DE102004019468B4 - Drive unit for a vehicle seat - Google Patents

Abstract

Drive unit (10) for a vehicle seat, in particular for a motor vehicle seat, with a plurality of motors (12), which are combined to form a multi-motor (72) with a common output, and at least one gear stage (14) coupled to the output of the multi-motor (72). In a particular situation, in a particular situation, the multi-motor (72) outputs a higher power due to a change in the circuit of the combined motors (12).

Description

The The invention relates to a drive unit for a vehicle seat.

such Drive units are for motorized adjustable vehicle seats used to adjust individual components relative to each other to an optimal seating position for the occupant to reach. They are both brush-commutated and electronic Commutated motors known. By means of the gear stage, the Reduced speed and at the same time the output torque can be increased.

Of the Invention is based on the object, a drive unit of to improve the type mentioned above. This object is achieved by a drive unit with multiple motors that become a multi-motor combined with a common output, and with at least a coupled to the output of the multi-motor gear stage, in a particular situation, the multi-motor due to a change the circuit of the combined engines gives a higher power, solved. Advantageous embodiments are the subject of the dependent claims.

By combining several motors into one multi-motor can do this adapted to different performance requirements and be space-saving and ergonomically favorable. The application area such a drive unit with a multi-motor is not on a vehicle seat limited. Rather, an assignment can also take place elsewhere Vehicle done, for example, in a window or a Sunroof.

In structurally simple way, for example, the motors are in parallel motor shafts a common engine mount arranged, with a common intermediate the output of the multi-motor forms. With the possibility The modular power definition can also be extremely high in the short term Services are retrieved. For example, if the motors of the Multimotors are normally connected in series, so they can in a special situation to be paralleled to due the higher one Tension a higher one Deliver performance. Such a situation is for example one Crash or an imminent crash of a vehicle.

Around mechanically connect the outputs of the motors of the multi-motor, it is advantageous if each engine, for example with a motor pinion, drives a common idler. For locking one of the Output side introduced torque can be provided, for example, that this Intermediate wheel form-fitting or frictionally engaged is lockable. As individual drive units for the multimotor come in simplest case known brush commutated Motors are used, however, are also very different types provided by electronically commutated motors.

electronic commutated, brushless Motors offer high electromechanical efficiency at the same time low installation space and low noise level. Several engines can with the associated Electronics without significant additional effort in their speed or Position synchronized with each other. The type of commutation offers the possibility, to detect a blocking condition, a maximum allowable blocking moment electrically define and monitor the temperature, and thus one against brush motors higher Energy density of the electromagnetic transducer to realize what a significant reduction in space and weight allowed. The integration The control electronics in the engine offers advantages in detection of block situations, the evaluation of existing sensors and the Coordination between electronic function and device to be driven, for example, when recording or programming parameters the motor behavior.

With two rotors with different speed and / or direction of rotation rotate, a relative movement can be generated, which is opposite to a Absolute value of the speed is low and continues from the gear stage can be suppressed to increase the output torque. The different speed and / or direction of rotation of the rotors is in a structurally simple manner preferably achieved in that the rotors have a different number of poles with each other, in turn, preferably different from the number of stator poles is, so too the speed of the rotors of the speed of the magnetic field of the stator differs.

One relationship the stator pole to the poles of the rotor, that of 2: 3 and 3: 2 different is possible Speed and / or rotational direction differences, which - for example by means of two rotors - one small relative motion can be generated, leading to a speed reduction with simultaneous increase the output side torque leads.

For low-noise or low-noise engine running, low heat generation, and low power consumption, the stator is preferably electronically commutated, while the rotors preferably carry permanent magnets as poles. It contributes in the circumferential direction of the Stators preferably every second stator pole a coil to close the magnetic flux across the adjacent stator pole. Stator and rotors may be arranged with respect to the central axis in radial sequence or axial sequence (pancake). To generate the different speeds, the poles of stator and rotors may differ by two, for example.

Of the Motor is preferably selectable from several engine variants, in the radial design for example, an internal rotor, an external rotor or a double rotor motor. Used in conjunction with one of several gear stage types Gear stage, with several gear stages in a row can be switched is a modular system available that with few modules a big Number of drive units manages to meet the different requirements cover.

A Training the gear stage as a differential gear, which under Utilization of two different speeds and / or directions of rotation Movement of an output generated about an axis, particularly small relative movements can be generated be that allow a low speed at the output. The can two different speeds and / or directions of rotation from the engine be routed to the gear stage or from the gear stage itself generated and by fixing a component with such Speed can be tapped at the other component as an output.

The Gear stage is preferably to a motor with a preferably electronically commutated stator and at least one magnetically with the stator interacting, rotating around the axis, carrying permanent magnets Rotor connected. Such a motor is quiet and runs with low friction. The gear stage can be in a friction wheel design with hollow and / or solid rollers or a gear design realized be, with the former design easier to manufacture is, with hollow rollers is also weight-reducing, and at the same time as a warehouse for can serve a rotor.

Next the electromechanical efficiency of the engine is for overall efficiency the drive unit also the efficiency of the gear stage of Meaning, why coaxial, fully symmetrical gearbox designs with one as possible small number of individual bearings, especially in friction wheel design without any additional storage but rather with its own storage function, are preferred.

