EP0544025A1 - Rotary piston engine for compressible and non-compressible medium - Google Patents

Abstract

The medium to be pumped enters the working space (20) in the induction phase via one of the two inlet ports (14) and the passage through the rotary piston (3). On completion of the induction phase, the medium is expelled through the outlet ports (15), via the same passage through the rotary piston (3), at top dead centre in the following expulsion phase. The passage through the rotary piston (3) begins at the end face, at the inlet/outlet ports, executes a right-angled bend in the rotary piston (2) and ends in the working space (20). Two inlet ports (14) and two outlet ports (15) in alternation, with a separating rib in between, are required in the circumferential direction. Since the flow of medium increases and decreases to the same extent in the induction phase and the expulsion phase, a constant flow of medium can be achieved using a suitable mechanism or lever system to ensure that the rotary piston has a lead relative to the shaft in the case of an excess of power and a lag in the case of a lack of power. The free inertia forces which arise due to the lead and the lag of the rotary piston are compensated by a flywheel with an opposing lead or lag. With the inventions under consideration, rotary piston machines can, depending on their design, be operated with compressible or incompressible media. Depending on the direction of power flow, they can operate as power-conversion machines (turbines) or power-producing machines (motors). Depending on the design, controlled or uncontrolled operation in both directions of rotation is possible. This is performed by shortening the expulsion phase in the circumferential direction and forcing the medium back into the induction line. Applications for rotary pistons of the inventions under consideration are: hydraulic machines in the form of hydraulic motors or hydraulic turbines, pumps for compressible and incompressible media, fans, gas turbines, steam turbines etc. The machines can in each case optionally be designed with or without constant delivery. The advantages of the rotary piston machines with the inventions under consideration are, above all, a high efficiency, quiet vibration-free running, a good intake capacity, constant delivery, high speeds and a compact construction. <IMAGE>

Description

TECHNICAL FIELD TO WHICH THE INVENTION RELATES:

The present invention relates to rotary piston machines.
Rotary piston machines can be operated with the present inventions, depending on the technical design, with compressible and non-compressible media. Depending on the direction of energy, they work as an engine (steam engines, turbines, etc.) or as a working machine (pumps). Depending on the technical version, regulated or unregulated operation is also possible in both directions of rotation. If the corresponding new developments are used, constant funding can be achieved without free mass forces. In addition, with two rotary piston machines in one unit as the engine and the work machine, speed control and also a hydraulic clutch can be implemented by regulating the medium flow with a flow control valve between the engine and the work machine.

PREVIOUS TECHNOLOGY:

The epitrochoid form has long been known from mathematics. For the first time, this design principle gained importance in the Wankel engine named after its inventor. The two-arch design is common. The internal rotary piston has three corner points and three sides in a double-arch housing. This creates three work rooms. There are currently a whole range of machines for the transport and compression of compressible media (e.g. air) or incompressible media (e.g. hydraulic oil) depending on the technical requirements. Basically one can distinguish between piston machines and turbo machines. Piston machines are mainly used to generate higher pressures. The basis of the piston machine is a periodically changing work area. The work area is filled with the compressible or non-compressible medium to be transported. Its pressure rises with compression and falls with expansion in an alternating sequence. In between, or in the case of non-compressible media at the same time, the charge change takes place with suction and ejection. Technical embodiments are piston compressors in versions with several pistons (compressors), vane compressors, screw compressors and the Roots blower.
The piston machines work according to the displacement principle by enlarging and reducing the working space.
The second group of machines for the transport and compression of media are the flow machines. In turbomachines, work is carried out on a continuously flowing medium via a rotor or rotor equipped with blades, and energy is thereby supplied to it, or energy is extracted from the flowing medium and converted into mechanical work. The direction of flow can be axial, radial or diagonal. It is characteristic of turbomachines that the medium is accelerated by the blades and the flow energy is returned to pressure energy when it emerges. Technical embodiments are centrifugal pumps, axial compressors, radial compressors etc.
The "Föttinger clutch" is particularly well known on hydraulic couplings.

ASSESSMENT OF THE PREVIOUS TECHNOLOGY:

The previous technical solutions are not very advantageous for a number of applications. The piston machines have the disadvantage that the medium is not transported continuously. Furthermore, the amount of the transported medium depends on the speed. The compression only depends on the compression ratio. In addition, free mass forces occur with the piston machines. Working as an engine is difficult with the piston machines.
The main disadvantage of turbomachines is that the medium must first be accelerated before it can be returned to pressure energy. On the other hand, it is advantageous over the piston machines that the medium is transported continuously and that there are no free mass forces.
Rotary piston machines for use as pumps are proposed in the inventions [DE 2 021 513, DE 2 242 247, DE A1 2 402 084 and 0 094 379 A1]. However, the disadvantages inherent in the piston machines could not be eliminated.

PRESENTATION OF THE INVENTION:

These various disadvantages are now to be overcome with the present inventions.

First, a distinction is made between compressible and non-compressible medium.
If the pressure of a compressible medium (e.g. air) has to be increased, this will also experience a volume reduction. In the case of a non-compressible medium (e.g. hydraulic oil), however, there is no significant volume reduction. Depending on the medium being transported, different designs are therefore expedient for the rotary piston machine. The power transmission from the rotary piston to the shaft takes place with an eccentric. The center of the rotary piston has a constant distance (namely the eccentricity) from the center of the shaft and thus also of the overall system.

The following descriptions always assume a double-armed rotary piston machine. Unless otherwise specified, the direction of rotation is counterclockwise. The state of the revolution is given in degrees.
First, a general description of the inventions is given. The specific description based on the drawings is given in the next chapter.

PRESENTATION OF A MACHINE FOR UNREGULAR CONVEYMENT OF A NON-COMPRESSIBLE MEDIUM (OPERATION AS A PUMP)

The rotary piston machine belongs to the group of piston machines. The energy conversion takes place exclusively by enlarging and reducing the work space. The flow rate of the medium should therefore be kept rather low.

• 1.) Es muß bei inkompressiblen Medien gewährleistet sein, daß während der gesamten Umdrehung des Rotationskolbens jeder Arbeitsraum entweder zur Druck- oder zur Saugleitung hin offen ist.
• 2.) Die Umschaltphasen müssen so beschaffen sein, daß der Umschaltbereich rasch überfahren wird und kein Kurzschluß zwischen Druck- und Saugleitung eintreten kann.
• 3.) Es muß im Umschaltbereich der Mediumsfluß gegen 0 gehen. 4.) Es muß stets ausreichender Durchflußquerschnitt gegeben sein.

The central problem for the time being is the positioning of the inlet channels and outlet channels in order to enable the gas exchange in the work rooms. The following requirements must be met:

• 1.) In the case of incompressible media, it must be ensured that each working area is open to either the pressure or suction line during the entire rotation of the rotary piston.
• 2.) The changeover phases must be such that the changeover range is quickly covered and no short circuit between the pressure and suction lines can occur.
• 3.) The medium flow must go to 0 in the switchover range. 4.) There must always be sufficient flow cross-section.

In order to be able to meet these requirements, the rotating rotary piston is used according to the invention for switching over the three working spaces between the suction line and the extension line.

During the suction phase, the medium enters the work area from the suction line via the inlet channel in the inlet and outlet flange and through the flow piston (one for each work area). Via the same passage through the rotary piston, the medium, after further rotation during the push-out phase, reaches the pressure line via the outlet channel in the inlet and outlet flange. The inlet channels and outlet channels are arranged so that the rotary piston bushing is connected to the suction line during the suction phase and to the pressure line during the pressure or extension phase.
The piston feed-through begins at the front of the piston, makes a right-angled arc in the piston, continues radially outwards and ends in the working area.
The medium is controlled via the slot control. (In contrast to the control with piston machines with pressure-dependent or controlled intake and exhaust valves per cylinder).

