JP6860457B2 - Non-contact vibration system and vibration suppression system for rotating machinery - Google Patents

Description

The present disclosure relates to a non-contact vibration system and a vibration suppression system for a rotating machine.

In industrial turbines such as steam turbines, rotational vibration tests are carried out as one of the performance tests. In this rotational vibration test, the rotating blades are excited (excited) by the vibration mode exciter while rotating the turbine within the rotation speed range required for the test. In this way, the vibration characteristics of the moving blade are obtained by detecting the vibration of the moving blade excited during rotation by the detector (see Patent Document 1).

Japanese Unexamined Patent Publication No. 2000-9781

In the above-mentioned patent documents, among a plurality of vibrators arranged over the entire circumference at positions facing the peripheral edges of the rotor blades, a vibration device selected in accordance with a preset vibration mode is specified. By turning it on at the timing, the rotor blades vibrate in the preset vibration mode.
However, in the above-mentioned patent document, since the exciters are arranged at predetermined intervals in the circumferential direction, the position and the vibration at which the rotor blades are desired to be vibrated corresponding to the preset vibration mode. There may be a deviation from the placement position of the vessel. Therefore, it may be difficult to vibrate the moving blades with high accuracy in the preset vibration mode.

In view of the above circumstances, at least one embodiment of the present invention aims to provide a non-contact vibration system capable of vibrating a moving blade with high accuracy in a preset vibration mode. Another object of the present invention is to provide a vibration suppression system for a rotating machine that suppresses vibration generated in the rotating machine.

(1) The non-contact vibration system according to at least one embodiment of the present invention is
A plurality of exciters arranged in the circumferential direction while being configured to be able to apply excitation force to the rotor blade row of the rotating machine,
A rotation speed sensor for detecting the rotation speed of the rotor blade row and
A controller for outputting a vibration signal to each of the plurality of vibrators is provided.
Said controller wherein a rotational speed rotational frequency f _rpm of the rotor blade sequence obtained from the detection result of the sensor, by using the natural frequency f _i blade at the N-clause diameter mode, f _{in =} f _rpm × It said excitation signal of frequency f _in, represented by N ± f _i, characterized in that it is configured to output to each of the vibrator.

According to the above configuration _{(1), f in = f} rpm × N by outputting vibration signals of the frequency _{f in,} represented by ± _{f i} to each of the vibrator, N clause diameter rotor blade row It is possible to accurately vibrate in the mode.

(2) In some embodiments, in the configuration of (1) above,
The plurality of exciters include a pair of exciters provided at an angle γ in the circumferential direction.
The controller uses the excitation signal output to one of the pair of exciters as a reference, and transmits the excitation signal having a phase difference of N × γ to the other of the pair of exciters. It is characterized in that it is configured to output to a shaker.

According to the configuration of (2) above, an excitation having a phase difference of N × γ is used as a reference for an excitation signal output to one of a pair of exciters provided with an angle γ offset in the circumferential direction. The vibration signal is output to the other exciter of the pair of exciters. As a result, the phase of the excitation signal output to the pair of exciters provided at an angle γ deviation in the circumferential direction can be optimized.

(3) In some embodiments, in the configuration of (1) or (2) above, the number of the exciters is 2N or less.

According to the above configuration (3), can be number is the following vibrator 2N, to vibrate the rotor blade row which is rotating at the natural frequency f _i of snowfall diameter mode nodal diameter number N .. As a result, the number of vibrators in the non-contact vibration system can be 2N or less, so that the cost increase of the non-contact vibration system can be suppressed.

(4) In some embodiments, in any of the configurations (1) to (3) above, the controller transfers the vibration signal represented by a sine wave or a sine half wave to each of the vibration devices. It is characterized in that it is configured to output to.

According to the configuration of (4) above, since the excitation signal represented by the sine wave or the sine half wave is output to each of the exciters, it becomes easy to excite in the set node diameter mode.

(5) In some embodiments, in any of the configurations (1) to (4), the controller determines the amplitude of the N-node diameter mode from among a plurality of waveform candidates of the excitation signal. It is characterized in that the maximum waveform is selected and the vibration signal of the selected waveform is output to each of the vibrators.

According to the configuration of (5) above, the waveform having the maximum amplitude in the N-node diameter mode is selected from a plurality of types of waveform candidates of the excitation signal, and the excitation signal of the selected waveform is the exciter. Since it is output to each of the above, it becomes easy to excite in the set node diameter mode.

(6) In some embodiments, in any of the configurations (1) to (5) above,
A reference position sensor for detecting a reference position signal indicating a reference position in the rotation direction of the rotor blade row is further provided.
The controller is characterized in that it is configured to generate the vibration signal according to the vibration timing determined based on the reference position signal.

According to the configuration of (6) above, the controller generates the vibration signal according to the vibration timing determined based on the reference position signal, so that the vibration in the N-node diameter mode with high accuracy is excited to the rotor blade train. Can be done.

(7) In some embodiments, in any of the configurations (1) to (6) above, the controller controls the vibration force of the vibration device with respect to the output time of the vibration signal by the controller. It is characterized in that it is configured to correct the excitation timing by each of the exciters based on the delay phase at the time of occurrence.

According to the configuration of (7) above, the excitation timing by each exciter is corrected based on the delay phase at the time when the excitation force is generated with respect to the output time of the excitation signal. The exciting force can be applied efficiently.

(8) In some embodiments, in any of the configurations (1) to (7) above,
The plurality of exciters
With the first exciter
A second exciter provided on the side opposite to the first exciter across the rotor blade row in the axial direction of the rotating machine, and
Including
The controller is configured to output a second excitation signal that is 180 ° out of phase with respect to the first excitation signal that is output to the first excitation device. It is characterized by.

According to the configuration of (8) above, the plurality of exciters are provided on the opposite side of the first exciter and the first exciter with the moving blade row sandwiched in the axial direction of the rotating machine. Includes 2 exciters. The controller is configured to output a second excitation signal that is 180 ° out of phase with respect to the first excitation signal that is output to the first excitation device. As a result, the rotor blade train can be vibrated with a stronger excitation force.

(9) In some embodiments, in any of the configurations (1) to (8) above,
Further provided with a vibration displacement detection device for detecting the vibration displacement of the rotor blade row,
The controller is characterized in that the vibration signal output to each of the vibrators is corrected so that the vibration displacement detected by the vibration displacement detection device approaches the target vibration displacement of the rotor blade row. And.

According to the configuration (9) above, the controller corrects the vibration signals output to each of the exciters so that the vibration displacement of the rotor blade row detected by the vibration displacement detection device approaches the target vibration displacement. To do. As a result, it is possible to excite the vibration in the N-node diameter mode with high accuracy in the rotor blade row.

(10) In some embodiments, in the configuration of (9) above,
The vibration displacement detection device is
A plurality of passage detection sensors arranged along the circumferential direction and for detecting the passage of each rotor blade in the rotor blade row,
A signal processing unit for processing the detection signals of the plurality of passage detection sensors, and
Including
The signal processing unit
Assuming that the rotor blades are not vibrating, the first passage timing at which each rotor blade passes through the plurality of passage detection sensors is calculated.
The calculated displacement due to vibration of the moving blades is calculated by comparing the calculated first passing timing with the second passing timing of each moving blade actually detected by the plurality of passing detection sensors.
It is characterized in that it is configured to calculate the vibration displacement of the rotor blades based on the calculated displacement due to the vibration of the rotor blades.

According to the configuration of (10) above, the vibration displacement detection devices are arranged along the circumferential direction, and a plurality of passage detection sensors for detecting the passage of each rotor blade in the rotor blade row and a plurality of passage detection sensors. It includes a signal processing unit for processing the detection signal of the sensor. The signal processing unit calculates the first passage timing at which each rotor blade passes through the plurality of passage detection sensors when it is assumed that the rotor blade train is not vibrating, and the calculated first passage timing and the plurality of passage detections are detected. The displacement due to the vibration of the moving blade is calculated by comparing with the second passage timing of each moving blade actually detected by the sensor, and the vibration displacement of the moving blade row is calculated based on the calculated displacement due to the vibration of the moving blade. As a result, the vibration displacement of the rotor blade row can be calculated with high accuracy, so that the accuracy of correction of the excitation signal in the controller is improved, and the vibration of the N-node diameter mode with high accuracy can be excited to the rotor blade row.

