DE3201309C2 - Adjustment mechanism for the rotary adjustment of two centrally mounted components - Google Patents

Abstract

The invention consists of a universally applicable adjustment mechanism, which enables a sensitive, continuous, centric adjustment of two components, can be integrated, ensures a high degree of security against shock loads while at the same time ensuring freedom from play and good handling. This is achieved by a gear arrangement in which several gears engage in both component brackets with different numbers of teeth. By rotating the gears, the two component bracket halves are shifted relative to one another. By coordinating the number of teeth and varying the modules and the pressure angle, it can be achieved that the operating pressure angle is the same on both component bracket halves. In this way, when there is a rearward load on the fitting plate, blocking no longer occurs via self-locking, but the forces are absorbed by the tooth which is in engagement without any torque. As a result, this tooth acts like a "feather key". A statically determined system can be achieved through favorable positioning of the gears in relation to one another, so that ultimately the system forces also cancel each other out. These regularities can be implemented on both internal and external gears.

Description

- that all forces and moments on the tooth in engagement cancel each other out, & h.

- That the adjustment mechanism is force-free, in that an involute toothing Always uses constant engagement ratios, in which the operating angle of engagement is used are the same on both fitting brackets (15 and 16),

- That the adjusting mechanism is moment-free, in that the operating rolling circles of the The fitting bracket (15) and the operating pitch circles of the fitting bracket (16) are the same, d. H. have equal pitch points.

2. Adjusting mechanism according to claim 1, characterized in that it is for both externally toothed as well as for internally toothed components.

3. Verstellmechanismiü 'na <"H claim 1 and / or 2, characterized in that it is elastically backlash-free by means of a bore in the Planeier.räde.-is (26) is executed.

The invention relates to an adjusting mechanism for Rotary adjustment of two centrally mounted components according to the preamble of claim 1.

A device for fine adjustment of backrests is for example from DE-PS 12 97 496 or also known from DE-PS 16 80128, in which a pivoting Baschlag flap with an internally toothed Gear train and the other fitting bracket is connected to an externally toothed gear train, wherein the externally toothed gear train runs by means of eccentric bolts in the internally toothed gear train. One relative displacement of these two fitting brackets is achieved by the difference in the number of teeth between Ring gear and spur gear is one. This hinge fitting is continuously adjustable and the Both fitting glasses remain constantly engaged during the pivoting, but the locking security is hereby achieved under load by means of the small difference in the number of teeth.

This small difference in the number of teeth results in a small friction angle (Tan λ <6 °), so that this mechanism becomes self-locking due to a critical sliding angle inclines and blocks the gear ratio. However, the self-locking angle between the two works Fitting brackets in such a way that adjustment under load is not possible.

Another disadvantage of this construction is the eccentric movement due to the eccentric adjustment of the two fitting lugs against each other. This movement is transmitted to the connecting parts and leads to a "tumbling" of the backrest. This "tumbling effect" in the area of the transfer tube may lead to sluggishness and thus to uselessness in practical use the backrest adjustment.

ίο A similar construction is also by DE-PA 26 09 607; FR-PS 24 55 869 also known this construction has an eccentric bolt on which an externally toothed gear wobbles.This externally toothed gear meshes with two internally toothed, centrally mounted ring gears, the difference in the number of teeth is also at least one.In this case, the wobble effect is no longer on the back transferred, but this hinge fitting also has the disadvantage that only high reduction ratios come into question in order to maintain a locking security, with the transmission being blocked by self-locking when loaded. This means that it cannot be adjusted under load.
It is also known that the static friction angle μ ₅ αι {/ ism Φ Mdytt) is not equal to the dynamic friction angle μάγη

The consequence of this is that when there is a dynamic load on an unloaded backrest, this backrest changes as a result their own weight and automatically adjusted when the dynamic friction angle is exceeded Behavior does not meet the high safety aspects of the automotive industry for the interior. Farther It must be taken into account that due to the small difference in the number of teeth, the pivoting of the backrest by one Another small swivel angle requires a very tedious operation of the handle Aspect consists in the fact that these teeth are not kept backlash-free for functional reasons can and therefore could breathe under extreme stress.

