WO2006120968A1 - ステアリングコラム装置 - Google Patents
ステアリングコラム装置 Download PDFInfo
- Publication number
- WO2006120968A1 WO2006120968A1 PCT/JP2006/309119 JP2006309119W WO2006120968A1 WO 2006120968 A1 WO2006120968 A1 WO 2006120968A1 JP 2006309119 W JP2006309119 W JP 2006309119W WO 2006120968 A1 WO2006120968 A1 WO 2006120968A1
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- WIPO (PCT)
- Prior art keywords
- tooth
- teeth
- steering
- angle
- telescopic
- Prior art date
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D1/00—Steering controls, i.e. means for initiating a change of direction of the vehicle
- B62D1/02—Steering controls, i.e. means for initiating a change of direction of the vehicle vehicle-mounted
- B62D1/16—Steering columns
- B62D1/18—Steering columns yieldable or adjustable, e.g. tiltable
- B62D1/184—Mechanisms for locking columns at selected positions
Definitions
- the present invention relates to a steering column device that supports a steering shaft so as to be adjustable in at least one of a tilt direction and a telescopic direction.
- a steering column device is an important safety safety part of a vehicle, and it is very important how to control the behavior at the time of a collision in order to ensure the safety of a passenger at the time of the collision.
- the steering column device itself is provided with an impact energy absorbing mechanism, and also plays an important role as a support member for the airbag stored in the steering wheel.
- a general steering column device can adjust the tilt angle of the steering wheel according to the physique and driving posture of the driver, and the axial direction of the steering wheel The position can be adjusted. Therefore, the steering column device has a conflicting function that the position and posture of the column body (ie, the steering wheel) must be easily adjusted, and that a predetermined position and posture must be secured in the event of a collision. Is required.
- the conventional steering column device that achieves such contradictory functions is required to be further improved due to the increasing demands on the operability of the user with various measures.
- Patent Document 1 discloses a steering column device capable of holding a column main body by superposing multiple friction plates and using a frictional force generated therebetween.
- Patent Document 2 German Patent No. 10212263
- Patent Document 3 US Patent Publication No. 2005Z0016315A1 Specification
- Patent Document 2 during tilt and telescopic adjustment, the gears that have been engaged are separated from each other, and after adjustment, the gears are engaged to adjust the position of the column body.
- a steering column device that can be securely held is disclosed.
- Patent Document 2 in the case of a mechanism that holds the position of the column main body by engaging the gears, when the gears are engaged after adjustment, the crests of the gears contact each other inherently. There is a risk of poor integration. In Patent Document 2, attempts have been made to suppress this, but this is not always sufficient.
- Patent Document 3 after tilting and telescopic adjustment, one of the spring-biased and movablely held teeth can be smoothly engaged with the other tooth, whereby the column body A steering column device capable of maintaining a position is disclosed.
- a complicated and large structure must be used to spring-bias one of the teeth.
- the present invention has been made in view of the problems of the prior art, and it is possible to provide a steering column device that can increase the holding force and is excellent in operation feeling while being lightweight and compact.
- the purpose is to provide.
- the steering column device that supports the steering shaft so that the position of the steering shaft can be adjusted with respect to at least one of the tilt direction and the telescopic direction.
- a column body that rotatably supports the steering shaft
- Second teeth that move integrally with the column body
- the first teeth and the second teeth mesh with each other to position the column body relative to the vehicle body;
- the first teeth and the second teeth are spaced apart from each other so that the column body can be adjusted in position relative to the vehicle body;
- a steering device is provided in which the first tooth and the second tooth are brought close to each other so as to be set to be greater than 0 degree and less than 90 degrees.
- One of the first tooth and the second tooth is provided on a pair of opposed first inclined surfaces, and the other of the first tooth and the second tooth is on the first pair of inclined surfaces. It may be formed on a pair of second inclined surfaces that face each other.
- the second inclined surface defined between the pair of first inclined surfaces and the central surface of the first inclined surface defined between the pair of first inclined surfaces and the pair of second inclined surfaces.
- the center plane of the surface is shifted from each other,
- Drive means for driving the center surface of the first inclined surface and the center surface of the second inclined surface closer to each other before engaging the first tooth with the second tooth.
- a steering apparatus according to any one of the first to third aspects, wherein the steering apparatus is connected to one of the first teeth and the second teeth.
- the one tooth is engaged with the other tooth of the first tooth and the second tooth by moving the lever so as to have an arcuate locus along with the lever. Also good.
- the steering device according to any one of the first to third aspects.
- at least one of the first tooth and the second tooth may have a tooth cross-sectional area that decreases in size toward the tip.
- the steering apparatus according to the first aspect further includes
- the first tooth is provided on the bracket fixed to the vehicle body
- the second teeth may be provided on the lever that tilts together with the column body.
- a steering apparatus according to the first aspect.
- a lever that is swingably supported by a bracket fixed to the vehicle body side, and as the lever rotates, telescopic movement of the column body relative to the lever is allowed;
- the first tooth is provided on a lever supported on the vehicle body side
- the second teeth are provided on the telescopic column body! /, Or even! /.
- the pair of first inclined surfaces may face each other with a predetermined angle to form a wedge shape
- the pair of second inclined surfaces may face each other with a predetermined angle to form a wedge shape
- the first teeth and the second teeth may be mixed with each other when a force is applied to the steering shaft, and the tooth traces are inclined in a direction in which the rate increases.
- the friction angle between the first tooth and the second tooth is set to z;
- a half apex angle of the first tooth and the second tooth is ⁇
- the angle formed by the tooth surface of the first tooth and the tooth surface of the second tooth with respect to the mating surface is j8, and the direction of the first tooth and the second tooth trace is the direction of the force.
- the tooth surface is arranged to satisfy the following conditional expression. ⁇ > tan (tan a ⁇ sin j8) — (90 ° — ⁇ ) (conditional expression)
- the squeezing surface means that when one tooth is moved so that the squeezing rate increases after the first tooth and the second tooth squeeze, A surface along the trajectory formed by the long axis.
