EP0991837A1 - Scharnier zum schwenkbaren lagern eines bauteils - Google Patents
Scharnier zum schwenkbaren lagern eines bauteilsInfo
- Publication number
- EP0991837A1 EP0991837A1 EP98939504A EP98939504A EP0991837A1 EP 0991837 A1 EP0991837 A1 EP 0991837A1 EP 98939504 A EP98939504 A EP 98939504A EP 98939504 A EP98939504 A EP 98939504A EP 0991837 A1 EP0991837 A1 EP 0991837A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- hinge
- force
- swivel
- pivoting
- brake
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 230000001105 regulatory effect Effects 0.000 abstract 5
- 230000000694 effects Effects 0.000 description 23
- 238000010586 diagram Methods 0.000 description 11
- 230000005484 gravity Effects 0.000 description 8
- 230000002401 inhibitory effect Effects 0.000 description 3
- 210000003660 reticulum Anatomy 0.000 description 3
- 229910000831 Steel Inorganic materials 0.000 description 2
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 238000013016 damping Methods 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 230000000630 rising effect Effects 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- 238000000418 atomic force spectrum Methods 0.000 description 1
- 230000006378 damage Effects 0.000 description 1
- 230000001934 delay Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 230000005764 inhibitory process Effects 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 238000001746 injection moulding Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000001960 triggered effect Effects 0.000 description 1
Classifications
-
- E—FIXED CONSTRUCTIONS
- E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
- E05D—HINGES OR SUSPENSION DEVICES FOR DOORS, WINDOWS OR WINGS
- E05D11/00—Additional features or accessories of hinges
- E05D11/08—Friction devices between relatively-movable hinge parts
-
- E—FIXED CONSTRUCTIONS
- E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
- E05D—HINGES OR SUSPENSION DEVICES FOR DOORS, WINDOWS OR WINGS
- E05D11/00—Additional features or accessories of hinges
- E05D11/08—Friction devices between relatively-movable hinge parts
- E05D11/082—Friction devices between relatively-movable hinge parts with substantially radial friction, e.g. cylindrical friction surfaces
- E05D11/084—Friction devices between relatively-movable hinge parts with substantially radial friction, e.g. cylindrical friction surfaces the friction depending on direction of rotation or opening angle of the hinge
-
- E—FIXED CONSTRUCTIONS
- E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
- E05D—HINGES OR SUSPENSION DEVICES FOR DOORS, WINDOWS OR WINGS
- E05D5/00—Construction of single parts, e.g. the parts for attachment
- E05D5/10—Pins, sockets or sleeves; Removable pins
-
- E—FIXED CONSTRUCTIONS
- E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
- E05Y—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES E05D AND E05F, RELATING TO CONSTRUCTION ELEMENTS, ELECTRIC CONTROL, POWER SUPPLY, POWER SIGNAL OR TRANSMISSION, USER INTERFACES, MOUNTING OR COUPLING, DETAILS, ACCESSORIES, AUXILIARY OPERATIONS NOT OTHERWISE PROVIDED FOR, APPLICATION THEREOF
- E05Y2900/00—Application of doors, windows, wings or fittings thereof
- E05Y2900/50—Application of doors, windows, wings or fittings thereof for vehicles
- E05Y2900/53—Type of wing
- E05Y2900/536—Hoods
-
- E—FIXED CONSTRUCTIONS
- E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
- E05Y—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES E05D AND E05F, RELATING TO CONSTRUCTION ELEMENTS, ELECTRIC CONTROL, POWER SUPPLY, POWER SIGNAL OR TRANSMISSION, USER INTERFACES, MOUNTING OR COUPLING, DETAILS, ACCESSORIES, AUXILIARY OPERATIONS NOT OTHERWISE PROVIDED FOR, APPLICATION THEREOF
- E05Y2900/00—Application of doors, windows, wings or fittings thereof
- E05Y2900/50—Application of doors, windows, wings or fittings thereof for vehicles
- E05Y2900/53—Type of wing
- E05Y2900/548—Trunk lids
Definitions
- the invention relates to a hinge for the pivotable mounting of a component, on which an actuating force striving to pivot it acts and with a pivoting brake which prevents this pivoting in the form of cooperating cylinder wedge surfaces on the hinge pin and on at least one of the hinge shields.
