AU2002340887A1 - Reciprocating piston engine comprising a rotative cylinder - Google Patents

Description

VER1TFCATION OF TRANSLATION

International Parte t Appliction No. PCT/E.P02/1].0196

/7

of /~t 4:; vatoiJ am the tralator of the documnl altached and I state that the following is a true rmnalation to the best of my knowledge and blieif of Internmational Patent Application No. PCTDEPO2/10196 tTfild I Septmber 2002.

DAT9D this S day of f c~- , 2004

guature of Tratslator)

F-8141

Reciprocating piston engine with rotating cylinder

The present invention relates to a reciprocating piston engine with rotating cylinder for

generating torque. The reciprocating piston engine preferably works as a combustion engine;

however, with various minor structural variations and arrangements of the control channels it can

also be used in areas of hydraulics. Furthermore, in accordance with the inventive solution, it

can be used for hydraulic pumps, overpressure pump, and vacuum pumps.

The best known representative of a rotary piston engine in the field of combustion engines is the

Wankel engine. It has a moving trochoidal piston that forms a working chamber. The piston

moves by means of internal gears and eccentric bearing of the engine shaft in the interior space

of an epitrochoid. The corners and lateral surfaces of the piston have sealing elements. Gas

exchange occurs by opening and closing slits in a housing enclosing the piston. The Wankel

engine is characterized by its total mechanical balance, its compact construction due to the lack

of a valve train. However, disadvantages are the low torque and the unfavorable combustion

chamber geometry with long combustion paths, resultant high hydrocarbon emissions, and

higher fuel and oil consumption and higher manufacturing costs compared to other reciprocating

piston engines. In addition, due to the working principle there is not a direct opportunity for

realizing a diesel engine with the Wankel principle.

The object of the present invention is to create a reciprocating piston engine whose overall

efficiency is increased relative to that of reciprocating piston engines in prior art, whose mass/performance ratio is improved, whose control is structurally simplified, whose production and assembly is less complex, whose smooth running is optimized, and whose pollutant emissions are reduced.

This object is achieved with a reciprocating piston engine with the features in accordance with

claim 1. Additional advantageous embodiments and further developments are cited in the

dependent claims.

A reciprocating piston engine with rotating cylinders has at least one piston per cylinder unit that

is arranged in a rotor housing, whereby in an internal area of the rotor housing there is a chamber

that has a contour about which the piston is arranged such that it can move 3600 in the rotatable

rotor housing, whereby the piston is coupled to the contour such that the contour effects a stroke

of the piston during the movement of the cylinder unit about the contour. This construction of

the reciprocating piston engine creates a completely new principle. While in the past with the

conventional reciprocating piston engines the cylinder housing was fixed and the reciprocating

pistons conveyed torque via a rotating crankshaft, in the present case the piston is arranged such

that with the rotor housing it can rotate 3600 about a contour. In addition this makes possible

combustion of a combustible medium in a combustion chamber such that pressure builds on the

piston. The pressure on the piston is also applied to the rotor housing. Since it is arranged

rotatable about the contour and the piston is coupled to the contour, torque occurs about the

contour, which leads to a rotary movement of the rotor housing about the contour. At the same

time, the coupling of contour and piston controls the stroke of the piston. This control realizes the cycles of the reciprocating piston engine such as induction, compression, combustion, and exhaust. The 4-cycle principle is preferably applied. However, with a suitable design it is also possible to apply the 2-cycle method. The torque generated depends especially on how many pistons are arranged in the rotor housing. This can be made dependent on the size of the rotor, and vibrations that occur can also be taken into consideration. In particular a plurality of rotor housings can be coupled to one another (in the manner of a radial engine) so that the result is a series of pistons situated one after the other that with the rotor housing are movable about a contour. Preferably one rotor housing has three, four, or more pistons.

Thus, in accordance with the invention the line of action of the piston of a cylinder unit (piston

stroke direction) is arranged in a plane and lies perpendicular to the axis of rotation of the rotor

such that the line of action runs in a straight line and eccentric to the axis of rotation of the rotor.

Preferably the contour is designed such that during a cycle a combustion chamber limited by the

piston is largely isochoric, that is, it has a constant volume. The combustion chamber does not

change over a certain period of time of the cycle. This achieves particularly high torque

generation about the contour since the combustion chamber itself remains largely constant. In

contrast to a different reciprocating piston engine, this results in complete combustion of the

combustion gas in the combustion chamber, and also the temperature that occurs during

combustion, and thus the increase in pressure in the combustion chamber, can be taken

advantage of for a long time. Such a period of an isochoric combustion chamber is adjusted

using the rotational speed. Another deciding factor is the length of the cycle. This is preferably at least 900, however in particular it is through a 1000 rotation about the contour. In a corresponding adaptation of the exhaust of the combusted gas, it is possible for a largely isochoric combustion chamber to be realized through approximately 1200 and more.

Preferably a rotor has four cylinder units that are arranged offset to one another by 900. It is

possible during the cycle for the piston to perform one stroke due to the geometry of the contour,

which is preferably closed. This especially makes sense when the intent is to ensure improved

flow, and thus combustion, in the combustion chamber. The stroke that is controlled by the

contour is preferably such that an induction stroke is clearly longer than an exhaust stroke.

Preferably the contour for this reciprocating piston engine has a path shape that has a first, a

second, a third, and a fourth segment, all of which are convex, concave, or linear. Each stroke

cycle of the piston is thus uniform. In particular the segments are connected to one another such

that largely uniform (negative or positive) acceleration of the piston is produced so that material

load is kept low. In particular in the area of the reversal points the contour is designed such that

compressive loads that occur due to the coupling of piston and contour remain as low as possible.

One embodiment of the contour provides that this is realized in a cam disk. The cam disk has a

slot. The slot is designed such that it provides the contour along which the piston travels

according to the coupling. Preferably the contour/curve guide is embodied such that they

perform at least one cycle during one complete rotation of the cylinder units.

Preferably the reciprocating piston engine has an eccentric disk and a first and a second cam disk.

The two cam disks are arranged opposite the eccentric disk and each has a congruent contour.

Between the two cam disks and the eccentric disk a connecting rod of the piston is guided into the slot via a corresponding guide. The controlled movement provided by the contour via the connecting rod is transferred to the piston, which completes its stroke along the cylinder chamber and its guide.

The piston is preferably guided via a needle-borne spacer shaft in the fixed cam mechanism. The

spacer shaft is preferably a single piece, for instance cast or forged. In one further design,

however, it is made of individual components that have been combined into a whole. The cam

mechanism is formed by the two cam disks and the eccentric disk. Offsetting the two flanks of

the slot curve provides play-free guidance for the piston. Each flank has its own roller that is

situated on the spacer shaft. The rollers run therethrough in opposing rotational directions and

are constantly held in place.

One further development of the reciprocating piston engine provides that a guide part that is

arranged on the piston is separated from the piston by a sealing part. The sealing part and the

guide part are coupled to the piston and are rotatably carried with it. The rotatably carried

coupling transfers the force acting on the piston to the rotor housing. The guide part is movably

arranged along a separate guide in the rotor housing. The guide part is preferably disposed at

least in part in the rotor housing. The sealing part, for instance formed via the piston with its

piston rings and the connecting rod connected thereto, thus forms a first arm, while the guide part

forms a second arm separated therefrom. These two arms are preferably connected to one

another again at a connecting rod bearing. Thus the sealing and guide part form a lever system.

It is preferred that the lever arm of the guide part is shorter than the lever arm of the sealing part.

