DE4209211A1 - Rotary torque load coupling with bi-directional action - has coil spring load element that can be subjected to torsion to spread coils to provide torque transmission function - Google Patents

Abstract

A bi-directional coupling provides a mechanical coupling between the input shaft (6) and the output shaft (2) using a coil spring (3). Dependent upon the setting condition, the unit can transmit or block the transmission in either direction of rotation. The coil spring is located on rotatable rings (9) with the ends located in further rings (7,7a). The shaft halves are located together on a needle roller bearing (12). Transmission of power between the halves depends upon the spring being subjected to a torsional load to cause the coils to spread and so grip the surface of an outer ring (4). Main bearings (A',B') support the shafts. USE/ADVANTAGE - Provides double-acting coupling mode.

Description

The invention relates to an LDS according to the preamble of Claim 1.

The LDS enables the Posi as a double-acting freewheel protection of a rotatable shaft (output shaft) in both directions of rotation and the drive of this rotatable wel le from the drive shaft in both directions of rotation.

The nor. Used in many areas of mechanical engineering paint, one-way freewheels allow the Drehbe movement of a shaft only in one direction of rotation while in the other direction of rotation, the rotational movement of this shaft ge is blocked. The shaft is positioned here therefore only in a certain direction of rotation.

There are numerous uses in which for adjustable Machines or devices positioning in both rotations directions is required.

This means that the Ma rail part, e.g. B. connected to a rotatable shaft ner tiltable container, in both directions of rotation dert can be driven while retroactively from Actuating torques acting on the shaft (Ab driving torques) can be blocked in both directions have to.

Such locks can also be used as automatically switching double-acting freewheels are considered.

From the described requirements, the explains for such a design element used designation "Load torque lock", abbreviated: LDS.

In summary it can be said that from the drive to the Ab drove an LDS and thus also a rotation torque can be transmitted in both directions of rotation,  while, conversely, a rotary movement and therefore also a Torque in both directions of rotation from the actuator, al not transferred from the output to the drive of an LDS that can. In both directions of rotation now passes through Sper LDS positioning of the output shaft and thus of the actuator.

It is known to use load torque locks using a cylindrical torsion spring (helical torsion spring, for example, with a circular or other, for example rectangular, spring wire cross sections) for different applications which have spring ends bent inwards: Version I; ( Fig. 1).

In a further developed and improved design who which the spring ends bent inwards are replaced by in Circumferential direction tapered spring ends, the ge with such Shaped spring end pieces are provided that the introduction the circumferential force when locking tangentially with if possible large lever arm.

Such is known from the patent specification DE 30 42 398 C2 LDS known for different applications: Version II.

In further development of these two known constructions, patent application P 42 02 415.3-26 dated January 29, 1992 requested protection for an LDS in which the circumferential force F _{u of} the drive torque element T _an in each direction of rotation was directly on the drive through from drive to output respective stop point (D) from the slotted drive shaft ( 6 ) to the with the output shaft ( 2 ) connected ne lever hub ( 1 ) without one of the two end pieces ( 7 and 7 a) of the two spring ends of the torsion spring ( 3 ) is applied by the circumferential force F _u : Version III.

The described known, gradually improved con structions of the LDS are further optimized by the patent application P 42 06 168.7 from February 28, 1992, in which protection is sought for support rings arranged radially between the torsion spring ( 3 ) and the slotted drive shaft ( 6 ) ( 9 ), which are preferably provided with helically arranged profiled recesses ("threads"), in which spring turns of the torsion spring ( 3 ) are embedded and guided.

By axially tensioning the spring coils, ie by pulling the torsion spring apart, it is achieved that the spring coils cannot touch one another: Version IV; (Line 9 in Fig. 2).

In these 4 known LDS constructions (versions I to IV), the bearings of the drive shafts ( 6 ) and the output shafts ( 2 ) were provided in the manner in which the bearing design according to FIG correspond. 1,.

Although this bearing concept has been tried and tested for many applications, there are disadvantages that always have a greater negative impact, the higher the transferable torques when locking (T _ab ) and driving through (T _an ).

These torque increases with otherwise the same reference measurements, such as. B. characteristic diameter D _m or D ₁ , number of spring turns, spring wire cross-section and spring wire dimension etc. are the desired consequences of the improvements described.

To the LDS version IV by the proposed improvements except for the conception of the bearings, the ge development goal of optimized torque transferability and operational safety has been practically achieved, ie that the LDS has a simple and compact structure (see FIGS. 2 and 3) can transmit the torques when locking (T _ab ) and when driving through (T _on ), which can transmit the external shaft journals of the input and output shafts ( 6 and 2 ) in terms of strength. ("balanced" construction).

