EP0158713A1 - Radially or axially coupling pusher rod mechanism for the ring pistons of a machine rotating at intermittent speed - Google Patents

Abstract

Machine having segmented pistons (K), rotating at an intermittent speed, with a stator (S) and a rotor (R). The stator has stator support slots (SN) and the rotor has rotor drive slots (RN). The one piston (or a set of pistons) rotates together with the rotor (R) by engagement in the rotor drive slot (RN), while the other piston (or the other set of pistons) remains stationary by engaging in the stator support slot (SN). In the next phase, by reversing the coupling of the pistons, the first piston is rotated with the rotor and the other piston remains stationary. <IMAGE>

Description

The invention relates to an addition to the features of the stator-rotor and rotor-stator dome tappet change-piston exchange coupling with a trapezoidal-angle-leg-part length-inner-outer-segment-piston, fastened to transverse sliding bushes inside and outside of the motor / pump-suction-displacer or relaxation annulus located radially therebetween with one-sided stator and rotor grooved rings with trapezoidal constriction coupling links between the trapezoidal grooves and the trapezoidal head tappet 1-⊕ rings with inner and outer segment pistons attached directly to them in the motor / pump annular space designed as an intermittent transmission annulus with returnable medium outputs on the stator abutment distribution piston piston angular lengths. the trapezoidal wedge expulsion of the coupled trapezoidal plunger heads by means of the transverse thrust hydraulic volume located axially behind them due to the uncoupled plunger sleeve cross-section located in the scanning path by shearing off the Umspülhydraulikvo lumens is fully supported by connecting the support side with the hydraulic pressure of the motor or the pump and connecting the coupling side with the negative pressure side by means of a rotary slide valve ring between the stator and rotor shafts / bore fit left and right of each of the required double ring spaces with volume performance in a 1: 1 volume: converter rotor angle -Relationship, optionally under jacket rotor or stator or core-input-output tube stator or shaft rotor.

In the selection catalog of these four-piece intermittent gear elements, the basis and the combinable execution potential types - only left for the exchange of variants - are here completely prepared for a kind of standard model, i.e. here the rest of the task, revealing the composition with drawings, like the segment pistons, is ready for the above development component to the inner and outer transverse sliding bushing with which trapezoidal groove and plunger heads are attached to the 1-⊕ (circular) bushing ring and the stator inputs or the piston bushing inputs and outputs can be drilled if the precision is mastered, the intermittent gear ring as Motor pump ring, ie now the inner and outer segment pistons can also be used directly as trapezoidal head tappets attached to transverse sliding bushes,

The solution is in

1.Feature, based on the basic application feature, with segment pistons in trapezoidal angle part length as a direct trapezoidal head tappet on an inner and on an outer transverse sliding piston bush, characterized by the combination combination with rigid fastening (e.g. radial pins and brazing) inner segment axial trapezoidal plunger head piston on axial bush transverse drive K1 / K2, Fig. 1, -a, -b, and outer segment axial trapezoidal plunger head piston K3 on axial transverse sliding bushing K4 with one-sided trapezoidal groove rings RN and SN with piston length of the same length as the trapezoidal angle leg, about 3 NT piston rod trapezoidal NT deep and the transverse sliding bushes in the ring space covering on the left, covering the right the grooves on the stator and rotor rings overlapping width with transverse displacement displacement annulus 5 and 6, on the inner bushing K2 and 7 u. 8 on the outer socket K4, into which connecting channels, e.g. Open axial bores 9 from rotary slide valve control, e.g. between input / output stator shafts / rotor face plate bore fit S / R 10 and over the central stator double groove ring SN 11, there from the radially inward leading connection channels 1, 2 to the inner displacement ring spaces 6. individually in the left and right, where they open into the support volume, and the radial flushing channels 13 in the stator center groove ring SN and 14 in the rotor nut ring RN between the inner and outer support displacement ring spaces 5 u.6 with 7 and 8 with the locking slide edge 15 each on the radial flushing channels 13, the sheared residual volume of which is switched off by the rotary slide valve control in the hydraulic negative pressure chamber, on the other hand Support displacement annulus side hydraulic pressure chamber connection is switched, and the inputs / outputs I / O of the motor / pump annulus K1 / K3 are optionally routed axially in the stator grooved ring SN or through the stator shafts / transverse slide piston bushing bore fit K2 / SE / A, in the stator grooved ring engagement angle position same input / output radial bores I / A at the front of the piston v and at the rear of the piston h in the downward direction Ev / Ah and during rotor groove coupling angle Av and Eh through the outlet basin bores 16 in the stator tube surface S / E / A with at least large radial bores 1.7 optionally opening in the Pipe intermediate outlet A and input center tube E through filler segments 18 in outlet A, optionally radially reversed as a jacket stator input / output bushing with the input and output distribution ring channels on the left and right 1⊕ with axial channel bores o