The two inlet channels in the inlet-outlet flange range approximately from 100 to 170 degrees and from 280 to 350 degrees. The two outlet channels range from 10 to 80 and from 190 to 260 degrees. This division applies provided that the feed-through channel runs through the rotary piston in the middle between two corner points of the rotary piston (see FIG. 10). There is a separator between the inlet and outlet channels. This separating web has at least the same width as the feed-through channel through the rotary piston in order to avoid short-circuits between the inlet and outlet channels.
For the location of the switchover point, it would be obvious to position it at 0, 90, 180, and 270 degrees as described above. However, this is not always advantageous. It should be borne in mind here that, due to the shape of the epitrochoid, the rotary piston is not rotationally symmetrical and does not rotate on a circular path. Therefore, the feedthrough channels through the rotary piston do not rotate in a rotationally symmetrical manner. As a result, the area is quickly passed at 90 degrees and 270 degrees, while the area is slowly passed at 0 degrees and 180 degrees. However, it is necessary that all four switchover areas are overridden as quickly as possible. Therefore, the channels through the rotary piston and the inlet channels and outlet channels are arranged so that the changeover is always as quick as possible. This is the case if the switching points are arranged at approximately 60, 120, 240 and 300 degrees. The optimal switching point at z. B. about 120 degrees is obtained when a line of intersection is made from the intersection of the eccentricity circle with the coordinate cross of 0 degrees through 90 degrees.
The exact location depends on the design.
The switchover points are comparable to the top and bottom dead centers in the piston engine. The funding increases along a sinus curve, reaches a maximum and then decreases again. In terms of delivery, the double-armed rotary piston machine behaves approximately like a reciprocating piston machine with three cylinders. There are no free mass forces.

IF ROTATIONAL-SYMMETRICAL RUN IS REQUIRED, THE FOLLOWING ACTION IS REQUIRED:

Rotationally symmetrical running means that continuous delivery at constant pressure causes constant rotation on the drive shaft.
This is not the case with the piston machine with pistons going up and down.
This is also not yet the case with the rotary piston machine, as was technically shown above. Hydraulically it behaves like a piston machine with three cylinders, but without free mass forces.

According to the invention, the following options are proposed in order to achieve rotational symmetry:
From the geometry it follows that the inflow and outflow on the pressure and suction side rise and fall with the same amplitude according to a sine function. The driving force acting in the tangential direction on the eccentricity circle also changes along a sine function during suction and compression. To achieve rotational symmetry, it must therefore be achieved with a suitable measure that the rotary piston leads ahead in relation to the drive shaft when there is excess power (of the rotary piston) and lags behind when there is insufficient power. The rotary piston is therefore not coupled directly to the drive shaft, but rather via a gear that technically manages the leading and lagging of the rotary piston.

Technical embodiments for achieving the pre- and post-exposure are e.g. B. gears with a narrower and wider tooth spacing, gears with a larger and smaller radius (non-circular gears) a planetary gear or a cycloid gear etc. These gears and gears are state of the art.

According to the invention, a solution is proposed that does not require gears. For this purpose, the connection between the rotary piston and the drive shaft is established with three lever arms. The control lever arm is controlled in a guideway so that the advance and retardation of the rotary piston is realized by the lever movement.

However, the leading and lagging of the rotary piston now causes free rotational mass forces. These inertia forces have to be balanced by a flywheel that moves in the opposite direction to the rotary piston. The opposite leading and lagging of the flywheel is also realized with non-circular gears or with the lever system described.

FLOW RATE CONTROL 0-100%

As has already been shown, the delivery rate for piston machines depends on the speed. For different applications, however, it would be advantageous if this connection did not exist. This is possible with the rotary piston machine with a development according to the invention.

The medium is z. B. from 90 to 180 degrees not transported through the outlet channel, but pushed back into the inlet channel. This is made technically possible so that the separator between the inlet and outlet at 0 and 180 degrees can be moved counterclockwise up to 90 and 270 degrees.

In this way, the inlet channels are extended in the circumferential direction in accordance with the setting of the separating webs and the outlet channels are shortened. The medium is thus pushed back into the inlet channels after passing over the bottom dead center.
The flow rate can thus be controlled from 0 to 100%. When operating as an engine, starting is only possible to a limited extent. The rotary piston machine only rotates if at least one bushing through the rotary piston is above an inlet channel.
One way to always be able to start up in flow-controlled operation is to create individual inlet channels that are run over by the passage through the rotary piston, and to feed these inlet channels with compressed or pressurized medium during the starting phase.
When regulating the flow rate, sufficient pressure accumulators (wind boilers) must be provided due to the pulsating flow.

REVERSE DIRECTION, MOTOR OPERATION AND TURBINE OPERATION:

According to the construction according to the invention, the direction of rotation can be reversed by reversing the direction of flow of the medium through the rotary piston machine. Likewise, a smooth transition between engine operation and turbine operation is only possible by reversing the direction of energy. Starting in uncontrolled turbine operation is also possible with non-compressible media, since at least one working area is always acted on by the pressure line.

ROTARY PISTON MACHINE FOR COMPRESSIBLE MEDIA:

In principle, the rotary piston machine described can also be used for compressible media for non-compressible media with continuous inlet and outlet slots. However, this embodiment is only advantageous if only transport of the medium and no major increase in pressure (compression) is required. For the compression of the compressible medium (e.g. air), another design for the rotary piston machine is appropriate. Regulation of the medium flow from 0 to maximum is possible. Constant delivery without changing the speed is only possible with uncontrolled rotary piston machines for compressible media. Rotationally symmetrical running is also possible for a given medium.

ROTARY PISTON MACHINE FOR COMPRESSIBLE MEDIA: OPERATION AS A MOTOR (COMPRESSOR, COMPRESSOR):

The rotary piston machine in the version under consideration is driven counterclockwise by a motor (e.g. electric motor).
The medium to be compressed is sucked in from 90 to 180 degrees (270 to 360 degrees) via the inlet duct. The medium in the work area is compressed from 180 to 270 degrees (0 to 90 degrees) and only pushed out at 270 degrees (90 degrees) when it has already been compressed. If only delivery and no major pressure increase is required, the compressed medium (e.g. air) can be pushed out earlier (e.g. at 260 degrees and 80 degrees). This applies to the application z. B. as a fan.

ROTARY PISTON MACHINE FOR COMPRESSIBLE MEDIA: OPERATION AS A TURBINE (ENGINE):

The following solution is required when operating as a power machine (e.g. for machine tools operated by compressed air):
The compressed medium (compressed air) is introduced at the point with the smallest working space volume V min. This is the case at 90 and 270 degrees at top dead center. In order to obtain a defined direction of rotation in this case counterclockwise, the inlet opening must be approximately 100 or 280 degrees, so that the rotary piston does not turn back over top dead center when starting. When working as a power machine, the medium relaxes up to 180 or 0 degrees and does the mechanical work by relaxing the medium. During the rotation of 180 to 270 or 0 to 90 degrees, the relaxed medium is pushed out via the outlet channel. A continuous outlet channel must therefore be created from 180 to 270 and from 0 to 90 degrees.
The difference to the machines for incompressible medium is that from 90 to 180 (270 to 360 degrees) no medium is added. The drive work is done by relaxing the compressed air. A peculiarity when used as an engine is that in the worst case, when there is no passage through the rotary piston above an inlet channel, the rotary piston cannot rotate. This problem is countered by installing small inlet ducts or individual openings from 100 to 160 degrees (280 to 340 degrees). Compressed air can be applied to these channels during the start-up phase. When a passage through the rotary piston is above these separate inlet channels, the compressed air flows into the corresponding work area. If there is an increased power requirement, these approach openings can also be supplied with compressed air during operation. In addition to the partially relaxed compressed air, there is new compressed compressed air and thus increased torque.

PRESENTATION OF THE MATHEMATICAL RELATIONSHIPS

The following description of the mathematical relationships is always based on a double-armed rotary piston machine. The direction of rotation is counterclockwise and starts at 0 degrees. The state of the rotation is given in degrees (0 to 360). The three work rooms are designated I, II and III. The corners of the rotary piston opposite the working spaces are designated 1, 2 and 3.

