EP1499799B1 - Rotary piston machine - Google Patents

Abstract

Disclosed is a rotary piston machine (10) comprising a housing (12) which is provided with a cylindrical inner wall (18) and at least one piston (22, 24, 26, 28) which is disposed inside said housing (12) and rotates around a longitudinal central axis (20) of the housing (12) while moving back and forth in a linear manner by means of a control mechanism (40, 58) so as to periodically enlarge and reduce the size of at least one chamber (86, 90, 96, 98, 100, 102) that is associated with the piston. Linear movement of the at least one piston (22, 24, 26, 28) occurs parallel to the longitudinal central axis (20) of the housing (12).

Description

The invention relates to a rotary piston machine, comprising a housing having a cylindrical housing inner wall, with at least one piston arranged in the housing, which can rotate about a longitudinal center axis of the housing, and thereby performs by a control mechanism, a reciprocating linear motion, which serves to periodically increase and decrease at least one chamber associated with the piston.

Such a rotary piston engine is preferably used as an internal combustion engine.

Rotary piston engines generally belong to a type of machinery in which one or more pistons revolve in a housing, wherein the orbital motion of the piston or pistons is usually superimposed on another type of movement around the one or more chambers associated with the piston (s), which are usually the one or more pistons Working chambers for a Carnot cycle process make it possible to increase and decrease in volume periodically.

From the document US-A-4 553 506 For example, a rotary piston machine is known that has a housing that has a cylindrical housing inner wall. In the housing two centrally located with respect to the longitudinal central axis of the housing piston are present, which rotate around the longitudinal central axis of the housing and thereby perform a reciprocating linear motion by a control mechanism, wherein the linear movement of the two pistons is directed in opposite directions. The two pistons each front of a chamber is assigned, which increase periodically in the reciprocating linear movement of the piston and shrink.

A comparable rotary piston machine is from the document US-A-5,351,657 known. Also in this rotary-piston machine, two pistons arranged longitudinally to the longitudinal central axis of the housing are present in a cylindrical housing, which encompass both a reciprocating linear movement parallel to the longitudinal central axis and a circulation movement perform the longitudinal central axis of the housing, wherein the linear movement is derived from the orbital movement by means of a suitable control mechanism.

From the document FR-A-2 546 232 a rotary piston machine is known which has three eccentrically arranged to the longitudinal central axis of the cylindrical housing piston, which rotate together about the longitudinal central axis of the housing and thereby, again controlled by a corresponding control mechanism, perform a reciprocating linear motion parallel to the longitudinal central axis of the housing.

A rotary piston machine with four eccentrically arranged to the longitudinal central axis and output shaft pistons, which perform a reciprocating linear motion in addition to the orbital movement about the longitudinal center axis of the housing, is from the document FR-A-2 079 555 known.

At one of the DE 100 01 962 A1 known rotary piston machine are arranged a plurality of pistons circumferentially distributed about the housing center axis of the housing. The pistons are mounted radially movable in the housing, wherein the control mechanism derives the radially directed reciprocating stroke of the piston from the orbital motion of the piston.

When using the known rotary piston engine as internal combustion engine with internal combustion, the individual working cycles of the intake, compression, expansion and ejection are thus realized by the radially directed reciprocating stroke movement of the individual pistons.

The control mechanism of the known rotary piston machine has a stationary cam piece arranged approximately on the center of the housing, the pistons each having at least one running member on its side facing the housing center axis, with which the pistons are guided along the control cam. The control mechanism is further configured so that each adjacent of the radially movable piston perform an opposite stroke. The pistons of the known rotary piston machine have at their in the direction of rotation of the piston leading and trailing end faces each have a toothing, and between the end faces of each adjacent piston is provided with a toothed mitumlaufende shaft, which meshes with the teeth of the two adjacent end faces of the piston in Intervention is.

A disadvantage of this known rotary piston machine can be seen in the fact that the radially directed linear movement of the pistons takes place alternately in the direction and against the action of the centrifugal force and the effect of the centrifugal force. In this case, the mass distribution with respect to the longitudinal center axis of the housing and thus also the moment of inertia of the piston changes constantly due to the radially directed lifting movement of the individual pistons. In addition, the housing-side housing fixed cam piece, which serves to guide the piston, due to the centrifugal forces and the mechanical coupling of adjacent, oppositely radially moving piston forces forces.

Another type of rotary piston engine is from the WO 98/13583 in which the individual pistons circulating in the housing are designed as swivel pistons which, in the case of their revolving movement, additionally perform rocker-like reciprocating movements in the housing. The control mechanism for controlling the rocker-like reciprocating pivotal movements of the individual pistons corresponds almost identical to that Control mechanism of the aforementioned known rotary piston machine with linearly movable radially pistons.

Even with this oscillating-piston engine, a disadvantage in the in relation to the longitudinal central axis of the housing not optimal mass distribution or in the incomplete cancellation of the resulting centrifugal forces of the individual pistons can be seen.

The invention has for its object to provide a rotary piston machine, in which it is possible that the working chambers for the Carnot cycle can be acted upon with a form, this form is to be generated by the piston in their reciprocating linear motion itself.

