METHOD AND APPARATUS FOR DETERMINING AIR MASS IN A CRANKCASE SCAVENGED TWO-STROKE ENGINE

Abstract: The mass of air M available for combustion within a cylinder 14 of a crankcase scavenged two-stroke engine 10 is obtained by estimating the mass of air M trapped within a crankcase chamber 18, prior to its transfer to the associated cylinder combustion chamber 40. The estimate for air mass is derived from the product of pressure P of the air in the crankcase chamber 18 and the crankcase chamber volume V at a selected engine cycle position during that portion of the engine cycle when the air is trapped and undergoes compression within the crankcase chamber 18 divided by a factor containing the trapped air temperature T at the selected engine cycle position.

Description: This invention relates to a method and apparatus for determining the mass of air within a crankcase chamber of a crankcase scavenged two-stroke engine. In a crankcase scavenged two-stroke engine, each cylinder has a separate crankcase chamber into which air is inducted during a portion of the engine operating cycle. The inducted air is trapped in the crankcase chamber and then compressed during a part of the engine cycle when the crankcase chamber is decreasing in volume and is then transferred to a combustion chamber where it is mixed with fuel for ignition. In order to control effectively the emission and performance characteristics of crankcase scavenged two-stroke engines, it is usually necessary to know the mass of air available at the time of combustion within a cylinder. Once such information is known, critical engine parameters, such as spark advance, fuelling requirements, and injector timing, can be adjusted to achieve the desired emission and performance objectives. Mass air-flow sensors are commercially available, and have been used with internal combustion engines in the past to provide the required information regarding the mass of air available for combustion. However, at the present time, mass-air flow sensors with sufficient accuracy are relatively expensive as compared to other sensors used for engine control. US-A-4,446,833 discloses a control arrangement for a fuel injection system of an internal combustion engine in which air is inducted into the combustion chamber from the engine crankcase chamber, comprising a pressure sensor for sensing the air pressure in the crankcase chamber at one or more predetermined points in an engine cycle and a control device for controlling the timing and amount of fuel discharged on the basis of the measured pressure and the engine position. EP-A-0,408,180 is a document falling within the state of the art under Article 54(3) EPC and discloses a method and apparatus for determining the mass of air transferred to a combustion chamber of a crankcase-scavenged two-stroke engine on the basis of the work done in compressing the air in the crankcase chamber between an initial crankcase volume and a final crankcase volume and of the change in the specific internal energy in the air between the initial crankcase volume and the final crankcase volume. During the calculations to obtain the mass of air, the Ideal Gas Law is used. Consequently, a need exists for an alternative technique for deriving an indication of the air mass available for combustion within crankcase scavenged two-stroke engines. According to an aspect of the present invention, there is provided a method of determining the mass of air within a crankcase chamber of a crankcase scavenged two-stroke engine characterised over the prior art by the features in the second portion of claim 1. According to another aspect of the present invention there is provided apparatus for determining the mass of air within a crankcase chamber of a crankcase scavenged two-stroke engine characterised over the prior art by the features in the second portion of claim 9. The present invention can provide a method and apparatus for determining the mass of air available for combustion within a cylinder of a crankcase scavenged two-stroke engine, with sufficient accuracy to enable proper engine control, and without requiring a mass air-flow sensor. In an embodiment, the mass of air available for combustion within a cylinder is obtained by estimating the mass of air trapped within a crankcase chamber, prior to its transfer to the associated cylinder combustion chamber. Advantageously, the mass of air available for combustion within the cylinder is obtained on the basis of indications of pressure, temperature, and the volume of air under compression within the crankcase chamber while the air is trapped. The estimate for