Seat belt retractor with electrically operated blocking device

Abstract

The present invention relates to a seat belt retractor, - a toothed control disk (21) rotatably mounted on the belt shaft; an electrically actuatable blocking device (100); a blocking lever (2) pivotally mounted in a pivot bearing on the first upstanding rim (16), - an electrically actuatable blocking device (100) stops the control disc (21) relative to the belt shaft, so that the belt shaft is blocked in the unwinding direction; a blocking lever (2) having a lever arm (22) on which a first spring (4) acts, the spring having a blocking tip arranged thereon, thereby preloading the blocking lever (2) into a position in which the blocking tip (25) engages with a toothing (26) of the control disc (21); - an electromagnet (3) arranged in the housing (1) and exerting a force, the blocking tip (25) being retracted from the teeth (26) of the control disc (21); The present invention relates to a seat belt retractor in which a second spring (17) is provided and the blocking lever (2) is arranged so that, regardless of its position, it is stationary against the second spring by means of its blocking arm (23) and is loaded by the blocking arm (23) during its pivoting movement out of the toothing (26) of the control disc (21).

Description

Technical Field

[0001] The present invention relates to a seat belt having an electrically actuable blocking device having the features of the preamble part of claim 1.

Background Art

[0002] An electrically actuable blocking device of this type is known, for example, from British Patent Application Publication No. 2398824(A).

[0003] Such a blocking device is used to stop an externally toothed control disk rotatably mounted on the belt shaft of a seat belt retractor relative to the belt shaft by engagement of a blocking lever, as a result of which a blocking pawl is forced to perform a control movement onto a toothed part fixed to the vehicle, as a result of which the belt shaft is blocked in the pulling-out direction.

[0004] In conventional mechanical locking devices, an inert mass is applied to the contact surface, which deflects when a predetermined vehicle deceleration is exceeded, thereby deflecting the locking lever and engaging it with the teeth of the control disc. Such mechanical locking devices are also called vehicle-sensing sensor devices. One problem with these mechanical locking devices is that the inert mass must always be aligned on the contact surface in a predetermined orientation relative to the vehicle's longitudinal and transverse axes, regardless of the installation geometry of the seat belt retractor, so that the belt shaft is not unintentionally locked. Therefore, the seat belt retractor must be designed individually for the vehicle, and in this design, the orientation of the contact surface and the mass applied to the contact surface are individually designed for the seat belt retractor to correspond to a predetermined orientation, taking into account the installation geometry of the seat belt retractor in the vehicle. Furthermore, in the case of seat belt retractors integrated into the front seats, for example in convertibles, when the tilt angle of the backrest is adjusted to access the back seat, or when the backrest is folded forward, an inert mass unintentionally bends against the contact surface, resulting in the problem that the locking lever is unintentionally pushed into the outer teeth of the control disc for control movement. Consequently, the seat belt retractor is locked in the pulling direction, the backrest cannot pivot further, or the occupant cannot fasten the seat belt. To prevent this, an additional disconnection or compensation mechanism must be provided, but these mechanisms can only operate in these cases so that occupant restraint is guaranteed in all cases in the event of an accident. As a result of achieving these objectives, this type of mechanical locking device is mechanically very complex.

[0005] In contrast to electrically operated blocking devices, as known, for example from British Patent Application Publication No. 2398824(A), the movement of the blocking lever is electrically controlled, and as a result, the previously required inert mass is eliminated. This allows the seat belt retractor to be mounted without change in different installation positions within the vehicle and within the backrest. Furthermore, blocking of the belt shaft can be controlled by an electrical signal emanating from a control device. In this case, the signal can be generated by the control device, which can also generate signals in response to other sensor devices or control systems. For example, when a dynamic assistance system is activated, the belt shaft is intended to be automatically blocked, and the dynamic assistance system is controlled, for example, in response to a signal from an optical sensor device. Thus, the electrically operated blocking device is also controlled directly or indirectly in response to a signal from an optical sensor device. Furthermore, since electrically operated blocking devices are not actuated by inertial forces and therefore do not need to be oriented in a specific direction relative to the direction of vehicle travel, they function in any orientation and position. Therefore, preferably, the seats can be placed in at least semi-autonomous vehicles, allowing the occupants to adjust the seats for improved communication with other occupants, for positioning in a stationary position, or to take advantage of the degrees of freedom provided by autonomous driving with a much wider range of adjustment than was possible with conventional non-autonomous vehicle seats.

