EP1499799A1

EP1499799A1 - Rotary piston machine

Info

Publication number: EP1499799A1
Application number: EP03722509A
Authority: EP
Inventors: Herbert Hüttlin
Original assignee: Individual
Current assignee: HUETTLIN, HERBERT
Priority date: 2002-04-19
Filing date: 2003-04-17
Publication date: 2005-01-26
Anticipated expiration: 2023-04-17
Also published as: JP2005523400A; EP1355053A1; ES2314198T3; WO2003089769A1; ATE260404T1; DE50200261D1; JP4237068B2; US20050066917A1; ES2213721T3; PT1355053E; DE50310676D1; ATE412113T1; EP1355053B1; DK1355053T3; US6986328B2; EP1499799B1

Abstract

The rotary piston engine (10) has a control mechanism (40,58) whereby each piston while rotating executes a linear movement to periodically increase and decrease the chamber (86,98) allocated to the respective piston. The linear movement of a piston (22) is carried out parallel to the longitudinal center axis (20) of the engine casing, and the piston with regard to this axis is installed eccentrically. At least one additional rotating piston (24-28) is installed on the side opposite the first with regard to the longitudinal center axis of the casing.

Description

Rotary piston engine

The invention relates to a rotary piston machine, with a housing which has a cylindrical housing inner wall, with at least one piston arranged in the housing, which can rotate about a longitudinal central axis of the housing, and thereby executes a reciprocating linear movement by means of a control mechanism which does so serves to periodically enlarge and reduce at least one chamber assigned to the piston. Such a rotary piston machine is known from DE 100 01 962 AI.

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

Rotary piston machines generally belong to a type of machine in which one or more pistons revolve in a housing, wherein the orbital movement of the piston or pistons is usually superimposed on another type of movement, around which one or more chambers associated with the piston or pistons usually form the working chambers for a Carnot cycle, periodically increasing and decreasing in volume.

In the rotary piston machine known from DE 100 01 962 AI, a plurality of pistons are arranged circumferentially distributed around the central axis of the housing. The pistons are mounted so as to be radially movable in the housing, the control mechanism deriving the radially directed reciprocating stroke movement of the pistons from the orbital movement of the pistons.

When using the known rotary piston machine as an internal combustion engine, the individual work cycles of 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 curve piece which is arranged approximately in the center of the housing, the pistons each having at least one running member on their side facing the center axis of the housing, with which the pistons are guided along the control curve. The control mechanism is also designed so that each adjacent one of the radially movable pistons performs an opposite stroke movement. The pistons of the known rotary piston machine each have a toothing on their end faces leading and trailing in the direction of rotation of the pistons, and between the end faces of adjacent pistons there is a co-rotating shaft provided with toothing, which meshes with the teeth of the two adjacent end faces of the pistons Intervention stands.

A disadvantage of this known rotary piston machine can be seen in the fact that the radial linear movement of the pistons takes place alternately in the direction and counter to the action of the centrifugal force and the action of the centrifugal force. Due to the radially directed stroke movement of the individual pistons, the mass distribution with respect to the longitudinal central axis of the housing and thus also the moment of inertia of the pistons changes constantly. In addition, the housing-centered housing-fixed curve piece, which serves to guide the pistons, is subjected to forces due to the centrifugal forces and the mechanical coupling of respectively adjacent, radially moving pistons in opposite directions.

Another type of rotary piston machine is known from WO 98/13583, in which the individual pistons rotating in the housing are designed as pivoting pistons, which additionally perform rocking-like pivoting movements in the housing during their rotational movement. The control mechanism for controlling the rocking back and forth swiveling movements of the individual pistons corresponds almost identically to that Control mechanism of the aforementioned known rotary piston machine with linearly radially movable pistons.

In this swinging piston machine, too, a disadvantage can be seen in the mass distribution which is not optimal with respect to the longitudinal center axis of the housing or in the incomplete cancellation of the resulting centrifugal forces of the individual pistons.

The invention has for its object to provide a new type of rotary piston machine, in which the periodic change in the volume of the at least one chamber is achieved in a different way.

According to the invention, this object is achieved with respect to the rotary piston machine mentioned at the outset in that the linear movement of the at least one piston takes place parallel to the longitudinal center axis of the housing.

In the rotary piston machine according to the invention, the at least one piston executes a linear movement parallel to the longitudinal central axis of the housing when it rotates around the longitudinal central axis of the housing. In this way, the at least one piston has no radially directed movement component. This has the advantage that the distance between the center of gravity of the at least one piston with respect to the longitudinal central axis of the housing, which forms the circumferential axis of the piston, is invariable. This achieves the advantage of improved smooth running of the rotary piston machine.

