EP1891299A1

EP1891299A1 - Rotary oscillating piston machine and method

Info

Publication number: EP1891299A1
Application number: EP06754294A
Authority: EP
Inventors: Wolfgang Haltenberger
Original assignee: Hydrotech Holding AG
Current assignee: Hydrotech Holding AG
Priority date: 2005-06-07
Filing date: 2006-06-06
Publication date: 2008-02-27
Also published as: WO2006131395A1; DE102005027017A1

Abstract

The invention relates to a device for compressing and/or displacing a fluid in at least one displacement chamber, said device comprising a rotary piston, which is positioned in the displacement chamber so that it can rotate about a rotational axis and can rotate on a plane that extends perpendicularly to the rotational axis. The device is characterised in that: an oscillating segment is situated on the rotary piston; the oscillating segment can be pivoted about an oscillating-segment axis on the rotational plane of the rotary piston, in order to execute an oscillating motion relative to the rotary piston, during the rotation of the latter; and the rotary piston and the oscillating segment divide the displacement chamber into two sub-chambers, whose size is respectively enlarged or reduced by the rotation of the rotary piston, the total volume of the displacement chamber remaining constant, whereby an enlargement of the first sub-chamber causes a reduction in size of the second sub-chamber. The invention also relates to a method for compressing and/or displacing a fluid, to a pump, a hydraulic energy converter and to an internal combustion engine.

Description

ROTATION DISPLACEMENT PISTON MACHINE AND METHOD

description

The invention relates to a device and a method for compressing and / or displacing a fluid, in particular a rotary piston compressor according to the preambles of claims 1 and 40 and a pump, a hydraulic force transducer and an internal combustion engine according to the preambles of claims 41, 42 and 43.

There are devices for compressing or displacing a fluid with a displacement chamber and a piston are known in which caused by the movement of the piston, a volume change of the displacement chamber and in this way a fluid located in the displacement chamber is compressed and / or displaced.

Such devices are used for example in internal combustion engines, in which a piston compresses a gaseous fluid in the displacement chamber, wherein the internal combustion engines differ in the design of their piston. In the most well-known combustion engines, the gasoline engine and the diesel engine, the piston is designed as a reciprocating piston exporting a stroke, the rotary engine, however, a rotating rotary piston is used.

What different types of engines have in common is that they convert the chemical energy stored in a fuel into mechanical work. The type of energetic conversion is similar in the different internal combustion engines and is done by converting the chemical energy into heat and then converting the heat into mechanical work. The conversion of the chemical energy is carried out by combustion of the fuel, the conversion of heat energy into mechanical work by their transfer to a fluid whose pressure increases and performs mechanical work in the resulting expansion. In conventional internal combustion engines carried by the lifting movement of a reciprocating piston or the rotational movement of a rotary piston for this purpose First, a compression of the fluid in the displacement chamber, caused by the movement of the piston and caused by the piston movement reduction of the displacement chamber. Fuel is injected into the compressed fluid and the resulting fuel mixture formed from the fluid and the fuel is ignited. By burning the fuel mixture, the pressure within the displacement increases, the fluid expands and drives the piston. In this way, the chemical energy stored in the fuel is converted into kinetic energy which causes a reciprocating motion in the reciprocating piston and a rotational movement of the piston in the rotary piston and generates a torque on a shaft.

Petrol and diesel engines differ in particular by the resulting compression of the fluid in the displacer and the ignition process. When gasoline engine is a compression of the fluid located in the displacement of atmospheric pressure to 20 to 30 bar, the fluid thus experiences by the piston movement, a compression ratio of compressed to non-compressed mixture of 20 to 30 to 1. An ignition of the compressed, to a temperature heated from 400 to 500 ⁰ C and mixed with fuel fluid via an external spark. In the diesel engine, however, the fluid is compressed depending on the design of the diesel engine up to 110 bar, so the fluid undergoes a compression ratio of 110 to one and is heated to 700 to 900 ⁰ C, so that injected into the compressed fluid itself fuel inflamed.

In a reciprocating engine, it is disadvantageous that measures to balance the mass of a lifting movement exporting reciprocating piston are necessary to ensure the smoothness of the engine and to compensate acting on the engine mass forces and moments. This problem is avoided by a rotary piston arrangement with a rotating rotary piston, so that separate measures for mass balance are not required. In one embodiment of the rotary piston arrangement, the Wankel engine, the rotary piston divides an epitrochoide-shaped displacement chamber into three partial spaces, in which a fluid is compressed by the rotation of the rotary piston circulating in the displacement chamber by means of an eccentric drive. The cross section of the rotary piston is formed in the plane of rotation, ie in cross section perpendicular to its axis of rotation, like an equilateral triangle with concave sides and has sealing regions in its corners, which run along the housing during the revolution of the piston. The disadvantage of such a rotary piston arrangement is that the displacement chamber shape created by the rotary piston is unfavorable and leads to high fuel consumption and high pollutant emissions. In addition, devices using rotary piston arrangements are limited in their achievable compression ratios and thus limited in their possible uses. In particular, with such devices no diesel engine similar construction of an internal combustion engine with auto-ignition is possible.

The present invention has for its object to provide devices and methods for compressing and / or displacing a fluid, with which a quiet running behavior can be achieved, which allow effective displacement and / or high compression of the fluid and are versatile.

The object is achieved by a device having the features of claim 1, a method having the features of claim 40 and a pump, a hydrodynamic torque converter and an internal combustion engine having the features of claims 41, 42 and 43.

A solution according to the invention provides a device, in particular a rotary piston compressor for compressing and / or displacing a fluid in at least one displacement chamber, wherein the device comprises a rotary piston which is arranged rotatably about a rotation axis in the displacement and so in a plane of rotation which is perpendicular to the axis of rotation extends, is rotatable. In this case - a pendulum segment is arranged on the rotary piston,

- The pendulum segment is parallel to the plane of rotation of the rotary piston pivotable about a pendulum segment axis to execute a pendulum motion relative to the rotary piston during a rotation of the rotary piston about the axis of rotation, - shares the rotary piston together with the pendulum segment the

Displacement space in two subspaces, which are each increased or reduced by the rotation of the rotary piston about the axis of rotation, wherein the total volume of the displacer remains constant, so that an increase of the first subspace causes a reduction of the second subspace and vice versa. The solution according to the invention thus provides a device which divides the displacement chamber into two subspaces by the rotary piston and the pendulum segment arranged on the rotary piston, which chambers are alternately enlarged and reduced by the rotational movement of the rotary piston and the pendulum movement of the pendulum segment relative to the rotary piston. The change in volume of the subspaces takes place in a differential manner, so that with a constant total volume of the displacer space, the reduction of the first subspace leads to an enlargement of the second subspace. The pendulum segment is arranged on the rotary piston, that it is pivotable in the plane of rotation of the rotary piston and during the rotation of the rotary piston about its axis of rotation performs a pendulum motion about the pendulum segment axis relative to the rotary piston. Due to the pendulum motion, the pendulum segment, together with the rotary piston, creates a sealing division of the displacement space into two partial spaces.

With the solution according to the invention, a device is provided which causes by means of the rotational movement of the rotary piston and the simultaneous pendulum movement of the pendulum segment, a division of the displacement in two subspaces, which are enlarged and reduced in a differential manner by the rotational movement of the rotary piston. The device according to the invention thus provides a piston arrangement with a rotating piston, which enables large displacement and / or compression ratios of a fluid located in the subspaces of the displacement chamber and at the same time ensures smooth running rotational behavior, so that the device is also suitable for high rotational speeds. The device thus combines the advantages of a reciprocating piston arrangement with those of a rotary piston arrangement, in particular by making the device possible compression and / or displacement ratios as with a reciprocating piston and a running behavior as with a rotary piston. With the device according to the invention therefore completely new designs, for example, a motor, a pump or a force converter are conceivable, which are characterized by a high achievable compression and / or displacement ratio at the same time efficient and quiet operation. Preferably, the volume of at least one of the subspaces during a revolution of the rotary piston about its axis of rotation changes from a minimum residual volume to a maximum volume and again to the minimum residual volume. In this way, a fluid located in the sub-chamber experiences a very large compression and / or displacement due to the rotation of the rotary piston, which is limited only by the compressibility of the fluid and the residual residual volume of the subspace.

The displacer is preferably arranged in a housing in which the rotary piston is rotatably mounted. The rotary piston divides together with the pendulum segment the displacer in two subspaces by the rotary piston during its rotation around its axis of rotation at least on a housing section sealingly along and the pendulum segment simultaneously sealingly abuts a further housing portion. The pendulum segment and the rotary piston are designed so that they behave sealingly to each other during the pendulum movement of the pendulum segment and to make a sealing connection, at least a portion of the pendulum segment rests against at least a portion of the rotary piston.

