DE3201309A1 - Central, continuous adjusting mechanism, which is free of moments and forces, for positioning the seat height, the seat distance and the backrest for commercial furniture and car seats - Google Patents

Abstract

The invention consists of a universally usable adjusting mechanism which allows sensitive, continuous, central adjustment of two components, can be integrated, and guarantees a high degree of safety against jerky loading, whilst maintaining freedom from backlash, and convenient handling. This is achieved by a gearing arrangement, in which a plurality of gearwheels engage in both component tabs having a different number of teeth. By rotating the gearwheels, the two halves of the component tabs are displaced relative to one another. It can be achieved, by matching the numbers of teeth and by varying the modules and the angle of engagement, that the operating angle of engagement is the same on both component tab halves. Consequently, when the fitting tab is loaded backwards, blocking no longer takes place via self-locking, but the forces are absorbed without torque on the engaged tooth. As a result, said tooth acts as a "feather key". By favourable positioning of the gearwheels relative to one another, a statically defined system can be achieved so that, finally, the system forces also eliminate one another. These regularities can be implemented on an internal and on an external toothing. <IMAGE>

Description

The invention relates to one specified in claim 1
Adjustment mechanism that is very universal for positioning and fixing components or components
some utility furniture as well as vehicle seats is suitable. This adjustment mechanism can be used both for parallel and non-parallel seat height adjustment as well as for feed positioning
of the seat frame and continue to use for the backrest positioning relative to the seat surface. This adjustment mechanism is used in particular to make the seated or
gives the driver an ergonomically optimal seating position
to be taken. The adjustment mechanism can both
operated by handwheel as well as by motorized drive
taking into account an optimal seating position
the setting conditions by the electric motor are very individual
controlled and can be restarted reproducibly at any time via a memory.

A device for fine adjustment of backrests is
for example from DE-PS 1 297 ^ 96 or DE-PS 1680 128
known, in which a pivoting fitting bracket with j
an internally toothed gear train and the other fitting bracket is connected to an externally toothed gear train,
the externally toothed gear train by means of eccentric bolts
runs in the internally toothed gear train. A relative displacement of these two fitting brackets is achieved by
that the difference in the number of teeth between the ring gear and the spur gear
is one. This hinge fitting is continuously j loaned and the two fitting brackets remain constantly in engagement during the j pivoting, but here the \

Locking safety under load by means of the low Zähne- \

number difference reached. {

This small difference in the number of teeth results in an I.

low friction angle ( / * tt * t < 6 ° ) » ^so that this mecha- ^:

nism as a result of a critical slip angle to the self- J

inhibition tends to block the gear ratio. *

However, the self-locking angle between the two -. lash out in such a way that adjustment under load is not possible
is.

. 4 ·

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 leads below Circumstances to a sluggishness and thus in practical use to a uselessness of the backrest adjustment.

A similar construction is also from DE-PS 2609 607; F-PS 2 ^ 55 869 known. This construction also has an eccentric bolt on which an externally toothed gear wobbles. This externally toothed gear meshes with two internally toothed, centrally mounted ring gears whose difference in number of teeth is also at least one. In this case, the wobble effect is no longer transferred to the backrest, but this hinge fitting also has the disadvantage that only high reduction ratios are possible to maintain locking reliability, whereby the transmission is blocked by self-locking when loaded. It is also known that the static friction angle Msioi- ( Uu & l φ Mdun.) Is not equal to the dynamic friction angle yU dyn .

The consequence of this is that when there is a dynamic load on an unloaded backrest, this backrest moves as a result of it Dead weight and automatically adjusted when the dynamic friction angle is exceeded. This behavior is sufficient not the high safety aspects of the automotive industry for the interior. Furthermore, it must be taken into account that due to the small difference in the number of teeth, the pivoting of the backrest by a small pivot angle makes a very tedious operation of the handle necessary. Another aspect is that this toothing for functional reasons not can be kept free of play and therefore could breathe under extreme stress.

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That is, as a result of the direction of the force, the im Engaging teeth away from each other. The over- j

The degree of coverage is changed and this effect leads, under certain circumstances, to the toothing slipping through.

