JP2018192889A - Seat drive device - Google Patents

Abstract

An object of the present invention is to stably connect a coupling cylinder in an axial direction with respect to an output shaft even when a rotational force is applied between the coupling cylinder of the clutch mechanism and an output shaft when the clutch mechanism is disconnected. It is to be able to move. A clutch mechanism includes a connecting cylinder configured to be connected to or disconnected from a driving shaft in an axial direction, and the clutch mechanism is coaxially inserted into the connecting cylinder to adjust the position of a vehicle seat. And an output shaft 470 connected to the mechanism. On the outer peripheral surface of the output shaft 470 of the clutch mechanism, a protrusion 473t extending in the axial direction is formed, and the inner periphery of the connecting cylinder 460 of the clutch mechanism. A flat surface 460f with which the protrusion 473t abuts from the rotation direction is formed on the surface, and the coupling cylinder 460 and the output shaft 470 of the clutch mechanism are brought into contact by the protrusion 473t and the flat surface 460f from the rotation direction. It is held so that it cannot rotate relative to the axis and can move relative to the axis. [Selection] Figure 13

Description

  The present invention relates to a seat drive device configured to rotate a plurality of drive shafts with a single motor, and to transmit the rotational forces of the plurality of drive shafts to a plurality of position adjusting mechanisms in a vehicle seat via a clutch mechanism, respectively. About.

  A clutch mechanism used in a seat driving apparatus related to this is described in Patent Document 1. As shown in FIG. 20, the clutch mechanism 100 described in Patent Document 1 includes an output shaft 102 connected to a seat position adjusting mechanism via a torque cable (not shown), and a shaft main body portion 102m of the output shaft 102. Is provided with a connecting cylinder 104 to be inserted coaxially. The outer peripheral surface of the shaft main body portion 102m of the output shaft 102 and the inner peripheral surface of the connecting cylinder 104 are generally formed in a hexagonal cross section, and can be moved relative to each other in the axial direction, and cannot be rotated around the shaft center. Is retained. The connecting cylinder 104 is provided with a front end fitting portion 104x that can be fitted to the drive shaft 107 of the worm wheel 106 rotated by a motor from the axial direction. Further, between the shaft main body 102 m of the output shaft 102 and the connecting cylinder 104, the connecting cylinder 104 is pressed in the fitting position direction (right direction) with the drive shaft 107 of the worm wheel 106, and the clutch mechanism 100. Is provided in a connected state.

  Further, the clutch mechanism 100 presses the flange 104f at the base end of the connecting cylinder 104 to the left, and the fitting between the connecting cylinder 104 and the drive shaft 107 of the worm wheel 106 against the spring force of the spring 108. A clutch pin 110 for releasing the engagement and an operating body 112 are provided. Then, as shown in FIG. 20, in a state where the operating body 112 is inclined leftward by the rotation of the clutch pin 110, the operating body 112 resists the flange portion 104f of the connecting cylinder 104 against the spring force. Press leftward. Thereby, the fitting between the front end fitting portion 104x of the connecting cylinder 104 and the drive shaft 107 of the worm wheel 106 is released. Further, when the operating body 112 is raised by the rotation of the clutch pin 110, the connecting cylinder 104 is moved in the right direction by the spring force, and the front end fitting portion 104x of the connecting cylinder 104 is the drive shaft of the worm wheel 106. 107 is fitted.

Japanese Patent No. 569536

  In the seat driving device, when the motor further rotates in the operation direction with the seat position adjusting mechanism reaching the operation limit position, the seat position adjusting mechanism and the output shaft 102 of the clutch mechanism 100 are connected to each other. The torque cable is twisted. Thereby, even after the motor is stopped, the rotational force caused by the twist of the torque cable is applied between the output shaft 102 of the clutch mechanism 100 and the connecting cylinder 104. Here, the outer peripheral surface of the shaft main body portion 102m of the output shaft 102 and the inner peripheral surface of the connecting cylinder 104 are formed in a hexagonal cross section. Thereby, in a state where a rotational force is applied between the shaft main body portion 102m of the output shaft 102 and the connecting cylindrical body 104, the outer peripheral surface of the shaft main body portion 102m and the inner peripheral surface of the connecting cylindrical body 104 are close to surface contact Thus, the frictional resistance at the time of relative movement in the axial direction increases. For this reason, when releasing the coupling of the clutch mechanism 100 after the motor is stopped, even if the flange 104f of the coupling cylinder 104 is pressed leftward by the clutch pin 110 and the operating body 112, the left direction of the coupling cylinder 104 ( The movement in the disconnection direction) may not be performed smoothly.

