DE1401395A1 - High pressure controls for rotary piston machines and rotary vane machines - Google Patents

Description

Applicant: Karl üickniann,

2420, Ishiki, Hayama-Machi, Miuragun, Kanagawa-ken, Japan.

Inventor: Karl Eickmann,

2420, Ishiki, Hayama-Machi, Miuragun, Kanagawa-ken, Japan.

High pressure-capable controls for rotary piston machines and rotary vane machines.

Subject of the invention

is a control system for rotary machinery keite- with liquid or through which the medium is passed into the rotors and out of the rotors addition grass operation, such as in particular hydraulic pumps, hydraulic motors, internal combustion engines, gas engines or steam engines, and in which a jteuerwelle in a The central bore of the machine rotor protrudes, which is suspended in such a way that it can follow rotational errors or axis errors of the machine actuator by adapting its axis, which cannot be positioned in advance, which has additional pressure balancing fields in order to compensate for pressure fields acting on it and which have flow-conducive channels that save air acceleration losses .

Control shafts for rotary machine ^ which are so suspended that they follow rotation errors of the machine rotors can, are already described in the patent ^ esuch E 16 937 Ia / 59e. The invention sets itself the task, the

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Efficiency of such controls already described to increase and improve their performance.

In this context, it is recognized that the hydraulic rotary machines in recent years a increasing application in industrial technology be-r was divorced. As the number of hydraulic machines used increases, so does the number of hydraulic machines Sum of the total efficiency losses that exist when the machines are used. The efficiency losses mean a loss of energies used, since they could not be made usable and mostly lost as heat. To save usable losses that are available to mankind Energies, increasing the overall efficiency of machines becomes more important as the number of the machines used or the sum of the services used increases. After the overall efficiencies of rational hydraulic machines today are already around and over 9CH »and the number of used Machines is constantly increasing, the problem with today's technology is the overall efficiency of such machines a few more percent, or even only a fraction of a percent, old gain of a tenth of a percent Brings overall efficiency in hydraulic machines Today, in the sum of the machine power used, more energy loss savings than an increase in efficiency, for example around 10- * years ago with the then lower total utilization of Energies through machines.

The invention recognizes that the previous statements of controls in rotary machines still have losses that can still be reduced, and therewith by reducing them These losses increase the efficiency of the tax waves can be increased further beyond the current state of the art. In particular, the friction losses are between »To further restrict the engine rotor and control shaft and the flow losses in the control shaft

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and the flow losses in Jur-jhtritt decrease in iie control shaft into the Jteuerwelle in the ilaschinenrouor and from the Maschinenronor out, if the causes are different loss sites are technically accurately detected and concentrated.
According to the invention this is achieved by

that: the luediuias channels of the steering shaft are streamlined; Be trained to deal with sudden widening or narrowing of the otrströmung to avoid corresponding losses;

May: the medium supply in the oteuerwelle axial or at an angle, if possible an acute angle to the axis;

that: the flow inlet and outlet streamlined through gradually changing channel cross-sections he follows;

that: the control shaft between the stationary housing and the control shaft flange is flexibly mounted;

that: they in the control shaft flange with balancing fields is provided into which the balancing medium can be passed;

that: it engages cylindrically in the machine rotor and in the machine rotor with pressure balancing fields is provided into which the balancing medium can be passed;

that: it has precise elements to secure it against rotation around its own axis; and thereby,

that: it is axially slidable, but axially precisely fixed by stops and pressure fields, as well as in Particularly high-efficiency execution examples in that the rotor window and the control shaft window are formed in this way, the inflowing iiediumeteilchen do not receive any sudden impulses Eaalten entry into the rotor or at the exit from the rotor, or support fields on the

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Controls are attached to the hydrodynamic load capacity cause.

The cylindrical design of the invention is reduced compared to planar or spherical control surfaces the diameter and thus the relative speed between Stator control mirror and rotor control mirror.

The inventive design of the stationary connecting parts between the control bolt and the machine housing with balancing fields, the control also relieves the load in the -Feeti-gung parts of effective forces and facilitated their ability to swim and thereby follow the rotation errors.

That of changes in the direction of flow and sudden changes Changes in cross-section relatively free canal entry and sewer outlet saves medium acceleration losses and vortex friction losses and flow separation losses. . . -.

