sp (r) divided by the duration between the two values. Similarly, the numerical derivative of the internal state value FI may be obtained. Thus, derivative values dpp (r) and dFI (r) may be generated. The derivative values dpp (r) and dFI (r) may be used to indicate movement of the first internal state indicating object (550, s _P1,T_D1).

Fig. 17 and 18 are illustrations of another example of visual indications of analysis results. Referring to fig. 17 and 18, the derivative values described above may be used to display an arrow 560 on the screen display 210S, the arrow 560 originating from the location of the first internal state indicating object (550, S _P1,T_D1) and having an extension that depends on the magnitude of the derivative values. In other words, the absence of arrow 560 means that the internal state is stable and does not change over a period of time. The arrow 560 in fig. 18 is longer than the arrow 560 in fig. 17, indicating that the internal state of the pump shown in fig. 18 changes faster than the internal state of the pump shown in fig. 17.

Fig. 19A is another example of a visual indication of the results of analysis of the internal state of the centrifugal pump 10. The visual indication analysis result example in fig. 19A is based on a polar coordinate system 520, as described above in fig. 16.

The most recent internal state indicating object 550 (r) indicates the current internal state of the pump 10. Another internal state indicating object 550 (r-1) indicates the most recent internal state prior to the pump 10.

The internal state indicating object 550 (1) indicates the internal state of the pump 10 when the flow rate is extremely low (well below BEP). It is noted that the flow rate will initially be very low when the centrifugal pump is started.

Referring to fig. 19A, as the flow approaches the BEP flow, the position of the internal state indicating object 550 (1) and the polar reference point (O, 530) at the origin gradually approaches, indicating that the flow gradually increases.

In this way, the current internal state of the centrifugal pump 20 may be represented and visualized, thereby allowing the operator 230 of the pump system 5 to intuitively understand its state. It is noted that the display of a single internal state indicating object 550, as shown in fig. 16, represents the current internal state or the most recently detected internal state of the pump 10, whereas the time course of the internal state indicating object from the initial state 550 (1) through intermediate states (e.g., 550 (p), 550 (p+1), and 550 (r-1)) to 550 (r), as shown in fig. 19A, displays a history representing the current internal state 550 (r) of the pump 10 as well as a plurality of early internal states. In FIG. 19A, the most recent early state is referred to as 550 (r-1). Some other early internal states shown in fig. 19A are then displayed as internal state indication objects 550 (p+4), 550 (p+1), 550 (p), and 550 (1). The internal status indicating object 550 (p+4) is shown very close to the origin, illustrating the operation of the pump at or very close to the optimal efficiency operating point 550 _BEP.

Referring to fig. 19A in conjunction with fig. 16 and the corresponding description above, it may be noted that fig. 19A clearly illustrates the advantages and useful information provided by data generated in accordance with the methods disclosed in the present disclosure (e.g., internal status indicating object 550). It should be noted that the internal state indicating object 550 represents the internal state of the pumping process.

Specifically, it is noted that polar angles X1 (r), FI (r), Φ (r), T _D、T_D1 represent the direction of departure of current operating point 205 from the current best efficiency operating point.

In this regard, it should be noted that when a pump is connected to fluid system 52, its optimal efficiency operating point may vary due to changes in back pressure of fluid system 52, etc. Data generated according to the methods disclosed in the present disclosure, e.g., polar angles X1 (r), FI (r), will advantageously provide very accurate information about the current operating point, and when the current operating point 205, 550 deviates from the optimal efficiency operating point, polar angles X1 (r), FI (r) will provide information about the direction of deviation of the current operating point 205, 550 from the current optimal efficiency operating point.

In summary, useful information provided by data generated in accordance with the methods disclosed in the present disclosure includes amplitude values Sp (r), S _p1, which represent the fluid pulsations associated with pump 10 detected during operation. Thus, the amplitude values Sp (r), S _p1 indicate the internal state of the pumping process, i.e. the current fluid pulsation amplitude.

Further, useful information provided by data generated according to the methods disclosed in the present disclosure includes polar values X1 (r), FI (r), which may indicate a current departure from the current BEP.

From such measurements made on a plurality of centrifugal pumps 10 coupled to the piping system 40 and the fluid material consumers 50, the detected polar angles (X1 (r), FI (r), Φ (r), T _D、T_D1) appear to always have a phase shift of about 180 degrees, or vice versa, when the internal state indicates that the object 550 and/or the operating points 205, 550 are shifted from an operating point below BEP to an operating point above BEP. Further, when the pump 10 is operating at BEP flow, the amplitudes X2 (r) Sp (r), S _P1 of the detected fluid pulsations are at a minimum, as discussed elsewhere in this disclosure (e.g., fig. 14A).

Thus, the radius (X2 (r) Sp (r), S _P1) indicates the amplitude of the detected fluid pulsation, an

The first polar angle (X1 (r), FI (r), Φ (r), T _D、T_D1) exhibits a phase shift of about 180 degrees when the internal state indicates that the object 550 and/or the operating point 205, 550 changes from below to above the BEP, or vice versa. Thus, it seems desirable to control the pump such that the current internal state 550 (r) moves toward the reference point (O, 530) in the polar graph, or to a position as close as possible to the reference point (O, 530).

Furthermore, for any pump/system combination, controlling the pump to have the internal status indicator 550 as close as possible to the reference point (O, 530) in the polar plot appears to operate at optimal efficiency and/or minimal pulsation.

Thus, it can be concluded that providing the status indication values X2 (r), sp (r), and X1 (r), FI (r) can improve the control capability of the fluid system. In particular, the methods and illustrations disclosed herein provide very clear and interpretable measurements, thereby greatly improving the operation of the pump 10 and the fluid systems 5, 40, 50. As described above, the parameter value X1 may indicate a direction of departure of the current operating point 205 from the current best efficiency operating point (BEP). In this regard, it should be noted that the flow-pressure characteristics of the fluid system may change during operation, and therefore the BEP may also change (see fig. 2B). Accordingly, the methods and illustrations disclosed herein can provide a way to detect a current operating point 205 in relation to a current BEP.

From such measurements made on some centrifugal pumps 10 coupled to the plumbing 40 and the fluid material consumer 50, another observation is that a single pump/system combination appears to create a unique pattern of movement of its internal state indicating object 550.

Fig. 19B, 19C and 19D illustrate a number of internal status indicating objects associated with the pump 10, such as status indicating objects 550 ₁、550₂ and 550 ₃, for example, the pump 10 operates below BEP and, as shown by status indicating objects 550 ₄、550₅ and 550 ₆, operates in conditions where flow exceeds BEP. The cloud black dot block is an internal status indication object 550 collected over a long period of time and under various operating conditions.

Fig. 19E is a schematic diagram of first time graphs 570, 570A of the amplitude of the detected fluid pressure pulsations P _FP in the centrifugal pump 10 having four impeller blades 310 (refer to fig. 19E in conjunction with fig. 2A). The time chart in fig. 19E is a polar graph, i.e., moving in a clockwise direction, 360 degrees corresponding to one rotation of the impeller 20. The radius at a point in the graph depends on the detected amplitude of the detected fluid pressure pulse P _FP.

The amplitude time graphs 570, 570A associated with the four impeller blades in fig. 19E show four highest amplitude peaks and four lowest amplitude peaks. It should be noted that the angular position of the amplitude peak varies according to the current operation state OP of the pump (refer to fig. 14A to 14F and the related discussion of fig. 16 to 19B). Thus, in a pump having L impeller blades, the amplitude time plot 570 shows the L highest amplitude peaks and the L lowest amplitude peaks, where L is the number of blades on the impeller in the pump 10. Thus, the amplitude time plot 570 appears to show one signal signature per blade 310. A single signal signature appears to exhibit one highest amplitude peak and one lowest amplitude peak.

Fig. 19F is another schematic diagram of a second time chart 570, 570B of the amplitude of the detected fluid pressure pulsation P _FP in the same centrifugal pump 10 as described in fig. 19E. The second time map 570, 570B is recorded at another time than the first time map 570, 570A of fig. 19E.

The inventors concluded that when the shape of the amplitude timing diagram 570 was studied over a long period of time and under various operating conditions, the shape change of the amplitude timing diagram 570 was dependent on the internal state X of the centrifugal pump 10.

The inventors concluded that the shape of the amplitude time plot 570 appears to be indicative of the internal state X of the pump 10. During normal operation, as shown in fig. 19E, the L signal signatures 572 ₁、572₂、572₃、572₄、572_L appear to exhibit a uniform shape or a substantially uniform shape.

However, as shown in fig. 19F, the shape of the single signal signature 572B ₃ may deviate from the shape of the other signal signatures.

The inventors concluded that the shape of the amplitude time plot 570B appears to indicate that the physical characteristics associated with at least one blade 310 or the physical characteristics associated with at least one impeller channel 320 deviate from normal. In other words, when the shape of a single signal signature deviates from the shape of other signal signatures, the deviation appears to indicate that the physical characteristics associated with at least one blade 310 or the physical characteristics associated with at least one impeller channel 320 deviate from normal. It is believed that such a deviation may indicate that the surface of the vane 310 is damaged, or that such a deviation may indicate that the impeller channel 320 is partially blocked by particles trapped in the impeller channel 320.

Examples of variable speed phase State parameter extractor

As described above, if the centrifugal pump impeller 20 rotates at the variable rotation speed f _ROT, analysis of the measurement data is more complicated. In fact, it appears that even very small changes in the rotational speed of the pump housing can have a very detrimental effect on the detected signal quality in terms of tailing effects. Thus, very accurate detection of the rotational speed f _ROT of the pump impeller 20 appears to be critical, and accurate compensation for any speed variations appears to be critical.

Referring to fig. 15A, the impeller speed detector 500 may transmit a signal indicating when the rotational speed is changing, as discussed in connection with fig. 9. Referring again to fig. 15A, signals S (j) and P (j) and a velocity value f _ROT (j) may be transmitted to the velocity variation compensation decimator 470. The speed change compensation decimator 470 may also be referred to as a fraction decimator. The decimator 470 is configured to decimate the digital measurement signal S _MD based on the received speed value f _ROT (j). According to one example, the decimator 470 is configured to decimate the digital measurement signal S _MD by a variable decimation factor D, which is adjusted during the measurement session based on the variable speed value f _ROT (j). Thus, the compensation extractor 470 is configured to generate the extracted number of vibration signals S _MDR such that the number of sample values per rotation of the rotating impeller is kept at a constant value, or kept at a substantially constant value, when the rotational speed varies. According to some embodiments, the number of sample values per revolution of the rotating impeller is considered to be a substantially constant value when the number of sample values per revolution of the rotating impeller varies by less than 5%, according to some embodiments. According to a preferred embodiment, the number of sample values per revolution of the rotating impeller is considered to be a substantially constant value when the number of sample values per revolution varies by less than 1%. According to a most preferred embodiment, the number of sample values per revolution of the rotating impeller is considered to be a substantially constant value when the number of sample values per revolution of the rotating impeller varies by less than 0.2%.

Thus, the embodiment of fig. 15A includes a fraction decimator 470 for decimating the sample rate by a decimation factor d=n/U, where U and N are both positive integers. Thus, the fraction decimator 470 advantageously causes the sampling rate to decimate the fraction. Thus, the speed change compensation decimator 470 is operable to decimate the signals S (j) and P (j) and f _ROT (j) by a fraction d=n/U. According to one embodiment, the values of U and N may be selected in the range from 2 to 2000. According to one embodiment, the values of U and N may be selected in the range from 500 to 1500. According to yet another embodiment, the values of U and N may be selected in the range from 900 to 1100. In this context, it should be noted that the term "score" is used in the following context: score (from latin fractus, "break") represents a portion of the whole or, more generally, any number of equal portions. In a positive common score, both the numerator and denominator are natural numbers. The numerator indicates some equal parts and the denominator indicates how many parts make up a unit or whole. The common score is a number representing a rational number. The same number may also be expressed in decimal, percent, or negative index. For example, 0.01, 1% and 10 ^-2 are all equal to a fraction of 1/100. Thus, the score d=n/U can be considered as an inverse score.

Thus, the resulting signal S _MDR transmitted by the fraction decimator 470 has a sample rate:

f_SR＝f_S/D＝f_S*U/N

Where f _S is the sample rate of the signal S _MD received by the fraction decimator 470.

The fractional value U/N depends on the rate control signal received on the input port 490. The rate control signal may be a signal indicative of the rotational speed f _ROT of the rotating impeller.

The variable decimator value D of the decimator may be set to d=f _S/f_SR, where f _S is the initial sample rate of the a/D converter and f _SR is a set point value that indicates the number of samples per revolution in the number of decimated vibration signal S _MDR. For example, when there are twelve (12) blades to be monitored in the impeller, the setpoint value f _SR may be set to 768 samples per revolution, i.e., the number of samples per revolution is set to fsr in the extracted number of vibration signals S _MDR. The compensation decimators 470, 470B are configured to generate the position signal P (q) at regular intervals of the decimated number of vibration signals S _MDR, the regular intervals being dependent on the setpoint value f _SR. For example, when f _SR is set to 768 samples per revolution, the position signal P (q) may be transmitted once per 768 samples of the extracted vibration signal S (q). In this way, the position signal P (q) represents a static angular position in a manner similar to the position signal value P _S discussed above.

According to another example, the compensation decimators 470, 470B are configured to generate the position signal P (q) once every L divided by the decimated vibration signal S (q) samples of f _SR. Accordingly, the position signal P (q) may be transmitted within a fixed interval of the decimated digital vibration signal S _MDR, which is L/f _SR. In this way, the position signal P (q) represents L static angular positions in a manner similar to the virtual position signal value P _C discussed above.

Thus, the sampling frequency f _SR (also referred to as f _SR2) of the output data value R (q) is lower than the input sampling frequency f _S by a factor D. The factor D may be set to any number greater than 1 and may be a score, as discussed elsewhere in this disclosure. According to a preferred embodiment, the factor D may be set to a value between 1.0 and 20.0. In a preferred embodiment, the factor D is a fraction that can be set to a value between about 1.3 and about 3.0. The factor D may be obtained by setting the integers U and N to appropriate values. Factor D is equal to N divided by U:

D＝N/U

According to one embodiment, the integers U and N may be set to large integers so that the factor d=n/U can follow the speed variation with minimal error. Selecting the variables U and N to be integers greater than 1000 is advantageous for high accuracy in adjusting the output sampling frequency to track rotational speed variations of the impeller 20. Thus, for example, setting N to 500 and U to 1001, d=2.002.

The variable D is set to a suitable value at the beginning of the measurement and this value is associated with the particular rotational speed of the rotating component to be monitored. Thereafter, during the measurement session, the fraction value D is automatically adjusted in response to the rotational speed of the rotating component to be monitored, such that the output signal S _MDR provides a substantially constant number of sample values per revolution of the rotating impeller.

Fig. 20 is a block diagram of an example of a compensation decimator 470. An example of this compensation decimator is shown as 470B.

The compensation extractor 470B may comprise a memory 604 adapted to receive and store the data value S (j) and information indicative of the respective rotational speed f _ROT of the rotary pump housing being monitored. Thus, the memory 604 may store each data value S (j) such that it is associated with a value indicative of the rotational speed f _ROT (j) of the pump housing that is monitored upon detection of the value of the sensor signal S _EA corresponding to the data value S (j). The provision of the data value S (j) associated with the corresponding rotational speed value f _ROT (j) is described with reference to fig. 7-13 above.

The compensation decimator 470B receives the signal S _MD with the sampling frequency f _SR1 as a sequence of data values S (j) and transmits the output signal S _MDR with the reduced sampling frequency f _SR on its output 590 as another sequence of data values R (q).

The compensation extractor 470B may comprise a memory 604 adapted to receive and store the data value S (j) and information indicative of the respective rotational speed f _ROT of the rotary pump housing being monitored. The memory 604 may store data values S (j) in blocks such that each block is associated with a value indicative of the relative rotational speed of the pump housing being monitored, as described below in connection with fig. 21.

The compensation decimator 470B may also include a compensation decimation variable generator 606 adapted to generate a compensation value D. The compensation value D may be a floating point number. Thus, in response to the received speed value f _ROT, the offset may be controlled to a floating point value such that the floating point value indicates the speed value f _ROT with a particular inaccuracy. As described above, the inaccuracy of a floating point value, when implemented by a properly programmed DSP, may depend on the ability of the DSP to generate the floating point value.

In addition, the compensation decimator 470B may also include a FIR filter 608. In this regard, the acronym FIR stands for finite impulse response. FIR filter 608 is a low-pass FIR filter with a specific low-pass cut-off frequency, suitable for decimation by a factor D _MAX. Factor D _MAX may be set to a suitable value, for example, 20.000. In addition, the compensation extractor 470B may also include a filter parameter generator 610.

The operation of the compensation extractor 470B is described below with reference to fig. 21 and 22.

Fig. 21 is a flow chart illustrating an embodiment of a method of operating the compensation sampler 470B of fig. 20.

