DE2647150A1 - Orbital engine, pump or motor - has internally meshing lobes with surfaces between lobes of rotor which periodically engage housing - Google Patents

Abstract

The engine, pump or motor with internally meshing lobes comprises a rotor (14) with n lobes (15) having continuous sealing engagement with the internal surface of a housing (20) having n+1 lobes. The rotor has, between any two lobes, a medial section (17) which during orbiting of the rotor periodically makes sealing engagement with the housing surface. The rotor has, between each medial section and each of the adjacent lobes, a connection section (19) which does not engage the housing surface. This approaches the characteristics of a constant vol. cycle and is suitable for an engine of the Stirling type.

Description

Rotary mechanism for pumps, fluid motors,

Heat engines and the like.

The invention relates to a rotating mechanism with relative to each other rotatable inner and outer bodies that have interacting 2 surfaces, which form chambers of variable volumes during the relative movement. In particular The invention relates to rotary mechanisms of useful configuration and construction for use in pumps, fluid motors, heat engines or the like.

Because of their special properties, those according to the invention are suitable Rotary mechanisms especially for use as so-called Stirling engines, the are also known as internal combustion engines with external combustion.

Special efforts have been made over the past few years the design, construction and further development of rotating mechanisms of various Configurations.

In this context, the comprehensive classification of the Referred to the prior art rotary piston machines, as they are from Helix Wankel in 'tRotary Piston Machine published by Iliffe Books Ltd., London, 1965. Some of these Efforts have met with considerable success; an example of this is the current one called the commercial success of the so-called "Wankel engine" in certain areas of application has found. Some effort has also been directed towards the use of the trochoidal ones Rotary mechanisms in the construction of Stirling engines.

In this context, for example, the work t'Stirling-Cycle Machines by Graham Walker, published by Oxford University Press, London, 1973, and the publications cited therein. Also, be on the See U.S. Patent 3,800,526.

Regardless of the great effort and intensive efforts on this one One area is a common shortcoming of the previously proposed systems of this type in the absence of a rotating mechanism with a configuration that conforms to a constant space process is largely similar. The invention is considered to be an important contribution to the art respected because it closes this previously existing gap in technology.

In short, the rotating mechanism of the present invention is volumetric Properties which largely correspond to those of an idealized internal combustion engine.

In principle, the rotating mechanism according to the invention has an outer body (also known as a stator) with a cavity and an inner body (also known as a Rotor), which in the cavity of the outer body for relative rotation in this cavity is inserted, the axis of the inner body opposite the axis of the outer body blank space is laterally offset, but is arranged parallel to it. The inner body has an outer surface that is substantially the end (1) a plurality of apex sections which are equal around its axis Distances are distributed and equidistant from it, (2) several middle sections, those with the same distances around the inner body axis each equally far from this axis are removed and each with a distance of two apex sections lie between these, and (3) there is a plurality of connecting sections, each Intermediate or middle section via a connecting section with the respectively adjacent one Vertex section is connected. The individual apex sections are at the Relative rotation of the bodies around their axes constantly in sealing contact with the inner surface the peripheral wall of the outer body cavity. Each middle section arrives periodically in and out of sealing contact with the inner surface of the peripheral wall of the outer body cavity, while the two bodies rotate relative to one another about the said axes. In other words: this special sealing contact with the aforementioned relative rotation occurs one after the other at every single middle section, and it occurs in a repetitive manner cyclic or periodic sequence, so that at any time one or two middle sections are temporarily in sealing contact with the inner surface of this peripheral wall. During the above-mentioned relative rotation, the seal does not come into contact at any point in time between the connecting portions and the inner surface of the peripheral wall of the outer body cavity, hereinafter referred to simply as the tread. The general shape or configuration a mechanism satisfying the foregoing requirements is substantial Modifications accessible. For example, the inner body can be any number of apex sections as long as at least two apex sections are provided. Mechanisms with three to six vertex sections are becoming common preferred, although systems with two or more than six vertices cut off have proven to be quite suitable for certain applications. It should be noted that the cavity of the outer body has essentially a multi-sided profile with the Number of vertex sections of the inner body by one page number exceeding.

Although not absolutely necessary, the apex sections each have essentially the same contour, with the middle or intermediate sections as well each having substantially the same contour and each central portion of two Apex sections is equally distant.

Although a variety of mechanical arrangements are possible, relates Another preferred embodiment of the invention relates to a rotating mechanism of the type outlined above, with the inner and outer bodies under control or definition of internal gears to perform a relative rotation to each other capital. As will become more apparent from the following description, possesses such an arrangement has the advantage that during the relative rotation of the two bodies the forces acting between the contact zones or surfaces between the outer body tread on the one hand and the apex and middle sections of the inner body on the other can arise, be monitored or controlled. Doing this can be excessive Wear of the contact surfaces of these two bodies effectively largely reduced will.

Obviously, the relative rotation between inside and The outer body of one body is stationary with respect to the other rotating body or stationary be held, or it can both bodies rotate, either with different angular velocities in the same Direction of movement or with any angular velocity, whether different or the same, in opposite directions.

In most cases, however, mechanisms are preferred of the invention applied in which the outer body relative to the inner body is stationary and the latter performs the rotary movement.

In another preferred embodiment of the invention, the Apex sections or at the middle sections, and best of all at both sections the inner body contoured sealing plates are provided. The invention relates to thus, for example, to the following preferred embodiments: (A) To a Rotation mechanism of the type described, in which each apex section consists of a contoured sealing plate, which between said relative rotation both bodies with progressive portions of their outer surface in sealing contact stands with the outer body tread; and (B) to a rotating mechanism of that described Type in which each central section consists of a contoured sealing plate that During this relative rotation progressively with certain sections of its outer surface periodically comes into seal contact with the outer body running surface. Particularly a device which comprises a combination of features (A) and (B) is preferred.

As will become more apparent from the following description, consists Another advantage of the volume change rotary mechanisms according to the invention in their Suitability for slot or valve control in the most advantageous and yet fundamentally simple mechanical arrangement.

For example, in a preferred embodiment of the invention a rotary mechanism of the type described is provided in which each axial end the cavity or running space of the outer body is closed by a plate which with a number of radially spaced control openings around the cavity axis or slots is provided> and wherein the inner body at its axial ends has a number of channels, each of which is arranged in such a way that upon relative rotation of the two bodies around their axes periodically establish a connection between one through the outer surface of the inner body and the tread of the outer body set Chamber and one of the control openings is made via one of the channels.

In this construction, the number of control openings is preferred in each plate by one greater than the number of apex sections of the inner body, while the number of channels at each axial end (face) of the inner body corresponds to the number of its Seheitel sections, although other arrangements are also possible are conceivable and possible.

Further advantageous embodiments of the invention are in one Rotation mechanism of the type just described, in which (1) the inner body has three apex sections and has a substantially three-sided profile, (2) the outer body an im has a substantially four-sided profile, (3) each side plate has four substantially evenly spaced around the axis of the cavity and has control openings substantially equidistant from this axis and each axial end or each end face of the inner body is provided with three channels is, each of which extends inward from the relevant side of the inner body extends. In this construction, the inner body also advantageously has six separate channels and six connecting sections, each three of these channels at each axial end or each end face of the inner body lie and from each of the six connecting sections such a channel emanates. It is particularly advantageous in this special training that the mouths of the successive channels around the circumference of the inner body alternating with one another are arranged so that the first, the third and the fifth channel on the one Face and the second, fourth and sixth channel on the other face of the Inner body lie.

According to a further preferred embodiment of the invention, the size of the transverse distance between the axes of the inner body and outer body corresponds to the expression n in whichn is the number of cheitel sections of the inner body, D is the distance between the R-dial outermost point on the inner body and its axis and R is the mean radius of curvature of the profiles of the apex sections.

Although other configurations are possible and applicable Rotary mechanisms that meet these conditions generally have excellent displacement properties (displacement characteristics), and they are easy to design and manufacture.

Rotary mechanisms of the type described, in which the length of the profile each vertex is about 0.25-2.75 radians equivalent, others make preferred embodiments of the invention.

In a further embodiment, the invention provides the application of the above outlined rotating mechanisms as a means for changing volume or space in a Stirling heat engine. As is known, a Stirling engine (1) comprises one Mechanism for cyclic or periodic change of the volumes of several assigned Chambers, (2) a heat rejection means, (3) a regenerator and (4) a heat supply device. According to the invention, an improved Stirling heat engine can be created using the rotating mechanism described is used as a mechanism for changing the chamber volumes.

The following are preferred embodiments of the invention the accompanying drawing explained in more detail. They show: FIG. 1 a schematic representation of the axial profile of a rotating mechanism according to the invention, which has an inner body with two apex sections and a three-sided outer body cavity, i? ig. 2 shows a representation similar to FIG. 1 of an inner body with three apex sections and a quadrilateral outer body cavity,)? ig. 3 a representation similar to FIG. 2, however, which shows a preferred mechanism in which the inner body has four apex sections and the outer body has a cavity with five sides, Fig. 4 a big one. 3 resembling Representation of an inner body with five apex sections, which is operational is arranged in a six-sided outer body cavity one 5 shows a similar illustration of a further modified embodiment. in which the inner body has six apex sections and a seven-sided outer body cavity FIG. 6 shows a representation similar to FIG. 5, in which the inner body or Rotor has seven apex sections and the outer body or stator has eight sides, Fig. 7A to 7F partially schematic D æ positions of a rotary mechanism according to of the invention, in which the inner body in six different step positions its rotational movement in the outer body cavity is shown and which, among other things, the Principle of permanent sealing contact between the apex sections of the inner body and the running surface of the cavity, the non-sealing relationship between the connecting portions of the inner body and the running surface as well as the periodic sealing contact between illustrate the central or intermediate sections of the inner body and the tread, in these figures also the use of an internal gear control according to others Features of the invention is shown.

