Method for operating a reciprocating internal combustion engine

Abstract

A method for operating a reciprocating internal combustion engine in an engine braking mode of operation is provided. The method includes closing, for a first time, at least one exhaust valve of at least one cylinder in the engine braking mode of operation within a working cycle, and opening for a first time, and closing, for a second time, the at least one exhaust valve of the at least one cylinder, and opening for a second time to thereby discharge compressed gas in the cylinder via a piston of the cylinder from the cylinder. After the first opening and before the second closing, the exhaust valve is kept open, until the cylinder is filled with gas which flows through at least one exhaust channel from at least one second cylinder of the reciprocating internal combustion engine.

Claims

1. A method for operating a reciprocating internal combustion six-cylinder engine in an engine braking mode of operation, where the engine includes a first cylinder bank with a first set of three cylinders in a row and a second cylinder bank with a second set of three cylinders in a row, and each of the first and second cylinder banks has its own common exhaust manifold, the method comprising the steps of: closing, for a first time, at least one exhaust valve of a first cylinder in the engine braking mode of operation within a working cycle, and opening for a first time the at least one exhaust valve within the working cycle, and closing, for a second time, the at least one exhaust valve of the first cylinder within the working cycle, and opening for a second time the at least one exhaust valve to thereby discharge compressed gas in the first cylinder via a piston from the first cylinder within the working cycle, and wherein after the first opening and before the second closing of the at least one exhaust valve, the at least one exhaust valve is kept open, until the first cylinder is filled with respective gas which flows through at least one respective exhaust channel introduced from a second cylinder and a third cylinder of the reciprocating internal combustion engine, the first, second, and third cylinders being different from one another and the gas from the second and third cylinders charges the first cylinder while the first, second, and third cylinders have a respective exhaust valve open simultaneously, wherein the at least one exhaust valve of the first cylinder after the first opening is at least partially kept open until 210 degrees of crank angle after top dead center (TDC), and wherein the reciprocating internal combustion engine is operated in an unfired condition without fuel injection during the engine braking mode of operation.

2. The method according to claim 1, further comprising: closing, for a first time, at least a second exhaust valve of the second cylinder in the engine braking mode of operation within a working cycle of the second cylinder, and opening the at least a second exhaust valve for a first time, and closing, for a second time, the at least a second exhaust valve of the second cylinder, and opening the at least a second exhaust valve for a second time thereby discharging compressed gas in the second cylinder from the second cylinder via a second piston of the second cylinder, and wherein the first cylinder is filled with at least a portion of the gas discharged from the second cylinder while the at least a second exhaust valve, after the second opening and before the first closing or after the first opening and before the second closing is at least partially open.

3. The method according to claim 1, further comprising: closing, for a first time, at least a second exhaust valve of the second cylinder in the engine braking mode of operation within a working cycle of the second cylinder, and opening the at least a second exhaust valve for a first time, and closing, for a second time, the at least a second exhaust valve of the second cylinder, and opening the at least a second exhaust valve for a second time thereby discharging compressed gas in the second cylinder from the second cylinder via a second piston of the second cylinder, and closing, for a first time, at least a third exhaust valve of the third cylinder in the engine braking mode of operation within a working cycle of the third cylinder, and opening the at least a third exhaust valve for a first time, and closing, for a second time, the at least a third exhaust valve of the third cylinder, and opening the at least a third exhaust valve for a second time to thereby discharge via a third piston of the third cylinder compressed gas in the third cylinder from the third cylinder, wherein the first cylinder is filled with at least a part of the gas discharged from the second cylinder, while the at least a second exhaust valve to its second opening and before the first closing is open and wherein the first cylinder having at least one part of the discharged from the third cylinder gas is filled, while after the first opening and the second closing, and the at least a third exhaust valve is at least partially open.

4. The method according to claim 1, wherein the exhaust valves in the engine braking mode of operation perform a smaller stroke than in a normal mode of operation different from the engine braking mode of operation.

5. The method according to claim 4, wherein the normal mode of operation is a traction operation of the reciprocating internal combustion engine.