Another advantage over the known rotary piston machine is that the rotary piston machine according to the invention Machine can be designed radially small, since the at least one piston does not have to execute a radial movement or a movement with a radial movement component. The rotary piston machine according to the invention is particularly suitable as an internal combustion engine, in which case the at least one chamber then serves as a work chamber for a Carnot cycle in which the work cycles of intake, compression, expansion and ejection take place.

It goes without saying that the rotary piston machine according to the invention preferably has more than one piston, the plurality of pistons then all performing linear movements directed parallel to the longitudinal center axis of the housing when rotating in the housing, as will be described hereinafter with reference to preferred configurations.

In a preferred embodiment, the piston is arranged off-center with respect to the longitudinal center axis of the housing, and in the housing at least one further piston is arranged which rotates around the longitudinal center axis and is arranged on the side facing away from the first piston with respect to the longitudinal center axis of the housing.

In this configuration, the rotary piston machine according to the invention can be implemented as an at least two-cylinder internal combustion engine, with the at least two pistons, which are opposite in relation to the longitudinal center axis and which do not necessarily have to be axially at the same height, with one identical configuration with respect to the piston the longitudinal center axis axisymmetric mass distribution can be achieved. The centrifugal forces that affect both pistons cancel each other out advantageously when circulating in the housing. The two pistons can be arranged so that the linear movement takes place in opposite directions to one another by means of the control mechanism, or the linear movement of the two pistons can be in the same direction.

In this context, it is further preferred if the further piston is arranged axially opposite the first piston at the same height.

In this embodiment, too, the advantage is achieved that the centrifugal forces of the two pistons can be offset against one another by their axially symmetrical arrangement with respect to the longitudinal center axis. As with the above-mentioned embodiment, two chambers can be formed in this arrangement, which are arranged offset by 180 ° to one another about the longitudinal central axis, so that two full working cycles are completed over a full revolution of the piston arrangement.

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

The advantage here is that the two opposing pistons are mutually supported against the centrifugal forces acting on them when rotating and in this way a surface friction of the pistons on the housing is switched off.

In a further preferred embodiment, the at least one piston is arranged and runs centrally around the longitudinal central axis around a piston central axis coinciding with the longitudinal central axis in the housing.

In this embodiment, the advantage of a structurally particularly simple embodiment of the rotary piston machine according to the invention is achieved. In this embodiment, centrifugal forces are eliminated from the outset without an additional piston arranged at the same axial height.

In a further preferred embodiment, at least one additional piston which is arranged around the longitudinal center axis and is arranged in a straight extension of the first piston is arranged in the housing.

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

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

The advantage here is that when the two pistons move in opposite directions, the individual strokes of the two pistons add up to an overall stroke, so that when the rotary piston machine according to the invention is used 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 in the opposite direction to the linear movement of the second piston, and the space between the mutually facing end faces of the first piston and the further piston forms a common chamber.

This measure has the advantage that the rotary piston machine according to the invention is in this way also balanced in terms of the linear movement of the at least two pistons, as a result of which vibrations of the rotary piston machine in the longitudinal direction are eliminated.

In a combination of the above-mentioned configurations, it is particularly preferred if at least four pistons are arranged in the housing, two of which are arranged axially at the same height opposite each other with respect to the longitudinal center axis of the housing, and two are each arranged in a linear extension to one another are.

In this embodiment of the rotary piston machine according to the invention with four pistons, the two pistons arranged opposite each other axially at the same height with respect to the longitudinal center axis of the housing each form a preferably rigid double piston, the two double pistons then being arranged in an axially linear extension to one another and together in rotate the housing around the longitudinal central axis and perform linear movements in opposite directions. In this embodiment, the one double piston and the other double piston are preferably each assigned a separate control mechanism for controlling the reciprocating linear movement when rotating in the housing. In a preferred embodiment, the control mechanism comprises at least one guide element arranged on the at least one first piston and at least one control curve formed in the inner wall of the housing, along which the guide element runs.

Such a control mechanism has the advantage over the control mechanism of the known rotary piston machine that it is less susceptible to wear, because, unlike the control mechanism of the known rotary piston machine, which comprises a cam piece arranged centrally in the housing and running members provided on the pistons, it does not have the effect of the the rotational movement of the pistons is subject to centrifugal forces. The at least one first piston is preferably provided with a shaft projecting radially from the side facing the housing inner wall, on which one or two rollers are arranged, while the control cam is preferably designed as a guide groove formed in the housing inner wall, into which the rollers engage and roll in the housing when the piston rotates.

