EP1144806B1 - Oscillating piston engine - Google Patents

Abstract

An oscillating-piston engine, comprising a housing, in which several pistons configured as two-armed levers are arranged pivotably, respectively, around a pivot axis being parallel to a central housing axis and moving commonly in a revolution direction. The pistons comprise running surfaces on a side facing away from said housing inner wall, which are guided alongside at least one control cam, when the pistons revolve in the housing, of a centrally housing-fixed cam piece, in order to control pivot movements of the pistons in the revolution. The control cam is configured as an inner contour on the cam piece, alongside of which the pistons are guided supported to a side of a centrifugal force via the running surfaces, The cam piece comprises another inner contour configured as a control cam alongside of which the pistons are guided supported to a direction of the central housing axis via the running surfaces.

Description

The invention relates to a swing piston machine, with a Housing in which several pistons designed as two-armed levers by one parallel to a central housing axis Swivel axis arranged pivotably and together in one Circulation direction are movable, with the pistons on their one Have side treads facing away from the inner wall of the housing when rotating the pistons in the housing along at least one Control curve of a central curve piece fixed to the housing are to the pivotal movements of the pistons when rotating control, the curve piece being designed as a control curve Has outer contour, along which the running surfaces of the pistons are supported towards the housing axis.

Such a swing piston machine is from WO 98/13583 known, the disclosure of which is hereby expressly included in the present Registration is involved.

Swing piston machines belong to a genus of internal combustion engines, in which the individual work cycles of admission, Compressing, igniting (expanding) and expelling the combustion mixture by rocker-like swivel movements of the individual pistons between two end positions.

The known oscillating piston machine has a center in the housing a curve piece fixed to the housing, one as a control curve has trained outer contour. The pistons point to hers facing away from the inner wall of the housing, i.e. the central curve piece facing sides on treads when rotating the pistons in the housing along the outer contour of the curve piece below constant contact with the same. The Swiveling movements of the pistons are thereby rotating Piston in the housing by guiding the tread of the Interaction of pistons along the outer contour of the curve piece controlled by a rolling engagement of adjacent pistons.

Although the known swing piston machine in terms of Has proven to be particularly favorable running properties you with regard to their wear resistance and functional reliability, especially in long-term and high-performance operation, still room for improvement.

Calculations on the kinematics of the well-known swing piston machine have namely shown that the centrifugal forces of the pivoting piston seen over a full cycle depending on the current one Different positions between a minimum and assume a maximum of what is due to the asymmetrical Mass position of the swivel pistons in relation to the center of the swivel axes of the individual pistons is to be explained. The difference between the centrifugal force minimum and the centrifugal force maximum at high speeds in the range of more than 1000 N.

The maximum centrifugal force occurs with each piston when he is in the so-called top dead center (OT) position (12 Clock position) or in the bottom dead center (UT) position (6 Clock position). This maximum on the leading lever arm of the piston in the TDC position Centrifugal force, this lever arm towards the outside Presses the inner wall of the housing, causes an equal size on the Curve piece directed towards the trailing lever arm of the same Piston's force. Because this trailing lever arm with the leading lever arm of the next trailing piston is in rolling engagement, the trailing lever arm presses of the leading piston the leading lever arm and thus the running surface of the trailing piston arranged thereon with increased force against the curve piece. Because on the leading Lever arm of the trailing piston, which is straight in the retracted 9 o'clock or 3 o'clock position, just acts a centrifugal minimum, so this minimal centrifugal force caused by the centrifugal force in the TDC position caused pressure force not compensated. The result is that the running surface of the trailing piston in the 9 o'clock position or the piston in the 3 o'clock position with very high force the curve piece is pressed, creating both the tread as well as the curve piece are loaded excessively.

In long-term operation, especially at high speeds, this can where the centrifugal forces are high, to an increased Wear or even damage to these parts.

From the above it follows that the toothing of the rolling engagement, which has to absorb opposing forces, even is even more stressed.

Furthermore, DE-OS-15 51 101 is a centrifugal piston internal combustion engine known, the six spaced pistons of approximately triangular shape that so on a circular drive wheel are pivotally mounted that they when circulating in the housing of the engine by the occurring Centrifugal forces are pressed against the inner wall of the housing. The control of the pivoting movement of the individual pistons is thereby due to a special trochoidal design of the inner wall of the housing causes. In the housing are also two fixed Guide cams with an outer contour arranged at low Engine speeds at which the centrifugal forces are low are to ensure that the pistons against the inner wall of the housing to be pressed to the functionality of the engine maintain at low speeds. This Centrifugal piston engine is, however, already required because of the special non-circular contouring of the housing inner wall disadvantageous.

