Method and device for controlling a test stand arrangement

Abstract

The invention relates to a device and to a method for controlling a test stand arrangement having a specimen and having a loading machine, which is connected to the specimen by a connecting shaft. An estimated value (T.sub.E,est) for for the internal torque (T.sub.E) of the specimen is determined and, from the estimated value (T.sub.E,est), while taking into account a natural frequency (f.sub.0) and a delay, a damping signal (T.sub.Damp) is determined and fed back into the control loop.

Claims

1. A method for controlling a test stand arrangement including a test specimen and a loading machine which is connected to the test specimen by a connecting shaft the test stand arrangement corresponding to a supercritical arrangement, the method including the following steps: determining an estimated value (T.sub.E,est) for an internal torque (T.sub.E) of the test specimen; determining a damping signal (T.sub.Damp) from the estimated value (T.sub.E,est) while taking into account a natural frequency (f.sub.0) of the test stand arrangement that is to be damped and a delay; and feeding the damping signal back into a control loop for controlling the test stand arrangement.

2. The method according to claim 1, characterized in that the estimated value (T.sub.E,est) is determined from the test specimen angular velocity (ω.sub.E) and the shaft torque (T.sub.ST).

3. The method according to claim 1, characterized in that, when determining the damping signal (T.sub.Damp) from the estimated value (T.sub.E,est), a band range comprising the natural frequency (f.sub.0) to be damped is filtered out and the filtered signal is delayed by the delay and amplified by an amplification (Gain).

4. The method according to claim 1, characterized in that the delay is a constant parameter.

5. A device for controlling a test stand arrangement, the device comprising: a test specimen; a loading machine which is connected to the test specimen by a connecting shaft; the test stand arrangement (4) corresponding to a supercritical arrangement, a damping unit including an estimating unit configured and arranged to establish an estimated value (T.sub.E,est) for the internal torque (T.sub.E) of the test specimen, and a filter configured and arranged to establish a damping signal (T.sub.Damp) from the estimated value (T.sub.E,est) on the basis of a natural frequency (f.sub.0) of the test stand arrangement that is to be damped and a delay and feeding said damping signal back into a control loop of the test stand arrangement.

6. The device of claim 5, characterized in that the estimating unit is further configured and arranged to determine the estimated value (T.sub.E,est) from a test specimen angular velocity (ω.sub.E) and a shaft torque (T.sub.ST).

7. The device of claim 6, wherein the estimating unit is configured and arranged to utilize a Kalman filter.

8. The device of claim 6, wherein the filter includes a delay element configured and arranged to operate as a FIFO memory for the device.

9. The device of claim 5, characterized in that the estimating unit is configured and arranged to utilize a Kalman filter.

10. The device of claim 9, wherein the filter includes a delay element configured and arranged to operate as a FIFO memory for the device.

11. The device of claim 5, characterized in that the filter includes a delay element configured and arranged to operate as a FIFO memory, facilitates parameterization and allows a constant parameter to be used for the delay.

12. A method for controlling a test stand arrangement including a test specimen and a loading machine which is connected to the test specimen by a connecting shaft—the test stand arrangement corresponding to a supercritical arrangement, the method including the following steps: determining an estimated value (T.sub.E,est) for an internal torque (T.sub.E) of the test specimen; determining a damping signal (T.sub.Damp) from the estimated value (T.sub.E,est) while taking into account a natural frequency (f.sub.0) of the test stand arrangement that is to be damped and a delay; and feeding the damping signal back into a control loop for controlling the test stand arrangement; characterized in that, when determining the damping signal (T.sub.Damp) from the estimated value (T.sub.E,est), a band range comprising the natural frequency (f.sub.0) to be damped is filtered out and the filtered signal is delayed by the delay and amplified by an amplification (Gain); characterized in that one or more of the following parameters are determined in advance of a simulation on the test stand arrangement: the delay, the amplification (Gain), and the band range.