In a first step S2000, the rotational speed f _ROT of the pump housing to be monitored is recorded in the memory 604 (fig. 20 and 21), and this can be done at approximately the same time that the vibration measurement is started. According to another example, the rotational speed of the pump housing to be monitored is measured over a period of time. The highest detected speed f _ROTmax and the lowest detected speed f _ROTmin may be recorded in, for example, the memory 604 (fig. 20 and 21).

In step S2010, the recorded speed value is analyzed in order to determine whether the rotational speed has changed.

In step S2020, the user interface 210, 210S displays the recorded speed value f _RO or the speed value f _ROTmin、f_ROTmax and requests the user to input a desired sequence value Oi. As described above, the pump housing rotation frequency f _ROT is generally referred to as "1 st order". An interesting signal may occur ten times (10 th order) per revolution of the pump housing. Furthermore, it may be interesting to analyze overtones of some signals, and thus it may be interesting to measure signals up to 100 th order, 500 th order and even higher. Thus, the user may input the order Oi using the user interfaces 210, 210S.

In step S2030, an appropriate output sampling rate f _SR is determined. In this disclosure, the output sampling rate f _SR may also be referred to as f _SR2. According to one embodiment, the output sampling rate f _SR is set to f _SR＝C*Oi*f_ROTmin,

Wherein,

C is a constant having a value greater than 2.0,

Oi is the number indicating the relationship between the rotational speed of the pump housing being monitored and the repetition frequency of the signal to be analyzed.

F _ROTmin is the minimum rotational speed of the monitored pump housing to be expected during an upcoming measurement session. According to one embodiment, the value f _ROTmin is the lowest rotational speed detected in step S2020, as described above.

The constant C may be selected to be a value of 2.00 (two) or more in consideration of the sampling theorem. According to embodiments of the present disclosure, the constant C may be preset to a value between 2.40 and 2.70.

According to one embodiment, the factor C is advantageously chosen such that 100 x C/2 represents an integer. According to one embodiment, the factor C may be set to 2.56. C is chosen to be 2.56 such that 100×c=256=2 to the power of 8.

In step S2050, the compensation extraction variable value D is determined. When the rotational speed of the monitored pump housing changes, the compensation extraction variable value D will change in accordance with the instantaneous detected speed value.

According to one embodiment, the maximum compensation decimation variable value D _MAX is set to the value of D _MAX＝f_ROTmax/f_ROTmin and the minimum compensation decimation variable value D _MIN is set to 1.0. Thereafter, an instantaneous real-time measurement is made of the actual speed value f _ROT, and an instantaneous compensation value D is set accordingly.

F _ROT is a value indicating the measured rotational speed of the rotary pump housing to be monitored.

In step S2060, actual measurement is started, and the desired total duration of measurement may be determined. The total duration of the measurement may be determined based on the desired number of revolutions N _R of the pump housing being monitored.

When the measurement starts, the digital signal S _MD is transmitted to the input 480 of the compensation decimator. Hereinafter, the signal S _MD is discussed in terms of a signal having a sample value S (j), where j is an integer.

In step S2070, data values S (j) are recorded in the memory 604, and each vibration data value S (j) is associated with the rotation speed value f _ROT (j).

In a subsequent step S2080, the recorded rotational speed value is analyzed, and the recorded data value S (j) is divided into data blocks according to the rotational speed value. In this way, a plurality of blocks of data value blocks S (j) may be generated, each data value block S (j) being associated with a rotational speed value. The rotational speed value indicates the rotational speed of the pump housing being monitored at the time of recording the specific block data value S (j). The individual data blocks may have mutually different sizes, i.e. the individual data blocks may hold mutually different numbers of data values S (j).

For example, if the monitored rotary pump housing rotates first at a first speed f _ROT1 during a first period of time and then changes speed during a second, shorter period of time, rotating at a second speed f _ROT2, the recorded data value S (j) may be divided into two data blocks, the first block data value being associated with a first speed value f _ROT1 and the second data block value being associated with a second speed value f _ROT2. In this case, the second data block will contain fewer data values than the first data block because the second time period is shorter.

According to one embodiment, when all recorded data values S (j) have been divided into blocks and all blocks have been associated with a rotational speed value, the method continues with step S2090.

In step S2090, the first block data value S (j) is selected, and the compensation extraction value D corresponding to the relevant rotation speed value f _ROT is determined. The compensation decimation value D is associated with a first block data value S (j). According to one embodiment, when all blocks have been associated with a corresponding compensation extraction value D, the method continues with step S2100. Therefore, the value of the compensation extraction value D is adjusted according to the speed f _ROT.

In step S2100, a block of data values S (j) and associated compensation extraction values D are selected, as described in step S2090 above.

In step S2110, a block of output values R is generated in response to the selected block of input values S and the associated compensation decimation value D. This may be accomplished as described with reference to fig. 22.

In step S2120, it is checked whether there are any remaining input data values to be processed. If there is another block of input data values to process, step S2100 is repeated. If there are no remaining blocks of input data values to process, the measurement session is complete.

Fig. 22A, 22B and 22C illustrate a flowchart of an embodiment of a method of operating the compensation sampler 470B of fig. 20.

In step S2200, a block of input data values S (j) and an associated specific compensation decimation value D are received. According to one embodiment, the received data is as described above in step S2100 of fig. 21. The received input data values S (j) in the block S of input data values are all associated with a particular compensation decimation value D.

In steps S2210 to S2390, the FIR filter 608 (see fig. 20) is adapted to the specific compensation extraction value D received in step S2200 and generates a set of corresponding output signal values R (q). This will be described in more detail below.

In step S2210, a filter setting appropriate for the particular compensation extraction value D is selected. As mentioned above in connection with fig. 20, FIR filter 608 is a low-pass FIR filter with a certain low-pass cut-off frequency suitable for decimation by a factor D _MAX. The factor D _MAX may be set to a suitable value, for example, 20.

The filter ratio F _R is set to a value that depends on the factor D _MAX and the particular compensation extraction value D received in step S2200. Step S2210 may be performed by the filter parameter generator 610 (fig. 20).

In step S2220, the start position value x is selected in the received input data block S (j). It should be noted that the starting position value x need not be an integer. FIR filter 608 has a length F _LENGTH and the starting position value x will then be selected based on the filter length F _LENGTH and the filter ratio F _R. The filter ratio F _R is set as in step S2210 above. According to one embodiment, the starting position value x may be set to x: =f _LENGTH/F_R.

In step S2230, a filter SUM value SUM is prepared and set to an initial value, for example SUM: =0.0.

In step S2240, a position j adjacent to and before the position x in the received input data is selected. The position j may be selected as an integer part of x.

In step S2250, a location Fpos in the FIR filter is selected, which corresponds to the selected location j in the received input data. Position Fpos may be a compensation number. Relative to the intermediate position of the filter, the filter position Fpos may be determined as:

Fpos＝[(x-j)*F_R]

Wherein F _R is the filtration ratio.

In step S2260, it is checked whether the determined filter position value Fpos is outside the allowable limit value, i.e. points to a position outside the filter. If this occurs, the following step S2300 is performed. Otherwise, step S2270 is performed.

In step S2270, a filter value is calculated by interpolation. It should be noted that adjacent filter coefficient values in the FIR low pass filter typically have similar values. Thus, the interpolation will advantageously be accurate. First, an integer position value IFpos is calculated:

IFpos =integer part of Fpos

The filter value Fval at location Fpos will be:

Fval＝A(IFpos)+[A(IFpos+1)-A(IFpos)]*[Fpos-IFpos]

Where A (IFpos) and A (IFpos +1) are values in the reference filter and filter position Fpos is a position between these values.

In step S2280, in response to the signal position j, an update of the filter SUM value SUM is calculated:

SUM:＝SUM+Fval*S(j)

In step S2290, move to another signal position:

set j: =j-1

Thereafter, the flow goes to step S2250.

In step 2300, a position j adjacent to and subsequent to position x in the received input data is selected. This position j may be selected as the integer part of x plus 1 (one), i.e. j: =1+x integer part.

In step S2310, a location corresponding to the selected location j in the received input data is selected in the FIR filter. Position Fpos may be a compensation number. Relative to the intermediate position of the filter, the filter position Fpos may be determined as:

Fpos＝[(j-x)*F_R]

Wherein F _R is the filtration ratio.

In step S2320, it is checked whether the determined filter position value Fpos is outside the allowable limit value, i.e. points to a position outside the filter. If this occurs, the following step S2360 is performed. Otherwise, step S2330 is performed.

In step S2330, a filter value is calculated by interpolation. It should be noted that adjacent filter coefficient values in the FIR low pass filter typically have similar values. Thus, the interpolation will advantageously be accurate. First, an integer position value IFpos is calculated:

IFpos =integer part of Fpos

The filtered value for location Fpos is:

Fval(Fpos)＝A(IFpos)+[A(IFpos+1)-A(IFpos)]*[Fpos-IFpos]

In step S2340, in response to the signal position j, an update of the filter SUM value SUM is calculated:

SUM:＝SUM+Fval*S(j)

in step S2350, move to another signal position:

Set j: =j+1

Thereafter, the process proceeds to step S2310.

In step S2360, the output data value R (j) is transmitted. The output data values R (j) may be transferred to the memory such that successive output data values are stored in successive memory locations. The value of the output data value R (j) is:

R(j):＝SUM

In step S2370, the position value x is updated:

x:＝x+D

In step S2380, the position value j is updated

j:＝j+1

In step S2390, it is checked whether a desired number of output data values have been generated. If the desired number of output data values is not generated, the process goes to step S2230. If the desired number of output data values has been generated, then go to step S2120 in the method described in relation to FIG. 21.

In practice, step S2390 is designed to ensure that an output signal value R (q) corresponding to the block of input data values S received in step S2200 is generated, and when an output signal value R corresponding to the input data value S has been generated, step S2120 in fig. 21 should be performed.

The method described with reference to fig. 22 may be implemented as a computer program subroutine, and steps S2100 and S2110 may be implemented as a main program.

Fig. 23 is another example block diagram of a state parameter extractor 450 (referred to as state parameter extractor 450C). As described below, the state parameter extractor 450C may include a vibration event signature detector, a position signal value detector, and a relationship generator. As described below, the vibration event signature detector may be implemented by a peak detector.

Accordingly, fig. 23 is a block diagram showing an example of a part of the analysis device 150. In the example of fig. 23, some of the functional blocks represent hardware, and some of the functional blocks may represent either hardware or functionality implemented by running program code on data processing device 350, as described in fig. 3 and 4. The apparatus 150 in fig. 5 illustrates one example of the analysis apparatus 150 illustrated in fig. 1 and/or 3. The parameter extractor 450 in the apparatus 150 of fig. 5 may be constituted by the state parameter extractor 450C of fig. 23.

According to various aspects of the solutions disclosed herein, the reference position signal values Ep, 1C, P _S、P_C are generated at L predetermined rotational positions of the rotatable impeller 20, which follow a pattern reflecting the angular positions of the L blades 310 in the impeller 20. Providing such reference position signal values Ep, 1C, and providing vibration event signature detection in the manner disclosed herein, it is possible to generate data indicative of the relationship of the current operating point 205, 550 to the optimal efficiency operating point in an advantageously accurate manner.

While the blades 310 have been illustrated as being positioned in an equidistant pattern (i.e., evenly distributed in the impeller 20), the solution may be used for other angular position patterns of the L-shaped blades 310 in the impeller 20. When using other angular position patterns of the L-shaped blades 310 in the impeller, it is important that the reference position signal values Ep, 1c are generated at L predetermined rotational positions of the impeller 20, which follow a pattern reflecting the angular position of the L-shaped blades 310 in the impeller 20.

Referring to fig. 5, the a/D converter 330 may be configured to convey a sequence of paired vibration measurement values S (i) associated with the respective position signal values P (i) to the state parameter extractor 450. The state parameter extractor 450 is configured to generate one or more parameter values X1, X2, X3, X.

The state parameter extractor 450 may be as shown in fig. 15A. In addition, the state parameter extractor 450 may also be as shown in fig. 23.

The state parameter extractor 450C of fig. 23 is adapted to receive a series of measured values S (i) and a series of position signals P (i) and the time relation between them.

Thus, a single vibration measurement value S (i) is associated with a corresponding position value P (i). Such signal pairs S (i) and P (i) are supplied to memory 970. Referring to fig. 23, state parameter extractor 450C includes memory 970. Memory 970 may receive data in the form of signal pairs S (i) and P (i) to analyze the temporal relationship between event occurrences in the received signals. Columns #2 and #3 in table 3 exemplify the data collected in memory 970 when the position signals 1, 1C are provided six times per revolution during one revolution of the impeller, since there are l=6 blades 310 in the impeller 20. Tables 4 and 5 provide more detailed information of example signal values for the first 1280 slots in table 3.

The position signals 1, 1C may be generated by the physical marking device 180, or/and some of the position signals 1C may be virtual position signals. The time series of position signal sample values P (i), P (j), P (q)) should be provided in a pattern of occurrence reflecting the angular position of the blades 310 in the impeller 20.

For example, when there are six (l=6) equidistant blades 310 in the impeller 20, the angular distance between any two adjacent blades 310 is 60 degrees. This is because 360 degrees is a complete revolution, and when l=6, the angular distance between any two adjacent vanes is 360/l=360/6=60. Thus, as shown in table 3, the corresponding time series of position signal sample values P (i) representing one revolution of the impeller 20 should comprise six (l=6) position signal values 1, 1C with corresponding occurrence patterns.

The state parameter extractor 450C also includes a position signal value detector 980 and a vibration event signature detector 990. The vibration event signature detector 990 may be configured to detect vibration signal events, such as amplitude peaks in the received sequence of measurement values S (i).

The output of the position signal value detector 980 is coupled to the START/STOP input 995 of the reference signal time counter 1010 and the START input 1015 of the event signature time counter 1020. The output of the position signal value detector 980 may also be coupled to a START/STOP input 1023 of the vibration event signature detector 990 for indicating the START and STOP of the duration to be analyzed. When a position signal value of 1, 1C is detected, the detector 990 sends a signal on its output.

The vibration event signature detector 990 is configured to analyze all sample values S (i) between two consecutive position signal values 1, 1C to detect the highest peak amplitude value Sp thereof. The vibration event signature detector 990 has a first output 1021 coupled to a STOP input 1025 of the event signature time counter 1020.

The reference signal time counter 1010 is configured to calculate the duration between two consecutive position signal values 1, 1C, thereby generating a first reference duration value T _REF1 on the output 1030. To achieve this, for example, the reference signal time counter 1010 may be a clock timer that counts the length of time between two consecutive position signal values 1, 1C. In addition, the reference signal time counter 1010 may count the number of slots between two consecutive position signal values 1, 1C (see table 3 column # 01).

The event signature time counter 1020 is configured to calculate a duration from the occurrence of the position signal value 1, 1C to the occurrence of the vibration signal event (e.g., amplitude peak). This can be achieved by:

the event signature time counter 1020 STARTs counting when the START (START) input 1015 receives information that the position signal value detector 980 detects that a position signal value 1, 1C is occurring.

The event signature time counter 1020 STOPs counting when the STOP (STOP) input 1025 receives information that the vibration event signature detector 990 detects a vibration signal event (e.g., amplitude peak) in the received sequence of measured values S (i).

In this way, the event signature time counter 1020 may be configured to calculate the length of time from the occurrence of the position signal value 1, 1C to the occurrence of the amplitude peak. The length of time from the occurrence of the position signal value 1, 1C to the occurrence of the amplitude peak is referred to herein as the second reference duration value T _REF2. The second reference duration value T _REF2 may be output on output 1040.

The output 1040 is coupled to an input of the relation generator 1050 for providing the second reference duration value T _REF2 to the relation generator 1050.

The relation generator 1050 also has an input coupled to receive the first reference duration value T _REF1 from the output 1030 of the reference signal time counter 1010. The relation generator 1050 is configured to generate a relation value X1 from the received second reference duration value T _REF2 and the received first reference duration value T _REF1. The relationship X1 may also be referred to as R _T(r);T_D; FI (r). An L number of relationships X1 may be generated per revolution of the impeller 20. In addition, the L relationship values X1 produced per revolution of the impeller may be averaged to produce one value X1 (r) per revolution of the impeller 20. In this way, the state parameter extractor 450C may be configured to provide an updated value X1 (r) once per revolution.

For clarity, an example of the relationship value X1 is generated in the following manner: referring to column #03 in table 4 in conjunction with fig. 23: the vibration sample value S (i) is analyzed by the vibration event signature detector 990 to detect the vibration signal signature S _FP.

The vibration signal signature S _FP may be represented as a peak amplitude sample value Sp. Referring to table 6, the highest vibration sample local oscillation amplitude S (i) can be detected by peak analysis. In the illustrated example, the vibration-like local oscillation amplitude S (i=760) is detected to maintain the highest peak Sp.

Upon detection of the peak Sp located in the time slot 760, a time relationship X1 may be established.