GEOMETRIC DESIGN:

Exzentrizität e :

12

Abstand R :

108

Ge Exzenterwellenwinkel Gk Rotationskolbenwinkel
$\text{Ge = 3 * Gk}$

Statt der Winkelbezeichnung phi wird hier G verwendet.
Das Verhältnis Abstand R zu Exzentrizität e wurde mit dem Verhältnis 9 : 1 festgelegt. Bei diesem Verhältnis enthält die umhüllende Epitrochoide keine Wendepunkte.The following main dimensions were chosen for the representation according to the invention:

Eccentricity e:

12th

Distance R:

108

Ge Eccentric shaft angle Gk Rotary piston angle
$\text{Ge = 3 * Gk}$

G is used here instead of the angle designation phi.
The ratio of distance R to eccentricity e was determined with the ratio 9: 1. At this ratio, the enveloping epitrochoid contains no turning points.

$\text{Yn=(e*(sin(Ge)))+(A*(sin(Ge/3)))}$

The individual points Xn and Yn of the epitrochoids are calculated with:

$\text{Xn = (e * (cos (Ge))) + (A * (cos (Ge / 3)))}$

$\text{Yn = (e * (sin (Ge))) + (A * (sin (Ge / 3)))}$

WORK SPACE VOLUME (CHAMBERS):

The first step is to investigate the mathematical relationship according to which the volume of the work space can be calculated.

In addition, it can be seen that in the OT area at 90 and 270 degrees the working space volume V _{H has} a minimum and in the UT area at 0 and 180 degrees the maximum. The increase and decrease in the absolute work space volume occurs between V _min and V _max according to the sin² function.

The increase in the workspace volume dV from OT to UT and the decrease in the workspace volume dV from UT to OT as a function of the angular velocity occurs according to a sine function. (see Figure 40)
The sine function is given in the rotary piston machine because no connecting rod is required for the transmission of the piston stroke to the crankshaft, as in the reciprocating piston machine, but rather the piston acts directly on the shaft, so to speak.

At the dead points 0, 90, 180 and 270 degrees where the switchover between inlet and outlet also takes place, the increase and decrease in the volume flow reaches a minimum and goes to 0. This is very advantageous, since at the switchover point between inlet and outlet the Medium flow is 0. In between, the volume flow increases according to the sine function until it reaches a maximum at 45, 135, 225, and 315 degrees and then decreases again and goes towards 0.

The following mathematical relationships result:

There are two working rooms connected to the inlet channel and one working room to the outlet channel, or one working room to the inlet channel and two working rooms to the outlet channel.

Where two work rooms are connected to the inlet channel or two work rooms to the outlet channel, the medium flow and the tangential force of these two work rooms can be added.

In addition to the main dimensions, V _max and V _min depend in particular on the design of the pistons. The smallest possible V _{min should} be aimed for, since a larger V _{min means} loss of efficiency (harmful space), especially with compressible media. The V _min also includes the passage through the rotary piston into the work area.

POWER TRANSFER:

The power transmission between the medium and the machine takes place on the piston surfaces. The pressure of the medium can be thought of as a surface force. It acts perpendicular to the piston surface and its imaginary line of action goes through the center of the rotary piston. The surface force can be broken down into a radial and tangential part using the angular relationships at the center of the rotary piston. Only the tangential part contributes to the rotation.

As the evaluation shows, radial and tangential forces increase and decrease along a sine function. If the piston surface is at 0, 90, 180 or 270 degrees, the tangential force is 0 and the radial force has a maximum. At 45, 135, 225 and 315 degrees, the tangential force Ft reaches the maximum and the radial force Fr approaches 0.

$\text{Fr = F * (cos(2*Gk))}$

$\text{F = A * p (Kolbenfläche im Arbeitsraum * Druck des Mediums)}$

Das gesamte auf die Exzenterwelle ausgeübte Drehmoment ergibt sich sohin mit

$\text{Md = (FtI + FtII + FtIII) * e}$

Die Tangentialkräfte der drei Arbeitsräume müssen vorzeichenrichtig addiert werden.The following therefore applies:

$\text{Ft = F * (sin (2 * Gk))}$

$\text{Fr = F * (cos (2 * Gk))}$

$\text{F = A * p (piston area in the working area * pressure of the medium)}$

The total torque exerted on the eccentric shaft also results with

$\text{Md = (FtI + FtII + FtIII) * e}$

The tangential forces of the three work spaces must be added with the correct sign.

ROTATIONAL PISTON BEFORE AND AFTER THE DRIVE SHAFT:

For the following explanations, reference is made to FIG. 41:
If constant conveyance is required, the following measure is necessary: In the range of approximately 6.5 degrees to 15 degrees (rotary piston) and multiples thereof, the shaft leads the rotary piston. In the range 0 to 6.5 degrees and multiples, where the delivery is smaller, the shaft is decelerated compared to the rotary piston.
For reasons of clarity, degrees of the rotary piston and degrees of shaft (eccentric auxiliary shaft) are identical here. Of course, the eccentric auxiliary shaft and shaft run at three times the angular speed of the rotary piston. This means that a complete cycle of lead and lag does not extend over 30 degrees as shown in Figure 41 but over 90 degrees.
The shaft rotates at a constant angular velocity. The rotary piston always hurries before or after the shaft.
The lead and lag for the angular resolution in question (e.g. 1 degree) can be calculated as follows:
In the range from 0 to 30 degrees, the delivery curves of workspaces I and III are first added.
In the range of 0 to 15 degrees, the area under the added curve is calculated starting from the intersection of curve III with the y-axis. The average area is calculated for the selected angular section (e.g. 1 degree). It is around 6.5 degrees. The average area is then divided by the areas under the angular sections 1, 2, 3 to 15 degrees. The corrected angular sections are thus obtained. In the range 0 to 6.5 degrees, they are less than 1 degree. From 6.5 to 15 degrees they are larger than 1. The corrected angular sections are added to the previously calculated angular sections. The total of these corrected angular sections must again be 15 degrees.
In the range from 15 to 30 degrees, the corrected angular sections are mirrored at 15 degrees. Then the leading and lagging are repeated analogously over the remaining rotation angle range.
The values in the 2 degree interval starting from 0 to 15 degrees are shown below as an illustration. The maximum deviation at 6.5 degrees is 0.27 degrees. 0 2nd 4th 6 7 8th 10th 12th 14 15 0 1.85 3.76 5.73 6.73 7.74 9.79 11.87 13.96 15

MASS FORCES:

The rotary piston machine has the advantage that the free mass forces can be completely balanced.
However, if constant conveyance has to be achieved by moving the rotary piston ahead and behind, free rotating inertial forces arise due to the advance and lag (acceleration and deceleration) of the rotary piston. These free mass forces of both the piston and the eccentric have to be compensated for by counter-rotating masses.
To balance the mass forces, all free masses must be calculated and then counter-rotating masses must be created.

PRESENTATION OF THE INVENTION WITH THE DRAWINGS:

At the outset it is stated that the primary focus of the drawings was to work out the meaning of the respective drawings. The drawings therefore do not claim to be formally correct. In particular, no invisible lines and edges have been shown with dashed lines. The individual machine parts are numbered consecutively and labeled in the legend sheet. Inlet channels are hatched with dots. Outlet ducts are cross-hatched. The hatching is to be understood as a coming and going arrow.

FIG. 1 shows in sectional drawing AA how the implementation by the rotary piston is carried out according to the invention.

This version is primarily suitable for non-compressible media. The cutting edge A-A is shown in Figure 6. The arrows on the cutting line represent the view from the left.

Eccentric shaft angle and rotary piston angle are in the starting position at 0 degrees in Figure 1.

The medium to be pumped enters through connections (not shown) at the inlet-outlet flange (11). There are two inlet channels (14) and two outlet channels (15) in the inlet-outlet flange (11). The inlet channels (14) range from about 60 to 120 degrees and from 240 to 300 degrees. There is a fixed separator (27) between the inlet and outlet channels. The bushings through the rotary piston (3) are in the 0 degree position at approximately 30 degrees, 120 degrees and 270 degrees. Working space II is connected to the inlet channel (14) in this rotary piston position. Working room III with the outlet duct (15). Working space I is at bottom dead center at 180 degrees and is switched counterclockwise from the inlet channel (14) to the outlet channel (15) in the direction of rotation under consideration. The current flow and torque ratios at 0 degrees are shown in FIG. 40.

