US20060214494A1 - Seat belt retractor - Google Patents

Seat belt retractor Download PDF

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Publication number
US20060214494A1
US20060214494A1 US10/543,893 US54389304A US2006214494A1 US 20060214494 A1 US20060214494 A1 US 20060214494A1 US 54389304 A US54389304 A US 54389304A US 2006214494 A1 US2006214494 A1 US 2006214494A1
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United States
Prior art keywords
take
drum
torsion bar
plate body
energy
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US10/543,893
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English (en)
Inventor
Takao Katayama
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Ashimori Industry Co Ltd
Original Assignee
Ashimori Industry Co Ltd
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Filing date
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Assigned to ASHIMORI INDUSTRY CO., LTD. reassignment ASHIMORI INDUSTRY CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KATAYAMA, TAKAO
Publication of US20060214494A1 publication Critical patent/US20060214494A1/en
Abandoned legal-status Critical Current

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60R—VEHICLES, VEHICLE FITTINGS, OR VEHICLE PARTS, NOT OTHERWISE PROVIDED FOR
    • B60R22/00—Safety belts or body harnesses in vehicles
    • B60R22/28—Safety belts or body harnesses in vehicles incorporating energy-absorbing devices
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60R—VEHICLES, VEHICLE FITTINGS, OR VEHICLE PARTS, NOT OTHERWISE PROVIDED FOR
    • B60R22/00—Safety belts or body harnesses in vehicles
    • B60R22/34—Belt retractors, e.g. reels
    • B60R22/46—Reels with means to tension the belt in an emergency by forced winding up
    • B60R22/4676—Reels with means to tension the belt in an emergency by forced winding up comprising energy-absorbing means operating between belt reel and retractor frame
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60R—VEHICLES, VEHICLE FITTINGS, OR VEHICLE PARTS, NOT OTHERWISE PROVIDED FOR
    • B60R22/00—Safety belts or body harnesses in vehicles
    • B60R22/28—Safety belts or body harnesses in vehicles incorporating energy-absorbing devices
    • B60R2022/286—Safety belts or body harnesses in vehicles incorporating energy-absorbing devices using deformation of material
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60R—VEHICLES, VEHICLE FITTINGS, OR VEHICLE PARTS, NOT OTHERWISE PROVIDED FOR
    • B60R22/00—Safety belts or body harnesses in vehicles
    • B60R22/28—Safety belts or body harnesses in vehicles incorporating energy-absorbing devices
    • B60R2022/286—Safety belts or body harnesses in vehicles incorporating energy-absorbing devices using deformation of material
    • B60R2022/287—Safety belts or body harnesses in vehicles incorporating energy-absorbing devices using deformation of material of torsion rods or tubes
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60R—VEHICLES, VEHICLE FITTINGS, OR VEHICLE PARTS, NOT OTHERWISE PROVIDED FOR
    • B60R22/00—Safety belts or body harnesses in vehicles
    • B60R22/28—Safety belts or body harnesses in vehicles incorporating energy-absorbing devices
    • B60R2022/288—Safety belts or body harnesses in vehicles incorporating energy-absorbing devices with means to adjust or regulate the amount of energy to be absorbed

