EP1704302A1

EP1704302A1 - Pivoting piston engine

Info

Publication number: EP1704302A1
Application number: EP04804143A
Authority: EP
Inventors: Herbert Hüttlin
Original assignee: Individual
Current assignee: Individual
Priority date: 2003-12-23
Filing date: 2004-12-21
Publication date: 2006-09-27
Also published as: CN1637233A; US20050135950A1; JP5004589B2; JP2007515593A; WO2005064119A1; CN1329628C; DE10361566B4; TWI252274B; US7435064B2; DE10361566A1; TW200523456A

Abstract

The invention relates to a pivoting piston engine, wherein the two pairs of pistons (32/36; 34/38) can pivot back and fourth in an opposite direction about a common pivoting axis (42) extending in an approximately perpendicular manner in relation to the peripheral axis (40). The two pairs of pistons (32/36; 34/38) are arranged in a crossed manner in relation to the pivoting axis (42) in such a manner that the working surfaces of two pistons of the two pairs of pistons (32/36; 34/38) are respectively arranged opposite each other, in order to form a working chamber (48, 50) therebetween. Each pair of pistons (32/36; 34/38) comprises a bearing section (52, 56) which is used to support the pair of pistons (32/36; 34/38) on the pivoting axis (42) and, respectively, a lateral wall section (54) which is used to laterally define one of the working chambers (48, 50) for the two pistons of the pair of pistons (32/36; 34/38). The bearing section (52, 56) and the lateral wall sections (54) are formed together as a single-piece and are arranged on the same side of the respective pairs of pistons (32/36; 34/38).

Description

Oscillating piston engine

The invention relates to a oscillating piston machine with a housing which has a substantially spherical housing inner wall, four pistons being arranged in the housing and rotating together around an approximately central axis of rotation, two of the four pistons each being approximately diametrical with respect to the axis of rotation Opposed pistons form a rigid piston pair, the two piston pairs being pivotable in opposite directions about a common pivot axis running approximately perpendicular to the circumferential axis, the two piston pairs being arranged crosswise with respect to the pivot axis, such that two pistons of the two piston pairs are located in each case face each other with their piston working surfaces in order to form a working chamber therebetween, each pair of pistons having a bearing section for mounting the pair of pistons on the swivel axis and a side wall section for both pistons of the pair of pistons for lateral limitation of one of the working chambers has. Such a swing piston machine is known from document WO 03/067033 AI.

Swinging piston machines belong to a genus of internal combustion engines in which the individual work cycles of intake, compression, ignition, expansion and ejection of the combustion mixture are mediated by reciprocating swiveling movements of the individual pistons between two settings.

The pivoting pistons run in the housing around a common rotational axis fixed to the housing, the rotational movement of the pistons being able to be tapped as a rotational movement of an output shaft. When the swiveling pistons rotate in the housing, the swiveling pistons carry out the mentioned reciprocating swiveling movements.

The aforementioned known oscillating piston machine has a housing which is spherical on the inside, the pivot axis of the pistons being formed by a common pivot axis which extends approximately through the center of the housing perpendicular to the circumferential axis.

Two pistons diametrically opposite each other with respect to the swivel axis are rigidly connected to one another to form a double piston, a bearing section being present between the two pistons of a pair of pistons, which is formed in the known swivel piston machine by a narrow bearing ring. Both pairs of pistons are mounted on their respective bearing rings on a pivot pin, which forms the pivot axis, so that they can be pivoted crosswise with respect to the pivot axis. The bearing rings of the piston pairs of the known oscillating piston machine are seated spaced from each other at about the ends of the journal, with another ring sitting on the journal between the two bearing rings, to which the output shaft is attached.

Furthermore, a side wall section for both pistons of the pair is arranged on each pair of pistons opposite the respective bearing section for the lateral limitation of the two working arms, the side wall section having a straight surface facing the working chamber, which is completely perpendicular to the pivot axis.

A disadvantage of the known design of a swinging piston machine of the type mentioned at the outset is that only a small overall length is available for the respective bearing section in the direction of the pivoting axis, which means that there is a fear of greater susceptibility to wear due to the design. In addition, the assembly of the known oscillating piston machine is more complex because the bearing ring of the output shaft is additionally placed on the journal. Another disadvantage is that the output shaft is guided past the piston to the pivot axis.

The object of the invention is to improve the oscillating piston machine of the type mentioned at the outset in such a way that the structural design is simplified, the assembly is simplified and the stability of the bearing of the piston pairs on the pivot axis is increased.

According to the invention, this object is achieved with respect to the swing piston machine mentioned at the outset in that the bearing section and the side wall sections are in one piece with one another are formed and arranged on the same side of the respective piston pair.