  The present invention has been made to solve the above-described problems, and the problem to be solved by the present invention is that when the clutch mechanism is disengaged, a rotational force is generated between the coupling cylinder of the clutch mechanism and the output shaft. This is to enable the connecting cylinder to stably move in the axial direction with respect to the output shaft even in a state in which is added.

  The above-described problems are solved by the inventions of the claims. According to the first aspect of the present invention, a plurality of drive shafts are rotated by a single motor, and the rotational forces of the plurality of drive shafts are selectively transmitted to a plurality of position adjusting mechanisms in the vehicle seat via respective clutch mechanisms. The clutch mechanism is connected to the drive shaft from the axial direction or connected to the connecting cylinder, and is inserted coaxially into the connecting cylinder, An output shaft coupled to the vehicle seat position adjustment mechanism, and either one of the inner peripheral surface of the coupling cylinder and the outer peripheral surface of the output shaft of the clutch mechanism has an axial direction. A flat surface extending in the axial direction is formed on one of the inner peripheral surface of the coupling cylinder and the outer peripheral surface of the output shaft of the clutch mechanism. Formed to extend, front By plane and said projection abuts the rotational direction, the connection cylinder of the clutch mechanism and said output shaft is incapable of relative rotation around the axis, is held axially movable relative.

  In the clutch mechanism according to the present invention, the flat surface and the protrusion are in contact with each other from the rotational direction, so that the coupling cylinder and the output shaft of the clutch mechanism are held so as not to be relatively rotatable about the axis and relatively movable in the axis direction. ing. That is, when the connecting cylinder of the clutch mechanism is connected to the drive shaft, the rotational force of the drive shaft is applied from the connecting cylinder to the output shaft through the contact portion between the flat surface and the protrusion. As described above, in a state where a rotational force is applied between the connecting cylinder of the clutch mechanism and the output shaft, the inner peripheral surface of the connecting cylinder and the outer peripheral surface of the output shaft are lined by the action of the protrusion and the flat surface. It is close to contact. For this reason, it is possible to reduce the frictional resistance when the connecting cylinder is moved in the axial direction with respect to the output shaft in a state where a rotational force is applied between the connecting cylinder of the clutch mechanism and the output shaft. As a result, when releasing the clutch mechanism, the connecting cylinder can be stably moved in the axial direction with respect to the output shaft.

  According to invention of Claim 2, the protrusion is formed in the cross-sectional arc shape. For this reason, a contact part will be in a line contact state in the state which the said protrusion and the plane contact | abutted in the rotation direction. Friction resistance when moving the connecting cylinder in the axial direction with respect to the output shaft can be minimized.

  According to invention of Claim 3, the internal peripheral surface of a connection cylinder and the outer peripheral surface of an output shaft are formed in polygonal shape. Here, the polygonal shape includes not only a normal polygon but also a star polygon.

  According to the invention of claim 4, the ridge is formed between adjacent planes of the output shaft across the ridge lines of the polygonal output shaft of the clutch mechanism. Accordingly, the radial dimension of the protrusion can be increased compared to the case where the protrusion having an arcuate cross section is formed for each plane, and the protrusion is in contact with the plane of the connecting cylinder from the circumferential direction. The strips are less likely to collapse.

  According to the invention of claim 5, the coupling cylinder and the output shaft of the clutch mechanism are made of resin. Formability between the coupling cylinder of the clutch mechanism and the output shaft is improved.

  According to the present invention, when releasing the connection of the clutch mechanism, even when a rotational force is applied between the connection cylinder body of the clutch mechanism and the output shaft, the connection cylinder body is stably placed in the axial direction with respect to the output shaft. Can be moved.

1 is a side view of a vehicle front seat (seat) including a seat driving device according to Embodiment 1 of the present invention. It is a top view of the sheet. It is a system outline explanatory drawing of the sheet drive. 1 is an overall exploded perspective view of a seat driving device according to Embodiment 1. FIG. It is a perspective view in the gear casing of the said seat drive device. It is an expanded sectional view of the center cam part in a gear casing. It is a front view showing the relationship between the clutch mechanism in a transmission casing, and the clutch pin (two-dot chain line) in a gear casing. It is a perspective view in the transmission casing of the said seat drive device. It is a perspective view showing the relationship between the said clutch mechanism and a clutch pin. It is a bottom view showing the connection release state of the clutch mechanism. It is a bottom view showing the connection state of the clutch mechanism. It is a disassembled perspective view of the clutch mechanism. FIG. 13 is a cross-sectional view (a cross-sectional view taken along the line XIII-XIII in FIG. 12) illustrating a relationship between the coupling cylinder and the output shaft of the clutch mechanism. It is a XIV arrow enlarged view of FIG. It is an expanded sectional view showing the relationship between the connection cylinder of the clutch mechanism which concerns on the example of a change, and an output shaft. It is sectional drawing of the output shaft of the clutch mechanism which concerns on the example of a change. It is sectional drawing of the output shaft of the clutch mechanism which concerns on the example of a change. It is sectional drawing of the output shaft of the clutch mechanism which concerns on the example of a change. It is sectional drawing of the output shaft of the clutch mechanism which concerns on the example of a change. It is a side view showing the clutch mechanism of the conventional seat drive device.

