JP2007091171A - Electric tilt type telescopic steering column - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a reducer means of change-over structure simple in output to a tilt shaft or a telescopic shaft. <P>SOLUTION: This device is provided with a planetary gear mechanism comprising a first rotating body 51 that is rotatable having a first shaft 51a, a second rotating body 52 that is rotatable having a second shaft that is coaxial with the first shaft 51a, a plurality of third rotating bodies engaged with both the first rotating body 51 and the second rotating body 52, and a rotation support frame 56 that is rotatable having a third shaft 53a that is coaxial with the first shaft and the second shaft while supporting a third rotating body 53 to be rotatable. Next, a fourth rotating body 54 and a fourth shaft 54a are provided to be engaged with external teeth 52q of the second rotating body 52. One of the first, the third, and fifth shafts 51a, 53a, and 55a is set as an input shaft, and the other two shafts are set as a pair of output shafts connected to the tilt shaft and the telescopic shaft, respectively. Lock means 6 and 7 are provided to lock either of the pair of the output shafts. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to an electric tilt telescopic steering column that facilitates a mechanism for switching transmission of driving force from a single motor to a tilt shaft or a telescopic shaft.

  An automobile uses an electric tilt telescopic steering column in which a tilt mechanism and a telescopic mechanism are operated by an electric motor. As a tilt mechanism in the electric tilt telescopic steering column, a tilt hinge is provided on the proximal side near the steering wheel, and a part of the steering shaft and a support part covering the part of the steering shaft are configured to be refracted by the tilt hinge part. In some cases, a tilt hinge is provided at the foot and the entire steering shaft is refracted at the tilt hinge.

An example of a conventional electric tilt telescopic steering column is disclosed in Patent Document 1. In this system, a tilt hinge is provided on the hand side, the screw shaft of the tilt mechanism and the screw shaft of the telescopic mechanism are individually arranged below the steering shaft, and the driving force from a single motor is transmitted by the transmission mechanism. It decelerates and switches the output to one of the two screw shafts.
JP-A-4-231263

  However, since this switching is configured to switch the meshing gears, the structure becomes complicated and the size increases.

  Accordingly, an object of the present invention is to provide an electric tilt telescopic steering column in which the above-described problems are solved and the structure of the switching mechanism is simplified.

  The invention according to claim 1 is a steering shaft that transmits a steering force input from the steering wheel to the steering wheel, a support member that rotatably supports the steering shaft, and a support member that is rotatably supported by the support member. A tilt shaft for tilting the steering wheel, a telescopic shaft that is rotatably supported by the support member and telescopically the steering wheel, a single motor, and a rotational force from the motor are input. In addition, in the electric tilt telescopic steering column provided with a reduction means for outputting to either the tilt axis or the telescopic axis, the first rotary body having a first axis as the reduction means, and the first axis A rotatable second rotating body having a second axis coaxial with the first rotating body and the second rotating body A plurality of third rotating bodies that mesh or roll in contact with each other, and a rotatable rotation that rotatably supports the third rotating body and has a third axis that is coaxial with the first and second axes. A three-axis reduction mechanism having a support frame, wherein any one of the first to third axes is an input shaft, and the remaining two axes are a pair of output shafts connected to the tilt shaft and the telescopic shaft, Locking means for locking any one of the pair of output shafts is provided.

  According to this invention, the rotation of the motor is transmitted to the speed reduction means via the input shaft, and after being decelerated by the speed reduction means, is transmitted to both the tilt axis and the telescopic shaft via the pair of output shafts. Therefore, by locking either one of the pair of output shafts by the locking means, either the tilt shaft or the telescopic shaft can be locked and the other can be selectively rotated. That is, the tilt axis or the telescopic axis can be selectively rotated by a single motor.

  According to a second aspect of the present invention, in the electric tilt telescopic steering column according to the first aspect, the fourth shaft is in mesh with or in rolling contact with the outer peripheral surface of the second rotating body, and is substantially parallel to the first to third shafts. A rotatable fourth rotating body is provided, and the fourth shaft is used as the input shaft or the output shaft instead of the second shaft.

  According to the present invention, one of the three axes of the first and third axes that are coaxial and the fourth axis that is substantially parallel to these two axes serves as the input shaft, and the remaining two axes Is a pair of output shafts.

  According to a third aspect of the present invention, in the electric tilt telescopic steering column according to the first aspect, the outer peripheral surface of the second rotating body meshes with a bevel gear or a worm / worm wheel, and is substantially perpendicular to the first to third axes. A rotatable fifth rotating body having a fifth shaft is provided, and the fifth shaft is used as the input shaft or the output shaft instead of the second shaft.

