Classifications

• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60N—SEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
  • B60N2/00—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles
  • B60N2/02—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable
  • B60N2/22—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60N—SEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
  • B60N2/00—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles
  • B60N2/02—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable
  • B60N2/22—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable
  • B60N2/225—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable by cycloidal or planetary mechanisms
  • B60N2/2252—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable by cycloidal or planetary mechanisms in which the central axis of the gearing lies inside the periphery of an orbital gear, e.g. one gear without sun gear
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60N—SEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
  • B60N2/00—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles
  • B60N2/02—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable
  • B60N2/20—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being tiltable, e.g. to permit easy access
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60N—SEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
  • B60N2/00—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles
  • B60N2/02—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable
  • B60N2/22—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable
  • B60N2/225—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable by cycloidal or planetary mechanisms
  • B60N2/2254—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable by cycloidal or planetary mechanisms provided with braking systems

Definitions

• the invention relates to a fitting for a vehicle seat with the features of the preamble of claim 1.
• the invention is based on the object to improve a fitting of the type mentioned. This object is achieved by a fitting with the features of claim 1.
• Advantageous embodiments are the subject of the dependent claims.
• a functional integration of the brake in the fitting is possible, in which components of the transmission fitting serve in a dual function and the control of the brake.
• the control can directly, ie by direct contact of the driver and / or eccentric to preferably provided for driving the wrap spring wrap arms and then applying the latter, or indirectly carried out, ie using intermediate components, such as discs or separate cam.
• the functional integration is preferably accompanied by a structural integration, for example, by an arrangement of the wrap spring arms in the center of the fitting or the inclusion of a designed for the braking action as a counterpart, separately trained wrap spring by a fitting or the integral formation of the wrap spring with a fitting, For example, as a collar, paragraph or wider bearing bore of the fitting.
• the inside or the outside can be the relevant area for generating the braking effect.
• Such a fitting which is provided on at least one vehicle seat side, is both reliable and low in terms of efficiency.
• drainage is to be understood that the two fittings cause by regular or irregular mechanical stimuli (vibrations or vibrations) rotation of the eccentric, which leads under the torque of the weight of the backrest to a rolling movement of the fittings with backward pivoting of the backrest.
• a brake is preferably provided on both sides of the vehicle seat.
• the wrap spring brake provides a high output-side locking torque, but rotates at a drive-side initiation of torque with a low in relation to the locking torque freewheeling torque.
• the driver is preferably designed so that it opens on the wrap spring and this dissolves the drive, for example by the driver has at least one driver cam, which opens when applied to a wrap spring arm with subsequent application of the latter acts on the wrap spring brake.
• the driver may have a receptacle for a wrap spring arm, possibly with play.
• the eccentric Since the eccentric due to its storage - on the one hand on the first fitting part and on the other fitting part - in the power flow and in addition to the teeth between the fittings receiving the output side introduced forces and torques including their fluctuations by mechanical excitations, the eccentric is preferably formed in that it acts closing on the wrap spring brake, so that it can generate its blocking moment and thus its braking effect, for example by the eccentric having a control cam, which acts on the wrap spring brake upon contact with a wrap spring arm with subsequent application of the latter.
• the eccentric can have a holder for a wrap spring arm, which may be subject to play.
• the mounting of the eccentric to a fitting should include all variants of the relative bearing of the eccentric and fitting part, ie the eccentric can be stored for example in (radially inward) a collar or paragraph of the fitting part or on (radially outside) the same
• the wrap spring brake generates its locking torque preferably by contact with a wrap spring bush, which is rotationally fixed to the second fitting part, preferably by a positive connection between suitable projections, for example radially projecting arms, the wrap spring bushing and a production-related internal toothing of the second fitting part.
• the wrap spring brake is preferably arranged within the wrap spring bush, so that it bears against the inner wall and their wrap spring arms protrude radially inwardly.
