DE8901360U1 - Device for converting a rotary movement into a longitudinal movement and vice versa - Google Patents

Description

JDIPL-ING. PETER OTTE PATENTAfWAbX-. .;;.;··. Representative at the European Patent Office / European Patent Office ^ '&iacgr;_§<:;;: Tiroler Straße

2196/ot/wi 17.11.1988

Mr Franz Georg Miller, August-Lämmle-Wea 10 7250 Leonberg

Device for converting a rotary motion into a Longitudinal movement and vice versa

State of the art

The invention is based on a device according to the preamble of claim 1.

Devices, actuators and systems in which a linear (stroke) movement can be converted into a rotary movement and vice versa are known in a large number of designs, for example steam engines, internal combustion engines and the like as active systems in which the linear movement of a pressurized piston is transmitted via a piston rod or connecting rod to a rotating body, for example a wheel or the crankshaft of a machine. The disadvantage of these drives is that

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that a highly uneven power transmission, for example from the piston to a crankshaft, is only possible within a limited angle.

These systems belong to the group of crank drives; a uniform power transmission is achieved, for example, in the basic form of the rack and pinion pairing and the many other associated designs.

Finally, devices for converting rotary movements into longitudinal movements and vice versa have become known under the term so-called ball screws, in which rolling elements of any shape, usually balls, run between a helical outer raceway in a housing and an inner raceway that also runs in a helical shape on a shaft. The following publications, for example, can be assigned to these ball-recirculating systems: DE-OS 2 241 206; DE-PS 27 50 054; DE-PS 28 23 729; European patent publication 0 102 855 are European patent publication 0 177 702. In all of these movements based on the principle of the ball screw, an inner spindle, possibly provided with helical grooves, is mounted in a sleeve or nut, whereby during the kinematic movement, balls running in the grooves are transported along the nut, so that at least one ball return channel must be provided within the nut. The balls therefore run within the

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Muttor around.

Finally, special solutions are known (DE-OS 30 48 917; DH-OS 24 16 946; European patent application 0 136 492 and European patent CC 60 320) which are suitable for locally converting a linear movement into a rotary movement, but which do not need to be discussed in more detail since they are not related to the subject matter of the present invention.

Overall, it can be stated that the known devices are complicated and expensive to construct, usually require a lot of space and in the majority of cases are particularly susceptible to wear, especially in the case of the ball screw principle that works with spring preload of the balls.

The invention therefore has the task of creating a device as an actuator for converting rotary movements into longitudinal movements and vice versa, which can be manufactured inexpensively and easily and operates with particularly low friction when converting the movement.

Advantages of the invention

The invention solves this problem with the characterizing features of the main claim and has the advantage that with a very simple structure and only a few required

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of the high structural components, a very precise implementation of the respective movements is possible, so that the device according to the invention can be used in particular for very sensitive control processes, for example valve flap drives, in assembly robots, where gripping accuracy is important, for carrying out swivel movements of all kinds, for example in machine tools and the like, but also for pumps of any type, in particular so-called thick matter pumps / also with forced return.

In principle, the possibility of using the device according to the invention for converting movements is unlimited, in particular because of the low friction, which is associated with correspondingly low wear. It is therefore also particularly advantageous in the present invention that, in one embodiment, the two outer and inner driving elements, which are usually balls, arranged directly parallel to one another, are accommodated in the same recess in the lifting part, i.e. they are directly adjacent to one another in this part.

In contrast to the usual accommodation of such a ball, which, following the shape of the ball, forms, for example, a hemispherical recess or a dome shape in which one half of the ball is mounted, while the other then slides along an outer guide groove or runs in it, in a preferred embodiment of the present invention the mounting in the lifting part for the two adjacent balls is of a simple, through-

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and therefore open hole is formed.

Therefore, in the known embodiments, the ball must run under friction on at least one side, namely usually slide along the back wall of its bearing recess when, for example, it performs a lifting movement along the guide groove, the present invention has the considerable advantage that the two balls located in the common bearing recess necessarily perform an opposite rotational movement during the movement taking place, i.e. can also roll against each other, so that only ball movements that roll against each other and no grinding movements can occur.

Apart from this particularly significant reduction in friction, one ball always forms part of the bearing recess for the other, which can therefore also be designed completely differently and the balls are only guided laterally in their bearing recess in a point-like manner, so they are practically not subject to any friction due to this point-like contact on both sides and due to the rolling working movements in the associated running channel or groove or on each other.

The considerable simplification of the bearing recesses for the balls is that these can be normal holes here in the lifting part, whereby the two twin balls are inserted into each hole in such a way that they sit with a little more than half of their volume in the bearing recess, i.e. inside, or with correspondingly less than half of their volume towards

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emerge from the outside of the bearing recess and engage in corresponding guide grooves or raceways.

It is also advantageous that the entire actuator according to the present invention consists essentially of structurally simple, rctaticnsssstricsK (rotating) parts, whereby by appropriate dimensioning with little structural effort and manufacturing effort, considerable forces, due to the available piston area, can be optimally transferred with little loss from the linear movement of the piston into the rotational movement of a rotary output, if one focuses on this special embodiment.

It is understood that in order to further reduce the influence of friction, the running grooves or guide grooves, whether they are arranged in a helical or axially straight line in the lifting part and/or in an outer housing groove, are designed to be partially circular in their ^first radial section, corresponding to the radius of the balls involved, so that here too a safe and low-friction, flush guide is achieved.

The basic concept according to the invention can be used as an actuator for generating a linear output movement or an output rotary movement in a wide variety of control, regulation or positioning processes, whereby, depending on the design, rotary movements can be generated over specified angular degrees and stroke movements over certain paths, also reciprocally and continuously rotating in the case of rotary movements;

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Furthermore, the present invention can be used as a pump, compressor, but also as a motor, whereby valve controls can also be easily implemented and derived from the rotary movements that occur anyway.

A further advantageous embodiment of the present invention consists in arranging the lifting part in the form of a piston within a working chamber and driving it in one direction or the other by a gaseous or liquid medium, with the output being a rotary movement by any angular degrees, even by more than one revolution if desired. In an advantageous embodiment, a larger number of ball pairs distributed over the circumference are then supported against the housing of the actuator thus formed and on the rotating output shaft, with these ball pairs simultaneously experiencing an axial displacement due to the moving piston. One ball of each ball pair arranged as a lifting part in a continuous bore in an apron-like extension of the piston runs in an outer, axially or helically arranged groove (in the housing) and the other, inner ball in a likewise helically or axially running groove or guide groove with the corresponding desired pitch, which results in a forced guide and both balls roll with little friction in their respective grooves and against each other.

Through the measures listed in the subclaims

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Advantageous further developments and improvements of the device according to the invention are possible. Particularly advantageous here is the possibility of installing an energy storage device in the form of a pre-tension spring in the rotating part and allowing it to act on the lifting part in such a way that it is automatically returned to a starting position, so that pressure only needs to be exerted on it from one direction for the piston to move.

