CN102801373A - Motor driving system and method - Google Patents

Abstract

The present invention provides a motor driving system capable of suppressing vibration of a resonance phenomenon independent of special control. The resonance phenomenon is characterized in that: shaft twisting vibration occurs on a generator shaft, the vibration becomes generator terminal voltage variation to be transmitted towards an inverter for driving the motor, so that the generator terminal voltage varies and the motor shaft vibrates, and the vibration further enables the generator shaft to vibrate. The motor driving system has a prime motor, a generator for generating electricity through driving of the prime motor, a converter for converting the electric power generated by the generator into the electric power with an expected frequency, a motor driven through the electric power supplied from the converter, and a driven device driven by the motor; wherein, a shaft resonant frequency of the generator shaft for transmitting a driving force of the prime motor towards the generator is different from a shaft resonant frequency of the motor shaft for transmitting a driving force of the motor towards the driven device.

Description

Electric motor drive system and method

Technical field

The present invention relates to the most suitablely prevent, connect the electric motor drive system and the method for the caused covibration of axle twisting vibration of the motor reel of motor and driven device by the generator shaft that connects prime mover and generator.

Background technology

In recent years, from saving viewpoint of energy, used through electric power converter mostly the power conversions of sending of generator was carried out electric motor driven technology as variable frequency to rotation load such as compressor, fan, air blasts.For example; Up to now; Carry out the system that is directly driven by steam turbine or gas turbine being carried out the motorized of variable speed drive through motor and power inverter; Because of system is different, turbo generator is set as power-supply device and exist, convert electric energy therefrom to situation that mechanical energy is carried out variable speed drive once more through power inverter and motor.But, because of the structure of system or the difference of controlled condition, and possibly on steam turbo generator, produce the axle twisting vibration, make generator shaft damaged.

About the axle twisting vibration between turbo generator; In DC power-supply system, study mostly; For example in TOHKEMY 2000-224896 communique, disclose when near the DC converting institute of turbo generator and DC power-supply system, being connected; Because of DC converting in the difference of condition of the electric power control carried out, and DC power-supply system is interfered with turbo generator, thus a vibrative situation of turbo generator.In addition; Disclose following technology: the axle twisting vibration is relevant with the state of the epitrochanterian torque that acts on generator; According to the DC converting of DC power-supply system the frequency variation of busbar voltage detect oscillation phenomenon, and pilot angle is changed suppress a twisting vibration.

In addition; Beyond DC power-supply system; A kind of control technology of following such power inverter is for example also disclosed in japanese kokai publication hei 11-27993 communique: in the power inverter and power-supply system of TRT as power supply that will be made up of the combination of engine and generator etc.; Through detecting the resonance frequency composition of TRT; And utilize resonance frequency to remove the vibration component of circuit for eliminating TRT, the situation that vibration is continued to increase thereby inhibition is interfered with the resonance frequency of the mechanical system of TRT.

[technical literature formerly]

[patent documentation]

[patent documentation 1] TOHKEMY 2000-224896 communique

[patent documentation 2] japanese kokai publication hei 11-27993 communique

In foregoing invention; There is following problem: promptly on generator shaft, produce the axle twisting vibration; This vibration becomes generator terminal variation in voltage and transmits with inverter to Motor Drive; Make the motor terminal voltage change and make the motor reel vibration; This vibration further makes the generator shaft vibration, produces covibration like this, and such covibration must be utilized control that makes said pilot angle variation or the control of eliminating the vibration component of said TRT; Suppress said vibration, the reliability of the inhibition effect of situation low-resonance phenomenon such as the control device generation misoperation that on the precision of the system that carries out said control, in said system, relates to, fault comparatively is short of.Problem of the present invention is to provide a kind of special control that does not rely on based on said system etc., just can suppress the electric motor drive system and the method for said vibration.