- a hinge in the sense of the application means an articulated connection with at least one axis, which has a shaft in the form of a hinge pin and a hub in the form of a pivotable hinge plate.
- Other names for such an articulated connection are, for example, (door) hinge or piano hinge.
- the hinge can also have two parallel axes, between which a hinge bridge is arranged.
- the hinge is used to pivot a component. It follows that the bearing element of the hinge is arranged so that it can pivot. However, this does not exclude that this overlapping element in turn bond in a further articulated Ver ⁇ is pivotally mounted, for example.
- the mentioned hinge bridge about said second axis.
- a swivel brake is understood to be an inhibiting device which provides a certain resistance to the swiveling of the swivel-mounted component under the action of an actuating force, in other words a counterforce which is generally less than the actuating force.
- the heating device acts as a swivel stop and prevents the component from swiveling under the effect of the positioning force .
- the actuating force acting on the pivotably mounted component can be of any type. It can be formed, for example, on components pivotable about a horizontal axis, such as flaps or folding seats, by gravity; it can be applied by an energy accumulator like a spring or it can be exercised spontaneously, for example by a gust of wind on a door.
- Cylinder wedge surfaces are understood to mean cams which gradually, in wedge-shaped fashion, rise on wedge-shaped surfaces of the hinge pin and of the hinge shield that face each other and are coaxial with the axis of the hinge, and then drop steeply again onto the cylinder surface, the cams on one of the components on one Arranged inner surface and on the other component on an outer surface and the rising directions of the cams are opposite to each other and wherein there is a joining gap between the cylinder wedge surfaces in a joining position, which is less than the height of the cams above their respective reference cylinder surface.
- DE 44 06 824 C describes a hinge with a swivel stop, which swivels a part mounted in a hinge pin under the action of actuating forces, by means of which swiveling should not be effected ! .prevents. This is intended to ensure that, for example, a door has self-locking in all pivoting positions of its opening angle range. In this case, the braking force of the swivel brake always exceeds the actuating force through which swiveling should not take place.
- Another example are car doors on which, depending on their position and depending on the inclination of the vehicle, gravity or a gust of wind exerts a very different moment, which should be compensated at least to the extent that a door is held in the open position and / or is not unintentionally braked accelerates from this position.
- Another example is folding seats in public transport or in permanently installed seating, which are usually lifted up by spring force. It is often desirable that they be held in the folded position so that they do not fold up when they get up for a short time.
- the automatic folding up should be triggered by briefly lifting it. Furthermore, such seats should not be strongly accelerated under the action of the spring force so as not to strike their upper system. You should therefore fold up braked at least in the end region of its pivoting movement.
- the object of the invention was accordingly to specify a dimensioning rule for the braking action and embodiments for a hinge with a swivel brake with cylindrical wedge surfaces, by means of which these requirements can be met in the best possible way.
- the course of the braking torque of the swivel brake is adapted to the course of the actuating forces acting on the component via the swivel angle in the sense that the actuating force is opposed, at least over a substantial part of the Schwenic angle, by a braking force which is less than the actuating force.
- the component can thus be pivoted in a substantial part of its pivot angle by the actuating force, but only braked, inhibited, slowed down. It is therefore not em more or less arbitrary chosen ⁇ Licher course of the braking torque of the swing brake between assumed start and end values, but a course, which is adapted to the course of the actuating forces acting on the pivotable component and is determined by parameters such as the mass of the pivotable component, the pivot arm of the center of gravity of the component, the pivot angle, the inclination of the pivot axis in space and others. Since these parameters can be very different from case to case, determining the course of the braking torque must be preceded by determining the course of the actuating forces and the desired course of the pivoting movement.
- the braking force of the pivoting brake can exceed the actuating force, so that the component is not pivoted in these areas by the actuating force, but is blocked.
- These areas are generally the start or end areas of the swivel angle, or in general terms, positions in which the component is to be held automatically.
- the swivel brake does not oppose the braking force in a range of the swivel angle according to claim 3. This applies in particular to a region in front of the start or end point of a swivel angle which is to be reached and held safely by means of the actuating force.
- the swivel brake according to claims 5 to 9 can be provided with a plurality of wedge surfaces which take effect in the different regions of the swivel angle and which, depending on the desired mode of operation, can be equipped with the same or opposite direction of inclination.
