DE1817123A1 - Piston engine - Google Patents

Description

Hermann Pope of V "Λ

St. Gecrgen / Federal Republic of Germany. 18 I / 123

Piston engine

The invention relates to a piston engine with a wobble drive, for example a two-stroke internal combustion engine or Steam engine with 6-cylinder counter-piston arrangement, its Pistons are arranged axially parallel to the shaft around this concentrically in a circle and are guided in the stationary cylinder block and are connected to a wobble ring which carries the connecting rod foot bearings and which carries bearing surfaces on its outside, which lead it in a bearing ring firmly connected to the swash plate and the shaft via bearing elements, the Swash ring on its inside by means of a device on the cylinder block that is aligned with its swash center is held non-rotatably.

So far there are only piston engines of this type with corresponding swash plate gears (crankless or swash-plate mechanism) known whose wobble rings (cage or wobble ring) are designed as relatively flat ring disks (USA patent 2,475,295), which are in frictional engagement with a much stronger swash plate connected to the shaft. Such Swash rings have flat thrust bearings on their outer edge (USA patents 1,808,664 and

The swash plate gears of all these piston engines have a thick-walled and possibly particularly stiffened construction of their swash plate rotation plate, in accordance with the flat design of their rope ring, in order to prevent the swash plate from being used by the

- 2 009848/0460

BATH ORIGINAL

Pistons transmitted gas pressure forces and the inertial forces to be able to support on the wobble ring.

However, such an arrangement can be extraordinary high and sudden combustion pressures (force peaks) , especially in the case of diesel engines, are not sufficient, because the pressure of the connecting rod located in the working stroke on a single or a few bearing elements in the area of Connecting rod over the flat, resilient wobble ring on the unyielding swash plate is transmitted, so that these bearing elements are overloaded and have a short service life achieve because, due to the flexibility of the flat wobble ring, the adjacent bearing elements are far less are burdened and do not support the forces. On the other hand, with an increased formation of flat wobble rings their mass excessively increased and the load on the bearing elements thereby in turn increased unacceptably because the Swash ring bearing must transmit the gas forces and the inertial forces.

The mass of the wobble ring would also be increased, if the connecting rod bearings were attached as additional mass in front of the wobble ring. The mass forces rise higher speeds as the square of the speed, so they very soon become critically high. For these reasons could Piston engines with wobble drive did not run fast enough so far and they were therefore compared to the piston engines with Crankshaft not powerful enough.

The swash plate gears of all these piston engines have a corresponding to the flat formation of their swash ring thick-walled and possibly particularly stiffened construction of their torsion discs, around which the pistons transmit!

- 3 00 98 48/0460

BATH ORIGINAL

To be able to support gas pressure forces and the inertia forces on the wobble ring.

It is an object of the invention to provide a piston engine with a swash plate drive which has these disadvantages the known piston engines are avoided or significantly reduced. The piston engine according to the invention is intended to structurally optimal way a vibration-free, quieter run and thus at the same time an increased speed (approx. 6000 Rpm) as well as greater engine power with a longer service life.

For a sufficient service life of the large roller or ball bearings at high speed it is necessary that the peak load on the rolling elements at the combustion pressure peaks makes up as small a part of the permissible limit load as possible, so that the inertia forces rapidly increasing at high speed can still be recorded without the service life becoming too short, e.g. for use in a motor vehicle.

The piston engine according to the invention should also be spatially compact and easy to assemble.

The invention lies in the improvement of the aforementioned Type of a piston engine with swash plate gear and is primarily characterized in that the swash ring is light and has great flexural and torsional rigidity, by having a box-shaped cross-section, preferably completely, but at least partially closed Has hollow profile. .

The wobble ring can preferably have an approximately square cross section. The connecting rod bearings be arranged within the box-shaped profile of the swash rings.

- 4 009848/0460

8A ORIGINAL

"* ■ '1117111

With this design of the wobble ring according to the invention, you basically achieve high torsional and flexural rigidity without increasing weight, so that the individual. Piston locally preferably in the upper and in the lower dead center £ _e y _D t _s large forces over a relatively large bearing elements and is ^ over a broad bearing surface sector of the wobble ring to the. Swash plate connected to the shaft can be transmitted **. . «

The peak pressures under the connecting rods in the dead centers as a result the particularly strong gas or inertia forces there (ignition pressure, high speeds) are therefore distributed over many Bearing body without overloading any of them.

