JP2016211293A - Brake equipment - Google Patents

Abstract

PROBLEM TO BE SOLVED: To restrict occurrence of noise when preventing components to be damaged.SOLUTION: In brake equipment, a gear 32 supported by a shaft 50A is rotated along with the movement of a braked object. In a torque limit part 80, a coil spring 82 is wound around a friction ring 84 supported so as to integrally rotate with the shaft, and the friction ring is engaged so as to integrally rotate by friction force according to an energizing force of the coil spring. The coil spring is engaged so as to integrally rotate with the gear by inserting an end part 82A into an engaging hole 94 of the gear. Thus, a restraining force generated by the rotation of the gear is limited by the friction force between the coil spring and the friction ring and transmitted to the gear, resulting in reduced travel speed of the braked object.SELECTED DRAWING: Figure 4A

Description

  The present invention relates to a braking device.

  Various kinds of buildings, such as sliding doors that open and close by moving the door, swinging doors (so-called doors), and folding doors such as folding doors (folding doors) Some of these fittings have a closer function that closes the opening with the door by moving the door in the closing direction of the opening. When the door (sliding door) suspended on the hanger rail is moved in the opening direction of the opening, the closer accumulates the urging force, and the accumulated urging force moves the door in the closing direction along the hanger rail. Closer device that closes the opening by closing (closer), etc. Also, as the closing function provided in the sliding door, the hanger rail on which the door is suspended can be tilted so that the closed side of the opening is low. And the door is configured to move in the closing direction by its own weight and close the opening.

  Some of these sliding doors are provided with a braking device that reduces the moving speed of the door before the opening is fully closed. The braking device applies a rotational load corresponding to the rotational speed when a gear such as a pinion provided on the door meshes with a rack provided on the hanger rail before the door reaches the fully closed position. To slow down the door. Thereby, the door of a sliding door moves to a fully closed position gently, and stops.

  By the way, if the door is forced to move in the closing direction, the braking device applies a large rotational load to the gear when the gear meshes with the rack, and suddenly brakes the door. In the braking device, a large rotational load that suddenly brakes the door is generated, and the gear that meshes with the rack may be damaged by receiving a large impact. From here, a sliding door braking device provided with a torque limiter has been proposed as an overload prevention mechanism that limits the application of a rotational load to a gear that meshes with a rack and rotates (see, for example, Patent Document 1).

  In the torque limiter of Patent Document 1, a plurality of notches are formed on the inner peripheral surface of the inner rotor of the brake brake unit, and a small ball or pin (hereinafter referred to as a small ball) urged by a coil spring enters. The rotation center shaft provided with the gear (pinion) is engaged with the inner rotor to rotate integrally. As a result, the pinion is given a rotational load from the braking brake unit. The torque limiter also has a large torque greater than a predetermined value acting on the rotation center axis, so that the small spheres come out of the notch against the spring force of the coil spring, and the inner rotor and the rotation center axis rotate relative to each other. To do. Thus, in Patent Document 1, the pinion can be rotated without receiving a rotational load from the brake brake portion, and damage to parts due to the pinion receiving a large rotational load from the brake brake portion can be prevented.

JP 2002-339648 A

  However, in a torque limiter that is engaged by entering a small ball into the notch, the small ball enters and leaves the notch repeatedly while the inner rotor and the rotation center shaft are rotating relative to each other. It is. When the small ball enters the notch, the small ball collides with the inner surface of the notch because it is urged by the urging force of the coil spring, and a collision noise may be generated, and this collision is repeated, Noise will be generated when the sliding door is closed.

  The present invention has been made in view of the above-described facts, and provides a braking device that prevents noise from being generated when preventing damage or the like from occurring in a part or the like when braking an object to be braked. With the goal.

  In order to achieve the above object, a braking device according to a first aspect of the present invention includes a rotating body that is rotated according to the movement of an object to be braked and a rotating shaft that is rotated by a rotating force, and suppresses rotation of the rotating shaft. A restraining force generating means that generates a restraining force that increases as the rotational force increases, and the rotating body and the rotating shaft of the restraining force generating means are connected by a frictional force, Limiting means for limiting the suppression force transmitted to the rotating body by the frictional force.

  In the braking device according to claim 1, when the rotating body rotates according to the moving speed of the object to be braked, the suppressing force generating means generates a suppressing force according to the rotating speed of the rotating body, and the generated suppressing force. The force is transmitted to the rotating body via the limiting means, so that the rotating body decelerates the moving speed of the controlled object.

  The restricting means connects the rotating body and the suppression force generating means by frictional force, and when the suppression force exceeds the frictional force, a relative rotation is generated between the rotating body and the rotating shaft and transmitted to the rotating body. Limit the restraint force Therefore, the limiting means limits the suppression force transmitted to the rotating body without generating noise, and prevents the rotating body and the like from being damaged.

  In the braking device according to claim 2, the restricting unit is engaged with the urging unit and a frictional force generated by the urging force of the urging unit so as to rotate integrally with the urging unit. It includes a friction engaging member, and connects the rotating body and the rotating shaft of the restraining force generating means via the biasing means and the friction engaging member.

  According to a third aspect of the present invention, in the braking device, the restricting unit includes a gear, a friction ring provided as the friction engagement member, and supports the gear so as to be relatively rotatable, and the friction ring. And a coil spring provided as the urging means and wound around the outer periphery of the friction ring, the coil spring having one end portion of the gear. It may be inserted into an engagement hole formed in a side surface and engaged with the gear so as to rotate integrally therewith, and as described in claim 4, the limiting means includes a gear and the frictional engagement. A friction ring provided as a joint member, a shaft that supports the gear so as to be relatively rotatable and supports the friction ring so as to rotate integrally, and a biasing means provided on an outer peripheral portion of the friction ring. A coiled spring, and the coiled spring is housed together with the friction ring in a recess formed by projecting one end radially outward and opening on one side of the gear. And the one end is accommodated in an engaging groove formed continuously on the side surface of the gear radially outward from the recess, and is engaged with the gear so as to rotate integrally therewith. good.

  Further, in the braking device according to claim 5, the limiting means includes a gear provided as the friction engagement member, a disc spring provided as the biasing means, and the disc spring. A shaft that supports the gear so as to be relatively rotatable, and a friction member that is opposed to the disc spring and is engaged with the shaft so as to rotate integrally therewith, between the disc spring and the friction member The gear may be engaged with a frictional force generated by the urging force of the disc spring.

  Further, as described in claim 6, in the brake device according to any one of claims 3 to 5, the gear may be used as the rotating body. Further, in the braking device according to claim 7, the suppression force generation unit includes a coil that generates an induced electromotive force according to a rotation speed of the rotation shaft in a cycle synchronized with the rotation of the rotation shaft. A circuit that forms a closed circuit between the rotator and the coil, and generates an induced electromotive force according to the rotation of the rotating shaft in the coil, thereby generating the suppressing force on the rotating shaft; , May be included.

  According to the present invention, since the restraining force generated according to the rotation of the rotating body is limited by the frictional force, it is possible to prevent the rotating body from being damaged while obtaining high silence. Have

It is a perspective view of the principal part which shows an example of the sliding door which concerns on 1st Embodiment. It is the side view of the principal part which looked at the sliding door shown to FIG. 1A from the close direction side. It is a perspective view of the principal part of the braking device concerning a 1st embodiment. It is a circuit diagram of the principal part which shows an example of a braking part. It is a schematic perspective view of the principal part which shows the torque limiting part which concerns on 1st Embodiment. FIG. 4B is a schematic side view of the torque limiter shown in FIG. 4A along the line 4B-4B of the gear. It is a schematic perspective view of the principal part which shows the torque limiting part which concerns on 2nd Embodiment. It is a schematic sectional drawing in alignment with the 5B-5B line of the gear of the torque limiting part shown in FIG. 5A. It is a schematic perspective view of the principal part which shows the torque limiting part which concerns on 3rd Embodiment. It is a schematic sectional drawing in alignment with the 6B-6B line of the gear of the torque limiting part shown in FIG. 6A. It is a perspective view of the principal part of the brake device which concerns on 4th Embodiment. It is a schematic side view of the principal part which shows the torque limiting part which concerns on 4th Embodiment. It is a schematic perspective view of the principal part which shows an example of the folding door which concerns on 5th Embodiment.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
[First Embodiment]
1A and 1B show a sliding door 10 according to the first embodiment. The sliding door 10 includes a door 12 and is provided in an opening 16 formed in a wall 14 such as a building, and closes the opening 16 by the door 12. In the first embodiment, the door 12 of the sliding door 10 functions as an example of a braking object. In the following description, the upper side in the vertical direction is shown as an arrow UP.