[0006] An electrically actuated blocking device 100, used by the applicant in the applicant's products and corresponding to an embodiment of UK Patent Application Publication No. 2398824(A), is shown in Figures 1 and 2. The electrically actuated blocking device 100 comprises, as basic elements, a housing 1 having an L-shaped basic structure comprising a base plate 15 and a first upright rim 16; a blocking lever 2 pivotably mounted on the first upright rim 16 of the housing 1; an electromagnet 3; and a first spring 4 held by one end of the housing 1 and connected by the other end of a lever arm 22 of the blocking lever 2 projecting outward from the first upright rim 16. The first spring 4 is designed as a tension spring, thereby preloading the blocking lever 2 into a position where the blocking lever 2 engages with the blocking tip 25 in the teeth 26 of the control disc 21, thereby returning and holding the control disc 21 relative to the belt shaft 20. The control disc 21, equipped with teeth 26, is shown only in Figure 9 in the seat belt retractor according to the present invention. In this way, as the belt shaft 20 rotates in the pull-out direction, the retaining claw is automatically pushed into the teeth fixed to the vehicle, and the belt shaft 20 is then prevented from further pulling out of the seat belt. The retaining lever 2 comprises a contour part 24 and a steel plate 5, the steel plate 5 facing the electromagnet 3, and so when the electromagnet is energized, the retaining lever 2 is attracted by the electromagnet 3 and thus pulled out from the teeth 26 of the control disc 21. As a result, the belt shaft 20 is then freely rotatable in the pull-out and pull-in directions. The advantage of this solution is that even in the event of a power outage or a malfunction of the electromagnet 3, the belt shaft 20 is prevented from pulling out, and in this case as well, the occupant is reliably restrained.

[0007] The electromagnet 3 comprises a base component 6 having a columnar central portion 7 and two radial flanges 8, one of which in each case protrudes radially outward from one of the ends of the central portion 7. The electromagnet 3 is held by the base component 6 on a base plate 15 of the housing 1. The base component 6 has a tubular through portion 14 within the central portion 7 and an annular intermediate space 9 radially outward on the central portion 7, the annular intermediate space 9 being confined toward the end central portion 7 by the radial flanges 8. Furthermore, the electromagnet 3 comprises a coil 10 having multiple windings, the coil 10 being located within the annular intermediate space 9 and making electrical contact with an external control device via a line 11 provided within the base component 6. In addition, the electromagnet 3 comprises a first iron core 12, the first iron core 12 being located within the tubular through portion 14 of the base component 6, with its free end facing the steel plate 5 of the blocking lever 2.

[0008] When coil 10 is energized, the locking lever 2 is attracted to close the first magnetic circuit I, which is defined by the first upright rim 16 of housing 1, the first core 12, and the portion of the locking lever 2 and base plate 15 between the first core 12 and the first upright rim 16, as shown in the right view of Figure 2. Furthermore, a damping element 13 is provided in the form of an essentially flexible tube, for example, a short piece of tube, and this element is clamped at its end between two extensions of the radial flange 8 facing the locking lever 2. The damping element 13 is positioned such that the free end of the locking lever 2 does not rest on the damping element 13 in the bent position (left view of Figure 2), but only rests on the central soft portion of the damping element 13 between the clamping points in the attracted position (right view of Figure 2). As a result, the attracting motion of the locking lever 2 is damped in the final stage of motion. As a result of this damping, a flexible stop is achieved, and disruptive "rattling noises" are avoided during the pulling motion of the stop lever 2 and any subsequent slight movements that may occur. [Overview of the project] [Problems that the invention aims to solve]

[0009] The object of the present invention is to provide a seat belt retractor equipped with an electrically operated blocking device that is improved with respect to blocking motion.