The Gear stage can be used as single-stage planetary differential gear with a sun gear, a set of planet wheels or wheels and be formed of a ring gear, wherein the sun gear and the ring gear rotatably connected to each rotor of the engine while a the planetary rollers or wheels supporting web serves as an output.

The Gear stage can also be used as a multi-stage planetary differential with one or more sun gears, one or more sentences inner planetary rollers, one or more sets of outer planetary rollers and one or more outer rings be formed, which is arranged concentrically to the central axis are, with the sun gears or the outer rings in terms of the axis are arranged axially adjacent. Different outer diameter the two sun wheels or different inner diameter of the two outer rings to lead too low speed differences.

The Gear stage can also be used as single-stage planetary differential with one or more sun gears, a set of preferably ungestufter planetary rollers and one or several ring gears be formed, which is arranged concentrically to the central axis are, with the sun gears or ring gears in terms of the axis are arranged axially adjacent. Different elasticities and different outer diameter the two sun wheels or different inner diameter of the two ring gears lead to low speed differences.

The said speed differences can, for example tapped by the two said adjacent transmission elements with different diameter of a fixed housing and one with the output connected is. In the execution with two outer rings is the housing fixed in contact with the stator while serving as a drive sun gear rotatably with a rotor of the Motors is connected.

Around on the one hand a bias to cohesion and centering apply the gear stage and on the other hand compensate for tolerances, have the ring gear or the outer ring preferably an elastic metal ring and a metal ring receiving elastomer bed on. A tallring bed with the Me receiving and axially locking bracket is preferably with a Bell connected to the trained as a hollow shaft output.

With a manual transmission, the direction of rotation of the output can be selectively switched without having to change the direction of rotation of the motor. This greatly simplifies the electronics for the engine. For switching is in a simple to manufacture embodiment, preferably by a Switching coil defined electromagnet provided, which cooperates with two repulsive permanent holding magnets, which are geometrically coupled to two adjacent, similar transmission elements to determine these frictionally or positively.

The Gear stage is preferably made of several gear stage types selectable. In conjunction with one of several engine variants selectable Motor is a modular system available that with few modules a big Number of drive units manages to meet the different requirements cover.

The Drive unit drives in the vehicle seat preferably an adjuster at. The drive unit is preferably in a load-absorbing Integrated transmission, the load-bearing transmission preferably a rotor directly or indirectly stores. The trained so adjuster has the advantage that separate transmission elements between the drive unit and the load-bearing transmission, For example, a poor efficiency worm gear or the like, as well as separate bearing elements for the rotor are dispensable. If in addition a continuous play-free storage of the rotor over the gear is up to the load-bearing gear, be the running noise greatly reduced.

With two drive units for two coupled, single adjuster does not have a transmission element and no extra Stage to the spatial Laying the same be provided. In addition, the load-bearing transmission must each adjuster only half of the total torque as a blocking moment record, which in addition to the elimination of the transmission element the design effort for this requirement for every load-bearing transmission significantly reduced.

One The preferred adjuster is a versatile rotary adjuster designed, in particular as a self-locking geared fitting with a first fitting part and a second fitting part, which by an eccentric driven by the drive unit rotate relative to each other. The fittings can each have a molded collar or an attached sleeve by means of which they store the eccentric and / or at least a part of the drive unit, preferably the entire drive unit including electronics for the Commutation, record. The eccentric, preferably on one the collar pulls or sleeve is stored, is preferably formed by a drivable Driving segment, two curved wedge segments, between the narrow sides the takeaway segment seizes play, and one between the each other facing broad sides of the wedge segments comprehensive and this in the circumferential direction apart oppressive Spring for game release.

Around preferably takes little components, takes place the integration of engine, gearbox and load-bearing gear, In particular geared fitting, preferably so that the components fulfill several functions at the interfaces. So can a collar with the housing firm to be held first outer ring or ring gear be connected or form this or this. The Mitnehmersegment can be formed at the output of the gear stage or be attached, in particular on the second outer ring or ring gear.

in the The following is the invention with reference to an illustrated in the drawing Embodiment with various engine variants, gear stage types and respective Modifications to this closer explained. Show it

1 a schematic diagram of the embodiment,

2A a first engine variant,

2 B a second engine variant,

2C a third engine variant,

3A a first gear stage type in friction wheel design,

3B the first gear stage type in gear design,

4 a schematic partial view of a second gear stage type as viewed in the direction of arrow IV 5 .

5 a section along the line VV in 4 .

6 an enlarged view of 5 .

7 a schematic view of a third gear stage type,

8th a section along the line VIII-VIII in 7 .

9 an end view of a switchable gear stage,

10 a side view too 9 .

11 a section along the line XI-XI of 9 .

12 a modification of the gear stage of 9 .

13A a locking device for the motor for blocking the output side introduced torques in the blocking state,

13B the locking device of 13A with starting engine,

14 a multi-motor with the engine shafts still empty,

15 the common output of the individual motors of the multi-motor,

16 the electrical connection of the motors of the multi-motor, and

17 an alternative connection of the individual motors in two states.

A drive unit 10 has an engine 12 and an output side of the engine 12 provided gear stage 14 on. The motor 12 is an electronically commutated motor with a stator 16 whose stator poles 18 are arranged in a star shape about an axis A. In the 2A to 2C Axis A perpendicular to the plane of the drawing defines the following directions in cylindrical coordinates. On every second of the twelve stator poles 18 is a coil 20 wrapped, with the coils 20 from a not shown, in the engine 12 integrated, DC-powered electronics periodically and temporally staggered to each other are energized to produce a spatially orbiting magnetic field.

