Seat belt retractor

Abstract

The invention relates to a seat belt retractor (1) comprising a belt spool (4) which is rotatably mounted in a housing and on which a seat belt can be wound, the housing being fastenable to a vehicle, and an electric motor (5) for driving the belt spool (4) in rotary motion, and a gear mechanism (6) which transmits the rotary motion from the electric motor (5) to the belt spool (4), wherein the gear mechanism (6) can be driven in a first force transmission path as an assembly in order to drive the belt spool (4) with a first torque, and the gear mechanism (6) can be driven to drive the belt spool (4) with a second torque by switching a speed-controlled and / or torque-controlled coupling (8), thereby opening a second force transmission path, wherein the coupling (8) has at least one coupling element (15) which is spring-loaded by a spring (12) into engagement in a first part (13) of the gear mechanism (6), wherein a drive wheel (17) which is connected in a rotationally fixed manner to the electric motor (5) is provided with a polygonal force transmission profile (19), and the coupling element (15) has at least one force transmission portion (20, 21) which abuts against the polygonal force transmission profile (19) and by which, as a result of a relative movement of the drive wheel (17) with respect to the coupling element (15) when a predetermined rotational speed and / or a predetermined torque and / or a predetermined rotational acceleration transmitted by the drive wheel (17) is exceeded, the coupling element (15) can be moved out of engagement in the first part (13) of the gear mechanism (6) against the force of the spring (12).

Description

[0001] This invention relates to a seatbelt retractor.

[0002] The seatbelt retractor has a load-bearing frame and a seatbelt reel as basic components. The seatbelt reel is rotatably mounted in the frame, and the seatbelt can be wound around the seatbelt reel. The frame is used not only to mount the seatbelt reel but also to fasten it to the seat structure or vehicle structure, and for this purpose is made of steel plates of corresponding thickness bent into a U-shape.

[0003] Furthermore, in modern seatbelt devices, the seatbelt retractor is equipped with an electric motor that, upon startup, drives the belt shaft to reversibly tighten the seatbelt, for example, in the winding direction. This electric motor is also fastened to the frame and arranged laterally to the belt shaft, with the drive shaft oriented parallel to the axis of rotation of the belt shaft. Additionally, a gear mechanism is known to be provided between the belt shaft and the electric motor, through which the rotational speed of the electric motor is converted into a predetermined rotational speed of the belt shaft. The use of the gear mechanism also allows for the use of the most compact possible electric motor with a high rotational speed. Therefore, although the use of a compact electric motor is made possible by the gear mechanism, a seatbelt retractor with increased installation space requirements is generally produced. Such seatbelt retractors are known, for example, from publication WO 03 / 0 99 619A2.

[0004] If the belt shaft is to be driven at different rotational speeds and torques, an additional gear stage must be provided, which further increases the installation space requirements. Such seat belt retractors are known, for example, from publication DE 19927 731C2.

[0005] Because the installation space available in the seat structure of a vehicle seat, or even in very small vehicles, is very limited in size and cannot be expanded as desired due to design reasons, the placement of such seat belt retractors in vehicle seats or even in small vehicles is fundamentally problematic.

[0006] DE 10 2018 219 040 A1 discloses a seatbelt retractor, wherein the installation space requirement is further reduced by driving a gear mechanism as a component in a first force transmission path and by providing a coupling that activates the gear mechanism and opens a second force transmission path through a switching operation. Thus, a gear mechanism with a single force transmission path can be used to achieve two different gear ratios. In this case, the gear mechanism itself is driven as a component (i.e., as a block) in the first force transmission path, and the gear mechanism parts themselves do not move relative to each other. Here, the coupling has a drive wheel driven by the electric motor and has three triangular openings that narrow radially outward, and in each triangular opening, a coupling pawl engages with a corresponding control pin. These coupling pawls are guided radially in a longitudinally displaceable manner and are each spring-loaded radially outward via a spring. To switch the coupling, when a specific rotational acceleration of the drive wheel is exceeded, the coupling pawls are pulled radially inward against the spring force, thereby releasing the rotational connection between the coupling pawls and the first part assigned to the gear mechanism.

[0007] In view of this background, the object of the present invention is to provide an improved seat belt retractor having an electric motor and a gear mechanism having a coupling with a simplified structure.

