Belt retractor

Abstract

The present invention relates to a belt retractor (1), comprising a belt shaft (4) rotatably mounted in a housing that can be fixed to a vehicle and around which a safety belt can be wound, an electric motor (5) for driving the belt shaft (4) into a rotational movement, and a gear mechanism (6) for transmitting the rotational movement from the electric motor (5) to the belt shaft (4), wherein the gear mechanism (6) is drivable to drive the belt shaft (4) with a first torque as an assembly in a first force transmission path, and the gear mechanism (6) is drivable to drive the belt shaft (4) with a second torque by shifting gears of a speed-controlled and / or torque-controlled coupling (8), thereby opening a second force transmission path, and the coupling (8) is engaged with a first portion (13) of the gear mechanism (6). and a gear mechanism (6) having at least one coupling element (15) spring-biased by a spring (12) to engage with the first part (13) of the gear mechanism (6), wherein a drive wheel (17) rotatably mounted and connected to an electric motor (5) is provided with a polygonal force transmission profile (19), the coupling element (15) having at least one force transmission portion (20, 21) abutting the polygonal force transmission profile (19), whereby, 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) is movable against the force of the spring (12) to disengage from the first part (13) of the gear mechanism (6) by relative movement of the drive wheel (17) with respect to the coupling element (15).

Description

[Technical Field]

[0001] The invention relates to a belt retractor having the features of the preamble of claim 1 .

[0002] The belt retractor has as its basic components a load-bearing frame and a belt reel, which is rotatably mounted in the frame and onto which the safety belt can be wound. The frame serves not only for the mounting of the belt reel but also for fastening to the seat structure or vehicle structure, and for this purpose the frame is made of steel plate of corresponding thickness bent into a U-shaped frame.

[0003] Furthermore, in modern safety belt systems, the belt retractor is provided with an electric motor, which drives the belt shaft when actuated, for example, to reversibly tighten the belt in the retracting direction. The electric motor is also fastened to a frame and arranged transversely to the belt shaft, with the drive shaft oriented parallel to the belt shaft's rotation axis. It is also known to provide a gear mechanism between the belt shaft and the electric motor, which is used to convert the rotational speed of the electric motor into a predetermined rotational speed of the belt shaft. The use of a gear mechanism also makes it possible to use an electric motor that is as compact as possible and has a high rotational speed. Therefore, despite the use of a compact electric motor made possible by the gear mechanism, belt retractors are generally manufactured with increased installation space requirements. Such belt retractors are known, for example, from WO 03 / 0 99 619 A2.

[0004] If the belt shaft is driven at different rotational speeds and torques, further gear stages must be provided, which further increases the installation space requirements. Such a belt retractor is known, for example, from DE 199 27 731 (C2).

[0005] The placement of such belt retractors on vehicle seats or even in small vehicles is fundamentally problematic, as the seating structure of a vehicle seat, or generally on a very small vehicle, is very limited in size and cannot be expanded as desired for design reasons.

[0006] German Patent No. 10 2018 219 040 (A1) discloses a belt retractor in which the installation space requirements are further reduced by providing a gear mechanism driven as a group within a first force transmission path and a shaft coupling that operates the gear mechanism by shifting and opens a second force transmission path. As a result, two different transmission ratios can be implemented using a gear mechanism with a single force transmission path. In this case, the gear mechanism itself is driven as a group, i.e., as a block, within the first force transmission path, without the gear mechanism components themselves moving relative to each other. Here, the shaft coupling has a drive wheel driven by an electric motor and has three triangular openings that narrow radially outward, with a shaft coupling pawl in each opening engaging a respective control pin. The shaft coupling pawls are guided radially in a longitudinally displaceable manner and are each spring-biased radially outward via a spring. To shift the coupling, the coupling pawls are pulled radially inwards against the spring force until a certain rotational acceleration of the drive wheel is exceeded, which releases the rotational connection between the coupling pawls and the first part assigned to the gear mechanism.

[0007] SUMMARY OF THE INVENTION In this context, it is an object of the present invention to provide an improved belt retractor having an electric motor and a gear mechanism including a shaft coupling of simplified structure.

[0008] To achieve the object, a belt retractor is proposed having the features of claim 1. Further advantageous developments of the invention can be taken from the dependent claims, the figures and the associated description.

