EP0784147B1 - Rotary piston machine - Google Patents

Description

The invention relates to a rotary piston machine with sealing rods according to the preamble of the claim 1. In the rotary piston machine previously known from US-A-3 809 026 with gasket sets, the rotors are in cross section elliptical and the seal sets in cross section partially round sealing rods built up, via a connecting part are rigidly connected. Based on these Construction generally lies only one of the two Sealing rods of a seal set on the lateral surfaces of the Rotors on, the other sealing rod is free and without system before, this is shown in Figure 8 of said patent. The sealing strips are therefore not guided, hit back and forth during operation and need additional Tools, such as the internal pressure, in the sealing position to be brought. Another disadvantage is the extraordinarily high friction between the rigid sealing rods and the rotary piston peripheral surfaces, each rotary piston is touched by the sealing rods at least twice. Have similar disadvantages with regard to sealing friction also those from French Patent Specification No. 657 191 and of the rotary piston machine previously known from EP 0 339 034 B1 on. When executed according to the French patent specification No. 657 191 ensure internal pressure, centrifugal force and in the direction of friction rigid sealing rods for increased friction as with the version according to EP 0 339 034 B1, in which the wedge-shaped Profile of the rigid sealing rods in connection with the internal pressure increases friction.

This is where the invention comes in. She has made it her goal the sealing system of a special rotary piston machine, the one inner, radial only by at least has four rotary lobes to improve the working space.

Proceeding from this, the invention proposes to solve this Task that the centers of the cross section of a Arcs delimiting rotary pistons with the radii r and R lie on the corner points of a diamond and that the center points the larger arcs the corner points with the larger ones Diamond angles are assigned, with the larger diamond angles Alpha are 5 ° to 50 ° larger than the smaller ones Angle beta and that the sealing rods in each of their perpendicular cross-sectional areas arranged in relation to their longitudinal axes have outwards by a circle are limited and that the sealing rods around their longitudinal axis are freely rotatable.

Such sealing rods are simply designed and very easy to manufacture parts, they can be axially in the Insert the gap area between two adjacent rotary pistons and therefore easy to assemble. You can do that too can be easily replaced by an end wall of the housing Will get removed. The sealing rods are with the rotary lobes, that seal them against each other, not firmly connected, rather, they are made by rotating pistons in the gaps inserted positioning parts held in place, which in turn address themselves to the Support rotary piston circumferential surfaces. Here is the one of the two guide rollers of a positioning part one side of a nip and the other guide roller on the other side of the same gap. Both guide rollers have such large cross-sectional dimensions that they do not can be moved through the gap and are through connected at least one connecting part. Because of of the one connecting them reaching through the gap Connecting part can be the two guide rollers of a positioning part do not remove from each other. she are therefore generally axially between two adjacent ones Rotary piston inserted or removed. The guide rollers can have holes or pins or lugs with which they hold the sealing rods in place to the gap without them to prevent rotation about the longitudinal axis of the sealing rod.

The gap between two adjacent rotary pistons is defined by the arcs delimited with two different radii, which also limit the rotary piston cross sections. Depending on the relative position two adjacent rotary lobes to each other, whereby the main straight lines of those in one plane Cross sections are always perpendicular to each other Gap delimited by an arc with a large radius R on one side and an arc with a smaller radius r on the other hand, a mixture of both arcs in the area of the connection points, or an arc with a smaller radius r on one side and one Circular arc with the large radius R on the other side. In practical operation, the shape of the Split constantly. To ensure that the guide rollers a positioning part in all rotary positions of the rotary pistons out of their peripheral surfaces with sufficient tightness be, the actual gap width of the gap must periodically change, since the two guide rollers of a positioning part through the connecting part always the same distance from each other. The actual gap width must be greatest when the main piston axis is straight the axis connecting line of two adjacent rotary lobe shafts includes an angle Phi of 45 ° in a cross-sectional plane, the rotary lobes are then in the V position. If the angle Phi = 0 °, the actual gap width of the The smallest gap, the rotary lobes are then in the T position. In operation, the is in the V position on the Acceleration attacking sealing rods greatest and in T-position smallest at maximum speed. In these two extreme positions of the rotary lobes, i.e. the V position and the T position, the guide rollers of a positioning part lie as close as possible to the circumferential surfaces of the rotary lobes, d. that is, the smallest possible mutual distance between the two Guide rollers of a positioning part should be in the T position the rotary piston must be the same size as in the V position.

