EP2954164A1

EP2954164A1 - Rotary piston engine

Info

Publication number: EP2954164A1
Application number: EP14704316.0A
Authority: EP
Inventors: Glenn Rolus Borgward
Original assignee: RB Holding GmbH; Brands and Products IPR Holding GmbH and Co KG
Current assignee: RB Holding GmbH; Brands and Products IPR Holding GmbH and Co KG
Priority date: 2013-02-07
Filing date: 2014-02-07
Publication date: 2015-12-16
Also published as: DE102013002311A1; WO2014122289A1; US20150377025A1

Abstract

The invention relates to a rotary piston engine comprising at least one rotary piston for compressing and/or expanding a working gas in at least one working chamber and to a method for compressing and/or expanding a working gas in a rotary piston engine. The aim of the invention is to improve a known rotary piston engine of the aforementioned type and a method for operating same such that an improved output and an increased efficiency are achieved. According to the invention, this is achieved in that the rotary piston engine comprises at least one rotary piston with at least one rotatably mounted rotational body and at least one sealing portion which can be moved relative to the rotational body for sealing the at least one working chamber. According to a second aspect of the invention, the rotary piston engine comprises a housing which has at least one lubricant channel for supplying lubricant to the rotary piston and/or for removing lubricant from the rotary piston. The third aspect of the invention relates to a method for compressing and/or expanding a working gas in a rotary piston engine, said working gas being compressed by a rotary piston in a first working chamber and transferred into a second working chamber in order to be ignited, wherein the working gas is supplied with fuel in the second working chamber and/or is further compressed.

Description

ROTARY PISTON ENGINE

The invention relates to a rotary piston engine with at least one rotary piston for compression and / or expansion of a working gas in at least one working chamber and a method for compression and / or expansion of a working gas in a rotary piston engine.

A similar rotary piston engine and a method for compression and / or expansion of a working gas in a rotary piston engine is known, for example, from DE 10 201 1 109 966.

Such a rotary piston engine for compression and expansion of a working gas comprises at least one working piston, about its axis of rotation i.d.R. a plurality of working chambers are formed and rotatable, in which the working gas is compressed, optionally ignited and expanded after ignition, wherein the working chambers in the axial direction and / or in the circumferential direction of the working piston can be arranged one behind the other. In addition, such a rotary piston engine i.d.R. at least one auxiliary piston with a complementary to the working piston geometry, which rolls sealingly on the working piston, so that at least one working chamber is formed with variable volume for compression and expansion of the working gas.

In contrast to a reciprocating engine classic design run all the working cycles (suction, compression, ignition, relax) of the rotary piston engine during the rotation of the rotary piston, without the rotary piston changes its direction of movement. Different working cycles can take place simultaneously in different working chambers. The explosion energy of the ignited working gas preferably acts directly in the circumferential direction on the working piston, which also takes over the compression of the working gas. As with an aircraft gas turbine, the explosion energy of the ignited working gas is thus used directly for driving the compressor or for compressing the working gas, so that, in theory, results in a particularly high efficiency of the rotary piston engine.

Known problems of rotary piston engines, however, are the compression losses due to comparatively long gas routing paths and sealing problems of the working chambers in the compression and expansion stage, the thermal expansion of the housing and the rotary piston, in particular by the large friction surfaces and high speeds, the centrifugal forces and inertia of the working gas with adverse effects on the gas flow and the mixing of the air-fuel mixture before ignition, the oil inlet into the working chambers in the operating or idle state, the controllability of the ignition by rapidly rotating piston, especially at different speeds (load changes ). This reduces the efficiency and economic efficiency of the rotary piston engine. For these reasons, the rotary piston engine could not prevail despite the numerous advantages over the reciprocating engines in practice so far.

The invention is therefore based on the object to improve a known rotary piston engine of the above type and a method for its operation to the effect that a better performance and a higher efficiency can be achieved. In this case, the flexibility in the feasibility and the ability to adapt to a wide variety of circumstances and expectations plays a role, in particular in order to meet a wide variety of applications. The focus of development is u. a. the usability of different fuels (gasoline, diesel, hydrogen, etc), as a foreign and as a diesel, the control possibility or adjustability at least in the same manner as the reciprocating engine (gas inlet, ignition timing, gas outlet, gas volume, volume, ignition chamber, etc.), the usability as concurrent engine eg for generators, combined heat and power plants and machine tools, as well as for the propulsion of land, water or air vehicles. The construction should be as simple as possible.

The object of the invention is achieved by individual solutions (aspects) which, taken alone but in particular in their interaction, enable a rotary piston engine and a method for its operation with improved performance and higher efficiency, wherein the individual solutions claimed both individually and in combination become.

According to a first aspect of the invention, the object is achieved by the rotary piston engine according to claim 1 for compressing and / or relaxing a working gas in at least one working chamber comprising at least one rotary piston with at least one rotatably mounted rotary body and at least one relative to the rotary body movable sealing portion for sealing the at least one working chamber. Owing to the thermal expansion of the material in each operating state of the rotary piston engine, sealing gaps between the stationary and rotating parts of the rotary piston engine can be better closed and sealed by means of the sealing section which can be moved relative to the rotary body, so that the pressure and fuel losses in the compressor chamber are reduced. tion and expansion stage and decrease the efficiency and cost of the rotary piston engine increases.

For a better understanding of the described and claimed invention, some terms are clarified in advance:

The terms axial, radial and circumferential direction respectively refer to the axis of rotation of each in question rotary piston. The axial direction is a direction along or parallel to the axis of rotation of the respective rotary piston. In contrast, a radial direction is a direction perpendicular to the said axis of rotation. The circumferential direction runs along the circumference of any circle whose center lies on the axis of rotation.

The first aspect of the invention, as previously mentioned, is primarily concerned with the sealing of the working chambers between the stationary and rotating parts of the rotary piston engine. The term sealing surface referred to in the context of this invention, the surface of a stationary or rotating part of the rotary piston engine, which faces a corresponding surface of a stationary or rotating part of the rotary piston engine - the so-called sealing partner - to prevent leakage of the working gas through the sealing gap between the sealing surfaces , In the present case, there are seals between stationary and rotating parts of the rotary piston engine (working piston or auxiliary piston relative to the housing) as well as seals between rotating parts of the rotary piston engine with each other (working piston against auxiliary piston).

It may be advantageous if the at least one rotary piston fulfills at least one of the following requirements:

The rotary piston is rotatable while maintaining the seal of the at least one working chamber about a rotation axis.

At least one rotary piston is a working piston for compressing and / or relaxing a working gas around whose axis of rotation the at least one working chamber is formed and / or rotated, wherein preferably at least two working chambers are arranged one behind the other in the axial direction and / or in the circumferential direction of the working piston. At least one rotary piston is an auxiliary piston having a geometry complementary to the working piston for sealingly displacing relative to the working piston, preferably to form at least one variable volume working chamber.

However, it may also be useful if the at least one rotational body fulfills at least one of the following requirements:

The rotational body comprises at least one sealing surface which at least temporarily seals the at least one working chamber during the rotational movement, the sealing surface preferably being deflected from the rotational body in the axial direction and / or in the radial direction and / or in the circumferential direction.

The rotary body comprises at least one receptacle for forming the at least one working chamber.

The rotary body comprises an adjustable geometry, so that the volume of at least one receptacle for forming the at least one working chamber is variable.

The rotary body comprises at least two receptacles for forming in each case a working chamber, wherein the receptacles are preferably arranged one behind the other in the axial direction and / or in the circumferential direction, wherein the receptacles are preferably dimensioned differently in the axial direction and / or in the radial direction and / or in the circumferential direction.

The rotary body comprises at least one cavity sealed relative to the at least one working chamber.

However, it can also prove to be practical if the at least one sealing section fulfills at least one of the following requirements:

The sealing portion comprises at least one sealing surface, which preferably deflects in the axial direction and / or in the radial direction and / or in the circumferential direction of the sealing portion, wherein the sealing surface is preferably formed as a rotationally symmetric surface or as a portion thereof, wherein the sealing surface is preferably in the form of a cylinder jacket and / or a cone shell and / or a ball shell or a circular disc or at least a portion thereof.

The sealing section comprises on a sealing surface at least one preferably linear sealing lip, which projects in the direction of a sealing partner, wherein the Sealing lip preferably in the circumferential direction wavy or sinusoidal, wherein the wave-shaped or sinusoidal sealing lip covers a phase angle of at least 180 ° around the circumference of the rotary piston.

The sealing section is arranged at least in sections at an axial and / or radial end of the rotary body, wherein the sealing section preferably engages over the rotary body in the axial direction and extends at least in sections along both axial ends of the rotary body.

The sealing portion is between a first state in which a sealing surface of the sealing portion is flush with or spaced from a sealing surface of the rotating body and / or with a sealing surface of another sealing portion, and a second state in which the sealing surface of the sealing portion in the direction of a sealing partner further protrudes beyond the sealing surface of the rotary body and / or over the sealing surface of another seal portion, reversibly convertible.

The sealing portion is movable along a line in a plane enclosing the axis of rotation of the rotary piston relative to the rotary body, preferably along or parallel to the axis of rotation of the rotary piston and / or radially and / or at an acute angle to the axis of rotation of the rotary piston.

The sealing portion is movable only along a, preferably straight, line relative to the rotational body, while all other movements of the sealing portion are locked relative to the rotational body.