air mass is preferably derived from the product of pressure of the air in the crankcase chamber and the crankcase chamber volume at a selected engine cycle position during that portion of the engine cycle when the air is trapped and undergoes compression within the crankcase chamber, divided by a factor containing the trapped air temperature at the selected engine cycle position. As a result, there is no need for a mass-air flow sensor in determining the air mass available for combustion within a cylinder. Preferably, the mass of air is estimated when the air is first trapped in the crankcase chamber so that the temperature of the trapped air is substantially the same as the crankcase intake air temperature which can be used as an approximation of the trapped air temperature. In an embodiment, the mass of air is estimated at more than one engine cycle position during compression of the trapped air and then averaged to provide a measure of the trapped air mass. The crankcase volume may be derived as a function of the engine cycle position at which the mass of trapped air is estimated. Preferably, the volume within a crankcase chamber at a given time is defined by the angular rotation of the engine crankshaft as measured by means already existing for the control of engine spark timing. As contemplated by a further embodiment, the temperature of air within the crankcase chamber at the engine cycle position at which the mass of trapped air is estimated, is derived as a function of the intake air temperature. Temperature sensors typically have long lag times relative to engine cycle time, and as a result, the measurement of intake air temperature is more accurate than the measurement of crankcase air temperature. Also, means for measuring intake air temperature already exists in conventional engine control systems. Consequently, by deriving crankcase air temperature as a function of air intake temperature, this embodiment typically does not require an additional temperature sensor. The pressure of air within the crankcase chamber is preferably derived from a conventional pressure sensor, disposed within the crankcase chamber. As a result, only the addition of a relatively inexpensive pressure sensor to a conventional computer controlled engine system is required to enable the determination of the mass of air available for combustion within an engine cylinder. Advantageously the estimated mass of air transferred to the combustion chamber is corrected to account for air leakage out of the crankcase and combustion chambers, and for the incomplete transfer of the mass of air from the crankcase to the combustion chamber. Thus, a more accurate estimate of the mass of air available for combustion can be obtained. An embodiment of the present invention is described below, by way of illustration only, with reference to the accompanying drawings, in which: Figure 1 is a schematic diagram of one cylinder of a crankcase scavenged two-stroke engine and a controller which includes an embodiment of system for estimating the mass of air available for combustion; and Figure 2 is a flow diagram representing an embodiment of program instructions executed by the controller of Figure 1 in determining the mass of air available for combustion. Referring to Figure 1, there is shown schematically a crankcase scavenged two-stroke engine, generally designated as 10, with a portion of the engine exterior cut away, exposing cylinder 14. Piston 12 resides within the wall of cylinder 14, with rod 16 connecting piston 12 to a rotatable crankshaft (not shown) disposed within crankcase chamber 18. Connected to engine 10 is an air intake manifold 20 with a throttle 22, and an exhaust manifold 24. Cylinder 14 communicates with exhaust manifold 24 through exhaust port 26 in the wall of cylinder 14. Intake manifold 20 communicates with cylinder 14 and crankcase chamber 18 through a reed valve checking mechanism 28, which opens into a common air transfer passage 30 linking crankcase port 32 with inlet port 34 in the wall of cylinder 14. Cylinder 14 is provided with a spark plug 36 and an electric solenoid driven fuel injector 38 projecting into combustion chamber 40. Associated with engine 10 are various conventional sensors known to the art, which provide typical signals related to engine control. Only the sensors used by this embodiment are described herein. Located within the air intake manifold 20 is a temperature sensor 44 for measuring manifold air temperature (MAT). Another sensor (not shown) provides a signal related to the atmospheric barometric pressure (BARO) for use in controlling engine 