Summary of the invention

In order to solve above-mentioned problem; In the present invention; A kind of electric motor drive system is provided; The generator that it possesses prime mover, generate electricity through the driving of said prime mover, the driven device that will become the transducer of the electric power of desired frequency by the power conversions that said generator sends, carry out drive electric motor, drive through said motor through the electric power of supplying with from said transducer; Said electric motor drive system is characterised in that, is different value with actuating force with said motor to a resonance frequency of the motor reel of said driven device transmission to the axle resonance frequency of the generator shaft of said generator transmission with the actuating force of said prime mover.

[invention effect]

According to the present invention, play not relying on special control, just can suppress the such effect of covibration of the axle twisting vibration under consistent with the resonance frequency of motor reel or the approximate situation of generator shaft.

Description of drawings

Fig. 1 is the figure of structure of motor drive or the system of execution mode 1 of the present invention.

Fig. 2 is two quality (マ ス モ デ Le) model framework chart of the vibrational system of expression turbo generator.

Fig. 3 is the illustraton of model of calculating of electric system damping coefficient De.

Fig. 4 is the figure of resonance than the relation of h and electric system damping coefficient.

Fig. 5 is the figure of varistructured motor of a resonance frequency or generator.

Fig. 6 has improved the axle varistructured motor of resonance frequency of versatility or the figure of generator.

Fig. 7 is the figure of structure of motor drive or the system of execution mode 2 of the present invention.

Fig. 8 is the motor drive of execution mode 3 of the present invention or the figure of system configuration.

Fig. 9 can change the motor of axle or the figure of generator.

Figure 10 is the figure of varistructured motor of axial length or generator.

Figure 11 has installed the motor of rotary body or the figure of generator on driving shaft.

[symbol description]

1 gas turbine (ガ ス タ one PVC Application)

2 generators

3,18 generator shafts

4,5 transformers

6 systems

7 electric power converters

8 motor

9,58 driven devices

10,20,51,53,56 motor reels

11 electric power converter controllers

12 electric power converter output current detectors

13 electric power converter output voltage detectors

14 fuel control units

15 converters

16 inverters

17 smmothing capacitors

19,21,52,54,60 inertia rotary bodies

The portion of calculating of 30 electric system damping coefficients

The portion of calculating of 40 generator terminal voltages

The portion of calculating of 41 load effective power (active power)

The portion of calculating of 42 generator loading torques

50 motor frameworks

55,57 shaft couplings

59 horizontal rail

100,101 diverter switches

102 current controllers

103 signal generating sources

104 current deviation arithmetic units

105 control model diverter switches

106 Motor Control are used constant

Constant is used in the control of 107 generators

Embodiment

Below, utilize accompanying drawing, execution mode of the present invention is described.

(execution mode 1)

Fig. 1 is overall structure figure of the present invention.Gas turbine 1 and the generator 2 that the mechanical energy of said gas turbine 1 is converted into electric energy combine through generator shaft 3.Inertia rotary body 19 is to be rotated through becoming one with said generator 2, is used to change the inertia rotary body 19 of the axle torsional resonance frequency of generator shaft 3, and it combines with generator 2 through the generator shaft 18 higher than generator shaft 3 rigidity.The revolving force and the rotating speed of 14 pairs of said gas turbines 1 of fuel control unit are controlled; Transformer 4 is changed the output voltage of said generator 2 to system voltage; Transformer 5 converts system voltage the input voltage of electric power converter into, and transformer 4 is connected via system 6 with transformer 5.Electric power converter 7 will be desired electric power from the power conversions of said transformer 5 outputs, and it comprises: the converter 15 that is made up of the diode electrically bridge rectification circuit that three-phase is received electricity exchange to carry out rectification; Make the smmothing capacitor 17 of said converter output smoothingization; And the inverter 16 that said smmothing capacitor voltage transitions is become three-phase alternating current.Motor 8 is by the driven by power of said electric power converter output, and driven device 9 is driven by said motor 8.In addition, motor 8 combines through motor reel 10 with driven device 9.Inertia rotary body 21 is rotated through becoming one with said motor 8, changes the axle torsional resonance frequency of motor reel 10, and combines with motor 8 through the motor reel 20 higher than motor reel 10 rigidity.And electric power converter controller 11 is operated said electric power converter 7 so that the output torque of said motor 8 or speed satisfy the mode of desired characteristic.The electric power converter output current detector (below; Be designated as current detector 12) output current of said electric power converter 7 is detected; Electric power converter output voltage detector (below, be designated as voltage detector 13) detects the output voltage of said electric power converter 7.The output signal of said current detector 12, voltage detector 13 is to electric power converter controller 11 inputs, and electric power converter controller 11 carries out various calculation process, and the signal of the said electric power converter 7 of output function.