[0009] According to the basic concept of the invention, it is proposed in accordance with claim 1 that a drive wheel rotatably mounted and connected to an electric motor is provided with a polygonal force transmission profile, and that the coupling element has at least one force transmission part abutting the polygonal force transmission profile, whereby when a predetermined rotational speed and / or a predetermined torque transmitted by the drive wheel is exceeded, the coupling element is movable out of engagement with the first part of the gear mechanism against the force of a spring by a relative movement of the drive wheel.

[0010] The advantage of this solution is that the drive wheel directly triggers the coupling movement of the coupling element by providing a corresponding force transmission surface against which the coupling element abuts via the polygonal profile. The coupling element itself is spring-loaded in the direction of engagement in the first section, and the spring force is designed so that the drive wheel moves the coupling element out of the engaged position and thereby releases the rotational connection created via the coupling element only after a predetermined rotational speed and / or torque and / or rotational acceleration is exceeded. By releasing the rotational connection, for example, the first force transmission path formed by the rotational connection can be interrupted and a second force transmission path can be opened. This second force transmission path can, for example, be equipped with a gear mechanism that, as a result of its operation, converts the rotational speed of the electric motor into a lower rotational speed transmitted to the belt shaft, for example, with a gear ratio of 1:80.

[0011] It is further proposed that the coupling element transmits the rotational movement of the drive wheels below a predetermined rotational speed and / or below a predetermined torque to the first part of the gear mechanism, so that the rotational movement of the electric motor in the case of low torque, low rotational speed and / or low rotational acceleration can be transmitted in a first force transmission path via the coupling element to the first part of the gear mechanism, for example with a gear ratio of 1:1, directly to the belt shaft, so that, for example, a safety belt retraction assistance into a parking position, a comfort function for adjusting the retraction force acting on the belt shaft, etc., can be implemented.

[0012] In this case, the coupling element preferably has an engagement portion that engages with the first portion of the gear mechanism and at least two force transmission portions that are symmetrical about an axis of symmetry extending through the engagement portion, and whereby the coupling element abuts the polygonal force transmission profile of the drive wheel. The coupling element transmits rotational motion to the first portion via the engagement portion. The transmission of force from the drive wheel to the coupling element is carried out by symmetric force transmission portions in both directions of rotation with as identical a force ratio as possible, and the coupling element can be mounted in two different orientations.

[0013] It is further proposed that the cross section of the polygonal force transmission profile has a triangular profile and that the coupling element surrounds the triangular profile at two corners. The coupling element engages and overlaps with the two corners of the force transmission profile, thereby transmitting the rotary drive motion in both directions of rotation. Furthermore, as a result, when one of the predetermined conditions is exceeded, the coupling element is pulled out of the engagement position in an engaged manner.

[0014] In this case, a triangular profile, preferably having an equilateral triangular geometry, allows for symmetrical force transmission in both rotation directions with as many identical force ratios as possible. Furthermore, as a result, the belt retractor can be assembled in three different positions on the drive wheel, which simplifies assembly. Since the ends of the triangular profile have the same geometry, it is irrelevant which end abuts the force-transmitting part of the coupling element.

[0015] It is further proposed that the coupling element is mounted on a second part of the gear mechanism, the second part having a rotatably mounted and connected gear by means of which the coupling element is in gear engagement with one or more gears of the transmission gear mechanism, so that the second part of the gear mechanism to which the coupling element is mounted simultaneously forms a drive part, by means of which a rotary motion is imparted to the transmission gear mechanism via the connected gears rotatably mounted thereon.

[0016] Furthermore, it is proposed that the second part has a stop surface against which the drive wheel having a force transmission profile abuts in a force-transmitting manner when a relative movement is performed. The relative movement is triggered when a predetermined rotational speed, a predetermined torque, and / or a predetermined rotational acceleration is exceeded. As a result, the coupling element is moved from the engaged position and the drive wheel abuts in a force-transmitting manner against the second part. As a result, the drive wheel drives the second part and, if the rotational connection between the drive wheel and the first part is simultaneously released, also drives the transmission gear mechanism via a gear connected to the drive wheel so as to be rotatably mounted.

