METHOD FOR OPERATING AN INTERNAL COMBUSTION ENGINE AND THE INTERNAL COMBUSTION ENGINE

Abstract

A method for operating an internal combustion engine is provided, wherein the internal combustion engine has at least one combustion engine and a fresh gas line and wherein a compressor, to which a trim adjuster is assigned, is integrated into the fresh gas line, said trim adjuster by which an edge section of the inlet cross section of a compressor wheel can be covered to a variable extent. In this case, the edge section of the inlet cross section is covered relatively little in a release position of the trim adjuster and covered relatively greatly in a covering position of the trim adjuster. It is provided that the trim adjuster is adjusted between the release position and the covering position, when substantially the same compressor pressure ratio and substantially the same fresh gas mass flow and substantially the same compressor efficiency are achieved in both operating positions.

Claims

1. A method for operating an internal combustion engine comprising an engine and a fresh gas line, the method comprising: integrating a compressor into the fresh gas line; and assigning the compressor to a trim adjuster via which an edge section of the inlet cross section of a wheel of the compressor is adapted to be covered to a variable extent, wherein an edge section of the inlet cross section is covered relatively little in a release position of the trim adjuster and is covered relatively greatly in a covering position of the trim adjuster; and adjusting the trim adjuster between the release position and the covering position, when substantially a same compressor pressure ratio and substantially a fresh gas mass flow and substantially a same compressor efficiency are achieved in both operating positions.

2. The method according to claim 1, wherein the trim adjuster covers the edge section of the inlet cross section as little as possible in the release position and/or covers it as much as possible in the covering position.

3. The method according to claim 1, wherein the compressor efficiency is determined based on a measured value for the pressure of the exhaust gas in an exhaust line of the internal combustion engine upstream of an exhaust gas turbine, which is connected to the compressor in a rotationally driven manner.

4. The method according to claim 1, wherein, in an application mode of the internal combustion engine for a plurality of operating states in each case the exhaust gas pressures are determined upstream of the exhaust gas turbine with the trim adjuster in the release position, on the one hand, and in the covering position, on the other, and an adjustment range for all operating conditions is derived therefrom, wherein the determined adjustment range is used for a normal operation of the internal combustion engine.

5. The method according to claim 1, wherein the trim adjuster is adjusted between the release position and the covering position when the same compressor efficiency plus a hysteresis value is achieved.

6. An internal combustion engine comprising: a combustion engine; and a fresh gas line; a compressor integrated into the fresh gas line, the compressor being assigned a trim adjuster by which an edge section of the inlet cross section of a wheel of the compressor is adapted to be covered to a variable extent, wherein the edge section of the inlet cross section is covered relatively little in a release position of the trim adjuster and covered relatively greatly in a covering position of the trim adjuster; and a control device configured for automatically executing a method according to claim 1.

7. The internal combustion engine according to claim 6, wherein the trim adjuster comprises an annular aperture.

8. The internal combustion engine according to claim 7, wherein the trim adjuster additionally comprises a flow guiding device by which at least one section of the fresh gas line is divided into a central flow region and a peripheral flow region, both of which in the region of the inlet plane of the compressor wheel transition into a flow chamber of the compressor, wherein the peripheral flow region is designed closable by means of the aperture.

9. The internal combustion engine according to claim 8, wherein at least one flow guiding device end section, located adjacent to the compressor wheel, is formed movable along the longitudinal axis, wherein the peripheral flow region in the region of the inlet plane of the compressor wheel is closed by this end portion in a closed position of the flow guiding device and released in an open position.

