CN113819158B - One-way clutch and seatbelt retractor - Google Patents
One-way clutch and seatbelt retractor Download PDFInfo
- Publication number
- CN113819158B CN113819158B CN202111149811.4A CN202111149811A CN113819158B CN 113819158 B CN113819158 B CN 113819158B CN 202111149811 A CN202111149811 A CN 202111149811A CN 113819158 B CN113819158 B CN 113819158B
- Authority
- CN
- China
- Prior art keywords
- pawl
- way clutch
- drive element
- friction ring
- pivot
- 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.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D41/00—Freewheels or freewheel clutches
- F16D41/12—Freewheels or freewheel clutches with hinged pawl co-operating with teeth, cogs, or the like
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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
- B60R22/34—Belt retractors, e.g. reels
- B60R22/46—Reels with means to tension the belt in an emergency by forced winding up
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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
- B60R22/34—Belt retractors, e.g. reels
- B60R22/46—Reels with means to tension the belt in an emergency by forced winding up
- B60R2022/4666—Reels with means to tension the belt in an emergency by forced winding up characterised by electric actuators
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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
- B60R22/34—Belt retractors, e.g. reels
- B60R22/46—Reels with means to tension the belt in an emergency by forced winding up
- B60R2022/468—Reels with means to tension the belt in an emergency by forced winding up characterised by clutching means between actuator and belt reel
Abstract
The present invention relates to a one-way clutch and a seatbelt retractor. The one-way clutch includes: driving element, driven element, pawl, snap ring and friction ring. The drive element is rotatable relative to the friction ring between a first rotational position in which the pawl is in a first pivotal position relative to the drive element, the pawl is disengaged from the driven element, the pawl rests with said locking means on the drive element, and a second rotational position in which the pawl is in a second pivotal position relative to the drive element radially inward from the first pivotal position, the pawl being engaged with the driven element. The pawl has a locking member which is an elastic member which locks with the drive element in an over-passing position when the pawl passes over the first pivot position in a radially outward pivot direction. When the irreversible pretensioning device is activated, the one-way clutch can be shifted and permanently held in an inactive state without affecting the irreversible pretensioning function.
Description
Technical Field
The present invention relates to the field of vehicle safety technology, and more particularly to a one-way clutch and a seatbelt retractor including such a one-way clutch.
Background
In vehicles, in particular passenger vehicles, safety belts can be used as an effective and reliable passive safety device, which is a mandatory configuration in the entire vehicle safety system. Under the development trend of electric and intelligent vehicles, the requirements of safety protection and wearing comfort of safety belts on passengers are continuously improved.
Some safety belts known in practice comprise irreversible pretensioning means comprising a pyrotechnic gas generator, a coil and a steel ball, a flexible rack or the like housed in the coil. In the event of an impending emergency of the vehicle, for example in the event of an impending vehicle crash, the vehicle control unit can issue a control command such that the pyrotechnic gas generator is activated, the pyrotechnic gas generator is detonated, a steel ball, a flexible rack or the like is moved out of the coil by the force of the explosion, the spool of the seat belt retractor is driven in the webbing take-up direction such that the webbing is taken up and thus the gap inside the seat belt retractor and between the webbing and the body of the occupant is eliminated, and therefore the occupant can be better restrained on the vehicle seat, and good protection of the seat belt against the occupant can be achieved in the event of an emergency of the vehicle.
In addition, some safety belts known in practice may also comprise reversible active pretensioning means in addition to the irreversible pretensioning means. The active pretensioning device may generally comprise a reversible electric motor, an electronic control unit for controlling the operation of the motor, a transmission and a one-way clutch. In the case of a vehicle operation, or when a warning to the occupant is required, the reversible motor can be activated according to a preset control logic, so that the reversible motor drives the belt drum of the seat belt retractor in the webbing-retracting direction via the transmission and the engaged one-way clutch, actively pretensioning the webbing to a suitable extent. The reversible motor is then reversed, for example after the dangerous situation has been eliminated or after a predetermined period of time has elapsed, releasing the active pretensioning of the webbing. The electronic control unit may, for example, obtain a control command from the vehicle control unit. When the active pretensioning device is activated, the one-way clutch located in the transmission path between the reversible motor and the winding drum acts both as a force-bearing component and as an output for the torque from the reversible motor. When the active pretensioning function is released, the one-way clutch is preferably completely decoupled from the other various functions of the conventional seatbelt retractor, at least substantially, in particular completely, without interfering with the other functions of the seatbelt retractor. For example, in the event of an unavoidable imminent collision, the irreversible pretensioning device is activated, wherein the pyrotechnic charge of the pyrotechnic gas generator is ignited, in which case the activated active pretensioning device preferably does not interfere with this irreversible pretensioning function.
Disclosure of Invention
The object of the present invention is to provide a one-way clutch and a seatbelt retractor comprising such a one-way clutch, in which the one-way clutch can be switched and permanently held in an inactive state when the irreversible pretensioning device is activated, and thus the active pretensioning device is deactivated without affecting the irreversible pretensioning function.