The reference position is represented by the data of table 6 column # 02. The reference position is represented by the values of phase angles FI, X1. As described in the disclosure above in connection with table 6, in column #02 of table 6, two position signal sample values P (i), carrying position signal values 1, 1C, are denoted as phase angles 0 degrees and 360 degrees, respectively.

Thus, column #02 of Table 6, in combination with column #03, may be considered to represent the location of the detected event signature 205, and/or to represent the physical location of the internal status indicating object 550, at an angular position of 213.75 degrees (see column #03 of Table 6 with FIG. 16 and/or FIG. 19A). When the optimal operating point is at the zero degree angular position, as shown in fig. 19A, an angular position of 213.75 degrees will represent a 213.75 degrees deviation from the optimal operating point.

However, as discussed elsewhere in this disclosure, when the operating point 550, 205 changes from below BEP to above BEP, the phase angle FI, X1 appears to be approximately 180 degrees phase shifted, or vice versa. Therefore, it seems to be meaningful to analyze the deviation of the current phase angle parameter values FI, X1 from the reference directions (represented as zero (0) degrees and 360 degrees in fig. 16, 17, 18, and 19A).

Any phase angle parameter value FI, X1 having a value exceeding 180 degrees can thus be converted into a phase deviation value FI _DEV, wherein,

FI_DEV＝FI-360

Thus, when the phase angle parameter values FI, X1 are 213.75 degrees (refer to table 6 column #03 in conjunction with fig. 16 and/or 19A), then the corresponding phase offset values FI _DEV are:

FI _DEV = FI-360 = 213.75-360 = -146.25 degrees

Thus, referring to fig. 19A and column #02 of table 6, the phase angle FI appears to indicate the relationship of the current operating point to the optimal efficiency point. In other words, the phase angle Φ (r) =fi (r) may exhibit a predetermined value when the pump is operated at the Best Efficiency Point (BEP) flow condition. When the phase angle Φ (r) =fi (r) deviates from a predetermined value, the deviation appears to indicate a deviation in operation from BEP flow conditions. In the example shown in fig. 19A, the predetermined value is zero (0) degrees, so the status indication object 550 _BEP, which indicates that the pump is operating under BEP flow conditions, displays a zero degree phase angle. Thus, the state indicating object related to the best efficiency operation 550 _BEP =550 (p+4) may have a phase angle Φ (r) =fi (r) =Φ (p+4) =0 degrees.

Thus, a deviation value indicating that the current operating point deviates from the BEP may be obtained by:

Calculating a total number of samples (N _B-N₀＝N_B-0＝N_B =1280) from a first reference signal occurring in sample number N ₀ =0 to a second reference signal occurring in sample number N _B =1280, and

Calculating another number of samples (N _P-N₀＝N_P-0＝N_P) from the first reference signal occurring in the number of samples N ₀ = 0 to the peak amplitude value Sp occurring in the number of samples N _P, and

The first time relation (X1, R _T(r);T_D; FI (R)) is generated from the further number N _P and the total number N _B. This can be summarized as:

X1(r)＝FI(r)＝R_T(r)＝R_T(760)＝(N_P-N₀)/(N_B-N₀)＝(760-0)/(1280-0)

When the above relation is expressed as phase angle FI, then:

FI (r) =360×760/1280= 213.75 degrees

Thus, the information indicating the instantaneous operation point X1 or identifying the instantaneous operation point X1 can be generated by:

calculating a total number of samples (N _B) from the first reference signal to the second reference signal, and

Calculating another number of samples (N _P) of the peak amplitude value Sp occurring from the first reference signal to the number of samples N _P, and

The first temporal relationship (X1, R _T(r);T_D; FI (R)) is generated from the relationship between the number of samples N _P and the total number of samples (i.e., N _B).

When the values of the phase angle parameter values FI, X1 exceed 180 degrees, they may be converted into phase deviation values FI _DEV, wherein,

FI_DEV＝FI-360

In this case, when

FI (r) =360×760/1280= 213.75 degrees

The corresponding phase offset value FI _DEV is:

FI _DEV = FI-360 = 213.75-360 = -146.25 degrees

As shown in fig. 19A.

Fig. 19A also shows, for clarity, the phase angle parameter value FI (p+1) and the corresponding phase deviation value FI _DEV (p+1) of the status indication object 550 (p+1).

Further, FIG. 19A also shows a phase deviation value FI _DEV (r-1) corresponding to the phase angle parameter value FI (r-1) of the status indication object 550 (r-1).

The relation generator 1050 may generate an update of the relation value X1, the frequency of delivery being dependent on the rotational speed of the impeller 20. The frequency of delivery may be adjusted according to the processing capabilities of the data processing device 350 (see, e.g., fig. 3). The state parameter extractor 450C may be configured to deliver updated values FI (r), X1 (r) once every 100 revolutions. The update values FI (r) and X1 (r) may be supplied, for example, once every 10 rotations.

Alternatively, the state parameter extractor 450C may also be configured to deliver the updated value X1 (r) once per revolution. In this way, the updated value of the delivery of X1 (r) may be based on the L value generated within a turn. The most recently updated value r of the first internal state parameter X1 (r) may be conveyed on the first state parameter extractor output 1060.

Referring to fig. 23, the vibration event signature detector 990 may be configured to detect the peak amplitude sample value Sp. The vibration event signature detector 990 has an output 1070 for delivering the detected vibration signal amplitude peak Sp. The detected vibration signal amplitude peak Sp may be fed from the output 1070 of the vibration signal peak amplitude detector 990 to the output 1080 of the state parameter extractor 450C. Output 1080 constitutes a second state parameter extractor output for delivering a second internal state parameter X2 (r), also referred to as Sp (r). The frequency of delivery of the second internal state parameter X2 (r) is the same as the frequency of delivery of the first internal state parameter X1 (r).

Furthermore, the first internal state parameter X1 (r) and the second internal state parameter X2 (r) are preferably simultaneously delivered as a set of internal state parameter data (X1 (r); X2 (r)). In the symbol X1 (r), the "r" is a number of samples indicating a slot, that is, an increase in the value of "r" indicates a lapse of time in the same manner as the number "i" in column #01 of table 3.

Improved pumps pump fluids at multiple flow rates

One problem addressed by the examples of the present disclosure is how to improve the pumping process of centrifugal pumps. This problem is solved by a system comprising, for example, a pump 10 with an adaptive volute and vibration sensor.

Another problem to be solved by the disclosed examples is how to improve the pumping process of centrifugal pumps under dynamic and variable fluid system conditions. This problem may be solved by, for example, a system including a pump 10 having an adaptive volute and vibration sensor, and a method of operating the system.

Fig. 24 shows pump 10 with adaptive volute 75A and sensors 70, 70 ₇₇、70₇₈.

Based on vibration data from the sensors 70, 70 ₇₇、70₇₈, the volume of the volute is controlled by adjusting the cross-sectional area of the volute to achieve an optimal efficient flow operating point while varying the rotational speed. Thus, the operating speed f _ROT of the impeller 20 may be controlled according to the desired flow rate, while controlling the cross-sectional area of the adaptive volute based on at least one internal state parameter X1, X2, X3, X.

The advantage of this solution is that it is able to provide the required flow rate Q _OUT while maintaining the internal state of the pump at or substantially at the optimum efficiency operating point.

The solution also provides the flow required for laminar or substantially laminar flow through the pump while maintaining the internal state of the pump at or substantially at the optimum efficiency operating point under dynamic and variable fluid system conditions. This has the advantage of minimizing or eliminating fluid pulsations, thereby achieving fluid delivery. Furthermore, this solution also minimizes or eliminates turbulence, thereby advantageously delivering fluid. The minimization or elimination of turbulence is valuable in many industries, for example, in the dairy industry, where it is desirable to deliver fluids that may be adversely affected by turbulence, such as dairy products.

The operation and function of the pump 10, 10A may be found in WO2021/055879, the contents of which are incorporated herein by reference.

The arrangement shown in fig. 24 may be used in conjunction with the example state parameter extractors 450, 450C illustrated in this disclosure. Referring to fig. 15A, as shown in fig. 24, a flag signal P (i) is provided that can be used to generate a flag signal, which is transmitted to an impeller speed value generator 500. Thus, during rotation of the impeller 20, the impeller speed value generator 500 will receive a marking signal P (i) having a position indicator signal value every 360/L degrees. Therefore, when the rotation speed f _ROT is constant, the fast fourier transformer 510 will receive the flag signal value P (j) =1 from the speed value generator 500 every 360/L degrees during the rotation of the impeller 20. Alternatively, the fast fourier transformer 510 will receive the marker signal value P (q) =1 from the decimators 470, 470B every 360/L degrees during rotation of the impeller 20 when the rotational speed f _ROT varies.

Further, when the speed value generator 500 receives the marking signal P (i) having the position indication signal value (e.g., P (i) =1) every 360/L degrees during rotation of the impeller 20, the speed value generator 500 will be able to generate an even more accurate speed value f _ROT (j).

As for the proper setting of the FFT 510 when a signal value P (j) =1 is received every 360/L degrees during rotation of the impeller 20, this means that the fundamental frequency will be the repetition frequency f _R.

Referring again to the fourier series (see equation 6 below):

wherein,

N=1 corresponds to the fundamental frequency of the signal F (t),

N=2 corresponds to the first harmonic portion of the signal F (t),

Ω=angular frequency of interest, i.e. (2 x pi x f _R),

F _R =frequency of interest, expressed in cycles per second,

T=time and,

Φ _n =phase angle of nth partials,

C _n =amplitude of nth partials.

In this embodiment, it should be noted that when FFT 510 receives one marker signal value P (j) =1 every 360/L degrees during rotation of impeller 20, the fundamental frequency will be one per blade 310.

As described above, the FFT 510 should be set in consideration of the reference signal. As described above, the position signals P (j), P (q) (see fig. 15A) can be used as reference signals for the digital measurement signals S (j), S (q).

According to some embodiments, when the FFT analyzer is configured to receive a reference signal, i.e. the position signals P (j), P (q), P _S、P_C, every 360/L degrees during rotation of the impeller 20, and L is the number of blades 310 in the impeller 20, then the FFT analyzer settings may be set to meet the following criteria:

The integer value Oi is set to one, i.e. equal to 1, and

The settable variables O _MAX and B _n are selected such that the mathematical expression is

Oi*B_n/Y

Becomes a positive integer.

In other words: when the integer value Oi is set equal to 1, then the settable variables O _MAX and B _n should be set to integer values, so that the variable N _R is a positive integer,

Wherein N is _R＝Oi*B_n/O_MAX

Using the above setting, i.e., the integer value Oi is set equal to 1, and referring to fig. 15A and equation 6 above, fft 510 may transmit an amplitude value C _n of n=1, i.e., C ₁ =sp (r). FFT 510 may also transmit the phase angle of the fundamental frequency (n=1), i.e. Φ ₁ =fi (r).

Referring to fig. 15A in conjunction with fig. 1 and equation 6 above, the state values Sp (r) =c ₁ and FI (r) =Φ ₁ may be communicated to a human machine interface (HCI) 210 for providing a visual indication of the analysis results. As described above, the displayed analysis results may include information indicating the internal state of the centrifugal pump process for enabling the operator 230 to control the centrifugal pump.

Referring to fig. 16, 17, 18, 19A and 19B, an example illustration of the visual indication of the analysis results is valid for the setting of the rotary pump impeller 20, as shown in fig. 24, whereby the FFT 510 will receive the marker signals P (i), P (j), P (q) with position indication signal values every 360/L degrees, where L is the number of blades 310 in the impeller 20.

Although the discussion above regarding the setting of FFT 510 relates to fourier series and equations 5 and 6 for the purpose of conveying an intuitive understanding of the context of the setting of FFT transformer 510, it should be noted that the use of digital signal processing may involve discrete fourier transforms (see equation 7 below):

equation 7:

Thus, in accordance with embodiments of the present disclosure, the Discrete Fourier Transform (DFT) described above may be included in signal processing for generating data indicative of the internal state of a centrifugal pump, such as discussed in connection with embodiments of the state parameter extractor 450. In this regard, reference is made to, for example, fig. 3, 4, 5, 15 and/or 24. In view of the above discussion of FFT and fourier series topics, discrete fourier transforms will not be discussed in further detail as the skilled reader of this disclosure is well aware thereof.

In summary, with respect to FFT 510 and the appropriate settings of equations 5 and 6 above, it should be noted that the phase angle of the nth partials (i.e., Φ _n) can be indicative of information identifying the instantaneous operating point. In particular, the phase angle of the nth partials (i.e., Φ _n) may indicate the position of toe 205, expressed as a fraction of the distance between two adjacent blades 310 in rotating impeller 20. Referring to table 6 above and fig. 14, the total distance between two adjacent blades may be considered 360 degrees, and the phase angle value of the nth partials (i.e., Φ _n) divided by 360 degrees may indicate a percentage of the total distance between two adjacent blades. This can be seen, for example, by comparing column #2 in tables 5 and 6 above. As described above, Φ _n =phase angle of the nth partials, C _n =amplitude of the nth partials. As described above, in consideration of the number L of blades in the rotating impeller 20 and the number of generated reference signals and the resulting order Oi of the signal of interest, the FFT 510 may be set to transmit the phase angle Φ _n of the nth partials and the amplitude C _n of the nth partials, so that the phase angle of the nth partials (i.e., Φ _n) may indicate information identifying the instantaneous operating point. Further, as described above, FFT 510 may be set such that variable N _R is a positive integer, where,

N_R＝Oi*B_n/O_MAX

And wherein the first and second heat sinks are disposed,

Oi is set to an integer value, e.g., the number L of blades 310,

O _MAX is set to an integer value,

B _n is set to an integer value.

Referring to fig. 24, an example system 700 includes a centrifugal pump 10, 10A having an adaptive volute 75A and sensors 70, 70 ₇₇、70₇₈.

The adaptive volute 75A of the present disclosure may include one or more mechanisms for adjusting the cross-sectional area of the volute so that the volute may maintain a near uniform static pressure, i.e., optimum efficiency operation (BEP), at the periphery of the impeller disposed within the housing 62 of the pump 10 (see also discussion relating to fig. 14A and 14D). For example, the cross-sectional area of the volute may be expanded or contracted according to one or more operating parameters of the pump and/or the fluid system to alter the optimal operating efficiency of the pump to maintain a higher operating efficiency under different conditions. The one or more operating parameters may include one or more internal state parameters disclosed in the present disclosure, e.g., internal state parameters X1, X2, X3, X, where the index m is a positive integer, as depicted in fig. 2C.

Thus, for example, the volute area may be enlarged or reduced to move the operating point of the pump according to the first parameter value, i.e., the first polar angle X1 (r), FI (r), Φ (r), T _D、T_D1.

In addition, the volute area may be enlarged or reduced to move the operating point of the pump based on the second parameter values, i.e., the detected amplitude values X2 (r), sp (r), S _P1 (representing the amplitude of the detected fluid pressure pulsation P _FP). According to another example, the volute region may be expanded or contracted to change the BEP of the pump according to the following parameters:

-a first parameter value, i.e. a first polar angle X1 (r), and based on

-A second parameter value, the detected amplitude value X2 (r) Sp (r).

The adaptive centrifugal pump 10A of fig. 24 has an impeller 20 that rotates at a rotational speed f _ROT under the drive of a shaft 710 during operation. The shaft is driven in rotation by a drive motor 715. The shaft 710 may be coupled to a drive motor 715 through a gear box 716.

Referring to fig. 24, sensors 70, 70 ₇₇、70₇₈ may be mounted on the housing 62 for generating vibration signals S _EA、S_MD, se (i), S (j), S (q) that depend on the fluid material pressure pulsation P _FP in the pump. The vibration sensor 70, 70 ₇₇、70₇₈ may include one or more sensors associated with fig. 2A.

The pump 10A may also be equipped with a position sensor 170 for generating position signals EP, PS, P (i), P (j), P (q) indicative of the rotational position of the impeller 20 relative to the housing 62. As shown in fig. 24, a position-marking device 180 associated with the impeller 20 may be provided such that as the impeller 20 rotates about the axis of rotation 60, the position-marking device 180 passes the position sensor 170 once per revolution of the impeller, thereby causing the position sensor 170 to generate a rotation-marking signal value PS. Position marker 180 is shown attached to shaft 710 in fig. 24, but this is only one example. The position signals EP, PS, P (i), P (j), P (q) are generated in the same manner as disclosed elsewhere in this disclosure (e.g., with reference to the disclosure of position sensor 170 and position marker 180 in connection with fig. 2A).

As described above, the centrifugal pump 10A in fig. 24 has the adaptive volute 75A. Referring to fig. 24, the example pump 10A includes a housing 62A having a moveable volute boundary wall 720. The volute boundary wall 720 is movable in a direction parallel to the axis of rotation 60.