  A hanger rail 18 is attached to the wall 14 above the opening 16. As for the hanger rail 18, the cross section along the direction which cross | intersects a longitudinal direction is formed in L shape, and one side of L shape is used as the base 18A, and the other side is used as the support part 18B. The hanger rail 18 is disposed so that the longitudinal direction thereof is along the upper end of the opening 16 on the wall 14 above the opening 16 (see FIG. 1A), and the base 18A is fixed to the wall 14. Further, the hanger rail 18 has a semicircular cross-section in which the tip end of the support portion 18B extending away from the wall portion 14 is bent upward and bent, and the bent tip is convex upward. A rail 20 is formed.

  In the sliding door 10, the door 12 is disposed below the support portion 18 </ b> B of the hanger rail 18. The sliding door 10 is provided with a bracket 22 on one end side in the longitudinal direction of the upper end surface of the door 12 and a bracket 24 on the other end side. In the brackets 22 and 24, a base plate 26A is fixed to the upper end surface of the door 12, and leg plates 26B are erected upward from the base plate 26A. In addition, the brackets 22 and 24 have a door wheel 28 rotatably attached to the surface of the leg plate 26B on the wall portion 14 side.

  As shown in FIG. 1B, the door 12 is suspended from the hanger rail 18 and supported by the doors 28 of the brackets 22 and 24 being placed on the rail portion 20 of the hanger rail 18. Further, the sliding door 10 shown in FIG. 1A has an opening portion from a closed position where the door 12 closes the entire area of the opening portion 16 by rolling the door wheel 28 along the longitudinal direction (opening / closing direction) on the rail portion 20. It is moved in the range up to the open position that opens the entire 16 area. As the sliding door 10, a known general configuration can be applied. In the first embodiment, a right-opening sliding door 10 is applied as an example. In the following description, the left side of the drawing in FIG. An opening direction of the opening 16 is indicated by an arrow OP.

  Here, the sliding door 10 applied to the first embodiment has a closer function in which the door 12 naturally (automatically) moves in the closing direction to close the opening 16. As an example, the closer function used for the sliding door 10 is configured such that the hanger rail 18 that supports the door 12 is inclined and fixed to the wall 14 so that the closing direction side is lower than the opening direction side. . In the sliding door 10, the door wheel 28 naturally rolls in the closing direction along the inclination of the rail portion 20 of the hanger rail 18, and the door 12 naturally moves to the closed position to close the opening 16.

  In the first embodiment, the sliding door 10 has a structure in which the door 12 naturally moves to the closed position as the closing function formed by the closing function means. It is not limited. For example, the closer function may include a so-called closer (closer device) that moves the door 12 to a closed position by a driving force. For the closer, a known configuration in which any one of an urging force such as a spring, oil pressure, air pressure, or the like is used as a driving force can be applied. For example, in a closer using an urging force, a driving portion provided with urging means such as a coil spring that generates an urging force is provided at the end of the hanger rail 18 in the closing direction, and the tip of the wire drawn from the driving portion is bracketed. The structure etc. engaged with 22 are applied. In the closer function, the urging force is accumulated in the urging means when the door 12 is moved in the opening direction of the opening 16 and the wire is pulled out, and the urging force accumulated when the hand is released from the door 12. Thus, the wire is wound up. As a result, the door 12 moves in the closing direction and closes the opening 16.

  On the other hand, the sliding door 10 includes a braking device 30. As an example, the braking device 30 is attached to the leg plate 26 </ b> B of the bracket 22 on the closing direction side of the door 12. In the first embodiment, the braking device 30 functions as an example of a braking device.

  The braking device 30 is provided with a gear 32 at a position above the support portion 18B of the hanger rail 18 on the wall portion 14 side. Moreover, the rack 34 corresponding to the gear 32 of the braking device 30 is attached to the upper surface of the support part 18B. The rack 34 has a longitudinal direction arranged along the longitudinal direction of the hanger rail 18, and is attached so as to be biased toward the closing direction side of the hanger rail 18. In the first embodiment, the gear 32 functions as an example of a rotating body.

  The rack 34 is in a state where the gear 32 of the braking device 30 is engaged and the gear 32 is engaged until the door 12 reaches the closed position when the door 12 reaches a preset position before the closed position. Thereby, when the door 12 having opened the opening 16 moves to the closed position, the sliding door 10 reaches a predetermined position before the closed position, and the gear 32 of the braking device 30 engages with the rack 34. The door 12 moves to the closed position with the gear 32 engaged with the rack 34. The gear 32 meshes with the rack 34, so that a rotational speed corresponding to the moving speed of the door 12 and a rotational force (rotating torque) corresponding to the moving speed of the door 12, the weight of the door 12, and the like are applied. The braking device 30 decelerates the moving speed of the door 12 by applying a braking torque, which is a rotational force in a direction to suppress the rotation, to the gear 32 that rotates in mesh with the rack 34. The braking device 30 gently stops the door 12 at the closed position by applying to the gear 32 a braking torque that increases as the rotational speed increases according to the rotational speed of the gear 32.

  The sliding door 10 is configured such that the door 12 is braked when the door 12 is closer to the open position than the preset position because the gear 32 meshes with the rack 34 at the preset position before the closed position. It can move without receiving a load such as torque. In the following description, the rotation direction of the gear 32 that meshes with and rotates with the rack 34 when the door 12 moves in the closing direction is indicated by an arrow R direction.

  FIG. 2 shows the braking device 30. The braking device 30 includes a housing 36. As shown in FIG. 1A, in the braking device 30, for example, the housing 36 is fixed to the leg plate 26 </ b> B of the bracket 22 and is moved integrally with the door 12. As shown in FIG. 2, the braking device 30 includes a transmission unit 38 and a braking unit 40. As an example, the transmission unit 38 is formed with a gear train of a plurality of gears, and transmits the rotational speed of the gear 32 according to the movement of the gear 32 in the closing direction of the door 12 to the braking unit 40. The braking unit 40 generates a rotational load that increases as the rotational speed increases in accordance with the rotational speed of the gear 32 transmitted via the transmission unit 38.

  The housing 36 is formed with a first recess 42 that is open on the surface opposite to the gear 32, and a second recess 44 that is open at the bottom of the first recess 42. In the housing 36, the transmission portion 38 is accommodated in the second recess 44 and closed by the partition plate 46, and the braking portion 40 is accommodated in the first recess 42 and closed by the cover 48.

  The transmission unit 38 includes shafts 50A, 50B, and 50C. The housing 36 has support holes 44A, 44B, 44C formed in the bottom surface of the second recess 44, and the partition plate 46 is supported by the support holes 46A, 46B so as to be coaxial with the support holes 44A, 44B, 44C of the housing 36. , 46C are formed. One end of the shaft 50A in the axial direction is inserted into the support hole 44A and protrudes from the housing 36, and the other end is inserted into the support hole 46A. The shaft 50B has one end inserted into the support hole 44B and the other end inserted into the support hole 46B. The shaft 50C has one end inserted into the support hole 44C and the other end inserted into the support hole 46C. As a result, the transmission portion 38 is supported so that the shafts 50A, 50B, and 50C are spanned between the bottom surface of the second recess 44 and the partition plate 46 so that their axes are parallel to each other, and are rotatable. .

  In the transmission portion 38, the gear 32 is provided on the shaft 50 </ b> A protruding from the housing 36, and the shaft 50 </ b> A can rotate together with the gear 32 by rotating the gear 32 in the closing direction (arrow R direction). The shaft 50A is attached so that the gear 52 rotates integrally. A two-stage gear 54 is attached to the shaft 50B, and an intermediate gear 56 is attached to the shaft 50C. The two-stage gear 54 is formed by a gear 54A having a smaller diameter than the gear 52 and a gear 54B having a smaller diameter than the gear 54A. The intermediate gear 56 has a smaller diameter than the intermediate gear 56 and is a two-stage gear in which a gear (not shown) on the back side (the back side of the paper surface in FIG. 2) of the intermediate gear 56 is integrated. Further, a gear (not shown) on the back side of the intermediate gear 56 (the back side in FIG. 2) has a smaller diameter than the gear 52, and the gear 54 </ b> B of the two-stage gear 54 has a smaller diameter than the intermediate gear 56. The large diameter and the small diameter of the gear indicate the difference in the outer diameter and also the difference in the number of teeth, and the large diameter gear indicates that the number of teeth is larger than that of the small diameter gear.

