RU2347088C1 - Screw ball four-cycle engine - Google Patents

Abstract

FIELD: engines and pumps.

SUBSTANCE: invention is related to the field of machine building, namely, to piston internal combustion engines. Substance of invention consists in the fact that every engine cylinder is equipped by its screw ball mechanism that converts rectilinear reciprocal movements of pistons into shaft rotary motion. In screw ball mechanism all kinematic pairs are equipped with rolling bodies, i.e. frictional torque of rolling pairs is minimum.

EFFECT: higher reliability of engine, simplification of its design, higher efficiency factor.

3 cl, 11 dwg, 2 tbl

Description

The invention relates to the field of mechanical engineering, and more particularly to reciprocating internal combustion engines, which belong to the widespread and numerous class of heat engines, in which the thermal energy generated by the combustion of fuel is converted into mechanical useful work. In these engines, the processes of fuel combustion, heat generation and its conversion into mechanical work occur directly inside the engine.

Famous internal combustion engine with a rodless mechanism (USSR copyright certificate No. 118471, class F01 B 9/02, 1958).

The rodless engine has a star-shaped arrangement of cylinders, and the pistons are pairwise rigidly interconnected by rods articulated through bearings with the middle necks of the crankshaft having a neck rotation with the piston systems and their associated rods moving along the axis of the opposing cylinders. The working shaft of this engine is made of two parts with crankshaft bearing for fixing in them on the radius of one quarter of the piston stroke of the extreme necks of the crankshaft, and is equipped with a connecting shaft, fixing with the help of gears the position of the cranks of both parts of the working shaft relative to each other.

The disadvantage of this engine is the complicated design of the crank mechanism, which has an additional connecting shaft with gears that fix the position of the parts of the cranks relative to each other, as well as the presence of a crankshaft.

From the patent literature known internal combustion engine, US patent No. 4553503, CL. F02B 75/25, 1985, the second option, Fig.24 and 25, which is taken as a prototype.

The engine contains a cylinder block with axially arranged cylinders in which the pistons are reciprocally mounted, a block head with intake and exhaust valves, an engine casing in which a mechanism for converting the reciprocating movements of the pistons into shaft rotation is installed. On the generatrix of the rotor cylinder of this mechanism, the right and left directions are made of arc troughs, balls are installed in these trenches, submerged half the diameter, and the second half of them are installed in the spherical holes of the sliders, the balls are installed with the possibility of interaction with the rotor grooves and with the spherical holes of the sliders when interacting small balls, and the sliders are connected by rods with pistons.

The main disadvantages of these engines are:

The profiles of the arc grooves on the cylindrical surface of the rotor hub are made with two inflection points / cm. Fig.31 /. With this angular arrangement of the grooves, the four-stroke cycle of the four-stroke engine is carried out in two rotor rotations, since the piston stroke is carried out by turning the rotor through an angle of 180 °, similarly as with engines with a crank mechanism.

The reciprocating movements of the sliders are carried out in the slide rails, and the forces from the gas pressure in the cylinder act on one ball mounted in the slide. The resulting force from the gas pressure in the cylinder is simultaneously transferred from the axial direction of the slider to the point of contact with the profile of the rotor trough. As a result, according to the theorem on the parallel transfer of forces, a moment arises equal to the resulting force relative to the point of contact of the ball with the profile of the rotor trough / cm. book S.M.Targ. Short course of theoretical mechanics. The science. Moscow, 1964, p. 58, p. 21 /. From this moment, friction of the slide along the guides, as well as the piston against the cylinder walls, arises. the slider is made in one piece with the piston rod. In addition, at the point of contact of the ball with the profile of the trough, the resulting force is decomposed into a force polygon of forces and one of the components creates friction of the slide along the guides.

All of the above friction losses significantly reduce engine power.

If this engine will have a cylinder diameter of 100 mm and a maximum cylinder pressure of 54 kgf / cm ² , then the resulting force acting on the piston from the expansion of gases in the cylinder will be 4240 kgf. And with a parallel transfer of forces, this resulting force is transferred to the ball. As a result, the static load on the ball, taking into account Hertz contact stresses, should be greater than or equal to the resulting force.

Static load is determined by the product

where β is the contact angle of the ball with the profile of the trough, which on average can be equal to 36 °, and cos = 0.80902.

Equating the resulting force to a static load and solving the above product relative to the diameter of the ball, its diameter will be 64.75 mm and weight 1.13 kg.

With this diameter of the ball, the design of the slider will be significantly increased in mass. And as you know, the inertia force of rectilinearly moving parts is equal to the product of the mass of rectilinearly moving parts and the acceleration of the piston, taken with the opposite sign. The inertia forces at the beginning of the piston stroke counteract its movement, and on the second half, on the contrary, help. But the expansion of gases in the cylinder is carried out at the beginning of the piston stroke, as can be seen from the indicator diagram / cm. book S.S. Balandin. "Rodless internal combustion engines." "Engineering", Moscow, 1972, p. 141, Fig. 1 /.

With a large mass, the inertia forces increase in the slider, and this significantly reduces the engine power and reduces the engine life.

