EP2936089A1

EP2936089A1 - Method for assessing an operating state of a turbomachine, and turbomachine

Info

Publication number: EP2936089A1
Application number: EP13798304.5A
Authority: EP
Inventors: Stefan BERTEN
Original assignee: Sulzer Management AG
Current assignee: Sulzer Management AG
Priority date: 2012-12-19
Filing date: 2013-11-26
Publication date: 2015-10-28
Also published as: US20150330393A1; CN104919288A; WO2014095251A1

Abstract

The invention relates to a method for assessing an operating state of a turbomachine (1), which turbomachine (1) comprises an impeller (2) arranged on a rotor axis (A), and the rotor axis (A) with the impeller (2) is mounted in a machine housing (3) of the turbomachine (1) in a manner rotatable about an axial direction (Z) in a shaft bearing (4). According to the invention, in the operating state of the turbomachine, a first force sensor (Sx) is used to measure a first force component (Fx) of a bearing force acting on the rotor axis (A) along a first direction (X), which first direction (X) is perpendicular to the axial direction (Z). A second force sensor (Sy) is used to measure a second force component (Fy) of the bearing force in a second direction (Y), which second direction (Y) is perpendicular to the axial direction (Z) and is preferably simultaneously perpendicular to the first direction (X). A resulting force (Fr) is then formed from the first force component (Fx) and the second force component (Fy), a frequency analysis is used to create a frequency spectrum (ΩS1, ΩS2) of the resulting force (Fr), the frequency spectrum (ΩS1, ΩS2) is compared with a reference spectrum (Ωref), and an operating state assessment is finally carried out therefrom for a predefined operating state of the turbomachine. The invention also relates to a turbomachine for carrying out the method according to the invention.

Description

Method for evaluating an operating state of a turbomachine, and turbomachine

The invention relates to a method for evaluating an operating state of a turbomachine, in particular a pump, as well as a

Turbomachine, in particular pump according to the preamble of the independent claims. The partial load operation of turbines or pumps, but especially not only in centrifugal pumps is usually associated with increased vibration levels, the performance of these machines negative

affect. The causes of this increase in vibration levels are often found in hydrodynamic processes, which are specifically determined by the partial load operation, among other things.

The interaction between rotating and stationary flow fields causes spatially and temporally distributed pressure fields, the mechanical natural frequencies of the impeller, but also those of the stationary

Can stimulate machine components. These vibrations, provided they are not sufficiently damped, can in the worst case to the

Destruction of the impeller, which is also called impeller or rotor, or damage or destruction of other parts of the machine

Turbomachine lead.

Since almost all modern high-performance machines of the aforementioned type, in particular the high-performance pumps are operated at variable speeds, operating points are those in which the pressure pulsations due to rotor-stator interaction (RSI) stimulate a natural frequency of the impeller, in practice almost inevitable.

Especially at partial load operation, other phenomena interfere with the phenomena of RSI pressure pulsations. Local detachments

affect the structure of the flow in the hydraulic channels of the pump and may cause further deformation and vibration at other frequencies.

It has been shown that while in the design volume flow, ie in operating ranges for which the pump is designed in normal operation, in addition to the inevitable mechanical imbalances only the RSI

Pressure pulsations contribute to the deformations of the impeller, while at partial load both stationary and rotating instabilities can occur.

Stationary separations in the stator, which manifests itself as a non-rotating zone of high pressure, followed by a pressure drop on the suction surface of the following in the direction of rotation vane causes additional pressure pulsations in the impeller as pressure pulsations in particular at the rotational frequency of the stator and their harmonic

Can manifest vibration components.

For certain volumetric flows, it is possible that this zone of high pressure begins to rotate more or less slowly, that is to say it becomes detached, ie. forms a separation zone and thus no longer remains spatially stationary. It has been shown that this detachment zone exerts a considerable influence on the mechanical load, for example a pump stage. It has further been found that the moving or rotating

Separation zone may even be responsible for the largest deformation of the impeller, in particular the impeller cover disc may be several times greater than the deformations due to the rotor-stator interaction. The local pressure increase due to the detachment thereby generates a radial force in the Case of rotating separation substantially with the

Angular velocity of detachment rotates.

This phenomenon can be detected in principle by means of the method of radial and / or axial wave vibration measurement. It could be shown that the shaft center of the rotor shaft is directly determined by the position of the separation zone.