At this, to describing with the relevant relational expression of mains side vibration.Fig. 2 is the figure that shows the axle twisting vibration between steam turbine and generator with two quality systems, τ _GBe steam turbine torque, τ _LBe generator loading torque, τ _sBe axle torsional torque, ω ₁Be steam turbine speed, ω ₂Be alternator speed, K is spring constant (a ば ね fixed number), D _mBe the damping coefficient of mechanical system, D _eBe the damping coefficient of electric system, unit all is the normalized quantity p.u. of rated point.In addition, T _A1Be the moment of inertia (inertia モ one メ Application ト) of steam turbine, T _A2Be the moment of inertia of generator, unit all is second.In Fig. 2, D _eShow the torque degree that electric property ground produces through the load (comprising control device) that is connected with generator of the speed increase that reduces generator.According to the equation of state of the secondary vibration system that obtains from figure, the characteristic equation of system becomes (1) formula.

[formula 1]

${\mathrm{<figure-callout\; id="3"\; label="s"\; filenames="HDA00001667198500011.png,HDA00001667198500051.png"\; state="\{\{state\}\}">s</figure-callout>}}^3+(\frac{D_m(T_{a1}+T_{a2})}{T_{a1}\&CenterDot;T_{a2}}+\frac{D_e}{T_{a2}}){\mathrm{<figure-callout\; id="2"\; label="s"\; filenames="HDA00001667198500031.png,HDA00001667198500051.png"\; state="\{\{state\}\}">s</figure-callout>}}^2+(\frac{K(T_{a1}+T_{a2})}{T_{a1}\&CenterDot;T_{a2}}+\frac{D_m\&CenterDot;D_e}{T_{a1}\&CenterDot;T_{a2}})s+\frac{K\&CenterDot;D_e}{T_{a1}\&CenterDot;T_{a2}}=0\&CenterDot;\&CenterDot;\&CenterDot;\left(1\right)$

At this, when the 4th of (1) formula being set to zero, when being approximately the quadratic expression shown in (2) formula, the relation of (3), (4) formula is set up.

[formula 2]

${\mathrm{<figure-callout\; id="2"\; label="s"\; filenames="HDA00001667198500031.png,HDA00001667198500051.png"\; state="\{\{state\}\}">s</figure-callout>}}^2+2\mathrm{\&zeta;}{\mathrm{\&omega;}}_{n}s+{\mathrm{\&omega;}}_{\mathrm{<figure-callout\; id="2"\; label="n"\; filenames="HDA00001667198500031.png,HDA00001667198500051.png"\; state="\{\{state\}\}">n</figure-callout>}}^2=0\&CenterDot;\&CenterDot;\&CenterDot;\left(2\right)$

[formula 3]

$2\mathrm{\&zeta;}{\mathrm{\&omega;}}_n=(D_m+\frac{{\mathrm{<figure-callout\; id="1"\; label="D\; e"\; filenames="HDA00001667198500021.png,HDA00001667198500022.png"\; state="\{\{state\}\}">D</figure-callout>}}_e}{1+n})\&CenterDot;\frac{{(1+n)}^2}{n\&CenterDot;T_a}\&CenterDot;\&CenterDot;\&CenterDot;\left(3\right)$

[formula 4]

${\mathrm{\&omega;}}_{\mathrm{<figure-callout\; id="2"\; label="n"\; filenames="HDA00001667198500031.png,HDA00001667198500051.png"\; state="\{\{state\}\}">n</figure-callout>}}^2=(K+\frac{D_m\&CenterDot;D_e}{T_a})\&CenterDot;\frac{{(1+n)}^2}{n\&CenterDot;T_a}\&CenterDot;\&CenterDot;\&CenterDot;\left(4\right)$

Wherein, in (3), (4) formula, establish n and serve as reasons the moment of inertia ratio of (5) formula definition, T _aBe the accelerating time till the normal speed that satisfies (6) formula.

