JP2575054B2 - Internal combustion engine - Google Patents

Abstract

An internal combustion engine has at least one piston (15, 16) which moves back and forth in a cylindrical piston bore (13, 14) and drives a rotationally supported crankshaft (30) through a connection rod (24, 25). The piston bore (13, 14) is arranged in a rotary element (10) rotationally supported in a housing (1). The rotary element (10, 17) and crankshaft (30) are cinematically coupled through a gear (40, 41, 42, 43) so that they can rotate in opposite directions (60 or 61). The piston bore (13, 14) arranged in the rotary element (10) communicates with an opening (20, 21) in the outer surface of the rotary element (10, 17) which moves past an inlet opening (50) and an outlet opening (51) in the housing (1) during rotation of the rotary element (10).

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention comprises at least one piston reciprocating within a cylindrical piston bore and acting on a crankshaft rotatably supported via a connecting rod, wherein the rotor is a piston / piston. The rotor is rotatably supported in the housing, and is rotatably coupled to the crankshaft by a gear device so that the rotor and the crankshaft rotate in opposite directions. The invention relates to an internal combustion engine in which a piston bore communicates with an opening formed in the outer surface of the rotor and passes in front of an inlet opening and an outlet opening provided in the housing during rotation of the rotor.

Such an internal combustion engine is known from U.S. Pat. No. 1,498,518. In this known internal combustion engine, cooling is effected externally by means of a water chamber arranged in the vicinity of the spark plug and by means of a fan wheel which is integrated in one end of the rotor. This patent does not teach how to lubricate moving parts.

It is an object of the present invention to provide an internal combustion engine of the above type having a combined oil delivery and delivery system that serves to lubricate various bearings and cool the piston area.

To this end, an oil carrier having an outlet opening in the vicinity of the connecting rod bearing and / or the crankshaft bearing and / or the crankshaft component penetrates the crankshaft and the oil discharge conduit has at least one piston.・
A piston extending away from the bore, the oil discharge conduit extending radially outwardly parallel to the piston bore for cooling the piston bore, wherein the origin of the oil discharge conduit within the piston bore is at top dead center. An internal combustion engine of the type described above, characterized in that it is not covered by the internal combustion engine.

The oil conduit means according to the invention furthermore allows the lubrication of the bearings and the oil cooling of the piston area to be achieved simultaneously with a single oil delivery / infeed means by utilizing the centrifugal force generated in the rotor.

A structurally simple variant of the oil conduit means for lubrication of the bearing is specified by the characterizing part of claim 2.

An improved arrangement for cooling in the piston area is specified by the features of claims 3 and / or 4.

An advantage of the embodiment as defined by the characterizing part of claim 5 is that the construction of the pistons operating in opposite directions in this way provides a smooth and quiet operating state and simplifies the construction. is there.

In U.S. Pat. No. 1,598,518, opposing pistons or cylinders are offset in the direction of the crankshaft axis. In an embodiment with an arrangement according to the features of claim 6, the pistons or cylinders are arranged coaxially, resulting in a flatter and more compact design, thereby reducing the weight. In addition, a quieter operating state is obtained. Useful variants of this embodiment are specified in the features of claims 7 and / or 8.

Preferred configurations of the rotor, the crankshaft and the gearing or of their operation coupled to one another are specified by the characterizing part of one or more of the ninth to thirteenth claims.

According to one or more of the features of claims 14 to 16, the position and the configuration of the inlet opening and the outlet opening are appropriately determined so that there is no valve and / or slide. The intake and exhaust phases can be controlled.

According to the characterizing part of claim 17, an operation mode in which fuel is conserved when the internal combustion engine is partially loaded is obtained.

Embodiments of the present invention and their more advantageous features are described in detail below with reference to the accompanying drawings.

 FIG. 1 is a sectional view of the first embodiment.

FIG. 2 is a sectional view of the first embodiment taken along line II-II of FIG.

FIG. 2a is a schematic diagram of a configuration that combines the operation of the rotor and the operation of the crankshaft.

FIG. 3 is a sectional view similar to FIG. 1, showing a second embodiment.

FIG. 4 is a view corresponding to FIG. 2 and schematically showing a modification of both the first and second embodiments.

