DE102010035164A1 - Rotary piston gas compressor used in automobile field, has cylindrical housing with rotary piston comprising ring segments connected with outer contours so as to form pressure surface - Google Patents

Abstract

The compressor has cylindrical housing (1-1) with a workspace in which rotary piston (1-2) comprising ring segments (1-21,1-21',1-22) is arranged in gastight state. The maximum outer radius of each ring segment is equal to the inner radius of the cylindrical housing. The minimum outer radius of each ring segment is smaller than the inner radius of the cylindrical housing. A pressure surface is formed by connecting the ring segments and outer contours (1-23,1-24).

Description

The invention relates to a gas compressor according to the preamble of claim 1. Such gas compressors are used in several areas of mechanical engineering, in particular as air compressors in motor vehicle construction and in gas pressure supply systems. Gas compressors are powered by a motor, z. B. electric or fuel engine operated. In gas compressors, the mechanical energy transforms the moving parts by compressing gaseous media into potential energy that is used in gas pressure equipment. The compression process is accompanied by internal energy losses due to highly turbulent gas movement, friction losses and unbalanced mass movement.

Rotary piston compressors have pistons inserted eccentrically into the housing and isolating valves which discharge from the housing and divide both in interaction of the working space with the low-pressure and high-pressure chambers. A rotary piston compressor of such construction is made DE 44 36 502 A1 known. Rotary piston compressors have pistons inserted eccentrically in the housing and piston valves that form rotating low and high pressure chambers. A rotary piston compressor of such construction is made WO 2007/025790 known. For high-pressure development in a line contact of the separator with rotating piston or housing large piston speed is necessary, causing friction losses.

Rotary piston compressors with housing Sliding axle screw plungers are made DE 3143193 A1 known. The disadvantage of this design is function-related high speed in the delivery of high pressure air, which causes large energy losses due to the acceleration and the movement of the air mass, friction losses and turbulence losses. The same disadvantage has rotary piston compressor DE 37 27 281 C2 with centrally located in the housing band-like displacement piston. Piston compressors used for high pressure have 2-stroke working process running in the same working space (clock 1, suction // cycle 2, compression and ejection). Piston compressors of this type are made WO 2010/041130 A1 . WO 2005/059362 A1 . WO 95/06204 . DE 39 09 531 A1 and many others known. The disadvantage, however, is that the back-and-forth motion causes the piston mass to lose a large amount of energy.

It is therefore the technical task to develop an energy-saving rotary piston gas compressor.

This object is solved by the characterizing features of claim 1. Further design options emerge from the subclaims 2 to 7.

Rotary piston gas compressor ( 1 ) operated by a motor ( 2 ), with a pressurized gas container ( 3 ) and a remote control system ( 4 ), with a working space, which centrally in cylindrical cavity of the housing ( 1.1 ) used rotary piston ( 1.2 ) has rotary pistons ( 1.2 ) of at least two pairs mirrored arranged ring segments ( 1.21 ; 1.21 ' ) and ( 1.22 ; 1.22 ' ), which outer contour radius have two different sizes and by gas-tight contact side surfaces and outer contours of the ring segments ( 1.21 ; 1.21 ' ) and ( 1.22 ; 1.22 ' ) with inner surface cylindrical cavity of the housing ( 1.1 ) Work Rooms ( 1.11 ; 1.11 ' ), while outer radius R _max ring segments ( 1.21 ; 1.21 ' ) is equal to the inner radius of the cylindrical hollow body, the housing ( 1.1 ) and outer radius R _min ring segments ( 1.22 ; 1.22 ' ) is smaller than the inner radius of the cavity the housing ( 1.1 ) and the outer contours of the wheel segments ( 1.21 ; 1.21 ' ) Rotary piston ( 2 ) with outer contours of the ring segments ( 1.22 . 1.22 ' ) on both sides with radial outer contours ( 1.23 ;) and ( 1.23 ' ) are connected and serve as a printing surface in 2-stroke work process.

