Behnam Reciprocating Mechanisms

A hydraulic schematic apparatus for short interval of time significant reduction of acting force by hydraulic piston, the said hydraulic piston driving a roller which moves back and forth and performs the action of end seaming, the apparatus at least comprises:

• A main hydraulic line, a hydraulic pump on the said main hydraulic line,
• an oil tank on the said main hydraulic line before the suction of said hydraulic pump acting as reservoir from which the said hydraulic pump draws oil and into which the returned oil will go,
• a hydraulic cylinder with double acting piston up stream of the said main hydraulic line on the said main line, the said main line going into the said hydraulic cylinder and coming out of the said hydraulic cylinder, the said hydraulic cylinder positioned after the said hydraulic pump's discharge, the said double acting piston moving a seaming roller back and forth, the said main hydraulic line taking the pressurized hydraulic oil into the hydraulic cylinder and taking the returned oil out of the said hydraulic cylinder,
• a control valve on the said main line placed after the discharge of the said hydraulic pump and before the said hydraulic cylinder for directing the direction of oil into or from said hydraulic cylinder, the said control valve having four connections, the first being the main line coming from hydraulic pump discharge, the second a line from the control valve to said oil tank and the third and the fourth lines are two lines going and coming from the said hydraulic cylinder with double action piston;
• the flow of hydraulic oil in the loop of the said main line in order is from oil tank to hydraulic pump to directional control valve to hydraulic cylinder and after that back to directional control valve and at the end back to the oil tank;
• the apparatus additionally comprising:
• a by pass line much smaller in diameter than the main line's diameter taken off the said main line after the said hydraulic pump discharge between the said discharge and said directional control valve, the said by pass line coming from said connection point and going either to the said oil tank or to the main line between the said hydraulic pump suction and the oil tank;
• the said by pass line is furnished with a solenoid valve which is normally closed and a globe valve;
• instead of the said globe valve a valve equivalent of a globe valve could replace it;
• the said solenoid valve being controlled by electrical controls which opens the said normally closed solenoid valve for a short interval of time at the beginning of the operation of the seaming and closes the same after the said short time interval is finished;
• the said solenoid valve shall be closed for the rest of the operation of seaming;
• the adjustment of the said globe valve allows the control of the pressure on said pump discharge during the said short time interval which requires significant reduction of pressure in the main line after the pump discharge.

An apparatus for a sliding arm with one degree of freedom slidable inside an adjustable closure in order to avoid minute slacks between touching sliding surfaces of the sliding arm and its closure for muffler cap spinning machine or a different application, the apparatus at least comprising:

• a sliding arm, a hollow closure, at least two flaps, sufficient number of positioning bolts, sufficient number of positioning nuts, sufficient number of minor adjustment bolts and sufficient number of minor adjustment nuts;
• the said sliding arm with rectangular cross section and with one degree of freedom is slidable along a direction perpendicular to said rectangular cross section;
• said sliding arm has four outside surfaces parallel to said direction of motion created by extrusion of the said rectangular profile;
• two of the four surfaces of the said four surfaces of said sliding arm which are adjacent are in close contact with two of the inside surfaces of the said hollow closure which are adjacent and the other two surfaces of the said four surfaces of the sliding arm each is in close contact with one surface of one of the said two flaps;
• the said hollow closure is for containing and guiding the said sliding arm;
• said hollow closure is attached to the frame of muffler cap spinning machine or to a stationary wall for a different application from one end and open from other end to accommodate the said sliding arm;
• said hollow closure having an inside rectangular cross section larger than the rectangular cross section of the said sliding arm where the plane of said cross section is perpendicular to direction of motion of the sliding arm and two of the four outside surfaces of the said sliding arm which are adjacent are in close contact with two of the adjacent inside surfaces of the hollow closure;
• the closure having slots to accommodate positioning blots on the sides which are in close contact with the said sliding arm in order to hold in place the said flaps in position with the aid of positioning nuts;
• the direction of the length of each of the said slots is perpendicular to the direction of motion of the sliding arm;
• for each positioning bolt there shall be one positioning nut;
• the hollow closure also having holes to accommodate minor adjustment bolts;
• the said holes are on the sides of the said hollow closure which are not in close contact with the sliding arm;
• the said two flaps each having an “L” shape cross section with 90 degrees right angle;
• said “L” shape cross section extruded along a direction perpendicular to the plane of said “L” shape cross section;
• the said “L” shape cross section having sufficient thickness to resist bending due to forces exerted to it by the sliding arm;
• the length of extrusion being substantially larger than the thickness of the said “L” shape profile;
• the said flap having six surfaces in total;
• four of said six surfaces being parallel to direction of extrusion of the “L” shape profile and the said direction of extrusion being parallel to that of direction of motion of sliding arm;
• the largest surface of each of the said two flaps being in close contact with one of the remaining two surfaces of the said four surfaces of the said sliding arm;
• the second smallest surface of the said four surfaces of the said flaps being in close contact with the inside surface of the said closure where the said slots of the closure are positioned;
• the said flaps each having holes located on the said second smallest surface of the flat perpendicular to the said surface;
• additionally the said two flaps are positioned such that the largest surface of each flap is perpendicular to the largest surface of the other flap;
• the positioning bolts going through the said slots in the body of the said hollow closure and the said holes in the said flats and positioning the flat and keeping each of the said flaps in position with the aid of positioning nuts such that the flap and the hollow closure are held between each of the positioning bolt head and the positioning nut;
• for each positioning bolt there shall be one positioning nut;
• the minor adjustment bolts each going through the said holes in the body of the said hollow closure such that the end of the bolt touching the second largest surface of the said flaps pushing the flap against the sliding arm and head of the said bolt is substantially above the outside surface of the said hollow closure;
• the said minor adjustment bolts each being held in place with the aid of two minor adjustment nuts such that the corresponding plate of the hollow closure is held firm between the said two minor adjustment nuts.