  In the transmission portion 38, the gear 52 of the shaft 50 </ b> A meshes with a small-diameter gear (not shown) provided on the back side of the intermediate gear 56 of the shaft 50 </ b> C, and the rotation of the shaft 50 </ b> A is increased and transmitted to the intermediate gear 56. Further, in the transmission portion 38, the intermediate gear 56 and the gear 54B of the two-stage gear 54 of the shaft 50B are engaged with each other, and the rotation of the intermediate gear 56 is increased to rotate the gear 54A of the two-stage gear 54. Thereby, the transmission unit 38 forms a gear train that transmits the rotation of the shaft 50A to the gear 54A, and the rotation speed of the gear 32 is increased and transmitted to the gear 54A.

  As an example, the braking unit 40 includes a generator 58 and a braking circuit unit 60. The generator 58 includes a rotor shaft 58A, and when the rotor shaft 58A of the generator 58 rotates, the braking circuit unit 60 generates a rotational load that increases as the rotational speed increases according to the rotational speed. The braking device 30 imparts a braking torque, which is a rotational force in a direction to suppress the rotation, to the gear 32 when the rotational load generated in the generator 58 is transmitted to the gear 32. In the first embodiment, the generator 58 and the braking circuit unit 60 function as an example of a suppression force generation unit, the generator 58 functions as an example of a rotator, and the rotor shaft 58A functions as an example of a rotation shaft.

  The partition plate 46 is formed with an insertion hole 46D, and the generator 58 is attached to the partition plate 46 with the tip end of the rotor shaft 58A inserted into the insertion hole 46D of the partition plate 46. Moreover, the braking circuit unit 60 is attached to the partition plate 46, for example, and is connected to the generator 58 by wiring (not shown).

  The generator 58 has a pinion 62 attached to the tip of the rotor shaft 58A protruding into the second recess 44 from the insertion hole 46D of the partition plate 46, and the pinion 62 meshes with the gear 54A of the two-stage gear 54 of the transmission unit 38. ing. Thus, in the braking device 30, the rotation of the gear 32 is transmitted to the rotor shaft 58A of the generator 58 via the transmission unit 38, and the rotor shaft 58A is rotated. At this time, the generator 58 is engaged with the gear 52 of the transmission portion 38 and a gear (not shown) having a smaller diameter than the gear 52, and the intermediate gear 56 and the gear 54B having a smaller diameter than the intermediate gear 56 are engaged with each other. The rotational speed of 32 is increased and the rotor shaft 58A is rotated.

  As an example, the generator 58 is a permanent magnet field motor. Examples of the permanent magnet field type motor include a DC motor (DC motor), a stepping motor, or an AC motor (AC motor). The permanent magnet field motor has a permanent magnet provided on the rotor side. There are some, and a permanent magnet provided on the stator side. Further, the motor includes an outer rotor type and an inner rotor side. As the generator 58 applied as a rotator, any motor may be applied as long as it is a permanent field type motor. In the first embodiment, a three-phase motor (three-phase AC motor) is used as an example of the generator 58. ) Is used.

  FIG. 3 shows an example of connection between the generator 58 and the braking circuit unit 60. The generator 58 includes a permanent magnet disposed on the rotor shaft 58A, and a U-phase coil 64U, a V-phase coil 64V, and a W-phase coil 64W (hereinafter collectively referred to as a three-phase winding on a stator not shown). A coil 64).

  The braking circuit unit 60 includes a braking circuit 60A. In the generator 58, each of the coils 64 is connected to the braking circuit 60A, and a closed circuit is formed between each of the coils 64 and the braking circuit 60A. As an example, each coil 64 of the generator 58 is connected to the braking circuit 60A so that the coils 64U, 64V, and 64W are Y-connected (star connected). Note that a closed circuit refers to a circuit that has no external power input and no external power output. Further, each coil 64 of the generator 58 and the braking circuit 60A are not limited to the Y connection, and any circuit that forms a closed circuit with the braking circuit 60A, such as a Δ connection (delta connection) or a connection for each coil 64. Connection methods can also be applied.

  The braking circuit 60A includes, as an example, a rectifier circuit 68 and a resistance circuit 70 connected to the rectifier circuit 68. The closed circuit formed by the coils 64 of the generator 58 and the braking circuit 60A in the first embodiment functions as an example of a suppression circuit. In the generator 58, an electromotive force is generated in each coil 64 as the rotor shaft 58A rotates, and a current i corresponding to the electromotive force generated by the coil 64 flows between each coil 64 and the braking circuit 60A.

  The rectifier circuit 68 is formed by connecting a plurality of diodes 72 as a bridge, for example, and rectifies an alternating current (alternating current) generated by the coil 64 of the generator 58. In the first embodiment, a Schottky barrier diode is used as an example of the diode 72. The resistance circuit 70 is formed by a variable resistor 74 using a semi-fixed resistor (trimmer) and a transistor 76. As an example, the transistor 76 is an npn bipolar transistor. In the resistance circuit 70, one of the terminals 74 </ b> A and 74 </ b> C of the variable resistor 74 whose resistance values are all resistance values is connected to the positive side of the rectifier circuit 68, and the other is connected to the negative side of the rectifier circuit 68. In the resistor circuit 70, the collector C of the transistor 76 is connected to the positive side of the rectifier circuit 68, the emitter E is connected to the negative side of the rectifier circuit 68, and the base B is the slider of the variable resistor 74. It is connected to the terminal 74B. As a result, a current i corresponding to the electromotive force (inductive electromotive force) generated in the coil 64 flows between each coil 64 of the generator 58 and the braking circuit 60 </ b> A, and the current i slides on the variable resistor 74. It can be adjusted according to the position of the child.

  In the braking unit 40, a current flows through each coil 64 by an induced electromotive force generated when the rotor shaft 58 </ b> A of the generator 58 using a permanent magnet field type motor rotates. As a result, the generator 58 generates a Lorentz force between the rotor shaft 58 </ b> A and each coil 64. In the generator 58 provided with a permanent magnet on the rotor shaft 58A, the Lorentz force is a force that suppresses the rotation of the rotor shaft 58A. The braking unit 40 acts as a braking torque that suppresses the rotation of the gear 32 when the Lorentz force generated by the generator 58 is increased via the transmission unit 38 and transmitted to the gear 32. In the following description, Lorentz force generated in the generator 58 will be described as braking torque.

  The Lorentz force generated by the generator 58 affects the current i flowing through the closed circuit including the coils 64U, 64V, and 64W, and increases as the current i increases. The current i affects the rotational speed of the rotor shaft 58A, and the current i increases as the rotational speed of the rotor shaft 58A, that is, the rotational speed of the gear 32 increases. Further, the current i changes according to the rotation of the rotor shaft 58A and the position of the slider of the variable resistor 74 provided in the resistance circuit 70 (base voltage of the transistor 76). From here, the braking unit 40 adjusts the resistance value (slider position) of the variable resistor 74 provided in the resistance circuit 70, for example, braking against the moving speed of the door 12 (rotational speed of the gear 32). The torque change characteristic is adjusted.

  By the way, the braking device 30 is provided with a torque limiting unit 80. 4A and 4B show the torque limiting unit 80 according to the first embodiment. In the first embodiment, the torque limiting unit 80 functions as an example of a limiting unit. The torque limiter 80 is provided between the gear 32 that rotates as the door 12 moves and the rotor shaft 58A of the generator 58 that generates a braking torque in accordance with the rotational speed of the gear 32. In the first embodiment, as an example, the torque limiting unit 80 is provided in the gear 32 so that the braking torque transmitted to the gear 32 is limited between the gear 32 and the shaft 50A.

  The torque limiting unit 80 includes a coil spring 82, a friction ring 84, and a one-way clutch 86. In the first embodiment, the coil spring 82 functions as an example of an urging means, the friction ring 84 functions as an example of a friction engagement member, and the one-way clutch 86 functions as an example of an intermittent means.

  As shown in FIG. 4A, the one-way clutch 86 is formed in a cylindrical shape, and the shaft 50A of the transmission unit 38 is inserted therein. The one-way clutch 86 rotates integrally with the shaft 50A by rotating in the closing direction (arrow R) direction of the gear 32, and rotates relative to the shaft 50A by rotating in the opening direction of the gear 32.