FIG. 5 is a schematic exploded elevation view of a control slide for partial load operation.

In the embodiment of the invention shown in FIGS. 1, 2 and 2a, the housing 1 of the internal combustion engine comprises a cylindrical wall 2, an upper flat cover disc 3 and, likewise, substantially It consists of a round lower base plate 4. The housing 1 is thus basically in the form of a round disk, whose height is equal to the height of the cylindrical wall 2. This housing is immobile. Rotor 10 rotates within housing 1. This rotor has two cylinders 11, 12 axially displaced from each other, a disk 35, and a race (track ring) 17.

The cylinders 11 and 12 have cylindrical piston bores 13 and 14 in which pistons 15 and 16 are reciprocally housed, respectively. Cylinders 11 and 12 in the form of inserts have inner race 17
It is firmly joined to. Ribs 18 and 19 (not shown in FIG. 1 for simplicity) serve to provide the entire rotor 10 with sufficient rigidity as a unit. The race 17 has openings 20,21 adjacent to the piston bores 13,14.
Connecting rods 24,25 are pistoned by piston bolts 22,23
Connecting rod bearings 36, 37 mounted on the crankshaft 30 while being pivotally mounted on
, So that the pistons move in opposite directions at the same time. The crankshaft 30 is supported with its lower bearing journal 31 penetrating the base plate 4. The upper bearing journal 32 of the crankshaft 30 is rotatably supported in a blind hole 33 provided in the disk 35. The disk 35 is a fixed component of the rotor 10 and rotates with the rotor. The power take-off shaft 34 is firmly joined to the disk 35 while being supported in the upper cover disk 3 of the housing 1. Therefore, the crankshaft 30 and the rotor 10
Are rotatable in opposite directions. Crankshaft
30 is also rotatable with respect to the housing 1.

The rotation of the rotor 10 (including the cylinders 11 and 12, the race 17, the ribs 18 and 19, the disk 35, and the power take-out shaft 34) and the rotation of the crankshaft 30 are connected by a planetary gear. The planet gears include an inner gear ring 40 (see FIG. 1) mounted below (in FIG. 1) the rotor 10;
A gear 41 mounted on the crankshaft 30 and two more
And two gears 42 and 43. The gears 42 and 43 are supported so as to pass through the base plate 4 of the housing 1. These gears are of two-stage type, ie, gears 42,4
3 has a first set of teeth 421,431 that mesh with the inner gear ring 40 of the rotor 10. The gears 42 and 43 are components of the crankshaft 30 or
It has a somewhat smaller diameter second set of teeth 422,432 that mesh with a gear 41 securely mounted to 30. In this way, the reciprocation of the piston causes the rotor 10 to rotate, thereby ensuring a limited rotation of the rotor 10 in the housing 1 and the rotation directions of the rotor 10 and the crankshaft 30 being opposite to each other. . This situation is shown schematically in FIG. 2a.

As can be seen from FIG. 2, the cylindrical wall 2 is provided with an entrance slit 50 and an exit slit 51 along the circumference thereof. The entrance slit 50 extends in an arc of about 70 °. The inlet slit 50 is covered with an inlet chamber 52, and an inlet opening 53 of the inlet chamber 52 communicates with, for example, a vaporizer (not shown). The exit slit 51 also extends over about 70 °. The outlet slit 51 communicates with an outlet chamber 54, which communicates with an exhaust pipe (not shown) through an outlet opening 55. If the openings 20 and 21 of the race 17 are Passing in front of slits 50 and 51, piston 1
The regions of the piston bores 13,14 of the cylinders 11,12 located radially outward of 5,16 also pass correspondingly in front of the slits 50,51 but communicate with them during their passage.

The relative positional relationship between the slit 50 and the slit 51 is as follows. When the cross section of the rotor 10 having the race 17 as a component is circular, the entrance slit 50 and the exit slit 51 are on the same semicircle as follows, that is, the entrance slit 50 is 270.
The outlet slits 51 are arranged side by side so as to be located in an angle range of ゜ to 360 ° and an exit slit 51 in an angle range of 180 to 270 °.