- the steering column device that supports the steering shaft so that the position of the steering shaft can be adjusted with respect to at least one of the tilt direction and the telescopic direction.
- a column body that rotatably supports the steering shaft
- Second teeth that move integrally with the column body
- the first teeth and the second teeth mesh with each other to position the column body relative to the vehicle body;
- the first teeth and the second teeth are spaced apart from each other so that the column body can be adjusted in position relative to the vehicle body;
- one of the first tooth and the second tooth is provided on a pair of opposed first inclined surfaces.
- the other of the first teeth and the second teeth may be formed on a pair of second inclined surfaces that respectively face the first pair of inclined surfaces.
- the pair of first inclined surfaces face each other with a predetermined angle to form a wedge shape
- the second inclined surfaces may also face each other with a predetermined angle to form a wedge shape.
- the friction angle between the first tooth and the second tooth is set to ⁇
- a half apex angle of the first tooth and the second tooth is ⁇
- the angle formed by the tooth surface of the first tooth and the tooth surface of the second tooth with respect to the mating surface is j8, and the direction of the first tooth and the second tooth trace is the direction of the force.
- the tooth surface may be arranged so as to satisfy the following conditional expression.
- the teeth are aligned with each other in the normal direction with respect to the tooth traces, and the forces are also moved in parallel.
- the teeth facing each other move in parallel with the tangential direction of the tooth trace and squeeze together.
- the tooth tips of the gears that mesh with each other or the tips of the tooth traces hit each other, and there is a high possibility that a poor meshing will occur.
- the “normal direction of the tooth trace” refers to a normal extending from the tooth trace with respect to a virtual surface including a plurality of tooth traces in the same gear part.
- the first tooth and the second tooth are in a normal direction and a tangential direction (direction parallel to the tangent line) with respect to the respective tooth traces.
- the meshing of the first tooth and the second tooth can be suppressed. Therefore, it is possible to avoid the deterioration of the operation feeling as in the case of using a multi-plate friction plate, and furthermore, after the first teeth and the second teeth are engaged, a large holding force can be exhibited.
- the “telescopic direction” refers to the axial direction of the steering shaft
- the “tilt direction” refers to the direction (particularly the vertical direction) intersecting with it.
- first teeth and the second teeth are formed on both surfaces of the tapered surfaces facing each other, a stronger holding force can be exhibited by the engagement of the teeth on both surfaces.
- At least one of the first tooth and the second tooth meshes with the second tooth when the cross-sectional area of the tooth decreases toward the tip. , So preferred.
- the first teeth and the second teeth have a tooth trace in a direction in which the engagement rate increases when a force is applied to the steering shaft at the time of a collision. Therefore, the larger the impact force applied to the steering shaft, the higher the engagement rate and the holding force. In addition, since the holding force can be secured even if the number of teeth is reduced, there is an advantage that a good operation feeling can be secured while being lightweight and compact.
- the engagement rate can be increased at the time of collision. it can.
- the tooth surface angle is determined by a certain three-dimensional relational expression so that 0 does not exceed the friction angle.
- FIG. 1 is a perspective view of a steering column device according to the present embodiment.
- FIG. 2 is a perspective view of a steering column device according to a modification.
- FIG. 3 is a perspective view of the telescopic gear base 6 and the telescopic gear member 8 in a combined state.
- FIG. 4 is a sectional view of the telescopic gear base 6 and the telescopic gear member 8 in a detached state. 5] (a) to (e) are telescopic gear bases 6 and telescopic gears where the disengagement force also reaches the combined state. 4 is a cross-sectional view of the gear member 8.
- FIG. 6 is a perspective view showing the relationship between the tilt gear base 7 and the tilt gear member 9.
- FIG. 7 is a perspective view showing a modified example of the telescopic gear base 6 and the telescopic gear member 8 which are effective in the present embodiment.
- FIG. 8 is a cross-sectional view showing a modified example of the telescopic gear base 6 and the telescopic gear member 8 which are effective in the present embodiment.
- FIG. 9 is a cross-sectional view similar to FIG. 6, showing a modification of the tilt gear base 7 and the tilt gear member 9 that can be applied to the present embodiment.
- FIG. 10 is a flow chart showing a method for manufacturing the telescopic gear base 6 and the telescopic gear member 8.
- FIG. 11] (a) to (g) are diagrams showing the processing states of the telescopic gear member 8 in the order of the manufacturing steps.
- FIG. 12] (a) to (e) are diagrams showing the processing states of the telescopic gear base 6 in the order of manufacturing steps.
- FIG. 13 is a view showing a die for processing the telescopic gear member 8, (a) is a top view thereof, and (b) is a side view thereof.
- FIG. 14 is a perspective view of a steering column device according to a modification.
- FIG. 15 is a perspective view of a steering column device according to a modification.
- FIG. 16 is a perspective view of a column body of a steering column device according to a modification.
- FIG. 17 (a) to (c) are cross-sectional views of a telescopic gear base 6 and a telescopic gear member 8 which are used in another embodiment.
- FIG. 18 is a perspective view of one of the teeth 6a of the telescopic gear base 6.
- FIG. 19A is a diagram showing a telescopic gear base 6 and a telescopic gear member 8 in a normal state according to the second embodiment.
- FIG. 19B is a view on arrow XIX B in FIG. 19A.
- FIG. 19C is a view on arrow XIX C of FIG. 19A.
- FIG. 20A is a diagram showing a telescopic gear base 6 and a telescopic gear member 8 according to a second embodiment at the time of collision.
- FIG. 20B is a view on arrow XX B in FIG. 20A.
- FIG. 20C is a view taken along arrow XX C in FIG. 20A.
- FIG. 21 is a view showing a conventional steering apparatus for explaining a third embodiment.
- FIG. 22 is a view showing a conventional gear mechanism for explaining a third embodiment.
- FIG. 23A is a side view of a gear member in a third embodiment when the tooth surface inclination angle is set to j8 and the tooth trace inclination angle is set to 0 degree.
