EP2326842A1

EP2326842A1 - Method for early detection of damage to valves in oscillating displacement pumps and oscillating displacement pumps comprising a built-in sensor system for using in said method

Info

Publication number: EP2326842A1
Application number: EP09743879A
Authority: EP
Inventors: Ronald Schmidt; Eberhard Schlücker; Piotr Reichel-Lesnianski; Peter Pawlitzki
Original assignee: Schafer & Urbach & Co KG GmbH; Friedrich Alexander Univeritaet Erlangen Nuernberg FAU
Current assignee: Schaefer & Urbach GmbH; Friedrich Alexander Univeritaet Erlangen Nuernberg FAU
Priority date: 2008-09-25
Filing date: 2009-09-14
Publication date: 2011-06-01
Anticipated expiration: 2029-09-14
Also published as: WO2010034632A1; DE102008037393B4; EP2326842B1; DE102008037393A1

Abstract

The invention relates to a method for the early detection of damage to valves in oscillating displacement pumps comprising at least three cylinders with or without a common pump head, by signal-based evaluation of measured pressure and structure-borne noise signals, digitalisation of the pressure signals, calculation of correlation coefficients by means of covariance analysis using the distribution of the structure-borne noise on each cylinder in the absence of a common pump head, or using fictive oscillation acceleration signals for each cylinder and associating valve damage to a cylinder in the presence of a common pump head, and triggering an alarm if pre-defined threshold values for the correlation coefficients are exceeded or not reached. The invention also relates to oscillating displacement pumps with integrated sensors for use in said method.

Description

Method for the early detection of valve damage in oscillating positive displacement pumps and oscillating positive displacement pumps with integrated sensors for use in these methods

Field of the invention

The present invention relates to novel methods for the early detection of valve damage in oscillating positive displacement pumps.

Moreover, the present invention relates to new oscillating displacement pumps with integrated sensors for non-invasive pressure measurement and non-invasive measurement of structure-borne noise.

Last but not least, the present invention relates to the novel use of the new reciprocating positive displacement pumps for the new methods of early detection of valve damage.

State of the art

Oscillating positive displacement pumps transfer energy to liquids through a (oscillating) displacer reciprocating in the pump working space. The oscillating movement of the displacer (rigid piston, elastic membrane or bellows) causes a periodic increase and decrease in the working space, the demarcation compared to pressure and suction line by valves, especially automatic valves, takes place.

An essential feature of oscillating positive displacement pumps is the principle-related separation of the pressure and suction lines by at least one closed valve. In contrast to rotating positive displacement pumps and centrifugal pumps, virtually no leakage flows occur as long as the valves are tight.

The performance-related delimitation of the pump working space is almost exclusively carried out by automatic valves. In order to ensure that the valves close and open without significant delay, careful design of all components, such as the geometry of the closing body and seat, feathering, materials, etc., is indispensable. Typical problems due to faulty valves are overpressure peaks when opening the pressure valves, negative pressure peaks when opening the suction valves, high noise emission and above all faster wear. The valve design and valve damage therefore have a major impact on the reliability and efficiency of the pumps.

As is known, the suction and pressure valves are subject to constant wear, which has a negative effect on the delivery rate and the dosing accuracy. In practice, it is therefore attempted to avoid this problem by exchanging the valves in good time from experience. Nevertheless, it can not be avoided that valves fail prematurely, often without warning. This causes unwanted economic and technical consequential damage due to the then necessary immediate business interruption.

The operators of oscillating positive displacement pumps are therefore anxious to valve damage in the early stages, d. H. as early as possible in order to be able to take timely appropriate action long before it can lead to serious injury leading to a pump shutdown with long downtime. Frequently, however, this fails because the previously known methods for early detection have a low sensitivity, which is insufficient to detect valve damage in the early stages, when the flow losses are still low. Or they require a sophisticated sensor technology for the detection of numerous different data, which must be evaluated in a complex manner.

As is known, a leaking pressure valve leads to a rapid pressure increase in the

Compression phase and a slower pressure reduction in the decompression phase.

In the case of a defective suction valve, the conditions are just the opposite: As a result of the leakage flow into the suction line more piston travel is required for compression; the

Relaxing to the level of suction pressure is completed faster. The concerned

Damage can be detected using indicator graphs for the pressure history.

In addition, these damages lead to an increased emission of structure-borne noise

Opening and closing the valves.

In principle, the pressure curve and structure-borne noise can be used to detect valve damage.

The following references provide an overview of the previously known methods for early fault detection on oscillating positive displacement pumps: Falko Haus, Methods for Early Disturbance Detection on Oscillating Positive Displacement Pumps, Progress Reports VDI, Series 8, Measurement and Control Technology, No. 1109, Reports from the Institute of Automation Technology of the TU Darmstadt, VDI Verlag GmbH, Düsseldorf, 2006, and

Ulrich Klapp, Monitoring and Fault Diagnosis of Oscillating Positive Displacement Pumps, Dissertation, 2004, Publication Series of the Department of Process Machinery and Systems Engineering, Friedrich-Alexander-University Erlangen-Nuremberg, Shaker Verlag, Aachen, 2005.