For the purpose of explaining the operation of the two-cylinder four-stroke internal combustion engine shown as an example, the initial or starting position of the piston 16 is assumed to be the position shown in FIG. If the rotor 10 rotates clockwise with respect to its starting position, as indicated by arrow 60, the opening 21 passes in front of the entrance slit 50. At the same time, the crankshaft 30 rotates counterclockwise as indicated by the arrow 61. This causes the piston 16 (and the piston 15) to move radially inward. Piston 16 draws a mixture of fuel and air (fresh air in the case of a diesel engine) through inlet slit 50. The piston 16 reaches the bottom dead center when the rotor 10 rotates 90 ° ahead of the starting position shown in FIG. At this time, the piston 16 is at the position 16 'shown by the broken line. At that point, the inhalation phase ends. The opening 21 is remote from an area that completely or partially overlaps the entrance slit 50. The compression phase then begins, in which the piston 16 is pushed radially outward as the crankshaft 30 and rotor 10 rotate forward in the direction indicated. Piston 16 from starting position
It reaches the top dead center when it reaches a position 180 ° off. Piston 16
When the piston reaches the top dead center, the piston 15 is at the position shown in FIG. At this position, ignition is performed by the spark plug 71. The explosion or expansion phase then begins. The piston starts moving radially inward again. In this process, the rotor 10 rotates forward in the direction of arrow 60 and eventually reaches a second bottom dead center. At this second bottom dead center,
The piston 16 has rotated 270 ° when viewed from the starting position shown in FIG. In doing so, the piston is in the position 16 "indicated by the dashed line. With continued rotation, the piston 16 moves once more radially inward and the exhaust gas evacuation phase begins, while at the same time the opening 21 is in front of the outlet spark plug 50. To drive the exhaust gas.
A full revolution cycle is achieved with only one revolution. This is due in particular to the fact that the rotor 10 and the crankshaft 30 rotate in opposite directions, the piston 16 makes two strokes during only one revolution of the rotor 10 or the crankshaft 30, and the suction and suction in the first stroke. Compression stage, second
The process involves performing the explosion and exhaust phases.

The cycle for piston 15 is obtained in the same manner as the cycle described above for piston 16, except that it is offset by half a revolution of rotor 10. In other words, piston 16
Is in the suction phase, the piston 15 is in the expansion phase.
When the piston 16 is in the compression phase, the piston 15 is in the exhaust phase. Conversely, when the piston 16 is in the expansion phase, the piston 15 is in the suction phase, and when the piston 16 is in the exhaust phase, the piston 15 is in the compression phase. The ignition of piston 15
This is performed by a spark plug 70 located above the spark plug 71 by a distance separated by the axis of both cylinders. Slits 50,51 are associated with both pistons 15,16. Note that only one spark plug can be used. For this purpose, the spark plug is located in the intermediate plane, ie facing both combustion chambers.

Lubrication is as follows, ie oil pump (not shown)
Bore 75 in the crankshaft 30 with oil under pressure
By sending it to Bore 75 is lateral bore 76,7
6 ', 78, 77, through which the connecting rod bearings 36, 37 and bearings 32, 33 are lubricated, while oil can freely flow into the housing 1 (bore 77). From now on, the oil flows radially under the effect of the centrifugal force and hits the lower surfaces of the pistons 15, 16 and therefore the cylinder / piston bore 1
It hits 3,14. Oil flows out through oil conduits 80,81.
The transfer of oil is also performed by centrifugal force. The reason is that the oil conduits 80 and 81 are disposed in the rotating rotor 10. Oil conduits 80,81 open into cylinder / piston bores 13,14 at the top dead center of pistons 15,16, just below the lower surfaces of pistons 15,16. From here the oil returns into the sump 90. Oil conduit 80 is cylinder / piston bore 13
Extending radially from the wall of the cylinder 11 to the race 17 at a relatively small distance, the cooling of the wall of the cylinder 11 is effected in this way. Oil conduit 80 then race 17
Along the axis of rotation and the race 17 is also cooled. The oil conduit 81 may be configured in the same manner as the oil conduit 80.