The known for the versions I to IV (according to Fig. 1) in the LDS bearing design of the drive shaft ( 6 ) with the bearing point A '(bearing 10 ) and the output shaft ( 2 ) with the bearing point B' (bearing 11 ) and with Interlocking storage in storage location C '(storage 12 ) has the following parts in the operating states "drive through" and "lock" / "unlock":

1) "drive through":

From Fig. 1 and 2 it can be seen that when driving through the eccentric, ie eccentrically at a distance (D ₁ -D ₂ ) / 2 acting from the shaft axis and with the drive speed number n _to circumferential force

e.g. B. with assumed left rotation of the drive shaft ( 6 ) at the stop D on the lever hub ( 1 ) and thus on the output shaft ( 2 ).

The drive shaft (6) and the output shaft (2) are thus defined by the force acting perpendicularly to the shaft axis with the drive speed n _of circumferential lateral force (radial force) F _'u loaded.

Hereby occurs the transferable Antriebsdrehmo T ment _to dependent, because of the characteristic structure of the present LDS conception necessarily systemic occurring inner lateral load (radial Bela stung) of the input and output shafts and the bearings on. This is undesirable, since the housing bearings ( 10 ) and ( 11 ) located in bearing points A 'and B' are continuously and dynamically driven by radial forces from the internal function of the LDS when driving through and without externally contacting the external shaft journals of the and forces acting on the output shafts (e.g. radial and / or axial forces caused by tooth forces, belt tension, etc.). This undesirably reduces the bearing life from the outset in the known bearing design (LDS versions I to IV).

With large lateral forces

If, in addition, because of the radial and axial bearing clearances to a n _of circumferential tilting (buckling, skewing) of the input and output shafts (6 and 2) against each other.

This can be the secure locking and unlocking, i.e. the actual main function of the LDS as a safety component, affect.

2) "Lock" / "Unlock":

From Fig. 1, 2 and 3 it can be seen that when locking the peripheral force acting eccentrically, ie eccentrically at a distance D _m / 2 from the shaft axis

e.g. B. assuming clockwise rotation of the output shaft ( 2 ) at the stop A via the end piece ( 7 a) in the loaded first spring turns of the torsion spring ( 3 ).

Here, the torsion spring ( 3 ) after completion of a small NEN necessary for locking pivoting movement of the construction parts that are in contact with the attachment point A (He hub hub ( 1 ), end piece ( 7 a), first loaded Federwindun gene) around the displacement (Blocking path) c frictionally locked against twisting in the ring ( 4 ). The frictional engagement of the torsion spring ( 3 ) seated under pretension in the cylindrical bore is enormously increased by pressing on the end piece ( 7 a), the pressure of the Federwin endings against the inner surface of the bore from the spring, which absorbs the circumferential force F _u , to the other, the free, unloaded spring end (here end piece 7 ) decreases.

A dependent on the inner longitudinal dimensions d, e, f of the LDS from the proportion of the lateral force F _u acting on the lever hub ( 1 ) is via the output shaft ( 2 ) on the bearing point B 'with the housing bearing ( 11 ) and the other part the lateral force F _u is transmitted via the inner bearing point C 'with the bearing ( 12 ) to the drive shaft ( 6 ) and from there to the bearing point A' with the housing bearing ( 10 ).

As a result, an internal transverse load of the drive shaft and the output shaft and all bearings occurs that is dependent on the transmitted output torque (locking torque) T _{and is} dependent on the characteristic structure of the present LDS concept.

This is undesirable since the housing bearings A 'and B' located in the bearings ( 10 ) and ( 11 ) when locked statically by radial forces from the inner function of the LDS even without the outside on the Wel lenzapfen the drive and Forces acting on the output shafts (e.g. radial and / or axial forces caused by tooth forces, belt tension, etc.). As a result, the static load-bearing capacity is undesirably reduced from the outset in the known mounting concept.

With large lateral forces

Furthermore, due to the radial and axial bearing play, the drive and output shafts ( 6 and 2 ) tilt against each other at standstill (buckling, misalignment).

This can be the secure locking and unlocking, i.e. the main functions of the LDS as a security structure affect part.

