EP1991792B1 - Torque motor - Google Patents

Description

The present invention relates to a rotary motor, preferably rotary drive for construction machinery, hoists, trucks and the like, with an elongated, approximately tubular housing, at least one axially slidably received in the housing piston, which is axially driven by application of a pressure medium in a pressure chamber and at least an axially fixed in the housing, about a rotational axis rotatably received shaft, wherein the piston has a Wellendurchgangsausnehmung with which the piston is axially displaceable on the shaft.

In such rotary motors, the axial movement of the piston, which can be acted upon by corresponding pressure chambers with a pressure medium, converted into a rotation of the shaft relative to the housing or of the housing relative to the shaft. Usually this is the shaft with the piston in screw engagement, which in turn is guided against rotation of the housing. Such a rotary motor shows, for example, the DE 201 07 206 in accordance with which the piston is guided, on the one hand, in a rotationally fixed manner to the inner lateral surface of the circular cylindrical housing and, on the other hand, in screw engagement on a threaded section of the shaft stands. If the piston is displaced axially by hydraulic or pneumatic loading in the housing, its axial movement is converted by the screw engagement into a rotational movement of the shaft. A problem here is the sealing of the piston relative to the shaft and / or with respect to the housing. For the seal between the piston and shaft beats the DE 201 07 206 to impart to the piston a sealing portion spaced from the screw engaging portion, which slides and seals on a shaft sealing portion. However, such piston designs are disadvantageous in terms of size and associated with high production costs. In addition, different power relationships result for the operation in different directions of rotation.

The US 3,183,792 shows a rotary motor in which the longitudinally displaceably guided piston sits on a helically twisted portion of the drive shaft. In order to prevent rotation of the piston, the said drive shaft is arranged offset eccentrically to the cylinder longitudinal axis. In another embodiment, the piston is threaded according to this document on two lateral, opposite guide pins, which prevent rotation of the piston.

Furthermore, from the JP 61-084403 A a rotary motor known whose longitudinally displaceably guided piston sits on a helically rotated drive shaft, which is arranged eccentrically and thus prevents rotation of the piston. According to another embodiment of this document, the piston sits on two transversely spaced drive shafts, which are coupled together via a spur gear.

Furthermore, from the JP 61-278606 A a rotary motor is known, the shaft of which has a helical cam portion on which a counterpart inserted into the axially displaceable piston slides, which is intended to effect a seal. The training of both the shaft and the piston is quite complicated here, also can not be effected over the entire travel of the piston constant rotational movement. Furthermore, the shows JP 63-130905 A a rotary motor in which the shaft has a helical toothing on which the piston sits with a matching screw thread-shaped teeth. The sealing of the piston relative to the piston rod is to be effected solely by the Schraubverzahnungseingriff, which of course brings corresponding leakage at high pressures and / or low viscosity media and allows only a little efficient operation. Similar problems also arise in the rotation of the piston against the cylinder.

Moreover, the known rotary motors with steep-thread toothing achieve only very poor efficiencies, as result from high surface pressures and friction surfaces quite large losses. As a result, the field of application of such rotary motors has hitherto also been limited to lubricant-containing print media.

Proceeding from this, the present invention has the object to provide an improved rotary motor of the type mentioned, which avoids the disadvantages of the prior art and further develops the latter in an advantageous manner. Preferably, a cost-effective and easy-to-seal piston shaft assembly is to be created, which allows the generation of high torques and large rotation angle with favorable efficiency with a short engine length, regardless of the pressure medium used.

This object is achieved by a rotary motor according to claim 1. Preferred embodiments of the invention are the subject of the dependent claims.

The present invention thus leaves the previous approach to provide a screw engagement between the shaft and the piston and implement the axial movement of the piston in a rotational movement between the shaft and housing via a rotationally fixed guidance of the piston on the housing. Instead, the piston actuates the shaft on the crank principle in conjunction with the wedging action of the pitch of a helical engagement path. Surprisingly, in this case the hitherto always pursued approach can be left, that the piston of rotary motors, which implement an axial movement of the piston in a rotational movement of the shaft, in whatever form to secure against rotation, what the present invention ignores. According to the invention, the shaft forms a crankshaft whose axis of rotation is offset from the shaft passage recess. The respective shaft piece sliding through the shaft passage recess has a lever arm relative to the axis of rotation of the shaft, which forms the radial force produced by the axial displacement of the piston and the pitch of the spiral engagement track between the shaft and the piston and / or between the piston and the housing Rotary movement of the shaft relative to the housing or vice versa. In order to achieve favorable Kraftabtragsverhältnisse, it is particularly provided that the Wellendurchgangsausnehmung is arranged approximately centrally in the piston relative to the piston cross-sectional area, being dispensed with an anti-rotation of the piston, so that a rotatability of the piston relative to the housing is given. The arrangement of the shaft passage recess approximately in the centroid of the cross-sectional area of the piston results in low tilting moments and low restraining forces, which is also supported by the rotatability of the piston and the lack of anti-rotation or separate guides. In addition, a maximum effective lever arm can be achieved at low Hemmkräften by the aforementioned central arrangement of the shaft passage hole at the same time. Although an off-center shaft through hole could further increase the lever arm of the shaft per se, counteracting forces with counter-rotating lever arms would nullify the effect, especially as tilting moments would have to be compensated in this case, which would degrade the efficiency. The rotatability of the piston relative to the housing also allows in principle a variable pitch of the wave profile.

Compared to previously common steep-thread toothing between the piston and shaft or piston and housing, the production cost can be significantly reduced, since simple geometries can be selected for the piston and in particular for the shaft. In particular, the forces can be removed over a large area and complicated configurations of the seals between the piston and shaft and also between the housing and the piston can be avoided; In addition, these are not subject to the stresses caused by the torque transmission in Schraubgewindeverzahnungen. The usable simple geometries of the shaft and also the piston benefit not only a simple and cost-effective production per se, which is also easily and quickly adaptable to changing installation dimensions, but also an improved surface finish on the shaft and the piston, whereby friction losses can be reduced , This, together with the lower surface pressures, results in a higher efficiency of the engine and, moreover, also permits use without lubricant-containing pressure media. For the production of shaft, piston and cylinder simple rotationally symmetric manufacturing processes can be used. In a further development of the invention, the vortex technique can be used in particular for the shaft.

In a further development of the invention, the shaft has a helical course around its axis of rotation. The crank portion of the shaft is, so to speak, entangled spatially in the form of a helix about the axis of rotation. The helical turn advantageously has a constant radial distance from the axis of rotation of the shaft, while the pitch viewed in the axial direction can change. Preferably, however, the helical crank portion has a constant pitch to convert axial movements of the piston in a uniform rotational movement.

The housing may be a simple cylinder tube with a cylindrical inner circumferential surface, which may be formed in particular circular cylindrical in the simplest embodiment of the invention, since a rotationally fixed guidance of the piston in the housing is not necessary. In the case of a cylinder tube of circular cross-section and also a circular cross-section shaft, the eccentric dimension of the shaft, ie the wave jump, can be approximately one quarter of the difference between cylinder diameter and shaft diameter, ie ε = ¼ (d _z -d _w ). As a result, the best possible efficiency of the machine can be achieved in a compact and simple structure.

Alternatively, the shaft with its crank portion could also have a straight course parallel to and spaced from its axis of rotation. In this case, in order to realize the crank principle, the housing could have a spirally twisted inner circumferential surface, so that upon axial movement of the piston, it will make a helical movement about the axis of rotation of the shaft. The spirally twisted formation of the inner lateral surface of the housing may optionally also be provided in combination with the above-described helical formation of the shaft, so to speak to add the slopes and, accordingly, a greater translation between the axial adjusting movement of the piston and the rotational movement of the shaft relative to the housing to reach.

In a development of the invention, the pair of force-producing surface pairs on the piston and housing and / or on the piston and shaft simultaneously forms a sealing surface pair. which seals the pressure chamber for pressurizing the piston. As a result, an extremely short length can be realized. In addition, can be formed on both sides of the piston equally large effective piston surfaces in the invention, so that the full piston area can be effectively used with equal forces in both directions. In fact, on both sides of the piston, the entire housing inner diameter surface is only available in a reduced manner around the shaft cross section as a piston pressure surface. As a result, the same torques can be generated with the same hydraulic or pneumatic pressures in both directions of drive. In addition, for a given pressure results in a maximum torque output.

In particular, in each case at least one seal between the shaft and the Wellendurchgangsausnehmung in the piston and between the piston outer circumferential surface and the Gehäuseinnenmantelfläche is used. Due to the simple geometry of these inner and outer circumferential surfaces of the piston and the associated surfaces of the housing and shaft simple sealing elements can be found for example in the form of proven standard ring seals use.