This geometric condition can only be achieved if the centers of the delimiting the cross section of a rotary piston Circular arcs with the radii r and R on the corner points a diamond and the centers of the larger ones Arcs assigned to the corner points with the larger diamond angles are, the larger diamond angles alpha by 5 ° up to 50 ° larger than the smaller diamond angles Beta. Just if this geometric condition is met and a corresponding one Rotary piston with its dimensions R and r and Alpha is present, you can with a selected sealing rod diameter d a necessary center distance A between two neighboring Determine the rotary piston on which the two guide rollers of a positioning part both in the V position and in T position of the rotary lobes must be guided closely. Detecting of the necessary center distance A can be achieved by gradually enlarge or reduce the same. You would choose a square instead of the diamond, then the smallest possible Distance of the guide rollers in the T position always smaller than in the V position and good guidance of the positioning parts would then not be possible. In the case of EP 0 339 034 B1 shown rotary piston cross sections in Fig. 5 and Fig. 6 are the center points of the rotary lobe cross sections Arcs on squares.

Fig. 1

ein Schnittbild durch eine Rotationskolbenmaschine nach der Erfindung mit eingelegten Dichtungssätzen,

Fig. 2

ein Schnitt durch ein Drehkolbenpaar mit Dichtungssatz gemäß Fig. 1,

Fig. 3a - Fig. 3b

ein Drehkolbenpaar mit Schnittbild eines Dichtungssatzes gemäß Fig. 1 und Fig. 2 mit Zapfen,

Fig. 4a - Fig. 4b

ein Positionierteil in Vorder- und Seitenansicht gemäß Fig. 1 bis Fig. 3b,

Fig. 5a - Fig. 5b

ein Drehkolbenpaar mit Schnittbild eines Dichtungssatzes mit Nasen,

Fig. 6a - Fig. 6b

ein Drehkolbenpaar mit Schnittbild eines Dichtungssatzes mit Führungswelle und einer Dichtstange,

Fig. 7a - Fig. 7b

ein Drehkolbenpaar mit Schnittbild eines Dichtungssatzes mit nur einem Positionierteil, einer Führungswelle, Entlastungsrollen und zwei Dichtstangen,

Fig. 8a - Fig. 8b

ein Positionierteil in Vorder- und Seitenansicht gemäß Fig. 7a - Fig. 7b,

Fig. 9a - Fig. 9b

ein Drehkolbenpaar mit Schnittbild eines Dichtungssatzes mit Positionierteilen gemäß Fig. 8a - Fig. 8b und zwei Dichtstangen,

Fig. 10a - Fig. 10b

ein Drehkolbenpaar mit jeweils einer umlaufenden Nut mit Rechteckprofil und Schnittbild eines Positionierteils mit einer Dichtstange,

Fig. 11a - Fig. 11b

wie Fig. 10a - Fig. 10b, aber mit zusätzlichen Entlastungsrollen,

Fig. 12a - Fig. 12b

wie Fig. 10a - Fig. 10b, aber mit Ausrundung im Nutgrund und zwei Dichtstangen,

Fig. 13a - Fig. 13b

ein Drehkolbenpaar mit jeweils zwei ausgerundeten Stufen, zwei Positionierteilen und zwei Dichtstangen,

Fig. 14a - Fig. 14b

wie Fig. 13a - Fig. 13b, aber mit zwei Führungswellen und zwei Dichtstangen mit Längsbohrungen,

