CN106170600A - Piston-cylinder units and door hinges with piston-cylinder units - Google Patents

Abstract

The invention relates to a piston-cylinder unit (16), comprising a cylinder (20) having a longitudinal axis L and a piston arrangement (22) inserted into the cylinder and movable along the longitudinal axis, the piston arrangement comprising a piston rod (24) and a piston, wherein the piston rod extends through the cylinder along the longitudinal axis so that the piston rod protrudes from the cylinder both at a first axial end (26) and at an opposite second axial end (28), wherein the piston separates a first working chamber filled with a damping fluid from a second working chamber filled with the damping fluid in the inner cavity of the cylinder, wherein the piston arrangement and the cylinder are connected to each other by a spiral connection so that they can perform a spiral movement relative to each other around the longitudinal axis L.

Description

Piston-cylinder unit and door hinge with piston-cylinder unit

technical field

The invention relates to a piston-cylinder unit comprising a cylinder with a longitudinal axis and a piston device inserted into the cylinder and movable along the longitudinal axis, the piston device having a piston rod and a piston, wherein the piston rod extends through the cylinder along the longitudinal axis Cylinder, so that the piston rod extends out of the cylinder both at the axial first end and at the opposite axial second end, wherein the piston connects the first working chamber filled with damping fluid with the filling chamber in the inner chamber of the cylinder A second working chamber with damping fluid is separated. The invention also relates to a door hinge comprising a first mounting element for mounting on a door leaf and a second mounting element for mounting on a door frame.

Background technique

Piston-cylinder units of the type mentioned at the outset are known in the prior art as damping elements, in which the piston arrangement penetrates the cylinder in the axial direction and the piston arrangement travels in the interior of the cylinder in the damping fluid in this axial direction. This type of damping element limits the linear movement of the two components with respect to their relative velocity or acceleration and damps impacts or shocks acting on the component. Such a piston-cylinder unit is known for example from DE 10 2011 006 011 A1 for a door construction, wherein the piston-cylinder unit is mounted between the door and the door frame such that the longitudinal axis of the cylinder is perpendicular to the swing axis of the door, and This piston-cylinder unit spans the angle between the door and the door frame. When opening or closing the door, the piston-cylinder unit is lengthened or shortened, wherein the movement of the door is damped by the movement of the piston arrangement in the damping fluid.

According to its basic principle of action, conventional piston-cylinder units are limited to the damping of linear displacement movements between two components, thereby limiting the field of application of the piston-cylinder unit. Door constructions of the above-mentioned type require relatively complex hinge arrangements and high construction spaces. Furthermore, in such a door structure, the maximum or minimum door opening angle is limited by the hinged configuration of the piston-cylinder unit.

Contents of the invention

Against this background, the object of the present invention is to provide a piston-cylinder unit which offers a wider range of applications or opens up new fields of application. It is also the object of the present invention to provide an improved door hinge which can be installed on the door in a small installation space and inconspicuously and which has a high degree of functionality.

According to a first aspect of the invention, the above object is achieved by a piston-cylinder unit comprising a cylinder with a longitudinal axis and a piston device inserted into the cylinder, movable along the longitudinal axis, having a piston rod and Piston, wherein the piston rod extends through the cylinder along the longitudinal axis so that the piston rod protrudes from the cylinder both at an axially first end and at an opposite axially second end, wherein the piston in the cavity of the cylinder will A first working chamber filled with a damping fluid is separated from a second working chamber filled with a damping fluid, wherein the piston device and the cylinder are connected to each other by a screw connection so as to enable a helical movement relative to each other about a longitudinal axis .

Thus, according to the invention, the piston means is connected to the cylinder by means of a screw connection, so that the relative movement between the piston means and the cylinder is forced to take place on a helical path. The movement between the piston arrangement and the cylinder is thus a combination of an axial movement component along the longitudinal axis and a rotational movement component about the longitudinal axis. Thus, the piston-cylinder unit according to the invention is not only suitable for damping linear movements between two components, but also simultaneously or alternatively for damping rotary movements, so that the piston-cylinder unit according to the invention can be used in new fields of application.

Preferably, a helical attachment or nut can be arranged fixedly or axially immovably on the inner side of the cylinder, wherein the attachment or nut is in helical engagement with a corresponding element of the piston arrangement. A compact and robust piston-cylinder unit is achieved by providing screw connections inside the cylinder.

In other variants of the present invention, the screw connection can be implemented as a multi-start thread or a ball thread, so as to achieve a very smooth connection. It is also conceivable to introduce a pin of one of the two components, cylinder and piston arrangement, into a rod guide of the other element of the cylinder and piston arrangement.

In a preferred embodiment of the invention it is provided that a rotation transmission element is arranged on the piston rod section arranged outside the piston-cylinder unit, which is connected to the piston rod in a rotationally transmittable and axially displaceable manner. , while the rotation transmitting element remains axially immovable but rotatable relative to the cylinder. Such an arrangement achieves the technical effect that a purely rotational movement can be damped, ie a movement between the two components without a translational component in the axial direction. The cylinder and the rotation transmission element are mutually rotatable under damping, wherein the translational component of the helical motion in the direction of the longitudinal axis of the cylinder is compensated by the axial displacement of the piston arrangement on the rotation transmission element. Therefore, this type of piston-cylinder unit can be used as a damping hinge in various applications.

The effects described in the last embodiment described above can also be achieved if a rotation transmission element is provided on the outer section of the cylinder, which is connected to the cylinder in a rotationally transferable and axially displaceable manner, whereas The rotation transmission element remains axially immovable but rotatable relative to the piston arrangement. In this variant, the rotation transmission element and the piston device can rotate relative to each other without a translational component and can thus be used as a component of a damped hinge, while the translational component of the helical movement between the piston device and the cylinder is compensated by the cylinder.

In order to ensure a defined damping behavior of the piston-cylinder unit, the first working chamber and the second working chamber are preferably connected to one another via at least one damping fluid channel formed in the piston or as a bypass channel on the cylinder. If the damping fluid channel is arranged in the piston, the available installation space in the piston can be better utilized and the length of the channel can be limited. Arranging at least one damping fluid channel as a bypass channel at the cylinder allows a variation of the damping behavior depending on the axial position of the piston arrangement relative to the cylinder. For example, it is conceivable to vary the number or cross-section of at least one bypass channel along the axial direction of the cylinder in order to set a predetermined damping behavior for a specific position of the piston arrangement in the cylinder, or even to stop the piston-cylinder completely at a specific axial position movement of the unit. This variation of the flow cross-section of the bypass channel depending on the axial position on the cylinder, in the case of a piston-cylinder unit for a door hinge, can be used, for example, to hold or lock the door at one or more predetermined swivel position from which the door can only be moved further with increased force expenditure.

In a piston-cylinder unit with damping fluid channels, a flow cross-section-influencing valve is preferably installed in at least one damping fluid channel or at an opening of at least one damping fluid channel. With such a valve, the damping behavior can be adapted and in particular controlled in a predictable manner. The valve is switchable between a first switching state and a second switching state, wherein the valve has different flow cross-sections in the two switching states in order to damp the movement of the piston arrangement to different degrees. In particular, the valve can also be adjusted to a closed state in which it completely closes the damping fluid channel. It is essentially envisaged here that the exchange of damping fluid between the first working chamber and the second working chamber is substantially completely blocked in the closed state of the valve, so that the movement of the piston arrangement in the cylinder is blocked.

At least one valve can be passively controlled in dependence on the pressure of the damping fluid prevailing in the first working chamber or in the second working chamber, so that the gate operates above or below at least one predetermined pressure threshold or/and at least one Switching occurs at a predetermined flow rate threshold. By using such valves, the damping behavior of the piston-cylinder unit can be adapted to externally supplied forces or movement dynamics. Thus, for example, the valve can be preloaded into the closed position and can be switched into the open position under the effect of a pressure in the damping fluid which exceeds a predetermined first threshold value. This function can be utilized, for example, in door hinges for holding the door in an unloaded state, preventing the door from being accidentally moved into an adjusted position (pressure in the damping fluid below a first threshold), and when intentionally opened or closed When the door is under the action of an external force (the pressure in the damping fluid is higher than a predetermined first threshold), it is used to allow the damped movement of the door.

In an advantageous development of the last-mentioned embodiment above, it is provided that the valve switches from the open position to the closed position when the pressure in the damping fluid falls below a second threshold value, which is smaller than the first threshold value. This means that a first force is required to move the cylinder and piston assembly relative to each other from a rest position, that is, a first pressure is required to move the valve from a closed position to an open position, which also means that in order to re-block the piston assembly and cylinder The movement between must be lower than the second force, that is, when the valve is lower than the second pressure, the valve will re-transition to the closed position, wherein the second force or the second pressure is lower than the first force or the first pressure respectively. In the specific application example, the piston-cylinder unit used as a door hinge means that, in order to release the door from the locked position, relatively high forces are required to push the door in the desired direction starting from the rest position, wherein the actual movement of the door The required force is less than the first force for releasing the door from the rest position.

The at least one valve of the damping fluid channel is preferably designed such that damping fluid flows through the valve in both directions and the valve can influence the flow cross section of the fluid in both directions in different switching positions. In this case, at least one valve itself can be designed as a bidirectional valve, which has, in particular, the same passage behavior or the same switching behavior for both flow directions. Alternatively or additionally, non-return valves can be provided in or on a plurality of damping fluid channels, respectively, which have opposite directions of action. Thus, each check valve itself allows the passage of damping fluid in one flow direction and blocks the passage of damping fluid in the opposite flow direction at least when the pressure threshold is exceeded. If desired, different non-return valves with different flow properties can also be used, in particular for the two flow directions.

As an alternative or in addition to the above-mentioned function of the at least one valve, it is conceivable that the at least one valve can be controlled by means of an adjusting element, ie in particular can be controlled from outside the cylinder. In this way, the damping behavior and in particular the blocking or release of the movement of the piston-cylinder unit can be controlled by manual actuation of the adjusting element or by externally controlling the adjusting element by means of an open-loop control/closed-loop control unit. For example, it can be a magnetic control device in which at least one valve is switched between different switching positions by means of a magnetic interaction between the valve body of the valve and the adjusting element.

According to a second aspect, the aforementioned inventive task is achieved by a door hinge comprising a first mounting element for mounting on a door leaf, a second mounting element for mounting on a door frame and a first mounting element according to the invention. A piston-cylinder unit according to an aspect, wherein one of the two mounting elements is rotatably connected to or formed by the cylinder, and wherein the other of the two mounting elements is rotatably connected to the piston rod or formed by the piston Rod formation. By virtue of the inventive features of the second aspect, the advantageous effects of the piston-cylinder unit of the first aspect described above can be applied to door hinges with corresponding advantages. In particular the rotational component of the helical movement according to the invention can be used in a structurally simple manner for damping the rotational movement of the door hinge, so that a compact and functional arrangement is achieved.

The cylinder and/or the piston rod are preferably axially displaceable and held in a rotationally fixed manner on the corresponding mounting element. The axial or translational movement component of the helical movement between the cylinder and the piston arrangement is thus compensated by the axial movement between the cylinder and the corresponding mounting element, or between the piston rod and the corresponding mounting element. As a result, the first mounting element and the second mounting element are connected to each other for a purely rotational movement (without a translational component), wherein this rotational movement is damped in the aforementioned manner by the piston-cylinder unit according to the invention.

In a particularly advantageous variant of the door hinge according to the invention, the hinge axis is identical to the longitudinal axis of the cylinder, about which the first mounting element is pivoted relative to the second mounting element. The piston-cylinder unit thus simultaneously forms an integral component of the hinge, ie the swivel bearing of the door hinge, on which the two mounting elements are mounted rotatable relative to each other. The piston-cylinder unit can then be integrated in the door construction particularly unobtrusively and with a small installation space.

The door hinge according to the second aspect of the invention preferably has an actuating element for manually actuating the above-mentioned adjusting element for adjusting the at least one valve, wherein the actuating element and the adjusting element are provided in particular for adjusting the at least one gate in this way, That is, the exchange of damping fluid between the first working chamber and the second working chamber is blocked substantially completely, or the blocking is released. The result is a door hinge which, on the one hand, enables the door to move in a damped and thus prevents unintentional knocking of the door, and which, on the other hand, can be fixed by the user in the desired door opening position.

Description of drawings

The invention is explained in detail below with the aid of preferred exemplary embodiments with reference to the drawings. in:

Figures 1a and 1b show a front view and a side view of a door hinge according to a first embodiment of the invention;

Fig. 2 shows a sectional view along line II-II in Fig. 1a of the door hinge of the first embodiment;

Figure 3a shows a schematic cross-sectional view of a door hinge according to a second embodiment of the invention in a section containing the longitudinal axis of the cylinder;

Figure 3b shows an enlarged view of the section containing the valve in Figure 3a;

FIG. 4 shows a schematic cross-sectional view of a door hinge according to a third embodiment of the invention in a section including the longitudinal axis of the cylinder.

detailed description

A first embodiment of a door hinge, designated collectively at 10 in the accompanying drawings, comprises a first mounting element 12 for attachment to either of the door leaf and the door frame, for attachment to the other of the door leaf and the door frame The second mounting element 14 and the piston-cylinder unit 16, by which the first mounting element 12 and the second mounting element 14 are rotatably connected to each other. As shown in the figures, the mounting elements 12, 14 can be formed by fastening lugs which are fastened to the door leaf or door frame by suitable fastening means, in particular screws screwed into the through-holes 18, not shown.

The piston-cylinder unit 16 comprises a cylinder 20 with a longitudinal axis L and a piston arrangement 22 inserted at least partially into the cylinder 20 , which piston arrangement has a piston rod 24 likewise extending along the longitudinal axis L. As shown in FIG. The piston rod 24 projects out of the cylinder 20 both at a first axial end 26 of the cylinder 20 and at a second end 28 opposite the first axial end 26 . In other words, the piston device 22 completely penetrates the cylinder 20 in the axial direction of the longitudinal axis L. As shown in FIG.

In a manner that will still be explained in more detail below, according to the invention, the piston device 22 is held in relation to the cylinder 20 in a helical movement about the longitudinal axis L. As shown in FIG. This means that the piston arrangement 22 and the cylinder 20 can only move relative to each other on a helical path around the longitudinal axis L, that is to say have both a rotational component around the longitudinal axis L and an axial movement component along the longitudinal axis L .

One of the two mounting elements 12 , 14 , here the second mounting element 14 , is connected to the piston arrangement 22 in a torque-transmittable but axially displaceable manner. A further mounting element, here the first mounting element 12 , can be fixedly connected to the cylinder. Alternatively, an axially displaceable connection may be provided between the cylinder 20 and either of the two mounting elements 12, 14, while the piston arrangement 22 is fixedly connected to the other mounting element. In this embodiment, longitudinal teeth are provided on the section of the piston rod 24 protruding from the second end 28 of the cylinder 20 , which matingly engage with corresponding longitudinal teeth of the receptacle 34 of the second mounting element 14 , the piston rod 24 is accommodated axially displaceably in this receptacle.

The internal structure of the piston-cylinder unit 16 will be described in detail below, especially with reference to FIG. 2 . The interior of the cylinder 20 contains a first working chamber 36 and a second working chamber 38 separated from each other by a piston 40 fastened to the piston rod 24 and forming part of the piston arrangement 22 . The two working chambers 36, 38 are filled with a damping fluid, in particular oil or another suitable liquid. In the illustrated embodiment, the working chambers 36 , 38 are delimited radially outwardly by a wall 42 of the cylinder 20 and at their longitudinal ends axially remote from the piston 40 by an end unit 44 , respectively. Delimited by 46, the end units are inserted at the ends 26, 28 of the cylinder 20, respectively, so as to seal the interior of the cylinder 20 to prevent the damping fluid from escaping. In particular, the end units 44 , 46 may each have a seal 48 sealingly against the periphery of the piston rod 24 and may have a bearing section 50 on which the piston rod 24 is arranged rotatably and movable relative to the cylinder 20 section.

The piston-cylinder unit 16 also comprises a screw connection 52 by means of which the relative movement between the piston arrangement 22 and the cylinder 20 is forced to take place on a helical path. In this embodiment, the screw connection 52 has a nut 54 fastened inside the cylinder 20 which is threadedly engaged with a threaded rod 56 of the piston arrangement 24 . The screw 56 can in particular be a sleeve with an external thread which surrounds the piston rod 24 and is fastened thereon, or can be realized directly by the external thread of the piston rod 24 . The threaded screw 56 may extend between the piston 40 and either of the end units 44, 46 over most of the axial length of the piston arrangement. In the illustrated embodiment, the screw 56 is disposed in the second working chamber 38 between the piston 40 and the second end unit 46 . The nut 54 may be secured to the wall 42 of the cylinder 20 in a suitable manner, for example by engaging at least one protrusion 58 protruding inwardly from the cylinder wall 42 with a corresponding recess 60 of the nut 54 .

Since the helical movement between the piston arrangement 22 and the cylinder 20 contains an axial movement component, for the relative movement between the piston arrangement 22 and the cylinder 20, an exchange of damping fluid between the first working chamber 36 and the second working chamber 38 is necessary ie, a reduction of one of the two working chambers 36 , 38 favors the other of the working chambers 38 , 36 . For this purpose, at least one damping fluid channel 62 - 1 can be provided in the piston 40 , which allows a defined exchange of damping fluid between the working chambers 36 , 38 or blocks this exchange. In the illustrated embodiment two damping fluid passages 62-1 and 62-2 are provided.

A valve 64 - 1 is preferably arranged in at least one damping fluid channel 62 - 1 in order to influence the flow of damping fluid through the associated damping fluid channel 62 - 1 . In this exemplary embodiment, in particular a first valve 64-1 is arranged in the first damping fluid channel 62-1 and a second valve 64-2 is arranged in the second damping fluid channel 62-2.

Valve 64-1 may preferably be a non-return valve, in which valve port 66-1 is closed by valve body 68-1, wherein valve body 68-1 is preloaded to valve port 66-1 by spring element 70-1 in order to close the valve Mouth 66-1. In this exemplary embodiment, the spring element 70 - 1 is a disc spring arrangement with at least one disc spring inserted coaxially on the piston rod 24 , wherein the disc spring arrangement is axially supported on the one hand The piston device 22 is supported on the other hand on the valve body 68-1 in order to preload the valve body 68-1 in the closed position.

The damping fluid channel 62-1 can be widened in its section close to the valve 64-1, in particular can have an opening in the region of the valve seat on which the valve body closes the damping fluid channel 62-1, the opening larger than the remaining damping fluid passage 62-1. In the embodiment shown in FIG. 2, the enlargement of the damping fluid passage 62-1 at the gate 64-1 is achieved by step drilling. The size of the valve port closed by the valve body has a decisive influence on the pressure required to open the valve. The step drilling can achieve the effect that a predetermined force is required as a function of the valve position, ie as a function of the valve opening, to hold the valve in the open position and/and to adjust to another open position. In particular, the step drilling of the illustrated embodiment achieves the effect that a relatively high force is required to move the valve from the closed position to the open position, while relatively low force is required to maintain the valve in this open position. Step drilling can have one or more steps. In the case of multiple steps, a correspondingly multi-stage opening or closing behavior of the valves can be achieved.

If a second valve 64-2 is provided, it can be designed correspondingly in the above-described manner, but with an axial direction of action opposite to that of the first valve 64-1. This means, for example in FIG. 2 , that the first valve body 68 - 1 is preloaded by the first spring element 70 - 1 in the direction towards the second axial end 28 of the cylinder 20 to close the first damping fluid channel 62 - 1 position, while the second valve body 68-2 of the second valve 64-2 is preloaded in the opposite direction, that is, in the direction toward the axial first end 26 of the cylinder 20, by the second spring element 70-2 , so as to close the second damping fluid channel 62-2.

The above-mentioned valves 64-1 and 64-2 constitute a pair of check valves acting in opposite directions, so that during the movement of the piston 40 along the helical path toward the first end 26 or the second end 28 of the cylinder 20, the two valves 64-2 One of valves 1 and 64-2 is always open against the force of the corresponding spring element 70-1, 70-2 and allows the passage of damping fluid, while the other valve 64-2, 64-1 remains in the closed position.

A door hinge 10a according to a second embodiment of the present invention will be described in detail below with reference to FIGS. 3a and 3b. Only the differences from the first exemplary embodiment are discussed in detail here, for the rest, reference is explicitly made to the above description of the first exemplary embodiment.

According to a second embodiment, the valve 64a comprises a spherical valve body 68a situated in a valve opening 66a which widens the damping fluid channel 62a funnel-shaped at the axial end. The diameter of the valve body 68a is slightly larger than the inner diameter of the damping fluid passage 62a. The valve body 68a is preloaded axially towards the valve port 66a by the spring element 70a in order to normally close the damping fluid channel 62a. The annular contact surface on which the valve body 68a abuts against the funnel-shaped opening 66a in the closed position of the valve 64a forms an annular valve seat.

The configuration of the valve 64a shown in Figures 3a and 3b has the effect that, in order to lift the valve body 68a from the valve port 66a, a force exceeding a first predetermined threshold is required, and then, when the valve body 68a has been removed from the valve port As the valve body 68a is lifted above the valve body 66a, the force required to hold the valve body 68a in the lifted position is less than the force required for the previous lifting due to the increase in the annular surface of the valve body 68a. In other words, the valve 64a returns from the open position to the closed position when the force acting on the valve body 68a is lower than a second predetermined threshold, which is less than the first predetermined threshold. As a result, the force required to bring the piston-cylinder unit 16 into motion from a rest position is greater than the force required to maintain the motion of the piston-cylinder unit 16 .

The working principle of the door hinges 10 and 10a of the first embodiment or the second embodiment of the present invention will be described in detail below with reference to the accompanying drawings.

If the mounting elements 12, 14 are fixedly connected to the door leaf or door frame in the intended manner, then during the opening and closing operation of the door, the torque introduced from the outside to the door hinge 10, 10a is transmitted via the mounting elements 12, 14 to the piston-cylinder unit 16 . In this exemplary embodiment, the torque of the second mounting element 14 is introduced into the piston device 22 via the longitudinal toothing of the receptacle 34 and the matching longitudinal toothing 32 of the piston rod 24 . The torque input to the piston-cylinder unit 16 between the piston device 22 and the cylinder 20 is forced into a helical relative motion via the screw connection 52, with the result that the piston 40 also moves with a translational component of motion (in the axial direction along the The longitudinal axis L) moves toward the first end 26 or the second end 28 of the cylinder 20. Such a movement is only possible when the input torque is sufficiently great to open or hold at least one valve 64-1, 64a in the open position against the force of the corresponding spring element 70-1.

The total stroke of the piston-cylinder unit 16 can be limited by suitable stop devices, for example on the end units 44 , 46 . In order to achieve a soft stop function, the end units 44 , 46 are preferably damped by means of elastomeric components against impacts, for example by means of the support section 50 being formed from an elastomeric material. Alternatively, the axial length of the screw 56 can be limited so that the axial braking is performed by the stop of the nut 54 at the threaded end of the screw 56 .

In a first variant of the first or second embodiment, an adjusting element can be provided which makes it possible to control at least one valve 64 - 1 , 64 a from outside the cylinder 20 . As a result, at least one valve 64 - 1 , 64 a , preferably all valves arranged in the piston 40 , can be forced to be adjusted manually into an open position or a closed position. In particular, the exchange of damping fluid between the first working chamber 36 and the second working chamber 38 can be completely blocked by adjusting all valves to the closed position, thereby locking the movement of the piston-cylinder unit 16 and fixing the door in the current opening position. position or off position.

A third embodiment of the present invention will be described in detail below with reference to FIG. 4 . Only the differences from the first or second exemplary embodiment are discussed in detail here, for the rest, explicit reference is made to the above description of the previous exemplary embodiment.

The door hinge 10 b of the second embodiment includes a bypass passage 72 having an axial length greater than that of the piston 40 in sealing contact with the inside of the cylinder 20 . If the piston 40 is located in the axial position of the bypass channel 72, which spans the piston 40 in the axial direction, the exchange of damping fluid between the first working channel 36 and the second working channel 38 is independent of at least one The switching position of the valve 64 , ie in particular also when the valve 64 is closed, is achieved via the bypass channel 72 . As a result, the axial movement of the piston 40 and the resulting helical movement of the piston device 22 relative to the cylinder 20 takes place independently of the switching position of the valve 64 at least at the axial level of the bypass channel 72 . The axial length of the bypass passage 72 predetermines the range of free movement of the piston.

In particular when the valve 64 is closed, the movement of the piston 40 in the area of the bypass channel 72 is damped, wherein this damping depends on the flow cross section of the bypass channel 72 . Several bypass channels can be arranged at the same axial position in order to increase the flow cross-section and reduce damping. As shown in Figure 4, a plurality of bypass passages can also be provided at different axial positions, so as to define different no-load operating ranges of the piston 40, in which the movement of the piston-cylinder unit is within the valve 64 off is also possible. Specifically shown here is a first bypass passage 72 - 1 near the first axial end 26 of the cylinder 20 , and a second bypass passage 72 - 2 near the second axial end 28 of the cylinder 20 . As a result, even when all valves 64 provided in the piston 40 are closed, the piston-cylinder unit of the third embodiment can move within specific ranges respectively at the end positions.

The provision of at least one bypass channel 72 may also have the advantage of simplifying the locking of the piston-cylinder unit 16b. Since the bypass channel 72 on the cylinder 20 is easily accessible from the outside, this provides a structurally simple way to influence the flow of the bypass channel 72 by regulating elements, i.e. valves or similar devices that can be manually or electrically controlled from the outside cross section.

Claims (15)

1. a piston-cylinder unit (16), it includes

Have the longitudinal axis (L) cylinder (20) and

Piston apparatus (22) that insert described cylinder (20), that can move along the described longitudinal axis (L), described piston apparatus has Piston rod (24) and piston (40),

Wherein, described piston rod (24) runs through described cylinder (20) along the described longitudinal axis (L), thus described piston rod is both axially First end (26) place, stretches out described cylinder (20) at contrary axial second end (28) place again,

Wherein, described piston (40) will be filled with in the inner chamber of described cylinder (20) first working chamber (36) of damper fluid with The second working chamber (38) being filled with damper fluid separates,

It is characterized in that, described piston apparatus (22) and described cylinder (20) are connected with each other by spiral connecting piece (52), thus Enable the two relative to each other for the helical movement around the described longitudinal axis (L).

Piston-cylinder unit the most according to claim 1 (16), it is characterised in that solid on the inner side of described cylinder (20) Surely spiral type adnexa or nut (54), wherein, described spiral type adnexa or described nut or the most axially displaceably it are provided with (54) with counter element (56) luer engages with of described piston apparatus (22).

3. according to the piston-cylinder unit (16) described in claim 1 or claim 2, it is characterised in that at described piston rod (24) be arranged at the section outside described piston-cylinder unit is provided with rotation transmitting element (34), described rotates transmission unit Part can transmit rotatably with described piston rod (24) and axially displaceably be connected, and described rotation transmitting element relative to Described cylinder (20) remains and is not axially movable but rotatable.

4. according to the piston-cylinder unit described in claim 1 or claim 2, it is characterised in that at the foreign section of described cylinder On be provided with rotation transmitting element, described rotation transmitting element and described cylinder can transmit rotatably and axially displaceably Connect, and described rotation transmitting element remains relative to described piston apparatus and is not axially movable but rotatable.

5. according to the piston-cylinder unit (16) described in aforementioned any one of claim, it is characterised in that described first working chamber And described second working chamber (38) is by least one damper fluid passage (62-1,62-2 (36)；62a；72) it is connected with each other, institute State damper fluid passage be formed in described piston (40) or be formed at described cylinder (20) place as bypass channel (72), its In, preferably it is provided with in described damper fluid passage or at the opening part of described damper fluid passage and affects flow cross section Valve (64；64-1、64-2；64a).

Piston-cylinder unit the most according to claim 5 (16), it is characterised in that described valve (64；64-1、64-2； 64a) can be adjusted to closed mode, under described closed mode, described valve completely closes described damper fluid passage (62- 1、62-2；62a；), particularly, the friendship of the damper fluid between described first working chamber (36) and described second working chamber (38) Change and substantially completely block.

7. according to the piston-cylinder unit (16) described in claim 5 or claim 6, it is characterised in that described valve (64； 64-1、64-2；64a) there is spherical valve body.

8. according to the piston-cylinder unit (16) described in any one of claim 5～7, it is characterised in that described valve (64；64- 1、64-2；64a) can be controlled by regulating element, particularly can magnetic control.

9. according to the piston-cylinder unit (16) described in any one of claim 5～8, it is characterised in that described valve (64；64- 1、64-2；64a) be preloaded in closed position, and in damper fluid, the work of the pressure that exceedes predetermined first threshold It is switched to open position under with.

Piston-cylinder unit the most according to claim 9 (16), it is characterised in that when the pressure in damper fluid is less than the During two threshold values, described valve (64；64-1、64-2；64a) being switched to closed position from open position, described Second Threshold is less than Described first threshold.

11. according to the piston-cylinder unit (16) described in any one of claim 5～10, it is characterised in that damp at least two In fluid passage (62-1,62-2) or the opening part of at least two damper fluid passage be respectively arranged with check-valves (64-1, 64-2), wherein said check-valves (64-1,64-2) has opposite effect direction.

12. 1 kinds of door hinges (10；10a；10b), it includes

For the first installation elements (12) being arranged on door leaf,

For the second installation elements (14) being arranged on doorframe, and

According to the piston-cylinder unit (16) described in aforementioned any one of claim,

It is characterized in that, in said two installation elements (12,14) can transmit rotatably with described cylinder (20) even Connect or formed by described cylinder, and another in said two installation elements (12,14) can transmit rotatably with described work Stopper rod (24) connects or is formed by described piston rod.

13. door hinges (10 according to claim 12；10a；10b), it is characterised in that described cylinder is or/and described work Stopper rod axially displaceably and is torsionally maintained at the described installation elements of correspondence.

14. according to the door hinge (10 described in claim 12 or claim 13；10a；10b), it is characterised in that described hinge Axle overlaps with the longitudinal axis (L) of described cylinder (20), described first installation elements (12) around described hinge axis relative to described Two installation elements (14) swing.

15. according to described in any one of claim 12～14, there is piston-cylinder unit according to claim 5 (16) Door hinge, it is characterised in that described door hinge has the operating element for manually handling described regulating element, in order to basic On block the exchange of damper fluid between described first working chamber and described second working chamber (36,38) completely, or release institute State blocking-up.