DE2109356A1 - Spring tensioning device especially for safety heel ski bindings and toe piece bindings - Google Patents

Description

Spring clamping device especially for safety heel ski bindings or toe binding.

The invention relates generally to a spring tensioner of increasing spring force over the tensioning path.

a) The increase in the spring force over the tensioning path is for example at Buffers are advantageous in order to avoid movement shocks in the case of tip forces that would occur if a moving mass collides with a larger mass or an inelastic object, to avoid. The braking delay starts small and increases and this is perceived as pleasant in a vehicle, for example. There will be damage and injuries avoided.

b) Often a approximately constant spring force required for valves, regulators, for example or clamping plates with movement of the elastic clamping body. This requirement can only be achieved with great effort. Thin, flat disc springs with a large D / d ratios can only meet this requirement to a limited extent for small forces and Paths in the case of large internal *, k ßstresses, c) A spring force that decreases over the clamping path is then he "wishes, if on all or part of the spring tensioning path a Rapid movement should take place, because then the constant action force of the Drive member has an excess of force for acceleration, such as with the toggle switch where the spring work back and forth is the same.

There are numerous spring tensioning devices in which eccentrics, cams, Knee levers, etc., are used, which are subject to strong friction, with strong changes in the coefficient of friction through dirt, rust, ice with poor maintenance and lubrication, and one or the other several of the claims under a), b) and c) are unable to cope with, For example, ski bindings that work outdoors, where the adjusted Security Verte often change and are not reproducible.

The setting values do not correspond to the trigger values.

With almost all ski bindings, the safety releases are gradual in front of you, i.e. when the maximum release values are reached and the release takes place, remain still receive declining forces for a certain time and a cracked path, which prevent the skier from quickly choosing the best fall position. very It is bad when the path is constantly occurring with the jolts that occur continuously until the safety release in the binding is too small, because then the impact energy is not can be absorbed, the bond opens unintentionally and unnecessarily, and on the other hand the clamping forces decrease during this time, the maximum value at the beginning of the shock path occurs and unhindered in turn unintentionally and unnecessarily opens the bond. It will take place in both cases falls that occur when using a binding without a safety device would not have happened. The wrong elements are often used.

In the case of ski bindings, forward or reverse forces acting in the ski direction are

Clamping forces are necessary to avoid play for good ski alignment. There are no known facilities that, for example, when driving over bumps, or in the case of soft boot soles, keep these constricting forces constant to allow for changes to avoid the set safety values.

Readjustments by the skier are at least to a large extent Mass basically inexpedient, if at all necessary, this should be carried out by the sports shop by means of test facilities.

With many known safety heel ski bindings, the one when you get on Clamping in yourself by means of a step plate are the force of entry too big, so that in soft snow and especially on slopes, this is very difficult or not possible at all.

The invention shows solutions for a jig for everyone Purposes and also for ski bindings that put the SkistleSel on the heel and on the tip of the boot clamp the ski.

New individual elements and devices of a new kind are shown and application examples for safety heel ski bindings for adults and simpler ones for children without the aforementioned Disadvantage. It also shows solutions for new tasks.

It can do anything imaginable during the tensioning and unclamping process and required movement characteristics can be controlled. It'll be easy wear-resistant elements used.

The invention is characterized by the use of a force-displacement transmission gear as a movement transmission medium between spring element w @ ksames in spring tension direction 1 and pressure member II. Which one over the whole or part of the clamping path has further increasing or and constant or and decreasing clamping force. This applies to both the clamping and the unclamping force.

With the devices of the invention the object is achieved all three to bring about the aforementioned states during the movement sequence in a system, Every single state @ a), b) or c) or every state pairing can be present in a device ab), ac) or bc).

dun The Erfing is particularly based on executable examples for safety heel bindings described in detail. Further training of the subject matter of the main claim will be by subclaims and secondary claims and on the basis of examples, the independent Solutions to the Unified Problem are presented as the following tasks and problems are solved, avoiding the disadvantages mentioned above £ Large vertical and horizontal elasticity. Large vertical itub up to 25 mm. Constant horizontal Forward thrust during the thrust movements. Rising vertical as needed Clamping forces, beginning with relatively small forces, thereby become with the many Small bumps are gentle on the ankles and do not tire. besides, is falling over when standing and driving a little sideways without risk to the joints, Tendons and bones possible against the small initial forces. For racers and good ones However, the driver can also keep the clamping force constant during the entire vertical stroke being held. Due to the large lifting height, lower release forces can be set will1 because bumps no longer open the bond, which is why bonds with smaller Lifting height by the skier to avoid unnecessary falls, since then Always set harder 0 In the event of a fall, sudden opening with a catapult acting ejection forces, the best fall position can then be chosen unchecked. Small entry forces, especially on steep slopes and with new deep snow, avoidance the problem of friction due to external and internal influences Execution through completely closed housing. Protection against pollution and Corrosion.