That is, as a result of the direction of force and the shortening of the head and foot, those in engagement push each other Teeth away from each other. The degree of coverage is changed and this effect may lead to to a slipping of the teeth.

Also one under DE-PS 26 60 395; FR-PS 23 61 082 known construction has similar properties. Here, the tumbling of the eccentric bolt is controlled by means of several pins, which are correspondingly larger Engaging holes in a counter plate canceled. Here, too, is driven by means of a planetary system and the holding forces in the crash test are realized by means of self-locking. In addition to the disadvantages already outlined there is also a larger play in the translation gear, which also increases the safety aspects the automotive industry is not enough.

In some constructions (FR-PS 23 07 495; FR-PS 15 66 179) the eccentric pin drive degenerates into one Slide shoe that drives the planet gear eccentrically.

Again, the locking security is only due to Friction laws are realized so that these constructions cannot be adjusted under load, keep the position even under dynamic loads.

Another construction is, for example, from DE-PS 26 04 489; FR-PS 22 99 984 known in which two swivel plates with internal teeth and different numbers of teeth with one sun gear and four Comb planet gears. The continuous drive

32 Ol 309

in this case represents a planetary gear system with 4 planetary gears represent.

The locking security is problematic here. To the To increase the coefficient of friction, an elastic element is also installed, which, when the vehicle moves backwards accordingly Load serves as a friction brake

This results in the disadvantage that at least part of the braking torque of the friction brake when actuated of the sun gear must be overcome. In addition, this construction has a large number of components on and is therefore complex and expensive to manufacture.

A similar construction is under DE-OS 29 07 134; FR-PS 24 50 713 known Also here acts it is a planetary gear system with 4 planetary gears via which the continuous drive takes place. The inhibiting mechanism when operated from the rear, a 4-pole sliding shoe is used. With backwards In actuation, these 4 concave sliding blocks act like ramps and the planet gears due to the play in the toothing as well as the large angle of contact (Eythelwein equation) tend to block the system. This way there will be a slip of the components prevented The locking safety of this adjustment mechanism is only ensured by the Realized sliding shoes, which act as a circumferential friction brake on the tip circle of the toothing. This system can only be made play-free with difficulty, otherwise the sliding blocks will not have an effect due to overdetermination or, in the other case, serve as a brake on the drive. It follows that this Mechanirmus cannot be adjusted under load. The safety aspect of the automotive industry must therefore also be questioned here be asked.

The invention is now based on the object while avoiding the problems described to create a universally applicable adjustment mechanism that, on the one hand, has a sensitive, centric Adjustment of the components enables, on the other hand, a high level of security against unintentional adjustment with simultaneous freedom from play and good handling guaranteed.

In the case of the adjusting mechanism of the type mentioned at the beginning, this task is performed by the characterizing Features of claim 1 solved.

With this design of the adjusting mechanism, a gear arrangement results in which the locking reliability not only from the difference in the number of teeth of the two fitting brackets and thus from the laws of friction, but primarily from the geometrical laws of the flank angle during tooth meshing depends. The safety aspect can thus be fully complied with, since the engaging tooth has one There are constant engagement ratios and, in addition, all occurring Completely cancel out forces and moments in the system. This results in a decisive advantage over the previous adjustment mechanisms. Due to this conception, an adjustment is also under Load possible because the construction is not based on any laws of friction.

The invention can be used in many ways and implemented in different embodiments will. In future, the entire adjustment mechanism could be completely integrated into the components to be adjusted and accordingly no longer needed to display a separate component, which is not just one would result in a considerable reduction in manufacturing costs, but at the same time result in a considerable saving in weight would lead.

As a result of the increasing demand for comfort from the automotive industry on a vehicle seat it is possible to operate the adjustment mechanism not only manually using a handwheel, but also in addition to be driven by means of an electric motor adjustment and the correspondingly different seating positions to save and to start again reproducibly.