The plant condition monitoring by deep diagnostic evaluation of structure-borne sound signals using the embedded PC technology is by R. Schmidt, E. Schlucker and O. Schade, Chair of Process Machinery and Plant Engineering, Friedrich-Alexander-University Erlangen-Nuremberg, in the lecture "System Condition Monitoring by Deep Diagnostic Evaluation of structure-borne sound signals "on the occasion of the Processnet in Aachen in October 2007 described.

In his dissertation, Ulrich Klapp already describes that the structure-borne noise emitted by a pump can be evaluated on the basis of the statistical relationship between pressure and sound signal using Pearson's correlation coefficient. This

Correlation coefficient is dimensionless and can take values between -1 and +1.

While correlation coefficients of -1 and +1 indicate a completely negative or positive linear relationship of the two signals, a value of 0 or close to 0 means that the time courses of structure-borne sound and pressure are independent of each other

Vibration is dominated by closing the valves: While the suction valve closes at low pressure, the pressure valve responds at delivery pressure. Consequently, there is no correlation between vibration intensity and pressure level. Thus, the formation of the correlation coefficient enables an evaluation of the sound signal of the pump, without having to know reference values for the undisturbed state. However, this concept is only tested on a simplex pump with a cylinder.

Method for early fault detection on oscillating displacement pumps by monitoring the pulsation of the flow or the pressure at the pressure side are described in German Patent DE 196 25 947 C1. Methods for monitoring and automatic early fault detection of valves by measuring the structure-borne noise or operating noise and their comparison with a reference signal level formed by the operating noise of the pump with intact valves are described in the German patent DE 103 22 220 2004.10.07.

Object of the present invention

The present invention was based on the object to find new methods for the early detection of valve damage in oscillating displacement with three or more cylinders, which no longer have the disadvantages of the prior art, but which allow, with little effort metrologically, d. H. without complex sensors, and with little effort in the evaluation quickly, reliably and with high sensitivity valve damage already in the initial stage, when the flow losses are still low to detect. This should make it possible to take timely countermeasures well before it can lead to serious injury, which leads to a pump shutdown with long downtime.

In addition, the new methods should allow in a simple way to determine which valves (pressure valves or suction valves) have damage and in which cylinders they are located.

Furthermore, the object of the invention was to provide new oscillating displacement pumps which are particularly suitable for use in the new methods.

Inventive solution

Accordingly, the new method for early detection of valve damage in an oscillating positive displacement pump with three or more cylinders, each comprising a driven displacer, a cylinder housing, a working space, a suction valve, a pressure valve and a cylinder head, found by signal-based evaluation of measured pressure and structure-borne sound signals, which comprises the following method steps:

(1) Pressure measurement on each cylinder by means of strain gages DMS, (2) digitizing the measured strain gauge signals by approximation by a rectangular function to find the rising and falling edges of the pressure profile for each cylinder,

(3) determination of the course of structure-borne noise during the suction stroke and during the pressure stroke at each cylinder head by measuring the vibration acceleration and calculation of the effective values a _ef τ,

(4) Calculation of the correlation coefficient r _{a, p} between the increase in the vibration acceleration of the structure-borne sound and the digitized pressure profile for each piston by covariance analysis, wherein a positive correlation coefficient r _{a, p} exceeding a predetermined threshold, a defect on the suction valve and a negative correlation coefficient r _ap , which falls below the predetermined threshold, indicates a defect in the pressure valve, and

(5) automatic triggering of an alarm if it exceeds or falls below the predetermined threshold value for the correlation coefficient r _ap .

In addition, the new method of early detection of multiple valve failures in a reciprocating positive displacement pump having three or more cylinders with a common pumphead, the cylinders each comprising a driven displacer, a cylinder housing, a working space, a suction valve and a pressure valve, has been measured by signal-based evaluation of measured pressure. and structure-borne sound signals found, comprising the following steps:

(1) Pressure measurement on each cylinder by means of strain gages DMS,

(2) digitizing the pressure profile determined on the basis of the measured strain gage signals by approximation by a rectangular function for finding the rising and falling edges of the pressure profile for each cylinder,

(3) Determination of the structure of structure - borne noise during the suction stroke and during the pressure stroke at a point of the pump head, where the structure of the structure - borne noise has the greatest sensitivity with the least noise, by measuring the vibration acceleration and calculating the effective values a _ef τ in the damaged state Pump, (4) calculation of two fictitious vibration acceleration signals for each cylinder from the measured vibration acceleration in the damage state of the pump such that once for the purposes of Saugventiltests during the suction stroke and for purposes of the pressure valve test once during the compression stroke of the measured

Course is replaced by a substitute value,

(5) Calculation of the correlation coefficient r _{a, p} between the calculated fictitious vibration acceleration signals and the digitized pressure curve in the damage state of the pump by covariance analysis, wherein a positive

Correlation coefficient r _{a, p} in the Saugventiltest that exceeds a predetermined threshold, a defect in at least one suction valve and a negative correlation coefficient r _{a, p} in the pressure valve test that falls below a predetermined threshold, indicates a defect in at least one pressure valve,

(6) Assignment of a valve damage to a cylinder by comparing the effective values a _eff of structure-borne noise in the damage state during a stroke of a displacer with the effective values a _e n on the flanks of the digitized pressure curve in the damage state, where an assignment to a cylinder is given the effective value a _e n changes exactly with the edges of a displacement stroke, as well

(7) automatic triggering of an alarm when exceeding and / or falling below predetermined threshold values for the correlation coefficient r _{a, p} .