A first aspect of the invention relates to a one-way clutch comprising:
a drive element rotatable in a first direction and a second direction opposite the first direction;
a driven element having a common axis of rotation with the drive element;
a pawl pivotally mounted to the drive element;
a stop ring;
the friction ring is in friction connection with the stop ring;
wherein the drive element is rotatable relative to the friction ring between a first rotational position in which the pawl is in a first rotational position relative to the drive element in which the pawl is disengaged from the driven element, and a second rotational position downstream of the first rotational position in the first direction in which the pawl is in a second rotational position relative to the drive element in which the pawl is pivoted radially inward from the first rotational position in which the pawl is engaged with the driven element;
Wherein the pawl has a locking member configured to lock with the drive element in an over-passing position that passes over the first pivot position in the radially outward pivot direction as the pawl passes over the first pivot position in the radially outward pivot direction;
wherein the locking member is an elastic member with which the pawl abuts against the drive element in the first pivot position.
By means of the one-way clutch, the active pretensioning function for the seatbelt retractor can be interposed in the seatbelt retractor and can then be released again. When the irreversible pretensioning device is activated, the one-way clutch can be shifted and permanently held in the inactive state, and thus the active pretensioning device is deactivated without affecting the irreversible pretensioning function, which can mean an increased safety of the safety belt.
In some embodiments, the pawl may have a sliding surface, the friction ring having guide means for guiding the sliding surface, in particular on both sides of the sliding surface, the pawl being pivotable relative to the drive element between a first pivot position and a second pivot position by the cooperation of the guide means with the sliding surface when the drive element rotates relative to the friction ring between the first rotational position and the second rotational position.
In some embodiments, the drive element may be a gear, friction wheel or pulley, in particular a spur gear.
In some embodiments, the driven element may be a gear, in particular a ratchet.
In some embodiments, the pawl may have a single pawl portion configured for coaction with the driven element.
In some embodiments, the pawl may have a free end remote from the pivot axis, in particular a pivot axis parallel to the rotation axis, the free end being configured for co-action with a driven element.
In some embodiments, with reference to the pivot axis, the sliding surface may protrude axially from the body of the pawl.
In some embodiments, the body of the pawl may have a flat outer side surface and the sliding surface may be coplanar with the outer side surface.
In some embodiments, the one-way clutch may include two pawls.
In some embodiments, the pivot axes of the two pawls lie on a single diametrical line with reference to the axis of rotation, in other words, the two pawls or the two pivot axes may have an angular spacing of 180 °. It will be appreciated that the angular spacing of the two pawls may be other than 180, for example the angular spacing may be 90, 120 or 150.
In some embodiments, the one-way clutch may include three pawls. Preferably, with reference to the rotation axis, the pivot axes of the three pawls may have an angular spacing of 120 ° from each other.
In principle, the number of pawls may be arbitrary, for example, a single pawl is also possible.
In some embodiments, the friction ring may have a single guide member for each sliding surface, which may have a radially inner contact portion and a radially outer contact portion, the sliding surface being guided between the radially inner contact portion and the radially outer contact portion.
In some embodiments, the friction ring may have a pair of guide members for guiding the sliding surface on both sides of the sliding surface, the pair of guide members having contact portions opposite to each other, the sliding surface being guided between the contact portions.
In some embodiments, any one of the contact portions may be configured for single-point, multi-point, linear, or planar contact with the sliding surface.
In some embodiments, the contact portion may have a cylindrical surface. The cylindrical surface may be in linear contact with the sliding surface. The cylinder may be a cylinder or an elliptical cylinder, or may be a portion of a cylinder or an elliptical cylinder.
In some embodiments, a first guide member of the pair of guide members may include a first portion protruding inward from the ring body of the friction ring, a second portion bent with respect to the first portion on a radially inner end of the first portion, and a third portion protruding axially from the second portion. Preferably, the second part can be configured as a plate, and further preferably, the second part extends in a radial plane perpendicular to the axis of rotation. Preferably, the third portion may be configured as a cylinder having a cylindrical surface as the contact portion.
In some embodiments, a second guide member of the pair of guide members may include an arm projecting inwardly from the ring body of the friction ring. Preferably, the free end of the arm may have a cylindrical surface as the contact portion. Preferably, the arm may be a curved arm. Further preferably, with reference to the rotation axis, the curved arm may comprise a first section extending substantially in a circumferential direction and a second section extending substantially in a radial direction.
In some embodiments, with reference to the axis of rotation, the third portion may be radially inward of the free end of the arm.
In some embodiments, with reference to the axis of rotation, the third portion and the free end of the arm may have substantially the same angular position or have an angular spacing in the circumferential direction, for example may have an angular spacing of 1 ° to 3 °.
In some embodiments, the friction ring may be mounted radially inward of the stop ring, wherein an outer circumferential surface of the friction ring may be frictionally coupled with an inner circumferential surface of the stop ring.
It will be appreciated that as an equivalent to "friction coupling", the friction ring may be coupled to the stop ring by magnetic force. For this purpose, at least one of the friction ring and the stop ring may have a permanent magnet. The friction ring can rotate relative to the stop ring against the magnetic force.
In some embodiments, the drive element and friction ring may each have a first tab configured to define a first rotational position of the drive element and friction ring relative to each other.
In some embodiments, the drive element and friction ring may each have a second projection configured to define a second rotational position of the drive element and friction ring relative to each other.
Alternatively, one of the driving element and the friction ring may have one projection, and the other of the driving element and the friction ring may have two projections between which the one projection may move. By the co-action of the one projection and the two projections, a first rotational position and a second rotational position of the drive element and the friction ring relative to each other can be defined.
