DE2406659A1 - ADJUSTABLE FLOW CONVERTER CAN BE USED AS A PUMP, MOTOR OR GEARBOX - Google Patents

Description

Patent attorneys

~! ra.A ^: "^ cker _{1? #} February 1974

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DR. K. SCHUMANN - DIPL.-ING. P. JAKOB 2 4 UD 0 0 Ό

Henry Schottler

8008 Country Club Lane, North Riverside, Illinois, USA

Adjustable flow converter that can be used as a pump, motor or gearbox

The invention relates to an adjustable flow converter which can be used as a pump, motor or gearbox for introduction or extraction of energy in or from a pressurized liquid.

There is a need for energy converters, e.g. Motors, pumps, gears and the like. Can be used, have a low weight, are compact, easy to manufacture and work economically. There is also a need for an energy converter whose fluidity Displacement is variable over a large operating range. An energy converter of the aforementioned type should with minimal fluid loss, a uniform and varied

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generate constant flow of liquid. Another essential feature of an effective liquid energy converter should_ consist in the fact that the conveying direction without a significant influence on the efficiency and the displacement states of the unit can be reversed.

The invention is directed to a liquid energy converter to create that has the properties described above.

The energy converter according to the invention is characterized in that a rotatable shaft is provided to which a cylindrical, rotatably mounted Kdbenkörper is connected, that a first and second row of spherical pistons are provided, each of which has a plurality of spherical pistons mounted to move back and forth in piston cylinders. ^T iron, the Äolben cylinders are evenly spaced in the piston body so that several pairs of spherical pistons are formed that each pair of spherical pistons is assigned a piston chamber arranged in the piston body, so that a radial reciprocating movement of the spherical pistons displaces the adjacent ones The liquid contained in the piston chamber causes a first and a second cam track to be provided which enclose the first and second row of spherical pistons and each have a plurality of evenly distributed cam lobes that extend inward to the piston body and touch the spherical pistons of a row so that the Ball pistons come into engagement with the cam lobes as a result of the relative rotation of the piston body with respect to the docking tracks and are moved radially back and forth, as a result of which the transducer works with the displaced liquid volume from the piston chambers, compared to the relative back and forth movement of the kucje! Ko lben a piston pair Drotjortional is that a control device for Eavs-

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movement of the cam tracks and thus the mutual displacement of the rotating cam elevations of the first cam track is provided opposite the cam elevations of the second cam track to the liquid displacement volume of the transducer to change by changing the relative reciprocation of the spherical pistons of a pair of spheres, and that a fluid connector is provided, the fluid velches subsequent to each piston chamber during operation of the transducer to and from each piston chamber.

The converter according to the invention can be used both as a motor, as a pump or as a hydraulic transmission. The converter has a compact design and is highly efficient in operation. In addition, the converter works with a liquid displacement, which can be continuously changed within a certain displacement range, namely by one Zero funding in the positive or negative direction. The inventive The converter is therefore advantageously versatile and meets the most diverse requirements, e.g. the change in fluid displacement, the change the speed and the output torque.

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Further features, advantages and details of the invention result can be derived from the "following description of several preferred exemplary embodiments with reference to the drawing.

1 shows a sectional view through an exemplary embodiment the variable displacement piston pump according to the invention;

Figure 2 is a sectional view of the pump taken along line 2-2 according to Figure 1;

3 shows a sectional view through a second exemplary embodiment the adjustable piston displacement pump according to the invention;

3A shows a partial sectional view of the second pump example along the line 3a-3a of Figure 3;

4 shows a sectional view of the second embodiment along the line 4-4 of Figure 3;

5 is a partially sectioned view of a fluid transmission according to the invention and

Fig. 6 is a partially sectioned view of another Embodiment of a fluid transmission according to the invention.

The first exemplary embodiment of the pump according to the invention is shown in FIGS. 1 and 2 and is given the reference number 10 Mistake. The pump has an essentially cylindrical pump housing 12 with removable covers arranged at the end 14 and 16. An input shaft 20 is mounted in a bearing 18 which is arranged in the end cover 16.

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A high-pressure sealing ring 22 is mounted in a groove in the shaft 20, which separates the interior of the housing 12 from the Seals bearing 18 receiving housing part. This allows the pump 10 to be used for high pressures, as any Oil loss from "the housing 12 is prevented along the shaft 20. The sealing ring 22 also prevents contamination of the liquid delivered by the pump through a lubricant leak of the lubricant supplied to the bearing 18.

The bearing 18 becomes stationary within the front cover 16 by means of a sealing and locking device set. A snap ring provided in the locking device 24 locks the device in the cover 16. Suitable sealing rings 27a, 27b close the bearing section for the bearing 18 from the atmosphere. The input shaft 20 has a shoulder 20a, which to prevent ■ An axial movement of the input shaft against one side of the bearing 18 is applied, while an engaging in the shaft Snap ring 28 rests against the opposite side of the bearing.

As can be seen in FIG. 1, the inside At the end of the input shaft 20 a hollow, cylindrical piston body 30. To facilitate machining and assembly the piston body 30 is preferably formed in one piece with the shaft 20. In the illustrated embodiment, the piston body 30 has two rows of radially Piston cylinders 32 and 34 on. Every row of cylinders and 34 consists of several cylinders evenly distributed over the circumference of the piston body 30. With a.preferred Exemplary embodiment, row 32 has nine radially extending cylinders 32a to i and row 34 has nine radially extending cylinders Cylinder 34a to i. The rows 32 and 34 are also

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arranged so that the cylinders 32a to i and 34a to i cover in the axial direction, as can be seen in FIG. In addition, irehrere axially extending bores of the piston body 30 piston chambers 31, which form the cylinders of the series Connect 32 with the adjacent aligned cylinders of row 34. As can be seen in Fig.l, they act on each other adjacent cylinders, such as cylinders 32a and 34a, thereby come together to prevent the pump from operating 10 into the liquid filling located in the piston chambers 31 Initiate energy.

According to the invention, each cylinder of the rows of cylinders 32 and 34 is provided with a spherical piston which reciprocates when the input shaft 20 rotates. Are accordingly a row of spherical pistons 36a to i in the cylinders 32 to i and a second row of spherical pistons 38a to i in the cylinders 34a to i arranged. In the preferred embodiment, all of the spherical pistons 36 and 38 have the same diameter, which is chosen so that the balls seal the corresponding cylinder without any piston rings or the like. necessary In addition, the inner ends of the cylinders 32a to i and 34a to i are provided with liquid passages 35a to i and 37a to i. The passages 35 and 37 form openings for the flow of liquid during the operation of the pump 10 to and from the cylinders 32 and 34. The liquid passages 35 and 37 are also arranged such that each spherical piston 36 and 38 protrudes partially radially beyond the circumference of the piston body 30 during the operation of the pump IO.

The exemplary embodiment of the pump IO shown in FIGS. 1 and 2 has a stationary cylindrical axle journal 40 on. The stub axle is snugly in a flange 13

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stored, which is arranged on the left front side of the housing 12 is. Suitable sealing rings 42a and 42b seal the connection between the axle journal and the left housing cover 14 from. The journal 40 is dimensioned and machined so that it is with a small tolerance within the hollow Central piece of the piston body 30 is received. The piston body 30 rotates during operation of the pump 10 the axle body 40. In the illustrated embodiment, the liquid pumped by the pump 10 is used for lubrication of the engaging friction surfaces of the piston body 3O and the Achszaofens 40 used by the the rotation of the piston body and lubricant supplied by the radial forces acting on the spherical pistons 36 and 38 is squeezed between these surfaces, as will be described below.

The journal 40 has a series of bores, the inlet and form outlet channels for controlling the flow of liquid through the pump 10. The left front cover 14 is provided with an inlet bore 11 which connects to a liquid collection chamber 42, which in the adjacent End of the journal 40 is arranged. A plurality of inlet channels extend through the journal 40 in the axial direction 44 to a point adjoining the cylinders 32 and 34 of the piston body 30. In the one shown in Figs The exemplary embodiment is the journal 40 with four inlet channels evenly spaced from one another 44a to 44 $ which are connected to the liquid collection chamber 42 stay in contact. Ttfie the Fig.l shows, extend four equally spaced radial inlet stanchions 45 through the journal 40 and ensure a fluid connection of all four inlet channels 44a to 44d. The bores 46 coincide with the first one in the axial direction

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Cylinder bank 32 and connect the cylinders 32a to i one after the other with the inlet ports 44a-d when the piston body 30 rotates. As can be seen in FIGS. 1 and 2, covers a second row with four radial inlet bores 48 in the axial direction with the second cylinder row 34. The radial bores 48 are axially aligned with the P'idialbohrunoen 46 and connect the cylinders 34a to i with the four inlet channels 44a to d when the piston body 30 rotates.

The pump 10 also has a liquid outlet bore 15 which connects to an annular liquid collection chamber 41 connects. The journal 40 is also provided with four axially extending outlet channels evenly spaced from one another 43a to d, which are arranged distributed between the inlet channels 44a to d at an even distance. One Row of four radial outlet bores 45 coincides in the axial direction with the first cylinder row 32. The bores 45 are also evenly distributed in the journal 40 and set between the cylinders 32a to i and the Outlet channels 43a to d successively a fluid connection when the piston body 30 rotates. An additional row of radial outlet bores 47 coincides with the second, cylinder row 34 and connects the cylinder 34a to i with the outlet channels 4 3a to d when the piston body 30 turns. The outlet bores 45 and 47 arranged in the journal 40 coincide in the axial direction.