  In the one-way clutch 86, a plurality of key grooves 90 (three as an example in the first embodiment) are formed on the outer peripheral surface along the axial direction. The friction ring 84 is formed in a cylindrical shape, and protrudes radially inward and extends in the axial direction corresponding to each of the key grooves 90 of the one-way clutch 86 on the inner peripheral surface. A strip 92 is formed along the axial direction. The one-way clutch 86 is inserted into the axial center portion of the friction ring 84, and the protruding portion 92 of the friction ring 84 enters the key groove 90, so that the friction ring 84 and the one-way clutch 86 are engaged so as to rotate together. The By providing the one-way clutch 86, the torque limiting unit 80 prevents the rotation of the gear 32 from being transmitted to the rotor shaft 58A of the generator 58 and generating a rotational load when the door 12 is moved in the opening direction. ing.

  In the first embodiment, a torsion coil spring (torsion spring) is used as an example of the coil spring 82. A coil spring 82 is wound around the outer periphery of the friction ring 84, and the outer periphery is tightened by the biasing force of the coil spring 82. The friction ring 84 is engaged with the coil spring 82 by a biasing force (pressing force) received from the coil spring 82, and is engaged with the coil spring 82 by the friction force between the friction ring 84 and the coil spring 82. ing. The coil spring 82 wound around the friction ring 84 has an end 82A on the gear 32 side projecting along the axial direction.

  On the other hand, the gear 32 provided with the torque limiting portion 80 is formed with a bottomed recess 88 opened on one side surface in the axial direction. The recess 88 has an inner diameter larger than the outer diameter of the coil spring 82 and is opened in a circular shape that is coaxial with the gear 32. In the gear 32, a torque limiting portion 80 (coil spring 82 assembled to the friction ring 84 and the one-way clutch 86) is accommodated in the recess 88. Further, the gear 32 is formed with a through-hole 88A into which the shaft 50A is inserted at a position that becomes an axial center portion on the bottom surface of the recess 88. In addition, an engagement hole 94 into which the end portion 82 </ b> A of the coil spring 82 housed in the recess 88 is inserted is formed on the bottom surface of the recess 88 of the gear 32.

  In the torque limiting portion 80 accommodated in the recess 88 of the gear 32, the end portion 82A of the coil spring 82 is inserted into the engagement hole 94 formed in the bottom surface of the recess 88, and the gear 32 and the coil spring 82 are integrated. Engaged to rotate. As a result, the gear 32 is supported via the torque limiting portion 80 so as to be rotatable integrally with the shaft 50A. As shown in FIG. 4B, the gear 32 is formed with a widened portion 32 </ b> A in which the intermediate portion in the radial direction is widened, so that the peripheral portion of the engagement hole 94 receives from the end portion 82 </ b> A of the coil spring 82. Sufficient strength can be obtained.

  In the torque limiting unit 80, the rotational force (rotational force in the direction opposite to the rotational direction of the gear 32) according to the braking torque received by the friction ring 84 via the shaft 50A exceeds the frictional force with the coil spring 82. As a result, the coil spring 82 and the friction ring 84 rotate relative to each other. At this time, the torque limiting unit 80 applies a braking torque corresponding to the dynamic friction force to the gear 32 by applying a dynamic friction force between the coil spring 82 and the friction ring 84.

  The gear 32 is attached with a cover member 96 that closes the opening of the recess 88. The cover member 96 is formed with an insertion hole 96A through which the shaft 50A is inserted, and a plurality of through holes 96B are formed at the peripheral edge. Further, a plurality of screw holes 88 </ b> B each corresponding to the through hole 96 </ b> B of the cover member 96 are formed in the gear 32 at the periphery of the recess 88. The cover member 96 is fixed to the gear 32 by screwing a screw 96 </ b> C inserted into the through hole 96 </ b> B into the screw hole 88 </ b> B of the gear 32, and closes the recess 88 of the gear 32.

  Here, the torque limiter 80 uses a coil spring 82 manufactured so as to obtain a preset frictional force with the friction ring 84. As a result, the braking device 30 functions as a torque limiter that applies a braking torque according to the rotation speed to which the gear 32 is applied to the gear 32 and limits the braking torque to be applied to the gear 32.

The operation of the first embodiment will be described below.
In the sliding door 10 applied to the first embodiment, by pulling the door 12 in the opening direction, the door wheel 28 provided on the door 12 rolls on the rail portion 20 of the hanger rail 18, and the door 12 opens. And the opening 16 is opened. Further, the sliding door 10 has a closer function, and when the hand is released from the door 12 in a state where the opening portion 16 is opened, the door wheel 28 naturally moves on the rail portion 20 along the inclination of the rail portion 20. It rolls and the door 12 moves in the closing direction to close the opening 16.

  Here, the sliding door 10 is provided with a braking device 30 on the door 12, and when the door 12 moving in the closing direction reaches a preset position before the closing position, the gear 32 of the braking device 30 is hangered. It meshes with a rack 34 provided on the rail 18 and rotates. In the braking device 30, the gear 32 is rotated at a rotational speed and a rotational force corresponding to the moving speed of the door 12 by the gear 32 meshing with the rack 34. In the braking device 30, the rotation of the gear 32 is transmitted to the shaft 50 </ b> A of the transmission unit 38 via the torque limiting unit 80, and the rotor shaft 58 </ b> A of the generator 58 is rotated at a rotation speed corresponding to the rotation speed of the gear 32.

  In the generator 58 using the permanent magnet field type motor, a Lorentz force serving as a rotational load of the rotor shaft 58A is generated according to the rotation speed of the rotor shaft 58A when the rotor shaft 58A rotates. In the braking device 30, the Lorentz force generated by the generator 58 is transmitted to the gear 32 as a braking torque. As a result, the sliding door 10 is decelerated at a speed at which the gear 32 moves while meshing with the rack 34, that is, a moving speed in the closing direction of the door 12, and the door 12 gently stops at the closed position and opens 16. Close.

  Further, the sliding door 10 is moved in the closing direction at a moving speed faster than the moving speed by the closer function when the door 12 is pulled in the closing direction. In this case, when the gear 32 meshes with the rack 34, the gear 32 is rotated at a higher rotational speed than when the door 12 is moved by the closer function. The braking device 30 generates a larger braking torque as the rotational speed increases in accordance with the rotational speed of the gear 32. Thus, even when the door 12 moves in the closing direction at a high movement speed, such as when the door 12 is pulled in the closing direction, the braking device 30 can surely decelerate the door 12 and gently stop at the closed position. .

  By the way, the sliding door 10 moves in the closing direction at a faster moving speed (hereinafter referred to as a moving speed faster than necessary) than when the door 12 is simply pulled by pulling the door 12 stronger than necessary. When the door 12 moves in the closing direction at a faster moving speed than necessary, the gear 32 meshes with the rack 34, whereby a high rotational speed and a large rotational force (rotational torque) are applied from the rack 34 to the gear 32. The That is, the gear 32 receives a large rotational force when meshed with the rack 34, and this rotational force is transmitted to the rotor shaft of the generator 58. As a result, the generator 58 generates an inertial force that accompanies the moment of inertia of the rotor shaft 58A, as the rotor shaft 58A rotates rapidly upon receiving a rotational force. The inertial force generated in the generator 58 is increased by the transmission unit 38 and transmitted to the gear 32 so that the gear 32 engaged with the rack 34 is prevented from rotating when the gear 32 receives a sudden rotational force from the rack 34. Works.

  Accordingly, when the door 12 is pulled more strongly than necessary, the gear 32 immediately after meshing with the rack 34 is prevented from rotating by the inertia force of the generator 58, and the gear 32 collides with the rack 34. Become. As a result, the sliding door 10 is damaged in parts such as the rack 34 meshing with the gear 32 in the gear 32, or the gear 32 is lifted from the rack 34, or the door 28 is detached from the rail portion 20 and the door 12 is hanger railed. It will come off from 18.

  Here, the torque limiting unit 80 provided in the braking device 30 transmits the rotation of the gear 32 to the rotor shaft 58A of the generator 58 by the frictional force between the coil spring 82 and the friction ring 84, and is generated by the generator 58. The braking torque is transmitted to the gear 32. The coil spring 82 and the friction ring 84 rotate integrally because the frictional force is larger than the rotational force generated by the inertial force generated by the generator 58 or the braking torque.