The mechanism that converts the reciprocating motion of the pistons into rotational motion of the rotor shaft has significant disadvantages. The lack of axial translational motion of the ball relative to the slider. In view of this, the ball cannot be rolled along the profile of the groove of the rotor sleeve, but slip with increased friction, because the ball center speed is equal to half the linear piston stroke velocity

where v ₀ is the average piston stroke speed.

The height of the gutter profile from the upper inflection point to the lower point is equal to the length of the piston stroke. But when the ball is rolling along the trough, the ball passes a path equal to half this piston stroke length. And since there is no axial translational motion of the ball relative to the slide, sliding occurs with increased friction, which significantly reduces engine power.

The indicator power of each engine depends on the average indicator pressure P. With an increase in the average indicator pressure, the indicator power and the degree of use of the working volume of the cylinder increase. The maximum value of the average indicator pressure in various engines depends on many factors that are available in each particular engine.

Knowing the average indicator pressure P, it is possible to determine the indicator power of the engine.

The tangential force T tangent to the contact circle of the rotor rotation, which creates the torque, can be determined by the ratio

where P ₀ - atmospheric pressure,

β _cf - the average value of the angle of elevation of the profile of the trough along the contact track, which is 27 ° 55 ', and the tangent is 0.5298.

From the above ratio it is seen that 52.88% of the average indicator pressure is used to obtain useful work, and 47.02% is lost.

For engines with a crank mechanism, 67.29% of the average indicator pressure is used to obtain useful work with a ratio of the radius of the crank to the length of the connecting rod equal to 1/38.

Known crankless four-stroke engine, patent of the Russian Federation No. 2187673, F02B 75/25, F01B 9/06 from 04.24.2001,

The engine contains a cylinder block with axially arranged cylinders in which the pistons are arranged for reciprocating movement, a cylinder head in which the valves are installed, a block body in which a multi-period spatial power mechanism is installed, which converts the reciprocating movements of the pistons into rotational shaft movement engine. On the front and rear end surfaces of the rim of the rotor-flywheel of the multi-period spatial power mechanism, right and left directions are made of toro-screw profiles with an even number of half-periods. Each half-period of the right direction is sequentially paired with a half-period of the left direction. Half-periods are separated by elliptical and hyperbolic inflection points. Each elliptical inflection point is the top dead center of the axial piston stroke, and the hyperbolic inflection point is the bottom dead center of the axial piston stroke. The front torodo-screw profile in the radial plane is formed by an arc of a circle of the front radial curvature and is made inclined relative to the radial plane. The rear torus-screw profile in the radial plane is formed by an arc of a circle of the rear radial curvature and is made inclined relative to the radial plane.

In the fork-shaped rod heads, working and auxiliary rollers are installed, on the outer surfaces of which grooves are made. The working and auxiliary rollers are installed with the possibility of interaction with the toro-screw profiles of the rim of the rotor-flywheel. The gas distribution mechanism is made in the form of two cam rollers coaxially connected by a bevel gear. The bevel gear is kinematically connected to the bevel gear mounted on the motor shaft. Valves in the cylinders are installed at equal distances from the diametrical plane of the cylinder block and parallel to the plane.

The technical problem solved by the invention does not discredit the novelty of the invention of patent No. 2187673.

In this technical solution, it is advisable to use the design of the gas distribution mechanism, which is patented in the above patent.

The technical problem solved by the invention:

Creation of a reliable, simple and compact constructional design of a new crankless internal combustion engine, in which each cylinder is equipped with its own screw-ball mechanism, in which the reciprocating movements of the pistons are converted into rotational movements.

The full use of the forces of average indicator pressure in useful work is achieved, thereby increasing the effective engine power without changing the processes in the cylinders.

Decrease in specific fuel consumption per unit of power.

The implementation of accurate directional movement of the piston rods and pistons in the cylinders.

Decrease in mechanical losses in all kinematic pairs.

Friction reduction in translational motion pairs.

Improving engine efficiency in general.

