JP2018134985A - Seat drive device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce the number of times that switching is carried out as a clutch mechanism whole by constantly connecting a clutch mechanism for one position adjustment mechanism, in a seat derive device in which a plurality of position adjustment mechanisms are selectively actuated by a single motor and output of the motor is distributed to each position adjustment mechanism via its respective clutch mechanism.SOLUTION: A seat drive device comprises: a clutch operation mechanism 30 that switches each of a plurality of clutch mechanisms 40S and so on to a connection state or a non-connection state in response to an operation force of linear movement of an operation handle 110; and a switch operation mechanism 60 that switches a switch 70 in response to an operation force of rotation movement of the operation handle 110. The operation handle 110 comprises return means 90 that is urged to return to a reference position at all times in an operation-cancelled state. In the reference position, the clutch operation mechanism 30 brings the clutch mechanism 40S to a connected state, and the other clutch mechanisms 40L and so on to a non-connected state. The switch operation mechanism 60 brings the motor 80 to a non-electrified state.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a sheet driving apparatus that adjusts the positions of a plurality of sheet movable portions by a single motor.

  Patent Document 1 discloses a sheet driving apparatus that adjusts the positions of a plurality of sheet movable portions by a single motor. According to such a seat driving device, the position adjustment of the four seat movable parts (seat front-back adjustment, vertical adjustment, seat back reclining angle adjustment, and seat cushion tilt angle adjustment) is performed using a single motor. It is configured as follows. For this reason, a clutch mechanism is provided in each path for distributing the output of the motor to a mechanism for adjusting each position. Then, the clutch corresponding to the mechanism for adjusting the position is connected, and the output of the motor is transmitted to the corresponding position adjusting mechanism. On the other hand, the clutch corresponding to the mechanism that does not perform position adjustment is in a disconnected state, and the output of the motor is not transmitted to the corresponding position adjustment mechanism.

  In such a seat driving device, when the position of a certain sheet movable portion is adjusted, the motor is operated after the clutch mechanism corresponding to the sheet movable portion is switched from the non-connected state to the connected state.

JP 2013-107624 A

  Therefore, the clutch mechanism is switched from the non-connected state to the connected state every time the position of the corresponding seat movable portion is adjusted, and returned to the non-connected state after the position adjustment is completed. Therefore, the clutch mechanism needs to ensure durability according to the position adjustment frequency.

  In view of such problems, the problem of the present invention is that a plurality of position adjustment mechanisms are selectively operated by a single motor, and a clutch mechanism is provided in each path for distributing the output of the motor to each position adjustment mechanism. In the seat driving apparatus, the clutch mechanism of one position adjusting mechanism is always connected, so that the number of switching times of the entire clutch mechanism is suppressed and the problem of durability of the clutch mechanism is suppressed.

  A sheet driving apparatus according to a first aspect of the present invention includes a motor having a single output shaft, a plurality of position adjustment mechanisms that receive the output of the motor, and adjust the positions of a plurality of sheet movable parts, and the plurality of position adjustment mechanisms. And a plurality of clutch mechanisms for selectively connecting an output shaft to each of the plurality of position adjusting mechanisms and an input shaft that is rotationally driven by the motor, and the motor is energized. Alternatively, a switch that switches to a non-energized state, an operation handle that is operated when adjusting the positions of the plurality of seat movable portions, and an operation force for the clutch of the operation handle to receive each of the plurality of clutch mechanisms. A clutch operating mechanism that switches between a connected state and a disconnected state; and a switch operating mechanism that switches the switch in response to an operating force for the switch of the operating handle. Provided. The operation handle passes through a reference position which is one of the operation positions for both the clutch and the switch, and can be operated to other operation positions. Returning means for urging to return to is provided. Further, at the reference position, the clutch operating mechanism places one of the plurality of clutch mechanisms in a connected state, puts the other clutch mechanism in a disconnected state, and the switch operating mechanism puts the motor in a non-energized state. .

  In the first invention, the number of movable sheet parts and position adjustment mechanisms may be three or more. Various types of known clutch mechanisms and switches can be employed. The operation handle may be integrated with the clutch and the switch, or may be separate.

  According to the first invention, the operating handle is in the non-operating state and at the reference position, and at this time, one of the clutch mechanisms is in the connected state. Therefore, when operating the position adjustment mechanism corresponding to the clutch mechanism in the connected state at the reference position, the position adjustment of the corresponding sheet movable portion can be performed only by the switch operation. As a result, the operation frequency of the clutch mechanism is suppressed and durability can be enhanced. Further, since the operation handle is always in the reference position in the non-operating state, the operation handle is always operated from the reference position, and it is not necessary to confirm the operation position of the operation handle when starting the operation.

  A seat driving device according to a second aspect of the present invention includes a motor having a single output shaft, a plurality of position adjusting mechanisms that receive the output of the motor and adjust the positions of a plurality of sheet movable portions, and the plurality of position adjusting mechanisms. And a plurality of clutch mechanisms for selectively connecting an output shaft to each of the plurality of position adjusting mechanisms and an input shaft that is rotationally driven by the motor, and the motor is energized. Or a switch that switches to a non-energized state, an operation handle that is operated when adjusting the positions of the plurality of seat movable portions, and an operation force that is one of linear movement and rotational movement of the operation handle, In response to a clutch operating mechanism that switches each of the plurality of clutch mechanisms to a connected state or a non-connected state, and the other operating force of linear movement and rotational movement of the operation handle, And a switch operation mechanism for operating switching the serial switch. The operation handle passes through a reference position, which is one of the operation positions in both linear movement and rotational movement, and can be operated to other operation positions. Returning means for urging to return to is provided. Further, at the reference position, the clutch operating mechanism places one of the plurality of clutch mechanisms in a connected state, puts the other clutch mechanism in a disconnected state, and the switch operating mechanism puts the motor in a non-energized state. .

  In the second invention, the linear movement of the operation handle may be one in which the rotation center of the operation handle is moved in any direction of up / down, left / right, front / rear, and diagonal. When there are a large number of sheet movable parts and position adjustment mechanisms (for example, four or more), a plurality of directions may be used in combination among the above-described up-down, left-right, and front-back directions.

