CN1246038A - shoe turn lock - Google Patents

Abstract

The present invention relates to a shoe buckle (1), comprising a rotating member (11) rigidly connected to a drive shaft (8) and a pulley (25) connected to the rotating member (11), wherein the buckle is characterized in that the tightening and loosening processes are improved so that they can be completed quickly. To achieve this, during the tightening process, when the pulley (25) is not loaded or has no significant load via a shoelace (28), there is no reduction ratio between the rotating member (11) and the pulley (25), or a reduction ratio lower than the reduction ratio when the pulley (25) is loaded or has a large load.

Description

shoe turn lock

The invention relates to a rotary lock for shoes according to the preamble of claim 1 .

This rotary lock is known from DE 4240916 C1. There, the transmission disc can be accommodated in the housing and mounted rotatably on the drive shaft. The transmission discs, optionally in different angular positions, are fixed in a rotationally fixed manner by means of one or more fasteners.

Furthermore, it is known from DE 4316340C1 that the fastener for the transmission disc is designed to elastically press against the stop part of the transmission disc. By means of a release element which can be actuated from the outside, the snap-in connection between the fastening element and the locking part can be canceled. Therefore, the transmission disc can rotate freely in the housing with the pulley, because the eccentric transmission is not effective at this time. This device is used to quickly loosen shoelaces when taking off shoes. So taking off the shoes can be done in a very short time such as a fraction of a second.

The object to be achieved by the invention is to improve a rotary lock of the type mentioned in the introduction so that the fastening process can also be carried out very quickly.

This object is achieved by the features specified in claim 1 .

By driving the pulley with a small reduction ratio at light loads, especially through a direct connection, i.e. a ratio of 1:1, the pulley is at the beginning of the tightening without, or at least without, a large tension caused by the tensioning of the shoelaces. Pulley load, fastening process can be carried out quickly. Only when the tightness of the shoelace is greater, the transmission is switched on, and the tightening process is completed with a lower rotational speed of the pulley than the rotating member but with greater force. The fastening process is thus carried out with the same effect in a very short time. This is especially advantageous for twist locks with large strap lengths, which are required for high-top shoes.

According to an advantageous improvement of the present invention, the following measures can be taken to automatically change the reduction ratio between the small load and the heavy load of the pulley, that is, the first friction clutch is set between the rotating member and the pulley, and the transmission disc A second friction clutch is provided with the housing or housing part. The first friction clutch is preferably adjusted in such a way or it can be adjusted in such a way that it causes the rotating part to be connected to the pulley until the pulley has a prescribed load, and from a higher load that can be adjusted if necessary Just disengaged the clutch. The second friction clutch is preferably adjusted in such a way or can be adjusted that the transmission disc can rotate during the direct connection between the rotating part and the pulley, in which case the eccentric transmission is braked and the first friction clutch When disengaged, the drive disc engages, ie prevents rotation, and thus activates the eccentric drive. In this way, the conversion of the driver level is automatically completed.

Further advantageous details of the invention are provided in the dependent claims and are explained further below with the aid of an exemplary embodiment represented in the drawing. In the attached picture:

Figure 1 is a cutaway side view of a rotary latch according to the present invention;

Fig. 2 or Fig. 2a to 2g each part of the first friction clutch;

Fig. 3 or Fig. 3a to 3e each part of the second friction clutch, wherein Fig. 3d represents the section I-I of Fig. 3c;

Fig. 4 or Fig. 4a to 4d The modification of each part of the second friction clutch;

Figure 5 is a perspective view of a shoe with a rotary lock provided on the instep;

Figure 6 is a perspective view of a shoe with a side mounted twist lock; and

Figure 7 is a perspective view of a shoe with a rear twist lock located in the heel area of the shoe.

The components of the rotary lock 1 for shoes shown in the cutaway side view of FIG. 1 include a housing 2 or a part of the housing. The housing has a flat bottom plate 3 and an upwardly protruding wall 4 . A bearing hole 5 is preferably centrally formed in the base plate 3 .