Another particularly advantageous design in the area of the twin balls as driving elements is based on the consideration that, although for slow-running units based on the present invention, the internal guidance of the two twin balls in the lifting part or in its extension (piston skirt), where the twin balls are held in radial bores, offers sufficient accuracy and resistance to wear and tear etc., for fast-running units it is advantageous to use the option of replacing the point-like support of each ball in its radial bore with an indirect, even more friction-free bearing.

This indirect bearing consists in the fact that balls are arranged in the radial bore of the lifting part or its extension, against which the driving balls are supported in the simplest case, so that they do not roll directly on the inner surface of the radial bore/ but on a ball crane-like power transmission or intermediate part, which absorbs the forces resulting from the driving balls.

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distributed and finally transferred to the lifting part or its extension by at least partially rolling along the inner wall of the radial bores.

This results in a particularly advantageous spread out and distribution of the acting forces, a better conversion of the resulting friction at least partially into rolling friction, so that it is generally avoided that the take-up balls become embedded in their radial bores during fast and long-term operation.

By interposing additional ball bearing rings, which support each other, on the inner wall of the respective radial bores that receive them and on the facing cam surfaces of the receiving balls, improved running conditions are achieved, particularly in units with fast movement sequences, whereby the possible designs of the ball rings used are accessible to a large number of variants.

Advantageously, the additional balls, ball bearing rings, support or bearing balls located in the radial bores are held by running cages or bushings that act as guides for them, which are made of hardened material and can be pressed into the radial bores of the lifting parts. To distinguish them from these inner balls, which run in the bushings or directly in the radial bore, the driving balls in the form of outer balls are supported on these inner balls and also hold them in position. The bushing that forms the cage for the inner balls can also be used in a bearing of the radial bores.

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dial bore(s) and secured against falling out by a spring ring.

If one compares the essential advantages of the present invention with a reciprocating piston engine, the following results. In a reciprocating piston engine, which converts its linear crank movement into a rotary movement via a crank drive, the torque applied per revolution is necessarily very uneven, so there are considerable maxima and minima in the torque curve, which are not only due to the pressure increase during the explosion of an ignitable mixture, but also mainly due to the fact that the angle at which the crankshaft journal supporting the connecting rod is located at the respective moment of the working cycle is included in the torque development .

In addition, in a reciprocating piston engine there is a direct relationship between the maximum torque that can be generated and the stroke of the piston, since the crankshaft determines the possible torque through the distance of the connecting rod's articulation point on the one hand, but on the other hand this dimension also determines the piston travel, i.e. the stroke.

The invention succeeds in breaking free from this geometric constraint - possible torque and stroke are independent of each other, since the diameter of the rotating part and the corresponding stroke part surrounding it can be designed as desired, which means that the paths and the steepness of the inner groove course can be changed.

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It is also possible, with great advantages, not only to set the gradient of the inner guide grooves as desired, for example, to make it flatter for a downward working stroke than for the upward return stroke, if you compare this with a reciprocating piston engine, which means different speeds of the piston depending on the direction, but you can also make the number of full strokes running up and down per circumference of the rotating part uneven. The latter means that, again in relation to the way a reciprocating piston engine works, the working stroke due to the explosion hits a different inner guide groove alternately, so that any wear can be distributed completely evenly.

In principle, the present development replaces the crankshaft principle, whereby a multitude of possible applications exist. For example, two of the movement systems according to the invention can work opposite each other with their rotating parts on a common gear, whereby it is then possible to arrange any number of such double units in a circle around another gear that is then jointly driven by the respective individual gears. In this way, a multitude of piston-cylinder units can be arranged in a small space, starting with the two-cylinder unit comprising only two units up to a twelve-cylinder unit or even beyond, in which six double units are then arranged in a plane shape around a common driven gear.

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Such a drive unit can be designed as a pneumatic motor, explosive engine (piston engine) or hydraulic motor, whereby any working process (two-stroke, four-stroke) can be used. Due to the small size, even with multi-cylinder units, these could be used directly as axle motors, also in a star-shaped arrangement.

The present invention is also particularly suitable for the implementation of stepper motors that can generate considerable torques per stroke or step sequence, as swivel drives of &khgr; ... over 360°, for example with spring return; as metering pumps with pistons or diaphragms for thick materials, as compressors, for example for low-pressure systems, as vacuum pumps, as stroke-rotary switches for precise positioning, as pure motion converters (stroke into torque or vice versa), also for hand or foot operation, as measured value sensors for rotary or stroke movements in the precision mechanical field.

drawing

Embodiments of the invention are shown in the drawing and are explained in more detail in the following description. They show: Fig. 1 a first embodiment of the present invention, which can be used in particular as an actuator, specifically for converting a linear (reciprocal) lifting movement into an output rotary movement; Fig. 2 a representation comparable to that of Fig. 1

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Embodiment, also in longitudinal section, where the control of the piston only takes place on one side, with it automatically returning to the starting position;

Fig. 3 is a view similar to that shown in Figures 1 and 2

comparable embodiment of an actuator, also in longitudinal section, additionally completed by locking and release systems acting on the rotary drive in such a way that the (reciprocal) lifting movement results in an output rotary step movement running continuously in one direction of rotation;

Fig. 4 an embodiment in which a continuous rotary movement can be converted into an oscillating stroke movement, preferably with additional control times for valve control options (flat disc valve);

Fig. 5 shows schematically in detail only

the working area of the driving twin balls in a first advantageous embodiment, in which intermediate additional bearing balls, preferably in the form of ball rings, are arranged in the radial bores of the lifting part or its extension;

Fig. 6 is a plan view of one side of the bearing ball ring arranged in the radial bore, against which an outer driving ball rests, initially axially and then with axial-radial force distribution during operation, corresponding to the section along the line VI-VI in Fig. 5;

Fig. 7 another embodiment of the arrangement

of intermediate bearing balls within the radial

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bore of the lifting part or its extension, wherein a plurality of adjacent ball rings with balls of smaller diameter are arranged in the radial bore;

Fig. 8 shows a further embodiment, also in partial representation, in which the two bearing ball rings directed at the inner and outer driving balls are supported inwards against each other and/or on an inner, additional ball ring lying in a gap;

Fig. 9 the possibility of arranging the ball rings on both sides from a large number of adjacent smaller balls, which are arranged in an extended shoulder of the radial bore;

Fig.10 is a schematic representation of an embodiment corresponding to the representation in Fig. 9, with the difference that the bearing ball rings made up of smaller balls are arranged in inner king recesses in the radial bore and are held there by the ball segments of the driving balls that are located on the outside;

Fig.11 shows a further embodiment in which only a common bearing ball ring is then preferably arranged in a central ring recess of the radial bore, against which the corresponding ball shells of the outer driving balls press from both sides;

