DE883905C - Rotary piston machine - Google Patents

Description

Rotary piston machine are known rotary piston machines with circular or circle-like and elliptical-like housings in which slide pistons for the seal between the piston barrel and the housing are provided. It is so far not succeeded with such machines with simple means and little Manufacturing effort a compensation of the centrifugal forces acting on the slide piston bring about.

With regard to the wear of the three main elements (piston drum, Slide piston and housing) were therefore the achievable speeds of such machines relatively low, and the leakage losses that occur as a function of time were high compared to piston engines.

This was shown, among other things, in the low pressure rating, which was possible when using such machines as compressors. The new construction according to the present invention avoids the disadvantages of those previously known Constructions by various details to be described below.

The present invention relates to a rotary piston machine, the multiple works effectively, wherein the piston drum is mounted centrally in the housing, which deviates significantly from the circular shape.

With this machine, either the piston drum can be stationary Rotate the housing, or the housing can revolve around the stationary piston barrel. Both parts can also be arranged to be rotatable in relative movement to one another. the Expediency of one or the other type of construction depends on the intended one Purpose of use. According to the invention come novel. Spool for use in which two spool pistons that are not diametrically opposite each other are rigidly connected to each other, each of these double slide pistons formed in this way is evenly curved and is guided in the piston drum so that its two Ends in constant contact with the wall of the housing during the revolutions of the The machine alternately protrudes more or less from the piston barrel.

This shape of the double slide piston in conjunction with the The housing shape to be selected is the contact surface for the double slide piston acting centrifugal forces from the narrow end edge to the wide side surface of the Relocated slide and thus significantly increasing the service life of the machine Achieved friction reduction between the slide ends and the housing.

By shifting the contact surface for the centrifugal forces that can be achieved in this way a considerable increase in speed compared to known construction methods is possible, which not only include the power-to-weight ratio of the machine and its construction costs are improved, but also as a result of the lower leakage losses at the high speed higher pressure levels and thus an improvement in the thermodynamic properties such machines can be achieved.

It is possible to seal the valve ends through appropriate boundary seals or due to the resilient construction, even when the housing starts to wear out or to keep the slide seal in contact with the housing.

The piston barrel is expedient in view of ease of manufacture and exact compliance with the fits for the slide guides in the assembled Executed construction.

The lateral sealing of the piston drum and the slide piston on the one hand and the housing side walls on the other hand, for example by slip ring seals or labyrinth seals and by mechanical or magnetic actuation the axially movable side walls, possibly influencing the contact pressure the side walls - can be brought about by the pressure of the medium used.

In addition, the hydrodynamic effect used in centrifugal pumps and fans can be used according to the invention thereby -be used for sealing that on the side walls of the housing in a suitable ratio to the piston drum diameter additional inlet openings for the medium used are provided, which causes the lateral seal due to the rotation of the piston drum itself by centrifugal force.

The effectiveness of this last type of seal depends on the speed, which is why a combination with Above other sealing means is appropriate.

The slide can be lubricated either by an additive to the medium Lubricants take place or through a central lubrication from the piston drum from, for example, through one or both hollow shaft journals of the piston drum and bores in the same, which lead to the double slide piston. For lubrication the above mentioned lubrication can be used for the sliding surface in the housing or a separate lubrication by either one of the lubricants through its Housing bushing that allows pores to pass through, for example made of pre-calibrated, compression molded Sintered material, or with lubricating inserts in the area of the least eccentricity of the housing.

As a result of the proposed construction It is very low path pressures of the double slide piston on the housing running surface also possible for certain purposes only by graphitizing the Housing or the. Only or both construction elements or by attachment to work lubrication-free of graphite ends in the slide piston, especially then, if the medium used has self-lubricating properties, e.g. S 02 fumes.

As with other known rotary piston machines, the inlet takes place and the outlet of the medium used into or out of the working spaces through the housing or slots made in the side walls of the housing. It is possible through Choice of slot height and slot position in the individual work areas of the multiple acting machine to each other different pressure levels and flow rates or Define filling quantities.

