DE1751073A1 - Crankshaft-less reciprocating machine - Google Patents

Description

March 27, 1968

Daisaku Odawara, No. 52o, Ueno Shiba-cho 5-cho, Sakai-shi, (Japan)

"Crankshaftless machine with reciprocating motion"

The invention relates to a crankshaft-less reciprocating machine with a different mechanism is provided as a conventional crank mechanism to convert a reciprocating motion into a rotary motion or vice versa. The mechanism has at least one pin which is fixedly connected to one or more pistons is to be immovable in relation thereto and which extends radially out of the piston and is endless Cam that is mounted in a fixed or a rotating part, with the pin and the cam and reciprocating said piston or pistons in conjunction with rotary motion of the rotating member bring,

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The invention relates to reciprocating machines Reciprocation, and more particularly to a crankshaft-less reciprocating machine which is provided with a novel mechanism to provide rotational movement to convert to a back and forth motion or vice versa

Common reciprocating reciprocating engines require a crank mechanism to convert reciprocating motion into rotary motion. The crank mechanism has disadvantages in that it involves severe energy losses through friction or otherwise. and it also generates noises and vibrations during operation. Accordingly, common machines with back and float leaves much to be desired in terms of operational efficiency. Furthermore, the crank mechanism has the A tendency to cause the cylinder to become ovoid through wear, resulting in shorter engine life.

In the crank mechanism, the vibrations may increase as the rotational speed increases. This is mainly due to an imbalance in the structure of connecting rods and crank arms. A further increase in the speed of rotation can result in the breaking of screw bolts That set the connecting rods and that

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• Counterweights thrown, causing serious damage to the side cover or motor housing leads.

The aforementioned disadvantages of conventional reciprocating piston motors stem from an imbalance in the Structure peculiar to the crank mechanism. Therefore, the above-mentioned disadvantages of conventional motors with Back and forth motion can only be avoided to a degree within certain limits, as long as the usual Crank mechanism is used.

In the conventional internal combustion engines with reciprocating pistons, the thermal efficiency of the engines depends to a greater extent from the timely opening and closing of the intake and exhaust valves. A machine High precision machining is therefore required in the manufacture of these valves. Since the training J

puff valves are exposed to high temperature exhaust gases, they are particularly exposed to damage. It is therefore not possible to ensure that the Valves operate properly for a long period of time in operation.

Summary of the invention

The invention overcomes all of the above-mentioned disadvantages of conventional reciprocating piston machines.

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Main aim of the invention let / a crankless masonine with to-and-fro movement you create “a new kind of thing Has mechanism that ensures that a back and forth Movement is converted into a (starting movement and a rotary movement In balanced operation in a reciprocating and movement "

Another aim is to create a movement conversion tool that has at least one pin that firmly connected to one or more pistons 1st »do so In relation to being immobile and the sloh radial extends from it to the outside »as well as an endless nook, which is mounted in a fixed or a rotating part »with the pin and the cam reciprocating the piston or the pistons with the rotary motion of the rotating part in connection "

In one type of embodiment of the invention, the circumferential part has a cam with a cam groove its inner side surface and a rotating shaft on, this shaft being carried by a fixed cylinder in which a piston is reciprocally arranged. In another type of embodiment, the revolving part a cylinder with a piston mounted in it and a revolving shaft or shafts that are fixed are attached to the cylinder, the rotating shaft or shafts being held by a fixed ophthalmic tube,

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which is formed with an endless cam groove on the inner side surface.

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Further features and advantages of the invention emerge from the following description of several in the attached schematic drawings of illustrated embodiments.

Fig. 1 is a longitudinal sectional view of an embodiment the pistonless reciprocating machine according to the invention,

Pig. Figure 2 is a side view of a hollow cylindrical Component that forms a groove,

Fig. 3 is a longitudinal sectional view of a second embodiment the invention,

Fig. 4 is a cross-sectional view along the line IV-IV of Fig. 6, a third embodiment of the Invention is shown -. .

Fig. 5 is a developed sectional view taken along the line Circle a of Fig. 4,

Fig. 6 is a longitudinal section not along the line VIrVI of Fig. 4,

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Fig. 7 is a sectional view of a fourth embodiment of the invention which is a modification of the third The embodiment is

Fig. 8 is a longitudinal sectional view of a fifth embodiment of the invention from two machines of the third embodiment, the back to back ' are ordered

Flg. 9 is a longitudinal sectional view of a sixth embodiment of the invention with a pin that sloh both inwardly and outwardly in a radial direction Direction stretches,

Fig. 10 is a longitudinal sectional view of a seventh embodiment the invention built as an internal combustion engine,

Fig. 11 is a longitudinal sectional view of an eighth embodiment of the invention, wherein the cam and the rotating shaft are connected to each other by a transmission,

Fig. 12 is a perspective view of a nooker device with a cam to control the "-eaug- and exhaust valves on one end surface and a gear on the other circumferential surface,

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Fig. 13 is a longitudinal sectional view of a ninth embodiment according to the invention »in which the rotating shaft extends through a fixed cylinder - block extends,

Figure 14 is a longitudinal view through a tenth . Embodiment of the invention wherein two pistons Are arranged face against face,