In three different engine variants is the engine 12 as an internal rotor motor with a radially inside the stator 16 arranged inner rotor 22 (first motor variant), as an external rotor motor with a radially outside of the stator 16 arranged outer rotor 24 (second engine variant) or as a double rotor engine, short duo engine, with an inner rotor 22 and an outer rotor 24 (third engine variant) provided. In all cases, inner rotor rotate 22 or outer rotor 24 about the axis A and carry along the stator 16 facing peripheral surface permanent magnets 26 , which are alternately poled in the circumferential direction. All permanent magnets used in the present application 26 preferably have a high permeability, for example by containing metals from the group of rare earths. An inner yoke ring 28 , which in the first and third engine variant of the inner rotor 22 and in the second engine variant, the stator 16 is assigned, and an outer yoke ring 30 , which at the first engine variant the stator 16 and in the second and third engine variants, the outer rotor 24 is assigned to close the magnetic flux through adjacent stator poles 18 , The two return rings 28 and 30 may optionally at the same time as a carrier of the permanent magnet 26 serve. The outer rotor 24 delivers due to the at a larger radius (compared to the inner rotor 22 ) effective magnetic forces a larger torque. All three engine variants are preferably formed in a hollow shaft design, ie, the area around the axis A is released.

The number of permanent magnets 26 is chosen so that its ratio to the number of stator poles 18 not equal to 2: 3 or 3: 2, which causes the rotation of inner rotor 22 or outer rotor 24 from the rotation of the magnetic field in the stator 16 differs. In the present case, the inner rotor 22 ten permanent magnets 26 and the outer rotor 24 fourteen permanent magnets 26 on. According to the different number of permanent magnets 26 In the case of the third engine variant (duo engine), the inner rotor rotates 22 and the outer rotor 24 in this case with different speeds (5: 7) and also in opposite directions of rotation, which is indicated in the drawing by arrows.

Instead of the radial structure of the engine can also be realized an axial structure be, d. H. the rotors (pancake) and the stator are axial arranged one behind the other.

The gear stage 14 serves to increase the speed of the motor 12 to be reduced with simultaneous translation of the engine 12 delivered torque. The gear stage 14 is designed as a differential gear, wherein various types are described below. For each type exists both a design as a gear planetary differential gear with flat, toothed planet gears and a preferred embodiment as a friction planetary differential gear with cylindrical, smooth planetary rollers, which - as the sun - can be hollow or solid. A hollow shaft design of the gear stage 14 in which the area around the central axis A remains free is preferred.

The first gear stage type is a one-stage planetary differential gear, which will be described first in the friction wheel design. The gear stage 14 Aligns with the central axis A of the engine 12 , Around the axis A is a sun gear 32 arranged on the peripheral surface of three planetary rollers 34 roll along, which in turn from a ring gear 36 be enclosed. The ring gear 36 provides for a radial preload and thus for a good rolling of the planetary rollers 34 without slippage. An annular bridge 38 carries on axial pin the planetary rollers 34 ,

The preferred combination of this first gear stage type is done with the third engine variant, the duo engine, but can also be done with the other engine variants, including brush-commutated motors. The inner rotor 22 is with the sun wheel 32 rotatably connected while the outer rotor 24 with the ring gear 36 rotatably connected. The jetty 38 serves as the output of the drive unit 10 , The respective diameters are in their dimensions on the speeds, torques and directions of rotation of the rotors 22 and 24 Voted. Preferably, the axial lengths of the sun gear 32 , Planetary roles 34 and ring gear 36 chosen so large that by means of the gear stage 14 a storage of the inner rotor 22 and the outer rotor 24 relative to the stator 16 he follows.

The gear design is true to the surface texture of the components with the friction wheel design, which is why the reference numerals of the corresponding components are supplemented by an apostrophe. sun 32 ' , Planetary gears 34 ' and ring gear 36 ' are each serrated, but are in the same way with the engine 12 coupled and perform the same relative movements, the web 38 again as an output serves.

The second gear stage type is a multi-stage planetary differential gear, which in turn is described in the radially layered friction wheel design, but is also possible in a gear design. Likewise, massive and / or hollow components can be used again. Around the axis A is again a sun gear 32 arranged on the peripheral surface of a layer of inner planetary rollers 34 is arranged. Inserted in each space are arranged axially one behind the other a first outer planetary roller 40 and a second outer planetary roller 42 , each about half the axial length of an inner planetary roller 34 have, wherein the second outer planetary roller 42 one opposite the first outer planetary roller 40 has slightly smaller diameter, which can be realized in a simple manner, for example, by the use of cylindrical rollers on the one hand from the metric and on the other hand from the imperial standard series. Instead of the cylindrical shape and a different shape for the rolling elements can be used.

One of the first outer planetary rollers 40 radially outwardly enclosing the first outer ring 44 and one of the second outer planetary rollers 42 radially outside surrounding second outer ring 46 , which each serve as a ring gear, span the planetary rollers in the radial direction 40 . 42 and 34 over all contact points at the same time to the sun wheel 32 out in front. This bias of the two radially stacked rows of rollers ensure that all roles support each other and a concentric radial symmetrical arrangement results, which is without slippage, so that a high efficiency of the gear stage 14 results. A web and thus an inner bearing of the planetary rollers is not required, but not excluded. The sun wheel 32 can be frontally provided with radially outwardly facing ribs to secure the planetary rollers in the axial direction, which is also possible with the other types of gear stages.

