• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a reciprocating piston engine (1), in particular having a variable compression ratio, at least one cylinder (2a, 2b, 2c, 2d) having a piston (3) and a connecting rod (4) connected to the piston (3) and a crankshaft (3). 5) of the reciprocating engine (1) is connected. The reciprocating piston engine (1) furthermore has a first sensor (6), which is arranged and arranged in a cylinder wall (7) of the at least one cylinder (2a, 2b, 2c, 2d), a relative movement between a piston skirt (8) of the Piston (3) and the cylinder wall (7) to detect. The invention also relates to a method (100) for diagnosing and / or controlling a type of reciprocating piston engine (1), in particular with variable compression ratio, and a system suitable for this purpose.
    公开号:AT518694A1
    申请号:T50499/2016
    申请日:2016-05-31
    公开日:2017-12-15
    发明作者:Siegfried Lösch Dr；Hüttner Thomas
    申请人:Avl List Gmbh；
    IPC主号:
    专利说明:

    Reciprocating piston engine and method and apparatus for diagnosis and / or control of a reciprocating engine
    The invention relates to a reciprocating engine, in particular with a variable compression ratio, which has at least one cylinder with a piston and a connecting rod which is connected to the piston and a crankshaft of the reciprocating engine. Furthermore, the invention relates to a method and a system for diagnosing and / or controlling such a reciprocating piston engine.
    Reciprocating engines with variable compression ratios are known from the prior art, the compression ratio ε, in this case especially in a technical sense, being understood as a ratio of the sum of (piston) volume Vh and compression or residual volume Vk to the compression or residual volume Vk
    In this way, a functionality of the reciprocating engine can be improved, in particular adapted to different load ranges.
    Various systems for varying the compression ratio in reciprocating engines are known in the prior art, for example from WO 2015/0555582 A2, AT 512334 A1 or DE 10 2012 020999 A1.
    In reciprocating engines of this type, in particular reciprocating internal combustion engines, with variable compression ratio, a diagnosis and / or control is advantageous to determine and adjust the piston position, in particular with respect to different crankshaft angle and / or the currently set compression ratio.
    Document DE 20 2009 015 316 U1 relates to a device for determining the position of a piston in a cylinder of an internal combustion engine with a light source, a light guide provided between light source and combustion chamber, and a light detector for light beams reflected from the piston head, wherein for the light beam to be introduced into the internal combustion engine and for the light beam reflected from the piston crown and to be supplied to the light detector separate optical fibers are provided, wherein the optical fibers connect to an image guide, which is used with its Hauptab-beam direction in the direction of the piston head pointing in a cylinder head of the internal combustion engine.
    The publication DE 10 2009 013 323 A1 relates to a method for automatically determining a current compression ratio of a reciprocating piston engine in operation, which has a variable compression volume, with at least one cylinder in which a piston is guided, which is connected via a connecting rod to the crankshaft, wherein the connecting rod is articulated to a crank of the crankshaft, the method comprising the steps of: a) triggering a signal at a time when the piston is approximately in the region of the bottom dead center, wherein the crankshaft assumes a defined rotational position, b Synchronous detection of the position of the piston by a measuring sensor and c) Determination of the compression ratio based on previously known and determined data.
    WO 2016/016187 A1 relates to a method for carrying out an on-board diagnosis in a reciprocating internal combustion engine with an adjustable compression ratio at top dead center (TDC), preferably by setting the effective length of a connecting rod, using the on-board diagnosis, to check the compression ratio of a cylinder.
    It is an object of the present invention to improve a reciprocating engine and its operation. In particular, it is an object of the invention to better determine and / or adjust the piston position and / or the compression ratio.
    This object is achieved by a reciprocating engine and a method or system according to the independent claims. Advantageous embodiments are the subject of the dependent claims. The teaching of the claims is expressly made a part of the description.
    In a first aspect of the present invention, a reciprocating engine, in particular with variable compression ratio, at least one cylinder with a piston and a connecting rod, which is connected to the piston and a crankshaft of the reciprocating engine, on. Preferably, the reciprocating engine further comprises a first sensor which is arranged in a cylinder wall of the at least one cylinder and adapted to detect a relative movement between a piston skirt of the piston and the cylinder wall.
    According to a second aspect of the invention, a method for diagnosis and / or control or a reciprocating piston engine, in particular with variable compression ratio, which has at least one cylinder with a piston and a connecting rod, which is connected to the piston and a crankshaft, the following steps :
    Determining a movement parameter of the piston of the reciprocating engine by means of a relative movement between a piston skirt of the piston and a cylinder wall; and determining a piston position parameter and / or a piston speed parameter based on the motion parameter.
    According to a third aspect of the invention is a system for diagnosis and / or control of a reciprocating engine, in particular with variable compression ratio, which has at least one cylinder with a piston and a connecting rod, which is connected to the piston and a crankshaft, for performing a method according to the invention and / or comprises: - means for determining a movement parameter of at least one piston of the reciprocating engine by means of a relative movement between a piston skirt of the piston and a cylinder wall; and means for determining a piston position parameter and / or a piston speed parameter based on the motion parameter.
    The invention is particularly based on the approach that from a movement of the piston, which can be determined by the determination of different piston positions, or one or more positions of the piston itself and other information, such as the piston speed and / or the respective present crankshaft angle, a Compression ratio of a reciprocating engine can be calculated. Furthermore, the invention is based on the finding that from a movement of the piston skirt relative to the cylinder wall, which can be detected by a sensor in the cylinder wall, a position of the piston can be detected and / or derived or calculated at one or more points in time.
    The reciprocating engine is in one embodiment a reciprocating internal combustion engine, in particular a charged or uncharged two- or four-stroke, in particular gasoline or diesel engine, in particular a motor vehicle, in particular a passenger car.
    In one embodiment, the compression ratio of one or more, in particular all cylinders of the reciprocating engine, in particular individually or uniformly, in particular jointly, adjustable, in particular reversible between a minimum and a maximum compression ratio. In order to change the compression ratio, in particular the length of the connecting rod can be adjusted.
    The invention makes use of the fact that a piston skirt of the piston sweeps or passes over different locations of the cylinder wall depending on the length of the connecting rod at different times and / or for different lengths of time. The distance of the piston skirt from the cylinder wall or the presence of the piston skirt at certain points of the cylinder wall, however, can be reliably determined by a number of known from the prior art sensors.
