DE2365057A1 - PRESSURE-CONTROLLED MACHINE, IN PARTICULAR PARALLEL AND IN-AXIS ROTARY PISTON MACHINE OR PUMP WITH COMBINATION - Google Patents

Description

PATENT AGENT ÜIPL.-ING. GERHARD SCHWAN

OFFICE: 8000 MUNICH 83 ELtENSTRASSE 32

Dec 28, 1973

72-CHL-5O5

EATON CORPORATION
1OO Erieview Plaza, Cleveland »Ohio 44114, V.St.A.

Pressure medium-operated machine, in particular parallel and
internal-axis rotary piston engine or pump with

Combing engagement

The invention relates to rotary motors operated by pressure medium
or pumps and is concerned in particular with a control slide arrangement for parallel and internal-axis rotary piston machines with meshing engagement.

The machine according to the invention is particularly suitable as a belt drive motor with a rotating housing, which is a conveyor belt,
Drives timing belt or the like. The invention is therefore explained in more detail below using such a motor. However, the control slide arrangement described can also be used with each
any other pressure medium operated machine used
be, in which a displacement organ executes a rotary movement with respect to another displacement element, as is the case with internal-axis rotary piston machines with meshing engagement.

Show internal-axis rotary piston machines with meshing engagement
an internally toothed, annular component with a number N of

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TELEPHONE: 0811/6012039 CABLE: ELECTRICPATENT MUNICH

Teeth, within which an externally toothed component is eccentrically arranged, which has a smaller number (N-1) of teeth and, together with the internally toothed component N, forms increasing and decreasing displacement cells when the one component makes a rotary movement with respect to an axis of the other component. An imaginary plane containing the axes of the two components, the plane of eccentricity, separates the ₅ increasing displacement cells located on one side of the plane from the decreasing displacement cells located on the other side of the plane. The plane of eccentricity rotates with the speed of the rotating component of the machine. The displacement cells on one side of the plane of eccentricity are connected to the high pressure side and the displacement cells on the other side of the plane of eccentricity are connected to the low pressure side of the machine via a control slide arrangement.

Various arrangements are known in order to ensure the required, functionally appropriate application of pressure medium. A known solution works with a so-called commutator control slide. A first slide element is provided with a number b < of pressure medium channels, each of which is connected at one end to a displacement cell. The other end of the N ports is sequentially connected to 2 (N-1) ports of a second slide member. The 2 (N-1) passages of the second slide element are in turn connected to the pressure medium inlet and the pressure medium outlet.

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N-1 passages of the second slide element "those with the pressure medium inlet are connected, alternate with N-I passages from ι which are connected to the pressure medium outlet. The relative Rotary movement of the Verdrängerba jtei'ie is used om over a cardan shaft to drive the second slide element and to provide the desired cycle and sequence control.

Such control slide arrangements work satisfactorily. However, they require a large number of individual parts that have to be manufactured with small tolerances in order to ensure the correct cycle sequence. This becomes particularly critical when the rotary piston machine is equipped with a large number of displacement cells in order to ensure very smooth operation . Additional problems arise when using an in-axis rotary piston machine. Meshing is used as a belt drive motor, in which the outer housing and not the output shaft rotates. Play in the drive assembly of the belt drive motor due to wear easily leads to undesirable orbital motion of the rotating casing. Such a belt drive motor * is known from US Pat. No. 3,552,893. It is provided with a conventional control slide arrangement which has an inner valve piston-shaped slide part and a slide sleeve and is actuated in the above-mentioned manner via a cardan shaft. Cycle errors can occur due to torsional deformations of the drive connection between the first and the. second component come. Another problem arises from the fact that a very long motor housing is required

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-A-

is to provide enough space for high-performance, radially loadable bearings to create, as in most use cases of Belt drive motors are necessary. The extra length is primarily due to the use of propeller shafts for propulsion traced back the slide parts.