The two outer rings 44 and 46 are basically the same structure, so that in the following only the first outer ring 44 is described. The first outer ring 44 has an elastic metal ring 48 made of steel, which on its radially inner side to the first outer planetary rollers 40 is applied and formed with a smaller inner diameter than the geometric arrangement of the enclosed rollers required to apply the bias. On the radially outer side and on the two axial end faces of the metal ring 48 in an elastomer bed 50 of the first outer ring 44 , The metal ring 48 and the plastic elastomer bed 50 together ensure a very even contact pressure. In addition, the elastomer bed insulates 50 the running noise and mitigates torque surges. The described two-part construction of the first outer ring 44 can also be at the ring gear 36 respectively. 36 ' be implemented of the first gear stage type. For axial securing of the first outer ring 44 with his metal ring 48 and his elastomer bed 50 is a holder 52 provided, which is designed in two parts for the purpose of assembly and the elastomer bed 50 radially outward and with two Borden frontally overlaps, which is also possible with the other types of gear stages.

For a rotational symmetry, which contributes to the avoidance of running noise, are the metal ring 48 and the elastomer bed 50 preferably formed continuously in the circumferential direction, but they can also be slotted or split, in particular slotted arrow-shaped, for example, if they rotatably with the holder 52 should be connected. In the gear stage 14 Dissipate the resulting heat is the elastomer bed 50 preferably good thermal conductivity, for example by incorporation of metallic or other thermally conductive fibers or filling of cavities or cutouts with a thermally conductive material. Between the metal ring 48 and the elastomer bed 50 can also be provided a thermal grease.

The small diameter difference between the first outer planetary rollers 40 and the second outer planetary rollers 42 and as a result, the inner diameter of the first outer ring 44 and the second outer ring 46 causes a difference in the speeds of the two outer rings 44 and 46 , This small speed difference is for a large reduction (for example, 200) of the gear stage 14 exploited when connected to the engine 12 connected.

The preferred combination of this second gear stage type is carried out with the first or second engine variant, but can also be done with other engine variants, including brush-commutated motors. The first outer ring 44 , more precisely, its holder 52 , For example, is fixed to the housing, ie with the stator 16 connected. The sun wheel serving as drive 32 comes with the inner rotor 22 (or the outer rotor 24 ), while the second outer ring 46 as a downforce 54 serves. Here, for example, designed as a hollow shaft output shaft with a bell-shaped end piece on the second outer ring 46 attached, more precisely to the holder 52 , In the present case, the second outer ring rotates 46 in the same direction to the sun wheel 32 , The selected structure of the second gear stage type makes a separate storage of the sun gear 32 and thus the inner rotor 22 (or outer rotor 24 ) and the second outer ring 46 , ie the output 54 dispensable, but does not exclude it. The storage of the inner rotor 22 (or outer rotor 24 ) in the gear stage 14 However, has the advantage that it is free of play and thus a noiseless running of the inner rotor 22 (or outer rotor 24 ) causes.

In a modified version of the second gear stage type is the (smaller) second outer ring 46 fixed to the housing and the (larger) first outer ring 44 the output, which is an opposite rotation of sun gear 32 and first outer ring 44 causes. With optional fixing of outer rings 44 and 46 on the housing and a resulting change of the output, for example by means of two latch systems or a circuit described in more detail later, a reversal of the direction of the output while maintaining the same direction of rotation of the sun gear 32 be achieved. The required electronics of the engine 12 can then be built much simpler, what the production of the engine 12 simplified.

Of the second gear stage type can be further modified by a other number of sets of rolls. General can one or more, axially successively arranged sun gears, a same Number of inner planetary rollers in a corresponding axial arrangement, optionally a set of central planetary rollers for synchronization, one or more sentences arranged axially behind one another, outer planetary rollers and a same number of outer rings be provided in a corresponding axial arrangement. The little one Speed difference is in accordance with the described manner between tapped two adjacent transmission elements. It is also conceivable instead of a sun gear plus a set of inner planetary rollers only a sun gear with a correspondingly large diameter, which directly on the next outer set planetary rolls rolls, and / or instead of a set of outer planetary rollers plus one outer ring only one outer ring with correspondingly small diameter, which directly on the next inner Set of planet rolls rolls to use.

The third gear stage type is again a single-stage planetary differential gear, which in turn is described in a radially layered friction wheel design, but also in a gear design is possible. The gear stage 14 Aligns with the central axis A of the engine 12 , Around the axis A is a sun gear 32 arranged on the peripheral surface of three planetary rollers 34 roll along. At about half of their axial length are the ungestuften planetary roles 34 from an annular first ring gear 36 enclosed, which has a low elasticity, that is relatively stiff. On the other half of their axial length are the planetary rollers 34 from a second ring gear 56 enclosed, which has a higher elasticity and a smaller inner circumference than the first ring gear 36 having. Both together conditionally deviates from the circular shape, by the system to the planetary rollers 34 slightly triangular shape of the second ring gear 56 , which is slightly exaggerated in the drawing and changes dynamically during operation. The elasticity differences are achieved by a suitable choice of material.