[0008] To achieve this objective, a seatbelt retractor has been proposed. Further preferred developments of the invention can be obtained from the dependent claims, drawings, and related description.

[0009] According to the basic idea of ​​the invention, the drive wheel, which is rotatably fixed to the electric motor, is provided with a polygonal force transmission profile, and the coupling element has at least one force transmission portion that abuts against the polygonal force transmission profile and, through the at least one force transmission portion, due to the relative movement of the drive wheel when the predetermined rotational speed and / or predetermined torque transmitted by the drive wheel is exceeded, the coupling element can move against the force of the spring and disengage from engagement in the first part of the gear mechanism.

[0010] The advantage of this solution is that the drive wheel directly triggers the coupling movement of the coupling element by providing a stress-transmitting surface through a polygonal profile. The coupling element itself is spring-loaded in the engagement direction within the first component, wherein the spring force is designed such that the drive wheel only moves the coupling element out of the engagement position after a predetermined rotational speed and / or predetermined torque and / or predetermined rotational acceleration has been exceeded, thereby releasing the rotational connection generated via the coupling element. By releasing this rotational connection, the first force transmission path generated by the rotational connection can be interrupted, for example, and a second force transmission path can be opened. In this second force transmission path, for example, a gear mechanism can be inserted, which, upon activation, converts the rotational speed of the electric motor into a lower rotational speed transmitted to the shaft, for example, at a gear ratio of 1:80.

[0011] Furthermore, it is proposed that the coupling element transmits the rotational motion of the drive wheel at a speed lower than the predetermined rotational speed and / or a torque lower than the predetermined torque to the first component of the gear mechanism. Therefore, under conditions of low torque, low rotational speed, and / or low rotational acceleration, the rotational motion of the electric motor can be directly transmitted to the first component of the gear mechanism via the coupling element in the first force transmission path, for example, to the belt shaft at a 1:1 gear ratio. This enables functions such as assisting in the seatbelt's winding into the parking position and providing comfort by adjusting the retraction force acting on the belt shaft.

[0012] In this configuration, the coupling element preferably has an engagement portion that engages with the first part of the gear mechanism, and the coupling element may have at least two force-transmitting portions that are symmetrical about an axis of symmetry extending through the engagement portion, and the coupling element abuts against the polygonal force-transmitting profile of the drive wheel through these force-transmitting portions. The coupling element transmits the rotational motion to the first part via the engagement portion. Because the force-transmitting portions symmetrical in the two rotational directions have as similar a force ratio as possible, force transmission occurs from the drive wheel to the coupling element, and the coupling element can be mounted in two different orientations.

[0013] Furthermore, it is proposed that the cross-section of the polygonal force transmission profile has a triangular profile, and the coupling element surrounds this triangular profile at both corners. The coupling element overlaps the force transmission profile at the two corners in a form-fitting manner, and thus transmits rotational drive motion in both rotational directions. Moreover, therefore, when one of these predetermined conditions is exceeded, the coupling element is driven in a form-fitting manner and pulled out from the engagement position.

[0014] In this method, symmetrical force transmission with the most similar force ratios can preferably be achieved in both rotational directions via a triangular profile having an equilateral triangular geometry. Furthermore, this facilitates assembly, as the seatbelt retractor can thus be assembled at three different locations on the drive wheel. Since the apexes of the triangular profile therefore have the same geometry, the apexes of the coupling elements that abut against the force transmission portion are particularly irrelevant.

[0015] Furthermore, it is proposed that the coupling element is mounted on a second part of the gear mechanism, and the second part has a gear that is rotatably fixedly connected to it, and the second part engages with one or more gears of the transmission gear mechanism via the gear. Therefore, the second part of the gear mechanism on which the coupling element is mounted simultaneously forms a drive device via the gear that is rotatably fixedly connected to it, and the rotational motion is introduced into the transmission gear mechanism via the drive device.

[0016] Furthermore, it is proposed that, in this configuration, the second component has a stop surface, and the drive wheel with a force-transmitting profile abuts against this stop surface by performing relative motion. Relative motion is triggered when a predetermined rotational speed, predetermined torque, and / or predetermined rotational acceleration is exceeded. Consequently, the coupling element moves out of the engagement position, and the drive wheel abuts against the second component by force transmission. Thus, the drive wheel drives the second component, and when the rotational connection between the drive wheel and the first component is simultaneously released, the transmission gear mechanism is also driven via a gear that is rotationally fixed to it.