In the following, the new methods are collectively referred to as "methods according to the invention".

Furthermore, the new oscillating displacement pump with three or more cylinders, each comprising a driven displacer, a cylinder housing, a working space, a suction valve, a pressure valve and a cylinder head, found in which at each cylinder on a wall to the working space, a strain gauge DMS not Invasive pressure measurement and a sensor for non-invasive measurement of structure-borne noise with the necessary electrical connection points for power supply lines and signal derivatives are integrated. Not least, the novel reciprocating positive displacement pumps having three or more cylinders with a common pump head, the cylinders each comprising a driven displacer, a cylinder housing, a working space, a suction valve, a pressure valve and a cylinder head, have been found on each cylinder on a wall to the working space a strain gauge strain gauge for non-invasive pressure measurement and at a point of the pump head on which the course of structure-borne noise has the greatest sensitivity with the least noise, in addition a sensor for non-invasive measurement of structure-borne noise with the required electrical connection points are integrated.

In the following, the new oscillating displacement pumps are collectively referred to as "positive displacement pumps according to the invention".

Furthermore, the use of the positive displacement pump according to the invention was found in the inventive method, which is hereinafter referred to as "inventive use".

Advantages of the invention

In view of the prior art, it was surprising and unforeseeable for the skilled person that the object on which the present invention was based could be achieved by means of the processes according to the invention, the positive displacement pumps according to the invention and the use according to the invention.

In particular, it was surprising that the processes according to the invention, the positive-displacement pumps according to the invention and the use according to the invention made it possible, with little technical effort, ie. H. without costly sensor technology, and with little effort in the evaluation quickly, reliably and with high sensitivity valve damage already in the initial stage, when the flow losses were still low to detect. This made it possible to take timely countermeasures well before it could lead to serious injury leading to a pump downtime with long downtime.

It was particularly surprising that the methods according to the invention allowed to easily determine, without sensors on each valve, which valves (pressure valves or suction valves) were damaged and in which cylinders they were located. Furthermore, it was surprising that the positive displacement pump according to the invention could be produced without much additional effort, were very robust and of long service life and could be operated for a particularly long time at constant high flow rates due to their excellent monitoring capabilities.

Overall, oscillating positive displacement pumps and in particular the positive displacement pumps according to the invention could be excellently monitored by the methods according to the invention also remotely, for example via the Internet or via computer leased lines. Therefore, a large number of oscillating positive displacement pumps could be centrally monitored at different locations, which is a further particular advantage of the invention.

In addition, surprisingly, there were other special advantages:

The methods according to the invention no longer require a trigger signal, which is why triggering or incremental encoders could be dispensed with in the positive-displacement pumps according to the invention, which simplified their production.

In the methods according to the invention, the sensors no longer had to be calibrated, since the methods according to the invention were based on normalized signal changes.

For the purposes of the method according to the invention, the sensors could be mounted on the oscillating positive displacement pumps within certain limits where the mounting involved the least expenditure. This also facilitated the production of the positive displacement pump according to the invention, which was technically and economically advantageous.

Detailed description of the invention

The methods according to the invention are used for the early detection of valve damage in oscillating positive displacement pumps.

The oscillating displacement pumps have three or more, preferably three to five and in particular three cylinders. Each cylinder includes a driven displacer. Preferably, the displacer is a plunger, a mechanically hinged membrane or a hydraulically articulated membrane, in particular a plunger. Accordingly, the oscillating positive displacement pump is a plunger pump, a diaphragm pump with a mechanically articulated membrane or a hydraulically articulated diaphragm pump or piston diaphragm pump, in particular a plunger pump.

The drive for the displacer may be a Geradschubkurbelantrieb, a Federnockentriebwerk with phase-controlled stroke adjustment or a magnetic linear drive. Preferably, a Geradschubkurbelantrieb is used.

In addition, the cylinder comprises a cylinder housing, a working space, a suction valve, a pressure valve and a cylinder head.

The cylinders of the oscillating positive displacement pumps, in particular the oscillating positive displacement pumps according to the invention, can also have a common pump head.

The suction valve and the pressure valve are preferably automatic. Preferably, loaded ball valves, plate valves, mushroom valves or conical valves are used.

