DE102015108829A1 - Double-acting lock cylinder and method of operating a double-acting lock cylinder - Google Patents

Abstract

The invention relates to a double-acting locking cylinder (20) with a cylinder (21) and a piston (22) which is movable in an axial direction (23) by means of a fluid pressure medium and which is connected to a spindle (35.2) via a non-self-locking thread (35). 37) is coupled. On the spindle (35.2), a first clamping double-cone body (45.1) is fixed, the self-locking clamped with a on the cylinder (21) attached to the second clamping double-cone body (45.2) in two locking positions (46.2) is. The spindle (35.2) is mounted on the first clamping double-cone body (45.1) on a first fluid-axial sliding bearing (53.1), which is acted upon by a first pressure medium inflow channel (54.1) with the fluid pressure medium and is mounted on a second fluid-axial sliding bearing (53.2), which is acted upon via a second pressure medium inflow channel (54.2) with the fluid pressure medium. A quantity divider (60) for dividing a main volume flow of the fluid pressure medium into a first part volume flow and into a second part volume flow includes a first pressure medium outflow channel (61.1) opening into the first pressure medium inflow channel (54.1) for the first part Volume flow and a second pressure medium outflow channel (61.2) opening into the second pressure medium inflow channel (54.2) for the second partial volume flow. The invention also relates to a method for operating the locking cylinder (20).

Description

The invention relates to a fluid operated, double-acting latching cylinder and a method of operating one or the fluid-operated, double-acting latching cylinder.

From the German patent application DE 10 2010 015 996 A1 and the parallel European patent applications EP 2 239 470 A2 . EP 2 570 679 A1 and EP 2 570 680 A1 the applicant are known pressure medium-operated, single-acting locking cylinder and methods for locking and unlocking of fluid-operated, single-acting locking cylinders. These locking cylinders each contain a cylinder and a piston and are only lockable either on train or only on pressure. For this purpose, in each case a rotatable about a rotation axis spindle is provided on the non-rotatably fixed a first locking cone surfaces having, self-locking, first clamping cone body is attached. The spindle comprises a spindle external thread, which engages with a piston internal thread of the piston to form a non-self-locking thread. In the region of a cylinder bottom of the cylinder, a second locking cone-surfaces exhibiting, non-rotatably, second clamping cone body is attached to this rotatably, which forms a clamping counter-cone body. In the locked state, the first clamping cone body and the second clamping cone body to form a deadlock are self-locking, so frictionally stuck by static friction, so that they are unlocked only under exercise of the clamping solving dissolving forces. Although these locking cylinders have proven themselves in practice, but their application and application is limited, namely either applications where the piston is subjected exclusively to pressure or applications where the piston is only subjected to train.

It is an object of the invention to provide a locking cylinder and method for operating a locking cylinder which is lockable to both pressure and tension, which is still comparatively simple, space-saving and robust in construction and relatively inexpensive Manufacturability nevertheless, even at high loads, provides a high level of operational reliability over a long time and offers both the retraction and the extension of the piston advantageous opportunities for operation regardless of the size of the respective load and the system pressure required thereby.

This object is achieved with respect to the locking cylinder by the features of claim 1, in particular by a fluid-operated, double-acting locking cylinder comprising a cylinder extending in the direction of a cylinder longitudinal axis and a piston having a first working chamber associated with a first piston side and one of them facing away, Comprises a second working chamber associated second piston side and with the aid of one of the first piston side via a first working chamber opening into the first working chamber and the second piston side via a second working chamber opening into the second working chamber fed fluid pressure medium in an axial direction parallel to the cylinder longitudinal axis in a second Direction and in a first direction opposite to the second direction relative to the cylinder, preferably linear, movable, but rotatably connected to the cylinder, wherein the piston rotatably with a he Most threaded body (mother or spindle) is connected, the first thread (female thread or spindle thread) with a second thread (spindle thread or nut thread) of a frictional, ie frictionally, by friction, and, preferably exclusively, by gravity, in particular by acting on the piston load , automatically or automatically, preferably without drive, in particular without the action or support of force accumulators, such as springs, lockable second threaded body (spindle or nut) to form a non-self-locking thread is engaged, and wherein the second threaded body about a parallel to the Cylinder longitudinal axis of the cylinder extending axis of rotation relative to the cylinder is rotatable and relative to the cylinder in the axial direction or parallel to the axis of rotation, preferably only slightly, axially displaceable, and one rotatable with the second threaded body, preferably rigid, composite ener or on the second threaded body rotationally fixed, preferably rigid, fixed, self-locking, first clamping double-cone body is provided, which has a first locking cone surfaces, self-locking, first clamping cone body and a second locking Having conical surfaces having self-locking, second clamping cone body, and wherein a rotatably with the cylinder, preferably rigid, connected or rotationally fixed to the cylinder, preferably rigidly mounted, self-locking, second clamping double-cone body provided comprising a third locking cone surfaces, self-locking, third clamping cone body and a fourth locking cone surfaces having self-locking, fourth clamping cone body, and wherein the first locking conical surfaces of the first clamping Double cone body by an axial movement of the second threaded body in the first direction to the third locking Cone surfaces of the second clamping double-cone body can be applied such that in the applied state of the second clamping double-cone body can absorb axial forces acting in the first direction on the second threaded body and the first locking conical surfaces and the third Locking conical surfaces to form a jamming together in a first locking position, both against rotation about the axis of rotation of the second threaded body ( 35.2 ) and against movement in the axial direction away from each other, self-locking, so frictionally by friction, are clamped, and wherein the second locking conical surfaces of the first clamping double-cone body by an axial movement of the second threaded body in the second direction the fourth locking conical surfaces of the second clamping double-cone body can be applied such that in the applied state the second clamping double-conical body can absorb axial forces acting in the second direction on the second threaded body and the second locking Conical surfaces and the fourth locking conical surfaces to form a jamming together in a second locking position, both against rotation about the axis of rotation of the second threaded body and against movement in the axial direction away from each other, self-locking, so frictionally locked by static friction, so that the locking cylinder both au f train in the first locking position and pressure in the second locking position can be locked and is locked in the applied state in the respective locking position such that the first clamping double-cone body only under exercise of the clamping solving release forces of the second clamping Double cone body is translatable into an unlocking position, in which the second threaded body is rotatable about its axis of rotation relative to the cylinder, and wherein the second threaded body is mounted on at least two fluid-axial bearings, of which a first fluid axial Sliding bearing - preferably with a first bearing surface of a first bearing body and the first bearing surface opposite the second bearing surface of a rotationally fixed, in particular rigidly connected to the cylinder or attached to the cylinder second bearing body, preferably in the form of a radially and transversely, in particular vertically , to the cylinder longitudinal axis se of the cylinder extending, preferably arranged between the first clamping double-cone body and the piston, in particular annular, approach, limited and - is intended to take in the first direction acting on the second threaded body axial forces, and of which a second Fluid-axial sliding bearing - preferably with a third bearing surface of a third bearing body and the third bearing surface opposite fourth bearing surface of a rotationally fixed, in particular rigid, connected to the cylinder or attached to the cylinder fourth bearing body, preferably a cylinder bottom of the cylinder limited and - Is intended to receive in the second direction acting on the second threaded body axial forces, and wherein the first fluid-axial slide bearing is acted upon via a first pressure medium inflow channel with or a fluid pressure medium, and wherein the second fluid-axial sliding bearing via a second pressure medium el-inflow channel can be acted upon with or a fluid pressure medium, and wherein a volume divider or flow divider identifiable, preferably a pressure medium main inflow comprehensive, especially single-acting or acting only in a flow direction, flow divider for dividing a, preferably the pressure medium Main inflow channel feedable, the main volume flow of the fluid pressure medium is provided in a first part-volume flow and in a second part-volume flow, which opens into the first pressure medium inflow channel for the first fluid-axial slide bearing first pressure medium outflow channel for the comprises first partial volume flow and a second pressure medium outflow channel opening into the second pressure medium inflow channel for the second fluid-axial plain bearing for the second partial volume flow. This makes it possible to convert the first double-cone body into a fluid-dynamic floating position, in which both a trouble-free, in particular locking or jamming, retraction of the piston and a trouble-free, in particular locking or jamming, extending the piston is possible and / or to keep the first double-cone body both during the retraction of the piston and during the extension of the piston always in a fluid-dynamic floating position or in a fluid-dynamic floating state, preferably each independent of the size of the Load and the system pressure required thereby. According to the invention, a particularly large negative efficiency can be realized at a standstill, whereby the safety of the self-locking can be increased compared to the known from the prior art constructions. The locking cylinder according to the invention may also be referred to as a locking cylinder-piston unit.

According to a preferred embodiment, it may be provided that the flow divider is a flow-controlled and / or pressure-controlled valve. This allows a further simplified, reliable and cost-effective design.

According to a particularly preferred embodiment, it can be provided that the flow divider comprises a housing with a, preferably a circular cylindrical inner circumference having, control piston receptacle, in which a, Also as a pressure compensator and / or slider markable, preferably a circular cylindrical outer circumference exhibiting, control piston with, preferably very little play, in particular in or with a clearance, guided relative to the control piston receptacle is slidably mounted in an axial direction, and wherein The control piston extends axially in the direction of a control piston longitudinal axis, has a control piston length and a first control piston end and extending away in an opposite direction in the axial direction second control piston end having from the first control piston end a the control piston length corresponding distance, and wherein in the housing a one, preferably designed as a fixed throttle, first throttle containing first inflow channel for a first partial volume flow of the fluid pressure medium and a one, preferably designed as a fixed throttle, second throttle second inflow channel for a z are arranged at least part of the volume flow of the fluid pressure medium, preferably which, at least in terms of throttle cross section and the throttle length is the same or identical designed as the first throttle, preferably wherein the control piston receptacle has an axial length which is smaller than the control piston length of the control piston, and wherein the control piston receptacle has a first receiving end and a second receiving end extending therefrom in an opposite direction in the axial direction, and wherein the control piston receptacle at its first receiving end, viewed in the axial direction, in a first control piston end receptacle for receiving the first control piston end of the control piston merges, in which the first inflow channel opens, and wherein the control piston receptacle at its second receiving end, viewed in the axial direction, merges into a second control piston end receptacle for receiving the second control piston end of the control piston, in the the second inflow channel opens, and wherein the first control piston end intake forms a first control throttle or a component of a first control throttle and the second control piston end intake forms a second control throttle or a component of a second control throttle, and wherein the first control piston end receptacle is fluidly connected to the first pressure medium outflow channel and the second control piston end receptacle is fluid-connected to the second pressure medium outflow channel. This makes it possible to achieve a particularly simple and reliable operation over a long period of time for converting the first double-cone body into a fluid-dynamic floating position, in which both a trouble-free, in particular locking or jam-free retraction of the piston Also, a trouble-free, in particular locking or jam-free, extension of the piston is possible and / or the first double-cone body both during retraction of the piston and during the extension of the piston always in a fluid-dynamic floating position or in a hydrodynamic floating state to hold, preferably each independent of the size of the load and the system pressure required thereby. Such a flow divider also has the advantage of ensuring a comparatively high degree of precision with regard to the volume flows to be distributed, even at elevated pressure differences. In addition, such a flow divider can be built very small, so that it takes up relatively little space. As a result, there is the advantageous possibility of accommodating such a flow divider in a preferably flanged control block, preferably attached to or on the cylinder, in which further or other control and / or regulating elements for controlling and / or regulating the locking cylinder can be accommodated ,

According to a particularly advantageous development of such a flow divider can be provided that the control piston in the axial direction pressure and / or flow controlled by the fluid pressure medium into a first shut-off position is displaceable, in which the control piston a first flow path from the first inflow channel to the first Pressure medium discharge channel with respect to a flow of the fluid pressure medium substantially or completely shuts off, while a second flow path from the second inflow channel to the second pressure medium discharge channel with respect to a flow of the fluid pressure medium is open or remains, and that the control piston in the axial direction by flow controlled the fluid pressure medium is displaceable into a second shut-off position, in which the control piston has a second flow path from the second inflow channel to the second pressure medium outflow channel with respect to a flow-through of the fluid pressure medium i substantially or completely shut off, while the first flow path from the first inflow channel to the first pressure medium outflow channel is or remains open with respect to a flow through the fluid pressure medium. By these measures, there is a particularly advantageous possibility, the locking cylinder when it is locked by jamming, unlock by applying the flow divider with the fluid pressure medium, which in the course of continued loading of the flow divider with the fluid pressure medium, automatically said fluid-dynamic Floating position or the said fluid-dynamic floating state of the first double-cone body can be achieved or is.

According to an advantageous development can be provided that the control piston receptacle in an imaginary, perpendicular to the Viewed control piston longitudinal axis trained cross-sectional plane, having an inner cross section, and that the first control piston end receptacle viewed in an imaginary, formed perpendicular to the control piston longitudinal axis first cross-sectional plane having a first inner cross-section which is greater than the inner cross-section of the control piston receptacle, and wherein the second control piston end receptacle viewed in an imaginary, formed perpendicular to the control piston longitudinal axis of the second cross-sectional plane having a second inner cross-section which is greater than the inner cross-section of the control piston receptacle. As a result, a further improvement in terms of the above advantages can be achieved.

It can be provided according to a particularly advantageous embodiment, that the first control piston end recording on one of the control piston receiving opposite first side, viewed in the axial direction, merges into a third control piston end recording, in which the first pressure fluid discharge channel directly or viewed indirectly and considered in an imaginary, perpendicular to the control piston longitudinal axis and parallel to the first cross-sectional plane formed third cross-sectional plane having a third inner cross-section corresponding to the inner cross-section of the control piston receptacle, so that the first control piston end of the control piston in the third control piston end Receptacle transferred and then there with, preferably very little play, in particular in or with a clearance fit, relative to the third control piston end receptacle in the axial direction slidably mounted and that the second control piston end receptacle on one of the control piston Aufn Aim opposite to the second side, viewed in the axial direction, in a fourth control piston end receptacle, in which the second pressure medium discharge channel opens directly or indirectly, and in an imaginary, formed perpendicular to the control piston longitudinal axis and parallel to the second cross-sectional plane Viewed fourth cross-sectional plane, having a fourth inner cross-section corresponding to the inner cross-section of the control piston receptacle, so that the second control piston end of the control piston in the fourth control piston end recording transferred and then there with, preferably very little play, in particular in or with a clearance fit is slidably mounted relative to the fourth control piston end receptacle in the axial direction. As a result, an even further improvement in terms of the above advantages can be achieved.

According to a particularly preferred embodiment, it can be provided that the control piston receptacle extending along a longitudinal axis and the first and second control piston end receptacle, preferably also the third and fourth control piston end receptacle, symmetrical to an imaginary, perpendicular to the longitudinal axis of the Regelkolben- Receiving trained symmetry plane are designed or that the housing of the flow divider or the flow divider is designed symmetrically to an imaginary, formed perpendicular to the longitudinal axis of the control piston receiving symmetry plane. As a result, an even further improvement in terms of the above advantages can be achieved.

According to a preferred embodiment, it may be provided that the flow divider in a arranged in the cylinder or attached to the cylinder, preferably flanged control block together with, preferably substantially all, control elements for controlling the locking cylinder and / or together with, preferably substantially all , Control elements for controlling the locking cylinder is arranged. This allows a particularly compact and safe construction can be achieved.

According to an alternative embodiment variant, the flow divider may be a gearbox divider comprising at least one first gear motor or at least one first gear pump for conveying the first part volume flow and at least one second gear motor or at least one second gear pump for conveying the second part Volume flow, which are coupled together via a shaft. As a result, if necessary, a greater efficiency can be achieved than with the use of a pressure compensator in conjunction with the associated throttles in the inflow channels.

According to a preferred embodiment it can be provided that the first clamping cone body and the second clamping cone body of the first clamping double-cone body are integrally connected and / or made of a part and / or that the third terminal Cone body and the fourth clamping cone body of the second clamping double-cone body are integrally connected and / or made of a part. These measures not only allow a simple and cost-effective production but also a particularly reliable construction.

