Friction-based counterweight mechanism

Abstract

A friction-based counterweight mechanism for coupling with a closure flap to assist the opening and closing of the closure flap for at least one section of a path between a fully closed position and a fully open position of the closure flap, wherein the counterweight mechanism comprises: an elongated element positioned on a longitudinal axis extending between the proximal and distal ends of the counterweight mechanism, the elongated element having a circumferential surface and a proximal end for coupling with either the closure flap or a vehicle body;A runner element comprising a body and at least one friction element attached to the body, wherein the runner element is positioned on the longitudinal axis for reciprocating movement along this axis and for forming contact between the at least one friction element and the circumferential surface, the contact serving to generate a frictional force in a first region along the longitudinal axis and in a second region along the longitudinal axis; and a support element coupled to the runner element at a proximal end for coupling at a distal end to, for example, a vehicle body or the closure flap, wherein the support element serves to guide the reciprocating movement. The friction-based counterweight mechanism can be designed as part of a preload strut, such as a shock absorber.

Description

AREA

[0001] This disclosure relates to a friction-based counterweight system for a closure flap. BACKGROUND

[0002] Some vehicles are equipped with a closing flap, such as a tailgate, which is driven between an open position (position 2) and a closed position (position 1) using an electric drive system. Holding systems have been proposed to equip such vehicles with the ability to assist the operator of the closing flap in maintaining a third position (or position 2) in a holding position during opening and closing operations, thus counteracting the weight of the closing flap itself. Without these holding systems, the closing flap can fall back down at the upper end of its operational opening range due to the weight of the flap exerting a closing torque greater than the opening torque provided by the electric drive system.Such proposed holding systems are in some cases complex and expensive and cannot provide adequate fail-safe modes (in the event of an electric motor malfunction or power loss) while maintaining reasonable manual effort from the operator. Furthermore, a need is recognized to provide a counterweight mechanism that can efficiently adjust the counterweight force to customer requirements for different weights and configurations (e.g., different centers of gravity) of the closing flap, including the ability to provide a third position for holding or stop-and-hold functionality of the closing flap.

[0003] Further disadvantages of current holding systems include aspects of their expansive shapes that consume valuable vehicle cargo space, the requirement to have additional lifting support systems in tandem, such as gas springs and other counterweight mechanisms, an unacceptable impact on manual opening and closing efforts requiring greater manual force from the operator at the flap handle, undesirable force peaks that do not provide smoother manual force / torque curves, the requirement to use vehicle battery power to maintain the third position in the holding position, and / or temperature effects that lead to variable manual effort required from the operator due to fluctuations in ambient temperature.

[0004] It is recognized that continuously applied forces in a counterweight mechanism can be problematic due to variations in geometry and / or operator positioning during the full lifting and lowering cycle of a gate flap, including the ability to provide the third holding position where desired. SUMMARY

[0005] It is an object of the present invention to provide a counterweight mechanism that avoids or mitigates at least one of the disadvantages described above.

[0006] Further disadvantages of current holding systems include aspects of their protruding shapes that consume valuable vehicle cargo space, the requirement for additional lifting assistance systems in tandem, such as gas springs and other counterweight mechanisms, an unacceptable impact on manual opening and closing efforts requiring greater manual force from the operator at the flap handle, undesirable force peaks that do not provide smoother manual force / torque curves, the requirement to use vehicle battery power to maintain the third position in the holding position, and / or temperature effects that lead to variable manual effort from the operator due to fluctuations in ambient temperature. In contrast to current systems, a friction-based counterweight mechanism is provided for coupling with a locking flap.to assist in opening and closing the closure flap for at least one segment of a path between a fully closed position and a fully open position of the closure flap, wherein the counterweight mechanism comprises: an elongated element positioned on a longitudinal axis extending between the proximal and distal ends of the counterweight mechanism, the elongated element having a circumferential surface and a proximal end for coupling with either the closure flap or a vehicle body; a runner element having a body and at least one friction element attached to the body, the runner element being positioned on the longitudinal axis for reciprocating movement along this axis and for forming contact between the at least one friction element and the circumferential surface,wherein the contact serves to generate a frictional force in a first area along the longitudinal axis and in a second area along the longitudinal axis; and a support element coupled at a proximal end to the runner element for coupling at a distal end to, accordingly, a vehicle body or the closing flap, wherein the support element serves to guide the reciprocating movement. The friction-based counterweight mechanism can be designed as part of a preload strut, such as a shock absorber.

[0007] A first aspect provided is a friction-based counterweight mechanism for coupling with a closure flap to assist the opening and closing of the closure flap for at least one section of a path between a fully closed position and a fully open position of the closure flap, wherein the counterweight mechanism comprises: an elongated element positioned on a longitudinal axis extending between the proximal and distal ends of the counterweight mechanism, the elongated element having a circumferential surface and a proximal end for coupling with either the closure flap or a vehicle body;a runner element comprising a body and at least one friction element attached to the body, wherein the runner element is positioned on the longitudinal axis for reciprocating movement along this axis and for forming contact between the at least one friction element and the circumferential surface, the contact serving to generate a frictional force between the circumferential surface and the friction element; and a support element coupled to the runner element at a proximal end for coupling at a distal end to, for example, a vehicle body or the closure flap, wherein the support element serves to guide the reciprocating movement.

[0008] A second aspect provided is a friction-based counterweight mechanism for coupling with a closure flap to assist in opening and closing the closure flap for at least one section of a path between a fully closed position and a fully open position of the closure flap, wherein the counterweight mechanism comprises: a housing with a proximal end for coupling the counterweight mechanism to either the closure flap or a vehicle body and with a distal end for coupling the counterweight mechanism to either the vehicle body or the closure flap, respectively;an elongated element mounted in the housing and positioned on a longitudinal axis extending between the proximal and distal ends of the housing, the elongated element having a circumferential surface and a proximal end coupled to the proximal end of the housing; a runner element comprising a body and at least one friction element attached to the body, the runner element being positioned on the longitudinal axis for reciprocating movement along it and for forming contact between the at least one friction element and the circumferential surface, the contact serving to generate a first friction force in a first region along the longitudinal axis and a second friction force, different from the first, in a second region along the longitudinal axis, the first region being spaced apart from the second region along the longitudinal axis;and a support element coupled at a proximal end to the runner element and at a distal end to the distal end of the housing, which serves to guide the back-and-forth movement.

[0009] A third aspect provided is a friction-based counterweight mechanism for coupling with a closure flap to assist the opening and closing of the closure flap for at least one section of a path between a fully closed position and a fully open position of the closure flap, wherein the counterweight mechanism comprises: an elongated element positioned on a longitudinal axis extending between the proximal and distal ends of the counterweight mechanism, the elongated element having a circumferential surface and a proximal end for coupling with either the closure flap or a vehicle body;A runner element comprising a body and at least one friction element attached to the body, wherein the runner element is positioned on the longitudinal axis for reciprocating movement along this axis and for forming contact between the at least one friction element and the circumferential surface, wherein the contact serves to generate a first frictional force in a first region along the longitudinal axis and a second frictional force, different from the first frictional force, in a second region along the longitudinal axis, the first region being spaced apart from the second region along the longitudinal axis; and a support element coupled to the runner element at a proximal end for coupling at a distal end to, for example, a vehicle body or a closure flap, wherein the support element serves to guide the reciprocating movement.

[0010] Further aspects, including operating procedures and other embodiments of the foregoing aspects, will become apparent based on the following description and the drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0011] Reference is made only to the attached drawings, which show:

[0012] Fig. 1. A side view of a vehicle with a locking flap arrangement is shown.

[0013] Fig. 2 an alternative embodiment of the vehicle of Fig. 1 is,

[0014] Fig. 3 is a graphical representation that shows the torque operating data as a function of the degree of opening for a friction counterweight mechanism of the in Fig. The closure flap arrangement shown in 1 shows,

[0015] Fig. 4 is an exemplary counterweight mechanism with a variable friction device, which is connected to the one in Fig. The closure flap arrangement shown in 1 is arranged in an assembly,

[0016] Fig. 5 embodiments with alternative cross-section of the in Fig. The counterweight mechanism shown in section 4 demonstrates

[0017] Fig. 6 an alternative embodiment of the in Fig. The counterweight mechanism shown in section 4 demonstrates

[0018] Fig. 7a, Fig. 7b further details of the in Fig. The counterweight mechanism shown in section 4 illustrates this.

[0019] Fig. 8 an exemplary application of the in Fig. The counterweight mechanism for a prestressing strut shown in section 4 is shown.

[0020] Fig. 9 further details of the in Fig. The prestressing strut shown in section 8 indicates

[0021] Fig. 10 an exploded view of the prestressing strut of the Fig. 8 is,

[0022] Fig. 11 an exemplary operation of the in Fig. The counterweight mechanism shown in section 4 demonstrates

[0023] Fig. Figures 12a, b, c show exemplary changes in frictional force due to variations in at least one friction configuration parameter.

[0024] Fig. 13 an alternative embodiment of the vehicle with a closure flap arrangement of the Fig. 1 shows,

[0025] Fig. 14a, b, c, d alternative embodiments of the prestressing strut according to Fig. 10 show,

[0026] Fig. 15a another alternative embodiment of the one described in the Fig. 4 and Fig. The counterweight mechanism shown in section 6 demonstrates

[0027] Fig. 15b another alternative embodiment of the one described in the Fig. 4 and Fig. The counterweight mechanism shown in section 6 demonstrates

[0028] Fig. 16a, b another alternative embodiment of the one described in the Fig. 4 and Fig. The counterweight mechanism shown in section 6 demonstrates

[0029] Fig. 17a, b another alternative embodiment of the one described in the Fig. 4 and Fig. The counterweight mechanism shown in section 6 demonstrates

[0030] Fig. 18a another alternative embodiment of a front view of a runner element of the in the Fig. 4 and Fig. The counterweight mechanism shown in section 6 demonstrates

[0031] Fig. 18b another alternative embodiment of a front view of a runner element of the in the Fig. 4 and Fig. The counterweight mechanism shown in section 6 demonstrates

[0032] Fig. 18c another alternative embodiment of a side view of a runner element of the in the Fig. 4 and Fig. The counterweight mechanism shown in section 6 demonstrates

[0033] Fig. 19 another alternative embodiment of the one described in the Fig. 4 and Fig. The counterweight mechanism shown in section 6 demonstrates and

[0034] Fig. 20 another alternative embodiment of the in the Fig. 4 and Fig. The counterweight mechanism shown in section 6 is shown. DETAILED DESCRIPTION OF EXAMPLE EXECUTION FORMS

[0035] In this description and the claims, the use of the articles "a", "an", or "the" is not provided in relation to an element in order to exclude the possibility of including multiple elements of that element in some embodiments. It is understood by a person skilled in the art that it would be possible for multiple elements of this element to be included in at least some embodiments in this description and the accompanying claims. Likewise, the use of a plural form in relation to an element is not provided in order to exclude the possibility that one element of this element is included in some embodiments. It is understood by a person skilled in the art that it would be possible for one element of this element to be included in at least some embodiments in this description and the accompanying claims. Examples of the closure flap arrangement 12

[0036] A counterweight mechanism is provided that can be advantageously used with vehicle shutter doors to provide fail-safe opening and closing modes in the event of a power actuator malfunction or disconnection, particularly for land-based, sea-based, and / or air-based vehicles. Other applications of the counterweight mechanism, generally for shutter doors both within and outside of vehicle applications, advantageously include assisting in the optimization of the overall holding forces and manual effort required to operate the shutter door. It is also recognized that the counterweight mechanism examples provided below can be advantageously used as the sole means of opening and closing shutter doors or advantageously in combination (e.g., in tandem) with other shutter door preloading elements (e.g.,...spring-loaded pivot joints, preload struts, etc.) can be used. In particular, the counterweight mechanism can be friction-based and can be used to provide a holding force (or holding torque) for the closing flap, as further described below. It is further recognized that the counterweight mechanism can be equipped with a preload element. 37 , such as a spring-loaded compression strut (strut), integrated and / or provided as a component of a closing flap assembly, as further described below. It is recognized that the preload element 37 , which includes the friction-based counterweight mechanism, can be implemented as a compression strut (see the Fig. 8 and Fig. 14a, b, c as exemplary types of compression struts / struts). The compression strut can be of the preload type (e.g., a spring and / or a gas charge providing the preload). The compression strut can be of the electromechanical type (e.g., driven by an optional integrated motor arrangement, with a spring and / or a gas charge providing preload).