No large sticky and icing surfaces, so no tearing forces either necessary. No large friction work, since the friction paths are small due to the small friction diameter, when force is applied to larger levers. therefore also insensitive to lubrication, especially when using cutting edge bearings. This would result in low wear and tear and permanent triggering forces that can be reproduced again and again with the same display.

As a touring binding, it is light weight, easy to switch and large clearance of at least 60 mm significant.

The same advantages result as a safety toe binding and a large side elasticity of 15 mm with a constant clamping force and jaw width with a sudden release of the following jaw opening for small ones Restoring forces.

Fig. 1 shows as an example a power-path transmission gear in the middle position with a mounted on the fixed joint 4 lever with lever arm 2, which is perpendicular to Direction of the action force A, and a lever arm 3. of the same effective lever length, which forms an angle smaller than 90 ° with the lever arm 2, with small Movements of the gear on lever arm 3 increase the effective lever length by the same factor reduced by which the force of the spring 1 increases according to its characteristic, and the Lever arm 2 hardly changes its effective lever length, the action force or tension force thus remains constant. The compression spring 1 is on the lever arm 3 with a blade bearing 21 stored. The action force A acts via a pressure member 11 on the pivot joint 22 on the lever arm 2.

Fig.2 shows a power-path "transmission gear with a rubber spring 1 and opposite lever arm position compared to Fig. 1 in which the clamping force A also remains constant, since the effective lever arm2 increases as the spring force increases elevated.

Fig. Shows a force-displacement transmission gear from Fig.1 and2 with an air spring 1 and a lever arm 2 with a lever arm 3 fixed to it form an angle smaller than 1800, whereby sow @@ lever arm3 to spring 1 and lever arm 2 do not form a right angle to the action force, the direction of the spring force and of the action force A, however, forming a right angle to each other Reduce the size of the gear unit and increase the effective lever lengths of the spring force and / of the action force, so that with constant action force there is an excess of force for quick actuation can result.

Fig. 4 shows a power-travel transmission with two opposing forces directed independent lever arms 2t and 3 'and external bearings 5 or 4 with their adjacent convex contact surfacesl4 and 13. When the gear is moving in the direction of the action force A, a very strong, infinitely variable arises on the transmission side Increase in the action force requirement, additionally by increasing the spring force because of their own characteristics, while the paths on the pressure member 11 are steadily smaller will.

FIG. 5 shows two unequally directed lever arms 2 'and 3' Lever length and one of the levers three cusps as rolling elements 15, when the gear is moving is switched in stages. When two rolling elements are in contact, a detent is created, similar to the effect of a locking groove, but with greater precision. The power requirement increases with decreasing paths.

Fig. 6 shows a force-displacement transmission gear with only one lever 2 ', which has a further arm 23. One of the rockable through the camp 30 Spring 1 acted upon rolling elements for example a rolling bearing can be between move two stops 19 'and 20'. When moving the gear in the direction of the action force A the lever tilts down to the right so that the rolling bearing se @@ is constantly moved to the right The beginning of the movement is drawn. Before the beginning was there Lever tilted down to the left. Up to the position shown increases in size the force of spring 1, then the spring force drops until the transmission reaches its system stop at 20 finds.

This happens suddenly, because if, for example, the power of action A applied by hand or through the foot @@ d, one does not have the power of action so quickly can take back as the spring moves the rolling element but then right away from the bearing 5 acts and holds the gear in the end position. To reverse the Transmission, the force of action must be reversed, one essential is sufficient for this smaller action force, as the effective levers on the double lever 2t are of unequal length. When you return, the movement work essentially takes over the stored work Energy in spring 1; this movement also happens suddenly.

Fig. 7 shows a power-distance transmission gear as in Fig. 4.

However, there is a transmission member between the lever arms 2 'and 3' 6 for example as a roller bearing, with its outer ring on lever 3 @ and the axis on Lever 2 'rolls, the career of which is limited by the stops 19' and 20 '. at Movement in the direction of the action force A moves through the opening to the right Angular position of levers 2t and 3 'accelerated, the transmission link to the right. The locking groove 69 causes a greater increase in the spring force before the release, thereby the sudden effect is increased. When the movement is reversed, the action force is reversed not around, only a lever arm on lever 2 is present.

FIG. 8 shows the same force-displacement transmission gear as in FIG But with a tension spring on the frame 17 and lever arm 3 ', and one on the frame t7 attached link 8 for the transmission link 6, which controls as Schlit @ is designed, with the vertical slot 18 the transmission link at the beginning of the Gear movement holds, so that first the spring force increases, then it is in the subsequent branch of the slot is steered to the right and it sets the abrupt Move on.