[0017] It is further proposed that the spring is formed by a bow spring, which is connected at a first end to the coupling element and at a second end to the second part. The advantages of using a bow spring are that it is cost-effective, that it is easy to assemble, and that it can be very simply connected in a force-transmitting manner to the coupling element and the second part, for example by means of openings or stop surfaces.

[0018] In this case, the second part can preferably have a guide along which the coupling element is guided by means of the engagement part. The movement of the coupling element is triggered by the spring force and the movement of the drive wheel, while the direction of the movement is determined by the guidance of the coupling element on the second part. In this case, guiding the coupling element in the region of the engagement part is particularly advantageous, since it allows the coupling element to be guided and supported as close as possible to the connection to be implemented with the first part. [Brief explanation of the drawings]

[0019] The present invention will be described below using preferred embodiments with reference to the accompanying drawings, in which: [Figure 1] 1 shows an assembled and disassembled belt retractor having two housing shells according to the present invention. [Figure 2] FIG. 2 is an exploded view of the belt retractor gear mechanism, electric motor, and shaft coupling disposed therebetween. [Figure 3] FIG. 2 is a cross-sectional view of the shaft coupling in a first position. [Figure 4] FIG. 4 is a cross-sectional view of the shaft coupling in a second position.

[0020] 1 shows a belt retractor 1 according to the invention, which is explained in more detail below, and which is made up of two housing shells 2 and 3, and which serves both to secure the belt retractor 1 to the vehicle, preferably in the narrow and elongated installation space of a vehicle seat, and to mount and secure the individual parts of the belt retractor 1. The housing may be part of a higher level structure of the vehicle seat or vehicle, such as a strut or bar.

[0021] The inside of the housing is provided with a plurality of webs 24 for mounting the belt retractor 1, which are oriented perpendicular to the belt retractor's rotation axis and are connected to the housing in a mating manner and rotatable about the rotation axis. The belt retractor 1 includes, as a basic component, a belt shaft 4 on which a safety belt for restraining a vehicle occupant can be wound. A non-reversible belt tensioner 7 is provided to drive the belt shaft 4 in the retracting direction and thus remove any belt slack present in the initial stage of an accident. An electric motor 5 and a gear mechanism 6 are also provided. The belt shaft 4, the non-reversible belt tensioner 7, the electric motor 5, and the gear mechanism 6 are arranged coaxially with one another. The electric motor 5, the gear mechanism 6, and the non-reversible belt tensioner 7 are each sized to have an outer dimension perpendicular to the belt shaft's rotation axis that is smaller than the maximum diameter of the belt fully wound on the belt shaft 4. Due to the angular cross-section of the housing, additional free space remains at the corners, which can be used for arranging other attachment parts, such as the tension drive tube of the non-reversible belt tensioner 7, or a control unit or electrical cables. The maximum outer dimension is therefore predetermined by the maximum diameter of the wound belt. Since the maximum diameter is in turn predetermined by the thickness of the belt strap and the maximum length of the wound belt strap and cannot be reduced without modifying the belt strap, the belt retractor 1 has a minimum dimension perpendicular to the rotation axis of the belt shaft 4 and can therefore also be arranged and fixed in very narrow and elongated free spaces of the vehicle seat and vehicle structure.

[0022] FIG. 2 shows an electric motor 5 with a gear mechanism 6, a shaft coupling 8 arranged therebetween, and an optional force limiting unit 11 which is additionally provided.

[0023] The gear mechanism 6 comprises as its basic components a shaft coupling 8, a transmission gear mechanism 9, here designed as a planetary gear, and a gear mechanism housing 10. The gear mechanism 6 is surrounded on the outside by the gear mechanism housing 10 and has a cylindrical basic shape. The gear mechanism housing 10 itself is tubular or annular and has on its inside an internal toothing within which the planet gears of the planetary gear rotate.

[0024] The electric motor 5 has a drive shaft 18 which is guided outwards and on which a drive wheel 17 is rotatably mounted via a gear engagement, so that the electric motor 8 directly drives the drive wheel 17 when activated.