    A cylinder wall according to the invention is the lateral boundary of the cylinder with which a piston cooperates to limit a working space, in particular combustion chamber, of a reciprocating piston engine.
    A piston according to the invention is that movable member of the reciprocating engine, which forms a closed cavity together with the surrounding housing, in particular with the cylinder wall and a cylinder head, the volume of which changes by the movement of the piston. In particular, a piston has a piston head, which is in contact with the one working chamber, a piston skirt, which extends along the cylinder wall, and a piston pin with its bearing, which connects the piston with the connecting rod.
    An inductive sensor according to the invention is a sensor which operates on the induction principle. For this purpose, in particular a coil (winding), a magnet, a constant or variable magnetic field and possibly a movement is required.
    In an advantageous embodiment of the reciprocating piston engine according to the invention, this has a second sensor, wherein the first sensor is arranged in such a way to detect the relative movement with respect to a top dead center (TDC) of the piston and the second sensor is arranged in such a way to detect the relative movement in the region of a bottom dead center (UT) of the piston. The provision of two sensors each at the top and bottom of the piston makes it possible to determine a possible elasticity in a variable compression ratio adjusting device, for example an elasticity of a hydraulically adjustable connecting rod.
    In a further advantageous embodiment of the reciprocating piston engine according to the invention, the piston has an electrically conductive and / or ferromagnetic material and the first sensor and / or the second sensor is an inductive sensor, in particular an eddy current sensor, or an optical sensor.
    In a further advantageous embodiment of the reciprocating piston engine according to the invention, the first sensor and / or the second sensor are / is arranged in such a way that the piston skirt completely passes over it during the relative movement. If the sensor in the cylinder wall during the movement of the piston completely run over by this, can the top and / or edge of the piston, that is, the respective upper and / or lower end of the piston skirt determine very reliable.
    In a further advantageous embodiment of the reciprocating piston engine according to the invention, this has a variable compression ratio and the first sensor is arranged in such a way that the piston skirt completely overrun only at at least substantially maximum compression ratio and / or the second sensor is arranged in such a way that the piston skirt completely overruns this only at a substantially minimum compression ratio. By this arrangement, the respective maximum deflections of the piston can be determined very reliable because when they are reached, only the respective sensor at top dead center or bottom dead center is not covered by the piston skirt.
    In a further advantageous embodiment of the reciprocating piston engine according to the invention, the first sensor and / or the second sensor are / is arranged in such a way that piston rings of the piston do not run over the first sensor and / or the second sensor during the relative movement.
    The features and advantages explained above in relation to the first aspect of the invention apply correspondingly to the second and third aspects of the invention and vice versa.
    In an advantageous embodiment of the method according to the invention, the determination of a piston position parameter comprises determining a first minimum value of the motion parameter and a second maximum value (Uok) of the motion parameter of the movement of the piston. Prior to determining the minimum and maximum values, the motion parameter is preferably filtered to remove disturbances introduced by the piston rings, for example, from the course of the parameter. The maximum value and the minimum value then preferably represent absolute minima or maxima with respect to the motion parameter which is generated at a sensor by the movement of the piston.
    In an advantageous embodiment, the inventive method further comprises the following steps:
    Detecting a rotational position parameter of a crankshaft of the reciprocating engine; and determining a crankshaft angle parameter based on the rotational position parameter.
    A rotational position parameter in the sense of this advantageous embodiment is preferably determined using an incremental encoder on the crankshaft.
    Accordingly, in an advantageous embodiment, the system comprises: - means for detecting a rotational position parameter of a crankshaft of the reciprocating engine; and means for determining a crankshaft angle parameter based on the rotational position parameter.
    In a further advantageous embodiment, the method according to the invention also has one of the following working steps: determining a compression ratio parameter based on the piston position parameter and / or the piston speed parameter, or determining a compression ratio parameter based on the piston position parameter and the crankshaft angle parameter.
    Accordingly, in an advantageous embodiment, the system comprises: means for determining a compression ratio parameter based on the piston position parameter and / or the piston speed parameter, or means for determining a compression ratio parameter based on the piston position Parameters and the crankshaft angle parameter.
    In a further advantageous embodiment of the method according to the invention, determining the piston position parameter comprises determining a first value of the motion parameter at a top dead center and / or second value of the motion parameter at a bottom dead center of the movement of the piston, wherein the method of further comprising the following step: - determining a compression ratio parameter based on the first value and / or the second value and the piston position parameter.
    Accordingly, in an advantageous embodiment, the system comprises means for determining a compression ratio parameter based on the first value and / or the second value and the piston position parameter.
    In a further advantageous embodiment, the method according to the invention furthermore has the following working steps: determining a value of a compression ratio on the basis of the first value of top dead center and / or the first value of bottom dead center.
    From the values of the top dead center and the bottom dead center values, the applied compression ratio of the reciprocating piston engine is obtained directly.
    Accordingly, in an advantageous embodiment, the system comprises means for determining a compression ratio parameter based on the first value and / or the second value and the piston position parameter.
    In a further advantageous embodiment of the method according to the invention, the determination of a piston position parameter further comprises the following steps: - Adjusting a target compression ratio of at least a first cylinder of the reciprocating engine from a first, in particular extremal, value to a second, in particular extremal, value; Determining a first value of the piston position parameter and / or a first value of the crankshaft angle parameter for the first value of the target compression ratio; and determining a second value of the piston position parameter and / or a second value of the crankshaft angle parameter for the second value of the target compression ratio, wherein determining a value of the compression ratio parameter based on the first and second values of the piston position parameter and / or the crankshaft angle parameter takes place.
    Accordingly, in an advantageous embodiment, the system comprises: means for adjusting a nominal compression ratio of at least one first cylinder of the reciprocating engine from a first, in particular extremal, value to a second, in particular extremal, value; - means for determining a first value of the piston position parameter and / or a first value of the crankshaft angle parameter for the first value of the target compression ratio; and means for determining a second value of the piston position parameter and / or a second value of the crankshaft angle parameter for the second value of the target compression ratio.
    In a further advantageous embodiment of the method according to the invention, the adjustment of a desired compression ratio has the working step: changing a nominal length of a connecting rod of the at least one first cylinder of the reciprocating piston engine.
    Accordingly, in an advantageous embodiment, the system comprises: means for changing a desired length of a connecting rod of the at least one first cylinder of the reciprocating piston engine.
    In a further advantageous embodiment, the method according to the invention also has the following working steps: detecting an inductive and / or optical signal which is influenced by the relative movement between the piston skirt of the piston and the cylinder wall; and - determining the motion parameter based on the inductive and / or optical signal.