Fig. 9 shows the same force-displacement transmission gear as in Fig. 8, only the path-dependent shape control takes place with a linked handlebar lever 8, which is connected to the pressure member 11 by means of joints 28 via a Winkelheb @@ 9/10 and 24 coupled @m Bahmen 17 and ortsfeat / mounted in Gélenk 25. The gear is shown in the initial or clamping position. and has a second lever arm 23 on lever 2t to keep it open.

Fig.I0 times this gear in the Ausepannstellung kept open To clamp the force, the act must first be reversed.

Fig. 11 shows the same force-displacement transmission gear as Fig. 9, However, the transmission member consists of a pair of blade bearing levers 7, which are articulated however, bearings 27 are fixedly mounted on levers 2 'and 32. The handlebar is mounted on one of the blade bearing levers 7 by means of a joint 66, It is a sudden toggle switch for clamping and unclamping reached the stops 18, between serve the angle lever arm 9 to swing with respect to the angle lever arm 10 can aim at a backlash in such a way that at a first part of the movement path the action force A increases according to the spring characteristic. until the left one Stop then only the transmission member 7 is moved to the right, and it the sudden release takes place.

The following figures show application examples of the described Gear elements for heel ski bindings with safety release when exceeded the permissible clamping force, which is permanently reliable for avoiding damage to the skier and act according to the invention. Any other combination of the above Gear elements also on different types of ski bindings, for example also on front bindings is possible.

Fig. 12 one of the many possible combinations and applications of the Invention in longitudinal section and FIG. 13 in cross section, one attached to the ski 44 Safety heel ski binding when clamped. It is used for getting in and out with your foot on the tread plate 56 on the pressure member 11. The frame 17 is at the same time the protective housing. The pressure member 11 is attached to the drive lever 2 'with a joint 22 with teeth 29 vertically adjustable fork 12 articulated.

14 shows this fork in plan view. The arm 9 on the angle lever 9/10 engages with its hinge pin 28 in the slot 18 of the handlebar 8 a at the other end carries a roller member 6.

This roller member is pressed by a tension spring suspended at 31 1 of the Abtriebshebelazn3 ', which, as shown in FIGS. 7 to 10, is opposite to the drive lever arm 2 'is directed. The tension spring is attached to the other side + fl of the suspension 30. For the clamping force adjustment is made by the removable, transparent cap and the adjusting screw 45. The display device is not shown. In the Clamped position open the two gear levers 2 'and 3' are wedge-shaped to the left.

The running surface on the lever 2 'is convex. On the track of the lever 3 ', which is just shown, is a stop to secure the clamping position 19 'and @ generation / a pressure point a locking groove is arranged. The hinge pin is located within half of the Sihlitz length 18. If a fall occurs, the lifts vertically upward heel force as an action force the fork 12 with the pressure member 11. Lever 2 'turns to the right4 Lever 3' to the left0 The wedge angle becomes smaller t the rolling element 6 remains behind until the bolt 28 on the angle arm 9 on Slot 18-t on the right. Until then, the forces of action increase. The handlebar 8 then pulls the rolling element 6 to the right for safety release of the binding up to the position shown in Fig. 15, which represents the open position.

The bolt 28 serves as a stop in the slot 18t of the handlebar 8 , while the pressure member t1 strikes the housing 17 at stop 20 'and the movement of the transmission system is limited.

The rolling element 6; is on the second arm 23, acts to the right of Joint 5 and thereby keeps the binding open. Can be opened by hand or with the Ski pole in the opening 52 of a release lever 33 * which is attached to the outer pin of the Hinge pin 5 is mounted on both sides of the housing 17 and on its second arm Fingers arranged at right angles in front of the rollers on both sides of the housing 6 Grip and pull into the release position. It can also, as can be seen in FIG. 29, a Push button 33 'with a wedge-shaped tip 65' mounted in the housing moves the roller 6 afterwards pull to the right to release the open position.

Fig.16 shows the feed spring device with that shown in Fig.1 Principle, with the lever mechanism 1, 3 and the feed spring 1, whereby changes in distance between front and heel binding, for example when driving over bumps, the feed force remains constant in order not to influence the safety release of both. The hinge pin 32 is on a bracket 32 and the spring 1 'is on a pressure regulating slide 31 mounted in a bracket 61 on the housing 17. The second cutting edge on the lever arm 2 is on a Boch 42 on a base plate that can be adjusted lengthways for different angles 38 stored. The housing 17 is either in a known manner with a slide guide 60, Fig13, guided in the base plate, or it is the frame 17 according to the invention according to FIGS. 18 and 17 with two vert @ -cal pendulum levers pair 34, 35 on joints 36, 37 on the housing and guided to be longitudinally movable at joints 40, 41 on brackets 39 of the base plate 38. The maximum Way is about 10 mm. The feed spring pushes the binding when not mounted to the stop 63 of the base plate 38. The binding must be adjusted so that when stepping into the binding at the stop 63 there is a play of about 5 mm, the Half of the maximum movement path results.

