WO2006040234A2

WO2006040234A2 - Caster

Info

Publication number: WO2006040234A2
Application number: PCT/EP2005/054590
Authority: WO
Inventors: Horst Hartkopf
Original assignee: Tente Gmbh & Co. Kg
Priority date: 2004-10-12
Filing date: 2005-09-15
Publication date: 2006-04-20
Also published as: DE202004016810U1; WO2006040234A3

Abstract

The invention relates to a caster (1) comprising a support (2), a swivel pin (3), at least one running wheel (4), and a device that is used for blocking the swiveling movement and is to be actuated by a pedal (8). The brake is engaged by horizontally displacing a brake part (B). In order to further develop a caster of said type in an advantageous manner regarding the design, the swiveling movement is blocked by vertically displacing a swivel catch (14).

Description

castor

The invention relates to a castor with a carrier and a Schwenkbol¬ zen further with at least one impeller and a device for pivoting feststellung which device is to be actuated by a pedal, further the braking intervention by horizontal displacement of a brake member er¬ follows.

Castors for equipment, furniture, nursing beds or the like have long been known from the prior art. A steering role of the type in question describes the German utility model 9413706. There, a foot lever having castor is designed as a double role. Both the wheels and the foot lever arranged between them are rotatably fixed by means of a wheel axle to a support member. For connection to appliances, furniture or the like, the support part has a protruding pivot pin about which the swivel castor is pivotable. When pressure is applied to the foot lever articulated within the carrier part in the direction of the ground support surface, a total determination of the castor wheel is achieved such that both the wheel arch and the pivotability are simultaneously blocked. In this regard, the foot lever has at its Radachsenanbin- training area a control cam, which cooperates upon actuation of the foot lever with a positioned in the support member braking member, wherein the spring-loaded brake member is displaced horizontally in pivot pin direction. This brake part is responsible for both the Radlaufblockierung as well as for the swivel blocking of the castor. For pivotal blocking, the brake member has a centrally arranged and horizontally aligned concave toothing with a vertical orientation. In addition, the braking part likewise has toothing in the form of brake shoes on its narrow side flanks. In the case of a displacement of the brake member, on the one hand the concave toothing interacts with a toothing of a toothed wheel which is aligned with it and which is arranged about the pivot pin axis. In addition, in each case, the toothing of the brake shoes, which dips into the rear side of the impeller inner side faces, also interacts with an inner ring toothing of the running wheels, which is in each case designed to be equivalent thereto. As a result, the brake part assumes a double function. On the one hand on the concave toothing, the function of the pivoting blocking and on the other hand on the brake shoe gearing the Radlaufblockierung.

The invention has for its object to develop a steering role of speech in the kind in the structural design in an advantageous manner.

This object is achieved initially and essentially in a steering roller with the features of claim 1, wherein it is based on the fact that the pivotal position er¬ follows by vertical displacement of a pivoting lock. As a result of such a design, a steering roller is provided with the constructive possibility of arranging pivoting stops within the steering roller carrier of the area which passes through the pivot pin or in the area provided by the pivot pin. The already serving the swivel training neck portion of the steering roller carrier can be used according to the arrangement and the sliding displacement of the swivel detent. For this arrangement and relocation in principle no separately to be provided radial space is needed. The vertical displacement of the pivotal lock is adjusted to the pivot axis orientation, so preferably parallel to this. The Schwenk¬ determination acts according to the inventive arrangement axially or indirectly with the pivot pin together. It is also advantageous to arrange the pivot lock in a space-saving manner, for example, with the formation of a half-shell-shaped plan.