10. The internal combustion engine according to claim 6, wherein an exhaust gas pressure sensor is integrated into an exhaust gas line of the internal combustion engine upstream of an exhaust gas turbine.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0019] 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:

[0020] FIG. 1 shows an internal combustion engine of the invention;

[0021] FIG. 2 shows a longitudinal section through a compressor for an internal combustion engine of the invention with an associated trim adjuster in a position covering an inlet cross section of a compressor wheel to the least possible extent;

[0022] FIG. 3 shows the compressor of FIG. 2 with the trim adjuster in a position covering the inlet cross section of the compressor wheel to the greatest possible extent;

[0023] FIG. 4 shows a characteristic map of a compressor according to FIGS. 2 and 3;

[0024] FIG. 5 shows the curves of the exhaust gas pressures upstream of the exhaust gas turbine of an exhaust gas turbocharger, comprising a compressor according to FIGS. 2 and 3, in each case, versus the reduced mass flow of the fresh gas through the compressor, on the one hand, with the trim adjuster of the compressor in the covering position and, on the other hand, with the trim adjuster in the release position;

[0025] FIG. 6 shows the curves, corresponding to FIG. 5, for the efficiencies of the exhaust gas turbocharger;

[0026] FIG. 7 shows the curves, corresponding to FIG. 5, for the efficiencies of the exhaust gas turbine;

[0027] FIG. 8 shows the curves, corresponding to FIG. 5, for the efficiencies of the compressor; and

[0028] FIG. 9 shows the curves, corresponding to FIG. 5, for the rotational speeds of the exhaust gas turbocharger.

DETAILED DESCRIPTION

[0029] FIG. 1 shows a schematic representation of an internal combustion engine of the invention with a combustion engine 10 designed as a gasoline engine and forming a plurality of cylinders 12. Cylinders 12, together with pistons guided up and down therein and a cylinder head delimit combustion chambers in which fresh gas is burned together with fuel. The fuel is injected, controlled by a control device 14 (engine control), by means of injectors 16 directly into the combustion chambers. The burning of the fuel/fresh gas mixture amounts leads to the cyclic up and down movements of the pistons, which in turn are transmitted in a known manner via connecting rods, not shown, to a crankshaft, also not shown, whereby the crankshaft is rotationally driven.

[0030] The fresh gas is supplied to combustion engine 10 via a fresh gas line and, for this purpose, drawn in from the environment via an intake port 18, cleaned in an air filter 20, and then fed into a compressor 22, which is part of an exhaust gas turbocharger. The fresh gas is compressed by compressor 22, then cooled in a charge air cooler 24, and then fed to the combustion chambers. Compressor 22 is driven by an exhaust gas turbine 26 of the exhaust gas turbocharger, said turbine being integrated into an exhaust gas line of the internal combustion engine. Exhaust gas, which forms in the combustion chambers of internal combustion engine 10 during the burning of the fuel/fresh gas mixture amounts, is discharged from combustion engine 10 via the exhaust gas line and thereby flows through exhaust gas turbine 26. This leads in a known manner to a rotational driving of a turbine wheel, which is connected rotationally fixed via a shaft 28 to a compressor wheel 30 (cf. FIGS. 2 and 3) of compressor 22. The rotational driving of the turbine wheel is thus transmitted to compressor wheel 30.

[0031] In order to realize the best possible use of the enthalpy of the exhaust gas to generate compression power by means of the exhaust gas turbocharger during operation of combustion engine 10 with varying loads and speeds, exhaust gas turbine 26 of the exhaust gas turbocharger can optionally have a device, controllable by control device 14, for variable turbine inflow (VTG) 32. This can comprise in a known manner a plurality of guide blades which are arranged in an inlet channel of exhaust gas turbine 26 and which are formed individually rotatable, it being able to adjust these together by means of an adjusting device. Depending on the rotational positions of the guide blades, these narrow more or less the free flow cross section in the inlet channel of exhaust gas turbine 26 and also influence the section of the primary inflow to the turbine wheel and the orientation of this inflow.

[0032] Downstream of compressor 22, a throttle valve 34, which can also be controlled by control device 14, is integrated into the charge air section, i.e., into the section of the fresh gas line that is located between compressor 22 and combustion engine 10.