In contrast to the known swiveling piston machine, the swiveling piston machine according to the invention therefore provides for the bearing section and the side wall sections to be integrated into each other in each pair of pistons, instead of providing the bearing section at one end of the piston and spaced apart from the side wall sections at the other end. The configuration according to the invention has the advantage, in particular when the output shaft is not guided up to the pivot axis, as is provided in preferred configurations that the bearing section can be made significantly longer and thus more stable in the direction of the pivot axis, and the further advantage is that that the side wall can be made inclined with respect to the pivot axis instead of flat and perpendicular to the pivot axis, as is also provided in a preferred embodiment.

In a preferred embodiment, the bearing section extends in the direction of the pivot axis over approximately half the width of the piston pair in the direction of the pivot axis.

If the two pairs of pistons are arranged crosswise next to one another, the two bearing sections of the pairs of pistons thus extend over the entire length of the extension of the pistons in the direction of the pivot axis, as a result of which the individual piston pairs can be mounted extremely stably on the pivot axis. In a further preferred embodiment, the respective side wall section on the bearing section extends from the outside inwards and is concavely curved from top to bottom.

This configuration, which is only made possible by the configuration of each pair of pistons according to the invention, has the advantage that the two working chambers or combustion bowls have curved side walls, which is particularly important with regard to the pressure distribution when igniting and expanding the fuel-air mixture ignited in the working chamber proves favorable because the entire expansion force acts on the piston working surface and does not fizzle on the side walls, which cannot make any contribution to the introduction of force into the swiveling movement.

It is further preferred if the respective side wall section extends in the direction of the pivot axis over the entire length of the bearing section.

By joining the two pairs of pistons crosswise, working chambers or combustion bowls are curved at the sides and at the bottom, which means that the entire pressure when expanding the ignited fuel-air mixture has a complete effect on the piston working surfaces, which are preferably flat, which increases the efficiency of the oscillating piston machine according to the invention is improved compared to the known swing piston machine.

In order to be able to implement these generally trough-shaped working chambers or combustion bowls, each piston has a side surface at its end opposite the side wall section, the shape of which corresponds to the side wall section of that piston is adapted with which this piston forms the respective working chamber.

The side wall section of each pair of pistons thus advantageously forms a guide surface for the respective counter-piston during the reciprocating pivoting movement of the pistons.

In expedient and advantageous structural configurations, each individual piston extends around the circumferential axis by approximately 90 °. Furthermore, a ratio between a dimension of each piston in the direction of the pivot axis and a dimension of each piston transversely to the pivot axis is in the range from approximately 1.5: 1 to 2.5: 1, and is preferably 2.2: 1 a maximum opening angle of the working chambers about the pivot axis in the range from about 40 ° to about 60 °, ie the reciprocating swing stroke of each pair of pistons is about half of the aforementioned maximum opening angle.

In a further preferred embodiment, the two pairs of pistons sit with their bearing sections on an axle journal which forms the swivel axis, wherein at the ends of the axle journal there is in each case a spherical cap-shaped end element which holds the pair of pistons together in the direction of the swivel axis.

This measure has the advantage that to mount the two pairs of pistons, they only have to be placed crosswise with their bearing sections on the axle journal, this arrangement then being placed on the ends of the axle journal by fitting the spherical cap-shaped end elements and correspondingly firmly connecting the end members to the axle journal - will hold, while the reciprocating pivoting movement of the pistons is guaranteed.

The spherical cap-shaped end element extends around the circumferential axis by approximately 90 °.

In connection with the configuration that each individual piston extends around the circumferential axis by approximately 90 °, the arrangement of the two pairs of pistons and the two spherical cap-shaped end elements results in a spherical configuration of this arrangement which is closed by 360 ° around the circumferential axis. The spherical cap-shaped end element preferably also extends around an axis perpendicular to the axis of rotation and the pivot axis by 90 °.

In a further preferred embodiment, the pistons are connected to at least one output shaft rotatable about the circumferential axis, which ends on the piston side in a first fork section outside the pivot axis, which is arranged with its two end sections between the end elements and is directly detachably connected to them.

Instead of leading the output shaft to the pivot axis and supporting it there with a bearing ring, as in the known oscillating piston machine, this configuration has the advantage that only the bearing sections of the two pairs of pistons only have to be supported on the journal of the pivot axis, as a result of which they move in the direction of the pivot axis can each be formed with the maximum length. On the outside, the fork section preferably has the shape of part of a spherical surface, as a result of which the fork section is divided into the overall inserts a gel-like configuration of the arrangement from the four pistons and the two end elements and is adapted to the inside of the spherical housing.