From DE-OS-15 26 408 an internal combustion engine is also with revolving piston, forming a closed chain. The pistons form together with the non-round, approximately oval cylinder jacket closed rotating working chambers variable Volume. The polygon formed by the pistons is a pentagon or polygon, with a regular pentagon being the most advantageous is seen. For controlling the piston movement two secondary rotors are provided, consisting of five segments exist, these segments articulated by means of bolts are. Rollers are mounted on the bolts, which over the Control the movement of the rotors while rolling, and by means of further bolts also the movement of the pistons. This configuration a swing piston machine is comparatively complex. Further disadvantages of this configuration are the non-circular configuration the housing inner wall and the articulated connection of the segments forming the two secondary rotors for controlling the Swiveling movement of the pistons.

Another swinging piston machine is known from US Pat. No. 3,642,391, in which the pistons are articulated in pairs are. The inside wall of this swing piston machine is not round, but rather elliptical. The piston swiveling movements are controlled by curve sections on which the pistons run with rollers. Also on this swing piston machine the non-circular contouring of the inner wall of the housing is disadvantageous.

The document US 3,438,358 discloses a swing piston machine, in which the pistons revolving around a curve piece fixed to the housing are designed as one-armed levers and not in pairs with each other are engaged.

The invention is therefore based on the object of a swing piston machine of the type mentioned at the outset, that the disadvantages mentioned above are avoided. The swing piston machine is said to have wear properties and functional reliability further improved become.

According to the invention, this object is achieved with a swing piston machine of the type mentioned in that the Curve section another control curve designed as an inner contour has, along which the piston over the treads are guided supported on the centrifugal force.

The swing piston machine according to the invention therefore continues assume that the pivoting movements of the individual pistons controlled when circulating through a central curve piece fixed to the housing be what is in the known swing piston machine compared to the known centrifugal piston internal combustion engine has proven to be advantageous. In the case of the invention However, the oscillating piston machine is in the form of an inner contour trained control curve, along which the running surfaces of the pistons are taken a measure to the centrifugal forces the piston halves or lever arms of the pistons. Thereby, that the control curve designed as an inner contour Taking up centrifugal forces, it is avoided that the centrifugal forces, in particular the maximum centrifugal forces in the TDC position occur via the rolling engagement on the tread or treads of the leading and trailing pistons and be transferred to the curve piece. That way Overloading of the treads and the curve piece avoided. Another advantage of the invention Configuration of the curve piece is that also the forces in the area of a rolling engagement between neighboring ones Piston, if there is one, also can be advantageously reduced.

Everyone experiences in the oscillating piston machine according to the invention Pistons advantageously both along an "outer guide" the known outer contour and an additional one "Inner guidance" along the inner contour of the curve section. A such a combination of internal and external guidance enables one Kinematically exact and at the same time dynamically favorable control the pivoting movements of the pistons when rotating in the housing, the significant advantage being achieved that the the outer contour guided treads in the 9 o'clock position and 3 o'clock in contrast to the well-known swing piston machine are relieved of pressure. Another advantage of the combination of Inner and outer guidance is that in a rolling engagement each adjacent piston this essentially none Control function more, but that the rolling engagement only has the function of a seal. This opens up the possibility of the rolling engagement instead of in the form of a toothing to design in the form of a smooth rolling surface, or even to forego a rolling engagement, as in one preferred embodiment is provided.

In a further preferred embodiment, the outer contour runs and the inner contour parallel to each other.

In this embodiment, the inner contour and the outer contour curves that are essentially complementary to one another on. Each piston is therefore both centrifugal and centripetal as if guided on a rail. The curve parallel to the outer contour Execution of the inner contour has the advantage that it is possible with simple means known from WO 98/13583 and proven swing piston machine according to the present Modify registration. For example, the Piston geometry and the geometry of the outer contour of the curve piece are taken over essentially unchanged, whereby then only on the curve piece an inner guide surface for the Piston must be provided.

In a further preferred embodiment, the inner contour is trained continuously in the circumferential direction.

The advantage here is that each piston has a full cycle centrifugal force side, i.e. is supported centrifugally so that centrifugal forces are absorbed in every rotary position and this reduces pressure loads in every rotational position.

Alternatively, it is also preferred if the inner contour in the circumferential direction only over one or more peripheral sections extends.

This allows a simpler structure of the swing piston machine can be achieved, in which case it is advantageous if the inner contour at least in the area of top dead center and the bottom dead center extends, for example from 10 a.m. to 2 a.m. And from 4 a.m. to 8 a.m.

In a further preferred embodiment, the curve piece has the outer contour and the at least one inner contour in one-piece training.

In this embodiment, the curve piece can be made in one piece are manufactured, whereby the manufacturing effort and reduced the number of parts entering the design can be. Starting from the curve piece of the known Swing piston machine can the inner contour provided according to the invention be molded during the manufacture of the curve piece. Another advantage of a one-piece design of Outer contour and inner contour is that a fixed Orientation of the two during operation of the swing piston machine is guaranteed in the long run.