[0025] In its basic structure, the shaft coupling 8 comprises a first part 13, a second part 14, a coupling element 15, and a spring 12. The first part 13 is ring-shaped and has a regular tooth profile 30 arranged radially inward. Furthermore, the first part 13 has a number of recesses radially outward, which are aligned with recesses in the gear mechanism housing 10. The end face of the first part 13 is covered by a cover disk 16. The cover disk 16 additionally has axially protruding fingers that engage with the radially outer recesses of the first part 13 and the gear mechanism housing 10, thereby fixing the first part 13 to the gear mechanism housing 10 so that it can be rotatably mounted in the circumferential direction. If the connection is made via a press fit, the axial fixing of the first part 13 to the gear mechanism housing 10 can additionally be performed. Radially inside, the first part 13 has a circular free space in which the second part 14 of the coupling 8 is rotatably arranged, as can be seen in Figures 3 and 4. The second part 14 is therefore also axially fixed after the cover disk 16 is attached. The cover disk 16 also 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, which engages in the free space provided radially inside the second part 14. Furthermore, the coupling element 15 is arranged in the free space of the second part 14, surrounding the force transmission profile 19 radially outward.

[0026] The polygonal force transmission profile 19 of the drive wheel 17 has the geometry of an equilateral triangle with three corners 27, 28, and 29 having identical angles and, consequently, lateral force transmission surfaces that are oriented in the same direction. The coupling element 15 has a radially protruding engagement portion 22, by means of which the coupling element 15 is radially displaceably guided in a guide 32 of the second part 14. Furthermore, the coupling element 15 has two arcuate arms that are symmetrical with respect to an axis of symmetry S that runs through the center of the engagement portion 22 and are substantially complementary to each other, thereby forming a semicircle. As can be seen in FIG. 3 , the coupling element 15 is formed with force transmission portions 20, 21 at the ends of the arms in each case, which are directed radially inward and surround the corners 28, 29 of the force transmission profile 19 of the drive shaft 17. The spring 12 is designed in the form of a bow spring and is attached to the coupling element 15 with its first end 25 in an opening arranged radially inward from the engagement portion 22 on the axis of symmetry S. Furthermore, the spring 12 is attached with its second end 23 in an opening in the second portion 14, which opening is also arranged on the axis of symmetry S in the unloaded position of the coupling element 15, i.e. when the electric motor 5 is stationary. Due to its spring properties and the arrangement of its two fixed ends 25 and 23, the spring 12 is designed to press the coupling element 15 with the engagement portion 22 radially outward and into engagement with the tooth profile 30 of the first portion 13. As a result, a rotational connection between the first portion 13 and the second portion 14 is created by the coupling element 15 in the unloaded state.

[0027] When the electric motor 5 in the initial position of the coupling element 15 shown in FIG. 3 is operated with low torque, low rotational speed, and / or low rotational acceleration, for example, when retracting the safety belt into the parking position or adjusting 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. The first part 13 is rotatably connected to the gear mechanism housing 10 via the cover disk 16, so that the entire gear mechanism 6 is driven as an assembly, which in turn drives the belt shaft 4 with a 1:1 transmission ratio. In this case, the belt shaft 4 can be driven in both directions of rotation via the two force transmission parts 20, 21, with force transmission via only one of the force transmission parts 20 or 21 depending on the direction of rotation. Since both the coupling element 15 and the force transmission profile 19 are oriented symmetrically with respect to the axis of symmetry S in the position shown in FIG. 3, identical force conditions occur in both directions of rotation. The second part 14 has, on its axial end face facing the planet gears, a centrally arranged gear 31 which engages with the planet gear teeth of the planet gears. Since the second part 14 rotates at the same rotational speed as the first part 13, the entire gear mechanism 6 is also pulled via the central gear 31. The entire gear mechanism 6 rotates as an assembly together with the first part 13 and the second part 14 at the rotational speed driven by the drive shaft 17, without the gears of the gear mechanism 6 additionally undergoing any relative rotational movement with respect to one another.