- the wedge surface pairings take effect one after the other and the swivel brake exerts braking force over a large swivel range.
- the wedge pairings come into effect depending on the swivel direction, whereby the swivel brake exerts increasing braking force in both swivel directions.
- the wedge surfaces can be provided with the same or different slopes, so that Depending on the direction of the swivel, the swiveling brake can be given a braking effect that is different or increases progressively or degressively with the swivel angle.
- the swivel brake annihilates at least 20% of the actuating force applied by the actuating force, i.e. the product of actuating force and swivel path by braking work, i.e. by the product of braking force and swivel path, i.e. converts into thermal energy in order to achieve sufficient braking of the movement of the component which is braked in each case.
- Figures 1 and 2 the principle of the wedge profiles in cross section through the swivel brake in two different positions.
- 11 and 12 show an embodiment of the spline profiles for the object of FIG. 9 and a force / swivel angle diagram of this embodiment
- 13 and 14 an execution orm of the spline profiles for particularly large swivel angles and a force / swivel angle diagram of this embodiment;
- 15 and 16 the representation of a foldable bed, for example in a motor vehicle, and a force / swivel angle diagram of this bed;
- Fig. 19 is a plan view of a partially broken
- Motor vehicle exterior mirror with swivel brakes 20 and 21 two partially sectional views of hinges with swivel brakes.
- An essential structural element of the present invention are the wedge profiles, the design and mode of operation of which will first be described.
- a hinge 1 has a hinge shield 2 which acts as a hub and which on its inner surface has a number of two, in the embodiment shown two offset by 180 'from one another, from an imaginary cylindrical surface 3 gradually, in a wedge shape in a clockwise direction to the inside Cams 5 rising to a line 4 and then again falling steeply onto the cylinder surface.
- the hinge pin 6 which acts as a shaft, has two cams 9 offset from one another by 180 ′′, gradually increasing from an imaginary cylinder surface 7 in a wedge shape counterclockwise to a line 8 and then falling steeply again onto the cylinder surface Back surfaces of the cams 5 and 9 on a joining gap 10, by means of which hinge plate 2 and hinge pin 5 can be inserted into each other, each back surface of a cam 5 of the hub 2 and a cam 9 of the shaft 6 form a coordinated pair of wedge surfaces a plurality of such wedge surface pairs which act in unison are arranged - they are referred to below as wedge surface pair 11.
- a wedge surface pair 11 therefore consists of at least one wedge surface pair, but it can also have a plurality thereof, as shown in FIG. but also three and technical sensible up to six pairs of wedge surfaces.
- the two wedge surface pairings 11 of FIGS. 1 and 2 have a working range of approximately 120 ". After passing through an angle of rotation of approximately 10 'to 15 *, they close the joining gap 10 and then come into frictional engagement with one another. This frictional engagement and thus the braking effect increases further Rotate to a maximum with increasing surface pressure Since the contact surfaces of the backs of cams 5 and 9 become shorter, the braking force then drops again despite increasing surface pressure, so that an angular range of approximately 120 * can be used for the braking effect.
- the parts of such hinges are usually made of steel.
- at least the friction surfaces are advantageously hardened.
- a pure line contact of the wedge surface pairings 11 which is subject to wear can be avoided in that the increase in the wedge surfaces follows a logarithmic spiral.
- paired splines 11 can also be provided with an initial idling range, after which they only come into frictional engagement and develop a braking effect.
- Fig. I the wedge surface pairings 11 are shown in their joining position, in which they can be pushed into one another.
- 2 shows the position which they assume in the working position: the hinge boizen 6 has rotated clockwise by approximately 90 'when the component carried by the hinge 1 is pivoted.
- the back surfaces of the cams 5 and 9 have approached each other, then touched and are then sliding against one another with increasing surface pressure.
- they have increasingly counteracted the rotational movement of the hinge pin 6 by frictional force and also performed deformation work and have thereby increasingly inhibited the pivoting movement or reduced the speed of this pivoting movement and dampened it.
- Fig. 3 shows a simple application of a hinge 1 with such a swivel brake 12 on the flap 13 of a glove box 14 of a car.
- the flap 13 is supported in a single long, or at two spaced hinges 1 and folded down to the dotted line position down ⁇ bar.
