DE19924645A1 - Rotary vane compressor or vacuum pump - Google Patents

Abstract

The invention relates to a rotary compressor (10), comprising an annular wall (13) and two lateral walls (15, 17) which encompass a compression chamber (26). A rotor (14) extends into said compression chamber (26), whose rotor axis (24) in operational mode lies eccentrically in relation to an annular wall axis (20). The annular wall (13) is rotatably mounted on at least one fixed running surface (19), whose running surface axis (22) is parallel and eccentric in relation to the annular wall axis (20) and is eccentric in relation to the rotor axis (24). In order to achieve as concentric a position as possible for the rotor (14) and annular wall (13) in an idling state and at the same time a precise positioning of the rotor (14) in relation to the annular wall (13) in an operational mode, the annular wall (13) can be rotated about an angle greater than 60 DEG relative to the running surface (19) between the operational mode and the idling state.

Description

The invention relates to a rotary vane compressor or Rotary vane vacuum pump (hereinafter referred to as rotary vane referred to more densely) with the ge in the preamble of claim 1 named features.

Rotary vane compressors of this type are used for compressing or starting suction of gaseous media. The medium enters the Compression space at a wide gap between the rotor and the ring wall and is by the rotating rotor slide moved into a narrowing area of the gap. The medi is between two rotors during this movement slide and enclosed the side walls and is thereby condensed. Before the narrowest part of the gap is in the ring wall formed an outlet opening that the compression space opens to an outlet line. The compressed medium will pushed out through this outlet opening, since it is not through the narrowest part of the gap can flow.

Rotary vane compressors are used in motor vehicles, those in conjunction with other units (hydraulic pump, water pump, alternator) are driven. Here, the Rotary vane compressors are generally not independent of the other units are shut down and constantly produces egg ne compaction and delivery performance. The rotary vane compressor therefore requires drive power even during a kind of "idling" and wear out. Therefore, the aim is for ei NEN drive of the rotary vane compressor in "idle" is required to reduce power loss and wear.

From DE 22 49 591 B2, which is the basis for the preamble of An Proof 1 forms, is a variable-volume rotary flask ben pump known, in which in a pump housing a rotor and an eccentric ring is also mounted, which surrounds the rotor. Around the eccentric ring should change the pump capacity  means not illustrated from the outside in its rotational position be adjusted. How this is to be done remains open.

From US 2,685,842 a rotary piston pump for fluid is knows, with an eccentric ring surrounded by a pump housing and is rotatably mounted in this on its outer lateral surface. The eccentric ring is only pumped by the pressure force Fluids twisted that within the pump housing to an on driven by the eccentric ring, and by a spring in pushed back its starting position.

Compressors are known from JP 63-140881 (A) and US 3,506,380, where a rotor is surrounded by an inner housing, which in an outer housing is slidable to the relative position of the Rotor to the inner housing and thus the delivery rate of the com to change pressors. The drive for moving the inner rim housing is fixed in place on the outer housing, with between Sealed bushings required for outer and inner housing are.

From US 5,051,070 is a rotary vane compressor for the Kom pression of a cooling gas in a motor vehicle known. This Documentation suggests that during idle the condensed Promote cooling gas through a bypass. The cooling gas nevertheless compressed, so that drive power is constantly required is. Furthermore, the cooling gas heats up by continuing to run de conveying through the bypass. Because the rotary vane compressor constantly promotes, it is subject to Ver even when idling wear.

WO 88/02438 describes a rotor machine that is used as combustion tion motor, fluid motor, fluid pump or compressor can be used is. To change the delivery rate of the rotor machine is the rotor relative to its housing transverse to its axis of rotation can be moved by eccentric bearings in the housing. The Rotor axis offset from the axis driving the rotor. This Axis misalignment must be compensated for so that the uniform drive of the rotor is guaranteed.  

The invention has for its object a rotary valve to create compressors of the type mentioned, in which the The disadvantages mentioned above are overcome and in particular one easy change to an energy-saving and wear reducing idle of the rotary vane compressor is possible.