[Embodiment 1]
Hereinafter, based on FIGS. 1-19, the sheet drive device which concerns on Embodiment 1 of this invention is demonstrated. The seat drive device according to the present embodiment is a device used in the vehicle front seat 1. Here, front and rear, right and left, and up and down shown in the figure correspond to front and rear, right and left of the vehicle front seat 1 and up and down.

<Overview of vehicle front seat 1>
As shown in FIGS. 1 and 2, a vehicle front seat 1 (hereinafter referred to as a seat 1) includes a seat cushion 3 that is a seat portion and a seat that is connected to the rear portion of the seat cushion 3 so as to be able to rotate back and forth. And back 2. In FIGS. 1 and 2, only the skeleton member of the sheet 1 is shown, and the pads, the skin, and the like are omitted. A recliner 8 for adjusting the reclining angle of the seat back 2 is provided at the hinge portion between the rear portion of the seat cushion 3 and the lower portion of the seat back 2.

  The seat 1 includes a pair of left and right lower rails 4 that are fixed on a vehicle floor (not shown) so as to extend in the vehicle front-rear direction, and upper rails 5 that are fitted to the respective lower rails 4 so as to be slidable back and forth. Yes. As shown in FIG. 1, brackets 5b are fixed on the front and rear of the upper rail 5, and the lower end of the front link 6 and the lower end of the rear link 7 are connected to these brackets 5b so as to be pivotable up and down. Has been. The upper end of the front link 6 and the upper end of the rear link 7 are connected to the cushion frame 3a of the seat cushion 3 so as to be vertically rotatable. Thereby, the seat 1 is configured to be movable back and forth with respect to the vehicle floor and to be adjustable in height from the vehicle floor.

  The recliner 8 of the seat 1 is provided with a reclining angle adjusting mechanism Mr for adjusting the reclining angle as shown in FIG. Further, as shown in FIG. 2, a slide adjusting mechanism Ms is provided on a rod (not shown) for sliding the left and right upper rails 5. Furthermore, a gear (not shown) for rotating the rear link 7 is provided with a lifter adjustment mechanism Ml for performing lifter adjustment.

<About Outline of Sheet Driving Device 30>
The seat driving device 30 is a device for selectively driving the reclining angle adjusting mechanism Mr, the slide adjusting mechanism Ms, and the lifter adjusting mechanism Ml of the seat 1 with a single motor 41. As shown in FIG. 3, the seat drive device 30 includes a motor 41, a power transmission mechanism 40 that selectively transmits the rotation of the motor 41 to each of the adjustment mechanisms Mr, Ms, Ml, and switching of the power transmission mechanism 40. And an operation mechanism 50 for driving the motor 41. Further, as shown in FIG. 4, the seat driving device 30 includes a transmission casing 400 that houses the power transmission mechanism 40 and a gear casing 56 that houses the operation mechanism 50.

  As shown in FIG. 4, the transmission casing 400 includes a casing left half 40 a and a casing right half 40 b, and the casing left half 40 a is connected to the center in the front-rear direction of the cushion frame 3 a on the right side of the seat cushion 3. (To be described later). The gear casing 56 includes a casing left half 56a and a casing right half 56b, and is connected to the transmission casing 400 in a state where the gear casing 56 is superimposed on the transmission casing 400 from the right side. Further, on the outside (right side) of the casing right half 56b of the gear casing 56, a slide operation knob 66, a recliner operation knob 67, and a lifter operation for operating the slide adjustment mechanism Ms, the reclining angle adjustment mechanism Mr, and the lifter adjustment mechanism Ml, respectively. A knob 68 is provided. Further, as shown in FIGS. 1 and 2, a motor 41 is fixed to the front part of the cushion frame 3 a on the right side of the seat cushion 3 in front of the transmission casing 400.

<About the operation mechanism 50>
As shown in FIG. 3, the operation mechanism 50 includes a slide clutch pin 51S and a lifter clutch pin 51L that operate the slide clutch mechanism 46S, the lifter clutch mechanism 46L, and the recliner clutch mechanism 46R of the power transmission mechanism 40, respectively. And a recliner clutch pin 51R. Further, the operation mechanism 50 has a center cam 52 that turns on the limit switch 59 for driving the motor when any one of the sliding clutch pin 51S, the lifter clutch pin 51L, and the recliner clutch pin 51R rotates. I have.