FIG. 1.1 summarizes the drawing in FIG. 1 and FIG. 6. Figure 1.1 is suggested for the summary.

In FIGURE 2 , the piston was rotated 30 degrees counterclockwise. The passage through the rotary piston (3) to work area I is above the outlet channel (15), since the work area volume decreases. The passage through the rotary piston (3) to work area II is above the inlet duct (14), since the work area volume increases. Working space III has reached the top dead center OT and is switched from the outlet channel (15) to the inlet channel (14). The passage through the rotary piston (3) is above the separating web (27). The center of the rotary piston MK has moved up to 90 degrees, while the rotary piston (2) has rotated 30 degrees around its own axis.

In FIGURE 3 , the center point MK of the rotary piston is at 180 degrees. In work space I, medium is pushed out via the outlet channel (15). Workroom II has reached bottom dead center at 0 degrees and is switched from the inlet duct (14) to the outlet duct (15). In workroom III, the workspace volume increases. The passage through the rotary piston (3) is above the inlet channel (14).

In FIGURE 4 , the center of the rotary piston MK is at 270 degrees. Workroom I has now reached top dead center at 270 degrees. In workroom II the volume decreases again. The passage through the rotary piston (3) is above the outlet channel (15). The volume continues to increase in workroom III. The passage through the rotary piston (3) is above the inlet channel (14).

In FIGURE 5 , the center of the rotary piston MK has again reached the starting position at 0 degrees. Working space I is connected to the inlet duct (14). Workroom II with the outlet duct (15). Working space III is switched from the inlet duct (14) to the outlet duct (15). Working area I has undergone a complete outlet cycle from FIG. 1 to FIG. 4. Working area III has gone through a complete inlet cycle from FIG. 2 to FIG. 5.
The course of the respective work space volume and torque can be followed with FIG. 40.

FIG. 6 shows the rotary piston machine from FIG. 1 in section BB. On the right side, the inlet-outlet flange (11) is shown with the inlet channels (14) visible in this sectional view. The rotary piston (2) is mounted on the shaft (4) and the eccentric (6) with the eccentric bearings (7). The two bushings (3) lead from the inlet duct (14) through the rotary piston (2) into the respective work area. On the drive flange (10) there is the pinion (9) in which the ring gear (8) located on the rotary piston (2) meshes. The shaft (4) with the eccentric (6) is mounted in the inlet / outlet flange (11) and in the drive flange (10) with the shaft bearings (5).
FIG. 6 also shows the section line AA for FIGS. 1-5. For the width of the inlet channels (14) and outlet channels (15) there is a dimension that is predetermined in terms of construction. If this is not sufficient or the flow losses are too high, inlet and outlet ducts with the associated passage through the rotary piston (3) could also be installed on the drive flange (10). The ring gear (8) and pinion (9) are then moved further inwards. For larger pressure increases (compression), several rotary piston machines can also be connected in series (in series). In the inlet-outlet flange (11) z. B. the inlet channel (14) and in the drive flange (10), which is also an inlet flange for the next stage, the outlet channel (15) for this stage and the inlet channel (14) for the next stage can be accommodated. Another way to make more space for the inlet-outlet channels is to choose a smaller eccentricity.

The embodiment for the rotary piston machine shown in FIG. 1 to FIG. 6 can be used for many applications. For example, as a hydraulic pump or hydraulic turbine. The advantage over conventional technical solutions is higher efficiency, smoother running due to the lack of free inertia forces and a more compact design. When used as a water pump, it is advisable to accommodate the ring gear and pinion outside the housing and to seal the bushing from the drive flange to the rotary piston with a seal (stuffing box). The rotary piston can be supported with shaft bearings and eccentric bearings in such a way that no more bearings are required at the inlet / outlet flange.

FIGS. 7 to 16 show further possibilities for the design of the inlet and outlet unit. Depending on the compressible or non-compressible medium, or whether the flow should be regulated independently of the speed, the inlet-outlet unit must be designed according to the requirements.

FIG. 7 shows an embodiment predominantly for conveying non-compressible medium. It is suitable for regulating the flow of the medium to be pumped independently of the speed. This is carried out according to the invention in such a way that the separating web (23) between the inlet and outlet is designed to be displaceable in the circumferential direction at 120 degrees and counterclockwise at 300 degrees. The separator (27) at 60 degrees and 240 degrees is fixed.
The separating web (23), which is rotatable in the circumferential direction, is additionally arranged in a guide (22) with a lever arm (25) so that it can rotate about its own axis. The lever arm (25) is aligned with the control pin (26), which runs in the guideway for the control pin (24) after being carried out by the rotary piston (3). The rotatable separating web (23) is displaced in the circumferential direction with the aid of the displacement unit (21).
The rotatable arrangement is necessary because the passage through the rotary piston (3) is not radially aligned during the rotation due to the eccentricity. The separating web (23) which can be pushed in the circumferential direction must therefore be aligned in the radial direction after being carried out by the rotary piston (3).
FIG. 8 and FIG. 9 show the sections DD and EE through the separating web (23).
With this technical design according to FIG . 7 , an adjustable hydraulic pump or hydraulic turbine can be built. Since this machine delivers intermittently, especially with a small medium flow, sufficient pressure accumulators must be provided. This version is useful when speed or power control of the prime mover or driven machine or other control of the medium flow is not possible.

In FIGURE 10 , the inlet channels (14) range from 90 to 180 and from 270 to 360 degrees. The outlet channels (15) range from 0 to 90 and from 180 to 270 degrees. The passage through the rotary piston (3) is located in the middle between two corner points of the rotary piston (2).
This version has the advantage that the area at bottom dead center at 0 and 180 degrees is passed over more slowly by the passage through the rotary piston (3).
For applications, the slow crossing of the separator at 0 and 180 degrees can be used. In particular, there is more time to push out pressureless medium.

In FIGURE 11 , only a single opening is provided for the inlet channel (14) as an inlet channel (14) at approximately 100 degrees and 280 degrees. This version is primarily intended for compressible media in the operating mode as a compressor or compressor. The passage through the rotary piston (3) is located in the middle between two corner points of the rotary piston (2). It can be made smaller here because the inlet channels (14) and outlet channels (15) have been arranged so that they can always be followed by the rotary piston (3). This has the advantage that the implementation by the rotary piston and thus V _min can be kept very small.

FIGURE 12 shows an embodiment for predominantly compressible medium in the operating mode of the controllable engine (turbine) with reversal of the direction of rotation. The direction of rotation is counterclockwise in the version shown.
The medium (e.g. compressed air) is introduced via the two inlet openings (28) at 100 and 280 degrees. The inlet opening (28) is located at 100 and 280 degrees in order to obtain the defined direction of rotation counterclockwise. Should not be carried out when starting the turbine If the rotary piston (3) is above the inlet opening (28), the rotary piston could not turn. Starting aids (32) are therefore created. These are openings through which compressed air is introduced when starting off. These starting aids (32) have no function in normal operation.
After the compressed medium (compressed air) has been introduced through the inlet opening (28) at 100 or 280 degrees, it does work by expansion. The rotary piston (2) rotates from 90 degrees to 180 degrees and does mechanical work. The extension phase ranges from 180 to 270 degrees or 0 to 90 degrees. The relaxed medium is pushed out through the outlet opening (29).