The object is according to the invention by a rotary slide valve solved more densely with the features of claim 1.

The invention is based on the knowledge that it is not zwin It is necessary that the ring wall, as in DE 22 49 591 B2 and US 2,685,842, stored in an outer housing is, but that it is sufficient if at least the ring wall on at least one fixed and non-rotatable socket is mounted. The ring wall is then more accessible and it can move drives are used for their rotation. It can although an outer housing must still be provided, this must be included the rotary vane compressor according to the invention, however, none Support function for the ring wall and can be special be designed to hold the drive.

In an advantageous embodiment of the invention, the ring wall connected to the side walls to form a housing and this Housing is mounted on the at least one socket.

The socket axis in the operating position is particularly advantageous development in the plane of symmetry between the rotor axis and the Ring wall axis arranged. With a minimal size of the socket thereby a maximum adjustment of the ring wall axis to the rotor axis possible. Is the socket axis in the center between the Ro gate axis and the ring wall axis arranged, so the rotor axis and the ring wall axis in idle in concentric shear position, so that the rotor and the guided in it Rotate or rotate the rotor slide around the same axis. It takes place then there is no relative movement between them. The rotor therefore the slide and the rotor do not wear in the area of Guides of the rotor slide.  

An advantageous development provides that the ring wall between between the operating position and the idling state Rotate 180 ° continuously. Due to the friction between the The rotor blades and the ring wall rotate the ring wall itself active and alternating from the operating position to idle state or from the idle state to the operating position. According to the invention, the ring wall is in the operating position and in the idle state with the sockets over the outer housing locked and unlockable for switching. This is for example only have a sealing and a check valve gender locking bolt required.

Another adjustment mechanism according to the invention provides that the ring wall between the operating position and idle was reversibly rotatable by 180 °. It is advantageous the ring wall by a self-locking worm drive rotatable. The rotor is particularly precise and infinitely variable Adjustable housing. Driving the worm can be done in easier Way done by an electric motor. As advantageous Al ternative the invention further provides that the ring wall is rotatable by a rotary vane motor. The wing motor can can be controlled particularly easily.

In a particularly advantageous development of the invention the ring wall is moved by means of the rotary slide supercharger or vacuum pump generated overpressure or Vacuum. For this purpose, for example, the locking bolt by applying the excess pressure to a pneumatic cylinder be done. The pneumatic cylinder unlocks the bolt, see above that the ring wall automatically due to friction in the void running condition rotates. The overpressure can also be on the rotary wing be created. The rotating wing moves the ring wall at ent speaking high pressure in the idle state. At low The rotary vane moves under pressure due to the friction of the rotor slide or a spring force back.  

The configurations can be developed so that the Ring wall in cross section deviates from the circular shape and from ver different circle segments with different radii is. The different radii make it possible to condense a space on the intake side and on the Specify a compression path on the pressure side. Two compression and intake section can be a seal distance to be determined.

With a first radius, a semicircle can be formed by the center of which runs the ring wall axis. The Verdich This extends the length of the processing line and the sickle height of the compression space at an outlet control edge enlarged.

Furthermore, in the direction of rotation immediately behind an outlet a circle segment with a second radius can be arranged, which is almost equal to the radius of the rotor. In this way is an extended sealing section between the pressure and the Intake side at the narrowest point between the rotor and the ring wall created that seals better. The circle segment spanned advantageously an angle of approx. 30 °.

Such a ring wall, which is not circular in cross section, can also for rotary vane compressors with those in the preamble of the An Proverb 1 mentioned features are used.

Preferred embodiments of a rotation according to the invention slide compressor are described in the following with the help of the enclosed schematic figures explained in more detail. It shows:

Fig. 1 shows a first embodiment of a rotary compressor according to the invention in a slide-in FIG. 2 II-designated cross-section,

Fig. 2 is a longitudinal section designated in FIG. 1 II-II,

Fig. 3 shows a second embodiment of a rotary compressor according to the invention, in a III-III in FIG. 4 designated cross-section

Fig. 4 shows the longitudinal section marked IV-IV in Fig. 3,

Fig. 5 shows a third embodiment of a rotary compressor according to the invention in Fig. Cross-section indicated by VV 7,

Fig. The cross-section indicated in Fig. 7 with VI-VI 6, and

Fig. 7 shows the longitudinal section designated VII-VII in Fig. 5.