In a further embodiment of the invention, the swash plate preferably has a greater elastic resilience than that Swash ring, because the latter cannot be given an infinitely high degree of rigidity despite its hollow box profile. The swash plate therefore has a significant effect through its lower strength or through the choice of a material with a lower modulus of elasticity, that the forces on the bearing body or the bearing surfaces are distributed over a wide area and the peak forces are made harmless.

The swash plate can therefore also be made of an aluminum, Beryllium, magnesium, or titanium alloy can be produced. But you have it in your hand, in the well-known catfish also with steel to achieve a certain flexibility through high strength and reduced wall thickness. The swash plate is therefore in essentially designed as a relatively thin and fluffy disc to give this certain flexibility in relation to the much larger one To achieve rigidity of the swash ring.

Because of the high dimensional rigidity of the wobble ring according to the invention, it can also be used for further weight training Light metal alloys, e.g. aluminum, beryllium, magnesium,

00984870 ** 0 "*

Manufacture titanium on top of which those made of harder metal Bearing metal surfaces can be shrunk on or glued on.

To save weight and, above all, to distribute the weight equally, the individual points of the wobble drive can be connected by means of energy beam welding can be combined to form particularly light and strong, residual stress-free elements of the wobble drive

By saving pewlchteln, there are considerably lower moments of inertia, the higher the speed, and thus also a higher one Enable engine power and at the same time allow a more compact structure of the swash plate gear. This more compact and At the same time the assembly facilitating the construction is given above all because the hub of the swash rotating disk is on the front side attached to the hollow shaft with only a small wall thickness Attachment to the shaft must be avoided at all costs. In an embodiment of the invention, this is achieved by the fact that these Tawael disks are mounted on a thick hollow shaft with only two bearings is fastened near their ends by front fastening by means of high-tensioned screws.

In this way one becomes in itself without external compulsion and only System held in two bearings and therefore completely free-swinging without fatigue weak points, one of which is the other Motor power is delivered via the Steok shafts attached to the outside in the hub of the wobble rotation disks. This combination a self-contained oscillation system with a plug-in whale for tapping the engine power is particularly constructive advantageous. The Steokwelle can also be slightly angularly movable or otherwise fastened in the hub without any radial constraint be.

- 6

009848/0460

This compact catfish is significantly affected by this * favorable that the outer counter bearing of the connecting rod bearing of a bearing ring is formed in which the opening through which the connecting rod protrudes from the connecting rod bearing is at least as large as the outer diameter of the pan on the connecting rod, however, is smaller than that of this outer diameter when the Piston engine painted working group, and that the connecting rod bearing is locked positively in every operating position iSt O

This will require the ones located on the connecting rod Bearing shells of the connecting rod bearing after being inserted into the parts of the connecting rod bearing attached to the wobble ring no longer to be secured separately from the outside, and assembly space is saved and the assembly still much easier. The swashplate transmission needs namely only in the state held perpendicular to the longitudinal axis of the shaft moves against the end face of the shaft and the foot bearings the connecting rods into the bearing openings on the Ta'imel ring to be used, then the connecting rod bearings are after Very sharp division of the swash plate incl. Swash ring with its fastening on the end face of the shaft is automatically finished because of the above-mentioned positive locking assembled.

With the design of the swash ring, which is hollow box-shaped in cross-section, and its particularly strong one Form stiffening, it is also possible at the same time to close the inner opening of the wobble ring with a larger inner diameter shape so that in the extended input

- 7th

009848/0460 bad original

installation space the device can be installed «with the Swash ring centric to its swash ent now relative to the cylinders is held in a torque-proof manner "which therefore there" absorbs the torque of the wobble ring.

The device can be based on a principle already in the US Patent 3,333,478 described bevel gear rim set, in which a fixed to the wobble ring attached bevel ring gear during the wobbling movement of the wobble ring against a non-rotatably supported on the engine block Oegen bevel gear rim rolls off. It is important that the The gear rim engagement takes place essentially in the axial direction, so that the wobble ring remains unconstrained in the radial direction, in order to switch off the transmission of radial constraining forces to the force-transmitting bearing elements. Such a bevel gear ring device can be opened when it shows signs of wear Adjust in axial direction within certain limits.

The device for the non-rotatable mounting of the wobble ring

but can also be designed as a ball and socket joint with axial grooves

to the be, with / the back torque between the wobble ring and an am Engine block supported sleeve element by in pairs of axial grooves lying, cage-guided ball rolling elements is transferred. at Such a device results in an economically inexpensive and particularly low-impact construction, in which also the exact setting on the tumbling center, i.e. the point of intersection of the tumbling midplane with the aohee of the well, is uncritical.