In some embodiments, with reference to the axis of rotation, the contact surface of the drive element and the first projection of the friction ring may deviate from a radial plane. Thus, when the mating first bumps are in contact, the force perpendicular to the contact surface is offset from the tangential direction.
In some embodiments, the stop ring may be a stator. This means that the stator is an at least substantially stationary component. The stop ring can be moved slightly after installation, for example, by a play of not more than 3 ° due to manufacturing tolerances or due to assembly requirements.
In some embodiments, the stop ring is capable of limited rotation, e.g., the stop ring is capable of limited rotation over an angular range of less than 30 °, e.g., 20 ° to 30 °, or less than 10 °.
In some embodiments, to limit the movement of the stop ring, the housing part of the transmission may have a pin which can be inserted into a recess of the stop ring.
In some embodiments, the drive element may have a chamber with a bottom on one axial end side of the drive element and open on the other axial end side of the drive element, in which the stop ring, friction ring and pawl may be accommodated. Preferably, an axial stop disk connected to the drive element can be mounted on the open further axial end face. The driven element is capable of passing through the opening of the bottom into the chamber. The axial stop disc may also have an opening through which the driven element passes if the driven element should look through the entire one-way clutch. Preferably, the opening of the axial stop disk can be configured identically to the opening of the bottom of the drive element.
In some embodiments, with reference to the rotational axis, in the first pivot position and/or in the second pivot position, the component of the pawl from the pivot axis to the free end occupies an angular area of no more than 90 °, in particular no more than 60 °, for example no more than 45 °, particularly preferably no more than 30 ° or no more than 20 °. Thus, the pawls occupy a small space in the one-way clutch, so that the entire one-way clutch can be compact.
In some embodiments, the locking component may be a snap element that snaps into a mating snap seat.
In some embodiments, the locking member may be a spring catch, which may effect locking in the over-passed position.
In some embodiments, the locking member may be a hook-like member, in particular an elastic hook-like member.
In some embodiments, the locking member may be a resilient member with which the pawl abuts against the drive element in the first pivot position.
In some embodiments, the locking member may have a hook configured to be hooked by the drive element when the pawl passes over the first pivot position in a radially outward pivot direction such that the pawl remains in the passing over position.
In some embodiments, the locking member may be injection molded onto the body of the pawl.
In some embodiments, the locking member protrudes from the body of the pawl in a direction away from the free end of the pawl.
In some embodiments, the drive element may have a projection having a mating hook, the pawl bearing with a hook against a surface of the projection adjacent the mating hook in the first pivot position, the hook being slidable on the projection as the pawl pivots relative to the drive element from the first pivot position toward the passing position such that the hook hooks with the mating hook.
In some embodiments, the protrusions may be injection molded onto the drive element. In particular, the protrusions may be injection molded on the bottom of the cavity of the driving element.
In some embodiments, the friction ring may have a resilient member that, in a first pivot position of the pawl relative to the drive element, presses against the pawl and resists movement of the pawl in a radially inward pivot direction away from the first pivot position. Therefore, in the first pivot position of the pawl, the elastic member can suppress the vibration of the pawl, prevent the pawl from rattling, collide with other members of the one-way clutch, and noise caused thereby.
In some embodiments, the resilient member of the friction ring may disengage from the pawl upon a predetermined stroke of the pawl away from the first pivot position in a radially inward pivot direction. The elastic element of the friction ring can thus substantially completely not influence the active pretensioning function of the one-way clutch.
In some embodiments, the resilient members of the friction ring may be fingers injection molded onto the ring body of the friction ring.
A second aspect of the invention relates to a seatbelt retractor comprising a take-up reel, a driving device and a one-way clutch, the driving device being in driving connection with a driving element of the one-way clutch, the take-up reel being in driving connection with a driven element of the one-way clutch.
In some embodiments, the drive device is a reversible motor.
In some embodiments, the drive is in driving connection with the drive element of the one-way clutch via a transmission. Preferably, the drive element may be an output gear of a transmission, in particular a spur gear.
In some embodiments, the transmission may be a gear transmission including a housing and a gear set housed in the housing. Alternatively, a belt drive or a wire rope drive is also possible.
In some embodiments, the spool and the driven element of the one-way clutch may be drivingly connected in a direct drive manner. Preferably, the driven element may be an integral part of the tape cartridge.
The technical features mentioned above, those to be mentioned below, and those shown in the drawings may be arbitrarily combined with each other as long as the combined technical features are not contradictory. All possible combinations of features are technical matters contained in the present application.
Drawings
Exemplary embodiments will now be described with reference to the accompanying drawings. Wherein:
fig. 1 is a perspective view of a spool and one-way clutch of a seatbelt retractor according to one embodiment of the present application.
Fig. 2 shows the structural units of an active pretensioner of a seatbelt retractor according to an embodiment of the present invention.
Fig. 3 is an exploded view of a one-way clutch for a seatbelt retractor according to an embodiment of the present invention.
Fig. 4 and 5 are front views of the one-way clutch of fig. 3 in a first state and in a second state.
Fig. 6 is a front view of a pawl of the one-way clutch of fig. 3.
Fig. 7 is a perspective view of a friction ring of the one-way clutch of fig. 3.
Fig. 8A is a partial view of a friction ring.
Fig. 8B is a partial view of the friction ring and drive element of the one-way clutch.