  According to the present invention, one of the three axes of the first and third axes that are coaxial and the fifth axis that is substantially perpendicular to these two axes serves as the input shaft, and the remaining two axes Is a pair of output shafts.

  According to a fourth aspect of the present invention, in the electric tilt telescopic steering column according to any one of the first to third aspects, the speed reduction means includes a rolling outer peripheral surface provided on the first rotating body, and the second rotation. The body is provided with a rolling inner peripheral surface, and the third rotating body comprising a gear or a roller that is rotatable around a turning axis substantially parallel to the first axis is formed by the rolling outer peripheral surface and the rolling inner peripheral surface. It is a planetary mechanism that is sandwiched between surfaces and rotates by meshing or rolling contact.

  According to this invention, the three-axis reduction mechanism constitutes a planetary gear mechanism using a gear or a planetary roller mechanism using a roller, and the first rotating body is a rotating body such as a sun gear positioned in the center, The second rotating body is a plurality of rotating bodies such as an internal gear positioned on the outer peripheral side, and the third rotating body is a rotating body such as a planetary gear positioned between the sun gear and the internal gear.

  According to a fifth aspect of the present invention, in the electric tilt telescopic steering column according to any one of the first to third aspects, the reduction means is provided on an outer peripheral surface of the first rotating body and an outer peripheral surface of the second rotating body, respectively. The third rotating body comprising a bevel gear provided with a bevel tooth and rotatable around a turning shaft arranged along a radial direction of the rotation support frame is the bevel tooth of the first rotating body and the second rotating body. It is a differential gear mechanism that meshes with both.

  According to the present invention, the three-axis reduction mechanism constitutes a differential gear mechanism using gears, the first rotating body is a bevel gear integrated with the left shaft of the vehicle body, and the second rotating body is the right shaft of the vehicle body. And the third rotating body is a plurality of bevel gears provided in the differential case.

  According to a sixth aspect of the present invention, in the electric tilt telescopic steering column according to any one of the first to third aspects, the speed reducing means rolls on the side surface of the first rotating body and the side surface of the second rotating body, respectively. The third rotating body, which is provided with a side surface and is rotatable about a pivot axis arranged along the radial direction of the rotation support frame, is a roller side surface of the first rotating body and the second rotating body. It is a differential roller mechanism sandwiched between and in contact with rolling.

  According to the present invention, the three-axis reduction mechanism constitutes a differential roller mechanism using a roller, the first rotating body is a disk integrated with the left shaft, and the second rotating body is a disk integrated with the right shaft. The third rotating body is a plurality of rollers provided in the differential case.

  According to the electric tilt telescopic steering column according to the present invention, since the three-axis reduction mechanism having one input shaft and two output shafts is used as the reduction means, the planetary gear mechanism and the differential gear mechanism, which are existing reduction mechanisms, are used. Can be used. In addition, when tilting or telescopic with a single motor, it is possible to switch the output to the tilt axis or telescopic axis only by providing a locking means for locking either of the two output shafts, and the structure of the switching mechanism Is simple.

Embodiments of an electric tilt telescopic steering column according to the present invention will be described below. Embodiments 1 and 2 show a case in which a tilt hinge is provided at the foot to tilt the entire steering shaft, and Embodiment 1 swings a tilt nut that is linearly moved by being screw-coupled to the tilt shaft. In this embodiment, the swing lever is swung by being connected to the tip of the moving lever via a link. In the second embodiment, the spur gear provided on the tilt shaft is formed on the arc surface of the tip of the swing lever. In this configuration, the rocking lever is directly rocked by meshing with the teeth.
(A) Embodiment 1
First, the first embodiment will be described. A front view of the electric tilt telescopic steering column is shown in FIG. 2, a bottom view is shown in FIG. 3, and a perspective view of the speed reducer is shown in FIG.

  As shown in FIG. 2, a lower shaft 1 connected to a steering wheel (not shown) and an upper shaft 2 connected to a steering wheel (not shown) are connected to each other so as to be relatively movable in the axial direction by a spline connection (not shown). A telescopic steering shaft 15 is configured. A universal joint (not shown) is provided at the left end of the lower shaft 1 so that it can be bent.

  A housing 5 is provided as a first support member that rotatably supports the lower shaft 1. A protrusion is formed on the upper portion of the housing 5 on the side of the steering wheel so as to protrude, and a tilt hinge hole 5a is formed in the protrusion so as to be swingably coupled to the vehicle body via a bolt (not shown). . This bolt becomes a tilt hinge.