    In particular, inductive and / or optical signals are particularly well suited to determine the relative movement of the piston skirt relative to the cylinder wall.
    Accordingly, in an advantageous embodiment, the system comprises: means for detecting an inductive and / or optical signal which is influenced by the relative movement between the piston skirt of the piston and the cylinder wall; and means for determining the motion parameter based on the inductive and / or optical signal.
    In a further advantageous embodiment of the method according to the invention, a value of the motion parameter depends on, in particular the shortest, distance between the piston skirt and a measuring point or a speed of the relative movement.
    In a further advantageous embodiment of the method according to the invention, the movement parameter is an electrical voltage which is generated by the inductive and / or optical signal.
    In a further advantageous embodiment of the method according to the invention, the inductive and / or optical signal is influenced in particular by means of the lower end and / or the upper end of the piston skirt.
    In a further advantageous embodiment of the method according to the invention, the speed parameter additionally takes into account a distance of the piston from the cylinder wall at a respective measurement time. If the velocity of the piston is detected via an induction in the inductive sensor by a piston movement, then the shape of the piston skirt and the distance of the piston skirt from the cylinder wall should be considered at the same time in order to calculate the exact speed values.
    In a further advantageous embodiment of the method according to the invention, the piston position parameter is determined by evaluating a profile of the motion parameter as a function of time, in particular by evaluating edges of the profile. Such a course can be seen in particular at what time and how often a piston skirt has moved over the sensor.
    In a further advantageous embodiment of the method according to the invention, the detected inductive and / or optical signal is filtered and the motion parameter is determined on the basis of the filtered inductive and / or optical signal.
    In a further advantageous embodiment of the method according to the invention, the motion parameter is determined exclusively for at least one predetermined crank angle range.
    In a further advantageous embodiment of the method according to the invention, the at least one predetermined crank angle range has an upper and / or lower dead center of at least one, in particular of the first, cylinder of the reciprocating engine and / or extends over at least 2 ° and / or over at most 135 °. Additionally or alternatively, one or the predetermined crankshaft angle range in one embodiment, in particular in each case, extends over at least 2 °, in particular over at least 5 °, in particular over at least 10 °, and / or at most 135 °, in particular at most 90 °, in particular at most 45 °.
    In a further advantageous embodiment of the method according to the invention, the motion parameter is determined on the basis of at least one mean and / or extremal value.
    In a further advantageous embodiment of the method according to the invention, a signal, in particular a diagnostic and / or control signal based on the motion parameter is output, in particular if the motion parameter meets a predetermined condition, in particular a predetermined upper limit and / or lower Limit value and / or lies outside of a predetermined range. This can be reacted to a detection of a faulty compression ratio advantageous.
    In a further advantageous embodiment of the method according to the invention, the first and / or second movement parameter is / are determined on the basis of or as a function of at least one difference between two middle and / or extreme, in particular maximum and / or minimum values. Values that determines movement and can specify this particular.
    A means in the sense of the present invention may be designed in terms of hardware and / or software, in particular a data or signal-connected, preferably digital, processing, in particular microprocessor unit (CPU) and / or a memory and / or bus system or multiple programs or program modules. The CPU may be configured to execute instructions implemented as a program stored in a memory system, to capture input signals from a data bus, and / or to output signals to a data bus. A storage system may comprise one or more, in particular different, storage media, in particular optical, magnetic, solid state and / or other non-volatile media. The program may be such that it is capable of embodying or executing the methods described herein so that the CPU may perform the steps of such methods and, in particular, control and / or monitor a reciprocating engine.
    In the present case, the term control also means, in particular, the output of control signals on the basis of a comparison with detected actual values, that is to say a regulation.
    In an advantageous embodiment of the method according to the invention, one or more, in particular all, working steps of the method are carried out completely or partially automated, in particular by the system or its means.
    Further advantageous developments of the present invention will become apparent from the following description of preferred embodiments. To show this, at least partially schematized:
    Figure 1 shows a first cross section of a first embodiment of a reciprocating engine according to the first aspect of the invention;
    FIG. 2 shows an enlarged detail of the area around a piston of the first exemplary embodiment of a reciprocating piston engine according to FIG. 1;
    FIG. 3 shows an enlarged section around a cylinder of a second embodiment of a reciprocating piston engine according to the invention;
    FIG. 4 shows an enlarged detail in the region around sensors of a reciprocating piston engine according to the invention according to FIGS. 1 and 2;
    Figure 5 is a diagram of a curve of an output parameter of an upper sensor of the first embodiment of the reciprocating piston engine according to the invention according to Figures 1 and 2;
    Figure 1 is a diagram of a course of an output parameter of a lower sensor of the first embodiment of the reciprocating piston engine according to the invention according to Figures 1 and 2;
    FIG. 7 shows a diagram of a profile of an output parameter of an upper sensor of the second exemplary embodiment of a reciprocating piston engine according to the invention according to FIG. 3;
    FIG. 8 shows a diagram of an evaluation of the output parameter according to FIG. 7; and
    9 shows a flowchart of an exemplary embodiment of a method for diagnosing and / or controlling a reciprocating piston engine according to the second aspect of the invention.
    Figure 1 shows a part of a motor vehicle with a reciprocating internal combustion engine 1 with a variable compression ratio and a system for diagnosing the reciprocating piston engine 1 according to an embodiment of the present invention.
    The reciprocating piston engine 1 has a crankshaft 5 and a plurality of cylinders 2a, 2b, 2c, 2d, in which pistons alternately compress a fuel-air mixture (see cylinder 2a), are driven by combustion of the mixture (cf. Cylinder 2b), air or mixture suck in (see cylinder 2c) and expel (see cylinder 2d) and this are coupled via connecting rod 4 with the crankshaft 5.
    The length of the connecting rod 4 and thus the compression ratio of the cylinder 2 a, 2 b, 2 c, 2 d and the reciprocating internal combustion engine 1 is adjustable by an engine ECU 15, as indicated in phantom in Fig. 1.
    The ECU 15 detects by means of a trigger wheel 14 a rotational position of the crankshaft 5 as a rotational position parameter and determines therefrom in particular values of a crankshaft angle parameter γ, for example γι, ι, 72,1,73,1, Yu.
