DE1401399A1 - High pressure rotary wing machine with a pressure compensation device - Google Patents

Description

Mochdruckfählge rotary vane machine with a pressure equalization device "The subject of the main patent is a high-pressure drobflügelmasohine with an equalization device, which consists of one or more equal scales formed by cylinders and pistons as pressure members * These have the following task in particular as a result of the working medium in the working chambers Axial pressure exerted on the rotor side wall and the resulting elongation of the tension members holding the rotor parts together (such as rotor bushing bolts or the like), the play between the rotor side walls and the capillary ring, which closes the working chambers radially near the outside, is increased and the leakage increases The equalization chambers counteract this increase in clearance by their pressure members exerting a counter pressure on the rotor side walls so that the material expansions caused by the axial pressures mi At least partially compensated for an inadmissibly large play between the moving parts and thus an unreasonable pressure and performance failure, -sver # 4; lust is thus prevented, -Here, however, there is the disadvantage that the high pressure pressure medium overflowing into the compensation chambers penetrates more or less into the joints between the individual parts of the rotor, in particular into the gap between an inner and an outer rotor side wall I can. This penetrating into the Spaltfuge Henge of Druckmittelo and their spread and impact load sind.kaum predictable and varies depending on material and manufacturing precision of Oeilog axi ---! Ile tension, viscosity of DruckmittelB etc.- It is therefore not readily guarantee the given that compensation actually takes place to the extent intended. In particular, it was also not possible to load the spar bolts or other tension members that held the rotor together in the axial direction against the pressure of the work equipment) up to the otherwise permissible load limit. The bolts had rather Uberdiniensioniert but werdent vias to Drehflägelmaschinen, -vielche for maximum performance determined sindv unsustainable ISTG because the carrying capacity of the bolts until just before the normally permissible load limit should be exploited.

The invention aims above all to remedy these disadvantages and consists to a significant extent in the fact that in the gap joints that connect to the equalizing chambers charged by the pressure medium of the equalizing device or to their inlets or outlets. One or more low pressure relief fields are switched on.This makes it possible to essentially limit the pressure fields of the equalization chambers to the expansion of the chambers while avoiding larger zones of indefinite pressure between the high pressure and low pressure zones and to clearly control the loads in the axial direction , The relief fields can be under external pressure in the simplest possible way. If necessary, special sealing elements can be provided between the pressure folders and the relief fields, even if they are not absolutely necessary , which are larger in the pressure part of the machine than in the suction part of the Vi machine and consequently generate a tilting moment that tries to tilt the rotor side walls.

These phenomena are particularly important for high-pressure machines. The axial load fluctuations that arise from the eccentric arrangement of the capsule rings and the resulting periodic change in volume of the chambers were relatively insignificant and negligible in the range of the previously usual medium and low pressures around and below 100 atmospheres. However, if the pressures rise beyond this, for example to several 100 atmospheres, the axial load fluctuations can only be controlled by four. In particular, the tension members holding the rotor together such as bolts or Additional tensioned and relaxed for an hour, possibly up to several 10,000 times per minute. This results in signs of fatigue in the tensioning material, which limit the service life # if the tendons are not significantly oversized. As above. However, such overdimensioning is not acceptable in the interests of maximum machine performance. It is therefore necessary to relieve the tendons in this respect too, apart from the fact that the inequality of the axial pressures also affects the smoothness of the rotors. the latter can be civil u * U. be improved by providing two or more pressure and suction fields per revolution. but at the same time the frequency in the periodic fluctuations of the social pressures is increased accordingly.

Accordingly, the invention aims to compensate for axial pressures that are unevenly or periodically changing with respect to the rotor over the circumference of the machine, in whole or in part same or in Same cycle as those of the working chambers, however, change in the opposite direction to these> in such a way that when a working chamber is enlarged, a compensation chamber, which is preferably approximately in the same radial direction as this one, for pressure equalization of the axial forces generated in the working chamber, is not reduced in size and, conversely, preferably such a countermeasure Change of working chambers and the respectively associated compensation chambers provided - that the sum of their cross-sections effective for the axial forces is constant or approximately constant during a rotor revolution, and that furthermore, based on any diametrical plane laid by the rotor axis, the sum of the working medium in the working chambers and the axial forces exerted by the medium in the compensation chambers on both sides of said diametrical plane gMeh or approximately equal.