The pump 10 also has a pair of ring cams 50 and 60, which during the operation of the pump 10, the reciprocating movement the ball piston 36 and 38 control. As can be seen in Fig.l, the ring cams 50 and 60 enclose the Piston body 30, the ring cam 50 radially above the ball

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piston row 36a to i and the annular cam 60 are arranged radially above the ball piston row 38a to i. The inner peripheral surface the ring cam 50 and 60 is formed by concave cam tracks 52 and 62 against which the ball pistons 36 and 38 run respectively. The cam tracks 52 and 62 have a radius of curvature - which is slightly larger than the radius of the adjacent balls 36 and 38, so that the balls during operation of the pump 10 center itself within the cam tracks. The cam tracks 52 and 62 also have several evenly spaced apart mutually arranged cam ridges which have the effect that the ball pistons 36, which roll on the cam tracks or 38 are reciprocated as the piston body 30 rotates. In a preferred embodiment, the cam track is 52 equipped with four evenly spaced apart cam elevations 52a to d and the cam track 62 with four cam elevations evenly arranged to one another 62a to d. The cam peaks have a uniform amplitude and a uniform wavelength and are at profiled in the preferred embodiment so that they cause a cycloidal displacement of the spherical pistons 36 and 38. The construction described above results in a substantially uniform overall flow over the entire displacement area the pump 10 achieved.

The ring cams 50 and 60 are held in a relatively stationary position during operation of the pump 10. Su this one. For this purpose, the pump housing 12 has a pair of rotatably mounted toothed rings 66 and 68 which surround the ring cams 50 and 60, respectively. The toothed rings 66 and 68 are in a lateral movement. movement with respect to the housing 12 prevented. On the inner peripheral surface of the toothed rings 66 and 68 are splines 67 and 69, respectively, "which correspond to those on the adjacent outer member the ring cams 50 and 60 arranged Kpilnuten or wedge

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slits stand in singing riff. Leave the keyways 67 and 69 an axial movement of the ring cams 50 and 60 within the housing 12 and also ensure that the ring cams Rotate 50 and 60 depending on the rotation of the toothed rings 66 and 68 connected to them.

The pump 10 is also equipped with a device by which the pump displacement is increasingly changed can by adjusting the circumferential position of the ring cams 50 and 60. The adjuster has beveled teeth 66a and 68a, which are arranged on the inner part of the toothed rings 66 and 68. The teeth 66a and 68a mesh with

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a drive bevel gear 70, which is in the pump housing 12 by means of a shaft 72 is mounted *. The shaft 72- is by means of needle bearings 73 stored in the housing 12, the needle bearings are sufficiently dimensioned that they the reaction torque, which is introduced into the shaft 72 during the operation of the pump 10, can take up. On the shaft 72 are suitable Sealing rings 75 are arranged, which serve for a liquid-tight sealing of the housing 12. A control handle 74 protrudes beyond the housing 12 and is connected to the shaft 72. As can be seen in Fig.l, the drive bevel gear 70 is rotated by a rotation of the control handle 74 and thus the circumferential position of the toothed rings 66 and 68 and the associated Ring cams 50 and 60 adjusted. In the illustrated embodiment, a movement of the drive bevel gear shifts 70 the ring cams 50 and 60 by the same distance in opposite directions and changes the relative axial position the cam peaks 52a to d compared to the cam peaks 62a to d.

According to the Rinctnocken 50 and 60 are within the

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Housing 12 arranged in a certain relative position with respect to the journal 40 to ensure that the liquid displacement of the pump within a large range in either the positive or negative direction of one Zero funding can be changed indefinitely. The ring cams 50 and 60 are initially aligned so that the cam peaks 52a to d, 45 ° with respect to the cam elevations 62a to d are offset. It is thereby achieved that the foot apices of the cam elevations 52a to d align axially with the head apices of the cam elevations 62a to d and vice versa, as can be seen in FIG. Furthermore, the ring cams 50 and 60 arranged in the housing 12 such that the maximum opening of the pump is achieved when one of the spherical pistons 36 or 38 rests against the head apex of the cam elevations 52a to d or 62a to d and if the other is axially aligned Ball piston 38 or 36 against the apex of the other cam cusps 62a to d or 52a to d is applied. The zero delivery of the pump 10 is characterized by this arrangement. In the embodiment shown in Figure 2, this zero delivery occurs when the spherical piston 38a against the head apex the cam elevation 62a rests and when the axially aligned spherical piston 36a against the apex between the cam ridges 52a and 52d is applied. During this operating state of the pump 10, the spherical pistons 36a coincide 38a and the liquid passages 35a and 37a radially with the radial outlet bores 45 and 47 in the stationary journal 40, whereby the maximum opening state is reached. The remaining liquid passages 35b to i and 37b to i correspond to different positions with respect to the inlet and Outlet holes 45 to 4.8 in the stationary journal 40 and provide accordingly for different conditions at the channel openings.

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All axially aligned spherical pistons, i.e., spherical pistons 36a to 38a, 36b to 38b, etc., are the same as described above Zero delivery state either against the top of the head or the apex of the cam ridges 52a to d and 62a to d. Since each axially aligned ball piston pair (e.g. 36a and 38a) moves back and forth in opposite directions under these conditions is that of each pair of ball pistons on the 'within the piston chamber 31 and the connected cylinder (e.g. 32a and 34a), the pumping force exerted is zero. V7 during the Rotation of the piston body 30 is the liquid located in the piston chambers 31 in this state only between the adjacent cylinders 32 and 34 and the resulting liquid displacement of the pump 10 is zero.

To the delivery rate compared to the previously described Ilull funding to a faximal conveyance in one or the other direction of the liquid flow to change, will the control handle 74 is twisted. For example, the control handle 74 and drive bevel gear 70 can be rotated so that the ring cam 50 is rotated counterclockwise; and the ring cam 60 is rotated clockwise, from the illustration according to FIG. The cam superelevations 52a to d are thereby shifted axially with respect to the cam elevations 62a to d. Under such conditions it is effected the rotation of the piston body 30, that the ball pistons 36 and 38 reciprocate and a pumping force on the exert liquid filling located within the piston chambers 31 or a suction force which sucks the liquid filling into the chambers 31, depending on the position of the bores adjoining the piston chambers. The maximum Pumping and suction action and thus the maximum liquid displacement of the pump 10 in a positive direction

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24Ö6659

of the liquid flow is achieved when the fock overheights 52a to d are axially aligned with the cams 62a to d. This state is achieved in that the ring cams 50 and 60 can be adjusted by 45 relative to one another. Since each ring cam rotates, this corresponds to one Rotation of each ring cam 50 and 60 by 22 1/2 ° to establish this condition> In this position, the aligned yoke pistons 36 and 38 (e.g. 36a and 38a) move together back and forth and therefore generate in the cylinders 32, 34 and the piston chambers 31 a maximum pressure flow or Suction flow of the liquid. The ring cams 50 and 60 can be between the above-described liullförderungs- and maximum Funding status can be adjusted continuously so that infinitely many displacement states of the pump 10 result.

According to the invention, the ring cams 50 and 60 via the Be rotated in one direction away from the zero-funding state, which is opposite to the direction described above in order to reverse the flow of liquid in the pump 10. the Liquid flow is reversed because of the relative position between the liquid passages 35, 37 and the inlet bores 46, 48 and the outlet bores 45 and 47 is reversed. The inlet bores 46 and 48 are now outlet bores, and the outlet bores 45 and 47 are now grounded Inlet holes. The pump works in the same way and allows the flow rate to be continuously adjusted between the zero funding and the maximum funding. The zero delivery takes place again when the pump does the in Fig.2 assumes the state shown. The reverse "flaximalförderung" or "negative subsidy" would occur if the Ring cams 50 and 60 shifted by a total of 45 compared to raider become (this corresponds to one rotation of each

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Ring cams by 22 1/2) so that the cams ■ coincide axially, so that the cam elevation 62a coincides with the cam elevation 52d, the cam elevation 62b with the cam elevation 52c, cie cam elevation 62c with cam elevation 52b and cam elevation 62d with cam elevation 52a cover.

The symmetrical design of the pump 10 according to the invention enables the pump to have the same efficiency operates when the input shaft 20 is rotated either clockwise or counterclockwise. The function the pump 10 will therefore only be described for the case in which the input shaft 20 rotated clockwise as shown in Fig.2.

The clockwise rotation of the input shaft 20 causes the piston body 30 to rotate at the same rotational speed like the shaft 20 also clockwise. The piston body 30 drives the spherical pistons 36 and 38 like a planet around the stationary journal 40 around. The spherical pistons 36 and 38 also roll along the annular Cam tracks 52 and 62 and the cam peaks. 52a to d and 62a to d give the ball pistons 36 and 38 a radial reciprocation. Due to the profile of the cokken overhaul 52a to d and 62a to d cause the spherical pistons 36 and 38 to follow a cycloidal displacement curve.

The pumping action of the reciprocating spherical pistons 36 and 38 is a function of the relative location of the ring cams 5O and 60. If the ring cams 50 and 60 coincide with zero delivery, as shown in Fig.2,

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then the reciprocating movement of the spherical pistons 36a to i is opposite to the reciprocating movement of the spherical pistons 38a to i (E.g. the spherical piston 36a moves radially outward, while the adjacent spherical piston 38a moves radially moved inwards). Since the reciprocating relative movement of each pair of pistons is zero, the liquid flows under such a state in the common chambers 31 only between the adjacent cylinders 32 and 34 back and forth and the liquid delivery of the pump 10 is zero.

A liquid delivery takes place in the pump 10 when the control handle 74 is rotated and thereby the ring cams 50 and 60 moved out of the above-described zero position will. The positive maximum delivery occurs, for example, when the control handle 74 is rotated so that the rotation of the ring cams 50 and 6o by a total of 45 compared to the zero position. As both ring cams are moved by turning the control handle 74 rotate simultaneously, but in opposite directions, is the maximum conveying position in the case of the one shown Embodiment reached when the ring cam 60 to 22 1/2 ° is rotated counterclockwise with respect to the zero state shown in FIG. In such a Position of the head vertices are aligned over the cams 62a and the head apex of the cam elevation 52a in the axial direction, they xienn at an angular position of 22 1/2 ° are opposite the vertical in Fig.2. The rest Cam elevations 62b to 52b, 62c to 52c and 62d to 52d also coincide in the axial direction. The rotation of the piston body 30 therefore causes in this state that the ball pistons 36 and 38 move back and forth together, so that each pair of spherical pistons has a maximum pumping action on the piston chambers 31 and the adjacent cylinders 35 and

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37 liquid contained exercises.