Figures 8A through 8F show in progressive sequence the manner in which the axial profiles of the outer surface of the inner body and the running surface of the outer body blank space for the rotary mechanism according to the invention can be derived, Fig. 9A to 92 schematic representations of a rotating mechanism according to Fig. 7A to 7F, in which the inner body is in the same six different sub-step positions of its rotational movement is shown and the inter alia the interaction between a slot or an opening and a control channel at one axial end of the Mechanism and the interaction between a slot or an opening and show a control channel at the other axial end of the mechanism, Fig. loA to loC a front, a central or

a rear cross section thereby a preferred inner body according to the invention with six control channels, three of which are on his one axial end or its one end face and three more on the other end face Fig. ii is an exploded and partially broken away perspective Illustration of a preferred rotating mechanism according to the invention, which is attached to each Front face a plate with several control openings or slots and an inner body with a configuration of the control channels essentially corresponding to Fig.

loA to loC, Fig. 12 shows an orthographic projection of the Rotation mechanism essentially of the type shown in FIG. 11, Sir.13 a schematic Representation of different stages of the rotary movement that occur simultaneously with two inventive, as Stirling engine interacting mechanisms occur, the top row (Fig. 13A to 13H) one and the bottom row (Fig. 13AF to 13HF) represent the other turning mechanism, Fi. 14 is a schematic representation of a idealized Stirling heat engine, the representations from 14A to 14H regarding the Tskt levels on the corresponding levels in the one above 13, FIG. 15 is a schematic perspective illustration of two rotary mechanisms operatively coupled to a common drive shaft according to FIG of the invention, which in the manner illustrated schematically in Fig. 13 as Stirling volume displacement or changing machine interact and which respectively have the basic construction according to FIG. 11, i? ig. 16 a partial side view, shown in section, of a heat transfer arrangement from a Heat removal device, a regenerator or heater device and a heat supply device, several such arrangements in the construction of FIG. 15 to form a Stirling heat engine according to the invention can be used, FIG graphical representation of volumetric analysis to compare performance a rotating mechanism according to the invention with that of a volumetric Stirling displacer and 18 shows a schematic representation of the axial profile of a particularly preferred rotating mechanism according to the invention, in which each apex section consists of a contoured sealing plate, the outer surface portions of which in the Relative rotation between the inner and outer body successively in sealing contact get with the inner surface or the running surface of the outer body cavity, and in which each middle section also consists of a contoured sealing plate, their outer surface sections continuously with the running surface during this relative movement get into sealing contact.

In the figures, corresponding parts are indicated by the same Reference numerals denoted. There are several parts in the various figures appear and often several identical parts are shown in one and the same figure are (e.g. apex sections, middle sections, connecting sections, inner bodies, Profiles etc.), is to avoid unnecessary repetition of the designation only a representative number of such parts denoted by numerals.

According to the figures, the rotating mechanism according to the invention has a Outer body or stator lo with a hollow or "piston" - space 12 in which an inner body or

Rotor 14 is arranged. Outer body lo and inner body 14 are rotatable relative to each other. In this rotating system, the axis 13 is the inner body 14 arranged at a distance, but parallel to the axis 11 of the cavity 12 (see Fig. 1 to 6). The inner body 14 has a cross-sectional profile made up of several apex sections 15, several intermediate or middle sections 17 and several connecting sections 19. The individual apex sections 15 are around the axis of the inner body 14 evenly spaced around and equidistant from the axis of the Inner body 14 arranged. As, for example, from the 'ig.

1 to 6, the apex portions 15 have at a given one Mechanism preferably substantially the same contour in each case, although this is not absolutely necessary. The middle sections 17 are likewise around the axis of the inner body distributed around the same distance from each other and equally far away from this axis, with all central portions of a given rotating mechanism preferably, but not necessarily, have substantially the same contour (See e.g. Figs. 1 to 6).

It can be seen that each middle section lies - preferably in each case with the same distance - between two apex sections 15. One between middle section 17 and a connecting section 19 lying at an apex section 15 connects these Sections with each other.

The inner surface or profile 20 of the peripheral wall, i.e. the tread of the outer body 10 determines the cross-sectional shape of the cavity 12. From FIGS. 1 to 6 it can be seen that the profile 20 consists of several pages or segments in one Number which is the total number of the apex portions 15 of the inner body 14 exceeds by one.

From FIGS. 7A to 7F it can be seen that during the relative rotation between outer body 10 and inner body 14 about their respective axes of each apex section 15 is in constant sealing contact with the profile 20. From the same figures it can also be seen that each predetermined central section 17 is periodically in sealing contact with the profile 20 and at other times during the relative rotation periodically released from profile 20. For example, in Fig. 7 is the one in the upper left Quadrants of the cavity 12, the central section 17 illustrated separated from the profile 20. According to Fig. 7B, the same middle section is further separated from the profile 20, however, due to its clockwise rotating movement, it has itself immediately Moved up to a point at which a sealing contact with the profile 20 takes place. Figures 7C and 7D illustrate this same central portion in successive ones Stages of its periodic sealing contact with the profile 20. According to FIG. 7E is this middle section no longer in sealing contact with the profile 20, rather it has just separated from the profile 20 due to the relative rotation. So it is It is readily apparent that this central section 17 is in the course of the relative rotation separated from the profile 20 during a predetermined part of the rotary movement (7gl FIG. 7F) remains in order to then restore the sealing contact in the same periodic manner. From FIGS. 7A to 7F it can also be seen that in a preferred embodiment, in which the central portions of the inner body 14, as shown, each in essential have the same contour at all times during the relative rotation between the bodies 10 and 14 at least one of the central portions in periodic sealing contact with the profile 20 stands. This is achieved in that with this mechanism a middle section begins its periodic sealing contact at a point in time at which another middle section just periodically emerges from the sealing contact begins to move out.

There is yet another feature shown in Figures 7A through 7F in that the connecting portions 19 at no time during the relative rotation come into sealing contact with the profile 20 between the bodies 10 and 14.

The connecting sections 19 can therefore have any cross-sectional shape, such as a substantially flat surface or an appropriately recessed one Have surface as long as they do not cut the profile 20 in such a way that the Rotational movement between the bodies 10 and 14 is hindered or prevented. the end the same reason, the shapes of the connecting sections need a given Inner body 14 not to be identical to one another, although of course the Use of a symmetrical, well-balanced inner body is generally preferred will.

A particularly important feature of the invention is that due to the periodic sealing contact and separation of each middle section with the from the profile 20 during the relative rotation between the inner body 14 and the outer body 10 very special and particularly advantageous volumetric displacement properties guaranteed. For example, they are through during this relative rotation the outer wall of the inner body 14 and the profile 20 formed chambers variable Volume periodically subjected to a subdivision or separation, whereby a pre-existing individual Chamber is divided into two chambers, which merge into one another or unite with one another as the rotation continues so that a single chamber is formed again. This feature can be for example from Figs. 7B, 7C, 7D and 7E, in Fig0 7B is the chamber 12a at their (lateral) ends through the seal contacts between profile 20 and the two adjacent vertex sections 15 set. 7B represents the adjacent central section 17 does not produce any sealing. As soon as the Position according to FIG. 7C is reached, on the other hand, the chamber 12a is due to the sealing contact, which took place between the facing central section 17 and the profile 20 has, divided into two smaller chambers 12a and 12b. When moving out of position According to FIG. 7D, the chambers 12a and 12b go into that according to FIG. 7E (FIG. 7D) again into a single larger chamber 12b (FIG. 7E).

From Fig. 7E it can be seen that just a new chamber 12a due to the Sealing contact has arisen through another central section 17, wherein this chamber when passing through, for example, the work stages according to FIG. 7F and 7A becomes a chamber similar to chamber 12a of FIG. 7B, which according to FIGS 7C and 7D is again divided into smaller chambers 12a and 12b.

Figures 7A to 7F illustrate yet another advantageous one Feature of the invention, namely the application of a definition or control by internal gears.

More precisely, there is a smaller gear wheel or scoring 16, which is axially is arranged to the inner body 14 and coaxially aligned with him, making possible a trochoid-like orbital movement with the adapted, toothed inner circumference an inner ring gear engaged axially to the cavity 12 of the outer body arranged and aligned coaxially on this is. Obviously are this pinion 16 and this ring gear 18, as shown schematically in FIGS. 7A to 7F are shown, normally closer to one axial end of the outer body 10 and the inner body 14 cooperating therewith (i.e. closer to the Drawing plane according to FIGS. 7A and 7F as the profile of the cavity 12 and the inner body 14 according to FIGS. 7A to 7F), with another to ensure best results Pinion 16 together with a further ring gear 18 at the other axial end or

on the other end face of the same outer body 10 and the inner body 14 are provided, namely further from the plane of the drawing according to FIGS. 7A to 7F removed0 Here the two pinions 16 and the inner body 14 are coaxially aligned with one another, wherein the inner body is a zone or a location between the zones or locations of the Pinion 16 takes in front of and behind him. Each pinion (regardless of whether two pinions or only one pinion are provided) is not by means of one in FIGS. 7A to 7F shown shaft (cf. the crankshaft 27 that can be used for this purpose according to FIG. 15) connected to the inner body 14 in such a way that this pinion is associated with The shaft and the associated inner body revolve as a unit. Regardless of whether a or two ring gears are used, the ring gear 18 is preferably stationary or stationary mounted, i.e. it preferably does not turn itself, although Arrangements are possible in which the ring gear rotates relative to the pinion. If two ring gears 18 are used, these and the outer body are hollow all coaxially aligned with one another, the outer body having a zone or a location between the zones or locations of the ring gears 18 in front of and behind him occupies. To simplify the illustration of pinion 16 and ring gear 18 are this shown in the figures as having sawtooth-shaped teeth wheels, while in practice, of course, any type of meshing Gears can be used which allow the desired trochoid-like rotation.