According to the invention this object is achieved by a rotary piston machine having a housing having a cylindrical housing inner wall, with at least one piston arranged in the housing, which can rotate about a longitudinal center axis of the housing, and thereby performs a reciprocating linear movement by a control mechanism, serving to periodically increase and decrease at least one of the first chamber associated with the piston, wherein the linear movement of the at least one piston is parallel to the longitudinal center axis of the housing, wherein the piston is arranged eccentrically with respect to the longitudinal central axis of the housing and in the housing at least a further piston surrounding the longitudinal central axis is arranged, to which at least one second chamber is assigned, which lies opposite the first chamber, and which is arranged with respect to the longitudinal central axis of the housing on the side opposite the first piston, wherein the pistons are guided in their linear motion by a rotor rotating around the longitudinal central axis together with the piston, which is axially immovable, and wherein the rotor has a center section lying on the longitudinal center axis of the housing, which the chamber associated with the first piston of the other Piston associated chamber separates, and wherein the first piston and the second piston facing away from the first and the second chamber end face, a third and fourth chamber are assigned, wherein the central portion of the rotor on the sides of serving as a pre-pressure chamber chambers is missing or so formed in that in each case two of the third and fourth chambers serving as a pre-pressure chamber communicate with one another.

In the rotary piston machine according to the invention, the at least one piston executes a linear movement directed parallel to the longitudinal center axis of the housing when it revolves around the longitudinal central axis of the housing. In this way, the at least one piston has no radially directed component of movement. Thereby, the advantage is achieved that the distance between the center of mass of the at least one piston with respect to the longitudinal center axis of the housing, which forms the axis of rotation of the piston, is fixed. As a result, the advantage of improved smoothness of the rotary piston machine is achieved.

Another advantage over from the DE 100 01 962 A1 known rotary piston machine is that the rotary piston engine according to the invention can be configured radially small-sized, since the at least one piston does not have to perform a radial movement or movement with a radial component of movement. The rotary piston machine according to the invention is particularly suitable as internal combustion engine with internal combustion, in which case the at least one chamber then serves as a working chamber for a Carnot cycle in which the working cycles of the intake, compression, expansion and ejection take place.

The plurality of pistons all execute linear movements directed parallel to the longitudinal central axis of the housing when circulating in the housing, as will be described hereinafter with reference to preferred embodiments.

The plurality of pistons all execute linear movements directed parallel to the longitudinal central axis of the housing when circulating in the housing, as will be described hereinafter with reference to preferred embodiments.

The piston is arranged eccentrically with respect to the longitudinal central axis of the housing, and in the housing at least one further, about the longitudinal central axis rotating piston is arranged, which is arranged with respect to the longitudinal center axis of the housing on the side facing away from the first piston.

The Rotationskolbenmaachine according to the invention is therefore realized as at least two-cylindrical internal combustion engine, with the opposite with respect to the longitudinal center axis arrangement of the at least two pistons, which need not necessarily be axially the same height, with an identical design of the piston with respect to the longitudinal center axis axisymmetric Mass distribution can be achieved. The centrifugal forces acting on both pistons advantageously cancel each other out when circulating in the housing. The two Pistons can be arranged so that the linear movement by means of the control mechanism takes place in opposite directions to each other, or the linear movement of the two pistons can be in the same direction.

Furthermore, the at least one piston is guided in its linear movement by a rotor rotating around the longitudinal central axis together with the piston, which is axially immovable.

The provision of a rotor has the advantage that from the rotor, the rotational movement of the at least one piston in the housing can be tapped via an output shaft connected to the rotor, for example. When the rotary piston machine according to the invention is used as an internal combustion engine in a motor vehicle. In this way, the rotational movement can be tapped centrally on the longitudinal center axis of the housing of the rotary piston machine, without complex transmission or countershafts are required. In this way, a conventional reciprocating engine can be simulated with the rotary piston engine according to the invention, but over which the rotary piston engine according to the invention has the considerable advantage that due to the orbital movement of the at least one piston via the rotor, which is axially immovable, the rotational energy can be derived.

In this case, the rotor has a lying on the longitudinal central axis of the housing central portion which separates the first piston associated chamber of the further piston associated chamber.

In this way, the rotor takes over without additional complex design measures and the function of a separation of the at least two chambers, which form, for example. In the case of using the rotary piston machine as an internal combustion engine working chambers for a Carnot cycle.

The central portion of the rotor is absent on the sides of the chambers serving as a pre-pressure chamber, or is designed so that each two of the serving as a pre-pressure chamber chambers communicate with each other.

It is advantageous that the serving as pre-pressure chambers chambers together form a Vordruckkammer with a total volume which is greater, preferably four times as large as the volume of at least one working chamber, whereby the precompressed in the pre-compressed air with an even higher form in the at least one working chamber can be initiated.

Each end face of the at least one piston is associated with a respective chamber, which shrink and enlarge in opposite directions, wherein one chamber can serve as a working chamber for a Carnot cycle and the other chamber as a pre-pressure chamber for generating a form to the working chamber with a form to apply.