This can adversely affect the rotor dynamics of the pump, but on the other hand can be used to detect rotating instabilities, as it is not always possible to use rotating separations with the aid of external rotors

To identify pressure sensors.

Furthermore, it is known that the Radseitenraumströmung is adversely affected by the presence of delamination in the stator. Namely, the inflow of fluid at low peripheral speed significantly reduces the fluid rotation in the wheel side space and thus affects the

Pressure distribution in the Radseitenraum and the resulting stationary and transient, ie temporally variable, including possibly also temporally periodically increasing and decreasing axial or radial forces. Again, this can be done with the help of axial and / or radial

Wave vibration measurements are detected. These known from the prior art phenomena and related problems and their detection by means of methods of wave vibration measurement was the inventor in the special case of pumps already in his dissertation "Hydrodynamics of High Specific Pumps for Off-Design Operating Conditions", thesis No 4642 (2010 ), Ecole Polytechnique Federale de Lausanne, extensively studied and published.

It is very important to determine when operating a turbomachine in a timely manner, if this is in an undesirable operating state described above. As mentioned earlier, it can be a massive Damage or, in the worst case, the destruction of the impeller or even of the entire machine, if such operating conditions are not detected in time and not timely appropriate

Countermeasures are taken, the machine returns as soon as possible in harmless operating conditions.

Unfortunately, these are operational states and the associated complex coupled ones described in detail above

Vibration processes are not readily apparent. As already mentioned, in principle both the stationary and the transient, ie temporally variable Druckschwankungs- and flow phenomena, in particular the stationary and rotating detachments in principle using the method of wave vibration measurement indirectly via the detection of the deflections of the rotor axis of the stator or impeller the machine can be detected. However, it has been shown that the data thus obtained no universal conclusions about the pressure fluctuation and flow phenomena in the turbomachine and thus no

Infer conclusion on their current operating state, ie one

Operating state evaluation based on such data is not possible.

The reason for this is that the size and geometry of the machine and their detailed structure, their performance or volume flow design, the type and condition of the pumped or to

turbinating fluid, and many other well-known to those skilled factors, the vibration behavior of the rotor shaft, ie the time-dependent deflection behavior of the rotor shaft co-determine. In other words, if a specific individual machine is considered in certain applications and under given operating conditions, then due to the time-dependent movement of the rotor shaft, no clear inference can be made as to the stationary and / or transient, ie time-varying, pressure fluctuation actually taking place in the machine Flow phenomena, in particular, can not be obtained on the harmful stationary and rotating separations.

This is only possible if very detailed calibration measurements are made beforehand on the individual machine, taking into account the very specific application in which the machine is to be operated later, e.g. depending on the type, consistency, or viscosity of the fluid to be pumped or turbinated, the mounting in which the pump is mounted as a whole, the strength and nature of the drive, an operating temperature of the fluid to be pumped, and many other relevant parameters.

Mathematically speaking, from the time-dependent deflections of the rotor shaft from a rest position by means of the method of axial and / or radial shaft vibration measurement, so the time-dependent measurement of the position of the rotor axis of the impeller, only useful conclusions on the actually occurring stationary and / or transient, ie temporally variable pressure fluctuation and flow phenomena are drawn when a very complex "transfer function" of the machine under detailed consideration of the special

Operating conditions is known, which establishes a relationship between the pressure fluctuation and flow phenomena on the one hand and the time-varying axial deflections of the rotor axis.

This is of course a method which is in many cases less suitable for practical applications, because for each individual machine and additionally taking into account all conceivable operating parameters, etc., the mentioned very elaborate

Calibration measurements must be made in order to then be able to draw the correct conclusions from the measurement of the radial and / or axial deflection movements of the rotor shaft.

However, this procedure is not only very time-consuming and therefore expensive, but in practice often not at all reliably feasible. As already mentioned, for example, the type of fluid to be processed by the machine play a role. However, its properties are in many cases not known in advance or can change in the course of the operation of the turbomachine in an unpredictable manner. If, for example, a substance such as crude oil is to be pumped, the consistency of the crude oil may change over time in a completely unpredictable manner. For example, the loading of gas, sand or water, or the chemical

Composition of the crude oil, etc. over time, causing massive effects, e.g. On the viscosity of the pumped crude oil may have, so that the calibrations carried out, ie ultimately used

Transfer function is no longer applicable and so drawn from the measured deflections of the rotor shaft the wrong conclusions. Also, the temperature of the fluid, the ambient temperature of the pump is exposed, or others, the skilled person known per se

Change parameters in an unpredictable way. In such cases, using the known method of axial and / or radial

Wave vibration measurement then possibly harmful operating conditions can not be detected, which can lead to damage or even destruction of the machine.