The stator abutment circle division is, for example, 12 NT for each segment division with 3rd stator abutment divisions = 36 NT in a circle⊕ with a pair of piston angle lengths 3/36 0 = 3 pistons K on the inner and Rigidly attached piston 3 to the outer cross slider sleeve, and -buchsenradialdicke rängervolumen _d with equal cross-sections or Querverschiebever-, on the right volume supplementary annular space only by 1/2 division ring segment offset eg stator SN. Depending on the piston mounting requirements in the annulus radial height, other stator abutment annulus divisions with correspondingly wider or narrower groove depth dimension requirements at the annulus width ratio: narrower up to the minimum annulus width, then axial inputs / outputs I / O / SN through the center stator double nut ring or outer jacket stator ring nut.

The second task is to omit the segment piston mounting and the transverse sliding bushes for radial installation bottlenecks or tubular motors / pumps in accordance with limited load-bearing capacity and only to use free piston segments in a constructive canting guide option. The solution is in

2nd feature, under the 1st feature, with segment pistons simultaneously acting as a trapezoidal head tappet on one side in the left rotor groove ring and right stator center groove double ring, engaging in the trapezoidal positive clutch constriction link, trapezoidal groove leg split length piston length, characterized by the free piston segment arc length x minimum width stator axis piston or bore passageway guide / segment-only shaft guide / segment guide bore / segment-only shaft guide / segment guide bore / segment-only shaft guide / segment guide bore / segmental shaft guide / segmental bore guide / segment guide bore Piston pair K1 / K2, Fig. 2, -a, -b, -c, in either 1/4, 0 piston length division, Fig. 2b and 2c, or 1 / 3⊕ piston length division, Fig. 2d, with a required segment piston minimum width and radial - Precision fit to accommodate the tilting load in the arch shell. The volume continuity can be achieved with 1 / 4⊕ piston length with 2 annulus sections again and with 1/3 ⊕ piston length only with 3 annulus sections, optionally again as core stator input / output double tube, S / I / O, Fig. B, -d, or Sheath stator input / output double socket S / I / O, Fig. 2c. In the case of the motor function, which is more resilient to pumps, the segment piston trapezoidal plunger heads can be rounded off according to the canting on the trapezoidal edges or can be provided with tapered rollers. The pinch volume between the trapezoidal displacement coupling space between the segment piston rod trapezoid heads and the trapezoidal groove in the ring is entered by minimal radial bores from inlet E and outlet A, like the main inputs S / E / A by radial bores,

The third task is to transfer the axial planing movement in a trapezoidal template setting to the drill bit crown bushes for deep-drilling pipe or sleeve hydraulic motors. An _L ö- sung this Intermittierendgetriebeanwendung is

3rd characteristic, under the 1st, with axial transverse sliding inner bush trapezoidal groove template movement, characterized by the axial transverse sliding segment piston-1-⊕-tappet ring bush K1 / K2, Fig. 3, -a, - which is extended axially on a motor plan side to a drilling tool holder by the piston bush transverse sliding movement. b, -c, with one-sided axially inner rotary slide valve control from the rotor bushing R attached to the rotor slot ring RN with rotary slide ring R / 11 into the input / output axial channel bores, engaging radially in the bore basket S / 9 in the stator groove ring bushing S, and in the axial transverse slide bushing shaft / rotor bushing bore fit K4 / R located Axialkanalkorb R20 eckbuchse _d from the Verdrängerringraumseite 7 via a stator 21, on the other Ver _d rängerringraum 8 away connected via Ra _d ialverbindungs- channel star 22 with the inner Verdrängerringraum 6 whose Ra _d ialkanalstern 22 with the a-Ausgangsaxialkanalbohrungskorb S / 9 is connected by means of Lä ngsnutsegmente S / 23 on the rotary valve ring R / 11 according to the switching requirement once connected to input E, the other through to output A, optionally as a jacket rotor R or this as a core rotor inside, optionally the axial planing feed stator reverse rotation S / 24, Fig. 3, the Axial planer-trapezoidal stencil contour S / 25, identical to that in the inside of the stator trapezoidal groove SN, turned back by a stator reverse passage consisting of pump ring space SRD, Fig. 3d, between the axial plane motor stator input and output channel basket S / 9 and stator tube rod S / 26, optionally as a single ring space or In relation to the circulation, as many motor ring spaces as possible until the torque and planing impulse is full, with an additional input tube sleeve above the rotor bushing R, whereas the axial transverse sliding bushes K / 2 by means of the stator inner tube S / 27 still used here.