In this manner it is possible to obtain particularly high torque generation on the rotor housing via

the connecting rod bearing, to which preferably both arms are attached. In particular the piston

with sealing part and guide part is matched to the contour such that the guide part and the sealing

part can each perform one stroke along a straight line in the rotor housing. This means that in

particular the guide part ensures that the pressure force acting on the piston is transferred to the

rotor housing. One stroke of the guide part is then preferably performed by means of a bearing,

in particular a rolling bearing. This is in particular designed such that it is in a position to be able

to transfer continuously a pressure force from the guide part to the rotor housing. The sealing

and guide part thus form a lever system for transferring a pressure force acting on the piston via

the guide part to the rotor housing. The piston with the sealing part and the guide part can be

made of one piece, for instance cast or forged. In a further embodiment, however, these are

made of individual components that have been combined into a whole. The axis of the guide

part perpendicularly intersects the axis of rotation of the rotor.

The piston limiting the combustion chamber is preferably designed such that a mixture rotation is

supported in the combustion chamber during the induction process. This occurs for instance

using a conical piston head arranged approximately central symmetrically that amplifies swirling

by creating a circular squeeze zone. Preferably an inlet angular momentum is obtained for

producing swirling in the combustion space by means of angular admission into the combustion

chamber. For this, an admission aperture is arranged inclined to the longitudinal axis of the

piston (stroke axis), for instance.

Furthermore the reciprocating piston engine has a rotor housing that has a rotationally

symmetrical exterior cover. First, this has the advantage that an imbalance on the rotor housing

is avoided thereby. This is why it is also preferred that corresponding components of the

reciprocating piston engine oppose one another and are thus arranged in pairs in order to avoid

corresponding unbalance torque at high rotational speeds, for instance from 5000 to 8000 min - ,

in particular of 12000 min' (revolutions per minute). Preferably desired is an arrangement of the

components such that the forces that are generated based on the rotation of the rotor housing

compensate one another. Also, a rotationally symmetrical exterior cover makes it possible for

gas supply and gas discharge in the combustion chambers in the rotor housing to be designed

particularly gas tight. One embodiment of the reciprocating piston engine has on the exterior

cover of the rotor housing a rotating gas exchange/sealing system, the surface of which radially

closes with, that is, is sealingly adjacent to, the exterior cover of the rotor housing. If the rotor

housing is arranged in a cover housing, the rotatably carried gas exchange/sealing system is in a

position to produce a seal between the cover housing and the rotor housing.

The rotor housing is preferably arranged in a cover housing that has at least a concave surface

that is arranged opposing an exterior cover of the rotor housing. The gas exchange/sealing

system is designed such that the combustion chamber(s) in the rotor housing are correspondingly

sealed during each of the cycles/phases: induction, compression, combustion, and exhaustion.

In addition, the sealing system ensures the most complete possible filling/evacuation of the

combustion chamber via a corresponding supply/discharge of the inflowing and outflowing gas.

For this, for instance arranged in the cover housing, are corresponding control channels or

The corresponding apertures along which the combustion chamber is filled and discharged. rotor control channels can be arranged along the surface opposing the exterior cover of the for housing or even lateral thereto along the side surface of the rotor housing. This is also true the control the gas exchange/sealing system. Due to the rotating gas exchange/sealing system,

channels, preferably in the form of slits, can be relatively long, for instance they can extend

across a 100 to 300 angle of rotation via discharge channel or for instance up to 1200 angle of

rotation via inlet channel or more; the inlet channel is preferably substantially longer than the

discharge channel. The depth and the width of the control channels and the distance between the

control channels depends on the size of the reciprocating piston engine. The control channels

can be appropriately adapted to the inflow conditions and to the respective pressures during

inflow and outflow.

Preferably the gas exchange/sealing system has a radially movable and preferably rotatable slide

element that is under pressure that is attached eccentrically on the exterior cover of the rotor

housing. This slide element is for instance held in a slot that is arranged eccentrically on the

exterior cover of the rotor housing. The slide element, which is preferably roller-borne, seals the

rotor chamber against the opposing cover chamber. For this, the roller-borne sliding ring

preferably also has a surface corresponding to that of the opposing cover housing. This is

preferably spherical. In addition, the sliding ring has at least one sealing lip, preferably two

sealing lips. The sealing lip touches the cover housing and thereby triggers a sealing effect. In

this manner it is ensured that the system is leak-tight, even if there is an overflow of an ignition

channel with a spark plug arranged therein. When for instance two sealing lips are arranged on a circular sliding ring, the first sealing lip encloses the second sealing lip. Both sealing lips are arranged circular in one another. The sliding ring also preferably performs an axial movement in addition to the radial movement. The axial movement is an axial rotational movement. For this, the sliding ring is attached eccentrically and is arranged with respect to the surface of the cover housing such that the latter produces a rotational movement on the sliding ring. The rotational movement has the advantage for instance that, due to it, any foreign bodies present are transported out due to the radial force and are thus removed from the path of travel.

In order to be able to reduce the torque on the rotor housing, an output drive is preferably flange

mounted to the rotor housing. This is done for instance by means of a speed-transforming gear,

preferably by means of a planetary gear. This makes it possible to increase the number of

rotations and also to decrease the number of rotations. Particularly smooth running can be

obtained when, in addition to the reciprocating piston engine, at least one additional

reciprocating piston engine is additionally arranged in a multiple arrangement one after the other

on one shaft. For instance this makes it possible for a first reciprocating piston engine to be

offset 1800 from a second reciprocating piston engine with respect to the phase of the cycle

segment. This improves running smoothness when there is simultaneous ignition of the first and

second reciprocating piston engines. One further embodiment provides that a plurality of

reciprocating piston engines present in multiple arrangement on one shaft or separate from one

another can each be turned on and off individually. It is also possible for ignition of a

reciprocating piston engine to be triggered for one cylinder. This is possible for instance when

using the reciprocating piston engine when decelerating to save fuel, as is known for motor vehicles. Another embodiment again has modifiable inlet and outlet apertures for the inflow and outflow of the medium to be ignited and for any air to be supplied. This modification is possible for instance by means of a throttle cross-section. The throttle cross-section is preferably controlled or regulated by means of an engine control unit corresponding to the required output.

For ensuring the most frictionless possible running of pistons and other movable components, the

reciprocating piston engine has a lubricating system that is independent of the installation

position of the reciprocating piston engine, that is, it is position-insensitive. The lubricating

system is embodied as position-insensitive circulating forced-oil lubrication. The oil is drawn in

from the oil ring by the annular gear pump. A pressure relief valve within the pump housing

limits the oil pressure and conducts the excess oil back into the intake channel of the pump.

From the pressure channel the oil is conducted through the oil filter to the oil force-feed nozzles.

From there, the lubricating oil travels into the rotor housing. The rotor housing has a plurality of

rotatably carried lubricating channels. These distribute the lubricating oil to the lubrication

points. Due to centrifugal forces, the lubricating medium, generally oil, is pressed outward so

that preferably the moving components are lubricated from the interior of the rotor housing

outward. In this manner it is possible to take advantage of the rotational speed of the

reciprocating piston engine in another manner.

The oil is returned via the rotor housing, which has a plurality of rotatably carried spin channels.

The centrifugal force presses the lubricating oil out through the spin channels. The oil is thrown

against the opposing oil ring aperture, drips down, and travels into the closed part of the oil ring.

There it is fed back into the lubrication cycle. This process is repeated continuously in order to

assure reliable position-insensitive lubrication. Preferably the oil ring can be rotated 3600, is

roller-borne, and is arranged on the front of the cover housing. Two sealing rings seal the oil

ring to the intake channel; these are securely joined to the cover housing. Sealing of the side

opposing the intake channel is performed by a sealing ring, axially movable and provided with a

compression spring, that continuously holds the oil ring in place. The cover housing has

apertures on the circumference through which the thrown oil travels into the oil ring aperture.