The inventive 'formation of the control window in the control shaft and rotor prevents sudden loss of momentum when the flow passes from the stationary control shaft into the rotor and vice versa and causes a rapid »not sudden» orbital acceleration of the medium mass in the direction of rotation and thus reduces the pulse pulse loss as well as the medium acceleration losses at the control average.bnv.dtre *. & * toWmi ^ MwWkV t.

The design according to the invention with the cylindrical control shaft and the associated features enables Utilization of the centrifugal force effective in the rotor windows to generate a negative pressure in the control shaft intake duct and in the rotor suction windows to increase the medium suction speed.

For the floating mounting of the control shaft in the rotor bore, fields can be incorporated, the hydrodynamic Carry out load-bearing forces, compressive forces or centering forces. '

The invention increases through the savings outlined

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the efficiency of the machines it controls and enables a considerable increase in output as a result of the Increase in flow velocities and the possible increase in relative velocities between stationary ones and rotating control parts.

Appropriate controls can have several hundred atü can still work with a high degree of efficiency. By exploiting the fluidic knowledge according to the invention the flow speed and the suction speed can be increased. In oil hydraulic Machines with common oil viscosities can reduce the self-priming speed, which was previously around 1.5-2 meters per second, increased to about 6-20 meters per second will. The outer diameter of the control shafts can be reduced. The reduction of the outside diameter in turn, brings a considerable reduction in heat loss and lechage loss between the rotating and stationary control parts. at As a result, you can increase the speed of high-performance machines. In oil hydraulic machines, the inventive Controls, for example, in the event of an oil leak of 4UO liters per hour and several pressures hundred atmospheres can still work at a high efficiency level at around 5000 revolutions per minute.

In addition to the described increase in overall efficiency, there is also a multiplication of the flow velocities and the multiplication of the speeds at full high pressure capability a considerable Increase in performance per unit weight. For example, according to the invention, cast from bronze Control shafts with a weight of 4 - 5 kg. Capable of oil hydraulic pumps or motors up to about 200 PS to be controlled reliably and efficiently. The increase in performance per control unit weight and the reduction of the control diameter in turn bring about the possibility of considerable weight, space and cost savings for the machines themselves.

BAD ORiGiNAL

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H01395

Me figure

shows the longitudinal section of an exemplary embodiment of the control according to the invention for rotary machines; in the case of the example according to FIG. 1, a hydraulic rotary machine, for example a hydraulic one Pump or a hydraulic motor.

Figure 2

shows a cross section through Figure 1, along the section line XI-II.

Figure 3

shows a cross section through Figure 1, along the section line III-III.

Figure 4

Shows a cross section through FIG. 1, along the Section IV-IV.

Figure 5

shows a cross section through Figure 1, along the section line V-V.

Figure 6

shows a cross section through Figure 1, along the section line VI-VI.

Figure 7

shows a cross section through another embodiment, which corresponds to the longitudinal section of Figure 1, along the section lines II-II-VII through Figure

Figure 8

shows a cross section through another embodiment, that in the longitudinal section of the. Figure 1 and moreover corresponds to a cross section of Figure 7, along the Section line III-II1-VIII through Figure 1. BATH

H01395

In Figures 1 to β; Item 1 the housing, Item 2 roller bearing, Item 3 roller bearing, Item 4- the drive shaft with wedge, Item 5 the eccentric bearing, Item 6 the cap ring, PoE. 7 the rotor, Poe. 8 the rotor sidewall, Poe. 9, 10, 11, 12, 13 and 14 rotor channels, pos. 15 dtn control shaft body, pos. 16 and 17 control shaft channels, Poe. 62 a reversing piston, Poe. 18, 19, 20 and 21 balance fields of the control shaft in the rotor, items 22, 23 and 24 changeover channels, items 25 and 26 locking parts of a control bore, items 27, 28 and 29 hydrodynamic support fields on the control shaft body, items 30, 31, 32 , 33, 34 and 35 pressure medium fields on the control shaft swivel bearing, items 36 and 37 medium channels through the control shaft swivel bearing disc, items 33 and 39 pressure fields on the control shaft bearing part, items 40 and 41 folding pins, item 42 the cardan ring, Poe. 43 Leokage bores, pos. 44 a bearing ring, pos. 45 a bearing ring, pos. 46 a bearing surface on the housing, pos. 47 and 48 elastic seals, pos. 49 and 50 connecting bores, pos. 51 the swivel bearing washer, pos. 52 and 53 the Line connections, pos. 54 the blades, pos. 55 the swivel runners, pos. 56 rotor working chambers, pos. 57 retaining bolts, pos. 58 bores for conveying the medium into hydrodynamic support bearings, pos. 59 and 60 control window webs in the control shaft and pos. 61 and 63 control window bars in the machine rotor, item 64 compression springs, items 65 and 66 working center lines, item 67 sliding blocks.