Out of housing ( 1.1 ) by the gas-tight sliding movement leaking separating slide ( 1.12 ; 1.12 ' ) contact with wheel segments ( 1.22 ; 1.22 ' ) and divide the work spaces ( 1.11 ; 1.11 ' ) in interaction with rotary pistons ( 1.2 ) on variable volume high pressure ( 1111 ) and low pressure chamber ( 1112 ), while the high pressure chamber have the exhaust valves ( 1.14 ; 1.14 ' ) with a compressed gas control device ( 1141 ) and the low pressure chamber ( 1111 ) has a non-adjustable inlet opening ( 1.15 )

The compressed gas control device ( 1 .141) the exhaust valves ( 1.14 ; 1.14 ' ) consists of air pressure cylinders ( 1.1411 ), in this cylinder running piston ( 1.1412 ), with a staff of the valve flap ( 1.1413 ), and a controllable pressure relief valve switch ( 1.1414 ), while air pressure cylinder ( 1.1411 ) with compressed air reservoir ( 3 ) through a line ( 7.2 ).

For the sliding movements the separating slide ( 1.12 ; 1.12 ' ) are as execution mechanisms, the electric tension and pressure magnets ( 1121 ) with rod-shaped anchors ( 1122 ), which after Stromrichtungswechsel by the remote control unit ( 4 ) the anchor ( 1122 ) and the separating slide ( 1.12 ; 1.12 ' ) move in the pulling direction away from the rotary piston axis or pressure direction to rotary piston axis, while the rod anchors ( 1122 ) with a suspension ( 1123 ), which in the event of a power failure in the remote control unit ( 4 ) or when switching off the compressor Bar anchor ( 1122 ) moved in the pulling direction and separating slide ( 1.12 ; 1.12 ' ) from workspaces ( 1.11 ; 1.11 ' ) immediately undresses.

The outer contours of the ring segments ( 1.22 ; 1.22 ' ) the rotary piston ( 1.2 ) have before ring segments ( 1.21 ; 1.21 ' ) Reductions ( 1221 ) of the surface - 5 - which by sliding contour ( 1222 ) with further parts outer contours ( 1.22 ; 1.22 ' ) are connected. The sliding path the separating slide ( 1.12 . 1.12 ' ) with the aid of an adjustment disk ( 1 .124) to bar anchors ( 1122 ) - 2 - the electric tension and compression magnets ( 1121 ) is limited so that the separator slide tips the surface of the subsidence ( 1221 ) do not reach.

The inner contours of ring segments ( 1.21 . 1.21 '; 1.22 ; 1.22 ' ) the rotary piston ( 1.2 ) are with the on side plates ( 1.13 ) of the housing ( 1.1 ) mounted drive shaft ( 1.25 ) - 3 - 4 By wheel spokes bent three-dimensionally in the form of a screw blade ( 1.24 ), while the wheel spokes ( 1.24 ) through filters ( 5.1 ) the protective cage ( 5 ) sucked air through inlet opening ( 1.14 ) of the housing ( 1.1 ) in low pressure chamber ( 1111 ) the workspaces ( 1.11 ; 1.11 ' ).

In the case ( 1.1 ) in front of a separating slide ( 1.12 ; 1.12 ' ) - 5 - Are the rotational angle (a) in the direction of rotation of the exhaust valves ( 1.15 ; 1.15 ' ), and after separating slide ( 1.12 ; 1.12 ' ) are the angular distance (b) the inlet openings ( 1.14 ; 1.14 ' ), wherein rotational angular distances (a, b) according to the equations (A, B) are calculated; the ring segments ( 1.21 ; 1.21 ' ) Rotary piston ( 1.2 ) have outer contour ( 1211 ) with circumferential angle (C) calculated according to equation (C) and the outer contours of the ring segments ( 1.22 ; 1.22 ' ) the rotary piston ( 1.2 ) have reductions ( 1221 ) of the surface in front of ring segments ( 1.21 ; 1.21 ' ), which by sliding contour ( 1222 ) with further parts outer contours ( 1.22 . 1.22 ' ), reductions ( 1221 ) Peripheral angle (d) which is greater than that calculated according to the equation (D). a = - ((0.5 · t ₁ ): ω ₂ ) + z · ω ₁ + s ₁ ) (A) b = (0.5 · t ₁ ): ω ₂ ) + z · ω ₁ (B) c = t ₁ · ω ₁ ) + (t ₂ · ω ₁ ) + z · ω ₁ (C) d = (t ₁ · ω ₁ ) + z · ω ₁ (D)

