DE2443290A1 - MACHINE WITH HYPERELLIPTICAL GEARS - Google Patents

Description

TlEDTKE - BüHLING "f \ INNE

Patent attorneys:

Dipl.-Ing.Tiedtke
Dipl.-Chem. Bühling
Dipl.-Ing. Chins

8 Munich 2

Bavariaring 4, PO Box 202403

Tel .: (089) 539653-56
Telex: 524845 tipat
cable address: Germaniapatent Munich

Munich, September 10, 1974 B 6195 / case G.63047 ·.

Luigi Murone
Rome, Italy

Machine with hyperelliptical gears

The invention relates to a novel

Machine.

The term "machine" in the sense used here includes:

a) prime movers, especially internal combustion engines]! (Diesel or gasoline engines) or machines with external combustion, .

b) work machines, especially pumps, and

c) Gear, in particular gear transmission with variable transmission ratio, i.e. with non-round gears,

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VI / 3

Deutschs Bank (Munich) Account 51/61070 Dresdner Bank (Munich) Account 3339644 "Postscheck (Mönchen) Account 67043-804

The object of the invention is to create a new and useful machine which, in its simplest form a transmission with gears with variable transmission ratio, "the use of which contains the production of pumps and motors particularly simple and easy, as well as enables more powerful training.

Furthermore, with the invention simple internal combustion engines with internal and external combustion with good Performances and simple, light and powerful pumps are created that are reversible to motors.

According to the invention, the new machine is essentially characterized in that it has at least one pair of the same Has gears whose profile was obtained from an ellipse,

According to an important aspect of the invention, the profile of the gears is hyperelliptical according to the following polar equation:

/ _s a ff

a sin ν · ^χ + F cos t Λ

where / represents the polar radius connecting the geometric center of the hyper-ellipse to one of its points V ; ä is the major semi-axis of the ellipse, b the smaller, and <X the angle thatJ? forms with the larger semi-axis.

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The invention will be explained below with reference to the description of exemplary embodiments with reference to the drawing nSher explained.

Fig. 1 shows how, starting from an ellipse, the polar equation of the profile "of the new hyperel Liptical gear can get; . .

Fig. 2 shows a schematic with solid lines hyperelliptical gear pair and dashed a hyperelliptical double gear pair, the work together, two being angularly displaced to each other but fixed on the same axis and two are on the same axis, but adjustable in angle relative to one another;

Fig. 3 shows the double pair in a special position;

ift. ¹ I represents a scheme that the structure and the

Function of an internal combustion engine explained in the

Figures 5, 6 and 7 are shown which are a cross-section

along the line V-V in Fig. 6, an axial section according to the line VI-VI of the Pig, 5 and 6 respectively. an exploded partial section of a

Represent part of the engine; 50981 1/1070

Fig. 8 shows one largely of the Fier. 5 corresponding Section of a first engine version with external combustion,

Fig. 9 shows schematically in cross section a simple one Pump with hyperelliptical gears;

FIG. 10 shows one that largely corresponds to FIG View of a modification of the engine with external combustion;

11 'shows schematically the relative arrangement of the

diametrical impellers to the two hyperelliptical gear pairs of the motor according to the Fig. 10.

For the production of a gear pair with a variable transmission ratio (i.e. non-circular gears) the problem of determining the profiles of two (non-circular) Wheels, which roll on each other when turning around their centers, without to shift against each other. For this to happen, it is necessary and sufficient that the following coupling conditions are met:

(1) a) The two profiles must have the same tangent at the point of contact;

b) the sum of the conjugate connecting points

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Radius must be constant (two points are to be understood as conjugate that belong to the two profiles and those at the rotation coincide),

c) the arcs described by the conjugate points on the two profiles must be the same.

These requirements are met by a square or hyper-ellipse, which is also a convex profile possesses, which is suitable for the formation of a gearwheel. To determine this hyper-ellipse, proceed as follows:

1, an ellipse E with the center O, the half-axes OA = a and OB = B (a> b), the polar radius f - OP and the deviation O ^ are determined and the two circumferences E are determined ₁ , Ep, the generatrices of the ellipse drawn, which have the radius a and b. If the perpendicular and the parallel to OA are drawn, which go through P, the two points R- and R _{2 are obtained on the perimeters E 1} and E ₂ , which lie on the same radius OR- that with OA the angle Θ , namely forms the eccentric deviation. If a radius OS _{1 is} drawn at 90 ° to the radius OR ₁ , it intersects the two generating circumferences at the points S- and Sp. If the parallel to OA is drawn through S ₂ or the perpendicular to OA through S-, one obtains the point Q in the intersection with the ellipse. The polar radius χΐ determined by this is conjugated with the polar radius /. If the two polar radii f and γ - are expressed as a function of θ, one obtains:

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(2) ? ² = a ² cos ² e + b ² sin ² 9

(3) / I ² = a ² sin ² e + b ² cos ² 9

The sum of these two equations gives: f ² + J> 1 ² '= a ² + b ²

Taking into account / sin p (= b sin θ and ufcos C ^ = a cos' Θ, we get:

(5) tgo <= I tg θ

If f is derived from θ in (2) and θ from OC in (5), you get:

(6) ^ - = (b ² - a ² )

There is now a curve m (still referred to as Pig. I)

considered, which is defined as the location of the points P * 'which around

2 2 ™ *

ξ s OF are away from the center 0. If one makes f - ξ , and consequently a = a and b = F, that is, one substitutes

O O Ο ■ ·

( S% a »b) s (J *, ¥, F) and V denotes the angle that the tangent t at F forms with the vector OF and s" denotes the length of the arc TfF (where X is the intersection of the Extension of OA jp ^ t m), one obtains from the previous

going equations:

(8) (j » ² , a ² , b ² ) = (f, ä, F)

= d B \ / ä F + (F- ä) * sin ² 2θ '

Apart from the sign in (10), (10) and (11) remain unchanged when the point P ~ is replaced by its conjugate ü (intersection of the extended radius S * ^ with the curve m), i.e. when the parameter θ is replaced by θ + ^ / 2.

Thus, taking into account the sign of (10), equations (9), (10), (11) completely satisfy the coupling conditions (1) for two curves which are the same as curve m but which are phase-shifted by Ti / 2 with respect to the parameter θ, ie at Coupling at the position conjugate with respect to θ. The curve m in question is referred to here as a quadratic or hyperellipse and its polar equation β (o <) is as follows:

a sin c ^ + b cos ¹ "(Λ

derived from equations (2), (8), (5) by obvious substitution.

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The equation for the tg V in polar representation that can be obtained from (5), (8), (10) is

(I ₃ ) tg ν =

(F - a) sin 2

while for the vertical component Y = FGT (G "is the point of intersection the perpendicular η through F with a radius OG ", the one Angle V with the guide radius OF forms) and the tangential component X = OC "with respect to the tangent t the following Equations apply:

CU) Y = f sin V
(15) X = f cos V

It is possible to prove that a second "elliptical" Solution exists which is given by the same ellipse E, but which is only rotated about one of its focal points. These too Solution is beneficial in certain applications, but in the applications envisaged here is the square ellipse best suited because of the centrality and mainly the regular return.

Without deviating from the purpose and concept of the invention, the hyper-ellipse (12) can be more or less approximate curve can be replaced, for example by the ellipse m, with the semiaxes a, F and the locus track

^ChUnß 509811/1070

2 2
XY
--W— + - "7 ⁼ *» ^ ^e ^ - ⁿ ^ iR · * is shown in dashed lines.

The formulas (12), (13), (14), (15) are for practical use Formation of a gear M with a hyperelliptical profile useful, the number of teeth must be divisible by four, so the curves m of the wheels to be coupled can be adapted conjugate.

As for the shape and manufacture of the teeth, the usual shapes and manufacturing processes can be used Find.

The two hyperelliptical, identical "■ gears M and N with semiaxes" and F in conjugate contact θ and θ + TIlZ are now taken into account, which are drawn continuously in FIG is aligned with the major semi-axis a of the other. This pair meets the requirements (1) and thus represents a gear (mechanical transmission) with a variable transmission ratio; this transmission ratio of the hyperelliptic pair M ₈ N can easily be determined by expressing the conjugate rotations c <and ß of M and N, as a function of θ via equations (5) and (8), ie

(16) tg (a s r tg θ and

(17) tgß = | tg (Θ ψ J ^) result

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(18) tgo <tgß = -! -.

Equation (18) represents the gear ratio of the pair M, N; in it the minus sign means that the two wheels are turning in opposite directions. In particular, a rotation of M by o {- -stones corresponds to a counter-rotation β of N according to

(19) tg ß * - JL ⁰ ä

It can be proven that (19) is a lower limit for (Ί8).