[0028] The opening of the coupling 8, for example for reversible belt tensioning, is achieved by increasing the power output of the electric motor 5 to a level exceeding a predetermined rotational speed, a predetermined torque, and / or a predetermined rotational acceleration. In this case, the drive wheel 17 rotates so quickly that the coupling element 15 lags behind and is pulled against the spring force of the spring 12 to the position shown in FIG. 4 . The coupling element 15 with the engagement portion 22 is now disengaged from the tooth profile 30, releasing the rotational connection between the first part 13 and the second part 14. This opens the coupling 8. At the same time, the drive shaft 17 brings the flank of the force-transmitting profile 19 into contact with the stop face 26 of the second part 14, thereby directly driving the second part 14 into a rotational movement. Meanwhile, the first part 13 is no longer driven because the coupling 8 is now open.

[0029] In this case, the rotational movement of the second part 14 is transmitted to the planetary gears via the central gear 31. The gear mechanism housing 10 is no longer driven and can additionally be locked to the vehicle via a locking device 33. In any case, the planetary gears rotate relative to the gear mechanism housing 10 and the rotational movement of the drive shaft 17 is converted into a slower rotational speed of the belt shaft 4, now with a gear ratio of 1:80. By converting a higher rotational speed into a lower rotational speed, the torque applied to the belt shaft 4 and thereby the retracting force applied to the safety belt are simultaneously increased.

[0030] As a result, the electric motor 5 can operate in a first power transmission path with a closed shaft coupling 8 and a deactivated gear mechanism 6 at a rotational speed of 60-180 rpm by rotating the gear mechanism 6 as a block, in order to retract the belt strap into the parking position after buckle release. If the proposed rotational speed is also the rotational speed of the belt shaft 4, the rotational drive motion can be further transmitted to the belt shaft 4 with a 1:1 transmission ratio. For reversible belt tensioning, the rotational speed of the electric motor 5 can be suddenly increased to 5,000-15,000 rpm, which is converted by the gear mechanism 6 in the second power transmission path, opened by the opening of the shaft coupling 8, to a lower rotational speed of approximately 140-420 rpm of the output gear 23 with a 1:80 transmission ratio. To shift the coupling 8, a significantly higher rotational drive speed of 5,000 to 15,000 rpm is used compared to the rotational drive speed of 60 to 180 rpm used to drive the belt shaft 4 in the first force transmission path. Therefore, the coupling 8, or the gear mechanism 6 in which the coupling 8 is integrated, can be designed to open only when a rotational drive speed of, for example, 1,000 rpm is exceeded. This ensures reliable transmission of the rotational drive motion of 60 to 180 rpm in the first force transmission path, preventing unintentional opening of the coupling 8 during the retraction of the safety belt into the parking position. Furthermore, as an alternative to speed-controlled opening, the coupling 8 can also be released if the torque to be overcome suddenly increases at the same or a decreasing rotational speed. This situation can occur, for example, when the safety belt is retracted into the parking position at high speed. When the safety belt is almost fully retracted, the torque to be overcome increases, and the coupling 8 is automatically shifted. By shifting the coupling 8, the rotational speed of the output gear 23 is reduced and the torque exerted by the output gear 23 is increased, so that the safety belt is subsequently retracted with a lower retraction speed and increased retraction force.

[0031] As a result of the planetary gears, the gear mechanism 6 has a single force transmission path, here a two-stage planetary gear. The proposed solution for transmitting the rotary drive motion via the gear mechanism 6, which rotates as a whole, creates a first force transmission path for performing the first function, here retracting the safety belt into the parking position, without requiring additional installation space. Furthermore, since the shifting of the coupling 8 is performed in a very simple manner by increasing the rotational speed, the second force transmission path is automatically opened when the rotational speed of the electric motor 5 is increased to tension the safety belt, i.e., for its second function. Therefore, the shifting of the coupling 8 is directly controlled by the change in function of the electric motor 5 itself.

[0032] Furthermore, the electric motor 5 and the gear mechanism 6 are cylindrical and oriented coaxially with each other and with the axis of rotation of the belt shaft 4. In addition, both the electric motor 5 and the gear mechanism 6 have a diameter, in cross section relative to their axes of rotation, that is smaller than the outer diameter of the wound belt when the belt strap is maximally retracted. This results in a very slim and elongated structure of the belt retractor, whose maximum outer dimension is predetermined by the maximum outer diameter of the wound belt. Since the maximum outer diameter of the wound belt is absolutely predetermined by the thickness and length of the retracted belt strap and cannot be reduced, the belt retractor can be made as small as possible in its dimension perpendicular to the axis of rotation of the belt shaft 4.

