DE1401421A1 - Machine or pump system - Google Patents

Description

Machine or 2-pump system. The invention relates to machines, pumps or similar systems (mechanisms). It is indifferent to machines of the type of internal combustion engines I whether they work with compression or spark ignition, according to the two- or four-stroke system or according to another suitable working cycle principle, as well as to machines that are operated with a pressure medium, such as steam machines and hydraulic machines. Furthermore, the invention can be used for pressure pumps as well as for suction and flushing pumps and for liquids as well as for gases. The invention has as its Aufgabes a mechanism to schaffeng the crowded (compact) and simple and Üo- well in the production-and can be assembled and disassembled for maintenance easy and f erner worked long and störunggfrei.

Furthermore, the invention wants to give an internal combustion engine to the hand, which is resilient and capable, a high power (performance): weight ratio (where the strength-to-weight ratio is large) that usually doesn't is heavily loaded (stressed), an essentially uniform- * torque developed and has an inherent degree of precompression when the machine mass itself is rotatable. A two-stroke internal combustion engine according to the invention is above also particularly simple in construction.

According to one characteristic of the invention, there is provided a machine or pump mechanism which comprises a cylinder in the form of a torus section. The cylinder is arranged entirely on one side of a first axis which passes through and in the axis of the generatrix of the torus A piston is arranged entirely on one side of a second axis and is mounted with respect to the second axis in such a way that it can swivel around a radius of the pitch circle of the torus. that it can oscillate relative to this along its pitch circle *, the second axis being arranged at an acute angle to the first axis, passing through the intersection of the first axis and the axis of the generatrix of the torus and lying in the plane of its pitch circle by a series of relative rocking movement - the Kölbäns in the cylinder e -: 'LÜe.rela-tive # -, # Dr>' e "- the cylinder and 'the second Axis; to the.' äi ## te 'AehäL> causes or vice versa.

. -After '-, a-ne-in-weirtbeen characteristic of the invention, a machine or PU # mpenmächanismüä is provided., - the two cylinders in the form of equal, toned sections. of the Elbe torus. -The cylinders are completely # on opposite sides of a -first axis and symmetrically to it; this axis goes through the axis of the generating of the torus and lies in the plane of its partial circles. The mechanism further comprises two on opposite sides of a second axis-and symmetrically therewith-anodized # and with-relation to the second axis in such a way. stored piston so that each piston can swivel around a radius of the pitch circle of the Toxus bine #. '" Each piston is accommodated in a cylinder in such a way - that it" can swing "relative to it along its pitch circle, the second axis being arranged at an acute angle to the first axis, through the intersection of the first axis and the axis. the generating line of the torus and lies in the plane of its pitch circle. A relative oscillation of the pistons to their corresponding cylinders causes a relative rotation between the cylinders on the one hand and the second axis on the other hand around the first axis or causes such an oscillation immediately afterwards.

According to a further characteristic of the invention is a machine or- "Pump mechanics: LamuE!, yg-seen, a row or rows - (or blocks) # -vQn -,., symmetry - around -, - comprises cylinders arranged on a first axis .. each cylinder having one Row has the shape of a Torua segment » its pitch circle forms a longitudinal line (meridian) of an imaginary sphere; this length line goes at opposite poles of the sphere forming points through the first axis, where the cylinders of the row a first zone of the sphere, arranged around the first axis take in. The mechanism also includes a plurality of cylinders for the bank of cylinders Pistons which are arranged symmetrically about a second axis on a turnstile (spider) and are mounted in such a way that each piston swivels by one radius the ball and all but one or two diametrically opposed pistons own circumferential movement with respect to the large number of pistons allowed. Every piston is housed in a cylinder so that it is relative to this # along it Partial circle can oscillate, whereby-the pistons for the cylinder row have a second within.der occupy the first spherical zone housed but arranged around the second axis.

The second axis is at an acute angle to the first axis arranged and goes through this at the center of the sphere, being by a relative Vibration of the pistons to their respective cylinders is a relative rotation between a cylinder bank and its second axis is effected around the first axis, or it causes such a vibration immediately afterwards.

A cylinder bank can stand still and the second axis can rotate about the first axis, so that a swashplate movement is imparted to the plurality of its pistons. Alternatively, a row of cylinders can rotate around the first axis - and a large number of its pistons can rotate around a fixed second set of axes, in which case the row of cylinders acts as a flywheel. According to yet another characteristic of the invention, a two-stroke internal combustion engine designed for effective pre-compression is provided which comprises a row or rows of cylinders arranged symmetrically about a first axis, each cylinder of a row having the shape of a toroid whose pitch circle is a meridian of an imaginary sphere forms; this longitudinal axis goes to opposite poles of the sphere-forming points through the first axis, the cylinders of the row occupying a first zone of the sphere, arranged around the first axis. The machine also comprises a plurality of pistons for the cylinder row, which are arranged symmetrically on a turnstile about a second axis and are mounted in such a way that each piston has a pivoting movement around a radius of the ball and all but one or two diametrically opposed pistons, allowing their own circumferential movement with respect to the large number of pistons. Each piston is accommodated in a cylinder in such a way that it can swing relative to this along its pitch circle, the pistons for the cylinder row occupying a second spherical zone housed within the first but arranged around the second axis. The second zone is arranged around the second axis. The second axis is provided at an acute angle to the first axis and passes through this in the center of the ball, and static (fixed), but in the circumferential direction adjustable closing elements are close to the outlet openings or close to the inlet and outlet openings of the cylinders arranged, where. a rotation of a cylinder bank - about the first axis and an associated rotation of the plurality of pistons - about its second axis is effected by a subsequent relative oscillation of the pistons to their respective cylindersv and such a rotation of the cylinder bank in cooperation with the in Closing members adjusted in the circumferential direction cause a subsequent exact and strong opening and closing of the outlet openings or the inlet and outlet openings in the most favorable control positions.

The pistons can each be a single-acting, one-sided piston; in this case only one compression chamber is used at each end of the cylinder. Alternatively, each piston may be double acting in that it is double-sided and comprises a pair of back to back arranged one-sided piston members, in which case both ends of each cylinder al a Kompressioneräume be used; this arrangement has the advantage of dynamic equilibrium. The mechanism may have two rows of cylinders a # Ufwei- 'sent wherein each row has the same axis and the -first-imaginary sphere each row has the same size as that of the other part and to cover (overlap). In this construction, each toroidal cylinder of one row is o.-L, 'fen against or in communication with a toroidal cylinder of the other row and the second axes are arranged in the same plane and go at equal inclinations to the first axis; but in the opposite sense through this, so that in operation piston pairs, each consisting of a piston in a cylinder of one row and a piston in a communicating cylinder of the other row of the device in their cylinders oscillate synchronously in opposite directions and successively alternately converge and diverge The space between each piston pair in the connection area between the corresponding pair of communicating toroidal cylinders is used as a compression space. The or each plurality of pistons are carried by a turnstile and each piston is attached to the turnstile by means of a hinge designed to compensate for the relative pivoting movements that occur between the piston and the turnstile during operation of the mechanism. One or each of two diametrically opposite main joints is designed so that it absorbs a pivoting movement between its piston and the turnstile. Such a pivoting movement takes place only around one axis through the or each Hauptverbindg that extends radially to the turnstile. -All other auxiliary joints must be designed so that they accommodate both relative pivoting movements and relative circumferential movements of the plurality of pistons between the corresponding pistons and the turnstile. This latter construction is due to the fact that the pitch circles of adjacent cylinders, which are separated by angles less than 180 degrees, converge as they approach each of the opposite poles of the imaginary sphere connected by the first axis.