  A jacket tube 11 is provided as a second support member that rotatably supports the upper shaft 2. The jacket tube 11 has a cylindrical shape, and a bearing (not shown) is provided between the vicinity of both ends of the jacket tube 11 and the upper shaft 2.

  The jacket tube 11 is provided so as to be movable in the axial direction of the steering shaft 15 with respect to the housing 5. That is, it is configured as follows. One end of the jacket tube 11 is inserted into the housing 5, and adjustment means (not shown) is provided for adjusting the play and slidability between the housing 5 and the jacket tube 11. Further, the jacket tube 11 can move relatively in the axial direction without rotating in the circumferential direction with respect to the housing 5.

  Next, a configuration for swinging the housing 5 up and down around the tilt hinge hole 5a in order to tilt a steering wheel (not shown) will be described. On both sides of the right end of the housing 5, a substantially triangular swing arm 19 is disposed. A first apex portion 19 a that is a base end portion of the swing arm 19 is coupled to a side surface of the housing 5 via a bolt 20 so as to be swingable. The second apex portion 19b, which is one tip of the swing arm 19, is in a position that swings in the vertical direction with respect to the first apex portion 19a, and the second apex portion 19b swings on a bracket 21 attached to the vehicle body. It is connected freely. That is, the shaft support portion 21a protruding downward from both ends of the bracket 21 and the second apex portion 19b of the swing arm 19 disposed inside the shaft support portion 21a are coupled so as to be swingable.

  A coupling structure between the shaft support portion 21a and the swing arm 19 will be described below. When the housing 5 swings around the tilt hinge hole 5 a, the portion of the bolt 20 screwed into the housing 5 swings around the tilt hinge hole 5 a and the joint between the bracket 21 and the swing arm 19. If the connecting portion is simply bolted, the distance between the axes of the connecting portion of the bracket 21 and the bolt 20 will be different during the swinging. Can no longer swing. For this reason, in order to absorb the increase / decrease in the distance between the shafts during the swinging and ensure the connection and the swinging, the shaft support portion 21a is connected to the first of the swinging arm 19 via the link 24 as the shaft distance variation absorbing means. It is connected to the two vertex portions 19b. Bolts 25 are used to connect both ends of the link 24.

  By swinging the swing arm 19 around the bolt 20, the housing 5 is moved up and down as a result, and as a result, the other end of the swing arm 19 is swung around the tilt hinge hole 5a. The third vertex portion 19c, which is a portion, is positioned so as to swing in the left-right direction with respect to the first vertex portion 19a, and is used for swinging the position of the third vertex portion 19c in the left-right direction in FIG. A mechanism is provided. That is, the tilt shaft 26 is supported on the lower portion of the housing 5 so as to be rotatable and substantially parallel to the axis of the steering shaft 15.

  The tilt shaft 26 is rotatably supported at one end vicinity by a shaft support portion 5d integral with the housing 5 via a bearing (not shown), and the other end of the tilt shaft 26 is provided with a driving means 3 fixed to the housing 5. Via the motor 29. A male screw is formed on the outer peripheral surface of the tilt shaft 26, and a tilt nut 32 is screwed to the tilt shaft 26. For this reason, when the tilt shaft 26 rotates, the tilt nut 32 moves along the axis of the tilt shaft 26.

  While the tilt nut 32 moves linearly in the left-right direction, the third apex portion 19c of the swing arm 19 moves while drawing an arc centered on the bolt 20, so if both are simply bolted together, Because the distance between the axes of the different, it does not move smoothly. For this reason, the tilt nut 32 and the third apex portion 19c of the swing arm 19 are connected via a link 33 as an inter-axis distance fluctuation absorbing means. That is, one end of the link 33 is swingably coupled to both side surfaces of the tilt nut 32 via the bolt 34, and the other end of the link 33 is connected to the third vertex 19 c of the swing arm 19 via the bolt 35. It is coupled so that it can swing.

  On the other hand, as shown in FIG. 3, a telescopic shaft 36 is provided substantially parallel to the axis of the steering shaft 15, and the telescopic shaft 36 is arranged in parallel with the tilt shaft 26. That is, a telescopic nut 42 is fixed to the shaft support portion 11 a of the jacket tube 11, one end of the telescopic shaft 36 is screwed to the telescopic nut 42, and the other end of the telescopic shaft 36 is also connected to the motor 29 via the driving means 3. It is connected to.