[0010] To achieve the objective, a seat belt retractor having the features of claim 1 has been proposed. Furthermore, preferred embodiments of the present invention can be obtained from the dependent claims, figures, and related description.

[0011] According to the basic concept of the present invention, a second spring is provided, and this second spring is positioned such that the stopping arm of the stopping lever remains stationary relative to the second spring regardless of its position, and tension is applied to the lever in the case of pivotal movement by the stopping arm extending from the teeth of the control disk.

[0012] The proposed solution has several advantages. The first advantage is that the second spring is tensioned by the pivoting motion of the stopping lever extending from the teeth of the control disc, and the stopping motion of the stopping lever during the pivoting motion of the teeth of the control disc is assisted by the force applied by the second spring during relaxation, in addition to the force applied by the first spring. As a result, the time required to stop the control disc, and therefore the time required to stop the belt shaft, can be reduced to, for example, less than 4 ms. Another advantage is that, since the stopping lever is stationary relative to the second spring regardless of its position, firstly, the motion of the stopping lever is initiated directly, and secondly, undesirable rattling noises are permanently prevented regardless of the position of the stopping lever. Furthermore, the stopping lever can be fixed in place by its permanent proximity to the second spring, regardless of its position, thereby preventing undesirable movement of the stopping lever.

[0013] Furthermore, it is proposed that a second spring supports the blocking lever in the region of the blocking arm, on the side opposite to the control disk. In the proposed advanced form, the blocking lever can be acted upon by pressure through simple support on the second spring. This eliminates the need for additional connections between the blocking lever and the second spring. Furthermore, the blocking lever is preferably stationary on the second spring using the blocking arm, and as a result, the blocking lever is acted upon by the lever arm through the blocking arm in tensile and compressive forces on two sides at two mutually spaced positions on either side of its pivot bearing.

[0014] Furthermore, it is proposed that a second spring is fixed by its first and second ends, and that the locking lever is held stationary by a locking arm against the spring portion of the second spring positioned between the first and second ends of the spring. The second spring is fixed to the locking lever in the form of a contact portion by being fixed to the locking device by its two ends, and together with the spring portion provided between the two fixed ends, simultaneously forms an elastic contact surface for the locking lever. In this case, the two ends of the second spring are fixed to the locking device in a tensile resistance manner such that they are pulled in the region of the spring portion during the pulling motion of the locking lever, and the tightening force generated in the spring in the process is absorbed by the locking device via the two fixed ends.

[0015] Furthermore, the blocking arm may preferably have a profile structure adapted to the surface of the spring on a surface provided to contact the second spring. The contact surface between the blocking lever and the second spring may be increased by this adapted profile or surface structure. In this case, the adapted profile structure may be molded to conform to the shape of the second spring in a tensioned and / or relaxed state. In this case, molding of the surface of the blocking lever in the longitudinal direction of the second spring and in the transverse direction of the second spring is available to form the surface structure. In this case, the profile structure may be realized, for example, in the form of one or two curves intentionally designed on the surface of the blocking lever, i.e., it may be intentionally designed to be non-uniform.

[0016] The profile structure can preferably be formed by multiple cams of different heights, with the tallest cam positioned in the center and the lower cams positioned laterally symmetrically with respect to the central cam of the tallest height. As a result of forming the proposed profile structure, the contact surface of the locking lever increases continuously from the initial smaller contact surface to the larger contact surface during the tightening of the second spring, thereby enabling the spring tension to increase along with the spring force, and consequently increasing the braking force acting on the locking lever.

[0017] Furthermore, the surface of the second spring may have a structure consisting of multiple grooves extending perpendicularly to the pivot axis of the locking lever. The proposed profiling has the advantage that the locking lever is secured by the grooves in an improved manner against lateral displacement of the second spring.