- the actuating force represents, by a pivot angle of about 90 'down and lies there on a stop, not shown.
- the basic course of this actuating force over the swivel angle is shown in FIG. 4 in the characteristic curve 15.
- the hinge 1 or at least one of several is equipped with the pivoting brake 12 according to the invention.
- This swivel brake is designed by the design of its wedge profiles so that the course of its braking force over the swivel angle corresponds in principle to the characteristic curve 16 of FIG. 4.
- This characteristic curve 16 of the braking force can exceed the characteristic curve 15 of the actuating force in the initial region of the swivel path from 0 ' , so that the flap in this region is not only secured by its locking, but also prevents the flap from rattling by the additional holding by means of the swivel brake.
- the flap 13 falls down under the effect of the actuating force, i.e. gravity.
- the actuating force does not act on the flap in its full height, but only with the difference between the positioning force 15 and the braking force 16, so that the downward movement of the flap is braked and slowed down.
- FIG. 5 shows an application of the swivel brake 12 according to the invention to the bonnet 17 or to the trunk lid 18 of a car.
- the weight of these flaps, which are mounted on hinges not shown here, is generally at least approximately balanced by a gas or steel spring. It is assumed that the actuating forces shown on the flaps 17, 18 in FIG Swivel range of about 45 '.
- a swivel brake 12 built into the hinges 1 of the flaps counteracts a braking force which approximately compensates for the actuating force over the swivel range with the curve indicated in the characteristic curve 20. It is also provided here that the braking force exceeds the actuating force in the open position of the flaps in order to keep them in this open position.
- Fig. 7 shows a flap 21 on a storage space 22, as it is often installed under the floor of buses.
- This closure flap 21 is also mounted in hinges 1, which are equipped with swivel brakes 12. Gravity acts on the flap 21, which can be pivoted by approximately 180 ', with the actuating force shown approximately in the characteristic curve 23 in FIG. 8.
- two pivot brake 12 may, in at least one of the hinges with opposing and 8 with the dash-dotted characteristic curve 24 and the dash-double-dotted characteristic curve 25.
- the effects of these braking forces add up to a braking force in accordance with the dashed-line brake characteristic line 26, which represents the actuating force in FIG Beginning region 27 and in the end region 28 of the pivoting angle of the flap 21 exceeds and opposes it in its central region to a sufficient extent.
- Wedge profiles with opposing courses of the braking forces are also used in the folding seat 29 of FIG. 9.
- the folding seat 29 is pressed against the backrest 32 with approximately linear torque by the actuating force indicated in FIG. 10 with the characteristic curve 30 of a spring (not shown) built into the hinges 1 of the folding axis 31.
- the course of the braking force is according to the dashed curve 33 selected so that it exceeds the actuating force in the start and end areas 27, 28 of the pivoting range extending over about 95 * .
- This course of the braking force is achieved by superimposing two braking force profiles 33 'and 33 ", which can be represented by means of two swivel brakes with opposite direction of incline and with a steeper increase in braking force 33" of the swivel brake effective in the upper end region 28.
- the wedge surface pairings with opposite direction of inclination can be arranged, for example, offset from one another in the direction of the axis of the hinge. However, if the swivel angle is only about 90 ", it is also possible to arrange the two wedge surface pairings offset circumferentially. This is shown in more detail in FIG. 11.
- these wedge surface pairings 11 'and 11 "lead, when rotated clockwise or counterclockwise, to the increases 35 and 36 of the braking torque shown in FIG. 12. It is understood that these increases, for example, by different Slopes and / or lengths of the wedge surface pairs can be designed differently.
- FIG. 13 shows an embodiment with which an increase in the braking force of wedge surface pairings can be achieved over a swivel path of 180 * or more.
- two wedge surface pairings 11 " and 11 ' offset from one another in the axial direction are provided, each with two wedge surface pairs, of which the wedge surface pair 11" lying behind in the direction of the view is shown with a larger diameter for the sake of visibility, but it can have the same diameter as that Wedge surface pairing 11 "located at the front.
- the wedge surface pairing 11" has idle areas" 37 of approximately 90 'each, in which there is still no increase in the cam 5 of the hub 2.
- the shaft 6 is turned counterclockwise, only the back surfaces of the pair of wedge surfaces 11 "come into frictional engagement, which leads to the increase in braking force 38 shown in dashed lines in FIG. 14.