Fig. 9 is a front view of the drive element of the one-way clutch of fig. 3.
Fig. 10 is a partial front view of the one-way clutch of fig. 3 in a third state.
Detailed Description
Fig. 1 is a perspective view of a spool 1 and a one-way clutch 10 of a seatbelt retractor according to an embodiment of the present invention. Fig. 2 shows the structural unit of the active pretensioner of the seatbelt retractor, which includes a one-way clutch 10 and further includes a drive 4 and a transmission 5 in the form of reversible motors. The structural unit shown in fig. 2 can be mounted on the winding drum 1 shown in fig. 1, wherein a gear, in particular a ratchet wheel, which is formed integrally with the winding drum 1 or is connected in a rotationally fixed manner coaxially, can be passed through the central opening of the one-way clutch 10 as the driven element 12 of the one-way clutch 10. The driven element 12 and the tape cartridge 1 may have a common axis of rotation 3. The reversible motor as the driving means 4 can be driven bi-directionally. The structural unit shown in fig. 2 may constitute an active pretensioner device of the seatbelt retractor.
Typically, the seatbelt retractor may comprise a frame, not shown, in which the seatbelt drum 1 is rotatably supported, to which the housing part 8 of the transmission 5 may be fixedly connected. As shown in fig. 2, the transmission 5 can be designed as a gear transmission, which has a housing. To show the gear set housed inside the housing, another housing component of the housing is removed to expose the gears of the gear set. The two housing parts of the housing of the transmission 5 may be plastic parts or metal parts. The drive 4 can be fastened to the housing part 8 of the transmission, for example by means of screws. Advantageously, when the housing part 8 is produced by injection molding, the housing part 8 can have a substantially cylindrical receptacle for receiving a substantially cylindrical electric motor. The pinion 6, which is fixedly connected to the output shaft or motor shaft of the drive 4 or is formed in one piece, meshes with the transmission gear 7, and the counter gear 9, which rotates coaxially with the transmission gear 7, meshes with an output gear which at the same time forms the drive element 11 of the one-way clutch. The one-way clutch 10, in addition to the driven element 12, can be accommodated as a module in the housing of the transmission 5. In principle, other devices known per se can be used for the drive 4 and the transmission 5, such as hydraulic drives, belt drives, wire rope drives, friction wheel drives, etc. A unidirectional drive 4 is also possible if the transmission 5 has a reversing mechanism.
Also visible in fig. 1 is a gear wheel 2 (which is shown in fig. 1 as a ball gear wheel), said gear wheel 2 being assigned to an irreversible pretensioning device, not shown, which may comprise a gas generator, a coil and a steel ball, a flexible rack or the like. For example, in the event of a crash of the vehicle, the powder of the gas generator is ignited, the gas generated by the gas generator drives a steel ball, flexible rack or the like accommodated in a coil, which impacts the gear wheel 2, so that the belt drum 1 is preloaded in the direction of the webbing winding, so that the occupant can be better restrained on the vehicle seat during the crash of the vehicle, and injuries to the occupant caused by the crash of the vehicle can be reduced or even completely avoided.
Fig. 3 is an exploded view of a one-way clutch 10 for a seatbelt retractor, which may be an integral part of a seatbelt retractor including the assembly shown in fig. 1 and 2, according to one embodiment of the present invention.
The one-way clutch 10 may include a drive element 11. Due to the bi-directional driving of the driving means 4, the driving element 11 is rotatable in a first direction D and a second direction R opposite to the first direction (see fig. 4 and 5). The first direction D may correspond to a webbing take-up direction of the spool 1. The second direction R may correspond to the webbing unwinding direction of the spool 1. The drive element 11 may be an output gear of the transmission 4. As shown in fig. 1 to 3 and 9, the drive element 11 may have a chamber which has a bottom on one axial end side of the drive element 11 and is open on the other axial end side of the drive element 11, on which an axial stop disk 18 connected to the drive element 11 may be mounted. The axial stop disc 18 may be a press-fit which can be crimped onto two pins 111 projecting from the bottom of the cavity of the driving element.
The one-way clutch 10 may include a stop ring 15, a friction ring 14, and two pawls 13 pivotally mounted on a pin 111. The pin 111 provides the pivot axis for the pawl. The axial stop disc 18 allows the axial positioning of the stop ring 15, the friction ring 14 and the pawls 13, preventing any one of them from coming out of the cavity of the driving element 11. The two pins 111 may lie on a diametric line, in other words, may have an angular spacing of 180 °.
The one-way clutch 10 may comprise a driven element 12, which driven element 12 may have a common rotational axis 3 with the driving element 11 (see fig. 1). The driven element 12 may be housed in the chamber. The driven element 12 can be passed through an opening 116 in the bottom of the driving element 11 into a chamber of the driving element 11. If the axial length of the driven element 12 is relatively long, the driven element 12 may extend from the axial stop disc 18 through an opening 19 of the axial stop disc 18, as shown in fig. 1.
The stop ring 15 may be a stator, which is at least substantially a stationary component. In alternative embodiments, the stop ring 15 can rotate only to a limited extent, for example, the stop ring can rotate only to a limited extent in an angle range of less than 30 °, for example, from 20 ° to 30 °, or less than 10 °. For this purpose, the housing part, which is not shown in fig. 2, may have at least one, for example three, pin which are inserted into a recess 20 (see fig. 3) in the outer circumference of the stop ring 15 during assembly, which pin may render the stop ring 15 essentially non-rotatable or may render the stop ring 15 only limitedly rotatable.