The fourth task, however, is to use the axial rotary planer motor of FIG. 3 in the system as a rotary axial planer mechanical gear. A solution is in

4. feature, under the third feature, with Axialhobel-rotating rotor R, characterized by the rotor socket connection axially ouble annulus section with only rotary motor rotor, Fig. 1, a _D or more such side by side until torque is full.

Design variants from Fig. 1, for example Fig. 4: Trapezoidal locking lugs and outer segment piston axial transverse sliding bushes TKB i u. a with suction displacement annulus in the pitch circle in the segment piston radial level K / K radially between the bushes B / B in the effective width axially between the trapezoidal ring flat sides N / N one-sided stator groove rings SN and rotor groove rings RN; required continuity double annulus sections axially left and right ( radial stratification possible, Fig. 6, a standard solution) in versions: jacket input / output stator tube, Fig. 4, and shaft rotor S / E / A / R with center rotor groove ring RN / RN wedged on the rotor shaft R; stator groove rings SN / SN on the outside left as an input / output junction flange with only one input and output channel I / O; through axial input / output sheath channels I / A connected to the right stator slot ring SN / I / O and a leakage line L. The segment pistons K / K in the theoretical C-round design are a pair of pistons in a circle, but divided into e.g. / 4, ie 4th stator abutment SW and rotor driver trapezoidal slots RM in the ring space. Intermittent gearbox walls form the suction displacement annulus by using the segment pistons K / K directly as (from the beginning so called there) dome tappet T with trapezoidal heads on the left and right, each in trapezoidal positive clutch cone stator and rotor nut rings, either in the stator or rotor nut ring SN or RN. engaging in the stator abutment groove SW or rotor driver groove RM in the forced clutch exchange, while the positive clutch is driven by the other annular space section at the stroke angle during the rotor groove ring travel movement of the rotor driver piston, while the same angular movement of 2 NT of the rotor R is more importantly a trapezoidal angle leg length piston K / K as a geometric trapezoidal nut - Requirement, of which 1/3 piston NT small division engaging in 3 times deeper stator abutment and rotor driver trapezoidal grooves SW / RM. The piston sleeves B overlap it with 1: 1 Ringraumabdichtüberdeckung the trapezoidal grooves SW / RM still on the opposite Einkuppelseite Auskuppelseite, the trapezoidal wedge residue sprouting support with respect to the ^R estaustrieb in the Einkuppelseite is. Trapezoidal wedge angle from the angular legs Groove depth NT: Trapezoidal groove angle leg length, eg outside a 125 m @ or 45 ⁰ , steeper on the inside with a safe distance close to the trapezoidal wedge self-escapement for as little residual drive support requirement as possible on the disengaged dome ram piston side. A piston pair division thus consists of 4 NT, where 1 NT = piston length angle = groove depth NT; e.g. 1/16 eiWith axially opposing stator abutment slots SW, the rotor driver slots RM are offset by 2 NT for stroke: Empty shift angle alternating j _e 2 NT rotor angle movement, Fig. 4.

Input / output axial holes I / O in the stator groove rings SN in the stator abutment groove SW are limited to the required I / O termination during the empty mode clutch, Fig. 5f, and the remaining required trapezoidal groove surface. Other larger inputs and outputs, possible through the piston bushing KB opposite the stator S, again according to FIG. 1, as radial input and output rotary slide bushes,