  As described above, the other ends of the tilt shaft 26 and the telescopic shaft 36 are connected to the single motor 29 via the speed reduction means 3, and the motor 29 and the speed reduction means 3 are coupled to the housing 5. . The speed reduction means 3 includes a first speed reduction means 3a and a second speed reduction means 3b, and a general known speed reduction means is used as the first speed reduction means 3a. As the second reduction means 3b, the one having the following configuration is used.

  In this Embodiment 1, the thing using the planetary gear mechanism is employ | adopted as a 3 axis | shaft reduction mechanism which comprises a reduction means. The configuration of the speed reduction means will be described below. As shown in FIG. 1, the speed reduction means includes a rotatable first rotating body (sun gear) 51 having a first shaft 51a, and a rotatable second shaft having a second shaft (not shown) coaxial with the first shaft 51a. The rotating body (internal / external gear) 52 meshes with both the rolling outer peripheral surface (external teeth) 51p of the first rotating body 51 and the rolling inner peripheral surface (internal teeth) 52p of the second rotating body 52. A plurality of third rotating bodies (planetary gears) 53 rotatable around a turning shaft 53b substantially parallel to the first shaft 51a, and the third rotating body 53 are rotatably supported and the first shaft 51a, A planetary gear mechanism is constituted by a rotatable rotation support frame 56 having a third shaft 53a coaxial with the second shaft.

  In the present embodiment, in the planetary gear mechanism described above, a fourth rotating body (flat surface) that meshes with the external teeth 52q of the second rotating body 52 and has a fourth shaft 54a substantially parallel to the first shaft 51a and the third shaft 53a. Gear) 54 is rotatably provided, and a fourth shaft 54a is used as an input shaft or an output shaft instead of a second shaft (not shown) of the second rotating body 52.

In the present embodiment, the first shaft 51a among the three shafts of the first shaft 51a, the third shaft 53a, and the fourth shaft 54a is an input shaft connected to the first speed reduction means 3a, and the remaining two shafts Of these, the third shaft 53 a is an output shaft connected to the telescopic shaft 36, and the fourth shaft 54 a is an output shaft connected to the tilt shaft 26.

  In order to lock one of the two output shafts, the third shaft 53a and the fourth shaft 54a, as shown in FIG. 1, the third shaft 53a and the fourth shaft 54a are provided with locking means 6 and 7, respectively. Is provided. The lock means 6 and 7 can move the lock gear 8 fixed to the third shaft 53a and the fourth shaft 54a and having teeth 8a, and the rod 9a engaged with the lock gear 8 by opening and closing the energizing circuit. The solenoid 9 is provided.

  Next, the operation of the electric tilt telescopic steering column will be described.

  In FIG. 2, in order to tilt a steering wheel (not shown), the solenoid 9 of the lock means 6 is energized to cause the rod 9a to protrude, the rod 9a is engaged with the lock gear 8, and the rotation of the third shaft 53a is locked. . Next, the output shaft of the motor 29 is rotated in either direction. Then, the rotational movement of the output shaft of the motor 29 is decelerated via the first reduction means 3a and the second reduction means 3b. The rotational force is input from the first shaft 51a to the second reduction means 3b and is output from the third shaft 53a and the fourth shaft 54a, but the third shaft 53a is locked, so the fourth shaft The tilt shaft 26, which is output only from 54a and connected to the fourth shaft 54a, rotates.

  When the tilt shaft 26 of FIG. 2 rotates, the tilt nut 32 moves along the tilt shaft 26, and the movement of the tilt nut 32 is transmitted to the third vertex portion 19 c of the swing arm 19 via the link 33, and the swing arm 19 swings in either direction around the bolt 20. Then, the second vertex portion 19b of the swing arm 19 moves up or down. This means that the position of the bolt 20 of the swing arm 19 moves up and down with respect to the bracket 21 fixed to the vehicle body, and the housing 5 coupled to the swing arm 19 via the bolt 20 is connected to the tilt hinge hole. It swings up and down around 5a. As a result, the entire steering shaft 15 swings in the vertical direction, and a steering wheel (not shown) tilts.

  Next, in order to telescopically steer a steering wheel (not shown in FIG. 2), the output shaft of the motor 29 is turned on while the rotation of the fourth shaft 54a is locked by energizing the solenoid 9 of the lock means 7 in FIG. Rotate in one direction. Then, the rotational movement of the output shaft of the motor 29 is decelerated via the first reduction means 3a and the second reduction means 3b. The rotational force is input from the first shaft 51a to the second reduction means 3b and is output from the third shaft 53a and the fourth shaft 54a, but the fourth shaft 54a is locked, so the third shaft The telescopic shaft 36 which is output only from 53a and connected to the third shaft 53a rotates.

