Cam machine with adjustment mechanism

Abstract

The invention relates to a cam machine with a control mechanism which will find application in various fields of mechanical engineering, such as compressor machines, hydraulic pumps, internal combustion engines and other types of engines in various land, sea and air vehicles, or in stationary units. The created cam machine improves the contact between the cam profiles (15a, 15b) of the cam bushings (16a, 16b) and the followers (1a, 1b). The main improvement of the machine is in the design of the regulating mechanism, which increases the reliability and the service life of the cam machine. In addition, simple and reliable control mechanisms are integrated in the machine, which at the same time simplifies the process of adjusting the cam machines.

Claims

1. A cam machine comprising: a housing (22, 31 and 21), a first and a second cylinder (26), a first piston (25) moving in the first cylinder (26) and a second piston (25) moving in the second cylinder (26), a cylindrical tubular 3D cam (20) with a cam channel on an inner cylindrical surface which channel is made so that a line forming its cross section is a concave line having two cam profiles (15a, 15b) and a bottom (59) between them, which is laterally located relative to an axis of the cylindrical tubular 3D cam (20) and at least two asynchronously moving followers (1a, 1b) located opposite each other, each follower (1a, 1b) containing two arms (37) connected respectively to one of the first and second pistons (25), wherein the two arms (37) are spaced at an angle to each other and are provided with tubular main bearing journals (2) with main rollers (3) each having an axis and placed in bearings at a free end of the respective arms (37) and each follower (1a, 1b) further comprises cylindrical plungers (6) located in the tubular main bearings journals (2), which cylindrical plungers (6) comprise additional bearing journals (4) bearing additional rollers (5), performing both rectilinear and rotational movement in a direction and around axes of the respective main rollers (3) so that each main roller and additional roller (3 and 5) is in contact with its respective profile (15a or 15b) of the cam channel, characterized in that the tubular main bearing journals (2) have threaded holes (13) in which screw regulators (7) are mounted, contacting indirectly or directly with the cylindrical plungers (6), where the indirect contact between the cylindrical plungers (6) and adjacent screw regulators (7) is made through elastic and bearing elements (8) and (10), and the direct contact is realized by pins (11), each of which is part of the corresponding adjacent screw regulator (7), where maximum clearances (57) formed by the indirect contacts between the pins (11) and the plungers (6) are at least equal to strokes of rectilinear motions of the plungers (6) at complete rotation of the cylindrical tubular 3D cam (20), and connections between each plunger (6) and the elements located in its respective bearing journal (2) are such that the plungers (6) are freely removable from the adjacent bearing journals (2) when the cam machine is disassembled.

2. The cam machine according to claim 1, characterized in that a functional insert (56b) is mounted in each plunger (6) in contact with the pin (11) while making direct contact between the respective screw regulator (7) and the plunger (6), wherein a thickness of a functional insert (56b) is adjustable by a thickness of a respective test insert which is monolithic or composed of several elements (9a, 9b and 9a), and at least one element (9b) of the test insert is easily deformable, as the reference thickness of the test insert (9a, 9b and 9a) is obtained by squeezing it under a working influence of the cam machine.

3. The cam machine according to either of claim 1 or 2, characterized in that each screw regulator (7) consists of a tubular cylindrical body (46), on an outer and an inner cylindrical surfaces of which an external and an internal thread are cut, respectively, an adjustable pin (47) and a fixing element (48) are screwed in the internal thread, and the clearance between each adjustable pin (47) and the adjacent plunger (6) of the functional insert (56b) being at least equal to an axial stroke of the plunger (6) at one complete rotation of the cylindrical tubular 3D cam (20).

4. The cam machine according to claim 1, characterized in that the cylindrical tubular 3D cam (20) is composite and comprises two cam bushings (16a, 16b), each having a corrugated cam profile (15a and 15b) on one side, and cam bushings (16a and 16b) are arranged at a distance from each other with their corrugated ends facing each other presenting convex parts of the cam profile of one of the bushings (16a, 16b) opposite to recesses of the cam profile of the other bushing (16a, 16b) comprising at least two guide columns (27) for reciprocating linear motion of each followers (1a and 1b), which columns (27) are parallel and equidistant from the axis of the cylindrical tubular 3D cam (20).