• the eccentric is at least partially, for example a single wedge segment of the same, both the first fitting part and the second fitting part is mounted with low friction, in particular by means of a sliding bearing and / or roller bearing and / or a surface treatment and / or surface treatment. Since the friction between the sliding bearing (or rolling bearing) and the relative to this sliding member is less than the direct friction between the wedge segments and the fitting parts, the losses are reduced when driving the fitting, ie during the adjustment movement, thus increasing the efficiency of the fitting elevated. With the same output power is thus a lower drive power required. The freedom from play and the strength are retained.
• the lower friction of the plain bearing compared to ordinary steel is due to a special surface treatment and / or surface treatment.
• a surface treatment for example mechanical
• surface treatment for example chemically
• application of a coating can also be carried out directly on the fitting parts.
• the lower friction of the rolling bearing compared to the sliding friction of ordinary steel is due to the rolling friction of the rolling elements.
• the plain bearings or rolling bearings etc. can also be provided in mixed combination.
• the eccentric may have two wedge segments, which are stretched apart, and thereby make the fitting at rest without play.
• the wedge segments preferably move in the axially same plane, which is parallel to the planes of movement of the fitting parts.
• the wedge segments according to the invention can also be formed in each case on a disk, in which case the two (eccentric) disks are arranged axially offset from one another.
• the eccentric can - in dispensing with the game release - also be in one piece, for example, be designed as a sychelelement or disc-shaped fixed eccentric, which simplifies the manufacture and assembly.
• the driver can be one-piece or multi-part.
• the higher loaded wedge segment is the wedge segment mounted on both sides by sliding bearings.
• the other wedge segment or-also preferably preferred - both wedge segments be supported on both sides by means of plain bearings.
• the fitting according to the invention can be operated both manually and operated by motor and be used in vehicle seats, preferably for an angle adjustable seat component, in particular seat part or back, for adjusting an angle within the seat component, for example, the inclination of the seat cushion relative to a base, the inclination of Thigh support relative to the seat frame or the inclination of wings, which serve to adjust the seat height to the seat frame or a base, or to adjust an angle relative to another seat component, for example, the inclination of the backrest relative to the seat part.
• an angle adjustable seat component in particular seat part or back
• an angle within the seat component for example, the inclination of the seat cushion relative to a base, the inclination of Thigh support relative to the seat frame or the inclination of wings, which serve to adjust the seat height to the seat frame or a base, or to adjust an angle relative to another seat component, for example, the inclination of the backrest relative to the seat part.
• Fig. 13 is a partial perspective view of the modification with two wrap spring brakes.
• a vehicle seat 1 for a motor vehicle has a seat part 3 and a backrest 4 that is adjustable in its inclination relative to the seat part 3.
• a manually for adjusting the inclination handwheel 5 on one side of the vehicle seat 1 rotates a drive shaft, not shown, which see horizontally in the transition region between seat part 3 and backrest 4 and on both sides of the vehicle seat 1 rotatably engages in each case a fitting 10 ,
• the backrest 4 is connected by means of the two fittings 10 with the seat part 3.
• the fitting 10 is designed as a geared fitting, in which a first fitting part 11 and a second fitting part 12 are connected to one another via a gear designed as an eccentric planetary gear mechanism for adjusting and locking.
• the two fitting parts 11 and 12 have a substantially flat shape and are made of steel.
• the first fitting part 11 is firmly connected to the structure supporting the hand wheel 5 and the drive shaft (in the present case the structure of the back 4), which is why in the exemplary embodiment the first component 11 is leaning against and therefore shown in the drawing above.
• the second fitting part 12 in the embodiment seat part fixed, ie connected to the structure of the seat part 3, and shown in the drawing below.
• the positions of the fitting parts 11 and 12 can be exchanged as required, ie the direction of the force flow through the fitting 10 can be opposite to the aforementioned arrangement of the fitting parts 11 and 12 opposite.
• the terms “support” and “support” used below are therefore not intended to be limiting of the direction of the force flow.