Displacement of the washing volume during the piston sleeve axial sealing during the empty shift coupling from left to right and right to left of the piston sleeve plan ring sides 5-6-7-8 optionally by larger piston sleeve bore of the inner Bi and smaller ø of the outer Ba., Optionally additionally by radial washing channels 13-14; or for limited speed only radial rinsing channels 13-14 with hydraulically locking shearing off of the support hydraulic volume behind the coupling side of the plan through the coupling side of the other piston bushing KB. To accelerate additionally, according to B: B, Fig. 5, rotor rotary slide valve control of the remaining closing hydraulic volume on and above the radial channel edge shear 5/14 u. 8/13; optionally additional hydraulic support for the piston sleeve seal behind the coupling side by connecting the pressure side motor inlet E or pump outlet A one direction or both directions via diverter valve, always the pressure side connected to the support volume 6/1: 1 and 7 and after clutch 7 and. 8, 5, e.g. schematically via input-output connection channels 12 via rotor rotary slide valve 10 u. 11 and radial-axial channels 9 in the support volume sides 6 u. 7 and 1: 1 reversed after clutch 5 u. 8, at each annulus section. Flatter trapezoidal angle legs possible with hydraulic support. For the simple hydraulic piston bush support, Fig. 1,2, the piston bushes KB need only be closed axially with radially elastic sealing rings; such can be used as check valves. Or the piston bushing rinsing volume is filled with air 6-8 using air inlet / outlet check valves and the leak volume is always pumped into the leak line, especially with a pneumatic motor anyway.

Variants at each shaft end, half a motor, Fig. 4, at the same time as shaft bearing between shaft R and stator jacket S, optionally screwed together with axial collar screws of the input / output stator flange I / O / S and stator jacket bushing S on the axial / radial bearing flange or bracket. Optionally, continuity double annulus sections, Fig. 4, with center double stator slot ring S / E / A and the rotor slot rings RN on the left outside at least axially repositioned. Optionally as core stator input / output tube S / I / O, Fig. 7b, and jacket rotor drum R with center stator; or left and right outer stator slot rings SN / I / O, Fig. 4, and center rotor double slot ring RN / R, optionally axially disassembled under drum R, separated by half a motor on the left and right.

Trapezoidal bar inner and outer segment piston axial transverse sliding bushes radial annulus superimposition of the continuity double annulus sections, Fig. 6; Stator = S; Rotor = R; Piston = K; Dome tappet = T, combined = TK; Piston bushes = _B , outside = a, inside = i; grooved rings = N; Stator abutment groove = SW; Rotor drive groove = RM; Empty flushing volume radial channels = ₁₃ in the stator slot ring, 14 in the rotor slot ring; Residual flushing axial channels through intermediate rams piston bushing / stator = B / S, between the annular spaces = _B i / _B a, above the rotor = B / R; Input = E; Output = A; Leakage line = L; for a direction leakage line from the rinsing channel 13 to output A; Stroke angle = H; Empty shift dome angle of the rotor = V; Rotor bearing with rotor grooved axial bearing with mutual eg shoulder bearings; optional coaxial collar screw connection = _S m on flange bearing; Piston pair stator abutment groove and rotor driver groove division: eg 1/4 ⊕ = 4 SW u. RM and 4 segment piston pairs K / K; Inlet / outlet intersection bores in stator flange S / E / A / SN; radial stator abutments of the two ring spaces SW / SW, on the other hand 1/8 0 offset outer a to inner i rotor nut rings RN on the rotor nut ring R with spline shafts / bore fit on the rotor shaft R; radially separated inner and outer rotor nut rings RN / RN; limited input and output axial bores I / O for permanent closure during empty shift dome angle V, Fig.-d u.-f; for Fi ^g . 1-7 the squeezing volume in the trapezoidal dome parallelogram V from RM to SW / I / O at the outer edges of the segment piston K / K flushing axial grooves cleared; Segment piston K soldered to the piston bushings B, optionally pinned, one piston K of a pair on the outer, the other on the inner bushing B, each on the outer and inner annulus. With 1: 1 measure volume 120 cm ³ / rev.

Motor function curve engine working spread pressure E in circumferential elevation plan view, Fig.-c, -e from top to bottom, in axial cross section, Fig.-a, left turn, stroke angle H an. rotor pistons R / K attacking the outer rotor driver grooves RM during idle shifting clutch V-angles of the same 2 NT = trapezoid groove angle-piston lengths of the rotor R, Fig.-e, and -a. On the other hand, medium pressure changed backwards from bottom to top, Fig.-e, -c, inner annular space, Fig.-e, in the lifting angle H and outer annular space, Fig.-c, in the empty displacement angle V of the rotor R; afterwards change of HV; backward = motor function curve of the forward rotating motor I / O = A / E. Inner annulus to outer annulus with the same circumferential volume in the stroke angle H. outer to inner groove depths = 1/16 of the circumference = piston length = trapezoidal groove leg length on the outside of the annulus. To lower Trapezkeil- ^R of the coupled piston and -riegels or -stössels TK larger Nuttiefenmaßverhältnis to the circumferential pitch estabstützung of 1 / 1.6 ⊕. Hydraulic support of the coupling is additionally possible as in FIG. 5. Core input and output tubes and jacket rotor optionally in accordance with FIG. 7, self-supporting or axially continuous stator axis S / I / O.