When intended "unlock" 1 and 3, after Fig. Z. B. assuming clockwise rotation of the slotted drive shaft ( 6 ), the end piece ( 7 a) on the stop position le B moves to the right until the frictional engagement of the housing ( 4 ; 5 ), which is initially still firmly in the cylindrical bore of the housing ( 4 ; 5 ) 3 ) is loosened by the desired "unlocking from behind" and the torsion spring is also dragged by the slotted drive shaft ( 6 ) when the remaining preload torque is overcome, ie it is turned.

An unwanted "unlocking from behind" must be avoided in any case, which is not guaranteed in the present known storage conception according to FIG. 1 because of the above-described lateral force F _u , which is characteristic of the functional principle of the present LDS concept and which also acts proportionately on the bearing ( 12 ) of bearing C '.

Due to the already explained above, at large transverse forces F _u , standstill tilting (buckling, misalignment) of the input and output shafts against one another and to a lesser extent also due to the static load on the bearing ( 12 ), this can be transferred through this bearing increase friction torque and the drive shaft (6) take friction at a free and unrestrained rotatable drive shaft (6) (for. example, in pure drive-side manual drive and lack of drive-side drive train, which has a braking effect).

Here, because of the present LDS concept tion in itself to be regarded as particularly advantageous smooth unlocking process (very low ent locking torque) an unwanted "unlocking from behind" enter.

3) Stability of storage:

The well-known for a long time and until today applied concept of storage of the input and output shafts (6 and 2) of FIG. 1 does not ensure the optimal storage stability as moments at the high input speed T _and the high output torques T _from (ho hey Locking moments) would be required, which are achieved by the improvements of versions II to IV. The increase is 2 to 3 times the torque transferability of version I ( Fig. 1) with the same basic dimensions.

The unsatisfactory storage stability is due to the flying bearing of the drive shaft ( 6 ) in the bearing point A 'with the two bearings ( 10 ) and the relatively small span (bearing distance e) from the drive shaft bearing in the bearings B' with the bearing ( 11 ) and C 'with the bearing ( 12 ).

The disadvantageous consequences of a storage stability which is unsatisfactory, especially with high torque transferability of the LDS according to FIG. 1, have already been described above.

The invention has for its object to eliminate the disadvantages and thus to create an LDS, the safe "drive through", a safe "lock" and a light "unlock" up to the highest transferable to drive and output torques without risk of Failure ensures and in which the housing bearing ( 10 ) of the bearing point A 'and ( 11 ) of the bearing point B' according to Fig. 2 when "driving through" completely unaffected by the effects of the system-related internal lateral forces F ' _u and F _{u and} remain at the entire storage (bearing points A ', B', C ', D') of the LDS has optimal stability ( Fig. 2) with a simple and compact overall construction.

This is shown according to the invention in the embodiment example in FIGS. 2 and 3, achieved in that only one bearing point is provided as a housing bearing for the slotted drive shaft ( 6 ) and for the output shaft ( 2 ).

These are the bearing point A 'with the bearing ( 10 ) and the La gerstelle B' with the bearing ( 11 ) each in the housing ( 4 with 5 and 8 ). These two housing bearings have a large bearing spacing f from one another (span of the bearings).

A floating bearing of the drive shaft ( 6 ) is not necessary.

The drive and output shafts are also stored two times in the bearing C 'with the bearing ( 12 ) and in the bearing D' with the roller bearing ( 13 ) not shown in Fig. 2 (for design reasons a needle bearing).

Sliding bearing according to a demanding 3 was shown in Fig. 2.

The bearings C 'and D' for the two interlocking bearings have the large bearing distance e.

This proposed optimized storage concept according to the invention leads to a simple and reliable construction and ensures optimum stability of all moving parts of the LDS, especially the two shafts. This applies above all to the LDS versions II to IV, which have been greatly improved in comparison to version I ( FIG. 1) and have a much higher torque transferability (T _an and T _ab ) with the same comparable main dimensions, and since with the additional inclusion of the Improving the storage concept according to the invention allow a very simple and extremely compact design. For LDS as an important safety component in a drivetrain, this progressive design brings the desired advantages in terms of: space requirements, operational safety, costs, weight, heat when driving through, universal installation and attachment options of the LDS as a compact unit, etc.