The device for holding the rope oil ring tightly but can also be used in a simple universal joint one side of the force acting on the engine block and the other side of the force acting on the swash ring.

- 8 009848/0460 _0AD

The device for the non-rotatable mounting of the swash ring can, for example, also with its part supported on the engine block be arranged at a small distance around the hollow shaft so that it is guided freely in the radial direction and in this way no constraining forces can occur and additional © loads . are avoided.

By the given with the hohlkaetenfurmigen formation of the swash ring, enlarged in the axial direction of the outer periphery - m surface of the swash ring, and the installation space for the ball bearing shaped Lagerelement® between d © m swash ring and the swash rotary disk is increased. The decisive factor here is above all that with the inventive! Bearing elements must also be adapted to increased engine speed and engine power, because the higher motor speed in the roller bearing bodies causes considerably greater centrifugal forces, which inevitably lead to the roller bearing bodies jamming. The problem is essentially eliminated according to the invention in that the roller bearing bodies are given a special support in the radial direction.

In detail, this is achieved according to the invention by that the designed as a ball «or roll rolling elements ™

Bearing elements or "roller bearing bodies, which are arranged on the outer circumference of the wobble ring between a wobble ring from the flange-like .Urnfsagsring a®f Tauraiel rotary disk encompassing the outside as an axially and radially acting bearing" are rounded on their radially outward side and against © ine low-friction support Eur support gog®n centrifugal force® «

The invented wobble door is not only applicable to the combustion engines mentioned at the beginning, but also, for example, to the Stirling engine or steam engine, where the steam can be supplied through the hollow shaft, from where it can be drawn radially outwards into the Is distributed in the middle of the cylinder and the associated controls can also be arranged within the foohlan Well®. . ^, η ^^ π ^ ΰΰ ^ ύΒ ^

The wobble according to the invention of the wobble plate drive described and claimed can also be advantageous if the swash plate gear is only used individually or is also operated from both sides via a "single" swash plate arranged between two swash rings.

In the preferred version as a two-stroke, 6-cylinder version In the Oegenkolbenstellung and the resulting total of 12 cylinders results in a particularly vibration-free engine run, because the resulting torque always remains positive and is also subject to minor fluctuations. The compact arrangement is also generally applicable in the automotive sector.

The invention is described below in several exemplary embodiments with reference to drawings in detail and with the respective Advantages described. It shows:

Pig. 1 shows a section along the line A-A in FIG

a piston engine according to the invention with a wobble drive,

2 shows a view of a swash ring embedded in the swash drive with a device for rotationally fixed Bracket of the swash ring with connecting rod bearings and with a Massenausgleiohsvorriohtung, with left and Various embodiments of a Taunelring according to the invention are shown on the right of the section line A-A are.

Fig. 3 shows a part of the engine through the dream engine after the

Invention with an embodiment of power transmission elements with cone Ir oll engager η,

- 10 009848 / tHSÖ ^BAD original

4 shows a section according to FIG. 3, in which the force transmission elements are designed in the form of ball bearings "

5 shows an intermediate sleeve part of that shown in FIGS. 1 and 2. FIG piston engine according to the invention,

6 shows a particular embodiment of the holding device of the axial guide joint shown in Fig. 1 and 2, but with incorporated in one piece Guide groove ^,

7 shows an opposing piston arrangement that can be used according to the invention, each with external wobble drives,

8 shows a longitudinal section through an entire piston engine with a swash plate gear, its swash rings each held in a rotationally fixed manner by means of gear rim sets.

In the piston engine shown in Fig. 1, its cylinders are 2 arranged in a cylinder block 3 axially parallel around a shaft 1 in a circle. This arrangement of the cylinder 2 offers the advantage of low space requirements and extensive noise reduction in that * that a vibration excitation · of the motor housing in particular of the cylinder cover and of conventional Engines under the crankshaft sump is avoided »This applies in particular to the execution of the 6-cylinder two-stroke piston engine in opposed piston arrangement, i.e. with a total of 12 pistons.

For this purpose, the shaft 1 is supported twice and thus statically determined, namely in radial bearings 48 _P di® located centrally to the cylinder block 3, which can also be located within the cylinder folock 3. Wave 1 is also extreme

Diameter designed to reduce the flexural vibrations of the shaft T bswo -costs within your radial bearing k8 As a result of the piston · = · and inertia forces ssu «, In this

Shaft 1 can be designed for large engine outputs made of light metal, e.g. even an aluminum «beryllium ··« Magnesium or titanium alloy exist, even if the hollow shaft 1 with relatively less Wall thickness is formed.