Figs. 1 to 7 show a rotary vane compressor, or a rotary vane vacuum pump 10 with a housing 12 which surrounds an annular wall 13 has a circular-cylindrical rotor 14. The rotor 14 has a rotor shaft 16 which passes through the housing 12 with its two end regions. The rotor shaft 16 is rotatably supported and has a rotor axis 24 . The annular wall 13 has an annular wall axis 20 and, together with two side walls 15 and 17, forms a compression space 26 .

The rotary vane compressor 10 is set in the operating position. In this operating position, the ring wall axis 20 and the rotor axis 24 extend parallel to one another and are spaced apart such that the rotor 14 in the lower region in the figures on the ring wall 13 of the compression chamber 26 almost abuts and in the upper region between the rotor 14 and the annular wall 13 is formed a gap. The compression chamber 26 narrows on both sides of the rotor 14 in cross section in a crescent shape downwards.

Rotor slides 28 are each slidably guided in the rotor 14 to the radius thereof. The rotor slide 28 are designed such that they abut and seal on the ring wall 13 due to their centrifugal force during operation of the rotor 14 . By means of the rotor slide valve 28 in operation, the sealing chamber 26 is divided into chambers.

During operation of the rotary vane compressor, gaseous medium flows into the chambers through an inlet opening 27 formed in the ring wall 13 (which is provided with a filter fleece in FIGS . 5 to 7). The rotor 14 rotates in the direction of the arrow x, encloses the medium in the chambers between two rotor slides 28 and moves it into the narrowing gap of the compression space 26 . The medium is compressed. In the narrowed area of the gap, the highly compressed medium flows through an outlet opening 29 , an outlet channel 30 and an outlet line 32 .

The ring wall axis 20 can be brought into a concentric position with respect to the rotor axis 24 . For this purpose, adjustment mechanisms are provided in order to move the ring wall 13 and parts of the housing 12 from the operating position to an idle state.

The adjustment mechanisms comprise two sockets 18 , which are fastened with supports 34 to a base 36 (divided into two in FIGS . 1, 2, 5, 6 and 7). The rotor shaft 16 is rotatably supported with needle bearings 37 in bores of the bushes 18 . The housing 12 is rotatably supported on the outer circumferences of the bushings 18 with needle bearings 39 . The sockets 18 have as an axis of their outer circumference a socket axis 22 which extends eccentrically and par allel to the rotor axis 24 . At the same time, the socket axis 22 extends eccentrically and parallel to the ring wall axis 20 .

In Fig. 1 and 2, a first embodiment of a rotary slide is shown berverdichters. The adjustment mechanism here also has a worm drive 38 which is arranged on the base 36 and comprises an electric motor 39 and a worm 41 driven thereby. The worm 41 tangentially engages in a toothing 40 which is formed on the outer circumference of the housing 12 . By means of the worm drive 38 , the Ge housing 12 and the ring wall 13 are rotatable about the sleeve axis 22 .

Since the ring wall axis 20 is eccentric to the bush axis 22 , when the ring wall 13 rotates, the ring wall axis 20 moves in the direction of a concentric position with respect to the rotor axis 24 . The crescent-shaped compression chamber 26 is there through to an annular space, the wall thickness, when rotating the housing 12 by 180 °, is the same thickness. The ring wall 13 is then in the optimal idle state, the rotor 14 does not compress and promote the medium enclosed in the chambers, but only circulates without pressure. The rotary vane compressor only requires the drive power to overcome the friction between the rotor vanes 28 and the ring wall 13 . There is no relative movement and therefore no friction between the rotor slides 28 and the guide slots of the rotor 14 .

