FI79265B - FOERFARANDE FOER REGLERING AV DRAG- ELLER BROMSKRAFTEN HOS DRIVMOTORERNA I EN VRIDAXELLOES ELEKTRISK DRAGVAGN VID HJULENS FAESTFRIKTIONSGRAENS. - Google Patents

Abstract

1. Method for the regulation of the driving or braking force of the traction motors (2) of dead-axle-free electrical traction vehicle at the static friction limit of the wheels with the use of an equipment (13), which integrates the acceleration or deceleration to be expected and the output magnitude of which by difference from the actual rotational axle speed is evaluated as measure of the wheel slip for reduction of the driving or braking moment, as pseudo-dead-axle, wherein the output signal of the integrating equipment is in the slip-free operation made to follow the actual rotational axle speed by way of a regulating circuit (14 to 18) acting on a further input of the integrating equipment (13), characterised by the following features : - the first time derivative of the rotational speed difference between pseudo-dead-axle and actual axle see diagramm : EP0159284,P6,F1 is formed in a differentiator (22) and a limit value stage (28) is driven thereby, the output of which imposes an additional input magnitude on the integrator (13) of the pseudo-dead-axle, - the additional input magnitude due to an inverter (34) has a sign opposite to the acceleration or deceleration control magnitude conducted to the integrator (13) and according to magnitude influences the direction of integration or halting of the integrator (13), - after a delay time formed by a timing member (30), an inverter (24) is connected between the differentiator (22) and the input of the limit value stage (28), - the limit value stage (28) has a relapse delay due to a feedback path (29), and - the delay time of the switching-in of the inverter (24) and the relapse delay of the limit value stage (28) are matched to the dynamic behaviour of the drive in such a manner that a gap between the appearance of the positive and the negative output signal of the differentiator (22) is filled on the modulation of the limit value stage (28).

Description

1 79265

The invention relates to a method for adjusting the traction and braking force of the traction motors of a non-rotating electric traction car at the wheel friction limit according to the preamble of claim 1.

Such a method for simulating an electronic axis of rotation is known, for example, from DE-OS 3 011 541. The speed of the apparent axis of rotation is then the output variable of the integrator, the input of which has the following quantities: the quantity corresponding to the expected acceleration based on the accelerating forces of the vehicle and its mass and the output signal of the comparator. The latter in each case forms the difference between the speed of the apparent axis of rotation and that selected from all the speeds of the axle, i.e. the lowest value is selected when driving and the highest value when braking. The output signal of the comparator affects the integrator only if the speed of the apparent rotation axis exceeds the selection speed with the present drive command or falls below the brake command and then steers the integrator back until the apparent speed corresponds to the selection speed. Differences in axle speeds with the speeds of the 25 apparent axles of rotation generate signals for wheel slip on the rail and utilize traction to limit braking force.

On the other hand, it is known that traction motors with a steep Md (n) web curve can achieve a very good utilization of the holding value if the torque parameter is not controlled by the torque according to the speed, but the characteristic curve parameter is made dependent on the actual vehicle speed. An example of this is American diesel electric locomotives, cf. see also ASME Publication 80-WA-35 / RT-3, pp. 1-9, published by Rail Transportation Division of the 2 79265

American Society of Mechanical Engineers from 1980.

In order to achieve a similar effect with AC traction motors, patent application P 3 244 288 is proposed.

However, the latter methods start from the premise that the actual vehicle speeds on the ground can be achieved metrologically, for which a genuine axis of rotation is required, or if it does not exist, a radar probe. In principle, locomotives no longer have rotary axles. Radar probes can be prevented by snow and ice formation so that they do not produce any real signal for a short time. An additional difficulty is that very high accuracy measurements are required. The stabilization of the radar probe and the corrections of the wheel diameter divisions must be so tuned that the mutual deviations remain small in relation to the optimal wheel slip of a few percent. In addition, due to the wear consumption of the wheel tires, automatic leveling devices are necessary.