Alternatively, however, it is also preferred if the curve piece is formed in several parts, at least a first Part of the control curve designed as an outer contour and at least a second part the at least one designed as an inner contour Control curve and the parts firmly together are connected.

This configuration proves to be easier to install when bringing the piston treads together with the Curve section as advantageous. The inner contour can be on one Ring flange be formed, which on the rest of the curve piece, that has the outer contour after inserting the pistons is flanged.

In a further preferred embodiment, the inner contour is on the inside of pocket-like flanges of the curve piece educated.

This measure is both manufacturing technology and assembly technology particularly advantageous. The Flange or the flanges can be integral with the rest, the part of the curve piece having the outer contour be, or as separate ring flanges, which then with the rest Part of the curve piece, which has the outer contour, positively connected, for example mortised. The pocket-like Flanges form an approximately inverted L-shaped Overlap of those treads that are used for guidance on the inner contour are provided.

In a further preferred embodiment, the curve piece has axially in the area of both axial ends of the pistons limits the inner contour.

In this embodiment, each piston is accordingly with its guided on both sides of the centrifugal force. The axially central Area of each piston, if this is provided, have the treads that radially on the outer contour supported inside.

It is further preferred if each piston has at least two treads, of which at least one is guided on the inner contour, while the at least one more Tread is guided on the outer contour.

This configuration advantageously opens up the possibility of to realize the treads by rollers, whereby then the at least one roller guided along the inner contour roll freely on this and the at least one on the outer contour Unroll the guided roller on this as well can.

In a further preferred embodiment, the treads are Surfaces of rollers rotatably attached to the pistons.

Rollers have the advantage that they are much smaller Friction along the inner contour or along the outer contour of the curve piece can be performed. The requirements on the lubrication of the treads can differ to piston-resistant sliding shoes can be significantly reduced.

In a further preferred embodiment, the pistons are each in pairs with each other.

This measure is advantageous, since the rolling engagement is then an additional one Control function for the back and forth swivel movement the piston can take over.

In a further preferred embodiment, the pistons are each in pairs over a toothless curved rolling surface with each other.

As previously mentioned, the forces in the area of Rolling engagement of adjacent pistons by the invention Guiding the pistons along the inner contour and even more the additional guidance of the pistons along the outer contour reduced, so that the rolling engagement is mainly still a sealing Function. Accordingly, the rolling engagement can also through a manufacturing technology easier than a toothing smooth rolling surface to be produced are shown.

As an alternative to a rolling engagement of adjacent pistons it is also preferred if the pistons are seen in the circumferential direction spaced in pairs by a separating element are, the separators together with the pistons circulate in the housing.

This configuration is particularly advantageous possible because the pivoting movement of the individual pistons both via the inner outer guide as well as on the outer inner guide of the curve section is completed. The individual pistons are then complete due to the no longer existing rolling engagement independently of each other, with the advantage that on the system between piston and separating element in a structurally simple Ways conventional seals can be used.

It is further preferred if each separating element has two Has sliding surfaces on which piston fist surfaces of the two respective corresponding to the respective separating element Slide the piston back and forth as it swivels.

The separating elements are therefore preferred in terms of Swiveling movement of the pistons stationary, and only run with it the piston in the housing in the circumferential direction. The dividers can move with the pistons between two Annular bodies at the respective end of the swing piston machine be firmly clamped.

It is further preferred if the piston fist surfaces the piston and the sliding surfaces of the separating elements are complementary curved are trained to each other.

The piston fist surfaces of the pistons can be convex, for example and the sliding surfaces of the separating elements are concave, or the other way around. Such a curved shape of the sliding Piston fist surfaces and sliding surfaces are optimal to the reciprocating pivoting movement of the individual pistons customized. The complementary shape of the piston fist surfaces and the sliding surfaces continue to allow over the entire Swing stroke of the pistons for an optimal sealing of the working chambers against the oil space of the oscillating piston machine if the Separating elements in the axial direction over the length of the interior extend the housing of the oscillating piston machine.

For this purpose, it is preferably provided in each sliding surface Separating elements to arrange at least one seal.

Such seals can be provided in the form of sealing lips be located in the same place where the corresponding Sealing lips in the end ring surfaces of the piston cage the longitudinal center axis of the oscillating piston machine on next are arranged.

The arrangement of the seals in the separators is however not mandatory, the seals can also be used instead of in the separators in the piston fist faces of the pistons his.

In a further preferred embodiment is in each sliding surface the separating elements a fire seal closer to the inner wall of the housing and an oil seal closer to the cam piece.