[0033] The internal combustion engine can comprise an exhaust gas recirculation line 36 for implementing a (low-pressure) exhaust gas recirculation, in which exhaust gas can be branched off from a section of the exhaust gas line which is located downstream of exhaust gas turbine 26 and in particular also downstream of an exhaust gas aftertreatment device 38, for example, a particulate filter, and can be introduced into a section of the fresh gas line upstream of compressor wheel 30. The amount of exhaust gas to be recirculated via exhaust gas recirculation line 36 can be controlled or regulated by means of a control valve 40, which can be activated by control device 14. Furthermore, an exhaust gas cooler 42 can be integrated into exhaust gas recirculation line 36 for cooling the exhaust gas guided over it.

[0034] Compressor 22 is assigned to a trim adjuster 44, by means of which the inflow of fresh gas to compressor wheel 30 can be influenced. For this purpose, trim adjuster 44 or an associated actuator can be controlled by control device 14. Exhaust gas recirculation line 36 can open into the fresh gas line upstream or on the side of trim adjuster 44 facing away from compressor wheel 30. An opening downstream of or in the region of trim adjuster 44 (and upstream of compressor wheel 30) is also possible.

[0035] FIGS. 2 and 3 each show in a longitudinal section a possible embodiment of a compressor 22 of an internal combustion engine of the invention. Said compressor 22 can be provided, for example, for an internal combustion engine according to FIG. 1, in which case trim adjuster 44 and a connection channel 46 for exhaust gas recirculation line 36 are then integral components of compressor 22. This is indicated in FIG. 1 by a dashed border.

[0036] Compressor 22 according to FIGS. 2 and 3 comprises a housing 50, which can represent a partial housing of an overall housing of an exhaust gas turbocharger. Housing 50 of compressor 22 forms a flow chamber 52 within which compressor wheel 30 is rotatably mounted. On the inlet side, flow chamber 52 has an inlet cross section lying in an inlet plane 54. Fresh gas can be fed from a compressor inlet 58 to compressor wheel 30 via an inlet channel 56 which is likewise formed by housing 50 of compressor 22. On the outlet side, flow chamber 52 is delimited by an outlet plane surrounding the outlet edges of wheel blades 60 of compressor wheel 30. This is adjoined by a diffuser chamber 62, which also surrounds the outlet edges of wheel blades 60, and then, as is no longer shown in FIGS. 2 and 3, by a compressor volute. A compressor outlet exits from the compressor volute.

[0037] Within inlet channel 56, trim adjuster 44 is located as close as possible to the inlet cross section of compressor wheel 30. Trim adjuster 44 comprises an iris diaphragm 48 with a design that is basically also known from photographic lenses. In a covering position according to FIG. 3, trim adjuster 44 prevents, as much as possible, an inflow of fresh gas to compressor wheel 30, which flows in the direction of compressor wheel 30, in an annular region of the inlet cross section, said region being located at the edge. Trim adjuster 44 thereby focuses this fresh gas flow onto a section, close to the hub, of compressor wheel 30. In contrast, in a release position according to FIG. 2, the fresh gas can flow into compressor wheel 30 over the entire inlet cross section. The aperture elements which form iris diaphragm 48 and which to open or close iris diaphragm 48 are each mounted pivotable about an axis within housing 50, are arranged in the release position completely in an annular recess 64 of housing 50.

[0038] It is provided according to the invention that, during operation of an internal combustion engine in accordance with FIG. 1, trim adjuster 44 is adjusted between the release position and the covering position, when the same compressor pressure ratio Try, the same (reduced) fresh gas mass flow ({dot over (m)}.sub.red), and substantially the same compressor efficiency .sub.V are reached in these two operating positions. An adjustment of trim adjuster 44 at only substantially the same compressor efficiency .sub.V occurs because the theoretical adjustment point is defined both by the same values for the compressor pressure ratio .sub.V and the reduced fresh gas mass flow {dot over (m)}.sub.red and by the same values for the compressor efficiency .sub.V, but a hysteresis value is provided for the actual adjustment, whereby a relatively frequent adjustment of trim adjuster 44 is to be avoided in a longer-lasting operation of the internal combustion engine in the range of the theoretical adjustment point. The corresponding hysteresis value here is, for example, 2%.