Since the entire four-stroke cycle is already obtained by each piston when the rotor 10 makes one revolution, the engine produces a lot of power at low speeds and can operate surprisingly quieter compared to engines with fixed cylinders become. Since the crankshaft and the rotor rotate in opposite directions, the smoothness of operation is further increased. Therefore, if the masses of the crankshaft and the rotor are properly selected, the vibration caused by them is partially compensated and the vibration damping effect is improved. can get. Furthermore, the rotor has an inlet slit 50 and an outlet slit.
Passing in front of 51, an engine without an intake valve, in other words, an engine with a very simple and inexpensive configuration is obtained. The problem of sealing can be solved very easily. The reason is that the race is provided on the outer surface of the race 17 and the housing 1
This is because all the sealed bodies sealed from the cylindrical wall 2 receive the centrifugal force during the rotation of the rotor 10 and come to the sealed position. In the case of a diesel engine, a seal or sealing strip is further provided.

The cooling action can also be obtained relatively easily with a suitable amount of oil. This is because the oil exits the oil conduit of the crankshaft and, due to the centrifugal force, reaches all places where lubrication or cooling is required. Furthermore, the engine has a very compact construction and is therefore relatively lightweight.

In the internal combustion engine shown as a second embodiment in FIG. 3, the housing 101 is also provided with a cylindrical wall 102, an upper flat cover.
It comprises a disk 103 and a substantially rounded lower base plate 104 likewise. The rotor 110 rotates within the stationary housing 101. This rotor 110 also
It has two cylinders 111, 112 but, unlike the first embodiment, is arranged coaxially, ie their longitudinal axes are in alignment. Two cylinders 111,11
Numeral 2 is configured as an insert, which is held between the upper disk 135 and the lower disk 135 ', which are components of the rotor 110. Similarly, the cylinders 111 and 112 have cylindrical piston bores 113 and 113 respectively accommodated so that the respective pistons 115 and 116 reciprocate in opposite directions.
It has 114. Cylinders 111 and 112 are disks 135 and 13
5 ′, and these cylinders are
It has annular sealing strips 107 and 108 for sealing from 02. It will be appreciated that in this second embodiment, too, the race may be provided in front of the cylinder. In this case the sealing strip is provided on the race. Connecting rod 124,12
5 is pivotally mounted on pistons 115, 116 by piston bolts 122, 123 (these are only suggested in the figures), and the flow axis of these connecting rods is aligned at the top dead center of the piston.

In this second embodiment, unlike the embodiment of FIG.
The two connecting rods 124 and 125 are different in configuration. The connecting rod 124 is substantially U-shaped and has a longitudinal extension in the middle of the cross bar connecting the two legs of the "U", which is extended via a piston bolt 122. It is pivotally connected to the piston 115. The free ends of each of the parallel longitudinally extending legs of the U-shaped connecting rod 124 are supported by connecting rod bearings 136, 136 'which are arranged coaxially, and these bearings are provided on the circumferential portion of the crankshaft 30. Two lateral crank discs 138, 13 facing each other in one position
9 is provided. Two parallel rod-shaped intermediate members 12
6,126 'can pivot with respect to the connecting rod 124 about a connecting rod bearing 136,136' located inside a U-shaped connecting rod 124 located far from the crank discs 138,139, but with two cranks. -The discs 138 and 139 are held so as not to rotate relative to each other. The ends of the intermediate members 126, 126 'are bent at an angle for this purpose and are pivotally connected by bearings 137 to another connecting rod 125. The length of the intermediate members 126, 126 'is the same as the diameter of the crank disks 138, 139. Connecting rod 125
Is located between the two intermediate members 126, 126 '. By doing so, the piston provided in the piston 116
The pivot point of the connecting rod 125 composed of the bolt 123 is the piston
U-shaped connecting rod 12 consisting of 115 piston bolts 122
It becomes coaxial with the pivot point of 4. The inner spacing between the connecting rod bearings 136, 136 'and between the legs of the U-shaped connecting rod 124 is somewhat greater than the thickness of the intermediate members 126, 126', and thus during rotation of the crankshaft 130, the intermediate members 126, 126 '. Is U
It becomes possible to penetrate the connecting rod 124, in other words, to pass between the legs of the connecting rod 124.