6. A reciprocating internal combustion engine for a motor vehicle, which is configured for performing a method according to claim 1.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) FIG. 1 depicts a diagram illustrating a method for operating a reciprocating internal combustion engine in an engine braking mode of operation, wherein three exhaust valves of respective cylinders of the reciprocating internal combustion engine perform, within a working cycle, two successive decompression strokes, to thereby realize a decompression brake with a particularly high engine braking power;

(2) FIG. 2 depicts an alternative embodiment of FIG. 1; and

(3) FIG. 3 depicts a diagram illustrating preferred ranges of the respective opening and closing times of the two successive decompression strokes, on the basis of a first exhaust valve.

DETAILED DESCRIPTION OF THE DRAWINGS

(4) The figures serve to illustrate a method for operating a reciprocating internal combustion engine of a motor vehicle. The reciprocating internal combustion engine is used to drive the motor vehicle and includes a total of, for example, six combustion chambers in the form of cylinders. The cylinders are arranged in series. A first set of three of these cylinders is arranged in a first cylinder bank, with a second set of three of these cylinders being arranged in a second cylinder bank. The cylinder banks each have a common exhaust manifold. The method is described with reference to one of the cylinder banks that is based on three of the six cylinders, wherein the following description can be readily transferred to the other cylinders and the other cylinder bank.

(5) In a first of the three cylinders, a first piston is arranged, wherein the first piston is translationally moved. In a second cylinder, a second piston is arranged, wherein the second piston is translationally moved. In the third cylinder, a third piston is also arranged, which is translationally moved. The three pistons are coupled by a respective connecting rod articulated to a crankshaft of the reciprocating internal combustion engine. The crankshaft is rotatably supported on a crankcase of the reciprocating internal combustion engine about a rotation axis relative to the crankcase. Due to the articulated coupling of the piston to the crankshaft, the translational movements of the pistons are transformed into a rotational movement of the crankshaft about its axis of rotation.

(6) In a normal operation of the internal combustion engine, a fired operation of the reciprocating internal combustion engine is carried out. Under this fired operation (normal operation) liquid fuel and air are introduced into the respective cylinders. This results in (in the respective cylinder) a fuel-air mixture that is compressed.

(7) The cylinders are associated with a respective intake channel, through which air can flow into the respective cylinders. The intake channel of the first cylinder is associated with a first intake valve which is movable between at least one closed position fluidly obstructing the intake channel of the first cylinder and at least one open position fluidly opening the intake channel of the first cylinder. Accordingly, a second intake valve is associated with the intake channel of the second cylinder, which is movable between a closed position, fluidly obstructing the intake channel of the second cylinder and at least one open position at least partially fluidly opening the intake channel of the second cylinder. Also, the intake channel of the third cylinder is associated with an intake valve which is movable between a closed position fluidly obstructing the intake channel of the third cylinder and at least one open position at least partially fluidly opening the intake channel of the third cylinder. If the respective intake valve is in its open position, air can flow through the intake channel in the cylinder.

(8) Due to ignition and combustion of the fuel-air mixture, exhaust gas is formed in the respective cylinder. At least one exhaust channel is associated to the respective cylinder, through which the exhaust gas may flow out of the respective cylinder. A first exhaust valve is associated with the exhaust channel of the first cylinder, which is movable between a closed position fluidly obstructing the exhaust channel of the first cylinder and at least one open position, which at least partially fluidly opens the exhaust channel of the first cylinder. A second exhaust valve is associated with the exhaust channel of the second cylinder, which is movable between a closed position fluidly obstructing the exhaust channel of the second cylinder and at least one open position, which at least partially fluidly opens the exhaust channel of the second cylinder. A third exhaust valve is also associated with the exhaust channel of the third cylinder, which is movable between a closed position fluidly obstructing the exhaust channel of the third cylinder and at least one open position, which at least partially fluidly opens the exhaust channel of the third cylinder. If the respective exhaust valve is in its open position, exhaust gas may flow from the respective cylinder through the respective exhaust channel.

(9) The air flows on a so-called intake side into the cylinder. Exhaust gas flows on a so-called exhaust or exhaust gas side out of the cylinders. On the exhaust side, an exhaust manifold is positioned, which is common to the three cylinders of the cylinder bank and which serves for guiding the out flowing exhaust gas from the cylinders. As will be explained below, the three exhaust valves can be positioned at least one time, that is at the same time, in the respective open position so that the cylinders are connected fluidically to each other via the exhaust manifold.