The object of the invention is therefore to propose a new method for the detection of harmful operating conditions of a turbomachine, in particular a pump, with which reliably actually occurring in the operating state stationary and / or transient, ie time-variable Druckschwankungs- and flow phenomena can be detected and from the Prior art known problems are avoided.

The objects of the invention solving this object are characterized by the features of independent claims 1 and 12.

The dependent claims relate to particularly advantageous

Embodiments of the invention. The invention thus relates to a method for evaluating a

Operating state of a turbomachine, which flow machine comprises an impeller arranged on a rotor axis, and the rotor shaft with impeller in a machine housing of the turbomachine is rotatably mounted about an axial direction in a shaft bearing. According to the invention, in the operating state of the turbomachine with a first force sensor, a first force component of a bearing force acting on the rotor axis is measured along a first direction, which first direction is perpendicular to the axial direction. With a second force sensor is a second

Force component of the bearing force measured in a second direction, which second direction is also perpendicular to the axial direction and preferably, but not necessarily, perpendicular to the first direction. Then, a resultant force is formed from the first force component and the second force component, by means of a frequency analysis, a frequency spectrum of the resulting force created, the frequency spectrum with a

Compared to the reference spectrum and finally becomes one

Operating state evaluation made at a given operating condition of the turbomachine. Furthermore, the invention relates to a turbomachine for carrying out the method according to the invention. Essential to the invention is thus that with at least two

Force sensors in at least two different directions, preferably, but not necessarily measured simultaneously two force components that act on the rotor axis in the operating state.

The decisive difference from the prior art is thus that not the deflections of the shaft are measured, but directly the forces acting on the shaft.

It is a key finding of the invention that the fact that the forces acting on the shaft and not the deflections of the shaft are measured and evaluated, the problems described in the beginning, at Known from the prior art wave vibration measurement can be practically completely avoided.

The data obtained by means of the force measurements according to the invention allow conclusions to be drawn about the pressure fluctuation and

Flow phenomena in the turbomachine and thus their current operating condition, which have a much more universal character than the data obtained from the wave vibration measurements.

Of course, for a reliable evaluation of

Measuring data according to the invention also have certain parameters

Turbomachine, how its geometry, performance, etc. are taken into account. But it's essentially just about

Machine-specific data that should once flow into a suitable calibration, which then monitors the operating state of the turbomachine, and under very different, even under initially unknown or predictable boundary conditions extremely reliable from the inventively obtained measurement data of the forces acting on the rotor axis forces can be determined.

In other words, if a specific individual machine is considered, then, due to the determination of the rotor acting on the rotor shaft

time-dependent forces by using the inventive

Method now a clear inference to the actually occurring in the machine stationary and / or transient, so temporally variable pressure fluctuation and flow phenomena,

particular to the detrimental stationary and rotating separations, without further parameters of concrete use, such as the type or viscosity of the fluid to be pumped,

Environment or machine temperature or other accompanying parameters should be considered. Another essential finding of the invention is that the enormously complex processes associated with stationary or transient detachments are much more reliable and easier to detect, if not the force components are evaluated individually in different directions, but if a suitable averaging in the form of a

mathematical standard is made, and thus in particular, for example, the vectorial amount of forces is evaluated. It has

Surprisingly, it has been shown that the separation phenomena in a turbomachine can be detected much more reliably for practical applications than when the individual force components are considered separately.

Thus, in particular when several cells of detachments occur simultaneously at different locations in the pump or even simultaneously with rotating detachments, the detachment phenomena can be detected much more reliably, easily and thus also more quickly with the method according to the invention, so that also when using the method according to the invention It is possible to react much earlier to developing detachment phenomena and possibly even then, when their emergence only begins, appropriate countermeasures can be initiated.

In this context, it is understood that in practice the

Force components are preferably measured over a predetermined period either at certain intervals or continuously or quasi-continuously, so that changes in the operating state can be tracked particularly well and in particular the occurrence of harmful stationary or transient detachments can be detected as soon as possible and appropriate countermeasures can be taken to the

Turbomachine back to a non-critical operating condition, preferably without or at least largely without detaching back. In principle, in a method according to the invention, a measurement of the first force components at a predetermined time interval to a measurement of the second force components is performed, wherein in practice the measurement of the first force components is particularly preferably carried out simultaneously with the measurement of the second force components.

