EP1214958B1 - Vibration damping device for skis etc. - Google Patents

Abstract

The shock absorber unit (7) has two shock absorber elements consisting of a cylinder and piston rod and relatively movable in a lengthwise direction against damping resistance and positioned on the ski's upper side. One of the damper elements is fixed on the ski (1) by a thrust-piece (2); the other element is detachably connected to another thrust piece (4). A coupling part (8) cooperates with a counter-coupling part adjustable between two positions.

Description

The invention relates to a device for damping of flexing movements of a ski or the like., With a damper unit, which has two in a longitudinal direction against damping resistance relative to each other displaceable damper elements (cylinder, piston rod) and the like on the top of the ski. is arranged, wherein the one damper element at a first fixed to the ski or the like. attached or attachable abutment held and the other damper element coupled with another abutment and disengageable, which in the direction of displacement away from the first abutment on the ski or the like. attached or attachable, wherein the other damper element is firmly connected in the direction of displacement with a coupling part which cooperates with an adjustable between two end positions mating coupling part of the other abutment, and wherein the coupling part in the one end position of the mating coupling part in the displacement direction relative to the other abutment positively held and in the other end position of the counter-coupling part is movable in the direction of displacement.

In one known from US 5,806,875 A such device, a pedal is arranged on the footprint of the ski boot on the ski in the ball area, coupled with sufficient pressure load the coupling part with the mating coupling part or with appropriate pressure relief of the pedal is decoupled from the mating coupling part. By means of adjustable preload suspension, the minimum force can be adjusted, which must be exerted on the pedal for coupling coupling part and mating coupling part. As a result, therefore, a dependent on the load of the ski effect or inefficiency of the damper elements is achieved.

From EP 0 492 658 A1 it is known to provide a double-acting hydraulic piston-cylinder unit for damping of flexing movements of a ski, wherein an adjustable throttle, which is arranged hydraulically between two chambers separated from the piston in the cylinder, hydraulic medium of a Chamber overflowed into the other chamber. By appropriate adjustment of the throttle, a different damping resistance can be adjusted.

The object of the invention is now, in a device of the type specified in addition to a setting with significant attenuation of flexing movements of the ski or the like. to allow a setting in which the constructive predetermined flex characteristic of the ski or the like. practically completely unchanged.

This object is achieved according to the invention in the device specified above in that the end positions are formed as locking positions.

The invention is based on the general idea, the damper assembly on and off to arrange by the one Damper element mechanically decoupled from the associated abutment or can be coupled to the abutment. This can on the one hand between the two abutments turn on a damping effective frictional connection by a damper element is brought into its coupled to the abutment state. On the other hand, a virtually kraftschlussfreier state is possible by the damper assembly is functionally separated mechanically from the aforementioned abutment.

According to a preferred embodiment of the invention, the other element of the damper assembly is fixedly connected in the longitudinal direction with a coupling part which cooperates with an adjustable between two end positions mating coupling part of the other abutment, wherein the coupling part in the one end position of the mating coupling part in the longitudinal direction relative to the other abutment positively held and is movable in the other end position of the counter-coupling part in the longitudinal direction.

In this way, a simple construction is ensured, wherein the damper unit in principle largely arbitrary, but according to a preferred embodiment may be designed so that especially so-called CounterflexBewegungen of the ski, in which the ends of the ski or sliding board swing relative to the binding area downwards, effectively attenuated, while flexing movements in which the ski ends move relative to the binding area up, are not or only slightly attenuated.

In a particularly advantageous embodiment, the counter-coupling part is designed as a slide, which positively holds a claw of the coupling part in one end position and releases in its other end position.

In this case, it is provided in particular to form the counter-coupling part as a rotary slide, which engages behind the claw in its one end position with part of its peripheral wall and holds in the longitudinal direction and releases the claw in its other end position with a recess of its peripheral wall in the longitudinal direction.

The rotary mounting of the rotary valve can be done by means of a slotted guide, which is arranged outside the axis of rotation, so that a correspondingly large space is available for the claw within the peripheral wall of the rotary valve.