It is advantageous that in the case of using the rotary piston engine according to the invention as an internal combustion engine with a self-charging the working chamber without external devices such as a compressor or a Turbocharger and without increasing the installation space of the rotary piston machine is achieved. While the working chamber, for example, in volume decreases, correspondingly increases the pre-pressure chamber, can be sucked into the fresh air. When expanding the working chamber after the ignition of the fuel / air mixture in the pre-pressure chamber previously sucked fresh air is compressed accordingly and can then be pressed under pressure after ejection of the burned fuel / air mixture from the working chamber in this, whereby the fuel / air mixture can be compressed in the next cycle with higher pressure. In particular, with the preferred embodiment of the rotary piston machine with four pistons, a particularly effective self-charging effect can be achieved. In this embodiment, the rotary piston machine according to the invention is particularly suitable as an internal combustion engine for operation with diesel or even biodiesel fuels.

The further piston can be arranged axially opposite the first piston at the same height.

Also in this embodiment, the advantage is achieved that the centrifugal forces of the two pistons can be canceled by their axisymmetric arrangement with respect to the longitudinal central axis against each other. As with the aforementioned embodiment, two chambers can be formed in this arrangement, which are arranged offset by 180 ° to each other about the longitudinal center axis, so that over a full revolution of the piston assembly two full cycles are completed.

In the context of the aforementioned embodiment, it is further preferred if the further piston is firmly connected to the first piston.

It is advantageous that support the two opposite pistons against each other against the forces acting on them during centrifugal centrifugal forces and in this way a surface friction of the piston is turned off the housing.

In a further preferred refinement, at least one further piston, which revolves around the longitudinal central axis and is arranged in a straight-line extension of the first piston, is arranged in the housing.

The advantage of this measure is that a plurality of chambers can be realized in the longitudinal direction of the housing, so that can be realized in this way also a multi-cylinder rotary piston machine.

In this context, it is preferred if the at least one chamber is formed by the space between mutually facing end faces of the first piston and of the further piston.

It is advantageous that add in opposite directions movement of the two pistons, the individual strokes of the two pistons to a total stroke, whereby in the case of using the rotary piston engine according to the invention as an internal combustion engine in the common chamber between the two pistons, the fuel / air mixture with a higher pressure can be compressed.

In a further preferred embodiment, the linear movement of the first piston is directed opposite to the linear movement of the second piston, and the space between the mutually facing end faces of the first piston and of the further piston forms a common chamber.

This measure has the advantage that the rotary piston machine according to the invention is mass-balanced in this way also with respect to the linear movement of the at least two pistons, whereby vibrations of the rotary piston machine are turned off in the longitudinal direction.

In a combination of the aforementioned embodiments, it is particularly preferred if at least four pistons are arranged in the housing, two of which are arranged opposite each other with respect to the longitudinal central axis of the housing axially opposite each other at the same height, and two each arranged in rectilinear extension to each other are.

In this embodiment of the rotary piston machine according to the invention with four pistons, the two axially with respect to the longitudinal center axis of the housing axially opposite each other at the same height arranged piston each have a preferably rigid double piston, the two double pistons are then arranged in an axially rectilinear extension to each other and together in the housing revolve around the longitudinal center axis and execute oppositely directed linear movements. In this embodiment, the one double piston and the other double piston is preferably assigned in each case a separate control mechanism for controlling the reciprocating linear motion when circulating in the housing.

The control mechanism comprises in a preferred embodiment, at least one arranged on the at least one first piston guide member and at least one formed in the housing inner wall cam, along which the guide member runs.

Such a control mechanism has over the control mechanism of the known rotary piston machine has the advantage that it is less susceptible to wear, because it differs from the control mechanism of the known rotary piston machine, which comprises a centrally arranged in the housing curve piece and provided on the piston runners, not the effect of the orbital motion of the piston caused centrifugal forces is subjected. As a guide member is preferably provided on the at least one first piston radially projecting from the housing inner wall side projecting axis on which one or two rollers are arranged, while the control cam is preferably formed as formed in the housing inner wall guide groove, in which engage the rollers and when rolling the piston in the housing unroll.

In connection with one or more of the aforementioned embodiments, according to which the first piston with respect to the longitudinal center axis, a further piston is arranged at the same axial height opposite and the two pistons are fixedly connected to each other, it is further preferred if on the first piston and the further piston is arranged in each case a guide member, wherein both guide members run along the same control cam.

It is advantageous that the center of gravity of the two opposing piston at the same height on the longitudinal center axis, ie the axis of rotation, is what would not be the case if only one of the two pistons a running member would be present. However, the latter embodiment can also be taken into consideration, in which case the piston which has no guide member, for mass balance with respect to the longitudinal central axis may have a corresponding additional mass.

In a further preferred refinement, a side of the at least one piston facing the inside wall of the housing is formed in cross section in the form of a partial circle.

This measure has the advantage that the housing inner wall facing side of the at least one piston is adapted to the circular inner contour of the housing inner wall, whereby a sealing of the piston can be carried out in an advantageously simple manner by circular segment-shaped seals. The side of the at least one piston facing the inner wall of the housing preferably extends over approximately 90 °.

In a first preferred embodiment variant, the admission pressure chamber is connected to the working chamber via a housing-outside line, in which preferably a valve, in particular controllable valve, is arranged.

The controllable valve may, for example, be a solenoid valve which is opened when a maximum admission pressure has been generated in the admission pressure chamber.

As an alternative to the aforementioned embodiment, however, the admission pressure chamber may also be connected to the working chamber directly through the piston, in which case at least one valve, preferably an automatic valve, is arranged in the piston.