Subsequent to the measurement of the force components, the resulting force can then be formed in the form of a mathematical norm from the first force components and the second force components, the resultant force being in particular the square root of the absolute value square of the force vector according to Fr = [Fx ² + Fy ² ] ^{1 2} is formed.

In order to be able to reliably interpret a measurement for a given operating state of the machine, first of all a reference spectrum of the resulting force must be created, which is a known one

Reference state of the machine represents, preferably a state in which the machine runs under optimal conditions, that is as possible without detachment. The reference spectrum of the resulting force is created by means of the frequency analysis in the reference operating state of the turbomachine.

To evaluate the operating state of the turbomachine in a different operating state, then a frequency spectrum of the resulting force is determined, as determined for the other operating state by measuring the first and second force components, wherein the

Frequency analysis for the generation of the frequency spectrum for the other operating state and / or for the preparation of the reference spectrum particularly preferably using a Fourier analysis method, in particular using a fast Fourier analysis method is performed.

In practice, the frequency analysis for the creation of the

Frequency spectrum of the resulting force of the other operating state advantageous, but not necessary, performed with the same method as the frequency analysis to create the reference spectrum.

For the concrete preparation of the operating condition assessment of the

Turbomachine in the other operating state, an intensity in the frequency spectrum at a predetermined comparison frequency with an intensity of the reference spectrum at the same predetermined

Comparison frequency is compared. Dodges the intensity at the

Comparative frequency in the frequency spectrum of the other operating state noticeably from the intensity at the same comparison frequency of

Reference spectrum significantly, so this indicates an undesirable operating condition of the turbomachine. The interpretation of

Deviations from the reference spectrum will be explained in more detail later with reference to the drawing.

In this case, a fundamental frequency can be selected as a comparison frequency particularly advantageous, which corresponds to a rotational frequency of the impeller, in particular equal to or equal to a multiple of the rotational frequency of the impeller is to determine a temporally and / or spatially stationary detachment.

For example, to correct the operating condition of the

To achieve turbomachine can be in a special

Embodiment, the determined operating condition assessment of a

Control means are supplied, with which the turbomachine can be suitably controlled or regulated in dependence on the operating state assessment, so that the turbomachine can be brought back into an undisturbed operating state.

In this case, the turbomachine in practice a turbine engine or a pump, in particular a single or multi-stage vertical or horizontal pump, in particular a pump for pumping

Multi-phase mixtures, in particular a high-line pump for Providing high pumping power or any other known turbomachine be.

The invention also relates to a turbomachine for

Implementation of a method according to the invention, which

Turbomachine comprises a arranged on a rotor axis impeller, wherein the rotor axis with impeller in a machine housing of the

Turbomachine is rotatably mounted about an axial direction in a shaft bearing. According to the invention, a first force sensor is on the

Rotor shaft provided that a first force component of a on the

Rotor axis acting bearing force along a first direction is measurable, which first direction is preferably perpendicular to the axial direction, and a second force sensor is provided on the rotor shaft, that a second force component of the bearing force is measured in a second direction, which second direction also preferably perpendicular to Axial direction and at the same time can be perpendicular to the first direction, but also obliquely, so can not be perpendicular to the first direction.

In this case, in a turbomachine according to the invention

Of course, in each case a plurality of force sensors, preferably a pair of two arranged on the rotor axis opposite force sensors may be provided so that the force component simultaneously or alternatively from two opposite directions along the direction is measurable, of course, in each case more force sensors, preferably a pair of two Force sensors arranged opposite the rotor axis can be provided, so that the force component can be measured simultaneously or alternatively from two opposite directions along the direction.

In practice, a drive device, in particular a computer-controlled activation device, may advantageously be provided, so that the flow machine can be controlled or regulated as a function of the operating state evaluation by means of the drive device, so that the Turbomachine using the results of the

inventive method automatically in an advantageous

Operating state can be controlled, or in such advantageous

Operating conditions can be maintained. In the following the invention will be explained in more detail with reference to the drawing. In a schematic representation:

Fig. 1 a an embodiment of an inventive

Flow machine;

1 b is a section along the section line 1-l according to FIG. 1 a; Fig. 2a shows a reference spectrum;

FIG. 2b shows a frequency spectrum for a state with a detachment; FIG.