The sealing section is movable while maintaining the sealing of the at least one working chamber relative to at least one further sealing section and / or to the rotary body.

The sealing portion is slidably guided on the rotating body.

The sealing portion seals the at least one working chamber in the axial direction and / or in the radial direction and / or in the circumferential direction.

The sealing portion is resiliently biased relative to the rotational body, wherein the resilient bias, the sealing portion and the rotational body preferably pushes apart or pulls together. The seal portion is adapted to be movable by the centrifugal force upon rotation of the rotary piston, the seal portion preferably being spaced from the rotational axis of the rotary piston by the centrifugal force.

The sealing portion has a chamfer at at least one end, preferably at a front end in the direction of rotation of the rotary piston, in order to facilitate penetration of the sealing portion into a complementary geometry of a sealing partner.

The sealing section is essentially a rotationally symmetrical component or a section thereof, wherein the sealing section is preferably formed in the shape of a circle segment, a ring segment or an arc.

The sealing portion forms an outer edge of the rotary piston.

The sealing portion is fixed in the axial direction and / or in the radial direction and / or in the circumferential direction positively on the rotary body.

The sealing section is made of a heat-resistant material, preferably ceramic.

The sealing portion is made of a ductile material, preferably copper. The sealing portion is made of a porous material.

The sealing portion is made of a material having the same coefficient of thermal expansion as the housing and / or at least one further rotary piston.

At least two sealing portions are arranged in the axial direction and / or in the radial direction and / or circumferentially adjacent and / or overlapping.

At least two sealing sections together form a continuous or closed or self-contained seal.

At least two sealing portions are movable relative to each other while maintaining a continuous or closed or self-contained seal.

At least two sealing portions are identical or symmetrical or complementary to each other. At least two sealing sections seal the at least one working chamber completely in the axial direction and / or in the radial direction and / or in the circumferential direction.

- At least two sealing portions are arranged in pairs on opposite axial ends of the rotating body.

- At least two sealing portions are resiliently biased against each other, wherein the resilient bias, the sealing portions preferably apart pushes or pulls together.

By means of at least one sealing section formed according to the above features, an improved sealing of the working chamber can be ensured in each operating state of the rotary piston engine, wherein the sealing section can be adapted particularly well to the properties of the respective sealing partners with regard to materials and contours.

In addition, it may be useful if the rotary piston engine has a housing which meets at least one of the following requirements:

The housing includes at least one inlet for introducing a working gas into the working chamber.

The housing includes at least one outlet to discharge a working gas from the working chamber.

The housing is at least partially constructed mirror-symmetrical, preferably mirror-symmetrical to a plane which is spanned by the axes of rotation of two rotary pistons.

The housing comprises at least two parts, preferably at least two substantially mirror-symmetrical parts, preferably at least two identical parts, in order to cover the rotary piston on different sides of its circumference.

The housing is substantially in a plane which is spanned by the rotational axes of two rotary pistons, or split in a plane parallel thereto. A housing according to the above features is easy to manufacture, compact and easy to install and, in the case of a required access to the rotating components of the rotary piston engine, also disassembled again.

According to a second aspect of the invention, the object formulated above is achieved by the rotary piston engine according to claim 6, preferably in conjunction with at least one of the preceding embodiments, for compressing and / or relaxing a working gas in at least one working chamber, with a housing and with at least one rotatable in the housing mounted rotary piston, wherein the housing has at least one lubricant channel for supplying lubricant to the rotary piston and / or for removing lubricant from the rotary piston. By means of pressure circulation lubrication via the lubricant channel, a better sealing of the working chamber can be ensured in each operating state of the rotary piston engine.

In an advantageous embodiment of the invention, the lubricant channel fulfills at least one of the following requirements:

The lubricant channel removes the lubricant from the rotary piston into a lubricant reservoir.

The lubricant channel is designed such that the lubricant collects in the lubricant container.

The lubricant channel extends at least in sections, preferably in an arc around the rotary piston and / or around the working chamber.

The lubricant channel is designed so that the lubricant adheres to the lubricant channel wall by adhesion.

The lubricant channel is designed so that the lubricant runs through the weight.

The lubricant channel extends at least partially within and / or au ßerhalb the housing.

The lubricant channel has a smaller radius of curvature in a vertex above the rotary piston than the largest radius of the rotary piston, wherein the lubricant channel below the vertex preferably has a larger radius of curvature than the largest radius of the rotary piston. The lubricant channel has at least one branch.

The lubricant channel comprises at least one lubricant feed line for supplying lubricant to the rotary piston, preferably to at least one bearing point of the rotary piston and / or to at least one sealing surface of the rotary piston.

The lubricant channel is part of a lubricant circuit, preferably a closed lubricant circuit, wherein the lubricant discharged from the rotary piston is preferably cleaned and returned to the rotary piston.

The lubricant channel according to the above features can distribute the required lubricant well over the contact surfaces to be lubricated and reliably dissipate the excess lubricant.

According to another advantageous embodiment of the invention, the lubricant channel has at least one receiving section for receiving lubricant from the rotary piston, wherein the receiving section fulfills at least one of the following requirements:

The receiving section opens to the rotary piston, preferably to at least one bearing point of the rotary piston and / or to at least one sealing surface of the rotary piston.

The receiving portion extends at least in sections in the circumferential direction of the rotary piston.

- The receiving portion is arranged radially outside and axially within the rotary piston, or radially inwardly and axially au ßerhalb the rotary piston.

The receiving portion is formed so as to receive the centrifugal force discharged from the rotary piston lubricant.

The receiving portion includes at least two parallel grooves separated by at least one wall portion, wherein the wall portion preferably tapers or widened in cross section from a proximal end to a distal end, and / or wherein the wall portion is seen in cross section between the proximal end and the distal end is concave, wherein the wall portion preferably has an arrow-shaped profile at the distal end seen in cross section, the tip of which is repelled from the proximal end of the wall portion. The receiving portion comprises at least two parallel grooves, which are preferably deeper than wide.

The receiving portion comprises a reflux barrier, which prevents leakage of the already received lubricant.

The receiving portion is designed to receive a lubricant supplied to the rotary piston by pressure circulation lubrication in the operating state and in the idle state of the rotary piston engine.

According to a third aspect of the invention, the object formulated above is also achieved by the method for compressing and / or relaxing a working gas in a rotary piston engine, preferably in a rotary piston engine according to at least one of the preceding embodiments, wherein the working gas is compressed by a rotary piston in a first working chamber is and is transferred to the ignition in a second working chamber, characterized in that the working gas is applied in the second working chamber with fuel and / or further compressed.

It may be advantageous if the method comprises at least one of the following steps:

- The compressed working gas is transferred by the rotary piston and / or by the housing of the rotary piston engine, preferably radially inwardly, from the first working chamber into the second working chamber.

The fuel is injected into the second working chamber before and / or during and / or after further compression.

The working gas is further compressed in the second working chamber by at least one reciprocating piston, the reciprocating piston preferably being driven pneumatically and / or hydraulically and / or mechanically, preferably by a cam or eccentric shaft coupled to the rotary piston movement, the reciprocating piston and the rotary piston being particularly preferably run at the same speed.

The working gas is already introduced in the compressed state in the first working chamber, wherein the compression is preferably carried out by a turbocharger.

The working gas is brought to the ignition in the second working chamber by applying fuel and / or by further compression. The ignited working gas is transferred by the rotary piston and / or by the housing of the rotary piston engine, preferably radially outward Shen, from the second working chamber into the first working chamber.

The preferred embodiments of the invention will be described below in detail with reference to the figures.

Brief description of the figures

Show it:

Fig. 1 are schematic views of a rotary piston engine according to the invention; In particular, Figure 1 a is a perspective view of a rotary piston engine according to the invention with a partially open housing which is separated in a plane enclosing the axes of rotation of the rotary piston; and Fig. 1 b is a schematic sectional view of a rotary piston engine according to the invention to illustrate the interaction of the individual components.

Fig. 2 are schematic views of the rotary piston of a rotary piston engine according to the invention; in particular Figure 2a is a side view of the rotary piston. FIG. 2b shows the rotary pistons with sealing sections in front view in a first state, in which sealing surfaces of the sealing sections and of the rotary body on the auxiliary piston are flush with one another; FIG. and FIG. 2c shows the upper auxiliary piston with sealing sections in an enlarged detail view and in a front view in a second state, in which the sealing surfaces of the sealing sections on the auxiliary piston protrude further in the axial direction beyond the sealing surfaces of the rotary body.

3 shows schematic views of a rotary piston designed as a working piston of the rotary piston engine according to the invention; in particular, FIG. 3a shows the rotary piston with sealing sections in a side view in a first state, in which sealing surfaces of the sealing section and of the rotary body are flush with one another; 3b shows the rotary piston with sealing sections in side view in a second state, in which the sealing surfaces of the sealing portions project beyond the sealing surfaces of the rotary body in the radial direction.