According to a particularly preferred embodiment it can be provided that the first clamping Double-cone body with its first locking cone surfaces and also the second clamping double-cone body with its third locking cone surfaces, viewed in the first direction, taper radially to the axis of rotation of the second threaded body and the first clamping double-cone body with its second locking cone surfaces and also the second clamping double-cone body with its fourth locking cone surfaces, viewed in the second direction, radial to the axis of rotation taper of the second threaded body.

Alternatively, however, it can also be provided that the first clamping double-cone body with its first locking cone surfaces and also the second clamping double-cone body with its third locking cone surfaces, in the first Direction, extend radially away from the axis of rotation of the second threaded body and the first clamping double-cone body with its second locking cone surfaces and also the second clamping double-cone body with its fourth locking cone Area, viewed in the second direction, expand radially away from the axis of rotation of the second threaded body.

It is understood that according to the following further alternatives can also be provided that the first clamping double-cone body with its first and second locking cone surfaces and that the second clamping double-cone body with his third and fourth locking cone surfaces, viewed in the first direction or viewed in the second direction, can taper radially towards the axis of rotation of the second threaded body or that the first clamping double-cone body with its first and second locking body Cone surfaces and that the second clamping double-cone body with its third and fourth locking cone surfaces, as viewed in the first direction or viewed in the second direction, can expand radially away from the axis of rotation of the second threaded body.

Preferably, the third locking cone surfaces of the second clamping double-cone locking body and the first locking cone surfaces of the first clamping double-cone locking body face and are the fourth locking cone surfaces of the second clamping double Cone locking body and the third locking cone surfaces of the first clamping double-cone locking body against.

According to a particular preferred embodiment, it can be provided that the first clamping double-cone body is at least partially or completely received in a limited by the second clamping double-cone body recess, in particular in a chamber of the cylinder, the Preferably on the one hand by a cylinder bottom of the cylinder and on the other hand, by a, preferably integrally connected to the cylinder or one or the cylinder base, radially and transversely, preferably perpendicular, extending to the cylinder longitudinal axis of the cylinder, between the first clamping double Cone body and the piston arranged, in particular annular, approach is limited, and wherein the first pressure medium inflow channel opens on a first locking cone surfaces associated with the first side of the first clamping double-cone body in the recess, and wherein the second pressure medium inflow channel on a second locking cone Fläc hen associated second side of the first clamping double-cone body opens into the recess, and wherein the recess is sealed by a seal against the second working chamber. Through these measures, a further improvement in terms of the above advantages can be achieved.

It can be provided according to a preferred embodiment, that in a region between the third clamping cone body and the fourth clamping cone body of the second clamping double-cone body either one, preferably annular, first pressure medium discharge channel is provided for discharging the fluid pressure fluid flowing through the first fluid-axial sliding bearing, which, in an unlocked position of the first clamping double-cone body, fluidly connected to the first fluid-axial sliding bearing, and preferably to the first and third Locking-cone surfaces adjacent, and which opens into the recess and a, preferably annular, second pressure-medium discharge channel for discharging the second fluid-axial slide bearing flowing fluid pressure means is provided, which, in an unlocked position of the first clamping Double-cone body, is fluidly connected to the second fluid-axial sliding bearing, preferably and to the second and fourth Locking-cone surfaces adjoins, and which opens into the recess, or a, preferably annular, common pressure-medium-discharge channel for discharging the first and the second fluid-axial sliding bearing flowing fluid pressure means is provided, which, in an unlocked position of the first clamping double-cone body, is fluidly connected to the first and the second fluid-axial sliding bearing, and preferably adjacent to the first, second, third and fourth locking conical surfaces, and opens into the recess. Through these measures, the reliability can be further increased. In particular, this can be realized in a particularly simple manner, a sequence control such that, starting from a locking position in which the locking cylinder is locked, automatically first the locking cylinder is unlocked and only then the piston is retracted or extended.

It can be provided according to a preferred development that the first pressure medium inflow channel, then when the first clamping Double-cone body and the second clamping double-cone body locked together in the first locking position and are clamped self-locking to form the deadlock against the first or common pressure medium-discharge channel by means of abutting first and third locking cone Is shut off and which, when the first clamping double-cone body and the second clamping double-cone body are lifted from each other in one or the unlocked position, with the first or common pressure medium-discharge channel via a and the second pressure medium inflow channel, when the first clamping double-cone body and the second clamping double-cone body are formed in a fluid-connected manner between the first and third interlocking conical surfaces locked together in the second locking position and clamped self-locking to form the deadlock, geg is shut off over the first or common pressure medium discharge channel by means of the adjacent second and fourth locking cone surfaces and which, when the first clamping double-cone body and the second clamping double-cone body from each other in one or the unlocked position are lifted, is fluidly connected to the second or common pressure medium discharge channel via a then formed between the second and fourth locking cone surfaces, preferably annular, second channel. Through these measures, a further improvement in terms of the above advantages can be achieved.

With regard to the method, the object of the invention is achieved by a method for operating, controlling and / or regulating a pressure-actuated, double-acting, in particular inventive, locking cylinder which comprises a cylinder extending in the direction of a cylinder longitudinal axis and a piston which has a first piston side associated with a first working chamber and a second piston side facing away therefrom and assigned to a second working chamber and parallel with one of the first piston side via a first working channel opening into the first working chamber and the second piston side via a second working channel opening into the second working chamber to the cylinder longitudinal axis in a second direction and in a first direction opposite to the second direction relative to the cylinder, preferably linear, movable, but non-rotatably connected to the cylinder, wob ei the piston is non-rotatably connected to a first threaded body (nut or spindle) whose first thread (nut thread or spindle thread) with a second thread (spindle thread or nut thread) of a frictional, ie frictionally, by friction, and, preferably exclusively, by gravity, in particular by a load acting on the piston, automatically, or automatically, preferably without drive, in particular without action or support of force accumulators, such as springs, lockable second threaded body (spindle or nut) to form a non-self-locking thread is engaged, and wherein the second Threaded body is rotatable about a parallel to the cylinder longitudinal axis of the cylinder extending axis of rotation relative to the cylinder and relative to the cylinder in the axial direction or parallel to the axis of rotation, preferably only slightly, axially displaceable, and wherein a with the second threaded body d Rehfest, preferably rigid, connected or rotationally fixed to the second threaded body, preferably rigid, fixed, self-locking, first clamping double-cone body is provided, the first locking cone surfaces having, self-locking, first clamping cone body and having a second locking cone surfaces, self-locking, second clamping cone body, and wherein a non-rotatable, preferably rigid, connected or non-rotatable, preferably rigid, fixed, self-locking, second clamping double Cone body is provided, which has a third locking cone surfaces, self-locking, third clamping cone body and a fourth locking cone surfaces having self-locking, fourth clamping cone body, preferably wherein the first clamping Double cone body with its first locking cone surfaces and also the second clamping double cone body with its, Preferably, the first locking cone surfaces opposite, third locking cone surfaces, viewed in the first direction, radially taper to the rotational axis of the second threaded body and the first clamping double-cone body with its second locking cone Surfaces and also the second clamping double-cone body with its, preferably the second locking cone surfaces opposite, fourth locking cone surfaces, viewed in the second direction, radially taper to the rotational axis of the second threaded body , And wherein the first locking conical surfaces of the first clamping double-cone body by an axial movement of the second threaded body in the first direction to the third locking conical surfaces of the second clamping double-cone body can be applied such that in the applied Condition of the second clamping double-cone body can absorb axial forces acting in the first direction on the second G ewindekörper act and the first locking conical surfaces and the third locking conical surfaces to form a jamming together in a first locking position, both against a Rotation about the axis of rotation of the second threaded body and against movement in the axial direction away from each other, self-locking, so frictionally by friction, are clamped, and wherein the second locking conical surfaces of the first clamping double-cone body by an axial movement of the second Threaded body in the second direction of the fourth locking conical surfaces of the second clamping double-cone body can be applied such that in the applied state of the second clamping double-cone body can absorb axial forces in the second direction on the second threaded body acting and the second locking conical surfaces and the fourth locking conical surfaces to form a jamming with each other in a second locking position, both against rotation about the axis of rotation of the second threaded body and against movement in the axial direction away from each other, self-locking, so frictional by static friction , pinch t, so that the locking cylinder is lockable both to train in the first locking position and pressure in the second locking position and is locked in the applied state in the respective locking position such that the first clamping double-cone body only under exercise of the clamping releasing release forces of the second clamping double-cone body can be converted into an unlocking position, in which the second threaded body is rotatable about its axis of rotation relative to the cylinder, and wherein the second threaded body is mounted on at least two fluid-axial bearings of which a first fluid-axial plain bearing, preferably with a first bearing surface of a first bearing body and the first bearing surface opposite the second bearing surface of a rotationally fixed, in particular rigidly connected to the cylinder or attached to the cylinder second bearing body, preferably in shape one radially and transversely, in particular perpendicularly, extending to the cylinder longitudinal axis of the cylinder, preferably arranged between the first clamping double-cone body and the piston, in particular annular, approach, limited and, is intended to absorb acting in the first direction on the second threaded body axial forces, and of which a second fluid-axial plain bearing, preferably with a third bearing surface of a third bearing body and the third bearing surface opposite fourth bearing surface of a rotationally fixed, in particular rigidly connected to the cylinder or attached to the cylinder fourth bearing body, preferably a cylinder base the cylinder, limited and, is intended to receive acting in the second direction on the second threaded body axial forces, and wherein the first fluid-axial slide bearing is acted upon via a first pressure medium inflow channel with or a fluid pressure medium, and wherein the second fluid-axial G Leitlager via a second pressure medium inflow channel with the or a fluid pressure medium is acted upon, and one or the volume as a flow divider or flow divider signable / r, preferably a pressure medium main inflow more comprehensive, in particular single-acting or acting only in a flow direction, flow divider for dividing a, preferably the pressure medium main inflow channel supplied, the main volume flow of the fluid pressure medium is provided in a first part-volume flow and in a second partial flow, the one in the first pressure medium inflow channel for the first fluid-axial Sliding bearing opening first pressure medium outflow channel for the first part volume flow and a second pressure medium inflow channel for the second fluid-axial slide bearing second pressure medium outflow channel for the second part volume flow includes, and wherein by means of the flow divider, at least during a moving, in particular Other extension, the piston in the first direction and also during a moving, in particular retraction of the piston in the second direction and each effected thereby rotating the second threaded body about its axis of rotation together with the first clamping double-cone body, a main Volumetric flow of the fluid pressure medium is divided into a first part-volume flow and a second part-volume flow such that a ratio of the flowing through the first pressure medium inflow through the first fluid-axial sliding bearing first part-volume flow of the fluid pressure medium and the by the second pressure medium inflow channel through the second fluid-axial sliding bearing inflowing second volume partial flow of the fluid pressure medium, preferably always, remains substantially constant or held, whereby the first clamping double-cone body both by means of the with fluid pressure medium acted upon first fluid-axial slide bearing and ver is fluid-stored in a fluid-dynamic floating position or in a fluid-dynamic floating state by means of the acted upon by the fluid pressure fluid second fluid-axial sliding bearing, preferably independent of a size of a load acting on the piston and a system pressure required thereby and / or remains or is held.

According to a very particularly preferred embodiment, it can be provided that said ratio, at least during a movement of the piston in both the first direction and in the second direction, regardless of the pressures or counterpressures of the fluid pressure medium acting in the first pressure medium inflow channel and in the second pressure medium inflow channel, preferably always in the Essentially remains constant or is held. In other words, it can be provided that the said ratio, at least during a movement of the piston in both the first direction and in the second direction, regardless of which pressure or back pressure of the fluid pressure medium in the first pressure medium inflow channel acts or is set and regardless of which pressure of the fluid pressure medium in the second pressure medium inflow channel acts or adjusts, preferably always, remains substantially constant or is held. As a result, the reliability is significantly improved.

According to a preferred variant of the method, it can be provided that the ratio, at least during a movement of the piston in both the first direction and in the second direction, is essentially 1: 1 or is maintained substantially at 1: 1. In this case, the first partial volume flow of the fluid pressure medium and the second partial volume flow of the fluid pressure medium are or remain substantially the same. This may be particularly advantageous when the first clamping double-cone body and / or the second clamping double-cone body are formed substantially symmetrically to an imaginary, arranged perpendicular to the axis of rotation or to the cylinder axis of symmetry ,

According to a particularly preferred embodiment, it can be provided that the flow divider comprises a housing with a, preferably a circular cylindrical inner circumference having, control piston receptacle in which a, also referred to as a pressure balance and / or slide, preferably having a circular cylindrical outer circumference, having control piston, Preferably, very little play, in particular in or with a clearance fit, guided relative to the control piston receiving slidably mounted in an axial direction, and wherein the control piston extends axially in the direction of a control piston longitudinal axis, has a control piston length and a a first control piston end and an extending away in an opposite direction in the axial direction away second control piston end having from the first control piston end corresponding to the control piston length distance, and wherein in the housing a one, preferably gest as a fixed throttle altete, first throttle-containing first inflow channel for a first partial volume flow of the fluid pressure medium and a one, preferably designed as a fixed throttle, second throttle second inflow channel for a second partial flow of the fluid pressure medium are arranged, preferably the, at least in terms Throttle cross-section and the throttle length is the same or identical designed as the first throttle, preferably wherein the control piston receptacle has an axial length which is smaller than an axial length of the control piston, and wherein the control piston receptacle with a first end in a first control piston end receptacle for Receiving a first control piston end of the control piston passes, in which the first inflow channel opens, and wherein the control piston receptacle merges with a second end in a second control piston end receptacle for receiving a second control piston end of the control piston, in which the second inflow channel opens, and w obei the first control piston end recording forms a first control throttle or a component of a first control throttle and the second control piston end recording forms a second control throttle or a component of a second control throttle, and wherein the first control piston end recording with the the first pressure medium outflow channel is fluidly connected and the second control piston end receptacle is fluidly connected to the second pressure medium discharge channel, so that the control piston, when a first pressure medium pressure, which forms in the first pressure medium outflow, during the first pressure means -Abströmkanal with the first part-volume flow of the fluid pressure medium is flowed through and a second pressure medium pressure, which forms in the second pressure medium outflow, while the second pressure fluid discharge passage is flowed through by the second partial volume flow of the fluid pressure medium, the same size are, located in a basic or middle position and If the control piston then deviates from a second pressure medium pressure, which flows when a first pressure medium pressure, which is formed in the first pressure medium outflow channel, while the first pressure medium discharge channel is flowed through by a first partial volume flow of the fluid pressure medium formed in the second pressure medium discharge channel, while the second pressure medium discharge channel is flowed through by a second partial volume flow of the fluid pressure medium, so that the first pressure medium pressure and the second pressure medium pressure differ by a pressure difference not equal to zero, simultaneously automatically moves with the formation of the pressure difference in the direction of the lower pressure medium pressure in the axial direction in a deviating from the basic or middle position and dependent on the pressure difference forming control position. As a result, it can be achieved to a particular degree that the said ratio of the first partial volume flow of the fluid pressure medium and of the second partial volume flow of the fluid pressure medium remains substantially constant.