For the operating state "drive through" has been achieved by the invention inventively proposed according to claim 1 storage concept ( Fig. 2) that the bearings of the two Ge housing bearings A 'with the bearing ( 10 ) and B' with the bearing ( 11 ) completely remain unloaded, since the system-related in other lateral forces F ' _u and F _u in the two interlocking positions of the input and output shafts in the bearings ( 12 ) of bearing C' and ( 13 ) of bearing D ', their bearings always only statically (or valid for the bearing ( 13 ) according to claim 2 not at all) are lifted. The housing bearings ( 10 ) and ( 11 ), which are completely unloaded when driving through, are therefore fully available for absorbing external axial and radial loads on the two external shaft journals of the drive and output shafts. To design the invention will propose according to claim 2 that the bearing distance of bearing A 'with the bearing ( 10 ) for the storage of the drive shaft ( 6 ) in the hous se ( 4 with 5 and 8 ) to the bearing C' with the bearing ( 12 ), which is one of the two inter-bearings of the drive shaft ( 2 ) in the drive shaft ( 6 ), is chosen as small as possible, preferably should go towards 0 (d → 0).

This ensures that especially when "locking" the  Storage stability of the LDS taking into account the occurring great lateral force

is optimized in that the proportion F _C 'of the transverse force F _u which is to be transmitted via the bearing point C' to the bearing ( 12 ) via the closed hollow shaft area of the drive shaft ( 6 ) to the bearing point A 'to the bearing ( 10 ), is then practically transmitted on a common line of action if the distance d approaches 0 (d → 0). There can then be no tilting moment (transverse moment) M = F _C ′ · d on the drive shaft ( 6 ), which causes standstill tilting (buckling, misalignment) of the drive and output shafts against each other and in the bearing D 'With the bearing ( 13 ) would cause a bearing force F _D '<0.

As with "locking", he is "driving through" handed stable storage with the largest possible storage stands f and (g-d) with (d → 0) at the occurring highs internal lateral forces

important prerequisite for perfect function.

For a further embodiment of the invention is proposed according to claim 3 ( Fig. 2), the intermounting of the drive shaft ( 6 ) on (according to Fig. 2: right) front end from its slotted hollow shaft area on the drive shaft ( 2 ) in the Bearing point D 'instead of a Wälzla ger ( 13 ) advantageous to increase over a (narrow) plain bearing.

This creates space axially so that the LDS can be constructed more narrowly. Furthermore, the costs for the roller bearing ( 13 ), which would be a Na dellager for design reasons, are saved.

The plain bearing is instead of the roller bearing at the bearing point D 'possible because of the proposal according to the invention in claim 2 to let the bearing distance d go to 0 (d → 0), whereby the plain bearing D remains practically unloaded when "locking" (F _D ′ → 0).

There is thus when locking the (small) Schwenkbe movements of the lever hub ( 1 ) and thus the output shaft ( 2 ) around the locking path c not the risk of unwanted "Ent lock from behind" by frictionally driving the drive shaft ( 6 ) because of in the case of plain bearings, higher frictional torque is to be expected compared to the rolling bearing. A frictional entrainment via the bearing ( 12 ) of the bearing point C 'does not occur because a roller bearing (preferably a needle bearing (cage-guided needles or vollna delig) is provided and there is no tilting (buckling, misalignment) of the drive and output shafts) can occur, as has already been stated.

In claim 4 protection is also sought for the variant at the bearing point C 'instead of the roller bearing ( 12 ) described above, a slide bearing despite the expected high radial force F _C ' to provide "locking". The prerequisite for this is that a type of plain bearing is selected which has only very small frictional torques in the small swiveling movements when locking in order to reliably rule out an unwanted "unlocking from behind".

Description of the exemplary embodiments of the invention shown in FIGS . 1, 2 and 3 according to claims 1 to 4:

• - Fig. 1: Front and side view of a known LDS with the hitherto usual and also today used situation conception.
  (LDS version I)
  With reference to FIG. 1 the known LDS will now be explained, the device for use in drive and Positionierein a tiltable container (z. B. a Gießpfan ne) is determined.

This explanation is also valid for the basic structure and the basic functions of the improved LDS proposed according to the invention and shown in FIGS. 2 and 3 as an exemplary embodiment.

The lever hub ( 1 ) is connected to the output shaft ( 2 ) which represents the actuator to be positioned in both directions of rotation (e.g. the tiltable container coupled to the output shaft).

The cylindrical torsion spring ( 3 ) (with circular or at its, e.g. rectangular wire cross-sections) with the two spring ends bent inwards sits under tension, which should be as small as possible due to the easier driving through, in the hardened and ground cylinder bore of the ring ( 4 ). This ring is firmly connected to the housing ( 5 ).

