JP2011112208A - Device with linear motion mechanism, and stabilizer device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a device with a small linear motion mechanism, and a stabilizer device. <P>SOLUTION: A rolling linear motion guide 21 is disposed between a casing 5 and a plate 12. The rolling linear motion guide 21 includes a substantially U-shaped plate-like guide groove 22 formed on the outer peripheral side of the plate 12; a guide piece 23 the outer peripheral side of which is press-fitted to a locking groove 6D of the plate case 6, and the inner peripheral side of which is slidably fitted in the plate-side guide groove 22; a ball 24 which is provided between the guide piece 23 and the plate-side guide groove 22 so as to be capable of rolling in an axial direction through groove portions 22A, 23A; a holder 25 which holds the ball 24 so as to be capable of rolling between the guide groove 22 and the guide piece 23; and a spring 27 which biases, between the holder 25 and a retainer 28, the ball 24 toward a ball housing space 26 formed between the guide groove 22 and the guide piece 23. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a device including a linear motion mechanism mounted on a vehicle such as an automobile and a stabilizer device suitable for suppressing the roll motion of a vehicle body.

  Some vehicles such as automobiles are provided with a stabilizer device in order to stabilize the posture of the vehicle body in a running state such as cornering. In recent years, in addition to the hydraulic stabilizer device that has been developed in the past, the development of an electric stabilizer device excellent in mountability has been carried out. An example of an electric stabilizer device is disclosed in Patent Document 1.

JP 2008-120175 A

  The stabilizer device is mounted on a vehicle and used to improve the traveling performance of the vehicle. In such a stabilizer device, it is desirable to reduce the space of the vehicle required for mounting, and miniaturization is desired. In addition to a stabilizer device, a device including a linear motion mechanism that converts a rotational motion into a linear motion is desired to reduce, for example, a mounting space on a vehicle, and downsizing is desired.

  The objective of this invention is providing the apparatus and stabilizer apparatus provided with the small-sized direct-acting mechanism.

  In order to solve the above problems, an apparatus including a linear motion mechanism adopted by the present invention includes a cylindrical casing, and a linear motion mechanism that is provided in the casing and converts rotational motion into linear motion, The linear motion mechanism performs a rotational motion in a state where axial displacement in the casing is restricted, and a first plate in which a plurality of first inclined portions extending in the circumferential direction are formed on a surface on one axial direction side; A plurality of second inclined portions provided in the casing so as to face the first plate in the axial direction and extending in the circumferential direction are formed on the surface on the other side in the axial direction facing the first plate. A second plate and a first and second plate which are sandwiched between the first inclined portion and the second inclined portion so as to be able to roll between the first and second plates; Multiple rolling members that approach and separate the two in the axial direction when the plate rotates relative to each other A plurality of rotation restricting mechanisms provided between the casing and the second plate, allowing the second plate to be displaced in the axial direction within the casing and restricting relative rotation between the two plates; Each of the rotation restricting mechanisms includes a plate-side guide groove provided in the second plate and opening toward the casing, and a plate-side guide groove fitted in the plate-side guide groove and provided in the casing. A casing side guide member that forms a rotor accommodating space between the casing side guide member and the plate side guide groove so as to be capable of rolling, and rolls in the axial direction within the rotor accommodating space. And an urging member for urging the axial rotator in the axial direction within the rotator accommodating space.

  Further, the stabilizer device adopted by the present invention includes a cylindrical casing, a first stabilizer bar provided in the casing so as to be relatively rotatable, a second stabilizer bar fixedly provided on the casing, A variable rigidity portion that is provided in the casing so as to connect the stabilizer bars and adjusts the torsional rigidity between the stabilizer bars, and the variable rigidity portions include the first stabilizer bar, the second stabilizer bar, and the like. A linear motion mechanism that linearly moves in accordance with the relative rotation, a biasing mechanism that biases the linear motion mechanism in a direction that suppresses the linear motion, and a biasing force adjustment that adjusts the biasing force of the biasing mechanism The linear motion mechanism is connected to the first stabilizer bar and is rotatably provided in the casing, and extends in a circumferential direction on a surface on one side in the axial direction. A first plate in which a plurality of inclined portions are formed, and is provided in the casing so as to be opposed to the first plate in the axial direction, on a surface on the other axial side facing the first plate. A second plate in which a plurality of second inclined portions extending in the circumferential direction are formed, and the first and second plates sandwiched between the first inclined portion and the second inclined portion. Between the casing and the second plate; and a plurality of rolling members that are axially movable when the first and second plates rotate relative to each other. And a rotation restricting mechanism that allows the second plate to be displaced in the axial direction within the casing and restricts relative rotation between the two plates. The rotation restricting mechanism is provided on the second plate and A plate-side guide groove opened toward the casing; A casing-side guide member that fits into a plate-side guide groove and that is provided in the casing and forms a rotor accommodating space between the plate-side guide groove, and the casing-side guide member and the plate-side guide groove An axial direction rolling element provided so as to be capable of rolling in between and axially rolling in the rolling element accommodation space, and urging the axial direction rolling element in the axial direction within the rolling element accommodation space And an urging member.

  ADVANTAGE OF THE INVENTION According to this invention, the apparatus and stabilizer apparatus provided with the linear motion mechanism can be reduced in size.

It is a system diagram showing an example of the entire configuration of a vehicle using a stabilizer device. It is a longitudinal section showing the stabilizer device concerning a 1st embodiment of the present invention. It is a disassembled perspective view which shows a stabilizer apparatus. It is an expanded sectional view which looked at the rotation control mechanism from the arrow IV-IV direction in FIG. It is a characteristic diagram which shows the relationship between the torque between each stabilizer bar, and a twist angle. It is a longitudinal cross-sectional view which shows the stabilizer apparatus which concerns on the 2nd Embodiment of this invention. It is an expanded sectional view which looked at the rotation control mechanism from the arrow VII-VII direction in FIG.

  Hereinafter, a stabilizer device will be described as an example of a device provided with a linear motion mechanism according to an embodiment of the present invention, and will be described in detail according to the accompanying drawings.

  FIG. 1 shows an overall configuration of a vehicle in which the stabilizer device 1 is used on the front wheel side and the rear wheel side. The control device 100 predicts and controls the degree of roll on the road surface in response to a signal from the steering angle, vehicle speed, or the like, for example, that the vehicle body has entered the corner. Operates to suppress the roll movement. As a result, the stabilizer device 1 is intended to prevent vehicle rollover, improve steering stability, or improve riding comfort.

