Methods and machines with reciprocating and rotating pistons with positive displacement

The present invention relates to methods and machines with reciprocating and rotating pistons with positive displacement which are connected through rotating sliders to rods of multirod eccentric rotor mounted on crank shaft, which eccentric rotor is connected to gear set which model the motion of the said pistons.

Prior art is the field of reciprocating and rotary piston machines and engines.

The object of the invention is to create pump, compressor or internal combustion engine with reciprocating and rotating pistons without intake and exhaust valves.

In accordance with the present invention there are 3 methods depending how the motion of reciprocating and rotating pistons is controlled. The methods determine the type and ratio of gear sets controlling the pistons, and as a sequence of this, the number of pistons, the number of extrema of the cycles of the machines per one revolution of the crank shaft and the revolutions of the crank shaft per one revolution of the rotor (CS/R). The methods are:

a) peritrochoid - with ratio of stationary gear with external gear teeth to planetary gear with internal gear teeth, which is a multiple of n : (n+1), where n can be any positive integer. The number of pistons in this case is (n+1). CS/R = (n+1).

b) epitrochoid - with ratio of stationary gear with external gear teeth to planetary crank gears with external gear teeth, which is a multiple of n : 1 , where n can be any positive integer. The number of planetary crank gears and pistons in this case is n + 1. CS/R = n + 1.

c) hypotrochoid - with ratio of stationary gear with internal gear teeth to planetary crank gears with external gear teeth, which is a multiple of n : 1, where n can be any positive integer bigger than 2. The number of planetary crank gears and pistons in this case is n - 1. CS/R = n - 1.

In all cases above the number of extrema of the cycles of the machines per one revolution of the crank shaft is 2n. This satisfies any two-stroke machine. The four-stroke machine requires 4 extrema of the cycles of the machine per one revolution of the crank shaft, therefore 2n/4 must be a positive integer.

For brevity ratios defined in a), b),c) will be called“Ratio”.

With transformation of classic slider-crank mechanism on Fig. 1 is best to understand the idea behind the methods for this invention. We take links (2) - crankshaft, link (3) - connecting rod and link (1 ) - ground and as links (2) rotates around point O, we start rotating link (3) around point A. In order to have repeatable cycles of rotation of links (2) to (3) there should be a proportion between those rotations. The solution is shown on Fig. 2. This is a pericycloid with Ratio n : (n+1) with Ratio of rotation of link (2) to link (3)

5 - ((n + 1) - n) : (n+1), where n is any positive integer. Here for simplicity the slider (4) is missing. On Fig. 3 we mount a rotating slider (4) on link (3). Then link (3) is changing its length and link (1) is constant and still is ground. If the embodiment of rotating slider (4) is a piston and link (1) is constant we can create rotating piston moved by transformed slider-crank i.e. reciprocating. Since we know that a pericycloid is an inverse

10 hypocycloid follows Fig.4, where the motion of links (2) and (3) can be transferred

through constant velocity link to rotating slider-crank (2^, (3i). The transformation of epicycloid motion is similar. On Fig.5 to 7 is shown how with transformed links (2), (3) and (4) can be created three types of machines following the methods described above. On Fig.5 is shown a schematic of a peritrochoid machine with Ratio 2:3. On Fig.6 is

15 shown a schematic of an epitrochoid machine with Ratio 2:1. On Fig.7 is shown a

schematic of a hypotrochoid machine with Ratio 4:1. On Fig.5 to 7 the sectors between reciprocating and rotating pistons periodically go through BDC and TDC following the extrema of corresponding curve.

Basic construction of a machine according to Fig. 5 is shown on Fig. 8. Here instead of

20 link (2) we have crank shaft (102), link (3) is substituted by multirod rotor (103)

eccentrically mounted on crank shaft (102), link (4) is rotating sliders (104) which slide on rods of (103) and rotate in pistons (105). Crank disk (106) is bolted to multirod rotor (103) and planetary gear with internal gear teeth (107). The planetary gear with internal gear teeth (107) is meshed to stationary gear with the external gear teeth (108). The gear set

25 (108):(107) control the rotation of multirod rotor (103) and reciprocating and rotating

motion of pistons (105). The piston sub assembly on Fig. 9 shows the face of piston (105) on view A, which is rectangular with oval corners. The piston sub assembly has 2x2 compression seals (109) and 1x2 oil seals (110). The construction of compression

(109) and oil (110) seal is identical with the difference in oil seals which have a groove all

BO around the perimeter. The construction of compression seals (109) is shown on Fig. 10.

