The mechanism may be used in astronautics, aircraft, shipbuilding, motor car construction, motorcycle construction, mining, radio electronics, power engineering, and other sectors of industry. The mechanism supposed is ideally suitable for the construction and manufacture of new type internal combustion engines, processing machine-tools, civil engineering, food production equipment, fixing-raking mechanisms, and etc.

There are known different gearwheel mechanisms at a technical level: from the simplest onstage gears to multistage gears constructed by means of consecutive connection of several onstage gears; from the units installed into mechanisms, devices, and machines to autonomous assemblies-reduction gears, gear-boxes, planetary gears, and differential mechanisms.

Mechanisms accomplishing the same task, namely the transformation of one type of motion into another type of motion, as the task performed by the mechanism supposed are also known, e. g. , the mechanism described in US patent No. 5 212 996. From the constructional standpoint, this mechanism is quite complex and includes planetary pinion gears.

The new mechanism supposed to be patented has been designed on the basis of a gearwheel mechanism for the transformation of rectilinear motion into rotary motion and vice versa, which has been described by the authors of this application in application LT 2001-102 (published by the State Patent Bureau in bulletin No. 4,2001) or in international publication WO 03/033945. The mechanism described in the publications mentioned includes a drive shaft with a conical pair of gearwheels fixed to its end. On the both sides of the drive shaft, symmetrically in regard to it, the crankshaft and external and internal engagement gearwheel systems, which are connected to each other by means of an idler wheel, are positioned.

In the mechanism mentioned, large axial forces act on the drive shaft. In addition to this, the sphere of application of the mechanism becomes narrower due to the running crankshaft ends positioned on the opposite sides of the mechanism.

The purpose of the supposed invention is to create a gearwheel mechanism as simple as possible, which would simplify all mechanical equipment and mechanisms which use wasteful mechanisms and equipment to transform rectilinear motion into rotary motion (for example, internal combustion engines). One amongst more specific tasks of this supposed invention is to reduce to a minimum the axial forces of a shaft and to use the obtained result of transformation in a more effective way.

The supposed gearwheel mechanism for the transformation of rotary motion into rectilinear motion and vice versa includes a drive shaft connected through the system of a gearwheel with crankshafts and the gearwheels placed on them. The innovation of this mechanism is that the gearwheel fixed to the drive shaft is engaged with two gearwheels with the same diameters symmetrically arranged in regard to this shaft. Crankshafts to the free ends of which movable crankshafts are installed are immovably fixed to the axes of these gearwheels ; the gearwheels engaged with having the same diameter gearwheels of internal and external engagement, connected to each other by means of external engagement, are immovably fixed to the movable crankshafts mentioned. The gearwheels mentioned perform a balancing function: they do not allow the free ends of crankshafts to revolve sideways by pushing the crankshaft axis, in this way the ends of the crankshafts perform rectilinear motion. In addition to this, the radiuses of all crankshafts and the gearwheels fixed to them have different values. However, they are arranged so that the radius of the crankshaft located on one side of the shaft axis is equal to the radius of a gearwheel located on the other side of the shaft axis and fixed to the crankshaft, whereas the total sum of radiuses of crankshafts is equal to the diameter of the internal engagement gearwheel.

The supposed invention may provoke large changes in the theory of machines and mechanisms, thereby this mechanism enables in the most rational way to use the force obtained and transferred in the course of rotary or rectilinear motion, to ensure the long lasting operation of such mechanisms, and to obtain accurate, even, rectilinear, and complex cyclic motions. In addition to this, the supposed mechanism is transforming rectilinear motion into rotary motion and vise versa by means of simple gearwheel drive systems only.

The possibility to express by a formula the motion of free ends of crankshafts, the possibility to enable the free ends of crankshafts to pass different distances, the possibility to enable the free ends of crankshafts to move at different angles including 0 ° and 180 ° should be added to the advantages of the supposed mechanism.

The supposed invention is explained by working drawings. The schematic diagram of the supposed mechanism is presented in the Fig. 1; the sectional view of the supposed mechanism-in Fig. 2; the kinematic diagrams of motion of the left and right sides of the supposed mechanism-in Fig. 3 and 4 appropriately.

The supposed mechanism includes casing 1 with drive shaft 2 installed in it, which by means of gearwheel 3 engaged with two having the same diameter gearwheels 4 and 5 and with immovably connected with the gearwheels mentioned crankshafts 6 and 7, on the ends of which movable crankshafts 8 and 9 are installed with immovably installed on them crankshafts 10 and 11, which are connected with having the same diameter gearwheels 12 and 13, which have internal and external engagements. The external engagement is rotating gearwheels 12 and 13 in different directions, whereas the free ends of movable crankshafts 8 and 9 are in rectilinear motion due the internal engagement of gearwheels 10 and 11 with gearwheels 12 and 13.

The radiuses rl of located on one side of the supposed mechanism crankshafts 7 and 9 are equal in regard to the axis of shaft 2 and radiuses r2 of located on the other side of shaft 2 crankshafts 6 and 8 are equal as well, whereas the sum of radiuses of all crankshafts is equal to the diameter 2r3 of the internal engagement gearwheel 12 or 13.

The mechanism supposed differs from other similar mechanisms in the following way.

When shaft 2 is rotating: 1. Distances of motion of free ends of crankshafts 8 and 9 may be different; 2. An angle of direction of motion of free ends of crankshafts 8 and 9 in regard to each other may be different-from 0 ° to 180 ° ; 3. The distance of motion of the free ends of crankshafts 8 and 9 may be different; 4. When acting on the free ends of crankshafts 8 and 9 by force that is in rectilinear motion, a torque for shaft 2 is obtained; 5. In the same plane, the rectilinear motion of two points is obtained either in the same direction or in an opposite direction or at an angle to each other.