The fire seal seals the work chambers in which the combustion process takes place, gas-tight, while the central Oil chamber arranged in the oscillating piston machine via the oil seal is additionally sealed against the working chambers.

In a further preferred embodiment, the oscillating piston machine has several chambers in the axial direction, whereby a set of pistons is arranged in each chamber, and the Sets of pistons offset from chamber to chamber in the direction of rotation are arranged to each other.

While the known swing piston machine in the axial direction is designed as a single-chamber system, results in the multi-chamber system Design of the advantage that the piston Torques initiated on the cam piece corresponding to the Number of chambers halved, divided into thirds or divided even further can be because the torque effective area of the Pistons are made correspondingly smaller in the axial direction can be. Due to the offset of the piston sets from one chamber to the next chamber the torque is applied to the middle Curve piece distributed more evenly in the circumferential direction.

As a result, the smooth running of the oscillating piston machine can advantageously increases and the load on the curve piece caused by all chambers are made in one piece or in several parts can be reduced even further.

Further advantages result from the description below and the attached drawing.

It is understood that the above and those below features to be explained not only in their respective specified combination, but also in other combinations or can be used alone without the frame to leave the present invention.

Fig. 1

einen Längsschnitt durch eine erfindungsgemäße Schwenkkolbenmaschine gemäß einem ersten Ausführungsbeispiel;

Fig. 2

einen Querschnitt durch die Schwenkkolbenmaschine entlang der Linie II-II in Fig. 1;

Fig. 3

einen Querschnitt durch die Schwenkkolbenmaschine entlang der Linie III-III in Fig. 1;

Fig. 4

einen Längsschnitt durch eine erfindungsgemäße Schwenkkolbenmaschine gemäß einem zweiten Ausführungsbeispiel, das gegenüber dem ersten Ausführungsbeispiel geringfügig modifiziert ist;

Fig. 5

einen Querschnitt durch die Schwenkkolbenmaschine entlang der Linie V-V in Fig. 4;

Fig. 5a

ein Detail aus Fig. 5 im vergrößerten Maßstab; und

Fig. 6

einen Querschnitt durch die Schwenkkolbenmaschine entlang der Linie VI-VI in Fig. 4.

An embodiment of the invention is shown in the drawing and is described in more detail below with reference to this. Show it:

Fig. 1

a longitudinal section through an inventive oscillating piston machine according to a first embodiment;

Fig. 2

a cross section through the oscillating piston machine along the line II-II in Fig. 1;

Fig. 3

a cross section through the oscillating piston machine along the line III-III in Fig. 1;

Fig. 4

a longitudinal section through a swing piston machine according to the invention according to a second embodiment, which is slightly modified compared to the first embodiment;

Fig. 5

a cross section through the oscillating piston machine along the line VV in Fig. 4;

Fig. 5a

a detail of Figure 5 on an enlarged scale. and

Fig. 6

3 shows a cross section through the oscillating piston machine along the line VI-VI in FIG. 4.

In Figures 1 to 3 is one with the general reference number 10 provided swing piston machine shown. The swing piston machine 10 is used, for example, in a motor vehicle used as an internal combustion engine.

The oscillating piston machine 10 has a housing 12 around its circumference on, which seals the oscillating piston machine 10 to the outside. The Housing 12 is substantially cylindrical, i.e. in cross section round, formed and extends over the axial length of the Swing piston machine 10. A housing inner wall 14 is in cross section axially continuous round.

The housing 12 is also, as is apparent from Fig. 1, from individual Housing segments constructed, namely from cylindrical Housing segments 16 and 18 and housing front segments 20 and 22, each of which is suitably tightly connected to one another are mortised and / or screwed, for example. Due to the construction of the housing 12 in individual housing segments the assembly of the oscillating piston machine 10 is considerably simplified and enables one in the case of a multi-chamber system Modular construction.

In the axial direction, the swing piston machine 10 is in two Chambers 24 and 26 divided.

A set of pistons is arranged in each of the chambers 24 and 26, 2, which is a cross section through the chamber 24 which shows pistons 28a to 28d of chamber 24. In both chambers 24 and 26 are thus arranged in each case four pistons 28a to 28d. The pistons are identical to those not shown Piston of the chamber 26 formed so that in the following only the chamber 24 with the pistons 28a to 28d arranged therein is described in more detail.

The pistons of the chamber 26 are identical to the pistons 28a to 28d of chamber 24, the pistons of chamber 26 are, however, about the pistons 28a to 28d of the chamber 24 µm about 45 °, seen in the circumferential direction, arranged offset.

The pistons 28a to 28d are each designed as two-armed levers, i.e. each of the pistons 28a to 28d has a first one Lever arm 30 and a second lever arm 32 with respect to one On pivot axis 34, which is exemplary for the piston 28a in Fig. 2 are designated. Each of the pistons 28a to 28d is thus assigned a pivot axis 34. The pivot axes 34 lie on a circle and are equidistant from each other.