(10) The intake valves and the exhaust valves are actuated, for example by means of at least one camshaft and thereby moved from the respective closed position into the respective open position and optionally held in the open position. This is also referred to as valve timing. By the camshaft, the intake valves and the exhaust valves can be opened at predetermined instants or positions of the crankshaft. Furthermore, a respective closing of the intake valves and exhaust valves is allowed by the camshaft at predetermined points in time or rotational positions of the crankshaft.

(11) The respective rotational positions of the crankshaft about its axis are commonly also referred to as crank angle degrees (CA). The figures now show diagrams, wherein the abscissa 10 indicates the rotational positions, i.e., the crank angle degrees of the crankshaft.

(12) The reciprocating internal combustion engine is designed as a four-stroke engine, in which a so-called working cycle of the crankshaft includes exactly two revolutions of the crankshaft. In other words, a working cycle includes exactly 720 (CA). Within such a working cycle, that is, within 720 (CA), the respective piston moves twice in its respective top dead center (TDC) and twice in its respective bottom dead center (BDC).

(13) The dead center, in the region, in fired operation of the reciprocating internal combustion engine, the compressed fuel-air mixture is ignited is referred to as top dead center (TDC). In order to provide a good readability of the diagram shown in the figure, the top dead center TDC is rechanneled twice, namely once at 720 crank angle degrees and once at 0 crank angle degrees, this being the same rotational position of the crankshaft and the camshaft.

(14) The references BDC for bottom dead center, TDC for top dead center and ITDC for ignition top dead center relate to the positions of the first piston. The 720 (CA) shown in the diagrams thus relates to one working cycle of the first cylinder and the first piston. Based on this working cycle of the first piston, the second piston and the third piston reach their respective bottom dead center and their respective upper dead center or ignition top dead center at different rotational positions of the crankshaft. The following description regarding the first exhaust valve and the first intake valve refers to the respective bottom dead center BDC at 180 (CA) and 540 (CA), the top dead center (upper charge exchange dead center) at 360 (CA) and the ignition top dead center ITDC of the first piston at 0 (CA) and 720 (CA) and can be readily referred also to the second exhaust valve of the second cylinder, however, based on the respective bottom dead center, top dead center and ignition top dead center of the second piston as well as to the third exhaust valve, however, based on the respective bottom dead center, top dead center and ignition top dead center of the third piston.

(15) With reference to the respective working cycle of the respective cylinder, the cylinders and thus the exhaust valves and the intake valves are operated in the same way.

(16) The diagrams also exhibit an ordinate 12, on which a respective stroke of the respective intake valve and of the respective exhaust valve is plotted. This stroke is travelled by the respective exhaust or respective intake valve, when opening and closing.

(17) In the diagram of FIG. 1, a dashed line is a curve 14. The curve 14 characterizes the motion, that is the opening and closing of the first intake valve of the first cylinder. For clarity in the diagram, only the movement of the first intake valve of the first cylinder is shown. In the diagram a solid line is a curve 16, which characterizes the opening and closing of the first exhaust valve of the first cylinder during engine braking mode of operation. A curve 18 provided with circles characterizes the opening and closing of the second exhaust valve of the second cylinder, based on the working cycle of the first cylinder and the first piston. A curve 20 provided with crosses characterizes the opening and closing of the third exhaust valve of the third cylinder, based on the working cycle of the first cylinder. Thus, the curve 18 of the second exhaust valve of the second cylinder is represented as delayed with an offset of a 480-degree crank angle, corresponding to a firing order 1-5-3-6-2-4 of a six-cylinder in-line engine, with respect to the working cycle of the first cylinder and accordingly the curve 20 of the third exhaust valve of the third cylinder by 240 degrees of crank angle. The higher the respective curve of 14, 16, 18, and 20 is, the more the intake valve or the respective exhaust valve is opened at a corresponding rotational position (crank angle degree) of the crankshaft. If the respective curve of 14, 16, 18, and 20 is on the ordinate value zero, the intake valve or the respective exhaust valve is closed. In other words, the curves 14, 16, 18, 20 represent respective valve lift curves of the intake valve or of the respective exhaust valves.