Accordingly, it is the object of the invention in particular based on a belt drive motor in the form of an internal To create a rotary piston engine, which is equipped with a simplified, reliable control slide arrangement is. A conveyor motor is to be created which has a rotating outer housing and in which the opposite Ends of a fixed through shaft so formed are that over them the pressure medium supply to the engine and the pressure medium discharge from the engine. One of the displacer parts should stand still while the other rotates and rotates executes in order for an improved spool function to care. It is also intended to provide a novel, positively acting control slide arrangement for a pressurized-medium-operated machine, in particular a parallel and internal-axis rotary piston engine or pump can be created with meshing engagement.

According to the invention, an elongated component is provided which is provided with an inlet and an outlet portion at its opposite ends. In the middle area of this component an externally toothed internal gear is permanently attached. An internally toothed one annular external gear includes the externally toothed

/^r,.^-; 409828 / a34 3 ... - ,. - ·

Eccentric internal gear. Comb the teeth of the two gears with each other and form enlarging and shrinking displacement cells, while the two gears perform a relative orbital and rotary motion. Because of the different teeth number of gears leads to an orbital movement of the external gear around the axis of the internal gear to a rotation of the external gear, which in turn is transmitted via roller or pin connections to a housing that is the housing of the belt drive motor forms.

According to a further feature of the invention, a number N of discontinuous or stepped recesses emanate from each axial end face of the external gear, which open into the internal surface of the external gear at points which are in the area of the displacement cells. Opposite each axial end face of the external gear is a stationary housing face which has an equal number N of passages. The passages and recesses are aligned and arranged in such a way that the orbital movement of the external gear provides a pressure medium connection between certain passages adjacent to the one axial end face and all expanding displacement cells as well as a pressure medium connection between certain passages adjacent the other axial end face and all decreasing displacement cells. In this way, all of the enlarging displacement cells lying on one side of a plane of eccentricity can be connected to the high-pressure side from one axial end face, while all of them

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shrinking displacer cells on the other side of the Eccentricity plane over the other nxial face with the Be connected to the low pressure side.

The invention is explained in more detail below using a preferred exemplary embodiment. In the; attached drawings show:

Figure 1 is a view of one end face of an engine,

Figure 2 is a section of the engine along line 2-2 of FIG Figure 1, and

Figures 3, 4, 5, 6, 7 and 8 are cross-sections along the respective ones Lines of Figure 2.

FIG. 2 shows a belt drive motor 10 for driving a conveyor belt (not shown). The engine 10 includes a housing assembly A which houses a displacement device B and a spool assembly C. The housing arrangement A has hollow cylindrical housing end parts 14 ₉ 15 which rest against an annular housing part 16. Depending on the desired direction of rotation of the housing arrangement A, pressure medium is supplied via the housing end part 14 or the housing end part 15 and discharged via the other housing end part. In the housing end parts 14, 15 a one-piece through shaft 12 is mounted, which is integrally connected in its middle section to an externally toothed internal gear 18. It goes without saying that it is in principle also possible to use the externally toothed internal gear as

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' BATH

to manufacture a separate component and then to attach it firmly to the shaft 12. The displacement device B includes the internal gear 18, which is eccentrically encompassed by an internally toothed ring-shaped external gear 20, which in turn sits within the ring housing part 16, - Via a roller drive 23, the combined revolving and rotary movement of the external gear 20 is converted into a pure rotary movement on the housing A implemented. The structure and mode of operation of the roller drive are known in detail from US Pat. No. 3,389,618. The control slide arrangement C has control slide elements 24, 25, which are seated within the housing end parts 14, 15 and which each seal against an axial end face of the external gear wheel 2O. Slide passages 26,27 of the control slide elements 24,25 come _{into connection with discontinuous or discontinuous recesses 28 β} 29, which are provided on the opposite axial end faces of the external gear 2O, when the external gear wheel 2O rotates around the internal gear wheel 18 are. ■

The cylindrical.Ringgehäuseteil 16 sits between the inner axial end faces 3O, 31 of the housing end parts 14, 15, whose outer axial end faces are designated by 32 and 33. Between the housing end 14 _S 15 and the annular housing part 16 shims 36 .are used on .the Urafangsflächen. the housing parts protrude and serve as guides for a multi-part, not illustrated tape. The spacer disks 36 and the housing parts 14, 15, 16 are connected to one another by means of an appropriate adhesive, for example epoxy resin

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connected to provide a compact construction. It understands that the housing assembly A held together in other ways can be, for example with the help of screws or by screwing the housing parts together.