The oil ring is divided into two parts, whereby a first oil ring housing is joined to a second oil

ring end housing. However, the oil ring can also comprise one part, for instance a cast part. A

float needle valve is arranged in the oil ring, whereby the float needle valve and the oil return

bores located in the cover housing return the excess oil to the lubrication cycle. The volume

content of the closed part of the oil ring should be less than, but no more than equal to, the

volume content of half of the oil ring aperture. This avoids unnecessary excess oil and

minimizes losses of all types. Inspection windows for checking the oil level are attached to the

oil ring and to the oil ring cover; the windows have markings. The oil level itself is regulated by

an oil fill plug and a drain plug arranged in the oil ring.

The reciprocating piston engine in accordance with the invention makes it possible to convert

energy contained in a combustible medium into mechanical energy. Through combustion, the

medium releases energy in the combustion chamber in which a movable piston is arranged, via

which piston the pressure energy occurring from combustion is converted to mechanical energy.

The pressure energy produces torque about a fixed axis, which leads to rotation of a combustion space with the combustion chamber and the piston about the fixed axis, whereby mechanical energy is removed via this rotation. This principle has the advantage that it can take advantage of a circular motion or acceleration with a long lever arm, whereby high torques occur about the fixed axis.

The following drawings illustrate one exemplary embodiment of a reciprocating piston engine in

accordance with the invention. These explain in detail how the energy contained in a

combustible medium is converted into mechanical energy by means of the inventive

reciprocating piston engine.

Fig. 1 is a front elevation of a section of a reciprocating piston engine (section A-B in

accordance with Fig. 2)

Fig. 2 is a side elevation of the reciprocating piston engine in Fig. 1;

Fig. 3 is a piston, with sealing part and guide part, guided on a contour;

Fig. 4 is a side elevation of the contour and one guide of the piston along the contour;

Fig. 5 is a gas exchange/sealing system for the reciprocating piston engine in Fig. 2;

Fig. 6 is a rotor seal of the gas exchange/sealing system in Fig. 5;

Fig. 7 is a sealing body of the gas exchange/sealing system in Fig. 5;

Fig. 8 is a sealing strip of the gas exchange/sealing system in Fig. 5;

Fig. 9 is a side seal spring of the gas exchange/sealing system in Fig. 5;

Fig. 10 is an oil ring in the lubricating system in Fig. 2;

Fig. 11 is a schematic view of a multiple arrangement of reciprocating piston engines.

Fig. 1 illustrates a reciprocating piston engine 1. It has a first piston 2, a second piston 3, a third

piston 4, and a fourth piston 5. The pistons 2, 3, 4, 5 are each arranged offset 900 in a rotor

housing 6 of the reciprocating piston engine 1. A space 7 is in the interior area of the rotor

housing 6. A curved guide or contour 8 is arranged in the space 7. The pistons 2, 3, 4, 5 each

perform one stroke, indicated by a double arrow. The piston 2, 3, 4, 5 runs along a straight first

guide 9. The first guide 9 is employed for the cylinder unit in the rotor housing 6. The piston 2,

3, 4, 5 has a piston head with a conical top 10 that is arranged central-symmetrically (centrically).

The top 10 forms part of the combustion chamber geometry. The illustrated conical shape of the

top 10 takes advantage of the angular momentum of the inflowing fuel/air mixture in the

induction process in order to obtain better swirling and thus better mixing in the combustion

space. This improves the subsequent combustion. For shaping the combustion chamber, the

conical top 10 can also be replaced by another top, whereby its geometry depends for instance on

how the medium to be burned, that is, the fuel, is supplied. For instance, different injection

methods can be used that are typical for an Otto engine or diesel engine. Among these are

injection methods without air swirling with a 6- or 8-hole injection nozzle, as is known for slow

running large diesel engines. A 3- or 5-hole injection nozzle can also be used, whereby during

direct injection the combustion air flowing to each of the pistons.2, 3, 4, 5, in the form of a

swirling stream effects formation of a mixture given the appropriate shape of the inlet element.

It is also possible to inject fuel onto the combustion chamber wall using an eccentrically

arranged single-hole nozzle into a trough-shaped combustion chamber. In addition to direct

injection methods, secondary chamber combustion methods such as for instance swirl chamber or precombustion chamber methods can be used. If the reciprocating piston engine 1 is designed appropriately, a charge stratification also works in which a ignitable mixture is produced at the spark plug by internal mixing, while a depleted mixture is present in the other area of the combustion chamber.

The reciprocating piston engine 1 can also be employed for a multifuel engine. Due to high

compression of the reciprocating piston engine 1, which can be y = 14 to y = 25 and greater, it is

possible to be able to process fuels of very different quality without damaging the engine. An

internal mixture formation is used, for instance, in which for supporting ignition an additional

fuel stream, injected directly into the combustion chamber, of 5 - 10% of the full fuel load

quantity ensures firing. In this latter case, an external mixture formation can also be used. Thus,

the reciprocating piston engine 1 can be used for a wide variety of fuels. These include alcohol or

gas, especially hydrogen, in addition to conventional gasoline or diesel fuels. The components

needed for the combustion process are arranged in a cover housing (not illustrated in greater

detail) in which the rotor housing 6 is situated.

In addition to different combustion methods, the manner in which the reciprocating piston engine

1 works can also be supported by various supercharging methods. Suitable for this are pressure

pulsation intake manifold supercharging, resonance charging, and switch-over flap

supercharging systems, whose induction pipe length can be changed depending on number of

rotations by opening or closing flaps. In addition to using these supercharging systems, which

exploits the dynamics of the air inducted (fluctuation in the air column), mechanical supercharging systems such as for instance positive displacement superchargers can also be used in piston, vane, or Roots types. Exhaust gas turbocharging can also be used, whereby the exhaust gas turbine to be used can be switched on or off depending on the number of rotations of the reciprocating piston engine 1. In addition to exhaust gas turbocharging, pressure wave supercharging with a pressure wave supercharger is also possible. Appropriate supercharging is furthermore supported by the use of charge-air cooling for the reciprocating piston engine 1. In this manner it is possible to obtain even higher compression. A corresponding supercharging unit is connected for instance directly or indirectly to the rotor housing 6 in order to be able to use its rotation energy.

The piston 2, 3, 4, 5 illustrated in Fig. 1 furthermore has a first piston ring 11 and a second piston

ring 12. Both piston rings 11, 12 seal a combustion chamber 13 from the space 7. In accordance

with the illustrated embodiment, the second piston ring 12 also assumes the function of an oil

scraper ring. The oil for lubricating the piston 2, 3, 4, 5 is caused to travel from the interior area

of the chamber 7 outward to the first guide 9. Furthermore, the piston can have expansion

controlling inserts, so that different materials and thus different coefficients of expansion can be

taken into account. For instance, the rotor housing 6 and the first guide 9 are made of aluminum.

Furthermore, it can be seen from Fig. 1 that the piston 2, 3, 4, 5 together with a connecting rod

15 forms a sealing part 14. The connecting rod 15 is joined directly to the piston 2, 3, 4, 5 - both

are rigidly coupled to one another. The design of the contour 8 permits the piston 2, 3, 4, 5 to be

guided linearly. Thus, for instance, it is possible to do without a piston pin and its bearing in the a linear guide for connecting rod. The contour 8 also has a curved segment in order to provide the coupling. Furthermore the piston in the reciprocating piston engine 1 in conjunction with the arranged on the connecting rod 15 is an aperture 16 for a connecting rod bearing 17, whereby 18 connects the contour 8 connecting rod bearing 17 receives a spacer shaft 18. The spacer shaft center of the piston to the connecting rod 15. The spacer shaft 18 is arranged eccentrically to the rod 15 preferably has a 2, 3, 4, 5. Thus the connecting rod 15 forms a lever arm. The connecting forces. bar shape in cross-section. This permits good reception and transfer of pressure connecting rod 15. Furthermore illustrated in Fig. 1 is that a guide part 19 is rigidly joined to the is for instance a bush The guide part 19 is arranged in a second guide 20. The second guide 20 The bearing arranged in the rotor housing 6. A bearing 21 is arranged about the guide part 19. in the second guide 21 permits the greatest possible friction-free movement of the guide part 19 system 20. The bearing 21 is preferably a rolling bearing. Since the guide part 19 forms a lever 6 with the sealing part 14, the bearing 21 is especially also able to transfer to the rotor housing in Fig. 1, the bearing pressure forces that occur according to the lever system. So, as illustrated locking 21 is moveable both relative to the second guide 20 and relative to the guide part 19. A 21 cannot radially ring 22 is arranged in the rotor housing 6 as a path limit so that the bearing about the exit the rotor housing 6 outward. This makes it possible for the guide part 19 to move of the second contour 8 via the second guide 20 in one 360o rotation, however without a surface is advantageously at guide 20 that transfers the force not being fully utilized. The bearing 21 least as long as the second guide 20.