According to a particularly advantageous embodiment of the invention, the seal is designed such that between the piston and the housing and / or between the piston and shaft each pressure pockets are formed, which can be fed from the piston driving the pressure chambers. In particular, peripheral circumferential sectors may be delimited by axially extending sealing elements in the circumferential direction on the piston skirt outer surface and / or on the lateral surface of the shaft passage recess in the piston, so that the corresponding peripheral sectors each form a pressure pocket, wherein one of the pressure pockets with the pressure chamber on the a piston side and the opposite pressure pocket with the pressure chamber on the opposite side of the piston can be brought into fluid communication. The pressure pockets are thus fed from different sides of the piston. This is based on the consideration that the radial forces to be removed always occur depending on the drive direction on the same side of the piston. The on the respective piston side for the respective hydraulic or pneumatic pressure occurring in a specific circumferential sector between the piston and the housing and / or between the shaft and the piston is selectively prevented by two axial sealing elements or - sections from flowing out of this peripheral sector on the other side of the piston, in the no radial forces are to be intercepted. As a result, a considerable reduction in friction can be achieved, which considerably affects the efficiency of the rotary motor. The radial forces to be absorbed can be intercepted to a considerable extent by the hydraulic or pneumatic pressure through such a pressure pocket formation and intelligent sealing arrangement. In a further development of the invention can be achieved analogously by a suitable Druckmediumführung and shaping of the seals pressure relief and possibly lubrication of the bearing points of the shaft.

In a further development of the invention, an overpressure protection is provided between the two pressure chambers of the engine, at least one which has a pressure chamber connecting a two pressure chambers, which in the normal case, i. is closed at a pressure below a predetermined threshold value of a pressure relief valve, which opens only when the said threshold value is exceeded. The overpressure protection can basically be integrated in the shaft in the form of a shaft recess. Advantageously, however, the overpressure protection can also be integrated in the piston, which facilitates the introduction of the overpressure channel, in particular in the case of a helical course of the shaft.

In order to achieve a favorable installation with simple production and favorable force removal, the shaft can advantageously be mounted on at least one end by means of a bearing plate or disk on the housing, preferably between the bearing plate and shaft, a releasable connection can be provided. In particular, a helically formed recess may be provided in the bearing plate, in which the shaft is received in register with a helical section. Advantageously, the helical shaft portion in the Lagerplattenausnehmung by a positive locking element, which may have various configurations, axially and / or radially braced or spread.

The shaft can be mounted differently at its two ends, preferably at one end by a fixed bearing and the other end by a floating bearing, so that the shaft is axially fixed only on one side.

In an advantageous embodiment of the invention, the entire construction of the housing is such or the bearing of the shaft designed such that the shaft together with the seated piston and preferably also together with the shaft supporting the bearing plate are taken out axially to one side of the housing can, which can be made accessible in a simple manner for the purpose of the seal replacement or maintenance of the piston and the seals. The engine may have a total, in particular unsymmetrical shape, in particular with regard to the end-side bearings.

The shaft or its crank section can basically have different cross-sectional geometries. According to an advantageous embodiment of the invention, the shaft has a simple circular cross-section.

Alternatively, the shaft may also have a flattened, in particular oval or ellipsoidal cross-section. As a result, advantages can be achieved with regard to the removal of the bending moment and the support of the deformation. In particular, the shaft can thereby better conform to a corresponding mating contour, so that a better support can be achieved.

Alternatively, the shaft may have other polygonal-shaped cross-sections, which may be advantageous for the compensation of bending forces, depending on the application, for example, in longer-lasting designs.

The shaft may have a constant along its optionally helically bent axis constant cross section in the invention, wherein advantageously the shaft surface smooth without grooves and projections, as they would be present in a screw thread toothing, is formed. Especially For example, the surface of the shaft can correspond to a continuous envelope surface, as occurs when, for example, a ball or a possibly differently shaped cross-sectional piece is moved along the optionally helically curved shaft axis. The shaft cross-sections thus advantageously have a constant geometry along the optionally curved longitudinal axis without cracks or other irregularities such as toothed grooves or the like. The shaft can advantageously be manufactured as an endless profile, which is cut to the desired length depending on the application, optionally also bearing journals being formed can be.

In an advantageous embodiment of the invention, the shaft may have an integrally formed bearing journal on one side, while the other shaft terminates on the other side in its helical profile, which is supported on a bearing plate.

The journal is advantageously according to an embodiment of the invention larger than the shaft in the region of its helical profile. In particular, the bearing pin can correspond approximately to the envelope, which wraps said helix or helical profile of the shaft. The diameter d _{L of} the bearing journal is advantageously the sum of the fourfold wave jump and the shaft diameter, ie d _L = 4ε + dw.

In particular, with relatively large shaft diameters and bearing journal can be provided, which are smaller than the Wellenduchmesser, in which case advantageously the bearing pin corresponds approximately to the inner envelope of the helical contour in order to achieve optimum bending stiffness, preferably d _L = d _w - 2ε applies.

The piston can also basically have different cross-sectional shapes. According to the invention, the piston has an annular outer peripheral contour, wherein in particular one of receiving pockets for sealing elements except circular cylindrical outer surface may be provided.

The Wellendurchgangsausnehmung in the piston may have different cross-sectional shapes, which are adapted in a further development of the invention to the respective shaft cross-section.

In order to minimize the friction losses and to further improve the efficiency of the engine, between the housing and the piston and / or the piston and the shaft in each case a rolling bearing may be provided preferably in the form of a ball bushing. Furthermore, abrasion-resistant and low-friction plastics can be used to minimize friction, from which the piston can be made, where appropriate, even the same sealing elements can be molded with.

Fig. 1

eine schematische räumliche Darstellung eines Drehmotors mit einer wendelförmig gebogenen Antriebswelle nach einer bevorzugten Ausführung der Erfindung,

Fig. 2

einen Längsschnitt durch den Motor aus Fig. 1,

Fig. 3

einen Querschnitt durch den Drehmotor aus den vorhergehenden Figuren, der auch die Hüllkurve der Welle zeigt,

Fig. 4

einen ausschnittsweisen Längsschnitt durch den Lagerabschnitt der Antriebswelle, die eine Wellenlagerung nach einer alternativen Ausführung der Erfindung mit vergrößerter Lagerscheibe für einen verbesserten stirnseitigen Lastabtrag,

Fig. 5

eine Draufsicht auf die Lagerscheibe aus Fig. 4, die die Position des Wellendurchtritts zeigt,

Fig. 6

eine ausschnittsweise Darstellung einer Antriebswelle nach einer alternativen Ausführung der Erfindung, bei der ein Abtriebswellenstummel integral einstückig mit der Antriebswelle verbunden ist,

Fig. 7

eine Schnittansicht eines mehrteilig ausgebildeten Kolbens nach einer bevorzugten Ausführung der Erfindung, wonach auf einem ringförmigen Kolbenträger beidseitig jeweils zwei Kolbenhalbschalen stirnseitig aufgesetzt sind,

Fig. 8

eine stirnseitige Draufsicht auf den Kolben aus Fig. 7,

Fig. 9

eine Schnittdarstellung eines aus zwei Halbschalen zusammengesetzten Kolbens nach einer alternativen Ausführung der Erfindung, bei der die Trennfuge entsprechend der Krümmung der Antriebswelle gebogen ist,

Fig. 10

ein Querschnitt durch den Kolben aus Fig. 9, der die Verschraubung der beiden Kolbenhalbschalen zeigt,

Fig. 11

eine Schnittansicht eines einteiligen Kolbens nach einer weiteren bevorzugten Ausführung der Erfindung mit Doppeldichtung und hydraulischer Druckkompensierung,

Fig. 12

eine stirnseitige Draufsicht auf den Kolben aus Fig. 11,

Fig. 13

eine Stirnansicht eines nicht erfindungsgemäßen oval ausgebildeten Kolbens , wobei die Antriebswelle im Schnitt und mit Ihrer Hüllkurve dargestellt ist,

Fig. 14

eine Stirnansicht eines ovalen Kolbens ähnlich Fig. 13, wobei jedoch auch die Antriebswelle einen ovalen Querschnitt besitzt,

Fig. 15

eine Stirnansicht eines nicht erfindungsgemäßen Kolbens mit einer eine mittige Einschnürung aufweisenden Ovalform, durch die eine verbesserte Abstützung der Antriebswelle erreicht werden kann,

Fig. 16

eine Schnittansicht durch einen nicht erfindungsgemäβen Drehmotor mit eiförmigem, polygonem Querschnitt der Antriebswelle und einem ebenfalls polygon ausgebildeten Kolben, die hinsichtlich Torsionssteifigkeit der Welle und der Kräftebalance am Kolben optimiert sind,