The chambers are preferably also reduced in such a way that the cross sections of the compensation chambers that are effective for the axial forces increase or decrease alternately with the rotor rotation between zero or approximately zero and an approximately largest axially effective cross section of the working chambers. With the invention, the periodic loading at least partially Changes to the tension members / avoidance. At the same time came possibly the smoothness of the machine and the Reliability in the sealing of the moving towards each other. all parts improved vierden.

The number of compensation chambers can correspond to that of the working chambers. In this case, each compensation chamber is expediently connected in a communicating manner to that working chamber with which it lies approximately in the same radial direction to the rotor axis. However can auchq compared with the number of Arbeitskammerng a larger or smaller number of balancing chambers iverden arranged. Multiple names can also be used.

Systems of #, equalization chambers can be combined with one rotary vane machine each.

According to a further feature of the invention, hydrodynamic balancing wedge fields in the form of recesses supplied with a Madium are provided between the capsule ring and one or both rotor side walls, which preferably extend downward in the circumferential direction and project in one and / or the other direction be distributed over the whole range. Since the capsule ring, although rotating at the same speed as the rotor, due to its eccentricity to the rotor axis, halative movements to this a.usf-Uhrtg arise as a result of the wedge effect, hydrodynamic pressure fields that counteract a decentering of the capsule ring and try to push it back into the central position.

The balancing wedge fields can preferably be completely or partially surrounded by grooves, which are connected to low pressure fields and delimit the pressure fields close to the outside. Further details and advantages of the invention can be found in the following description of exemplary embodiments. 1 shows an axial section through a rotary vane machine with balancing fields and additional low pressure fields, namely in section along line 1-1 of FIG. 29, FIG. 2 a section along line 2-2 of FIG. 19, FIG. 3 an axial section through another Execution of the machine with equalization. kammerng the volume of which alternately increases with the Uklauf the machine and verkleinertg Fig. 4 a section along line 44 of Fig. 39 Fig. 5 is a section along line 5-5 of 7IG. 39 Fig. 6 a section along line 6.6 of the pia * 3 = d Fig. 7 is a view of the capsule ring in j? Hawks direction 7 of Fig. 6, In AusfUhrungebeispiel according to Fig. 1 and 2 are a circumferential tubular shaft 10, which in mounted in a manner not shown on a stationary cylindrical bearing and star body, the rotor 11 with the axially inner rotor side walls 12 and 13 and the axially outer rotor side walls 14 and 15 pushed on. The wings 16e, one of which is indicated by dashed lines in Fig. 1 , are mounted in slots of the hotors 11 and preferably extended into the inner side wall 12 or 13 , in which they are guided in a known manner in radial slots 17 (Fig. 2) 1 " each which lie in a plunge with the radial slots in the rotor 11. In the embodiment it is assumed that five blades are distributed over the circumference.

Eccentric to the rotor 11 is the capsule ring 18 which is supported in a manner not shown on its outer circumference on a housing that runs together with it, a so-called rotary carrier ring or, with the intermediate maintenance of suitable roller bearings, on a stationary housing and can rotate in it. The rotor 119, the axially inner rotor side walls 12 and 13, as well as the wings 17 and the capsule ring 18 , the working camps 19 are limited, which with each revolution of the rotor 11 from a smallest volume to a largest volume and then decrease again to the smallest volume . According to the main patent, the rotor side edges 12 and 13 lie tightly against the end faces of the rotor 11 , while they have a small amount of running play relative to the capsule ring 18. The axially outer Rotoreeitenwände 14 and 15 are formed haubenförrii g, by using axially directed ring walls 20 and 21, the axially inner Itotorseitenwände 12, 13 complete radially a0, s and viie at their free end faces approximately with gle-iChem game, the inner Side 12 and 13 rest on the capsule ring 18.