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The main part of the controller 15 according to the invention is the Control shaft. It consists of a shaft with a rear splash. It can be made in one piece, for example be poured. In order to be able to follow concentricity errors of the rotor, or to be able to follow incorrect positions of the rotor, must the axis of the control shaft can be moved radially and also ■ be pivotable. On the other hand, it must not revolve around its axis turn. Both are achieved in a precise way by how shown in Figure 4 that the control shaft by means of the bolts 40 is held in the cardan ring 42, the parts being able to swing around the pin axes, and the cardan ring 42 is held in sliding shoes 67, on which the cardan ring can slide axially, and the sliding shoes 67 by bolts 41 are held, around the axes of which sliding blocks, gimbals and control shaft can oscillate, while the bolts 41 are fixed in the housing in a stationary manner. The bolts 41 and 40 are generally perpendicular to each other. You can use bolts 41 instead of a stationary fastening in the housing also be kept in a special ring. If you have a arranges such a ring rotatable relative to the housing, you can thereby the control shaft a leading or a give lagging attitude to the rotor windows. The control shaft and cardan ring can slide on the bolt and swing around the bolt axes, while the gimbal can also slide axially on the sliding blocks. Through this the control shaft can all rotation errors, vibrations and axial displacements of the rotor ideally follow.

At the same time, the suspension described is a precise safeguard against rotation of the control shaft around its own Axis guaranteed. This security is special Importance, because compliance in the peripheral direction would impair the efficiency of the control. Ss it has been shown that the fuses used so far against rotation by bolts with large play in bores had not worked with sufficient precision.

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Due to the swivel barice it and the ability to shift Control shaft arise. Sealing problems. The seal is guaranteed by the fact that the rear control shaft flange is provided with a spherical bearing surface will. The bearing surface can be raised, as shown in FIG. 1, or it can be partially shaped as a hollow sphere. The control shaft flange 15 presses axially against the swivel disk 51. On the control shaft shaft side, the swivel disk 51 is provided with a spherical bearing surface, which is shown in FIG its dimensions correspond to those of the Steuerweilenflanschea. The swivel disk 51 is thus sealing and slidable on the surface of the control shaft 15 · Both parts can against each other while maintaining a good seal in the direction of the spherical surfaces, perform any sliding movement. On the rear side, the pivot disc 51 is flat and lies on a flat sealing surface of the Housing on. The swivel disk 51 can slide as desired on the flat surface of the housing. It is secured against twisting in the peripheral direction by the bolts 57, as shown in FIG. At this point, a simple, slightly extended bolt lock is sufficient. Holes, as in Figure 5 is shown. In the axial direction are housings plane wall, swivel disk 51 and flange of the control shaft 15 are conveniently pressed against one another by springs. Such Springs are shown by way of example at item 64. With the arrangement described, the housing, swivel plate 51 and Flange of the control shaft 15 slide against each other so that full mobility of the control shaft, with the exception of rotation around its own axis, is guaranteed while maintaining the seal.

The axial fastening is ensured by pressing the parts together. There is spring pressure on one side and thus a certain kachgibigkeit against thermal expansion certificate gen. By 'the sliding shoes 67 are axial movements of the Control shaft due to thermal expansion phenomena or also due to axial manufacturing tolerances of the individual parts

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enables.

It is already known that there, where the control shaft has its control window of the pressure channel and the suction channel, the pressure of the working medium acts radially on the control shaft and would press it on one side against the rotor bore. This phenomenon is counteracted by the known arrangement of pressure balancing fields _{18, 19 and} 20 and 21. The pressure balancing fields 19 and 20 are opposite the window of the control channel 17 and thus balance the forces from the window of the channel 17. The balancing fields 18 and 21 are opposite the control window of the channel 16 and balance the forces on the control shaft from its window.