Definitions

  • the present invention relates to a seatbelt retractor provided with an energy-absorbing means, which, in case of a vehicle emergency, restrains a webbing from being pulled out to restrain movements of vehicle occupant and absorbs an impact load acting on the vehicle occupant.
  • JP 2001-301569A discloses a webbing take-up apparatus (seatbelt retractor) including a lock base (locking base) provided on one end of a cylindrical spool (take-up drum) which winds up webbing in a manner that a relative rotation with the spool is possible, a lock means which prevents a rotation of the lockbase in the direction of the webbing pulled out in case of a vehicle emergency, a torsion bar inserted into the spool, one end of which is coupled with the spool, the other end of which is coupled with the lock base, which generates a torsional deformation in a state where the lock means prevents a rotation of the lock base in the direction of the webbing pulled out, a wire, one end of which is fixed to the lock base
  • the cutting position drifts depending on the tensile force of the webbing, namely, the pull-out speed of the wire being pulled out from the spool. Accordingly, the cutting is not performed at a constant position, and the resistance in the webbing pulled out is not stabilized, which is disadvantageous.
  • an object of the present invention is to solve the above conventional problems.
  • the first object of the invention is to make an energy-absorbing means which provides a resistive load capable of appropriately selecting the amount of the energy absorption, and to thereby halt the wire at a constant position and stabilize the resistance in the webbing pulled out.
  • the second object is to make an energy-absorbing means which halts to provide the load, and to make it capable of freely adjusting the timing of halting, in a manner that it is able to perform an optimum energy absorption in correspondence with the physical make-up of vehicle occupant, scale of a vehicle collision, and time and so forth.
  • the third object is to make an energy-absorbing members not generate excessive energy absorptions in switching the resistive loads, and to stabilize the provision of load by the energy-absorbing members, so that the vehicle occupant can easily be halted at specified positions.
  • a seatbelt retractor comprises a take-up drum on which webbing is wound, a take-up shaft, one end of which is coupled with one end of the take-up drum in a manner that a relative rotation with the take-up drum is impossible, which is biased in the direction of the webbing taken up, an emergency lock mechanism which restrains a rotation in the direction of the webbing pulled out, a clutch mechanism located near the other end of the take-up shaft, a plate body provided close to a side on the other end of the take-up drum, which is provided on the other end of the take-up shaft through the clutch mechanism, and an energy-absorbing means located between the side of the take-up drum and the plate body, which provides a resistive load by mutually performing a relative rotation, wherein the clutch mechanism switches a first state where the plate body is provided on the other end of the take-up shaft in a manner that a relative rotation with the take-up shaft is impossible into a second state where the plate body is provided on the other end of
  • a seatbelt retractor comprises a take-up drum on which webbing is wound, a torsion bar inserted through the take-up drum, one end of which is coupled with one end of the take-up drum in a manner that a relative rotation with the take-up drum is impossible, which is biased in the direction of the webbing taken up, an emergency lock mechanism located on the other end of the torsion bar, which restrains a rotation in the direction of the webbing pulled out, a lock actuating device which actuates the emergency lock mechanism in case of a vehicle emergency, a clutch mechanism located near the other end of the torsion bar, a plate body provided close to a side on the other end of the take-up drum, which is provided on the other end of the torsion bar through the clutch mechanism, and a second energy-absorbing means located between the side of the take-up drum and the plate body, which provides a resistive load by mutually performing a relative rotation, wherein the clutch mechanism switches a first state where the plate body
  • the lock actuating device actuates the emergency lock mechanism in case of a vehicle emergency
  • the other end of the take-up shaft or the torsion bar is restrained from rotating in the direction of the webbing pulled out, and the take-up drum is also restrained from rotating.
  • the one end of the take-up shaft or the torsion bar 4 is coupled with the take-up drum being driven to rotate in a manner that a relative rotation is impossible, and the other end thereof is coupled with the emergency lock mechanism which has restrained the rotation in a manner that a relative rotation is impossible, therefore, the take-up shaft or the torsion bar, while generating a torsional deformation, rotates the take-up drum.
  • the take-up shaft or the torsion bar (first energy-absorbing means) and the second energy-absorbing (EA) means are in operation.
  • the clutch mechanism being put in operation through a clutch actuating mechanism at an arbitrary timing switches the plate body into the second state where the plate body is able to rotate relatively with the other end of the take-up drum or the torsion bar, and the clutch mechanism makes the take-up shaft or the torsion bar alone perform the energy absorption (EA).
  • the provision of the resistive load is stopped without any contact with the energy-absorbing means (wire) being the second energy-absorbing means, excessive energy absorption is not generated in the switching, the provision of load becomes stabilized, and the vehicle occupant can easily be halted at specified positions.
  • a seatbelt retractor is that, in the seatbelt retractor according to the second aspect of the invention, the clutch mechanism includes in a manner that a relative rotation with the emergency lock mechanism is impossible, at least one joint pawl pivoted to be turnable to a side of the plate body on the opposite side to the take-up drum, which comes in contact with the joint plate to turn outwardly, a release ring retained by a casing fixed on a side plate of a housing on the other end of the torsion bar to be movable in the axial direction while rotating, which is located on a periphery of the joint pawl; and a clutch release mechanism which actuates the release ring attached to the casing.
  • the lock actuating device actuates the emergency lock mechanism
  • the torsion bar and the second energy-absorbing (EA) means provide loads in practice
  • the webbing is pulled and the take-up drum is rotated in the direction of the webbing pulled out.
  • the plate body slightly rotates integrally with the take-up drum, so that a relative rotation is generated between the plate body and the joint plate coupled with the emergency lock mechanism to be impossible of a relative rotation, and the inner circumference of the joint pawl comes in contact with the joint plate, which presses the joint pawl outwardly.
  • the joint pawl Since-the release ring is located on a periphery of the joint pawl, the joint pawl is restrained from expanding outwardly. As the clutch release mechanism actuates the operation, the release ring is made to move in the axial direction of the torsion bar while rotating, and is detached from the circumference of the joint pawl, and hence the joint pawl expands outwardly. Since the plate body is accordingly detached from the joint plate which has restrained the rotation of the plate body, the plate body rotates integrally with the take-up drum, the provision of the resistive load by the wire (energy-absorbing member) is halted, and only the energy absorption (EA) by the torsion bar is performed.