- FIG. 23B is a front view of the gear member as seen in FIG. 23A from the left direction of FIG. 23A.
- FIG. 23C is an enlarged view of the main part of FIG. 23A.
- FIG. 23D is an enlarged view of the main part of FIG. 23B.
- FIG. 23E is a view on arrow XXIII E in FIG. 23C.
- FIG. 24 shows a gear member when the inclination angle of the tooth trace is inclined by ⁇ degrees in FIG. 23C.
- FIG. 25 is a comparative view showing a case where a gear mesh is constituted by a set of tooth surfaces for explaining the fourth embodiment.
- FIG. 26 is a perspective view showing a gear member of a fourth embodiment.
- FIG. 1 and 2 are perspective views of the steering column device according to the first embodiment of the present invention.
- FIG. 1 shows a locked state
- FIG. 2 shows a released state.
- the cylindrical column body 1 is attached to a vehicle body (not shown) via brackets 2 and 3.
- a steering shaft S for connecting a steering wheel (not shown) and a steering mechanism is inserted into the column body 1 and is rotatably supported by a bearing (not shown).
- a plate-like telescopic gear base 6 is fixed to the side of the column body 1, while a plate-like tilt gear base 7 is fixed to the bracket 2.
- the telescopic gear base 6 has a length corresponding to the adjustment width of the column body 1 in the telescopic direction.
- the tilt gear base 7 has a height corresponding to the adjustment width of the column body 1 in the tilt direction.
- the column body 1 has a long hole for a telescopic slide.
- a tiltable shaft long hole (not shown) provided in the bracket 2 and a telescopic shaft long hole (not shown) provided in the column main body 1 are connected to a rotatable shaft 5a with an operation lever 5 Is installed.
- Telescopic gear member 8 is fixedly attached to operation lever 5 corresponding to telescopic gear base 6, and tilt gear member 9 is formed in a body corresponding to tilting gear base 7. Has been.
- a cam type rotary clamp mechanism 10 is provided at the base of the operation lever 5.
- the cam type rotary clamp mechanism 10 operates to operate the operation lever 5 to generate a clamp by the cam effect and to position the tilt telescope.
- the cam type rotary clamp mechanism 10 can be provided with a stopper function of the operation lever 5 to control the gear meshing and rate of the gear base and gear member. You can have it.
- the telescopic gear member 8 When the operation lever 5 is rotated to the position shown in FIG. 1, the telescopic gear member 8 is engaged with the telescopic gear base 6 while moving in an arc shape, and the tilt gear base 7 is tilted. The gear member 9 is engaged. On the other hand, when the operating lever 5 is rotated to the position shown in FIG. 2, the telescopic gear member 8 is detached from the telescopic gear base 6 while moving in an arc shape, and the tilting gear base 7 is tilted. The gear member 9 for use is disengaged.
- FIG. 3 is a perspective view of the telescopic gear base 6 and the telescopic gear member 8 in a combined state, and the telescopic gear member 8 is positioned with respect to the vehicle body.
- FIG. 4 is a cross-sectional view of the telescopic gear base 6 and the telescopic gear member 8 in a detached state.
- the telescopic gear base 6 has a plurality of teeth (first teeth) 6a on both outer surfaces of a tapered surface that becomes narrower as it is directed downward, and the telescopic gear member 8 is wider as it is applied upward.
- the taper surface has a plurality of teeth (second teeth) 8a at the same pitch on both inner surfaces.
- the taper angle ⁇ of the taper surface of the telescopic gear base 6 and the telescopic gear member 8 is set to be 9 °, but the taper angle is an acute angle of 0 ° or more. I just need it.
- the end of the tooth 6a (the lower end in the figure) of the telescopic gear base 6 has a radius of curvature R2. Contoured at the end of the tooth 8a of the telescopic gear member 8 (upper end in the figure) with a radius of curvature R3 so that the tapered surfaces can be easily fitted together! / ⁇ .
- the ends of the teeth 6a and 8a are contoured with arcs, but the radius of curvature is arbitrary and is not necessarily required. It is also possible to outline with a straight line instead of an arc. In that case, it is desirable to connect the tooth trace and the straight line with an arc having an arbitrary curvature radius.
- the tooth traces of the telescopic gear base 6 and the telescopic gear member 8 are formed in an arc shape having a radius R (FIG. 1) with the clamp rotation axis of the operation lever 5 as the center. Since the telescopic gear member 8 is fixed to the operation lever 5, the movement axis trace of the tooth 8a is an arc. Therefore, by forming the tooth traces of the telescopic gear base 6 and the telescopic gear member 8 in an arc shape having the same radius R, the operation feeling is improved when the teeth 6a and 8a are engaged with each other.
- FIG. 5 is a cross-sectional view of the telescopic gear base 6 and the telescopic gear member 8 from the detached state to the combined state.
- the operation of combining the telescopic gear base 6 and the telescopic gear member 8 will be described.
- the teeth 6a of the telescopic gear base 6 and the teeth 8a of the telescopic gear member 8 facing each other are in a state in which the direction of the tooth traces is opposite (FIG. 5 (a)). .
- the telescopic gear base 6 and the telescopic gear member 8 are engaged with each other immediately before they are engaged with each other (FIG. 5 (a) force is also shown in FIG. 5 (e)), the telescopic gear base 6 And the approaching force of the telescopic gear member 8 is set to be less than 90 degrees, which is greater than 0 degree and less than 90 degrees. In this way, the two members are moved closer together to achieve the combination.
- the telescopic gear member 8 attached to and integrated with the telescopic gear base 6 is engaged with the telescopic gear base 6 by the rotation of the operation lever 5.
- the force applied to the lever 5 directly to the telescopic gear member 8 it is possible to perform a reliable engagement.
- the turning amount force of the operation lever 5 is the combined amount of the telescopic gear base 6 and the telescopic gear member 8, the column body 1 can be securely fixed with a simple structure.
- FIG. 6 is a perspective view showing the relationship between the tilting gear base 7 and the tilting gear member 9.