10. Electromagnetic sensors 48 and 50 provide pulsed signals indicative of crankshaft rotational angle (ANGLE) and the top dead centre (TDC) position for cylinder 14, by sensing respectively movement of the teeth on ring gear 52 and disc 54, which are attached to the end of the engine crankshaft. Computer 56 is a conventional digital computer used for engine control, and includes a central processing unit, random access memory, read only memory, an analog-to-digital converter, input/output circuitry, and clock circuitry. Signals from the previously mentioned sensors flow through the indicated paths and serve as inputs to computer 56. Using these inputs, computer 56 performs the appropriate computations, and provides an output FUEL SIGNAL to fuel injector 38 and an output SPARK ADVANCE signal to ignition system 58. Ignition system 58 generates a high voltage SPARK signal, which is applied to spark plug 36 at the appropriate time, as determined by the SPARK ADVANCE signal supplied by computer 56 and the position of the engine crankshaft given by the ANGLE and TDC input signals. Ignition system 58 may include a standard distributor or take any other appropriate form. The operation of engine 10 will now be briefly described based upon a cycle occurring in cylinder 14. During the upstroke, piston 12 moves from its lowest position in cylinder 14 towards top dead centre. During the upward movement of piston 12, air inlet port 34 and exhaust port 26 are closed off from the combustion chamber 40, and thereafter, air is inducted into crankcase chamber 18 through reed valve 28. Air in combustion chamber 40, above piston 12, is mixed with fuel from injector 38 and compressed until spark plug 36 ignites the mixture near the top of the stroke. As combustion is initiated, piston 12 begins the downstroke after top dead centre, reducing the volume of crankcase chamber 18 and of the air inducted therein, due to closure of reed valve 28. Towards the end of the downstroke, piston 12 uncovers exhaust port 26 to release the combusted fuel, followed by the uncovering of inlet port 34, enabling compressed air within the crankcase chamber 18 to flow through the air transfer passage 30 into cylinder 14. The cycle begins again when piston 12 reaches the lowest point in cylinder 14. As can be seen, the air inducted into the crankcase chamber 18 is trapped therein from the engine position at which the reed valve 28 closes (substantially at piston top dead centre) to the engine position at which the inlet port 34 is uncovered. In order to control of the emission and performance characteristics of the crankcase scavenged, two-stroke engine 10 effectively, it is necessary to know the mass of air available in cylinder 14 at the time of combustion. Once this information is known, critical engine parameters such as spark advance, fuelling requirement, and injector timing can be adjusted to achieve the engine emission and performance objectives. Assuming the mass of air under compression within the crankcase chamber 18 behaves as an ideal gas, the mass of air trapped within the crankcase chamber can be determined at any point in time during which the air is trapped, from the ideal gas law expression M = PV/RT where P is the pressure in the crankcase chamber 18, T is the temperature of the trapped air, V is the volume of the crankcase chamber 18 and R is the universal gas constant. In order to determine the trapped air mass M on the basis of expression (1), the computer 56 must be provided with means for deriving the air pressure within crankcase 18 and the temperature of the trapped air. In the preferred embodiment, air pressure is obtained by disposing a pressure sensor 46 within crankcase chamber 18 to measure the pressure and develop a corresponding signal CCP for input to computer 56. Pressure sensor 46 may be any type of known pressure sensor which is capable of sensing the air pressure within crankcase chamber 18. A conventional temperature sensor could be used to measure the temperature of the air trapped in the crankcase 18. However, temperature sensors typically have long response times relative to the time required for the compression process, making it difficult to obtain an accurate measurement for trapped air temperature. Accordingly, an approximation is used for the trapped air temperature which eliminates the necessity of a crankcase temperature sensor. The initial temperature T1 of the trapped air when the reed valve 28 first closes at the start of compression is approximately equal to the air intake temperature. The temperature of the trapped air while undergoing compression, and until the