According to FIGS. 7A to 7F, the trochoid-like relative rotation is used between Pinion 16 and associated ring gear - by means of appropriate dimensioning, Arrangement and alignment of these elements - in addition, a compulsion or a control to the simultaneous trochoid-like relative rotation between the inner body 14 and Outer body 10, which takes place in the cavity 12 to exercise. As a result, torsional forces premature wear in the absence of this control or this compulsion the contact sections of the inner wall of the outer body as well as apex and / or Midsections of the inner body could be kept under control and partially through the interaction between the pinion and the associated ring gear annihilated0 The used expression "Innenzabnradsteuer" is intended to mean this special one Denote type of determination or control, the term "internal" in the sense should be understood that the definition or control of the pinion through his Arrangement takes place within the ring gear, this definition or control acts at least partially mechanically on the inner body, while this at the same time revolves in the cavity of the outer body. Of course you could do this control or definition as well as "external control" if one assumes that this constraint on the ring gear due to its outer position relative to the pinion is exercised. In any case, this arrangement creates stress concentrations controlled at the sealing points between inner body 14 and profile 20.

In fact, if the parts are manufactured accordingly, these bearing loads can occur almost lifted and the seals between the inner body 14 and Profil7a0llein be maintained by a lubricant film0 Figures 8A through 8F illustrate one way on which the preferred geometric configurations can be developed in the design of the devices according to the invention. Although these figures use this technique in conjunction with a system with three vertex sections 15, the same general procedure can readily be applied to developing or defining preferred configurations for systems with each use any convenient number of apex sections, with the preferred Embodiments of the invention using this preferred geometric Configurations possesses the inner surface of the peripheral wall or the running surface of the Outer body cavity essentially has a profile that is defined by the radial direction extreme points of a series of hypotrochoid curves which are determined by the row of dots describing a vertex section of the inner body is outlined, this tracking of the row of dots with a trochoid-like circumferential inner body occurs while the axis of the outer body served as the reference base. As a result, in these preferred embodiments has the outer surface of the inner body (with the exception of the connecting sections) essentially the profile that is created by the in the radial direction innermost points of the epitrochoid curves is determinedf which are traced by the series of points which form the inner surface of the peripheral wall circumscribe the outer body cavity, this tracing the row of dots at trochoidal orbital movement of the outer body with an axis serving as a reference base of the inner body takes place. Illustrated to clarify the foregoing Fig0 8A shows a body with an arbitrary shape, but three equidistant from one another arranged and equidistant from the axis 13 of the inner body having apex sections 15 has. In FIG. 8A, the axis 11 is also expressed geometrically -to be generated or to be constructed outer body shown. The axes 11 and 13 are in a suitable, arbitrarily set Distance laterally or in the transverse direction away from each other. Fig. 8B illustrates the result of the trochoidal rotation of said body with as a reference base serving axis 11, doho the axis of the outer body, its inner profile (cavity) should be developed.

To simplify the illustration, only a limited one is shown in FIG. 8B Number of successive positions of said body illustrated. Of course, a significantly larger number of such positions can be selected be to very close partial distances of the rotary motion to determine points for to achieve follow-up or pursuit. Fig0 8C illustrates the tracing, which are created by connecting (drawing through) the outermost points in the radial direction on the apex portions 15 in each individual rotational position in this developing process results. This defines the profile 20 of the outer body cavity. The next The step in this conceptual or geometric process is to use the To consider profile 20 as a cavity of a final (tangible) body, its configuration, with the exception of the profile, is unimportant for the present purpose is. It only needs to be mentioned that this outer body is now with The axis 13 of the inner body serving as a reference base is rotated like a trochoid will. Fig. 8D illustrates the profile 20 as it is based on a preselected Number of consecutive positions during this rotary movement results. In this case could in turn have a much larger number of positions between the points shown can be provided in order to allow a larger number of to be tracked to guarantee points to be followed up; Nevertheless, it can be seen from Fig0 8D, that by connecting the innermost points in the radial direction of this series of epitrochoid curves an outer profile with a symmetrical three-sided shape 21 is determined, the three Has apex sections 15, which for all Purposes and in each Respect to the apex portions of Fig. 8A. That also Intermediate or middle sections 17 having form 21 effectively represents a preliminary stage of the inner body of the system to be developed. As mentioned, the connecting sections between the apex sections 15 and the middle sections 17 with the profile 20 do not come into contact with the seal. Therefore, Fig. 8E is one of many Illustrates possibilities on which the form 21 by radial recess of the same in the areas in which the connecting sections are to be located for Shape of the inner body 14 is modified. In the form shown, the connecting sections are 19 of the inner body are substantially linear segments which are adjacent to each other Edges or edges of an apex section 15 and a middle section 17 with one another associate. In Fig. 8F this inner body 14 is in the profile 20 of the outer body cavity 12 drawn in, the outer body itself not being illustrated in more detail, because, as mentioned, his only part that is essential for the present purpose is his Inner wall, i.e. the tread is.

As can be seen, the inner body 14 and the profile 20 in FIG the relative positions according to FIG. 8F five spaces between them, FIG. 8F one shows of numerous rotational positions in which this device simultaneously there are two sealing contacts between two different middle sections (cf. Points a and b, which in a three-dimensional device according to the invention in practice, of course, linear sealing lines running in the axial direction represent) 0 Since the apex sections are always in sealing contact with the profile 20, these result in three sealing points (as in the illustrated embodiment there are three vertices) in connection with those indicated at a and b Sealing points in the position according to Fig. 8F five sealing points, which in turn form five rooms or chambers. During most of the rotation in a three-vertex system, there are four such chambers while five chambers are formed periodically} when a vertex section in a "corner" of the profile 20 (see. Fig. 8F) is centered, while in the further relative rotation one of these chambers disappears. This abolished chamber goes of course into an adjacent chamber. Similar considerations apply to the invention Systems with two, four or more apex sections, although this depends on the number of Rooms or chambers is different in each case. In a system with two apex sections For example, there are normally three chambers, while periodically one temporary fourth chamber occurs.

Further advantageous features of the invention relate to the extremely favorable slot control, which can be found in modified embodiments the invention can achieve.

These tax relationships, the periodic opening and closing of the chambers each having a variable volume opposite the outside of the Allow outer body cavity are shown in FIGS. 9A to 9F, iOA to 10C as well 11 and 12 illustrated. Although these figures refer to a device with referring to three vertices, it is readily apparent that the above The principles described also apply to devices according to the invention with two or four or more vertex sections are applicable and valid for it.

Referring to Fig. 11, in a preferred slot control system of the present invention Rotary mechanism at each axial end or each end face of this mechanism in each case a control orifice plate 30 is provided which spans the ends of the chambers seal with variable volume. Apart from the control openings and explanatory Channels the inner surfaces of the plates 30 are under manufacture a seal in sliding contact with the axial ends, i.e. the end faces of the inner body 14. If desired, between the mutually movable surfaces thin films of lubricant, annular sealing elements or other suitable sealing arrangements or materials be provided. The number of provided in each control plate 30 Control orifices 35 is normally one larger than the number of apex sections 15 of the inner body 14o The number of control channels 25 on each end face of the inner body however, normally corresponds to the number of apex sections 15 of the inner body 14. The control ports 35 are equidistant from the axis of the outer body cavity 12 arranged radially around this axis. Generally these are control ports distributed at more or less even distances from each other and arranged in such a way that that they are periodically in accordance with the control channels in the operation of the rotating mechanism 25 of the inner body 14 arrive.

In FIGS. 9A to 9F, only one such control opening and are in each case one such channel at each end of the illustrated system is illustrated to in this way to simplify the relevant representations and understanding to facilitate the relevant circumstances0 In practice, however, are at each Several control openings and control channels are provided on the front side (see FIG. 11). In 9A to 9F is an end plate 30 (not shown) on the viewer closer axial end or

Front face pierced control opening 35 with 35f and one in the the same end face of the inner body 14, the pierced control channel 25 is denoted by 25f, where the letter "f" of the numbers 25f and 35f according to FIGS. 9A to 9F and FIG. 10A and 12 indicates that these elements are located on the "front" Axial end or the end face of the rotor (or the control slot). Likewise, in FIGS. 9A to 9F show the control opening 35 in the end plate 30 (not shown) at the axial end further away from the viewer with 35r and the one facing away The end face of the inner body 14 denotes the pierced channel 25 with 25r, wherein the letter "r" in Figures 9A to 9F and in Figures 10C and 12 refers to that these elements are at the "rear" axial end or the rear Face. For the sake of clarity in FIGS. 9A to 9F as well as of Fig. 12, openings 35f and channels 25f are in solid lines and the control opening 35r and the channels 25r are shown in dashed lines. The end face of the inner body 14 having the channels 25f is in sliding and sealing engagement with the inner surface of plate 30 at the "front" axial end the rotating device, while the end face of the inner body provided with the channels 25r 14 in sliding and sealing contact with the inner surface of the plate 30 at the "rear" axial end of the device is. 9A to 9F (and FIG. 12) are therefore all of the variable volume chambers such as chamber 12a etc. by the sealing contact between the inner wall or profile 20 of the outer body 10 and apex sections as well periodically also between this inner wall and the central sections of the inner body 14 and also by the sliding sealing contact between the inner end faces of the plates 30 and the facing end faces of the inner body 14 from one another separated. As a result, a compressible working fluid can be variable in these Volume-owning chambers 12a etc. are introduced or derived from them, if either the channel 25f to the control port 35f or a channel 25r to a Control port 35r is aligned. At all other times during the relative rotation between inner body 14 and outer body 10, if due to the Absent no entry or exit of the fluid from such a match a certain chamber with variable volume is possible, this is done in this chamber contained working fluid either expanded or compressed, depending on whether the volume of the chamber in question in the given section of the relative rotation enlarged or reduced.

