DE102022002826A1 - Load lifting system (LHS) / load lifting and turning system (LHWS) / torque difference scale (DDW) / torque difference scale with braking system (DDW*) and universal load lifting system (ULHS *) - Google Patents

Abstract

System for lifting and turning a load with a traverse with a load pickup point for receiving and transmitting a tensile load to the system, a functional unit arranged on the traverse for distributing a torque difference resulting from the tensile load, a braking unit arranged on the functional unit for regulating the torques -Difference as an integrated part of the functional unit, at least two stop points arranged on the load, two oppositely pulling sling means, these being designed to be connected to the at least two stop points, the functional unit being designed in such a way that the tensile load of the two sling means can be regulated and transferred to the at least two sling points, the functional unit having a differential gear for compensating for deviating lengths of the sling means, or wherein the functional unit has two differential shafts which are connected to one of the two sling means by a traction cable to compensate for deviating lengths of the sling means.

Description

<1>

The invention relates to load-lifting systems (LHS), load-lifting-turning systems (LHWS), which enable the function of controlled turning or controlled, partial rotation of components as an optional main function and their combination with targeted function carriers Lead the conception of universally applicable load lifting equipment or universal load lifting systems (ULHS*).

<2>

The well-known technology of load turning devices, for example according to the patent DE 202010001499 is designed for turning large and/or bulky loads using e.g. B. 2 x large load belts, into which the component to be turned, the workpiece, is previously inserted, wrapped around it and then turned, motor-driven, by means of the load belts or placed in the desired rotational position orientation and can therefore advantageously be turned several times and changing the direction of rotation.

<3>

In Figure 1, the load-lifting system (LHS) (1) or load-lifting-turning system (LHWS) (1) according to the invention is shown sketched and positioned as a functional placeholder, with the component to be turned or lifted (2) or load part (2) with its weight (G) and center of gravity (S) is or is to be connected to the LHS (1) or LHWS (1) by means of suitable attachment points (a) or attachment means (a). is. The load lifting device (1) including the load part (2) is attracted or lifted as a total load by means of a tensile force (Z) at its load-bearing point (3) by the crane hook that usually receives it.

<4>

According to the invention, the LHS (1) or LHWS (1) according to Figure 1 for the construction or storage or to ensure an energetically usable torque potential includes the construction principle of a torque difference balance (DDW) as an essential, integrated functional unit and this in combination with brake functionality (B) in the LHS (1) or LHWS (1). This common functional assembly consisting of (DDW) and (B), hereinafter referred to as functional assembly (DDW*), with the functions of a torque differential balance including an integrated brake (B) or integrated braking system (B), is an essential feature the LHS (1) or LHWS (1) according to the invention. The used or usable function of the scale with the stop side (4) and stop side (5) pulling in opposite directions according to the invention is an integrated part of this LHS (1) or LHWS (1) or (DDW*) according to the invention.

<5>

The brakeable functional assembly DDW* according to the invention has, effects, enables and ensures a potential excess torque in one direction of rotation or there is a conscious and advantageously usable torque difference, a torque imbalance as an energetic potential in the design-related direction of rotation within the LHS according to the invention (1 ) or LHWS (1), as soon as the load of the component to be lifted (2) is attracted or raised via the attachment points or means (a) or with the attached LHS (1) or LHWS (1) and as long as the load or the component (2) to be turned is not yet back in a torque-stable position or rotational position orientation. A freely hanging load part (2) only has a “torque-stable position” for the LHS (1) or LHWS (1) functionally for the (DDW*) according to the invention when only one of the opposing load sides (4) or (5) remains. is tensile towards the load part (2) and the distance (k) between the perpendiculars of the crane hook-related tensile force (Z) and the resulting weight (G) in the center of gravity (S) then aligns virtually congruently.