When the telescopic shaft 36 rotates, the telescopic shaft 36 is screwed into the telescopic nut 42 in FIG. 3, and the jacket tube 11 moves relative to the housing 5 in the axial direction as the telescopic shaft 36 rotates. As a result, the upper shaft 2 moves in the axial direction, and the steering wheel telescopes.
(B) Embodiment 2
Next, a second embodiment will be described. Since the basic configuration is shown in the first embodiment, parts having the same functions as those in the first embodiment are denoted by the same reference numerals and will be described with reference to FIGS.

  As shown in FIG. 6, as in the first embodiment, the jacket tube 11 is movable along the axial direction with respect to the housing 5, and the interior of the jacket tube 11 with respect to the lower shaft 1 inside the housing 5. The upper shaft 2 is also movable along the axial direction.

  First, a configuration for tilting the steering wheel will be described. In this embodiment, as in the first embodiment, a substantially triangular swing arm 19 is provided between the bracket 21 fixed to the vehicle body and the housing 5 that supports the lower shaft 1. That is, the first vertex 19 a of the swing arm 19 is coupled to the housing 5 so as to be swingable via the bolt 30, and the second vertex 19 b is coupled to the bracket 21 via the link 24. As shown in FIG. 5, the swing arm 19 is formed with an arc portion 19 </ b> P centered on the bolt 30, and teeth are formed along the arc portion 19 </ b> P. A spur gear 60 connected to the motor 29 via the driving means 3 is engaged with the arc portion 19P.

  Next, a configuration for telescoping the steering wheel will be described. This configuration is also the same as that of the first embodiment. As shown in FIG. 6, a telescopic nut 42 is fixed to the shaft support portion 11a of the jacket tube 11, and the steering shaft 15 is connected to the telescopic nut 42 in a threaded manner. One end of a telescopic shaft 36 substantially parallel to the axis is supported. A motor 29 is connected to the other end of the telescopic shaft 36 via the driving means 3.

  As described above, the swing arm 19 and the telescopic shaft 36 are coupled to the single motor 29 via the speed reduction means 3, and the motor 29 and the speed reduction means 3 are coupled to the housing 5. The speed reduction means 3 includes a first speed reduction means 3a and a second speed reduction means 3b, and a general speed reducer is used as the first speed reduction means 3a. And the thing of the structure shown below is used as the 2nd deceleration means 3b.

  In the first embodiment, as shown in FIG. 1, the fourth shaft 54 a uses the speed reducing means that is substantially parallel to the first shaft 51 a and the third shaft 53 a, but in the second embodiment, the configuration shown in FIG. 4 is used. Use deceleration means. That is, in order to output to the arcuate surface 19P of the swing arm 19 in FIG. 6, instead of the fourth shaft 54a in the first embodiment, a fifth shaft 55a substantially perpendicular to the first shaft 51a and the third shaft 53a. It has. Other configurations are the same as those in FIG.

  The structure of this deceleration means will be described in detail with reference to FIG. This speed reduction means is rotatable with a first shaft 51a and a fifth shaft 55a substantially perpendicular to the third shaft 53a so that a bevel tooth 52t is formed on the outer peripheral surface of the second rotating body 52 and meshes with the bevel tooth 52t. A fifth rotating body (bevel gear) 55 is provided, and the fifth shaft 55a is used as an input shaft or an output shaft. The fifth shaft 55a is also provided with a lock means 7.

  As shown in FIG. 5, the fifth shaft 55 a is provided with a spur gear 60, and the spur gear 60 meshes with the teeth of the arcuate surface 19 </ b> P of the swing arm 19. Here, the spur gear 60 is directly attached to the fifth shaft 55a. However, the fifth shaft 55a is not only the output shaft but also the tilt shaft. Is provided.

  In order to oscillate the third apex portion 19c of the oscillating arm 19, in the first embodiment, the linear motion of the tilt nut is converted into the arc motion of the third apex portion 19c. However, in the second embodiment, since the power is transmitted by the gear, the inter-shaft distance fluctuation absorbing member is not required.

  Next, the operation of the electric tilt telescopic steering column will be described.