The journal 6 of the drive shaft 8 , which is arranged with its center line 7 perpendicular to the base plate 3 , is inserted into the bearing hole 5 . The end 9 of the drive shaft 8 opposite the journal 6 is rigidly connected via an intermediate link designed as an intermediate disc 10 to a rotary part 11 (for example a rotary knob). The rotating part 11 has an anchor ring surface 12, and its inwardly directed projection 13 engages positively in the annular groove 14 or in the recess of the wall 4 in such a way that the rotating part 11 cannot actually move along the drive shaft. 8 is displaced in the direction of the centerline 7, but is mounted rotatably. The position of the drive shaft 8 is thereby determined.

Concentric with the drive shaft 8 and rotatably mounted on the journal 6 is a transmission disc 15 placed on the inside of the bottom plate 3 . An eccentric disc 16 is arranged above the transmission disc 15 . It has a circular central opening 17 through which the eccentric disk 16 is rotatably mounted on a disk-shaped circular eccentric or eccentric section 18 of the drive shaft 8 . Accordingly, the eccentric disc 16 is mounted eccentrically with respect to the center line 7 and is rotatable about this center line 7 and about this eccentric section 18 , corresponding to the eccentricity of the eccentric wheel or eccentric section 18 .

In the region of its edge, the transmission disc 15 has upwardly protruding teeth 19 , for example in the form of round pillows 20 ( FIG. 3 c ). They interact with downwardly protruding teeth 21 formed in the edge region of the eccentric disk 16 . The tooth 21 is formed, for example, according to FIG. 3 a by a cone 22 . The teeth 21 of the eccentric disk 16 form the outer teeth, and the teeth 19 of the drive disk 15 form the inner teeth. According to the required reduction ratio, the round pillow 20 of the transmission disc 15 is less than the round platform 22 present on the eccentric disc 16 . The center of the round pillow 20 is on a circle concentric with respect to the axis of rotation of the transmission disc 15, which is smaller than the circle where the round platform 22 is located, and the center of the platform 22 is also located on a circle concentric with the axis of rotation of the eccentric disc 16 superior. The transmission disc 15 and the eccentric disc 16 constitute an eccentric transmission known for example from DE 4240916 C1.

The eccentric disc 16 has a plurality of circular holes 23, in which connecting pins 24 of belt pulleys 25 whose diameter is smaller than the diameter of the circular holes 23 are respectively inserted. The pulley 25 is arranged above the eccentric disc 16 . It has a central bearing hole 26 , through which the belt pulley is mounted without play, but rotatably, on a circular and disk-shaped bearing section 27 of the drive shaft 8 . The bearing section 27 is arranged concentrically with respect to the center line 7 of the drive shaft 8 .

The shoelace 28 is connected with the pulley 25 in a conventional manner, it is guided by the shoelace buckle 29 of the shoe 30, and the pulley 25 can be rotated to tighten or loosen the shoelace by the rotating member 11 (see FIG. 5 ).

A stop 32 designed as a U-shaped spring is embedded in the gap 31 between the pulley 25 and the intermediate disk 10 . The U-shaped arc section 33 of the stop 32 surrounds a lever 34 projecting into the recess 31 on the upper side of the pulley 25 directly or at a lateral distance. In this embodiment, the inner clear width 32 . 1 of the U-shaped spring or stop 32 is greater than the width 34 . 1 or diameter of the lever 34 . Therefore allow a small angle of rotation between the U-shaped spring or the stopper 32 and the driving lever 34, and this driving lever will not drive the U-shaped spring or the stopper 32 within the scope of this angle of rotation.

The legs 35 and 36 of the U-shaped spring or stop 32 project inwardly towards the drive shaft 8 . Each leg 35 , 36 presses elastically and prestressed laterally against the detent part 37 . In this embodiment, the braking portion 37 is designed as a polygon, ie hexagonal. Structural parts such as the driving lever 34 of the belt pulley 25, the U-shaped spring or the stopper 32 and the braking part 37 or hexagon of the drive shaft 8 constitute the rigid connection between the belt pulley 25 and the rotating member 11 or the rotating member. The first friction clutch R1 between the intermediate discs 10.