inlet port 34 is uncovered to transfer the trapped air to the cylinder, is approximated by the expression T2 = T1*(P2*V2)/(P1*V1). where T2 is the temperature of the trapped air at crankcase volume V2 and pressure P2, and P1 and V1 are the initial crankcase pressure and volume when the reed valve 28 first closes at the start of compression. Accordingly, on the basis of the foregoing relationships, the temperature of the trapped air is approximately based upon the output of the temperature sensor 44 located in the intake manifold 20 and which measures the manifold air temperature. As can be seen from Figure 1, the temperature sensor 44 supplies a signal MAT to the computer 56 which is the equivalent of the initial temperature T1 of the trapped air when the reed valve 28 is first closed. Based upon the known relationship between the volume of crankcase cavity 18 and the angular rotation of the crankshaft from top dead centre, the volume V of equation (1) can be derived from the pulsed signals TDC and ANGLE, provided by electromagnetic sensors 50 and 48 respectively. The angle of crankshaft rotation from top dead centre is obtained by counting the number of pulses occurring in the ANGLE signal, after the occurrence of a pulse in the TDC signal, and then multiplying the number of pulses counted by the angular spacing of teeth in the ring gear 52. In one embodiment of the invention, the mass of air in the crankcase chamber 18 is computed by the expression (1) at a single point during compression of the trapped air such as when the reed valve 28 first closes, and when the temperature of the trapped air is approximately equal to the manifold air temperature MAT. In another embodiment, two or more measurements of the trapped air mass are made and then averaged. For example, a second measurement of the trapped air mass may be made just prior to the opening of the intake port 34 and then averaged with the first measurement made when the air mass was first trapped. In response to each occurrence of top dead centre in cylinder 14, indicated by a pulse in the TDC signal, the computer 56 executes a program stored in its memory which computes the mass of air M trapped in the crankcase chamber 18, makes corrections for air leakage and incomplete air transfer, and thereafter computes engine control outputs for that particular cylinder based upon the corrected estimate of air mass available for the next ignition event. The flow diagram of Figure 2 illustrates the steps in the stored routine that are executed by computer 56 in response to each occurrence of top dead centre in cylinder 14. Programming of computer 56 to implement this series of steps will be clear to any skilled programmer. Referring now to Figure 2, the flow diagram will be described with respect to the occurrence of top dead centre in cylinder 14, which causes entry into the routine at step 59. The program begins at step 60 where the computer determines and stores initial conditions by sampling input signals CCP, MAT and BARO and stores these values as P1, T1 and BARO, respectively. P1 is the initial crankcase air pressure, and T1 is the initial crankcase air temperature, both determined just prior to the beginning of compression within crankcase chamber 18. The stored values of P1 and T1 are representative of the initial pressure and temperature of the trapped air since the reed valve 28 closes substantially at top dead centre. The initial value for the volume V1 of crankcase chamber 18, at top dead centre, is known for engine 10 and is permanently stored in the computer read only memory. In another embodiment, the measurement of the initial temperature and pressure of the air when first trapped may be made at some small angle after top dead centre. The program next proceeds to step 62 where the trapped air mass M1 based on the parameters P1 and T1 read and stored at step 60 and the volume V1 retrieved from memory is determined using the expression (1) set forth above. In one embodiment, this value is used as the final computed value of the trapped air mass. At step 64, a decision is made as to whether the current rotational angle of the crankshaft angle ϑ is equal to an angle ϑ2 at which a second determination of the trapped air mass is to be made. The engine rotational angle ϑ is continuously computed and updated outside the present routine, using the TDC and ANGLE inputs as described previously. In the preferred embodiment of the present invention, ϑ2 is assigned a value corresponding to the point in rotation where the air inlet valve 34 in the cylinder wall 14 is about to open. If the crankshaft has not rotated