To carry out the method according to the invention, the oscillating displacement pumps, in particular the positive displacement pumps according to the invention, can still be equipped with a conventional and known trigger or incremental encoder, by means of which the speed of the pump can be determined if necessary. However, it is a very particular advantage of the inventive method and the oscillating displacement pump according to the invention that no trigger is needed.

The oscillating positive displacement pumps, in particular the oscillating positive displacement pumps according to the invention, can be used in many ways. In particular, they can be used as metering pumps, for example for precise metering of fluids in the laboratory, as industrial pumps, for example in chemical plants, process plants and in refinery technology, or as flushing pumps, for example, for horizontal and deep drilling in the oil industry, construction or geothermal. there The delivered volume flows can be up to several 100 m ³ / h at working pressures up to several 1,000 bar.

The first method according to the invention is particularly well suited for the early detection of valve damage in an oscillating positive displacement pump, in particular in an oscillating positive displacement pump according to the invention, in which each cylinder has its own cylinder head. The inventive method is based on the signal-based evaluation of measured pressure and structure-borne sound signals.

In this case, the pressure in the working space of each cylinder by means of strain gauges DMS, which on the wall to the working space, e.g. are mounted on the circumference of the piston liners, measured. It is a further particular advantage of the methods according to the invention that all conventional and known types of strain gauges DMS can be used.

The pressure measurement is preferably carried out piezoelectrically by means of semiconductor DMS. The resulting strain gage signal does not have to be calibrated, but it is sufficient to indicate the pressure in volts, because it depends solely on the pressure change when opening and closing the valves in the suction and pressure stroke.

To evaluate the measured DMS signals, the pressure curve is digitized, d. H. , the measured pressure profile is approximated by a rectangular function to find the rising and falling edges of the pressure profile for each cylinder. The times or the crank angles of the flanks then correspond to the respective end points of the suction and compression strokes.

Preferably, to determine the pressure curve, the maximum or minimum pressure measured during the entire recording is determined and its difference divided into 100 equal intervals. Then, the relative frequency at which each data point falls within one of the 100 intervals is determined. The absolute maximum in the thus determined histogram above the 50th interval is considered to be the mean pressure of the pressure stroke, and the absolute maximum below the 50th interval is considered to be the mean pressure of the suction stroke.

For the purpose of the advantageous evaluation of the structure-borne noise, in the approximation at the lower and upper dead centers, the displacer is preferably in each case a window of preferably ± 5% of the stroke is hidden. This means that the pressure profile is first digitized and then the rising and falling edges are determined. Around the detected edges around then the blanking window is placed. The partial strokes of the individual pistons at the beginning and at the end of the measurement are completely ignored in each case, ie the evaluation basically begins with the first edge in the digital pressure curve and ends at the last edge. This procedure is easy to automate.

The course of the structure-borne noise during the suction stroke and during the pressure stroke is determined on each cylinder by the measurement of the vibration acceleration in volts and the calculation of the effective values a _e n. As is known, the effective value of a _e n can by using the equation (1) or calculated by using the equation (2) can be approximately calculated:

Preferably, the rms values a _{eff are} calculated using equation (1), the integral preferably being calculated according to the chordal trapezoidal method

To measure structure-borne noise, the usual and known sensors can be used.

Preferably, the vibration acceleration is measured by means of conventional and known piezoelectric accelerometer as sensors, since they have better dynamics compared to displacement and fast sensors.

All conventional and known data processing systems can be used for the storage and evaluation of the measured signals, provided that they have sufficient computing and storage capacity. Preferably, an embedded PC is used, as described by R. Schmidt, E. Schlucker and O. Schade, Department of Process Machinery and Plant Engineering, Friedrich Alexander University Erlangen -Nuremberg, in "system condition monitoring by deep diagnostic evaluation of structure-borne sound signals", lecture held at Processnet, Aachen, October 2007.

In the next method step, the correlation coefficient r _{a, p} between the increase in the vibration acceleration of the structure-borne noise and the digitized pressure curve for each cylinder is calculated by covariance analysis. As is known, equation (3) can be used for this purpose:

The correlation coefficient r _{a, p} is the normalized covariance of the two signals pressure and structure-borne sound. A value of the correlation coefficient near +1 or -1 indicates a high positive or negative linear relationship of the two signals, while a value of 0 indicates that the time courses of structure-borne sound and pressure are independent or at least correlate nonlinearly.

Physically, it is exploited that, in the case of a damaged suction valve, fluid is forced back out of the working space onto the suction side during the pressure stroke, which then begins to cavitate as it flows through the narrow damaged area. The resulting in the cavitation noise cause an increase in the vibration acceleration of structure-borne noise during the compression stroke and thus a better correlation of structure-borne noise with the pressure curve as in the faultless state.

Damage to pressure valves can be detected by the same principle. Here then, however, the backflow of the fluid from the pressure side into the working space is responsible for the increased generation of noise.

Thus, a positive correlation coefficient r _{a, p} indicates a defect at the suction valve, whereas a negative correlation coefficient r _ap indicates a pressure valve leakage.