(18) The process described below is performed in an engine braking mode of operation of the reciprocating internal combustion engine. In FIG. 1, curve 14 shows that the first intake valve of the first cylinder is opened in the area of the top dead center of the first piston and is closed in the area of the bottom dead center of the first piston. The first intake valve therefore performs an intake stroke 22, so that gas may flow, as fresh air, through the intake channel of the first cylinder in the same, wherein this gas is sucked in by the piston moving from the top dead center to the bottom dead center.

(19) As is shown by curve 16, within a working cycle of the first cylinder or of the first piston, the first exhaust valve is closed twice and opened twice.

(20) In relation to the intake 22 of the first intake valve, the first exhaust valve of the first cylinder within the working cycle of the first cylinder or of the first piston is closed for the first time at a rotational position indicated by 1S1 shortly before 480 (CA) of the crankshaft. This rotational position 1S1 is within the intake stroke 22. Within the working cycle of the first cylinder or of the first piston, the first exhaust valve is opened for the first time shortly before 660 (CA) of the crankshaft after the first closing at a rotational position indicated by 1O1. Subsequently, the first exhaust valve is closed for a second time at a rotational position indicated by 2S1 shortly after 240 (CA) of the crankshaft. Thereafter, the first exhaust valve is opened for a second time at a rotational position of the crankshaft indicated by 2O1 at about 270 (CA).

(21) By the first closing, the fresh air in the first cylinder is compressed by the first piston. Through the first opening and the second closing, the first exhaust valve performs a first decompression stroke 24 within the working cycle of the first cylinder, so that the first cylinder performs a first decompression cycle. In this case, through the first opening (at 1O1), the fresh air, previously compressed by the first piston or the gas previously compressed by the first piston is discharged from the first cylinder through the exhaust channel of the first cylinder, without using the compression energy stored in the compressed gas, for moving the first piston from its top dead center to its bottom dead center. Since the reciprocating internal combustion engine had to provide energy for compressing the gas in a previous moment, this therefore causes a braking of the reciprocating internal combustion engine and therefore of the motor vehicle. Due do the second opening at rotational position 2O1, and the first closing 1S1, the first exhaust valve performs a second decompression stroke 26 within the working cycle of the first cylinder, so that the first cylinder performs a second decompression cycle.

(22) In this second decompression stroke 26, i.e., second decompression cycle, within the working cycle of the first cylinder or piston, gas, which was compressed by the first piston in the first cylinder is discharged for a second time through the exhaust channel of the first cylinder, without the possibility to use the compression energy stored in this gas for moving the piston from the top dead center to the bottom dead center. In this way, in the engine braking mode of operation, a particularly high braking power may be achieved, i.e., a particularly high engine braking power.

(23) In the engine braking mode of operation, the first exhaust valve and the second and third exhaust valves perform a substantially lower stroke as in normal operation, that is during fired operation of the reciprocating internal combustion engine.

(24) Curve 18 in the figure also shows that in the engine braking mode of operation within a working cycle of the second cylinder or of the second piston, the second exhaust valve of the second cylinder is closed for the first time at a rotational position of the crankshaft designated as 1S2. With respect to the intake stroke of the second intake valve of the second cylinder, not shown in the figure, this first opening is also carried out in the area of the intake stroke of the second intake valve, and in particular within the intake stroke of the second intake valve. Within the working cycle of the second cylinder, the second exhaust valve is opened for the first time after the first closing at a rotational position of the crankshaft designated as 1O2. Subsequently, the second exhaust valve is closed a second time at a rotational position of the crankshaft designated as 2S2, and then opens again for a second time in a rotational position of the crankshaft within the working cycle of the second cylinder designated as 2O2. Through the first opening (at rotational position 1O2) and the second closing (at rotational position 2S2) of the second exhaust valve, the second exhaust valve performs a first decompression stroke 28. Through the second opening and the first closing, the second exhaust valve performs, within the working cycle of the second cylinder, a second decompression stroke. By first closing the second exhaust valve, gas is compressed in the form of fresh air, which was sucked in as a result of opening of the second intake valve of the second piston into the second cylinder. In the curve of the first decompression stroke 28 of the second exhaust valve, that is to say in the curve of a first decompression cycle of the second cylinder, the compressed gas is discharged via the second exhaust channel from the second cylinder, so that compression energy stored in the compressed gas cannot be utilized to move the second piston from its top dead center back to its bottom dead center. This process is repeated during the second decompression stroke 30, so that the second cylinder also performs two decompression cycles within a working cycle of the second cylinder.