<6>

The braking functionality (B) integrated in the (DDW*) can be varied or released from a blocking advantageously according to the invention and in terms of safety. The brake unit (B) has, for example, the functions: blocking or blocking, unlocked, throttled or releasing, throttled, releasing or completely released. With a simple design of the LHS (1), LHWS (1) according to the invention, this can be preset manually or mechanically quantitatively, for example as a throttle brake or as a throttle brake that can be released mechanically, which in terms of safety, for example, returns to a locking function secured by a spring action, if with the brake system (B) braking is not targeted. In more complex designs of the LHS (1), LHWS (1) according to the invention, the desired, necessary braking functionality (B) of the LHS (1), LHWS (1) can be achieved via controlled actuators and, for example, via radio operation to control the LHS (1), LHWS (1) are sent and can therefore be set, changed and controlled wirelessly, for example.

<7>

By means of the brake functionality (B), which is integrated with the torque difference balance (DDW*) according to the invention, the load (2) can be raised off the ground using the LHS (1) or LHWS (1) according to the invention, for example when the brake is blocked and Then, with the brake function effectively throttling, the rotation or turning of the load component (2) hanging free from the ground can be initiated and carried out.

<8>

By means of the brake functionality (B), which is integrated according to the invention with the torque difference balance (DDW*), the load (2) can be brought into contact with the ground using the LHS (1) or LHWS (1) according to the invention while the brake function is effectively throttling tightened and the turning maneuver can be carried out, for example by 90°, while maintaining contact with the ground.

<9>

LHS (1), LHWS (1) can be implemented, for example, without a motor drive unit within the LHS (1), LHWS (1), a limited turning or a corrective orientation of the load part (2) or a limited rolling of the load part (2 ) with ground contact.

<10>

Examples of designs of torque-difference balances (DDW) or with brake functionality as a DDW* concept are presented in more detail in the following explanations from section <17>.

<11>

First of all, the traverse concepts according to Figure 2 in combination with the (LHS) (1) or (LHWS) (1) according to the invention will be discussed, which will play a major role with regard to the technical implementation of universal load lifting devices. The (LHS) (1) or (LHWS) (1) are mounted on or coupled to the traverse and the corresponding sling ropes (a) or load straps (a), load chains (a) are usually attached via deflection rollers (U ) is deflected towards the attachment points (a) on the load part (2) in a direction-related manner, so that the sling ropes, straps and chains can be attached to the respective load part (2) as perpendicularly as possible to the direction of gravity. In addition, the truss constructions offer the possibility of feeding the sling ropes, straps and chains to a truss fixed point stop (f) or fixing them there via usually mounted deflection rollers, shafts, components (U), which increases the load capacity of the corresponding, deflected pulling stop connection of the LHS (1), LHWS (1) is also doubled due to the double engagement of the load rope, for example. In addition, it should be noted that truss concepts can also be equipped or combined with several (LHS) (1) or (LHWS) (1). These must be designed to function synchronously with each other to ensure a safe operating state of the traverse concept and with sufficient safety.

<12>

If a crane-independent or self-sufficient lifting function according to Figure 3 is implemented in combination with the LHS (1) or LHWS (1) according to the invention, then this provides an essential, further functionality for a corresponding concept of a universal load-lifting system ( ULHS*) with brakeable, lockable lifting function system (HS*). The combination of a torque-difference balance according to the invention with a braking system (DDW*) plus a preset and/or controllable lifting function system (HS*), which also has integrated braking functionality, opens up the desired option of a self-sufficient lifting towards the crane. The insertion, the functional positioning of the brakeable, lockable lifting system (HS*) can take place on the level between (DDW*) and the load pickup point (3) towards the crane hook or the functional positioning of the lifting system (HS*) can take place on the level Position between the assembly (DDW*) and the load part (2) connected to it in terms of stops. The lifting system (HS*) can, for example, be sufficiently dimensioned in terms of motor for the motorized stroke up and down of the load part (2) or the motor drive power of the lifting system is, for example, limited to the function of tightening the sling connections, e.g. the slinging ropes in the tightening setup mode and lowering under load, for example, can be done against the braking functionality of the braking function integrated in the (HS*) or by means of, for example, a single-acting hydraulic cylinder with spring return, motor use within the lifting system (HS*) can even be dispensed with for a simple design. With this combination of (DDW*) plus (HS*) = (ULHS*) according to the invention, it is possible to lift the load part (2) to be raised or lowered or lowered, regardless of the functional scope of the crane system carrying this combination, for example using high-quality creep mode to move.