  In the torque limiting unit 80, the force in the direction of preventing the rotation of the gear 32 such as the braking torque generated by the generator 58 and the rotational force due to the inertial force exceeds the frictional force between the coil spring 82 and the friction ring 84. Then, the coil spring 82 and the friction ring 84 rotate relative to the frictional force (static frictional force). At this time, a frictional force (dynamic frictional force) acts between the coil spring 82 and the friction ring 84, whereby the friction ring 84 rotates following the coil spring 82 that rotates integrally with the gear 32. Further, the gear 32 receives a braking torque corresponding to a preset frictional force (dynamic frictional force) between the coil spring 82 and the friction ring 84 which is smaller than the braking torque generated by the generator 58.

  Therefore, even if the door 12 moves in the closing direction at a faster moving speed than necessary, the sliding force 10 causes the inertial force and braking torque received by the gear 32 to reduce the frictional force between the coil spring 82 and the friction ring 84. Since it is suppressed so that it does not exceed, it is prevented that the gear 32, the rack 34, etc. are damaged, and the door 12 is prevented from being detached from the hanger rail 18. Further, since the braking device 30 applies a braking torque corresponding to the frictional force to the gear 32, the moving speed of the door 12 is reliably decelerated. Further, when the moving speed of the door 12 is decelerated, the braking device 30 causes the coil spring 82 and the friction ring 84 to rotate together by the frictional force, so that the gear 32 has a braking torque corresponding to the decelerated moving speed of the door 12. Receive.

  Furthermore, since the torque limiting unit 80 limits the braking torque generated by the generator 58 by the frictional force, the braking applied to the gear 32 because the door 12 moves in the closing direction at a moving speed faster than necessary. No noise is generated even when the torque is limited. Therefore, the braking device 30 provided with the torque limiting unit 80 can obtain high silence.

  In the first embodiment, the generator 58 and the braking circuit unit 60 are used in the braking unit 40 provided as the suppression force generating unit. However, the braking circuit unit 60 uses the Lorentz force according to the rotational speed of the rotor shaft 58A. Any configuration that can generate (rotational load) in the generator can be applied. In the first embodiment, the Lorentz force generated in the generator 58 is used as the suppression force. However, the suppression force generation means is not limited to the generator 58, and an arbitrary configuration such as a pneumatic type or a hydraulic type may be applied. Can do. In the first embodiment, by using the generator 58 as the suppression force generating means, it is not necessary to prevent oil leakage when the hydraulic type is applied, and air intake / exhaust noise when the pneumatic type is applied. It has become.

[Second Embodiment]
Next, a second embodiment will be described. The basic configuration of the second embodiment is the same as that of the first embodiment. In the second embodiment, the same functional parts as those of the first embodiment are described in the first embodiment. The same reference numerals as those in FIG.

  5A and 5B show a torque limiting unit 100 according to the second embodiment. The torque limiter 100 is used in place of the torque limiter 80 of the braking device 30 of the first embodiment. The torque limiting unit 100 uses a gear 102 instead of the gear 32 and uses a coil spring 104 instead of the coil spring 82. In the second embodiment, the torque limiting unit 100 functions as an example of a limiting unit, the gear 102 functions as an example of a rotating body, and the coil spring 104 functions as an example of an urging unit.

  In the second embodiment, a torsion coil spring is used as an example of the coil spring 104. One end 104 </ b> A of the coil spring 104 protrudes outward in the radial direction of the coil spring 104. Further, the gear 102 has an end surface (for example, an end surface on the housing 36 side) facing the coil spring 104 and an outer diameter of the coil spring 104 (an outer diameter not including the end portion 104A protruding from the coil spring 104). Correspondingly, a bottomed recess 106 opened in a circular shape is formed. Further, the gear 102 is formed with a groove-like engaging portion 106 </ b> A that is formed outward from the concave portion 106 in the radial direction. In the second embodiment, the engaging portion 106A functions as an example of an engaging groove.

  In the torque limiting unit 100, the coil spring 104 is accommodated in the recess 106 of the gear 102, and the end 104A of the coil spring 104 is inserted into the engaging portion 106A, so that the coil spring 104 rotates integrally with the gear 102. Is engaged. Further, a through hole 108 is formed in the bottom surface of the recess 106 in the gear 102. The gear 102 has the shaft 50A of the transmission portion 38 inserted into the through hole 108 and is rotatable with respect to the shaft 50A, and can rotate integrally with the frictional force between the friction ring 84 and the coil spring 104.

  The gear 102 may be rotatably supported by the shaft 50A by providing a bearing in the through hole 108. The gear 102 is attached with a cover member 96 that closes the opening of the recess 106. The cover member 96 is fixed to the gear 102 by screwing the screw 96 </ b> C inserted into the through hole 96 </ b> B into the screw hole 88 </ b> B of the gear 102, and closes the recess 106 of the gear 102.

  The torque limiting unit 100 formed in this way is applied with a braking torque that generates a rotational force that exceeds the frictional force between the friction ring 84 and the coil spring 104 on the gear 102, so that the friction ring 84 and the coil The spring 104 is relatively rotated. Thus, the torque limiting unit 100 limits the inertial force and braking torque transmitted to the gear 102 meshing with the rack 34 so as not to exceed the frictional force between the friction ring 84 and the coil spring 104.

  Therefore, since the torque limiting unit 100 limits the braking torque transmitted to the gear 102, the door 12 is moved in the closing direction at a speed faster than necessary, so that a large inertia force is applied to the gear 102 meshing with the rack 34. Even if it acts, the rack 34 and the gear 102 are prevented from being damaged, and the door 12 is prevented from being detached from the hanger rail 18. In addition, since the torque limiting unit 100 applies a braking torque limited by frictional force to the gear 102, the moving speed of the door 12 can be surely reduced, and when the moving speed of the door 12 is reduced, the gear 102 And the shaft 50A are integrally rotated by frictional force, and the door 12 can be gently stopped at the closed position. Further, since the torque limiting unit 100 limits the braking torque generated by the generator 58 by the frictional force, even if the braking torque is limited because the door 12 moves in the closing direction at a faster moving speed than necessary, It does not generate noise.

  On the other hand, as shown in FIG. 4A, the torque limiting portion 80 applied to the first embodiment projects the end portion 82A of the coil spring 82 engaged with the gear 32 in the axial direction. The widened portion 32A is formed in the upper portion to increase the thickness along the axial direction. For this reason, the gear 32 requires a mounting space corresponding to its thickness.

  On the other hand, as shown in FIG. 5B, the torque limiting unit 100 according to the second embodiment is configured such that the end 104 </ b> A of the coil spring 104 engaged with the gear 102 is moved outward in the radial direction of the gear 102. Is heading to. As a result, the gear 102 provided with the torque limiting unit 100 can be thinner in the axial direction than the gear 32, can save more space than the gear 32, and can be arranged in a narrow space.

  That is, in the torque limiting portion 80, since the end portion 82A of the coil spring 82 is inserted into the engagement hole 94 formed in the bottom surface of the recess 88 of the gear 32 and engaged, the gear 32 meshes with the rack 34. The load concentrates on the peripheral edge of the engagement hole 94 that engages with the end 82A of the coil spring 82. For this reason, the gear 32 is formed with a widened portion 32 </ b> A, and the thickness along the axial direction (thickness of the bottom surface) is increased. Since the torque limiting portion 100 is engaged with the end portion 104A of the coil spring 104 accommodated in the engaging portion 106A formed on the gear 102, the gear 102 is more in the axial direction than the gear 32. The thickness can be reduced.

[Third Embodiment]
Next, a third embodiment will be described. The basic configuration of the third embodiment is the same as that of the first embodiment. In the third embodiment, the same functional parts as those in the first or second embodiment are given the same reference numerals as those in the first or second embodiment, and detailed description thereof is omitted. .

  6A and 6B show a torque limiting unit 110 according to the third embodiment. The torque limiter 110 is used in place of the torque limiter 80 of the braking device 30 of the first embodiment. The torque limiting unit 110 uses a gear 112 instead of the gear 32. Furthermore, in the first and second embodiments, the coil springs 82 and 104 are used as the biasing means, but in the third embodiment, the disc spring 114 is used as another example of the biasing means. In the third embodiment, the torque limiting unit 110 functions as an example of a limiting unit, the gear 112 functions as an example of a rotating body, and the disc spring 114 functions as an example of a biasing unit.