When the piston engine is designed in an opposed piston arrangement According to FIG. 7, the shaft 1 passes centrally through the cylinder block 2 and forms with the ends attached Swash drives T a self-contained system of forces, the radial bearings 48 are only burdened by the rotating or tumbling parts. The one present when the engine is in a horizontal position The load diagram of the shaft 1 is shown schematically in the upper part of FIG.

Where or _o the projects out of the cylinder block 3 ends · - term piece of the shaft 1, a swash engine T is as close to the cylinder block J5 rigidly · During the opposed piston engine of extremely large diameter of the shaft 1 described above, above all, is therefore especially advantageous because when assembling the engine it is simply stooped through the cylinder block J> and the wobble drive T can be securely fastened to the shaft 1 (at the front end 5 of this shaft 1) without additional flanges. As a result, the end of the shaft 1 protruding from the cylinder block 3 and the distance between one of the radial bearings 48 and the center of the TauMltrl «tm« rlc8 T can be kept extremely short. When the shaft 1 is designed as a hollow shaft, the wobble drive T with its wobble rotation base 4 is fastened by means of screws 43 at an annular plate T that is sunk into the front end 5, a stub shaft 8 engaging within the hollow shaft in a mounting element 9 which is attached to the annular plate 7 and dl · swash plate 4 centric with large play is Hindu guided, with which possible Bi «g« achwingu »e« nd «· shaft end *

can not transfer to the stub shaft 8.

The stub shaft 8, from which the torque of the engine is removed but can also be in the hub of the wobble rotation « disk directly attached, with the swash rotating disk 4, e.g. by an arrangement (not shown) of through tensioning screws on the end face of shaft 1 or the end face 9a of the mounting element 9 attached can be. With opposed piston design, this attachment also via a screw arrangement passing through the hollow shaft . made in an additionally stiffened, braced form. Centering is facilitated by a centering shoulder and / or a Pafistlft 46 * which also includes the setting the exact angle of rotation of the swash plate 48 on the shaft 1 is facilitated «, Dl © fastening screws 4-5 can also go through to Halt © rungs @ l @ m®nt 9 «open in this way the dl © tumble red & tlonsscholbe 4 is in a firm frictional engagement - connected to the end © 5 <S @ r Well® 1 and also the In fact, it is advantageous to use the bending stresses of the shaft 1 at Tauraeltriefowerken dles @ r kind with the swashplate rotating disk 4 ^ together circulate "

Innerhslb-der Taum © lpotationssch @ ib® 4 a swash ring 10 held against the cylinders 2 is arranged, which is rotatably .folded over a Äxlalführerg © l®nk 13 by a mounting device, ie around the front end 5 of the shaft 1 arranged and supported pol & tiv on cylinders 2 non-rotatably lsfc _o ■■ -

This mounting device is left on its a to the Taurae! Rotation disk k , - supporting the ÄJtialführer joint

The end can be moved radially at least to a limited extent »in order to ensure that the axial guide joint 15 is held without restraint, so that the axial guide joint 13 any small Counter movements from the power transmission system between the swash ring 10 and the swash plate 4 can give way radially with respect to *. This means increased service life and simplified manufacture

In the embodiment according to FIGS. 1 and 5, the holding device is in at least two sections in the axial direction divided and has at least two mutually independent, rotated by 90 ° to each other and diametrically to the shaft axis arranged, axially interlocking and each radially displaceable claw ears. The claws 55 engage of the sleeve intermediate part 14a into the grooves 57 on the cylinder block 3, while the two sections via claws and Grooves are interconnected.

In the axial direction, the individual parts of the holding device are held together by the rope rotation bracket 4, optionally via an intermediate ring. Both parts thus guarantee a cardan joint «holding of the axial guide» joints in two main directions.

A one-piece part can also be used as a mounting device 14b (Pig. 6) are used, the 3 claws 55 of which are curved "flanks and thus guarantee the necessary full degrees of freedom in the radial direction *

However, this purpose can also be fulfilled by a cross-wedge coupling, in which the

009848/0460 Original bathroom

The bearing pressure exerted by the engine parts is free! do not impede the eccentric movement of the mounting device.

The sleeve 18 has axial guide grooves on its circumference 17, in which guide bodies 15 (e.g. balls) can be moved. Fig. 6 shows a special embodiment 14b of a combination of the sleeve intermediate part 14a with the sleeve 18 in one piece and the axial guide grooves already firmly arranged thereon 17, whereby the non-constrained, non-rotatable in the axial direction This combined part is held by its claws 55 engaging in grooves on the cylinder block 3.