In connection with one or more of the above-mentioned configurations, according to which a further piston is arranged opposite one another at the same axial height with respect to the longitudinal central axis and the two pistons are firmly connected to one another, it is further preferred if on the first piston and a further guide member is arranged in each case, the two guide members running along the same control curve.

It is advantageous here that the center of gravity of the two pistons located at the same height on the longitudinal center telachse, ie the axis of rotation, which would not be the case if only one of the two pistons had a running member. However, the latter embodiment can also be taken into account, in which case that piston which has no guide member can have a corresponding additional mass for mass compensation with respect to the longitudinal center axis.

In a further preferred embodiment, a side of the at least one piston facing the housing inner wall is designed in cross section in the form of a partial circle.

This measure has the advantage that the side facing the housing inner wall of the at least one piston is adapted to the circular inner contour of the housing inner wall, as a result of which the piston can be sealed in an advantageously simple manner by means of seals in the form of circular sections. The side of the at least one piston facing the housing inner wall preferably extends over approximately 90 °.

Furthermore, it is preferred if the at least one piston is guided in its linear movement by a rotor which rotates about the longitudinal central axis together with the piston and is axially immovable.

The provision of a rotor has the advantage that the rotary movement of the at least one piston in the housing can be tapped from the rotor 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 centered on the longitudinal central axis of the housing of the rotary piston machine. can be gripped without the need for complex transmission or countershafts. In this way, a conventional reciprocating piston engine can be simulated with the rotary piston machine according to the invention, compared to which the rotary piston machine according to the invention has the considerable advantage that the rotational energy can be dissipated due to the rotating movement of the at least one piston via the rotor, which is axially immobile.

In preferred configurations, the rotor can be designed as a sleeve or as an axis.

In connection with one of the aforementioned configurations, according to which at least two pistons are arranged opposite one another with respect to the longitudinal central axis, be it at axially the same height or at axially different positions, it is further preferred if the rotor lies on the longitudinal central axis of the housing Has a central section that separates the chamber assigned to the first piston from the chamber assigned to the further piston.

In this way, the rotor also takes over the function of separating the at least two chambers without additional complex construction measures, which, for example, form working chambers for a Carnot cycle when the rotary piston machine is used as an internal combustion engine.

In a further preferred embodiment, each of the two end faces of the at least one piston is assigned a chamber which shrink and enlarge in opposite directions, the one chamber being the working chamber for a Carnot cycle and the other chamber serves as a pre-pressure chamber for generating a pre-pressure in order to apply a pre-pressure to the working chamber.

It is advantageous here that when the rotary piston machine according to the invention is used as an internal combustion engine, the working chamber is self-charged without external devices such as a compressor or a turbocharger and without increasing the installation space of the rotary piston machine. For example, while the working chamber is reduced in volume, the pre-pressure chamber into which fresh air can be drawn increases accordingly. When the working chamber expands after the fuel / air mixture is ignited, the fresh air previously sucked into the pre-pressure chamber is compressed accordingly and can then be pressed into the working chamber under pressure after the burned fuel / air mixture has been expelled, as a result of which the fuel / Air mixture can be compressed with higher pressure in the next cycle. In particular with the configuration of the rotary piston machine with four pistons described above, 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.

In a further preferred embodiment, the central section of the rotor on the side of the chambers serving as the pre-pressure chamber is absent or is designed such that two of the chambers serving as the pre-pressure chamber communicate with one another. It is advantageous here that the chambers serving as pre-pressure chambers together form a pre-pressure chamber with a total volume that is larger, preferably four times as large as the volume of the at least one working chamber, as a result of which the air pre-compressed in the pre-pressure chambers enters the at least an even higher pre-pressure a working chamber can be initiated.

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

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

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

The advantage of this measure is that there is no need for a connecting line on the outside of the housing between the pre-pressure chamber and the working chamber, as a result of which the rotary piston machine takes up less space. The aforementioned automatic valve can, for example, be a flutter valve.

Alternatively or in combination with the aforementioned configuration of the rotary piston machine with at least one pre- pressure chamber and at least one working chamber, however, it is also preferred if the two end faces of the at least one piston are each assigned a chamber which shrink and enlarge in opposite directions, both chambers serving as working chambers for a Carnot cycle.

This measure has the advantage that, for example, two cylinders of a conventional engine can be simulated with only one piston, a further particular advantage being that the expansion of one working chamber after the ignition of the fuel / air mixture, the compression of the other working chamber, who just sucked in the new fuel / air mixture. In one of the preferred configurations mentioned above, according to which the rotary piston machine has a total of four pistons, this configuration can be used, for example, to simulate a conventional six-cylinder engine.

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

Further advantages and features result from the following description and the attached drawing.