    FIG. 2 shows one of the cylinders 2a, 2b, 2c, 2d of the reciprocating internal combustion engine 1 according to FIG. 1 at top dead center OT, in which the piston 3 is in the next possible position on the cylinder head. The combustion chamber (not shown) on the cylinder head is limited in this case by the top of the piston 3 and by the cylinder walls 7 downwards. The piston skirt 8 serves to guide the piston 3 in the cylinder 2a, 2b, 2c, 2d and cooperates with the cylinder wall 7, which is cylindrical in the illustrated embodiment. In the region of the piston skirt 8 and sealing rings are arranged which seal a remaining gap between the piston skirt 8 and the cylinder wall 7.
    In the cylinder wall 7, in particular perpendicular to the main axis of the cylinder 2 a, 2 b, 2 c, 2 d, openings or measuring points 10, 11 are introduced. By means of these openings 10, 11, at least one sensor, in the embodiment shown a first sensor 6 and a second sensor 9, determine whether the piston skirt 8 is at the height of the first sensor 6 and / or the second sensor 9 and preferably also whether the piston 3 is in the vicinity of these sensors 6, 9.
    The sensors 6, 9 are preferably inductive sensors, in particular eddy-current sensors, in the magnetic field of which the piston 3, which comprises or consists of an electrically conductive and / or ferromagnetic material, depends on the distance from the sensors 6, 9 causes a change.
    In Fig. 2, the lower edge 12 of the piston skirt 8 is spaced at a distance d1 from the upper, first sensor 6. In this case, the magnetic field of the first eddy current sensor 6 is preferably no longer influenced by the piston 3.
    The resulting by a movement of the piston 3 change in the field of the sensors 6, 9 can be output, for example as a voltage signal U. Such a voltage signal can subsequently be used as a movement parameter in the sense of the invention.
    Moves the piston 3 during rotation of the crankshaft 5 by the action of the connecting rod 4 in the position of the so-called bottom dead center, the maximum remote position of the piston 3 from the cylinder head (not shown), so in the illustrated embodiment, the piston 3 and upper edge 13 of the piston 3 from the second eddy current sensor 9 and the associated opening 11 in the cylinder wall 7 also spaced at a distance d2. Also in this position, the piston 3 preferably has no influence on the field of the second eddy current sensor. 9
    FIG. 3 shows a further, second exemplary embodiment of a reciprocating internal combustion engine 1 according to the invention. The piston 3 is shown both at top dead center OT and as piston 3 'at bottom dead center UT. Fig. 3 additionally shows the cylinder head 16, which closes a combustion chamber 17 with the piston 3.
    In contrast to the exemplary embodiment of FIG. 3, in the exemplary embodiment shown here, the first eddy current sensor 6 is arranged such that the lower edge 12 of the piston 3 no longer has the first eddy current sensor 6 or the associated opening in the cylinder wall 7 at top dead center OT covered.
    Furthermore, in contrast to FIG. 2, the lower eddy current sensor 9 is arranged in such a way that it or the associated opening in the piston wall 7 is covered by the piston 3 'at the bottom dead center.
    FIG. 4 shows by way of example how the first eddy current sensor 6 and the second eddy current sensor 9 are arranged in a cylinder 2 a, 2 b, 2 c, 2 d. In particular, the sensors 6, 9 are sealed with respect to the interior of the cylinder to the cylinder wall 7 and against a cooling channel with seals.
    An inventive system for diagnosis and / or control of a reciprocating internal combustion engine 1 is preferably formed by the first eddy current sensor 6 and, if present, by the second eddy current sensor 9 and a control or evaluation unit 15. Further preferably, such a system also has a device 14 for determining the crankshaft angle γ, in particular a transmitter wheel / trigger wheel or an incremental encoder.
    Such a system is generally suitable for determining piston positions. Thus, on the one hand it can be determined whether the piston 3 is in the region of the first eddy current sensor 6 and / or the second eddy current sensor 9 (Umk) or whether it is outside the range of the eddy current sensors 6, 9 (Uok). If the field of the first eddy current sensor 6 and / or of the second eddy current sensor 9 furthermore has a ball characteristic, then the piston 3 can still be perceived by the respective eddy current sensor 6, 9 at a certain distance dmax, the signal strength depending on the distance d, is in particular proportional to the distance. In addition, the piston position in those positions of the piston 3, in which none of the eddy current sensors 6, 9 can detect the piston 3, via a determination of a piston position parameter Umk, Uok and a piston speed parameter Ü and a subsequent interpolation based on the speed Ü done. For example, the speed of passing the upper edge 12 and the lower edge 13 on the eddy current sensors 6, 9 can be determined. Furthermore, a determination of the speed Ü can be determined via a strength of the field induced or changed by the piston 3 at the eddy current sensors 6, 9.
    In addition, the piston skirt 8 is preferably not completely parallel to the cylinder wall 7, but has different distances from the cylinder wall 7 over its course. Depending on the distance between a portion of the piston skirt 8 covering the eddy current sensors 6, 9 and the eddy current sensors 6, 9, the field of the eddy current sensors 6, 9 is influenced to different degrees. These values of the influence of the respective field can also make a statement about the piston position, because the piston position is reflected in a corresponding value of the piston position parameter Umk, Uok.
    In particular, however, the method 100 according to the invention and the system according to the invention are also suitable for, so-called on-board diagnostics or control of a reciprocating internal combustion engine 1 with a variable compression ratio ε. With the system and method according to the invention can be closed in this case on the respective present compression ratios ε.
    The variable compression ratio can be achieved, in particular, by changing the connecting rod length, wherein in relation to the exemplary embodiments, differentiation between extended connecting rod (index a) and retracted connecting rod (index e) is simplified.
    For the purposes of the present description, the piston position parameter is represented as a digital value with the values Umk, that is to say with pistons at the level of a respective eddy current sensor 6, 9 or Uok, ie without pistons at the level of the eddy current sensor 6, 9 As can be seen from the preceding description and also from the diagrams shown below with profiles of the movement parameter U of the piston 3, other values of the piston position parameter can also be defined as a function of the movement parameter U, which then each have a specific value Position of the piston 3 can be assigned.
    Figure 5 shows a diagram with curves of voltage signals Ua and Ue, which represent a movement parameter of the piston 3 of a reciprocating piston engine 1 according to the first embodiment of Figures 1 and 2.
    The method according to the invention will be explained below with reference to the diagrams of FIGS. 5 to 8 and with reference to the flowchart of FIG. 9.