The further advantage of this embodiment is that the at least one output shaft can also be connected to the piston arrangement in a particularly stable manner, because the fork section can extend further in the direction of the pivot axis of the piston than was the case with the bearing ring of the known pivoting piston machine with which the output shaft was mounted on the pivot of the swivel axis. In addition, the output shaft no longer has to be guided past the pistons, which therefore does not restrict the pivoting stroke of the pistons.

It is particularly preferred if the end sections of the first fork section have a positive connection to the end elements.

This ensures a rotationally fixed connection of the first fork section to the end elements and thus to the piston arrangement, which is able to transmit large torques to the output shaft.

In a further preferred embodiment, the end sections of the first fork section widen from the output shaft to their outer end.

It is advantageous here that the connection between the first fork section and the two end elements with which the piston pairs are held together can be made particularly stable. In expedient and advantageous constructive configurations, a ratio between the dimension of the fork section in the direction perpendicular to the pivot axis in its center to the corresponding dimension of the fork section at its ends is in the range of approximately 1: 1.5 to 1: 2.5, this ratio is preferably about 1: 2.

Furthermore, a ratio between the dimension of the fork section in the direction perpendicular to the pivot axis at its ends and the dimension of the fork section in the direction of the pivot axis is in the range from approximately 1: 2 to approximately 1: 4, and is preferably approximately 1: 1.375.

A ratio of the thickness of the fork section in the region of the output shaft to the dimension of the fork section in the direction of the pivot axis is preferably in the range of approximately 1: 2 to 1: 4, preferably it is approximately 1: 2.75.

The latter measure makes the fork section very solid and stable, so that it can transmit high torques from the rotating movement of the pistons to the output shaft.

In a further preferred embodiment, a second, essentially identical fork section is arranged opposite the first fork section and is detachably connected to the end elements.

Overall, this results in a spherical configuration of the overall arrangement from the piston pairs, the two spherical cap-shaped end elements and the two fork sections, whereby all elements of this arrangement can be made particularly stable and solid.

The second fork section preferably has a further output shaft, so that the oscillating-piston machine according to the invention has a total of two output shafts, one of which can be used, for example, to drive units such as alternators and the like, and the other output shaft can be guided to a clutch or a transmission can, in the event that the oscillating piston machine according to the invention is used as a drive motor for a motor vehicle.

In a further preferred embodiment, the first and / or second fork section extend by about 90 ° to the axis of rotation and to the pivot axis and are formed on the outside on the surface of a sphere.

In a further preferred embodiment, a side of the first and / or second fork section facing the piston rear surfaces of the pistons is curved so as to be complementary to the piston rear surfaces.

It is advantageous here that between the piston rear surfaces, ie the sides of the pistons facing away from the piston working surfaces, and the respective side of the fork sections facing these piston rear surfaces, chambers are formed which have a variable volume during the reciprocating pivoting movement of the individual pistons, the minimal volume of which Volume can become almost zero. This is particularly preferred if pre-pressure chambers are formed between the piston rear surfaces and the corresponding facing side of the fork section (s), which can be used for pre-compressing combustion air, as is already provided in the known oscillating piston machine. However, the aforementioned chambers can also simply serve as cooling chambers for cooling the pistons.

As in the known oscillating piston machine, each piston also has a roller in the oscillating piston machine according to the invention, the roller axis preferably being inclined at an angle of approximately 30 ° to 50 °, preferably approximately 35 °, with respect to the piston working surface.

The rollers are preferably conical, with an imaginary extension of each cone resulting in a cone tip which lies in the center of the housing, as a result of which the control mechanism for the pivoting movement of the pistons is optimally adapted to the spherical symmetry of the oscillating piston machine.

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

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

Figure 1 is an overall view of a swing piston machine according to the invention with a closed housing.

FIG. 2 shows the oscillating piston machine in FIG. 1, the housing being partially broken open, the oscillating piston machine being shown in a first operating position;

3 shows the oscillating piston machine in FIGS. 1 and 2 in another exemplary operating position;

4 shows a perspective view of an overall arrangement of pistons, end elements and output shafts with fork sections of the oscillating piston machine in FIGS. 1 to 3;

FIG. 5 is an enlarged view of the arrangement of the pistons alone compared to FIG. 4;

6 shows the piston arrangement in FIG. 5 in an exploded view of the two pairs of pistons;

Fig. 7 is an exploded view of the arrangement of the journal, the end elements and the two output shafts with fork sections. the oscillating piston machine in Figures 1 to 3 in isolation; 8 is a view along the output shaft of the arrangement of the two end elements and a fork section; and

Fig. 9 is a cross-sectional view of the oscillating piston machine in Fig. 1 to 3 to explain further details of the same.

With reference to FIGS. 1 to 9, the configuration of a swing piston machine provided with the general reference number 10 is described in more detail below. The oscillating piston machine 10 serves, for example, and preferably as an internal combustion engine.