[0017] Furthermore, it is proposed that the spring is formed of a bow spring, which is connected to the coupling element at a first end and to the second part at a second end. The advantage of using a bow spring is that it is cost-effective, easy to assemble, and can be very easily connected to the coupling element and the second part in a force transmission manner (e.g., through an opening or a stop surface).

[0018] In this configuration, the second part may preferably have a guide in which the coupling element is guided via an engagement portion. The movement of the coupling element is triggered by a spring force and the movement of the drive wheel, and the direction of movement is defined by the guidance of the coupling element on the second part. In this case, guiding the coupling element in the region of the engagement portion is particularly advantageous, as the coupling element is thus preferably guided as close as possible to the connection to be made with the first part and receives support there.

[0019] The invention will now be explained using preferred embodiments with reference to the accompanying drawings. The following is shown:

[0020] Figure 1The seatbelt retractor according to the present invention has two housings in an assembled and disassembled state.

[0021] Figure 2 Exploded view of the gear mechanism of the seat belt retractor, the electric motor, and the coupling arranged therebetween.

[0022] Figure 3 The coupling is shown in a cross-sectional view in its first position, and

[0023] Figure 4 A cross-sectional view of the coupling in the second position.

[0024] Figure 1 A seatbelt retractor 1 according to the invention is shown, which has a housing consisting of two housing shells 2 and 3, and is used not only to fasten the seatbelt retractor 1 to the vehicle, preferably to the narrow, elongated mounting space of the vehicle seat, but also to install and fasten the various parts of the seatbelt retractor 1, which will be described in more detail below. The housing may also be part of the vehicle seat or a higher-level structure of the vehicle, such as a pillar or bar.

[0025] The housing internally houses multiple tabs 24 for mounting the seatbelt retractor 1. These tabs are oriented perpendicular to the rotation axis of the seatbelt retractor and are connected to the housing in a form-fitting manner and rotatably fixed relative to the rotation axis. The seatbelt retractor 1 has a belt shaft 4 as a basic component, on which the seatbelt for restraining the passenger can be wound. Furthermore, an irreversible belt tensioner 7 is provided to drive the belt shaft 4 in the winding direction, thus eliminating any belt slack present in the early stages of an accident. Additionally, an electric motor 5 and a gear mechanism 6 are provided. The belt shaft 4, the irreversible belt tensioner 7, the electric motor 5, and the gear mechanism 6 are arranged coaxially with each other. Furthermore, the electric motor 5, the gear mechanism 6, and the irreversible belt tensioner 7 are dimensioned on their external dimensions perpendicular to the rotation axis of the belt shaft such that they are smaller than the maximum diameter of the wound belt fully wound on the belt shaft 4. Because the cross-section of the housing has an angular design, additional free space is provided in these corners. This additional free space can be used, for example, to arrange the tensioning drive tube of the irreversible belt tensioner 7 or other attachment parts, such as control units or even wiring. Therefore, the maximum external dimension is predetermined by the maximum diameter of the winding belt. Since the maximum diameter is also predetermined by the thickness of the seat belt and the maximum length of the seat belt to be wound and cannot be reduced without altering the seat belt, the seat belt retractor 1 has a minimum possible dimension perpendicular to the axis of rotation of the belt shaft 4, and thus can be arranged and secured in the very narrow and elongated free space of the vehicle seat and vehicle structure.

[0026] Figure 2The electric motor 5 and gear mechanism 6, coupling 8 arranged therebetween, and optional force limiting unit 11 are shown.

[0027] The gear mechanism 6 includes a coupling 8 as a basic component, a transmission gear mechanism 9 designed here as planetary gears, and a gear mechanism housing 10. The gear mechanism 6 is externally surrounded by the gear mechanism housing 10 and has a basic cylindrical shape. The gear mechanism housing 10 itself is tubular or annular and has internal teeth on its inner side in which the planetary gears of the planetary gears roll.

[0028] The electric motor 5 has a drive shaft 18 that is directed to the outside, and a drive wheel 17 is fixed to the drive shaft in a rotationally fixed manner via a toothed engagement. When started, the electric motor 8 therefore directly drives the drive wheel 17.