It goes without saying that the features mentioned above and those yet to be explained below can be used not only in the combination indicated in each case, but also in other combinations or on their own without departing from the scope of the present invention. Embodiments of the invention are shown in the drawing and are described in more detail below with reference to this. Show it:

Figure 1 is a perspective, partially sectioned illustration of a rotary piston machine according to a first embodiment in a first operating position.

FIG. 2 shows the rotary piston machine in FIG. 1 in a second operating position;

3 shows the rotary piston machine in FIGS. 1 and 2 in a third operating position;

FIG. 4 shows the rotary piston machine in the operating position shown in FIG. 3 in a partially broken representation;

5 shows a perspective illustration of an individual part of the rotary piston machine in FIGS. 1 to 4;

Figures 6a) to d) a longitudinal section through the rotary piston machine in Figures 1 to 4 in four different operating positions;

Figures 7a) to d) each have a section along the line VII-VII in Figures 6a) to d);

Figures 8a) to d) sections along the lines VIII-VIII in Figures 6a) to d); Figures 9a) and b) the longitudinal sections corresponding to Figures 6a) and 6b) of a rotary piston machine according to a further embodiment in two operating positions;

Figures 10a) and b) each have a section along the line X-X in Figures 9a) and b);

Figures 11a) and b) each have a section along the line XI-XI in Figures 9a) and b);

Figures 12a) to d) a longitudinal section corresponding to Figures 6a) to 6d) through a rotary piston machine according to a further embodiment in four different operating positions;

Figures 13a) to d) each have a section along the line XIII-XIII in Figures 12a) to d);

Figures 14a) to d) each have a section along the line XIV-XIV in Figures 12a) to d);

Figures 15a) to d) each have a section along the line XV-XV in Figures 12a) to d);

1 to 8 show a rotary piston machine provided with the general reference number 10 according to a first exemplary embodiment.

The rotary piston machine 10 is used here as an internal combustion engine. The rotary piston machine 10 has a housing 12 which has an essentially cylinder-symmetrical basic shape. At its longitudinal ends, the housing 12 is closed by a housing cover 14 and a housing cover 16, although a different division of the housing 12 can also be considered, as can be seen, for example, from FIG. 6a).

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

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

In the housing 12 there is at least one first piston 22, and in the exemplary embodiment shown there are a further second piston 24, which can only be seen in the perspective representations in FIG. 4, a further third piston 26 and a further fourth piston 28, the can also be seen in the perspective view only in FIG. 4.

Of the four pistons 22 to 26, two pistons are firmly connected to each other to form a double piston, namely these are 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 each produce 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 in the housing 12 together around the longitudinal central axis 20 according to an arrow 34, so that the longitudinal central axis 20 can also be referred to as the circumferential axis.

The first piston 22 and the further pistons 24 to 28 perform reciprocating linear movements when rotating around the central longitudinal axis 34 of the housing 12 by a control mechanism to be described later, these linear movements being directed parallel to the central longitudinal axis 34, as with a double arrow 36 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 can be seen from the cross-sectional representations in FIGS. 7a) to 7d).

The further second piston 24 and the further fourth piston 28 are located opposite the first piston 22 with respect to the longitudinal central axis 20, ie on the side of the longitudinal central axis 20 facing away from the first piston 22. The further second piston 24 is arranged opposite the first piston 22 at the same axial height, while the further fourth piston 28 is arranged axially offset opposite the first piston 22. The further third piston 26 is arranged in the housing in a straight extension to the first piston 22, ie is in the same circumferential position as the first piston 22 with respect to the longitudinal central axis 20. In contrast, the second piston 24 and the fourth piston 28 are circumferential - Direction with respect to the first piston 22 and the third piston 26 arranged offset by 180 °. Since the first piston 22 is firmly connected to the further second piston 24, the first piston 22 and the second piston 24 perform linear movements in the same direction parallel to the longitudinal central axis 20 when rotating in the housing 12. Likewise, the further third piston 26 and the further fourth piston 28 perform linear movements in the same direction due to their fixed connection by means of the connecting piece 32 when rotating in the housing 12.

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, pistons 22, 24 on the one hand and pistons 26 and 28 on the other hand either move towards or away from each other. However, all four pistons 22 to 28 do not change their rotational position relative to one another when rotating around the longitudinal central axis 20.

The four pistons 22 to 28 are identical to one another in terms of their geometry and dimensions. Because of the 20 axisymmetric with respect to the longitudinal central axis. The arrangement of the four pistons 22 to 28 completely compensate for the centrifugal forces which occur when the pistons 22 to 28 rotate around the longitudinal central axis 20. In addition, the inertia occurring during the linear movement of the pistons 22 to 28 is also compensated for in the rotary piston machine 10 because the first double piston formed from the pistons 22 and 24 is linearly opposed 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 is provided in FIGS. 1 to 4 and 6 with the general reference numeral 40, which is subsequently only referred to the piston 22 is described.