Practice has shown that, for high-pressure, high-performance machines, the balancing of the control shaft in the rotor and its displaceable suspension alone are not sufficient to ensure high-efficiency operation. Rather, reaction forces occur from the oil channels 56 and 57 in the swivel plate and also from άφ & control shaft channels 16 and 17 in connection with the lines flanged in position 52 and 55, which try to lift the control shaft from the swivel plate 51. Due to the fact that the channels 16 and 17 of the control shaft are usually unevenly pressurized, these forces are mostly unilateral and favor a one-sided lifting of the flange of the control shaft 15 from the swivel plate 51. Therefore, the swivel plate 51 bit balancing fields' 50 are provided which equalize the pressure from the bore 57, and are provided with balancing fields that equalize the pressure from the bore 56. The balancing fields can consist of any number, but their total must be dimensioned in such a way that they achieve the balancing of the corresponding other forces. It is particularly simple to design the balancing fields as continuous bores through the swivel disk 51. Ee. however, it is also possible to place the balancing fields in the spherical flange of the control shaft 15, or in the

• "9098U / 0070 BADORiGlNAL

Incorporate the flat surface of the plan wall of the housing. ·

Also the work force from the balancing fields 30 and 31 try to lift the control shaft 15 from the S.cawenkscheibe 51. This is prevented by having on the back of the flange of the control shaft 15 also balancing pressure fields positions 38 and 39 incorporated will. JUthrough the holes 49 and 50 pressure medium is in the compensation fields 38 and 39 are directed. Simply can the compensation fields 38 and 39 are designed as hanging channels. Conveniently, part of the balancing fields 38 and 39 is applied to the higher and the other Part with the lower pressure, for example the balancing channel 38, with the pressure of the control shaft channel 16, or the Balancing field 30 and the balancing ring 39 with the Pressure of the control shaft channel 17 or the pressure balancing field 31. The connection of the parts to one another is through Bores or channels made. The mentioned pressure equal fields and channels can be dimensioned so that all unilateral forces on the control shaft and the pivot bracket are canceled and only a contact pressure on the swivel plate 51 remains in the axial direction. By the measures described, full displaceability of the control shaft with simultaneous sealing is achieved even in high-pressure, high-performance machines.

However, not only static medium pressures occur on the control shafts of high-pressure, high-performance rotary machines, in particular rotary lobes or rotary vane machines the control shaft on. Rather, the control shaft also has its own weight. However, this is relatively small and could be in High-performance machines may be neglected. At high speed and high flow velocities in the channels 16 and 17 occur on the control shaft · in addition dynamic · back pressure, flow acceleration reaction pressure · and impulse pressure · on. Despite the static balancing fields, the sum of these forces is eccentric cause the control shaft to be positioned in the rotor bore. the

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however, eccentric mounting causes an increase in the friction between the stationary control shaft and the rotating rotor. In addition, the eccentric mounting increases the Leakage losses between the control shaft and the rotor bore. The leakage losses described reach approximately that when the control shaft is fully eccentric in the rotor bore 2.5 times a centric bearing. In the case of strong heating due to increased friction, even more.

According to the invention, precautions are taken to ensure a certain centering of the control shaft in a central position Ensure rotor boring of parts moving relative to one another without mechanical contact. The control shaft is closed provided with hydrodynamic support fields 27, 28 and 29 for the purpose. As a result of the high rotational speeds of the rotor around the control shaft, the wedge-shaped hydrodynamic support fields 27, 28 and 29 pressure medium wedges that generate pressure fields. The narrower the gap between Control shaft and rotor as a result of eccentric displacement of the control shaft, the more the hydrodynamic increases Pressure of the wedge-shaped hydrodynamic support field and presses thus the control shaft in the central position. The hydrodynamic support fields 27, 28 and 29 thus cause a automatic centering of the control shaft and prevent its eccentric position. The support fields 27 »28 and 29 thus act as centering fields without mechanical contact with parts. Any number of hydrodynamic support fields, as shown in FIGS. 6 and 1, can be provided on the control shaft circumference to be ordered. The hydrodynamic support fields are practically exposed to the working medium through bores 58 » In high-performance machines practically with the pressure medium of the high pressure channel, or with special lubricants.