Fig.12 also shows a detail and partly in perspective the arrangement of the ball rings for the bearing balls in a common outer race, which is inserted into the radial bore in the manner of a half ball bearing and where

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the balls inserted into the race are also held by the outer driving balls ;

Fig.13 finally shows another possible embodiment in which the bearing ball rings on both sides are inserted in an axially outwardly open ring recess of hemispherical shape and are held in this by the respective facing ball , while

Fig. 14 shows a further simplified ^embodiment in which the Luager ball rings on both sides are inserted into an inner ring cavity of the lifting part or its extension and are held on its walls, on each other and in their position by the two outer driving balls;

Fig.15 shows a preferred embodiment,

in which (four) inner balls in an inserted raceway cage rest on both sides against the cage and against each other and provide corresponding (four) support points for the outer balls, whereby

Fig.16 shows schematically and for better understanding the arrangement of the inner balls in the bushing in a plan view;

Fig.17 shows another embodiment in which

the outer balls are held directly in a raceway cage inserted into the radial bore without any additional auxiliary or support balls, whereby, as

Fig.18 shows that the running cage can also be divided into two parts ;

Figures 19 and 20 show the two-part barrel*

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cage with options for bearing clearance adjustment and the

Figures 21 and 22 show the assembly of two units lying one inside the other and in

Fig.22 then a larger number of double units, arranged in a star shape and in this sense forming a twelve-cylinder engine, which work on a common internal gear.

Finally, Fig.23 shows a partial section of an improved piston guide.

Description of the embodiments

The basic idea of the present invention is to transfer linear or rotary movements into one another without any problems and with little wear and friction by providing three structural parts, a rotary part, a lifting part and an outer casing or housing part, whereby twin balls or pairs of balls are arranged as drivers in the lifting part, lying directly parallel next to one another and adjacent to one another, which are guided outwards in appropriately designed and shaped grooves or guide slots on the one hand in the rotary parts and on the other hand in the surrounding housing shape. Based on this basic concept, a large number of possible applications and designs open up, of which only a few are explained below for better understanding; it is first of all clear that with the devices now specifically explained, the opposite direction of movement is always possible, i.e. the force generated can either be the lifting movement (linear movement) or the

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Rotational movement can be a rotary movement, whereby the other movement is always the starting value, and furthermore the invention is not limited to the embodiments presented.

In Fig. 1, the actuator is designated with 10; it comprises a lifting part 12 arranged to slide within a housing 11 and a rotating part 13 mounted to rotate within the same housing 11. The housing 11 can consist of two parts, a lower housing part 11a and an upper housing part 11b.

In the embodiment shown, the lifting part 12, which is referred to below as the piston, is mounted in a bore 13 of the upper housing part 11b in a sliding (or possibly rotatable) manner, while the lower housing part 11a (these expressions are related to the representations in the drawing and do not restrict a spatial orientation)

. a stepped bore 15 accommodates the rotating part L3 , which in the illustrated embodiment is mounted via a special bearing 16 (ball bearing, deep groove bearing, axial thrust bearing &ogr;. etc.).

In this arrangement, the rotating part 13 and the piston 12 also engage with one another, advantageously in such a way that a downwardly drawn piston ring skirt or an annular wall 12a receives and surrounds the rotating part 13 above the bearing 16. In this embodiment, the piston 12 forms a first working chamber 17 with the inner wall of the bore 14, while a second working chamber is formed when the piston is raised, which is formed by the stepped bore 15 of the lower housing part.

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11a, the inwardly projecting rotary part 13 and the piston underside.

An essential feature of the present invention is that there are kinematic connections between the cylindrical recess 18 of the piston 12, formed by the piston skirt 12a and the extension of the rotary part projecting into it, as well as between the bore 15 receiving this piston extension, i.e. the piston skirt 12a, and the piston skirt, which form positive guide means for the relative movement sequence.

Thus, in the embodiment shown, ball pairs 19a, 19b, 19c... are accommodated in bores on the lower edge of the piston skirt 12a in transverse or radial bores 20 of the piston skirt 12a, the arrangement being such that the respective twin balls sit practically flush in their bearing recesses formed by the bores 20, but protrude outwards by about half on both sides when they are essentially flush with one another in their respective bearing recesses.

With these "ball halves" projecting beyond their bearing bores 20, the twin balls engage in raceways or guide grooves of the adjacent components, ie the smaller balls are also seated in guide grooves 21 of the inner housing bore, while the inner balls engage in guide grooves '22 of the rotary table 13. It goes without saying that the guide grooves 21 and 22 are also designed in such a way that

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these correspond flush in their recess shape in the width of the spherical half - shape, whereby the thickness of the piston recess 12a forming the bearing bores 20 corresponds approximately to a sphere diameter.

In the embodiment shown, the preferred method for generating an output rotary movement is to drive the piston movement; therefore, in addition and only very schematically, a pressure supply 23 is shown, consisting of a drive motor 24 with a downstream pump 25, an electrical or electronic circuit part 26 and a changeover valve 27, which is designed here as a 6/2-way valve.

Furthermore, in this case, the outer (housing) guide grooves 21 are preferably designed as completely axially extending grooves, while the inner rotary part X grooves 22 run helically with any desired pitch, preferably a pitch of 45°.

Furthermore, in order to ensure safe guidance of the piston 12 | via its piston skirt 12a, which is also referred to as piston '^;

shaft, with the housing lower part 11a and the rotating part, which in this case is designed as an output shaft, depending on the length of the rotating part i» given axial distance from each other and preferably symmetrical to the housing axis, further ball pairings can be provided, as it is also understood that these ball pairings 19a, 19b... can not only be provided as a pair of two directly opposite each other as shown in Fig. 1.

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non, but evenly distributed over the circumference, a large number of twin balls can be provided in correspondingly distributed bearing bores 20 in the piston skirt 12a, for example as many as the adjacent groove arrangement in the rotating part allows. This naturally also depends on the diameter of the balls. This distributes the load over a large number of driver pairs, so that on the one hand there is improved smooth running, combined with the possibility of moving strong forces.

It is also apparent that if an additional rotary movement of the piston 12 is permitted, the outer guide grooves 21 can also run in a helical incline, so that depending on the direction of the inclination, transmissions or reductions of the rotary movement with a reference to the linear movement for a given stroke are obtained, in the manner of a differential gear, as can be readily seen. A possible basic function of the present invention therefore consists in the electronic control circuit 26 switching the solenoid valve from the position shown in the drawing to the other position, i.e. the pressure (hydraulic or pneumatic) generated by the feed pump 25, which causes the downward movement of the piston, is reversed; the working chamber 17 is relieved and the pressure medium now acts on the underside of the piston. This causes the piston to move upwards, with the outer balls of each double ball pair in the outer guide grooves, which for the sake of simplicity are initially shown as axially running.