It can be provided according to a preferred variant, that when the first clamping double-cone body is clamped self-locking with the second clamping double-cone body in the first locking position and when the fluid pressure medium is supplied to the first inflow, the control piston is moved from its basic or center position in a second shut-off position or held in a second shut-off position in which the second pressure medium Outflow channel and therefore also the second pressure medium inflow channel against the second inflow channel is blocked against inflow of the pressure medium, while a first flow path between a first inflow channel and the first pressure medium outflow channel is open, so that the fluid pressure medium through the first inflow channel in the first Pressure medium outflow channel and from there through the first pressure medium inflow channel can either flow to transfer the first clamping double-cone body by a continued supply of the fluid pressure medium in an unlocked position or flows, so that the first clamping double cone Body is transferred to an unlocked position, and that when the first clamping double-cone body is clamped self-locking with the second clamping double-cone body in the second locking position and when the fluid pressure medium is supplied to the second inflow, the control piston from its basic or middle nstellung is moved into a first shut-off position or held in a first shut-off position in which the first pressure medium discharge channel and therefore also the first pressure medium inflow channel is blocked against inflow of the pressure medium, while a second flow path between a second inflow channel and the second pressure medium -Abströmkanal is open, so that the fluid pressure medium through the second inflow channel in the second pressure medium outflow channel and from there through the second pressure medium inflow channel can either flow to the first clamping double-cone body by a continuous supply of the fluid pressure medium to transfer into an unlocked position or flows, so that the first clamping double-cone body is transferred to an unlocked position. In this way, the locking cylinder, when it is by means of the clamping double-cone body self-locking, so frictionally jammed by static friction, and thus locked, are unlocked particularly easy and effective, what in the course of a continued pressurization of the flow divider is achieved with the fluid pressure medium, automatically said fluid-dynamic floating position or the said fluid-dynamic floating state of the first double-cone body.

As an alternative to the use of the pressure compensator or the regulating piston-containing quantity portion, a flow divider may be provided, which is one or the gearbox divider, the at least one of the first part-volume flow-promoting first gear pump and the second part-volume flow-promoting second Gear pump which are coupled together via a shaft or the one such that, at least during movement of the piston in the first direction and also in the second direction and thereby respectively caused rotation of the second threaded body about its axis of rotation together with the first clamping Double-cone body, the said ratio of the first part-volume flow of the fluid pressure medium and the second part-volume flow of the fluid pressure medium remains substantially constant.

According to a particularly preferred variant of the method it can be provided that either, starting from the first locking position, in which the first clamping double-cone body and the second clamping double-cone body are clamped self-locking, at least first or only the first fluid Axial slide bearing is acted upon by the flow divider and the fluid-connected first pressure medium inflow channel with the fluid pressure medium, or, starting from the second locking position, in which the first clamping double-cone body and the second clamping double cone Body are clamped self-locking, first at least or only the second fluid-axial slide bearing on the flow divider and the fluid-connected second pressure medium inflow channel is acted upon by the fluid pressure medium, either to a lifting of the first clamping double-cone body of the second To effect clamping or double-cone body in a lift-off and unlocking position Lifting the first clamping double-cone body is effected by the second clamping double-cone body in a lift-off and unlocking, in which the first clamping double-cone body and the second clamping double-cone body are either at least partially lifted from each other, so that their locking cone surfaces at least partially no longer touch, or are completely lifted off each other, so that their locking cone surfaces no longer touch, and that only then the pressure means of the first or second working chamber, either to allow, support and / or cause a movement of the piston in the axial direction, or whereby the piston is moved in the axial direction. In this way, an advantageous sequence control can be realized, in which over a long time particularly safe and low-wear operation of the locking cylinder is possible.

It is understood that the above features and measures in the context of executability individually or in any combination can be combined.

Further features, measures, advantages and aspects of the invention will become apparent from the following description part, in which two preferred embodiments of the invention are described with reference to FIGS.

Show it:

1 a locking cylinder according to the invention in a longitudinal cross-section with an integrated control unit in a schematic representation, illustrating a driving position "extending", both under oppressive load and pulling load;

2 the locking cylinder in a representation according to 1 to illustrate a driving position "retracting", both with pushing load and with pulling load;

3 the locking cylinder according to 1 at standstill and locked state with pulling load;

4 the locking cylinder according to 1 at standstill and locked state under pressing load;

5 a cross section of an integrated in the control unit of the locking cylinder flow divider according to a first embodiment, with an integrated, forming a pressure compensator control piston;

6 a schematic representation of a second embodiment of a flow divider, which is a gearbox divider with two coupled via a shaft gear pumps.

The locking cylinder 20 includes a cylinder 21 and a piston 22 , The locking cylinder 20 can also be referred to as locking cylinder-piston unit. The piston 22 is in the cylinder 21 in an axial direction 23 displaceable, but non-rotatable to the cylinder 21 stored. The piston 22 is opposite a cylinder jacket inner wall 24 of the cylinder 21 through a ring seal 25 sealed. The piston 22 is on his in the direction of the cylinder axis 26 of the cylinder 21 facing away from each other pages 27.1 . 27.2 by a fluid, in particular hydraulic, pressure medium, preferably oil, acted upon, a pressure medium-assisted movement of the piston 22 in a first direction 28.1 and in a second direction 28.2 , opposite to the first direction 28.1 to enable. At the locking cylinder 20 It is a pressure-medium-operated, double-acting locking cylinder, which can be locked both on train and on pressure. The fluid pressure medium can via a first working channel 29.1 on the from a cylinder bottom 30 of the cylinder 21 pointing away first page 27.1 of the piston 22 in a first working chamber 31.1 be fed to a movement of the piston 22 along the cylinder 21 or parallel to the cylinder longitudinal axis 26 in the second direction 28.2 to reach. In addition, the fluid pressure medium via a second working channel 29.2 on the second page 27.2 of the piston 22 that from the first page 27.1 away and to the cylinder bottom 30 points, in a second working chamber 31.2 be fed to a movement of the piston 22 along the cylinder 21 or parallel to the cylinder longitudinal axis 26 in the first direction 28.1 to reach.

The first working chamber 31.1 is opposite the second working chamber 31.2 over the ring seal 25 of the piston 22 sealed. The ring seal 25 rests in an outward to the cylinder jacket inner wall 24 open ring groove 33 of the piston 22 from. The piston 22 is designed with a tubular hollow body, which also with piston rod 34 is designated. The piston 22 forms an annular projection which is non-rotatable with the piston rod 34 connected is. The piston rod 34 extends from the first page 27.1 of the piston 22 in the axial direction 23 coaxial or parallel to the cylinder longitudinal axis 26 of the cylinder 21 , The piston 22 is one-piece with a designated also with first threaded body nut 35.1 educated. The mother 35.1 has a designated as the first thread and designed as an internal thread nut thread 36.1 on. The nut thread 36.1 forms in the embodiment shown a piston thread of the piston 22 , The nut or piston thread 36.1 is engaged with a designated also with a second thread and designed as an external thread spindle thread 36.2 one referred to as a second threaded body spindle 35.2 on which the piston 22 is guided. The nut or piston thread 36.1 and the spindle thread 36.2 form a non-self-locking thread 37 out. Preferably, this is not self-locking thread 37 designed to be right-handed. But it can also be designed left-handed. Preferably, the nut or piston thread 36.1 and the spindle thread 36.2 each designed as one, in particular multi-speed, coarse thread, preferably trapezoidal coarse thread. Preferably, an eight-speed coarse thread can be used.

The cylinder 21 is on one side 38.1 that of the piston 22 pointing away end of the spindle 35.2 is assigned by a the piston rod 34 enclosing lid 39 completed. This can, as shown in the figures, in one piece with the cylinder 21 be connected or manufactured. However, it can also be connected in several parts with the cylinder. The ring-shaped lid 39 has one to the piston rod 34 open annular groove 40 on. In this ring groove 40 supports a ring seal 41 from which the first working chamber 31.1 seals to the outside. On his other side 38.2 is the cylinder 21 through a cylinder bottom 30 forming lid or head completed. This can preferably be in several parts with the cylinder 21 be connected.

The spindle 35.2 is one parallel to the cylinder longitudinal axis 26 of the cylinder 21 arranged axis of rotation 43 relative to the cylinder 21 rotatable. The spindle 35.2 is relative to the cylinder 21 in the axial direction 23 or parallel to the cylinder longitudinal axis 26 of the cylinder 21 axially displaceable, and only slightly. In the embodiment shown, the double arrow is used 44 characterized axial displaceability of the spindle 35.2 or is the axial spindle clearance only about 1.5 to 2.5 mm. The spindle 35.2 is solely due to gravity, in particular by a on the piston rod 34 or on the piston 22 acting load F, automatically or automatically, without drive and without the action or support of force accumulators, such as tension or compression springs, against rotation about its axis of rotation 43 relative to the cylinder 21 as well as against a movement or displacement in the axial direction 23 , both in the first direction 28.1 as well as in the second direction 28.2 , self-locking, so frictionally by static friction, clamped and lockable in this way. So it's not just a frictional self-locking locking the spindle 35.2 with respect to a rotation about its axis of rotation 43 relative to the cylinder 21 realizable, but also a locking of the spindle 35.2 against movement or displacement in the axial direction 23 , both in the first direction 28.1 as well as in the second direction 28.2 , The lock according to the invention is thus a type of double-self-locking lock.

For this purpose are a first clamping double cone body 45.1 and second clamping double cone body 45.2 provided, with respect to the first clamping double-cone body 45.1 acts as a counter-clamp double-cone body. The first clamp double cone body 45.1 is at the spindle 35.2 rotatably attached and the second clamping double cone body 45.2 is on the cylinder 21 secured against rotation. The first clamp double cone body 45.1 and the second clamp double cone body 45.2 are designed so coordinated that the first clamping double-cone body 45.1 with the second clamping double cone body 45.2 to form a deadlock self-locking, so frictionally by static friction in a first locking position 46.1 (please refer 3 ) and in a second locking position 46.2 (please refer 4 ) is clamped, so that in the self-locking jammed condition, both in the first locking position 46.1 as well as in the second locking position 46.2 , the first clamping double-cone body 45.1 and with it the spindle 35.2 relative to the second clamp double cone body 45.2 and thus to the cylinder 21 , in particular against rotation of the first clamping double-cone body 45.1 around the axis of rotation 43 relative to the second clamp double cone body 45.2 and also against movement or displacement in the axial direction 23 locked so that the first clamping double-cone body 45.1 and with it the spindle 35.2 only in the exercise of the clamping solving dissolving forces of the second clamping double-cone body 45.2 and thus of the cylinder 21 in an unlocked position 92 (see. 1 and 2 ) is convertible, in which the spindle 35.2 together with the first clamp double cone body attached thereto 45.1 around the axis of rotation 43 relative to the cylinder 21 , preferably free, is rotatable.

The first clamp double cone body 45.1 includes a first locking cone surfaces 48.1 having, frustoconically shaped, self-locking, first clamping cone body 47.1 and a second locking cone surfaces 48.2 having, frusto-conically shaped, self-locking, second clamping cone body 47.2 , The first clamp double cone body 45.1 is disc-shaped or designed as a double-cone-stump disc. The first clamp double cone body 45.1 is rotationally symmetrical to the axis of rotation 43 the spindle 35.2 or to the cylinder longitudinal axis 26 of the cylinder 21 designed.

The second clamping double cone body 45.2 includes a third locking cone surfaces 48.3 having self-locking, third clamping cone body 47.3 and a fourth locking cone surfaces 48.4 having, self-locking, fourth clamping cone body 47.4 , The second clamping double cone body 45.2 is rotationally symmetrical to the cylinder longitudinal axis 26 of the cylinder 21 or to the axis of rotation 43 the spindle 35.2 designed. Preferably, one is the first clamp double cone body 45.1 receiving recess or chamber 49 rotationally symmetrical to the cylinder longitudinal axis 26 of the cylinder 21 or to the axis of rotation 43 the spindle 35.2 designed. A recess or chamber 49 in which the first clamping double-cone body 45.1 in the axial direction 23 is slidably received or arranged, on the one hand by a cylinder bottom part 50 of the cylinder bottom 30 of the cylinder 21 and on the other hand of an annular approach 51 limited. The chamber or recess 49 points, in a cylinder longitudinal axis 26 considered cross-section, a T-shaped cross section.

The first clamp double cone body 45.1 tapers with its first locking cone surfaces 48.1 and also the second clamp double cone body 45.2 tapers with its first locking cone surfaces 48.1 opposite third locking cone surfaces 48.3 , in the first direction 28.1 considered, radially to the axis of rotation 43 the spindle 35.2 out. In addition, the first clamping double cone body tapers 45.1 with its second locking cone surfaces 48.2 and also the second clamp double cone body 45.2 tapers with its second locking cone surfaces 48.2 opposite fourth locking cone surfaces 48.4 in the second direction 28.2 considered, radially to the axis of rotation 43 the spindle 35.2 out.

The first locking cone surfaces 48.1 with the spindle 35.2 non-rotatably connected first clamping double-cone body 45.1 and the third locking cone surfaces 48.2 . 48.4 the cylinder bottom side, second clamping double cone body 45.2 close with the rotation axis 43 the spindle 35.2 or with the cylinder longitudinal axis 26 of the cylinder 21 a first angle of inclination 52.1 one ( 3 ). The second locking cone surfaces 48.2 of the first clamp double cone body 45.1 and the fourth locking cone surfaces 48.2 . 48.4 of the second clamping double cone body 45.2 close with the rotation axis 43 the spindle 35.2 or with the cylinder longitudinal axis 26 of the cylinder 21 a second angle of inclination 52.2 one ( 4 ). The first inclination angle 52.1 and the second inclination angle 52.2 are the same size; it is preferably about 6.5 degrees. At these angles of inclination, or more generally, at angles of inclination of about 4 to 13 degrees, preferably 4 to 10 degrees, depending on the selected material pairing and other parameters in an axial juxtaposition or nesting of the first clamping double-cone body can be 45.1 and the second clamp double cone body 45.2 achieve a self-locking such that the first clamping double-cone body 45.1 and the second clamp double cone body 45.2 both no longer relative to each other about the cylinder longitudinal axis 26 of the cylinder 21 or about the axis of rotation 43 the spindle 35.2 are rotatable and no longer relative to each other in the axial direction 23 are movable or displaced, so not away from each other in one direction. Because there is a self-locking by a jamming of the two clamping double-cone body 45.1 . 45.2 one another, in which they are frictionally clamped together by static friction.

The first locking conical surfaces 48.1 of the first clamp double cone body 45.1 are due to an axial movement of the spindle 35.2 in the first direction 28.1 at the third locking conical surfaces 48.4 of the second clamping double cone body 45.2 of the cylinder 21 be applied so that in the applied state of the second clamping double-cone body 45.2 Can absorb axial forces in the first direction 28.1 on the spindle 35.2 act. Furthermore, the second locking conical surfaces 48.2 of the first clamp double cone body 45.1 by an axial movement of the spindle 35.2 in the second direction 28.2 at the fourth locking conical surfaces 48.4 of the second clamping double cone body 45.2 of the cylinder 21 be applied so that in the applied state of the second clamping double-cone body 45.2 Can absorb axial forces in the second direction 28.2 on the spindle 35.2 act.

The spindle 35.2 is by means of the first clamping double-cone body 45.1 at least two fluid-axial bearings 53.1 53.2 stored, of which a first fluid-axial plain bearing 53.1 destined to be in the first direction 28.1 on the spindle 35.2 to absorb acting axial forces, and of which a second fluid-axial sliding bearing 53.2 destined to the second direction 28.2 on the spindle 35.2 to absorb acting axial forces. The first fluid-axial plain bearing 53.2 is via a first pressure medium inflow channel 54.1 acted upon by the fluid pressure medium and the second fluid-axial slide bearing 53.2 is via a second pressure medium inflow channel 54.2 acted upon by the fluid pressure medium.

The first clamp double cone body 45.1 is in the second clamping double cone body 45.2 limited chamber 49 of the cylinder 21 or the cylinder bottom 30 added. The chamber 49 is on the one hand by a cylinder bottom part 50 of the cylinder 21 and on the other hand through the annular projection 51 limited, the, preferably in one piece, with the cylinder 21 connected or formed. The approach 51 extends radially and perpendicular to the cylinder longitudinal axis 26 of the cylinder 21 in the direction of the spindle 35.2 , The approach 51 is between the first clamp double cone body 45.1 and the piston 22 arranged.