The calculation of the correlation coefficient r _ap can likewise easily be automated. Preferably, the measured structure-borne sound signals and the pressure profile are measured continuously or at intervals and automatically evaluated in data processing systems, and the resulting correlation coefficients r _{a, p} are stored permanently or for a certain amount of time. If appropriate, the measured signals can be compared with reference signals.

The storage and evaluation need not happen on site, but the measured signals can be transmitted via the Internet or via computer leased lines to a central data processing system, where their evaluation and storage take place.

If the evaluation shows that the correlation coefficient r _{a, p} a predetermined threshold value for the correlation coefficient r _{a, p} exceeds or falls below, is automatically triggered an alarm. This may be an audible and / or visual alarm. This alarm can be triggered locally on the defective pump and / or in a central switching point. In severe cases, emergency shutdown can be triggered with or without a previous alarm.

One skilled in the art may determine the appropriate threshold based upon his or her general knowledge and experience or on the basis of a few orienting attempts.

The second method according to the invention serves for the early detection and localization of multiple valve failures in an oscillating positive displacement pump, which comprises the components described above, the cylinders of which, however, have a common pump head, by signal-based evaluation of measured pressure and structure-borne noise signals.

As in the case of the first method according to the invention, in the second method according to the invention the pressure measurement is carried out on each cylinder by means of strain gauges DMS, as described above.

Likewise, the digitization of the pressure profile determined on the basis of the measured strain gage signals, as described above in the first method according to the invention, is carried out. In contrast to the first method according to the invention, however, the windowing only has to be carried out for one cylinder or displacer, after which the windows for each cylinder can be calculated by shifting by 120 ° in each case.

For the second method according to the invention, it is essential that the course of structure-borne noise during the suction stroke and during the pressure stroke only at a point of the pump head, where the course of structure-borne noise has the greatest sensitivity with the least noise, by measuring the vibration acceleration and calculation the effective values a _e n in the damage state of the pump is determined.

The point of the pump head on which the course of structure-borne noise has the greatest sensitivity with the least noise at the same time can be determined by the person skilled in the art on the basis of his general knowledge, where appropriate with the aid of a few orienting experiments. Preferably, this point is in the region of the central cylinder head.

In addition, it is essential that two fictitious vibration acceleration signals are calculated for each cylinder from the measured vibration acceleration in the damage state of the pump. This is done so that once for the purposes of Saugventiltests once during the suction stroke and for purposes of the pressure valve test once during the compression stroke of the measured curve is replaced by a replacement value.

The person skilled in the art may determine the substitute value based on his general knowledge and experience and / or on the basis of a few orienting experiments.

The effective value a _e n in the good condition of the oscillating positive displacement pump is preferably used as substitute value, which can be determined automatically during the first startup and stored in a data processing system, in particular an embedded PC. However, any other nonzero positive numerical value is also suitable. Preferably, this numerical value is not significantly greater than the effective value a _e n in the good condition. Namely, the size of the selected number determines the sensitivity of the method according to the invention, with larger values reducing the sensitivity.

The calculation of the two fictitious vibration acceleration signals can be easily automated. By covariance analysis, the correlation coefficient r _{a, p} between the calculated fictitious vibration acceleration signals and the digitized pressure curve in the damage state of the pump is calculated. Preferably, this equation (3) is used.

In this case, a positive correlation coefficient r _{a, p} in the Saugventiltest that exceeds a predetermined threshold, indicates a defect in at least one suction valve. A negative correlation coefficient r _{a, p} in the pressure valve test, which falls below a predetermined threshold, however, indicates a defect in at least one pressure valve.

The valve damage determined in this way or the valve damage determined in this way is or will be assigned to a cylinder by measuring the effective values a _e n of the structure-borne noise in the damage state during a stroke of a displacer with the effective values a _e n at the flanks of the digitized pressure curve in the damage state compares. An assignment to a cylinder is given if the effective value a _e n changes exactly with the edges of a displacement stroke.

Both the calculation of the correlation coefficient r _{a, p} and the assignment of the valve damage or the valve damage to a cylinder can be easily automated.

Preferably, the measured structure-borne noise signals and the pressure curve are measured continuously or at intervals and automatically evaluated taking into account the fictitious vibration acceleration in data processing systems, and the resulting correlation coefficients r _{a, p} are stored permanently or for a certain amount of time. If appropriate, the measured signals can be compared with reference signals.

If the evaluation shows that the correlation coefficient r _{a, p} a predetermined threshold value for the correlation coefficient r _{a, p} exceeds or falls below, is automatically triggered an alarm. This may be an acoustic and / or act optical alarm. This alarm can be triggered locally on the defective pump and / or in a central switching point. In severe cases, emergency shutdown can be triggered with or without a previous alarm.

According to the invention, it is advantageous if the sensors described above are already integrated in the oscillating displacement pumps. "Integrated" means that the sensors are installed in the displacement pumps according to the invention in the required places, so that the positive displacement pumps according to the invention are delivered with the sensors to the customer. The sensors are built in such a way that they do not loosen or become damaged during long-term operation, but can be easily replaced if necessary. Suitable fastening devices are common and known.