The function of the pump 10 that results when the pump adopts the maximum delivery state is understandable when one imagines that the pump from the zero delivery position, which is shown in Figure 2, in the previously described maximum delivery set up is brought. If the piston body 30 rotates clockwise at a constant speed, then the spherical pistons 36a to i and 38a to i roll on the annular cams 50 and 60, respectively. The cam peaks 52a to d have the effect that the spherical pistons 36a to i move back and forth radially in the cylinders 32a to i, and so do the cams 62a to i cause the spherical pistons 38a to i to move back and forth radially in the cylinders 34a to i. When the piston body 30 rotates, the spherical pistons 36a-i and 38a-i move radially outward, if the liquid passages 35a to i and 37a to i a liquid connection with the inlet channels 44a to d to the produce radial inlet bores 46 and 48. Any outward movement of the ball pistons 36a-i and 38a-i therefore causes a suction stroke, through which liquid into the common chambers 31 and the adjoining chambers Cylinder 32a to i and 34a to i is sucked in from the common liquid collection chamber 42. Same way the rotation of the piston body 30 causes the spherical pistons 36a to i and 38a to i to move radially inward, when the liquid passages 35a to i and 37a to i have a liquid connection via the radial outlet bores 45 and 47 with the outlet channels 43a to d. Each inward piston movement therefore causes one Pressure stroke through which the liquid from the chambers 31 and the adjacent cylinders 32a to i

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and 34a to i into the common liquid collection chamber 41 is pumped. As can be seen in Fig.2 Et, is by this adjustment of the pump 10 achieves that each row of spherical pistons 36 and 38 (e.g. 36a and 38a) alternate one Performs suction and pressure strokes, so that a cycle is ended when the piston body 30 has rotated 90 °. on in this way, each row of spherical pistons performs four complete pumping cycles with one rotation of the input shaft 20. How also can be seen in Fig.2, are in this setting of the pump 10, the rows of spherical pistons 36 and 38 (e.g. 36a and 38a) with respect to the pump cycle in each operating condition of the pump 10 out of phase (e.g. one row of pistons begins the pumping or suction stroke, while the other row of pistons a pump or suction stroke ended, etc.). It results from the fact that the suction and pump strokes are offset laterally to each other, so that a uniform and. uninterrupted pump delivery is achieved.

The pump delivery can be infinitely variable between zero delivery and maximum delivery is adjusted by moving the ring cams 50 and 60 axially by adjusting the control handle 74 are offset against each other. The control handle 74 can also be rotated in the opposite direction so that a negative liquid flow through the pump 10

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follows. The negative liquid flow results when the ring cam 60 in relation to FIG. 2 against the clock clockwise and the ring cam 50 can be adjusted clockwise. With such setting, the circumferential position of the cam peaks 52a to d and 62a to d in relation to the outlet channels 43a to d and 44a to d and the radial bores 45 to 48 in the stationary "journal 40 reversed. The spherical pistons 36 and 38 move outward during a suction stroke when the adjacent fluid bores

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gene 35 and 37 with the inlet bores 46 and 48 of the journal 40 are in communication, and the ball piston 36 and 38 move inward during a pumping stroke when the liquid passages 35 and 37 with the outlet bores of the journal 40 are in connection.

The pump 10 therefore works in exactly the same way as has already been described, but the liquid drainage is through reverse the pump by moving the liquid outlet bore to the inlet bore and the liquid inlet bore 11 to the Outlet hole is. The negative maximum liquid flow is achieved when the ring cams 50 and 60 are so axial are set so that the vertices of the feet of the cam superelevations 62a with the vertices of the foot of the cam elevations 52 d cover. Such a setting of the cams 62a and 52d would with an adjustment of the ring cams 50 and 60 by 22 1/2 ° γοη of the vertical center line occur to the left of the pump 10 if the exemplary embodiment shown in FIG. 2 is used as a basis. the negative liquid flow through, the pump can also be continuously adjusted by the ring cams 50 and 60 to appropriate intermediate positions between the Zero position and the position described above for a maximum negative liquid flow brought v / ground.

Figures 3 and 4 show another embodiment of a continuously variable pump according to the invention. The pump 100 shown in Figures 3 and 4 work essentially in the same way as the pump 10 shown in Fig.l and 2. The pump 100 is, however, with lateral Connections are provided which permit the use of a stationary axle journal 40 arranged within the pump 10 superfluous. The side connections for the pump 1OO

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JIi

possible a more compact design of the pump, easier processing and better assembly. the Lateral connections also make it possible for the liquid channels within the pump 100 to be enlarged can and that the fluid friction losses are reduced.

The pump 100 has a substantially cylindrical Purapen housing 112 with a removable cover 114 arranged on the end face. A bearing is located in the front cover 114 118 arranged in which an input shaft 120 is mounted. A sealing ring 122 is in a locking device 124 arranged and seals the pump housing 112, 114. A snap ring 126 attaches the locking device 124 fixed within the front cover 114. In grooves of the shaft 120 snap rings 127a and 127b are used, whereby the input shaft 120 is prevented from moving axially. As can be seen in Figure 3, the interior is The end of the X-shaft 120 is rotatably mounted in a bearing that is arranged in the housing 112.

The pump 100 also has an annularly designed, rotatably mounted piston body 130, which is inside the Housing 112 is arranged between the ends of the input shaft 120. Arranged on the central part of the input shaft 120 Splines mesh with corresponding splines of the piston body 130. Through the spline between the piston body 130 and the input shaft 120 is caused that the piston body and the input shaft with the same Rotate speed while the piston body can be displaced in the axial direction, so that the piston body Center the ball piston yourself.

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The piston body 130 is provided with two rows of radially extending piston cylinders 132 and 134. With the one shown Exemplary embodiment, each row has nine piston cylinders 132a to i and 134a to i. The piston cylinders 132a to i and 134a to i are uniform over the circumference of the piston body 130 arranged distributed and fj Λten in the axial direction. In addition, several axially extending bores are provided in the piston body 130, the liquid piston chambers 131 form and adjoining one another for a fluid connection aligned cylinders, such as cylinders 132a and 134a, and which axial outlets for pump 1OO form. The rows of spherical pistons 136a to i and 138a to i are arranged in the piston cylinders 132a to i and 134a to i, respectively. The spherical pistons 136 and 138 in the illustrated embodiment have the same diameter and seal the Piston cylinder 134 and 136 off. The piston body 130 is also provided with liquid passages 135a to i and 137a to i provided which the inner ends of the piston cylinders 132a to i and 134a to i with the adjacent piston chambers 131 connect.

The pump shown in Figures 3 and 4 also has a Connection insert 140, which is provided with connection channels, by means of which the liquid flow through the pump is passed through. The insert 140 is ring-shaped and is arranged at one end of the pump housing 112 in such a way that that it engages around the input shaft 120 (at the left end of the housing in relation to FIG. 3). The connection between the insert 140 and the housing 112 is sealed by sealing rings 141 and several locking bolts 142 prevent the insert 140 from rotating within the housing 112. The bolts 14 2 allow lateral locking

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Postponement of the stake. 140 by a small distance, can assume a position of equilibrium when the pump is in operation is. A coil spring 143 is arranged coaxially to the input shaft 120 and extends between the housing 112 and the Insert 140 extends and biases the insert 140 in the direction of the rotatably mounted piston body 130.

The connection insert 140 is equipped with several channels that guide the flow of liquid through the pump 100. An inlet bore 111 provided in the housing 112 connects to an annular plenum 113 for the entering Liquid. The collective camera 113 is in turn with a row of four evenly spaced from one another axially extending inlet channels 144a to d in connection, which extend in the axial direction of the connection insert 140 extend. A second row of axially extending inlet channels 145a to d is also arranged in the end face Cover 114 arranged and coincides in the axial direction with the inlet channels 144a to d. Multiple radial and axial Running liquid channels 146 extend through the cover 114 arranged on the end face and the housing 112 and connect inlet passages 145a-d to plenum 113. Axial passages 144a-d and 145a-d are arranged to communicate with the piston chambers 131 of the piston body 130 come into connection when the piston body. by 130 turns.

The pump housing 112 also has an outlet bore 115, v / elche with an annular liquid collection chamber 116 communicates. Four evenly spaced apart axially through the insert 140 Outlet cannula 14 7a to d are connected to the liquid collection chamber

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mer 116 and the rotating piston chambers 131 of the piston * body 130 connected. A second row of axially extending outlet channels 148a to d is also arranged in the end face Cover 114 is provided, these outlet channels being aligned with the outlet channels 147a to d in the axial direction. More noble ones Radially and axially running liquid channels 149 extend through the cover arranged on the end face 114 of the housing 112 and connect the channels 148a to d with the liquid collecting chamber 116. As can be seen in FIG is, the inlet channels 144 and 145 and the outlet channels 147 and 148 form inlet and outlet ports on both sides of the piston body 130 are arranged in the same distribution. ,

• ·

The connections described above ensure that the KoI-KanBnern 131 successively with the inlet channels 144a to d, 145a to d and the outlet channels 147a to d and 148a to d are connected when the piston body 130 rotates. The reciprocating motion of the ball pistons 136 and 138, the is caused due to the rotation of the piston body 130, therefore causes a displacement of the liquid from the Inlet bore 111 through the pump to outlet bore 115.