(11) The vibration suppression system for a rotating machine according to at least one embodiment of the present invention is
A plurality of exciters arranged in the circumferential direction while being configured to be able to apply excitation force to the rotor blade row of the rotating machine,
A vibration displacement detection device for detecting the vibration displacement of the rotor blade row, and
A rotation speed sensor for detecting the rotation speed of the rotor blade row and
A controller for outputting a vibration signal to each of the plurality of vibrators is provided so that the vibration displacement detected by the vibration displacement detection device becomes small.
Said controller wherein a rotational speed rotational frequency f _rpm of the rotor blade sequence obtained from the detection result of the sensor, by using the natural frequency f _i blade at the N-clause diameter mode, f _{in =} f _rpm × characterized in that it is configured to generate the excitation signal of frequency f _in, represented by N ± f _i.

According to the configuration of (11) above, a controller for outputting a vibration signal to each of a plurality of vibration devices is provided so that the vibration displacement detected by the vibration displacement detection device becomes small. The controller includes a rotation frequency f _rpm of rotor blade row obtained from the detection results of the speed sensor, by using the natural frequency f _i blade at the N-clause diameter _{mode, f in = f rpm × N} ± It is configured to generate an excitation signal of frequency f _in, represented by f _i.
Thus, by outputting the excitation signal of frequency f _in, represented by _{f in = f rpm × N ±} f i to each of the vibrator, effective vibration in N clause diameter mode rotor blade row Can be suppressed.

(12) In some embodiments, in the configuration of (11) above,
The vibration displacement detection device is
A plurality of passage detection sensors arranged along the circumferential direction and for detecting the passage of each rotor blade in the rotor blade row,
A signal processing unit for processing the detection signals of the plurality of passage detection sensors, and
Including
The signal processing unit
Assuming that the rotor blades are not vibrating, the first passage timing at which each rotor blade passes through the plurality of passage detection sensors is calculated.
The calculated displacement due to vibration of the moving blades is calculated by comparing the calculated first passing timing with the second passing timing of each moving blade actually detected by the plurality of passing detection sensors.
It is characterized in that it is configured to calculate the vibration displacement of the rotor blades based on the calculated displacement due to the vibration of the rotor blades.

According to the configuration (12) above, the vibration displacement detection devices are arranged along the circumferential direction, and a plurality of passage detection sensors for detecting the passage of each rotor blade in the rotor blade row and a plurality of passage detection sensors. It includes a signal processing unit for processing the detection signal of the sensor. The signal processing unit calculates the first passage timing at which each rotor blade passes through the plurality of passage detection sensors when it is assumed that the rotor blade train is not vibrating, and the calculated first passage timing and the plurality of passage detections are detected. The displacement due to the vibration of the moving blade is calculated by comparing with the second passage timing of each moving blade actually detected by the sensor, and the vibration displacement of the moving blade row is calculated based on the calculated displacement due to the vibration of the moving blade. As a result, the vibration displacement of the rotor blade row can be calculated accurately, so that the vibration of the rotor blade row in the N-node diameter mode can be suppressed more effectively.

According to at least one embodiment of the present invention, the moving blade can be vibrated with high accuracy in a preset vibration mode. Further, according to at least one embodiment of the present invention, vibration generated in the rotating machine can be effectively suppressed.

FIG. 5 is a configuration diagram showing a rotary vibration test device incorporating a vibration mode vibration device of the non-contact vibration system according to the first embodiment. The block diagram which shows the vibration mode exciter of the non-contact excitation system which concerns on Embodiment 1. FIG. The schematic diagram which shows the vibration state of the rotor blade train. The block diagram which shows the control system which controls the vibration mode excitation apparatus of the non-contact excitation system which concerns on Embodiment 1. FIG. Explanatory drawing which shows the relationship between a stationary coordinate system and a rotating coordinate system. The waveform diagram which shows various examples of a vibration command signal. A waveform diagram showing an image of the output characteristics (current squared and exciting force) of the exciter. FIG. 5 is a configuration diagram showing a rotary vibration test device incorporating a vibration mode vibration device of the non-contact vibration system according to the second embodiment. Explanatory drawing which shows the excitation state in Embodiment 2. The figure which shows the structure which concerns on the detection method of the vibration mode of the moving blade row in Embodiment 3. The explanatory view of the waveform processing which concerns on the detection method of the vibration mode of the rotor blade row in Embodiment 3. The graph which shows the vibration waveform of the 1st rotor blade. The graph which shows the mode shape of 6-node diameter mode as an example of the mode shape of the vibration to excite the rotor blade train, and the mode shape of the actual vibration mode generated in the rotor blade train. The flowchart which shows the process which corrects the distortion of the mode shape of the N node diameter mode executed by the controller which concerns on Embodiment 3. The block diagram which shows the whole structure of the vibration suppression system of the rotary machine which concerns on Embodiment 4. FIG. 5 is a flowchart showing a vibration suppression process executed by the controller according to the fourth embodiment. FIG. 5 is a diagram schematically showing an example of the mode shape of the vibration of the rotor blade row before the vibration suppression treatment according to the fourth embodiment and the mode shape when the vibration of the rotor blade row is suppressed by the vibration suppression treatment.

Hereinafter, some embodiments of the present invention will be described with reference to the accompanying drawings. However, the dimensions, materials, shapes, relative arrangements, etc. of the components described as embodiments or shown in the drawings are not intended to limit the scope of the present invention to this, but are merely explanatory examples. Absent.
For example, expressions that represent relative or absolute arrangements such as "in a certain direction", "along a certain direction", "parallel", "orthogonal", "center", "concentric" or "coaxial" are exact. Not only does it represent such an arrangement, but it also represents a state of relative displacement with tolerances or angles and distances to the extent that the same function can be obtained.
For example, expressions such as "same", "equal", and "homogeneous" that indicate that things are in the same state not only represent exactly the same state, but also have tolerances or differences to the extent that the same function can be obtained. It shall also represent the existing state.
For example, an expression representing a shape such as a quadrangular shape or a cylindrical shape not only represents a shape such as a quadrangular shape or a cylindrical shape in a geometrically strict sense, but also an uneven portion or chamfering within a range in which the same effect can be obtained. The shape including the part and the like shall also be represented.
On the other hand, the expressions "equipped", "equipped", "equipped", "included", or "have" one component are not exclusive expressions that exclude the existence of other components.

[Embodiment 1]
The non-contact vibration system 100 according to the first embodiment of the present invention will be described with reference to FIGS. 1 to 7.
The non-contact excitation system 100 includes a vibration mode excitation device 110 (see FIGS. 1 and 2) and a controller 200 (see FIG. 4) as main members.

<Explanation of rotary vibration test device 50 and vibration mode excitation device 110>
First, the rotary vibration test apparatus 50 will be described with reference to FIG. The rotary vibration test device 50 incorporates the vibration mode excitation device 110 of the non-contact vibration system 100 of the present embodiment to perform a rotary vibration test.

As shown in FIG. 1, the turbine 40 has a rotating shaft 41 and a rotor blade row 42. The moving blade row 42 is formed by arranging a large number of moving blades 42a radially on the rotating shaft 41. When the turbine 40 is subjected to a rotational test vibration, the rotary shaft 41 is rotatably supported by the rotary support columns 52 and 53 with the rotor blade row 42 arranged in the test chamber 51. In the test chamber 51, the vibration mode exciter 110 is arranged in close proximity to the rotor blade row 42.
Further, a rotation detector 60 for detecting the rotation speed of the turbine 40 and the zero position in the rotation direction is arranged close to the rotation shaft 41.