<13>

In the conceptual model according to Figure 4, according to the invention, all e.g. 3x or 4x stops of the (LHS) (1) or (LHWS) (1) according to the invention are deflected towards the load part (2) via deflection rollers (U) and each end-related (e.g. rope end-related) to a common one Tension load lifting shaft (ZHW*) is fixed and wound over it in the same direction. Then this (ZHW*) acts as a traverse-related fixed point collection point for the ends of the sling ropes, straps, chains fixed here and acts as an integrated lifting unit in combination with the winding speed in the same direction, in the same direction and with the same size (effective diameter d = constant) on the shaft in combination with the inventive (LHS) (1) or (LHWS) (1) towards the load part (2). The lifting unit integrated or combined according to the invention via a tensile load lifting shaft (ZHW*) can, for example, in principle be designed as a horizontal shaft concept according to Figure (4-a) or as a vertical shaft concept according to Figure (4-b). This makes various concepts possible for implementation, such as tensile load lifting shafts (ZHW*) with integrated motor-brake unit (M/B), which can, for example, lift and lower loads (2) in a controlled manner with high-quality creep speed operation, or where the lifting unit can only be used in a quasi-controlled manner in the unloaded state in the course of picking up the load part (2) for rope tensioning with low power, the motor is used to shorten the rope and then effectively block the rope and for later, for example, to set the load part (2) down again on a work table, the available stroke path (h) of the lifting unit is braked, e.g. in Creep speed and virtually without engine power input, as a function can be released in a controlled manner.

<14>

Instead of the brakeable tension-load-lift shaft (ZHW*) in Figure (4-a) and Figure (4-b), Figure 5 shows a combined lifting drive for the (LHS) (1) or (LHWS) (LHWS) according to the invention ( 1) the concept of a brakeable linear stroke drive (LHA*) or linear drive (LHA*) used to change the length of the rope ends together and to the same extent as a package or in a mechanical connection. A lifting cylinder is shown as an example of a brakeable linear lifting drive (LHA*) in Figure 5, which contains the sum of the rope ends (SE) from the 2x load ropes on the load side (4) and 1x counter-rotating load rope on the load side (5) of the LHS* (1) or the LHWS* (1) and supports the load on the side of the load engagement point (3) or the crane hook or the traverse bridge. The example shown of a hydraulic cylinder with spring return and stroke distance (h) can be reset in a spring-resetting manner by opening the valve without load intervention of the load part (2), then the valve is closed, for example; Then a load (2) can be raised and this can then be lowered by opening the valve according to the valve opening and the preset throttling in the lifting range (h) of the lifting cylinder used. This example without a motor-operated pump unit in the hydraulic concept of the cylinder shown is an exemplary simple solution option that does not require any energy supply from outside or from a battery storage device attached to the traverse. Examples of possible linear hydraulic systems, linear drives such as rack and pinion drives or ball screws etc. offer a variety of possible implementation options of a brakeable, lockable linear stroke drive (LHA*) in combination according to the invention with the (LHS) (1) or (LHWS) according to the invention ) (1) and this coupled with various options for control and energy supply.