The device according to said patent application DE-OS 3 011 541 for using an apparent rotary axis instead of a real speed measurement does not, of course, lead to success. On the one hand, significant errors in the integrator over time cannot be avoided and, on the other hand, a slightly higher acceleration than the actual acceleration of the vehicle must always be set so as not to impede driving. Therefore, it is necessary to correct the output signal of the integrator again whenever a non-slip run exists. This is done with comparator connections that reset the integrator. However, they require that, after each slip, a correspondingly strong limitation of the engine torque as quickly as possible 35 reaches a re-rotation situation, or at least a situation in which very small micro-slips occur. If the torque is limited only in relation to the slip, i.e. here the speed difference is the speed of the apparent axis of rotation / the speed of the drive shaft, then the integrator 5 will control the apparent axis of rotation at its predetermined acceleration to further higher speeds, even if the vehicle slows down more and more. The sliding of the wheel should slowly but inevitably get out of control.

A method for controlling such an integrator coupling is already known, which avoids this disadvantage by providing a further reverse input signal to the integrator under the control of a decreasing torque in the event of wheel slip (DE-PS 2 917 673). However, this method has the disadvantage that when processing the stator frequency of a traction motor directly in the integrator, it is not possible to use a method for smoothing a very steep natural characteristic of an AC asynchronous motor according to patent application P 3 244 288.

It is an object of the invention to provide a method which allows a more precise control of the integrator for an apparent axis of rotation and which allows the proposed method to smooth the effective Md (n) characteristic of an AC motor for use with a controlled wheel slip at a friction value limit even in vehicles hitherto for direct measurement of speed on a chassis.

This object is solved according to the invention according to the features of claim 1. The invention can be used in connection with all vehicle engines whose engines are driven with torque or current control. The prerequisite in this case is that the motor control is so reaction-rapid that the deceleration times occurring in the torque fluctuations remain sufficiently short compared to the time course during the acceleration-35 phases. Preferred embodiments of the invention 4 79265 can be taken from the subclaims.

The invention will now be described in more detail by means of a schematic embodiment.

The figures show: Fig. 1 is a block diagram for drive shaft control in connection with an inverter-supplied AC traction motor; Fig. 2 shows the passage of torque over the wheel slip; Figures 3 and 3a are block diagram additions to improve torque limitation.

10 In Fig. 1, 1 is denoted by an inverter which supplies an AC drive motor 2. The shaft speed is measured by a tachogenerator 3 (or an inverter with its evaluation devices). In input control 4, a setting value-15 derived from the torque setpoint for the motor slip cycle number fguoχx is applied to one of the inputs 4. 5 shows, instead of the actual vehicle speed measured on the chassis, the speed of the apparent axis of rotation, which is compared at the reduction point 6 with the measured speed of the axle speed of the forging generator 3. The speed difference 20 observed at the subtraction point 6 is divided in the divider device 7 by a suitable constant given in 8 or by a factor depending on the speed and / or traction. Multiplication by its reciprocal value is also possible. The value obtained is subtracted from the holding value of the motor slip cycle number fsso11 at subtraction point 9. In the adder 25 10, the sum of the cycle number fpunane and the desired motor slip is formed as the inverter cycle number to the stator cycle number of the drive motor 2.

The value of the expected acceleration or deceleration, derived from the traction or braking force and the vehicle mass, is derived at 11. For this purpose, locomotives must take into account the load to be towed, which can be done by automatic conversion. This value is integrated in the integrator 13 as the speed value of the apparent axis of rotation. The integrator 13 is dimensioned so that it integrates the small difference much faster than the corresponding acceleration of the vehicle, so that the rotational speed of the apparent axis of rotation would slowly advance above the actual speed of the vehicle. The integrator 13 therefore receives additional feedback via the comparator 14, the switching points 15 and 16 and the single-path rectifiers 17, 18 or other devices which only transmit signals of only one polarity in each case and the summing point 12. The comparator 14 compares the output of the integrator, i.e. the speed of the apparent axis of rotation, with the speed of the actual shaft. The positive difference (i.e. the apparent axis of rotation rotates faster) is provided via 17 to the integrator 13 only in the "driving" operating situation (15 closed) and thus steers the apparent axis of rotation downwards until it corresponds to the speed of the actual axis. The negative difference (i.e., the apparent rotation axis rotates more slowly) is given through 17 to the integrator 13 only in the "braking" operating condition (16 closed) and steers the apparent axis of rotation upwards until a coincidence with the actual axis speed exists. as the actual axle rotates, accelerates or decelerates more than in the vehicle.The speed values correspond to each other, i.e. there are no speed differences in 6.