to the angle ϑ2, step 64 is repeated. When step 64 determines that the crankshaft rotational angle ϑ is equal to ϑ2, the signal CCP is sampled and stored as P2 at step 66. The temperature of the trapped air mass is then computed at step 68 from the values of P1, T1, V1, P2 and the crankcase volume V2 at the rotational angle ϑ2 which is known for engine 10 and is permanently stored in the computer read only memory. The program next proceeds to step 70 where the trapped air mass M2 based on the parameters P2, the computed temperature value T2, and the volume V2 retrieved from memory is determined using the expression (1) set forth above. In one embodiment, the trapped air mass may be based solely on the computed value M2. However in this embodiment, the value for mass air M within the crankcase chamber is computed by averaging the two determined trapped air mass values M1 and M2. This determination of air mass M is done at the step 72. At step 74, the program looks up a leakage correction factor LCF in a table stored in memory, using the values of P1 and BARO stored at step 60. The leakage correction factor LCF represents the percentage of the mass of air M remaining within the crankcase chamber 18 at the end of compression, after air loss due to leakage through reed valve 28 and gaskets sealing the crankcase chamber. The stored values for the leakage correction factor are pre-determined as a function of P1, which is substantially equal to the intake manifold pressure, and atmospheric barometric pressure BARO. The amount of air leakage through crankcase seals is a function of the difference between the crankcase pressure and BARO, while the amount of air leakage through the reed valve is a function of the difference between crankcase pressure and the pressure within intake manifold 20, as indicated by P1. At step 76, the program computes M', the mass of air contained within the crankcase after correction for leakage. The value for M' is computed by multiplying the value of M computed at step 72 by the leakage correction factor LCF found at step 74, or M' = M*LCF. At step 78, the program looks up a value for trapping efficiency TE in a table stored in memory, using values for M', calculated in the previous step 76, and the current engine speed in RPM, derived by determining the number of TDC pulses which occur per minute. The trapping efficiency TE represents that percentage of the corrected mass air M' within crankcase chamber 18 which is transferred and captured within combustion chamber 40, after closure of air inlet port 34 and exhaust port 26. Values for trapping efficiency are pre-determined as a function of the mass of air M' in crankcase chamber 18, and the engine RPM, which is related to the time available for air to pass through inlet port 34 or be lost out exhaust port 26. Next at step 80, the appropriate air/fuel ratio A/F for cylinder 14 is looked up in a stored table, using values for the corrected mass air M' and the engine RPM. The desired values the air/fuel ratio table are pre-determined by standard engine dynamometer measurements known to those skilled in the art of engine control, as are the other conventional look-up tables referred to herein. At step 82, the mass of air CMA, which is available for combustion within cylinder 14 is computed by multiplying the corrected crankcase air mass M', found at step 76, by the trapping efficiency TE, found at step 78, according to the equation CMA = M'*TE. In the remaining steps 84 to 88, the combustion chamber mass air CMA, found at previous step 82, is used to compute standard engine control parameters. At step 90, the injector fuel pulse width FPW is computed according to the following: FPW = K*CMA*[1/(A/F)], where K is a predetermined scaling constant stored in memory, CMA was found in step 82, and A/F is the air/fuel ratio determined in step 80. Next, at step 86, the proper timing for the fuel pulse to injector 38 is looked up in the appropriate table stored in memory, based upon the value of the engine RPM and the combustion chamber air mass CMA. Using the computed values for fuel pulse width FPW and the injector timing, computer 56 provides the appropriate FUEL SIGNAL (see Figure 1) to injector 38. Finally, at step 88, the correct spark advance for cylinder 14 is found in a stored look-up table as a function of engine RPM and combustion chamber air mass CMA. Computer 56 provides ignition system 58 with the SPARK ADVANCE signal so that spark plug 36 can be fired at the proper time in advance of top dead centre for cylinder 14. After the above steps have been executed, the routine is exited at point 90.