In order to prevent the medium from being conveyed into the outlet line, it suffices to enlarge the narrowest gap between the ring wall 13 and the rotor 14 (0.02 to 0.05 mm) by a few tenths of a millimeter. For this purpose, the ring wall 13 only has to be rotated by a substantially smaller angular amount than 180 °. However, compressed medium is then conveyed to the intake side and blown out there, thus driving power is consumed and inefficiency is generated.

On the outer periphery of the housing 12 , an outlet ring 42 is easily seen, which surrounds the housing 12 , sealed by means of two seals 43 to this and is integrally formed on the base. From the lassring 42 forms an annular space 45 into which the outlet channel 30 from the housing 12 and the outlet line 32 of the soc kels 36 open. The outlet ring 42 thus connects the outlet line 32 with the outlet channel 30 of the housing 12 both in the operating position and in the idle state and in any intermediate position.

In FIGS. 3 and 4 a second embodiment of a rotary vane compressor 10 is shown. To adjust between the operating position and the idle state, a locking mechanism with a bolt 44 is provided in addition to the sockets 18 . The bolt 44 engages in a first recess 46 , which is arranged conically and open to the outside on the circumference of the housing 12 . The bolt 44 is biased by a spring 50 . From the exit line 32 extends through the bolt 44th Between the recess 46 and the bolt 44 , a seal 48 is arranged, the device 32 seals between the outlet channel 30 and the Austrittslei. Opposite the recess 46 of the housing is at the periphery of a second, similar to the recess 46 from recess 52 is formed. Inside the bolt 44 , a return check valve 54 is arranged, which temporarily closes the outlet line 32 as an outlet valve. The available space is thus optimally used.

In order to move the housing 12 from the operating position to the idle position, the bolt 44 is briefly pulled out of the recess 46 against the spring 50 . This can be done pneumatically, hydraulically or electromagnetically. The Ge housing 12 is then freely rotatable about the bushings 18 . It is in consequence of the friction between the rotor slides 28 and the ring wall 13 carried by the rotor 14 . It rotates be referred to Fig. 3 counterclockwise, while the bolt 44 rests by spring force on the circumference of the housing 12 and slides along it.

After rotating the housing 12 through 180 °, the bolt 44 engages in the second recess 52 . In this position, the housing 12 and the ring wall 13 are in the idle state and remain there until the bolt 44 is withdrawn again.

The bolt 44 can be ausgebil det together with actuators such that it is automatically retracted when a mi nimale or a maximum pressure threshold is reached. In this way, the delivery rate of the rotary vane compressor can be controlled automatically.

In Figs. 5, 6 and 7, a third embodiment is shown a rotary vane compressor. The housing 12 is partially surrounded by an outer housing 52 in which the supports 34 are integrated. On the outside of the side wall 17 , a rotary vane motor 56 is arranged, which is shown in particular in FIG. 6. The rotary vane motor 56 comprises a rotary vane 58 which is connected to the housing 12 and can be reversibly rotated 180 ° in a segment of an annular channel 60 . The rotary wing 58 has labyrinth seals 59 on the circumference and on the end faces and is supported in its end positions on damper disks 61 . The ring channel 60 is sealed by a seal 54 on the circumference of the side wall 17 between the housing 12 and the outer housing 52 .

In this embodiment, the outlet opening 29 leads into an outlet duct 30 which leads through the side wall 15 of the housing 12 . There, a flexible outlet line 32 is connected by means of a rotary joint 64 (swivel screw connection), which enables it to follow the 180 ° rotation of the housing 12 without kinks.

If no compressed air acts on the rotary wing 58 , this is ge infol ge the friction of the rotor slide 28 or by a spring (not shown) in the position shown in Fig. 6 ge. The housing 12 and the annular wall 13 are then in the operating position Be. If the engine is idling when the engine is switched off, the rotary vane compressor is automatically set to the operating position after a short time, thus ensuring that the compressed air tank is refilled in any case. With an empty compressed air tank, for example after a long standstill phase of a truck, the rotary vane compressor is started from the operating position.

Comes with compressed air on the rotary wing 58 , this performs a rotation of 180 ° from the operating position and moves the housing 12 and the annular wall 13 into the idle state.