  As shown in FIG. 5, a recliner drive gear 55 </ b> R is arranged at a position corresponding to the recliner operation knob 67 in the casing left half 56 a of the gear casing 56 that houses the operation mechanism 50. Then, the rotation center shaft 55RC of the recliner drive gear 55R and the recliner operation knob 67 are connected in a state where relative rotation is impossible. The recliner drive gear 55R meshes with the gear of the recliner clutch pin 51R. For this reason, when the recliner operation knob 67 is rotated, the recliner clutch pin 51R rotates about the axis via the recliner drive gear 55R.

  A lifter clutch pin 51L is disposed at a position corresponding to the lifter operation knob 68, and a rotation center shaft 51LC of the lifter clutch pin 51L is connected to the lifter operation knob 68 in a state in which the lifter operation knob 68 is not relatively rotatable. For this reason, when the lifter operation knob 68 is rotated, the lifter clutch pin 51L rotates about the axis. Further, a slide drive gear 55S is arranged at a position corresponding to the slide operation knob 66, and the rotation center shaft 55SC of the slide drive gear 55S and the slide operation knob 66 are connected in a state where relative rotation is impossible. Yes. The slide drive gear 55S meshes with the gear of the slide clutch pin 51S. For this reason, when the slide operation knob 66 is rotated, the slide clutch pin 51S rotates about the axis via the slide drive gear 55S.

  As shown in FIG. 9, the output protrusion 51e is eccentric from the rotation center shaft 51LC at the axial ends (left ends) of the slide clutch pin 51S, the lifter clutch pin 51L, and the recliner clutch pin 51R. Is provided. The output protrusion 51e performs an arc motion as the corresponding clutch pins 51S, 51L, 51R rotate about the axis. The output protrusions 51e of the sliding clutch pin 51S, the lifter clutch pin 51L, and the recliner clutch pin 51R pass through an arcuate guide through hole (not shown) in the casing left half 56a of the gear casing 56. It protrudes (left side). Each of the output protrusions 51e protruding from the casing left half 56a of the gear casing 56 to the back side (left side) is an arcuate guide through hole 40S, 40L, 40R in the casing right half 40b of the transmission casing 400 shown in FIG. Is inserted into the transmission casing 400. As shown in FIG. 7, each output protrusion 51e is associated with an operating body 465 (described later) of the sliding clutch mechanism 46S, the lifter clutch mechanism 46L, and the recliner clutch mechanism 46R of the power transmission mechanism 40. Match.

  As shown in FIG. 5, a center cam 52 is provided in the casing left half 56a of the gear casing 56 so as to be surrounded by the sliding clutch pin 51S, the lifter clutch pin 51L, and the recliner clutch pin 51R. As shown in FIG. 6, the center cam 52 is provided with protrusions 52b to 52d that protrude outward in the radial direction corresponding to the clutch pins 51S, 51L, and 51R. Each clutch pin 51S, 51L, 51R is provided with a pair of protruding engaging portions 51Sa, 51La, 51Ra, and these engaging portions 51Sa, 51La, 51Ra correspond to the corresponding protruding portions of the center cam 52. It arrange | positions with the clearance gap between the circumferential direction both sides of 52b-52d.

  When any one of the clutch pins 51S, 51L, 51R is rotated, the engaging portions 51Sa, 51La, 51Ra of the rotating clutch pins 51S, 51L, 51R are the protrusions 52b-52d of the center cam 52. And the center cam 52 rotates. Note that the engaging portions 51Sa, 51La, 51Ra of the clutch pins 51S, 51L, 51R that are not rotating do not come into contact with the protrusions 52b to 52d of the center cam 52.

  On the outer periphery of the center cam 52, a gear portion 52a is formed at a position where the protrusions 52b to 52d are not provided, and the gear portion 57a of the switch link 57 meshes with the gear portion 52a. When the switch link 57 rotates in response to the rotation of the center cam 52, the limit switch 59 provided on the upper portion of the casing left half 56a shown in FIG. The operation piece (not shown) on the forward rotation side or the reverse rotation side is operated. The limit switch 59 is connected to the motor electrical circuit so that the motor 41 can be driven to rotate forward or backward.

<About the power transmission mechanism 40>
As shown in FIG. 3, the power transmission mechanism 40 receives the operation of the slide operation knob 66, the recliner operation knob 67, or the lifter operation knob 68 to adjust the rotation of the motor 41 to the slide adjustment mechanism Ms of the seat 1 and the reclining angle adjustment. This is a mechanism for transmitting to the mechanism Mr or the lifter adjusting mechanism Ml. As shown in FIGS. 7 and 8, the power transmission mechanism 40 includes a single motor output shaft 42 that receives the rotational force of the motor 41, and a worm 43 is formed on the motor output shaft 42. The worm 43 is engaged with a pair of worm wheels 44 and 45 that are vertically dispersed. Thereby, the rotation output of one axis from the motor 41 is converted into two axes.