It is now assumed that (as shown by dashed lines in FIG. 2 and FIG. 3) on a shaft Q two identical hyperelliptical wheels M and M ~ are keyed at an angle offset from one another by Ti / 2 and occupy a position which by rotating the wheel M by C? C = —w— and οι s - - jp. It is also assumed that two hyperelliptical wheels N ₁ and N ₂ are loosely mounted on the shaft 01, each in engagement with the wheels M ₁ and M _2. The position of these wheels N ₁ and N ₂ is the one that would take the Rad.N when the wheel M from the position shown in Figure 2 Lage'heraus um.o ^ _o = -. "- would twisted. Accordingly, in the position shown, the larger axes' of the wheels N ₁ and N _{2 are} at an angular distance from one another of 2 ß _Q

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2A43290

The machine obtained according to the aforementioned measures is referred to here as a "double hyperelliptical pair" M ₁ N ₁ ZM ₃ N ₂ with half-waves ", F and axes of rotation 0,0 '.

If one continues from the transmission ratio of (18), with «the rotation of the shaft 0, thus of the complex Q, M M ₀ , with B ₁ = -arc tg (-3- cot tf) the corresponding rotation of

c · a

and with ß _? = arctg (~ - tgCtf) denotes that of N ₂ and

a
calculates the difference between the values of ftp ^unc * ^ i obtained as a function of OT, a parameter £ is found (hereinafter referred to as "angular deviation") which largely determines the variability of the mutual angular distance between the wheels N ₁ and N ₂ when changing of ^ expresses, namely

(20) £ = ß ₂ - B ₁ = arctg (-—- tg (X) + arctg (~ * ·

a a

If the traced discrete values of Oi are now inserted in (20), the corresponding fourths of £ are obtained , namely: '

(21)

ex C. 0 τ iz TT / £ ^{2 ß} o 3/4 U TT- 2 ß _o - ii

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From this table (21) it can easily be seen that the deviation £ between the minimum value ί „= 2 R
and the maximum value £ _R = ~ iC - 2 ß _Q changes, ie

(22) 2 8> _o % £ ^ (IC -2 A _o ), namely

with an (angular) frequency o (* 7Γ, so that £ assumes the same value for every half revolution of the shaft 0. This can also be seen clearly from FIG
with each quarter turn of the shaft Q each of the wheels N ₁ ,
N ₂ occupies exactly the previous position of the other wheel.

Due to the aforementioned important features, the hyperelliptical gear train can advantageously be used for transmissions with variable gear ratios
Find use. In particular, the simple and the
double pairs to create new types of pumps and rotary motors with variable volume ■. In this case, the angular frequency o ( = ⁷ T of the double pair drive eliminates the distribution mechanisms that are generally used for
Ignition, exhaust, suction and the like are otherwise required, whereby the advantage of simplicity, less bulkiness and lower weight is given.

A more detailed explanation of the structure and function of a hyperelliptic combustion circulating combustion engine is now made to Fig. ¹ I, 5, 6 and 7 taken respect.

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In Fig. 4 the functional scheme of the engine is shown and in the Fip. 5, _9, 6 and 7, its structure is shown.

In Fig. ¹ \ a hyperelliptical double wheel pair 26, 27, 28 and 29 with the radii, b and the axes of rotation O and O \ is shown, in which the angle divergence £ (20) the limit values 2ß and (K-ZSb ) of the area (22). The two ο ο

Partial drives 26,27 and 28,29 are attached at an axial distance, with the two RSder 27 and 28 on the output shaft 8 are arranged at a distance, while on two identical half-waves 19, 20 with a common axis 0 'each per half-wave the wheels 26 and 29 are keyed.

Between the two pairs 26, 27 and 23, 29, a motor cylinder 1 is arranged with a ^{cylindrical chamber 15 lying on the same axis as the axis O 1} , that is to say on the same axis as the half-shafts 19, 20.

^{Two diametrical rotors i} »6, 117 _/ each of which is fastened to a different half-shaft 19, 20 rotate in the chamber 15.

Each of the runner consists of a "V-shaped rigid body" (fixed surface angle) with the axis O ¹ and a fixed angle £ ₂ ^ ^2ß _o ^{»durcn of the} engine cylinder 1 and the half-waves is limited ^s 19,20. ■

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Each of the two runners ^ 6,47 (which are pushed into one another, as will emerge from the later explanation) is Fixedly connected via one of the half-shafts 19, 20 to one of the gears 26, 29, to which the runners have the same orientation exhibit.