[formula 5]

$n=\frac{T_{a2}}{T_{a1}}\&CenterDot;\&CenterDot;\&CenterDot;\left(5\right)$

[formula 6]

T _a＝T _a1+T _a2 …(6)

Can know the damping coefficient ζ of electrical secondary system and the intrinsic vibration angular frequency of electrical secondary system by (3), (4) formula _nRepresent by (7), (8) formula respectively, because of electric system damping coefficient D _eAnd make vibration characteristics (ζ, the ω of system _n) change.

[formula 7]

${\mathrm{\&omega;}}_n=(1+n)\sqrt{\frac{K+\frac{D_m\&CenterDot;D_e}{T_a}}{n\&CenterDot;T_a}}\&CenterDot;\&CenterDot;\&CenterDot;\left(7\right)$

[formula 8]

$\mathrm{\&zeta;}=\frac{D_m(1+n)+D_e}{2\sqrt{n(T_a\&CenterDot;K+D_m\&CenterDot;D_e)}}\&CenterDot;\&CenterDot;\&CenterDot;\left(8\right)$

Then, utilize Fig. 3, the portion of calculating 30 of electric system damping coefficient is described.In Fig. 3, by dotted line piece corresponding with the portion of calculating 30 of the electric system damping coefficient of Fig. 2.In Fig. 3 and following explanation, the effective power of establishing generator output and generator loading is P, and alternator speed is ω ₂, generator terminal voltage is V, the generator loading torque is τ _L, the value of their rated points is respectively P ₀, ω ₂₀, V ₀, τ _L0, be respectively Δ P, Δ ω from the variable quantity of rated point ₂, Δ V, Δ τ _LOn the other hand, if supposition is that magnetic field is constant near rated point, then generator terminal voltage V and alternator speed ω ₂Be directly proportional, its conversion gain is V ₀/ ω ₂₀Its portion of calculating 40 with generator terminal voltage is corresponding, can be explained by (9) formula.

[formula 9]

$V=({\mathrm{\&omega;}}_{20}+\mathrm{\&Delta;}{\mathrm{\&omega;}}_2)\&CenterDot;\frac{V_0}{{\mathrm{\&omega;}}_{20}}=V_0+\frac{\mathrm{\&Delta;}{\mathrm{\&omega;}}_2{V}_0}{{\mathrm{\&omega;}}_{20}}\&CenterDot;\&CenterDot;\&CenterDot;\left(9\right)$

Because (9) formula the right and V ₀+ Δ V is corresponding, and therefore (10) formula is set up.

[formula 10]

$\mathrm{\&Delta;V}=\frac{\mathrm{\&Delta;}{\mathrm{\&omega;}}_2{V}_0}{{\mathrm{\&omega;}}_{20}}\&CenterDot;\&CenterDot;\&CenterDot;\left(10\right)$

The portion of calculating 41 of load effective power in addition, is according to load characteristic output and the corresponding load effective power of generator terminal voltage V P.On the other hand, generator loading torque tau _LP is ω at alternator speed with generator output ₂The time have the relation of (11) formula, corresponding with the portion of calculating 42 of generator loading torque.

[formula 11]

${\mathrm{\&tau;}}_L=\frac{P}{{\mathrm{\&omega;}}_2}=\frac{P_0+\mathrm{\&Delta;P}}{{\mathrm{\&omega;}}_{20}+\mathrm{\&Delta;}{\mathrm{\&omega;}}_2}\&CenterDot;\&CenterDot;\&CenterDot;\left(11\right)$

Because (11) formula the right and τ _L0+ Δ τ _LCorrespondence, therefore (12) formula is set up.