The subjects of the further claims are explained below with reference to the subject matter of claim 1, but may also be significant in their independent formulation. Thus, it proves to be advantageous that the braking part and pivoting stopper formed as separate parts are motion-connected via a wedge-type association. In this way, in spite of the angle including different traverse paths of the brake member and the swivel actuator, an interaction of these components is advantageously provided so that they preferably move together at least in terms of a return movement into the non-engaged position. Alternatively, an independent displacement of, for example, the pivot lock can also be made possible by an intent-toned cancellation of the wedge allocation, for example, to form a non-braked fixed castor position of the swing lock alone. It is preferably provided that the wedge interaction of the brake part and swiveling fastener for dragging one of the parts into the inactive position during the impact of the other part is formed. As a biasing element spielsweise a compression spring or the like can be used. The latter can co-operate either with the swivel lock or else with the brake part in order to transfer the respective component from the active position into an inactive position. Regardless of the assignment of the compression spring it is force-storing compensated during the transfer of the inactive position in the active position of the swing stop or the brake member to deliver¬ the necessary application force. In addition, other force-storing elements can provide the admission. Another advantage results from the measure that the brake member is divided into two, wherein the brake member consists of a wedge-coupling part and an engagement part. In this case, the wedge-coupling part practically serves as a connecting bridge between the swiveling fastener and the engagement part forming a brake member. It is further proposed that the engagement member is slidably connected transversely to the horizontal direction of movement of the brake member with the wedge-coupling part. As a result, the engagement part is optionally interchangeable with simple steps and without special tool. Also, by the aligned transversely to the wedge-coupling part engagement part, the actual braking surface of the brake partly widened. For triggering or displacement of the brake member or the swivel lock, it is proposed that the foot lever has two connecting jaws cooperating respectively with the brake member and with the swivel lock. The displacement cams can be designed, for example, as control cams, which in turn radially surround the wheel axle. It is also advantageous that the foot lever is arranged pivotable about a horizontal axis and that the brake part is caught by means of a slot opening on the horizontal axis. Preferably, the horizontal axis is gebil¬ det of the wheel axle. By means of the longitudinal extent of the slot opening, the brake part is limited in its displacement path, with the slot ends in each case serving as end stops. In addition, the braking part is guided over the oblong hole opening cooperating with the horizontal axis during its displacement. Furthermore, the invention proposes that the carrier has an insertion opening running parallel to the horizontal axis for mounting the engagement part on the wedge coupling part. This proves to be advantageous from an assembly point of view, since in this way the engagement part connected to the wedge coupling part can be mounted or exchanged without great effort. Another advantage is the fact that castors with the same mechanics design can be produced in different castor width. In order to take into account each widening of the castor, only the engaging member must be adapted to the respective desired castor width in the longitudinal direction, wherein the wedge-coupling part or the swivel lock need no structural changes. Even the insertion opening formed from the support requires no change in its basic contour. As a result, manufacturing cost and material savings are achieved thereby.

An exemplary embodiment of the invention will be explained below with reference to drawings. It shows: Figure 1 is a trained as a castor double role in perspective An¬ view.

Fig. 2 is an exploded perspective view of the steering roller;

3 shows a cross section of the non-blocked steering roller.

4 shows the section according to the representation in FIG. 3, with the foot lever displaced into the blocking position; FIG.

5 shows the section along the line V - V in Fig. 3;

Fig. 6 shows the section along the line VI - VI in Fig. 3 and

7 shows the section along the line VII - VII in Fig. 4th

The steering roller bears the reference numeral 1. The core of this steering roller 1 is a carrier 2 forming a housing, which in turn is made of a plastic material, for example polyamide. A production of the carrier 2 from a metal material such as steel sheet is also possible. In the usual place, the carrier 2 has a vertically projecting, a Montage¬ pin forming pivot pin 3 for pivotally fixing the steering roller 1 to furniture, appliances, nursing beds or the like. The broad sides of the carrier 1 are each flanked by impellers 4 which are aligned congruently to one another. These are fixed in a rotatably movable manner on the carrier 2 via a wheel axle 5 aligned transversely to the pivot pin 3 and centrally passing through the carrier 2. The respective attachment of the wheels 4 at the front ends of the wheel axle 5 in a conventional manner and is therefore not described or illustrated here in detail. For receiving the wheel axle 5, the carrier 2 has a centrally arranged circular bearing opening 6, which in turn is adapted in diameter to the diameter of the wheel axle 5. The wheels made of a plastic material, for example polyamide, are each surrounded by a tread that is softer in shape. In this case, in each case the running surface can also be made of a plastic material. As a material, for example, a polyurethane material can be pulled up, whereby the wheels 4 ensure increased ride comfort. In addition, the wheels 4 each have a closure element in the form of cover caps 7 on their outwardly facing circular broadside surfaces. These made of a plastic material circular cover caps 7 cover each except the tread the außensei¬ term wheel body of the wheels 4. As a result, both the front ends of the wheel axle 5 and the wheel body of the wheels 4 are protected in a known manner from dirt or the like.