Fig. 17

eine ausschnittsweise Schnittansicht des Lagerbereichs der Antriebswelle des Drehmotors ähnlich Fig. 4 nach einer weiteren bevorzugten Ausführung der Erfindung, bei der ein an der Lagerscheibe befestigter Steuerschieber zur Endlagendämpfung und/oder stufenlosen Einstellung der Endlage vorgesehen ist,

Fig. 18

eine schematische Darstellung zweier Drehmotoren, die nach einer bevorzugten Ausführung der Erfindung hydraulisch miteinander synchronisiert sind,

Fig. 19

eine Längsschnittansicht eines Drehmotors der keine Ausführung der Erfindung darstellt, bei der zwei Antriebswellen in einem gemeinsamen Gehäuse angeordnet und von einem gemeinsamen Axialstellkolben antreibbar sind,

Fig. 20

eine Querschnittsansicht des Drehmotors aus Fig. 19, die in gemeinsamen Kolben sowie die beiden damit in Eingriff befindlichen Wellen geschnitten zeigt,

Fig. 21

einen Längsschnitt durch einen Drehmotor nach einer weiteren Ausführung der Erfindung, bei der die als Kurbelwelle ausgebildete Antriebswelle einen geraden Kurbelabschnitt besitzt, während der Kolben in einem spiralartig verdrehten Gehäuserohr längsverschieblich geführt ist,

Fig. 22

eine Querschnittsansicht des Drehmotors aus Fig. 21, die die Gehäusewandung und die Welle im Schnitt zeigt,

Fig. 23

eine ausschnittsweise Längsschnittdarstellung eines Drehmotors nach einer bevorzugten Ausführung der Erfindung, der eine Abtriebs-Getriebestufe aufweist, die in das Gehäuse bzw. den stirnseitigen Gehäusedeckel integriert ist,

Fig. 24

einen Längsschnitt durch einen Drehmotor nach einer weiteren bevorzugten Ausführung der Erfindung, bei der die wendelförmig gebogene Antriebswelle an ihrem Enden kugelgelenksartig gelagert ist,

Fig. 25

einen Querschnitt durch den Drehmotor aus Fig. 24,

Fig. 26

einen Längsschnitt durch einen einteiligen Kolben mit geteilt ausgebildeten Drucktaschen,

Fig. 27

eine Draufsicht auf den Kolben aus Fig. 26,

Fig. 28

einen Längsschnitt durch einen einteiligen Kolben mit geteilten Drucktaschen, die durch eine S-förmig umlaufende Dichtung erzeugt sind,

Fig. 29

eine Draufsicht auf den Kolben aus Fig. 28,

Fig. 30

einen Längsschnitt durch einen Drehmotor nach einer weiteren bevorzugten Ausführung der Erfindung, bei der eine Diagonaldichtung zwischen Kolben und Gehäuse und/oder zwischen Welle und Kolben vorgesehen und die Welle mit innerhalb ihres inneren Hüllprofils ausgeformten Abtriebswellenzapfen versehen ist,

Fig. 31

eine Seitenansicht der Welle des Drehmotors aus Fig. 30,

Fig. 32

eine Stirnansicht der Welle aus Fig. 31 in Blickrichtung des in Fig. 31 eingetragenen Pfeils A,

Fig. 33

eine Stirnansicht einer Wellenbefestigung an einer Lagerplatte nach einer bevorzugten Ausführung der Erfindung mit einem Formschlußelement in Form einer Schubplatte,

Fig. 34

eine Schnittansicht der Wellenbefestigung an der Lagerplatte aus Fig. 33,

Fig. 35

eine Stirnansicht einer Wellenbefestigung an einer Lagerplatte nach einer weiteren bevorzugten Ausführung der Erfindung mit einem Formschlußelement in Form einer Zahnplatte,

Fig. 36

eine Schnittansicht der Wellenbefestigung an der Lagerplatte aus Fig. 35,

Fig. 37

eine Stirnansicht einer Wellenbefestigung an einer zweiteiligen Lagerplatte nach einer weiteren bevorzugten Ausführung der Erfindung mit einem Formschlußelement in Form eines Schubstützrings,

Fig. 38

eine Schnittansicht der Wellenbefestigung an der Lagerplatte aus Fig. 37,

Fig. 39

eine Stirnansicht einer Wellenbefestigung an einer Lagerplatte nach einer weiteren bevorzugten Ausführung der Erfindung mit einem Formschlußelement in Form einer Schubmutter,

Fig. 40

eine Schnittansicht der Wellenbefestigung an der Lagerplatte aus Fig. 39,

Fig. 41

eine Stirnansicht einer Wellenbefestigung an einer Lagerplatte nach einer weiteren bevorzugten Ausführung der Erfindung mit einem Formschlußelement in Form einer Schubmutter,

Fig. 42

eine Schnittansicht der Wellenbefestigung an der Lagerplatte aus Fig. 41,

Fig. 43

eine Stirnansicht einer Wellenbefestigung an einer Lagerplatte nach einer weiteren bevorzugten Ausführung der Erfindung mit einem Formschlußelement in Form einer Schubmutter sowie einem Absatz an der Welle,

Fig. 44

eine Schnittansicht der Wellenbefestigung an der Lagerplatte aus Fig. 43,

Fig. 45

eine Stirnansicht einer Wellenbefestigung an einer Lagerplatte nach einer weiteren bevorzugten Ausführung der Erfindung mit einem Formschlußelement in Form einer Schlitzschubplatte,

Fig. 46

eine Schnittansicht der Wellenbefestigung an der Lagerplatte aus Fig. 45,

Fig. 47

eine Stirnansicht einer Wellenbefestigung an einer Lagerplatte nach einer weiteren bevorzugten Ausführung der Erfindung mit einem Formschlußelement in Form einer innenliegenden Schlitzschubplatte,

Fig. 48

eine Schnittansicht der Wellenbefestigung an der Lagerplatte aus Fig. 47,

Fig. 49

eine Stirnansicht einer Wellenbefestigung an einer Lagerplatte nach einer weiteren bevorzugten Ausführung der Erfindung mit einem die Welle aufspreizenden Spreizkonus,

Fig. 50

eine Schnittansicht der Wellenbefestigung an der Lagerplatte aus Fig. 49,

Fig. 51

eine Stirnansicht einer Wellenbefestigung an einer Lagerplatte nach einer weiteren bevorzugten Ausführung der Erfindung mit einem abgestuften Wellenende, das in einer abgestuften Lagerplattenausnehmung sitzt,

Fig. 52

eine Schnittansicht der Wellenbefestigung an der Lagerplatte aus Fig. 51,

Fig. 53

eine Stirnansicht einer Wellenbefestigung an einer Lagerplatte nach einer weiteren bevorzugten Ausführung der Erfindung mit einem exzentrisch abgeschrägten Wellenende, das in einer komplementären Lagerplattenausnehmung sitzt,

Fig. 54

eine Schnittansicht der Wellenbefestigung an der Lagerplatte aus Fig. 53,

Fig. 55

eine Stirnansicht einer Wellenbefestigung an einer Lagerplatte nach einer weiteren bevorzugten Ausführung der Erfindung mit Formschlußelementen in Form von radialen Gewindestiften,

Fig. 56

eine Schnittansicht der Wellenbefestigung an der Lagerplatte aus Fig. 55, und

Fig. 57

einen schematischen Längsschnitt durch einen Drehmotor nach einer bevorzugten Ausführung der Erfindung, bei dem die Welle an ihren Enden verschieden gelagert ist und zusammen mit dem Kolben axial aus dem Motorgehäuse entnehmbar ist.

The invention will be explained in more detail with reference to several embodiments and associated drawings. In the drawings show:

Fig. 1

3 is a schematic perspective view of a rotary motor with a helically curved drive shaft according to a preferred embodiment of the invention.

Fig. 2

a longitudinal section through the engine Fig. 1 .

Fig. 3

a cross section through the rotary motor from the preceding figures, which also shows the envelope of the shaft,

Fig. 4

1 is a longitudinal sectional view through the bearing portion of the drive shaft, the shaft bearing according to an alternative embodiment of the invention with an enlarged bearing plate for an improved frontal load transfer,

Fig. 5

a plan view of the bearing disc Fig. 4 showing the position of the shaft passage,

Fig. 6

1 is a fragmentary view of a drive shaft according to an alternative embodiment of the invention in which an output shaft stub is integrally connected integrally with the drive shaft;

Fig. 7

3 a sectional view of a multi-part piston according to a preferred embodiment of the invention, according to which two piston half-shells are mounted on the front side on an annular piston carrier on both sides,

Fig. 8

a frontal plan view of the piston Fig. 7 .

Fig. 9

a sectional view of a composite of two half-shells piston according to an alternative embodiment of the invention, in which the parting line is bent according to the curvature of the drive shaft,

Fig. 10

a cross section through the piston Fig. 9 showing the screw connection of the two piston half-shells,

Fig. 11

a sectional view of a one-piece piston according to another preferred embodiment of the invention with double seal and hydraulic pressure compensation,

Fig. 12

a frontal plan view of the piston Fig. 11 .