[formula 12]

$\mathrm{\&Delta;}{\mathrm{\&tau;}}_L\&cong;\frac{\mathrm{\&Delta;P}-{\mathrm{\&tau;}}_{L0}\&CenterDot;\mathrm{\&Delta;}{\mathrm{\&omega;}}_2}{{\mathrm{\&omega;}}_{20}}\&CenterDot;\&CenterDot;\&CenterDot;\left(12\right)$

Therefore, the damping coefficient D of electric system _eThrough the distortion of (12) formula, can express by (13) formula.

[formula 13]

$D_e=\frac{\mathrm{\&Delta;}{\mathrm{\&tau;}}_L}{\mathrm{\&Delta;}{\mathrm{\&omega;}}_2}\&cong;\frac{\mathrm{\&Delta;P}}{\mathrm{\&Delta;}{\mathrm{\&omega;}}_2\&CenterDot;{\mathrm{\&omega;}}_{20}}-\frac{{\mathrm{\&tau;}}_{20}}{{\mathrm{\&omega;}}_{20}}\&CenterDot;\&CenterDot;\&CenterDot;\left(13\right)$

At this, as an example, in the portion of calculating 41 of load effective power, assumed load is the situation of the ohmic load of resistance value R [p.u.].

At this moment, P=V ²/ R, P ₀=V ₀ ²The relation of/R is set up.Therefore, as cancellation R from this two formula, and when P found the solution, can access (14) formula.

[formula 14]

$P={(V_0+\mathrm{\&Delta;V})}^2\&CenterDot;\frac{P_0}{V_0^2}\&cong;P_0+2\frac{P_0\mathrm{\&Delta;V}}{V_0}\&CenterDot;\&CenterDot;\&CenterDot;\left(14\right)$

Because (14) formula the right and P ₀+ Δ P is corresponding, and therefore (15) formula is set up.

[formula 15]

$\mathrm{\&Delta;P}=2\frac{P_0\mathrm{\&Delta;V}}{V_0}\&CenterDot;\&CenterDot;\&CenterDot;\left(15\right)$

And,, then obtain (16) formula if with (10) formula, (15) formula substitution (13) formula.

[formula 16]

$D_e=2\&CenterDot;\frac{P_0}{{{\mathrm{\&omega;}}_{20}}^2}-\frac{{\mathrm{\&tau;}}_{20}}{{\mathrm{\&omega;}}_{20}}\&CenterDot;\&CenterDot;\&CenterDot;\left(16\right)$

In normalizated unit, rated value is 1.Therefore, when with P ₀=ω ₂₀=τ _L0During=1 substitution (16) formula the right, D _e=1.That is, when ohmic load is connected with generator, the damping coefficient D of electric system _eBecome 1.Relative therewith, for example when considering constant power load (Δ P=0) with example that generator is connected, with Δ P=0 substitution (13) formula, thus D _e=-1.In this case, become negative damping, thereby on the direction of encouraging alternator speed change (vibration), produce generator torque.Especially at the damping coefficient D of mechanical system _mUnder the little situation, the damping coefficient ζ of said electrical secondary system becomes below 0, and expression becomes diverging system.

More than; It is the situation that ohmic load or constant power load is connected in generator; But in the system of reality, as shown in Figure 1, come the corresponding damping coefficient De that determines electric system by the characteristic of transformer, electric power converter, motor, mechanical axis, driven device etc.The damping coefficient De of electric system especially by the generating pusher side the axle resonance frequency fn [Hz] with motor side the axle resonance frequency fr [Hz] relation significantly about; Wherein, The axle resonance frequency fn [Hz] of generating pusher side is by the moment of inertia of gas turbine 1 and generator 2 and the spring constant decision of generator shaft 3, and the axle resonance frequency fr [Hz] of motor side reaches the moment of inertia of the driven device that drives through motor 8 and the spring constant decision of motor reel 10 by motor 8.For example, Fig. 4 is the damping coefficient D with the electric system relevant with system shown in Figure 1 _eBe the longitudinal axis, be transverse axis with resonance than h, and elect fn the curve chart of parameter as by the fn of (17) formula definition and fr.