As can be seen from the illustrations, the carrier 2 is assigned a foot lever 8 at a known location between the wheels 4. This foot lever 8, which has approximately the shape of a crescent in cross-section, has an actuating portion 9, which has a groove and runs parallel to the wheel axle 5, which projects beyond the respective running surfaces of the running wheels 4 at a small distance. The surface Verrillung the operating portion 9 is to prevent the foot from slipping off the actuating foot when operating the foot lever 8, for example by the foot of an operator. As can be seen in particular from the illustrations in FIGS. 3 and 4, the actuating section 9 aligned obliquely on the wheel axis 5 lies above a horizontal axis a surrounding the wheel axle 5. About a the actuating portion 9 gege¬ lying bearing arm 10 of the foot lever 8 is connected within the approximately skeletal shaped integral support 2 motion. In this regard, the bearing arm 10, which has approximately a pear-shaped basic contour, has a circular bearing opening 11 introduced transversely thereto and surrounding the wheel axle 5. Thus, on the one hand, the foot lever 8 is aligned with it Horizontal axis a and on the other hand, the operating portion 9 of the foot lever 8 about the running surfaces of the wheels 4 pivotally.

As the basic position in FIG. 3 shows, the bearing arm 10 has control cams in the form of displacement cams 12 and 13 arranged around the wheel axle 5 and stepped from the outer wall. The orientation of the sliding cams 12 and 13 is such that the Displacement cam 12 following the pivot pin 3 vertically and the displacement cam 13 on the Actuate supply section 9 facing horizontally aligned. The shift cams 12 and 13, which are formed in a stepped manner from the rounded pear-shaped section, interact on the one hand with a vertically oriented pivot lock 14 and on the other hand with a horizontally oriented brake part B. Here, the displacement cam 12 is assigned to the pivot lock 14 and the displacement cam 13 of the brake member B.

The pivot lock 14 is mounted vertically displaceably in a vertically oriented carrier cavity 15 in the carrier 2 and positioned coaxially to a pivot axis b. In addition, the pivot lock 14 cooperates in the total determination of the steering roller 1 shown in FIG. 4 with a pivoting recess A arranged vertically about the pivot axis b. Part of this pivoting device A is the already mentioned vertically extending pivot pin 3. The trained in a known manner pivoting recess A has on the underside and of the pivot pin 3 abge¬ a transverse to the pivot axis b aligned bevel gear 16 with a ner on the pivot lock 14 facing teeth 17th ,

About the teeth 17 of the bevel gear 16, the pivoting action A cooperates with the pivot lock 14. In this regard, has the approximately L-shaped in cross-section swivel lock 14 at its facing to the bevel gear 16 free front end of the L-leg 14 'a vertically abra¬ ing circular segment toothing 18, which in turn in the total blocking the steering roller 1 with the teeth 17 of the bevel gear 16 rotatably cooperating.