The pendulum motion of the pendulum segment is advantageously effected by the physical forces on the pendulum segment during the rotation of the rotary piston about its axis of rotation. In particular, the pendulum segment is deflected by the forces acting on the pendulum segment, caused by the rotational movement of the rotary piston and arranged on the rotary piston pendulum segment centrifugal forces and pressed against a housing portion. But it is also possible and advantageous zwangszusteuem the pendulum motion of the pendulum to ensure in this way that the pendulum motion of the pendulum segment is synchronous to the rotation of the rotary piston and a sealing division of the displacement is ensured by the pendulum motion of the pendulum segment.

In a preferred embodiment, the rotary piston of the device has at least one base plate which is parallel to the plane of rotation perpendicular to the axis of rotation of the

Rotary piston extends and is arranged rotatably in the housing about the axis of rotation of the rotary piston. On the base plate and firmly connected with this one Closing element which extends on the base plate and is formed so that it runs during the rotation of the rotary piston sealing along at least one housing portion and thus produces the seal between the housing and rotary piston and on the other during the pendulum movement of the pendulum segment relative to the rotary piston sealing abuts a surface of the pendulum segment so as to effect the seal between the rotary piston and pendulum segment. Due to the design of the closure element and the sealing effect between rotary piston and housing, rotary piston and pendulum segment and pendulum segment and housing, caused by the pendulum motion, the division of the displacement is ensured in two subspaces.

Preferably, the cross section of the closure element is designed to be sickle-shaped parallel to the plane of rotation of the rotary piston. In this case, the shutter member may be defined in cross section parallel to the plane of rotation of the rotary piston by an outer side having an outer radius RA measured from the rotation axis of the base plate and an inner side having an inner radius R1 measured by the pendulum segment axis the sickle shape of the inner radius Rl is greater than the outer radius RA. The outside of the closure element moves along a housing section during the rotation of the rotary piston and the inside faces the shuttle segment. During the pendulum motion, the pendulum segment moves along the inside of the closure element, wherein the pendulum segment is such that the inside of the closure element facing side of the pendulum segment sealingly abuts the inside of the closure element and thus on the rotary piston.

The pendulum segment is arranged according to the invention about the pendulum segment axis rotatably mounted on the rotary piston. In this case, the pendulum segment axis is preferably arranged on the base plate, is offset from the axis of rotation of the base plate by a distance D and extends perpendicular to the plane of rotation, so that the pendulum segment can be pivoted in the plane of rotation of the rotary piston relative to the rotary piston. Preferably, the pendulum segment in cross-section parallel to the plane of rotation of the rotary piston on a curved side, which can be described by a radius Rl about the pendulum segment axis. The curved side of the Pendulum segments and the inside of the closure element thus have a similar shape and curvature and are both by the radius Rl about the pendulum segment axis writable. The pendulum segment is arranged on the rotary piston, that the curved side of the pendulum segment to the inside of the closure element shows, so that the pendulum segment can thus be moved about the pendulum segment axis while the curved side of the pendulum segment sealingly abuts the inside of the closure element.

In order to achieve the sealing division of the displacement in two subspaces, the pendulum segment is during the rotation of the rotary piston about its axis of rotation on a housing section and performs for this purpose a pendulum motion.

Preferably, the pendulum segment lies with one of the end portions of the curved

Side during the rotation of the rotary piston around its axis of rotation sealing on

Housing, wherein always one of the end portions of the curved side rests against the housing, while the rotation of the rotary piston about its axis of rotation sections but also both end portions of the curved side can touch the housing.

The pendulum segment is preferably shaped in cross-section parallel to the plane of rotation in the region of the end portions of the curved side of the pendulum segment. In an advantageous embodiment, the end sections of the curved side can be described in each case by a radius RZ by a center of the end portions of the curved side on the shuttle segment spaced from the pendulum segment axis. The end portions of the curved side are preferably arranged so that they have a maximum distance of 2RA to each other along a line which is defined by the center points associated with the end portions of the curved sides. The position of the centers of the curved portion end portions on the shuttle segment is determined by the line defined by the midpoints of the end portions passing through the rotational axis of the base plate of the rotary piston when the shuttle segment is in a non-deflected position centered relative to the rotary piston. Thus, the pendulum segment is in its normal position in which it is arranged symmetrically to the connecting line of pendulum segment axis and rotation axis of the rotary piston, ie in the central position during its pendulum motion. In an advantageous variant, the end sections of the curved side of the pendulum segment can also be formed as a circular in cross-section parallel to the plane of rotation of the rotary piston, extending perpendicular to the plane of rotation of the rotary piston sealing elements, which are arranged rotatably about one axis of rotation on the pendulum segment and can be described by a radius RZ , By using such separate sealing elements, which are rotatably mounted on the pendulum segment, the friction between housing and pendulum segment can be minimized during the rotation of the rotary piston about its axis of rotation, reduces material wear and the performance of the device can be improved.

The further shaping of the pendulum segment in cross-section parallel to the plane of rotation is basically arbitrary and serves to connect the curved side of the pendulum segment and the sealingly abutting on a housing portion end portions of the curved side with the pendulum segment axis. An advantageous embodiment in this case has two further sides, which are formed so that they form with their essential extension directions approximately at an angle in the range up to 90 ° to each other and are each connected to an end portion of the curved side of the pendulum segment. The contour of the pendulum segment in this case has therefore in cross-section parallel to the plane of rotation of the rotary piston approximately the shape of a pie-shaped circular segment which is bounded by the curved, the closure member facing side and the two other sides in cross-section parallel to the plane of rotation of the rotary piston.

Preferably, the housing of the device is designed such that it has a first wall portion whose contour in cross-section parallel to the plane of rotation of the rotary piston describes a circular section and which is spaced by the radius RA from the axis of rotation of the base plate. The first wall section circumscribes an angle greater than or equal to 180 ° and is arranged such that the axis of rotation of the rotary piston is located in the fictitious center of the circle describing the first wall section, so that the closure element arranged on the rotary piston, the outside of which is also surrounded by the radius RA can be described about the axis of rotation of the rotary piston, during the rotation of the rotary piston moves about its axis of rotation sealingly along the first wall section. In addition, the housing has a second wall section whose contour in cross-section parallel to the plane of rotation of the rotary piston preferably represents a circle section defined by a radius RA, wherein the center of the second wall section may be spatially offset relative to the center of the first wall section. The pendulum segment movement is then such that one of the end portions of the curved side of the pendulum segment rests against one of the two wall sections and thus effects the sealing division of the displacement chamber into two partial spaces.

In order to ensure that the pendulum segment rests against one of the two wall sections of the housing and the sealing space sealingly divides into two subspaces, the pendulum motion of the pendulum segment can be guided by a guide means, thus be positively controlled in this way. By the guide means the movement of the pendulum segment is fixed relative to the housing, so as to ensure that the pendulum segment always runs along one of the two wall sections and thus fulfills its sealing function to one of the two wall sections.

The guide means may be formed, for example, as a guide element arranged fixedly on the housing with a circular cross-section parallel to the plane of rotation of the rotary piston having a radius RF = (RA-2RZ) at the center of the second wall section on the housing and perpendicular to the plane of rotation of the rotary piston extends. The pendulum segment is designed so that the guide element cooperates with the pendulum segment and, for example, by a suitable shaping of the pendulum segment causes the pendulum motion. In particular, the guide means by an intervention in the pendulum segment zwangssteuem the pendulum motion of the pendulum segment, the pendulum segment for this purpose may have a recess in its inner region.

In addition, it is conceivable that, when the end portions of the curved side of the pendulum segment are formed by means of sealing elements, the guide element cooperates with the sealing elements arranged on the pendulum segment and thereby the pendulum movement of the pendulum segment during the rotation of the rotary piston leads.

In an alternative embodiment, the guide means is formed by at least one guide pin which is fixedly arranged on the pendulum segment. To the

Guide the pendulum segment during the rotation of the oscillating piston, the guide pin can engage in a groove in the housing, the groove in the

Housing is designed so that the pendulum segment is guided during its rotation along the wall sections of the housing and always rests one of the end portions of the pendulum segment on one of the two wall sections.

The contour of the displacement of the device is described in cross-section parallel to the plane of rotation of the rotary piston in one embodiment by enveloping circles with the radius RA, which indicate the contour of the first and second wall portion of the housing, the centers of the first and second wall portion associated enveloping circles spatially offset are arranged. The position of the centers of the two enveloping circles relative to each other can be described by an angle about a pivot axis, wherein the position of the pivot axis in the cross-sectional plane parallel to the plane of rotation of the rotary piston is defined by an intersection of the two enveloping circles. The angle, which describes the position of the first and the second wall portion to each other, defines the shape and also the working behavior of the device. At an angle of 0 °, the cross-section is parallel to the plane of rotation of the rotary piston of the housing circular, the outside of the closure element is always on the housing, and the displacer is not divided during the rotation of the rotary piston about its axis of rotation into subspaces, so that no change in volume Subspaces done. This corresponds to an idling of the device, in which no change in volume caused by the rotation of the rotary piston. If the angle is not equal to zero, then the outer side of the closure element during the rotation on the first wall portion and the end portions of the curved side of the pendulum segment on the second wall portion of the housing. The displacer is thus divided into two subspaces, which are enlarged and reduced in a differential manner during the rotation of the rotary piston. In an alternative embodiment, the contour of the displacement in the cross section parallel to the plane of rotation of the rotary piston by two spaced, with their openings facing each other circular halves of radius RA can be described, which are interconnected by connecting lines so that extended by an intermediate piece contour with gives an elongated circular shape.