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

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

The control cam 44 is designed in the form of a guide groove 52 formed in the housing inner wall 18. The guide groove 52 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, which are in the corresponding portions 54 and 56 the guide groove 52 run, 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, that the roller 48 and the roller 50, respectively, only on one side of their respective assigned section 54 or 56 are in contact, do not experience any reversal of rotation in the guide groove 52.

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

The second piston 24, as can be seen from Fig. 6a), is equipped with a guide member which is identical to the guide member 42 and on which two rollers are arranged accordingly, the guide member 42 being along the same cam 44, i.e. in the same guide groove 52, runs. The control mechanism 40 thus represents a common control mechanism for the double piston formed from the pistons 22 and 24.

As can also be seen from FIG. 6a), the rollers 48 and 50 and correspondingly the guide groove 52 can 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 curve 60 is mirror-symmetrical with respect to the control curve 44 of the control mechanism 40 with respect to the central cross-sectional plane of the housing 12 , The pistons 22 to 28 are guided in their linear movement by a rotor 62, which is shown in isolation in FIG. 5.

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

The rotor 62 has two trough-like recesses 64 and 66 (see, for example, FIG. 8a) offset 180 ° with respect to the longitudinal central axis 20 (see, for example, FIG. 8a)), of which only the recess 64 in FIG. 5 you can see. The mutually opposite walls of the trough-like recesses 64 and 66 have a partially circular cross section. Between the recesses 64 and 66, the rotor 62 has a sole or a central section 68 which separates the recesses 64 and 66 from one another. In the middle section 68, two elongated holes 70 and 72 are also recessed, through which the connecting pieces 30 and 32 (see FIG. 4) extend. Instead of the elongated holes 70 and 72, the central section 68 can also have differently shaped openings there, or the central section 68 can be completely absent in this area, i.e. extend with respect to the longitudinal direction of the rotor 62 only over a central portion of the same.

The rotor 62 is circular in cross section, the two recesses 64 and 66 extending approximately over 90 ° with respect to the longitudinal central axis 20 in the circumferential direction. Likewise, the central section 68 of the rotor 62 extends at its broad ends approximately over 90 ° or a quarter of the full circumference. The central section 68 of the axially immovable rotor 62, with which the pistons 22 to 28 rotate together, lies centrally on the longitudinal central axis 20 of the housing 12. At the end of the rotor, shaft 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 exemplary embodiment shown, the shaft extension 74 projects from the housing 12 with a toothed end piece 78, and likewise the shaft extension 76 projects from the housing with a toothed end piece 80. However, it can also be provided that the end piece 80 is omitted and that the housing cover 16 is made closed over the shaft extension 76. The orbital movement of the rotor 62 can be tapped as rotational energy via the end piece 78 and / or the end piece 80, ie the end piece 78 and / or the end piece 80 can serve as an output shaft.

In addition, measures, for example support rollers, can be provided on the rotor 62 in order to support the rotor 62 against lateral forces in the housing 12 in the case of a large overall length.

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

A side 85 of each piston 22 to 28 facing away from the side 82 and facing the longitudinal central axis 20 is likewise designed in cross section in the form of a partial circle, the center of the circle of which is from the center of the circle of the partial circle is spaced, which forms the side 82 of the pistons 22 to 28, respectively. Each piston 22 is thus approximately almond-shaped or lenticular in cross-section.

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

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

Correspondingly, the pistons 24 and 28 are assigned chambers 98, 100 and 102, which are arranged offset by 180 ° with respect to the chambers 86, 90 and 96 with respect to the longitudinal central axis 20.

The chambers 86 and 98 are completely separated from one another by the central section 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 section 68 of the rotor 62, and a seal 106, which seals the piston 26 against the housing inner wall 18 and the central section 68 of the rotor 62, completely separated.

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

In contrast, the chambers 90 and 100 communicate with one another via the elongated hole 70, and the chambers 96 and 102 also communicate with one another via the elongated hole 72, which, however, can also be modified in accordance with an embodiment to be described later in that the chambers 90 and 100 or 96 and 102 do not communicate with each other. As already mentioned above, the elongated holes 70 and 72 can also be shaped differently or the central section 68 can be missing at these points, as a result of which the chambers 90 and 100 as well as 96 and 102 likewise communicate with one another and each form a double total volume.