  2 to 5 show a first embodiment of the present invention. The stabilizer device 1 is rotatably attached to the vehicle body side constituting the vehicle via a bush at the center in the length direction, and both ends are connected (coupled) to the left and right wheel sides as shown in FIG. ing. Further, the stabilizer device 1 is a variable that connects the first stabilizer bar 2, the second stabilizer bar 3, and the stabilizer bars 2 and 3, and adjusts the torsional rigidity between the stabilizer bars 2 and 3. And a rigid portion 4.

  The first stabilizer bar 2 disposed on the left side of the vehicle body is made of flexible spring steel and is bent into a desired shape as shown in FIG. 1 according to the layout of the vehicle body. The base end side of the first stabilizer bar 2 is connected to the second stabilizer bar 3 via the variable rigidity portion 4, and the tip end side is connected to the left wheel side. Further, the proximal end side of the first stabilizer bar 2 has a bolt 20 on a ball and ramp mechanism 9 (to be described later) acting as a mechanism for transmitting torsional motions with torsional rigidity (hereinafter referred to as a linear motion mechanism). Etc. are connected (linked).

  The second stabilizer bar 3 disposed on the right side of the vehicle body is made of spring steel having flexibility in substantially the same manner as the first stabilizer bar 2, and substantially the same as the first stabilizer bar 2 as shown in FIG. It is bent to form a symmetrical shape. The base end side of the second stabilizer bar 3 is connected to the first stabilizer bar 2 via the variable rigid portion 4, and the tip end side is connected to the right wheel side. Further, the base end portion of the second stabilizer bar 3 is mechanically connected (linked) to a motor case 8 of the casing 5 described later.

  The base end side of the first stabilizer bar 2 and the base end side of the second stabilizer bar 3 are arranged on the axis OO as shown in FIG. 2, and the axis OO is centered with respect to the vehicle body side. It is supported so as to be rotatable in the twisted direction.

  The variable rigidity portion 4 provided by connecting the first stabilizer bar 2 and the second stabilizer bar 3 adjusts the torsional rigidity between the stabilizer bars 2 and 3. The variable rigidity portion 4 includes a casing 5, a ball and ramp mechanism 9, a coil spring 15, and an urging force adjustment mechanism 16.

  The casing 5 forming the outer shape of the variable rigid portion 4 is formed as a cylindrical container extending in the axial direction along the axis OO. The casing 5 is made of a highly rigid metal material or the like, and includes a plate case 6, a lid body 7, and a motor case 8. As shown in FIG. 2, the plate case 6 includes a cylindrical tube portion 6A extending in the axial direction along the axis OO, and one axial direction side of the tube portion 6A (right end portion in FIG. 2). A bottom portion 6B that is provided so as to close the shaft, a shaft insertion hole 6C that is positioned on the inner peripheral side of the bottom portion 6B and that is rotatably inserted along with the output shaft 19C, and an inner portion of the cylindrical portion 6A. A circumferential plate is formed at intervals, and includes a second plate 12, which will be described later, and a plurality of locking grooves 6D as a plurality of locking portions for holding the piston 17 in a locked state in the casing 5.

  Further, the lid body 7 located on the other axial side of the casing 5 (the left end side in FIG. 2) has a stepped cylindrical shape, on the left end side of the plate case 6 so as to close the left end portion of the cylindrical portion 6A. It is fixed using fastening bolts 30 and the like described later. In addition, two bearings 7 </ b> A made of, for example, a pair of angular ball bearings are provided on the inner peripheral side of the lid body 7. Each of the bearings 7A supports the first stabilizer bar 2 together with a first plate 10 (to be described later) in the lid body 7 so as to be rotatable, and the axial thrust load acting on the first plate 10 together with the lid body 7. It will be accepted.

  On the other hand, the motor case 8 provided on the right side of the plate case 6 accommodates an electric motor 19 which will be described later, and as shown in FIG. 2, a cylindrical portion 8A along the axis OO and the cylindrical portion 8A. It is formed in a bottomed cylindrical shape by a bottom 8B whose right end is closed. Further, the opening portion of the cylindrical portion 8A is fixed to the cylindrical portion 6A of the plate case 6 using a fastening bolt 30 or the like which will be described later, and the fixed shaft 19B of the electric motor 19 is non-rotatably inserted at the center position of the bottom portion 8B. A shaft fixing hole 8C to be fitted is formed. The center portion of the bottom portion 8B is integrally connected to the base end portion of the second stabilizer bar 3, whereby the casing 5 is rotated so as to rotate relative to the first stabilizer bar 2. The stabilizer bar 3 is integrally rotated.

  In this case, the casing 5 not only houses a ball and ramp mechanism 9 as a linear motion mechanism and a coil spring 15 (a biasing mechanism that applies thrust to the linear motion mechanism) described later, but also the casing 5 itself It acts as a transmission member for transmitting torsional force, that is, torsional torque. Thereby, the structure of the stabilizer apparatus 1 can be simplified, and the casing 5 of the variable rigid portion 4 has a configuration effective for simplifying the structure.

  The first stabilizer bar 2 is mechanically connected to one end of the ball and ramp mechanism 9, and the second stabilizer bar 3 is mechanically connected to the other end of the ball and ramp mechanism 9. The ball and ramp mechanism 9 is an example of the linear motion mechanism, and includes a first plate 10, a second plate 12, and a ball 14. A thrust based on an urging mechanism acts on the first plate 10 and the second plate 12, and the first plate 10 and the second plate are caused by this thrust (that is, the urging force of the coil spring 15). The balls 14 are pressed against the lamps 11 and 13 respectively formed on 12. The ball and ramp mechanism 9 adjusts the torque transmission coefficient based on the thrust and the groove shape of the ramps 11 and 13.

  Here, the ball and ramp mechanism 9 as the linear motion mechanism is housed in the casing 5 so as to be located closer to the left side on the other side in the axial direction of the plate case 6. The ball and ramp mechanism 9 includes a first plate 10 that rotates integrally with the first stabilizer bar 2 and a second plate provided in the plate case 6 so as to face the first plate 10 in the axial direction. A plate 12, a ball 14 as a rolling member that is arranged between the plates 10 and 12 and is made of a rigid body that can roll along the groove shape of the ramps 11 and 13, and rolling as a rotation restricting mechanism described later. The linear guide 21 is comprised. The rolling member is not limited to the spherical ball 14 and may be a rolling member such as a tapered roller as long as it rolls.

  When a relative rotational movement occurs between the first stabilizer bar 2 and the casing 5 mechanically connected to the second stabilizer bar 3, the ball and ramp mechanism 9 responds along the axis OO accordingly. A linear motion in the axial direction (indicated by arrows A and B in FIG. 2) is generated. The ball and ramp mechanism 9 adjusts the torque transmission coefficient according to the groove shape of the lamps 11 and 13, and adjusts the torsional rigidity, that is, the characteristics of the stabilizer device 1.