The inlet housing end part 14 has an elongated chamber 38 extending from the end face 32 and having a bore 40 Larger diameter is in connection, which extends to the inner end face 3O of the housing end part 14. In a similar way the outlet housing end part 15 is provided with an elongated chamber 39 which extends from the end face 33 and with a to the end face 31 reaching bore 41 is in communication. There are recesses in the chambers 38, 39 of the housing end parts 14, 15 designed to accommodate needle bearings 42, 43 and seals 44, 45, by means of which the one-piece shaft 12 reaching through the chambers 38, 39 is supported and sealed. The wave 12 is provided with inlet and outlet connections 48,49, the opposite flats 5O for receiving a C-shaped, Have not illustrated tensioning device to prevent rotation of the shaft 12.

Bores 53, 54, closed with plugs at their outer end, extend from the outer surface of the housing end parts 14, 15 to a point beyond the chambers 38 and 39, respectively. Two longitudinal lubrication channels 56, 58 and 57, 59 run from the bores 53 and 54, respectively inner end face 3O _f 31 of the housing end parts 14 and 15. They allow the roller drive between the external gear

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2Ö and the ring housing part 16 to lubricate by leaking Pressure medium via the shaft clearance 60.61 from the high pressure to Allow the low pressure side to reach.

The N teeth 21 of the external gear 20 are formed by rollers in a manner known per se. The internal gear 18 has N-1 external teeth. The eccentricity e corresponds to the distance between the axis 64 of the external gear and the axis 65 of the internal gear. As is apparent from Figure 4, the teeth of the gears 18,2O N form Verdrängerzellen 22, wherein all enlarging Verdrängerzellen on one side of the axes 64 _r 65 containing rotating eccentricity YY and all contracting Verdrängerzellen are on the other side of this plane. In the embodiment illustrated in Figures 4, 5 and 6, N is equal to 14-

If the internal gear 18 is held against rotation, this leads to: External gear 2O a hypocycloid revolving movement around the internal gear 18, the axis 64 describing a circle around the axis 65, the radius of which is equal to the eccentricity e. At this Movement of the external gear 20 becomes each of the N positive displacement cells 22 enlarged and reduced while the external gear 2O rotates by a distance corresponding to a tooth width. The plane of eccentricity Y-Y rotates at an angular speed that is equal to the rotational speed of the external gear 20.

On the outer surface of the external gear 2O are a plurality of in

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- 1O -:

Axially directed grooves 67 arranged distributed around the direction are provided, while the inner surface of the annular housing part 16 is seen with an equal number of grooves 68. The grooves 67,68 of the external gear 2O and 16 form Ringgehäuseteiis to - "- \ sqmmen a plurality of split holes 69. In each hole 69; sits a drive roller 70. About the drive rollers 7O the \\ ν ·, ring housing part 16 in the same direction and with the same; [. Speed as the external gear rotated 2O. In order for the most uniform possible drive connection between the external gear 2Q and; ■ the annular housing part 16 to ensure, in both directions of rotation, the number of drive rollers 7O and the divided punch 69 is roll equals the number of Verdrängerzellen 22 and are the driving 'and the holes 69 on radial lines intermediate the angular ■■> ■ · _ j see the rollers forming the teeth 21 cut in half. The effective J. diameter of each divided hole 69 is equal to the diameter>,:; /, of the drive roller 7O plus the eccentricity e of the gears 18 _t 2o ₃ "I- _.; This relationship ensures that only the rotary movement, not *" · tf *. but the orbital movement of the external gear 2O is transmitted to the ring housing part 16. .

The cylindrical spool members 24,25 are in the off: arranged classified bores 4O and 41 so firmly that the axial end faces 72 ^ 73 of the control valve members 24,25 are aligned with the · · ■ ■ end faces 30,31 of the housing end 14 _S 15 . A central opening extends through the control slide elements 24, 25, with slight play for receiving the shaft 12 being provided. Pie control slide elements 24,25 are, for example, about

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a press fit, set in the bores 4O, 41 so that. they rotate together with the housing 16. The axial length of the control slide elements 24, 25 is somewhat smaller than the oxiole length of the bores 4O, 41 of the housing parts. "1 4,1 5, .. to form annular openings 74 and 75, respectively.