  The gear 112 of the torque limiting portion 110 has an insertion hole in which one end face in the axial direction is formed with a recess 116 that is circularly opened according to the outer diameter of the disc spring 114, and the shaft 50 </ b> A is inserted into the bottom surface of the recess 116. 118 is formed. In the gear 112, the disc spring 114 is accommodated in the recess 116. As an example, the torque limiting portion 100 is provided with two disc springs 114 in pairs, the inner ring portions 114 </ b> A are in contact with each other, and the outer ring portion 114 </ b> B of one disc spring 114 is on the bottom surface of the recess 116 of the gear 112. It contacts and is accommodated in the recess 116.

  As shown in FIGS. 6A and 6B, the torque limiting portion 110 is disposed so as to be relatively rotatable by inserting a cylindrical ring 124 into a circular hole (not shown) opened in the inner ring portion 114A of the pair of disc springs 114. Has been. The ring 124 is connected to one end side in the axial direction so that a circular friction plate 126 whose outer diameter corresponds to the outer diameter of the outer ring portion 114B of the disc spring 114 rotates integrally. Further, as shown in FIG. 6A, the ring 124 has a plurality of protruding ridges 92 formed on the inner peripheral surface, and the protruding ridges 92 enter the key grooves 90 of the one-way clutch 86 inserted into the ring 124. 86 is engaged so as to rotate integrally. In the fourth embodiment, the friction plate 126 functions as an example of a friction engagement member.

  The gear 112 includes a cover member 120 that closes the opening of the recess 116. For example, the cover member 120 has an insertion hole 120 </ b> A formed in an axial center portion. As shown in FIG. 6A, the cover member 120 has a plurality of through holes 120B formed in the outer peripheral portion, and the gear 112 has a screw hole 112A corresponding to the through hole 120B of the cover member 120. The cover member 120 is fixed to the gear 112 by screwing a screw 120 </ b> C inserted into the through hole 120 </ b> B into the screw hole 112 </ b> A of the gear 112.

  As shown in FIG. 6B, the torque limiting portion 110 inserted into the recess 116 of the gear 112 abuts against the friction plate 126 formed on the ring 124 by the inner surface of the cover member 120 that closes the recess 116, so that the friction plate A pair of disc springs 114 are compressed between 126 and the bottom surface of the recess 116. The pair of disc springs 114 are capable of rotating together with the ring 112 provided with the gear 112 and the friction plate 126 by an urging force generated by being compressed between the bottom surface of the recess 116 of the gear 112 and the friction plate 126. Is engaged.

  The torque limiting unit 110 is inserted into the insertion hole 120 </ b> A formed in the cover member 120 and the one-way clutch 86 in the shaft 50 </ b> A of the transmission unit 38. As a result, the torque limiting unit 110 is configured such that the gear 112 is rotatably supported by the shaft 50A, and the frictional force between the bottom surface of the recess 116 of the gear 112 and the disc spring 114, the disc spring 114 and the friction plate 126 , And the friction force between the friction plate 126 and the inner surface of the cover member 120, the shaft 50A can rotate integrally. In the third embodiment, as an example, the friction force between the disc spring 114 and the friction plate 126 is made larger than the friction force between the inner surface of the cover member 120 and the friction plate 126, and the disc spring is used. The friction force between the disc spring 114 and the bottom surface of the recess 116 of the gear 112 is made larger than the friction force between the disc spring 114 and the friction plate 126, and the friction force between the disc spring 114 and the friction plate 126 is increased. The braking torque is limited.

  When the door 12 is moved in the closing direction and the gear 112 is engaged with the rack 34 and the gear 112 is rotated in the closing direction, the torque limiting unit 110 is caused by the frictional force between the disc spring 114 and the friction plate 126. The rotation of the gear 112 in the closing direction (arrow R direction) is transmitted to the shaft 50A. As a result, the rotation of the gear 112 is transmitted to the rotor shaft 58A of the generator 58, and the generator 58 generates an inertial force or a braking torque according to the rotation speed of the gear 112. Further, the torque limiting unit 110 counteracts the frictional force when the rotational force due to the braking torque transmitted to the shaft 50A exceeds the frictional force (static frictional force) between the disc spring 114 and the friction plate 126. 114 and the friction plate 126 rotate relative to each other. At this time, the gear 112 receives an inertial force or a braking torque corresponding to a frictional force (dynamic frictional force) between the disc spring 114 and the friction plate 126.

  Thus, even if the door 12 of the sliding door 10 moves in the closing direction at an unnecessarily high moving speed, the torque limiting unit 110 applies the inertia force of the generator 58 received by the gear 112 when meshing with the rack 34 to the disc spring 114. And the friction plate 126 is suppressed so as not to exceed the friction force. Further, the torque limiting unit 110 is configured to reduce the braking torque generated in the gear 112 meshing with the rack 34 between the disc spring 114 and the friction plate 126 even when the door 12 of the sliding door 10 moves in the closing direction at a moving speed faster than necessary. It suppresses to the braking torque according to the friction force between. Therefore, the torque limiting unit 110 prevents the rack 34, the gear 112, and the like from being damaged even if the door 12 of the sliding door 10 moves in the closing direction at a higher moving speed than necessary, and the door 12 is hanger rail. 18 is prevented from coming off. Further, since the torque limiting unit 110 applies a braking torque according to the frictional force to the gear 112, the moving speed of the door 12 can be surely decelerated, and the moving speed of the door 12 is decelerated. And the pair of disc springs 114 rotate together by frictional force. Thereby, the door 12 is gently stopped at the closed position.

  Further, since the torque limiting unit 110 limits the braking torque transmitted to the gear 112 by the frictional force between the disc spring 114 and the friction plate 126, the door 12 is closed in the closing direction at a faster moving speed than necessary. No noise is generated when moving to. In the third embodiment, the disc spring 114 and the friction plate 126 are accommodated in the recess 116 formed in the gear 112. However, the present invention is not limited to this, and the recess 112 is not formed in the gear 112. A configuration in which the disc spring 114 is compressed with the friction plate 126 may be applied.

[Fourth Embodiment]
Next, a fourth embodiment will be described. The basic configuration of the fourth embodiment is the same as that of the first embodiment. In the fourth embodiment, the same functional parts as those in the first, second or third embodiment are given the same reference numerals as those in the first, second or third embodiment. Detailed description is omitted.

  FIG. 7 shows a braking device 130 according to a fourth embodiment. The brake device 130 is provided with a gear 128. The braking device 130 is used instead of the braking device 30 according to the first embodiment, and is attached to the door 12 (see FIG. 1). In the fourth embodiment, the braking device 130 functions as an example of a braking device. Further, in the fourth embodiment, a gear 128 is provided instead of the gear 32, and the gear 128 meshes with a rack 34 provided on the hanger rail 18. In the fourth embodiment, the gear 128 functions as an example of a rotating body.

  The braking device 130 includes a first housing 132 and a second housing 134. The braking device 130 includes a transmission unit 136 and a braking unit 40. In the fourth embodiment, the transmission unit 136 is used in place of the transmission unit 38.

  In the first housing 132, a recess 138 is formed on the surface opposite to the gear 128, and the transmission unit 136 is accommodated in the recess 138. The second housing 134 is formed with a recess (not shown) on the surface on the first housing 132 side to accommodate the generator 58 and the braking circuit unit 60 of the braking unit 40. In the braking device 130, a base plate 140 is disposed between the first housing 132 and the second housing 134, and the first housing 132 and the second housing are connected and integrated with the base plate 140 interposed therebetween. As for the braking device 130, the 1st housing 132 and the 2nd housing 134 which were integrated are attached to the bracket 22 (refer FIG. 1) of the door 12 via the attachment bracket which is not shown in figure.

  The base plate 140 has the generator 58 and the braking circuit unit 60 attached to the surface on the second housing 134 side. Further, the base plate 140 has an insertion hole 140A, and the generator 58 has the rotor shaft 58A inserted into the insertion hole 140A so that the tip of the rotor shaft 58A protrudes into the recess 138 of the first housing 132. In this state, it is attached to the base plate 140.

  The transmission unit 136 includes shafts 142A and 142B. In the first housing 132, a bearing 144A corresponding to the shaft 142A and a bearing 144B corresponding to the shaft 142B are provided on the bottom surface of the recess 138. The base plate 140 has a support hole 140B corresponding to the shaft 142A and a support hole 140C corresponding to the shaft 142B.

  The transmission portion 136 is inserted into the bearing 144A so that one end of the shaft 142A protrudes from the first housing 132, and the other end of the shaft 142A is inserted into the support hole 140B of the base plate 140 so as to be rotatable. It is supported by. In addition, one end of the shaft 142B is inserted into the first housing 132 bearing 144B, and the other end of the shaft 142B is inserted into the support hole 140C of the base plate 140 so that the transmission portion 136 is rotatably supported. ing.