In the exemplary embodiment illustrated in FIGS. 1 to 6, 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 pre-pressure with which the working chambers 86 and 98 act can be.

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

The chambers 86 and 98 serving as working chambers are assigned a total of one spark plug 118 for emitting ignition sparks and one injection nozzle 120 for injecting a fuel, for example gasoline, diesel or biodiesel.

According to FIGS. 7a) to d), the chambers 86 and 98 in the housing are also assigned an outlet opening 122 for ejecting the combusted fuel / air mixture.

According to FIGS. 8a) to d), the chambers 96 and 102 serving as pre-pressure chambers are also assigned a common suction opening 124, wherein the corresponding suction opening in the housing 12 is also assigned to the chambers 90 and 100 also serving as pre-pressure chambers.

The function of the rotary piston machine 10 will now be described in more detail with reference to FIGS. 6 to 8.

FIGS. 6a), 7a) and 8a) show the rotary piston machine in a first operating position, which corresponds to the operating position in FIGS. 3 and 4, respectively. In the chamber 86, the fuel-air mixture, which is maximally compressed, is ignited via the spark plug 118. The combusted fuel-air mixture has just been completely ejected from the chamber 98. The chambers 96, 102 serving as pre-pressure chambers were through the suction opening 124, in which a corresponding valve, preferably an automatic valve, for example a flap valve, can be arranged completely filled with air. Likewise, the chambers 90 and 100 serving as pre-pressure chambers were completely filled with fresh air through a corresponding suction opening.

Starting from FIGS. 6a), 7a) and 8a), the pistons 22 to 28 rotate clockwise around the longitudinal central axis 20 together with the rotor 62 and have become the operating position in FIGS. 6b), 7b) and 8b) (cf. 1) rotated by about 45 °. The fuel / air mixture previously ignited in the chamber 86 now expands in the volume-increasing chamber 86, while in the chamber 98 from the pre-pressure chambers 90, 100 and 96, 102, which decrease in volume and thereby the fresh air previously introduced compress, fresh air is pressed in. As shown in FIG. 6 b), the valve 110 is opened in order to admit the fresh air pre-compressed from the chambers 90, 100 and 96, 102 serving as pre-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 approximately four times as large, (pre) compression of the air pressed into the chamber 98 occurs.

The pistons 22 and 24 meanwhile move parallel to the longitudinal central axis 22 according to an arrow 126, 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, respectively mediated by the control mechanisms 40 and 58, respectively. After a further rotation of the pistons 22 to 28 by 45 ° about the longitudinal central axis 20, the operating position shown in FIGS. 6c), 7c) and 8c) (see FIG. 2) is reached, in which the chamber 98 has reached its maximum volume and is filled with pre-compressed fresh air, while the opposite chamber 86, which is not visible in the drawing, likewise assumes its largest volume after the previously ignited fuel / air mixture has completely expanded. In contrast, the chambers 90, 100 and 96, 102 now have their minimum volume.

By a further rotation of the pistons 22 to 28 by 45 °, the operating position reached in FIGS. 6d), 7d) and 8d) is reached, in which the fresh air previously admitted into the chamber 98 is continuously compressed further by the pistons 24, 28 according to arrows 130 and 132 to move towards each other again in the opposite direction. In the chamber 86, which is not visible in FIGS. 6d), 7d) and 8d) and which now also decreases in volume again, because the pistons 22 and 26 also move towards one another in accordance with the arrows 130, 132, the fully expanded fuel now becomes Air mixture ejected from the outlet opening 122 by reducing the volume of the chamber 86. Corresponding fresh air is sucked in from the outside into the chambers 90, 100 and 96, 102, which are now increasing in volume again.

After a further rotation of the pistons 22 to 28 by 45 °, starting from FIGS. 6d), 7d) and 8d), the state shown in FIGS. 6a), 7a) and 8a) is reached again, but now the pistons 24 and 28 "above "and the pistons 22 and 26 are" below ". In other words, the pistons 22 to 28 have previously rotated a total of 180 ° about the longitudinal center axis. se 20 completed, and the four work cycles of intake, compression, expansion and ejection were run through once. Accordingly, two full working cycles are completed with a full rotation of the pistons 22 to 28 through 360 ° about the longitudinal central axis 20.

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

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

Correspondingly, the chambers 96 'and 102' associated with the pistons 26 "and 28 ', which also communicate with one another, are directly connected to the chambers 86' and 98 'via valves 140 with the chambers 86' and 98 'connected.