It proves to be a significant advantage that the sensors can be integrated at the points where they can be mounted with the least effort.

The sensors of the positive displacement pump according to the invention are equipped with the necessary electrical connection points for power supply lines and signal derivatives, so that they can be easily connected to peripheral devices such as embedded PCs and other data processing systems.

As a result, the positive displacement pumps according to the invention can be used excellently for the processes according to the invention. They can be produced without much additional effort. They are robust and of long service life. Because of their excellent monitoring capabilities, they can be operated without any problems for a particularly long time at constantly high flow rates. Switch points on the valves can be detected very early, so that appropriate countermeasures can be taken without causing a long failure of the positive displacement pump according to the invention.

embodiments experimental arrangement

For the embodiments, a high-pressure plunger pump with three cylinders and a common pump head (triplex pump) series HPP 550-4 with a maximum flow rate of 660 l / min and a maximum operating pressure of 1,500 bar Schäfer & Urbach, Ratingen, Germany, was used.

The pressure curve in each cylinder was measured in volts with the aid of a semiconductor strain gauge DMS attached to the respective cylinder.

In experiments 1 to 3 (see Table 1) for normal-state performance, the course of structure-borne noise using a piezoelectric accelerometer was measured as a structure-borne sound sensor in volts on each cylinder head.

In the further experiments 4 to 14 (see Tables 2 and 3), the course of structure-borne noise was measured only with the aid of a piezoelectric accelerometer as structure-borne sound sensor in volts at the central cylinder head.

The first cylinder seen from the suction line is hereinafter referred to as cylinder I. The central cylinder is referred to as cylinder Il and the cylinder to which the pressure line was connected, referred to as cylinder III.

The measured values were recorded with a LABVIEW program specially configured for the examinations with a sampling rate of 50 kHz per measuring point for one second per test run and stored in text files. The structure-borne sound signals were additionally filtered with 31 kHz low-pass. All other signals were recorded unfiltered.

Operating behavior of the high-pressure plunger pump in the normal state

It was first determined the performance of the high-pressure plunger pump in the normal state. The data obtained served as a reference for further investigations. Table 1 gives an overview of the experimental conditions.

Table 1: Normal performance - experimental conditions Experiment no. Pressure ^a) / bar Speed ^b) / 1 / minute

100 100

100 250

100 500

a) mean pressure, measured on the pressure side at a throttle; b) speed set at the process control station of the trainer;

The result was the following signal characteristic.

The DMS signals of the three cylinders showed the expected pressure curve in the working space. Thus, the DMS signals could be used to approximate the working space pressure. The qualitative course of the structure-borne sound signals showed at each measuring point the typical peaks when opening and closing the valves. In addition, no abnormalities were present. The delivery pressure showed no appreciable influence on the qualitative course of structure-borne noise. All three structure-borne noise sensors provided the same information content. However, the structure-borne sound course at the cylinder head of the cylinder Il (central cylinder head) showed the highest sensitivity with at the same time lowest noise.

The influence of the operating condition on structure-borne noise was also investigated. For this, the effective values a _e n were borne sound signals considered. The peaks of the valve opening and closing operations were faded out. A separate evaluation of structure-borne noise for pressure and suction stroke was not possible in the present high-pressure plunger pump, since there were at least one piston in the pressure stroke and a piston in the suction stroke at any time. The measurements showed a relatively weak influence of the delivery pressure on the structure-borne noise, which was stronger and then clearly increasing at higher speeds. At low speed, on the other hand, the dependence of structure-borne noise on pressure was not clear. However, the change in structure-borne noise with pressure variation was so small that it could be neglected. The speed had a very strong and also increasing influence on the structure-borne sound, which is due to the higher speed at a higher speed and thus to a greater kinetic energy of all sound-causing effects was due. All three structure-borne sound measuring points showed the same trend, but the measuring point at the central cylinder head delivered the signal with the highest intensity, so that in the following only these were used.

Experimental investigation of a pressure valve damage

It was installed a manually damaged pressure valve in the cylinder I. Table 2 gives an overview of the experimental conditions used and of the correlation coefficients r _{a, P} calculated by covariance analysis on the basis of the measured structure-borne sound signals and the measured pressure profiles.

Table 2: Examination of pressure valve damage - test conditions

Experiment no. Pressure ^a) / bar speed ^b) / 1 / min r _ap ^c)

20 100 - 0.1

5 20 500 - 0.165

50 100 - 0.46

7 50 500 - 0.04

8 100 100 -0.66

9 100 500 -0.07 10 500 500 - 0.1 1

Comparison:

Idle 0 500 -0.04

a) mean pressure, measured on the pressure side at a throttle; b) speed set at the process control station of the trainer; c) correlation coefficient

The installation of the faulty pressure valve resulted qualitatively in a greatly exaggerated structure-borne noise during the intake stroke, which is characteristic of damage to the pressure valve.