The technical problem is solved in that each cylinder is equipped with its own rotary-ball mechanism, which converts the reciprocating movements of the pistons into rotational movements of the drive shaft. The rotor of the screw-ball mechanism is mounted coaxially with the piston rod and is connected via double row thrust and radial bearings, and is connected to the drive shaft by a ball joint. On the generatrix of the cylindrical surface of the rotor of the screw ball mechanism, right and left directions are made of arc-arc grooves with an angle of inclination of helical lines at an angle of 45 ° and with an even number of half-periods of movements. Each half-period of the right direction is sequentially conjugated with a half-period of the left direction by arcs of circles of equal curvature. The half periods are separated by the upper and lower inflection points, and each upper inflection point is the top dead center of the piston stroke, and the lower inflection point is the bottom dead center of the piston stroke. The profiles at the upper and lower inflection points are made semi-ellipsoid in the form of two lateral arcs of circles of radius R _and tangentially conjugate with arcs of contact with an angle of contact equal to 45 ° relative to the perpendicular to the axis of the rotor passing through the center of the ball and are formed convex along the turned pitch circle of the rotor cylinder and concave arcs of circles of the same radius R, which are smoothly and tangentially conjugated by helical lines of the right and left directions, and the distance from the upper inflection point is d lower inflection point equal to half the piston stroke H = 0,5S. The profiles of the right and left grooves in the cross section are arched, defined by a radius R _f , with a contact angle of 45 ° relative to the radial plane passing through the center of the ball 17. Contact raceways of the right and left grooves are made depending on the direction of movement of the piston - forward stroke " P "and return stroke" B ". In the grooves of the rotor through a half-period balls are installed, which are placed in the nests of the separator, made in the form of a ring. The cylinder block is mounted coaxially with the engine housing, and the holes made in the housing are aligned coaxially with the cylinders. Oval-shaped grooves are made in each hole of the engine casing at equal distances around the circumference, and thrust bushings are installed in these grooves of the oval-shaped profile. On the surfaces facing the rotor, these inserts have reciprocal arc troughs with a contact angle of 45 ° relative to the radial plane passing through the center of the ball of the axial direction. The balls interact with the raceways of the rotor grooves and with the raceways of the thrust liners made in the grooves. By forming the inner opening of the rotor vintosharovogo mechanism formed poluellipsovidnogo axial direction groove profile formed as two circular arcs of radius R about _LS conjugate arcs depressions with an angle of contact pressure equal to 45 ° relative to a radial plane passing through the centers of the balls. Mating half-ellipsoidal profile grooves are made along the generatrix of the cylinder surface of the drive shaft. In the grooves are rows of balls that are installed in the nests of the separator, made in the form of a sleeve. The balls are installed with the possibility of interaction with the raceways of the rotor and the drive shaft, made on the side surfaces of the grooves at the rotor and at the drive shaft. A semi-ellipse-shaped groove profile is formed along the generatrix surface of the piston rod cylinder, formed in the form of two arcs of circles with a radius R of tangents _relative to arches of valleys with a pressure angle equal to 45 ° relative to the radial plane passing through the centers of the balls with raceways on the lateral surfaces. Mating half-ellipsoidal profile grooves are also made in the hole of the rod guide sleeve. In the grooves of the piston rod and the guide sleeve, rows of balls are installed, which are installed in the nests of the separator, made in the form of a sleeve. The balls interact with the raceways of the piston rod and the guide sleeve, and the raceways are made on the side surfaces of the grooves of the guide sleeve. The drive shafts of the screw-ball mechanism are connected by their gears to the gear of the motor shaft.

The rotor of the screw-ball mechanism with a drive shaft and the piston rod with a rod guide sleeve are connected by ball joints of rolling with a contact of each ball at four points and a pressure angle of 45 ° relative to the radial plane, and the ratio of the radius R _yn to the diameter of the ball is in the range 0.505-0.520d _w .

For one revolution of the rotor of the screw-ball mechanism with six half-periods of movements, one and a half four-stroke duty cycles or three four-stroke duty cycles for two rotor rotations are carried out.

The distance from the upper inflection point to the lower inflection point of the screw-arc rotor troughs at the point-to-point contact of the balls with the screw-arc rotor troughs and the thrust liners is determined by the value of H = 0.5S, and with a three-point contact this distance will be equal to H = 2 / 3S.

With a three-point contact, the troughs of the thrust inserts are made in the form of two lateral arcs of circles of radius R _and tangentially conjugated by arcs of the troughs with a contact angle of 45 ° relative to the plane passing through the center of the ball, i.e. semi-ellipsoid.

The length of the grooves of the thrust liners is determined depending on the points of contact of the balls with the screw-arc grooves and the grooves of the thrust liners. With two-point contact, the length is H = 0.5S + 0.707d _w , and with a three-point contact this length will be H = 2 / 3S + 0.707d _w .

Along the generatrix of the cylindrical surface of the rotor of the screw ball mechanism, right and left directions are made of arc-arc grooves with an angle of inclination of helical lines at an angle of 45 ° with an even number of half-periods t, and the profiles of the grooves in the cross section / normal / are made semi-ellipsoid, formed in the form of two side arcs of circles of radius R _w conjugate arcs on the depressions to the contact angle of 45 ° relative to the perpendicular to the rotor axis passing through the center of the ball, the response to the axial direction poluellipsovidnog Trench profile in cross section and formed on the surfaces facing the rotor in the thrust bushings, and balls mounted in the troughs cooperate with contact paths forming chetyrehtochetny contact.

Depending on the purpose of the engine, the rotor of the screw ball mechanism can have four half-periods of movements, six half-periods of movements, eight half-periods of movements, etc. The contact of the balls with the gutters: two-point, three-point and four-point.

The helix elevation angles range from 20 to 60 °, and the more optimal angle is 45 °.

The number of cylinders is determined depending on the purpose of the engine and its power: two-cylinder, four-cylinder, six-cylinder, eight-cylinder, etc.

Rotary-screw motors can be made in the form of blocks connected (several blocks) by a reducer.

For example, three blocks with four cylinders in each block. In this version, the three-block four-stroke engine will have a power of 688.5 hp. or 506.3 kW. A three-block two-stroke engine with four cylinders in the block will have a power of 1377 hp. or 1012.5 kW, and the speed of 750 rpm.

Three-block two-stroke engine can be used as the main engine in a helicopter.

Engines, the cylinders of which are equipped with screw-ball mechanisms, are structurally simple. For their manufacture does not require special equipment.