This is a compression seal sub-assembly. It consists of two P-shaped seals (109) with oval top corners mounted against each other in the channels of the piston (105). The legs are slightly inclined outward. They have a notch parallel to the horizontal side, so almost all the length of the legs is half thin. The bottom of each leg is radius-ed, so these round ends meet the horizontal notches. One very important part of construction of peritrochoid machine is the bottom ring (114). The bottom ring (114) is preassembled with multirod rotor (103) but was not shown on Fig. 9 for clarity of exposition. This assembly is shown on Fig. 1 1. The purpose of bottom ring (114) is to allow for free motion of rods of multirod rotor (103) and to guarantee the proper sealing of the volumes between reciprocating and rotating pistons (105). The necessary and sufficient condition for this is to rotate the bottom ring (1 14) with velocity equal to the velocity of multirod rotor (103). This is achieved by cranks (111), which are connected to crank disk (106) with washers (112) and retaining rings (113) on one side and pins on bottom ring (114). The proper sealing and the slot in bottom ring (114) are shown in detail B of Fig. 11. An isometric cross section of a peritrochoid machine with Ratio 2:3 is on Fig. 12. Here are shown the main parts mentioned above plus housing left (115) and housing right (1 16). The internal sides of housing left (115), housing right (1 16) and bottom ring (114) create volume with square cross section with oval corners similar to the face of piston (105) with some clearance for seals (109) and (110). The internal sides of housing left (1 15) and housing right (1 16) press on legs of seals (109) and (110) to create required pressure for reliable sealing of volumes between reciprocating and rotating pistons (105).

Basic construction of a machine according to Fig. 7 is shown on Fig. 13. Here instead of link (2) we have crank shaft (302), link (3) is substituted by multirod rotor (303) eccentrically mounted on crank shaft (302), link (4) is rotating sliders (304) which slide on rods of (303) and rotate in pistons (305). Crank disk (306) is bolted to multirod rotor (303) and connected to planetary crank gears with external gear teeth (307). The planetary crank gears with external gear teeth (307) are meshed to stationary gear with the internal gear teeth (308). The gear set (308):(307) control the rotation of multirod rotor (303) and reciprocating and rotating motion of pistons (305). The piston sub assembly on Fig. 14 shows the face of piston (305) on view A, which is rectangular with oval corners. The piston sub assembly has 2x2 compression seals (309) and 1x2 oil seals (310), W- oil seal right (311) and W-oil seal left (312). The function of W-oil seals (311) and (312) is to prevent oil leak in the exhaust and intake ports. The construction of compression (309) and oil (310) seal is identical with the difference in oil seals which have a groove all around the perimeter. The construction of compression seals (309) is shown on Fig. 15.

It is similar to the design on Fig. 10. It consists of two P-shaped seals (309) with oval top corners mounted against each other in the channels of the piston (305). The legs are slightly inclined outward. They have a notch parallel to the horizontal side, so almost all the length of the legs is half thin The bottom of each leg is radius-ed, so these round ends meet the horizontal notches. W-oil seal sub-assembly is shown on Fig. 16: W-oίI seal right (311), W-oil seal left (312). W-oil seals are incorporated on both sides of the piston to prevent leak of oil in exhaust and intake ports. The bottom legs of W-oil seals are slightly tapered outward (similar to compression seal (309)) to create allowable pressure. The legs of W-oil seals have a notch perpendicular to their length and from this notch till the end are half thin, similar to compression and oil seals (309) and (310).

Similar to compression and oil seals (309) and (310), the end of the legs of W-oil seals (311 ) and (312) are radius-ed. They have oil groove all around (similar to oil seal (310)). One very important part of construction of hypotrochoid machine is the bottom ring (313). The bottom ring (313) is preassembled with multirod rotor (303) but was not shown on Fig. 13 for clarity of exposition. This assembly is shown on Fig. 17. The purpose of bottom ring (313) is to allow for free motion of rods of multirod rotor (303) and to guarantee the proper sealing of the volumes between reciprocating and rotating pistons (305). The necessary and sufficient condition for this is to rotate the bottom ring (313) with velocity equal to the velocity of multirod rotor (303). This is achieved by cranks (314), which are connected to crank disk (306) with washers (315) and retaining rings (316) on one side and pins on bottom ring (313). The proper sealing and the slot in bottom ring (313) are shown in detail B of Fig. 17. An isometric cross section of a hypotrochoid engine with Ratio 4:1 is on Fig. 18. Here are shown the main parts mentioned above plus housing left (317) and housing right (318). The internal sides of housing left (317), housing right (318) and bottom ring (313) create volume with square cross section with oval corners similar to the face of piston (305) with some clearance for seals (309) and (310). The internal sides of housing left (317) and housing right (318) press on legs of seals (309) and (310) to create required pressure for reliable sealing of volumes between reciprocating and rotating pistons (305). Also the internal sides of housing left (317) and housing right (318) press on sides of W-oil seals (311) and (312) to create required pressure for reliable sealing of sides of reciprocating and rotating pistons (305).