As can be seen from FIGS. 2 and 8, the N slide passages 26, 27 of the control slide elements 24, 25 protrude, and the openings 74, 75 are connected to four radially directed passages 76, 77 of the shaft 12. The passages-76 _f 77 are in turn connected with longitudinally extending inlet and outlet passages 78,79 at the opposite ends of the shaft 12th Since the arrangement is illustrated here as an engine, all of the inlet slide passages 26 can be connected to the high pressure side and all outlet slide passages 27 can be connected to the low pressure side of the machine.

As can be seen from Figure 3, the slide passages 26 of the Control slide element 24 with one another the same dimensions; the slide passages 26 are also equidistant from one another distributed around the circumferential surface of the control slide element 24. It should be emphasized that the input control slide element aligned in the bore 4O in such a way, aa3 after assembly a slide passage 26a lies on one side of a line perpendicular to the plane of eccentricity (the one illustrated in FIG Position this is the axis 64), while a diametrically opposite slide passage 26b on the other side

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this line runs. Thus, according to Figure 3, the passage 26a extends from the axis 64 upwards, while one side of this
Passage essentially in line contact with axis 64
stands. The passage 26b, however, extends from the axis 64 to
below and is also with its one side surface practically in line contact with the axis 64. In order to align the passages 26a and 26b in the best way, the line is used as a. axis
of the housing 16 is defined perpendicular to the final assembly
the plane of eccentricity. The slide passages 27 of the
Control slide member 25 raised the same size as the slide passages 26; they are distributed in the circumferential direction at equal intervals around the outer surface of the control slide element 25.
It should be emphasized that the outlet control slide element 25 is aligned in the bore 41 as a mirror image with respect to the control slide element 24. As shown in Figure 7 seen _s extends a passage 27a substantially of, that of the corresponding Einlaßdurehlasses 26a is opposite to one side of a plane perpendicular to the eccentricity axis of the housing 16 in a direction corresponding to that. The corresponding diametrically opposed passage 27b goes from the other side of this line in one
Direction from » ai-a is opposite to that of the corresponding inlet port 27a. In the position illustrated in FIG. 7, one side surface of the passage 27a is essentially in line contact with the axis 64 and extends therefrom
Passage from the axis 64 downwards, while a side face
de ^ Through kJ.sses 37b _essentially: is in line contact with the axis 64 and / on, this axis runs upwards from. -The Ph-

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The position of the valve passages 27 thus represents a mirror image of the phase position of the valve passages 26 ₃ and vice versa "

According to Figure 2, the outer gear 20 oe each of its rs · · '·· len end faces 80,81 with a number N of discontinuous licnsr:.!, Or non-through recesses 28,29 provided. The openings 28, 29 can cooperate with the relevant slide valve bodies 26, 27. The recesses 28 are distributed in the circumferential direction at equal intervals around the inner surface of the external gear 20. They extend inward from the end face 8O and open into the inner surface of the external gear wheel 2O in such a way that they are connected to the displacement cells 22. In a corresponding manner, the outlet recesses 29 are distributed in the circumferential direction at equal intervals around the external gear 20, each recess extending inward from the end face 81 and opening into the inner surface of the external gear 20. From Figure 4 it can be seen that one edge of the recesses 28, 29 starts from a radius of the external gear 20 that the recesses 28 and 29 are at a small angle cC in front of or behind the center of the associated displacement cell, depending on of the direction of rotation of the external gear 20 and of whether the recess 28 or 29 is an inlet or an outlet channel.