The adjustment mechanism is very universal for positioning and fixing components or components some utility furniture as well as vehicle seats suitable. This adjustment mechanism can be used both for the parallel and non-parallel seat height adjustment as well as for the advance positioning of the Use the seat frame and continue to position the backrest relative to the seat surface. This adjustment mechanism serves in particular to provide the person who sets the sentence or the car driver with an ergonomic 'optimal sitting position to be taken. Verstellmcehanismus can can be operated both by handwheel and by motorized drive, taking into account an optimal Seat position the setting conditions electromotively; -2hr individually controlled and via a memory can be restarted reproducibly at any time.

In the following description, the invention is based on exemplary embodiments in connection with the drawings explained

It shows

Fig. 1 shows a seat with an adjusting mechanism as a seat height adjuster in parallel and translationally moved embodiment,

F i g. 2 a seat with adjustment mechanism as a seat height adjustment with independent height adjustment (front and rear),

3 shows a seat with an adjustment mechanism in pure parallel execution,

F i g. 4 an adjustment mechanism used to position the seat frame as a result of relative displacement from top to bottom slide rail,

Fig. 5 is equipped with an adjusting mechanism Backrest,

F i g. 6 a backrest equipped with an adjustment mechanism, in which the adjustment mechanism is used for Headrest tilt adjustment is used,

F i g. 7 shows an illustration of the adjustment mechanism for adjusting two components by means of internal gearing,
F i g. 8 shows a cross section along the line IV-IV,

F i g. 9 the law of meshing of a planetary gear drive,

FIg. 10 the generation of the same pitch points and directions of force for both fitting brackets,
11 shows the radial forces on the adjustment mechanism,

12 shows an illustration of the adjustment mechanism for adjusting two components by means of external toothing,
F i g. 13 shows a cross section along the line VV,

14 shows an adjustment mechanism; .n an integrated embodiment,

F i g. 15 shows a section along the line VI-VI.

One shown in FIG. 1 underlying seat comprises a seat surface 10 and an upper part of a slide rail 11. Both components are connected by 2 adjustment mechanisms 12, both adjustment mechanisms 12 by means of a transmission rod 13 and a handwheel 14 syn-

can be operated chronologically. The one fitting flap 16 is rigidly attached to the slide rail 11. The other fitting bracket 15 is attached in an articulated manner to the seat surface 10. Both fitting straps IS, 16 are through the adjustment mechanism 12 centrally connected and their position can be determined by turning the handwheel 14 as a result a relative movement between the fitting tabs 15 and 16 centrically fine adjust. Through this is based on the articulated lever 17 a parallel seat height, with simultaneous translational Seat adjustment achieved According to FIG. 2 and 2a is the adjustment mechanism 12 for independent height adjustment of the seat 10 opposite the upper part of the slide rail 11 is used. By pressing the front Handwheel 14 or actuation of the rear handwheel 14 can be the hinged fitting tabs 15 relative to the fitting brackets 16 rigidly attached to the upper slide rail 11 independently of adjustment the headrest 25 is used. In this application, the fitting bracket 15 is with the headrest 25 and the fitting bracket 16 firmly connected to the backrest 24. By operating the handwheel 14 the headrest 25 can be pivoted and fixed in any position.

In Fig. 7, the adjustment mechanism 12 is shown. The procedure for determining the forces and freedom from moments of the adjusting mechanism 12 is to be shown as an example on the statically determined system (a 3 degrees of freedom => 3 planet gears). The same considerations apply to all other translation combinations. As a result of the more complex geometrical design of the internal toothing, the principles on which the adjusting mechanism 12 is based are explained using the internal toothing as an example.
In Fig. 7 is a technology well-known

each other fine, disguise. On the basis of the known principle of Piancienradami iebc. The particularly

Steering bracket 18, the seat 10 can be brought into an independent height and inclination position.

Instead of the additional hinge bracket 18, the same effect can also be achieved by means of the one shown in FIG. 2a shown Reach the elongated hole.

The embodiment according to FIG. 3 is analogous to the exemplary embodiments already shown. Instead of the individual adjustment the adjustment mechanism 12 is used to operate a pair of scissors made up of two intersecting hinged plates 19 and 20 consists, and which are each rigidly connected to the fitting bracket 15 and 16, used. By turning the handwheel 14, a central fine adjustment of the two fitting brackets takes place 15 and 16 via the hinge plates 19 and 20, the seat surface 10 can be raised in parallel and in can be firmly positioned at any seat height.