The rotor unit formed by the R, gate 11 9, the inner oe -. 'Te-nvir - #. Nde 12 and 13 and the outer side walls 14 and 15 is held by the end disks 22 and 23 , of which the end disk 23 L is firmly connected to the door shaft 10 or forms a piece with it, while the double disk 22 is pushed onto the rotor shaft and is held axially, for example, by a snap ring 24, in such a way that the end disk 221 and 221 are closed the axially outer rotori # eitenivand 14 there is an axial play.

Ents . According to the main patent, there are formed between the axially outer rotor side and the end disk 22 out of 217, namely by the fact that the rotor side wall 14 has several cylindrical recesses 26 distributed over the circumference "in each of which All pistons are engaged by the cylindrical projection 27 of the end plate 22. In this case, the cylindrical walls of the Lusgleichkammer 25 are sealed by sealing rings 28.

If necessary, instead of several ring-shaped compensation chambers 25 formed by individual cylinders 26 and pistons 27 , a single ring-shaped compensation chamber which is centered on the rotation axis can be provided, which is formed by 'an annular' recess (26) and an annular piston (27) the balance chambers 25 receive their pressure medium, for example, by individual bores 30) which is formed with an annular space 31 at the radial periphery of the axially inner Rotorseiteriviand 12 between it and the axial annular wall 20 of the outer rotor side wall * the annular space 31 can-with the slots 17 in the Rotoraeitenwand 12 are in communication o independently tone these are supplied with pressure medium. A, the ring chamber 31 corresponding further annular chamber 32 eats on the axially opposite side between the inner Rotorseitenwaüd 13 and the axially projecting annular wall 21 of the outer ILotorseitenivand 15 vorg6sehen. chamber 32 here with the chamber 31 are in communicating connection and as well as this one Mrackoyat «« belong to # welohen a « Draekaus- equal to the Rotorteitenteilt b "t is for 71U4al and e.g. via the rotor shaft 10 4: is esterified * The third coat in the equal chambers 25 presses the axially outer Reterzeiteawand 14 against the inner side wall 12 and thus the warning from the leeil-ex 149 12 # 11 ' 13 and 15 existing retor unit against the l "aoheibe 23, o On the other hand, Badacheibt is 22 « snap ring 24 m2 also on the rotor shaft 10 The effect in the Chamber of Labor 19 in the social direction Pressure is thus the bridge in the Ausgleiehekanaern 25 and thus # prevents the game * like the individual toilets of the rotor as well as bendere between the Reter wide walls 129 13 »d den Kapaelring 18, is pre-enlarged * In order to prevent # that the equalization chambers 25 or from the input camarx 31 # 32 into the gap joints 33 or * 34 between the axially inner tmd the exial outer Retor sidewall penetrating Xedium suoätzliohe pressure Telder products are inventive ii, Porja from extensions 35 and 36 proceeded in ' the amial inner Rotereeiteewände 12 and 13 in Unfangi @. direction each between the ßehlitsen 16 for the ] 'lU «l 17 e #, # »4 * working, tet an tmt # wii au zigs 2 emerges to / in sector or white aÄreisekt-shaped #entalt habex. Every bat. Load field 35 stands above bores 379 . Tree 38 and holes 39t each Entlaotausa field 36 via holes 40 and 41 in connection with the outer pen. If necessary , die rings 42 can be inserted into grooves 43, which do not disregard the deslanting areas 35 and 36, respectively. In yig. 1 is a Butlantunisteld 35 is shown with Diohtrin "43 on the left side, while dan Entlanta ngs field 36 worked on the right side of the Pig.1 without Diebtring Entlantungefolder result of this can, for example, the pressure aua de x tree 31 at most only slightly in the Spaltfuge $ 33 spread out as a result of the Entlastaffltelder 35 (or 36), a steep Draokabfall occurs within the Trenntuge the Steutrumg the Arbeitakammern int in Fig. 1 in Ausführungebeispiel in individual not shown, It is carried out, for example via channels 449 in a suitable manner from the nioht This central control body is in a suitable wine * depending on the rotation of the rotors controlled ww * rdeite In the embodiment according to Pigi> 3 to 7 , the rotor is on the rotor shaft 110, which can be stored in the same way as the rotor shaft 10 of the first embodiment 111 mounted with the rotor side disks 1129 1139 114 and 115. The blades 116 (Pig, 4) are mounted in the slots 117 of the rotor 111 so as to be radially movable and can again engage in corresponding slots in the rotor side walls 112 and 113 . The wings run on the capsule ring 118 # where lll.'dem between the rotor capsule ring 118, the side walls 112 and 113 and the wings 116, the working chambers are formed 119, of which in the illustrated Ausführungebeispiel corresponding to the number of the wings total of six chambers 119a bio 119f (Fig. 4) provided and which increase according to the eccentricity of the capsule ring 118 to the rotor 111 with each revolution of the rotor once from about zero to a maximum and then decrease again from this maximum to about zero.