Because each displacement cell 22 runs between adjacent teeth 21 of the external gear 20, each of the recesses 28, 29 extends in width from one tooth 21 to a point which corresponds to half the distance between adjacent teeth. There-

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it should be emphasized that the discontinuous; Recesses are arranged with respect to the teeth 21 of the outer gear 20 that the lying on the inlet side & r: recess er. 2.8 are a mirror image of the recesses 29 on the outlet side, namely in the same way as was _{discussed above for the inlet and outlet slide passages 26 and} 27. Thus, according to FIGS. 4 and 6, there is an inlet recess 28x adjacent to tooth 21x, while the corresponding outlet recess 29x is arranged adjacent to tooth 21y. The space between the teeth 21 χ and 21y forms a displacement cell 22k. In addition, the height of each recess 28,29 must extend beyond the slide passages 26,27 by a distance which is at least equal to the eccentricity e of the arrangement.

At a certain point in time and in a certain position stand, as can best be seen from FIGS. 4 and 6, N / 2 Inlet passages 26 in connection with recesses 28, which lead to widening displacement cells lying on one side of the plane of eccentricity, while N / 2 outlet passages 27 are connected with recesses that decrease in size- ' the displacer cells on the other side of the plane of eccentricity to lead. This relationship is maintained in the illustrated embodiment ensured by the dimensioning of the slide openings 26,27 and the recesses 28,29. Is the width of a displacer cell as the circumferentially measured distance between defines two radial lines emanating from the center of the housing or axis 64 and adjacent ones forming the teeth

t-ίϊ ■; ". J

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Halve rolls, and becomes about half that distance from those formed by the rolls. Teeth occupied, the remaining half the distance is divided equally between the recesses 28,29. The SchieberdurchiäSHs 25,27 take essentially the same width as the. Recesses 28 ..29 to ensure a suitable flow of pressure medium between the DurchJaasen and the recesses. The control slide cycle can be set by varying the width of the slide openings 26, 27 and the recesses 28, 29.

On the inlet side, a specific inlet passage 26a is always assigned to the same recess 28x and the same displacement cell 22x. The same assignment applies to the outlet side. Thereby, the manufacture and assembly of the device are considerably simplified. .

The control slide arrangement C also has a pressure relief channel 86 which extends diagonally from one to the other end face of the displacement device B, as can be seen from FIGS. 2, 4, 5 and 6.

The housing assembly A is firmly seated in an unillustrated one Receiving the flats 5O of the inlet and outlet port 48, 49 to prevent the shaft 12 from rotating. A ribbon or strap (not illustrated) with three separate, side-by-side sections is wrapped around the Wrapped around the outer surface of the housing assembly A, each band

section between the outwardly protruding spacer washers 36 fits and is guided by these.

Pressurized pressure medium, for example pressurized oil, is introduced into the inlet cone 78 by a pump (not shown) and passes through the radially extending passages 76 into the annular opening 74 and from there into the slide passages 26, all slide passages 26 being pressurized. Because of the geometric relationship between the slide passages 26, 27 ″ and the recesses 28, 29 illustrated in FIGS. 4 and 6, a connection only takes place between the inlet slide passages 26 and the inlet recesses 28, which enlarge with lying on one side of the plane of eccentricity YY Displacement cells 22. In a similar way, on the low-pressure side of the arrangement, the decreasing displacement cells are only connected via the associated outlet recesses 29 with outlet slide valve ports 27. The pressure medium passes from outlet slide ports 27 via the annular opening 75 into the radially extending ports 78; it flows from there via the outlet channel 79 to a collecting container (not shown). During operation, the control slide elements 24 and 25 rotate in synchronism with both the housing 16 and the external gear 20 de of the recesses 28 _r 29 of the external gear 2O a complicated orbital movement with respect to the associated inlet or outlet passage 26,27 <jus. This relative movement represents the for

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the pressure medium connections required for the machine to work here.

Pressurized pressure medium introduced at the inlet side of the machine causes the external gear wheel 20 to rotate and revolve around the internal gear wheel 18 counterclockwise (FIG. 5) in this way. However, only the rotary movement of the external gear 20 can be transmitted to the ring housing part 16 via the drive rollers 7O. A rotary movement of the housing arrangement A ₁ thus occurs, as a result of which a band, belt or the like is driven. If the pressure medium inlet and outlet connections are reversed, the motor runs in the opposite direction.