Fig. 2c shows a frequency spectrum for a state with two separations.

The special embodiment of an inventive

According to FIG. 1 a or FIG. 1 b, a turbomachine, which is referred to in its entirety by the reference numeral 1, is used very generally, and in particular in the specific embodiment of FIG. 1 a, to convey a pumping fluid possibly comprising an ingredient. The pumping fluid is at an inlet pressure P1 at a low pressure side LP of the pump 1 ready and is in the operating state by means of a in a

Shaft bearing 4 about a rotor axis A rotatably mounted impeller 2 on a high pressure side HP of the pump 1 transported.

The rotor axis A with impeller 2 is mounted rotatably about an axial direction Z in the shaft bearing 4 in a machine housing 3 of the turbomachine 1 configured as a pump. According to the present invention, a first force sensor Sx is provided on the rotor shaft 2 in such a way that a first force component Fx of the rotor axis A in the operating state acting bearing force along a first direction X is measurable, which first direction X in the preferred embodiment according to FIG. 1 a and FIG. 1 b is perpendicular to the axial direction Z. In addition, a second

Force sensor Sy provided on the rotor shaft 2 such that a second force component Fy of the bearing force in a second direction Y is measured, which second direction Y in the preferred embodiment of Fig. 1a and Fig. 1b perpendicular to the axial direction Z and at the same time preferably perpendicular to the first direction X lies.

1 b, which shows a section along the section line II according to FIG. 1 a, illustrates somewhat more clearly the arrangement of the force sensors Sx, Sy on the rotor shaft 2. The force sensors Sx, Sy measure in operation the corresponding force components acting on the rotor shaft act.

In the present embodiment is then measured from the

Force components Fx, Fy the resulting force Fr in the form of a

mathematical standard, here according to Fr = [Fx ² + Fy ² ] ^{1 2} formed and by means of fast Fourier analysis, also known under the abbreviation FFT, first a reference spectrum Qref according to Fig. 2a created that optimal

Operating state, ie a reference operating state of the pump corresponds, in which there are substantially no detachments. Of the

Reference mode can be e.g. an operating condition for which the pump was designed and in which it is normally operated, often in continuous operation.

Now, if the operating condition of the pump changes, e.g. because it must be operated in a first part-load range, it may happen that a detachment forms within the pump housing.

This can then be derived, for example, from the frequency spectrum Ω.S ^, because here a comparison of the intensity in the frequency spectrum Ω.S ^ at a given comparison frequency Ω with the intensity of Reference spectrum at the same frequency results in that the intensity at the comparison frequency Ω, the value of which was chosen here to Ω0, which corresponds directly to the rotational frequency of the impeller 2, is significantly higher than in the reference spectrum. If such a deviation is detected, which indicates a replacement, for example, an alarm can be automatically triggered, which indicates an operator that he must regulate the pump in another operating state. Or it can also be done via the above-mentioned drive an automatic correction of the operating state of the pump.

In principle, the method according to the invention even allows the number of detachments to be determined. FIG. 2c shows a frequency spectrum D.sub.S2 of another operating state in which the intensity at the double reference frequency 2.OMEGA..sub.0 is markedly increased at the same frequency as compared to the reference spectrum .OMEGA..sub.β.sup

Spectrum D.S2 at the simple reference frequency Ω0 is only insignificantly changed compared to the reference spectrum.

It is understood that all embodiments of the invention described in the context of this application are to be understood by way of example only and by way of example and that the invention is particularly, but not exclusively, all

suitable combinations of the described embodiments includes, as well as simple developments of the invention, which also give the expert without further inventive step also informal.

Claims

claims

1 . Method for evaluating an operating state of a

Turbomachine, which turbomachine one at one

Rotor axle (A) arranged impeller (2), and the rotor axis (A) with impeller (2) in a machine housing (3) of the turbomachine rotatably mounted about an axial direction (Z) in a shaft bearing (4), characterized in that in the operating state of

Turbomachine with a first force sensor (Sx) a first

Force component (Fx) of a force acting on the rotor axis (A)

Bearing force along a first direction (X) is measured, which first direction (X) is perpendicular to the axial direction (Z), and with a second force sensor (Sy) a second force component (Fy) of the bearing force in a second direction (Y) is measured which second direction (Y) is perpendicular to the axial direction (Z) and preferably at the same time perpendicular to the first direction (X), from the first force component (Fx) and the second force component (Fy) a resultant force (Fr) is formed by means of a Frequency analysis a frequency spectrum (Ω.S ^, D.S2) of the resulting force (Fr) is created, the frequency spectrum (Ω.S ^, D.S2) is compared with a reference spectrum (Qref) and from this an operating condition assessment at a given operating condition the turbomachine is made.