The advantage of this measure is that it can be dispensed with a housing-external connection line between the pre-pressure chamber and the working chamber, whereby the rotary piston machine takes up less space. The aforementioned automatic valve may, for example, be a flutter valve.

The rotary piston machine according to the invention can be used as an internal combustion engine or as a compressor.

Further advantages and features will become apparent from the following description and the accompanying drawings.

It is understood that the features mentioned above and those yet to be explained not only in the particular combination given, but also in other combinations or alone, without departing from the scope of the present invention.

Fig. 1

eine perspektivische, teilweise geschnittene Darstellung einer Rotationskolbenmaschine gemäß einem ersten Ausführungsbeispiel in einer ersten Betriebsstellung;

Fig. 2

die Rotationskolbenmaschine in Fig. 1 in einer zweiten Betriebsstellung;

Fig. 3

die Rotationskolbenmaschine in Figuren 1 und 2 in einer dritten Betriebsstellung;

Fig. 4

die Rotationskolbenmaschine in der in Fig. 3 dargestellten Betriebsstellung in einer teilweise aufgebrochenen Darstellung;

Fig. 5

eine perspektivische Darstellung eines Einzelteils der Rotationskolbenmaschine in Figuren 1 bis 4;

Figuren 6a) bis d)

einen Längsschnitt durch die Rotationskolbenmaschine in Figuren 1 bis 4 in vier verschiedenen Betriebsstellungen;

Figuren 7a) bis d)

jeweils einen Schnitt entlang der Linie VII-VII in Figuren 6a) bis d);

Figuren 8a) bis d)

Schnitte entlang der Linien VIII-VIII in Figuren 6a) bis d);

Figuren 9a) und b)

den Figuren 6a) und 6b) entsprechende Längsschnitte einer Rotationskolbenmaschine gemäß einem weiteren Ausführungsbeispiel in zwei Betriebsstellungen;

Figuren 10a) und b)

jeweils einen Schnitt entlang der Linie X-X in Figuren 9a) und b);

Figuren 11a) und b)

jeweils einen Schnitt entlang der Linie XI-XI in Figuren 9a) und b);

Embodiments of the invention are illustrated in the drawings and will be described in more detail with reference to this. Show it:

Fig. 1

a perspective, partially sectioned view of a rotary piston machine according to a first embodiment in a first operating position;

Fig. 2

the rotary piston machine in Fig. 1 in a second operating position;

Fig. 3

the rotary piston machine in FIGS. 1 and 2 in a third operational position;

Fig. 4

the rotary piston machine in the in Fig. 3 shown operating position in a partially broken representation;

Fig. 5

a perspective view of an item of the rotary piston machine in FIGS. 1 to 4 ;

FIGS. 6a) to d)

a longitudinal section through the rotary piston machine in FIGS. 1 to 4 in four different operating positions;

FIGS. 7a) to d)

in each case a section along the line VII-VII in FIGS. 6a to d);

FIGS. 8a) to d)

Sections along the lines VIII-VIII in FIGS. 6a to d);

FIGS. 9a) and b)

the FIGS. 6a) and 6b ) corresponding longitudinal sections of a rotary piston machine according to a further embodiment in two operating positions;

FIGS. 10a) and b)

in each case a section along the line XX in FIGS. 9a) and b) ;

FIGS. 11a) and b)

in each case a section along the line XI-XI in FIGS. 9a) and b) ;

In FIGS. 1 to 8 is a provided with the general reference numeral 10 rotary piston machine according to a first embodiment shown.

The rotary piston engine 10 is used herein as an internal combustion engine.

The rotary piston machine 10 has a housing 12 which has a substantially cylindrically symmetrical basic shape. At its longitudinal ends, the housing 12 is closed by a housing cover 14 and a housing cover 16, but also a different division of the housing 12 may be considered, such as, for example Fig. 6a ).

The housing 12 has a cylindrical housing inner wall 18, which is thus circular in cross section.

A longitudinal central axis 20 forms the cylinder axis of the housing inner wall 18th

In the housing 12 is at least a first piston 22, and in the embodiment shown, a further second piston 24, which in the perspective views only in Fig. 4 to see is another third piston 26 and another fourth piston 28, which also in the perspective view only in Fig. 4 can be seen, arranged.

Of the four pistons 22 to 26, two pistons are firmly connected to a double piston, namely the first piston 22 and the third piston 24, which form a first double piston, and the second piston 26 and the fourth piston 28, the form a second double piston. The first piston 22 is fixedly connected to the third piston 24 via a first connecting piece 30, and the third piston 26 is fixedly connected to the fourth piston 28 via a second connecting piece 32. The connecting pieces 30 and 32 respectively establish a rigid connection between the pistons 22 and 24 or 26 and 28.

The first piston 22 and the further pistons 24 to 28 run together in the housing 12 about the longitudinal central axis 20 according to an arrow 34, so that the longitudinal center axis 20 can also be referred to as a revolving axis.

The first piston 22 and the other pistons 24 to 28 lead when running around the longitudinal central axis 34 of the housing 12 by a later to be described control mechanism reciprocating linear movements, these linear movements are directed parallel to the longitudinal central axis 34, as with a double arrow 36th is indicated.