    First, an inductive or possibly also optical signal, which is triggered or influenced by the relative movement between the piston skirt 8 of the piston 3 and the cylinder wall 7, is detected. In particular, this signal is filtered numerically and a motion parameter U is determined therefrom 101. A movement parameter for a connecting rod 4 in the extended state is designated Ua with FIGS. 5 and 6; a movement parameter for a connecting rod in the retracted state is shown here denoted by Ue.
    The movement parameter U based on the signal generated by the first eddy current sensor 6 and / or the second eddy current sensor 9, which is indicated by a voltage in the diagram, increases with increasing distance d of the piston 3 from the respective sensor 9. The lowest voltage value of the movement parameter is thus generated when the piston 3 is in the position in which the piston skirt 8 is closest to the respective sensor 6, 9.
    The curves of the motion parameters Ua, Ue shown in FIG. 5 represent parameters derived from the real measuring signals. The two curves Ua, Ue each associated angular courses indicate a theoretical ideal course of the motion parameter, respectively in the extended and retracted state. Accordingly, Uok indicates the value of the motion parameter when the piston 3 is not in the range of the first eddy current sensor 6 and UoK.reai is the corresponding real value of the motion parameter derived from the measurement signal. Accordingly, the motion parameter value Umk or UMK, reai indicates the theoretical or real motion parameter value when the piston is in the region of the first eddy current sensor 6. It can be seen from the movement parameters Ua, Ue that the piston 3 enters the area dmax of the first eddy current sensor 6 at a crankshaft angle γ of approximately 250 °, and therefore the movement parameter leaves the value UoK.reai. The subsequent tines a crankshaft angle γ of about 270 ° represent signal interference, which are caused by the piston rings at the upper end of the piston 3. The closest distance d between the piston skirt 8 and the first eddy current sensor 6 is recorded at a crankshaft angle of approximately γ = 310 °, which complements the movement parameter value UMK, reai. Shortly thereafter, the lower edge 12 of the piston skirt 8 passes over the first sensor 6 and the movement parameter Ua rises again to the value UoK.reai, ie, the piston skirt 8 is no longer in the range dmax of the first eddy current sensor 6. At a crankshaft angle of γ = 360 °, the piston 3 reaches the position as shown in Fig. 2. Thereafter, the piston 3 moves back down and sweeps first with the lower edge 12 of the piston skirt 8, the first sensor 6, whereupon the movement parameter Ua again falls to UMK, reai and then mirror symmetry to the previously described upward movement of the piston 3, an increase in the Movement parameter value Ua has until again the piston crown rings initiate a disturbance of the measurement signal and then the upper edge 13 of the piston flank 8 again sweeps over the upper sensor 6, whereupon the motion parameter value remains at UoK.reai.
    A course with a corresponding characteristic also results for the movement parameter Ue with retracted connecting rod.
    As shown in FIG. 5, in the motion parameter Ue, the respective timings, particularly with respect to the crankshaft angle γ at which the piston skirt 8 passes over the first eddy current sensor 6, are different from the values in the motion parameter Ua. This is due to the fact that with shortened connecting rod and ascending movement of the piston 3, the first sensor 6 is reached later, but in the downward movement of the piston 3 then correspondingly reached earlier. The corresponding values Uok, Umk are evaluated as piston position parameters, that is, as characteristic values for determining the piston position with respect to the sensors 6, 9 and the absolute piston position 102.
    The characteristic values of a crankshaft angle parameter 103-2, which is derived in particular from the rotational position of the crankshaft 103-1, are respectively plotted on the ordinate of FIG.
    In particular, γχ, 2 is that crankshaft angle parameter value at which the lower edge 12 of the piston skirt 8 sweeps over the first eddy current sensor 6 in the upward movement of the piston 3, and γχ, 3 is respectively that crankshaft angle parameter value at which the lower edge 12 of the piston skirt 8 sweeps over the upper sensor 6 again during the downward movement of the piston 3. From these two crankshaft angle parameter values, a compression ratio parameter value öa and öe can be determined 104b respectively in the extended state and in the retracted state.
    Alternatively to the crankshaft angle γ, the respective compression ratio parameter can be determined by means of the piston position parameter U and a piston speed parameter Ü derived therefrom 104a. In this case, it is used that with known length of the piston skirt 8 and a known speed of the piston 3 during the up and down movement and the time period between a first sweeping of the first eddy current sensor 6 during the upward movement of the piston 3 and a second sweeping of the first eddy current sensor 6 during a downward movement of the piston 3 can be determined, how far the piston 3 has moved up to the cylinder head.
    The diagram of FIG. 6 shows the course of a movement parameter for an extended connecting rod Ua and a retracted connecting rod Ue to two lower, second eddy current sensor 9 according to the first embodiment of Figures 1 and 2.
    The piston position parameter and its parameter values as well as the crankshaft angle parameter can be determined according to FIG. 5. Since the piston 3 moves farther from the second sensor 9 with the connecting rod 4 in the downward movement of the piston 3 than when the connecting rod 4 is extended, the compression ratio parameter value 5e is greater than the corresponding compression ratio parameter 5a with the connecting rod 4 extended.
    Fig. 7 shows the course of the movement parameter U at the upper, first eddy current sensor 6 of the second embodiment of a reciprocating internal combustion engine 1 according to the invention as shown in FIG. 3. Again, the course of the movement parameter U, as in Fig. 5, the Change of a field signal at the upper, first eddy current sensor 6 at. Also in Fig. 7, the movement parameter value drops abruptly, also here show the characteristic noise of the piston rings while the piston 3, the first eddy current sensor 6 passes. Thereafter, the movement parameter U falls and reaches the piston position parameter value ÜMK.reai, which indicates that the piston skirt 8 completely covers the first eddy current sensor 6. At a crankshaft angle ya, 2 of about 340 °, the movement parameter U increases, which indicates that the piston 3 or the piston skirt 8 has completely overrun the upper eddy current sensor 6.
    In contrast to the course of the motion sensor parameter Ua, Ue in FIG. 5, the motion parameter U in FIG. 7 does not rise to its initial value UoK.reai, which is assigned to a piston position in which the piston skirt 8 is the first Eddy current sensor 6 is not covered and the first eddy current sensor 6 no longer detects the piston 3 (ie, d> dmax). Instead, the motion parameter U remains below the position parameter value UoK.reai. This means that the field of the upper eddy current sensor 6 is still influenced by the piston 3. This is due to the fact that the upper eddy current sensor, as shown in Fig. 3, at the top dead center OT of the piston 3 is substantially closer to the lower edge 12 of the piston skirt 8, as is the case for example in the first embodiment of FIG is (ie d <dmax) ·
    The voltage value at the point P at a crankshaft angle γ of about 360 ° depends on the distance d of the lower edge 12 of the piston skirt 8 from the first eddy current sensor 6, and is in particular proportional to this. The point P or its voltage value Uot therefore indicates a distance d of the lower edge 12 of the piston skirt 8 from the first eddy current sensor 6. From the position of the point P, therefore, the piston position can be derived. This is therefore also a piston position parameter in the context of the invention.