The crankshaft 130 is different from the first embodiment,
The upper bearing journal of the crankshaft, which is connected so that it does not rotate relative to the power takeoff shaft 134,
132 fits into holes 133,133 'provided in disks 135,135' and is supported by these disks. Also in the second embodiment, the crankshaft 130 and the rotor 110 can rotate in directions opposite to each other.
Can rotate in the opposite direction with respect to the housing 101.

The rotation operation of the rotor 110 and the rotation operation of the crankshaft 130 are coupled using a planetary gear.
It has the same configuration and function as the planetary gears shown in FIGS. 1, 2 and 2a. Therefore, this planetary gear will not be described further here. Thus, in FIG.
The same reference numerals as those used in the drawings are shown with 1 added to the front.

The lubrication and cooling of the internal combustion engine according to the second embodiment of FIG. 3 takes place in a manner which is structurally similar to the first embodiment. Oil is pumped into the axial bore 175 and crankshaft 130 by an oil pump (not shown). The bore 175 includes the crank disks 138, 139, the bearings 136, 136 ', 137 and the intermediate member 12.
The interior of 6,126 'extends continuously and terminates in a lateral channel 178 which opens radially outward in a bearing bore 133'. Bore 1 inside cylinder / piston bore 113,114
To get 75 exits: That is, the grooves or channels 177 are connected near the bearings 136, 136 ', 137 by connecting rods 124, 12
5, intermediate members 126, 126 'or crank disks 138, 139
On opposite surfaces of the

Also in the second embodiment, the oil discharged from the bore systems 175 and 177 hits the lower surfaces of the pistons 115 and 116 by the action of centrifugal force,
It also strikes the inner surfaces of the cylinder / piston bores 113,114. The oil is pumped out via oil conduits 180, 180 'preferably spaced at regular intervals along the inner circumference of the piston bores 113, 114, which oil conduits are provided with wide circumferential grooves on the outer circumference of the cylinders 111, 112. It leads to 181,181 '. The grooves 181, 181 'extend along most of the length of the cylinders 111, 112 and are suitable as cooling-like conduits in the area of the cylinders. Discharge conduits 182, 182 'are oil conduits with grooves 181, 181'
A narrow inner annular groove 183 is formed in the base plate 104 opposite the discharge conduit and is itself provided with two bores 184, 184 'in the end region of the disk 135' remote from 180, 180 '. Through the oil reservoir 190, for example.
In this second embodiment, the inlet opening and the outlet opening have the first
It is preferable to provide related chambers corresponding to the entrance chamber and the exit chamber of the embodiment. This is also true for spark plug 170. The spark plug 170 is provided at a position on the outer periphery of the housing 101 in the middle of the housing 101 because the cylinder or the piston is arranged coaxially and the combustion chamber is arranged coaxially.

However, in both the first and second embodiments of the present invention, it is also possible for the various stages of the four-stroke operation to proceed as shown schematically in FIG. The symbols in FIG. 4 are defined as follows. OT is top dead center, AS is exit closed, UT is bottom dead center, ES is entrance closed, ZZ
Is the ignition timing, AO is the opening of the outlet, and E is the opening of the inlet.
Inhalation is performed during the period S, compression is performed during the period P, and
The mixture is burned during the period, and the combustion gas is exhausted during the period E. As can be seen from this schematic drawing, starting from the state where the two pistons indicated by solid lines are located at the top dead center,
Arrow 161 opposite to the clockwise direction of crankshaft 130
When the rotor 110 is rotated in the direction of
Rotate in the direction of. Inlet slit 150 and outlet slit 1
Because 51 overlaps each other in a tapered state, the intake of fresh air is performed by the piston 116 simultaneously with the remaining exhaust of the combustion mixture from the combustion chamber. The range of overlap between the entrance slit 150 and the exit slit 151 is preferably in the range of 5 ° to 15 °. This overlap is advantageous because a negative pressure is created during the evacuation of the remaining combustion mixture, which is advantageous for simultaneous starting suction. The suction phase continues at bottom dead center UT (piston position 116 'shown by the dashed line) over an angular range of 30 ° to 60 ° taking into account inertia. Following that, ES
Although compression occurs at the point of time, the spark plug 170 is provided immediately before the top dead center OT (the position of the piston 115 shown in the drawing). The compression mixture is ignited. Thus, from the OT, a combustion phase of the mixture, in other words, an expansion phase, is carried out, which is about 30 ° above the bottom dead center position UT.
Continues up to the 60 ° angle range. At that point, the outlet slit 151 opens, in other words, the cylinder chamber communicates with the outlet slit 151, and the exhaust of the combustion mixture starts, at which point the exhaust phase or the discharge phase of the mixture overlaps the intake phase again. I do. Such a process would require a time and position of 180 for the other piston.
It is performed in a state shifted by ゜. This is because the exit opening 151 is 1
It extends over an angular range from 20 ° to 150 ° to 275 ° to 185 °, meaning that the inlet opening 150 extends over an angular range from 255 ° to 265 ° to 390 ° to 420 °.

