Abstract
Provided is a dynamometer system dynamo control device that can accurately reproduce a no-load state. The dynamo control device includes controllers that are designed, using a H-infinity control or a μ-design method, such that, for a generalized plant that outputs observation output and a controlled variable from external input and from control input, the response from the input until the variable is shortened. The generalized plant includes a dynamic characteristics model wherein the characteristics of a dynamometer system are identified such that the angular acceleration is output from the external input and the control input. The controlled variable is the difference between the angular acceleration calculated for an engine alone on the basis of the external input and the angular acceleration calculated by the dynamic characteristics model.
Claims
1. A dynamo control device for a dynamometer system, the dynamometer system including a dynamometer connected to a test piece generating torque in response to a command from an external control device through an intermediate connection body, a torque detector detecting torsional torque of the intermediate connection body, a rotation speed detector detecting a rotation speed of the dynamometer, and an inverter supplying electric power to the dynamometer, the dynamo control device for the dynamometer system generating a torque current command to the inverter based on detection signals of the torque detector and the rotation speed detector so as to realize a no-load state where a load is not applied to the test piece, wherein the dynamo control device includes a controller designed by applying a control system design method called an H∞ control or a μ synthesis to a generalized plant, wherein the generalized plant outputs a first observation output corresponding to the detection signal of the torque detector, a second observation output corresponding to the detection signal of the rotation speed detector and a prescribed controlled variable from an external input corresponding to torque generated in the test piece and a control input corresponding to the torque current command, wherein the generalized plant includes a dynamic characteristic model identifying a characteristic of the dynamometer system so that angular acceleration of the test piece is output from the external input and the control input based on the equation of motion of a three-inertia system, wherein the three-inertia system is configured by connecting the test piece, the intermediate connection body and the dynamometer each having an original inertia moment, wherein the controlled variable of the generalized plant is a signal obtained by multiplying a weighting function having an integration characteristic by a difference between angular acceleration of the test piece in the state of being disconnected from the intermediate connection body and the dynamometer calculated by multiplying an inverse number of the inertia moment of the test piece by the external input and angular acceleration of the test piece calculated by the dynamic characteristic model, and wherein the controller is designed by numerical calculation based on the control system design method so that responsiveness from the external input to the controlled variable in the generalized plant decreases.
2. The dynamo control device for the dynamometer system according to claim 1, wherein the dynamic characteristic model of the generalized plant includes an inverter model identifying a characteristic of the inverter, a mechanical model identifying a characteristic of the three-inertia system, a torque detection model identifying a characteristic of the torque detector, and a rotation speed detection model identifying a characteristic of the rotation speed detector.
3. The dynamo control device for the dynamometer system according to claim 2, wherein an output obtained by multiplying the control input by a prescribed proportional gain is set as an input of the inverter model, wherein an output of an integrator provided in an output terminal of the torque detection model is set as a first observation output, and wherein an output of a proportional gain provided in an output terminal of the rotation speed detection model is set as a second observation output.
4. The dynamo control device for the dynamometer system according to claim 2, wherein the control input is set as an input of the inverter model, wherein an output obtained by multiplying a prescribed proportional gain by a difference between an output of the rotation speed detection model multiplied by a prescribed proportional gain and an output of an integrator provided in an output terminal of the torque detection model is set as a first observation output, and wherein an output of the torque detection model is set as a second observation output.
5. The dynamo control device for the dynamometer system according to claim 2, wherein an output obtained by combining the control input with an output obtained by multiplying a prescribed proportional gain by a difference between an output of the rotation speed detection model multiplied by a prescribed proportional gain and an output of an integrator provided in an output terminal of the torque detection model is set as an input of the inverter model, and wherein an output of the torque detection model is set as an observation output.
6. The dynamo control device for the dynamometer system according to claim 2, wherein the control input is set as an input of the inverter model, and wherein an output obtained by multiplying a prescribed proportional gain by a difference between an output of the rotation speed detection model multiplied by a prescribed proportional gain and an output of an integrator provided in an output terminal of the torque detection model is set as an observation output.