Here, the configuration of the vibration mode exciter 110 will be described with reference to FIG. 2, which is shown as viewed from the rotor blade row 42 side.
As shown in FIG. 2, the annular support ring 113 is supported by the pedestal 112 arranged on the bed 111. An annular mounting jig 114 is attached to the inner peripheral side of the support ring 113. In this example, eight exciters 115-1 to 115-8 and eight exciters 116-1 to 116-8 are attached to the mounting jig 114. The number of exciters 115-1 to 115-8 and the number of receivers 116-1 to 116-8 installed is not limited to eight, and the number of the exciters can be set arbitrarily. In the present embodiment, as will be described later, since the rotor blade row 42 is configured to give an exciting force, it is possible to excite the rotor blade train 42 with highly accurate vibration in the N-node diameter mode. , The number of vibrators 115 can be reduced as compared with the conventional non-contact vibration system. For example, in the present embodiment, accurate vibration in the N-node diameter mode can be excited to the rotor blade row 42 by a number of exciters 115 that is twice (2N) or less of the number of node diameters N.

The exciters 115-1 to 115-8 are electromagnets, and when an electric current is supplied, they generate an attractive force that attracts the moving blades 42a. When the moving blade 42a, which is a magnetic material, passes at high speed, the vibration receivers 116-1 to 116-8 generate a voltage by an electromagnetic induction action, and output this induced voltage as a detection signal.

The exciters 115-1 to 115-4 are arranged side by side in the circumferential direction in the right region of the mounting jig 114 in FIG. Specifically, the exciters 115-2, 115- are located at positions shifted clockwise by 11.25 °, 22.5 °, and 33.75 ° when viewed from the arrangement position of the exciter 115-1. 3,115-4 are arranged.
The exciters 115-5 to 115-8 are arranged side by side in the circumferential direction in the left region of the mounting jig 114 in FIG. Specifically, the exciter 115-6, 115- is located at a position deviated by 11.25 °, 22.5 °, and 33.75 ° in the clockwise direction when viewed from the arrangement position of the exciter 115-5. 7, 115-8 are arranged. Further, the exciter 115-5 is arranged at a position displaced by 180 ° in the circumferential direction when viewed from the exciter 115-1.
It should be noted that 11.25 ° = (90 ° ÷ 8), 22.5 ° = (90 ° ÷ 8) × 2, and 33.75 ° = (90 ° ÷ 8) × 3.

When performing a rotary vibration test, a rotational force is input to the rotary shaft 41 by a rotary drive source (not shown) to rotate the turbine 40 at a rotation speed required for the test. Further, in a preset vibration mode (for example, 8-node diameter mode), the rotor blades 42a vibrate in the out-of-plane direction, that is, in the direction intersecting the surface in which the rotor blades 42a are arranged in the rotor blade row 42. A suction force is applied to the rotor blades 42a by the shakers 115-1 to 115-8 to vibrate the rotor blades 42a.

When the rotor blade row 42 vibrates, the vibration receivers 116-1 to 116-8 output a detection signal according to the vibration state at that time, and the controller 200 vibrates the rotor blade 42a based on the detection signal. Vibration mode, etc.) can be detected. FIG. 3 is a schematic view showing a state in which the rotor blade row 42 vibrates in the out-of-plane direction in the 8-node diameter mode.
In this way, when the rotating rotor blade row 42 is vibrating in the preset vibration mode, the state of the rotor blade 42a is detected by various sensors (not shown) attached to the rotor blade 42a. , The vibration response of the moving blade 42a is measured, and the vibration characteristics (natural frequency, damping, etc.) are analyzed.

<Explanation of controller 200>
Next, the configuration of the controller 200 and the control by the controller 200 will be described with reference to FIG. The controller 200 is an information processing device in which software (program) and hardware (computer) cooperate to perform information processing. In FIG. 4, each arithmetic processing function (arithmetic processing process) is shown as a block diagram. Is shown.

From the input unit 210, a node diameter number N (where N is an integer) indicating a preset vibration mode (node diameter mode) is input to the controller 200. The controller 200 outputs vibration command signals a1 to a8 from the energization command units 201-1 to 201-8 so that the rotor blade row 42 vibrates in the vibration mode indicated by the number of node diameters N (N node diameter mode). .. The vibration command signals a1 to a8 have their waveforms, output timings, frequencies, and phases adjusted, and the adjusted states will be described later.

The amplifiers 220-1 to 220-8 generate the excitation currents A1 to A8 having the waveform, output timing, frequency, and phase corresponding to the excitation command signals a1 to a8, and the amplifiers 115-1 to 115. Supply to -8. The current detection sensors 221 to 221-8 sense the waveform, output timing, frequency, and phase of the excitation currents A1 to A8 and feed back the feedback signals f1 to f8 to the energization command units 201-1 to 201-8. .. The energization command units 201-1 to 201-8 receive feedback signals f1 to f8 and perform feedback control to more appropriately adjust the waveform, output timing, frequency, and phase of the vibration command signals a1 to a8.

When the exciting currents A1 to A8 whose waveform, output timing, frequency, and phase are appropriately adjusted are supplied to the exciter 115-1 to 115-8 in this way, the exciter 115-1 to 115 −8 generates an attractive force according to the waveform, output timing, frequency, and phase of the excitation currents A1 to A8, and vibrates the rotating blade row 42.

The vibration receivers 116-1 to 116-8 output detection signals b1 to b8 according to the vibration of the rotating blade row 42. The detection signals b1 to b8 are amplified by the amplifiers 2221-222-8 and then sent to the vibration mode detection unit 202 of the controller 200. The vibration mode detection unit 202 detects the vibration mode of the rotor blade row 42 based on the detection signals b1 to b8. The detected vibration mode waveform is displayed on the display unit 203.

The rotation detector 60 detects the rotation speed of the turbine 40 and the zero position in the rotation direction, and outputs the rotation speed signal R and the zero position signal Z. The rotation speed signal R and the zero position signal Z are sent to the controller 200.

Here, how to select and adjust the waveform, output timing, frequency, and phase of the vibration command signals a1 to a8 will be described.

In addition to the above-mentioned energization command unit 201-1 to 201-8, vibration mode detection unit 202, and display unit 203, the controller 200 includes an integrated calculation / command unit 204, a vibration frequency / phase calculation unit 205, and a vibration timing calculation. It has a unit 206, a vibration waveform selection unit 207, and an adjustment phase calculation unit 208. These arithmetic units cooperate to perform the following arithmetic processing.

(Determining the frequency of the vibration command signal)
The vibration frequency / phase calculation unit 205 vibrates the rotor blade row 42 in the N node diameter mode when the node diameter number N (for example, N = 8) is input from the input unit 210, and the vibration command signals a1 to a8 Frequency (vibration frequency) is obtained based on the following findings.
Prior to the following calculation, the excitation frequency / phase calculation unit 205 moves the frequency (rotation frequency) f _rpm of the moving blade train 42 and the motion seen from the stationary coordinate system based on the rotation speed signal R and the zero position signal Z. The rotation angle α of the blade row 42 is acquired.

FIG. 5 schematically shows the rotating blade row 42, where α is the rotation angle of the moving blade row 42 as seen from the stationary coordinate system, and θ is the rotation of the moving blade row 42 as seen from the rotating coordinate system. It is an angle, and the rotation speed of the rotor blade row 42 is 2πf _rpm . Therefore, the relationship between θ and α is
θ = 2πf _rpm t ± α ・ ・ ・ (1)
Will be.
_{The equation x θ} expressing the shape of the vibration mode in the rotating coordinate system is expressed by the following equation (2). Incidentally, f _i is the natural frequency of the blade 42a in snowfall diameter mode nodal diameter number N. X _i is an arbitrary value and is determined by the suction force of the exciters 115-1 to 115-8.
_{x θ = X i cos (2πf} i t + Nθ) ··· (2)
Substituting the equation (1) into the equation (2) indicating the shape of the vibration mode in the rotating coordinate system, the equation x _θ expressing the shape of the vibration mode in the stationary coordinate system is expressed by the following equation (3).
_{x θ = X i cos (2π} (Nf rpm ± f i) t + Nα) ··· (3)

Therefore, if the rotor blade row 42 is rotating at a frequency _{f rpm,} the vibration frequency _{f in} the vibration command signal a1 to _a8, if the _{f in = f rpm × N ±} f i, nodal diameter number N it is possible to vibrate the blades 42a at the natural frequency f _i of the snowfall diameter mode.
Vibration frequency and phase calculation unit 205, based on the above findings, determined as the vibration frequency _{f in = f rpm × N ±} f i of vibration command signal a1 to a8.