In principle, the contour of the displacement is freely selectable within certain limits, it must be ensured that the displacement is always divided by the closure element and the pendulum segment sealing in two subspaces. The guide means for guiding the pendulum segment during the rotation of the rotary piston is in this case in each case adapted so that the pendulum segment is guided sealingly with its end portions along the wall sections of the housing.

In a variant of the invention, the displacer space enclosed by the housing has a constant volume which can not be changed during operation. The housing shape is then defined, for example, by a constant angle between the enveloping circles describing the first and second wall sections. In an alternative variant, however, the displacement is variable in its volume and can be changed during operation of the device. Via a volume change of the displacement chamber, the ratio of the volumes of the partial spaces can be adjusted to one another and thus the compression ratio of maximum compressed to maximally expanded volume of both partial spaces of the device can be determined.

Preferably, the volume change of the displacement chamber is effected by a pivoting of the second wall section about a pivot axis whose position is defined by the intersection of the two enveloping circles describing the cross section of the first and second wall section in the plane of rotation of the rotary piston. The pivot axis lies in the end region of the first wall section and extends perpendicular to the plane of rotation of the rotary piston. By pivoting the second wall section relative to the first wall section about the pivot axis, the volume of the displacement chamber can be changed and the compression ratio of maximum compressed to maximally expanded volume of the subspaces can be adjusted. In an alternative embodiment, the change in volume can also take place via a displacement of the wall sections relative to one another.

The geometric relationships of the device can be described by means of the contours of the components of the rotary piston, the pendulum segment and the housing in the cross-sectional plane parallel to the plane of rotation. In particular, a variant of the device is completely described by the radii RA, Rl, RZ and RF and the positions of the axis of rotation of the rotary piston, the pendulum segment axis and the center of the second wall portion. It is conceivable that the geometrical dimensions of the arrangement change perpendicular to the plane of rotation. However, the positions of the axis of rotation and the pendulum segment axis must be independent of the position relative to the plane of rotation, so that the rotary piston is rotatable about the axis of rotation and the pendulum segment is pivotable about the pendulum segment axis. It is also conceivable that the radii do not change perpendicular to the plane of rotation and the arrangement by constant radii RA, Rl, RZ and RF and a height H can be described and up and / or down through formed by the housing cover and / or the base plate is limited.

The task is also solved by a method for compressing and / or displacing a fluid. In the method according to the invention

a pendulum segment which is pivotably arranged on the rotary piston in the plane of rotation carries out a pendulum movement relative to the rotary piston during the rotation of the rotary piston about the axis of rotation,

- Shares the rotary piston together with the pendulum movement exporting pendulum segment the displacer in two subspaces and

- The subspaces are each increased or decreased by the rotation of the rotary piston about the rotation axis, wherein the total volume of the displacement chamber remains constant, so that an increase of the first subspace causes a reduction of the second subspace and vice versa.

With the method according to the invention, the displacement is divided by the rotation of the rotary piston about its axis of rotation, which extends perpendicular to the plane of rotation of the rotary piston, and a simultaneous pendulum movement of the pendulum segment in two sub-spaces, which are alternately enlarged and reduced in a differential manner. The process thus creates the opportunity to efficient way to effect a high compression of a located in a subspace of the displacement fluid.

In addition, the task is solved by a pump, a hydrodynamic torque converter and an internal combustion engine with a device for compressing or displacing a fluid with the features explained above.

The pump according to the invention has for this purpose a device in which a fluid is sucked by means of the rotational movement of the rotary piston through an inlet valve in an expanding subspace and is discharged through the subsequent compression of the subspace by an outlet valve.

The hydrodynamic torque converter according to the invention has a device according to the invention for compressing or displacing a fluid with which mechanical energy is converted into flow energy and flow energy in turn into mechanical energy. A possible embodiment has a first device as a drive, which converts a mechanical torque into a hydrodynamic pressure, and a second device as an output, which is connected to the first device, for example via hoses and converts the hydrodynamic pressure back into a mechanical torque. Such a torque converter can be used, for example, as a transmission which converts large torques into high pressures by means of the device and via the compression ratios achievable with the device and transmits them with a low-volume fluid.

In the internal combustion engine according to the invention, the device is used to compress a fluid located in a partial space of the device, to mix with fuel and to generate a torque by the combustion of the fuel. For this purpose, the internal combustion engine preferably has two devices which are connected to one another via a shaft, the first device causing a compression of a fuel mixture and the second device being set in rotational motion by the ignition of the compressed fuel mixture and the resulting expansion. The speed control of the internal combustion engine can either be controlled via the addition of the fuel, as is customary in conventional internal combustion engines. But it is also possible, the Speed control of the internal combustion engine via a change in the volume enclosed by the housing of the device.

The idea underlying the invention will be explained in more detail with reference to several embodiments in the following figures. Show it:

Figures 1A-F are schematic transverse and longitudinal sectional views of the lower part, middle part and upper part of a first embodiment of the device for compressing or displacing a fluid;

Figure 2 is a perspective and partially exploded view of the central part of the first embodiment of the device;

Figure 3A-F are schematic transverse and longitudinal sectional views of the lower part, middle part and upper part of a second embodiment of the device;

Figures 4A-G are schematic cross-sectional views of an apparatus for compressing or displacing a fluid in various positions of the rotary piston of an embodiment during its revolution;

Figure 5 is a schematic plan view of an embodiment of the

Rotary piston with a pendulum segment arranged thereon;

Figure 6 is a schematic representation of a housing shape;

Figure 7A-C are schematic cross-sectional views of a third embodiment of the variable displacement volume device;

Figure 8 is a schematic longitudinal sectional view through a further embodiment of the device with adjustable

Verdrängerraumvolumen;

Figure 9 is a schematic sectional view of an embodiment of a

Internal combustion engine with an internally arranged mechanical output; Figure 10A-F are schematic transverse and longitudinal sectional views of the lower part, middle part and upper part of a third embodiment of the device;

Figure 11 is a schematic representation of a second housing form and

FIG. 12 shows a schematic cross-sectional view of the middle part according to FIG. 10D in a rotated position.

FIGS. 1A to 1F and 3A to 3F show, in longitudinal section and cross-sectional views, two embodiments of a device for compressing and / or displacing a fluid. FIGS. 1A to 1F and 3A to 3F respectively show schematically longitudinal sections and cross sections through a top, a middle and a bottom part of two devices, while FIG. 2 shows a perspective view of the middle part of the device according to the embodiment according to FIG. 1A to 1 F shows. By definition, the longitudinal sectional views are oriented perpendicular to the plane of rotation 111 of a rotary piston 2 (FIG. 2), while the cross-sectional views are oriented parallel to the plane of rotation 111 of the rotary piston 2. From FIGS. 1A to 1F and 3A to 3F, respectively, an overall view of the respective apparatus is obtained by superimposing the individual longitudinal sections representing the upper, middle and lower part.

The movement of the device, in particular the nature of the pendulum movement of the pendulum segment 3 during the rotation of the rotary piston 2 about its axis of rotation 110 is explained with reference to FIGS. 4A to 4G.

The device according to FIGS. 1A to 1 F and FIG. 2 has a rotary piston 2 arranged in a housing 1, which comprises an upper and a lower base plate 21, 21 ', which extends parallel to the plane of rotation 11 of the rotary piston 2 and which Waves 210, 210 'extending perpendicularly to the plane of rotation 111 of the rotary piston 2 and means for supporting 10 are rotatably mounted in the region of the upper and lower parts in the housing 1 (FIGS. 1A, 1B and 1E, 1F). Between the base plates 21, 21 'and fixedly connected to these is in the region of the central part of the device, as shown in Figure 2 can be seen, a closure element 22 is arranged, which forms the rotary piston 2 together with the upper and lower base plate 21, 21'. Also between the base plates 21, 21 'is a pendulum segment 3 via a pendulum segment axis 31 extending perpendicularly to the plane of rotation 111 of the rotary piston 2 between the base plates 21, 21 'is pivotally connected to the rotary piston 2 (FIGS. 1C, 1D and 2). The pendulum segment axis 31 can be formed, for example, via an axis between the base plates 21, 21 "fixed axis about which the pendulum segment 3 is pivotable.