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21 of the lower housing part 11a, whereby on the one hand a rotary movement of the piston 12 is arrested, but on the other hand at the same time the inner balls are given the opportunity to run off the outer "rear balls" so to speak and of course at the same time to take them along by engaging in the helical guide grooves 22 on the rotary part in order to carry out a rotary movement.

The advantage of low friction can be seen here if one imagines that the outer ball of the ball pair on the left in the drawing plane of Fig. 1 performs a rotational movement in an anti-clockwise direction when the piston moves upwards. In the same way, the inner ball belonging to this pair performs a rotational movement essentially in a clockwise direction, so that it can be seen that at their respective (point-like) contact area the balls do not rub against each other, but effectively contact each other auj.aUi.Sn f WxS aUCn ui3 i*j.Sxii3Ii ricxxG xititSlTiia j.*/ \aSjT

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It is understood that the angle of the rotary movement results from the pitch of the inner guide grooves, from the length of the rotating part and the possible stroke of the piston, and also from whether the outer guide grooves 21 in the lower housing part 11a run axially or are also helically inclined in one or the other direction and possibly even alternating pitches occur within a groove.

By reversing the piston 12 on one or the other side with pressure medium,

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The stroke and the working speed can be determined by means of the valve 27 which is actuated by the actuator, whereby an indicator device 28 can also be provided for the rotational position assumed by the rotating part, in this case the output shaft. This can be embedded in the upper part of the output shaft in the form of a rod and can be operated by means of pistons.

e, and upper housing closure bcdsn ilbsr sbdichtsRdc Lsgsr

'( 29, but it can also be carried out in a suitable manner

be arranged directly on the output shaft, pointing downwards. From the respective rotation position, limit switches (which also include scanning of the

■■ piston stroke movement is possible) signals for the control

.■ circuit 26, which is then mainly

can be used for redirection, or a remote signal evaluation is carried out.

The connection of the with its stepped inner bore 15 the continuation of the piston 12, i.e. the KoI- h benschürze 12a receiving housing base ila with

the upper housing part 11b can be done by screwing 30. Just as the piston skirt 12s extends into the bore of the lower housing part 11a, the piston skirt 12a also receives the « rotating part 13 in its own bore 18, so that these three parts of the housing

§ part 11a, piston skirt 12a and the upper drive

e The rotating parts are, so to speak, telescoped into each other.

The piston 12 is guided in a sealed manner in the cylindrical recess 14 of the upper housing part 11a; the at least one seal is designated 31.

The embodiment shown in Fig. 2 corresponds in essential parts and in its basic structure to the representation in Fig. 1, so that the same parts

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are provided with the same reference numerals; an exception is the principle of piston return, for which purpose a force accumulator 32 is provided in the actuator of Fig. 2, which is designed as a return spring 33. The return spring 33 sits in a recess in the form of a cylindrical receiving bore 34 in the rotary part 13 and is supported upwards, i.e. against the piston bottom 35, via an axial bearing 36, which absorbs the relative rotation between the piston 12 and the rotary part 13 .

The compression spring 33 is dimensioned in such a way that after the downward stroke of the piston 12 has been carried out, the spring preload is overcome and the piston is moved upwards into its starting position while maintaining the rotational energy emitted by the rotating part 13 or even when idling. In this case, only a 3/2-way valve 27' is required to control the working space 17* formed between the piston 12 and the upper housing part 11b, while the lower inlet or outlet opening only serves for venting purposes, i.e. is a vent opening 37. Attention is drawn to the fact that in the longitudinal sections of Figures 2 and 3, the inner and outer guide grooves for the twin balls are shown running axially for the sake of simplicity, in order to indicate the optional options for their helical design.

The basic concept of the embodiment shown in Fig. 3 also corresponds to that of the embodiments 4a and 4b.

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1 and 2, i.e. actuator for generating a rotary movement on the output side when pressure is applied to a lifting part on one or both sides, with the difference that in this embodiment of Fig. 3 the rotary movement generated on the output side is discontinuous, but in a given direction, with constant reciprocal movement of the lifting part. Here too, the same parts are provided with the same reference numerals, possibly with a different structure but similar function with a comma at the top, with a separate output shaft 38 being provided in addition, which is driven by the rotating part 13' which is now located inside. Here too, the principle of piston return by means of a compression spring 33' takes place, with the pot-shaped structure of the output shaft 38, which is stepped several times, temporarily supporting the rotating part 13' within a first diameter 38a via a first gear element 39, which itself sits in a second bore diameter 38b. Another gear element 40 supports the output shaft 38 in a mounting hole 41 of the lower housing part

11a. If necessary, a sawtooth-like, closed, circumferential groove shape could also be considered, possibly without the gear elements 39, 40. The two gear elements 39 and 40 are designed as ftUck anti-rotation/freewheels are designed and prevent backward rotation of the output shaft 38 during the reciprocal drive movement of the piston 12.

The function of the actuator of Fig. 3 is then such that during a first stroke movement of the piston 12, preferably during the «bwttrts directed movement, whereby ssur control the 3/2-way valve shown in Fig. 2

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device can be used, the output shaft 38 is driven by the rotating part 13', which here carries out a rotary movement in the usual way, via the freewheel 39, while then, with the opposite stroke, the freewheel 39 enables the rotating part 13* to rotate back, but at the same time the reverse rotation lock 40 (additionally) prevents or ensures that the output shaft 38 is held in the rotary position it has reached and does not undergo an uncontrolled reverse rotation. The reverse rotation lock can therefore be a ratchet lock or something similar; the cycle then repeats itself, so that with each downward stroke the output shaft 38 performs a rotary movement in a predetermined direction and comes to a standstill with the upward stroke (or vice versa).

It is understood that the actuators shown in Figures 1 to 3 are amenable to a large number of modifications; for example, instead of the piston seal 31, a suitably modified piston can be sealed using a so-called rolling membrane, which is clamped with its outer edge between the upper housing part 11b and the lower housing part 11a and is slipped over the piston or is attached to the piston with its inner edge in such a way that the rolling membrane rolls in a free space between the piston circumferential surface and the inner cylinder wall.

In order to illustrate the versatility of the possible applications and designs, Fig. 4 shows a further example of a device driven "in reverse" which then

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can work as a pump or compressor. The basic principle of the invention is also implemented in this embodiment of Fig. 4 and parts with the same functions are provided with the same reference numerals and an additional comma at the top.

The main difference to the design of Figures 1 to .? is that the "inner" guide groove 22' in the rotary part 13' is designed in a closed circuit, so that when the rotary part 13' is acted upon by an external rotary drive, the piston 12* can perform a reciprocating movement through the engagement of the inner ball of the two twin balls mounted in it in the circumferential guide groove 22' on the rotary part. Such a unit can therefore be used as a pump or compressor, preferably as a so-called thick matter pump.

Since in the illustrated embodiment the circumferential guide groove 22' in the rotating part 13' runs up and down twice, two pairs of balls can also be used to transmit force and movement, since when the rotating part 13' rotates, these are in a different place than the other ball, but are always at the same height in the guide groove 22'. When the rotating part 13' rotates, the piston 12' therefore performs a two-fold cube movement.