4 shows schematic views of a rotary piston designed as a working piston of the rotary piston engine according to the invention according to an advantageous variant; in particular Fig. 4a in particular the working piston with sealing sections in side view and an enlarged side view of a detail; 4b shows the working piston with sealing sections in front view in a first state in which sealing surfaces of the sealing section and of the rotary body are flush with one another; and FIG. 4c shows the rotary piston with sealing sections in front view and an enlarged front view of a detail in a second state in which the sealing surfaces of the sealing section protrude beyond the sealing surfaces of the rotary body in the radial direction; FIG. and Fig. 4d is a front view of a rotary piston with a plurality of rows of sealing portions in a first state in an enlarged detail view. various schematic views of a rotary piston engine according to the invention in various steps; in particular Fig. 5a is a schematic sectional view of the rotary piston engine according to the invention for illustrating the power strokes in a reciprocating piston system or in the expansion stage (system A); 5b is a schematic front view of the rotary piston engine according to the invention with exposed rotary piston. 5c shows a schematic sectional view of the rotary piston engine according to the invention for explaining the work cycles in a rotary piston system or in the compression stage (system B); and Figs. 5d-f are simplified and reduced views based on Figs. 5a-c. various schematic views of a rotary piston engine according to the invention in various steps; in particular Fig. 6a is a simplified schematic sectional view of the rotary piston engine according to the invention for explaining the power strokes in the reciprocating system or in the expansion stage (system A). and Fig. 6b is a schematic front view of the rotary piston engine of Fig. 6a for explaining the power strokes in the rotary piston system or in the compression stage (system B). different views of a modification of the rotary piston engine according to the invention of FIG. 6; FIG. 7a and FIG. 7b being based essentially on FIGS. 6a and 6b. schematic views of a rotary piston engine according to the invention with internal Hubkolbensystem to illustrate different drive concepts for the reciprocating piston; In particular, FIG. 8a shows a reciprocating piston system with a pneumatic or hydraulic drive, wherein the reciprocating piston movement is dependent on the rotational movement. supply of the working piston can be decoupled; 8b, a reciprocating piston system with crank drive and connecting rod connection to the axis of rotation of the working piston; and FIG. 8c shows a reciprocating system with cam drive and two end-side ignition chambers. a schematic sectional view of a rotary piston engine according to the invention with internal Hubkolbensystem with cam drive and an end-side ignition chamber, the reciprocating piston is mechanically driven by the camshaft designed as the axis of the working piston. schematic views showing a first chronological series of steps of the inventive method for compression and expansion of a working gas in the rotary piston engine according to the invention according to the eighth embodiment of the invention; 10a shows the rotary piston when closing the gas outlet of the ignition chamber, FIG. 10b shows the reciprocating piston sucking the working gas from system B into the ignition chamber and the rotary piston sucking air into the working chamber of system A; 10c shows the rotary piston when closing the gas inlet of the ignition chamber and when drawing air into the working chamber of system A; and Fig. 10d shows the reciprocating piston when compressing the working gas in the ignition chamber of system B. Schematic views illustrating a second chronological series of steps of the inventive method for compressing and relaxing a working gas in the rotary piston engine according to the invention following the first series; in particular Fig. 1 1 a the reciprocating piston when blocking the gas inlet of the ignition chamber with simultaneous ignition by injection or spark ignition and the rotary piston when blocking the intake of the working chamber of system A; Fig. 1 1 b the rotary piston when opening the gas outlet of the ignition chamber for discharging the working gas in the working chamber and the reciprocating piston when displacing the residual gases from the ignition chamber and blocking the gas reflux into the ignition chamber to avoid pressure on the piston top and to relieve the lifting system (eg via the cam); Fig. 1 1 c the rotary piston when opening the gas inlet of the ignition chamber for shock purging by precompressed air from system A due to the piston shape and when expanding the working gas into and in the rotating working chamber to drive the working axis; and FIG. 1 d shows the rotary piston 4 when the gas outlet is opened to eject the combustion gases. schematic views showing a subsequent to the second series third chronological series of steps of the inventive method for compression and expansion of a working gas in the rotary piston engine according to the invention; in particular Fig. 12a, the rotary piston when closing the gas outlet of the ignition chamber, the exhaust of the combustion gases from the first working chamber and the suction of air into the second working chamber; FIG. 12b shows the reciprocating piston during the aspiration of the working gas into the ignition chamber; FIG. 12c shows the rotary piston when the gas outlet of the first working chamber is blocked, when it is opened to the chamber of the lower auxiliary piston for discharging the residual gases into the housing and when closing the gas inlet of the ignition chamber; and FIG. 12d the reciprocating piston during the compression of the working gas. schematic views of a rotary piston engine according to the invention according to an advantageous embodiment; in particular FIG. 13 a shows a schematic perspective partial view of the rotary piston motor according to the invention with a partially opened housing; 13b is a schematic sectional view of the rotary piston engine according to the invention according to FIG. 13a, perpendicular to the axes of rotation of the rotary pistons; FIG. 13c shows alternative embodiments of receiving sections of a lubricant channel for receiving lubricant; FIG. 13d are schematic views of the course of the lubricant channel and the receiving portion about one of the rotary piston, from which the lubricant is derived; Fig. 13e is a schematic side view of an auxiliary piston formed as a rotary piston during rotation, wherein the discarded by centrifugal force or centrifugal lubricant is shown schematically by drops. schematic views of a rotary piston engine according to the invention according to a further advantageous embodiment; in particular Fig. 14a is a schematic sectional view of the rotary piston engine according to the invention perpendicular to the axes of rotation of the rotary piston in the intended installation position; and Fig. 14b shows the rotary piston engine of Fig. 14a in an inclined position in which the rotary piston engine is inclined relative to the intended installation position about an axis parallel to the axes of rotation by the angle a / 2. schematic views of a rotary piston engine according to the invention according to a further advantageous embodiment of the invention; In particular, FIG. 15 a shows a schematic sectional view of a rotary piston engine according to the invention. right to the axes of rotation of the rotary pistons; and Fig. 15b is a schematic partial sectional view of the rotary piston engine of Fig. 15a taken along the axis of rotation of the upper auxiliary piston to show the course of the lubricant channel. schematic views of a rotary piston engine according to the invention according to yet another advantageous embodiment of the invention; in particular Figure 16a is a schematic perspective partial view of a rotary piston engine according to the invention with a partially open housing. FIG. 16b shows a schematic sectional view of the rotary piston motor according to the invention perpendicular to the axes of rotation of the rotary pistons; FIG. and FIG. 16c shows a schematic partial sectional view of the rotary piston motor from FIG. 16b along the axis of rotation of the upper auxiliary piston to show the course of the lubricant channel.

Detailed Description of the Preferred Embodiments

In the description, the same reference numerals are used for the same features and, as far as possible, dispensed with a repeated description.

The rotary piston engine 1 according to FIG. 1 operates according to the process principle described above for the compression and expansion of a working gas, and comprises a working piston 4, about the axis of rotation 40 working chambers 2 are formed and rotatable to compress the working gas, ignite if necessary and after the Ignite ignition. The working chambers 2 are spaced in the axial direction and in the circumferential direction of the working piston 4 or arranged one behind the other. The working piston 4 comprises a rotatably mounted in the housing 5 rotating body 41 with a plurality of movable sealing portions 42 for sealing the working chambers 2 and two receptacles 43 for forming a respective working chamber 2, which are separated by slide 44. Each of the two auxiliary pistons 3 comprises two rotary bodies 31, 34 rotatably mounted together in the housing 5, on which movable sealing sections 32, 33, 35, 36 are mounted for sealing the working chambers 2, the rotary bodies 31, 34 being tuned to the rolling geometry of the working piston 4 Have Wälzgeometrie to move sealingly relative to the working piston 4 and the housing 5.

The working gas is introduced in a known manner through an inlet (51, see Fig. 8-12) in the working chambers 2 and compressed by rotation of the working piston 4, possibly ignited and relaxed after ignition in the working chambers 2. For use with fuel and for ignition, the working gas can be transferred through a channel (not shown) from the compression stage in the expansion stage. The working gas can also be ignited in one of the working chambers 2.

The housing 5 has a lubricant channel 6 for the supply and removal of lubricant S to and from the upper auxiliary piston 3. This lubricant channel 6 includes, among other receiving portions 60 for receiving the discarded by centrifugal force of the rotary piston 3 lubricant. For pressure circulating lubrication of bearing points and axial sealing surfaces of the rotary piston 3 with lubricant, a plurality of lubricant supply lines 65 (FIG. 1 a) can run through the housing 5. Further details on the lubricant guide will be described later in connection with FIGS. 13 to 16.

FIG. 2 shows schematic views of the rotary pistons 3, 4 of the rotary piston engine 1 according to the invention and in particular illustrates the functioning of the sealing sections 32, 33, 35, 36 and 42. As described above in connection with FIG. 1, each of the two auxiliary pistons 3 comprises of the rotary piston engine 1 according to the invention two rotatably mounted in the housing 5 rotational body 31, 34, wherein on each rotation body 31, 34 movable sealing portions 32, 33, 35, 36 are mounted to seal the working chambers 2. By means of these sealing portions 32, 33, 35, 36, the auxiliary piston 3 can maintain the sealing of the working chamber 2 even with rotation about its axis of rotation 30 and with thermally induced material expansions.

Each rotation body 31, 34 also comprises a cavity 37 (FIG. 2 a) sealed relative to the working chamber 2 and sealing surfaces 31 a / b / c, 34 a, which are in the axial direction, in the radial direction and in the circumferential direction of the rotation body 31, 34, 41 / b / c, which temporarily seal the working chamber 2 during the rotational movement of the rotary body 31, 34.