The correlation coefficients r _{a; P} were expected to be negative, indicating the pressure valve damage. The results also showed that even at a relatively low pressure of 20 bar, at low speeds, the magnitude of the correlation coefficient r _{a, p} increased by a factor of more than 10. This was sufficient to accept the correlation coefficient r _{a; P} as a safe criterion for detecting valve damage. However, in the higher speed experiments, the correlation was not so good, but even at high speed and higher pressures from 100 bar upwards, the increase in the amount of correlation coefficient r _{a; P was} sufficient to be used as a criterion for valve damage , Overall, it was found that, depending on the speed, different thresholds were to be used to detect valve damage, while the influence of pressure could be neglected.

Experimental examination of multiple valve damage

To investigate multiple valve damage, a damaged suction valve and a damaged pressure valve were installed in cylinder I (experiments No. 1 1 to 13, see Table 3). In a further experiment, a damaged pressure valve was installed in the cylinder I and a damaged suction valve in the cylinder II (test No. 14, see Table 3).

Table 3 gives an overview of the experimental conditions used.

Table 3: Examination of multiple valve damage - experimental conditions

Experiment no. Pressure ^a) / bar Speed ^b) / 1 / minute

1 1 100 100 12,300,100

13,500,500

14 100 100

The correlation of structure-borne noise and pressure curve was no longer present with multiple valve damage. This was because a single Saugventilschaden caused a high vibration acceleration of the structure-borne noise in the compression stroke and a lower vibration acceleration in the suction stroke. In a pressure valve damage, the conditions were reversed accordingly. That is, sound and working space pressure did not correlate. In case of multiple valve damage, such as with a simultaneous defect in the suction and pressure valve or simultaneous valve damage in different cylinders, the vibration acceleration of the structure-borne noise was high, depending on the constellation both during a part or during the entire suction and pressure stroke. The method described above could therefore no longer be used here.

Therefore, for each cylinder, the structure-borne sound signal was replaced once during the suction stroke and once during the compression stroke by a fictitious acceleration signal. As a substitute value, the previously measured and stored effective value a _e n in the good condition of the pump was selected. Subsequently, the correlation coefficient r _{a, p was} calculated according to equation (3). Thus, the correlation of structure-borne noise and working space pressure is given again.

The results obtained were to be interpreted as follows:

Suction valve damage occurred when the suction valve test for at least one cylinder indicated a positive correlation exceeding a predetermined threshold. Negative correlations in the suction valve test were therefore definitely an indication of an undamaged suction valve. Pressure valve damage occurred when the pressure valve test for at least one cylinder indicated a negative correlation that fell below a predetermined threshold. Positive correlations in the pressure valve test were therefore definitely an indication of an undamaged pressure valve.

The assignment of a valve damage to a cylinder was made by comparing the effective values a _e n of the structure-borne noise in the damage state during a stroke of a piston with the effective values a _e n at the flanks of the digitized pressure curve in the damage state. An assignment to a particular cylinder was given when the effective value a _e n changed exactly with the flanks of a piston stroke.

Table 4 gives an overview of the calculated correlation coefficients r _ap for the operation of the high-pressure submersible piston pump both in good condition (tests Nos. 1 to 3, see Table 1) and in the damaged condition (Tests Nos. 11 to 14, see Table 3) ).

Table 4: Correlation coefficients r _ap when operating in the good condition (experiments Nos. 1 to 3) and in the damaged state (experiments Nos. 11 to 14)

Attempt Suction Valve Test Pressure Valve Test No. Cylinder No .: Cylinder No .:

I Il I Il

1 -o, r -0,14 * -o, ir 0,14 * 0,12 * 0,35 ^*

-0.59 ^* -0.2 ^* -0.38 ^* 0.05 ^* 0.2 ^* -o, or

-0.76 ^* -0.05 ^* -0.22 ^* -0.14 * 0.16 ^* 0.0 ^*

1 1 o, 6r 0.62 ^* 0.56 ^* -0.64 *** -0.47 ** -0.49 * 12 0.55 ^* o, 6r 0.53 ^* -0.63 ^*** -0.43 ^** -0.47 ^* 13 0.62 *** 0.64 ** 0.58 ^** -0.63 ^*** -0.46 ^** -0.47 ^*

14 0.14 * 0.55 ^* 0.48 ^* -0.63 ^* -0.34 ^* -0.34 ^*

^* Good condition;

** still indifferent; * ^** alarm condition!

Claims

claims

1. A method for early detection of valve damage in an oscillating positive displacement pump with three or more cylinders, each comprising a driven displacer, a cylinder housing, a working space, a suction valve, a pressure valve and a cylinder head, by signal-based evaluation of measured pressure and structure-borne sound signals, characterized by the the following process steps:

(1) Pressure measurement on each cylinder by means of strain gages DMS,

(5) automatic triggering of an alarm if it exceeds or falls below the given threshold for the

Correlation coefficients r _{a, p} .