As in the first embodiment, compensation chambers 125 are also provided in this case, which are formed between the axially outer rotor agite disk 114 and the end disk 122. Through the end disk 1229, which is worn on the rotor shaft 110 by means of a pressure ring 124, and the axially opposite end eecheibo 123 , the rotor parts were held together in the previously planed manner and kept axially under pressure by the working medium in the working chambers 119 or by the counteracting pressure medium in the compensation chambers 125 As in the first exemplary embodiment, you can also in this 7 all relief chambers. or two fields 135 and 136 may be provided. The capsule ring 118 supports eiLoh-also in wines known to eich # by means of a Outer surface 145 against a paint application ring 146 from # which together with the Roterwelle and the However, individual rotor parts are eccentric to these (decrowing 746 4) revolves. The working chambers 119 are connected via the channels 144 in Roto: # 111 in not shown in detail Cry-so controlled # that each over half a Turn in the working chambers 119 lower Draek and high pressure during the other half turn - Does % .Z * work in the execution example shown * kauchine ale pump or Gebline, so would be in'Pfeilriaht = ga Uig-4) in the event of a threat to the left of the pis. 4 that to be promoted or to be condensed. * Naditux now resides in the chambers 119a, b and o are under-Annaugdruok and on top NaOH exceeding the highest position (or, depending natli regulation m * 2 # or closer) in the Kammera 119d9 9 and f put under pressure or demanded will. The closed-in redium would result. 4eseen in the right working chambers 119d9 a uM f a high axial pressure »in the left working chamber 119a # b and o, on the other hand, have a ', slight axial pressure (possibly also zero or a negative pressure) e. With each revolution of the rotor, each point would initially lower an area around its circumference . hieraut an area high Azialdruckes durchlaufeng so that the di # Üotorteile cohesive Blementeg in Ausführungsbeiepiel so the rotor shaft 110t possibly also clamping bolt od.dS1d4 which the rotor parts axially durchsetzeng according to the Umdrehungezahl deo # rotor would be periodic Belastungsschwankungen.unterworfen.% looks To compensate for these Sehivankungen the Erfindm4 now f he following Sinrichtgng before # corresponding to the number of Plügel 116 are A »-gleichekammern periodically varying size over the circumference of the rotors Yerteilti the chambers (such as" six) are formed by Auenehmungen 149 in the axially outer Rotoreeitenwand 114th Serving recesses each have a radially directed channel-shaped Toll 150r senen inner space part 151 and an outer Raxmteil 152 on the actual. The equalizing chamber is formed while the inner space part is connected to the shaft via bores 10'5, 153a (7ig * 3). In the canal part 150 , a slide valve 154 is slidably mounted in the radial direction. He weistt-As inebezondere 2ige 5 zeigtr an in 'circumference direction of the rotors verlautend # aohlitaf özmige opening 155 move to Y in which a block 156 loading in the circumferential direction is mounted movably * The Gleitetein 156-by a connecting pin 157, the through slots 158 (74 , 3) Hindu leads in the rotor side walls 114 and 112 are connected to the capoel ring 118tteat * Seals 159 and 160 can prevent the equilibrium 152 against the pugea on slide valve 154 as well as against the parting line between the axially outer rotor side wall 114 and the Badocheibe 122 seal. The axial length of the adjusting chambers 152 is only a fraction of the amial length of the working chambers 1199 no dala auoh bd the same cross section in a radial plane, the adjusting chambers have a smaller volume than the working chambers babea and auah 'when there is a correlating connection between aungleiobs and working chambers, the working wines of the latter is virtually unaffected by dit Augleiehekammeza * 'the Wirkungaweiee the periediseh changing compensations chambers 152 is at best from Pig * 5 can be seen * How do already erlämtertg in the in? eat. 4 and 5 shown rotary position of the machine in one direction of rotation of the rotor in the direction of the arrow &'the working chambers 119a1 b and o in terms of volume. Since the sliding slides 154 move by means of the connecting bolts 157 and the sliding legs 156 in the radial direction with the capillary ring 118 capped and fixedly, the sliding slides 154 adjacent to the working chambers 119a to o, according to the eccentricity of the capsular ringon during this movement radially outward Their limited compensation chambers 152ag b and o on the left half of the pig. 5, while the lower chamber 152a about their maximum Volaen has # is the volume of the upper chamber 152a virtually reduced to zero Conversely, larger on the rechtea half of the Pig, 5, the Aungleiohnkammera 152d, 9, and: t from a Voiumen. the almost zero intg back to their maximum volumeg while the working chambers 119d # e and t close to them decrease from their maxt »to zero or mhezu zero.