7. The dynamo control device for the dynamometer system according to claim 2, wherein the control input is set as an input of the inverter model, wherein an output obtained by multiplying a prescribed proportional gain by a difference between an output of the rotation speed detection model multiplied by a prescribed proportional gain and an output of an integrator provided in an output terminal of the torque detection model is set as a first observation output, and wherein an output of a high-pass filter provided in the output terminal of the torque detection model is set as a second observation output.
8. The dynamo control device for the dynamometer system according to claim 2, wherein an output obtained by multiplying a prescribed proportional gain by the control input is set as an input of the inverter model, wherein an output of the torque detection model is set as a first observation output, and wherein a difference between an output of the rotation speed detection model multiplied by a prescribed proportional gain and an output of the torque detection model is set as a second observation output.
Description
BRIEF DESCRIPTION OF THE DRAWINGS
(1) FIG. 1 is a diagram illustrating the configuration of a dynamometer system that uses a dynamo control device according to an embodiment of the present invention.
(2) FIG. 2 is a diagram illustrating a control system design method based on an H ∞ control and a μ synthesis using a generalized plant.
(3) FIG. 3 is a diagram illustrating the detailed configuration of a generalized plant of Example 1.
(4) FIG. 4 is a diagram illustrating a three-inertia system model corresponding to a mechanical system of a dynamometer system.
(5) FIG. 5 is a diagram illustrating the detailed configuration of a dynamo control device of Example 1.
(6) FIG. 6 is a bode diagram of a controller of Example 1.
(7) FIG. 7 is a diagram illustrating the change in engine speed when an engine is started in the dynamometer system using the dynamo control device of Example 1.
(8) FIG. 8 is a diagram illustrating the detailed configuration of a generalized plant of Example 2.
(9) FIG. 9 is a diagram illustrating the detailed configuration of a dynamo control device of Example 2.
(10) FIG. 10 is a bode diagram of controllers Gc1 and Gc2 of Example 2.
(11) FIG. 11 is a diagram illustrating the detailed configuration of a generalized plant of Example 3.
(12) FIG. 12 is a diagram illustrating the detailed configuration of a dynamo control device of Example 3.
(13) FIG. 13 is a bode diagram of controllers Gc1 and Gc2 of Example 3.
(14) FIG. 14 is a diagram illustrating the detailed configuration of a generalized plant of Example 4.
(15) FIG. 15 is a diagram illustrating the detailed configuration of a dynamo control device of Example 4.
(16) FIG. 16 is a bode diagram of a controller Gc1 of Example 4.
(17) FIG. 17 is a diagram illustrating the detailed configuration of a generalized plant of Example 5.
(18) FIG. 18 is a diagram illustrating the detailed configuration of a dynamo control device of Example 5.
(19) FIG. 19 is a bode diagram of a controller Gc2 of Example 5.
(20) FIG. 20 is a diagram illustrating the detailed configuration of a generalized plant of Example 6.
(21) FIG. 21 is a diagram illustrating the detailed configuration of a dynamo control device of Example 6.
(22) FIG. 22 is a bode diagram of controllers Gc1 and Gc2 of Example 6.
(23) FIG. 23 is a diagram illustrating the detailed configuration of a generalized plant of Example 7.
(24) FIG. 24 is a diagram illustrating the detailed configuration of a dynamo control device of Example 7.
(25) FIG. 25 is a bode diagram of controllers Gc1 and Gc2 of Example 7.
(26) FIG. 26 is a diagram illustrating the configuration of a conventional dynamometer system.
(27) FIG. 27 is a diagram illustrating the change in rotation speed when an engine is started in a no-load state of the conventional dynamometer system.