While the valves 138, 140 in FIG. 9a) are shown in their closed position, the pistons 22 'to 28' in their position which is maximally displaced towards the center of the housing 12 ' move, the valves 138 and 140 in Fig. 9b) are shown in their open position when the pistons 22 'to 28' move in opposite directions and the chambers 90 ', 100 * and 96' and 102 'decrease in volume. In this way, the chamber 98 'ready for suction between the pistons 24' and 28 'can be acted upon by pre-compressed air from the chambers 90', 100 'and 96' and 102 '.

FIGS. 12a) - d) to 15a) - d) show a further exemplary embodiment of a rotary piston machine provided with the general reference number 10 ′ *, which differs from the rotary piston machine 10 by the following features.

The rotary piston machine 10 ″ in turn has four pistons 22 ″ to 28 ″, to which chambers 86 ″, 90 ″, 96 ″, 98 ″, 100 ″ and 102 ″ are assigned. In contrast to the rotary piston machine 10 and also to the rotary piston machine 10 ', the chambers 90 ″, 96 ″, 100 ″ and 102 ″ do not serve as pre-pressure chambers but, like the chambers 86 ″ and 98 ″, also serve as working chambers for a Carnot cycle.

In contrast to the previous exemplary embodiments, the chambers 90 ″ and 100 ″ ″ do not communicate with one another, but are completely separated from one another via the central section 68 ″ of the rotor 62 ″. Likewise, the chambers 96 ″ and 102 ″ Completely separated from one another via the central section 68 ″ of the rotor 62 ″ and also serve as working chambers for a Carnot cycle. The chambers 90 ″ and 100 ″ are correspondingly assigned an inlet duct 142 for fresh air and an outlet duct 144 for expelling the combusted fuel-air mixture. Furthermore, the chambers 90 ″ and 100 ″ are jointly assigned a further spark plug 146 and a further injection nozzle 148. The inlet passage 142, the outlet passage 144, the spark plug 146 and the injection nozzle 148 are in relation to the corresponding inlet passage 108 ″, outlet passage 122 ″, the spark plug 118 ″ and the injection nozzle 120 ″, which are the chambers 86 ″ and 98 '' are arranged offset by 90 ° about the longitudinal central axis 20 ''.

In the same way, the chambers 96 ″ and 102 ″ are assigned a further inlet duct 150, outlet duct 152, a spark plug 154 and an injection nozzle 156, which are in the same circumferential position as the inlet duct 142, the outlet duct 144, and the spark plug 146 and injector 148 associated with chambers 90 "and 100".

In this design, a six-cylinder engine is simulated by means of the rotary piston machine 10 ″, the work cycles of intake, compression, expansion and ejection in the chambers 90 ″, 100 ″ and 96 ″, 102 ″ compared to the corresponding work cycles in the chambers 86 "and 98" are offset by 90 °.

FIGS. 12a) - d) to 15a) - d) show four operating positions of the rotary piston machine 10 ″, in which the pistons 22 ″ to 28 ″ have moved a total of 135 ° about the longitudinal central axis 20 ″ A full rotation of the pistons 22 "to 28"'over 360 ° around the longitudinal central axis 20 "becomes a full working cycle in the chambers 86" and 98 " carried out, likewise in each of the chambers 90 ″ and 100 ″ and 96 ″ and 102 ″, so that a total of six complete working cycles in the rotary piston machine 10 ″ take place with one full revolution.

It goes without saying that further modifications of the rotary piston machine 10, 10 'or 10' 'are possible within the scope of the present invention.

For example. it is conceivable to provide only the pistons 22 and 24 as double pistons in the rotary piston machine 10, while the pistons 26 and 28 can 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 can also be provided, while the pistons 24 and 26 are omitted and corresponding transverse walls are provided in the rotor 62 for delimiting the chambers 86 and 98. Such an arrangement would in turn lead to a mass-balanced configuration also with regard to the linear movement of the pistons 22 and 28.

Claims

claims

Rotary piston machine, with a housing (112; 168) which has a cylindrical housing inner wall (18), with at least one piston (22-28; 162, 164) which is arranged in the housing (112; 168) and which is about a longitudinal central axis (20; 166) of the housing (12; 168), and thereby executes a reciprocating linear movement by means of a control mechanism (40, 58; 170, 172), which serves to at least one of the pistons (22-28; 162, 164 ) associated chamber (86, 90, 96, 98, 100, 102; 192, 194, 196) periodically enlarged and reduced, characterized in that the linear movement of the at least one piston (22-2δ; 162, 164) parallel to Longitudinal central axis of the housing (12; 168) takes place.

Rotary piston machine according to claim 1, characterized in that the piston (22) is arranged eccentrically with respect to the longitudinal central axis (20) of the housing (12) and in the housing (12) at least one further piston (24, 28) rotating around the longitudinal central axis ) is arranged, which is arranged with respect to the longitudinal central axis (20) of the housing (12) on the side opposite the first piston (22).