5. The cam machine according to claim 1, characterized in that the cam channel is made so that an upper and a lower dead centres (49, 50) a distance between the cam profiles (15a, 15b) of the channel of the cylindrical tubular 3D cam (20) in the cross section is the largest, and the distance in the cross section (55) between the cam profiles (15a, 15b) of the channel of the 3D composite cam (20) between any two adjacent dead centres (49, 50) is the smallest, so that the movement of the additional bearing rollers (5) along the axes of the main bearing rollers (3) is minimized.

6. The cam machine according to claim 1, characterized in that the cam channel is designed in such a way that narrow grooves (51) are formed along rolling lines of the additional bearing rollers (5), having the greatest depth in the upper and the lower dead centres (49, 50) and their depths between any two adjacent dead centres (49, 50) are minimal, so that the movement of the additional bearing rollers (5) along the axes of the main bearing rollers (3) is minimized.

7. The cam machine according to claim 4, characterized in that each of the two cam bushings (16a and 16b) of the cylindrical tubular 3D cam (20) is fixedly and coaxially connected to a tubular element (19) which is located between them.

8. The cam machine according to claim 4, characterized in that the connection and orientation between the two cam bushings (16a and 16b) of the cylindrical tubular 3D composite cam (20) is made by a tubular element (41) which is a rotor of an electric machine and transmission of torque between the cam bushings (16a and 16b) is realized by means of teeth (43) and sockets (42), which are located on contact fronts of the cam bushings (16a and 16b), and a stator (68) of the electric machine is fixedly connected to the housing elements (31) of the cam machine.

9. The cam machine according to claim 4, wherein a connection and orientation between the two cam bushings (16a and 16b) of the cylindrical tubular 3D cam (20) is made by two flanges (36a and 36b), one flange on each of the bushings (16a) and (16b), which flanges (36a and 36b) are located around the sides of the corrugated cam profiles (15a) and (15b), the connection between the flanges (36a) and (36b) being fixed and secured by orienting fasteners.

10. The cam machine according to claim 9 characterized in that a gear ring (45) is made on a periphery of the flanges (36a) and (36b) for transmitting mechanical energy to an external working machine or for receiving energy from an external source of mechanical energy.

11. The cam machine according to claim 4, the wherein a connection and orientation between the two cam bushings (16a and 16b) of the 3D composite cam (20) is made by at least two lugs (39a or 39b) located around the sides of each of the bushings (16a and 16b) having corrugated cam profiles (15a and 15b) and connected together, wherein the connection between the lugs (39b) and (39a) of the cam bushings is fixed and is provided by means of orienting fasteners.

12. The cam machine according to claim 4 further comprising a two-cylinder compressor or hydraulic pump characterized in that the two-cylinder compressor or hydraulic pump comprise at least one cylinder head (61), hermetically dosing the cylinder (26) or one of the cylinders (26), performing a working cycle in it, wherein a fluid exchange accompanying filling and emptying processes of the cylinder (26) or the cylinders (26) is effected by a means (71) and (72) for opening and closing the compressor chamber (73).

13. The cam machine according to claim 12, characterized in that it has at least one cylinder head (61), hermetically closing the cylinder (26) or one of the cylinders (26), performing an operating cycle in it, wherein the fluid exchange accompanying the operating cycles in the cylinder (26) or cylinders (26) is realized by at least one kinematic circuit consisting of a 2D cam (40a or 40b) which is fixedly connected to a nearest adjacent side of the 3D composite cam (20), and rocker (64a or 64b), which can rotate around axis (62) under the influence of the 2D cam (40a or 40b), at least one suction or discharge valve (65a or 65b) performing reciprocating motion under the influence of the rocker (64a or 64b) and at least one return spring (67) holding the suction or discharge valve (65a or 65b) in a closed position when not activated by the rocker (64a or 64b).

