The invention relates to a method for requirement-based servicing of an injector in a common rail system in which a load factor is calculated and is set as decisive for the servicing recommendation of the injector.
DE 10 2005 048 532 A1 discloses a method for monitoring the mechanical components of a drive engine in a vehicle in which in a first step the operating data of the component are acquired as a load spectrum, and a characteristic variable of the component is ascertained in a second step. If there is a risk of a fault in the component, in a third step the loading of the component is reduced or limited, which is intended to prevent the vehicle being immobilized for a short time. In addition, the driver is informed about the risk of a fault, and the predicted residual running time is displayed.
U.S. Pat. No. 9,416,748 B2 discloses a method for monitoring an injector in which a coking factor is calculated on the basis of the residence time in the rotational speed classes and torque classes. The injection period is then correspondingly adapted on the basis of the coking factor, which is intended to permit the exhaust gas limiting values to be complied with.
Taking the prior art described above as a basis, the invention is based on the object of developing a method for requirement-based servicing of an injector.
This object is achieved by means of a method having the features of claim 1. The refinements are presented in the dependent claims. In this context, during ongoing operation of the engine, a current operating point is first stored as a function of the rail pressure and of the fuel injection mass, said current operating point is then multiplied by a damage factor and is subsequently stored as a reference injection cycle as a function of the rail pressure and of the fuel injection mass. The damage factor describes the hydrodynamic loading of the common rail system. The damage factor is read out from a damage factor characteristic diagram as a function of the rail pressure and of the fuel injection mass. The damage factor can also optionally be weighted on the basis of the fuel temperature. After the calculation of the reference injection cycles, the sum thereof is calculated and stored as a total reference injection cycle. A load factor is then in turn determined from the total reference injection cycle and the maximum permissible injection cycles by forming quotients, which load factor is set as decisive for the servicing recommendation of the injector. Finally, a comparison of the load factor with a limiting value defines whether either a servicing recommendation to replace the injector is generated or whether a residual running time, within which non-problematic further operation is possible, is predicted.
For the end customer, the invention provides the advantage of even further improved transparency in that the assignment of individual ways of behaving and servicing intervals or servicing costs is indicated. For example also in that the end customer can access the current operating data by means of an app. The invention provides the advantage both for the manufacturer of the internal combustion engine as well as for the end customer that a service technician can be dispatched even before the expiry of the maximum service life of the injector. However, if an injector fails, thanks to the invention a history which can be tracked uninterruptedly can be retrieved. Likewise, the data can be used as a basis for the re-development of an injector.
A preferred exemplary embodiment is illustrated in the figures, in which:
FIG. 1 shows a system diagram,
FIG. 2 shows a characteristic diagram of the injection cycles,
FIG. 3 shows a characteristic diagram of the damage factor,
FIG. 4 shows a characteristic diagram of the fuel temperature,
FIG. 5 shows a characteristic diagram of the reference injection cycle and
FIG. 6 shows a program sequence diagram.
FIG. 1 shows a system diagram of an electronically controlled internal combustion engine 1 with a common rail system. The common rail system comprises the following mechanical components: a low-pressure pump 3 for feeding fuel from a fuel tank 2, a variable intake throttle 4 for influencing the volume of fuel flowing through, a high-pressure pump 5 for feeding the fuel under increased pressure, a rail 6 for storing the fuel and injectors 7 for injecting the fuel into the combustion chambers of the internal combustion engine 1. The common rail system can also optionally be embodied with individual accumulators, wherein then, for example, an individual accumulator is integrated as an additional buffer volume for the fuel in the injector 7. A passive pressure limiting valve 10 is provided as protection against an inadmissibly high pressure level in the rail 6, which pressure limiting valve 10 opens, for example, at a rail pressure of 2400 bar, and in the opened state diverts the fuel from the rail 6 into the fuel tank 2.
The mode of operation of the internal combustion engine 1 is determined by an electronic engine control unit 9 which includes the customary components of a microcomputer system, for example a microprocessor, I/O modules, buffers and storage modules (EEPROM, RAM). The operating data which are relevant for the operation of the internal combustion engine 1 are applied in characteristic diagrams/characteristic curves in the memory modules. The electronic engine control unit 9 uses these to calculate the output variables from the input variables. FIG. 1 illustrates the following input variables by way of example: the rail pressure pCR, which is measured by means of a rail pressure sensor 8, an engine rotational speed nMOT, optionally the individual accumulator pressure pE and an input variable EIN. The term input variable EIN includes the further signals, for example a signal with a specification of the power by the operator, and the charge air pressure of an exhaust gas turbocharger. FIG. 1 illustrates, as output variables of the electronic control unit 9, a signal PWM for actuating the intake throttle 4, a signal ve for actuating the injectors 7 (start/end of injection) and an output variable AUS. The output variable AUS is representative of the further actuation signals for performing open-loop and closed-loop control of the internal combustion engine 1, for example for an actuation signal for activating a second exhaust gas turbocharger in the case of sequential turbocharging. Via this interface 15, the manufacturer of the internal combustion engine can read out data and, when necessary, react early by dispatching a service technician. Likewise, the operator can access the current operating data.