As can be seen in FIG. 2, the L-leg 14 'is approximately circular-shaped in cross-section. As a result, the shape of the circular segment toothing 18 is taken into account. About the concave inner wall of the L-leg 14 'of the pivot lock 14 by means of an equivalent thereto formed convex portion 19 of the support cavity 15 within the carrier 2 can be guided vertically. In addition, the L-leg 14 'rearwardly directed to the respective narrow sides toward each other and vertically aligned guide ribs 20 are formed, which in turn are dimensioned smaller in its longitudinal extent than the longitudinal extension of the L-leg 14'. The latter guide ribs 20 slide during vertical displacement of the swivel arrester 14 within a rear-cut section 21 of the carrier cavity 15. The undercut section 21 aligned coaxially to the swivel axis b is dimensioned in its vertical longitudinal extension such that it is oversized to the longitudinal extension of the guide ribs 20 has. This oversize is in conformity with the vertical displacement path of the pivot lock 14. In addition, the hin¬ terschnittene section 21 in this regard forms a stop limit for the pivot lock 14 so that it meshes properly over its circular segment teeth 18 with the teeth 17 of the bevel gear 16.

The L-leg 14 "of the pivoting stop 14, which is enclosed with the L-leg 14 'at an angle at right angles, is oriented transversely to the pivot axis b, as shown in the illustrations Back of the L-bridge 14 ". Also rooted on the back of the L-bar 14 "is a vertically projecting pin 22, which in turn is spaced apart from the back of the L-leg 14 'and flanked respectively by the vertical guide ribs 20. The pin 22 serves for vertical Guide of a spring element in the form of a compression spring 23, which in turn with a Windungsende backwards on the L- The other opposite section or the winding end of the compression spring 23 lies in an equivalent vertical adjustment 24 of the carrier 2. The free end 25 of the L-bar 14 "facing the operating section 9 is step-shaped formed, the latter cooperates with a projection 26 of the support cavity 15 in the total determination of the steering roller 1 stop limited.

The bottom of the L-bar 14 "facing the bearing arm 10 of the foot lever 8 is for the most part traversed by a semi-open cavity 27 of approximately rectangular cross-section As can be seen in particular from FIG. 3, the bottom of the cavity 27 is step-shaped, thereby forming the body Step 28 has an outer contour which corresponds to that of the vertically aligned displacement cam 12 of the bearing arm 10. Via this step 28 of the cavity 27, the pivot lock 14 interacts with the bearing arm 10 of the footrest 8 such that the outer wall of the displacement cam 12 and In addition, the region of the bearing arm 10 which is inserted into the cavity 27 is flanked in each case by the inner walls of the longitudinal side walls 29 of the cavity 27 at a small distance (cf., in particular, the sectional illustration in FIG.

At the created by the cavity 27, congruent aligned side walls 29 each vertically projecting and facing the horizontal axis a coupling elements 30 in the form of gleich¬ schenkligen triangles rooted in turn each have the same thickness direction as that of the side walls 29. In addition, the arrangement the coupling elements 30 are positioned such that they are centered in the longitudinal extension of the L-web 14 ". By means of these coupling elements 30, the entire pivot-lock fastener 14 cooperates with the brake part B.

With regard to the design of the brake part B, it is provided that this is composed of two separate construction elements, namely, made a cooperating with the pivot lock 14 wedge-coupling member 31 and a slide connected to this engagement part 32. The aligned transversely to the horizontal axis a and the wheel axle 5 approximately cuboid-shaped wedge coupling member 31 has a U-shaped cross-section, wherein the congruent aligned U-legs 33 are each traversed by the horizontal axis a aligned slots 34. By way of the obliquely aligned oblong holes 34 or by the wheel axle 5 inserted in each case in the slots 34, the braking part B denominated overall is guided transversely to the horizontal axis a linearly. In each case, the slot ends of the slots 34 serve as cooperating with the lateral surface of the wheel axle 5 end stops. Like the inner wall of the side walls 29 of the pivoting stop 14, the inner walls of the U-legs 33 flank the outer broad surfaces of the bearing arm 10 at a small distance. As a result, the bearing arm 10 and the foot lever 8 practically within the carrier 2 immovable, ie in the direction of the horizontal axis a, caught. In addition, both the swivel lock 14 and the wedge coupling part 31 are flanked by the inner wall of the support cavity 15, so that they are also secured against transverse displacement.