- this pair of wedge surfaces 11" after passing through an angle of rotation of approximately 90 ' Has reached its maximum braking force and this begins to drop, the back surfaces of the wedge surface pair 11 * come into frictional engagement, which when viewed in their own right generate the braking force 38 'shown in broken lines in FIG.
- the braking forces 38 and 38 'of the two wedge surface pairings 11 "and 11” add up to the total line 39 drawn in solid lines in the diagram in FIG. 14.
- a swivel brake using the example of a handle 44 as it is often arranged on the roof edge in the interior of cars, is shown in all details for the sake of example.
- These handles are pivoted so that they can be moved from a rest position in which they lie against the headlining, can be folded down if necessary. Due to the force of a built-in spring, they are swung up into the rest position when they are released and held in this rest position.
- the handle 44 is supported at both ends by means of two hinges 1 and 1 '.
- These hinges comprise a shaft connected in a rotationally fixed manner to the handle 44 in the form of bearing pins 45 and 46 and a hub in the form of two bearing eyes 47 and 48, respectively, each seated on bearing plates 49, by means of which the handle can be fastened to the body of a motor vehicle.
- the bearing pins 45, 46 have a polygon 50 at one end, with which they engage in corresponding recesses in the handle and are thus connected to the latter in a rotationally fixed manner.
- the bearing pins 45, 46 are inserted during the assembly of the handle through an opening in the latter, which is then closed by means of a pressed-in stopper 51.
- a torsion spring 52 around the bearing pin 45, which engages with one end in one of the bearing eyes 47 and with the other end in the bearing pin 45.
- the torsion spring 52 is biased so that it pushes the handle 44 in the position shown upwards.
- a tube 53 is fastened in its bearing eyes 48, in which the bearing pin 46 can be rotated. This tube 53 can be injected into the bearing eyes 48 during the manufacture of the bearing plate 49, which is preferably carried out by injection molding.
- the tube 53 Since the angular position of the tube 53 in the bearing eyes 48 is important for the functional effect of the wedge surface pairings, the tube 53 has a groove 54, with which it can be inserted into the injection mold in a certain angular position and is secured in it and injected.
- the tube 53 and the bearing pin 46 of the hinge 1 ' have, in a region 55, coordinated wedge surface pairings 11. Their effect is shown in the force / angle of rotation diagram of FIG. 18 via the pivoting angle of the handle 44 of 110 * .
- the actuating force of the spring 52 corresponds to the course of the characteristic curve 56, that of the braking force of the swivel brake of the characteristic curve 57. In the assumed swiveling range of the handle, the actuating force of the spring 52 decreases from the value A to the value B.
- the wedge surface pairings 11 are advantageously dimensioned and positioned such that they initially allow the handle 44 to perform an uninhibited pivoting movement over a pivoting angle of, for example, 35 '.
- the frictional or braking force of the pair of wedge surfaces 11 should be dimensioned such that it does not exceed the force of the spring 52 so that spring force is always present which reliably pushes the handle back into the rest position.
- the braking force of the wedge surface pairings should therefore not increase above the value C below the value B. In the rest position, the braking force of the wedge surface pairings also has the effect of holding the handle in this rest position. The braking force C then exceeds the spring force B Harmless if, for example, the handle is released in the swung-out position and swings back into the rest position with momentum.
- Fig. 19 shows an application in which two swing brakes are inserted in each of two cooperating hinges. It is an exterior mirror 59 of a motor vehicle, which should be able to evade when subjected to correspondingly high forces in order to avoid injuries.
- the housing 61 containing the mirror 60 is mounted in a hinge 62, which in turn can be pivoted via a coupling member 63 into a further hinge 65 which is fixedly arranged on the body 64 of the vehicle.
- the housing 61 is pulled against bearing surfaces 67 by means of a spring 66 articulated on it and on the body 64.
- the housing 61 If the housing 61 is acted upon, for example, by an actuating force acting from the front which exceeds the moment applied by the spring 66, the housing evades this force by pivoting around the hinge 62 to the rear. Correspondingly, the housing 61 and the coupling member 63 deflect forward by an actuating force acting on the housing from behind by pivoting about the hinge 65. After the actuating force ceases to exist, the housing 61 snaps back into its starting position under the action of the spring 66.
