Method for controlling and limiting a speed of a turbocharger

Abstract

A method for controlling a speed of a turbocharger that is in operative connection with a compressor, the steps including: provision of a setpoint for the speed of the turbocharger on the basis of a model-based precontrol for a calculation of a desired boost pressure ahead of the turbocharger; determination of an actual value for the speed of the turbocharger; control of an actuator of the turbocharger in order to compensate for the difference between the desired value and the actual value for the speed of the turbocharger. A main signal and a subsidiary signal are provided during the determination of the actual value for the speed of the turbocharger, wherein the main signal and the subsidiary signal are combined in order to validate the actual value for the speed of the turbocharger.

Claims

1. A method for controlling a speed of a turbocharger that is in operative connection with a compressor, the method comprising: providing a setpoint value for the speed of the turbocharger on the basis of a model-based pre-control for a calculation of a desired boost pressure ahead of the turbocharger; determining an actual value for the speed of the turbocharger; controlling an actuator of the turbocharger to compensate for a difference between the setpoint value and the actual value for the speed of the turbocharger; and providing a main signal and a subsidiary signal during the determination of the actual value for the speed of the turbocharger, wherein the main signal and the subsidiary signal are combined in order to validate the actual value for the speed of the turbocharger, wherein a minimum threshold and a maximum threshold are calculated from the main signal in the determination step, and wherein a leakage factor is produced as a function of the subsidiary signal, the minimum threshold and the maximum threshold.

2. The method according to claim 1, wherein the leakage factor equal to 0 is produced if the subsidiary signal is less than a minimum threshold or wherein the leakage factor equal to 1 is produced if the subsidiary signal is greater than a maximum threshold or wherein the leakage factor is interpolated between 0 and 1 if the subsidiary signal is between the minimum threshold and the maximum threshold.

3. The method according to claim 1, wherein the main signal and the subsidiary signal are combined with the aid of a Kalman filter.

4. The method according to claim 1, wherein a setpoint limiting for the speed of the turbocharger takes place in the provision of the setpoint for the speed of the turbocharger.

5. The method according to claim 1, wherein the actual value for the speed of the turbocharger is captured in the subsidiary signal in the determination step.

6. The method according to claim 1, wherein the actual value for the speed of the turbocharger is provided in the subsidiary signal from a turbine model in the determination step.

7. The method according to claim 1, wherein the actual value for the speed of the turbocharger is provided in the main signal from a compressor model or with the aid of a conversion from a detected actual boost pressure.

8. The method according to claim 1, wherein a same mathematical model and/or same parameters is/are used in operation of the turbocharger for the setpoint for the speed of the turbocharger and for the actual value for the speed of the turbocharger in the main signal.

9. The method according to claim 1, wherein at least one thermodynamic quantity is used as a parameter in operation of the turbocharger, the at least one thermodynamic quantity comprising a temperature ahead of the compressor, a pressure ahead of the compressor, and/or a mass flow of an intake air through the compressor.

10. A turbocharger for operating a compressor having a control unit that is designed to control the operation of the turbocharger in accordance with the method according to claim 1.

11. A computer program product configured to be stored in a storage device of a control unit according to claim 10, wherein the computer program product performs the method when at least partially executed in a computing unit of the control unit.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) The present invention will become more fully understood from the detailed description given hereinbelow and the accompanying drawings which are given by way of illustration only, and thus, are not limitive of the present invention, and wherein:

(2) FIG. 1 shows a schematic flowchart of a possible control method within the meaning of the invention in which the speed of a turbocharger is controlled as the controlled variable,

(3) FIG. 2 shows a schematic flowchart of a compressor model,

(4) FIG. 3 shows a schematic representation of a main signal and of a subsidiary signal within the meaning of the invention,

(5) FIG. 4 shows a schematic flowchart of a control method according to the invention, in which the speed of the turbocharger is controlled as the controlled variable,

(6) FIG. 5 shows a schematic explanation of a combination of an actual value for a speed of a turbocharger within the scope of the invention,

(7) FIG. 6 shows a diagram for a control according to the invention, and

(8) FIG. 7 shows a diagram for a prior art control.

DETAILED DESCRIPTION

(9) In the various figures, the same features of the invention are always provided with the same reference symbols, for which reason these are only described once as a general rule.

(10) FIG. 1 schematically shows the principle of a control R of a speed N in operation of a turbocharger 100 for a compressor 101, in which the speed N as the controlled variable is derived from a compressor model VM for a boost pressure P of a turbocharger 100.