It is also possible by arranging additional cavities in the piston drum in a manner known per se different pressure levels between to achieve the individual workspaces. It is also possible by arrangement from overflow ducts to the rotatable in this case to the housing Side walls to bring about stepless pressure and volume regulation.

In the case of machines that work automatically, the impetus for this variability of pressure gradation or volume regulation of the medium used itself, for example by pneumatic or hydraulic actuation of the side walls to be rotated, be effected, if necessary also by thermostatically or mechanically operating Regulator organs (Fhehkraft regulators etc.). The machine according to the invention can be multi-stage operated, either by the various types of filling described above and pressure gradation or by arranging several successively connected and either different in width or in diameter or in eccentricity different assemblies, with a complete machine unit under each assembly is to be understood.

With regard to the special thermal conditions in use this machine as an internal combustion engine is proposed in the working method with the help of internal combustion a housing shape that of those of a double-acting compressor, one working side for suction and compress, to use the other working side for expanding and pushing out, so that in the special case of the internal combustion engine with internal combustion results in a simple-looking way of working.

However, if this machine is in the area of greatest compression thermal difficulties due to the ignition and combustion occurring at this point with regard to the durability of the material used, it is advisable to instead of a fuel-air mixture prepared outside the machine To suck in fresh air and in this fresh air in every second work area of the machine Introduce fuel by injecting or blowing in or sucking in, so that the other work rooms by circulating the ones not used for incineration Fresh air cause internal cooling of the machine, whereby the compression ratio different sizes can be selected in the wash or work rooms.

The power requirement for circulating this cooling air becomes part of it or fully through their heat absorption from the machine parts to be cooled, namely Housing, piston barrel and double slide piston, and through the work of expansion the heated air balanced, whereby under certain conditions with expedient choice of the different compression ratios over the necessary Power for the air circulation also results in an excess power, which on the reintroduction of the heat loss can be traced back to this work process. This gives the possibility of an increase in the overall efficiency, albeit a small one given the internal combustion engine.

Thus not only occurs from the outlet of such internal combustion engines Residual gas, but a mixture of residual gas and heated cooling air, which in a or several other rotary piston machines, which in this case are doubled again would work effectively, can still be exploited.

It is also possible for this emerging from the first rotary piston machine Gas mixture, since its oxygen has not yet been completely burned off, in a second Machine, which in this case should have a similar training as the first, again by introducing additional fuel for a second combustion to use.

In internal combustion engines with external combustion, two are with each other Coupled machines of various sizes were provided, the first as a compressor the combustion air necessary for combustion and beyond that to achieve it a desired combustion temperature promotes necessary cooling and excess air, while the second is the gases burned in intermediate combustion chambers processed as a power machine. Such a machine is used for both the compressor side as well as for the engine side, multi-stage operation is possible. aside from that For example, in engines, the residual expansion following the engine side be utilized in thrusters in a manner known per se.

The advantage over known machines with external combustion lies in the possibility of using higher pressure ratings as well as in the possibility the use of variable speeds.

By arranging appropriate reversing organs, it is possible by alternately closing the inlet and outlet slots, change the direction of rotation bring about.

In the case of vacuum pumps, the described utilization of the hydrodynamic Principle in the area of high vacuum, a residual molecular suction through the in the side walls the housing attached channels brought about.

In Figs. I to 3 are exemplary embodiments of the new rotary piston machine shown schematically. Fig. I shows a central section across the drum axis by the rotary piston engine designed as a compressor or as a compressed air or steam engine in double-acting design with the piston valves i, the piston drum 2, the Housing 3 with cooling jacket 4, the low-pressure channels 5 and the high-pressure channels 6. For use as a compressor, the strongly drawn out ones apply to the movement of the medium Arrows 7 and 8, while the dashed arrows g and for use as a motor io indicate the movement of the medium emitting energy. The direction of rotation of the piston drum when used as a compressor is also indicated by a strongly marked arrow ii, shown by the dashed arrow 12 when used as a motor. The crescent-shaped ones delimited between the piston drum 2 and the housing 3 by the slide i Work rooms or cells 13, 14, 15, 16 take the medium inside the machine during the work of the same in a known manner.