  • EA energy absorption
  • the plate body rotates integrally with the take-up drum in the normal use of the seatbelt retractor
  • the emergency lock mechanism actuates the operation
  • the plate body is put into the state where it cannot rotate integrally with the take-up drum
  • the clutch release mechanism of the clutch mechanism actuates the operation
  • the clutch mechanism can be easily installed.
  • the load of the energy-absorbing means becomes zero without increasing, and the switching of the load can smoothly be performed.
  • a seatbelt retractor is that, in the seatbelt retractor according to the third aspect of the invention, the clutch release mechanism includes a gas generator which generates gas in a cylinder attached to the casing at an arbitrary timing, and a piston pressed and driven by a gas pressure in the cylinder, which presses the circumference of the release ring to rotate the release ring.
  • a seatbelt retractor is that, in the seatbelt retractor according to the fourth aspect of the invention, the release ring is provided with a contact on the circumference thereof, which comes in contact with the piston, and plural tapered parts located with a uniform spacing on the circumference thereof, and the casing which holds the release ring is provided with projections corresponding to the tapered parts of the release ring.
  • the tapered parts provided on the circumference of the release ring are guided to the projections of the casing, and the release ring being rotated is made to move in the axial direction of the torsion bar.
  • the tapered parts are located on the circumference of the release ring with a uniform spacing, it is possible to move the release ring in a state where the plane of the release ring is vertical to the axis.
  • the piston driven by the gas pressure rotates the release ring in one breath, and it can release the joint pawl toward the circumference at once in defiance of the frictional resistance by contacts.
  • the release ring Since the release ring is made to move in the state where the plane of the release ring is vertical to the longitudinal direction of the torsion bar, the contact of the joint pawl with the release ring is released at once, in the switching of the clutch, there is not any excessive load generated, except the load supplied by the second energy-absorbing means.
  • a seatbelt retractor is that, in the seatbelt retractor according to any one of the first through the fifth aspects of the invention, the clutch mechanism is provided with a pawl holder which positions and supports the joint pawls, and the pawl holder is provided with ribs integrally formed thereon, which biases the joint pawls in the axial direction and will not return the joint pawls to the initial positions after operating the joint pawls.
  • the positions of the joint pawls in the first state are maintained by biasing the springs.
  • the outwardly expanded joint pawls are restrained from returning to the initial positions by the ribs of the pawl holder, and are retained at the positions where they are expanded. Further, the joint pawls retained there restrain the release ring from returning to the circumference of the joint pawls.
  • a seatbelt retractor is that, in the seatbelt retractor according to any one of the second through the sixth aspects of the invention, the second energy-absorbing means includes a curved path provided on a side of the take-up drum on the other end of the torsion bar, and a wire, one end of which is fixed to a take-up part of the plate body, a substantially medium part of which is located in the curved groove.
  • the joint pawls are biased by a spring force, if, in the normal use of the seatbelt retractor, the joint pawls are made to rotate together with the take-up drum and so forth, the joint pawls will be positioned at the specified positions, which stabilizes the operation of the joint pawls.
  • the plate body prevents the joint pawls and the release ring from returning to specified positions in the first state where the plate body is provided on the other end of the take-up drum in a manner that a relative rotation is impossible from the second state where the plate body is provided on the other end of the take-up drum in a manner that a relative rotation is possible. Therefore, it is possible to stabilize a resistive load by the torsion bar without adding a load by the second energy-absorbing means.
  • FIG. 1 is a front view of the whole seatbelt retractor according to the present invention.
  • FIG. 2 is an exploded perspective view explaining the assembling of a housing, a take-up drum, a torsion bar, a locking base, a base stopper, and so forth of the seatbelt retractor illustrated in FIG. 1 ;
  • FIG. 3 is an exploded perspective view explaining the assembling of the take-up drum, the plate assembly, a retainer, and a pawl holder;
  • FIG. 4 is an exploded perspective view explaining the assembling of a plate assembly which is illustrated in FIG. 3 ;
  • FIG. 5 is a side view of the plate assembly
  • FIG. 6 is a front view partly in section of the plate assembly
  • FIG. 7 is a partly enlarged front view in section illustrating another embodiment of the plate assembly
  • FIG. 8 is a front view in section of an assembly in which the plate assembly and the take-up drum illustrated in FIG. 3 are assembled;
  • FIG. 9 is a partly cutaway side view of the assembly illustrated in FIG. 8 ;
  • FIG. 10 is a front view in section, in which the assembly illustrated in FIG. 8 is turned;
  • FIG. 11 is a partly cutaway side view of the assembly illustrated in FIG. 10 ;
  • FIG. 12 is an exploded perspective view explaining the assembling of a housing, a casing, and so forth, which are illustrated in FIG. 2 ;
  • FIG. 13 is an exploded perspective view of a release ring, the casing, a piston, a gas generator, a gas generator holder, and so forth;
  • FIG. 14 is an enlarged perspective view of the pawl holder
  • FIG. 15 is an enlarged perspective view of a joint pawl
  • FIG. 16 is a partly cutaway side view of a clutch mechanism before actuating the operation
  • FIG. 17 is a plan view in section of the clutch mechanism illustrated in FIG. 16 ;
  • FIG. 18 is a partly cutaway side view explaining a state where the clutch mechanism is engaged (first state);
  • FIG. 19 is a plan view in section of the clutch mechanism illustrated in FIG. 18 ;
  • FIG. 20 is a partly cutaway side view explaining a state where the clutch mechanism is released (second state);
  • FIG. 21 is a plan view in section of the clutch mechanism illustrated in FIG. 20 ;
  • FIG. 22 is an exploded perspective view explaining the assembling of the locking base, a lock clutch, a cover, and so forth;
  • FIG. 23 is an exploded perspective view explaining the assembling of the torsion bar, the lock pawl, the locking base, and so forth;
  • FIG. 24 is a diagram illustrating the relation between a tensile force acting on the webbing and the amount of the webbing pulled out.
  • FIG. 1 is a front view of the whole seatbelt retractor according to the invention
  • FIG. 2 is an exploded perspective view explaining the assembling of a take-up drum 2 , a connector 3 , a housing 9 , a torsion bar 4 , a locking base 5 , a base stopper 7 , and so forth which constitute the major part of the seatbelt retractor illustrated in FIG. 1 .
  • the seatbelt retractor is provided with the substantially cylindrical take-up drum 2 on which webbing is wound.
  • the torsion bar 4 is inserted through the center of the take-up drum 2 , and one end of the torsion bar 4 is coupled integrally with one end of the take-up drum 2 by means of the connector 3 , described later, and it is supported by a pair of side plates ( 9 b , 9 c ) to freely rotate.