    From the respective value Uot of this piston position parameter, a compression ratio parameter is preferably determined 104c. For this purpose, the value Uot is subtracted from the value Uok or Umk of the piston position parameter, so that preferably the values of the compression ratio parameter AUi or AU2 result. From the magnitude of the values AUi and AU2, the compression ratio of a reciprocating internal combustion engine 1 can be directly deduced.
    This is shown in the diagram of FIG. 8. There, the course of the compression ratio parameter AUi over a number of thermodynamic cycles of a reciprocating internal combustion engine 1 is plotted. Achieved AUi a relatively high value of about 3 volts, this means that the lower edge 12 of the piston 3 is relatively far away from the upper eddy current sensor 6, the connecting rod is therefore extended and a relative compression ratio ε in the respective cylinder 2a, 2b , 2c, 2d reached. In this area, the compression ratio parameter in Fig. 8 is therefore designated as AUi, a. Correspondingly, the cylinder pressures at different crankshaft angles γ are also relatively high, and the pressure of the control pressure Psteueroei, which controls the extendable connecting rod 4, is low. From about n = 120 thermodynamic cycles, the pressure of the control pressure Psteueroei changes its value and increases. Accordingly, the connecting rod 4 enters and the determined from the piston position parameters compression ratio parameter AUi decreases. Therefore, the compression parameter in this area is denoted by AUi, e. By means of the respective value of the compression ratio parameter and / or the change in the cylinder pressure Pzyi, it can be determined from this diagram whether the compression ratio has led to the desired direction and in particular to the desired value by a change in the control pressure Pregoei.
    On the basis of the respective compression ratio parameter AUi, AU2can be determined at least qualitatively how the compression ratio in the pistons 2a, 2b, 2c, 2d of a reciprocating internal combustion engine 1 has changed. If the relationship between the respective compression ratio parameter AUi, AU2 and the compression ratio ε is defined by an assignment rule, in particular by a function or by a field, or stored in a data memory, the exact value of a compression ratio ε can also be determined in a further working step 105 Basis of the respective compression ratio parameter Δ, Ai, Au2 are determined.
    For functional testing or diagnosis of the variability of the compression ratio ε of a reciprocating internal combustion engine 1, the method can also provide that a change in the compression ratio ε actively initiate to determine by means of the respective compression ratio parameters δ, AUi, AU2 at different times, whether a change the compression ratio has occurred.
    For this purpose, a nominal compression ratio of at least one first cylinder 2a, 2b, 2c, 2d of the reciprocating internal combustion engine 1 is preferably set from a first, in particular extremal, value ε3 to a second, in particular extreme, value εε104. Thereafter, a first value Uot.i, Uut.i of the movement parameter U at a top dead center OT and / or a bottom dead center UT and / or the crankshaft angle Pa-parameter γι, ι, γ2, ι, γ3, ι, γ4, ι for the first value of the target compression ratio ε3 and a second value Uot, 2, Uut, 2 of the motion parameter U at a top dead center OT and / or a bottom dead center UT or the crankshaft angle parameter γι, 2, Y2 .2, Y3.2, Y4,2 for the second value of the target compression ratio εε.
    The determination of a value of a relative compression ratio parameter 104c is then based on the first and second values of the piston position parameter U.
    Preferably, the control device 15 or the method 100 checks whether the respectively obtained value of the compression ratio parameter δ, AUi, ΔΙΙ2 is outside a predetermined range, in particular falls below a predetermined minimum value, which should be at a determination of the compression ratio between the maximum and minimum value 106. If this is not the case or if the compression ratio parameter value is within the predetermined range (step 106: "N"), the controller 15 returns, or the method 100 is again returned to the operating step 101 to the method 100 perform again. Otherwise, or with too small a deviation between the compression ratio parameter value δ, AUi, ΔΙΙ2 for a maximum and a minimum target compression ratio or their differences (step 106: "Y"), the controller 15 enters in a step 107 corresponding diagnostic signal indicative of the operation of the reciprocating internal combustion engine 1 in an insufficient manner and then returns to step 101.
    Although exemplary embodiments are explained in the present description, it is pointed out that these exemplary embodiments are merely examples which are not intended to limit the scope of protection, the application and the structure in any way. Rather, the expert is given by the preceding description, a guide for the implementation of at least one exemplary embodiment, with various changes, in particular with regard to the function and arrangement of the described components, can be made without leaving the scope, as it turns out according to the claims in these equivalent combinations of features.
    LIST OF REFERENCES 1 reciprocating piston engine 2a, 2b, 2c, 2d cylinder 3 piston 4 connecting rod 5 crankshaft 6 first sensor 7 cylinder wall 8 piston skirt 9 second sensor 10,11 measuring point / opening 12 lower edge 13 upper edge 14 rotation angle encoder 15 control unit U movement parameters
    Umk, Uok, P piston position parameter Ü piston speed parameter γ crankshaft angle parameter γι, j2, j3, Y4 characteristic value of the crankshaft angle parameter 8a, 8e, 8 compression ratio δ, AUi, AU2 compression ratio parameter d distance
    权利要求:
    Claims (24)
    [1]
    claims
    A reciprocating piston engine (1), in particular with a variable compression ratio, comprising: at least one cylinder (2a, 2b, 2c, 2d) with a piston (3) and a connecting rod (4) connected to the piston (3) and a crankshaft (5) of the reciprocating piston engine (1), a first sensor (6) which is arranged and arranged in a cylinder wall (7) of the at least one cylinder (2a, 2b, 2c, 2d), a relative movement between a piston skirt (8 ) of the piston and the cylinder wall (7).
    [2]
    2. Reciprocating piston engine (1) according to claim 1, having a second sensor (9), wherein the first sensor (6) is arranged in such a way to detect the relative movement in the region of a top dead center (TDC) of the piston (3) and the second sensor (9) is arranged in such a way to detect the relative movement in the region of a bottom dead center (TDC) of the piston (3).