• a toothed wheel 16 with external teeth and, on the first fitting part 11, a toothed ring 17 with internal toothing, which mesh with one another, are formed on the second fitting part 12.
• the diameter of the top circle of the external toothing of the toothed wheel 16 is smaller by at least one tooth height than the diameter of the root circle of the internal toothing of the ring gear 17.
• the corresponding difference in the number of teeth of the toothed wheel 16 and ring gear 17 enables a rolling movement of the ring gear 17 on the toothed wheel 16.
• the first fitting part 11 has on the side facing the gear 16 concentric with the internal toothing of the ring gear 17 a molded collar 19.
• a driver 21 is mounted by means of a hub 22 with game.
• the driver 21 made of plastic, by the arrangement of which directional indications used are defined, is provided centrally with an axially extending bore 23 matching a spline profile of the drive shaft. Further, the driver 21 has an integrally formed driver segment 25, which is arranged in an arc around a part of the collar 19 around.
• On the collar 19 are at least indirectly with its curved inner side two wedge segments 27 a and 27 b supported, which store with their curved outer sides in the second fitting part 12 rotatably pressed first slide bearing 28.
• the friction between the outside of the metallic wedge segments 27a and 27b and the inside of the sleeve-shaped first sliding bearing 28 is significantly less than it the direct friction between the wedge segments 27a and 27b and the fitting parts 11 or 12 would be.
• the driver segment 25 grasps with play between the narrow sides of the wedge segments 27a and 27b, while the mutually facing broad sides of the wedge segments 27a and 27b respectively support an angled end finger of an annularly wound spring, referred to below as omega spring 30.
• the omega spring 30 presses the wedge segments 27a and 27b apart in the circumferential direction and thus provides the fitting 10 at rest without play.
• the driver 21 is axially secured on the outside of the first fitting part 11 by a clip-on circlip 31. To accommodate the axially acting forces is welded in a conventional manner to the two fitting parts 11 and 12 depending on a not shown in the drawing retaining plate which engages over the other fitting part, without hindering the adjustment movement.
• an eccentric which lies in the power flow between the fitting parts 11 and 12 and is mounted thereon.
• the driver segment 25, which can also be expected to eccentric, is outside the power flow.
• the eccentric pushes in extension of the direction of eccentricity, the gear 16 and the ring gear 17 at a so defined engagement point into each other.
• a torque is first transmitted to the driver 21 and then to the eccentric thus defined, which slides along the first sliding bearing 28 with displacement of the direction of eccentricity and thus with displacement of the engagement point of the gear 16 in Sprocket 17, which is a staggering rolling movement of the fitting parts 11 and 12 together.
• a second sliding bearing 41 is provided to reduce this friction, which sits virtually immobile (adhesive) on the first wedge segment 27a and slides with low friction on the collar 19, so functionally corresponds to the first sliding bearing 28.
• the second sliding bearing 41 is formed as a ring segment, which extends over slightly less than the inside of the first wedge segment 27a, while in the second embodiment, the second sliding bearing 41 is formed as a nearly completely closed ring, on which also the less loaded second wedge segment 27b is sitting. Since otherwise - except for geometric adjustments to the shape of the second sliding bearing 41 - the two embodiments match, carry the same and equivalent components the same reference numerals.
• the second sliding bearing 41 is disposed on the inside of the collar 19 in an area free of the hub 22 and the heavier loaded first wedge segment 27a is supported therein by means of a cantilever.
• the friction between the first wedge segment 27a and the collar 19 has not only an effect on the efficiency, but also on the self-locking of the gear of the fitting 10.
• at least one of the two fittings 10 of the vehicle seat 1 despite the two-sided sliding bearing of the first wedge segment 27a self-locking remains and locked in the idle state against the output side introduced torques, according to the invention in this fitting 10 is provided in the idle state of the fitting 10 effective brake, namely a
• Wrap spring brake 44 which is arranged in a wrap spring bushing 46 and frictionally rests against its inner wall due to their bias.