[0037] With reference to Fig. 1 is a vehicle 10 with a bodywork 11 shown, which includes one or more locking flaps 14 features an exemplary configuration of the closure flap. 14 is a closure flap arrangement 12 , which employ a friction-based counterweight mechanism 15 (e.g. in a prestressing element) 37 (included, for example, a compression strut or a shock absorber) and a locking flap drive system 16(which includes, for example, an electrically driven motor / drive). For the vehicles 10 can the locking flap 14 a partition wall or door that is in front of an opening 13 , which are used for entering and exiting the interior of the vehicle 10 It is used by people and / or cargo, is typically hinged, but sometimes also attached by other mechanisms, such as rails. It is also recognized that the closing flap 14 as an access panel or flap for vehicle systems 10 , such as engine rooms, and also for conventional vehicle trunks 10 of the vehicle type. The locking flap 14 can be opened to provide access to the opening 13 to provide, or be closed to allow access to the opening 13to secure or otherwise restrict it. It is also recognized that there are one or more intermediate holding positions of the locking flap. 14 between a fully open position and a fully closed position, as can be achieved at least partially through the counterweight mechanism. 15 will be provided as described below. The counterweight mechanism 15 This can, for example, be the preloading movement of the locking flap. 14 away from one or more intermediate holding positions, which are also referred to as third-position holds (TPHs) or stop-N-holds once positioned there. It is also recognized that the counterweight mechanism 15 as a component of the closure flap assembly 12 It can be provided that the component of the counterweight mechanism 15 from one or more prestressing struts 37can be separated. The functionality of the friction-based counterweight mechanism 15

[0038] The locking flap 14 can be opened manually and / or via the locking flap drive system 16 be electronically driven, with the driven closure flaps 14 They can be found in minibuses, luxury vehicles, SUVs, and the like. Furthermore, one feature of the locking flap is... 14 , that due to the weight of the material used in the manufacture of the closure flap 14 materials used; any form of power-assisted opening and closing mechanism (or mechanisms) is used to enable the opening and closing operation of the locking flap by an operator (e.g. the driver of the vehicle). 14to promote. The power-assisted opening and closing mechanism(s) is / are supported by the counterweight mechanism. 15 , any prestressing elements 37 (e.g. spring-loaded pivot joints, spring-loaded struts, gas-loaded struts, electromechanical struts, etc.) and the flap drive system 16 , when it is part of the closure flap assembly 12 is used, created so that the counterweight mechanism 15 is configured to provide a friction-based holding torque (or friction-based holding force) that holds the plate around the third position against the weight of the closure flap in at least one section of the opening / closing path. 14 It works to maintain the position of the locking flap. 14 to support holding the third position. It is recognized that an electromechanical strut has a leadscrew. 140(see the Fig. 14a, b, c) may have a rotor element that is either actively (i.e., driven) by a (e.g., electric) motor or passively driven, so that the leadscrew is free to rotate appropriately about its longitudinal axis, but is not actively driven by a motor. It is recognized that a rotor element 45 (see the Fig. 4, Fig. 6) can be coupled. It is recognized that the friction-based counterweight mechanism 15 as an independent counterweight mechanism for the locking flap 14 may be configured and / or as a component of a prestressing element 37 It can be configured (e.g., it can be included as an internal component of a strut).

[0039] The counterweight mechanism 15is configured, for example, to provide a friction-based holding torque (or a friction-based holding force) that holds against the weight of the closure flap. 14 acts to maintain the open position of the locking flap 16 to maintain in a section of the path defined as a holding range of a third (e.g., intermediate) position. As discussed, the friction-based holding torque (or friction-based holding force) can be applied over the full range of motion of the closure flap. 14 (e.g. in size) can be varied, thereby creating an advantage in generating the friction-based holding torque (or friction-based holding force), the magnitude of which can be varied in different sections of the full range of motion of the closure flap. 14 Variable is (see e.g. the Fig. 12a, b, c).

[0040] In another example, the counterweight mechanism 15configured to provide a friction-based torque (or friction-based force) that acts against the opening torque (or opening force) of any preload elements in at least one section of the path between the intermediate holding position and the fully closed position. 17 or the closing flap drive system 16 It works. In another example, the counterweight mechanism 15 configured to provide a friction-based torque (or friction-based force) that acts against any closing torque (or any closing force) of any preloading elements in at least one section of the path between the intermediate holding position and the fully closed position. 37 or the closing flap drive system 16It works. As discussed, the friction-based holding torque (or friction-based holding force) can be applied over the full range of motion of the closure flap. 14 (e.g. in size) can be varied, thereby providing the advantage of generating the friction-based holding torque (or friction-based holding force), the magnitude of which can be varied in different sections of the full range of motion of the closure flap. 14 variable, is created (see e.g. the Fig. 12a, b, c).

[0041] In another example, the counterweight mechanism 15 configured to provide a friction-based torque (a friction-based force) that acts against the opening torque (the opening force) of any preload elements in at least one section of the path between the intermediate holding position and the fully open position. 37 or the closing flap drive system 16It works. In another example, the counterweight mechanism 15 configured to provide a friction-based torque (or friction-based force) that acts against any closing torque (or any closing force) of any preloading elements in at least one section of the path between the intermediate holding position and the fully open position. 37 or the closing flap drive system 16 It works. As discussed, the friction-based holding torque (or friction-based holding force) can be applied over the full range of motion of the closure flap. 14 (e.g. in size) can be varied, thereby providing the advantage of generating the friction-based holding torque (or friction-based holding force) that is present in different sections of the full range of motion of the closure flap. 14 is created in variable size (see e.g. the Fig. 12a, b, c).

[0042] In another example, the counterweight mechanism 15 configured to provide a friction-based torque (or friction-based force) that acts against the opening torque (or opening force) of any preload elements in at least one section of the path between the fully open position and the fully closed position. 37 or the closing flap drive system 16 It works. In another example, the counterweight mechanism 15 configured to provide a friction-based torque (or friction-based force) that acts against the closing torque (or closing force) of any preloading elements in at least one section of the path between the fully open position and the fully closed position. 37 or the closing flap drive system 16It works. As discussed, the friction-based holding torque (or friction-based holding force) can be applied over the full range of motion of the closure flap. 14 (e.g. in size) can be varied, thereby providing the advantage of generating the friction-based holding torque (or friction-based holding force) that is present in different sections of the full range of motion of the closure flap. 14 is created in variable size (see e.g. the Fig. 12a, b, c).

[0043] In Fig. 3 is an exemplary initial curve against the center of gravity of the closure flap with the axis of rotation 18 (see Fig. 1) Measured torque T (the quantity) against the degree of opening D (0 D represents the fully closed position, while 80 D represents the fully open position) is shown for the torque T that was measured when the flap was closed. 14is positioned at a position of the degree of opening D. It is stated that curve C1 represents the measure of the torque T over a degree of opening D, determined solely by the weight of the closing flap. 14 The curve C2 represents a total counterweight torque T (which is contributed, for example, by the preload element(s)). 37 and / or the closing flap drive system 16 (contributes) above a degree of opening D without any contribution from the friction-based counterweight mechanism 15 The curve C3 represents a total counterweight torque T (which is e.g. due to the preload element(s)) 37 and / or the closing flap drive system 16 (contributes) above a degree of opening D with a contribution from the friction-based counterweight mechanism 15 represented. As can be seen, the frictional force FR (see Fig. 4) the friction-based counterweight mechanism 15 Between the closed position (measured at 0D) and the open position approaching 40D, it is configured to contribute little to no substantial frictional force FR. Between approximately 40D and 80D, curves C2 and C3 diverge due to the friction-based counterweight mechanism. 15 is configured to generate the frictional force FR and thereby provide the complement of the frictional force FR, which is equivalent to the frictional torque T, to promote the combined counterweight torque T (including the torque T of the frictional force FR) being greater than the weight of the closure flap. 14 The torque itself is provided by curve C1. To be clear, curve C2 represents the counterweight torque T without including the friction-based counterweight mechanism. 15, therefore the counterweight torque T provided along curve C2 is smaller than the weight torque T of the closing flap 14 This is provided along curve C1 as the degree of opening increases from approximately straight to the fully open position at approximately 60 D and continues at approximately 80 D. It is recognized that the closing flap 14 as such, for any degree of opening greater than approximately 60 D, would sink if the friction-based counterweight mechanism 15 as part of the closure flap assembly 12 is not included (which is represented by curve C2).

[0044] As will be shown below, the friction-based counterweight mechanism can be used. 15 generated frictional force FR (see Fig. 4) be configured to switch between one or more sections between the fully open position and the fully closed position (in dashed lines) of the closure flap 14 (see Fig. 1) to vary in size.

[0045] As can be seen, curve C1 lies openly below curve C2 between 0 D and approximately 20 D, representing that the weight of the closure flap 14 The provided torque T is greater than the total counterweight torque T (which is provided, for example, by the preload element(s)). 37 and / or the closing flap drive system 16 (contributes) is, therefore the closure flap 14 is preloaded to the closed position unless an additional opening torque is provided by manual effort from the vehicle operator and / or an additional opening torque is provided by a kickstart spring53 (see Fig. 7b) is provided, as is known in the art. Once the 20D open position is reached to be fully open, curve C2 is larger than curve C1 until approximately the 58D open position is reached, at which point curve C2 and curve C1 intersect (designated by “THP”), which is the holding point of the third position (where, for example, the total counterweight torque and the plate weight torque are balanced) for the exemplary configuration of the closure flap. 14 Defined. Any positioning of the closure flap. 14 Beyond the approximately 58 D open position, the locking flap would sink (fall back down to the closed position). 14 lead to this, as the weight of the locking flap causes 14 The provided torque T is greater than the total counterweight torque T (which is provided, for example, by the preload element(s)). 37and / or the closing flap drive system 16 (contributes) is, therefore the closure flap 14 The flap is preloaded back to the closed position unless an additional opening torque is created by manual effort from the vehicle operator to maintain the closure flap. 14 to support the movement back to the holding point THP of the third position.

[0046] Alternatively and advantageously for curve C3, as soon as the weight of the closure flap 14 The created torque T begins (at about 40 D) to counteract the total counterweight torque T, the resistance friction torque generated by the counterweight mechanism. 15 is created, in addition to the total counterweight torque T (which is created, for example, by the preload element(s)) 37 and / or the closing flap drive element 16The added amount contributes to the total counterweight torque T (which is provided, for example, by the preload element(s)). 37 , the friction counterweight mechanism 15 and / or the closing flap drive system 16 (contributed) greater than the torque T caused by the weight of the closure flap 14 is provided to hold and thereby prevent the sinking for the open positions of the closure flap. 14 to prevent in a holding range of the third position (shown by the hatched area TPR between curves CC and C1) between approximately 40° and fully open at approximately 80°. As such, it can be seen that if the friction-based counterweight mechanism 15 is used to prevent the provided total counterweight torque T from being smaller than that caused by the weight of the closure flap. 14The provided torque T is used, consequently causing the drop above the D degree open upper range of the movement of the closure flap. 14 is advantageously prevented.

[0047] In addition to the above, another example is the counterweight mechanism. 15 configured to provide a friction-based torque (or friction-based force) that acts against the closing torque (or closing force) provided by the weight of the closure flap in at least one section of the path between the intermediate holding position and the fully closed position. 14 is created. In another example, the counterweight mechanism is... 15configured to provide a friction-based torque (or friction-based force) that acts against the closing torque (or closing force) provided by the weight of the closure flap in at least one section of the path between the intermediate holding position and the fully open position. 14 It is created, and it takes effect. In another example, the counterweight mechanism... 15 configured to provide a friction-based torque (or friction-based force) that acts against the closing torque (or closing force) provided by the weight of the closure flap in at least one section of the path between the fully closed position and the fully open position. 14 What is created has an effect.