The two ring gears 36 and 56 provide a radial preload with high contact pressure and thus for a good rolling of the planetary rollers 34 without slippage, with the sun gear 32 compensates for the radial forces. With a drive via the sun gear 32 instead of a bridge, the ratio of the internal ring gears for a ratio of 200 need not be 200/199, but can be chosen more generous and thus less tolerable. In addition or instead of the sun wheel 32 For example, a web which supports the planetary rollers can be provided in the same way as the first gear stage type as a drive or a bearing cage fixing the planetary rollers. It may be provided in a modified version, two axially successively arranged sun gears of different elasticity in com bination with a ring gear or other combinations of continuous or divided sun gears and ring gears of different elasticity. The planetary rollers can also be stepped.

To the deformation of the second ring gear 56 on a rigid shaft for the output 54 to transfer or alternatively support the housing fixed, is the second ring gear 56 from an elastomer bed enclosing this radially outside 50 added, For example, a rubber ring, which in turn radially within a holder 52 is arranged. The elastomer bed 50 can also be used as a further component of a ring gear having a metal ring 56 be considered. Instead of the elastomer bed 50 but also elastic spokes for the second ring gear 56 or an axial or radial tap, optionally with the interposition of a pot with deformable walls or a damper elements having perforated disc, be provided. The slightly non-uniform movement of the ring gear 56 is preferably not or only slightly compensated.

The preferred combination of this third gear stage type is done with the first or second engine variant, but can also be done with other engine variants, including brush-commutated engines. The first ring gear 36 For example, is fixed to the housing, ie with the stator 16 connected. The sun wheel serving as drive 32 comes with the inner rotor 22 (or the outer rotor 24 ), while the second ring gear 56 as a downforce 54 serves. Here, for example, designed as a hollow shaft output shaft with a bell-shaped tail on the second ring gear 56 attached, more precisely to the holder 52 , The respective diameters must be at most in the same orders of magnitude, so that there is a further translation option by the choice of the diameter. Preferably, the axial lengths of the sun gear 32 , Planetary roles 34 and ring gear 36 chosen so large that by means of the gear stage 14 a storage of the inner rotor 22 and the outer rotor 24 relative to the stator 16 he follows. With the selected structure of the third gear stage type is also a separate storage of the sun gear 32 and thus the inner rotor 22 (respectively.

outer rotor 24 ) and the second ring gear 56 , ie the output 54 dispensable, but does not exclude it.

The gear stage 14 can be designed as a manual transmission, by means of which at the same direction of rotation of the engine 12 the direction of rotation of the output 54 is switchable, which is explained in more detail below with reference to the second gear stage type. As with the second gear stage type, sits on the sun gear 32 a set of inner planetary roles 34 , on which in turn a set of first planetary roles 40 is arranged, that of a first outer ring 44 is held biased, and axially offset therefrom a set of second planetary rollers 42 from a second outer ring 46 is kept biased. The second outer ring 46 forms part of the output 54 , The axial length of the inner planetary rollers 34 is chosen so that axially adjacent to the first outer ring 44 on the second outer ring 46 opposite side a third outer ring 58 is arranged, which with bias the inner planet rolls 34 directly includes. The outer diameter of the first outer ring 44 and the third outer ring 58 at least approximately agree.

A wrap 60 is supported in the middle of the housing and otherwise with a part of their windings around the first outer ring 44 and with another part of their turns around the third outer ring 58 looped. At the two free ends of the wrap spring 60 is in each case a permanent magnet as a holding magnet 61 arranged, wherein the mutually facing poles of the two holding magnets 61 repel each other. The holding magnets 61 preferably have a high permeability, for example by containing metals from the group of rare earths. Between the two holding magnets 61 is a core 62 made of soft iron, around which an energizable with optional polarity switching coil 63 is wound.

In the de-energized state of the switching coil 63 are both holding magnets 61 at the core 62 which closes the magnetic flux locally. Both outer rings 44 and 58 and thus the gear stage 14 are determined by it. With the exception of the current supply of the coils 20 of the stator 16 is also the switching coil 63 energized. Depending on the current direction, one of the two holding magnets 61 still attracted and the other repelled. The latter opens this side of the wrap 60 , whereby the appropriate outer ring 44 or 58 will release. Depending on which outer ring 44 or 58 is determined results in the same direction of rotation of the motor 12 and with it the sun wheel 32 from the determination of the direction of rotation of the second outer ring 46 and thus the downforce 54 ,

In addition to the described manual transmission with frictional locking device, a manual transmission with a positive solution is conceivable in a modified version. As in 12 shown, the holding magnets 61 For example, on ratchets 64 be arranged, which lock the respective teeth bearing outer rings switchable. The operation is as described above.

The locking device can also serve to lock torques in the idle state, the output from the output 54 be initiated. Such a lock does not need at the gear stage 14 It can also be done between engine 12 and gear stage 14 be provided.

As in 13A is shown, for example, the output shaft of the engine 12 on the one hand with a motor pinion 66 provided, which in one with the sun wheel 32 connected intermediate wheel 67 engages, and on the other hand frictionally with a Steuerschei be 68 with two cams 68 ' connected. At rest, two spring-loaded ratchets engage 64 at least approximately positively in the intermediate 67 and lock this, in particular against the output side introduced torques. With the onset of the rotary motion of the motor 12 becomes the control disk 68 rotated, with the cams 68 ' in contact with control contours 64 ' the pawls 64 come and thereby the ratchets 64 from the idler 67 dig out, as in 13B shown. The intermediate wheel 67 can now be driven freely, the frictional engagement with the control disc 68 is preferably canceled. In a preferred embodiment, the control disk 68 not frictionally engaged with a rotating axis, but rotatably with the non-rotating motor part and this in turn rotatably supported by a small angular range to the housing. As a result of the torque between the motor pinion 66 and so connected tax disc 68 This now twists automatically when the engine is switched on 12 and thus controls the ratchets 64 also automatically off. The type of motor commutation is irrelevant for this locking device. The locking can also be done in a frictional execution.