Fig. 13

an end view of a non-inventive oval-shaped piston, wherein the drive shaft is shown in section and with your envelope,

Fig. 14

similar to an end view of an oval piston Fig. 13 but also the drive shaft has an oval cross-section,

Fig. 15

an end view of a non-inventive piston having a central constriction having oval shape, through which an improved support of the drive shaft can be achieved

Fig. 16

a sectional view through a non-erfindungsgemäβen rotary motor with egg-shaped, polygonal cross-section of the drive shaft and a likewise polygon-shaped piston, with respect to torsional stiffness the shaft and the balance of forces are optimized on the piston,

Fig. 17

a fragmentary sectional view of the bearing portion of the drive shaft of the rotary motor similar Fig. 4 according to a further preferred embodiment of the invention, in which a control slide fastened to the bearing disk is provided for cushioning the end position and / or stepless adjustment of the end position,

Fig. 18

a schematic representation of two rotary motors, which are hydraulically synchronized with each other according to a preferred embodiment of the invention,

Fig. 19

a longitudinal sectional view of a rotary motor is not an embodiment of the invention, in which two drive shafts are arranged in a common housing and driven by a common Axialstellkolben,

Fig. 20

a cross-sectional view of the rotary motor Fig. 19 that shows cut in common pistons as well as the two shafts engaged with it,

Fig. 21

a longitudinal section through a rotary motor according to a further embodiment of the invention, in which the drive shaft designed as a crankshaft has a straight crank section, while the piston is guided longitudinally displaceably in a spiral-twisted housing tube,

Fig. 22

a cross-sectional view of the rotary motor Fig. 21 showing the housing wall and the shaft in section,

Fig. 23

1 is a partial longitudinal sectional view of a rotary motor according to a preferred embodiment of the invention, which has a driven gear stage, which is integrated in the housing or the front-side housing cover,

Fig. 24

a longitudinal section through a rotary motor according to another preferred embodiment of the invention, in which the helically curved drive shaft is mounted at its ends like a ball joint,

Fig. 25

a cross section through the rotary motor Fig. 24 .

Fig. 26

a longitudinal section through a one-piece piston with split pressure pockets,

Fig. 27

a plan view of the piston Fig. 26 .

Fig. 28

a longitudinal section through a one-piece piston with split pressure pockets, which are generated by an S-shaped circumferential seal,

Fig. 29

a plan view of the piston Fig. 28 .

Fig. 30

a longitudinal section through a rotary motor according to another preferred embodiment of the invention, in which a diagonal seal between the piston and the housing and / or between the shaft and piston provided and the shaft is provided with formed within its inner envelope profile output shaft journal,

Fig. 31

a side view of the shaft of the rotary motor Fig. 30 .

Fig. 32

an end view of the shaft Fig. 31 in the direction of the in Fig. 31 registered arrow A,

Fig. 33

an end view of a shaft attachment to a bearing plate according to a preferred embodiment of the invention with a positive locking element in the form of a thrust plate,

Fig. 34

a sectional view of the shaft attachment to the bearing plate Fig. 33 .

Fig. 35

an end view of a shaft attachment to a bearing plate according to another preferred embodiment of the invention with a positive locking element in the form of a tooth plate,

Fig. 36

a sectional view of the shaft attachment to the bearing plate Fig. 35 .

Fig. 37

an end view of a shaft attachment to a two-part bearing plate according to a further preferred embodiment of the invention with a positive locking element in the form of a thrust support ring,

Fig. 38

a sectional view of the shaft attachment to the bearing plate Fig. 37 .

Fig. 39

an end view of a shaft attachment to a bearing plate according to a further preferred embodiment of the invention with a positive locking element in the form of a push nut,

Fig. 40

a sectional view of the shaft attachment to the bearing plate Fig. 39 .

Fig. 41

an end view of a shaft attachment to a bearing plate according to a further preferred embodiment of the invention with a positive locking element in the form of a push nut,

Fig. 42

a sectional view of the shaft attachment to the bearing plate Fig. 41 .

Fig. 43

an end view of a shaft attachment to a bearing plate according to a further preferred embodiment of the invention with a positive locking element in the form of a push nut and a shoulder on the shaft,

Fig. 44

a sectional view of the shaft attachment to the bearing plate Fig. 43 .

Fig. 45

an end view of a shaft attachment to a bearing plate according to another preferred embodiment of the invention with a positive locking element in the form of a slot thrust plate,

Fig. 46

a sectional view of the shaft attachment to the bearing plate Fig. 45 .

Fig. 47

an end view of a shaft attachment to a bearing plate according to a further preferred embodiment of the invention with a positive locking element in the form of an internal slot thrust plate,

Fig. 48

a sectional view of the shaft attachment to the bearing plate Fig. 47 .

Fig. 49

an end view of a shaft attachment to a bearing plate according to a further preferred embodiment of the invention with a spreading cone spreading the shaft,

Fig. 50

a sectional view of the shaft attachment to the bearing plate Fig. 49 .

51

an end view of a shaft attachment to a bearing plate according to another preferred embodiment of the invention with a stepped shaft end which sits in a stepped Lagerplattenausnehmung,

Fig. 52

a sectional view of the shaft attachment to the bearing plate 51 .

Fig. 53

an end view of a shaft attachment to a bearing plate according to a further preferred embodiment of the invention with an eccentrically beveled shaft end, which sits in a complementary Lagerplattenausnehmung,

Fig. 54

a sectional view of the shaft attachment to the bearing plate Fig. 53 .

Fig. 55

an end view of a shaft attachment to a bearing plate according to a further preferred embodiment of the invention with interlocking elements in the form of radial screws,

Fig. 56

a sectional view of the shaft attachment to the bearing plate Fig. 55 , and

Fig. 57

a schematic longitudinal section through a rotary motor according to a preferred embodiment of the invention, in which the shaft is mounted differently at their ends and can be removed together with the piston axially from the motor housing.

The in the FIGS. 1 to 3 The rotary motor shown comprises a tubular, cylindrical housing 1, which is closed at its two end faces in each case by a Lagerdekkel 2. The housing 1 can be made of an endless profile, which has been cut to the desired length. In the interior of the housing 1, a piston 3 is received axially displaceable, which divides the interior of the housing 1 into two pressure chambers 4 and 5, which can be acted upon in the illustrated embodiment via pressure medium lines in the bearing caps 2 with pressure medium, so that, depending on which the two chambers 4 or 5 is acted upon with pressure medium, the piston 3 moves axially in the housing 1 back and forth.

Furthermore, a drive shaft 6 is accommodated in the housing 1, which is rotatably mounted in the illustrated embodiment on both bearing caps 2, so that it can be rotated about an axis of rotation 7 parallel to the longitudinal axis of the cylindrical housing 1. As Fig. 1 and Fig. 2 show, the drive shaft 6 in the illustrated embodiment is helically rotated about the said axis of rotation 7, wherein the drive shaft 6 to the said axis of rotation 7 has an eccentricity, which gives the respective engagement portion of the shaft with the piston a lever arm with respect to the axis of rotation 7. The drive shaft 6 is screwed, so to speak, about the axis of rotation 7 around and actuates the lever arm on the wedge effect of the slope. In cross section, the drive shaft 6 in the in FIGS. 1 to 3 drawn execution circular. It can consist of an endless profile which has been cut to the desired length. On the front side, it is in each case attached to a bearing plate 8, on which in turn a rotationally fixed fixedly extending through the bearing cap 2 extending output shaft in the form of a stub shaft 9.

As Fig. 2 shows, the piston 3 has a Wellendurchgangsausnehmung 10 with which the piston 3 is longitudinally displaceable on the drive shaft 6, wherein the piston according to its preferably helical Wellendurchgangsausnehmung undergoes a rotation in the displacement on the shaft. The Wellenendurchgangsausnehmung 10 is circular in cross section as the drive shaft 6, wherein viewed in the axial direction, the Wellendurchgangsausnehmung 10 is adapted to the curved course of the drive shaft 6 and has a dekkungsgleichen curved course with the shaft.

Advantageously, the geometry ratios and the arrangement of the drive shaft 6 are selected such that the Wellendurchgangsausnehmung 10 is located substantially centrally in the cross-sectional area center of gravity of the piston 3, so that the piston 3 is balanced with respect to the forces induced by the drive shaft 6, in particular no tilting moments occur. For this purpose, the drive shaft 6 is radially offset with its axis of rotation 7 with respect to the longitudinal center axis of the housing 1 and the piston 3, and advantageously as far as possible, so that the drive shaft 6 with a center as possible between their two ends or depending on the slope with several portions of the inner circumferential surface of the housing 1 is present or supported thereon. In Fig. 2 this point is indicated by the reference numeral 11. It is understood that this point migrates upon rotation of the drive shaft 6. In the case of a cylinder tube of circular cross-section and also a circular cross-section shaft, the eccentric dimension of the shaft, ie the wave jump, can be approximately one quarter of the difference between cylinder diameter and shaft diameter, ie ε = ¼ (d _z -d _w ). As a result, the best possible efficiency of the machine can be achieved in a compact and simple structure.