[0048] As discussed above, the counterweight mechanism 15It is also configured to provide an opening torque (also referred to as an opening force) that acts against the weight of the closing flap. 14 acts to close the locking flap 14 to pre-load the open position. Therefore, it is considered advantageous that the counterweight mechanism 15 is configured to provide a resistance-based opening torque (or a resistance-based opening force) that acts against the weight of the closure flap 14 acts to close the locking flap 14 to preload towards the open position (e.g., away from the fully closed position and preloaded towards the open position), and also to create a closing torque (also referred to as a closing force) that can be matched to the weight of the closing flap. 14 acts to close the locking flap 14to preload towards the closed position (e.g., moving away from the fully open position and preloaded towards the closed position). A discussion of how the resistance elements of the counterweight mechanism 15 The configurations are further provided below. The configuration of the closure flap arrangement 12

[0049] What the vehicles 10 As far as the locking flap is concerned, 14 a tailgate, as in Fig. 1 shown, or it can be any other type of closure flap 14 be, for example, an upward-swinging vehicle door (i.e., what is sometimes called a gull-wing door) or a conventional type of door that is hinged at a forward-facing or rearward-facing edge of the door, thus allowing the door to swing away from (or towards) the opening. 13 in the bodywork 11 of the vehicle 10to swing (or slide). Sliding door versions of the locking flap are also available. 14 and convertible top door designs of the locking flap 14 Considered, sliding doors can be a type of door that is opened by horizontal or vertical sliding, whereby the door is either mounted on a track or hangs from a track, creating a larger opening. 13 for the equipment that goes through the opening 13 Loading and unloading without obstructing access. Convertible doors are a type of door located on top of the vehicle. 10 sits and unfolds in some way to cover the opening 13 To provide access for the vehicle's occupants (e.g., a car's convertible top, an aircraft's canopy, etc.). Convertible top doors can be attached to the body. 11the vehicle may be connected to the front, side or rear of the door (e.g., pivoted on a defined axis of rotation and / or connected for movement along a rail), as the application allows.

[0050] Once again in Fig. 1 is merely an example in the context of a vehicle application of a closure flap. 14 It is movable between a closed position (shown in a dashed outline) and an open position (shown in a solid outline). In the illustrated embodiment, the closing flap pivots. 14 between the open position and the closed position around a rotational axis 18 , preferably horizontal or otherwise parallel to a support surface 9 of the vehicle 10 is configured. In other embodiments, the axis of rotation can be 18exhibit any other orientation, such as vertical or otherwise at an angle to the support surface 9 of the vehicle 10 extending outwards. In other embodiments, the closing flap can 14 move the locking flap in a manner other than pivoting 14 It can, for example, be moved along a predetermined track or can be subjected to a combination of translation and rotation between the open and closed positions.

[0051] In Fig. 1. As discussed above, the examples of the counterweight mechanism can 15 , which below refers to the closure flap arrangement 12 They are presented as the only means of opening and closing support to prevent the locking flaps from sinking. 14 can be used themselves (see Fig. 2), or they can be combined (e.g. in tandem or otherwise integrated) with one or more other flap pretensioning elements 37 (e.g. spring-loaded pivot joints, struts such as gas springs or spring-loaded struts, etc.) are used, which provide a primary connection of the closure flap. 14 with the vehicle body 11 at a swivel joint 18 , 38 (see Fig. 1) create. In the general operation of the closure flap 14 can the closing flap drive system 16 to a distal end of a connecting rod 35 (which is also referred to as a lever mechanism or lever arm or lever element) coupled, which is used to open the locking flap 14 as a secondary connection between the locking flap and the vehicle body 11 to connect so that the locking flap preload element 37and the connecting rod 35 pivotable at spaced locations on the closure flap 14 They can be attached as shown. In this way, the other end of the connecting rod connects. 35 the locking flap 14 at a swivel joint 36 swiveling. It is recognized that the connecting rod 35 It can even be configured, upon request, as a non-preloading element (e.g., a solid rod) or as a preloading element (e.g., a gas- or spring-assisted extension strut).

[0052] Once again in Fig. 1. One or more optional locking flap preload elements can be used. 37 It is intended that the locking flap 14 everywhere in at least one section of the path between the open position and the closed position, pushing towards the open position and holding the locking flap. 14Support in the open position. The locking flap preload elements 37 These could be, for example, extension gas springs that connect to the locking flap at their proximal end. 14 and at its distal end with the vehicle body 11 are pivotably connected. In the embodiment shown, there are two preload elements. 37 (one on the left side of the vehicle) 10 and one on the right side of the vehicle 10 ), however, in the view shown a prestressing element 37 hidden by the other. For example, see Fig. 13, the friction-based counterweight mechanism 15 on one side of the locking flap 14 as a prestressing element 37 with motor drive to the locking flap 14 be coupled so that a support element 52 a leadscrew 140 is (see the Fig. 14a, Fig. 14b), which is achieved by an arrangement of a motor 136 is actively driven, with a second counterweight mechanism 15 in a differently configured prestressing element 37 on the other side of the locking flap 14 is included, so that the second counterweight mechanism 15 through the movement of the locking flap 14 is operated passively.

[0053] If the locking flap 14 As the preload elements move between the open and closed positions, the torques (or forces) exerted by them change. 37 and through the weight of the locking flap 14 even on the locking flap 14 can be exercised. In one embodiment, the closure flap can be 14 exhibit any position between the open and closed positions, where the torque (or force) exerted by the preload elements 37on the locking flap 14 is exerted, the torque (or force) that is (or is) caused by the weight of the closure flap 14 on the locking flap 14 is exerted, cancels out (i.e., the torque or force of the preload element(s)) 37 acts against the weight of the locking flap 14 ). The torque (or force) exerted by the preload elements can be reduced beyond this point (which may be referred to as an equilibrium point or otherwise as the intermediate holding position). 37 The torque (or force) exerted by the weight of the plate 14 is exerted, overcoming the force, which consequently results in a net torque (or net force) away from the closed position, thus causing the closure flap to... 14is preloaded to the open position (i.e., the torque or force of the preloading element(s)) 37 acts against the weight of the locking flap 14 ). At this point, the torque (or force) exerted by the weight of the plate can be considered. 14 The torque (or force) exerted by the preload elements 37 is exerted, overcoming, which consequently results in a net torque (or net force) towards the closed position, whereby the closing flap 14 is pre-loaded towards the closed position. Even when the locking flap is moved. 14 However, the torque or force of the preload element (or elements) acts towards the closed position. 37 against the weight of the locking flap 14 In this way, the effect of the prestressing element (or elements) 37, to provide a torque or force that always acts against the weight of the locking flap 14 It acts (i.e., always provides a closing torque or closing force). It is recognized that the “3rd position hold” can also be referred to as an “intermediate hold position” or a “stop and hold position”.

[0054] In addition to the operation of the optional locking flap preload elements described above 37 can include one or more counterweight mechanisms 15 in addition to the prestressing elements 37 (as in Fig. 1 shown) or in replacement of the prestressing elements 37 (as in Fig. 2 is shown) is provided. Regarding Fig. 1. For example, one or more counterweight mechanisms can be used. 15 They are designed to act to control the movement of the locking flap. 14to maintain the closed position or otherwise restrict the movement of the locking flap 14 to prevent it from remaining in the closed position, i.e., to keep the locking flap in place. 14 to provide support in the open position (e.g., intermediate holding positions and / or the fully open position). One or more counterweight mechanisms. 15 can be attached, for example, to the vehicle body 11 coupled or otherwise attached to the vehicle body 11 be attached and with the locking flap 14 be connected in a swiveling manner.

[0055] If the locking flap 14 moving between the open and closed positions, the torques (or forces) exerted by each counterweight mechanism can 15 , the prestressing elements 37 and through the weight of the locking flap 14 even on the locking flap 14The application of the locking mechanism varies. In one embodiment, the locking flap can 14 exhibit any position between the open and closed positions at which the combined torque (or combined force) exerted by each counterweight mechanism 15 and the prestressing elements 37 on the locking flap 14 The torque (or force) exerted by the weight of the plate 14 The force exerted upon it cancels out the force exerted on it. Above this point (which may be called an equilibrium point or otherwise the intermediate holding position), the combined torque (or combined force) exerted by any counterweight mechanism can be determined. 15 and the prestressing elements 37 on the locking flap 14 The torque (or force) exerted by the weight of the plate 14is exerted itself, overcoming which consequently results in a net torque (or net force) away from the open intermediate position and consequently the movement of the closure flap. 14 restricts to the closed position. At this point, the torque (or force) exerted by the weight of the plate can be reduced. 14 exerted, the combined torque (or combined force) that is (or is) exerted by each counterweight mechanism 15 and the prestressing elements 37 on the locking flap 14 is exerted, overcoming which consequently results in a net torque (or net force) towards the fully closed position and consequently the closure flap. 14 Pre-loaded away from the open intermediate position. Exemplary configurations of the counterweight mechanism 15

[0056] In Fig. Figure 4 is an exemplary configuration of the friction counterweight mechanism. 15 shown, which is an elongated element 40 (e.g. a rod, a tube, etc.) comprising a longitudinal axis 41 defined. The elongated element 40 can along the longitudinal axis 41 a number of different areas 42 , 44 exhibit. It is recognized that these different areas 42 , 44 exhibit various frictional force configuration parameters, such as, but not limited to: a different diameter (the diameter or element width in the area 42 could be, for example, the diameter or element width in the area 44 be different); a different surface roughness 50 , which contribute to the variability of the coefficient of friction between the surface 50 in the various areas 42 , 44and a runner element 45 contributes to, as further described below (the surface roughness in the area 42 could be, for example, due to the surface roughness in the area 44 be different); a different contact surface between the runner element 45 and the contact surface 50 (the contact area in the area 42 could, for example, be from the contact surface in the area 44 be different); and / or have different contact pressures between the runner element 45 and the contact surface 50 (the contact pressure in the area 42 could be due to the contact pressure in the area 44 (may be different). It is recognized that the selection of the geometric configuration and / or the material surface 50 of the elongated element 40 and / or the friction elements 48 of the runner element 45as such, to result in a variability of the frictional force FR (e.g. in magnitude) that is caused by the friction-based counterweight mechanism 15 is generated when the attached locking flap 14 to move between the open and closed positions. A support element 52 can be attached to the locking flap 14 (see Fig. 1) or the vehicle body 11 be coupled at a distal end (e.g. Fig. 7a, Fig. 10) and at a proximal end to the runner element 45 be coupled, and consequently for the relative motion of the runner element 45 along the axis 41 provide. Alternatively, the support element can 532 as a leadscrew 140 be provided for (e.g. Fig. 14a, Fig. 14c), which is attached to one end of the runner element 45 is coupled (e.g. Fig. 14c), so that the runner element 45at the end of the leadscrew 140 around the axis 41 rotates, and / or the (e.g. through a threaded hole) 161 ) through the runner element 45 is coupled (e.g. Fig. 14a), wherein the runner element 45 as such around and along the lead screw 140 rotates when the runner element 45 along the longitudinal axis 41 It is also recognized that the runner element is moving. 45 not on the leadscrew 140 rotates the runner element 45 rather, it moves linearly along the longitudinal axis 41 and linearly along a body of the leadscrew 140 , when the leadscrew 140 around the longitudinal axis 41 and within the threaded hole 161 turns.

[0057] In Fig. Figure 4 merely illustrates a variation of the frictional force FR (e.g., in size) that can be achieved by varying the diameter of the elongated element. 40 is generated, but it is recognized that the different areas could be configured alternatively, as described above and below, to provide the variability (e.g. in magnitude) of the generated frictional force FR.