9A to 9F show the individual states or stages of the continuous, clockwise relative rotation of the inner body 14 in Profile 20 or shown on the tread. The inner body 14 runs from the end visible in these figures, like a trochoid around its own Axis essentially clockwise. Seen from the other front area the inner body would, however, rotate counterclockwise. In the position according to Fig0 9A is neither between the channel 25f and the control opening 35f nor between Channel 25r and control port 35r coincide, but channel 25f and control port 35f are about to coincide with each other.

The chamber 12a is fully closed or sealed in FIG. 9A. During the rotary movement into the position according to FIG. 9B, the control opening 35f is opened the match with the channel 25f opened, the opening size on this Point is significant. When rotating from the position shown in FIG. 9A to the position According to FIG. 9B, the channel 25r does not yet come into alignment with the control opening 35r, although these passages are comparative in this section of the orbital movement lie close to one another when moving from the position shown in FIG. 9A to the position according to FIG. 9B, the volume of the chamber 12a has decreased. When turning further the control opening opens from the position according to FIG. 9B into that according to FIG. 9C 35r due to the correspondence with the channel 25r, while the control opening 35f due to the further Agreement with the channel 25f further remains open, the volume of the chamber 12a has further decreased and a new chamber 12b has formed with increasingly increasing volume. Approximately at the point in time at which the chamber 12b forms as a separate chamber Channel 25r and control port 35r initially in mutual correspondence. At the The transition from the position according to FIG. 9C to the state according to FIG. 9B remain Control ports 35f and 35r wide open, where V is the opening size between channel 25f and control opening 35f reduced in size in preparation for closing and the The size of the passage between the channel 25r and the control opening 35r increases. In addition, has the chamber 12b continues to enlarge, while the chamber 12a a further decrease in volume has experienced. On further rotation from the position according to FIG. 9D into that According to FIG. 9E, the control opening 35f is closed, while the control opening 35r remains open with increasing passage size, the chamber 12b continues to enlarge and chamber 12a has disappeared as a result of its transition into chamber 12b. Obviously the control port 35f is closed at about the time when the Chamber 12a ceases to exist as a separate or independent chamber. In the further rotary movement from the position according to FIG. 9E into the position according to FIG. 9F, the control opening 35f remains closed, while the control opening 35r is flat is closed so that the chamber 12b is now in a closed or completely sealed state. It also has the volume the chamber 12b further enlarged.

FIGS. IOA to IOC illustrate the three-dimensional one even more clearly Shape of the inner body 14 and in particular the relative spatial arrangement of the control channels on the opposite end faces of the inner body. The section according to Fig0 10A is at the "front" axial end of the inner body, i. at the one closer to the viewer Front face out. Of the The same general cross-section according to FIG. 10A is, however, over a certain finite distance depending on the depth of the control channels 25f from the front The end face of the inner body is present up to the central section according to FIG. 10B. The section according to Fig.

10B is passed through the center of the inner body 14, i.

halfway between the front face (Fig. 10A) and the rear End face (Fig. 10C). This general cross section according to FIG. 10B also remains unchanged over a finite distance, i.e. over a distance that a predetermined distance from the central plane in the direction of the viewer or extends the drawing plane and away from it. Fig.? OC, on the other hand, is a through the "rear" axial end or the rear end face of the inner body 14, i.e. the axial end, further away from the viewer, is a cross-section. Of the general cross-section according to Fig0 10C is again over a finite, of the depth of the control channels 25r depending distance or zone away from the rear end face the same towards the middle section according to FIG. 10B. Usually the channels own 25f and 25r have the same depth and shape, and the difference lies in their spatial Arrangement in and opposite the inner body 14.

This spatial arrangement can possibly best be achieved by doing this explain that the sections according to Fig. 10A to IOC as three-dimensional, flat 1 slices each of the same thickness can be considered. These three "slices" have it the outline according to Fig0 10A, 10B or Fig. IOC. Now you think of the three "discs" assembled into a layered construction, in which the "disk" according to 10B is located between the "slices" according to FIG. 10A and IOC and all "slices" remain in the same angular alignment to one another as the sections according to Fig. 10A to IOC. In this way, a three-dimensional model of an inner body or 0 rotor 14 clarify0 is evident with none there is a direct connection between one of the channels 25f and one of the channels 25r, since these channels, although superimposed, are axially spaced apart from one another by a distance are separated, which in this three-dimensional model of the thickness of the "disk" corresponds to Fig. 10B, which effectively acts as a wall that the channels 25f and 25r separates from one another in the axial direction. It is also assumed on the basis of this Model can be seen that the axially separated channels 25f and 25r at a system having three vertices are arranged or oriented in such a way that that their longitudinal axes are axially spaced apart from one another cross at right angles0 For example, intersect the longitudinal axis of the channel 25f in the lower portion of Fig. 10A and the longitudinal axis of the channel 25r in the lower part of Fig. 10C to each other at a right angle. The same goes for the longitudinal axes of channels 25f and 25r in the upper left quadrant of Fig. 10A and Fig. iOC and for the longitudinal axes of channels 25f and 25r in the upper right quadrant of Figures 10A and 10C, respectively. This axially separated, right-angled intersection these longitudinal axes and in particular the relative orientation and arrangement of all Channels 25f and 25r and all control openings 55f and 35r can now be based on from Fig0 12 easily recognize.

In FIG. 12, the inner body 14 is in the same position as in FIG Fig. 9A is shown, but with all six control channels and all eight control openings or slots of the rotating device are shown in the illustrated embodiment there is in each case a channel 25f in the longitudinal direction at one of the apex section in question 15 associated connecting section 19, each channel 25f having an open end or has a mouth which the other, the relevant apex section 15 associated connection section is facing. For example let us consider the control channel 25f in the lower right quadrant of FIG.

This channel 25f runs approximately parallel to the connecting section 19, which is on the right side of this figure, and this channel 25f opens directly on the connecting section 19, which according to FIG. 12 is the open or mouth end this channel 25f forms. The same positional relationship to the connecting section facing in each case also applies to the other two channels 25f and to all three channels 25r according to Fig. 12o From Fig. 12 it can also be seen that during the rotary movement successive Apex sections 15 in a predetermined, identical position relative to the profile 20 each of the successive control channels 25f each have the same position occupies as the immediately preceding control channel, and the same is also true for the successive control channels 25r. If the inner body 14 according to Fig. 12 rotates, for example, clockwise so that the apex portion 15 at the top of Fig. 12 to the position of the apex portion in the lower right The quadrant of FIG. 12 is taken by those located at this first vertex section Channels 25f and 25r are currently still from the channels 25f and 25r on the second apex section assumed positions, at the same time move in this clockwise direction following rotation of the inner body, the channels 25f and 25r on the one on the left Page of Fig. 12 to the positions indicated by the Channels 25f and 25r respectively at the top of FIG. 12 have been cleared. An exact Review of FIG. 12 and application of the principles disclosed therein should be understood thus enable those skilled in the art to develop such inner bodies or rotors with appropriately arranged control channels regardless of the number of the apex sections provided in such inner bodies and apply. In this context it should be pointed out that the inner body resp. Rotor 14 the device shown in perspective in FIG the arrangement of the control channels illustrated in more detail in FIGS. 10A, 10B, 10C and 12 and that the control openings or

slots and control channels of these preferred embodiments in 9A to 9F, 10A to IOC, 11 and 12 are illustrated together, From Fig. 12 also shows that in the illustrated embodiment, each plate 30 (see. Also FIG. 11) has four control openings 35, so that at each axial At the end or each end face of the inner body 14, four storage openings 35 with three Control channels 25 cooperate. In the illustrated embodiment, these are Control openings from the axis of the outer body cavity each equidistant and distributed around their axis at equal distances from one another. The radial distance these control openings from the axis of the outer body cavity is large enough around the control openings 35 periodically with the control channels with which they interact, to get in agreement. With reference to FIG. 12 in connection with the the above disclosure, the person skilled in the art should therefore be able to the rotary systems according to the invention using the disclosed control relationships or to design times and apply them in practice.

From the above description it is readily apparent that the rotating mechanism of the present invention readily lends itself to use in a variety of ways is adaptable for purposes, for example on pumps, fluid motors, heat engines, Compressors and the like. As mentioned at the beginning, is a salient characteristic of the rotary mechanism according to the invention its particularly good suitability for according to the Stirling principle working internal combustion enginesO In this field of application, the inventive Rotary mechanism has the unique advantage that it has volumetric characteristics respectively.

Guaranteed characteristics that are close to those of an idealized Internal combustion engine lie. This peculiarity can be seen in more detail in FIGS. 13 and 14 emerged.

Fig. 13 schematically illustrates various stages of the simultaneous Rotary movement of two rotary mechanisms according to the invention, which are used as a Stirling volume displacement machine interact with each other. A typical displacement arrangement of this type, which according to the principle described with reference to FIG. 13 works, is shown in Fig. 15 in perspective Illustration illustrated. In the embodiment shown in FIGS are two rotary mechanisms of the type shown in Fig0 11 and 12 at a distance from each other one behind the other arranged with their respective housings (i.e. the outer bodies 10) axially on top of one another aligned and their inner body 14 rigid with a common eccentric crankshaft 27 are connected.

The inner bodies 14 are attached to the crankshaft 27 in such a way that that one inner body is angularly displaced by 1800 at any time compared to the other is. This angular displacement is illustrated in FIG. 13, in which the upper The series of representations (i.e., Figures 13A through 13H) represent a series of sequential rotational positions of the inner body 14 of the one rotor unit in the series arrangement and the lower row of representations (dos. Fig. 13AF to 13HF) the corresponding sequential rotational positions of the inner body 14 of the other rotor unit illustrate in the row arrangement. Obviously, the angular displacement remains between the individual inner bodies in each of the successive positions each constant at a size of 1800 (cf. e.g. Fig. 13A with Fig. I3AF, Fig0 13B with Fig. 13BF, Fig. 13C with Fig0 13CF, etc.). So the inner bodies are in everyone Spare a moment at an angle of 1800 to each other The two runner units are therefore arranged in balancing relation on the eccentric crankshaft so that that a complete state of equilibrium of the moments of force a neutral axis is reached.