The movable scroll boundary wall 720 may form a plane perpendicular to the direction of the axis of rotation 60. The movable volute boundary wall 720 is curved with an inner radius that may correspond to the radius R _MIC of the impeller 20 (see fig. 24 and fig. 14D, part II). The outer radius of the moveable volute boundary wall 720 gradually widens to accommodate the pump volute 62A.

The movable volute boundary wall 720 may be coupled to an actuator 725 configured to move 727 the movable volute boundary wall 720 in response to the volume setpoint signal U2 _SP、V_PSP. Accordingly, the actuator may be configured to move 727E the movable volute boundary wall 720 in one direction 727E, thereby expanding the volute cross-sectional area in response to the "expansion value" provided by the volume setpoint signal V _PSP、U2_SP. Conversely, the actuator may be configured to move the movable volute boundary wall 720 in a direction 727C, thereby contracting, i.e., diminishing, the volute cross-sectional area in response to the "decrease" provided by the volume setpoint signal V _PSP、U2_SP. Accordingly, the volume of volute 75A may be adjusted so that a controlled variable flow Q _OUT is output from pump outlet 66 at a certain impeller speed f _ROT (please refer to fig. 24 in conjunction with any of fig. 2A, 2D, 2E, 14A-14G).

By adjusting the cross-sectional area of the volute to control the volume of the volute based on vibration data from the sensors 70, 70 ₇₇、70₇₈, an optimal efficiency flow operating point can be achieved while varying the rotational speed f _ROT. Thus, the operating speed f _ROT of the impeller 20 may be controlled according to the desired flow rate, while the cross-sectional area of the adaptive volute is controlled according to at least one of the internal state parameters X1, X2, X3, X. The advantage of this solution is that it is possible to maintain the internal state of the pump at a desired operating point in relation to the BEP, e.g. at or substantially at the optimum efficiency operating point, while providing the desired flow rate Q _OUT.

Referring to fig. 24, the centrifugal pump controller 240 may be configured to provide an impeller speed set point U1 _SP、f_ROTSP to control the rotational speed f _ROT of the impeller 20. According to some embodiments, the set point U1 _SP、f_ROTSP is set by the operator 230.

As described above, the centrifugal pump controller 240 may also be configured to provide a volume setpoint signal V _PSP、U2_SP to control the outlet fluid volume per revolution of the impeller. According to some embodiments, the set point U2 _SP、V_PSP is set by the operator 230.

To assist the operator 230, the control room may include HCIs 210, 210S (see also fig. 1A and/or 1B) coupled with the analysis device 150 or the monitoring module 150A configured to provide information indicative of the internal state X of the centrifugal pump 10. The HCI 210 may include a display 210S, which may be configured to communicate information related to one or more of fig. 16, 17, 18, 19A, 19B, 19C, 19D, 19E, and/or 19F.

Thus, the system 700 provides an improved user interface 210, 210S, 250 that enables the operator 230 to control the pump 10A, thereby improving the pumping process of the centrifugal pump 10A.

Fig. 25A shows another example system 700R including pumps 10A, 10A _R with adaptive volutes 75A _R and sensors 70, 70 ₇₇、70₇₈. Fig. 25A shows a cross-sectional side view of the pump 10a _R, i.e., a view of the impeller rotation axis 60 parallel to the plane of the paper.

Fig. 25B is a cross-sectional top view of the pump 10a _R shown in fig. 25A.

The system 700R shown in fig. 25A and 25B may include the features of the system 700 disclosed and described above in connection with fig. 24, but in the example system 700R of the example pump 10a _R, the radially outer boundary wall 732 of the adaptive volute is movable.

As described above, centrifugal pump 10a _R in fig. 25 has adaptive volute 75a _R. Referring to fig. 25A, the example pump 10a _R includes a housing 62a _R having a moveable volute boundary wall 732. The movable volute boundary wall 732 is movable in a direction perpendicular to the axis of rotation 60 of the impeller 20. The movable volute boundary wall 732 may form a movable spiral 732. In this way, the movable spiral wall 732 may provide adjustable gradual widening of the adaptive spiral case 75a _R.

The moveable volute boundary wall 732R may be coupled to an actuator 725R that is configured to cause radial movement 727 of the moveable volute boundary wall 732R in response to the volume setpoint signal V _PSP、U2_SP. Accordingly, the actuator 725R may be configured to move 727E the movable volute boundary wall 732R in a direction 727E, thereby expanding the volute cross-sectional area in response to the volume setpoint signal V _PSP、U2_SP providing an "expansion value". Likewise, the actuator may be configured to move the movable volute boundary wall 720 in a direction 727C, which direction 727C causes the volute cross-sectional area to shrink, i.e., to become smaller, in response to the "decrease" provided by the volume setpoint signal V _PSP、U2_SP. In this way, the volume of scroll 75A _R can be adjusted so that variable flow Q _OUT (see fig. 25A and/or 25B and any of fig. 2A, 2D, 2E, 14A to 14G) can be controlled from pump outlet 66 at a certain impeller speed f _ROT.

By adjusting the cross-sectional area of the volute to control the volume of the volute based on vibration data from the sensors 70, 70 ₇₇、70₇₈, an optimal efficiency flow operating point can be achieved while varying the rotational speed f _ROT. Thus, the operating speed f _ROT of the impeller 20 may be controlled according to the desired flow rate, while the cross-sectional area of the adaptive volute is controlled according to at least one of the internal state parameters X1, X2, X3, x.the.

Referring to fig. 24 and fig. 25A and 25B, when the operator wishes to increase the flow rate Q _OUT of the pump 10, the operator can adjust the impeller speed setting f _ROTSP to a higher value until the desired pump 10 flow rate Q _OUT is obtained. Conversely, when the operator wishes to decrease the flow rate Q _OUT of the pump 10, the operator can adjust the impeller speed setting f _ROTSP to a lower value until the desired pump 10 flow rate Q _OUT is achieved.

The advantage of this solution is that it is possible to maintain the internal state of the pump at a desired operating point in relation to the optimum efficiency operating point (BEP) while providing the desired flow rate Q _OUT. When it is desired to operate the pump at or substantially at the optimal efficiency operating point, the operator may adjust the flow set point signal value V _PSP、U2_SP to a value that causes the parameters X1, FI to adopt the reference value corresponding to the optimal efficiency operating point. The FI values corresponding to the optimal efficiency operating points for a single pump may depend on the physical location of the sensors 180 and 70 on the pump 10, 10A _R.

Fig. 24 and 25A and 25B illustrate different configurations of providing a pump with adaptive volutes 75A, 75A _R, but it is noted that the present disclosure is not limited to the illustrated pump configuration. The configuration and function of the pump 10, 10A may be as disclosed in WO2021/055879, the contents of which are incorporated herein by reference. Further features and advantages of the present disclosure will be appreciated by those skilled in the art on the basis of the above-described embodiments. Accordingly, the disclosure is not to be limited by what has been particularly shown and described, except as indicated by the appended claims.

Fig. 26 shows a schematic and schematic diagram of another embodiment of a system 730 comprising pumps 10A, 10A _R with adaptive volutes 75A, 75A _R and sensors 70, 70 ₇₇、70₇₈. In fig. 25A, the pump 10A is shown in a cross-sectional side view, i.e., a view of the impeller rotation axis 60 parallel to the plane of the paper. The system 730 in fig. 26 may include and be configured with components in any of the other embodiments described in this disclosure, e.g., the configurations associated with fig. 1-25. In particular, the apparatus 150, 150A shown in fig. 26 may be configured in accordance with any other embodiment described in this disclosure (e.g., the embodiments related to fig. 1-25). However, in the embodiment of system 730 shown in fig. 26, device 150 includes a monitoring module 150A and a control module 150B. Although the apparatus 150 is illustrated as two blocks, it should be understood that the apparatus 150 may be provided entirely as a single entity 150, including a monitoring module 150A and a control module 150B, as shown by the unified reference 150.

System 730 is configured to control the internal state of pump 10A, 10A _R with adaptive volute 75A, 75A _R and sensor 70, 70 ₇₇、70₇₈.

The system 730 may include means 170, 180 for generating a position signal related to the rotational position of the impeller 20 in the pump 10A, 10A _R. The apparatus 170, 180 may include a position sensor 170 and a marker 180, as described elsewhere in this disclosure, for generating a time series of position signal sample values P (i), P (j), P (q).

Sensors 70, 70 ₇₇、70₇₈ are provided that are configured to generate vibration signals S _EA、S_MD, se (i), S (j), S (q) that are dependent on the fluid material pressure pulsation P _FP. The vibration signals S _EA, se (i), S (j), S (q) may include a time sequence of vibration sample values Se (i), S (j), S (q).

The apparatus 150 of the system 730 may include a monitoring module 150A and a control module 150B. The monitoring module 150A comprises a state parameter extractor 450, 450C configured to detect a first occurrence of a first reference position signal value in said time sequence of position signal sample values P (i), P (j), P (q) (see table 2, table 3 and table 4 above, wherein column #2 shows a position signal having values 1, 1C).

The state parameter extractor 450 may be configured to detect a second occurrence of a second reference position signal value 1, 1C, 360 degrees in said time sequence of position signal sample values P (i), P (j), P (q). The state parameter extractor 450, 450C may further be configured to detect the occurrence of the event signatures S _P (r), sp in said time series of vibration sample values Se (i), S (j), S (q).

The state parameter extractor 450 may be configured to generate data indicative of a first temporal relationship FI (r), X1 (r) between:

Event signature occurs, and

First occurrence and second occurrence.

As described above, the system 730 includes the control module 150B configured to receive data from the pump monitoring module 150, 150A indicative of the internal state of the pump 10A, 10A _R. The data indicative of the internal state may include any information generated or transmitted by the state parameter extractor 450, as described in this disclosure with respect to any of fig. 1-25. Referring to fig. 26, control module 150B includes a regulator 755 for controlling an adaptive volute (75A) based on:

The operating point reference FI _REF (r) (see figure 26),

The first time relationship FI (r), X1 (r) (see FIGS. 1-25), and

The operating point error value FI _ERR (r) (see fig. 26).

The operating point error value (FI _ERR (R)) depends on the operating point reference value FI _REF (R) and the first time relation R _T(r)、T_D, FI (R) (see fig. 3-26). The operating point reference FI _REF (r) may be generated by manual input (not shown in fig. 26), but may also be done as discussed above in connection with fig. 1A and/or 1B, for example.

As shown in fig. 26, the operating point error value (FI _ERR (R)) may depend on the difference between the operating point reference value FI _REF (R) and the first time relationship R _T(r)、T_D, FI (R), X1 (R).

The regulator 755 may be configured to control an operating parameter, such as the rotational speed of the impeller and/or the cross-sectional area of the adaptive volute, in accordance with the operating point reference FI _REF (r).

The state parameter extractor 450 may be configured to generate the first time relation R _T(r);T_D; FI (r); x1 (r) as a phase angle (FI (r)).

The regulator 755 may be configured to include a proportional-integral-derivative controller (PID controller). In addition, the regulator 755 may be configured to include a proportional-integral controller (PI controller). In addition, the regulator 755 may be configured to include a proportional controller (P controller).

Alternatively, the adjuster 755 may be configured to include a kalman filter, also referred to as a Linear Quadratic Estimate (LQE). Kalman filtering is an algorithm that uses a series of observed measurements over time, including statistical noise and other inaccuracies, and estimates unknown variables by estimating a joint probability distribution of the variables within each time frame, which is often more accurate than estimates based on only a single measurement.

Fig. 27 shows a schematic block diagram of a distributed process monitoring system 770. Reference numeral 780 relates to a client location having a pump 10 with a rotatable impeller 20 as discussed above with respect to the previous figures in this document. The client location 780, which may also be referred to as a client portion or pump location 780, may be, for example, a location of a mining company, such as a manufacturing pump for manufacturing cement.

The distributed process monitoring system 770 is operable when one sensor 70 or several sensors 70, 70 ₇₇、70₇₈ are attached at or at a measurement point on the pump.

Measurement signals S _EA and E _P (see, e.g., fig. 1, 27, 26, 25) may be coupled to an input port of pump position communication device 790. Pump position communication device 790 may include an analog-to-digital converter 795 for a/D conversion of measurement signals S _EA and E _P. a/D converter 975 may operate as disclosed elsewhere in this document with respect to a/D converter 330, e.g., in conjunction with fig. 3 and 5. Pump position communication device 790 has a communication port 800 for bi-directional data exchange. The communication port 800 may be connected to a communication network 810, for example via a data interface 820, for enabling the transfer of digital data corresponding to the measurement signals S _EA and E _P. The communication network 810 may be the world wide web, also known as the internet. Communication network 810 may also include a public switched telephone network.

The server computer 830 is connected to a communication network 810. The server 830 may include a database 840, user input/output interfaces 850 and data processing hardware 852, as well as communication ports 855. The server computer 830 is located at a server location 860, the server location 860 being geographically spaced apart from the pump location 780. The server location 860 may be in a first city, such as first capital diego mols, sweden, and the pump location 780 may be in a country near the pump, and/or in another country, such as norway, australia, or the united states. Alternatively, the server location 860 may be in a first part of one country and the pump location 780 may be in another part of the same country. The server location 860 may also be referred to as a vendor component 860 or a vendor location 860.

According to one example, the central control location 870 includes a monitoring computer 880 having data processing hardware and software for monitoring and/or controlling the internal status of the pump 10 at the remote pump location 780. The monitoring computer 880 may also be referred to as a control computer 880. The control computer 880 may include a database 890, user input/output interfaces 900 and data processing hardware 910, as well as communication ports 920, 920A or several communication ports 920, 920A, 920B. The central control location 870 may be spaced a geographic distance from the pump location 780. The central control location 870 may be in a first city, such as first capital diego mols, sweden, and the pump location 780 may be in a country near the pump, and/or in another country, such as norway, australia, or the united states. Alternatively, the central control location 870 may be in a first part of one country and the pump location 780 may be in another part of the same country. Through communication ports 920, 920A, control computer 880 can be coupled to communicate with pump position communication device 790. Accordingly, the control computer 880 may receive measurement signals S _EA and E _P (see, e.g., fig. 1, 27, 26, 25) from the pump position communication device 790 via the communication network 810.

The system 770 may be configured to receive the measurement signals S _EA and E _P in real-time or substantially real-time, or to monitor and/or control the pump 10 from the location 870 in real-time. Further, the control computer 880 may include the monitoring modules 150, 150A as disclosed in any of the examples of this document, for example, as disclosed in connection with any of the above figures 1-26.

The provider company may occupy a server location 860. The vendor company may sell and deliver the device 150 and/or the monitoring module 150A and/or software for such a device 150 and/or monitoring module 150A. Thus, the provider company may sell and deliver software for the control computer 880 at the central control location 870. Such software 370, 390, 400 is discussed, for example, in connection with fig. 4. Such software 370, 390, 400 may be transmitted through transmission over the communications network 810. Alternatively, such software 370, 390, 400 may be transmitted as a computer readable medium 360 for storing program code. Thus, the computer programs 370, 390, 400 may be provided as an article of manufacture comprising a computer storage medium having the computer programs encoded therein.

According to an exemplary embodiment of the system 770, the monitoring computer 880 may substantially continuously receive measurement signals S _EA and E _P (see, e.g., fig. 1, 27, 26, 25) from the pump position communication device 790, e.g., via the communication network 810, so as to be able to continuously or substantially continuously monitor the internal state of the pump 10. The user input/output interface 900 at the central control location 870 may include a screen 900S for displaying images and data, as discussed in connection with the HCI 210 elsewhere in this document. Thus, the user input/output interface 900 may include displays or screens 900S, 210S for providing visual indications of analysis results. The displayed analysis results may include information indicative of the internal state of the centrifugal pump process for enabling an operator 930 at the central control location 870 to control the centrifugal pump 10.

Further, the monitoring computer 880 at the central control location 870 may be configured to communicate information indicative of the internal status of the centrifugal pump process to the HCI 210 via the communication ports 920, 920B and via the communication network 810. In this way, the monitoring computer 880 at the central control location 870 may be configured to enable the operator 230 at the client location 780 to control the centrifugal pump. The local operator 230 at the client location 780 may be placed in the control room 220 (see fig. 1A and/or 1B and/or 27). Thus, the client locations 780, 220 may include a second pump location communicator 790B. The second pump position communication device 790B has a communication port 800B for bi-directional data exchange, and the communication port 800B may be connected to the communication network 810, for example, via a data interface 820B.

Although two position communicators 790, 790B have been described for clarity, a single pump position communicator 790, 790B and/or a single communication port 800, 800B may alternatively be provided for bi-directional data exchange. Thus, items 790 and 790B may be integrated into one unit at pump location 780, as well as items 820 and 820B may be integrated into one unit at pump location 780.