[0058] Furthermore, in Fig. 4 for the exemplary frictional force variation parameter of the changes in the diameter of the elongated element 40 a varying cross-sectional dimension (e.g. the area) 42 of a first diameter and the area 44 a second diameter) shown, so that the first area 42 a larger cross-sectional dimension (e.g. a larger diameter) than the cross-sectional dimension of the second area 44The intended result of increasing the diameter is to reduce the frictional force FR (e.g., in magnitude) compared to the area. 44 to increase when the runner element 45 in the area 42 moved, (see Fig. 12a, where the frictional force quantity FR is in the range 44 greater than in the area 42 is). The change in frictional force FR as such between the areas 42 , 44 It can also occur due to changes in other friction parameters (e.g., a change in the friction parameter between the areas). 42 , 44 (Besides the diameter, such as a change in the contact area, a change in the coefficient of friction due to a change in surface roughness and / or a change in contact pressure, but not limited to these). In Fig. 12b is for the exemplary frictional force variation parameter of the changes in the diameter of the elongated element. 40 a varying cross-sectional dimension (e.g. the area) 42 of a first diameter and the area 44 a second diameter) shown, so that the first area 42 a smaller cross-sectional dimension (e.g. a smaller diameter) than the cross-sectional dimension of the second area 44 This is the intended result of reducing the diameter, the frictional force FR (e.g., in size) compared to the area. 44 to reduce when the runner element 45 in the area 42 moved, (see Fig. 12b, where the frictional force quantity FR in the range 44 lower than in the area 42 is). The change in frictional force FR (e.g., in magnitude) as such between the areas 42 , 44It can also occur due to changes in other friction parameters (e.g., a change in the friction parameter between the areas). 42 , 44 (Besides the diameter, such as a change in the contact area, a change in the coefficient of friction due to a change in surface roughness and / or a change in contact pressure, but not limited to these). In Fig. 12c is for the exemplary frictional force variation parameter of the changes in the diameter of the elongated element. 40 a varying cross-sectional dimension (e.g. the area) 42 of a first diameter and the area 44 a second diameter and a third area 43 ) shown, so that the first area 42 a smaller cross-sectional dimension (e.g. a smaller diameter) than the cross-sectional dimension of the second area 44 exhibits and the third area 43Furthermore, it has a smaller dimension than the second area. 44 This is the intended result of increasing and then decreasing the diameter, to increase and then decrease the frictional force FR (e.g., in size) as the runner element changes. 45 from the area 42 to the area 44 and then to the area 43 moved (see Fig. 12c), where the frictional force quantity FR is in the range 44 larger than in the areas 42 , 43 is). The change in frictional force FR as such between the areas 42 , 43 , 44 It can also occur due to a change in other friction parameters (e.g., a change in the friction parameter between the areas). 42 , 43 , 44other than the diameter, such as a change in the contact area, a change in the coefficient of friction due to a change in surface roughness and / or a change in contact pressure, but not limited to these).

[0059] The example of changing the diameter of the elongated element is used again. 40 , which in Fig. Figure 4 is shown, with reference to the runner element. 45 (e.g. a cage) that contains a body 46 and one or more friction elements 48 (e.g. a leaf spring) is located on the elongated element 40 positioned and configured to move along the longitudinal axis 41 of the elongated element 40 to move back and forth (e.g., to move TR). The friction element(s) 48 can (can) as in the position on the body 46be configured to be fixed, while also being comparable to the variation in any other selected friction parameter of the different areas. 42 , 44 of the elongated element 40 regarding the body 46 in response to variations in the cross-sectional dimension (e.g., diameter). It is recognized that the cross-sectional dimension can have any desired shape, e.g., circular (e.g., a diameter, as shown), four-sided (e.g., square, rectangular), egg-shaped, or others, as exemplified in Fig. 5 is shown.

[0060] In the Fig. The elongated element supports the example shown in section 4. 40 the runner element 45 on an outer circumferential surface 50 (the runner element 45 is e.g. for the back-and-forth movement on the outer surface 50 of the elongated element 40 (positioned). Fig. 6 is an alternative embodiment of the friction counterweight mechanism 15 shown, which is the runner element 45 exhibits that is located on an inner circumferential surface 50 of the elongated element 40 supported, which is configured as a hollow tube, (the runner element 45 is e.g. for the back-and-forth movement on the inner surface 50 of the elongated element 40 (positioned). Various configurations of the runner element are available. 45 and the elongated element 40 as such for the friction counterweight mechanism 15 considers both different cross-sectional shapes and different internal and / or external circumferential surfaces. 50 for contact with the friction elements 48 includes. In the in Fig. The example shown in section 6 would involve a movement from the area 44 to the area 42to a decrease in the frictional force FR (e.g., of size) due to an increase (i.e., a change) in the friction configuration parameter (e.g., the diameter of the element width) of the areas 42 , 44 of the elongated element 40 lead.

[0061] If the runner element 45 along the elongated element 40 When TR moves, the friction element(s) are therefore located with the surface 50 of the elongated element 40 in contact, consequently generating a frictional force FR (see the Fig. 4 and Fig. 6) due to the combined configuration of the friction configuration parameters (e.g., a selected coefficient of friction, a selected contact pressure, a selected contact area) between the friction element(s) 48 and the surface 50 cause in a cross-sectional area 42with a larger cross-sectional dimension for the outer surfaces 50 (see Fig. 4) The frictional force FR is expected to be greater than in a cross-sectional area 42 with a smaller cross-sectional dimension. Alternatively, in a cross-sectional area 42 with a smaller cross-sectional dimension for the inner surfaces 50 (see Fig. 6) expects the frictional force FR to be greater than in a cross-sectional area 42 with a larger cross-sectional dimension. It is recognized that the contact between the friction element(s) 48 and the surface 50 generated frictional force FR as such along the longitudinal axis 41 of the elongated element 40 It can be variable if the cross-sectional dimension (e.g., the diameter) is varied (or if any one or any two or more of the friction configuration parameters are varied).

[0062] In the Fig. 7a, Fig. 7b, Fig. 8 is the counterweight mechanism 15 shown, with the elongated element 40 The ease of explanation has not been demonstrated. The runner element 45 with the friction element(s) 48 as such, it rests on a support element 52 positioned. The support element 52 is (in this exemplary case via an attached bumper spring) 53 ) at a distal end 54 to the locking flap 14 (see Fig. 1) or the vehicle body 11 coupled and is at a proximal end 56 to the runner element 45 coupled. The elongated element is complementary. 40 to the vehicle body 11 or to the locking flap 14 coupled. If the support element 52 as such along the longitudinal axis 41When moved, the attached runner element 45 along the elongated element 40 postponed (see Fig. 4) A proximal end 58 (see Fig. 4) of the elongated element 40 can, for example, be permanently attached to the vehicle body 11 be coupled, while the distal end 54 of the support element 52 firmly attached to the locking flap 14 can be coupled (see Fig. 7b). If the locking flap 14 as such, it moves between the open and closed positions (see Fig. 1) the distance between the proximal end changes 58 of the elongated element 40 and the distal end 54 of the support element 52 , thereby causing the back-and-forth movement of the runner element 45 along the longitudinal axis 41 of the elongated element 40 is provided. When the runner element 45moving (or tending to move), generates the friction element(s) 48 The frictional force FR. It is recognized that the frictional force FR can be defined as dry friction, which resists the longitudinal (and / or rotational) relative motion of two solid surfaces in contact. Dry friction is subdivided into static friction (“friction at rest”) between stationary surfaces and kinetic friction between moving surfaces. Therefore, the frictional force between the friction element(s) would be... 48 and the surface 50 The generated frictional force FR is a static frictional force FR when the closure flap 14 is held stationary in the holding area THR of the third position (see Fig. 3) Alternatively, the friction element(s) between the friction element(s) would be 48 and the surface 50 The generated frictional force FR is a sliding frictional force FR when the closure flap14 both within and outside the holding area THR of the third position between the open and closed positions (see Fig. 3).

[0063] In addition to the above, the frictional force FR can be influenced by factors such as, but not limited to: the type of materials in contact (which affect the coefficient of friction between the resisting element(s)). 48 and the surface 50 define) and their surface type or coatings (the different areas 42 , 43 , 44 They may, for example, have different surface coatings that have different coefficients of friction with the resistive elements. 48 show); the extent of the contact surface between the resistive element(s) 48 and the surface 50, so that a larger surface area is proportional to a greater frictional force FR (some areas 42 , 43 , 44 The elongated element can, for example, be configured so that the respective circumferential surface 50 in the respective area 42 , 44 with a larger number or a smaller number – a different number of resistance element(s) 48 – compared to another of the areas 42 , 43 , 44 is in contact and consequently a change in surface contact between the different areas 42 , 44 creates); and / or the normal pressure (or the load – e.g., the normal force), as caused, for example, by the change in cross-sectional dimensions between different areas. 42 , 43 , 44 is represented (e.g., a greater normal force between the surface of the leaf springs). 48 and the surface50 for the area diameter 44 compared to the area diameter 42 for the in Fig. 4 shown counterweight mechanism 15 The normal force can be defined as the net force that presses two parallel surfaces together; its direction being towards the surfaces (i.e., the surface of the friction element). 48 , which deal with the surface 50 of the elongated element 40 (is in contact) is perpendicular.

[0064] Furthermore, it is recognized that the direction of the frictional force FR against the surface 48 , 50 is opposite to the movement that the surface 48 , 50 would be experienced in the absence of friction. Consequently, in the static case, the frictional force FR is exactly what it needs to be to prevent movement between the surfaces. 48 , 50to prevent this; so that the frictional force FR balances the net force that tends to cause such movement. In this case, the Coulomb approximation creates a threshold for this force FR above which the movement would begin (i.e., the flap would close). 14 (would sink), instead of providing an estimate of the actual frictional force FR. This maximum frictional force FR is known as the follow-through friction. Furthermore, it is recognized that the frictional force FR is always exerted in a direction that corresponds to the motion (for sliding friction) or the potential motion (for static friction) between the two surfaces (the contact between the friction element). 48 and the surface 50 ) counteracts this.

[0065] It is also recognized that the coefficient of friction (COF) is often a dimensionless scalar value that represents the ratio of the frictional force FR between two bodies (e.g., the surface). 50and the friction element 48 ) and the force that presses them together (i.e., the normal force). The coefficient of friction depends on the materials used for the surfaces in contact. Coefficients of friction can range from close to zero to greater than one. For surfaces at rest relative to each other, the COF is the static coefficient of friction. This static COF is usually larger than its kinetic counterpart. For surfaces in relative motion, the COF is the kinetic coefficient of friction.

[0066] In Fig. 15a is an alternative embodiment of the friction counterweight mechanism 15 shown, which is the runner element 45 exhibits, which is due to the support element 52 (or the leadscrew) 140 ) on an inner circumferential surface 50 of the elongated element 40supported, which is configured as a hollow tube, (the runner element 45 is e.g. for the back-and-forth movement on the inner surface 50 of the elongated element 40 positioned). As such, other configurations of the runner element are 45 and the elongated element 40 for the friction counterweight mechanism 15 considered, including both other cross-sectional shapes and other inner and / or outer circumferential surfaces 50 for contact with the friction elements 48 The friction elements 48 can a pair of blocks 48 be those which are prestressed by one or more prestressing elements 51 (e.g. a spring placed between the pair of blocks) 48 (used together) away from each other and in contact with the perimeter surface 50 are predisposed, as they are within the body 59 of the runner element 45are appropriate. It is recognized that the body 59 to the leadscrew 140 can be coupled (see the Fig. 14a, Fig. 14c, Fig. 14d) and / or to one or more sections of the housing 112 , 114 can be coupled (see the Fig. 14b, Fig. 14c).