  That is, the ball and ramp mechanism 9 can change the axial stroke of the second plate 12 according to the phase difference due to the relative rotation between the first stabilizer bar 2 and the casing 5, that is, the relative rotation angle between the two. At that time, the stroke amount relative to the relative rotation angle can be adjusted by the groove shape of the lamps 11 and 13. Further, the reaction force of the coil spring 15 is determined by the stroke amount of the second plate 12, which becomes the torque of the variable rigidity portion 4. At that time, the torque can be adjusted by setting the lead angle of the lamps 11 and 13.

  As shown in FIG. 2 and FIG. 3, the first plate 10 provided at the left portion in the plate case 6 includes a fitting cylinder portion 10 </ b> A extending in the axial direction along the axis OO, and the fitting 3 sector arm portions 10B protruding outward in the radial direction from the right end portion of the cylindrical portion 10A and spaced apart from each other in the circumferential direction. Each sector arm portion 10B has a substantially fan shape as shown in FIG. It is formed as a finished plate. And each sector arm part 10B of the 1st plate 10 is arrange | positioned in the position which becomes alternate in the circumferential direction with respect to each spring receiving part 28A of the retainer 28 mentioned later.

  Here, in the fitting cylinder portion 10A of the first plate 10, the base end side of the first stabilizer bar 2 is connected by using a locking means such as a spline. In this state, the first plate 10 It is fixed to the first stabilizer bar 2 with bolts 20 and the like which will be described later. As a result, the first plate 10 can rotate with respect to the second stabilizer bar 3 together with the first stabilizer bar 2.

  Further, in each sector arm portion 10B of the first plate 10, a first ramp 11 as a first inclined portion extends in the circumferential direction of the plate 10 on the right end surface (front surface) side, for example, a total of 3 One is provided. Here, the lamp 11 provided in each sector arm portion 10B is formed as a concave inclined groove curved in an arc shape. Further, each lamp 11 is formed as an arc-shaped groove as an inclined portion that becomes a deepest portion at the center in the length direction and becomes shallow with a desired curvature from the deepest portion toward both ends.

  On the other hand, the second plate 12 provided facing the right side of the first plate 10 is formed in a thick disk shape centering on the axis OO, as shown in FIGS. , And an extending cylinder portion 12A extending in the axial direction from the outer peripheral side. The extending cylinder portion 12A surrounds a left side portion of a coil spring 15 described later from the outside in the radial direction, protects the coil spring 15 from the outside, and the urging force stably acts on the second plate 12. Thus, the coil spring 15 is guided. Further, on the inner peripheral side of the second plate 12, an axial through hole 12 </ b> B into which a bolt 20 described later is inserted with a gap is provided.

  Here, on the outer peripheral side of the second plate 12, as shown in FIGS. 2 and 3, a rolling linear motion guide 21, which will be described later, disposed at substantially equal intervals in the circumferential direction is provided, and the rolling linear motion guide 21. The guide piece 23 is fitted in each rotation stop groove 6 </ b> D of the plate case 6. The second plate 12 is configured such that relative rotation in the casing 5 is restricted by a rolling linear motion guide 21 described later, and the axial movement in the casing 5 is smoothed.

  In addition, three second lamps 13 as second inclined portions are provided on the left end surface (front surface) of the second plate 12 facing the first plate 10. The three lamps 13 are formed in an arcuate shape, almost the same as the first lamp 11, with the central part in the length direction being the deepest part, and the slope that becomes shallower from the deepest part toward both ends. It is formed as an arc-shaped groove as a part.

  The first and second lamps 11 and 13 can adjust the riding comfort of the vehicle by their groove shapes (curved shapes). That is, in a range where the torsion angle between the first plate 10 and the second plate 12 is small, it is desired that the biasing force of the coil spring 15 described later is reduced so as not to affect the riding comfort of the vehicle. In a large range, it is desired to increase the urging force of the coil spring 15 and suppress the roll during turning.

  In order to realize such a requirement, the groove shape of the first and second lamps 11 and 13 hardly generates a torsional torque in a range where the torsion angle between the first plate 10 and the second plate 12 is small. In this way, the non-linear characteristic such as the arc shape having a large curvature radius and the curvature radius being reduced so that the torque suddenly rises when the torsion angle enters a large range can be adjusted by the groove shape. Further, the groove shape and profile of the lamps 11 and 13 may be determined in accordance with desired characteristics such as combining curves and straight lines.

  Three balls 14 sandwiched between each sector arm 10 </ b> B of the first plate 10 and the second plate 12 are accommodated between the first lamp 11 and the second lamp 13. Each ball 14 has an outer diameter dimension such that each sector arm portion 10B of the first plate 10 and the second plate 12 do not come into contact with each other in a state of being accommodated between the lamps 11 and 13. It is formed as a metal ball or the like.

  The ball-and-ramp mechanism 9 configured as described above normally presses the first plate 10 and the second plate 12 in a direction approaching each other by a biasing force of a coil spring 15 to be described later. A ball 14 is disposed at the deepest part of each lamp 11, 13. Thus, the first stabilizer bar 2 and the second stabilizer bar 3 are urged so as to always have an initial angle (an angle at which the vehicle is not inclined) by an urging force of a coil spring 15 described later.

  On the other hand, when the first stabilizer bar 2 and the second stabilizer bar 3 (casing 5) rotate relative to each other about the axis OO, the first lamp 11 and the second lamp 13 are in the circumferential direction. Therefore, the ball 14 moves from the central portion of each of the lamps 11 and 13 to the end side. Thereby, each plate 10 and 12 is displaced to the direction which mutually spaces apart in an axial direction according to the inclination of each lamp | ramp 11 and 13. FIG. In this case, the torsional rigidity at this time is increased by increasing the biasing force of the coil spring 15 pressing the second plate 12 against the first plate 10 by the biasing force adjusting mechanism 16 described later. Can do.

  A coil spring 15 as an urging mechanism provided in the plate case 6 located on the right side of the second plate 12 urges the plate 12 in a direction to suppress the linear movement of the second plate 12. Thus, the second plate 12 is made of an elastic member that generates a pressing force that presses the second plate 12 toward the first plate 10. When the coil spring 15 is used as the elastic member, only one member is required. For example, the workability during assembly can be improved as compared with the case where a plurality of disc springs are used.

  An urging force adjusting mechanism 16 provided in the casing 5 for adjusting the urging force of the coil spring 15 is configured as a load applying portion that applies an initial load of an arbitrary size in the expansion and contraction direction of the coil spring 15. . The urging force adjusting mechanism 16 includes a piston 17 as a moving means provided in the plate case 6, a screw member 18, an electric motor 19 as a driving means provided in the motor case 8, and a controller and the like. The apparatus 100 is roughly configured.