[0029] In its basic structure, the coupling 8 includes a first part 13, a second part 14, a coupling element 15, and a spring 12. The first part 13 is formed in the shape of a ring with a regular tooth profile 30 arranged radially on the inner side. Furthermore, the first part 13 has a plurality of grooves radially on the outer side and aligned with grooves in the gear housing 10. The first part 13 is covered at its end face by a cover plate 16, which additionally has axially projecting fingers that engage with the first part 13 and the radially outer grooves of the gear housing 10, thereby fixing the first part 13 circumferentially relative to the gear housing 10 in a rotationally fixed manner. If the connection is achieved via a pressure fit, this additionally achieves axial fixation of the first part 13 relative to the gear housing 10. The first part 13 has a radially circular free space on its inner side, in which the second part 14 of the coupling 8 is rotatably arranged, such as... Figure 3 and Figure 4 As shown. Therefore, after the cover plate 16 has been attached, the second part 14 is also axially fixed. Furthermore, the cover plate 16 has a central opening through which the drive wheel 17 extends. The drive wheel 17 has a polygonal force transmission profile 19 at its free end, through which the drive wheel engages in the free space radially inwardly disposed in the second part 14. Furthermore, a coupling element 15 is arranged in the free space of the second part 14 such that it radially surrounds the force transmission profile 19 on the outer side.

[0030] The polygonal force transmission profile 19 of the drive wheel 17 has an equilateral triangle geometry, with three corners 27, 28, and 29 of the same angle, and therefore lateral force transmission surfaces with the same orientation. The coupling element 15 has a radially projecting engagement portion 22 through which the coupling element is radially displaceable within the guide 32 of the second part 14. Furthermore, the coupling element 15 has two bow-shaped arms that are symmetrical about an axis of symmetry S extending through the center of the engagement portion 22 and approximately complementary to each other to form a semicircle. At the ends of these arms, the coupling element 15 forms force transmission portions 20, 21, respectively, which point radially inward and through which the coupling element surrounds the corners 28, 29 of the force transmission profile 19 of the drive shaft 17, as shown in… Figure 3 As can be seen, spring 12 is designed in the form of a bow spring and is attached to coupling element 15 at its first end 25 in an opening arranged radially inward from engagement portion 22 on the axis of symmetry S. Furthermore, spring 12 is attached to an opening in second part 14 at its second end 23, which is arranged such that in the unloaded arrangement of coupling element 15, i.e., when electric motor 5 is stationary, it is also on the axis of symmetry S. With regard to its spring characteristics and the arrangement of the two fixed ends 25 and 23, spring 12 is designed such that it radially pushes coupling element 15, having engagement portion 22, outward to engage in the toothed profile 30 of first part 13. Therefore, in the unloaded state, a rotational connection is created between first part 13 and second part 14 via coupling element 15.

[0031] In electric motor 5 Figure 3 When the coupling element 15 is in its initial position and operating at low torque, rotational speed, and / or rotational acceleration, such as for example, to wind a seatbelt into a parking position or to adjust the retraction force applied to the belt shaft 4 (comfort function), the drive wheel 17 drives the first part 13 via the force transmission profile 19 and the coupling element 15. Since the first part 13 is rotatably fixed to the gear mechanism housing 10 via the cover plate 16, the entire gear mechanism 6 is driven as a component, and thus the belt shaft 4 is driven at a 1:1 gear ratio. In this case, the belt shaft 4 can be driven in two rotational directions via two force transmission sections 20, 21, wherein force transmission occurs only via one of the force transmission sections 20 or 21 depending on the rotational direction. Because both the coupling element 15 and the force transmission profile 19 are... Figure 3The positions of the components are symmetrically oriented about the axis of symmetry S, thus generating the same force conditions in both rotational directions. On its axial end face facing the planetary gear, the second component 14 has a centrally located gear 31 that engages with the teeth of the planetary gears. Since the second component 14 rotates at the same speed as the first component 13, the entire gear mechanism 6 is also driven via the central gear 31. The entire gear mechanism 6, together with the first component 13 and the second component 14, rotates as a component at a speed driven by the drive shaft 17, while the gears of the gear mechanism 6 do not perform any further relative rotational motion relative to each other.