• – Maximale Drehzahl des Rotationskolben (1.2) n – in U/Min;
• – die Winkelgeschwindigkeit ω₁ des Rotationskolben (1.2) – in °/Sec
• – Drehgeschwindigkeit ω₂ des Rotationskolben (1.2) – in m/1°
• – Außenradius R_max. Ringsegmentes (1.21) Rotationskolben (1.2) – in m;
• – Außenradius R_min. Ringsegmentes (1.22) Rotationskolben (1.2) – in m;
• – Stärke t₁ des Trennschiebers (1.12) – in m;
• – Einsatzzeit Z des Einschiebens des Trennschiebers (1.12; 1.12') – in Sec.
• – Maß t₂ der Einlassöffnung (1.15) – in m;
• – Sicherheitszulage S₁ für den Trennschieber (1.12) – in °

Decisive for the calculation are:

• - Maximum speed of the rotary piston ( 1.2 ) n - in RPM;
• The angular velocity ω _{1 of} the rotary piston ( 1.2 ) - in ° / sec
• - rotational speed ω _{2 of} the rotary piston ( 1.2 ) - in m / 1 °
• - outer radius R _max. Ring segment ( 1.21 ) Rotary piston ( 1.2 ) - in m;
• - outer radius R _min. Ring segment ( 1.22 ) Rotary piston ( 1.2 ) - in m;
• Thickness t _{1 of} the separating slide ( 1.12 ) - in m;
• - Operating time Z of inserting the isolating slide ( 1.12 ; 1.12 ' ) - in Sec.
• Dimension t _{2 of} the inlet opening ( 1.15 ) - in m;
• - Security allowance S ₁ for the separating slide ( 1.12 ) - in °

The application of the calculation results the measure of distances (a, b) between axes exhaust valves ( 1.14 ) and inlet openings ( 1.15 ) to the axis of the separating slide ( 1.12 ; 1.12 ' ) and the measure (c) the rotary piston tip ring segment ( 1.21 ; 1.21 ' ) avoids the blockage by collision of the rotary piston tip ring segment ( 1.21 ; 1.21 ' ) and isolating slide ( 1.12 ; 1.12 ' ). The separating slide ( 1.12 ; 1.12 ' ) must be read by the remote control unit ( 4 ) Has been used and withdrawn in milliseconds quickly according to service time Z, with the openings in the exhaust valves ( 1.14 ) Inlet opening ( 1.15 ) closed on time and opened. The remote control unit ( 4 ) should work undisturbed.

In every case, the blockage avoided by collision of the wheel segment ( 1.21 ; 1.21 ' ) and the separating slide ( 1.12 ; 1.12 ' ) the suspension ( 1123 ), with which the electrical tension and compression magnets ( 1121 ) the execution mechanisms of the sliding movements of separating slide ( 1.12 ; 1.12 ' ) are equipped. In the event of a power failure in the remote control unit ( 4 ) or when switching off the compressor moves the suspension ( 1123 ) the bar anchors ( 1122 ) in the pulling direction and separating slide ( 1.12 ; 1.12 ' ) from workspaces ( 1.11 ; 1.11 ' ) immediately undresses.