FIG. 5 is an expanded view showing a portion of the cylindrical wall 102 having the entrance slit 150. FIG. This embodiment, which can be used for both the embodiment of FIG. 1 and the variant of FIG.
Although the slide 192 and the exit slit are not shown, a slide is provided in the same manner.
Work to partially cover For this purpose, slide 19
2 is a symmetric concave portion 193 of a specific curved shape and a trigger mechanism 19
4, the trigger mechanism lever 195 can be driven to move between position V (full load) and position T (partial load), and the entrance slit 150 opens substantially completely at full load. The slide 192 is disposed on the circumference and is therefore curved according to the wall 102 and can move along the wall 102 from one side. It will be appreciated that without such a configuration, two opposing slides that can move toward each other may be used.

With respect to the above embodiments, a configuration having two opposed piston / cylinder units has been described, but more than two,
For example, a configuration with four, six or eight piston / cylinder units may be used, where each pair of units is angularly offset according to the number of units and the outer diameter of the cylinder relative to the housing. It will be appreciated that axial displacements may be shorter.

Claims (17)

(57) [Claims] A cylindrical piston bore (13, 14, 113, 114)
A rotor (10,100) having at least one piston reciprocating within and acting on a crankshaft (30,130) rotatably supported via a connecting rod (24,25,124,125)
Are housed in piston bores (13, 14, 113, 114) and the rotor is rotatably supported in the housing (1, 101) such that the rotor and crankshaft rotate in opposite directions (60, 160 and 61, 161 respectively). Gear device (4
0,41,42,43,140,141,142,143) and movably connected to the crankshaft (30,130) by the rotor (10,110).
The piston bores (13, 14, 113, 114) provided therein have openings (20, 2) formed in the outer surface of the rotor (10, 17, 100, 117).
1), the connecting rod bearing (36) in the internal combustion engine configured to pass in front of the inlet opening (50) and the outlet opening (51) provided in the housing when the rotor (10, 110) rotates. 37, 136, 137) and / or bearings for the crankshaft (32, 132) and / or oil conduit means (7) with outlet openings near the crankshaft discs (138, 139).
5,175) penetrate through the crankshaft (30,130), an oil discharge conduit (80,180) extends away from at least one piston bore (13,113), and an oil discharge conduit (80,1).
80) extends radially outward parallel to the piston bore (13,113) to cool the piston bore (13,113) and the oil discharge conduit (80,180) in the piston bore (13,113)
An internal combustion engine characterized in that the starting point of the internal combustion engine is located so as not to be covered by the piston (15, 115) located at the top dead center. 2. An outlet opening in the vicinity of the connecting rod bearing (136) includes an axial groove or channel formed in the outer surface of the crankshaft disk (138, 139) and / or the connecting rod (124, 125). The internal combustion engine according to claim 1, wherein the internal combustion engine is constituted by (117). 3. The oil discharge conduit (180) has a piston bore (1).
13,114) are distributed in the inner peripheral part and the outer part of the cylinder, and communicate with a groove (181) formed in the outer peripheral part of the piston bore. 2. The internal combustion engine according to claim 1, wherein the internal combustion engine communicates with a discharge bore (184) formed in the 135). 4. The two piston bores (13, 14, 113, 114) which are formed at 180 ° from each other are provided in the rotor (10, 110).
The connecting rods (24, 124, 125) of the crankshaft (30, 130) are engaged with two connecting rod bearings (36, 37, 136, 136 ', 137) which are offset by 180 ° from each other. 2. The internal combustion engine according to claim 1. 5. The connecting rod bearings (136, 136 ', 136), wherein the longitudinal axes of the piston bores (113, 114) are aligned with one another.
137) An internal combustion engine according to claims 1 or 4, characterized in that 137) are arranged symmetrically with respect to the longitudinal axis of the piston bore in a corresponding relationship. 6. At least one of the two connecting rods (124, 125) is substantially U-shaped, and the other connecting rod (12, 126 ') is pivoted through an intermediate member (126, 126').