[0018] Furthermore, it is proposed that the second spring be formed by a coil spring. Coil springs can be manufactured very cost-effectively in mass production and can be procured and installed as finished parts. In this case, they also have the advantage that, due to the winding, they already have a profile surface structure with grooves and can be used to laterally fix the locking lever in place, as described above.

[0019] Furthermore, it has been proposed that a second spring be positioned at an angle of 5 to 15 degrees with respect to the pivot axis of the locking lever, thereby extending the length of the second spring within the same installation space width, and thereby improving the spring characteristics. If a coil spring is provided, the winding pitch can be further compensated by the proposed arrangement in which the coil spring is positioned at the same angle in a corresponding manner opposite to the winding pitch. Thus, the second spring can be positioned such that the groove between the windings is perpendicular to the pivot axis of the locking lever.

[0020] Furthermore, it is proposed that an impact damper to limit the pivoting motion of the blocking lever be provided on the fixed opposing surface of the blocking lever and / or blocking device. The movement of the blocking lever in the final stage can be further damped by the impact damper. In this case, noise generation that may occur when the blocking lever makes contact, even though it is stationary on the second spring, can be further reduced by the damping characteristics of the impact damper. For this purpose, the impact damper can be formed from, for example, a plastic material having low hardness or from an elastomer.

[0021] In this case, a particularly preferred design of the electromagnet can be achieved by having a coil with a through-opening, an iron core positioned in the electromagnet, the iron core exerting a magnetic force on a blocking lever via a steel plate when a voltage is applied to the coil, and acting on the blocking lever against the force of a first spring to cause a blocking or unblocking motion.

[0022] Furthermore, in this case, it is proposed that the movement of the blocking lever is forced by at least a first magnetic circuit formed by a first iron core, an upright first rim, and the base plate and the portion of the blocking lever between the first iron core and the upright first rim. [Brief explanation of the drawing]

[0023] The present invention will be described below based on preferred embodiments with reference to the accompanying figures. [Figure 1] Figure 1 is an exploded view of a conventional electrically operated blocking device. [Figure 2] Figure 2 is a cross-sectional view of a conventional electrically actuated blocking device having blocking levers in two different positions. [Figure 3] Figure 3 shows the deployed electrically actuated blocking device in a different diagram. [Figure 4] Figure 4 shows different enlarged detail views of the deployed electrically actuated blocking device. [Figure 5]FIG. 5 is a different enlarged detailed view of the deployed electrically actuatable blocking device. [Figure 6] FIG. 6 is a different enlarged detailed view of the deployed electrically actuatable blocking device. [Figure 7] FIG. 7 is a different enlarged detailed view of the deployed electrically actuatable blocking device. [Figure 8] FIG. 8 is a different enlarged detailed view of the deployed electrically actuatable blocking device. [Figure 9] FIG. 9 shows a side view of a seat belt retractor according to the invention comprising a deployed blocking device having blocking levers in two different positions.

BRIEF DESCRIPTION OF THE DRAWINGS

[0024] FIG. 3 shows a deployed electrically actuatable blocking device 100 according to the invention, which blocking device 100 is conceptually used in a seat belt retractor known in the prior art and replaces the blocking device 100 in FIGS. 1 and 2. The developed blocking device 100 is described in its basic structure with reference to FIGS. 1 and 2 and corresponds to the blocking device 100 known in the prior art. For this reason, the description in the introduction part of this specification is referred to, and only the structural features of the developed blocking device 100 different therefrom and the advantages resulting from the developed blocking device 100 are described below.

[0025] Figure 3 shows the deployed stopper device 100 in a position having a curved stopper lever 2, corresponding to the position of the stopper device 100 seen in the left-hand view of Figure 2. In the left-hand view of Figure 9, the same deployed stopper device 100 is seen on a seat belt retractor according to the present invention with a curved stopper lever 2, while the same stopper device 100 with a non-curved stopper lever 2 is seen in the right-hand view. In the stopper position, the stopper lever 2 engages with the stopper tip 25 in the teeth 26 of the control disc 21, thereby stopping the control disc 21 against the belt shaft 20, and consequently the stopper claw is forced to stop the belt shaft 20 in the pull-out direction for the control movement of the seat belt retractor fixed to the vehicle into the teeth. The belt shaft 20 is then prevented from pulling out the seat belt wrapped over it.