<15>

In many versions, motor-driven, controllable, remote-controlled lifting units (LHA*) or (ZHW*) on the traverse or with regard to the LHS (1) or LHWS (1), powered as possible wirelessly from mobile battery storage, are certainly advantageous concepts chosen. The design options are certainly conceivable and possible to implement in a wide range of applications. The essential potential and advantages of using an integrated motor-driven lifting unit or, for example, a tensile load lifting shaft (ZHW*) or a linear lifting drive (LHA*) are in combination with the (LHS) (1) or (LHWS) ( 1), given regarding the functions: rope shortening or rope lengthening + rope tightening when positioning the load part (2) in the corresponding working space of the (LHS) (1) or (LHWS) (1) + the possible integrated lifting functions in lifting and/or in lowering direction of the load part (2) and this installed lifting functionality can be advantageously designed, for example, with high-quality radio operation and slow speed mode, which the crane system carrying this unit at the load point (3) may not have even in this quality. With an integrated lifting unit in combination with the (LHS) (1) or (LHWS) (1) according to the invention, this unit becomes a quasi-universal load-lifting system (ULHS*).

<16>

To further increase the integrated range of functions and to promote the increased use of the load-lifting systems (LHS) (1) or load-lifting-turning systems (LHWS) (1) or universal load-lifting systems (1) according to the invention ULHS*) is the additional component according to the invention bination with a powerful and operationally reliable load profile recording tool is a consistent approach. The data collection of the load profile of the (LHS) (1) or load-lifting-turning system (LHWS) (1) or (ULHS*) for the consistent and correct determination of the “theoretical remaining useful life of crane systems” is ensured by means of calibrated sensors to be measured and stored in a data-secured manner, in reference to the operated crane system, in the load profile recording tool integrated in combination according to the invention. The relevant data collected must be made available via interface functions for further data transfer.

<17>

Below, more specific explanations of the torque-difference balances (DDW) according to the invention or including a brake system (B) as a combination assembly (DDW*) are shown, which have been mentioned several times in the previous explanations and play a central role.

<18>

Figure 6 shows the concept of “bearing-suspended differential gears (DG) as (DDW) plus integrated brake system (B) as a combination assembly (DDW*)”. The differential gear (DG) is mounted and suspended via 2x bearings (L) to the supporting frame with the load bearing point (3) of the LHS (1) or LHWS (1). The deflection shaft (uw) and the 2x balance shafts (aw1) and (aw2) are wound in opposite directions on the stop side. Braking (B) between DDW or (DG) and the carrier with anchor point (3) is carried out using a brake disc system as shown in the drawing (other braking systems such as drum brakes are also possible).

<19>.

A useful advantage of the differential gear (DG) in the (DDW) or (DDW*) is the possibility of cable length compensation between the crane hook (3) or LHS (1), LHWS (1) towards the load part (2) by With the brake released or throttled, the cable length compensation can take place with limited sling cable lengths. If the component (2) is lifted slightly as a test, the distance (k) (see Figure 1) between the tensile force (Z) and the center of gravity (S) of the load part (2) can be immediately and advantageously evaluated in terms of direction and size. By correcting the crane hook position towards the component's center of gravity (S), the rope can be tightened again in order to then achieve a vertical lifting movement that is as axially stable as possible.

<20>

Figure (6-a) shows the concept of the differential gear (DG) mounted on bearings with 1x sling cable winding on the deflection shaft (uw) and 1x opposing sling cable winding on the 2x balancing shafts (aw1) and (aw2). In addition, the bearings (L) and 2x brake systems (B) of the combination assembly DDW* are shown.

<21>

Figure (6-b) shows the concept according to Figure (6-a), but here with load straps wound in opposite directions. Here too, 2x brake systems (B) are shown on the 2x balancer shafts. Solutions with an additional brake (B) on the deflection shaft side or with only 1x (B) on the deflection shaft side are also conceivable.

<22>

In picture [6-c) the (DG) is shown cut open and sketched with the main bearing points (L). Here it becomes clear again how the differential gear (DG) can be suspended from the carrier with a stop point (3) and how the (DG) is integrated as a construction of the (DDW). This illustration is shown as an example with 1x brake unit (B) on the wheel of the deflection shaft.