  According to the second invention, the same effect as the first invention can be achieved. In addition, the operation handle for the clutch and the switch are integrated, and the operation for the clutch or the operation for the switch is distinguished by linear movement and rotational movement. Therefore, the clutch operation and the switch operation can be performed without changing the operation handle. Further, since the operation handle is integrated, the space occupied by the operation handle can be reduced. Furthermore, since the operation handle for the clutch and the switch are distinguished depending on the way of movement, the operation space (compared to the configuration in which the clutch and the switch are differentiated by the operation stroke in the same movement operation ( (Operation stroke) can be reduced.

  According to a third aspect of the present invention, in the first or second aspect of the invention, the clutch mechanism that is in the connected state at the reference position corresponds to a position adjustment mechanism that adjusts a front / rear slide position of the seat among the plurality of seat movable portions. It is supposed to be.

  According to the third aspect of the present invention, the clutch mechanism corresponding to the position adjustment mechanism that adjusts the front / rear slide position of the seat having a high adjustment frequency is always connected. Therefore, the effect of suppressing the operation frequency of the clutch mechanism is further enhanced.

  According to a fourth aspect of the present invention, in any one of the first to third aspects, the clutch operation mechanism receives an operation force of linear movement of the operation handle to bring each of the plurality of clutch mechanisms into a connected state or a disconnected state. The switch operation mechanism is configured to switch the switch in response to an operation force of the rotational movement of the operation handle, and the operation force of the linear movement of the operation handle is changed to the switch operation mechanism. An operation force transmission mechanism is provided that transmits the operation force transmitted to the clutch operation mechanism and the rotational movement of the operation handle to the switch operation mechanism.

  According to the fourth aspect of the present invention, the operation force for linear movement of the operation handle can be transmitted to the clutch mechanism and the operation force for rotational movement of the operation handle can be transmitted to the switch.

  According to a fifth aspect of the present invention based on the fourth aspect, the operating force transmission mechanism includes an Oldham joint, and the switch operating mechanism receives the operating force of the rotational movement of the operating handle at the Oldham joint. A rotating body that rotates to switch the switch, and the rotation shaft of the operation handle passes through the rotation body and transmits an operation force for linear movement of the operation handle to the clutch operation mechanism. Yes.

  According to the fifth aspect, the rotational movement of the operating handle is transmitted to the rotating body to operate the switch, and the linear movement of the operating handle is transmitted to the clutch operating mechanism through the rotating shaft of the operating handle passing through the rotating body. To operate the clutch mechanism. Therefore, rotational movement and linear movement of the operating handle can be distinguished from each other and transmitted to the switch and the clutch operating mechanism. In addition, since the switch is operated by the rotation of the rotating body, the switch can be fixed to the fixed side member, and the wiring connected to the switch can be prevented from moving in accordance with the operation of the operation handle.

  According to a sixth aspect of the present invention, in any one of the first to fifth aspects, the clutch operation mechanism includes a center gear that rotates in response to an operation force of the operation handle, and a plurality of peripheral gears that rotate while meshing with the center gear. Prepare. The plurality of peripheral gears are combined with the plurality of clutch mechanisms, respectively, and are rotated to selectively connect the plurality of clutch mechanisms.

  According to the sixth aspect of the invention, the clutch operating mechanism for operating each clutch mechanism in response to the operating force of the operating handle is constituted by one center gear and peripheral gears corresponding to each clutch mechanism. Therefore, each clutch mechanism can be operated via a single center gear, and the configuration is simplified and the operating force of the operation handle is reduced compared to a case where each clutch mechanism is operated by individual members. Can do.

  According to a seventh aspect, in the sixth aspect, the clutch operating mechanism is configured to switch each of the plurality of clutch mechanisms to a connected state or a non-connected state in response to an operation force for linear movement of the operation handle. The switch operating mechanism is configured to receive the operation force of the rotational movement of the operation handle to switch the switch, and receives the operation force of the linear movement of the operation handle to convert it into a rotational motion. And a conversion mechanism for transmitting to the center gear.

  According to the seventh aspect of the invention, the linear movement of the operation handle is converted into a rotational motion by the conversion mechanism and transmitted to the center gear. Therefore, the clutch operation of the operation handle can be linearly moved, and can be distinguished from the rotational movement of the switch operation. As a result, the operation handles can be combined into one.

  According to an eighth invention, in any one of the first to seventh inventions, there are three seat movable portions, and three sets of the position adjusting mechanism and the clutch mechanism are provided corresponding to the three seat movable portions. Of these, one clutch mechanism is in a connected state at the reference position, and the other two clutch mechanisms are in a connected state at both sides of the reference position in the operation of moving the operation handle.

  According to the eighth aspect, the clutch mechanism is in the connected state on both sides of the reference position in the operation operation of moving the operation handle. Therefore, it is possible to easily understand the position adjustment of the total three sheet movable parts.

  A ninth invention is a clutch mechanism other than the clutch mechanism corresponding to the reference position when the operation handle is in the reference position and the operation handle is at a position other than the reference position in the fourth or fifth invention. The operation handle is provided with an operation restricting mechanism that enables the rotational movement of the operation handle in a state in which the operation handle is in a connected state, and prevents the rotational movement of the operation handle in a state other than those positions.

  According to the ninth aspect of the present invention, when the operating handle is at the reference position or other operating position and any one of the clutch mechanisms is in the connected state, the operating handle can be rotated and the operating handle can be operated. When the clutch mechanism is in the middle of switching between the connected state and the non-connected state, the operation handle is prevented from rotating. Therefore, it is possible to prevent a problem that the motor is operated due to the switch being switched during the switching of the clutch mechanism between the connected state and the non-connected state.