2. The method of claim 1, wherein a measurement of the first

Force components (Fx) is performed at a predetermined time interval to a measurement of the second force components (Fy), wherein the measurement of the force components (Fx) is preferably carried out simultaneously with the measurement of the force components (Fy).

3. The method of claim 1 or 2, wherein the resultant force (Fr) in the form of a mathematical standard of the first force components (Fx) and the second force components (Fy) is formed, in particular according to Fr = [Fx ² + Fy ² ] ^{1 2 is} formed.

4. The method according to any one of the preceding claims, wherein the

Reference spectrum (Qref) from the resulting force (Fr) by means of the frequency analysis in a reference operating state of

Turbomachine is created.

5. The method according to any one of the preceding claims, wherein the

Frequency analysis for the generation of the frequency spectrum (Ω.S ^, D.S2) and / or for the preparation of the reference spectrum (Qref) using a Fourier analysis method, in particular using a fast Fourier analysis method is performed.

6. The method according to any one of the preceding claims, wherein the

Frequency analysis to create the frequency spectrum (QS1, D.S2) using the same method as the frequency analysis to create the reference spectrum (Qref).

7. The method according to any one of the preceding claims, wherein the

Creation of the operating condition assessment of the turbomachine an intensity in the frequency spectrum (Ω.S ^, D.S2) at a predeterminable

Comparison frequency (Ω) is compared with an intensity of the reference spectrum at the predetermined comparison frequency (Ω).

8. The method according to claim 7, wherein as comparison frequency (Ω) a

Fundamental frequency (Ω0) is selected, which corresponds to a rotational frequency of the impeller (2), in particular equal to or equal to one

Multiples of the rotational frequency of the impeller (2) is selected.

9. The method according to any one of the preceding claims, wherein a temporally and / or spatially stationary detachment is determined.

10. The method according to any one of the preceding claims, wherein the determined Betnebszustandsbewertung a drive means is supplied and the turbomachine in dependence on the

Operating state rating is controlled or regulated.

1 1. Method according to one of the preceding claims, wherein the

Turbomachine a turbine engine or a pump,

in particular a single or multi-level vertical or horizontal

Pump, in particular a pump for pumping

Multi-phase mixtures, in particular a high-line pump for providing high pumping power is.

12. Turbomachine for carrying out a method according to one of claims 1 to 1 1, which turbomachine on a rotor axis (A) arranged impeller (2), and the rotor axis (A) with impeller (2) in a machine housing (3) of Turbomachine rotatable about an axial direction (Z) in a shaft bearing (4) is mounted, characterized in that a first force sensor (Sx) on the rotor shaft (2) is provided such that a first force component (Fx) on the rotor axis (A ) bearing force along a first direction (X) is measurable, which first direction (X) preferably perpendicular to

Axial direction (Z) is located, and a second force sensor (Sy) on the

Rotor shaft (2) is provided that a second force component (Fy) of the bearing force in a second direction (Y) is measured, which second direction (Y) is preferably perpendicular to the axial direction (Z) and at the same time preferably perpendicular to the first direction (X) ,

13. Turbomachine according to claim 12, wherein in each case a plurality

Force sensors (Sx), preferably a pair of two on the rotor axis (A) arranged opposite force sensors (Sx) is provided so that the force component (Fx) simultaneously or alternatively from two opposite directions along the direction (X) is measurable and / / or wherein in each case a plurality of force sensors (Sy), preferably a pair of two on the rotor axis (A) arranged opposite force sensors (Sy) is provided so that the force component (Fy) simultaneously or alternatively from two opposite directions along the direction (X) measurable is.

14. Turbomachine according to claim 12 or 13, wherein a

Control device, in particular a computer controlled

Control device is provided so that by means of

Control device, the turbomachine is controlled or regulated in dependence on the operating state evaluation.

15. Turbomachine according to one of claims 12 to 14, wherein the turbomachine, a turbine engine or a pump, in particular a single or multi-stage vertical or horizontal pump, in particular a pump for pumping