Advantageously, the surface pairs, which cause the transmission of force between the drive shaft 6 and the piston 3 and between the piston 3 and the housing 1, so the outer surface of the drive shaft 6 and the inner circumferential surface of the Wellendurchgangsausnehmung 10 on the one hand and the piston outer lateral surface and the housing inner circumferential surface on the other hand sealing surface pairs, which seal the pressure chambers 4 and 5. Advantageously, gaskets 12 and 13 are integrated in these surface pairs in order to avoid pressure losses. The shaft seal 12 is seated in the illustrated embodiment in the Wellendurchgangsausnehmung 10 and slides on the outer surface of the drive shaft 6 from. The housing seal 13 is seated on the piston outer lateral surface and seals the piston 3 with respect to the housing 1, on which said seal 13 slides off. Both seals are formed in the illustrated embodiment as sealing rings.

If one of the pressure chambers 4 or 5 pressurized medium, the piston 3 moves axially. This axial adjusting movement leads to a rotation of the drive shaft 6 about the axis of rotation 7, since each passing through the Wellendurchgangsausnehmung 10 helical section of the drive shaft 6 has a corresponding lever arm with respect to the axis of rotation 7 and the slope of the drive shaft 6 wedge effect exerts the axial force of the Moves piston 3 in a lever arm actuating radial force. The drive shaft 6 is driven by the cranking principle by the axial adjusting movement of the piston 3. Since the Wellendurchgangsausnehmung 10 sits in the center of the piston 3, the forces transmitted from the drive shaft 6 on the piston have approximately no lever arm, so that these forces cause approximately no torque on the piston. The piston 3 need not be guided against rotation in the housing 1. This has an advantageous effect on the seals 12 and 13.

The in the Fig. 1 to 2 shown embodiment brings considerable benefits. First, the direct insertion of the drive shaft 6 in the Wellendurchgangsausnehmung 10 and the piston 3 in the housing 1 with each integrated seal the required installation length shortened and it can be generated by a small slope of the helical course of the drive shaft 6, a large torque. It will be introduced into the piston 3 and via this in the housing 1 substantially radial forces. Compared to the conventional solutions with steep teeth or coarse thread toothing, the production cost for both the piston outer guide as well as the piston inner guide to the shaft can be significantly reduced. Ideally, very easy to produce shapes and components are used, which can be manufactured endless and assembled according to demand and length. By the load attack at the middle of the coil, the lever length and the pitch of the helical drive shaft 6 can be set almost arbitrarily. A low pitch and a large lever arm generate great moments. In addition, the piston surface can be used effectively, with equal forces in both directions can be achieved. In essence, the entire housing internal cross-sectional area minus the shaft cross-sectional area is available as the effective piston area. Furthermore, due to the low surface pressures and lubricant-free or low-pressure media such as water or air can be used.

Advantageously, a part of the axial load transfer via the bearing plate 8, by means of which the drive shaft 6 is mounted frontally at the housing end, especially if a large-scale bearing plate 8 is used, as this Fig. 4 shows. The drive shaft 6 extends in its helical shape and pitch in the bearing plate 8 and transmits through its spiral shape over the entire surface of the torque on the bearing plate, where they can be secured only by means of an axial and / or radial securing, for example in the form of a screw 14 against withdrawal. If, for example, the pressure chamber 4, the in Fig. 4 shown, mandated with pressure medium, this pushes the piston 3 to the right, which is transmitted to the drive shaft 6, an axial force, the drive shaft 6 according to Fig. 4 tried to pull to the right. However, the same pressure in the pressure chamber 4 also acts on the bearing plate 8, which partially compensates for this axial force. As Fig. 5 shows, the bearing plate 8 can remove the torque via a plurality of screw 15, whereby seals 16 and 17, the seal of the pressure chamber 4 is ensured.

Fig. 6 shows the drive shaft 6 with a directly connected or connected shaft frusto-conical output shaft 9. Advantageously, while the diameter of the output shaft stub 9 and the width of the bearing plate 8 is not greater than the diameter of the output shaft 6 itself, so that a shaft seal 12 for sealing the piston 3 relative to the shaft 6 can be pushed over the drive shaft stub 9 away on the drive shaft 6. This is advantageously supported by a bevel 18 on the bearing plate 8. The entire drive shaft 6 together with the connected output stub shaft 9 is designed such that an elastic sealing ring with an inner diameter corresponding to the outer diameter of the drive shaft 6, can be slid over the entire shaft assembly.

Advantageously, however, the drive shaft 6 is preferably connected at one of its ends releasably connected to a separately formed plate 8 as the location Fig. 33 ff show. The support of the drive shaft 6 via a separate bearing plate 8 makes it possible to remove very high axial and transverse forces with superimposed torques without having to accept excessive production costs.

It is particularly preferred if there is a connection of the type Helix-in-Helix between the bearing plate and the drive shaft, i. the drive shaft 6 sits with its spiral or helical course in a likewise spiral or helical recess 50 in the bearing plate 8. Advantageously, while the helical shaft portion is axially and / or radially fixed in the helical recess 51 of the bearing plate by means of a positive locking element 51 and possibly advantageously braced or spread, whereby the releasable joints caused by the helix radial clearance can be eliminated.

As the FIGS. 33 and 34 show, the drive shaft 6 with its helical contour per se unchanged in the bearing plate 8 and the provided therein also helically contoured recess 50 run into it. The form-locking element 51 is formed in this embodiment of a - roughly speaking - crescent-shaped thrust plate 52 which engages in a radially extending groove 53 in the drive shaft 6 and is supported on the bearing plate 8. For mounting, the bearing plate 8 is pushed on the drive shaft inward or rotated until the thrust plate 52 can be placed in the groove 53, after which the bearing plate 8 retracted can be. The end face provided in the bearing plate 8 recess for receiving the thrust plate 52 can this purpose in FIG. 33 have shown recess 54 which has oversize in the circumferential direction to allow the turning back. When tightening the mounting screws 55, the thrust plate 52 spreads between the preferably wedge-shaped groove 53 and the preferably conical recess 54 in the bearing plate 8, whereby a backlash, preloaded axial and radial lock is created.

As the FIGS. 35 and 36 show, instead of in Fig. 33 also show a toothed plate 56 used as a positive locking element for securing the shaft and the bearing plate use. The toothed plate 56 is toothed at one end and tapered at the other end or wedge-shaped in order to be able to be tipped. By means of fastening screws 55, a backlash-free radial and axial securing can also be created here, cf. Figs. 35 and 36 , wherein advantageously no rotation of the flange is necessary.

In the execution of the FIGS. 37 and 38 is used as a form-locking element 51 for fixing the drive shaft 6 in the helical recess of the bearing plate 8, a thrust support ring 57. The bearing plate 8 is in this case in two parts, wherein advantageously the parting plane lies outside the fluid guide. The thrust support ring may be designed to be multi-part or one-piece slotted resilient. The thrust support ring 57 may be formed on the inside and / or outside conical and / or tapered, so that when contracting the two bearing plate parts axial and radial clamping of the connection is achieved. Alternatively or additionally, a nominal gap may be present between the two bearing plate parts with respect to the helical recess formed in them, so that the two bearing plate parts during linear tightening of the clamping device connecting them while preventing relative rotation of the two bearing plate parts, which by linear guides, for example. In the form of guide pins - preferably by means of guide screws 58 - can be effected, brace with respect to the helical contour and jammed on the drive shaft 6.