  In FIG. 6, in order to tilt a steering wheel (not shown), the output shaft of the motor 29 is rotated in either direction while the solenoid 9 of the lock means 6 is energized to lock the rotation of the third shaft 53a. Then, the fifth shaft 55a of the second reduction means 3b rotates, and the rotational motion of the fifth shaft 55a is transmitted to the swing arm 19 through the spur gear 60 and the teeth of the arc portion 19P, and the swing arm 19 is It swings around the bolt 20. As the swing arm 19 swings, the position of the second apex portion 19b of the swing arm 19 swings in the vertical direction, so that the housing 5 swings in the vertical direction about the tilt hinge hole 5a. The steering wheel tilts.

  In FIG. 6, in order to telescope a steering wheel (not shown), the output shaft of the motor 29 is rotated in any direction while the solenoid 9 of the lock means 7 is energized to lock the rotation of the fifth shaft 55a. Then, the third shaft 53a of the second reduction means 3b rotates, the rotational movement of the third shaft 53a is transmitted to the telescopic shaft 36, and the telescopic nut 42 to which the telescopic shaft 36 is screwed moves. Thus, the jacket tube 11 moves in the axial direction, whereby the upper shaft 2 moves together with the jacket tube 11 in the axial direction, and the steering wheel telescopes.

  In the first and second embodiments, the speed reduction means shown in FIGS. 1 and 4 is shown as the second speed reduction means 3b constituting the speed reduction means 3. However, the speed reduction means may be in various modes depending on the layout of the tilt axis and the telescopic axis. I need something. The mode of the deceleration means will be described below.

  As a first classification for determining the mode of the speed reduction means, the planetary mechanism shown in FIGS. 8A and 8B and the planetary mechanism shown in FIGS. It can be divided into four modes with the differential mechanism shown in d). Each mechanism includes a rotatable first rotating body 51 having a first shaft 51a, a rotatable second rotating body 52 having a second axis (not shown) coaxial with the first shaft 51a, a first A plurality of third rotating bodies 53 that mesh or roll into contact with both the rotating body 51 and the second rotating body 52, and rotatably support the third rotating body 53, and the first shaft 51a, the first shaft It is composed of a rotatable support frame 56 that has two axes (not shown) and a third axis 53a that is coaxial.

  8 (a) and 8 (b) show a mode using a planetary mechanism, and FIG. 8 (a) shows a mode using a planetary gear mechanism by meshing of the gear shown in the first embodiment. b) is an embodiment using a planetary roller mechanism by rolling contact of rollers. In either case, the first rotating body 51 is provided with a rolling outer peripheral surface (external teeth or rolling surfaces) 51p, while the second rotating body 52 is provided with a rolling inner peripheral surface (internal teeth or rolling surfaces) 52p. A third rotating body (planetary gear or planetary roller) 53 that is rotatable about a turning shaft 53b substantially parallel to the first shaft 51a is sandwiched between the rolling outer peripheral surface 51p and the rolling inner peripheral surface 52p, and meshes with each other. Or it rotates in contact with rolling.

  According to this invention, the three-axis reduction mechanism constitutes a planetary gear mechanism using a gear or a planetary roller mechanism using a roller, and the first rotating body is a rotating body such as a sun gear positioned in the center, The second rotating body is a rotating body such as an internal gear positioned on the outer peripheral side, and the third rotating body is a plurality of rotating bodies such as a planetary gear positioned between the sun gear and the internal gear.

  FIG. 8C shows an embodiment using a differential mechanism. Umbrella teeth 51 r and 52 r are provided on the outer peripheral surface of the first rotating body 51 and the outer peripheral surface of the second rotating body 52, respectively. A third rotating body 53 formed of a bevel gear that is rotatable about a turning shaft 57 arranged along the radial direction of the bevel meshes with both of the bevel teeth 51r and 52r.

  According to the present invention, the three-axis reduction mechanism constitutes a differential gear mechanism using gears, the first rotating body is a bevel gear integrated with the left shaft of the vehicle body, and the second rotating body is the right shaft of the vehicle body. And the third rotating body is a plurality of bevel gears provided in the differential case.

  FIG. 8D shows an embodiment using a differential mechanism. Rolling side surfaces 51 s and 52 s are provided on the side surface of the first rotating body 51 and the side surface of the second rotating body 52, respectively. A third rotating body 53 made of a roller that is rotatable around a turning shaft 59 arranged along the radial direction is sandwiched between the rolling side surfaces 51 s and 52 s of the first rotating body 51 and the second rotating body 52 and rolls. It is like that.

  According to the present invention, the three-axis reduction mechanism constitutes a differential roller mechanism using a roller, the first rotating body is a disk integrated with the left shaft, and the second rotating body is a disk integrated with the right shaft. The third rotating body is a plurality of rollers provided in the differential case.