[0026] Instead of the previously provided damping element 13 (see Figures 1 and 2), a second spring 17 is provided, which is held by its two ends 18 and 19 on opposing extensions of the radial flange 8 facing the stop lever 2. The second spring 17 is designed as a coil spring having multiple windings and grooves 33 disposed between the windings on its surface, and has a spring portion 27 provided between the two ends. The second spring 17 is positioned to support the stop lever 2 with the spring portion 27 on a profile structure 28 provided on the underside of the stop arm 23. Thus, the stop lever 2 also rests on the second spring 17 in the bent position, using it as an elastic contact point, and as a result, the stop lever 2 is also fixed in place in the bent position, i.e., fixed against unintended pivoting from the teeth due to the spring force exerted by the second spring 17. The second spring 17 is positioned at an angle of 5 to 15 degrees with respect to the pivot axis of the locking lever 2, i.e., slightly obliquely, thereby increasing the spring length with the same installation width. Furthermore, if the orientation of the second spring 17 is opposite to the pitch of the coil spring windings, the winding pitch can be compensated so that the groove 32 between the windings is oriented perpendicular to the pivot axis of the locking lever. Here, the windings having the groove 33 formed between them form a surface structure that secures the locking lever 2 against lateral sliding relative to the second spring 17. If the second spring 17 is not designed as a coil spring, for example as a leaf spring, this surface structure can also be formed in the form of a recess in the second spring 17. The second spring 17 is preferably made of metal, which results in less temperature dependence and greater resistance to aging with respect to its properties compared to the use of a plastic spring.

[0027] Furthermore, in addition to the first upright rim 16, a second upright rim 35 facing the first rim 16 is provided on the base plate 15, and a second magnetic circuit can be closed via this second rim to increase the attractive force of the electromagnet 3. Furthermore, the second rim 35 can also serve to support the upper radial flange 8, or to hold the second spring 17. However, attaching the second spring 17 to the radial flange 8 of the electromagnet 3 is advantageous in this case because the second spring 17 is positioned in the part that exerts an attractive force on the blocking lever 2 when the electromagnet 3 is energized, thus directly buffering the movement of the blocking lever 2 when the electromagnet 3 is energized.

[0028] A slot 34 for securing the blocking device 100 to the seat belt retractor, particularly the housing of the seat belt retractor, is provided on the second rim 35, as can be seen in the enlarged view of Figure 6. The same slot 34 can also be provided in addition to the first upright rim 16, thereby allowing the blocking device 100 to be held on both sides.

[0029] Furthermore, an impact damper 33 is provided on the side of the steel plate 5 facing the radial flange 8, below the retaining lever 2. Line 11 is designed here as a contact pin guided vertically downward in the form of a dimensionally stable metal pin, as can also be seen in Figure 5.

[0030] When the electromagnet 3 is energized, the locking lever 2 is attracted by the magnetic force exerted on the steel plate 5 by the electromagnet 3, thereby rotating so that the locking tip 25 disengages from the teeth 26 of the control disc 21. As a result, the control disc 21 is released and, due to its spring load, rotates in the opposite direction relative to the belt shaft 20 by a small angle, thereby pulling the locking claw away from the teeth fixed to the vehicle, and as a result the belt shaft 20 can rotate freely in the pulling and retracting directions. At the same time, the first spring 4 and the second spring 17 are pulled by the pulling motion of the locking lever 2. In this case, the locking lever 2 tightens the first spring 4 via the lever arm 22 while applying a tensile force. At the same time, the locking lever 2 applies pressure to the second spring 17, which is stationary below it, via the locking arm 23, thereby deforming the second spring 17 in an arc shape toward the base plate 15. The locking arm 23 of the locking lever 2 has a profile structure 28 on its underside, consisting of three cams 29, 30, and 31 of different heights, as seen in Figure 4. The tallest cam 29 is positioned in the center between two lower cams 30 and 31 of the same height. Furthermore, the two lower cams 30 and 31 of the same height are positioned symmetrically with respect to the taller central cam 29, i.e., at the same distance from it. Thus, during the pulling motion of the locking lever 2, the second spring 17 is initially pulled by the central cam 29, and the two lower cams 30 and 31 come to rest on the second spring 17 only later, preferably simultaneously. In this way, the second spring 17 is continuously pulled by the cams 29, 30, and 31, and the tightening motion of the locking lever 2 is decelerated to its end by the rising spring force. Therefore, the cams 29, 30, and 31 form surfaces that conform to the curvature of the tensioned second spring 17 in relation to the highest point or line of their end faces. Of course, the cams 29, 30, and 31 may also be concavely curved in their longitudinal extension and have surfaces in their cross-section that conform to the curvature of the second spring 17, so that the cams 29, 30, and 31 remain stationary with respect to the second spring 17 over a wider area of ​​their periphery.

