JP2015511288A - Preventing pump surging in compressors - Google Patents

Abstract

Countermeasures against pump surging in which a plurality of characteristic values of the compressor (2) are monitored during operation, set value ranges for the plurality of characteristic values are given in advance, and when some characteristic values exceed or fall below the set value range The pump surging prevention method in the compressor (2) in which (24, 26, 28) is executed needs to prevent the pumping of the compressor even at a relatively high operation output. Therefore, the plurality of characteristic values have characteristic values related to the rotation noise of the compressor (2). [Selection] Figure 1

Description

  In the present invention, a plurality of characteristic values of a compressor are monitored during operation, a set value range is given in advance to the plurality of characteristic values, and a countermeasure against pump surging is achieved when some of the characteristic values are above or below the set value range. The present invention relates to a method for preventing pump surging in a compressor. The present invention further relates to a fluid machine having a compressor and a control device connected to a plurality of sensors formed on the data input side for detecting characteristic values during operation.

  In particular, gas turbine compressors tend to pump under certain conditions. If the counter pressure in the flow direction is too great, the compressor will no longer supply air and the flow direction will be reversed locally or rather completely. In local backflow, some of the air stays in the compressor and rotates with the blades. This is referred to as rotational separation of the flow (swirl stall). On the other hand, in the case of so-called compressor pumping (deep surging), the medium completely flows backward, and severe surging occurs against the sliding direction.

  These two aerodynamic effects can have serious consequences. While rotary delamination due to significant vibrations can cause material damage, pump surging can cause all blades to delaminate instantaneously. In either case, the flow of air to the combustion chamber of the gas turbine is interrupted and the gas turbine is shut down.

  Typically, the compressor characteristic value map in which the pressure ratio between the inlet pressure and the final pressure is shown with respect to the supply amount is divided into a stable range and an unstable range by a pumping boundary. Pumping occurs when the operating point of the compressor enters an unstable range due to a decrease in supply (throughput) or an increase in final pressure (supply level).

  In general, the control electronics or software of a fluid machine controller defines a pumping boundary distance that is sufficiently far from the pumping boundary for operation under design conditions. For example, under actual conditions such as reduced utility frequency, high ambient temperature and / or air humidity, low fuel heating value, or due to compressor aging, contamination, or failure, the pumping boundary may reach the operating characteristic curve. May fall below. This will result in immediate pumping of the compressor.

  One or more sensors, often configured as differential pressure switches, are installed at the inlet (suction cone) of the compressor, which is slightly below the limit as soon as the flow through the compressor is interrupted during pumping. The gas turbine is immediately shut down by closing the fuel valve. The pumping protection pressure switch, however, does not detect the approach to the pumping boundary, but only prevents re-pumping of the compressor and in some cases prevents mechanical damage to the compressor by an immediate interruption of the fuel supply It is.

  In further development, therefore, compressor pressure ratio limited regulators are often used. This type of regulator monitors the characteristic values of the compressor (pressure ratio, commercial power supply frequency, front guide vane position and temperature, ambient conditions such as air humidity), and this is a pumping boundary characteristic value map specific to the compressor Compare with reliable value from. When the actual operating point approaches the pumping boundary, i.e. above or below a pre-set setpoint range, a countermeasure against pump surging is executed.

  However, the disadvantages of the two methods described above are that they do not take into account compressor aging or large amounts of dirt or damage, and the pumping of the compressor can no longer be reliably prevented as the operating time of the fluid machine increases. .

  Further, for example, Patent Document 1 discloses that a pressure sensor and / or a microphone is arranged in an upstream chamber of a combustor to detect the state of compressed air in the chamber. The signal is evaluated for analysis of the impending pumping phenomenon. Similarly, U.S. Pat. No. 6,057,077 proposes using a shock wave of compressed air or other acoustic phenomena for pumping notice. Again, microphones and similar pressure sensors are used. The drawback, however, is that this type of sensor has a very limited lifetime at high ambient temperatures.

US Patent Application Publication No. 2009/005071 European Patent Application Publication No. 2375081

  Therefore, an object of the present invention is to provide a method for preventing pump surging in a compressor and a compressor or fluid machine that reliably prevents pumping of the compressor even at a relatively high operating output.

  With regard to the method, the above-mentioned problems are solved according to the invention by the fact that the plurality of characteristic values include characteristic values related to compressor rotation noise.