If necessary, the arrangement can be made so that in each case the sum of the socially effective transverse center of a compensation chamber 152 (e.g. 152a) and a working chamber 119 (e.g. 119a) attached to it would be constant or close to the rotors of the rotor Ausgleiahakammern by eutsproehende conjunction with them, each supplied superior Arbeitakammern equal pressure, so is the sum of IL% ialdrUckt which wirdp exerted by the medium in both chambers axially outward corresponding to the constant axial effective cross-sectional konstantt so long s the pressure of the medium constant is # So each within the suction or pressure area. Another possibility of pressure equalization is # that the equalization chambers 152 are each connected to an approximately diametrically opposite working chamber @ Longitudinal plane on both sides-the same or approximately the same size and Ax ialdruokdifferenzeng which cause overturning moments on the rotor # have been practically completely or largely excluded. For example, the lower left equalization. Chamber 152a with the working chamber 119d located at the top right, and also the working chamber 119a located at the bottom left with the compensation chamber 152d located at the top right 152d, on the other hand, the same size * tilting moments_ # voloht looking for the Rotoe to tilt a cross bar * IL Wei «, ehend therefore / .ßrrer, avoided no matter which Druok in the Chambers or at which point in the circumference the relevant working and balancing chambers are located.

Of course, the equalization chambers do not need to be directly connected to the working chambers assigned to them. Similar to the working chambers, they can be periodically connected to the suction or pressure system of the rotor in a suitable manner # oo that the previously operated pressure ratios result * Under certain circumstances Sufficient to auohp if * the unequal chambers are constantly connected to the pressure zone of the mas.chinev because in this area too the fluctuations in the axial loads are not only reduced during movement through the draokzone area axially effective cross-section of the respectively assigned working chambers held g ao that the - axial pressure in the Auagleiehakammern lies between the azialex pressure # which the working medium, in the state of a low pressure on the one hand and a high pressure on the other hand in the axial direction on the rotor A different perfect balance of the axial forces can be achieved especially if the pegs with iodine **. Been durohlaufen Rotorum'.auf two or more SaugzolLen and two or more Draokzonen and accordingly periodically Aungleicheka 'em provided with pressurized fluid' * The further it is possible "in a second non gdzeichneten Ausgleichskammereyaterg which with respect to the compensation chambers 152 on the same or is arranged on the opposite axial side of the working chambers or the Kapoelringsg to achieve an opposite axial pressure compensation by corresponding connection of the chambers to each other b-two through appropriate control elements, the chambers of the second systems with suction pressure # if the assigned to them (e.g. about the same radial . Ausgleichskammem lying position) or the Arbeitakammern-1 system are under pressure and vice versa, also in this way, an extremely broad Ausachaltung the axial Belastungsa chwankungen can be achieved.