1 is a perspective view of a vehicle front seat to which a seat driving device according to a first embodiment of the present invention is applied. It is a system outline explanatory view of a 1st embodiment. It is operation explanatory drawing of the operation handle in 1st Embodiment. It is an expansion disassembled perspective view which shows the drive mechanism part in 1st Embodiment. It is a back surface side expansion perspective view of the operation handle in a 1st embodiment. It is action | operation explanatory drawing of the Oldham coupling in 1st Embodiment, and shows the state which has a control handle in a reference position by non-operation. FIG. 7 is an operation explanatory view similar to FIG. 6, showing a state where the operation handle is rotated forward from the state of FIG. 6. FIG. 7 is an operation explanatory view similar to FIG. 6, showing a state where the operation handle is reversed from the state of FIG. 6. FIG. 7 is an operation explanatory view similar to FIG. 6, showing a state where the operation handle is slid forward from the state of FIG. 6. FIG. 10 is an operation explanatory view similar to FIG. 6, showing a state where the operation handle is rotated forward from the state of FIG. 9. FIG. 10 is an operation explanatory view similar to FIG. 6, showing a state where the operation handle is reversed from the state of FIG. 9. FIG. 7 is an operation explanatory view similar to FIG. 6, showing a state in which the operation handle is slid rearward from the state of FIG. 6. FIG. 13 is an operation explanatory view similar to FIG. 6, showing a state where the operation handle is rotated forward from the state of FIG. 12. FIG. 13 is an operation explanatory view similar to FIG. 6, showing a state where the operation handle is reversed from the state of FIG. 12. It is an enlarged front view which extracts and shows the clutch operation mechanism, clutch mechanism, and conversion mechanism in a 1st embodiment, and shows the state where an operation handle is not operated and it is in a standard position. FIG. 16 is an enlarged perspective view showing the clutch operation mechanism, the clutch mechanism, and the conversion mechanism in the same manner as in FIG. 15, and shows a state where the operation handle is not operated and is at the reference position. FIG. 16 is an enlarged front view similar to FIG. 15, showing a state where the operation handle is slid forward. FIG. 17 is an enlarged perspective view similar to FIG. 16, showing a state where the operation handle is slid forward. FIG. 16 is an enlarged front view similar to FIG. 15, showing a state where the operation handle is slid rearward. FIG. 17 is an enlarged perspective view similar to FIG. 16, showing a state where the operation handle is slid rearward. It is an expansion disassembled perspective view which shows the drive mechanism part in 2nd Embodiment of this invention. It is a back surface side expansion perspective view of the operation handle in a 2nd embodiment. It is operation | movement explanatory drawing of the operating force transmission mechanism in 2nd Embodiment, and shows the state which has a non-operating operation handle in a reference position. It is operation | movement explanatory drawing similar to FIG. 23, and shows the state which rotated the operation handle forward from the state of FIG. It is operation | movement explanatory drawing similar to FIG. 23, and shows the state which reversed the operation handle from the state of FIG. FIG. 24 is an operation explanatory view similar to FIG. 23, showing a state where the operation handle is slid forward from the state of FIG. 23. FIG. 24 is an operation explanatory view similar to FIG. 23, showing a state where the operation handle is slid rearward from the state of FIG. 23.

  FIG. 1 shows a first embodiment of the present invention. This embodiment shows an example in which the seat driving device of the present invention is applied to a vehicle front seat (hereinafter simply referred to as a seat) 1. In each figure, each direction in the state which mounted | wore the vehicle with the sheet | seat 1 is shown by the arrow. In the following description, the description regarding the direction is made based on this direction.

  FIG. 1 shows the positional relationship of the sheet driving apparatus 100 in the entire sheet 1. In the seat 1, a seat back 2 that forms a backrest is fixed to the back of a seat cushion 3 that constitutes a seat so that the seat 1 can rotate back and forth. Therefore, a recliner (not shown) 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.

  A headrest 4 that supports the head of the seated occupant from the rear is provided at the upper end of the seat back 2. Further, the right side portion of the seat cushion 3 is covered with a side shield 9 including the lower portion of the seat back 2. The side shield 9 accommodates a driving device 100 of a seat driving device that can adjust the position of a plurality of seat moving parts according to the preference of a passenger seated on the seat 1. An operation handle 110 constituting an operation member in the driving device 100 is exposed to the outside of the side shield 9 so as to be operated by a seated occupant.

  The seat 1 is fixed to the vehicle floor so as to be movable back and forth. Therefore, a pair of lower rails 7 is fixed to the vehicle floor below the left and right sides of the seat cushion 3. An upper rail 8 is fitted in each lower rail 7, and is slidable in the front-rear direction with respect to the lower rail 7. The upper rail 8 is provided with a slide adjustment mechanism 50S of the driving device 100, and the slide position of the seat 1 can be adjusted by the slide adjustment mechanism 50S.

  A front link (not shown) and lower ends of the rear links 5 and 6 are connected to the upper rails 8 via brackets. A seat cushion 3 is fixed to the upper ends of the front links and rear links 5 and 6. Yes. The front link and the rear links 5 and 6 are tiltable in the front-rear direction with respect to the bracket. The rear link 5 is provided with a lifter adjusting mechanism 50L of the driving device 100, and the height of the seat 1 can be adjusted by adjusting the angle of the rear link 5 by the lifter adjusting mechanism 50L.

  The recliner is provided with a reclining angle adjusting mechanism 50R of the driving device 100, and the reclining angle of the seat back 2 can be adjusted by the reclining angle adjusting mechanism 50R.

  FIG. 2 shows a system outline of a sheet driving apparatus including the driving apparatus 100. The slide adjustment mechanism 50S, the lifter adjustment mechanism 50L, and the reclining angle adjustment mechanism 50R are connected to the motor 80 via clutch mechanisms 40S, 40L, and 40R, respectively. Here, the clutch mechanism 40S is in a state where the motor 80 and the slide adjustment mechanism 50S are always connected, and is not connected when the lifter adjustment mechanism 50L and the reclining angle adjustment mechanism 50R are operated. The clutch mechanisms 40L, 40R are always in a disconnected state between the motor 80, the lifter adjusting mechanism 50L, and the reclining angle adjusting mechanism 50R, and are connected when the lifter adjusting mechanism 50L and the reclining angle adjusting mechanism 50R are operated. The

  Each of the clutch mechanisms 40S, 40L, 40R is configured to be actuated by receiving an operation force of the operation handle 110. That is, the operation force of the operation handle 110 is transmitted to the clutch operation mechanism 30 by the operation force transmission mechanism 120 and also transmitted to operate the switch operation mechanism 60. The clutch mechanisms 40S, 40L, and 40R are operated by the operation force transmitted to the clutch operation mechanism 30. On the other hand, the switch operating mechanism 60 operates the switch 70 and energizes the switch 80 to operate the motor 80.

  The operating handle 110 is provided with return means 90, and the operating handle 110 is urged to return to a predetermined reference position in a non-operating state. When the operation handle 110 is at the reference position, the clutch mechanism 40S is in a connected state, and the clutch mechanisms 40L and 40R are in a disconnected state. Further, the switch operating mechanism 60 does not operate the switch 70.