Fig. 15a - Fig. 15b

ein Drehkolbenpaar mit jeweils zwei rechteckigen Stufen, zwei Positionierteilen und zwei rollengelagerten Dichtstangen mit Dichtscheiben,

Fig. 16a - Fig. 16b

ein Drehkolbenpaar mit einem Dichtungssatz, wobei der Dichtstangenaußendurchmesser größer ist als der Durchmesser des Kreisumfangs, der den Profilquerschnitt einer Führungswalze begrenzt,

Fig. 17a - Fig. 17b

ein Drehkolbenpaar mit einem Dichtungssatz, wobei die axiale Länge der Dichtstangen kleiner ist als deren Außendurchmesser.

The advantages achieved by the invention consist in particular in that the changed shape of the conventional rotary pistons makes it possible to have well-functioning sealing rods made of round rods that closely fit against the peripheral surfaces of the rotary piston, which roll on the rotating pistons rotating in the same direction and whose friction on the rotary pistons is reduced by rolling friction . Further advantages and features of the invention emerge from the remaining claims and the following description of non-restrictive exemplary embodiments, which are explained in more detail with reference to the drawings, in which:

Fig. 1

2 shows a sectional view through a rotary piston machine according to the invention with inserted sealing sets,

Fig. 2

2 shows a section through a pair of rotary pistons with a seal set according to FIG. 1,

Figures 3a-3b

2 shows a pair of rotary lobes with a sectional view of a seal set according to FIG. 1 and FIG.

Figures 4a-4b

2 a positioning part in front and side view according to FIGS. 1 to 3b,

5a-5b

a pair of rotary lobes with a sectional view of a seal set with lugs,

6a-6b

a pair of rotary lobes with a sectional view of a seal set with a guide shaft and a sealing rod,

Figures 7a-7b

a pair of rotary lobes with a sectional view of a seal set with only one positioning part, a guide shaft, relief rollers and two sealing rods,

Figures 8a-8b

6 a positioning part in front and side view according to FIGS. 7a-7b,

Figures 9a-9b

8 shows a pair of rotary pistons with a sectional view of a seal set with positioning parts according to FIGS. 8a-8b and two sealing rods,

Figures 10a-10b

a pair of rotary lobes, each with a circumferential groove with a rectangular profile and sectional view of a positioning part with a sealing rod,

Figures 11a-11b

like FIGS. 10a-10b, but with additional relief rollers,

Figures 12a-12b

as in FIGS. 10a-10b, but with rounding in the base of the groove and two sealing rods,

Figures 13a-13b

a pair of rotary lobes, each with two rounded steps, two positioning parts and two sealing rods,

14a-14b

like FIGS. 13a-13b, but with two guide shafts and two sealing rods with longitudinal bores,

Figures 15a-15b

a pair of rotary pistons, each with two rectangular steps, two positioning parts and two roller-bearing sealing rods with sealing washers,

Figures 16a-16b

a pair of rotary pistons with a seal set, the outer diameter of the sealing rod being larger than the diameter of the circumference which limits the profile cross section of a guide roller,

Figures 17a-17b

a pair of rotary lobes with a seal set, the axial length of the sealing rods being less than their outer diameter.