13. The method of claim 12, characterized in that the delay (Delay) is a constant parameter.

14. A method for controlling a test stand arrangement including a test specimen and a loading machine which is connected to the test specimen by a connecting shaft—the test stand arrangement corresponding to a supercritical arrangement, the method including the following steps: determining an estimated value (T.sub.E,est) for an internal torque (T.sub.E) of the test specimen; determining a damping signal (T.sub.Damp) from the estimated value (T.sub.E,est) while taking into account a natural frequency (f.sub.0) of the test stand arrangement that is to be damped and a delay; and feeding the damping signal back into a control loop for controlling the test stand arrangement; characterized in that the estimated value (T.sub.E,est) is determined from the test specimen angular velocity (ω.sub.E) and the shaft torque (T.sub.ST); characterized in that, when determining the damping signal (T.sub.Damp) from the estimated value (T.sub.E,est), a band range comprising the natural frequency (f.sub.0) to be damped is filtered out and the filtered signal is delayed by the delay and amplified by an amplification (Gain).

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) The present invention is described in greater detail in the following with reference to FIGS. 1 to 4, which show exemplary, schematic and non-limiting advantageous embodiments of the invention. In the drawings:

(2) FIG. 1 is a schematic view of a test stand arrangement,

(3) FIG. 2 is a schematic view of a mathematical model of a dual-mass oscillator,

(4) FIG. 3 is a block diagram of an exemplary controller structure according to the invention and

(5) FIG. 4 is a block diagram of active damping according to the invention.

DETAILED DESCRIPTION

(6) FIG. 1 is a schematic view of the essential components in a test stand. A test specimen 1, for example an internal combustion engine, is connected, by means of a connecting shaft 3, to a loading machine 2 which applies a load moment to the test specimen in accordance with a test run. In the context of the present description, the unit consisting of the test specimen 1, loading machine 2 and connecting shaft 3 is also referred to as a test stand arrangement 4.

(7) An automation system 5 determines controlled variables and provides these to the test stand arrangement 4, for example a controlled variable for the loading machine torque T.sub.D of the loading machine 2 and a controlled variable for the pedal position α of the test specimen 1. The controlled variables are converted into the corresponding manipulated variables by a control mechanism 6 of the loading machine 2 or a control mechanism 6′ of the test specimen 2.

(8) The actual values of the controlled variables are determined by the automation system 5 via corresponding sensors, for example the actual values shown in FIG. 1 for the test specimen angular velocity ω.sub.E, the loading machine angular velocity ω.sub.D, and the shaft torque T.sub.ST.

(9) The oscillation behavior of the test stand arrangement 4 can be mathematically modelled as a dual-mass oscillator, as shown in FIG. 2. In addition to the values defined above for the shaft torque T.sub.ST, the loading machine torque T.sub.D, the test specimen torque T.sub.E, the loading machine angular velocity ω.sub.D and the test specimen angular velocity ω.sub.E, the model also contains the shaft rigidity c, the shaft damping d, the test specimen moment of inertia θ.sub.E and the loading machine moment of inertia θ.sub.D, by means of which natural frequencies of the system and the damping are mathematically determined.

(10) For a test stand arrangement 4, a single natural frequency f.sub.0 can usually be determined by means of modeling as a dual-mass oscillator. The dimensions of the connecting shaft 3 are usually selected such that this natural frequency is under the ignition frequency of the working range of a test specimen 1. The natural frequency is in this case in the range between the speed of the starter and the idle speed of the test specimen, and is therefore only briefly passed through by the test stand 4 upon starting the test specimen 1. An arrangement of this kind is referred to as a “supercritical arrangement.”

(11) A 4-cylinder engine having a working range of 600 to 6000 rpm can be taken as an example. At 600 rpm this results in an ignition frequency of 20 Hz. For a supercritical arrangement, the shaft connection is therefore dimensioned such that a natural frequency of 15 Hz, for example, is produced for the test stand arrangement.

(12) However, in practical use, in particular in test runs using prototypes that are as of yet untested, disturbances can also be produced below the ignition frequency that can also excite the natural frequency. The natural frequency can, for example, be excited by a 0.5th order (of the rotational frequency) of a disturbance generated by the test specimen.