  FIG. 3 shows how to operate the operation handle 110. The operation handle 110 is linearly movable in the front-rear direction of the seat around the reference position. Further, the operation handle 110 can be rotated and moved so as to be forward and backward with respect to a reference position.

  As shown in FIGS. 2 and 3, when the operation handle 110 is at the reference position, the clutch mechanism 40S is in the connected state as described above, and the slide adjusting mechanism 50S is in a state of receiving the output of the motor 80. . Further, when the operation handle 110 is linearly moved forward, the clutch mechanism 40L is brought into a connected state, and the lifter adjusting mechanism 50L is brought into a state of receiving the output of the motor 80. Further, when the operation handle 110 is linearly moved rearward, the clutch mechanism 40R is brought into a connected state, and the reclining angle adjusting mechanism 50R is brought into a state where the output of the motor 80 is received.

  The operation handle 110 can be rotated at each position of linear movement. When the operation handle 110 is rotated at each linear movement position, the switch 70 is operated to rotate the motor 80 forward or backward. When the operation handle 110 is released and is not operated, the operation handle 110 is returned to the reference position by the urging force of the return means 90 for both linear movement and rotational movement.

  FIG. 4 shows the main part of the driving apparatus 100 in an exploded manner. Each clutch mechanism 40S, 40L, 40R is accommodated between the clutch case halves 34a, 34b constituting the clutch case 34, and distributes one rotational output of the motor 80 to each output shaft 41S, 41L, 41R. It is configured. Specifically, as shown in FIGS. 15 and 16, one rotational output of the motor 80 is received by a pair of helical gears 43 and 44, and the helical gears 43 and 44 are respectively connected to the input shafts 42 </ b> S of the clutch mechanisms 40 </ b> S, 40 </ b> L and 40 </ b> R. The rotational output is distributed to 42L and 42R. Each clutch mechanism 40S, 40L, 40R is selectively connected, and rotation of the input shafts 42S, 42L, 42R corresponding to the clutch mechanisms 40S, 40L, 40R in the connected state is output shafts 41S, 41L, Output to 41R. The rotation of each output shaft 41S, 41L, 41R is transmitted to the slide adjustment mechanism 50S, the lifter adjustment mechanism 50L, and the reclining angle adjustment mechanism 50R via the power transmission cables 51S, 51L, 51R, respectively, as shown in FIG.

  As shown in FIGS. 4, 15, and 16, a center gear 31 and peripheral gears 32S, 32L, and 32R are rotatably disposed on the right side surface of the clutch case half 34a. The peripheral gears 32S, 32L, 32R are opposed to the clutch mechanisms 40S, 40L, 40R across the wall surface of the clutch case half 34a, and the engaging pieces 32Sa, 32La of the peripheral gears 32S, 32L, 32R, 32Ra is configured to operate each of the clutch mechanisms 40S, 40L, and 40R through a through hole formed in the wall surface of the clutch case half 34a.

  The center gear 31 is in a position surrounded by the peripheral gears 32S, 32L, 32R, meshes with the peripheral gears 32S, 32L, 32R, and rotates the peripheral gears 32S, 32L, 32R by the rotation of the center gear 31. It is configured. The center gear 31 includes a gear portion 31a and an engaging portion 31b. The gear portion 31a has gears that engage with the peripheral gears 32S, 32L, and 32R formed on the outer periphery, and the engaging portion 31b includes the gear portion 31a. It is formed in a part of the right side protruding in a pin shape.

  A conversion gear 33 is coupled to the engaging portion 31b of the center gear 31 so as to be swingable in the front-rear direction. A gear portion 33a is formed at the upper end portion of the conversion gear 33, and a pin-like engagement portion 33b protruding rightward is provided at the lower end portion.

  The center gear 31, the peripheral gears 32S, 32L, 32R, and the conversion gear 33 are covered by a gear cover 122 that covers the right side of the clutch case half 34a. An arcuate fixed gear 122a is formed at the upper end portion of the gear cover 122 (see FIG. 15), and the gear portion 33a of the conversion gear 33 is meshed with the fixed gear 122a. The fixed gear 122a, the conversion gear 33, and the center gear 31 constitute a conversion mechanism in the present invention.

  As shown in FIG. 4, in the driving device 100, the operating force transmission mechanism 120 includes an Oldham joint. The Oldham coupling includes an operation handle 110, an intermediate member 123, a switch cover 121, and a switch cam 124.

  The switch cam 124 corresponds to the rotating body in the present invention, has an overall shape that is a cup shape protruding rightward, and can be fitted into a circular opening 121 a of the switch cover 121. An opening 124a is formed at the center of the cup shape of the switch cam 124, and a key 124b protrudes along the diameter direction on the right side surface of the cup shape. Further, on the cup-shaped outer periphery, a protrusion 60 for operating the switches 71 and 72 (both switches 71 and 72 are combined to constitute the switch 70) is formed to protrude. The switches 71 and 72 are fixed to the left side surface of the switch cover 121 so as to face the protrusion 60. The protrusion 60 corresponds to the switch operating mechanism 60 described with reference to FIG.

  The intermediate member 123 is formed in a rectangular plate shape, and an opening 123c is formed in the center of the rectangle. A groove 123b is formed on the left side surface of the intermediate member 123 along a rectangular diagonal line, and a groove 123a is formed on the right side surface along a diagonal line in a direction intersecting with the diagonal line of the groove 123b. The intermediate member 123 is superposed on the right side surface of the switch cam 124, and the key 124b of the switch cam 124 is slidably fitted along the groove 123b in the groove 123b of the intermediate member 123.

  As shown in FIGS. 4 and 5, on the left side surface of the operation handle 110, a rotation shaft 110 a is formed projecting leftward at the center, and a key 110 b is formed projecting along the diameter direction of the operation handle 110. . The operation handle 110 is superposed on the right side surface of the intermediate member 123 with the rotating shaft 110a passing through the opening 123c of the intermediate member 123. At this time, the key 110b of the operation handle 110 is slidably fitted in the groove 123a of the intermediate member 123 along the groove 123a. The rotating shaft 110a has a cylindrical shape as a whole, but two side surfaces that are flat and parallel to each other are formed by chamfering the side surface portions that face each other across the axis of the cylinder.

