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In this investigation a newly designed gear drive mechanism that controls the intake valve opening (IVO) and closing (IVC) angles is studied. The control scheme is based on maximizing the engine brake power (P) and specific fuel consumption (BSFC) at any engine speed by continuously varying the phase between the cam shaft angle and the crank shaft angle. A single-cylinder engine is simulated by the “LOTUS” software to find out the optimum phase angle for maximum power and minimum fuel consumption at a given engine speed. The mechanism is a plane- tary gear drive designed for precise and continuous control. This mechanism has a simple design and operation condi- tions which can change the phase angle without limitation. Keywords: Mechanism Design; Planetary Gear; Variable Valve Timing; Spark Ignition Engines; Performance 1. Introduction In internal combustion engines, variable valve timing (VVT), also known as Variable valve actuation (VVA), is a generalized term used to describe any mechanism or method that can alter the shape or timing of a valve lift event within an internal combustion engine 1-6. The (VVT) system allows the lift, duration or timing (in vari- ous combinations) of the intake and/or exhaust valves to be changed while the engine is in operation, which have a significant impact on engine performance and emissions. In a standard engine, the valve events are fixed, so per- formance at different loads and speeds is always a com- promise between drivability (power and torque), fuel economy and emissions. An engine equipped with a variable valve actuation system is freed from this con- straint, allowing performance to be improved over the engine operating range 7-10. Some types of variable valve control systems optimize power and torque by varying valve opening times and/or duration. Some of these valve control systems optimize performance at low and mid-range engine speeds. Others focus on enhancing only high-rpm power. Other systems provide both of these benefits by controlling valve timing and lift. There are many ways in which this can be achieved, ranging from mechanical devices to hydraulic, pneumatic and camless systems 11-14. Hydraulic sys- tem suffer from many problems including viscosity change of the hydraulic medium due to the temperatures change, the liquid tends to act like a solid at high speed, and hydraulic systems must be carefully controlled, which require the use of powerful computers and very precise sensors. Pneumatic system utilizing pneumatics to drive the engine valves would in all probability not be feasible because of their complexity and the very large amount of energy required for compressing the air. Camless system (or, free valve engine) uses electromagnetic, hydraulic, or pneumatic actuators to open the poppet valves instead. Common problems include high power consumption, accuracy at high speed, temperature sensitivity, weight and packaging issues, high noise, high cost, and unsafe operation in case of electrical problems. Multiair system (or Uniair) is an electro-hydraulic variable valve actuation technology controlling air intake (without a throttle valve) in petrol or diesel engines. The system allows optimum intake valve opening schedules, which gives full control over valve lift and timing. 2. Continuous Variable Valve Timing (CVVT) First, The (CVVT) system offers a unique ability to have Copyright 2013 SciRes. ENG O. H. M. GHAZAL, M. S. H. DADO 246 independent control of the intake and exhaust valves in an internal combustion engine 15-17. For any engine load criteria, the timing of intake and exhaust can be inde- pendently programmed and the engines performance could be optimized under all conditions. However, if valve timing could be controlled independent of crank- shaft rotation, then a near infinite number of valve timing scenarios could be accommodated which would dra- matically improve fuel economy and emission levels of an automobile. These systems are used in several automo- biles with gasoline engine like Toyota, Nissan, Honda, and others. In 2010, Mitsubishi developed and started mass production of its 4N13 1.8 L DOHC I4 worlds first passenger car diesel engine that features a variable valve timing system. One of the high effective mechanisms proposed for controlling variable valve timing is planetary gear me- chanism. The planetary gearbox arrangement is an eng- ineering design that offers many advantages. One ad- vantage is its unique combination of both compactness and outstanding power transmission efficiencies. A ty- pical efficiency loss in a planetary gearbox arrangement is only 3% per stage. This type of efficiency ensures that a high proportion of the energy being input is transmitted through the gearbox, rather than being wasted on me- chanical losses inside the gearbox. Another advantage of the planetary gearbox arrangement is load distribution. Because the load being transmitted is shared between multiple planets, torque capability is greatly increased. The more planets in the system the greater load ability and the higher the torque density. The planetary gearbox arrangement also creates greater stability due to the even distribution of mass and increased rotational stiffness. Hence, in this work we will present a new design of planetary gear drive mechanism for Continuous variable valve timing IC engine. 