  • a spiral spring 19 ( FIG. 1 ) is mounted on the side plate 9 c , which constantly biases the take-up drum 2 to rotate in the take-up direction of the webbing, and the torsion bar 4 is biased to rotate in the take-up direction of the webbing.
  • the seatbelt retractor in this embodiment has the structure which winds up slackness in the webbing by a gas pressure, and so forth in case of a vehicle emergency such as a collision, and restrains the movements of vehicle occupant by a pretensioner 15 ( FIG. 1 ) furnished on the side plate 9 c.
  • the locking base 5 resembling a substantially disk-like shape is coupled integrally with the other end outside of the torsion bar 4 on the side of the side plate 9 b of the housing, and it constitutes an emergency lock mechanism which restrains a rotation in the direction of the webbing pulled out.
  • a clutch mechanism located near the other end of the torsion bar 4 , while a second energy-absorbing means, described later, is located on the other end of the torsion bar 4 , close to the side on the other end of the take-up drum 2 , wherein the torsion bar 4 (first energy-absorbing means) and the second energy-absorbing means perform the absorption of impact energy in case of a vehicle emergency.
  • the housing 9 is made from a metal plate by a press-molding in a manner the right and left side plates ( 9 b , 9 c ) rise up from both the sides of a back-plate fixed to the vehicle body, and the section of the housing forms a substantially U-letter.
  • the base stopper 7 is to prevent the locking base 5 from coming off from the take-up drum 2 .
  • the one end of the torsion bar 4 is engaged with a hole of the connector 3 having the same shape thereof, and the other end is coupled with the locking base 5 to be able to rotate integrally.
  • the connector 3 is supported to freely rotate with the opening 9 d bored on the side plate 9 c of the housing 9 , and it is also engaged with a hexagonal engagement recess being formed on the one end of the take-up drum 2 to correspond with the external shape of the connector 3 , whereby the torsion bar 4 is capable of rotating integrally with the take-up drum 2 .
  • the emergency lock mechanism actuates the operation and the other end of the torsion bar 4 is fixed, the one end of the torsion bar 4 will rotate integrally with the take-up drum 2 by the webbing being pulled out. That is, the torsion bar 4 is twisted by the rotational force of the take-up drum 2 , thus the energy of pulling out the webbing can be absorbed by the torsion resistance thereof.
  • the torsion bar 4 functions as the first energy-absorbing means.
  • FIG. 3 is an exploded perspective view explaining the assembling of a plate assembly 2 e .
  • the plate assembly 2 e comprises a plate body 2 a , a spiral wire 2 b with plural winds, and a disk member 2 c having plural projections 2 q located circumferentially around a center hole.
  • one end 2 g of the wire is fixed to the plate body 2 a , and the other end 2 h of the wire is suspended to the backside of the disk member 2 c (viewed from FIG. 3 ).
  • FIG. 4 is an exploded perspective view illustrating the whole of the second energy-absorbing means.
  • the plate assembly 2 e and the take-up drum 2 are attached with a retainer 2 d.
  • FIG. 5 is a side view of the plate assembly 2 e
  • FIG. 6 is a front view partly in section of the same, wherein the plate assembly 2 e is assembled with the plate body 2 a , the wire 2 b , and the disk member 2 c , as illustrated in FIG. 3 .
  • a substantially circular receiving recess 2 f which constitutes a part of the second energy-absorbing means is formed on the side where the locking base is mounted on the take-up drum 2 , namely, on the end face of the left side in the drawing. Further, an engagement hole 2 k which receives a boss 5 c ( FIG. 2 ) of the locking base is formed on the center of the receiving recess 2 f .
  • the engagement pins 14 to be engaged with the wire 2 b are formed at specified places on the periphery of the receiving recess 2 f positioned outside the engagement hole 2 k on the bottom face. And, the slopes 2 t ( FIG. 5 ) are formed at the specified places for engaging with the wire 2 b .
  • three semi-circular engagement pins 14 are formed integrally to project from the bottom face of the receiving recess 2 f along the circumference thereof, wherein the wire 2 b is formed in spiral, and the circumference 2 i thereof ( FIG. 3 ) is formed in curvature, which conforms to the circular sliding face of the engagement pins 14 .
  • FIG. 5 is a side view of the plate assembly 2 e in which the individual components illustrated in FIG. 3 are assembled.
  • the disk member 2 c and the plate body 2 a are engaged integrally with each other in a state where the spiral wire 2 b is interposed between both. That is, the plate body 2 a and the disk member 2 c form a take-up part 2 m with a distance approximately equivalent to the diameter of the wire 2 b , and the disk member 2 c is coupled with the plate body 2 a in a manner that a relative rotation between both is impossible.
  • the curved one end 2 g of the wire 2 b is placed and fixed in a curved groove 2 n ( FIG. 6 ) of the plate body 2 a.
  • the wire 2 b having the one end thereof fixed to the plate body 2 a passes through the gap between the plate body 2 a and the disk member 2 c , and when the take-up drum 2 and the plate assembly 2 e perform a relative rotation, the wire 2 b reaches the upper face of the plate body 2 a being the take-up part 2 m.
  • the disk member 2 c covers take-up part 2 m of the plate body 2 a and the one end 2 g of the wire 2 b in the assembly state.
  • FIG. 6 is a front view which shows the internal structure of the plate assembly 2 e , part of which is sectioned.
  • the curved groove 2 n is formed on the take-up part 2 m of the plate body 2 a by means of substantially semi-circular plural projections 2 p, and the one end 2 g of the wire 2 b is placed in the curved groove 2 n and is coupled therewith.
  • the curvature radius of the curved groove 2 n is formed smaller than that of the curved path 2 j ( FIG. 4 ) of the take-up drum 2 .
  • FIG. 7 illustrates another embodiment of the curved groove 2 n.
  • the plural projections 2 p of the plate body 2 a at least one set of ribs 2 r facing to each other are formed between the projections 2 p forming the curved groove 2 n , and the gap between the ribs 2 r is made narrower than the diameter of the wire 2 b.
  • FIG. 8 is a front view in section illustrating a state where the take-up drum 2 illustrated in FIG. 4 and the plate assembly 2 e are assembled
  • FIG. 9 is a partly cutaway side view of the assembly illustrated in FIG. 8
  • FIG. 10 is a front view in section, illustrating a state where the take-up drum 2 rotates to a certain degree after the emergency lock mechanism actuates the operation in the assembly illustrated in FIG. 8
  • FIG. 11 is a partly cutaway side view in the same state.
  • the second energy-absorbing means having the above construction is contained in a space delimited between the take-up drum 2 and the locking base 5 .
  • the emergency lock mechanism actuates the operation, as the take-up drum 2 rotates, the wire 2 b illustrated in FIG. 8 and FIG. 9 is wound into the take-up part 2 m, as illustrated in FIG. 10 and FIG. 11 .
  • the wire 2 b relatively moves between the disk member 2 c and the plate body 2 a , along the curved circumference 2 i projected from the circumferential face of the disk member 2 c , while sliding on the three semi-circular engagement pins 14 of the take-up drum 2 .
  • the emergency lock mechanism actuates the operation, in case of a vehicle emergency such as a collision, the locking base 5 coupled with the other end of the torsion bar 4 is blocked in rotating in the direction of the webbing pulled out. And, when a rotational torque more than a predetermined value acts on the take-up drum 2 , due to the load acting on the webbing, the one end of the torsion bar 4 (first energy-absorbing means) actuates a torsional deformation.