  The switch cover 121 is superposed and fixed on the right side surface of the gear cover 122. A guide groove 122b that is long in the front-rear direction is formed at the center of the gear cover 122 so as to guide the linear movement of the operation handle 110. The guide groove 122b allows the rotation shaft 110a of the operation handle 110 to be rotatably fitted when the operation handle 110 is in the reference position, the forward linear movement position, and the rearward linear movement position. However, in a state where the position of the operation handle 110 is in the middle of these three positions, the size is set to receive the chamfered two-surface width of the rotating shaft 110a. For this reason, the operation handle 110 can rotate forward and reverse at the reference position, the forward linear movement position, and the backward linear movement position, but can rotate during the movement to those positions. I can't. The chamfering structure of the rotating shaft 110a and the structure of the guide groove 122b as described above constitute an operation restriction mechanism in the present invention.

  The engaging portion 33 b of the conversion gear 33 is disposed so as to penetrate the guide groove 122 b of the gear cover 122, and the tip of the engaging portion 33 b is fitted and coupled to the center hole of the rotating shaft 110 a of the operation handle 110.

  A torsion coil spring 92 is provided between the center gear 31 and the clutch case half 34a. The torsion coil spring 92 generates a biasing force when the center gear 31 is rotated with respect to the clutch case half 34a. Thus, the rotational position of the center gear 31 is always returned to the reference position.

  When the operation handle 110 is linearly moved, the conversion gear 33 is swung by the engagement of the gear portion 33a and the fixed gear 122a, and the center gear 31 coupled to the conversion gear 33 via the engaging portion 31b is rotated. (See FIGS. 17-20). In this state, the torsion coil spring 92 generates a biasing force, and when the movement operation of the operation handle 110 is released, the operation handle 110 is returned to the reference position.

  A torsion coil spring 91 is provided between the switch cover 121 and the switch cam 124. The torsion coil spring 91 generates an urging force when the switch cam 124 is rotated with respect to the switch cover 121. The rotational position of the switch cam 124 is always returned to the reference position.

  When the operation handle 110 is rotated, the switch cam 124 is rotated through the intermediate member 123 (see FIGS. 7, 8, 10, 11, 13, and 14). In this state, the torsion coil spring 91 generates a biasing force, and when the movement operation of the operation handle 110 is released, the operation handle 110 is returned to the reference position. The torsion coil springs 91 and 92 correspond to the return means 90 described with reference to FIG.

  6-14 show the operating state of the Oldham coupling. 15 to 20 show the operating state of the clutch operating mechanism 30. FIG.

  FIG. 6 shows a non-operation state in which the operation handle 110 is neither linearly moved nor rotated. At this time, the operation handle 110 is at the reference position, and in the clutch operation mechanism 30, as shown in FIGS. 15 and 16, the clutch mechanism 40S is in the connected state, and the clutch mechanisms 40L and 40R are in the non-connected state. Yes. That is, the engagement piece 32Sa of the peripheral gear 32S does not press the operation part 40Sa of the clutch mechanism 40S, and the engagement pieces 32La, 32Ra of the peripheral gears 32L, 32R are operated by the operation parts 40La of the clutch mechanisms 40L, 40R. 40Ra is pressed.

  FIG. 7 shows a state in which the operation handle 110 is rotated and moved forward (clockwise) from the state of FIG. At this time, the switch cam 124 is rotated clockwise in FIG. 7 via the intermediate member 123, and the protrusion 60 operates the switch 71 to cause the motor 80 to rotate forward. As a result, the rotation of the motor 80 is transmitted to the slide adjusting mechanism 50S via the clutch mechanism 40S and the power transmission cable 51S, and the seat 1 is slid in either the front-rear direction, for example, forward.

  When the operation is released from the state where the operation handle 110 is rotated as shown in FIG. 7, the Oldham coupling returns to the state shown in FIG. 6 by the biasing force of the torsion coil spring 91 (see FIG. 4), and the operation handle 110 is returned to the reference position. Return.

  FIG. 8 shows a state in which the operation handle 110 is rotated from the state shown in FIG. 6 to the reverse side (counterclockwise). At this time, the switch cam 124 is rotated counterclockwise in FIG. 8 via the intermediate member 123, and the protrusion 60 operates the switch 72 to reversely rotate the motor 80. As a result, the rotation of the motor 80 is transmitted to the slide adjusting mechanism 50S via the clutch mechanism 40S and the power transmission cable 51S, and the seat 1 is slid in either the front-rear direction, for example, rearward.

  FIG. 9 shows a state in which the operation handle 110 is linearly moved forward from the state of FIG. At this time, as shown in FIGS. 17 and 18, the conversion gear 33 is swung via the rotation shaft 110a of the operation handle 110, and the center gear 31 is rotated clockwise in FIG. As a result, the clutch mechanism 40S is disconnected and the clutch mechanism 40L is connected. The clutch mechanism 40R continues to be disconnected. That is, the engagement piece 32Sa of the peripheral gear 32S presses the operation portion 40Sa of the clutch mechanism 40S, and the engagement piece 32La of the peripheral gear 32L releases the pressure of the operation portion 40La of the clutch mechanism 40L. The pressing of the operating portion 40Ra of the clutch mechanism 40R by the engagement piece 32Ra of the peripheral gear 32R is continued.

  FIG. 10 shows a state in which the operation handle 110 is rotated from the state of FIG. 9 to the forward rotation side (clockwise). At this time, the switch cam 124 is rotated clockwise in FIG. 10 via the intermediate member 123, and the protrusion 60 operates the switch 71 to cause the motor 80 to rotate forward. As a result, the rotation of the motor 80 is transmitted to the lifter adjustment mechanism 50L via the clutch mechanism 40L and the power transmission cable 51L, and moves the seat 1 in one of the vertical directions, for example, upward.

  As shown in FIG. 10, when the operation is released from the state in which the operation handle 110 is linearly moved forward and rotated forward, the center gear 31 and the peripheral gears 32S and 32L are urged by the urging force of the torsion coil spring 92. , 32R and the conversion gear 33 return to the states shown in FIGS. Further, the Oldham coupling returns to the state shown in FIG. 6 by the biasing force of the torsion coil spring 91, and the operation handle 110 returns to the reference position.

  FIG. 11 shows a state in which the operation handle 110 is linearly moved forward from the state of FIG. 6 and the operation handle 110 is further rotated to the reverse side (counterclockwise). At this time, as shown in FIGS. 17 and 18, with the clutch mechanism 40L in the connected state, as shown in FIG. 11, the projection 60 operates the switch 72, reverses the motor 80, and the seat 1 is moved in the vertical direction. Either, for example, moves downward.