Fig. 15 is a longitudinal sectional view of an eleventh embodiment implementation of the invention,

Fig. 16 is a sectional view of a buffer device interposed between the pin and the rolling bearing; 1st,

Fig. 17 is a developed view for explaining various Shapes of the cam groove,

Fig. 18 is a longitudinal sectional view of a twelfth embodiment the invention,

Fig. 19 is a longitudinal sectional view of a thirteenth embodiment the invention,

Flg. 20 is a longitudinal sectional view of a fourteenth embodiment of the invention built as a circulation pump,

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Pig. 21 is a sectional view taken along line XXl / XXI of Fig. 20,

j Pig. 22 is a longitudinal sectional view of a fifteenth

Embodiment of the invention, and

Fig. 2j5 is a longitudinal sectional view of a sixteenth Embodiment of the invention.

The invention will then be explained in detail with reference to a first to the eleventh embodiment which are described in Pig. 1 through 17 are shown, each has a rotating part, which consists of a cam and a rotating shaft and wherein the rotating shaft Shaft is carried by a solid cylinder.

In Fig. 1, a piston 2 attached to one end of a piston rod 4 is mounted in a cylinder 2 of a fixed cylinder block 21 so that said piston can slide in the cylinder but is held against rotation relative to the cylinder. At the other End of the piston rod 4 for sliding movement in the cylinder 2, just like the piston J, a pin holder 7 is arranged to which a pin 8 is attached, which extends radially extends outwards and is such that it converts a reciprocating motion into a circular motion or vice versa. A cam 20 that is concentric

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is mounted with the cylinder 2, is attached to a rotating shaft 1 and fixed motionless in relation to said rotating shaft. This cam encloses that part of the cylinder 2 in which the pin 8 works. The rotating shaft 1 is rotatably mounted on the cylinder block 21 through a bearing 1 ^r f. The cam 20 has two hollow cam parts 6 and 6 'which form a cam groove 18 on the inner surface of the cam. The pin 8 extends through a slot in the cylinder block 21 and its front end fits loosely in the cam groove % 18.

The cam groove 18 forms a closed or endless curve on the inner side surface of the cam 20. The cam 20 is constructed so that the piston J> makes at least one reciprocating movement for every complete revolution of the cam.

The cam parts 6 and 6 'are hollow cylindrical members each of which has a curved end, and these curved ends of the two hollow cylindrical cam parts 6 and 6' are complementary to each other as in Pig. 2 shown. The two cam parts β and 6 ', which are arranged as shown in Fig. 2 , are in the Nckeeinriehtung 20 In such a way ur.t ev ^ ebra ·· ^ :, das ;;

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are removed to create the cam groove 18 of the desired width .

When energy is passed into a working chamber 19, the through the cylinder 2 and the piston 3 in Pig. 1 shown Machine is formed, the piston moves with it

a reciprocating motion. The movement of the piston 5 causes the pin holder 7 to move in a reciprocating motion in the cylinder, so that the pin received in the cam groove 18 also moves axially to the piston. This forces the cam device 20 and the rotating shaft to rotate. Conversely, when the cam device 20 is rotated by the rotating shaft 1 by any external force, the cam groove 18 rotates and the pin 8 received in it causes the pin holder 7 and thus the piston 3 in the cylinder 2 to reciprocate move, with the volume of the working chamber can be changed 19th

It is apparent that when the machine is used as an internal combustion engine or as an expansion engine , the rotating shaft 1 serves as an output shaft, but when the machine is used as a pump or a compressor, the αν rotating shaft acts as the input shaft.

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that there is a multitude of cylinders in the machine. An example of such a construction is shown in FIG. 5 as a second embodiment of the invention. In the figure, two piston rods 4-, which have a piston 3 at one end, are provided at the other end with a common pin holder 7, the pistons 3 being oriented in opposite directions. Two units of this piston-pin holder combination are housed coaxially in a fixed cylinder block 21. In the embodiment shown, the cylinder 2 has the "shape (^

an elongated cylinder in the cylinder block, with the two piston-pin holder combinations forming a common working chamber therebetween. The cam devices 20, which correspond in number to the piston-pin holder combination units, are mounted concentrically in the cylinder 2 for rotation their outer circumferential surface and this gear 22 'is in engagement with a gear 25 which is attached to the rotating shaft 1. Accordingly , the reciprocating movement of the pistons 3 causes the cam device 20 to rotate through the pin 8 which is received in the cam groove and the rotational movement of the cam means in turn causes the rotating shaft 1 to rotate through the meshing gears 22 and 23. It is evident from the figure that the two units of pistons - Pen holder combination in the

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Relation to the central cross section of the cylinder block 21 form a mirror-image arrangement. It's clear, that the number of the above-mentioned units which are arranged coaxially in the cylinder, not to two, as shown here, is limited and that the number of · units that can be assembled is theoretically infinite is.