In FIGURE 13 , the sectional view FF of the inlet-outlet flange (11) shows how flow control and reversal of the direction of rotation can be carried out.
For this purpose, the entire inlet-outlet unit (13) (hatched with lines 45 degrees) is rotated by 90 degrees in the circumferential direction. This enables the direction of rotation to be reversed with the control cylinder reversing the direction of rotation (19), the control ring reversing the direction of rotation (17) and the control channel reversing the direction of rotation (30).
The inlet channels (14) are positioned at 90 and 270 degrees. The outlet channels (15) at about 20, 160, 200 and 340 degrees. The medium is thus introduced into the working space (20) via the inlet channels (14) and the inlet openings (28) and through the rotary piston (3). The relaxed medium is pushed out via the outlet openings (29) and the outlet channels (15). In the inlet-outlet unit rotatable (13) there is the control ring flow control (16) (lines hatched vertically) with the control cylinder flow control (18), and the control channel flow control (31). The maximum flow is set in the position shown.

FIGURE 14 shows the direction of rotation in the clockwise direction. For this purpose, the inlet-outlet unit (13) was rotated by 90 degrees. The outlet openings (29) now range from 100 to 170 degrees and from 280 to 350 degrees. The inlet openings (28) are at about 80 and 260 degrees. The flow control control ring (16) has been moved to the central position. This means that only the first four outlet openings (29) are pushed out. The remaining four outlet openings (29) are compressed again. In the next inlet phase, as much compressed medium can no longer flow in, since there is already partially compressed medium in the work space (20). This is how flow and power control comes about.

FIGURE 15 (section GG) shows a section at approximately 170 degrees. The side outlet channel (15) and the control channel for the direction of rotation (30) can be seen here. If this control channel is pressurized, the inlet-outlet unit (13) rotates counterclockwise. This means that the rotary piston (2) also runs counterclockwise.

FIGURE 16 (section HH) shows the section at approximately 260 degrees. In this drawing, the inlet channel (14) is shown coming from the right from the inlet / outlet flange (11). It should also be noted that this inlet duct (14) has been drawn in the drawings 13 and 14 for the sake of clarity, although it is not visible in this illustration.

With the possibilities shown in FIGS. 12 to 16 , a turbine can be operated in a flow-controlled manner in both directions of rotation with compressible medium. The direction of rotation can be reversed either by turning the control ring by hand or by applying pressure from the pressure medium. The flow control could be load dependent or be operated manually. Possible applications would be e.g. B. tools operated by compressed air (pneumatic screwdrivers, pneumatic drills etc.). With the version shown in FIGURE 12 without reversing the direction of rotation, compressible medium in particular can be transported. Applications would be e.g. B. fans in various technical designs but also compressors for air, coolants and gas turbines and steam turbines.

FIGURES 20 to 27 show possibilities of how constant flow can be achieved without free mass forces.
Constant flow can be achieved if the rotary piston leads or lags the shaft in a 15 degree interval by a maximum of 0.27 degrees with respect to the rotary piston.
The solution according to the invention is that the lead and lag are carried out either by suitable non-circular gears or with a lever system.

In FIGURES 20 to 22 , a lever system is proposed according to the invention which works as follows:
On the eccentric auxiliary shaft (35), which is driven by the rotary piston (2), two joints of the eccentric auxiliary shaft (43) are attached to the eccentric auxiliary shaft (35). The drive joint lever (38) with the joint drive shaft (41) is attached to the shaft (3). The control articulated lever (39) is rotatably connected to the articulated drive shaft (41). The intermediate joint (42) is firmly connected to the control joint lever (39). The connection between the joint drive shaft (41) and the joint eccentric auxiliary shaft (43) is made with the intermediate joint lever (40). A triangle is thus formed with the joints intermediate joint (42), joint eccentric auxiliary shaft (43) and joint drive shaft (41). If the control joint lever (39) is deflected outwards, the angle between the drive joint lever (38) and joint eccentric auxiliary shaft (43) is reduced. The shaft (4) leads in relation to the rotary piston (2). If the control joint lever (39) is deflected inwards, the angle between the drive joint lever (38) and the joint eccentric auxiliary shaft (43) increases. The shaft (4) lags behind the rotary piston (2) or the eccentric auxiliary shaft (35).
The radial rotation of the control joint lever (39) is carried out via the guide roller inner track (36) and the guide roller outer track (37) which run in the guide track milled in the drive flange (10) for leading and trailing (34). FIG. 21 shows the guideway for advance and retardation (34) with the guide rollers again separately. The deflection of the control joint lever (39) is determined using the values from the required advance and retardation (see FIG. 41) and the angular relationships on the control joint lever (39). The control link lever (39) is extended in the circumferential direction beyond the guide rollers (36, 37) up to about 170 degrees in order to create a mass balance for the reciprocating movements with the flywheel control link lever (44). For reasons of strength and symmetry, the entire lever system is also installed displaced by 180 degrees in the circumferential direction.

FIGURE 22 section MM shows a section through the articulated lever. Since free rotational masses on the rotary pistons (2) and the eccentric auxiliary shaft (35) result from the leading and lagging, it is necessary to create a mass balance. Therefore, the system with the lever arms is also used for the opposite drive of the flywheel (45).

On the eccentric auxiliary shaft (35), which is driven by the rotary piston (2), two joints of the eccentric auxiliary shaft (43) are attached. The drive joint lever (38) with the joint flywheel (47) is attached to the auxiliary shaft flywheel (46). The control lever (39) is with the Articulated flywheel (47) rotatably connected. The intermediate joint (42) is firmly connected to the control joint lever (39). The connection between the flywheel joint (47) and the eccentric auxiliary shaft joint (43) is established with the intermediate joint lever (40). A triangle is thus formed with the joints intermediate joint (42), joint eccentric auxiliary shaft (43) and joint flywheel mass (47). If the control joint lever (39) is deflected outwards, the angle between the drive joint lever (38) and joint eccentric auxiliary shaft (43) is reduced. The auxiliary shaft flywheel (46) leads in relation to the rotary piston (2). If the control joint lever (39) is deflected inwards, the angle between the drive joint lever (38) and the joint eccentric auxiliary shaft (43) increases. The auxiliary shaft flywheel (47) lags behind the rotary piston (2) or the eccentric auxiliary shaft (35).
The radial rotation of the control joint lever (39) is carried out via the guide roller inner track (36) and the guide roller outer track (37) which run in the guide track milled in the inlet / outlet flange (11) for leading and trailing (34).
To design the flywheel mass, all free rotary mass forces must be calculated. The required guideway for leading and trailing the flywheel can then be determined using the angular relationships.
The entire lever system can of course also be accommodated in a separate housing.
This solution for obtaining constant funding without free mass forces has the main advantage that there is practically no loss of efficiency due to the lever system.

FIG. 23 section RR and the section illustration FIGURE 24 show a solution with a planetary gear.
The external gear drive gear (51) is located on the inside of the eccentric auxiliary shaft (35). The planetary gear drive gears (50) with the auxiliary shaft planet gear drive gears (57) are mounted on the drive flange (10). The internal gear drive gear (52) is attached to the shaft (4). The planetary gear is designed as a non-circular gear with teeth offset in the circumferential direction or radial direction, so that the required advance and lag can be realized according to FIG. 41.

FIG. 24 shows a section through the planet gears with the section SS. The planetary gear was also used to drive the flywheel. The external gear flywheel (54) is driven with the eccentric auxiliary shaft (35).
The internal gear flywheel (55) is driven via the planetary gear flywheel mass (53) on the auxiliary shaft planetary gear flywheel mass (56). The flywheel internal gear (55) forms a unit with the flywheel auxiliary shaft (46) and the flywheel mass (45). The planetary gear flywheel and in particular the external gear flywheel (54) is designed as a non-circular gear and designed so that the free rotary masses are balanced.
Speed translation between the eccentric auxiliary shaft (35) and shaft (4) can also be carried out with the planetary gear.

In the representations FIGURE 25 to FIGURE 27 , the transmission for the drive and flywheel is not arranged below the rotary piston but outside in a separate housing (60). The drive wheel (62) is driven by the output shaft (61), which is coupled to the shaft (3) of the rotary piston machine. The auxiliary wheel (63) is driven by an internal gear. The drive pinion (65) with the drive shaft (69) is driven by the auxiliary wheel (63) with the internal gear drive (64). At the same time, the pinion flywheel (67) with the shaft flywheel (68) and the flywheel mass (45) is driven with the auxiliary wheel (63) and the internal gearwheel flywheel (66). The internal gears drive (64) with the drive pinion (65) are designed as non-round gears to realize the pre-lag. The mass balance is carried out with the gear pair of internal gear flywheel (66) and pinion flywheel (67).
FIGURE 26 with the section TT shows a section through the drive wheels.
FIGURE 27 with the section UU shows a section through the gear pair for mass balancing.