In the illustrated embodiment of FIGS. 13 and 15 are all Control openings or slots in the plates 30f and 30r of the two rotor units arranged in the manner explained in connection with FIG. The in Fig. 15 and 13 therefore shows the Stirling displacement machine in each of the two Plates 30f each have four control openings 35f, which are in the same position are located like the control openings 35f according to FIG. 12. The machine according to FIG Fig0 15 in each of the two plates 30r has four control openings 35r, the The position corresponds to that of the control openings 35r according to FIG. The control openings 35f and 35r according to FIG. 15 are for the most part not visible in this figure because they are enclosed by the distributors or collectors 40f and 40r to be explained in more detail below are. It can be seen that in the two rotating mechanisms according to FIG. 15 enclosed inner body or motors each control channels according to the Channels 25f and 25r according to FIG.

The system shown schematically in Fig. 13 has a heat output or discharge device 32 (sometimes also as "low-temperature storage" or "heat sink" (heat dump)), a Rewgenerator 33 (sometimes also as a heat accumulator " or thermodynamic sponge ") and a heat supply device 34 (sometimes also known as high-temperature storage "or" heater ").

The mode of operation of the system according to FIG. 13 (dos. Of a system, at the two inner bodies each have three apex sections) comprises five at the same time running cycles, each of which has four separate phases or cycles, namely a charging cycle, a compression cycle, a regeneration cycle and an expansion stroke. In operation, these four cycles all run simultaneously, but in a different cycle each time. One of these measures also occurs - namely the loading - in two cycles at the same time. The respective clock relationships are given in Table I in which the operations of the four in the five cycles (Cycle A to E) occurring phases or cycles depending on the total number of degrees the angular rotation of the inner body are shown. In the operation of such a machine it can be seen that there is inevitably a time delay until a predetermined one Amount (control volume) of a working fluid completely from a portion of the Machine (e.g. a first chamber) through another section of the machine (e.g. Control openings, pipes, heat exchangers, etc.) to another section of the machine (E.g. a second chamber) has flowed in. In practice there are therefore cases in which different proportions of a control volume of the working fluid actually are simultaneously subjected to different phases or cycles of the cycle. The transitions from phase to phase or from cycle to cycle are therefore not clearly delimited in practice The following description of the beginning and the end of the various Bars is therefore simplified to a certain extent (for example, the effect of the time delay largely neglected) in order to understand the essential characteristics of the working method to facilitate. For example, the phase or clock transitions are a function the angular rotation in Table I is given by way of example only, so that they should not be construed as fixed and clear dividing lines.

TABLE I Simultaneous cycle sequence with respect to angular rotation 0 ° -90 ° 90 ° -180 ° 180 ° -270 ° 270 ° -360 ° 360 ° -450 ° 450 ° -540 ° 540 ° -630 ° 630 ° -720 ° 720 ° -810 ° cycle A complaint compr. Rain. Expan. Besch. Besch. Kompr. Rain.

Cycle B expan. Besch. Besch. Kompr. Rain. Expan. Besch. Besch. Kompr.

Cycle C rain. Expan. Besch. Besch. Kompr. Rain. Expan. Besch. Besch.

Cycle D compr. Rain. Expan. Besch. Besch. Kompr. Rain. Expan. Complaint

Cycle E loading compr. Rain. Expan. Besch. Besch. Kompr. Rain. Expan.

Loading = loading (filling) compr. = Compression rain. = Regeneration Expan. = Expansion As Table I shows, the four phases run or cycles of a given cycle always in the following order: Loading (Filling), compression (compression), regeneration and expansion. There is also it can be seen that in the device described, the loading or filling takes place during a rotation of the two inner bodies or rotors through 180 °. the the other three phases or clocks take place during an angular rotation held by 900 of the inner body. In other words, it encompasses a complete cycle a total of 4500 angular rotation.

The fact that emerges from the table is of particular importance, that at any time the expansion stroke takes place in one of the cycles, because this expansion stroke forms the actual work cycle.

To illustrate this mode of operation, FIG. 13 shows in detail illustrates the processes that take place during a machine cycle according to the Cycle A according to Table I take place. Obviously, according to FIG. 13 the following rotational angle positions in the game: 13A and 13AF - 0 ° 1, and 13BF -13C and 13CF - 180 ° 13D and 19DF - 2700 13E and 13EF - 315 ° 13F and 13FF - 360 ° 13G and 13GF - 450 ° 13H and 15HF -In the following explanation, which only refers to referring to any of the five simultaneous cycles will only apply to those Currents, chambers and associated elements or facilities are referred to, which are in play in the cycle concerned0 Although Fig. 13, for example shows several chambers, only certain of these chambers are displayed to the involved in the explanatory cycle, so that only reference is made to these chambers will. The other chambers take part in the other cycles on various occasions.

At the start of operation in the system of FIG. 13, a in the chamber 12a according to FIG. 13A contained, hot, compressible working fluid via the regenerator 33a introduced into the chamber 12af according to FIG. 13AF. While the fluid flows through the generator, part of its thermal energy is extracted and used for later use saved, which at the same time marks the beginning of the loading cycle represents. Since the inner bodies or rotors are arranged in series continuously in If you turn clockwise, this transfer or flow of the working fluid lasts further on, this flow being caused by the progressive decrease in volume of the chamber 12a (see Fig.

13A, 13B and 13C) and the progressive increase in volume of the Chamber 12af (see. Fig. 13AF to 13CF) is favored.

In the transition from FIGS. 13A and 13AF to FIGS. 13C and 13CF the volume of the chamber 12a decreases continuously and progressively, while the Volume of the chamber 12af increases continuously and progressively, and since the sum of these changing volumes remains comparatively constant, the approaches Volume displacement characteristics of this system closely match the volumetric characteristics according to the ideal Stirling heat engine in their corresponding work stages Figures 14A, 14B and 14C. The positions of Figures 13C and 13CF represent the end of the charging cycle and the start of the compression cycle.

When moving over the positions shown in FIGS. 13C and 13CF in addition, the alternating flow between chamber 12a and chamber 12af is ended, and the working fluid just received from the chamber 12af is discharged into the heat dissipation device 32 let in, which the working fluid by further heat withdraws, which is discharged from the system, then transferred to the low-temperature storage tank. This flow shown in FIG. 13DF corresponds to that in the Stirling engine occurring process according to Fig. 14D. As can be seen, the flow is limited 13DF, which during the rotary movement from the position according to FIG. 13CF in the position according to Fig.

13DF takes place, caused by the reduction in volume of the chamber 12af. Furthermore, the heat dissipation device 32 remains for the passage during this phase of the working fluid effectively blocked because the downstream side leading to the chamber 12bf Slot or control opening is closed at this time. As a result, will the working fluid is compressed in the chamber 12af and in the heat dissipation device 32, and this compression is due to the release of thermal energy from the working fluid to the heat dissipation device 32 supported. Figure 13DF illustrates the end of the Compression stroke.

Figure 13EF illustrates the flow that occurs during the regeneration phase or the regeneration cycle takes place, which takes place at the end of the compression cycle (Fig. 13DF) begins and lasts until the beginning of the expansion stroke (Fig. 13FF).

On further rotation from the positions according to FIG. 13D and FIG. 13DF namely, in the position according to FIG. 13E and FIG. 13EF, the pressure in the chamber 12bf leading control port opened, whereby according to Fig0 13EF an alternating flow of the introduced compressed working fluid from the chamber 12af into the chamber 12bf will. The compressed working fluid flows out of the chamber 12af via the Heat removal device 32, the regenerator 33a and the heat supply device 34 into chamber 12bf. Obviously, chamber 12bf learns at this point of the cycle an increase in volume while the volume of the chamber 12af decreases, thereby ensuring a volumetric process which is the ideal process 14E is closely approximated. During the Flow around between the chambers 12af and 12bf will continue to receive the heat energy that during the alternating flow process of the charging cycle was stored in the regenerator 33, to the compressed Fluid delivered as it flows through the regenerator. aside from that further heat energy is transferred to the compressed working fluid while this passes through the heat supply device 34 on its way to the chamber 12bf. The hot, compressed working fluid flowing into the expanding chamber 12bf therefore has a high level of own energy, which can be converted into usable work performance leaves. On further rotation from the position shown in FIGS. 13E and 13EF into that 13F and 13FF, the alternating flow is within the mechanism of FIG the chamber 12af to the chamber 12bf until the position according to Fig.

13F and 13FF is reached, at which point the outflow is off the chamber 12af because of the closing of the control opening, which allows an outflow from the Chamber 12af allowed to be terminated. The closing of this control opening is marked the end of the regeneration cycle.

On further rotation from the position according to FIG. 13FF into the position 13GF begins the expansion phase or the expansion stroke, wherein in the Heat removal device 32, the regenerator 32a and in the heat supply device 34 contained hot, compressed working fluid continues to flow into the chamber 12bf, while their volume increases.

As with this continued flow, the fluid from the heat supply means 34 flows into the chamber 12b, the fluid is immediately before his Entrance into this chamber continues to be supplied with thermal energy. By expanding this Working fluid in the chamber 12bf thus becomes a work output in the form one on the inner body 14 (and on the crankshaft not shown in FIG. 13 27) transmitted torque reaches 0 that in Fig. 13F and 13FF The illustrated section of the cycle thus represents the beginning of a positive work process, i.e. the expansion phase, in the system, this process continuing until the rotational positions 13G and 13GF are achieved. This process corresponds to the work expansion phase of the ideal Stirling cycle, which begins at FIG. 14F and ends at FIG. 14G.