It is clear that the above-mentioned units of the piston-pin holder combination are not only coaxial but can also be arranged parallel to and evenly around the axis of the rotating shaft 1. A multitude the machine shown in Fig. 1 can be arranged around the axis of the rotating shaft 1 and parallel to it. This arrangement is shown in Figures 4-6. The engine shown in these figures comprises six cylinders 2, the are mounted around the rotating axis 1 and parallel to it. The cam device 20 is formed with a cam groove 18, which accommodates therein all pins 8, each of which is on the pin holder 7 of each unit of the piston and pin holder combination is arranged and extends radially outward. In this arrangement the cylinders need 2 not to be arranged around the rotating shaft 1 on a circle. They can be arranged so that they are arranged on a plurality of concentric circles as shown in FIG. In this case you can

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Units of the piston-pin holder combination, which are arranged on different circles, can be combined with one another in a suitable manner and the pin holders of these units can be firmly connected to one another, so that the pin of the unit, which is arranged on the circle of the largest diameter, extend radially can to be received in the cam groove. It is obvious that the units of the piston-pin-holding combination, which are fixedly connected to one another with their pin holding parts A , can move as a unit in a reciprocating motion.

Fig. 8 shows a machine consisting of two sets of the machine 6, which is in an end-to-end relationship with respect to the end plate of the cam means are arranged, which is made in one piece. In this design, the pistons are symmetrical in relation to each other arranged to the cam device 20. When two cam grooves 18 are symmetrical with respect to the central surface of the cam means 20, the pistons move symmetrically with respect to the central surface of the cam means. A fully balanced design can thus be achieved in a reciprocating machine.

The machine shown in FIG. 9 has a thickening 24 which surrounds the rotating shaft 1. The thickening 24 is

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formed with a cam groove 15 in the form of a closed or endless curve on its outer peripheral surface. The pin 8 not only extends radially outward to be loosely received in the cam groove 18, but also through the pen holder 7 and radially downwards to be loosely received in the cam groove 15. Like the cam groove 18, the cam groove 15 is formed by placing the curved ends of two hollow cylindrical parts 5 and 5 'in a spaced relationship be brought from each other.

The cam grooves 15 and 18 are constructed so that each pin 8 is always kept perpendicular to the axis of the piston when the pistons move in a reciprocating motion. The machine shown in Fig. 9 has roller bearings, such as roller bearings, attached to that part of the pin 8 that extends through the slot 16 so that the thrust of the is generated when the pin 8 moves along the winding surfaces of the Cam grooves 15 and 18 moved, up from the rolling bearing can be taken. ·, ^ "

Each of the pins 8 of the machine shown in Fig. 9 has two ends which are received in the cam grooves 15 and 18 and held therein. This arrangement does not allow pairs of forces © that a bending force is brought to act on the piston 3, so that

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the pistons against scratching the Innenoberriüoiv-. ¹ ^ bz cylinder, since the force brought by the Ko.LOp ₁ "- \> / ur action is divided and directed to the p, -yc ^ti! < -I ^ - \ - '· - lying ends of the pin 8 is., each end of the pin 8 trugt substantially half of the force that is brought to an end of the pin to the action, if only one end of the pin is received in the cam groove. This is an advantage provided by the invention in the

Construction of machines of this type is offered. Λ

A device is already known in which a piston, has a pin protruding therefrom and received in a groove formed in a cylinder is, whereby the piston can move in its rotary motion in the cylinder when the latter is in the latter moved in a reciprocating motion. In this known device, the piston and the cylinder move in a rotary motion in addition to the reciprocating sliding motion in relation to each other. That makes it un- ™

possible to create an effective seal for the machine even when a piston ring is used. There however, the piston and cylinder do not move in rotational motion relative to each other in the machine constructed in accordance with the present invention, the engine can be sealed as effectively as when a piston ring is used in the crank mechanism

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would. There is also an additional advantage of the machine nach.der invention in the fact that it is free from imbalance in operation, the two movement conversion occurs, which was a disadvantage of the machine which has to rely on the usual crank mechanism.

Pig. 10 shows a seventh embodiment of the invention, in which the crankless machine is built with reciprocating motion like an internal combustion engine. This machine has a solid cylinder block so that it is possible to use most of the elements of a conventional internal combustion engine to accommodate in the machine without "any modification.

In Pig. 10 is each of the pistons 3 on one of the cylinders 2 mounted, which are formed in the cylinder block 21, which is attached to an outer housing 15 and in relation is immobile to this. Each piston 3 has an attached pin 8 extending radially therefrom extends, the end of each pin 8 being received in the cam groove 18 by a double roller bearing device 9 which is in the inner surface of the cam device 20 is formed.

The cam device 20 is attached to the rotating shaft by a flange 12 and the cam device 20 and the rotating shaft 1 revolve as one unit.

