EP3101283B1 - Double acting locking cylinder and method for operating a double acting locking cylinder - Google Patents

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, forming a non-self-locking Thread is engaged with a piston internal thread of the piston. 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.

Drives of this type are also from the document DE 29714664 already known.

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 with regard to the locking cylinder by the features of claim 1, in particular by a fluid-operated, double-acting locking cylinder solved, which comprises a cylinder extending in the direction of a cylinder and a piston which comprises a first working chamber associated with a first piston side and a facing away, a second working chamber associated second piston side and with the aid of one of the first piston side via a in the first Working chamber opening first working channel and the second piston side via an opening into the second working chamber second working channel 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 connected to a first threaded body (nut or spindle) whose first thread (female thread or spindle thread) with a second thread (spindle thread or female thread) of a r eibschlüssig, ie frictionally by friction, and, preferably exclusively, due to gravity, in particular by a load acting on the piston, automatically or automatically, preferably without drive, in particular without the action or support of energy stores, such as springs, lockable second threaded body (spindle or nut ) is engaged to form a non-self-locking thread, 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 rotatable and relative to the cylinder in the axial direction or parallel to the axis of rotation, preferably only slightly , is axially displaceable, and wherein a rotationally fixed to the second threaded body, preferably rigid, connected or rotationally fixed to the second threaded body, preferably rigidly mounted, self-locking, a first clamping double-cone body is provided, which has a first locking cone surfaces, self-locking, first clamping cone body and a second locking cone 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 is provided, the third locking cone surfaces having, self-locking, third terminal And having a fourth locking cone surfaces, 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 of the third locking cone surfaces of the second clamping double-cone body can be applied such that in the applied state of the second e 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, against rotation about the Rotation axis 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 of the fourth locking cone surfaces of the second clamping double-cone body can be applied such that in the applied state, the second clamping double-cone body can absorb axial forces 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 by static friction, are clamped, so that the locking cylinder can be locked 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 the exercise of the clamping solving dissolving forces of the second clamping double-cone body can be converted into an unlocked position, in which the second threaded body is rotatable about its axis of rotation relative to the cylinder, and wherein the second threaded body at least Said two fluid-axial plain bearings is mounted, 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 second bearing surface of a rotationally fixed, in particular rigidly connected to the cylinder or at the cylinder attached to the second bearing body, preferably in the form of a radially and transversely, in particular perpendicularly, to the cylinder longitudinal axis of the cylinder extending, preferably arranged between the first clamping double-cone body and the piston, in particular annular, approach, limited and - to is determined 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 a third bearing surface opposite the 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 take in the second direction acting on the second threaded body axial forces, and wherein the first fluid Axial sliding bearing via a first pressure medium inflow channel with the or a fluid pressure medium is acted upon, and wherein the second fluid-axial slide bearing is acted upon via a second pressure medium inflow channel with or a fluid pressure medium, and one as a volume flow divider or Flow divider signable, a pressure medium main inflow more comprehensive, single-acting or acting only in a flow direction flow divider vorgese vorgese for dividing a pressure medium main inflow channel supplied main volumetric flow of the fluid pressure medium in a first part-volume flow and in a second partial flow hen is the one in the first pressure medium inflow channel for the first fluid-axial slide bearing opening first pressure medium outflow channel for the first part volume flow and in the second pressure medium inflow channel for the second fluid-axial slide bearing second Druckmittel- Outflow channel for the second part volume flow includes. 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 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 to maintain 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, 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 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 regulating-piston end and a second regulating-piston end extending therefrom in an opposite direction in the axial direction, which has a distance corresponding to the regulating-piston length from the first regulating-piston end, and wherein one in the housing, preferably as a Fixed throttle-shaped, 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 arranged for a second partial volume flow of the fluid pressure medium, preferably, at least as regards the 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 a first receiving end and a thereof in has an opposite direction in the axial direction away extending second receiving end, 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 into the 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, into which the second inflow channel opens, and wherein 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 receiving fluidly connected to the first pressure medium outflow channel and the second control piston end receptacle is fluidly connected to the second pressure medium outflow channel. This makes it possible to achieve a particularly simple and also for a long time reliable, robust solution for the first double cone body in to transfer a fluid-dynamic floating position, in which both a trouble-free, in particular locking or jamming, retraction of the piston as well as a trouble-free, in particular locking or jamming, extending the piston is possible and / or the first double-cone body both always during the retraction of the piston and during the extension of the piston in a fluid-dynamic floating position or in a hydrodynamic floating state, 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 through the fluid pressure medium substantially or completely shuts off, while a second flow path from the second inflow channel to the second pressure medium outflow channel with respect to a flow through the fluid pressure medium is open or remains, and that the control piston in the axial direction flow controlled by the fluid pressure medium into a second shut-off position is displaceable, in which the control piston a second flow path from the second inflow channel to the second pressure medium outflow channel with respect Passage of the fluid pressure medium substantially or completely shuts off, while the first flow path from the first inflow channel to the first pressure medium outflow channel with respect to a flow through the fluid pressure medium is open or remains. 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, it can be provided that the control piston receptacle, when viewed in an imaginary cross-sectional plane formed perpendicular to the control piston longitudinal axis, has an internal cross-section, and that the first control piston end receptacle is in an imaginary first axis perpendicular to the control piston longitudinal axis Viewed 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 in an imaginary, formed perpendicular to the control piston longitudinal axis second cross-sectional plane, a second inner cross-section has, 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 which has 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 partial volume flow, which are coupled to each other 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, in viewed in the first direction, tapering 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 Tapered surfaces, viewed in the second direction, taper radially towards the axis of rotation 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 cones locking body and the third locking cone surfaces of the first clamping double-cone locking body.

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 for discharging the the first fluid-axial bearing fluid flowing through 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 preferably to the first and third locking cone Adjacent surfaces, 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 adjacent to the second and fourth locking conical surfaces, and which opens into the recess, or a, preferably annular, common pressure medium-discharge channel for discharging the fluid pressure medium flowing through the first and the second fluid-axial sliding bearing is provided which, in an unlocking position Position of the first clamping double-cone body, is fluidly connected to the first and the second fluid-axial sliding bearing, preferably and 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 clamped self-locking to form the deadlock, is shut off from the first or common pressure fluid discharge channel by means of abutting first and third locking cone surfaces and then when the first clamping double Kegel body and the second clamping double-cone body are lifted from one another in one or the unlocked position, with the first or common pressure fluid discharge channel via a then between the first and third locking cone surfaces formed, preferably annular, first channel is fluidly connected, and that the second pressure medium inflow channel, when the first clamping double-cone body and the second clamping double-cone body locked together in the second locking position and are clamped self-locking to form the deadlock, opposite the first or common pressure medium discharge channel v is closed off by means of the adjoining second and fourth locking cone surfaces and which, when the first clamping double-cone body and the second clamping double-cone body are lifted from one another in one or the unlocked position, with the second or common pressure medium discharge channel via a then formed between the second and fourth locking cone surfaces, preferably annular, second channel fluidly connected. Through these measures, a further improvement in terms of the above advantages can be achieved.

The invention task is solved in terms of the method by a method for operating, controlling and / or regulating a pressure-medium-operated, double-acting, in particular inventive, locking cylinder, the comprises a cylinder extending in the direction of a cylinder longitudinal axis and a piston which comprises a first piston side associated with a first working chamber and a second piston side thereof facing away from a second working chamber and which by means of one of the first piston side via a first opening into the first working chamber Working channel and the second piston side via an opening into the second working chamber second working channel 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 rotationally fixed is connected to the cylinder, wherein the piston rotatably connected to a first threaded body (nut or spindle), the first thread (nut thread or spindle thread) with a second thread (spindle thread or female thread) of a frictionally engaged , ie frictionally by friction, and, preferably exclusively, due to gravity, in particular by a load acting on the piston, automatically, preferably without drive, in particular without the action or support of force accumulators, such as springs, lockable second threaded body (spindle or nut ) is engaged to form a non-self-locking thread, 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 rotatable and relative to the cylinder in the axial direction or parallel to the axis of rotation, preferably only slightly , is axially displaceable, and wherein a rotationally fixed to the second threaded body, preferably rigid, connected or rotationally fixed to the second threaded body, preferably rigidly mounted, self-locking, a first clamping double-cone body is provided, which has a first locking cone surfaces, self-locking, first clamping cone body and a second locking cone 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 is provided, the third locking cone surfaces having, self-locking, third terminal Tapered 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 cone Double cone body with its, preferably the first locking cone surfaces opposite, third locking cone surfaces, in the first direction viewed 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 his, preferably the second locking Opposite, fourth locking cone surfaces, viewed in the second direction, taper radially towards the axis of rotation of the second threaded body, and wherein the first locking conical surfaces of the first clamping double-conical 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 state, the second clamping double-cone body can absorb axial forces in the first direction to the second Thread body 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 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 stuck by static friction, 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 to 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 receive 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, against rotation about the axis of rotation of the second G ewindekörpers and against movement in the axial direction away from each other, self-locking, so frictionally by static friction, are clamped, so that the locking cylinder can be locked both train in the first locking position and pressure in the second locking position and in the applied state in the respective Locking position is locked such that the first clamping double-cone body can be converted only under exercise of the clamping solving release forces of the second clamping double-cone body in an unlocked position in which the second threaded body about its axis of rotation relative to the Cylinder is rotatable, 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 one of the first Bearing surface opposite second bearing surface of a non-rotatably, in particular rigid, connected to the cylinder or attached to the cylinder second bearing body, preferably in the form of a radially and transversely, in particular perpendicular, extending to the cylinder longitudinal axis of the cylinder, preferably between the first clamping double Cone body and the piston arranged, 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 a 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 bottom of the cylinder, limited, and, destined, in the second direction to the second Gewind Take ekörper acting 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 slide bearing via a second pressure medium inflow channel with or a fluid pressure medium can be acted upon, and wherein one or as a volume flow divider or flow divider denzeichenbare / r, a pressure medium main inflow comprehensive, single-acting or acting only in a flow direction flow divider for dividing the pressure medium main inflow channel supplied main volumetric flow of the fluid pressure medium is provided in a first part-volume flow and in a second part-volume flow, the one opening into the first pressure medium inflow channel for the first fluid-axial slide bearing first pressure medium outflow channel for the first part volume flow and a second pressure medium outflow channel for the second part volume flow which opens into the second pressure medium inflow channel for the second fluid axial plain bearing, and wherein, with the aid of the flow divider, at least during a movement, in particular extension, the piston in the first direction and also during a moving, in particular retraction, of the piston 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, 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 inflow through the first pressure medium inflow through the first fluid-axial sliding bearing first part-volume flow of the fluid pressure medium and by the second Pressure medium inflow through the second fluid-axial sliding layer r flowing second volume partial flow of the fluid pressure medium, preferably always, remains substantially constant or is held, whereby the first clamping double-cone body both by means of the acted upon by the fluid pressure fluid first fluid-axial sliding bearing and by means of the is acted upon by the fluid pressure fluid second fluid-axial slide bearing, preferably independent of a size of a load acting on the piston and a system pressure required thereby is fluid-stored in a fluid-dynamic floating position or in a fluid-dynamic floating state and / or remains or is held.