5. The internal combustion engine according to claim 5, wherein the internal combustion engine is pivotally connected to the internal combustion engine (5,124). 7. One connecting rod (124) has a U-shape, the other connecting rod (125) has a flat rod-like shape, and two parallel rod-shaped intermediate members (126, 126 ') have both ends connected to a crankshaft (13).
7. The internal combustion engine according to claim 6, wherein the internal combustion engine is connected to two connecting rods (124, 125) in a state of being rigidly connected to the connecting rod so as to be pivotable therebetween. 8. An outlet opening in the vicinity of the connecting rod bearing (136) includes an axial groove or channel formed in the outer surface of both or either or both of the rod-shaped intermediate member (126, 126 ') and the connecting rod (124, 125). The internal combustion engine according to claim 1, 2 or 7, characterized by comprising (177). 9. The rotor (10) has a cylindrical race (17) rotatably attached to the housing (1), and the openings (20, 21) are provided in the race (17). The piston bore (13, 14) communicates radially inward, and the race (1
Cylinders (11, 12) provided inside 7) are ribs (18, 1).
9) reinforced against each other and against the race (17)
9. The internal combustion engine according to claim 1, wherein the oil discharge conduit (80) for cooling extends along the race (17). 10. The crankshaft (30) has one end (31).
Is rotatably supported in one of two plates (3, 4) respectively forming a cap and a bottom of the housing (1), and the other end (32) of the crankshaft (30).
The power take-off shaft (34) is supported within a disk (35) that is part of the rotor (10), and the power take-off shaft (34) is securely connected to the rotor (10). The internal combustion engine according to any one of the nine items. 11. The crankshaft (130) has both ends (131, 1).
32) is rotatably supported in plates (103, 104) respectively forming caps and bottoms of the housing (101) and penetrates the disc (155), and one end of the crankshaft (130) is connected to a power take-off shaft. (134)
11. The internal combustion engine according to any one of claims 1 to 10, wherein the internal combustion engine is connected so as not to rotate relative to the internal combustion engine. 12. A gear device comprising: a gear ring (40, 140) mounted on a rotor (10, 110); and two gears (42, 43, 142, 14) supported by a housing and engaged with the gear device.
3) and one gear (41, 141) connected to the crankshaft (30, 130) in mesh with the two gears (42, 43, 142, 143). An internal combustion engine according to any one of the preceding claims. 13. The two gears (42, 43, 142, 143) each have two sets of teeth (421, 422, 431, 421), one above the other.
432,1421,1422,1431,1432), the sets of teeth having different diameters, one set of teeth (421,431,1421,1431) meshes with the gear ring (40,140) of the rotor (10,110), The other set of teeth (422,432,1422,1432) is the crankshaft (3
13. The internal combustion engine according to claim 12, wherein the internal combustion engine is in mesh with a gear (41,141). 14. An inlet opening (50) and / or outlet opening (51) extending into the cylindrical wall (2) of the housing (1) over an angle of about 70 °. The internal combustion engine according to any one of claims 1 to 13, wherein: 15. The inlet opening (150) and / or the outlet opening (151) extend into the cylindrical wall (102) of the housing (101) over an angular range of about 125 ° to 165 °. The internal combustion engine according to any one of claims 1 to 13, characterized in that: 16. An inlet opening (50, 150) and an outlet opening (51).
16. The device according to any one of claims 1 to 15, characterized in that the are arranged adjacent to each other and overlapped along the cylindrical wall (2, 102) of the housing (1, 101). An internal combustion engine as described. 17. An inlet opening (50, 150) and an outlet opening (51).
An internal combustion engine according to any one of claims 1 to 16, characterized in that the internal combustion engine is completely or partially covered by slider means (192).