14. A cam machine comprising: a housing (22, 31 and 21), a cylinder (26), a piston (25) moving in the cylinder (26), a cylindrical tubular 3D cam (20) with a cam channel on an inner cylindrical surface which channel is made so that a line forming its cross section is a concave line having two cam profiles (15a, 15b) and a bottom (59) between them, which is laterally located relative to an axis of the cylindrical tubular 3D cam (20) and an asynchronously moving followers (1a, 1b) located opposite each other, each follower (1a, 1b) having two arms (37) connected respectively to one of the piston (25) and a balancing element (60), wherein the two arms (37) are spaced at an angle to each other and are provided with tubular main bearing journals (2) with main rollers (3) each having an axis placed in bearings at a free end of the respective arms (37) and each follower (1a, 1b) further comprises cylindrical plungers (6) located in the tubular main bearings journals (2), which cylindrical plungers (6) comprise additional bearing journals (4) bearing additional rollers (5), performing both rectilinear and rotational movement in a direction and around axes of the respective main rollers (3) so that each main roller and additional roller (3 and 5) is in contact with its respective profile (15a or 15b) of the cam channel, characterized in that the tubular main bearing journals (2) have threaded holes (13) in which screw regulators (7) are mounted, contacting indirectly or directly with the cylindrical plungers (6), where the indirect contact between the cylindrical plungers (6) and the adjacent screw regulators (7) is made through elastic and bearing elements (8) and (10), and the direct contact is realized by pins (11), each of which is part of the corresponding adjacent screw regulator (7), where maximum clearances (57) formed by the indirect contacts between the pins (11) and the plungers (6) are at least equal to strokes of rectilinear motions of the plungers (6) at complete rotation of the cylindrical tubular 3D cam (20), and connections between each plunger (6) and the elements located in its bearing journal (2) are such that the plungers (6) are freely removable from the bearing journals (2) when the cam machine is disassembled.

15. The cam machine according to claim 14, characterized in that a functional insert (56b) is mounted in each plunger (6) in contact with the pin (11) while making direct contact between the respective screw regulator (7) and the plunger (6), wherein a thickness of a functional insert (56b) is adjustable by a thickness of a respective test insert which is monolithic or composed of several elements (9a, 9b and 9a), and at least one element (9b) of the test insert is easily deformable, as the reference thickness of the test insert (9a, 9b and 9a) is obtained by squeezing it under a working influence of the cam machine.

16. The cam machine according to claim 14, characterized in that each screw regulator (7) consists of a tubular cylindrical body (46), on an outer and an inner cylindrical surfaces of which an external and an internal thread are cut, respectively, an adjustable pin (47) and a fixing element (48) are screwed in the internal thread, and the clearance between each adjustable pin (47) and the adjacent plunger (6) of the functional insert (56b) being at least equal to an axial stroke of the plunger (6) at one complete rotation of the cylindrical tubular 3D cam (20).

17. The cam machine according to claim 15, characterized in that each screw regulator (7) consists of a tubular cylindrical body (46), on an outer and an inner cylindrical surfaces of which an external and an internal thread are cut, respectively, an adjustable pin (47) and a fixing element (48) are screwed in the internal thread, and the clearance between each adjustable pin (47) and the adjacent plunger (6) of the functional insert (56b) being at least equal to an axial stroke of the plunger (6) at one complete rotation of the cylindrical tubular 3D cam (20).

18. The cam machine according to claim 14, characterized in that the cylindrical tubular 3D cam (20) is composite and comprises two cam bushings (16a, 16b), each having a corrugated cam profile (15a and 15b) on one side, and cam bushings (16a and 16b) are arranged at a distance from each other with their corrugated ends facing each other convex parts of the cam profile of one of the bushings (16a, 16b) opposite to recesses of the cam profile of the other bushing (16a, 16b) comprising at least two guide columns (27) for reciprocating linear motion of each followers (1a and 1b), which columns (27) are parallel and equidistant from the axis of the cylindrical tubular 3D cam (20).

19. The cam machine according to claim 14, characterized in that the cam channel is made so that an upper and a lower dead centres (49, 50) a distance between the cam profiles (15a, 15b) of the channel of the cylindrical tubular 3D cam (20) in the cross section is the largest, and the distance in the cross section (55) between the cam profiles (15a, 15b) of the channel of the 3D composite cam (20) between any two adjacent dead centres (49, 50) is the smallest, so that the movement of the additional bearing rollers (5) along the axes of the main bearing rollers (3) is minimized.