FIG. 28 shows a schematic block diagram of yet another embodiment of a distributed process monitoring system 940. Reference numeral 780 relates to the pump position of the pump 10 having the rotatable impeller 20 as discussed above with respect to the previous figures in this document. The distributed process monitoring system 940 of fig. 28 may include components and be configured as described in any other embodiments described in this disclosure, for example, as described with respect to fig. 1-28. In particular, the monitoring device 150 shown in fig. 28, also referred to as a monitoring module 150A, may be configured as described in any other embodiment described in this disclosure, for example, as described with respect to fig. 1-28. In particular, the process monitoring system 940 shown in FIG. 28 may be configured to include the monitoring module 150A, as disclosed in connection with FIG. 27, but located at a central control location 870.

Further, in the process monitoring system 940 shown in FIG. 28, the pump location 780 includes the control module 150B as described above in connection with FIG. 26.

Thus, the internal state of the pump 10 may be automatically controlled by the control module 150B located at or near the pump location 780, while the monitoring computer 880 at the central control location 870 may be configured to communicate information indicative of the internal state of the centrifugal pump process to the HCIs 900, 900S to enable the operator 930 at the central control location 870 to monitor the internal state of the centrifugal pump 10.

Measurement signals S _EA、S_EA77、S_EA78 and E _P (see, e.g., fig. 1, 27, 26, 25) may be coupled to an input port of pump position communication device 790. Pump position communication device 790 may include an analog-to-digital converter 795 for a/D conversion of measurement signals S _EA、S_EA77、S_EA78 and E _P. a/D converter 975 may operate as disclosed elsewhere in this document with respect to a/D converter 330, e.g., in conjunction with fig. 3 and 5. Pump position communication device 790 has a communication port 800 for bi-directional data exchange. The communication port 800 may be connected to a communication network 810, for example, via a data interface 820. The communication port 800 may be connected to a communication network 810, for example via a data interface 820, for enabling the transfer of digital data corresponding to the measurement signals S _EA、S_EA77、S_EA78 and E _P.

Further, the client location 780 may include a second pump location communicator 790B. The second pump position communication device 790B has a communication port 800B for bi-directional data exchange, and the communication port 800B may be connected to the communication network 810, for example, via a data interface 820B, to enable receipt of data indicative of the internal status of the pump 10 by the control module 150B.

As shown in fig. 28, data indicative of the internal state of the pump 10 may be generated by the monitoring module 150A located at a central location 870.

Although FIG. 28 depicts two position communication devices 790, 790B for clarity, a single pump position communication device 790, 790B and/or a single communication port 800, 800B may alternatively be provided for bi-directional data exchange. Thus, items 790 and 790B may be integrated into one unit at pump location 780, as well as items 820 and 820B may be integrated into one unit at pump location 780.

FIG. 29 shows a schematic block diagram of yet another embodiment of a distributed process control system 950. Likewise, reference numeral 780 relates to the pump position of the pump 10 having the rotatable impeller 20 as discussed above with respect to the previous figures in this document. The distributed process monitoring system 950 of fig. 29 may be configured as described in any other embodiment described in this disclosure, for example, with respect to fig. 1-28. In particular, the monitoring device 150 shown in fig. 28 and 29, also referred to as a monitoring module 150A, may be configured as described in any other embodiment described in this disclosure, for example, as discussed with respect to fig. 1-28. In addition, the process monitoring system 950 shown in FIG. 29 may be configured to include the control module 150B as described above in connection with FIG. 26 and the monitoring module 150A as disclosed in connection with FIG. 27.

In the example of fig. 29, the monitoring module 150A and the control module 150B are disposed at a control location 870. Control location 870 may be remote from pump location 780. Data communication between control location 870 and pump location 780 may be provided via data ports 820 and 920 and communication network 810, as discussed above in connection with previous figures.

Various examples are disclosed below:

example 1 relates to a system for monitoring an internal condition of a centrifugal pump (10), the centrifugal pump having a housing (62) with a rotatable impeller (20) disposed therein, the housing (62) defining:

a volute (75); and

A shaped portion (63) separating a first portion (77) of the volute (75) from a second portion (78) of the volute to form a pump outlet (66) for delivering fluid material (30) from the volute, the impeller (20) defining a plurality (L) of impeller channels for pressing the fluid material (30) into the volute (75) by centrifugal force upon rotation of the impeller (20), resulting in vibrations (V _FP) having a repetition frequency (f _R) that is dependent on the impeller rotation speed (f _ROT).

2. The system of any of the preceding examples, further comprising:

a monitoring unit (150B) for receiving:

A first vibration signal (S _FP;S_EA、S_MD, se (i), S (j), S (q)), comprising a time sequence of vibration sample values (Se (i), S (j), S (q)), indicative of vibrations (V _FP1) exhibited by a first housing portion defining the first volute section (77);

And

A second vibration signal (S _FP;S_EA、S_MD, se (i), S (j), S (q)), comprising a time sequence of vibration sample values (Se (i), S (j), S (q)), indicative of vibration (V _FP2) by a second housing portion (X102) defining the second volute portion (78);

the monitoring unit includes:

A state parameter extractor (450) configured to detect an occurrence of a first vibration signal event signature (S _p (r); sp) in the first vibration signal;

The state parameter extractor (450) is configured to detect an occurrence of a second vibration signal event signature (S _p (r); sp) in the second vibration signal.

3. The system of any of the preceding examples, wherein:

The state parameter extractor (450) is configured to generate data indicative of a temporal relationship between the first vibration signal event signature and the second vibration signal event signature; and

-An analyzer for detecting the internal state of the centrifugal pump (10) based on the time relation.

4. The system of any of the preceding examples, wherein:

The state parameter extractor (450) is configured to generate data indicative of a mutual order of occurrence between the first vibration signal event signature and the second vibration signal event signature; and

-An analyzer (X451) for evaluating or detecting an internal state of the centrifugal pump (10) based on the mutual occurrence sequence.

Example 5 relates to a system for monitoring an internal condition of a centrifugal pump (10) having a rotatable impeller (20) with a plurality (L) of blades (310) for engaging a fluid material (30) when the impeller (20) is rotated, resulting in a vibration (V _FP) having a repetition frequency (f _R) that is dependent on a rotational speed (f _ROT) of the impeller (20).

6. The system of any of the preceding examples, comprising:

a monitoring unit for receiving:

Signals (E _p, P (i), P (j), P (q)) indicative of the rotational position of the rotatable impeller (20), and

Signals (S _FP;S_EA、S_MD, se (i), S (j), S (q)) indicative of the vibrations (V _FP), the monitoring unit being configured to extract a first state value (R _T(r);T_D; FI (R)) indicative of an operating point of the centrifugal pump (10) from the vibration signal and the position signal.

7. The system of any of the preceding examples, comprising:

a state parameter extractor (450) configured to detect a first occurrence of a first reference position signal value (1; 1C, 0%) in a time sequence of position signal sample values (P (i), P (j), P (q));

-the state parameter extractor (450) is configured to detect a second occurrence of a second reference position signal value (1; 1c; 100%) in the time sequence of position signal sample values (P (i), P (j), P (q));

The state parameter extractor (450) is configured to detect a third occurrence of an event signature (Sp (r); sp) in a time sequence of vibration sample values (Se (i), S (j), S (q));

The state parameter extractor (450) is configured to generate data indicative of a first duration between the first occurrence and the second occurrence; and

The state parameter extractor (450) is configured to generate data indicative of a second duration between the third occurrence and at least one of the first occurrence and/or the second occurrence;

The state parameter extractor (450) is configured to generate data indicative of a first temporal relationship (R _T(r);T_D; FI (R)) between:

The second duration, and

The first duration; and

-An analyzer (X451) for determining an internal state of the centrifugal pump (10) based on:

An operating point reference value (FI _REF (r)),

The first time relation (R _T(r);T_D; FI (R)), and

Operating point error value (FI _ERR (r)), wherein,

The operating point error value (FI _ERR (r)) depends on:

The operating point reference value (FI _REF (r)), and

The first time relationship (R _T(r);T_D; FI (R)).

Example 8 relates to a system for monitoring an internal condition of a centrifugal pump (10), the centrifugal pump having a housing (62) with a rotatable impeller (20) disposed therein, the housing (62) defining:

a volute (75); and

-A shaped portion (63) forming a pump outlet (66) separating a first portion (77) of the volute (75) from a second portion of the volute, the impeller (20) defining a plurality (L) of impeller channels for pressing the fluid material (30) into the volute (75) by centrifugal force when the impeller (20) is rotated, resulting in a vibration (V _FP) having a repetition frequency (f _R) that depends on a rotational speed (f _ROT) of the impeller (20).

9. The system of any of the preceding examples, comprising:

a monitoring unit for receiving:

Signals (E _p, P (i), P (j), P (q)) indicative of the rotational position of the rotatable impeller (20) relative to the housing, and

Signals (S _FP;S_EA、S_MD, se (i), S (j), S (q)) indicative of the vibrations (V _FP),

The monitoring unit includes:

A state parameter extractor (450) configured to:

a first state value (R _T(r);T_D; FI (R); X1) is extracted from the vibration signal and the position signal, indicating the internal state, e.g. an operating point, during operation of the centrifugal pump (10).

10. The system according to any of the preceding examples, wherein,

The shaped portion includes a volute tongue that separates a first portion (77) of the volute (75) from a second portion of the volute.

11. The system according to any of the preceding examples, wherein,

The first volute section (77) has a first cross-sectional area, and

The second volute section has a second cross-sectional area, and the first cross-sectional area is less than the second cross-sectional area.

12. The system according to any of the preceding examples, wherein,

A vibration sensor connected to the housing for generating a vibration signal (S _FP;S_EA、S_MD, se (i), S (j), S (q)); the vibration sensor is configured to generate the vibration signal based on a vibration (V _FP1) displayed by the housing.

13. The system according to any of the preceding examples, wherein,

The position marker (180) is disposed on a rotatable member configured to rotate when the rotatable impeller (20) rotates, and

The position sensor is configured to generate a position signal indicative of a predetermined rotational position of the rotatable impeller (20), the position signal comprising a time sequence of position signal values (P (i), P (j), P (q)).

14. The system of any of the preceding examples, comprising:

A first sensor for generating a first vibration signal (S _FP;S_EA、S_MD, se (i), S (j), S (q)); the first sensor is configured to generate the first vibration signal based on vibrations (V _FP1) displayed by a first housing portion (X101) defining the first volute section (77); and

A second sensor for generating a second vibration signal (S _FP;S_EA、S_MD, se (i), S (j), S (q)); the second sensor is configured to generate the second vibration signal based on vibrations (V _FP2) exhibited by a second housing portion (X102) defining the second volute section (78).

Example 15 relates to a system for monitoring an internal state of a centrifugal pump (10) having a rotatable impeller (20) with a plurality (L) of blades (310) for engaging a fluid material (30) when the impeller (20) rotates, resulting in a vibration (V _FP) having a repetition frequency (f _R) that depends on a rotational speed (f _ROT) of the impeller (20).

Example 16 relates to a system for monitoring an internal operating condition of a centrifugal pump (10) having a housing (62) with a rotatable impeller (20) disposed therein, the housing (62):

Limiting

A volute (75); and

-A shaped portion (63) forming a pump outlet (66) separating a first portion (77) of the volute (75) from a second portion of the volute, the impeller (20) defining a plurality (L) of impeller channels for pressing fluid material (30) into the volute (75) by centrifugal force when the impeller (20) is rotated, resulting in a housing vibration (V _FP) having a repetition frequency (f _R) dependent on a rotational speed (f _ROT) of the impeller (20).

Example 17 relates to a system for monitoring an internal operating condition of a centrifugal pump (10) having a housing (62) with a rotatable impeller (20) disposed therein, the housing (62):

Limiting

A volute (75); and

-A shaped portion (63) forming a pump outlet (66) separating a first portion (77) of the volute (75) from a second portion of the volute, the impeller (20) defining a plurality (L) of impeller channels for pressing a fluid material (30) into the volute (75) by centrifugal force upon rotation of the impeller (20), resulting in a pulsation (V _P) in said fluid material (30) having a repetition frequency (f _R) depending on the rotation speed (f _ROT) of the impeller (20).

18. The system according to any of the preceding examples, wherein,

The fluid material pulsation causes vibration (V _FP) of the housing (62).

19. The system of any of the preceding examples, comprising:

a monitoring unit for receiving:

Signals (E _p, P (i), P (j), P (q)) indicative of the rotational position of the rotatable impeller (20) during operation of the centrifugal pump (10), and

Signals (S _FP;S_EA、S_MD, se (i), S (j), S (q)) indicating the vibration (V _FP).

20. The system of any of the preceding examples, comprising:

-a state parameter extractor (450) configured to extract data indicative of a first state value (R _T(r);T_D; FI (R); X1)) from the vibration signal and the position signal, indicative of the internal state of the centrifugal pump (10).

21. The system of any of the preceding examples, comprising:

a monitoring unit for receiving:

Signals (S _FP;S_EA、S_MD, se (i), S (j), S (q)) indicative of said vibrations (V _FP), said monitoring unit comprising:

The state parameter extractor (450) is configured to detect a third occurrence of an event signature (S _p (r); sp) in the time series of vibration sample values (Se (i), S (j), S (q));

The state parameter extractor (450) is configured to generate data indicative of a first temporal relationship (R _T(r);T_D; FI (R); X1) between:

The second duration, and

The first duration; and

-An analyzer (X451) for detecting said internal state of said centrifugal pump (10) based on said first relation (R _T(r);T_D; FI (R)).

22. The system of example 21, wherein,

The first relationship (R _T(r);T_D; FI (R)) constitutes a first state value (R _T(r);T_D; FI (R); X1).

23. The system according to any of the preceding examples, wherein,

The analyzer is configured to detect the internal state based on:

An operating point reference value (FI _REF (r)),

The first relationship (R _T(r);T_D; FI (R)), and

Operating point error value (FI _ERR (r)), wherein,

The operating point error value (FI _ERR (r)) depends on:

The operating point reference value (FI _REF (r)), and

The first time relationship (R _T(r);T_D; FI (R)).

24. The system of any of the preceding examples, comprising:

The second duration, and

The first duration; and

-An analyzer (X451) for evaluating the internal state of the centrifugal pump (10) based on:

An operating point reference value (FI _REF (r)),

The first relationship (R _T(r);T_D; FI (R)), and

Operating point error value (FI _ERR (r)), wherein,

The operating point error value (FI _ERR (r)) depends on:

The operating point reference value (FI _REF (r)), and

The first relationship (R _T(r);T_D; FI (R)).

25. The system of any of the preceding examples, wherein:

The analyzer (X451) generates the first state value (R _T(r);T_D; FI (R)) indicative of an operating point of the centrifugal pump (10) based on the first relationship (R _T(r);T_D; FI (R)).

26. The system of any of the preceding examples, wherein:

The operating point reference value (FI _REF (r)) is a predetermined relationship value indicative of an optimum efficiency operating point of the centrifugal pump (10); and

The analyzer (X451) generates the first state value (R _T(r);T_D; FI (R)) indicative of an operating point of the centrifugal pump (10) based on the operating point error value (FI _ERR (R)).

27. The system of any of the preceding examples, further comprising:

A sensor for generating the vibration signal (S _FP;S_EA、S_MD, se (i), S (j), S (q)) when the centrifugal pump (10) displays the vibration (V _FP).

28. The system of any of the preceding examples, wherein:

The centrifugal pump (10) comprises:

-said rotatable impeller (20); and

A housing (62) in which the impeller (20) is disposed, the housing (62)

The device comprises:

an inlet (64) for receiving the fluid material (30), and

An outlet (66) for delivering the fluid material (30) propelled by the impeller (20) as the impeller (20) rotates; and wherein the first and second heat sinks are disposed,

The sensor is configured to generate the vibration signals (S _FP;S_EA、S_MD, se (i), S (j), S (q)) when the housing exhibits the vibration (V _FP).

29. The system of any of the preceding examples, wherein:

the housing (62) defines a volute (75) configured as a curved funnel that increases in cross-sectional area as it approaches the outlet (66).

30. The system of any of the preceding examples, wherein:

The impeller (20) blades (310) define a plurality (L) of impeller channels for forcing the fluid material (30) into the volute (75) by centrifugal force as the impeller (20) rotates.

31. The system of any of the preceding examples, wherein:

The centrifugal pump (10) comprises

-Said rotatable impeller (20); and

A housing (62) in which the impeller (20) is disposed, the housing (62) defining a volute (75) configured as a curved funnel having a cross-sectional area;

The housing (62) has a shaped portion (63) for separating a first portion (77) of the volute (75) from a second portion (78) of the volute;

the first volute section (77) has a first cross-sectional area, and

The second volute section (78) has a second cross-sectional area, and the first cross-sectional area is less than the second cross-sectional area.