Engines are environmentally friendly, because fuel consumption of 121 g / horsepower per hour or 155 g / kW hour.

The invention is illustrated by drawings.

Figure 1 shows a rotary screw four-stroke engine, a longitudinal section;

figure 2 is the same, a longitudinal section of a screw-ball mechanism;

figure 3 is the same, a top view in partial section of figure 1;

figure 4 is the same, view B in figure 3;

figure 5 is the same, the profiles of the grooves of the rotor of the expanded pitch circle;

figure 6 is the same, a cross section along aa of figure 2;

Fig.7 is the same, the cross-section of the interaction of the ball with the grooves of the rotor and the thrust liner;

on Fig is the same, the cross-section of the interaction of the balls of the ball joints of rolling with the contact of the balls at four points;

figure 9 is the same, a diagram of the interaction of the ball with the groove of the rotor and the thrust liner at the time the piston starts;

figure 10 is the same, the view of the thrust liner and its gutter;

figure 11 is the same, the interaction diagram of the ball with the groove of the rotor and the thrust liner at the time of the return stroke of the piston.

The rotary screw four-stroke engine contains a cylinder block 1, to the ends of which a motor block 2 and a cylinder head 3 are coaxially connected. In the cylinder block 1, cylinders 4 are installed in axial and diametrically opposite one another holes, in which pistons 5 are mounted with the possibility of reciprocating motion. In the engine housing 2 coaxially to the cylinders are made holes in which the rotors of 6 screw-ball mechanisms are installed, which transform the movements. Each rotor 6 is mounted on the drive shaft 7 and is coaxially connected via combined double row thrust and radial ball bearings with a piston rod 8. The rotor 6 is made in the form of a hollow cylinder with an internal flange. A groove of a persistent double-row ball bearing is made on the outer ledge of the flange. On the end surfaces of the flange 9 of the piston rod 8, grooves are made. Response troughs are also made on the outer casing 10. Between the rotor trough, rows of balls 11 are mounted in the separator sockets. Balls 11 are installed with the possibility of interaction with the grooves of the flange of the rotor 6, the flange of the piston rod and the cage 10 as a whole are a double-row thrust ball bearing. A groove is made in the hole of the flange of the rotor 6. The reciprocal chute is also made on the trunnion of the piston rod 8. Between the grooves of the rotor flange and the trunnion of the piston rod are rows of balls 12, which are located in the nests of the separator. Balls 12 are installed with the possibility of interaction with the grooves of the rotor flange and the trunnion of the piston rod, and in general are a radial ball bearing. The combined ball bearings are closed by a cover 13, and the cover is centered and fixed to the flange of the rotor 6. Along the generatrix of the cylindrical surface of the rotor 6, arc-arc grooves 14 are made with an angle of inclination of the helical lines at an angle of 45 ° with an even number of half-periods of movements. Each half-period of the right direction is sequentially conjugated with a half-period of the left direction by arcs of circles of equal curvature. Half-periods are divided by the upper 15 and lower 16 inflection points. The profiles of the troughs at the upper and lower inflection points are made semi-ellipsoidal in the form of two lateral arcs of circles of radius R _{w with} respect to the arches of the valleys with a contact angle of 45 ° relative to the perpendicular to the axis of the rotor passing through the center of the ball 17. The distance from the upper inflection point to the lower point the inflection is determined by the value of N. The value of this distance is determined in direct proportion to the number of contact points of the balls 17 with the grooves of the rotor and thrust liners.

With point-to-point contact, H = 0.5S.

With a three-point contact, H = 2 / 3S,

where S is the piston stroke.

The profiles of the right and left screw-arc rotor grooves in the cross section are arched, defined by a radius R _w with a contact angle of 45 ° relative to the radial plane passing through the center of the ball 17. The pitch circle in the cross section of the rotor 6 is aligned with the raceways of both the right and left directions of half-periods of movements. Contact raceways of the right and left gutters are made in direct proportion to the direction of movement of the piston - forward stroke "P" and return stroke "B". In the grooves of the rotor 6 through the half-period t, balls 17 are installed, which are placed in the sockets of the separator 18, which is made in the form of a ring.

Oval-shaped grooves are made in each hole in the engine casing 2 at equal distances around the circumference, in which thrust liners 19 are installed with axial grooves facing the surface of the rotor 6. The grooves of the thrust liners are made depending on the point contact of the balls 17 with the rotor grooves. When the two-point contact of the balls 17 in the chute thrust pads arc in cross section, the radius R _w outlined with contact angle of 45 ° relative to a radial plane passing through the center of the ball 17. When the three-point contact of the balls 17 in the chute thrust pads are made poluellipsovidnymi as two side an arc of circles of radius R _{f with} respect to the troughs conjugated by arcs with a contact angle of 45 ° relative to the radial plane passing through the center of the ball. In this embodiment, the balls 17 are in contact with the thrust liners at two points. Balls 17 are installed with the possibility of interaction with the grooves of the rotor and thrust liners. Along the generatrix of the cylinder of the inner hole of the rotor 6 there are made a semi-ellipsoid profile of the axial direction of the groove 20, formed in the form of two lateral arcs of circles of radius R _w , tangentially conjugated by arcs of the depressions with a contact – pressure angle of 45 ° relative to the radial plane passing through the centers of the balls 21. Response a semi-elliptical profile of the groove 22 of the axial direction is made along the generatrix of the cylinder of the drive shaft 7, between the grooves there are rows of balls 21 installed in the sockets of the separator 23, made leg in the form of a sleeve. Balls 21 are installed with the possibility of interaction with the grooves of the rotor 6 and the grooves of the drive shaft 7, and as a whole comprise a ball connection of rolling with a four-point contact of the balls with grooves. In the presence of this connection, the reciprocating motion is rolling and at the same time the transmission of torque from the rotor to the drive shaft, i.e. transmission of torque from the rotor to the drive shaft.