The four pistons 22 to 28 are each arranged eccentrically with respect to the longitudinal central axis 20 of the housing 12, as shown in the cross-sectional views in FIG FIGS. 7a) to 7d ).

The further second piston 24 and the further fourth piston 28 are the first piston 22 with respect to the longitudinal center axis 20 opposite, that is arranged on the side facing away from the first piston 22 side of the longitudinal central axis 20. In this case, the further second piston 24 is disposed opposite to the first piston 22 at the same axial height, while the other fourth piston 28 is arranged offset axially opposite the first piston 22. The further third piston 26 is arranged in the housing in straight extension to the first piston 22, that is, with respect to the longitudinal center axis 20 in the same circumferential position as the first piston 22. In contrast, the second piston 24 and the fourth piston 28 in the circumferential direction with respect to the first piston 22 and the third piston 26 offset by 180 °.

Since the first piston 22 is fixedly connected to the further second piston 24, the first piston 22 and the second piston 24, when circulating in the housing 12, execute linear movements directed in the same direction parallel to the longitudinal central axis 20. Likewise, the further third piston 26 and the further fourth piston 28 due to their fixed connection by means of the connecting piece 32 when circulating in the housing 12 in the same direction directed linear movements.

In contrast, the relative linear movements between the first piston 22 and the second piston 24 on the one hand and the third piston 26 and the fourth piston 28 on the other hand are directed in opposite directions. In other words, the pistons 22, 24 on the one hand and the pistons 26 and 28 on the other hand move either toward or away from each other. However, all four pistons 22 to 28 do not change their rotational position when revolving about the longitudinal central axis 20 relative to each other.

The four pistons 22 to 28 are formed identical to each other in terms of their geometry and dimensions. Due to the axisymmetric with respect to the longitudinal central axis 20. Arrangement of the four pistons 22 to 28, the centrifugal forces occurring during the rotation of the pistons 22 to 28 around the longitudinal center axis 20 compensate completely. In addition, in the rotary piston machine 10, the inertia occurring during the linear movement of the pistons 22 to 28 also compensates because the first double piston formed from the pistons 22 and 24 is opposite in direction to the second double piston formed from the pistons 26 and 28 in the housing 12 emotional.

As already mentioned, a control mechanism is provided for deriving the linear movement of the individual pistons 22 to 28 from their orbital movement about the longitudinal central axis 20, which in FIGS. 1 to 4 and 6 is provided with the general reference numeral 40, which will be described below only with respect to the piston 22.

The control mechanism 40 comprises a arranged on the first piston guide member 42 and formed in the housing inner wall 18 control cam 44 along which the guide member 42 runs.

The guide member 42 is fixedly connected to the first piston 22 and has a journal 46 and a fixed to the axle 46 first roller 48 and a second roller 50 on. The roller 48 has a smaller outer diameter than the roller 50.

The control cam 44 is in the form of a guide groove 52 formed in the housing inner wall 18. The guide groove 52 in this case has a portion 54 of smaller diameter and a portion 56 of larger inner diameter, corresponding to the outer diameter of the roller 48 and the outer diameter of the roller 50. By providing two rollers 48 and 50 of different diameters, in the corresponding sections 54 and 56 run the guide groove 52, it is ensured that each roller 48 and 50 has only one direction of rotation about the journal 46 when running in the guide groove 52, that is, the roller 48 and the roller 50, which only one side of their respective associated section Abut 54 and 56, during rotation in the guide groove 52 experience no rotation reversal.

The control cam 44 in the form of the guide groove 52 extends completely around the longitudinal center axis 20 and represents a closed control curve, which, in order to derive the linear movement of the pistons 22 to 28 from the orbital motion of the same about the longitudinal central axis 20, a correspondingly curved shape, the approximately has the shape of a circle bent around a diameter. The pitch of the control cam 44 along the longitudinal central axis 20 determines the stroke of the piston 22nd

The second piston 24 is as shown Fig. 6a ), provided with a guide member 42 identically formed guide member on which two rollers are arranged accordingly, wherein the guide member 42 along the same cam 44, that is, in the same guide groove 52 runs. The control mechanism 40 thus constitutes a common control mechanism for the double piston formed from the pistons 22 and 24.

Like also out Fig. 6a ), the rollers 48 and 50 and correspondingly the guide groove 52 may also be conical.

A corresponding control mechanism 58 is provided for the further double piston formed from the pistons 26 and 28, which differs from the control mechanism 40 only in that a control cam 60 with respect to the control cam 44 of the control mechanism 40 is formed mirror-symmetrically with respect to the cross-sectional center plane of the housing 12 ,

The pistons 22 to 28 are guided in their linear movement by a rotor 62, which in Fig. 5 is shown in isolation.

The rotor 62 has a generally cylindrical shape, which is adapted to the inner wall 18 of the housing 12 of the rotary piston machine 10.