The pump 100 is also equipped with a device that reduces the pressure between the rotating Piston body 130 and the stationary cover 114 arranged on the end face and the insert 140 are used. A low one Pressure between the piston body 130 and the adjacent stationary components is therefore desirable so that the Rotate piston body 130 at a high speed and the pumps can operate with high fluid pressures. As in 3 and 3A can be seen, the mutually adjacent

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adjacent surfaces of the piston body 130 and the stationary insert 140 and the cover 114 with annular pressure relief grooves 117a and 117b. A pair of radially extending slots 117c (see FIGS. 3A and 4) provide a direct connection between the outer pressure relief groove 117a with the Niederdruckiimenraum of the housing 112 ago. The internal pressure relief; nut 117b is also there in direct connection with the low-pressure interior of the housing 112, as can be seen from FIGS. 3 and 3A is. The grooves 117 and 117b reduce the pressure between the piston body 130, the insert 140 and the end face arranged cover 114 to a minimum. Correspondingly, the pump 100 only has a small area, that of the high pressure liquid in the pump 100 so that fluid friction losses are kept to a minimum v; he the.

The pressure acting on the rotating piston body 130 is further reduced by a pressure equalization device, which are arranged in the channels 144a-d and 147a-d of the insert, respectively. As Fig. 3 shows, A suitable pressure piston 180 is arranged in each channel 144a to d and 147a to d in the vicinity of the housing end 112. The outer side of each plunger 180 contacts the housing 112, and a sealing ring 181 ensures a liquid-tight seal of the corresponding channel. The inner end of each piston 180 forms a round pressure surface 182 which is arbitrarily larger than the Cross section of the channels 144a to d and 147a to d is formed. Those located in channels 144a-d and 147a-d High pressure fluid exerts in both axial directions the same in the cross-sectional area of the channels 144 and 147

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Compressive force, but the high pressure fluid exerts an unbalanced axial force (to the left with respect to the Fig.3) on the area A (see Fig.3A), the size of the contact surface between the piston body 130 and the Bet 140 is determined. The pressure area 182 of each piston 180 is a certain amount larger than the cross-sectional area of the channels 144 and 147, so that the pressure surface 182 acting liquid pressure causes a reaction force (with respect to the Fig. 3 to the right), which the against the Area A compensates for the pressure force acting. The pressure relief grooves 117a and 117b reduce the effective pressure area A. The effective pressure achieved by the pressure loss, which is also used tends to separate the piston body 130 from the insert 140, is approximately half the operating pressure.

Therefore, in the preferred embodiment, is the equalizing pressure area 182 (which is larger in diameter than the diameter of channels 144 and 147) is slightly larger designed as half of the opposite pressure surface A (see FIG. 3A), so that the pump 100 during operation generates a small fluid pressure and thus a small pretensioning force (in relation to FIG. 3 to the right), which serves to twist the rotating piston body in all load conditions of the pump for a secure seal 130 and the connections of the insert 140 and the cover 114. Such a liquid biasing force is supported the essentially constant pretensioning force of the compression spring 143. By means of the device described above, the Fluid pressure and that acting on the insert 140 and the piston body 130 during the operation of the pump 100 Reaction forces balanced.

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A pair of ring cams 150 and 160 are provided in the pump for reciprocating motion of the ball pistons 135a to i or 138a to i. The cams 150 and 160 are ring-shaped and encompass the piston body 130, being arranged in the radial direction of the ball pistons 136 and 138. The inner circumference of the ring cams 150 and 160 have curved skirt tracks 152 and 162, which have a slightly larger radius of curvature than the radius of the spherical pistons 136 and rolling on them 138.

The cam tracks 152 and 162 are equipped with a plurality of evenly distributed cam protrusions, against which abut the ball pistons 136 and 138 and which cause the ball pistons to reciprocate when the Piston body 130 of the exemplary embodiment shown in FIGS is rotated, and there are four evenly distributed cam lobes 152a to d and 162a-d on each cam track 152 and 162, respectively. The. Cam peaks v / iron an equal amplitude and Wavelength on and are designed so that they cause a cycloidal movement of the spherical pistons 136 and 138, so that the amount of liquid delivered by the pump 100 is essentially uninterrupted over the entire pump delivery area is even.

The ring cams 150 and 160 are during the operation of the pump 100 by means of two rotatably mounted toothed rings 166 and 168 are held stationary relative to one another. Toothed rings 166 and 168 are grounded by housing 112 and the Cover 114 prevented from axial movement. The inner surface of each ring gear has keyways 169 that are marked with

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mesh with corresponding keyways or slots located on the adjacent outer periphery of the ring cams 150 and IGO. The keyways 169 enable axial movement of the cam ring 150 and 160 _r within the housing 112 so that the ball plungers 136 and 138 is able to center in the cam tracks 152 and 162 itself. The keyways 169 also cause the ring cams 150 and 160 to rotate with the ring gears 166 and 168.

As already in connection with the description of the pump 10 was carried out, the displacement capacity of the pump 100 can be increased by adjusting the cam rings 150 and 16O to be changed. Beveled teeth 166a ur *: 168a are arranged on the inner part of the toothed rings 166 and 168, through which this setting can be made. The teeth 166a and 168a mesh with a drive bevel gear, not shown, which is connected to a control shaft 170. A control handle 172 is keyed to the shaft 170 so that an adjustment of the ring cams 150 and 160 can be made by hand. As already in connection with the description of the pump 10, rotation of the control handle 172 causes the cam rings to rotate. 15O and 16o caused by an equal amount in opposite directions, so that the axial position between the cams 152a to d and 162a to d is changed and thus the reciprocating movement of the ball pistons 136 and 138.

As has also already been stated, the ring cams 150 and 160 are initially in a certain position with respect to the Channels of the insert 140 and the lid arranged so that the pump 100 over a large liquid delivery area

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9)

can be set both in the positive and in the negative direction starting from zero delivery. The ring cams 150 and 160 are initially arranged in such a way that the cam peaks 152a to d are phase-shifted by 45 ° with respect to the cam peaks 162a to d. Such an alignment initially ensures that the apices of the cams 152a to d are axi .. ^! cover with the head apices of the cam ridges 162a to d and vice versa. In addition, the ring cams 150 and 160 in the housing 112 are set in such a way that a maximum channel opening for the pump 100 is achieved when one of the spherical pistons 136 or 138 rests against the head edge 1 of one of the cam lobes 152a to d or 162a to d and when the other axially aligned spherical piston 138 or 136 touches the apex of the other cam elevation 162a to d or 152a to d. Such a position corresponds to the zero delivery of the pump 100. During the full delivery of the pump 100, the outlet channels 147a and 148a are aligned in the axial direction, so that the connection with one of the piston chambers 131 located in the rotating piston body 130 is opened to the maximum. Since the axially aligned spherical pistons, such as, for example, spherical pistons 136a and 138a, lie against either the head apex or the foot apex of the adjacent cam lobes 152a to d or 162a to d, the spherical pistons move back and forth in opposite directions. The resultant delivery of the liquid contained in the piston chambers 131 is therefore zero.

To reduce the delivery rate of the pump from a zero-order state The control handle is used to increase to a maximum delivery state either in one or the other flow direction 172 rotated. In Figure 4, the pump 100 is in a such a position shown in which the maximum positive

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Delivery rate is achieved. The ring cams 150 and 160 are set so that the cam peaks 152a to d axially align with the cam elevations 16 2a to d and the cam elevations 152a and 162a are opposite to the vertical center line of the Puinpe 100 by 22 1/2 ° in relation to adjusted to the Fig. 4 to the right. One rotation of the piston body 130 clockwise causes a maximum liquid delivery of the pump 100 in a positive direction, the liquid entering through inlet bore 111 and exiting through outlet bore 115.

The setting of the pump 100 for maximum positive delivery is shown in FIG. Since the cam peaks 152a to d and 162a to d ^ sr ring cams 150 and 160 axially overlap, the overlapping ball pistons 136a and 138a, etc. move back and forth together. If that is, the piston body 130 rotates clockwise with respect to FIG. 4, then the congruent spherical pistons move 136i and 138i between the cam lobes 152d, 162d and 152a, 162a on the ring cams 150 and 160 radially Outside. At the same time, the piston body 130 assumes a position such that the piston chambers 131 with the spherical pistons I36i and 138i cover with the axially extending inlet channels I44d and 145d. The outward movement the spherical pistons I36i and 138i therefore create a suction force which removes fluid from the inlet collector 113 sucks into the adjoining piston chamber 131. The suction stroke continues when the piston body 130 is rotates and the connection opening between the chamber 131 and the inlet channels 144d and 145d is increasingly reduced.

The rotation of the piston body 130 then brings the ball piston

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ben 136i and 138i in a position which is shown by the congruent spherical pistons 136a and 138a in FIG. In this State, the piston chamber 131 coincides axially with the outlet channels 147a and 148a and the ball pistons 136i and I38i (which now correspond to the spherical pistons 136a and 138a shown in FIG. 4) approach ckm cam cusps 152a and 162a. The following rotation of the piston body 130 causes therefore that the ball pistons 136i and 138i with the cam lobes 152a and 162a come into contact and presses the balls radially inward, whereby this a pressure or Exercise the pump stroke. The liquid located in the chamber 131 is therefore via the outlet channels 147a and 148a in the liquid collection chamber 116 is pumped for the exiting liquid. The pumping stroke of the spherical pistons 136i and 138i is completed and a subsequent suction stroke is initiated, when the spherical pistons 136i and 138i remove those of the spherical piston 136b and 138b assume the position shown in FIG.

As shown in FIG. 4, the four cam increases cause 152a to d and 162a to d mean that each of the congruent spherical pistons rows 136i, 138i, 136a, 138a, etc. performs four complete suction and pressure strokes with each rotation of the piston body 130. In addition, the structure causes of the pump 100 according to the invention that the rows of covering one another Ball pistons perform the pressure or suction stroke in each operating state of the pump 100 at different times. The movement of the spherical pistons is therefore out of phase, so that a substantially uniform delivery of the liquid takes place by the pump 100.