3. The Gear Drive Mechanism Design After the text edit has been completed, the paper is ready for the template. Duplicate the template file by using the save as command, and use the naming convention pre- scribed by your journal for the name of your paper. In this newly created file, highlight all of the contents and import your prepared text file. You are now ready to style your paper. 3.1. A Description The proposed gear drive mechanism is designed by Prof. M. Dado from mechanical engineering department at the University of Jordan. This mechanism guarantees a pre- cise and continuous camshaft phasing for intake and ex- haust valves in internal combustion engine. The phase angle between the camshaft and crankshaft changes re- lated to engines speed, which improve engines per- formance and emissions. The mechanism shown in Figure 1 is a planetary gear train system consisting from an external sun gear (3), planetary gears (2) carried by two planet arms (1), and an internal ring gear (4) with external worm teeth meshing with a worm gear (5) which is connected to a stepper motor interfaced to the engine computer control system. When the stepper motor shaft is stationary, which is the prevailing case, the ring gear is also stationary. This yields a constant speed ratio between the crank shaft and the camshaft. A rotation of the stepper motor shaft leads to the rotation of the ring gear resulting in additional rotation for the planetary gears and the external sun gear and the camshaft. This additional rotation results in phase change between the crank shaft and the cam shaft. 3.2. Mechanism Installation The mechanism is operated by planetary gear train to continuously and precisely change the phase angle be- tween camshaft and crank shaft. The internal ring gear has an external worm tooth so it can acts like a worm wheel. It trains with the worm. The mechanism is operated by planetary gear train to continuously and precisely change the phase angle between camshaft and gear. The four identically planetary gears are meshing with the ring gear and the sun gear and they are carried by the two arms. The mechanism (Figure 2) is installed to the internal combustion engine as follows: The mechanism is carried by bearing in such way that the camshaft (6) and the sun gear shaft are coaxial and then shafts are connected by the Figure 1. The components of the mechanism. Copyright 2013 SciRes. ENG O. H. M. GHAZAL, M. S. H. DADO 247 Figure 2. The mechanism installation. spline coupling (7). One of the planet arms (1) is con- nected with the crank shaft (9) by chain or timing belt (8). The worm gear shaft is connected mechanically with a stepper motor. The stepper motor is equipped with sensors and power supply, which are connected to the CPU to control the motion of the worm gear. 3.3. The Method of Operation The method of the mechanism operation is easy and sim- ple and its described below: 1) When the stepper motor shaft is stationary, which is the prevailing case, the ring gear is also stationary. The rotation of the arm by the crank shaft causes the rotation of the ring according to the equation: 4311TT1 (1) where: 3the speed of the sun gear (3), which is also the speed of the camshaft; 1the speed of the arm (1). T1 and T4 are the number of teeth of the sun gear and the number of internal teeth for the ring gear, respectively. The relationship between the number of teeth for the sun gear, planetary gears, and internal ring gear is: 432TTT2 (2) where: T2the number of teeth for the planetary gears (2). 2) When the stepper motor have a signal from the CPU it will rotate according to the required shift angle resulting in the rotation of the worm gear (5), which will cause the rotation of the ring gear and consequently an additional rotation of the planetary gears. 3) This rotation resulting in additional rotation for the sun gear, which is connected with the camshaft, according to the following equation 35346T TT T5 (3) where: 3the shift angle for the camshaft; 5the angle of rotation for the worm gear; T5, T6the number of teeth for worm gear and external teeth for the ring gear, respectively. 4) The arm will not be affected by this rotation, because it is coupled to the crankshaft. 5) The additional rotation for the sun gear which is connected to the camshaft results in phase change between camshaft and crank shaft of value 1. 3.4. The Advantages of the Mechanism The main advantages of the above mechanism over other mechanisms can be summarized as follows: 1) The change in the phase angle is constrained to the motion of the stepper motor, which can be controlled with accuracy up to 1.8 degrees for each step with zero over- shoot. This value will be smaller for the camshaft de- pending on the gear teeth numbers. 