[0031] Furthermore, an impact damper 33 is provided on the underside of the stopping arm 23 of the stopping lever 2, and this impact damper faces the upper side of the radial flange 8 of the electromagnet 3, preventing the stopping lever 2 from directly contacting the radial flange 8 by its steel plate 5, even under the most unfavorable circumstances, as shown in Figure 7. The impact damper 33 has a tip, which causes the impact damper 33 to initially rest on the surface of the radial flange 8, and due to its shape, this tip increases the damping of the stopping lever 2 during the pulling motion. The impact damper 33 can be formed from, for example, a low-hardness plastic material such as an elastomer.

[0032] Figure 8 shows the attachment of the stop lever 2 to the upright first rim 16. The stop lever 2 is provided with an arm that protrudes laterally, forming an intermediate space 2b. The first rim 16 is provided with an arm 16a that protrudes upward from there, and the arm 16a engages with the intermediate space 2b. Therefore, the stop lever 2 is attached laterally to the upright rim 16. Furthermore, the intermediate space 2b simultaneously forms a stopper to restrict the movement of the stop lever 2 in the direction of the upright rim 16.

[0033] The second spring 17 is positioned at an angle not equal to 90 degrees with respect to the longitudinal axis of the blocking lever 2, preferably at an angle of 5 to 15 degrees with respect to the pivot axis of the blocking lever 2, thereby allowing the use of a longer second spring 17 with the same width as the blocking device 100 but correspondingly with more flexible spring characteristics. If the second spring 17 is designed as a coil spring, the winding pitch can be compensated by the arrangement of the second spring 17 to such an extent that the groove 33 is oriented almost perpendicular to the pivot axis of the blocking lever 2. As a result, the blocking lever 2 has improved retention on the spring 17 by the profile structure 28 and is fixed in an improved manner against lateral sliding on the second spring 17.

[0034] In addition to cushioning the pulling motion, it can be further considered that the advantage of the second spring 17 is that, when the electromagnet 3 is deactivated, the second spring 17 supports the stopping motion of the stopping lever 2 in the tensile position, and, in addition to the first spring 4, further pushes the stopping lever 2 against the teeth 26 of the control disc 21. As a result, the time of stopping the control disc 21 in the pulling direction, and therefore the time of stopping the belt shaft 20, can be reduced. Thus, the stopping lever 2 is driven for the pivoting motion required for locking by both the tensile force applied by the first spring 4 and the compressive force applied by the second spring 17.

[0035] Overall, the movement of the locking lever 2 can be performed with substantially lower, more natural motion and therefore substantially more controlled, than was possible in prior art solutions with only one first spring 4, both during the pulling motion toward the locking device 100 and during the locking motion toward the teeth 26 of the control disk 21, by the provided second spring 17 and the pressure applied through said spring. In particular, the provided second spring 17 causes the locking lever 2 to perform a pivoting motion from two sides during the locking operation, and the torques exerted on the locking lever 2 by the first spring 4 and the second spring 17 are added to each other. A further advantage of the present invention is that even if the first spring 4 does not exert a spring force on the locking lever 2 for any reason, or exerts only a lower spring force, the locking lever 2 can still perform the locking motion because the locking motion is performed by the second spring 17.