The two sealing sections 32, 33 on one of the rotary bodies 31 (FIGS. 1 b, 2 b) are symmetrical to one another and are arranged in pairs on opposite axial ends of the rotary body 31, where the sealing sections 32, 33 are toothed and complementary in the circumferential direction Contour contours of the rotating body 31 and can be axially displaced away from the rotary body 31 and to the rotary body 31 while maintaining a continuous seal. The sealing portions 32, 33 are each resiliently biased relative to the rotary body 31, 34, wherein the resilient bias repels each of the sealing portions 32, 33 of the rotary body 31. As is shown by way of example in FIG. 2 a in greater detail, the sealing section 32 comprises at its axial sealing surface 32 b a line-shaped sealing lip 32 d, which extends in the direction the working piston 4 protrudes and runs sinusoidally in the circumferential direction. Due to the wave shape, a so-called. Erosion of the sealing portion 32 is prevented in the sealing partner 4, since the sealing lip does not always cooperate with the sealing partner 4 at the same point, but the contact point meanders in the radial direction. As a result, the wear of the seal portion 32 as well as the abrasion on the working piston 4 can be reduced. Preferably, all sealing portions 32, 33, 35, 36 have such sealing lips 32d. The sealing lips 32d are preferably ridges which protrude beyond the respective sealing surface 32b, but are integrally connected to the respective sealing portion 32 and consist of its material.

The two sealing portions 35, 36 (Fig. 1 b, 2b) of the other rotating body 34, however, are complementary to each other and arranged in pairs at the opposite axial ends of the rotating body 34, wherein the sealing portions 35, 36 intermeshed and intermeshing positively in the circumferential direction and while maintaining a continuous seal axially apart and can be moved against each other. The sealing portions 35, 36 are resiliently biased against each other, wherein the resilient bias urges the sealing portions 35, 36 apart.

The sealing portions 32, 33, 35, 36 include various sealing surfaces 32a / b / c, 33a / b / c, 35a / b / c, 36a / b / c, in the axial direction, in the radial direction, and in the circumferential direction of the respective sealing portion 32, 33, 35, 36 reject. The in the radial direction of the sealing portion 32, 33, 35, 36 repellent sealing surfaces 32a, 33a, 35a, 36a preferably have the shape of a cylinder jacket portion, while in the axial direction of the sealing portion 32, 33, 35, 36 facing sealing surfaces 32b, 33b, 35b, 36b are preferably formed in the form of circular or ring segments.

In order to seal the working chamber 2 in the axial direction, the sealing portions 32, 33, 35, 36 between a first state in which the respective sealing surface 32 b, 33 b, 35 b, 36 b of the sealing portion 32, 33, 35, 36 flush with or at a distance to an adjacent sealing surface 31 b, 34 b of the rotary body 3 closes, and a second state in which the sealing surface 32 b, 33 b, 35 b, 36 b further in the direction of the housing 5 or the working piston 4 as a sealing partner on the sealing surface 31 b, 34 b of the rotating body 31, 34 protrudes reversibly convertible. While maintaining the sealing of the working chamber 2, each sealing portion 32, 33, 35, 36 movable only parallel to the axis of rotation 30 of the rotary piston 3 relative to the rotary body 31, 34, 41, while all other degrees of freedom of movement of the sealing portion 32, 33, 35, 36 relative to the Rotation body 31, 34 are locked and blocked. The movement of the sealing portion 32, 33, 35, 36 relative to the rotary body 31, 34 can compensate for example, increased gap dimensions due to a heat-related material expansion.

The sealing sections 32, 33, 35, 36 have chamfers 35d, 36d at their front end in the direction of rotation, in order to facilitate penetration of the sealing section 32, 33, 35, 36 into a corresponding complementary geometry of the working piston 4 as a sealing partner during rolling.

The sealing portions 32, 33, 35, 36, 42 are preferably made of a heat-resistant material such as ceramic, of a ductile material such as copper or of a porous material, wherein the material of each sealing portion 32, 33, 35, 36 preferably has the same coefficient of thermal expansion as the housing 5 and / or the working piston 4, so that thermally induced material stresses due to different thermal expansion coefficients can be prevented or at least reduced.

As can be seen in FIG. 3, each rotation body 41 comprises a substantially cylindrical middle part 4a and two circular-disk-shaped axial side parts 4b, at the axial end sides of which a plurality of movable sealing sections 42 are mounted for sealing the working chambers 2. The sealing portions 42 are substantially identical and circular segment-shaped or ring-segment-shaped and arranged in two axially adjacent rows, which are offset in the circumferential direction by about half the circumferential length of a sealing portion 42, on the externa ßeren peripheral edge of the working piston 4. The sealing portions 42 are accordingly adjacent in the circumferential direction and arranged overlapping in the axial direction, wherein the sealing portions 42 form a continuous and circumferentially closed, axially end-side seal of the working chamber 2 at both axial ends of the rotating body 41. The sealing portions 42 are relatively movable while maintaining the self-contained seal. By means of these sealing portions 42, the working piston 4 can maintain the sealing of the working chamber 2 even during rotation about its axis of rotation 40.

Radial au ßerhalb the cylindrical central portion 4a and axially within the circular-disk-shaped side parts 4b two receptacles 43 for forming a respective working chamber 2 in the circumferential direction of the rotating body 41 are arranged one behind the other and separated by slide 44 (Fig. 3a / b), wherein the slide 44 a on the Wälzgeometrie the associated auxiliary piston (not shown) have matched Wälzgeometrie or involute geometry to roll sealingly against the auxiliary piston and the housing. The geometry of the rotation body 41 is for example by changing the axial length or by spacing the two axial side parts 4b adjustable so that the volume of the receptacles 43 can be changed to form the working chambers 2. The geometry of the auxiliary piston is then adapted accordingly.

The rotary body 41 comprises sealing surfaces 41 a / b / c, in the axial direction (41 b), in the radial direction (41 a) and in the circumferential direction (41 c) from the rotating body 41 and reject the work chambers 2 formed in the receptacles 43 during Seal the rotational movement of the rotating body 41 to the outside. This is in particular a seal for the working piston 4. The individual sealing portions 42 are movable by the centrifugal force in the radial direction during rotation of the working piston 4 and are increasingly spaced with increasing speed from the axis of rotation 40 of the working piston 4.

The sealing portions 42 are resiliently biased in the direction of the rotation body 41, wherein the resilient bias the sealing portions 42 in the direction of the rotation body 41, i. against the deflection caused by the centrifugal force pulls.

As a result, the increase in efficiency by specially shaped working piston 4 with internal recesses 43 to form the working chambers 2, the centrifugal seal by the radially movable sealing portions 42 on the rotary body 41 of the working piston 4, and the complementarily shaped auxiliary piston 3 with the lateral and in the axial Direction of movable seal portions 32, 33, 35, 36 accomplished on the rotating bodies 31, 34. The shape of the working piston 4 with the work chambers 2 located in the piston volume allows a centrifugal force seal with possibly resiliently biased sealing portions 42, which seals the working piston 4 closed at both axial ends in the circumferential direction with respect to the housing 5. As a result, an axial seal to the housing 5 is no longer needed. A plurality of rows of staggered sealing portions 42 counteract rapid wear due to the greater area than a single row and form a labyrinth seal which makes the working gas harder to escape even as the seal portions 42 translate in the radial direction and therewith gaps between circumferentially adjacent ones Seal sections 42 arise. The working piston 4 has no lateral contact with the housing 5, whereby no frictional heat is generated. In addition, it can expand without being stuck to the housing 5.

The inside auxiliary pistons 3 are mounted with lateral sealing portions 32, 33, 35, 36, so that a lateral seal to the working piston 4 takes place. These sealing portions 32, 33, 35, 36 may be spring-mounted and may also use the centrifugal force, if a component of motion in the radial direction is possible. The contact with the side wall via the sealing portions 32, 33, 35, 36. The rotary body 31, 34 of the auxiliary piston 3 can be formed according to material saving and easier.

In an alternative embodiment according to FIG. 4, a plurality of movable sealing sections 42 for sealing the working chambers 2 are also attached to the two circular-disk-shaped axial side parts 4b of the working piston 4 on the outside. The sealing portions 42 are in turn substantially identical and circular segment-shaped or annular segment-shaped but arranged in only one row on the externa ßeren peripheral edge of the working piston 4. The individual sealing sections 42 are accordingly arranged only in the circumferential direction and not in the axial direction adjacent (FIG. 4b / c). The two sealing portions 42, which overlap a slider 44 in the circumferential direction, are directly connected to each other in the axial direction by a connecting part 42d, wherein the connecting part 42d breaks through the axial side parts 4b of the working piston 4 and the comb of the slider 44 in the radial direction forms (Fig. 4a). This connecting part 42d is deflected in the radial direction with the deflection of the sealing sections 42 caused by centrifugal force, wherein the maximum deflection of the sealing sections 42 in the radial direction by the maximum possible immersion depth of the slider 44 and the connecting part 42d in the complementary geometry of the sealing partner or the auxiliary piston 3 is limited. Thereby, the deflection of the connected via the connecting part 42d sealing portions 42 is automatically regulated, wherein the maximum deflection can be transferred to the other sealing portions.