A construction known under DE PS 26 6θ 395} F-PS 236I 082 also has similar properties. Here, the wobbling of the eccentric bolt is eliminated by means of several pins that engage in correspondingly larger shaped bores in a counter plate. In addition to the disadvantages already described, there is also a greater play in the transmission gear, which also does not meet the high safety aspects of the automotive industry.

In addition to the centrally mounted eccentric bolts, some constructions (F-PS 75 12 103} F-PS 1566 179) a sliding shoe. Here the eccentric adjustment movement is taken over by the sliding shoe. Again, the Locking security realized only due to the laws of friction, so that these constructions Do not allow it to be adjusted under load, or maintain the position under dynamic loads.

j Another construction is, for example, from the j

DE-PS 26 Ok 489 known, in which two swivel plates!

i with internal teeth and different numbers of teeth with;

a sun gear and four planet gears can engage in both gears. As a result of the actuation of the sun gear by means of a handwheel, the planetary gears are driven and a relative adjustment takes place between the two swivel plates. Here, too, the locking reliability is based on the utilization of a critical friction angle. To increase this effect, an elastic element is also installed as a further safety variant, which is intended to increase the expected self-locking in the event of a corresponding load. This construction therefore has a large number of components and is therefore _v

complex and expensive to manufacture.

A similar construction is under F-PS 24 50 713 known. Here, too, are two swivel plates with internal teeth of different numbers of teeth into which four planet gears engage at the same time. These planet gears are driven by a sun gear or a 4— pole sliding shoe driven centrically. The forced rotation of the sun gears is thus realized via the sliding shoe, the sliding shoe at the same time increasing the friction surface and taking into account the wrap angle (Eytelwein equation), a high frictional force can be transmitted, so that the locking reliability this adjustment mechanism is also based on the self-locking principle and here too the safety aspect the automotive industry must be called into question.

The invention is now based on the object of avoiding the problems described To create a universally applicable adjustment mechanism which, on the one hand, enables sensitive, centric adjustment the components enables, on the other hand, a high degree of security against unintentional adjustment while at the same time Free of play and good handling guaranteed.

This object is achieved in the adjusting mechanism with the features specified in claims 1-9. With this Design of the adjusting mechanism results in a gear arrangement in which the locking security is not only on the difference in the number of teeth in both fitting plates and thus from the laws of friction, but primarily from the geometric laws of the Flank angle depends on the meshing. The safety aspect can thus be fully complied with, since the most intrusive Tooth constant engagement conditions are present and, in addition, all forces and Completely cancel out moments in the system. This results in a decisive advantage over the previous adjustment mechanisms. Due to this concept, adjustment is also possible under load, as there is no friction

the principles of construction are based. ⁿ

The invention can be used in many ways and in j

different embodiments can be realized. f

In the future, the entire adjustment mechanism could be complete;

be integrated into the components to be adjusted and = accordingly no longer needed a separate component

deliver, which is not only a significant reduction in;

Would result in manufacturing costs, but at the same time to]

leads to a significant weight saving. j

I As a result of the ever increasing demand for comfort _:

the automobile industry on a vehicle seat there is the ] possibility of not only manually adjusting the adjustment mechanism {

to be operated by means of a handwheel, but also to be driven by means of an electric motor adjustment and to save the correspondingly different seating positions and to approach them again in a reproducible manner.

In the following description, the invention is explained (for example) with reference to drawings.

It shows; . .

Fig. 1: a seat with an adjusting mechanism as a seat height adjuster translatory in paraleller savie j

wegter embodiment. j

Fig. 2: a seat with an adjustment mechanism as a seat height adjuster with independent height adjustment j

( front and back) {

Fig. 3 J a seat with an adjustment mechanism in pure parallel execution.

Fig. Ki an adjustment mechanism used to position the seat frame as a result of relative displacement from the upper to the lower slide. COPY

- tf - -

5J shows a backrest equipped with an adjusting mechanism.

6: an equipped with an adjusting mechanism Backrest in which the adjustment mechanism is used to adjust the headrest angle.