In the event of a wheel slip, the "driving" axle accelerates more strongly than the vehicle. The integrator 13 can now no longer be included via feedback, because in 17 the signal of this polarity is not passed through. In 6, a speed difference arises, such as between the drive shaft and the actual shaft of rotation. During braking, the polarity of the difference changes, which is why the feedback signal is passed through 16, 18.

The speed difference signal in 30 6 then controls the drive motor torque, as described in reference numerals 1-10.

At this stage, however, the speed of the apparent axis of rotation has reached a value which no longer corresponds to the speed of the speed on the base, but to the speed of a shaft already rotating on a rail 6 79265, which is necessary to transmit the maximum possible traction. This is because during the occurrence of this slip, starting from the pure rotation of the drive shaft, this accelerates hardly measurably no-5 faster than the vehicle and the integrator can still follow the speed of the shaft. The stronger acceleration of the drive shaft only starts when this has exceeded the maximum friction value slip.

Without further measures, the apparent rotary axis integrator 13 would now continue to rotate freely, whereby the apparent axis of rotation would gradually become faster and faster relative to the vehicle. The drive shaft should thus likewise have an ever-increasing slip and eventually even be slid.

To prevent this, but without filling the drive shaft, the device according to the invention can be used with reference numerals 19-34 with steep traction losses.

Here, 19, 20, 21 form a hub change device, 20 which in braking operation changes the polarity of the speed difference signal. 22 is a differentiation device which forms the first temporal derivation of the speed difference signal. 23: 1-la is a first order deceleration member, which slightly smooths the rise of the output signal from 22. Switch points 25 25, 26 and inverter 24 form a pole reversing device for this signal. 28 is a threshold phase, the input of which further has a differentiating feedback 29 via the summing location 27. 30 denotes a time deceleration member through which switches 25 and 26 of the hub-30 actuator are controlled from the output of the limit value stage 28. The switch 31 is likewise controlled from the output of the limit value step 28 and further switches on the acceleration or deceleration hold value (expected acceleration) and 33 of the added constant the signal generated by the inverter 34 through the time element device 35 32 and the summing position 12 to the input of the virtual rotary axis integrator 13.

This device works as follows:

When there is a speed difference in the differential generator 5, the wheels, as described above, have exceeded the slip at the kis-5 sides, which allows the maximum transmission. They fall into an unstable sliding range, i.e. with increasing slip, the holding value becomes lower again. The now-increasing torque surplus accelerates only 10 small rotating masses of the wheel set with the traction motor relative to the mass of the vehicle relatively quickly. The increase in speed difference is detected in the differentiator 22 and causes the limit value stage 28 to operate via the deceleration element 23 (for filtering short-term disturbances), the switch 25 and the summing point 27. Their output-15 signal controls the switch 31, so that the signal formed from one of the expected acceleration values 11 and one of the constants added to it (33) and inverted in the inverter 34 will operate at the input-20 of the integrator 13 and the adder 12. The time element 32 allows part of the signal to pass immediately and the rest to rise to full height with a first order time delay. There is no signal deceleration in the time element 32, as symbolically indicated.

The integrator 13 thus becomes slower and starts, 25 as soon as the additional signal exceeds the direct signal, to integrate in the opposite direction. The speed of the apparent rotary axis becomes smaller again. Thus, the speed difference in 6 first rises even faster, but at the same time, with a larger speed difference signal-30, the torque of the traction motor is also reduced even more strongly. The acceleration of the wheel set continues to cease as a result, the wheel set starts to "slow down" again, i.e. to return to a stable sliding range. Since then the speed of the wheel set again approaches the number of revolutions of the apparent axis of rotation-35, the speed difference signal at 6 also becomes smaller again. The downward control of the integrator via the switch 31 must now be maintained until the wheel set has again reached a stable sliding range, i.e. the holding / sliding curve has exceeded the holding value maximum. In the other 5 cases, the system would remain in an unstable area and eventually slip.

For this purpose, a pole reversing device with switching points 25 and 26 operates and inverts and 24. It reverses the polarity of the limit value phase 28 so that this becomes sensitive to a negative decrease in the [d (An)] / dt, i.e. the speed difference signal. The switching takes place with the output signal of the limit value stage 28 after the deceleration time of the time element 30.