The housing 1 of the device forms in the region of the middle part of a displacement chamber 6, which is divided by the rotary piston 2 and arranged on the rotary piston 2 pendulum segment 3 in two subspaces 61, 62. The displacer space 6 formed by the subspaces 61, 62 is limited in the plane of rotation 11 1 to the outside by a first and a second wall portion 1 1, 12 and is upward and downward in the direction perpendicular to the plane of rotation 111 by the upper and lower base plate 21, 21 'completed.

The rotary piston 2 is rotatably arranged in the housing 1 and rotates in operation about its axis of rotation 110. By the rotational movement of the rotary piston 2, the pendulum segment 3 is set in a pendulum motion, which runs synchronously to the rotation of the rotary piston 2, so that the period of the pendulum movement of the circulation period of the rotary piston 2 corresponds. Due to the pendulum movement, the pendulum segment 3 is deflected towards the second wall section 12 and lies during the rotation of the rotary piston 2 about its axis of rotation 110 on the second wall section 12.

In order to achieve the separation of the displacer 6 in two subspaces 61, 62, the pendulum segment 3 has two sealing elements 32, 33, which are cylindrical and rotatable about axes of rotation 321, 331 are arranged on the pendulum segment 3 and of which one always on the second wall portion 12th the housing rests laterally in a sealing manner. This is due to the pendulum motion of the pendulum segment

3 and the concomitant deflection of the pendulum segment 3 toward the second wall section 12 causes. In the position shown in Fig. 1D of

Rotary piston 2 and arranged thereon pendulum segment 3 is the of the

Pendulum segment axis 31 seen from right seal member 32 on the second

Wandungsabschnitt 12, thereby causing during the rotation of the

Rotary piston 2 about its axis of rotation 110, the pendulum segment 3 performs a pendulum motion and in this way relative to the rotary piston 2 to the Pendulum segment axis 31 is pivoted to the second wall portion 12 out. The first subspace 61 of the displacer space 6 is bounded laterally in the cross-sectional plane parallel to the plane of rotation 111 by the pendulum segment 3, the inside 221 of the closure element 22 and the first wall section 11, while the second subspace 62 is defined by the pendulum segment 3, the outside 222 of the closure element 22 and the second wall portion 12 is completed. By a rotational movement of the rotary piston 2 and a simultaneous oscillating movement of the pendulum segment 3, by means of which one of the sealing elements 32, 33 always causes a seal to the second wall portion 12, the subspaces 61, 62 alternately increased and decreased, the compression and expansion of the subspaces 61st , 62 occurs at a constant total volume of the displacement chamber 6 in a differential manner. An increase in the volume of the first subspace 61 thus inevitably leads to a decrease in the volume of the second subspace 62. A fluid located in the subspaces 61, 62 is compressed or expanded in this way or, depending on the design and use of the device, fed or ejected.

In the embodiment shown in FIGS. 1A to 1F and 2, the pendulum movement of the pendulum segment 3 about the pendulum segment axis 31 is effected by the physical forces prevailing during the rotation of the rotary piston 2. If the pendulum segment 3 is in the deflected position, ie not in the central position on the rotary piston 2, then the center of gravity of the pendulum segment 3 lies outside a line which points through the pendulum segment axis 31 and the rotation axis 110 of the rotary piston 2 and represents an axis of symmetry of the rotary piston 2 the pendulum segment 3 is pressed against the second wall section 12 of the housing 1 by the centrifugal force arising on account of the rotational movement and acting on the pendulum segment 3.

During the rotation of the rotary piston 2, there are two times in which the pendulum segment 3 passes through the central position on the rotary piston 2, the center of gravity of the pendulum segment 3 is thus short on the line between pendulum segment axis 31 and rotation axis 1 10 of the rotary piston 2. In this position, the sum of the centrifugal forces acting on the pendulum segment 3 is zero, the position of the pendulum segment 3 is not stable, so that the pendulum segment 3 in the further rotational movement of the rotary piston from this position occurs and in turn with one of its sealing elements 32, 33 is pressed against the second wall portion 12.

In order to ensure that always one of the sealing elements 32, 33 of the pendulum segment 3 rests against the second wall section 12, the movement of the pendulum segment 3 can be guided and thus positively controlled.

An embodiment of the device with measures for guiding the pendulum segment 3 is shown in FIGS. 3A to 3F, which differs from the first embodiment according to FIGS. 1A to 1F in that the upper part of the device shown in FIGS. 3A and 3B as a fixed, the displacer 6 final lid of the housing 1 is formed, on which a in the middle part extending guide member 4 is arranged to guide the pendulum movement of the pendulum segment 3 and fixedly connected to the housing 1. The middle part and the lower part of the device, shown in FIGS. 3C and 3D or FIGS. 3E and 3F, substantially correspond to the first embodiment according to FIGS. 1C to 1F, wherein in the middle part additionally the guide element 4 via a recess 304 in FIG Pendulum segment 3 engages in the pendulum segment 3. With the guide member 4 causes the pendulum movement of the pendulum segment 3 is guided during the rotation of the rotary piston 2, the position of the pendulum segment 3 is thus constantly defined by the guide member 4, so as to ensure that a sealing element 32, 33 of the pendulum segment 3 always applied to the second wall portion 12.

The mode of action of the guide element 4 can be explained with reference to FIG. 3D. The guide element 4 is formed as a cylindrical member having a circular cross section parallel to the plane of rotation 111 of the rotary piston 2 and extends from the lid of the housing 1 formed by the upper part of the device according to FIGS. 3A and 3B perpendicular to the plane of rotation 111 into the recess 304 in the shuttle segment 3, which is designed in the interior of the pendulum segment 3 so that the guide element 4 can not touch the pendulum segment 3 at any time. The guide element 4 interacts with the sealing elements 32, 33 arranged on the pendulum segment 3 and is operatively connected to guide the pendulum segment 3 with one of the sealing elements 32, 33 via the sides of the sealing element 32, 33 facing the recess 304 in the pendulum segment 3. In the in Fig. 3D illustrated position of the rotary piston 2 is the guide element 4 on the inside of the pendulum segment axis 31 from the right looking sealing element 32 and thus causes the leadership of the sealing element 32 along the second housing section 12th

The operation and the sequence of movement of the device for compressing and / or displacing a fluid are shown in FIGS. 4A to 4G, in which the rotary piston 2 and the pendulum segment 3 arranged on the rotary piston 2 are in different positions during the rotation of the rotary piston 2 about the axis of rotation 110 are shown. The device shown in FIGS. 4A to 4G is based on the embodiment according to FIGS. 3A to 3F, so that the pendulum movement of the pendulum segment is guided by the guide element 4 about the axis of rotation during the rotation of the rotary piston.

In the device shown in FIGS. 4A to 4G, the inlet and outlet of the fluid to be displaced and / or compressed during operation are effected by an inlet valve 51 and an outlet valve 52, respectively, which are provided in the first and second wall sections 11, 12. The inlet and outlet valves 51, 52 are not necessarily arranged in the wall sections 11, 12 of the housing, but may also be in the base plate 21, 21 'of the rotary piston 2 or the upper, forming a lid portion of the housing 1.

The sequence shown in FIGS. 4A to 4G is based on a clockwise direction of rotation U of the rotary piston 2, wherein in general the direction of rotation of the device can be selected as desired.

At a first time (FIG. 4A), the pendulum segment 3 is located in a central position on the rotary piston 2, that is, it is aligned symmetrically with respect to the closure element 22. At this time, the displacement chamber 6 is completely formed by the first part space 61, the volume of which corresponds to the total volume of the displacement 6 and by the second wall portion 12 and the first two sides 301, 302 of the pendulum segment 3 and arranged on the pendulum segment 3 sealing elements 32nd 33 is laterally delimited in the cross-sectional plane parallel to the plane of rotation 111. Perpendicular to the plane of rotation, as can be seen from FIGS. 3A to 3F, the displacement chamber 6 is on one side by a Base plate 21 and completed on the other side by a formed by the housing 1 cover. The closure element 22 rests with its outside 222 against the first wall section 11 of the housing 1, while the sealing elements 32, 33 are both arranged at the opposite transition regions from the first wall section 11 to the second wall section 12, which are arranged in the region of the inlet 51 and the outlet valve 52 , abut the housing 1.

At a second time (FIG. 4B), the rotary piston 2 has rotated in the direction of rotation U by an angle. The pendulum segment 3 is pivoted relative to the closure element 22 about the Pendelsegrnentachse 31, thereby causing the guide member 4 is in operative connection with the cylindrical sealing member 32 and the sealing member 32, the pendulum segment 3 deflects toward the second wall portion, so that the of the pendulum segment axis 31st seen from right sealing element 32 abuts the second wall portion 12. Due to the interaction of the guide element 4 and the sealing element 32, the deflection of the pendulum segment 3 is positively controlled and the sealing closure between the sealing element 32 and the second wall section 12 is ensured. Between the closure element 22 and the right sealing element 32, a second subspace 62 has been created in the region of the inlet valve 51. Since the total volume of the displacement chamber 6 formed by the first and second sub-spaces 61, 62 is constant, the volume increase of the second subspace 62 is necessarily associated with a decrease in volume of the first subspace 61. The first subspace 61 is always bounded by a wall portion 11, 12, the first and second sides 301, 302 of the pendulum segment 3 and the inner side 221 of the closure element 22, while the second subspace 62 always between the second wall portion 12, the outside of the closure element 22 and the curved side 303 of the pendulum segment 3 is formed. By the reduction of the first subspace 61, caused by the rotational movement of the Rotationskoibens 2 from the position shown in FIG. 4A towards the position in Fig. 4B, a fluid in the first subspace 61 is thus displaced or, when the exhaust valve 52 is closed, compressed. At the same time, due to the increase in volume of the second subspace 62, a fluid is drawn through the inlet valve 51 into the second subspace 62.