When the positions according to FIGS. 13G and 13GF are reached, the Machine completes a full cycle, which is in the positions shown in FIG. 13A and 13AF began. The positions shown in FIGS. 13G and 13GF therefore represent simultaneously represents the beginning of a new cycle corresponding to the cycle described above. This means that the position according to FIGS. 13G and 13GF marks the beginning of the loading or filling phase represents, in which the hot, compressible, in the chamber 12bf according to FIG. 13GF contained working fluid in the manner shown by the Regenerator 33b is performed, in which part of the thermal energy of the fluid removed and saved for later use. Flows from the regenerator 33b the fluid then enters chamber 12b (Figures 13G and 13H). It can thus be seen that which occurs in the course of Figures 13G and 13GF to Figures 13H and 13HF Operations correspond to the operations involved in transitioning from FIGS. 13A and 13AF take place on Figures 13B and 13BF, and that all of that described Duty cycle repeatedly repeated0 In summary, it can be said that in operation a Stirling heat engine using two rotating mechanisms of the previous described type, in which each inner body 14 has three apex sections has five cycles or

Bars of the type described do not influence each other at the same time Way take place so that a continuous Power output is guaranteed. In other words: these five cycles or clocks run at all times to different (offset from one another) phases (see. Table I), so that constantly a positive power output takes place in one of these cycles.

Fig. 15 illustrates the manner in which the fluid ve division to achieve the flow of working fluid between the mechanisms and in this can be effected during operation of the machine. In the illustrated embodiment lines or distributors or collectors 40f are attached to the plates 30f in such a way that that they are above the four control openings 35f of each of these plates, wherein in Fig. 15 only partially shows such a control opening. In a similar way are closed lines or distributors or collectors 40r so on the plates 30r attached so that they the four, not shown in Fig. 15 control openings 35r cover each plate 30r. The headers 40f and 40r each serve as separate ones Inlet and outlet channels for the individual openings 35f and 35r. With others In other words: all four control openings 35f and 35r of a given plate are through a collector 40f and 40r separated from each other.

The four collectors thus together form sixteen channels, of which one at a time leads to or from one of the sixteen control openings. Of simplicity For the sake of this, these channels are each designated in Fig. 15 with Roman numerals I to XVI, the four channels not visible in FIG. 15 being arranged as follows: channel V is on the left panel 30r, approximately at the back of channel I and essentially in alignment with channel VII (only slightly offset, as in the case from channels I and III, where channel VII is slightly higher than channel V); Channel VIII is located on the left panel 30r, approximately behind channel IV and more generally Alignment to channel VI, but slightly offset from it (see channels II and IV); Canal XIII is located on the right plate 3Or, approximately at the rear from channel IX and generally aligned with channel XV, but slightly offset from it (see channels IX and XI); Channel XVI is on right plate 30r, approximately at the rear of canal XII, generally on canal with a slight offset XIV aligned (see channels X and XI).

Each of these individual channels is by means of a suitable one, not shown line or a pipe or the like. either with the inlet or outlet of the Regenerator 33 (Fig. 16) or with the inlet or outlet let one out of the heat dissipation device 32, the regenerator 33 and the heat supply device 34 existing system (Fig. 16), in which the devices 32, 33 and 34 are arranged in series and the regenerator 33 is located between the other two devices.

Fig. 16 illustrates a heat transfer assembly that includes a Series connection of the heat removal device 32, the regenerator 33 and the heat supply device 34 has.

That without passing through the devices 32 or 34 the regenerator Working fluid flowing through 33 enters at an inlet 38 and exits an outlet 39 off. The working fluid to be conducted through devices 32, 33 and 34 passes at an inlet 36 into this system in order to flow out of it via the outlet 37. In the interior of the regenerator 33 are ribs 45 or similar heat transfer bodies or elements are provided, which absorb the heat quickly depending on the case or able to release and which are arranged or designed so that the fluid flowing in at inlet 38 to flow through regenerator 33 and able to leave it at outlet 39. Since in the regenerator 33 heat transfer resp.

exchanges take place, the regenerator is normally with a suitable jacket or insulation Mistake, to avoid excessive heat loss in the system.

In the construction of a Stirling heat engine according to the invention using a displacer assembly of the type shown in FIG. 15 becomes four Heat transfer assemblies of the type shown in FIG. 16 are used. The connections between channels I to XVI and these four heat transfer assemblies given in Table II. Obviously there are inlet 36, outlet 37, inlet 38 and outlet 39 of each of the four heat transfer assemblies by attached small ones Letters a, b, c and d marked. For example, the reference numbers relate 36a, 37a, 38a and 39a to the inlet, outlet, inlet and outlet of one of these arrangements. The corresponding parts of another heat transfer arrangement are indicated by 36b, 37b, 38b and 39b, respectively, and so on.

TABLE II Compounds in a Preferred Stirling Heat Engine According to the invention connector of the heat transfer channel support arrangement I inlet 36a II inlet 38b III inlet 36c IV inlet 38d V outlet 37c VI outlet 39a VII Outlet 37a VIII Outlet D9c IX Inlet 38a X Inlet 36b XI Inlet 38c XII Inlet 36d XIII outlet 39d XIV outlet D7d XV outlet 59b XVI outlet 37b in the In operation, a prime mover with the structure described above works on the basis of the above Manner, being subjected to the repetitive phase passes that take place simultaneously in the manner indicated in Table I.

This becomes even clearer if one follows the path which one is given Describes the amount (control volume) of the working fluid through the entire machine. In the following list, therefore, the path to simplicity is followed more closely half with a predetermined amount of that contained in the chamber 12a (Fig. 13A) Working fluid begins.

This initially hot working fluid performs the following steps: 1. Exit chamber 12a 2. Passage through channel IX 3. Entry into inlet 38a 4. Passage through regenerator 33a 5. Outflow via outlet 39a 6. Flow through channel VI 7th entry into chamber 12af 8 exit from chamber 12af 9th passage through channel I 10. Flow into inlet 36a 11o flow through the heat removal device 32a 12. Flow through the regenerator 33a 13. Flow through the heat supply device 34a 14. Outflow via outlet 37a 15. Flow through channel VII 16. Entry into Chamber 12bf 17o exit from chamber 12bf 18o flow through channel II 190 flowing in in inlet 38b 20o flow through regenerator 33b 21 ¢ outflow via outlet 39b 22. Flow through Canal XV.

23. Entry into chamber 12b 24. Exit from the chamber 12b 25th pass through channel X 26th entry into inlet 36b 27th pass through Heat removal device 32b 28th pass through regenerator 33b 29th pass through Heat supply device 34b 30. Exit via outlet 37b 31. Passage through channel XVI 32. Entry into chamber 12c 33. Exit from chamber 12c 34. Flow through channel XI 35. Entry into inlet 38c 36. Pass through regenerator 33c 37. Exit via Outlet 39c 38. Passage through channel VIII 39. Entry into chamber 12cf 40. Exit from chamber 12cf 41st pass through channel III 42. entry into inlet 36c 43rd pass through heat dissipation device 32c 44th pass through regenerator 33c 45th pass through heat supply device 34c 46th exit via outlet 37c 47th passage through Canal V 48. Entry into chamber 12df 49. Exit from chamber 12df 50. Passage through channel IV 51o entry into inlet 38d 52. Passage through regenerator 33d 53. Exit via outlet 39d 54. Passage through channel XIII 55e Entry into chamber 12d 56o exit from chamber 12d 57o flow through channel XII 58. Entry into inlet 36d 59o pass through heat dissipation device 32d 60. pass through regenerator 33d 61. Passage through heat supply device 34d 62. Exit via outlet 37d 63. Passage through channel XIV 64. Entry into chamber 12a.

From step 64, the process repeats itself continuously through the beginning with level 1. From the above list it can be seen that the working fluid is subjected to the same sequence of work steps four times, i.e. the Steps 1 to 16, 17 to 32, 33 to 48 and 49 to 64 while the working fluid flows through the entire machine. It can be seen that this is the specified amount or the control volume of the working fluid is repeated in the course of these work steps subject to the respective changes of state that occur with the four phases or cycles of the Stirling cycle.

The following sequence of work steps is involved: loading compression Regeneration expansion (filling) steps: (1) - (7) (8) - (11) (12) (13) - (16) (17) - (23) (24) - (27) (28) (29) - (32) () 3) - (39) (40) - (43) (44) (45) - (48) (49) - (55) (56) - (59) (60) (61) - (64) It will be apparent to those skilled in the art that the above Explanation regarding the 64 work steps for the operation of the special, explained Stirling engine applies, which has two rotating mechanisms, each with an inner body works with three apex sections0 while with other Stirling machines according to the invention the same sequence of the basic phases resp.

Cycles (charging, compression, regeneration, expansion) occur, depend on the flow guide for the working fluid and the total number of work steps, which are necessary so that the control volume of the working fluid a complete Circulation can be carried out by the machine, depending on the number and type of used Turning mechanisms.

Fig. 17 particularly illustrates a graphical representation advantageous feature of the Stirling volume displacement machine of the type shown in FIG. 15. Figure 17 shows four curves, the top two of which are for performance of the volume displacer according to FIG. 15 and the two lower ones for an ideal Stirling piston engine are valid. In each of these curves is the volume of a specific displacement chamber plotted as a function of time (or the crankshaft angle), corresponding to a Process as described by Graham Walker in "Stirling-Cycle Machines", pp. 10-13, in detail is described. The abscissa indicates the time for each curve, while the ordinates the four curves indicate the volume of the chambers concerned. The top two Curves A and B illustrate the net and total volume changes that occur in the chambers in a volume displacer according to the invention during a complete Duty cycle occur. The loading phase extends from T1 to T2, the compression phase from T2 to T3, the regeneration phase from T3 to T4 and the expansion phase from T4 to T5. The two lower curves C and D illustrate the net or total volume changes that of his ideal Stirling piston machine take place during the same working cycle and in the same time interval (T1 to T5). From these curves it can be seen that the net volume changes between curves A and B show the net and total volume changes during the entire cycle (T1 to T5) between curves C and D are very close to the ideal Stirling engine. In other words: The inventive Volume displacer works in every work phase in a very similar way to the idealized model of the Stirling engine, to which no precise approximation has apparently yet been achieved.