The drive rollers 7O are lubricated by pressure medium, the via the small shaft play 6O on the high pressure side of the machine exits and the drive rollers 7O via the bore 53 and the lubrication channels 56,58 is supplied. The pressure medium is drawn from the gap between the external gear 20 and the ring housing part 16 via the bore 54 and the lubrication channels 57, 58 in the housing end part 15 derived. Depending on the conditions on the inlet side of the machine, the pressure medium comes from the shaft clearance 61 into the annular opening 75 and from there over the radially extending Passages 77 into the outlet channel 79.

On the high pressure side of the displacement device B at the axial end face leaking pressure medium is via the pressure relief

409828/0343

stungskanal 86 to the lying on the low pressure side axial Front surface and leaves the machine in the normal way via the outlet slide openings 27 "

While the invention has been described above in connection with a motor, it is understood that the machine can also be used in a corresponding manner as a pump by the
Machine supplied under low pressure pressure medium and the housing assembly A is set in rotation.

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Claims (12)

- 19 A η s ρ r ü c h e Ί .'jsteuerschieberanordmjng for a pressure medium operated machine, in which. an internally toothed component is arranged eccentrically to an externally toothed component which has a smaller number of teeth, the two components with meshing engagement with the formation of a predetermined number of increasing and decreasing displacement cells can be moved against each other and with an eccentricity plane containing the axes of the two components increasing Verdrängerzellen separated on the one side of the plane of said contracting Verdrängerzellen on the other side of the plane, characterized by a first control slide element with a plurality of first slide passages which receive pressure fluid from the high pressure side of the machine, whose number is equal to the number of Verdrängerzellen and each of which is permanently assigned to a specific displacement cell, a second control slide element with several second slide passages, via which pressure medium reaches the low-pressure side of the machine, the number of which corresponds to the number of displacement ellen corresponds and each of which is permanently assigned to a specific displacement cell, by means that ensure a pressure medium connection between each expanding displacement cell on one side of the eccentricity plane and the associated first slide passages, as well as means that ensure a pressure medium connection between each decreasing displacement cell on the other side of the eccentricity plane and the assigned 4 0982 8 / QK 3 ■ - "" · '· - Provide 2O th second gate openings. 2. Control slide arrangement according to claim T, characterized in that the pressure medium-operated machine has a housing with an inlet which is constantly connected to all passages of the first control slide element, and an outlet which is continuously connected to all passages of the second control slide element, that the externally toothed component executes a rotary movement around the axis of the control slide elements and that each of the control slide elements has an axial end face which is in engagement with an axial end face of the internally toothed component in such a way that the passages in the two are due to the circumferential movement of the internally toothed component relative to the control slide elements Control slide elements are opened and closed. 3. Control slide arrangement according to claim 2, characterized in that that both axial end faces of the internally toothed component with several distributed in the circumferential direction in 'evenly spaced arranged 'discontinuous recesses' are provided, the number of which is equal to the number of displacer cells and of each of which starts from an axial end face of the internally toothed component and in its inhen circumferential area in the area a displacer cell opens. 4. Control slide arrangement according to claim 3, characterized in that that the slide passages and the recesses on one 409828/0343 axial face of the internally toothed component is a mirror image of the recesses and the slide passages on the other axial end face of the internally toothed component are arranged. 5. Pressure medium operated machine, characterized by a housing, an internally toothed component arranged in the housing, an externally toothed component seated in the internally toothed component Component, the internally toothed. Component provided with a predetermined number of teeth and eccentric with respect to the externally toothed component is arranged such that it can perform a rotary movement and a rotary movement, the teeth of the two components during their relative movement, forming a predetermined number of increasing and decreasing ones Combing displacement cells with one another, furthermore by means for mounting the internally toothed component in such a way that it perform an orbital movement with respect to an axis of the housing can, a first control slide element with a plurality of first slide passages, the number of which is equal to the number of Displacement cells and each of which is constantly assigned to a specific displacement cell, is a second control slide element with several slide gates, the number of which corresponds to the number of displacement cells and of which each one permanently specific displacement cell is assigned, means for a pressure medium connection between each of the enlarging Displacement cells and the associated first slide passages provide, as well as means for a pressure medium connection 409828/0343 between each of the shrinking displacer cells and provide the associated second slide openings. 