  • the take-up drum 2 rotates to a degree corresponding to the torsional deformation in the torsion bar 4 , and at the same time, the other end of the torsion bar 4 , which is fixed, rotates in the direction of the webbing pulled out, whereby the impact energy is absorbed. And, the actuation of the torsional deformation in the torsion bar 4 generates a relative rotation between the take-up drum 2 and the locking base 5 . The absorption of the impact energy by the second energy-absorbing means actuates based on this relative rotation.
  • the plate body 2 a to which the one end 2 g of the wire 2 b is fixed is coupled with the locking base 5 , and it does not rotate, while since the engagement pins 14 formed integrally with the take-up drum 2 turn, the wire 2 b is pulled between the engagement pins 14 . That is, the wire 2 b slides between the engagement pins 14 while being positioned by the slopes 2 t, while being sequentially pulled to meander between the engagement pins 14 . At this moment, there generate a high sliding resistance and a bending resistance in the wire 2 b , and hence the sliding resistance and the bending resistance absorb the impact energy.
  • both the torsion bar 4 (first energy-absorbing means) and the second energy-absorbing means operate as the energy-absorbing mechanism, and absorb the impact energy in case of a vehicle emergency.
  • the clutch mechanism releases the engagement of the plate body 2 a with the locking base 5 of the emergency lock mechanism, and puts the plate body 2 a from the state of a relative rotation with the take-up drum 2 being possible into the state of a united rotation with the take-up drum 2 being possible with the locking base 5 detached.
  • This clutch mechanism switches the first state where a relative rotation of the plate body 2 a with the other end of the torsion bar 4 is impossible into the second state where a relative rotation of the plate body 2 a with the other end of the torsion bar 4 is possible. It also comprises the clutch release mechanism which actuates the switching at an arbitrary timing after detecting a vehicle collision.
  • the clutch mechanism comprises, as shown in FIG. 2 , a joint plate 5 b ( FIG. 23 ) coupled with the emergency lock mechanism in a manner that a relative rotation is impossible, and three joint pawls 12 being pivoted to be turnable on the opposite side of the take-up drum 2 to the plate body 2 a , which are in face contact with the joint plate 5 b to turn outward.
  • the joint pawl 12 ( FIG. 15 ) is a bow-formed member, and a pin 12 b is formed on the one end thereof.
  • the pin 12 b is pivoted on the opposite side of the take-up drum 2 to the plate body 2 a .
  • the joint pawl 12 turns with the pin 12 b as the center.
  • the joint pawl 12 has an inner projection 12 a ( FIG. 15 ) formed on the center of the inner wall, and a notch 12 c ( FIG. 15 ) formed on the other end inside.
  • a pawl holder 13 (resin spring) ( FIG. 14 ) in a sectional concave and circular form is provided in order to position and support the joint pawls 12 .
  • the pawl holder 13 is provided, on the circumference thereof in correspondence with the positions of the joint pawls 12 , with nail-formed parts 13 c each having ribs 13 a formed thereon. Inwardly slant slopes 13 b formed on the ribs 13 a and the nail-formed parts 13 c come into contact with the outer faces of the joint pawls 12 . This contact and the resin spring functions to bias the joint pawls 12 continuously toward the axial center.
  • the plate body 2 a is provided with projections 2 s which restrain the joint pawls 12 from turning relative to the plate body 2 a immediately after the joint pawls 12 climb over the ribs 13 a of the pawl holder 13 , the joint pawls 12 are clamped by the rib backsides 13 d of the pawl holder and the projections 2 s of the plate body so that the joint pawls 12 are prevented from turning to the plate body 2 a.
  • FIG. 12 is an exploded perspective view explaining the assembling of a release ring 8 , the housing 9 , a casing 10 , and so forth being the components for releasing the clutch.
  • FIG. 14 is an enlarged exploded perspective view of the release ring 8 , the casing 10 , a piston 10 a , a gas generator 10 b , a gas generator holder 11 , and so forth, which are illustrated in FIG. 13 .
  • the clutch release mechanism will be described with reference to FIG. 12 and FIG. 13 .
  • the release ring 8 is mounted to be rotatable on the casing 10 fixed to the side plate 9 b of the housing on the other side of the torsion bar 4 ( FIG. 2 ), which is located on the circumferences of the joint pawls 12 .
  • the clutch release mechanism is made up with the casing 10 , the gas generator 10 b which generates gas in a cylinder 10 e at an arbitrary timing after detecting a vehicle collision, and the piston 10 a , which is pressed and driven by the gas pressure in the cylinder, and presses the circumference of the release ring 8 to rotate the release ring 8 .
  • the gas generator 10 b is attached to the casing 10 by the gas generator holder 11 .
  • the release ring 8 is provided with a contact 8 b which comes in contact with the piston 10 a , and three tapered parts 8 a located with a uniform spacing on the circumference thereof.
  • the casing 10 which holds the release ring 8 is provided with tapered projections 10 d corresponding to the tapered parts 8 a of the release ring 8 rotated.
  • the piston 10 a pressed and driven by the gas pressure comes in contact with the contact 8 b formed on the circumference of the release ring 8 , and hence the release ring 8 rotates.
  • the tapered parts 8 a of the release ring 8 are guided by the tapered projections 10 d of the casing, and the release ring 8 retreats toward the take-up drum 2 ( FIG. 2 ) and retreats from the circumferences of the joint pawls 12 ( FIG. 2 ).
  • FIG. 16 through FIG. 21 are partly cutaway side views and plan views in section, which explain the operation of the clutch mechanism.
  • the clutch mechanism switches the first state where a relative rotation of the plate body 2 a with the other end of the torsion bar 4 is impossible into the second state where a relative rotation of the plate body 2 a with the other end of the torsion bar 4 is possible.
  • the joint pawls 12 are biased toward the axial center by the slopes 13 b ( FIG. 14 ) formed on the ribs 13 a of the pawl holder 13 .
  • the three joint pawls 12 are fixed at the most inwardly convergent position, in non-contact with the inner circumference of the release ring 8 , and the inner projections 12 a of the joint pawls 12 are in contact with projections 5 d of the joint plate 5 b.
  • an engagement tooth 6 b of a lock pawl 6 engages with the lock teeth 9 a ( FIG. 2 ) formed on the side plate 9 b of the housing, thus generating a relative rotation between the joint plate 5 b and the plate body 2 a which will continue to rotate.
  • a relative rotation is generated between the joint pawls 12 and the projections 5 d of the joint plate, whereby the projections 5 d of the joint plate press the inner projections 12 a of the joint pawls 12 , so that the joint pawls 12 receive a force toward the circumference, and they are prone to expand outwardly.
  • the joint pawls 12 When the force exceeds the biasing force of the pawl holder 13 , the joint pawls 12 come in contact with the inner-circumferential wall of the release ring 8 .
  • the joint pawls 12 come in contact with the inner-circumferential wall of the release ring 8 and the outward expansion thereof is restrained, the locking base 5 and the plate body 2 a become integrated with each other, and a relative rotation is generated between the take-up drum 2 and the plate body 2 a , so that the wire 2 b is pulled and the second energy absorption is performed, in addition to the energy absorption by the torsion bar 4 .