The in Fig. 4 shows the upper half 21 and the lower half 22 of a slide rail. Both are connected by the adjustment mechanism 12. The fitting bracket 15 is shown in FIG Embodiment connected to the upper slide rail half 21. The fitting bracket 16 has an elongated hole, into which a bolt 23 of the lower slide rail half 22 is fitted. Let by operating the handwheel 14 the two Gleitschienenhäifte 21 and 22 move steplessly against each other and in any desired Position the position firmly.

One shown in FIG. The application example shown in FIG. 5 shows a complete feeling of sitting with the backrest 24 whose inclination to the seat 10 is continuously adjustable. The fitting bracket 15 of the adjustment mechanism is used for this setting 12 with the backrest cheek of the backrest 24 rigidly connected, while the second fitting bracket 16 is firmly mounted on the seat 10. The inclination adjustment the backrest 24 is made by rotating the handwheel 14. For better power absorption another adjustment mechanism 12 can be attached to the other side of the seat, which with the aid of the transmission rod 13 is synchronized with the other adjusting mechanism 12 with handwheel 14 to operate is the fine adjustment, positioning and determination of the inclination between the backrest 24 and seat 10 is identical to the pivot axis of the fitting straps 15 and 16 and can be continuously adjusted in fix each position.

Another application example is shown in FIG. 6. Here, an adjusting mechanism 12 is not only as shown in FIG. 5 for positioning the backrest 24 but a further adjustment mechanism 12 for centric pivoting of the adjustment mechanism 12 is that the planet gears 26 not only revolve around the sun gear 27 and at the same time engage in the internal teeth of the fitting plate 15 and the fitting plate 16, but that the contour of the tooth flanks is designed so that the direction of force and force application point of the fitting plate 16 and the fitting plate 15 despite different Number of teeth are identical and the forces at Belasi - ^ ng cancel each other out on the circumference. This has the consequence that the meshing teeth of the planetary gears 26 in the event of a rearward load (displacement of the fitting bracket 16 opposite fitting bracket 15) act like three parallel keys. By means of sun gear 27 can be known in Way the planet gears 26 are driven and due to a difference in the number of teeth between the fitting plate 15 and fitting bracket 16 there is a continuous relative displacement of the two fitting brackets 15.16.

Both planet gears 26 and sun gear 27 are designed so that they can represent identical parts. That Square hole of these gears 26, 27 is not only used to drive and to reduce the weight of the adjustment mechanism 12, but also to compensate for elastic deformations, so that the Planetary gears can be installed preloaded and thus play-free running of the adjustment mechanism 12 is guaranteed

F i g. 8 shows the actuation of the sun gear 27 by means of handwheel 14 and transmission rod 30. So that the both fitting brackets 16 and 15 mesh with the planetary gears 26 even in the event of a load, the retaining plates become 28 and 29 are required, which join the two fitting tabs 15, 16.

To explain the freedom from moments and forces of the adjusting mechanism 12, the toothing geometries must be considered. F i g. 9 shows the laws of engagement of an involute toothing. Involute gearing has the advantage over all other types of gearing that it is not only inexpensive and insensitive to changes in center distance, but also has constant engagement ratios, whereby the direction of force is constant and always goes through the pitch point ) is determined by the tangent to the base circle r _g v of the planetary gear 26 and the base circle r _g n of the internally toothed fitting bracket 15

32 Ol

Force application direction or the operating pressure angle ac _w . A profile shift of the sun gear 27 and planet gears 26 affects the axle spread, but not the base circles r _g j \ r _g n. In order to obtain defined engagement conditions, it is necessary as a condition of the sum of the axial distance between sun gear 27 and Plancienrad 26 plus the base circle r _g u Planet wheel 36 always be larger than the base circle radius r _g 3i of the internally toothed fitting bracket 15.

Accordingly, the operating pressure angle a _w and thus the direction of force engagement can be influenced with the aid of the profile shift. The base circles, in turn, can be influenced by the pressure angle. If these basic toothing laws are taken into account, the same operating pressure angle a _w and thus a constant direction of force on the fitting brackets 15 and 16 can be achieved.