20. The cam machine according to claim 14, characterized in that the cam channel is designed in such a way that narrow grooves (51) are formed along rolling lines of the additional bearing rollers (5), having the greatest depth in the upper and the lower dead centres (49, 50) and their depths between any two adjacent dead centres (49, 50) are minimal, so that the movement of the additional bearing rollers (5) along the axes of the main bearing rollers (3) is minimized.

21. The cam machine according to claim 18, characterized in that each of the two cam bushings (16a and 16b) of the cylindrical tubular 3D cam (20) is fixedly and coaxially connected to a tubular element (19) which is located between them.

22. The cam machine according to claim 18, characterized in that the connection and orientation between the two cam bushings (16a and 16b) of the cylindrical tubular 3D composite cam (20) is made by a tubular element (41) which is a rotor of an electric machine and transmission of torque between the cam bushings (16a and 16b) is realized by means of teeth (43) and sockets (42), which are located on contact fronts of the cam bushings (16a and 16b), and a stator (68) of the electric machine is fixedly connected to the housing elements (31) of the cam machine.

23. The cam machine according to claim 18, wherein a connection and orientation between the two cam bushings (16a and 16b) of the cylindrical tubular 3D cam (20) is made by two flanges (36a and 36b), one flange on each of the bushings (16a) and (16b), which flanges (36a and 36b) are located around the sides of the corrugated cam profiles (15a) and (15b), the connection between the flanges (36a) and (36b) being fixed and secured by orienting fasteners.

24. The cam machine according to claim 23 characterized in that a gear ring (45) is made on a periphery of the flanges (36a) and (36b) for transmitting mechanical energy to an external working machine or for receiving energy from an external source of mechanical energy.

25. The cam machine according to claim 18, wherein a connection and orientation between the two cam bushings (16a and 16b) of the 3D composite cam (20) is made by at least two lugs (39a or 39b) located around the sides of each of the bushings (16a and 16b) having corrugated cam profiles (15a and 15b) and connected together, wherein the connection between the lugs (39b) and (39a) of the cam bushings is fixed and is provided by means of orienting fasteners.

26. The cam machine according to claim 18 further comprising a two cylinder compressor or hydraulic pump characterized in that the two-cylinder compressor or hydraulic pump comprise at least one cylinder head (61), hermetically dosing the cylinder (26) or one of the cylinders (26), performing a working cycle in it, wherein a fluid exchange accompanying filling and emptying processes of the cylinder (26) or the cylinders (26) is effected by a means (71) and (72) for opening and closing the compressor chamber (73).

27. The cam machine according to claim 26, characterized in that it has at least one cylinder head (61), hermetically closing the cylinder (26) or one of the cylinders (26), performing an operating cycle in it, wherein the fluid exchange accompanying the operating cycles in the cylinder (26) or cylinders (26) is realized by at least one kinematic circuit consisting of a 2D cam (40a or 40b) which is fixedly connected to a nearest adjacent side of the 3D composite cam (20), and rocker (64a or 64b), which can rotate around axis (62) under the influence of the 2D cam (40a or 40b), at least one suction or discharge valve (65a or 65b) performing reciprocating motion under the influence of the rocker (64a or 64b) and at least one return spring (67) holding the suction or discharge valve (65a or 65b) in a closed position when not activated by the rocker (64a or 64b).

Description

DESCRIPTION OF THE ATTACHED FIGURES

(1) This invention is illustrated in the accompanying drawings, in which:

(2) FIG. 1 is a sectional view of a double piston cam machine;

(3) FIG. 2a is a general view of a cam adjustment mechanism unit;

(4) FIG. 2b is a sectional view of the cam machine adjustment unit of FIG. 2a;

(5) FIG. 2c is a view of indirect contact between a screw regulator and a plunger;

(6) FIG. 2d is a view of a direct contact between a screw regulator and a plunger;

(7) FIG. 3 is an axonometric view of a cam machine adjustment mechanism;

(8) FIGS. 4a, 4b and 5 represent a package of test inserts before and after they are used to set up the cam machine and functional insert;

(9) FIG. 6a is a sectional view of a screw regulator with an adjustable pin;

(10) FIG. 6b is assembly diagram in axonometric view of a screw regulator with an adjustable pin;

(11) FIG. 7 is a sectional view of cam bushings in working position;