From the foregoing description it can be seen that the preferred Stirling heat engines according to the invention have at least two rotating mechanisms are arranged in counterbalancing relationship on an eccentric crankshaft 27. Usually there are only two such rotating mechanisms on a given one Crankshaft (see. Fig. 15) arranged cooperating with one another. Here are the inner body 14 of the two rotating mechanisms arranged so that they opposite the The crankshafts are twisted by 1800 to each other, i.e. the centroids of these inner bodies are around the common eccentric crankshaft with an angular displacement from 1800 to each other. However, it is also possible to use systems with more than to design two such rotating mechanisms. For example, four rotating mechanisms be arranged on a predetermined crankshaft and oriented so that the one Pair of the rotating mechanisms in the manner previously described to generate torque cooperates on the crankshaft, while at the same time the other pair of these rotating mechanisms also cooperates in the manner described and on the same crankshaft additional torque is generated, so that an increased output power is realized can be. Internal gear control systems are preferably used in the Stirling machines according to the invention of the type described used, as can be seen on the crankshaft each any number of pinions 16 for rotation in the associated ring gears 18 can be mounted. In the device according to FIG. 15, for example, a pinion / ring gear combination be mounted at or near each axial end of the crankshaft 27, two such Combinations to ensure the desired Control or Establishing the orbital movement of the two inner bodies of the system can be used. If desired, however, another such combination can be used between the two Rotating mechanisms as shown in FIG. 15 can be mounted, so that a total of three such combinations ensure the desired circulation control.

As mentioned, is one of the preferred Stirling heat engines according to the invention, each axial end or each end face of the cavity 12 of the Outer body 10 by each of the two used two or more rotating mechanisms a plate 30 provided with control openings or control slots, wherein each plate is associated with facilities that during the relative rotation between Inner bodies 14 and outer bodies 10 of these mechanisms each have a predetermined, repetitive flow path for compressible working fluid through the machine through it (see e.g. the flow path according to steps 1 to 64 according to the above List).

Since there are high pressures in a Stirling engine, the Pay special attention to waterproofing. An advantageous feature of the invention Heat engines consists in that each rotating mechanism is completely self-contained is complete and only one shaft 27, which performs a pure rotary movement, emerges from its housing. The individual rotating mechanisms can therefore by means of the currently available sealing materials and methods are permanently hermetically sealed will. The inner seals on the apex sections 15 and the middle sections 17 are subject to similar sealing requirements and techniques as in the already known rotary piston machines, the Stirling machines according to the invention no internal combustion takes place, form on the inner surfaces on which the seals need to be maintained, no fuel or combustion deposits In terms of the pollution-free Operation is thus the Preservation of waterproofing due to the presence or accumulation of harmful Foreign substances are not noticeably affected. In addition, if the lubricant is added directly to the working fluid, which according to the invention is readily available is possible, constant lubrication can be achieved and thus maintenance and Maintenance.

setting effort can be reduced0 Fig. 18 illustrates the use of contoured sealing plates on the inner body 14. It is on each apex section a sealing plate or sealing strip 42 is provided, which is inserted into a corresponding groove in the outer surface of the inner body used and set in an appropriate manner or attached.

Likewise, a sealing plate 43 is useful in a configuration corresponding recess used, whereby a sealing surface on each central section is created. From Fig. 18 it can be seen that the profile of the inner body 14 is not significantly changed by the sealing plates 42 and 43. These sealing plates should preferably be made of specially developed metal alloys or dglo for manufacture the seal contact with the profile 20 exist, so that a better and longer effective sealing can be achieved and the sealing surfaces, if necessary or desirable to be able to be replaced periodically. It is possible to use the Sealing plates 42 and 43 to be placed under transverse prestressing by slightly changing their profile is made larger than the profile of the recess in which it is used should be. As a result, the sealing plates tend to be slightly buckle and flex so that they maintain the seal without excessive Support wear and tear or increased friction. As can be seen, the sealing strips and plates made of suitable metals, composites or suitable plastics and in fact, for similar sealing purposes, are already various Materials known. Whether such sealing plates or sealing strips used or not, the outer profile of the inner body 14 should preferably be a have regular and even configuration, so that the inner body around its Axis is balanced. In this way, excessive seal wear, Vibration and leakage during operation can be largely eliminated.

As can be seen, the invention thus provides a rotating mechanism created that can work with external combustion and the performance with high Efficiency, with low pollution levels and using fuels low quality generated. In addition, they need these Stirling machines from externally supplied thermal energy does not necessarily come from combustion processes. Rather, the thermal energy supplied to the system via the heat supply device 34 can be used from various types of heat sources, such as from nuclear processes, from solar energy, from electrical energy and the like.

Numerous changes and modifications are obvious to those skilled in the art of the embodiments disclosed above of the invention possible without being dated The scope and principles of the invention are deviated from.

In summary, rotating mechanisms are thus with the invention Chambers of variable volume created, which are suitable for pumps, fluid motors, Heat engines or the like. suitable.

A Stirling heat engine using such is disclosed Turning mechanisms. The improved volume displacement characteristics of these mechanisms stem from the fact that certain sections (apex sections) of the inner body (Rotor) are in constant sealing contact with the wall of the cavity, opposite which the inner body circulates like a trochoid that other sections (middle sections) of Inner body periodically in seal contact during this orbital movement get with the wall, and that still other sections (connecting sections) during this turning resp.

Always keep orbital movement out of contact with this wall.

The Stirling heat engine described has volumetric Properties that are very similar to those of an idealized machine.

Claims (43)