The supposed mechanism operates in the following way: Drive shaft 2 installed in casing 1 is rotating gearwheel 3, which is engaged with two having the same diameter gearwheels 4 and 5, which are symmetrically positioned on the opposite sides of gearwheel 3 or shaft 2. Crankshafts 6 and 7 are immovably installed on axes of gearwheels 4 and 5. Movable crankshafts 8 and 9 are installed on the free ends of these crankshafts, whereas gearwheels 10 and 11 immovably installed on the mentioned crankshafts 8 and 9 by means of internal engagement are connected with having the same diameter gearwheels 12 and 13 of internal and external engagement. These gearwheels are permanently connected by external engagement and rotate in opposite sides. Their task is to balance the motion of the free ends of crankshafts 8 and 9, by shifting the axis of a crankshaft they prevent the free ends of crankshafts from rotating aside. In this way, when rotating around their axis, the free ends of crankshafts 8 and 9 are in rectilinear motion.

The radiuses r, of located on one side of the supposed mechanism crankshafts 7 and 9 are equal in regard to the axis of shaft 2 and radiuses r2 of located on the other side of shaft 2 crankshafts 6 and 8 are equal as well, whereas the sum of radiuses of all crankshafts is equal to the diameter 2r3 of the internal engagement gearwheel 12 or 13.

Let us to consider the operation of the supposed mechanism.

Since: 2rl + 2r2 = 2r3, where r1 + r2 = r3, thus, radius RI, of gearwheel 11 equals to: Ril = r2.

Radius R10 of gearwheel 10 equals to: Rio = pi.

The sum of radiuses of gearwheels 11 and 10 is equal to radius R12 of an internal engagement gearwheel: R12 = R10 + R11 = r1 + r2 = r3.

Radiuses RIO and Rll of gearwheels 11 and 10 are not equal to each other and differ from the value r3/2 by the same value: 10 - R11 = r3 - 2r2 = 2rl-r3- Therefore gearwheels 10 and 11 with radiuses : R10 = r1 and R11 = r2, - will make the following number of rotations per rotation of gearwheels 4 and 5: 2 #r3 + 2 # (2r1 - r3) 2 #r3 + 4 #r1 - 2 #r3 = = 2 n (rotations); 2 #r1 2 #r1 2 #r3 - 2 #(r3 - 2 r2) 2 #r3 - 2 #r3 + 4 #r2 <BR> <BR> = = 2 n (rotations).<BR> <P> 2 #r2 2 #r2 Since gearwheels 12 and 13 rotate in opposite sides, the distance passed by gearwheel 11, the radius of which is Rll = r2, becomes longer by value l11 equal to: l11 = 2 # (2 r2 - r3).

The distance passed by gearwheel 10, the radius of which is R10 = r1, becomes shorter by value 1, 10 equal to: l10 = 2 # (r3 - 2 r1).

The free ends of crankshafts 8 and 9 are shifted from a dead point by means of gearwheel engagement, therefore an angle between drive crankshafts may have values from 0° to 180°.

The equation of motion of the free ends of crankshafts 8 and 9.

Let us consider the left and right sides of the mechanism together (Fig. 3 and Fig. 4).

As the crankshaft CM is turning at an angle oc (Fig. 3), the point B moves forward to the point BI ; the central point A of gearwheel 11, whose radius R11 = r2, moves forward to point As ; the direction of rotation of gearwheel 13, whose radius 13 = r3, is opposite to the direction of rotation of the crankshaft OA.

The distance passed by the point B - Sy will be equal to: Sy = OB-OBI = BB1 ; Since the triangle OA, BL is an isosceles one: OA, = Bl ; OC CBi = OA, cos a = ABl cos a ; then: OB, OA, cos a + A, B, cos a r, cos a + r1 cos ez = 2 r, cos a.

Sy = 2 ri-2 rl cos a = 2 rl (I-cos a) ; Since: r1 = r3 = r2, then: Sy = 2(r3 - r2)(1 - cos α); ymax = 2(r3 - r2), if α = 00; yn = = - 2(r3 - r2), if α = 180 ; .

As the crankshaft O1A1 is turning at an angle α (Fig. 4), point B, moves forward to point B2 ; the central point A1 of gearwheel 10, whose radius R, = rs, moves forward to point A2; whereas gearwheel 12, whose radius Rs2 = r3, will rotate in the same direction as the crankshaft Oral.

The distance passed by point B1 - Sy will be equal to: Sy = O1B1 - O1B2; According to the triangle OlA2B2, OIA2 = A2B2.

O1C1 = C1B2 = O1A2 cos α = A2B2 cos a, then: O1B2 = O1A2 cos α + A2B2 cos α = r2 cos α + r2 cos α = 2 r2 cos a.

Sy = 2 r2 - 2r2 cos α = 2r2 (1 - cos α); since: r2 = r3 - r1, then: Sy = 2 (r3 - r1)(1 - cos α). ymax = 2(r3 - r1), if angle α = 1800, ymin = - 2 (r3 - r1), if angle α = 0°.

Smax = 4 (r3 - r1).

The supposed mechanism has the following advantages in comparison with other known mechanisms transforming rotary motion into rectilinear motion: firstly, the supposed mechanism has more simple structure, whereas the operating free ends of crankshafts are positioned on one side of the supposed mechanism; secondly, unbalanced exertions eliminate perpendicular force acting the longitudinal axis of a shaft. In addition to this, the manufacture of the supposed mechanism is comparatively cheap due to the simple structure of parts.