The oscillating piston machine 10 has a housing 12 which is composed of a first housing half 14 and a second housing half 16.

The housing halves 14 and 16 are assembled along a dividing line 18, which is not perpendicular but is arranged obliquely with respect to an axis of symmetry 20 of the oscillating piston machine 10, which at the same time also represents the circumferential axis of the pistons, as will be described later. This oblique course of the dividing line 18 for taking apart the housing halves 14 and 16 has the advantage that technical elements provided in the housing, such as candles and nozzles 22, 24 or valves 26, 28, can be suitably arranged without these elements passing through the housing dividing line be affected.

2 and 3, the housing 12 has been partially cut open in two mutually perpendicular sectional planes, whereby further details of the oscillating piston machine 10 can be seen within the housing 12. The representations in FIGS. 2 and 3 are not identical with respect to the previously described elements 22-28 with FIG. 1, but this is insignificant for the purposes of explaining the present invention.

An inner wall 30 of the housing 12 is essentially spherical.

Four pistons (cf. FIG. 9) 32, 34, 36, 38 are arranged in the housing 12 and are partially covered in FIGS. 2 to 8. These pistons 32-38 rotate in the housing 12 together around a rotation axis 40.

In addition, the pistons 32-38 perform pivoting movements about a pivot axis 42 which is approximately perpendicular to the rotational axis 40 when the pivoting piston machine 10 is in operation, as indicated by arrows 44 and 46 in FIG. 9.

Two pistons diametrically opposite each other with respect to the center of the housing or the swivel arm 42 form a rigid piston pair, namely the pistons 32 and 36 form the piston pair 32/36, and the pistons 34 and 38 form the piston pair 34/38. When the pistons 32-38 revolve around the circumferential axis 40, the piston pair 32/36 accordingly pivots around the pivot axis 42 in the direction of the arrows 44 (clockwise) when the piston pair 34/38 pivots in the direction of the arrows 46 (counterclockwise). executes, and vice versa.

In addition, with reference to FIGS. 4 through 6, details of pistons 32-38 are described in more detail. Each piston has a piston working surface, ie the piston 32 a piston working surface 32a, the piston 34 a piston working surface 34a, the piston 36 a piston working surface 36a and the piston 38 a piston working surface 38a. 5, for example, only the piston working surfaces 32a and 34a of the pistons 32 and 34 can be seen. The piston working surfaces 32a and 34a form a first working chamber or combustion bowl 48, and the piston working surfaces 36a and 38a of the pistons 36 and 38 form a second working chamber or combustion bowl 50 (cf. FIG. 9).

Each pair of pistons, and this can be seen most clearly in FIG. 6 by the pair of pistons 32/36, has a bearing section 52 for mounting the pair of pistons 32/36 on the pivot axis 42. Furthermore, each pair of pistons, as can also be seen best in FIG. 6 for the pair of pistons 32/36, has two side wall sections which laterally delimit the working chambers 48 and 50. The side wall section 54, which laterally delimits the working chamber 48, is visible for the piston 32 in FIG. 6. The bearing section 52 and the side wall section 54 (or the side wall section of the piston 36 diametrically opposite the side wall section 54, not visible in FIG. 6) are formed in one piece with one another and are arranged on the same side of the respective piston pair 32/36 or 34/38, as this can best be seen for the piston pair 32/36 in FIG. 6. A bearing section 56 and a side wall section 58 of the piston pair 34/38 can be partially recognized in FIG. 6.

The bearing sections 52 and 56 of the piston pairs 32/36 and 34/38 are symmetrical with respect to the pivot axis 42, the side wall section 54 with respect to the pivot axis 42 being another side wall section which is hidden in the figures is approximately diametrically opposite, likewise the side wall section 58 of the piston pair 34/38 is diametrically opposite another side wall section with respect to the pivot axis 42, which is not visible in FIG. 6.

The bearing section 52 and the bearing section 56 each have a bore 60 or 62, with which the piston pairs 32/36 or 34/38 are pivotally mounted on a fixed journal 64 (see FIG. 7).

The bearing sections 52 and 56 extend in the direction of the pivot axis 42 over approximately half the width of the respective piston pair 32/36 or 34/38 in relation to the direction of the pivot axis 42. The two piston pairs 32/36 and 34/38 Now, as shown in FIG. 5, arranged crosswise with respect to the pivot axis 42, the piston pairs 32/36 and 34/38 are mounted over the entire length of the journal 64 and thus particularly stably about the pivot axis 42.

5 shows the side wall section 55 of the piston 34 which laterally delimits the working chamber 48 together with the side wall section 54 of the piston 32.