Fig. 7 ϊ a representation of the adjustment mechanism in a first embodiment for adjusting two components by means of internal teeth.

8: a cross section along the line IV - IV

9 5 shows the law of meshing of a planetary gear drive.

Fig. 10: the generation of the same pitch points and directions of force for both fittings.

Fig. 11: the cancellation of the radial forces on the adjustment mechanism,

Fig. 12: an illustration of the adjustment mechanism in a first embodiment for adjusting two components by means of external teeth.

13J shows a cross section along the line V-V.

14: an adjusting mechanism in an integrated design.

Fig. 15: a section along the line VI - VI.

A seat on which FIG. 1 is based comprises a seat surface 10 and an upper part of a slide rail 11. Both components are connected by two adjustment mechanisms 12, both adjustment mechanisms being able to be operated synchronously by means of a transmission rod 13 and a handwheel Ik. One fitting tab side 16 is rigidly attached to the slide rail 11. The other fitting 'tab side 15 is articulated on the seat surface 10

solidifies. Both fitting flap sides are centrally connected by the adjusting mechanism 12 and their position i

can be adjusted by turning the handwheel lh as a result of a relative movement between the fitting brackets 15 -

and 16 fine-tune centrically. This is under Based on the articulated lever 17 a parallel Seat height achieved with simultaneous translational seat adjustment.

According to FIGS. 2 and 2 a, the adjustment mechanism 12 for independent height adjustment of the seat 10 is opposite the upper part of the slide rail 11 is used. By loading

j actuation of the front handwheel Ik or actuation of the?

rear handwheel 14 can be the articulated befes- j

final fitting tabs 15 relative to the one on the top: j Slideways 11 rigidly attached fitting brackets i6 fine-adjust independently of one another. Based on the hinge bracket 18 can bring the seat surface 10 into an independent height and inclination position will.

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

The embodiment according to FIG. 3 is analogous to that already shown embodiments. Instead of the individual adjustment, the adjustment mechanism 12 is used for actuation a pair of scissors, which consists of two intersecting hinge plates 19 and 20, and which each with the fitting flap 15 and 16 are rigidly connected, used.

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By turning the handwheel "\ k , a central fine adjustment of the two fitting straps 15 and 16 takes place and the seat surface 10 can be raised in parallel via the hinge straps 19 and 20 and firmly positioned at any seat height. The embodiment shown in FIG. K shows the upper half 21 and the lower half 22 of a slide rail. Both are connected by the adjusting mechanism 12. In the embodiment shown, the fitting bracket 15 is firmly connected to the upper slide rail By operating the handwheel 14, the two slide rail halves 21 and 22 can be moved steplessly against one another and can be fixedly positioned in any desired position.

An application example shown in FIG. 5 shows a complete seat with a backrest 2k whose inclination to the seat surface 10 is continuously adjustable. For this setting, the fitting bracket 15 of the adjustment mechanism 12 is rigidly connected to the backrest cheek of the backrest 2k , while the second fitting bracket 16 is firmly mounted on the seat 10. The inclination of the backrest is adjusted by turning the handwheel "\ k . For better absorption of force, a further adjustment mechanism 12 can be attached to the other side of the seat, which can be operated with the aid of the transmission rod 13, synchronously with the other adjustment mechanism 12 with handwheel I ^ The fine adjustment, positioning and determination of the inclination between the backrest and the seat surface is identical to the pivot axis of the fitting brackets 15 and and can be continuously fixed in any position.

Another application example is shown in FIG. 6. Here, an adjusting mechanism is not only used as in FIG. 5 for positioning the backrest 2k, but another

Adjusting mechanism 12 used for central pivot adjustment of the headrest 25. In this
Application is the fitting bracket 15 with the
Headrest 25 and the fitting bracket 16 are firmly connected to the backrest 2k. By operating the handwheel Tk , the headrest can be swiveled and in each
fix any position.