For a better understanding of the invention, reference is made in the following description to the accompanying drawings which show the subject matter of the invention by way of example. Therein, Fig, 1 is an axial section through a rotary (star) motor, which forms an embodiment of the invention. FIG. 2 shows a crack of the turnstile removed from the engine according to FIG. 1 and also shows the pistons in section. Fig. 3 shows a section through the turnstile alone along the line III-III of Fig. 2. In Fig. 4 there is shown a sectional view of a fixed closure member which cooperates with an outlet opening. Figure 5 illustrates a view in axial section of two motors of Figures 1 to 3e coupled together and modified to act as one motor. Fig. 6 is a partial axial section through a rotary motor similar to that shown in Figs. 1 to 3 , but mechanical means. to counteract the centrifugal force of the rotating pistons and have a modified connection between the turnstile and the axial shafts of the motor '. FIG. 7 shows a partial view of the mechanical means which are provided to counteract the centrifugal force of the rotating pistons in the engine according to FIG. 6 . Fig. 8 shows an axial section through a Umlaufmtor darg the back to the but similar in FIGS. 1 to 3 shown ISTG hydraulic has means of the centrifugal force of the orbiting piston counteract a further modified connection between the hub UUED the axial shafts of the Motor and other design changes. Fig. 9 is a partial section of the turnstile according to the line IX - IX of Figure 8 and shows a part of the hy- draulic systems.. FIG. 10 shows a partial section along the line X - X of FIG. 9 and shows a further partial view of such a hydraulic system. Fig. 11 is a view of a shown in Figs. 8 and 9 shown from a radially outer point. Fig. 12 shows a partially sectioned side view of a main piston 89 takes the darg 9 and 11 used in connection with the aid of piston of FIGS.. FIG. 13 illustrates a view of the piston according to FIG. 12 in the manner of FIG. 11. Pig. 14 is a greatly enlarged sectional view of a detail 8 of FIG 9.v 9 and 12. In Figure 15 is a partially sectional side view is shown of a modified assistance piston, DER -... A corresponding piston according to Figs 89 9 and 11, he set to . FIG. 16 shows a view of the piston according to FIG. 15 in the manner according to FIG. 11 . 17 illustrates a partial axial section of a modification of the hydraulic system according to FIG. 10.

An embodiment of the invention is shown in FIGS. 19 2 and 3 in the form of a two-stroke gasoline engine, which aufwe is a row of six symmetrically arranged and on bearings 2 about a shaft 3 rotatable cylinders. In order to attenuate heat transfer from the cylinders to these bearings during or immediately after the engine is running, insulating liners 4 are arranged between the bearings and the cylinder block. Each cylinder 5 has the shape of a torua segment, the generatrix of which forms a meridian of an imaginary sphere; this meridian passes through the axis of the shaft 3 at points forming opposite poles of the sphere, the cylinders occupying a first zone of the sphere arranged around the axis of the shaft. A double-acting, double-sided piston is housed in each cylinder in such a way that it swings along its pitch circle and both ends of each cylinder are used as compression and combustion chambers. The pistons are arranged on a turnstile 7 , which is held between a nut 9 and an annular shoulder 10 rotatably on bearings 8 around a sleeve 11 which is non-rotatable by means of bolts 11a and held in such a way around the shaft 3 that the axis of the Sleeve arranged at an acute angle to the axis of the shaft and this goes in the center of the imaginary sphere. The sleeve and the bearings are accommodated in a space within the cylinder row which is delimited by an inner annular wall 12.

The pistons are arranged on the spider in such a way that they occupy a second zone of the imaginary sphere housed within the first but arranged around the axis of the sleeve. The connections between the piston and the hub are designed as a piston pin 13 and secured at its ends 14 on the radial arms 15 of the turnstile by means of slots 16 in which those ends 14, perforated retaining caps 17 and screws 18, the voltages through the openings of the Pass caps through and are screwed into the turnstile arms, as shown at the bottom of FIG. The arms 15 extend with play through slots in the inner annular wall 12 which opens against adjacent cylinders. Ball joints are provided to accommodate (to compensate) the pivoting movements between the pistons and the turnstile, in that the middle area of each piston pin is designed as a ball 19 or by a ball 19 being rigidly attached to the inner area of each piston pin located within a pair of mating shells 20 carried by j (#the cbIbIbIbIbIbIben. Two diametrically opposed main ball joints receive only pivotal movements between their respective pistons and the turnstile and therefore the mating shells are bolted to the pistons at 21. As described above, a Such pivoting movement only about an axis through Aes main joint, which extends radially to the turnstile, so that the joints need only be simple pivot joints - although the main joints have been described as ball joints. The other four auxiliary joints also move between their respective pistons and the turntable uz in the circumferential direction of the set of six pistons. This additional movement adjustment by the auxiliary ball joints is provided by the fact that each respective piston can slide around and along a straight cylindrical guide sleeve 22 with the mating shells enclosed therein and between an annular shoulder 23 and an internal screw 24. Since the guide sleeve is straight, such a special movement is de facto rather a combination of a tendon movement and a pivoting movement about an axis through the joint parallel to the axis of the sleeve . A. a real circumferential movement 'and therefore causes a very light one Radial movement which, due to its insignificance, is absorbed by the work cycle. This radial movement can, however, be used as a pumping action to support the lubrication. Uin the manufacture, to facilitate assembly and disassembly of the engine DASC, # row are the cylinder 'and the turnstile formed of two main parts, each thief each other transversely to their respective middle planes - are connected. For the cylinder row, tack (locating) bolts 25, interlocking surfaces 26, flanges 27 and a flange connection ring are provided of the two parts 28, 29 which are held together by means of screws 30; this ensures that the two parts of the series can be cursed quickly and accurately. tend to be attached to each other. For the same purpose, interlocking surfaces 31 and screws inserted into aligned bores 32 are provided for the turnstile. The pistons can be made of a light metal alloy and provided with grooves to accommodate conventional piston rings. The intake system of the engine includes an inlet opening for a carburized mixture. which is provided in or, as shown, around the shaft 3z and via an annular passage 33 between the shaft 3 and a sleeve 349 provided with a flap and which is rotatable with the cylinder bank-q and openings 35 is in communication with the outlet openings 36 which are arranged in the inner wall of the cylinder bank; these inlet openings are covered and opened when the pistons 6 swing in their cylinders. The outlet openings 37 are arranged approximately opposite the inlet openings, that is to say in the outer annular wall 38 of the cylinder bank, and are in communication with an outlet conduit, not shown, which is carried by and surrounds the cylinder bank. This outlet line itself can comprise an expansion and damping chamber or, as an alternative, the outlet openings can be open to a fixed line which is arranged on a closed intermediate piece remote from the rotating cylinder row. In this case, an exhaust fan is provided in the exhaust system to draw all gases through the system and to prevent the gases from leaking through the backlash between the exhaust pipe and the cylinder block. Rinse but (removal) of the burnt gases from the cylinders durchzuführeng a supercharging itself is with respect to two-stroke engines with the conventional arrangement of an inlet and outlet port ineffective because necessarily laßöffnung a corner. during a portion of the intake-Kompreasionshubes remains open. the modified two-stroke engine however, which will be described later, is most suitable for both purging and supercharging with a supercharger. The ends of each cylinder are terminated by cylinder heads which are integral with the parts of the cylinder block or, as shown, Form parts of two conical bodies 39 , which by the Z cylinder block members removable and having end plates 40 mounted thereon; bolts, not shown, are provided for fastening the conical bodies and end plates to the cylinder block. Each cylinder head carries a spark plug 41 and this can be arranged in a suitable manner with its axis parallel to the shaft 3 and in this way a ring of six spark plugs is provided on each side of the cylinder block. The head end of each spark plug extends through an opening 42 in an end plate 40 and supports a flat plate 43; when the engine is operating, the plates 43 of each spark plug ring come into electrical contact with a fixed plate, not shown. A magnetic coil or a magnetic ignition system (not shown) is provided to generate and supply the required current to the appropriate spark plugs via the fixed plates. Thereby the fixed plates and rotating cylinder block act as a manifold for the timely creation of a spark in the correct cylinder. A dry sump lubrication system can be used in which the lubricant is pumped through a line 44 or other lines formed in the shaft 3 and arranged in such a way that the lubricant is delivered to the area in which it is needed. The lubricant then moves from these parts against the outer periphery of the rotating cylinder block, where it is collected, returned to the sump and finally recirculated, although the lubrication of the pistons and cylinders is also through the use of the gasoline-oil system can be reached.