[0032] The coupling 8 is opened by increasing the power of the electric motor 5 (e.g., for reversible belt tension) to a degree exceeding a predetermined rotational speed, predetermined torque, and / or predetermined rotational acceleration. In this case, the drive wheel 17 rotates so rapidly that the coupling element 15 lags behind and is pulled in against the spring force of the spring 12. Figure 4 In the position shown, the coupling element 15 with the engagement portion 22 disengages from the tooth profile 30, and the rotational connection between the first part 13 and the second part 14 is released. Thus, the coupling 8 is opened. Simultaneously, the drive shaft 17 abuts against the side of the force transmission profile 19 on the stop surface 26 of the second part 14, and therefore subsequently directly drives the second part 14 to rotate, while the first part 13 is no longer driven due to the opened coupling 8.

[0033] In this configuration, the rotational motion of the second component 14 is transmitted to the planetary gears via the central gear 31. The gear mechanism housing 10 is no longer driven and can be additionally locked to the vehicle via the locking device 33; in any case, the planetary gears rotate relative to the gear mechanism housing 10, and the rotational motion of the drive shaft 17 is now converted into a slower rotational speed on the belt shaft 4 at a gear ratio of 1:80. Due to the conversion of the higher rotational speed into a lower rotational speed, the torque applied to the belt shaft 4 and the resulting retraction force on the seatbelt both increase simultaneously.

[0034] Therefore, the electric motor 5 can operate in the first force transmission path with a 1:1 gear ratio and a rotational speed of 60 rpm to 180 rpm when the coupling 8 is closed and the gear mechanism 6 is disengaged, so that the seat belt can be wound into the parking position by rotating the gear mechanism 6 as a block after unhooking. If the proposed rotational speed is also the rotational speed of the belt shaft 4, the rotational drive motion can also be further transmitted to the belt shaft 4 with a 1:1 gear ratio. For reversible belt tensioning, the rotational speed of the electric motor 5 can be suddenly increased to 5000 rpm to 15000 rpm, which is converted by the gear mechanism 6 in the second force transmission path opened by the coupling 8 to a lower rotational speed of approximately 140 rpm to 420 rpm at a gear ratio of 1:80 for the output gear 23. To switch the coupling 8, a significantly higher rotational drive speed of 5000 rpm to 15000 rpm is used compared to the rotational drive speed of 60 rpm to 180 rpm when driving the belt shaft 4 in the first force transmission path. Therefore, the coupling 8, or the gear mechanism 6 with an integrated coupling 8, can be designed to open only, for example, at rotational drive speeds exceeding 1000 rpm. Thus, the transmission of rotational drive motion from 60 rpm to 180 rpm in the first force transmission path occurs reliably, and unintentional opening of the coupling 8 during the seatbelt winding operation into the parking position is prevented. Furthermore, as an alternative to speed-controlled opening, the coupling 8 can also open when the torque to be overcome suddenly increases at the same or reduced rotational speed. This occurs, for example, when the seatbelt is wound up at high speed into the parking position. As the seatbelt subsequently winds up almost completely, the torque to be overcome increases, and the coupling 8 automatically switches. By switching the coupling 8, the rotational speed of the output gear 23 decreases, and the torque applied by the output gear 23 increases, causing the seatbelt to subsequently wind up with a lower retraction speed and a greater retraction force.

[0035] Due to the planetary gears, specifically a two-stage planetary gear system, the gear mechanism 6 has a single force transmission path. Using the proposed solution of transmitting rotary drive motion via the rotating gear mechanism 6 as a component, a first force transmission path is created to achieve the first function—winding the seatbelt into the parking position—without additional installation space requirements. Furthermore, the switching of the coupling 8 occurs very simply by increasing the rotational speed, such that when the rotational speed of the electric motor 5 increases to tension the seatbelt, i.e., for its second function, the second force transmission path automatically opens. Therefore, the switching of the coupling 8 is controlled directly by changing the function of the electric motor 5 itself.

[0036] Furthermore, the electric motor 5 and gear mechanism 6 are cylindrical and coaxially oriented with each other and with the axis of rotation of the belt shaft 4. Moreover, in cross-section relative to their axis of rotation, both the electric motor 5 and gear mechanism 6 have a diameter smaller than the outer diameter of the winding belt when the seatbelt is wound to its maximum extent. This results in a very small, elongated structure for the seatbelt retractor, the maximum external dimension of which is predetermined by the maximum outer diameter of the winding belt. Since the maximum outer diameter of the winding belt is absolutely predetermined by the thickness and length of the seatbelt to be wound and cannot be reduced, the seatbelt retractor can be formed with the minimum possible size having a rotation axis perpendicular to the belt shaft 4.