If desired and if there is sufficient space, the turned parts 13* can also be extended if the area containing the guide groove(s) is long enough.

nt» «· <»· ta .. &igr;

17.11*1988 - 27-

Additional guide grooves, which are axially superimposed, can be provided on the rotating part, into which diametrically opposed ball pairs then engage, so that the forces acting on a ball pair can be kept within limits by the distribution achieved in this way. The additional ball slots can also be arranged at an angle. An advantageous embodiment of the embodiment of Fig. 4 is that control movements for inlet and outlet openings of the pump or compressor working chamber formed by the piston 12' and the surrounding wall of the upper housing part 11b* can be derived simultaneously from the rotary movement of the rotary part 13'.

Thus, a rotatable disk 42 can be arranged in the head of the upper housing part 11b, which has passage openings 42a, 42b which correspond to duct openings 43a, 43b in the housing at certain angular positions; in other angular positions they cover them.

The valve disk 42, which in this respect forms a valve control, is advantageously driven by the sealed piston bottom from the rotating part 13', for which purpose the valve disk 42 has a rotation axis 44.

In order to adjust the opening and closing times of the passage openings 42a, 42b with respect to the passage openings 43a, 43b in the housing, with a fixed drive connection of the valve disc 42 with the rotary

2196/ot/wi

17.11.1988 - 28 -

part 13' whose guide groove 22' βγ should be designed such that compensation times result which are represented by the horizontal partial corners 22a ¹ , 22b' in the guide track. During these horizontal courses the rotating part 13' and thus also the adjusting disk 42 rotates; there is no "over-movement" so that these times can be used for closing and opening times in the valve area.

The basic function of such a device is such that when the piston moves (suction) through the kinematic engagement between the piston 12' and the rotating part 13' via the ball pairs, the corresponding inlet valve openings are released; these are closed when the stroke stops due to the horizontal guide grooves; the upward stroke then takes place with the working space completely closed, at the end of which the outlet valve area is opened. The working sequence of such a pump therefore consists of the strokes of suction, compression and discharge - working processes that can also be used with kinematic reversal, so that the possible basic principle of an active internal combustion engine, such as a gasoline or diesel engine, can be implemented in principle, either with the valve control shown or with a valve control system. Such an internal combustion engine with rotary valve control has advantages over the known crank drive systems, since the power transmission occurs evenly over the stroke and is not a function of the respective angular position in the crank drive.

2196/ot/wi

*7. 11.1988 - 29 -

A particularly advantageous embodiment of the present invention will be discussed below; this embodiment concerns the possibility of controlling the interaction between the two twin balls and

each radial bore of the lifting part or its extension, i.e. the piston ring 12s, should be designed indirectly. This can be recommended if the unit is a high-speed unit, for example a hydraulic motor, since in this way the force transfer between the outer and inner driving ball and the radial bore - the contact is basically point-like - can be evened out, distributed and reduced in the pressure peaks.

In Figures 5 to 14, only partial sections of the lifting part or its extension, usually the piston skirt, are shown; in Fig. 5, the radial bore 20 of the piston 12, as the lifting part will be referred to in the following - but this can also be the piston skirt 12a - receives ball rings 45a, 45b, preferably on both sides, since the outer driving balls 19 protrude into the radial bore 20 on both sides.

The ball cages are made up of bearing balls 46 that are smaller in diameter than the driving balls and are basically arranged in the same way as a ball bearing in

are arranged in a mutually adjacent sequence in the radial bore 20 in the ring shape shown very schematically in Fig. 6.

In this way, each bearing ball ring 45a,

2196/ot/wi

17.11.1988 - 30 -

45b inner ring surfaces of the desired diameter, against which the outer driving balls 19 are pressed or rest, whereby one of the number of bearing balls

46 in the ball crane? corresponding number of point-shaped supports on the spherical shell shape of the driving balls 19; It is understood that the diameter, which is ultimately formed from the sequence of point-shaped contacts, depends on the diameter of the large driving balls 19, the diameter of the small bearing balls 46, the number of bearing balls and accordingly also the diameter of the radial bore 20. In Fig. 6 an assumed diameter

47 is shown in dashed lines, along which the half-shell of the driving ball rests on the formed ball ring 45a, 45b at each bearing ball in point-like contact, whereby each driving ball naturally with its tapered ball shell part also penetrates between the bearing balls 46, as indicated in FIG. 5 in dashed lines at 48, so that the bearing balls 46 are also held on their outer ring ring by the driving ball and its pressing or holding effect.

If the bearing balls 46 are supported radially outward on the cylinder wall of the radial bore 20 in the piston skirt 12a that receives them, they can be supported inward in a variety of ways, which are discussed below with reference to the illustration in Figures 7-14, whereby the basic procedure is always such that a ball ring made of bearing balls that is axially open to the outside creates the contact circular ring shape against which the outer driving

2196/ot/wi

17.11.1988 - 31 -

balls 19 (on both sides) in a point-like manner, namely according to the number of bearing balls 46 in the ring.

In Fig. 5 it is shown that the bearing balls 46 in the two outer ball rings 45a, 45b can either be supported on an additional inner ball ring 49 , which is then arranged with a gap but also completely in the shape of a ring in the radial bore 20. In order to prevent the balls of the inner ball ring from falling inwards, a cylindrical intermediate piece with an outer diameter that corresponds to the inner diameter of the ball ring can be provided or inner ring flanges that project inwards, shown in dashed lines in Fig. 5, can be provided.

50 should be provided, against which the bearing balls 46 rest inwards, the inner ring flanges being advantageously completed by smaller ring flanges 51, so that the ball rings are guided on both sides and it is also ensured that they do not rotate sideways (to a larger diameter of an oval shape).

However, it is also possible, as shown in Fig. 14, which will be discussed immediately, to arrange the two ball rings 45a ¹ , 45b* and with correspondingly different dimensions of the components involved directly adjacent to one another in the modified radial bore 20* of the piston skirt 12a, so that the individual bearing balls 46 of the ball rings support one another. The smaller, retained ring projections

51 ensure that the ball cranes

;··;'··&igr;&igr;&pgr;.·;hi&igr;

2196/ot/wi

17.11.1988 - 32 -

cannot be adjusted laterally or transversely in the radial bore.

In the embodiment of Fig. 7, a large number of comparatively small bearing balls 46* are provided in a large number of consecutive ball rings 52 to 56, which are then also supported on the inside. In order to prevent middle bearing balls 46' from falling inwards, additional support ball rings 57 can be provided; this depends on the geometric dimensions and must be decided on a case-by-case basis.

In the embodiment of Fig. 8, which again shows the inner rotating part 13 with its oblique grooves, only a few bearing balls are provided to form the two outer ball rings 58 and 59, for example four bearing balls 46, so that a single inner support ball 57* can be sufficient to give the structure stability.