The described arrangement of support bearings and centering bearings allows the relative speeds between stationary and rotor parts to be multiplied.

Housing 1, eccentric bearing 5, roller bearings 2 and 3, capsule ring

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6, working chamber !! 56, rotor 7 and rotor side walls 8 operate in a known manner. The work equipment enters the Machine rotor through the control shaft channel 17 and escapes out of it through the control shaft channel 16, or it enters it in the reverse manner through the control shaft channel 16 and leaves it through the control shaft channel 17 · In the case of the Entering through the control shaft duct 17, the working fluid comes from the conduit connector 52 through the housing duct 65 and through the swivel disk channel 36 and the control shaft channel 17 into the rotor 7 and through the rotor window la the rotor working chamber 56. The channels 65, 36, 17 and 9 are advantageously streamlined, without sharp edges and without sudden changes in cross-section and without sudden changes in direction to save flow friction losses and flow acceleration losses to train. The rotor channels 9, 10,

11, 12, 13 and 14 in the axial direction inclined to the control shaft «naahae, in order to achieve a gradual deflection of the flow in the direction of the rotor working chamber. at the rotation of the rotor acts in the rotor channels 9, 10, 11,

12, 13 and 14 the centrifugal force on the working means. These causes a pressure increase in the flow in the radial direction away from the rotor center point and a pressure drop, possibly vacuum in radial direction to the center of the rotor. The slightest pressure is therefore at the height of the Control shaft outer diameter. The fiction proper training of the rotor channels 9 to 14 and the control shaft channels 16, 17, the Sehwenkscheibenkanäle 36 and 37 and the Gehäueekanäle 65 and 66 allow a Vermehrfaohune Current fair speeds in the canals with low losses. In the case of self-priming machines, they allow one Increasing the intake speed in the intake ducts.

When the working medium enters the rotor 7 from the stationary control shaft 15, it receives a pulse in the direction of rotation. This impulse exerts a braking force on the Rotor off. Iueat »Iioh causes the sudden impulse on the

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flowing parts a strong contraction and vortex formation in the rotor ducts. According to the invention, the sudden impulse can be weakened and accelerated quickly convert, whereby one can save energy and, above all, reduce contraction acceleration losses. Bas happens As a result, the rotor channels do not hit the control shaft in the radial direction, but at an angle to it. The working equipment then t-itt out of the control shaft channel 17 in the direction of the arrow in FIG. 2 into the rotor duct 12. When a medium particle enters the rotor duct 12, the rotates right wall of the channel 12 in Figure 2 in front of the mass part, so that at the moment of passage of the control shaft in the rotor has not yet applied any rotational directional acceleration force the flowing mass particle is created. Srst gradually, corresponding to the streamlined, curved shape of the rotor duct 12, the mass particle experiences as it progresses in radial direction is the path acceleration in the direction of rotation, until it finally reaches the orbit speed of the rotor, at very high rotational speeds one can Use channel 13 according to FIG. 7, which restricts sudden impulses and flow contraction with their losses even at high speeds.

When the medium emerges from the rotor into the control shaft into it, it is practical to form the channel in accordance with position 11 in FIG. At very high speeds you can also use a channel, as in position 14 of the Figure 3 is shown, use. If you give the channels the shape according to position 11 in Figure 3 or according to position 14 in 8 shows, the impulses on the control shaft are reduced and the contraction when passing from the rotating to the stationary control part, or rather, reduces these phenomena and their deadlines.

Each working chamber can therefore be equipped with a special rotor inlet channel, such as position 13 in FIG. 7 and with a special rotor outlet duct, as in item 14 in FIG. 8. The two channels mentioned can be axial offset from each other and the windows of the control shaft

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be appropriately designed speaking. As from the figures 7 and 8, the rotor window of the rotor chamber can be seen so far ahead or behind that it reaches the control shaft on the side opposite the chamber. In the case of several working chambers, however, this requires that the individual Channels are arranged axially offset from one another.