According to a very particularly preferred embodiment, it can be provided that the said ratio, at least during a movement of the piston both in the the first direction as well as in the second direction, regardless of the in the first pressure medium inflow and in the second pressure medium inflow channel acting or adjusting pressures or counterpressures of the fluid pressure medium, preferably always, remains substantially 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 a housing with a, preferably a circular cylindrical inner circumference having, control piston receptacle, in which a, also referred to as a pressure compensator and / or slide, preferably a circular cylindrical outer circumference, having control piston with, preferably very little play, in particular in or with a clearance fit, out 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 a thereof away in an opposite direction in the axial direction extending 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 first inflow channel for a first part-volume flow of the fluid pressure means u nd a, preferably designed as a fixed throttle, second throttle second inflow channel for a second part-volume flow of the fluid pressure medium are arranged, preferably, at least in terms of throttle cross-section and the throttle length is the same or identical designed as the first throttle, preferably the control piston receptacle having an axial length which is smaller than an axial length of the control piston, and wherein the control piston receptacle merges with a first end in a first control piston end receptacle for receiving a first control piston end of the control piston, in which the first inflow channel opens, and wherein the control piston receptacle merges with a second end into a second control piston end receptacle for receiving a second control piston end of the control piston, into which the second inflow channel opens, and wherein the first control piston end receptacle 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 receptacle is fluidly connected to the first pressure medium discharge channel and the second control piston end receptacle is fluidly connected to the second pressure medium outflow channel so that the control piston, when a first pressure medium pressure is formed in the first pressure medium outflow channel, during the first pressure medium outflow channel with the first part Volumetric flow of the fluid pressure medium is flowed through and a second pressure medium pressure, which is formed in the second pressure medium outflow channel, while the second pressure medium outflow channel is flowed through with the second partial volume flow of the fluid pressure medium, are equal in size, in a basic or center position and the control piston, if a first he pressure fluid pressure, which is formed in the first pressure medium discharge channel, while the first pressure medium discharge channel is flowed through with a first partial volume flow of the fluid pressure medium, deviates from a second pressure medium pressure, which forms in the second pressure medium outflow channel , While the second pressure medium discharge passage is flowed through by a second partial flow rate 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 Direction of the lower pressure medium pressure in the axial direction moves to a different from the basic or center position and dependent on the pressure difference forming control position. This can be achieved to a particular degree that said ratio of the first partial volume flow of the fluid pressure medium and 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 middle 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 is shut off against the second inflow channel 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 the first clamping double cone Body through a f ortetzten supply of the fluid pressure medium into an unlocking 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 with the second clamping double cone -Body in the second locking position is clamped self-locking and when the fluid pressure medium is supplied to the second inflow, the control piston is moved from its basic or middle position in a first shut-off position or held in a first shut-off, in which the first pressure fluid outflow channel and that's why the first pressure medium inflow channel is shut off against an inflow of the pressure medium, while a second flow path between a second inflow channel and the second pressure medium outflow channel is open, so that the fluid pressure medium through the second inflow channel into the second pressure medium outflow channel and from there through the second pressure medium inflow channel can flow either 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. 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 includes, which are coupled to each other via one or the shaft such that at least during movement of the piston in the first direction and also 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, 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 is supplied, either to a movement of the To enable, support and / or cause 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.

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.

Fig. 1

einen erfindungsgemäßen Verriegelungszylinder in einem Längsquerschnitt mit einer integrierten Steuereinheit in einer schematischen Darstellung, zur Veranschaulichung einer Fahrstellung "Ausfahren", sowohl bei drückender Last als auch bei ziehender Last;

Fig. 2

den Verriegelungszylinder in einer Darstellung gemäß Figur 1 zur Veranschaulichung einer Fahrstellung "Einfahren", sowohl bei drückender Last als auch bei ziehender Last;

Fig. 3

den Verriegelungszylinder gemäß Figur 1 im Stillstand und verriegelten Zustand bei ziehender Last;

Fig. 4

den Verriegelungszylinder gemäß Figur 1 im Stillstand und verriegelten Zustand bei drückender Last;

Fig. 5

einen Querschnitt eines in der Steuereinheit des Verriegelungszylinders integrierten Mengenteilers gemäß einem ersten Ausführungsbeispiel, mit einem integrierten, eine Druckwaage ausbildenden Regelkolben;

Fig. 6

eine schematische Darstellung eines zweiten Ausführungsbeispiels eines Mengenteilers, bei dem es sich um einen Zahnradmengenteiler mit zwei über eine Welle miteinander gekoppelten Zahnradpumpen handelt.

Show it:

Fig. 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;

Fig. 2

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

Fig. 3

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

Fig. 4

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

Fig. 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;

Fig. 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 lock cylinder 20 includes a cylinder 21 and a piston 22. The lock cylinder 20 may also be referred to as a lock cylinder-piston unit. The piston 22 is displaceable in the cylinder 21 in an axial direction 23, but rotatably mounted to the cylinder 21. The piston 22 is sealed against a cylinder jacket inner wall 24 of the cylinder 21 by a ring seal 25. The piston 22 is on its in the direction of the cylinder longitudinal axis 26 of the cylinder 21 facing away from each other sides 27.1, 27.2 by a fluid, in particular hydraulic, pressure medium, preferably oil, acted upon to a pressure fluid 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 allow. The locking cylinder 20 is a fluid-operated, double-acting Locking cylinder, which can be locked both on train and on pressure. The fluid pressure medium can be supplied via a first working channel 29.1 on the side facing away from a cylinder bottom 30 of the cylinder 21 first side 27.1 of the piston 22 in a first working chamber 31.1 to a movement of the piston 22 along the cylinder 21 and parallel to the cylinder longitudinal axis 26 to reach in the second direction 28.2. In addition, the fluid pressure medium via a second working channel 29.2 on the second side 27.2 of the piston 22, which faces away from the first side 27.1 and toward the cylinder bottom 30, are fed into a second working chamber 31.2 to a movement of the piston 22 along the Cylinder 21 and parallel to the cylinder longitudinal axis 26 in the first direction 28.1 reach.

The first working chamber 31. 1 is sealed off from the second working chamber 31. 2 via the annular seal 25 of the piston 22. The ring seal 25 is supported in an annular groove 33 of the piston 22 which is open towards the outside of the cylinder jacket inner wall 24. The piston 22 is designed with a tubular hollow body, which is also designated with piston rod 34. The piston 22 forms an annular projection which is non-rotatably connected to the piston rod 34. The piston rod 34 extends from the first side 27.1 of the piston 22 in the axial direction 23 coaxially or parallel to the cylinder longitudinal axis 26 of the cylinder 21. The piston 22 is formed integrally with a designated also with first threaded body nut 35.1. The nut 35.1 has a designated as the first thread and designed as an internal thread nut thread 36.1. The nut thread 36.1 forms in the illustrated embodiment, 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 also 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. Preferably, the non-self-locking thread 37 is 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 as a, in particular multi-start, coarse thread, preferably trapezoidal coarse thread designed. Preferably, an eight-speed coarse thread can be used.

The cylinder 21 is closed on one side 38. 1, which is assigned to the end of the spindle 35. 2 facing away from the piston 22, by a cover 39 enclosing the piston rod 34. This can, as shown in the figures, integrally connected to the cylinder 21 and be prepared. However, it can also be connected in several parts with the cylinder. The ring-shaped cover 39 has an open towards the piston rod 34 annular groove 40. In this annular groove 40, a ring seal 41 is supported, which seals the first working chamber 31.1 to the outside. On its other side 38.2 of the cylinder 21 is closed by a cylinder bottom 30 forming the lid or head. This can preferably be connected in several parts with the cylinder 21.

The spindle 35.2 is rotatable relative to the cylinder 21 about a rotation axis 43 arranged parallel to the cylinder longitudinal axis 26 of the cylinder 21. The spindle 35.2 is relative to the cylinder 21 in the axial direction 23 and parallel to the cylinder longitudinal axis 26 of the cylinder 21 axially displaceable, and only slightly. In the exemplary embodiment shown, the axial displaceability of the spindle 35.2 marked with the double arrow 44 or the axial spindle clearance is only about 1.5 to 2.5 mm. The spindle 35.2 is solely due to gravity, in particular by a force acting on the piston rod 34 and the piston 22 load F, automatically or automatically, drive-free and without the action or support of force accumulators, such as tension or compression springs, against rotation around its axis of rotation 43 relative to the cylinder 21 and against movement or displacement in the axial direction 23, both in the first direction 28.1 and in the second direction 28.2, self-locking, so frictionally by static friction, clamped and locked in this way. It is thus not only a frictional self-locking locking of the spindle 35.2 with respect to a rotation about its axis of rotation 43 relative to the cylinder 21 realized, 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, a first clamping double-cone body 45.1 and second clamping double-cone body 45.2 are provided, which acts as a counter-clamping double-cone body with respect to the first clamping double-cone body 45.1 , The first clamping double-cone body 45.1 is rotatably mounted on the spindle 35.2 and the second clamping double-cone body 45.2 is rotatably attached to the cylinder 21. The first clamp double cone body 45.1 and the second clamp double cone body 45.2 are designed to be coordinated with each other so 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 (see FIG. 3 ) and in a second locking position 46.2 (see FIG. 4 ) can be clamped, so that in the self-locking jammed condition, both in the first locking position 46.1 and in the second locking position 46.2, the first clamping double-cone body 45.1 and thus the spindle 35.2 relative to the second clamping double cone Body 45.2 and thus to the cylinder 21, in particular against rotation of the first clamping double-cone body 45.1 about the rotation axis 43 relative to the second clamping double-cone body 45.2 and also against movement or displacement in the axial direction 23 is locked such that the first clamping double-cone body 45.1 and thus the spindle 35.2 only under exercise of the clamping solving release forces of the second clamping double-cone body 45.2 and thus of the cylinder 21 in an unlocking position 92nd (see. FIGS. 1 and 2 ) is convertible, in which the spindle 35.2, together with the first clamping double-cone body 45.1 attached thereto about the rotational axis 43 relative to the cylinder 21, preferably freely rotatable.

The first clamping double cone body 45.1 comprises a first locking cone surfaces 48.1 having frustoconical shaped, self-locking, first clamping cone body 47.1 and a second locking cone surfaces 48.2 having frusto-conically shaped, self-locking, second Clamp cone body 47.2. The first clamping 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 designed rotationally symmetrical to the rotational axis 43 of the spindle 35.2 or to the cylinder longitudinal axis 26 of the cylinder 21.

The second clamping double-cone body 45.2 comprises a third locking cone surfaces 48.3 having, self-locking, third clamping cone body 47.3 and a fourth locking cone surfaces 48.4, 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 rotational axis 43 of the spindle 35.2 designed. Preferably, a recess or chamber 49 accommodating the first clamping double-conical body 45.1 is designed to be rotationally symmetrical with respect to the cylinder longitudinal axis 26 of the cylinder 21 or to the axis of rotation 43 of the spindle 35.2. A recess or chamber 49, in which the first clamping double-cone body 45.1 is slidably received or arranged in the axial direction 23, on the one hand by a cylinder bottom portion 50 of the cylinder bottom 30 of the cylinder 21 and on the other hand limited by an annular projection 51 , The chamber or recess 49 has, viewed in a cylinder longitudinal axis 26 containing cross section, a T-shaped cross-section.

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

The first locking-cone surfaces 48.1 of the spindle 35.2 rotatably connected to the first clamping double-cone body 45.1 and the third locking-cone surfaces 48.2, 48.4 of the cylinder bottom side, second clamping double-cone body 45.2 close with the Rotation axis 43 of the spindle 35.2 or with the cylinder longitudinal axis 26 of the cylinder 21, a first inclination angle 52.1 a ( Fig. 3 ). The second locking-cone surfaces 48.2 of the first clamping 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 axis of rotation 43 of the spindle 35.2 or with the cylinder longitudinal axis 26 of the cylinder 21 a second inclination angle 52.2 a ( Fig. 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 clamping double-cone body 45.2 achieve a self-locking in such a way that the first clamping double-cone body 45.1 and the second clamping 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 rotational axis 43 of the spindle 35.2 rotatable are as well as no longer movable relative to each other in the axial direction 23 or displaced, so not away from each other in one direction. Because it enters a self-locking by a jamming of the two clamping double-cone body 45.1, 45.2 with each other, in which they are frictionally clamped together by static friction.

The first locking conical surfaces 48.1 of the first clamping double-conical body 45.1 are such by an axial movement of the spindle 35.2 in the first direction 28.1 to the third locking conical surfaces 48.4 of the second clamping double-conical body 45.2 of the cylinder 21 can be applied, 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 spindle 35.2. Further, the second locking conical surfaces 48.2 of the first clamping double-conical body 45.1 by an axial movement of the spindle 35.2 in the second direction 28.2 on the fourth locking conical surfaces 48.4 of the second clamping double-conical body 45.2 of the cylinder 21st be applied so 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 spindle 35.2.

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

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

The first pressure-medium inflow channel 54.1 opens into the chamber 49 on a first side 55.1 of the first clamping double-conical body 45.1 assigned to the first interlocking conical surfaces 48.1 of the first clamping double conical body 45.1. The inflow channel 54.2 opens into the chamber 49 on a second side 55.2 of the first clamping double-conical body 45.1 assigned to the second locking-cone surfaces 48.2 of the first clamping double-conical body 45.1.

The first clamping double-conical body 45.1 is rotatably attached to a non-threaded second spindle part 56.2 of the spindle 35.2, which in turn is non-rotatably mounted on a spindle thread 36.2 having the first spindle part 56.1 of the spindle 35.2. Preferably, the first Spindle part 56.1 and the second spindle part 56.2 of the spindle 35.2 integrally connected or made of one piece. The second spindle part 56.2 of the spindle 35.2, which is not provided with a spindle thread, is received in a bore 57 of the annular projection 51 extending radially inwards and transversely to the cylinder longitudinal axis 23 of the cylinder 21. The lug 51 has an open to the unthreaded second spindle part 56.1 of the spindle 35.2 annular groove 58, on the wall, a ring seal 59 is supported. About the ring seal 59 is the first clamping double-cone body 45.1 receiving recess or chamber 49 sealed relative to the second working chamber 31.2.

The first pressure-medium inflow channel 54.1 which opens into the chamber 49 is fluid-connected to a first pressure-medium outflow channel 61.1 of a flow divider 60, 60.1, 60.2 and the second pressure-medium inflow channel 54.2, which likewise opens into the chamber 49, is connected to 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 comprises a pressure medium main inflow channel 62, which branches into a first inflow channel 62.1 and a second inflow channel 62.2. The flow divider 60; 60.1, 60.2 is used to divide a main volume flow of the fluid pressure medium which can be supplied to the pressure medium main inflow channel 62 into a first partial volume flow of the fluid pressure medium into one of the first pressure medium outflow channel 61.1 and thus to the first pressure medium inflow channel 54.1 and into one second one Pressure medium discharge 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 in the pressure medium main inflow channel 62 of the flow divider 60; 60.1, 60.2, it is possible to transfer the first clamping double-cone body 45.1 in the chamber 49 into a fluid-dynamic floating position 63 (see FIG FIGS. 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 during movement of the piston 22 in both the first direction 28.1 and in the second direction 28.2 always in one or the fluid-dynamic floating position 63 or in a Keep fluid-dynamic floating state, regardless of the size of the load F and thereby required system pressure.

According to a in FIG. 5 illustrated, preferred, first embodiment of the flow divider 60; 60.1 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 comprises a housing 64 having a circular-cylindrical inner circumference having a circular cylindrical control piston receptacle 65 for a relative to this displaceable control piston 66, which is also denoted by pressure compensator and / or slide. In the control piston receptacle 65 is the circular cylindrical outer circumference having a circular or cylindrical Regulating piston 66 with very little clearance, in or with a clearance fit, guided relative to the control piston receptacle 65 slidably mounted in an axial direction 67. Preferably, the control piston 66 is in the control piston receptacle 65 of the housing 64 of the flow divider 60; 60.1. 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 piston end 70.1 and a second control piston end 70.1 extending away therefrom in an opposite direction in the axial direction 67. The second control piston end 70.2 has a distance corresponding to the control piston length from the first control piston end 70.1. The first inflow channel 62.1 comprises a first fixed throttle 71.1. The second inflow channel 62.2 comprises a second fixed throttle 71.2. The first fixed throttle 71.1 and the second fixed throttle 71.2 are designed identically at least with regard to the throttle cross section and the throttle length. The control piston receptacle 65 has a first receiving end 73.1 and a second receiving end 73.2 extending therefrom in an opposite direction in the axial direction 67. The control piston receptacle 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 control piston ends 70.1, 70.2 can be on both sides on the control piston receptacle 65 addition. When the control piston ends 70.1, 70.2 of the control piston 66 with a respective equal part length on the facing away from each other receiving ends 73.1, 73.2 of the control piston receptacle 65 and on the perpendicular to the longitudinal axis 69 of the control piston receptacle 65 formed imaginary plane of symmetry 79 also extend, is the control piston 66 in the in FIG. 5 72 shown. The control piston receptacle 65 is at its first receiving end 73.1, viewed in a first axial direction 67.1, in a circular cylindrical inner cross-section having or circular cylindrical 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 opens. The control piston receptacle 65 is at its second receiving end 73.2, viewed in a second axial direction 67.2, in a circular cylindrical internal cross-section or circular cylindrical second control piston end receptacle 74.2 for receiving the second control piston end 70.2 of the control piston 66, in which the second inflow channel 62.2 opens. The first regulating-piston end receptacle 74.1 forms part of a first regulating throttle 75.1 and the second regulating-piston end receptacle 74.2 forms a component of a second regulating throttle 75.2. The first control piston end receptacle 74.1 is fluidly connected to a first pressure medium outflow channel 61.1 of the flow divider 60, and the second control piston end receptacle 74.2 is fluidically connected to a second pressure medium outflow channel 61.2 of the flow divider 60. The control piston receptacle 65 has, viewed in an imaginary, perpendicular to the control piston longitudinal axis 68 formed cross-sectional plane, an inner cross-section. The first control piston end receptacle 74.1, viewed in an imaginary, perpendicular to the control piston longitudinal axis 68 formed first cross-sectional plane, a first inner cross-section which is greater than the inner cross-section of the control piston receptacle 65. The second control piston end receptacle 74.2 has an imaginary Viewed perpendicular to the control piston longitudinal axis 68 formed second cross-sectional plane, a second inner cross section, which is also larger than the inner cross section the control piston receptacle 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 regulating-piston end receptacle 74.1, on a first side opposite the control piston receptacle 65, viewed in the first axial direction 67.1, passes into a circular-cylindrical inner circumference or circular-cylindrical, third regulating-piston end receptacle 74.3, into which the first pressure medium Outflow 61.1 opens. The third control piston end receptacle 74.3 has, viewed 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 third inner cross section corresponding to the inner cross section of the control piston receptacle 65, so that the first control piston end 70.1 of the control piston 66 in the third control piston end receptacle 74.3 convertible and then there with very little play, preferably with a same game as in the control piston receptacle 65, in or with a clearance, relative to the third control piston end receptacle 74.3 in the Axial direction 67 is slidably mounted. The second regulating-piston end receptacle 74.2, on a second side opposite the control piston receptacle 65, viewed in the second axial direction 67.2, passes into a circular-cylindrical inner circumference or circular-cylindrical, fourth regulating-piston end receptacle 74.4, into which the second pressure medium Outflow 61.2 opens. The fourth control piston end receptacle 74.4 has, viewed in an imaginary, perpendicular to the control piston longitudinal axis 68 and parallel to the second cross-sectional plane formed fourth cross-sectional plane, a fourth inner cross section, which corresponds to the inner cross section of the control piston receptacle 65, so that the second control piston end 70.2 of the control piston 66 in the fourth control piston end receptacle 74.4 transferred and then there with very little play, preferably with a same game as in the control piston receptacle 65, in or with a clearance, relative to the fourth control piston end Receptacle 74.4 is slidably mounted in the axial direction 67. The third and fourth regulating-piston end receptacles 74.3, 74.4 are each provided with an annular end wall 77.1, 77.2 of the housing 64 of the flow divider 60 extending radially inwards or to the longitudinal axis 69 of the control piston receptacle 65; 60.1 limited. The first end wall forms a first stop 77.1 for the first regulating-piston end 70.1 of the regulating piston 66. The second end wall forms a second stop 77.2 for the second control piston end 70.2 of the control piston 66.

The control piston 66 is pressure-controlled or flow-controlled by the fluid pressure medium in the first axial direction 67.1 displaceable in a first shut-off position in which it abuts with its first control piston end 70.1 on the first stop 77.1 and in which the control piston 66 a first flow path of the first inflow channel 62.1 to the first pressure medium outflow channel 61.1 shuts off 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. Further, the control piston 66 is flow-controlled by the fluid pressure medium in the second axial direction 67.2 displaceable in a second shut-off position in which it abuts with its second control piston end 70.2 on the second stop 77.2 and 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 62.2 to the first pressure medium outflow channel 61.1 is open or remains with respect to a flow through the fluid pressure medium.

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

The most important component of this flow divider 60; 60.1 is also referred to as a pressure compensator or acting as a pressure balance control piston 66. The control piston 66 is in the axial direction 67 and in the longitudinal direction relative to a housing 64 of the flow divider 60; 60.1 displaceable up to the respective stop 77.1, 77.2. In the divided inflow line (first and second inflow channel 62.1, 62.2) of the flow divider 60; 60.1 is in each case a throttle 71.1, 71.2 with preferably exactly the same throttle cross-section (throttle bore and throttle length). The movable control piston 66 or slide 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 to the bore of the control piston receptacle 65 each exactly aligned bore (third and fourth control piston end receptacle 74.3, 74.4) of the same fit and causes there throttling or even a blockage of this channel. The interaction of this 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, in the case of a hydraulic pressure medium, the hydrodynamic law is applicable. Through these two throttles 71.1, 71.2 flows only the same pressure medium flow in a time unit when the pressure difference or the pressure difference before and after both throttles 71.1, 71.2 is exactly the same. A tie of this pressure gradient is caused by the two throttles 71.1, 71.2 downstream, axially displaceable, control piston 66 (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 slide its position relative to the housing 64 of the flow divider 60; 60.1 changes accordingly. Viewed in the flow direction in front of the two throttles 71.1, 71.2 eh equal pressure anyway, because there the pressure chamber is the same. The following example can clarify the function of the control piston 66 as a pressure compensator: If no fluid pressure fluid can flow out through a tight fit of the first clamping double-conical body 45.1 on the relevant outflow side, the pressure compensator or the control piston 66 closes on the latter due to the pressure accumulation 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 clamping double-cone body 45.1 in the cylinder 21 solves or has solved. The flow divider 60; 60.1 Thus, it has the property of always dividing the pressure fluid 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 is always substantially at the same value ("balanced"). 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 notable as a security cylinder locking cylinder 20 and the piston rod 34 (underneath the load) only undisturbed and can retract when the rotating together with the spindle 35.2 about its axis of rotation 43 first clamping double cone -Body 45.1 during the extension and retraction in a kind of forced floating 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 FIG. 6 schematically illustrated an alternative embodiment of a flow divider 60, which is a gearbox divider 60.2. This gearbox divider 60; 60.2 comprises a first gear motor or 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 conveying the second part volume flow. The first gear pump 80.1 and the second gear pump 80.2 are forcibly coupled together via a shaft 81. Also with this gearbox divider 60; 60.2, a ratio of the two partial volume flows can be kept essentially constant at approximately 1: 1.

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

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 the second fluid-axial sliding bearing 53.1 53.2 pressurizing fluid pressure medium provided. The pressure medium discharge channel 83 adjoins the first, second, third and fourth locking conical surfaces 48.1, 48.2, 48.3, 48.4 and opens into the chamber 49. The pressure medium discharge channel 83 is when the first clamping double-cone body 45.1 is in its fluid-dynamic floating position 63, with the first and the second fluid-axial slide bearings 52.1, 53.2 both via a then between the first and third locking-cone surfaces 48.1, 48.3 trained, annular, first channel 84.1 fluidly connected and via a then between the second and fourth locking-cone surfaces 48.2, 48.4 formed, annular, second channel 84.2 fluidly connected.

If the first clamping double-cone body 45.1 and the second clamping double-cone body 45.2 locked together in the first locking position 46.1 to form the deadlock self-locking, is the first pressure medium inflow channel 54.1 opposite the pressure medium discharge channel 83 by means of the then abutting each other first and third locking cone surfaces 48.1, 48.3 shut off. If, starting from this, the first clamping double cone body 45.1 and the second clamping double cone body 45.2 are lifted apart from one another in an unlocking position 92, then the first pressure medium inflow channel 54.1 is connected to the pressure medium discharge channel 83 via the then between the first and third locking cone surfaces formed, annular, first channel 84.1 fluidly connected.

If the first clamping double-conical body 45.1 and the second clamping double-conical body 45.2 are locked together in the second locking position 46.2 self-locking jamming to form the deadlock, second pressure medium inflow 54.2 opposite to the pressure medium-discharge channel 83 locked by means of the abutting second and fourth locking cone surfaces 48.2, 48.4. If, starting from this, the first clamping double-cone body 45.1 and the second clamping double-cone body 45.2 are lifted apart from one another in an unlocking position 92, then the second pressure-medium inflow channel 54.2 is in communication with the pressure-medium discharge channel 83 between the second and fourth locking-cone surfaces 48.2, 48.4 formed, annular, second channel 84.2 fluidly connected.

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

Preferably, only two connection lines 86 and 87 can be provided for 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 are provided. Each of these connection lines 86 and 87 can thus serve both as a supply 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 Umschaltventile88.1, 88.2, in particular in the form of a 2-2-way valve, and two load-holding Senkbrems valves or lowering brake valves 89.1, 89.2 , 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 connection 97.1, 97.2, to which a control line or a control channel 98.1, 98.2 is connected. The inlet 95.1 of the first load-holding Senkbrems valve or lowering brake valve 89.1 is connected to the The first working chamber 31.1 is fluid-connected via the fluid channel 29.1, which is also referred to as the first working channel, and the outlet 96.1 of the first load-holding lowering brake valve or lowering brake valve 89.1 is fluid-connected to the first connecting channel 87. The first control channel 98.1 of the first load-holding Senkbrems valve or lowering brake valve 89.1 is fluidly connected to the second connection channel 86. In contrast to this, the second inlet 95.2 of the second load-holding lowering brake valve or lowering brake valve 89.2 is fluid-connected to the second working chamber 31.2 via the fluid channel 29.2, which is also referred to as the second working channel, and the second outlet 96.2 of the second load-holding lowering brake valve or Lowering brake valve 89.2 is fluidly connected to the second connection channel 86. The second control channel 98.2 of the second load-holding Senkbrems valve or lowering brake valve 89.2 is fluidly connected to the first connection channel 87.

Preferably, the respective load-holding Senkbrems valve or the Senkbrems valve 89.1, 89.2 be acted upon by the spring force of a spring 99.1, 99.2, the force that is exerted by the fluid pressure fluid via the respective control channel 98.1, 98.2 , counteracts.

Preferably, the respective passageway between the respective inlet 95.1, 95.2 and the respective outlet 96.1, 96.2 of the respective lowering brake valve 89.1, 89.2 then, when the respective control channel 98.1, 98.2 is not acted upon by fluid pressure medium or is depressurized, so that possibly at the respective inlet 95.1, 95.2 pressure medium under pressure, 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 are used. Because in the closed position of the respective lowering brake valve 89.1, 89.2, the piston 22 can not continue to lower. In this way, if necessary, independently of or in addition to a mechanical locking of the locking cylinder 20, respectively of the piston 22, a fluidic, in particular hydraulic, securing the locking cylinder 20, respectively of the piston 22, can be achieved.

With the aid of the second load-holding lowering brake valve or lowering brake valve 89.2 can be effected or is effected that upon application of the piston 22 on its first side 27.1 with the located in the first working chamber 31.1 fluid pressure fluid to form a working pressure, causing a displacement of the piston 22 in the second direction or retraction direction 28.1, at the same time in the second working chamber 31.2 on the second side 27.2 of the piston 22, a pressure exerted by the pressure medium located in the second working chamber 31.2 acts. The counter-pressure acting in the second working chamber 31.2 is maintained at pressure values with the aid of the second lowering brake valve 89.2 during the application of the fluid to the first working chamber 31.1 and consequently during a movement of the piston 22 in the second direction or in the retraction direction 28.2 are smaller than the working pressure in the first working chamber 31.1, so that during the movement of the piston 22 in the second direction 28.2 a controlled braking of the piston 22 in the second direction 28.2 is effected. As a result, an uncontrolled advance of the piston 22 in the second direction 28.2 can be avoided.

With the aid of the first load-holding lowering brake valve or the lowering brake valve 89.1, it can be effected or caused that when the piston 22 is acted upon on its second side 27.2 with the pressure medium located in the second working chamber 31.2 to form a working pressure, causing a displacement of the piston 22 in the first direction or extension direction 28.1, at the same time in the first working chamber 31.1 on the first side 27.1 of the piston 22, a counter pressure exerted by the pressure medium in the first working chamber 31.1 acts. The counterpressure acting in the first working chamber 31.1 is maintained at pressure values, which are always lower than the working pressure in, with the aid of the first counterbalance valve 89.1 during pressurization of the second working chamber 31.2 with pressure medium and consequently during movement of the piston 22 in the first direction 28.1 are the second working chamber 31.2, so that during the movement of the piston 22 in the first direction 28.1 a controlled braking of the piston 22 in the first direction 28.1 is effected. As a result, an uncontrolled advance of the piston 22 in the first direction 28.1 can be avoided.

The first connection channel 87 is fluidly connected via the first channel 91. 1 to the pressure medium main inflow channel 62 of the flow divider 60. 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 toward the flow divider 60, but blocks in the opposite direction. The second connection channel 86 is fluidly connected via the second channel 91. 2 to the pressure medium main inflow channel 62 of the flow divider 60. 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 toward the flow divider 60, but blocks 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 of the recess or chamber 49 of the cylinder 21 is fluidly connected to the first and second switching valve 88.1, 88.2. These switching valves 88.1, 88.2 are each a 2-way valve. The first switching valve 88.1 is of a in the FIGS. 1 to 4 shown first passage position 100.1, in which the fluid pressure medium from the pressure medium discharge passage 83 of the chamber 49 can flow into the first working chamber 31.1, operable or switchable in a first blocking position, in which the flow path from the pressure medium discharge passage 83 to the first working chamber 31.1 is locked. The second switching valve 88.1 is of a in the FIGS. 1 to 4 shown second passage position 100.2, in which the fluid pressure medium from the pressure medium discharge channel 83 of the chamber 49 can flow into the second working chamber 31.2, operable or switchable in a second blocking position, in which the flow path from the pressure medium discharge channel 83 to the second working chamber 31.2 is locked. In the first passage position 100.1 of the first switching valve 88.1 and also in the second passage position 100.2 of the second switching valve 88.2 is each a basic position in which the switching valves 88.1, 88.2 due to an application of fluid pressure fluid via one fluid-connected to the pressure fluid discharge channel first and second control channel 101.1, 101.2 held or transferred. Each switching valve 88.1, 88.2 thus forms a means for the need or switchable blocking or releasing a passageway. The control for switching the first switching valve 88.1 from its first basic or passage position 100.1 into its first blocking position takes place via a third control channel 101.3, which is fluid-connected to the second connecting channel 86. The control for switching the second switching valve 88.2 from its second basic or passage position 100.2 into its second blocking position takes place via a fourth control channel 101.4, which is fluid-connected to the first connecting channel 87.

The function of the entire, in an end housing or control block 82 of the locking cylinder 20 integrated control unit 85 with the corresponding control or regulating elements 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, the second connection channel 86 is acted upon by fluid pressure medium, while the first connection channel 87 by means of a suitable, not shown in the figures means , is depressurized or is. As a result, the fluid pressure medium can flow through the second connection channel 86 and, at a branch thereof, out through the second channel 91. 2 with a main volume flow into the pressure medium main inflow channel 62 of the flow divider 60. The pressure compensator 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 opening into the recess or chamber 49 of the cylinder 21 first pressure medium inflow channel 54.1 and a second part-volume flow of the main volume flow in the recess or chamber 49th the second pressure medium inflow channel 54.2 opening out of the cylinder 21 in such a way that the ratio of the first partial volume flow of the fluid pressure medium flowing through the first fluid-inflow inflow channel 54.1 and that passing through the second pressure medium inflow channel 54.2 passes through the first second fluid-axial sliding bearings 53.2 flowing second volume partial flow of the fluid pressure medium, at least during 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, 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 counterpressures of the fluid pressure medium always remains substantially constant. As a result, the first clamping double-conical body 45.1 is or remains independent of both by means of the first fluid-axial bearing 53.1 charged with the fluid pressure medium and by means of the second fluid-axial bearing 53.2 acted upon by the fluid pressure medium Size of a force acting on the piston 22 load F (on pressure or train) and thereby required system pressure, always in a fluid-dynamic floating position 63 and in a fluid-dynamic floating state fluidly stored (see FIGS. 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. The fluid pressure medium flowing into the recess or chamber 49 via the first and second pressure-medium inflow channels 54.1, 54.2 flows while maintaining the bilateral axial fluid-sliding bearing of the first clamping double-conical body 45.1 and its At the same time, the first switching valve 88.1 is in its first blocking position, while the second switching valve 88.2 is in its second passage position 100.2, so that the fluid pressure medium from the pressure-medium discharge channel 83 can flow through a second pressure medium channel 102.2 into the second working chamber 31.2 to a movement of the piston 22 in the first direction 28.1 or to a movement of the piston 22 in the first direction 28.1 or to effect an extension of the piston rod 34 in the extension direction 28.1.

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, the first connection channel 87 is subjected to fluid pressure medium, while the second connection channel 86 by means of the means not shown in the figures, depressurized is switched. As a result, the fluid pressure medium can flow through the first connection channel 87 and, at a branch thereof, out through the first channel 91.1 with a main volume flow into the pressure medium main inflow channel 62 of the volume distributor 60. The pressure compensator or the control piston 66 of the flow divider 60; 60.1 now controls a first part-volume flow of the main volume flow in the opening into the recess or chamber 49 of the cylinder 21 first pressure medium inflow channel 54.1 and a second part-volume flow of the main volume flow in which in the recess or chamber 49 of the Cylinder 21 opening second pressure medium inflow channel 54.2 such that the said ratio, as already described above, always substantially 1: 1 or remains substantially at 1: 1. Also in this case, that flows 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 Fluidgleitlagerung the first clamping double-cone body 45.1 and its fluid-dynamic floating position 63 in the recess or chamber 49th But now is the first switching valve 88.1 in its 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 can flow into the first working chamber 31.1 to cause 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.

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, the fluid pressure medium in the first working chamber 31.1 is displaced into the first working channel 29.1 and can from there via the first lowering brake valve 89.1 to flow into the first connecting channel 87, which serves here as a reflux channel. In this case, by means of the first lowering brake valve 89.1 in the first working chamber 31.1, a working pressure in the second working chamber 31.2 counteracting counter or brake pressure is maintained, which causes the piston 22 and consequently the piston rod 34 is not uncontrolled in the first Move direction or extension direction 28.1, in particular can not lead uncontrolled in the extension direction 28.1. In order always to ensure a sufficiently large back pressure in the first working chamber 31.1 with increasing working pressure in the second working chamber 31.2, the first lowering brake valve 89.1 is coupled to the second control channel 98.2, which is in fluid communication with the second connection channel 86. In this way, the first lowering brake valve 89.1 opens a passageway between the first working channel 29.1 and the first connection channel 87 depending on the operating pressure acting in the second working channel 29.2 or in the second working chamber 31.2, preferably proportional to the working pressure, so that with increasing Working pressure in the second working chamber 31.2 by means of the first lowering brake valve 89.1 a corresponding, preferably proportional, increasing back pressure 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 located in the second working chamber 31.2 fluid pressure fluid is displaced in the second working channel 29.2 and can from there via the second Senkbrems valve 89.2 to flow into the second connecting channel 86, which serves as reflux channel here. In this case, with the aid of the second lowering brake valve 89.2 in the second working chamber 31.2, a counteracting or brake pressure counteracting the working pressure in the first working chamber 31.1 is maintained, which causes the piston 22 and consequently the piston rod 34 not to move uncontrolled in the second Move direction or retraction 28.2, in particular, can not lead uncontrolled in the retraction 28.2. To always ensure a sufficiently large back pressure in the second working chamber 31.2 with increasing working pressure in the first working chamber 31.1, the second lowering brake valve 89.2 is coupled to the first control channel 98.1, which is connected to the first Connection channel 87 is fluidly connected. In this way, the second lowering brake valve 89.2 opens a passageway between the second working channel 29.2 and the second connecting channel 86 depending on the operating pressure acting in the first working channel 29.1 or in the first working chamber 31.1, preferably proportional to the working pressure, so that with increasing Working pressure in the first working chamber 31.1 by means of the second lowering brake valve 89.2 a corresponding, preferably proportional, increasing back pressure 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 retraction or extension 28.2, 28.1 of the piston rod 34 in conjunction with a self-locking locking the locking cylinder 20, both Anschlußkänale 86 and 87 by means of the not shown in the figures Switched by depressurized. Then it comes alone by the weight of the piston rod 34 and the piston 22, but especially when the piston rod 34 is loaded with a load F (pressure or train), by gravity automatically or automatically to a lock on the spindle 35.2 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 with each other and consequently to a locking of the spindle 35.2 inter alia against rotation around Your axis of rotation 43.

When the piston rod 34 is stressed by a load F in tension (in the first direction 28.1), then a first locking position 46.1 is established, as in FIG FIG. 3 shown. In this case, the first clamping double-cone body 45.1 via its first locking cone surfaces 48.1 with the third locking-cone surfaces 48.3 of the second clamping double-conical body 45.2 of the cylinder 21 self-locking, so frictionally jammed by static friction ,

When the piston rod 34 is subjected to pressure (in the second direction 28.2) by a load F, then a second locking position 46.2 is established, as in FIG FIG. 4 shown. Here, the first clamping double-cone body 45.1 is self-locking, so frictionally jammed by static friction on 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 ,

In the locking cylinder 20 according to the invention, the clamping force between the two clamped double-cone bodies 45.1, 45.2 clamped together increases proportionally with increasing load F. As a result, at each load F an 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, further movement of the piston 22 and the load F acting thereon via the piston rod 34 can be reliably prevented be, not only in a normal operation of the locking cylinder 20, but also in a pressure failure of the pressure fluid system or in a possibly occurring leakage of the pressure fluid system. The locking cylinder 20 according to the invention offers a higher locking safety than previously known, locking cylinder which lock by friction friction, but not self-locking, ie frictional by static friction, by jamming.

To start from the in FIG. 4 shown second locking position 46.2 or starting from the FIG. 3 shown first locking position 46.1 to achieve unlocking of the first clamping double-cone body 45.1 of the second clamping double-cone body 45.2 to a movement of the piston 22 in the axial direction 23 and a retraction or extension 28.2, 28.1 To enable the piston rod 34, depending on whether the piston 22 is to be moved in the first direction 28.1 or in the second direction 28.2, either the second connection channel 86 or the first connection channel 87 pressurized with 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 flow part 60th

Now, when the first clamp double cone body 45.1 in the in FIG. 4 shown second locking position 46.2 is the second pressure medium inflow channel 54.2 for the chamber 49 against the pressure medium discharge channel 83 by means of the abutting 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 means that the control piston 66 is moved to its first stop and shut-off position, in which then the first inflow channel 62.1 of the flow divider 60; 60.1 with respect to the first pressure medium outflow channel 61.1 of the flow divider 60; 60.1 and thus in relation to the Recess or opening into the chamber 49 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 at the opening into the recess or chamber 49, second pressure medium inflow channel 54.2 and consequently also in the second fluid-axial plain bearings 53.2. If then the system pressure and accordingly in the second fluid-axial plain bearings 53.2 resulting pressure fluid pressure of the fluid pressure medium is sufficiently large or is, as a result, the self-locking jamming of the first clamping double-conical body 45.1 is released and the first clamping double Cone body 45.1 lifts from the fourth locking cone surfaces 48.4 of the second clamping double cone body 45.2 in the first direction 28.1. As a result, an annular, second channel 84.2 is formed between the second locking conical surfaces 48.2 of the first clamping double conical body 45.1 and the fourth locking conical surfaces 48.4 of the second clamping double conical body 45.2 (cf. , FIGS. 1 and 2 ), so that at the same time with the formation of this channel 84.2, the fluid pressure medium from the opening into the recess or chamber 49 second pressure medium inflow channel 54.2 via or through the annular second channel 84.2 in the opening into the recess or chamber 49 pressure medium Abführ channel 83 can flow. As a result, it comes in the opening into the recess or chamber 49 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 opening into the recess or chamber 49 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 61.2 and the second pressure medium inflow 54.2, with the result that the resulting pressure difference immediately equalized by the pressure compensator or by the control piston 66 or "balanced" becomes. In the course of this, the control piston 66 moves, 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. As a result, the first passageway from 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 open or open, so that the fluid pressure fluid also via the first pressure medium inflow channel 54.1 into the recess or chamber 49 and from there via the between the first locking cone surfaces 48.1 of the first clamping double-conical 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 flows into the opening into the recess or chamber 49 common pressure medium discharge channel 83.

But when the first clamp double cone body 45.1 in the in FIG. 3 is shown, the first pressure medium inflow channel 54.1 for the chamber 49 against the pressure medium discharge channel 83 by means of the abutting first and third locking conical 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 to that of the control piston 66 is moved to its second stop and shut-off, in which then the second inflow channel 62.2 of the flow divider 60; 60.1 with respect to the second pressure medium outflow channel 61.2 of the flow divider 60; 60.1 and thus opposite the opening into the recess or in the chamber 49 second pressure medium inflow channel 54.2 is blocked or is. In this way, then the maximum pressure medium pressure of the fluid pressure medium at the first pressure medium discharge channel 61.1 of the flow divider 60; 60.1 and thus also at the opening into the recess or chamber 49, the first pressure medium inflow channel 54.1 and consequently also in the first fluid-axial plain bearing 53.1. If then the system pressure and accordingly the resulting in the first fluid-axial plain bearing 53.1 fluid pressure of the fluid pressure medium is sufficiently large or is, as a result, 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 from the third locking cone surfaces 48.3 of the second clamping double cone body 45.2 in the second direction 28.2. As a result, an annular, first channel 84.1 is formed between the first locking conical surfaces 48.1 of the first clamping double conical body 45.1 and the third locking conical surfaces 48.3 of the second clamping double conical body 45.2 (cf. , FIGS. 1 and 2 ), so that at the same time as the formation of this channel 84.1, the fluid pressure medium from the opening into the recess or chamber 49 first pressure medium inflow channel 54.1 via or through the first annular channel 84.1 in the opening into the recess or chamber 49 pressure medium Abführ channel 83 can flow. As a result, it comes in the opening into the recess or chamber 49 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 opening into the recess or chamber 49 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 an increase in pressure 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 equalized by the pressure compensator or by the control piston 66 or "balanced" becomes. In the course of this, the control piston 66 moves, 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. As a result, 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 open 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 via the between the second locking cone surfaces 48.2 of the first clamping double-conical 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 flows into the opening into the recess or chamber 49 common pressure medium discharge channel 83.

In the two aforementioned cases, the control piston 66, starting from the respective stop and shut-off position, moves in the direction of the respective other stop 77.2, 77.1 into a basic or middle position 72, in which the pressure difference of the pressure medium 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 61.2 of the flow 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 flow part 60; 60.1 and consequently in the opening into the recess or chamber 49 first pressure medium inflow channel 54.1 and the second part volume flow in the second pressure medium outflow channel 61.2 of the flow part 60; 60.1 and consequently in the opening into the recess or chamber 49 second pressure medium inflow channel 54.2 are substantially equal or are kept or remain.

Depending on which of the two switching valves 88.1, 88.2 is blocked and which other of the two switching valves 88.2, 88.1 is open, then the fluid pressure medium flows from the pressure medium discharge channel 83 either via the first pressure medium channel 102.1 into the first working chamber 33.1, whereby the Piston 22 in the second direction 28.2 and the piston rod 34 is moved in the retraction direction 28.2, or via the second pressure medium channel 102.2 in the second working chamber 31.2, whereby the piston 22 moves in the first direction 28.1 and the piston rod 34 in the extension direction 28.1 becomes.

It can be seen, also with reference to the figures, that the flow direction via the flow divider 60 to the two in the axial direction 23 facing away from each other end faces 55.1, 55.2 of the first clamping 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 the piston rod 34, extends or retracts. 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 is acted upon on a piston side 27.1, 27.2 of its two facing away piston sides 27.1, 27.2 with the fluid pressure medium, whereby a movement of the piston 22nd in the axial direction 23 and thereby rotation of the spindle 35.2 is effected together with the first clamping double-cone body 45.1.

LIST OF REFERENCE NUMBERS

20

Locking Cylinder / Locking 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 (from 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 angle of inclination (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 recording end (from 65)

73.2

second recording end (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

Claims (15)

1. Double-acting locking cylinder (20) operated by pressure medium, which comprises a cylinder (21) extending in the direction of a cylinder longitudinal axis (26) and a piston (22) which has a first piston side (27.1) associated with a first work chamber (31.1) and a second piston side (27.2) facing away from the first piston side and associated with a second work chamber (31.2) and which with the help of a fluid pressure medium feedable to the first piston side (27.1) by way of a first work channel (29.1) communicating with the first work chamber (31.1) and to the second piston side (27.2) by way of a second work channel (29.2) communicating with the second work chamber (31.2) is movable relative to the cylinder (21) 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), but is connected with the cylinder (21) to be secure against rotation relative thereto,
   wherein the piston (22) is connected with a first threaded body (35.1), for example nut or spindle, to be secure against rotation relative thereto, the - first - thread (36.1), for example nut thread or spindle thread, of the threaded body being disposed in engagement with a second thread (36.2), for example nut thread or spindle thread, of a second threaded body (35.2), for example nut or spindle, which is automatically lockable by friction couple and gravitational force, with formation of a non-self-locking thread (37),
   wherein the second threaded body (35.2) is rotatable relative to the cylinder (21) about an axis (43) of rotation extending parallel to the cylinder longitudinal axis (26) of the cylinder (21) and is axially displaceable relative to the cylinder (21) in the axial direction (23),
   wherein a first clamping double-cone body (45.1) connected with the second threaded body (35.2) to be secure against relative rotation thereto is provided, the first clamping double-cone body comprising a first clamping cone body (47.1) having first locking cone surfaces (48.1) and a second clamping cone body (47.2) having second locking cone surfaces (48.2),
   wherein a second clamping double-cone body (45.2) connected with the cylinder (21) to be secure against relative rotation thereto is provided, the second clamping double-cone body comprising a third clamping cone body (47.3) having third locking cone surfaces (48.3) and a fourth clamping cone body (47.4) having fourth locking cone surfaces (48.4),
   wherein the first locking cone surfaces (48.1) of the first clamping double-cone body (45.1) can be so placed against the third locking cone surfaces (48.3) of the second clamping double-cone body (45.2) by an axial movement of the second threaded body (35.2) in the first direction (28.2) that in the placed-against state the second clamping double-cone body (45.2) can absorb axial forces acting on the second threaded body (35.2) in the first direction (28.1) and the first locking cone surfaces (48.1 and the third locking cone surfaces (48.3) with formation of clamping with one another are clamped in self-locking manner in a first locking setting (46.1) not only against rotation about the axis (43) of rotation of the second threaded body (35.2), but also against movement away from one another in the axial direction (23),
   wherein the second locking cone surfaces (48.2) of the first clamping double-cone body (45.1) can be so placed against the fourth locking cone surfaces (48.4) of the second clamping double-cone body (45.2) by axial movement of the second threaded body (35.2) in the second direction (28.2) that in the placed-against state the second clamping double-cone body (45.2) can absorb axial forces acting on the second threaded body (35.2) in the second direction (28.2) and the second locking cone surfaces (48.2) and the fourth locking cone surfaces (48.4) with formation of clamping with one another are clamped in self-locking manner in a second locking setting (46.2) not only against rotation about the axis (43) of rotation of the second threaded body (35.2), but also against movement away from one another in the axial direction (23),
   so that the locking cylinder (20) is lockable not only in tension in the first locking setting (46.1), but also in compression in the second locking setting (46.2) and in the placed-against state is locked in such a way in the respective locking setting (46.1, 46.2) that the first clamping double-cone body (45.1) is transferrable, only under exertion of release forces, which releasing the clamping, from the second clamping double-cone body (45.2) to an unlocking setting (92) in which the second threaded body (35.2) is rotatable about the axis (43) of rotation thereof relative to the cylinder (21),
   wherein the second threaded body (35.2) is mounted on at least two fluid axial slide bearings (53.1, 53.2), of which a first fluid axial slide bearing (53.1) is intended for the purpose of absorbing axial forces acting on the second threaded body (35.2) in the first direction (28.1) and of which a second fluid axial slide bearing (53.2) is intended for the purpose of absorbing axial forces acting on the second threaded body (35.2) in the second direction (28.2),
   wherein the first fluid axial slide bearing (53.1) can be acted on by the or a fluid pressure medium by way of a first pressure medium inflow channel (54.1),
   wherein the second fluid axial slide bearing (53.2) can be acted on by the or a fluid pressure medium by way of a second pressure medium inflow channel (54.2), and
   wherein a quantity divider (60; 60.1, 60.2), which comprises a pressure medium main inflow channel and acts only in a throughflow direction, for dividing up a main volume flow, which can be fed to the pressure medium main inflow channel, of the fluid pressure medium into a first part volume flow and into a second part volume flow is provided, the divider comprising a first pressure medium outflow channel (61.1), which communicates with the first pressure medium inflow channel (54.1) for the first fluid axial slide bearing (53.1), for the first part volume flow and a second pressure medium outflow channel (61.2), which communicates with the second pressure medium inflow channel (54.2) for the second fluid axial slide bearing (53.2), for the second part volume flow.
2. Locking cylinder according to claim 1, characterised in that the quantity divider (60; 60.1) is a flow-controlled and/or pressure-controlled valve.
3. Locking cylinder according to claim 1 or 2, characterised in that the quantity divider (60; 60.1) comprises a housing (64) with a regulating piston receiver (65) in which a regulating piston (66) is received to be displaceable, under guidance with small play, relative to the regulating piston receiver (65) in an axial direction (67),
   wherein the regulating piston (66) extends axially in the direction of a regulating piston longitudinal axis (68) and has a regulating piston length as well as a first regulating piston end (70.1) and a second regulating piston end (70.2), which extends in the axial direction (67) away therefrom in an opposite direction and which has from the first regulating piston end (70.1) a spacing corresponding with the regulating piston length,
   wherein a first inflow channel (62.1), which includes a first throttle (71.1), for a first part volume flow of the fluid pressure medium and a second inflow channel (62.2), which includes a second throttle (71.2), for a second part volume flow of the fluid pressure medium are arranged in the housing (64),
   wherein the regulating piston receiver (65) has a first receiver end (73.1) and a second receiver end (73.2) extending in the axial direction (67) away therefrom in an opposite direction,
   wherein the regulating piston receiver (65) goes over at its first receiver end (73.1), as considered in axial direction (67), into a first regulating piston end receptacle (74.1), with which the first inflow channel (62.1) communicates, for reception of the first regulating piston end (70.1) of the regulating piston (66),
   wherein the regulating piston receiver (65) goes over at its second receiver end (73.2), as considered in axial direction (67), into a second regulating piston end receptacle (74.2), with which the second inflow channel (62.2) communicates, for reception of the second regulating piston end (70.2) of the regulating piston (66),
   wherein the first regulating piston end receptacle (74.1) forms a first regulating throttle or a component of a first regulating throttle (75.1) and the second regulating piston end receptacle (74.2) forms a second regulating throttle or a component of a second regulating throttle (75.2) and
   wherein the first regulating piston end receptacle (74.1) is in fluid communication with the first pressure medium outflow channel (61.1) and the second regulating piston end receptacle (74.2) is in fluid connection with the second pressure medium outflow channel (61.2).
4. Locking cylinder according to claim 3, characterised in that the regulating piston (66) is displaceable in the axial direction (67) under pressure and/or flow control by the fluid pressure medium into a first blocking setting (78.1) in which the regulating piston (66) blocks a first flow path from the first inflow channel (62.1) to the first pressure medium outflow channel (61.1) with respect to throughflow of the fluid pressure medium whilst 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 throughflow of the fluid pressure medium and that the regulating piston (66) is displaceable in the axial direction (67) under flow control by the first pressure medium into a second blocking setting (78.2) in which the regulating piston (66) blocks a second flow path from the second inflow channel (62.2) to the second pressure medium outflow channel (61.2) with respect to throughflow of the fluid pressure medium whilst 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 throughflow of the fluid pressure medium.
5. Locking cylinder according to claim 1, characterised in that the quantity divider (60; 60.2) is a gear quantity divider (60.2), which comprises 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 part volume flow, which are coupled together by way of a shaft (81).
6. Locking cylinder according to any one of the preceding claims, characterised in that the first clamping double-cone body (45.1) is at least partly or entirely received in a recess (49), which is bounded by the second clamping double-cone body (45.2), of a cylinder part of the cylinder (21), which recess is bounded by a projection (51) extending radially and transversely to the cylinder longitudinal axis (26) of the cylinder (21) and arranged between the first clamping double-cone body (45.1) and the piston (22), wherein the first pressure medium inflow channel (54.1) communicates with the recess (49) on a first side (55.1), which is associated with the first locking cone surfaces (48.1), of the first clamping double-cone body (45.1), wherein the second pressure medium inflow channel (54.2) communicates with the recess (49) on a second side (55.2), which is associated with the second locking cone surfaces (48.2), of the first clamping double-cone body (45.1), and wherein the recess (49) is sealed relative to the second work chamber (31.2) by a seal (59).
7. Locking cylinder according to claim 6, characterised 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 discharge of the fluid pressure medium flowing through the first fluid axial slide bearing is provided, which first pressure medium discharge channel in an unlocking setting of the first clamping double-cone body is in fluid connection with the first fluid axial slide bearing and communicates with the recess
   and
   a second pressure medium discharge channel for discharge of the fluid pressure medium flowing through second fluid axial slide bearing is provided, which second pressure medium discharge channel in an unlocking setting of the first clamping double-cone body is in fluid connection with the second fluid axial slide bearing and communicates with the recess
   or
   a common pressure medium discharge channel (83) for discharge of the fluid pressure medium flowing through the first and the second fluid axial slide bearings (53.1, 53.2) is provided, which common pressure medium discharge channel in an unlocking setting (92) of the first clamping double-cone body (45.1) is in fluid connection with the first and the second fluid axial slide bearings (53.1, 53.2) and communicates with the recess (49).
8. Locking cylinder according to claim 7, characterised in that the first pressure medium inflow channel (54.1) - when the first clamping double-cone body (45.1) and the second clamping double-cone body (45.2) are locked together in the first locking setting (46.1) and, with formation of the clamping, are subject to self-locking clamping - is blocked relative to the first or common pressure medium discharge channel (83) by means of the mutually contacting first and third locking cone surfaces (48.1, 48.3) and - when the first clamping double-cone body (45.1) and the second clamping double-cone body (45.2) are lifted off one another into an or the unlocking setting (92) - is in fluid connection with the first or common pressure medium discharge channel (83) by way of a first channel (84.1) then formed between the first and third locking cone surfaces (48.1, 48.3)
   and
   that the second pressure medium inflow channel (54.2) - when the first clamping double-cone body (45.1) and the second clamping double-cone body (45.2) are locked together in the second locking setting (46.2) and, with formation of the clamping, are subject to self-locking clamping - is blocked relative to the first or common pressure medium discharge channel (83) by means of the mutually contacting second and fourth locking cone surfaces (48.2, 48.4) and - when the first clamping double-cone body (45.1) and the second clamping double-cone body (45.2) are lifted off one another into an or the unlocking setting (92) - is in fluid connection with the second or common pressure medium discharge channel (83) by way of a second channel (84.2) then formed between the second and fourth locking cone surfaces (48.2, 48.4).
9. Method of operating a double-acting locking cylinder (20) according to any one of the preceding claims, operated by pressure medium, which comprises a cylinder (21) extending in the direction of a cylinder longitudinal axis (26) and a piston (22), which has a first piston side (27.1) associated with a first work chamber (31.1) and a second piston side (27.2) facing away from the first piston side and associated with a second work chamber (31.2) and which with the help of a fluid pressure medium feedable to the first piston side (27.1) by way of a first work channel (29.1) communicating with the first work chamber (31.1) and to the second piston side (27.2) by way of a second work channel (29.2) communicating with the second work chamber (31.2) is movable relative to the cylinder (21) 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), but is connected with the cylinder (21) to be secure against rotation relative thereto,
   wherein the piston (22) is connected with a first threaded body (35.1), for example nut or spindle, to be secure against rotation relative thereto, the - first - thread (36.1), for example nut thread or spindle thread, of the threaded body being disposed in engagement with a second thread (36.2), for example nut thread or spindle thread, of a second threaded body (35.2), for example nut or spindle, which is automatically lockable by friction couple and gravitational force, with formation of a non-self-locking thread (37),