In operation, all pistons exert pressure one after the other via their joints against the turnstile, but a rotational force is only exerted on the cylinder block via the main joints. When a rotary force is applied to the turnstile, the pistons describe one around the axis of the sleeve, while the cylinders describe another # .circular path around -.- the axis of the shaft and. are at an angle to each other - the circular paths of the pistons and the cylinder are at the same angle p # so that the pistons swing one after the other - in their cylinders .. whereby the arms - of the turnstile in and along the slots - in the inner ring wall of the cylinder block. A piston moving on its circular path moves through a point where it is closest to the axis of shaft 3 - that is, where it has come closest to the Zvlin.derkopf .-. Beielner continues to move over this point increases its speed of rotation up to a maximum pull in which it reaches a point. which is furthest away from the shaft - the piston thus develops - during this section, its, movement - a moment and this developed moment supports the rotation of the cylinder while the piston again approaches the axis of shaft 3 . At its end protruding from the motor, the fixed shaft 3 is against pressure and rotation by means of a nut 45a, a washer 45b and. a disk wedge 45Q is attached to an anchorage 45. The anchorage itself is attached to the machine structure 45e by screws 45d-.

The anchorage has, e.g. B. at eine.Öffnung 45f for receiving the carburized Gemisohes, and has an edge portion 45g, which, erstreckt- against -the engine and a ring: space, 45h formed around the f este shaft which. with. is connected to the "passage 33 ". Between the edge section 45g and the flanged sleeve 34 there is a resilient annular sealing and bearing member 451, either freely arranged or attached to one or the other member is.

The torque given to the cylinder block can be dissipated via an output shaft 46 which is arranged on the fixed shaft 3 and has a flange 47 fastened to the cylinder block by means of U-bolts 48. The output shaft is housed in a spacer sleeve 49 which is rotatable with the shaft and the cylinder block. The sleeve 49 holds the motor at a distance from a bearing 49a for the output shaft, which is held in a bearing housing 49b between an annular shoulder 490 and a snap ring 49d. The storage housing . Use-is attached to the machine housing 45e with 'screws 49e. The bearing 49a is designed in such a way that it permits thermal elongation of the output shaft during operation of the engine. In a two-stroke engine, as specifically described, the usual arrangement of inlet and outlet ports, which is necessary for an early opening of an exhaust port to adequately relieve pressure in a cylinder prior to admitting a new charge, inevitably has the disadvantage that the outlet opening is closed late, so that it remains open during part of the compression stroke and is therefore disadvantageous for effective pre-compression. The motor can be, however, modified so that for the pre-compacting and also- for rinsing of the engine - can find a supercharger effective use. To this end, effective opening and closing at the outlet ports or at both the inlet and outlet ports at the required time can be achieved by the arrangement of fixed members which rotate not with the cylinder blocks but with respect to the outlet ports or the inlet -and outlet openings are arranged so that they open and close the openings one after the other .. In Fig. 4, ist.eines-a fixed member 37a shown. which with an outlet opening 37 in the outer annular wall 38 of a cylinder block zusammenwirkt..Man must imagine that the cylinder block rotates in the direction of the arrow and the associated one of the outlet piston is in its bottom dead center, as illustrated in FIG. 1. The solid member is arranged so that it closes the outlet opening at least during the Zeitraumejs of Verdiohtungshubee between the bottom dead center and closing the Auelaßöffnung by the piston, so as to improve the effectiveness of the Verdichtungehubes and between the bottom dead center and closing the inlet port, a To enable pre-compression. Appropriately, the fixed locking members can be provided in the form of sleeves which, depending on requirements, can be in one piece or in several pieces. The sleeves or the individual parts forming the sleeves can then be assembled in such a way that their position can be adjusted and the point in the motor circuit at which the openings are covered can be regulated. This allows the properties of the engine to be changed. Of course, ßinregulating the position of these sleeves corresponds to the change . In addition, the setting can be made while the engine is running. The sleeves can not only be adjusted for the purpose of giving the engine the necessary power and rotation, but they can also be used while the engine is running adjustable, automatically or pneumatically provided so that, for. B. the operating characteristics of the motor can be changed by varying its speed or revolution.

The construction described results in an extremely compact and lightweight motor which has proven to be very powerful in practice. However, significant changes can be made in the particular embodiments of the engine. In the particular embodiment described, for. B. double-acting double-sided pistons are provided. Instead of these, however, single-sided pistons that act single-sided can be used. Furthermore, where multiple cylinder blocks are provided, one or more of these blocks can, if necessary, be used to charge other cylinder blocks with gases. Alternatively, the engine can be designed as a four-stroke gasoline engine or as a two- or four-stroke diesel engine. The motor can be used either as a small format motor and a small compartment, e.g. B. to drive emergency vehicles, use in which case. he. so_- aus - ebild et istg.that it rotates at high speedv-o ## er -er-can also be built at a relatively low speed as a diesel engine with a large capacity, which in particular can be useful for use at sea. If a large engine is provided, which has a large number of cylinders, then there is actually a ship's engine, the rotational speed of which can be such that the engine can be directly coupled to the propeller. As a result, the interposition of a reduction gear between the machine shaft and the screw shaft is superfluous. Of course, if the screws should also be able to run back, a reverse gear must be provided. except for a two-stroke machine that can run equally effectively in every direction.

5 shows a modification of the engine described in detail, in which the cylinders at one end of the block communicate with the cylinders of another block of the same type, instead of being closed off by cylinder heads. The two cylinder blocks can-together rotate about the same shaft and the bushings 10 for the two hubs 7 are at the same angle to the shaft 3, but inentgegengesetztem sense, inclined so that a part of the modified engine, an I Ö piegelbild the other part is. With this arrangement, the spaces between the pairs of corresponding pistons 6 in the connecting areas between the communicating cylinder pairs 5 are used as compression and combustion spaces. As a result, the angle between the axis of each turnstile 7 and the axis of the shaft 3 can be reduced and a powerful, powerful,. capable machine working at high pressure.

The improved engine is generally relatively small in size Pront area for a given force output and the thermal expansion is due to the Uniform symmetry of the high temperature areas within the engine mass. The missing a flywheel allows a considerable weight saving up to such Extent that the engine can be made easily portable.