FIGURE 28 shows the technical design of a rotary piston machine, where the drive unit with the necessary bearings shaft bearing (5), eccentric bearing (7), auxiliary bearing rotary piston (48), ring gear (8), pinion (9) and the shaft (4) with eccentric ( 6) is housed in its own housing. The rotary piston (2) runs in the epitrochoid (1), which is sealed off from the drive unit with a stuffing box (49) or other suitable seals. This version is particularly necessary and appropriate for contaminated and non-lubricating media.

FIG. 30 shows an application for stepless control of a hydraulic flow , as would be suitable, for example, for driving in a motor vehicle.
A drive machine (80) (electric motor, gasoline engine, diesel engine, gas turbine, etc.) drives the external gear of a planetary gear (81). The main rotary piston machine (82) is driven by the planet gears. The compressed medium flow coming from the main rotary piston machine (82) is conducted via the flow control valves (86) to the four drive rotary piston machines (84). The drive rotary piston machines (84) drive the drive wheels (85). If the drive rotary piston machines (84) and drive wheels (85) are to rotate more slowly, the medium flow is throttled with the flow control valves (86). The pressurized medium flow then passes through the flow control valve control turbine (87) to the control rotary piston machine (83), which drives the external gear of the planetary gear (81). The control rotary piston machine (83) is driven so that it supports the drive machine (80) in the direction of force. The speed of the main rotary piston machine (82) decreases due to the differential effect of the planetary gear (81) to the extent that the speed of the control rotary piston machine (83) increases. The drive machine (80) is thus also relieved and the power supply and speed can be reduced. In the design, the control rotary piston machine (83) is expediently designed to be smaller than the main rotary piston machine (82).

The arrows indicate the direction of force (mechanical or hydraulic). The speed of the drive machine (80) can be controlled for a given power requirement so that it achieves optimum efficiency. The power of the drive machine (80) can therefore be adapted exactly to the need. The differential effect between the four drive wheels results automatically. Furthermore, an ASR (anti-slip control) can be installed similar to the ABS. The regulation of the entire system is expediently carried out using a microcomputer. The power of the drive machine (80) is then specified by the microcomputer. The driver uses the accelerator pedal to set the driving speed instead of the engine speed. With this drive system, significant energy savings can be made through optimal, economical operation of the drive machine.

FIGURE 40 shows the curves V _HI V _HII and V _HIII . These curves represent the course of the absolute working space volume depending on the angle. The curves follow a sin² function.
The curves dV _I dV _II and dV _III represent the increase and decrease of the medium flow in the respective work rooms. The curves Md _I Md _II and Md _III represent the torque curve of the individual work rooms. These curves follow a simple sine function. It can also be seen from FIG. 40 how the absolute work space volume oscillates between the maximum value Vmax (bottom dead center) and the minimum value Vmin (top dead center).
The sinusoidal curves dV as well as the sinusoidal curves, which represent the torque curve, assume positive and negative values. Depending on whether the work area is in the inlet or outlet phase (pressure or suction phase). The curves of the individual work rooms are shifted by 60 degrees.
Funding is provided above the x axis. Therefore dV is positive. Suction takes place below the x-axis. dV is negative.
The torque curves of the tangential torque, which are shown in dashed lines, run analogously to the dV curves. Below the x-axis, the Md curves were shown with a smaller amplitude. This indicated that the pressure in the intake line can be lower than in the pressure line. This means that the torque to be applied is also smaller.

FIGURE 41 shows the effects of the lead and lag of the rotary piston. Where two work spaces (pressure or suction side) contribute to the funding, the two curves are added. The graduation of the input or output shaft / 3 is shown on the X axis below. The leading and lagging of the rotary piston is shown on the top. Section A shows the advance and retardation of the rotary piston (top) with respect to the drive shaft (bottom) in an enlarged view. Furthermore, the lines for the constant medium flow and the constant torque dV _medium and Md _{medium are} entered, which result from the leading and lagging of the rotary piston. For reasons of clarity, the degrees of rotary pistons and degrees of shaft (eccentric auxiliary shaft) are identical here. Of course, the eccentric auxiliary shaft and shaft run at three times the angular speed of the rotary piston. This means that a complete cycle of lead and lag does not extend over 30 degrees as shown in Figure 41, but over 90 degrees. This was also taken into account in FIGURE 21 with the guideway for advance and retardation.

LEGEND:

(X)

X axis

(Y)

Y axis

(E)

Inlet duct (14)

(A)

Exhaust duct (15)

(M)

The center of the entire system

(MK)

Center of the rotary piston

(OT)

Top dead center (90 and 270 degrees)

(UT)

Bottom dead center (0 and 180 degrees)

(R)

Radius of the rotary piston

(e)

eccentricity

(1)

Epitrochoids (peritrochoids)

(2)

Rotary piston

(3)

Carried out by rotary pistons

(4)

wave

(5)

Shaft bearing

(6)

eccentric

(7)

Eccentric bearing

(8th)

Sprocket

(9)

pinion

(10)

Drive flange

(11)

Inlet flange

(13)

Inlet-outlet unit rotatable

(14)

Inlet duct (E)

(15)

Outlet duct (A)

(16)

Control ring flow control

(17)

Control ring reversal of direction of rotation

(18)

Control cylinder flow control

(19)

Control cylinder reversal of direction of rotation

(20)

working space

(21)

Displacement unit

(22)

Guide for rotating separator

(23)

Divider rotatable

(24)

Guideway for control pin

(25)

Lever arm

(26)

Control pin

(27)

Separator fixed

(28)

Inlet openings

(29)

Exhaust ports

(30)

Control channel reversal of direction of rotation

(31)

Control channel flow control

(32)

Start-up inlet openings

(34)

Guideway for advance and retardation

(35)

Eccentric auxiliary shaft

(36)

Guide roller inner track

(37)

Leading role outside track

(38)

Drive joint lever

(39)

Control arm

(40)

Intermediate joint lever

(41)

Joint drive shaft

(42)

Intermediate joint

(43)

Articulated eccentric auxiliary shaft with articulated lever

(44)

Inertia control arm

(45)

Flywheel

(46)

Auxiliary shaft flywheel

(47)

Joint flywheel

(48)

Auxiliary bearing rotary piston

(49)

Stuffing box

(50)

Planetary gear drive gear

(51)

External gear drive gear

(52)

Internal gear drive transmission

(53)

Planetary gear flywheel

(54)

External gear flywheel

(55)

Internal gear flywheel

(56)

Auxiliary shaft planetary flywheel

(57)

Auxiliary shaft planetary gear drive gear

(60)

casing

(61)

Output shaft

(62)

drive wheel

(63)

Auxiliary wheel

(64)

Internal gear drive

(65)

Drive pinion

(66)

Internal gear flywheel

(67)

Pinion flywheel

(68)

Wave flywheel

(69)

drive shaft

(70)

Internal gear drive wheel

(80)

Power generation machine (diesel engine, gasoline engine, gas turbine)

(81)

Gear unit (planetary gear)

(82)

Main rotary piston machine

(83)

Control rotary piston machine

(84)

Drive rotary piston machines

(85)

Drive wheels

(86)

Flow control valves

(87)

Flow control valve control turbine

(88)

Hydraulic fluid reservoir

(89)

Hydraulic pressure line

(90)

Hydraulic suction line

LITERATURE

Patent specifications
[DE 2 021 513, DE 2 242 247, DE A1 2 402 084 and 0 094 379 A1]
DUBBEL paperback for mechanical engineering edition 16
OIL HYDRAULICS G. Bauer Teubner study scripts
OTTO AND DIESEL ENGINES Grohe Vogel Buchverlag