In the embodiment example described above, as from the Plg. 39, 6 and 7, in the lateral end faces the capsule rings 118 indentations are incorporated into pom-vonruten 161, which see in the circumferential direction of the capillary rings and in both circumferences close to their ends, forming the wedge spaces 162 and 16 the same taper in a wedge shape. They may be available through Querbohruhgen 163 in conjunction * Zweekmäßig are also in small distance from the cusped rooms 162 and 16? AQuernittelL 164 and 165 the z.Be vorgeaeheng communicate with the outside air * If appropriate, instead of the transverse grooves 1649 165 or preferably in addition to these ra & dial inside or radially further outside the wedge-shaped grooves 161 with-the viorgesehen 167 aeing as di @ Bm in Fig, indicated etrichpunktiert * the wedge-shaped grooves described outside air or another low pressure in Related grooves 166 and 161 can be used in greater numbers on the periphery of the rotor ferteilt wine, wherein the number of grooves that of Arbeitskammert or * correspond Auagleichekammern or may also be different from the number of these chamber * * the Wirkungeweine the wedge-shaped grooves 1619 which takes in the capsule ring also ans or partly ** can be arranged in the rotor side walls and which are marked with e In a Utdimg aB a work or assistance medium, for example a Diohl or Sohmiermittelg has been supplied with the following # During the rotation of the capsule rings 118 revolving with the rotor, the latter constantly moves relative to the rotor side walls 112, 114 or 1139 115 ax, the movement is in this case the rotation of the Rotorseitenwändo partially, leading partially retarded, further superimpose sth gege "eitigoWird part weep radially outwards and partially radially directed einwärte, all serve four movements now e Viedium (in a not shown Weiseg for example, a sealant or Sohmiermittel) in the Grooves or other openings, as a result of the relative movement between the capsule ring and the rotor side walls in the direction of the relative movement, the medium penetrates into the wedge-shaped trees 162 or 162a and thereby creates a hydrodynamic pressure field at an acute angle to each other standing surfaces exert pressure

The same occurs among other things, on the diametrically opposite side of the capsule ring respectively, of the side wall concerned when ilun of £ "#. 'To a side wall apselring for example due to eccentricities more passes than the other # is the Medlumskeil in the wedge-shaped space 162, 162a concentrated, thereby increasing the hy-drodynadbahe pressure force * same time, the Druak increasing the distance of the wedge surfaces bounding Teiie exmässigt in diametrically opposite thrust key field result. in a decentering of the capsule ring so .161 centering hydrodynainische Druckkräft & batten on the hydrodynamic wedge surfaces counteract the decentering of the capsule ring and push e back into the central position. At high relative speeds, the hydrodynamic centering forces become very strong and can exceed the frictional forces in the suspension of the capsule rings many times over, so that the capsule ring floats is guaranteed between the hydrodynamic centering fields. These processes take place in a verry narrow azialen Abetandetoleranz of generally only a few Nundertetel mm this Balanoierungekeilfelder causing keyways or other wedge-shaped recesses may also extend over the ggazenUmfang of 360 under an acute angle to Seitenfläohe the capsule ring or the Rotoraeitenwalad * The radial and / or in the circumferential calibration Tung extending Niederdrucknuten 164t 165 and 166p 167 allow # precise dimensioning of the hydrodynazieehea Draokkeil- or Zentrierungefelder to erzieleng particular danng when the Intlastungsnutex with Wiederdruokräumen or * are connected to the outside air * it is dadurchirerhindertg that check the hydrodynamic Draokkeilfelder ungleichmäßt # able to propagate far into the opalt between capsule ring and red side walls,