In FIG. 7, the described creation mechanism is 12
shown. The procedure for determining the forces and freedom from moments of the adjustment mechanism should
exemplarily on the statically determined system (- 3 degrees of freedom ag> 3 planet gears). Same
Considerations apply to all other translation combinations »as a result of the more complex geometrical
Design of the internal toothing, the basic principles of the adjustment mechanism are to be explained using the example of internal toothing.

7 is one known in the art Principle of planetary gear drives. The special feature 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 bracket 15 and the fitting bracket 16, but also the contour of the tooth flanks is constructed in such a way that the direction of force and the point of force application the fitting bracket 16 and the fitting bracket 15 are identical despite a different number of teeth and the forces cancel each other out under load on the circumference. That has

in the ,

with the result that the meshing teeth of the planetary; wheels 2.6 with rearward loading (shifting the
Fitting bracket 16 opposite fitting bracket I5) act like three parallel keys. By means of sun gear 27, in known

wise the planet gears are driven and as a result
a tooth number difference between the mounting tab 15 and _e fitting tab 16, a continuous relative displacement of the two fitting lugs.

Both planet gears 2.6 and sun gear 27 are designed so that they can represent identical parts. The square hole of these gears is not only used to drive and reduce the weight of the adjustment mechanism 12, but also to compensate for elastic deformations, so that the planet gears can be installed preloaded and thus a play-free running of the adjustment mechanism is guaranteed.

Fig. 8 shows the actuation of the sun gear 27 by means of hand wheel 14 and transmission rod 3 ° · So that the two fitting tabs 16 and 15 also in case of load with the Planetary gears 26 mesh, the retaining plates 28 and 29 are required, which join the two fitting brackets.

To explain the freedom of moments and forces of the adjustment mechanism, the gear geometries are to be considered. 9 shows the laws of engagement of an involute toothing. The involute toothing has opposite all other types of gearing have the advantage that they are not only inexpensive and insensitive to Achsabs state changes, but at the same time has constant engagement ratios, the direction of force is constant and always goes through the pitch point. The determination of the outer pitch point of a planetary gear (Planet gear 26 and internal toothing) is indicated by the tangent to the base circle r 3I of the planet gear 26

and the base circle 32 of the internally toothed fitting bracket 15 is determined. This tangent intersects the vertical one The axis of symmetry in the pitch point, and its slope gives the direction of force application or the operating pressure angle at. A profile shift of sun gear 27 and planet gears 26 influences their center distance, but not the base circles. In order to get defined engagement conditions,

As a condition, the sum of the center distance between the sun gear 27 and the planet gear 2ö plus the base circle r of the planet gear 26 must always be greater than the base circle radius 32 of the internally toothed fitting bracket 15. As a result, the operating angle of engagement 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 and thus a constant direction of force on the fitting brackets 15 and 15 can be achieved.

To generate a moment equilibrium, the rolling circles of the fitting bracket 15 and the rolling circles the fitting bracket 16 be the same. This can be done with different Measures are achieved. One possible measure is shown in FIG. If you let one low pitch error according to DIN 3962 specified toothing qualities between planetary gear and internal toothing, so the pitch circles of the fitting bracket 15 and 16 and thus also the base circles r of the fitting straps 15 and 16 can be changed. The common Tangent to the base circle r of the fitting bracket 15 or 16 and to the base circle r of the planetary gear

taking into account the center distance between the sun gear 27 and planet gear 26 result in the respective pitch points. These parameters can be varied that the force application points of fitting bracket 15 and become identical.

In order to have the same force application point and the force

directions of the mounting bracket I5 and 16 congruent with loading \

come, the pressure angle of the fitting brackets must j

page 15 opposite the fitting flap side 1o (or j

also the pressure angle of the entire left fitting J half compared to the right fitting half)

will. :

These regularities have the consequence that the operating engagement angles are identical and the forces are not only intervene at the same point, but also at the same angle. As a result, the circumferential forces increase rearward drive on the engaging teeth of the Planet gears 26 on. In this case, the intervening act Teeth of the planetary gears 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 is identical to the pitch circle and direction of force of the fitting bracket 16, occurs when the sun gear is rotated 27 no moment at the engaging tooth of the planetary gear 26 and thus the adjustment mechanism can also Adjust under load, since blocking does not occur due to self-locking.