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The rotating shaft 1 is not directly in the cylinder block 21 stored. The rotating shaft 2 is held by a shaft 14 / that on the cylinder block 21 by a bearing 28 is fixed in the flange 12. The cam device 20 is rotatable from the outer housing 1;> supported by a roller bearing 17. Each pin 8 is in the cam groove 18 by a roller bearing device or a roller bearing 9 added, at its outer end away from the piston 3 is mounted. It is evident that all the forces, which are brought to act on the pistons 3 / by the pins 8 are received and that the forces acting on the piston in the axial direction, effective in a rotating force can be converted along that the cam groove 18 acts. The greater the distance between is the cam groove and the axis of rotation of the rotating part, the greater the torque of said torque. In other words, the 'force exerted by the cam groove and carried by the pins is decreased per unit area. This offers advantages in the construction of the machine I. Preferably, the rolling bearing device can have the largest possible diameter. It is obvious, that the larger the diameter of the rolling bearing device is, the lower the number of revolutions of the rolling '" storage facility around the pin 8. '

On the end surface of the cam device 20 opposite the end surface on which the rotating shaft 1 is connected

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there are arranged cams 10 and 11 formed with cam surfaces 29 and JiO , respectively (Pig. 12). The fixed cylinder block 21 has lugs J54 and 35 which are arranged to lie on the paths of the cam surfaces 10 and 11, respectively. The lugs actuate swing arms 62 ′ and 53 by push rods 37 and 38, respectively, and thereby open and close the inlet and outlet valves 2β. J6 are spark plugs and 25 is a cylinder head in which intake and exhaust pipes are formed.

The cam groove in the embodiment shown in Fig. 10 has the shape of a curve as shown in Fig. 17b is. Fig. 10 is a sectional view showing and through the machine in two planes perpendicular to one another the central axis of the machine.

The eighth embodiment shown in FIG. 11 represents a development of the second embodiment shown in FIG. 3. The cylinder block 21 has a plurality of cylinders 2 extending through it and two pistons 3 mounted in each which are attached to opposite ends of a piston rod 4. In the middle part of each piston rod 4 there is a pin holder J ₁ - from which a pin extends radially outward. The end of each pin 8 is through a double roller bearing device 9 in the

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Cam groove 18 added, which in the cam device 20 is designed, as in the embodiment shown in Fig. 10

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leadership form, r Pail is. In the embodiment according to FIG. 11, each cylinder is provided with an intake and exhaust valve 26 and a spark plug J> 6 , the yen * tiles and spark plugs being arranged on opposite end surfaces of the cylinder block 21.

The cam device 20 is provided with a gear .22 on its A outer peripheral surface which meshes with a gear 2j5 which is keyed to the rotating shaft 1 ■ ■ which is rotatably supported in the fixed cylinder block 21. Like that the case with the embodiment shown in Fig. 3 embodiment., the reciprocating movement of the piston 5 in the rotary movement of the cam means by the -Stift-cam assembly converted 20 _s which is in turn transformed into die_Drehbewegung the rotating shaft 1 by the gears , creating a force

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This embodiment is provided with spark plugs ~ *> 6 , as already mentioned above. It is evident / that if the engine is provided with dispensing pumps and nozzles the engine can operate as a diesel engine. The cam groove of the embodiment according to FIG. 11 has the shape of a

curve shown in Fig. 17b. Fig. 11 is a '. Pattern ■

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sees that the machine is in two planes perpendicular to each other shows and through the central axis of the machine.

Fig. 12 shows the cam parts 10 and 11 and their respective ones Cam surfaces 29 and JO. These cam surfaces 10 and 11 are disposed on opposite end surfaces of the cam device 20. That Gear 22 is mounted on the outer peripheral surface of the cam device 20.

The ninth embodiment shown in FIG. 13 is one Modification of the embodiment shown in Fig. 10, at which the rotating shaft 1 extends through the fixed cylinder block 21. The mechanism for operating the valves, The piston, cam directions and cam groove according to this embodiment are identical to that shown in FIG Embodiment with the exception that the cam device 20 is not rotatably mounted in an outer housing is, but connected to the rotating shaft 1 and is immobile in relation to it, said rotating shaft 1 is rotatably supported by cylinder block 21 through bearings 17. This arrangement is advantageous when the machine rotates at high speed because the peripheral speed of the cam device becomes large increases when the revolving speed of the machine is increased, making it difficult to use the cam mechanism to hold on their outer surface. the

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Bearings 17 are preferably with thrust bearing surfaces j31 Mistake.

The tenth in'Pig. The embodiment shown in FIG. 14 has two Piston 3, face versus face in a single Cylinder 2 are housed. The two pistons in a cylinder have a stroke that is twice as large '

how the stroke of a single piston is and the space -

between the two pistons changes its volume with

a speed twice as fast as -that Speed / with which the room would change, if only one piston was used. This allows to achieve a high resistance to heat during operation. The cam devices 20 are rotatably arranged within the cylinder block 21 in its opposite end portions. Each cam device 20 is provided with a cam groove 18 formed on the inside surface. Opposite Ends of the pin 8 extend radially from " the pen holder 7 to the outside, which after it has been connected to the Piston j5 connected under piston rod 4 and immovable in relation to it, in the form of a sliding block 40 has. These opposite ends of the pin 8 are received in the cam groove 18 by a roller bearing 9 » Each cam device 20 has on its outer circumferential surface a gear 22 which is in mesh with a gear 23 which is keyed on the rotating shaft 2 ■ is, '■

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Said slide block 40 is slidably mounted within a sleeve 39 connected to the cylinder block 21 and is immobile in relation to it. The sleeve 39 is formed with a slot 16 through the opposite ends of the pin 8 extend.