The friction ring 14 may be frictionally coupled with the stop ring 15. For this purpose, the friction ring 14 may be mounted radially inside the stop ring 15, wherein the outer circumferential surface of the friction ring 14 is frictionally coupled with the inner circumferential surface of the stop ring 15. The friction ring 14 may have two ends opposite to each other with the compression spring 16 installed therebetween, so that the friction ring 14 may permanently and stably maintain the friction coupling with the stop ring 15. In operation of the one-way clutch 10, the friction ring 14 and the stop ring 15 remain stationary until the friction force between the friction ring 14 and the stop ring 15 is overcome; after this friction force is overcome, the friction ring 14 can rotate relative to the stop ring 15.
Fig. 4 is a front view of the one-way clutch 10 of fig. 3 in a first state, and fig. 5 is a front view of the one-way clutch 10 in a second state, in which the axial blocking disc 18 of the one-way clutch 10 is removed to expose the structure of the one-way clutch 10 in the chamber of the drive element 11, which is hidden by the axial blocking disc 18, in order to show the internal structure.
In the first state of the one-way clutch 10 as shown in fig. 4, the drive element 11 is in a first rotational position relative to the friction ring 14, which can be defined by one first cam 114, 144 on each of the drive element 11 and the friction ring 14. As shown in fig. 8B, the first projection 114 of the drive element 11 rests against the first projection 144 of the friction ring 14, thereby defining a first rotational position of the drive element 11 and the friction ring 14 relative to each other, in which case the second projection 115 of the drive element 11 is separated from the second projection 145 of the friction ring 14. Starting from the first state, when the drive element 11 rotates in the second direction R, the friction ring 14 rotates together with the drive element 11 in the second direction R, wherein the first rotational position of the drive element 11 and the friction ring 14 relative to each other can be kept unchanged.
In the second state of the one-way clutch 10 as shown in fig. 5, the drive element 11 is in a second rotational position relative to the friction ring 14, which can be defined by one second cam 115, 145 on each of the drive element 11 and the friction ring 14. As can be seen from fig. 8B, the second cam 115 of the drive element 11 can rest against the second cam 145 of the friction ring 14, so that a second rotational position of the drive element 11 and the friction ring 14 relative to one another can be defined, in which case the first cam 114 of the drive element 11 and the first cam 144 of the friction ring 14 are separated from one another. Starting from the second state, when the drive element 11 rotates in the first direction D, the friction ring 14 rotates together with the drive element 11 in the first direction D, wherein the second rotational position of the drive element 11 and the friction ring 14 relative to each other can be kept unchanged.
As shown in fig. 8A, the first and second projections 144, 145 of the friction ring 14 may advantageously be provided in the region of the friction ring's mutually opposite free ends and axially protrude from the ring body 140 (see fig. 7) of the friction ring. It will be appreciated that the two lugs of the friction ring may be provided in any suitable location. With reference to the axis of rotation 3, when the first projection 114 of the driving element 11 comes into abutment with the first projection 144 of the friction ring 14, the force of the first projection 114 of the driving element 11 on the first projection 144 of the friction ring 14 deviates from the tangential direction. As regards the course of the contact surface of the first cam 114 of the drive element 11, reference can be made to fig. 9, which deviates from the radial direction.
The friction ring 14 may have a guiding structure that cooperates with the pawl 13. The guide structure may be configured to: as shown in fig. 4, in a first rotational position of the drive element 11 relative to the friction ring 14, such that the pawl 13 is in a first pivot position relative to the drive element 11, in which first pivot position the pawl 13 is disengaged from the driven element 12; and as shown in fig. 5, in a second rotational position of the driving element 11 relative to the friction ring 14, the pawl 13 is brought into a second pivot position relative to the driving element 11, in which second pivot position said pawl 13 is engaged with the driven element 12.
The active pretensioning process of the active pretensioning device including the one-way clutch 10 may be performed as follows:
starting from the first state shown in fig. 4, the drive device 4 drives the drive element 11 of the one-way clutch 10 in the first direction D in accordance with a control command. At this time, the friction ring 14 is held stationary with the stop ring 15 by friction coupling. The drive element 11 rotates relative to the friction ring 14 starting from a first rotational position relative to each other until a second rotational position relative to each other as shown in fig. 5 is reached, at the same time as the pawl 13 pivots relative to the drive element 11 from a first pivot position as shown in fig. 4 to a second pivot position as shown in fig. 5. Then, the friction force of the friction ring 14 and the stop ring 15 is overcome by the driving force of the driving element 11, and the friction ring 14 rotates together with the driving element 11 in the first rotation direction D, as the mating second protrusions 115, 145 meet. Since the pawl 13 is engaged with the driven member 12, the driving force is transmitted from the driving member 11 to the webbing take-up drum 1 via the pawl 13 and the driven member 12, so that the webbing take-up drum 1 pretensions the webbing in the webbing take-up direction. The rotational travel of the drive element 11 in the first rotational direction D can be preset. The achievement of the rotational travel may be associated with at least one of the following conditions, for example: reaching a predetermined degree of pretension on the webbing; the driving element 11 rotates a set angle in the first rotation direction D; the motor is operated for a predetermined period of time; the current of the motor reaches a predetermined threshold.