At a third and fourth time (FIGS. 4C and 4D), the rotary piston 2 has turned further in the direction of rotation U, and has the volume of the second sub-space 62 increases at the expense of the volume of the first subspace 61. The sealing element 32 rests continuously on the second wall section 12, effected by the guidance of the guide element 4, and establishes the seal between the first and second sub-spaces 61, 62.

At a fifth point in time (FIG. 4E), the rotary piston 2 has rotated relative to the position in FIG. 4A in the direction of rotation U by 180 °. In this position, the volume of the first subspace 61 is minimal, while the volume of the second subspace 62 is maximum. The closure element 22 is facing the second wall portion 12 at this time, the pendulum segment 3 is in a central position on the rotary piston 2 and has with its pendulum segment axis 31 to the first wall section 1 first

During the further rotary movement of the rotary piston 2 (FIGS. 4F and 4G), the second partial space 62 is reduced, so that a fluid located in the second partial space 62 is compressed. The guide element 4 now acts on the of the

Pendulum segment axis 31 seen from left sealing element 33 and in turn causes a deflection of the pendulum segment 3 toward the second wall portion 12 of the housing, so that the sealing element 33 abuts the second wall portion 12 and causes a seal.

The periodic rotation movement is now periodically continued with the state of FIG. 4A. In the transition from the state according to FIG. 4G to the state according to FIG. 4A, the volume of the second subspace 62 is reduced by the rotational movement of the rotary piston 2 to a minimum residual volume, so that a fluid located in the second subspace 62 experiences a very large compression.

The volume change of the first subspace 61 during the rotation of the rotary piston 2 about the rotation axis 110 is relatively small and writable by the ratio of maximum volume (see FIG. 4A) to minimum volume (see FIG. 4E) of the first subspace 61 in the subspace 61 fluid is thus also relatively low. The second subspace 62, on the other hand, during the rotation of the rotary piston 2 about its axis of rotation 110, performs a volume change from a minimum residual volume (FIG. 4A) to a maximum volume (FIG. 4E) and again to the minimum residual volume, so that one in the second subspace 62 fluid undergoes a large compression or expansion during the rotation of the rotary piston 2. The compression ratio achievable via the change in volume of the second subspace 62 is therefore large, but practically limited by the compressibility of the fluid and a minimal residual volume of the second subspace 62.

The pendulum movement of the pendulum segment 3 is guided during the rotation of the rotary piston 2 about its axis of rotation 110 by the guide member 4 and thus positively controlled. The guide element 4 ensures that a sealing element 32, 33 always bears against a wall section 11, 12 in order to bring about the sealing division of the displacement chamber 6 into its two partial spaces 61, 62. The pendulum movement. of the pendulum segment 3 is supported by the prevailing during the rotational movement of the rotary piston 2 physical forces on the pendulum segment 3, so that an additional contact pressure of the sealing elements 32, 33 on the respective wall portion 1 1, 12 is generated by the centrifugal forces caused by the rotational movement.

5 illustrates the geometric design of the individual parts of the rotary piston 2 and of the pendulum segment 3 according to the second embodiment shown in FIGS. 3A to 3F in a plan view of the rotary piston 2 and the pendulum segment 3 arranged on the rotary piston 2.

On the base plate 21 of the rotary piston 2, the closure element 22 is arranged on the one hand and firmly connected to this and on the other hand via the pendulum segment axis 31, the pendulum segment 3 mounted pivotably. The closure element 22 has a sickle-shaped shape in cross-section parallel to the plane of rotation 111 of the rotary piston 2 and has an inner side 221 which can be described by an inner radius R1 about the pendulum segment axis 31 and an outer side 222 which is defined by an outer radius RA about the rotation axis 110 of the rotary piston 2 is writable on. As can be seen in FIGS. 1D and 3D, the closure element 22 extends perpendicular to the rotation plane 111 over the height of the middle part of the device.

The pendulum segment 3 arranged on the base plate 21 is delimited in cross-section parallel to the plane of rotation 111 essentially by three sides 301, 302, 303, from where the first two sides 301, 302 are at an angle of approximately 90 ° to each other and in the connecting region of the pendulum segment axis 31, which extends perpendicular to the plane of rotation 111, is arranged. The third side 303 of the pendulum segment 3 is curved and is described by the inner radius Rl to the pendulum segment axis 31. The third pendulum segment side 303 nestles in shape of the inside 221 of the closure element 22, so that the pendulum segment 3 in a pendulum motion about the pendulum segment axis 31 runs with its third side 303 along the inside 221 of the closure element 22 and forms a sealing transition. The pendulum segment axis 31 is arranged offset by a distance D from the axis of rotation 110 of the rotary piston 2.

The pendulum segment 3 extends, as can be seen in FIGS. 1 D and 3D, perpendicular to the plane of rotation 111 over the height of the middle part of the device, ie over the entire displacer space 6 and is defined by the upper and lower base plates 21, 21 'according to FIG 1A to 1F or by the lower base plate 21 and the cover formed by the housing 1 according to FIGS. 3A to 3F. The pendulum segment 3 seals the subspaces 61, 62 of the displacement chamber 6 relative to each other, but can, in particular with the use of suitable lubricants, relative to the upper and lower base plate 21, 21 'and along the housing 1 to move smoothly.

On pendulum segment 3, the two cylindrical sealing elements 32, 33 are arranged, which are rotatably mounted about the axes of rotation 321, 331, have a circular cross-section with a radius RZ and extend over the height of the formed in the middle part of the device displacement chamber 6 (see FIG. 1C and 3C). The axes of rotation 321, 331 of the sealing elements 32, 33 are arranged in the cross-sectional plane parallel to the plane of rotation 11 1 so that the distance between the axes of rotation in the cross-sectional plane parallel to the plane of rotation 111 2RA - 2RZ and the two axes of rotation 321, 331 interconnecting line in a non-deflected pendulum segment position 3, that is centrally positioned on the rotary piston 2 pendulum segment 3, passes through the axis of rotation 110 of the rotary piston 2 and at the same time perpendicular to the axis of rotation 31 and the axis of rotation 110 facing symmetry axis of the rotary piston 2. The maximum distance between the outer sides of the sealing elements 32, 33 along the line connecting the axes of rotation 321, 331 is 2RA in this case. The guide member 4, which serves in the embodiment shown in FIGS. 3A to 3F for guiding the pendulum movement of the pendulum segment 3, is arranged on the housing 1 and extends into the recess 304 in the pendulum segment 3, has a cylindrical shape with a circular cross section with the Radius RF = RA - 2RZ and extends with its longitudinal axis perpendicular to the plane of rotation 111. The longitudinal axis of the guide element 4 is arranged in the cross-sectional plane parallel to the plane of rotation 1 1 1 in the center 120 of the second wall portion 12 of the housing 1, so that the guide element 4 so is aligned concentrically with the second wall portion 12. The shape of the recess 304 in the pendulum segment 3 is predetermined by the guidance of the pendulum segment 3 to be realized. In the embodiment shown in FIGS. 3A to 3F, an interaction between pendulum segment 3 and guide element 4 takes place exclusively via the sealing elements 32, 33 in that the guide element 4 interacts with and is in contact with at least one of the cylindrical sealing elements 32, 33. Direct contact between pendulum segment 3 and guide element 4 is to be avoided in this case, and accordingly the shape of the recess 304 in the pendulum segment 3 is to be selected. In the embodiment shown in FIGS. 3A to 3F, the contour of the recess 304 is circular in cross-section parallel to the plane of rotation 111, describable by a sufficiently large radius around a point passing through the intersection of the line connecting the two pivot axes 321, 331 with the line the pendulum segment axis 31 is defined extending symmetry axis of the pendulum segment 3. It is also conceivable, instead of the sealing elements 32, 33 to use an integrally formed pendulum segment 3, in which the sealing elements 32, 33 are integrated into the pendulum segment 3 and the guide element 4 interacts directly with the inside of the recess 304.