Claims (1)

ü Drahflüßelma00hin & with a Druckausleiohnirorrichtungt consisting of one or more Augleiohnkammerag whose Draokfolder counteract the axial pressures exerted by the working medium in the working chambers on the -otor side walls # in particular in such a way that the pressure elements forming the compensation chambers (e.g. cylinder and piston) are threatened with a pressure medium - z * B * middle tension members such as clamping bolts of a rotor bushing od.dglo - the rotor side walls press against the red and inebesundere -according to patent (B 19 130 Ia / 14b) p characterized @ that in the gap joints (33p34), which are attached to the pressure means the Ausgleichsvorriohtung beaufachlagte Aungleichekamer or -kamern (25) or to the same beliefernd @ Druckmittelsyatem anechliegeng for preventing a Auebreitenn the or Druakfolder the Ausgleiohakammern aanehlien- # end to the beaufachlagten of pressure medium Kumern or channels, one or more Bntlae "tuugafelder (359 36) low pressures n switched on 2.) rotary wing Kanehine according to claim 1.dadu'roh kon- seio "etldaß with subdivision of the rotor sidewall in one-axial interior of it. Side wall facing the rotor . (12,13) and an axially outer side wall (14,15) tvobei the separating joint (33v34) was close to the two side bulges on the printed medium, m.ß, on the outer circumference% .er Sidewall connected int, one or more ent- Lastungenkammerags, e.g. in the form of depressions (35,36) are arranged in one of the two side walls and lower via channels (37,38939; 40941) with rooms Druokee, e.g. the Aunsenatmoophäre are connected. 3.) according to claim 2.-daduroh gekonnzeieh- aetvdag the axially inner SeitenabKben (12913) for Leading the wing on radial lead wire (17) and the Entlaatungotelder (35.36) on the circumference of the side aoheiben arranged distributed between the slots (17) and 4.) rotary vane machine according to claim 1 bb 3, dadureh ge Konnzeiohnetud that the 2nUaatunefelder 35936 given the Druokteldern der Auagleiohverrioktxndg in the separating joints through beoonderegdie Entlaatungefolder aBziag- Förnig unachligeaendgin grooves inserted DiehIelemen'te (42943) are disconnected, Still printable revolving nose hook with a front Direction for the inclusion of the work module in the Working comb = on the rotor side walls AxialdrU * ko # which is within the with the red unrunning parts according to the rotorualtuf see changing axial transverse alignment of work chambers poriodinch pre-greening and downsizing, especially close Claim 1 to 4.gekennseiehnet duroh with the rotor (111) non-rotating balancing chambers (152) ideren axial Cross-section * is identical or essentially same cycle of the working chambers (119) however, the opposite of these changes in* Enlargement of a work chamber (112 # to Druokaus- equally suitable.z, B. roughly in the same radial direction lying equalization chamber (152) diminished and vice versa. 6.) DrehtlUgelnasohike according to Anspruoh 5, gokenncoiohn * t by such a change of work chambers (119) and each assigned Aungleiakkammern (152) vdst die Sum of their transverse sections effective for the axial forces while a rotormlax tea is coming or approaching is constant * 7.) Drehtlägeliiasehine according to claim 5 and 6p & ekonanstek- net duroh such a mutual change of work kommern (119) and Aungleiehkämmern (152) 0 that related placed on any of the Rotorachne * 'Diene- tral level the sum of the yam work modim in the Workers and those from the medium in the aungleick chambers exerted axial forces on both sides of the 4th The metric plane is equal to or annkhe = * d is equal to gronn iot. 8,) Drehfl (igelmanchJ.ne to Anapruoh5 am 7.dadtwoh gekonn- seichnetid that the transverse forces acting for the axial forces intersects the Ausgleiehkammera (152) po # riediaoh alternating between zero or almost zero and ei * « the largest axially effective cross-section of the ar * oettakm- more or nearly the same cross-sections or reduced tra. 9.) Drehtlägelnaachine