Basic construction of a machine according to Fig. 6 is shown on Fig. 19. Here the design is identical to hypotrochoid machine on Fig. 13 with only one difference: instead of stationary gear with the internal gear teeth (308) there is a stationary gear with external gear teeth (208). Therefore the gear set (208):(307) control the rotation of multirod rotor (303) and reciprocating and rotating motion of pistons (305). One possible application of this invention is by hypotrochoid method with n = 4 as internal combustion engine. In this case the engine will have n - 1 = 3 pistons and 2n = 8 extrema of cycles for 1 revolution of crankshaft. The condition for internal combustion engine 2n / 4 = 2 is satisfied. CS/R = (n - 1) = 3, therefore the total extrema of cycles for 1 revolution of the rotor is 2n (n - 1) = 24. The main parts of this machine were shown on Fig. 13 to 18. On Fig. 20 to 27 are shown 8 extrema of cycles.

On Fig. 20 the position of the rotor (303) through the pistons (305) gives the following distribution of chambers: chamber3 -exhaust, chamber2 - intake, chamberl - TDC- ignition. Piston (305)-3 closes top intake sector, but still is opening top exhaust sector. Piston (305)-1 closes bottom exhaust sector, but still is opening bottom intake sector.

At this moment the crank shaft (302) is pointing chamberl and is in unstable equilibrium. The pressure in combustion chamberl transfers as force through pistons (305)-1 , (305)- 3 and rotating sliders (304)-1 , (304)-3 to rods (303)-1 , (303)-3 of rotor (303) as projections perpendicular to the sides of rods (303)-1 , (303)-3. These projections are about 99% of total forces acting on pistons. The resultant force is acting on rotor (303) being collinear to rod (303)-2 and is acting like in convenient ICE on crank shaft (302) but is about 1.7 times bigger because the pressure is on two pistons!! As a result of the inertia forces the crank shaft (302) rotates CCW (like in convenient ICE). Rotating crank shaft (302), rotates rotor (303) and with rotor (303) the resultant force rotates and is acting with increased leverage of crank shaft (302) until rotating chamberl reaches BDC. The rotation of rotor (303) and crank shaft (302) is controlled by gear set (308) : (307).

On Fig. 21 piston (305)-3 closes top intake sector, but top exhaust sector is opened. Piston (305)-1 closes bottom intake and exhaust sectors. Chamberl is at work. The resultant force is still acting and the leverage on crank shaft (302) is bigger. There is additional torque in the same direction of rotation, because the leverage on rod (303)-1 is bigger than the same on rod (303)-3. Chamber3 is at position exhaust. Chamber2 is at BDC, ready to start compression.

On Fig. 22 chamber3 is at TDC after exhaust .Here both top intake and exhaust sectors are opened allowing proper scavenging of the chamber. Piston (305)-1 is closing bottom intake and exhaust sector. Chamberl is at work. The resultant force is still acting and the additional torque in the same direction of rotation is bigger. Chamber2 is at compression.

On Fig. 23 piston (305)-3 opens top intake sector. Chamber3 is at intake. Piston (305)-2 is about to close the exhaust sector. The interval between this and previous picture allows for good scavenging of chamber3. Piston (305)-1 still closes bottom intake and exhaust sectors. Chamberl is at BDC after work. At this moment the crank shaft (302) is in stable equilibrium (like in convenient ICE). Chamber2 is at compression.

On Fig. 24 piston (305)-2 closes top exhaust sector. Piston (305)-1 opens bottom exhaust sector but bottom intake sector is closed. Chamber2 is at TDC - ignition. Here we have mirror image of Fig. 20 with chamberl . Chamberl is at exhaust. Chamber3 is at intake.

On Fig. 25 piston (305)-2 closes both top intake and exhaust sectors. Piston (305)-1 still closes bottom intake sector. Bottom exhaust sector is still opened. Chamber3 is at BDC after intake. Chamberl is at exhaust. Chamber2 is at work.