Each of the four pivot axes 34 extends in the axial direction parallel to a central housing axis 36. The pistons 28a to 28d are in each case about their respective pivot axis 34 two end positions can be swung back and forth, whereby in the first End position of the respective lever arm 30 with its outside the housing inner wall 14 and in the second end position accordingly the respective lever arm 32 with its outside the housing inner wall 14 abuts.

For this purpose, each of the pistons 28a to 28d is one by one axially extending axle 38 is pivotally mounted itself is unmovable. Each axle 38 forms the respective one Pivot axis 34 of the individual pistons 28a to 28d.

The pistons 28a to 28d are still in pairs with each other in rolling engagement. For this purpose, the pistons 28a to 28d in each case in the circumferential direction on both ends of teeth 40 which comb each other. The piston 28a stands, for example thus with both the piston 28b and the piston 28d in Rolling engagement. The rolling engagement formed by the toothing 40 is tight, so that between the housing inner wall 14th and the outer sides opposite the housing inner wall 14 the pistons 28a to 28d formed by the working chambers 42 Rolling engagement are hermetically sealed.

Instead of the toothing 40, the individual pistons 28a to 28d also have a convexly curved rolling surface 44 which is shown in Fig. 2 with broken lines, with each other are in rolling engagement, in which case adjacent ones of the rolling surfaces 44 sealing in each pivoting position of the pistons 28a to 28d lie against each other in order to achieve hermetic tightness to ensure the working chambers 42.

The pistons 28a to 28d also run together in the housing 12 in a circumferential direction 46 around the central housing axis 36 around. The with rotating axis rods 38 are against the inner wall of the housing 14 sealed, using centrifugal seals 47, as described in detail in WO 98/13583, to which reference is made for a more detailed description.

Between each two adjacent ones of the axle rods 38, the corresponding one Section of the housing inner wall as well as two neighboring ones Lever arms 32 and 30 'accordingly become one of the working chambers 42 formed in the embodiment shown with four pistons 28a to 28d accordingly four working chambers 42 in the direction of rotation 46, which are sealed against one another. The volume of the working chambers 42 changes as it rotates the piston 28a to 28d corresponding to the reciprocating Swiveling movements of the pistons 28a to 28d to the different Work cycles of suction, compression, ignition (Expanding) and ejecting.

A cam piece 48 is arranged in the center of the housing 12, which extends through chamber 24 and chamber 26. The curve piece 48 is different from the pistons 28a to 28d trained fixed to the housing.

The curve piece 48 has at least one designed as a control curve Inner contour 50 on (see. Fig. 3).

The pistons 28a to 28d, in turn, face the inner wall of the housing 14 facing away or facing the curve piece 48 Side treads 52 on when rotating the piston 28a to 28d in the housing 12 along the control cam Inner contour 50 are guided. This will make the pistons 28a to 28d along the curve piece 48 on the centrifugal force side supported supported.

The inner contour 50 is on the curve piece 48 in the area of a Axial end of the pistons 28a to 28d arranged.

A second with respect to the course of the curve with the inner contour 50 is identical and is designed as a control curve inner contour 52 on the curve piece 48 in the area of the opposite axial End of the pistons 28a to 28d arranged. Point at this end the pistons 28a to 28d each have a further running surface 54, that along the rotation of the respective piston 28a to 28d the inner contour 52 of the curve piece 48 is guided.

In the chamber 26, the curve piece 48 has the inner contours 50 and 52 corresponding, also designed as control curves Inner contours 56 and 58, which serve to corresponding, treads not shown in the arranged in the chamber 26 Guide the piston supported on the centrifugal side.

In the area between the inner contours 50 and 52 or between the inner contours 56 and 58, the curve piece 48 also has an outer contour designed as a control curve. The outer contour 62 extends axially into the area of the inner contours 50, 54, 58, 60 or ends axially in the middle between the inner contours 50 and 54 or 58 and 60.

The pistons 28a to 28d each have at least one further one Running surface 64, which in the rotation of the pistons 28a to 28d in the housing 12 along the outer contour 62 of the curve piece 48 are guided, whereby the pistons 28a to 28d also radially are supported inwards towards the central housing axis 36.

In the exemplary embodiment, each piston 28a to 28d has three Treads 64, which are axially spaced from each other, and which together along the outer contour 62 of the curve piece 48 are led.

The inner contours 50, 54, 58 and 60 of the curve piece 48 are each on the inside of a flange forming a pocket 66, 68, 70 and 72, respectively.