    [3]
    3. Reciprocating piston engine (1) according to claim 1 or 2, wherein the piston (3) comprises an electrically conductive and / or ferromagnetic material and wherein the first sensor (6) and / or the second sensor (9) an inductive sensor, in particular an eddy current sensor , or is an optical sensor.
    [4]
    4. Reciprocating piston engine (1) according to one of the preceding claims, wherein the first sensor (5) and / or the second sensor (9) are arranged in such a way that the piston skirt (8) passes over it completely in the relative movement.
    [5]
    5. Reciprocating piston engine (1) according to one of the preceding claims with variable compression ratio, wherein the first sensor (6) and / or the second sensor (8) are arranged in such a way or is that the piston skirt (8) this only at least essentially completely exceeded the maximum compression ratio.
    [6]
    6. Reciprocating piston engine (1) according to one of the preceding claims, wherein the first sensor (6) and / or the second sensor (9) are arranged in such a way that piston rings of the piston (4), the sensors (6) in the Do not drive over relative movement.
    [7]
    7. Method (100) for diagnosing and / or controlling a reciprocating piston engine (1), in particular with a variable compression ratio, which has at least one cylinder (2a, 2b, 2c, 2d) with a piston (3) and a connecting rod (4), wherein the connecting rod is connected to the piston (3) and a crankshaft (5), wherein the method (100) comprises the following steps: determining (101) a movement parameter (U) of the piston (3) of the reciprocating piston engine (1) a relative movement between a piston skirt (8) of the piston (3) and a cylinder wall (7); and determining (102) a piston position parameter (Umk, Uok, Uot, Uut) and / or a piston speed parameter (Ü) based on the motion parameter.
    [8]
    8. The method of claim 7, wherein determining a piston position parameter comprises determining a first minimum value of the motion parameter and a second maximum value of the motion parameter ).
    [9]
    The method (100) according to claim 7 or 8, further comprising the steps of: detecting (103-1) a rotational position parameter of the crankshaft (5); and determining (103-2) a crank angle parameter (γ) based on the rotational position parameter.
    [10]
    The method (100) of any of claims 7 to 9, further comprising one of the following steps of: determining (104a) a compression ratio parameter (δ) based on the piston position parameter (Umk, Uok, Uot, Uut) and Piston speed parameter (i /); or determining (104b) a compression ratio parameter (δ) based on the piston position parameter (Umk, Uok) and the crankshaft angle parameter.
    [11]
    11. The method (100) of claim 7, wherein determining the piston position parameter (102) comprises determining a first value (Uot) of the movement parameter (U) at a top dead center (TDC) and / or or second value (Uut) of the motion parameter (U) at a bottom dead center (UT) of the movement of the piston (3); and wherein the method (100) further comprises the step of: determining (104c) a compression ratio parameter (AUi; ΔΙΙ2) based on the first value (Uot) and / or the second value (Uut) and the piston position parameter (Umk, Uok, P).
    [12]
    12. The method of claim 7, further comprising the steps of: determining a value of a compression ratio based on the compression ratio parameter (δ; AUi; AU2).
    [13]
    13. The method according to claim 7, wherein the determination of a piston position parameter further comprises the following steps: adjusting a desired compression ratio of at least one first cylinder (2a, 2b, 2c , 2d) of the reciprocating piston engine (1) from a first, in particular extremal, value (ea) to a second, in particular ext-remale, value (ee); Determining (102-2) a first value of the piston position parameter (Umk, i, Uok, i, Uot, ij Uut, i) and / or a first value (γι, ι; 72,1; 73,1; 74, i) the crankshaft angle parameter (7) for the first value of the target compression ratio (£ a); and determining (102-3) a second value of the piston position parameter (Umk, 2, Uok, 2, Uot, 2, Uut, 2) and / or a second value (71,2; 72,2: 73,2; 74,2) of the crankshaft angle parameter (7) for the second value of the target compression ratio (ee), wherein determining (104a, 104b, 104c) a value of the compression ratio parameter (δ; AUi; AU2) based on the first and second value of the piston position parameter and / or the crankshaft angle parameter.
    [14]
    14. The method (100) according to claim 13, wherein adjusting a target compression ratio (ε3, εθ) by changing a desired length of the connecting rod (4) of the at least one first cylinder (2a, 2b, 2c, 2d) of Reciprocating engine (1) takes place.
    [15]
    15. Method (100) according to claim 7, wherein the determination of the movement parameter (101) further comprises the following steps: detecting an inductive and / or optical signal which is generated by the relative movement between the piston skirt (8) of the piston (8). 3) and the cylinder wall (7) is influenced; and determining the motion parameter (U) based on the inductive and / or optical signal.
    [16]
    16. Method (100) according to one of claims 7 to 15, wherein a value of the movement parameter (U) from the, in particular shortest, distance (d) of the piston skirt (8) to a measuring point (10, 11) and / or a speed of relative movement depends.
    [17]
    A method (100) according to claim 15 or 16, wherein the motion parameter (U) is an electrical voltage generated by the inductive and / or optical signal.
    [18]
    18. Method (100) according to one of claims 15 to 17, wherein the inductive and / or optical signal is influenced by means of a lower end (12) and / or an upper end (13) of the piston skirt (8).
    [19]
    19. Method (100) according to one of claims 7 to 18, wherein the speed parameter (Ü) additionally takes into account a distance of the piston skirt (8) from the cylinder wall (7) at a respective measurement time.
    [20]
    20. Method (100) according to one of claims 7 to 19, wherein values of the piston position parameter (Umk, Uok) and / or values of the crankshaft angle parameter are evaluated by evaluating a profile of the motion parameter (U), in particular as a function from the time or the crankshaft angle, preferably by evaluating edges of the course, is determined.
    [21]
    21. The method according to claim 7, wherein the motion parameter is determined exclusively for at least one predetermined crank angle range.
    [22]
    22. Method (100) according to claim 21, wherein the at least one predetermined crank angle range (5e, 5a) has an upper and / or lower dead center (OT, UT) of at least one, in particular of the first, cylinder (2a, 2b, 2c, 2d). the reciprocating piston engine (1) and / or extends over at least 2 ° and / or at most 135 °.
    [23]
    23. Method (100) according to claim 7, further comprising the following operating step: outputting (107) a signal, in particular a diagnosis and / or control signal on the basis of the movement parameter (U), of the piston position parameter ( Umk, Uok), the piston speed parameter (¢ /), the compression ratio parameter (δ; AUi; ΔΙΙ2) and / or the compression ratio (ε), in particular if the respective parameter fulfills a predetermined condition.