The Fig.5 shows a first embodiment for a hydrostatic transmission 200 according to the invention. The GE-

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Drive 200 is designed for constant performance and is made up of a similar type of pump 100 as described above two units that are connected to each other in such a way that the speed can be changed.

In Figure 5, the right part of the transmission 200 is from a adjustable displacement pump 100A formed, both in construction and in operation essentially the corresponds to the pump 100 described above. The left part of the transmission 200 is driven by a hydraulic motor lOOB with variable Speed formed. The construction of the motor lOOB essentially corresponds to the Ρμπιρβ described above 1OO, but works in reverse.

The pump 100A of the transmission 200 is driven by the rotation of the Input shaft 220 driven. The pump 100A then conveys the liquid under high pressure into the motor 100B. Of the Motor 10OB in turn drives the output shaft 230. The liquid displacement of the pump 100A can continuously in a positive or negative direction in a certain range by adjusting the control lever 222 to be changed. In the same way, the liquid delivery of the motor 10OB can be steplessly adjusted by an actuation of the control lever 2 32 can be changed.

Since the arrangement of the components of the pump 100A and the motor 10OB is essentially identical to the arrangement of the components of the pump 100, which is shown in FIGS. 3 to 4, these components are not shown again in FIG shown. However, Figure 5 shows the fluid connections between the pump 100A and the motor 10OB in a schematic Way. The pump 100 «v has a housing 112A and 112A

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a connection insert 140A. In the housing 112A are a plurality of evenly distributed and axially extending liquid outlet channels 149A are provided, which the axially aligned outlet channels 147A of the connection insert 14OA and the channels 148A (the ones shown in FIG are not shown, see Fig. 3) connect with each other. The. Outlet channels 149A, 147A and 148, (not shown) are shared with a common annular outlet plenum 116A connected. The exhaust valve chamber 116A operates as the intake plenum 113B for the engine 10OB. As already in connection with the description of FIGS. 3 and 4 in detail, the liquid delivery of the pump 100A caused by the fact that the liquid emerges from the piston chambers 131A, which in a rotating Piston body 130A are arranged. The displaced liquid is collected in a common pool chamber 116A, in order to then be passed into the engine 10OB.

The pump 100A also has evenly spaced apart inlet channels, and channels 144a to d and 145a to d and connection channels 146, like this one already are shown in Figures 3 and 4. The inlet channels in 5 are not shown, are optionally arranged at a distance from the outlet channels described above and are communicated with an annular common inlet plenum 113B. The inlet plenum 113B operates in the same way like the outlet collecting chamber for the engine lOOB. In the engine 10OB there are several evenly distributed liquid inlet channels 146B arranged, which coincide with the outlet channels 149A of the pump 100A and connected to them are. The motor also has a connection insert 10OB, which is connected to the connection insert IQOA of the pump

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covers in the axial direction. The engine intake ports 145B are evenly arranged in the Kotor insert 14OB and distributed coincide in the axial direction with the outlet channels 14 7A of the pump 100A. As shown in Figures 3 and 4, has the engine 10OB also has intake ports 144B (not shown) which are axially aligned with and with the intake ports 145B these are connected via the inlet channels 146B ν. ^. The liquid gets into the itotor lOOB from the annular plenum 116A conveyed through channels 146B, 144B and 145B. The liquid then strcrat into the piston chambers 131B, -die are arranged in the rotatably mounted piston body 13OB. The motor 10OB v / e is also at an equal distance from one another arranged outlet channels 147a to d and 148a to d, as well as the connecting channels 149, 'as shown in FIG and 4 can be seen. These outlet channels for the engine 10OB, which are not shown in FIG. 5, are connected to the collecting chamber 116A in fluid communication with the collection chamber 116A as both an outlet collection chamber for the engine lOOB as well as an inlet collecting chamber for the pump 1ΟΟΛ serves.

The transmission 200 is also equipped with a compression spring 143A, which exerts an axial prestressing force on the mating connection inserts 140A and 140B. The compression spring 143A therefore presses the inserts 140A and 140B onto the adjacent piston bodies 130A and 130B, respectively, so that the liquid seal at the contact surfaces between the rotating piston bodies and the stationary connection insert is improved. In the flow path of the channels 147A and 145B, a common pressure piston 180A is arranged, the serves to distribute the compressive forces acting in the axial direction on the inserts 140A and 140B in the same way.

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3i

chen, as already in connection with the in Fig.3 pressure piston 130 shown has been described. In the transmission 200 according to the invention, the pressure piston 180A a central bore so that the fluid from the pump channel 147A through during operation of the transmission through the piston and into the engine inlet conduit 145B.

With regard to the other features, the construction of the pump 100A and the motor 1003 correspond to the construction of FIG Pump 100, which is shown in FIGS. In addition, the pumps 100 and 100A behave in operation exactly the same. The motor 10OB operates in the reverse manner of the pumps 100 and 100A and becomes vc;> is driven by the fluid supplied under pressure by the pump 100A to in turn drive the output shaft 230. As well as The motor 10OB as well as the pump 100 are continuously variable within a certain range in the positive or negative Direction adjustable.

During operation of the static transmission 200, the output speed and the direction of rotation of the output shaft 230 can be changed by operating the control lever 222 and. When the pump lOOA at its zero delivery is set, then no liquid is supplied from the pump 100A to the motor 10OB, and the speed the output shaft 230 is zero, regardless of how the setting of the IOTOR 10OB is made. When the pump lOOA dex "type is set that the liquid is pumping increases, then the output speed of the engine will take 10OB and the shaft 2 30 proportionally until they reach the respective maximum speed for the corresponding setting of the motor

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Reached IOOB. If the control levers 222 and 232 do so are set so that the pump 100A and the motor IOOB charged with the same amount of liquid, then the speed of the output shaft 230 corresponds to the speed of the input shaft 220 of the pump.

When the fluid displacement of the motor IOOB is smaller is 1ΌΟΑ than the selected delivery rate of the pump, then acts the transmission 200 as a transmission gear. When the fluid displacement of the motor IOOB is half of the selected Liquid delivery of the pump corresponds to 100A, then correspond the engine speed and the speed of the output shaft 23Ο twice the pump speed and the speed of the input shaft 220. When the motor IOOB fluid displacement is greater than the pump fluid displacement 100A, then the gear 200 acts in the same way as a reduction gear. When the engine displacement is twice the Pump delivery corresponds, then the speed of the output shaft 230 corresponds to half the speed of the input shaft 220.

In this way the motor IOOB and the pump 100A be continuously adjusted, so that a translation into slow or fast can be achieved by the transmission 200 can, whereby the gear ratios can be varied over a wide range. In addition, the direction of rotation of the output shaft 2 3o arbitrarily selected v / ground by the pump 100A is set so that either one positive or negative liquid flow is generated. Further, when the speed of the engine IOOB for any particular Pump setting is doubled, then the torque of the rotor shaft 230 is reduced by a factor of 1/2

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usv /. The transmission 200 is therefore very versatile and can be set in such a way as to meet the requirements placed on the transmission under the most varied of conditions to be fulfilled.

The. Fig.6 shows a second embodiment; gsbeispiel for a hydrostatic transmission 300 according to the invention. In contrast to the transmission 200 described above, the one shown is used Transmission 300 for generating an essentially constant output moment at a constant fluid pressure. As can be seen in FIG. 6, the transmission 300 has a pump 10OC and a motor 400, which in FIG Connection with the pump forms a variable speed hydrostatic transmission.

The construction and function of the pump 10OC contained in the transmission 300 corresponds to the features of those described above Pump 100A of transmission 200. Pump 100OC is driven by rotation of input shaft 320 and pumps the liquid under high pressure into the motor 400. The motor 400 then drives the output shaft 330. By adjusting the control lever 322, the liquid can be conveyed of the pump 10OC can be continuously adjusted in a certain range and in a positive or negative manner Direction. In this constant torque transmission 300, the fluid displacement is that of the coupled Motor 4 constant and corresponds to a multiple of the liquid delivery of the pump 10OG. With the one shown The exemplary embodiment is the liquid displacement of the motor about three times as large as the liquid delivery of the pump 10OC.

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The structural details of the pump 10OC have already been described in detail in connection with the pumps 100 and 100A. The pump 10OC has a housing 112C and a connector insert 140C. Four evenly spaced apart, axially extending liquid outlet channels 149C and 147C (and 148A _f see FIG. 3) are connected to a common annular outlet collection chamber 116C. The liquid delivery of the pump 10OC is caused by the fact that the liquid exits under pressure from the piston chambers 131C which are arranged in the rotating piston body 130C. This liquid is collected under high pressure in the collection chamber 116C in order to flow from there into the coupled motor 400. The plenum 116C serves as an inlet fluid swirl chamber for the engine 400.

The pump 10OC v / e is also four equally spaced apart inlet channels and lines 144a to d, 145a to d and the connecting channels 146 that are already are shown in Figures 3 and 4. These inlet conduits and channels are the aforementioned outlet channels 147C, 148A and 149C mutually associated so that the piston chambers 131C by the rotation of the piston body 130C during the Operation of the pump 10OC are successively connected to the inlet and outlet channels. The inlet ducts and lines (not shown in Fig.6) are with a ring-shaped Inlet Israel chamber 413 connected. The gear 3OO is designed so that the liquid from the motor to the pump is returned. The inlet collecting chamber 4 30 is therefore used also as a liquid outlet plenum for engine 400.