The respective side wall section 54, 55 (FIG. 5) extends on the associated bearing section 52 or 56 from the outside inwards and concave from top to bottom, as can best be seen from the illustrations in FIGS. 5 and 6. The respective side wall sections 54, 55 and the further side wall sections not visible in FIG. 5 extend in the direction of the pivot axis 42 over the entire length of the bearing section 52 or 56 in the direction of the pivot axis 42. By integrating the side wall sections 54, 55 (and the remaining side wall section 58, not visible in FIGS. 5 and 6) into the bearing sections 52 and 56, the bearing sections 52 and 56 are very solid and stable, in particular at the outer ends of the journal 64 educated.

The curvature of the side wall sections 54 and 58 and the corresponding associated side wall sections, which cannot be seen in the figures, result in curved working chambers or combustion bowls 48 and 50, and only the piston working surfaces 32a to 38a are designed to be flat, as a result of which the expansion of the fuel takes place -Air mixture after ignition ignites pressure almost exclusively on the piston working surfaces 32a to 38a, as is desired for high efficiency.

At its end opposite the side wall section, each piston 32-38 has a side surface whose shape is adapted to the side wall section of the piston with which this piston forms the respective working chamber.

This is shown in FIG. 6 for the piston 32, the end of which opposite the side wall section 54 has a side surface 66, the shape of which is adapted to the side wall section of the piston 34, the pistons 32 and 34 forming the working chamber 48. The side wall section of the piston 34, which cannot be seen in FIG. 6, has the same shape as the side wall section 54 of the piston 32 except for mirror invertedness. The same applies correspondingly to the other pistons 36, 38. Each piston 32-38 extends around the circumferential axis 40 by approximately 90 °, as shown in FIG. 5 for the piston 32.

Furthermore, there is a relationship between a dimension b of each piston 32-38 in the direction of the pivot axis 42 and a dimension h of each piston 32-38 transverse to the pivot axis 42, i.e. that is, a ratio of the width and height of each piston working surface 32a to 38a, in the range from approximately 1.5: 1 to 2.5: 1, in the present case this ratio is 2.2: 1.

Furthermore, a maximum opening angle of the working chambers 48 or 50 about the pivot axis 42 lies in the range from approximately 40 ° to approximately 60 °, as shown in FIG. 5 for the working chamber 48. The minimum opening angle is about 0 °.

As already mentioned, the two pairs of pistons 32/36 and 34/38 sit with the bearing sections 52 and 56 on the journal 64 (FIG. 7). At the ends of the journal 64, a spherical cap-shaped end element 68 or 70 is arranged, which, as shown in FIG. 4, holds the piston pairs 32/36 and 34/38 together in the direction of the pivot axis 42. In Fig. 7 only the two end elements 68, 70 are shown together with the journal 64 without the pistons. The end elements 68 and 70 are firmly screwed to the journal 64 during assembly. The journal 64 serves as a bearing for the piston pairs 32/36 and 34/38 for the reciprocating pivoting movement of the pistons 32-38.

The end elements 68 and 70 extend around the circumferential axis 40 by approximately 90 ° (cf. FIG. 8) and likewise about an axis perpendicular to the pivot axis 42 and to the circumferential axis (40) (cf. FIG. 7). The oscillating piston machine 10 also has two output shafts 72 and 74 (cf. in particular FIGS. 4 and 7) with which the pistons 32-38 are connected in a rotationally fixed manner. For the rotatable connection of the output shafts 72 and 74, each of the two has a fork section 76 (output shaft 72) and 78 (output shaft 74) at one end. The output shafts 72 and 74 are rotatably connected to their respective fork section 76 and 78, respectively.

The fork sections 76 and 78 end outside the pivot axis 42, as can be seen in particular from Fig. 7, i.e. the output shafts 72 and 74 are not guided to the middle of the housing, but end outside the middle of the housing.

The fork sections 76 and 78 each have end sections 80, 82 and 84, 86, which are arranged between the spherical cap-shaped end elements 68 and 70 and are directly connected to them in detachable fashion, a screw connection being used here for the releasable connection, as in FIG. 7 is shown.

However, the connection is not only made by means of screws, but the end sections 80, 82 and 84, 86 are also positively connected to the end elements 68 and 70, for which purpose the end elements 68 have lateral projections, namely projections 88, 90 (end element 68) and 92 , 94 (end element 70) which engage in corresponding grooves 96, 98 (shown here only for fork section 76).

8, the end sections 80, 82 and 84, 86 of the fork sections 76, 78 widen starting from the respective output shaft 72 or 74 towards its outer end.

Here, a ratio between a dimension B _{: of} the fork section 76 or 78 in its center in the direction perpendicular to the pivot axis 42 to the corresponding dimension B _{2 of} the fork section 76 or 78 at its ends is in the range from approximately 1: 1.5 to 1: 2.5, in this case around 1: 2.