Fig. 1 illustrates the four pistons 2, 3, 4, 5, each in a different working position. Arrows indicate

the direction of rotation. The first piston 2 is just beginning induction, the second piston 3 is

situated approximately at the end phase of induction, the third piston 4 is situated at the end of

the ignition phase, the fourth piston 5 is situated in the work phase. Corresponding to the

respective positions of the pistons 2, 3, 4, 5, the guide part 19 is in a different position within the

second guide 20. However, the bearing 21 is dimensioned such that it can project radially

inward via the second guide 20. So that the bearing 21 does not strike the contour 8 for instance

when the reciprocating piston engine 1 is idling, a corresponding path limit can be provided.

This is for instance present on the guide part 19 itself, for instance by means of a material

projection. Alternatively, the second guide 20 can itself have such a path limit. The bearing 21

is preferably also lubricated. The lubricant is supplied using the oil force feed nozzle 58, which

supplies all components with sufficient lubricating oil.

Furthermore, it can be seen from Fig. 1 that the contour has a first segment A, a second segment

B, and a third segment C. Each of these is curved. The curvature is designed such that the guide

part 19 and the piston 2, 3, 4, 5 can travel linearly along the first guide 9 or the second guide 20.

The third segment C is especially at least in part designed such that during the work phase that

takes place there the piston 2, 3, 4, 5 remains largely constant in its position within the first guide

9. Thus the combustion chamber 13 does not change during the work phase. This leads to

particularly high pressure production in the combustion chamber 13. Via the lever system made

of sealing part 14 and guide part 19, this effects particularly high torque transfer to the rotor

housing 6. In a fourth segment D the contour 8 has a shape such that the piston 2, 3, 4, 5 is controlled such that it is possible for the combusted gas to flow out of the combustion chamber

13. For this, the contour 8 in Segment D has a largely linear area. Furthermore the contour 8 is

designed such that canting of the piston is prevented in both the upper and in the lower dead

center. This also results in reduced noise. In addition the lateral pressure of the piston 2, 3, 4, 5

on the cylinder wall 9 is minimized.

Fig. 1 furthermore illustrates a slide element 24 in the gas exchange/sealing system 23. The gas

exchange/sealing system 23 is arranged on an exterior cover 23a of the rotor housing 6. This

causes the gas exchange/sealing system 23 to be rotatably carried with the rotor housing 6. The

gas exchange/sealing system 23 has a roller-borne slide element 24 that is fixed eccentrically

resiliently on one cylinder end 25 in a slot 26 and lies sealingly against the combustion chamber

13. The slide element 24 has a roller-borne sliding ring 27 that has a first sealing lip 28 and a

second sealing lip 29. The sliding ring 27 is adapted to an opposingly arranged surface of a

cover housing 30. The sealing lips 28 , 29 have a sealing action with the surface of the cover

housing 30. If the respective slide element 24 overflowed via an ignition channel 31 in which a

spark plug 32 is arranged, a spark is advantageously not triggered until the spark plug 32 is

situated within the round first sealing lip 28. The geometry of the ignition channel 31 in the

cover housing 30 is preferably designed such that both sealing lips 28, 29 ensure sealing. Thus

the slide element 24 acts as a type of safety lock: when the ignition channel 31 is overflowed, if

a certain gas volume can still escape via the first sealing lip 28, it is at least captured via the

second sealing lip 29. The glide element 24 is itself designed within the slot 26 such that it is not

possible for the compressed gas to escape laterally along the slot 26. For this, the slot 26 can have for instance one or more sealing rings. Because of the resilient bearing of the glide element

24, it is in a position to assure the seal when the inlet channel 33 and the outlet channel 34 and

the ignition channel 31 are overflowed by corresponding counter-pressure to the surface of the

cover housing 30.

Via a corresponding supply and discharge of the inflowing gas, the sealing system 23 ensures the

most complete possible filling/evacuation of the combustion chamber. For this, arranged for

instance in the cover housing 30 are corresponding control channels 33, 34 along which the

combustion chamber is filled and evacuated. The control channels 33, 34 are arranged along the

surface opposing the exterior cover 23a of the rotor housing 6. This also applies to the gas

exchange/sealing system 23. Due to the rotating gas exchange/sealing system 23, the control

channels 33, 34 can be relatively long. Preferably the inlet channel 33 is substantially longer

than the outlet channel 34. The depth of the control channels 33, 34 and the width of the control

channels 33, 34 and the distance between the control channels 33, 34 depends on the size of the

reciprocating piston engine.

Fig. 2 illustrates a lateral cross-section of the reciprocating piston engine 1 in accordance with

Fig. 1. It can be seen that the gas exchange/sealing system 23 has a sealing body 35. Sealing

strips 36 are arranged on the sealing bodies 35. The sealing strips 36 are placed under pressure

radially using side seal springs 37. The sealing bodies 35 are themselves also able to exert a

pressure on the sealing strips 36. The pressure is exerted in the circumferential direction. For

this each sealing body 35 carries a leg spring 38. The leg spring 38 thus provides a seal between

the sliding ring 27/slide element 24 and the sealing strip 36 adjacent to the slide element 24. The slide element 24 is attached eccentrically, whereby the degree of eccentricity is indicated by the angle V. Sealing bodies 35, sealing strips 36, and side seal springs 37 are fixed bilaterally on the exterior cover 23a of the rotor housing 6. This makes it possible for the gas exchange channels and the combustion chamber 13 to be completely sealed. This seal is also provided when the rotor 6 passes over the ignition channel 31/the spark plug 32. The gas exchange/sealing system

23 is thus in a position to effect sealing of the combustion space and also sealing during gas

exchange. The gas exchange/sealing system 23 also makes it possible for gases to enter and exit

via radial apertures. This means that the complete control unit required for gas exchange that is

necessary for conventional reciprocating piston engines is not needed, which leads to a

substantial reduction in components and to better gas exchange. The reciprocating piston engine

1 illustrated in Fig. 1 works with four cycles (induction, compression, work, exhaust). Thus, in

one rotation of the rotor housing 6 two pistons complete one working cycle, for instance pistons

2 and 3.

The reciprocating piston engine 1 has a cover housing 30 that is divided into two parts. A first

partial cover housing 39 is joined to a second partial cover housing 40. The rotating rotor

housing 6 is arranged in the cover housing 30. The rotor housing 6 is preferably also divided

into two parts. A first partial rotor housing 41 is joined to a second partial rotor housing 42. The

surface of the cover housing 30 that opposes the exterior cover 23a of the rotor housing 6 is

curved, in fact, it is concave. With regard to sealing, this spherical design of the surfaces has the

advantage that it is easier to obtain a gas-tight seal by means of the gas exchange/sealing system

23, whereby the production tolerances for the gas exchange/sealing system 23 are selected such that the functional spaces are adequately sealed, even despite the freedom of movement the movable parts have. Furthermore, a port 43 is arranged on the cover housing 30. This is the port 1 and which for the discharge channel 34. The inlet channel 33, which is illustrated only in Fig.

runs farther in the cover housing 30, is arranged opposing the piston such that gas is supplied in. The degree of eccentrically. In this manner a swirling effect is generated when the gas flows

eccentricity is again indicated by the angle V.