The parts of this engine are normally not as heavily loaded as in conventional internal combustion engines and lubrication of the cylinders can be supported by the centrifugal force that arises from the rotation of the cylinders, with the periodic acceleration of the rotation of the pistons also contributing. In operation of a mechanism according to the invention, the Style described with reference to the embodiment illustrated in FIGS. 1 to 3 the machine ie beim.Rotierenlassen a cylinder block about a fixed Wave G are due to the more Andes at a orbiting piston, and intermediate the piston and its connection With the centrifugal force causing extraordinary bearing loads, very high working speeds * subject to certain conditions * - In order to facilitate your conditions and thereby to greatly increase the permitted rotational speeds, improvements are made within the scope of this invention, while those on a piston essentially and automatically compensate centric, spherical forces acting in all of its rotational speeds within the assumed speed ranges, equation: LoJaz.alt: Lg provide an automatic compensation for a differential expansion that occurs within the mechanism from the temperature rises as a result of the increased n speeds and output power. As is known, the centrifugal force increases essentially with the square of the speed of rotation; if ala4-also dex in Figs. 1 to 3 described motor without impermissible bearing load between a piston and its lagerverbd.ndung.mit the turnstile at a speed of 5000 revolutions in the minute run but-d, fese, load approximately by four times if the speed is increased to 10,000 revolutions per minute. The following improvements are provided in order to be able to take over the above or beyond that without causing extraordinary storage bumps. In the case of a solo transmission, the connection is between one. Piston and the J) rehkzeuz modified so that they -ei = limited movement In. each direction of the piston radial with reference to that; Turnstile. Serving is caused by this # that cl: Ler K7vg9,1- an # clto piston pin - correspond within two * r- of the Sehalen. under brewed: Lotg where the piston with reference to dtem shells can slide radially to the turnstile. oeite. can the Itcplben movable with regard to this gohalen sein3 in which case the shells are relieved to accommodate a pivoting movement between the shells and the piston on the one hand and the piston pin on the other hand around the radius of the turnstile. Alternatively, such a pivoting movement can also be compensated for by letting the piston move around this radius with respect to the shells. The piston is also connected to one end of a lever arrangement at a point of the turnstile located radially inward of the ball of the piston pin and between two adjacent radial arms of the turnstile. The connection point is slightly offset from the pivot point, which can be viewed as fixed with reference to the turnstile. On the side of the pivot point opposite the connection point of the piston with the lever arrangement, a counterweight is also provided, pivotable about this pivot point, which is significantly smaller and lighter than the piston, but which has a mechanical advantage because its center of gravity is considerably wider away from the pivot point as that connection point. With particular reference to in Figs. 1 to 3 here leIctor, is the detached connection between a double-acting double-sided piston and the rotary cross according to the Pig. 6 and 7 formed in that a part the piston 6 is cut away between its ends, where- by e: #n transverse slot 50 results from the turnstile is strengthened radially outward and undercut at 50a. In * the slot a bore 51 is incorporated, which around a Raäius * of the turnstile. Runs cylindrically. The bore 51 interrupts the walls of the slot and results in a recess in the bottom. The radially inner ends of two corresponding semi-cylindrical shells 52 , which receive the ball 19 on the piston pin 13 , are arranged within the bore. The bottom of the slot points. spaced from the piston pin to permit thermal expansion and pivoting movement of the piston with respect to the piston pin, and the depth of the undercut is dimensioned to allow radial sliding movement of the piston about the respective cups. Since the corresponding shells with one another and also the recess are cylindrical and the slot is widened at 50a, there is also compensation for the pivoting movement between the piston and the corresponding shells around the radius de.a turnstile a. The bottom of the undercut, which forms part of the bore 51 , opens into a smaller chamber 539 which has a cylindrical wall and a concave spherical bottom which in turn is open to an even, smaller cylindrically shaped bore that opens up towards an opening on the radial. inner side of the intermediate portions of the piston extends. Inside the chamber 54 is an enlarged end 55 of a connecting piece 56 , the enlarged end forming a concave spherical ring shoulder 57 which fits into the concave spherical bottom of the chamber. The connecting piece has a shaft 58 which is close to a cylinder in cross section and which extends with play through the bore 54 and thus allows limited flexibility in all directions between the piston and the connecting piece. The radially inner end 59 of the connecting shaft has an external screw thread which is screwed into an internally screw- threaded bore or opening in an anchoring member 60 which has a smooth cylindrical bore through it. The smooth cylindrical bore has an axis which extends perpendicular to the plane of the turnstile and accommodates an eccentric section 60a of a cylindrical control shaft 61 in a displaceable and rotatable manner. The fact that a sliding movement is provided enables the connecting member to move out of the turnstile plane that could be required during the rotation of the motor. The axis of the smooth bore and thus that of the eccentric Abedhnittes of the control shaft intersects the axis of the connecting piece and is slightly offset from the axis of the control shaft that a force of the control shaft acting along the axis of the connecting piece a moment about this axis granted. In a plane parallel to the plane of the turnstile, a brake ring 62 is provided on each side of the turnstile concentric with the turnstile. The rings have the same diameter and each has at its Umfan # in the same waste was holes, one for each piston. The axis of each hole is perpendicular to the plane of the turnstile and thus perpendicular to the planes of the rings and each hole receives one end of a control shaft 61 which can rotate therein.

The brake rings and the control shaft are reminiscent of a short-circuit armature and the rings also form the only bearing for the control shafts.

!) The opposite ends of each control shaft 61 extend through openings in the rings and a counterweight 63 is attached to each protruding end, the center of gravity of which is on the side of the axis of the control shaft opposite the one without the connecting pieces. This counterweight is gewichtergäßig considerably smaller and lighter than the piston, but gives it from a working beitsgewinn, because the distance between the centroid of the control shaft is considerably greater the counterweights and the axis than the distance by which the axis of the Verbindungestückes against over- offset from the axis of the control shaft. The working balance of the counterweight in relation to the piston, the corresponding weights of the counterweight and the piston and their corresponding radii of rotation are set in reciprocal relationship so that the centrifugal force controls the orbiting Calving is balanced accordingly by the attendant force, d-It is exerted on the piston via the connecting member, Webel, serve Zuntrobekraft through the moment entetehil his- "ite the rotating counterweights through the centrifugal force - »wg-b will To take into account the expansion of the wire ei # inderblookon is the aforementioned * worthless relationship * r chosen values so that wipe in practice the $ centrifugal , = d there is a slight imbalance in the Zuntrobe forces *, It acts on each piston when the engine is cold deg the additional force slightly exceeds the centrifugal force weighs. The cylinder block either expands or contracts depending on the temperature. The part (Kreia) durohmesser of the group of cylinder bores changes slightly. In view of. However, the gain in work of the counterweight over the piston causes a slight increase in the radius of rotation of the cylinder resulting from a small increase in the partial diameter of the cylinder, and a greater reduction in the radius of rotation of the counterweight. Even if this change does not noticeably change the gain in work output, there is a noticeable change in the ratio of the corresponding rotation radii of the counterweight a and the piston, which reduces the ratio of the propulsive force to the centrifugal force from a value slightly exceeding equality to a value just below the Equals equality. -Uie pistons therefore do not exert any significant centrifugal pressure on their respective cylinder walls, even when they are circling. Also-between the ball of the piston bolt and the two entaprochendeng shells carrying it there is no noticeable drag from the centrifugal force. The engine can therefore 'have been run safely at very high speeds and even'# if an increase in engine speed is accompanied by a further expansion of the cylinder blocks' heat, the resulting change in the ratios of the threat radii changes a counterweight and a piston q between the two The plunging and accelerating forces acting on the piston benteheiide equilibrium only so insignificantly that an externally negligible centrifugal force arising therefrom is slightly within the safety limits.

In the case of a modified connection between the piston and the turnstile, the ball 19 is firmly attached to the piston pin 13 in the case of a main piston. In the case of an auxiliary piston, however, the ball 19 is slidably arranged on the piston pin 13 to compensate for its movements around the turnstile, as shown in FIG. 7 .

The arrangement of sliding ball on the piston Durchholzen for connecting an assistance piston and the hub has an advantage over the corresponding arrangement shown in FIGS. 1 to 3, in which the ball 19 fixed to the piston pin 13 and the auxiliary piston straight to and along a cylindrical guide sleeve 22 is slidably provided 'which includes corresponding shells 20 which receive the ball'. In the earlier arrangement, the torque contributions from the auxiliary pistons to the cylinder block are transmitted to the main pistons via the turnstile # where they complement the direct torque contributions from the main pistons. The Dr & Omen, t transmitted from all the pistons to the cylinder block can therefore only be felt as a reaction between the main pistons and their respective cylinder walls. According to the guide ball arrangement shown in Fig. 7 , the torque contributions of the auxiliary pistons to the cylinder block are not transmitted via the turnstile and the main piston but rather by a direct action between each auxiliary piston and its cylinder wall. The reaction between each piston and its cylinder wall thus contributes to the transmission of a torque to the cylinder block, so that the pressure on the cylinder walls is equalized. The non-sliding connection between each main piston and the turnstile is of course retained »to ensure correct circumferential adjustment of the turnstile with respect to the cylinder block.

The connection, particularly described with reference to FIGS. 1 to 3, between the turnstile 7 and the fixed central shaft 3 of the cylinder block can be used; however, it can also be modified according to FIG. 6. that the fixed shaft 3 is provided with a crank 64 from which a cylindrical bearing portion 615 extends on an axis which converges at an acute angle with the axis of the fixed shaft in the center of the imaginary sphere. In a case in which the angled bearing section 65 approaches the center of the imaginary sphere, this section is connected to the inner end section 66 and the fixed shaft which lies on its axis. The output shaft 46, which is rotatable with the cylinder block and coaxial with the fixed shaft 3, is designed at its inner end section as a milled ball 67 ; the recess 68 within the ball is cylindrically open around the axis of the output shaft and on the side facing away from it. The inner end section 66 of the fixed shaft 3 ′ is arranged within the recess 68 and suitable bearings 69 lie between this end section and the cylindrical wall of the recess and allow the ball 67 to rotate about the inner end section of the fixed shaft. Needle bearings are preferably used as shown. The outer surface of the ball is arranged spherically around the center of the imaginary ball and the hub * .70 of the twist cross is either formed in one piece with these arms 15 , as shown, or is rigidly attached to it and has an inner annular, concave-spherical surface 71, which includes the ball 67 and thus allows a universal joint between the turnstile and the ball. For the purpose of assembly a the turnstile is divided at its center plane, so that the annular spherical surface of the turnstile hub is divided along an equatorial line. One side 72 of the hub is elongated opposite to the output shaft 46 and has an inner, essentially cylindrical space 73 which is open at one end. within this' space is the angled bearing portion 65 of the fixed shaft unsuitable bearings 74 are provided between this bearing portion and the cylinder wall of the space 73 so that the turnstile can rotate about the bearing portion. Here, too, needle bearings are preferably used as shown. According to another improvement by which the centrifugal force of a rotating piston is substantially compensated, the connection between a piston and the turnstile is modified again in order to allow a limited movement of the piston radially to the turnstile. This is done in that the ball on the piston pin is replaced by a circular disk or a cylinder, the axis of which is radial to the turnstile, whereby the piston can slide onto the disk or the cylinder radially to the turnstile. A recess opening radially outwards is provided in the piston radially inside the disk or cylinder, and sealing means are arranged between the recess and a radially inner surface common to the cylinder or the cylinder. A hydraulic fluid is passed into the recess in the piston and a pressure is generated which is essentially proportional to the rotational speed of the cylinder block and thus essentially proportional to the centrifugal force exerted by the rotating piston on the walls of its cylinder and within its connection to the turnstile .