- the tilting gear base 7 which is easy to explain, is shown in a state of being cut in half. Yes.
- the tilt gear base 7 has a plurality of teeth (first teeth) 7a on both inner surfaces of a tapered surface that becomes narrower as it is directed to the left in the figure, and the tilt gear member 9 is on the right in the figure.
- a plurality of teeth (second teeth) 9a are provided at the same pitch on both outer surfaces of the tapered surface that becomes wider toward the direction.
- the teeth 9a of the tilt gear member 9 begin to mesh from point A in Fig. 6 when they begin to mesh with the teeth 7a of the tilt gear base 7. In other words, it is possible to reduce the incidence of misalignment by causing the teeth 7a and 9a to mesh together with one tooth force and then adjacent teeth to mesh sequentially.
- the angle and shape may be limited. Absent. Such a configuration is equally applicable to the telescopic gear base 6 and the telescopic gear member 8. Can be used. Further, in the present embodiment, the telescopic gear base 6 and the telescopic gear member 8 and the tilt gear base 7 and the tilt gear member 9 are provided only on one side of the column main body 1. By providing the same configuration on both sides, it is possible to double the lock resistance, increase the symmetry, and further stabilize the operation.
- FIG. 7 is a perspective view showing a modified example of the telescopic gear base 6 and the telescopic gear member 8 which are useful for the first embodiment.
- the tooth traces of the teeth 6a of the telescopic gear base 6 and the teeth 8a of the telescopic gear member 8 are made straight rather than arcuate, thereby improving the ease of forming. .
- Such a configuration can be similarly applied to the tilt gear base 7 and the tilt gear member 9.
- FIG. 8 is a cross-sectional view showing a modified example of the telescopic gear base 6 and the telescopic gear member 8 that work on the first embodiment.
- the teeth 6a of the telescopic gear base 6 and the ends (points E and F) of the teeth 8a of the telescopic gear member 8 are not outlined by arcs or straight lines. It has a shape, which increases the ease of molding. Such a configuration can be similarly applied to the tilt gear base 7 and the tilt gear member 9.
- FIG. 9 is a cross-sectional view similar to FIG. 6, showing a modification of the tilting gear base 7 and the tilting gear member 9 that can be applied to the first embodiment.
- Such a configuration can be similarly applied to the telescopic gear base 6 and the telescopic gear member 8.
- FIG. 10 is a flowchart showing a method for manufacturing the telescopic gear base 6 and the telescopic gear member 8 using a method by press molding.
- FIG. 11 is a diagram illustrating the processing states of the telescopic gear member 8 performed using the method by rolling molding in the order of the manufacturing process.
- FIG. 12 is a diagram showing the processing state of the telescopic gear base 6 in the order of the manufacturing process.
- FIG. 13 is a view showing a die for processing the telescopic gear member 8, wherein (a) is a top view thereof and (b) is a side view thereof.
- the first die D1 has a cylindrical shape, and a protrusion Dla continuous in the circumferential direction is formed at the center thereof, and teeth Dlb aligned in the circumferential direction are formed on both sides thereof.
- the second die D2 has a cylindrical shape, and a protrusion D2a continuous in the circumferential direction is formed at the center thereof. However, both sides are cylindrical surfaces.
- FIG. 13 (b) by inserting the plate material B between the dies D1 and D2 that rotate in the opposite direction, a predetermined processing is performed on the plate material B to be produced.
- step S101 of FIG. 11 the long plate material is cut to determine the blank length, and the material B is formed (upper surface). Figure 11 (a)))).
- step S102 the sheet material B is inserted by shifting the center between the dies Dl and D2 shown in FIG. 13 to form the teeth 8a and the grooves 8c and 8d (FIG. 11 (b is a top view). ) And a side view of FIG. 11 (c)))).
- step S103 the end side of the plate material B where the teeth 8a are not formed is bent (see FIG. 11 (d) which is a top view and FIG. 11 (e) which is a side view)). Thereafter, the telescopic gear member 8 is obtained by bending the groove 8c, 8d into a substantially U shape (see FIG. 11 (f) which is a top view and FIG. 11 (g) which is a side view). ).
- step S101 of FIG. 11 the long plate material is cut to determine the blank length, and the material B is formed (in the top view).
- step S102 the sheet material B is inserted with the centers of the dice D1 and D2 shown in FIG. 13 aligned to form the teeth 6a and the grooves 6c and 6c (see FIG. 12 (top view)).
- step S102 the sheet material B is inserted with the centers of the dice D1 and D2 shown in FIG. 13 aligned to form the teeth 6a and the grooves 6c and 6c (see FIG. 12 (top view)).
- Figure 12 (c) which is a side view)).
- step S103 the grooves 6c and 6c facing the plate material B are cut to obtain the telescopic gear base 6 (FIG. 12 (d) which is a top view and a side view). (See Figure 12 (e)).
- the telescopic gear base 6 FIG. 12 (d) which is a top view and a side view).
- two telescopic gear bases 6 are formed at one time. The same applies to the tilt gear base 7 and the tilt gear member 9.
- the gear base or gear member is formed by a sheet metal press, by pressure-pressure powder molding, by injection molding, die casting, thixomolding, or the like, by plastic working Alternatively, any molding method such as molding by cutting may be applied.
- the gear members 8 and 9 are simultaneously moved by the operation lever 5, they may be individually moved by separate operation levers.
- the column body main body or the tilt bracket (on the side fixed to the vehicle body) can be formed with a die force. There is a method of integrally forming a gear when manufacturing by a strike.
- FIG. 14 is a perspective view of a steering column device according to a modification.
- the telescopic gear base 6 and the telescopic gear member 8 are formed by combining teeth 6a and 8a only on one side, respectively, and the tilting gear base 7 and the telescopic gear member 9 are respectively Teeth 7a and 9a are formed and joined only on one side. Teeth can be formed only on one side by combining any one of the telescopic gear base 6 and the telescopic gear member 8, the tilting gear base 7 and the telescopic gear member 9.