PREFERRED MODE FOR CARRYING OUT THE INVENTION
(28) Hereinafter, an embodiment of the present invention will be explained in detail while referencing the drawings. FIG. 1 is a diagram illustrating the configuration of a dynamometer system 1 that uses a dynamo control device 6 according to the present embodiment. The dynamometer system 1 includes an engine E which serves as a test piece, a dynamometer D which is connected to the engine E through a substantially bar-shaped shaft S, an engine control device 5 which controls the engine E through a throttle actuator 2, an inverter 3 which supplies electric power to the dynamometer D, a dynamo control device 6 which controls the dynamometer D through the inverter 3, a shaft torque sensor 61 which detects the torsional torque of the shaft S, and an encoder 62 which detects the rotation speed of an output shaft SD of the dynamometer D.
(29) The shaft torque sensor 61 detects torsional torque acting on a portion which is close to the dynamometer D in relation to the engine E in the shaft S extending from the engine E to the dynamometer D from, for example, a strain amount in the twisting direction of the shaft S and transmits a signal substantially proportional to the detection value to the dynamo control device 6.
(30) The engine control device 5 starts the engine E at a prescribed timing and controls the output of the engine E in a prescribed manner.
(31) The dynamo control device 6 generates a torque current command corresponding to a torque value to be generated in the dynamometer D based on the detection signals of the shaft torque sensor 61 and the encoder 62 so that the power generated by the engine E is absorbed in a prescribed manner and inputs the torque current command to the inverter 3. The dynamo control device 6 is configured by mounting a controller K on a computer, in which the controller K is designed by applying a robust control system design method called an H ∞ control or a μ synthesis to control target defined by a generalized plant P that outputs a prescribed controlled variable z and a prescribed observation output y from a prescribed external input w and a prescribed control input u illustrated in FIG. 2 so that responsiveness from the external input w to the controlled variable z decreases.
(32) The generalized plant P is used in the robust control system design method and includes a weighting function for identifying a control specification and a dynamic characteristic model of a control target. Since a detailed procedure of numerically deriving the controller K attaining a desired control from the generalized plant P according to the H ∞ control or the μ synthesis is described in detail in, for example, “Linear Robust Control”, written by Kang-Zhi LIU, published by CORONA PUBLISHING CO., LTD., 2002 or “Control System Design Based on MATLAB”, edited by Kenzo NONAMI, written by Hidekazu NISHIMURA and Mitsuo HIRATA, published by Tokyo Denki University Press, 1998, the detailed description thereof will be omitted herein. Hereinafter, the detailed configuration of the generalized plant P and the dynamo control device 6 derived therefrom will be described in Examples 1 to 7.
EXAMPLE 1
(33) FIG. 3 is a diagram illustrating the detailed configuration of the generalized plant Pa of Example 1. In a generalized plant Pa of Example 1, the input signal w indicates an external input and corresponds to engine torque generated in the engine. The input signal u indicates a control input output from a controller (not illustrated) and corresponds to a torque current command input to the inverter. The output signal z indicates a controlled variable and corresponds to a difference value which needs to be decreased according to an H ∞ control or a μ synthesis. The detailed content of the difference value will be described later. Two output signals y1 and y2 respectively indicate first and second observation outputs input to a controller (not illustrated) and correspond to the detection value of the shaft torque sensor and the detection value of the encoder.
(34) The generalized plant Pa includes a dynamic characteristic model 7 which identifies the characteristics of the dynamometer system 1 illustrated in FIG. 1 so that the angular acceleration of the engine is output from the external input w and the control input u and a controlled variable calculation unit 8 which calculates the controlled variable z based on the external input w and the output of the dynamic characteristic model 7.
(35) The dynamic characteristic model 7 includes mechanical models P4 to P9 identifying the characteristics of a three-inertia system obtained by connecting the engine, the shaft, and the dynamometer, a shaft torque detection model P10 identifying the shaft torque detection characteristics by the shaft torque sensor, a rotation speed detection model P11 identifying the rotation speed detection characteristics of the dynamometer by the encoder, and an inverter model P12 identifying the torque current control characteristics by the inverter.