Alternative designs according to Figures 9 and 10 are constructed in such a way that the ball rings 60, 61 and 60', 61' on both sides are inserted into external or internal annular grooves made as recesses in the radial bore 20, in which they are supported on all sides and inward falling is prevented by the ball shells of the two driving balls 19 which are in contact with all balls at points, as explained in detail above. The number of balls in the running grooves 62 and their size can be

&bull;&bull;&bull;&bull;&bull;I

he

2196/ot/wi

17.11.1988 - 33 -

be arbitrary and in accordance with the respective requirements.

An interesting example is shown in Fig. 11; here the two ball rings that come into contact with the ball shells of the drive balls have shrunk into a single, internal ball ring 63 or have been combined in a crane, which is arranged in an inner ring groove 64 as a ball track in the radial bore 20 of the piston skirt 12a. ^It goes without saying that the dimensions of the balls must be such that the drive balls 19 that are in contact with the common ball ring from the outside do not interfere with one another - the drive balls 19 may only touch one another very slightly in the middle.

Fig. 12 shows a practical embodiment in which ball rings 65, 66, which directly adjoin one another with their inner surfaces, are accommodated in an annular raceway 67, which can also be made of hardened material, for example, and is inserted into the radial bore 20 of the piston skirt 12a, for example in a press fit. The inner raceway is in any case concavely curved in a trough-like manner, so that the two ball rings 65, 66 are stabilized in their position and cannot move sideways.

In the embodiment of Fig. 13, the arrangement of the respective ball ring is finally such that the ball ring 68 in a front-side

2196/ot/wi

17.11.1988 - 3 4 -

Ring groove 69, which runs on the outside around a possibly still present, but not necessarily required radial bore 20*. In cross section, the ring groove 69 is hemispherical with, if desired, a more protruding ring wall 70 on the outside, so that the bearing balls 46 cannot fall out under any circumstances when the outer bearing balls 19 are in contact.

It goes without saying that the embodiments of intermediate ball bearing options shown do not limit the invention. All of these embodiments enable an equalization of the pressures occurring during operation, thus reducing pressure peaks and in particular ensuring a long service life for the units created by the invention, even when they are extremely fast-running.

As already mentioned in Fig. 12, Fig. 15 shows an enlarged partial section of a cage 67' which forms the guide for inner balls 71 and is inserted into the radial bearing recess 20 of the lifting part 12. The cage 67', which, due to its trough-shaped groove with raised edge areas 67a, 67b on both sides, provides preferably hardened raceways for these inner balls and, depending on their number, supports them in such a way that the inner balls run against each other, the raceways and the two outer balls 19 with the least possible wear. The guide bush 67* sits in a shoulder 72 of the bearing recess 20 and is secured against falling out, for example by a spring ring or snap ring 73.

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ti ;

2196/ot/wi

17.11.1988 - 35 -

01« Distribution of the inner balls, which have a mutual contact angle of preferably between 45 and 50°, is as clearly shown in Fig. 16; there are preferably four balls arranged on one side and designated 71a and correspondingly and offset from the first balls 71a on the other side inner balls designated 71b are provided, so that for the respective outer ball 19 there are then a total of four support points formed by the inner or support balls on the side facing them.

In an alternative embodiment, it is also possible to let the outer driving balls run directly in appropriately designed sections of guide bushings 67", as shown in Figures 17 - 20, without using any inner support or auxiliary balls at all. The guide bushing for the outer and inner driving balls has an inner projection 74 against which the two driving balls 19 rest. The balls can thus run on this inner, spherically shaped projection and, if desired, also on each other.

In one embodiment of the bushing that directly accommodates the driving balls 19, this can also be split in two, as shown in Fig. 18, so that it consists of the two partial bushings 67a", 67b". In Fig. 18, these two partial bushings lie directly against one another and hold the two driving balls 19 firmly on the outside by means of a half-sided trough-shaped groove, i.e. inwardly projecting ring projections (following the spherical shape), so that they are against one another.

2196/ot/wi

17.11.1988 - 36 -

and on the running surfaces formed by the two partial supports 67a"/ 67b".

Depending on whether the split bushing shape for directly receiving the driving balls has a common internal projection similar to that shown at 74 in Fig. 17 or ring projections on both sides, holding the balls inwards, as shown in Figures 19 and 20, the two partial bushings can be pushed apart from one another by a central, wedge-shaped intermediate element 75 when it penetrates more or less deeply (Fig. 19) to adjust their position, or the two partial bushings can be pressed towards one another by external, for example distributed screws 76, as shown in Fig. 20.

Fig. 21 shows, in a highly schematic manner, two opposing actuators or units 10', 10", whereby each of these units can be designed as shown in the basic embodiment of Fig. 1. The output shafts of the two units 10', 10" work on a common central gear 77, so that a double unit is created, whereby the rotary movement generated can then be taken from this gear in any desired manner.

Such a basic principle also enables the construction of larger engines with a corresponding number of cylinder units, as shown in Fig. 22 using a selected twelve-cylinder engine. In this embodiment, which is also highly schematic, a total of six double units are shown as follows:

·« · M MM ft· *·

2196/ot/wi

17.11.1988 - 37 -

The arrangement of the wings 21 is plate-shaped and distributed at the same angular distance from one another around a common central gear 78, on which the individual inner gears 77 of each double unit then work. It goes without saying that any number of cylinder units can be connected to one another as required.

One more thing should be noted. The radial holes in the lifting part, which in certain embodiments form the receptacle for bushes to be inserted into it, which then in turn receive the inner support or guide balls, naturally also follow a partial circle shape where they penetrate outwards due to the general circular shape of the lifting part, and if you do not want to make the bushes to be inserted into these receiving holes to also form such a circular shape - so that bush parts do not protrude inwards and a secant shape is formed on the outside, then you can either provide flats in the receiving parts wherever such bushes occur, or you can insert the bushes so that they protrude or run inwards and then make corresponding flats in the opposite directions. However, you can also make the length of the bush shorter than the receiving holes, as shown in Fig. 15, so that there is nothing further to worry about here.

When converting a reciprocating movement, as occurs, for example, when a device according to the invention is used in the manner of a reciprocating piston engine, it may be useful to

2196/ot/wi

17.11.1988 - 38 -

The working stroke can be made to run with a different gradient compared to the return stroke, so that the piston moves at different piston speeds depending on whether it is currently performing a working stroke or a return stroke. It is also possible to let the half-oscillation of the inner groove, which characterizes an upward and downward stroke, as shown in Fig. 4, run repeatedly over 4' the circumference of the rotating part in a 4-wheel count, so that then,

' when working strokes are in a uniform sequence with

Alternate return or compression strokes, with the respective working stroke continuously hitting different internal grooves in the rotating part to avoid uneven wear.