(12) FIG. 8 is an unfolded view of the outer edges of a variable width cam channel;

(13) FIG. 9 is a cross-section of a cam channel between adjacent dead positions of the pistons at a variable width cam channel;

(14) FIG. 10 is a cross-sectional view of a cam channel through the dead position of a piston at a variable width cam channel;

(15) FIG. 11 is an unfolded view of the outer edges of a constant width cam channel;

(16) FIG. 12 is a cross-sectional view of a cam groove through the dead position of a piston in narrow grooves cam profiles;

(17) FIG. 13 is a cross-sectional view of a cam channel between adjacent dead positions of the pistons in track cam profiles;

(18) FIG. 14 is a 3D composite cam with an orienting tubular element combined with an electric machine rotor;

(19) FIG. 15 shows a cam bushing with a flange for attachment to its opposite cam bushing and a gear ring made on the periphery of the flange;

(20) FIG. 16 is a cam bushing with lugs for attachment to its opposite cam bushing;

(21) FIG. 17 is a sectional view of a two-cylinder cam machine realized as a compressor or hydraulic pump; and

(22) FIG. 18 is a sectional view of a cam machine realized as a single-cylinder internal combustion engine in combination with an electric generator.

EXAMPLES OF THE INVENTION

(23) According to the invention, various double- or single-piston cam machines can be implemented, which perform different operating cycles depending on the user's need, and which cam machines can be compressors, pumps, internal combustion engines or combinations of the above.

(24) The created cam machine with adjusting mechanism shown in FIG. 1 includes a tubular 3D composite cam 20 which comprises cam bushings 16a and 16b and a tubular element 19 which orients the cam bushings 16a and 16b in such a way that their cam profiles 15a, 15b and the bottom 59, which is part of the tubular element 19, form a cam channel along the inner cylindrical surface of the 3D composite cam 20. The cam machine also comprises two identical followers 1a and 1b, each of which has two arms 37. Towards the free ends on the arms 37 main bearing journals 2 and main bearing rollers 3 are mounted. The main bearing journals 2 have a tubular geometry and in their cylindrical cavities additional bearing journals 4 are placed, on which additional bearing rollers 5 are mounted. The main bearing rollers 3 of the followers units 1a and 1b contact the cam profiles 15a and 15b of the cam bushings 16a and 16b, respectively. The 3D composite cam 20 is mounted on bearings bilaterally in cylinder blocks 21 and 22 by means of an axial 23 and a radial 24 bearing on each side. Each follower 1a and 1b is connected to a piston 25, which is located in a respective cylinder 26. The axes of the cylinders 26 coincide with the axis of the 3D composite cam 20. The axial guidance of the followers 1a and 1b is performed by guide columns 27, which are mounted on bearings in the cylinder blocks 21 and 22. The reciprocating motion of the followers 1a and 1b is transformed into a rotation of the 3D composite cam 20, which transmits the rotational motion to a gear 28, which is fixedly connected to the 3D composite cam 20. The gear 28 is engaged with another gear 29, which drives an output shaft 30. The shaft 30 is mounted on bearings in the cylinder block 21 and the crankcase 31 (engine casing).

(25) The structural unit representing the cam machine adjusting mechanism is shown in FIGS. 2a, 2b, 2c and 3.

(26) FIGS. 2a, 2b and FIG. 3 show that the additional bearing journals 4 are mounted in holes located in the lugs 32 of the cylindrical plungers 6. On the opposite side of the lugs 32, on each plunger 6, a cylindrical cavity 33 is made, visible in FIG. 3, which houses a package of disc springs 8 and an axial bearing 10, which are mounted on a pin 11 of a screw regulator 7. The screw regulator 7 has a threaded stem 34, through which it is screwed into a threaded hole 13 located in the bottom 14 on each main bearing journal 2. The threaded hole 13 and the bottom 14 are visible in FIG. 3. Through the nut 12 the screw regulator 7 is fixed when adjusting the cam mechanism. Each plunger 6 is mounted radially in the cylindrical cavity 33 of its respective main bearing journal 2 by means of a radial bearing 35 which does not restrict the displacement 17 of the plunger 6 in the direction of the axis of its adjacent main bearing journal 2. It is also seen from FIG. 2b that the plunger 6 can also perform a rotational movement 18 around the axis of the adjacent main bearing journal 2 simultaneously with the displacement 17 in the direction of the same axis. The displacement 17 provides a constant contact between each additional roller 5 land the corresponding cam profile 15a or 15b, and the rotation 18 allows self-orientation of the additional rollers 5 relative to their respective cam profile, based on the principle of least resistance, thus eliminating the additional rollers 5 slippage when rolling on the respective cam profile 15a or 15b.