Furthermore, it is preferably provided to design the damper so that it exclusively or entirely predominantly only so-called counterflex movements of the ski, i. Movement of the ski ends relative to the ski area downwards, dampens. Regardless of whether the damper is uncoupled from one of its abutments or not, protection is claimed for this general idea.

Moreover, with regard to preferred features of the invention to the claims and the following explanation of the drawing, reference is made to a particularly preferred embodiment is described in detail.

Fig. 1

einen Längsschnitt durch die erfindungsgemäße Vorrichtung,

Fig. 2

einen Querschnitt entsprechend der Schnittebene II-II in Fig. 1,

Fig. 3

eine perspektivische Ansicht des Kupplungsteiles von schräg oben,

Fig. 4

eine perspektivische Ansicht des Gegenkupplungsteiles von schräg unten und

Fig. 5

eine perspektivische Schnittdarstellung eines erfindungsgemäßen Dämpfers.

It shows

Fig. 1

a longitudinal section through the device according to the invention,

Fig. 2

a cross section corresponding to the sectional plane II-II in Fig. 1,

Fig. 3

a perspective view of the coupling part obliquely from above,

Fig. 4

a perspective view of the mating coupling part obliquely from below and

Fig. 5

a perspective sectional view of a damper according to the invention.

According to FIG. 1, a first, substantially plate-shaped abutment part 2 is arranged resting on the ski upper side on a ski 1 shown in partial detail. The Fixing of the abutment part 2 on the ski 1 is effected by means of a likewise substantially plate-shaped holding part 3, which surrounds the right in Fig. 1 end of the abutment part 2 and engages positively with a toothing in a counter-toothing on the abutment part 2. The holding part 3 is attached to the ski 1 with screws, not shown.

In the ski longitudinal direction away from the holding part 3, a further abutment part 4 is arranged at the other end of the abutment part 2, which is attached to the ski 1 with screws 5. In the abutment part 4, which as well as the abutment part 2 and the holding part 3 is made of plastic, a sliding guide 6 made of metal is embedded, cf. Fig. 2. This sliding guide 6 surrounds with cross-sectionally C-shaped wheels, which face each other with their Konkavseiten, correspondingly shaped longitudinal edges of the abutment part 2, which shifts during flexing movements of the ski in the longitudinal direction relative to the sliding guide 6 and the abutment part 4. This is due to the fact that the abutment part 4 is arranged vertically away from the neutral bending zone of the ski 1 and held in the longitudinal direction of the ski at a greater distance from the sliding guide 6 by means of the holding part 3.

Within a longitudinal direction extending in the corresponding recess of the abutment part 2 of the cylinder designed as a piston-cylinder unit hydraulic damper 7 is arranged under clamping or latching. The piston rod of the damper 7 is connected to a coupling part 8 - see. Also Fig. 3 - connected, which extends in a corresponding longitudinal channel on the underside of the abutment part 2 and under a fixed integrally formed on the abutment part 4 guide plate 9 - see. Fig. 1 - passes.

The coupling part 8 cooperates with a counter-coupling part 10, which is formed in a manner shown below as a rotary valve and about a vertical pivot axis S -. Fig. 1 - rotatably mounted on the abutment part 4.

The elements for pivotal mounting of the mating coupling part 10 are arranged at a distance from the pivot axis S and substantially comprise an integrally formed on the abutment part 4 and visible in Fig. 1 arcuate web 11, in a well-visible in Fig. 4 groove 12 on the underside of the mating coupling part 10 engages with game in the bow direction, ie the groove 12 forms a guide slot for the web 11, such that the counter-coupling part 10 can drehverstellen between two end positions. In addition, the counter-coupling part 10 engages under the guide plate 9 of the abutment part 4 with a radially outwardly projecting edge 13th