- the telescopic gear base 6, the telescopic gear member 8, and the tilt gear base 7 may be formed integrally with the force separately from the column main body 1 and the operation lever 5.
- the tooth surface property approaches that of the flat plate, but even if it is flat, the effect of maintaining the position by friction can be obtained.
- the holding function of the column device works.
- FIG. 15 is a perspective view of a steering column device according to a modification.
- the telescopic gear base 6 is integrated with the column body 1, that is, teeth 6 a are formed on both side surfaces of the column body 1.
- the telescopic gear member 8 has a plate shape with a semi-cylindrical inner peripheral surface that is bolted to the operation lever 5 at one end, and has teeth 8a formed at positions on the inner peripheral surface corresponding to the teeth 6a. Yes.
- the control lever 5 is rotated counterclockwise from the position shown in FIG. 15, the telescopic gear member 8 wraps around the lower half of the column body 1, and the teeth 6a and 8a are engaged with each other. Become.
- FIG. 16 is a perspective view showing a column body of a steering column device according to a modification.
- the column body 1 is formed by a sheet metal press.
- the column body 1 is formed by punching from a flat plate and bending it so as to be rounded in order to ensure ease of molding and light weight.
- the telescopic gear base 6 is integrally formed with one side edge lb of the column body 1, that is, before the sheet metal press, teeth 6a are formed on both sides of the flat side edge lb. Therefore, manufacturing is easy.
- the operating lever 5 can be driven around a shaft 5a movable along a long hole la extending in the axial direction, and teeth (not shown) formed in a part thereof mesh with the teeth 6a.
- the telescopic gear base 6 may be provided on the other side edge lc of the column body 1, or by providing it on both sides, a high holding force can be secured. Regardless of the side edge lb or lc that forms the telescopic gear base 6, both ends of the column body 1 are rounded inward so that a bearing (not shown) that rotatably supports the steering shaft 4 is provided. Since the holding portions ld and Id can be formed, a low-cost steering column device can be provided.
- FIG. 17 is a cross-sectional view of a telescopic gear base 6 and a telescopic gear member 8 that are used in another embodiment.
- the operation lever 5 to which the telescopic gear base 6 is coupled is fixed to the shaft 5a and rotates integrally.
- a rotating cam 5b is attached to the shaft 5a, while a fixed cam 5c is attached to a column body (not shown) so that the rotation angle 5b rotates with respect to the fixed cam 5c according to the rotation of the shaft 5a. It has become.
- the shaft 5a is assumed to be urged rightward by preload in FIG.
- the rotating cam 5b and the fixed cam 5c constitute drive means.
- the center surface of the taper surface on both sides of the telescopic gear base 6 (extending perpendicular to the paper surface) is PL6, and the center surface of the taper surface on both sides of the telescopic gear member 8 (extending perpendicular to the paper surface) If PL8 is PL8, the center planes PL6 and PL8 are displaced in the axial direction of the shaft 5a in the detached state shown in FIG. 17 (a).
- FIG. 18 is a perspective view of one of the teeth 6 a of the telescopic gear base 6.
- the tooth 6 a having a triangular cross section perpendicular to the longitudinal direction preferably but not limited to an isosceles triangle
- has a tapered shape and more specifically, has a cross sectional area of the tooth.
- the tip of the tip is thin and sharply formed. Since the tooth 6a has such a tapered shape, it can be smoothly engaged with the tooth 8a of the telescopic gear member 8. Similarly, the teeth 8a of the telescopic gear member 8 may be tapered. Such a configuration can be similarly applied to the tilt gear base 7 and the tilt gear member 9.
- the tilt 'telescopic steering device is characterized in that the tooth traces are inclined so that the squeezing rate r? Increases due to the force applied at the time of collision.
- the same reference numerals are given to members of the second embodiment similar to the above-described first embodiment, and detailed description thereof is omitted.
- FIG. 19 is a diagram showing the telescopic gear base 6 and the telescopic gear member 8 at a normal time
- FIG. 20 is a diagram showing the telescopic gear base 6 and the telescopic gear member 8 at the time of a collision. .
- FIGS. 19A and 20A are views of the gear base 6 and the gear member 8 as viewed from the side in the vehicle body direction, respectively, and FIGS. 19B and 20B are views of the arrows XIX B and XX B in FIGS. 19A and 20A, respectively.
- 19C and 20C are views taken along arrows XIX C and XX C in FIGS. 19A and 20A, respectively.
- the holding force at this time is F2.
- the telescopic gear base 6 and the telescopic gear member 8 receive a force Fc that relatively moves in the axial direction of the steering shaft 1 (see FIG. 20 (a)).
- the force Fc is a component Fx in the direction along the tooth muscles of the teeth 6a and 8a and It is decomposed into the component Fy in the orthogonal direction.
- the force component Fx is a force that presses the telescopic gear base 6 toward the telescopic gear member 8
- the telescopic gear base 6 is a telescopic gear as shown in FIGS. 20A and 20B. It is pushed into member 8.
- the teeth 6a and 8a are formed on the tapered surfaces of the telescopic gear base 6 and the telescopic gear member 8, the teeth 6a and 8a are pressed toward each other.
- the contact rate 7? "Becomes larger than the normal contact rate 7? '. Therefore, the holding force F3 at the time of collision is higher than the holding force F2 at the normal time.
- the holding force can be increased according to the strength of the impact force, that is, according to the present embodiment, the number of teeth can be reduced.
- ⁇ is set to be 90 degrees or less.
- the tilting gear base 7 and the tilting gear member 9 can similarly provide an angle to the tooth muscles.
- the tooth traces of the telescopic gear base 6 and the telescopic gear member 8 are formed in an arc shape having a radius of curvature R (FIG. 1) centered on a straight force control lever 5. Since the telescopic gear member 8 is fixed to the operation lever 5, the movement axis trace of the tooth 8a has an arc shape. If the tooth traces formed in the arc shape of the telescopic gear base 6 and the telescopic gear member 8 are taken out and the inclination of the tooth traces is in the range of 0 to 90 degrees, the collision will occur. The gear ratio increases with time input. Further, since the tooth traces are arc-shaped, the operation feeling is improved when the teeth 6a and 8a are engaged with each other.