[formula 17]

$h=\frac{f_r}{f_n}\&CenterDot;\&CenterDot;\&CenterDot;\left(17\right)$

Curve chart by Fig. 4 can know, near h=1, be the fn=fr place, and D _eObtain minimum.In addition, can know, then can be in practicality guarantee the D more than the ohmic load in the fn of fully wide scope (2.5Hz to 20Hz) if resonance is chosen as the scope of h≤0.9 or h>=1.1 than h _eTherefore; Below; Under the situation of

, propose to change to the concrete method of h≤0.9 or h>=1.1.Constitute resonance than the fr of h under the situation of approximate Double inertia, can represent by (18) formula.In (18) formula, JM is the moment of inertia of motor 8, and JL is the moment of inertia of driven device 9, and KF is the spring constant of motor reel 10.Therefore; Through increasing the JM of equivalence in (18) formula; Can reduce fr; And can avoid

in order to realize this purpose; In this execution mode, make motor 8 be two axle construction shown in Figure 5, and form the structure that the inertia rotary body can be installed on by the axle of driven object opposition side.The varistructured example of axle resonance frequency to being made up of motor framework 50 shown in Figure 5, motor reel 51, inertia rotary body 52, the motor reel 53 of axle resonance frequency change usefulness describes.At this moment, consider axle resonance frequency fn=10 [Hz], axle resonance frequency fr=10 [Hz] (JM=105 [kgm of motor side with respect to the generating pusher side ²], JL=640 [kgm ²], KF=356110 [Nm/rad]) situation.In this case, can know, through being 30 [kgm moment of inertia by (18) formula ²] inertia rotary body 52 be installed on motor reel 53, can change to fr=9 [Hz].

[formula 18]

$f_r=\frac{1}{2\mathrm{\&pi;}}\sqrt{K_F(\frac{1}{J_M}+\frac{1}{J_L})}\&CenterDot;\&CenterDot;\&CenterDot;\left(18\right)$

More than, be operation, but, also can change to h>=1.1 through making the generator shaft side have the structure same with Fig. 5 to the motor reel that is used to be altered to h≤0.9.For example, fn can be represented by (19) formula under the situation of approximate Double inertia.In (19) formula, T _A1Be the moment of inertia of steam turbine 1, T _A2Be the moment of inertia of generator 2, K is the spring constant of generator shaft 3.Therefore, through increasing the T of the equivalence in (19) formula _A2, can reduce fn, and to h>=1.1 changes.

[formula 19]

$f_n=\frac{1}{2\mathrm{\&pi;}}\sqrt{K(\frac{1}{T_{a1}}+\frac{1}{T_{a2}})}\&CenterDot;\&CenterDot;\&CenterDot;\left(19\right)$

In addition, when making up system shown in Figure 1, fn and fr may not be known in the design phase, also exist in the situation that the erecting bed is found fn=fr for the first time.In this case, the moment of inertia of inertia rotary body 18,21 can not determine in advance.In addition, shown in enforcement mode 2, exist and hope accurately to set the situation of said resonance than h.At this, as shown in Figure 6, through forming the structure that multi-disc inertia rotary body 52,54 etc. can be installed, also can accurately set resonance at the scene and comparing h.

(execution mode 2)

In execution mode 1, connect each one on generator and motor respectively.But as shown in Figure 7 in this execution mode corresponding with more massive generating field, generator 2 is the i platform, and motor 8 is the j platform, and they are connected with shared system.But in Fig. 7, the explanation of symbol is identical with the situation of Fig. 1.In this case, when the axle resonance frequency of generator i is fn (i), the axle resonance frequency of motor j is when being fr (j); Through make by h (i, j)=fr (j)/resonance of fn (i) definition than h (i, h (i is all satisfied in whole combinations j); Or h (i j)≤0.9; J)>=1.1, thus no matter under what kind of operating condition, the portion of calculating 30 of electric system damping coefficient is D _eAll be more than 1, thereby guarantee the stability of system.As an example, considering has 3 in generator, 3 systems that are connected with shared system of motor.Particularly; Resonance frequency at each generator shaft is fn (1)=10 [Hz], fn (2)=8 [Hz], fn (3)=11 [Hz], and the resonance frequency of each motor reel is under the situation of fr (1)=10 [Hz], fr (2)=8 [Hz], fr (3)=9 [Hz], becomes fn (1)=fr (1)=10 [Hz]; Fn (2)=fr (2)=8 [Hz]; H (1,1)=h (2,2)=1.Under these circumstances, utilize the method shown in the execution mode 1, fr (1) is changed to 9 [Hz] from 10 [Hz], fr (2) is changed to 7.2 [Hz] from 8 [Hz], thereby can guarantee the stability of entire system.