In the region of the pivot axis S is on the underside of the mating coupling part 10 a partially radially outwardly open recess 14 is formed, into which a damper remote claw-shaped end 15 of the coupling part 8 can be inserted with a corresponding rotational position of the mating coupling part 10. By appropriate rotational adjustment of the mating coupling part 10 can be integrally formed on a locking piece 16 are inserted into a locking recess 17 adjacent to the claw-shaped end 15 of the coupling part 8. In this position, which is shown in Fig. 1, the coupling part 8 and the mating coupling part 10 are coupled together, ie the claw-shaped end 15 of the coupling part 8 is held within the recess 14 of the mating coupling part 10 in the longitudinal direction, with the result that the piston rod the damper 7 is displaced relative to the cylinder of the damper 7 during flexing movements of the ski 1, and the damper 7 accordingly generates a damping resistance counteracting the flexing movements.

In contrast, when the mating coupling member 10 is rotated to its other end position, the locking piece 16 of the mating coupling part 10 completely out of the locking recess 17 of the coupling part 8 out, so that the claw-shaped end 15 of the coupling part 8 is released and the coupling part 8 and the mating coupling part 10 is decoupled from each other are. If flex movements of the ski 1 now occur, the coupling part 8 is displaced into the cylinder of the damper 7 during the first flexing movement with insertion of the piston rod. However, then the coupling member 8 is held in the shifted position by the resistance of the damper 7 more or less, with the result that the damper 7 performs no strokes in the flex movements and accordingly remains ineffective.

This in turn subsequently a locking of the claw-shaped end 15 of the coupling part 8 in the counter-coupling part 10 is possible, even if the claw-shaped end 15 assumes a position outside the recess 14 of the mating coupling part 10, a ramp 18 is formed on the locking piece 16, which cooperates with a counter ramp 19 on the claw-shaped end 15 of the coupling part 8 and the claw-shaped End 15 with a corresponding rotation of the mating coupling part 10 in the recess 14 einschiebt.

Instead or in addition, it may also be provided that the piston rod of the damper 7 is weakly biased in Ausschieberichtung such that it seeks herauszukriechen from an inserted into the cylinder of the damper 7 position. This can be ensured that the claw-shaped end 15 again takes a position in the recess 14 of the mating coupling part 10 after a certain delay time and accordingly a rotational adjustment of the mating coupling part 10 is made possible by inserting the locking piece 16 into the locking recess 17.

The Drehendlagen the mating coupling part 10 are formed as locking positions, in which not shown, formed on the abutment part 4 locking elements with locking recesses 20 on the mating coupling part 10 cooperate.

The upper side of the left in Fig. 1 end portion of the abutment part 4 and the top of the holding part 3 are used to hold the toe or heel side shoe holder assemblies 21 of a ski binding. This shoe holder assemblies 21 are indicated by dashed lines in Fig. 1. The inventive Device for damping flex movements of a ski or the like. So also takes on the function of a stand or spacer plate for the ski binding.

5 shows a particularly preferred embodiment of the damper 7. This is designed as a piston-cylinder unit with a cylinder 22 and a piston 23 displaceable therein with a piston rod 24 arranged on one side.

The cylinder 22 has a multi-stepped cylinder bore 25 which continues at the right in Fig. 5 the end of the cylinder 22 in a cylinder bore 25 equiaxed filling bore 26, which is arranged in a integrally formed on the cylinder 22 bottom 27 and through an opening in the filling 26th Pressed ball 28 is closed.

Within the adjacent to the bottom portion 27 of the cylinder bore 25, which has a slightly smaller diameter than that provided for the piston 23 central portion of the cylinder bore 25 is a compressible foam body 29 with closed porous, gas-filled cell structure and the filling bore 26 coaxially continuing and the foam body 29 fully penetrating axial bore held by press fit.

The foam body 29 may for example consist of cellular rubber or silicone foam with a density of about 0.5 g / cm ³ .