  FIG. 12 shows a state where the operation handle 110 is linearly moved backward from the state of FIG. At this time, as shown in FIGS. 19 and 20, the conversion gear 33 is swung via the rotation shaft 110a of the operation handle 110, and the center gear 31 is rotated counterclockwise in FIG. As a result, the clutch mechanism 40S is disconnected and the clutch mechanism 40R is connected. The clutch mechanism 40L continues to be disconnected. That is, the engaging piece 32Sa of the peripheral gear 32S presses the operating portion 40Sa of the clutch mechanism 40S, and the engaging piece 32Ra of the peripheral gear 32R releases the pressing of the operating portion 40Ra of the clutch mechanism 40R. The pressing of the operating portion 40La of the clutch mechanism 40L by the engagement piece 32La of the peripheral gear 32L is continued.

  FIG. 13 shows a state in which the operation handle 110 is rotated from the state of FIG. 12 to the forward rotation side (clockwise). At this time, the switch cam 124 is rotated clockwise in FIG. 13 via the intermediate member 123, and the protrusion 60 operates the switch 71 to cause the motor 80 to rotate forward. As a result, the rotation of the motor 80 is transmitted to the reclining angle adjusting mechanism 50R via the clutch mechanism 40R and the power transmission cable 51R, and the seat back 2 moves in the front-rear direction relative to the seat cushion 3, for example, forward. .

  As shown in FIG. 13, when the operation is released from the state in which the operation handle 110 is linearly moved rearward and rotated forward, the center gear 31 and the peripheral gears 32S and 32L are urged by the urging force of the torsion coil spring 92. , 32R and the conversion gear 33 return to the states shown in FIGS. Further, the Oldham coupling returns to the state shown in FIG. 6 by the biasing force of the torsion coil spring 91, and the operation handle 110 returns to the reference position.

  FIG. 14 shows a state in which the operation handle 110 is linearly moved backward from the state of FIG. 6, and the operation handle 110 is further rotated in the reverse direction (counterclockwise). At this time, in the state where the clutch mechanism 40R is in the connected state as shown in FIGS. 19 and 20, as shown in FIG. 14, the projection 60 operates the switch 72, reverses the motor 80, and the seat back 2 is moved to the seat cushion. 3 moves in the front-rear direction, for example, backward.

  As described above, the operation handle 110 is in the non-operating state and at the reference position, and at that time, one clutch mechanism 40S is in the connected state. Therefore, when operating the slide adjustment mechanism 50S corresponding to the clutch mechanism 40S in the connected state at the reference position, the corresponding seat 1 can be slid by simply rotating the operation handle 110. As a result, the operation frequency of the clutch operation mechanism 30 is suppressed. In addition, since the operation handle 110 is always in the reference position in a non-operating state, the operation handle 110 is always operated from the reference position, and it is not necessary to check the operation position of the operation handle 110 at the start of the operation. .

  Generally, the slide adjustment mechanism 50S has the highest adjustment frequency among the slide adjustment mechanism 50S, the lifter adjustment mechanism 50L, and the reclining angle adjustment mechanism 50R. In the first embodiment, the clutch mechanism 40S of the slide adjustment mechanism 50S having a high adjustment frequency is in a connected state at the reference position of the operation handle 110. Therefore, the effect of suppressing the operation frequency of the clutch operation mechanism 30 is further enhanced.

  Further, the selective connection of the clutch mechanisms 40S, 40L, and 40R and the operation of the switch 70 are performed by the operating force transmission mechanism 120 including the Oldham coupling and the clutch operating mechanism 30 according to the moving direction of one operating handle 110. Therefore, the clutch operation and the switch operation can be performed without changing the operation handle 110. In addition, since the operation handle 110 is integrated for the clutch and the switch, the space occupied by the operation handle 110 can be reduced. Further, since the operation handle 110 is distinguished from the clutch and the switch depending on the way of movement, the operation space is compared with the case where the clutch and the switch are distinguished by the operation stroke in the same movement operation. (Operation stroke) can be reduced.

  In addition, since the switch 70 is fixed to the switch cover 121 that is a fixed member, it is possible to prevent the wiring (not shown) connected to the switch 70 from moving as the operation handle 110 is operated. Thereby, the possibility of poor connection of wiring to the switch 70 can be suppressed.

  The clutch operating mechanism 30 for operating the clutch mechanisms 40S, 40L, 40R in response to the operating force of the operating handle 110 is composed of one center gear 31 and peripheral gears 32S, 32L, 32R. Therefore, each clutch mechanism 40S, 40L, 40R can be operated via one center gear 31, and the configuration is simplified compared to a case where each clutch mechanism 40S, 40L, 40R is operated by an individual member. In addition, the operating force of the operating handle can be reduced.

  In addition, the clutch mechanism 40L or 40R is in a connected state on both sides of the reference position of the operation handle 110, respectively. For this reason, it is possible to easily understand the operations for adjusting the positions of the total three movable sheet portions.

  Further, when the operation handle 110 is in the reference position or other operation position and any of the clutch mechanisms 40S, 40L, 40R is in the connected state by the operation restriction mechanism by chamfering the rotating shaft 110a of the operation handle 110. The operation handle 110 can be rotated. However, when the operation handle 110 is being operated and the clutch mechanisms 40S, 40L, 40R are in the middle of switching between the connected state and the disconnected state, the operation handle 110 is prevented from rotating. Therefore, it is possible to prevent a problem that the switch 80 is switched during the switching of the clutch mechanism between the connected state and the non-connected state, and the motor 80 is operated.

  FIG. 21 shows a second embodiment of the present invention. The feature of the second embodiment over the first embodiment is that the operation force transmission mechanism 120 in the first embodiment is replaced with the operation force transmission mechanism 220 in the second embodiment. The other configurations are the same, and the repetitive description of the same parts is omitted.

  As shown in FIG. 21, the gear cover 222 has a structure similar to that of the gear cover 122 in the first embodiment, except that guide pins 222a protrude rightward on both front and rear sides of the guide groove 222b. It is a point.