(Determination of the phase of the vibration command signal)
Further, the vibration frequency / phase calculation unit 205 calculates the phases of the vibration command signals a2, a3, a4, a5, a6, a7, and a8 with respect to the vibration command signal a1 as follows.
That is, the exciters 115-2, 115-3, 115 are displaced clockwise by 11.25 °, 22.5 °, and 33.75 ° when viewed from the arrangement position of the exciter 115-1. -4 is arranged, and 180 °, 180 ° + 11.25 °, 180 ° + 22.5 °, 180 ° + 33.75 ° shift in the clockwise direction when viewed from the arrangement position of the exciter 115-1. Exciters 115-5, 115-6, 115-7, 115-8 are arranged at the above positions. Therefore, when the number of node diameters is N, the phase lag (phase shift) of the vibration command signals a2, a3, a4, a5, a6, a7, and a8 with respect to the vibration command signal a1 is 11.25 ° × N, 22. .5 ° x N, 33.75 ° x N, 180 ° x N, (180 ° + 11.25 °) x N, (180 ° + 22.5 °) x N, (180 ° + 33.75 °) x N And. When N = 8, 11.25 ° × N is 90 °, 22.5 ° × N is 180 °, and 33.75 ° × N is 270 °.

Generally speaking, with respect to the phase of the excitation command signal a1 sent to the specific exciter 115-1 determined in advance, a predetermined angle γ is mechanically applied to the specific exciter 115-1. The phase of the vibration command signal sent to the exciter placed at the deviated position is deviated by N × γ.

In this way, the excitation frequency / phase calculation unit 205 determines the frequencies of the excitation command signals a1 to a8 and the phases of the excitation command signals a2 to a8 with respect to the excitation command signal a1.

(Determination of vibration timing)
The vibration timing calculation unit 206 determines the output timing (vibration timing) of the vibration command signals a1 to a8 based on the rotation speed signal R and the zero position signal Z output from the rotation detector 60. That is, the excitation force is applied to the same position in the circumferential direction of the rotor blade row 42 to determine the output timing for efficiently generating the vibration in the N-node diameter mode.
For example, the vibration timing calculation unit 206 sets the zero position signal Z every one rotation or every few rotations so that the position where the rotor blade 42a is excited by the vibration device 115-1 is the same in the circumferential direction. Based on this, the output timing of the vibration command signal a1 is corrected.

(Determining the waveform of the vibration command signal)
The vibration waveform selection unit 207 determines various waveforms as the signal waveforms of the vibration command signals a1 to a8. For example, the rectangular waveform shown in FIG. 6 (a), the sine half wave shown in FIG. 6 (b), and the sine wave shown in FIG. 6 (c) are defined (set) in advance, and a specific waveform is defined among them. Is selected and determined as the signal waveform of the vibration command signals a1 to a8.

Integrated computing and command unit 204, excitation frequency f _in a phase of vibration command signal a1~a8 obtained in the vibration frequency and phase calculation unit 205, and, vibration command signal obtained by the vibration timing calculating unit 206 The output timings (vibration timings) of a1 to a8 are held.

Integrated computing and command unit 204, retained excitation frequency _{f in} a phase, output timing, rectangular waveform (see FIG. 6 (a)) of the vibration command signal a1~a8 the current command unit 201-1～201- The rotor blade row 42 is pre-vibrated by the exciter 115-1 to 115-8 to output from No. 8. Then, the vibration mode waveform at this time is taken in from the vibration mode detection unit 202, and the amplitude of the vibration mode waveform is stored.
The integrated operation-instruction unit 204 holds the excitation frequency _{f in} a phase, output timing, half sine (Fig 6 (b) see) the vibration command signal a1~a8 energization command portion of 201-1 The rotor blades 42 are pre-vibrated by the exciters 115-1 to 115-8, which are output from ~ 201-8. Then, the vibration mode waveform at this time is taken in from the vibration mode detection unit 202, and the amplitude of the vibration mode waveform is stored.
Furthermore, integrated computing and command unit 204, retained excitation frequency _{f in} a phase, output timing, sinusoidal wave (FIG. 6 (c) refer) to vibration command signal a1~a8 energization command of 201-1～ The output is output from 201-8, and the rotating blade train 42 is pre-vibrated by the exciters 115-1 to 115-8. Then, the vibration mode waveform at this time is taken in from the vibration mode detection unit 202, and the amplitude of the vibration mode waveform is stored.
Then, a waveform that can maximize the amplitude of the vibration mode waveform, that is, a waveform that easily causes vibration in the N-node diameter mode (for example, a sine wave) is determined.

(Calculation of adjustment phase)
The adjustment phase calculation unit 208 is set with adjustment phases θc1 to θc8 for correcting (adjusting) the response delay of each of the exciters 115-1 to 115-8. FIG. 7 shows the output characteristic of any one of the exciters 115-1 to 115-8, and FIG. 7 (a) shows the waveform obtained by squaring the excitation current input to the exciter. , FIG. 7B shows the exciting force (suction force) output from the exciting device. Since the delay of the excitation force of the exciter can be known from the characteristics of FIGS. 7A and 7B, the adjustment phase for correcting the delay of the excitation force is set in the adjustment phase calculation unit 208. ..

Further, the adjustment phase calculation unit 208 is set with adjustment phases θc11 to θc18 for correcting (adjusting) the detection response delay of the current detection sensors 221 to 221-8. The adjustment phases θc11 to θc18 are obtained by measuring the detection response delay characteristic of the current detection sensors 221 to 221-8 in advance.

Further, the adjustment phase calculation unit 208 is adjusted to correct (adjust) the response delay from the detection of the rotation speed and the zero position to the output of the rotation speed signal R and the zero position signal Z by the rotation detector 60. The phases θcr and θcZ are set. The adjustment phases θcr and θcZ are obtained by measuring the response delay characteristic of the rotation detector 60 in advance.

Eventually, after the excitation command signals a1 to a8 are output from the energization command units 201-1 to 201-8 to the adjustment phase calculation unit 208, the excitation force is output from the exciters 115-1 to 115-8. In order to correct the delay that occurs until the current detection sensor is used, the adjustment phases θc1 to θc8 for the exciters 115-1 to 115-8 and the adjustment phases θc11 to θc18 for the current detection sensors 221 to 221-8 are used. The adjustment phases θcr and θcZ for the rotation detector 60 are set.

The integrated calculation / command unit 204 determines the waveform, output timing, frequency, and phase of the vibration command signals a1 to a8 as follows.

(1) Vibration command signal a1
Excitation frequency _{f in} the vibration command signal a1 was determined by the vibration frequency and phase calculation unit 205, employing the vibration frequency _{f in = f rpm × N ±} f i.
As the vibration timing (output timing), the output timing for the vibration command signal a1 determined by the vibration timing calculation unit 206 is adopted.
The waveform of the vibration command signal a1 determines the waveform determined by the vibration waveform selection unit 207.
The phase of the vibration command signal a1 is phase-adjusted by the adjustment phases θc1, θc11, θcr, and θcZ obtained by the adjustment phase calculation unit 208.

(2) Vibration command signal a2
Excitation frequency _{f in} the vibration command signal a2 was determined by the vibration frequency and phase calculation unit 205, employing the vibration frequency _{f in = f rpm × N ±} f i.
As the vibration timing (output timing), the output timing for the vibration command signal a2 determined by the vibration timing calculation unit 206 is adopted.
The waveform of the vibration command signal a2 determines the waveform determined by the vibration waveform selection unit 207.
The phase of the vibration command signal a2 is phase-adjusted by the adjustment phases θc2, θc12, θcr, and θcZ obtained by the adjustment phase calculation unit 208, and further, the vibration is obtained by the vibration frequency / phase calculation unit 205. The phase shift for the command signal a2 (the phase shift with respect to the excitation command signal a1) is also adjusted.