After the start-up of the limit value step 28 with an increasing speed difference, the time element 30 elapses a time interval, which roughly corresponds to what the system apparent rotational shaft torque reduction-rotating mass wheel set / drive motor needs for the reversal of the effect when the wheel slides. Then follows the switching in 25 and 26 and the limit value step 28 now becomes controlled negatively from the 20 signals in the erodifferentizer 22, which is now inverted in 24, still positive. The gap between the disappearing positive signal, 25, and the new signal, 26, is filled by feedback 29, which, after the start of the limit step 28, supplies an additional short-term signal 25 via the summing point 27 to the input of the limit step 28. Its temporal duration is determined to match that of the time element 30.

Thus, the speed of the apparent axis of rotation is controlled backwards by the integrator 13 so much that the set of wheels 30 has again returned to a stable sliding range. From now on, the speed difference value rises again when the speed of the apparent axis of rotation has further decreased, because the torque transmitted to the rail now becomes smaller again and the speed of the wheel set decreases 35 slower than that of the apparent axis of rotation. The negative output value of the differentiator 9 79265 22 disappears again and the limit value step 28 is reversed. The switch 31 opens and the integrator 13 accelerates the apparent axis of rotation again, as before the start of the event.

5 If the grip value on the rails has not improved in the meantime, so that the predetermined traction can be fully transferred again, the event is repeated. The set of wheels then again passes over the maximum holding value to the unstable sliding range and is repeated in the manner described, etc.

In connection with Figure 2, the event is further described. It is shown: on the abscissa, the speed n of the wheel set, where no is the speed corresponding to the instantaneous speed of the vehicle when the wheel set rotates without slip. Δn is the slip of the wheels on 15 rails, calculated for a better understanding of the km / h circumferential speed. The ordinate has a torque acting on the Md wheel set; Md. , torque preset in motor control. H: 11a is denoted by the holding value curve, shown here as the torque transferred from the wheel set to the rails, depending on the slip Λ n. 101-106 are consecutive wheel set torque / speed work points, 101'-106 'corresponding points on the holding line through which the engine characteristic curve Md (n), 101 "-106" is set in each case from the motor control. The horizontal arrows 101-106 25 points respectively corresponding to the characteristic of the motor 101 "-106" indicates how much Δη signal is transferred over moottoriominaiskäyriä 7, 9 and 10 in Figure 1. The length of the arrow is relative, therefore, Δη signal.

Let’s look at the event from point 101 onwards. 30 As the holding torque is slightly higher than the torque transmitted by a slip of less than 2 km / h on the maximum holding value curve, the wheel set starts to rotate in an unstable sliding range. With higher acceleration a small Δη has already been generated, the engine characteristic 101 "has shifted slightly 35 and the torque has decreased from 101 'to 101. accelerates along the curve portion 107, increasing the Δη value and decreasing the torque, as indicated by the changed values in 102. The rising Δη signal causes the limit value step 28 in Fig. 1 to wake up and thus triggers the apparent rotation of the rotary axis integrator 13.

The rotational speed of the apparent axis of rotation becomes back-10 sinusoidal and thus the Δη signal becomes even larger and reduces the torque so much that it now falls below the holding curve H. The excess torque becomes negative and the wheel set begins to decelerate and again reach the maximum holding value. The other passed points 104 and 105 indicate that the An signal then becomes smaller. The wheel set again approaches the apparent axis of rotation and decelerates faster than this as the torque rises again.

In the meantime, the time element 30 (Fig. 1) has run out of 20 and reversed the signal at the input of the limit step 28, so that this is now controlled negatively from the [d (dn)] / dt signal to positive and the speed of the apparent rotation axis decreases further. Only after passing through point 105 in direction 106 does Δη no longer decrease. [d (An)] / dt 25 then becomes zero and finally positive again and the limit value step 28 reverses. The apparent axis of rotation accelerates again, the wheel set rotates as the torque rises again to point 101, and the event begins again. In this way, the wheel set continuously oscillates around the maximum gripping value, therefore until the predetermined torque holding value exceeds it.