Between the outer circumference of the piston 23 and the inner circumference of the piston 23 receiving central portion of the cylinder bore 25 at least one throttle gap 30 is formed, through which communicate the cylinder bore parts in front of and behind the piston 23 with each other. In addition, an axial stepped bore 31 is arranged in the piston 23, whose relative to the diameter larger portion piston rod side is arranged, in such a way that the opening cross-section is partially covered by an annular step 32 on the piston rod 24. Within the section of the stepped bore 31 with a larger diameter, a spherical closing body 33 is arranged in the example shown, with which the conical annular step 34 of the stepped bore 31 cooperates in the manner of a valve seat, that is, the closing body 33, whose diameter is smaller than the diameter of the closing body 33 receiving part of the stepped bore 31, and the annular step 34 form a check valve which opens at a pressure gradient in the direction of the piston rod 24 and closes at opposite pressure gradient.

At the left in Fig. 5 piston rod side end of the cylinder 22, a guide bush 35, for example, Delrin 100, arranged for the piston rod. This bush 35 is held axially between an inner cone on the cylinder 22 and a disc-shaped bottom 36, which is held by a flanged or pressed to the bottom 36 end edge of the cylinder 22. The guide bushing 35 is externally sealed by an O-ring relative to the cylinder 22 and internally by a U-ring relative to the piston rod 24.

Piston 23 and piston rod 24 are connected in the example shown by the fact that the piston 23 is pushed with a central axial bore on a threaded extension 37 of the piston rod 24 and stretched by means of a threaded extension 37 nut 38 against the annular step 32 of the piston rod 24.

In the manufacture of the damper 7 is completely prefabricated, but without pressing the ball 28 into the filling hole 26. Before the subsequent filling, the piston rod is pulled out in Fig. 5 to the left, so that the piston 23 reaches its end position on the packing 35. Now, the cylinder 22 is filled by the filling bore 26 with hydraulic medium. This filling may optionally be done with overpressure. Then, the filling bore 26 is closed by means of the ball 28.

Now, when the piston rod is moved to the right in Fig. 5, the foam body 29 is increasingly elastically compressed, since the penetrating into the cylinder 22 piston rod 24 displaces hydraulic fluid. The foam body 29 thus forms a "volume buffer", by which the hydraulic medium in the cylinder 22 is kept free of bubbles and optionally also kept under constant pressure, regardless of the temperature of the hydraulic medium. By the compressed foam body 29, a hydraulic restoring force is exerted on the piston rod 24, which is the piston rod 24 with the piston 23 in Fig. 5 to the left in or to push almost to the left end position.

When pressure stroke of the piston 23 and piston rod 24, in Fig. 5, this is the direction of movement to the right, the non-return valve formed by the closing body 33 and the annular step 34 of the stepped bore 31, its open position, so that the pressure stroke counteracts only a small hydrodynamic resistance. When Zughub, however, closes the closing body 33 and the annular step 32 formed check valve, so that from the piston 23 in the cylinder 22 divided cylinder chambers communicate only via the throttle gap or the throttle gaps 30 between the outer periphery of the piston 23 and inner circumference of the cylinder 22 with each other and When Zughub a correspondingly large hydrodynamic resistance occurs.

As a result, therefore, the pressure stroke is weak and the Zughub pronounced or strongly attenuated.

When the damper 7 is arranged in accordance with FIG. 1 and the coupling part 8 and the counter-coupling part 10 are coupled together, the piston 23 and piston rod 24 move weakly damped pressure strokes relative to the cylinder 22 during flexing of the ski as the ski ends move upwards relative to the binding area out. On the other hand, in counterflex movements of the ski, when the ski ends move downwards relative to the binding area of the ski, heavily damped pull strokes occur.

If the damper 7 is filled under pressure with hydraulic medium, the foam body 29 is more or less compressed in all positions of the piston 23 and the piston rod 24, i. the hydraulic medium is constantly under pressure. Accordingly, the seal package 35 is constantly acted upon by pressure. This is advantageous because so that the sealing elements are constantly pressed hydraulically on adjacent surfaces of the piston rod 24 and the cylinder 22 and remain dense.