As the enlarged detail in Fig. 4c shows by way of example, the sealing portion 42 may include at its radial sealing surface 42a a line-shaped sealing lip 42e, which projects in the direction of the housing 5 and extends sinusoidally in the circumferential direction. As a result, even in the case of the radially movable centrifugal seal, the waveform prevents the seal section 42 from being eaten into the sealing partner, since the point of contact of the sealing lip 42e to the housing 5 meanders in the axial direction and thus does not always cover the same points. Consequently, the wear of the seal portion 42 and the abrasion on the housing 5 can be reduced. Preferably, all sealing portions 42 have such sealing lips 42e, wherein the sealing lips 42e of the circumferentially and / or axially adjacent sealing portions 42 are preferably matched to one another such that a circumferentially continuous and self-contained wave pattern results. The sealing lips 42e are formed as ridges of the material of the respective sealing portion 42 and fitted ckig connected to this, to protrude beyond the sealing surface 42a in the direction of the sealing partner 5.

In the following, a variant of the rotary piston engine according to the invention is described with reference to Figures 5 to 12, in which a reciprocating piston 71 with anti-cyclical (non-linear) up and down movement for recompression of compressed by the working piston 4 working gas is used. The reciprocating piston 71 is located in a control console 7 which can be adjusted in the circumferential direction in the housing 5 and which is described in a similar manner in DE 10 201 1 109 966. The control console 7 comprises a cylinder with a reciprocating piston 71 oscillating in the cylinder, at the ends of which two ignition chambers 70 are formed, each of which is filled by an ignition chamber inlet 74 and emptied again by an ignition chamber outlet 74. The working gas contained or generated in the ignition chambers 70 is an air-fuel mixture that is ignited by autoignition or spark ignition, e.g. via a respective spark plug 72, can be made to explode.

The control of the reciprocating piston 71 is effected by a camshaft or the rotation axis 40 of the working piston with a specially shaped cam 75 with or without a connecting rod connection, or by a pneumatic or a hydraulic lifting system (FIGS. 8a to c). The advantages of the embodiment result from the fact that compared to only one auxiliary piston 3 in one revolution, all four work cycles are made possible and the working chamber 2 can be used to flush the ignition chamber 70.

Characteristic of the equipped with the reciprocating piston 71 rotary piston engine are also the shortened Gasführungswege and the high compression ratio, which is achieved by the synergetic interaction of the rotary piston system with the reciprocating system, whereby the advantages of both systems are particularly advantageous. For a closer examination of the method according to the invention, it is expedient to consider the processes and working steps of the two systems A and B, wherein:

System A (Fig. 5a / d, 6a, 7a, 8-12) denotes the reciprocating system, comprising the ignition chamber 70 with adjustable cross-section (volume) and after-compressor (reciprocating piston 71), and

System B (Figures 5c / f, 6b, 7b) designates the rotary piston system comprising the rotating gas charging unit for pressure loading the ignition chamber 70 with working gas in the gas flow direction. The advantages of the Hubkolbensystem, in particular the camshaft, are to be seen in that the ignition chamber 70 may remain closed longer by the reciprocating piston 71 as in a continuous upward and downward movement of a normal crankshaft, so that an unwanted volume expansion, or a running back of the working gas is prevented; the gas inlets 73 of the ignition chamber 70 can be closed and remain so that better control can be achieved; the combustion pressure takes place laterally and does not act on the lifting piston 71, the lifting piston 71 being supported by the cylinder wall, which relieves the lifting system and the drive shaft; and

by the shape of the cam 75, a slow or fast movement, e.g. can be allowed for compression or closing.

The cam 75 can be spring-mounted for the controlled movement in the direction of the axis or guided by a mechanism. The illustrations are merely exemplary in order to show the principle, but alternative reciprocating controls are also possible.

The cam 75 preferably controls the reciprocating piston 71 so that the gas in the cylinder (or in the ignition chamber 70 of the reciprocating piston system) is compressed and subsequently displaced therefrom, with the reciprocating piston 71 remaining in the uppermost position until complete expansion in the working rotary piston 4 took place.

To optimize the combustion performance of the Zündkammerquerschnitt is preferably manually adjustable, for example. With the aid of a screwdriver. The Hubkolbenverdichtungungssystem invention is not limited to a rotary piston engine. The filling of the cylinder can, for example, be taken over by a Wankel engine. Likewise, the reciprocating piston system can also be used for pre-compression of a working gas for a subsequent thermodynamic process in a rotary piston engine.

Outer mixture formation (the fuel is mixed outside the firing chamber 70) may not be useful in rotary piston engines because of the complex gas paths. Internal mixture formation (the fuel is admixed within the ignition chamber 70) is therefore preferred. In the reciprocating piston system according to the invention, for example, it is not necessary to use an auxiliary rotary piston 3 for the active compression of the working gas by the rotating components in addition to the working rotary piston 4. Alone by the downward movement of the reciprocating piston 70, a working gas can be actively sucked into the ignition chamber and compressed by the subsequent upward movement of the reciprocating piston 70.

Since the working rotary piston according to the invention has side parts 4b which bound a working chamber 2 on both sides in the axial direction of the working rotary piston 4, only one radial seal of the working chamber 2 is still significant relative to the housing 5 required. Since the working chamber 2 is already limited by the axial side parts 4b of the working rotary piston 4, eliminates at these points a seal to stationary housing parts. Because the sealing lips in this case are only designed to seal in one direction, complex constructions can be largely prevented. In addition to a lower heating and frictional heat within the rotary piston engine according to the invention thereby also long-term benefits such as reduced wear. Since both the working rotary piston 4 and the auxiliary rotary piston 3 assigned to it have substantially the same circumferential speeds, much lower relative speeds occur between the rotating components than between rotating and stationary components.

The inventive method for compression and expansion of a working gas, which will be described below with reference to FIGS. 5 to 12, provides that the working gas is compressed by the working piston 4 in the first working chamber 2 and for ignition in the second working chamber or Ignition chamber 70 is transferred, wherein the working gas in the second working chamber or ignition chamber 70 is supplied with fuel and / or further compressed.

In this case, for example, air is introduced into the first working chamber 2 in uncompressed state or already in the compressed state as working gas. The compression of the working gas prior to introduction into the first working chamber 2 can, for example, be done by a turbocharger. In the first working chamber 2, the working gas is compressed by the rotation of the working piston 4. The fuel may be injected into the second working chamber or ignition chamber 70 before, during and / or after further compression. The working gas is further compressed in the second working chamber or ignition chamber 70 by the reciprocating piston 71, wherein the reciprocating piston 71 can be pneumatically, hydraulically or mechanically driven as previously explained. Alternative drive concepts for the reciprocating piston 71 are shown in FIGS. 8a to 8c and in FIG. 9 schematics. presented. In a pneumatic or hydraulic reciprocating drive, the reciprocating motion of the rotary piston movement can be decoupled. On the other hand, if the reciprocating piston is mechanically driven by a cam or eccentric shaft coupled to the rotary piston movement, the reciprocating piston 71 and the rotary piston 4 preferably run at the same speed. As a result, the working cycles in the first and second working chambers 2, 70 can be better coordinated with each other.

FIGS. 5e to 5f schematically illustrate the processes in both systems A and B, whereby the following method steps are performed in a total of four cycles with two firings per revolution:

System B:

A sucking the working gas through the gas inlet 51 into the working chamber 2;

B pre-compression of the working gas in the working chamber 2 by rotation of the working piston 4;

C filling the ignition chamber 70; System A:

D sucking the working gas through the ignition chamber inlet 73 into the ignition chamber 70 by lowering the piston 71 and increasing the volume of the ignition chamber 70;

E compressing the gas mixture in the ignition chamber 70 by upward movement of the reciprocating piston 71 and reducing the volume of the ignition chamber 70 (with external mixture formation), possibly in conjunction with the injection of fuel into the ignition chamber 70 (with internal mixture formation);

F ignition of the air-fuel mixture (autoignition or spark ignition by the spark plug 72);

G burning and expanding the working gas from the ignition chamber 70 through the Zündkammerauslass in the working chamber 2; and

H discharging the exhaust gases from the working chamber 2;

System B (when using a turbocharger) I Use of system A emissions

Fig. 6a and 6b illustrate the working cycles in the reciprocating system (system A) and in the rotary piston system (system B). The recompression in system A takes place via a reciprocating piston 71 which oscillates in the ignition chamber 70, the internal mixture formation taking place via fuel injection into the ignition chamber 70. During auto-ignition of the air-fuel mixture, the mixture is compressed until the ignition point is reached, or the fuel injection takes place in the compressed working gas or an already compressed air-fuel mixture until the ignition point is reached. A spark ignition of the air-fuel mixture via the spark plug 72nd

In system B, gas losses due to leaks over the seals are accepted when drawing in the air. Accordingly, the gas charging unit is designed for suction and pre-compression of a larger amount of air. The pre-compressed air volume serves for pressure loading of the ignition chamber.

The compression pressure can be adjusted and influenced that, for example, in system A, the volume of the ignition chamber 70 is changed via the reciprocating piston 71 and / or in system B, the volume of the working chamber 2 by coaxial displacement of the side parts (4b) of the working piston 4 or through Replacement of the working piston 4 is changed, in particular when the rotary body 41 of the working piston 4 is not formed integrally with the axis.

10 to 12 show schematic views for illustrating a chronological sequence of steps of the method according to the invention for compressing and relaxing a working gas in the rotary piston engine according to the invention.