In Fig. 6, the shape of the displacer 6 forming housing 1 is shown in cross-section parallel to the plane of rotation 111. The inner contour of the housing 1, which describes the displacement 6, can be described by two pitch circles with the radius RA, which are each associated with a wall section 11, 12. The center of the first pitch circle, whose left portion in FIG. 6 represents the first wall portion 11, corresponds to the position of the rotation axis 110 of the rotary piston 2, so that the closure element 22 of the rotary piston 2, the outside 222 also by the radius RA about the axis of rotation 110 is writable, so with its outside 222 along the first wall portion 11 runs and itself this tightly clings. The center 120 of the second pitch circle, the right-hand portion of which forms the second wall portion 12, is offset from the rotation axis 110 of the rotary piston 2. The spatial arrangement of the two pitch circles can be characterized by an angle α, which is formed between two lines pointing through a pivot axis 130 and one of the centers 110, 120 of the pitch circles.

The two wall sections 11, 12 of the housing 1, which laterally delimit the displacer space 6 parallel to the plane of rotation 11 1 of the rotary piston 2 and can be described by the two pitch circles, are therefore arranged eccentrically. The rotary piston 2 rotates about the axis of rotation 110 in the center of the first wall portion 1 1, while the guide member 4 is positioned in the center 120 of the second wall portion 12. Since the guide element 4 interacts with the cylindrical sealing elements 32, 33, the guide element 4 and the sealing elements 32, 33 in cross section parallel to the plane of rotation 1 11 of the rotary piston 2 have a circular contour with the radius RF = RA-2RZ or the radius RZ wherein the axes of rotation 321, 331 of the sealing elements 32, 33 are arranged spatially offset on the pendulum segment 3 (see Fig. 5), and the sealing elements 32, 33 during the rotation of the rotary piston 2 about the rotation axis 110 with the pendulum segment 3 arranged thereon inevitably Guide element 4 must pass on its side facing the second wall portion 12, the guide member 4 deflects the pendulum segment 3 via the arranged on the pendulum segment 3 sealing elements 32, 33 to the second wall portion 12 out and thus performs the sealing elements 32, 33 sealingly on the second wall portion 12 along. Due to the opposing arrangement of the sealing elements 32, 33 on the pendulum segment 3, one of the two sealing elements 32, 33 always bears against the second wall section 12 and establishes a sealing transition between the pendulum segment 3 and the second wall section 12.

In an alternative embodiment shown in FIGS. 10A to 10F, the guide means is realized by guide pins 40 arranged fixedly on the pendulum segment 3, which engage in a groove 45 in the housing 1 through a recess 46 in the base plates 21, 21 '. The embodiment shown in FIGS. 10A to 10F essentially corresponds to the configuration explained with reference to FIGS. 1A to 1F the device, wherein additionally the two guide pins 40 are provided. The guide pins 40 are advantageously inserted into bores of the pendulum segment 3 and rotatably or rotatably connected to the pendulum segment 3. It is also conceivable in this context, the guide pins 40 integrally formed with the pendulum segment 3.

The guide pins 40 extend perpendicularly from the pendulum segment 3 through the base plates 21, 21 'into the groove 45 in the upper and lower part of the housing 1. It is also conceivable to provide the guide pins 40 and the groove 45 only on one side, so that the guide pins 40 extend only on one side of the pendulum segment 3 and only in the upper or lower part of the housing 1, a groove 45 is formed. However, a two-sided execution of the guide pins 40 and the groove 45 offers the advantage of a stable, symmetrical design, especially for applications where large torques acting on the rotary piston 2.

Fundamentally, it is also conceivable to provide only one guide pin 40 which effects the guidance of the pendulum segment 3. However, an embodiment with two guide pins arranged symmetrically on the pendulum segment 3, as shown in FIGS. 10A to 10F, is advantageous in order to ensure a stable and reliable guidance of the rotary piston.

The groove 45 is formed so that the pendulum segment 3 is guided by the engaging in the groove 45 guide pins 40 during the rotational movement of the rotary piston 2 so that an end portion 32 ', 33' always rests against the wall portion 12 of the housing 1. The shape of the groove 45 is dependent on the inner contour of the housing 1, so the wall sections 11, 12 to choose.

Fig. 12 shows the Rotationskoiben 2 in a rotated position in which the pendulum segment 3 is deflected and rests with its end portion 33 'on the wall portion 12 of the housing 1. The guide pins 40 run around in the groove 45 and thus perform the pendulum motion of the oscillating piston such that always one of the two end portion 32 ', 33' of the pendulum segment 3 rests against the wall portion 12. The groove is, as explained with reference to FIGS. 10A to 10F, formed in the housing 1 in the upper and / or lower part (Fig. 10 A, B and Fig. 10 E, F) of the device and in Fig. 12 only for illustration indicated by dashed lines. In the embodiment shown in FIGS. 10A to 10F, the displacer space 6 is shaped with its wall sections 11, 12 corresponding to the cross-sectional view shown in FIG. 11. The inner contour of the housing 1 describing the cross-section of the displacement chamber 6 is formed by the two wall sections 11, 12 which can be described by two circular halves of radius RA pointing towards each other with their openings whose centers 110, 120 are spaced apart from each other and over straight sections are connected to a closed contour. The first wall section 11 is formed by the lower half of the circle in Fig. 11, while the second wall section includes the upper half of the circle and the vertical, the circular halves connecting sections. The pendulum segment 3 rests exclusively on the second wall section 12 during the rotation of the rotary piston 2.

According to the shape of the displacement chamber 6, the groove 45 is divided into two sections, namely a guide section 450 and a return section 451 (see FIG. 10B). The guide portion 450 is configured such that the distance of the guide portion 450 of the groove 45 to the wall portion 12 is constant. The return section 451, on the other hand, represents the connection between the two ends of the guide section 450 for returning the guide pins 40 engaging in the groove 45. The design of the return section 451 is in principle arbitrary and, in particular, does not have to be adapted to the guide pins 40 correctly when two guide pins 40 are used become. The return section 451 then only has to ensure that a guide pin 40 located in the region of the return section 451 can reach the other end of the guide section 450. If, by contrast, only one guide pin 40 is used, then the return section 451 is also designed in a precise fit such that the guide pin 40 is guided by the groove 45 at all times and the pendulum segment 3 bears against the wall section 12.

In general, the contour of the displacement chamber 6 in cross-section parallel to the plane of rotation of the rotary piston 2 can be selected within wide limits and so optimized for optimal Verdrängerraumform out. However, the shape of the first wall portion 11 is in this case at least partially circular to choose so that the crescent-shaped closure member 22 sealingly to the first Wall section 11 can slide along. The shape of the second wall portion 12, however, is limited only in that the pendulum segment 3 with one of its end portion 32, 33 and 32 ', 33' always rest against the wall portion 12 during rotation of the rotary piston 2 and can perform a pendulum motion. The groove 45 for guiding the pendulum segment 3 is in each case adapted to the shape of the wall section 12, so that guidance of the pendulum segment 3 along the wall section 12 is ensured.

The recess 46 in the base plates 21, 21 'of the rotary piston 2 must be such that a contact of the guide pins 40 and the base plates 21, 21 "in any position of the pendulum segment 3 is excluded during the rotation of the rotary piston the recesses 46 are sufficiently large, an exact fit is not required.

In the embodiment according to FIGS. 10A to 10F, the pendulum segment 3 is formed in one piece by the sealing elements 32, 33 being integrated into the pendulum segment 3 in the form of end sections 32 ', 33'. The outer surface of the pendulum segment 3 in the region of the sealing end portions 32 ', 33' of the curved third side 303 of the pendulum segment 3 is here modeled in cross-section of the contour of the cylindrical sealing elements 32, 33, wherein the guide pins 40 each in the center of the at least partially circular end portions 32nd ', 33' are arranged. However, it is only essential in the shaping of the sealing end sections 32 ', 33' that it must be ensured that the end sections 32 ', 33' cooperate sealingly with the wall sections of the housing 1 and thus seal between the subspaces 61, 62 of the displacer chamber 6 produce.

In principle, even with the use of guide pins 40, a design with rotatably mounted sealing elements readily possible.

It is also conceivable, analogous to the embodiment according to FIGS. 3A to 3F, to limit the housing on one side by a housing cover, ie to provide no second base plate 21 '. A device with two base plates 21, 21 ', as shown in FIGS. 10A to 10F, may for example be advantageous in order to enable a bilateral downforce. The devices according to FIGS. 1 to 6 and 10 and 11 can be used for a multiplicity of applications. For example, the device may be used as a pump that, according to the process shown in FIGS. 4A to 4G, draws a fluid through the inlet valve 51 alternately into the first and second sub-chambers 61, 62 and ejects it from the outlet valve 52. Likewise, a use as an internal combustion engine is conceivable. For this purpose, fuel may be injected and ignited into the fluid compressed in the second compartment 62 (see FIG. 4G), thereby causing expansion of the fluid in the compartment 62 which exerts a force on the closure member 22 and in this way the rotary piston 2 put in a rotary motion. Due to the high achievable compression ratios, caused by the change in volume of the subspaces 61, 62 of the displacer 6, in particular the second subspace 62 from a maximum volume to a residual residual volume and again to the maximum volume, interpretations as a diesel engine with auto-ignition are just as conceivable as gasoline engines.