The pressure generated in the recess tends to push the piston and the disk or the cylinder apart and thus exert a force directed radially inward on the piston. By relating the radius of rotation of the piston, its weight and the base area of the cavity therein to the pressure exerted within the cavity, a difference is made between the radially inwardly directed force and the centrifugal force acting on the rotating piston, im essential equilibrium. represents. The piston hovers so to speak under all speed conditions and temperature changes with a merely negligible pressure between piston and cylinder walls in its cylinder. This relationship is automatically maintained during the entire speed and temperature range. In particular with reference to the motor shown in FIGS. 1 to 3 , the further modified connection between a double-acting double-sided piston and a turnstile is formed according to FIGS. 8 to 14. In this modification, the portion of the piston 6 located between its ends is cut out in such a way that a transverse slot 75 with parallel sides is provided which extends radially outward from the turnstile. In the bottom of the slot a recess 76 is cut which extends cylindrically around a radius of the rotary cross. In the case of an auxiliary piston according to FIGS. 89, 9 and 11 , two identical sleeve sections 77 are slidably accommodated in the slot, between which a circular disk 78 is located, the axis of which is radial to the turnstile. The disc is formed in one piece with the piston pin 13 from -._ and the curved surface of the disc is interrupted on each side by an arched slot 79 "which extends radially outward from the disc. The behlitz takes a correspondingly shaped arched rib 80 on the is on the surface of each sleeve supported against the disk, the arrangement being such that it allows limited pivoting movement of the sleeve sections and the piston about the axis of the disk while relative movement between the sleeve sections and the disk in the axial direction'or-r is prevented in the radial direction with respect to the hub. Since the side walls of the Schlltzes-in an auxiliary piston and the glettend mating surface a] each Hüleenabschnittes planar # as 11 can be seen in FIG., may henceforth the Hüleenabschnitte in any direction with respect to the piston slides around movements of the piston in the circumferential direction of the turnstile and also take up radially to it. In contrast, a main piston is designed like the Pig. 12 and 13 show. There are two identical sleeve sections for the disc 78 of the piston pin in the form of extensions 140 of the side walls of the cross section 75 provided with parallel side walls, which are either formed in one piece with the piston 6 or rigidly attached to it To enable movement of the piston around the disk, the complementary cylindrical bearing surfaces of the extensions and the disk are designed without interruptions. Otherwise, the connection of the main piston shown in FIGS. 12 and 13 is identical to the connection shown in FIGS. 8 ″ q and 11 for an auxiliary piston.

A chamber 81 in the disc is open radially inwardly towards the turnstile and interrupts the radially inner surface of the disc. A pressure buffer 82 is provided on this radially inner surface, which produces a radially inner surface that is assigned to the disk and, apart from an opening 83 in the center of the plate, which closes off chamber 81. The pressure buffer extends slightly over the delimitation lines of the disc so that it overlaps the sleeve sections or extensions and is spaced from the bottom of the sole seat so that limited movement allows the pistons relative to the rotating cradle. is. In the Auenehmung 76, a radially inner waste is cut an annular bearing member 84 and Dichtunge- same tend * untergebrachtg which is provided tung 'with a resilient Dichtungsvorrich-, for example in the form of an O-Ringeo 85 and the Bod, the en Perception interacts. A more extensive, radially outwardly lying section 86 of the annular sealing and bearing member 84 is separated from its radially inner section by a radially inwardly directed annular shoulder 87 at a distance from the bottom of the slot in the piston outer portion 86 of annular sealing and bearing member 84 has two concentric annular panels 88 and 88a supported against the radially inner surface of pressure buffer 82 ; the outer field 88a and the annular recess 88b between that and the inner field 88 lie outside the axially protruding circumference of the radially inner section of the annular diaphragm and bearing member. One or more slots 88a are cut in the outer panel for a purpose described below.

The chamber 81 in the disc 78 is connected to a chamber in a turnstile arm via lines 89 in the piston necks and the turnstile arm, the chamber in the lirehkreuzarm is a port network of a "radial threaded hole for the screw 18f in connection with the cap 17 an and * of the piston pin on the Drotkreunarm. Radial after outside the comber agent e a Eineatoptropfene 90 upstream beneath the radially inner * inde of the drill hood is. Radially inward of the insert plug is an outwardly directed annular shoulder 91 from which a narrower bore extends radially inward to a further radially outwardly directed shoulder 92; From this shoulder 92 an even narrower bore 93 extends to the surface of a cylindrical housing 94 which is provided within the hub 70 of the turnstiles a. Within this bore and said narrower bore, a plunger 95 is housed, which can move in a radially sliding manner with respect to the turnstile. The plunger has a radially outer section by section 969 which fits in said bore, and a radially narrower inner Abe chnitt 97, which is intended for said narrower bore. The two sections are separated from one another by a radially inwardly directed annular shoulder 98 , an annular space 99 being left between the shoulder 98 and the shoulder 91 in the turnstile arm, which is open to the interior of the motor via an opening 100. The space 101 radially outside of the plunger piston is also, as shown, vented towards the inside of the motor via the opening 102 or is in connection with the low pressure side of a pump, which will be mentioned later. There is an opening for connection to this pump vorgemeheng which is released by the piston .. when the pressure in the room mentioned, the requirement strides. The piston is hollow and contains a spring-loaded attlen RUakochlagvontilgliedv e.g. in the form of a sphere 103, which is pressed against its seat near the radially inner end of the piston by a compression spring 104; this spring is held between the valve member and a tubular member 105 which is disposed within the piston near its radially outer end * The Verbindung'zwiechen the hub and the fixed control shaft 3 of the cylinder block is similar to the corresponding., in Fig. 6.gezeigten Connection, the fixed shaft having a backing 64 from which a cylindrical bearing part 65 extends-on an axis which at the center of the imaginary sphere converges at an acute angle with the axis of the fixed shaft in a region where the As the angled bearing section approaches the center of the imaginary sphere, this section is connected to the inner end section 66 of the fixed shaft, which lies on its axis The cylinder block is flush at its-inner end 106 for connection to the cylinder block by means of screws 107 and -with an inner Ge housing 108 with: a planach-vbraeheng with the housing 108 having slots for a relative movement of the rotating cross arms Ball toes and perpendicular to the common axis of the solid wool and the output shaft, is divided into two parts; the two housing parts have interlocking surfaces 109 and screws 110 are provided to properly position and fasten the parts. The end face of the inner housing, which interacts with the inner end face of the output shaft, is interrupted by a countersunk bore 111 , - which leads to an inwardly open cylindrical outer recess 112 .. which lies axially to the output shaft v This recess takes a cylindrical shaft 113 on which is formed in one piece with a larger ball 67 . This sphere is concentric with the imaginary sphere. An axial threaded bore 114 in the shaft receives a screw 115 with a countersunk head which is inserted into the countersunk bore 111. The threaded bore 113 is continued through a smooth bore 116 to the center of the ball; A plug 117 is inserted into the smooth bore 116 , which is supported against the screw and holds one end of a compression spring 118 for a check valve, for example in the form of a ball 119, which is pushed against a seat and a short, narrow bore 120 closed * This hole leads into a cylindri - #. see recess 68, which runs coaxially with the output shaft and is open on the side facing away from the shaft.