The abrupt contacts the separating slide ( 1.12 ; 1.12 ' ) with ring segments ( 1 . 21 ; 121 ' ) avoid reductions ( 1221 ) of the surface - 5 -, and with the help of the adjustment discs ( 1124 ) to bar anchors ( 1122 ) - 2 - the electric tension and compression magnets ( 1121 ) limited sliding path the gate valve ( 1.12 . 1.12 ' ). The thickness (t ₁ ) of the separator pusher tips is smaller than the depressions ( 1221 ) with circumferential angle (d), which do not reach Trennschieberspitzen.

When exceeding the pressure setpoint specified by the user, the outlet valve opens ( 1.14 ) independently and leaves compressed air in compressed air tank ( 3 ) to flow out. When compressed air in compressed air tanks ( 3 ) has reached the predetermined pressure setpoint, the overpressure valve switch ( 1.1414 ) by remote control system ( 4 ) the engine off.

After each full rotation of the rotary piston, the entire workspace is without back Movement used the piston simultaneously for two bars of the working process.

The invention will be explained in more detail with reference to an embodiment.

The new rotary piston gas compressor is described below in the version with a two-pointed rotary piston ( 1.2 ), as well as assembling 1 , Cross sections of the gas compressor ( 1 ) - 2 . 3 . 4 , "Off-on" position of the compressed gas control device ( 1141 ) the exhaust valves - 6 and in a representation of the successive movements - 7 , is shown. In this new rotary piston gas compressor a complete cycle of the 2-stroke working process is 180 °, ie after a full rotation the rotary piston simultaneously run two cycle.

To show:

1 the rotary piston gas compressor in assembly,

2 Cross section to rotor axis;

3 Cross section along the rotor axis and isolating slide

4 Cross section along the rotor axis and exhaust valves

4a . 4b Cross-section along the outlet valves and inlet openings

5 Use the gate valve without abrupt contact with rotary piston

6 "Off-on" position of the compressed gas control device ( 1141 ) the exhaust valves

7 Illustration of successive movements of the rotary piston

Rotary piston gas compressor ( 1 ) is by a motor ( 2 ) operated. Compressed gas flows out of rotary piston gas compressor ( 1 ) to the compressed gas tank ( 3 ) and gas pressure setpoint determines the user through the remote control system ( 4 ) 1

The working space rotary piston gas compressor ( 1 ) forms centrally in cylindrical cavity of the housing ( 1.1 ) used rotary piston ( 1.2 ) 2 The rotary piston ( 1.2 ) consists 2 from two pairs mirrored arranged ring segments ( 1.21 . 1.21 ' ) and ( 1.22 . 1.22 ' ), which outer contour radius have two different sizes and by gas-tight contact side surfaces and outer contours of the ring segments ( 1.21 . 1.21 ' ) and ( 1.22 . 1.22 ' ) with inner surface cylindrical cavity of the housing ( 1 ) Work Rooms ( 1.11 . 1.11 ' ) form. Outer radius R _max. Ring segments ( 1.21 . 1.21 ' ) is equal to the inner radius of the cylindrical hollow body, the housing ( 1 ) and outer radius R _min. Ring segments ( 1.22 . 1.22 ' ) is smaller than the inner radius of the cavity the housing ( 1 ) and the outer contours of the wheel segments ( 1.21 and 1.21 ' ) Rotary piston ( 1.2 ) with outer contours of the ring segments ( 1.22 and 1.22 ' ) on both sides with radial outer contours ( 1.23 . 1.24 ) and ( 1.23 ' . 1.24 ' ) are connected and serve as a printing surface in 2-stroke work process.

Out of housing ( 1.1 ) by the gas-tight sliding movement leaking separating slide ( 1.12 ; 1.12 ' ) contact with wheel segments ( 1.22 ; 1.22 ' ) and divide the work spaces ( 1.11 ; 1.11 ' ) in interaction with rotary pistons ( 1.2 ) on variable volume high pressure ( 1111 ) and low pressure chamber ( 1112 ) The high pressure chamber ( 1111 ) have the exhaust valves ( 1.14 ; 1.14 ' ) with a compressed gas control device ( 1141 ) and the low pressure chamber ( 1112 ) has a non-adjustable inlet opening ( 1.15 ).