(3) Vibration command signals a3 to a8
Excitation frequency _{f in} the vibration command signal a3~a8 was determined by the vibration frequency and phase calculation unit 205, employing the vibration frequency _{f in = f rpm × N ±} f i.
As the vibration timing (output timing), the output timings for the vibration command signals a3 to a8 determined by the vibration timing calculation unit 206 are adopted.
The waveforms of the vibration command signals a3 to a8 are determined by the vibration waveform selection unit 207.
The phase of the vibration command signals a3 to a8 is adjusted by the amount of the adjustment phases θc3 to θc8, θc13 to θc18, θcr, and θcZ obtained by the adjustment phase calculation unit 208 obtained by the vibration frequency / phase calculation unit 205. Further, the phase shift for the vibration command signals a3 to a8 (the phase shift with respect to the vibration command signal a1) is also phase-adjusted.

The integrated calculation / command unit 204 outputs the excitation command signals a1 to a8 having the waveform, output timing, frequency, and phase determined as described above from the energization command unit 201-1 to 201-8. Command.
As a result, the excitation command signals a1 to a8 having the waveform, output timing, frequency, and phase-adjusted phase determined as described above are output from the energization command units 201-1 to 201-8 to be excited. Excitation currents A1 to A8 corresponding to the command signals a1 to a8 are supplied to the exciters 115-1 to 115-8, and the rotor blades 42a are vibrated (suctioned) by the exciters 115-1 to 115-8. .. As a result, it is possible to excite the rotor blade row 42 with accurate vibration in the N-node diameter mode corresponding to the number of node diameters N input from the input unit 210.

As described above, in the present embodiment, by adjusting the waveform, output timing, frequency, and phase of the excitation command signals a1 to a8, the vibration mode of the N-node diameter mode with high accuracy corresponding to the input node diameter number N Is easily excited to the rotor blade row 42.
That is, by controlling the shape of the waveform of the vibration command signals a1 to a8, it becomes easier to excite in the set node diameter mode, and by controlling the frequency and the vibration timing of the vibration command signals a1 to a8, it is useless. It is possible to input the exciting force to the moving blade accurately, and by controlling the phase of the exciting command signals a1 to a8 according to the mode shape, it is possible to input the exciting force according to the vibration mode, which is set. It becomes easier to excite the vibration mode.

In this way, the excitation force of the rotor blade row 42 can be synchronized and the excitation force can be input without waste. Therefore, even if the number of excitation devices is reduced as compared with the conventional case, the desired excitation is achieved. The mode can be properly excited.

That is, the non-contact vibration system 100 according to the first embodiment described above has the following effects.
(1) The non-contact excitation system 100 is configured so that excitation force can be applied to the rotor blade rows 42 of the rotating machine, and a plurality of exciters 115 arranged in the circumferential direction and the rotor blade rows 42. A rotation speed sensor 60, which is a rotation speed sensor for detecting the rotation speed, and a controller 200 for outputting a vibration signal to each of the plurality of vibration units 115 are provided. Controller 200, a rotation frequency _{f rpm} of rotor blade row 42 obtained from the detection result of the rotation detector 60, by using the natural frequency _{f i} of the blade 42a in N clause diameter _mode, f in _{= f rpm} and it is configured to output a vibration signal of a frequency f _in represented by × N ± f _i to each of the vibrator 115.
_Thus, by outputting _{f in = f rpm × N ±} f i excitation current A1~A8 a vibration signal of a frequency _{f in,} represented by the respective vibrator 115, a rotor blade row 42 It is possible to accurately vibrate in the N-node diameter mode.

(2) The plurality of exciters 115 include a pair of exciters 115 provided at angles γ in the circumferential direction. The controller 200 uses the excitation signal output to one of the pair of exciters 115 as a reference, and transmits the excitation signal having a phase difference of N × γ to the other of the pair of exciters 115. It is configured to output to the exciter 115.
As a result, the phase of the excitation signal output to the pair of exciters 115 provided at an angle γ deviation in the circumferential direction can be optimized.

(3) number can be the following vibrator 115 2N, to vibrate the rotor blade row 42 is rotating at a natural frequency f _i of snowfall diameter mode nodal diameter number N. As a result, the number of the exciters 115 in the non-contact excitation system 100 can be 2N or less, so that the cost increase of the non-contact excitation system 100 can be suppressed.

(4) The controller 200 is configured to output a vibration signal represented by a sine wave or a sine half wave to each of the vibration devices 115.
As a result, an excitation signal represented by a sine wave or a sine half wave is output to each of the exciters 115, so that it becomes easy to excite in the set node diameter mode.

(5) The controller 200 selects the waveform having the maximum amplitude in the N-node diameter mode from a plurality of types of waveform candidates of the excitation signal, and applies the excitation signal of the selected waveform to each of the exciters 115. It is configured to output to.
As a result, the waveform having the maximum amplitude in the N-node diameter mode is selected from a plurality of types of waveform candidates of the excitation signal, and the excitation signal of the selected waveform is output to each of the exciter 115. Therefore, it becomes easy to excite in the set node diameter mode.

(6) The non-contact vibration system 100 includes a rotation detector 60, which is a reference position sensor that detects a reference position signal indicating a reference position in the rotation direction of the rotor blade row 42. The controller 200 is configured to generate a vibration signal according to the vibration timing determined based on the reference position signal.
As a result, the controller 200 generates the vibration signal according to the vibration timing determined based on the reference position signal, so that the vibration in the N-node diameter mode with high accuracy can be excited to the rotor blade row 42.

(7) The controller 200 corrects the excitation timing by each of the exciters 115 based on the delay phase at the time when the excitation force is generated by the exciter 115 with respect to the output time of the excitation signal by the controller 200. It is configured in.
As a result, the excitation timing by each exciter 115 is corrected based on the delay phase at the time when the excitation force is generated with respect to the output time of the excitation signal, so that the excitation force is applied to the rotor blade row 42. Can be given efficiently.

[Embodiment 2]
Next, with reference to FIGS. 8 and 9, a device that excites the rotor blade row 42 of the turbine 40 by two vibration mode exciters 110a and 110b will be described as the second embodiment.

As shown in FIG. 8, in the second embodiment, two vibration mode exciters 110a and 110b are arranged facing each other with the rotor blade row 42 of the turbine 40 sandwiched between them. As a result, the exciter 115-1 to 115-8 and the exciter 116-1 to 116-8 are arranged on one side of the rotor blade row 42, and the exciter 115 is also arranged on the other side of the rotor blade row 42. -1 to 115-8 and receivers 116-1 to 116-8 are arranged. The vibration mode excitation devices 110a and 110b have the same structure as the vibration mode excitation device 110 shown in the first embodiment. In FIG. 8, the same ones shown in FIG. 1 are designated by the same reference numerals, and duplicate description will be omitted.

FIG. 9A shows an exciting force (suction force) generated by the vibration mode exciter 110a, and the moving blade 42a is moved to the vibration mode exciter 110a side as it goes upward in the vertical axis direction in the figure. It shows that the suction force becomes stronger.
FIG. 9B shows the exciting force (suction force) generated by the vibration mode exciter 110b, and the moving blade 42a is moved to the vibration mode exciter 110b side as it goes downward in the vertical axis direction in the figure. It shows that the suction force becomes stronger.

As shown in FIGS. 9A and 9B, when the vibration mode excitation device 110a has the maximum excitation force (suction force), the vibration mode excitation device 110b has the minimum excitation force (suction force). Therefore, the phases of the suction forces of both are shifted by 180 ° so that the excitation force (suction force) of the vibration mode excitation device 110b is maximized when the excitation force (suction force) of the vibration mode excitation device 110a is the minimum. ing.
That is, the excitation currents A1 to A8 (excitation command signals a1 to a8) supplied to the exciters 115-1 to 115-8 of the vibration mode exciter 110a and the exciter 115-1 of the vibration mode exciter 110b. The phase difference between the vibration currents A1 to A8 (vibration command signals a1 to a8) supplied to ~ 115-8 is set to 180 °.
Therefore, as shown by the alternate long and short dash line in FIG. 9 (c), the force for exciting the rotor blade 42a is the excitation force (solid line) generated by the vibration mode exciter 110a and the force generated by the vibration mode exciter 110b. The vibration force (dotted line) is added, and the rotor blade 42a can be vibrated with a stronger vibration force.