Alternatively, the drive shaft 6 can be held in the Lagerplattenausnehmung 50 by means of a sliding nut 59, as in the FIGS. 39 to 44 shown. In the execution after FIGS. 39 and 40 the thrust nut 59 is provided with an external thread and an internal thread, so that it can be screwed to the bearing plate 8 and the drive shaft 6 in order to clamp the drive shaft 6 in the Lagerplattenausnehmung 50. According to the FIGS. 41 and 42 the thrust nut 59 is screwed by means of an internal thread to the drive shaft 6, wherein the helical contour is discontinued in the bearing plate 8, so that the drive shaft 6 with its shoulder, which forms the transition from the Helixkontur the drive shaft 6 to its threaded portion against the corresponding Shoulder can be stretched in the Lagerplattenausnehmung. In addition, the thrust nut is supported on the bearing plate side on a conical Schubmutterausnehmung, so that a Radialspiel eliminating centering is achieved, see. Fig. 42 ,

In the execution of the FIGS. 43 and 44 the helical contour of the drive shaft has a diameter taper, which can be produced in a simple manner, and thus a shoulder 60 with which it can be tensioned against the inside of the bearing plate 8. Advantageously, a simple clamping nut 61 is screwed on the end face on the shaft end, which spans against the bearing plate 8 and thus pulls the shoulder 60 of the drive shaft 6 against the bearing plate 8, see. Fig. 44 ,

According to the FIGS. 45 and 46 can be fixed by a slot thrust plate 62 in the helical recess 50 of the bearing plate 8, the drive shaft 6, which is inserted radially from the outside into a slot in the bearing plate 8 until it engages in a circumferentially provided groove on the drive shaft 6, see. Fig. 46 , The slot thrust plate 62 can be approximately lens-shaped overall - roughly speaking. FIGS. 47 and 48 show a basically similar design, but here the slot thrust plate 62 is inserted from the inside into a slot-shaped recess in the bearing plate 8, which is formed deeper than the width of the slot thrust plate, so that the slot thrust plate 62 can first be inserted so deeply that the Drive shaft goes into the Lagerplattenausnehmung 50. The slot thrust plate 62 is then advantageously through pushed a cone or an eccentric screw 63 radially inwardly into the groove in the drive shaft 6 and clamped, see. FIGS. 47 and 48 , In principle, this could also be reversed and the slot thrust plate 62 first sunk in a too deep shaft groove and then stretched outwards into the bearing plate slot.

In order to achieve a particularly secure elimination of any play between the drive shaft 6 and the bearing plate 8, a widening of the shaft cross-section can be provided which presses the shaft portion stuck in the helical Lagerplattenausnehmung 50 with the bearing plate 8, as the FIGS. 49 and 50 demonstrate. For this purpose, the drive shaft 6 has an end face, preferably a conical recess, into which an expansion cone 64 can be inserted axially in order to widen the wave contour. For example, for this purpose, the expansion cone can be pulled by a clamping screw in the shaft recess. Alternatively or additionally, the expansion cone can be pressed. Advantageously, the drive shaft can be widened into the plastication area, so that joint compression occurs. This can be particularly advantageous in conjunction with an eccentric widening, which can be achieved by a corresponding insertion direction of the expansion cone 64. Alternatively, however, it is also possible to work with a centric expansion achievable by a centric introduction of the expansion cone 64. Depending on the cone angle, the connection can be released again in the elastic deformation area.

An alternative drive shaft bearing plate connection show the FIGS. 51 and 52 , After this, the shaft section seated in the bearing plate recess 50 has a plurality of cylindrical, preferably also slightly conical, steps 65, which are preferably arranged within the helical contour or within the helical envelope surface of the drive shaft 6, so that they can be machined or otherwise machined out of the helix contour , Preferably, the gradations are offset relative to each other with respect to their respective geometric axes, cf. 51 so that 50 moments are transmitted via the congruently formed gradations of Lagerplattenausnehmung can. Advantageously, this design of the drive shaft-bearing plate connection allows a linear right-angled or paraxial pressing process and a simple manufacturing process. By a slightly conical design of the gradations on the drive shaft and / or the Lagerplattenausnehmung radial clearance can be eliminated. The axial securing can be provided separately, for example in the form of a screw nut, which is screwed onto the shaft end and stretches against the bearing plate 8, cf. Fig. 52 ,

As an alternative to such gradations, the drive shaft 6 may also have eccentrically offset circumferential surface sections 66 and 67 in the region of its shaft section located in the bearing plate 8, which may be formed in particular by a one-sided conical bevel in the otherwise helical contour of the drive shaft 6. The bearing plate recess is designed to be complementary. By the offset of the two peripheral surface portions 66 and 67 and torques can be transmitted. The drive shaft is axially secured as before by a nut and clamped to the bearing plate.

The FIGS. 55 and 56 continue to show a pin connection between the drive shaft 6 and the bearing plate 8, wherein also here the drive shaft 6 is seated with a helically contoured shaft portion in the likewise helical Lagerplattenausnehmung. Several pins 68, preferably threaded pins are advantageously introduced outside the fluid guide between the bearing plate 8 and the drive shaft 6, wherein the pins 68 are screwed in the illustrated embodiment radially from the outside into the bearing plate 8 until they engage in the drive shaft 6, see. Fig. 56 ,

The piston 3 of the rotary motor can basically be designed differently. The FIGS. 7 and 8 a piston carrier 19 is annular and forms with its radially outer portion of the outer circumferential surface of the piston 3. The front end of the piston carrier 19 has two circular recesses, in each of which two inner half shells 20 and 21 can be used, each together an annular shell form, the inner circumferential surface together form the Wellendurchgangsausnehmung 10. Advantageously, 20 and 21 of the inner sealing ring 12 can be used between the front-mounted inner half-shell pairs.

The one-piece piston carrier 19 advantageously has an inner diameter which is sufficiently large to be slid over the end bearing plates 8 of the drive shaft 6.

An alternative, also multi-part piston training show the FIGS. 9 and 10 , Here, the piston 3 consists of two piston half-shells 22 and 23, which are aufeinandersetzbar in the radial direction. The parting line 24 advantageously extends arcuately, as this Fig. 9 shows. In particular, it can follow the likewise arcuate course of the shaft passage recess 10, which corresponds to the helical course of the drive shaft 6. The two piston half-shells 22 and 23 can be screwed together by means of screws 25 and centering sleeves 26.

As Fig. 9 shows, two inner sealing rings 12 and two outer sealing rings 13 are provided on the piston 3 in the illustrated embodiment.

Alternatively, the piston 3 may also be formed in one piece. Such an embodiment show the FIGS. 11 and 12 , which requires the corresponding releasable connection of the drive shaft 6 with the bearing plates 8 and a formation of the bearing or driven shaft journal within the inner envelope of the drive shaft 7, as still in connection with FIGS. 30 to 32 is described. Here, too, two axially spaced-apart inner seals 12 and outer seals 13 are provided, each extending in an annular manner around the corresponding piston outer and inner circumferential surface. This can advantageously be used to fill between the respectively formed between a pair of sealing rings, annular pressure pockets 27 and 28 with hydraulic or pneumatic pressure from the respective pressure-responsive pressure chamber 4 and 5 respectively. For this purpose corresponding feed bores 29 are formed in the piston, on the one hand in the end faces open the piston 3 and on the other hand open into said pressure pockets 27 and 28 on the lateral surfaces of the piston between the sealing rings. Via a valve 30, the connection of the feed holes 29 can be controlled with the respective pressure side, see. Fig. 11 , About such from the pressure chambers 4 and 5 fed pressure pockets 27 and 28 on the one hand, the induced radial forces can be at least partially intercepted and on the other hand, the friction can be considerably reduced, which significantly improves the efficiency of the rotary motor.

As Fig. 13 shows, the piston 3 may also have an oval cylindrical shape. As a result, the piston chamber can be better utilized on the one hand by the displacement of the force application point. On the other hand, the false lever to the flat side of the piston is smaller. In particular, in a balanced piston, a greater wave jump can be achieved. Furthermore, it should be noted that in the in Fig. 13 shown oval shape of the piston, the envelope 31 of the helically bent drive shaft 6 is better, ie over a longer curve section to the inner circumferential surface of the housing 1. However, a better support of the drive shaft 6 can be achieved on the housing 1, which is particularly important for longer designs in which the axial forces can induce larger shaft bends.

As Fig. 14 shows, the drive shaft 6 may have an oval or ellipsoidal cross-section. This improves the stability of the drive shaft 6 in the bending direction. The flat side of the oval or ellipsoidal cross section of the drive shaft 6 can better conform to the likewise oval or ellipsoid inner surface of the housing 1, whereby a better support is achieved.

The supporting effect can be further improved by the fact that the inner circumferential surface of the overall - roughly speaking - oval-shaped housing 1 experiences a constriction in the middle, so that the narrow side is better used on the envelope 31 of the drive shaft 6, as this Fig. 15 shows.

As Fig. 16 shows, the drive shaft 6 can also receive an egg-shaped or polygonal cross-section which is thicker towards the envelope outside and thinner toward the inside, whereby the drive shaft 6 is optimized in terms of its bending and torsional rigidity. Also, the housing 1 and the outer circumferential surface of the piston 3 has such a polygonal cylinder contour, which is thicker on one side and thinner to the side on which the drive shaft 6 is supported. However, a compact, force balanced cylinder can be achieved.

In order to achieve a cushioning and / or a continuous adjustment of the end position of the piston 3, in the in Fig. 17 shown an adjustable spool 32 may be provided, which is associated with the pressure medium supply or discharge line 33 through which the pressure chamber 4 and 5 can be filled and emptied. About the spool 32, the opening cross section of said conduit 33 can be changed. Will he be completely closed, like this Fig. 17 shows, the piston 3 can not go further to the left; he has reached his final position.