The compressed gas control device ( 1141 ) - 6 - the exhaust valves ( 1.14 ; 1.14 ' ) consists of air pressure cylinders ( 1.1411 ), in this cylinder running piston ( 1.1412 ), with a staff of the valve flap ( 1.1413 ), and a controllable pressure relief valve switch ( 1.1414 ). The air pressure cylinder ( 1.1411 ) is with compressed air storage ( 3 ) through a line ( 7.1 ) and overpressure valve switch ( 1.1414 ) through the pipe ( 4.3 ) with remote control system ( 4 ).

For the sliding movements the separating slide ( 1.12 ; 1.12 ' ) are as execution mechanisms, the electric tension and pressure magnets ( 1121 ) with rod-shaped anchors ( 1122 ), which after Stromrichtungswechsel by the remote control unit ( 4 ) the anchor ( 1122 ) and the separating slide ( 1.12 ; 1.12 ' ) in pulling direction away from rotary piston axis - 7a 0 ° and 7f 150 ° - or in compression direction - 7a 25 ° to 7e Move 135 ° to the rotary piston axis.

The rod anchors ( 1122 ) are equipped with a suspension ( 1123 ), which in the event of a power failure in the remote control unit ( 4 ) or when switching off the compressor, the rod anchors ( 1122 ) moved in the pulling direction and separating slide ( 1.12 ; 1.12 ' ) from workspaces ( 1.11 ; 1.11 ' ) immediately undresses.

To abrupt contact the gate valve ( 1.12 ; 1.12 ' ) with ring segments ( 1.21 ; 121 ' ), the outer contours have the ring segments ( 1.22 ; 1.22 ' ) the rotary piston ( 1.2 ) in front of ring segments ( 1.21 ; 1.21 ' ) Reductions ( 1221 ) the surface 5 , which by sliding contour ( 1222 ) with further parts outer contours ( 1.22 ; 1.22 ' ) are connected.

The sliding path the separating slide ( 1.12 . 1.12 ' ) with the aid of an adjustment disk ( 1124 ) to bar anchors ( 1122 ) the electric tension and pressure magnets ( 1121 ) is limited so that the separator slide tips the surface of the subsidence ( 1221 ) do not reach.

The inner contours of ring segments ( 1.21 . 1.21 '; 1.22 . 1.22 ' ) the rotary piston ( 1.2 ) are with the on side plates ( 1.13 ) of the housing ( 1.1 ) mounted drive shaft ( 1.25 ) 3 and 4 by three-dimensional in the form screw blade bent wheel spokes ( 1.24 ) connected. The wheel spokes ( 1.24 ) driving through filters ( 5.1 ) the protective cage ( 5 ) 1 sucked air through inlet opening ( 1.15 ) of the housing ( 1.1 ) in low pressure chamber ( 1111 ) the workspaces ( 1.11 ; 1.11 ' ). When rotating the rotary piston ( 1.2 ) moves the remote control unit ( 4 ) by change of direction in execution mechanisms ( 1121 . 1121 ' ) according to the rotational movement of the rotary piston in the pulling direction and in the pressure direction to the rotary piston axis the separating slide ( 1.12 . 1.12 ' ). This results in gas compressor ( 1 ) at the same time the workspaces ( 1.11 . 1.11 ' ), which consists of housing ( 1 ) outlet gate valves ( 1.12 . 1.12 ' ) in interaction with rotary pistons ( 1.2 ) on variable volume high pressure ( 1111 . 1111 ' ) And low pressure chamber ( 1112 . 1112 ' ) - 7a to. 7f ,