The rotor 62 has for receiving the pistons 22 to 28 two 180 ° offset with respect to the longitudinal central axis 20 by 180 ° trough-like recesses 64 and 66 (see, for example. Fig. 8a )), of which in Fig. 5 only the recess 64 can be seen. The opposing walls of the trough-like recesses 64 and 66 are formed part-circular in cross-section. Between the recesses 64 and 66, the rotor 62 has a sole or a central portion 68 which separates the recesses 64 and 66 from each other. In the central portion 68, two slots 70 and 72 are further recessed, through which the connecting pieces 30 and 32 (see. Fig. 4 ). Instead of the elongated holes 70 and 72, the middle section 68 may also have differently shaped openings there, or the central section 68 may be completely absent in this area, ie extend only over a central partial area of the rotor 62 relative to the longitudinal direction.

The rotor 62 is seen in cross-section circular, with the two recesses 64 and 66 extend approximately 90 ° with respect to the longitudinal central axis 20 in the circumferential direction. Likewise, the central portion 68 of the rotor 62 extends at its wide ends about each 90 ° and a quarter of the full circumference.

The central portion 68 of the axially immovable rotor 62, with which the pistons 22 to 28 rotate together, is located centrally on the longitudinal center axis 20 of the housing 12. At the rotor end extensions 74 and 76 are provided, via which the rotor 62 in the housing 12, more precisely, in the housing covers 14 and 16, is rotatably mounted. In the embodiment shown, the shaft extension 74 protrudes with a toothed end piece 78 out of the housing 12, and also protrudes the shaft extension 76 with a toothed end piece 80 from the housing. However, it may also be provided to omit the end piece 80 and to design the housing cover 16 closed over the shaft extension 76. Via the end piece 78 and / or the end piece 80, the rotational movement of the rotor 62 can be tapped as rotational energy, i. the end piece 78 and / or the end piece 80 can serve as an output shaft.

Incidentally, measures, for example. Support rollers may be provided on the rotor 62 to support the rotor 62 against lateral forces in the housing 12 at a large length.

Each of the pistons 22 to 28 has, as described below for the piston 22, a housing inner wall 18 facing side 82 which is formed in cross section in the form of a partial circle, so that each of the pistons 22 to 28 adapted to the outside of the housing inner wall 18 is. The side 82 extends over a circle angle of about 90 °.

A page 82 opposite side 85 of each piston 22 to 28, which faces the longitudinal center axis 20 is also formed in cross-section in the form of a pitch circle whose circle center point of the circle center of the pitch circle spaced, which forms the side 82 of the pistons 22 to 28, respectively. Thus, each piston 22 is approximately almond-shaped or lenticular in cross section.

Each of the pistons 22 is associated with at least one chamber which periodically decreases in volume due to the reciprocating linear movement of the pistons 22 to 28 and increases.

The first piston 22 is assigned to a front side 84, a first chamber 86. The piston 22 is at one of the end face 84 opposite end face 88, a second chamber 90 assigned. The third piston 26 is in turn assigned to one of the end face 84 of the first piston 22 facing end face 92, the chamber 86, so that the chamber 86 is associated with both pistons 22 and 26 together. On one of the end face 92 facing away from the end face 94 of the piston 26 is assigned a further chamber 96. Due to the oppositely directed linear movement of the pistons 22 and 26 relative to each other, the volumes of the chambers 90 and 96 decrease as the volume of the chamber 86 increases and vice versa.

In a corresponding manner, the pistons 24 and 28 associated chambers 98, 100 and 102, which are arranged offset relative to the chambers 86, 90 and 96 with respect to the longitudinal center axis 20 by 180 °.

The chambers 86 and 98 are completely separated from each other by the central portion 68 of the rotor 62. The chamber 86 is separated from the chambers 90 and 96 by means of a seal 104 which seals the piston 22 against the housing inner wall 18 and against the central portion 68 of the rotor 62, and a seal 106, which seals the piston 26 against the housing inner wall 18 and the central portion 68 of the rotor 62, completely separated.

Similarly, the chamber 98 is completely separated from the chambers 100 and 102 via seals 108 and 110 to the pistons 24 and 28, respectively.

In contrast, the chambers 90 and 100 communicate with each other via the slot 70, and also the chambers 96 and 102 communicate with each other via the slot 72. As mentioned above, the slots 70 and 72 may also be otherwise standardized, or the central portion 68 may be absent at these locations, whereby the chambers 90 and 100 as well as 96 and 102 also communicate with each other and each form a double total volume.

In the in FIGS. 1 to 6 illustrated embodiment, the chambers 86 and 98 serve as working chambers for a Carnot cycle, and the chambers 90, 100 and 96, 102 serve as pre-pressure chambers for generating a form, with which the working chambers 86 and 98 can be acted upon.

For this purpose, the chambers 90 and 100 are connected via an opening 104 in the housing 12 and a connecting line 106 with the chambers 86 and 98, depending on which of the chambers 86 or 98 just in the orbital movement of the piston 22 to 28 to the longitudinal central axis 20 facing an inlet opening 108. In the inlet opening 108, a valve 110 is arranged, which is designed as a controllable valve, in particular solenoid valve, 112. The chambers 96 and 102 are correspondingly via an opening 114 and a connecting line 116 with the interposition of the valve 110 with the inlet opening 108 in connection.

The working chambers serving as chambers 86 and 98 is a total of a spark plug 118 for the delivery of spark and an injection nozzle 120 for injecting a fuel, for example. Gasoline, diesel or biodiesel assigned.