When locking of the output shaft (2) of the LDS we kenden output torque T _from the torsion spring (3) is obtained by the pressing of the lever hub (1) at the stop point A - if the output torque T _from veering is - the applied inwardly bent spring end additional Lich spread apart and locked against twisting in the ring ( 4 ) because the frictional engagement of the prestressed in the cylindrical bore torsion spring is enormously increased by pressing, the pressure of the spring turns against the inner surface of the bore from the spring end, which the circumferential force takes up to others, the free spring end, decreases.

The drive shaft (6) is formed in the region of the two according to NEN bent spring ends as a slotted sleeve (hollow shaft) in such a manner that the torsion spring (3) over the respective stop point - stop point B, if the on drive torque T is _in clockwise - the infra gekom can be relaxed, the spring end bent inwards.

The frictional engagement is loosened, and the torsion spring ( 3 ) can be dragged along by overcoming the remaining preload torques from the drive shaft ( 6 ), ie rotated.

The drive torque T _an is in this operating state of driving through the adjacent, inwardly bent spring end of the drive shaft ( 6 ) from the drive shaft ( 1 , 2 ) directly positively transmitted via the impact point B.

An LDS of the type described can only work reliably if the following conditions, which are shown here in simplified form, are fulfilled for the games (tangential games, twisting games):
a <b <c.

Only then can the full output torque T _ab be braked in both directions of rotation in all possible operating states without hindrance by the stop faces of the slotted sleeve of the drive shaft ( 6 ), that is to say blocked.

The same applies when driving through, that only if the conditions mentioned ge are met, the torsion spring ( 3 ) is unlocked without a wall, and the drive torque T _on in both directions of rotation without obstruction by the striking surfaces of the slotted sleeve of the drive shaft ( 6 ) the drive shaft to the output shaft ( 1 , 2 ) can be transferred.

The games are shown in Fig. 1, side view, and arise when the drive shaft ( 1 , 2 ) and the drive shaft ( 6 ) come into contact with the stop points A and B against the inwardly bent spring ends of the pretension in with slight clockwise rotation the cylindricity rule bore of the ring occurs (4) seated a torsion spring (3) before a torque transmission from T _and / or T is present _from.

The play a must be greater than the displacement path (block way) c the loaded spring end at the stop A when locking to build up the additional friction between spring turns and bore, so that when Lock a simultaneous unlocking of the torsion spring (un deliberate "unlocking from behind") cannot occur.

• - Fig. 2 and 3: front and side view of the proposed to the claims 1 to 4 proposed optimized storage concept.

Referring to Figs. 2 and 3, the detailed Be is now scription of FIG. 1 supplemented.

The above description remains fully valid except for the note that instead of the inwardly bent spring ends of the torsion spring ( 3 ) in an advantageous manner spring end pieces ( 7 and 7 a) are used, which functionally when locking, unlocking and driving through essentially correspond to the bent parts of the two spring ends of the rotary spring.

The end pieces can, to some application examples mention as slotted or split clamps that are frictionally, positively or are integrally connected to the spring wire.

The end pieces can also through the spring wire itself (e.g. also by upsetting, by radial pins in the spring wire etc.).

To Fig. 2 and 3, improvements are the patent application P 42 06 168.7 drawn (LDS version IV) by the spring support rings (9) axially tensioned with "ge Gewindegän" about the first, ie somewhat exploded torsion spring (3). The resulting Axi alsspiel S _a ensures that the spring turns can no longer touch each other.

Thanks to all improvements (LDS versions I to IV), the torque transferability when "driving through" (T _on ) and when "locking" (T _down ) was increased considerably. The storage concept of the LDS, which is to be improved in accordance with the invention, must take this increase to 2 to 3 times the value into account.

In the bearing points A 'with the bearing ( 10 ) and B' with the bearing ( 11 ), which have the greatest possible bearing distance f, the drive shaft ( 6 ) and the output shaft ( 2 ) are mounted in the housing ( 4 with 5 and 8 ) .

The additional support of the input and Abtriebswel len is carried out by the two inter-bearing in the bearing C 'with the bearing ( 12 ) and in the bearing point D' with the narrow slide bearing shown in Fig. 2 of the slotted drive shaft ( 6 ) on right end of your slotted hollow shaft area (sleeve area) with the greatest possible bearing distance (gd), where d should go towards 0 (d → 0).

The axial support of the two shafts in one direction tion, here inwards, takes place via contact point E. This simple support is possible because of the very small swiveling movements of the drive and output shaft len against each other.