If you want to improve the (cylindrical) guidance of the piston 12 in the housing according to Fig. 1, then you can, as shown in Fig. 23,

&iacgr; part 12a outside additional axial grooves 80 straight

continuously arranged, which have additional axial housing grooves

F 21'. Fitted into these two guide grooves

80, 21* additional guide balls 81 are arranged, which securely support the piston body against the surrounding housing, center it and protect it against tilting or scraping (see also the small sectional drawing below the housing in Fig. 23).

What all embodiments have in common is that additional compression or suction chambers are formed during the piston movement, which can be used for other purposes, e.g. for flushing and/or compression.

2196/ot/wi

17.11.1988 - 39 -

All features presented in the description, the following claims and the drawing can be essential to the invention both individually and in any combination with one another.

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Claims (1)

DIPL-ING. PETER OTTE PATENT ATTORNEY .··. ··;: .··. . wooi«* Representative at the European Patent Office / European Patent Attorney :..: \ * : _#> : _: 11rolejä*aÖeJ5 2196/ot/wi 17.11.1988 Mr Franz Georg Miller, August-Lämmle-Weg 10 Leonberg Protection claims 1. Device (actuator) for converting a (continuous) rotary movement into a (reciprocating) longitudinal movement and vice versa, with a rotary part mounted to carry out the rotary movement and a lifting part in kinematic operative connection with this, characterized in that at least one first inner driving element and at least one second outer driving element are accommodated in the lifting part (piston 12) in such a way that parts of the inner driving element are also guided in inner guide grooves (22, 22') of the rotary part (13) which are adjacent to the lifting part (piston 12) and parts of the outer driving element are guided in outer guide grooves (21) of a further component which is adjacent to the lifting part (piston 12) on the other side. 2. Device according to claim 1, characterized in that the driving elements are arranged in pairs immediately next to each other and adjacent to each other in a common bearing recess (20) in the lifting · · · 11114t l· · * · 4 Il Il I *· * · I Il I* I 2196/ot/wi 17.11.1988 - 2 - part (piston 12) are mounted (twin ball arrangement). 3. Device according to claim 1 or 2, characterized in that the inner and outer driving elements adjacent pairs (19a, 19b) of balls . which run in corresponding semicircularly grooved inner and outer guide grooves (22, 22'; 21). 4. Device according to one of claims 1 to 3, characterized in that an extension on the piston in the form of a piston skirt (12a) receives in a central recess the area of the rotary part (13) having the inner guide grooves (22, 22') and that the respective ball pairs (19a, 19b) forming the inner and outer take-up element are received in radial bores (20) of the piston skirt wall. 5. Device according to one of claims 1 to 4, characterized in that the piston skirt (12a) at least partially receiving the rotary part (13) is arranged in a bore (15) of the further, stationary component, in the inner wall of which the outer guide grooves (21) are incorporated. 6. Device according to one of claims 1 to 5, characterized in that the piston (12) forming the lifting part is in a bore (14) of a stationary &bull; * « · I ( t Il &bull;«ii * &igr; i · « itii 2196/ot/wi 17.11.1988 Housing is mounted in a slidable and sealed manner, which together with the other component forms an upper and a lower housing part (lib, lla) which are connected (screwed) to one another in the transition area and accommodate the rotating part (13), the piston skirt (12a) and the piston (12) in a multi-stepped inner bore. 7. Device according to one of claims 1 to 6, characterized in that the respective inner The balls of the ball pairs are each formed in a helical shape, preferably with a pitch of 45°, in the inner guide grooves (22, 22') of the rotating part (13), which each accommodate slightly more than half of the balls. 8. Device according to one of claims 1 to 7, characterized in that the outer guide grooves (21) arranged in the inner wall of the bore of the lower housing part (11a) and accommodating approximately half of the outer balls of the ball pairs are designed to be axially straight or to run helically at any angle in one direction or the other. 9. Device according to one or more of claims 1 to 8, characterized in that the rotating part (13) is mounted in the housing lower part (11a) via a (also pressure-loaded) roller bearing (16). 10. Device according to one of claims 1 to 9, characterized in that ?,to generate the reciprocal stroke movement of the piston (12) a pressure &bull; ·· * With M Il ·*·*· tt Il &bull; ff · t &igr; ( « I &igr; » · * · * &igr;&igr; ■ &igr;&igr; ·« * · I It ti I » ·« IM Il If Il iil6/ot/wi 17.11.1988 - 4 - control device (23) is provided, which supplies the piston top or bottom alternately with a hydraulic or pneumatic pressure medium via a multi-way valve (27), while simultaneously venting the other Dr Uökfäünie. 11. Device according to claim 10, characterized in that for the alternating application of pressure to both sides of the piston (12), a 6/2-way valve (27) is provided which is actuated by a pump (25) driven by a drive motor (24) and is controlled by an (electrical or electronic) control device (26). 12. Device according to one of claims 1 to 11, characterized in that radial receiving bores for a number of ball pairs are arranged at the same height and at equal angular intervals over the circumference of the piston skirt \12&aacgr;;, with corresponding associated outer and inner guide grooves, to improve the smooth running and to distribute the force. 13. Device according to one of claims 1 to 12, characterized in that axially offset from a first bearing row of radial bores accommodating ball pairs, further radial bores, preferably also at a uniform angular pitch and engaging in the same outer and inner guide grooves. 2196/ot/wi
17.11.1988 14. Device according to one of claims 1 to 13, characterized in that when the lifting piston (12) is acted upon only on one side and the other pressure connection is designed as a vent connection , an energy accumulator (32) is provided which returns the piston to its starting position. which absorbs and stores the return energy during the pressurized stroke of the piston (12). 15. Device according to claim 14, characterized in that the pressure accumulator is a preload spring (33) which is accommodated in a bore (34) of the rotary part (13) and is supported against the facing piston bottom via an axial thrust bearing (36) (Fig. 2). 16. Device according to claim 14 or 15, characterized in that a 3/2-way valve (27 ¹ ) acted upon by a pressure medium is provided for controlling the piston stroke in only one direction. 17. Device according to one or more of claims 1 to 16, characterized in that a rotational position indicator device (28*) is provided, preferably firmly connected to the rotary part (13). 18. Device according to claim 17, characterized in that the rotational position indicator device (28, 28') is the electrical or electronic control circuit (26) is used to reverse the valves (27, 27') supplying the pressure medium when the 2196/ot/wi 17.11.1988 a respective end position« 19. Device according to one of claims 1 to 18, characterized in that in order to achieve a rotational movement of the rotating part (13*) in only one direction with repeated reciprocating stroke movement of the piston (12), at least one additional gear element in the form of a freewheel (39) is provided, which causes rotational drive in only one direction and releases it in the other direction (Fig. 3). 20. Device according to claim 19, characterized in that the rotary part (13*) drives an output shaft (38) mounted separately in the housing (11), on which a reverse rotation lock (40) engages. 