[0067] If the runner element 45 along the elongated element 40 TR moves (when it passes through the support element) 52 or the leadscrew 140 (is pushed / pulled), therefore the friction element(s) is / are located there. 48 with the surface 50 of the elongated element 40in contact, consequently generating a frictional force FR due to the combined configuration of the friction configuration parameters (e.g., a selected coefficient of friction, a selected contact pressure, also referred to as normal force, and / or a selected contact area, etc.) between the friction element(s) 48 and the surface 50 cause in a cross-sectional area 42 with a larger cross-sectional dimension for the outer surfaces 50 (see Fig. 4) The frictional force FR is expected to be greater than in a cross-sectional area 42 with a smaller cross-sectional dimension. Alternatively, in a cross-sectional area 42 with a smaller cross-sectional dimension for the inner surfaces 50 (see Fig. 6) expects the frictional force FR to be greater than in a cross-sectional area 42with a larger cross-sectional dimension. It is recognized that the contact between the friction element(s) 48 and the surface 50 generated frictional force FR as such in magnitude along the longitudinal axis 41 of the elongated element 40 This can be variable if the cross-sectional dimension (e.g., the diameter) is varied (or if any one or two or more of the friction configuration parameters are varied). During the movement of the runner element 45 can the opposite brake pads 48 between each one above and within the slots 53 of the body 59 slide. The spring 51 is done during the assembly process of the runner element 45 compressed and therefore contributes to the selection and configuration of the magnitude of the frictional force FR that exists between the blocks 48 and the surface 50is generated. This frictional force FR can, for example, be a function of the relative translational and / or relative rotational motion (in the case of a rotating rotor element). 45 – e.g. under the influence of the power spindle 140 after the Fig. 14a, Fig. d) between the surface 50 and the runner element 45 be, if the surface 50 has a variable internal cross-sectional dimension, such as a variable internal diameter (see Fig. 6) One advantage of this friction braking mechanism, which is in Fig. As shown in Figure 15, the friction surfaces of the blocks 48 and the circumferential area 50 envelop each other, which can reduce the contact stresses and wear of the mating parts and helps to distribute the relatively large frictional forces within the small space of the runner element. 45 to generate. Furthermore, it is recognized that the blocks 48 the in Fig. The embodiment of the runner element shown in 15 can be configured as shown in Fig. 4 is shown, so that the elongated element 40 the runner element 45 on an outer circumferential surface 50 supports (the runner element) 45 e.g. for the back-and-forth movement on the outer surface 50 of the elongated element 40 is positioned), whereby the blocks 48 (e.g. via one or more springs) 51 ) to each other and consequently to the outer circumferential surface 50 , to which the body is attached for movement along (and optionally around), would be pre-stressed.

[0068] In Fig. 15b is an alternative embodiment of the friction counterweight mechanism 15 after Fig. 15a shown, which is the runner element 45 exhibits, which is due to the support element 52 (or the leadscrew) 140 ) on an inner circumferential surface 50of the elongated element 40 , which is configured as a hollow tube, is supported, (the runner element 45 is e.g. for the back-and-forth movement on the inner surface 50 of the elongated element 40 positioned when it passes through the support element 52 or the leadscrew 140 (is pushed / pulled). Other configurations of the runner element are available. 45 and the elongated element 40 as such for the friction counterweight mechanism 15 considered, including both other cross-sectional shapes and other inner and / or outer circumferential surfaces 50 for contact with the friction element 48 The friction elements 48 can a pair of blocks 48 be those which are prestressed by one or more prestressing elements 51 (e.g. a spring placed between the pair of blocks) 48(used together) away from each other and in contact with the perimeter surface 50 are predisposed because they are internal to the body 59 of the runner element 45 are appropriate.

[0069] In the Fig. 16a, b is an alternative embodiment of the friction counterweight mechanism 15 shown, which is the runner element 45 exhibits, which is due to the support element 52 (or the leadscrew) 140 ) on an inner circumferential surface 50 of the elongated element 40 , which is configured as a hollow tube, is supported, (the runner element 45 is e.g. for the back-and-forth movement on the inner surface 50 of the elongated element 40 positioned when it passes through the support element 52 or the leadscrew 140 (is pushed / pulled). Various configurations of the runner element are available. 45 and the elongated element 40as such for the friction counterweight mechanism 15 considered, including both other cross-sectional shapes and other inner and / or outer circumferential surfaces 50 for contact with the friction elements 48 The friction elements 48 can be a pair of leaf spring inserts 48 be those which are formed by one or more spring bodies 51 away from each other and in contact with the circumferential surface 50 are predisposed because they are internal to the body 59 of the runner element 45 are appropriate.

[0070] If the runner element 45 along the elongated element 40 If TR moves, the friction element(s) is / are therefore located with the surface. 50 of the elongated element 40in contact, whereby, consequently, due to the combined configuration of the friction configuration parameters (e.g., a selected coefficient of friction, a selected contact pressure, which is also referred to as a normal force, and / or a selected contact area, etc.), the generation of a frictional force FR1, FR2 between the friction element(s) 48 and the surface 50 cause in a cross-sectional area 42 with a larger cross-sectional dimension for the outer surfaces 50 (see Fig. 4) The frictional force magnitude FR1, FR2 is expected to be greater than in a cross-sectional area 42 with a smaller cross-sectional dimension. Alternatively, in a cross-sectional area 42 with a smaller cross-sectional dimension for the inner surfaces 50 (see Fig. 6) is expected to have a greater frictional force magnitude FR1, FR2 than in a cross-sectional area 42with a larger cross-sectional dimension. It is recognized as such that the frictional force quantity FR1, FR2, which exists between the contact between the friction element(s) and the surface 50 is generated along the longitudinal axis 41 of the elongated element 40 It can be variable if the cross-sectional dimension (e.g., the diameter) is varied (or if any one or any two or more of the friction configuration parameters are varied).

[0071] During the movement of the runner element 45 The opposite leaf spring inserts can 48 inside the slots 53 of the body 59 are located. The spring 51 is done during the assembly process of the runner element 45 compressed and consequently contributes to the selection and configuration of the amount of frictional force FR1, FR2 that exists between the leaf spring inserts 48 and the circumferential area50 is generated. This frictional force quantity FR1, FR2 can, for example, be a function of the relative translational and / or the relative rotational motion (in the case of a rotating rotor element). 45 – e.g. under the influence of the power spindle 140 after Fig. 14) between the surface 50 and the runner element 45 be, if the surface 50 has a variable inner diameter (see Fig. 6) It is stated that the magnitude FR1 of the frictional force would be smaller than the magnitude FR2 of the frictional force based on the different linear (e.g., stroke) directions of motion TR1 and TR2. Regarding the direction TR1, the friction between the surface would 50 and the surface 55 cause the opposing leaf spring inserts 48 against the spring 51 provided preload in relation to each other and into their respective slots 53forced. This is in comparison to direction TR2, when the friction between the surface 50 and the surface 55 would cause the opposing leaf spring inserts 48 away from each other and out of their respective slots 53 be forced (and consequently with the force exerted by the spring) 51 provided preload work), to generate a greater normal force (and consequently a corresponding magnitude FR2 of frictional force) between the surfaces 50 , 55 than to generate TR1 for the opposite direction of movement. The one in the Fig. Friction-based counterweight mechanism shown in 16a, b 15 As such, different magnitudes of frictional force FR1, FR2 are created depending on the relative linear direction of movement of the runner element. 45 along the longitudinal axis 41(i.e., the direction of movement TR1 is opposite to the direction of movement TR2. It is further recognized that the leaf spring inserts 48 the in the Fig. The embodiment of the runner element shown in 16a, b can be configured as shown in Fig. 4 is shown, so that the elongated element 40 the runner element 45 on an outer circumferential surface 50 supports (the runner element) 45 is e.g. for the back-and-forth movement on the outer surface 50 of the elongated element 40 positioned), whereby the leaf spring inserts 48 (e.g. via one or more springs) 51 ) to each other and consequently to the outer circumferential surface 50 , to which the body is attached for movement along (and optionally around), would be pre-stressed.

[0072] In the Fig. 17a, b is an alternative embodiment of the friction counterweight mechanism 15shown, which is the runner element 45 exhibits, which is due to the support element 52 (or the leadscrew) 140 ) on an inner circumferential surface 50 of the elongated element 40 , which is configured as a hollow tube, is supported, (the runner element 45 is e.g. for the back-and-forth movement on the inner surface 50 of the elongated element 40 configured when it is through the support element 52 or the leadscrew 140 (is pushed / pulled). Other configurations of the runner element are available. 45 and the elongated element 40 as such for the friction counterweight mechanism 15 considered, including both other cross-sectional shapes and other inner and / or outer circumferential surfaces 50 for contact with the friction elements 48 The friction elements 48 can be a pair of bets 48be those which are formed by one or more spring bodies 51 away from each other and in contact with the circumferential surface 50 are predisposed because they are internal to the body 59 of the runner element 45 are appropriate.

[0073] If the runner element 45 along the elongated element 40 If TR moves, the friction element(s) is / are therefore located there. 48 with the surface 50 of the elongated element 40 in contact, consequently generating a frictional force FR1, FR2 due to the combined configuration of the friction configuration parameters (e.g., a selected coefficient of friction, a selected contact pressure, also referred to as normal force, and / or a selected contact area, etc.) between the friction element(s) 48 and the surface 50 cause in a cross-sectional area 42with a larger cross-sectional dimension for the outer surfaces 50 (see Fig. 4) The magnitude of the frictional force FR1, FR2 is expected to be greater than in a cross-sectional area 42 with a smaller cross-sectional dimension. Alternatively, in a cross-sectional area 42 with a smaller cross-sectional dimension for the inner surfaces 50 (see Fig. 6) expects the magnitude FR1, FR2 of the frictional force to be greater than in a cross-sectional area 42 with a larger cross-sectional dimension. It is recognized as such that the size FR1, FR2 of the frictional force that occurs between the contact between the friction element(s) 48 and the surface 50 is generated along the longitudinal axis 41 of the elongated element 40It can be variable if the cross-sectional dimension (e.g., the diameter) is varied (or if any one or any two or more of the friction configuration parameters are varied).

[0074] During the movement of the runner element 45 can the opposing stakes 48 inside the slots 53 of the body 59 are located. The spring 51 is done during the assembly process of the runner element 45 compressed and consequently contributes to the selection and configuration of the amount of size FR1, FR2 of the frictional force that exists between the inserts 48 and the circumferential area 50 is generated. This frictional force quantity FR1, FR2 can, for example, be a function of the relative translational and / or the relative rotational motion (in the case of a rotating rotor element). 45 – e.g. under the influence of the power spindle 140 after Fig. 14) between the surface50 and the runner element 45 be, if the surface 50 has a variable inner diameter (see Fig. 6) It is stated that the magnitude FR1 of the frictional force would be smaller than the magnitude FR2 of the frictional force based on the different linear (e.g., stroke) directions of motion TR1 and TR2. Regarding the direction TR1, the friction between the surface would 50 and the surface 55 cause the opposing stakes 48 against the spring 51 provided preload around their respective pivot points 57 to each other and into their respective slots 53 forced. This is in comparison to direction TR2, when the friction between the surface 50 and the surface 55 would cause the opposing leaf spring inserts 48 around their respective pivot points 57away from each other and out of their respective slots 53 be forced (and consequently with the force exerted by the spring) 51 (provided preload work) to generate a greater normal force (and consequently a corresponding frictional force FR2) between the surfaces 50 , 55 than to generate TR1 for the opposite direction of movement. The one in the Fig. Friction-based counterweight mechanism shown in 17a, b 15 As such, different magnitudes of frictional force FR1, FR2 are created depending on the relative linear direction of movement of the runner element. 45 along the longitudinal axis 41 (i.e., the direction of movement TR1 is opposite to the direction of movement TR2). It is further recognized that the deployments 48 the in the Fig. The embodiment of the runner element shown in 17a, b can be configured as shown in Fig. 4 is shown, so that the elongated element40 the runner element 45 on an outer circumferential surface 50 supports (the runner element) 45 is e.g. for the back-and-forth movement on the outer surface 50 of the elongated element 40 positioned), whereby the leaf spring inserts 48 (e.g. via one or more springs) 51 ) to each other and consequently to the outer circumferential surface 50 , to which the body is attached for movement along (and optionally around), would be pre-stressed.