An apparatus for reciprocating the linear motion of a piston to rotational motion for internal combustion engine for a crank shaft mechanism;

• said apparatus provides a longer length of power stroke than that of intake stroke thus improving fuel efficiency;
• the apparatus at least comprises:
• a cylinder, a piston, a crank cam and an “n” shape double pin where each pin possibly furnished with a bushing, the said “n” shape double pin acting as connection mechanism;
• the said crank cam only rotatable about its central shaft's axil with the central shaft mounted in the engine block from two sides and a hollow cam for every piston and the said hollow cam and the shaft are one solid piece;
• the said hollow cam being open from one end and closed or partially closed from opposite side and from this said closed side attached to the central shaft and the profile of the weir of the hollow cam having a shape close to an oval shape profile, but not exactly an oval, made of curves tangent at points of intersection;
• and said profile plane of the cam's weir being perpendicular to the central axil of the crank cam and said profile having four quadrants;
• the said four quadrants angularly are 90 degrees apart from each other such that the two lines going through every two opposite quadrants are perpendicular;
• two of the said four quadrants which are on the opposite side of each other being substantially closer to the center of the shaft compare to the other two quadrants which are opposite to each other;
• one of the said two quadrants which are closer to the center of the shaft is the closet to of all four quadrants to the center of the shaft;
• as the crank cam rotates and each of the said four quadrants pass through the connection mechanism which connects the piston to said crank cam's weir each of the said four quadrants will correspond to one of the top or bottom dead center positions of the piston;
• the distance of each the said four quadrants to the central axil of the crank cam is addressed by the thermodynamics requirement of the combustion engine in order to obtain best efficiency, but the main feature of the said crank cam is the fact that the corresponding quadrants for power stroke and intake stroke are positioned such that the length of the power stroke is longer than that of intake stroke;
• the said cylinder is inside engine block to hold and guide the said piston inside it;
• the central axil of the said cylinder is perpendicular to the central axil of rotation of the said crank cam;
• the said piston has a piston rod;
• at one end of the said piston rod, the actual piston part which is slidable inside the cylinder with one degree of freedom, is attached to the said piston rod and at the opposite end of the said piston rod a round pin possibly furnished with a bushing is attached to the said piston rod;
• the said piston section and said pin and the said piston rod are one solid piece;
• the said pin has a hole smaller in diameter than the diameter of the said pin;
• the said hole's central axil is collinear with the pin's axil;
• the central axil of the said round pin is perpendicular to direction of motion of the piston and parallel to central axil of rotation of the said crank cam;
• the said pin at one end of the said piston is possibly furnished with a bushing;
• either the outside surface of the said pin or in the case of using a bushing for the said pin, the outside surface of the said bushing is in close contact with the outside surface of the said cam's weir;
• the said double pin has the shape of small “n” and the central axil of the said two pins are parallel and each pin has a circular cross section and the two pins are connected with a link and the two pins and the link being one solid piece and appearing as an “n” shape;
• said double pin is acting as connection mechanism connecting the said piston to said crank cam's weir;
• the said double pin rotatable about the central axil of one of the said two pins which is being placed inside the hole said at the end of said piston's pin and the central axil of the said pin of the said double pin has only one degree of freedom and moves at the same time with the same speed and distance and in the same direction of the said piston;
• and the other pin of the said double pin possibly furnished with a bushing is placed inside the weir of the said crank cam such that the weir of the hollow cam is held with no slack between this second pin of the said double pin and the said pin at one end of the piston;
• the said second pin of the said double pin has two degree of freedom and its outside surface or the outside surface of its bushing is in close contact with the inside surface of the cam's weir;
• the weir of the said crank cam is held between the said second pin of the said double pin and the pin at end of said piston such that there shall be no slack between them;
• as the piston operates the connection mechanism causes reciprocation of the linear motion of the piston to rotational motion of the crank cam;
• the two axils of the said pin are parallel to the central axil of rotation of the crank cam;
• the complete four stroke cycle of a combustion engine using the said apparatus is a 360 degrees rotation of the said crank cam;
• the said four quadrants of the said crank cam as they come to pass through the concoction mechanism, the said piston is brought to one of the dead center positions inside the said cylinder;
• the distance between the said quadrants of the said crank cam to the central axil of rotation of the crank cam will address the thermodynamics requirements of the combustion engine;
• in particular the distance that the piston travels down the cylinder during the power stroke is longer than that of intake stroke;
• thus allowing the piston to generate more power than normal for the same amount of fuel;
• of the said four quadrants of the said crank cam, the quadrant that is the closest to the crank cam's central axil once passing through the connection mechanism it corresponds to end of power stroke and beginning of exhaust stroke;
• the quadrant which reaches the connection mechanism after the said previous quadrant, once it reaches the connection mechanism it corresponds to end of exhaust stroke and beginning of intake stroke;
• this quadrant is substantially farther from the crank cam's central axil than the previous quadrant;
• the quadrant which reaches the connection mechanism after the said previous quadrant is the quadrant which is the second closest to the crank cam's central axil and once passing through the connection mechanism it corresponds to end of intake stroke and beginning of compression stroke;
• the quadrant which reaches the connection mechanism after the said previous quadrant is the quadrant which once it reaches the connection mechanism it corresponds to end of compression stroke and the beginning of power stroke;
• this quadrant is substantially farther from the crank cam's central axil than the previous quadrant.