• Takt 1 – Bei Drehbewegung den Rotationskolben (1.2) 7c- bis 7f der Volumen der Niederdruckkammer (1.112) vergrößert sich und wird mit dem Luft befühlt.
• Takt 2 – Gleichzeitig wird Volumen der Hochdruckkammer (1.111) verkleinert sich und die Luft wird verdichtet 7c- bis 7d, dabei bleiben die Auslassventile (1.14; 1.14') geschlossen – 6a, weil Luftdruck in Zylinder (1.1411) der Druckgassteuerungseinrichtung (1.141) größer ist, als Luftdruck in Hochdruckkammer (1.111). Nach dem Überschreiten des dem Anwender vorgegebenen Drucksollwerts in Hochdruckkammer (1.111) lauft sich der Druckluft aus Zylinder (1.1411) – 6b durch steuerbaren Überdruckventilschalter (1.1414) der Druckgassteuerungseinrichtung (1.141) aus, den Ventilklappe (1.1413) wird geöffnet und Druckluft strömt – 6b durch Leitungen (7) zum Druckluftspeicher (3).

In both workspaces ( 1.11 . 1.11 ' ) at the 180 ° rotation of the rotary piston ( 1.2 ) takes place simultaneously the 2-stroke cycle with clock 1 - Feelings and clock 2 - compressing and pushing out:

• Clock 1 - When rotating the rotary piston ( 1.2 ) 7c - to 7f the volume of the low pressure chamber ( 1112 ) increases and is felt with the air.
• Clock 2 - At the same time volume of the high pressure chamber ( 1111 ) shrinks and the air is compressed 7c - to 7d , the exhaust valves ( 1.14 ; 1.14 ' ) closed - 6a because air pressure in cylinder ( 1.1411 ) of the compressed gas control device ( 1141 ) is greater than air pressure in the high pressure chamber ( 1111 ). After exceeding the user-specified pressure setpoint in the high-pressure chamber ( 1111 ) the compressed air runs out of cylinder ( 1.1411 ) - 6b by controllable overpressure valve switch ( 1.1414 ) of the compressed gas control device ( 1141 ), the valve flap ( 1.1413 ) is opened and compressed air flows - 6b through lines ( 7 ) to the compressed air reservoir ( 3 ).

At the end of the cycle - 7f - becomes air pressure cylinder ( 1411 ) with the compressed air through the line ( 7.1 ) from compressed air storage ( 3 ) and the valve flap ( 1.1413 ) is closed, the workrooms ( 1.11 . 1.11 ' ) are new to the air and are prepared for the new cycle.

The remote control unit ( 4 ) controls the compressed air difference between the compressed air reservoir ( 3 ) and in high-pressure chamber ( 1111 ). When compressed air in compressed air tanks ( 3 ) has reached the user specified pressure setpoint, the pressure relief valve switch ( 1.1414 ) by remote control system ( 4 ) engine, avoids compressed air flap ( 7.2 ) on the lines ( 7 ) the pressure loss in the compressed air reservoir ( 3 ).

After regular and unexpected turn off the rotary piston gas compressor ( 1 ) the isolating valves ( 1.12 . 1.12 ' ) by the suspension ( 1123 ), which rod anchors ( 1122 ) Pulling direction moves, from working spaces ( 1.11 . 1.11 ' ) pulled out immediately and the blocking by collision of the wheel segment ( 1.21 . 1.21 ' ) and isolating slide ( 1.12 . 1.12 ' ) is avoided.

In proposed rotary piston gas compressor ( 1 ) The air sucked into the working space is compressed in the same room and gets no rotational movement. Proposed engineering solution avoids energy losses in acceleration and movement of air mass, friction losses and turbulence losses.

LIST OF REFERENCE NUMBERS

1

Rotary piston gas compressor

1.1

casing

1.11

working space

1111

High-pressure chamber

1112

Low-pressure chamber

1.12

separating slide

1121

Train print Magnets

1122

Rod-shaped anchor

1123

suspension

1124

alignment discs

1.13

side plate

1131

Support for the working shaft

1.14

outlet valve

1141

Compressed air control device

1.1411

Air Cylinder

1.1412

piston

1.1413

valve flap

1.1414

Pressure relief valve switch

1.2

rotary piston

1.21

Ring segments with outer contour radius R _max.