The achievable by the device compression and displacement ratios are determined by the writable by means of the two sub-circles and limited by the first and second wall portion 11, 12 housing shape and by the housing enclosed by the displacement chamber 6. 7A to 7C show various embodiments of the device with different displacement chamber sizes, which are determined by different arrangements of the displacement chamber 6 enclosing wall sections 1 1, 12 relative to each other. In particular, in FIGS. 7A to 7C, the second wall section 12 is arranged in a different position relative to the pivot axis 130. It is conceivable that the second wall portion 12 is variable and pivotable about the pivot axis 130 in operation and thus the volume of the displacer 6, 61, 62 is adjustable during operation or that the second wall portion 12 is fixed relative to the first Wandungsabschnitti 1 is arranged.

In the arrangement shown in Fig. 7A, the second wall portion 12 is pivoted relative to the first wall portion 1 1 about the pivot axis 130 on the end point of the first wall portion by an angle of 12.5 °. This results in a large maximum volume of the second subspace 62 and thus a high achievable compression ratio. In the arrangement shown in FIG. 7B, the pivoting angle of the second 12 to the first 1 1 wall section has a size of 7 °, so the maximum volume of the second partial space and the compression ratio that can thus be achieved are smaller.

In the arrangement shown in Fig. 7C, the pivot angle is 0 °. In this case, no second subspace 62 is formed during the rotation of the rotary piston 2 about its axis of rotation 110, and the first subspace 61 experiences no change in volume. This case corresponds to an idling of the assembly in which no work is done to displace or compress a fluid.

It is conceivable to set the achievable compression and displacement ratios during operation via the arrangement of the wall sections 11, 12 of the housing 1. 8 shows a longitudinal section through an arrangement with a displacement chamber 6, 61, 62 whose volume can be changed by pivoting the second wall section 12 about the pivot axis 130. The assembly has a base and a central portion which correspond to the arrangements shown in Figs. 3C to 3F. For adjusting the displacer volume, the upper part of the arrangement has a piston top plate 41 enclosed in the housing 1, which is fixedly connected to the guide element 4 and the second wall section 12 and via an adjusting lever 44 cooperating with a lever 42 and a vertical connecting piece 43 about the pivot axis 130 can be pivoted. By pivoting the piston top plate 41 about the pivot axis 130 (see FIGS. 7A to 7C), the second wall portion 12 and the guide member 4, which are fixedly connected to the piston top plate 41, also pivoted, so that a volume change of the displacement chamber 6, 61st , 62 bounded by the first and second wall sections 11, 12. During the pivoting operation, the guide element 4 always remains in the center 120 of the second wall section 12 (see FIG. 6), so that a change in volume of the displacement chamber 6, 61, 62 is given by the guide element 4 while maintaining the guidance of the pendulum segment movement.

Alternatively, in particular with a housing shape as shown in FIG. 1 1, a volume change can also take place via a displacement of the wall sections 11, 12 relative to one another, whereby the distance between the circular sections 11, 12 representing circular halves is increased or decreased by the displacement. 9 shows an embodiment of an internal combustion engine having two devices 700, 700 'interconnected by a shaft 701 and of which the first 700 is for compressing the fluid and the second 700' for generating the torque. During operation of the internal combustion engine, the fluid is sucked into the first device 700 via an inlet pipe, compressed in the device and conducted in a compressed state via a channel 710 into an antechamber 711. The supply of the compressed fluid is controlled by two valves 740, 741. Into the compressed chamber located in the antechamber 711, fuel is injected via an injection nozzle 720 and ignited with a spark plug 730. By combusting the compressed fluid and fuel mixture, the fluid expands and drives the second device 700 'by rotating the rotary piston 2 of the second device 700' and thus the shaft 701 on which the rotary pistons 2 of both the first and second rotary pistons For each rotation of the rotary piston 2 about its axis of rotation, which is concentric with the shaft 701, the process runs once, the compression and the torque generation exclusively in the second subspace 62 of the Displacement chamber 6 of the first or second device 700, 700 'take place because a larger compression can be achieved in the second subspace 62 and the compression ratios in the first and second subspace 61, 62 are fundamentally different either via an externally arranged on the shaft 701 output or via a zwis Chen the two devices provided internal output 760th

The materials used to construct the device with its components, in particular the rotary piston 2, the pendulum segment 3 and the housing 1 depend on

Application and the forces and pressures occurring. For

Internal combustion engines, for example, can generally be used materials, such as those used in other engine types, ie in particular

Steel or suitable metal alloys having the required strength properties. For smooth operation and reduction of

Friction losses and abrasion can be used in operation suitable lubricants that allow a smooth and low-wear operation.

The possible uses of the device are not limited to the embodiments described here. A device using the device Torque converter can be used, for example, for a variety of vehicle types, in particular as a transmission or hydraulic power transmission devices for motor vehicles, but also, for example, as a power transmission device for bicycles or other means of transport in which a torque generated is transmitted to a drive medium.

Bezugszeichentiste

1 housing

10 storage

11 First wall section

110 axis of rotation of the rotary piston

111 rotation plane

12 second wall section

120 midpoint of the second wall section

130 pivot axis

Rotary piston 1, 21 "base plate of the rotary piston 10, 210 'shaft 2 closure element 21 inside of the closure element 22 outside of the closure element

Pendulum segment 01 First pendulum segment side 02 Second pendulum segment side 03 Third pendulum segment side 04 Recess in pendulum segment 1 Pendulum segment axis 2 First sealing element 2 'First end section 21 Rotary axis of the first sealing element 3 Second sealing element 3' Second end section 31 Rotary axis of the second sealing element

Guide element 0 Guide pin 1 Piston top plate 2 Lever 3 Vertical connector 4 Lever 5 Groove 450 guide section

451 return section 46 recess

51 inlet valve

52 exhaust valve

6 displacement chamber

61 First subspace

62 Second subspace

700 device for compacting

700 'device for generating a torque

701 wave

710 channel

711 Pre-chamber 720 Injector 730 Spark plug 740, 741 valves

751 inlet pipe

752 Outlet tube 760 Inner output

RA outer radius of the closure element

Rl inner radius of the closure element

RZ radius of the sealing element

RF radius of the guide element

D Distance between the axis of rotation of the rotary piston and pendulum segment axis

U direction of rotation of the rotary piston

Claims

claims

1. Device, in particular Rotationspendelkolbenverdichter, for compressing and / or displacing a fluid with a rotary piston, the one

Rotary axis is rotatably disposed in a Verdrängerraum and is rotatable in a plane of rotation which extends perpendicular to the axis of rotation,

characterized,

that

- On the rotary piston (2) a pendulum segment (3) is arranged,

- The pendulum segment (3) parallel to the plane of rotation (1 1 1) of the rotary piston (2) about a pendulum segment axis (31) is pivotable during a rotation of the rotary piston (2) about the axis of rotation (110)

Perform pendulum movement relative to the rotary piston (2),

- The rotary piston (2) together with the pendulum segment (3) dividing the displacement chamber (6) into two subspaces (61, 62), which are each increased or reduced by the rotation of the rotary piston (2) about the axis of rotation (1 10) wherein the total volume of the displacement chamber (6) remains constant, so that an enlargement of the first partial space (61) causes a reduction of the second partial space (62) and vice versa.

2. Apparatus according to claim 1, characterized in that changes the volume of at least one of the subspaces (62) during a revolution of the rotary piston (2) about the axis of rotation (110) periodically from a minimum residual volume to a maximum volume and again to the minimum residual volume.

3. Apparatus according to claim 1 or 2, characterized in that the displacement chamber (6) by a housing (1) is enclosed, in which the rotary piston (2) about the axis of rotation (110) is rotatably mounted.

4. The device according to at least one of the preceding claims, characterized in that the rotary piston (2) during the rotation about the axis of rotation (110) at least in a housing portion (11, 12) sealingly along the housing (1).

5. The device according to at least one of the preceding claims, characterized in that by the pendulum movement, the pendulum segment (3) always sealingly against a housing portion (1 1, 12).

6. Device according to at least one of the preceding claims, characterized in that the rotary piston (2) and the pendulum segment (3) are formed so that the pendulum segment (3) during the pendulum movement relative to the rotary piston (2) always sealed to a portion ( 22) of the

Rotary piston (2) is applied.

7. Device according to at least one of the preceding claims, characterized in that the pendulum movement of the pendulum segment (3) is positively controlled.

8. Device according to at least one of the preceding claims, characterized in that the rotary piston (2) has a base plate (21, 21 ') which extends parallel to the plane of rotation (111) of the rotary piston (2).

9. The device according to claim 8, characterized in that the base plate (21, 21 ') about which in perpendicular to the plane of rotation (111) extending axis of rotation (110) is rotatably disposed in the housing (1).