The types of gear stages described can be found in the drive unit 10 be used in various combinations. In addition to the previously described combinations of individual motors 12 and associated individual gear, the outputs then still together with each other to a multi-motor described below 72 combined, is also the combination of gearless single motors with individual pinions 66 and downstream, common gear stage feasible.

In a motor carrier 70 are several engine shafts 71 each provided around a central bearing for a common idler 67 are arranged. The in the engine shafts 71 introduced engines 12 , for example, three pieces, then grip with engine sprockets 66 in this intermediate, which - as described above - can be locked against an output side torque introduced. The multimotor so formed 72 is then by means of the intermediate wheel 67 to a gear stage 14 coupled, for example, to a sun gear 32 one of the gear stage types described above. The type of motor commutation is irrelevant here.

The mechanically parallel connected motors 12 are usually operated electrically in series in series. In 16 this is based on two engines 12 represented and expandable in a conventional manner to a plurality of motors. Between the engines 12 are one or more relays 74 intended, including electronic equivalent circuits are to be understood. Normally, due to the series connection, the operating voltage is distributed at least approximately equally to the existing motors 12 ,

In certain situations, it may be desirable for the drive unit 10 gives a higher speed and / or a higher torque. Such a situation is - in the case of use of the drive device 10 in a vehicle - a crash. The of the drive unit 10 driven devices should then occupy certain positions as quickly as possible in order to increase occupant protection, for which it is accepted that the drive unit 10 possibly subsequently unusable. Another particular situation would be a quick adjustment of one or more adjusters of a vehicle seat over a large area, such as folding the backrest (free pivoting) in combination with a longitudinal adjustment to facilitate access to a rear row of seats (easy entry).

In the present embodiment of the multi-motor 72 be through an unillustrated vehicle electronics, the existing relay 74 operated so that the series circuit is canceled and the motors 12 be switched in parallel. Increasing the applied voltage increases the power consumption of the individual motors 12 and the multi-motor 72 overall, at least in the short term, preferably until the driven devices have reached the desired positions. Thermodynamic effects can be neglected due to the short operating times. The control of the relays 74 can - in the case of application for a crash situation - take place even before the actual crash, if the existing crash sensors of the vehicle electronics provide indications of an imminent crash. The solution is thus presave-capable.

In case of operation of the multi-motor 72 with a star connection of the coils 20 there is the possibility, as in 17 indicated switching in the special situation, the operation in a star circuit with center tap, in order to reduce the effective resistance and also to increase performance in the short term.

The current supply with the star connection is also particularly well suited for a combination with the third engine variant and a locking device. One of the two rotors according to the third engine variant is mechanically blocked when the special situation by means of the locking device. The downstream gear stage 14 then acts as a differential gear with higher translation (less lesser reduction). The other rotor runs after switching to the center tap because of the lower resistance with height rer power consumption, what then ultimately the desired increase in output power 54 causes.

The inventively provided drive unit 10 is in this case for driving a adjuster 80 used within a vehicle, the drive unit 10 can also be used elsewhere. The adjuster 80 has in the general case two relatively movable components, between which the drive unit 10 with their downforce 54 acts. The low speed of the output 54 delivers a large torque. It can be means for implementing the rotational movement of the output 54 in a linear movement in the adjuster 80 be provided. It can also be used for any setting direction of the adjuster 80 be provided a separate drive unit. Examples of the adjuster 80 In the field of vehicle seats, a backrest inclination adjuster, in particular in the form of a self-locking transmission fitting, a seat height adjuster acting between two transmission links of a four-bar linkage, a seat incline adjuster pivoting the front edge of a seat cushion, or a seat longitudinal adjuster longitudinally traversing the vehicle seat. The adjuster 80 but can also be a window or a mirrors adjuster.

In many applications, two similar, individual adjuster act 80 together to move a component together. For example, in vehicle seats usually on both sides of the vehicle seat the same, individual adjuster 80 present, which are coupled in a known solution in pairs by means of a rotatable transmission rod and synchronized. With the drive unit according to the invention 10 , which requires very little space, can for each individual adjuster 80 a couple own drive unit 10 be provided, which then for example by means of electronics for electronic commutation of the motor 12 or - in the case of a vehicle seat - are synchronized via the rigidity of the structure of the vehicle seat.