The two diametrical runners divide the cylindrical chamber 15 into four variable spaces (volumes) V ₁ , ^V 2 »VV

This conceptually constitutes a single cylinder rotary engine, four-stroke cycle and four variable volumes, each of which makes the four strokes in a single revolution, since (X = TT (21).

Since the fixed angle £ ρ ^ er runner was determined with the only restriction £ ₂ * =: 2ß_, the minimum angular opening £ _Q and the largest angular opening C ₁ for each of the four variable volumes and thus also the compression ratio - »of the engine is determined.

(23)

(25) f * L ·. -

6 0 9 ^a 8 1 1/1 0 7 0

For example, in the explanatory drawings:

(26) / (a = 60 mm; b = 30 mm) f ₂ = 26.5 °;
= 1 / 10.2

= 26.5 °; 2 [beta] _Q = 53 [deg.]; € _Q = 8 °; £ 1 = 82 °;

In the initial position of Fig. Ί- are diametrically opposed to each other two minimum volumes V ^, V, with Winkelöffnunp £ _Q and two maximum volumes V ₂ , V ₁₄ ^{with winkelöfi> now} ß € \ , which at the beginning of the rotation o ( after the motor shaft 8 increase or decrease right or left (20), (21), (22). Since the ignition area is determined along the upper surface line of the cylinder, i.e. above the volume V ^, an exhaust port 6 and a suction port 5, both with the (angle) · size £ * 2 »to _{exactly match the sliders U6 9} U7 on the lower part of the cylinder (Fig. 5).

However, the ignition range only comes into contact with the variable volumes V ₁ , V ₂ , V 1, V ^ when they approach the minimum value c. Therefore, no periodic sequence of the ignition is required and spark plugs 3 (or injection nozzles) can work continuously. Apart from early or retarded ignitions (which must be determined by experiment), the exhaust port also converts to the intake or inlet port and vice versa if the direction of rotation of the motor shaft is reversed.

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The above technically discussed engine has a generally designated 1 cylinder on his upper part has recesses 2 for spark plugs or injection nozzles 3, which in a wedge-shaped groove 4 along an inner Surface line end. The exhaust and suction lines 5 and 6 are formed laterally. The lower part is a cylindrical one Space 7 is provided in which the drive shaft 3 runs. The cylinder 1 has a jacket 9 for a cooling liquid its constant cooling on all parts, including the bottom at 9A. The fluid from any known supply runs into and out of the jacket shell through passages or bores 10, 11. In the lowest part of the cylinder 1 is a Usual oil pan 12 with connection and collection holes 13,1Ί intended.

For the lateral delimitation of the cylindrical chamber 15 in the cylinder 1, two identical plug-shaped inner ones are used Front parts 16 used. These front parts carry the two half-shafts 19 and 20 by means of bearings 17 and seals 18. The lubrication the bearing is ensured via the channels 21, which are excluded from the end parts 16 and which are provided with cavities 22 in Connection that are limited to the outside by so-called. Outer heads 23, which are equal to each other.

These outer heads are oval, cup-shaped and are provided with supporting outer flanges 2H , into which a shoulder 25 of the inner end parts 16 engages. The outer head 23 delimit the cavity 22 in which the hyperelliptical gears 26,27,

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28 and 29 for the two drives are arranged. The gears 26 and 29 are mounted on the half-shafts 20 and 19, respectively, while the other two sit on the motor shaft 8. The outer heads 23 hold the half-shafts 19, 20 or the motor shaft B by means of bearings 30 and 31 mounted in correspondingly designed bearings 32, 32A therein the lubrication of the cylinder chamber 15 cannulas 35 »36 are provided in connection with the cavities 22, which receive the lubricant supplied via the openings 37. The channels 35 connect to conventional Einführpfropfen 38, the bearings JSA outwardly verschließenj where SINOE 30 is arranged the bearing _s and which introduce the lubricant into the axial hole HO of the half shafts 19,20 from where it is then transferred to the required places of non- Drawn passages arrives.

The two half-shafts 19, 20, which are identical to one another, are arranged on the same axis in the cylindrical chamber 15 and, as already mentioned, are rotatably supported in the bearings 17, 30. At their opposite inner ends they have a cylindrical receptacle ¹ Jl. Kl in each of the shots, the correspondingly shaped end of a Führungskorpers ¹ J2 is fitted, which runs through in the axial direction and is provided with a flange ¹ O, which is arranged between the ends of the half shafts 19 ₉ 20 and this' abuts addition, the half-waves provided with diametrically opposed longitudinal grooves ΊΊ, which through ^ i ₁ PgH ₀ diametrical slot passage ^ 5

ORJGiNAL INSPECTED

are connected to each other.