The cylindrical recess 68 in the ball rotatably receives the inner end portions 66 of the fixed shaft 3, preferably as shown with needle bearings 69. A portion of the inner housing 108 also rotatably receives a portion of the fixed shaft on the other side of the force "Seen from the inner end section, and here too, needle bearings are preferred in the manner shown. Between these bearings and the housing 108 , heat-insulating sleeves 4 are inserted. The cylindrical housing 94 within the turnstile extends axially from the turnstile, the output shaft 46 is open and partially encompasses the ball 67. Between this housing and the ball there is a bearing insert 122 for fitting . sen the ball into the housing. The bearing insert is made of good quality material, such as phosphor bronze, which is used to facilitate assembly in the area of the. The center plane of the turnstile is divided into two rings, which have concave spherical inner surfaces and cylindrical outer surfaces. The former are complementary to the face of the ball, the latter to the face of the cylindrical housing 94 of the hub. The bearing insert 122 is held in its position between an annular shoulder 123 within the hub and a retaining ring 124 'which is attached to the output shaft end of the hub by means of screws 125. Beyond the shoulder against the fixed shaft 3 tapers Aie inner surface of the hub with play from the ball to a further narrower cylindrical open end space 739 which extends axially from the turnstile and - preferably, as shown "- via needle bearings 74 rotatably the angled bearing section 65 of the Said even narrower bore 93 in the turnstile arm, which extends to the surface of the cylindrical housing # 4 of the turnstile hub and surrounds the ball 67 , communicates with an opening 1.26 in the bearing insert 122. This opening is in turn periodically during a predetermined alignment between the two with a radial bore 127 in the ball 67 in connection.

The radial bore in the ball as well is in communication with a section of the smooth bore 116 in the ball, which contains the spring 118 for the check valve. Said short, narrower bore 120, which is open against the cylindrical recess 68 in the ball 67 , is in communication with a line 128 which goes through the fixed shaft 3. This connection is made via a solid tubular insert 129 which is tightly inserted, for example by means of an O-ring 130, into the inner bore 131 in the inner section 66 of the fixed shaft and acts as a seal and bearing with the bottom of the cylindrical recess 68 in the ball around the opening of the aforementioned short, narrower bore 120 in the KU-k-el, - 'initially tightly fitting, cooperates primarily through' a compression spring 152 between the tubular insert 11-9 and an annular shoulder "133 at one end of said bore 131 in the inner end portion of the fixed wall where this bore communicates with conduit 128. The line 1-28 in the fixed shaft is in contact with the high pressure side of a pump, not shown. M. bindingv * those under a pressure of something over that for the Engine is the maximum pressure required, -delivers hydraulic fluid as described below. The pump is preferably provides a spring discharge pump hydraulisehe PlüssIgkeit below a set Impulsäruck and 'for example by means of a Exzenternocken- or crank arrangement operates, the wird.-Im driven by the engine is operating at: thus leads pressure through the conduit 128 in the fixed shaft 3 found that it enters the bore 131 in the inner end section 66 of the: fe-Aten shaft 34o it acts against the end of the tubular insert 129 cooperating with the spring and increases the spring pressure on the tubular insert; this improves its sealing interaction around the opening of said short, narrower bore in ball 67; then-the-hydraulic fluid opens the valve in the ball and enters the radial Bohrum-, in it * When the sewn, even narrower bore in the turnstile arm with the radial bore 127 in the, #. ugel flahtete the hydraulic fluid enters into the space lying radially inward from the plunger.134- The pressure in the space 101. lying radially outward from the plunger is # controlled by the centrifugal force $ that by the circling plunger -95-. is exercised. Initially, i. H. before the hydraulic Ä near the liquid in the radial type from the plunger 95 If space 134 occurs, the corresponding condition can be expressed mathematically as follows. be: there is 1? the initial pressure ok In the radIal away from the diving. piston located space 1.01, A is the effective area of the radially outer j # niiei3 of the ligugh piston " m means the Kolbenmaäset w stands for the speed of the engine and r is the radius of rotation of the l # auohk-piston, 0.-0 if the If hydraulic fluid enters the space 134 located radially inward from the plunger 95 , then the initial pressure in the space 101 located radially outward from the plunger is increased without practically increasing the radius of rotation of the plunger, since the hydraulic fluid is essentially not compressed. ., it is the new corresponding condition mathematiBch can therefore approximately be expressed as follows: ri 1 A = M w 2 r + F 2 a; is P 1 is the zoom erte pressure in the radial aubwärte means from Tauchkölben located space and P2 the Pressure in the space located radially inward from the plunger and is at the same time the effective area of the radially inner end of the plunger Calibration can different -Be-expressed yet f olgend: 21 = 1 MW 2 r / A + 22 a / A.

For the flow of hydraulic fluid through the non-return valve in the immersion tank from the space radially inwards to the space radially outwards, however, the following is: 22 > Pl Therefore-iatt 2 2 mwr / A 22 a / A. According to this list: 2 1? a) > mw r. 2 The last expression shows aiso., T. that for the flow of hydraulic fluid through the nonreturn valve in the plunger 95 from the space 134 radially inside the same - to the space 101 located radially outside the same, the effective area of the radially outer ": ndes of the plunger. greater than its rajial., # 4npres end and that the difference between these areas and the pressure in the space located radially inward from the plunger must be so great that the product thereof exceeds the centrifugal force exerted by the circling deaf piston. will be explained later, is de facto advantageous, the plunger 95 would move radially outward regardless of the liquid which is fed into the space 101 located radially outward of the plunger and fills this space, until it is firmly attached to the insert plug 90 is applied and could not fulfill a hydraulic function because of the fact that small amounts of hydraulic fluid Once introduced into this space.9 the pressure cannot drop in it and tries to push the piston radially inwards until the opening 102 for this space is free and excess hydraulic fluid either, as shown, to the interior of the motor or to the low-pressure side of the Pump is piped. The arrangement ensures in this way that the plunger is in a substantially constant radial position, whereas the motor rotates at any speed within its working range. Since the radial position of the plunger is essentially kept constant.9, the pressure in the space 101 located radially outward from the plunger is essentially proportional to the square of the speed of rotation of the iviator within its working range. The maximum speed at which the space located radially outward of the tauoh piston can be refilled depends on the maximum delivery pressure of the spring dispensing pump. Currently, up to Betriebsgeschwindigkeiten-, 10000 revolutions ig d er-- minute and above the eye according to the gefafti LeiPtungskraft of the engine. The pressure in the space 101 located radially outward from the plunger can also be felt in the chamber 81 provided in the incline 78 , since the two are connected to one another via the lines 89 within the turnstile arm and the piston pin. The same pressure also occurs in the recess 76 in the piston, namely within the annular sealing and bearing member 84. The hydraulic pressure thus exerts a radially inwardly directed compressive force against the bottom of the recess and counteracts the centrifugal force exerted by the rotating piston The pressure spreads evenly over the entire floor area. The two acentric fields 88 and 88a, which are supported against the pressure buffer 82 and result in a highly effective seal even when high loads are applied, which are mainly absorbed by the hydraulic pressure which acts against the opposite surfaces which from fields 88 and 88a.versc) are goals. Hy - drauliscÜ # e # FlüsAigkeit in portions of the inner FEL- of 88 has the #durch the -kreisenden -Tauchkolben -ausgeübten pressure and leaking Nur slightly beyond the inner box 'umeine Grenzschkierung zw: to form ischendiesem und'dem print buffer.

The leakage of hydraulic fluid -leaves in - the -AusnehmÜug-88b between the inner and - the outer field a reservoir, the pressure of which essentially corresponds to the pressure inside the Noto-re, since the-outer field 88a 88c "slots" - there is. The ' 8 r' ing-shaped reservoir of hydraulic fluid outside the inner field '* # ensures the maintenance of lubrication between the inner field and the pressure buffer.