(execution mode 3)

State execution mode on the implementation at 1,2 o'clock, and need correctly infer the resonance frequency fn of generator shaft and motor reel, the mechanism of fr.Therefore, in this execution mode, motor 8 and generator 2 are provided the torque applying mechanism that shakes that adds of broadbands such as M series of signals or white noise.In Fig. 8; Possess will add the torque of shaking to apply the switch that object switches to generator or motor be diverter switch 100 or 101; Diverter switch 100 or 101 is for when selecting A side contact; The generating pusher side is applied and adds the torque of shaking, when selecting B side contact, motor side is applied the structure that adds the torque of shaking.In addition, diverter switch 100 and 101 also can be the structure that physically links.On the other hand, electric power converter controller 11 is made up of following device: the current controller 102 that comprises PWM output; Current deviation arithmetic unit 104; The signal generating source 103 of M series of signals or white noise etc.; Generator control is with constant 107; Motor Control is with constant 106; And the control model diverter switch 105 of electric generator/electric motor.In addition, generator control with constant 107 and Motor Control with constant 106 comprise generator or motor intrinsic winding inductance, winding resistance, induced voltage constant, electric rated value etc.If use this structure, then infer under the situation of axle resonance frequency of generator in hope, said diverter switch 100,101 is swung to A contact side, if select generators control to use constant, then generator shaft is added and shake afterwards through control model diverter switch 105.Under this state, if read the speed detector that is installed in separately on the generator shaft or the signal of acceleration transducer, carry out fft analysis, then can learn the resonance frequency fn of generator shaft.If change diverter switch 100,101 and control model diverter switch 105, then can learn the resonance frequency fr of motor reel too.

(execution mode 4)

In execution mode 1, on the axle that the inertia rotary body is installed in motor 8 or generator 2, thereby can make a variation of resonant frequency.In this execution mode, through structure shown in Figure 9, can change the motor reel 56 that connects motor and driven device, thereby the spring constant of axle self is changed, and make a variation of resonant frequency.Particularly; As shown in Figure 9; The varistructured electric tools power backup of axle resonance frequency motivation framework 50, motor reel 51, driven device 58, connect motor and driven device motor reel 56, be connected motor reel 51 with the shaft coupling (カ Star プ リ Application グ) 55 of motor reel 56, when being connected the shaft coupling 57 of motor reel 56 and driven device 58; As motor reel 56; Axle through tensile modulus of elasticity, the shaft diameter of preparing many raw materials in advance are different is changed, thereby makes a variation of resonant frequency.Be adjusted into through this operation, the axle resonance frequency of motor reel side becomes different values with the axle resonance frequency of generator shaft side.

In above concrete example, show the example of the driving shaft that can change motor side, but equally also can constitute the system of the driving shaft that can change the generating pusher side.