  Here, the electric motor 19 is housed in the motor case 8 and is arranged side by side in the axial direction with the ball and ramp mechanism 9, a piston 17 and a screw member 18 described later. However, the present invention is not limited to this. For example, when the axial length of the casing 5 is limited, an electric motor as a driving unit is arranged in parallel with the screw member 18, and power including, for example, a plurality of gears is used. It is good also as a structure which rotationally drives the screw member 18 via a transmission mechanism.

  The piston 17 as the moving means is formed in a stepped cylindrical shape as shown in FIG. 2, and is provided to face the plate 12 so as to sandwich the coil spring 15 between the second plate 12. The piston 17 has a large-diameter spring receiving portion 17A as an annular flange projecting radially outward from the axial end (right end) side. Further, on the outer peripheral side of the spring receiving portion 17A, three engagement projections 17B are formed at intervals in the circumferential direction, and each engagement projection 17B engages with each rotation stop groove 6D of the plate case 6. Yes. Thereby, the piston 17 is connected to the casing 5 so as to be movable in the axial direction in a state in which the rotation is restricted.

  Further, a female screw 17C made of, for example, a trapezoidal screw is formed on the inner peripheral side of the piston 17, and the female screw 17C, together with a male screw 18B of a screw member 18 described later, performs a rotational movement by a later-described electric motor 19 in a straight line of the piston 17. A screw mechanism is configured as a linear motion conversion mechanism that converts motion.

  The screw member 18 screwed to the inner peripheral side of the piston 17 has a shaft attachment portion 18A on the base end side attached to the output shaft 19C of the electric motor 19, and the shaft attachment portion 18A is integrated with the output shaft 19C. Rotate. Further, on the outer peripheral side of the screw member 18, a male screw 18B made of a trapezoidal screw that is screwed into the female screw 17C of the piston 17 is formed. The male screw 18B constitutes a screw mechanism together with the female screw 17C.

  Here, the piston 17 is screwed to the screw member 18 via a female screw 17C made of a trapezoidal screw and a male screw 18B. Therefore, unless the screw member 18 is rotationally driven by the electric motor 19, the piston 17 is not displaced in the directions indicated by arrows A and B in FIG. 2, and the piston 17 is moved by the biasing force of the coil spring 15. It does not move in the axial direction (directions indicated by arrows A and B in FIG. 2).

  The electric motor 19 as a driving means protrudes from a main body portion 19A containing a stator, a rotor and the like (both not shown) and a right end portion of the main body portion 19A, and rotates into a shaft fixing hole 8C of the motor case 8. The fixed shaft 19B, which is impossible to insert, and the output shaft 19C that protrudes from the left end of the main body 19A and is connected to the rotor are roughly configured. Further, the output shaft 19 </ b> C is inserted into and fitted to the shaft mounting portion 18 </ b> A of the screw member 18 in the shaft insertion hole 6 </ b> C of the plate case 6.

  In the biasing force adjusting mechanism 16 configured as described above, as shown in FIG. 2, the initial load of the coil spring 15 is determined by the distance between the second plate 12 and the spring receiving portion 17 </ b> A of the piston 17. In this case, when the screw member 18 is rotationally driven by the electric motor 19 and the piston 17 is linearly moved toward the second plate 12 (in the direction of arrow A in FIG. 2), the springs of the second plate 12 and the piston 17 are used. The space | interval dimension with the receiving part 17A can be made small, and the initial load of the coil spring 15 can be adjusted to a heavy load side.

  On the other hand, when the screw member 18 is rotationally driven in the reverse direction by the electric motor 19 and the piston 17 is moved in the direction away from the second plate 12 (the direction indicated by the arrow B in FIG. 2), the second plate 12 and the piston The distance between the 17 spring receiving portions 17A and the coil spring 15 can be adjusted to the small load side.

  Therefore, the urging force adjusting mechanism 16 rotates the screw member 18 by the electric motor 19 and adjusts the initial load of the coil spring 15, so that the stabilizer bars 2 and 3 are connected as shown by the characteristic line 31 shown in FIG. The torque as the torsional rigidity with respect to the torsion angle is variably adjusted. That is, the torque with respect to the torsion angle between the stabilizer bars 2 and 3 is variably adjusted within the hatched range in FIG. 5 according to the traveling state such as straight traveling or cornering traveling. Therefore, even if the initial load of the coil spring 15 is adjusted, the force acts toward the torsion angle 0 between the stabilizer bars 2 and 3 does not change.

  Between the cylindrical portion 6A of the casing 5 (plate case 6) and the second plate 12, there are provided a total of three sets of rolling linear motion guides 21 that are spaced apart from each other in the circumferential direction as a rotation restricting mechanism. The rolling linear motion guides 21 are arranged at equal intervals at positions different from the lamps 13 in the circumferential direction of the second plate 12. These rolling linear motion guides 21 restrict the relative rotation of the second plate 12 within the cylindrical portion 6A of the plate case 6, and the second plate 12 smoothly moves in the axial direction within the cylindrical portion 6A. It compensates for the displacement.

  Here, as shown in FIGS. 2 to 4, the rolling linear motion guide 21 is provided on the outer peripheral side of the second plate 12 so as to face each rotation stop groove 6 </ b> D of the plate case 6 in the radial direction. Plate-side guide groove 22 formed as a substantially U-shaped concave groove so as to open toward the surface, and fixedly provided on the inner peripheral side of the plate case 6 and slidably fitted into the plate-side guide groove 22 A guide piece 23 as a casing side guide member to be joined, a sphere 24 as an axial rolling element provided so as to be able to roll between the guide piece 23 and the plate side guide groove 22, and the sphere 24 as a plate A holder 25 that is movably held between the side guide groove 22 and the guide piece 23, and a sphere accommodation space 26 as a rolling element accommodation space formed between the plate side guide groove 22 and the guide piece 23. Hold the sphere 24 toward A spring 27 as an urging member for urging together with 25, is constituted by a retainer 28 to be described later.

  Here, the plate-side guide groove 22 extends in the axial direction of the second plate 12 as shown in FIG. 2, whereby the extending cylinder portion 12 </ b> A is partially cut away. Further, an arc-shaped groove portion 22A having a curvature slightly larger than the outer diameter of the sphere 24 is formed on the bottom side of the plate-side guide groove 22, and the groove portion 22A has a second shape as shown in FIG. The plate 12 extends in the axial direction.

  As shown in FIG. 4, the guide piece 23 is fitted into the rotation stop groove 6 </ b> D of the plate case 6 by means such as press fitting, and is firmly fixed to the inner peripheral side of the plate case 6. In addition, the guide piece 23 is provided with an arc-shaped groove 23A having a curvature slightly larger than the outer diameter of the sphere 24 at a position facing the groove 22A of the plate-side guide groove 22 in the radial direction with the sphere 24 interposed therebetween. The groove portion 23 </ b> A is formed as a concave groove extending in the axial direction of the guide piece 23.