Furthermore, a ratio between the dimension B _{2 of} the fork sections 76 and 78 to the dimension B _{3 of} the fork section 76 and 78 in the direction of the pivot axis 42 is in the range from approximately 1: 2 to approximately 1: 4, in the present case approximately 1 : 1.375.

A thickness D of the fork sections 76 and 78 in the area of the respective output shaft 72 and 74, ie in the middle of the respective fork section 76 and 78, is in the range of approximately 1: 2 to 1: 4 in relation to the dimension B ₃ , in the present case at approximately 1: 2.75.

The extent of the fork sections 76 and 78 corresponding to the dimension B ₃ , expressed as an angle about an axis that is both perpendicular to the rotational axis 40 and to the pivot axis 42, is approximately 90 °, so that the two fork sections 76 and 78 together with the End elements 68 and 70 form a full angle of 360 ° about this axis, that is to say thus a ball, for which purpose the outer sides of the fork sections 76 and 78 have a spherical surface shape. The ratio of the dimension B _x to the dimension B ₃ is in the range from approximately 1: 2 to approximately 1: 4, in the present case approximately 1: 2.75.

Correspondingly, the ratio between the diameter of the output shafts 72 and 74 at its end, which is directly connected to the fork sections 76 and 78, and which is only slightly smaller than the dimension _{ι r} , is roughly in the same ratio mentioned above.

As best seen in FIG. 4, each piston 32-38 has a piston back surface, as shown in FIG. 4 with reference numeral 100 for piston 32 and 102 for piston 34, which is arched, one being side 104 or 106 (cf. FIG. 7) facing these piston rear surfaces 100 and 102 is complementary to these piston rear surfaces 100 and 102.

Between the piston rear surfaces 100 and 102 (the same applies to the remaining pistons 36 and 38) and the corresponding facing side 104 and 106 (and corresponding to the other two sides of the fork sections 76 and 78) thus become opposed to the working chambers 48 and 50 reducing and enlarging two chambers formed, which can be used as pre-pressure and / or cooling chambers.

Regarding the use as pre-pressure chambers and the way in which the pre-pressure chambers communicate with the working chambers, reference is made in particular to document WO 03/067033 AI, the content of which is hereby expressly incorporated into the present application. For this purpose, the pre-pressure chambers formed between the piston rear faces 100 and 102 and the respectively facing sides 104 and 106 of the fork sections 76 and 78 are periodically flooded with fresh air, which is compressed during the continuously repeating volume reduction. The compression of the air in the pre-pressure chambers thus formed leads to a heating of the pre-pressure air. If the fresh air thus pre-compressed is introduced into the working chambers 58 and 50 in a heated manner, the efficiency of the combustion is reduced due to the heating of the pre-compressed air. It is therefore provided in the present swing piston machine that the fresh air pre-compressed in the pre-pressure chambers is pre-cooled before it is introduced into the working chambers 48 and 50, respectively. These precooling measures can be provided in the supply lines 101 from the pre-pressure chambers into the working chambers 48 or 50, for example by cooling registers on the supply lines 101 or 103.

Furthermore, for the case, as can be seen in FIG. 6, that cavern-like cavities 105 are present in the piston rear surfaces 100 and 102, on the sides of the fork sections facing for example these piston rear surfaces 100 and 102 (for example 104 and 106) 76 or 78 on the latter, projections complementary or at least substantially complementary to the cavern-like cavities 105 are provided, which protrude into the cavern-like cavities 105 with the sides 104 and 106 of the fork sections 76 and 78 when the piston rear side surfaces 100 and 102 approach each other, so that the fresh air in the cavern-like cavities 105 of the pre-pressure chambers formed between these sides 100 or 102 or 104 or 106 from the cavern-like Cavities 105 is displaced, whereby the pre-compression of the fresh air is further improved.

While in the aforementioned document WO 03/067033 AI the connection between the pre-pressure chambers and the working chambers can be made either through pipes running outside the housing of the oscillating piston machine or directly through flap valves through the pistons 32-38, the connection could also be provided of the pre-pressure chambers with the working chambers 48 and 50 in the present swinging piston machine by means of a control disc positioned on the two main shafts directly on the fork sections 76 and 78, respectively. Such a control disk would then have two suction openings offset by 180 ° opposite one another, and two identical openings would be provided in the housing, which are arranged accordingly in the control direction. If both openings of the control disks coincide with the openings in the housing in the vicinity of the main bearing, fresh air can then be drawn in from the pre-pressure chambers into the working chambers 48 and 50. As soon as the control discs continue to turn, the openings in the housing are closed, the suction process ends and the pre-compression process begins.