(36) The configuration of the mechanical system of the dynamometer system 1 can be approximated as a three-inertia system model obtained by connecting three rigid bodies each having an original inertia moment illustrated in FIG. 4 through two spring components. In FIGS. 3 and 4, “J1” corresponds to the inertia moment [kgm.sup.2] of the engine, “J2” corresponds to the inertia moment [kgm.sup.2] of the shaft, and “J3” corresponds to the inertia moment [kgm.sup.2] of the dynamometer. “K1” corresponds to the spring stiffness [Nm/rad] between the engine and the shaft and “K2” corresponds to the spring stiffness [Nm/rad] between the shaft and the dynamometer.
(37) When the configuration of the mechanical system of the dynamometer system 1 is approximated as the three-inertia system model illustrated in FIG. 4, the motion equation is expressed by combining the transfer functions “1/J1”, “1/s”, “K1/s”, “1/J2.Math.s”, “K2/s”, and “1/J3.Math.s” with the mechanical models P4 to P9 of FIG. 3. Furthermore, for example, specific values obtained in advance by an actual machine are used as the detailed values of these three inertia moments J1 to J3 and the spring constants K1 and K2.
(38) The transfer function Gy1(s) of the shaft torque detection model P10, the transfer function Gy2(s) of the rotation speed detection model P11, and the transfer function Gu1(s) of the inverter model P12 are determined in advance for each system.
(39) The controlled variable calculation unit 8 calculates a difference value obtained by subtracting the angular acceleration (the output of the block P4) of the engine calculated by the dynamic characteristic model 7 from the angular acceleration (the output of the block P1) of the engine unit obtained by multiplying the inverse number of the inertia moment J1 of the engine unit by the external input w corresponding to the engine torque and calculates the controlled variable z by multiplying a prescribed weighting function G(s) by the difference value. In the weighting function G(s), for example, a function having an integration characteristic is used. As described above, in the invention, a difference value between the angular acceleration of the engine unit and the angular acceleration of the engine calculated by the dynamic characteristic model is set as the controlled variable z and the controller is designed according to an H ∞ control or a μ synthesis so that the responsiveness from the external input w to the controlled variable z decreases. Thus, it is possible to derive a controller having both the shaft inertia compensation effect of compensating the shaft inertia of the dynamometer and the resonance suppression effect of suppressing the mechanical resonance.
(40) FIG. 5 is a diagram illustrating the detailed configuration of a dynamo control device 6a of Example 1. Two controllers Gc1 and Gc2 derived from the generalized plant Pa are used in the dynamo control device 6a. The controller Gc1 is derived so as to correspond to the first observation output y1, and the controller Gc2 is derived so as to correspond to the second observation output y2.
(41) FIG. 6 is a bode diagram of the controllers Gc1 and Gc2 of Example 1. In FIG. 6, the upper diagram indicates the gain characteristics and the lower diagram indicates the phase characteristics. As illustrated in FIG. 6, the integration characteristics are recognized in the low range of the controller Gc1 and the proportional characteristics are recognized in the low range of the controller Gc2. The integration characteristics and the proportional characteristics are used as control elements used to compensate the shaft inertia of the dynamometer. Meanwhile, a gain decreases at a prescribed mechanical resonance point in the high ranges of the controllers Gc1 and Gc2. From the description above, according to the controllers Gc1 and Gc2 and the dynamo control device 6a using the controllers, it is possible to apparently obtain both the shaft inertia compensation effect of compensating the shaft inertia in a no-load state in the engine and the resonance suppression effect of suppressing the mechanical resonance point.
(42) Furthermore, the responsiveness of the shaft inertia compensation control can be evaluated based on the integration characteristics and the proportional characteristics of the controllers Gc1 and Gc2 at a certain frequency. For example, the controllers Gc1 and Gc2 of FIG. 6 have about 10 Hz of responsiveness.
(43) FIG. 7 is a diagram illustrating the change in engine speed when the engine is started in the dynamometer system using the dynamo control device of FIG. 6. In FIG. 7, a measurement result of the system that uses the dynamo control device of FIG. 6 is indicated by a thin solid line. Further, a bold dotted line indicates a result measured when the engine and the shaft are separated so that the engine actually gets into a no-load state, that is, an ideal value in the shaft inertia compensation. As illustrated in FIG. 7, the thin solid line and the bold dotted line substantially match each other. According to the system using the dynamo control device 6a of this example, since the shaft inertia of the dynamometer is compensated when the engine is started, a starting waveform corresponding to the engine unit is certainly obtained. That is, it is verified that the no-load state of the engine can be realized by using the dynamo control device of this example.