From the above description and the illustration in the figure it is clear that the pin is received and held in the cam groove 18 at its opposite ends. The cam groove 18 of the machine shown in FIG. 14 is in the form of one shown in FIG. 17b. Although the machine is recorded with a cam groove for four-stroke operation, the machine is built so that two burns occur during one revolution of the rotating shaft 1 and the intake and exhaust valves are also built for two-stroke operation. Accordingly, the machine can develop a higher power than other motors of the same displacement. As can be seen from the foregoing description, the sleeve 39 and the sliding block 40 do not move in a rotational movement in relation to one another, but in a sliding movement in relation to one another. The pin 8 carries roller bearings 9 on its ends, as is the case in the embodiments shown in FIGS. 10, 11 and 13. A bearing 41 for holding the piston rod 4 is mounted on the inner end of the sleeve 39.

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Said sleeve 39 and the slide block 40 serve in a certain way as a cylinder and piston and constitute a device for supplying the cylinder 2 with an air-fuel mixture. The bearing 41 is formed with a conduit 44 therethrough, in which a valve 4j is mounted which is under the influence of a spring 48. This spring normally pushes the valve 43 in a direction to shut off the conduit 44. When the pressure in a working chamber III rises and the pressure in a working chamber 11 in the cylinder 2 becomes negative, the valve 43 is opened in order to deliver an air fuel from the chamber III to the chamber II The sliding block 40 is provided with a valve 42 and a spring 49, which serve as a shut-off device Chamber is negative and when the pressure in this chamber rises as a result of the sliding movement of the sliding block 40, the valve is closed to prevent the air-fuel mixture from flowing backwards in the working chamber III. The sliding block 40 is provided with a main line 51 for the The air-fuel mixture feed line is formed and a branch line 50 branches off from said main line in order to open into the working chamber III, the valve 42 being mounted therein.

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The air-fuel mixture in the working chamber III begins to be compressed 'when the slot is completely closed and sealed by the slide block 40. The volume in working chamber III is larger than that in the working chamber 1 in the cylinder, so that a sufficiently large amount of an air-fuel mixture of the Chamber III can be supplied.

As the pistons 3 slide outwardly as shown, and the outlet ports 32 are opened during a combustion stroke, the exhaust gases are through the said Openings 32 drained. The suction openings 47 are also open and allow the compressed air-fuel mixture in the chambers II in the chamber I. through lines 45 and 46 and the suction openings 47 mentioned. The valve 43 for everyone Passage 44 remains closed. 31 denotes air supply lines.

Fig. 15 shows an embodiment similar to the fifth embodiment 8 combined with the sixth embodiment according to FIG. 9 and operates as an internal combustion engine. In the present embodiment, the cam device 20 having the shape shown in FIG. 5 is with a thickening 24, through which the rotating shaft 1 extends and in relation to it un-

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is movable. The rotating shaft is rotatably mounted on the cylinder block 21 through the bearings 17. The cam grooves 18, formed by the hollow cylindrical members 6 and 6 'are on the inner side surface of the thickening 2.4 of the cam device 20 arranged during

the cam grooves 15 * those of the hollow cylindrical parts 5 and 5 'are formed on the outer side surface the thickening 24 are arranged. Each pin 8 extending through each piston 3 and radially outward and extending inwardly, has opposite ends locked in the cam grooves 18 and 15, respectively, by a roller bearing are included. The cam grooves 18 and 15 are in proportion arranged to each other in such a way that the pin 8, its opposite ends in said Cam grooves are added, is correctly arranged radially. Each pin 8 is provided with roller bearings 25 on the part where the pin 8 extends through the slot 16, to absorb the thrust applied to the pin when the reciprocating motion of the plunger converted into the rotational movement of the cam device 20 will. The forces required to transform the motion are distributed to the opposite ends of the pin, thereby reducing the forces which are applied to each end of the pin and the side surfaces of the cam grooves. These Arrangement is very important in the design of the machine advantageous.

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In the present embodiment, the cam parts are 1O and 11 for controlling the suction and discharge valves 26 on the end surface of the hollow cylindrical Part 5 'arranged, which is arranged over the thickening 4 in a comprehensive relationship. The cam device, which is the rotating part is rotatably supported by the rotating shaft 1, so that the structure is suitable for high speed circulation.

In the embodiments shown in FIGS. 10, 11, 15 and 15 have the roller bearings rented on the opposite ends of the pin 8 in the form of double Roller bearings. This arrangement allows a heavy load to be withstood and the speed at the same time to distribute between the two roller bearings and the relative speed of the outer ring and the ρ to reduce the inner ring of each roller bearing when the machine is rotating at high speed.

A buffer device for absorbing shocks can be mounted between the pin and the roller bearing device in order to reduce the shock to which the pin 8 is exposed. This buffer device may be one using oil or one made of rubber. The embodiment shown in Fig. 16 uses oil. As shown, the pin has 8 at its end

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a washer provided with a groove .54, in the one outer disc 55 is bordered, the. split in two and has protruding parts that bear against the grooves of the disc 54. Between the grooves of the Disc 5 ^ and the protruding parts of the. outer Washer 55 there is a gap 56 in the oil is arranged sealed. In this case, the action brought about by the roller bearing device Do not transfer the impact directly to the pen, but rather, from ' to the. oil steamed in the space 56, whereby one Be. »· Damage to the pin 8 is prevented. 57 shows (HEinge to prevent oil leakage.