Claims (10)

Rotary piston machine with a jacket in the form of an epitrochoid (1) or peritrochoidal shape, preferably in a two-arch design with a triangular rotary piston (2) for transporting compressible and non-compressible gases, liquids or emulsions, hereinafter referred to as media, in the operating mode engine (turbine) or machine (pump) characterized in that the medium on one or both end faces (10, 11) of the housing through inlet channels (14) and outlet channels (15) preferably running in the circumferential direction with a separating web (27), preferably with the width of the passage through the rotary piston (3) is promoted as a separation between inlet channels (14) and outlet channels (15), and by bushings through the rotary piston (3), which enter the end faces of the rotary piston (2) in the axial direction and exit in the working spaces (20) in the radial direction one or both end faces (10, 11) preferably are arranged between the corner points of the rotary piston (2) and so the switching of the medium flow between the inlet channel (14) and the outlet channel (15) is carried out by the rotating rotary piston (2), and that there are preferably three bushings through the rotary piston (2), if an end flange is designed as an inlet / outlet flange (11) or preferably six bushings through the rotary piston (2) if both end flanges are arranged as inlet / outlet flanges (11), each is preferably located in the middle between two corner points of the rotary piston (2) and the four separators (27) between the inlet duct (14) and outlet duct (15) are preferably each at 0 degrees, 90 degrees, 180 degrees and 270 degrees and the inlet region in the counterclockwise direction is preferably from 90 degrees to 180 degrees and from 270 Degrees to 360 degrees, and the outlet range preferably from 0 degrees to 90 degrees and from 180 degrees to 270 degrees d in the clockwise direction of rotation, the inlet area preferably from 90 degrees to 0 degrees and from 270 degrees to 180 degrees and the outlet area preferably from 180 degrees to 90 degrees and from 360 degrees to 270 degrees, or that the rotary piston machine is flowed through in countercurrent, whereby on both end faces an inlet-outlet flange (10) and in the rotary piston a total of six bushings through the rotary piston (3) are housed and in the direction of rotation counterclockwise the inlet area of the medium flow from the front end drive to the front end output from 90 degrees to 180 degrees, and the associated outlet area ranges from 180 degrees to 270 degrees and for the medium flow from the front side output to the front side drive the inlet area extends from 270 degrees to 360 degrees and the outlet area ranges from 0 degrees to 90 degrees and in the direction of rotation with the clockwise direction the inlet area of the medium flow from the front side Drive to the front side output of 270 degrees bi s 180 degrees and the associated outlet area extends from 180 degrees to 90 degrees, and for the medium flow from the front side output to the front side drive the inlet area ranges from 90 degrees to 0 degrees and the outlet area ranges from 0 degrees to 270 degrees and that when used as an internal combustion engine ( Turbine) the medium (gasoline or gas mixture) is ignited with a suitable device at the top dead centers. Rotary piston machine according to claim 1 with inlet duct (14) and outlet duct (15), characterized in that the switchover point is preferably located on the cutting lines for rapid passage over the switchover region via the separating webs (27) between the inlet duct (14) and outlet duct (15) are formed by the intersection of the eccentricity circle with the coordinate cross, and so the switching range at one double-armed rotary piston machine is preferably about 60 degrees, 120 degrees, 240 degrees and 300 degrees, and in the counterclockwise direction of rotation, the inlet area preferably ranges from 60 degrees to 120 degrees and from 240 degrees to 300 degrees and the outlet area from 120 degrees to 240 Degrees and ranges from 300 degrees to 60 degrees, and in the clockwise direction of rotation the inlet range preferably ranges from 120 degrees to 240 degrees and from 300 to 60 degrees, and the outlet range ranges from 60 degrees to 120 degrees and from 240 degrees to 300 degrees and the bushings through the rotary piston (3) from the center between two corner points of the rotary piston are also rotated preferably 60 degrees clockwise. Rotary piston machine according to claim 1. - 2. in a flow-controllable design for compressible and non-compressible media, characterized in that the respective opposite switching area between inlet and outlet, that is to say the respective opposite separating web (27), is designed to be stationary and the other opposite dividing webs (23) in one Sliding unit (21) are arranged rotatably in the circumferential direction, and that the rotatable separating webs (23) on the sliding unit (21) about their own axis with a lever arm (25), which is connected to the control pin (26), in a guideway for the control pin ( 24) is rotatably arranged in the circumferential direction, are rotatable, so that the rotatable and displaceable separating webs (23) are always aligned parallel to the feed-through slot by the rotary piston (3), and the medium, depending on the position of the displaceable separating webs (23), is partially completely restored is fed back into the inlet channel (14) and for di e Reversing the direction of rotation, the entire inlet-outlet unit (13) is arranged rotatable by 90 degrees in the circumferential direction and that as a starting aid in operation as an engine (turbine) separately start-up inlet openings (32) in the range of preferably 120 degrees to 150 degrees and from 300 degrees to 330 degrees for the counterclockwise direction of rotation and start-up inlet openings (32) of preferably 30 degrees to 60 degrees and 210 degrees to 240 degrees for the clockwise direction of rotation, and these are preferably acted upon when required with medium when starting. Rotary piston machine according to claims 1-3 in a design for non-compressible and preferably compressible media in a flow-controllable design and with reversal of the direction of rotation, characterized in that in the end flanges a 90 degree circumferential direction with suitable actuating devices such as manual actuation, actuation with a gear and ring gear or actuation with a round cylinder , driven with compressible or non-compressible medium, rotatable inlet / outlet unit (13) is installed, in which, when the direction of rotation is considered, counterclockwise rotation, inlet openings (28) in the rotatable inlet / outlet unit (13) for radially out of the end flange at 90 degrees and 180 Degrees coming inlet channel (14) preferably at 100 degrees to the inlet channel (14) at 90 degrees and 280 degrees to the inlet channel (14) at 270 degrees and 170 degrees running after 180 degrees and 350 degrees running after 0 degrees, whereby in the considered direction of rotation counterclockwise, the inlet openings (28) at 170 degrees and 350 degrees have no function and are blocked, and from 10 to 80 degrees and from 190 to 260 degrees in the inlet-outlet unit (13) outlet openings (29) or outlet channels (15) are preferably introduced according to claim 3 and preferably at 10, 170, 190 and 350 degrees in the end flanges outlet channels (15) are created and the outlet openings (29) with a circumferential direction with suitable actuating devices such as manual actuation, actuation with gear and Sprocket or actuation with a cylinder with compressible or non-compressible medium rotatable flow control ring, which is preferably adjustable in the range of 10 to 80 degrees in the circumferential direction, so that the medium depending on the position of the flow control ring is pushed out either through the outlet channel (15) fixed in the inlet / outlet flange (11) is or is compressed again, and that in the clockwise direction the inlet-outlet unit (13) is moved 90 degrees clockwise so that the outlet openings (29) range from 90 degrees to 180 degrees and from 270 degrees to 360 degrees, the inlet openings (28) at 80 degrees and 260 degrees to the inlet channels (14) are open and the inlet openings (28) are blocked at 10 degrees and 190 degrees, and that as a starting aid in operation as an engine (turbine) separate inlet openings (32) in Range of preferably 120 degrees to 150 degrees and from 300 degrees to 330 degrees for counterclockwise rotation and nd inlet openings (32) for starting preferably 30 degrees to 60 degrees and 210 degrees to 240 degrees for the clockwise direction of rotation, and these are preferably acted upon when required when starting or with increased power requirements and that in the version for portable machine tools the container with compressed medium (compressed air tank) is attached directly to the machine tool (compressed air drill, pneumatic screwdriver etc.) and reloaded at the compressed air supply if required. Rotary piston machine according to claims 1-4, characterized in that the simultaneous increase and decrease of the entire medium flow due to the geometry of the individual working spaces is compensated for by the rotary piston machine, either in a separately arranged housing, preferably flanged to the rotary piston machine, or in the housing of the rotary piston machine itself a drive joint lever (38) with the drive joint (41) is attached to the drive shaft of the flanged housing (69) or on the drive shaft of the rotary piston machine (4), and the control joint lever (39) with the intermediate joint (42) is rotatably attached to the drive joint (41) is, and with the intermediate joint lever (40) the connection between the intermediate joint (42) and joint eccentric auxiliary shaft (43) with the eccentric auxiliary shaft (35) in the rotary piston machine or the output shaft (61) of the separately arranged housing coupled to the shaft of the rotary piston machine äuses is produced, and the leading and lag between rotary pistons with eccentric auxiliary shaft (35) in the rotary piston machine or the output shaft (61) of the separately arranged housing coupled to the shaft of the rotary piston machine on the one hand and drive shaft of the separately arranged housing (69) or drive shaft (4 ) the rotary piston machine, on the other hand, by guiding the control lever (39) in the radial direction in a guideway for leading and trailing (34) while in the drive flange (10) or inlet / outlet flange (11) of the rotary piston machine or in an end flange of the separately arranged housing the rotation is carried out, and that the joint system consisting of drive joint lever (38), control joint lever (39) and intermediate joint lever (40) rotated 180 degrees in the circumferential direction and that on the control joint lever (39) a flywheel mass (44) to compensate for the radially effective Forces is attached and thus constant medium flow through the rotary piston machine is achieved. Rotary piston machine according to claims 1-4, characterized in that the simultaneous increase and decrease of the medium flow due to the geometry of the individual work spaces through the rotary piston machine by means of a suitable, preferably composite gear with an intermediate wheel Like planetary gear, cycloid gear or other gear, which is either in a separately arranged housing, which is preferably flanged to the rotary piston machine, or in the rotary piston machine itself, is compensated for by the rotary piston (3), a centrally rotating eccentric auxiliary shaft (35) with an internal gear ( 51) is driven, and the internal gear (51) drives planet gears (50) and the planet gears (50) drive the internal gear drive gear (52) seated on the shaft (4) or a drive gear in a separately arranged housing from the output shaft (61) (62) is driven by the internal gear drive wheel (70), and via an auxiliary gear (63) the drive pinion (65) is driven on the drive shaft (69) and the entire gear unit is designed as a non-circular gear with teeth offset in the radial or circumferential direction is, so that the required advance and retardation r Achievement of constant flow between the drive shaft of the separately arranged housing or drive shaft of the rotary piston machine on the one hand, and the output shaft of the separately arranged housing or rotary piston with eccentric auxiliary shaft on the other hand, and thus constant medium flow through the rotary piston machine is achieved. Rotary piston machine according to claims 1-6, characterized in that the free rotational mass forces of the rotary piston occurring due to the leading and lagging in the embodiment according to claims 5 and 6 with an auxiliary shaft, preferably as a hollow shaft above the drive shaft, flywheel mass (46) or in a separate one Auxiliary shaft or hollow shaft flywheel housed on the housing, on which the oppositely advancing and lagging flywheel (45) is attached, is compensated by an articulated lever on the auxiliary shaft flywheel mass (46) with the joint auxiliary shaft flywheel mass (47), and on the joint auxiliary shaft flywheel mass ( 47) the control link lever (39) with the intermediate link (42) is rotatably mounted, and with the intermediate link lever (40) the connection between the intermediate link (42) and the joint eccentric auxiliary shaft (43) is made in the rotary piston machine or drive wheel (62) of the separately arranged housing will and the necessary opposite The leading and lagging between the rotary piston (2) and the eccentric auxiliary shaft (35) in the rotary piston machine or drive wheel (62) of the separately arranged housing on the one hand and the auxiliary shaft flywheel (46) on the other hand by guiding the control link lever (39) in a radial direction in a in the drive flange or An outlet flange of the rotary piston machine or a guide track milled in a front flange of the separately arranged housing for advance and retardation (34) is carried out during the rotation, and that the joint system comprising the joint auxiliary shaft, flywheel mass, control joint lever and intermediate joint lever is arranged again rotated by 180 degrees in the circumferential direction and that a flywheel control link lever (44) is attached to the control link lever (39) to compensate for the radially effective forces Rotary piston machine according to claims 1-7, characterized in that the free rotational mass forces of the rotary piston occurring due to the leading and lagging in the embodiment according to claims 5 and 6 by a suitable preferably composite gear, planetary gear or cycloid gear or another gear, which either in a separate arranged and preferably flanged to the rotary piston machine or arranged in the rotary piston machine itself is compensated for by the rotary piston (3) a centrally rotating eccentric auxiliary shaft (35) with an external gear flywheel (54) is driven and the external gear flywheel (54) drives the planetary gear flywheel (53) and the planetary gears flywheel (53) drive the internal gear flywheel (55) rotating on the auxiliary shaft flywheel (46), or in a separate housing from the output shaft (61) a drive wheel (62) with the internal gear drive wheel (70) is driven, and via an auxiliary gear (63) and the internal gear flywheel (66) the pinion on the flywheel shaft (68) with the flywheel mass (45) is driven, and the entire gear unit is designed as a non-circular gear with teeth offset in the radial direction or in the circumferential direction, so that the entire free rotational mass forces are canceled. Technical arrangement with a composite gear, preferably a planetary gear or other suitable gear according to the prior art and preferably a rotary piston machine according to claims 1 to 8 coupled with work machines or power machines and characterized in that at least two rotary piston machines according to claims 1 to 8 with a composite gear, preferably planetary gear of one Machine for power generation preferably gasoline engine, diesel engine, gas turbine or electric motor etc. are driven, or a machine that absorbs mechanical force such as generator, pump etc. operate and are preferably coupled to an inner or outer wheel of a composite transmission, and that a rotary piston machine that is preferably mechanically coupled to the planet gears or the auxiliary gear of the composite transmission as the main rotary piston machine, and a rotary piston machine preferably works with the Au Ssenrad or inner wheel of the composite gear connected works as a control rotary piston machine and with control elements such as flow control valves, flow meters, etc., the medium flow through the main rotary piston machine and the control rotary piston machine is controlled such that for the energy direction from the machine for power generation (engine, etc.) to the main rotary piston machine and for compression or pressurized medium, if not all of the energy provided by the machine for power generation is required by the energy consumers downstream of the main rotary piston machine, the excess energy that is supplied by the main rotary piston machine as compressed medium is fed into the control rotary piston machine, this as a machine for power generation ( Turbine) works and thus supports the engine and subsequently also the speed of the main rotary piston by the transmission ratio machine is reduced and this thus delivers less compressed medium flow, and that in a further operating mode with a smooth transition mechanical energy is fed into the control rotary piston machine and this works like the main rotary piston machine as a machine which absorbs mechanical energy and releases energy to the medium (motor) ; and that for the energy direction from the compressed or pressurized medium via the main rotary piston machine to the machine which absorbs mechanical force (generator etc.) if the generator does not require all of the energy presented, the excess energy which is presented by the main rotary piston machine as mechanical energy is shown in the control rotary piston machine is fed in, it works as a machine that absorbs mechanical energy and emits hydraulic energy (motor) and thus relieves the load on the machine that absorbs mechanical force (generator, etc.) and, as a result, also the speed of the main rotary piston machine through the transmission ratio is reduced and this thus delivers less mechanical energy, and that in a further operating mode with a smooth transition energy is fed from the medium into the control rotary piston machine and this like the main rotary piston machine as a machine that absorbs energy from the medium and emits mechanical energy (turbine) and that this technical arrangement also works as a clutch and speed ratio with the aid of the flow control elements, which are controlled by a suitable, preferably electronic control device. Rotary piston machine according to claims 1 to 9, characterized in that the components shaft (4) with eccentric (6), toothed ring (8), pinion (9), the bearing for shaft (5) and auxiliary bearing rotary piston (48), and all if required necessary internals for advance and retardation of the rotary piston and balance mass balance in a separate drive housing, and only the rotary piston (2) runs in the epitrochoid (1), and that as a seal between the drive housing and epitrochoid a stuffing box (49) or similar suitable Seals are used.

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