EXAMPLE 2
(44) FIG. 8 is a diagram illustrating the detailed configuration of a generalized plant Pb of Example 2. In the description below, only the difference from the generalized plant Pa of Example 1 of FIG. 3 will be described. The same reference numerals will be given to the same components as those of the generalized plant Pa of Example 1, and the detailed description thereof will be omitted.
(45) As described above by referring to FIG. 6, the controller derived to obtain the shaft inertia compensation effect has the integration characteristics and the proportional characteristics as a result. In Example 2, the generalized plant Pb having the control element is used in order to separate the control element essential for obtaining the shaft inertia compensation effect from the controller.
(46) The generalized plant Pb of this example additionally includes an integrator P13 and two gain blocks P14 and P15 from the generalized plant Pa of Example 1. More specifically, in Example 2, the output of the integrator P13 provided in the output terminal of the torque detection model P10 is set as the first observation output y1, and the output of the gain block P14 of the inertia moment J2 of the shaft provided in the output terminal of the rotation speed detection model P11 is set as the second observation output y2. Further, in Example 2, an output obtained by multiplying a prescribed proportional gain K as the reference of the control responsiveness by the control input u is set as an input of the inverter model P12.
(47) FIG. 9 is a diagram illustrating the detailed configuration of a dynamo control device 6b of Example 2. Two controllers Gc1(s) and Gc2(s) derived from the generalized plant Pb are used in the dynamo control device 6b. The controller Gc1 is obtained so as to correspond to the first observation output y1, and the controller Gc2 is obtained so as to correspond to the second observation output y2. Here, since the integrator and the proportional gain are included in the generalized plant Pb in advance as described above, the characteristics of the integrator and the proportional gain are separated from the derived controllers Gc1 and Gc2. For this reason, the dynamo control device 6b additionally includes an integrator and two proportional gains K and J2 essential for the shaft inertia compensation control as illustrated in FIG. 9 other than the two controllers Gc1 and Gc2 derived from the generalized plant Pb.
(48) FIG. 10 is a bode diagram of the controllers Gc1 and Gc2 of Example 2. In FIG. 10, the upper diagram indicates the gain characteristics and the lower diagram indicates the phase characteristics. According to this example, since the integrator or the proportional gain is included in the generalized plant Pb, the controllers Gc1 and Gc2 having the same gain proportional characteristics in the low range are derived. In this way, since both controllers Gc1 and Gc2 have the same gain in the low range, there is an advantage that the responsiveness is easily evaluated compared with the case where the generalized plant Pa of Example 1 is used.
(49) Furthermore, it is effective to feed back the high-range shaft torque signal in order to obtain the resonance suppression effect. However, as illustrated in FIG. 9, the shaft torque signal is attenuated in the high range by the integrator and is set as an input of the controller Gc1. On the contrary, according to the controller Gc1 of this example, the high-range gain increases so as to compensate the attenuation in the high range due to the integrator. Thus, the resonance suppression effect is not impaired compared with Example 1.
(50) Further, for example, when the generalized plant Pa of Example 1 is used, the characteristic of the inertia compensation amount is included in the controller Gc2 of FIG. 5. For this reason, when the controller is derived and the inertia compensation amount is changed, the controller needs to be derived again by an H ∞ control or a μ synthesis. On the contrary, when the generalized plant Pb of this example is used, the characteristic of the inertia compensation amount is separated from the controller Gc2 as the gain block J2 of the shaft inertia moment as illustrated in FIG. 9. Thus, according to this example, the inertia compensation amount can be easily changed by the adjustment of the gain J2 without using an H ∞ control or a μ synthesis again even after the controller is derived by the H ∞ control or the μ synthesis. Further, a gain block K as a loop gain is also separated from the controllers Gc1 and Gc2. For this reason, the loop gain can be easily changed within a certain range without performing the H ∞ control or the μ synthesis again similarly to the inertia compensation amount. Furthermore, although not illustrated and described in detail, the same effect as FIG. 7 can be obtained even in the dynamometer system using the dynamo control device 6b of Example 2.