2) The worm gear, which is connected to the stepper motor and meshing with ring gear, offers a self-locking mechanism for ring gear. That will guarantee a constant speed ratio between the camshaft and crank shaft for specific phase angle, which is necessary for good engine operation. 3) In this mechanism there is no limitation for phase angle changing value, except the limitation imposed by the engines performance envelop. 4. Cam Phasing OptimizationMaximizing Power Output In this work, the optimum values for intake and exhaust valve timing have been calculated to maximize brake power. These values were used to calculate and compro- mise the brake power and fuel consumption for different engines speeds and compression ratios. For the purpose of analyzing the engine characteristics the dimensions were considered with Lotus Engineering Software. The Lotus Engine Simulation and analysis program is an in-house code developed by LOTUS ENGINEERING Company since the late 1980s. Validation of global per- Copyright 2013 SciRes. ENG O. H. M. GHAZAL, M. S. H. DADO Copyright 2013 SciRes. ENG 248 which means that one revolution of the arm results in 4 revolutions of the camshaft (and the sun gear). This re-quires keeping the velocity ratio between crankshaft and the arm equals two to obtain the velocity ratio between the camshaft and the crankshaft equals two, which is neces-sary for four stroke IC engine operation. formance parameters of power, volumetric efficiency and fuel consumption has been performed on a wide range of current production engines. The simulation model of 4-cylinder engine (Figure 3) has been built to find out the optimum phase angle for maximum power. The engine geometry data and valve timings are as shown in Table 1. Input data such as inlet pressure, temperature, equivalence ratio are also intro- duced for all runs. Also the required exit data such as the back pressure are given. The calculations were carried out for the default and optimum values of valve timing which are given in Table 2. The optimization engine variable is to find the maximum brake power output. The speed is varied from 1000 - 6000 rpm. The effects of optimum valve timings values and default values on the brake power and for different compression ratio (CR) are illus-trated in Table 3 and Figure 4 through 6. On the other hand, the relationship between the stepper motor angle and camshaft angle is obtain from Equation (3) 355353467.5N NNN (6) That mean when the stepper motor (and worm gear) rotates 7.5 degrees, the camshaft rotates one additional degree. The dimensions of the mechanism can be found as fol- lowing: we assume that planetary gear, sun gear, and ring gear are helical gears with helical angle = 30 and module m = 1 mm and the face width f = 20 mm. In addition, the worm teeth has lead angle = 10 and axial pitch p = 2 mm. From these assumptions we find out that the diameter of the mechanism are not more than 150 150 50 mm, so it can be installed in engine room eas- ily. 5. The Application of the Mechanism (Example) The data given in Table 2 were used to calculate the re-quired values of shift angle for worm gear. To illustrate the work of the above mentioned mechanism we have made the following assumptions: 6. Conclusion 325620,20,2,45TTTT (4) A planetary gear drive mechanism is designed and im-plemented to optimize the performance of a four stroke single-cylinder engine. The mechanism precisely and continuously changes the phase angle between the cam shaft and crank shaft angles. The effect of optimizing the phase angle at a given speed on the brake power is From Equations (1) and (2) we get: 431202 2060and4T (5) Figure 3. The simulation model of IC engine. O. H. M. GHAZAL, M. S. H. DADO 249 Table 1. Base engine geometry, fuel is gasoline (C8H18). Type of engine 4-stroke Bore 82 mm Stroke 80 mm No. of cylinders 4 Compression ratio 8 - 14 Inlet throat dia. 26.5 mm Exhaust throat dia. 22.5 mm Max. valve lift 8 mm IVO angle bTDC 10 deg IVC angle aBDC 66 deg EVO angle bBDC 38 deg EVC angle bTDC 38 deg Speed 1000 - 6000 rpm Table 2. Optimum values of valve timing for maximum power and different speeds. Valve timings Inlet valve timing Exhaust valve timing Speed, rpm Open, bTDC Close, aBDC Open, bBDC Close, aTDC 1000 25 30 55 32 2000 33 37 65 39 3000 44 43 70 45 4000 49 47 70 51 5000 51 50 70 53 6000 57 60 70 57 Table 3. (a) Brake power for optimum and default values of valve timing for different speeds; (b) Brake power for op- timum and default values of valve timing for different speeds. (a) CR 8 CR 10 Speed rpm Opti Def % incre Opti Def % incre 1000 3.73 2.78 34 4.1 2.98 37 2000 7.8 6.09 28 8.35 6.52 28 3000 11.7 9.37 25 12.56 10.05 25 4000 15.31 12.4 23 16.47 13.38 23 5000 18.56 15.2 22 20.07 16.43 22 6000 21.39 17.7 21 23.22 19.13 21 (b) CR 12 CR 14 Speed, rpm Opti Def % incre Opti Def % incre1000 4.21 3.11 35 4.3 3.24 33 2000 8.76 6.8 29 9.07 7.06 28 3000 13.1 10.5 25 13.69 10.91 25 4000 17.3 14.0 23 18.01 14.58 24 5000 21.1 17.3 22 22.02 17.97 23 6000 24.5 20.2 22 25.62 21.03 22 Figure 4. The effect of optimum valve values and default values on brake power (CR 8). 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