The motor 400 is housed in an enlarged housing 412. Four liquid outlet channels 449 and four liquid

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Fluid inlet channels 446 are arranged alternately distributed over the housing 412. The engine inlet ducts 446 adjoin the engine inlet plenum chamber 116c and the outlet ducts 149 adjoin the motor outlet plenum chamber 413. The outer end of the motor housing 412 is provided with a cover 414 arranged on the end face ¹ . r> sen. The cover 414 accommodates a suitable bearing 419 in which the output shaft 330 is supported. Snap rings 420 are inserted into grooves in the output shaft 330 and rest against the bearing 419 and prevent axial movement of the shaft 330 during the operation of the transmission 300. The cover 414 arranged on the end face also has a plurality of radially running liquid channels 449A and 446A, which directly adjoin the axially running channels 449 and 446, respectively. Four additional axially extending channels 449B and 446B are attached to the ra-. dial running channels 449A and 446Λ and connect the channels 449, 446 and 449A, 446A with the interior of the motor 400. Between the end cover 414 and the housing 412 suitable O-ring seals 401 are arranged, which for a liquid-tight seal of the channels 449 and 446 cares.

The motor 400 is also equipped with a ring-shaped connection insert 440, which in the axial direction with the pump insert 140C is aligned. Four inlet ports 444 are arranged in the insert 440 at an even distance from one another and in the axial direction in alignment with the engine inlet ducts 446B and pump outlet ports 147C and 148A. Those from the plenum 116c through the pump channels 147C pumped liquid 'is through this in The inlet ducts 444 located in the insert 440 are fed into the engine 400. The connection insert 44O of the motor 400 has

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also four outlet channels running in the axial direction 147, which are arranged at a uniform distance between the axially extending channels 444 (the channels 147 are not shown in Figure 6, but appear in Figure 3). The outlet channels 147 coincide in the axial direction with the engine exhaust ducts 449B and are connected to the engine exhaust collecting chamber 413 by the radial ducts 449C, which are shown in FIG. 6 with dashed lines.

The motor 400 also has a rotatably mounted piston body 430. The piston body 430 is with the output shaft 330 connected via suitable splines 421 so that the rotation of the piston body rotates the shaft causes. The piston body 430 of the transmission 400 corresponds to an enlarged version of one side of the piston body 130 of the pump 100 according to FIGS. 3 and 4. The piston body

430 of the illustrated transmission v / e has nine radially extending cylinders 434. In each cylinder 434 there is a backward and floating ball piston 438. Each cylinder 434 'is connected to an axial bore via a radial bore 437

431 connected. The bores 431 are in the piston body, per 430 arranged in such a way that they are axially aligned with the liquid channels 444, 447, 446B and 449B, if the piston body 4 30 rotates relative to the stationary insert 440 and the cover 414 arranged on the end face.

The motor 400 is equipped with an annular cam 450 on which the ball pistons 438 roll. The cam ring 450 encloses the piston body 4 30 and has a curved cam track 452, the radius of curvature of which is somewhat larger than the radius of the spherical piston rolling on it 4 33

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JO

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'3Sl

is. Like the cam tracks 152 and shown in FIG 162, the cam track 452 also has a plurality of curl superelevations arranged uniformly at a distance from one another, against which the ball pistons 438 run against. In the preferred embodiment of Figure 6, the cam track four equally spaced cams which have an equal amplitude and wavelength and which are further processed to have a Cause cycloidal movement of the ball pistons 438. The ring cam 450 is by means of a suitable device, such as a pin 451 fixed to the housing 412 is prevented from rotating. However, the pen leaves an axial movement of the annular cam 450 so that the ball pistons 438 and the cam track 452 are self-centering.

The motor 400 operates in the opposite direction as the previously described pump 100. When the pump 10OC a Pressure flow is generated, then the liquid is under high pressure from the pump 10OC via the inlet channels 444 and 444 446B in four. KoIbenkammerη 431 directed. The supplied High-pressure fluid flows into four piston cylinders 434 and presses the ball pistons 438 radially outward against the cam track 452 convert the radial to-and-fro movement of the Kugelkdben 438 into a rotational movement of the piston body 430 to. The movement of the piston body 430 causes the piston body to move connected output shaft 330 driven ^ As the piston body 430 rotates, the come with liquid filled four piston chambers 4 31 with the engine exhaust ports 147 and 449B in alignment. Those arranged on the - ■ cam track 452 Elevations then cause the liquid to be pushed out of the piston chambers 431 into the outlet channels

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449B and 147 and in the collecting chimney 413.

If the pump 10OC is operated in the negative direction, then the direction of rotation of the motor 400 is reversed. The liquid coming from the pump 10OC flows into the engine outlet passages 147 and 14913 and enters the alternating four piston chambers 431. Then tr ^ t the liquid from the r ^A otor 400 and enters the intake ports 446B and 444. In this inversion operation, the functions return the Flüssigkeitssarnmelkainmern 116C and 413 also in order.

As can be seen in FIG. 6, the transmission 300 furthermore a compression spring 143C which is clamped between corresponding surfaces of the pump 10OC and the motor 400. The compression spring 143C exerts an axially directed prestressing force on the aligned connection inserts 140C and 440 and presses the inserts against the adjacent piston bodies 130C and 430, creating a liquid-tight seal is achieved between the stationary inserts and the rotating piston bodies. A common plunger 180C is in the flow axis of the aligned channels 147C, and 148A, 147 and serves to balance the axial forces exerted on the inserts 140C and 440, the balance is achieved in the same way as in connection with the description of FIG. 3 with reference to the pressure piston 180 has already been executed. The pistons 180C v / iron a central bore so that the liquid from the pump channels 147C and 148C during operation of the transmission 300 through the pistons into the motor passages 444 and 444 147 flows.

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The hydrostatic transmission 300 is used to reduce the speed and to increase the torque and generates a substantially constant output torque at constant Fluid pressure. The speed reduction of the transmission 300 is achieved by the motor 400, its fluid displacement volume is greater than the delivery volume of the pump lOOC. In the illustrated embodiment the liquid displacement of the motor 400 is about three times as large as the liquid delivery of the pump lOOC. Therefore, at maximum pump delivery, the engine speed is approximately one third of the speed of the Pump corresponds to lOOC. The torque magnification properties of the transmission 300 are based on the fact that (if it is assumed that there are no liquid flow losses) theoretically the input power of the pump 10OC the output power of the motor 400 corresponds to each predetermined liquid delivery. Since the performance turns out to be The function of the torque multiplied by the speed results in the lower speed compared to the pump speed Speed of the motor 400 to a larger torque output of the motor 400.

The illustrated pumps, motors and gears according to the invention have many advantages. E.g. the performance the flow converter (pump or motor) is improved by the fact that the spherical pistons in the radial direction instead of in the axial direction Direction can be moved back and forth. When the pistons move radially, they support the spherical pistons in the pumps acting centrifugal forces the return movement of the pistons. Because the centrifugal force acting on the spherical pistons in the square of the speed of rotation of the spherical pistons

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takes, becomes the one responsible for pumping fluids into sininity required filling pressure is proportionally reduced when the device operates as a pump.

In addition, the use of the reciprocating spherical pistons in pairs creates a common KoI-benkarnmer in which Xolbenkkörev are connected, a liquid pumping of the Strömvmgswandlers allows the invention is changeable. For whom only a device with a reciprocating ball piston is used, like this is the case, for example, with the motor 400 shown in FIG Is the case, then the liquid pumping of the converter constant. The configuration of the preferred embodiment also enables the liquid pumping of the Converter infinitely changeable in a certain range and from an Ilullförderstatus either to a positive one or negative direction is adjustable. This feature of the invention results from the evenly spaced to each other and symmetrically arranged cam elevations on the adjustable cam tracks on which the Roll off the piston.

The preferred cam profile, the one cycloidal movement the spherical piston causes a steady flow of fluid through the converter. The cycloid Piston motion also reduces fluid flow rate, flow noise, erosion, and cavitation in the converter, since the spherical pistons are controlled in such a way that the piston acceleration is approximately zero when the subsequent liquid passages are open. The preferred use of nine pairs of ball pistons and eight adjacent ones Liquid passages (four flow channels and

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four outlet channels), in conjunction with the cycloidal piston movement, leads to an improvement in the fluid flow properties of the converter because the connection openings are produced with a faster increasing speed than the increase in the speed of the ball head.

The arrangement according to the invention of the piston chambers and liquid passages in the pump or the motor also lead to uniform flow conditions, low liquid flow speeds and small liquid friction losses. The invention provides a common fluid collection chamber for the inlet and outlet sides of the transducer (e.g., chambers 113 and 116 in Figure Z) to keep fluid suction and pressure changes to a minimum. The fluid passages in the transducer are designed to allow even fluid flow to and from the common collection chambers. In the embodiment shown in FIGS. 1 and 2, four pairs of spherical pistons 36 and 38 are simultaneously connected to the common inlet collecting chamber 42 via channels 44, 46 and 48. Since the suction strokes of the spherical pistons follow each other laterally, the inlet manifold 42 is simultaneously connected to four pairs of piston chambers, the pistons of which have different stroke positions (i.e. one pair of pistons is at the end of the suction stroke, one pair of pistons begins the suction stroke and two pairs of pistons assume a middle stroke position ). Likewise, in the pump 10 shown in FIGS. 1 and 2, four pairs of spherical pistons 3G, 38 are simultaneously connected to the common outlet collecting chamber 41 via the channels 43, 45 and 47. In this way it results

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that the liquid delivery in the collecting chamber 41, the is also effected in succession by the respective pairs of spherical pistons 36 and 38, uniformly and continuously he follows.