Claims e rotary mechanism for pumps, fluid motors, Heat engines or the like. Consisting of an outer body with a cavity and one used in the latter while enabling a rotary or orbital movement Inner body, the axis of which is laterally opposite that of the outer body cavity offset, but arranged parallel to this axis, characterized in that that the inner body (14) has an outer surface that is basically in cross section (1) of several evenly spaced around the axis of the inner body and apex sections (15), (2) equidistant from this axis several intermediate or middle sections (17) around the axis of the inner body around at equal distances and each arranged at the same distance from this axis are and each arranged at a distance between two apex sections (15) are, and (3) a plurality of connecting sections (19), each of which has one Connect the middle section to the adjacent apex section that each apex section (15) during the relative rotation of the two bodies about their axes in constant sealing contact with the inner (running) surface (20) of the peripheral wall of the cavity in the outer body, that each middle section (17) periodically in Gasket contact with this running surface (20) arrives and periodically moves away from it separates, with none during this relative rotation Seal contact takes place between the connecting sections (19) and the running surface (20) that the outer body (12) has a multi-sided profile in cross section, in which the Cavity has one side more than the number of apex sections of the inner body and that each central section is periodic during said relative rotation in sealing contact with each of the successive sides of the multi-sided Profile. 2. Rotary mechanism according to claim 1, characterized in that the Inner body has 3 - 6 apex sections. 3. Rotary mechanism according to claim 1, characterized in that the inner and outer body relative rotation under the control of an internal gear assembly (internal gearing constraint). 4. Rotary mechanism according to claim 1, characterized in that the The outer body is stationary in relation to the inner body and that the inner body has a rotary or to carry out a rotary movement. 5. Rotary mechanism according to one of claims 1 to 4, characterized in that that the apex sections and the middle sections are each substantially the same Have contour and that each middle section of two apex sections is equidistant. 6. rotating mechanism according to claim 1 or 5, characterized in that that the inner body has two apex sections has and that the Outer body cavity has a substantially three-sided profile. 7. rotating mechanism according to claim 1 or 5, characterized in that that the inner body has three apex sections and that the outer body cavity has a substantially four-sided profile. 8. rotating mechanism according to claim 1 or 5, characterized in that that each apex section is formed by a contoured sealing plate or strip is that during the relative rotation of the inner and outer body about their axes with successive sections of its outer surface in sealing contact with the Inner surface or running surface of the peripheral wall of the outer body cavity arrives. 9. rotating mechanism according to claim 1 or 5, characterized in that that each central section is formed by a contoured sealing plate, which during the relative rotation between said bodies with successive sections their outer surface comes into sealing contact with the running surface. 10. Rotary mechanism according to claim 1 or 5, characterized in that that inner and outer body the relative rotation under the compulsion or the control perform an internal gearing constraint. 11. Rotary mechanism according to claim 1 or 5, characterized in that that each axial end or each end face of the cavity of the outer body through a plate is covered with several mm -the axis of the cavity around it Spaced distributed control openings or slots is provided1 and that the inner body in its axial ends resp. End faces having a number of control channels1 each are arranged so that they periodically establish a connection during said relative rotation between one through the outer surface of the inner body and said running surface produced chamber and one of the control openings via one of the control channels. 12. Rotary mechanism according to claim 11, characterized in that each plate has a number of control openings one greater than the number of Seheitel sections of the inner body and that the number of control channels on each face of the inner body of the number of its apex sections is the same. 13. Rotary mechanism according to claim 11, characterized in that the inner body has three apex sections and one essentially three-sided Profile has that the outer body cavity has an essentially four-sided profile has that each plate is provided with four control openings1 around the axis of the cavity substantially equally spaced around and substantially each are equidistant from this axis, and that in each end face of the inner body three control channels are provided, each from the relevant side of the inner body run out inwards. 14. Rotary mechanism according to claim 13, characterized in that the inner body has six separate control channels and six connecting sections, that three control channels are each provided on one end face of the inner body are and that of each of the six connecting sections in each case a control channel to going off inside. 15. Rotary mechanism according to claim 14, characterized in that the mouths of the control channels following one another around the circumference of the inner body are arranged alternately so that the first, the third and the fifth control channel on one and the second, fourth and sixth control channel are on the other end of the inner body. 16. Rotary mechanism according to claim 5, characterized in that each axial end or each end face of the cavity of the outer body by a plate is covered with several radially spaced around the axis of the cavity distributed control openings is provided that the inner body at its axial ends or end faces is provided with several control channels, each arranged in such a way are that they rotate around their axes during the relative rotation between the inner and outer bodies around a connection between one through the outer surface of the inner body and the tread of the outer body cavity formed chamber and one of the control openings or produce one of the control channels, and that the inner and outer bodies rotate relative to each other Perform under internal gear control or definition. 17. A rotating mechanism according to claim 5, characterized in that the distance of the transverse or lateral distance between the axis of the inner body and the axis of the outer body cavity is practically the expression corresponds, where n is the number of apex sections of the inner body, D is the distance between the outermost point in the radial direction on the inner body and its axis and K is the mean radius of curvature of the profiles of the apex sections. 18. Rotary mechanism according to claim 5, characterized in that the The length of the profile of each apex section is approximately 0.25-2.75 radians. 19. Rotating mechanism for pumps, fluid motors, heat engines Or the like., Consisting of an outer body with a cavity and one in the latter while enabling a rotary or orbital movement used inner body, its Axis laterally offset from that of the outer body cavity, but parallel is arranged on this axis, characterized in that the inner or running surface the peripheral wall of the outer body cavity has a substantially profile that through the outermost points in the radial direction of a series of hypotrochoid curves is formed, which portion of the inner body by a number of a crown circumscribing points are outlined while using the inner body as a reference base serving axis of the outer body rotates like a trochoid that the outer surface of the inner body, with the exception of the connecting sections, essentially has a profile, the formed by the innermost points in the radial direction of a series of epitrochoid curves which is outlined by a series of points circumscribing said tread while the outer body! with the axis of the inner body serving as a reference base rotates like a trochoid that each vertex section during said relative rotation is in constant sealing contact with said running surface and that everyone Central section periodically in sealing contact with during this relative rotation reaches the said tread and is periodically released from it. 20. Rotary mechanism according to claim 19, characterized in that the inner body has two apex sections and that the outer body cavity has an essentially three-sided profile. 21. Rotary mechanism according to claim 19, characterized in that the inner body has three apex sections and that the cavity is essentially one has a four-sided profile. 22. Rotary mechanism according to claim 19, characterized in that each apex section formed by a contoured sealing plate or strip is that during the relative rotation of the inner and outer body about their axes with successive sections of its outer surface in 1) contact with the Inside surface or running surface of the peripheral wall of the outer body cavity arrives. 23. Rotary mechanism according to claim 19, characterized in that each ld; ttelabschnitt is formed by a contoured sealing plate, which during the relative rotation between said bodies with successive sections their outer surface comes into sealing contact with the running surface. 24. Rotary mechanism according to claim 19, characterized in that each connecting section has a profile that corresponds to that through the innermost points generated profile corresponds or is recessed from this radially. 25. Rotary mechanism according to claim 49, characterized in that the profile of the outer body cavity from the outermost points in the padial direction is slightly expanded from evenly. 26. Drehechanlsmus according to claim 19, characterized in that Inner and outer body the relative rotation under the compulsion or the control of a Perform internal gearing constraint. 27. Rotary mechanism according to claim 19, characterized in that each axial end or each end face of the cavity of the outer body by a Plate is covered with several spaced around the axis of the cavity distributed control openings or slots is provided, and that the inner body has a number of control channels in its axial ends or end faces, which are each arranged so that they are periodic during said relative rotation a connection between one through the outer surface of the inner body and the said Running surface formed chamber and one of the control openings via one of the control channels produce. 28. Rotary mechanism according to claim 27, characterized in that each plate has a number of control openings which is one greater than the number of the apex section of Has inner body and that the number of control channels on each face of the Inner body of the number of its apex sections is the same. 29. Rotary mechanism according to claim 27, characterized in that the inner body has three apex sections and one essentially three-sided Profile has that the outer body cavity has a substantially four-sided profile possesses that each plate is provided with four control openings around the axis of the cavity substantially evenly spaced around and substantially each are equidistant from this axis, and that in each end face of the inner body three control channels are provided, each from the relevant side of the inner body run out inwards. 30. Rotary mechanism according to claim 29, characterized in that the inner body has six separate control channels and six connecting sections, that three control channels are each provided on one end face of the inner body are and that of each of the six connecting sections in each case a control channel to going off inside. 31. Rotary mechanism according to claim 30, characterized in that the mouths of the control channels following one another around the circumference of the inner body are arranged alternately so that the first, the third and the fifth control channel on one and the second, fourth and sixth control channel are on the other end of the inner body. 32. Rotary mechanism according to claim 19, characterized in that Each axial end or each end face of the cavity of the outer body by a Plate is covered with several radially around the axis of the cavity around Spaced distributed control openings is provided that the inner body at its axial ends or end faces is provided with several control channels, each are arranged so that they are in the relative rotation between the inner and outer body around their axes a connection between one through the outer surface of the inner body and the tread of the outer body cavity formed chamber and one of the control ports or produce one of the control channels, and that the inner and outer bodies rotate relative to each other Perform under internal gear control or definition. 33. Rotary mechanism according to claim 32, characterized in that the inner body has three apex sections and one essentially three-sided Profile has that the outer body cavity has a substantially four-sided profile possesses that each plate is provided with four control openings around the axis of the cavity substantially evenly spaced around and substantially each are equidistant from this axis, and that in each end face of the inner body three control channels are provided, each from the relevant side of the inner body run out inwards. 54. Rotary mechanism according to claim 19, characterized in that the distance of the transverse or lateral distance between the axis of the inner body and the axis of the outer body cavity is practically the expression corresponds, in which the number of vertex sections of the inner body 3 D is the distance between the outermost point in the radial direction on the inner body and its axis and R is the mean radius of curvature of the profiles of the vertex sections. 35. Rotary mechanism according to claim 19, characterized in that the length of the profile of each Seheitel section is about 0.25 - X.75 radians. 36. Stirling heat engine with a cyclic mechanism or periodic change in the volumes of several associated chambers, with one Heat removal device, a regenerator or heater and a heat supply Device, characterized in that the mechanism for changing the volumes the chambers is a rotating mechanism that has an outer body with a cavity and an inner body inserted in the latter, allowing a relative rotation to it has, the axis of which laterally or in the transverse direction at a distance from the axis of the Outer body cavity, but lies parallel to this axis that the inner body has an outer surface, which in cross section basically consists of several around the Axis of the inner body distributed around the same distance and always the same Far from this axis arranged Beheitel sections, several around the axis of the Distributed around the inner body at equal distances and equidistant from this Axis distant middle sections, each with a distance between two apex sections lie, and there is a plurality of connecting sections, each having a central section connect with an adjacent apex section that the apex sections during the relative rotation of the inner and outer body around said axes, respectively in constant Sealing contact with the inner or running surface the peripheral wall of the outer body lfohlraums stand that each middle section during this relative rotation periodically comes into seal contact with the running surface and periodically comes free of it, while there is no seal contact during this relative rotation takes place between the connecting sections and said running surface that the outer body has a multi-sided profile in cross section, one side more than the number of apex portions of the inner body, and that each Central section periodically in seal contact during said relative rotation with each of the successive sides of the multi-sided profile. 37. Machine according to claim 36, characterized in that at least two rotating mechanisms on an eccentric crankshaft in counterbalancing relationship are arranged. 38. Machine according to claim 37, characterized in that the inner body each rotating mechanism has three apex sections and that the outer body cavity each rotating mechanism has a substantially quadrilateral profile. 39. Machine according to claim 37, characterized in that inside and outer body relative rotation under the control of an internal gear assembly (internal gearing constraint). 40. Machine according to claim 37, characterized in that each axial End or each end face of the outer body any turning mechanism is covered by a plate with several control openings that radially around the Axis of the cavity are distributed around at intervals, and that the inner body each Rotary mechanism in its axial end or its end face a number of control channels has, which are each arranged so that during the relative rotation between inner and outer bodies around said axes periodically a connection between ender formed by the outer surface of the inner body and said tread Chamber and a control opening is made via one of the control channels. 41. Machine according to claim 37, characterized in that the inner body each rotating mechanism has three apex sections and the outer body cavity each rotating mechanism has an essentially four-sided profile that inner and outer bodies rotate relative to each other under the control or determination able to carry out by an internal gear arrangement that each axial end or each end face of the cavity in the outer body each turning mechanism by a plate with a plurality of control openings distributed radially around the axis of the cavity at intervals is covered and that the inner body of each rotating mechanism at its axial ends or end faces is provided with several control channels, each arranged in such a way are that the relative rotation between the inner and outer body around the said Axes around periodically establish a connection between one through the outer surface of the Inner body and the tread of the cavity formed chamber and one of the control openings Can be produced via one of the control channels, the inner body being a rotary or Able to carry out orbital movement. 42. Machine according to claim 36, characterized in that at least two rotating mechanisms on an eccentric crankshaft in counterbalancing relationship are arranged to each other and that each axial end or each end face of the outer body cavity each s rotating mechanism by one provided with control holes or slots Plate is covered, the means are assigned which during the relative rotation between the inner and outer bodies of the mechanisms predetermined, repetitive Flow paths for a compressible working fluid through the machine determine. 43. Machine according to claim 36, characterized in that at least two rotating mechanisms in counterbalancing relationship on an eccentric crankshaft are arranged so that the inner body and the crankshaft have a common rotational movement able to perform, while the outer body of the rotating mechanisms compared to the Inner bodies stand still that the outer profile of the inner body of each rotating mechanism is regular and uniform so that the inner body is balanced about its axis is that the inner body of each rotating mechanism has three apex portions and the outer body cavity each has a four-sided profile, and that each axial end or each end face of the cavity of the outer body each Rotation mechanism by a plate provided with control openings or slots is covered, the means are assigned which one during the rotary movement predetermined, repetitive flow path for a compressible working fluid through the machine.