The first pressure medium inflow channel 54.1 opens on one of the first locking cone surfaces 48.1 of the first clamp double cone body 45.1 assigned first page 55.1 of the first clamp double cone body 45.1 in the chamber 49 , The second pressure medium inflow channel 54.2 opens on a second locking cone surfaces 48.2 of the first clamp double cone body 45.1 assigned second page 55.2 of the first clamp double cone body 45.1 in the chamber 49 ,

The first clamp double cone body 45.1 is rotationally fixed to a non-threaded second spindle part 56.2 the spindle 35.2 attached, which in turn rotatably on a spindle thread 36.2 having the first spindle part 56.1 the spindle 35.2 is attached. Preferably, the first spindle part 56.1 and the second spindle part 56.2 the spindle 35.2 connected in one piece or made in one piece. The second spindle part not provided with a spindle thread 56.2 the spindle 35.2 is in a hole 57 of radially inward and outward transverse to the cylinder axis 23 of the cylinder 21 extending, annular approach 51 added. The approach 51 has a to the unthreaded second spindle part 56.1 the spindle 35.2 open ring groove 58 on whose wall is a ring seal 59 supported. About the ring seal 59 is the first clamp double cone body 45.1 receiving recess or chamber 49 opposite the second working chamber 31.2 sealed.

The one in the chamber 49 opening first pressure medium inflow channel 54.1 is with a first pressure medium outflow channel 61.1 a flow divider 60 . 60.1 . 60.2 fluidly connected and also in the chamber 49 opening second pressure medium inflow channel 54.2 is with a second pressure medium outflow channel 61.2 of the flow divider 60 . 60.1 . 60.2 fluidly connected. The flow divider 60 . 60.1 . 60.2 includes a pressure medium main inflow channel 62 that is in a first inflow channel 62.1 and a second inflow channel 62.2 branched. The flow divider 60 ; 60.1 . 60.2 serves for the division of the pressure medium main inflow channel 62 can be supplied to the main volume flow of the fluid pressure medium in a the first pressure medium outflow channel 61.1 and thus the first pressure medium inflow channel 54.1 to be supplied first part-volume flow of the fluid pressure medium and in a second pressure medium outflow channel 61.2 and thus the second pressure medium inflow channel 54.2 to be supplied second part volume flow of the fluid pressure medium.

By supplying the fluid pressure medium into the pressure medium main inflow channel 62 of the flow divider 60 ; 60.1 . 60.2 there is the possibility of the first clamping double cone body 45.1 in the chamber 49 in a fluid-dynamic floating position 63 to convict (see 1 and 2 ), in which both a trouble-free, in particular lock or jam-free, moving the piston 22 in the first direction 28.1 as well as a trouble-free, in particular lock or jam-free, moving the piston 22 in the second direction 28.2 is possible. Above all, by supplying the fluid pressure medium in the pressure medium main inflow channel 62 of the flow divider 60 ; 60.1 . 60.2 the possibility of the first clamping double cone body 45.1 while moving the piston 22 both in the first direction 28.1 as well as in the second direction 28.2 always in one or the fluid-dynamic floating position 63 or to keep in a fluid-dynamic floating state, regardless of the size of the load F and the system pressure required thereby.

According to a in 5 illustrated, preferred, first embodiment of the flow divider 60 ; 60.1 it is a fluid flow or fluid pressure controlled valve. In other words, it is a valve controlled by the flow of the fluid pressure medium or by the pressure of the fluid pressure medium. This valve or this flow divider 60 ; 60.1 includes a housing 64 with a circular cylindrical inner circumference having or circular cylindrical control piston receptacle 65 for a relative to this movable control piston 66 , which is also denoted by pressure compensator and / or slider. In the control piston intake 65 is the a circular cylindrical outer circumference having or circular cylindrical control piston 66 with very little clearance, in or with a clearance fit, guided relative to the control piston receptacle 65 in an axial direction 67 slidably mounted. Preferably, the control piston 66 in the control piston intake 65 of the housing 64 of the flow divider 60 ; 60.1 be honed. The control piston 66 extends axially in the direction of a control piston longitudinal axis 68 , The control piston 66 has a control piston length. The control piston 66 has a first control spool end 70.1 and one of them in an opposite direction in the axial direction 67 away extending second control piston end 70.1 on. The second control piston end 70.2 points from the first control piston end 70.1 a distance corresponding to the control piston length. The first inflow channel 62.1 includes a first fixed throttle 71.1 , The second inflow channel 62.2 includes a second fixed throttle 71.2 , The first hard throttle 71.1 and the second hard throttle 71.2 are at least designed identically with regard to the throttle cross section and the throttle length. The control piston intake 65 has a first recording end 73.1 and one of them in an opposite direction in the axial direction 67 away extending second receiving end 73.2 on. The control piston intake 65 has an axial length which is smaller than the control piston length of the control piston 66 so that the control piston 66 with its two facing away from each other rule piston ends 70.1 . 70.2 on both sides via the control piston receptacle 65 can stand out. When the control piston ends 70.1 . 70.2 of the control piston 66 each with the same length over the mutually facing receiving ends 73.1 . 73.2 the control piston intake 65 or over the perpendicular to the longitudinal axis 69 the control piston intake 65 trained, imaginary symmetry plane 79 extend out, is the control piston 66 in the in 5 shown basic or middle position 72 , The control piston intake 65 goes to her first recording end 73.1 in a first axial direction 67.1 considered, in a one circular-cylindrical inner cross-section having or circular cylindrical first control piston end recording 74.1 for receiving the first control piston end 70.1 of the control piston 66 over into which the first inflow channel 62.1 empties. The control piston intake 65 goes to her second recording end 73.2 in a second axial direction 67.2 considered, in a circular cylindrical inner cross-section having a circular or cylindrical second control piston end recording 74.2 for receiving the second control piston end 70.2 of the control piston 66 over into which the second inflow channel 62.2 empties. The first control piston end intake 74.1 forms part of a first control throttle 75.1 off and the second control piston end recording 74.2 forms part of a second control throttle 75.2 out. The first control piston end intake 74.1 is with a first pressure medium outflow channel 61.1 of the flow divider 60 fluidly connected and the second control piston end recording 74.2 is with a second pressure medium outflow channel 61.2 of the flow divider 60 fluidly connected. The control piston intake 65 points in an imaginary, perpendicular to the control piston longitudinal axis 68 trained cross-sectional plane, an inner cross section. The first control piston end intake 74.1 points in an imaginary, perpendicular to the control piston longitudinal axis 68 formed viewed first cross-sectional plane, a first inner cross-section which is greater than the inner cross-section of the control piston receiving 65 , The second control piston end intake 74.2 points in an imaginary, perpendicular to the control piston longitudinal axis 68 formed viewed second cross-sectional plane, a second inner cross section, which is also greater than the inner cross section of the control piston receiving 65 , The first inner cross section of the first control piston end receptacle 74.1 and the second inner cross section of the second control piston end receptacle 74.2 are the same size. The first control piston end intake 74.1 goes on one of the control piston intake 65 opposite first side, in the first axial direction 67.1 considered, in a circular cylindrical inner circumference having or circular cylindrical, third control piston end recording 74.3 over into which the first pressure medium outflow channel 61.1 empties. The third control piston end intake 74.3 points in an imaginary, perpendicular to the control piston longitudinal axis 68 Viewed parallel to the first cross-sectional plane formed third cross-sectional plane, a third inner cross-section, the inner cross-section of the control piston receiving 65 corresponds, so that the first control piston end 70.1 of the control piston 66 in the third control piston end recording 74.3 convertible and then there with very little play, preferably with a same game as in the control piston recording 65 , in or with a clearance fit, relative to the third control piston end receptacle 74.3 in the axial direction 67 is slidably mounted. The second control piston end intake 74.2 goes on one of the control piston intake 65 opposite second side, in the second axial direction 67.2 considered, in a circular cylindrical inner circumference having or circular cylindrical, fourth control piston end recording 74.4 over into which the second pressure medium outflow channel 61.2 empties. The fourth control piston end intake 74.4 points in an imaginary, perpendicular to the control piston longitudinal axis 68 Viewed parallel to the second cross-sectional plane formed fourth cross-sectional plane, a fourth inner cross-section, the inner cross-section of the control piston receiving 65 corresponds, so that the second control piston end 70.2 of the control piston 66 in the fourth control piston end recording 74.4 convertible and then there with very little play, preferably with a same game as in the control piston recording 65 , in or with a clearance fit, relative to the fourth control piston end receptacle 74.4 in the axial direction 67 is slidably mounted. The third and fourth control piston end intake 74.3 . 74.4 are each with a radially inward or to the longitudinal axis 69 the control piston intake 65 towards extending, annular end wall 77.1 . 77.2 of the housing 64 of the flow divider 60 ; 60.1 limited. The first end wall forms a first stop 77.1 for the first control piston end 70.1 of the control piston 66 out. The second end wall forms a second stop 77.2 for the second control piston end 70.2 of the control piston 66 out.

The control piston 66 is pressure or flow controlled by the fluid pressure medium in the first axial direction 67.1 slidable in a first shut-off position, in which he with his first control piston end 70.1 at the first stop 77.1 strikes and in which of the control piston 66 a first flow path from the first inflow channel 62.1 to the first pressure medium outflow channel 61.1 with respect to a flow through the fluid pressure medium, while a second flow path from the second inflow channel 62.2 to the second pressure medium outflow channel 61.2 is open or remains with respect to a flow through the fluid pressure medium. Furthermore, the control piston 66 flow-controlled by the fluid pressure medium in the second axial direction 67.2 displaceable in a second shut-off position, in which he with his second control piston end 70.2 at the second stop 77.2 strikes and in which of the control piston 66 a second flow path from the second inflow channel 62.2 to the second pressure medium outflow channel 61.2 with respect to a flow through the fluid pressure medium, while the first flow path from the first inflow channel 62.2 to the first pressure medium outflow channel 61.1 is open or remains with respect to a flow through the fluid pressure medium.

The control piston 66 containing flow divider 60 ; 60.1 is symmetrical to an imaginary, perpendicular to the control piston longitudinal axis 68 of the control piston 66 trained symmetry plane 79 designed. At the in 5 shown flow divider 60 ; 60.1 is a single-acting or acting only in a flow direction flow divider.

The most important part of this flow divider 60 ; 60.1 is also referred to as a pressure compensator or acting as a pressure compensator control piston 66 , The control piston 66 is in the axial direction 67 or in the longitudinal direction relative to a housing 64 of the flow divider 60 ; 60.1 up to the respective stop 77.1 . 77.2 displaceable. In the shared inflow line (first and second inflow channel 62.1 . 62.2 ) of the flow divider 60 ; 60.1 there is one throttle each 71.1 . 71.2 preferably with exactly the same throttle cross-section (throttle bore and throttle length). The movable control piston 66 or slider moves, depending on the pressure difference in the outgoing lines 61.1 . 61.2 ; 54.1 . 54.2 , in a first direction of displacement 67.1 or in a second direction of displacement 67.2 on the with the bore of the control piston intake 65 each exactly aligned bore (third and fourth control piston end recording 74.3 . 74.4 ) Same fit and causes there throttling or even blocking this channel. The interaction of these three components divides the from the flow divider 60 ; 60.1 outflowing pressure medium flow of the fluid pressure medium in a ratio of almost exactly 1: 1. Preferably, the inaccuracy is a maximum of +/- 2 percent, but this does not matter in this application. With regard to the two dimensionally identical throttles 71.1 . 71.2 is, in the case of a hydraulic pressure medium, the hydrodynamic law applicable. Through these two chokes 71.1 . 71.2 only the same pressure medium flow flows in a unit of time if the pressure gradient or the pressure difference before and after both throttles 71.1 . 71.2 is exactly the same. A tie of this pressure gradient is by the two chokes 71.1 . 71.2 downstream, axially displaceable, control piston 66 causes (hence the term "pressure compensator"), by, depending on the pressure ratio in the of the flow divider 60 ; 60.1 to the locking cylinder or to its chamber 49 for the first clamping double cone body 45.1 outgoing lines 61.1 . 61.2 ; 54.1 . 54.2 , the control piston 66 or slider its position relative to the housing 64 of the flow divider 60 ; 60.1 changes accordingly. Viewed in the flow direction before the two throttles 71.1 . 71.2 anyway there is equal pressure, because there the pressure chamber is the same. The following example may be the function of the control piston 66 clarify as a pressure compensator: Can by sticking the first clamping double-cone body 45.1 on the discharge side in question no fluid pressure medium flow, closes the pressure balance or the control piston 66 by the pressure accumulation on this blocked side of the first clamping double-cone body 45.1 automatically the other side, so that the flow divider 60 ; 60.1 locks both sides and only opens again when the jammed first clamp double cone body 45.1 in the cylinder 21 has solved or solved. The flow divider 60 ; 60.1 Thus, it has the property of always dividing the pressure medium flow of the fluid pressure medium from zero to a maximum almost exactly in a ratio that is substantially 1: 1, because the pressure difference through the pressure compensator or through the control piston 66 always kept substantially ("balanced") at the same value. The pressure medium flow of the fluid pressure medium can be specified, for example, in liters / minute.

By using the flow divider 60 ; 60.1 is achieved that the inscribable as a security cylinder locking cylinder 20 or its piston rod 34 (with changing load) can only undisturbed extend and retract, if the together with the spindle 35.2 around its axis of rotation 43 rotating first clamping double cone body 45.1 during the extension and retraction in a kind of forced swimming position 63 in a fluid-dynamic floating state between its two end stops (clamping positions and first and second locking position 46.1 . 46.2 ) remains.

In 6 schematically is an alternative embodiment of a flow divider 60 illustrated, which is a gearbox divider 60.2 is. This gearbox divider 60 ; 60.2 includes a first gear motor and a first gear pump 80.1 for conveying the first part volume flow and a second gear motor or a second gear pump 80.2 for the promotion of the second partial volume flow. The first gear pump 80.1 and the second gear pump 80.2 are about a wave 81 forcibly coupled with each other. Also with this gearbox divider 60 ; 60.2 For example, a ratio of the two partial volume flows can be maintained substantially constant at about 1: 1.

On the cylinder 21 is in the area of its cylinder bottom 30 a control block 82 attached, for example, flanged. The control block 82 includes a plurality of control and / or regulating elements for controlling and / or regulating the locking cylinder 20 or for operating the locking cylinder 20 , One of these control or regulating elements is preferably one or more than the flow divider according to the invention 60 ,

Between the third clamping cone body 47.3 and the fourth clamping cone body 47.4 of the second clamping double cone body 45.2 is an annular pressure medium discharge channel 83 for discharging the first and second fluid-axial sliding bearings 53.1 53.2 provided pressurizing fluid pressure medium. The pressure medium discharge channel 83 is adjacent to the first, second, third and fourth Locking cone surfaces 48.1 . 48.2 . 48.3 . 48.4 and enters the chamber 49 , The pressure medium discharge channel 83 is when the first clamping double cone body 45.1 in its fluid-dynamic floating position 63 located, with the first and with the second fluid-axial slide bearing 52.1 . 53.2 both over one then between the first and third interlock cone surfaces 48.1 . 48.3 trained, annular, first channel 84.1 fluidly connected as well as then between the second and fourth locking cone surfaces 48.2 . 48.4 trained, annular, second channel 84.2 fluidly connected.

If the first clamping double-cone body 45.1 and the second clamp double cone body 45.2 together in the first locking position 46.1 are locked self-locking jammed under formation of the deadlock, is the first pressure medium inflow channel 54.1 opposite the pressure medium discharge channel 83 by means of the then adjacent first and third locking cone surfaces 48.1 . 48.3 shut off. If this is the case, the first clamping double cone body 45.1 and the second clamp double cone body 45.2 from each other in an unlocked position 92 are lifted, is the first pressure medium inflow channel 54.1 with the pressure medium discharge channel 83 via the then formed between the first and third locking cone surfaces, annular, first channel 84.1 fluidly connected.