The modified pump 100 according to FIGS. 3 and. 4 is also provided with liquid passages that provide a uniform Create flow with minimal fluid friction losses. The pump 100 has large axial inlet channels 144 and 145 and outlet channels 147 and 148, which successively come into congruence with the common piston chambers 131, while the piston body 130 rotates. The inlet channels 154 and 155 lead from the common inlet manifold 113 to the piston carriages 131 and the outlet channels 147 and 148 lead from the piston chambers 131 to the common outlet collecting chamber 116. Because of this axial ducting On both sides of the piston body 130, the channel area in the pump 100 can be made very large, so that the flow rate and the fluid friction losses in the pump can be reduced. The design The pump 100 allows the channels downstream of the piston body 130 to be expanded to any size can be so that the flow velocity and the fluid friction losses are kept to a minimum will.

The embodiment shown in Fig.l and 2 of The invention also enables an adequate lubrication of the axle journal machined with close tolerances in a simple manner 40 and the piston body 30. Due to the radial stroke of each spherical piston 36, 38 only a small one is not balanced radial load in the journal 40, the

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2406653

Piston body 30 and the shaft 20 initiated. Since each of the nine ball pistons 36 and 38 of the piston pairs four strokes per Rotation of the piston body 30 executes, v / eil on the cam tracks 52 and 62 four! the radial direction of the resulting small, unbalanced force 72 times per "-" rotation of the piston body 30. For this reason, the journal 40 and the rotating piston body 30 is set in a weak vibration, through which a pinch lubrication zv / ischen the sicii contacting surfaces of the piston body and the pin is caused.

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Claims (1)