-If the corresponding masses of the plunger 95 'and of the piston 6, dfle corresponding radii of rotation of the immersion piston and the . Piston and the corresponding surfaces of the radially outer unde-S 'of the plunger, and of the bottom of the-Auan-ehmung 76 in the -olbe'n-miteihaiid'i3r are mutually related, then-the same within * the work shop. hes of the engine by the pressure of the hydraulic fluid against the piston radially, - waxed exerted - pressure force essentially H the centrifugal force of the rotating piston, since these two Values essentially the square of the 'speed of rotation speed of the Mot # PU7fefies range are proportional. The piston is thus within its cylinder even at high Geßchwindigkeiten substantially levitated and exerts only a very slight pressure Ge Gen the cyl: indian-aue walls, resulting in yields only very slight friction and wear. A thermal expansion caused by the heat generated in the motor does not noticeably change this equilibrium "in that the radius of rotation of the plunger increases with an increase in the radius of rotation of the piston, determined by the radial position of the pressure outlet opening 102", so that the The ratio between the two radii of revolution remains essentially unchanged.

.A differential expansion that occurs approximately between the Drehkxeuz and the cylinders and a movement between a piston and the turnstile are absorbed by the play between a piston and the turnstile or by the play between the pressure buffer and the bottom of the Schlitzve in the piston. Inebesonde e / Meig. 8 is also; the in Fig. 1 ge-- showed the inner annular wall 12 of the cylinder block B, which replaces the inner housing 108 and there is no direct connection between the two. However, in order to correctly connect and fasten the two Ab #,: Eichiutt # e to each other, each section comprises an outer centering surface 136 of the inner housing - this surface can -in the be frustoconical, conical, or any other suitable shape; it further comprises an x-shaped spacer 137 which cooperates with the flanges 27 and the two parts 28 and 29 of the flange attachment bracket The inflow line is also modified, since the carburized mixture is fed to the cylinders via the lines 138 in the section of the inner housing 108 which is on the other side of the tube with respect to the inner end section 66 64. From the interior of the inner housing, the mixture flows through the slots therein for the movement of the turnstile arms into an annular space 139, which passes through the inner housing, the pistons and the two cylinders block parts is limited. The space 139 is in communication with the inlet openings 36. The outlet openings 37 are provided as before. The conical bodies 39 forming the cylinder heads are provided as before, except that the end plates 40 are omitted. The spark plugs 41 are also arranged in the idea shown in Fig. 1 and are provided with flat plates 43 which cooperate with the fixed plates, not shown. The iliotor is mounted in a manner similar to that of the in-pig. 1 is similar to shown; the fixed vie is attached to the structure 45e via an apertured v "4-5 through which a carburized mixture is supplied to the conduits 138 and a resilient annular sealing and bearing member 45i. The member 45i is between the anchoring 45 and the inner housing 108 either cantilevered or fixed to one of the two 4iles. At the outer end of the fixed cases, a suitable coupling, "ig 128a, is attached, which receives a supply line leading from the pump, not shown, to the line 128. The output shaft is rotatably mounted in a bearing 49a, which takes up a longitudinal expansion of the shaft. It is located in a bearing housing 49b which is attached to the structure 45e. The retaining ring 49f, which is arranged on the bearing housing by means of screws 49g, replaces the snap ring 49d shown in FIG. 1 and holds the bearing in its housing. . The compound represented ih Figures 8, 9 and 11 for an auxiliary piston, in the manner shown in Figures 15 and 16 for use with the d.en in Fig. 12 and 13 , the main piston shown can be modified. For this purpose, the middle section 141 of the piston pin is provided with a rectangular 14 * cross section and the disk is provided in the form of two identical dcheioensegmente 142. Each segment can slide axially with respect to the piston pin along a side surface of its rectangular central portion. The #cheibensegmente are radial to the turnstile.between the; Pressure buffer 82 and a cover plate 143 held, which is fastened by means of screws 144 or on other suitable rails on the radially outer surface of the rectangular ldi * .; part section of the piston pin. The pressure buffer has an opening 83 in its center and this extends through a short opening which is arranged on one side of the pressure buffer. This light sits strictly within a correspondingly designed recess 146 which is open towards the radially inner surface of the rectangular central section of the piston pin, so that the pressure buffer rests against this inner surface. The opening in the pressure buffer is connected to an opening 147 Boeen of said recess in connection.-This opening f u,. ** hxt to 'e-Iner' line 89 in the piston pin, through the hydr-auli- see 21 overabundance is fed. Otherwise the connection is with. which is shown for a main piston in Figs. 12 and 3 ten identical. As above in connection with FIG. 7 with the arrangement of a ball 19 sliding on the piston pin for connecting an auxiliary piston to the turnstile under Vex use of a different: Lebbaren saw segment 142 in the ties between the auxiliary colleges and the turntable: reuz exVähnt was "Is -the transmission of a torque to the cylinder- block of an action between each piston and its Zyl: inderwand accompanies, whereas the application makes it more solid , # Jeheiben and sliding sleeve sections in the connections between the egg piston and the turnstile the transmission a -Drehmonentes on the cylinder looking through a Weeheel- effect between: delete the main piston and: its corresponding cylinder derwa-Naen takes place. In comparison to the one shown in FIGS . 8 and 10 The constructed construction is used in an -Alternative f # o ': rm according to the Fig. 17 hy "out: Li: Bdhe -21u, *" sis: i.gke: it of the Radfalbohrung 127 In the Ball via a line 148 supplied, -hirt, which by dfLe'Abtxleb; B- e 46 and those with a, sunk 115 Into the interior of the ball 67 , where s. ie 'the J x M-exe -End of the xadial Boeh, -rung 127 t:, ri # ft .-- Be di, n '' er i # IchLan Al, na- tivkoüstrukt: ion 12-t d3äe: Üii # zpfe ö valve glIed, 11-93 at: in4-- pressure-f #, outer- 1tü ünd fe 94 Bobxung 120, die- in 8 ühd 10 geZ "" e: ig ;, t e ': - L: nah *, $ Ball omitted and the line 128, the tubular insert 129 and its compression spring 132, which are also shown in the gIg. 8 and 10 are missing in the fixed shaft 3-.

The hydraulic fluid is passed either through the fixed shaft, as shown in FIGS. 8 and 10 , or through the output shaft, as shown in FIG. 17 .

So that the radial bore 127 in the ball is constantly in communication with the space 134 located radially inside the plunger 95 in the turnstile arm, the opening 126 in the bearing insert 122 between the cylindrical housing 94 in the turnstile hub and the ball is alternatively widened, as shown in FIG. 17 , and takes the inner end of a robT-shaped insert 149 in the turnstile arm. This tubular insert is formed at its inner end with a concave ephä3 # -1-sche.n surface which is complementary to the spherical surface and cooperates with it in a sealing and sliding manner. --- The concave inner end surface of the tubular insert is interrupted by a recess 150 which is so wide that the radial bore in the ball is always open towards this recess. The bottom of the recess is interrupted by a narrower bore 151 which extends axially to the tubular insert and is open to its outer end. B. arranged by means of an O-ring 152 in a recess 153 of the turnstile arm, which is open against the surface of the cylindrical G in the turnstile hub, and is urged firmly against the ball by an -Oruckfeder'154. This compression spring is held between the outer end of the tubular insert and a shoulder 155 in the space 134 radially inward of the plunger in the rotating hub.

An alternative to the ringföxmigen with two fields provided sealing and bearing element 85, which is described with reference to in Fig. 14 has the same external b diameter üfter seinei whole thickness and comprises three konzentrisehe fields, of which the two inner verseheni with slots and so that the hydraulic fluid in the two annular reservoirs between the three fields has the same pressure as the hydraulic fluid within the inner field. Other panel arrangements are contemplated which incorporate features of both of the described embodiments.