On the generatrix of the cylinder surface of the piston rod 8, a semi-ellipsoidal profile of grooves 24 is formed, formed in the form of two circular arcs on the sides with a radius R of the _{grooves relative} to the arches of the valleys with a pressure angle equal to 45 ° relative to the radial plane passing through the centers of the balls 25. The semi-ellipsoidal profile of the groove 26 made in the hole of the guide sleeve 27 of the piston rod. Between the grooves there are rows of balls 25 located in the sockets of the separator 28, made in the form of a sleeve. Balls 25 are installed with the possibility of interaction with raceways of the grooves of the piston rod and the guide sleeve. The guide sleeve 27 is mounted and secured to the end of the motor housing 2. The pistons 5 are centered and connected to the rod by a threaded connection and locked with a washer 29. The drive shafts 7 are mounted on ball bearings 30 and 31, and gears 32 are mounted on the shafts between the bearings. Central motor shaft 33 is mounted on three ball-bearing bearings 34, 35 and 36, and between bearings 30 and 34 a gear 37 is mounted on the shaft, which is kinematically connected to the gears of the drive shafts.

A gear 37 is mounted on the shaft 33, which is kinematically connected with the gears 32 of the drive shafts 7. The gear 38 of the oil pump drive / which is not shown in the drawing / is integral with the shaft 33. An auxiliary gear drive gear 39 and a gas distribution drive gear 40 are mounted on the central shaft 33.

The gas distribution mechanism is made in the form of two cam distribution rollers 41, coaxially connected by a bevel gear 42, which is kinematically connected with a bevel gear 40 mounted on the central shaft of the engine. Inlet 43 and outlet 44 valves are installed in the cylinder head 3 at equal distances from the diametrical plane and perpendicular to this plane. The inlet 43 and outlet 44 valves are actuated by the respective rocker arms 45 and 46, which are mounted on the axles 47. The rocker arms 45 and 46 contain adjustable screws 48, which interact with the caps 49, and rollers 50, which are installed with the possibility of interaction with the cams of the distribution rollers 41. Each camshaft has four cams located in a circle. The stem of each valve with its spring is closed by a cap 49, and each cap is made in the form of a glass and connected to the valve stem. With a bevel gear 39, a drive shaft 51 of an auxiliary machinery drive is kinematically coupled. At the end of the central shaft 33, a flywheel 52 with a clutch gear is mounted.

The main mechanism of the new engine is a rotary-ball mechanism, which converts the reciprocating movements of the pistons into rotational motion of the drive shaft, and the main part of this mechanism is the rotor 6. Rotor 6 makes complex movements - reciprocating along the axis and rotating around the same axis at the same time torque. Ball connection of the rotor 6 with the drive shaft 7 provides reciprocating motion-rolling of the rotor relative to the drive shaft 7 and simultaneously transmitting rotation and torque from the rotor to the drive shaft.

Ball connection of the piston rod 8 by the guide sleeve 27 provides reciprocating motion-rolling of the piston rod relative to the guide sleeve, as well as the linear movement of the piston relative to the cylinder.

The screw-ball mechanism has several design options that differ in the number of half-periods of movements, the presence of balls 17 in the screw-arc grooves of the rotor 6 and the number of contact points of the balls with the grooves of the rotor and thrust bearings 19.

First option

Six half-periods of movements are made along the outer cylindrical surface of the rotor, three balls 17 are installed in the grooves, which interact with the rotor grooves and thrust liners in point-to-point contact.

In this embodiment, for one revolution of the rotor 6, one and a half four-cycle cycles or three four-cycle cycles for two rotor rotations are performed.

In one half-cycle of movement, the rotor passes a path equal to 0.5S, and at the same time rotates through an angle of 60 °.

The gear ratio from the drive shaft to the engine shaft is 1.5.

Second option

Four half-periods of movements are made along the outer cylindrical surface of the rotor, two balls 17 are installed in the grooves, which interact with the rotor grooves and thrust liners at point-to-point contact.

In this embodiment, one four-stroke cycle is carried out per revolution of the rotor.

In one half-cycle of movement, the rotor passes a path equal to 0.5S, and at the same time rotates through an angle of 90 °.

The gear ratio from the drive shaft to the engine shaft is equal to one.

In the first and second embodiments, the translational speed of the rotor is equal to half the average piston speed.

Third option

In this embodiment, a three-point contact of the balls 17 with the grooves of the rotor and thrust liners is made. In this embodiment, the balls 17 are in one point in contact with the grooves of the rotor, and in two points with thrust liners.