The release of the active pretensioning function of the active pretensioning device can be essentially reversed:
starting from the second state shown in fig. 5, the drive device 4 drives the drive element 11 of the one-way clutch 10 in the second direction R in accordance with a control command. At this time, the friction ring 14 is held stationary with the stop ring 15 by friction coupling. The driving element 11 rotates relative to the friction ring 14 from the second rotational position relative to each other until the first rotational position relative to each other as shown in fig. 4 is reached, at the same time as the pawl 13 pivots relative to the driving element 11 from the second rotational position as shown in fig. 5 to the first rotational position as shown in fig. 4, the pawl 13 being disengaged from the driven element 12. Then, as the mating first protrusions 114, 144 meet, the friction force of the friction ring 14 and the stop ring 15 is overcome by the driving force of the driving element 11, and the friction ring 14 rotates together with the driving element 11 in the second rotation direction R, collectively returning to the initial position. Since the pawl 13 is disengaged from the driven element 12, the tape cartridge 1 can be operated independently of the active pretensioning device.
Fig. 6 is a front view of one of the pawls 13 of the one-way clutch 10. The two pawls 13 of the one-way clutch 10 may be identically or similarly configured. The pawl 13 may have a body 31, for example made by casting or powder metallurgy. The body 31 may have a shaft bore 34. The pawl 13 may be pivotally mounted on the pin 111 of the drive element 11 via the shaft bore 34. The shaft hole 34 or the pin 111 may define a pivot axis of the pawl 13, which may be parallel to the rotation axis 3. The pawl 13 can have a free end 32 remote from the pivot axis, the free end 32 being configured for co-action with the driven element 12 in the form of a gear, in particular a ratchet.
The pawl 13 may have a flat outer surface with which the sliding surface 33 may be coplanar. The sliding surface 33 may protrude axially from the body 31 of the pawl 13. The sliding surface 33 can cooperate with the guide structure of the friction ring 14 such that the pawl 13 can pivot relative to the drive element 11 between the first pivot position and the second pivot position, respectively, when the drive element 11 rotates relative to the friction ring 14 between the first pivot position and the second pivot position. Each pawl 13 may occupy a small angular area over the entire circumference of the drive element 11. For example, with reference to the rotation axis 3, in the first pivot position and/or in the second pivot position, the angular area taken up by the component of each pawl 13 from the pivot axis to the free end 32 may not exceed 60 °, for example not exceed 45 °, in particular not exceed 30 °, in particular not exceed 20 °.
An exemplary embodiment of the guiding structure of the friction ring 14 is described in detail below with reference to fig. 7. For each pawl 13, the friction ring 14 may have pairs of guide members 141, 142 for guiding the sliding surface 33 on both sides of the sliding surface 33 of that pawl 13. The pair of guide members 141, 142 have contact portions opposed to each other, between which the sliding surface 33 is guided.
The first guide member 141 of the two guide members may include a first portion 41 protruding inward from the ring body 140 of the friction ring 14, a second portion 42 bent with respect to the first portion 41 on a radially inner end of the first portion 41, and a third portion 43 protruding in an axial direction from the second portion 42. The first portion 41 may have a decreasing width from a radially outer portion to a radially inner portion. The second part 42 may be configured as a plate, wherein the plate-shaped body may extend substantially in a radial plane perpendicular to the rotational axis of the friction ring (which rotational axis may coincide with the rotational axis 3 of the tape cartridge 1 or the driven element 12). The third portion 43 may be configured as a cylindrical body having a cylindrical surface as the contact portion. The sliding surface 33 may be in linear contact with the cylindrical surface of the third portion 43. The second of the two guide members 142 may comprise an arm projecting inwardly from the ring body of the friction ring 14, the free end 44 of which arm may have a cylindrical surface as a contact portion. The arm may be a curved arm. For example, with reference to the rotation axis 3, the bending arm may comprise a first section extending substantially in a circumferential direction and a second section extending substantially in a radial direction. With reference to the axis of rotation 3, the third portion 43 may be radially internal to the free end of the arm. With reference to the axis of rotation 3, the third portions 43 may have substantially the same angular position in the circumferential direction as the free ends 44 of the arms or be spaced apart from each other (in other words, with an angular spacing).
As shown in fig. 3 to 6, the pawl 13 may have a locking member 35. The locking member 35 may be an elastic member. The locking member 35 may have a hook 36. The locking member 35 may be injection molded onto the body 31 of the pawl 13. Advantageously, said locking member 35 can protrude from the body 31 of the pawl 13 in a direction facing away from the free end 32 of the pawl 13.
In a first pivot position of the drive element 11 relative to the friction ring 14, the pawl 13 can rest with the locking part 35 on the drive element 11. More specifically, the driving element 11 may have a projection 112, and the locking member 35 may rest with the hook 36 against the projection 112 in the first pivot position of the pawl 13. The projection 112 may be injection molded onto the bottom of the cavity of the drive element 11. The projection 112 may have a mating hook 117 that cooperates with a hook of the locking member 35. Advantageously, the drive element 11 may be a plastic gear, in particular may be produced by injection molding, and the projection 112 may be an integrally formed part of the injection molded drive element. It is also possible that the drive element 11 can have a metal body and that the projection 112 is injection-molded onto the metal body.