If the first clamping double-cone body 45.1 and the second clamp double cone body 45.2 together in the second locking position 46.2 are clamped self-locking jammed under formation of the deadlock is second pressure medium inflow channel 54.2 opposite the pressure medium discharge channel 83 by means of the adjoining second and fourth locking cone surfaces 48.2 . 48.4 shut off. If this is the case, the first clamping double cone body 45.1 and the second clamp double cone body 45.2 from each other in an unlocked position 92 are lifted, is the second pressure medium inflow channel 54.2 with the pressure medium discharge channel 83 over the then between the second and fourth locking cone surfaces 48.2 . 48.4 trained, annular, second channel 84.2 fluidly connected.

In the control block 82 of the locking cylinder 20 , which is in the area of the cylinder bottom 30 or the two clamping double cone body 45.1 . 45.2 is provided is a control unit 85 integrated with several, also with fluid channels designated flow and connection channels and control or regulating elements. The control unit is exemplary in 1 illustrated schematically with broken lines. The control elements are in the 1 to 4 and 6 , as usual in such circuit diagrams, drawn with circuit symbols or symbols of fluid technology.

It can be preferred only two connecting cables 86 and 87 be provided for an alternating supply and discharge of the fluid pressure medium. In the exemplary embodiments shown, a first connecting line 87 and a second connecting line 86 intended. Each of these connecting cables 86 and 87 So can serve as both a flow line and as a return line. For this purpose, a switching or control valve not shown in the figures can be provided, which is fluid-connected to a supply device for the fluid pressure medium, likewise not shown in the figures. The supply device may include a pump, preferably also a tank, for the fluid pressure medium.

The control unit 85 has as essential control or regulation elements at least the flow divider 60 , two changeover valves 88.1 . 88.2 , in particular in each case in the form of a 2-2-way valve, and two load-holding Senkbrems valves or Senkbrems valves 89.1 . 89.2 on, preferably also two check valves 90.1 . 90.2 ,

Each load-holding lowering brake valve or lowering brake valve 89.1 . 89.2 has an inlet 95.1 . 95.2 , an outlet 96.1 . 96.2 and a control terminal 97.1 . 97.2 on, on which a control line or a control channel 98.1 . 98.2 connected. The inlet 95.1 the first load-holding Senkbrems valve or lowering brake valve 89.1 is with the first working chamber 31.1 via the also referred to as the first working channel fluid channel 29.1 fluidly connected and the outlet 96.1 the first load-holding Senkbrems valve or lowering brake valve 89.1 is with the first connection channel 87 fluidly connected. The first control channel 98.1 the first load-holding Senkbrems valve or lowering brake valve 89.1 is with the second connection channel 86 fluidly connected. In contrast, the second inlet 95.2 the second load-holding lowering brake valve or lowering brake valve 89.2 with the second working chamber 31.2 via the also referred to as the second working channel fluid channel 29.2 fluidly connected and the second outlet 96.2 the second load-holding lowering brake valve or lowering brake valve 89.2 is with the second connection channel 86 fluidly connected. The second control channel 98.2 the second load-holding lowering brake valve or lowering brake valve 89.2 is with the first connection channel 87 fluidly connected.

Preferably, the respective load-holding lowering brake valve or the lowering brake valve 89.1 . 89.2 by the spring force of a spring 99.1 . 99.2 to be charged or to be the force of the the fluid pressure medium via the respective control channel 98.1 . 98.2 exercised, counteracts.

Preferably, the respective passageway between the respective inlet 95.1 . 95.2 and the respective outlet 96.1 . 96.2 the respective lowering brake valve 89.1 . 89.2 then, if the respective control channel 98.1 . 98.2 is not acted upon by fluid pressure medium or is depressurized, shut off, so that possibly at the respective inlet 95.1 . 95.2 Pressurized pressure medium the respective lowering brake valve 89.1 . 89.2 can not happen. In this way, the respective lowering brake valve as a load-holding lowering brake valve 89.1 . 89.2 be used. Because in the locked position of the respective lowering brake valve 89.1 . 89.2 can the piston 22 do not lower further. In this way, if necessary, regardless of or in addition to a mechanical locking of the locking cylinder 20 , respectively the piston 22 , a fluidic, in particular hydraulic, securing the locking cylinder 20 , respectively the piston 22 , be achieved.

With the help of the second load-holding lowering brake valve or lowering brake valve 89.2 can be effected or is caused when an impact of the piston 22 on his first page 27.1 with the one in the first working chamber 31.1 fluid pressure fluid under formation of a working pressure, the displacement of the piston 22 in the second direction or retraction direction 28.1 causes, simultaneously in the second working chamber 31.2 on the second page 27.2 of the piston 22 a through the in the second working chamber 31.2 located pressure medium applied counter pressure acts. The one in the second working chamber 31.2 acting back pressure is with the help of the second lowering brake valve 89.2 during the application of the first working chamber 31.1 with fluid pressure fluid and thus during movement of the piston 22 in the second direction or in the retraction direction 28.2 maintained at pressures that are always less than the working pressure in the first working chamber 31.1 are, so when moving the piston 22 in the second direction 28.2 a controlled braking of the piston 22 in the second direction 28.2 is effected. This may cause an uncontrolled advance of the piston 22 in the second direction 28.2 be avoided.

With the help of the first load-holding lowering brake valve or the lowering brake valve 89.1 can be effected or is caused when an impact of the piston 22 on his second page 27.2 with the in the second working chamber 31.2 located pressure medium to form a working pressure, a displacement of the piston 22 in the first direction or extension direction 28.1 causes, simultaneously in the first working chamber 31.1 on the first page 27.1 of the piston 22 one by the one in the first working chamber 31.1 located pressure medium applied counter pressure acts. The one in the first working chamber 31.1 acting back pressure is with the help of the first lowering brake valve 89.1 during the admission of the second working chamber 31.2 with pressure medium and consequently during a movement of the piston 22 in the first direction 28.1 kept at pressures that are always less than the working pressure in the second working chamber 31.2 are, so when moving the piston 22 in the first direction 28.1 a controlled braking of the piston 22 in the first direction 28.1 is effected. This may cause an uncontrolled advance of the piston 22 in the first direction 28.1 be avoided.

The first connection channel 87 is over the first channel 91.1 with the pressure medium main inflow channel 62 of the flow divider 60 fluidly connected. The first channel 91.1 contains the first check valve 90.1 , The first check valve 90.1 allows a flow of the fluid pressure medium to the flow divider 60 towards, but locks in the opposite direction. The second connection channel 86 is over the second channel 91.2 with the pressure medium main inflow channel 62 of the flow divider 60 fluidly connected. The second channel 91.2 contains the second check valve 90.2 , The second check valve 90.2 allows a flow of the fluid pressure medium to the flow divider 60 towards, but locks in the opposite direction. The first and second check valves 90.1 . 90.2 each contain at least one locking member. Preferably, the locking member may be a ball.

The pressure medium discharge channel 83 the recess or chamber 49 of the cylinder 21 is with the first and second switching valve 88.1 . 88.2 fluidly connected. At these changeover valves 88.1 . 88.2 each is a 2-2-way valve. The first switching valve 88.1 is from one in the 1 to 4 shown first passage position 100.1 , in which the fluid pressure medium from the pressure medium discharge channel 83 the chamber 49 in the first working chamber 31.1 can flow, in a first blocking position operable or switchable, in which the flow path of the pressure medium discharge channel 83 to the first working chamber 31.1 Is blocked. The second switching valve 88.1 is from one in the 1 to 4 shown second passage position 100.2 , in which the fluid pressure medium from the pressure medium discharge channel 83 the chamber 49 in the second working chamber 31.2 can flow, in a second blocking position operable or switchable, in which the flow path of the pressure medium discharge channel 83 to the second working chamber 31.2 Is blocked. At the first passage position 100.1 of the first switching valve 88.1 and also at the second passage position 100.2 the second switching valve 88.2 are each about a basic position in which the switching valves 88.1 . 88.2 due to a pressurization with fluid pressure medium via in each case one fluid-connected to the pressure medium discharge channel first or second control channel 101.1 . 101.2 be held or transferred. Each changeover valve 88.1 . 88.2 So forms a means to demand or switchable blocking or releasing a passage way. The control for switching the first switching valve 88.1 from his first basic position 100.1 in its first blocking position via a third control channel 101.3 that with the second connection channel 86 fluidly connected. The control for switching the second switching valve 88.2 from its second basic or passage position 100.2 in its second blocking position via a fourth control channel 101.4 that with the first connection channel 87 fluidly connected.

The function of the whole, in an end housing or control block 82 of the locking cylinder 20 integrated control unit 85 with the appropriate control or regulating organs or elements, is described below.

During a movement of the piston 22 in the first direction 28.1 or during extension of the piston rod 34 in the extension direction 28.1 , becomes the second connection channel 86 subjected to fluid pressure medium, while the first connection channel 87 is depressurized by means of a suitable, not shown in the figures means, or is. As a result, the fluid pressure medium through the second connection channel 86 and at a branch thereof, leaving through the second channel 91.2 with a main volume flow in the pressure medium main inflow channel 62 of the flow divider 60 stream. The pressure balance or the control piston 66 of the flow divider 60 ; 60.1 now regulates a first part-volume flow of the main volume flow in the in the recess or chamber 49 of the cylinder 21 opening first pressure medium inflow channel 54.1 and a second partial volume flow of the main volume flow in the in the recess or chamber 49 of the cylinder 21 opening second pressure medium inflow channel 54.2 such that the ratio of the through the first pressure medium inflow channel 54.1 through the first fluid-axial sliding bearing 53.1 inflowing first part-volume flow of the fluid pressure medium and by the second pressure medium inflow channel 54.2 through the second fluid-axial sliding bearing 53.2 inflowing second volume partial flow of the fluid pressure medium, at least during a movement of the piston 22 in the first direction 28.1 and also during a movement of the piston 22 in the second direction 28.2 , regardless of the in the first pressure medium inflow channel 54.1 and in the second pressure medium inflow channel 54.2 acting or adjusting pressures or back pressures of the fluid pressure medium always remains substantially constant. As a result, the first clamping double-cone body is or remains 45.1 both by means of the acted upon by the fluid pressure fluid first fluid-axial slide bearing 53.1 as well as by means of acted upon by the fluid pressure fluid second fluid-axial bearing 53.2 regardless of a size one on the piston 22 acting load F (on pressure or train) and thereby required system pressure, always in a fluid-dynamic floating position 63 or fluidly stored in a fluid-dynamic floating state (see 1 and 2 ). Said ratio is in the embodiment shown substantially 1: 1, so that therefore the first part-volume flow of the fluid pressure medium and the second part-volume flow of the fluid pressure medium are substantially equal or remain. That of the recess or chamber 49 via the first and second pressure medium inflow channel 54.1 . 54.2 inflowing fluid pressure medium flows while maintaining the two-sided axial fluid sliding bearing of the first clamping double-cone body 45.1 and its fluid-dynamic floating position 63 in the recess or chamber 49 in the pressure medium discharge channel 83 , At the same time is the first switching valve 88.1 in its first blocking position, while the second switching valve 88.2 in his second passage position 100.2 is located so that the fluid pressure fluid from the pressure medium discharge channel 83 via a second pressure medium channel 102.2 to the second working chamber 31.2 can flow to move the piston 22 in the first direction 28.1 or a movement of the piston 22 in the first direction 28.1 or to an extension of the piston rod 34 in the extension direction 28.1 to effect.

During a movement of the piston 22 in the second direction 28.2 or during retraction of the piston rod 34 in the retraction direction 28.2 , becomes the first connection channel 87 subjected to fluid pressure medium, while the second connection channel 86 is depressurized by means of the means not shown in the figures. As a result, the fluid pressure medium through the first connection channel 87 and at a branch thereof, outgoing through the first channel 91.1 with a main volume flow in the pressure medium main inflow channel 62 of the quantity distributor 60 stream. The pressure balance or the control piston 66 of the flow divider 60 ; 60.1 now regulates a first part-volume flow of the main volume flow in the in the recess or chamber 49 of the cylinder 21 opening first pressure medium inflow channel 54.1 and a second partial volume flow of the main volume flow in the in the recess or chamber 49 of the cylinder 21 opening second pressure medium inflow channel 54.2 such that said ratio, as already described above, is always substantially 1: 1 or in the Essentially at 1: 1 remains. Also in this case flows that of the recess or chamber 49 via the first and second pressure medium inflow channel 54.1 . 54.2 inflowing fluid pressure medium while maintaining the two-sided axial fluid sliding bearing of the first clamping double-cone body 45.1 and its fluid-dynamic floating position 63 in the recess or chamber 49 in the pressure medium discharge channel 83 , But now is the first switching valve 88.1 in his first passage position 100.1 while the second switching valve 88.2 is in its second blocking position, so that the fluid pressure fluid from the pressure medium-discharge channel 83 via a first pressure medium channel 102.1 to the first working chamber 31.1 can flow to a movement of the piston 22 in the second direction 28.2 or to retract the piston rod 34 in the retraction direction 28.2 to effect.

During a movement of the piston 22 in the first direction 28.1 or during extension of the piston rod 34 in the extension direction 28.1 This will be in the first working chamber 31.1 located fluid pressure medium in the first working channel 29.1 displaced and can from there via the first lowering brake valve 89.1 in the here as reflux channel serving first connection channel 87 flow out. It is using the first lowering brake valve 89.1 in the first working chamber 31.1 the working pressure in the second working chamber 31.2 counteracting counter or brake pressure maintained, which causes the piston 22 and consequently the piston rod 34 not uncontrolled in the first direction or extension direction 28.1 move, in particular not uncontrolled in the extension direction 28.1 can lead the way. To work with increasing pressure in the second working chamber 31.2 always a sufficiently large back pressure in the first working chamber 31.1 to ensure is the first lowering brake valve 89.1 with the second control channel 98.2 coupled to the second connection channel 86 fluidly connected. In this way opens the first lowering brake valve 89.1 a passageway between the first working channel 29.1 and the first connection channel 87 depending on the in the second working channel 29.2 or in the second working chamber 31.2 acting working pressure, preferably in proportion to the working pressure, so that with increasing working pressure in the second working chamber 31.2 with the help of the first lowering brake valve 89.1 a corresponding, preferably proportional, increasing backpressure in the first working chamber 31.1 can be achieved or achieved.

During a movement of the piston 22 in the second direction 28.2 or during retraction of the piston rod 34 in the retraction direction 28.2 that will be in the second working chamber 31.2 located fluid pressure medium in the second working channel 29.2 displaced and can from there via the second lowering brake valve 89.2 in the here serving as reflux channel second connection channel 86 flow out. It is using the second lowering brake valve 89.2 in the second working chamber 31.2 the working pressure in the first working chamber 31.1 counteracting counter or brake pressure maintained, which causes the piston 22 and consequently the piston rod 34 not uncontrolled in the second direction or retraction 28.2 move, in particular not uncontrolled in the retraction direction 28.2 can lead the way. To work with increasing working pressure in the first working chamber 31.1 always a sufficiently large back pressure in the second working chamber 31.2 to ensure is the second lowering brake valve 89.2 with the first control channel 98.1 coupled to the first connection channel 87 fluidly connected. In this way opens the second lowering brake valve 89.2 a passageway between the second working channel 29.2 and the second connection channel 86 depending on the one in the first working channel 29.1 or in the first working chamber 31.1 acting working pressure, preferably in proportion to the working pressure, so that with increasing working pressure in the first working chamber 31.1 with the help of the second lowering brake valve 89.2 a corresponding, preferably proportional, increasing backpressure in the second working chamber 31.2 can be achieved or achieved.