1211

Outer contour with circumferential angle (c)

1.22

Ring segments with outer contour radius R _min.

1221

Lowering in outer contour with circumferential angle (d)

1222

Sliding contour in outer contour

1.23

Radial outer contour

1.24

wheel spokes

1.25

working shaft

2

engine

3

Compressed gas storage

4

Remote control system

4.1

Control line to the engine

4.2

Control cable to train pressure magnets

4.3

Control line to overpressure valve switch

5

protective cage

5.1

air filter

6

protective cage

7

Compressed air lines

7.1

Line to overpressure valve switch 1.1414

7.2

Pneumatic rear flap

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 4436502 A1 [0002]
• WO 2007/025790 [0002]
• DE 3143193 A1 [0003]
• DE 3727281 C2 [0003]
• WO 2010/041130 A1 [0003]
• WO 2005/059362 A1 [0003]
• WO 95/06204 [0003]
• DE 3909531 A1 [0003]

Claims (8)

Rotary piston gas compressor ( 1 ) operated by a motor ( 2 ), with a pressurized gas container ( 3 ) and a remote control system ( 4 ), with a working space, which centrally in cylindrical cavity of the housing ( 1.1 ) used rotary piston ( 1.2 ), characterized in that rotary piston ( 1.2 ) of at least two pairs mirrored arranged ring segments ( 1.21 ; 1.21 ' ) and ( 1.22 ; 1.22 ' ), which outer contour radius have two different sizes and by gas-tight contact side surfaces and outer contours of the ring segments ( 1.21 ; 1.21 ' ) and ( 1.22 ; 1.22 ' ) with inner surface cylindrical cavity of the housing ( 1.1 ) Work Rooms ( 1.11 ; 1.11 ' ), while outer radius R _max. Ring segments ( 1.21 ; 1.21 ' ) is equal to the inner radius of the cylindrical hollow body, the housing ( 1.1 ) and outer radius R _min. Ring segments ( 1.22 ; 1.22 ' ) is smaller than the inner radius of the cavity the housing ( 1.1 ) and the outer contours of the wheel segments ( 1.21 ; 1.21 ' ) Rotary piston ( 2 ) with outer contours of the ring segments ( 1.22 . 1.22 ' ) on both sides with radial outer contours ( 1.23 ) and ( 1.23 ' ) are connected and serve as a printing surface in 2-stroke work process. Rotary piston gas compressor ( 1 ), characterized in that housing ( 1.1 ) by the gas-tight sliding movement leaking separating slide ( 1.12 ; 1.12 ' ) with wheel segments ( 1.22 ; 1.22 ' ) and share the work spaces ( 1.11 ; 1.11 ' ) in interaction with rotary pistons ( 1.2 ) on high pressure variable volume ( 1111 ) and low pressure chamber ( 1112 ), while the high-pressure chamber ( 1111 ) the exhaust valves ( 1.14 ; 1.14 ' ) with a compressed gas control device ( 1141 ) and the low pressure chamber ( 1111 ) has a non-adjustable inlet opening ( 1.15 ) Rotary piston gas compressor ( 1.1 ), characterized in that the compressed gas control device ( 1141 ) the exhaust valves ( 1.14 ; 1.14 ' ) from air pressure cylinder ( 1.1411 ), in this cylinder running piston ( 1.1412 ), with a staff of the valve flap ( 1.1413 ), and a controllable pressure relief valve switch ( 1.1414 ), while air pressure cylinder ( 1.1411 ) with compressed air reservoir ( 3 ) through a line ( 7.1 ). Rotary piston gas compressor ( 1 ), characterized in that for the sliding movements the separating slide ( 1.12 ; 1.12 ' ) as execution mechanisms the electric tension and pressure magnets ( 1121 ) with rod-shaped anchors ( 1122 ), which at Stromrichtungswechsel by the remote control unit ( four ) the anchor ( 1122 ) and