In addition, the guiding of the connecting rod or the piston along the contour 8 can be seen in Fig. in 2. The contour 8 is formed by one eccentric disk 44 and by two slots 47 that are congruent in the terms of course and that are arranged in mutually opposing cam disks 45, 46. Arranged Rollers slots 47 is a spacer shaft 18, the ends 48, 49 of which each have one rolling bearing 50.

51 are allocated to the rolling bearings 50. The rollers 51 and the spacer shaft 18 run along the

contour 8. A needle bearing 17 is arranged on the spacer shaft 18 as connecting rod bearing. It

is characterized especially in that it can receive and transfer high bearing forces. This is

advantageous for the forces and torques that occur from the sealing part and guide part 19 of because of the lever system. The external flank of the slot 47 receives the centrifugal forces forces. the pistons 2, 3, 4, 5, whereby the curve flank of the eccentric disk 44 receives the gas

The roller-borne roller 51 has play against the internal curve flank of the slot 47. Since it the performs one rotation about its own axis when rolling on the external curve flank, which has

wrong direction relative to the other curve flank. This play is avoided using the eccentric disk 44,

since the two flanks of the slot curve 47 are offset to one another and each flank has its own and roller 51 on the spacer shaft 18. The rollers 51 then run in opposing directions of rotation can be kept permanently in place. The cam disks 45, 46 are arranged opposing the eccentric disk

44, whereby the contours are bolted to one another congruent and immovable. The cam disks 45,

46 and the eccentric disk 44 are themselves rigidly joined via the housing cover 52 to the cover

housing 30. The cam disks 45, 46 and the eccentric disk 44 further support a rotor housing

bearing, embodied in this case as a rolling bearing 53.

Fig. 2 illustrates a lubricating system 54. The lubricating system 54 is arranged in the rotor

housing 6 and on the cover housing 30 and has an oil pump 55. This is coupled via the driving

plate 56 to the rotor housing 6 such that it is driven. The lubricating system 54 is designed

independent of the installation position of the reciprocating piston engine, that is, as position

insensitive circulating forced-oil lubrication. The oil is drawn in from the oil ring 57 by the

annular gear pump 55, and a pressure relief valve within the pump housing limits the oil pressure

and conducts the excess oil back into the intake channel of the pump. From the pressure channel

the oil is conducted through the oil filter to the oil force-feed nozzles 58. From there, the

lubricating oil travels into the rotor housing 6. For the sake of clarity the pressure relief valve,

oil filter, and oil channels are not illustrated in greater detail, even in the individual drawings.

The rotor housing 6 has a plurality of rotably carried lubricating channels 59; these distribute the

lubricating oil to the lubrication points. Due to centrifugal forces, the lubricating medium,

generally oil, is pressed outward so that preferably the moving components are lubricated from

the interior of the rotor housing 6 outward. In this manner it is possible to take advantage of the

rotational speed of the reciprocating piston engine in another manner. The oil is returned via the rotor housing 6, which has a plurality of rotatably carried spin channels 60. Centrifugal force presses the lubricating oil out through the spin channels 60. The oil thrown against the opposing oil ring aperture 61, drips down, and travels into the closed part of the oil ring 57. There it is fed back into the lubrication cycle. This process is repeated continuously in order to assure reliable position-insensitive lubrication.

Preferably the oil ring 57 can be rotated 3600, is borne on rollers 62, and is arranged in the first

partial cover housing 39. Two sealing rings 64 seal the oil ring 57 to the intake channel 63; these

are securely joined to the first partial cover housing 39. Sealing of the side opposing the intake

channel 63 is performed by a sealing ring 66, axially movable and provided with a compression

spring 65, that is fixed in a slot 67 and that continuously holds the oil ring 57 in place. The first

partial cover housing 39 has apertures 68 on the circumference through which the thrown oil

travels into the oil ring aperture 61. The oil ring 57 is divided into two parts, whereby a first oil

ring housing 69 is joined to a second oil ring end housing 70. However, the oil ring 57 can also

comprise one part, for instance a cast part. A float needle valve 71 is arranged in the oil ring 57.

The float needle valve 71 and the oil return bores 72 located in the first partial cover housing 39

return the excess oil/leaks to the lubrication cycle.

In order to have adequate oil pressure present when the reciprocating piston engine 1 is started, it

is furthermore possible to also have for instance an oil accumulator container present. This is

always maintained under pressure when the reciprocating piston engine 1 is being operated. This

pressure does not decrease even when the reciprocating pressure engine 1 is turned off. On the contrary, it does not release this pressure until the reciprocating piston engine 1 is to be started.

It is also possible to provide an oil pump separate from the rotor housing 6. This can be supplied

for instance via an external energy source such as a battery. Another embodiment provides that

an oil pump is itself supplied via an external energy source and also via the reciprocating piston

engine 1 itself. It is possible to switch from the one energy source to the other energy source at a

pre-definable time.

Fig. 2 illustrates an output drive 73 of the reciprocating piston engine 1. The output drive 73 can

act directly on a device receiving mechanical energy. Furthermore it is possible to provide a

coupling. One further embodiment provides for providing a gear. Preferably the gear is a

planetary gear 74. A further advantage is obtained when an infinitely variable speed

transmission is employed.

The reciprocating piston engine 1 is then in a position to be operated at a constant speed. The

required speed of the device receiving the energy is then adjusted by means of the infinitely

variable speed transmission. In this manner it is also possible to change the torque that is taken.

In addition to using an infinitely variable speed transmission, it is also possible to use a gear with

gear steps.

Fig. 3 illustrates a cut-out of the reciprocating piston engine 1 as illustrated in Fig. 1 and Fig. 2.

The lever system made of sealing part 14, guide part 19, and contour 8 is illustrated. The rollers

51 of the lever system are situated along the contour 8 in a position in which a high torque is a triangle of forces transferred to the rotor housing 6. This transfer is indicated as an example by F of 2600 N acts on with corresponding dimensioning. While for instance a maximum gas force , the piston center the center of the piston 2, 3, 4, 5, the distance 12 of for instance 38 mm between 2, 3, 4, 5 axis and the roller center axis at a dynamic effect based on the geometry of the piston 340. leads to a calculated dynamic effect direction that results in an angle B of approximately on the rotor With a corresponding design of the guide part 19, transferred to the acting force L of approx. 25 housing 6 results in a force F2 of approx. 3850 N. An average effective length 1 how the mm is assumed (effective center lever arm). Using this example, it is demonstrated force acting on the piston 2, 3, 4, 5 can be used by means of the lever system to increase torque.

The increase in force of F1 = 2600 N to F2 =3850 N is only an example in this case. Depending this is on the on the modification to the lever paths and the force-transferring surfaces, whether the current application piston 2, 3, 4, 5 or even on the guide part 19, the torque most suitable for for the can be adjusted, for instance taking into account stresses occurring in the materials used

individual components. In addition to the linear guide of the pistons 2, 3, 4, 5 and of the guide is also possible to part 19 illustrated in Fig. 3, with appropriate adaptation of the contour 8 it 5 itself or of both provide a curved guide either of the guide part 19 or even of the piston 2, 3, 4, that in in combination with one another. For this, the contour 8 is appropriately adapted such is also possible one 3600 rotation piston 2, 3, 4, 5 and guide part 19 can run along their guide. It

to be able use the geometry of the piston surface to appropriately adjust the force introduction offset to effect into the lever system. Thus, it is possible to provide a resulting force introduction the lever the piston axis, instead of centrally. For instance, a resulting force introduction into external system eccentric to the piston center axis is possible, in particular in the area of an piston area for obtaining a large lever arm. This is possible for instance using an appropriate surface design of the piston 2, 3, 4, 5. It is furthermore useful when the guide part 19 can extend radially far outward for force transfer. This improves the torque effect. In particular it makes it possible that, using the radial extension of the guide part 19, the integral of the surface force on the guide part 19 is designed such that it either runs in a uniformly increasing function or in an exponential function.