[0075] In the Fig. 18a, b, c is an alternative embodiment of the friction counterweight mechanism 15 shown, which is the runner element 45 exhibits, which is due to the support element 52 (or the leadscrew) 140 ) on an inner circumferential surface 50 of the elongated element 40 , which is configured as a hollow tube, is supported, (the runner element 45is, for example, suitable for back-and-forth movement on the inner surface 50 of the elongated element 40 as well as for rotation around the longitudinal axis 41 configured when it is through the leadscrew 140 (is pushed / pulled). Other configurations of the runner element are available. 45 and the elongated element 40 as such for the friction counterweight mechanism 15 considered, including both other cross-sectional shapes D1, D2, D3 as well as other inner and / or outer circumferential surfaces 50 for contact with the friction elements 48 The friction elements 48 Can one or more arms be affected by pre-existing conditions? 48 (where, for example, only 4 (examples shown) are those which are provided by one or more prestressing elements 51 outwards and in contact with the circumferential surface 50 are predisposed because they are internal to the body 59 of the runner element 45are appropriate. In this example, the pre-stressed arms can 48 a cam-shaped surface 55 exhibit and each around a pre-stress site 61 of the body 59 to have a pre-existing condition.

[0076] If the runner element 45 spirally along the elongated element 40 and around the longitudinal axis 41 If TR moves, the friction element(s) is / are therefore located there. 48 with the surface 50 of the elongated element 40 in contact, whereby, due to the combined configuration of the friction configuration parameters (e.g., a selected coefficient of friction, a selected contact pressure, also referred to as normal force, and / or a selected contact area, etc.), the generation of a frictional force FR1, FR2 between the friction element(s) 48 and the surface 50 cause in a cross-sectional area42 with a larger cross-sectional dimension for the outer surfaces 50 (see Fig. 4) The magnitude of the frictional force FR1, FR2 is expected to be greater than in a cross-sectional area 42 with a smaller cross-sectional dimension. Alternatively, in a cross-sectional area 42 with a smaller cross-sectional dimension for the inner surfaces 50 (see Fig. 6) expects the magnitude FR1, FR2 of the frictional force to be greater than in a cross-sectional area 42 with a larger cross-sectional dimension. It is recognized that the size FR1, FR2 of the frictional force as such, which exists between the contact between the friction element(s) 48 and the surface 50 is generated along the longitudinal axis 41 of the elongated element 40It can be variable if the cross-sectional dimension (e.g., the diameter) is varied (or if any one or any two or more of the friction configuration parameters are varied).

[0077] During the movement of the runner element 45 can the already stressed arms 48 inside the slots 53 of the body 59 are located. The component of the spring 51 (e.g. the more effective leaf spring) of the pre-loaded arms 48 is done during the assembly process of the runner element 45 compressed and consequently contributes to the selection and configuration of the amount of size FR1, FR2 of the frictional force that exists between the preloaded arms 48 and the circumferential area 50 is generated. This frictional force FR can, for example, be a function of the relative rotational motion (in this case, of a rotating runner element). 45 – e.g. under the influence of the power spindle 140 after Fig. 14) between the surface 50 and the runner element 45 It should be stated that the magnitude FR1 of the frictional force would be smaller than the magnitude FR2 of the frictional force based on the different directions of rotation R1 and R2; with respect to the direction R1, the friction between the surface would be 50 and the surface 55 cause the already stressed arms 48 against the spring component 51 created pre-load in relation to each other and into their respective slots 53 forced. This is in comparison to the direction of rotation R2, when the friction between the surface 50 and the surface 55 would cause the already stressed arms 48 away from each other and out of their respective slots 53 be forced (and consequently with the spring component 51 work on the created pre-existing strain to reduce the strain on the arms. 48away from the body location 61 to preload), in order to create a greater normal force (and consequently a greater magnitude FR2 of the frictional force) between the surfaces 50 , 55 than to generate the opposite direction of rotation R1. The friction-based counterweight mechanism 15 as such, who is in the Fig. As shown in 18a, b, c, different magnitudes of the frictional force FR1, FR2 are created depending on the direction of rotation of the movement of the runner element. 45 around the longitudinal axis 41 (i.e., the direction of movement R1 is opposite to the direction of movement R2). It is further observed that the pre-loaded arms 48 the embodiment of the runner element, which is in the Fig. As shown in 18a, b, c, they can be configured as shown in Fig. 4 is shown, so that the elongated element 40 the runner element 45 on an outer circumferential surface 50 supports (the runner element)45 is e.g. for the back-and-forth movement on the outer surface 50 of the elongated element 40 positioned), whereby the pre-loaded arms 48 (e.g. via one or more spring components) 51 ) to the body location 61 and consequently to the outer circumferential surface 50 would be forced to the point where the body is attached for movement along (and around).

[0078] In Fig. 19 is an alternative embodiment of the friction counterweight mechanism 15 shown, which is the runner element 45 exhibits that is caused by the leadscrew 140 on an inner circumferential surface 50 of the elongated element 40 , which is configured as a hollow tube, is supported, (the runner element 45 is e.g. for the back-and-forth movement on the inner surface 50 of the elongated element 40 configured when it is through the leadscrew 140(is pushed / pulled). Other configurations of the runner element are available. 45 and the elongated element 40 as such for the friction counterweight mechanism 15 considered, including both other cross-sectional shapes and other inner and / or outer circumferential surfaces 50 for contact with the friction elements 48 The friction elements 48 are for contact with the circumferential surface 50 on the body 59 appropriate.

[0079] If the runner element 45 along the elongated element 40 TR1, TR2 moves, therefore the friction element(s) is / are located there. 48 with the surface 50 of the elongated element 40in contact, consequently generating a frictional force FR1, FR2 due to the combined configuration of the friction configuration parameters (e.g., a selected coefficient of friction, a selected contact pressure, also referred to as normal force, and / or a selected contact area, etc.) between the friction element(s) 48 and the surface 50 cause in a cross-sectional area 42 with a larger cross-sectional dimension for the outer surfaces 50 (see Fig. 4) The frictional force FR1, FR2 is expected to be greater than in a cross-sectional area 42 with a smaller cross-sectional dimension. Alternatively, in a cross-sectional area 42 with a smaller cross-sectional dimension for the inner surfaces 50 (see Fig. 6) expects the frictional force FR1, FR2 to be greater than in a cross-sectional area 42with a larger cross-sectional dimension. It is recognized that the frictional force FR1, FR2 as such, which exists between the contact between the friction element(s) 48 and the surface 50 is generated along the longitudinal axis 41 of the elongated element 40 It can be variable if the cross-sectional dimension (e.g., the diameter) is varied (or if any one or any two or more of the friction configuration parameters are varied).

[0080] This quantity FR1, FR2 of the frictional force can, for example, be a function of the relative translational and / or relative rotational motion (in the case of a rotating runner element). 45 – e.g. under the influence of the power spindle 140 after Fig. 14) between the surface 50 and the runner element 45 be, if the surface 50has a variable internal cross-sectional dimension, such as a variable internal diameter (see Fig. 6) The friction-based counterweight mechanism 45 can also be a pair of plates 72 , 74 exhibit, so that a prestressing element 51 (e.g. a spring) the rotating surface 73 the rotating plate 72 , which are in a fixed position (on the longitudinal axis) 41 ) is positioned due to the rotation of the runner element 45 around the longitudinal axis 41 , when the power spindle 140 through the drive mechanism 136 is being filmed (see Fig. 14), against a fixed position (on the longitudinal axis 41 ) the rotationally stationary surface 75 (which, for example, does not rotate) the record 74 forces itself. If the runner element 45 If TR1 were moved in a linear direction, the compression of the preload element would occur.51 decrease (e.g. the length of the prestressing element) 51 extend) and consequently the clamping of the plates 72 , 74 against each other through the preloading element 51 decrease, which would lead to a decrease in the magnitude FR1 of the frictional force if the runner element 45 continues to move in the linear direction TR1. If, in contrast, the runner element 45 If TR2 moves in the opposite linear direction, the length of the prestressing element would change. 41 shorten (e.g. the compression of the preload element) 51 increase) and consequently the clamping of the plates 72 , 74 against each other through the preloading element 51 increase, which would lead to an increase in the magnitude FR2 of the frictional force if the runner element 45 continues to move in the linear direction TR2. The position of the runner element. 45As such, it describes the relative expansion or compression of the preload element. 51 and consequently makes the frictional force FR1, FR2 a function of the relative position of the runner element. 45 along the longitudinal axis 41 The relative rotational movement of the surfaces 73 , 75 in relation to each other (due to the rotation of the runner element) 45 through the drive of the power spindle 140 ) in combination with the length of the prestressing element 51 due to the position of the runner element 45 on the longitudinal axis 41 As such, it influences the frictional force quantity FR1, FR2, which is caused by the translational and rotational movement of the runner element. 45 with respect to the longitudinal axis 41 is generated.

[0081] In Fig. 20 is an alternative embodiment of the friction counterweight mechanism 15 shown, which is the runner element 45exhibits that is located on an inner circumferential surface 50 of the elongated element 40 , which is configured as a hollow tube, is supported, (the runner element 45 is e.g. for the back-and-forth movement on the inner surface 50 of the elongated element 40 (positioned). Various configurations of the runner element are available. 45 and the elongated element 40 for the friction counterweight mechanism 15 considered, including both other cross-sectional shapes and other inner and / or outer circumferential surfaces 50 for contact with the friction elements 48 The friction elements 48 are for contact with the circumferential surface 50 on the body 59 appropriate. Alternatively, the body would 59 the friction elements 48 not in contact with the circumferential surface 50exhibit (e.g. due to changes in the cross-sectional dimensions of the elongated element) 40 , due to a lack of friction elements 48 on the body 59 etc.).

[0082] Regarding the influence of friction elements 48 the friction element(s) is / are located 48 with the surface 50 of the elongated element 40 in contact when the runner element 45 along the elongated element 40 TR1, TR2 moves, whereby, due to the combined configuration of the friction configuration parameters (e.g., a selected coefficient of friction, a selected contact pressure, which is also referred to as a normal force, and / or a selected contact area, etc.), the generation of a quantity FR1, FR2 of the frictional force between the friction element(s) 48 and the surface 50 is caused in a cross-sectional area 42with a larger cross-sectional dimension for the outer surfaces 50 (see Fig. 4) The magnitude of the frictional force FR1, FR2 is expected to be greater than in a cross-sectional area 42 with a smaller cross-sectional dimension. Alternatively, in a cross-sectional area 42 with a smaller cross-sectional dimension for the inner surfaces 50 (see Fig. 6) expects the magnitude FR1, FR2 of the frictional force to be greater than in a cross-sectional area 42 with a larger cross-sectional dimension. It is recognized that the contact between the friction element(s) 48 and the surface 50 generated frictional force FR1, FR2 as such along the longitudinal axis 41 of the elongated element 40It can be variable if the cross-sectional dimension (e.g., the diameter) is varied (or if any one or any two or more of the friction configuration parameters are varied).