The outer bearing of the Axialfüferungegelenks 13 form axial PUhrungsrillen 1β ara inner diameter of the (received by the wobble rotation bracket 4) wobble ring 10. A guide body 15 encompassing KKfig 14 runs during the pivoting movement of the wobble ring 10 over dan wobble center Z to a stop plate 19, which is concentric on the de at cylinder block 3 abgewannen Flash "d®a Tauiaelriinge 10 attached let" Instead of such Ansohlagpl & tte can & h @ r AUOH simply an Adjustable stop on the Tauraelrotationascheibe provided leg. In any case, it is important that the center of the wobble plane of the cage and its guide body lies in the wobble plane of the wobble ring.

The apparatus sur drehf "et" n supporting the wobble ring relative to ä®m cylinder block 3 can gemäi Fig. 8 instead of as an axial guide @ g®lenk also in the form of two calibrating each other abwälzender K © ^ g®l Mükrä! Ize 61 and 62 be carried out " from

d®r E © g © lsata <23Paii5s 61 firmly supported on the cylinder block 3, its bearing material layer 65 di® shaft 1

- 15

BATH

touched. The bevel gear set 6o is on the wobble center ^ aligned.

The wobble ring 10 is designed as a preferably box-shaped hollow profile enlarged in the axial direction, in particular with larger cavities 47 in a wobble ring body. The wobble ring 10 can initially be made of two axial sections that are firmly connected to one another. One axial section can consist of a bottom ring 58 which, according to FIG. 3, is permanently welded or also glued to the other section in the course of assembly. According to FIG. 2, left half of the individual cavities 47 may however be forth ^v plates sealed at the top by single deck also. Electron beam welding or pulse welding is particularly suitable for welding because it enables largely distortion-free welding without large amounts of welding material. Such a weld, which takes place within V-shaped grooves into which wires are welded by means of energy pulse welding, is shown in FIG. 4 as weld 80 and in FIG. 8 as welds 81, 82a and 82b and 83.

Duroh this special profiled shape of the swash ring 10 is ee possible, the connecting rod bearing 12 with their respective associated, possibly cylindrical, base subsets practically completely sink into the swash ring 10. This also ensures that the pivot point of the connecting rod bearing is arranged in the middle plane of the wobble (with wobble center Z), so that all working movements associated with the wobble are reduced to the smallest possible time. resulting in a practically pure sinusoidal motion with a correspondingly smooth run even for a short time

- 16 009848/0460 bad original

■ i »& α fr.

intermittent combustion «as can be achieved with a diesel engine leaves. Since the axial guide joint 13 with his Pivot center lies in the Taurael center Z, the movement of its guide balls 15 is the same in both directions, so that they cannot jam the straight axial guide grooves 16 and 17.

Through the aforementioned interlocking spatial arrangement of swash ring 10 and connecting rod bearing 12 is a considerable improved torsional and flexural strength of the swash ring 10 achieved without the axial or radial dimensions of the wobble drive increase significantly, so that this as optimally compact construction is feasible.

In doing so, the Maas forces In, which are released especially with high tumbling accelerations, can be controlled Limits held »

This purpose is also served by the special shape of the tumble rotation disk 4, which is designed to be "cylinder block" 5 open and cup-shaped in such a way that it absorbs most of it of the swash ring 10 receives. In this case, the edge portion of the wobble rotation plate can be a separate circumferential ring be designed, which engages around the swash ring 10.

In order to keep the inertial force caused by the accelerating tumbling movement · as low as possible, the material used * can have a low specific weight, as the special profiled shape already provides a high level of resistance to twisting and twisting »as %. & * At Leiohtnjetalleglerunetn ( Aluminum, magnesium,% itan) is present; « ÄixtgmM der er -

'.- ■■ - ■ - ■■,: 8AD ORIGINAL

009848/0410

increased dimensional stability for the wobble ring 10 but also simpler unhardened steels can be used, although a ring of hard material must be attached to the wobble ring 10 (glued, shrunk), which deceives the bearing surfaces of the force transmission elements. These bearing surfaces can also only be formed after the ring has been attached. ,, »The ₁ ,, bearing surfaces can consist of a steel ring that is cast over a plastic model using the form mask process and hardened by carburizing at the most stressed areas. The connection the bearing surfaces with the wobble ring 10 can also be done by pulse or electron welding

The rigidly configurable swash ring 10 must be compared to the Taumelrotationssoheibe 4 be much less elastic naohglebig. The wobble ring 10 according to the invention therefore also measures not necessarily made of highly elastic, heavy material exist.