The locking member 35 lifts from the projection 112 when the pawl 13 is pivoted in a radially inward pivoting direction relative to the drive element 11 from the first pivot position. The protrusions 112 do not interfere with the active pretensioning function.
If the irreversible pretensioner is activated immediately after the activation of the active pretensioner, the pyrotechnic gas generator of the irreversible pretensioner is ignited, the spool 1 is driven by the irreversible pretensioner at a significantly increased rotational speed in the webbing take-up direction, and therefore the driven element 12 rotating at high speed impacts the pawl 13 with high energy, so that the pawl 13 bounces from the second pivot position in the radially outward pivot direction toward the first pivot position and passes over the first pivot position. The locking part 35 of the pawl 13 is then locked with the drive element 11 in the passing position. In particular, the hook 36 of the locking member 35 can slide on the projection 112 of the driving element 11 until the hook 36 of the locking member 35 catches on the mating hook 117 of the projection 112, so that the pawl 13 can no longer pivot about the pivot axis, remaining disengaged from the driven element 12, as shown in fig. 9. The active pretensioner device therefore does not interfere with the irreversible pretensioning function of the seatbelt retractor and the force limiting function which may be provided, which can improve the safety of the operation of the seatbelt.
As shown in fig. 3 to 5, the one-way clutch 10 may include a return spring 17. For this purpose, the drive element 11 can have a pin 113 and the friction ring 14 can have a pin 143, the return spring 17 being able to be suspended at its two ends on the pins 113, 143. In the absence of a load, the return spring 17 can hold the friction ring 14 together with the stop ring 15 in an initial position relative to the drive element 11.
As shown in fig. 3 to 5 and 7, the friction ring 13 may have a resilient member 146, which resilient member 146 presses the pawl 13 and resists the pawl 13 from moving in a radially inward pivoting direction from the first pivot position in the first pivot position of the pawl 13 relative to the drive element 11. The resilient member 146 is out of contact with the pawl 13 upon a predetermined stroke of the pawl 13 in a radially inward pivoting direction away from the first pivot position and thus does not interfere with the active pretensioning function. The resilient members 146 may be fingers that are injection molded onto the ring body 140 of the friction ring. In the first pivot position, the finger may be rotated in the opposite direction to the rotation of the free end of the pawl, with reference to the pivot axis of the pawl 13. As shown in fig. 4, with reference to the pivot axis of the pawl 13, the direction of extension of the finger is right-handed and the direction of rotation of the free end 32 is left-handed. In the initial position of the pawl 13, the locking part 35 of the pawl 13, which is designed as an elastic part, can counteract a pivoting movement of the pawl 13 in the radially outward pivoting direction, and the elastic part 146 of the friction ring 14 can counteract a pivoting movement of the pawl 13 in the radially inward direction, so that vibrations of the pawl 13 about the pivot axis in the initial position can be suppressed, rattling of the pawl 13, impacts with other parts of the one-way clutch 10 and noise generated thereby can be avoided.
It is noted that the terminology used herein is for the purpose of describing particular aspects only and is not intended to be limiting of the disclosure. As used herein, the singular forms "a", "an" and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise. It will be understood that the terms "comprises" and "comprising," and other similar terms, when used in this specification, specify the presence of stated operations, elements, and/or components, but do not preclude the presence or addition of one or more other operations, elements, components, and/or groups thereof. The term "and/or" as used herein includes all arbitrary combinations of one or more of the associated listed items. In the description of the drawings, like reference numerals always denote like elements.
The thickness of elements in the drawings may be exaggerated for clarity. It will also be understood that if an element is referred to as being "on", "coupled" or "connected" to another element, it can be directly on, coupled or connected to the other element or one or more intervening elements may be present therebetween. Conversely, if the expressions "directly on … …", "directly coupled to … …" and "directly connected to … …" are used herein, it is intended that there are no intervening elements present. Other words used to describe the relationship between elements should be interpreted similarly such as "between … …" and "directly between … …", "attached" and "directly attached", "adjacent" and "directly adjacent", and so forth.
Terms such as "top," "bottom," "over," "under," and the like are used herein to describe one element, layer or region's relationship to another element, layer or region as illustrated in the figures. It will be understood that these terms are intended to encompass other orientations of the device in addition to the orientation depicted in the figures.
It will be understood that, although the terms "first," "second," etc. may be used herein to describe various elements, these elements should not be limited by these terms. These terms are only used to distinguish one element from another element. Thus, a first element could be termed a second element without departing from the teachings of the present inventive concept.
Finally, it is pointed out that the above embodiments are only intended to understand the invention and do not limit the scope of protection thereof. Modifications to the above would be obvious to those of ordinary skill in the art, but would not bring the invention so modified beyond the scope of the present invention.
Claims (20)
1. A one-way clutch, the one-way clutch comprising:
-a driving element (11) rotatable in a first direction (D) and in a second direction (R) opposite to the first direction;
-a driven element (12) having a common axis of rotation (3) with the driving element;
a pawl (13) pivotally mounted to the drive element;
a stop ring (15);
a friction ring (14) frictionally coupled to the stop ring;
wherein the drive element is rotatable relative to the friction ring between a first rotational position in which the pawl is in a first rotational position relative to the drive element in which the pawl is disengaged from the driven element, and a second rotational position downstream of the first rotational position in the first direction in which the pawl is in a second rotational position relative to the drive element in which the pawl is pivoted radially inward from the first rotational position in which the pawl is engaged with the driven element;
wherein the pawl has a locking member (35) configured to lock with the drive element in an over-passing position that passes over the first pivot position in the radially outward pivot direction when the pawl passes over the first pivot position in the radially outward pivot direction;
wherein the locking member is an elastic member with which the pawl abuts against the drive element in the first pivot position.