(27) FIGS. 2c and 2d show that two types of contact are made between each screw regulator 7 and its respective plunger 6—indirect and direct. The indirect contact illustrated in FIG. 2c is realized through the disc spring package 8 and the axial bearing 10. The direct contact illustrated in FIG. 2d is made only in cases when the inertial forces from the reciprocating motion of the followers 1a and 1b are sufficiently large to overcome the resistance of the disc springs 8 and to move the plunger 6 until it touches the pin 11 of the screw regulator 7. The direct contact is made by functional insert 56b.

(28) FIG. 3 is an assembly diagram of the cam machine control unit. It shows clearly that it is possible to remove the plunger 6 freely without any restrictions from the main bearing journal 2 in the direction from the screw regulator 7 to the additional roller 5. The movement of the plunger 6 is limited in this direction only by the cam profile 15a or 15b when the adjusting unit is mounted in the cam machine assembly.

(29) FIG. 4a shows a package of test inserts 9a, 9b and 9a before adjusting the cam machine, and FIG. 4b the same package after. The deformation of the package of test inserts, 9a, 9c and 9a, reflects the influence of the production tolerances on the displacement 17. The insert 9b/9c is easily deformable, where the easily deformable insert is marked 9b before being crushed and 9c thereafter. FIG. 5 compares the height of the transformed composite test insert with the height of the functional insert 56b.

(30) FIGS. 6a and 6b show a screw regulator 7 consisting of three parts: a body 46, an adjustable pin 47 and a fixing screw 48. Through the composite screw regulator 7 it is possible to achieve a more precise adjustment of the cam mechanism, both with the use of inserts and without them.

(31) FIGS. 7, 8, 9 and 10 illustrate one way to minimize the relative displacement 17 of the additional rollers 5 in the direction of the axes of the main rollers 3. For this purpose, FIG. 7 shows two cross sections of the cam profiles 15a and 15b of the cams bushings 16a and 16b of the 3D composite cam 20. One of the sections shown in FIG. 10 also passes through the dead position 49/50 of the pistons 25, and the other, as shown in FIG. 9, through an intermediate position 55 which is located between two adjacent dead positions 49/50. Comparing the cross-sectional contour of FIG. 9 and the cross-sectional contour of FIG. 10, it is seen that the width of the cam channel of the 3D composite cam 20 shrinks at intermediate positions 55 and widens at dead positions 49/50. FIG. 8 shows that the transitions from narrowing to widening of the cam canal and vice versa take place gradually, where 53 and 54 are edges of the cam profiles 15a and 15b.

(32) FIGS. 11, 12 and 13 illustrate two additional ways to minimize the relative displacement 17 of the additional bearing rollers 5 in the direction of the axes of the main bearing rollers 3.

(33) In the first alternative method shown in FIG. 12, on the cam profiles 15a and 15b of the cam bushings 16a and 16b, narrow grooves 51 are made for the additional bearing rollers 5. The depths of the grooves 51 are maximum in the dead positions 49/50 of the pistons 25 and the depths of the grooves 51 gradually reach their minimum in the intermediate positions 55 of FIG. 11. In cases where the minimum depths of the grooves 51 are equal to 0, then the cross sections in the intermediate positions 55 of FIG. 11 look as shown in FIG. 9.

(34) In the second alternative method shown in FIG. 13, on the cam profiles 15a and 15b of the cam bushings 16a and 16b, narrow tracks 52 are made for the additional bearing rollers 5. Their heights are maximum in the intermediate positions 55 of the pistons 25 in FIG. 11 and the heights of tracks 52 gradually reach their minimum in dead positions 49/50. In cases where the minimum heights of the tracks 52 are equal to 0, then the cross sections of the cam channel in the dead positions 49/50 in FIG. 11 look as shown in FIG. 10.