    [24]
    24. System for diagnosis and / or control of a reciprocating engine (1), in particular with a variable compression ratio, which has at least one cylinder (2a, 2b, 2c, 2d) with a piston (3) and a connecting rod (4), which with the Piston (3) and a crankshaft (5) is connected, wherein the system (1) for implementing a method according to one of claims 7 to 23 is arranged and / or comprising means for determining a movement parameter of at least one piston of the reciprocating piston means a relative movement between a piston skirt of the piston and a cylinder wall; and means for determining a piston position parameter and / or a piston speed parameter based on the motion parameter.
    类似技术:
    公开号 | 公开日 | 专利标题
    DE19955250B4|2005-05-04|Method and device for monitoring the function of a variable cylinder compression
    DE102016115157A1|2017-02-23|Method and system for pre-ignition control
    EP3188947B1|2018-05-23|Method and controller for recognizing a combustion process in an internal combustion engine of a hybrid vehicle
    EP2929167B1|2016-10-26|Method for determining a cylinder pressure-crankshaft position assignment for an internal combustion engine
    DE102005012942A1|2006-09-28|Method and device for operating an internal combustion engine
    DE10001518B4|2008-11-13|Method for lubricating a cylinder in an internal combustion engine and a cylinder lubrication system and a connecting element
    WO2009132897A1|2009-11-05|Method for determining the rail pressure in a common rail system, and common rail injection system
    EP2122143B1|2012-05-02|Indicating arrangement and method for determining an engine parameter
    DE4215581B4|2004-05-06|System for controlling a solenoid-controlled fuel metering device
    EP0456244B1|1994-09-14|Test procedure for combustion engines during assembly
    DE4308541A1|1994-09-22|Method and device for controlling and / or regulating an actuator
    DE102007024823B4|2014-10-23|Method and device for determining a drive parameter for a fuel injector of an internal combustion engine
    AT518694B1|2019-08-15|Reciprocating piston engine and method and apparatus for diagnosis and / or control of a reciprocating engine
    DE102011009132B4|2017-03-02|Method for controlling an engine valve of an internal combustion engine
    AT520079B1|2019-01-15|Reciprocating piston engine and method and apparatus for diagnosis and / or control of a reciprocating engine
    DE10028885B4|2010-12-09|Method and device for detecting the combustion chamber pressure occurring in a combustion chamber of an internal combustion engine
    DE102017209112B4|2019-08-22|Method for determining the current compression ratio of an internal combustion engine during operation
    DE4408425A1|1994-12-22|Method and device for adjusting the angular position of a cam shaft
    DE102006015968B3|2007-11-08|Adaptation method and adaptation device of an injection system of an internal combustion engine
    AT518268B1|2017-09-15|Method and system for diagnosing and / or controlling a reciprocating engine with a variable compression ratio
    DE102014215657A1|2016-02-11|Method for interpretatively detecting a pre-ignition in a combustion chamber of an internal combustion engine
    EP1743093B1|2010-01-20|Process and device for regulating the course of combustion in an internal combustion engine
    DE102020207172B3|2021-07-01|Method for determining a camshaft position of an internal combustion engine
    DE2716822B2|1980-12-18|Method and device for determining the air throughput in a gasoline-fueled internal combustion engine
    DE102016011379A1|2018-03-22|Method for determining a valve timing for a gas exchange valve of an internal combustion engine
    同族专利:
    公开号 | 公开日
    WO2017207659A1|2017-12-07|
    US20190345872A1|2019-11-14|
    CN109563786A|2019-04-02|
    AT518694B1|2019-08-15|
    DE112017002746A5|2019-02-14|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE102005024046A1|2005-05-25|2006-11-30|Robert Bosch Gmbh|Internal combustion engine for vehicle, has cylinder hole that is partially interspersed by magnetic field and is surrounded by induction coil that is arranged in area of upper and lower slack points of piston|
    DE102005054627A1|2005-11-16|2007-05-24|Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr|Device for measurement of current position of lifting piston of lift piston machine, has sensor arranged in range of piston spray nozzle, which extends with position bottom dead center to free space|
    DE102006033062A1|2006-07-14|2008-01-17|Fev Motorentechnik Gmbh|Measurement of actual motor compression ratio, of the moment, has sensors at the crank and the piston to register a crank trigger angle together with a sensor signal evaluation unit|
    EP2194244A1|2008-12-02|2010-06-09|Wärtsilä Schweiz AG|Lubricating device and method for lubricating a baring surface of a cylinder wall|
    DE202012100653U1|2012-02-27|2013-05-28|Makita Corp.|Internal combustion engine with improved ignition timing and ignition timing control|
    JP3593282B2|1999-05-19|2004-11-24|本田技研工業株式会社|Sensor mounting structure for piston behavior analysis|
    KR100351998B1|2000-08-23|2002-09-11|현대자동차주식회사|Measurement apparatus for piston ring|
    PL1717015T3|2005-04-25|2017-06-30|Hermann Schwelling|Baling press with a Safety device for the movement of the press plate|
    CN104043656B|2013-03-14|2016-04-27|宝山钢铁股份有限公司|Static pressurize is utilized to test the method for dynamical roll gap hydraulic state|DE102018104292A1|2018-02-26|2019-08-29|Avl List Gmbh|Sensor device for a length-adjustable connecting rod|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50499/2016A|AT518694B1|2016-05-31|2016-05-31|Reciprocating piston engine and method and apparatus for diagnosis and / or control of a reciprocating engine|ATA50499/2016A| AT518694B1|2016-05-31|2016-05-31|Reciprocating piston engine and method and apparatus for diagnosis and / or control of a reciprocating engine|
    PCT/EP2017/063204| WO2017207659A1|2016-05-31|2017-05-31|Reciprocating piston machine and method and device for diagnosing and/or controlling a reciprocating piston machine|
    US16/306,019| US20190345872A1|2016-05-31|2017-05-31|Reciprocating piston machine and method and device for diagnosing and/or controlling a reciprocating piston machine|
    CN201780047419.4A| CN109563786A|2016-05-31|2017-05-31|Conventional engine and method and apparatus for being diagnosed and/or being controlled to conventional engine|
    DE112017002746.2T| DE112017002746A5|2016-05-31|2017-05-31|Reciprocating piston engine and method and apparatus for diagnosis and / or control of a reciprocating engine|
    [返回顶部]