Figure 18 illustrates a ski binding similar to that shown in Figures 12-15 represents / with the only inventive simplification that the drive lever arm 2 'is arranged rigidly on the pressure member 11, and the link arm 10' on its joint 24 has a slot 59 in order to avoid being forced during movement.

In addition, the protective housing 64 is attached to the angle lever 9/10, or the housing takes over the function of the angle lever. The advantage is a low one Housing in the clamped state with relatively simple shielding against snow etc.

19 shows a simplified extension of a ski binding that rides on the ski boot heel in a clamping position and has a completely closed housing 17. The inner parts are basically the same. Only the feed spring adjusting screw 45 is provided on the suspension on the housing side. DieGelenkbo @@ n 22 @ a @ en for the pressure member 11, covered with plastic disks 55 Schlit @@ 47 of the housing 17 as a frame, which are arranged in a circular arc around the G @ steering 5 of the lever 2 ', and both engage on this pin On the side of the housing 17, tension members 58 are articulated, which at their other end, encompassing the boot heel 43, attack obliquely forward and downward on longitudinally adjustable joints 51 of a base plate 50 under the heel. The support on the ski boot takes place, for example, with the fork 12 in the Absat @hohlk @ hle as the upper support point and on a lower step; 1e 53 of the rear vertical Ab @@ part. The line to the line runs between these support points. When you fall @@ rd lift the bindings with the boots @ tz @ about 25 m @ g @. The hinge pin in slot 47 moves downwards, the lower contact point upwards, the pulling direction of the tension members comes to lie within the lower hinge point and the housing 17 tilts to the right and hits the plate 49, as shown in Fig. 20 and 21. Avoid approximate stops (not shown) on the base plate 50 and on the housing 17, each limiting in both directions a tipping over of the binding in inappropriate positions, the binding remains open behind the heel. By applying slight pressure from behind on the housing, it automatically jumps into its riding clamping position.

The binding can also be designed so that it is optionally available in its closed position is so close behind the heel that the heel is so close slides on the Gabe112 and then on the lower point 53, thereby tightening the binding, which then automatically jumps into its clamping position when you step in. Of this can be removed from the heel notch 52 by hand or with a ski pole and the ski boot can be lifted out of the binding.

Fig. Shows an extension of the example according to Fig. 21-19, thereby that the binding with a light, ice-free changeover device for the Touring (according to P 1955216.0) is provided, whereby the tension member 58 optionally up The binding is then raised according to the invention about 50 mm to the horizontal with an upper contact point 70 with Sinstelleinrichtung on the heel, and the The lower contact point under the fork remains in the AbsatshohlkehU. A safety release in touring is prevented because the direction of pull is always above the lower support point and the forces are almost perpendicular to the direction of movement of the pressure member in the slot 47 lie, so not enough.

The binding can also be designed to be used for downhill skiing is hinged in the hinge point 51 of the base plate and adjustable in an upper Contact point 70 on the heel and lower contact point with fork 12 in the ab @@ t @ hchlkehle and when triggered the housing 17 to the right lin the Absat.hohlkehl. as Pivot point tilts as it is already known.

For the sake of accuracy of setting and triggering, the Suspension on the standardized abutment is more practical.

Figw22 .: shows a very simple bond according to the inventive Basic elements with a change in translation, mainly for children, similar to Figs. 12-15 but only with a drive gear lever 2 '. The transmission element is a flip-flop element 7, between stops t9 'and 20t of the double-armed drive lever 2t, 23 to a swivel joint 68, which lies on the left inside the lever arm 2 ', to the right and left can tip. When tilted to the right, the binding remains in the release position at the stop 201 in which the tensile force line Z of the spring 1 on the right at the hinge point 5, which acts as a dead center, as shown in FIG. From this release position the binding can be stepped back into the clamping position with the step plate 56. The handlebar 8 with slot 18 'carries the second swivel joint 66 on the rocker arm 7, on the hinge pin of which the tension spring 1 is suspended. At the bottom of the frame 17, the is again designed as a housing, the further articulation point 30 of the spring 1 is like this selected that the pull line Z in the clamping position to the left of the joint 68 as dead point and is moved so far to the right of the joint 68 in the release position that it is still to the right of the @@ enkes 5 runs, al @ o also this second dead point according to the invention skips. It can also be used to further simplify the bonding process for children 17, 18 with the drive lever 2t rigidly arranged on the pressure member and a liftable one Housing are formed.