  The transmission portion 136 is attached to the tip portion of the shaft 142A protruding from the first housing 132 so that the gear 128 that meshes with the rack 34 (see FIG. 1) rotates integrally. Further, the transmission unit 136 is provided with a gear 146 on the shaft 142A, and a gear (not shown) that meshes with the gear 146 and a pulley 148 are attached to the shaft 142B so as to rotate integrally with the shaft 142B. Further, the transmission unit 136 is provided with a pulley 150 having a smaller diameter than the pulley 148. The pulley 150 is attached to the rotor shaft 58 </ b> A of the generator 58 that protrudes from the base plate 140 into the first recess 138. Further, the transmission unit 136 is provided with an endless belt 152 that is wound around the pulleys 148 and 150.

  For example, a toothed belt (timing belt) is used as the belt 152, and toothed pulleys are used as the pulleys 148 and 150. As a result, the transmission unit 136 reliably transmits the rotational speed and torque between the pulley 148 and the pulley 150 by the belt 152. The transmission unit 136 has a gear ratio between a gear 146 and a gear (not shown) provided on the shaft 142B that meshes with the gear 146 so that the rotational speed of the gear 32 is increased and transmitted to the rotor shaft 58A of the generator 58. A gear ratio between the pulley 148 and the pulley 150 is set.

  When the door 12 moves in the closing direction and the gear 128 meshes with the rack 34, the transmission unit 136 rotates the gear 128 in the closing direction at a rotational speed corresponding to the moving speed of the door 12, and passes through the belt 152. The rotation of the gear 128 is transmitted to the rotor shaft 58A of the generator 58. The transmission unit 136 can transmit the inertial force or braking torque generated by the rotation of the rotor shaft 58 </ b> A to the gear 128 via the belt 152. Thereby, the braking device 130 decelerates the moving speed of the door 12 moving in the closing direction, and gently moves the door 12 to the closed position of the opening 16.

  Incidentally, the braking device 130 is provided with a torque limiting portion 154. In the fourth embodiment, as an example, a torque limiting portion 154 is provided between the shaft 142A and the gear 146. In the fourth embodiment, the torque limiting unit 154 functions as an example of a limiting unit.

  FIG. 8 shows a torque limiter 154 applied to the fourth embodiment. In addition, in FIG. 8, the gear 146 is shown in the cross section cut | disconnected along radial direction. As the torque limiting portion 154, a one-way clutch 86 provided on the coil spring 82, the friction ring 84, and the axial center portion of the friction ring 84 so as to be integrally rotatable is used. In the torque limiting unit 154, the shaft 142A of the transmission unit 136 is inserted into the one-way clutch 86, and the shaft 142A is rotated in the closing direction together with the gear 128, whereby the shaft 142A and the friction ring 84 are integrally rotated.

  The gear 146 is provided with a bearing 156 at the shaft center portion, and a shaft 142A is inserted into the bearing 156 and supported rotatably. Further, in the torque limiting portion 154, the end portion 82 </ b> A of the coil spring 82 is directed to the gear 146. The gear 146 has an engagement hole 158 formed on the surface facing the coil spring 82. The end portion 82A of the coil spring 82 is inserted into the engagement hole 158 of the gear 146, and the torque limit portion 154 is engaged so that the coil spring 82 and the gear 146 rotate together.

  When the door 12 is moved in the closing direction and the gear 128 is engaged with the rack 34 of the hanger rail 18, the braking device 130 configured in this way is rotated in the closing direction. In the braking device 130, the shaft 142 </ b> A rotates in the closing direction together with the gear 128, and the rotation of the shaft 142 </ b> A is transmitted to the gear 146 because the coil spring 82 and the friction ring 84 are engaged by a frictional force. In addition, the braking device 130 transmits the rotation of the gear 146 to the rotor shaft 58A of the generator 58 via the belt 152, and the rotor shaft 58A is rotated at a rotational speed corresponding to the moving speed of the door 12, thereby generating the generator 58. Rotational load corresponding to the rotational speed is generated. In the braking device 130, the rotational load generated in the generator 58 is transmitted to the gear 32 as a braking torque via the belt 152. Thereby, the moving speed of the door 12 is decelerated and gently stops at the closed position.

  On the other hand, when the door 12 is moved in the closing direction at a faster moving speed than necessary, the braking device 130 applies a large inertial force (the inertial force of the generator 58) to the gear 128 when the gear 128 meshes with the rack 34. . Further, in the braking device 130, when the gear 128 is engaged with the rack 34 and rotated while the door 12 is moved in the closing direction at a moving speed faster than necessary, the generator 58 generates a large braking torque. The torque limiter 154 causes the coil spring 82 and the friction ring 84 to friction when the rotational force corresponding to the inertial force generated by the generator 58 or the braking force exceeds the friction force between the coil spring 82 and the friction ring 84. Relative rotation against the force. As a result, the braking device 130 is configured such that the shaft 142 </ b> A and the gear 146 rotate relative to each other, and a frictional force (dynamic frictional force) is generated between the relatively rotating coil spring 82 and the friction ring 84. The force is transmitted to the gear 32 as a braking torque.

  Therefore, even if the door 12 is moved at a faster moving speed than necessary, the moving speed is surely reduced and the door 12 is gently stopped at the closed position. In addition, the braking device 130 suppresses the inertial force that the gear 128 receives from the generator 58 when the gear 128 meshes with the rack 34 even when the door 12 is moved at a faster moving speed than necessary. Parts such as the rack 34 are not damaged. Further, since the torque limiting unit 154 limits the braking torque by the frictional force between the coil spring 82 and the friction ring 84, no noise is generated when the braking torque is limited.

  As described in the fourth embodiment, the transmission of the rotation of the gear 128 to the generator 58 is not limited to the transmission unit 38 using the gear train, but the transmission unit 136 using the belt 152 may be used. The transmission of the rotation of the gear 128 to the generator 58 is not limited to the configuration using the gear train or the belt 152. For example, the gear 128 may be provided on the rotor shaft 58A of the generator 58. Any configuration can be applied in which the rotation can be accurately transmitted to the rotor shaft 58A of the generator 58 and the braking torque generated by the generator 58 can be transmitted to the gear 128.

  In the first to third embodiments described above, the torque limiting units 80, 100, and 110 serving as limiting means are used between the rotating body and the shaft that supports the rotating body. As described in the fourth embodiment, the shaft may be provided between the shaft 142A that rotates integrally with the rotating body and the gear 146 of the transmission unit 136. The limiting means is not limited to these, and can be provided at an arbitrary position as long as it is in a transmission system that transmits the rotation of the rotating body to the suppressing force generating means such as the generator 58.

[Fifth Embodiment]
Next, a fifth embodiment will be described. The basic configuration of the fifth embodiment is the same as that of the first embodiment described above. In the fifth embodiment, functional components similar to those of the first to fourth embodiments are described. Are given the same reference numerals as in the first to fourth embodiments, and the description thereof will be omitted.

  In the first embodiment, the sliding door 10 has been described as an example of a door that opens and closes the opening, but in the fifth embodiment, a folding door is applied. In FIG. 9, the middle folding door 160 applied as an example of the folding door which concerns on 5th Embodiment is shown. In the folding door, a plurality of doors are connected, and when the opening is opened and closed, the plurality of doors are folded. The middle folding door 160 includes two doors 162 and 164, and the opening 16 is opened by folding the doors 162 and 164. In the following description, the closing direction side is referred to as the door 162 and the opening direction side is referred to as the door 164.

  The folding door 160 has a door 162 and a door 164 connected to each other by a hinge 166, and is folded by being rotated so that the doors 162 and 164 approach each other around the hinge 166. The folding door 160 is provided with a support shaft 164A at the end of the door 164 on the opening direction side, and with a support shaft 162A at the end of the door 162 on the closing direction side.

  As for the folding door 160, the hanger rail 18 is arrange | positioned at the wall part 14 above the opening part 16. As shown in FIG. The hanger rail 18 is attached to the wall portion 14 so that the longitudinal direction is along the horizontal direction. Further, the folding door 160 is provided with a slider 168 on the closing direction side. The slider 168 includes a long block base 168A as an example. The base 168A is disposed such that the longitudinal direction thereof is along the longitudinal direction of the hanger rail 18, and brackets 22 and 24 are attached to the upper surface.