[0037] The coupling 8 is understood herein as a component of the gear mechanism 6, such that the first part 13 and the second part 14 are naturally parts of the coupling 8, but are therefore also parts of a higher-level component of the gear mechanism 6. For this purpose, the coupling 8 is preferably arranged on the input side of the gear mechanism 6 facing the electric motor 5.

[0038] The electric motor 5 is preferably voltage-controlled, and as a result of applying different voltages, it causes different torques acting on the belt shaft 4 or different retraction forces applied to the seat belt. In the normal wearing state of the seat belt, a voltage of 2V to 3V is applied, thereby reducing the retraction force to the lowest possible level, yet sufficient to reliably pull the seat belt toward the passenger after movement. To wind the seat belt into the parking position after unfastening, the voltage is increased to 9V, causing the seat belt to wind into the parking position with increased retraction force. Furthermore, during reversible tensioning operations, the voltage is also increased to 12V, which can be increased to approximately 36V, for the possible additional function of reversible belt tensioning with increased retraction force.

Claims

1. A seatbelt retractor (1), comprising: - A belt shaft (4), which is rotatably mounted in the housing and around which a seatbelt can be wound, the housing being fastened to a vehicle, and - Electric motor (5), the electric motor being used to drive the belt shaft (4) to rotate, and - Gear mechanism (6), which transmits the rotational motion from the electric motor (5) to the belt shaft (4), wherein - The gear mechanism (6) can be driven as a component in the first force transmission path to drive the belt shaft (4) with a first torque, and - The gear mechanism (6) can be driven to drive the belt shaft (4) with a second torque by switching a speed-controlled and / or torque-controlled coupling (8), thereby opening a second force transmission path, wherein - The coupling (8) has at least one coupling element (15), which is spring-loaded by a spring (12) to engage in the first part (13) of the gear mechanism (6). Its features are, - The drive wheel (17) connected to the electric motor (5) in a rotationally fixed manner is provided with a polygonal force transmission profile (19), and - The coupling element (15) has at least one force transmission portion (20, 21) that abuts against the polygonal force transmission profile (19) and through the at least one force transmission portion, due to the relative movement of the drive wheel (17) relative to the coupling element (15) when exceeding a predetermined rotational speed and / or predetermined torque and / or predetermined rotational acceleration transmitted by the drive wheel (17), the coupling element (15) is able to move out of engagement with the first part (13) of the gear mechanism (6) against the force of the spring (12). - The coupling element (15) is mounted on the second part (14) of the gear mechanism (6), and - The second part (14) has a rotatably connected gear (31), which engages with one or more gears of the transmission gear mechanism (9) via the gear. - The spring (12) is formed of a bow spring, which is connected to the coupling element (15) at a first end (25) and to the second part (14) at a second end (23).

2. The seatbelt retractor (1) according to claim 1, characterized in that, - The coupling element (15) transmits the rotational motion of the drive wheel (17) at a speed lower than the predetermined rotational speed and / or a torque lower than the predetermined torque to the first part (13) of the gear mechanism (6).

3. The seatbelt retractor (1) according to claim 1 or 2, characterized in that, - The coupling element (15) has a engagement portion (22) that engages in the first part (13) of the gear mechanism (6), and - The coupling element (15) has at least two force transmission portions (20, 21) that are symmetrical about an axis of symmetry (S) extending through the engagement portion (22) and the coupling element (15) abuts the polygonal force transmission profile (19) of the drive wheel (17) through the at least two force transmission portions.

4. The seatbelt retractor (1) according to claim 3, characterized in that, - The cross-section of the polygonal force transmission profile (19) has a triangular profile, and - The coupling element (15) surrounds the triangular profile at the two corners (27, 28, 29).

5. The seatbelt retractor (1) according to claim 4, characterized in that, - The triangular outline has the geometry of an equilateral triangle.

6. The seatbelt retractor (1) according to claim 3, characterized in that, - The second part (14) has a stop surface (26), and the drive wheel (17) having the force transmission profile (19) abuts against the stop surface in a force transmission manner by performing the relative motion.

7. The seatbelt retractor (1) according to claim 6, characterized in that, - The second part (14) has a guide (32), in which the coupling element (15) is guided by the engagement portion (22).

Images