About the in Fig. 18 shown control scheme, two rotary motors can be synchronized in a simple manner with respect to their rotational movements over the printing medium. Advantageously, the two rotary motors can be identical to each other and essentially the execution of the FIGS. 1 to 3 correspond. The pressure chambers 4 and 5 of the respective motors are each filled via a common pressure line 34 and 35, which forks on a flow divider 36 and leads into the respective pressure chambers 4 and 5 of the two motors.

Fig. 19 shows, however, an embodiment of a rotary motor with two mechanically synchronized via a common piston 3 drive shafts 6. As shown in Figures 19 and 20, the piston 3 in this embodiment advantageously has a flattened cross-section, in particular it may be formed oval or ellipsoidzylindrisch so that arranged on the resulting flat sides of the correspondingly shaped housing 1, the two drive shafts 6 can be. The common piston 3 has in this case two Wellendurchgangsausnehmungen 10, with which the piston 3 slides slidably on the two drive shafts 6.

Advantageously, the two drive shafts 6, which are each formed helically in the manner described above, offset in their helical turns to each other, so stuck in the two Wellendurchgangsausnehmungen 10 counter-curved shaft sections. As a result, the resulting radial forces, which are induced by the shaft in the piston 3, can be compensated.

As the Figures 19 and 20 show, in such a double - shaft design of the motor advantageously centrally a guide rod 37 may be used in the interior of the housing 1, which connects the two end - side housing - or bearing cap 2 together. The piston 3 has a corresponding recess which is slidably seated on said guide rod 37. The guide rod 37 causes in addition to the piston guide a power input for the hydraulic pressure by connecting advantageously the front-side housing sections. In addition, the piston area is reduced, which can be of importance in particular for very large engine designs.

It can be achieved by different arrangements of the wave profiles relative to each other different advantages. While the in Fig. 20 shown installation position allows a large axial distance of the two shafts with compact outer dimensions, the waves can according to a further preferred embodiment of the invention also as in Fig. 20A shown to achieve a transverse force compensation. As Fig. 20A shows, acting in the installation position of the shafts shown there, the forces acting on the piston by the waves forces F1 and F2 against each other, so that the resulting bearing reaction force corresponds to about zero. The axes of rotation 7 of the drive shafts 6 are not on the connecting line between the two Wellendurchgangsausnehmungen, but are offset transversely thereto, see. Fig. 20A ,

The FIGS. 21 and 22 Although in this embodiment, the drive shaft 6 is also designed as a crankshaft, but it has a straight course, which is offset from the axis of rotation 7 of the drive shaft and extending parallel to said axis of rotation 7 , see. Fig. 21 , To drive the drive shaft 6 on the crank principle, the inner circumferential surface of the housing 1 is helically or helically about the axis of rotation 7 of the drive shaft 6 around in twisted or screwed, so that the piston 3 performs a helical rotation about the axis of rotation 7 at an axial displacement around. As a result, the drive shaft 6 is rotated according to a crank.

In order to adjust the output speed or the output rotation angle and the achievable output torques to the requirements even with a given housing length and shaft pitch, can, as Fig. 23 shows in the housing 1 and / or in the bearing cap 2 a Abtriebsübersetzungs- or reduction gear 38 may be integrated. In particular, the drive shaft 6 bearing bearing plate 8 have a spur gear, which meshes with an output gear 39 which drives an abrasion shaft 40, which is also mounted on the housing 1, the end side closing bearing cap 2 and passes through it, see. Fig. 23 ,

The FIGS. 24 and 25 show an embodiment that basically the of FIGS. 1 to 3 is similar and in other areas this corresponds. Alternatively to the in the FIGS. 1 to 3 As shown embodiment, the drive shaft 6 is not rigidly connected to the bearing discs or plates 8, but connected like a ball joint with them.

Similar to the execution of the FIGS. 11 and 12 also show the FIGS. 26 and 27 a one-piece piston, in which two axially spaced inner seals 12 and outer seals 13 are provided, each annular run around the corresponding piston outer and inner circumferential surface around. Unlike the execution after Fig. 11 In addition to this circumferentially extending seals axially extending sealing elements are provided which on opposite sides of the piston (see. Fig. 27 ) connect the two axially spaced seals 12 and 13 together. By said axial sealing webs 12a and 13a, the circumferentially between the seals 12 and 13 extending pressure pockets 27 and 28 are divided so that they are half-ring shaped on opposite circumferential sides. As a result, the pressure pockets can be fed from the pressure chambers 4 and 5, depending on which side of the pressure applied to the piston 3. As FIGS. 26 and 27 show, said pressure pockets 27 and 28 fed via feed holes 29a and 29b once from the pressure chamber 4 and once fed from the pressure chamber 5.

The FIGS. 28 and 29 show a corresponding piston training like the FIGS. 26 and 27 , In contrast, however, there are no two spaced apart, provided in the circumferential direction seals provided, but only such a seal, however, by an S-shaped curve, see. Fig. 28 , or simplified only diagonal course in sections on the pressure chamber 4 side facing and in an opposite section to the pressure chamber 5 facing side of the piston 3 is offset, in each case over about half the circumference of the piston. About this S-shaped or diagonal course, like him Fig. 28 also shows two sector-shaped pressure pockets are divided from each other, which are fed in the above manner from the various pressure chambers 4 and 5 ago.

At the in Fig. 30 shown further embodiment of the present invention are also formed between the piston 3 and the housing 1 and between the piston 3 and the shaft 6 opposed pressure pockets, which are delimited in the illustrated embodiment, however, by an annular seal 13 and 12, respectively each extends diagonally across the circumference of the piston, as this Fig. 30 shows. The pockets get this way an oblique wedge-like training in which the depth of the pressure pockets viewed in the circumferential direction increases or decreases in opposite directions. It is understood that here is the one pressure pocket with the one piston side and the other pressure pocket with the other side of the piston in pressure communication, so that when pressure is applied to a pressure chamber which is fed a pressure pocket and pressurizing the other pressure chamber of the rotary motor, the other pressure pocket. This also allows a corresponding pressure relief can be achieved.

Furthermore, the different in Fig. 30 shown embodiment of the rotary motor by the formation of the shaft 6 and the associated output shaft journal 9. How the FIGS. 31 and 32 show, the shaft 6 has a relatively large shaft diameter with a relatively small eccentricity of the axis of rotation 7. The bearing or drive shaft journal 9 are advantageously formed in the interior of the inner envelope profile of the shaft 6 and can thereby be integrally formed integrally with the shaft body. In Fig. 32 Reference numeral 41 denotes the inner envelope profile of the shaft 6, within which said bearing or driven shaft journal 9 extends.

As Fig. 30 shows, the shaft 6 is attached in the illustrated embodiment via two bearings 42 on the housing covers, which may be rigidly connected to the housing 1 in this embodiment. In particular, the shaft 6 is clamped between two tapered roller bearings, which shorten the relevant for the bending of the shaft, effective bearing distance. About clamping screws 43, the bearing caps can be clamped on each other or on the housing 1. About seals 44 and 45, the respective bearing cap on the one hand against the bearing or driven shaft journal 9 and on the other hand sealed against the housing.

A particularly advantageous embodiment of the rotary motor shows Fig. 57 , In an advantageous embodiment of the invention, the housing or the bearing of the shaft is designed such that the drive shaft 6 can be taken out together with the seated piston 3 and together with the bearing cap 8 axially to one side of the housing 1, thereby easily to the Purpose of a seal change or maintenance of the piston and the seals can be made accessible. Advantageously, a second bearing plate need not be dismantled for this purpose first. The engine may have a total, in particular unsymmetrical shape, in particular with regard to the end-side bearings.

The drive shaft 6 is mounted differently at its two ends, namely at one end by a fixed bearing and the other end by a floating bearing, so that the shaft is axially fixed only on one side. As a result, a statically determined storage of the shaft is achieved with a total of compact design with a play-free recording of the axial forces. This compact design is particularly advantageous when using the rotary motor as a blade drive due to the very cramped space there.

In order to achieve a convenient installation with simple production and favorable force removal, the shaft is advantageously mounted at one end by means of a bearing plate or disk 8 in one of the aforementioned embodiments of the housing 1, preferably between the bearing plate and shaft releasably connected to one of the above embodiments according to the FIGS. 33 to 56 can be provided. At the opposite end, the drive shaft 6, however, has an integrally integrally formed shaft extension 69, which sits in a front-side housing cover and the floating bearing of the drive shaft 6 forms. The shaft extension 69 has a larger diameter than the helical crankshaft section of the drive shaft 6 and can correspond in particular to about the helix of the drive shaft 6 inscribing imaginary cylindrical envelope surface, which in turn can correspond to the original shaft blank contour from which the shaft is worked out.