Fig. 4 illustrates a top view of the cut-out from Fig. 3. The rollers 51 that are adjacent to the

contour 8 are pressed thereagainst via a centrifugal force F3 of for instance 800 N. The

centrifugal force depends on the rotational speed. The first cam disk 45 and the second cam disk

46 are designed such that they can receive this centrifugal force. In the work cycle the rollers 51

that are adjacent to the contour 8 of the eccentric disk 44 are pressed thereagainst using a gas

force F1 of for instance 2600 N. The eccentric disk 44 is designed such that it can

correspondingly receive this gas force. If the lever system has appropriate components, it can be

adapted to a corresponding reciprocating piston engine 1 with other dimensions. Preferably the

guide part 19 is one piece, whereby it can also be bolted to the lever system as a bush element.

In particular this permits a modular construction system to be used. The modular construction

system contains for instance pistons, connecting rod, bearing, rollers, eccentric disk, cam disks,

etc.

Fig. 5 illustrates the gas exchange/sealing system 23 from Fig. 2. As illustrated in Fig. 5, the gas

exchange/sealing system 23 has four slide elements 24, eight sealing bodies 35, sixteen sealing adapted to the sealing strips 36, and sixteen side seal springs 37. Sealing strips 36 are sealingly pressure on the bodies 35 and to the slide elements 24. The side seal springs 37 exert radial sealing bodies 35 and sealing strips 36.

5. The slide element 24 has a Fig. 6 is an exploded illustration of a slide element 24 from Fig. sealing roller-borne sliding ring 27, upon which are arranged a first sealing lip 28 and a second

a race 76, and a cup spring 77 as lip 29. The sliding ring 27 is fixed together with a ball cage 75, The interior a radial pressure device for the slide element 24 in a slot 26 situated on the cylinder.

sealing ring 78 seals the slide element 24 against the combustion chamber 13. Fig. 1 illustrates

combustion how the slide element 24 is fixed and how the slide element 24 is sealed from the

chamber 13.

sealing body 35 contains a Fig. 7 illustrates a sealing body 35 from Fig. 5 in greater detail. The the leg spring 38 on the leg spring 38 that is fixed via a cylinder pin 79. A pressure is exerted via sealing sealing strips 36 to be arranged in the sealing body 35. The leg spring 38 presses the

the sealing strips 36 strips 36 outward so that when installed a dynamic effect in the slot presses 36 in onto the slide element 24 in the circumferential direction. This also holds the sealing strips permits their position. In this manner the seal is created for the gas exchange. In addition, this The sealing the components to be sealed that are situated in the interior of the rotor housing 6.

bodies 35 can comprise for instance silicon nitrite.

Fig. 8 illustrates a sealing strip 36. It has a first end 80 and a second end 81. The first end 80 is

adapted to the slide element 24 corresponding to the seal. The second end 81 is also designed

such that it receives pressure from the leg spring 38 and transfers [it] into the sealing strip 36 to

the first end 80 in particular uniformly. The sealing strip 36 can itself also comprise silicon

nitrite.

Fig. 9 illustrates one option for exerting radial pressure on a sealing strip 36. This radial pressure

device takes the form of a side seal spring 37. The waves mean that the side seal spring 37

permits a plurality of force introduction points to be applied to the sealing strip 36 distributed

across its circumference. This leads to uniform exertion of pressure in the radial direction and

thus to a particularly effective seal.

Fig. 10 illustrates an oil ring 57 of the lubricating system 54. The oil ring 57 has two parts. A

first oil ring housing 69 is connected to a second oil ring end housing 70. The oil ring 57 has a

first segment E and a second segment F. These are each radially allocated to the axis of rotation

of the oil ring 57. The segment E is the closed part, the segment F is the open part of the oil ring

57. The volume content of the closed part in the segment E of the oil ring should be less than but

nor more than equal to the volume content of half the oil ring aperture of the segment F. This

avoids unnecessary excess oil and minimizes oil and hydraulic losses. Oil return occurs via the

float needle valve 71, which is arranged in the oil ring 57 and in the oil return bores 72 in the

first partial cover housing 39. The oil ring 57 is preferably borne on rollers 62 so that it can

rotate more easily 3600 about its own axis. For controlling the oil level, inspection windows 82

57 and to the oil that have markings to be able to measure the oil level are attached to the oil ring the oil drain plug 84, which ring cover. The oil level itself is regulated by the oil fill plug 83 and

are arranged in the oil ring 57.

1a, lb, 1c. These are Fig. 11 illustrates a multiple arrangement of reciprocal piston engines supercharger device 85. coupled to one another. Furthermore, this multiple arrangement has a

This can for instance contain a charge-air cooling 86 that is usefully provided in an exhaust gas

supercharger. The reciprocating piston engines are supplied lubricating agent via a lubricating

device 87. The lubricating device is preferably coupled to the reciprocating piston engines la, lubrication is lb, 1c such that it is driven by them. Then a position-insensitive forced feed providing an external preferably used for the lubricating device 87. There is also the option of 88, for instance lubricating device 87. This is supplied for instance via an external energy source

a battery. Furthermore an electronics unit 89 is provided in connection with the reciprocating For instance one or piston engines la, lb, lc. The electronics unit 89 controls or regulates them. off. The a plurality of these reciprocating piston engines 1a, lb, Ic can be turned on or on and off. electronics unit 89 also controls ignition. For instance the ignition can also be turned via a Furthermore, the electronics unit 89 regulates or controls the fuel quantity that is supplied to the fuel reservoir container 90 through a corresponding mixture preparation 91 or the like be reciprocating piston engines l a, lb, I c. An exhaust treatment apparatus 92 can also

connected to the reciprocating piston engines la, lb, 1c. This is for instance a catalytic converter,

an exhaust gas return, etc. This is preferably also controlled or regulated by means of the

electronics unit 89, via the fuel supply.

A consumer 93 can be connected to the reciprocating piston engines la, lb, Ic; it converts

energy that originates in the engines. An intermediate member 94 is preferably also arranged

between the consumer 93 and the reciprocating piston engines 1a, lb, 1c. The intermediate

member is for instance a coupling, a gear, or something else.

The reciprocating piston engine l a, l b, 1c can also be employed in an interconnection with one

or a plurality of other energy supply devices 95. This can be a fuel cell, a battery, or the like.

The energy supply device 95 also supplies the consumer 93 with energy. The energy supply

device 95 can be turned on and off via the electronics unit 89, just like one or more of the

reciprocating piston engines la, lb, Ic. The reciprocating piston engines la, lb, lc can for

instance act as the basic supplier. The energy supply device 95 is only turned on as needed. The

reverse is also possible. The two can also supplement one another.

The reciprocating piston engine as described above is preferably operated either alone or with in other units. For instance, the reciprocating piston engine can be used for the energy generator

a stationary application. For instance, this is possible for block heating and power stations.

Other stationary applications are small energy suppliers or transportable units such as emergency offers generating sets. Furthermore, because of its construction, the reciprocating piston engine

the opportunity to be used for commercial motor vehicles, passenger cars, or even small piston equipment such as lawnmowers, saws, and other such equipment. The reciprocating

engine can also be used in other transportation means such as motorcycles and mopeds.