To stop the movement of the piston 22 in the axial direction 23 or to stop the entry or exit movement 28.2 . 28.1 the piston rod 34 in conjunction with a self-locking locking the locking cylinder 20 , both are connection channels 86 and 87 depressurized by means of the means not shown in the figures. Then it comes alone by the weight of the piston rod 34 and the piston 22 but especially if the piston rod 34 with a load F (on pressure or train) is acted upon by gravity automatically or automatically to a lock on the spindle 35.2 non-rotatably mounted first clamping double-cone body 45.1 with the second clamping double cone body 45.2 of the cylinder 21 by a self-locking jamming of these two components 45.1 . 45.2 together and as a result to a locking of the spindle 35.2 among other things against a rotation about your axis of rotation 43 ,

When the piston rod 34 by a load F on train (in the first direction 28.1 ), then poses a first locking position 46.1 a, like in 3 shown. Here is the first clamping double cone body 45.1 about his first locking cone surfaces 48.1 with the third locking cone surfaces 48.3 of the second clamping double cone body 45.2 of the cylinder 21 self-locking, so frictionally jammed by static friction.

When the piston rod 34 by a load F on pressure (in the second direction 28.2 ), then poses a second locking position 46.2 a, like in 4 shown. Here is the first clamping double cone body 45.1 over its second locking cone surfaces 48.2 with the fourth locking cone surfaces 48.4 of the second clamping double cone body 45.2 of the cylinder 21 self-locking, so frictionally jammed by static friction.

In the locking cylinder according to the invention 20 increases the clamping force between the two jammed clamp double cone bodies 45.1 . 45.2 with increasing load F proportional to. As a result, at each load F always secure locking of the spindle 35.2 against rotation about its axis of rotation 43 relative to the cylinder 21 can be achieved and as a result, a further movement of the piston 22 and at this over the piston rod 34 attacking load F can be safely prevented, and not only in a normal operation of the locking cylinder 20 , but also in the case of a pressure failure of the pressure medium system or in the event of any leakage of the pressure medium system occurring. The locking cylinder according to the invention 20 offers a higher locking safety than previously known, locking cylinders that lock frictionally by sliding friction, but not self-locking, so frictionally by static friction, by jamming.

To start from the in 4 shown second locking position 46.2 or starting from the 3 shown first locking position 46.1 an unlocking of the first clamping double-cone body 45.1 from the second clamp double cone body 45.2 to achieve a movement of the piston 22 in the axial direction 23 or an entry or exit movement 28.2 . 28.1 the piston rod 34 will allow, depending on whether the piston 22 in the first direction 28.1 or in the second direction 28.2 is to be moved, either the second connection channel 86 or the first connection channel 87 subjected to fluid pressure medium.

As a result, the fluid pressure medium flows with the main volume flow in the pressure medium main inflow channel 62 of the quantitative part 60 ,

If now the first clamping double-cone body 45.1 in the in 4 shown second locking position 46.2 is the second pressure medium inflow channel 54.2 for the chamber 49 opposite the pressure medium discharge channel 83 by means of the adjoining second and fourth locking cone surfaces 48.2 . 48.4 shut off. As a result, this leads to the admission of the flow divider 60 ; 60.1 via the pressure medium main inflow channel 62 with the fluid pressure medium that the control piston 66 is moved to its first stop and shut-off, in which then the first inflow 62.1 of the flow divider 60 ; 60.1 opposite the first pressure medium outflow channel 61.1 of the flow divider 60 ; 60.1 and thus with respect to the recess or in the chamber 49 opening first pressure medium inflow channel 54 .1 is shut off or is. In this way, then the maximum pressure medium pressure of the fluid pressure medium at the second pressure medium outflow channel 61.2 of the flow divider 60 ; 60.1 and thus also in the recess or chamber 49 opening, second pressure medium inflow channel 54.2 and consequently also in the second fluid-axial sliding bearing 53.2 at. If then the system pressure and accordingly in the second fluid-axial bearing 53.2 As a result, the resulting pressure fluid pressure of the fluid pressure medium is sufficiently large, is the self-locking jamming of the first clamping double-cone body 45.1 solved and the first clamping double-cone body 45.1 lifts off the fourth locking cone surfaces 48.4 of the second clamping double cone body 45.2 in the first direction 28.1 from. As a result, forms between the second locking cone surfaces 48.2 of the first clamp double cone body 45.1 and the fourth locking cone surfaces 48.4 of the second clamping double cone body 45.2 an annular, second channel 84.2 from (cf. 1 and 2 ), so coinciding with the training of this channel 84.2 , the fluid pressure medium from the into the recess or chamber 49 opening second pressure medium inflow channel 54.2 over or through the annular second channel 84.2 in the recess or chamber 49 opening pressure medium discharge channel 83 can flow. As a result, it comes in the in the recess or chamber 49 opening second pressure medium inflow channel 54.2 and thus in the second pressure medium outflow channel 61.2 of the flow divider 60 ; 60.1 to a pressure drop or to a pressure equalization with the first pressure medium outflow channel 61.1 and the first pressure medium inflow channel 54.1 and at the same time in the recess or chamber 49 opening first pressure medium inflow channel 54.1 and thus in the first pressure medium outflow channel 61.2 of the flow divider 60 ; 60.1 to an increase in pressure or to a pressure equalization with the second pressure medium outflow channel 61.2 and the second pressure medium inflow channel 54.2 , with the result that the resulting pressure difference immediately from the pressure compensator or from the control piston 66 equalized or "balanced" is. In the course of this, the control piston moves 66 , with continued supply of the fluid pressure medium, starting from its first Stop and shut-off position in the direction of the second stop 77.2 , This then also the first passageway of the first inflow channel 62.1 of the flow divider 60 ; 60.1 to the first pressure medium outflow channel 61.1 of the flow divider 60 ; 60.1 free or open, so that the fluid pressure medium via the first pressure medium inflow channel 54.1 in the recess or chamber 49 and from there over the one between the first locking cone surfaces 48.1 of the first clamp double cone body 45.1 and the third locking cone surfaces 48.3 of the second clamping double cone body 45.2 formed first annular channel 84.1 also in the recess or chamber 49 opening common pressure fluid discharge channel 83 flows.

But if the first clamping double-cone body 45.1 in the in 3 shown first locking position 46.1 is the first pressure medium inflow channel 54.1 for the chamber 49 opposite the pressure medium discharge channel 83 by means of the abutting first and third locking cone surfaces 48.1 . 48.3 shut off. As a result, this leads to the admission of the flow divider 60 ; 60.1 via the pressure medium main inflow channel 62 with the fluid pressure medium that the control piston 66 is moved to its second stop and shut-off, in which then the second inflow 62.2 of the flow divider 60 ; 60.1 opposite the second pressure medium outflow channel 61.2 of the flow divider 60 ; 60.1 and thus with respect to the recess or in the chamber 49 opening second pressure medium inflow channel 54.2 is locked or is. In this way, then the maximum pressure medium pressure of the fluid pressure medium at the first pressure medium outflow channel 61.1 of the flow divider 60 ; 60.1 and thus also in the recess or chamber 49 opening, first pressure medium inflow channel 54.1 and consequently also in the first fluid-axial plain bearing 53.1 at. If then the system pressure and accordingly in the first fluid-axial bearing 53.1 As a result, the resulting pressure fluid pressure of the fluid pressure medium is sufficiently large, is the self-locking jamming of the first clamping double-cone body 45.1 solved and the first clamping double-cone body 45.1 lifts off the third lock-cone surfaces 48.3 of the second clamping double cone body 45.2 in the second direction 28.2 from. As a result, forms between the first locking cone surfaces 48.1 of the first clamp double cone body 45.1 and the third locking cone surfaces 48.3 of the second clamping double cone body 45.2 an annular, first channel 84 .1 (cf. 1 and 2 ), so coinciding with the training of this channel 84.1 , the fluid pressure medium from the into the recess or chamber 49 opening first pressure medium inflow channel 54.1 over or through the first annular channel 84.1 in the recess or chamber 49 opening pressure medium discharge channel 83 can flow. As a result, it comes in the in the recess or chamber 49 opening first pressure medium inflow channel 54.1 and thus in the first pressure medium outflow channel 61.1 of the flow divider 60 ; 60.1 to a pressure drop or to a pressure equalization with the second pressure medium outflow channel 61.2 and the second pressure medium inflow channel 54.2 and at the same time in the recess or chamber 49 opening second pressure medium inflow channel 54.2 and thus in the second pressure medium outflow channel 61.2 of the flow divider 60 ; 60.1 to a pressure increase or to a pressure equalization with the first pressure medium outflow channel 61.1 and the first pressure medium inflow channel 54.1 , with the result that the resulting pressure difference immediately from the pressure compensator or from the control piston 66 equalized or "balanced" is. In the course of this, the control piston moves 66 , with continued supply of the fluid pressure medium, starting from its second stop and shut-off position in the direction of the first stop 77.1 , This then also the first passageway from the second inflow channel 62.2 of the flow divider 60 ; 60.1 to the second pressure medium outflow channel 61.2 of the flow divider 60 ; 60.1 free or open, so that the fluid pressure medium via the second pressure medium inflow channel 54.2 in the recess or chamber 49 and from there over the between the second locking cone surfaces 48.2 of the first clamp double cone body 45.1 and the fourth locking cone surfaces 48.4 of the second clamping double cone body 45.2 formed annular second channel 84.2 also in the recess or chamber 49 opening common pressure fluid discharge channel 83 flows.

In the two aforementioned cases, the control piston moves 66 , starting from the respective stop and shut-off position, in the direction of the other stop 77.2 . 77.1 to a basic or middle position 72 , in which the pressure difference of the pressure medium pressure in the first pressure medium outflow channel 61.1 of the flow divider 60 ; 60.1 and the pressure medium pressure in the second pressure medium outflow channel 61.2 of the quantitative part 60 ; 60.1 or the pressure difference across the two fixed throttles 71.1 . 71.2 is approximately or substantially zero, so that then the first part-volume flow in the first pressure medium outflow channel 61.1 of the quantitative part 60 ; 60.1 and consequently in the recess or chamber 49 opening first pressure medium inflow channel 54.1 and the second partial volume flow in the second pressure medium outflow channel 61.2 of the quantitative part 60 ; 60.1 and consequently in the recess or chamber 49 opening second pressure medium inflow channel 54.2 are essentially the same size or are held or remain.

Depending on which of the two changeover valves 88.1 . 88.2 locked and which other of the two changeover valves 88.2 . 88.1 is opened, then flows the fluid pressure fluid from the pressure medium-discharge channel 83 either via the first pressure medium channel 102.1 in the first working chamber 33.1 , causing the piston 22 in the second direction 28.2 or the piston rod 34 in the retraction direction 28.2 is moved, or via the second pressure medium channel 102.2 in the second working chamber 31.2 , causing the piston 22 in the first direction 28.1 or the piston rod 34 in the extension direction 28.1 is moved.

It can be seen, also with reference to the figures, that the direction of flow via the flow divider 60 on the two in the axial direction 23 facing away from each other end faces 55.1 . 55.2 of the first clamp double cone body 45.1 (due to the rest of the control arrangement) is always the same, regardless of whether the locking cylinder 20 , respectively its piston rod 34 , in or out. In addition, a sequence control is realized such that first the first clamping double-cone body 45.1 is released from its jamming and only then the piston 22 on a piston side 27.1 . 27.2 his two facing away from each other piston sides 27.1 . 27.2 is acted upon by the fluid pressure medium, whereby a movement of the piston 22 in the axial direction 23 and thereby a rotation of the spindle 35.2 together with the first clamp double cone body 45.1 is effected.

LIST OF REFERENCE NUMBERS

20

 Locking cylinder / lock cylinder-piston unit

21

 cylinder

22

 Piston / batch

23

 axially

24

 Cylinder jacket inner surface

25

 ring seal

26

 cylinder longitudinal axis

27.1

 first (piston) side

27.2

 second (piston) side

28.1

 first direction / extension direction

28.2

 second direction / retraction direction

29.1

 first working channel / fluid channel

29.2

 second working channel / fluid channel

30

 Cylinder base / lid / head

31.1

 first working chamber

31.2

 second working chamber

33

 ring groove

34

 Rod / hollow body

35.1

 first threaded body / (piston) nut

35.2

 second threaded body / spindle

36.1

 first thread / nut / piston / internal thread

36.2

 second thread / spindle / external thread

37

 non-self-locking thread

38.1

first page (from 21 )

38.2

second page (from 21 )

39

 cover

40

 ring groove

41

 ring seal

43

 axis of rotation

44

 Double arrow (spindle play)

45.1

 first clamping double cone body

45.2

 second clamping double cone body

46.1

 first locking position

46.2

 second locking position

47.1

first clamping cone body (from 45.1 )

47.2

second clamping cone body (from 45.1 )

47.3

third clamping cone body (from 45.2 )

47.4

fourth clamping cone body (from 45.2 )

48.1

first locking cone surfaces (from 47.1 . 45.1 )

48.2

second locking cone surfaces (of 47.2 . 45.1 )

48.3

third locking cone surfaces (from 47.3 . 45.2 )

48.4

fourth locking cone surfaces (from 47.4 . 45.2 )

49

 Recess / chamber

50

 The cylinder bottom part / lid

51

 (annular) approach

52.1

first inclination angle (from 48.1 . 48.2 )

52.2

second inclination angle (from 48.3 . 48.4 )

53.1

 first fluid-axial plain bearing

53.2

 second fluid-axial plain bearing

54.1

 first pressure medium inflow channel

54.2

 second pressure medium inflow channel

55.1

first (forehead) side (from 45.1 )

55.2

second (forehead) side (from 45.1 )

56.1

 first spindle part

56.2

 second spindle part (thread-free)

57

Bore (from 51 )

58

Ring groove (in 51 )

59

Ring seal (in 58 )

60

 flow divider

60.1

 Flow divider / valve

60.2

 Flow divider / gear flow divider

61.1

 first pressure medium outflow channel

61.2

 second pressure medium outflow channel

62

 Pressure medium main inflow duct

62.1

 first inflow channel

62.2

 second inflow channel

63

 Float / floating condition

64

 casing

65

 Control piston Recording

66

 Control piston / pressure regulator / slide

67

 axial direction (double arrow)

67.1

 first axial direction

67.2

 second axial direction

68

 Control piston longitudinal axis

69

Longitudinal axis (from 65 )

70.1

 first control piston end

70.2

 second control piston end

71.1

 first (fixed) throttle

71.2

 second (fixed) throttle

72

 Basic or middle position

73.1

first end of recording (from 65 )

73.2

second end of recording (from 65 )

74.1

 first control piston end intake

74.2

 second control piston end intake

74.3

 third control piston end intake

74.4

 fourth control piston end intake

75.1

 first rule throttle

75.2

 second control throttle

77.1

 first end wall / stop

77.2

 second end wall / stop

79

 plane of symmetry

80.1

 first gear pump

80.2

 second gear pump

81

 wave

82

 control block

83

 Pressure fluid discharge conduit

84.1

 (annular) first channel

84.2

 (annular) second channel

85

 control unit

86

 (second / r) connection line / connection channel

87

 (first / r) connection line / connection channel

88.1

 first changeover valve

88.2

 second changeover valve

89.1

 first (load-holding) lowering brake valve

89.2

 second (load-holding) lowering brake valve

90.1

 first check valve

90.2

 second check valve

91.1

 first channel

91.2

 second channel

92

 (Lift-off and) unlocked position

95.1

 inlet

95.2

 inlet

96.1

 outlet

96.2

 outlet

97.1

 control connection

97.2

 control connection

98.1

 control channel

98.2

 control channel

99.1

 feather

99.2

 feather

100.1

first passage position (basic position) (from 88.1 )

100.2

second passage position (basic position) (from 88.2 )

101.1

 first control channel

101.2

 second control channel

101.3

 third control channel

101.4

 fourth control channel

102.1

 first pressure medium channel

102.2

 second pressure medium channel

F

 load

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102010015996 A1 [0002]
• EP 2239470 A2 [0002]
• EP 2570679 A1 [0002]
• EP 2570680 A1 [0002]