Fig. 2 shows the basic structure in basically the same scheme the rotary piston engine as an internal combustion engine. This is where the sliders are also i can be displaced in the piston drum 2 along its line of curvature and slide with it their ends along the housing. There is also a cooling jacket on this machine 4 provided outside the housing. Located in the piston drum 2 in the cells 2oa offset by two slide divisions additional cavities 17, which to reduce the compression ratio provided for this machine Serve cooling air. In the housing 3 there is an inlet device shortly after the intake duct s 18 for the fuel, which in the scheme shown here as an injection valve for periodic injection (four injections per engine revolution) is.

The area of the highest compression is also located in the housing an ignition device that ignites the fuel-air mixture, which also each Machine revolution to carry out four ignitions in this illustrated construction Has. This can be done either with the help of a single spark plug ig and a corresponding one Translation of the interrupter to the piston drum shaft take place; however it is too possible, with wider machines several Spark plugs 19 side by side to be arranged and ignited one after the other, the ignition current in a known manner is to be routed through a distributor.

Through the intake channel 5, as a result of the increasing working space fresh air is sucked in when the piston drum 2 rotates. As the workrooms pass by 2o at the injection valve 18, this injects the precisely metered required amount of fuel into the fresh air drawn in. With further rotation of the piston drum 2 this fuel-air mixture is initially compressed and ignited by means of the spark plug 1g and relaxes with further rotation, releasing energy to the piston drum 2 over the spool 1 until the latter release the exhaust duct 6 and the burnt The fuel-air mixture escapes through the exhaust duct 6.

The internal cooling takes place in such a way that the cold rooms 2o11 ' with the additional cavities 17 in the piston drum 2 fresh air through the intake channels 5 suck in, compress the same in a lower compression ratio, themselves relax after passing the top dead center of the machine and finally also through the exhaust duct 6 while mixing with the residual combustion gas already present in this escape.

The cooling air takes in this process both from the housing 3 in the area the hotter zones as well as from the piston drum 2 and the slides 1 heat, which partially transfers energy to the slide 1 during the expansion process of the cooling air gives off in the propulsion sense.

Fig. 3 shows a cross section through the compressor or steam engine Drawn rotary piston machine parallel to the piston drum axis. In this drawing is again the piston drum 2 with the piston valves 1 in the housing 3 with a cooling jacket 4 shown. In addition, the arrangement of the can be seen from this drawing The piston drum delimiting the flanges 21 of the piston drum shaft journals 22, the side housings 23 with the movable annular disks 24, the adjustability of which is indicated by external Spur gearing 25 is indicated, for example. In these movable washers 24 there are lateral cavities 26 through which the described effect is more infinitely variable Pressure and volume regulation is brought about.

From Fig. 3 the arrangement of the multiple on the circumference can also be seen provided openings 27 for the medium of the low pressure side, which through the Rotational movement of the piston drum side parts 21 through the gaps 28 to the piston drum circumference Is centrifuged and experiences such an increase in pressure that a frictionless Sealing between the movable annular disks 24 on the one hand and the piston drum 2 and the piston drum side parts 21 on the other hand is achieved.

In the case of the sealing of the piston drum shafts 22 with respect to the spaces of the rotary piston machine that are acted upon by the working medium, the end seal 29 is shown as an example of a corresponding sealing member. Furthermore, a further sealing member 30 is provided as a shaft seal against external influences. The shaft bearings 31 are located between these two sealing elements and can be lubricated in an oil bath or with the aid of circulating lubrication.

Fig. 4 shows the theoretical shape of the housing and the slider as well those geometric values that are necessary for calculating the shape of the housing.

The mathematical determination of the housing shape results from the basic requirement, that when guiding one end B1 of a double slide piston on the cross section of the housing forming curve K also the second end EZ of the same double slide piston slides along the curve K.

The following must be observed in detail: The circular arcs B, which form the center lines of the double slide piston, are always at the same distance from the drum axis A. Therefore, the distance between the centers Z of these arcs from the axis A is constant, i.e. the centers Z move on a circle around the axis A. Its radius AZ = R. - The set of all end points E of the arcs B running along the housing wall is now determined by the conditions: AZ = R = const.

EiZ = EZZ = P = const.