  A recliner clutch mechanism 46R is detachably coupled to the drive shaft 44a of the upper worm wheel 44. A slide clutch mechanism 46S is detachably coupled to the front drive shaft 45a of the lower worm wheel 45. Furthermore, a lifter clutch mechanism 46L is coupled to the rear drive shaft 45b of the lower worm wheel 45 in a detachable state. The output shafts 47R and 47L of the recliner clutch mechanism 46R and the lifter clutch mechanism 46L are connected to the reclining angle adjusting mechanism Mr and the lifter adjusting mechanism Ml via torque cables (not shown), respectively. The output shaft (not shown) of the sliding clutch mechanism 46S is connected to the slide adjusting mechanism Ms via two helical gears 48S and 49S and a torque cable (not shown). Here, since the configurations of the clutch mechanisms 46R, 46S, and 46L are the same, the configuration of the lifter clutch mechanism 46L will be described based on FIG.

<About the configuration outline of the lifter clutch mechanism 46L of the power transmission mechanism 40>
9 to 12, the lifter clutch mechanism 46L includes a connecting cylinder 460 that connects the drive shaft 45b on the rear side of the worm wheel 45 and the output shaft 47L, or releases the connection. . A shaft main body 470 (see FIG. 12) of the output shaft 47L is inserted into the connecting cylinder 460 in a state where the shaft main body 470 (see FIG. 12) is relatively movable in the axial direction and is not relatively rotatable around the axis. A spring 461 that presses the connecting cylinder 460 to the drive shaft 45b side (front side) of the worm wheel 45 is mounted between the connecting cylinder 460 and the shaft main body 470 of the output shaft 47L. As a result, the connecting cylinder 460 moves forward along the shaft main body of the output shaft 47L by the spring force of the spring 461, and the front end 462 of the connecting cylinder 460 is connected to the worm wheel 45 as shown in FIG. The drive shaft 45b is fitted. In this state, the lifter clutch mechanism 46L is held in the connected state. 9 and 10 show the released state of the lifter clutch mechanism 46L.

  A flange portion 463 that projects outward in the radial direction by a certain dimension is formed at the rear end portion of the connecting cylinder 460. Further, the lifter clutch mechanism 46 </ b> L includes a gate-type operating body 465 that straddles the connecting cylinder 460 on the front side of the flange portion 463. The operating body 465 includes upper and lower leg portions 465k and a beam portion 465h that connects the distal ends of both leg portions 465k, and the base end portion 465b of both leg portions 465k is rotatable as shown in FIG. Is connected to the casing left half 40a of the transmission casing 400. Further, the rear surface of the beam portion 465h of the operation body 465 is configured to be able to contact the flange portion 463 of the connecting cylinder 460, as shown in FIGS. For this reason, when the operating body 465 is tilted backward about the base end portion 465b of the both leg portions 465k, the flange portion 463 is pushed rearward, and the connecting cylinder 460 moves backward against the spring force of the spring 461. Further, a cam surface 465c is formed on the front side of the beam portion 465h of the operation body 465 so as to contact the side surface of the output protrusion 51e of the lifter clutch pin 51L. As shown in FIGS. 7 to 9, the cam surface 465c is formed in a mountain shape, and is configured to protrude most forward at the center position of the beam portion 465h.

  For this reason, the operating body 465 rotates around the base end portion 465b as shown in FIG. 9 in a state where the output protrusion 51e of the lifter clutch pin 51L is in contact with the center of the cam surface 465c of the operating body 465. It moves and comes to tilt most backward. Thereby, the connection cylinder 460 is held at the retreat limit position (connection release position) against the spring force of the spring 461. From this state, when the lifter clutch pin 51L rotates about its axis and the output protrusion 51e moves up and down from the center of the cam surface 465c of the operating body 465 by an arc motion, the connecting cylinder 460 is driven by the spring force of the spring 461. Advances, and the operating body 465 rotates in the standing direction. As shown in FIG. 11, the front end 462 of the connecting cylinder 460 is connected to the drive shaft 45b of the worm wheel 45 until the operating body 465 stands upright and the connecting cylinder 460 advances to the forward limit position. It comes to fit. That is, the lifter clutch mechanism 46L is in a connected state. Here, each clutch mechanism 46R, 46S, 46L is maintained in the disengaged state by the output protrusion 51e of each clutch pin 51R, 51S, 51L being always in contact with the center of the cam surface 465c of the operating body 465. Has been. 10 and 11, the lifter clutch pin 51L is omitted.