In one half-cycle of movement, the rotor passes a path equal to 2 / 3S,

where S is the axial stroke of the piston.

The rotational speed of the rotor is equal to 2/3 of the average piston speed.

The preferred option is the first, because the rotor is centered on three points with respect to the motor housing.

Determination of power increase parameters

The main parameters for increasing power are:

The average effective pressure, since the effective engine power is directly proportional to the average effective pressure.

The average piston speed that determines engine speed.

The average effective pressure is less than the average indicator pressure by the average pressure of mechanical losses.

The average indicator pressure is the pressure that during one stroke of the piston performs work equal to the work of gases per cycle.

The average pressure of mechanical losses depends on the design of the engine, and especially on the degree of use of the working volume of the cylinder.

Large losses of average indicator pressure occur during the conversion of reciprocating movements of the pistons into rotational motion of the crankshaft.

равно 0,6729. Следовательно, для получения полезной работы используется 67,29% среднего индикаторного давления, а 32,71% теряется.For example, for an engine with a ratio of the crank radius to the length of the connecting rod equal to 1 / 3.8 in the angle of rotation of the crankshaft from 0 to 180 °, the average value of the ratio

equal to 0.6729. Therefore, to obtain useful work, 67.29% of the average indicator pressure is used, and 32.71% is lost.

In a rotary-ball engine, along the cylindrical surface of the rotor 6, the screw-arc grooves are made with a helix angle of 45 °, and the average reduced angle tangent is 0.9469. To obtain useful work, 94.69% of the average indicator pressure is used, and 5.31% is lost. As a result, the average effective pressure increases by 27.4% relative to existing engines.

The average piston speed, which determines the engine speed, is determined taking into account the number of half-periods of movements in relation to

where Z is the number of half-periods of movements,

S - piston stroke, m,

n is the number of revolutions of the rotor, rpm

For example, with six half-periods of movements and 1500 rpm of the rotor, and the piston stroke is 0.1 m, the average piston speed is 15 m / s.

This makes it possible to force the engine for speed.

Engine operation

The sequential interaction of the cylinders is carried out through the drive shafts 7 of the gears 32, which are kinematically connected with the gear 37 mounted on the motor shaft 33.

The workflow is a set of sequential and periodically repeating cycles in each cylinder of the engine. Workflows that occur during one stroke of the piston / part of the duty cycle / are called tact.

The strokes of a four-stroke engine: 1 - inlet or filling, 2 - compression, 3 - combustion and expansion / stroke /, 4 - exhaust gases.

The operation of the cylinders per revolution of the engine shaft is given in table 1.

Table 1 Cylinders The first Second Third Fourth So you one four 3 2 2 one four 3 3 2 one four four 3 2 one

At the moment of direct piston stroke from the top dead center to the bottom dead center, the rotor passes the path from the lower inflection point to the upper inflection point. At the moment the piston returns from the bottom dead center to the top dead center, the rotor passes from the upper inflection point to the lower inflection point.

At the moment of the rotor movements, the balls 17 together with the separator 18 make movements from the lower position to the upper and back from the upper position to the lower.

In the process of the third stroke / third cylinder / there is combustion and expansion / stroke / with a direct stroke of the piston. At the beginning of a measure, the fuel received at the end of the second measure is burned up intensively. Due to the release of large amounts of heat, the temperature and pressure in the cylinder increase sharply. Under pressure, the piston moves and the gases expand.

The resulting force from the gas pressure on the piston through the piston rod is transmitted to the rotor and balls 17 and is evenly distributed between the balls, forming three component forces. These components in the interaction of the balls 17 with screw-arc grooves of the rotor 6 and with the grooves of the thrust liners 19 are expanded, forming circumferential forces tangent to the pitch circle of the profiles of the rotor grooves.

From the expansion of gases in the cylinder, the piston makes a direct stroke, and the rotor makes complex movements, travels from the lower inflection point to the upper inflection point and at the same time rotates around the axis by a rotation angle of 60 °. The rotational movement from the rotor 6 is transmitted through a ball connection to the drive shaft 7. And from the drive shaft through the gear 32 sitting on the drive shaft, the gear 37 mounted on the central shaft of the engine. The gear ratio of the gears is 1.5, during which time the central shaft 33 of the engine will rotate through an angle of 90 °.

Similar gas expansion cycles are sequentially carried out in the remaining cylinders, and the order of the cylinders is 1-2-3-4.

Thus, for one revolution of the engine shaft, four gas expansion cycles are carried out, one cycle in each cylinder.

Flywheel 52 is a battery of kinetic energy. During gas expansion cycles, part of the work performed in the cylinders is useful, part is spent on overcoming mechanical losses, and the rest is excess work spent on increasing the kinetic energy of the moving parts of the remaining compression, intake and exhaust cycles.

With four gas expansion strokes successively in four cylinders for one revolution of the motor shaft 33, smaller fluctuations in the angular velocity of the shaft are provided, i.e. less uneven engine rotation.

With a six-half-rotor, six strokes of the piston are carried out, and one and a half four-cycle cycles are performed in the cylinders per revolution of the rotor. During this same time, the engine shaft will make a half turn.