32. The system of any of the preceding examples, further comprising:

A second sensor for generating a second vibration signal (S _FP;S_EA、S_MD, se (i), S (j), S (q)); the second sensor is configured to generate the second vibration signal based on vibrations (V _FP2) exhibited by a second housing portion (X102) defining the second volute section (78);

A state parameter extractor (450) configured to detect a fourth occurrence of an event signature (S _p (r); sp) in the time sequence of first vibration signal sample values (Se (i), S (j), S (q));

The state parameter extractor (450) is configured to detect a fifth occurrence of the event signature (S _p (r); sp)) in a time sequence of second vibration signal sample values (Se (i), S (j), S (q));

the state parameter extractor (450) is configured to generate data indicative of a mutual order of occurrence between the fourth event and the fifth event; and

-An analyzer (X451) for evaluating the internal condition of the centrifugal pump (10) based on the mutual occurrence sequence.

Example 33 is directed to a system, comprising:

A centrifugal pump (10) having

A housing (62) in which the rotatable impeller (20) is disposed,

The housing (62) defines:

A central pump inlet (64) for fluid material (30),

An outlet (66), and

A volute (75),

The rotatable impeller (20) has:

a plurality (L) of blades for pressing fluid material (30) from a central pump inlet (64) into a volute (75) as the rotatable impeller (20) rotates, resulting in a fluid material pulsation (V _P) having a repetition frequency (f _R) that depends on a rotational speed (f _ROT) of the rotatable impeller (20);

The system further comprises:

A vibration sensor for generating a vibration signal (S _FP;S_EA、S_MD, se (i), S (j), S (q)) depending on a pulsation (V _P) of a fluid material;

A position sensor for generating a signal (E _p, P (i), P (j), P (q)) indicative of the rotational position of the rotatable impeller (20) relative to the housing, and

A state parameter extractor (450) configured to:

a first state value (R _T(r);T_D; FI (R); X1) is extracted from the vibration signal and the position signal, which is indicative of the internal state of the centrifugal pump (10) during operation.

34. The system of any of the preceding examples, wherein:

The rotatable impeller (20) has:

a plurality (L) of blades for forcing fluid material (30) from a central pump inlet (64) into a volute (75) as the rotatable impeller (20) rotates, resulting in a flow of fluid material having a repetition frequency (f _R) that is dependent on a rotational speed (f _ROT) of the rotatable impeller (20).

Example 35 relates to a system for monitoring an internal condition of a centrifugal pump (10) having a housing (62) with a rotatable impeller (20) disposed therein, the housing (62) defining a volute (75) and a shaped portion (63) forming an outlet (66), the rotatable impeller (20) defining a plurality (L) of impeller channels for pressing a fluid material (30) into the volute (75) upon rotation of the impeller (20), resulting in a fluid material pulsation (V _P) having a repetition frequency (f _R) that depends on a rotational speed (f _ROT) of the rotatable impeller (20); the system comprises:

A state parameter extractor (450) configured to:

A first state value (R _T(r);T_D; FI (R); X1) is extracted from the vibration signal and the position signal, which is indicative of the internal state during operation of the centrifugal pump (10).

36. The system of any of the preceding examples, wherein:

The vibration sensor is configured to generate the vibration signal based on a vibration (V _FP1) exhibited by the housing in response to fluid material pulsations (V _P).

37. The system according to any of the preceding examples, wherein,

The vibration sensor is attached to a housing (62).

38. The system according to any of the preceding examples, wherein,

The position sensor (170) is configured to generate the position signals (E _p, P (i), P (j), P (q)) from the position marks (180).

39. The system of any of the preceding examples, wherein:

The state parameter extractor (450) is configured to detect a first occurrence of a first reference position signal value (1; 1C, 0%) in a time sequence of position signal sample values (P (i), P (j), P (q));

The second duration, and

The first duration.

40. The system of any of the preceding examples, wherein:

The data indicating a first relationship (R _T(r);T_D; FI (R); X1) is the first state value (R _T(r);T_D; FI (R); X1).

41. The system of any of the preceding examples, further comprising:

an analyzer (X451) for evaluating an internal state of the centrifugal pump (10) based on:

An operating point reference value (FI _REF (r)),

The first relationship (R _T(r);T_D; FI (R), and

Operating point error value (FI _ERR (r)), wherein,

The operating point error value (FI _ERR (r)) depends on:

The operating point reference value (FI _REF (r)), and

The first relationship (R _T(r);T_D; FI (R)).

42. The system of any of the preceding examples, wherein:

When the operating point reference value (FI _REF (r)) is adjusted to a value indicative of the pump optimum efficiency flow (BEP),

The operating point error value (FI _ERR (r)) indicates that the pump operating point deviates from the pump optimum efficiency flow (BEP).

43. The system of any of the preceding examples, wherein:

A deviation of the operating point error value (FI _ERR (r)) from a zero value indicates that the pump operating point deviates from the pump optimal efficiency flow (BEP).

44. The system according to any of the preceding examples, wherein,

The vibration signal comprises a time sequence of vibration sample values (Se (i), S (j), S (q)) indicative of vibrations (V _FP1) displayed by the housing; and

The position signal comprises a time sequence of position signal values (P (i), P (j), P (q)).

45. The system of any of the preceding examples, further comprising:

-a shaped portion (63) forming said outlet (66).

46. The system according to any of the preceding examples, wherein,

The shaped portion (63) couples the volute to an outlet (66) of the pump.

47. The system according to any of the preceding examples, wherein,

The forming section (63) includes a volute tongue separating a first portion (77) of the volute (75) from a second portion of the volute.

48. The system according to any of the preceding examples, wherein,

The outlet (66) includes a volute tongue separating a first portion (77) of the volute (75) from a second portion of the volute.

49. The system according to any of the preceding examples, wherein,

The position marker (180) is located on the rotatable portion such that the position signal (E _p, P (i), P (j), P (q)) includes a reference position signal value (1; 1C,0%; 100%) at a predetermined angular position relative to the volute tongue.

50. The system according to any of the preceding examples, wherein,

The position marker (180) is located on the rotatable portion such that the position signal (E _p, P (i), P (j), P (q)) comprises a reference position signal value (1; 1C,0%; 100%) indicative of at least one predetermined angular position relative to the outlet (66).

51. The system according to any of the preceding examples, wherein,

The rotatable impeller (20) comprises blades (310) defining said number (L) of impeller channels.

52. The system of any preceding example, particularly when dependent on example 49, wherein,

The state parameter extractor (450) is configured to detect the occurrence of an event signature (Sp (r); sp) in a time sequence of vibration sample values (Se (i), S (j), S (q)).

53. The system of any preceding example, particularly when dependent on example 49, wherein,

The state parameter extractor (450) is configured to detect the occurrence of an event signature (Sp (r); sp) in a time sequence of vibration sample values (Se (i), S (j), S (q)); and

The state parameter extractor (450) is configured to determine, based on the reference position signal value (1; 1C,0%; 100%) and the time sequence of vibration sample values (Se (i), S (j), S (q)),

Data is generated indicating the angular position of the rotatable impeller (20) when the event signature (Sp (r); sp) occurs.

Example 54 relates to a system, comprising:

A centrifugal pump (10) is provided with:

a housing (62) in which the rotatable impeller (20) is disposed,

The housing (62) defines:

A central pump inlet (64) for fluid material (30),

An outlet (66), and

A volute (75),

The rotatable impeller (20) has:

A plurality (L) of blades for pressing fluid material (30) from a central pump inlet (66) into a volute (75) as the rotatable impeller (20) rotates, resulting in a flow of fluid material having a pulsation (V _P) of a repetition frequency (f _R) that depends on a rotational speed (f _ROT) of the rotatable impeller (20);

The system further comprises:

A state parameter extractor (450) configured to:

55. The system according to any of the preceding examples, wherein,

The vibration signal comprises a time sequence of vibration sample values (Se (i), S (j), S (q)) indicative of vibrations (V _FP 1) displayed by the housing; and

The position signal comprises a time sequence of position signal values (P (i), P (j), P (q)); the time series of position signal values (P (i), P (j), P (q)) comprises reference position signal values (1; 1C,0%; 100%) indicative of a predetermined angular position of the rotatable impeller relative to the housing.

56. The system of any preceding example, particularly when dependent on example 55, wherein,

The state parameter extractor (450) is configured to:

Based on the reference position signal value (1; 1C,0%; 100%) and the time series of vibration sample values (Se (i), S (j), S (q)), data is generated indicating the angular position of the rotatable impeller (20) relative to the housing when the event signature (S _p (r); sp) occurs.

57. The system of any preceding example, particularly when dependent on example 56, wherein,

The data indicative of the angular position of the rotatable impeller (20) relative to the housing at the occurrence of the event signature (S _p (R); sp) is the first state value (R _T(r);T_D; FI (R); X1).

58. The system according to any of the preceding examples, wherein,

The fluid material pulsation causes vibration (V _FP) of the housing (62).

59. The system according to any of the preceding examples, wherein,

The operating point error value (FI _ERR (r)) depends on the difference between:

The operating point reference value (FI _REF (r)), and

First relation (R _T(r);T_D; FI (R))).

60. The system according to any of the preceding examples, wherein,

The operating point error value (FI _ERR (r)) indicates that the pump operating point deviates from the operating point reference value (FI _REF (r)).

61. The system of any of the preceding examples, further comprising:

A drive motor for causing the rotational speed (f _ROT) of the impeller (20) in response to a drive motor speed control signal (U1 _SP); wherein,

The operating point error value (FI _ERR (r)) is indicative of a deviation of the drive motor control signal value from a drive motor set point (U1 _SP,F_ROTSP) associated with the operating point reference value (FI _REF (r)).

62. The system of any of the preceding examples, further comprising:

A drive motor for causing said rotational speed (f _ROT) of the impeller (20) in response to a drive motor speed control signal; wherein,

The operating point error value (FI _ERR (r)) is indicative of the impeller speed (f _ROT) and an impeller speed set point (f _{ROT_SP};U1_SP,F_ROTSP).

63. The system of any of the preceding examples, further comprising:

A regulator for controlling the impeller rotation speed (f _ROT) based on,

An operating point reference value (FI _REF (r)),

The first relationship (R _T(r);T_D; FI (R), and

Operating point error value (FI _ERR (r)), wherein,

The operating point error value (FI _ERR (r)) depends on:

The operating point reference value (FI _REF (r)), and

The first relationship (R _T(r);T_D; FI (R)).

64. The system of any of the preceding examples, further comprising:

A drive motor for rotating the impeller (20) at the rotational speed (f _ROT) in response to a drive motor speed control signal; wherein,

The regulator is configured to control an impeller speed set point (f _{ROT_SP};U1_SP,F_ROTSP) in accordance with the operating point reference value (FI _REF (r)).

65. The system according to any of the preceding examples, wherein,

The event signature (S _p (r); sp) is the vibration signal amplitude peak.

66. The system according to any of the preceding examples, wherein,

The impeller passage is a passage from a pump inlet (64) to the volute.

67. The system according to any of the preceding examples, wherein,

The impeller passage is a rotatable passage having an impeller opening facing the volute such that the impeller opening rotates as the impeller rotates.

68. The system of any of the preceding examples, further comprising

-A tubing coupled to the pump outlet (66) for receiving the fluid material (30)

69. The system according to any of the preceding examples, wherein,

The regulator is configured to control a volute setpoint value (U2 _SP) in accordance with the operating point reference value (FI _REF (r)), and wherein,

The volute is an adaptive volute (75) having an adjustable volume, and wherein,

The volute set point value (U2 _SP;V_PSP) controls the adjustable volute volume.

70. The system according to any of the preceding examples, wherein,

The event signature is indicative of a fluid pressure (P _FL、P₅₄) generated when a rotating impeller (20) interacts with the fluid material (30).

71. The system according to any of the preceding examples, wherein,

The state parameter extractor (450) is configured to generate the first time relation (R _T(r);T_D; FI (R)) as a phase angle (FI (R)).

72. The system according to any of the preceding examples, wherein,

The state parameter extractor (450) is configured to generate the event signature as an amplitude value (S _p(r);Sp;C_L(r);C₁ (r)).

73. The system according to any of the preceding examples, wherein,

The state parameter extractor (450) comprises a fourier transformer configured to generate the first time relation (R _T(r);T_D; FI (R)).

74. The system according to any of the preceding examples, wherein,

The state parameter extractor (450) is configured to count the total number of samples (N _B) from the first occurrence to the second occurrence, and

The state parameter extractor (450) is configured to count another number of samples (N _P) from a first occurrence to a third occurrence, and

-The state parameter extractor (450) is configured to generate the first time relation (R _T(r);T_D; FI (R)) based on the another number and the total number; or wherein the first and second heat exchangers are arranged in a row,

The state parameter extractor (450) is configured to generate the first time relation (R _T(r);T_D; FI (R)), wherein:

The relation between the further number and the total number is indicative of an internal state of the centrifugal pump (10).

Example 75 relates to a system for monitoring an internal operating condition of a centrifugal pump (10) having a housing (62) with a rotatable impeller (20) disposed therein, the housing (62)

Limiting

A volute (75); and

Forming a shaped portion (63) of the pump outlet (66) separating a first portion (77) of the volute (75) from a second portion of the volute, the impeller (20) defining a plurality (L) of impeller channels for pressing the fluid material (30) into the volute (75) by centrifugal force as the impeller (20) rotates, the pulsation (V _P) having a repetition frequency (f _R) that depends on a rotational speed (f _ROT) of the impeller (20);

Example 76 relates to a system for monitoring an internal state of a centrifugal pump (10) having a rotatable impeller (20) comprising vanes (310) defining a plurality (L) of impeller channels for pressing a fluid material (30) into a volute (75) as the impeller (20) rotates, resulting in a fluid material pulsation (V _P) having a repetition frequency (f _R) that depends on a rotational speed (f _ROT) of the impeller (20);

Example 77 relates to a centrifugal pump apparatus (X310), comprising:

A centrifugal pump (10) is provided with:

a housing (62) in which the rotatable impeller (20) is disposed,

The housing (62) defines:

a pump inlet (64) for fluid material (30),

An outlet (66) for fluid material (30), and

A volute (75),

The rotatable impeller (20) has:

-a plurality (L) of blades for pressing fluid material (30) from a pump inlet (64) into a volute (75) upon rotation of the rotatable impeller (20), resulting in a flow of fluid material having a pulsation (V _P) with a repetition frequency (f _R) that depends on the rotational speed (f _ROT) of the impeller (20);

the centrifugal pump apparatus (X310) further comprises:

A position sensor for generating a position signal (E _p, P (i), P (j), P (q)) indicative of the rotational position of the rotatable impeller (20) relative to the housing, and

-A pump position data port (X211) connectable to a communication network (X250) for data exchange with a pump monitoring device (X150) for monitoring an internal state of the centrifugal pump (10);

-a pump position communication device (X212) configured to deliver via the pump position data port (X211):

Data (S _FP;S_EA、S_MD, se (i), S (j), S (q)) indicative of the vibration signal, and

Data (E _p, P (i), P (j), P (q)) indicative of the position signal.

Example 78 relates to a pump monitoring device (X320) for cooperation with a centrifugal pump device (X310) according to any one of the preceding examples,

The pump monitoring device (X320) comprises:

A monitoring device data port (X221) connectable to a communication network (X250) for data exchange with the centrifugal pump device (X310);

A monitoring device communication device (X222) configured to receive via the monitoring device data port (X221):

Data (S _FP;S_EA、S_MD, se (i), S (j), S (q)) indicating the vibration signal, and

Data (E _P, P (i), P (j), P (q)) indicating the position signal;

The pump monitoring device (X320) further comprises:

A state parameter extractor (450) configured to extract a first state value (T _D1,R_T(r);T_D; FI (r); X1) indicative of an internal state of the centrifugal pump (10) during operation from the vibration signal and the position signal.

79. The pump monitoring device of any of the preceding examples, further comprising:

A screen display (210S); and wherein the first and second heat sinks are disposed,

The received vibration signal (S _FP;S_EA、S_MD, se (i), S (j), S (q)) is dependent on a fluid material pulsation (V _P); the vibration signal comprises a time sequence of vibration sample values (Se (i), S (j), S (q)); and wherein the first and second heat sinks are disposed,

The state parameter extractor (450) is configured to detect the occurrence of an event signature (S _p (r); sp) in the time sequence of vibration sample values (Se (i), S (j), S (q));

The state parameter extractor (450) is configured to display on the screen display (210S):

a polar coordinate system, the polar coordinate system having:

reference point (O), and

A reference direction (0, 360); and

A first internal state indicating object (S _P1、T_D1) indicating the internal state at a first polar angle (T _D1) relative to the reference direction (0, 360), the first polar angle (T _D1) indicating an angular position of the rotatable impeller (20) relative to the pump casing when the event signature (S _p (r); sp) occurs.

Example 80 is directed to a system, comprising:

A centrifugal pump (10) having

A housing (62) in which the rotatable impeller (20) is disposed,

The housing (62) defines:

A central pump inlet (64) for fluid material (30),

An outlet (66), and

A volute (75),

A rotatable impeller (20) having:

A plurality (L) of blades for pressing fluid material (30) from a central pump inlet (64) into a volute (75) as the rotatable impeller (20) rotates, resulting in a pulsation (V _P) of fluid material having a repetition frequency (f _R) that depends on a rotational speed (f _ROT) of the rotatable impeller (20).