: An alternative to the plunger piston 95 described in FIGS. 89, 9 and 10 provides an extension piston which has the same cross-section over its entire length and does not have a longitudinal bore. With such a construction, the conduit leads from the pump directly to the space 101 provided radially outward of the plunger and the radially inward space 134 formed by the plunger is closed to the interior of the cylinder block with the exception of a ventilation passage a. As before, the radial position of the piston is determined by the radial arrangement of the opening 102 for the space located radially outward from the plunger piston; this opening is released by the piston. if the pressure in this space slightly exceeds the requirements. A further alternative is that one daring to dispense with a circular plunger and just the recess in a flask equipped with a pump verbindet.9 which generates a pressure at least for part of their Volumsaustoßes he d d substantially a square d er'- speed propor tional istt with which the motor rotates. Such a pump is preferably located outside of the 'motor', although it can also be mounted inside and driven by the motor. The connections In. the turnstile arms between the line in the fixed shaft or the output shaft and the outer expansions 76 in the pistons are provided either in two opposite or alternating or in all six turnstile arms in order to maintain the dynamic balance of the crosshair. This is particularly important where plungers are used. One useful arrangement is to supply hydraulic fluid to the chambers in the discs via alternate turnstile arms, as shown in Figure 9 , supplying the two piston recesses 76 to other opposing lines. The recesses 76 can alternatively be connected to one another, although this is not necessary. The two improvements described above, by means of which the centrifugal force of a rotating piston is to be essentially balanced, namely mechanically by means of a counterweight and lever arrangement, as shown in FIGS. 6 and 7 is shown, or hydraulically by applying a pressure fluid to the piston.'wIe 'die- Pig. 8 - 'to 17 show, * can be used in combination or alternatively . H. the center of the ball, the disk or the cylinder on the piston pin, can lie on the partial circle line of the piston or, with reference to this, soaps slightly radially inwards or outwards, in order to allow the piston to fluctuate in its cylinder to keep an axis as small as possible, which runs tangentially Z - around the turnstile and through the center of the joint when the piston is closest to a cylinder head, ie at top dead center, and when the combustion gases are ignited. An explosive force acting against a piston naturally results in a moment; around this axis; but a rösulting moment also results at the top dead center in the opposite sense as a result of the momentary difference - between the turning radii of the two ends of the piston - and consequently also a difference in the centrifugal force applied to both ends of the piston. The relationship between these opposite moments depends on various factors, such as the rotor design, the rotation speed and. the throttle opening and these factors are therefore taken into account9 in order to determine the most favorable position for the center of articulation with respect to the piston. ...

Claims (2)

2 a, tent a., N spx ü 'che # : (: 1: # 2 Masc, hinen- or I? Umpenanl age (Mech-gini smus) - "characterized by a cylinder in the form of a torus section that is completely ISTL disposed at a 3eite a first axis which passes through the axis of the torus in the generatrix and d it is plane of its pitch circle and by a piston der.zur entirety to a Be te a second axis arranged with respect to the second axis such is mounted so that it can perform a pivoting movement around a radius of the pitch circle-the torus "the piston is housed in the cylinder so that it can swing relative to this along the pitch circles and the second axis is arranged at an acute angle to the first axis is, passes through the intersection of the first axis and the axis of the generatrix of the torus and lies in the plane of its pitch circle, -iviobei also a relative rotation between the cylinder and through a relative oscillation movement of the piston in the cylinder of the second axis around the first axis, or vice versa. 2. Machine or pump mechanism, characterized by two cylinders in the form of the same separate sections of the same toxue, which lie entirely on opposite sides of a first axis and symmetrically to it, which goes through the axis of the generating of the torua and -in the Plane whose mVeilkreises lies, and by two completely on opposite sides of a second axis and symmetrically arranged and with reference to the second axis so mounted pistons that each can perform a pivoting movement about a circle of the partial circle of the torus, each Piston is housed in a cylinder so that it can swing relative to this one along the rope circle and the second 'Lehse is arranged at an acute angle to the first axis, passes through the intersection of the first axis and the axis of the generatrix of the torus and in the plane of which: eeilkreiaes lies, furthermore by a relative oscillation of the pistons to their corresponding Zy linderii causes a relative rotation between the cylinders on the one hand and the second axis on the other hand about the first axis, or causes such an oscillation immediately thereafter. 3. Machine or pump nmA LeaAismus, marked Characterized by a row or rows (or blocks) of cylinders arranged symmetrically about a first axis, each of which has the shape of a torua segment, the circles of which form a line of length (meridlan) of an imaginary sphere, this line of length forming opposite poles of the sphere - igh the points through the first ach 7utnd the cylinders of the series occupy a first zone of the ball arranged around the first axis, further characterized by a plurality of pistons for the cylinder row, which are symmetrically arranged on a spider around a second axis in such a way and are mounted in such a way that each piston swivels allows its own circumferential movement with respect to the plurality of pistons around a radius of the valve and all but one or two diametrically opposite pistons, each piston being accommodated in a cylinder so that it can oscillate relative to this along its pitch circle and the pistons for the row of cylinders occupy a second spherical zone housed within the first but arranged around the second axis, the (second axis) being arranged at an acute angle to the first axis and passing through this in the center of the sphere, furthermore by a rurlat: Lve oscillation of the pistons to their corresponding cylinders a: relative rotation between a cylinderr e series and its second axis is caused around the first axis or it causes such an oscillation 'directly thereon. 4. Mechanism according to claim 3, characterized in that each piston is mounted on a piston pin which in turn is connected at each end to an Ikde of a radial arm of a turnstile, the connection between each piston and its piston pin being provided so that it Pivoting movement of the piston about a pivot point on the piston pin and also, except for one of the two diametrically opposed pistons, "one-movement of the piston along its piston pin permits 5. 1" mechanism according to claim 4, characterized in that the movement of a piston is made possible along its piston pin by the fact that the pivot point for the piston is fixed (stationary) with --dezug on the piston pin and the piston is enabled to move transversely to itself relative to these points. 6. Mechanism according to claim 4, characterized in that the movement of a piston along its piston pin is made possible in that the center of gravity for the piston is provided so that it is itself movable along the Kölbenbolsend, but this is stationary with reference to the piston . Mechanism according to claims 4-5 or 69, characterized in that the mechanism is rotatable about a fixed shaft coaxial with the first axis and each piston is movable radially to the plurality of pistons so that any differential expansion between the spider and the cylinder block can be compensated 8. Mechanism according to claim 7, characterized in that each piston is connected to a lever system which comprises a counterweight, so that a centrifugal force acting on the rotating counterweight generates a tightening force which essentially counteracts the centrifugal force acting on the piston (or (it compensates). Mechanism according to claim 7, characterized in that each piston is subjected to a radially inward hydraulic pressure which is substantially proportional to the square of the speed of rotation of the mechanism, the arrangement being such that the radially inward inward pressure on the rotating piston a Zustr generated, which essentially counteracts the centrifugal forces (or it balances). 10. Mechanism according to claim 9, characterized in that d - aß the hydrauli se. The liquid under this pressure is fed to the piston via lines either in the first shaft or in an output shaft and lines in the radial arms of the turnstile and in the piston pin which can be rotated by the mechanism and coaxially with the fixed shaft. 11. Mechanism according to claim 1-0, characterized in that the lines in the turnstile arms are interrupted by chambers, in each chamber a plunger is housed in a substantially constant radial -hage and the centrifugal force acting on the rotating plunger (earlier) mentioned pressure generated. 12. Mechanism according to claim 10 "characterized in that the lines in the fixed or in the Abtribbswelle are supplied with hydraulic fluid by a pump which itself generates that pressure. 13. Mechanism according to one of claims 7 to 12, characterized in that the mechanism is provided in the form of an internal combustion engine having spark plugs arranged so that as the engine rotates each spark plug in turn moves into electrical contact with and out of some fixed member, through which fixed member the spark plug an electrical pulse is supplied. 14. mechanism according to one of the preceding Anspüüche 7 to 13, characterized-in that the mechanism comprising i. the form eunes Zweitaktverbrennungemotors »adapted for effective Vorlierdichtung and has stationary closure members, facing the outlet openings or opposite to both the inlet and outlet ports ngen the cylinder are arranged, wherein a rotation of the cylinder block about the first axis and a corresponding (simultaneous) rotation of the plurality of pistons. the second axis of which is caused by a subsequent relative oscillation of the pistons to their respective cylinders and-such a rotation_ of the cylinder block in cooperation with the fixed closing members a subsequent exact and strong opening and closing at the outlet ports or the inlet and outlet ports at the most favorable times causes. -15. Engines constructed and arranged to operate essentially as described above with reference to the accompanying drawings.