- FIG. 21 and FIG. 22 show a gear structure disclosed in Japanese Patent Laid-Open No. 9-221043 as a gear structure of a conventional steering device, for comparison with a third embodiment to be described later of the present invention.
- the collision force that moves in the direction of the arrow is applied to the column 101, the lever shaft 103, the lever 104, and the gear 105 attached to the lever 10 when the vehicle collides.
- the movement force S of these members 101, 103, 104, 105 is suppressed by the engagement of the gear 106 and the gear 105 attached to the bracket 102.
- an excessive collision force F acts as shown in Fig. 22
- the component force Fa generated by the collision force being decomposed by the friction surface is larger than the friction force Fb generated on the gear surface.
- the lever 104 is separated from the gear 106 together with the gear 105, so that the lever clamp state is released. In other words, the gear engagement itself deviates and the clamped state cannot be maintained.
- the frictional force Fb may be set to be larger than the component force Fa of the collision force.
- the component force Fa F sin a using the apex angle oc
- the half-vertex angle of the gear is generally set to 25 or 30 degrees. If the apex angle of the tooth is set small, the tooth root thickness becomes small and sufficient tooth strength cannot be secured, and the processability of the tooth becomes extremely difficult. Therefore, setting the apex angle of the above gear smaller than the friction angle is not a realistic solution.
- the entire tooth surface is inclined by
- the direction of the tooth trace is inclined by ⁇ degrees with respect to the direction in which the collision force acts.
- the half apex angle of each tooth is ⁇
- the inclination angle of the tooth surface with respect to the meshing direction of the teeth is ⁇ 8
- the tooth trace direction is the collision force direction.
- the angle is defined as ⁇ .
- FIGS. 23 to 23 showing an embodiment in which the inclination angle ⁇ of the tooth trace is 90 °.
- Fig. 23 (b) is a view of the gear member 'gear base viewed from the axial direction of the vehicle body.
- Figure 23 ⁇ is a view from the side of Fig. 23 ⁇ .
- 23C is an enlarged view of the main part of FIG. 23B, and
- FIG. 23D is an enlarged view of the main part of FIG. Fig. 23 ⁇ is a view taken along arrow XXIII in Fig. 23C.
- the entire tooth surfaces of the gear base and the gear member according to the third embodiment are inclined at an angle j8 with respect to the meshing surface.
- the meshing surface is a trajectory formed by the long axis of the gear member when the gear member is moved so that the meshing rate increases after the gear base and the gear member are meshed. It is a surface along.
- the surface P is defined as a surface parallel to the meshing surface and crossing a part of the tooth trace.
- the tooth muscle joint is maintained by the frictional force generated on the line segment appearing on this plane P as described in detail below.
- the point corresponding to the apex of the tooth is a 1 and the two points corresponding to the bottom of the tooth trace are bl and b2, respectively.
- a2 be the point where the surface that passes through the line segment bl-b2 and is perpendicular to the surface P intersects the apex of the tooth trace.
- b be the intersection with surface P on the normal of surface P passing through point a2.
- the half apex angle ⁇ is 1Z2 of the angle bl'c'b2 as shown in Fig. 23E
- the inclination angle ⁇ of the tooth surface is the angle b'al'a2 as seen in Fig. 23C. It is represented by
- the angle ⁇ is defined as the angle between the line segment a 1-bl and the collision direction.
- the angle ⁇ can be said to be an angle formed by the direction in which the frictional force acts and the direction of the collision force.
- This angle ⁇ is a parameter that defines the difficulty of gear removal as described later.
- a point where the normal of the line segment al-a2 passing through the point b intersects the line segment al-a2 is defined as a point c. Furthermore, for the following explanation, the side defined by points al and b is side A, the side defined by points bl and b is side B, and the side defined by points b and c is side C. Express.
- FIG. 24 is a diagram corresponding to FIG. 23D.
- the tooth traces in Fig. 24 tilted (90 °- ⁇ ) degrees in the direction in which the teeth mesh together from the tooth traces in Fig. 23D, so the line segment al-bl, the direction in which the frictional force acts, collides.
- the angle formed with the direction is ⁇ + (90 ° — ⁇ ) degrees.
- - ⁇ + (90 °- ⁇ ) ⁇ tan (tan ⁇ ⁇ sin j8)-(90 ° — ⁇ )
- Table 1 shows an example where ⁇ , j8, and ⁇ are maintained with and without being maintained in the third embodiment.
- the tooth trace direction is inclined by ⁇ degrees to increase the meshing rate r? Furthermore, by defining an inclination angle of
- gear A and gear B are relative to each other in the collision force direction or the normal direction of the engagement direction. Easy to displace. That is, the gear meshing rate drops and eventually the gear meshing is lost. In order to prevent this, it is necessary to increase the rigidity of each member of the steering device in order to prevent relative displacement between the gear A and the gear B. However, it is almost impossible to meet these requirements.
- the tooth surface angles ⁇ , j8, ⁇ , and 0 are set by a certain three-dimensional relational expression so that 0 does not exceed the friction angle. By doing so, it is possible to prevent a decrease in the length of meshing in the direction of the tooth traces and a decrease in the rate of meshing. As a result, there is an effect that the teeth that are meshed do not come off even when an excessive load is applied.
- the present invention has been described in detail with reference to the embodiments, the present invention should not be construed as being limited to the above-described embodiments, but may be changed or modified as appropriate without departing from the spirit of the invention.
- the combination of the gear base and the gear member may be arbitrary even if they have the opposite configuration.
- the steering device may be configured by combining the first to fourth embodiments described above.