EXAMPLE 3
(51) FIG. 11 is a diagram illustrating the detailed configuration of a generalized plant Pc of Example 3. In the description below, only the difference from the generalized plant Pa of Example 1 of FIG. 3 will be described. The same reference numerals will be given to the same components as those of the generalized plant Pa of Example 1, and the detailed description thereof will be omitted.
(52) Similarly to Example 2, in this example, the generalized plant Pc including the control element, such as the integrator or the proportional gain essential for obtaining the shaft inertia compensation effect, is used in order to separate the control element from the controller.
(53) In the generalized plant Pc of this example, the integrator 13, two gain blocks P14 and P15, and an adder P16 are added from the generalized plant Pa of Example 1. More specifically, in Example 3, an output obtained by multiplying a prescribed proportional gain K as the reference of the control responsiveness by an output obtained by subtracting the output of the integrator P13 provided in the output terminal of the torque detection model P10 from the output of the gain block P14 of the shaft inertia moment J2 provided in the output terminal of the rotation speed detection model P11 is set as the first observation output y1. Further, the output of the torque detection model P10 is set as the second observation output y2.
(54) FIG. 12 is a diagram illustrating the detailed configuration of a dynamo control device 6c of Example 3. Two controllers Gc1(s) and Gc2(s) derived from the generalized plant Pc are used in the dynamo control device 6c. The controller Gc1 is obtained so as to correspond to the first observation output y1, and the controller Gc2 is obtained so as to correspond to the second observation output y2. Here, due to the same reason as Example 2, the dynamo control device 6c additionally includes an integrator and two proportional gains K and J2 essential for the shaft inertia compensation control as illustrated in FIG. 12 other than the two controllers Gc1 and Gc2 derived from the generalized plant Pc.
(55) FIG. 13 is a bode diagram of the controllers Gc1 and Gc2 of this example. In FIG. 13, the upper diagram indicates the gain characteristics and the lower diagram indicates the phase characteristics. According to this example, since the integrator or the proportional gain is included in the generalized plant Pc, the substantially same effect as Example 2 is obtained. Furthermore, according to this example, the controller effective for the shaft inertia compensation control only corresponds to the controller Gc1. As described above in Example 2, since a signal attenuated in the high range by the integrator is set as an input of the controller Gel, the high-range gain of the controller Gc1 increases. However, in this example, since the shaft torque detection signal of the controller Gc2 is fed back as illustrated in FIG. 13, the high-range gain of the controller Gc1 is small compared with Example 2. Furthermore, although not illustrated and described in detail, even in the dynamometer system using the dynamo control device 6b of Example 3, the same effect as FIG. 7 can be obtained.
EXAMPLE 4
(56) FIG. 14 is a diagram illustrating the detailed configuration of a generalized plant Pd of Example 4. In the description below, only the difference from the generalized plant Pa of Example 1 of FIG. 3 will be described. The same reference numerals will be given to the same components as those of the generalized plant Pa of Example 1, and the detailed description thereof will be omitted.
(57) Similarly to Example 2, in this example, the generalized plant Pd including the control element, such as the integrator or the proportional gain essential for obtaining the shaft inertia compensation effect, is used in order to separate the control element from the controller. Further, in Example 1, two observation outputs y1 and y2 are defined, but in this example only the observation output y1 is used.
(58) In the generalized plant Pd of this example, the integrator P13, two gain blocks P14 and P15, and two adders P16 and P17 are added from the generalized plant Pa of Example 1. More specifically, in Example 4, the output of the torque detection model P10 is set as the observation output y1. Further, an output obtained by combining the control input u with the output obtained by multiplying a prescribed proportional gain K as the reference of the control responsiveness by a difference value obtained by subtracting the output of the integrator P13 provided in the output terminal of the torque detection model P10 from the output of the rotation speed detection model P11 multiplied by the inertia moment J2 of the shaft is set as an input of the inverter model P12.