(35) FIG. 14 shows an assembly diagram of the 3D composite cam 20. In this case, coaxial orientation between the cam bushings 16a and 16b is provided by a tubular element 41. The tubular element 41 is also a rotor of an electrical machine. Permanent magnets 44 are fixed to the outer cylindrical surface of the tubular element 41. Angular orientation and torque transmission between the cam bushings 16a and 16b is effected by teeth 43 and sockets 42. They are arranged on the contact front of the cam bushings 16a and 16b. FIG. 14 also shows 2D cams 40a and 40b, which drive the valves of a valve timing mechanism of an internal combustion engine.

(36) FIG. 15 shows a cam bushing 16a or 16b having a flange 36 around the side of the cam bushing with a corrugated cam profile 15a/15b. The flange 36 is used to make a connection between the cam bushings 16b and 16a. Holes 38 for fastening and/or orientation elements are made on the front surface of the flange 36, which provide a fixed connection and orientation between the two cam bushings 16a and 16b. A gear ring 45 is made on the periphery of the flange 36, through which a rotational movement of the output or input shaft 30 is transmitted or received.

(37) FIG. 16 shows a cam bushing 16a or 16b, which has lugs 39 for attachment to the opposite cam bushing 16b or 16a. Holes 58 are made in the lugs 39, which are used for elements, such as threaded connections and/or pins, which provide a fixed connection and angular orientation between the two cams 16a and 16b.

(38) FIG. 17 shows a cam machine realized as a two-cylinder compressor. The compressor cylinders 26 are hermetically sealed with cylinder heads 61 in which compressor chambers 73 are made. Atmospheric air is supplied to each cylinder 26 by a low pressure check valve 71 and the compressed air is removed by another high pressure return valve. 72. When the pistons 25 move to a lower dead centre, a pressure is created lower than the atmospheric and the atmospheric air enters the cylinders 26. When the pistons move to a top dead centre, the air compresses in the cylinders 26 and the compressor chamber 73 and overcomes the spring force of the check valves 72. In this way the valves 72 open and the compressed air leaves the cylinders 26.

(39) FIG. 18 illustrates one of the many possible combinations between a cam machine, an electric machine, a compressor and a hydraulic pump. In this case, the cam machine is a single-cylinder spark-ignition internal combustion engine to which an electric machine is integrated. The follower 1a is connected to a balancing element 60 instead of a piston 25 in order to balance the inertial forces of the reciprocating motion of the two followers 1a and 1b together with all the elements carried by them. The only cylinder 26 is hermetically sealed with a cylinder head 61, as in the compressor shown in FIG. 17. The rotor 41 of the electric machine is made as shown in FIG. 14, and the stator 67 is fixedly connected to the housing element 31, which in this case is an integral part from the cylinder block 22. The generated output energy is obtained in the form of electricity dissipated through the wires 69 and mechanical torque transferred through the gears 28 and 29 and the output shaft 30. The valve timing mechanism of the engine shown consists of two kinematic circuits. One of them controls the access of fresh working substance in the cylinder 26, and the other controls the output of the spent working substance. Each of the kinematic circuits consists of a 2D cam 40a or 40b, which is fixedly connected to the composite 3D cam 20 and which further drives the rocker 64a or 64b. The rockers rotate about fixed axes 62 and the contact of each rocker with its 2D drive cam 40a or 40b is made with a roller 63. At its other end, each rocker contacts the suction or discharge valve 65a or 65b. The valves 65a or 65b successively open and close the openings of the combustion chamber 70 under the influence of the pressure coming from the rocker 64a or 64b or the springs 67.

(40) The created cam machine can be part of a cam hybrid unit. In this case, one of the following three cycles is realized in its cylinder 26 or in one of its cylinders 26, namely: an internal combustion engine, a hydraulic or a pneumatic machine. In its opposite cylinder 26, if the opposite piston 25 is not replaced by a balancing element 60, an identical or different cycle from the cycle in the first cylinder is realized, where the unit operates in one of the following three modes—as a source, as a consumer or simultaneously as a source and a consumer of electrical, mechanical, hydraulic, pneumatic, or any possible combination of the energies listed above.