According to Fig. 7a ) to d) is assigned in the housing the chambers 86 and 98 nor an outlet port 122 for ejecting the combusted fuel / air mixture.

The serving as pre-pressure chambers chambers 96 and 102 is according to FIGS. 8a ) to d) further associated with a common intake port 124, wherein the likewise serving as pre-pressure chambers chambers 90 and 100, a non-illustrated corresponding intake port in the housing 12 is assigned.

Subsequently, the function of the rotary piston machine 10 based on the FIGS. 6 to 8 described in more detail.

In FIGS. 6a), 7a) and 8a ), the rotary piston machine is shown in a first operating position, the operating position in Fig. 3 respectively. Fig. 4 equivalent. In the chamber 86, just above the spark plug 118, the fuel-air mixture, which is compressed to the maximum, ignited. From chamber 98 just burned fuel-air mixture was completely expelled. The serving as pre-pressure chambers chambers 96, 102 was through the suction port 124, in which a corresponding valve, preferably an automatic valve, for example. A flutter valve can be arranged, completely filled with air. Likewise, the serving as pre-pressure chambers chambers 90 and 100 which a corresponding intake completely filled with fresh air.

Starting from FIGS. 6a), 7a) and 8a ) run the pistons 22 to 28 clockwise about the longitudinal central axis 20 together with the rotor 62 and have to the operating position in Fig. 6b), 7b) and 8b ) (see. Fig. 1 ) rotated by about 45 °. The previously ignited in the chamber 86 fuel / air mixture now expands in the volume-increasing chamber 86, while in the chamber 98 of the pre-pressure chambers 90, 100 and 96, 102, which shrink in volume and thereby the previously introduced fresh air compact, fresh air is forced into it. As in Fig. 6b ), the valve 110 is opened in order to admit the fresh air precompressed from the chambers 90, 100 or 96, 102 serving as admission pressure chambers into the chamber 98. Since the maximum volume of the chambers 90, 96, 100, 102 together is greater than the maximum volume of the chamber 98, namely about four times as large, enters a (pre-) compression of the pressed into the chamber 98 air.

The pistons 22 and 24 meanwhile move according to an arrow 126 parallel to the longitudinal central axis 22, and the pistons 26 and 28 move in the opposite direction according to an arrow 128 parallel to the longitudinal central axis 20. The longitudinal movement of the pistons 22, 24 and 26, 28 is mediated by the control mechanisms 40 and 58, respectively.

After a further rotation of the piston 22 to 28 by 45 ° about the longitudinal central axis 20, the in FIGS. 6c), 7c) and 8c ) (see. Fig. 2 ), in which the chamber 98 has reached its maximum volume and is filled with precompressed fresh air, while the invisible in the drawing opposite chamber 86 also assumes its full volume after complete - expanding the previously ignited fuel / air mixture. In contrast, the chambers 90, 100 and 96, 102 now have their minimum volume.

By a further rotation of the piston 22 to 28 by 45 °, the in Figures 6d), 7d) and 8d reached operating position, in which now the previously introduced into the chamber 98 fresh air is continuously further compressed by the piston 24, 28 according to arrows 130 and 132 in the opposite direction to move toward each other again. In the in Figures 6d), 7d) and 8d ) invisible chamber 86, which now also decreases in volume again because the pistons 22 and 26 also according to the arrows 130, 132 to move toward each other, now the fully expanded fuel-air mixture by reducing the volume of the chamber 86 from the Outlet opening 122 ejected. In the chambers 90, 100 and 96, 102, which now increase in volume again, according to fresh air is sucked from the outside.

After a further rotation of the piston 22 to 28 by 45 ° starting from Figures 6d), 7d) and 8d ) will be back in FIGS. 6a), 7a) and 8a ), but now the pistons 24 and 28 are "up" and the pistons 22 and 26 are "down". In other words, the pistons 22 to 28 until then have a total of 180 ° rotation about the longitudinal central axis 20 completed, and thereby the four power strokes of the inlet, compacting, expanding and expelling were once passed through. Accordingly, in a full revolution of the pistons 22 to 28 by 360 ° about the longitudinal center axis 20 two full cycles completed.

In FIGS. 9a) and b), 10a) and b) and 11a) and b) an embodiment of a rotary piston machine 10 'slightly modified from the previously described embodiment is shown, which differs from the rotary piston machine 10 by the following features.

The pistons 22 'and 24' associated chambers 90 'and 100', which in turn serve as pre-pressure chambers for acting on the chambers 86 'and 98' with a generated in the chambers 90 'and 100' form, and wherein the chambers 90 ' and 100 'in turn communicate with each other, are not connected via housing outside lines to the chamber 86' or 98 ', but directly via the piston 22' and 24 '. For this purpose, the pistons 22 'and 24' are hollow, and in the pistons 22 'and 24' are each a valve 138 is arranged, which is designed as an automatic valve, preferably as a flutter valve.

Accordingly, the pistons 26 'and 28' associated chambers 96 'and 102', which also communicate with each other, directly to the chambers 86 'and 98' in the piston 26 'and 28' existing valves 140 with the chambers 86 'and 98 'connected.