Claims: A method of determining the mass of air within a crankcase chamber (18) of a crankcase scavenged two-stroke engine having an operating cycle which includes a portion during which air is inducted into a crankcase chamber (18) of the engine, a portion during which the inducted air is trapped in the crankcase chamber and is thereafter compressed as the crankcase chamber is reduced in volume, and a portion during which the compressed inducted air is transferred to the combustion chamber; the method comprising the steps of determining at a predetermined point in the operating cycle the pressure (P) of the air mass (M) trapped within the crankcase chamber; and determining the mass of air (M) for transfer to the combustion chamber; characterised by determining the volume (V) of the crankcase chamber at the predetermined point in the operating cycle; determining the temperature (T) of the air mass within the crankcase chamber at the predetermined point in the operating cycle; and in that the step of determining the mass of air (M) for transfer to the combustion chamber comprises deriving a value indicative of the mass of air (M) for transfer to the combustion chamber in accordance with the expression M = PV/RT, in which P is the determined pressure (P), V is the determined volume (V), T is the determined temperature (T) and R is the Universal Gas Constant. A method according to claim 1, wherein the volume (V) of the crankcase chamber is derived as a function of the engine cycle position. A method according to claim 1 or 2, wherein the crankcase chamber air temperature (T) is derived as a function of intake air temperature. A method according to any preceding claim, wherein the predetermined point in the operating cycle is the point at which the inducted air is first trapped in the crankcase chamber, wherein the temperature (T) of the air mass within the crankcase chamber is taken to be substantially equal to intake air temperature. A method according to claim 1, 2 or 3, wherein the pressure (P), the volume (V) and the temperature (T) of the air mass within the crankcase chamber are determined at each of a plurality of predetermined points in the operating cycle of the engine, and the value indicative of the mass of air for transfer to the combustion chamber is obtained as a function of the average of the values obtained at the predetermined points in the operating cycle. A method according to any preceding claim, wherein the step of deriving a value indicative of air mass for transfer to the combustion chamber includes the step of obtaining a correction value indicative of the effect of air leakage from the crankcase chamber. A method according to any preceding claim, wherein the step of deriving a value indicative of air mass for transfer to the combustion chamber includes the step of obtaining a correction value indicative of the effect of imperfect transfer of air from the crankcase chamber to the combustion chamber. A method according to claim 7, wherein the step of obtaining a correction value indicative of the effect of imperfect transfer of air to the combustion chamber includes the steps of determining a trapping efficiency value representative of the amount of the mass of air trapped in the crankcase chamber which is to be transferred to and then trapped in the combustion chamber (40); and adjusting the derived value indicative of the mass of air trapped in the crankcase chamber on the basis of the determined trapping efficiency value. Apparatus for determining the mass of air within a crankcase chamber (18) of a crankcase scavenged two-stroke engine having an operating cycle which includes a portion during which air is inducted into a crankcase chamber (18) of the engine, a portion during which the inducted air is trapped in the crankcase chamber and is thereafter compressed as the crankcase chamber is reduced in volume, and a portion during which the compressed inducted air is transferred to the combustion chamber; the apparatus comprising a pressure sensor (46) for determining at a predetermined point in the operating cycle the pressure (P) of the air mass (M) trapped within the crankcase chamber; and processing means (56) for determining the mass of air (M) for transfer to the combustion chamber; characterised by means (56) for determining the volume (V) of the crankcase chamber at the predetermined point in the operating cycle; a temperature sensor (44) for determining the temperature (T) of the air mass within the crankcase chamber at the predetermined point in the operating cycle; and in that the processing means (56) is adapted to derive a value indicative of the mass of air (M) for transfer to the combustion chamber in accordance with the expression M = PV/RT, in which P is the determined pressure (P), V is the determined volume (V), T is the determined temperature (T) and R is the Universal Gas Constant. Apparatus according to claim 9, wherein the processing means (56) is adapted to obtain a correction value indicative of the effect of air leakage from the crankcase chamber. Apparatus according to claim 9 or 10, wherein the processing means (56) is adapted to obtain a correction value indicative of the effect of imperfect transfer of air from the crankcase chamber to the combustion chamber. Apparatus according to claim 11, wherein the processing means (56) is adapted to determine a trapping efficiency value representative of the amount of the mass of air trapped in the crankcase chamber which is to be transferred to and then trapped in the combustion chamber (40); and to adjust the derived value indicative of the mass of air trapped in the crankcase chamber on the basis of the determined trapping efficiency value.

Inventors: REINKE, PAUL EDWARD, STILES, STEVEN DOUGLAS
Applicants: GENERAL MOTORS CORPORATION
Application year: 1991
Main classification: F02D41
IPC codes: F02B75, F02D41, G01F1, F02D45