Claims (17)

1. Device for damping flex movements of a ski (1) or the like, with a damper unit (7) which has two damper elements (cylinder, piston rod), which are displaceable relative to one another in a longitudinal direction counter to damping resistance, and is arranged on the upper side of the ski or the like, the one damper element being retained on a first abutment (2) which is or can be attached firmly to the ski or the like and the other damper element being coupled connectably and disconnectably to a further abutment (4) which is or can be attached to the ski or the like at a distance from the first abutment in the displacement direction, the other damper element being connected firmly in the displacement direction to a coupling part (8) which interacts with a counter-coupling part (10), which is adjustable between two end positions, of the further abutment (4), and the coupling part (8) being in the one end position of the counter-coupling part (10) retained positively in the displacement direction relative to the other abutment (4) and in the other end position of the counter-coupling part (10) movable in the displacement direction, characterized in that the end positions are designed as catching positions.
2. Device according to Claim 1, characterized in that the counter-coupling part (10) is designed as a slider which in the one end position positively retains a claw (15) of the coupling part (8) and in the other end position releases it.
3. Device according to Claim 2, characterized in that the counter-coupling part (10) is designed as a rotary slider which in its one end position engages behind the claw (15) with a part (16) on its peripheral wall and retains it in the longitudinal direction and in its other end position releases the claw (15) in the longitudinal direction with a recess in its peripheral wall.
4. Device according to one of Claims 1 to 3, characterized in that the two abutments (2, 4) are retained in the longitudinal direction on the ski (1) or the like with a large spacing in comparison with the longitudinal extent of the damper unit (7).
5. Device according to one of Claims 1 to 4, characterized in that the parts (2, 4) forming the abutments are guided on one another in the longitudinal direction in a slider-like manner.
6. Device according to one of Claims 1 to 5, characterized in that the coupling part (8) is guided on at least one abutment part (2) in a slider-like manner.
7. Device according to one of Claims 1 to 6, characterized in that one abutment part (2) is held firmly in an adjustable manner in the longitudinal direction on a holding part (3) which is arranged on or can be attached to the ski (1) or the like.
8. Device according to Claim 7, characterized in that the holding part (3) and the one abutment part (2) together form a base for receiving a ski binding with heel-end and toe-end boot-holder units (21).
9. Device according to one of Claims 1 to 8, characterized in that the damper unit (7) is weakly prestressed and seeks to creep into its one state in which the coupling part (8) and the counter-coupling part (10) can be coupled to one another.
10. Device according to one of Claims 1 to 9, characterized in that the damper (7) designed as a piston/cylinder unit is held with its cylinder positively or non-positively in a recess of the one abutment part (2).
11. Device according to one of Claims 1 to 10, characterized in that a hydraulic damper (7), preferably with gel-like or paste-like hydraulic medium, is provided.
12. Device according to Claim 11, characterized in that the damper (7) damps exclusively or to a greater extent counterflex or backflex movements of the ski (1) or sliding board.
13. Device according to Claim 12, characterized in that the damper (7) designed as a piston/cylinder unit has a piston rod (24) arranged on one side on the piston (23) and also a compressible foamed-material body (29) arranged in the cylinder, which is compressed during the pressure stroke of the piston rod and expands elastically during the tension stroke of the piston rod.
14. Device according to Claim 12 or 13, characterized in that a choke gap (30) or a choke opening is designed or arranged between the outer circumference of the piston (23) and the inner circumference of the cylinder (22).
15. Device according to one of Claims 12 to 14, characterized in that at least one non-return valve (32, 33) opening in the direction of the piston rod (24) is arranged in the piston (23).
16. Device according to Claim 15, characterized in that the non-return valve (32, 33) is designed with a stepped bore (31) passing axially through the piston (23) and with a valve body (33) which is arranged in the wider part of the stepped bore with regard to the diameter and is held captive in a cage-like manner between the annular step (34) of the stepped bore acting as a valve seat and an edge (32) on the piston rod (24) which is arranged at the outlet opening of the non-return valve and slightly overlaps the outlet opening.
17. Device according to one of Claims 12 to 16, characterized in that, on that side of the cylinder (22) facing away from the piston rod (24), a filling opening (26) is arranged in the cylinder bottom (27) coaxially with an axial duct in the foamed-material body (29) adjacent to this bottom.

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