2. A method for early detection of multiple valve damage in a reciprocating positive displacement pump with three or more cylinders with a common pump head, wherein the cylinders each have a driven displacer, a

Comprise a cylinder housing, a working space, a suction valve and a pressure valve, by signal-based evaluation of measured pressure and structure-borne sound signals, characterized by the following process steps:

(1) Pressure measurement on each cylinder by means of strain gages DMS,

(3) Determination of the structure of structure-borne noise during the suction stroke and during the pressure stroke at a point of the pump head where the structure of the structure-borne noise has the greatest sensitivity with the least noise, by measuring the vibration acceleration and calculating the effective values a _e n in the damaged state Pump,

(4) calculating two fictitious vibration acceleration signals for each cylinder from the measured vibration acceleration in the damaged state of the pump so that once for the purposes of Saugventiltests during the suction stroke and for purposes of the pressure valve test during the pressure stroke, the measured curve is replaced by a substitute value,

(5) Calculation of the correlation coefficient r _{a, p} between the calculated fictitious vibration acceleration signals and the digitized one

Pressure curve in the state of damage of the pump by covariance analysis, wherein a positive correlation coefficient r _{a, p} in the Saugventiltest exceeding a predetermined threshold, a defect in at least one suction valve and a negative correlation coefficient r _{a, p} in the pressure valve test, which falls below a predetermined threshold, a defect indicates at least one pressure valve,

(6) Assignment of a valve damage to a cylinder by comparing the effective values a _e n of the structure-borne sound in the damage state during a stroke of a displacer with the effective values a _e n at the flanks of the digitized pressure curve in the damage state, wherein an assignment to given a cylinder, if the rms value a _{eff changes} exactly with the edges of a Verdrängerhubs, as well

(7) automatic triggering of an alarm when exceeding and / or falling short of preset thresholds for the

Correlation coefficients r _a , _p .

3. The method according to claim 2, characterized in that the substitute value of the effective value a _e n in Gutzustand the oscillating positive displacement pump or a positive number is greater than zero.

4. The method according to claim 2 or 3, characterized in that the point of the pump head at which the course of structure-borne noise has the greatest sensitivity with the least noise, the central cylinder head.

5. The method according to any one of claims 1 to 4, characterized in that the oscillating positive displacement pump has three or five cylinders.

6. The method according to any one of claims 1 to 5, characterized in that the oscillating positive displacement pump is a plunger pump, a diaphragm pump with a mechanically articulated membrane or a hydraulically articulated diaphragm pump or piston diaphragm pump.

7. The method according to any one of claims 1 to 6, characterized in that the valves are automatic.

8. The method according to any one of claims 1 to 7, characterized in that the valves are loaded ball valves, plate valves, mushroom valves or conical valves.

9. The method according to any one of claims 1 to 8, characterized in that the displacer is driven by a Geradschubkurbelantrieb.

10. The method according to any one of claims 1 to 9, characterized in that are used as strain gauges strain gauge semiconductor DMS.

1 1. A method according to any one of claims 1 to 10, characterized in that piezoelectric acceleration sensors are used as sensors for measuring the structure-borne sound.

12. The method according to any one of claims 1 to 1 1, characterized in that are used for the detection and evaluation of structure-borne sound signals embedded PC systems.

13. The method according to any one of claims 1 to 12, characterized in that the digitization of the DMS signals by means of a data processing system.

14. The method according to any one of claims 1 to 13, characterized in that the calculation of the correlation coefficient by means of a data processing system takes place.

15. The method according to any one of claims 1 to 13, characterized in that an optical and / or acoustic alarm or emergency shutdown is triggered.

16. Oscillating positive displacement pump with three or more cylinders, each comprising a driven displacer, a cylinder housing, a working space, a

Suction valve, a pressure valve and a cylinder head, which are integrated on each cylinder on the wall to the workspace a strain gauge strain gauge for non-invasive pressure measurement and a sensor for non-invasive measurement of structure-borne noise with the necessary electrical connection points for power supply lines and signal leads.

17. Oscillating positive displacement pumps having three or more cylinders with a common pump head, wherein the cylinders each comprise a driven displacer, a cylinder housing, a working space, a suction valve, a pressure valve and a cylinder head, wherein on each cylinder on the wall to

Arbeitsraum a Strain Gauge DMS for non-invasive pressure measurement and at a point of the pump head on the course of structure-borne noise has the greatest sensitivity with the least noise, also integrated a sensor for non-invasive measurement of structure-borne noise with the necessary electrical connection points for power supply lines and signal derivatives are.

18. Oscillating positive displacement pump according to claim 17, characterized in that the point of the pump head, at which the course of structure-borne noise has the greatest sensitivity with the least noise, in the region of the central cylinder head.

19. Use of the oscillating positive displacement pump according to one of claims 16 to 18 for methods for the early detection of valve damage.

20. Use according to claim 19, characterized in that the oscillating positive displacement pump according to claim 16 are used for the method for the early detection of valve damage according to claim 1.

21. Use according to claim 80, characterized in that the oscillating displacement pump according to claim 17 or 18 for the method for

Early detection of multiple valve damage according to claim 2 are used.