[0033] The coupling 8 is here understood to be an assembly of the gear mechanism 6, and the first part 13 and the second part 14 are therefore naturally part of the coupling 8, but are therefore also part of a higher-level assembly of the gear mechanism 6. To this end, the coupling 8 is preferably arranged on the input side of the gear mechanism 6 facing the electric motor 5.

[0034] The electric motor 5 is preferably voltage-controlled, with different voltages resulting in different torques acting on the belt shaft 4 or different retraction forces being exerted on the safety belt. During normal wear of the safety belt, a voltage of 2-3 V is applied, thereby reducing the retraction force to the lowest possible level, yet still sufficient to reliably retract the safety belt toward the occupant after the occupant moves. To retract the safety belt into the parking position after unbuckling, the voltage is increased to 9 V so that the safety belt is retracted into the parking position with increased retraction force. Furthermore, during the reversible tensioning operation, the voltage is also increased to 12 V. This can be increased to approximately 36 V for the optional additional application of reversible belt tension with increased retraction force.

Claims

1. A belt retractor (1), a belt shaft (4) rotatably mounted in a housing that can be fixed to the vehicle and on which a safety belt can be wound; an electric motor (5) for driving the belt shaft (4) into rotational movement; a gear mechanism (6) for transmitting the rotational motion from the electric motor (5) to the belt shaft (4), The gear mechanism (6) is drivable as an assembly in a first force transmission path to drive the belt shaft (4) with a first torque. the gear mechanism (6) is operable to drive the belt shaft (4) with a second torque by shifting gears of a speed-controlled and / or torque-controlled coupling (8), thereby opening a second force transmission path; The shaft coupling (8) has at least one coupling element (15) that is spring-loaded by a spring (12) to engage with a first part (13) of the gear mechanism (6). a gear mechanism (6), a drive wheel (17) connected to said electric motor (5) in a rotatable manner, said drive wheel (17) being provided with a polygonal force transmission profile (19); The coupling element (15) has at least one force transmission portion (20, 21) abutting the polygonal force transmission profile (19), whereby When a predetermined rotational speed and / or a predetermined torque and / or a predetermined rotational acceleration transmitted by said drive wheel (17) is exceeded, The coupling element (15) is movable against the force of the spring (12) so as to disengage from the first part (13) of the gear mechanism (6) by relative movement of the drive wheel (17) with respect to the coupling element (15).

2. 2. The belt retractor (1) according to claim 1, wherein the coupling element (15) transmits rotational movement of the drive wheel (17) below the predetermined rotational speed and / or below the predetermined torque to the first part (13) of the gear mechanism (6).

3. The coupling element (15) has an engagement portion (22) that engages with the first portion (13) of the gear mechanism (6); the coupling element (15) has at least two force transmission portions (20, 21) symmetrical with respect to 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); A belt retractor (1) according to claim 1 or 2.

4. the cross section of said polygonal force transmission profile (19) has a triangular profile; said coupling element (15) surrounds a triangular force transmission profile (19) at two corners (27, 28, 29); A belt retractor (1) according to any one of claims 1 to 3.

5. 5. The belt retractor (1) according to claim 4, wherein said triangular force transmission profile (19) has the geometry of an equilateral triangle.

6. The coupling element (15) is attached to the second part (14) of the gear mechanism (6), The second part (14) has a gear (31) rotatably connected thereto, by means of which the second part (14) is in gear engagement with one or more gears of a transmission gear mechanism (9). A belt retractor (1) according to any one of claims 1 to 5.

7. 7. The belt retractor (1) according to claim 6, wherein the second part (14) has a stop surface (26) against which the drive wheel (17) having the force transmission profile (19) comes into force-transmitting contact as the relative movement is carried out.

8. The spring (12) is formed by a bow spring, the bow spring being connected at a first end (25) to the coupling element (15); 8. A belt retractor (1) according to claim 6 or 7, connected at a second end (23) to said second part (14).

9. A belt retractor (1) according to any one of claims 6 to 8, which is dependent on claim 3, wherein the second part (14) has a guide (32) along which the coupling element (15) is guided with respect to the engagement part (22).

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