In a further development of the invention, an overpressure protection 70 is provided between the two pressure chambers 4 and 5 of the engine, which has at least one connecting the two pressure chambers overpressure channel 71, which in the normal case, ie is closed by a pressure relief valve 72 at pressures below a predetermined threshold, which opens only when the said threshold value is exceeded. The overpressure protection can basically be integrated in the shaft in the form of a shaft recess, as this Figure 57 shows. Advantageously, the overpressure protection can alternatively or additionally also be integrated in the piston 3, which facilitates the introduction of the overpressure channel 72, in particular in the case of a helical course of the shaft 6. In order to set the pressure relief valve 72, which is advantageously adjustable in terms of its opening pressure, also from the outside, in the illustrated embodiment, an access point in the form of a screw plug 73 is provided in one of the frontal housing cover through which provided on the piston 3 pressure relief valve 72 through the housing can be actuated from the outside, cf. Fig. 57 ,

As Fig. 57 shows, provided on the piston outside and inside seals 12 and 13 each have a diagonal course, whereby the oil skimming effect is vorgebaut. Due to the constant change of plant in right-left-run a lubricating film cushion is built up by the repeatedly filling lubricating film bags, which seal themselves automatically when load changes on the cylinder wall.

Claims (26)

1. A rotary motor, preferably a pivot drive for construction machinery, hoisting gear, trucks and the like, comprising an elongate, approximately tubular housing (1), at least one piston (3) which is axially displaceably received in the housing (1) and which can be axially driven by the charging of a pressure medium in a pressure chamber (4, 5) as well as at least one shaft (6) which is received axially fixedly in the housing (1) and rotatably around an axis of rotation (7) with the piston (3) having a shaft passage cut-out (10) by which the piston (3) is axially displaceably seated on the shaft (6), characterized in that the shaft (6) forms a crankshaft whose axis of rotation (7) is offset with respect to the shaft passage cut-out (10) of the piston (3), with the shaft passage cut-out (10) being arranged centrally in the piston (3) with respect to the piston cross-section and with the piston (3) being rotatable with respect to the housing (1).
2. A rotary motor in accordance with the preceding claim, wherein the shaft (6) has a helical extent around its axis of rotation (7).
3. A rotary motor in accordance with claim 1, wherein the shaft (6) has a straight extent parallel to its axis of rotation (7).
4. A rotary motor in accordance with one of the preceding claims, wherein the housing (1) has a spirally rotated inner jacket surface.
5. A rotary motor in accordance with claim 2, wherein the housing (1) has a circular cylindrical inner jacket surface.
6. A rotary motor in accordance with one of the preceding claims, wherein the shaft (6) has a circular cross-section and the piston (3) has a circular outer peripheral contour.
7. A rotary motor in accordance with one of the preceding claims, wherein the shaft passage cut-out (10) in the piston (3) is adapted to the cross-section of the shaft (6), in particular corresponds to the shaft cross-section, and/or is adapted in its axial extent to the axial extent of the shaft contour.
8. A rotary motor in accordance with one of the preceding claims, wherein a surface pair effecting the axially displaceable guidance and/or the radial force support of the piston (3) at the piston (3) and at the housing (1) and/or at the piston (3) and at the shaft (6) simultaneously forms a sealing surface pair for the sealing of the pressure chamber (4, 5) for the pressure charging of the piston (3).
9. A rotary motor in accordance with one of the preceding claims, wherein a seal (12) is inserted between the shaft (6) and the shaft passage cut-out (10) in the piston (3) and/or a seal (13) is inserted between the outer jacket surface of the piston and the inner jacket surface of the housing, with the seal (12), (13) being formed such that pressure pockets (27, 28) which can be fed from the pressure chamber (4, 5) are formed between the piston (3) and the housing (1) and/or between the piston (3) and the shaft (6).
10. A rotary motor in accordance with the preceding claim, wherein mutually oppositely disposed peripheral sectors (41), (42) at the outer jacket surface of the piston and/or at the inner jacket surface of the shaft passage cut-out (10) are bounded in the peripheral direction of the piston (3) by axially extending sealing elements and/or sealing element sections (43, 44) and each form a pressure pocket (27, 28) of which the one is in pressure or flow communication with the one piston end-face side and the other is in pressure or flow communication with the oppositely disposed piston end-face side, with mutually oppositely disposed peripheral sectors (41, 42) at the outer jacket surface of the piston and/or at the inner jacket surface of the shaft passage cut-out (10) being bounded by a sealing element extending diagonally over the piston periphery and each forming a pressure pocket (27, 28) of which the one is in pressure or flow communication with the one piston end-face side and the other is in pressure or flow communication with the oppositely disposed piston end-face side.
11. A rotary motor in accordance with one of the preceding claims, wherein a roller bearing is provided between the housing (1) and the piston (3) and/or between the piston (3) and the shaft (6).
12. A rotary motor in accordance with one of the preceding claims, wherein the piston (3) is made in multiple parts such that each piston part per se can be pushed over a support stump at a crankshaft end.
13. A rotary motor in accordance with the preceding claim, wherein the piston (3) has a ring-shaped piston carrier (19) which at least partly forms the outer jacket surface of the piston and onto which at least one inner half-shell pair can be set at the end-face side which forms the shaft passage cut-out in the assembled state.
14. A rotary motor in accordance with one of the preceding claims, wherein the piston (3) has equally large effective piston surfaces at its two oppositely disposed end-face sides.
15. A rotary motor in accordance with one of the preceding claims, wherein the housing (1) and the support of the shaft (6) at the housing are made such that the shaft (6) can be axially removed from the housing (1) together with the piston seated thereon, in particular also together with a support disk (8) secured to the shaft.
16. A rotary motor in accordance with one of the preceding claims, wherein the shaft (6) is made differently and/or is differently supported at its two ends.
17. A rotary motor in accordance with the preceding claim, wherein the shaft (6) is supported at the housing (1) at one end by an axial fixed bearing and at its other end by an axial loose bearing.
18. A rotary motor in accordance with one of the preceding claims, wherein the shaft (6) is supported at at least one of its two ends in each case at a support plate and/or support disk (8) which respectively bounds a pressure chamber (4, 5) at the end-face side and/or can be charged by the pressure in the pressure chamber (4, 5), with the shaft (6) extending into a cut-out in the support plate and/or support disk (8) and transmitting torque via the cut-out over the fully area onto the support plate and/or support disk (8).
19. A rotary motor in accordance with the preceding claim, wherein the cut-out in the support plate and/or support disk (8) has a helical extent into which the likewise helical extent of the shaft (6) extends, with the helical shaft section seated in the cut-out being axially and/or radially fixed, preferably anchored, with respect to the cut-out by a shape matching element.
20. A rotary motor in accordance with claim 18, wherein the shaft (6) has a plurality of respectively circular cylindrical steps and mutually eccentrically offset steps in the region of the cut-out of the support plate (8) which are disposed inside its helical extent and which can be clamped against the support plate.
21. A rotary motor in accordance with one of the preceding claims, wherein the shaft (6) has a preferably integrally shaped support and/or output shaft pin (9) which extends inside an inner envelope surface of the shaft section and/or whose diameter (d_L) approximately corresponds to the shaft diameter (d_w) less double the shaft eccentricity (ε), that is d_L = d_w - 2ε.
22. A rotary motor in accordance with one of the claims 1 to 20, wherein the shaft (6) has a preferably integrally shaped support and/or output shaft pin (9) which is larger than a shaft diameter and substantially corresponds to an outer envelope surface of the shaft section and/or whose diameter (d_L) approximately corresponds to the sum of the shaft diameter (d_w) and four times the shaft eccentricity (ε), also d_L = d_w + 4ε.
23. A rotary motor in accordance with one of the preceding claims, wherein feedable pressure pockets are formed at the support sites of the shaft (6) between the housing (1) and the support section at the shaft side, wherein mutually oppositely disposed peripheral sectors at the inner jacket surface of the shaft support cut-out of the housing and the associated support pin at the shaft side are bounded by axially extending sealing elements and/or sealing element sections in the peripheral direction of the support pin and each form a pressure pocket of which the one or the other can be brought into communication with the adjoining pressure chamber in dependence on the rotary drive direction.
24. A rotary motor in accordance with one of the preceding claims, wherein the piston (3) is made from a dry sliding material, preferably a wear-resistant and low-friction synthetic material, preferably a ceramic material and/or plastic.
25. A rotary motor in accordance with one of the preceding claims, wherein the piston (3) is made in a resilient manner in at least one load direction of the rotary motor such that the piston (3) forms a damping element in the named at least one load direction.
26. A rotary motor in accordance with one of the preceding claims, wherein the at least one pressure chamber (4, 5) is in communication with an excess pressure line whose through flow is controlled by an excess pressure valve, with the excess pressure line and the excess pressure valve advantageously being arranged in the piston (3).

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