<23>

Figure 7 shows the concept of “bearing-mounted differential gears (DG) with differential lock (DSp) as (DDW) plus integrated brake system (B) as a combination assembly (DDW*)”. The function of the differential lock (DSp) can be controlled, for example, using a hydraulic or electrical actuator. The function of the differential lock is released in the LHS (1) or LHWS (1) if necessary to advantageously compensate for the cable length and is otherwise set as a locking function.

<24>

Figure (7-a) shows an example of 2x wheels for the stop side of the deflection shaft and 2x brake disc systems (B) on the balancer shafts.

<25>

Figure (7-b) shows an example of 1x wheels for 1x deflection and 2x balance shafts and 1x brake system (B) for the deflection shaft.

<26>

Figure 8 shows the design principle of “pulling cable-connected coupling of 2 x differential shafts (DW) plus brake system (B) as a combination assembly DDW*”. The 2 x differential shafts (DW) are coupled via a length-compensating stop assembly either on the load side (4) or on the load side (5) via, for example, a mounted deflection roller (6) or, for example, a load ring eyelet (7). This means that the 4x sling ropes, straps and chains result in 3x sling connections in the direction of the load part (2). This concept is comparable to the concept of differential gears as DDW. This can also be used to advantageously implement additional rope length compensation between the crane hook and the attached load part (2) using the slinging ropes, straps and chains (a). With this solution, the differential lock (DSp) can be easily accessible and therefore advantageously implemented on the load side (4) or load side (5) coupled in relation to length compensation. For this purpose, the coupling point can be set so that the coupling point no longer allows a change in the rope position to the coupling point. There are certainly a variety of solutions for this, such as a decouplably pre-tensioned clamping of the 3 ropes at the coupling point or a decouplably pre-tensioned clamping of the length-compensating rope (see above) to the coupling point.

<27>

Figure 9 shows the concept of a “differential shaft (DW) with the same or virtually the same diameter (d) of the differential shaft members or segments plus an integrated brake system (B) as a combination assembly DDW*”. The torque difference desired according to the invention between the stop side (4) and the opposing stop side (5) is achieved or determined here via the different number of stop points per stop side (4) or stop side (5).

<28>

In picture (9-a) 2x slings are drawn on the load side (4) and 1x on the load side (5), so that with an assumed equal tensile force per sling, a torque load in a ratio of 2 to 1 is applied to the diameter-related constant or quasi-constant differential shaft (DW ) results.

<29>

In picture (9-b) 3x to 2x sling straps are shown on the load side (4) to the load side (5) plus 1x brake system (B) as a concept DDW*.

<30>

In picture (9-c) 1x to 1x sling ropes are drawn on the load side (4) to the load side (5), whereby on the load side (5) a doubling of the sling ropes towards the load part (2) is realized via a sling node (8). which creates a ratio of 2:1 stops on the load side (5) to the load side (4). For example, 2x load ropes can simply be attached to the attachment node (8), which in turn are attached to the load part (2).

<31>

In picture (9-d), a traverse (9) acts instead of the anchor point (8) in picture (9-c) to achieve 3 anchor points and thus an unequal moment load distribution of the DDW* between the load side (4) and (5). .

<32>

In picture (9-e), instead of the stop node (8), the deflection roller (6) or a load ring eyelet (7) as shown in picture 8 acts in order to achieve 3x stop points for the load part (2).

<33>

Figure 10 shows the DDW* concept with a common differential shaft (DW) plus an integrated brake system (B) with different diameters (d1, d2) of the DW segments as a DDW* combination assembly wound in opposite directions.

<34>

Picture (10-a) shows 1x a 3-series differential shaft (DW), mounted on one side (L) and with 1x brake (B) as DDW* with pull cable sides (4) and (5) wound in opposite directions.

<35>

Picture (10-b) shows 1x a 3-series differential shaft (DW), mounted on one side (L) and with 1x brake (B) as DDW* with tension band sides (4) and (5) wound in opposite directions.