The remote from the U-web 35 free ends of the U-legs 33 of the wedge coupling member 31 each have directly on the edge region above the wheel axle 5 arranged wedge-shaped depressions 36. These recesses 36, which extend parallel to the horizontal axis a, are designed in their shape such that they are respectively adapted to the coupling elements 30 of the pivoting stop 14. That is, in the basic position of the steering roller 1, the coupling elements 30 of the pivoting lock 14 completely immersed in the equivalent formed recesses 36 of the wedge coupling member 31, wherein both the tapered coupling elements 30 and the recesses 36 each with their tips on the Bodenstellfläche the castor 1 point. The flanked by the U-legs 33 back of the U-web 35 of the wedge coupling member 31 is also like the cavity 27 of the pivoting lock 14 to form a step 37 is step-shaped. The step 37 cooperates with the horizontally oriented displacement cam 13 of the actuating arm 10 of the foot lever 8 such that the step 37 is adapted to the outer contour of the shift cam 13 and both outer contours in the Grund¬ position of the steering roller 1 touch each other. Both the step 28 of the swivel lock 14 and the step 37 of the wedge coupling part 31 are positioned so that they are ready to take each in the Verschwenkungsbahn the shift cam 12 and 13 of the bearing arm 10.

As already mentioned, the engagement part 32 oriented parallel to the horizontal axis a is push-connected to the wedge-coupling part 31. To realize this form-fitting connection, a dovetail connection S is provided, it being provided that the foot lever 8 facing breast of the U-web 35 of the wedge coupling member 31 parallel to the Horizon¬ talachse a extending male counterpart 38 of this Schwalbenschwanzver¬ bond S owns. The female configuration 39 of the dovetail connection S is assigned to the engagement part 32 in such a way that it is formed from the spine facing the wheel axle 5. The longitudinal extent of the female formation 39 amounts to approximately three quarters of the longitudinal extension of the engagement part 32. In this way, a stop forming a bottom 40 is formed within the female formation 39. As a result, the engagement part 32 can be pushed onto the wedge coupling part 31 in a stop-limited manner.

In order to connect the engagement part 32 with the wedge coupling part 31 inserted in the support cavity 15 and displaceable transversely in the wedge coupling part 31, an insertion opening 41 running parallel to the horizontal axis a is provided. The latter insertion opening 41 is formed from the carrier 2, wherein the insertion openings of the insertion opening 41 oriented in alignment with each other are assigned to the respective broad side surfaces of the carrier 2. Of the Cross section of the insertion opening 41 is adapted to the cross section of the engagement steep 32. Both the engagement part 32 and the insertion opening 41 each have a rounded portion oriented vertically relative to the representations, the convex breast of the engagement pointing steeply 32 in the direction of the running surfaces of the running wheels. The opposite concave ausgebil¬ dete portion of the insertion opening 41 is spaced in the Grund¬ shown in Fig. 3 position of the steering roller 1 of the convex breast of the engaging part. This is because by this distance the engagement steep 32 within the Ein¬ thrust opening 41 is horizontally displaceable, wherein the horizontal narrow sides of the insertion opening 41 flank the horizontal narrow sides of the engagement member 32 leadership.

The convexly shaped breast of the engagement part 32 carries in each case on the narrow-sided edge region integrally formed and horizontally oriented steep-edge toothing 42.