Fuel consumption can be reduced with this new reciprocating piston engine. It is also possible, it. The now and in the future, to satisfy the worldwide known exhaust gas regulations with of revolutions. reciprocating piston engine provides a very high torque at very low numbers

Therefore very good driving performance is possible. In particular the reciprocating piston of the engine can be used for vehicles that are operated with hydrogen. The structure noise reciprocating piston engine results as a matter of principle in a reduction in resultant

emissions. This makes it possible to use the reciprocating piston engine even in noise-sensitive

areas. The construction of a reciprocating piston engine in a modular system with many identical

components makes it possible to reduce production costs. Because of the work principle, a valve complex components in conventional reciprocating piston engines such as for instance

train are not needed. Despite this they are reliable. There are few wear parts because of the

fundamentally different construction compared to conventional reciprocating piston engines.

This makes maintenance easier. In addition, this makes it easier to exchange the components at

less cost. The reciprocating piston engine is designed such that both sealing and appropriate

lubrication are assured despite unavoidable heat expansion and any corresponding deformation,

even for components under stress, and functionality is assured even with progressive wear.

The functioning principle permits many options for operating the reciprocating piston engine.

For instance, it is advantageous to undertake combustion of the fuel at the same cylinder volume

in the work cycle. The reciprocating piston engine is also designed such that in the work cycle

no inertial forces act against the gas forces. The advantageous 4-cycle method with separate gas exchange provides little loss compared to conventional piston engines. The design of the piston with sealing part and guide part as lever system makes possible high force transmission and high torque. The combustion space can be kept compact, which again requires only a small combustion space surface. What this permits is that the reciprocating piston engine can be liquid-cooled but also air-cooled. Since the point of application of the piston guide lies far outside of the rotor point of rotation, great torque is generated using the gas force in conjunction with the lever arm in the cycle. Furthermore, advantageously only one spark plug and one carburetor or injection nozzle is needed on the reciprocating piston engine. This reduces the number of components that have to be maintained and that are also subject to wear. Combustion space sealing occurs by means of a sliding ring that in particular can be rotating. The rotation provides the fuel/air mixture a swirl that is advantageous for combustion. The seal between the cover housing and the rotor housing occurs using the fixed sealing elements in a secure manner.

Using an appropriate gear, for instance a planetary gear, it is possible to increase the number of

revolutions of the reciprocating piston engine for the consumer. Another advantage and thus a

particular flexibility for the employability of the reciprocating piston engine is a position

insensitive oil supply. The reciprocating piston engine can be used in all conceivable installation

positions. Despite this, the oil supply is always assured. Overall, the separation of inlet and

discharge outlet channels also enables adequate cooling of all stationary and moving components.

This is further supported by the separation of combustion chambers from other movable parts of

the engine. The reciprocating piston engine thus ensures high output and certain function with

low susceptibility to faults.

List of reference symbols used

1 Reciprocating piston engine 24 Slide element

la Reciprocating piston engine 25 Cylinder end lb Reciprocating piston engine 26 Slot/cylinder 1c Reciprocating piston engine 27 Sliding ring 2 Piston 28 First sealing lip 3 Piston 29 Second sealing lip 4 Piston 30 Cover housing Piston 31 Ignition channel 6 Rotor housing 32 Spark plug 7 Chamber 33 Inlet channel 8 Contour 34 Discharge channel 9 Guide 35 Sealing body Top 36 Sealing strip 11 Piston ring 37 Side seal spring 12 Piston ring 38 Leg spring 13 Combustion chamber 39 First partial cover housing 14 Sealing part 40 Second partial cover housing Connecting rod 41 First partial rotor housing 16 Aperture/connecting rod 42 Second partial rotor housing 17 Connecting rod bearing 43 Port 18 Spacer shaft 44 Eccentric disk 19 Guide part 45 Cam disk Second guide 46 Cam disk 21 Bearing 47 Slot/contour 22 Locking ring 48 End/spacer shaft 23 Gas exchange/sealing system 49 End/spacer shaft 23a Exterior cover 50 Rolling bearing

51 Rollers/spacer shaft 74 Planetary gear 52 Housing cover 75 Ball cage 53 Rolling bearing 76 Race 54 Lubricating system 77 Cup spring Oil pump 78 Interior sealing ring 56 Driving plate 79 Cylinder pin 57 Oil ring 80 First end/sealing strip 58 Oil force-feed nozzles 81 Second end/sealing strip 59 Lubricating channels 82 Inspection windows Spin channels 83 Oil fill plug 61 Oil ring aperture 84 Oil drain plug 62 Rollers/oil ring 85 Supercharger device 63 Intake channel 86 Charge-air cooling 64 Two sealing rings 87 Lubricating device Compression spring 88 Energy source 66 Sealing ring 89 Electronics unit 67 Slot/sealing ring 90 Fuel reservoir container 68 Apertures/partial cover housing 91 Mixture preparation unit 69 First oil ring housing 92 Exhaust treatment apparatus Second oil ring end housing 71 Float needle valve 93 Consumer 72 Oil return bores 94 Intermediate member 73 Output drive 95 Energy supply device

1. Reciprocating piston engine

with a contour (8) that forms a closed curve guide,

with a rotor housing (6) that is rotatably arranged with respect to said contour (8) and that transfers the acting torque to the drive or output drive of said reciprocating piston engine,

with at least one unit (la, lb, Ic, ld) that is arranged in said rotor housing (6) and that comprises a cylinder (9) and a piston (2, 3, 4, 5), whereby the line of action of said piston (2, 3, 4, 5) in said cylinder (9) lies in a plane perpendicular to the axis of rotation of said rotor housing (6) and is eccentric to the axis of rotation of said rotor housing (6) and in a straight line,

with one connecting rod (15) that is rigidly coupled to said piston (2, 3, 4, 5) and by being guided along said contour (8) transfers the controlled movement specified thereby to said piston (2, 3, 4, 5),

characterized in that joined to said connecting rod (15) is a guide part (19) that is arranged movable along a separate guide in said rotor housing (6), whereby said piston (2, 3, 4, 5) with said connecting rod (15) and said guide part (19) can each perform one stroke along a straight line in said rotor housing (6).

2. Reciprocating piston engine in accordance with claim 1, characterized in that a connecting rod bearing (17) for guiding on said contour (8) is embodied in the area of the connecting point of connecting rod (15) and guide part (19).

3. Reciprocating piston engine in accordance with claim 1 or 2, characterized in that said separate guide for said guide part (19) is a linear guide, the longitudinal axis of which intersects the axis of rotation of said rotor housing (6).

4. Reciprocating piston engine in accordance with claim 2, characterized in that said linear guide (20) of said guide part (19) is a bush (20) and in that a rolling bearing (21) is arranged about said guide part (19), displaceable in the longitudinal direction of said bush (20).

5. Reciprocating piston engine in accordance with claim 4, characterized in that said rolling bearing (21) is movable relative to said guide part (19) and said bush (20), whereby said rolling bearing (21) is prevented from exiting outward in the longitudinal direction of said guide part (19) by a path limit.

6. Reciprocating piston engine in accordance with claim 4, characterized in that said path limit is a locking ring (22) affixed in said rotor housing (6).

7. Reciprocating piston engine in accordance with claim 5 or 6, characterized in that said rolling bearing (21) is at least as long as said bush (20).

8. Reciprocating piston engine in accordance with any of the preceding claims,

characterized in that four units (la, lb, Ic, ld) comprising cylinder (9) and pistons (2, 3, 4, 5) are provided, whereby the lines of action of said pistons are arranged offset to one another by 900 in the plane perpendicular to the axis of rotation of said rotor (6).