(59) FIG. 15 is a diagram illustrating the detailed configuration of the dynamo control device 6d of Example 4. The controller Gc1(s) derived from the generalized plant Pd so as to correspond to the observation output y1 is used in the dynamo control device 6d. Here, due to the same reason as Example 2, the dynamo control device 6d additionally includes an integrator and two proportional gains K and J2 essential for the shaft inertia compensation control as illustrated in FIG. 15 other than the controller Gc1 derived from the generalized plant Pd.
(60) FIG. 16 is a bode diagram of the controller Gc1 of this example. In FIG. 16, the upper diagram indicates the gain characteristics and the lower diagram indicates the phase characteristics. According to this example, since the integrator or the proportional gain is included in the generalized plant Pd, the substantially same effect as Example is obtained. Furthermore, in this example, since only the observation output y1 of the generalized plant Pd is used, only one high-order controller Gc1 is used. For this reason, according to this example, a bumpless process is easily performed when the shaft inertia compensation control is switched to a different control. Furthermore, although not illustrated and described in detail, even in the dynamometer system using the dynamo control device 6d of Example 4, the same effect as FIG. 7 can be obtained.
EXAMPLE 5
(61) FIG. 17 is a diagram illustrating the detailed configuration of a generalized plant Pe of Example 5. In the description below, only the difference from the generalized plant Pc of Example 3 of FIG. 11 will be described. The same reference numerals will be given to the same components as those of the generalized plant Pc of Example 3, and the detailed description thereof will be omitted.
(62) In the generalized plant Pc of Example 3, the output of the torque detection model P10 is set as the observation output y2. However, in the generalized plant Pe of this example, the output is deleted and only one observation output is used. That is, in the generalized plant Pe of this example, an output obtained by multiplying a prescribed proportional gain K as the reference of the control responsiveness by an output obtained by subtracting the output of the integrator P13 provided in the output terminal of the torque detection model P10 from the output of the gain block P14 of the inertia moment J2 of the shaft provided in the output terminal of the rotation speed detection model P11 is set as the observation output y1.
(63) FIG. 18 is a diagram illustrating the detailed configuration of a dynamo control device 6e of Example 5. The controller Gc1(s) derived from the generalized plant Pe so as to correspond to the observation output y1 is used in the dynamo control device 6e. Here, due to the same reason as Example 2, the dynamo control device 6e additionally includes an integrator and two proportional gains K and J2 essential for the shaft inertia compensation control as illustrated in
(64) FIG. 18 other than the controller Gc1 derived from the generalized plant Pe.
(65) FIG. 19 is a bode diagram of the controller Gc1 of Example 5. In FIG. 19, the upper diagram indicates the gain characteristics and the lower diagram indicates the phase characteristics. According to this example, since the integrator or the proportional gain is included in the generalized plant Pd, the substantially same effect as Example 2 is obtained. Particularly, when the gain block K as the loop gain is separated from the controller Gc1 (see FIG. 18), the loop gain can be easily changed within a certain range without performing the H ∞ control or the μ synthesis again. Furthermore, in this example, since only one observation output y1 of the generalized plant Pe is used, only one high-order controller Gc1 is derived. For this reason, according to this example, a bumpless process is easily performed when the shaft inertia compensation control is switched to a different control. Furthermore, although not illustrated and described in detail, even in the dynamometer system using the dynamo control device 6e of Example 5, the same effect as FIG. 7 can be obtained.
EXAMPLE 6
(66) FIG. 20 is a diagram illustrating the detailed configuration of a generalized plant Pf of Example 6. In the description below, only the difference from the generalized plant Pc of Example 3 of FIG. 11 will be described. The same reference numerals will be given to the same components as those of the generalized plant Pc of Example 3, and the detailed description thereof will be omitted.