• the Schlingfederbuchse 46 for example, made of an aluminum alloy or plastic is rotatably mounted on the second fitting part 12 by three by 120 ° staggered three-groups of radially (and / or axially) protruding Schlingfederbuchsenarmen 48 positively in the on the back of the gear 16th engage internal teeth formed by the stamping process.
• the first wedge segment 27a is provided with an axially projecting control cam 51, which is arranged with play in the circumferential direction between the two wrap spring arms 50.
• between or “within” is meant an arrangement that refers to the smaller of the two possible angular ranges in the circumferential direction, while “outside” refers to the larger of the two possible angular ranges in the circumferential direction.
• An investment of the control cam 51 to a Schlingfederarm 50 with subsequent application of the latter acts closing on the wrap brake 44, ie the wrap brake 44 brakes - due to a widening outer diameter thereof and an increased friction on the wrap spring bushing 46 - and prevents rotation of the eccentric defining Components relative to the second fitting part 12. With the blockage of the eccentric and the first fitting part 11 is fixed relative to the second fitting part 12.
• a first cam 53 and on the other hand in the region between the ends of the Mitêtmentes 25th is arranged with approximately the same radial distance, a second driving cam 55 is provided, both of which project axially.
• the two drive cam 53 and 55 are arranged with play the wrap spring arms 50 together with the control cam 51, ie the drive cam 53 and 55 are arranged in the circumferential direction outside the wrap spring arms 50.
• the third exemplary embodiment according to FIG. 7 is similar to the previous exemplary embodiments, in particular the second exemplary embodiment, unless otherwise described below, for which reason identical or substantially identical components bear the same reference numerals.
• a sickle 127 In the collar 19 of the first fitting part 11 of the unchanged trained driver 21 is supported, while on the collar 19 (ie on the outside) a sickle 127 is supported, which is arranged sickle-shaped around a part of the collar 19 around and with its curved outside the in the second fitting part 12 rotatably pressed first slide bearing 28 superimposed.
• the sickle segment 127 corresponds to an integral combination of the two wedge segments 27a and 27b.
• the driver segment 25 summarizes with play between the narrow sides of the sickle segment 127.
• the retaining ring 31 and the retaining plates, not shown in the drawing correspond to the previous embodiments.
• an eccentric which lies in the power flow between the fitting parts 11 and 12 and is mounted thereon.
• the eccentric pushes in extension of the direction of eccentricity, the gear 16 and the ring gear 17 at a so defined engagement point into each other.
• a torque is first transmitted to the driver 21 and then on the eccentric thus defined, which slides along the first sliding bearing 28 with displacement of the direction of eccentricity and thus under displacement of the point of engagement of the gear 16 in the ring gear 17th what is a staggering rolling movement of the fittings 11 and 12 together.
• the efficiency of the fitting 10 depends appreciably on the friction between the sickle segment 127 and the Collar train 19 off.
• the second plain bearing 41 is provided to reduce this friction, which is designed as a virtually completely closed ring.
• the second slide bearing 41 is either immovably mounted on the collar train 19, for example, slotted execution or adhered in closed form, and leaves the Sichelsegement 127 slide with little friction along, or the second slide bearing 41 sits virtually immobile (adhesive) on the sickle segment 127 and slides with low friction on the collar 19, so in each case corresponds functionally to the first sliding bearing 28.
• the fitting 10 remains self-locking in the idle state and locked against the output side introduced torques, in turn, the wrap spring brake 44 is provided.
• the them receiving and frictionally retaining Schlingfederbuchse 46 has all around radially projecting Schlingfederbuchsenarme 48, which may also be realized in the two previous embodiments.
• the wrapper bushing arms 48 engage in a form-fitting manner in the internal toothing formed on the rear side of the toothed wheel 16 by the stamping process.