<36>

Picture (10-c) shows 1x a 3-series differential shaft (DW), bearings on both sides (L) and with 1x brake (B) as DDW* with pull cable sides (4) and (5) wound in opposite directions.

<37>

Picture (10-d) shows 1x a 3-series differential shaft (DW), bearings on both sides (L) and with 1x brake (B) as DDW* with tension band sides (4) and (5) wound in opposite directions.

<38>

For concepts where direct rope length compensation or a rope length change of the stops relative to each other via the LHS (1), LHWS (1) is not possible, it may be advisable to be able to adjust the rope lengths on the respective rope.

<39>

Figure 11 shows the concept “DDW* with coupled differential shafts (DW) plus integrated braking system (B) with different diameters (d1, d2) of the DW segments with coupling links (K)”.

<40>

Coupling links (K) as connecting components in Figures (11-a) and (11-b) are, for example, a chain, a toothed belt or V-belt; in Figure (11-c) the coupling link is a coupling, which may be advantageously released to adjust the cable length and otherwise locks, and in Figure (11-d) a spur gear assembly (V) with an integrated braking system (B) is the frictionally connecting link Differential shafts (DW). More than 2x differential shafts (DW) can also be connected via coupling links (K).

<41>

Sling ropes or sling load straps can also be fixed to a wheel body or shaft segment in half their length and then wound symmetrically outwards as a double rope or on top of each other as a double load strap, so that one load side (4) or (5) can be used by a DW coil wound in this way, for example. Remove segment 2x stop connections.

QUOTES INCLUDED IN THE DESCRIPTION

This list of documents listed by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 202010001499 [0002]

Claims (13)