<Operation of Sheet Driving Device 30>
For example, when the height of the seat 1 is adjusted, the lifter operation knob 68 outside the gear casing 56 provided on the right side of the seat cushion 3 is rotated upward or downward. For example, when the lifter operation knob 68 is rotated upward, the lifter clutch pin 51L of the operation mechanism 50 is rotated leftward in FIG. As a result, the output protrusion 51e of the lifter clutch pin 51L performs a circular arc motion downward in FIG. As a result, the output protrusion 51e of the lifter clutch pin 51L operates the lifter clutch mechanism 46L of the power transmission mechanism 40. That is, the output protrusion 51e of the lifter clutch pin 51L moves downward from the center of the cam surface 465c in the operating body 465 of the lifter clutch mechanism 46L. As a result, the connecting cylinder 460 of the lifter clutch mechanism 46L moves forward by the spring force of the spring 461, and the lifter clutch mechanism 46L enters the connected state.

  Further, when the lifter clutch pin 51L rotates to the left, the center cam 52 in FIG. 6 rotates to the right due to the engagement between the engaging portion 51La and the protrusion 52c. As a result, the switch link 57 rotates to the left by the gear meshing action, and the projecting piece 57b of the switch link 57 operates the operation piece on the forward rotation side of the limit switch 59 (see FIG. 5). As a result, the motor 41 rotates in the forward direction, and the rotational force of the motor 41 is lifter adjusted via the worm 43 of the motor output shaft 42 of the power transmission mechanism 40, the worm wheel 45, the lifter clutch mechanism 46L, and the torque cable. It is transmitted to the mechanism Ml. As a result, the lifter adjusting mechanism Ml is driven to raise the sheet 1.

  Here, when the lifter operation knob 68 is released, the lifter operation knob 68 returns to the original position, the motor 41 stops, and the output protrusion 51e of the lifter clutch pin 51L is located at the center of the cam surface 465c of the operation body 465. The lifter clutch mechanism 46L is released from the connection state. Further, when the lifter operation knob 68 is rotated downward, the motor 41 is reversed in the above-described procedure, and the seat 1 is lowered. Further, when the front / rear position of the seat 1 is adjusted, the slide operation mechanism 66 is rotated forward or backward to drive the slide adjustment mechanism Ms according to the above-described procedure, thereby moving the seat 1 back and forth. When the reclining angle of the seat 1 is adjusted, the reclining angle adjustment mechanism Mr is driven by the above-described procedure by rotating the reclining operation knob 67 forward or backward, so that the reclining angle of the seat 1 is increased or decreased. To change.

<About the connecting cylinder 460 and the shaft main body 470 of each clutch mechanism 46R, 46S, 46L>
Here, since the configurations of the clutch mechanisms 46R, 46S, and 46L are the same as described above, the connecting cylinder 460 and the like of the lifter clutch mechanism 46L will be described as a representative with reference to FIGS. As shown in FIG. 12, the shaft main body 470 of the output shaft 47L of the lifter clutch mechanism 46L is formed with a connecting portion 471 to which the end portion of the torque cable is connected in a relatively non-rotatable manner, and coaxially with the connecting portion 471. And an insertion portion 473 to be inserted into the connecting cylinder 460. A flange-shaped spring receiver 472 is formed at a boundary position between the connecting portion 471 and the insertion portion 473 of the shaft main body portion 470. Then, one end of a coil-shaped spring 461 disposed around the insertion portion 473 is received by the spring receiver 472 of the shaft main body portion 470. Further, the other end of the coiled spring 461 is received by a step (not shown in the figure) of a spring accommodating hole 460 b formed at the rear end of the connecting cylinder 460.

  The insertion portion 473 of the shaft main body portion 470 of the output shaft 47L is formed in a substantially hexagonal column shape as shown in FIGS. And the outer peripheral surface 473s of the insertion part 473 of the axis | shaft main-body part 470 is formed with the cross-sectional arc-shaped protrusion 473t extended in an axial direction across each ridgeline (illustration omitted) of a hexagonal column. That is, each protrusion 473t is provided at the boundary position of each plane 473f constituting the hexagonal column. The shaft main body 470 of the output shaft 47L is a resin injection molded product.

  As described above, the spring accommodating hole 460b is formed at the rear end portion of the connecting cylinder 460, and the insertion portion 473 of the shaft main body 470 is inserted into the back side (front side) of the spring accommodating hole 460b. The hexagonal hole 460j is formed up to the position of the front end 462 of the connecting cylinder 460. And the said level | step difference which receives the other end of the spring 461 is formed in the boundary position of the spring accommodating hole part 460b and the hexagonal hole 460j. The diameter dimension of the hexagonal hole 460j of the connecting cylinder 460 is set to be larger than the diameter dimension of the insertion portion 473 of the shaft main body 470 by the clearance. Here, the connecting cylinder 460 is also a resin injection-molded product like the shaft main body 470 of the output shaft 47L.