  The spherical body 24 rolls between the two groove portions 22A and 23A, and the second plate 12 on the groove portion 22A side is axially moved with respect to the guide piece 23 on the groove portion 23A side. Reduce frictional resistance when displaced. That is, the spherical body 24 as an axial direction rolling element compensates for the smooth movement of the second plate 12 in the axial direction within the cylindrical portion 6A of the casing 5 (plate case 6).

  In this case, the holder 25 is formed as a small part having a substantially U shape as shown in FIG. 3, and the plate-side guide groove as shown in FIG. 22 and the guide piece 23. The holder 25 functions as a drop-off preventing member that prevents the spherical body 24 from being pulled out from between the groove portions 22A and 23A. The holder 25 also functions to maintain the initial position.

  In addition, a plurality of (for example, two) circular shallow groove portions 25A are provided at the end portion of the holder 25 at positions facing the respective spring receiving portions 28A of the retainer 28, and each of the shallow groove portions 25A and the respective spring receivers of the retainer 28 are received. Between the portion 28A, a spring 27 is disposed to bias the spherical body 24 toward the washer 29 (see FIG. 2) with a biasing force sufficiently smaller than that of the coil spring 15.

  The washer 29 is formed of an annular flat plate that is located in the extended cylindrical portion 12A and is in contact with or fixed to the end surface of the second plate 12, and receives the urging force of the coil spring 15 together with the second plate 12. I accept. The washer 29 has a function of suppressing together with the holder 25 the sphere 24 from being pulled out of the sphere housing space 26 formed between the plate-side guide groove 22 and the guide piece 23. For this reason, the holder 25 and the washer 29 are disposed at a position sandwiching the sphere 24 in the sphere housing space 26 from the front and rear (both sides in the axial direction).

  The retainer 28 is a backup member that is disposed so as to be sandwiched between the first plate 10 and the second plate 12 and supports a spring 27 as an urging member from the back side. As shown in FIG. 3, the retainer 28 has a total of three spring receiving portions 28 </ b> A extending radially outward, and each spring receiving portion 28 </ b> A is located between each spring 27 and the shallow groove portion 25 </ b> A of each holder 25. Are arranged in a preset state. Thereby, each spring 27 urges the sphere 24 together with the holder 25 toward the sphere housing space 26.

  Further, each spring receiving portion 28 </ b> A of the retainer 28 is arranged at a position alternately in the circumferential direction of the casing 5 so as not to overlap with each sector arm portion 10 </ b> B of the first plate 10 in the axial direction. Accordingly, the spheres 24 of the three sets of rolling linear motion guides 21 are arranged at positions different from each other of the balls 14 of the ball and ramp mechanism 9 in the circumferential direction of the casing 5, and are arranged at equal intervals. ing.

  Furthermore, a plurality of fastening bolts 30 are provided on the outer peripheral side of the casing 5 at intervals in the circumferential direction. That is, the lid body 7 located on the left side in FIG. 2 is flange-coupled to the left end side of the plate case 6 (cylindrical portion 6A) using the fastening bolt 30 or the like. Further, the cylinder portion 8A of the motor case 8 is flange-coupled to the right end side of the plate case 6 (cylinder portion 6A) using a fastening bolt 30 or the like.

  The stabilizer device 1 according to the first embodiment is configured as described above. Next, the operation thereof will be described.

  First, when the vehicle is traveling straight, the vehicle body hardly rolls. For this reason, the torsional rigidity required for the stabilizer device 1 is small, and the stabilizer bars 2 and 3 can be independently rotated relatively easily. Thereby, for example, even when one of the wheels falls into the recess during straight traveling, only one of the wheels can be stroked, and a stable traveling posture can be obtained.

  That is, based on information such as steering angle, accelerator opening, brake operation status, lateral acceleration, etc., the driving status is judged and the vehicle travels straight (the steering operation that generates a large roll is not performed). If it is determined that the screw member 18 is rotated by the electric motor 19 in an arbitrary direction, the second plate 12 and the spring receiving portion 17A of the piston 17 are separated from each other as shown in FIG. Separate with.

  As a result, the initial load applied to the coil spring 15 is reduced, so that the torque that is the torsional force required to relatively rotate the first stabilizer bar 2 and the second stabilizer bar 3 is also reduced. Therefore, since the torsional rigidity of the stabilizer device 1 can be reduced, the left and right wheels can stroke independently according to the unevenness of the road surface, and a good riding comfort can be obtained.

  Next, when driving the corner by operating the steering, it is necessary to suppress the outward roll. Therefore, the stabilizer device 1 rotates the screw member 18 in the direction opposite to the previous direction by the electric motor 19 to reduce the distance between the second plate 12 and the spring receiving portion 17A of the piston 17 to reduce the piston 17. It is moved in the direction of arrow A in FIG.

  As a result, the initial load applied to the coil spring 15 is increased, so that the torsional force required to relatively rotate the first stabilizer bar 2 and the second stabilizer bar 3 is also increased. Therefore, the stabilizer device 1 can suppress the rolling of the vehicle body to the outside by increasing the torsional rigidity between the stabilizer bars 2 and 3, and can stabilize the traveling posture of the vehicle during cornering.

  In the control during cornering, the initial load (spring force) of the coil spring 15 is increased by the urging force adjusting mechanism 16 when traveling at the left corner or traveling at the right corner. Thus, when traveling on mountain roads, even when the left corner and the right corner continue alternately as in the case of slalom traveling, after the torsional rigidity between the stabilizer bars 2 and 3 is once increased, the speed and It is only necessary to make fine adjustments according to the size of the corner, and frequent driving of the electric motor 19 can be eliminated.

  Therefore, when it is determined that the vehicle is in a roll running situation in which a relatively large roll is generated based on information such as steering angle, accelerator opening, brake operation status, lateral acceleration, and car navigation information, Increases the initial load (spring force) of the coil spring 15 by the biasing force adjustment mechanism 16. Then, when the straight running continues for a predetermined time, the initial load (spring force) of the coil spring 15 may be reduced.

  Thus, according to the first embodiment, the non-linear characteristics can be obtained by making the profiles of the lamps 11 and 13, that is, the groove shape arc, so that the riding comfort can be improved.

  A variable stiffness portion 4 that adjusts torsional stiffness between the first stabilizer bar 2 and the second stabilizer bar 3 is converted into a linear motion from the relative rotational motion between the stabilizer bars 2 and 3. A ball-and-ramp mechanism 9; a coil spring 15 that urges the second plate 12 of the ball-and-ramp mechanism 9 in the axial direction toward the first plate 10 to suppress the linear movement; and the coil spring 15 And an urging force adjusting mechanism 16 for adjusting the urging force.