As described above, in the non-contact excitation system 100 according to the second embodiment described above, the plurality of exciters 115 are the exciter 115 as the first exciter included in the vibration mode exciter 110a and the rotating machine. The second exciter included in the vibration mode exciter 110b provided on the side opposite to the exciter 115 as the first exciter across the rotor blade row 42 in the axial direction is included. The controller 200 is configured to output a second excitation signal that is 180 ° out of phase with respect to the first excitation signal that is output to the first excitation device. ..
As a result, the rotor blade train can be vibrated with a stronger excitation force.

In the first embodiment, the vibration receivers 116-1 to 116-8 arranged in the vibration mode excitation device 110 are used, and in the second embodiment, the vibration receivers 116-1 to 116-8 arranged in the vibration mode excitation devices 110a and 110b are used. Although the vibration state (vibration mode) of the rotor blade row 42 of the turbine 40 is detected, the means for detecting the vibration mode is not limited to this.
For example, the vibration receivers 116-1 to 116-8 may not be arranged on the vibration mode excitation devices 110, 110a, 110b, and instead, the vibration detection sensor may be attached to the moving blade 42a or the like.

Further, in the first embodiment, the vibration mode detection unit 202 and the display unit 203 are provided in the control roller 200, but the vibration mode detection unit 202 and the display unit 203 are not provided in the control roller 200, and the vibration mode detection is performed. The unit 202 and the display unit 203 may be provided in the external system.

[Embodiment 3]
Next, the third embodiment will be described with reference to FIGS. 10 to 14.
In the first and second embodiments described above, the vibration mode of the rotor blade row 42 is detected based on the detection signals output from the vibration receivers 116-1 to 116-8. In the third embodiment, the vibration mode of the rotor blade row 42 is detected based on the detection signal from the passage detection sensor for detecting the passage of each rotor blade 42a arranged around the rotor blade row 42. Hereinafter, a detailed description will be given. In the following description, the same components as those in the first embodiment are designated by the same reference numerals, and the differences will be mainly described. The points not particularly described are the same as those in the first embodiment.

FIG. 10 is a diagram showing a configuration according to a method for detecting a vibration mode of the rotor blade row 42 in the third embodiment. The first moving blade 42a-1, the second moving blade 42a-2, the third moving blade 42a-3 ... The nth moving blade 42a-n, which are n moving blades 42a, are attached around the rotating shaft 41. Has been done. In the vibration mode exciter 110 according to the third embodiment, the first passage of m passage detection sensors 117 at equal pitch or unequal pitch is performed at a position facing the outer peripheral side (tip side) end of each rotor blade 42a. The detection sensor 117-1, the second pass detection sensor 117-2, the third pass detection sensor 117-3 ... The mth pass detection sensor 117-m is installed. Each passage detection sensor 117 may be, for example, an optical sensor, a capacitance type sensor, or an eddy current type sensor. As long as the passage of the moving blade 42a can be detected, various detection type sensors can be used for the passage detection sensor 117.
The detection signal of each passage detection sensor 117 is configured to be input to the controller 200 and processed by the controller 200.
That is, the vibration displacement detection devices 70 according to the third embodiment are arranged along the circumferential direction, and include a plurality of passage detection sensors 117 for detecting the passage of each rotor blade 42a of the rotor blade row 42, and a plurality of passages. It includes a controller 200 as a signal processing unit for processing the detection signal of the detection sensor 117.
The controller 200 is also input with the signal of the rotation detector 60 described above, which is a reference position sensor for detecting the zero position (reference position) of the rotation shaft 41.

FIG. 11 is an explanatory diagram of waveform processing according to the method for detecting the vibration mode of the rotor blade row 42 in the third embodiment. In FIG. 11, the outputs of the first pass detection sensor 117-1, the second pass detection sensor 117-2, the third pass detection sensor 117-3, ... Are shown in order from the top, and the rotation detector 60 is shown at the bottom. Shows the output. The solid line shows the output from each passage detection sensor 117 in the reference state where the rotor blade row 42 is not vibrating. The broken line indicates the output from each passage detection sensor in the state where the rotor blade row 42 is vibrating (vibration state).
The first passage detection sensor 117-1 has a signal S11 due to the passage of the first rotor blade 42a-1, a signal S12 due to the passage of the second rotor blade 42a-2, and a signal S13 due to the passage of the third rotor blade 42a-3.・ Output. The second passage detection sensor 117-2 outputs a signal S21 due to the passage of the first rotor blade 42a-1, a signal S22 ... due to the passage of the second rotor blade 42a-2, and so on. Similarly, the third passage detection sensor 117-3 outputs the signal S31 ... Due to the passage of the first rotor blade 42a-1.

The controller 200 calculates the first passage timing at which each rotor blade 42a passes through each passage detection sensor 117 assuming that the rotor blade row 42 is not vibrating. That is, the controller 200 calculates the output timing of the signal from each passage detection sensor 117, which is estimated to be output in the reference state, as the first passage timing, as shown by the solid line in FIG.
Further, the controller 200 acquires the passing timing of each moving blade 42a as the second passing timing based on the signal actually detected by each passing detection sensor 117 as shown by the broken line in FIG.
Then, the controller 200 compares the calculated first pass timing with the second pass timing of each rotor blade 42a actually detected by each pass detection sensor 117, and calculates the pass time difference Δτ.

Specifically, the controller 200 has a passage time difference Δτ1 between the reference state and the vibration state of the first rotor blade 42a-1 at the installation position of the first passage detection sensor 117-1 for the first rotor blade 42a-1. The passage time difference between the reference state and the vibration state of the first rotor blade 42a-1 at the installation position of the second passage detection sensor 117-2 Δτ2, and the first rotor blade 42a- at the installation position of the third passage detection sensor 117-3. The transit time difference Δτ3 ... Between the reference state and the vibration state of 1 is calculated. Similarly, for the other rotor blades 42a-2 to 42an, the controller determines the reference state and vibration state of each rotor blade 42a-2 to 42a-n at the installation position of each passage detection sensor 117. The transit time difference Δτ of each is calculated.

The controller 200 displaces (amplitude) δ1-1 and δ1-2 with respect to the first rotor blade 42a-1 based on the transit time difference Δτ calculated as described above and the peripheral speed u of the rotor blade row 42. , Δ1-3 ...
By plotting the amplitudes δ1-1, δ1-2, δ1-3 ... Obtained in this manner with the time axis as the horizontal axis as shown in FIG. 12, the vibration waveform of the first rotor blade 42a-1. Is obtained. FIG. 12 is a graph showing the vibration waveform of the first rotor blade 42a-1. That is, the controller 200 plots the calculated amplitudes δ1-1, δ1-2, δ1-3 ... With the time axis as the horizontal axis as shown in FIG. 12, so that the vibration of the first rotor blade 42a-1 is vibrated. Get the waveform.

The controller 200 similarly acquires vibration waveforms for the other rotor blades 42a-2 to 42an. Then, the controller 200 calculates the vibration displacement of the rotor blade row 42 in the out-of-plane direction based on these acquired vibration waveforms, and detects the vibration mode of the rotor blade row 42.

As described above, the vibration displacement detection devices 70 described above are arranged along the circumferential direction, and a plurality of passage detection sensors 117 for detecting the passage of each rotor blade 42a of the rotor blade row 42, and a plurality of passage detections. It includes a controller 200 as a signal processing unit for processing the detection signal of the sensor 117. The controller 200 calculates the first passage timing at which each rotor blade 42a passes through the plurality of passage detection sensors 117 assuming that the rotor blade row 42 is not vibrating. The controller 200 calculates the displacement (amplitude) of the moving blades 42a due to vibration by comparing the calculated first passing timing with the second passing timings of the moving blades 42a actually detected by the plurality of passing detection sensors 117. The controller 200 calculates the vibration displacement of the rotor blade row 42 based on the calculated displacement of the rotor blade 42a due to the vibration.
As a result, the vibration displacement of the rotor blade row 42 can be calculated accurately.