10. Device according to one of claims 8 and 9, characterized in that the rotary piston (2) on the base plate (21, 21 ') arranged and with this firmly connected closure element (22) extending from the base plate (21, 21 ') in the displacement chamber (6).

11. The device according to claim 10, characterized in that the closure element (22) during the rotation of the rotary piston (2) about the rotational axis (110) sealingly at least along a housing portion (11, 12) runs.

12. The device according to claim 11, characterized in that the closure element (22) sealingly abuts the pendulum segment (3) during the pendulum movement of the pendulum segment (3).

13. The device according to at least one of claims 10 to 12, characterized in that the closure element (22) together with the pendulum segment (3) dividing the displacement chamber (6) into two part dreams (61, 62), by the rotation of the rotary piston ( 2) are compressible and expandable about the axis of rotation (110).

14. The device according to at least one of claims 10 to 13, characterized in that the cross section of the closure element (22) parallel to

Rotation plane (111) of the rotary piston (2) is sickle-shaped.

15. The apparatus according to claim 14, characterized in that the cross section of the closure element (22) parallel to the plane of rotation (111)

by an outer side (222) having an outer radius (RA) measured from the axis of rotation of the base plate (21, 21 '), and

by an inner side (221) having an inner radius (R1) measured by the pendulum segment axis (31), is defined, wherein the inner radius (Rl) is greater than the outer radius (RA) and thus the closure element (22) has a crescent-shaped cross-section.

16. Device according to one of claims 8 to 15, characterized in that the pendulum segment (3) to the on the base plate (21, 21 ') arranged, perpendicular to the plane of rotation (111) of the rotary piston (2) extending pendulum segment axis (31) is rotatably connected to the base plate (21, 21 ") of the rotary piston (2), wherein the pendulum segment axis (31) from the rotation axis (110) of the base plate (21, 21 ') offset by a distance (D).

17. The device according to at least one of claims 10 to 16, characterized in that the pendulum segment (3) in cross section parallel to the plane of rotation (111) has a curved side (303) by a constant radius (Rl) of the pendulum segment axis (31 ) spaced and the

Closing element (22) of the rotary piston (2) faces.

18. The apparatus according to claim 17, characterized in that the pendulum segment (3) with one of the end portions (32, 33) of the curved side (303) always sealingly against a housing portion (11, 12).

19. The apparatus according to claim 18, characterized in that the pendulum segment (3) in the end portions (32, 33) of the curved side (303) in the cross section parallel to the plane of rotation (111) is round shaped.

20. The device according to at least one of claims 18 and 19, characterized in that the end portions (32, 33) each by a radius (RZ) about one of the pendulum segment axis (31) spaced center (321, 331) of the end portions (32, 33) on the pendulum segment (3) are writable.

21. The device according to at least one of claims 18 to 20, characterized in that the end portions (32, 33) along a by the midpoints (321, 331) of the end portions (32, 33) facing line a maximum distance (2RA) to each other ,

22. The device according to at least one of claims 18 and 21, characterized in that the by the centers (321, 331) of the end portions (32, 33) defined by the axis of rotation (110) of the base plate (21, 21 ') of the rotary piston (2) leads, when the pendulum segment (3) in a relative to

Rotary piston (2) centered, undeflected position is located.

23. The device according to at least one of claims 18 to 22, characterized in that the end portions of the curved side (303) through in

Cross section parallel to the plane of rotation (1 1 1) circular, perpendicular to

Rotation plane (1 11) of the rotary piston (2) extending sealing elements

(32, 33) are formed, each about a parallel to the axis of rotation (1 10) of the

Rotary piston (2) aligned rotational axis (321, 331) rotatably mounted on the pendulum segment (3) and by a radius (RZ) are writable.

24. Device according to at least one of the preceding claims, characterized in that the housing (1) has a first wall portion (11) which in cross-section parallel to the plane of rotation (111) describes a circular section and by a radius (RA) of the axis of rotation (110) of the

Rotary piston (2) is spaced.

25. The device according to claim 24, characterized in that the first wall section (11) of the housing (1) circumscribes an angle greater than 180 °.

26. Device according to at least one of claims 24 to 25, characterized in that the rotary piston (2) during the rotation of the

Rotary piston (2) about the axis of rotation (110) with the outside (222) of the

Closing element (22) sealingly along the first wall portion (11) of the housing (1) runs.

27. The device according to at least one of claims 24 to 26, characterized in that the housing (1) has a second wall portion (12) which in cross-section parallel to the plane of rotation (111) one by one

Radius (RA) defined circle portion, wherein the center (120) of the second Wandungsabschnitts (12) relative to the center (1 10) of the first Wandungsabschnitts (11) may be arranged spatially offset.

28. The device according to claim 27, characterized in that the pendulum segment (3) during the rotation of the rotary piston (2) about its axis of rotation (110) moves so that it rests sealingly on the second wall portion (12).

29. Device according to one of the preceding claims, characterized in that the pendulum movement of the pendulum segment (3) by a guide means (4) during the rotation of the rotary piston (2) is guided about its axis of rotation (110).

30. The device according to claim 29, characterized in that the guide means as a guide element (4) having a parallel to the plane of rotation (111) circular cross-section with a radius (RF) is formed, wherein the guide element (4) in the center (120) of the second Wandungsabschnitts (12) on the housing (1) is arranged and extending perpendicular to the plane of rotation (111).

31. The device according to claim 30, characterized in that the guide element (4) for guiding the pendulum movement of the pendulum segment (3) cooperates with the pendulum segment (3) arranged sealing elements (32, 33).

32. Apparatus according to claim 29, characterized in that the guide means by at least one guide pin (40) is formed, which is fixedly arranged on the pendulum segment (3) and in a groove (45) in the housing (1) engages.

33. Apparatus according to claim 32, characterized in that the groove (45) in the housing (1) is formed and provided to guide the at least one guide pin (40) so that the pendulum segment (3) during its rotation along the wall sections ( 11, 12) of the housing (1) is guided.

34. Device according to one of claims 1 to 33, characterized in that by the housing (1) enclosed Verdrängerraum (6) has a constant volume.

35. Device according to one of claims 1 to 33, characterized in that the by the housing (1) enclosed displacement chamber (6) has a variable volume during operation.

36. Apparatus according to claim 35, characterized in that on the volume of the displacement chamber (6), the compression ratio of maximum compressed to maximum expanded volume of the subspaces (61, 62) of the device is adjustable.

37. Apparatus according to claim 36, characterized in that the volume of the displacement chamber (6) by a pivoting or displacement of the second wall portion (12) is variable.

38. Device according to one of the preceding claims, characterized in that the dimensions of the housing (1), the rotary piston (2) and the pendulum segment (3) perpendicular to the plane of rotation (111) vary.

39. Apparatus according to claim 38, characterized in that the dimensions of the housing (1), the rotary piston (2) and the pendulum segment (3) descriptive radii (RA, Rl ₁ RZ, RF) change perpendicular to the plane of rotation (111) ,

40. A method for compressing and / or displacing a fluid with a device in which a rotary piston, which is arranged rotatably about a rotation axis in a Verdrängerraum, in a plane of rotation which is perpendicular to the

Axis of rotation extends, rotates,

characterized,

that

a pendulum segment (3) pivotably mounted on the rotary piston (2) in the rotation plane (11 1) during the rotation of the rotary piston (2) about the axis of rotation (110) performs a pendulum motion relative to the rotary piston (2), - the rotary piston (2 ) together with the pendulum movement exporting

Pendulum segment (3) divides the displacement chamber (6) into two subspaces (61, 62) and

- The subspaces (61, 62) by the rotation of the rotary piston (2) about the axis of rotation (110) are each increased or decreased, the total volume of the displacement chamber (6) remains constant, so that an enlargement of the first subspace (61) a Reduction of the second

Subspace (62) causes and vice versa.

41. pump for displacing a fluid,

marked by

A device for compressing or displacing a fluid according to any one of claims 1 to 39.

42. Hydrodynamic force transducer for transforming and transmitting forces,

marked by

a device for compressing or displacing a fluid according to one of

Claims 1 to 39.

43. combustion engine for power generation,

marked by

a device (700, 700 ') for compressing or displacing a fluid according to any one of claims 1 to 39.

44. An internal combustion engine according to claim 43, characterized in that the internal combustion engine comprises two devices (700, 700 ') interconnected via a shaft (701) according to one of claims 1 to 37, wherein the first device (700) causes a compression of a fuel mixture and the second device (700 ') is caused to rotate by the ignition of the compressed fuel mixture and the resulting expansion.

45. Internal combustion engine according to claim 44, characterized in that a speed control of the internal combustion engine via the addition of the fuel is effected.

46. An internal combustion engine according to claim 45, characterized in that a speed control of the internal combustion engine via a change in the housing of the device (700, 700 ') enclosed Verdrängerraumvolumens is effected.