The desired effect can also be achieved if the working chamber has only one window, position 12 in FIG. 2 or Position 11 ^ n Figure 3 has. You can then use the inflow part des Fea # | «^ Mlbt4'al offset to the discharge part. Ro-

12 then receive special flow websö; · -öl; '-; ^ | ^, · ^ | ί | ^ ρ ^ β control shaft 15 then receives special

no special training of the ^ 12, 13 or 14 iat, has the Steutrwe11β only the usual, well-known control webs

Positions 54 and 55 show blades of known rotary piston machines)! and position 4 the shaft of an exemplary Machine.

In the case of the control of rotary vane machines, it is often It is necessary to conduct the pressure from the control shaft duct, which is subject to higher pressures, under the vanes 54. The channels 22, 23, 24 and 68 can be reached by means of a known reversal. From canal 68 the pressure medium can then be passed through bores under the wings 54. The connection of the corresponding channel is reversed in a known manner by the Reversing piston 62. The reversing piston 62 runs in a Control bore of the control shaft 15 · This control bore must have stops to limit the ·· piston stroke. This can be arranged practically by a ring as shown in item 25. The ring. Is divided into several parts, for example 3 to 7 parts, radially slashed. You can then put the individual parts into the Insert the ring groove of the hole. A bushing 26 is then pressed cylindrically between the individual parts of position 25

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and crimps part 26 at the end. The closure of the control bore is then perfect. The part 26 can hold bores ent through which pressure medium is passed into Steuerwellenbalancierungefeider.

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Claims (1)