The passages 45 allow the attachment of the diametrical Rotors 46, 47, which represent the pistons of the present engine. In particular, each of the runners consists of diametrically opposite equal parts 46A, B and 47A, B which are approximately half of their length in the LSngsnuten 44 of the associated Half waves are let in and by means of an approach Reach into the diametrical slot 45. Two by the Slot 45 and the two parts of the runner leading screw bolts 48 hold the two parts tightly together. The two parts of each runner extend as previously indicated and shown, cantilevered over the other half-shaft, so that the two rotors 46, 47 axially on half of their Are pushed into one another length and jointly sweep over the hood space of the cylinder 15. Wise viewed in cross-section the two parts of the runners outside the half-waves accommodating them have a stiff V-shape. Along its perimeter where the waterproofing must be provided between the four chambers V1, V2, V3, V4, are in corresponding seats or grooves Usual elongated seals 49 are used (for example metallized graphite) known in the art of rotating internal combustion engines such as Vfankel engines.

The gears 27, 28 are keyed onto the shaft 8 with their larger diameters at right angles to one another. In the starting position (Fig. 5), the two opposing spaces Vl and V3 have a small size, while the others

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opposing spaces V2 and Vl have the maximum size. If the motor shaft 8 is rotated counterclockwise by "If U , the space Vl the combustion stroke, V2 the exhaust stroke, V3 the intake or intake stroke and V4 the compression stroke. If the shaft UmTD ₂ * ⁿ is rotated in the opposite direction, the cycles of the volumes V2 and Vl are interchanged. When turning in the counterclockwise direction, the opening 6 is used for letting out and the opening 5 for sucking in or letting in, while the ratios are reversed when the direction of rotation is reversed. In the one shown in the figures Execution, cycle pre- and post-cycle processes are obtained by working off the edges 60 of the runners and reducing the size of the ignition grooves ¹ J so that they can be reconciled with both directions of rotation.

It is important to note that each clock runs of the cycle within a quarter revolution of the shaft 8, because the repetition rate sk of the angular divergence £ same IC, so DA9 all four strokes of suction, "the compression, relaxation and the exhaust of an each of the four variable volumes (Vl, V2, V3, νΊ) during a single rotation off run · and therefore take place at each rotation four Nutζtakte (relaxation or combustion), so eight for two turns, as many as a standard eight-cylinder Engine would result.

The advantages that can be achieved on the basis of the invention are : Quite a simple design of the motor that does not have any

Ignition distribution and no suction and exhaust valve required,

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Possibility of using mist lubrication instead the circuit lubrication, inertial symmetry of the rotating masses, high achievable speed, large intake and exhaust openings and compact training with less weight.

In Fig. 8, a hyperelliptical thermal rotary engine with external combustion is shown. This Motor represents a modification of the internal combustion engine as described above, so that only the differences are indicated and the same reference numerals are used for the same or equivalent parts, but are preceded by the number "10". In this engine, the combustion area has been replaced by two new openings: an exhaust opening 106A and an intake opening 105A, which are formed in a diametrically opposite position to the pre-existing openings 105 and 106. Through this two independent circuits are created, which are externally connected in series or in a package. The reason is Gases or saturated vapors, which are charged with thermal energy from the outside, relax and thereby mechanical To achieve work. Therefore, the two intake openings 105, 105A are smaller than the two exhaust openings 106, 106A, the width being determined according to the desired relaxation. This double engine allows the energetic Conversion process in two ways:

A) by means of an open circuit using always new, via a single heat supply (single generator and parallel connection), or by means of two heat supplies (two generators and series connection) charged gas and expelling the

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- ■ 21 -

2A43290

used gas; or

B) in a closed circuit using the energetically charged gas in one of the two circuits with recirculation to the generator of the applied gas via the second Circle (series connection).

A modification of the motor of FIG. 8 is shown in FIGS. 10, 11. The same reference symbols with the prefix "20" are used here to designate the same parts or corresponding parts. The decisive difference is that the smallest volumes arise with a diameter perpendicular to that of FIG. 8, since the rotors 2ΟΊ6 and 20Ί7, contrary to the state according to FIG. 8, are wedged onto the corresponding half-waves 2019 and 2020 so ₉ that an angle of 90 ° (ß " - ^ / 2 ^ ^m ^ ^{t of the} Keßeren axis of the associated gear 2026, 2029 arises, Tn of FIG. 11, the double hyperelliptical pair 2026, 2027 and 2028 _s 2029 is shown in the respective limit position (22) For the rest, what has been said with regard to FIG. 8 applies.