Claims (20)

Pressure medium operated, double-acting locking cylinder ( 20 ), which extends in the direction of a cylinder longitudinal axis ( 26 ) extending cylinder ( 21 ) and a piston ( 22 ), one of a first working chamber ( 31.1 ) associated first piston side ( 27.1 ) and a second, a second working chamber ( 31.2 ) associated second piston side ( 27.2 ) and which by means of one of the first piston side ( 27.1 ) via one in the first working chamber ( 31.1 ) first working channel ( 29.1 ) and the second piston side ( 27.2 ) via one into the second working chamber ( 31.2 ) second working channel ( 29.2 ) deliverable fluid pressure medium in an axial direction ( 23 ) parallel to the cylinder longitudinal axis ( 26 ) in a second direction ( 28.2 ) and in a first direction ( 28.1 ) opposite to the second direction ( 28.2 ) relative to the cylinder ( 21 ) movable, but non-rotatable with the cylinder ( 21 ), wherein the piston ( 22 ) rotatably with a first threaded body (nut or spindle) ( 35.1 ) whose first thread (female thread or spindle thread) ( 36.1 ) with a second thread (spindle thread or female thread) ( 36.2 ) of a frictional and gravitational self-locking second threaded body (spindle or nut) ( 35.2 ) to form a non-self-locking thread ( 37 ), and wherein the second threaded body ( 35.2 ) about a parallel to the cylinder longitudinal axis ( 26 ) of the cylinder ( 21 ) extending axis of rotation ( 43 ) relative to the cylinder ( 21 ) rotatable and relative to the cylinder ( 21 ) in the axial direction ( 23 ) is axially displaceable, and wherein one with the second threaded body ( 35.2 ) rotatably connected first clamping double-cone body ( 45.1 ) is provided, which has a first locking cone surfaces ( 48.1 ) first clamping cone body ( 47.1 ) and a second locking cone surfaces ( 48.2 ) having second clamping cone body ( 47.2 ), and wherein one with the cylinder ( 21 ) rotatably connected second clamping double-cone body ( 45.2 ) having a third locking cone surface ( 48.3 ) third clamping cone body ( 47.3 ) and a fourth locking cone surfaces ( 48.4 ) fourth clamping cone body ( 47.4 ), and wherein the first locking conical surfaces ( 48.1 ) of the first clamping double-cone body ( 45.1 ) by an axial movement of the second threaded body ( 35.2 ) in the first direction ( 28.1 ) on the third locking conical surfaces ( 48.3 ) of the second clamping double cone body ( 45.2 ) can be applied such that in the applied state of the second clamping double-cone body ( 45.2 ) Can absorb axial forces acting in the first direction ( 28.1 ) on the second threaded body ( 35.2 ) and the first locking conical surfaces ( 48.1 ) and the third locking conical surfaces ( 48.3 ) to form a jamming with each other in a first locking position ( 46.1 ), against rotation about the axis of rotation ( 43 ) of the second threaded body ( 35.2 ) as well as against a movement in the axial direction ( 23 ) are clamped away from each other, self-locking, and wherein the second locking conical surfaces ( 48.2 ) of the first clamping double-cone body ( 45.1 ) by an axial movement of the second threaded body ( 35.2 ) in the second direction ( 28.2 ) on the fourth locking conical surfaces ( 48.4 ) of the second clamping double cone body ( 45.2 ) can be applied such that in the applied state of the second clamping double-cone body ( 45.2 ) Can absorb axial forces acting in the second direction ( 28.2 ) on the second threaded body ( 35.2 ) and the second locking conical surfaces ( 48.2 ) and the fourth locking conical surfaces ( 48.4 ) to form a jamming together in a second locking position ( 46.2 ), against rotation about the axis of rotation ( 43 ) of the second threaded body ( 35.2 ) as well as against a movement in the axial direction ( 23 ) away from each other, are self-locking jammed, so that the locking cylinder ( 20 ) both on train in the first locking position ( 46.1 ) as well as pressure in the second locking position ( 46.2 ) is lockable and in the applied state in the respective locking position ( 46.1 . 46.2 ) is locked in such a way that the first clamping double-cone body ( 45.1 ) only by exerting the clamping solving dissolving forces of the second clamping double-cone body ( 45.2 ) in an unlocked position ( 92 ) is convertible, in which the second threaded body ( 35.2 ) about its axis of rotation ( 43 ) relative to the cylinder ( 21 ) is rotatable, and wherein the second threaded body ( 35.2 ) on at least two fluid-axial plain bearings ( 53.1 . 53.2 ), of which a first fluid-axial plain bearing ( 53.1 ) is intended to be in the first direction ( 28.1 ) on the second threaded body ( 35.2 ) to absorb acting axial forces, and of which a second fluid-axial plain bearing ( 53.2 ) is intended to move in the second direction ( 28.2 ) on the second threaded body ( 35.2 ) to receive acting axial forces, and wherein the first fluid-axial sliding bearing ( 53.1 ) via a first pressure medium inflow channel ( 54.1 ) is acted upon with or a fluid pressure medium, and wherein the second fluid-axial bearing ( 53.2 ) via a second pressure medium inflow channel ( 54.2 ) is acted upon with or a fluid pressure medium, and wherein a flow divider ( 60 ; 60.1 . 60.2 ) is provided for dividing a main volume flow of the fluid pressure medium in a first part-volume flow and in a second part-volume flow, the one in the first pressure medium inflow channel ( 54.1 ) for the first fluid-axial plain bearing ( 53.1 ) opening first pressure medium outflow channel ( 61.1 ) for the first part volume flow and one in the second pressure medium inflow channel ( 54.2 ) for the second fluid-axial plain bearing ( 53.2 ) opening second pressure medium outflow channel ( 61.2 ) for the second part volume flow. Locking cylinder according to claim 1, characterized in that it is in the flow divider ( 60 ; 60.1 ) is a flow and / or pressure-controlled valve. Locking cylinder according to claim 1 or 2, characterized in that the flow divider ( 60 ; 60.1 ) a housing ( 64 ) with a control piston receptacle ( 65 ), in which a control piston ( 66 ) guided with little play relative to the control piston receptacle ( 65 ) in an axial direction ( 67 ) is slidably mounted, and wherein the control piston ( 66 ) axially in the direction of a control piston longitudinal axis ( 68 ), has a control piston length and a first control piston end ( 70.1 ) and one of them in an opposite direction in the axial direction ( 67 ) extending away second control piston end ( 70.2 ), which from the first control piston end ( 70.1 ) has a distance corresponding to the control piston length, and wherein in the housing ( 64 ) a first throttle ( 71.1 ) containing the first inflow channel ( 62.1 ) for a first partial volume flow of the fluid pressure medium and a second throttle ( 71.2 ) containing the second inflow channel ( 62.2 ) are arranged for a second partial volume flow of the fluid pressure medium, and wherein the control piston receptacle ( 65 ) a first receiving end ( 73.1 ) and one thereof in an opposite direction in the axial direction ( 67 ) extending second receiving end ( 73.2 ), and wherein the control piston receptacle ( 65 ) at its first receiving end ( 73.1 ), in the axial direction ( 67 ), into a first control piston end receptacle ( 74.1 ) for receiving the first control piston end ( 70.1 ) of the control piston ( 66 ) into which the first inflow channel ( 62.1 ), and wherein the control piston receptacle ( 65 ) at its second receiving end ( 73.2 ), in the axial direction ( 67 ), into a second control piston end receptacle ( 74.2 ) for receiving the second control piston end ( 70.2 ) of the control piston ( 66 ) into which the second inflow channel ( 62.2 ), and wherein the first control piston end receptacle ( 74.1 ) a first control throttle or a component of a first control throttle ( 75.1 ) and the second control piston end receptacle ( 74.2 ) a second control throttle or a component of a second control throttle ( 75.2 ), and wherein the first control piston end receptacle ( 74.1 ) with the first pressure medium outflow channel ( 61.1 ) is fluid-connected and the second control piston end receptacle ( 74.2 ) with the second pressure medium outflow channel ( 61.2 ) is fluidly connected. Locking cylinder according to claim 3, characterized in that the control piston ( 66 ) in the axial direction ( 67 ) pressure and / or flow controlled by the fluid pressure medium in a first shut-off position ( 78.1 ) is displaceable, in which the control piston ( 66 ) a first flow path from the first inflow channel ( 62.1 ) to the first pressure medium outflow channel ( 61.1 ) with respect to a flow through the fluid pressure medium, while a second flow path from the second inflow channel ( 62.2 ) to the second pressure medium outflow channel ( 61.2 ) is or remains open with respect to a flow of the fluid pressure medium, and that the control piston ( 66 ) in the axial direction ( 67 ) flow-controlled by the fluid pressure medium in a second shut-off position ( 78.2 ) is displaceable, in which the control piston ( 66 ) a second flow path from the second inflow channel ( 62.2 ) to the second pressure medium outflow channel ( 61.2 ) with respect to a flow through the fluid pressure medium, while the first flow path from the first inflow channel ( 62.1 ) to the first pressure medium outflow channel ( 61.1 ) is or remains open with respect to a flow through the fluid pressure medium. Locking cylinder according to claim 3 or 4, characterized in that the control piston receptacle ( 65 ) in an imaginary, perpendicular to the control piston longitudinal axis ( 68 viewed trained cross-sectional plane having an inner cross section, and that the first control piston end receptacle ( 74.1 ) in an imaginary, perpendicular to the control piston longitudinal axis ( 68 Viewed trained first cross-sectional plane, having a first inner cross section, which is greater than the inner cross section of the control piston receptacle ( 65 ), and wherein the second control piston end receptacle ( 74.2 ) in an imaginary, perpendicular to the control piston longitudinal axis ( 68 Viewed formed second cross-sectional plane, having a second inner cross section, which is greater than the inner cross section of the control piston receptacle ( 65 ). Locking cylinder according to claim 5, characterized in that the first control piston end receptacle ( 74.1 ) on one of the control piston receptacle ( 65 ) opposite the first side, in the axial direction ( 67 ) into a third control piston end receptacle ( 74.3 ), in which the first pressure medium outflow channel ( 61.1 ) and in an imaginary, perpendicular to the control piston longitudinal axis ( 68 ) and parallel to the first cross-sectional plane formed third cross-sectional plane, a has third inner cross section, the inner cross section of the control piston receiving ( 65 ), so that the first control piston end ( 70.1 ) of the control piston ( 66 ) into the third control piston end receptacle ( 74.3 ) and then there with little play relative to the third control piston end receptacle ( 74.3 ) in the axial direction ( 67 ) is displaceably mounted and that the second control piston end receptacle ( 74.2 ) on one of the control piston receptacle ( 65 ) opposite the second side, in the axial direction ( 67 ) into a fourth control piston end receptacle ( 74.4 ), in which the second pressure medium outflow channel ( 61.2 ) and in an imaginary, perpendicular to the control piston longitudinal axis ( 68 ) and viewed parallel to the second cross-sectional plane formed fourth cross-sectional plane, having a fourth inner cross-section, the inner cross-section of the control piston receptacle ( 65 ), so that the second control piston end ( 70.2 ) of the control piston ( 66 ) into the fourth control piston end receptacle ( 74.4 ) and then there with little play relative to the fourth control piston end receptacle ( 74.4 ) in the axial direction ( 67 ) is slidably mounted. Locking cylinder according to one of claims 3 to 6, characterized in that along a longitudinal axis ( 69 ) extending control piston receptacle ( 65 ) and the first and second control piston end receptacle ( 74.1 . 74.2 ), preferably also the third and fourth control piston end receptacle ( 74.3 . 74.4 ), or the housing of the flow divider ( 60 ; 60.1 ) or the flow divider ( 60 ; 60.1 ) symmetrical to an imaginary, perpendicular to the longitudinal axis ( 69 ) of the control piston intake ( 65 ) formed symmetry plane ( 79 ) are designed or is. Locking cylinder according to one of the preceding claims, characterized in that the flow divider ( 60 ; 60.1 ) in a cylinder arranged in the cylinder or on the cylinder ( 21 ) attached control block ( 82 ) together with control elements for controlling the locking cylinder ( 20 ) and / or together with control elements for controlling the locking cylinder ( 20 ) is arranged. Locking cylinder according to claim 1, characterized in that it is in the flow divider ( 60 ; 60.2 ) around a gearbox divider ( 60.2 ), the at least one first gear motor or at least one first gear pump ( 80.1 ) for conveying the first part volume flow and at least one second gear motor or at least one second gear pump ( 80.2 ) for conveying the second partial volume flow, which is transmitted via a shaft ( 81 ) are coupled together. Locking cylinder according to one of the preceding claims, characterized in that the first clamping cone body ( 47.1 ) and the second clamping cone body ( 47.2 ) of the first clamping double-cone body ( 45.1 ) are integrally connected and / or made of a part and / or that the third clamping cone body ( 47.3 ) and the fourth clamping cone body ( 47.4 ) of the second clamping double cone body ( 45.2 ) are integrally connected and / or made of one part. Locking cylinder according to one of the preceding claims, characterized in that the first clamping double-cone body ( 45.1 ) at least partially or entirely in one of the second clamping double-cone body ( 45.2 ) limited recess ( 49 ) of a cylinder part of the cylinder ( 21 ), which extends through a radially and transversely to the cylinder longitudinal axis ( 26 ) of the cylinder ( 21 ) extending between the first clamping double-cone body ( 45.1 ) and the piston ( 22 ) ( 51 ) is limited, and wherein the first pressure medium inflow channel ( 54.1 ) on one of the first locking cone surfaces ( 48.1 ) associated first page ( 55.1 ) of the first clamping double-cone body ( 45.1 ) in the recess ( 49 ), and wherein the second pressure medium inflow channel ( 54.2 ) on one of the second locking cone surfaces ( 48.2 ) associated second side ( 55.2 ) of the first clamping double-cone body ( 45.1 ) in the recess ( 49 ), and wherein the recess ( 49 ) by a seal ( 59 ) opposite the second working chamber ( 31.2 ) is sealed. Locking cylinder according to claim 11, characterized in that in a region between the third clamping cone body ( 47.3 ) and the fourth clamping cone body ( 47.4 ) of the second clamping double cone body ( 45.2 ) either a first pressure medium discharge channel for discharging the fluid flowing through the first fluid-axial slide bearing Pressure medium is provided which, in an unlocked position of the first clamping double-cone body, fluidly connected to the first fluid-axial sliding bearing and which opens into the recess and a second pressure medium-discharge channel for discharging the second fluid Axial sliding bearing by flowing fluid pressure medium is provided which, in an unlocked position of the first clamping double-cone body, fluidly connected to the second fluid-axial sliding bearing and opens into the recess or a common pressure medium-discharge channel ( 83 ) for discharging the first and second fluid-axial plain bearings ( 53.1 . 53.2 ) is provided by flowing fluid pressure means which, in an unlocked position ( 92 ) of the first clamping double-cone body ( 45.1 ), with the first and second fluid-axial plain bearings ( 53.1 . 53.2 ) is fluid-connected and into the recess ( 49 ) opens. Locking cylinder according to claim 12, characterized in that the first pressure medium inflow channel ( 54.1 ), when the first clamp double cone body ( 45.1 ) and the second clamping double cone body ( 45.2 ) with each other in the first locking position ( 46.1 ) are locked and clamped self-locking to form the deadlock, with respect to the first or common pressure medium-discharge channel ( 83 ) by means of the abutting first and third locking cone surfaces ( 48.1 . 48.3 ) and which, when the first clamping double-cone body ( 45.1 ) and the second clamping double cone body ( 45.2 ) of each other in one or the unlocked position ( 92 ) are lifted off with the first or common pressure medium discharge channel ( 83 ) via a then between the first and third locking cone surfaces ( 48.1 . 