  Each guide pin 222 a is fitted into a pair of front and rear guide grooves 223 a of the switch base 223, so that the switch base 223 can move in the front-rear direction on the right side surface of the gear cover 222. The switch base 223 is formed by a plate body in which a portion for forming the guide groove 223a protrudes in an arm shape on both front and rear sides. Between the pair of front and rear guide grooves 223a, an opening 223b through which a rotation shaft 210a of the operation handle 210 described later is formed is formed, and a pair of switches 71 and 72 are provided below the pair of front and rear guide grooves 223a. Are fixed on the right side of the plate.

  On the right side surface of the gear cover 222, the switch cover 221 is put and fixed with the switch base 223 interposed therebetween. An operation handle 210 is provided on the right side surface of the switch cover 221. The operation handle 210 has a rotating shaft 210 a that is disposed through the openings 221 a and 223 b of the switch cover 221 and the switch base 223 and the guide groove 222 b of the gear cover 222 and is fitted to the engaging portion 33 b of the conversion gear 33. Has been fixed. The opening 221a of the switch cover 221 is formed long in the front-rear direction so that the operation handle 210 can be moved back and forth. On the other hand, the opening 223b of the switch base 223 is sized so that the rotation shaft 210a of the operation handle 210 is just fitted so that the switch base 223 also moves back and forth following the back and forth movement of the operation handle 210.

  As shown in FIG. 22, on the left side surface of the operation handle 210, a rotation shaft 210a is provided at the center so as to protrude to the left side, and a cam 210b is formed around the rotation shaft 210a. The rotary shaft 210a is chamfered in the same manner as the rotary shaft 110a of the operation handle 110 in the first embodiment. The cam 210b is formed so as to operate the switches 71 and 72. When the operation handle 210 is in a non-operation state, neither of the switches 71 and 72 is operated, and the operation handle 210 is on the forward rotation side. The switch 71 is operated when it is rotated and the switch 72 is operated when it is rotated to the reverse side.

  A torsion coil spring 93 is provided between the operation handle 210 and the switch base 223, and the torsion coil spring 93 generates a biasing force when the operation handle 210 is rotated with respect to the switch base 223. The rotational position of the operation handle 210 is always returned to the reference position. The torsion coil spring 92 is provided in the same manner as in the first embodiment, and the torsion coil springs 92 and 93 correspond to the return means 90 described with reference to FIG.

  FIG. 23 shows a non-operation state in which the operation handle 210 is neither linearly moved nor rotated. At this time, the operation handle 210 is at the reference position, and neither of the switches 71 and 72 is operated. In the clutch operation mechanism 30 similar to the first embodiment, as shown in FIGS. 15 and 16, the clutch mechanism 40S is in a connected state, and the clutch mechanisms 40L and 40R are in a disconnected state.

  FIG. 24 shows a state in which the operation handle 210 is rotated from the state of FIG. 23 to the forward rotation side (clockwise). At this time, the cam 210b operates the switch 71 to cause the motor 80 to rotate forward. As a result, the rotation of the motor 80 is transmitted to the slide adjusting mechanism 50S via the clutch mechanism 40S and the power transmission cable 51S, and the seat 1 is slid in either the front-rear direction, for example, forward.

  FIG. 25 shows a state in which the operation handle 210 is rotated from the state shown in FIG. 23 to the reverse side (counterclockwise). At this time, the cam 210b operates the switch 72 to reversely rotate the motor 80. As a result, the rotation of the motor 80 is transmitted to the slide adjusting mechanism 50S via the clutch mechanism 40S and the power transmission cable 51S, and the seat 1 is slid in either the front-rear direction, for example, rearward.

  FIG. 26 shows a state in which the operation handle 210 is linearly moved forward from the state of FIG. At this time, as shown in FIGS. 17 and 18, the conversion gear 33 is swung via the rotation shaft 210a of the operation handle 210, and the center gear 31 is rotated clockwise in FIG. As a result, the clutch mechanism 40S is disconnected and the clutch mechanism 40L is connected. The clutch mechanism 40R continues to be disconnected.

  As shown in FIG. 26, the switch base 223 is also moved linearly together with the rotating shaft 210a of the operation handle 210. In this state, when the operation handle 210 is rotated and moved forward (clockwise) or reverse (counterclockwise), the motor 80 is rotated as described with reference to FIGS. The rotation of the motor 80 is transmitted to the lifter adjustment mechanism 50L via the clutch mechanism 40L and the power transmission cable 51L, and moves the seat 1 upward or downward.

  FIG. 27 shows a state in which the operation handle 210 is linearly moved backward from the state of FIG. At this time, as shown in FIGS. 19 and 20, the conversion gear 33 is swung via the rotation shaft 210a of the operation handle 210, and the center gear 31 is rotated counterclockwise in FIG. As a result, the clutch mechanism 40S is disconnected and the clutch mechanism 40R is connected. The clutch mechanism 40L continues to be disconnected.

  As shown in FIG. 27, the switch base 223 is also moved linearly together with the rotating shaft 210a of the operation handle 210. In this state, when the operation handle 210 is rotated and moved forward (clockwise) or reverse (counterclockwise), the motor 80 is rotated as described with reference to FIGS. The rotation of the motor 80 is transmitted to the reclining angle adjusting mechanism 50R via the clutch mechanism 40R and the power transmission cable 51R, and moves the seat back 2 forward or backward with respect to the seat cushion 3.

  Also in the second embodiment, it is possible to achieve the same effect as the first embodiment. Further, the operation force transmission mechanism 220 in the second embodiment can reduce the number of parts compared to the operation force transmission mechanism 120 in the first embodiment. Furthermore, in the second embodiment, since the Oldham coupling in the first embodiment is not used, the operation force of the operation handle 210 can be reduced.

  As mentioned above, although specific embodiment was described, this invention is not limited to those external appearances and structures, A various change, addition, and deletion are possible in the range which does not change the summary of this invention. For example, in the above embodiment, the plurality of position adjustment mechanisms are the slide adjustment mechanism 50S, the lifter adjustment mechanism 50L, and the reclining angle adjustment mechanism 50R. However, the present invention is not limited to such a configuration. That is, at least a part of the plurality of position adjustment mechanisms may be replaced with another position adjustment mechanism. Alternatively, another position adjustment mechanism may be added.

  In the above embodiment, the present invention is applied to a vehicle seat, but may be applied to a seat mounted on an airplane, a ship, a train, or the like. Further, the present invention may be applied to a seat installed indoors like a movie theater seat.