Load-lifting system LHS (1) or load-lifting-turning system LHWS (1) according to Figure 1 with the functionality according to the invention for building or storing or ensuring an energetically usable torque potential via the construction principle of a torque -Difference scale (DDW) as an integrated functional unit and this in combination with brake functionality (B) in the LHS (1) or LHWS (1). This common functional assembly consisting of (DDW) and (B), hereinafter referred to as functional assembly (DDW*), with the functions of a torque-difference balance including an integrated brake (B) or integrated braking system (B) is an essential feature of the invention LHS (1) or LHWS (1). The used or usable function of the balance or torque balance with counter-pulling and wound stop side (4) and stop side (5) is an additional component of the LHS (1) or LHWS (1) or (DDW*) according to the invention Claim 1 . The use of truss solutions (see Figure 2) including at least 1x LHS (1) or LHWS (1) is hereby also claimed under patent law. Load-lifting system (LHS) (1) or load-lifting-turning system (LHWS) (1) according to Claim 1 as a concept of a universal load-lifting system (ULHS*) according to Figure 3 combined with a preset and/or controllable lifting function system (HS*), which also has integrated braking functionality. The insertion, the functional positioning of the brakeable, lockable lifting system (HS*) can take place on the level between (DDW*) and the load pickup point (3) towards the crane hook or the functional positioning of the lifting system (HS*) can take place on the level between the Assembly (DDW*) and the load part (2) connected to it in terms of stops. The lifting system (HS*) can, for example, be sufficiently dimensioned in terms of motor for the motorized stroke up and down of the load part (2) or the motor drive power of the lifting system is, for example, limited to the function of tightening the sling connections, e.g. the slinging ropes, in the tightening setup mode and that Lowering under load can, for example, be carried out against the braking functionality of the brake function integrated in the (HS*) or by means of, for example, a single-acting hydraulic cylinder with spring return, the use of a motor within the lifting system (HS*) can even be dispensed with for a simple concept. With this combination of (DDW*) plus (HS*) = (ULHS*) according to the invention, it is possible to lift the load part (2) to be raised or lowered or lowered, regardless of the functional scope of the crane system carrying this combination, for example using high-quality creep mode to move. Universal load lifting system (ULHS*) in accordance Claim 2 , whereby, according to Figure 4, traverse concepts are used with a brakeable lifting function system (HS*), whereby the (HS*) works on the principle of a tensile load lifting shaft (ZHW*), where the ends of the load ropes, belts, chains, for example (DDW*) can be fixed on a common shaft or on mechanically coupled shafts and can be tightened or lowered with the same path or speed, so that the load part (2) can be raised or lowered in an orientationally stable manner via the (ZHW*). In picture (4-a) the concept is shown sketched with a horizontal tensile load lifting shaft (ZHW*) and in picture (4-b) the concept is drawn with a vertical tensile load lifting shaft (ZHW*). Universal load lifting system (ULHS*) in accordance Claim 2 , whereby, according to Figure 5, traverse concepts are used with a brakeable lifting function system (HS*), whereby the (HS*) works on the principle of a brakeable linear lifting drive (LHA*) or linear lifting drive (LHA*), where the ends of the (DDW*) load ropes, straps, for example, are coupled by means of a common fixed stop and can be braked, blocked, tightened or lowered with the same distance or speed. Load-lifting system (LHS) (1) or load-lifting-turning system (LHWS) (1) or universal load-lifting system (ULHS*) in accordance with Claim 1 until Claim 4 , which are additionally equipped according to the invention in combination with a load profile recording tool. The data collection of the load profile of the (LHS) (1) or load-lifting-turning system (LHWS) (1) or (ULHS*) for the consistent and correct determination of the “theoretical remaining useful life of crane systems” is ensured by means of calibrated sensors to be measured and secured in terms of data technology, in reference to the operated crane system, to be stored in the load profile recording tool integrated in combination according to the invention and the relevant data collected is to be made available via interface functions for further data transmission. Construction principle of the functional assembly DDW* according to the invention according to Figure 6 with the concept of a differential gear (DG) mounted on bearings as DDW plus an integrated brake system (B) as a combination assembly DDW* and according to the text, sections <18> to <22>. Construction principle of the functional assembly DDW* according to the invention by coupling 2x differential shafts (DW) using pull cable connections ner coupling of the differential shafts (DW) via the load side (4) or via the load side (5) as shown in the exemplary illustration in Figure 7 plus the integrated brake system (B) and as per text sections <23> to <25>. Construction principle of the functional assembly DDW* according to the invention Claim 6 until 7 in conjunction with the integrated function of a differential lock (DsP) as an option according to Figure 7 and Figure 8 and according to text sections <23> and <26>. Construction principle of the functional assembly DDW* according to the invention according to Figure 9 with the concept as a differential shaft (DW) with the same or virtually the same diameter (d) of the differential shaft members or segments plus an integrated braking system (B) as a combination assembly DDW*. The torque difference of the DDW* is ensured by means of different numbers of stops on the oppositely pulling or wound load sides (4) and (5) of the DDW* and see text sections <27> and <32>. Construction principle of the functional assembly DDW* according to the invention according to Figure 10 with the concept of common differential shafts (DW) with different diameters (d1, d2) of the DW segments plus integrated braking system (B) and see text sections <33> and <38>. Construction principle of the functional assembly DDW* according to the invention according to Figure 11 with the concept of coupled differential shafts (DW) plus integrated brake system (B) with different diameters (d1, d2) of the DW segments with coupling links (K) and see text sections <39> and <41>. Rope length setting concept (SEK*), which uses (function carrier see picture (4-b)) of a (ZHW*) plus motor brake unit (M/B) the rope ends of one of the 2 load sides, which are deflected via deflection rollers (U). (4) or (5) can be rolled up or unrolled together and at the same rope speed or can be subtracted or added to the working space of the LHS (1) or LHWS (1) and thus the oppositely pulling load sides (4) and (5) of the LHS ( 1) or LHWS (1) according to the invention can be set up or aligned together to tighten the rope towards the load part (2). The motor brake unit (M/B) should function in a blocking manner when not activated or in the basic position. Instead of the ropes mentioned, chains or load straps are also included in this claim. All combination solutions according to the Claims 1 until 12 .

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