The pivotal fixing or mounting of the ready-Lenkrol¬ le 1 to a device or the like is carried out in a conventional manner on the pivot pin 3 of the castor 1. If during use of the steering roller 1, if necessary, a total determination of the steering roller 1 is necessary, the Fußhe¬ bel 8th about its actuating portion 9 by means of Fußdruckbeaufschlagung the operator about the horizontal axis a and the wheel axis 5 to floor pivotally pivoted, so that the foot lever 8 in the direction of Bodenstell¬ surface of the steering roller 1 moves. In the course of this, the displacement cams 12 and 13 of the foot lever 8 also pivot about the horizontal axis a. In this case, the sliding cam 12 which cooperates with the step 28 of the cavity 27 of the pivoting device 14 displaces the pivoting stop vertically upward against the spring force of the compression spring 23 until the circular segmental toothing of the pivoting stop 14 properly engages in the toothing 17 of the bevel gear 16 of the pivoting drive A. engages locking or combs with this. In order to avoid an overstroke of the support cavity 15 in the To prevent cal displaceable pivotal lock 14, both the Füh¬ rungsrippen 20 and the step 25 of the pivot lock 14 are provided, which in turn limited stop limited by the undercut portion 21 and the projection 26 cooperate (see in particular the illustration in Fig. 4). Now in a known manner trained Schwenk¬ A is pivotally blocked, so that the steering roller 1 is no longer pivotable about the pivot axis b.

Along with the vertical displacement of the swiveling holder 14, the foot lever 8 also displaces the wedge-coupling part 31 forming the brake part B and the grip-connected part 32 such that the wedge coupling part 31 in the carrier cavity 15 and the Engagement part 32 are displaced horizontally displaceable in the insertion opening 41 until the arranged on the respective edge region of the engagement member 32 steep flank teeth 42 engage blocking in Radkranzverzahnungen 43 of the respective wheels 4.

With regard to the positioning of the Radkranzverzahnungen 43 is provided that they are respectively positioned on the Radkörperinnenflächen the wheels 4 centrally around the bearing opening 6 and in the mounted state each in circular wells 44, in which the respective Steilflankenverzahnun¬ gene 42 of the engagement steep 32 protrude, the broad sides of the carrier 2 einliegen. The Radkranzver¬ trained 43 equivalent to the Steilflankenverzahnungen 42 are directed towards each other in the assembled state and each centered about the horizontal axis a. Due to the above-described interaction of the brake member B or its steep flank teeth 42 with the wheel rim teeth 43 having wheels 4 is zuge¬ going to block the pivoting mechanism A, the brake blockage of the wheels 4 realized. Thus, a total determination of the steering roller 1 is achieved. Due to the eccentrically shaped displacement cam 12 and 13 is in connection tion with the transverse force acting spring load a latching of the pedal 8 in the total determination of the steering roller 1 given.

In the course of the horizontal displacement of the brake member B or of the wedge coupling member 31, the coupling elements 30 of the pivoting lock 14 glide out of the depressions 36 of the wedge coupling member 31, respectively, until the tips of the coupling elements 30 each extend to the edge region of the depressions 36 abut. This sliding-out of the coupling elements 30 caused by the horizontal displacement of the wedge coupling part 31 has a supporting effect on the vertical displacement of the pivot lock 14 (compare, in particular, the illustration in FIG. So that during the pivoting of the foot lever 8 no overtravel is exerted on the pivot lock 14 or on the brake part B, the foot lever 8 is stop-limited in its pivoting path. For this purpose, the foot lever 8 has below its operating portion 9 parallel to the horizontal axis aligned a and aligned in the mounted state on the lateral surface of the carrier 2 projections 45. These act after reaching the Schwenkendstellung of Fuß¬ lever 8 with formed from the support 2 locking projections 46 together which are associated near the edge region of the opening of the carrier cavity 15 and at a distance flank the bearing arm 10 of the foot lever 8.