On Fig. 26 piston (305)-2 closes both top intake and exhaust sectors. Both bottom intake and exhaust sectors are opened - chamberl is at TDC after exhaust. Here is a mirror image of Fig. 22 about scavenging the chamberl . Chamber2 is at work. Chamber3 is at compression.

On Fig. 27 piston (305)-2 closes both top intake and exhaust sectors. Both bottom intake and exhaust sectors are opened - chamberl is at intake. Here is a mirror image of Fig.

23 about scavenging the chamberl This time piston (305)-3 is about to close the exhaust sector. Chamber2 is at BDC after work. Chamber3 is at compression.

The advantages versus conventional reciprocating four-stroke engine are (comparing equal forces due to pressure in working chambers):

a) Single cylinder engine has 1 ignition per two revolutions of crank shaft. The

hypotrochoid engine has 2 ignitions per one revolution of crankshaft, i.e. is equivalent to four cylinder engine.

b) The theoretical torque of the engine is more than 3 times bigger because of the “two piston effect”.

c) The power is up to 50% bigger because of lack of valves (aerodynamic and

mechanical efficiency) and better thermal distribution (thermodynamic efficiency) d) About 3 to 4 times better power to volume ratio and respectively power to weight ratio.

e) Better balancing of rotating parts. ln the drawings:

Fig.1 is the ancient slider-crank mechanism. Here are links (1), (2) and (3) and slider (4).

Fig. 2 is a pericycloid with Ratio n : (n+1) with Ratio of rotation of link (2) to link (3) - ((n + 1) - n) : (n+1), where n is any positive integer.

Fig. 3 is transformed slider-crank mechanism with rotating slider (4) on link (3).

Link (1) is constant and still ground.

Fig.4 is conversion of hypocycloid motion (1), (2), (3) through constant velocity link to rotating slider-crank (2i), (3i). Similar conversion is possible for epicycloid motion.

Fig.5 is a schematic of a three-piston peritrochoid machine. Ratio 2:3

Fig.6 is a schematic of a three-piston epitrochoid machine. Ratio 2:1.

Fig.7 is a schematic of a three-piston hypotrochoid machine. Ratio 4: 1.

Fig. 8 is an exploded view of the basic parts of a peritrochoid machine with Ratio 2:3. Parts are: crankshaft (102), multirod rotor (103), rotating sliders (104), piston

(105), crank disk (106), planetary gear with internal gear teeth (107) meshed to stationary gear with external gear teeth (108).

Fig. 9 is partially exploded view of piston sub-assembly: piston (105), compression seals (109) and oil seals (110). Fig. 10 is a compression seal sub-assembly. It consists of two P-shaped seals

(109).

Fig.11 is a constant-velocity sub-assembly. New parts are: cranks (1 11), washers (112), retaining rings (1 13) and bottom ring (114).

Fig. 12 is an isometric cross section of a peritrochoid machine with Ratio 2:3 showing the main parts mentioned above plus housing left (115) and housing right

(116). Fig. 13 is an exploded view of the basic parts of a hypotrochoid machine with Ratio 4:1. Parts are: crankshaft (302), multirod rotor (303), rotating slider (304), piston (305), crank disk (306), planetary crank gears with external gear teeth (307) meshed to stationary gear with internal gear teeth (308). Fig. 14 is a piston sub-assembly: piston (305), compression seals (309), oil seals

(310), W- oil seal right (31 1), W-oil seal left (312).

Fig. 15 is a compression seal sub-assembly: two identical seals (309).

Fig. 16 is a W-oil seal sub-assembly: W-oil seal right (31 1), W-oil seal left (312

Fig.17 is a constant-velocity sub-assembly. New parts are: cranks (314), washers (315), retaining rings (316) and bottom ring (313)

Fig. 18 is an isometric cross section of a hypotrochoid engine with Ratio 4: 1 showing the main parts mentioned above plus housing left (317) and housing right (318).

Fig. 19 is an exploded view of the basic parts of a epitrochoid machine with Ratio 2: 1. New part is a stationary gear with external gear teeth (208).

Fig. 20 to 27 represent a transverse cross sections through housing right (318) with 2 intake sectors (ins) and housing left (317) with 2 exhaust sectors (exs) of the hypotrochoid internal combustion engine. The pistons (305) divide the volume between the housing left (317), housing right (318) and bottom ring (313) on three rotating volumes called chamberl , chamber2 and chamber3. Fig. 20 to 27 give 8 out of total 24 extrema of chamberl , chamber2 and chamber3 for one full rotation of the rotor (303).