Further, in the third embodiment, the vibration displacement of the rotor blade row 42 in the out-of-plane direction calculated as described above and the vibration displacement of the vibration in the N-node diameter mode to be excited by the rotor blade row 42 The difference is calculated, and the vibration signal is corrected so that the difference becomes small.
FIG. 13 is a graph showing the mode shape of the 6-node diameter mode as an example of the mode shape of the vibration to be excited by the rotor blade row 42 and the mode shape of the actual vibration mode generated in the rotor blade row 42. ..

For example, there is a slight difference in the fixed state of the rotor blade 42a from the rotating shaft 41, or there is a slight difference within the manufacturing tolerance of the rotor blade 42a. Since there is a slight difference in the natural frequency of each blade 42a, the mode shape of the N-node diameter mode may be distorted even if an exciting force is applied so as to vibrate in the N-node diameter mode. For example, even if the rotor blade row 42 is to be vibrated in the 6-node diameter mode in which the mode shape is arranged as shown by the curve 91 shown by the alternate long and short dash line in FIG. 13, the actual vibration mode shape of the rotor blade row 42 is shown in FIG. There is a risk of distortion as shown by the curve 92 shown by the solid line of 13.
Therefore, in the present embodiment, the distortion of the mode shape in the N-node diameter mode is corrected as follows.

FIG. 14 is a flowchart showing a process of correcting the distortion of the mode shape in the N-node diameter mode executed by the controller 200. For example, when the output of the vibration command signal from the controller 200 is started so as to vibrate in the N-node diameter mode, the process of this program is executed by the controller 200.
In step S10, the controller 200 calculates the mode shape of the N-node diameter mode to be excited to the rotor blade row 42 as the target mode shape. Next, in step S20, the controller 200 calculates the actual vibration mode shape of the rotor blade row 42 from the vibration displacement of the rotor blade row 42 calculated as described above based on the output signal from the passage detection sensor 117. To do. Then, in step S30, the controller 200 calculates the difference between the target mode shape calculated in step S10 and the actual vibration mode shape calculated in step S20.

In step S40, the controller 200 determines whether or not the difference between the target mode shape calculated in step S30 and the actual vibration mode shape is within a predetermined allowable range.
If the difference between the target mode shape and the actual vibration mode shape is not within a predetermined allowable range, step S40 is negatively determined, and the process proceeds to step S50. In step S50, the controller 200 performs a correction process for adjusting the waveform, output timing, frequency, and phase of the vibration command signals a1 to a8 so that the actual vibration mode shape approaches the target mode shape. Then, the controller 200 controls each unit so as to output the excitation currents A1 to A8 corresponding to the excitation command signals a1 to a8 after the correction process, and returns to step S20.
If the difference between the target mode shape and the actual vibration mode shape is within a predetermined allowable range, step S40 is positively determined, and the process by this program ends.

As described above, the non-contact vibration system 100 according to the present embodiment includes a vibration displacement detection device 70 for detecting the vibration displacement of the rotor blade row 42. The controller 200 corrects the vibration command signals a1 to a8 so that the vibration displacement detected by the vibration displacement detection device 70 approaches the target vibration displacement of the rotor blade row 42, so that the vibration displacement devices 115-1 to 115- The vibration currents A1 to A8, which are the vibration signals output to each of 8, are corrected.
As a result, accurate vibration in the N-node diameter mode can be excited in the rotor blade row 42.

[Embodiment 4]
The fourth embodiment will be described with reference to FIGS. 15 to 17.
In the fourth embodiment, the amplitude of the vibration in the N-node diameter mode approaches zero by utilizing the principle of correcting the distortion of the mode shape in the N-node diameter mode in the third embodiment. That is, in the fourth embodiment, the vibration of the moving blade row 42 is canceled by applying an exciting force to the vibrating rotor blade row 42. In the following description, the same components as those in the third embodiment are designated by the same reference numerals, and the differences will be mainly described. The points not particularly described are the same as those in the third embodiment.

FIG. 15 is a block diagram showing the overall configuration of the vibration suppression system 300 of the rotating machine according to the fourth embodiment. The vibration suppression system 300 includes a vibration exciter 115-1 to 115-8, a vibration displacement detection device 70, a rotation detector 60, and a controller 200. The vibration displacement detection device 70 includes the passage detection sensor 117, that is, the first passage detection sensor 117-1 to the mth passage detection sensor 117-m, and the controller 200 as a signal processing unit for processing the detection signal of the passage detection sensor 117. And include.

FIG. 16 is a flowchart showing a vibration suppression process executed by the controller 200. For example, when the vibration suppression system 300 according to the fourth embodiment is started, the processing of this program is executed by the controller 200.
In step S110, the controller 200 calculates the vibration displacement of the rotor blade row 42 based on the output timing of the signal from each passage detection sensor 117, as described in the third embodiment. Then, in step S120, the controller 200 determines the vibration mode of the rotor blade row 42 based on the vibration displacement of the rotor blade row 42 calculated in step S110. That is, the controller 200 obtains the number of nodal diameters N of the vibration in the nodal diameter mode based on the vibration displacement of the rotor blade row 42 calculated in step S110.

In step S130, the controller 200 generates vibration command signals a1 to a8 that cancel the vibration of the rotor blade row 42. That is, the controller 200 has known nodes in advance, such as the node diameter number N calculated in step s120 and the frequency (rotation frequency) f _{rpm of the moving blade train 42 calculated based on the detection signal from the rotation detector 60.} on the basis of the natural frequency _{f i} of the blade 42a in snowfall diameter mode diameter of several N, determined as the vibration frequency _{f in = f rpm × N ±} f i of vibration command signal a1 to a8.
Then, the controller 200 determines the phases of the vibration command signals a2, a3, a4, a5, a6, a7, and a8 with respect to the vibration command signal a1 in the same manner as in the first embodiment. Further, the controller 200 determines the output timing (vibration timing) of the vibration command signals a1 to a8 based on the rotation speed signal R and the zero position signal Z output from the rotation detector 60. Further, the controller 200 determines the waveform and amplitude of the vibration command signals a1 to a8 based on the vibration displacement of the rotor blade row 42 calculated in step S110.

In step S130, the controller 200 moves by performing the same processing as the correction processing of step S50 of FIG. 14 in the above-described third embodiment based on the vibration displacement of the rotor blade row 42 calculated in step S110. The waveform, output timing, frequency, and phase of the vibration command signals a1 to a8 are further adjusted so that the vibration amplitude of the blade row 42 approaches zero.

In step S140, each unit is controlled so as to output the excitation currents A1 to A8 corresponding to the excitation command signals a1 to a8 generated in step S130.

By executing the processes from step S110 to step S140 in this way, a vibrating force is applied to the rotor blade row 42 vibrating in the mode shape as shown by the solid line curve 93 in FIG. The vibration of 42 is canceled, and the amplitude of the vibration of the rotor blade row 42 approaches zero as shown by the curve 94 of the two-point chain line in FIG. FIG. 17 shows an example of the mode shape of the vibration generated in the rotor blade row 42 before the vibration suppression treatment is performed, and the case where the vibration generated in the rotor blade row 42 is suppressed by the vibration suppression treatment. It is a figure which shows typically the mode shape of.