the separating slide ( 1.12 ; 1.12 ' ) move in the pulling direction away from the rotary piston axis or pressure direction to rotary piston axis, while the rod anchors ( 1122 ) with a suspension ( 1123 ), which in the event of a power failure in the remote control unit ( four ) the bar anchors ( 1122 ) moved in the pulling direction and separating slide ( 1.12 ; 1.12 ' ) from workspaces ( 1.11 ; 1.11 ' ) immediately undresses. Rotary piston gas compressor ( 1 ), characterized in that the outer contours of the ring segments ( 1.22 ; 1.22 ' ) the rotary piston ( 1.2 ) the reductions ( 1221 ) of the surface in front of ring segments ( 1.21 ; 1.21 ' ) which by sliding contour ( 1222 ) with further parts outer contours ( 1.22 ; 1.22 ' ), while the sliding path the separating slide ( 1.12 . 1.12 ' ) with the aid of an adjustment disk ( 1124 ) to bar anchors ( 1122 ) the electric tension and pressure magnets ( 1121 ) are so delimited that separator slide tips the surface of the subsidence ( 1221 ) do not reach. Rotary piston gas compressor ( 1 ), characterized in that the inner contours ring segments ( 1.21 ; 1.21 '; 1.22 . 1.22 ' ) the rotary piston ( 1.2 ) with the on side plates ( 1.13 ) of the housing ( 1.1 ) mounted drive shaft ( 1.25 ) by three-dimensional in the form of screw blade bent wheel spokes ( 1.24 ), while the wheel spokes ( 1.24 ) through filters ( 5.1 ) the protective cage ( 5 ) sucked air through inlet opening ( 1.14 ) of the housing ( 1.1 ) in low pressure chamber ( 1111 ) the workspaces ( 1.11 ; 1.11 ' ). Rotary piston gas compressor ( 1 ), characterized in that in the housing ( 1.1 ) in front of a separating slide ( 1.12 ; 1.12 ' ) with angular distance (a) in the direction of rotation of the exhaust valves ( 1.15 ; 1.15 ' ) are inserted, and after separating slide ( 1.12 ; 1.12 ' ) with the angular distance (b) the inlet openings ( 1.14 ; 1.14 ' ), wherein rotational angular distances (a, b) according to the equations (A, B) are calculated; the ring segments ( 1.21 ; 1.21 ' ) Rotary piston ( 1.2 ) have outer contour ( 1211 ) with circumferential angle (C) calculated according to equation (C) and the outer contours of the ring segments ( 1.22 ; 1.22 ' ) the rotary piston ( 1.2 ) have reductions ( 1221 ) of the surface in front of ring segments ( 1.21 ; 1.21 ' ), which by sliding contour ( 1222 ) with further parts outer contours ( 1.22 . 1.22 ' ), reductions ( 1221 ) Peripheral angle (d) which is greater than that calculated according to the equation (D). a = - ((0.5 · t ₁ ): ω ₂ ) + Z · ω ₁ + s ₁ ) (A) b = (0.5 · t ₁ ): ω ₂ ) + Z · ω ₁ (B) c = (t ₁ · ω ₁ ) + (t ₂ · ω ₁ ) + Z · ω ₁ (C) d = (t ₁ · ω ₁ ) + Z · ω ₁ (D) Decisive for the calculation are: - Maximum speed of the rotary piston ( 1.2 ) n - in RPM; The angular velocity ω _{1 of} the rotary piston ( 1.2 ) - in ° / sec - rotational speed ω _{2 of} the rotary piston ( 1.2 ) - in m / 1 ° - external radius R _max. Ring segment ( 1.21 ) Rotary piston ( 1.2 ) - in m; - outer radius R _min. Ring segment ( 1.22 ) Rotary piston ( 1.2 ) - in m; Thickness t _{1 of} the separating slide ( 1.12 ) - in m; - Operating time Z of inserting the isolating slide ( 1.12 ; 1.12 ' ) - in Sec. Dimension t _{2 of} the inlet opening ( 1.15 ) - in m; - Security allowance S ₁ for the separating slide ( 1.12 ) - in °;

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