It should be noted that the cam groove i8 of the Üurbellosen Machine with reciprocating motion according to the invention can be variable in shape and shape, depending on whether the machine is used for two-stroke or four-stroke operation. Since the side surface of the cam device, which is large in its area, can be used to accommodate the cam groove, it is possible not only Provide two-stroke or four-stroke operation as mentioned above, but also, if necessary, one Six-stroke operation. It has so far been the case with machines of this type It has been common for the piston to rotate during a rotary motion can only perform a reciprocating motion. The present invention allows the piston, a up to three reciprocating movements or more during

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perform an orbital motion, thereby increasing the performance is increased accordingly. Fig. 17 is a developed view showing the shape and configurations of the cam groove 18 for shows each application area. In the figure, the piston 3, the piston rod 4, the pin 8, the roller bearing device 9 and the cam groove 18 shown schematically. Fig. Figure 17a shows the cam groove for two stroke operation when used with a compressible medium. Figures 17b and 17c are the cam grooves for four-stroke or six-stroke operation. When an internal combustion engine is running at high speed is operated, the cooling is an important problem. The cam groove for the cycle with a cooling stroke is shown in Figure 17d. In this case the cooling cycle is designed to remove heat directly from the surfaces of the Remove the piston and cylinder by drawing in air through suction and releasing it in the same way around the cylinder to rinse completely. The piston does not need to travel the entire distance of the stroke in the cooling stroke. The usual The procedure is that the piston moves in the back and forth movement only over part of the distance of the stroke, as shown in Figure 17d. It is thus one of the advantages of the present invention that the pistons are so arranged may move in reciprocating motion through part of the stroke if necessary is.

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The aforementioned feature of the present invention makes this crankless reciprocating machine useful as an expansion machine. When an expandable material is made to work in the working chamber to generate a rotational force, it is desirable that the expansion stroke of the piston be extended. It is so beneficial to take precautions so that the 180 ° angle of rotation is used as an expansion stroke and the remaining 180 ° angle is used as the exhaust, intake and compression strokes. The cam groove suitable for use with this application is in Pig. 1Te ₁ shown. ■

The cam groove for a two-stroke operation with a no compressible medium is in Pig. 1.7f.

From the above description it is clear that The crankless reciprocating machine according to the invention for all types of. Work adapted can be, in which the length of the effective stroke of the Piston and the time interval required for the piston to cover the distance of the stroke Can be changed at will. In particular, the machine can be designed in such a way that the piston is in rapid advance and slow backward movement moves or stops for a predetermined period of time.

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The following are the embodiments of the invention recalling Pig. 18 to 22 described, wherein the circumferential part has a cylinder device which has a piston mounted therein and a rotating shaft or shafts fixedly attached to the cylinder assembly and wherein an endless cam groove is formed on the inner side surface of a fixed housing is.

In Fig. 18, rotating shafts 61 are concentrically connected to one another at opposite ends of a cylinder device 80 and are immovable in relation to one another. These parts, which constitute the rotating part, are rotatably mounted in a fixed housing 81 through bearings 77 which support said rotating shafts 61. A cylinder 62 is formed in the cylinder device 80. Sliding in this cylinder 62 is a piston 63 to which a piston rod 64 is attached at one end. The piston rod 64 is fixedly connected at the other end to a pin holder 67, which can slide in the cylinder 62 together with the piston 6j5 as a unit, and has a motion conversion pin 68 which protrudes radially outward from the cylinder. The pin 68 extends through a base seat 76 which is formed in the cylinder 80 and the front end of the pin 68 is received in and movable in a nook groove 78 which is formed from two nook parts 66 and 66 * , the

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are arranged on the inner side surface of the fixed housing. The cam groove has the shape of a closed one Curve on the inner side surface of the fixed housing and the piston 6j5 makes at least one reciprocating motion while cylinder 80 rotates fully one time.

The cam parts 66 and 66 'are hollow cylindrical parts, each of which has a curvilinear end like that of the ™

The case with the cam parts 6 and 6 'according to FIG. At least one of the rotating shafts 61 which are axially aligned and immovable in relation to one another, extends through one of the end walls of the fixed housing 81 and acts as an output shaft when the engine is used as an internal combustion engine or expansion machine. However, it acts as an input shaft when the machine used as a pump or compressor.

In the machine shown in Fig. 18, and when the Piston 6j in a reciprocating motion by the energy which is fed to the working chamber 79, which is represented by the cylinder 62 and piston 63, is moved the utifthhalter 67 is also in a reciprocating motion in the cylinder 62 because of its connection with the piston through the piston rod 64. This forces the pin 68 to move along the cam groove 78. the

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^; Movement of the pin 68 in turn causes the piston 6j5 and the cylinder device 80 and thus the rotating shafts 61 to rotate. Conversely, if the cylinder

'device 80 is caused to move by a force } .. turn, which from the outside to the rotating shafts 61 to "■ - '·

* · Action is applied, the pin 68 moves along the cam groove 78, which means that the pin

£ holder 6j and the piston rod 64 force the piston 6j5,

ί ■ ■

$ ■■ itself in a reciprocating motion in the cylinder

'i-
? i. 62 to move, thereby increasing the volume of the working chamber

79 to change.