Such control disks can be provided if the main bearing of the internal motor (piston pairs 32/36 or 34/38) is provided by a plain bearing that requires a smaller outer diameter than a ball bearing or roller bearing.

Finally, as best seen in FIG. 5, each piston has a roller 108 (piston 32), 110 (piston 34), 112 (piston 36) and 114 (piston 38). The casters 108-114 are part of a control mechanism for deriving the reciprocating pivoting movement of the individual pistons 32-38 from their orbital movement about the orbital axis 40. For a more detailed description, reference is also made in this regard to document WO 03/067033 AI, the disclosure of which is by reference is expressly included herein.

As shown in FIG. 9 for the roller 112 of the piston 36, the roller axis of each roller 108-114 is at an angle β of approximately 30 ° to 50 °, in the present case of approximately 35, with respect to the corresponding piston working surface 32a-38a °, inclined.

4 and 5 and 9 respectively, the rollers 108-114 are conical, an imaginary extension of each cone giving a cone tip which lies in the center of the housing of the housing 12, as in FIG. 9 for the roller 110 of the piston 34 is indicated.

The rollers 108-114 run, as is provided in the oscillating piston machine according to WO 03/067033 AI, in control cams in the housing 12 which are trapezoidal in cross section.

However, it can also be provided that the control cams in the housing 12 instead of a trapezoidal cross section in a semicircular cross section, and in the pistons where the guide shafts of the guide rollers 108-114 are installed, a hemispherical cavity each so that between the Pistons 32 - 38 and the respective guide groove, one ball takes over the piston guidance, the hemispherical is embedded in the respective piston 32-38 and hemispherically in the arcuate cam groove in the housing 12. The balls can thus be rotated in the respective pistons as well as in the cam groove. The hemispherical cavity provided in the respective piston, which receives the ball, will be continuously lubricated from the inside so that the ball can be moved in this recess as smoothly as possible.

4 shows the ready-to-assemble arrangement of the pistons 32-38, the end elements 68 and 70 and the output shafts 72 and 74 with the respective fork sections 76 and 78. Correspondingly, the rollers 108-114 are already mounted on the pistons 32-38. The entire arrangement shown in FIG. 4, which except for the working chambers 48 and 50 has the shape of a closed solid ball, now essentially only needs to be enclosed by the housing halves 14 and 16 in order to form the oscillating piston machine 10.

FIG. 2 shows the oscillating-piston machine 10 with the pistons 32-38, of which, however, not all of which are visible, in a first operating position, while the pistons 32-38 in the representation according to FIG. 3 compared to FIG. 2 about the rotational axis 40 have moved slightly, and at the same time have performed a corresponding pivot stroke about the pivot axis 42.

With regard to the function and mode of operation of the oscillating piston machine 10, reference is also made here to the document WO 03/067033 AI, the content of which is incorporated into the present disclosure in this regard.

Claims

claims

Swing piston machine, with a housing (12), which has a substantially spherical housing inner wall, wherein four pistons (32 - 38) are arranged in the housing (12), which rotate together around an approximately central axis of rotation (40), of which four Pistons (32 - 38) each form two rigid pistons (32/36, 34/38) with diametrically opposite pistons relative to the center of the housing, the two piston pairs (32/36, 34/38) around a common, approximately perpendicular to the axis of rotation (40) extending pivot axis (42) can be pivoted back and forth in opposite directions, the two piston pairs (32/36, 34/38) being arranged crosswise with respect to the pivot axis (42) such that two pistons of the two piston pairs ( 32/36, 34/38) with their piston working surfaces (32a, 34a, 36a, 38a) to form a working chamber (48, 50) therebetween, each pair of pistons (32/36, 34/38) having a bearing section (52 , 56) for mounting the pair of pistons (32/36 , 34/38) on the pivot axis (42) and for each piston of the piston pair (32/36, 34/38) each have a side wall section (54, 55, 58) for the lateral limitation of one of the working chambers (48, 50), characterized in that the bearing section (52, 56) and the side wall sections (54, 55, 58) are integrally formed with one another and are arranged on the same side of the respective piston pair (32/36, 34/38).

2. Swing piston machine according to claim 1, characterized in that the bearing section (52, 56) in the direction of the swivel axis (42) over about half the width of the piston pair (32/36; 34/38) in the direction of the swivel axis (42) extends.

3. Swing piston machine according to claim 1 or 2, characterized in that the respective side wall section (54, 55, 58) on the bearing section (52, 56) extends from the outside inwards and concave from top to bottom.

4. Swing piston machine according to claim 3, characterized in that the respective side wall section (54, 55, 58) extends in the direction of the swivel axis (42) over the entire length of the bearing section (52, 56).