4 EIZA + 4 EJA = 4 EIZE2 = 2 a = const. These conditions are fulfilled, for example, when Z is ß in circulation of the point on the circle with AZ = Rum A the angle HZ A = that forms the bisector ZH of the sheet B with ZA, a periodic function of the double angle 99 _ ZAO, the AZ forms with the o-line, it follows, for example ß = ß0 COS-297.

Then the length of the radius vector AE = y to the curve points results As can be seen, the following conditions apply for v = y (9p) so El and EZ actually run along the same curve K, 2. y (q9 + 18o °) = y (p), that is, the curve K is centrally symmetric, 3. y (- P) = y (P) and y (18o ° - cp) = y (97), i.e. h: the curve K is also axially symmetrical to two axes, the length of which results for p = o and p = go ° according to If these semiaxes a and b are given arbitrarily by K, then the last two equations "result in two equations for determining four parameters: 1. O = EZ = radius of curvature of the double slide piston, 2. 4EIZE2 = half arc angle, 3rd R = AZ = radius of the arc center circle, 4th ßo = ß ... = maximum of 4th EZA = ß or in radians: the maximum displacement of the slide at the points of passage through the piston drum (based on a central position), two of which can be assumed at will. For example, it could still be used for a desired value can be used, e.g. B. as is the case for the ellipse.

Furthermore, a certain small value could be prescribed for ß.

Or in another case, O = b and again ß0 could be set small (vertical passage of the slide piston through the piston barrel).

It has been found to be particularly useful if B = so 2 a = go ° and is chosen. Then follows where R and ßo result from a2 = R2 (1.5 - cosßo -E- sinßo) b2 = R2 (1.5 - cosßo - sinßo). For example, for b / 2 = o, 84: ß, = 5 ° b / a = o, 7i: ß, = io ° b / a = o, 61: ß, = 15 '.

So we see that. for axial ratios b / a greater than about 2/3, ß, remains quite small. Therefore it results approximately so that finally the simple expression: remains as an approximate solution for the radius vector to the points E of the curve K.

This approximation will be sufficient in most practical cases be. For b / a greater than 2/3 the deviation is given by the approximation equation above certain curve K is less than the ideal curve which satisfies the exact equation as o, i ° / o.

The present statements all apply to rotary piston machines with a double-acting mode of operation or when used as a four-stroke internal combustion engine with a single-acting mode of operation. For machines with n-fold operation, 2 97 under cos or sin must be replaced by (np).

Claims (18)