In Fig. 1, a piston arrangement 8 is a sectional view Rotary piston machine shown in a gas-tight Interior 4 of a housing 6 is located. It is made up of four constructed with each other identically designed rotary pistons 10, which are designed as straight cylinders. In Figure 1 sees their cross sections 20, the end faces 12 are identical. The end faces are made up of four circular arc pieces 22,24 limits the different radii, namely a larger radius R and a smaller radius r, to have. The centers of the arcs of the arcs are located 22.24 on the corner points 38.40 of a diamond and the Centers of the larger arcs 24 are the corner points 40 associated with the larger diamond angles, the larger Diamond angles alpha or α are larger by 5 ° to 50 ° than the smaller diamond angles beta or β. The circular arc pieces 22, 24 are placed alternately at connection points 26, in these they go tangentially into one another about. Each rotary lobe 10 has one associated with it rotatably connected in the housing 6 shaft 16 rotatably runs through its geometric central axis 14. The single ones Shafts are rotationally synchronized with each other by a gear, so that the relative angular position of the individual rotary lobes 10 to each other remains. The rotary pistons 10 are rotatable in the same direction as an arrow 18. The End faces of the rotary pistons 10 are arranged in alignment with one another, are therefore on the same level. The four rotary pistons 10 limit laterally by their curved Circumferential surfaces 30 an inner work space 28, which at its End areas is limited by surfaces of the housing 6, the delimiting surfaces by a spacer bar 2 be kept at a distance. Between the neighboring rotary pistons 10 there is a gap S, the actual one Gap width S 'periodically with the rotation of the rotary lobes 10 changes. The gap width S 'is greatest when the rotary piston main axis straight line 84 with the axis connecting line 86 forms an angle Phi or ϕ of 45 ° and it is smallest if the angle Phi or ϕ is 0 °.

The seal between adjacent rotary pistons 10 is achieved by seal kits 32, with S for each gap a seal set 32 is provided. The seal kits 32 are made up of positioning parts 34 and sealing rods 36, each positioning part 34 has two guide rollers 44, with which it is in the gap area between the rotary lobes 10 on the adjacent rotary piston peripheral surfaces 30 supported and thus centered. Otherwise, the two are Guide rollers 44 of a positioning part 34 by at least a connecting part 50 between two adjacent rotary pistons 10 reaches through, connected and can thus do not move away from each other. The two also point Guide rollers 44 of a positioning part 34 so large Cross-sectional dimensions indicate that they are not through the gap can be moved through. The actual seal of the gap between two adjacent rotary pistons 10 achieved with a round sealing rod 36, the cross section 37 is limited to the outside by a circle and by Lugs 52 or bores 54 and / or pins 56 of the guide rollers 44 is held in its position to the gap.

The center distance A of two adjacent rotary pistons 10 in Figure 1 results from the selected rotary piston dimensions R and r and diamond angle alpha and the selected sealing rod diameter d and must be so large that the smallest possible mutual Distance E between two guide rollers 44 of a positioning part 34 in the rotary lobe position with Phi = 45 ° or at largest gap width S 'is as large as the smallest possible mutual distance of the guide rollers 44 at the Rotary piston position with Phi = 0 ° or with the smallest gap width S '.

The associated center distance A can be determined by graphic or arithmetic iteration. In one practical example, the large radius R is 60 Millimeters, the small radius r is equal to 20 millimeters, the large diamond angles alpha equal to 100 ° and the sealing rod diameter d is 7.5 millimeters. The determined center distance is 89.2 millimeters. There is a diamond side always as large as the difference R - r in the example given equal to 40 millimeters, which also results from the geometric Condition for tangential transitions at the connection points 26 of the arcs 22.24 results. In the example given and also in FIG. 1, the profile cross sections 46 of FIG Guide rollers 44 delimited by circumferences 48, each have the same radius as the sealing rods 36. With the rotary lobe position with Phi = 45 ° and with the rotary lobe position with Phi = 0 ° the center points of the Circles, the circumferences 48 of the profile cross sections 46 of the guide rollers 44 in the area of contact with the rotary lobes 10 limit on the center line 42 of the associated sealing rods 36 abutting rotary piston peripheral surfaces 30. This geometric relationship also applies when the radii of the circumferences 48 of the guide roller profile cross sections 46 are larger than the radii of the sealing rod cross-sections 37. So the rotary piston 10 in the example given with the radii R = 60 millimeters and r = 20 millimeters a 4 millimeter deep groove 64 for guiding larger guide rollers 44 get 50 with wider connecting parts, the radius of the guide roller profile cross section 46 delimiting circumference 48 at least in the contact area with the rotary lobes 10 by 4 millimeters larger than that Radius of curvature of those abutting the rotary piston peripheral surfaces 30 Seal rod surfaces 74. The radius of the Guide roller profile cross section 46 limiting circumference 48 would then at least be in contact with the rotary lobes 10 assume the value of 7.75 millimeters. From manufacturing technology For reasons, it will usually make sense to use the guide roller profile cross section in its entire area by the Limit circumference 48. A very practical method the optimal center distance between two adjacent rotary pistons to determine consists of the following:

To the previously selected values of the radii R and r and the Diamond angle α in such a way that a well-defined Rotary lobe contour results, you choose a sealing rod diameter in the right size ratio.

Then you draw a pair of rotary lobes in the T position (Phi = 0 °), the gap width S 'initially being zero. To the Rotary piston faces are drawn one round Line at a distance that corresponds to the sealing rod radius, as a geometric location for the sealing rod cross-sectional centers. About the T position drawn in this way a V position (Phi = 45 °) is then drawn. In the T position and the V position intersect lines around the sealing rod radius, in each case two points, the point spacing in the V position is initially larger than in the T position. Now you pull a rotary lobe with its view drawn in Direction of the axis connecting line 86 gradually from his Opposite away (center distance enlargement) until the point distance is the same in the T position and the V position. The existing one Center distance is the optimal center distance A. This The method described is particularly suitable when used computer-assisted drawing systems (CAD devices).

In the embodiment according to Figures 1 to 3b each seal set 32 from two positioning parts 34 and a sealing rod 36. The sealing rod 36 is thereby Pin 56 held, each on one of the two Guide rollers 44 of a positioning member 34 and the engage in the bores 60 of the sealing rod 36. there have the circular circumferential length 48 of the guide roller profile cross sections 46 the same outer diameter as the sealing rods 36. In Figure 2, the angle of rotation ϕ = 22.5 °, in Figure 3a and Figure 3b is the angle of rotation ϕ = 0 °.

In the exemplary embodiment according to FIGS. 4a and 4b, a Positioning part 34 with guide rollers 44, pins 56 and Connecting part 50 shown, as in Figures 1 to 3b is used.

In the exemplary embodiment according to FIGS. 5a and 5b, a Sealing set 32 shown in longitudinal section, with its positioning parts 34 lugs 52 for holding the sealing rod 36 are attached.

In the exemplary embodiment according to FIGS. 6a and 6b, a Sealing rod 36 with longitudinal bore 60 shown on a Guide shaft 62 is rotatably mounted. The side ends the guide shaft 62 are in bores 54 of the guide rollers 44 held.

In the exemplary embodiment according to FIGS. 7a and 7b, a Sealing set 32 shown, which consists of a positioning part 34, two guide shafts 62, two sealing rods 36 and two rotatable stored relief rollers 88 there. It supports the positioning part 34 additionally over the relief rollers 88 on the rotary piston peripheral surfaces 30 and reduced so the friction.

In the exemplary embodiment according to FIGS. 8a and 8b, a Positioning part 34 shown, as shown in Figure 7a - Figure 7b and Figure 9a - Figure 9b is used. They have over a connecting part 50 connected guide rollers 44 holes 54 for receiving guide shafts 62 or pins.

In the exemplary embodiment according to FIGS. 9a and 9b, a Sealing set 32 with two mutually parallel Sealing rods 36 shown, the sealing rods 36 through machined pins in the holes 54 of the guide rollers 44 are rotatably mounted.

In the exemplary embodiment according to FIGS. 10a and 10b, a Sealing set 32 with a rotatably mounted sealing rod 36 and a positioning part 34, whose guide rollers 44 are guided in grooves 64 which in the rotary piston peripheral surfaces 30 are incorporated with the same depth everywhere. Figure 10a and Figure 10b are with the values of practical Exemplary embodiment drawn on a scale of 1: 1.