(11) The goal of the control R is that the turbocharger 100 provides sufficient output at low exhaust gas flows and to the extent possible does not exceed its load limit, in particular its maximum permissible speed N, at high speeds, and specifically under different operating conditions, even in the event of leakages L in the intake system of the compressor 101.

(12) FIG. 1 schematically shows the sequence of a possible method within the meaning of the invention for controlling R, and in particular limiting, of a speed N of a turbocharger 100 that is in operative connection with a compressor 101, comprising the following steps:

(13) 1) Provision of a setpoint Nsoll for the speed N of the turbocharger 100 on the basis of a model-based precontrol Mp for a calculation of a desired boost pressure Psoll ahead of the turbocharger 100, which is to say with the aid of a model-based precontrol Mp for a calculation of a desired boost pressure Psoll ahead of the turbocharger 100 and a conversion Upn of the desired boost pressure Psoll ahead of the turbocharger 100 into the setpoint Nsoll for the speed N of the turbocharger 100,
2) Determination of an actual value Nist for the speed N of the turbocharger 100,
3) Control of an actuator S of the turbocharger 100 in order to compensate for the difference between the desired value Nsoll and the actual value Nist for the speed N of the turbocharger 100.

(14) According to the invention, a main signal HS and a subsidiary signal NS are provided during the determination of the actual value Nist for the speed N of the turbocharger 100 in step 2), wherein the main signal HS and the subsidiary signal NS are combined as shown in FIGS. 4, 5, and 6 in order to validate the actual value Nist for the speed N of the turbocharger 100.

(15) The invention proposes here, firstly, to use the speed N of the turbocharger 100, and not the boost pressure P ahead of the turbocharger 100, as the controlled variable in the control R of a controlled variable in operation of a turbocharger 100 (see FIGS. 1 and 2). In this instance, the maximum permissible speed Nmax of the turbocharger 100 can be taken directly into account, or in other words be included in the control, for example as a maximum settable setpoint Nsoll for the speed N of the turbocharger 100 (see FIG. 2). To obtain the setpoint Nsoll for the speed N of the turbocharger 100, the desired boost pressure Psoll ahead of the turbocharger 100 is calculated from the known model-based precontrol Mp and is converted into a setpoint Nsoll for the speed N of the turbocharger 100 (an exemplary conversion Upn according to a compressor model VM can be seen in FIG. 2).

(16) Moreover, an actual value Nist for the speed N of the turbocharger 100 is ascertained within the scope of the invention from two signals HS, NS (see FIGS. 4, 5, and 6) as a combined actual value Nist for the speed N of the turbocharger 100. As shown in particular by FIGS. 4, 5, and 6, a validation of the actual value Nist modeled in step 2) for the speed N of the turbocharger 100 is carried out within the scope of the invention by comparison of two signals HS, NS.

(17) The main signal HS for the speed N of the turbocharger 100 can still be derived from the compressor model VM. A subsidiary signal NS for the speed N of the turbocharger 100 can be obtained from either a turbine model TM or a sensor value Nsensor, as is indicated by FIGS. 4 and 5.

(18) As is shown in FIG. 3, these speed signals HS, NS correlate with one another in a system with no leakage L in the intake path ahead of the compressor 101. In the case of leakage L in the intake path ahead of the compressor 101, the main signal HS takes on smaller values than the subsidiary signal NS, because the subsidiary signal NS is not affected by the leakage L.

(19) In FIG. 3, three regions 1, 2, 3 are indicated in this regard: a permissible region 1 (no leakage s), a limit region 2 (possible or moderate leakage m), and an impermissible region 3 (large leakage I).

(20) As is indicated in FIGS. 3 and 5, the actual value Nist for the speed N of the turbocharger 100 can be set essentially equal to the main signal HS in the permissible region 1. In the limit region 2, the main signal HS can advantageously be raised. In the impermissible region 3, the actual value Nist for the speed N of the turbocharger 100 can be determined to be essentially equal to the subsidiary signal NS.

(21) As is indicated in FIG. 5, the invention intervenes in the speed control loop according to FIG. 1 in the event of discrepancies between the main signal HS and the subsidiary signal NS that can be attributed to a leakage L.