2. A one-way clutch according to claim 1, characterized in that the locking member has a hook (36) configured to be hooked by the drive element when the pawl passes over the first pivot position in a radially outward pivot direction, so that the pawl is held in the passing over position.
3. A one-way clutch according to claim 2, characterized in that the drive element has a projection (112) with a mating hook (117), the pawl bearing with the hook against a surface of the projection adjacent to the mating hook in the first pivot position, the hook sliding on the projection as the pawl pivots relative to the drive element from the first pivot position towards the over-position such that the hook hooks with the mating hook.
4. A one-way clutch according to any one of claims 1 to 3, wherein the locking member is injection molded onto the body of the pawl.
5. A one-way clutch according to any one of claims 1 to 3, wherein the locking member protrudes from the body of the pawl in a direction away from the free end of the pawl.
6. A one-way clutch according to any one of claims 1 to 3, characterized in that the pawl has a free end (32) remote from a pivot axis parallel to the rotation axis, the free end being configured for co-action with a driven element.
7. A one-way clutch according to any one of claims 1 to 3, characterized in that the pawl has a sliding surface (33), the friction ring has a guide member (141, 142) for guiding the sliding surface, and the pawl is pivotable relative to the drive element between the first pivot position and the second pivot position by co-action of the guide member and the sliding surface when the drive element rotates relative to the friction ring between the first rotational position and the second rotational position.
8. A one-way clutch according to claim 7, characterized in that the sliding surface protrudes axially from the body (31) of the pawl with reference to the pivot axis of the pawl.
9. A one-way clutch according to any one of claims 1 to 3, characterized in that the one-way clutch comprises two pawls whose pivot axes lie on a diametric line with reference to the axis of rotation.
10. A one-way clutch according to any one of claims 1 to 3, wherein the friction ring is mounted radially inward of the stop ring, wherein an outer peripheral surface of the friction ring is frictionally coupled with an inner peripheral surface of the stop ring.
11. A one-way clutch according to claim 1 to 3,
The drive element and the friction ring each have a first projection (114, 144) configured for defining a first rotational position of the drive element and the friction ring relative to each other; and/or
The drive element and the friction ring each have a second projection (115, 145) configured for defining a second rotational position of the drive element and the friction ring relative to each other.
12. The one-way clutch of claim 11, wherein the contact surface of the drive element and the first tab of the friction ring are offset from a radial plane with reference to the rotational axis.
13. A one-way clutch according to any one of claims 1 to 3, wherein the stop ring is a stator or the stop ring is limited in rotation.
14. A one-way clutch according to any one of claims 1-3, characterized in that the drive element has a chamber with a bottom at one axial end side of the drive element and being open at the other axial end side of the drive element, in which chamber the stop ring, friction ring and pawl are accommodated, on the open other axial end side an axial stop disc (18) connected to the drive element being mounted, the driven element being able to enter the chamber through an opening (116) of the bottom.
15. A one-way clutch according to any one of claims 1 to 3, characterized in that, with reference to the rotational axis, in the first pivot position and/or the second pivot position, the angular area taken up by the component parts of the pawl from the pivot axis to the free end does not exceed 60 °.
16. A one-way clutch according to any one of claims 1 to 3, characterized in that the friction ring has a resilient member (146) which, in a first pivot position of the pawl relative to the drive element, presses against the pawl and resists the pawl from moving in a radially inward pivot direction from the first pivot position.
17. The one-way clutch of claim 16, wherein the resilient member of the friction ring is out of contact with the pawl when the pawl is displaced a predetermined stroke in a radially inward pivoting direction from the first pivot position.
18. The one-way clutch of claim 16, wherein the resilient member of the friction ring is a finger element injection molded onto the ring body of the friction ring.
19. A one-way clutch according to any one of claims 1 to 3, wherein the driving and driven elements are gears.
20. A seatbelt retractor comprising a take-up reel (1), a drive device (4) and a one-way clutch (10) according to any one of claims 1 to 19, the drive device being in driving connection with a drive element (11) of the one-way clutch, the take-up reel being in driving connection with a driven element (12) of the one-way clutch.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111149811.4A CN113819158B (en) | 2021-09-29 | 2021-09-29 | One-way clutch and seatbelt retractor |
| PCT/CN2022/121295 WO2023051454A1 (en) | 2021-09-29 | 2022-09-26 | Seatbelt retractor and clutch |
| EP22789838.4A EP4326583A1 (en) | 2021-09-29 | 2022-09-26 | Seatbelt retractor and clutch |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111149811.4A CN113819158B (en) | 2021-09-29 | 2021-09-29 | One-way clutch and seatbelt retractor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN113819158A CN113819158A (en) | 2021-12-21 |
| CN113819158B true CN113819158B (en) | 2023-08-15 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111149811.4A Active CN113819158B (en) | 2021-09-29 | 2021-09-29 | One-way clutch and seatbelt retractor |
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| CN (1) | CN113819158B (en) |
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| CN113819158A (en) | 2021-12-21 |
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