21. Device according to claim 19 or 20, characterized in that the rotating part (13*) which is alternately driven in one and the other direction of rotation by the ball pairing mechanism by the piston (12) drives the output shaft (38) via a freewheel clutch (39) only in one direction of rotation, with the anti-reverse lock additionally acting on the output shaft. 22. Device according to one of claims 19 to 21, characterized in that the output shaft (38) partially receives the rotary part (13') in a bore via the interposed freewheel (39) and itself in a stepped bore (41) of the 2196/ot/wi 17.11.1988 - 7 - lower gear nut position dia), preferably via the anti-reverse lock (40). 23. Device according to one or more of claims 1 to 22, characterized in that at least one of the guide grooves (22, 22', 21) on the rotary part ( ^13f ) or on the inner wall of the further component (lower housing part 11a) is designed as a self-contained path in a helical or sawtooth shape (Fig. 4). 24. Device according to claim 23, characterized in that, in order to generate a repeated reciprocating pump or compressor stroke movement of the piston (12), the rotary part (13') has at least one self-contained guide groove (22') running at least once upwards and downwards, into which at least one ball pair mounted in a radial bore of the piston skirt (12a") engages. 25. Device according to claim 24, characterized in that the outer guide grooves in the lower housing part (Ha') are designed to run axially straight. 2S. Device according to claims 23 to 25, characterized in that means for controlling inlet and outlet openings (42a, 43a; 42b, 43b) for the compressor or pump working chamber are provided (Fig. 4) 27. Device according to claim 26, characterized in 2196/ot/wi 17.11.1988 - 8 - net that a rotating valve disc (42) is provided with passage openings (42a, 42b) aligned at certain angular positions with passage openings (43a, 43b) of the housing, which derives its rotary drive from the rotation of the rotating part (13·). 28. Device according to one of claims 23 to 27, characterized in that the guide groove(s) (22') formed in the closed circuit in the Rotating part (13 ¹ ) for forming stroke dead times, which are simultaneously valve opening and closing control times, is/are designed to run horizontally in certain areas (curve reversal points) (22a ¹ ). l 29. Device according to claim 28, characterized in that the valve disc (42) for sealing consists of a ceramic material and cooperates with a further ceramic sealing disc (42·) mounted stationary in the housing with corresponding passage openings. 30. Device according to one or more of claims 1 to 29, characterized in that at least one of the driving balls (19) is only indirectly received in the radial bore (20) of the lifting part or its extension (piston skirt 12a). 31. Device according to claim 30, characterized in that in the radial bore (20) of the lifting part Jt I Tf ff *
i IIII * I * &igr;! · * * I &iacgr;. r &bull; I L &uacgr; te Ulli < I Cu Au I > Il (Ul O & ti ".49 2196/ot/wi 17.11.1988 - 9 - (piston 12 or piston skirt 12a) a ring of bearing balls (46) in the form of a ball ring (45a, 45b) is arranged, against which the respective facing driving ball (19) rests from the outside (Fig. 5-16). 32. Device according to claim 30 or 31, characterized in that each ball ring (45a, 45b) is formed from an annular, adjacent sequence of bearing balls (46) which are arranged in at least one radial bore (20) of the lifting part in such a way that an axial ring guide is produced in addition to the contact formed by the ball shell of the driving ball (19) and the radial cylindrical surface of the receiving bore (Fig. 5). 33. Device according to claim 32, characterized in that the axial ring guide is formed by outer and/or inner ring projections (50, 51) which prevent the bearing balls (46) from deflecting in an oblique-axial direction. 34. Device according to one of claims 30 to 33, characterized in that the support of the bearing balls forming the ball rings (45a, 45b; 52, 53, 54, 55, 56; 58, 59; 60, 61; 60', 61*; 65, 66; 45a', 45b ¹ ) is achieved inwardly by further ball rings (49) arranged there, an axial/radial intermediate piece, support balls, by the ball rings lying directly against one another on the inside or by being accommodated in annular grooves (62) forming running channels (Fig. 5-10). &bull;4*1 I &igr; ti« » &igr; ■ * I III»·»* 2196/ot/wi 17.11.1988 - 10 - 35. Device according to claim 30 or 31, characterized in that only one central ball ring (63) is arranged in the radial bore (20) of the lifting part, against which the outer driving balls (1..9) rest from both sides. (Fig. 11) 36. Device according to claim 35, characterized in that the one ball ring (63) common to both take-up balls (19) is arranged in a central ring recess of the radial bore (20). 37. Device according to claim 30 or 31, characterized in that each take-up ball rests against a ball crane (68) inserted into an annular groove on the front side. (Fig. 13) 38. Device according to claim 37, characterized in that the annular groove is hemispherical in cross section in adaptation to the bearing balls (46) received by it. 39. Device according to one of claims 1-38, characterized in that an inner guide bush (67, 67') which receives support or guide balls (71; 71a, 71b) and forms a running cage is inserted into the radial receiving bore (20) of the lifting part (12). 40. Device according to claim 39, characterized in that the guide bush (67*) has on both sides inwardly directed annular projections of the partial spherical shape 2196/ot/wi 17.11.1988 - 11 - following the received inner balls (71), such that the inner balls (71; 71a, 71b) run on the grooved running surfaces of the guide bush, on each other and on the outer driving balls (19). 41. Device according to claim 39 or 40, characterized in that four or another number of ball rings are arranged on each side with mutual offset of the two ball rings. 42. Device according to one of claims 1-29, characterized in that the receiving balls (19) are arranged directly in a guide bush (67') received by the radial receiving bore (20) in the lifting part (12). 43. Device according to claim 42, characterized in that the guide bush (67") for receiving the driving balls (19) comprises them with a central inner annular projection (74) and/or with external annular projections on both sides directed inwards, each of which follows the partial spherical shape. 44. Device according to claim 42 or 43, characterized in that the guide bush (67") directly receiving the driving balls (19) consists of two guide bushes (67a", 67b"). 45. Device according to claim 44, characterized in that adjusting means (wedge shape 75; screws 76) are provided for adjusting the bearing play. 4 · if · 2196/ot/wi 17.11.1988 - 12 - are the two guide part buaheen (67a", 6-7b") push apart-bsw, mntenpgea&mdash;&eegr;&tgr;&tgr;- 46. Device according to one or more of claims 1-45, characterized in that the drive parts of two devices are directed towards each other and work on a common drive element (gear wheel 77) to form a double unit. 47. Device according to claim 46, characterized in that any number of double units (star-shaped) are arranged next to one another, whereby all gear wheels (77) of the double units (10 ¹ , 10") work on a common central gear (78). 48. Device according to one of claims 1-47, characterized in that in the piston lower part (12a) and in the housing lower part (11a) surrounding it, additional longitudinal grooves (80, 21') are arranged for additional guidance and centering of the piston relative to the housing, in which one or more guide balls (81) run. 49. Device according to one of claims 1-48, characterized in that the additional compression or suction spaces created during the piston movement are also used as working spaces for flushing and/or (pre)compression.