(22) The actual value Nist of the combined speed Nist can, as shown in FIG. 5, be determined as follows:

(23) 1. A minimum threshold SWmin and a maximum threshold SWmax are determined as a function of the main signal HS (see FIG. 3).

(24) A leakage factor LF is produced by comparison of the main signal HS and the subsidiary signal NS, e.g. as follows:

(25) If the subsidiary signal NS is less than the minimum threshold SWmin, a leakage factor equal to 0 is produced.

(26) If the subsidiary signal NS is greater than the maximum threshold SWmax, a leakage factor equal to 1 is produced.

(27) If the subsidiary signal NS is between the two thresholds SWmin and SWmax, a leakage factor is interpolated between 0 and 1.

(28) 2. A validated actual value Nist of the combined speed N is produced as a function of the leakage factor LF.

(29) As is indicated in FIG. 5, the validated actual value Nist of the combined speed N can be determined, for example with the aid of a Kalman filter KF whose parameters are determined as a function of the leakage factor LF.

(30) A robust prevention (see FIG. 6) of overspeeds Nist>Nmax (see FIG. 7) independently of the instantaneous operating situation is made possible with the aid of the invention. At the same time, the intervention in the control loop takes place in such a manner that repercussions on the dynamic behavior of the closed control loop with respect to stability and the tendency to oscillate are minimized.

(31) A setpoint limiting for the speed N of the turbocharger 100 can advantageously take place in step 1) in the provision of the setpoint Nsoll for the speed N of the turbocharger 100, in which setpoint limiting the maximum permissible speed Nmax of the turbocharger 100 is taken into account as the limit value. Due to the control R of the speed N, it is advantageously possible to cap the pressure-based value of the speed N with a mechanical limit value so that the controller can control precisely to this limit value when this limit is reached.

(32) According to FIG. 2, it is possible that the same mathematical model, in particular the compressor model VM, and/or the same (thermodynamic) parameters is/are used in operation of the turbocharger 100 for the setpoint Nsoll for the speed N of the turbocharger 100 in step 1) and the actual value Nist for the speed N of the turbocharger 100 in the main signal HS in step 2). The compressor model VM and the parameters used are explained with the aid of FIG. 2.

(33) As FIG. 2 shows, the following thermodynamic quantities can be used or taken into account as parameters in operation of the turbocharger 100 in the conversion Upn of the boost pressure P into the boost speed N of the turbocharger 100: a pressure PvV ahead of the compressor 101, a mass flow dm/dt of an intake air through the compressor 101 as well as a temperature ahead of the temperature TvV ahead of the compressor 101. As is shown in FIG. 2, these parameters are incorporated into the speed N of the turbocharger 100 by means of a characteristic map K.

(34) FIG. 6 shows a control R within the meaning of the invention in the case of a leakage L in which has been ascertained as a subsidiary signal NS through a turbine model TM. At the same time, it is possible that the speed N for the subsidiary signal NS can be sensed. According to FIG. 5 it is also possible that both options can contribute to forming the subsidiary signal NS in the framework of a choice A in the control R. Since the controller now uses a combined speed Nist that is greater than the setpoint Nsoll, the boost pressure control deviation (˜300 mbar) is not compensated by the controller.

(35) FIG. 7 shows a control without a combination of the actual value within the meaning of the invention, which was taken into account in FIG. 6. In FIG. 7 the controller controls the boost pressure Pist or the speed Nist modeled through the compressor to the desired speed Nsoll and in doing so endangers the turbocharger T beyond the load limit Nist>Nmax.

(36) The turbocharger 100, which can be operated in accordance with a method, represents a further aspect of the invention in addition to the method. As is shown in FIG. 4, according to the invention the turbocharger 100 has a control unit 10 that is designed to control the turbocharger 100 accordingly. It is possible here that the control unit 10 can be implemented in an engine controller 10* of an internal combustion engine or as a separate control unit 10 of the turbocharger 100. Provided in the control unit 10 is a storage device 11 in which can be stored a computer program product that, when at least partially executed in a computing unit 12 of the control unit 10, performs a method that can proceed as described above.

(37) The above description of the figures describes the present invention solely within the framework of examples. Individual features of the embodiments can of course be freely combined with one another insofar as technically appropriate without departing from the scope of the invention.

(38) The invention being thus described, it will be obvious that the same may be varied in many ways. Such variations are not to be regarded as a departure from the spirit and scope of the invention, and all such modifications as would be obvious to one skilled in the art are to be included within the scope of the following claims.