In the exemplary embodiment according to FIG. 11a and FIG. 11b, the up to onto the rotatably mounted relief rollers 88 as in FIG 10a and FIG. 10b, the advantages result reduced friction as in the embodiment of the figure 7a and 7b.

In the exemplary embodiment according to FIGS. 12a and 12b, a Sealing set 32 shown, which is constructed similarly to in Figure 10a and Figure 10b, but with two sealing rods 36 and Fillets 80 in the groove base 68. The guide rollers 44 also have correspondingly rounded curves.

In FIGS. 10a to 12b, the respective grooves have 64 in the same cross-sectional profile 76 throughout.

In the exemplary embodiment according to FIGS. 13a and 13b, a Seal set 32 with two rotatably mounted sealing rods 36 and two positioning parts 34 are shown, their guide rollers 44 are performed in stages 66 on the rotary piston end faces 12 are attached. The stages 66 in the Step base 70 fillets 82 on what the manufacture in particular facilitated in the manufacturing process. Appropriately fitting The guide rollers 44 also have curves.

In the exemplary embodiment according to FIGS. 14a and 14b, a Sealing set 32 shown, similar to that in Figures 13a and 13b is constructed, but the rotatable sealing rods 36 with longitudinal bores 60 in which guide shafts 62 are stored, the ends in bores 54 of the guide rollers 44 are held.

In the exemplary embodiment according to FIG. 15a and FIG. 15b, a sealing set 32 is shown, which is constructed similarly to FIG. 13a and FIG. 13b, but whose sealing rods 36 are roller-mounted in the guide rollers 44, the roller bearing being sealed by sealing disks 58 and the steps 66 being none Have fillets 88.
In FIGS. 13a to 15b, the respective stages 66 have the same cross-sectional profile 78 throughout.

In the exemplary embodiment according to FIGS. 16a and 16b, a Sealing set 32 shown, the sealing rods 36 on the Guide rollers 44 are rotatably mounted. The sealing rods 36 thus have a larger outer diameter d than the circumferences 48, which the profile cross sections 46 of the guide rollers 44 limit. The sealing rods 36 roll during operation on the bottom of the groove 68, which are incorporated in the rotary piston 10 Groove 64. Due to the enlarged sealing rod outer diameter d becomes the operating speed of the sealing rods 36 advantageously reduced and their wear surface increased.

In the exemplary embodiment according to FIG. 17a and FIG. 17b, a sealing set 32 is also shown, the sealing rods of which are mounted on the guide rollers 44 and have larger outer diameters d than the circumferences 48 of the guide roller profile cross sections 46, the respective axial length of the sealing rods 36 being smaller than their outer diameter d.
Compared to FIGS. 16a and 16b, this advantageously reduces the movable masses.

Claims (14)

1. Rotary piston engine

   A. with a piston arrangement (8) accommodated in a gasproof inner space (4) of a housing (6) and made up of at least four separate rotary pistons (10), all being substantially identically structured and having end faces (12) arranged in alignment with one another, which are non-rotatably connected to shafts (16), assigned to them in each case, carried rotatably in the housing (6), running through their geometric central axes (14) and rotatably synchronised with one another via gears, with which shafts they are rotatable in the same direction of rotation (18) about their geometric central axes (14), which are vertical to their end faces and/or cross-sections (20), which are constructed as straight cylinders whose cross-sections (20) parallel to the rotary piston end faces (12) are limited in each case by four circular arcs (22, 24) with two different radii r, R, the circular arc pieces of which with the same radius r or R all have the same arc length in each case and are placed together alternately at connection points (26), at which they merge into one another tangentially and which laterally limit an inner working space (28) by their curved circumferential faces (30), wherein between adjacent rotary pistons (10) there is a gap S with a periodically changing width S' in each position,