81. The system of example 80, further comprising:

A state parameter extractor (450) configured to:

82. In a digital monitoring system for generating and displaying information related to an internal state of a centrifugal pump (10) having a housing defining a volute (75) in which a rotatable impeller (20) is disposed for pressing a fluid material (30) from a central pump inlet (64) into the volute (75) upon rotation of the rotatable impeller (20), resulting in a fluid material flow having a pulsation (V _P) with a repetition frequency (f _R) that is dependent on a rotational speed (f _ROT) of the impeller (20);

A computer-implemented method of representing the internal state of the centrifugal pump (10) on a screen display (210S),

The method comprises the following steps:

Receiving a signal (E _p, P (i), P (j), P (q)) indicative of a rotational position of the rotatable impeller (20) relative to the housing, the position signal comprising a time sequence of position signal values (P (i), P (j), P (q)), the time sequence of position signal values (P (i), P (j), P (q)) comprising reference position signal values (1; 1C,0%; 100%), indicative of at least one predetermined angular position of the rotatable impeller relative to the housing, and

Receiving a vibration signal (S _FP;S_EA、S_MD, se (i), S (j), S (q)) dependent on the pulsation (V _P) of the fluid material; the vibration signal comprises a time sequence of vibration sample values (Se (i), S (j), S (q));

detecting the occurrence of an event signature (S _p (r); sp) in the time series of vibration sample values (Se (i), S (j), S (q));

displaying on the screen display (210S):

a polar coordinate system, the polar coordinate system having:

reference point (O), and

A reference direction (0, 360); and

-A first internal state indicating object (S _P1、T_D1), -said internal state being indicated at a first polar angle (T _D1) with respect to said reference direction (0, 360), said first polar angle (T _D1) being indicative of an angular position of the rotatable impeller (20) with respect to the pump casing upon occurrence of said event signature (S _p (r); sp).

83. In a digital monitoring system for generating and displaying information related to an internal state of a centrifugal pump (10) having a housing defining a volute (75) in which a rotatable impeller (20) is disposed for pressing a fluid material (30) from a pump inlet (64) into the volute (75) upon rotation of the rotatable impeller (20), resulting in a fluid material flow having a pulsation (V _P) with a repetition frequency (f _R) that is dependent on a rotational speed (f _ROT) of the impeller (20);

The method comprises the following steps:

-receiving a signal (E _p, P (i), P (j), P (q)) comprising a reference position signal value (1; 1c,0%; 100%) indicative of at least one predetermined angular position of the rotatable impeller relative to the housing, and

displaying on the screen display (210S):

a polar coordinate system having

Reference point (O), and

A reference direction (0, 360); and

84. In a digital monitoring system for generating and displaying information related to an internal state of a centrifugal pump (10) having a housing defining a volute (75) in which a rotatable impeller (20) is disposed for pressing a fluid material (30) from a pump inlet (64) into the volute (75) upon rotation of the rotatable impeller (20), resulting in a fluid material flow having a pulsation (V _P) with a repetition frequency (f _R) that is dependent on a rotational speed (f _ROT) of the impeller (20);

The method comprises the following steps:

receiving signals (E _p, P (i), P (j), P (q)) indicative of the rotational position of the rotatable impeller (20) relative to the housing,

Generating a position reference value (1; 1C,0%; 100%) based on the signals (E _p, P (i), P (j), P (q)), such that the position reference value is provided a first number of times in each rotation of the rotatable impeller (20), the first number of position reference values being indicative of a first number of predetermined rotational positions of the rotatable impeller (20), and

displaying on the screen display (210S):

a polar coordinate system having

Reference point (O), and

A reference direction (0, 360); and

A first internal state indicating object (S _P1、T_D1), the internal state being indicated at a first polar angle (T _D1,R_T (r); FI (r); X1) relative to the reference direction (0, 360), the first polar angle (T _D 1) indicating an angular position of the rotatable impeller (20) relative to the pump casing upon occurrence of the event signature (S _p (r); sp).

85. A computer-implemented method for generating and displaying information related to an internal state of a centrifugal pump (10) having a housing defining a volute (75) in which a rotatable impeller (20) is disposed for propelling fluid material (30) from a pump inlet (64) into the volute (75) upon rotation of the rotatable impeller (20), resulting in a fluid material flow having a pulsation (V _P) with a repetition frequency (f _R) that is dependent on a rotational speed (f _ROT) of the impeller (20);

The method comprises the following steps:

Receiving a signal (E _p, P (i), P (j), P (q)) comprising a reference position signal value (1; 1C,0%; 100%) indicative of at least one predetermined angular position of the rotatable impeller relative to the housing,

Detecting the occurrence of an event signature (S _p (r); sp, 205) in the time series of vibration sample values (Se (i), S (j), S (q));

-representing the internal state of the centrifugal pump (10) on a screen display (210S) by displaying on the screen display (210S):

a polar coordinate system, the polar coordinate system having:

reference point (O), and

A reference direction (0, 360); and

A first internal state indicating object (550; S _P1、T_D1), the internal state being indicated at a first polar angle (T _D1,R_T(r);T_D; FI (r); X1) relative to the reference direction (0, 360), the first polar angle (T _D 1) indicating an angular position of the rotatable impeller (20) relative to the pump casing when the event signature (S _p (r); sp, 205) occurs.

86. The method of any of the preceding examples, further comprising:

displaying on the screen display (210S):

The first internal state at a first radius (S _p1) from the reference point (O) is indicative of an object (S _P1、T_D1), the first radius (S _p1) being indicative of an amplitude of the pulsation.

87. The method of any of the preceding examples, wherein,

The impeller has the first number of blades.

88. The method of any of the preceding examples, wherein,

The predetermined rotational position is the position of the impeller blades relative to the pump outlet.

89. The method of any of the preceding examples, wherein,

The predetermined rotational position is a specific angular position of the impeller blade tips relative to the pump outlet.

90. The method of any of the preceding examples, wherein,

The predetermined rotational position is a particular angular position of the impeller blade tips relative to the volute tongue.

91. The method of any of the preceding examples, wherein,

The reference direction (0, 360) indicates a specific angular position of the rotatable impeller relative to the housing.

92. The method of any of the preceding examples, wherein,

The housing includes a volute tongue, and

The reference direction (0, 360) corresponds to a rotational position of the impeller blade tip in its closest position with respect to the volute tongue.

93. The method of any of the preceding examples, wherein,

The first polar angle (T _D1) is indicative of an instantaneous angular position of the rotatable impeller (20) relative to the pump casing when the event signature signal (S _p (r); sp) occurs during operation of the centrifugal pump.

94. The method of any of the preceding examples, wherein,

The specific angular position is the predetermined angular position such that the reference position signal value (1; 1c,0%; 100%) is indicative of the reference direction (0, 360).

Example 95 relates to a computer program for performing the method according to any of the preceding examples, the computer program comprising computer program code means adapted to perform the steps of the method according to any of the preceding examples when said computer program is run on a computer.

96. The computer program according to any of the preceding examples, embodied on a computer readable medium.

97. The system according to any of the preceding examples, wherein,

The housing includes at least two stationary vanes positioned between the volute and the impeller.

98. The system according to any of the preceding examples, wherein,

The housing comprises at least one stationary blade positioned at a radial distance from the rotation axis (60) of the impeller, said radial distance being greater than the radius of the impeller.

99. In a digital monitoring system for generating and displaying information related to an internal state of a centrifugal pump (10) having a housing defining a volute (75) in which a rotatable impeller (20) is disposed for urging fluid material (30) from a pump inlet (64) to an outlet (66) via the volute (75) upon rotation of the rotatable impeller (20);

a computer-implemented method of displaying the internal state of the centrifugal pump (10) on a screen display (210S),

The method comprises the following steps:

-receiving a signal (E _p, P (i), P (j), P (q)) comprising a reference position signal value (1; 1c,0 °,360 °) indicative of at least one predetermined angular position of the rotatable impeller relative to the housing, and

Receiving a vibration signal (S _FP;S_EA、S_MD, se (i), S (j), S (q)) dependent on the pulsation (P _FP) of the fluid material; the vibration signal comprises a time sequence of vibration sample values (S (q)), wherein the sample values (Se (i), S (j), S (q)) have amplitude values;

displaying on the screen display (210S):

a polar coordinate system having

Reference point (O), and

A reference direction (0, 360); and

Amplitude time plot (570, 570A) comprising at least one vibration sample value (S (q)), plotted as:

A polar angle (FI (q)) of the vibration sample relative to the reference direction (0 °,360 °), and

A vibration sample radius (S (q)) from the reference point (O); the vibration sample radius (S (q)) indicates the amplitude of the vibration sample value (S (q)).

100. The method of example 99, wherein,

The amplitude time graph (570, 570A) comprises at least a portion of the time series of vibration sample values (S (q)), wherein individual vibration sample values (S (q)) are plotted as:

-a single vibration sample polar angle (FI (q)) with respect to said reference direction (0 °,360 °), and having

-An individual vibration sample radius (S (q)) from the reference point (O); and wherein the first and second heat sinks are disposed,

-The vibration sample polar angle (FI (q)) corresponds to the angular position of the impeller (20) when the vibration sample value (S (q)) is detected during pump operation; and

The amplitude time plot (570, 570B) has a shape that is indicative of the internal state of the pump (10).

101. A method of operating a centrifugal pump (10) having a housing (62) with a rotatable impeller (20) disposed therein, the rotatable impeller (20) having a plurality (L) of blades for forcing fluid material (30) from a pump inlet (66) into a volute (75) as the rotatable impeller (20) rotates, the method comprising:

Receiving a vibration signal (S _FP;S_EA、S_MD, se (i), S (j), S (q)) dependent on the pulsation (V _P) of the fluid material;

Receiving signals (E _p, P (i), P (j), P (q)) indicative of a rotational position of the rotatable impeller (20) relative to the housing;

Information indicating an internal state of the centrifugal pump (10) is generated based on the vibration signal and the position signal.

102. The method of example 101 or any of the preceding examples, wherein,

The generating comprises extracting a first state value (FI, X1; FI (r); X1 (r)), indicative of an internal state of the centrifugal pump (10) during operation.

103. The method of example 102 or any of the preceding examples, wherein,

The generating includes generating an amplitude time map (570, 570A), wherein the amplitude time map (570) has a shape that is indicative of an internal state of the pump (10).

104. The method of example 103 or any of the preceding examples, wherein,

The amplitude time graph (570) shows a predetermined number (L) of signal signatures.

105. The method of any of the preceding examples, wherein,

The signal signature exhibits at least one highest amplitude peak and at least one lowest amplitude peak.

106. The method of any of the preceding examples, wherein,

During normal operation of the pump, the predetermined number (L) of signal signatures exhibit a uniform shape or a substantially uniform shape.

107. The method of any of the preceding examples, wherein,

When a single signal signature shows a shape that is different from the shape of other signal signatures, this deviation indicates that a fault exists.

108. The method of any of the preceding examples, wherein,

When a single signal signature exhibits a shape that deviates from the shape of other signal signatures, the deviation indicates that the physical feature associated with the blade (310) or the physical feature associated with the impeller channel (320) deviates from normal.

109. The method of any of the preceding examples, further comprising:

Detecting the occurrence of an event signature (S _p (r); sp) in a time sequence of vibration sample values (Se (i), S (j), S (q)); and

Based on the reference position signal value (1; 1C,0%; 100%) and the time series of vibration sample values (Se (i), S (j), S (q)), at the occurrence of an event signature (S _p (r); sp), data is generated representing the angular position (FI (r); X1) of the impeller (20) relative to the housing.

110. The method of any of the preceding examples, wherein,

The data indicative of the angular position is the first state value (FI (r); X1).

111. The method of any of the preceding examples, wherein,

Detecting a first occurrence of a first reference position signal value (1; 1C, 0%) in a time sequence of position signal sample values (P (i), P (j), P (q));

Detecting a second occurrence of a second reference position signal value (1; 1C; 100%) in the time sequence of position signal sample values (P (i), P (j), P (q));

Detecting a third occurrence of an event signature (S _p (r); sp) in the time series of vibration sample values (Se (i), S (j), S (q));

generating data indicative of a first duration between the first occurrence and the second occurrence; and

Generating data indicative of a second duration between the third occurrence and at least one of the first occurrence and/or the second occurrence;

generating data indicating a first relationship (FI, FI (r)) between

A second duration of time, and

A first duration.

112. The method of any of the preceding examples, wherein,

The data indicating the first relationship (R _T(r);T_D; FI (R); X1) is a first state value (R _T(r);T_D; FI (R); X1).

113. The method of any of the preceding examples, further comprising:

determining an internal state of the centrifugal pump (10) based on:

An operating point reference value (FI _REF (r)),

First relation (R _T(r);T_D; FI (R)), and

Operating point error value (FI _ERR (r)), wherein,

The operating point error value (FI _ERR (r)) depends on:

Operating point reference value (FI _REF (r)), and

First relation (R _T(r);T_D; FI (R))).

114. The method of any of the preceding examples, further comprising:

information indicating an internal state (X) of the centrifugal pump (10) is delivered to the user interface (210, 210S).

115. The method of any of the preceding examples, wherein,

The first state value (FI, X1; FI (r); X1 (r)) is based on:

The occurrence time of the fluid pressure pulsation event (S _p (r)); and

The time of occurrence of the rotation reference position.

116. The method of any of the preceding examples, wherein,

The first state value (X1; X1 (r)) is a time relation value (FI, FI (r)) based on:

The occurrence time of the fluid pressure pulsation event (S _p (r)); and

At least two times of occurrence of the rotation of the reference position.

117. A computer program product comprising a non-transitory computer readable storage medium having thereon a computer program comprising program instructions, the computer program loadable into one or more processors and configured to cause the one or more processors to perform the method of any of the preceding examples.

118. A computer program product comprising a non-transitory computer-readable storage medium having thereon the computer program of example 117.

119. A system for monitoring an internal state of a centrifugal pump (10), the system being configured to perform the method according to any of the preceding examples.

120. The system of example 119, further comprising one or more hardware processors configured to perform the method of any of the preceding examples.

121. A method of operating a centrifugal pump (10) having a housing forming a volute (75) in which a rotatable impeller (20) is disposed for pressing a fluid material (30) into the volute, the method comprising:

Monitoring a fluid pressure pulsation event within the pump casing;

Generating a vibration signal indicative of an occurrence of the first fluid pressure pulsation event based on the monitoring;

Generating a reference signal indicative of a rotational reference position of the rotating impeller;

The time relation value (FI, FI (r)) is determined based on:

the occurrence time of the fluid pressure pulsation event (S _p (r)); and

The reference signal.

122. The method of example 121, further comprising:

The operating parameters of the pump are determined based on:

the determined time relation value (FI, FI (r)).

123. The method of example 122, wherein,

The operating parameters include a rotational speed set point value (U1 _SP,f_ROTSP) for controlling the rotational speed (U1, f _ROT) of the impeller (20).

124. The method of any of the preceding examples, wherein,

The volute is an adaptive volute (75) having an adjustable cross-sectional area.

125. The method of example 124, wherein,

The operating parameters include a volute set point value (U2 _SP;V_PSP) for controlling the adjustable cross-sectional area.

126. The method of any of the preceding examples, wherein,

The volute is an adaptive volute (75) having:

a first adjustable cross-sectional area (A77), and

A second adjustable cross-sectional area (A78), wherein,

The operating parameters include a volute set point value (U2 _SP;V_PSP) for controlling the first and second adjustable cross-sectional areas simultaneously.

127. The method of any of the preceding examples, wherein,

The volute is an adaptive volute (75) having an adjustable volume, and wherein the operating parameter comprises a volute setpoint value (U2 _SP;V_PSP) for controlling the adjustable volute volume.

128. The method of any of the preceding examples, wherein,

The volute set point value (U2 _SP;V_PSP) controls the pump outlet fluid volume per revolution of the impeller.

129. The method of any of the preceding examples, wherein,

The time relation value (FI, FI (r)) is indicative of an internal state (205, 550, x) of the centrifugal pump (10).

130. The method of any of the preceding examples, wherein,

The time relation value (FI, FI (r)) is indicative of a current operating point (205, 550; x) of the centrifugal pump (10).

131. The method of any of the preceding examples, wherein,

The time relation value (FI, FI (r)) indicates a current operating point deviation (FI _DEV;FI_DEV (p+1); 550 (p+1)) from the optimum efficiency operating point of the centrifugal pump (10).

132. The method of any of the preceding examples, further comprising:

The determined operating parameters (U1, f _ROT;U2_SP;V_PSP) are displayed on a user interface as suggestions to the user.

133. The method of any of the preceding examples, further comprising:

A signal is sent to the regulator to change the operation of the pump to correspond to the determined operating parameter (U1, f _ROT;U2_SP;V_PSP).

134. The method of any of the preceding examples, wherein,

The volume of the adaptive volute is adjusted during pump operation.