9. Reciprocating piston engine in accordance with any of the preceding claims, characterized by a design of said contour (8) such that said unit (la, lb, 1c, ld) comprising cylinder (9) and pistons (2, 3, 4, 5) completes at least one work cycle when said rotor housing (6) makes one complete rotation.

10. Reciprocating piston engine in accordance with claim 9, characterized by a design of said contour (8) such that during the work cycle of said unit (la, lb, 1c, ld) the combustion chamber (13) limited by said unit's pistons (2, 3, 4, 5) is at least largely isochoric.

11. Reciprocating piston engine in accordance with any of claims 2 through 10, characterized in that said contour is formed by an eccentric disk (44) and by two congruent slots (47) arranged in mutually opposing cam disks (45, 46) and in that a spacer shaft (8) on which is situated said connecting rod bearing (17) is provided with end-side rollers (51) that are held in place in said slots (47).

12. Reciprocating piston engine in accordance with any of the preceding claims, characterized in that said rotor housing (6) has on its exterior cover (23a) a gas exchange/sealing system (23) that is at least partially sealingly adjacent to a cover housing (30) of said reciprocating piston engine (1).

13. Reciprocating piston engine in accordance with claim 12, characterized in that said gas exchange/sealing system (23) has a radially movable and rotatably borne slide element (24) that is under pressure.

14. Reciprocating piston engine in accordance with claim 13, characterized in that said gas exchange/sealing system (23) has sealing strips (36) that are sealingly adapted to said slide element (24) and to the sealing body (35).

15. Reciprocating piston engine in accordance with any of the preceding claims, characterized in that a position-insensitive lubricating system (54) is provided with an oil ring (57) that is borne on rollers (62), rotatable about its own axis 3600.

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32

Ansprche

1. Hubkolbenmaschine

- mit einer Kontur (8), die eine geschlossene Kurvenffthirung bildet,

- mit einem Rotorgehause (6), das drehbar in bezug auf die Kontur (8) angeordnet ist und das dem An- oder Abtrieb der Hubkolbenmaschine dienende Drehmoment ibertrigt,

- mit mindestens einer in dem Rotorgehiuse (6) angeordneten Einheit (la, lb, 1c, 1d), die aus einem Zylinder (9) und einem Kolben (2, 3, 4, 5) besteht, wobei die Wirkungslinie des Kolbens (2, 3, 4, 5) in dem Zylinder (9) in einer Ebene senkrecht zur Drehachse des Rotorgehluses (6) liegt sowie exzentrisch zu der Drehachse des Rotorgehaiuses (6) ausgerichtet und geradlinig ist,

- mit einem Pleuel (15), das starr mit dem Kolben (2, 3, 4, 5) verbunden ist und durch Fihrung entlang der Kontur (8) die durch diese vorgegebene gesteuerte Bewegung an den Kolben (2, 3, 4, 5) tibertrigt,

- dadurch gekennzeichnet, dass mit dem Pleuel (15) ein Ffihrungsteil (19) verbunden ist, das entlang einer gesonderten Ftthrung im Rotorgehiuse (6) beweglich angeordnet ist, wobei der Kolben (2, 3, 4, 5) mit dem Pleuel (15) und das FUhrungsteil (19) jeweils entlang einer Geraden im Rotorgehause (6) eine Hubbewegung ausftihren konnen.

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2. Hubkolbenmaschine nach Anspruch 1, dadurch gekennzeichnet, dass im Bereich der Verbindungsstelle von Pleuel (15) und Fiihrungsteil (19) ein Pleuellager (17) zur Ffthrung an der Kontur (8) ausgebildet ist.

3. Hubkolbenmaschine nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die gesonderte Ftihrung far das Ftthrungsteil (19) eine lineare Ftthrung ist, deren Ldngsachse die Drehachse des Rotorgehluses (6) schneidet.

4. Hubkolbenmaschine nach Anspruch 3, dadurch gekennzeichnet, dass die lineare Filhrung (20) des Fiihrungsteils (19) eine Laufbuchse (20) ist und dass um das Fiihrungsteil (19) ein in Ldngsrichtung der Laufbuchse (20) verschiebbares Wilzlager (21) angeordnet ist.

5. Hubkolbenmaschine nach Anspruch 4, dadurch gekennzeichnet, dass das Wilzlager (21) gegentiber dem FUihrungsteil (19) und der Laufbuchse (20) beweglich ist, wobei ein Austritt des WaIzlagers (21) in Lqngsrichtung des Ftihrungsteils (19) nach auBen durch eine Wegbegrenzung verhindert ist.

6. Hubkolbenmaschine nach Anspruch 4, dadurch gekennzeichnet, dass die

Wegbegrenzung ein im Rotorgehiuse (6) angebrachter Sicherungsring (22) ist.

7. Hubkolbenmaschine nach Anspruch 5 oder 6, dadurch gekennzeichnet, dass das Wilzlager (21) mindestens eben so lang ist wie die Laufbuchse (20).

8. Hubkolbenmaschine nach einem der vorhergehenden Ansprtiche, dadurch gekennzeichnet, dass vier aus Zylinder (9) und Kolben (2, 3, 4, 5) bestehende Einheiten (la, lb, 1c, Id) vorgesehen sind, wobei die Wirklinien der Kolben in der Ebene senkrecht zur Drehachse des Rotors (6) um 90' zueinander versetzt angeordnet sind.

9. Hubkolbenmaschine nach einem der vorhergehenden Anspriche, gekennzeichnet durch eine derartige Ausbildung der Kontur (8), dass bei einem vollstandigen

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34

Umlauf des Rotorgehauses (6) die aus Zylinder (9) und Kolben (2, 3, 4, 5) bestehende Einheit (1 a, 1b, 1c, 1d) zumindest einen Arbeitstakt vollfthrt.

10. Hubkolbenmaschine nach Anspruch 9, gekennzeichnet durch eine derartige Ausbildung der Kontur (8), dass wthrend des Arbeitstaktes der Einheit (1 a, l b, 1c, 1d) der von deren Kolben (2, 3, 4, 5) begrenzte Verbrennungsraum (13) zumindest im Wesentlichen isochor ist.

11. Hubkolbenmaschine nach einem der Anspriche 2 bis 10, dadurch gekennzeichnet, dass die Kontur (8) von einer Hubscheibe (44) sowie von zwei in einander gegentiberliegenden Kurvenscheiben (45, 46) angeordneten verlaufskongruenten Nuten (47) gebildet ist und dass eine Verbindungswelle (8), auf der sich das Pleuellager (17) befindet, mit endseitigen Rollen (51) vorgesehen ist, die in den Nuten (47) aufAnlage gehalten sind.

12. Hubkolbenmaschine nach einem der vorhergehenden AnsprUiche, dadurch gekennzeichnet, dass das Rotorgehaiuse (6) auf seinem AuBenmrnantel (23a) ein Gaswechsel-Dichtsystem (23) aufweist, das an einem Mantelgehiuse (30) der Hubkolbenmaschine (1) zumrnindest teilweise abdichtend anliegt.

13. Hubkolbenmaschine nach Anspruch 12, dadurch gekennzeichnet, dass das Gaswechsel-Dichtsystem (23) ein unter Druck stehendes, radial bewegliches und drehbar gelagertes Gleitelement (24) aufweist.

14. Hubkolbenmaschine nach Anspruch 13, dadurch gekennzeichnet, dass das Gaswechsel-Dichtsystem (23) Dichtleisten (36) aufweist, die dem Gleitelement (24) sowie dem Diehtk6rper (35) dichtend angepaBt sind.

15. Hubkolbenmaschine nach einem der vorhergehenden Ansprtiche, dadurch gekennzeichnet, dass ein lageunabhingiges Schmiersystem (54) mit einem Olring (57) vorgesehen ist, welcher auf Rollen (62) gelagert um seine eigene Achse 3600 drehbar ist.