(25) The same applies to the third cylinder. In the engine braking mode of operation within a working cycle of the third cylinder or of the third pistonas can be seen from the curve 20a first closing is performed at a rotational position of the crankshaft designated as 1S3. Subsequentlywithin the working cycle of the third cylinderthe third exhaust valve opens for the first time at a rotational position of the crankshaft designated as 1O3. Thereafter, the third exhaust valve is closed for a second time at a rotational position of the crankshaft designated as 2S3. Subsequently, the third exhaust valve is opened for a second time at a rotational position of the crankshaft designated 2O3. Through the first opening (at rotational position 1O3) and the second closing (at rotational position 2S3) the third exhaust valve performs, within a working cycle, a first decompression stroke 32, so that the third cylinder performs a first decompression cycle. As in the first cylinder and the second cylinder, the rotational position 1S3, at which the third exhaust valve is closed for the first time within the working cycle of the third cylinder or the third piston, lies also in the same area, and preferably within the intake stroke of the intake valve of the third cylinder. As a result of the first closing of the third exhaust valveas with the first cylinder and the second cylindergas in the form of fresh air, which has been sucked in through the opening of the third intake valve into the third cylinder by means of the third piston, is compressed by means of the third piston. Through the first opening (at rotational position 1O3) of the third exhaust the compressed gas is discharged from the third cylinder, so that compression energy stored in the compressed gas cannot be used to move the third piston from its top dead center to its bottom dead center.

(26) Through the second opening (at rotational position 2O3) and the first closing (at rotational position 1S3) the third exhaust valve performs within the working cycle of the third cylinder a second decompression stroke 34, wherein during the second decompression stroke 34 of the third exhaust valve, the third cylinder performs a second decompression cycle. Also in the second decompression cycle, compressed gas is discharged through the third exhaust channel from the third cylinder so that the compression energy stored in the compressed gas cannot be used to move the third piston from the top dead center into the bottom dead center. As the first exhaust valve within the working cycle of the first cylinder and the second exhaust valve within the working cycle of the second cylinder, the third exhaust valve of the third cylinder performs within the working cycle of the third cylinder two decompression strokes 32, 34 which are sequentially executed within the working cycle of the third cylinder. Thus, the three cylinders perform within their respective working cycle two consecutive decompression cycles, yielding extremely high engine braking power in the engine braking mode of operation.

(27) The degree of crank angle at which the second and third exhaust valve respectively open and close are correspondingly offset by 240 (CA) or 480 (CA) with respect to the first cylinder.

(28) To obtain now a particularly high engine braking power during engine braking mode of operation, it is contemplated that the first exhaust valve of the first cylinder is held open after the first opening (at rotational position 1O1) and before the second closing (at rotational position 2S1) after the first performed decompression until the first cylinder is filled again with a gas flowing on the exhaust side via the second exhaust channel from the second cylinder, and with gas flowing on the exhaust side from the third cylinder through the third exhaust channel. Based on the curve 16, it can be seen that the first exhaust valve is kept open until just after 240 degrees of crank angle after top dead center ITDC of the first piston or is completely closed just after 240 degrees crank angle after top dead center ITDC. In relation to the working cycle of the first cylinder, the second decompression stroke 30 of the second exhaust valveas is shown in FIG. 1is still completely within the first decompression stroke 24 of the first exhaust valve. The first decompression stroke 32 of the third exhaust valve is also partially inside both the second decompression stroke 30 and inside the first decompression stroke 24, since the third exhaust valvewith respect to the working cycle of the first cylinderis opened already before 180 degrees of crank angle after the top ignition dead center of the first piston. This means that all three exhaust valves are opened temporarily at the same time at the rotational position 1O3 through the first opening of the third exhaust valve, so that the cylinders are fluidly connected to each other via the exhaust manifold. In this way, the first cylinder may be charged with gas from the second cylinder and from the third cylinder for the second decompression cycle (decompression stroke 26) following the first decompression cycle (decompression stroke 24), whereby a particularly high engine braking power is obtained. The first cylinder is thereby filled for this second decompression with gas from the second decompression cycle of the second cylinder and with gas from the first decompression cycle of the third cylinder.