• the wrap spring brake 44 For driving, the wrap spring brake 44 in turn has the two wrap spring arms 50, while the safety segment 127 is provided with the axially projecting control cam 51, which is arranged between the two wrap spring arms 50.
• the aforementioned definition of “between”, “inside” and “outside” applies.
• a system of the control cam 51 to a Schlingfederarm 50 with subsequent application of the latter acts closing on the wrap spring brake 44.
• a first driver cam 53 and a second driver cam 55 is again provided on the driver 21, which receive the wrap spring arms 50 between them.
• the driver 21 consists on the one hand of a hub 22 for storage with clearance in the collar 19 of the first fitting part 11 and for receiving the drive shaft in a central bore 23, wherein the hub 22 on the outwardly facing front side has a cover.
• the driver 21 consists of a separately formed, non-rotatably connected to the hub 22, perforated drive plate 224 with two integrally formed Mit videsegmenten 25, which are arranged in a semicircle around a portion of the collar 19 around and between them have a gap.
• an eccentric ring 226 is supported on the turn with its curved inside the two wedge segments 27a and 27b are supported, which store with their curved outer sides in the second fitting part 12 rotatably pressed first slide bearing 28.
• the friction conditions are as in the previous embodiments.
• the two driver segments 25 grasp with play between the narrow sides of the wedge segments 27a and 27b, while the facing broad sides of the wedge segments 27a and 27b each support an angled end finger of a Omega spring 30, wherein the Omega spring 30 is disposed on the other side of the drive plate 224 and the Grasp end finger through a gate of the drive plate 224.
• the omega spring 30 presses the wedge segments 27a and 27b apart in the circumferential direction and thus provides the fitting 10 at rest without play.
• the retaining ring 31 and the retaining plates, not shown in the drawing correspond to the previous embodiments.
• an eccentric which lies in the power flow between the fitting parts 11 and 12 and is mounted thereon.
• the eccentric expresses the extension of the direction of centricity of the gear 16 and the ring gear 17 at a so defined engagement point into each other.
• a torque is first transmitted to the driver 21 and then to the eccentric thus defined, which slides along the first sliding bearing 28 under Verlager- tion of the direction of eccentricity and thus under displacement of the point of engagement of the gear 16 in Sprocket 17, which is a staggering rolling movement of the fitting parts 11 and 12 together.
• the efficiency of the fitting 10 depends appreciably on the friction between the eccentric ring 226 and the collar 19.
• the second sliding bearing 41 is provided to reduce this friction, which is designed as a nearly completely closed ring.
• the second sliding bearing 41 is either pressed on the collar 19 and allows the eccentric ring 226 to slide along with little friction, or the second sliding bearing 41 is virtually immovable on the eccentric ring 226 and slides with low friction on the collar 19, so each corresponding to the first functional bearing so functionally 28th
• the fitting 10 remains self-locking in the idle state and locked against the output side introduced torques, in turn, the wrap spring brake 44 is provided.
• the them receiving and frictionally retaining Schlingfederbuchse 46 has all around radially projecting Schlingfederbuchsenarme 48.
• the wrap spring bushing arms 48 engage in a form-locking manner in the internal toothing formed on the rear side of the toothed wheel 16 by the stamping process.
• the wrap spring brake 44 in turn has the two wrap spring arms 50, while the eccentric ring 226 is provided with the axially projecting control cam 51, which engages through an opening in the drive plate 224 and is arranged in the circumferential direction between the two wrap spring arms 50.
• the above definition applies to "between”, “within” and
• the fifth exemplary embodiment according to FIGS. 10 and 11 is similar to the previous exemplary embodiments, in particular the third exemplary embodiment, unless otherwise described below, for which reason identical or substantially identical components bear the same reference numerals.
• a fixed eccentric 327 has a cylindrical disk-shaped basic body, which with its outer side supports the first sliding bearing 28 press-fitted in the second fitting part 12, and an integrally formed hub arranged eccentrically to the center of the basic mold, which by means of the second sliding bearing 41 in the collar 19 of the first fitting part 11 is stored.