(67) In the generalized plant Pf of this example, a high-pass filter P17 is added from the generalized plant Pc of Example 3. More specifically, in Example 6, the output of the high-pass filter P17 provided in the output terminal of the torque detection model P10 is set as the second observation output y2. The first observation output y1 is similar to that of Example 3.
(68) FIG. 21 is a diagram illustrating the detailed configuration of a dynamo control device 6f of Example 6. Two controllers Gc1(s) and Gc2(s) derived from the generalized plant Pf are used in the dynamo control device 6f. The controller Gc1 is derived so as to correspond to the first observation output y1, and the controller Gc2 is derived so as to correspond to the second observation output y2. Here, due to the same reason as Example 3, the dynamo control device 6f additionally includes an integrator, two proportional gains K and J2, and a high-pass filter essential for the shaft inertia compensation control as illustrated in FIG. 21 other than two controllers Gc1 and Gc2 derived from the generalized plant Pf.
(69) FIG. 22 is a bode diagram of the controllers Gc1 and Gc2 of this example. In FIG. 22, the upper diagram indicates the gain characteristics and the lower diagram indicates the phase characteristics. According to this example, since the integrator or the proportional gain is included in the generalized plant Pf, the substantially same effect as Example is obtained. Furthermore, in this example, a high-pass filter is added compared with Example 3. Comparing with the result of Example 3 illustrated in FIG. 13, the low-range characteristics of the controller Gc2 become the proportional characteristics in Example 3. However, in this example, the low-range characteristics of the controller Gc2 become the integration characteristics due to the effect of the high-pass filter. Furthermore, although not illustrated and described in detail, even in the dynamometer system using the dynamo control device 6f of Example 3, the same effect as FIG. 7 can be obtained.
EXAMPLE 7
(70) FIG. 23 is a diagram illustrating the detailed configuration of a generalized plant Pg of Example 7. In the description below, only the difference from the generalized plant Pc of Example 3 of FIG. 11 will be described. The same reference numerals will be given to the same components as those of the generalized plant Pc of Example 3, and the detailed description thereof will be omitted.
(71) The generalized plant Pc (see FIG. 11) of Example 3 and the generalized plant Pg (see FIG. 23) of this example have a different installation position of the gain block P14 multiplied by the proportional gain K. In this example, an output obtained by multiplying the control input u by a prescribed proportional gain K as the reference of the control responsiveness is set as an input of the inverter model P12.
(72) FIG. 24 is a diagram illustrating the detailed configuration of a dynamo control device 6g of Example 7. Two controllers Gc1(s) and Gc2(s) derived from the generalized plant Pg are used in the dynamo control device 6g. The controller Gc1 is obtained so as to correspond to the first observation output y1, and the controller Gc2 is obtained so as to correspond to the second observation output y2. Here, due to the same reason as Example 2, the dynamo control device 6c additionally includes an integrator and two proportional gains K and J2 essential for the shaft inertia compensation control as illustrated in FIG. 25 other than two controllers Gc1 and Gc2 derived from the generalized plant Pg.
(73) FIG. 25 is a bode diagram of the controllers Gc1 and Gc2 of Example 7. In FIG. 25, the upper diagram indicates the gain characteristics and the lower diagram indicates the phase characteristics. According to this example, since the integrator or the proportional gain is included in the generalized plant Pg, the substantially same effect as Example 2 is obtained. Particularly, since the gain block K as the loop gain is separated from the controllers Gc1 and Gc2 (see FIG. 24), the loop gain can be easily changed within a certain range without performing the H ∞ control or the μ synthesis again.
EXPLANATION OF REFERENCE NUMERALS
(74) 1 dynamometer system E engine (test piece) S shaft (intermediate connection body) D dynamometer Pa, Pb, Pc, Pd, Pe, Pf, Pg generalized plant 3 inverter 6a, 6b, 6c, 6d, 6e, 6f, 6g dynamo control device 61 shaft torque sensor (torque detector) 62 encoder (rotation speed detector) 7 dynamic characteristic model 8 controlled variable calculation unit P4 to P9 mechanical model P10 torque detection model P11 rotation speed detection model P12 inverter model