  • the piston 10 a ( FIG. 13 ) operates to rotate the release ring 8 , whereby the rotation of the release ring 8 guides the tapered parts 8 a of the release ring 8 to the tapered projections 10 d of the casing ( FIG. 13 ).
  • the release ring 8 retreats toward the take-up drum 2 , and retreats from the circumferences of the joint pawls 12 at the same time.
  • the joint pawls 12 come in face contact with the joint plate 5 b to expand outwardly, and become detached from the projections 5 d of the joint plate, whereby the plate body 2 a is released from the locking base 5 .
  • FIG. 22 is an exploded perspective view explaining the assembling of the emergency lock mechanism, which is made up with the locking base 5 , a lock clutch 16 , a cover 18 , and so forth.
  • FIG. 23 is an exploded perspective view explaining the assembling of the torsion bar 4 , the lock pawl 6 , the locking base 5 , and so forth.
  • a spring receiving part 16 a is formed to project on one side of the lock clutch 16 , and the spring receiving part 16 a is engaged to be relatively movable with a play inside a spring containing part 5 a resembling a recessed-groove shape, which is formed on the locking base 5 .
  • the spring receiving part 16 a is elastically biased in a specified direction by a return spring 17 made of a coil spring retained in the spring containing part 5 a , and the lock clutch 16 is made to rotate synchronously with the locking base 5 in a state of being biased in the direction of the webbing pulled out.
  • the torsion bar 4 is inserted in a hole bored through the cylindrical boss 5 c, which is formed to project from the side of the locking base 5 in the direction of facing the take-up drum 2 , whereby, the torsion bar 4 is coupled with the locking base 5 to be rotatable integrally.
  • the lock clutch 16 has a projected guide groove 16 c formed thereon, and into the guide groove 16 c, an interlocking pin 6 a formed on the lock pawl 6 ( FIG. 23 ) is slid and guided.
  • the interlocking pin 6 a is made to be slid and guided into the projected guide groove 16 c by a relative rotation of the lock clutch 16 and the locking base 5 against the biasing force by the return spring 17 .
  • This sliding and guiding of the interlocking pin 6 a makes it possible to freely project or retreat the engagement tooth 6 b of the lock pawl 6 from the circumference of the locking base 5 .
  • the emergency lock mechanism is made up with the locking base 5 , the lock pawl 6 , the lock teeth 9 a ( FIG. 2 ) formed on the housing 9 , the lock clutch 16 , and so forth.
  • a cover 18 is provided with a lock actuating mechanism which actuates the emergency lock mechanism in response to an abrupt pull-out of the webbing and an abrupt variation in the acceleration.
  • the locking base 5 and the lock pawl 6 are attached with the joint plate 5 b.
  • the engagement tooth 6 b is formed on a tip of the lock pawl 6 , and the lock pawl 6 is located to be slidable on the locking base 5 by the interlocking pin 6 a .
  • the lock teeth 9 a with which the engagement tooth 6 b of the lock pawl 6 is able to engage are formed on the side plate 9 b of the housing 9 , and in case of a vehicle emergency, the engagement tooth 6 b of the lock pawl 6 is engaged with the lock teeth 9 a , and this engagement restrains the locking base 5 from rotating in the direction of the webbing pulled out.
  • the second energy-absorbing means is contained in a space delimited by the take-up drum 2 and the locking base 5 , there is not a substantial size expansion in the axial direction of the seatbelt retractor to sacrifice the compactification, although the second energy-absorbing means is provided separately from the torsion bar 4 .
  • the structures of the wire 2 b and the engagement pins 14 which constitute the second energy-absorbing means are equally simple, and the manufacturing process thereof is rather simple as well.
  • FIG. 24 is a diagram illustrating the relation between a tensile force acting on the webbing and the amount of the webbing pulled out.
  • the whole energy-absorbing load of the seatbelt retractor is the sum f 3 of an energy-absorbing load f 1 when the torsion bar 4 generates a torsional deformation and an energy-absorbing load f 2 by the second energy-absorbing means, as illustrated in FIG. 24 .
  • the area of the energy absorption by the torsional deformation in the torsion bar 4 can be set freely independently.
  • the area of the energy absorption by the second energy-absorbing means can be set to overlap a part of the area of the energy absorption by the torsional deformation in the torsion bar 4 , thereby securing a high energy-absorbing load equivalent to the sum of both the energy-absorbing loads, in the part of the area of the energy absorption by the torsional deformation in the torsion bar 4 .
  • a low energy-absorbing load can be set only by the energy-absorbing function by the torsional deformation in the torsion bar 4 .
  • the adjustment of the whole energy-absorbing load of the seatbelt retractor is related to various factors such that it is related not only to the modifications of the diameter and material of the torsion bar 4 , but also to the modifications of the size, shape, and material of the second energy-absorbing means.
  • it is possible to realize a desired energy-absorbing load not depending on the modifications such as expansion of the diameter of the torsion bar 4 and modification of the material thereof, but by means of the design modification of the other remaining factors. That is, it is possible to easily set the energy-absorbing load high, without sacrificing the compactification of the seatbelt retractor by reducing the diameters of the torsion bar 4 and the take-up drum 2 .
  • both the torsion bar 4 and the second energy-absorbing means can be modified, by adjusting the energy-absorbing load and adjusting the energy-absorbing area in both the means, it becomes possible to easily meet the demand for a specific energy characteristic based on differences of the vehicle structure, and also possible to flexibly meet various needs.
  • the adjustment of the sliding resistance between the wire 2 b and the engagement pins 14 based on various factors such as a shape of the curved path, roughness of the contact faces of both, and size of the contact area and so forth.
  • the adjustment of the sliding resistance is set based on various factors in this manner, for example, if a modification of part of the factors becomes difficult due to the restrictions of the dimensions, modifying the other factors will make it possible to adjust the sliding resistance comparably easily to an arbitrary value required.
  • the seatbelt retractor of the invention is provided with the torsion bar 4 and the second energy-absorbing means, and also employs the clutch mechanism. Thereby, it is possible to appropriately select the amount of the energy absorption, by actuating both or only the torsion bar 4 at the actuating time of the energy absorption. And, after actuating the energy absorption by using both, in order to achieve an optimum energy absorption in correspondence with parameters such as physical make-up of vehicle occupant, scale of a vehicle collision, and time, it is possible to stop the provision of load by the second energy-absorbing means on the way, and to perform the energy absorption only by the torsion bar.
  • the present invention is useful for a seatbelt retractor which absorbs an impact load acting on a vehicle occupant in case of a vehicle emergency such as a collision, and secures the vehicle occupant.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Automotive Seat Belt Assembly (AREA)
US10/543,893 2003-01-31 2004-01-29 Seat belt retractor Abandoned US20060214494A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2003024342A JP4166095B2 (ja) 2003-01-31 2003-01-31 シートベルトリトラクター
JP2003-024342 2003-01-31
PCT/JP2004/000793 WO2004067338A1 (ja) 2003-01-31 2004-01-29 シートベルトリトラクター