The manufacture of the particular “it” large cavities provided swash ring 10 with the axial guide grooves 16 fixedly arranged on the inner diameter diameter, for example by a correspondingly precisely manufactured casting or Drop forged part made in which the sleeve 18 with their axial guide grooves 17 or that the guide grooves 17 containing pieces of material cast in one operation are, after an exact joint processing of these parts that are exactly related to one another during operation the separation takes place.

Between the inner diameter of the pot-shaped Taumelrotationssoheibe% and the Außenendurehrneeser des.

- 18th

009848/0480 BAD obginal

Swash ring 10 are arranged force transmission elements which, according to FIG. 1, can be designed as tapered roller bearings arranged in a plane of the swash plate, the rollers 20a and 20b of which are arranged alternately between their running surfaces 10a and 21a or 10b and 21b that the axes of rotation R1 or R2 of the rollers 20a and 20b, each in pairs, approximately diagonally opposite one another on the wobble rotation disk 4, run approximately parallel to one another in each rotational position of the wobble rotation plate 4. This version of the bearing rollers 20a and 20b (two interlocking bearings) arranged in a plane of rotation axis at different working angles, in which the forces to be transmitted are transmitted in both axial directions, is particularly intended for smaller piston motors, while the e.g. The arrangement shown in FIG. 3 absorbs greater forces, since in this case only half of the seed rolls carry in an axial direction. In the case of the tapered roller bearings described, the individual tapered roller tries, according to the parallelogram of forces, due to a force to be transmitted depending on the taper inclination and a force component proportional to the centrifugal forces of the rollers themselves, in the axial direction and in the direction of their widest diameter / in order to reduce the friction caused by these forces, The rollers 20a and 20b are rounded at their outer, wider end faces, and are separately supported around their axis of rotation against forces directed in the direction of their axis of rotation in the apex area of this rounding. A relatively low-friction support has proven to be particularly advantageous for the large-diameter bearings required for tumble drives, because relatively high centrifugal forces resulted at high speeds. " ^: - ^K ■■" - -

- 19th

009848/0460 _8AD

In order to achieve a particularly low coefficient of friction, the rolling track surfaces of the rollers 20a, 20b or of the rollers 22, 23 according to FIGS. 1 and. 3 at least partially executed diverging to the corresponding bearing surfaces 21a and 10b or 21a and 10a, so that the thereby formed space with a surrounding oil film itself can fill. Such oil wedge films have a high load-bearing capacity and allow high speeds, with the rolling elements only reaching about half the relative speed, because they slide on the oil film.

Fig. 3 shows an arrangement of force transmission elements in the form of a double roller bearing, in which the axes of rotation of the frustoconical rollers 22 and 23 of the respective bearings are arranged at an angle to each other and the double roller bearing absorbs axial tensile and compressive forces as well as radial forces. According to Flg. 1 The force transmission element lying in a wobble rotation plane is here pulled apart and arranged in two wobble rotation planes. The axial forces are also transmitted in both directions here. However, the pressure forces mainly transmit the bearing raceway attached to the rotating swash plate A, while the tensile forces are mainly absorbed by the circumferential ring 21 encompassing the swash ring. With this arrangement, the axial forces of the tapered rollers have a similar effect, so that the facing and in particular rounded end faces 22a and 23a are supported against one another via a guide ring 2k , which leads to the respective rollers 22 and 2? towards the associated bearing surfaces 25 and 26 which are perpendicular to the respective axes of rotation.

- 20th

0098 4 8/0460 sad original.

To a greater elasticity and the resulting to achieve a higher load capacity of rollers 22 and 23, a relatively wide axial bore 27 is provided in these rollers, into which centering pins 28 projecting perpendicularly from the bearing surfaces 25, 26 of the guide ring 24. The rollers 22 and 23 are supported against the centrifugal forces in an annular area around the axial bore.

On the guide ring 24 is for its easier centering a resilient locking wire ring on its outer circumference 29 is arranged, which is held in the inner wall of the circumferential ring 21 of the pot-like rotary swashplate 4 will.

In Fig. 4 an arrangement is shown in which the rollers from Fig. 3 are replaced by a double ball bearing, their balls 30 and 31 point against the bearing surfaces 25 and 26 of the guide ring »24 and at which is the axis of rotation of the respective balls 30 and 31 runs through this point of contact.