6. Pressure medium-operated machine according to claim 5, characterized in that the first and the second control slide element are mounted such that they rotate synchronously with the rotational movement of the internally toothed component. 7. Pressure medium-operated machine according to claim 6, characterized in that the first and the second control slide element are arranged on axially opposite sides of the internally toothed component and, due to the rotational movement of the internally toothed component, the first and second slide passages in the first and second control slide element of the type open and it can be concluded that the pressure medium connection between each of the increasing displacement cells and the associated passages in the first control slide element and for the pressure medium connection between each of the decreasing displacement cells and the associated passages of the second control slide element is provided. 8. Pressure medium operated machine, characterized by a housing with an annular housing part, an internally toothed component arranged within the annular housing part, one between the internally toothed component and the ring housing part located drive assembly that a rotating drive movement between 409 828/0343 transmits these components and at the same time a mutual Orbital movement allows a rotatably.gelagerte in the housing .Wave, which forms a pressure medium inlet and a pressure medium outlet at its axial ends, a seated on the shaft and External toothed component reaching over part of the shaft, whose Number of teeth smaller than that of the. internally toothed component, the internally toothed component being eccentric with respect to the externally toothed component is arranged and can perform a rotary movement and a rotary movement with respect to this, while whose teeth of the toothed components to form a predetermined number of enlarging and reducing Displacement cells mesh with each other, and wherein the axes of the toothed components one during the operation of the machine determine the moving plane of eccentricity that the enlarging Displacement cells separates from the shrinking displacement cells, as well as by a control slide assembly that for a pressure medium connection between the inlet and the displacement cells lying on one side of the plane of eccentricity as well as for a pressure medium connection between the outlet and the displacement cells lying on the other side of the plane of eccentricity cares. 9. Pressure medium-operated machine according to claim 8, characterized in that that the Steuc.hieberanordnung a first control slide element with a plurality of first slide passages and a second control slide element with several second slide passages has that all the first slide passages are constantly with 409828/0343 the inlet and all second slide passages constantly with the Outlet are in pressure medium connection and that the first and the second control slide lines are arranged fixed to the housing in such a way that a relative movement between them is prevented. 10..DruGkmittelbetatigte machine according to claim 9, characterized in, that 'both axial end faces of the internally toothed Component with several distributed in the circumferential direction at the same distance secondary, discontinuous recesses are provided; » each of which has an axial end face of the internally toothed Component goes out and in its inner circumferential surface in Area of a displacement cell opens. 11. Pressure medium-operated machine according to claim 1O, characterized in that that the slide passages and the recesses on one axial end face of the internally toothed component are mirror images arranged to the recesses and the slide passages on the other axial end face of the internally toothed component are. 12. Belt drive motor., Characterized by a one-piece shaft with an externally toothed component extending over a central section of the shaft and on opposite shaft ends provided tubular sections which form a pressure medium inlet and a pressure medium outlet for the engine, a first hollow cylindrical housing section that attaches the shaft which includes one side of the externally toothed component and in which 409828/0343 the shaft is mounted, a second hollow cylindrical housing section, which sits on the other side of the externally toothed component and in which the shaft is mounted, a cylindrical one Ring housing section, which is connected to the first and the second housing section and with this together the Housing forms an internally toothed component whose number of teeth is greater than that of the externally toothed component and that is arranged within the ring housing section eccentrically to the externally toothed component and can be moved relative to it, wherein the teeth of the toothed components during the relative movement to form a plurality of decreasing and enlarging displacement cells mesh with one another, furthermore by a between the ring housing section and the internally toothed Component seated drive arrangement, by means of which the ring housing section is rotatable around the externally toothed component as a function of the hypocycloid movement of the internally toothed component. as well as by one functionally between the inlet at one end the shaft and the outlet at the other end of the shaft seated control slide assembly, which the inlet with the enlarging Displacement cells and the outlet with the shrinking displacement cells connects and the internally toothed component into one Causes hypocycloid movement around the externally toothed component, "4098 28/034 3 Blank page