<About the operation of the connecting cylinder 460 and the shaft body 470>
Next, the case where the connecting cylinder 460 of the lifter clutch mechanism 46L receives the rotational force of the drive shaft 45b of the worm wheel 45 and rotates counterclockwise in FIG. 13 will be described (see white arrows). When the connecting cylinder 460 rotates counterclockwise with respect to the insertion part 473 of the shaft main body 470, the flat surface 460f of the hexagonal hole 460j of the connection cylinder 460 protrudes from the shaft main body 470 (insertion part 473) as shown in FIG. It abuts on the right side of the strip 473t in a state close to line contact. And the rotational force of the connection cylinder 460 is transmitted to the shaft main-body part 470 (insertion part 473) of the output shaft 47L via the line contact part of the plane 460f of the hexagon hole 460j, and the protrusion 473t. When the connecting cylinder 460 rotates clockwise with respect to the insertion part 473 of the shaft body 470, the flat surface 460f of the hexagonal hole 460j of the connection cylinder 460 is the protrusion 473t of the shaft body 470 (insertion part 473). Abuts on the left side in a state close to line contact.

  Here, for example, if the seated person continues to operate the lifter operation knob 68 upward even after the seat 1 stops at the upper limit position, the lifter clutch mechanism 46L and the torque cable are connected with the lifter adjustment mechanism Ml not moving. The rotational force of the motor is applied. For this reason, the torque cable is twisted. Thereby, after the motor 41 is stopped, the rotational force resulting from the twisting of the torque cable is applied between the shaft main body 470 (insertion portion 473) of the output shaft 47L of the lifter clutch mechanism 46L and the connecting cylinder 460. Become.

  As described above, the flat surface 460f of the hexagonal hole 460j of the connecting cylinder 460 in the lifter clutch mechanism 46L is in a state close to line contact with the protrusion 473t of the shaft main body portion 470 (insertion portion 473) of the output shaft 47L. It is in contact. Therefore, the friction resistance when the connecting cylinder 460 moves in the axial direction with respect to the shaft main body portion 470 (insertion portion 473) of the output shaft 47L in a state where a rotational force is applied to the lifter clutch mechanism 46L is compared. Can be kept small. Therefore, the connecting cylinder 460 can be stably moved in the disconnecting direction in a state where the torque generated by twisting of the torque cable is applied to the lifter clutch mechanism 46L.

<Advantages of Sheet Driving Device 30 According to the Present Embodiment>
In the clutch mechanisms 46R, 46S, and 46L of the drive device 30 according to the present invention, the inner peripheral surface of the connecting cylinder 460 and the outer peripheral surface of the shaft main body portion 470 (insertion portion 473) of the output shaft 47L are formed in a hexagonal shape. . Furthermore, a projecting ridge 473t having an arcuate cross section extending in the axial direction is formed on the outer peripheral surface of the shaft main body 470 (insertion portion 473). Abutting from the direction of rotation. That is, when the coupling cylinder 460 of the clutch mechanisms 46R, 46S, 46L is coupled to the drive shaft 45b of the worm wheel 45, the rotational force of the drive shaft 45b is coupled via a line contact portion between the protrusion 473t and the flat surface 460f. The cylindrical body 460 is added to the insertion portion 473 of the output shaft 47L (shaft body portion 470).

  As described above, in a state where a rotational force is applied between the coupling cylinder 460 of the clutch mechanisms 46R, 46S, and 46L and the insertion portion 473 of the output shaft 47L (the shaft main body 470), the hexagonal hole 460j of the coupling cylinder 460 and The insertion portion 473 of the output shaft 47L (shaft body portion 470) is in a state close to line contact by the action of the protrusion 473t. For this reason, when the clutch mechanisms 46R, 46S, and 46L are disconnected, the connecting cylinder 460 is moved even when a rotational force is applied between the connecting cylinder 460 and the insertion portion 473 of the output shaft 47L (the shaft main body 470). The frictional force when moving in the axial direction with respect to the output shaft 47L can be reduced as compared with the conventional case. As a result, when the clutch mechanisms 46R, 46S, and 46L are disconnected, the connecting cylinder 460 can be stably moved in the axial direction with respect to the output shaft 47L. Further, the protrusion 473t is formed between the adjacent flat surfaces 473f across the ridge lines of the hexagonal columnar insertion portion 473 of the output shaft 47L. Accordingly, the radial dimension of the protrusion 473t can be increased as compared with the case where the protrusion 473t having an arc cross section is formed for each flat surface 473f, and the protrusion 473t extends from the circumferential direction to the flat surface 460f of the connecting cylinder 460. When contacting, the protrusion 473t is not easily crushed.