Here, a hexagonal detent section 37 extends upwards into a correspondingly designed groove 10.1 of the intermediate disk 10 or, if no intermediate disk 10 is provided, into a corresponding groove of the rotary disk 11. This results in a rotational connection of the intermediate disk 10 or the rotary part 11 to the drive shaft 8 . The fixed connection between these parts is preferably achieved by means of a precision fit or a force fit, in which case the intermediate disc 10 or the rotating part 11 is pressed against the detent part 37 .

A second friction clutch R2 is arranged between the transmission disc 15 and the housing 2 or housing part. In the exemplary embodiment, the second friction clutch is designed in such a way that an elastic stop 38 in the form of a stop spring is arranged between the housing 2 and the transmission disc 15, which is fixed either to the housing 2 or to a housing part or to on the transmission disc 15, and can be elastically locked in the stop groove 39 of the transmission disc 15 or the housing 2 or a part of the housing. The retaining spring 38 can preferably be designed in the form of a non-closed annular spring, which has a small section 40 pointing inwards (see FIG. 3 e ). This small section 40 is elastically inserted into a stop tooth 41 on the outer circumference 42 of the transmission disc 15 (see FIG. 3c ). The ring section 38.1 of the retaining spring 38 elastically and prestressed surrounds a housing part adjoining the transmission disk 15, which is the wall 4 in FIG. 1 . The segment 40 passes through a hole 43 in the wall 4 or the housing 2 or a housing part and rests elastically against the locking tooth 41 .

In order to quickly unlock the rotary buckle 1 and thus quickly take off the shoe 30 from the fastened state, an unlocking part 44 that can be manipulated from the outside is provided, which is mounted on the stop part 38 in such a way that it can Its stop part, here the small section 40 of the stop spring 38, is placed in the unlocked position in a known manner.

The second friction clutch R2 can preferably be designed in such a way that it locks only on one side, ie it only disengages the clutch in one direction, ie in the tightening direction. This is achieved in the exemplary embodiment in that the locking tooth 41 has an oblique sliding edge 45 in the tightening direction and a steep side 46 in the opening direction.

The rotary lock 1 can be detachably mounted on a fixing plate 47 fixed or fixable on the shoe 30 by its shell 2 or shell part, preferably replaceable or its shell 2 or shell Parts can form a structural unit with the fastening plate 47 .

According to FIG. 5, the fastening plate 47 can be mounted on the instep web 49 covering the instep 48 or on the tongue. Rotary lock 1 or fixed plate 47 is arranged or can be arranged on the instep region on the shoe 30 as shown in Figures 5,6 and 7 example, on the upper 51 of side shoe 30 especially in the region around the lateral malleolus, or rear In the heel area of upper shoe 30.

Preferably, the engagement force of the first friction clutch R1 and optionally also the engagement force of the second friction clutch R2 can be adjusted, in particular from the outside, so that individual adjustments can be made by the user.

A variant of the eccentric disk 16 and the transmission disk 15 is shown in FIGS. 4 a to 4 d. In this design, the toothing 21 of the eccentric disk 16 is integrated with the outer edge 52 , wherein the toothing 19 of the transmission disk 15 is designed as the plate surface 15 . 1 with the external toothing 19 . The height of the plate surface 15.1 is equal or approximately equal to the height of the outer edge 52 of the eccentric disc 16 and the height of the teeth 21 . Thus, smooth sliding of the two discs 15, 16 relative to each other is guaranteed.

The mode of action of the rotary lock according to the invention is as follows:

Assume that the rotary buckle 1 secured to the shoe 30 is in the open position and the shoelace 28 is fully unfastened, such as is the case when the shoe 30 is lifted off the instep tab 49 or the tongue. In this state, in principle, the belt pulley 25 needs to be rotated more than one turn, and most of them will be rotated more than one turn until the tightening force of the shoelace 28 is increased and the real tightening process starts with a larger pulling force. In this first practically load-free closing region, when the rotary member 11 is rotated in the tightening direction, the sides 35 and 36 of the hexagon 37 bear against the pretension force by means of the U-shaped spring 32, through which The U-shaped arc section 33 acting on the pulley 34 of the pulley 25 entrains the pulley 25 without the intermediate connection of the eccentric drive 15 , 16 . Therefore, the pulley 25 has no load and can turn the eccentric disc 16 and the transmission disc 15 engaged with it because the second friction clutch R2 is disengaged at this moment by its connecting pin 24 . Thus, the first friction clutch R1 is engaged in this engagement region, while the second friction clutch R2 is disengaged, wherein the small section 40 of the annular spring slides along the beveled sliding edge 46 of the transmission disk 15 .