In Figs. 5, 6 and 7, a third embodiment is shown a rotary vane compressor. The housing 12 is partially surrounded by an outer housing 52 in which the supports 34 are integrated. On the outside of the side wall 17 , a rotary vane motor 56 is arranged, which is shown in particular in FIG. 6. The rotary vane motor 56 comprises a rotary vane 58 which is connected to the housing 12 and can be reversibly rotated 180 ° in a segment of an annular channel 60 . The rotary wing 58 has labyrinth seals 59 on the circumference and on the end faces and is supported in its end positions on damper disks 61 . The ring channel 60 is sealed by a seal 54 on the circumference of the side wall 17 between the housing 12 and the outer housing 52 .

In this embodiment, the outlet opening 29 leads into an outlet duct 30 which is guided through the side wall 15 of the housing 12 . There, a flexible outlet line 32 is connected by means of a rotary connection 64 (swivel screw connection), which enables it to follow the 180 ° rotation of the housing 12 without kinks.

If no compressed air acts on the rotary wing 58 , this is ge infol ge the friction of the rotor slide 28 or by a spring (not shown) in the position shown in Fig. 6 ge. The housing 12 and the annular wall 13 are then in the operating position Be. If the engine is idling when the engine is switched off, the rotary vane compressor is automatically set to the operating position after a short time, thus ensuring that the compressed air tank is refilled in any case. Thus, when the compressed air tank is empty, for example after a long standstill phase of a truck, the rotary slide compressor is started from the operating position.

Comes with compressed air on the rotary wing 58 , this performs a rotation of 180 ° from the operating position and moves the housing 12 and the annular wall 13 into the idle state.

In FIGS. 8 and 9, a fourth embodiment of a rotary vane compressor 10 is shown. The rotor shaft 16 is rotatably supported in an outer housing 70 in needle bearings 68 . On the inside of the outer housing 70 , needle bearings 66 are arranged on the rotor shaft 16 next to the needle bearings 68 , on which the housing 12 is rotatably mounted. The housing 12 and the ring wall 13 are thus rotatable about the rotor axis 24 . In the outer housing 70 , an annular channel 71 is formed on the side wall opposite the friction clutch 72 , which is sealed by means of two seals 73 on the side wall 17 . In the. Annular channel 71 axially opens outlet channel 30 . Radially, the outlet line 32 opens into the annular channel 71 , which thus connects the compression chamber 26 with the outlet line 32 in each win cell position of the housing 12 .

In the outer housing 70 , a clutch designed here as a friction clutch 72 is formed, which has spring-loaded pistons and engages on the outside of the side wall 15 . With this Reibkupp development 72 , the housing 12 and the annular wall 13 can be fixed to the outer casing 70 . The rotary vane compressor is then in the operating position shown. If the Ge housing 12 by the friction clutch 72 z. B. released by means of compressed air to the piston, it rotates as a result of the friction between the rotor slides 28 and the annular wall 13 with the rotor 14 . The medium is not compressed between the rotor 14 and the rotating housing 12 . The rotary slide compressor is in the idle state.

The advantage of this embodiment compared to z. B. one external disengageable shaft coupling is that at Stopping the rotary vane compressor white the drive shaft terlaufen and thus a tandem drive z. B. for a hydraulic system pump is enabled.

In Fig. 10, a fifth embodiment of a rotary vane compressor is shown. The rotor shaft 16 is rotatably mounted in an outer housing 74 with needle bearings 72 and 79 . In the outer housing 74 , the housing 12 is axially displaceable and rotatably guided by a key 75 in a groove 77 . The side wall 15 is through the outer housing 74 , the ring wall 13 and the side wall 17 are formed by the housing 12 . The housing 12 protrudes with a first end face in a first circumferential groove 78 in the outer housing 74 and opposite with the second end face in a second circumferential groove 80 . The housing 12 is at its end areas on the inner and outer circumference in the circumferential grooves 78 and 80 sealed by seals 76 . Springs 81 are arranged in the second circumferential groove, which bias the housing 12 into the first circumferential groove 78 . A line 82 is connected to the outer housing 74 and leads to the first circumferential groove 78 .