<Example of change>
Here, the present invention is not limited to the above-described embodiment, and can be modified without departing from the gist of the present invention. In the present embodiment, as shown in FIGS. 13 and 14, an example is shown in which a protrusion 473t having an arcuate cross section extending in the axial direction is formed in the insertion portion 473 of the output shaft 47L (the shaft main body portion 470). However, as shown in FIG. 15, a protrusion 460t having an arcuate cross section is formed on a plane 460f in the vicinity of the corner of the hexagonal hole 460j of the connecting cylinder 460, and the insertion portion 473 of the output shaft 47L (shaft body portion 470). It is also possible to form a hexagonal prism. Further, in the present embodiment, an example in which the insertion portion 473 of the output shaft 47L (shaft main body portion 470) is formed into a substantially hexagonal column shape and the hexagonal hole 460j is formed in the connecting cylinder 460 is shown. However, as shown in FIG. 16, it is also possible to form the insertion portion 473 of the output shaft 47L (shaft main body portion 470) into a substantially triangular prism shape and form a triangular hole in the connecting cylinder 460. In addition, as shown in FIG. 17, the insertion portion 473 of the output shaft 47 </ b> L (the shaft main body portion 470) can be formed into a substantially quadrangular prism shape, and a square hole can be formed in the connecting cylinder 460. Further, as shown in FIG. 18, the insertion portion 473 of the output shaft 47 </ b> L (shaft body portion 470) can be formed into a substantially cross-sectional star shape, and a cross-section star-shaped hole can be formed in the connecting cylindrical body 460. As shown in FIG. 19, the insertion portion 473 of the output shaft 47 </ b> L (the shaft main body portion 470) can be formed into a substantially gear shape in cross section, and a substantially gear shape hole can be formed in the connecting cylinder 460. Furthermore, although the vehicle seat 1 has been described in the present embodiment, the present invention can also be applied to seats of airplanes, ships, trains, and the like.

DESCRIPTION OF SYMBOLS 1 ... Seat 30 ... Sheet drive device 41 ... Motor 44 ... Worm wheel 44a ... Drive shaft 45 ... Worm wheel 45a ... Drive shaft 45b ... · Drive shaft 46S · · · Sliding clutch mechanism 46R · · · Recliner clutch mechanism 46L · · · Lifter clutch mechanism 460 · · · Connecting cylinder 460t · · · Projection 460f · · Plane 460j · · Hexagonal hole 47R · .... Output shaft 47L ... Output shaft 470 ... Shaft body 473 ... Insertion part 473t ... Projection 473f ... Planar Ml ... Lifter adjustment mechanism (position adjustment mechanism)
Mr ... Reclining angle adjustment mechanism (position adjustment mechanism)
Ms ... ・ Slide adjustment mechanism (position adjustment mechanism)

Claims (5)

A seat drive device configured to rotate a plurality of drive shafts with a single motor and selectively transmit the rotational forces of the plurality of drive shafts to a plurality of position adjusting mechanisms in a vehicle seat via a clutch mechanism, respectively. There,
The clutch mechanism is connected to the drive shaft from the axial direction and connected to the connecting cylinder, and is inserted coaxially into the connecting cylinder and connected to the vehicle seat position adjusting mechanism. Output shaft, and
A plane extending in the axial direction is formed on one of the inner peripheral surface of the coupling cylinder and the outer peripheral surface of the output shaft of the clutch mechanism,
On either one of the inner peripheral surface of the coupling cylinder and the outer peripheral surface of the output shaft of the clutch mechanism, a ridge that contacts the flat surface from the rotation direction is formed to extend in the axial direction.
When the flat surface and the protrusion are in contact with each other from the rotational direction, the coupling cylinder body and the output shaft of the clutch mechanism are held so as not to rotate relative to each other around the axis and to be relatively movable in the axis direction. Sheet drive device. The seat driving device according to claim 1,
The protrusion is a sheet driving device formed in an arc shape in cross section. A seat driving device according to claim 1 or 2, wherein
The seat driving device in which an inner peripheral surface of the connecting cylinder and an outer peripheral surface of the output shaft are formed in a polygonal shape. A seat driving device according to claim 2,
The protrusion is a seat driving device formed between adjacent planes of the output shaft across the ridge lines of the polygonal output shaft of the clutch mechanism. The sheet driving apparatus according to any one of claims 1 to 3,
The coupling cylinder and the output shaft of the clutch mechanism are seat drive devices made of resin.

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