In order to generate a nominal torque adjustment weight, the rolling circles of the fitting bracket 15 and the rolling circles of the fitting bracket 16 must be the same. This can be achieved with various measures. One possible measure is shown in FIG. If a slight pitch error is permitted between the planetary gear 26 and the internal toothing in accordance with the toothing qualities specified in DIN 3962, the pitch circles of the fitting bracket 15 and 16 and thus also the base circles r _{g of} the fitting bracket 15 and 16 can be changed. The common tangent to the base circle r _{g of} the fitting bracket 15 or 16 and to the base circle r _{g of} the planetary gear 26, taking into account the center distance between the sun gear 27 and the planet gear 26, results in the associated rolling points. These parameters can be varied so that the force application points of the fitting bracket 15 and 16 are identical.

In order to get the force directions of the fitting bracket 15 and 16 congruent in addition to the same force application point, the pressure angle λ »of the fitting bracket side 15 compared to the fitting bracket side 16 (or the pressure angle <x _{w of} the entire left fitting half compared to the right fitting half) must be changed .

These regularities have the consequence that the operating pressure angles a _{w become} identical and the forces not only intervene at the same point but also at the same angle. As a result, the circumferential forces cancel each other out at the meshing teeth of the planetary gears 26 when they are driven backwards. In this case, the engaging teeth of the planetary gears 26 act like parallel keys on the circumference on the two fitting brackets 15 and 16.

Since the pitch circle and direction of force of the fitting bracket 15 are identical to the pitch circle and direction of force of the fitting bracket 16, when the sun gear 27 is rotated, there is no torque on the meshing tooth of the planetary gear 26 and thus the adjustment mechanism 12 can also be adjusted under load, as blocking due to self-locking does not occur

F i g. 11 shows the resulting axial forces on the Adjustment mechanism IZ With every loaded gear pair, the center points of the axis strive as a result of the meshing Normal forces and the resulting radial forces apart. This means that the center distance Backlash and degree of overlap changed For this reason, the adjustment mechanism 12 designed in such a way that the radial forces generated during engagement are equal and move towards the center of the Raise sun gear 27 out. This has the consequence that the adjusting mechanism 12 moves with each introduction of force automatically centered. The toothing laws apply in the same way to the external toothing. Fig. 12 shows an externally toothed fitting plate 33 and an externally toothed fitting plate 34 with different numbers of teeth. The toothing is cut into the fitting bracket half Fig. 13, which have the same center. In these gears z. B. three planet gears 26 a (statically determined system). These planet gears 26 can, for. B. actuated by an internally toothed handwheel 35 will.

As with the internal gearing, not only self-locking but also force and achieve freedom from moments due to the same tooth flank contour on the adjustment mechanism 12.

Since this adjustment mechanism 12 as a result of its gearing mechanism optimal power introduction and load structure 14, the internal toothing of the fitting bracket 15 is made directly by a forming process integrated into the backrest cheek 40 of the backrest 24. Turn the handwheel 14 in 15, the sun gear 27 is driven and the planetary gears 26 are used for fine adjustment between the backrest cheek 40 and the fitting bracket 16, which in this case is not mounted directly on the seat, but via an adapter 41 of the z. B. by means of three rivets 42 is connected to the fitting bracket 16, adapted to the connection dimensions of the seat. By holding plates 43 and 44 the entire adjustment mechanism 12 is held together. The reinforcement tube 45 is with the Backrest cheek 40 firmly connected, stiffens the construction and at the same time protects the transmission tube 46.

In addition 8 sheets of drawings

Claims (1)

32 Ol 309 claims: 1. Adjustment mechanism for the rotary adjustment of two centrally mounted components, one component side of which with the fixed unit and its other component side with the product unit to be adjusted is connected, each component side is provided with a toothing that has a different number of teeth having, wherein a planetary drive is arranged between the component sides, the planetary gears mesh with one or more teeth simultaneously in both gears on the same pitch circle and can be driven by means of a handwheel or motor, characterized in that