If the shoelace 28 is wrapped around the pulley 25 to such an extent that the shoelace is under tension, the pulley 25 is loaded and prevented from further rotation. In this case, the engagement force of the first friction clutch R1 is overcome, and the sides 35 and 36 rattle past along the edges of the hexagon 37 . When the rotary part 11 rotates further, the drive shaft 8 now continues to rotate and causes the eccentric disk 16 to rotate eccentrically via the eccentric wheel or eccentric part 18 . In this case the teeth 21 of the eccentric disk 16 roll on the teeth 19 of the transmission disk 15 . The eccentric disk 16 with the belt pulley 25 connected thereto via the connecting pin 24 rotates slower than the rotary part 11 according to the reduction ratio of the eccentric drive (here, for example, 7:1). The shoe 30 can thus be closed slowly but firmly. In order to open the rotary lock 1 and take off the shoe 30, the unlocking part 44 can be pulled and the transmission disc 15 can be unlocked. The pulley 25 can thus rotate freely.

As mentioned above, with the present invention it is possible to carry out a quick closing process in the relaxed state, a strong tightening process in the subsequent fastening zone, and a very fast opening of the rotary latch.

The rotary lock 1 according to the invention can be used for various types of shoes, in particular sports shoes, travel shoes or leisure shoes.

Claims (25)