  As described above, as the first class, the speed reduction unit uses a mode in which a three-axis speed reduction unit uses an existing planetary mechanism (gear or roller) and a differential mechanism (gear or roller) as shown in FIG. As an example of how to use the existing speed reduction means, for example, the planetary gear mechanism of FIG. 8A is used as shown in FIG. Four modes can be considered by adding the fourth axis or the fifth axis to the gear mechanism, and using the fourth axis and the fifth axis as the input / output axes.

  FIG. 9A shows a mode in which the planetary gear mechanism is used as it is. The first shaft 51a, the third shaft 53a, and the second shaft 52a that is provided so as to surround the third shaft 53a and constitutes a double shaft. Are the input shafts, and the remaining two axes are a pair of output shafts connected to the tilt shaft and the telescopic shaft, respectively. As the lock means for locking either one of the pair of output shafts, for example, the lock means 6 is provided on the third shaft 53a, and the lock means 7 is provided on the second shaft 52a.

  FIG. 9B shows that the planetary gear mechanism is provided with a rotatable fourth rotating body 54 that has a fourth shaft 54a that meshes with the outer peripheral surface of the second rotating body 52 and that is substantially parallel to the first to third shafts 51a to 53a. The fourth shaft 54a is used as an input shaft or an output shaft in place of the second shaft, and any one of these three shafts is used as an input shaft, and the remaining two shafts are used as the tilt shaft and the telescopic shaft. A pair of output shafts connected to each of the shafts. As the lock means for locking either one of the pair of output shafts, for example, lock means 6 and 7 are provided on the third shaft 53a and the fourth shaft 54a.

  9 (c) and 9 (d) are embodiments in which a fifth shaft 55a substantially perpendicular to the first to third shafts is provided in place of the second shaft of the planetary gear mechanism. FIG. 9C shows a mode adopted in the second embodiment. A bevel tooth 52t is formed on the outer peripheral surface of the second rotating body 52, and the fifth rotating body 55, which is a bevel gear, is engaged with the bevel tooth 52t. It is a thing. In the embodiment of FIG. 9 (d), a worm wheel 52u is formed on the outer peripheral surface of the second rotating body 52, and the fifth rotating body 55, which is a worm, is engaged with the worm wheel 52u. In any case, a fifth shaft 55a substantially perpendicular to the first to third axes is provided, the fifth shaft 55a is used as an input shaft or an output shaft instead of the second shaft, and one of these three shafts is used as an input shaft. The remaining two axes are defined as a pair of output shafts connected to each of the tilt shaft and the telescopic shaft. As the lock means for locking either one of the pair of output shafts, for example, the lock means 6 and 7 are provided on the third shaft 53a and the fifth shaft 55a.

In addition, classification by the third classification is possible depending on which of the three axes is used as the input axis. For example, in the case of using the planetary gear mechanism of FIG. 8A, a mode in which the first shaft 51a is an input shaft as shown in FIG. 10A and a third shaft 53a as shown in FIG. 10B. And an aspect using the fourth axis 54a as the input axis as shown in FIG. 10C. In either case, the lock means 6 and 7 are provided on the remaining two shafts which are output shafts. 8A, 9B, and 10A are the same diagram.
As described above, in the first classification, it is classified into four modes according to the type of the three-axis reduction mechanism, in the second classification, it is classified into four aspects depending on the axis added to each mechanism, and in the third classification, which input shaft is selected. Since it is classified into three modes depending on whether or not, a total of 4 × 4 × 3 = 48 modes can be considered. When selecting the input shaft, the output shaft is not decelerated and is at the same speed as the input shaft, or conversely increased with respect to the input shaft. By doing so, the rotational speed of the output shaft can be adjusted.

  In addition, although the locking means is individually provided for each of the two output shafts, one of the two output shafts may be selectively locked by a single locking means. In the second embodiment, the mode of FIG. 9C is adopted, but the mode of FIG. 9D may be adopted.

1 is a perspective view showing a main part of an electric tilt telescopic steering column (Embodiment 1). FIG. The front view of an electric tilt telescopic steering column (Embodiment 1). The bottom view which shows an electric tilt telescopic steering column (Embodiment 1). A perspective view showing a principal part of an electric tilt telescopic steering column (Embodiment 2). A perspective view showing the vicinity of a swing arm of an electric tilt telescopic steering column (Embodiment 2). The front view which shows an electric tilt telescopic steering column (Embodiment 2). A top view which shows an electric tilt telescopic steering column (Embodiment 2). The block diagram which shows four aspects when the kind of 3 axis | shaft deceleration mechanism of a deceleration means differs as 1st classification. As a second classification, for example, when a planetary gear mechanism is used, a configuration diagram showing four modes depending on how to use the mechanism. As a third classification, for example, when using a planetary gear mechanism, a configuration diagram showing three modes depending on which of the three axes is used as an input shaft.