With a four-half-rotor, four piston strokes are performed, and in the cylinders one four-stroke cycle is performed per revolution of the rotor, and the engine shaft makes one revolution.

The main characteristic of each engine is power. The power of a rotary-ball engine is determined by a similar methodology as that of engines with a crank mechanism, but taking into account the tact ratio of this engine.

In the numerator of the ratio for determining engine power, the values are entered - the piston stroke and the number of shaft revolutions. But these values determine the average speed of the piston C. Replacing in this ratio the values — the piston stroke and the number of shaft revolutions by the average piston speed C and, accordingly, specifying the number in the denominator, we obtain two relations in the form of equality

where F is the piston area, cm ² ,

Pe is the average effective pressure, kgf / cm ² ,

n is the number of cylinders.

In the second ratio, the average piston speed and the average effective pressure are the main values that determine the power of a rotary-ball engine, and their values are defined above.

To compare the qualitative assessment, I give the characteristics of the engine of the Ulyanovsk plant "Volga Motors" type UMZ-249.10 and two screw-ball engines, which are given in table No. 2.

table 2 Name UMP-249.10 Rotary engines 1. The diameter of the cylinder, mm
2. Piston stroke, mm one hundred one hundred
92 one hundred
one hundred 92 3. The number of cylinders four four four 4. The degree of compression 8.8 8.8 8.89 5. The working volume, l 2.89 2.89 3.14 6. Ef. pressure, kgf / cm ² 10.38 14.61 14.61 7. The speed of the piston, m / s 13.8 13.8 15.0 8. Engine power, hp 150 211 229.5 9. Liter power, hp / l 51.9 73 73.1 10. Rotation, rpm 4500 1500 1500 11. Fuel consumption g / h.p. 185 131 121

The table above shows that with an increase in the average piston speed of 1.2 m / s, the power increases by 18.5 hp.

Based on the thermodynamic calculation, the average indicator pressure of the rotary-ball engine is determined, the value of which is P = 15.426 kgf / cm ² .

The average effective pressure is determined by the equation

P = 15.426 × 0.9469 = 14.61 kgf / cm ² .

To improve the efficiency of a rotary-ball engine, the duty cycle is carried out with a continuous expansion, the essence of which is as follows. The nominal compression ratio is increased by 1 ... 2 units, and so that the engine does not detonate, we increase the angle of the closing delay of the intake valve 43. In this case, part of the charge is ejected from the cylinder at the beginning of the compression stroke, as a result of which the beginning of the charge compression process is delayed, i.e. The actual compression ratio is reduced. The degree of expansion, on which profitability mainly depends, remains equal to the nominal degree of compression, i.e. greater than the actual compression ratio.

To compensate for the decrease in cylinder charge, it is necessary to increase the piston stroke accordingly. In this engine, an increase in the piston stroke slightly affects the dimensions of the engine.

The use of the extended extension cycle as a means of increasing efficiency in rotary-ball engines is advisable, because specific fuel consumption is reduced by 10-12% compared with the usual cycle.

The degree of perfection of the design of a rotary-ball engine is explained by the fact that each cylinder is equipped with a rotary-motion-converting mechanism. One of the main advantages of this mechanism is that the conversion of the reciprocating movements into rotational movements is carried out by the interaction of the balls 17 with the screw-arc grooves of the rotor 6 and with the grooves of the thrust liners 19 with minimal power loss to overcome friction.

Ball joints of rolling / rolling guides /, the main advantages of which are: low resistance to movement, independence of this resistance from speed, insignificant difference between the forces of rest friction and movement. This allows you to provide both fast and slow uniform movements, as well as high accuracy of the installation positions of the moving piston relative to the cylinder, the rotor relative to the motor housing 2 and relative to the drive shaft 7.

With accurate and rectilinear movement of the piston relative to the cylinder, reliable operation of the piston-cylinder group is ensured and the engine's engine life is increased.

A variant of the four-point contact of the balls 17 with the screw-arc rotors of the rotor and the channels of the thrust liners. The profiles of these grooves in the cross section / normal / are semi-ellipsoidal with raceways along the lateral surfaces, the contact angles are 45 ° relative to the perpendicular to the axis of the rotor 6 passing through the center of the ball 17. The value of this angle allows better control of the dimensions, reduce contact stress between the balls and gutters under any working conditions, but in general the service life of the mechanism increases. This is confirmed by the fact that in the process of interaction of the balls 17 with the grooves, the load acting on each ball is equally distributed between two forces.

Screw-ball mechanisms can be widely used in two-stroke engines.

For example, a two-stroke engine, the cylinders of which are equipped with screw-ball mechanisms, and their rotors have six half-periods of motion each. For one revolution of the rotor, three push-pull duty cycles are carried out. With four cylinders with a diameter of 100 mm and an average piston speed of 15 m / s, the engine power will be 459 hp. or 337.5 kW, and liter 146.2 hp / l or 107.5 kW / l.

Rotary-screw engines can be widely used in cars, tractors, tanks, helicopters, hydrofoils, mobile generators and other vehicles and technical fields where simplicity and compactness, light weight and minimal vibration are of paramount importance.