135. The method of any of the preceding examples, wherein,

The time relation value (FI, FI (r)) is based on:

the occurrence time of the fluid pressure pulsation event (S _p (r)); and

The time of occurrence of the rotational reference position.

136. The method of any of the preceding examples, wherein,

The time relation value (FI, FI (r)) is based on:

The occurrence time of the fluid pressure pulsation event (S _p (r)) and the at least two occurrence times of the rotational reference position.

137. A computer program product comprising a non-transitory computer readable storage medium having thereon a computer program comprising program instructions, the computer program being loadable into one or more processors and configured to cause the one or more processors to perform the method of any of the preceding examples.

138. A system for operating a centrifugal pump (10), the system being configured to perform the method according to any of the preceding examples.

139. The system of example 138, further comprising one or more hardware processors configured to perform the method of any of the preceding examples.

140. The system of examples 138 or 139, further comprising a centrifugal pump having:

An impeller; and

An adaptive housing (62A) forming an adaptive volute (75A) in which the impeller is disposed, the adaptive housing (62A) having an inlet for receiving fluid from an external environment and an outlet for discharging the adaptive volute fluid propelled by the impeller, the adaptive housing (62A) being configured to adjust the volute volume based on the determined at least one operating parameter.

141. A centrifugal pump (10) having a housing forming a volute (75; 75A) in which is disposed a rotatable impeller (20) for pressing fluid material (30) into the volute, resulting in fluid pressure pulsations (P _FP);

The centrifugal pump includes:

A sensor for generating a signal (S _FIMP;S_EA、S_MD, se (i), S (j), S (q)) indicative of the fluid pressure pulsation (P _FP).

142. The centrifugal pump (10) according to any of the preceding examples, wherein,

The sensor (70, 70 ₇₈、70₇₇) is attached to the housing (62) of the pump.

143. The centrifugal pump (10) according to any of the preceding examples, wherein,

The sensor (70, 70 ₇₈、70₇₇) is mounted on the pump housing (62) for generating a vibration signal (S _EA、S_MD, se (i), S (j), S (q)) from the fluid material pressure pulsation (P _FP).

144. The centrifugal pump (10) according to any of the preceding examples, wherein,

The sensor (70, 70 ₇₈、70₇₇) includes an accelerometer.

145. The centrifugal pump (10) according to any of the preceding examples, wherein,

The sensor (70, 70 ₇₈、70₇₇) includes an accelerometer including a sensor configured to generate the signal (S _FIMP;S_EA、S_MD, se (i), S (j), S (q)) indicative of the fluid pressure pulsation (P _FP).

146. The centrifugal pump (10) according to any of the preceding examples, wherein,

The sensor (70, 70 ₇₈、70₇₇) includes a semiconductor silicon substrate configured as a MEMS accelerometer.

147. The centrifugal pump (10) according to any of the preceding examples, wherein,

The sensor (70, 70 ₇₈、70₇₇) includes a piezoelectric accelerometer configured to generate the signal (S _FIMP;S_EA、S_MD, se (i), S (j), S (q)) indicative of the fluid pressure pulsation (P _FP).

148. The centrifugal pump (10) according to any of the preceding examples, wherein,

The sensor (70, 70 ₇₈、70₇₇) is a piezoresistive sensor configured to generate the signal (S _FIMP;S_EA、S_MD, se (i), S (j), S (q)) indicative of the fluid pressure pulsation (P _FP).

149. The centrifugal pump (10) according to any of the preceding examples, wherein,

The sensor (70, 70 ₇₈、70₇₇) is an acceleration sensor configured to generate the signal (S _FIMP;S_EA、S_MD, se (i), S (j), S (q)) indicative of the fluid pressure pulsation (P _FP).

150. The centrifugal pump (10) according to any of the preceding examples, wherein,

The sensor (70, 70 ₇₈、70₇₇) comprises a coil and magnet arrangement configured to generate an acceleration signal (S _FIMP;S_EA、S_MD, se (i), S (j), S (q)) indicative of the fluid pressure pulsation (P _FP).

151. The centrifugal pump (10) according to any one of the preceding examples, further comprising:

A position marking device (180) for causing the position sensor (170) to generate an impeller rotation marking signal (EP; P _S).

151. The centrifugal pump (10) according to any of the preceding examples, wherein,

The position marking device (180) is arranged in connection with the impeller (20) such that when the impeller (20) rotates about the rotation axis (60), the position mark (180) passes the position sensor (170) at least once per rotation of the impeller.

152. The centrifugal pump (10) according to any of the preceding examples, wherein,

The position-marking device (180) includes a reflective strip (180) attached to a rotating member associated with the pump.

153. The centrifugal pump (10) according to any one of the preceding examples, further comprising:

A position sensor (170) for generating a position signal (EP, PS, P (i), P (j), P (q)) in cooperation with the position-marking device (180).

154. The centrifugal pump (10) according to any of the preceding examples, wherein,

The position sensor (170) comprises a light source (170), for example a laser light source.

155. The centrifugal pump (10) according to any of the preceding examples, wherein,

The position sensor (170) comprises a light source (170) for generating position signals (EP, PS, P (i), P (j), P (q)) in cooperation with the reflection band (180).

156. The centrifugal pump (10) according to any of the preceding examples, wherein,

The position-marking device (180) comprises a metal part (180) or a magnetic part (180).

157. The centrifugal pump (10) of example 156, wherein,

The position sensor (170) includes an inductive probe (170) configured to detect the presence of the metallic component (180) or magnetic component (180).

158. The centrifugal pump (10) according to any of the preceding examples, wherein,

The position sensor (170) comprises a hall effect sensor (170) for generating the position signal (EP, PS, P (i), P (j), P (q)).

159. The centrifugal pump (10) according to any of the preceding examples, wherein,

The position marker device (180) is mounted on a shaft connected to the impeller (20).

160. A centrifugal pump arrangement (5; 10;730;780; 720) comprising a centrifugal pump (10) according to any of the preceding examples.

161. The centrifugal pump apparatus (730; 780; 720) of example 160, further comprising:

a first centrifugal pump apparatus data port (800, 820) connectable to a communication network;

A first centrifugal pump apparatus communication device (790) configured to communicate via the first centrifugal pump apparatus data port (820):

Data indicating the vibration signal (S _FIMP;S_EA、S_MD, se (i), S (j), S (q)).

162. The centrifugal pump apparatus (730; 780; 720) of example 160, further comprising:

Data (S _FIMP;S_EA、S_MD, se (i), S (j), S (q)) indicative of the vibration signal, and

Data (E _p, P (i), P (j), P (q)) indicative of the position signal.

163. The centrifugal pump apparatus (730; 780; 720) of example 160, further comprising:

A sensor for generating a signal (S _FIMP;S_EA、S_MD, se (i), S (j), S (q)) indicative of the fluid pressure pulsation (P _FP),

A position sensor for generating signals (E _p, P (i), P (j), P (q)) indicating the rotational position of the impeller, and

Data (E _p, P (i), P (j), P (q)) indicative of the position signal.

164. The centrifugal pump apparatus according to any of the preceding examples, wherein the communication network comprises the world wide web, also known as the internet.

165. The centrifugal pump apparatus of any of examples 161-164, further comprising:

A second centrifugal pump apparatus data port (800B; 820B) connectable to a communication network;

a second centrifugal pump apparatus communication device (790B) configured to communicate with a second centrifugal pump apparatus via said second centrifugal pump apparatus data port (800B; 820B):

Data (FI; X1 (r); X2; sp (r); X5, fROT) indicative of the internal state of the centrifugal pump.

165. The centrifugal pump apparatus of any of the preceding examples, further comprising:

a second centrifugal pump apparatus communication device (790B) configured to communicate with said second centrifugal pump apparatus data port (800B; 820B):

Data (R _T(r);T_D;FI(r);X1(r);X2,Sp(r),f_ROT,dR_T (R); dSp (R)) indicative of the operating point (205) of the centrifugal pump.

166. The centrifugal pump apparatus of any of the preceding examples, further comprising:

a human-machine interface (HCI; 210) for enabling user input/output; and

The human-machine interface (HCI; 210) is configured to display data (FI; X1 (r); X2, sp (r); X5, fROT) indicative of the internal state (X) of the centrifugal pump on the screen display (210S).

167. The centrifugal pump apparatus of any of the preceding examples, further comprising:

a human-machine interface (HCI; 210) for enabling user input/output; and

The human-machine interface (HCI; 210) is configured to display data (FI; X1 (r); X2, sp (r); X5, fROT) indicative of an operating point (205) of the centrifugal pump on the screen display (210S).

168. The centrifugal pump apparatus of any of the preceding examples, wherein:

the second centrifugal pump apparatus communication device (790B) is

The first centrifugal pump apparatus communication device (790), and

The second centrifugal pump apparatus data port (800B; 820B) is

The first centrifugal pump apparatus data port (820).

169. The centrifugal pump apparatus of any of the preceding examples, further comprising:

a control module (150, 150B) configured to receive the data (FI; X1 (r); X2, sp (r); X5, fROT) indicative of an internal state of the centrifugal pump.

170. The centrifugal pump apparatus of any of the preceding examples, wherein:

The control module (150, 150B) comprises:

a regulator (755) configured to control a rotational speed (U1, fROT) of the impeller (20) based on the data (FI; X1 (r); X2, sp (r); X5, fROT) indicative of an internal state of the centrifugal pump; and/or

A regulator configured to control a rotational speed (f _ROT) of an impeller (20) based on the data (FI; X1 (r); X2, sp (r); X5, fROT) indicative of an internal state of the centrifugal pump; and/or

An adjustor configured to control an adjustable volute volume of the centrifugal pump based on the data (FI; X1 (r); X2, sp (r); X5, fROT) indicative of an internal state of the centrifugal pump.

171. The centrifugal pump apparatus of any of the preceding examples, wherein:

The control module (150, 150B) comprises:

A regulator (755) configured to control the rotational speed (U1, fROT) of the impeller (20) based on the value (FI (r)) indicative of the operating point (205) of the centrifugal pump, and/or

A regulator configured to control an adjustable volute volume of the centrifugal pump based on the value (FI (r)) indicative of an operating point (205) of the centrifugal pump.

172. A monitoring device (870; 880; 150A) for cooperation with a centrifugal pump device according to any one of the preceding examples or according to any one of examples 160 to 171,

The monitoring device includes:

a monitoring device data port (920, 920A) connectable to a communication network (810) for data exchange with the centrifugal pump device; wherein,

The monitoring device (870; 880; 150A) is configured to receive via the monitoring device data port (920, 920A):

Data indicating vibration signals (S _FIMP;S_EA、S_MD, se (i), S (j), S (q)); and

Data indicating position signals (E _P, P (i), P (j), P (q));

The monitoring device (870; 880; 150A) further comprises:

a state parameter extractor (450) configured to generate data (FI; X1 (r); X2, sp (r); X5, fROT) indicative of an internal state of the centrifugal pump based on the vibration signal and the position signal.

173. A monitoring device (870; 880; 150A) for cooperation with a centrifugal pump device according to any one of the preceding examples or according to any one of examples 160 to 171,

The monitoring device includes:

Data indicating vibration signals (S _FIMP;S_EA、S_MD, se (i), S (j), S (q));

The monitoring device (870; 880; 150A) further comprises:

A state parameter extractor (450) configured to generate data (FI (r); X1 (r); X2, sp (r); X5, f _ROT) indicative of an internal state of the centrifugal pump based on the vibration signal.

174. The monitoring device of any of the preceding examples, wherein:

The monitoring device (870; 880; 150A) is configured to transmit to the centrifugal pump device via the monitoring device data port (920, 920A):

data (FI; X1 (r); X2, sp (r); X5, fROT) indicating the generation of the internal state of the centrifugal pump.

175. The monitoring device according to any of the preceding examples, wherein the monitoring device (870; 880;150 a) is configured to generate and transmit to the centrifugal pump device:

A value (R _T(r);T_D; FI (R)) indicative of the operating point (205) of the centrifugal pump.

176. An assembly for mating with a centrifugal pump device according to any one of the preceding examples or according to any one of examples 160-171, the assembly comprising:

A monitoring module (150; 150A),

A control module (150; 150B), and

At least one component data port (920, 920a,920 b) connectable to a communication network (810) for exchanging data with the centrifugal pump apparatus; wherein,

The monitoring module (150; 150A) is configured to receive via the component data port (920, 920A):

Data (S _FIMP;S_EA、S_MD, se (i), S (j), S (q)) indicating the vibration signal, and

Data (E _P, P (i), P (j), P (q)) indicating the position signal;

a monitoring module (150; 150A) is configured to generate data (FI; X1 (r); X2, sp (r); X5, fROT) indicative of an internal state of the centrifugal pump based on the vibration signal and the position signal,

The control module (150; 150B) is arranged to communicate with the centrifugal pump apparatus via an assembly data port (920, 920B), and

The control module (150, 150B) comprises:

A regulator (755) configured to control a rotational speed (U1, fROT) of an impeller (20) based on the data (T _D;FI(r);R_T(r);X1(r);X2,Sp(r);X5,f_ROT) indicative of an internal state of the centrifugal pump; and/or

177. The assembly according to any of the preceding examples, wherein the assembly is arranged at a location geographically remote from the centrifugal pump (10).

Claims

1. A method of operating a centrifugal pump (10) having a housing (62) with a rotatable impeller (20) disposed therein, the rotatable impeller (20) having a plurality (L) of blades for forcing fluid material (30) from a pump inlet (66) into a volute (75) upon rotation of the rotatable impeller (20), the method comprising:

receiving a vibration signal (S _FP;S_EA,S_MD, se (i), S (j), S (q)) from the fluid material pulsation (V _p);

Receiving a signal (E _p, P (i), P (j), P (q)) indicative of a rotational position of the rotatable impeller (20) relative to the housing;

2. The method of claim 1, wherein,

The generating comprises extracting a first state value (FI, X1; FI (r); X1 (r)) indicative of an internal state of the centrifugal pump (10) during operation.

3. The method according to claim 1 or 2, wherein,

4. The method according to any of the preceding claims, wherein,

The amplitude time graph (570) displays a predetermined number (L) of signal signatures.

5. The method according to any of the preceding claims, wherein,

6. The method according to any of the preceding claims, wherein,

During normal operation of the pump, a predetermined number (L) of signal signatures exhibit a uniform shape or a substantially uniform shape.

7. The method according to any of the preceding claims, wherein,

When a single signal signature shows a shape that deviates from the shape of other signal signatures, the deviation indicates that there is a fault.

8. The method according to any of the preceding claims, wherein,

When a single signal signature shows a shape that deviates from the shape of other signal signatures, the deviation indicates that the physical feature associated with the blade (310) or the physical feature associated with the impeller channel (320) deviates from normal.

9. The method of any of the preceding claims, further comprising:

detecting the occurrence of an event signature (Sp (r); sp) in the time series of vibration sample values (Se (i), S (j), S (q)); and

Based on a time sequence of reference position signal values (1; 1C,0%; 100%) and the vibration sample values (Se (i), S (j), S (q)), data are generated indicating an angular position (FI (r); X1) of the impeller (20) relative to the housing when the event signature (Sp (r); sp) occurs.

10. The method according to any of the preceding claims, wherein,

The data indicative of the angular position is a first state value (FI (r); X1).

11. The method according to any of the preceding claims, wherein,

detecting a third occurrence of an event signature (Sp (r); sp) in the time sequence of vibration sample values (Se (i), S (j), S (q));

generating data indicative of a first relationship (FI, FI (r)) between:

The second duration, and

The first duration.

12. The method according to any of the preceding claims, wherein,

13. The method of any of the preceding claims, further comprising:

-determining the internal state of the centrifugal pump (10) based on:

An operating point reference value (FI _REF (r)),

First relation (R _T(r);T_D; FI (R)), and

Operating point error value (FI _ERR (r)), wherein,

The operating point error value (FI _ERR (r)) depends on:

The operating point reference value (FI _REF (r)), and

The first relationship (R _T(r);T_D; FI (R)).

14. The method of any of the preceding claims, further comprising:

Information indicative of an internal state (X) of the centrifugal pump (10) is conveyed to a user interface (210, 210S).

15. The method according to any of the preceding claims, wherein,

The first state value (FI, X1; FI (r); X1 (r)) is based on:

the time of occurrence of the fluid pressure pulsation event (Sp (r)); and

The time of occurrence of the rotation reference position.

16. The method according to any of the preceding claims, wherein,

the time of occurrence of the fluid pressure pulsation event (Sp (r)); and

At least two times of occurrence of the rotation of the reference position.

17. A computer program product comprising a non-transitory computer readable storage medium having thereon a computer program comprising program instructions, the computer program being loadable into one or more processors and configured to cause the one or more processors to perform the method of any of the preceding claims.

18. A system for monitoring an internal state of a centrifugal pump (10), the system being configured to perform the method according to any one of claims 1-16.

19. The system of claim 18, further comprising one or more hardware processors configured to perform the method of any of claims 1-16.