The rotary vane compressor is shown in Fig. 10 in the operating position. In order to put the rotary vane compressor in an idle state, compressed air can be passed through line 82 to the end face of housing 12 . The housing 12 is thereby axially displaced against the springs 81 and the side wall 17 moves away from the rotor 14 . An annular gap is formed between the rotor 14 and the side wall 17 , through which a pressure equalization takes place between the chambers. The rotary vane compressor then does not generate any compression and delivery capacity.

It is also possible to provide the annular wall 13 of the housing 12 in the region of the circumferential groove 78 with an annular groove which, during the axial displacement of the housing 12, enters the region of the rotor 14 and through which pressure compensation between the chambers can then also take place .

FIG. 11 illustrates a preferred further development of the annular wall 13 according to the first, third, fourth and fifth execution form represents.

While in conventional rotary vane compressors the annular wall is circular in cross-section, the annular wall 13 'shown in FIG. 11 is composed of individual circular segments A, B, C and D which are each designed with different radii.

The circular segment A represents the compaction section and the actual working area. It extends from the point of a maximum sickle height H _m to an outlet control edge 88 (start of outlet) and a sickle height H _A present there, comprises an angle of 180 ° and has a radius R ₁ . The ring wall axis 20 'of the ring wall 13 ' runs through the center of this semicircle with radius R ₁ .

The circular segment B represents the transition from the compression section to the sealing section C and is formed by a radius R ₂ . The outlet opening 29 extends over this distance.

The circular segment C forms the seal between the pressure side and the suction side, extends over approximately 30 ° and is designed with a radius R ₃ . The radius R ₃ is larger than the radius R by the radial play of the rotor 14 (0.02 to 0.05 mm).

The circular segment D represents the transition from the sealing section to the compression section and is formed by the radius R ₄ . Over this area, the inlet opening 27 extends with egg ner inlet control edge 86 .

The centers of all of the radii R ₁ , R ₂ , R ₃ and R ₄ outgoing circle segments lie on the connecting line between the location of the maximum sickle height H _M and the Auslaßsteuerkan te 88 (start of exhaust).

The liver pass from radius R ₂ to radius R ₃ and from radius R ₃ to radius R ₄ is in each case formed by a short straight line.

The advantages of this ring wall geometry are that the compression distance is extended and, compared to known rotary vane compressors, has more chambers involved in the compression. The differential pressures between the chambers are therefore smaller in each case. Furthermore, the cross-sectional height H _{A is} increased from the laßsteuerkante 88 and thus pressure and temperature peaks are avoided. The throttling effect on the sealing section is increased by a longer and constantly narrow gap and thus overflow losses are reduced.

The number of rotor slides depends on the pressure ratio (final pressure to suction pressure). The greater this pressure ratio, the greater the number of rotor slides. Furthermore, the inlet control edge 86 shifts in the direction of rotation with increasing pressure ratio.

Claims (20)