1. The buckle of the shoe, which has a rotating part rigidly connected with the drive shaft and a pulley connected with the rotating part, when the rotating part is turned in order to fasten the shoe, the shoelace can be wound on the pulley, in order to take off The shoelace can be unrolled from the pulley when the rotating part is turned, and a self-locking eccentric transmission device is provided between the rotating part and the pulley, which has a rotatable and deflectable in a plane parallel to the pulley. An eccentric transmission disc guided by displacement, the eccentric transmission disc is rotatably mounted on the eccentric wheel of the drive shaft, and the eccentric transmission disc has at least one circular hole on a circle concentric with its axis of rotation, in this one or One or each of these round holes is inserted into a connecting pin located on the pulley, which is characterized in that: for the tightening process, when there is no load on the pulley (25) or through the shoelace (28) on the pulley ( 25) When acting on the less load, there is no effective reduction ratio between the rotating part (11) and the belt pulley (25) or there is a load or a small reduction ratio when the load is larger than the belt pulley (25). 2. The rotary lock according to claim 1, characterized in that: a first friction clutch (R1) is provided between the rotating member (11) and the pulley (25), and a friction clutch (R1) is provided between the transmission disc (15) and the housing ( 2) Or a second friction clutch (R2) is provided between the casing parts. 3. The rotary lock according to claim 1 or 2, characterized in that: the second friction clutch (R2) is only after the first friction clutch (R1) is disengaged when the rotating member (11) rotates in the tightening direction before joining. 4. Rotary lock according to claim 3, characterized in that the second friction clutch (R2) is a friction clutch which acts only in one direction. 5. The rotary lock according to claim 3 or 4, characterized in that the second friction clutch (R2) is designed as an elastic stop (38), which is either fixed on the housing (2) or a housing part, or It is fixed on the transmission disc (15), and it can be locked in the stop groove (39) provided on the transmission disc (15), the housing (2) or the housing part. 6. The rotary lock as claimed in one of claims 3 to 5, characterized in that the second friction clutch (R2) is adjustable in the disengagement direction by means of an externally actuatable release element (44). 7. The rotary lock as claimed in one of claims 3 to 6, characterized in that the elastic stop (38) can be moved against its elastic force towards the unlocked position. 8. The rotary lock according to any one of claims 3 to 7, characterized in that: the transmission disc (15) has stop teeth (41) on the outer circumference (42); and the stop member (38) is designed as Unclosed annular spring, which surrounds the housing part (wall 4) adjacent to the transmission disc (15) under the action of pretension, and passes through a hole (43) in the housing part (wall 4) and direction to The small segment (40) of the inner finger is elastically pressed against the stop tooth (41). 9. The rotary lock according to one of claims 1 to 8, characterized in that the first friction clutch (R1) is connected directly to the rotating part (11) or indirectly or in particular via the drive shaft (8) or a stopper (32) fixedly or substantially fixedly arranged with the pulley (25) and a brake directly or indirectly arranged on or rigidly connected to the pulley (25) or the rotating member (11) part (37), the stopper (32) elastically acts on the braking part. 10. The rotary lock according to claim 9, characterized in that: the pulley (25) has a radially protruding lever (34), and the braking part (37) is designed as a polygon or a toothed ring and made On the drive shaft (8); and, establish a U-shaped spring as the stopper (32), its U-shaped arc section (33) surrounds the driving lever (34), and its limit starts from the driving lever (34) It extends towards the polygon or towards the toothed ring, in which case one edge ( 35 or 36 ) is elastically pressed against each side of the polygon or the toothed ring. 11. The rotary lock according to claim 10, characterized in that the inner clear width (32.1) of the U-shaped arc (33) is greater than the width or diameter (34.1) of the lever (34). 12. According to one of claims 1 to 11, the rotary lock is characterized in that: the drive shaft (8) has a braking part (37) for the first friction clutch (R1), a ) a concentric circular disk-shaped support section (27) is used to support the pulley (25), a disk-shaped eccentric section (18) is used to support and guide the eccentric disk (16), and there is a drive shaft (8) A concentric journal (6) is used to support the drive shaft (8) within the housing (2) or housing part. 13. The rotary lock according to claim 12, characterized in that the braking part (37) is designed as a hexagon. 14. The rotary lock according to one of claims 1 to 13, characterized in that the following rotary lock parts follow from the rotary part (11): - first friction clutch (R1), - pulleys (25), - eccentric disc (16), - Transmission disc (15) and second friction clutch (R2). 15. Rotary lock according to one of claims 1 to 14, characterized in that the braking part (37) arranged on the drive shaft (8), in particular a polygon or toothed ring, extends all the way to the rotating part (11 ) or in an intermediate link (10) rigidly connected thereto and is guided in a rotationally fixed manner therein. 16. The rotary lock according to claim 15, characterized in that: the polygonal or toothed ring designed as the braking part (37) is fixed on the rotating part (11) or the intermediate link (10) with a sliding seat or press fit Inside. 17. The rotary lock according to claim 15 or 16, characterized in that: the intermediate link (10) is designed as a disc concentric with the drive shaft (8), and forms a shaft with the casing (2) or a part of the casing. The relative position of the neck (6) is concentric to the drive shaft (8) bearing. 18. The rotary lock according to any one of claims 1 to 17, characterized in that the rotary part (11) has an anchor ring surface (12) which is closed or segmentally arranged concentrically with the drive shaft (8), and which It can be locked with a housing supporting part (14) in such a way that the rotating member (11) cannot move axially, but can be rotatably supported, and this locking device constitutes a joint with the journal ( 6) Matched thrust bearings. 19. The rotary lock according to any one of claims 1 to 18, characterized in that the housing (2) or parts of the housing are detachably and detentably inserted or can be inserted into a fastening lock which can be fixed to the shoe (30). plate (47). 20. Rotary lock according to one of claims 1 to 18, characterized in that the housing (2) or the housing part forms a structural unit with the fastening plate (47) fixed or fixable to the shoe (30) . 21. The rotary lock according to claim 19 or 20, characterized in that: the fixing plate (47) is installed or can be installed on the instep piece (49) of the shoe (30) covering the instep (48) or the shoe (30 ) on the tongue. 22. The rotary lock according to claim 19 or 20, characterized in that the fastening plate (47) is mounted or can be mounted on a lateral web (52) which at least partially covers the instep. 23. The rotary lock according to claim 19 or 20, characterized in that the fastening plate (47) is mounted or can be mounted on the shoe upper (51) at the side or at the rear. 24. The rotary lock as claimed in one of claims 1 to 23, characterized in that the engagement force of the first friction clutch (R1) is adjustable. 25. The rotary lock as claimed in one of claims 1 to 24, characterized in that the engagement force of the second friction clutch (R2) is adjustable.

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