10

drive unit

12

engine

14

gear stage

16

stator

18

stator

20

Kitchen sink

22

inner rotor

24

outer rotor

26

permanent magnet

28

Interior return ring

30

Outside return ring

32 32 '

sun

34

(inner) planetary roller

34 '

planet

36 36 '

(First) ring gear

38

web

40

first outer planetary roller

42

second outer planetary roller

44

first outer ring

46

second outer ring

48

metal ring

50

elastomer bed

52

bracket

54

output

56

second ring gear

58

third outer ring

60

wrap

61

holding magnet

62

core

63

switching coil

64

toothed pawl

64 '

control contour

66

pinion

67

idler

68

control disc

68 '

cam

70

engine support

71

motor shaft

72

Multi engine

74

relay

80

adjuster

A

axis

Claims (65)

Drive unit ( 10 ) for a vehicle seat, in particular for a motor vehicle seat, with a plurality of motors ( 12 ) leading to a multi-motor ( 72 ) are combined with a common output, and at least one to the output of the multi-motor ( 72 ) coupled gear stage ( 14 ), where in a particular situation the multimotor ( 72 ) due to a change in the circuit of the combined engines ( 12 ) gives a higher performance. Drive unit according to claim 1, wherein the motors ( 12 ) in engine shafts ( 71 ) of a motor carrier ( 70 ) of the multi-motor ( 72 ) are arranged. Drive unit according to claim 1 or 2, wherein a common intermediate wheel ( 67 ) the output of the multi-motor ( 72 ). Drive unit according to claim 3, wherein each motor ( 12 ) with a motor pinion ( 66 ) the intermediate wheel ( 67 ) drives. Drive unit according to claim 3 or 4, wherein the intermediate wheel ( 67 ) is positively lockable and / or frictionally lockable. Drive unit after one of the preceding the claims, wherein at least one of the plurality of motors ( 12 ) is electronically commutated. Drive unit according to one of the preceding claims, wherein the engine ( 12 ) a stator ( 16 ) and at least one with the stator ( 16 ) magnetically interacting rotor (A) rotating around an axis (A) 22 . 24 ) having. Drive unit according to one of the preceding claims, wherein the motors ( 12 ) of the multi-motor ( 72 ) are normally connected in series. Drive unit according to claim 8, wherein the motors ( 12 ) of the multi-motor ( 72 ) are switchable in parallel in the particular situation. Drive unit according to one of claims 7 to 9, wherein in a particular situation the engine ( 12 ) due to a change in the circuit of the stator ( 16 ) gives a higher performance. Drive unit according to one of the preceding claims, wherein the stator ( 16 ) of the motor ( 12 ) with its coils ( 20 ) is normally connected with a star connection. Drive unit according to one of claims 8 to 11, wherein in the particular situation a center tap of the star connection he follows. Drive unit according to one of claims 10 to 12, wherein in the particular situation one of the rotors ( 22 . 24 ) is blocked. Drive unit according to one of claims 8 to 13, with such a special situation a crash, an imminent Crash or a quick setting is. Drive unit according to one of claims 8 to 14, wherein two rotors ( 22 . 24 ) are provided which rotate at different speed and / or direction of rotation. Drive unit according to claim 15, wherein the rotational speed of the rotors ( 22 . 24 ) of the speed of the magnetic field of the stator ( 16 ) deviates. Drive unit according to claim 15 or 16, wherein the rotors ( 22 . 24 ) with each other a different number of poles ( 26 ) exhibit. Drive unit according to one of claims 8 to 17, wherein the number of poles ( 26 ) of the rotors ( 22 . 24 ) of the number of stator poles ( 18 ) is different. Drive unit according to one of claims 8 to 18, wherein the ratio of the stator poles ( 18 ) to the poles ( 26 ) of the rotor ( 22 . 24 ) is different from 2: 3 and 3: 2. Drive unit according to one of claims 8 to 19, wherein the rotors ( 22 . 24 ) Permanent magnets ( 26 ) as a pole. Drive unit according to claim 20, wherein the permanent magnets ( 26 ) Contain metals from the group of rare earths. Drive unit according to one of claims 8 to 21, wherein in the circumferential direction of the stator ( 16 ) exactly every second stator pole ( 18 ) a coil ( 20 ) wearing. Drive unit according to one of claims 8 to 22, wherein the stator ( 16 ) and the rotors ( 22 . 24 ) are arranged in radial or axial sequence with respect to the axis (A). Drive unit according to claim 23, wherein a radially inside of the stator ( 16 ) arranged inner rotor ( 22 ) and / or a radially outside of the stator ( 16 ) arranged outer rotor ( 24 ) is provided. Drive unit according to claim 17, 18 and 24, wherein the number of poles ( 26 ) of the inner rotor ( 22 ) by two less than the number of stator poles ( 18 ) and / or the number of poles ( 26 ) of the outer rotor ( 24 ) by two greater than the number of stator poles ( 18 ). Drive unit according to one of the preceding claims, wherein the engine ( 12 ) is formed in a hollow shaft design. Drive unit according to one of the preceding claims, wherein the engine ( 12 ) is selectable from several engine variants. Drive unit according to one of the preceding claims, wherein the gear stage ( 14 ) is designed as a differential gear which, taking advantage of two different speeds and / or directions of rotation, a movement of a driven ( 54 ) is generated about an axis (A). Drive unit according to one of claims 8 to 28, wherein the gear stage ( 14 ) at least one rotor ( 22 . 