- both hinges 62 and 65 are provided with swivel brakes 12, by means of which this snap back slows down, delays and dampens becomes.
- the braking force of the brake should not exceed the torque applied by the spring 66 in any area of the swivel angle.
- the correct angular position of the wedge surface pairings with respect to the swivel range also plays a decisive role for the correct selection of the course of the braking force of a swivel brake according to the invention.
- the devices described below with reference to FIGS. 20 and 21 are provided.
- the hinges 1 have a first hinge plate 68 and a second hinge plate 69, which are connected to one another by a hinge pin 70.
- the hinges 1 are fastened to a fixed component and, on the other hand, a pivotable component by means of screws which reach through holes 71.
- the hinge pins 70 rotate in a first axial area 72 in the hinge plates 68 and 69 and are fastened in a second axial area 73 in the respective other hinge plate 69 and 68, respectively.
- the first axial region 72 of the hinge pin 70 and the bearing bore of the hinge shields 68, 69 assigned to it have the wedge surface pairings 11 already described.
- a nut 74 which can be screwed onto the end region of the hinge pin 70 designed as a thread, or a clamping ring 75, in cooperation with a collar 76, secure the hinge pins in the hinge plates.
- the profiles of the second. Axial region 73 of the hinge pin 70 and the bearing bore of the hinge plate 69 is conical.
- the conical surfaces can be pressed into one another by means of a fastening screw 77, so that the hinge pin 70 and the hinge plate 69 are connected to one another in a rotationally fixed manner.
- the one in the drawing for the sake of clarity WO 98/59139 _ ? _ PCT / EP98 / 03611
- the cone angle which is markedly exaggerated, can be small, so that a high holding force against twisting can be achieved under high surface pressure.
- the hinge pin 70 When pivoting the movable component, the hinge pin 70 is rotated in the hinge plate 68.
- the wedge surfaces of the wedge surface pairings 11 slide onto one another and increasingly increase the frictional engagement between the parts. As a result, the pivoting movement is increasingly inhibited.
- the extent of this inhibition may be changed in the hinge plate 69 in a different starting position 'by rotation of the hinge pin 70 and be adjusted when worn.
- the conical seat in the axial region 73 is loosened by loosening the screw 77 and the hinge pin 70 is rotated so far with a tool that engages a key surface 78 on the circumference of the collar 76 that the intended inhibitory effect is present.
- the conical seat in the new mutual position is pressed into one another again by tightening the fastening screw 77.
- the hinge pin 70 is secured in the hinge plate 68 by means of a nut 79 which can be screwed onto a thread at the upper end of the hinge pin 70.
- profiling in the form of a toothing 80 is used on the second axial area 73 of the hinge pin and in the bore of the hinge pin. This interlocking toothing 80 can be designed as a serration.
- the hinge plate 68 is pulled off the hinge pin, ie the component mounted by means of the hinge 1 is lifted out. Now the hinge pin 70 can be rotated with a tool engaging the key surface 78. When this has been done, the hinge plate 68 is put back on the hinge pin 70, the Sliding teeth 80 in another position. Finally, the hinge plate 68 is fastened again on the hinge pin 70 by means of the nut 79.
- the hinge pin 70 and the bore of the hinge plate 68 are provided at least on one side with conical projections 81, by means of which the parts are tightened against one another when the nut 79 is tightened and are prevented from rattling.