Here are the flanges 68 and 70, the inner contours 54 and 58 form on its radial inside, in one piece with the remaining body of the curve piece 48 is formed. The flange 66 and 72, on the other hand, are formed on ring flanges 74 and 76, the form-fitting with the rest of the body of the curve piece 48 are connected and mortised with it. The ring flanges 74 and 76 are still on their respective axial outside form-fitting with the housing end segment 22 or the housing end segment 20 connected to the housing so that the ring flanges 74 and 76 with the rest of the body of the curve piece 48 form a housing-fixed arrangement.

The treads 64, which are guided along the outer contour 62 are, as well as the treads 52 and 56, which along the inner contours 50 and 54 are guided, are surfaces of rollers 78 rotatably mounted on the pistons 28a to 28d or 80. The rollers 78, each piston 28a to 28d two has, lie exclusively on the inner contour 50 or 54, while the rollers 80, each of which pistons 28a to 28d has three, only on the outer contour 62 issue.

The running surfaces 64 stand when the pistons 28a to 28d rotate with constant contact with the outer contour 62. The treads 52 and 56 are below when the pistons 28a to 28d rotate constant contact with the inner contour 50 or 54.

3, it should be noted that the treads 52 the rollers 78 not the outer contour 62 of the curve piece 48 touch, but spaced from this with slight play are so that the rollers 78 as the pistons 28a rotate to 28d roll freely on the inner contour 50 of the curve piece 48 can.

The rollers 78 and 80 are preferably on a common Bolt that passes axially through the rollers 78 and 80, stored. The running surfaces 54 and 52 of the rollers 78 are in constant contact with the inner contour 50 during of the pistons 28a to 28d revolving along the inner contour 50 guided, while the treads 64 of the rollers 80 while rotating the piston 28a to 28d in constant contact with the Outer contour 62 of the curve piece 48 guided along the same are.

As can be seen from FIG. 3, the inner contour 50 extends in Full circumferential direction on the curve piece 48.

Together with the ring flanges 74 and 76, the curve piece 48 formed in several parts, whereby the assembly of the Swing piston machine 10, more precisely the insertion of the Pistons 28a to 28d and assembling with the curve piece 48 is facilitated.

In Figures 2 and 3, the swing piston machine 10 is in one Operating position shown, in which the piston 28a, more precisely said its lever arm leading in the direction of rotation 46 30 is located at top dead center (OT). The one trailing the piston 28a Piston 28d, i.e. more precisely its leading lever arm 30 ', on the other hand, is at its maximum radially inward retracted position. On the leading lever arm 30 des leading piston 28a acts in this position when rotating, especially at high speeds, a maximum centrifugal force. This maximum centrifugal force is however over the tread 52 and 56, respectively, on the inner contour 50 of the curve piece 48 are guided, taken up by the inner contour 50. Thereby this high centrifugal force is not over the trailing lever arm 32 of the leading piston 28a on the leading lever arm 30 'of the trailing piston 28d, which is in the 9 o'clock position, so that the tread 64 'or Running surfaces 64 'of the piston 28d not excessively against the curve piece 48 can be pressed. Likewise, this centrifugal force will not on the subsequent lever arm 32 'of the leading piston 28b and therefore not as a pressure force on its leading lever arm 30 '', which is in the 3 o'clock position, so that its tread 64 "is relieved of pressure.

The curve piece 48 also has axially extending bores 82, 84 and 86 on that of the oil mist cooling or oil lubrication of the treads 50, 54 and 64 of the pistons 28a to 28d and the Lubricate the rollers 78, 80.

As already mentioned at the beginning of the description, the Swing piston machine 10 in the axial direction as a multi-chamber system configured, more precisely in the embodiment shown said as a two-chamber system.

The pistons arranged in the chamber 26, which in the drawing unspecified, indicate their leadership along the curve piece 48 the same design as pistons 28a to 28d of chamber 24.

The pistons of the chamber 26 can also be pivoted on axle rods stored, of which in Fig. 1 two axle rods 88 and 90 opposite Pistons can be seen. The axle rods 88, 90 as well the other two, not visible in the drawing Axle bars are relative to the axle bars 38 on which the pistons 28a to 28d of the chamber 24 are pivoted about 45 ° staggered.