While the valves 138, 140 in Fig. 9a ) are shown in their closed position, wherein the piston 22 'to 28' in their maximum shifted to the center of the housing 12 'position move, the valves 138 and 140 are in Fig. 9b ) in its open position, when the pistons 22 'to 28' move apart in opposite directions and the chambers 90 ', 100' and 96 'and 102' shrink in volume. In this way, the suction-ready chamber 98 'between the pistons 24' and 28 'can be pressurized with precompressed air from the chambers 90', 100 'and 96' and 102 '.

It is understood that in the context of the present invention, further modifications of the rotary piston machine 10, 10 'are possible.

For example. it is conceivable to provide only the pistons 22 and 24 as a double piston in the rotary piston machine 10, while the pistons 26 and 28 may be omitted. In this case, however, the linear movement of the pistons 22 and 24 would not be mass-balanced. On the other hand, only the piston 22 and the piston 28 may be provided, while the pistons 24 and 26 would be omitted and in the rotor 62 corresponding transverse walls for limiting the chambers 86 and 98 are provided. Such an arrangement would in turn lead to a mass-balanced configuration also with respect to the linear movement of the pistons 22 and 28.

Claims (13)

1. A rotary piston machine, comprising a housing (12) which has a cylindrical housing inner wall (18), and at least one piston (22, 26) which is arranged in the housing (12) and which can rotate about a longitudinal mid-axis (20) of the housing (12) and at the same time executes, by means of a control mechanism (40, 58), a to-and-fro linear movement which serves for periodically enlarging and reducing at least one first chamber (86) assigned to the piston (22, 26), the linear movement of the at least one piston (22, 26) taking place parallel to the longitudinal mid-axis of the housing (12), the piston (22, 26) being arranged eccentrically with respect to the longitudinal mid-axis (20) of the housing (12), and the housing (12) having arranged in it at least one further piston (24, 28) which rotates about the longitudinal mid-axis (20) and which is assigned at least one second chamber (98) located opposite the first chamber (86), and which is arranged, with respect to the longitudinal mid-axis (20) of the housing (12), on the side located opposite the first piston (22), the pistons (22-28) being guided in their linear movement by a rotor (62) which rotates jointly with the pistons (22-28) about the longitudinal mid-axis (20) and which is axially immovable, and the rotor (62) having a middle portion (68) which lies on the longitudinal mid-axis (20) of the housing (12) and which separates the chamber (86) assigned to the first piston (22, 26) from the chamber (98) assigned to the further piston (24, 28), and the first piston (22, 26) and the second piston (24, 28) being assigned, on their end face facing away from the first or the second chamber (86, 98) respectively, a third and a fourth chamber (90, 96, 100, 102), wherein the middle portion (68) of the rotor (62) is absent on the side of the chambers (90, 96; 100, 102) serving as boost pressure chambers or is configured such that in each case two of the third and fourth chambers (90, 100; 96, 102) serving as boost pressure chambers communicate with one another.
2. The rotary piston machine of Claim 1, characterized in that the further piston (24) is arranged opposite the first piston (22) at the same height axially.
3. The rotary piston machine of Claim 2, wherein the further piston (24) is firmly connected to the first piston (22).
4. The rotary piston machine of anyone of the preceding claims, wherein the housing (12) has arranged in it at least one further piston (26) which rotates about the longitudinal mid-axis (20) and which is arranged in the rectilinear prolongation of the first piston (22).
5. The rotary piston machine of Claim 4, wherein the at least one first chamber (86) is formed by the space between mutually confronting end faces of the first piston (22) and of the further piston (26).
6. The rotary piston machine of anyone of Claims 1 through 5, wherein the linear movement of the further piston (26) is directed opposite to the linear movement of the first piston (22).
7. The rotary piston machine of anyone of Claims 1 through 6, wherein the housing has arranged in it at least four pistons (22-28), of which in each case two pistons (22, 24; 26, 28) are arranged opposite one another at the same height axially with respect to the longitudinal mid-axis (20) of the housing (12) and in each case two pistons (22, 26; 24, 28) are arranged in the rectilinear prolongation of one another.
8. The rotary piston machine of anyone of the preceding claims, wherein the control mechanism (40, 58) comprises at least one guide member (42) arranged on the at least one piston (22-28) and at least one control cam curve (44, 60) which is formed in the housing inner wall (18) and along which the guide member (42) runs.
9. The rotary piston machine of anyone of Claims 2 through 8, wherein a guide member (42) is arranged in each case on the first piston (22) and the further piston (24) located opposite at the same height axially, the two guide members (42) running along the same control cam curve (44).
10. The rotary piston machine of anyone of the preceding claims, wherein one side of the at least one piston (22-28), the said side facing the housing inner wall (18), is designed in cross section in the form of a part-circle which extends over an angle of circle of preferably about 90°.
11. The rotary piston machine of anyone of the preceding claims, wherein the first and the second chamber (86, 98) serve as working chambers for Carnot cycles.
12. The rotary piston machine of anyone of Claims 1 through 11, wherein the boost pressure chamber is connected to the working chamber via a connecting line (106, 116) which is located on the outside of the housing and in which a valve (110), in particular a controllable valve (102), is preferably arranged.
13. The rotary piston machine of anyone of Claims 1 through 12, wherein the boost pressure chamber is connected to the working chamber directly through the piston (22-28), at least one valve (138, 140), preferably an automatic valve, being arranged in the piston (22-28).

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