  Therefore, when the torsional rigidity is adjusted, the variable rigidity portion 4 adjusts whether the urging force of the coil spring 15 is reduced or increased by the urging force adjusting mechanism 16, so that the same applies to the left corner and the right corner. It can be a control.

  As a result, even when the left corner and the right corner continue alternately, a female screw 17C and a male screw 18B made of trapezoidal screws are formed between the piston 17 and the screw member 18 of the biasing force adjusting mechanism 16. Since the torsional rigidity between the stabilizer bars 2 and 3 only needs to be increased once, and the frequent drive of the electric motor 19 can be eliminated, the power saving and the configuration are simplified by reducing the number of adjustment operations. Therefore, it is possible to reduce the size.

  In addition, the ball and ramp mechanism 9 is connected to the first stabilizer bar 2 to form a first plate 10 on which the first lamp 11 is formed, and to the second stabilizer bar 3 to form a second lamp 13. And a total of three balls 14 sandwiched between the first plate 10 and the second plate 12 while being housed in the first lamp 11 and the second lamp 13. These balls 14 are constituted by three sets of rolling linear guides 21 disposed between the casing 5 and the second plate 12 so as to be alternately arranged.

  As a result, the ball and ramp mechanism 9 can convert the relative rotational motion that is twisted between the stabilizer bars 2 and 3 into a linear motion with a simple configuration, and the configuration can be simplified. Thereby, the stabilizer apparatus 1 can be reduced in size and the freedom degree of the attachment with respect to a vehicle body can be raised.

  In particular, as shown in FIGS. 2 to 4, the rolling linear motion guide 21 has a substantially U-shaped recess on the outer peripheral side of the second plate 12 so as to oppose each rotation stop groove 6 </ b> D of the plate case 6 in the radial direction. A plate-side guide groove 22 formed as a groove, a guide piece 23 whose outer peripheral side is press-fitted into the rotation stop groove 6D of the plate case 6 and whose inner peripheral side is slidably fitted in the plate-side guide groove 22, and the guide A sphere 24 provided between the piece 23 and the plate side guide groove 22 via the groove portions 22A and 23A so as to be able to roll in the axial direction, and the sphere 24 between the plate side guide groove 22 and the guide piece 23. A holder 25 that holds the roll so as to be able to roll, and a spring 27 that biases the sphere 24 between the holder 25 and the retainer 28 toward a sphere containing space 26 formed between the plate-side guide groove 22 and the guide piece 23. And consists of

  As described above, a total of three sets of rolling linear motion guides 21 are provided between the cylindrical portion 6A of the casing 5 (plate case 6) and the second plate 12 so as to be spaced apart from each other in the circumferential direction. The relative rotation of the second plate 12 within the cylindrical portion 6A of the plate case 6 can be restricted, and the second plate 12 can be compensated for smooth displacement in the axial direction within the cylindrical portion 6A. it can.

  That is, when the relative rotation between the stabilizer bars 2 and 3 is converted into linear motion by the ball and ramp mechanism 9, the second plate 12 is moved in accordance with the relative rotation between the first plate 10 and the second plate 12. 1 is displaced in the direction away from the plate 10 (the direction indicated by the arrow B in FIG. 2). At this time, the sphere 24 of the rolling linear motion guide 21 rolls in the axial direction (the direction indicated by the arrow B in FIG. 2) between the groove portion 22A of the plate-side guide groove 22 and the groove portion 23A of the guide piece 23. The frictional resistance generated between the side guide groove 22 and the guide piece 23 is reduced.

  Further, when both of them rotate relative to each other in a direction to return the twist between the stabilizer bars 2 and 3, the direction in which the second plate 12 approaches the first plate 10 by the biasing force of the coil spring 15 (indicated by the arrow in FIG. 2). A direction). For this reason, the spherical body 24 of the rolling linear motion guide 21 rolls in the axial direction (direction of arrow A in FIG. 2) between the groove portion 22A of the plate-side guide groove 22 and the groove portion 23A of the guide piece 23, and the plate The frictional resistance generated between the side guide groove 22 and the guide piece 23 is reduced.

  At this time, the sphere 24 is accommodated in the sphere accommodating space 26 between the plate-side guide groove 22 and the guide piece 23 by the washer 29, and is sandwiched between the holder 25 and the washer 29 by the urging force of the spring 27. Return to state. The spring 27 biases the sphere 24 in the direction indicated by the arrow B via the holder 25, so that when the torque is not generated between the stabilizer bars 2 and 3 (the friction force is acting on the sphere 24), the sphere 24 Is prevented from moving between the groove portions 22A and 23A due to the inertial force due to the movement of the vehicle body, and is always compensated for starting rolling (operation) from a predetermined initial position (for example, the position shown in FIG. 2). The required stroke can be ensured with minimal space.

  As a result, when the relative rotation between the stabilizer bars 2 and 3 is converted into a linear motion by the ball and ramp mechanism 9, a large torque is generated between the cylindrical portion 6A of the casing 5 and the second plate 12. In addition, the frictional resistance generated between the plate-side guide groove 22 and the guide piece 23 can be reduced by rolling the spherical body 24, and the occurrence of hysteresis and the like can be suppressed to realize a small-sized rolling linear motion guide with low resistance. can do.

  Further, a total of three sets of rolling linear motion guides 21 are arranged at equal intervals at positions different from the lamps 13 in the circumferential direction of the second plate 12. For this reason, it is possible to prevent the plates 10 and 12 of the ball and ramp mechanism 9 from being increased in size by the rolling linear motion guide 21 and to keep the outer diameter dimension small. When the second plate 12 is displaced away from the first plate 10 during operation as a stabilizer, the ball 24 of the rolling linear guide 21 rolls so that it partially protrudes between the plates 10 and 12. In addition, the space formed in the circumferential direction between the three balls 14 can be effectively used as the space for the sphere 24.

  The biasing force adjusting mechanism 16 is connected to the piston 17 that contacts the coil spring 15, a screw member 18 that is screwed to the piston 17 to convert the rotational motion into the linear motion of the piston 17, and the screw member 18. Since it is configured by the electric motor 19 and the control device 100 such as a controller, the initial load of the coil spring 15 can be adjusted using the electric motor 19 that is easy to control, and downsizing due to simplification of the configuration, Manufacturing cost can be reduced.

  Further, the lamps 11 and 13 provided on the plates 10 and 12 are formed as arc-shaped grooves whose central part in the length direction becomes the deepest part and becomes shallow toward both ends. Thereby, in the range where the torsion angle between the stabilizer bars 2 and 3 is small, the spring load of the coil spring 15 affecting the torque can be lowered to improve the riding comfort. In addition, in the range where the torsion angle between the stabilizer bars 2 and 3 is large, the spring load of the coil spring 15 can be increased to increase the torsional rigidity, and the roll during the cornering can be suppressed and the running posture can be stabilized. Can be made.