- the nut 79 can have a conical shoulder 81.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Pivots And Pivotal Connections (AREA)
- Braking Arrangements (AREA)
- Chairs For Special Purposes, Such As Reclining Chairs (AREA)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19726536A DE19726536A1 (de) | 1997-06-23 | 1997-06-23 | Scharnier zum schwenkbaren Lagern eines Bauteils |
DE19726536 | 1997-06-23 | ||
PCT/EP1998/003611 WO1998059139A1 (de) | 1997-06-23 | 1998-06-16 | Scharnier zum schwenkbaren lagern eines bauteils |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0991837A1 true EP0991837A1 (de) | 2000-04-12 |
EP0991837B1 EP0991837B1 (de) | 2001-09-12 |
Family
ID=7833332
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP98939504A Expired - Lifetime EP0991837B1 (de) | 1997-06-23 | 1998-06-16 | Scharnier zum schwenkbaren lagern eines bauteils |
Country Status (7)
Country | Link |
---|---|
US (1) | US6349449B1 (de) |
EP (1) | EP0991837B1 (de) |
JP (1) | JP2000513062A (de) |
KR (1) | KR20010020492A (de) |
DE (2) | DE19726536A1 (de) |
ES (1) | ES2163881T3 (de) |
WO (1) | WO1998059139A1 (de) |
Families Citing this family (33)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19835572A1 (de) * | 1998-08-06 | 2000-02-10 | Scharwaechter Ed Gmbh | Anschlußeinrichtung zur Verbindung eines Türfeststellers mit einem Kraftwagentürscharnier |
JP3097958B1 (ja) * | 1999-08-23 | 2000-10-10 | 日本ベルボン精機工業株式会社 | 伸縮装置および三脚 |
DE20006953U1 (de) * | 2000-04-15 | 2000-07-06 | Utescheny-Endos GmbH, 75059 Zaisenhausen | Puffereinrichtung für drehbare Bauteile, wie beispielsweise Dachhaltegriffe oder Sonnenblenden eines Fahrzeuges |
DE20102954U1 (de) * | 2001-02-20 | 2002-07-04 | Findlay Industries Deutschland GmbH, 82538 Geretsried | Aufbewahrungsfach |
DE10222898A1 (de) * | 2001-06-11 | 2002-12-19 | Klingelhoefer Jost | Mit einer integrierten Brems- und Halteeinrichtng ausgestattetes Türscharnier |
FR2835581B1 (fr) * | 2002-02-04 | 2005-07-01 | Itw Fastex France | Dispositif ralentisseur de rotation et utilisation de celui-ci |
FR2858004A1 (fr) * | 2003-07-25 | 2005-01-28 | Bernard Laville | Charniere d'un nouveau type |
DE102004034247B3 (de) * | 2004-07-14 | 2006-01-19 | Ise Innomotive Systems Europe Gmbh | Türscharnier für Kraftfahrzeuge |
US7163248B2 (en) * | 2004-11-08 | 2007-01-16 | Lear Corporation | Automotive console with adjustable armrest |
US7240941B2 (en) * | 2004-11-08 | 2007-07-10 | Lear Corporation | Vehicle storage assembly with adjustable door |
KR100668886B1 (ko) * | 2005-11-02 | 2007-01-12 | 현대자동차주식회사 | 차량용 글로브 박스의 힌지구조 |
US7667959B2 (en) * | 2005-12-20 | 2010-02-23 | Nokia Corp. | Foldable electronic device having double-axis hinge and locking spring |
US7891055B1 (en) * | 2006-01-27 | 2011-02-22 | Gary Combs | Replacement hinge pin |
TWI292860B (en) * | 2006-02-16 | 2008-01-21 | Asustek Comp Inc | A variable-torque rotation shaft with low weariness |
DE102006008525A1 (de) * | 2006-02-22 | 2007-08-30 | Hans-Peter Goller | Vorrichtung zum Befestigen einer Fahrzeugtür |
WO2007095896A1 (de) * | 2006-02-22 | 2007-08-30 | Hans-Peter Goller | Anlenkvorrichtung |
DE102008026128A1 (de) * | 2008-05-30 | 2009-12-03 | BSH Bosch und Siemens Hausgeräte GmbH | Scharnier für Dunstabzugshaube und Dunstabzugshaube |
DE102010062318A1 (de) * | 2010-12-02 | 2012-06-06 | Sedus Stoll Ag | Gebremstes Lager sowie Möbelstück, insbesondere Klapptisch |
US9295334B2 (en) | 2011-09-06 | 2016-03-29 | Series International, Llc | Hinge mechanism with non-cylindrical pin |