As described above, the vibration suppression system 300 according to the fourth embodiment is configured to be able to apply a vibrating force to the moving blade row 42 of the rotating machine, and has a plurality of vibrating devices 115 arranged in the circumferential direction. It is detected by a vibration displacement detection device 70 for detecting the vibration displacement of the blade row 42, a rotation detector 60 which is a rotation speed sensor for detecting the rotation speed of the moving blade row 42, and a vibration displacement detection device 70. A controller 200 for outputting a vibration signal to each of the plurality of vibration devices 115 is provided so that the vibration displacement becomes small. Controller 200, a rotation frequency _{f rpm} of rotor blade row 42 obtained from the detection result of the rotation detector 60, by using the natural frequency _{f i} of the blade 42a in N clause diameter _mode, f in _{= f rpm} It is configured to generate an excitation signal of frequency f _in represented by × N ± f _i.
Thus, by outputting _{f in = f rpm × N ±} f i excitation current A1~A8 a vibration signal of a frequency _{f in,} represented by the respective vibrator 115, the rotor blade row 42 Vibration in the N-node diameter mode can be effectively suppressed.

In the fourth embodiment, the vibration displacement detection devices 70 are arranged along the circumferential direction, and a plurality of passage detection sensors 117 for detecting the passage of each rotor blade 42a of the rotor blade row 42, and a plurality of passage detection sensors. It includes a controller 200 as a signal processing unit for processing the detection signal of 117. The controller 200 calculates the first pass timing at which each rotor blade 42a passes through the plurality of passage detection sensors 117 when it is assumed that the rotor blade train 42 is not vibrating, and the calculated first pass timing and the plurality of pass timings are calculated. The displacement due to the vibration of the moving blades 42a is calculated by comparing with the second passing timing of each moving blade 42a actually detected by the passing detection sensor 117. The controller 200 calculates the vibration displacement of the rotor blade row 42 based on the calculated displacement of the rotor blade 42a due to the vibration.
As a result, the vibration displacement of the rotor blade row 42 can be calculated accurately, so that the vibration of the rotor blade row 42 in the N-node diameter mode can be suppressed more effectively.

The present invention is not limited to the above-described embodiment, and includes a modified form of the above-described embodiment and a combination of these embodiments as appropriate.
For example, in each of the above-described embodiments, the vibration state of the moving blade 42a is detected by using the vibration receiver 116 and the passage detection sensor 117. However, instead of the vibration receiver 116 and the passage detection sensor 117, for example, a strain gauge attached to each rotor blade 42a may be used to detect the vibration state of the rotor blade 42a. Further, instead of the passage detection sensor 117, a plurality of pressure sensors arranged at the same positions as the passage detection sensor 117 are used, and the vibration state of the moving blade 42a is detected by detecting the fluctuation of the wind pressure accompanying the passage of the moving blade 42a. It may be detected.
The number of strain gauges and pressure sensors arranged is appropriately set according to the vibration mode to be excited.

In the above-described embodiment, the turbine 40 has been described as an example of the vibration control target of the non-contact vibration system 100 and the vibration suppression system 300, but the vibration control of the non-contact vibration system 100 and the vibration suppression system 300 described above has been described. The target is not limited to the turbine 40, and may be any rotating body having a plurality of blades used in various rotating machines. For example, it may be a rotating body of various rotating machines used in a steam turbine, a gas turbine, a turbo compressor, a pump, a blower, a water turbine, a wind turbine, a vacuum pump, and the like.

40 Turbine 42 Moving blade row 42a Moving blade 50 Rotational vibration test device 60 Rotation detector 70 Vibration displacement detection device 100 Non-contact vibration system 110, 110a, 110b Vibration mode vibration device 115 Vibration device 116 Vibration receiver 117 Passage detection sensor 200 Controller 300 Vibration suppression system

Claims (12)

A plurality of exciters arranged in the circumferential direction while being configured to be able to apply excitation force to the rotor blade row of the rotating machine,
A rotation speed sensor for detecting the rotation speed of the rotor blade row and
A controller for outputting a vibration signal to each of the plurality of vibrators is provided.
Said controller wherein a rotational speed rotational frequency f _rpm of the rotor blade sequence obtained from the detection result of the sensor, by using the natural frequency f _i blade at the N-clause diameter mode, f _{in =} f _rpm × non-contact vibration system, characterized in that it is configured so that the excitation signal of frequency f _in, represented by N ± f _i output to each of the vibrator. The plurality of exciters include a pair of exciters provided at an angle γ in the circumferential direction.
The controller uses the excitation signal output to one of the pair of exciters as a reference, and transmits the excitation signal having a phase difference of N × γ to the other of the pair of exciters. The non-contact excitation system according to claim 1, wherein the non-contact excitation system is configured to output to a shaker. The non-contact excitation system according to claim 1 or 2, wherein the number of the exciters is 2N or less. The invention according to any one of claims 1 to 3, wherein the controller is configured to output the vibration signal represented by a sine wave or a sine half wave to each of the vibration devices. Non-contact vibration system. The controller selects a waveform having the maximum amplitude in the N-node diameter mode from a plurality of types of waveform candidates of the vibration signal, and transfers the vibration signal of the selected waveform to each of the vibration devices. The non-contact vibration system according to any one of claims 1 to 4, wherein the non-contact vibration system is configured to output to. A reference position sensor for detecting a reference position signal indicating a reference position in the rotation direction of the rotor blade row is further provided.
The non-one of claims 1 to 5, wherein the controller is configured to generate the vibration signal according to a vibration timing determined based on the reference position signal. Contact excitation system. The controller is configured to correct the excitation timing by each of the exciters based on the delay phase at the time when the excitation force is generated by the exciter with respect to the output time of the excitation signal by the controller. The non-contact excitation system according to any one of claims 1 to 6, wherein the non-contact vibration system is characterized. The plurality of exciters
With the first exciter
A second exciter provided on the side opposite to the first exciter across the rotor blade row in the axial direction of the rotating machine, and
Including
The controller is configured to output a second excitation signal that is 180 ° out of phase with respect to the first excitation signal that is output to the first excitation device. The non-contact excitation system according to any one of claims 1 to 7. Further provided with a vibration displacement detection device for detecting the vibration displacement of the rotor blade row,
The controller is characterized in that the vibration signal output to each of the vibrators is corrected so that the vibration displacement detected by the vibration displacement detection device approaches the target vibration displacement of the rotor blade train. The non-contact vibration system according to any one of claims 1 to 8. The vibration displacement detection device is
A plurality of passage detection sensors arranged along the circumferential direction and for detecting the passage of each rotor blade in the rotor blade row,
A signal processing unit for processing the detection signals of the plurality of passage detection sensors, and
Including
The signal processing unit
Assuming that the rotor blades are not vibrating, the first passage timing at which each rotor blade passes through the plurality of passage detection sensors is calculated.
The calculated displacement due to vibration of the moving blades is calculated by comparing the calculated first passing timing with the second passing timing of each moving blade actually detected by the plurality of passing detection sensors.
The non-contact vibration system according to claim 9, wherein the vibration displacement of the rotor blades is calculated based on the calculated displacement of the rotor blades due to vibration. A plurality of exciters arranged in the circumferential direction while being configured to be able to apply excitation force to the rotor blade row of the rotating machine,
A vibration displacement detection device for detecting the vibration displacement of the rotor blade row, and
A rotation speed sensor for detecting the rotation speed of the rotor blade row and
A controller for outputting a vibration signal to each of the plurality of vibrators is provided so that the vibration displacement detected by the vibration displacement detection device becomes small.
Said controller wherein a rotational speed rotational frequency f _rpm of the rotor blade sequence obtained from the detection result of the sensor, by using the natural frequency f _i blade at the N-clause diameter mode, f _{in =} f _rpm × vibration suppression system of the rotating machine, characterized in that it is configured to generate the excitation signal of frequency f _in, represented by N ± f _i. The vibration displacement detection device is
A plurality of passage detection sensors arranged along the circumferential direction and for detecting the passage of each rotor blade in the rotor blade row,
A signal processing unit for processing the detection signals of the plurality of passage detection sensors, and
Including
The signal processing unit
Assuming that the rotor blades are not vibrating, the first passage timing at which each rotor blade passes through the plurality of passage detection sensors is calculated.
The calculated displacement due to vibration of the moving blades is calculated by comparing the calculated first passing timing with the second passing timing of each moving blade actually detected by the plurality of passing detection sensors.
The vibration suppression system for a rotating machine according to claim 11, wherein the vibration displacement of the rotor blades is calculated based on the calculated displacement of the rotor blades due to vibration.

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