  Next, FIG. 6 and FIG. 7 show a second embodiment of the present invention. The feature of this embodiment is that the axial direction rolling element of the rotation restricting mechanism is constituted by cylindrical rollers. In the present embodiment, the same components as those in the first embodiment described above are denoted by the same reference numerals, and the description thereof is omitted.

  In FIG. 6, the rolling linear motion guide 41 as the rotation restricting mechanism employed in the second embodiment is substantially the same as the rolling linear motion guide 21 described in the first embodiment. A guide piece 43, a roller 44 as an axial rolling element, a holder 45, a roller accommodating space 46 as a rolling element accommodating space, a spring 47 as an urging member, and a retainer 48 are constituted.

  In this case, the plate-side guide groove 42 is formed to extend in the axial direction of the second plate 12 in the same manner as the plate-side guide groove 22 described in the first embodiment. However, a groove 42A having a U-shaped cross section extends in the axial direction of the second plate 12 to guide the cylindrical roller 44 in the axial direction on the bottom side of the plate-side guide groove 42 as shown in FIG. It is formed as a concave groove.

  Further, as shown in FIG. 7, the guide piece 43 is fitted into the rotation stop groove 6 </ b> D of the plate case 6 by means such as press fitting, and is firmly fixed to the inner peripheral side of the plate case 6. However, the guide piece 43 is provided with a U-shaped groove 43A having a groove width slightly larger than the outer diameter of the roller 44 at a position facing the groove 42A of the plate-side guide groove 42 across the roller 44. The groove 43A is formed as a concave groove extending in the axial direction of the guide piece 23.

  The roller 44 formed as a cylindrical body rolls between the two groove portions 42A and 43A in the axial direction, and the second plate 12 on the groove portion 42A side moves to the groove portion 43A side. The axial displacement with respect to the guide piece 43 is smoothed. That is, the roller 44 as an axial direction rolling element reduces the frictional resistance when the second plate 12 moves in the axial direction within the cylindrical portion 6A of the casing 5 (plate case 6).

  The holder 45 is formed in substantially the same manner as the holder 25 described in the first embodiment, and the plate-side guide groove 42 as shown in FIG. And the guide piece 43. The holder 45 functions as a drop-off preventing member that suppresses the roller 44 from being pulled out from between the groove portions 42A and 43A.

  Further, the spring 47 and the retainer 48 as the urging member are configured in the same manner as in the first embodiment, and the spring 47 is arranged in a preset state between each spring receiving portion 48A of the retainer 48 and the holder 45. The roller 44 is urged toward the washer 29 (see FIG. 6). The holder 45 and the washer 29 sandwich the roller 44 from the front and rear (both sides in the axial direction) in the roller accommodating space 46 formed between the plate-side guide groove 42 and the guide piece 43, and the roller 44 is outside. It has a function to suppress extraction.

  Thus, also in the second embodiment configured as described above, it is possible to obtain substantially the same operational effects as those of the first embodiment described above. In particular, according to the second embodiment, by using the cylindrical roller 44 as the axial direction rolling element, for example, it can be formed at a lower cost than the sphere 24 used in the first embodiment, and has high rigidity. It can be set as the member which has.

  In the first embodiment, the guide piece 23 as the casing side guide member is fitted into the rotation stop groove 6D of the plate case 6 by means such as press-fitting and fixed to the inner peripheral side of the plate case 6. The case has been described as an example. However, the present invention is not limited to this, and for example, a casing-side guide member may be integrally formed on the inner peripheral side of the casing formed of the plate case 6 or the like. Such a change may also be applied to the second embodiment.

  Moreover, in each said embodiment, the case where the three lamps 11 and 13 are provided in each plate 10 and 12 of the ball-and-ramp mechanism 9, and the three balls 14 are accommodated in each lamp 11 and 13 is taken as an example. I gave it as an explanation. However, the present invention is not limited to this, and for example, two or four or more lamps 11 and 13 and two or four or more balls 14 may be provided. Also, the rolling linear motion guides 21 and 41 as the rotation restricting mechanism may be configured to be provided in two sets or four or more sets so as to be alternated with the balls 14 in the circumferential direction.

  In each of the above embodiments, the case where the coil spring 15 is used as an urging mechanism for urging the second plate 12 in the direction of suppressing the linear motion has been described as an example. However, the present invention is not limited to this, and other elastic members such as a disc spring and a rubber spring may be used.

  In each of the above-described embodiments, the case where the screw mechanism including the female screw 17C of the piston 17 and the male screw 18B of the screw member 18 is constituted by a trapezoidal screw has been described as an example. However, the present invention is not limited to this, and another screw mechanism such as a ball screw may be used. Here, the case where a trapezoidal screw is used and the case where a ball screw is used are compared. Since the trapezoidal screw has low reverse operability, once it is moved to the side of increasing the rigidity, the characteristics can be maintained without consuming electric power. However, when the electric system or the like fails, the position of the piston 17 is determined, and it may be difficult to return to a predetermined roll rigidity.

  On the other hand, the ball screw has high mechanical efficiency and good reverse operation, so it settles down to soft characteristics at the time of failure and can distribute the front and rear rolls as intended. I must. Since each has advantages and disadvantages, it is recommended to select as appropriate according to requirements.

  In each of the above embodiments, the first stabilizer bar and the second stabilizer bar have been described as having flexibility. However, in the present invention, even a rigid body that has substantially no flexibility and is extremely rigid. Good. Therefore, the first stabilizer bar and the second stabilizer bar can be made of a light and highly rigid material.

  Furthermore, in the said embodiment, the stabilizer apparatus 1 was mentioned as an example and demonstrated as an apparatus provided with the linear motion mechanism. However, the present invention is not limited to this. For example, various devices such as a disc brake described in Japanese Patent No. 3297706 convert the rotational motion of the actuator into an axial displacement and transmit it to the brake pad. The present invention can also be applied to an apparatus having a linear motion mechanism.

  Next, the invention included in the above embodiment will be described. The plurality of rotation restricting mechanisms are disposed at positions different from the second inclined portions in the circumferential direction of the second plate. Thereby, it can prevent that the 1st, 2nd plate of a linear motion mechanism enlarges with a rotation control mechanism, and can suppress the outer-diameter dimension small. When the second plate is displaced away from the first plate during operation as a stabilizer, the axial rolling element of the rotation restricting mechanism is partially protruded between the first and second plates. The space that can be rolled and formed in the circumferential direction between the rolling members of the linear motion mechanism can be effectively utilized as the space for the axial direction rolling element.