   B. and with sets of seals (32) consisting of positioning parts (34) and sealing rods (36), wherein to each gap S is assigned a set of seals (32), which in each case has at least one sealing rod (36) which has a cross-sectional width which is larger than the width S' of the gap S and which is held in its position in relation to the gap S by at least one positioning part (34) which reaches through between two adjacent rotary pistons (10) and which cross-sectional width has a length corresponding at a maximum to the length of the rotary pistons (10),

   characterised in that
   the central points of the circular arcs (22, 24) with the radii r and R limiting the cross-section (20) of a rotary piston (10) are located on the corner points (38, 40) of a rhombus and the central points of the larger circular arcs (24) are assigned to the corner points (40) with the larger rhomboid angles, wherein the larger rhomboid angles Alpha (á) are 5° to 50° larger than the smaller rhomboid angles Beta (â) and in each of their cross-sections (37) arranged vertically to their longitudinal axes (42) the sealing rods (36) have cross-sectional faces which are limited outwardly by a circle and the sealing rods (36) are freely rotatable about their longitudinal axis (42).
2. Rotary piston engine according to Claim 1,
   characterised in that
   each positioning part (34) has two parallel guide cylinders (44) located opposite one another, with which it is supported on two adjacent rotary pistons (10) and which are connected to one another via at least one connecting part (50) .
3. Rotary piston engine according to Claim 1 or 2,
   characterised in that
   the profile cross-section (46) of a guide cylinder (44) parallel to the rotary piston cross-sections (20) and sealing rod cross-sections is limited at least in the region where it touches the rotary pistons (10) by the circumference (48) of a circle whose diameter has one to four times the value of the sealing rod outer diameter d.
4. Rotary piston engine according to one of Claims 1 to 3,
   characterised in that
   the guide cylinders (44) have projections (52) or bores (54) and/or pins (56) by which the sealing rods (36) are held in their position in relation to the gap S.
5. Rotary piston engine according to one of Claims 1 to 4,
   characterised in that
   each set of seals (32) has at least two sealing rods (36) parallel to one another with outer diameters d identical to one another.
6. Rotary piston engine according to one of Claims 1 to 5,
   characterised in that
   the guide cylinders (44) are guided by grooves (64) located on the rotary pistons (10) and/or steps (66) on the end face of the rotary pistons and are supported on the bottom of the groove (68) and/or bottom of the steps (70).
7. Rotary piston engine according to one of Claims 1 to 6,
   characterised in that
   the grooves (64) and/or steps (66) located on the rotary pistons (10) have the same cross-sectional profile (76, 78) throughout their course.
8. Rotary piston engine according to one of Claims 1 to 7,
   characterised in that
   the grooves (64) and/or bottom of the steps (70) located on the rotary pistons have hollows (80, 82).
9. Rotary piston engine according to one of Claims 1 to 8,
   characterised in that
   the width (72) of the connecting part (50) is 0.2 to 3 times the sealing rod outer diameter d.
10. Rotary piston engine according to one of Claims 1 to 9,
    characterised in that
    the sealing rods (36) are carried on rollers in the guide cylinders (44) of the positioning parts (34).
11. Rotary piston engine according to one of Claims 1 to 9,
    characterised in that
    the sealing rods (36) have longitudinal bores (60) in which guide shafts (62) or pins (56) are carried, which are held by the guide cylinders (44).
12. Rotary piston engine according to one of Claims 1 to 4 and 6 to 11, characterised in that
    one of the two guide cylinders (44) of a positioning part (34) has relief rollers (88) with which the positioning part is additionally supported on the rotary piston circumferential faces (30), wherein the outer diameters of the relief rollers are the same size as the outer diameters d of the sealing rods.
13. Rotary piston engine according to one of Claims 1 to 2, 5, 7 to 9 and 11, characterised in that
    the sealing rod outer diameters d are larger than the diameters of the peripheries (48) on the profile cross-section (46) of the guide cylinders (44) in the region where they touch the rotary pistons (10).
14. Rotary piston engine according to one of Claims 1 to 2, 5, 7 to 9, 11 and 13 characterised in that
    the axial length of a sealing rod has 0.2 to 40 times the value of the sealing rod outer diameter d.

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