48.3 ) formed first channel ( 84.1 ) is fluidly connected, and that the second pressure medium inflow channel ( 54.2 ), when the first clamp double cone body ( 45.1 ) and the second clamping double cone body ( 45.2 ) with each other in the second locking position ( 46.2 ) are locked and clamped self-locking to form the deadlock, with respect to the first or common pressure medium-discharge channel ( 83 ) by means of the adjoining second and fourth locking cone surfaces ( 48.2 . 48.4 ) and which, when the first clamping double-cone body ( 45.1 ) and the second clamping double cone body ( 45.2 ) of each other in one or the unlocked position ( 92 ) are lifted off, with the second or common pressure medium-discharge channel 83 via a then between the second and fourth locking cone surfaces ( 48.2 . 48.4 ) formed second channel ( 84.2 ) is fluidly connected. Method for operating a pressure-medium-operated, double-acting locking cylinder ( 20 ), in particular according to one of the preceding claims, which extends in the direction of a cylinder longitudinal axis ( 26 ) extending cylinder ( 21 ) and a piston ( 22 ), one of a first working chamber ( 31.1 ) associated first piston side ( 27.1 ) and a second, a second working chamber ( 31.2 ) associated second piston side ( 27.2 ) and which by means of one of the first piston side ( 27.1 ) via one in the first working chamber ( 31.1 ) first working channel ( 29.1 ) and the second piston side ( 27.2 ) via one into the second working chamber ( 31.2 ) second working channel ( 29.2 ) deliverable fluid pressure medium in an axial direction ( 23 ) parallel to the cylinder longitudinal axis ( 26 ) in a second direction ( 28.2 ) and in a first direction ( 28.1 ) opposite to the second direction ( 28.2 ) relative to the cylinder ( 21 ) movable, but non-rotatable with the cylinder ( 21 ), wherein the piston ( 22 ) rotatably with a first threaded body (nut or spindle) ( 35.1 ) whose first thread (female thread or spindle thread) ( 36.1 ) with a second thread (spindle thread or female thread) ( 36.2 ) of a frictional and gravitational self-locking second threaded body (spindle or nut) ( 35.2 ) to form a non-self-locking thread ( 37 ), and wherein the second threaded body ( 35.2 ) about a parallel to the cylinder longitudinal axis ( 26 ) of the cylinder ( 21 ) extending axis of rotation ( 43 ) relative to the cylinder ( 21 ) rotatable and relative to the cylinder ( 21 ) in the axial direction ( 23 ) is axially displaceable, and wherein one with the second threaded body ( 35.2 ) rotatably connected first clamping double-cone body ( 45.1 ) is provided, which has a first locking cone surfaces ( 48.1 ) first clamping cone body ( 47.1 ) and a second locking cone surfaces ( 48.2 ) having second clamping cone body ( 47.2 ), and wherein one with the cylinder ( 21 ) rotatably connected second clamping double-cone body ( 45.2 ) having a third locking cone surface ( 48.3 ) third clamping cone body ( 47.3 ) and a fourth locking cone surfaces ( 48.4 ) fourth clamping cone body ( 47.4 ), and wherein the first locking conical surfaces ( 48.1 ) of the first clamping double-cone body ( 45.1 ) by an axial movement of the second threaded body ( 35.2 ) in the first direction ( 28.1 ) on the third locking conical surfaces ( 48.3 ) of the second clamping double cone body ( 45.2 ) can be applied in such a way that in applied state of the second clamping double-cone body ( 45.2 ) Can absorb axial forces acting in the first direction ( 28.1 ) on the second threaded body ( 35.2 ) and the first locking conical surfaces ( 48.1 ) and the third locking conical surfaces ( 48.3 ) to form a jamming with each other in a first locking position ( 46.1 ), against rotation about the axis of rotation ( 43 ) of the second threaded body ( 35.2 ) as well as against a movement in the axial direction ( 23 ) are clamped away from each other, self-locking, and wherein the second locking conical surfaces ( 48.2 ) of the first clamping double-cone body ( 45.2 ) by an axial movement of the second threaded body ( 35.2 ) in the second direction ( 28.2 ) on the fourth locking conical surfaces ( 48.4 ) of the second clamping double cone body ( 45.2 ) can be applied such that in the applied state of the second clamping double-cone body ( 45.2 ) Can absorb axial forces acting in the second direction ( 28.2 ) on the second threaded body ( 35.2 ) and the second locking conical surfaces ( 48.2 ) and the fourth locking conical surfaces ( 48.4 ) to form a jamming together in a second locking position ( 46.2 ), against rotation about the axis of rotation ( 43 ) of the second threaded body ( 35.2 ) as well as against a movement in the axial direction ( 23 ) away from each other, are self-locking jammed, so that the locking cylinder ( 20 ) both on train in the first locking position ( 46.1 ) as well as pressure in the second locking position ( 46.2 ) is lockable and in the applied state in the respective locking position ( 46.1 . 46.2 ) is locked in such a way that the first clamping double-cone body ( 45.1 ) only by exerting the clamping solving dissolving forces of the second clamping double-cone body ( 45.2 ) in an unlocked position ( 92 ) is convertible, in which the second threaded body ( 35.2 ) about its axis of rotation ( 43 ) relative to the cylinder ( 21 ) is rotatable, and wherein the second threaded body ( 35.2 ) on at least two fluid-axial plain bearings ( 53.1 . 53.2 ), of which a first fluid-axial plain bearing ( 53.1 ) is intended to be in the first direction ( 28.1 ) on the second threaded body ( 35.2 ) to absorb acting axial forces, and of which a second fluid-axial plain bearing ( 53.2 ) is intended to move in the second direction ( 28.2 ) on the second threaded body ( 35.2 ) to receive acting axial forces, and wherein the first fluid-axial sliding bearing ( 53.1 ) via a first pressure medium inflow channel ( 54.1 ) is acted upon with or a fluid pressure medium, and wherein the second fluid-axial bearing ( 53.2 ) via a second pressure medium inflow channel ( 54.2 ) is acted upon by or a fluid pressure medium, and wherein one or the flow divider ( 60 ; 60.1 . 60.2 ) is provided for dividing a main volume flow of the fluid pressure medium in a first part-volume flow and in a second part-volume flow, the one in the first pressure medium inflow channel ( 54.1 ) for the first fluid-axial plain bearing ( 53.1 ) opening first pressure medium outflow channel ( 61.1 ) for the first part volume flow and one in the second pressure medium inflow channel ( 54.2 ) for the second fluid-axial plain bearing ( 53.2 ) opening second pressure medium outflow channel ( 61.2 ) for the second part volume flow, and wherein by means of the flow divider ( 60 ; 60.1 . 60.2 ), at least during a movement of the piston ( 22 ) in the first direction ( 28.1 ) and also during movement of the piston ( 22 ) in the second direction ( 28.2 ) and each thereby caused by rotation of the second threaded body 35.2 around its axis of rotation ( 43 ) together with the first clamping double cone body ( 45.1 ), a main volume flow of the fluid pressure medium in a first part-volume flow and in a second part-volume flow is divided such that a ratio of the by the first pressure medium inflow channel ( 54.1 ) through the first fluid-axial plain bearing ( 53.1 ) inflowing first part-volume flow of the fluid pressure medium and by the second pressure medium inflow channel ( 54.2 ) through the second fluid-axial plain bearing ( 53.2 ) flowing second volume partial flow of the fluid pressure medium remains substantially constant, whereby the first clamping double-cone body ( 45.1 ) by means of both the fluid pressure medium acted upon first fluid-axial sliding bearing ( 53.1 ) as well as by means of the acted upon by the fluid pressure fluid second fluid-axial bearing ( 53.2 ) in a fluid-dynamic floating position ( 63 ) is stored fluidly and / or remains. A method according to claim 14, characterized in that the ratio, at least during a movement of the piston ( 22 ) in both the first direction ( 28.1 ) as well as in the second direction ( 28.2 ), regardless of the in the first pressure medium inflow channel ( 54.1 ) and in the second pressure medium inflow channel ( 54.2 ) acting pressures of the fluid pressure medium remains substantially constant or is held. A method according to claim 14 or 15, characterized in that the ratio is substantially 1: 1. Method according to one of claims 14 to 16, characterized in that the flow divider ( 60 ; 60.1 ) a housing ( 64 ) with a control piston receptacle ( 65 ), in which a control piston ( 66 ) guided with little play relative to the control piston receptacle ( 65 ) in an axial direction ( 67 ) is slidably mounted, and wherein the control piston ( 66 ) axially in the direction of a control piston longitudinal axis ( 68 ), has a control piston length and a first control piston end ( 70.1 ) and one of them in an opposite direction in the axial direction ( 67 ) extending away second control piston end ( 70.2 ), which from the first control piston end ( 70.1 ) has a distance corresponding to the control piston length, and wherein in the housing ( 64 ) a first throttle ( 71.1 ) containing the first inflow channel ( 62.1 ) for a first partial volume flow of the fluid pressure medium and a second throttle ( 71.2 ) containing the second inflow channel ( 62.2 ) are arranged for a second partial volume flow of the fluid pressure medium, and wherein the control piston receptacle ( 65 ) with a first end into a first control piston end receptacle ( 74.1 ) for receiving the first Regulating piston end ( 70.1 ) of the control piston ( 66 ) into which the first inflow channel ( 62.1 ), and wherein the control piston receptacle ( 65 ) with a second end into a second control piston end receptacle ( 74.2 ) for receiving the second control piston end ( 70.2 ) of the control piston ( 66 ) into which the second inflow channel ( 62.2 ), and wherein the first control piston end receptacle ( 74.1 ) a first control throttle or a component of a first control throttle ( 75.1 ) and the second control piston end receptacle ( 74.2 ) a second control throttle or a component of a second control throttle ( 75.2 ), and wherein the first control piston end receptacle ( 74.1 ) with the first pressure medium outflow channel ( 61.1 ) is fluid-connected and the second control piston end receptacle ( 74.2 ) with the second pressure medium outflow channel ( 61.2 ) is fluidly connected, so that the control piston ( 66 ), when a first pressure medium pressure arising in the first pressure medium outflow channel ( 61.1 ), while the first pressure medium outflow channel ( 61.1 ) is flowed through by the first part volume flow of the fluid pressure medium and a second pressure medium pressure, which in the second pressure medium outflow channel ( 61.2 ), while the second pressure medium outflow channel ( 61.2 ) flows through the second part-volume flow of the fluid pressure medium, are the same size, in a basic or middle position ( 72 ) and the control piston ( 66 ), when a first pressure medium pressure, which in the first pressure medium outflow channel ( 61.1 ), while the first pressure medium outflow channel ( 61.1 ) is flowed through by a first partial volume flow of the fluid pressure medium, deviates from a second pressure medium pressure, which in the second pressure medium outflow channel ( 61.2 ), while the second pressure medium outflow channel ( 61.2 ) is flowed through by a second partial volume flow of the fluid pressure medium, so that the first pressure medium pressure and the second pressure medium pressure differ by a pressure difference not equal to zero, simultaneously with the formation of the pressure difference in the direction of the lower pressure medium pressure in the axial direction ( 67 ) into one of the basic or middle position ( 72 ) moved deviating position. A method according to claim 17, characterized in that when the first clamping double cone body ( 45.1 ) with the second clamping double cone body ( 45.2 ) in the first locking position ( 46.1 ) is clamped self-locking and when the fluid pressure medium the first inflow channel ( 62.1 ), the control piston ( 66 ) from its basic or central position ( 72 ) in a second shut-off position ( 78.2 ) or in a second shut-off position ( 78.2 ) is held, in which the second pressure medium outflow channel ( 61.2 ) and the second pressure medium inflow channel ( 54.2 ) with respect to the second inflow channel ( 62.2 ) is blocked off against an inflow of the pressure medium, while a first flow path between a first inflow channel ( 62.1 ) and the first pressure medium outflow channel ( 61.1 ) is open, so that the fluid pressure medium through the first inflow channel ( 62.1 ) in the first pressure medium outflow channel ( 61.1 ) and from there through the first pressure medium inflow channel ( 54.1 ) can either flow to the first clamp double cone body ( 45.1 ) by a continued supply of the fluid pressure medium in an unlocking position ( 92 ) or flows, so that the first clamping double-cone body ( 45.1 ) in an unlocked position ( 92 ), and that when the first clamping double cone body ( 45.1 ) with the second clamping double cone body ( 45.2 ) in the second locking position ( 46.2 ) is clamped self-locking and when the fluid pressure medium the second inflow channel ( 62.2 ), the control piston ( 66 ) from its basic or central position ( 72 ) is moved into a first shut-off position or held in a first shut-off position, in which the first pressure medium outflow channel ( 61.1 ) and the first pressure medium inflow channel ( 54.1 ) is blocked off against an inflow of the pressure medium, while a second flow path between the second inflow channel ( 62.2 ) and the second pressure medium outflow channel ( 61.2 ) is open, so that the fluid pressure medium through the second inflow channel ( 62.2 ) in the second pressure medium outflow channel ( 61.2 ) and from there through the second pressure medium inflow channel 54.2 can either flow to the first clamp double cone body ( 45.1 ) by a continued supply of the fluid pressure medium in an unlocking position ( 92 ) or flows, so that the first clamping double-cone body ( 45.1 ) in an unlocked position ( 92 ) is transferred. Method according to one of claims 14 to 16, characterized in that it is in the flow divider ( 60 ; 60.1 ) around one or the gearbox divider ( 60.1 ), the at least one first part of the volume flow promoting first gear pump ( 80.1 ) and a second part of the volume flow promoting second gear pump ( 80.1 ), which via one or the shaft ( 81 ) are coupled together in such a way that at least during the movement of the piston ( 22 ) in the first direction ( 28.1 ) and also in the second direction ( 28.2 ) and a respective thereby caused rotation of the second threaded body ( 35.2 ) about its axis of rotation ( 43 ) together with the first clamping double cone body ( 45.1 ), said ratio of the first part-volume flow of the fluid pressure medium and the second part-volume flow of the fluid pressure medium remains substantially constant. Method according to one of claims 14 to 19, characterized in that either starting from the first locking position ( 46.1 ), in which the first clamping double-cone body ( 45.1 ) and the second clamping double cone body ( 45.2 ) are clamped self-locking, at least first or only the first fluid-axial plain bearing ( 53.1 ) via the flow divider ( 60 ; 60.1 . 60.2 ) and the fluid-connected first pressure medium inflow channel ( 54.1 ) is acted upon by the fluid pressure medium or starting from the second locking position ( 46.2 ), in which the first clamping double-cone body ( 45.1 ) and the second clamp double cone body 45.2 are clamped self-locking, at least first or only the second fluid-axial plain bearing ( 53.2 ) via the flow divider ( 60 ; 60.1 . 60.2 ) and the fluid-connected thereto second pressure medium inflow channel ( 54.2 ) is applied to the fluid pressure medium, either to a lifting of the first clamping double-cone body ( 45.1 ) of the second clamping double cone body ( 45.2 ) in a lifting and unlocking position ( 92 ) or whereby a lifting of the first clamping double-cone body ( 45.1 ) of the second clamping double cone body ( 45.2 ) in a lifting and unlocking position ( 92 ) in which the first clamping double-cone body ( 45.1 ) and the second clamping double cone body ( 45.2 ) are either at least partially offset from each other so that their locking cone surfaces ( 48.1 . 48.2 ; 48.3 . 48.4 ) are at least partially out of touch, or are completely lifted off of each other, so that their locking cone surfaces ( 48.1 . 48.2 ; 48.3 . 48.4 ) and that only then the pressure medium of the first or second working chamber ( 31.1 . 31.2 ) is supplied either to a movement of the piston ( 22 ) in the axial direction ( 23 ) to enable, assist and / or cause or cause the piston ( 22 ) in the axial direction ( 23 ) is moved.

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