Fig. 26 shows a clamping device with only one gear lever 2 'and as a further feature a tipper: 7 * the raceway side a rolling element 6 carries, the other Ara 66 can also tilt back and forth, on him is the tension spring 1 articulated, the line of pull of which runs to the left of the fixed joint 5. This device ne @ especially short career only required minimal friction work, is very easy and suitable as a child binding.

Of course, according to the invention, this device, as well as that shown in FIG. 27, additionally with a link element 8 for the exact path-dependent Triggering are provided and with a control of the fork 12, or in yet In a simpler way, the gear lever is arranged rigidly on the fork 12. The Fig. 27 is almost the same as Fig. 26, but with it the arm 7 is in a joint 66 of the second gear lever 3 'mounted.

Fig. 29 shows a safety heel ski binding in which the path-dependent Control that depends on the action movement driven by the second arm 23 of the lever 2 'is derived. At the joint 24 of this arm 23 is a slotted bar 76 mounted, in the slot 18t of which the hinge pin 24 'of the angle lever arm engages 10 a, whose stationary bearing 25 is below the front arm of the lever 2 '. The other angle lever arm 9 has at its end the joint 28 in which the handlebars 8 is mounted, which carries the transmission link as a triple roller 6 at its end One of which on track 13 of lever 3 'and the other two on a pair of levers 2 ', roll track 14. The clamping position is drawn.

It can also be seen in this figure that the fork 12 is considerable must raise until the lever arm 23 with the slotted bar has lowered so far, so that the other end of the slot rests on the bolt 24 ', and then the transmission link 6 moved to the right for travel-dependent quick release. According to the invention happens this w @ wet shortly before due to the wedge-shaped: ~ - opening to the right Lever 2 'and 3' the transmission link also automatically switches itself to quick switching would have moved.

This device with a link in all examples described has two major advantages: on the one hand, it acts as a pressure point, on the other hand, it is at the triggering reaches the exact travel height and clamping height.

In this figure, the clamping fork 12 is controlled by a control plate 77, in the vertically extending control cam 78 a roller 22> rolls, controlled in such a way that that the smallest flexing movement occurs on the heel. There is also an im Housing 17 guided push button 33 'shown, which is wedge-shaped with its inclined surface 65' behind the roller 6 reaches when you trigger the trigger by hand or with a ski pole want to cause.

Fig. 28 graphically shows the approximate path that the transmission.

link 6 for the safety release and reconnection for all Ski bindings on the heel and also the toe of the boot describes the minimum have a gear lever 2 ', on which a transmission member 6, or 7 and 7 can be moved longitudinally is arranged. I-II is the way in which the spring work is applied> sfobed with heel bindings, the force increases and with toe bindings at the toe of the boot expediently remains constant 0 route II-III is during the High-speed switching, in which the stored spring work is discharged.

With the route III- is initially when a heel binding occurs, because it had passed a dead center to keep it open, only a very small amount to bring up to work, until then after passing the dead center, a considerable The amount of stored work becomes free for sudden clamping.

With a toe-cheek binding, even with a large icy Away to the side and further release path, the corresponding jaws jump back completely. According to the invention, it is designed in such a way that a dead center is not passed.

30 shows such a safety toe binding in plan view in clamping position, view of the inner parts, and the housing cut according to B-B, Fig.31 the same in cross section A-A, and Fig.32 the same as Fig.30> however in a right rebound up to the elastic lateral path E. Dash-dotted 79 the side position is indicated after the maximum release distance L.

The gear elements of Fig. 12 were used as a basis. To be smaller Any other combination could have been chosen to build. It was for two tile combinations are used on each side of the jaw, each arranged in a mirror-inverted manner. However, the angle levers 9/10 were combined into a rigid T-piece, so that the Joints 24 and 25 act for both systems. The housing 17 is on this T-piece attached so that it swings out.

11 The jaws 12 are articulated on the pressure member Jaw arms are longer than the side arms, so that they are safe when driving center yourself. The output levers 3 'find their stop on the inside Bolts 80 t on the other side of these bolts strike the arm sides 10 as a result the movement of the whole system is limited.