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US20060214494A1 true US20060214494A1 (en) 2006-09-28

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ID=32820761

Family Applications (1)

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US10/543,893 Abandoned US20060214494A1 (en) 2003-01-31 2004-01-29 Seat belt retractor

Country Status (6)

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US (1) US20060214494A1 (ja)
EP (1) EP1600342B1 (ja)
JP (1) JP4166095B2 (ja)
KR (1) KR101105623B1 (ja)
DE (1) DE602004005320T2 (ja)
WO (1) WO2004067338A1 (ja)

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US20080073967A1 (en) * 2006-08-30 2008-03-27 Honda Motor Co., Ltd. Seat belt retractor mounting system
US20080203210A1 (en) * 2007-02-28 2008-08-28 Kabushiki Kaisha Tokai-Rika-Denki-Seisakusho Webbing retractor
CN107791998A (zh) * 2017-12-08 2018-03-13 沈阳金杯锦恒汽车安全系统有限公司 一种安全带卷收器芯轴组件结构
US20180086304A1 (en) * 2015-04-24 2018-03-29 Kabushiki Kaisha Tokai-Rika-Denki-Seisakusho Webbing take-up device
US10434976B2 (en) 2018-02-27 2019-10-08 Ford Global Technologies, Llc Seatbelt assembly
US10518740B2 (en) 2018-02-27 2019-12-31 Ford Global Technologies, Llc Seatbelt assembly
US10525929B2 (en) 2018-02-27 2020-01-07 Ford Global Technologies, Llc Seatbelt assembly
US10543806B2 (en) 2018-02-27 2020-01-28 Ford Global Technologies, Llc Seatbelt assembly