  In particular, by arranging the rotation restricting mechanisms at equal intervals in the circumferential direction of the second plate, a space formed in the circumferential direction between the rolling members of the linear motion mechanism is provided for the axial rolling element. It can be used more effectively as a space.

  A first stabilizer bar rotatably provided on the casing so as to rotate integrally with the first plate; a second stabilizer bar fixedly provided on the casing; and the first stabilizer bar provided in the casing. Rotating motion with a simple configuration by including a biasing mechanism that biases the second plate toward the first plate so as to suppress the linear movement of the two plates in the axial direction. Can be converted into a linear motion, and the configuration can be simplified. Thereby, a stabilizer apparatus can be reduced in size and the freedom degree of the attachment with respect to a vehicle body can be raised.

  Further, the linear motion mechanism may be applied to the first plate on which the first inclined portion is formed, the second plate on which the second inclined portion is formed, and the first inclined portion and the second inclined portion. Since it is comprised by rolling members, such as the ball | bowl or the tapered roller which were accommodated, a rotational motion can be converted into a linear motion with a simple structure, and a structure can be simplified. Thereby, a stabilizer apparatus can be reduced in size and the freedom degree of the attachment with respect to a vehicle body can be raised.

  Furthermore, since the biasing force adjusting mechanism can convert the rotational motion into a linear motion using, for example, a screw mechanism, by including a biasing force adjusting mechanism that adjusts the biasing force of the biasing mechanism. As a driving source, driving means such as an electric motor can be used, and the configuration can be simplified and the manufacturing cost can be reduced.

DESCRIPTION OF SYMBOLS 1 Stabilizer apparatus 2 1st stabilizer bar 3 2nd stabilizer bar 4 Variable rigidity part 5 Casing 9 Ball and ramp mechanism (linear motion mechanism)
10 1st plate 11 1st lamp | ramp (1st inclination part)
12 2nd plate 13 2nd lamp | ramp (2nd inclination part)
14 balls (rolling member)
15 Coil spring (biasing mechanism)
16 Biasing force adjustment mechanism 17 Piston 17C Female thread (screw mechanism)
18 Screw member 18B Male screw (screw mechanism)
19 Electric motor (drive means)
21, 41 Rolling linear motion guide (rotation restriction mechanism)
22, 42 Plate side guide groove 23, 43 Guide piece (casing side guide member)
24 Sphere (Axial Roller)
25, 45 Holder 26 Sphere housing space (roller housing space)
27, 47 Spring (biasing member)
28, 48 Retainer 29 Washer 44 Roller (Axial Roller)
46 Roller receiving space (Roller receiving space)

Claims (6)

A cylindrical casing, and a linear motion mechanism that is provided in the casing and converts rotational motion into linear motion,
The linear motion mechanism is
A first plate in which a plurality of first inclined portions extending in the circumferential direction are formed on a surface on one side in the axial direction while performing rotational movement in a state in which axial displacement in the casing is restricted;
A plurality of second inclined portions provided in the casing so as to face the first plate in the axial direction and extending in the circumferential direction on a surface on the other side in the axial direction facing the first plate. Two plates,
When the first and second plates rotate between the first and second plates in a state of being sandwiched between the first and second inclined portions and the first and second plates rotate relative to each other. A plurality of rolling members that approach and separate the two in the axial direction;
A plurality of rotation restriction mechanisms provided between the casing and the second plate, allowing the second plate to be displaced in the axial direction within the casing and restricting relative rotation between the two plates;
Each rotation regulating mechanism is
A plate-side guide groove provided in the second plate and opening toward the casing;
A casing-side guide member that fits in the plate-side guide groove and is provided in the casing and forms a rotor accommodating space between the plate-side guide groove;
An axial direction rolling element provided so as to be capable of rolling between the casing side guide member and the plate side guide groove and rolling in the axial direction within the rolling element accommodation space;
An apparatus provided with a linear motion mechanism comprising the axial direction rolling element and an urging member that urges the axial direction rolling element in the axial direction within the rolling element accommodation space.   2. The apparatus including the linear motion mechanism according to claim 1, wherein the plurality of rotation restricting mechanisms are arranged at positions different from the second inclined portions in the circumferential direction of the second plate.   The apparatus having a linear motion mechanism according to claim 2, wherein the plurality of rotation restricting mechanisms are arranged at equal intervals in a circumferential direction of the second plate. A first stabilizer bar rotatably provided on the casing so as to rotate integrally with the first plate;
A second stabilizer bar fixed to the casing;
An urging mechanism that is provided in the casing and that urges the second plate toward the first plate so as to suppress the linear movement of the second plate in the axial direction. Item 4. A device comprising the linear motion mechanism according to Item 1, 2, or 3.   The apparatus provided with the linear motion mechanism of Claim 4 provided with the biasing force adjustment mechanism which adjusts the force which the biasing mechanism biases. A cylindrical casing, a first stabilizer bar provided on the casing so as to be relatively rotatable, a second stabilizer bar fixedly provided on the casing, and the stabilizer bar so as to connect the stabilizer bars. A variable rigidity portion that adjusts the torsional rigidity between the stabilizer bars.
The variable rigid portion includes a linear motion mechanism that linearly moves in accordance with relative rotation between the first stabilizer bar and the second stabilizer bar, and an urging force that biases the linear motion mechanism in a direction that suppresses the linear motion. An urging mechanism, and an urging force adjusting mechanism for adjusting an urging force of the urging mechanism,
The linear motion mechanism is
A first plate connected to the first stabilizer bar and rotatably provided in the casing, wherein a plurality of first inclined portions extending in the circumferential direction are formed on a surface on one axial side;
A plurality of second inclined portions provided in the casing so as to face the first plate in the axial direction and extending in the circumferential direction on a surface on the other side in the axial direction facing the first plate. Two plates,
When the first and second plates rotate between the first and second plates in a state of being sandwiched between the first and second inclined portions and the first and second plates rotate relative to each other. A plurality of rolling members that approach and separate the two in the axial direction;
A rotation restricting mechanism that is provided between the casing and the second plate, allows the second plate to be displaced in the axial direction within the casing, and restricts the relative rotation of the two plates;
The rotation regulating mechanism is
A plate-side guide groove provided in the second plate and opening toward the casing;
A casing-side guide member that fits in the plate-side guide groove and is provided in the casing and forms a rotor accommodating space between the plate-side guide groove;
An axial direction rolling element provided so as to be capable of rolling between the casing side guide member and the plate side guide groove and rolling in the axial direction within the rolling element accommodation space;
The stabilizer apparatus which comprises this axial direction rolling element by the urging member which urges | biases axially within the said rolling element accommodation space.

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