  In this case, the present invention should not rely solely on predefined characteristic value maps and adjustable operating values to reliably prevent pump surging even when the operating output of the fluid machine is high. Starting from the consideration that suitable measurements should be used for preventive detection. Preventive detection would be possible if the corresponding measurement has already detected an approach to the pumping boundary in the form of swirling stall, ie in the form of rotational separation of the flow. In this case, this type of flow separation has been found to cause vibrations in the compressor stage, increasing pressure pulsations and further vibrations. Since these pressure pulsations and vibrations change the rotational noise of the compressor, changes in the rotational noise will prevent pumping impending accordingly. Therefore, a characteristic value related to compressor rotation noise should be measured and used to prevent pump surging.

 Various characteristic values and various sensors that can indicate vibrations in the compressor can be used to detect changes in rotational noise. For example, a high dynamic pressure sensor can be used to detect the aforementioned pressure pulsations. Above all, the disadvantage is that this type of pressure sensor is not stable for a long time and is not suitable for all operating conditions of the fluid machine (increased dirt, humidity, increased humming, cleaning of the compressor, etc.) That is. It is therefore advantageous if the measured characteristic value related to the rotational noise of the compressor is the vibration amplitude or vibration frequency of the fluid machine component. The pressure pulsation is thus also transmitted to the components of the fluid machine. Rotational noise can therefore be determined via mechanical vibrations of the corresponding components of the gas turbine. In this case, sensors and transmitters suitable for this are long-lived because they are insensitive to the above operating conditions.

 Advantageously, the component with the corresponding sensor is the shaft and / or housing of the turbine and / or compressor. Rotational noise is particularly well detected with respect to imminent approach to the pumping boundary based on vibrations of the turbine and / or compressor housing and / or shaft.

 It is advantageous if the characteristic values used further include the shaft speed, the final compressor pressure and / or the position of the front guide vanes. This further improves the preventive detection of pumping. This is because the rotational noise is determined particularly well by this kind of additional characteristic value, for example by a special evaluation algorithm, especially in a computer prepared for measurement.

 In a particularly advantageous embodiment, countermeasures against pump surging include a decrease in turbine outlet temperature set point and / or a decrease in fuel mass. Within the adjustment frame of the fluid machine, a decrease in the set value of the turbine outlet temperature results in opening the adjustable pre-stage guide vanes of the compressor. The reduction in fuel mass reduces the compressor pressure and thus the compressor pressure ratio very quickly. As an alternative, the air at the end of the compressor can be removed, for example, by an anti-ice valve of the compressor. Similarly, it is preferable to take out the air by the anti-ice valve also at the compressor inlet. This similarly reduces the compressor pressure ratio.

 It is advantageous if the fluid machine is formed with a compressor and a control device for carrying out the method described above.

  A problem related to a fluid machine having a compressor and a control device connected to a plurality of sensors on the data input side and configured for detecting characteristic values during operation is a characteristic in which one of the sensors is related to rotational noise of the compressor. It is solved by being formed for value detection.

 In this case, it is advantageous if each sensor is a vibration sensor. This sensor is advantageously formed as a vibrometer. This vibration meter is particularly advantageous if it measures the acceleration in a piezoelectric manner, such as a piezoelectric accelerometer CA901 from Meggitt. This accelerometer has a long life and is robust to high temperatures, dirt and compressor cleaning.

 In an advantageous embodiment, each sensor is associated with a turbine and / or compressor shaft and / or housing. In this case, it is advantageous to install corresponding sensors at several points around the compressor, ideally in the radially outer bore, ie not in the flow channel.

 It is advantageous if the generator installation comprises the fluid machine described above.

  An advantage gained by the present invention is that the intended measurement of the rotational noise of the compressor of the fluid machine can detect the approach to the pumping boundary or swivel stall before the actual pumping occurs. This can be achieved particularly simply by means of a corresponding vibration transmitter which measures the pressure change of a single rotating compressor blade. The compressor rotational noise is determined by a control device such as a computer having a special evaluation algorithm, for example, by other transmitters (shaft rotational speed, compressor final pressure, position of the front guide vane). This also makes it possible to detect foreign objects that can lead to failure of the compressor flow channel and its parts. This type of foreign matter can also cause rotational noise changes. Failures that occur in the components downstream of the compressor are thus avoided.

  The present invention will be described in detail with reference to the drawings.

FIG. 1 is a schematic sectional view of the upper half of a compressor of a gas turbine.

  The fluid machine 1 partially shown in the figure is configured as a gas turbine. Only the compressor 2 is shown from the gas turbine. The compressor 2 has a guide vane 6 fixed or fixed to the housing 4, which is in the flow channel 8 between the compressor inlet 10 and the compressor outlet 12. The first guide vane 6 in the air flow direction is formed as an adjustable front guide vane 14. This regulates and throttles the supply of air to the flow channel 8.