• - Result: The LDS according to FIGS. 2 and 3 is very simple and extremely compact as a self-contained machine part or as a built-in or add-on unit. B. be attached and combined via a marked flange mounting univer sell. There are also combinations with different types of coupling, such as. B. Si safety slip clutches possible.
• The lubrication can e.g. B. as oil lubrication or grease Lubrication with its own filling or in combination with the lubrication circuit of the connected machine (e.g. Gearbox).
• - In summary, it is found that the LDS proposed according to the invention has the following advantages over the known designs:
  • - All bearings of the input and output shafts ( 6 and 2 ) are stable, statically determined and have the largest possible bearing distances f and (gd) with d → 0.
  • - The inner bearings of the drive and the output shaft ( 6 and 2 ) are designed and arranged by the two interlocking bearings C 'and D' with, as with the bearings A 'and B', the largest possible bearing distance (gd) that the two housing bearings A 'with the bearing ( 10 ) and B' with the bearing ( 11 ) during "drive through" are not acted upon by the system-related internal transverse forces (internal radial forces), but these two housing bearings run around completely unloaded and are thus available for absorbing any external additional loads on the external shaft journals of the input and output shafts (e.g. external radial and / or axial forces).
  • - A bearing load by an internal radial force F _D '(internal transverse force) at the bearing point D' is not present when driving through.
  • - Tilting (buckling, misalignment) of the input and output shafts ( 6 and 2 ) against each other cannot occur.
  • - At the bearing point D 'a simple (narrow) plain bearing can be provided in a space-saving and cost-effective manner instead of a more complex roller bearing.
  • - There is no danger of unwanted "unlocking from behind" when "locking", ie the operational safety of the LDS as a safety component is guaranteed.
  • - The LDS according to FIGS. 2 and 3 represents a balanced con construction, which is very simple and extremely compact and which, as a self-contained unit, is independent in a drive train or as a built-on or built-in unit or combined with various types of couplings high torque transfer availability when "locking" and "driving through" and with high operational reliability is versatile.

Claims (4)

1. Load torque lock (LDS) with a torsion spring ( 3 ) located in a bore D _a with pre-tensioning, with a preferably circular or rectangular (or quadratic) spring wire cross-section, with the initiation of a circumferential force F _u depending on the direction of rotation of an output-side torque T when locking _from in one of the two bent spring ends (e.g. according to FIG. 1) or in one of the two spring end pieces ( 7 or 7 a, e.g. according to FIGS. 2 and 3) of the two spring ends, and wherein when driving through (driving) from the drive to the transmission of a circumferential force F _u 'depending on the direction of rotation of a drive-side torque T _to the lever shaft ( 2 ) connected to the output shaft ( 1 ), characterized in that the drive shaft ( 6 ) and the output shaft ( 2 ) each have a bearing point (A 'or B') in the housing ( 4 with 5 and 8 ) with a large bearing distance f of the bearing points A 'and B' from each other, namely the drive shaft ( 6 ) the bearing point A 'with the bearing ( 10 ) and the output shaft ( 2 ) has the bearing point B' with the bearing ( 11 ), wherein, in addition, the drive shaft ( 6 ) and the output shaft ( 2 ) are mounted twice in the bearing position len C 'with the bearing ( 12 ) and in D' with the bearing ( 13 ) (in Fig. 2, instead, a plain bearing is shown according to claim 3), the large bearing distance (gd) of the bearing points C 'and D' from each other exhibit. 2. load torque lock (LDS) according to claim 1, characterized in that the axial distance d, the bearing A 'with the bearing ( 10 ) for the mounting of the drive shaft ( 6 ) in Ge housing ( 4 with 5 and 8 ) to Bearing point C 'has with the bearing ( 12 ), which is in the bearing arrangement of the drive shaft ( 2 ) in the drive shaft ( 6 ), is as small as possible and preferably goes to 0 (d → 0). 3. load torque lock (LDS) according to claims 1 and 2, characterized in that the intermeshing of the slotted drive shaft ( 6 ) on the output shaft ( 2 ) in the bearing point D 'instead of a rolling bearing ( 13 ) via a sliding position tion he follows. 4. load torque lock (LDS) according to claims 1 to 3, characterized in that the intermeshing of the output shaft ( 2 ) in the drive shaft ( 6 ) in the bearing point C 'instead of a roller bearing ( 12 ) via a plain bearing.

• - Documents considered for the assessment of patentability:
• Patent DE 30 42 398 C2
  from May 29, 1991
  Patent application P 42 02 415.3
  from 29.01.92
  Patent application P 42 06 168.7
  from 28.2.92.