according to claim 9 am & .due to this »- seiehnetgdaß the number of distributed around the circumference " Ausgleiokkammera (152) equals the number of work coa- Mera (119) isto according to claim 5 to 9, characterized the Aungleiebkumern (152) for Beau: facälaguag through the workuaodim with each while radially grounded working chambers (119) ka »u- alsierimt verbundex are, according to claim 5 am 9 gdaduroh gekexn »eiebnettthat the aungletok chambers (») only Submission by the » working media with the respective while diametrically opposite bzwin reference aut the druok parody acted in the opposite direction Work chambers (119) are connected in a comannizing manner, neck claim 5 am 8, lo or ll # daduroh gekeanzeiohnet. that every working chamber (119) consort with her (152) there are sayings, Threatening wing machine according to Änopruoh 5'bie 9911 or 12g dadurek geke »osio" etv that the aungleiehkannem only Deaufschlagvag thirth the work which is etekende under æmok etek notim atiadig nit the press scene of the machine bound eats * 14,) Droh: flügelnaaohiao && oh Anspruth 3 to 13 # dadurth konzeiMaati that several gynteas from on the Vatang distributed in particular such that the kumern the one Systems hixaiehliah the Druokipe in reverse wiv the radially assigned & amorn the other Systeastaleo a, ß, the ilLammers dea an aja-teas with iaugdruokpdie Chambers of the other system with work adruok -peauta & lagt been according to claims 5 to 14. konnzeiohnetp that the Aunaleiohxammers (152) by the exaantriuch at the fliotor (111) circulating Zxaentorriag- (118) be controlled, 16.) DrehflUgelmaschine according to claim 5 am overall 159dadurch konaseichnetgdag the arialb Unge of the Aungleiohka «ern (152) only a fraction of the social length of the work- chambers (119) is, c17.) according to claim 5 am 15gdaduxoh characterizing tgdaß the formation of their Gj * aoo pre- aaderlichen Aungleiohk «mern (158) run in r & 4i & l- the Jianalfdmigtn lLa »ern (150) ale bZolb @ n acting * ' Sliding slide valve (154) depending on the% 4 * r rotor arm Äung 61eiten and daduroh the ala AungleieU «nera 4152) Serving rooms alternately enlarge = and reduce 18. Rotary vane machine according to Anspruah'17, characterized geke = aeiohiietu that preferably with the arrangement of the compensation chambers. (152) in the hotor side walls (e.g. 114) the slide valve (154), e.g. through slot openings (159) in the side walls (114t112) with the capsule ring (118) rotating eccentrically to the rotor through connecting links such as bolts, webs or the like.) are connected. 19. Threatening wing machine according to claim 17 and 189, characterized in that the sliding slide (154) -by the capsule ring (118) are inevitably taken in the radial direction # in the circumferential direction, however, have a game. 20. Rotary vane machine according to claim 17 to 19, characterized in that the slide valve (154) radially guided in a hotorseitenwand (114) on slide bars (156) is mounted in the circumferential guides (e.g. slots 155) in engage the slide (154) and in turn duroh connecting links (157) are connected to the Kapoelring (118) . -21.-High-pressure rotary vane machine with a capsule ring that controls the wing movement eccentrically to the rotor and with rotor side walls that run together with the rotor and that lie tightly against the capsule ring at the sides. inebezender * naoh address 1 to 20) characterized vdaä &, see the capsule ring (118) and one or both rotor side walls (1149112j113j, 115) hydrodynamic balanoierwXoktiltelder In the form of Aunäparmgen supplied with a medium (161) provided narrowly extended in the circumferential direction see tapering in one direction and / or the other. Rotary wing dqaehine according to claims 211 and 229daduroh gekennzeiohnett that the balancing wedge fields (161) are completely or partially surrounded by relief fields, especially grooves (1649165,166.167) ), preferably connected to the external pressure or another low pressure zone,