Free piston systems, Fig. 2, trapezoidal axial bolt segment piston 1/4-uerSchallenguerführung between core u. Sheath sliding fit for limited torque load; Taken into account V _e rkantungs braking friction on the free-standing side of the piston, a trapezoidal angle leg pitch length flask with 1/3 NT piston Axialtrapez-bolt heads in one-sided stator and Rotornutringe SN-SN-SN in Statorwiderlagernut SW or Rotormitnehmernut RM engagingly, geometrically as Zwangsumkuppeltrapezengpasskulissenpärallelogramm in which with 2 NT rotor angle of rotation the empty shift conversion takes place; the rotor piston to the stator piston and the stator abutment piston to the rotor driving piston S / K: R / K u. R / K to S / K. 1. NT = 1/4 0. Rotor driver grooves RM of the two continuity-supplementing annular space sections offset by 2 NT with coaxial identical stator abutment grooves SW. Radial inputs / outputs I / O through the stator S. In the case of hydraulic medium, the squeezing volume during the empty shift coupling in the trapezoidal shifting link is omitted in, for example, output connection channels Av. Not necessary with pneumatics. Dimension the width of the annular space between the ring N / N sides for measuring motors, e.g. for 10 cm ³ / rev. Grooved angle leg made to radius, wound. Segment piston end faces K for axial flushing channels shortened from the coupling squeeze volume by half r height 7m volumen. Stator slot rings SN pinned to stator S. Rotor nut rings RN pinned to rotor R. Forward / reverse medium changeover possible.

Design variants: Stator input / output jacket tube S / I / O, Fig. 2 _b , known to be mounted and sealed with R shaft rotor.

Stator input / output core tube S / I / A, Fig. 2a, e.g. axially continuous with drum rotor R between stator S, e.g. -The wheel fork is supported on both sides and sealed with an external inlet and outlet.

Cantilever load-bearing transverse guide on or under plane-guided segment pistons K, Fig. 7, by means of a wedge / groove element pair t between piston K and trapezoidal axial bolt segment pistons T / K, which under stator filler rings S in the stator groove rings SN in stator abutment SW or in the rotor ring sides RN in Engage rotor driver grooves RM. The crossguide ^V erkan processing load receiving wedges t only in segment K piston width in half the width of the trapezoidal segment Axialriegel piston T / K engaging, in the plan piston K t of the wedge firmly; t-slot full T-width.

Optionally as a jacket stator input / output tube S / E / A, Fig. 7a, with shaft rotor R. Or as a core stator input / output tube S / I / A, Fig. 7b, with jacket rotor drum R, self-supporting or axially continuous with stator fork, e.g. Wheel fork. Radial floor dimensions: narrowest version, Fig. 7b, optionally with radially high piston K, Fig. 7a, with 1 ⊕ - piston pair division, Fig. 7c; or 1./2 ⊕-; 1./3 ⊕; 1/4 ⊕ or 1/5 ⊕ piston pair division with correspondingly larger core φ and the same annular space radial level height; optionally many axial ring spaces.

Claims (5)