[0039] In order to determine a switching range for compressor 22 which takes into account said hysteresis value, the two compressor characteristic maps for operation of compressor 22 with trim adjuster 44 are determined in a known manner in an application mode of the internal combustion engine in a release position, on the one hand, and in a covering position, on the other, and placed in relation to one another, as is shown by way of example in FIG. 4. The compressor characteristic map, which is drawn by solid lines, is the one that describes the operation of compressor 22 with trim adjuster 44 in the release position, whereas the compressor characteristic map, which is drawn by dotted lines, characterizes the operation of compressor 22 with trim adjuster 44 in the covering position.

[0040] Furthermore, for a plurality of defined compressor pressure ratios Try, in each case the compressor efficiency .sub.V is determined in an operation with trim adjuster 44 in the release position, on the one hand, and with trim adjuster 44 in the covering position, on the other hand. In this case, the compressor efficiency .sub.V is determined as a function of a measurement of the exhaust gas pressure in the exhaust line of the internal combustion engine upstream of exhaust gas turbine 26. The two corresponding curves (versus the reduced fresh gas mass flow), again for trim adjuster 44 in the release position (solid line) and for trim adjuster 44 in the covering position (dotted line), are determined in FIG. 5 for an exemplary compressor pressure ratio .sub.V based on a boost pressure p.sub.2 of 1600 mbar. The corresponding curves for the efficiencies .sub.ATL of the exhaust gas turbocharger as a whole (FIG. 6) and for the efficiencies .sub.T, .sub.V of exhaust gas turbine 26 (FIG. 7) and compressor 22 (FIG. 8), influencing these efficiencies .sub.ATL of the exhaust gas turbocharger, are shown in a further diagram. The diagram of FIG. 9 additionally shows the curves for the rotational speeds n.sub.ATL of the exhaust gas turbocharger during the corresponding measurements.

[0041] In the (double) characteristic map according to FIG. 4, curves corresponding to different values of the efficiency differences between the two operating positions of trim adjuster 44 are drawn for the area in which the two compressor characteristic maps overlap and in which, consequently, operation of compressor 22 with trim adjuster 44 in either the covering position or the release position is basically possible. Positive percentage values here indicate an efficiency advantage for operating compressor 22 with trim adjuster 44 in the covering position, whereas negative percentage values indicate an efficiency advantage for operating compressor 22 with trim adjuster 44 in the release position. The dotted line shows the (equality) curve on which the compressor efficiencies .sub.V are identical or the differences in efficiencies are zero. A theoretical adjustment point for adjusting trim adjuster 44 between the release position and the covering position for a defined compressor pressure ratio .sub.V and a defined reduced fresh gas mass flow {dot over (m)}.sub.red therefore lies on this curve, a hysteresis value of 2% being taken into account for an actual adjustment. If therefore, for example, compressor 22 is operated with trim adjuster 44 in the release position at a specific compressor pressure ratio .sub.V and a specific reduced fresh gas mass flow {dot over (m)}r.sub.ed, in which an efficiency advantage is achieved compared with a corresponding operation with trim adjuster 44 in the covering position (i.e., the position of such an operating point would be to the right of the dashed curve in the map of FIG. 4), and during further operation, the compressor pressure ratio .sub.V and/or the reduced fresh gas mass flow {dot over (m)}r.sub.ed change such that this operating point shifts in the direction of the dashed equality curve, then the trim adjuster is not adjusted when the dashed equality curve is reached, but only when (and if) the operating point reaches the curve for the two-percent efficiency advantage (hysteresis value) of an operation of compressor 22 with trim adjuster 44 in the covering position. In FIG. 4, this is illustrated for the full load curve, drawn as an example, by means of a cross, which designates the theoretical adjustment point, and a circle, which designates the actual adjustment point. In the same way, an adjustment from the covering position to the release position would only take place upon reaching a relevant efficiency advantage of 2%, as shown in FIG. 4 on the basis of the adjustment point marked by a rectangle on the full load curve.

[0042] 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: