SE1551153A1 - Swivel and / or pivot-lockable roll as well as displacement device with such roll - Google Patents

Abstract

The invention first relates to a pivotable and / or pivotable block, designed into the blocking position by means of a spring biased roller (4), in particular guide roller, wherein an operating bolt is provided, which by means of a coupling actuating means is movable into a blocking or releasing position. In order to further improve a roller of the type in question in an advantageous manner, it is proposed that the coupling actuating means self-actingly move as a result of the spring load starting from a release position and / or a pivot blocking position into the blocking position. The invention further relates to a displacement device (1) with a pivotable and / or rotatable lockable design, into the blocking position by means of a spring biased roller (4), in particular guide roller, wherein a control bolt is provided, which by means of a coupling actuating means is displaceable into a locking or release position, wherein the roller (4) is in a permanent blocking position without the intervention of a user. In order to further improve a device of the type in question, it is proposed that the device (1) has an operating part (48), with which the user, by approaching or touching the operating part (48), can cause the release position during the procedure (joint figure: Fig. 1). )

Description

The invention firstly relates to a pivot- and / or rotatable-shaped roller, in blocking position by means of a spring pre-tensioned roller, in particular guide roller, wherein a control bolt Jr is provided, which Jr fO means a movable and / or rotatable locking roller. coupling actuator to a blocking or releasing device.

Rolls of the type in question are kanda. In this case, reference is made, for example, to DE 10 2007 039 208 A1. The contents of this patent application will hereby be fully incorporated in the description of the present invention, also for the purpose of including criteria relating to this patent application in the claims of the present invention.

The blocking stand is in particular a rotary blocking stand, in which a rotational movement of the roller impeller around its horizontal axis is prevented. Such a rotary locking option is also possible with so-called buck wheels. Guide rollers, on the other hand, Jr further, insofar as they are not Jr blocked, pivotable about a vertical axis. Also in this context, as, for example, Jr edge through the above-mentioned patent application, a blocking stand for arch blocking is provided. Insofar as there is an arch and / or rotation lock, there is also talk of a total loosening of the guide roller.

Such rollers find use, for example, for sick songs, furniture or the like.

It is advisable to foresee a control bolt, via which the locking position (turning and / or arch locking position) of the roller can be taken. The control bolt is preferably spring biased in the blocking position. A release of the blockage takes place accordingly while overcoming the spring force.

In the state of the art mentioned above, a clutch actuating means for actuating the control bolt is provided, via which clutch actuating means the control bolt can be intentionally moved by a user from the blocking position into a release position. The release stand may be the rotary release stand alone, in addition to a total release stand, in which the roller Jr is both rotatable and pivotable.

With regard to the state of the art, one can see a technical problem with the invention in that it is advantageously further improved by the roll of the type in question.

A possible solution to the task is given according to a first inventive idea with respect to a roller, in which it is assumed that the coupling actuating means moves automatically as a result of spring load starting from a release position and / or an arch blocking position into the blocking position.

The invention relates to a transfer device with a pivotally and / or rotatably shaped, in blocking position by means of a spring biased roller, in particular guide roller, wherein a control bolt Jr is provided, which Jr is displaceable by means of a clutch actuating means to a blocking or release stall. a user is permanently in the blocking position.

The release and / or arch block position cannot be self-contained. Rather, a deliberate intervention by the user is required, which intervention leads to the attainment and maintenance of the release and / or swing blocking position (while maintaining the rotatability of the impeller about its wheel axle). With the failure of the engagement on the part of the user, the clutch actuator moves and preferably has the control bolt self-acting as a result of spring load back to the total blocking position. It is hereby established that in particular the rotary blocking of the roller, furthermore in particular the rotary blocking of all rollers belonging to a movable object, such as a sick song, is only originated, if the user intentionally causes this, in order to move the object. Otherwise the roller will move into the blocking position, possibly total unloading. The movable object is correspondingly secured against a self-acting rolling away, for example against a self-acting rolling down on a sloping surface. With regard to the transfer device, a further inventive idea is that the device has an operating part, with which the user can, by approaching or touching the operating part, cause the release position during the time of the intervention.

In a preferred embodiment, the user may choose between a rotary release stand and a total release stand of one or more of the rollers of the article.

Nardi, an operating part can be arranged on the movable fork, for example in the form of a handle or a lever, which operating part for releasing the roll during the moving process is to be continuously maneuvered. In the case of a handle, for example a rotatable handle, or in the case of a lever, the rotary release position or the total release position of the roller can optionally be taken through the angle of rotation or the lever carriage in the design of the roller as guide roller.

Such a maneuvering for rotary release and / or total release of the roller can furthermore also be achieved, for example, by a 15s. The user, in particular a legitimate user for moving the object, brings the roller directly into the preferred release position by maneuvering the lock by means of a corresponding key.

Furthermore, also, for example in a handling bar or the like belonging to the movable object, possibly contactless operating operating part, for example a sensor, in particular approach sensor or contact sensor, can be arranged, which in the case of corresponding contact or approach facilitates the movement of the coupling means into the release housing.

In the case of a release given by touch or mechanical displacement, it is further preferred to provide the device with two operating parts, for example in a handling bar, which operating parts are spaced apart from each other. This requires grasping or touching the control parts with the ram hands.

In addition, a contactless tripping is also possible, for example by designing the control part as an electronic receiver. The user, in particular a eligible 4 user, has a corresponding electronic sander, for example in the form of a chip card provided with a chip, which can be worn in the clothes. For example, an RFID detection may be envisaged.

In particular in the case of a mechanical design of the operating part or parts, the action on the coupling actuating means can take place by means of a reptile or a bowden wire. A rod can also be provided. In addition, an electromotive actuation of the clutch actuating means can also be envisaged, this in particular in the case of electrical or electronic design of the actuating part, for example in the form of a laser or a sensor. With a handle or lever device, an electromotive maneuver can also be triggered.

The control bolt can be directly or indirectly exposed to the effect of the spring force. For this purpose, for example, a correspondingly arranged compression spring can be provided, which on one side rests on the control bolt and on the other side rests on, for example, a housing belonging to the roller.

The spring force can also directly or indirectly affect the clutch actuator and via the clutch actuator indirectly actuate the control bolt.

The coupling actuating means can be a lever device, on which lever device the spring can directly act for loading the system into the blocking position.

In a possible design, the clutch actuator is a clutch cam which is movable about an axis perpendicular to the longitudinal axis of the control bolt. A spring directly acting on the coupling actuating means or the coupling cam may be, for example, a shank spring, which acts in the direction of rotation of the coupling cam, in particular in the direction of the blocking position.

The coupling cam can have one or more, for example two or three, coupling designs fixed by a stop or an overflowable resistor, a coupling design in the activated state with respect to a line extending vertically through a pivot axis having the coupling cam for creating a sea arm is offset. designed in relation to the straight line.

In this case, in particular during direct spring loading of the control bolt, which control bolt cooperates with the coupling cam and with the coupling design of the coupling cam, a torque effect of the coupling cam acts in the direction of the locking position of the roller. A self-healing of the ridge in the release position is thus counteracted.

The coupling design cooperates with an actuating bolt of the control bolt towards the coupling cam. This habit can be convexly arched towards the coupling design or be provided with an inclined surface, which arching or inclined surface supports the self-acting repair of the coupling cam in the event of loss of the user-side load.

The coupling cam can be arranged in a pick-up having the roller, for example a mounting pin, which pick-up in all cases forms a fixed stop for the blocking stand. The blocking position of the coupling cam and the coupling actuator, respectively, is defined by the stop on the receiving side.

Preferably, the maximum release position is also limited in impact. This can be achieved by an additional fixed stop in the area of the recording.

The coupling cam and the coupling impact means respectively have correspondingly designed and positioned abutment areas, for co-operation with the fixed abutment of the pick-up.

An intermediate position between the blocking position and the maximum release position can be defined by an overflowable resistance. The overflowable resistance can be given by a coupling design of a coupling cam. The overflowable resistance preferably defines the total release position (rotational and pivot release position) of the roller. With the overflow of the resistor and the corresponding further displacement of the coupling actuating means, for instance further rotation of the coupling cam, the stop-limited rotation release position 6 of the roller is preferably accommodated. Also in this rotary release position, the coupling design offset to the straight lines described above can extend through the rotary axis of the coupling cam, this distance, as well as in the rotary release position, settling in the rotational direction of the coupling cam in the direction of the release coupling position. The control bolt acting on the coupling design as a result of the spring force exposes the coupling design to action and acts on the coupling cam to follow it back in the direction of the blocking stall.

In the rotary release position, the pivotability of the roller is blocked.

The ranges and value ranges or manga or ranges listed above and below, respectively, include with respect to the description of all intermediate values, in particular in 1/10 steps of the respective dimension, possibly also dimensionless. For example, the statement 1 to 2 mm also includes the description of 1.1 to 2 mm, 1 to 1.9 mm, 1.1 to 1.9 mm, 1.3 to 1.6 mm, etc., the description of 2 to 3 mm. mm also the description of 2.1 to 3 mm, 2 to 2.9 mm, 2.1 to 2.9 mm, 2.3 to 2.6 mm, etc. This description can on the one hand serve to delimit a named area boundary from below and / or from above, alternatively or supplementary, but also for the description of one or more singular values of a currently specified area.

The invention is further elucidated below with the aid of the accompanying drawings, which, however, only show exemplary embodiments. A part which is only elucidated with respect to one of the embodiments and in a further embodiment due to the special property appearing there is not replaced by another part, is thus also described for this further embodiment as a possible present part. The drawings show: Fig. 1 in perspective representation a transfer device in the form of a hospital song with operating parts for transferring the clutch actuating means in guide rollers to a release position, concerning a first embodiment; Fig. 2 shows a roll according to the embodiment of Fig. 1 in perspective view; Fig. 3 the vertical cut through the roller, concerning the blocking stall; Fig. 4 is a representation corresponding to Fig. 3, relating to a total release position; Fig. A further representation corresponding to Fig. 3, concerning the rotational release position of the roller; Fig. 6 is the magnification according to VI in Fig. 5, concerning a second embodiment for acting on the coupling actuating means; Fig. 7 is a view corresponding to Fig. 6, concerning a further embodiment; Fig. 8 is a perspective view of a part of a handling area for the transfer device with an operating part according to the first embodiment; Fig. 9en according to Fig. 8 corresponding representation with an alternative operating part; Fig. A further representation corresponding to Fig. 8 with an alternative operating part and a controllable wile; Fig. 11 shows a further embodiment of an operating part in a representation according to Fig. 8; Fig. 12 is a representation according to Fig. 8, corresponding to a contactless operating part in the form of a receiver, with assignable sanders.

Shown and described is first with respect to figure 1 a transfer device 1. This device 1 Jr in the case shown is a hospital song, with a song frame 2, which Jr fixed to a chassis 3. 8 In the area of the four horns of the chassis 3 is in in all cases a roller 4 arranged.

The song frame 2 preferably has at least one main handling area 5 for the displacement of the song, for example in the form of a handling rod.

The rollers 4 are preferably designed as guide rollers, which guide rollers are pivotable in the use position around a vertical axis y, so that p5 s5 is set in particular to facilitate a cornering of the device 1.

Such guide rollers are in particular assigned to the foot area of the device 1, while assigned to the main area of the device, possibly also so-called buck wheels, can be arranged, which correspondingly are not pivotable about a vertical axis.

In particular with respect to p5 figures 2 to 5, a roller 4 is shown in the form of a double roller, i.e. with tv5 impellers 6 and a bar housing 7.

The bar housing 7 first has a circular cylindrical sectional area, p5 whose ram side surfaces in all cases a flywheel 6 is arranged. The impeller shaft x passes through the corresponding circular cylinder section of the bar housing 7 centrally.

Starting from this circular cylinder section of the bar housing 7, a bar housing section 8 develops approximately tangentially. This is preferably designed as a circular housing cylinder, with a cylinder shaft, which in use position coincides with the vertical axis y and with the pivot axis of the roller 4, respectively.

A mounting pin 9 is designed extending outwards over the free front surface of the barhouse section 8, shown vertically in the state of use. This pin is aligned coaxially with the barhouse section 8 and dives with a diameter reduced section towards the visible area into the barhouse section 8. Mounting pin 9 experiences a row against the inner cradle of the barhouse section 8 through two ball bearings 10 and 11. These are viewed in the axial direction of the barhouse section 8 only by being at a distance by means of an intermediate ring 12 almost directly arranged one below the other.

For IOW of this device, the mounting pin 9 is freely pivotable about the axis y which centrally passes through the bar housing section 8 opposite the bar housing 7.

In the mounting stage 9, a coupling actuating means 13 in the form of a coupling cam 14 is the hall. This is pivotable about an angle steering wheel towards the vertical axis y and thus perpendicular to the pivot axis of the roller 4 directed axis z, the shaft z centrally undergoing a hexagonal receptacle 15 of the coupling cam 14. Continuing on rear sides of this hexagonal receptacle 15 has the mounting pin 9 surrounding the coupling cam 14 16 for engaging a tool 17 acting on the coupling cam 14.

The clutch actuator 13, which in the embodiments according to Figures 1 to 6 is a clutch cam 14, acts on a control bolt 18 which occupies the pivot shaft y in the middle. This is elongate rod-shaped with a square cross-section formed in the area of cooperation with the diameter-reduced section of the mounting pin 9. The mantle bolt 18 is over-closed, torsionally fixed, but axially relatively displaceably connected to the mounting pin 9.

On the upper free front surface 19 the operating bolt 18 has the coupling cam 14 cooperates with, with respect to the axis of rotation z arranged on different diameter lines, coupling designs 20, 20 'and 20 ", for different axial alignment of the operating bolt 18. The front surface 19 is preferably convexly shaped towards the clutch actuator 13.

The coupling configurations 20 'and 20 "are designed with respect to the shaft z as radially projecting coupling noses, while the coupling design 20 forms a surface cooperating with the front surface 19 of the operating bolt 18.

The coupling design 20 ', which is present in the center in the direction of rotation of the coupling cam 14, is then designed as an overflowable resistor.

The control bolt 18 forms below the ball bearings 10, 11 a directional load part 21. This can be formed by wing sections 22 extending radially outwards with respect to p5 to the axis y.

The control bolt 18 extends downwards over the directional part 21. The free spirit of the control bolt 18, which is away from the coupling cam 14, is radially supported by receiving in a central half-cylinder section of a projected impeller brake portion 23. The cylinder section has the impeller brake portion 23 and the spring shaft portion 23. further in the direction of the control bolt 18. Handl is a cylinder compression spring 24 provided. This abuts with one end on the underside of a radial collar has the impeller brake part 23 and with the other end on one in the parallel plane to the radial collar and consequently perpendicular to the pivot axis y extending the bat 25 has the bar housing 7.

Above the cylinder compression spring 24, the control bolt 18 is directly biased over the impeller brake part 23 upwards in the direction of the clutch actuating means 13.

The PA impeller brake part 23 is a cantilever 26 pA-shaped. This was carried on the sides in the usual rolling direction of operation above the impeller shaft x in a transverse section U-shaped opening holder 27, for receiving tv5 for engaging on the impeller 6 suitable engaging parts 28, 29. These engaging parts 28, 29 are in the holder 27 with respect to p5 impeller shaft x displaceable in radial direction, whereby the displacement carriage Jr horizontally impact-limited radially outAt. In this direction radially outwards, the engaging parts 28, 29 are loaded by pressure springs 30 each supporting on the holding bottom.

In the area of the spirits used away from the compression springs 30, the engaging parts 28, 29 engaging teeth 31 are formed. These Yrs are designed for co-operation with an impeller-inside, circumferential toothing 32. The device is further preferably selected so that a co-operation occurs between the engaging teeth 31 and the impeller-toothing 32 with respect to the impeller shaft x in the usual roll direction of use at the highest point at the pre-existing one. the impeller 6. The displaceable control bolt 18 slidable towards the cylinder compression spring 24 in the axial direction cooperates in a position of the clutch actuating means 13 with its directional part 21 with a 15 counterpart 33 received in the bar housing section 8. The latter Jr. rotated the housing 18 through the housing in the case of axial displaceability, this further has a diameter-expanding opening area of the bar housing section 8 towards the outer diameter, the welding counterpart 33 has a jacket wall adapted to the diameter reference means described above, from which radially in the axial direction viewed in the middle 1 of the maneuver 8 penetrated lAsbotten 34 is deleted. This lock bottom 34 has depressions 35 adapted to the direction lock part 21 tvA in the basic drawing adapted to the wing sections 22.

On the underside, the locking base 34 is provided with a circumferential toothing 36 for co-operation with a substantially lower locking counterpart 33 coaxially arranged to this direction deflected blocking part 37. The latter has water against the welding counterpart 33 a surface with a counter-toothing 38.

The locking counterpart 33 and the turn-blocking part 37 are biased in the direction of the directional part 21, to which each part has a cylinder spring. Thus, the pivot blocking part 37 is loaded by means of a second cylinder compression spring 39 against the directional part 21. This second cylinder compression spring 39 rests on the pivot blocking part 37, on the underside away from the receiving tooth 38. In the second breath, the second cylinder compression spring 39 enters a ring space having the impeller brake part 23, for standing on it has formed the radial collar. The second cylinder compression spring 39 acts in the same direction as the first cylinder compression spring 24.

Concentrically to the second cylinder compression spring 39, a third cylinder compression spring 40 is provided. This rests on the usual barrel front surface of the impeller brake-sided half-cylinder section and loads the cradle of the locking counterpart 33 on the underside for biasing the locking counterpart 33 in the direction of the coupling actuator 13, the locking counterpart 33 being in the housing 7 and the housing housing section, respectively. Via the coupling actuating means 13, the roller 4 can be brought into different functional positions, thus (having the coupling cam 14 rotatable around the shaft z) into a neutral position (total release position) as shown in Figure 4, in which the roller 4 can be used as a guide roller, at release s5val of the rotation as well as the pivotability, further in a total solution shown in figure 3, in which the AN / al rotation as well as the pivoting is sparred, and in a flywheel position shown in figure 5, in which the pivotability is sparred, however Jr the rotatability of impellers 6 released (rotary release position).

In the neutral position and the guide roller position (total release position) according to Figure 4, the impellers 6 are freely rotatable about their impeller axis x and at the same time the whole roller is freely pivotable about the pivot axis y. This is achieved by bringing the coupling cam 14 into a pivotal position. which the central coupling design 20 'acts on the front surface 19 of the control bolt 18, the directional load part 21 in this neutral position remains at an axial distance above the depressions 35 of the counterpart 33. Correspondingly, the counterpart 33 and the directional lock part 21 are not engaged.

Via the directional locking part 21 of the mantle bolt 18, the pivot-blocking part 37 is also slid into a position radially spaced from the counterpart 33, so that no dimensional closure is achieved between these parts either. To MO hence the free range of motion of the roller around the axis y is achieved.

Via the control bolt 18, the impeller brake part 23 is also brought into an axial position against the force of the cylinder compression spring 24, used in the engaging teeth 31 of the engaging parts 28, 29 in a spacer position to the impeller-side toothing 32, whereby the free rotational movement of the impellers 6 is achieved.

The movement of the clutch actuator 13, has the clutch cam 14, takes place from the total solution according to Fig. 3 into the neutral stall according to Fig. 4 and into the impeller stand according to Fig. 5 (with respect to the representations in Figs. 3 to 5 due to the counterclockwise rotation of the clutch cam 14) against cylinder the force of the compression spring 24, which acts via the control bolt 18 against the coupling configurations 20 to 20 ". 13 The central position of the coupling cam (14) (total release position) is not loaded, thus more preferably not self-hammering. However, this coupling cam position must be intentionally maintained by the user of displacement. cI5 otherwise the coupling design 20 'slides back over the convex front surface 19 of the operating bolt 18 and thus a reversal of the coupling cam 14 into the overall loading stall is achieved.

This is done in particular as a result of external influencing means, such as through a tool 17 inserted and turned in the hexagon socket 15.

With respect to p5 a straight line running vertically through the axis of rotation of the coupling cam 14, which preferably coincides with the vertical axis y and with the pivot axis, respectively, the coupling design 20 'for providing the neutral position with a spacer on the front surface 19 of the control bolt 18. The spacer 1 a Jr. 2 mm, more preferably 1.2 to 1.5 mm. As a result, a sea arm is created, which under the influence of the force of the cylinder compression spring 24 tends to load the coupling cam 14 in a direction of rotation in the direction of the total solution according to Figure 3. The external influence is lost, for example via the tool 17, so forcibly controlled via the cylinder compression spring 24 and the control bolt 18 coupling cam 14 back into the overall release.

From the outside of the neutral position, by turning the clutch cam 14 in one or the other direction, that is to say with respect to the representations in Figures 3 to 5 clockwise or counterclockwise, either the total solution or the impeller position is achievable.

In Figure 3, the total unloading of the roller 4 is shown. The coupling cam 14 is rotated about the axis z from the neutral stand according to Fig. 4 with respect to the production in the counterclockwise direction from this position.

By the pivoting of the coupling cam 14, the flat and in this position preferably parallel to the accrued front surface 19 the coupling design 20 extending into the operative position, which tints an axial displacement wave upwards of the control bolt 18, 14 which is shown in the direction of the coupling cam 14. The corresponding 18 supported by the cylinder compression spring 24 abutment-limited upwardly, the abutment limitation being formed by the shaped directional part 21 facing the free neck section of the mounting pin 9 projecting into the bar housing section 8. The axial displacement carriage of the control bolt 18 in the neutral position according to Figure 4 figure 3 is for example about 4 mm.

Due to the axial displacement up of the control bolt 18, in turn in the direction of the coupling cam 14 via the cylinder compression spring 39, the arch blocking part 37 loaded with the formed counter-toothing 38 enters the toothing 36 of the counterpart 33. As a result, the roller 4 is pivot-blocked.

In addition, in this total alignment of the impeller brake part 23 raised p5 sA, it is set that the engaging teeth 31 have the engaging parts 21 and 29 engage in the impeller-sided toothing 32.

The total load of the clutch cam 14 and the clutch impact agent 13, respectively, is self-sustaining as a result of the spring force impact and the impact limitation.

Further starting from the neutral stall according to Figure 4, by (further) counterclockwise rotation of the clutch cam 14 the impeller stand according to Figure 5 is achieved. This clutch cam stall is also limited in abutment, to which a stop surface 42 is formed on the clutch cam 14 adjacent to the clutch design 20, which abutment surface edge section has the mounting pin 9.

Via the coupling design 20 "acting in this position, the control bolt 18 is displaced into the axially lowest position against the spring force of the cylinder compression spring 24, while carrying the impeller brake part 23.

Via the vertical displacement downwards of the control bolt 18, the pivot blocking part 37 is also slapped along, during pressure pressure by the second cylinder compression spring 39.

The directional welding part 21 formed on the control bolt 18 is brought with its wing sections into engaging position to the depressions 35 of the locking counterpart 33, in order to obtain a rotational locking of the roller 4.

Also in this pulley stall, the acting clutch design 20 "assumes a distance b to the vertical axis y, preferably an aistand b from 2 to 3 mm, further for example 2.7 mm. Thus, also in this stall a sea arm is given, which due to the spring force influence of the actuating bolt 18 and acting via this p5 coupling cam 14 tend to load the coupling cam 14 in the direction of the total welding.

In the absence of the unilateral action on the coupling cam 14, this self-acting is rotated back to the total solution according to Figure 3, this during overflow of the neutral intermediate position. The central coupling design 20 'is thus designed as an overflowable resistor. This self-acting reversal is supported by the convex front surface 19 of the control bolt 18.

With the exception of the overall solution according to Figure 3, preferably no other rotating position of the coupling cam 14 or any other position of the coupling actuating means 13 is self-holding stable.

As an alternative to the device of a rotatable coupling cam 14, according to the schematic representation in Figure 7, a sea-arm device 43 can also be provided. TV 5 lever arms are provided, one lever arm being articulated at the mounting pin side and the other lever arm being articulated at the upper free spirit of the control bolt 18. The ram armatures are connected to each other through the Ongjarnsled.

Due to the action of the lever arm device 43, as a result of a displacement of the lever arm from an angled position into a nearly stretched position (cf. dotted line representation in Figure 7), the control bolt 18 is moved vertically downwards to achieve the neutral position and beyond to achieve the flywheel position.

The one-sided effect on the clutch actuator 13 preferably takes place by remote maneuvering. 16 ardi are in a design mechanical means provided. In a further design, electrical means may also be provided.

Thus, the clutch actuator 13 may be directly or indirectly remotely maneuverable via a reptile or as shown — via a bowden wire 44. In Figure 1, such an embodiment is shown.

In the handling area 5 of the transfer device 1 Jr in this exemplary embodiment a hand-maneuverable sea arm 45 is arranged. This lever 45 acts as a kind of handbrake (although also with the opposite effect - activation of the lever 5 causes a release of the brake), Jr correspondingly in an inertial bearing around a fixed part 46, fixed in the handling area 5 (cf. also figure 8). the arm 45 acts on the bowden wire 44, which in turn attacks a sea arm 47. the arm 47 is rotatably attached to the tool 17, which tool 17 is inserted in the hexagon socket 15 of the coupling cam 14.

As a result of actuation of the lever arm, the lever arm 47 is tightened via the bowden wire 44 and via this the tool 17 and the corresponding coupling cam 14 are rotated about the axis of rotation z. The displacement of the lever 45 over the half possible displacement carriage 5 causes the actuating bolt 18 with the centrally located coupling design 20. the roll-neutral stand. This position can be haptically detectable as a result of the resistance that arises during the action by means of the coupling design 20 '.

By further displacement of the sea lever, the clutch cam 14 can be inserted into the flywheel stand.

As long as the user holds the sea arm 45 in one or the other position, the coupling cam 14 remains in the corresponding pivot position and thus the corresponding roller 4 in its corresponding release position. 17 If, on the other hand, the sea arm 45 is released, the system is moved automatically back into the basic position via the spring-loaded control bolt 18, namely the total displacement.

As further shown in Figure 1, a moving device 1 or 5 rollers 4, for example the foot-side rollers 4, can be provided with such a device. The ram rollers 4 can be maneuvered via a common maneuvering part 48, for example in the form of a lever arm 45. P5 advantageously a device is fixed by two separate operating parts 48, for example the lever arm 45, which are further preferably fixedly spaced apart from each other at the handling area 5. Salunda Jr . a maneuvering of the maneuvering parts with ram hands necessary to release the roller brake and move the device 1.

Alternatively, the lever arms 45 can be configured differently, for the effect of p5 and assigned roller 4, respectively. Thus, a lever arm 45, for example that in the usual displacement direction of the transfer device 1 right of the lever 45, can be designed so that via this Jr the assigned roller 4 can only be brought into the total release position (swivel roll position). The second sea arm 45, for example the left sea arm 45, is configured to achieve the total release position of the assigned roller 4, as well as by further extraction and thus via overflow of this position to achieve the flywheel position (swing position).

A bowden wire 44 can also act on the roller side directly on the coupling actuating means 13. Such a design is shown, for example, in Figure 6. This bowden wire end attacks the coupling cam 14 directly through the front side of the vertically pointing mounting pin 9, in order to move it out as a result. the total alignment into the neutral position and via this into the impeller position.

By means of such a bowden wire 44 a coupling actuating means 13 in the form of a sea-arm device 43 according to figure 7 can also be maneuvered. For example, this spirit of the bowden wire 44 in the articulation point between the ram hooves has the hopper device 43, so as to move this lever device 43 from its angled position into the nearly stretched stance. As an alternative to the design of the operating part 48 as a lever, in particular as a hand lever, this can also be in the form of a rotatable handle 55 (cf. Figure 9). Above the angle of rotation, the neutral position or the buckle stall can optionally be taken.

An exemplary electrical release is shown in Figure 10. For example, the operating part 48 is a load 50 inserted in a load bar 49 fixed to the handling area 5. An electrical contact can be closed via the load 50, for which a suitable key 51 is required. As a result, the movement of the transfer device can be limited to a entitled person.

The transfer device 1 further preferably has a power disturbance (not shown) of one or more electric motors 52, which, for example, acts on a tool 17 lying in the hexagon socket 15.

By inserting and turning the key 51, a contact is closed, so that the electric motor 52 is extended with current. Preferred is such a design for rollers 4, which have only two positions, namely a total loading and a release position and a torsion and pivot release position, respectively.

As long as the key 51 remains rotated in the IAset 50, the electric motor 52 maintains the corresponding release position, so that the device 1 is movable. With the key 51 pulled out, the system is automatically reset, in particular as a result of the tensioning of the cylinder compression spring 24, whereby also the tool 17 is retracted via the control bolt 18 and the rotating cam 14 which rotates.

According to the representation in Figure 11, the operating part 48 can also be a capacitive sensor 56, in particular a pressure or distance sensor. With registration of the handling area 5 in the area of the operating part 48, a corresponding signal is generated in particular for electromotive movement of the clutch actuating means 13, thus in particular a signal for moving the clutch actuating means 13 into the release position.

A contactless release for moving the clutch actuating means 13 into the roll release stand is also possible. According to the representation in Figure 12, at the handling area 5, an electronic receiver 53 can be arranged, for example an RFID receiver.

A particularly eligible person for moving the device 1 has at his disposal a assignable transmitter, for example an RFID transmitter, furthermore in the form of a card 54 with a corresponding chip. The card 54 in this case constitutes the operating part 48.

By approaching the receiver 53 with the card 54, a corresponding signal is generated, in particular for electromotive movement of the clutch actuating means 13 into the release position.

The above embodiments serve to illustrate the inventions included in the application, which in all cases independently further develop the state of the art at least by the following combinations of criteria, namely: A roller, which is characterized by the coupling actuating means 13 following a spring load or release from arch-blocking stance automatically moves into the blocking stall.

A roller, which is characterized in that the control bolt 18 is subjected to the action of the spring force.

A roller which is characterized by the spring force acting on the clutch actuating means 13.

A roller, which is characterized in that the coupling actuating means 31 is a coupling cam 14, which is movable about an axis z perpendicular to the longitudinal axis of the control bolt 18, and that the coupling cam 14 has one or more coupling designs 20, 20 'fixed by a stop or an overflowable resistance. 20 ", wherein a coupling design 20 ', 20" in the activated state with respect to a straight line of rotation of a coupling cam 14 of the coupling cam 14 for creating a sea arm for creating a sea arm is offset in relation to the straight line.

A roller, which is characterized in that the coupling design 20 to 20 "cooperates with a control bolt 18 facing the coupling cam 14.

A roller, which is characterized in that the coupling cam 14 is arranged in a receptacle of the roller 4, for example a mounting pin 9, which in the usual case forms a fixed stop for the blocking stall.

A roll, which Jr can be characterized by the fact that the maximum release position Jr grant limited.

A roller which is characterized in that an intermediate position between the blocking position and the maximum release position is defined by an overflowable resistance.

A device which is characterized in that the device 1 has an operating part 48, with which the user, by approaching or touching the operating part 48, can cause the release position during the time of the engagement.

All described criteria Jr (separately, but also in combination with each other) are essential to the invention. The description of the application also includes the description content of the associated / attached priority documents (copy of the pre-painting) as far as the content and the hall are concerned, also for the purpose of including criteria for these documents in the application. The subclaims characterize with their criteria independent inventive further developments of the state of the art, in particular in order to make partial applications on the basis of these requirements.

. 26 outriggers 27 holders 28 engaging part 29 engaging part compression spring 31 engaging tooth 32 toothing 33 welding counterpart 34 welding base deepening 36 toothing 37 arch blocking part 38 counter-toothing 39 cylinder-pressure spring cylinder-compression spring 41 shoulder 42 abutment surface 43 receiver 54 card 5 rotatable handle 56 sensor 22 distance mat distance mat x flywheel shaft ysvangaxel zvridaxel 23

Claims (1)

Claim claim 1. Swivel and pivotable block, designed into the blocking means by means of a spring (24) prestressed roller (4), in particular guide roller, a control bolt (18) being provided, which by means of a coupling actuating means (13) is movable into a blocking or releasing stall, characterized in that the clutch actuating means (13) moves automatically to IOW of the spring load starting from a releasing stall and / or an arch blocking stall into the blocking stall. Roller according to Claim 1, characterized in that the control bolt (18) is subjected to action by means of the spring force. Roller according to one of the preceding claims, characterized in that the spring force acts on the coupling actuating means (13). A roller according to any one of the preceding claims, characterized in that the coupling actuating means (13) has a coupling cam (14), which rotates about an axis (z) perpendicular to the long axis of the control bolt (18), and that the coupling cam (14) has one or more coupling designs (20, 20 ', 20 ") fixed by a stop or an overflowable resistor, wherein a coupling design (20, 20") in the activated state with respect to p 5 extends vertically through a pivot axis (z) of the coupling cam (14) at the use stand The straight line for creating an MN / arm is staggered in relation to the straight line. Roller according to any one of the preceding claims, characterized in that the coupling design (20 to 20 ") cooperates with a control of the control bolt (18) facing the coupling cam (14). 6. Roller according to any one of the preceding claims, characterized in that the coupling cam (14 ) is arranged in a receptacle of the roller (4), for example a mounting pin (9), which in the usual case forms a fixed abutment for the blocking stall.24 Roll according to the preceding claim, characterized in that the maximum release stall Jr is abutment-limited. Roll according to the preceding claim, characterized in that an intermediate position between the blocking position and the maximum release position Jr defined by an overflowable resistance 9. Movement device (1) with a pivotable and / or rotary blocking design, into the blocking position by means of a spring (24 pre-tensioning roller (4), in particular guide roller, wherein a mantiver bolt (18) is provided, which is displaceable by means of a coupling actuator. electricity (13) into a blocking or releasing stall, the roller (4) being permanently in the blocking stall without the intervention of a user, characterized in that the device (1) has an operating part (48), with which the user, by approaching or touching of the operating part (48) can cause the release position during the time of the engagement. Roll or transfer device, characterized by one or more criteria according to any one of claims 1 to 8. 1 / 1. // • 11 \ •• / '"44 ° 2/44 16 1 6 La: ti 4 4/8 127 - '1, 21-, 33' 38: 401. 391 18 1. k • 6/42 19 7 / / 43 8 / If q: 11 49 48 9 / •• = 1— 1 0 1 0 i 41 7