  The folding door 160 is attached to a pivot 164A of the door 164 that is rotatably supported by the wall portion 14 on the opening direction side of the opening 16. Further, in the folding door 160, the support shaft 162A of the door 162 is rotatably connected to the lower surface of the base 168A of the slider 168. The folding door 160 is suspended so that the slider 168 can move in the opening direction and the closing direction along the hanger rail 18 by placing the door wheel 28 of the slider 168 on the rail portion 20 of the hanger rail 18. Further, the folding door 160 is supported by the slider 168 and the doors 162 and 164 are moved in the opening direction (arrow OP direction) and the closing direction (arrow CL direction) of the opening 16.

  The folding door 160 closes the opening 16 by moving the door 162 together with the slider 168 in the closing direction and expanding the doors 162 and 164 in a straight line. Further, in the folding door 160, when the door 162 is pulled in the opening direction, the slider 168 moves in the opening direction on the rail portion 20 along the hanger rail 18, and the door 162 and the door 164 are connected by a hinge 166. The opening 16 is opened by moving in the opening direction while being overlapped by being bent at the bent portion.

  As for the folding door 160, the closer 170 is provided in the edge part of the close direction side of the hanger rail 18, for example. As an example, the closer 160 is provided so that the wire 172 can be pulled out, and a general configuration in which winding means for urging and winding the wire 172 in a direction opposite to the pulling direction (the pulling direction) is applied. .

  In the closer 170, the tip of the wire 172 is connected to, for example, the bracket 22 provided on the slider 168, and the wire 172 is pulled out by moving the slider 168 in the opening direction together with the doors 162 and 164, and the wire 172 is wound up. The urging power for the purpose is stored. Further, when the hand is released from the door 162 or the like that opened the opening 16, the closer 170 winds up the wire 172 by the stored urging force and moves the slider 168 back in the closing direction. When the slider 168 is moved in the closing direction, the door 164 moves in the closing direction together with the door 162 and the opening 16 is closed.

  On the other hand, the folding door 160 has the braking device 30 attached to the bracket 22 of the slider 168 and is racked at a preset position (a preset position before the closed position of the door 162) of the support portion 18B of the hanger rail 18. 34 is attached. In the folding door 160, when the door 162 moves in the closing direction and the slider 168 reaches a preset position, the gear 32 of the braking device 30 meshes with the rack 34, and the gear 32 moves in the closing direction of the door 162. That is, the gear 32 provided with the torque limiting unit 80 is rotated in the closing direction at a rotation speed corresponding to the moving speed of the slider 168. In the fifth embodiment, the braking device 30 is used as an example. However, the braking device 30 may be provided with the torque limiting unit 100 or the torque limiting unit 110 instead of the torque limiting unit 80, and may be bent. The door 160 may be replaced with a braking device 130 instead of the braking device 30.

  In the braking device 30, when the gear 32 is rotated in the closing direction, the generator 58 generates a braking torque according to the rotation speed of the gear 32, and the generated braking torque is transmitted to the gear 32. As a result, the braking device 30 suppresses the rotation speed of the gear 32 that rotates while meshing with the rack 34, the movement speed of the slider 168, that is, the movement speed of the doors 162, 164 is reduced, and the doors 162, 164 are loosened. To close the opening 16.

  In addition, when the door 162 is pulled strongly in the closing direction, the door 162 and the slider 168 move at a speed faster than necessary. The braking device 30 limits the inertial force or braking torque acting on the gear 32 by the frictional force between the coil spring 82 and the friction ring 84. Therefore, even if the slider 168 moves at a faster moving speed than necessary, the braking device 30 may damage the gear 32 and the rack 34 due to the inertial force acting on the gear 32, or the door 162 (slider 168) may become a hanger rail. The moving speed of the doors 162 and 164 is surely reduced while preventing the door 16 from being detached from the door 18, and the opening 16 is gently closed by the doors 162 and 164. Further, since the braking device 30 limits the braking torque by the frictional force between the coil spring 82 and the friction ring 84, no noise is generated.

  As described in the fifth embodiment, the braking devices 30 and 130 can be provided not only in the sliding door 10 but also in the folding door 160. The braking devices 30, 130, etc. are not limited to the sliding door 10 and the folding door 160, but may be any door that opens and closes an opening by moving the door, such as a swing door (door), a double door, a double door, and a sliding door. It can be applied to the door (joint) of composition. At this time, when the door moving in the closing direction reaches a preset position before the closing position, the rotating body is engaged with the engaging member and rotated according to the moving speed of the door. It ’s fine.

  In the above-described embodiment, the coil springs 82 and 104 and the disc spring 114 have been described as examples of the biasing unit used as the limiting unit. However, the configuration of the limiting unit is not limited thereto. The restricting means uses an arbitrary urging means and a friction engagement member formed so that a frictional force is generated between the urging means and the urging means. Various configurations for transmitting the rotation of the rotating body and transmitting the suppression force to the rotating body can be applied. Further, the limiting means is not limited to the structure using the frictional force generated by the urging force of the urging means, and any structure that transmits the rotation and the rotational force using the frictional force can be applied.

  Further, in the present embodiment, the one-way clutch 86 serving as the interrupting unit is provided in the torque limiting unit that functions as the limiting unit. However, the present invention is not limited thereto, and the interrupting unit is provided between the gear 32 and the rotor shaft 58A of the generator 58. Can be provided at any position where rotation is transmitted.

DESCRIPTION OF SYMBOLS 10 Sliding door 12,162,164 Door 16 Opening part 18 Hanger rail 20 Rail part 28 Door 30,130 Braking device 32,102,112,128 Gear (rotary body)
34 Rack 38, 136 Transmission unit 40 Braking unit 50A, 142A Shaft 58 Generator 58A Rotor shaft 60 Braking circuit unit 80, 100, 110, 154 Torque control unit 82, 104 Coil spring 84 Friction ring 86 One-way clutch 114 Disc spring 126 Friction plate 170 closer

Claims (7)

A rotating body that is rotated according to the movement of the braking object;
A suppressing force generating means that includes a rotating shaft that is rotated by a rotating force, and that suppresses the rotation of the rotating shaft and generates a suppressing force that increases as the rotating force increases;
Limiting means for connecting the rotating body and the rotating shaft of the suppression force generating means by frictional force, and limiting the suppression force transmitted to the rotating body by the frictional force;
Including braking device.   The restricting means includes an urging means and a friction engagement member engaged so as to rotate integrally with the urging means by a frictional force generated by the urging force of the urging means, and the urging means and the friction The braking device according to claim 1, wherein the rotating body and the rotating shaft of the restraining force generating means are connected via an engaging member. The limiting means includes a gear, a friction ring provided as the friction engagement member, a shaft that supports the gear so as to be relatively rotatable, and supports the friction ring so as to rotate integrally, and as the biasing means. A coil spring provided and wound around the outer periphery of the friction ring,
3. The braking device according to claim 2, wherein one end of the coil spring is inserted into an engagement hole formed in a side surface of the gear and is engaged with the gear so as to rotate integrally therewith. The limiting means includes a gear, a friction ring provided as the friction engagement member, a shaft that supports the gear so as to be relatively rotatable, and supports the friction ring so as to rotate integrally, and as the biasing means. A coil spring provided and wound around the outer periphery of the friction ring,
The coil spring has one end protruding outward in the radial direction, and is housed together with the friction ring in a recess formed by opening on one side of the gear, and the one end is the gear. The braking device according to claim 2, wherein the braking device is accommodated in an engaging groove formed continuously on the side surface in the radial direction from the concave portion so as to rotate integrally with the gear.   The restricting means includes a gear provided as the friction engagement member, a disc spring provided as the biasing means, a shaft that supports the gear so as to be relatively rotatable via the disc spring, and the disc spring. And a friction member engaged with the shaft so as to rotate integrally therewith, and is engaged with the gear by a frictional force generated by a biasing force of the disc spring between the disc spring and the friction member. The braking device according to claim 2.   The braking device according to any one of claims 3 to 5, wherein the gear is used as the rotating body. The suppression force generating means is
A rotator comprising a coil that generates an induced electromotive force according to the rotational speed of the rotary shaft at a period synchronized with the rotation of the rotary shaft;
A suppression circuit that forms a closed circuit with the coil and generates the suppression force on the rotating shaft by generating an electromotive force in accordance with the rotation of the rotating shaft in the coil;
The braking device according to any one of claims 1 to 6, further comprising:

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