[0083] This frictional force FR1, FR2 can, for example, be a function of the relative translational and / or the relative rotational motion (in the case of a rotating rotor element). 45 – e.g. under the influence of the power spindle 140 after Fig. 14) between the surface 50 and the runner element 45 be, if the surface 50 has a variable internal cross-sectional dimension, such as a variable internal diameter (see Fig. 6) The friction-based counterweight mechanism 45 can also the plates 72 , 74 , 76 exhibiting such that one or more prestressing elements 51 (e.g. a spring) the rotating surface(s) 73the rotating plate(s) 72 , 76 due to the rotation of the runner element 45 around the longitudinal axis 41 , when the power spindle 140 through the drive mechanism 136 is being filmed (see Fig. 14) against the rotationally stationary surface(s) 75 (which do not rotate, for example) the plate 74 force. If the runner element 45 Moving in the linear direction TR1, the compression of the preload element would occur. 51 decrease (e.g. the length of the prestressing element) 51 extend) and consequently the clamping of the plates 72 , 74 , 76 against each other through the preloading element 51 decrease, which would lead to a decrease in the magnitude FR1 of the frictional force if the runner element 45 continues to move in the linear direction TR1. If, in contrast, the runner element 45If TR2 moves in the opposite linear direction, the length of the prestressing element would change. 51 shorten (e.g. the compression of the preload element) 51 increase) and consequently the clamping of the plates 72 , 74 , 76 against each other through the preloading element 51 increase, which would lead to an increase in the magnitude FR2 of the frictional force if the runner element 45 continues to move in the linear direction TR2. The linear position of the runner element. 45 As such, it describes the relative expansion or compression of the preload element. 51 and consequently makes the magnitude FR1, FR2 of the frictional force a function of the relative position of the runner element. 45 along the longitudinal axis 41 The relative rotational movement of the surfaces 73 , 75 in relation to each other (due to the rotation of the runner element) 45 through the drive of the power spindle140 ) in combination with the length of the prestressing element 51 due to the position of the runner element 45 on the longitudinal axis 41 As such, it influences the magnitude of the FR1, FR2 frictional force caused by the translational and rotational movement of the runner element. 45 with respect to the longitudinal axis 41 is generated.

[0084] It is generally recognized that the configuration of the perimeter surface 50 (e.g. different diameters, different distances / different cross-sectional areas between opposing surfaces / walls of the circumferential surface) 50 , different coefficients of friction) can determine the magnitude of the frictional force FR when the runner element 45 (e.g. linear, rotating or both linear and rotating) along the elongated element 40moved. Similarly, it is recognized that the configuration of the surface 55 the friction elements 48 (e.g., exerting a normal force against the circumferential surface) 50 due to the differently configured prestressing element(s) 51 of the body 59 , different coefficients of friction) of the surface 55 etc.) can determine the magnitude of the quantity FR of the frictional force when the runner element 45 (e.g. linear, rotating or both linear and rotating – which is also referred to as spiral) along the elongated element 40 It is also recognized that the configuration (e.g., the shape, type, orientation, size, etc.) of the friction elements is affected. 48 can determine the magnitude of the frictional force FR when the runner element 45 (e.g. linear, rotating or both linear and rotating) along the elongated element40 moved.

[0085] It is further recognized that the magnitude FR of the frictional force is due to: the linear relative motion between the surfaces 50 , 55 (e.g. linear friction, as for example for the in Fig. 10 shown prestressing strut 37 ); the relative rotational motion between the surfaces 50 , 55 (e.g. rotational friction, as found, for example, in the runner element) 45 after the Fig. 16a, b, Fig. 17a, b is generated); and / or the relative spiral motion between the surfaces 50 , 55 (e.g. spiral friction, as found, for example, in the electromechanical shock absorber) 37 after Fig. 14a is generated when the runner element 45 can be generated (rotates).

[0086] It is further recognized that the generated quantity FR is the frictional force against the stroke position of the runner element. 45along the longitudinal axis 41 of the elongated element 40 due to changes in the diameter of the circumferential surface 50 at various locations along the longitudinal axis 41 , changes in the distance (of the distances) between opposing surfaces / walls of the perimeter area 50 at various locations along the longitudinal axis 41 and / or different coefficients of friction) at different locations along the longitudinal axis 41 can be variable. Examples of the variability of the quantity FR, the frictional force against the stroke position of the runner element. 45 are exemplary in the Fig. 4 and Fig. 6 and Fig. 12a, b, c shown.

[0087] It is further recognized that the generated quantity FR is the frictional force against the stroke position of the runner element. 45 along the longitudinal axis 41 of the elongated element 40due to the consistency of the diameters of the circumferential surface 50 at various locations along the longitudinal axis 41 , the consistency of the distance (of the distances) between opposite surfaces / walls of the circumferential area 50 at various locations along the longitudinal axis 41 and / or the consistency of the coefficient(s) of friction at different locations along the longitudinal axis 41 can be constant.

[0088] It is further recognized that the generated quantity FR of the frictional force is against the relative direction of motion of the runner element. 45 along the longitudinal axis 41 of the elongated element 40 due to differences in the normal force between the surfaces 50 , 55 through the cooperation of the friction elements 48 and the circumferential area 50 based on the configuration of the operation of the friction elements, which depends on the direction of movement48 The force exerted in relation to each other can be variable. The pair of friction elements 48 This can be achieved, for example, with a larger size in one direction of movement TR compared to the opposite direction of movement along the longitudinal axis. 41 be pre-loaded away from each other (and consequently in contact with the surface with a greater force) 50 (be forced to). Examples of this variability in the magnitude FR of the frictional force against the stroke position of the runner element. 45 are, for example, in the Fig. 16 and Fig. 17 shown.

[0089] It is further recognized that the generated frictional force FR acts against the relative direction of rotation of the runner element's movement. 45 around the longitudinal axis 41 of the elongated element 40 due to the differences in normal force between the surfaces 50 , 55 through the cooperation of the friction elements 48and the circumferential area 50 based on the configuration of the operation of the friction elements, which depends on the direction of rotation 48 The force exerted in relation to each other can be variable. The pair of friction elements 48 This can be achieved, for example, with a larger size in one direction of rotational motion R compared to the opposite direction of motion along the longitudinal axis. 41 be pre-loaded away from each other (and consequently in contact with the surface with a greater force) 50 (be forced to). Examples of this variability in the magnitude FR of the frictional force against the direction of rotation R of the runner element. 45 are, for example, in the Fig. 18a, b, c shown. Examples of the prestressing element 37 contained counterweight mechanism 15

[0090] In Fig. 8 is a prestressing element 37 , which is referred to as a prestressing strut, with a body59 shown, which had a first end 60 for connecting with a locking flap 14 (or a vehicle body / frame) 11 ) and a second ending 62 for connecting to a vehicle body / vehicle frame 11 (or a closure flap) 14 ) depending on the orientation of the prestressing element configuration 37 , if it is in the locking flap system 12 (see Fig. 1) is installed. In this configuration, the counterweight mechanism exhibits 15 The elongated element is merely an example. 40 , which is inside 64 of the body 59 is positioned, and the runner element 45 , which is at the proximal end 56 of the support element 52 coupled, on. The distal end 54 of the support element 52 is at the second end 62(e.g. via an optional element) 66 – a spring) of the preload element 37 (e.g. of the strut) coupled, while the proximal end 48 of the elongated element 40 to the other end 60 is coupled. Examples include the following areas: 42 , 44 with differing cross-sectional dimensions. However, it is also recognized that any of the other influencing factors mentioned above could also be varied, either additionally or alternatively (e.g., each area has the same cross-sectional dimensions but a different surface treatment – ​​one area, for example, has a rougher surface quality than the other, consequently resulting in different values ​​of the respective coefficient of friction between the areas). 42 , 44 are provided).

[0091] As shown, the prestressing element 37a strut that contains an elastic element of a spring 68 to create a counterweight torque T (see Fig. 3) during operation of the closure flap 14 exhibits during the movement between the open and closed positions (see Fig. 1). In Fig. 9 are further details of the elongated element 40 , which is achieved through an optional element 70 (e.g. a connector) to the end 60 the prestressing strut 37 coupled, shown by way of example, where the spring 68 the prestressing strut 37 around the friction counterweight mechanism 15 is positioned the runner element 45 with the friction elements 48 with the surface 50 is in contact with the support tube 52 with the runner element 45 to guide the back-and-forth movement of the runner element 45 along the elongated element 40is connected and the body 59 the prestressing strut 37 as a housing for the spring 68 and the friction counterweight mechanism 15 It works.

[0092] In Fig. 10 is the exemplary prestressing strut 37 to accommodate the friction counterweight mechanism 15 shown. The body 59 The prestressing strut consists of a number of body elements. 80 , to control the expansion and compression of the body 59 during the operation of the closure flap 14 between the open and the closed position (see Fig. 1) to promote, thereby ensuring that the body 59 as a protective housing for the internal components (e.g. the spring) 68 ) the prestressing strut 37 and the enclosed friction counterweight mechanism 15 It works. The body 59 can the optional body elements 80of a sheathing tube 82 , of a sliding tube 84 , a sliding coating 86 , of a filling tube 88 and the end covers 90 exhibit. Internally, the spring can 68 about the optional spring seats 94 between the end caps 92 It is also a sequence of keyways. 100 on the sliding tube 84 shown, which are configured to use matching keyways 102 on the sheathing tube 82 to work together, consequently to prevent rotation between the component parts of the prestressing strut 37 to ensure that the preload strut is positioned between the open and closed positions of the locking flap. 14 is operated.

[0093] In Fig. 11 is the prestressing strut 37 in an extended position (when the locking flap 14e.g., is fully open and / or is located in the holding area THR of the third position – see Fig. 3) and in a compressed position (when the locking flap is closed) 14 e.g., in the closed position – see Fig. 1) shown what the back-and-forth movement of the runner element is. 45 along the elongated element 40 and the expansion / contraction of the spring 68 (e.g., the prestressing element) which is in the body 59 (e.g., the casing) is illustrated.

[0094] In the Fig. 13 and Fig. 14a, b, c, d is an embodiment of the friction-based counterweight mechanism 15 for the motor vehicle 10 shown. An electromechanical shock absorber. 37 as an exemplary prestressing element 37 includes a lower housing 112 , an upper case 114 and an extendable shaft / rod35 A swivel mount 18 , located at one end of the lower casing 112 It is located and can be swivelled to a section of the vehicle body. 11 be attached to an inner cargo area in the vehicle 10 defined. A second swivel mount 38 is at the distal end of the extendable shaft 116 regarding the upper casing 114 It is attached and can be swivelled on the tailgate. 14 of the vehicle 10 appropriate.

[0095] In Fig. 14 is the interior of the lower case 112 A more detailed example is shown below. The lower casing 112 creates a cylindrical side wall 122 , which is a chamber 124 defined. A swivel mount 18 is on an end wall 126 of the lower case 112 proximal to the vehicle body 11 attached. The upper casing 114creates a cylindrical side wall 40 (which is also referred to as an elongated element), which is a chamber 34 defined, which is open at both ends. The cylindrical side wall 40 (which is also referred to as an elongated element) has a circumferential surface 50 (as part of the friction-based counterweight mechanism) 15 ) for the intervention with the runner element 45 (which is also part of the friction-based counterweight mechanism) 15 is) on. A distal frontal wall 128 of the lower case 112 includes an opening 130 , so that the chamber 124 and the chamber 134 are connected to each other. The upper casing 114 can have a smaller diameter than the lower casing 112 exhibit. However, it is being considered that the lower casing 112 and the upper case 114They can also be designed as a single cylinder or truncated cone. Other form factors for the lower housing. 112 and the upper case 114 will occur to experts in the field. The upper casing 114 can be used with the lower case 112 be formed in one piece or can be attached to the lower housing by conventional means (e.g. threaded couplings, welded connections, etc.). 112 be attached. An optional engine-transmission arrangement. 136 is located in the chamber 124 and can be an integral component of the electromechanical strut 37 be (e.g. inside the housing) 112 , 114 are located as shown, or alternatively, are outside the housing 112 , 114 are located – which is not shown).