(execution mode 5)

In execution mode 4,, make a variation of resonant frequency through the diameter of axle that changes the motor reel 56 that connects motor and driven device, the tensile modulus of elasticity (ヤ Application グ leads) of raw material.Relative therewith, in this execution mode 5, through structure shown in Figure 10, the axial length of the motor reel 56 that connects motor and driven device is changed, thereby the spring constant of driving shaft is changed, and then make a variation of resonant frequency.Particularly; Shown in figure 10; In the bottom surface of motor framework 50 horizontal rail 59 is set, and prepares the driving shaft of different other of a plurality of axial lengths of using as motor reel 56 in advance, utilize said horizontal rail 59 to adjust; Be replaced by said other driving shaft, thereby make a variation of resonant frequency.Through motor framework 50 being moved forward and backward with respect to driven device 58 in orbit and fixing, thereby can tackle and axial length changes the variation of driven device together 58 and the distance of motor framework 50.In above concrete example, show the example of the driving shaft that can change motor side, but same, also can generator be placed on the horizontal rail, and formation can be changed the system of the driving shaft of generating pusher side.

(execution mode 6)

In execution mode 1, making motor 8 is two axle construction, and on by the axle of the opposition side of driven object, the inertia rotary body is installed, and makes a variation of resonant frequency thus.Relative therewith, in this execution mode 6,, on the axle of driven object side, the inertia rotary body is installed, thereby the moment of inertia of motor is changed, and then make a variation of resonant frequency through structure shown in Figure 11.Particularly, in Figure 11,, prepare the different member of a plurality of moments of inertia in advance and change, thereby make a variation of resonant frequency as the inertia rotary body 60 that is installed on the motor reel 56.

Claims (12)

1. electric motor drive system; It is by constituting like lower member: promptly prime mover, the generator that generates electricity through the driving of said prime mover, will become the transducer of the electric power of desired frequency, the driven device that utilizes the electric power supplied with from said transducer to carry out drive electric motor, utilize said motor to drive by the power conversions that said generator sends; Said electric motor drive system is characterised in that

The axle resonance frequency of the generator shaft that the actuating force of said prime mover is transmitted to said generator is different values with actuating force with said motor to the axle resonance frequency of the motor reel of said driven device transmission.

2. electric motor drive system according to claim 1 is characterized in that,

The axle resonance frequency of said motor reel is got 0.9 below or the value more than 1.1 divided by the value that obtains of axle resonance frequency of said generator shaft.

3. electric motor drive system according to claim 1 is characterized in that,

Regulate the length of said motor reel, change the axle resonance frequency of said motor reel.

4. electric motor drive system according to claim 1 is characterized in that,

Adjust the length of said generator shaft, change the axle resonance frequency of said generator shaft.

5. electric motor drive system according to claim 1 is characterized in that,

One or more inertia rotary bodies are installed on said motor reel, are changed the axle resonance frequency of said motor reel.

6. electric motor drive system according to claim 1 is characterized in that,

One or more inertia rotary bodies are installed on said generator shaft, are changed the axle resonance frequency of said generator shaft.

7. electric motor drive system according to claim 1 is characterized in that,

Through material or the shaft diameter that changes said motor reel, change the axle resonance frequency of said motor reel.

8. electric motor drive system according to claim 1 is characterized in that,

Through material or the shaft diameter that changes said generator shaft, change the axle resonance frequency of said generator shaft.

9. electric motor drive system according to claim 1 is characterized in that,

The electric power converter controller that possesses the axle resonance frequency of inferring said generator shaft or motor reel.

10. electric motor drive system according to claim 9 is characterized in that,

Said electric power converter controller applies comprise M series of signals or white noise wide band to said generator shaft or motor reel and adds the torque of shaking, and infers the axle resonance frequency of said generator shaft or motor reel.

11. electric motor drive system according to claim 9 is characterized in that,

Said electric power converter controller possesses: the current controller that said inverter is carried out current-order; Generation is used to carry out the signal generating source of the current signal of said current-order; And the deviation arithmetic unit of the deviation of the output current of the said inverter of computing and said current signal.

12. an electric motor drive method, it comprises:

The actuating force of prime mover is made the operation of said generator for electricity generation to the generator transmission via generator shaft;

To become the operation of the electric power of desired frequency by the power conversions that said generator sends through transducer;

The operation of coming drive motor through the electric power of supplying with from said transducer;

The actuating force of said motor is driven the operation of said driven device to the driven device transmission via the motor reel of the axle resonance frequency with value different with the axle resonance frequency of said generator shaft.

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