Explanation of symbols

3 ... 2nd deceleration means 5 ... Housing (1st support member)
6, 7 ... Locking means 11 ... Jacket tube (second support member)
DESCRIPTION OF SYMBOLS 15 ... Steering shaft 26 ... Tilt axis 29 ... Motor 36 ... Telescopic shaft 51 ... 1st rotary body 51a ... 1st axis 51p ... Rolling outer peripheral surface 51r, 52r, 52t ... Umbrella tooth 51s, 52s ... Rolling side surface 52 ... 1st Two-rotating body 52a ... Second shaft 52p ... Rolling inner peripheral surface 52u ... Warm wheel 53 ... Third rotating member 53a ... Third shaft 53b ... Swivel shaft 54 ... Fourth rotating member (spur gear)
54a ... fourth shaft 55 ... fifth rotating body (bevel gear, worm)
55a ... 5th axis (tilt axis)
56 ... Rotation support frame

Claims (6)

A steering shaft for transmitting a steering force input from a steering wheel to a steering wheel; a support member for rotatably supporting the steering shaft; and a support member rotatably supported by the support member and tilting the steering wheel A tilt shaft, a telescopic shaft that is rotatably supported by the support member and telescopically steers the steering wheel, a single motor, a rotational force from the motor, and the tilt shaft or the telescopic shaft In an electric tilt telescopic steering column equipped with a deceleration means that outputs to either
As the speed reducing means, a rotatable first rotating body having a first axis, a rotatable second rotating body having a second axis coaxial with the first axis, the first rotating body, and the second rotation. A plurality of third rotating bodies that mesh or roll into contact with both of the bodies, a rotation that rotatably supports the third rotating body and has a third axis that is coaxial with the first axis and the second axis. A three-axis reduction mechanism having a freely rotating support frame;
One of the first to third axes is an input shaft, and the remaining two axes are a pair of output shafts connected to the tilt shaft and the telescopic shaft,
An electric tilt telescopic steering column provided with a lock means for locking one of the pair of output shafts. In the electric tilt telescopic steering column according to claim 1,
A rotatable fourth rotating body having a fourth axis that meshes with or is in rolling contact with the outer peripheral surface of the second rotating body and that is substantially parallel to the first to third axes is provided, and a fourth axis is substituted for the second axis. An electric tilt telescopic steering column, wherein the input shaft or the output shaft is used. In the electric tilt telescopic steering column according to claim 1,
An outer peripheral surface of the second rotating body is engaged with a bevel gear or a worm / worm wheel, and a rotatable fifth rotating body having a fifth axis substantially perpendicular to the first to third axes is provided. Instead, the electric tilt telescopic steering column is characterized in that the fifth shaft is the input shaft or the output shaft. In the electric tilt telescopic steering column according to any one of claims 1 to 3,
The speed reducing means has a rolling outer peripheral surface provided on the first rotating body, while a rolling inner peripheral surface is provided on the second rotating body and rotates about a turning axis substantially parallel to the first axis. An electric tilt telescope characterized in that it is a planetary mechanism in which the third rotating body composed of a free gear or roller is sandwiched between the rolling outer peripheral surface and the rolling inner peripheral surface and rotates by meshing or rolling contact. Steering column. In the electric tilt telescopic steering column according to any one of claims 1 to 3,
The speed reducing means is provided with bevel teeth on the outer peripheral surface of the first rotating body and the outer peripheral surface of the second rotating body, respectively, and is rotatable about a turning shaft arranged along the radial direction of the rotating support frame. An electric tilt telescopic steering column, wherein the third rotating body comprising a bevel gear is a differential gear mechanism that meshes with both the bevel teeth of the first rotating body and the second rotating body. In the electric tilt telescopic steering column according to any one of claims 1 to 3,
The speed reduction means is provided with rolling side surfaces on the side surface of the first rotating body and the side surface of the second rotating body, respectively, and is a roller that is rotatable around a turning axis arranged along the radial direction of the rotating support frame. An electric tilt telescopic steering column, wherein the third rotating body is a differential roller mechanism that is sandwiched between rolling side surfaces of the first rotating body and the second rotating body to make rolling contact.

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