(13) According to the invention, in order to greatly reduce effects of this kind, this description discloses active damping, which is described in the following with reference to FIG. 3, with one part of the controller structure for the loading machine being shown schematically in FIG. 3.

(14) As an input of a speed controller 7, a control deviation is formed as a difference between a target value of the loading machine angular velocity ω.sub.D,Target and the actual value of the loading machine angular velocity ω.sub.D. The speed controller 7 establishes a controlled variable for the loading machine torque T.sub.D on the basis of the control deviation, which variable is transmitted to the test stand arrangement 4 (or to the control mechanism 6 thereof shown in FIG. 1). In this case the controlled variable is corrected by a damping signal T.sub.Damp that is determined by a damping unit 8 on the basis of the shaft torque T.sub.ST and the test specimen angular velocity ω.sub.E.

(15) For this purpose, the damping unit 8 comprises an estimating unit 9 which determines an estimated value T.sub.E,est for an internal torque T.sub.E of the test specimen 1. The internal torque T.sub.E of the test specimen cannot be directly measured on the test stand and can therefore be considered a non-measurable disturbance variable of the control loop. However, this variable is an essential variable as the control input variable for active damping, since it contains the excitation for the dual-mass oscillator system.

(16) In order to establish the estimated value T.sub.E,est for the internal torque T.sub.E, the estimating unit 9 can comprise a Kalman filter which is optimized for the corresponding frequency range and determines the estimated value T.sub.E,est on the basis of the shaft torque T.sub.ST and the test specimen angular velocity ω.sub.E. The filter unit 10 then converts the estimated value T.sub.E,est obtained by the estimating unit 9 into the damping signal T.sub.Damp.

(17) The filter unit 10 is shown schematically in greater detail in FIG. 4. In the filter unit 10, the signal of the estimated value T.sub.E,est is first freed from the DC component by means of a high-pass filter 11. The low-pass filter 12 arranged downstream is optional and is only required if the higher AC components in the manipulated variable for the loading machine 2 exceed the threshold values for the loading machine 2. The high-pass filter 11 and the low-pass filter 12 can therefore be considered a band-pass filter 13 which filters a band range comprising the natural frequency to be damped out of the signal of the estimated value T.sub.E,est.

(18) In order to compensate for the down times, a delay (Delay) is then applied to the signal in a delay element 14 and the signal is amplified in an amplifier 15 in order to obtain the damping signal T.sub.Damp in an optimum amplitude for damping.

(19) In order to produce the delay (which can also be interpreted as a phase change) in a simple manner, the delay element can be designed as a FIFO memory having a constant (or parameterizable) length. A constant length is admissible because a specific and known frequency (the natural frequency) is intended to be damped. It is also assumed that this is a periodic disturbance, and this also matches test results and is confirmed in the technical literature.

(20) Under these assumptions, the following phase errors can be compensated for using the FIFO memory: systematic errors, since the damping torque is not introduced at the shaft but instead in the air gap of the loading unit (90° phase error) phase errors which occur as a result of non-zero phase response of different filter networks in the control or as a result of down times in the closed-loop control loop.

(21) The optimum degree of damping can be set by a parameterizable amplification in the amplifier 15.

(22) Both the parameterizable value of the amplification and the delay or phase compensation can be determined in advance in a simulation of the test run, and therefore do not have to be determined by trial and error.

LIST OF REFERENCE SIGNS

(23) Test specimen 1 Loading machine 2 Connecting shaft 3 Test stand arrangement 4 Automation system 5 Control mechanism 6, 6′ Speed controller 7 Damping unit 8 Estimating unit 9 Filter 10 High-pass filter 11 Low-pass filter 12 Band-pass filter 13 Delay element 14 Amplifier 15 Pedal position α Loading machine torque T.sub.D Shaft torque T.sub.ST Test specimen moment of inertia θ.sub.E Loading machine angular velocity ω.sub.D Test specimen angular velocity ω.sub.E Shaft rigidity c Shaft damping d Loading machine moment of inertia θ.sub.D Test specimen moment of inertia θ.sub.E