- the first tooth and the second tooth are in directions other than the normal direction and the tangential direction (including directions parallel to the tangent line) with respect to the respective tooth traces. Since it is made to approach and unite along the direction, the incompatibility of the 1st tooth and the 2nd tooth can be controlled. Accordingly, it is possible to avoid the deterioration of the operation feeling as in the case of using a multi-plate friction plate, and further, after the first teeth and the second teeth are engaged, a large holding force can be exhibited. In particular, when the first tooth and the second tooth are first meshed, the meshing rate can be increased by sliding the two teeth in the direction of the tooth trace and increasing the meshing rate.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Steering Controls (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP06745970.1A EP1884444B1 (en) | 2005-05-06 | 2006-05-01 | Steering column device |
US11/913,760 US7810409B2 (en) | 2005-05-06 | 2006-05-01 | Steering column apparatus |
JP2007528253A JP5061900B2 (ja) | 2005-05-06 | 2006-05-01 | ステアリングコラム装置 |
Applications Claiming Priority (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2005134974 | 2005-05-06 | ||
JP2005-134974 | 2005-05-06 | ||
JP2005143434 | 2005-05-17 | ||
JP2005-143434 | 2005-05-17 | ||
JP2006072616 | 2006-03-16 | ||
JP2006-072616 | 2006-03-16 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2006120968A1 true WO2006120968A1 (ja) | 2006-11-16 |
Family
ID=37396477
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2006/309119 WO2006120968A1 (ja) | 2005-05-06 | 2006-05-01 | ステアリングコラム装置 |
Country Status (4)
Country | Link |
---|---|
US (1) | US7810409B2 (ja) |
EP (1) | EP1884444B1 (ja) |
JP (1) | JP5061900B2 (ja) |
WO (1) | WO2006120968A1 (ja) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
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JP2008137393A (ja) * | 2005-11-21 | 2008-06-19 | Nsk Ltd | ステアリングコラム装置 |
JP2008230452A (ja) * | 2007-03-22 | 2008-10-02 | Nsk Ltd | ステアリングコラム装置 |
US8359144B2 (en) * | 2010-11-01 | 2013-01-22 | GM Global Technology Operations LLC | Driveline lash management in powertrain systems |
WO2015016311A1 (ja) * | 2013-07-31 | 2015-02-05 | 株式会社ジェイテクト | ステアリング装置 |
Families Citing this family (11)
Publication number | Priority date | Publication date | Assignee | Title |
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DE102005036582A1 (de) * | 2005-08-01 | 2007-02-08 | Thyssenkrupp Presta Ag | Verstellbare Lenksäule für ein Kraftfahrzeug |
GB0723485D0 (en) * | 2007-11-30 | 2008-01-09 | Trw Das A S | Adjustable steering column assembly |
FR2932143B1 (fr) * | 2008-06-04 | 2011-09-02 | Zf Systemes De Direction Nacam Sas | Colonne de direction reglable amelioree pour vehicules automobiles |
CN102762277A (zh) * | 2009-12-18 | 2012-10-31 | 斯凯约尼克公司 | 通过形成ii族碳酸盐和二氧化硅的二氧化碳固定 |
CN102905951B (zh) * | 2011-03-31 | 2015-05-13 | 日本精工株式会社 | 转向柱装置 |
DE102011054606B3 (de) | 2011-10-19 | 2013-02-28 | Thyssenkrupp Presta Aktiengesellschaft | Lenkspindellagereinheit zur drehbaren Lagerung einer Lenkspindel |
DE102011054598B3 (de) | 2011-10-19 | 2013-01-17 | Thyssenkrupp Presta Ag | Lenkspindellagereinheit zur drehbaren Lagerung einer Lenkspindel |
DE102011054597A1 (de) * | 2011-10-19 | 2013-04-25 | Thyssenkrupp Presta Aktiengesellschaft | Lenkspindellagereinheit |
DE102011056674B3 (de) | 2011-10-19 | 2012-12-06 | Thyssenkrupp Presta Aktiengesellschaft | Lenksäule für ein Kraftfahrzeug |
US9352769B2 (en) * | 2013-04-24 | 2016-05-31 | Nsk Ltd. | Steering apparatus |
JP6304542B2 (ja) * | 2014-06-20 | 2018-04-04 | 株式会社ジェイテクト | ステアリング装置 |
Citations (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0616171U (ja) * | 1992-08-06 | 1994-03-01 | 日本精工株式会社 | チルト式ステアリング装置 |
JPH0683558U (ja) * | 1993-05-19 | 1994-11-29 | 光洋精工株式会社 | チルトステアリング装置 |
JPH07232649A (ja) * | 1994-02-25 | 1995-09-05 | Fuji Kiko Co Ltd | 車両用ステアリング装置 |
JPH0811725A (ja) * | 1994-06-30 | 1996-01-16 | Fuji Kiko Co Ltd | 車両用ステアリングコラム |
JPH0820347A (ja) * | 1994-07-04 | 1996-01-23 | Nippon Seiko Kk | チルト式ステアリングコラム装置 |
JPH09221043A (ja) * | 1996-02-16 | 1997-08-26 | Nippon Seiko Kk | チルト式ステアリング装置 |
JPH1035511A (ja) | 1996-04-18 | 1998-02-10 | Etab Supervis | 自動車用ステアリングコラム |
US6419269B1 (en) | 1999-09-20 | 2002-07-16 | Delphi Technologies | Locking system for adjustable position steering column |