The method has the particular advantage that in the first working chamber formed by the rotary piston large amounts of air can be sucked in and already strongly compressed, without loss of efficiency caused by fuel leakage. The fuel can then be supplied to the already compressed working gas in the closed volume of the second working chamber, so that the risk of fuel leakage is reduced. In this case, a diesel engine can be realized when the working gas is brought to the ignition in the second working chamber by applying fuel and / or by further compression. The subsequent compression in the second working chamber ensures thorough mixing of the air-fuel mixture. Alternatively, the air-fuel mixture can be ignited by a spark plug. To increase the efficiency of the rotary piston engine according to the invention further effective measures can be taken in the field of lubricant guide, which will be described below with reference to Figures 13 to 16.

In an advantageous embodiment according to FIG. 13, the lubricant channel 6 is designed to lead the lubricant S to the upper and lower auxiliary pistons 3 and to discharge them from there into a lubricant reservoir. The lubricant channel 6 extends, as shown in Fig. 13a / b / d, in sections around the upper (and lower) auxiliary piston 3 and around the working chamber 2 around. The lubricant passage 6 is constructed such that the lubricant S dropped by the centrifugal force (FIG. 13e) from the upper and lower auxiliary pistons 3 firstly adheres to the lubricant passage wall by gravity and then to the collecting vessel (not shown) at the bottom of the rotary piston engine 1 by gravity is dissipated. The lubricant channel 6 may be partially within and in sections outside ßerhalb the housing 5 run.

A receiving portion 60 for receiving the centrifugal force-dropped lubricant S extends radially outward and axially within the upper and lower auxiliary pistons 3 in the circumferential direction and opens to the outer surface of the upper and lower auxiliary piston 3. The receiving portion 60 includes, for example, a plurality of parallel grooves 61 which each separated by a wall portion 62 and preferably deeper than they are wide. Exemplary alternative embodiments of such receiving sections 60 are shown in cross section in a plane intersecting the axes of rotation 30, 40 of the rotary pistons 3, 4 in FIG. 13c. By constructive measures can be accomplished in the receiving portion 60, in particular on the upper auxiliary piston 3, a non-return valve, which prevents a backflow of the already absorbed lubricant S from the receiving portion 60. For example, the wall portions 62 of the receiving portion 60 are formed at its distal end in an approximately arrow-shaped, with the arrowhead away from the proximal end. The centrifugal force from the rotary piston 3 dropped lubricant S penetrates through the spaces between the wall portions 62 in the grooves 61 and meets due to the arrowheads to low resistance. A backflow of the lubricant S from the receiving portion 60 is prevented on the one hand, that the lubricant S adheres to the wall of the lubricant channel by adhesion, on the other hand, that the lubricant S in the arrow-shaped fanned ends of the wall sections 62 gets stuck and thus not on the directly below lying auxiliary piston 3 can drip back. By the weight of the lubricant S flows in the lubricant channel 6 along the channel wall down and is discharged in the direction of the collecting container and collected there. 13d shows schematic views of the course of the lubricant channel 6 and the receiving portion 60 relative to the upper auxiliary piston 3. In a vertex 63 of the lubricant channel 6, preferably above the upper auxiliary piston 3 in one of the rotational axes 30, 40 of the rotary piston 3, 4 enclosing Plane is, the radius of curvature of the lubricant channel 6 may be smaller than the largest radius of the upper auxiliary piston 3. By this geometry, the outflow of the lubricant S in the lubricant channel 6 in the direction of the collecting container by the influence of the weight can be favored. On the other hand, below the vertex 63, the radius of curvature of the lubricant channel 6 is preferably greater than the maximum radius of the upper auxiliary piston 3. Alternatively, the lubricant channel 6 may include a larger radius of curvature than the largest radius of the upper auxiliary piston both at the apex 63 and below it.

Fig. 14a shows a schematic sectional view of another advantageous embodiment of the rotary piston engine according to the invention perpendicular to the axes of rotation of the rotary piston 3, 4 in the intended installation position and Fig. 14b, the rotary piston engine 1 of Fig. 14a in an inclined position, in which the rotary piston engine 1 with respect to the intended Installation position about an axis parallel to the axes of rotation is inclined by the angle a / 2. The reflux of the lubricant S accommodated in the lubricant channel 6, in particular to the upper auxiliary piston 3, is stopped by limiting sections 66 which extend at least in sections in the circumferential direction of the upper auxiliary piston 3. Radially outwardly of the restricting portions 66, there are provided oil collecting portions which allow tilting and tilting of the rotary piston engine 1 without the backflow of the oil to the auxiliary piston 3. The limiting sections 66 and Olführwege can be designed such that the rotary piston engine 1 can even be operated "lying" when the axes of the auxiliary piston 3 and the working piston 4 are arranged substantially in a horizontal plane.

In a further advantageous embodiment according to FIG. 15, the lubricant channel 6 comprises a plurality of lubricant feed lines 65a extending through the housing 5 for pressure circulation lubrication of the bearing points 38 and the axial sealing surfaces of the rotary piston 3 with lubricant S. The lubricant feed lines 65a distribute the lubricant S over the axial sealing surfaces of the rotary piston 3. The lubricant S flowing away from the axial sealing surfaces of the rotary piston 3 is collected in channel sections 65b, which extend radially inside and axially outside the upper auxiliary piston 3 and above the bearing points 38, and fed to the bearing points 38 of the rotary piston 3. The effluent S from the bearings 38 of the rotary piston 3 lubricant S is in channel sections 65c, the arcuate radially run inside and axially outside the upper auxiliary piston 3 below the bearings 38, collected. The excess lubricant S is discharged directly via the lubricant channel 6, in which the arcuate channel sections 65b, 65c open via branches 64, into the collecting container, possibly filtered and fed back via the lubricant supply lines 65. As a result, a self-contained lubricant circuit can be accomplished.

In a further advantageous embodiment according to FIG. 16, the lubricant can be conducted directly into the lubricant channel 6 from the axial sealing surfaces of the rotary piston 3 via the upper channel sections 65b-without the detour via the bearing points 38 of the rotary piston 3. This can ensure that only unconsumed lubricant reaches the bearing points 38 of the rotary piston 3. The channel sections 65b, 65c are constructed in such a way that the lubricant S flows under the influence of the weight of the axial sealing surfaces and the bearing points 38 of the rotary piston 3 in the channel sections 65b, 65c and from there via the branches 64 in the lubricant channel 6 and finally in the collection container passes. Although the embodiments of the invention have been described separately from each other, the features disclosed in the embodiments of the invention can also be used in combination with each other.

Advantages of the invention

In summary, the invention discloses various advantageous solutions and embodiments for rotary piston engines 1 and pumps.

In an advantageous embodiment of the invention, the rotary piston engine according to the invention comprises an auxiliary piston 3 with sealing parts or sealing portions 32, 33, 35, 36 for sealing the auxiliary piston 3 relative to the working chambers 2 of the working piston 4. This embodiment follows the basic principle that two laterally on or in the rotary body 31, 34 of the auxiliary piston 3 movably mounted arcuate sealing portions 32, 33, 35, 36 are pressed by spring pressure to the outside of the respective sealing partner, or the housing 5 or the piston 4. The serrated shape is intended to prevent the sealing sections 32, 33, 35, 36 from rotating relative to the rotating bodies 31, 34 of the auxiliary piston 3 and to reduce the slip of the gas. In addition, the sealing portions 32, 33, 35, 36 provide a smaller friction surface with respect to the housing 5 and the working piston 4. About a pressure circulation lubrication, the lateral sealing portions 32, 33, 35, 36 are additionally lubricated. In a further advantageous embodiment of the invention, the rotary piston engine according to the invention comprises a working piston 4 with sealing parts or sealing portions 42 for lateral sealing of the working chambers 2 relative to the housing 5. This embodiment is based on the basic principle that laterally on or in the rotating body 41 of the working piston 4 movably mounted, arcuate sealing portions 42 are pressed by the centrifugal force with rotating working piston 4 against a resilient bias radially outward Shen to the housing 5 or the auxiliary piston 3. Again, a jagged shape of the seal portions 42 can prevent twisting against the rotation body 41 of the power piston 4 and reduce the slip of the gas. If the sealing portions 42 are arranged overlapping in a plurality of rows, the gaps formed in the radial deflection of the sealing portions 42 in the gaps can be covered and closed by the overlapping sealing portions 42 so that even lower pressure losses are achieved.

In a further advantageous embodiment of the invention, the sealing portions 32, 33, 35, 36, 42 are preferably made of materials that provide less wear or a better sliding property than the respective rotary pistons 3, 4, for example copper, ceramics, etc .. Die Sealing portions 32, 33, 35, 36, 42 are preferably only on the Au ßenkante the rotary body 31, 34, 41 attached or formed to seal the working chambers 2 better. Alternatively or additionally, the sealing sections 32, 33, 35, 36, 42 can also cover a lateral surface and / or at least one axial end side of the rotary bodies 31, 34, 41, so that, for example, a type of heat protection is formed with respect to the working chamber 2. In this case, ceramic is suitable as a material. Another possibility is the bevel of the front in the direction of rotation of the sealing portions 32, 33, 35, 36, 42, ie where, for example, the male and female Wälzgeometrien of the auxiliary piston 3 and the working piston 4 meet, so that the male rotary piston 3, 4 does not strike in material expansion or due to displacement on the edge of the female rotary piston 3, 4. This results in the advantages of a better seal to the side walls of the working chambers 2, even with material expansion. The sealing sections 32, 33, 35, 36, 42 can moreover be exchanged more easily and cost-effectively than the rotary pistons 3, 4. The rotary pistons 3, 4 can be made narrower and more flexible in addition to the sealing sections 32, 33, 35, 36, 42 be adapted to certain conditions.