Fig. 11 shows the resulting axial forces on the Adjustment mechanism 12. For every loaded gear pair the center points of the axis strive as a result of the acting normal forces and the resulting radial forces apart. This changes the center distance, backlash and degree of overlap. Because of this, the Adjustment mechanism designed so that the engagement resulting radial forces are equal and cancel each other out towards the center of the sun gear. This has the consequence that the adjusting mechanism 12 with each introduction of force automatically centered.

The toothing laws also apply to the external toothing. 12 shows an externally toothed fitting plate 33 and an externally toothed fitting plate "} k of different numbers of teeth. The toothing is cut into the fitting plate half of FIG one operated by an internally toothed handwheel 35, but also by relocating the handling point

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can be operated in another axis by a gear pair (gear 35 and component 35) by means of handwheel 37. The rotary movement can be controlled by means of the transmission rod 38 be transferred to a second adjustment mechanism. The retaining plate 39 is used exclusively for fastening and guidance of the gear 36. As with the internal toothing Here, too, not only self-locking but also freedom of force and moments as a result Achieve the same tooth flank contour on the adjustment mechanism.

Since this adjustment mechanism has optimal force units and load structure due to its toothing geometry, the internal toothing of the fitting bracket 15 is integrated directly into the backrest cheek ^ O of the backrest 2k in FIG. By turning the handwheel 1k in Fig. 15, the sun gear 27 is driven and the planetary gears 26 make a fine adjustment between the backrest cheek ^ O and the fitting bracket 16, which in this case is not mounted directly on the seat, but via one of the consumers individually required adapter 4i, which is connected to the fitting bracket 16, for example by means of three rivets k2, is adapted to the connection dimensions of the seat. The entire adjustment mechanism is held together by holding plates A-3 and kk. The reinforcement tube h <y is firmly connected to the backrest cheek, stiffens the construction and at the same time protects the transfer tube 46.

This adjustment mechanism requires few components, is particularly robust, light and inexpensive to manufacture, runs centrically and can be operated continuously even under load} it can be designed without play and through favorable force distribution characteristics in the Integrate the component to be operated.

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Claims (1)

PATENT CLAIMS j 1.] Adjustment mechanism for the rotary adjustment of two centrally mounted components, one component side of which is connected to the stationary unit and the other component side of which is connected to the product unit to be adjusted, each component side being provided with a toothing, the one
has different number of teeth between which
a planetary drive is arranged, the planetary gears with one or more teeth at the same time
engage in both gears on the same pitch circle and driven by handwheel or motor are characterized in that this adjustment mechanism on the drive side adjusted centrally; can be, but on the output side without { Additional equipment such as sliding shoes, brakes, etc. j due to the meshing tooth flank contour, of the planetary gears 26 not only achieves self-locking ^: can be, but also all j Cancel forces and moments in the system. : '{ 2. Adjustment mechanism according to claim 1, characterized in that it adjusts in the loaded state
leaves. 3. Adjusting mechanism according to claim 1-2, characterized in that it can be adjusted centrally in
stops in any position and is loaded there
can be. H. Adjusting mechanism according to claims 1-3 »characterized in that the toothing of the
Swivel parts 15 and 16 directly through a forming process
can be introduced into the connection components ^ O so that the
Toothings and thus the entire mechanism in the Product can be integrated. BAD ORiGINAL . a 5. Adjusting mechanism according to claim 1 - h, characterized in that all planet gears 26 and Sun gear 27 have the same tooth geometry \ and can be identical parts. 6. Adjusting mechanism according to claim 1 - 5t, characterized in that that it can be used for both externally toothed and internally toothed products can. 7. Adjusting mechanism according to claims 1-6, characterized in that it is due to the elastic design kept largely free of play by means of a bore in the planetary gears 26 while saving weight can be. 8. Adjusting mechanism according to one or more of the preceding Claims, characterized in that the direction of force and thus the pressure angle of the The teeth remain constant during operation. BATH ORIGINAL