US20130078027A1 (en) * | 2011-09-23 | 2013-03-28 | First Dome Corporation | Rotary shaft structure |
DE102012001276A1 (de) * | 2012-01-25 | 2013-07-25 | Gm Global Technology Operations, Llc | Verstellvorrichtung, Kraftfahrzeugsitz, Kraftfahrzeug und Verfahren hierzu |
US8857016B2 (en) | 2012-03-26 | 2014-10-14 | Toyota Motor Engineering & Manufacturing North America Inc. | Hinge assembly |
DE102012020265B3 (de) * | 2012-10-12 | 2013-11-28 | Audi Ag | Türaußengriffanordnung für eine Fahrzeugtüre eines Fahrzeugs |
JP6051127B2 (ja) * | 2013-09-02 | 2016-12-27 | 日立アプライアンス株式会社 | 冷蔵庫 |
US20150286255A1 (en) * | 2014-04-07 | 2015-10-08 | Apple Inc. | Variable friction clutch for a portable computer |
DE102014215432B4 (de) * | 2014-08-05 | 2019-06-13 | Adient Luxembourg Holding S.À R.L. | Gesicherte Armlehne |
CN106050036B (zh) * | 2016-06-30 | 2017-12-01 | 青岛海尔股份有限公司 | 铰链组件及冰箱 |
US10344511B2 (en) * | 2016-10-21 | 2019-07-09 | Hewlett-Packard Development Company, L.P. | Hinge damper |
US10081228B2 (en) * | 2016-11-08 | 2018-09-25 | Mahmoud Razzaghi | Car visor |
DE102018206316B4 (de) * | 2018-04-24 | 2021-06-24 | Audi Ag | Abgedichtetes Staufach für ein Kraftfahrzeug und Kraftfahrzeug mit einem solchen Staufach |
US11026515B2 (en) | 2018-11-15 | 2021-06-08 | Series International, Llc | Beam seating system |
US11523681B2 (en) * | 2019-12-09 | 2022-12-13 | Inno-Sports Co., Ltd. | Frame and table having structure for reducing vibration |
US11808069B2 (en) * | 2021-04-23 | 2023-11-07 | Te Connectivity Solutions Gmbh | Print in place assembly hinge |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2458707A (en) * | 1946-02-23 | 1949-01-11 | Jacobs Co F L | Visor |
GB2177057A (en) * | 1985-07-04 | 1987-01-14 | John Connor | Vehicle sun visor |
JPH057629Y2 (de) * | 1986-08-29 | 1993-02-25 | ||
DE4406824C2 (de) * | 1994-03-02 | 1996-02-08 | Hans Kuehl | Scharnier mit Schwenkhemmung |
DE19600063A1 (de) * | 1995-11-21 | 1997-05-28 | Scharwaechter Gmbh Co Kg | Kraftwagentürscharnier mit Brems- und Haltefunktion |
CZ331796A3 (en) * | 1996-01-03 | 1997-07-16 | Scharwaechter Gmbh Co Kg | Door hinge of motor vehicle with braking and holding-down functions |
DE19625556A1 (de) * | 1996-06-26 | 1998-01-02 | Hans Dipl Ing Kuehl | Scharnier mit Schwenkbremse |
DE19625557A1 (de) * | 1996-06-26 | 1998-01-08 | Hans Dipl Ing Kuehl | Scharnier für Türen mit Schwenkhemmung |
-
1997
- 1997-06-23 DE DE19726536A patent/DE19726536A1/de not_active Withdrawn
-
1998
- 1998-06-16 US US09/446,798 patent/US6349449B1/en not_active Expired - Fee Related
- 1998-06-16 DE DE59801461T patent/DE59801461D1/de not_active Expired - Fee Related
- 1998-06-16 ES ES98939504T patent/ES2163881T3/es not_active Expired - Lifetime
- 1998-06-16 WO PCT/EP1998/003611 patent/WO1998059139A1/de not_active Application Discontinuation
- 1998-06-16 JP JP11503720A patent/JP2000513062A/ja active Pending
- 1998-06-16 EP EP98939504A patent/EP0991837B1/de not_active Expired - Lifetime
- 1998-06-16 KR KR1019997012170A patent/KR20010020492A/ko not_active Application Discontinuation
Non-Patent Citations (1)
Title |
---|
See references of WO9859139A1 * |
Also Published As
Publication number | Publication date |
---|---|
JP2000513062A (ja) | 2000-10-03 |
DE59801461D1 (de) | 2001-10-18 |
ES2163881T3 (es) | 2002-02-01 |
KR20010020492A (ko) | 2001-03-15 |
US6349449B1 (en) | 2002-02-26 |
DE19726536A1 (de) | 1998-12-24 |
EP0991837B1 (de) | 2001-09-12 |
WO1998059139A1 (de) | 1998-12-30 |
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