• the second sliding bearing 41 is pressed, for example, in the collar 19 and allows the fixed eccentric 327 slide along with low friction (and is designed as a closed ring) or sitting practically immovable on the Festexzenter 327 and slides with low friction in the collar 19 (and is as formed almost completely closed ring).
• the second slide bearing 41 corresponds in each case functionally to the first slide bearing 28 and, due to the reduced friction, influences the efficiency of the fitting 10 analogously to the previous exemplary embodiments.
• the driver 21 is rotatably mounted by means of its hub 22 within the hollow hub of the Festexzenters 327 and coupled with a free travel on entrainment, ie the driver 21 takes the Festexzenter 327 after passing through the idle in Circumferential direction with.
• the retaining ring 31 and the retaining plates, not shown in the drawing correspond to the previous exemplary embodiments.
• the fixed eccentric 327 forms an eccentric, which lies in the power flow between the fitting parts 11 and 12 and is mounted thereon.
• the eccentric pushes in extension of the direction of eccentricity, the gear 16 and the ring gear 17 at a so defined engagement point into each other.
• a torque is first transmitted to the driver 21 and then on the eccentric thus defined, which slides along the first sliding bearing 28 with displacement of the direction of eccentricity and thus under displacement of the point of engagement of the gear 16 in Sprocket 17, which is a staggering rolling movement of the fitting parts 11 and 12 together.
• a wrap spring brake 44 is again provided.
• the them receiving and frictionally retaining Schlingfederbuchse 46 has all around radially projecting Schlingfederbuchsenarme 48.
• the wrap spring bushing arms 48 engage in a form-fitting manner in the internal toothing formed on the rear side of the toothed wheel 16 by the stamping process.
• the wrap spring brake 44 For driving, the wrap spring brake 44 in turn has the two wrap spring arms 50, while the fixed eccentric 327 is provided with the axially projecting control cam 51, which is arranged between the two wrap spring arms 50.
• the aforementioned definition of “between”, “inside” and “outside” applies.
• a system of the control cam 51 to a Schlingfederarm 50 with subsequent application of the latter acts closing on the wrap spring brake 44.
• a first driver cam 53 and a second driver cam 55 is again provided on the driver 21, which receive the wrap spring arms 50 between them.
• a modification is possible, according to which a respective loop spring brake 44 is provided per direction of rotation, which are opposite closing.
• Each Schlingfederbremse 44 is then a Schlingfederarm 50 on the first wedge segment 27a, sickle segment 127, fixed eccentric 327 or the respective control cam 51 mounted or otherwise attached, preferably free of play, while the other two Schlingfederarme 50 each have a drive cam 53 or 55 - after passing through a small Leerwegs - are acted upon, which is shown schematically in Fig. 12.
• the driver 21 is driven, one of the two wrap spring brakes 44 is opened (released) by the driver cam 53 or 55 and the other by the first wedge segment 27a, etc.
• the two wrap spring brakes 44 are arranged axially next to each other in the same wrap spring bushing 46, which is shown in Fig. 13.
• wrap spring bushing is integrally formed with the second fitting part 12, in that the material region, which forms the bearing opening for receiving the first slide bearing 28, is axially somewhat extended in the manner of a collar pull, and with its outside, ie its rear side facing away from the bearing side, the wrap spring brake 44 receives.

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• Engineering & Computer Science (AREA)
• Aviation & Aerospace Engineering (AREA)
• Transportation (AREA)
• Mechanical Engineering (AREA)
• Chairs For Special Purposes, Such As Reclining Chairs (AREA)
• Braking Arrangements (AREA)
• Seats For Vehicles (AREA)

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Citations (4)

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• 2005
  • 2005-06-22 DE DE102005028779A patent/DE102005028779B4/de not_active Expired - Fee Related
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