The axle rods 38 of the chamber 24 and the axle rods 88, 90 and the other two axis rods of the chamber 26 form together with three ring bodies 92, 94 and 96 a rigid cylindrical piston cage, which together with the pistons 28a to 28d of the chamber 24 and the piston of the chamber 26 revolves together. The axle bars 38 of the chamber 24 are firmly connected to the ring bodies 92 and 94, while all axis rods 88, 90 of the chamber 26 with the Annular bodies 94 and 96 are firmly connected. The first ring body 92 is rotatable and tight on the ring flange 74 of the curve piece 48 stored. The third ring body is corresponding 96 rotatable and tight on the ring flange 76 of the curve piece 48 stored. The middle ring body 94 is rotatable on the outer sides the flanges 68 and 70 of the curve piece 48 are mounted. The third ring body 96 carries on its axially outer side a ring gear 98 which has an external toothing 100 which with a corresponding toothing of a change gear 102 meshes again with a corresponding toothing 104 of a ring gear 106 combs, the rotationally fixed with an output shaft 108 Swing piston machine 10 is connected. The rotation of the third Ring body 96 around the central housing axis 36 thus causes Rotary motion of the output shaft 108, which then turns into a drive train of the motor vehicle in which the oscillating piston machine 10 is installed, transmitted via a clutch disc 110 can be.

Furthermore, the oscillating piston machine has for each chamber 24, 26 Spark plugs 112 and 114, as well as an inlet cross-section 116 and an outlet cross section for each chamber 24 and 26.

Because of the way the oscillating piston machine works, here referred to WO 98/13583, in which in Fig. 5 the individual Work cycles of the oscillating piston machine 10 are shown.

4 to 6 is a compared to the swing piston machine 10th 1 to 3 slightly modified embodiment a swing piston machine 10 'shown, in the following only the differences to the oscillating piston machine 10 according to 1 to 3 are described. Same or comparable Features as in the oscillating piston machine 10 were with the same Reference signs followed by an apostrophe.

Features and functions of the oscillating piston machine 10 'on the hereafter not explicitly referred to, are with those the oscillating piston machine 10 identical.

While in the oscillating piston machine 10 according to FIGS. 1 to 3 the Pistons 28a to 28d in pairs with each other in roller engagement stand, the pistons 28a 'to 28d' of the swing piston machine 10 'seen in pairs in the circumferential direction a separating element 140, 142, 144, 146 spaced apart, wherein the separating elements 140, 142, 144, 146 with the pistons 28a 'to 28d 'circulate in the housing 12'.

The four separating elements 140 to 146 extend according to FIG. 4 over the axial length of the chamber 24 ', and corresponding separating elements extend between the pistons in chamber 26 ' also over the axial length of this chamber 26 '.

The separating elements 140 to 146 are between the ring bodies 94 ' and 92 'or 96' and 94 'clamped and relative to them Ring bodies immobile.

Because the pistons 28a 'to 28d' through the separating elements 140 to 146 are spaced apart, the pistons 28a ' to 28d 'kinematically independent of each other. It means that the reciprocating swiveling movements of the individual pistons 28a 'to 28d' solely by guiding the pistons 28a 'to 28d' are conveyed along the curve piece 48 '.

The separators 140 to 146 face the same as on the separator 140 is shown as an example, two sliding surfaces 148 and 150 on which piston fist faces 152 (pistons 28a ') and 154 (Piston 28b ') of the two corresponding ones on the separating element 140 adjacent pistons 28a 'and 28b' at their Slide the swivel motion back and forth.

5a, the separating element 140 is enlarged in sections Scale shown. In the sliding surfaces 148 and 150 seals are embedded in the separating element 140, specifically Fire seals 156 and 158, which are closer to the housing inner wall 14 ' are arranged horizontally, and two oil seals 160 and 162, which are arranged closer to the curve piece 48 '.

The fire seals 156 and 158 seal the working chambers 42 ' gas-tight to the longitudinal center axis of the oscillating piston machine 10 ' off while the oil seals 160 and 162 for sealing of the housing-centered oil chamber against the working chambers 42 '.

The seals 156 to 162 also extend over the full axial length of separators 140 to 146.

By designing the oscillating piston machine 10 'with the Separating elements 140 to 146 can be almost classic piston seals provide their sealing effects with high certainty can be predetermined.

6 there are fire seals 156 and 158 and the oil seals 160 and 162 in the separators 140 to 146 at the same level where the fire and oil seals in the Annular bodies 92 'and 94' and 96 'are seated, as in Fig. 6 with the Reference numeral 164 is indicated.

While the seals in the embodiment shown according to 4 to 6 arranged in the separating elements 140 to 146 themselves the seals can also be reversed in the Piston fist surfaces 152 and 154 of the pistons 28a 'to 28d' are arranged his.

5 and 6, the sliding surfaces are 148 and 150 of the separating elements 140 to 146 are concavely curved formed, while the piston fist faces 152 and 154 of the Pistons 28a 'to 28d' complementarily curved and convex are. This causes the piston fist faces 152 and 154, respectively the piston 28a 'to 28d' in their reciprocating Swivel movement always at a minimum distance on the sliding surfaces 148 or 150 of the separating elements 140 to 146 passed.