In yet another advantageous embodiment of the invention, the housing 5 of the rotary piston engine according to the invention is designed not only for receiving rotary pistons 3, 4, but in particular for collecting and discharging lubricants S of the rotary piston 3, 4 in a collecting container or an oil pan. The invention uses the centrifugal force of the rotating rotary pistons 3, 4, to drop the existing on the rotary piston 3, 4 lubricants, for example, oil pressure recirculation lubrication, collect and the lubricant channel 6 in the housing behind the piston 4, at least partially around the working piston 4 around, or via drain lines au outside the housing 5 to derive in the oil pan. In the process, a receiving section 60 provided with catching grooves 61 or slots traps oil running down or drips down in the housing 5 in the area of the auxiliary piston 3 and conducts it via the lubricant channel 6 into the oil pan. As a result, the working piston 4 is less contaminated with oil residues and the working chambers 2 in the compression and in the expansion stage before being filled with oil are protected (cf risk of oil shock in the reciprocating piston). Especially with the intended pressure circulation lubrication higher pressures and larger amounts of oil are possible, which allows a more constant and safer lubrication at high speeds.

The receiving portion 60 with Ölfangrillen 61 in the circular arc portion of the housing portion for receiving the auxiliary piston 3 favors the adhesion of the oil by adhesive force and passes the splashing on the housing wall oil controlled on the housing wall along in the sump. This accomplishes an efficient oil drainage system. Traps and / or depressions in the lateral area of the auxiliary piston 3 located above the working piston 4 discharge run-down or dripping oil (e.g., the slide bearing) and pass it to the collection container. As a result, the working piston 4 is less contaminated with oil residues and protected the working chambers 2 in the compression and in the expansion stage before running with oil. Excess oil in a reciprocating engine is the cause of the so-called oil strike and bad combustion. With positive pressure lubrication, higher pressures and larger volumes of oil are possible, allowing more consistent and safer lubrication at high speeds. Since the auxiliary piston 3 does not touch the overlying housing 5, no lubrication is required. This results in fewer problems with friction, thermal expansion and fit. The lubricant channel 6 is designed to control the dripping oil in the rest state as well as in the operating state controlled, and to create a larger receiving area for the spun-off oil.

Further preferred embodiments of the invention result from any combination of the features described in the embodiments. List of Reference Rotary piston engine

working chamber

auxiliary piston

working piston

casing

lubricant channel

control panel

Rotation axis - auxiliary piston

, 34 rotary bodies - auxiliary pistons

a, 34a axial sealing surfaces - auxiliary piston

b, 34b radial sealing surfaces - auxiliary piston

c, 34c Sealing surfaces in circumferential direction - auxiliary piston

, 33 Sealing sections - auxiliary piston

a, 33a radial sealing surfaces - seal section auxiliary piston

b, 33b axial sealing surfaces - seal section auxiliary piston

c, 33c Sealing surfaces in circumferential direction - Sealing section auxiliary piston Sealing lip - Sealing section auxiliary piston

, 36 Sealing sections - auxiliary piston

a, 36a radial sealing surfaces - seal section auxiliary piston

b, 36b axial sealing surfaces - seal section auxiliary piston

c, 36c Sealing surfaces in circumferential direction - Sealing section auxiliary piston, 36d Chamfers - Sealing section auxiliary piston

Cavity - auxiliary piston

Rotary axis - working piston

Rotary body - working piston

a radial sealing surfaces - working piston

b axial sealing surfaces - working piston

c sealing surfaces in the circumferential direction - working piston

Sealing sections - working piston

a radial sealing surfaces - sealing section Arbeitskolbenb axial sealing surfaces - sealing section working piston

c Sealing surfaces in circumferential direction - Sealing section Working piston Connecting section - Sealing section Working piston Sealing lip - Sealing section Working piston

Recording - working piston

Slider - working piston

Gas inlet - housing

Gas outlet - housing

Receiving section - lubricant channel

Groove - lubricant channel

Wall sections - lubricant channel

Vertex - lubricant channel

Junction - lubricant channel

Lubricant supply line - lubricant channel

a Channel sections - lubricant channel

b Channel sections - lubricant channel

c Channel sections - lubricant channel

Limiting section - lubricant channel

ignition chamber

reciprocating

spark plug

Inlet ignition chamber

Outlet ignition chamber

Cam / cam

Claims

Expectations

Rotary piston engine (1) for compressing and/or expanding a working gas in at least one working chamber (2), comprising at least one rotary piston (3, 4) with at least one rotatably mounted rotating body (31, 34) and at least one opposite the rotating body (31, 34 , 41) movable sealing section (32, 33, 35, 36, 42) for sealing the at least one working chamber (2).

Rotary piston engine (1) according to claim 1, characterized in that the at least one rotary piston (3, 4) meets at least one of the following requirements: a. The rotary piston (3, 4) can be rotated about an axis of rotation (30, 40) while maintaining the seal of the at least one working chamber (2). b. At least one rotary piston (3, 4) is a working piston (4) for compressing and/or expanding a working gas, around the axis of rotation (30, 40) of which the at least one working chamber (2) is formed and/or rotates, preferably at least two working chambers

(2) are arranged one behind the other in the axial direction and/or in the circumferential direction of the working piston (4). c. At least one rotary piston (3, 4) is an auxiliary piston

(3), which has a geometry complementary to the working piston (4) in order to roll in a sealing manner relative to the working piston (4), preferably in order to form at least one working chamber (2) with a variable volume.

Rotary piston engine (1) according to at least one of the preceding claims, characterized in that the at least one rotating body (31, 34, 41) meets at least one of the following requirements: a. The rotating body (31, 34, 41) comprises at least one sealing surface (31 a/b/c, 34a/b/c, 41 a/b/c), which at least temporarily seals the at least one working chamber (2) during the rotational movement, wherein the sealing surface (31 a/b/c, 34a/b/c, 41 a/b/c) preferably faces away from the rotating body (31, 34, 41) in the axial direction and/or in the radial direction and/or in the circumferential direction. b. The rotating body (41) comprises at least one receptacle (43) to form the at least one working chamber (2). c. The rotating body (31, 34, 41) has an adjustable geometry so that the volume of at least one receptacle (43) can be changed to form the at least one working chamber (2). d. The rotating body (31, 34, 41) comprises at least two receptacles (43) to each form a working chamber (2), the receptacles (43) preferably being arranged one behind the other in the axial direction and/or in the circumferential direction, the receptacles (43) are preferably dimensioned differently in the axial direction and/or in the radial direction and/or in the circumferential direction. e. The rotating body (31, 34, 41) comprises at least one cavity (37) which is sealed off from the at least one working chamber (2).

4. Rotary piston engine (1) according to at least one of the preceding claims, characterized in that the at least one sealing section (32, 33, 35, 36, 42) meets at least one of the following requirements: a. The sealing section (32, 33, 35, 36, 42) comprises at least one sealing surface (32a/b/c, 33a/b/c, 35a/b/c, 36a/b/c, 42a/b/c), which preferably in the axial direction and / or in the radial direction and / or in the circumferential direction from the sealing section (32, 33, 35, 36, 42), the sealing surface (32a / b / c, 33a / b / c, 35a / b / c, 36a/b/c, 42a/b/c) is preferably designed as a rotationally symmetrical surface or as a section thereof, the sealing surface (32a/b/c, 33a/b/c, 35a/b/c, 36a/b /c, 42a/b/c) preferably has the shape of a cylindrical jacket and/or a conical jacket and/or a spherical jacket or a circular disk or at least a section thereof. b. The sealing section (32, 33, 35, 36, 42) comprises at least one sealing surface (32a/b/c, 33a/b/c, 35a/b/c, 36a/b/c, 42a/b/c). preferably linear sealing lip (32d, 42e) which projects in the direction of a sealing partner (4, 5), the sealing lip (32d, 42e) preferably extending in a wave-shaped or sinusoidal manner in the circumferential direction, the wave-shaped or sinusoidal sealing lip (32d, 42e) extending around the Circumference of the rotary piston covers a phase angle of at least 180 °. c. The sealing section (32, 33, 35, 36, 42) is arranged at least in sections on an axial and/or radial end of the rotating body (31, 34), wherein the sealing section (32, 33, 35, 36, 42) preferably overlaps the rotating body (31, 34) in the axial direction and extends at least in sections along both axial ends of the rotating body (31, 34). d. The sealing section (32, 33, 35, 36, 42) is between a first state in which a sealing surface (32b, 33b, 35b, 36b, 42b) of the sealing section (32, 33, 35, 36, 42) is flush with or at a distance from a sealing surface (31 b, 34 b, 41 b) of the rotating body (3) and / or with a sealing surface of another sealing section (32, 33, 35, 36, 41), and a second state in which the sealing surface (32b, 33b, 35b, 36b, 42b) of the sealing section (32, 33, 35, 36, 42) further in the direction of a sealing partner (4, 5) via the sealing surface (31b, 34b, 41b) of the rotating body (31 , 34, 41) and/or protrudes beyond the sealing surface of another sealing section, can be reversibly transferred. e. The sealing section (32, 33, 35, 36, 42) can be moved along a line in a plane enclosing the axis of rotation (30, 40) of the rotary piston (3, 4) relative to the rotary body (31, 34, 41), preferably along or parallel to the axis of rotation (30, 40) of the rotary piston (3, 4) and/or radially and/or at an acute angle to the axis of rotation (30, 40) of the rotary piston (3, 4). f. The sealing section (32, 33, 35, 36, 42) can only be moved along a preferably straight line relative to the rotating body (31, 34, 41), while all other movements of the sealing section (32, 33, 35, 36, 42 ) are locked relative to the rotating body (31, 34, 41). G. The sealing section (32, 33, 35, 36, 42) is relative to at least one further sealing section (32, 33, 35, 36, 42) and/or to the rotating body (31.) while maintaining the sealing of the at least one working chamber (2). , 34, 41) movable. H. The sealing section (32, 33, 35, 36, 42) is displaceably guided on the rotating body (31, 34, 41). i. The sealing section (32, 33, 35, 36, 42) seals the at least one working chamber (2) in the axial direction and/or in the radial direction and/or in the circumferential direction. j. The sealing section (32, 33, 35, 36, 42) is resiliently prestressed relative to the rotating body (31, 34, 41), the resilient prestressing the sealing section (32, 33, 35, 36, 42) and the rotating body (31, 34, 41) preferably pushes apart or pulls together. k. The sealing section (32, 33, 35, 36, 42) is designed such that it can be moved by the centrifugal force when the rotary piston (3, 4) rotates, the sealing section (32, 33, 35, 36, 42) preferably being moved by the Centrifugal force is spaced from the axis of rotation (30, 40) of the rotary piston (3, 4).