PATENT CLAIMS: i. Rotary piston machine with sickle-shaped work spaces and centrally mounted piston drum, characterized in that two each are not diametrically opposite spool pistons are rigidly connected to each other, each of these so formed double piston (i) is evenly curved and in the piston barrel (z) is guided so that its two ends during the revolutions of the machine with constant contact with the correspondingly shaped housing (3) alternately more or protrude less from the piston barrel (2) (Fig. i and 2). 2. Rotary piston machine according to claim i, characterized in that either the piston drum (2) is in the fixed housing (3) rotates or that the housing (3) around the fixed The piston drum (2) revolves or that both rotate in relative motion to one another. 3. Rotary piston machine according to claim i and 2, characterized by a housing shape for which the centers (Z) of the arcs (B) forming the center lines of the double pistons (i) have a constant distance (AZ) from the drum axis (A) and for the at Guide one end point (El) of the circular arcs (B) on the curve (K) that forms the cross-section of the housing, and the second end point (E2) also slides along the curve (Fig.4). 4. Rotary piston machine according to claim i to 3, characterized by a housing shape for which the angle (@@. HZ A = ß), which the bisector (HZ = eO), of the circular sector (El ZEz) determined by the circular arc (B) with the radius (AZ = R) of the arc center circle, follows the periodic function ß = ßo cos n cp and thus the guide beam (AE = r) to the points (E) of the housing curve (K) through the function is determined, whereby of the parameters = EZ = radius of curvature of the double slide piston, R = AZ = radius of the arc center circle, a = 1/2 .. El ZEz = half of the arc angle, ßo = maximum of HZ A = ß any two can be set as desired and the other two from the equations are to be calculated, where a and b are the desired semi-axes of the housing curve (K), p is the angle (- ZA0) between the respective radius (AZ) of the arc center circle and the 0-line and n is to be set equal to 2, if it is a double-acting machine or a single-acting internal combustion engine, and should be set greater than 2 if it is a machine with an n-fold effect (Fig. 4). 5. Rotary piston machine according to claim x to 4, characterized by a housing shape for which the circular arcs (B) quarter circles with the radius and the center-to-center distance and the housing curve (K) follows exactly or approximately the equation y = 1/2 (a i- b) -1/2 (a - b) cos np, where a and b are the desired semi-axes of the housing curve (K). 6. Rotary piston machine according to claims x to 5, characterized in that the uniformly curved double pistons (i) on the circumference of the piston drum (2) in the same or for a special purpose are also inevitably led interlocking at uneven intervals. 7: Rotary piston machine according to Claims 1 to 6, characterized in that the double pistons (i) are inherently resilient along the center line of the arc of curvature and resilient at their two ends touching the housing (3), suitably under magnetic Influence-sealing end pieces made of a sealing and low-friction material own. 8. Rotary piston machine according to claim 7, characterized in that the End pieces of the double slide piston (i) in the latter towards the housing wall (3) are arranged displaceably. G. Rotary piston machine according to claims i to $, characterized characterized in that in the piston drum (2) in each case between the outlet openings two adjacent double slide piston (i) cavities (i7) are located, their size determined by the desired compression ratio. zo. Rotary piston machine according to claim i to g, characterized in that the piston drum (2) along the Double piston guides are designed divided and by external flanges or rings (2i) is held together. ii. Rotary piston machine according to claims i to io, characterized characterized in that for the lateral seal between the piston drum (2) and Double slide piston (i) on the one hand and the side housings (23) of the housing (3) on the other hand in the latter additional inlet openings (27) for the to be processed Medium are arranged such that the distance between these openings from the drum axis is smaller than the radius of the piston barrel (2). 12. Rotary piston machine according to claim i to ii, characterized in that annular discs (24) in the side housings (23) are arranged four rotatable and have overflow channels (26), so that depending on the the selected position of the annular disks (24), both the suction volume and the pressure gradation can be set in different ways. 13. Rotary piston machine according to claim i to 12, characterized characterized in that the four rotatable in the side housings (23) mounted washers (24) are also movable perpendicular to their surface, the seal being mechanical or is influenced magnetically. 14. Rotary piston machine according to claim x to 13, characterized in that the height and position of the slots for inlet and outlet (5 or 6) of the driving medium used or the medium to be compressed in the case of the multiple acting machine are selected if necessary so that in the individual work areas different pressure levels and filling or delivery rates are achieved will. 15. Rotary piston machine according to claim i to 14, characterized in that it contains a control device through which the impulse for the variability of pressure gradation or volume regulation of the medium used itself by pneumatic or -hydraulic actuation of the annular disks (24) to be rotated or by thermostatically or mechanically operating regulator organs, such as centrifugal governors, is effected. 16, Arrangement of several one behind the other; different widths or diameters and / or rotary piston machines with different eccentricity according to claim i up to 15 to achieve a multi-level operation, possibly on the same Drive shaft. 17. Rotary piston machine according to claim i to 16, characterized in that that when used as an internal combustion engine with internal combustion only each second cell (2o) combustion chamber, so receives fuel supplied while the cells in between (2od) are only cold cells, i.e. only receive fresh air (Fig. 2). 18. Rotary piston machine according to claim 17, characterized in that it a similar machine is connected downstream and instead of fresh air from that sucks in any mixed gas from combustion gases and heated cooling air. ig. Rotary piston mechanism according to claims i to 16, characterized in that when used as an internal combustion engine with external combustion, two or more rotary piston engines are arranged one behind the other, the first being the compressor for combustion promotes the required combustion air and, if necessary, cooling and excess air, while the second and possibly further rotary piston machines are the ones in between Combustion chambers process burned gases as an engine, if necessary on the same drive shaft. 2o. Rotary piston engine according to claims to ig, thereby characterized in that it is followed by a nozzle when used for engines which takes advantage of the residual expansion.