DE10212263A1 (de) | 2002-03-20 | 2003-10-02 | Daimler Chrysler Ag | Verriegelungsvorrichtung für zwei relativ zueinander verschiebbare Komponenten |
DE10234514B3 (de) | 2002-07-30 | 2004-01-29 | Nacam Deutschland Gmbh | Positionseinstellvorrichtung für Kraftfahrzeuglenksäulen |
JP2004291782A (ja) * | 2003-03-26 | 2004-10-21 | Toyota Motor Corp | 車両用ステアリング装置の摩擦式チルトロック構造 |
JP2005001444A (ja) * | 2003-06-10 | 2005-01-06 | Toyota Motor Corp | 衝撃吸収式ステアリングコラム装置 |
US20050016315A1 (en) | 2003-07-21 | 2005-01-27 | Hubert Breuss | Locking device of a steering column adjustable in at least one adjustment direction |
Family Cites Families (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5943169Y2 (ja) * | 1980-01-28 | 1984-12-20 | 日野自動車株式会社 | テイルトステアリング装置 |
JPS60144569U (ja) * | 1984-03-07 | 1985-09-25 | 日本精工株式会社 | チルト式ステアリング装置 |
US4941766A (en) * | 1986-12-19 | 1990-07-17 | Teleflex Incorporated | Tilt wheel universal |
JPH0394373U (ja) * | 1990-01-19 | 1991-09-26 | ||
GB2281539A (en) * | 1993-09-01 | 1995-03-08 | Torrington Co | Adjustable vehicle steering column assembly |
JP3517453B2 (ja) * | 1994-09-30 | 2004-04-12 | 富士機工株式会社 | 車両用ステアリングコラム |
JPH08268299A (ja) * | 1995-03-31 | 1996-10-15 | Nissan Shatai Co Ltd | チルト式ステアリング装置のステアリングコラム支持構造 |
JP3772582B2 (ja) * | 1999-03-29 | 2006-05-10 | 日本精工株式会社 | チルト式ステアリング装置 |
JP2000289628A (ja) * | 1999-04-12 | 2000-10-17 | Nsk Ltd | チルト・テレスコ式ステアリング装置 |
JP2000344115A (ja) * | 1999-06-04 | 2000-12-12 | Fuji Kiko Co Ltd | 車両用ステアリングコラム |
US6481310B2 (en) * | 2000-04-24 | 2002-11-19 | Delphi Technologies, Inc. | Fine increment tilt mechanism |
JP2003118595A (ja) * | 2001-08-06 | 2003-04-23 | Nsk Ltd | 車両用ステアリング装置及びその製造方法 |
US7069809B2 (en) * | 2001-12-27 | 2006-07-04 | Nsk, Ltd. | Vehicle tilt type steering device |
US6851332B2 (en) * | 2002-11-08 | 2005-02-08 | Daimlerchrysler Corporation | Cam lock tilt cartridge |
JP4212936B2 (ja) * | 2003-03-19 | 2009-01-21 | 日本精工株式会社 | エネルギー吸収式ステアリングコラム |
-
2006
- 2006-05-01 US US11/913,760 patent/US7810409B2/en not_active Expired - Fee Related
- 2006-05-01 EP EP06745970.1A patent/EP1884444B1/en not_active Expired - Fee Related
- 2006-05-01 JP JP2007528253A patent/JP5061900B2/ja active Active
- 2006-05-01 WO PCT/JP2006/309119 patent/WO2006120968A1/ja active Application Filing
Patent Citations (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0616171U (ja) * | 1992-08-06 | 1994-03-01 | 日本精工株式会社 | チルト式ステアリング装置 |
JPH0683558U (ja) * | 1993-05-19 | 1994-11-29 | 光洋精工株式会社 | チルトステアリング装置 |
JPH07232649A (ja) * | 1994-02-25 | 1995-09-05 | Fuji Kiko Co Ltd | 車両用ステアリング装置 |
JPH0811725A (ja) * | 1994-06-30 | 1996-01-16 | Fuji Kiko Co Ltd | 車両用ステアリングコラム |
JPH0820347A (ja) * | 1994-07-04 | 1996-01-23 | Nippon Seiko Kk | チルト式ステアリングコラム装置 |
JPH09221043A (ja) * | 1996-02-16 | 1997-08-26 | Nippon Seiko Kk | チルト式ステアリング装置 |
JPH1035511A (ja) | 1996-04-18 | 1998-02-10 | Etab Supervis | 自動車用ステアリングコラム |
US6419269B1 (en) | 1999-09-20 | 2002-07-16 | Delphi Technologies | Locking system for adjustable position steering column |
DE10212263A1 (de) | 2002-03-20 | 2003-10-02 | Daimler Chrysler Ag | Verriegelungsvorrichtung für zwei relativ zueinander verschiebbare Komponenten |
DE10234514B3 (de) | 2002-07-30 | 2004-01-29 | Nacam Deutschland Gmbh | Positionseinstellvorrichtung für Kraftfahrzeuglenksäulen |
JP2004291782A (ja) * | 2003-03-26 | 2004-10-21 | Toyota Motor Corp | 車両用ステアリング装置の摩擦式チルトロック構造 |
JP2005001444A (ja) * | 2003-06-10 | 2005-01-06 | Toyota Motor Corp | 衝撃吸収式ステアリングコラム装置 |
US20050016315A1 (en) | 2003-07-21 | 2005-01-27 | Hubert Breuss | Locking device of a steering column adjustable in at least one adjustment direction |
Non-Patent Citations (1)
Title |
---|
See also references of EP1884444A4 |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2008137393A (ja) * | 2005-11-21 | 2008-06-19 | Nsk Ltd | ステアリングコラム装置 |
US8011268B2 (en) * | 2005-11-21 | 2011-09-06 | Nsk Ltd. | Steering column system |
JP2008230452A (ja) * | 2007-03-22 | 2008-10-02 | Nsk Ltd | ステアリングコラム装置 |
US8359144B2 (en) * | 2010-11-01 | 2013-01-22 | GM Global Technology Operations LLC | Driveline lash management in powertrain systems |
WO2015016311A1 (ja) * | 2013-07-31 | 2015-02-05 | 株式会社ジェイテクト | ステアリング装置 |
Also Published As
Publication number | Publication date |
---|---|
EP1884444B1 (en) | 2017-03-08 |
US7810409B2 (en) | 2010-10-12 |
JP5061900B2 (ja) | 2012-10-31 |
EP1884444A4 (en) | 2012-06-06 |
EP1884444A1 (en) | 2008-02-06 |
US20090044656A1 (en) | 2009-02-19 |
JPWO2006120968A1 (ja) | 2008-12-18 |
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