P 7830 Claims IJ Adjustable flow converter which can be used as a pump, motor or gearbox for introducing or extracting energy into or from a pressurized liquid, characterized in that a rotatable shaft (20,120) is provided with which a cylindrical, rotatably mounted piston body (30,131 ) connected is that a first and a two * .; -Ball piston series are provided, each of which has a plurality of ball pistons (36a to i, 38a to i, 136a to i, 138a to i) mounted back and forth in piston cylinders (32,34; 132,134), the piston cylinders being evenly spaced are arranged in the piston body in such a way that several pairs of spherical pistons are formed so that a piston chamber (31, 131) arranged in the piston body is assigned to each piston pair, so that a radial reciprocating movement of the spherical pistons displaces the one in the adjacent piston chamber contained liquid causes a first and a second ^ ockenbahn (52,62,152,162) are provided, which enclose the first and second row of spherical pistons and in each case several equally distributed arranged cam elevations (52a to d, 62a to d, 152a to d, 162a to d) which extend inward to the piston bodies and touch the spherical pistons of a row, FO that the spherical pistons as a result of the relative movement of the piston body s opposite cen cam tracks rait the - 46 - 409833/0859 Excesses come into engagement and are moved radially back and forth, whereby the flow converter with the displaced Fluid volume from the piston chambers works, which is the relative reciprocating motion of the spherical pistons of a pair of pistons is proportional to the fact that a control device (66 to 74, 166 to 172) for the movement .of the cam tracks and thus to the established time shift the cam peaks rotating in the circumferential direction the first cam track geqenüber the cam elevations of the second cam track is provided to the liquid displacement volume of the flow transducer by changing the relative reciprocating motion of the spherical pistons of a Piston pair is changed, and that a liquid connector (40) is provided which the liquid subsequently passes to and from each piston chamber during operation of the transducer. Adjustable flow converter that can be used as a pump, motor or gearbox for introducing or removing Energy in or from a pressurized liquid, characterized in that a rotatable shaft (20> 120) is provided with which a cylindrical, hollow, rotatably mounted piston body (30,130) is connected that a first and second row of spherical pistons is provided, each of which is several in itself Ball pistons (36a to i, 38a to i, 136a to i, 138a to i), the rows of spherical pistons being arranged in the piston body in such a way that that several pairs of spherical pistons are formed, that each pair of spherical pistons is arranged in the piston body Piston scanner (31,131) is assigned, so that a radial back and forth movement of the spherical piston causes a displacement - 47 - 409833/0859 the liquid contained in the adjacent piston chamber causes a first and a second cam track (52,62) are provided which coincide axially and the The piston body radially surrounds the first or second row of spherical pistons in alignment, so that each cam track has several evenly formed and evenly distributed cam elevations (52a to d, 62a to d, 152a to d, 162a to d), which extend inwardly towards the piston body and which are radially aligned Ball pistons touch a row, so that the ball pistons as a result of the relative movement of the piston body opposite the cam tracks with the aligned cams are superelevations come into engagement and are moved radially backwards, whereby the liquid from the piston chambers (31) depending on the relative reciprocation of the spherical pistons of each pair of pistons is displaced that a control device (66 to 74, 166 to 172) for movement the cam tracks and thus for the mutual displacement of the crouching cantilevers rotating in the circumferential direction the first -lockenbahn opposite the cam elevations of the second liockenbahn is provided to the liquid displacement volume of the flow converter to change by the relative reciprocation of the spherical pistons of a pair of pistons is changed, that a cylindrical Connection piece (40) is provided, which extends into the hollow central part of the piston body (30) extends and a plurality of radially extending inlet and outlet bores (46,48,45,47) which alternate in the same distance from one another are arranged distributed over the circumference of the connecting piece, so that the rotation of the The piston body opposite the connecting piece has the effect that each piston chamber (31) subsequently enters a liquid - 48 - 409833/0859 connection with the radially extending inlet and outlet bores comes that a liquid inlet sanitary chamber (42) is provided, which is arranged by means in the connecting piece Inlet channels (44a to d) is connected to the respective inlet bores (46,4 8), and that a liquid outlet collection chamber (41) is provided, which by means of outlet channels (43a to d) connected to the respective outlet bores (45, 47) is. 3. Adjustable flow converter that can be used as a pump, motor or gearbox for introducing or extracting energy in or from a pressurized liquid, characterized in that a rotatable Shaft (120) is provided, as well as a first and a second row of spherical pistons, each row having a plurality of piston cylinders has spherical pistons (136a to i, 138a to i) mounted so that they can be moved back and forth, the piston cylinders in evenly spaced are arranged in the piston body that the rows of pistons have an equal number of spherical pistons which are arranged in such a way that spherical piston pairs are formed v / earth that each spherical piston pair a piston chamber (131) arranged in the piston body is assigned, so that a radial back and forth movement the pair of spherical pistons causes the liquid contained in the adjacent piston chamber to be displaced, that a first and a second cam track (152,162) are provided which coincide axially and the piston body Radially aligned with the first or second row of balls enclose that each cam track several evenly formed and evenly distributed cam grooves rhöhunrren (152a to d, 162a to d), which - 49 - 4 09833/0859 extend inwardly to the piston body and touch the radially aligned spherical pistons of a row, so that the Ball piston as a result of the relative movement of the piston body in relation to the cam tracks with the aligned cam elevations come into Kingriff and are moved back and forth radially, whereby the converter with your displaced fluid volume from the KoIbenkaminern works / which of the relative reciprocating movement of the spherical pistons of a pair of pistons is proportional to that one. Control device (166 to 172) for the movement of the cam tracks and thus for the mutual Shift of the threatening in the circumferential direction Nockenüberhöhuncren opposite the first liockenbahn the cam lobes of the second cam track is provided to change the fluid displacement volume of the flow transducer by the relative reciprocating motion the spherical piston of each piston pair is changed, that a liquid connection device is provided, which the liquid during the operation of the flow converter below to and from each bi ο ib enk amme r Piston chamber leads away that the fluid connection device is arranged on each side of the piston body, having fluid connector (140, 114) axially aligned with depi piston body / the connector pieces axially extending inlet and outlet bores (145, 147, 146, 148) which are at equal spacing from one another distributed over the circumference, arranged alternately in the respective connection piece, the inlet and connect outlet bores to the piston body in such a way that that a rotation of the piston body causes each piston arm successively with the inlet and Outlet bores comes into communication and that a liquid collecting device (113,116) is provided with - 50 - 409833/0859 communicates with the inlet and outlet bores, so that the liquid is supplied to the inlet bores and is v / e directed from the outlet bores. 4. Flow converter according to one of claims 1 to 3, characterized characterized in that the spherical pistons (36,38,136,138) have the same dimensions and the same number of spherical pistons in each row of spheres is included and that the cam ridges (52a to d, 62a to d, 152a to d, 162a to d) of the cam tracks (52,62,152,162) are of uniform design and are arranged at corresponding locations. 5. Flow converter according to one of the address 1 to 4, thereby characterized in that the cam lobes (52a. to d, 62a to d, 152a to d, 162a to d) are profiled in such a way that they have a cycloidal to-and-fro movement of the rolling on them Ball piston (36,38,136,138) cause so that a a substantially uniform flow of liquid is generated through the flow vanfiler. 6. Ströraungswandler according to any one of claims 1 to 5, characterized in that the control device (66 to 74, 166 to 172) an adjustment of the cam tracks (52,62,152,162) in the circumferential direction between allows a maximum delivery position and a zero delivery position, the maximum delivery position then is taken when there is dip rjocking (52a to d, 62a to d, 152a to d, 162a to d) of the first and second cam tracks, which are common in pairs - 51 ■ - 409833/0859 The spherical pistons move back and forth in the adjoining common flow chamber, in cover in the axial direction, and the zero delivery position is assumed when the cam superelevations the first and second cam tracks which reciprocate the ball pistons of each pair in opposite directions cause radial directions in the adjoining common flow chamber, maximally against each other are out of phase. 7. Flow converter according to one of claims 1 to 6, characterized characterized in that the control device (66 to 74, 166 to 172) an adjustment of the Cam tracks {52,62,152,162) from a zero delivery position to a maximum conveying position made possible by the cam tracks in the circumferential direction against each other in a clockwise direction displaced v / ground, so that a liquid flow in a certain direction through the flow transducer takes place, and that the control device an adjustment of the cam tracks from the zero delivery position in the maximum conveying position made possible by moving the cam tracks counterclockwise by one To cause fluid flow in a second specific direction through the flow transducer, so that the control device enables a reversal of the liquid flow through the flow converter. 8. Flow converter according to one of Claims 1 to 7, characterized in that the control device Has cream rings (66,68,166,163), each connected to the riocVenbahnen (52,62,152,162) are, as well as a movably mounted drive pinion - 52 - 409833/0859 (70), which is in engagement with the respective toothed rings and the cam tracks are in opposite directions in the circumferential direction emotional. 9. Device according to one of claims 1 to 8, characterized characterized in that the cam tracks (52, 62, 152, 162) have a cross section provided with a curvature have, the radius of the curvature being greater than the radius of the spherical pistons resting against the tiockenbahnen (36,38,136,138). 10. Flow converter according to one of claims 1 to 9, characterized marked that de, * center of curvature of the cam tracks (52,62,152,162) in the axial direction from the central, center point of the ball pistons touching the cam tracks inwards is offset so that the reaction forces exerted by the ball pistons on the cam tracks change the cam tracks Press together and ensure that the cam tracks j η assume a stationary position in the axial direction. 11. Flow converter according to one of claims 1 to 10, characterized in that each radially running ball piston row nine ball pistons (36,38, 136,138) and each cam track (52,62,152,162) four im evenly spaced cams (52a to d, 62a to d, 152a to d-, 162a to d) have, so that the ball piston and the cam superelevation. require a substantially uniform and sustained flow of liquid cause by the flow converter. 12. Strömunrrswandler a ¹ of claims 1 to 11, characterized in that the liquid AO9833 / 0859 capacity fitting (40) a liquid inlet manifold (42), to which a plurality of inlet channels (44a to d) are connected, which are inserted into inlet bores (46a to d, 48a to d) open, which are evenly spaced from the spherical chambers (31) are arranged so that the connecting piece (40) further has a liquid outlet chamber (41), which are followed by several outlet channels (43a to d) which open into outlet bores (45a to d, 47a to d), v / elche at an even distance from the piston chambers (31) are arranged, and that the inlet and outlet bores are arranged alternately in the piston body (30), so that a rotation of the piston body each piston chamber (31) subsequently in a fluid connection with the sin- and x outlet bores come. 13. Flow converter according to one of claims 1 to 12, characterized characterized in that the cross sections of the piston chambers (31) and the inlet and outlet bores (46,48,45,47) are essentially the same size and that the inlet and outlet bores are arranged in an alternating manner so that each rotating piston chamber (31) closes an inlet bore and the following outlet bore opens essentially simultaneously. 14. Flow converter according to one of Claims 1 to 13, there- ' characterized in that four outlet bores (45 or 47) and four evenly distributed inlet bores (46 or 4 8) in an alternating arrangement are provided to each other. -54- 409833/0859 15. Flow converter according to one of claims 1 to 14, characterized characterized in that the flow converter is an adjustable liquid displacement pump (10). IS. Flow converter according to one of Claims 1 to 15, characterized in that the flow converter has an adjustable liquid displacement motor. 17 · Flow converter according to one of Claims 1 to 16, characterized in that the piston chambers (131) have bores which extend in the axial direction and extend through the piston body (130) and have a certain cross-section that the 3in-IaI? - and outlet bores formed in the fluid fittings (140,114) are arranged, have essentially the same cross section as the piston chambers, that the bores are distributed evenly spaced in the piston body and are arranged with the inlet or outlet. Auslaßbohrunaen on both sides of the piston body arranged fluid fittings axially cover so that each rotating piston chamber has a pair of aligned Closes inlet openings and substantially simultaneously closes a subsequent pair of aligned outlet openings opens. 18. Hydrostatic speed converter with a rotatably mounted input and output shaft and a liquid motor, depending on the drive of the Ausoancrswelle . of the amount of liquid supplied to the motor is used, whereby the speed converter has an adjustable fluid - 55 - 409833/0859 24,6659 SG Positive displacement pump which is connected to the input shaft and feeds the motor with the liquid as a function of the rotation of the input shaft, characterized in that a rotatably mounted cylindrical piston body vUOC; is rotatably connected to the Einanaswelle \ itO) that ine first and second row of spherical pistons are provided, each of which has a plurality of spherical pistons (36, 38) mounted so as to be movable to and fro in piston cylinders (32, 34), the Xolbenzvlinder at equal spacing in the Piston bodies are arranged in such a way that several pairs of spherical pistons are formed that each spherical piston pair is assigned a piston chamber (31) arranged in the piston body, so that a radial reciprocating movement of the spherical piston causes a displacement of the liquid contained in the adjacent piston chamber, that a first and a second cam track (o2, b2) are provided which coincide axially and radially enclose the spherical body in alignment with the first and second row of spherical pistons, so that each cam track has a plurality of uniformly formed and evenly distributed cam elevations (52a to d, 62a to d) which extend inwardly to the piston body and the radial flu right spherical pistons touch a row, so that the spherical pistons as a result of the relative movement of the piston body against the cam tracks with the aligned cam lobes come into alignment and move radially back and forth, whereby the liquid from the piston comb ^ rn (31) depending on the relative to and fro movement of the spherical pistons of each piston pair3 is displaced, so that a control device (322) for moving the cam tracks and thus for mutual displacement of the cam which coincides with each other in the circumference direction - 56 - 409833/0859 Elevation of the first cam track compared to the elevation of the cam the second cam track is provided to change the liquid displacement volume of the pump, by changing the relative reciprocation of the spherical pistons of a pair of pistons, and that a fluid connection device (14OC) is provided to x-zelche the liquid during the operation of the pump subsequently each piston chamber leads back and forth from each piston chamber, and in that a liquid connection device (440) is provided which draws the liquid from the in the pump (lOOC) arranged piston chambers leads to the liquid motor (400), so that the Hotor is driven, in turn to drive the outlet shaft (330) as a function of the liquid delivery by the pump. 19. Speed converter according to claim 18, characterized in that g e k e η η, that the control device (322) arranged in the pump (10OC) adjusts the mock tracks (52,62) allows in the circumferential direction between a maximum conveying position and an ilull conveying, wherein The maximum funding position is taken when the llockenüberhöhunqen (52a to d, 62a to d) of the first and second. Cam track, which is a pair of common reciprocating motion of the ball piston in the adjoining one cause common flow chamber to cover in the axial "direction, and the ilullförderstellurig is then taken when the cam elevations of the first and second cam tracks require a back and forth movement the spherical piston of each pair in opposite radial directions in the adjoining common Effect flow chambers, maximally out of phase with one another are. - 57 - 409833/0859 20. Speed converter according to claim 13 or 19, characterized in that g that the control device (322) can be reversed and the cam tracks from the Jüllförderstatus are displaceable to the maximum conveying state, the cam tracks in a clockwise direction against each other can be adjusted in order to achieve a flow through the pump (10OC) in a certain direction, and counterclockwise to reverse the flow through the pump. 21. Hydrostatic speed converter with a rotatably mounted input and output shaft and one with the £ ίτι-output shaft verbunceneji and from this pump driven, which depends on the rotation of the input shaft displaced a volume of liquid, with an adjustable Liquid displacement motor connected to the output shaft is connected and this rotates depending on the displaced liquid supplied to the motor, thereby characterized in that a rotatably mounted cylindrical piston body (130A) mit.der Input shaft (220) is rotatably connected that a first and a second ball piston row are provided which each have a plurality of spherical pistons (36, 38) mounted so as to be movable to and fro in piston cylinders (32, 34), wherein the piston cylinders evenly spaced in the Xolbenkörpsr are arranged so that several pairs of spherical pistons are formed that each pair of spherical pistons Assigned piston chamber (31) arranged in the piston body is, so that a radial reciprocating movement of the ball piston displaces the adjacent piston piston Liquid contained causes caß a first and a second .JockenbcJin (52, G2) are provided, the - 58 - 409833/0859 coincide axially and radially enclose the piston body in alignment with the first or second row of spherical pistons, so that each cam track has a plurality of uniformly formed uni-distributed looseness (52a to _{62a to d r} ) / which extend inward to the piston body and the radially aligned ones Touch the spherical pistons in a row so that the spherical pistons come into engagement with the aligned cam lobes as a result of the relative movement of the piston body with respect to the cam tracks and move radially back and forth, whereby the liquid from the spherical chambers (31) depending on the relative backward and movement of the spherical pistons of each pair of pistons is displaced so that a control device (232) for shifting the circumferentially congruent -tfockenüberhöhuntren of the first * :! LJockenbahn is provided opposite the EJocken superelevation of the second LJockenbahn to change the fluid displacement volume of the engine by changing the relative reciprocating movement of the ball pistons of a ball pair, that a fluid connection device (13Oß) is provided, which the fluid during operation of the engine subsequently to each piston chamber and away from each piston chamber, and that fluid connection devices (14OB 140A) are provided which connect the piston chambers located in the photo to the pump (100A). 22. Speed converter according to claim 21, characterized in that the control device (232) of the Motors (lOOB) an adjustment of the .clock tracks (52,62) in the circumferential direction between a maximum conveying position and a liullförderstellung allows, where, the maximum Föräerstelluna is taken when - 59 - 409833/0859 SO the cam excesses (52a to d, 62a to d) of the first and a second cam track that is shared in pairs The spherical pistons move back and forth in the adjoining common flow chamber, in cover the axial direction, and the zero delivery position is assumed when the cam excess height of the first and second cam track, which reciprocate the ball pistons of each pair in opposite ' radial bearings, in the adjoining common 8 tröinunrrs chamber, cause maximally against each other are out of phase. 23. The variator of Claim 21 oäer ^m 22, characterized in that the control means (232) is reversible and the iiockenbahnen of the .JuIlförderzustand to the maximum flow condition are slidable, said IJockenbahnen be adjusted clockwise qeaeneinander to flow through the motor ( lOOB) in a given direction, and counterclockwise to reverse the flow through the motor. - 60 - 409833/0859 Blank page