Quadruple internal gearbox element for rotary segment piston motor / pump with inner and outer segment piston transverse sliding bushes, 1. Claim according to the basic application feature, with segment pistons in trapezoidal angle leg length as a direct trapezoidal head tappet on an inner and on an outer transverse sliding piston bush, characterized by the combination combination with rigid fastening (e.g. radial pins and brazing), inner segment axial trapezoidal plunger head piston on axial transverse slide, two bushes on axial transverse slide 1 Fig. 1., - a, -b, and outer segment axial trapezoidal plunger head piston K3 on axial transverse slide bushing K4 with one-sided trapezoidal groove rings RN and SN with piston length of the same length as the trapezoidal angle leg part about 3 NT piston plunger trapezoidal NT deep and the transverse sliding bushes in the annular space-covering grooves on the left and right the stator and rotor rings overlapping width with transverse displacement displacement annulus 5 and 6 on the inner bushing K2 and 7 u. 8 on the outer bushing K4, into which connecting channels, e.g. axial bores 9., open out from the rotary slide valve control, e.g. between input / output stator shafts / rotor face plate bore fit S / R 10 and over the central stator double groove ring SN 1.1, there from the outside radially inward connecting channels 12 to the inner displacement annular spaces 6 individually in the left and right, where they open into the support volume, and the radial flushing channels 13 in the stator center groove ring SN and 14 in the rotor groove ring RN between the inner and outer support displacement annular spaces 5 and 6 with 7 and 8 with the locking sliding edge 15 each the radial rinsing channels 13, the sheared residual volume of which is switched from the rotary slide valve control into the hydraulic negative pressure chamber, on the other hand, hydraulic pressure chamber connection is connected on the support displacement annulus side, and the inputs / outputs I / O of the motor / pump annulus K1 / K3 are optionally led out axially in the stator groove ring SN or you Through the stator shaft / transverse slide piston bushing bore fit K2 / SE / A, in the stator slot ring engagement angle position directly through the same inlet / outlet radial holes E / A at the front of the piston v and at the rear of the piston h with downward direction Ev / Ah and during the rotor groove engagement angle Av and Eh through the sink holes 16 in the stator tube surface S / E / A with at least large radial bores 1.7 optionally open-ended in the tube intermediate outlet A and the input center tube E through filler segments 18 in output A, optionally radially reversed as a jacket stator input-output bushing with the input-output distributor ring channels on the left and right 1 ⊕ with axial channel bores. 2. - according to claim u.Hauptp. , with segment pistons as trapezoidal head tappet on one side engaging in the left rotor groove ring and right stator center groove double ring engaging in the trapezoidal positive clutch constriction backdrop trapezoidal groove leg split length piston length, characterized by the free piston segment arc length x, minimum width stator axis or rotor shaft / rotor shaft / segment piston still bore 1 guide 2 Fig , -a, -b, -c, in either 1/4 ⊕ piston length division, Fig. 2b and 2a, or 1/3 ⊕ piston length division, Fig. 2d, with a required segment piston minimum width and radial constriction precision to accommodate the tilting load in the arch shell. The volume continuity can be achieved with 1/4 ⊕ piston length with 2 annulus sections again and with 1/3 ⊕ piston length only with 3 annulus sections, optionally again as core stator input / output double tube, S / I / O, Fig. B, -d, or Sheath stator input / output double socket S / I / O, Fig. 2c. 3. - according to claim. 1., with axial transverse sliding inner bush trapezoidal groove link template movement, characterized by the axial transverse sliding segment piston piston-1-⊕ tappet ring bushing K1 / K2, Fig. 3, -a, -b, -c, with axially on a motor plan side for a drilling tool receptacle correspondingly extended to a greater extent one-sided axially inner rotary slide valve control from the rotor bushing R attached to the rotor groove ring RN with rotary slide ring R / 11 into the input / output axial channel bores, engaging radially in the bore basket S / 9 in the stator groove ring bushing S and in the axial transverse slide bushing shaft / rotor bushing bore fit K4 / R of the axial channel basket R20 Verdrängerringraumseite 7, connected via a Statordeckbuchse 21, on the other Verdrängerringraum 8 across the radial connecting channel 22 with the inner star Verdrängerringraum 6 whose Ra _d ialkanalstern 22 with the a-Ausgangsaxialkanalbohrungskorb S / 9 is connected by means of Längsnutsegmente S / 23 at Drehsch ieberring R / 11 in accordance with the switching requirement, connected once to input E, the other time to output A, either as a jacket rotor R or this as a core rotor on the inside, optionally the axial planing feed stator reverse rotation S / 24, Fig. 3, the axial planer chisel trapezoidal template contour S / 25, identical to that in the trapezoidal groove SN inside, turned back by a pump ring space SRD, Fig. 3d consisting Statorrück- _d rehdurchlaß between Axialhobelmotorstator input-output channel selection S / 9 and Statorrohrstange S / 26, either as a single annulus or rotating relative side by side as many motor annular spaces to pivot and Axialhobelstoßmoment is full of further input pipe sleeve. passed through the rotor bushing R, whereas the axial transverse sliding bushes K / 2 by means of the stator inner tube S / 27 still used here. 4. - according to claim 1, with axial planer-rotary rotor R, characterized by rotor sleeve connection axially with only a rotary motor rotor, Fig. 1, a _D oppelringraumsektion or several such side by side until torque is full.

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