The one in Pig. The machine shown in 18 can be arranged in such a way that that several cylinders can be mounted. An example of this adaptation is shown in Fig. 19 as a thirteenth Embodiment of the invention shown. In Fig. 19 are two pistons 63 and 6j5, each at one end of each : that of the piston rods 64 and 64 attached to their ™ other end on opposite sides of a common Pin holder 67 are attached and the pistons are arranged in a back-to-back relationship and form one unity. Two units are shown mounted coaxially in cylinder 80. The cylinders 62 have the shape an elongated cylinder in the cylinder device, with two pistons in the middle and the cylinder wall one represent a common working chamber. Two cam grooves 78 ■ and 78 bind on the inner side surface of the fixed

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-; ■ 33 ■

Housing 81 formed. As can be seen from the figure, the two units form a mirror-image arrangement in relation to the central cross-section of the Cylinder assembly 80. It will be understood that the invention is not limited to the number and arrangement of units as described and illustrated herein, and that the number of units shown in FIG the cylinder can be arranged, theoretically infinite - like that of the pail in the second in Flg. 3 illustrated embodiment is.

It is also clear that the multiple units of the cylinders can be arranged not only coaxially, as shown in FIG. 19, but parallel and around the axis "of the rotating shaft, such as the third in FIGS. K, 5 and β Embodiment shown and on a plurality of concentric circles, as shown in FIG.

The fourteenth embodiment, as shown in FIG. 20, is shown as a circulating pump. The cylinder device 80 including the cylinder 6.2, which are arranged parallel to and around the axis of the rotating shaft 61, the spacer collar 82, the piston rod support 74, the spacer ring 83 and the bearing washer. 72 are

all keyed to the rotating shaft 61 for rotation therewith as a unit. The bearing bracket 72 is rotatable, held by the fixed bracket 81 by a Sehuhlsger Bk-

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and has bearing openings 73 > to receive and hold a piston rod at one end. Each piston rod 64 is held at the other end by one of the bearing parts 65, each of which represents the bottom of the cylinder 62. The bearing parts 65 also serve to center the pistons 63 with respect to the cylinders 62. The pin holder 67 through which a pin 68 extends radially outward is essentially in the middle part of each piston rod 64

P and extends inward. The pin 68 has a radial outer end that is held in the cam groove 78 by a roller bearing 69 is added in the form of a roller bearing. Forces acting on the piston 63 are on the Focused pen 68. It is apparent that by providing the pin with the roller bearing as above mentioned, forces that act on the piston rods in the axial direction are effectively converted into forces, which act on the pin to press it in such a way that

t that it rolls along the cam groove.

The piston rod seat 74 is formed with a slot 76 disposed axially of the piston rod 64 for receiving therein the inner end portion of the pin 68 which extends radially inward. The slot 76 serves to guide the inner end portion of the pin 68, which moves in a reciprocating motion with the piston rod 63 as a unit . The outer side surface of the piston rod support 74 is close to the

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Slot 76 serves to maintain the smooth surface of the To hold the pin holder 67 and to prevent the axial deviation of the piston rod 64. The inner side surface of the piston rod seat 74 in the vicinity of the Slot 76 is used to a sliding device 75 to keep that mounted on the inner end of the pin 68 is. The sliding device 75 is supported by a roller bearing held, for example, from four rollers 70 that insists on four points on the inner end of the ™

Are arranged pin (see Fig. 21). This arrangement ensures that the pin 68 is held in such a manner that it is positively and axially aligned at all times. It is perfectly clear. " that there is significant _s hold the pen in a position au, in which it is positively axially aligned at all times, because the Wälzlager'69 has the tendency-auszygleittsn forth from the cam groove 78 when άατ pin 68 is not aligned positively axially . j

The cam groove 78 is generally inclined in relation to the direction of reciprocation of the piston rod 64. The provision of the sliding device 75 serves to prevent the piston rod 64 from deviating. which is caused by the arrangement described above and the deviation of the piston rod 64, which is caused by the centrifugal forces acting on it, when the number of revolutions of the

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Machine increases. The cam groove 78 aims to to exert a force on the pin that is axially aligned with the piston rod 64. This force acts at the same time to cause the pen 68 to move parallel to the plane of the figure around the pen holder 67 turns. The provision of the slider 75 also serves to prevent this effect. The friction pull of the Piston rod 64 on the piston rod support 7 ^ can through ^ the roles of the slider 75 are reduced.

In Pig. 20, the fixed housing 81 is provided with a front cover 92 attached thereto. This cover has a suction opening 91 and an outlet opening 95. In this case, the cam groove is in the form of a curve, Fig. 17f, for two-stroke work. The distance between the suction port 91 and the outlet port 92 should be chosen so that the distance is large, to prevent than the diameter of the cylinder 62 in order that the W two openings are brought by one of the cylinders 62 in short-circuit connection when the cylinder in question is disengaged from correspondence with the suction port and moved in correspondence with the discharge port. Since the cylinder 62 is completely sealed by the front cover between the two openings, it is advantageous to stop the operation of the pistons in this transition period, since in such a case the machine will handle an incompressible medium.