In order to solve the total determination of the steering roller 1, spielsweise must by means of the toe of the foot of the operator on the underside of the operating portion 9 of the foot 8 to the rock axis wegab pivotally movable in a known manner. In the course of Rückverlage¬ tion of the pedal 8, the prestressed compression spring 23 pushes the Schwenk¬ fastener 14 vertically downward in the normal position. As a result of the spring-force-supported downward displacement, the coupling elements 30 of the pivoting fastener 14 slide back into the depressions 36 of the wedge-coupling part, which results in a concomitant horizontal rearward displacement into the basic position of the entire brake part B shown in FIG. 3 and the pivot lock 14 Episode has. In this case, the elongated holes 34 arranged in the wedge coupling part 31 and positioned about the wheel axis 5 serve as a guide, the respective slot ends of the elongated holes 34 respectively providing end stops. Thus, the blocking between the pivot lock 14 and pivoting arm A and between engagement steep 32 and the wheels 4 is repealed. As a result of the return displacement of the foot lever 8 into the starting position, the supporting action on the pivot lock 14 and on the brake part B cooperating with the pivot lock 14 is canceled, so that these shift backward by means of the prestressed compression spring 23. A shifted back entrainment of the pivoting lock 14 and the brake member B by the Fuß¬ lever 8 is preferably not shown as shown. Alternatively, however, the Fuß¬ lever 8 may be positively connected to the pivot lock 14 so that upon a pivoting back of the foot lever 8 in the initial position, the spring-loaded return displacement of pivot lock 14 and brake member B is supported.

For assembly or replacement of the engagement member 32, only one impeller 4 must be removed from the steering roller 1 in order to get to the arranged in the trough 44 insertion opening 41 of the carrier 2. If the engagement member 32 is removed, the male counterpart 38 of the wedge coupling member 31 is well operable in the insertion opening 41 a. Since the engagement is slid 32 only on its female mold 39 on the male counterpart 38 of the wedge coupling member 31, no special tool is necessary for replacement or assembly of the engaging member 32. In addition, the proper insertion end position of the engagement part 32 over the bottom 40 forming stop of the female formation 39 is always guaranteed.

By the above-described embodiment of the Einerichtes the steering roller 1 in particular of the engaging member 32 is given the possibility advantageously to produce castors with different width, this Beibe¬ attitude of the same embodiment of the Einerichtes, with only the Trä- ger 2 and the engaging member 32 are modified such that the carrier 2 in its width and the engagement member 32 must be changed in its extension length.

All disclosed features are essential to the invention. The disclosure content of the associated priority documents (copy of the prior application) is hereby also incorporated in full in the disclosure of the application, also for the purpose of including features of these documents in claims of the present application.

Claims

1. Steering roller (1) with a support (2) and a pivot pin (3), further with at least one impeller (4) and a device for pivotal position, which device by a foot lever (8) is to be actuated, wherein further Brake intervention by horizontal displacement of a brake member (B) takes place, characterized in that the Schwenkfeststel¬ ment by vertical displacement of a pivotal lock (14).

2. Castor according to claim 1 or in particular, characterized gekenn¬ characterized in that the separate parts designed as a brake member (B) and pivot lock (14) are connected by a wedge mapping movement.

3. A castor according to one or more of the preceding claims or in particular according thereto, characterized in that the wedge-interaction of brake member (B) and pivot lock (14) for entrainment of one of the parts is formed in the inactive position upon application of the other part.

4. Castor according to one or more of the preceding claims or in particular according thereto, characterized in that the brake member (B) is divided into two parts.

5. Castor according to one or more of the preceding claims or in particular according thereto, characterized in that the braking part (B) consists of a wedge-coupling part (31) and an engagement part (32).

6. Castor according to one or more of the preceding claims or in particular according thereto, characterized in that the engagement part (32) transverse to the horizontal direction of movement of the brake member (B) with the wedge-coupling part (31) is push-connected.

7. Castor according to one or more of the preceding claims or in particular according thereto, characterized in that the foot lever (8) has two zu¬ each with the brake member (B) and with the pivot lock (14) sammenwirkende displacement cam 12 and 13.

8. A castor according to one or more of the preceding claims or in particular according thereto, characterized in that the foot lever (8) about a horizontal axis (a) is pivotally mounted and that the brake member (B) by means of a slot opening (34) on the horizontal axis (a ) is caught.

9. A castor according to one or more of the preceding claims or in particular according thereto, characterized in that the carrier (2) has a parallel to the horizontal axis (a) extending insertion opening (41) for mounting the engagement part (32) on the wedge-coupling part ( 31).