(29) The first exhaust valve should be kept open after first opening 1O1 and before the second closing 2S1 at least until the first cylinder is filled with gas flowing through at least one exhaust channel from at least one second cylinder of the reciprocating internal combustion engine. This means that the first cylinder should be filled with gas of the second or third cylinder at least and thus the first cylinder is only filled with gas by another cylinder.

(30) This principle can also be transferred easily to the second cylinder and the third cylinder. This means that, for example, the second cylinder for its second decompression cycle within the working cycle of the second cylinder is filled that is it's being charged with gas from the first cylinder and with gas from the third cylinder. The third cylinder is charged within the working cycle of the third cylinder for the second decompression cycle with gas from the first cylinder and with gas from the second cylinder. This is advantageous becauseas can be seen for example from the figure based on the first cylinderafter the intake stroke 22 of the first intake valve and before the second decompression cycle or before the second decompression stroke 26, no intake stroke is performed by the first intake valve. This means that the first cylinder after the intake stroke 22 and before the second decompression cycle may not be filled with gas via the intake channel of the first cylinder. Therefore, it is intended to fill the first cylinder with gas for its second decompression cycle via the exhaust channel of the second cylinder, which gas comes from both the second cylinder as well as from the third cylinder.

(31) Thus, there is an overlap between the second closing of the first exhaust valve andbased on the working cycle of the third cylinderthe first opening of the third exhaust valve. Advantageously, by the overlapping of the respective first opening of a first exhaust valve and a second closing of a third exhaust valve and/or the first closing of a second exhaust valve, pressure peaks in the exhaust manifold may be reduced through overflowing of gas from the first into the third and/or second cylinder. Also, due to the overlapping of the respective second opening of a first exhaust valve with the first decompression stroke of the third exhaust valve, pressure peaks in the exhaust manifold may be avoided due to the overflow of gas from the first into the third cylinder. Further an overlap between the first opening of the third exhaust valve andbased on the working cycle of the second cylinderthe first closing of the second exhaust valve takes place. Further, the second closing of the first exhaust valve occurs after the first closing of the second exhaust valve so that both gas from the second cylinder as well as gas from the third cylinder may flow into the first cylinder. Thus, the first cylinder is charged two times, that is, with gas from the second cylinder and with gas from the third cylinder.

(32) In FIG. 2, an alternative embodiment of FIG. 1 is shown. The same lines and same points are provided in FIG. 2 with the same reference numerals as in FIG. 1. In the diagram of FIG. 2 the unchanged curve 14 of FIG. 1 is plotted. The curves 16, 18 and 20 have, in contrast to FIG. 1, respectively earlier closing times of first decompression strokes 24, 28 and 32. The second closing 2S1 2S2 and 2S3 of the first decompression strokes 24, 28 and 32 takes place 30 degrees crank angle earlier; thus, for example, the first exhaust valve closes at about 210 degrees crank angle and the first closing timings 1S1, 1S2 and 1S3 of the second, unchanged decompression strokes 26, 30, 34 are temporally successive to the second closing 2S1 2S2 and 2S3 of the first decompression strokes 24, 28 and 32.

(33) In FIG. 3, a graph illustrating preferred ranges of the respective opening and closing times of the two successive decompression strokes is illustrated by way of the first exhaust valve. The following description is also readily applicable to the other cylinders and the other cylinder banks. The same lines and same points are provided in FIG. 3 with the same reference numerals as in FIG. 1 and FIG. 2. In the diagram of FIG. 2 the unchanged curve 14 of FIG. 1, is plotted. Furthermore, in FIG. 3 two curves 16 (solid line) and 16 (dashed line) of the first exhaust valve are shown, which indicate, by curve 16, the earliest possible opening times 1O1 at about 610 degrees of crank angle and 2O1 at about 250 degrees crank angle and closing times 1S1 at about 400 degrees crank angle and 2S1 at about 210 degrees crank angle. Accordingly, the curve 16 indicates the latest possible opening time points 1O1 at about 680 degrees crank angle and 2O1 at about 320 degrees crank angle and closing times 1S1 at about 680 degrees crank angle and 2S1 at about 320-degree crank angle. The resulting areas of possible first and second opening times and of first and second closing times are combined with one another.