In addition, piston compressors and piston pumps of various capacities can be created with a screw-ball mechanism. In these machines, rotational movements are converted into rectilinear reciprocating movements.

Equations, definitions of geometric dimensions, half-periods of movements and diameters along the pitch circle are contained in the method for calculating rotary-ball engines.

Claims (3)

1. A rotary screw four-stroke engine containing a cylinder block with axially arranged cylinders in which the pistons are arranged for reciprocating motion, a cylinder head in which the intake and exhaust valves are installed, a motor housing in which the mechanism for converting the reciprocating pistons is installed in the rotational movement of the shaft, along the generatrix of the rotor cylinder of this mechanism, the right and left directions are made of arc grooves, immersed in these grooves balls half the diameter, and the second half of the diameters are installed in the spherical holes of the sliders, the balls are installed with the possibility of interaction with the grooves of the rotor and with the spherical holes of the sliders in the interaction of small balls, and the sliders are connected by rods with pistons, characterized in that each cylinder is equipped with its own screw ball a mechanism that converts the reciprocating motion of the piston into the rotational movement of the drive shaft, the rotor of the screw-ball mechanism is mounted coaxially with the piston rod and soy Dinan through double-row thrust and radial ball bearings, and connected to the drive shaft by a ball joint, along the generatrix of the cylindrical surface of the rotor of the screw-ball mechanism are made right and left directions arc-arc grooves with an angle of inclination of the helical lines at an angle α with an even number of half-periods of movements t, each half-period of the right direction sequentially interfaced with a half-period of the left direction by arcs of circles of equal curvature, half-periods are separated by upper and lower inflection points, each upper inflection point is the top dead center of the piston stroke, and the lower inflection point is the bottom dead center of the piston stroke, the profiles at the upper and lower inflection points are made semi-ellipsoid in the form of two lateral arcs of circles of radius R _z , tangent to the arcs of the depressions with a contact angle equal to 45 ° relative to the perpendicular to the axis of the rotor passing through the center of the ball 17, and along the unfolded pitch circle of the rotor cylinder on a plane are formed by convex and concave arcs of circles with the same a value of radius R, which are smoothly and tangentially connected with helical lines of the right and left directions, and the distance from the upper inflection point to the lower inflection point is equal to half the stroke of the piston 0.5S, the profiles of the right and left grooves in the cross section are arched, outlined by the radius R _w an angle of contact equal to 45 ° relative to the radial plane passing through the center of the ball 17, the contact raceways of the right and left grooves are made depending on the direction of movement of the piston - forward stroke "P" and return stroke "B", in the grooves mouth In half a period, balls are installed, which are placed in the nests of the separator made in the form of a ring, the cylinder block is mounted coaxially with the engine housing, and the holes made in the housing are aligned coaxially with the cylinders, in each opening of the engine housing equal grooves are made of equal oval profile , in these grooves there are installed oval-shaped profile thrust liners, on the surfaces facing the rotor at these liners there are reciprocal arc troughs with a contact angle of 45 ° relative to the radial of the plane passing through the center of the ball of the axial direction, the balls interact with the raceways of the grooves of the rotor and with the raceways of the thrust liners made in the grooves, along the generatrix of the inner hole of the rotor of the screw-ball mechanism there are made a semi-ellipsoid profile grooves of the axial direction, formed in the form of two side arcs of circles of radius R _Well, with regard to conjugate arcs cavities with a pressure angle of 45 ° relative to a radial plane passing through the centers of the balls, the response poluellipsovidnog groove profiles are made along the generatrix surface of the drive shaft cylinder, rows of balls are placed in the grooves, which are installed in the seats of the separator made in the form of a sleeve, balls interact with the raceways of the rotor and the drive shaft, made on the side surfaces of the grooves near the rotor and the drive shaft, on the lateral surface of the piston rod of the cylinder formed poluellipsovidnogo groove profile formed as two circular arcs of radius r _w, about conjugated arcs depressions pressure angle p 45 ° relative to the radial plane passing through the centers of the balls with raceways on the lateral surfaces, the response semi-ellipse-shaped grooves are made and in the holes of the rod guide sleeve, rows of balls are installed in the grooves of the piston rod and rod guide sleeve, which are installed in the seats of the separator made in in the form of a sleeve, balls interact with the raceways of the piston rod and the guide sleeve, which are made on the side surfaces of the grooves of the guide sleeve, drive shafts intosharovyh gear mechanisms are connected to the sixfold of the motor shaft. 2. The engine according to claim 1, characterized in that along the cylindrical surface of the rotor of the screw-ball mechanism, grooves are made containing six half-periods of motions t in which three balls 17 are placed, and three thrust liners are installed in the opening of the engine housing, with one rotation of the rotor one and a half four-cycle cycles or three four-cycle cycles for two rotor rotations are carried out. 3. The engine according to claim 1, characterized in that along the cylindrical surface of the rotor of the screw-ball mechanism on the surfaces facing the rotor of the thrust liners, semi-elliptical profile grooves are made in the form of two side arcs of circles of radius R _w , relative to the arches of the troughs with a contact angle equal to 45 ° relative to the perpendicular to the axis of the rotor passing through the center of the ball 17, while the balls 17 interact with the grooves, making contact at four points.

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