I. The sealing section (32, 33, 35, 36, 42) has a chamfer (35d, 36d) on at least one end, preferably on a front end in the direction of rotation of the rotary piston (3, 4), to prevent penetration of the sealing section (32, 33, 35, 36, 42) into a complementary geometry of a sealing partner (4, 5). m. The sealing section (32, 33, 35, 36, 42) is essentially a rotationally symmetrical component or a section thereof, wherein the sealing section (32, 33, 35, 36, 42) is preferably designed in the shape of a circular segment, ring segment or arcuate. n. The sealing section (32, 33, 35, 36, 42) forms an outer edge of the rotary piston (3, 4). o. The sealing section (32, 33, 35, 36, 42) is positively secured to the rotating body (31, 34, 41) in the axial direction and/or in the radial direction and/or in the circumferential direction. p. The sealing section (32, 33, 35, 36, 42) consists of a heat-resistant material, preferably ceramic. q. The sealing section (32, 33, 35, 36, 42) consists of a ductile material, preferably copper. r. The sealing section (32, 33, 35, 36, 42) consists of a porous material. s. The sealing section (32, 33, 35, 36, 42) consists of a material that has the same coefficient of thermal expansion as the housing (5) and/or at least one further rotary piston (3, 4). t. At least two sealing sections (32, 33, 35, 36, 42) are arranged adjacent and/or overlapping in the axial direction and/or in the radial direction and/or in the circumferential direction. u. At least two sealing sections (32, 33, 35, 36, 42) together form a continuous or closed or self-contained seal. v. At least two sealing sections (32, 33, 35, 36, 42) can be moved relative to one another while maintaining a continuous or closed or self-contained seal. w. At least two sealing sections (32, 33, 35, 36, 42) are identical or symmetrical or complementary to one another. x. At least two sealing sections (32, 33, 35, 36, 42) completely seal the at least one working chamber (2) in the axial direction and/or in the radial direction and/or in the circumferential direction. y. At least two sealing sections (32, 33, 35, 36, 42) are arranged in pairs at opposite axial ends of the rotating body (31, 34, 41). e.g. At least two sealing sections (32, 33, 35, 36, 42) are resiliently prestressed against each other, the resilient prestressing preferably pushing the sealing sections (32, 33, 35, 36, 42) apart or pulling them together.

5. Rotary piston engine (1) according to at least one of the preceding claims, characterized in that the rotary piston engine (1) has a housing (5) which meets at least one of the following requirements: a. The housing (5) comprises at least one inlet to admit a working gas into the working chamber (2). b. The housing (5) comprises at least one outlet for discharging a working gas from the working chamber (2). c. The housing (5) is constructed at least in sections with mirror symmetry, preferably with mirror symmetry to a plane that is defined by the axes of rotation (30, 40) of two rotary pistons (3, 4). d. The housing (5) comprises at least two parts, preferably at least two essentially mirror-symmetrical parts, preferably at least two identical parts, in order to cover the rotary piston (3, 4) on different sides of its circumference. e. The housing (5) is essentially divided in a plane that is spanned by the rotation axes (30, 40) of two rotary pistons (3, 4), or in a plane parallel thereto.

Rotary piston engine (1), preferably according to at least one of the preceding claims, for compressing and/or expanding a working gas in at least one working chamber (2), with a housing (5) and with at least one rotary piston (3) rotatably mounted in the housing (5). 4), characterized in that the housing (5) has at least one lubricant channel (6) for supplying lubricant (S) to the rotary piston (3, 4) and/or for removing lubricant (S) from the rotary piston (3, 4 ) having.

Rotary piston engine (1) according to claim 6, characterized in that the lubricant channel (6) meets at least one of the following requirements: a. The lubricant channel (6) leads the lubricant (S) from the rotary piston (3, 4) into a lubricant container. b. The lubricant channel (6) is designed such that the lubricant (2) collects in the lubricant container. c. The lubricant channel (6) runs at least in sections, preferably in an arc shape, around the rotary piston (3, 4) and/or around the working chamber (2). d. The lubricant channel (6) is constructed in such a way that the lubricant (S) adheres to the lubricant channel wall through adhesion. e. The lubricant channel (6) is designed in such a way that the lubricant (S) flows out due to the force of weight. f. The lubricant channel (6) runs at least in sections inside and/or outside the housing (5). G. The lubricant channel (6) has a smaller radius of curvature in a vertex (63) above the rotary piston (3, 4) than the largest radius of the rotary piston (3, 4), with the lubricant channel (6) below the vertex (63) preferably having one has a larger radius of curvature than the largest radius of the rotary piston (3, 4). H. The lubricant channel (6) has at least one branch (64). i. The lubricant channel (6) comprises at least one lubricant supply line (65) for supplying lubricant (S) to the rotary piston (3, 4), preferably to at least one bearing point (38) of the rotary piston (3, 4) and/or to at least one sealing surface the rotary piston (3, 4). j. The lubricant channel (6) is part of a lubricant circuit, preferably a closed lubricant circuit, wherein the lubricant (S) removed from the rotary piston (3, 4) is preferably cleaned and fed back to the rotary piston (3, 4).

8. Rotary piston engine (1) according to claim 6 or 7, characterized in that the lubricant channel (6) has at least one receiving section (60) for receiving lubricant (S) from the rotary piston (3, 4), the receiving section (60) meets at least one of the following requirements: a. The receiving section (60) opens towards the rotary piston (3), preferably to at least one bearing point (38) of the rotary piston (3, 4) and/or to at least one sealing surface of the rotary piston (3, 4). b. The receiving section (60) runs at least in sections in the circumferential direction of the rotary piston (3, 4). c. The receiving section (60) is arranged radially outside and axially inside the rotary piston (3, 4), or radially inside and axially outside the rotary piston (3, 4). d. The receiving section (60) is designed such that it receives the lubricant thrown off by the rotary piston (3, 4) due to centrifugal force. e. The receiving section (60) comprises at least two parallel grooves (61) which are separated from one another by at least one wall section (62), wherein The wall section (62) preferably tapers or widens from a proximal end to a distal end when viewed in cross-section, and/or wherein the wall section (62) is concave between the proximal end and the distal end when viewed in cross-section, wherein the wall section ( 62) preferably has an arrow-shaped profile at the distal end when viewed in cross section, the tip of which points away from the proximal end of the wall section (62). f. The receiving section (60) comprises at least two parallel grooves (61), which are preferably deeper than they are wide. G. The receiving section (60) includes a non-return valve that prevents the already received lubricant (S) from escaping. H. The receiving section (60) is designed to receive a lubricant (S) supplied to the rotary piston (3) by pressure circulation lubrication in the operating state and in the idle state of the rotary piston motor.

9. A method for compressing and/or expanding a working gas in a rotary piston engine (1), preferably in a rotary piston engine (1) according to at least one of the preceding claims, wherein the working gas passes through a rotary piston (3, 4) in a first working chamber (2). is compressed and transferred to a second working chamber for ignition, characterized in that the working gas in the second working chamber is supplied with fuel and / or further compressed.

10. The method according to claim 9, characterized in that the method comprises at least one of the following steps: a. The compressed working gas is transferred from the first working chamber (2) into the second working chamber through the rotary piston (3, 4) and/or through the housing (5) of the rotary piston motor (1), preferably radially inwards. b. The fuel is injected into the second working chamber before and/or during and/or after further compression. c. The working gas is further compressed in the second working chamber by at least one reciprocating piston, the reciprocating piston preferably being operated pneumatically and/or hydraulically and/or mechanically, preferably by one with the rotary on piston movement coupled cam or eccentric shaft, is driven, with the reciprocating piston and the rotary piston particularly preferably running at the same speed. d. The working gas is already introduced into the first working chamber (2) in the compressed state, the compression preferably taking place by a turbocharger. e. The working gas is ignited in the second working chamber by applying fuel and/or by further compression. f. The ignited working gas is transferred from the second working chamber into the working chamber (2) through the rotary piston (3, 4) and/or through the housing (5) of the rotary piston motor (1), preferably radially outwards.