5. Swinging piston machine according to one of claims 1 to 4, characterized in that each piston (32 - 38) at its end opposite the side wall section (54, 55 58) has a side surface, the shape of which on the side wall section (54, 55, 58) adapted to the piston with which this piston forms the respective working chamber (48, 50).

6. Swinging piston machine according to one of claims 1 to 5, characterized in that each individual piston (32 - 38) extends around the circumferential axis (40) by approximately 90 °.

7. Swing piston machine according to one of claims 1 to 6, characterized in that a ratio between one Dimension (b) of each piston (32-38) in the direction of the pivot axis (42) and dimension (h) of each piston (32-38) transverse to the pivot axis (42) in the range of approximately 1.5: 1 to 2.5 : 1, preferably 2.2: 1.

8. swing piston machine according to one of claims 1 to 7, characterized in that a maximum opening angle (α) of the working chamber (48, 50) about the pivot axis (42) in the range of about 40 ° to about 60 °.

9. swing piston machine according to one of claims 1 to 8, characterized in that the two pairs of pistons (32/36, 34/38) sit with their bearing sections (52, 56) on a pivot pin (52) forming axle journal (64), and that at the ends of the journal (64) there is a spherical cap-shaped end element (68, 70) which holds the piston pairs (32/36; 34/38) together in the direction of the pivot axis (42).

10. Swing piston machine according to claim 9, characterized in that the spherical cap-shaped end element (68, 70) extends around the circumferential axis (40) by approximately 90 °.

11. Swing piston machine according to claim 9 or 10, characterized in that the spherical cap-shaped end element (68, 70) extends around an axis perpendicular to the circumferential (40) and to the swivel axis (42) by approximately 90 °.

12. Swing piston machine according to one of claims 9 to 11, characterized in that the pistons (32 - 38) with at least one output shaft rotatable about the circumferential axis (40) Shaft (72, 74) are connected, which ends on the piston side in a first fork section (76, 78) outside the pivot axis (42), which is arranged with its two end sections (80-86) between the end elements (68, 70) and directly with this is releasably connected.

13. Swing piston machine according to claim 12, characterized in that the end sections (80-86) of the first fork section (76, 78) have a positive connection to the end elements (68, 70).

14. Swing piston machine according to claim 12 or 13, characterized in that the end sections (80-86) of the first fork section (76, 78) widen starting from the output shaft (72, 74) towards their outer end.

15. Swing piston machine according to one of claims 12 to 14, characterized in that a ratio between the dimension (B _j ) of the fork portion (76, 78) in the direction perpendicular to the pivot axis (42) in its center to the corresponding dimension (B ₂ ) of Fork portion (76, 78) at its ends is in the range of about 1: 1.5 to 1: 2.5, preferably about 1: 2.

16. Swing piston machine according to one of claims 12 to 15, characterized in that a ratio between the dimension (B ₂ ) of the fork section (76, 78) in the direction perpendicular to the pivot axis (42) at its ends to the dimension (B ₃ ) of the fork section (76, 78) in the direction of the pivot axis (42) is in the range from approximately 1: 2 to approximately 1: 4, preferably approximately 1: 1.375.

17. Swing piston machine according to one of claims 12 to 16, characterized in that a ratio of the thickness (D) of the fork section (76, 78) in the region of the output shaft (64) to the dimension (B ₃ ) of the fork section (76, 78) in Direction of the pivot axis (42) is in the range of about 1: 2 to 1: 4, preferably about 1: 2.75.

18. Swing piston machine according to one of claims 12 to 17, characterized in that the second fork section (76) opposite a second substantially identical fork section (78) is arranged, which is also releasably connected to the end elements.

19. Swing piston machine according to claim 18, characterized in that the second fork section (78) has a further output shaft (74).

20. Swing piston machine according to one of claims 12 to 19, characterized in that the first and / or second fork section (76, 78) extends around an axis perpendicular to the circumferential (40) and to the swivel axis (42) and is / are on the outside spherical surface.

21. Swinging piston machine according to one of claims 12 to 20, characterized in that a piston rear side surfaces of the pistons (32-38) facing side of the first and / or second fork section (76, 78) is curved so as to complement the piston rear surfaces.

22. Swinging piston machine according to one of claims 12 to 21, characterized in that pre-pressure and or cooling chambers are formed between the piston rear surfaces and the corresponding facing side of the fork section (76, 78).

23. Swinging piston machine according to one of claims 1 to 22, characterized in that each piston (32-38) has a roller (108-114), the roller axis of which, with respect to the piston working surface, is preferably at an angle of approximately 30 ° to 50 ° is inclined by about 35 °.

24. Swinging piston machine according to claim 23, characterized in that the rollers (108-114) are conical, an imaginary extension of each cone giving a cone tip which lies in the center of the housing.