  Rotor blades 18 are arranged on shafts 16 in the direction of air flow behind the guide vanes 6 and 14, respectively. The rotor blades 18 and the guide vanes 6, 14 are respectively arranged in the ring of the flow channel 8 in a spoke shape. The rings of the guide vanes 6 and 14 form one stage of the compressor 2 together with the rings of the moving blades 18 that follow in the flow direction.

  A plurality of sensors not shown in detail are arranged for early detection of impending pumping. In particular, if vibration sensors 20 formed as piezoelectric acceleration sensors are installed in radially outer holes mounted at 90 ° angles, it is possible to detect mechanical vibration and image rotational noise of the compressor 2. To.

  The rotational noise is determined by an evaluation algorithm 22 executed by a control device (not shown) such as a computer as software. In this case, in addition to the vibration data of the vibration sensor 20, other data of the corresponding transmitter or sensor is added to the evaluation algorithm. This includes shaft speed, compressor pressure ratio between compressor inlet 10 and compressor outlet 12, front guide vane position, compressor and turbine shaft vibration and housing vibration.

  If the rotational noise or vibration form of an existing vibration measuring instrument changes due to the approach to the pumping boundary, the computer sends a signal (binary etc.) to perform a corresponding countermeasure to prevent pumping.

  Countermeasures include anti-ice valve opening 24, turbine outlet temperature decrease 26, fuel quantity decrease 28. Other treatments can also be provided. Countermeasures are executed according to the results detected by the evaluation algorithm 22 as necessary. For example, only some or several of the above countermeasures may be performed. Further, notification to the operator 30 is also performed.

  When foreign matter is flying in the flow channel 8 of the compressor 2, this is likewise confirmed by a change in rotational noise. Intrusion of a foreign object similarly notifies the operation control device or the operator 30. The operation control device or the operator decides to stop and check the compressor 2 or the fluid machine 1 depending on the action to be taken. Foreign material intrusions that lead to secondary disasters or damage to compressor components are detected and reported unless they occur instantaneously. In contrast to the strong damage that occurs instantaneously, FOD (Foreign Object Detection) 32 causes automatic treatment such as shutting down the gas turbine.

DESCRIPTION OF SYMBOLS 1 Fluid machine 2 Compressor 4 Housing 6 Guide vane 8 Flow channel 10 Compressor inlet 12 Compressor outlet 14 Front stage guide vane 16 Axis 20 Vibration sensor 22 Evaluation algorithm 24 Anti-ice valve opening 26 Turbine outlet temperature drop 28 Fuel amount Decrease 30 Operator 32 FOD (Foreign Object Detection)

Claims (13)

A plurality of characteristic values of the compressor (2) are monitored during operation, a set value range for the plurality of characteristic values is given in advance, and a countermeasure against imminent pump surging when some characteristic values are above or below the set value range In the method for preventing pump surging in the compressor (2) in which the measures (24, 26, 28) are executed,
The plurality of characteristic values have characteristic values related to rotational noise of the compressor (2);
A method for preventing pump surging in a compressor, wherein the characteristic value related to rotational noise of the compressor (2) is a vibration amplitude and / or vibration frequency of a component of the fluid machine (2).  The method of claim 1, wherein an acceleration of the component is detected to determine the rotational noise.   3. Method according to claim 1 or 2, characterized in that the component is a turbine and / or a shaft (16) and / or a housing (4) of the compressor (2).   4. The method according to claim 1, wherein the plurality of characteristic values include a shaft rotational speed, a compressor final pressure, and / or a front guide vane position.   The method according to one of the preceding claims, characterized in that the countermeasure against pump surging comprises a reduction (26) in the set point of the turbine outlet temperature and / or a reduction in the fuel mass (28).   Method according to one of the preceding claims, characterized in that the compressor (2) is part of the fluid machine (1).  A compressor (2) and a control device formed for carrying out the method according to one of claims 1 to 6. In the control device connected to the plurality of sensors formed to detect the operating characteristic value on the compressor (2) and the data input side,
One of the sensors is a vibration sensor (20) arranged to detect a characteristic value related to rotational noise of the compressor (2), each sensor being arranged in a component of a gas turbine;
A compressor (2) and a control device characterized in that mechanical vibrations of the components are determined by this sensor.   The compressor according to claim 8, wherein the sensor is disposed on a non-rotating component of the gas turbine.   The compressor according to claim 8 or 9, wherein the sensor is configured as an acceleration sensor.  A fluid machine (1) having a compressor (2) according to claim 8, 9 or 10.   The fluid machine (1) according to claim 11, wherein the sensors are attached to the shaft (16) and / or the housing (4) of the turbine and / or the compressor (2), respectively.   A generator installation comprising a fluid machine (1) according to claim 11 or 12.

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