FIG. 2 shows a characteristic diagram 11 of the injection cycles EZ. A plurality of exemplary operating points of the injection cycles EZ are illustrated in the characteristic diagram 11 as a function of the rail pressure pCR and of the fuel injection mass qV. In practice, this characteristic diagram can be embodied as a 20 times 20 matrix. For reasons of better clarity, the injection cycles are standardized to a million injection cycles. Therefore, for example the operating point EZ(1/4) is defined by a rail pressure pCR=1020 bar and a fuel injection mass qV=30 mg (milligrams). The operating point itself has the value 46.76 times one million injection cycles. The point EZ(9/9) has the highest value, specifically 68.32, within the characteristic diagram. In other words: the characteristic diagram 11 represents a load spectrum of the frequency of an operating point within the rail pressure injection mass classes.
FIG. 3 shows a characteristic diagram 12 of the damage factor HSF. The damage factor HSF describes the hydrodynamic loading on the common rail system. The characteristic diagram 12 shows the same reference points of the rail pressure pCR and of the fuel injection mass qV as the characteristic diagram 11 of the injection cycles EZ. In practice, the characteristic diagram 12 is therefore also embodied as a 20 times 20 matrix. Values of the damage factor HSF are illustrated within the characteristic diagram 12. The highest value within the characteristic diagram 12 is occupied by the number 1. This value corresponds to the critical operating point with the highest intensity of wear, here the point HSF(4/8) with a rail pressure pCR=1790 bar and a fuel injection mass qV=210 mg. The reference points HSF(1/4) and HSF(9/9) correspond to the two points EZ(1/4) and EZ(9/9) of the characteristic diagram 11. The characteristic diagram 12 is populated either with the data from back-measured field engines or with data from a test stand run. The further description is provided in conjunction with FIG. 4 in which a characteristic diagram 13 of the fuel temperature TKR is illustrated. The characteristic diagram 13 is provided as an option, wherein a relatively high fuel temperature brings about qualitatively a relatively large amount of damage. The values of the damage factor HSF are weighted by means of the characteristic diagram 13. The characteristic diagram 13 therefore has the same reference points as the characteristic diagrams 11 and 12. Therefore, for example the reference point TKR(1/4) corresponds to the reference point EZ(1/4) in the characteristic diagram 11 and to the reference point HSF(1/4) in the characteristic diagram 12. The fuel temperatures are illustrated in OC within the characteristic diagram 13.
The further description applies jointly to FIGS. 5 and 6, wherein in FIG. 5 the characteristic diagram 14 of the reference injection cycles REZ, and in FIG. 6 the method are illustrated as a program sequence diagram. In S1, the current operating point BP is stored in the characteristic diagram 11 of the injection cycles EZ as a function of the rail pressure pCR and of the fuel injection mass qV, for example as EZ(9/9). Then, at S2 the damage factor HSF which corresponds to this is read out from the characteristic diagram 12, that is to say the reference point HSF(9/9). This reference point can optionally also be weighted by means of the fuel temperature, step S2A. At S3, the reference injection cycle REZ is then calculated by multiplying the current operating point BP by the damage factor HSF. The value of the reference injection cycle REZ(9/9) in FIG. 5 is consequently calculated from the value of EZ(9/9), value: 68.32 times one million, multiplied by the value of HSF(9/9), value: 0.8, to yield 54.65 times one million injection cycles. The further values of the reference injection cycles of the characteristic diagram 14 are calculated in an analogous fashion. Subsequently, at S4 a total reference injection cycle REZ(ges) is calculated by forming sums of the reference injection cycles REZ. At S5, the maximum number of injection cycles EZ(krit) is read in. The maximum number is determined at the manufacturer of the injection combustion engine from trials on a component test bench. An exemplary value of the maximum permissible injection cycles is EZ(krit)=100 million injection cycles, which corresponds to a total service life of the injector of 8900 hours. At S6, a load factor HI is calculated by forming quotients from the total reference injection cycle REZ(ges) and the maximum number of injection cycles EZ(krit). The load factor corresponds to the hydrodynamic loading of the injector. Then, at S7 it is tested whether the load factor HI is less than or equal to a limiting value GW, for example GW1. If this is the case, interrogation result S7: yes, at S8 a residual running time tRP is predicted for non-problematic further operation of the internal combustion engine, and the program sequence is continued at S1. If the result of the testing at S7 is that the load factor HI is higher than the limiting value GW, interrogation result S7: no, the load factor HI is set as decisive for the servicing recommendation to replace the injector. For this purpose, at S9 a time margin tRV for the still remaining further operation is calculated. Subsequently at S10 a servicing recommendation is output to the operator, wherein the servicing recommendation indicates replacement of all the injectors of the internal combustion engine. Therefore, the program sequence diagram is then ended.
LIST OF REFERENCE NUMBERS
1 Internal combustion engine
2 Fuel tank
3 Low-pressure pump
4 Intake throttle
5 High-pressure pump
6 Rail
7 Injector
8 Rail pressure sensor
9 Electronic engine control unit
10 Pressure limiting valve
11 Characteristic diagram of injection cycles (EZ)
12 Characteristic diagram of damage factor (HSF)
13 Characteristic diagram of fuel temperature (TKR)
14 Characteristic diagram of reference injection cycles (REZ)
15 Interface
Patent Application
20200158043