If z.ei gear lever 2 'and 3' as in Fig. 5 over a roller that If one of the levers is stationary, have contact, the transmission will change Hardly when moving, as long as the contact is near the line that lines the center of the joint connects. In the case of the binding according to FIGS. 30, 32, conversely, this teaching was used laughed. The stop 19 'on the lever 2' remains during the elastic movement to E the effective Lever arm at lever 2 'constant, but it will much larger in the case of lever 3 'because the contact is substantially above the joint connection line lies. This compensates for the increase in the spring force during path E, and the clamping force in area E remains constant. At the end of this path, see this drawn position in Figure 32, the arm 8 begins on the left in the slot 18 ' adjacent bolt28 to pull the transmission link to the left just before his Self-start is and suddenly the right jaw takes the release end position marked 79 from which it jumps back into the entry position when the ski boot shears off The width of the jaw width remains approximately constant in the area E and is up to Release end position L larger.

25 shows a force-displacement diagram of a heel ski binding.

The vertical clamping forces (VDlllnie) rise steeply, set in the case of relatively small force values, in order to pass through the very many small impacts soft buffer effect to protect the joints, tendons and muscles of the leg. In the end elastic path, the buffer effect is strong. Then a hump follows the as lighter Pressure point is noticeable. The curve then drops practically vertically, correspondingly the sudden release, 3 bindings with a step plate, the values are negative and throw out the ski boot like a catapult. The dashed line shows the power requirement to overcome the dead center, which is very small and always already above the abscissa Sufficiently large stored work for automatic, further clamping for Disposal. 0v The horizontal feed forces are practically constant not the set clamping forces in the ninter and front binding.

There have been shown many embodiments for ski bindings that present independent solutions for a uniform problem with corresponding elements} further combinations of the elements shown are possible, both in form than in the local arrangement according to the essence of the invention

Claims (1)