1 Vehicle front seat (seat)
2 Seat back 3 Seat cushion 4 Headrest 5 Rear link 6 Rear link 7 Lower rail 8 Upper rail 9 Side shield 110, 210 Operation handle 110a, 210a Rotating shaft 110b Key 210b Cam 120, 220 Operation force transmission mechanism 121, 221 Switch cover 121a, 221a Opening 122, 222 Gear cover 122a Fixed gear (conversion mechanism)
222a Guide pins 122b, 222b Guide groove 123 Intermediate members 123a, 123b Groove 123c Opening 124 Switch cam (Rotating body)
124a Opening 124b Key 223 Switch base 223a Guide groove 223b Opening 30 Clutch operating mechanism 31 Center gear (conversion mechanism)
31a Gear part 31b Engagement part 32S, 32L, 32R Peripheral gear 32Sa, 32La, 32Ra Engagement piece 33 Conversion gear (conversion mechanism)
33a Gear part 33b Engaging part 34 Clutch cases 34a, 34b Clutch case halves 40S, 40L, 40R Clutch mechanisms 40Sa, 40La, 40Ra Operation parts 41S, 41L, 41R Slide adjustment mechanism 50L Lifter adjustment mechanism 50R Reclining angle adjustment mechanism 51S, 51L, 51R Power transmission cable 60 Protrusion (switch operation mechanism)
70, 71, 72 Switch 80 Motor 90 Return means 91, 92, 93 Torsion coil spring 100 Driving device

Claims (9)

A motor having a single output shaft;
A plurality of position adjusting mechanisms for receiving the output of the motor and adjusting the positions of the plurality of sheet movable parts;
A plurality of clutch mechanisms which are arranged corresponding to the plurality of position adjusting mechanisms and individually selectively connect an output shaft to each of the plurality of position adjusting mechanisms and an input shaft which is rotationally driven by the motor; ,
A switch for switching the motor to an energized state or a non-energized state;
An operation handle that is operated when adjusting the positions of the plurality of seat movable parts;
A clutch operation mechanism that receives an operation force for the clutch of the operation handle and switches each of the plurality of clutch mechanisms to a connected state or a non-connected state;
A switch operating mechanism that receives an operation force for the switch of the operation handle and switches the switch.
The operation handle passes through a reference position which is one of the operation positions for both the clutch and the switch, and can be operated to other operation positions, and always returns to the reference position in the operation release state. A return means for energizing
In the reference position, the clutch operation mechanism is a seat drive in which one of the plurality of clutch mechanisms is in a connected state, the other clutch mechanism is in a non-connected state, and the switch operating mechanism is in a non-energized state. apparatus. A motor having a single output shaft;
A plurality of position adjusting mechanisms for receiving the output of the motor and adjusting the positions of the plurality of sheet movable parts;
A plurality of clutch mechanisms which are arranged corresponding to the plurality of position adjusting mechanisms and individually selectively connect an output shaft to each of the plurality of position adjusting mechanisms and an input shaft which is rotationally driven by the motor; ,
A switch for switching the motor to an energized state or a non-energized state;
An operation handle that is operated when adjusting the positions of the plurality of seat movable parts;
A clutch operating mechanism that receives an operating force of either one of linear movement and rotational movement of the operating handle and switches each of the plurality of clutch mechanisms to a connected state or a non-connected state;
A switch operating mechanism that receives the operation force of the other of the linear movement and the rotational movement of the operation handle and switches the switch.
The operation handle passes through a reference position which is one of the operation positions in both linear movement and rotational movement, and can be operated to other operation positions, and always returns to the reference position in the operation released state. A return means for energizing
In the reference position, the clutch operation mechanism is a seat drive in which one of the plurality of clutch mechanisms is in a connected state, the other clutch mechanism is in a non-connected state, and the switch operating mechanism is in a non-energized state. apparatus. In claim 1 or 2,
The clutch mechanism that is in a connected state at the reference position corresponds to a position adjustment mechanism that adjusts a front / rear slide position of the seat among the plurality of seat movable portions. In any one of Claims 1-3,
The clutch operation mechanism is configured to switch each of the plurality of clutch mechanisms to a connected state or a non-connected state in response to an operation force of linear movement of the operation handle,
The switch operation mechanism is configured to switch and operate the switch in response to the operation force of the rotational movement of the operation handle,
A seat driving device including an operation force transmission mechanism for transmitting an operation force for linear movement of the operation handle to the clutch operation mechanism and for transmitting an operation force for rotational movement of the operation handle to the switch operation mechanism. In claim 4,
The operating force transmission mechanism includes an Oldham coupling,
The switch operation mechanism includes a rotating body that is rotated in response to an operation force of the rotational movement of the operation handle in the Oldham joint and switches the switch.
The seat drive device is configured such that a rotation shaft of the operation handle passes through the rotating body and transmits an operation force for linear movement of the operation handle to the clutch operation mechanism. In any one of Claims 1-5,
The clutch operating mechanism is
A center gear that rotates in response to an operation force of the operation handle;
A plurality of peripheral gears that mesh with the center gear and rotate,
The plurality of peripheral gears are combined with the plurality of clutch mechanisms, respectively, and are rotated to selectively connect the plurality of clutch mechanisms. In claim 6,
The clutch operation mechanism is configured to switch each of the plurality of clutch mechanisms to a connected state or a non-connected state in response to an operation force of linear movement of the operation handle,
The switch operation mechanism is configured to switch and operate the switch in response to the operation force of the rotational movement of the operation handle,
A seat driving device including a conversion mechanism that receives an operation force of linear movement of the operation handle, converts the operation handle into a rotational motion, and transmits the rotation to the center gear. In any one of Claims 1-7,
There are three seat moving parts, and correspondingly, the position adjusting mechanism and the clutch mechanism are provided in three sets,
Of the three clutch mechanisms, one clutch mechanism is in a connected state at the reference position, and the other two clutch mechanisms are in a connected state at both sides of the reference position in the operation of moving the operation handle. Sheet drive device. In claim 4 or 5,
In a state where the operation handle is in the reference position, and in a state where the operation handle is in a position other than the reference position and a clutch mechanism other than the clutch mechanism corresponding to the reference position is in a connected state, the operation A seat driving device comprising an operation restricting mechanism that enables rotational movement of the handle and prevents rotational movement of the operation handle in a state other than those positions.

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