Claims (18)

1. An oscillating-piston engine, comprising a housing (12; 12'), in which several pistons (28a-28d; 28a'-28d') configured as two-armed levers are arranged pivotably, respectively, around a pivot axis (34) being parallel to a central housing axis and movable commonly in a revolution direction (46), wherein the pistons (28a-28d; 28a'-28d') have running surfaces (52, 56, 64) on their side facing away from a housing inner wall (14; 14'), the running surfaces, when the pistons (28a-28d; 28a'-28d') revolve in the housing, being guided alongside of at least one control cam of a centrally housing-fixed cam piece (48; 48'), in order to control the pivot movements of the pistons in revolution, wherein the cam piece (48; 48') has an outer contour (62) configured as control cam, alongside of which the running surfaces (52, 56, 64) of the pistons (28a-28d; 28a'-28d') are guided supported in the direction to the housing axis (36), characterized in that the cam piece (48, 48') has another control cam configured as inner contour (50, 54) on the cam piece (48; 48'), alongside of which the pistons (28a-28d; 28a'-28d') are guided supported to the side of the centrifugal force via the running surfaces (52, 56, 64).
2. The oscillating-piston engine of claim 1, characterized in that the outer contour (62) and the inner contour (50, 54, 58, 60) run parallel to each other.
3. The oscillating-piston engine of claim 1 or 2, characterized in that the inner contour (50, 54) is configured continuous in revolution direction (46).
4. The oscillating-piston engine of anyone of claims 1 through 3, characterized in that the inner contour (50, 54) extends only over one or more circumferential sections in the revolution direction (46).
5. The oscillating-piston engine of anyone of claims 1 through 4, characterized in that the cam piece (48; 48') has the outer contour (62) and the at least one inner contour (54) in a one-piece configuration.
6. The oscillating-piston engine of anyone of claims 1 through 4, characterized in that the cam piece (48; 48') is configured in several parts, wherein at least a first part has the outer contour (62) and at least a second part the at least one inner contour (50), and the parts are firmly connected to each other.
7. The oscillating-piston engine of anyone of claims 1 to 6, characterized in that the inner contour (50, 54) is arranged on an inner side of a flange (66, 68) of the cam piece (48), said flange forming a bag.
8. The oscillating-piston engine of anyone of claims 1 through 7, characterized in that the cam piece (48; 48'), in the region of both axial ends of the pistons (28a-28d; 28a'-28d'), respectively, has, axially limited, the inner contour (50, 54).
9. The oscillating-piston engine of anyone claims 1 through 8, characterized in that each piston (28a-28d; 28a'-28d') has at least two running surfaces (52, 56, 64), of which at least one is guided at the inner contour (50, 54), while the at least another running surface (64) is guided at the outer contour.
10. The oscillating-piston engine of anyone of claims 1 through 9, characterized in that the running surfaces (52, 56, 64) are surfaces of rollers (78, 80) being rotatably mounted on the pistons (28a-28d; 28a'-28d').
11. The oscillating-piston engine of anyone of claims 1 through 10, characterized in that the pistons (28a-28d) are, respectively in pairs, in rolling engagement with each other.
12. The oscillating-piston engine of claim 11, characterized in that the pistons (28a-28d) are, respectively in pairs, in rolling engagement with each other via an unteethed curved rolling surface (44).
13. The oscillating-piston engine of anyone of claims 1 through 10, characterized in that the pistons (28a'-28d'), seen in circumferential direction, are spaced, respectively, in pairs via a respective dividing element (140-146), wherein the dividing elements (140-146) revolve together with the pistons (28a'-28d') in the housing (12').
14. The oscillating-piston engine of claim 13, characterized in that each dividing element (140-146) has two sliding surfaces (148, 150), on which piston fist surfaces (152, 154) of the two respective corresponding pistons (28a'-28d'), which are adjacent to the respective dividing element (140-146), slide to and fro during their pivot movement.
15. The oscillating-piston engine of claim 14, characterized in that the piston fist surfaces (152, 154) of the pistons (28a'-28d') and the sliding surfaces (148, 150) of the dividing elements (140-146) are configured curvedly complementary to each other.
16. The oscillating-piston engine of claim 14 or 15, characterized in that in each sliding surface (148, 150) of the dividing elements (140-146), respectively, at least one seal is arranged.
17. The oscillating-piston engine of claim 16, characterized in that in each sliding surface (148, 150) a fire seal (156, 158) nearer to the housing inner wall (14') and an oil seal (160, 162) nearer to the cam piece (48') is arranged.
18. The oscillating-piston engine of anyone of claims 1 through 17, characterized in that it has several chambers (24, 26; 24', 26') in axial direction, wherein in each chamber (24, 26; 24', 26') a set of pistons (28a-28d; 28a'-28d') is arranged, and wherein the sets of pistons (28a-28d; 28a'-28d') are displaced to each other from chamber (24; 24') to chamber (26; 26') in circumferential direction.

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