Claims Spring tensioning device with a spring element with a spring force increasing over the tensioning path, in particular for safety heel ski bindings or front jaw bindings, characterized by the use of a force-displacement transmission as a movement transmission means between the spring element (1) and pressure member (11) which is effective in the spring tensioning direction further increasing over all or part of the tensioning path; or and @ .glelchreebende or and has decreasing elasticity. Device according to claim 1, characterized in that the force-displacement transmission gear of at least one lever arm (3) pivotable about a fixed point (4) as an output member (3) insists on the counter to the force of the spring element hinged to it (1) the action force (A) acts on the pressure member (11), and that only affects the the spring element (1) effective lever length of the output member (3) as a function reduced by its angular position when moving in the direction of the action force (Fig. 1). 3. Device according to claims 1 and / or 2, characterized in that that the force-displacement transmission gear as a drive member with the output lever arm (3) connected lever arm (2), whose to the direction of the action force (Ä) effective lever length depends on its angular position when moving Enlarged in the direction of action (Fig. 2). 4. Device according to claims 1 to 3, characterized in that that the power ~ path transmission as a drive member with the output lever arm (3) verbundeben lever arm (2), both to the direction of the spring force and to the direction of the action force (A7 have an angular position. (Fig. 3) Device according to claim 1, characterized in that that the force-displacement transmission gear is made with two transverse to the direction of force extending, independent lever arms (2 ', 3'), which are directed against each other and have their joint bearings (5, 4) next to one another on both sides outside (Fig. 4, 7-21). 5. Apparatus according to claim 1 and 4, characterized in that the force-displacement transmission gear consisting of two transversely to the direction of force, independent lever arms (2 ', 3') be @ t @ ht, which their bearings (4, 5) with different Have a gap on one side (Fig. 5). 7. Device according to claims 1, 5 and 6, thereby ge @@ lnnseichnet, da @@ di @ Heb @ l @ rme (2 ', 3') find their contact on surfaces (13, 14), from one or both of which are, for example, convex or and concave wholly or partially curved (Fig. 4, 5), or and R @@ tnuten (69) have (Fig. 7). 8. Device according to claims 1, 5 to 7, characterized in that d @@@ mind @@@ ens one of the lever @ rme (2 ', 3') as contact points several cusps or Has rollers (15), the contact lines of which are each in a line that passes through the center of the bearing (5, 4) runs (Fig. 4-5). Device according to Claim 1 and / or one or more of the preceding and following claims, characterized in that the force-displacement transmission gear @ has at least one pivotable H @ b @ l (2 -, 3 ') as a drive and / or output link, on this lever arm a transmission link (6> 7) depending on aer Idt-, cb an actlons * raft (irumoaiJy; ial pressure member (1 (II) detachable Be. movement of the drive member is longitudinally movable, which for transmission which against the force of the Federel @ ment @ s we. kenden Ak @ ionkraft (A) serves (Fig. 6-22). 10. The device according to claim characterized in that only one Drive lever (2 ') is used, and the transmission link (6, 7) the spring (i) bears pendulously on it (Fig. 6) 11. Device according to claims 9 and 10. characterized by the fact that the drive lever (2t) is double-armed (23) is formed, and the transmission member (6, 7) movable in the longitudinal direction of both arms is (Fig. 6-24). 12. Device according to claims 9 to 11. characterized in that the transmission member (6, 7) as a tilting Wäiz "or sliding member is formed (Fig. 5, 6-24). 13. Device according to claims 1 to 12. characterized in that Ansc @ would be (19, 20), for example the levers (2, 3 2 ', 3'), the movement of the whole system and stops (19 @, 20 ') For example, at the end of the tracks (13, t4) of the levers (2t, 3 ') the movement of the transmission member (6, 7) in both directions (Fig. 6-24). 14. Device according to claims 9 to 13, characterized in that that the transmission member (6,7) and the forces acting on it in the release or latching point Such an angular position to the drive lever (2 ') or in addition to the Ab @ ri @ bshebel (3 ') reach $, @ o there a force component that arises backwards or forwards the transmission link automatically moves backwards or forwards (Fig. 6, 17). 15. Device according to claims 9 to 14, characterized in that the transmission member (6, 7) by means of steering form-fit members (8) for example with a handlebar or curves, Schlit @ en. Wedges, cams are coupled in a longitudinally movable manner, and the dtese gear is connected to the pressure member (11) transmitting the action movement (Fig.11-24). 16. Device according to claims 1 to 15, characterized in that one or more bearings or joints are designed as knife-edge bearings (t6) (Fig. 1, 11) 17. 56), which is retained in the clamping position by the adjustable clamping force of a spring element (i) with an increasing characteristic curve, using the device according to claims 1 to, characterized in that the pressure member (11) to initiate the action force (A) connected to the lever arm <2 ') serving as drive @@ lied is, and a # with the pressure member (11) articulated to a pivot point (25) fixed on the frame (17) pivotable angle lever (9, 10) as a control lever for the longitudinal @ movable transmission member (6, 7) on the power Distance translation @ gear is used, and by means of stops (18) or slots (18 ') etc. in the course of the handlebar (8) and Winkelh @ beis (9, 10) is provided with a backlash due to movement play in the direction of movement g * 1t -24, 8). 18. Device according to claim 1, characterized in that the g @ k @ nnz @ ichnet Lever arm (2 ') is connected to the pressure member (11) by a joint (22), and the Frame (17) is designed as a protective housing (Fig. 12, 13, 15, 19-24). 19. Device according to claims 1 to 17, characterized in that that the lever arm (2 ') is rigidly connected to the pressure member (11), and the control arm (10) has a slot (59), and that the angle lever (9,10) with the protective housing (64) forms a unit (Fig.17, 18). 20. Device according to the jnd Claims, or or characterized in that only one lever (2t) is arranged for the force-displacement transmission @ transmission, and the transmission element as a rocker arm (7) between two stops (19 ', 20') on the lever (2 ', 23) is designed to swing, which is rotatably mounted on the lever arm (2 ') in front of its bearing (5) on a further pivot bearing (68) and that the handlebar (8) is rotatably mounted on the other end in a joint (66) (Figs. 22,23). 