According to FIG. 8, the balls 70 and 71 can also be in cage rings 73 and 74 out and supported against centrifugal forces, the between two ground side surfaces (see B. 75) against the shaking movement of the Taumairing »a special support have »In addition, the balls and rollers can be used for further Weight allowance can also be made hollow *

Gamäß Flg. 1 and 3 are the connecting rod bearings 12 with the associated Base sections 11 are designed and ala hollow bodies with one, as can also be seen in FIG. 2, eccentrically Oil hole 33 provided, weloha during the piston travel around the

-

0-09848 / 0460 _6A o

Top dead center connects an oil channel J> k in the connecting rod 35 with the oil reservoir created in the hollow connecting rod bearing, which is connected to the entire Sclimler oil supply. The oil accelerated in the upward direction of the piston in the storage space is thus conveyed by its inertia through the released oil channel j54 to the piston connecting rod bearing when the piston 42 reverses its path at top dead center. During the downward movement following this reversal of the path, the oil bore 33 is closed by the connecting rod socket 39 so that the oil is pumped into the oil channel y \ in one direction each time in the region of the top dead center. The oil is fed into the base sections 11 via an inlet opening in the bottom of the wobble ring 10 and the space between two membrane sheets 3 ^ a, which rest resiliently on the floor of the wobble ring 10 and are connected to the central oil supply,

The connecting rod socket 39 holding the cover, which is a simple Snap ring 36 may be, is dimensioned such that the clear width of its upper ring 38 the AuSendurohmaasw the connecting rod socket 39 corresponds, so that this «in the Assembly easily inserted into the cover 36 vertically can be and after the assembly of the ring 38 by your the wobbling movement of the wobble ring 10 corresponding working group is kept in constant engagement. For that he can The outer diameter of the pan 39 must in any case be so much smaller than the clear width of the upper ring 38, that of the Pan 39 in operation coated working group, the pan 39 is at least partially overlapped by the bearing ring 37, It should be noted that in the case of the Tauinel Trlebwerk described Tensile forces on the connecting rod bearing 12 hardly occur anyway and the cover 36 or its bearing ring 37 accordingly can be weakly dimensioned,

009848/0460 bathroom

2 also shows the disk-like circular ring segments attached as a mass balancing device K $ , which in this embodiment consist of thin sheet metal strips and which are clamped by means of screws 44 in order to provide a quick and easy and, above all, particularly precise balancing option required in series production create·

In the case of the opposed piston arrangement shown in FIG. 7, in which the drive shaft is mounted in the cylinder block, while if the wobble drives are located on both sides outside the cylinder block 3, an extraordinarily uniform one became Torque detected. In addition, the best possible scavenging of the combustion gases is achieved in that sioh open and close the inlet and outlet slots in an offset manner. It occurs with relatively little additional effort, the sloh through the assembly of a second wobble drive results in a almost twice the performance increase with half the space required - and avoiding the need to install additional units twice.

The coaxial circular arrangement of the cylinder of the piston engine described and the also circular The configuration of the wobble drive allows the design of an opposed piston engine, which in an optimally compact construction with correspondingly low compared to the normal, about half the power to weight ratio works.

009848/0460

Claims (1)