[0096] The optional engine-transmission arrangement 136 can an engine 142, a clutch, a planetary gearbox and a power spindle 140 (which can alternatively be used as a leadscrew) 140 (is referred to as) contains, which can be used to define the runner element 45 along the longitudinal axis 41 to transport or otherwise guide the engine 142 can within the chamber 124 near the front wall 126 be appropriate. The engine 142 It could be a bidirectional DC motor. The electrical power and the direction control for the motor. 142 can be supplied via electrical cables passing through (not shown) openings in the front wall 126 in the vehicle body 11 are connected. The clutch is connected to the engine via an output shaft. 142 connected. The clutch can selectively engage the output shaft of the motor. 142and the planetary gear set. The clutch is an electromechanical gear clutch that engages the planetary gear set, e.g., when the motor 142 is activated. When the clutch is engaged, torque is drawn from the engine. 142 The torque is transmitted through the planetary gear set. When the clutch is disengaged, no torque is transmitted between the engine and the transmission. 142 and transmitted to the planetary gear system, so that the occurrence of reverse drive can be limited if the tailgate 14 It is closed manually. The planetary gearbox can, for example, be a two-stage planetary gearbox that multiplies the torque for the power spindle. 140 provides. The power spindle 140 extends into the upper casing 114 As such, it is recognized that in the case where the motor arrangement 136 The guide spindle is present. 140 can be driven, i.e., actively by the rotary motion of the motor assembly136 , which are connected to the leadscrew 140 is coupled, can be rotated. Alternatively, in the case where the motor arrangement 136 is not present, the leadscrew 140 under the influence of friction, which occurs between the runner element 45 and the leadscrew 140 in the bore 161 is present around the longitudinal axis 41 rotate, i.e., passively through the linear movement of the runner element 45 be rotated if it is the leadscrew 140 turns.

[0097] The extendable shaft 35 creates a cylindrical side wall 154 , which is a chamber 156 defined, and can be concentric between the upper case 114 and the power spindle 140 It should be attached. As previously described, the swivel mount 38 at the distal end of the extendable shaft 35fastened. The proximal end of the extendable shaft 35 is open. A mother 45 (which is also known as the runner element) 45 (is referred to as) is around the proximal end of the extendable shaft. 35 regarding the lower casing 112 attached and is connected to the power spindle 140 coupled to the rotary motion of the power spindle 140 into the linear movement of the extendable shaft 35 along the longitudinal axis 41 the power spindle 140 to implement the drive nut 45 may contain keyways extending into opposing coaxial slots located inside the elongated element 40 are designed to prevent the mother from 45 turns when the mother 45 along the longitudinal axis 41 moved. Alternatively, the mother 45without the keyways, so that it is consequently free to rotate when the nut 45 along the longitudinal axis 41 moved, without deviating from the scope of protection of the invention. An integrally formed outer edge. 164 on the upper case 114 Can a surrounding seal be created between the chamber? 134 and create the exterior. As in Fig. As shown in 4, the runner element 45 a sequence of friction elements 48 , which relate to the body 59 are suitable for the intervention (e.g. pre-stressed) with the circumferential surface 50 of the elongated element 40 exhibit.

[0098] A spring housing 138 is in the lower case 112 provided for and is formed by the cylindrical side wall 122 , the front wall 128 and a flange 166 defined. Within the spring housing 138 is a power spring 68around the power spindle 140 wrapped and creates a mechanical counterweight to the weight of the tailgate 14 The power spring 68 , which is preferably made of a steel strip, supports the lifting of the tailgate 14 both in its driven and undriven modes of the electromechanical shock absorber 37 An end to the power spring 68 is at the power spindle 140 attached, while the other is attached to a section of the cylindrical side wall 122 is attached. If the extendable shaft 35 The power spring is located in its retracted position. 68 tightly around the power spindle 140 wound. When the power spindle 140 rotates to extend the shaft 35 to pull out the power spring 68 in accordance with the movement of the runner element 45along the elongated element 40 (which the contact of the friction elements 48 with the circumferential area 50 caused) unwound, releasing its stored energy and generating an axial force through the extendable shaft 35 transfers to lift the tailgate 14 to support. If the power spindle 410 rotates to extend the shaft 16 to pull in the power spring 68 in accordance with the movement of the runner element 45 along the elongated element 40 (which the contact of the friction elements 48 with the circumferential area 50 caused) by rewinding around the power spindle 140 Reloaded.

[0099] In the Fig. 14a, Fig. 14b also shows that the counterweight mechanism 15 the moving body 45 may exhibit, which is connected to the lower case 112and / or the upper case 114 is connected so that the runner element 45 along the surface 50 moved, which through the other of the casings 112 , 114 the runner element 45 is provided adjacent to the property.

[0100] It is recognized that the differently configured prestressing elements 48 , which have been discussed above, can be used independently of each other if they are in the body 59 of the runner element 45 for a special prestressing element 37 (e.g., a shock absorber) are attached. The runner element 45 for example, only shows the leaf spring inserts 48 after the Fig. 16a, b, only shows the blocks 48 after the Fig. 15a, b, etc. Alternatively, two or more differently configured prestressing elements can be used. 48, which have been discussed above, are combined with each other and consequently occur together in the body 59 of the runner element 45 be attached and / or they can be in separate respective bodies 59 , which represent the same elongated element 40 are attached, (i.e., two or more runner elements) 45 , the respective differently configured friction elements 48 for the same elongated element 40 exhibiting features located at various points along the longitudinal axis 41 (are positioned) are configured. For example, it is recognized that any of the configurations of the friction element is not correct. 48 , which are in the Fig. 1 to Fig. 20 are shown, with any other configuration of the friction element 48 , which are in the Fig. 1 to Fig. The 20 shown can be combined. It is considered that the number of combinations of the different friction elements is limited. 48 (e.g. two or more) is limited only by the developer's imagination when considering the different embodiments of the various configurations of the friction element. 48 , which are in the Fig. 1 to Fig. 20 are shown, which refers to.

[0101] In light of the foregoing, the friction-based counterweight mechanism 15 as such in a number of different form factors of the prestressing element 37 It must be included. An example is the shock absorber without the leadscrew. 140 (see Fig. 10), wherein the runner element 45 consequently only linearly along the longitudinal axis 41 moved. Another example is the shock absorber with the leadscrew. 140 (see Fig.10), e.g. with or without the motor arrangement 136 , which are attached to the runner element 45 is coupled, whereby the runner element 45 consequently both linearly along the longitudinal axis 41 as well as rotating around the longitudinal axis 41 moved (i.e., a spiral relative motion).

Claims

[1] Friction-based counterweight mechanism for coupling with a shutter flap to assist the opening and closing of the shutter flap for at least one section of a path between a fully closed position and a fully open position of the shutter flap, the counterweight mechanism comprising: an elongated element positioned on a longitudinal axis extending between the proximal and distal ends of the counterweight mechanism, wherein the elongated element has a circumferential surface and a proximal end for coupling with either the closure flap or a vehicle body, a runner element comprising a body and at least one friction element attached to the body, wherein the runner element is positioned on the longitudinal axis for a back-and-forth movement along this axis and for forming a contact between the at least one friction element and the circumferential surface, wherein the contact serves to generate a frictional force between the circumferential surface and the friction element, and a support element coupled at a proximal end to the runner element for coupling at a distal end to a vehicle body or the closure flap, wherein the support element serves to guide the back-and-forth movement. [2] Friction-based counterweight mechanism according to claim 1, wherein the support element is a lead screw coupled to the body to provide the rotation of the runner element about the longitudinal axis. [3] Friction-based counterweight mechanism according to claim 2, wherein the lead screw drives the runner element both along and about the longitudinal axis. [4] Friction-based counterweight mechanism according to claim 2, wherein the frictional force is variable based on the direction of rotation of the leadscrew. [5] Friction-based counterweight mechanism according to claim 1, wherein the contact serves to generate the frictional force as a first frictional force quantity in a first region along the longitudinal axis and the frictional force as a second frictional force quantity different from the first frictional force quantity in a second region along the longitudinal axis, wherein the first region along the longitudinal axis is spaced apart from the second region. [6] Friction-based counterweight mechanism according to claim 4, wherein the contact serves to generate the frictional force as a first frictional force quantity in a first region along the longitudinal axis and the frictional force as a second frictional force quantity different from the first frictional force quantity in a second region along the longitudinal axis, wherein the first region along the longitudinal axis is spaced apart from the second region. [7] Friction-based counterweight mechanism according to claim 1, wherein the support element is a lead screw such that the runner element is coupled to a distal end of the lead screw. [8] Friction-based counterweight mechanism according to claim 2, wherein the support element is a leadscrew such that the runner element is coupled to a body of the leadscrew via a threaded bore. [9] Friction-based counterweight mechanism according to claim 2, wherein the lead screw is actively driven by a motor arrangement. [10] Friction-based counterweight mechanism according to claim 1, further comprising the closure flap coupled to the counterweight mechanism on one of its sides, such that the support element is a lead screw actively driven by a motor arrangement, and comprising a second counterweight mechanism coupled to another side of the closure flap, such that the movement of the closure flap passively actuates the second counterweight mechanism. [11] Counterweight mechanism for coupling with a closure flap to assist the opening and closing of the closure flap for at least one section of a path between a fully closed position and a fully open position of the closure flap, the counterweight mechanism comprising: a housing with a proximal end for coupling the counterweight mechanism to either the locking flap or a vehicle body and with a distal end for coupling the counterweight mechanism to either the vehicle body or the locking flap, respectively. an elongated element that is mounted in the housing and positioned on a longitudinal axis extending between the proximal and distal ends of the housing, wherein the elongated element has a circumferential surface and a proximal end coupled to the proximal end of the housing, a runner element comprising a body and at least one friction element attached to the body, wherein the runner element is positioned on the longitudinal axis for a reciprocating movement along this axis and for forming a contact between the at least one friction element and the circumferential surface, wherein the contact serves to generate a first frictional force in a first region along the longitudinal axis and a second frictional force, different from the first frictional force, in a second region along the longitudinal axis, wherein the first region along the longitudinal axis is spaced apart from the second region, and a support element coupled at a proximal end to the runner element and at a distal end to the distal end of the housing, which serves to guide the back-and-forth movement. [12] Counterweight mechanism according to claim 11, further comprising an elastic element located in the housing between the proximal end of the housing and the distal end of the housing, wherein the elastic element is configured to provide a counterweight force in the form of a preload strut element to assist in opening and closing the closure flap. [13] Counterweight mechanism according to claim 11, wherein the first region further comprises a first friction configuration parameter which is different from a second friction configuration parameter of the second region, such that a change in the first and second friction configuration parameters by the at least one friction element when the runner element moves from the first region to the second region results in a change in the friction force magnitude. [14] Counterweight mechanism according to claim 13, wherein the first friction configuration parameter is a width dimension of the elongated element and the second friction configuration parameter is another width dimension of the elongated element. [15] Counterweight mechanism according to claim 11, wherein the elongated element has a third area along the longitudinal axis for generating the frictional force through contact. [16] Friction-based counterweight mechanism for coupling with a closure flap to assist the opening and closing of the closure flap for at least one section of a path between a fully closed position and a fully open position of the closure flap, the counterweight mechanism comprising: an elongated element positioned on a longitudinal axis extending between the proximal and distal ends of the counterweight mechanism, wherein the elongated element has a circumferential surface and a proximal end for coupling with either the closure flap or a vehicle body, a runner element comprising a body and at least one friction element attached to the body, wherein the runner element is positioned on the longitudinal axis for reciprocating movement along this axis and for forming contact between the at least one friction element and the circumferential surface, wherein the contact serves to generate a first friction force in a first region along the longitudinal axis and a second friction force, different from the first friction force, in a second region along the longitudinal axis, wherein the first region along the longitudinal axis is spaced apart from the second region, and a support element coupled at a proximal end to the runner element for coupling at a distal end to a vehicle body or the closure flap, wherein the support element serves to guide the back-and-forth movement. [17] Friction-based counterweight mechanism according to claim 16, which further comprises a first region having a first friction configuration parameter which is different from a second friction configuration parameter of the second region, such that a change in the first and second friction configuration parameters by at least one friction element when the runner element moves from the first region to the second region results in a change in the friction force magnitude. [18] Friction-based counterweight mechanism according to claim 17, wherein the first friction configuration parameter is a width dimension of the elongated element and the second friction configuration parameter is another width dimension of the elongated element. [19] Friction-based counterweight mechanism according to claim 16, wherein the elongated element has a third area along the longitudinal axis for generating the frictional force through contact. [20] Friction-based counterweight mechanism according to claim 1, further comprising the closure flap coupled to the counterweight mechanism on one side of it, such that the support element is a lead screw actively driven by a motor arrangement, and comprising a second counterweight mechanism coupled to another side of the closure flap, such that the movement of the closure flap passively actuates the second counterweight mechanism.