Claims

1. It is a seat belt retractor, - A rotatably mounted belt shaft, - A toothed control disc (21) is rotatably mounted thereon, - An electrically operable blocking device (100), - A housing (1) having a base plate (15) and an upright first rim (16), - A stop lever (2) is pivotably mounted within the pivot bearing of the upright first rim (16) and comprises a steel plate (5), - The electrically operated blocking device (100), by engaging the blocking lever (2) within the teeth, stops the control disk (21) relative to the belt shaft, thereby causing the blocking claw to perform a movement that engages with the teeth of the seat belt retractor fixed to the vehicle, thereby blocking the belt shaft in the pulling direction. - The blocking lever (2) has a lever arm (22) that protrudes outward from the first rim (16), and a first spring (4) acts on the lever arm (22), and the first spring (4) preloads the blocking lever (2) to a position where it engages with the blocking tip (25) located at the end of the blocking arm (23) and the teeth (26) of the control disk (21), - An electrically operated blocking device (100) comprising an electromagnet (3) disposed within the housing (1) which exerts a force on the blocking lever (2) when energized, and which, by this force, pulls the blocking lever out from the teeth (26) of the control disk (21) together with the blocking tip (25), Equipped with, A seat belt retractor characterized in that a second spring (17) is provided, the second spring (17) is positioned such that the blocking lever (2) is fixed in a predetermined position by permanent proximity to the second spring (17) regardless of its position, and tension is applied by the blocking arm (23) during the pivoting motion of the control disk (21) from the teeth (26).

2. - The seat belt retractor according to claim 1, characterized in that the second spring (17) supports the blocking lever (2) in the region of the blocking arm (23) on the side facing away from the control disk (21).

3. - The seat belt retractor according to claim 1 or 2, wherein the second spring (17) is fixed at a first end (18) and a second end (19), the stopping lever (2) abuts against the spring portion (27) of the second spring (17) at the stopping arm (23), and the spring portion (27) is positioned between the first end (18) and the second end (19) of the second spring (17).

4. - The seat belt retractor according to any one of claims 1 to 3, wherein the blocking arm (23) has a surface provided so as to abut the second spring (17) and has a profile structure (28) that is adapted to the surface of the second spring (17).

5. - The seat belt retractor according to claim 4, wherein the profile structure (28) is formed by a plurality of cams (29, 30, 31) of different heights, the cam (29) with the greatest height being located in the center, and the cams (30, 31) with lower heights being arranged laterally symmetrically with respect to the central cam (29) with the greatest height.

6. The seat belt retractor according to claim 4, characterized in that the surface of the second spring (17) has a structure consisting of a plurality of grooves (32) that extend perpendicularly to the pivot axis of the stopping lever.

7. - The seat belt retractor according to any one of claims 1 to 6, characterized in that the second spring (17) is formed by a coil spring.

8. - The seat belt retractor according to claim 6, characterized in that the second spring (17) is positioned at an angle of 5 to 15 degrees with respect to the pivot axis of the blocking lever (2).

9. A seat belt retractor according to any one of claims 1 to 8, characterized in that an impact absorber (33) that limits the pivoting motion of the stopping lever (2) is provided on a fixed opposing surface of the stopping lever (2) and / or the stopping device (100).

10. - The electromagnet (3) comprises a coil (10) having a through-opening (14), - A seat belt retractor according to any one of claims 1 to 9, characterized in that an iron core (12) is placed in the through opening (14), and the iron core exerts a magnetic force on the stop lever (2) via the steel plate (5) when a voltage is applied to the coil (10), thereby acting on the stop lever (2) against the force of the first spring (4) to cause a stop movement or a release movement.

11. - The seat belt retractor according to claim 10, characterized in that the movement of the stop lever (2) is forced by at least the iron core (12), the upright first rim (16), and the portion of the base plate (15) and the stop lever (2) between the iron core (12) and the upright first rim (16).

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