EP2570679B1 - Cylinder piston unit with locking means and correspondind methods for locking and unlocking - Google Patents

Description

The invention relates to a locking cylinder according to the preamble of claim 1. The invention also relates to a method for locking a locking cylinder according to claim 8 and a method for unlocking a locking cylinder according to claim 9.

Such locking cylinders seem, for example, from the DE-OS 20 39 296 and from the DE 196 33 412 A1 to have become known in the form of frictionally locking working cylinders. In these working cylinders, a frictional locking of a spindle rotatable relative to a cylinder can take place by means of friction rings in the manner of a friction brake. In the case of failure of the hydraulic system or in the event of leakage, the spindle is automatically locked by friction solely by gravity and supported by the load acting on the piston, ie by frictional engagement. To unlock the Friction rings, a friction ring of the friction rings can be lifted together with the spindle using a pressure exerted by a fluid pressure medium pressure from the other friction ring in the axial direction, so that then the spindle is rotatable about its axis of rotation relative to the cylinder, which then coupled to the spindle Piston is movable in the axial direction. The safety of this cylinder against unlocking and consequently against a decrease in the load is limited by design.

There are also known other working cylinder with integrated friction brake, the axially movable brake body, which cause due to a permanently acting on this spring force of one or more springs, a deceleration and consequent stopping of a piston. These brake bodies can be released under the action of a fluid pressure medium on this in a direction opposite to the spring force of the spring / n or lifted in the axial direction of the counter-brake bodies, so that then a displacement of the piston relative to the cylinder is possible. All of these cylinders are comparatively complex in terms of manufacture and construction and, due to the design, require comparatively much space.

Such a cylinder is for example from the DE 297 20 838 U1 known. In this case, a spindle is rotatably supported at its one end via two thrust bearings about its axis of rotation relative to a cylinder in such a way that it is clamped secured to one of the thrust bearing against axial displacement. The other thrust bearing supports a rotationally fixed to the spindle mounted rotary cone with outer cone, which rotatably attached to the cylinder attached and can be used as a hub brake, axially displaceable against the spring force of a spring, cone-shaped brake piston with inner cone can be braked. This braking device allows only a frictional braking of the spindle and consequently of this coupled via the self-locking spindle thread piston. The braking force exerted by the compression spring remains the same regardless of the load to be moved by means of the piston, so that this working cylinder is only suitable for lifting or lowering comparatively light loads, but not for moving heavy loads, without any significant loss of security comes.

Other working cylinders of this type are for example from DE 38 31 459 A1 and from the US 6,612,221 B1 known. These working cylinders are linear actuators whose pistons are fastened to a piston rod in a thread-free manner or secured against axial movement relative to the piston rod. These cylinders also comprise conical brake bodies, which are constantly acted upon by the spring forces of one or more springs, whereby a frictional locking of the piston relative to the cylinder is achievable. These brake bodies can be released by the action of pressure forces of a fluid pressure medium against the spring forces of the springs.

In case of DE 38 31 459 A1 the conical surfaces of a clamping cone designed as an outer cone and forming part of the piston act on the conical surfaces of a plurality of clamping tongues of a spreader ring, each of which is provided with an inner cone and elastically deformable in the radial direction. These are evenly spaced arranged distributed over the circumference and also form part of the piston. The facing away from the respective inner cone cylindrical outer surfaces of the clamping tongues facing the cylindrical inner surfaces of a cylinder jacket of a cylinder housing. At rest, the clamping tongues are urged by the spring force of disc springs in the radial direction outwards pressed against the cylinder jacket. By this widening of the expansion tongues a frictional clamping between the clamping tongues and the cylinder housing is effected, whereby the cylinder housing and the piston and thus also the piston rod are frictionally coupled with each other. This construction is complex and not suitable for lifting or lowering large loads.

In case of US 6,612,221 B1 a tubular conical clamping element with outer cone is provided on a piston rod, which is fixed to a cylinder and which is intended to frictionally cooperate with the outer surface of a piston rod. On this clamping element a rectilinear, extending in the axial direction ball bearing is added. In this ball bearing in turn a flange-shaped brake actuating body is added, which is constantly acted upon by the spring force of a plurality of compression springs in the axial direction such that in the idle state, the piston rod is frictionally locked to the cylinder. The ball bearing serves to reduce the friction between the brake actuating body and the clamping element, so that it can come in this area to no jamming. Also, this cylinder is relatively complex in design and manufacture and security against unlocking is limited, so that this Working cylinder is not suitable for lifting and / or lowering large loads.

From the DE 10 2007 024 736 A1 the applicant is a mechanically lockable pressure lock cylinder with one-sided Fluidgleitlagerung known. In this locking cylinder a plurality of axially displaceable locking bolts are provided, which can intervene due to the spring forces of these locking bolts associated compression springs in the recess provided with locking recesses on a spindle rotatably mounted flange-shaped approach. Thereby, a rotation of the spindle in a rotational direction with the formation of a positive locking can be blocked, while the spindle remains rotatable in the other rotational direction about its axis of rotation relative to the cylinder. For receiving axial forces acting in the load direction on the spindle, the flange-shaped projection is formed with a cylindrical and coaxial with the axis of rotation of the spindle formed support and bearing body which extends in the axial direction to the cylinder bottom of the cylinder and at its cylinder bottom side end Having a normal to the axis of rotation of the spindle formed flat support and bearing surface. This support and bearing surface is opposite to a likewise flat counter-support and bearing surface of a plain bearing disc, which is supported on the cylinder base. The support and bearing surface and the counter-support and -lagerfläche may form a fluid fluid pressurizable hydrostatic fluid bearing. The flange-shaped approach is based on its side facing away from the locking recesses on a needle bearing, which also serves to support the spindle. The locking security of this locking cylinder meets high demands even with large loads and / or high piston speed. However, this locking cylinder is accordingly elaborately constructed and also requires a corresponding amount of production time and costs.

Such a cylinder is also off DE 36 29 677 A1 known. It is accordingly an object of the invention to provide a locking cylinder and a method of locking and a method for unlocking a locking cylinder available with a comparatively simple, space-saving and robust construction and at relatively low cost manufacturability, yet, even at high loads, a high operational reliability over a long time.

This object is achieved in a surprisingly simple manner, in particular by the features of claims 1, 8 and 9.

Accordingly, the invention preferably relates to a locking cylinder having a cylinder and a piston which, by means of a fluid pressure means which can be supplied to a working channel or both sides of the piston via a working channel or both sides of the piston via these sides, is parallel to the longitudinal axis of the cylinder in a first direction and in a second direction opposite to the first direction is movable, and which is provided with a piston thread, the formation of a non-self-locking thread with a spindle thread frictionally, ie non-positively by friction and, preferably exclusively, by gravity, in particular acting on the piston Load, automatically or automatically, preferably drive-free, in particular without action or support of force accumulators, For example, springs, lockable spindle is engaged, which is rotatable relative to the cylinder about a parallel to the longitudinal axis of the cylinder arranged axis of rotation and relative to the cylinder in the axial direction or parallel to its axis of rotation, preferably only slightly, axially displaceable, and wherein a first Working chamber associated with a first side of the piston, preferably limited by this, and is arranged in the, in particular second, direction of axial movement of the piston parallel to the longitudinal axis of the cylinder or parallel to the axis of rotation of the spindle viewed behind or behind the piston and wherein a second working chamber is associated with, preferably delimited by, a second side of the piston and, viewed in the said direction, is arranged in front of the piston, and at least two locking support bodies which are convertible into a mutual frictional locking engagement are provided, which are intended frictionally locking the spindle against rotation about its axis of rotation and receiving axial forces acting on the spindle in the second direction, preferably such that the spindle is locked in the locked state against movement in the second direction on the cylinder, at least one first Locking support body of the lock-support body rotatably, preferably rigidly connected to the spindle or is attached to the spindle and wherein at least a second lock-supporting body of the lock-supporting body rotationally fixed, preferably rigidly, with the Cylinder is connected or attached to the cylinder, and wherein the spindle is mounted on at least two, preferably axially spaced, thrust bearings, of which a first thrust bearing is intended to receive in the first direction acting on the spindle axial forces, and of which a second thrust bearing is intended to receive axial forces acting on the spindle in the second direction, and wherein the spindle is connected or formed to a first bearing body having a first bearing surface which is rotatable, preferably rigid, of a second bearing surface; The first bearing surface of the first bearing body and the second bearing surface of the second bearing body forming the second thrust bearing, which as a, preferably hydrostatic, fluid-plain bearing connected to the cylinder or attached to the cylinder second bearing body, preferably the cylinder base is designed, which is acted upon by a first fluid channel with or with the fluid pressure medium or, and wherein the first locking-supporting body as a first locking cone surfaces having, self-locking or self-locking, first Clamp cone body is designed and wob ei the second locking-support body are designed as a second locking cone surfaces having, self-locking or self-locking, second clamping cone body, and wherein the locking conical surfaces of the clamping cone body clamped together self-locking or are clamped self-locking, and wherein between a first working chamber fluid-connected to the first working channel and a second fluid channel, in particular a return or discharge channel, a means for limiting the pressure and / or flow of the pressure medium via or through a passageway between the first working channel and the second fluid channel depending on the pressure in a fluidically connected to the second working chamber second working channel is arranged, and wherein the means is designed as a lowering brake valve or load-holding lowering valve, which is one with the second Working chamber fluid-connected control channel for controlling or regulating the pressure in the second working chamber counteracting back pressure in the first working chamber is coupled.

In other words, when their locking conical surfaces abut each other, the clamping cone bodies can be frictionally jammed together by friction with each other, or the clamping cone bodies, when their locking conical surfaces are abutted against each other, frictionally be jammed by friction with each other self-locking.

By the above measures is or is a frictional self-locking clamping-locking the spindle against rotation about its axis of rotation relative to the cylinder as well as against movement or displacement of the spindle or with this rotatably coupled first clamping cone body can be reached or reached in the axial direction or in a direction parallel to the axis of rotation of the spindle.

The locking cylinder according to the invention can be made particularly simple and inexpensive in space-saving and particularly robust construction and offers due to the per se self-locking clamping lock or deadlock a comparatively high reliability in all expected operating conditions, ie not only in normal operation, but also in the occurrence of overloads and / or in case of any pressure loss or leakage. In contrast to the known from the prior art friction-locking locking or braking structures according to the invention a per se self-locking locking the spindle relative to a rotation about its axis of rotation relative to the cylinder achievable or achieved, so even without that drive or load-related forces would be introduced via the spindle. In other words, according to the invention, a double or 2-fold self-locking locking of the spindle can be achieved relative to the cylinder.

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.

Characterized in that a first working chamber associated with a first side of the piston, preferably delimited by this, and in the, in particular second, direction of axial movement of the piston parallel to the longitudinal axis of the cylinder or parallel to the axis of rotation of the spindle viewed behind or is arranged after the piston, and that a second working chamber associated with, preferably delimited by a second side of the piston, and, viewed in the said direction, is arranged in front of the piston, and that between a fluidically connected to the first working chamber first working channel and a second fluid channel, in particular one or the return or discharge channel, a means for limiting the pressure and / or volume flow of the pressure medium via or in a passageway between the first working channel and the second fluid channel depending on the pressure in one with a second working chamber fluid-connected second working channel, angeor dnet is, depending on the pressure of the pressure medium in a working chamber, the pressure of the pressure medium be controlled or regulated in a provided on the other side of the piston working chamber such that always a sufficient back pressure is formed so that an uncontrolled axial movement, in particular an uncontrolled advance, the piston and consequently the piston rod and the load can be avoided or prevented can.

Characterized in that it is said means to a lowering brake valve or a load-holding lowering brake valve coupled to a fluidically connected to the second working chamber control channel for controlling or regulating the pressure in the second working chamber counteracting back pressure in the first working chamber or fluid-connected, an uncontrolled axial movement, in particular a lead, of the piston in one or the, in particular second, direction can be avoided or prevented.

Parallel to such a means or parallel to the input and output of such a lowering brake valve or load-holding brake valve may preferably be provided a means for shutting off a passageway in a flow direction and for releasing the passageway in an opposite flow direction. Such an agent may preferably be a check valve.

The clamping cone bodies may preferably be designed frusto-conical. At least one of the clamping cone bodies, in particular the first clamping cone body can be designed with or as a conical disk or truncated cone disk.

The locking cylinder may preferably have a hollow piston or a piston nut, with an internal thread, in combination with a spindle with an external thread. It is understood, however, that the locking cylinder may alternatively also have a hollow spindle or a spindle nut, with an external thread, in combination with a piston with an external thread.

The locking cylinder may preferably be a rotatably mounted relative to the cylinder threaded spindle in combination with a rotatably mounted relative to the cylinder spindle nut, in particular with a threaded piston, which may be connected to a led out of the cylinder drive body, in particular a piston rod. Alternatively, in kinematic reversal of the locking cylinder may comprise a non-rotatable threaded spindle and a rotatably mounted spindle nut, in particular a threaded piston.

It can preferably be provided that the first locking support body and the first bearing body are integrally connected or manufactured and / or form a, preferably common, first locking support and bearing body and / or that the second locking support Body and the second bearing body are integrally connected or manufactured and / or form a, preferably common, second locking support and bearing body. As a result, an even more simplified, compact and robust construction in conjunction with a particularly simple cost-effective production can be achieved.

In an inventive development can be provided that the first locking support and bearing body as a first locking cone surfaces having, self-locking or self-locking acting, first clamping cone body is formed and that the second locking support and bearing body as a second locking cone surfaces having, self-locking or self-locking , second clamping cone body is formed. As a result, the advantages described above can be achieved to a particular extent.

According to a particularly preferred embodiment, it may be provided that the first locking cone surfaces of the first clamping cone body with the axis of rotation of the spindle form a first angle of inclination and that the second locking cone surfaces of the second clamping cone body with the longitudinal axis of the cylinder or with the axis of rotation of the spindle form a second inclination angle, wherein the first inclination angle and the second inclination angle is equal, preferably four to ten or thirteen, in particular four to seven degrees, preferably six to seven degrees. In this way, in combination with favorable material pairings always a frictional characterized by static friction clamping connection between the clamping cone bodies in conjunction with a self-locking or in conjunction with a negative efficiency of the compound per se can be achieved. In contrast, it has been shown in elaborate experiments that depending on the chosen seemingly appropriate material pairings of cone bodies whose inclination angle is greater than 10 to 13 degrees, no self-locking clamping connection is achieved.

According to an advantageous development can be provided that the first clamping cone body with or as an outer cone is formed and that the second clamping cone body is formed with or as an inner cone. It is understood, however, that alternatively the first clamping cone body can also be formed with one or as an inner cone and that the second clamping cone body can also be formed with or as an outer cone.

Furthermore, it can be provided that the first clamping cone body tapers conically in the direction of the axis of rotation of the spindle and in the direction away from the piston or towards a cylinder bottom of the cylinder and / or that the first clamping cone element tapers. Body tapers conically towards the axis of rotation of the spindle and towards the piston towards or away from the cylinder bottom.

Furthermore, it can be provided that the first locking cone surfaces of the first clamping cone body are arranged in the region or on the side thereof pointing away from the piston or toward the cylinder base or the cylinder base, and in that the second locking cone surfaces of the second clamping cone body are arranged in the region or on the side thereof pointing in the direction of the pistons or away from the cylinder base and / or that the first locking conical surfaces of the first clamping cone Cone body in the region or on which in the direction of the piston toward or from the cylinder bottom side facing away are arranged and that the second locking cone surfaces of the second clamping cone body in the region or in the direction of the piston away or to the cylinder bottom facing side are arranged.

In an advantageous development it can be provided that the first clamping cone body forms one end of the spindle, preferably a cylinder bottom end of the spindle. In other words, one end of the spindle, preferably the cylinder bottom end of the spindle, may be formed with or as the first clamping cone body. As a result, a particularly simple and inexpensive to produce and compact and robust construction is possible.

Furthermore, it can be provided that the second bearing body is formed with or as a cylinder bottom of the cylinder or with the cylinder bottom of the cylinder and / or that the second bearing body as, preferably integrally connected to the cylinder or produced, in particular is formed radially and transversely to the longitudinal axis of the cylinder or to the axis of rotation of the spindle extending approach, which is arranged between the first clamping cone body and the piston.

Furthermore, it can be provided that the first clamping cone body is mounted on the fixed bearing, preferably rigidly connected to the cylinder or on one or the cylinder base via the first axial bearing.

Furthermore, it may be provided that the first axial bearing is a roller bearing, in particular a needle bearing, preferably a ring bearing and / or a fluid bearing which is preferably acted upon or acted upon by a fluid pressure medium or fluid. In other words, therefore, both the first axial bearing and the second axial bearing can be designed as a, preferably hydrostatic, fluid plain bearings. This can be an even more cost effective and robust As well as space-saving design can be achieved, up to a construction in which an inventive locking cylinder is locked not only on pressure or only on train, but both pressure and train.

It may be of particular advantage that the first clamping cone body is at least partially received in a recess, in particular in a chamber, of the cylinder, preferably one or the cylinder bottom of the cylinder, on the one hand by a or the cylinder bottom of the cylinder Cylinder and on the other hand by a, preferably integrally connected to the cylinder or produced, in particular radially and transversely to the longitudinal axis of the cylinder or to the axis of rotation of the spindle extending approach is limited. As a result, an advantageous basis for a particularly preferred regulation or control of the locking and / or lift-off process can be created while still simpler and comparatively space-saving and robust construction.

This is particularly true when the approach between the first cone-clamping body and the piston is arranged.

These advantages and additionally particularly advantageous pressure conditions can be achieved in that the first clamping cone body is at least partially received in a recess, in particular a chamber, of the cylinder, preferably one or the cylinder bottom of the cylinder, into which the first fluid channel opens on a first side of the first clamping cone body, which is inclined to the axis of rotation of the spindle towards the first locking cone surfaces assigned. In other words, the first fluid channel can be arranged on that side of the first clamping cone body to which its or the first locking cone surfaces incline.

A further improvement in terms of the above advantages can be achieved by inserting into the recess on a second side of the first clamping cone body pointing away from the first side of the first clamping cone body, preferably immediately adjacent to the first locking cone body. Conical surfaces of the first clamping cone body, a second fluid channel opens, and wherein in the locked state, in which the clamping cone bodies abut against each other, the first fluid channel and the second fluid channel through a first locking cone surfaces containing Part of the first clamping cone body separated from each other, in particular sealed against each other.

Furthermore, it can be provided that a second fluid channel or the second fluid channel opens into the recess immediately adjacent to the first locking cone surfaces of the first clamping cone body.

A particularly advantageous pressure distribution can be achieved in that the first fluid channel or the second fluid channel opens in a region of the recess or the fluid plain bearing containing or cutting the axis of rotation of the spindle.

It may be particularly advantageous if the recess is sealed by a seal against the piston or against a or the working chamber, which is formed between the cylinder and the piston and the of the The first clamping cone body facing side of the piston, possibly also of the second bearing body and / or of the approach is limited and into which the working channel opens. As a result, the operability and reliability can be achieved or increased to a particular extent.

Similarly, this may alternatively or additionally be accomplished by having the first fluid channel and / or the second fluid channel opposite a working chamber formed between the cylinder and the piston and facing the first pinch-cone body Side of the piston, possibly also of the second bearing body and / or of the approach is limited and into which the working channel opens, is sealed by a or the seal or are.

It may be of particular advantage if the seal bears against a thread-free part of the spindle arranged between the first clamping cone body and the spindle thread and / or the piston and is supported on the second bearing body and / or on the projection.

According to a particularly preferred embodiment, it can be provided that the recess, viewed in a cross section containing the longitudinal axis of the cylinder or the axis of rotation of the spindle and viewed parallel to the longitudinal axis or to the axis of rotation, has a T-shaped cross section. As a result, it is possible to realize a locking cylinder which is particularly precise and locks securely, both from a functional point of view and from a safety point of view. The first clamping cone body and the second clamping cone body or the at least partially limited recess of this can preferably be designed rotationally symmetrical. The first clamping cone body can be designed rotationally symmetrical to the axis of rotation of the spindle and the second clamping cone body and / or at least partially limited recess can be designed rotationally symmetrical to the longitudinal axis of the cylinder or to the axis of rotation of the spindle ,

A further simplified, space-saving and robust construction can be achieved in that the first axial bearing and / or the second axial bearing is arranged in the recess and / or is formed with the recess bounding wall parts.

A further improved construction can be realized in that the first thrust bearing is arranged between the first clamping cone body and the second bearing body and / or the lug and / or that the second thrust bearing is arranged between the first clamping cone body and the lug ,

Particularly advantageous bearing and support conditions can be achieved in that the first thrust bearing is at least partially mounted in a bearing annular groove of the recess or formed or limited with a bearing annular groove of the recess.

For a functionally reliable operation of the locking cylinder, it may be of particular advantage if the first bearing surface of the first clamping cone body, viewed in a projection perpendicular to the axis of rotation of the spindle, ie in a direction parallel to the axis of rotation of the spindle Projection direction, is greater than a spindle surface of the spindle, which is located on the sealed by the seal of the first clamping cone body at least partially receiving recess side of the seal and in, preferably directly or directly, fluid connection with one or the working chamber is preferably acted upon by the pressure medium located in one or the working chamber, which is formed between the cylinder and the piston and of the side facing the first clamping cone body side of the piston. possibly also of one or the second bearing body and / or the approach is limited and opens into the working channel.

Alternatively or additionally, it may be provided that the first bearing surface of the first clamping cone body that can be acted upon or acted upon by the fluid pressure medium has an outer diameter and that the seal has an inner diameter, the outer diameter of the first bearing surface being larger, preferably much larger is, as the inner diameter of the seal or as the outer diameter of the unthreaded portion of the spindle against which the seal is applied and / or which is in fluid communication with the working chamber. As a result, the above-mentioned advantages can also be achieved or further improved.

A suitable for many or even all expected operating conditions axial bearing of the rotatable spindle, ie in any phase and in any position, even in case of failure of the hydraulic or in case of leakage, can be achieved if the fluid bearing during a movement of the piston both in the first direction as well as in the second direction and / or during one, preferably arbitrary, Rotation of the spindle about its axis of rotation, preferably in the course or during the stopping of the piston, in particular in any holding position of the piston, is acted upon or fluid fluid pressure medium is such that the clamping cone bodies are detached from each other, in particular, are lifted apart from each other so that their locking cone surfaces do not touch, preferably so that the spindle is then unlocked.

A particularly advantageous unlocking of the self-locking and friction locked by static friction clamping cone body can be achieved that at least one of the clamping cone body of a locking position in which the locking cone surfaces of the clamping cone body by frictionally Stiction with each other self-locking connected or jammed, are, preferably exclusively, by acting on the hydrostatic fluid bearing with the fluid pressure medium, in particular under elevated pressure, in a, preferably a rotation of the spindle about its axis of rotation relative to the cylinder enabling, unlocking position can be transferred is or be transferred. In this way, it is thus possible to release the initially self-locking locked cone-cone body at least so far in the axial direction of each other, that in principle rotation of the spindle relative to the cylinder and thus therefore an unlocking of the spindle can be reached, wherein still one frictional connection between the corresponding clamping cone bodies can be maintained or can be. Consequently, therefore, the friction between the corresponding clamping cone bodies can also be stepped or continuously regulated.

Furthermore, it can be provided that at least one of the clamping cone body from a locking position in which the locking cone surfaces of the clamping cone body are frictionally connected by friction with each other self-locking or clamped, preferably exclusively, by an application of the hydrostatic fluid bearing bearing with the fluid pressure medium, preferably under elevated pressure, in a, preferably a rotation of the spindle about its axis of rotation relative to the cylinder enabling, lifting and unlocking position are transferred, in which the clamping cone bodies are lifted from each other, so that their locking cone surfaces no longer touch. Consequently, in this way, a complete unlocking of the corresponding clamping cone body can be realized, so that then takes place between the corresponding clamping cone bodies virtually no friction, you see once of the usually negligible friction by between the Clamp-cone bodies available pressure medium.

According to a preferred embodiment of the invention can be provided that in a housing, preferably in a provided in the region of the thrust bearing and / or cylinder bottom of the cylinder or in the cylinder bottom end housing, fluid channels or flow and connection channels and a control unit forming control and / or control elements between connecting lines or holes for an alternating supply or discharge of the pressure medium and fluid channels or lines to both sides of the piston provided working chambers and the fluid bearing are arranged. These measures give a particularly compact unit. Due to the integration of the control unit, external control and / or regulating organs together with the associated, susceptible to damage lines omitted or they are not needed. The mounting safety is improved at one and at the same time reduced installation costs.

According to a particularly preferred development, it can be provided that the, preferably all, control and / or regulating members of the control unit are self-medium-actuated or self-medium-controlled by the pressure medium. In this way, you get a more space-saving and robust as well as more cost-effectively manufacturable construction. Preferably can be completely dispensed with electrical lines. The locking cylinder can preferably be safely operated exclusively by means of a pump for the pressure medium for a long time.

It can preferably be provided that a means for releasing a first passageway between the fluid channel and a first connection channel of the connection channels and for, preferably substantially simultaneous, blocking a second passageway between a fluid channel fluid-fluid bearing fluid channel and two alternately serving as a flow channel or return channel between the fluid channel and a second connection channel of the connection channels or for releasing the second passageway between the fluid channel and the second connection channel and for, preferably substantially simultaneous, blocking the first passageway between the fluid channel and the first connection channel is arranged. Such a means may preferably be a shuttle valve and / or such means may be formed with double check valves. This allows an even more compact and robust construction be achieved in conjunction with long-term safe operation.

According to a particularly preferred embodiment of the invention can be provided that between the first fluid channel, which is when the locking-supporting body or the clamping cone body are clamped together, shut off from the fluid fluid with the fluid bearing fluid channel and the when the interlocking support bodies and the clamping conical bodies are lifted apart from one another, is fluidically connected to the fluid channel, and a second fluid channel, which is in fluid communication with one or the working chamber, preferably with one or the second working chamber fluidly connected between the piston and a lid of the cylinder associated with the free end of the spindle, means for switching or releasing or, if necessary, throttling or releasing a passageway between the first fluid channel and the second fluid channel, is arranged. Such a means may preferably be a shut-off valve or a throttle / passage changeover valve, in particular a 2-2-way valve. This can preferably be coupled or fluid-connected to a switching or actuating channel, by means of which, when it is acted upon by the pressure medium, switching from a passage position into a blocking position or from a passage position into a throttle position can be achieved. As a result, even safer operation of the locking cylinder according to the invention can be realized.

The invention also relates to a method for non-rotatable frictional locking of the rotatable about its axis of rotation Spindle of the locking cylinder having the features of at least one claim of Claims 1 to 7 against rotation about the axis of rotation relative to the cylinder, at least one of the locking support bodies being unlocked to permit rotation of the spindle about its axis of rotation relative to the cylinder. Preferably, in one or the axial direction parallel to the axis of rotation of the spindle or to the longitudinal axis of the cylinder, transferred into a locking position, preferably displaced, is in which the locking-support body frictionally locked by static friction and thus clamped together self-locking, that they can only be transferred into the unlocked position by exercising release forces that release the deadlock. By such a method, a particularly simple and secure locking of the spindle and consequently of the piston relative to the cylinder can be achieved.

In a further development of this method, it can be advantageously provided that at least one of the locking support bodies is parallel to an unlocking position, in which the spindle is freely rotatable about its axis of rotation relative to the cylinder, preferably in one or the axial direction to the axis of rotation of the spindle or to the longitudinal axis of the cylinder is transferred to the locking position in which the locking support body frictionally jammed by static friction and are clamped together so self-locking that you only under exercise of the clamping solving dissolving forces in the Unlocked position in which the spindle about its axis of rotation relative to the cylinder is substantially freely or freely rotatable.

Furthermore, it can be provided that the locking-cone surfaces having locking-support body from a lifting and unlocking position in which the locking-support body are lifted apart from each other so that their locking-cone surfaces do not touch, preferably in one or the axial direction parallel to the axis of rotation of the spindle or to the longitudinal axis of the cylinder, be transferred to an investment and locking position, in which the locking cone surfaces of the locking support body abut each other and non-rotatably by friction friction and are clamped together so self-locking that you can be transferred only under exercise of the clamping release separating forces in the Abhebe- and unlocked position.

The invention also relates to a method for unlocking the non-rotatably and frictionally, ie non-positively by friction, and by gravity, preferably by a load acting on the piston, automatically, preferably without drive, in particular without the action or support of force accumulators, such as springs, against rotation about its axis of rotation relative to the cylinder of the locking cylinder having the features of at least one claim of claims 1 to 7, locked spindle, wherein the spindle is locked in the locked state by means of the locking support body frictionally against rotation about its axis of rotation relative to the cylinder wherein the latch support bodies receive axial forces acting on the spindle in the second direction, preferably such that the spindle is locked in the locked state against movement in the second direction on the cylinder, the latch support bodies be transferred to an unlocking position in which the spindle is rotatable about its axis of rotation relative to the cylinder, and wherein at least one of the locking-supporting body from a locking position in which the locking-supporting body frictionally by friction against rotation and thus self-locking with each other are clamped that they only under exercise of the clamping solving dissolving forces, preferably in one or the axial direction parallel to the axis of rotation of the spindle or to the longitudinal axis of the cylinder in a rotation of the spindle about its axis of rotation relative to the cylinder enabling unlocking position can be transferred, transferred to the unlocked position, preferably moved, is. As a result, a clamping connection according to the invention can be particularly easily released or unlocked.

The unlocking can be achieved in a particularly simple manner in that the locking-supporting body of the locking position in which they are frictionally clamped by friction with each other self-locking, preferably exclusively, by applying the hydrostatic fluid bearing with the fluid pressure fluid under elevated pressure, preferably in one or the axial direction parallel to the axis of rotation of the spindle or to the longitudinal axis of the cylinder, into a rotation of the spindle about its axis of rotation relative to the cylinder enabling unlocking position are transferred or transferred to an unlocking, in which is relatively free to rotate freely relative to the cylinder.

Furthermore, it can be provided that the locking-cone surfaces having locking-support body of the Locking position in which they are frictionally clamped by friction with each other self-locking, preferably exclusively, by acting on the hydrostatic fluid bearing with the fluid pressure fluid under increased pressure, preferably in one or the axial direction parallel to the axis of rotation of the spindle or to the longitudinal axis the cylinder, in a, preferably a rotation of the spindle about its axis of rotation relative to the cylinder enabling, lifting and unlocking position are transferred, in which the locking support body are lifted from each other, so that their locking-cone surfaces no longer touch.

According to a particularly preferred implementation of the unlocking can be provided that, preferably by means of a or the control device, first the fluid bearing is subjected to the pressure medium to allow rotation of the spindle about its axis of rotation relative to the cylinder and / or order a lifting of the locking-support body or the clamping cone body from the locking position in which they are frictionally clamped together by friction with each other, to effect in a lifting and unlocking, in which the locking support body or the Clamping cone body are lifted apart from each other so that their locking cone surfaces at least partially no longer touch, and that only then the pressure medium is supplied to a working chamber, which is assigned to one side of the piston, preferably limited by this is, either about a movement of the piston in an axial direction parallel to the length axis of the cylinder or parallel to the axis of rotation of the spindle to enable or effect or whereby a movement of the piston in the axial direction enables, supports or effects. Such a procedure has particular advantages when the piston or the piston rod is to be moved axially, in particular in the direction of a load to be moved, in particular in order to minimize operational wear or to allow any axial movement of the piston or the piston rod.

In a particularly preferred embodiment, the fluid bearing can first be acted upon by one or the fluid channel or supply channel with the pressure medium, whereby a lifting of the locking support body or the clamping cone body, from the locking position in which they by frictional Stiction are clamped together, in a lift-off and unlocking, is effected, in which the locking-support body or the clamping cone body are at least partially lifted from each other, so that their locking-cone surfaces at least partially no longer touch and thereby opening or forming a passageway or gap between and along the opposite in the off-hook locking-cone surfaces, which is fluidly connected to one or the fluid channel or discharge channel, preferably via one or the Working channel, is fluidly connected to the working chamber or, so that the piston with the is acted upon by the fluid or discharge channel in the working chamber or flowing pressure medium, either to allow movement of the piston in an axial direction parallel to the longitudinal axis of the cylinder or parallel to the axis of rotation of the spindle to support or effect , or whereby a movement of the piston in the axial direction allows, is supported or effected. This can be especially compact and inexpensive construction a particularly safe operation can be realized.

In a particularly advantageous development, it can be provided that the locking support bodies are designed as self-locking or self-locking clamping cone body.

According to the invention can also be provided that a plurality of first clamping cone bodies, preferably of two first clamping cone bodies rotatably connected to the spindle or fixed to the spindle and that one, preferably numerically corresponding, plurality of second clamping Cone bodies, preferably of two second clamping cone bodies, rotatably connected to the cylinder or are fixed to the cylinder. Furthermore, it can be provided that the first clamping cone bodies are designed and manufactured in one piece as a clamping double cone body. Alternatively or additionally, it can be provided that the first clamping cone body and / or that the second clamping cone body is or are each designed as a clamping double-cone body. By the above measures, a locking cylinder can be realized, which is lockable both on pressure and on train in the manner according to the invention. Preferably, the clamping double-conical body or bodies may be formed symmetrically to an axis or plane perpendicular to the axis of rotation of the spindle or perpendicular to the longitudinal axis of the cylinder. Furthermore, it can be provided that the clamping cone body, in particular of the clamping double-cone body, are each designed as an outer cone or as an inner cone. The locking cone surfaces of the clamping cone body, in particular of the clamping double-cone body, can form or enclose with the axis of rotation of the spindle or with the longitudinal axis of the cylinder a different angle of inclination or, preferably, an equally large angle of inclination. The locking conical surfaces of the clamping cone bodies, in particular of the respective clamping double-cone body, may point in the same or preferably in different directions. The locking cone surfaces of the clamping cone bodies, preferably a first clamping double cone body, may face away from each other and the locking cone surfaces of the clamping cone body, preferably a second clamping double cone Body, can face each other or face each other.

Alternatively, it can be provided that the locking conical surfaces of the clamping cone body, preferably a first clamping double-cone body, facing each other or can face each other and that the locking conical surfaces of the clamping cone Body, preferably a second clamping double-cone body, facing away from each other.

It is understood that the above features in the context of executability individually or in any combination can be combined with each other.

Further features, 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 auf Druck verriegelbaren Verriegelungszylinder in einem Längsquerschnitt in einer teilweise schematisierten Darstellung;

Fig. 2

einen erfindungsgemäßen auf Zug verriegelbaren Verriegelungszylinder in einem Längsquerschnitt in einer teilweise schematisierten Darstellung;

Fig. 3

einen auf Druck verriegelbaren Verriegelungszylinder in einer Ansicht gemäß Fig. 1, mit einer schematischen Darstellung einer integrierten Steuereinheit;

Fig. 4

einen auf Zug verriegelbaren Verriegelungszylinder in einer Ansicht gemäß Fig. 2, mit einer schematischen Darstellung einer integrierten Steuereinheit.

Show it:

Fig. 1

a pressure-lockable locking cylinder according to the invention in a longitudinal cross-section in a partially schematized representation;

Fig. 2

a lockable lock cylinder according to the invention in a longitudinal cross section in a partially schematic representation;

Fig. 3

a pressure lockable lock cylinder in a view according to Fig. 1 with a schematic representation of an integrated control unit;

Fig. 4

a lockable on train locking cylinder in a view according to Fig. 2 , with a schematic representation of an integrated control unit.

In FIG. 1 is a lockable pressure lock cylinder 20 and in FIG. 2 a lockable on train locking cylinder 120 is illustrated in each case in a longitudinal cross-section. Identical components, elements and directional arrows are provided with the same reference numerals. Different components, elements and arrows are designated in the train lockable locking cylinder 120 with 100-numerals, while corresponding components, elements and arrows are designated in the pressure-lockable locking cylinder 20 with 10-digits.

Each locking cylinder 20, 120 comprises a cylinder and a displaceable therein in the axial direction 59, but non-rotatably mounted to the cylinder 21 piston 22. Der Piston 22 is sealed relative to the cylinder inner wall of the cylinder 21 by a ring seal 37 and on its in the direction of the longitudinal axis 25 of the cylinder 21 facing away from each other sides 23.1, 23.2 by a fluid, in particular hydraulic, pressure medium, preferably oil, acted upon by a pressure medium assisted To allow movement of the piston 22 in a first direction 31 or in a second direction 32. In the pressure-lockable lock cylinder 20, the first direction 31 is the extension direction and the second direction 32 is the retraction direction of the piston 22. In contrast, the lock-lock cylinder 120 is the first direction 31 the retraction direction and in the second direction 32 about the extension direction of the piston 22. The pressure medium can be supplied via a first working channel 24.1 on the cylinder bottom 40 facing side 23.1 of the piston 22 in a first working chamber 48 to a movement of the piston 22 along the Cylinder 21 in the second direction 32 to achieve. In addition, the pressure medium via a second working channel 24.2 on a second side 23.2 of the piston 22, which points away from the first side 23.1, fed into a second working chamber 49 to achieve a movement of the piston 22 along the cylinder 21 in the first direction 31 to be able to.

The first working chamber 48 is sealed relative to the second working chamber 49 via a ring seal 37 of the piston 22. The seal 37 is supported in an annular groove of the piston 22 that is open outwards to the cylinder jacket inner wall. The piston 22 forms a projection which is non-rotatably connected to the piston rod 22.1. The piston rod 22.1 extends from the annular second side 23.2 of the piston 22 in the axial direction 59 coaxial with the longitudinal axis 25 of the cylinder 21 and to the rotational axis 33 of the spindle 30. The piston 22 is designed as a tubular hollow body and has a designated as a piston thread 26 internal thread. The piston 22 may also be referred to as a piston nut. The piston thread 26 is engaged with an external thread, also referred to as a spindle thread 28, of the spindle 30, on which the piston 22 is guided. The piston thread 26 and the spindle thread 28 form a non-self-locking thread 27. Preferably, the non-self-locking thread 27 is designed right-handed, but can also be designed left-handed. Preferably, the piston thread 26 and the spindle thread 28 in each case as one, 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 at its the free end 71 of the spindle 30 associated side by a piston rod 22.1 receiving cover 40.1. This can, as shown in the figures, be integrally connected to the cylinder 21 or produced; However, it can also be connected in several parts with the cylinder 21. The ring-shaped piston cover 40.1 surrounds the piston rod 22.1 and has an open towards the piston rod 22.1 annular groove. In this annular groove, a ring seal 60 is supported, which seals the second working chamber 49 to the outside. On its other side, the cylinder 21 is closed by a lid or head forming the cylinder bottom 40. This can preferably be connected in several parts with the cylinder 21.

The spindle 30 is arranged about a parallel to the longitudinal axis 25 of the cylinder 21 arranged rotational axis 33 relative to the cylinder 21 and is also relatively axially displaceable relative to the cylinder 21 in the axial direction 59 or parallel to the longitudinal axis 25 of the cylinder 21. In the exemplary embodiments shown, the axial displaceability of spindle 30 indicated by double arrow 34 or the axial spindle clearance is only about 1.0 to 1.5 mm. The spindle 30 is frictionally, ie non-positively by friction, and in the embodiments shown exclusively by gravity, in particular by a force acting on the piston 22 load 29, 129, automatically or automatically, drive-free and without the action or support of power stores, such. B. tension or compression springs, lockable. In other words, the spindle 30 is self-locking lockable and indeed double-self-locking according to the invention.

For this purpose, first in the region of the end 69 of the spindle 30 pointing away from the free end 71 of the spindle 30, which is the cylinder-bottom-side end 69 of the spindle 30, two locking support elements which can be converted into a mutual frictional locking engagement are provided. Body 35, 36; 135, 136 provided. These are intended to be able to lock the spindle 30 frictionally against rotation about its axis of rotation 33 and to be able to absorb axial forces acting on the spindle 30 in the second direction 32, in the embodiments shown such that the spindle 30 is in the locked state secured against movement in the second direction 32 secured to the cylinder 21, here at the cylinder bottom 40, is supported. The first lockup support body 35, 135 of the lockup support bodies 35, 36; 135, 136 is rotatably, preferably rigidly connected to the spindle 30 and secured to the spindle 30. The second Lockup support body 36; 136, the lockup support bodies 35, 36; 135, 136 is non-rotatably, preferably rigidly connected to the cylinder 21 or to the cylinder bottom 40 or attached to the cylinder 21, here on the cylinder base 40, preferably in one piece.

The spindle 30 is here at two axial bearings 38 spaced apart in the axial direction 38, 39; 138, 139 stored. A first thrust bearing 38; 138 is intended to receive axial forces acting on the spindle 30 in the first direction 31. The second thrust bearing 39; 139, the thrust bearings 38, 39; 138, 139 is intended, in its function as a fluid sliding bearing, to receive axial forces acting on the spindle 30 in the second direction 32.

The spindle 30 is further provided with a first bearing body 41; 141 provided, the first bearing surface 43; 143 having a second bearing surface 44; 144 a rotationally fixed, preferably rigid, connected to the cylinder 21 and attached to the cylinder 21 second bearing body 42; 142, here the cylinder bottom 40, opposite. The first bearing surface 43; 143 of the first bearing body 41; 141 and the second bearing surface 44; 144 of the second bearing body 42; 142 form the second thrust bearing 39; 139 off. The second thrust bearing 39; 139 is inventively as a, preferably hydrostatic, fluid bearings 45; 145 designed, in particular via a first fluid channel 46; 146 is acted upon with or with the fluid pressure medium. According to the invention, the first locking-supporting body 35; 135 as a first locking cone surface 51; 151, self-locking or self-locking acting, first clamping cone body 53; 153 and the second lock-up support body 36; 136 is as a second Locking cone surfaces 52; 152, self-locking or self-locking acting, second clamping cone body 54; 154 designed. The locking cone surfaces 51, 52; 151, 152 of these clamping cone bodies 53, 54; 153, 154 can be clamped together self-locking. For this purpose, in each case fixed in rotation with the spindle 30 clamp-cone body 53; 153 are displaced in the first direction 32 parallel to the longitudinal axis 25 of the cylinder 21 until its locking cone surfaces 51; 151 at the opposite, counter-surface forming locking cone surfaces 52; 152 of the second clamp-cone body 54; Abut 154, wherein the clamping cone body 53, 54; 153, 154 can be frictionally clamped by friction with each other self-locking or can be. It is in this way not only frictional self-locking locking of the spindle 30 with respect to a rotation about its axis of rotation 33 relative to the cylinder 21 feasible, but also a locking of the spindle 30 against a movement or displacement in the axial direction 59, in particular in the first Direction 31. The lock according to the invention is thus a kind of double-self-locking lock.

The clamping cone bodies 53, 54; 153, 154 are each frustoconical shaped. The first clamping cone body 53; 153, the rotatably connected to the spindle 30 and rotatably attached to the spindle 30 is here in each case as a conical disk or as a cone-butt-disk 55; 155 designed. The respective first clamping cone body 53; 153 and the respective second clamping cone body 54; 154 are rotationally symmetrical to the axis of rotation 33 of the spindle 30 and to the longitudinal axis 25 of the cylinder 21 designed.

The respective first clamping cone body 53; 153 is in each case in a designed as a chamber recess 75; 175 of the cylinder bottom 40 received or arranged. The recess 75 is preferably also rotationally symmetrical to the longitudinal axis 25 of the cylinder 21 and to the axis of rotation 33 of the spindle 30 designed. The respective first clamping cone body 53; 153 is rotatably connected to or fixed to a non-threaded portion 50 of the spindle 30, which in turn rotatably connected to the spindle thread 28 having part of the spindle 30 is connected or attached thereto. The not provided with a spindle thread portion 50 of the spindle 30 is in a bore of a radially inwardly and transversely to the longitudinal axis 25 of the cylinder 21 extending projection 72; 172 recorded. The approach 72; 172 is here between the respective first clamping cone body 53; 153 and the first working chamber 48 is arranged. The approach 72; 172 has an open to the unthreaded portion 50 of the spindle 30 annular groove on the wall, a ring seal 76 is supported. About the ring seal 76, the respective recess or chamber 75; 175 sealed against the first working chamber 48.

In the illustrated embodiments, the first lockup support body 35; 135 and the first bearing body 41; 141 made in one piece and each form a common first locking support and bearing body 61; 161 out, here in the form of the clamping cone disc 55; 155. Also formed by a part of the cylinder bottom 40 second locking support body 36; 136 and the second bearing body 42; 142 are made in one piece and form a common second locking support and bearing body 62; 162 off. The first lockup support and bearing body 61; 161 as a first locking cone surfaces 51; 151 comprising self-locking or self-locking acting first clamping cone body 53; 153 formed and the second locking support and bearing body 62; 162 is referred to as a second locking cone surface 52; 152 having, self-locking or self-locking second clamping cone body 54; 154 trained.

The first locking cone surfaces 51; 151 of the rotatably connected to the spindle 30 first clamping cone body 53; 153 close with the axis of rotation 33 of the spindle 30, a first inclination angle 63; 163. The second locking cone surfaces 52; 152 of the cylinder bottom side clamping cone body 54; 154 close to the longitudinal axis 25 of the cylinder 21 and with the axis of rotation 33 of the spindle 30 has a second inclination angle 64; 164. The inclination angle 63; 163 of the locking cone surfaces 51; 151 of the rotatably connected to the spindle 30 first clamping cone body 53; 153 and the inclination angle 64; 164 of the locking cone surfaces 52; 152 of the rotatably connected to the cylinder 21 second clamping cone body 54; 154 are the same size and here are each preferably about 6.5 degrees. At these inclination angles 63, 64; 163, 164 or more generally at angles of inclination of about 4 to 13 degrees, preferably from 4 to 10 degrees, can be, depending on the selected material pairing and other parameters in juxtaposition or nesting of the first clamping cone body 53; 153 and the second clamping cone body 54; 154 to achieve a self-locking in such a way that the first clamping cone body 53 and the second clamping cone body 54 and that the first clamping cone body 153 and the second clamping cone body 154 is no longer relative to each other around the Longitudinal axis 25 and about the axis of rotation 33 are rotatable and also no longer relative to each other can be moved or displaced in the axial direction 59, that is also not in the first direction 31, ie here in a direction away from each other. Because it then enters a self-locking by jamming of the respective two clamping cone body 53, 54 and 153, 154 a.

The first clamping cone body 53; 153 is as outer cone 56; 156 formed while the second clamping cone body 54; 154 as an inner cone 57; 157 is formed. In the pressure-lockable lock cylinder 20, the first clamp-cone body 53 tapers conically toward the rotational axis 33 of the spindle 30 and toward the cylinder bottom 40 of the cylinder 21. In contrast, the first clamping cone body 153 of the train lockable lock cylinder 120 tapers toward the piston 22 and away from the cylinder bottom 40 but also toward the rotation axis 33 of the spindle 30. In the pressure-lockable lock cylinder 20, the first lock-taper surfaces 51 of the first clamp-cone body 53 non-rotatably connected to the spindle 30 are in the direction away from the piston 22 and toward the cylinder bottom 40 of the cylinder 21 Arranged side 65 and the second locking cone surfaces 52 of the rotatably connected to the cylinder 21 second clamping cone body 54 are in the direction. to the piston 22 and from the cylinder bottom 40 facing away side 66 is arranged. In contrast, in the lockable on train lock cylinder 120, the first locking cone surfaces 151 of the rotatably connected to the spindle 30 first clamping cone body 153 facing in the direction of the piston 22 and away from the cylinder bottom 40 away Page 165 arranged and the second locking cone surfaces 152 of the rotatably connected to the cylinder 21 second clamping cone body 154 are arranged on its in the direction of the piston 22 away or to the cylinder bottom 40 side facing 166.

In the lockable pressure cylinder lock cylinder 20, the second bearing body 42 is formed with a part of the cylinder bottom 40 of the cylinder 21, while in the train lockable lock cylinder 120, the second bearing body 142 as the, preferably integrally connected to the cylinder 21 or manufactured itself radially inwardly and transversely to the longitudinal axis 25 of the cylinder 21 and to the axis of rotation 33 of the spindle 30 extending lug 172 is formed.

In the locking cylinders 20; 120 is the respective first clamping cone body 53; 153 via the first thrust bearing 38; 138 on the fixed, preferably rigid, connected to the cylinder 21 approach 72 or cylinder bottom 40 stored. The first thrust bearing 38, 138 in the exemplary embodiments shown is in each case a roller bearing designed as a needle bearing in the form of a ring bearing. This needle bearing is partially received in each case in a bearing annular groove 78, 178, which is formed coaxially to the longitudinal axis 25 of the cylinder 21. The bearing groove 78; 178 delimits each chamber or recess 75; 175th

The respective recess 75; 175, in which the respective first clamping cone body 53; 153 axially slidably received or arranged in the axial direction 59, on the one hand by a part of the cylinder bottom 40 of the cylinder 21 and on the other hand by the respective projection 72; 172 limited. This chamber or recess 75; 175 has a T-shaped cross section 77; 177 on.

In the case of the pressure-lockable locking cylinder 20, a first fluid channel 46, via which the fluid sliding bearing 45 can be acted upon by pressure medium, opens into a region of the recess 75 containing the longitudinal axis 25 of the cylinder 21. Accordingly, this first fluid channel 46 opens a first side 65 of the first clamping cone body 53, the one of the axis of rotation 33 of the spindle 30 inclined toward first locking cone surfaces 51; 151 is assigned. In the region of the other side 66 of the first clamping cone body 53, a second fluid channel 47 opens into the recess 75, specifically here immediately adjacent to the first locking cone surfaces 51 of the first clamping cone body 53. In the locked state in which the locking cone surfaces 51; 52, the clamping cone body 53; 54 abut each other, the first fluid channel 46 and the second fluid channel 47 are separated by a first locking cone surfaces 51 containing part of the first clamping cone body 53 from each other and sealed from each other.

By contrast, in the case of the locking cylinder 120 which can be locked in tension, a situation which is basically or approximately 180 degrees results around a situation normal to the longitudinal axis 25 of the cylinder 21 or to the axis of rotation 33 of the spindle 30. Accordingly, there opens the first fluid channel 146 immediately adjacent to the first locking cone surfaces 151 of the first clamping cone body 153 in the recess 175, ie on the first side 165 of the first clamping cone body 153, the approach 172nd opposite. On the other side 166 of the first clamping cone body 153 opens in the recess 175, a second fluid channel 147, in a longitudinal axis 25 of the cylinder 21 containing or cutting portion of the recess 175. When the clamping cone bodies 153 and 154 are clamped against each other abutting each other, the first fluid channel 146 of separated from and sealed to the second fluid channel 147 by a portion of the first clamping cone body 153 containing the first locking cone surfaces 151.

Viewed in a projection perpendicular to the axis of rotation 33 of the spindle 30, ie in particular in one of the sheet plane of the FIGS. 1 and 2 corresponding cutting plane, the first bearing surface 43; 143 of the first clamping cone body 53; 153 larger than a spindle surface of the spindle 33, which is on the by the seal 76 of the first clamping cone body 53; 153 at least partially receiving recess 75; 175 sealed side 83 of the seal 76, said seal 76 is in fluid communication with the first working chamber 48. In this spindle surface is an annular surface which is bounded on the one hand in the radial direction by the cylindrical outer surface of the not provided with the spindle thread portion 50 of the spindle and on the other hand with the outer diameter or external thread 28 of the spindle 30. The acted upon by the fluid pressure medium first bearing surface 43; 143 of the first clamping cone body 53; 153 has an outer diameter 80; 180, which is larger, is preferably much larger than the inner diameter 81 of the seal 76 or as the outer diameter 82 of the unthreaded portion 50 of the spindle 30th

Hereinafter, the operation of the lock cylinder 20; 120 described in more detail, starting with the lockable on pressure lock cylinder 20:

In the idle state, in which neither the working channel 24.1 nor the fluid channel 46 is subjected to pressure under pressure, ie when the pressure medium system is pressureless, the spindle 30 is double-self-locking against the cylinder 21 against rotation about its axis of rotation 33 and against lifting locked in the first direction 31 jammed. Starting from this locking position can now, for example, for the purpose of extending the piston 22 and lifting the load 29 in the first direction 31, pressure medium either first via the first fluid channel 46 and then thereafter via the first working channel 24.1 or preferably simultaneously via the first fluid channel 46 and the first working channel 24.1 are supplied, so that accordingly either first the recess 75 and then the first working chamber 48 is acted upon with pressure medium or preferably by the recess 75 and the first working chamber 48 are acted upon simultaneously with pressure medium. In the course of this, the self-locking jamming between the rotatably connected to the spindle 30 first clamping cone body 53 and the rotatably connected to the cylinder 21 second clamping cone body 54 is released, whereupon the spindle 30, optionally also the piston 22 at the same time , shifted in the first direction 31, that is raised here or be. In this case, there is initially no or substantially no rotation of the spindle 30 about its axis of rotation 33 relative to the cylinder 21. However, as soon as, or at the latest, when the first clamping cone body 53 connected to the spindle 30 is connected to the rolling bearing 38 comes to the plant, the begins Spindle 30 due to friction about its axis of rotation 33 to rotate. As a result of this and due to the threaded coupling with the spindle 30 via the non-self-locking thread 27, the piston 22 can move in the first direction 31, ie here in the extension direction or upwards, whereby the load 29 can be lifted. In the course of this displacement of the piston 22 in the first direction 31 pressure fluid flows through the first working channel 24.1 in the first working chamber 48 and at the same time in the second working chamber 49 optionally located pressure medium flows through the second working channel 24.2. During this movement of the piston 22 in the first direction 31, the fluid sliding bearing 39 is or are subjected to pressure medium in such a way that the clamping cone bodies 53, 54 are detached from one another, in particular lifted off from one another in such a way that their locking Do not touch the conical surfaces 51, 52, so that then the locking cone surfaces 51, 52 are in a lifting and unlocking.

If the piston 22 moving in the first direction 31 is now to be stopped, then the first working channel 24.1 can be depressurized. If both the first working channel 24.1 and the first fluid channel 46 are depressurized, the piston 22 together with the spindle 30 and rotatably connected thereto first first clamping cone body 53 due to the direction of gravity, ie in the second direction 32nd , acting load 29 in the second direction 32, by the intended small axial play from here about only 1.0 to 1.5 mm, until the first clamping cone body 53 at or in the second clamping cone Body 54 self-locking jammed stuck.

It is understood, however, that optionally only the first working channel 24.1 can be depressurized, but not the first fluid channel 46, so that then during the stopping of the piston 22, the fluid bearing 45 is still acted upon with pressure medium and will and accordingly with the Spindle 30 rotatably connected first clamping cone body 53 can still be kept lifted from the second clamping cone body 54 or possibly regulated, can be held in an intermediate position in which a brake friction but not jamming the Clamping cone body 53, 54 occurs.

For moving the piston 22 in the second direction 32, that is here in the retraction direction for the purpose of lowering the load 29 or only for the purpose of retraction of the piston 22, pressure medium can be supplied via the first fluid channel 46, wherein only then or simultaneously pressure medium can be supplied in the second working channel 24.2. Thereby, the rotatably connected to the spindle 30 first clamping cone body 53 together with the threaded spindle 30 and the piston 22 in the first direction 31 are moved or raised, in turn until the first clamping cone body 53 on the rolling bearing 38th comes to the plant, whereupon the spindle 30 begins to rotate together with the rotatably connected with it first clamping cone body 53 in the now opposite direction, whereupon the piston 22 together with the load 29 in the second direction 32, ie here in Einfahrrichtung is moved. In this case, the pressure medium located in the first working chamber 48 can flow out via the first working channel 24.1.

During the movement of the piston 22 in the second direction 32, the first fluid channel 46 is always with pressure medium acted upon, so that in this case the fluid-sliding bearing 45 is constantly acted upon with pressure medium and at the same time rotatably connected to the spindle 30 first clamping cone body 53 of the non-rotatably connected to the cylinder 21 second clamping cone body 54 in a lift - And unlocked position is lifted, in which their locking cone surfaces 51, 52 do not touch, so that is then the first clamping cone body 53 and the spindle 30, preferably substantially free to the spindle rotation axis 33 relative to the cylinder 21 can rotate.

When the fluid sliding bearing 45 is formed by acting on the first fluid channel 46 with pressure medium and thereby the first clamping cone body 53 is lifted from the second clamping cone body 54 such that their locking conical surfaces 51, 52 no longer touching, the pressure medium supplied through the first fluid channel 46 of the recess 75 through a then formed between the locking cone surfaces 51 and 52 of the clamping cone body 53 and 54 ring gap through and then ßend by the second Flow fluid channel 47.

For stopping the piston 22 moving in the second direction 32, both the second working channel 24.2 and the first fluid channel 46 can now be depressurized, so that the spindle 30, together with the first clamping cone, is immediately caused by the acting load 29 -Body 53 moves in the second direction 32, again only to the small spindle-shifting play from here about 1.0 to 1.5 mm, until the first clamping cone body 53 at or in the second terminal Cone body 54 self-locking jammed stuck. Then the spindle 30 is against rotation by this self-locking clamp lock locked about its axis of rotation 33 relative to the cylinder 21 as well as against an axial lifting in the axial direction 59, ie in the first direction 31, so that in turn also a double self-locking is achieved.

The operation of the lockable lock cylinder 120 will now be described in more detail.

In the idle state in which neither the working channel 24.1 nor the fluid channel 146 is pressurized, ie when the pressure medium system is pressureless, the spindle 30 is double-self-locking against the cylinder 21 against rotation about its axis of rotation 33 and against lifting locked in the first direction 31 jammed. Starting from this locking position can now, for example, for the purpose of retraction of the piston 22 and lifting the load 129 in the first direction 31, pressure medium either first via the first fluid passage 146 and then via the second working channel 24.2 or preferably simultaneously via the first fluid channel 146 and be supplied to the second working channel 24.2, so that accordingly either first the recess 175 and then the second working chamber 49 is acted upon by pressure medium or by preferably the recess 175 and the second working chamber 49 are acted upon simultaneously with pressure medium. In the course of this, the self-locking jamming between the rotatably connected to the spindle 30 first clamping cone body 153 and the rotatably connected to the cylinder 20 second clamping cone body 154 is released, whereupon the spindle 30, optionally also the piston 22 at the same time , shifted in the first direction 31, that is raised here or be. there At first, however, there is no or substantially no rotation of the spindle 30 about its axis of rotation 33 relative to the cylinder 21. However, as soon as or at the latest when the first clamping cone body 153 connected to the spindle 30 rotates against the rolling bearing 138 comes to rest, the spindle 30 begins to rotate due to friction about its axis of rotation 33. As a result of this and due to the threaded coupling with the spindle 30 via the non-self-locking thread 27, the piston 22 can move in the first direction 31, ie here in the retraction direction or upwards, whereby the load 129 can be lifted. In the course of this displacement of the piston 22 in the first direction 31 pressure fluid flows through the second working channel 24.2 in the second working chamber 49 and at the same time in the first working chamber 48 optionally located pressure medium flows through the first working channel 24.1. During this movement of the piston 22 in the first direction 31, the fluid sliding bearing 139 is or are subjected to pressure medium in such a way that the clamping cone bodies 153, 154 are detached from one another, in particular lifted off from one another in such a way that their locking Do not touch cone surfaces 151, 152 so that then the locking cone surfaces 151, 152 are in a lifting and unlocking.

If the piston 22 moving in the first direction 31 is now to be stopped, then the second working channel 24.2 can be depressurized. If both the second working channel 24.2 and the first fluid channel 146 are depressurized, the piston 22 together with the spindle 30 and rotatably connected thereto first clamping cone body 153 due to the in the direction of gravity, ie in the second direction 32nd , acting load 29 in the second direction 32 from, namely by the intended low axial play from here about only 1.0 to 1.5 mm, until the first clamping cone body 153 on or in the second clamping cone body 154 self-locking jammed stuck.

It is understood, however, that optionally only the second working channel 24.2 can be depressurized, but not the first fluid channel 146, so that then during the stopping of the piston 22, the fluid bearing 145 is still acted upon with pressure medium and is and accordingly with the Spindle 30 rotatably connected first clamping cone body 153 can still be kept lifted from the second clamping cone body 154 or possibly regulated, can be held in an intermediate position in which a brake friction but not jamming the Clamping cone body 153, 154 enters.

For moving the piston 22 in the second direction 32, ie here in the extension direction for the purpose of lowering the load 129 or only for the purpose of extending the piston 22, pressure medium can be supplied via the first fluid channel 146, wherein only then or simultaneously pressure medium can be supplied in the first working channel 24.1. Thereby, the rotatably connected to the spindle 30 first clamping cone body 153 can be moved together with the threaded spindle 30 and the piston 22 in the first direction 31 and raised, in turn until the first clamping cone body 153 on the rolling bearing 138th comes to the plant, whereupon the spindle 30 begins to rotate together with the rotatably connected with it first clamping cone body 153 in the now opposite direction, whereupon the piston 22 together with the load 129 in the second direction 32, ie here in Extension direction is moved. In this case, the pressure medium located in the second working chamber 49 can flow out via the second working channel 24.2.

During the movement of the piston 22 in the second direction 32 or the first fluid channel 146 is constantly acted upon with pressure medium, so that while the fluid-slide bearing 145 is constantly acted upon with pressure medium and at the same time rotatably connected to the spindle 30 connected first clamping Cone body 153 is lifted from the rotatably connected to the cylinder 21 second clamping cone body 154 in a Abhebe- and unlocked position in which their locking cone surfaces 151, 152 do not touch, so that is then the first Clamping cone body 153 and the spindle 30, preferably substantially free to rotate about the spindle rotation axis 33 relative to the cylinder 21.

When the fluid sliding bearing 145 is formed by pressurizing the first fluid channel 146 and thereby the first clamping cone body 153 is lifted from the second clamping cone body 154 such that their locking conical surfaces 151, 152 no longer touching, the pressure medium supplied through the first fluid channel 146 of the recess 175 175 through a then formed between the locking cone surfaces 151 and 152 of the clamping cone body 153 and 154 ring gap and then through the second fluid channel 147th flow out.

In order to stop the piston 22 moving in the second direction 32, both the first working channel 24.1 and the first fluid channel 146 can now be depressurized, so that then due to the acting Load 129 immediately moves the spindle 30 together with the first clamping cone body 153 in the second direction 32, again only to the small spindle-shifting play from here about 1.0 to 1.5 mm, until the first Clamping cone body 153 on or in the second clamping cone body 154 self-locking clamped stuck. Then, the spindle 30 is locked by this self-locking clamping lock against rotation about its axis of rotation 33 relative to the cylinder 21 as well as against an axial lifting in the axial direction 59, ie also in the first direction 31, so that in turn also one double self-locking is achieved.

In the case of the locking cylinders 20, 120 according to the invention, the clamping force between the respectively clamped conical bodies 53 and 54 or 153 and 154 clamped with each other increases with increasing load 29; 129 proportionally. As a result, at any load an always secure locking of the spindle 30 against rotation about its axis of rotation 33 relative to the cylinder 21 can be achieved and as a result, further movement of the piston 22 and acting on this load 29, 129 can be reliably prevented, and although not only in a normal operation of the locking cylinder 29, 129, 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, 120 according to the invention provide a higher locking security than previously known frictionally locking locking cylinder.

It is understood that for the control and / or control of the various operating conditions or functions of the locking cylinder 20, 120, this with a device for Rules and / or taxes of the pressure medium can be coupled or provided, which in the FIGS. 1 and 2 not shown.

Two preferred embodiments of locking cylinders 20, 120 equipped with control units 85, 185 according to the invention are shown in FIGS Figures 3 and 4 shown. Except for the integrated control units 85, 185, these locking cylinders are designed the same as those in the FIGS. 1 and 2 illustrated locking cylinder 20, 120, so that in this regard can be made to the above statements.

In an end housing or control block of the respective locking cylinder 20, 120, in the region of the thrust bearings 38, 39; 138, 139 is provided, a control unit 85, 185 with a plurality, also as fluid channels 46, 146; 91, 191; 97, 197; 99, 199; 103, 203; 106, 206 designated flow and connection channels and control members 108, 208; 88; 90; 98, 98 ', 198; 104 integrated, which are shown as usual in such circuit diagrams, with circuit symbols or symbols of fluid technology. In this case, preferably only two connecting lines 86 and 87 or bores for an alternating supply and discharge of the pressure medium can be provided. Each of the connecting lines 86 and 87 can thus serve as a supply line or as a return line. For this purpose, a switching or control valve not shown in the figures may be provided, which is fluidly connected to a supply device for the pressure medium also not shown in the figures, which may contain a pump and a tank for the pressure medium.

Each control unit 85, 185 has as essential control or regulating organs at least one load-holding lowering brake valve or lowering brake valve 90, a shuttle valve 104, at least one check valve 88, 92, preferably also a switching or changeover valve, in particular in shape a 2-2-way valve 98, 198, on.

The respective load-holding lowering brake valve or lowering brake valve 90 has an inlet 95, an outlet 96 and a control connection to which a control line or a control channel 91 is connected. At the in FIG. 3 shown, pressure-lockable locking cylinder 20, the inlet 95 of the lowering brake valve 90 is fluidly connected to the first working chamber 48 via the also referred to as working channel fluid channel 24.1 and the outlet 96 is fluidly connected to the connection channel 86. In contrast, in the case of FIG. 4 shown, lockable on train locking cylinder 120, the inlet 95 of the lowering brake valve 90 to the second working chamber 49 fluidly connected via the also referred to as working channel fluid channel 24.2 and the outlet 96 is fluidly connected to the connection channel 87. Connected in parallel with the inlet 95 and the outlet 96 of the respective lowering brake valve 90 is a check valve 92 fluidly connected, which blocks a flow of the pressure medium from the inlet 95 to the outlet 96, but allows in the opposite direction. As a locking member 93 may be used, for example, a ball. Preferably, the respective lowering brake valve 90 can be acted upon by the spring force of a spring 94, which counteracts the force exerted by the pressure medium via the control channel 91, 191 force. Preferably, the passageway between the inlet 95 and the outlet 96 of the lowering brake valve 90 is when the control channel 91 is not acted upon by pressure medium or is depressurized, shut off, so that possibly at the inlet 95 under pressure pressure medium the Senkbrems valve 90 can not happen. In this way, the lowering brake valve can be used as a load-holding lowering brake valve. Because in the closed position of the valve 90, the piston 22 can not lower further. In this way, optionally, regardless of or in addition to a mechanical locking hydraulic locking can be achieved. The outlet 96 of the respective lowering brake valve 90 is fluidly connected to a fluid passage 107 or 207 which is fluidly connected to the port 86 in the case of the pressure-lockable lock cylinder 20 and fluidly connected to the port 87 in the case of the lock-lock cylinder 120 ,

In the case of the pressure-lockable locking cylinder 20 can be effected by means of the load-holding lowering brake valve or the lowering brake valve 90 or causes when pressurizing the piston 22 on its second side 23.2 with the located in the second working chamber 49 Pressure fluid to form a working pressure, which causes a displacement of the piston 22 in the retraction direction 32, simultaneously acting in the first working chamber 48 on the first side 23.1 of the piston 22 by the pressure medium in the first working chamber 48 applied back pressure. The counterpressure acting in the first working chamber 48 is kept at pressure values, which are always lower than the working pressure in the second working chamber, by means of the lowering brake valve 90 during the pressurization of the second working chamber 49 and consequently during retraction of the piston 22 in the retraction direction 32 49 are, so that at the retracting or lowering movement the piston 22 in the retraction 32, a controlled deceleration of the piston 22 in the retraction 32 is effected. As a result, an uncontrolled advance of the piston 22 in the lowering or retraction direction 32 can be avoided.

In the case of lockable on train locking cylinder 120 can be effected with the help of the load-holding lowering brake valve or the lowering brake valve 90 or causes when pressurizing the piston 22 on its first side 23.1 with the located in the first working chamber 48 Pressure fluid with the formation of a working pressure, which causes a displacement of the piston 22 in the extension direction 32, simultaneously acting in the second working chamber 49 on the second side 23.2 of the piston 22 by a pressure medium in the second working chamber 49 applied back pressure. The counterpressure acting in the second working chamber 49 is maintained at pressure values, which are always lower than the working pressure in the first working chamber, by means of the lowering brake valve 90 during the pressurization of the first working chamber 48 and consequently during the extension of the piston 22 in the extension direction 32 48, so that in the extension or lowering movement of the piston 22 in the extension direction 32, a controlled braking of the piston 22 in the extension direction 32 is effected. As a result, an uncontrolled advance of the piston 22 in the lowering or extension direction 32 can be avoided.

Between the first fluid channel 46, 146 fluidically connected to the fluid sliding bearing 45, 145 and the two connecting channels 86, 87 serving alternately as a flow channel or return channel is a shuttle valve 104 as a means for Releasing a first passageway between the first fluid channel 46, 146 and the porting channel 86 and, preferably substantially simultaneously, shutting off a second passageway between the first fluid channel 46, 146 and the other porting channel 87 or for releasing the second passageway between the first fluidic channel 46 , 146 and the connection channel 87 and, preferably substantially simultaneously, shut off the first passageway between the fluid channel 46, 146 and the connection channel 86 is arranged. The shuttle valve 104 preferably has only one locking member 105, such as a ball on.

The functions of the said means 104 can be described as follows: If, for example, the connection channel 87 is pressurized, ie serves as a supply channel or is switched, the pressure medium can flow via the fluid channel 106 or 197 into the shuttle valve 104, whereby the shuttle valve 104 blocks the passage to the other connection channel 86 and the pressure medium from the shuttle valve 104 in the first fluid passage 46, 146 can flow to act on the fluid sliding bearing 45, 145. However, if the other connection channel 86 is pressurized, ie serves as a flow channel or is connected, the pressure medium via the fluid channel 97 and 206 in the shuttle valve 104 flow, whereby the shuttle valve 104 blocks the passage to the other port 87 and the Pressure medium from the shuttle valve 104 in turn in the first fluid passage 46, 146 for acting on the fluid sliding bearing 45, 145 can flow.

The respective switching or changeover valve, which is a 2-2-way valve 98, 198, forms in the case the pressure-lockable lock cylinder 20 is a means for switching off or releasing a passageway as required, and in the case of the lockable lock cylinder 120, provides a means for throttling or releasing a passageway as required.

The respective passageway or the respective valve 98, 198 is arranged in the case of the pressure-lockable locking cylinder 20 between the fluid channel 47 and the fluid channel 103, which opens into the second working channel 24.2, and is in the case of lockable on train locking cylinder 120 between the Fluid channel 147 and the fluid channel 203 arranged, which opens into the first working channel 24.1. The respective fluid channel 47, 147 is when the lock-supporting bodies 35, 36; 135, 136 and the clamping cone bodies 53, 54; 153, 154 frictionally abutting each other, compared to the fluid with the fluid bearing 45, 145 fluidly connected fluid channel 46, 146 shut off. However, when the lockup support bodies 35, 36; 135, 136 and the clamping cone bodies 53, 54; 153, 154 are lifted apart from each other in particular due to an action on the fluid sliding bearing 45, 145 with pressure medium, so that between the opposing locking cone surfaces 51, 52 and 151, 152, a gap or passageway is formed for the pressure medium is the fluid channel 46, 146 then serving as a supply channel for the fluid sliding bearing 45, 145 fluidly connected to the fluid channel 103, 203 then serving as a discharge channel for the fluid sliding bearing 45, 145. In the case of the pressure-lockable locking cylinder 20, the fluid channel 103 is fluidly connected to the second working chamber 49, which is between the piston 22 and a free end 71 of the spindle 30th associated cover 40.1 of the cylinder 21 is arranged. In the case of the lock-lock cylinder 120, the fluid passage 203 is fluidly connected to the first working chamber 48 disposed between the piston 22 and the cylinder bottom 140 of the cylinder.

The function of the entire, in an end housing or control block of the locking cylinder 20, 120 integrated control unit 85, 185 with the corresponding control or regulating gates 108, 208; 88; 90; 98, 98 ', 198; 104 is described separately below for both the pressure-lockable latch cylinder 20 and the train-lockable latch cylinder 120.

For the purpose of extending the piston rod 22.1 of the pressure-lockable latching cylinder 20 in the extension direction 31, the connection channel 86 is subjected to pressure medium. As a result, the pressure medium can flow out through the connection channel 86 and out of it at a branch point, both through the fluid channel 97 fluid-connected to the shuttle valve 104 and through the fluid channel 107 fluid-connected to the lowering brake valve 90 and the check valve 92. The pressure medium in the fluid channel 97 can now flow into the shuttle valve 104, which thereby or pressure-releasing, the passageway to the fluidic with the fluid bearing 45 fluid-connected fluid channel 46, while substantially simultaneously through the locking member 105 of the shuttle valve 104, the passageway to the fluid channel 106th is shut off. In this way, therefore, the fluid bearing 45 is subjected to pressure medium. At the same time, the pressure medium via the check valve 93 arranged parallel to the lowering brake valve 90 in the first working channel 24.1 and consequently in the first working chamber 48 flow, which is formed between the neck 72 of the cylinder bottom 20 and the piston 22 and which can form there. In this way, therefore, the fluid sliding bearing 45 and the first working chamber 48 are acted upon substantially simultaneously with the pressure medium. As a result, the first clamping cone body 53 designed as a cone-butt disc 55 with an outer cone 56 lifts off from the second clamping cone body 54, which is designed with an inner cone, in the direction 31 until the first clamping cone -Body 53 abuts the thrust bearing 38. Due to the friction effects occurring at the latest, also in conjunction with the working pressure acting simultaneously in the first working chamber 48, the spindle 30 can rotate so that the piston 22 and consequently the piston rod 22.1 are thereby moved in the extension direction 31 as a result.

As a result of the lift-off of the first clamping cone body 53 designed as a cone-stump disc 55 from the second clamping cone body 54, a passageway or gap is formed between the opposing locking cone surfaces 51. 52 of the two clamping cone body 53, 54. However, then there penetrating pressure fluid can not pass through the fluid channel 47 in the fluid channel 103 and the second working channel 24.2, because due to the loading of the fluid channel 97 with the pressure medium from there at a branch outgoing control channel 99 of the check valve 98 is also acted upon by the pressure medium, whereby the shut-off valve 98 of the in FIG. 3 shown passage position 100 is transferred to a blocking position 101 or was. In FIG. 3 is shown as an alternative to the shut-off valve 98 also another shut-off valve 98 'schematically. at this two check valves are provided in the blocking path, of which each check valve blocks a flow of the pressure medium in the direction of the other non-return valve.

In the case of said pressurization of the connection channel 86, the other connection channel 87 is depressurized by means of a suitable means not shown in the figures. In this way, upon extension of the piston rod 22.1 in the extension direction 31, the pressure medium located in the second working chamber 49 between the piston 22 and the cylinder cover 40.1 via the second working channel 24.2 and viewed in this flow direction before the branch point of the fluid channel 106 of the connection channel 87 check valve 88 flow into and then serve as a return passage connecting channel 87.

For the purpose of retracting the piston rod 22.1 of the pressure-lockable locking cylinder 20 in the retraction direction 32 of the connecting channel 87 is acted upon by pressure medium, while the other connection channel 86 is depressurized. The pressure medium can then flow through the connection channel 87 into the fluid channel 106 which is fluidically connected to the shuttle valve 104, so that the blocking element 105 of the shuttle valve 104 thereby or, as a result of pressure, moves from the in FIG. 3 position shown in a passageway between the fluid channel 97 and the fluid channel 46 shut-off position reaches, in which the pressure fluid from the fluid passage 106 through the shuttle valve 104 in the fluid fluid bearing 45 fluidly connected to the fluid channel 46 can flow or flows.

Due to the between the connecting channel 87 and the second working channel 24.2 parallel to the fluid bearing 45 comprehensive flow path arranged check valve 88 ensures that the inflowing through the connection channel 87 pressure medium first applied to the fluid bearing 45 and only after lifting the cone-butt Washer 55, so the first clamping cone body 53, of the second clamping cone body 54 and a consequent creation of a gap or passageway along the opposite locking-cone surfaces 51, 52 of the two clamping cone Body 53, 54, the pressure medium, here via the second working channel 24.2, can flow into the second working chamber 49, to then cause an axial movement of the piston 22 and the piston rod 22.1 in the retraction 31.

For this purpose, the shut-off valve 98 is in the in FIG. 3 shown passage position 100. This position is, possibly supported by a pointing away from the fluid channel 47 control channel 102 is reached. Because the connection channel 86 is depressurized, the control channel 99 of the shut-off valve 98, which is fluid-connected to the latter via the fluid channel 97, is then depressurized, so that the shut-off valve 98 in the in FIG. 3 shown passage position 100 remains.

Characterized in that in this operating and exemplary embodiment, first the fluid bearing 45 is acted upon by pressure medium and forcibly only then the second working chamber 49 is supplied or acted upon by the pressure medium, first the rotatably secured to the spindle 30 first clamping cone body 53rd lifted from the second clamping cone body 54, so that then a rotation of the spindle 30 about its axis of rotation 33 relative to the cylinder 21 is possible, and only then can the pressure medium flow through said gap or passageway in the second working chamber 49 to cause axial movement of the piston 22 and consequently the piston rod 22.1 in the retraction direction 32 , As a result, a rotation of the spindle 30 about its axis of rotation 33 is effected relative to the cylinder 21, so that conditionally then the piston rod 22.1 can retract in the retraction 32.

During retraction of the piston 22 and the piston rod 22.1 in the retraction 32, the pressure medium in the first working chamber 48 is displaced in the first working channel 24.1 and can flow from there via the lowering brake valve 90 in the connecting channel 86 serving here as a reflux channel. In this case, with the aid of the lowering brake valve 90 in the first working chamber 48 a working pressure in the second working chamber 49 counteracting counter or brake pressure is maintained, which causes the piston 22 and consequently the piston rod 22.1 does not move uncontrolled in the retraction 32 , in particular, can not lead in an uncontrolled manner in the retraction direction 32. To always ensure a sufficiently large back pressure in the first working chamber 48 with increasing working pressure in the second working chamber 49, the lowering brake valve 90, as in FIG. 3 shown schematically, be coupled via the control channel 91 which is fluidly connected to the second working channel 24.2 and with the second working chamber 49. In this way, the lowering brake valve 90 opens a passageway between the first working channel 24.1 and the connecting channel 86 depending on the working pressure acting in the second working channel 24.2 or in the second working chamber 49, namely Preferably proportional to the working pressure, so that with increasing working pressure in the second working chamber 49 by means of the lowering brake valve 90, a corresponding, preferably proportional, increasing back pressure in the first working chamber 48 can be achieved or achieved.

For the purpose of extending the piston rod 22.1 of the lockable on train locking cylinder 20 in the extension direction 32 of the connecting channel 86 is acted upon with pressure medium, while the other connection channel 87 is depressurized. The pressure medium can then flow through the connection channel 86 into the fluid channel 206 which is fluidically connected to the shuttle valve 104, so that the blocking element 105 of the shuttle valve 104 thereby or, as a result of pressure, moves from the in FIG. 4 position shown in the passageway between the fluid passage 206 and the fluidic fluid bearing 145 fluidly connected fluid passage 146 releasing passage position passes while substantially simultaneously the passageway between the fluid passage 197 and the fluid passage 146 is shut off. The pressure medium can thus now flow from the fluid channel 206 via the shuttle valve 104 into and through the fluid channel 206 and pressurize the fluid sliding bearing 145.

Due to the check valve 88 arranged between the connection channel 86 and the first working channel 24.1 parallel to the fluid sliding bearing 145, it is ensured that the pressure medium flowing through the connection channel 86 first acts on the fluid sliding bearing 145 and only after the cone-butt disk has been lifted off 155, ie the first clamping cone body 153, of the second clamping cone body 154 and a Resulting creation of a gap or passageway along the opposite locking-cone surfaces 151, 152 of the two clamping cone body 153, 154, the pressure medium, here via the first working channel 24.1, in the first working chamber 48 can flow to then causing an axial movement of the piston 22 and the piston rod 22.1 in the extension direction 32.

For this purpose, the throttle / passage change-over valve 198, which is designed as a 2-way valve, is located in the in FIG. 4 shown passage position 200. This position is, possibly supported by a pointing away from the fluid channel 147 control channel 202 achieved. Because the connection channel 87 is depressurized, the control channel 199 of the valve 198, which is fluidically connected to the latter via the fluid channel 197, is then also depressurized, so that the valve 198 in the in FIG. 4 shown passage position 200 remains.

Because in this operating and exemplary embodiment first the fluid sliding bearing 145 is subjected to pressure medium and forcibly only then the first working chamber 48 is supplied or acted upon by the pressure medium, first the rotationally fixed to the spindle 30 first clamping cone body 153 lifted from the second clamping cone body 154, so that then a rotation of the spindle 30 about its axis of rotation 33 relative to the cylinder 21 is possible, and only then can the pressure medium through a gap or passageway between the opposite locking cone Surfaces 151, 152 of the two clamping cone bodies 153, 154 flow into the first working chamber 48 in order to effect an axial movement of the piston 22 and consequently of the piston rod 22.1 in the extension direction 32.

This causes a rotation of the spindle 30 about its axis of rotation 33 relative to the cylinder 21, so that conditionally then the piston rod 22.1 can extend in the extension direction 32.

During the extension of the piston 22 or the piston rod 22.1 in the extension direction 32, the pressure medium in the second working chamber 49 is displaced into the second working channel 24.2 and can flow from there via the lowering brake valve 90 into the connection channel 87 serving here as a return flow channel. In this case, with the aid of the lowering brake valve 90 in the second working chamber 49 a working pressure in the first working chamber 48 counteracting counter or brake pressure is maintained, which causes the piston 22 and consequently the piston rod 22.1 does not move uncontrolled in the extension 32 , in particular not uncontrolled in the extension direction 32 can lead. To always ensure a sufficiently large back pressure in the second working chamber 49 with increasing working pressure in the first working chamber 48, the lowering brake valve 90, as in FIG. 4 shown schematically, be coupled via the control channel 191, which is fluidly connected to the first working channel 24.1 and with the first working chamber 48. In this way, the lowering brake valve 90 opens a passageway between the second working channel 24.2 and the connecting channel 87 depending on the operating pressure acting in the first working channel 24.1 or in the first working chamber 48, preferably proportional to the working pressure, so that with increasing working pressure in the first working chamber 48 with the aid of the lowering brake valve 90, a corresponding, preferably proportional, increasing back pressure in the second working chamber 49 can be achieved or achieved.

For the purpose of retracting the piston rod 22. 1 of the lockable latch lock cylinder 20 in the retraction direction 31, the connection channel 87 is subjected to pressure medium. As a result, the pressure medium can flow out through the connection channel 87 and at a branch thereof, both through the fluid channel 197 fluid-connected to the shuttle valve 104 and through the fluid channel 207 fluid-connected to the lowering brake valve 90 and the check valve 92. The pressure medium in the fluid channel 197 can now flow into the shuttle valve 104, which thereby or pressure-releasing, the passageway to the fluid with the fluid bearing 145 fluid-connected fluid channel 146, while substantially simultaneously through the locking member 105 of the shuttle valve 104, the passageway to the fluid passage 206th is shut off. In this way, so the fluid bearing 145 is pressurized with pressure medium. At the same time, the pressure medium can flow via the check valve 93 arranged parallel to the lowering brake valve 90 into the second working channel 24.2 and consequently into the second working chamber 49 which is formed between the cylinder cover 40.1 and the piston 22 or which can form there , In this way, therefore, the fluid sliding bearing 145 and the second working chamber 49 are acted upon substantially simultaneously with the pressure medium. As a result, the first clamping cone body 153 configured as a cone-butt disk 155 with an outer cone 156 comes off the second clamping cone body 154, which is designed with an inner cone, in the direction 31 until the first clamping cone Body 153 abuts the thrust bearing 138. Due to the friction effects occurring at the latest, also in conjunction with the simultaneously acting in the second working chamber 49 working pressure can the spindle 30 rotate so that then conditionally the piston 22 and consequently the piston rod 22.1 are moved in the extension direction 31.

As a result of the lifting off of the first clamping cone body 153 designed as a cone-butt disc 155 from the second clamping cone body 154, a passageway or gap is formed between the opposing locking cone surfaces 151, 152 of the two clamping cone body 153, 154. The then there penetrating pressure fluid can then pass through the fluid passage 147 and the throttle of the throttle / passage changeover or switching valve 198 in the fluid passage 203 and from there into the unpressurized port channel 86 , because due to the pressurization of the fluid channel 197 with the pressure medium from there to a branch outgoing control channel 199 of the valve 198 is also acted upon by the pressure medium, whereby the valve 198 of the in FIG. 4 shown passage position 200 is transferred to a throttle position 201 or was.

During said pressurization of the connection channel 87 with pressure medium, the other connection channel 88 is depressurized by means of a suitable means not shown in the figures. In this way, when retracting the piston rod 22.1 in the retraction direction 31, the pressure medium in the first working chamber 48 between the piston 22 and the projection 172 of the cylinder bottom 140 via the first working channel 24.1 and viewed in this flow direction before the branch point of the fluid channel 206th Check valve 88 located in the connection channel 86 flow into and out of the connection channel 86, which then serves as a return channel.

The invention may also be summarized as follows:

The invention relates to a locking cylinder 20, 120 with a cylinder 21 and a relative to this by means of a pressure medium in the axial direction 59 movable and non-rotatably connected to the cylinder piston 22. The piston 22 is provided with a piston thread 26, which forms a non-self-locking Thread 27 with a spindle thread 28 of a spindle 30 is in Engriff, which is rotatable about an axis of rotation 33 relative to the cylinder 21 and slidable in the axial direction relative to the cylinder 21. The spindle 30 is rotationally fixed with a first locking cone surfaces 51, 151 having self-locking first clamping cone body 53; 153, the locking cone surfaces 51, 151 with second locking cone surfaces 52, 152 of a second self-locking clamping cone body 54, 154 are self-locking clamped. The invention also relates to a method for the rotationally fixed frictional locking of a spindle 30 and to a method for unlocking a rotatably and frictionally locked spindle 30.

LIST OF REFERENCE NUMBERS

20 lock cylinders 36 (second) Locking Support Body 21 cylinder 37 poetry 22 piston 38 (first) thrust bearing / 22.1 piston rod Rolling Bearings / Needle Roller Bearings / Ring Bearings 23.1 (first) page of 22 39 (second) thrust bearing / 23.2 (second page Fluid bearings from 22 40 cylinder base 24.1 (First) 40.1 (Cylindrical) cover working channel 41 (first) bearing body 24.2 (second) working channel 42 (second) bearing body 43 (first) storage area 25 Longitudinal axis of 21 44 (second) storage area 26 Piston thread 45 Fluid bearings 27 not self-locking 46 (first) fluid channel thread 47 (second) fluid channel 28 spindle thread 48 (first) working chamber 29 load 49 (second) working chamber 30 spindle 50 thread-free part 31 first direction from 30 32 second direction 51 (first) interlocking 33 Rotation axis of 30 Cone surface / n 34 Double arrow / axial displacement / 52 (second) locking cone surface / s Sliding clearance / axial spindle play 53 (first) clamping cone body 35 (first) Locking Support Body 54 (second) clamping cone body 55 Cone pulley / Cone frustum-disc 78 Storage-ring groove 56 outer cone 80 outer diameter 57 inner cone from 43 58 Part of 53 81 Inner diameter 59 axially from 76 60 poetry 82 outer diameter from 50 61 (first) locking support 83 Page of 76 and bearing body 85 Control unit / 62 (second) locking support control device and bearing body 86 Channel / port channel / 63 (First) drilling tilt angle 87 Channel / port channel / drilling 64 (Second) 88 Rückströmsperrmittel / tilt angle check valve 65 (first page 89 Blocking member of 88 from 53 90 Medium / (load-holding) lowering brake valve 66 (second page 91 Fluid channel / control channel from 53 92 Rückströmsperrmittel / 67 (first page check valve from 54 69 (Cylinder-bottom-side) 93 Blocking member of 92 The End 94 feather from 30 95 Inlet of 90 71 (free) end 96 Outlet of 90 from 30 97 fluid channel 72 approach 98 Medium/ 75 recess / 2-2-way valve chamber shut-off valve / 76 poetry Through valve 77 T-shaped 98 ' Medium/ Cross section of 75 2-2-way valve shut-off valve / 145 Fluid bearings Through valve 146 (first) fluid channel 99 Switching / control channel 147 (second) fluid channel 100 Passage position 151 (first) interlocking 101 blocking position Cone surface / n 102 Fluid channel / 152 (second) Beaufschlagungskanal Locking cone surface / n 103 fluid channel 153 (first) clamping cone 104 Medium/ body Shuttle valve / 154 (Second) Double check valve Clamp cone body 105 locking member 155 Cone pulley / 106 fluid channel Cone frustum-disc 107 fluid channel 156 outer cone 108 Tax or 157 inner cone control devices 158 Part of 153 120 lock cylinders 161 (First) 129 load Lock Support and Bearing Body 135 (First) 162 (Second) Locking the support body Locking supporting 136 (Second) and bearing body Locking the support body 163 (First) 138 (First) tilt angle Thrust bearing / roller bearing / 164 (second) inclination angle Needle roller bearings / ring bearings 165 (first) 139 (second) thrust bearing / Page of 153 Fluid bearings 166 (second page 140 cylinder base from 153 141 (first) bearing body 167 (first page 142 (second) bearing body from 154 143 (first) storage area 144 (second) storage area 172 approach 175 Recess / chamber 177 T-shaped cross section of 175 178 Storage-ring groove 180 Outer diameter of 143 185 control unit 191 Switching / control channel 197 fluid channel 198 Medium / 2-way valve Shut-off valve / two-way valve 199 Switching / control channel 200 Passage position 201 throttle position 202 Fluid channel / admission channel 203 fluid channel 206 fluid channel 207 fluid channel 208 Control organs

Claims (13)

1. Locking cylinder (20, 120) comprising a cylinder (21) and a piston (22), which is movable parallel to the longitudinal axis (25) of the cylinder (21) in a first direction (31) and in a second direction (32) opposite to the first direction (31) with the assistance of a fluid pressure medium feedable to one side (23.1) of the piston (22) by way of a work channel (24.1) or to both sides (23.1, 23.2) of the piston (22) by way of work channels (24.1, 24.2) associated with these sides (23.1, 23.2) and which is provided with a piston thread (26) disposed in engagement, with formation of a non-self-locking thread (27), with a spindle thread (28) of a spindle (30), which is automatically lockable frictionally and by gravitational force and which is rotatable relative to the cylinder (21) about an axis (33) of rotation, the axis of rotation being arranged parallel to the longitudinal axis (25) of the cylinder (21), and axially displaceable relative to the cylinder (21) in axial direction (59) and wherein a first work chamber (48, 49) is associated with a first side (23.1, 23.2) of the piston (22) and is arranged behind or after the piston (22) as considered in the direction (32) of an axial movement of the piston (22) parallel to the longitudinal axis (25) of the cylinder (21) or parallel to the axis (33) of rotation of the spindle (30) and wherein a second chamber (29, 48) is associated with a second side (23.2, 23.1) of the piston (22) and is arranged in front of the piston (22) as considered in the said direction, wherein at least two locking support bodies (35, 36; 135, 136) are provided which are transferrable into mutual frictional locking engagement and which are intended frictionally lock the spindle (30) against rotation about the axis (33) of rotation thereof and of accepting axial forces acting on the spindle (30) in the second direction (32), wherein at least one first locking support body (35; 135) of the locking support bodies (35, 36; 135, 136) is connected with the spindle (30) to be secure against relative rotation and wherein at least one second locking support body (36; 136) of the locking support bodies (35, 36; 135, 136) is connected with the cylinder (21) to be secure against relative rotation and wherein the spindle (30) is mounted at at least two axial bearings (38, 39; 138, 139), of which a first axial bearing (38; 138) is intended to accept axial forces acting on the spindle (30) in the first direction (31) and of which a second axial bearing (39; 139) is intended to accept axial forces acting on the spindle (30) in the second direction (32) and wherein the spindle (30) is connected or constructed with a first bearing body (41, 141) having a first bearing surface (43, 143) opposite a second bearing surface (44, 144) of a second bearing body (42; 142) connected with the cylinder (21) to be secure against relative rotation and wherein the first bearing surface (43; 143) of the first bearing body (41; 141) and the second bearing surface (44, 144) of the second bearing body (42; 142) form the second axial bearing (39; 139), which is constructed as a fluid slide bearing (45, 145) loadable or loaded with a or the fluid pressure medium by way of a first fluid channel (46; 146), characterised in that the first locking support body (35; 135) is constructed as a self-locking first clamping code body (53, 153) having first locking cone surfaces (51; 151) and that the second locking support body (36; 136) is constructed as a self-locking second clamping cone body (54; 154) having second locking cone surfaces (52; 152), and wherein the locking cone surfaces (51, 52; 151; 152) of the clamping cone bodies (53, 54; 153, 154) are capable of self-locking wedging together and wherein arranged between a first work channel (24.1, 24.2) in fluid connection with the first work chamber (48, 49) and a second fluid channel (107, 86; 207, 87) is a means (90) for limiting the pressure and/or volume flow of the pressure medium via or through a passage path between the first work channel (24.1, 24.2) and the second fluid channel (107, 86; 207, 87) in dependence on the pressure in a second work channel (24.2, 24.1) in fluid connection with the second work chamber (49, 48) and wherein the means (90) is formed as a lowering brake valve or load-retaining lowering brake valve (90) which is coupled with a control channel (91), which is in fluid connection with the second work chamber (49, 48), for control or regulation of a counterpressure, which opposes the pressure in the second work chamber (49, 48), in the first work chamber (48, 49).
2. Locking cylinder according to claim 1, characterised in that the first clamping cone body (53; 153) is received at least partly in a recess (75; 175), particularly in a chamber (75; 175), of the cylinder (21), which is bounded on the one hand by a cylinder base (40) of the cylinder (21) and on the other hand by a projection (72; 172) preferably connected or produced integrally with the cylinder (21) and particularly extending radially and transversely to the longitudinal axis (25) of the cylinder (21).
3. Locking cylinder according to claim 3, characterised in that the recess (75, 175) is sealed by a seal (76) relative to the piston (22) or relative to a work chamber (48), which is formed between the cylinder (21) and the piston (22) and is bounded by the side (23.1) of the piston (22) facing the first clamping cone body (53; 153), optionally also by the second bearing body (142) and/or by the projection 72; 172), and into which the work channel (24.1) opens.
4. Locking cylinder according to any one of claims 1 to 3, characterised in that the fluid slide bearing (45; 145) is so loaded by the fluid pressure medium during movement of the piston (22) not only in the first direction (31), but also in the second direction (32) and/or during rotation of the spindle (30) about the axis (33) of rotation thereof, preferably also in the course of or during stopping of the piston (22), particularly also in a stop setting of the piston (22), that the clamping cone bodies (53, 54; 153, 154) are detached from one another, particularly are so lifted off one another that the locking cone surfaces (51, 52; 151, 152) are not in contact.
5. Locking cylinder according to any one of claims 1 to 4, characterised in that fluid channels (46, 146; 91, 191; 97, 197; 99, 199; 103, 203; 106, 206) and control and/or regulating elements (108, 208; 88; 90; 98, 98', 198; 104), which form a control unit (85, 185), are arranged in a housing, preferably in an end housing provided in the region of the axial bearing (38, 39; 138, 139) and/or of a cylinder base (40) of the cylinder (21) or in the cylinder base (40), between connecting lines or bores (86, 87) for alternate feed and discharge of the pressure medium and fluid channels (24.1, 24.2) to work chambers (48, 49), which are provided on both sides of the piston (22), and to the fluid slide bearing (45, 145).
6. Locking cylinder according to any one of the preceding claims, characterised in that arranged between a fluid channel (46, 146), which is in fluid connection with the fluid slide bearing (45, 145), and two connecting channels (86, 87) serving alternately as outward channel or return channel is a means (104) for freeing a first passage path between the fluid channel (146, 146) and a first connecting channel (86) of the connecting channels (86, 87) and for blocking, preferably substantially simultaneously, a second passage path between the fluid channel (46, 146) and a second connecting channel (87) of the connecting channels (86, 87) or for freeing the second passage path between the fluid channel (46, 146) and the second connecting channel (87) and for blocking, preferably substantially simultaneously, the first passage path between the fluid channel (46, 146) and the first connecting channel (86).
7. Locking cylinder according to any one of the preceding claims, characterised in that arranged between a first fluid channel (47, 147), which when the locking support bodies (35, 36; 135, 136) or the clamping cone bodies (53, 54; 153, 154) are wedged together is blocked relative to the fluid channel (46, 146) in fluid connection with the fluid slide bearing (45, 145) and which when the locking support bodies (35, 36; 135, 136) or the clamping cone bodies (53, 54; 153, 154) are lifted off one another is in fluid connection with the fluid channel (46, 146), and a second fluid channel 9103, 24.2; 203, 24.1), which is in fluid connection with a or the work chamber (49, 48), is a means (98, 98'; 198) for blocking or freeing, as required, or for throttling or freeing, as required, a passage path between the first fluid channel (47, 147) and the second fluid channel (103, 24.2; 203, 24.1).
8. Method for frictional locking, so as to be secure against relative rotation, of the spindle (30), which is rotatable about the axis (33) of rotation thereof, of the locking cylinder (20, 120), which has the features of at least one of claims 1 to 7, against rotation relative to the cylinder (21) about the axis (33) of rotation, characterised in that at least one of the locking support bodies (35; 135) is transferred from an unlocking setting, which enables rotation of the spindle (30) about the axis (33) of rotation thereof relative to the cylinder (21), to a locking setting, in which the locking support bodies (35, 36; 135, 136) are frictionally wedged together by adhesive friction to be secure against relative rotation and self-locking in such a manner that they are transferrable to the unlocking setting only with exertion of release forces releasing the wedging.
9. Method of unlocking the spindle (30) which is automatically locked to be secure against relative rotation and frictionally as well as by gravitational force against rotation about the axis (33) of rotation thereof relative to the cylinder (21) of the locking cylinder (20, 120) having the features of at least one of claims 1 to 7, wherein the spindle (30) in the locked state is frictionally locked by means of the locking support bodies (35, 36; 135, 136) against rotation about the axis (33) of rotation thereof relative to the cylinder (21), wherein the locking support bodies (35, 36; 135, 136) accept axial forces acting on the spindle (30) in the second direction and wherein the locking support bodies (35, 36; 135, 136) are transferrable into an unlocking setting in which the spindle (30) is rotatable about the axis (33) of rotation thereof relative to the cylinder (21), characterised in that at least one of the locking support bodies (35, 135) is transferred into the unlocking setting from a locking setting in which the locking support bodies (35, 36; 135, 136) are frictionally wedged together by adhesive friction to be secure against relative rotation and self-locking in such a manner that they are transferrable into an unlocking setting, which enables rotation of the spindle (30) about the axis (33) of rotation thereof relative to the cylinder (21), only with exertion of release forces releasing the wedging.
10. Method according to claim 9, characterised in that the locking support bodies (35, 36; 135, 136) are transferred from the locking setting, in which they are frictionally wedged together by adhesive friction to be self-locking, by loading of the hydrostatic fluid slide bearing (45; 145) with the fluid pressure medium to an unlocking setting enabling rotation of the spindle (30) about the axis (33) of rotation thereof relative to the cylinder (21) or to an unlocking setting in which the spindle (30) is capable of substantially unhindered or free rotation relative to the cylinder (21).
11. Method according to claim 10, characterised in that the locking support bodies (35, 36; 135, 136) having locking cone surfaces (51, 52; 151, 152) are transferred from the locking setting, in which they are frictionally wedged together by adhesive friction to be self-locking, by loading of the hydrostatic fluid slide bearing (45; 145) with the fluid pressure medium to a lifted-off and unlocking setting in which the locking support bodies (35, 36; 135, 136) are lifted off one another so that the locking cone surfaces (51, 52; 151, 152) thereof are no longer in contact.
12. Method according to at least one of claims 9 to 11, characterised in that, preferably with the assistance of a or the control device (85, 185), initially the fluid slide bearing (45, 145) is loaded with the pressure medium so as to enable rotation of the spindle (30) about the axis (33) of rotation thereof relative to the cylinder (21) and/or to produce lifting-off of the locking support bodies (35, 36; 135, 136) or the clamping cone bodies (53, 54; 153, 154) from the locking setting, in which they are frictionally wedged together by adhesive friction, into a lifted-off and unlocking setting in which the locking support bodies (35, 36; 135, 136) or the clamping cone bodies (53, 54; 153, 154) are lifted off one another so that the locking cone surfaces (51, 52) thereof at least in part are no longer in contact and that only subsequently is the pressure medium fed to a work chamber (48, 49), which is associated with a side (23.1, 23.2) preferably bounded by this, of the piston (22) so as to enable, assist or produce movement of the piston (22) in an axial direction (59) parallel to the longitudinal axis (25) of the cylinder (21) or parallel to the axis (33) of rotation of the spindle (30).
13. Method according to claim 12, characterised in that initially the fluid slide bearing (45, 145) is loaded with the pressure medium by way of a or the fluid channel (46, 146), whereby lifting-off of the locking setting bodies (35, 36; 135, 136) or of the clamping cone bodies (53, 54; 153, 154) from the locking setting, in which they are frictionally wedged together by adhesive friction, into a lifted-off and unlocking setting is produced, in which the locking support bodies (35, 36; 135, 136) or the clamping cone bodies (53, 54; 153, 154) are at least partly lifted off one another so that the locking cone surfaces (51, 52) thereof at least in part are no longer in contact and in that thereby formed between and along the locking cone surfaces ( 51, 52), which are mutually opposite in the lifted-off state, is a passage path in fluid connection with a or the fluid channel (47, 147), which is in fluid connection with the work chambers (48, 49), so that the piston (22) is loaded by the pressure medium, which is flowing through the fluid channel (47, 147) into the work chambers (48, 49), so as to enable, assist or produce movement of the piston (22) in an axial direction (59) parallel to the longitudinal axis (25) of the cylinder (21) or parallel to the axis (33) of rotation of the spindle (30).

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