Pei the two variations of the external combustion engine Winke1 the smallest-volume can be reduced £ to the tolerance limit, because the compression ratio Ϋ (25) no longer has any importance. In addition, the direction of rotation of the drive shaft is specified because of the different angular opening of the intake and exhaust.

From the above, it is evident that 509811/1070

a hyperelliptical pump with double circuit is nothing more than a motor with external combustion, with the only difference that in this case the two intake openings are the same as the two exhaust openings, whereby the direction of operation can be reversed by reversing the direction of rotation. There are again two independent circuits that can work separately in series or in parallel. The alignment ß _{o of} the runners to the double hyperellipse pair can be arbitrary. In particular, an embodiment similar to FIG. 8 with βp = O can be changed from one according to FIGS. 10 and 11 with B> 2 - 7Γ /? can be distinguished. Apart from the cooling and other less important details, reference is made to what has been said with regard to the thermal engine for external combustion.

FIG. 9 shows, in a schematic section, a simple hyperelliptical pump, which can also be used for only one single pump hyperelliptical pair of wheels 300, 301. This pump is the same as the usual gear pumps, with the only difference that the round gears are replaced by the hyperelliptical gear pair. In Fig. 9 are the double cylinder with 302, 303 and the shafts, one of which is driven, with 30 * 1 and 305, the usable space with 3O6 and the suction and Outlet lines designated 307, 30B.

The hyperelliptical pumps according to the invention can be converted into mechanical motors without any modification if the liquid flowing through corresponds to • '509811/1070

has sufficient mechanical energy (fiefjIlIe ₈ pressure and the like). In this case, the mechanical energy of the liquid is transferred to the motor shaft whereby it _s is usable. Because of their simple form and function and the lack of valves, distributors and other accessories, these machines are suitable to work continuously or alternately as pumps or as mechanical motors »

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Claims (1)

Claims 1.JMachine with at least one engaged Pair of identical gears, characterized by a variable Lich transmission ratio and through one out of an ellipse derived profile of the gears. 2. Machine according to claim J, characterized in that the profile of the gears follows the hynerelliptic curve at least comes close to the following polar equation: K ζ a F ä sin oi + F cos <V where J * is the polar radius that connects the geometric center of the hyperellipse with one of its points F, a is the major semiaxis of the hyperellipse, F is the smaller and Oi is the angle that ζ forms with the major semiaxis. 3. Machine according to one of the preceding claims, characterized in that it is a transmission, which has at least one pair of hyperelliptical gears of the same * design and in mesh with one another. U ₉ machine according to claim 2 or 3, characterized in that the hyperelliptical profile approximates an ellipse with the largest and smallest half-diameter a and F, respectively. 509811/1070 5. Machine according to one or more of the preceding claims, characterized in that it is at least has a double pair of gears which are roughly hyperelliptical, two of which are "angularly displaced but with one another are connected, and the other two mesh with the previous ones, but assume a relative angular displacement know. 6. Machine according to claim 5, characterized in that ^Q it has at least two diametrical rotors which are sealingly mounted in a common cylinder, each of which is firmly connected to one of the two gears, which can experience a relative Viinkelverstellung so that they are together can form different changeable volumes with the cylinder. 7. Machine according to claim 6, characterized in that are preferably arranged on a generatrix of the cylinder ignition devices (for a gasoline engine) or injectors (for a diesel engine) in a Mut. 8. Machine according to claim 7, characterized in that the ignition or injection devices are arranged on the cylinder where the variable volumes assume their minimum value. 9. A machine according to claim 7 or 8, characterized in that the ignition or injection devices constantly 50981 1/1070 are effective. 10. Machine according to one or more of the preceding claims 7 to 9, characterized in that the cylinder Has inlet and outlet openings, which through the Runners can be locked and which are arranged essentially opposite the ignition or injection devices. 11. Machine according to one or more of the preceding claims 5 to 10, characterized in that the cylinder is arranged between two cooperating pairs of wheels which are mounted in chambers supplied with lubricant, wherein the lubricant arrives at the required points by means of pitting. 12. Machine according to one or more of the preceding claims, characterized in that instead of the ignition or injectors a further pair of intake and exhaust channels is attached opposite to the first pair. 13. Machine according to one or more of the preceding claims, characterized in that the width of the suction opening is smaller in relation to that of the outlet opening. 50981 1/1070 Blank page