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.if. ■

According to the invention, this can easily be achieved by choosing the curve of the cam groove in such a way that the part in the curve that the Interruption of the path of the piston, in right th angles to the axis of the piston rod is arranged. In a conventional mechanism. It is impossible to use the Compression stroke of pistons to stop at this point, causing frequent damage to the machine revealed. It is common practice to have a pressure relief valve in front of

watch, whereby a medium is led under high pressure to ^{1 of} the openings in order to prevent damage. The disadvantage of this arrangement is that there is a limit to the high pressure that can be reached because of this relief. -

The advantages of the crankless reciprocating machine according to the invention can be summarized as follows: · '■ "' i

1.) The invention allows that in the machine many cylinders are housed, which are either 'coaxial or are arranged around the axis of the machine, whereby the performance of the machine is increased.

2.) The arrangement that the rotating part balanced irr its construction and operation let _{s p} allows the machine with high. To let speed circulate "

■ iV. - 27 - G08833 / Q686 ί

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with no damage due to the imbalance of the Part can enter while rotating at high speed.

j5.) The invention allows an airtight seal to create for the working chamber or the chambers can fluctuate with their volume because less Probability of a gas leak is present than with conventional machines of the same type.

4.) The invention allows that the machine in two or more cycles, as desired, during one revolution works by properly choosing the shape of the cam groove, and

5.) The invention gives wide leeway in choosing the ratio of one stroke to another during of an operating cycle.

The invention is not restricted to the embodiment shown in the drawings, but is to be protected by US patents according to the appended claims.

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Claims (1)

P a ten ta η s ρ r ti c h e i 1. Crankless machine with reciprocating motion, characterized in that one piston or several pistons - which are moved in reciprocating motion and a rotating part is present, which moves in rotation, and that these parts go through with one another at least one pin are connected, λ which is fixedly connected to said piston and extends radially outward and an endless cam groove in a fixed part or the named rotating part is trained. 2. A reciprocating crankless machine according to claim 1, characterized in that said circumferential part a cam © inriehtimg and, a - ■ circumferential Shaft, the said Noekeaeinrich- with an endless cam groove on its inner " Side surface is formed and a KqXben sur Reciprocating movement is arranged in a fixed cylinder. , 3. Crankless reciprocating machine according to claim 1, characterized in that the. ge ™ called the rotating part a cylinder and a rotating part Has shaft that is firmly attached to said cylinder, 0 09833/0696 BADORfGfNAL said cylinder means accommodating a reciprocating piston and said rotating shaft is held by a solid, housing, this solid housing having an endless cam groove on its interior Side surface is formed. K. A crankless reciprocating machine according to claims 1 or 2, characterized in that a plurality of working chambers, each formed by a cylinder and a piston and having a variable volume, are axially of said piston are arranged. 5. crank lots machine with reciprocating motion according to any one of the preceding claims, characterized in that a plurality of working chambers is provided, each of which is formed by a cylinder and a piston and. with a variable volume, these cylinders and pistons being arranged parallel to and around the axis of a rotating shaft or on a plurality of concentric circles which are arranged around the axis of the rotating shaft. 6. A reciprocating crankless machine according to any one of the preceding claims, characterized in: that a pin which is fixedly connected at one end to a piston and extends radially outward from it -. ¹ M) - 0 0 S 8 3 3/0 6 S Ü extends, at the other end in an endless cam groove is added by a roller bearing and, if necessary, a buffer device. .7. Crankless machine with back and forth. Moving after any one of the preceding claims, characterized in that a pin which is fixed at one end connected to a piston. and radially outwards extending through a slot located in a fixed or rotating cylinder to at the other end to be received in an endless cam groove, a roller bearing which is arranged on the part which against said slot. 8. Crankless machine with reciprocating motion according to any one of the preceding claims, characterized in characterized in that the endless cam groove is constructed so that a piston has one or a plurality of reciprocating. and performs reciprocating movements in a cylinder, while the rotating part makes one complete revolution executes. 9. Crankless machine with reciprocating motion behind Any of the preceding claims, characterized in that the endless cam groove is so constructed is that the distance traveled by a piston is moving to and fro in a cylinder ~ 'k \ - 001633/0690 BATH ORIGINAL " Hz and / or the speed of movement thereof can be changed from stroke to stroke. 10. A reciprocating crankless machine according to claims 4 to 9, characterized in that two pistons are disposed face to face in a cylinder to form opposed pistons 11. Crankless machine with reciprocating motion behind ■ i ■ Claims 3 to 10, characterized in that ¹ the axis of rotation of the cam and the axis of rotation of the rotating shaft are not aligned with each other and the cam and the rotating shaft are connected to each other for rotation by gears. 12. Crankless machine with reciprocating motion according to Any of the preceding claims, characterized in that a pin extends through a piston and has two ends that protrude radially outward and inward to be received in corresponding groove grooves to become. . 0 »» 833 / 0δΙ6 BATH * ORIGINAL H3 Lee rse i te