This mode of operation is shown in Figure 2 for the case where the torque holding value is relatively close above the holding limit. In order for the event to operate with the same certainty even when a holding value is greatly given for a longer period of time, including a holding value of 11,79265, the method according to the invention can be supplemented according to FIG. Such a device consists of an integrator 37 controlled by a [d (£ n)] / dt value from the differentiator 22 and even 5 through a rectifying stage 35 passing through a positive half-wave. The integrator 37 only returns via feedback from its own output via the summing point 36. It returns to zero like a first order deceleration element when no signal comes from 22. The output of the integrator proportionally reduces the torque holding value from A in the subtractor 38. A further improvement is provided by multiplying its output value by a predetermined holding value by means of a multiplier 39, as shown in Fig. 3a.

With a suitable selection of integration parameters, each event of Figure 2 as curve 107 passes between points 101 and 103 through the positive [d (Än)] / dt output of differentiator 22 slightly increases the output of integrator 37 and thus causes a small decrease in torque holding value. If the events follow each other rapidly, then they are accumulated by the integrator 37 before it is temporarily restored by its feedback, thus gradually forming a greater reduction in the holding value, until the events of Fig. 2 become rarer or cease again. Thus, the torque holding value is automatically kept tightly above the holding limit.

If it is desired to use the method according to the invention for non-AC traction motors, the An output of the totalizer 6 can be connected to the device instead of the input of the divider 7, which affects the corresponding motor characteristic parameter (e.g. motor voltage in DC traction motors). Md = f (n) are steep enough. Otherwise, it is connected to the same device 35 to reduce the torque holding value.

i2 79265 as to integrator 37 in Figure 3 or 3a. However, this requires a sufficiently rapid adjustment of the traction motor, which does not require excessive waiting and manufacturing times for the reduction of the condition compared to the ta-5 event according to FIG.

Claims (2)

13 79265 1. A method for adjusting the traction or braking force of electric traction motors (2) of a non-rotating axle at 5 wheel holding friction limit using an expected acceleration or deceleration integrating device (13) as an apparent rotation limiting axis 10, characterized by the following features: the differentiator (22) generates a first time derivative (d (Än) / dt) of the difference between the rotational speeds of the apparent axis of rotation and the actual axis of rotation and controls the limit stage (28) whose output switches the apparent axis of rotation for the integrator (13) to the additional input variable, the additional input variable has an inverted sign relative to the acceleration or deceleration control variable derived for the integrator (13) by the inverter (34) and affects the integration direction or the hold of the integrator (13) according to the respective variable, after a delay time formed by the time element (30), an inverter (24) is connected between the input of the differentiator (22) and the limit stage (28), the limit stage (28) has a determined regeneration delay via feedback (29), the inverter (24) the recurrence delay of the limit value stage (28) is adapted to the dynamic behavior of the drive in such a way that when controlling the limit value stage 30 (28), the gap between the occurrence of the positive and negative output signal of the differentiator (22) is filled. A method according to claim 1, characterized in that an additional integrator (37) is connected to the output of the differential speed variable (Δη) differentiator (22) via a conductive member (35) with a positive variable 14,79265, the output of which is summed (36) at its input. ) resets the integrator (37) without an input signal to zero like a first-order delay-5 member, and that the output-input variable of the integrator (37) is used to proportionally limit the torque holding value of the traction motor. is 79265 1. A method for adjusting a drive or a bromine kraft with a drive motor (2) and a drive electrically with 5 drives in a high speed friction genome from an anchor and (13) by integrating the accelerators with retardation, the shafts of the shafts from the axles of the sheaves are used for the purpose of gliding on the sheave with 10 drives or torques, the shifts being different from the shifts: (i) these rotations have been used with pseudovridaxeln och den verkliga axeln och 15 and gränsvärdessteg (28), vars utgäng kopplar en tilläggs-ingängsstorhet till pseudovridaxelns Integrator (13), styrs medelst detta tidsderivat, tidelggsing & ngs accelerations- or 20 retardations stored in an inverter (34) for a maximum of three years lt fall, integrringsriktningen ell integratorns (13) hällning, efter en medelst et tidsorgan (30) bildad fördröj-25 unstid kopplas en inverter (24) mellan differentiraren (22) och gränsvärdesstegets (28) ingäng, gränsvärdessteget (28) genpvis external copying (29) best external copying, forwarding hosts inverters (24) increments 30 and higher values (28) external copying (up to the number of different dynamic outputs), 22) positive and negative output signals. 35 2. For the purposes of paragraph 1, the provisions of this Regulation shall apply, mutatis mutandis.