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GB2400351B (en) * 2003-04-09 2006-06-07 Autoliv Dev Improvements in or relating to a load limiting arrangement
JP5078110B2 (ja) * 2006-06-15 2012-11-21 タカタ株式会社 シートベルトリトラクタおよびこれを備えているシートベルト装置
JP5323223B2 (ja) * 2012-03-16 2013-10-23 タカタ株式会社 シートベルトリトラクタおよびこれを備えているシートベルト装置
JP6306537B2 (ja) * 2015-05-29 2018-04-04 株式会社東海理化電機製作所 ウェビング巻取装置

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JP4526631B2 (ja) * 2000-01-24 2010-08-18 オートリブ株式会社 シートベルト装置
JP2001287621A (ja) * 2000-04-07 2001-10-16 Tokai Rika Co Ltd ウェビング巻取装置
JP2001301569A (ja) * 2000-04-24 2001-10-31 Tokai Rika Co Ltd ウェビング巻取装置及び車両
JP3723423B2 (ja) * 2000-05-31 2005-12-07 エヌエスケー・オートリブ株式会社 シートベルト装置

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US3666198A (en) * 1969-07-12 1972-05-30 Gen Motors Corp Seat belt reel
US4323205A (en) * 1979-07-19 1982-04-06 Nippon Soken, Inc. Safety seat-belt retractor
US5607118A (en) * 1995-08-11 1997-03-04 Alliedsignal Inc. Retractor with adjustable load limiting levels
JPH09202211A (ja) * 1996-01-24 1997-08-05 Tokai Rika Co Ltd ウエビング巻取装置
US6241172B1 (en) * 1996-06-26 2001-06-05 Autoliv Development Ab Belt retractor with adjustable force-limiting device
US5823570A (en) * 1996-10-10 1998-10-20 Trw Vehicle Safety Systems Inc. Seat belt retractor with energy management
US5961060A (en) * 1997-08-05 1999-10-05 Daimler-Benz Aktiengesellschaft Belt roller for a safety belt system of a passenger seat
US5967442A (en) * 1997-10-21 1999-10-19 Trw Occupant Restraint Systems Gmbh Force limiter for a seat belt restraint system
US6206315B1 (en) * 1998-06-04 2001-03-27 Trw Occupant Restraint Systems Gmbh & Co. Kg Unit comprising at least two torsion bars for limiting the force in a belt retractor
US6216972B1 (en) * 1998-09-10 2001-04-17 Trw Occupant Restraint Systems Gmbh & Co. Kg Device for force limitation in a vehicle occupant restraint system
US6564895B1 (en) * 1998-12-07 2003-05-20 Trw Occupant Restraint Systems Gmbh & Co. Kg Belt retractor for a vehicle safety belt and method for actuating the belt retractor
US6416006B1 (en) * 1998-12-07 2002-07-09 Trw Occupant Restraint Systems Gmbh & Co. Kg Belt retractor for a vehicle safety belt
US6616081B1 (en) * 1999-06-16 2003-09-09 Autoliv Development Ab Belt retractor with switchable force limiter
US20020017583A1 (en) * 2000-05-02 2002-02-14 Hideaki Yano Seat belt retractor
US6598822B2 (en) * 2000-10-26 2003-07-29 Kabushiki Kaisha Tokai-Rika-Denki-Seisakusho Webbing retractor
US20020070307A1 (en) * 2000-12-08 2002-06-13 Takata Corporation Seat belt retractor
US20030192976A1 (en) * 2002-04-16 2003-10-16 Palliser Martyn Neil Seat belt retractor with multi-level load limiting
US20030192975A1 (en) * 2002-04-16 2003-10-16 Palliser Martyn Neil Seat belt retractor
DE20210812U1 (de) * 2002-07-17 2002-11-21 Trw Repa Gmbh Gurtaufroller mit Kraftbegrenzungsfunktion
US6969022B2 (en) * 2003-10-14 2005-11-29 Key Safety Systems, Inc. Seat belt retractor

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080073967A1 (en) * 2006-08-30 2008-03-27 Honda Motor Co., Ltd. Seat belt retractor mounting system
US7497521B2 (en) * 2006-08-30 2009-03-03 Honda Motor Co., Ltd Seat belt retractor mounting system
US20080203210A1 (en) * 2007-02-28 2008-08-28 Kabushiki Kaisha Tokai-Rika-Denki-Seisakusho Webbing retractor
US20180086304A1 (en) * 2015-04-24 2018-03-29 Kabushiki Kaisha Tokai-Rika-Denki-Seisakusho Webbing take-up device
US10434978B2 (en) * 2015-04-24 2019-10-08 Kabushiki Kaisha Tokai-Rika-Denki-Seisakusho Webbing take-up device
CN107791998A (zh) * 2017-12-08 2018-03-13 沈阳金杯锦恒汽车安全系统有限公司 一种安全带卷收器芯轴组件结构
US10434976B2 (en) 2018-02-27 2019-10-08 Ford Global Technologies, Llc Seatbelt assembly
US10518740B2 (en) 2018-02-27 2019-12-31 Ford Global Technologies, Llc Seatbelt assembly
US10525929B2 (en) 2018-02-27 2020-01-07 Ford Global Technologies, Llc Seatbelt assembly
US10543806B2 (en) 2018-02-27 2020-01-28 Ford Global Technologies, Llc Seatbelt assembly

Also Published As

Publication number Publication date
EP1600342B1 (en) 2007-03-14
DE602004005320D1 (de) 2007-04-26
KR20050091092A (ko) 2005-09-14
JP4166095B2 (ja) 2008-10-15
DE602004005320T2 (de) 2007-12-20
KR101105623B1 (ko) 2012-01-18
EP1600342A1 (en) 2005-11-30
WO2004067338A1 (ja) 2004-08-12
JP2004262262A (ja) 2004-09-24
EP1600342A4 (en) 2006-02-15

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