1. Rotary vane compressor or vacuum pump ( 10 ) with an annular wall ( 13 ; 13 ') and a pair of side walls ( 15 , 17 ) enclosing a compression or evacuation chamber ( 26 ) which is sickle-shaped in cross section, the annular wall ( 13 ; 13 ') has a ring wall axis ( 20 ; 20 '), and with a rotor ( 14 ) which extends in the compression chamber ( 26 ) and limits it to the inside, the compression chamber ( 26 ) dividing rotor slide ( 28 ) and one Has rotor axis ( 24 ) which is parallel to the ring wall axis ( 20 ; 20 '), the ring wall axis ( 20 , 20 ') and the rotor axis ( 24 ) being arranged eccentrically with respect to one another at least in an operating position, characterized in that at least the ring wall ( 13 ; 13 ') can be moved from the operating position into an idle state. 2. Rotary vane compressor according to claim 1, characterized in that at least the ring wall ( 13 ; 13 ') in the direction of a to the rotor axis ( 24 ) concentric position of the ring wall axis ( 20 ; 20 ') is adjustable. 3. Rotary vane compressor according to claim 2, characterized in that at least the ring wall ( 13 ; 13 ') on at least one fixed and non-rotatable bushing ( 18 ) and the rotor ( 14 ) in the bushing ( 18 ) is rotatably mounted, the bushing axis ( 22 ) is arranged parallel and eccentrically to the Ringwandach se ( 20 ; 20 ') and eccentrically to the rotor axis ( 24 ). 4. Rotary vane compressor according to claim 3, characterized in that the sleeve axis ( 22 ) in the operating position Be in the central plane, preferably in the center between rule's rotor axis ( 24 ) and the ring wall axis ( 20 ; 20 '). 5. Rotary vane compressor according to claim 4, characterized in that the ring wall ( 13 ) between the operating position Be and the idle state can be rotated by 180 ° continuously. 6. Rotary vane compressor according to one of claims 3 to 5, characterized in that the annular wall ( 13 ) is locked in the operating position and in the idle state with the socket ( 18 ) and can be unlocked for switching, so that they result in friction between the infol ge Rotates rotor slides ( 28 ) and the ring wall ( 13 ) from the operating position to the idle state or from the idle state to the operating position. 7. Rotary vane compressor according to claim 4, characterized in that the annular wall ( 13 ; 13 ') between the operating position and the idle state can be rotated by 180 ° in each case. 8. Rotary vane compressor according to one of claims 2 to 4 and 7, characterized in that the ring wall ( 13 ) is rotatable by a worm drive ( 38 ). 9. Rotary vane compressor according to one of claims 2 to 4 and 7, characterized in that the ring wall ( 13 ) by a rotary vane motor ( 56 ) is rotatable. 10. Rotary vane compressor according to claim 1, characterized in that at least the ring wall ( 13 ; 13 ') in the idle state with the rotor ( 14 ) is freely rotatable. 11. Rotary vane compressor according to claim 10, characterized in that the annular wall ( 13 ; 13 ') rotatably mounted about the ro tor axis ( 24 ), in particular through the side walls ( 15 , 17 ) on a shaft ( 16 ) of the rotor ( 14 ) is supported. 12. Rotary vane compressor according to claim 10 or 11, characterized in that at least the ring wall ( 13 ; 13 ') is held in the operating position by means of a clutch ( 72 ). 13. Rotary vane compressor according to one of claims 10 to 12, characterized in that on the outside of a side wall ( 17 ) an annular channel ( 71 ) is formed which is connected to the compression chamber ( 26 ) and an outlet line ( 32 ). 14. Rotary vane compressor according to claim 1, characterized in that at least the ring wall ( 13 ; 13 ') is axially displaceable. 15. Vane compressor according to claim 14, characterized in that with the annular wall ( 13 ; 13 ') a side wall ( 17 ) is axially displaceable. 16. Rotary vane compressor according to one of the preceding claims, characterized in that the displacement of the annular wall ( 13 ; 13 ') is controlled by means of the overpressure or vacuum generated by the rotary vane compressor or the rotary vane vacuum pump. 17. Rotary vane compressor according to claim 1 to 4 and 7 to 16, characterized in that the annular wall ( 13 ') from several circular segments (A, B, C, D) each of different radii (R ₁ , R ₂ , R ₃ , R ₄ ) is formed. 18. Rotary vane compressor according to claim 17, characterized in that a semicircle is formed with a first radius (R ₁ ) through the center of which the annular wall axis ( 20 ') extends. 19. Rotary vane compressor according to claim 18, characterized in that a second radius (R ₃ ) in egg nem in the direction of rotation of the rotor ( 14 ) behind an outlet channel ( 29 ) lying circle segment (C) extends over an angle of approximately 30 ° and only is a radial clearance greater than the Ra dius (R) of the rotor ( 14 ). 20. Rotary vane compressor according to one of claims 17 to 19, characterized in that the centers, from which the Ra dien (R ₁ , R ₂ , R ₃ , R ₄ ) start, on a connecting line between rule's point of maximum sickle height H _M and from an outlet control edge ( 88 ).