21. Device according to claims 16 to 19. characterized in that a hand or ski pole to be operated Member, wedge-shaped in front of the transmission member (6, 7) reaching through the housing (17, 64), such as a push button, or lever (33) with notch (52) rotatably mounted on the outer journal of the hinge pin (5) fixed to the frame, with wedge-shaped attacking angular fingers (65) (Fig. 12, 13). 22. Device according to claims 17 to 21. characterized in that the frame (17) in the ski direction up to a stop (63) is guided longitudinally movable (Fig. 13, 17). 23 * ». Device according to claim characterized in that the frame (17) is known to be longitudinally movable in a slide guide (60) the base plate (38) on the ski (44) is (Fig. 13). 24. Device according to claim 22, characterized4 that the frame (17) on both sides in two vertical pendulum levers (35) in joints (36, 37, 40, 41) opposite the base plate (38) on the ski (44) is guided longitudinally schwi @ bar (Fig.17,18) 25. Device according to claims 22 to 24, in particular also 2, characterized in that a feed spring (1 ') extends forward in the ski direction on a thrust adjustment screw (31) of a bracket (61) on the frame (17) and to the rear on a lever arm (3) supported on a bracket (62) of the frame (17) on a Joint (32) is rotatably mounted, and that the second lever arm (2) fixed on the first is supported on a bracket (42) that @ Gr @@@@ atte (38) on the ski (Fig. 15, 16) 26. Spring tensioning device as a safety heel ski binding according to several of the preceding claims, in particular 17 to 20, characterized in that it has a completely closed housing (17) as a frame to which the pressure fork (12) is directly fastened in a vertically adjustable manner, and that it rides in the clamped state on the ski boot heel and is supported at at least one point or a pair of points at the same height, and pin of the joint (22) for the pressure member (11) and the lever arm (2 ') through radial and the local Fixed joint (5) arranged slots (47) protrude on both sides of the housing (t7), on which a pair of tension members (58> is articulated, which at the other ends, encompassing the boot heel, on a longitudinally adjustable base plate (50) under the boot heel Joints (51) engages (Fig. 19-21. 24). 27. Device according to claim 20, characterized in that the clamping fork (12) in the heel fillet as the upper support point and on the rear one vertical surface of the paragraph (43) engages as a second lower support point (53) (Fig. 15-21). 28. Device according to claim 26. characterized in that the clamping fork (12) in the heel fillet as a lower support point and as a second upper support point (70) of the housing (17) grips the heel (73) (Fig. 19, 24). 29. Device according to claims 26 to 28, known thereby characterized in that / has a / switching device (P 1955216.0) for vertical Hochachaltung the tension members (58) to the horizontal for the touring run, with the Support points according to claim 27 and for downhill skiing according to claim 26 (Fig. 24) 30. Device according to claims 26 to 29. characterized in that the pulling direction of the tension members (58) between the respective upper and lower support points (Fig. 19, 24). 31, device according to several of the preceding claims, characterized characterized in that only one drive lever (2 ') is incorporated, and between them its stops (19, 20 ') a rocker arm (0 pendulum, and a transmission link (6) is arranged rollable, the other end of the rocker arm between two stationary Stops (20 ", 19 ') can be moved, and a suspension for the central position spring (1) coaxial with the rocker arm and in this position perpendicular to the Running track (14) upright, with the spring suspension at the end of the rocker arm (7) in one Pivot Pin (66) (Fig 269. 32./ Device according to several of the preceding claims, characterized characterized in that two transmission jacks @ (2 ', 3') are incorporated, and between their stops (19 ', 2a) a rocker arm (7) pendulum-capable, and via a transmission link (6) is arranged rollable, the other end of the rocker arm in a joint (66) of the other gear lever (3 ') pivotally mounted, and in its central position with the spring (1) coaxially perpendicular to the track (14) of the drive lever (2 ') standing (Fig. 27) 33, device according to claims 1 to 30, characterized in that that the drive lever (2 ') is provided with a longer double arm t) whose End is coupled to an angle lever (9/10), and that its arm (10) @ extends approximately horizontally on the other side of the track (14) of the lever (2 '), with a stationary bearing (g5) arranged in the angle tip towards the pressure member, and that the other angle arm extends vertically to the track, at its end has a joint (28) on which the handlebar (8) for the transmission member (6, 7) is articulated, and that in the course of the control members a movement play e.g. through slot (18 ') is provided (rig. 29) o 34 device according to claim 32, gekennseichnet characterized in that a control plate (77) with a vertical slot (78) the lower part of the pressure member with its bole (22 @) guides vertically (Fig. 29). 35 Spring tensioning device as a safety front linkage with vertically adjustable jaws that reach on both sides of the ski boot tip in front of and over the boot sole, are rotatable about a vertical axis and are held in the clamping position by the adjustable tensioning force of a spring element with an ascending line , using the device according to claims 1 to and up to 3/1 ì534) characterized in that a separate gear and control device is arranged for each jaw (Fig.30-32). 36 Device according to claim, characterized in that the Control device consisting of a T-shaped lever (9, 9, 10) as a carrier of the housing (64) consists of one arm (10) in the inner joints (24) of the two pressure members (11) is articulated, and its two other arms (9, 9) on the two handlebars (8) are articulated, and that the two drive levers (2 ') are one-armed, with one on the clamping side Stop (19 ') for the support members are formed, and at their portable End of the two outer joints (22) of the pressure members (11) are articulated (Fig.30-32). 37. Device according to claims 35 and 36, characterized thereby, that two further outer gear levers (3r) are arranged, at their movable Ends (21) a common tension spring (1) suspended transversely to the ski direction the whole The gear system on the Änschllagen (80) in the clamped state holds the pretension at the same time on the other flanks by striking the control arm (10) serve as a tripping path limiter, and that the runway (13) on the output lever (3 ')) for constant clamping forces in the elastic area (E) in direction the swing-out movement outside the connecting line through the fixed joints (5, 4) of the gear lever (2 ', 3') are (Fig 30-32). 38. Device according to claims 3 to characterized that the joints (24) on the pressure limbs (11) have short slots (81) transverse to the ski direction for frontal shock absorption (Fig. 30). 39. Spring tensioning device according to all claims 1 to 38 thereby marked that with the specified elements further combinations by swapping be designed.