   wherein the second threaded body (35.2) is rotatable relative to the cylinder (21) about an axis (43) of rotation extending parallel to the cylinder longitudinal axis (26) of the cylinder (21) and is axially displaceable relative to the cylinder (21) in the axial direction (23),
   wherein a first clamping double-cone body (45.1) connected with the second threaded body (35.2) to be secure against relative rotation thereto is provided, the first clamping double-cone body comprising a first clamping cone body (47.1) having first locking cone surfaces (48.1) and a second clamping cone body (47.2) having second locking cone surfaces (48.2),
   wherein a second clamping double-cone body (45.2) connected with the cylinder (21) to be secure against relative rotation thereto is provided, the second clamping double-cone body comprising a third clamping cone body (47.3) having third locking cone surfaces (48.3) and a fourth clamping cone body (47.4) having fourth locking cone surfaces (48.4),
   wherein the first locking cone surfaces (48.1) of the first clamping double-cone body (45.1) can be so placed against the third locking cone surfaces (48.3) of the second clamping double-cone body (45.2) by an axial movement of the second threaded body (35.2) in the first direction (28.2) that in the placed-against state the second clamping double-cone body (45.2) can absorb axial forces acting on the second threaded body (35.2) in the first direction (28.1) and the first locking cone surfaces (48.1 and the third locking cone surfaces (48.3) with formation of clamping with one another are clamped in self-locking manner in a first locking setting (46.1) not only against rotation about the axis (43) of rotation of the second threaded body (35.2), but also against movement away from one another in the axial direction (23),
   wherein the second locking cone surfaces (48.2) of the first clamping double-cone body (45.1) can be so placed against the fourth locking cone surfaces (48.4) of the second clamping double-cone body (45.2) by axial movement of the second threaded body (35.2) in the second direction (28.2) that in the placed-against state the second clamping double-cone body (45.2) can absorb axial forces acting on the second threaded body (35.2) in the second direction (28.2) and the second locking cone surfaces (48.2) and the fourth locking cone surfaces (48.4) with formation of clamping with one another are clamped in self-locking manner in a second locking setting (46.2) not only against rotation about the axis (43) of rotation of the second threaded body (35.2), but also against movement away from one another in the axial direction (23),
   so that the locking cylinder (20) is lockable not only in tension in the first locking setting (46.1), but also in compression in the second locking setting (46.2) and in the placed-against state is locked in such a way in the respective locking setting (46.1, 46.2) that the first clamping double-cone body (45.1) is transferrable only under exertion of release forces, which release the clamping, from the second clamping double-cone body (45.2) to an unlocking setting (92) in which the second threaded body (35.2) is rotatable about the axis (43) of rotation thereof relative to the cylinder (21),
   wherein the second threaded body (35.2) is mounted on at least two fluid axial slide bearings (53.1, 53.2), of which a first fluid axial slide bearing (53.1) is intended for the purpose of absorbing axial forces acting on the second threaded body (35.2) in the first direction (28.1) and of which a second fluid axial slide bearing (53.2) is intended for the purpose of absorbing axial forces acting on the second threaded body (35.2) in the second direction (28.2),
   wherein the first fluid axial slide bearing (53.1) can be acted on by the or a fluid pressure medium by way of a first pressure medium inflow channel (54.1),
   wherein the second fluid axial slide bearing (53.2) can be acted on by the or a fluid pressure medium by way of a second pressure medium inflow channel (54.2),
   wherein a quantity divider (60; 60.1, 60.2), which comprises a pressure medium main inflow channel and acts only in a throughflow direction, for dividing up a main volume flow, which can be fed to the pressure medium main inflow channel, of the fluid pressure medium into a first part volume flow and into a second part volume flow is provided, the divider comprising a first pressure medium outflow channel (61.1), which communicates with the first pressure medium inflow channel (54.1) for the first fluid axial slide bearing (53.1), for the first part volume flow and a second pressure medium outflow channel (61.2), which communicates with the second pressure medium inflow channel (54.2) for the second fluid axial slide bearing (53.2), for the second part volume flow, and
   wherein with the help of the quantity divider (60; 60.1, 60.2) at least during 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 a respective resulting rotation of the second threaded body (35.2) about the axis (43) of rotation thereof together with the first clamping double-cone body (45.1), a main volume flow of the fluid pressure medium is divided into a first part volume flow and a second part volume flow in such a way that a ratio of the first part volume flow, which flows through the first pressure medium inflow channel (54.1) to the first fluid axial slide bearing (53.1), of the fluid pressure medium and the second volume part flow, which flows through the second pressure medium inflow channel (54.2) to the second fluid axial slide bearing (53.2), of the fluid pressure medium remains substantially constant, whereby the first clamping double-cone body (45.1) not only by means of the fluid axial slide bearing (53.1) loaded by the fluid pressure medium, but also by means of the second fluid axial slide bearing (53.2) loaded by the fluid pressure medium is and/or remains fluid-mounted in a fluid-dynamic floating setting (63).
10. Method according to claim 9, characterised in that the ratio at least during movement of the piston (22) not only in the first direction (28.1), but also in the second direction (28.2) remains or is kept substantially constant regardless of the pressures, which act in the first pressure medium inflow channel (54.1) and in the second pressure medium inflow channel (54.2), of the fluid pressure medium.
11. Method according to claim 9 or 10, characterised in that the ratio is substantially 1:1.
12. Method according to any one of claims 9 to 11, characterised in that the quantity divider (60; 60.1) comprises a housing (64) with a regulating piston receiver (65) in which a regulating piston (66) is received to be displaceable, under guidance with small play, relative to the regulating piston receiver (65) in an axial direction (67),
    wherein the regulating piston (66) extends axially in the direction of a regulating piston longitudinal axis (68) and has a regulating piston length as well as a first regulating piston end (70.1) and a second regulating piston end (70.2), which extends in axial direction (67) away therefrom in an opposite direction and which has from the first regulating piston end (70.1) a spacing corresponding with the regulating piston length,
    wherein a first inflow channel (62.1), which includes a first throttle (71.1), for a first part volume flow of the fluid pressure medium and a second inflow channel (62.2), which includes a second throttle (71.2), for a second part volume flow of the fluid pressure medium are arranged in the housing (64),
    wherein the regulating piston receiver (65) goes over by a first end into a first regulating piston end receptacle (74.1), with which the first inflow channel (62.1) communicates, for reception of the first regulating piston end (70.1) of the regulating piston (66) and wherein the regulating piston receiver (65) goes over by a second end into a second regulating piston end receptacle (74.2), with which the second inflow channel (62.2) communicates, for reception of the second regulating piston end (70.2) of the regulating piston (66),
    wherein the first regulating piston end receptacle (74.1) forms a first regulating throttle or a component of a first regulating throttle (75.1) and the second regulating piston end receptacle (74.2) forms a second regulating throttle or a component of a second regulating throttle (75.2) and
    wherein the first regulating piston end receptacle (74.1) is in fluid communication with the first pressure medium outflow channel (61.1) and the second regulating piston end receptacle (74.2) is in fluid connection with the second pressure medium outflow channel (61.2),
    so that the regulating piston (66) - when a first pressure medium pressure, which forms in the first pressure medium outflow channel (61.1), whilst 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 forms in the second pressure medium outflow channel (61.2), whilst the second pressure medium outflow channel (61.2) is flowed through by the second part volume flow of the fluid pressure medium are of the same size - is disposed in a basic setting or centre setting (72)
    and the regulating piston (66) - when a first pressure medium pressure, which forms in the first pressure medium outflow channel (61.1), whilst the first pressure medium outflow channel (61.1) is flowed through by a first part volume flow of the first fluid pressure medium, differs from a second pressure medium pressure, which forms in the second pressure medium outflow channel (61.2), whilst the second pressure medium outflow channel (61.2) is flowed through by a second part volume flow of the fluid pressure medium, so that the first pressure medium pressure and the second pressure medium pressure differ from one another by a pressure difference not equal to zero - simultaneously with formation of the pressure difference moves in the axial direction (67) in the direction of the lower pressure-medium pressure into a setting differing from the basic setting or centre setting (72).
13. Method according to claim 12, characterised in that when the first clamping double-cone body (45.1) is clamped in self-locking manner with the second clamping double-cone body (45.2) in the first locking setting (46.1) and when the fluid pressure medium is fed to the first inflow channel (62.1) the regulating piston (66) is displaced from its basic setting or centre setting (72) into a second blocking setting (78.2) or is kept in a second blocking setting (78.2) in which the second pressure medium outflow channel (61.2) and the second pressure medium inflow channel (54.2) are blocked relative to the second inflow channel (62.2) against inflow of the pressure medium, whilst 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
    either
    can flow through the first inflow channel (62.1) into the first pressure medium outflow channel (61.1) and from there through the first pressure medium inflow channel (54.1) so as to transfer the first clamping double-cone body (45.1) into an unlocking setting (92) through a continued feed of the fluid pressure medium
    or
    flows through the first inflow channel (62.1) into the first pressure medium outflow channel (61.1) and from there through the first pressure medium inflow channel (54.1) so that the first clamping double-cone body (45.1) is transferred into an unlocking setting (92)
    and
    when the first clamping double-cone body (45.1) is clamped in self-locking manner with the second clamping double-cone body (45.2) in the second locking setting (46.2) and when the fluid pressure medium is fed to the second inflow channel (62.2) the regulating piston (66) is displaced from its basic setting or centre setting (72) into a first blocking setting or is kept in a first blocking setting in which the first pressure medium outflow channel (61.1) and the first pressure medium inflow channel (54.1) are blocked relative to the second inflow channel (62.2) against inflow of the pressure medium, whilst 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
    either
    can flow through the second inflow channel (62.2) into the second pressure medium outflow channel (61.2) and from there through the second pressure medium inflow channel (54.2) so as to transfer the first clamping double-cone body (45.1) into an unlocking setting (92) through a continued feed of the fluid pressure medium
    or
    flows through the second inflow channel (62.2) into the second pressure medium outflow channel (61.2) and from there through the second pressure medium inflow channel (54.2) so that the first clamping double-cone body (45.1) is transferred into an unlocking setting (92).
14. Method according to any one of claims 9 to 11, characterised in that the quantity divider (60; 60.1) is a or the gear quantity divider (60.1), which comprises at least one first gear pump (80.1) conveying the first part volume flow and at least one second gear pump (80.2) conveying the second part volume flow, which are so coupled together by way of a or the shaft (81) that at least during movement of the piston (22) in the first direction (28.1) and also in the second direction (28.2) and a respective resulting rotation of the second threaded body (35.2) about the axis (43) of rotation thereof together with the first clamping double-cone body (45.1) 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.
15. Method according to any one of claims 9 to 14, characterised in that
    either
    starting from the first locking setting (46.1) in which the first clamping double-cone body (45.1) and the second clamping double-cone body (45.2) are clamped in self-locking manner initially at least or only the first fluid axial slide bearing (53.1) is loaded with the fluid pressure medium by way of the quantity divider (60; 60.1, 60.2) and the first pressure medium inflow channel (54.1) in fluid connection therewith
    or
    starting from the second locking setting (46.2) in which the first clamping double-cone body (45.1) and the second clamping double-cone body (45.2) are clamped in self-locking manner initially at least or only the second fluid axial slide bearing (53.2) is loaded with the fluid pressure medium by way of the quantity divider (60; 60.1, 60.2) and the second pressure medium inflow channel (54.2) in fluid connection therewith
    either to cause lifting of the first clamping double-cone body (45.1) off the second clamping double-cone body (45.2) into a lifted-off and unlocking setting (92) or whereby lifting of the first clamping double-cone body (45.1) off the second clamping double-cone body (45.2) into a lifted-off and unlocking setting (92) is produced, in which the first clamping double-cone body (45.1) and the second clamping double-cone body (45.2) are either lifted at least partly off one another so that the locking cone surfaces (48.1, 48.2; 48.3, 48.4) at least in part are no longer in contact or are completely lifted off one another so that the locking cone surfaces (48.1, 48.2; 48.3, 48.4) are no longer in contact
    and that only subsequently is the pressure medium fed to the first or second work chamber (31.1, 31.2) either to enable, assist and/or cause movement of the piston (22) in the axial direction (23) or whereby the piston (22) is moved in the axial direction (23).

Images