1401383 Claim 1 / » High-pressure control for rotary piston and three-wing machines mix i'liquid, grass or steam operation,, vie Hydraulic Pumps, Hydraulic Motors, Combustion Rotary Motors, Compressed air pumps and compressed air motors, gas motors or steam motors, with supply and discharge channels for the working medium to the rotors and with pressure fields and pressurized medium directed in opposite directions Balancing fields on the control shaft shaft in the central rotor bore, characterized in that the control shaft for free movement in a cardan ring with precise protection against peripheral rotation Suspended around the control shaft axis by cardan ring bolts with guide rails for axial mobility of the control shaft is that the control shaft bearing flange is provided with a spherical bearing surface that between conduit annulus flat surface and spherical control shaft bearing flange a radially slidable swivel plate with one side spherical and one-sided planar axial end surface is arranged, and that between the spherical Plansch the Control shaft and the radially slidable swivel disk or, or and the stationary line connection plane surface Druckmittelbalancierungsfeider are appropriate. Claim 2 High pressure control according to patent claim 1 and characterized in that the ochwenkscheibe (pos. 51 in Figure 1 and Figure 5) each with at least one channel for the supply of working medium and at least one channel is provided for the discharge of work equipment, and that they have at least one or has several balancing fields, in the pressure medium, out of the Working medium channels is directed so that the A2§i | ts central channels and who oppose them, looking towards the axis, associated balancing fields are connected communicating Mt. - 9 09814 ^ 070 ^ • ', ν-, Λ, Claim _3 High-pressure capable control according to patent claims 1 and 2 and characterized in that the balancing fields are present both in the planar end surface of the tilt plate and in the spherical end surface of the tilt plate. Claim 4 High pressure control according to claims 1 to 3 or some of the same and characterized in that the balancing fields in the swivel plate as by the Swivel plate through holes are formed. Claim 5 High pressure control according to claims 1 to 4 or some of them and characterized in that, " (Pigur 5) several balancing fields, for example 4. or more, in swivel disk diameter to save,.; ,, to the side of the connecting line through the two worka? central duct center lines are arranged, Claim 6 High pressure-capable control according to patent claims 1 to 5 or some of the same and characterized in that there are Swivel disk against rough rotation around its own: axis by bolts (item 57 in Figure 5) with a little clearance is secured in holes. '..-, .- ■ - .. Claim 7 High pressure control according to claims 1 to 6 or some of the same and characterized in that the swivel plate (pos. 51) is supported by axial sliding bolts and a cardan ring is secured against rotation about its own axis. BATHROOM OBIGINAL 9QMU / 0070-- Claim 8 High pressure control according to claims 1 to 7 or some of the same and characterized in that the control shaft (Poe. 15) by springs (Pos. 64) against the Swivel hinge (item 51) and thus control shaft, swivel hinge and housing connection plane face pressed against each other will. Claim 9 High-pressure control according to claims 1 to 8 or some of the same and characterized in that im Control shaft flange pressure medium channels or .Ringkanäle (Poe. 38 and 39) are attached, in which pressure medium can be passed that a force in the axial direction the steering shaft (Poe. 15) exercises. Claim 10 High pressure control according to claims 1 to 9 or some of the same and characterized in that the Drucksdttelkanäle of claim 9 so sealed are that the seals (pos. 47 and 48) can slide axially are. Claim 11 High-pressure control according to patent claims 1 to 10 or some of the same and characterized in that dl · axially slidable seals of claim 9 rearward on an axially inaccessible wall or disc (Item 44) to which they can transmit the reaction pressure of the AnpreBdruokes of claim 9. Claim 12 High-pressure control according to claims 1 to 11 or some of the same and characterized in that the axially unyielding 3oheibe (item 44) of the patent claim. 11 verso old on a spherical surface. 9098U / 0070 hen is with which it rests on a corresponding spherical surface of a ring (pos. 45), which in turn rests with a flat rear wall on an axially fixed flat surface (pos. 46) on which it can slide radially so that in the event of axial displacement of the control shaft (item 15) due to the sliding ability of the plane surface and the spherical surface of the ring (pos. 45) on and relative to its neighboring parts (pos. 46) and (pos. 44) as well as due to the radial Slidability of the flat surface of the disc (item 44) on the flat rear of the control shaft flange, no cabling occur between the named parts and the swivel mechanism (pos. 5l), the seals (pos. 47 and 48). the edges (pos. 64), the washer (pos. 44), and the ring (Item 45) adjust the axial displacements of the control shaft (Item 15) in relation to one another. Claim 13 High-pressure control according to patent claims 1 to 12 or some of the same and characterized in that the working central ducts (pos. 16 and 17) in the direction of the control shaft axis or at an acute angle thereto in the control shaft (pos. 15), the swivel disk (pos. 51 ), or the housing connection part are arranged. Claim 14 High pressure control according to claims 1 to 13 or some of the same and characterized in that the working medium ducts (Pos. Io and 17) are streamlined, so without abrupt and sudden changes in direction and cross-section are trained. Claim 15 High pressure capability control in claims 1 to 14, or some the same and in accordance with by DAJ the work medium passages or lorselben in section according Pif (pos. 16 and 17); ur 1 seen to the control shaft axis, at an acute angle learning rotor (Pos 7 ^ ~. u • <· ίϊ Γ ^Λ '■ ' Π 0 7 0 BAD ORIGINAL open out or open out, or the rotor window (pos. 9 » 10, 11, 12, 13 or 14) engage the rotor at the same or a similar angle. Claim 16 High pressure control according to patent claims 1 to or some of the same and characterized in that the control shaft control windows and the rotor control windows (Figures 2, 3 »7 and 8, Pos. 12, 11, 13 or 14) are designed so that the flow without sudden impulses swiftly accelerated on the rotational path in or out of the rotor, or can enter and exit by the rotor window walls in the vicinity of the control shaft circumference do not meet radially on the control shaft, but at an acute angle to it, preferably so that the tangent of the acute Angle in the vicinity of the control shaft periphery is the quotient of the radial component of the flow velocity and corresponds to or approximates the rotor speed. Claim 17 High pressure control according to patent claims 1 to or some of the same and characterized in that hydrodynamic support fields or hydrodynamic centering fields are attached to the circumference of the control shaft, in such a way that that in the control shaft surface recesses are incorporated, the bottom surfaces in the direction of rotor rotation ai * h approach the circle periphery of the control shaft and can be routed into the working medium or lubricant so that it is hydrodynamic when viewed relative to the periphery Pressure wedges can arise when the rotor rotates. Claim 18 High pressure control according to claims 1 to 17 or some of the same and characterized in that a reversing piston in a bore in the oteuerwelle (item 15) (Item 62) is present, the axial stroke of which is through BAD G 9088U / 0O70 Stops (pos. 25 and 26) are limited to 13t, which consist of multi-part sleeves with radial flanges engage in bore ring grooves and> 1ie have central bolts or lungs that engage centrally in the divided rings and thus hold them in the hanging grooves, while the central Hung by flanges or flange and bordering or flange and snap ring axially in multiple shared rin £ are held. BAD 9098U / 0Ö7Q