24 ) stores. Drive unit according to one of the preceding claims, wherein the gear stage ( 14 ) is realized in a friction wheel design with hollow and / or solid rollers. Drive unit according to one of claims 1 to 30, wherein the gear stage ( 14 ) is a gear design. Drive unit according to one of the preceding claims, wherein the gear stage ( 14 ) as at least one-stage planetary differential gear with one or more sun gears ( 32 ; 32 ' ), at least one set of planetary rollers ( 34 ) or wheels ( 34 ' ) and one or more ring gears ( 36 . 36 ' . 56 ) or outer rings ( 44 . 46 ) is trained. Drive unit according to claim 32, wherein the sun gear ( 32 . 32 ' ) and the ring gear ( 36 . 36 ' ) rotatably with one rotor each ( 22 . 24 ) of the motor ( 12 ) are connected. Drive unit according to claim 32 or 33, wherein a web ( 38 ) the planetary rollers ( 34 ) or wheels ( 34 ' ) wearing. Drive unit according to claim 34, wherein the web ( 38 ) as an output ( 54 ) serves. Drive unit according to claim 34, wherein the web ( 38 ) serves as a drive. Drive unit according to one of claims 32 to 36, wherein two sun gears ( 32 ) and / or two ring gears ( 36 . 56 ) have different elasticities. Drive unit according to one of claims 32 to 37, wherein the sun gears ( 32 ) and / or outer rings ( 44 . 46 ) are arranged concentrically to the axis (A). Drive unit according to one of claims 32 to 38, wherein two sun gears ( 32 ) or two outer rings ( 44 . 46 ) or two ring gears ( 36 . 56 ) are arranged axially adjacent to the axis (A). Drive unit according to one of claims 32 to 39, wherein two sun gears ( 32 ) different outer diameters or outer circumferences and / or two outer rings ( 44 . 46 ) different inner diameter and / or two ring gears ( 36 . 56 ) have different inner circumferences. Drive unit according to claim 40, wherein one of the two adjacent gear elements with different diameter or elasticity or inner circumference is fixed to the housing and one with the output ( 54 ) or forms this. Drive unit according to claim 41, wherein the sun gear ( 32 ) rotatably with a rotor ( 22 . 24 ) of the motor ( 12 ), an outer ring ( 44 ) or a ring gear ( 36 ) with the stator ( 16 ) and an outer ring ( 46 ) or a ring gear ( 56 ) with the output ( 54 ) or forms this. Drive unit according to one of claims 32 to 42, wherein the ring gear ( 36 . 36 ' ) or the outer ring ( 44 . 46 ) an elastic metal ring ( 48 ) and a metal ring ( 48 ) receiving elastomer bed ( 50 ) or the ring gear ( 56 ) yourself the metal ring ( 48 ) and in the elastomer bed ( 50 ) is recorded. Drive unit according to claim 43, wherein a holder ( 52 ) the elastomer bed ( 50 ) with the metal ring ( 48 ) and secures axially. Drive unit according to claim 44, wherein a bell of the output formed as a hollow shaft ( 54 ) with the bracket ( 52 ) connected is. Drive unit according to one of claims 32 to 45, wherein a slight non-uniform movement of the ring gear ( 56 ) is only partially compensated. Drive unit according to one of claims 32 to 46, wherein the planetary rollers ( 34 ) or wheels ( 34 ' ) are formed ungraded. Drive unit according to one of the preceding claims, wherein the gear stage ( 14 ) is formed in a hollow shaft design. Drive unit according to one of the preceding claims, wherein the gear stage ( 14 ) is designed as a manual transmission. Drive unit according to one of claims 32 to 48 and according to claim 49, wherein at least two different outer rings ( 44 . 58 ) and / or ring gears ( 36 . 56 ) and / or sun gears ( 32 ) are detectable switchable. Drive unit according to Claim 50, in which the direction of rotation of the motor remains the same ( 12 ) determining the direction of rotation of the output ( 54 ) Are defined. Drive unit according to one of claims 49 to 51, wherein the gear ratio can be selected by determining. Drive unit according to one of claims 49 to 52, wherein for a frictional locking a wrap spring ( 60 ) is provided. Drive unit according to one of claims 49 to 53, wherein at least one toothed pawl (A) for a positive locking ( 64 ) is provided. Drive unit according to one of claims 49 to 54, wherein when the drive unit is switched on ( 10 ) the detection is automatically and mechanically canceled. Drive unit according to one of claims 49 to 55, wherein for switching a switching coil ( 63 ) with a core ( 62 ) is provided, which with mutually repellingly arranged holding magnets ( 61 ) cooperates. Drive unit according to one of the preceding claims, wherein the gear stage ( 14 ) is selectable from several gear stage types. Drive unit according to one of the preceding claims, wherein the drive unit ( 10 ) an adjuster ( 80 ) of the vehicle seat drives. Drive unit according to claim 58, wherein the adjuster ( 80 ) at least two components forming a load-absorbing transmission ( 81 . 82 ) having. Drive unit according to claim 59, wherein the drive unit ( 10 ) is integrated in the load-bearing transmission. Drive unit according to claim 59 or 60, wherein the load-bearing gearbox drives the rotor ( 22 . 24 ) stores. Drive unit according to claim 61, wherein the rotor ( 22 . 24 ) via the gear stage ( 14 ) is mounted continuously backlash to the load-bearing gearbox. Drive unit according to one of claims 58 to 62, wherein two individual adjusters ( 80 ), with each individual adjuster ( 80 ) a drive unit ( 10 ) is integrated in the load-bearing transmission. Drive unit according to claim 63, wherein the two drive units ( 10 ) by means of electronics for the electronic commutation of the motors ( 12 ) are synchronized. Drive unit according to one of claims 56 to 62, wherein the adjuster ( 80 ) is designed as a self-locking geared fitting.