Rotary piston machine according to claim 2, characterized in that the further piston (24) is arranged axially opposite the first piston (22) at the same height.

Rotary piston machine according to claim 3, characterized in that the further piston (24) is fixedly connected to the first piston (22).

Rotary piston machine according to claim 1, characterized in that the at least one piston (162, 164) is arranged centrally around the longitudinal central axis (166) and rotates in the housing (168) around a central piston axis coinciding with the longitudinal central axis (166).

Rotary piston machine according to one of the preceding claims, characterized in that in the housing (12; 168) at least one further piston (26; 164) rotating around the longitudinal central axis (20; 166) is arranged, which is in a straight line extension of the first piston (22; 162) is arranged.

Rotary piston machine according to claim 6, characterized in that the at least one chamber (86; 194) is formed by the space between facing end faces of the first piston (22; 162) and the further piston (26; 164).

Rotary piston machine according to one of claims 2 to 7, characterized in that the linear movement of the further piston (26; 164) is directed opposite to the linear movement of the first piston (22; 162).

Rotary piston machine according to one of claims 1 to 4 or 6 to 8, characterized in that at least four pistons (22-28) are arranged in the housing, of which In each case two pistons (22, 24; 26, 28) are arranged axially opposite one another at the same height with respect to the longitudinal central axis (20) of the housing (12), and two pistons (22, 26; 24, 28) in a straight line extension are arranged to each other.

10. Rotary piston machine according to one of the preceding claims, characterized in that the control mechanism (40, 58; 170, 172) at least one on the at least one piston (22-28; 162, 164) arranged guide member (42; 174, 176) and at least one control cam (44, 60; 178) formed in the housing inner wall (18), along which the guide member (42; 174, 176) runs.

11. Rotary piston machine according to one of claims 3 or 4 or 6 to 9 and according to claim 10, characterized in that a guide member (42) is arranged on the first piston (22) and the other piston (24) lying axially at the same height , wherein both guide members (42) run along the same cam (44).

12. Rotary piston machine according to one of the preceding claims, characterized in that one of the housing inner wall (18) facing side of the at least one piston (22-28) is formed in cross section in the form of a partial circle which extends over a circular angle of preferably about 90 ° ,

13. Rotary piston machine according to one of the preceding claims, characterized in that the at least one piston (22-28; 162, 164) by one around the longitudinal center Axis (20; 166) together with the at least one piston (22-28; 162, 164) rotating rotor (62; 182), which is axially immobile, is guided in its linear movement.

14. Rotary piston machine according to claim 13, characterized in that the rotor (182) is designed as a sleeve or as an axis.

15. Rotary piston machine according to claim 13 or 14, characterized in that the rotor (62) has a central portion (68) lying on the longitudinal central axis (20) of the housing (12), which comprises the chamber (86) associated with the first piston (22). separates from the chamber (98) associated with the other coils (24) opposite with respect to the longitudinal central axis (20).

16. Rotary piston machine according to one of the preceding claims, characterized in that two end faces of the at least one piston (22-28) each have a chamber (86, 90, 96, 98, 100, 102) assigned to them, which reduce and enlarge in opposite directions to one another , wherein one chamber (86, 98) serves as a working chamber for a Carnot cycle and the other chamber (90, 96, 100, 102) serves as a pre-pressure chamber for generating a pre-pressure in order to close the working chamber (86, 98) with a pre-pressure apply.

17. Rotary piston machine according to claim 15 and 16, characterized in that the central section (68) of the rotor (62) on the side of the chambers (90, 96; 100, 102) serving as the pre-pressure chamber is missing or is designed such that because two of the chambers (90, 100; 96, 102) serving as the pre-pressure chamber communicate with each other.

18. Rotary piston machine according to claim 16 or 17, characterized in that the pre-pressure chamber is connected to the working chamber via a housing-outside connecting line (106, 116), in which a valve (110), in particular a controllable valve (112), is preferably arranged.

19. Rotary piston machine according to claim 16 or 17, characterized in that the pre-pressure chamber is connected to the working chamber directly through the piston (22-28), wherein in the piston (22-28) at least one valve (138, 140), preferably an automatic valve is arranged.

20. Rotary piston machine according to one of claims 1 to 15, characterized in that both end faces of the at least one piston (22-28; 162 164) each have a chamber (86, 90, 96, 98, 100, 102; 192, 194, 196 ) is assigned, which decrease and enlarge in opposite directions to each other, whereby both chambers (86, 90, 96, 98, 100, 102; 192, 194, 196) serve as working chambers for a Carnot cycle.