Hermann Pabst St. Georgen / Federal Republic of Germany. Claims Piston engine, for example a two-stroke internal combustion engine or steam engine with 6 cylinders in opposed piston arrangement, the piston of which is axially parallel to the longitudinal axis in the Circle arranged concentrically around this and guided in the stationary cylinder block and with a the connecting rod bearing bearing wobble ring are connected, which is guided on its outside bearing elements in a swash plate firmly connected to the shaft, wherein the wobble ring on its inside by means of a device aligned with its wobble center on Cylinder block held in a rotationally fixed manner, characterized in that the wobble ring (10) has a transverse unit box-shaped, at least partially closed Has a hollow profile. 2. Piston engine according to claim 1, characterized in that the cross section of the hollow profile of the wobble rings (10) has approximately square dimensions 3. Piston engine according to claim 1 or 2, characterized in that the Pleuelfuflsfer (12) run predominantly in the hollow profile-like Tauaelring (10) are arranged sunk. OOM4IS04I0 4-, piston engine according to claim J>, characterized in that the connecting rod bearings (12) are supported on a sleeve-shaped base (11) or pin (11. ') which extends through to the bottom of the wobble ring (10), and on this as well are attached to the top of the swash ring facing the cylinder (2). 5. Piston engine according to one of the preceding claims, characterized in that the hollow profile-like Swash ring (10) non-rotatably relative to the cylinder block (3) holding device (13) arranged centrally within the inner circumference of the swash ring 1st and the plane (E) going through the pivot centers of the connecting rod bearing (12) through the wobble center (Z) of this Device runs » 5ο piston engine according to claim 5, characterized in that that the swash ring (10) relative to the cylinder block (3) non-rotatably holding device (13, 60) on the Shaft (1) is supported and is radially movable 1st. ^r . Piston engine according to one of the preceding claims, characterized in that the hub (4a) of the rotary swash plate (A) is attached to the front side on the preferably hollow central shaft (1) by means of pretensioned screws and on its side facing away from the cylinder block (3) with a hollow one Because (1) equiaxed Steok shaft (8), which has a smaller diameter, is provided for the power transmission of the piston engine. 009848/0460 8. Piston engine according to one of the preceding claims, characterized in that the elastic resilience of the wobble rotatlon disc (4) is significantly greater is than that of the swash ring (TO). 9. Piston engine, in particular according to one of the preceding claims 1 to 8, wherein the pan or the cup-like foot bearings each connecting rod from open is held in the wobble ring by a counter-bearing with spherical segment-shaped bearing surfaces, characterized in that the counter-bearing is one in a bearing ring (37) has provided opening (38) through which the The connecting rod (35) protrudes from the connecting rod bearing (12) and is at least as large as the outside diameter of the socket on the connecting rod, but smaller than that of this outer diameter at Operation of the piston engine swept working circuit, and that the connecting rod bearing (12) thus in every operating position positively locked 1st, 10. Piston engine, " ¹ In particular, according to one of the preceding claims, in which the bearing elements carrying the wobble ring are roller bearing bodies which are axially and radially positioned on the outer circumference of the wobble ring between a flanachike circumferential ring (21) of the rotary wobble plate (4) that encompasses the outside of the wobble ring acting bearing are arranged, characterized in that the roller bearing bodies (22, 23i 30, 31; 70, 71) are rounded on their radially outward Plloh * and thus (20a ¹ , 24, 73, 74) to support against * .B Centrifugal forces preferably start over the bottom line of this surface on guide surfaces (24 _# 25) with the formation of an oil wedge film. BATH ORIGINAL 009848/0460 11. Piston engine according to claim 10, in which the bearing elements have double WKlζlager with frustoconical rollers, the axes of rotation of which are arranged at an angle to each other for the purpose of absorbing both axial tensile and compressive forces and radial forces, characterized in that the rollers (20a and 20b as well as 22 and 23) on the end face (20a ¹ and 20b 'as well as 25 and 26) of their radially outwardly directed end face are rounded in such a way that their uniform line is in a circumferential direction like the guide surface nestles and the guide one However, there is no »area for this iner «olle ie / diverges and in the course of each a role from the apex / diverges and in the course of each a lubricating wedge film on this outwardly located Has surface. 12. Piston engine according to Anspruoh 11, characterized in that that the rollers (20a and 20b and 22 and 23) old are provided with a further axial bore (27) and are supported in their outer end face. 13. Piston engine according to one of the Aneprüohe 11 or 12, characterized in that there is one known to sioh Crossed roller bearing with the guide surface d «r, and the axis of the rolling elements shifted at an angle a radially outward glowing roll at the same time represents the tread of the others and vice versa, 14. Piston engine according to one of the tests 10 to 13 characterized in that dl · rollers (22 and in well-known guide pins on "in" cage (28). 0098 * 8/0460 15. · Piston engine according to claim 10 «characterized in that that the rolling bearing elements are balls (350, J51). 16. Piston engine according to one of the tests 10 to 15 * characterized in that the KKfigrlnge supporting the roller bearing bodies (70, 71) between two ground side surfaces (75) against the shaking movement of the wobble ring (10) separately are trimmed. 17. Piston engine according to one of the preceding claims, characterized in that the outer periphery of the Wobble rotation plate (4) a mass balance (43) from thin sheet metal provided let that be attached to several are attached via their points distributed around the surface. 18. Piston engine according to one of the preceding Ajissproht, characterized in that dtr Tatunelring from several, in particular axially separate parts, which are assembled into a box-shaped hollow profile are. 19. A method for producing a piston engine naoh one of the preceding claims 1 to 17 and in particular according to claim 18, characterized in that that items of the Tavunel engine duroh connection by means of energy beam welding into particularly light ones and solid, tension-free ducks de * tauiroltriebnerks are joined together. 009848/0460 * AD original